multiple-chiller-system-design-and-control-trane-applications-engineering-manual.pdf

Applications
Engineering
Manual
Multiple-Chiller-System
Design and Control
SYS-APM001-EN (March 2001)

Multiple-Chiller-System
Design and Control
Mick Schwedler, applications engineer
Ann Yates, information designer

Preface
The Trane Company, in proposing these system design and application
concepts, assumes no responsibility for the performance or desirability of any
resulting system design. System design is the prerogative and responsibility of
the system designer.
© 2001 American Standard Inc. All rights reserved
SYS-APM001-EN
This manual examines chilled-water-system components, configurations,
options, and control strategies. The goal is to provide system designers with
options they can use to satisfy the building owners’ desires, but this manual is
not intended to be a complete chiller-system design manual.
System designers may get the most use from this manual by familiarizing
themselves with chilled-water-system basics and understanding the benefits of
various options. Thereafter, when a specific job will benefit from these
advantages, consult appropriate sections of the manual in detail.
The Engineers Newsletters that are referenced in this manual are available at:
www.trane.com/commercial/library/newsletters.asp

SYS-APM001-EN iii
Contents
Introduction ...........................................................................................1
Chilled-Water-Plant Basics ...............................................................2
Chiller...........................................................................................................2
Loads ...........................................................................................................5
Chilled-water distribution system .............................................................7
Condenser-water system .........................................................................10
Controls ....................................................................................................11
Chilled-Water-System Options .....................................................13
Chilled- and condenser-water temperatures .........................................13
Chilled- and condenser-water flow rates ...............................................15
Misconceptions about low-flow rates .....................................................24
System Configurations ....................................................................27
Parallel chillers .........................................................................................27
Series chillers ...........................................................................................29
Primary–secondary (decoupled) systems ..............................................31
Pumping Arrangements...................................................................36
Flow-based control ...................................................................................38
Chiller sequencing ...................................................................................39
Variable-Primary-Flow Systems ...................................................40
VPF advantages ........................................................................................41
VPF caveats ..............................................................................................41
Chiller sequencing ...................................................................................43
Chilled-Water-Control Options .................................................... 47
Chilled-water reset—raising and lowering.............................................47
Critical valve reset ....................................................................................48
Design Considerations ....................................................................49
Chilled-water pump configurations.........................................................49
Bypass line sizing......................................................................................50
Amount of fluid in the loop......................................................................50
Plant expansion.........................................................................................51

SYS-APM001-EN
Contents
iv
Chilled-Water- System Variations ................................................54
Heat recovery ...........................................................................................54
Preferential loading .................................................................................54
Unequal chiller sizing ..............................................................................58
Series-counterflow application................................................................58
Applications outside the chiller’s range .................................................60
Chilled-Water-System Issues ........................................................63
Low ∆T syndrome .....................................................................................63
Check valve in the bypass line.................................................................63
Failure recovery ........................................................................................64
Alternative energy sources ......................................................................64
Contingency .............................................................................................66
Condenser-System Variations ......................................................69
Condenser flow configurations ..............................................................69
Cooling-tower-fan control methods .......................................................71
Plate-and-frame heat exchanger .............................................................72
Well, river, or lake water ..........................................................................72
Condenser-water temperature control ...................................................72
Condenser-water pump options ..............................................................73
Retrofit opportunities ...............................................................................75
Conclusion ............................................................................................78
Glossary .................................................................................................79
References ............................................................................................82
Index ........................................................................................................85

Contents
SYS-APM001-EN v
Figures
Figure 1 Typical vapor-compression chiller ....................................... 2
Figure 2 Valve-controlled loads .......................................................... 6
Figure 3 Uncontrolled coil................................................................... 7
Figure 4 Simplified distribution system............................................. 9
Figure 5 Chilled-water-system performance at part load ................. 19
Figure 6 Annual system operating costs ........................................... 23
Figure 7 System energy comparison (no pipe)................................. 25
Figure 8 Parallel chillers with single, common pump....................... 27
Figure 9 Parallel chillers with separate, dedicated chiller pumps.... 28
Figure 10 Series chillers ........................................................................ 29
Figure 11 Decoupled arrangement....................................................... 31
Figure 12 Production loop..................................................................... 33
Figure 13 Distribution loop ................................................................... 34
Figure 14 Campus pumping arrangement........................................... 36
Figure 15 Tertiary pumping arrangement............................................ 37
Figure 16 Decoupled system supply tee.............................................. 37
Figure 17 Temperature-sensing............................................................ 38
Figure 18 Variable-primary-flow system.............................................. 40
Figure 19 Double-ended decoupled system........................................ 53
Figure 20 Parallel preferential loading arrangement .......................... 55
Figure 21 Sidestream preferential loading arrangement ................... 56
Figure 22 Plate-and-frame heat exchanger.......................................... 57
Figure 23 Series-counterflow arrangement......................................... 59
Figure 23a Equal lift concept................................................................... 59
Figure 24 Flow rate out of range for equipment ................................. 60
Figure 25 Temperatures out of range for equipment.......................... 61
Figure 26 Precise temperature control, multiple chillers.................... 62
Figure 27 Failure recovery..................................................................... 64
Figure 28 Manifolded condenser-water pumps................................... 69
Figure 29 Chiller-tower energy consumption ..................................... 73
Figure 30 Decoupled condenser-water system ................................... 74
Figure 31 Chiller-tower selection with different chiller capacities ..... 76

SYS-APM001-EN
Contents
vi
Tables
Table 1 Recommended chiller-monitoring points per
ASHRAE Guideline 3-1996 ...................................................11
Table 2 Standard rating conditions for absorption chillers.............15
Table 3 Standard rating conditions for chilled-water systems .......16
Table 4 Low-flow conditions for chilled-water pump ......................17
Table 5 Low-flow conditions for cooling tower................................17
Table 6 Low-flow conditions for condenser-water pump................17
Table 7 Total system power ...............................................................18
Table 8 Effect of decreased water temperature................................20
Table 9 Retrofit capacity changes......................................................21
Table 10 Reduced flow-rate effect .......................................................24
Table 11 Flow-rate-fluctuation examples............................................44

SYS-APM001-EN 1
Introduction
Many building owners continually search for solutions that allow their
businesses to offer higher quality, and to be more competitive and profitable.
HVAC systems designers often use chilled-water systems to provide high-
quality, cost-effective air conditioning for building owners. With the advent of
more flexible chillers, system-level controls, and software analysis tools, the
number of chilled-water-systems options has exploded.

SYS-APM001-EN
2
Chilled-Water-Plant Basics
Chilled-water plants consist of these functional parts:
n Chillers that produce chilled water
n Loads, often satisfied by coils, that transfer heat from air to water
n Chilled-water distribution pumps and pipes that send chilled water to the
previously mentioned loads
n Condenser-water pumps, pipes, and cooling towers that reject heat
(for water-cooled chillers)
n Controls that coordinate the operation of the mechanical components
together as a system
Chiller
There are a variety of water chiller types. Most commonly, they are absorption,
centrifugal, helical rotary, and scroll. Some reciprocating chillers are also
available. Chillers can be either air- or water-cooled. Major vapor-compression
chiller components include an evaporator, a compressor(s), a condenser, and
an expansion device(s). This manual discusses the chiller’s evaporator and
condenser and their relationship to the chilled-water plant.
Figure 1 Typical vapor-compression chiller
Condenser
Evaporator
Compressor

SYS-APM001-EN 3
Evaporator
The evaporator section of a water chiller is a shell-and-tube, refrigerant-to-
water heat exchanger. Depending on the chiller's design, either the refrigerant
or the water is contained within the tubes.
n In a flooded shell-and-tube evaporator, cool, liquid refrigerant at low-
pressure enters the distribution system inside the shell and moves
uniformly over the tubes, absorbing heat from warmer water that flows
through the tubes.
n In a direct-expansion (DX) shell-and-tube evaporator, warmer water fills the
shell while the cool, lower-pressure liquid refrigerant flows through the
tubes.
In either design, there is an approach temperature, which is the temperature
difference between the refrigerant and exit water stream. The approach
temperature is a measure of the heat transfer efficiency of the evaporator.
Effect of chilled-water temperature
For a given chiller, as the leaving chilled-water temperature drops, the
refrigerant temperature and pressure must also drop. Conversely, as the
leaving chilled-water temperature rises, so do the refrigerant temperature and
pressure. When the leaving chilled-water temperature changes, the work a
compressor must do also changes. The effect of leaving chilled-water
temperature change on power consumption can be 1.0 percent to 2.2 percent
per degree fahrenheit [1.8 percent to 4.0 percent per degree celsius]. Always
consider the energy consumption of the entire system—not only the chiller. It is
important to remember that although reducing leaving chilled-water
temperature penalizes the chiller, it may benefit the pumps because less water
is pumped through the system. System interactions are covered in more detail
in the next section Chilled-Water-System Options.
Effect of chilled-water flow rate
Since the evaporator is a heat exchanger, it is sensitive to water flow rate.
Excessive flow may result in high water velocity, erosion, vibration, or noise.
Insufficient flow reduces heat-transfer efficiency and causes poor chiller
performance. Some designers have concerns over low flow rates causing
fouling. Generally, as Webb and Li3
noted, these concerns are unwarranted
since the chilled-water loop is a closed system, thus reducing the chances of
materials entering the system and causing fouling. Chilled-water flow through
the chiller must be kept within specific minimum and maximum limits. Contact
the manufacturer for these limits.

SYS-APM001-EN
4
Some chiller controls can accommodate very little flow variation during
machine operation.
2
Other, more sophisticated, chiller controls allow some
flow variation. Some chillers can tolerate flow-rate variations of as much as 30
percent per minute or greater, while others can only tolerate up to 2 percent per
minute. It is important that chiller capabilities are matched to system
requirements. Contact the chiller manufacturer to determine allowable rate of
flow variation before varying the flow through the evaporator in a chiller. Flow
variation is discussed in detail in the section Variable-Primary-Flow Systems,
page 40.
Water-cooled condenser
To cool a building or process, the transferred heat must ultimately be rejected.
The total amount of heat rejected includes the sum total of the evaporator load,
the compressor work, and the motor inefficiency. In a hermetic chiller, where
the motor and compressor are in the same housing, these loads are all rejected
through the condenser. In an open chiller, where the motor is separate from the
compressor and connected by a shaft, the motor heat is rejected directly to the
surrounding air. The evaporator load and the compressor work are rejected
through the condenser and the motor heat must be taken care of by the air-
conditioning system.
Effect of condenser-water temperature
For a given chiller, as the leaving condenser-water temperature rises,
refrigerant temperature and pressure also rise. Conversely, as leaving
condenser-water temperature drops, so do refrigerant temperature and
pressure. As the refrigerant pressure and temperature changes, the work a
compressor must do also changes. The effect of leaving-condenser-water
temperature change on power consumption can be 1.0 percent to 2.2 percent
per degree fahrenheit [1.8 percent to 4.0 per degree celsius]. Always consider
the energy consumption of the entire system—not just the chiller. It is
important to remember that although raising the leaving condenser-water
temperature penalizes the chiller, it may benefit the pumps and cooling tower
through the use of reduced flow rates and higher thermal driving-forces on the
tower. System interactions are covered in more detail in the section Condenser-
System Variations, page 69.
Effect of condenser-water flow rate
Since the condenser is a heat exchanger, it is sensitive to water flow rate. For
example, excessive flow may result in high water velocity, erosion, vibration, or
noise, while insufficient flow reduces heat transfer efficiency and causes poor
chiller performance. Therefore, condenser-water flow through the chiller should
be kept within a specific range of limits, except during transient startup

SYS-APM001-EN 5
conditions. Contact the manufacturer for these limits. Some chillers may allow
extended operation below the selected flow rates.
If water velocity through the condenser tubes is too low for significant periods
of time and the water is extremely hard, long-term fouling of the tubes may
also occur. Webb and Li
3
tested a number of internally-enhanced condenser
tubes at low velocity (3.51 ft/s [1.07 m/s]) and high water hardness. While they
found that some of the internally-enhanced tubes fouled, in the long term they
concluded:
Because of the high hardness and low water velocity used in these
tests, we do not believe that the fouling experienced is typical of that
expected in commercial installations. With use of good maintenance
practices and water quality control, all of the tubes tested are probably
suitable for long-term-fouling applications.
It is important to remember that a chiller selected for low flow (as discussed in
the next section Chilled-Water-System Options) does not necessarily have low
velocity through its tubes. If tube fouling is a major concern, consider the use of
smooth, rather than internally-enhanced, tubes in the condenser for ease of
cleaning.
Air-cooled condenser
Obviously, air-cooled chillers do not use condenser-water, since they reject their
heat by having ambient air passed across refrigerant-to-air heat exchangers. In
packaged air-cooled chillers, the manufacturers attempt to provide optimal
performance by staging fans in response to chiller load and ambient, dry-bulb
temperature.
Loads
In comfort-cooling applications, loads are usually satisfied by air handlers
equipped with coils to transfer heat from conditioned space air to circulating
chilled-water. Air is thus cooled and dehumidified as it passes across the finned
surface of the cooling coils. Since the psychrometric process of conditioning air
takes place at the coils, selection of the optimum coil size and type from the
wide variety available is important for proper system performance.

SYS-APM001-EN
6
Some specialized process loads do not involve cooling air. Instead, they may
involve heat transfer directly within a piece of process equipment, such as the
cooling jacket of an injection-molding machine. Heat transferred from the loads
can be controlled in a number of ways:
n Three-way valve
n Two-way valve
n Variable-speed pump
n Uncontrolled coils
Three-way valve load control
A three-way control valve regulates the amount of water passing through a coil
in response to loads. The valve bypasses unused water around the coil and
requires a constant flow of water in the system, regardless of load. A drawback
of this bypass is that the temperature of the water leaving the three-way valve
is reduced at part-load conditions. This can be a major cause of so-called “low
∆T syndrome” discussed on page 63 in the section Chilled-Water-System
Issues. Three-way valves are used in many existing systems.
Figure 2 Valve-controlled loads
Two-way valve load control
A two-way, water modulating valve at the coil performs the same water
throttling function as the three-way valve. The coil sees no difference between
these two methods. The chilled-water system, however, sees a great difference.
In the case of the two-way valve, all flow in the coil circuit is throttled. No water
is bypassed. Consequently, a system using two-way valves is a variable-flow
chilled-water system. The temperature of the water leaving the coil is not
diluted by bypass water so at part-load conditions, the system return-water
temperature is higher than with three-way valve control.
Three-Way Valve Two-Way Valve
Cooled Air Cooled Air

SYS-APM001-EN 7
Variable-speed pumping load control
By using a pump for each coil, the flow may be controlled by varying the pump
speed. In such systems, there may be no control valves at the coil. This can
reduce both the valve and the valve installation costs.
Uncontrolled coils
Figure 3 shows a control variation using an uncontrolled or “wild”coil. In this
system, control of the conditioned air supply is executed by face-and-bypass
dampers that permit a portion of the air to bypass the coil surface. Advantages
of the strategy are the elimination of control valves and improved part-load
dehumidification. A disadvantage is that all the water is pumped all the time;
however, in systems with very small water pressure drops, this system
arrangement may work economically.
Figure 3 Uncontrolled coil
Chilled-water distribution system
Chilled water is circulated through fixed piping—most commonly steel, copper,
or plastic—that connects the chiller with various load terminals. Piping is sized
to meet a project’s pressure loss, water velocity, and construction cost
parameters. Pressure drop is overcome by the use of a chilled-water pump.
Cooled Air Mixture
Bypass Damper
Face Damper
Air Handler

SYS-APM001-EN
8
Chilled-water pump
The purpose of the chilled-water pump is to circulate chilled water within the
loop. Generally, the pump must overcome the frictional pressure losses caused
by the piping, coils, and chiller and the pressure differential across open control
valves in the system. The pump, while working at the system static pressure,
does not need to overcome this static pressure. For example, in a forty-story
building the pump need not overcome the static pressure due to those forty
stories.
The pump is typically located upstream of the chiller, however it may be
anywhere in the system, provided that the pump:
n meets the minimum pump net positive suction-head requirements. That is,
the system pressure at the pump inlet must be both positive and high
enough to allow the pump to operate properly;
n maintains the minimum dynamic pressure head at critical system
components (usually the chiller). If the dynamic pressure head is not high
enough at these components, proper flow will not be established through
them;
n accommodates the total pressure (static head plus dynamic head) on
system components such as the chiller’s evaporator, valves, etc.
Note that the pump heat is added to the water and must be absorbed by the
chiller. Generally, this represents a very small temperature increase.
Multiple pumps are often used for redundancy. Depending on the terminal
control devices and system configurations, the chilled-water pumps may be
either constant or variable-flow.

SYS-APM001-EN 9
Distribution piping
By itself, the distribution system is easy to understand. Figure 4 shows a
simplified distribution system consisting of multiple cooling coils, each
controlled by a thermostat that regulates the flow in its respective coil. The
valves may be either three-way or two-way. As previously discussed, three-way
valves require constant water flow, while two-way valves allow the water flow
in the system to vary. As flow varies, the pump may simply ride its curve or use
a method of flow control such as a variable-speed drive. See the section System
Configurations, on page 27, for a detailed discussion of distribution-system
options.
Figure 4 Simplified distribution system
The distribution system may contain other components, such as an expansion
tank, control valves, balancing valves, check valves, and an air separator, to
name a few. The density, and therefore the volume, of the water in a “closed”
chilled-water distribution system varies as it undergoes changes in
temperature. The expansion tank allows for this expansion and contraction of
water volume.
Pump
Loads
Distribution
Piping
Chiller
Expansion
Tank
2000 ASHRAE HVAC Systems and
Equipment Handbook, Chapter 12,
Hydronic Heating and Cooling System
Design
1
contains additional reference
information on the components of a
chilled water distribution system.

SYS-APM001-EN
10
Condenser-water system
As in chilled-water distribution systems, condenser-water system piping—most
commonly steel, copper, or plastic—is sized to meet a project’s operating
pressure, pressure loss, water velocity, and construction cost parameters.
Pressure drop through piping and the chiller’s condenser, plus the cooling-
tower static lift, is overcome by use of a condenser-water pump.
Cooling tower
To reject heat, water is passed through a cooling tower where a portion of it
evaporates, thus cooling the remaining water. A particular cooling tower’s
effectiveness at transferring heat depends on water flow rate, water
temperature, and ambient wet bulb. The temperature difference between the
water entering and leaving the cooling tower is the range. The temperature
difference between the leaving water temperature and the entering wet-bulb
temperature is the approach.
Effect of load
As the building load—or heat rejection—decreases, range and approach also
decrease. This means that when the building is at part load, the cooling tower
can provide colder water at the same ambient wet-bulb temperature.
Effect of ambient conditions
As ambient wet-bulb temperature drops, the approach—at a constant load—
increases. This must be considered when cooling-tower-control strategies are
developed. Detailed descriptions of these conditions appear in the subsection,
Chiller-tower energy balance, page 72. For additional information, refer to 2000
ASHRAE HVAC Systems and Equipment Handbook, Chapter 36, “Cooling
Towers.”
1

SYS-APM001-EN 11
Controls
The chilled-water supply temperature is usually controlled at the chiller. Most
commonly, supply water temperature is used as the sensed variable to permit
control of chiller capacity to meet system load demand. Supply-temperature
control strategies may be used on either constant- or variable-flow systems. As
previously discussed, flow control is executed at the load terminals using three-
way or two-way valves, or separate pumps for each coil.
Control capabilities run the gamut from slow-acting pneumatic controls, to
electromechanical controls, to sophisticated digital controls that use algorithms
tuned to give superior performance.
Chiller control
Today’s chiller controls are capable of doing more than simply turning the
chiller on and off. At a minimum, these controls should monitor:
n Safety points such as bearing temperatures and electrical points that, when
out of range, may cause motor failure.
n Data points that may cause operational problems if corrective action is not
taken. An example is low chilled-water or refrigerant temperature, which
may result in freezing in or around the evaporator tubes.
n General points that should be logged daily to ensure proper chiller
performance.
Table 1 lists the ASHRAE-recommended monitoring points.
Table 1 Recommended chiller-monitoring points per ASHRAE Guideline 3-1996
Chilled
Water
Flow
Condenser
Water
Flow
Inlet Pressure Inlet Pressure
Inlet Temperature Inlet Temperature
Outlet Pressure Outlet Pressure
Outlet Temperature Outlet Temperature
Evaporator
Approach Temperature
Condenser
Approach Temperature
Refrigerant Pressure Refrigerant Pressure
Refrigerant Temperature Refrigerant Temperature
Oil
Level
Refrigerant
Level
Pressure Compressor Discharge Temperature
Temperature Additional Required
Additional Required Vibration Levels

SYS-APM001-EN
12
In addition to monitoring data, it is vital that the chiller controls alert operators
to possible problems. Diagnostic messages are necessary for the operator to
respond to safety issues and data points that are outside normal operating
ranges.
While communicating these diagnostic messages is a requirement, some chiller
controls include factory-installed programming that responds to the diagnostic
messages. For example, when the chilled-water temperature nears freezing, the
chiller sends a diagnostic message and adapts its operation by reducing the
compressor capacity, raising the chilled-water temperature to a safer condition.
Finally, the chiller controls should communicate with a system-level controller.
There are many system aspects that are outside the chiller’s direct control, such
as condenser-water temperature and the amount of fluid flowing through the
evaporator and condenser. To minimize the system energy costs, the system
controls must coordinate chiller, pump, cooling-tower, and terminal-unit
controls. This can only be done if adequate information is communicated from
each system component to the system-level controls.
Pump control
In so-called constant flow systems, the pumps are either on or off, providing
relatively constant flow when in the on position. In practice, some flow
variation will occur as system pressure drop changes. In a variable-flow system,
pump control is most often performed by maintaining a pressure differential at
a selected point in the system. For example, a variable-speed drive will increase
its speed if the sensed pressure differential is too low, or slow down if the
pressure differential is too high. The control point is selected to minimize over-
pressuring the system and to assure adequate flow at all critical loads. Optimal
pumping control strategies are addressed in Critical valve reset, page 48.
Chapter references
1 2000 ASHRAE HVAC Systems and Equipment Handbook, Chapter 12,
Hydronic Heating and Cooling System Design and Chapter 36, Cooling
Towers, American Society of Heating, Refrigeration and Air-Conditioning
Engineers.
2 Schwedler, M., PE and Bradley, B.; “An Idea for Chilled-Water Plants Whose
Time Has Come...Variable-Primary-Flow Systems,” Engineers Newsletter,
Volume 28, No. 3, The Trane Company, 1999.
3 Webb, R.L. and Li, W.; “Fouling in Enhanced Tubes Using Cooling Tower
Water, Part I: Long-Term Fouling Data,” International Journal of Heat and
Mass Transfer, 2000.

SYS-APM001-EN 13
Chilled-Water-System Options
There are many chilled-water-system design options; however, in a basic sense,
each option is a function of flow, temperature, system configuration, and
control. This section discusses the effect of flow rate and temperature
decisions.
It is important to remember that temperatures and flow rates are variables. By
judicious selection of these variables, chilled-water plants can be designed to
both satisfy chilled-water requirements and operate cost effectively.
Chilled-water systems are often designed using flow rates and temperatures
applied in testing standards developed by the Air-Conditioning and
Refrigeration Institute (ARI), ARI 550/590 –1998
1
for vapor compression chillers
and ARI 560–1992
2
for absorption chillers. These benchmarks provide
requirements for testing and rating chillers under multiple rating conditions.
They are not intended to prescribe the proper or optimal flow rates or
temperature differentials for any particular system. In fact, as component
efficiency and customer requirements change, these standard rating conditions
are seldom the optimal conditions for a real system. There is great latitude in
selecting flow rates, temperatures, and temperature differences.
Chilled- and condenser-water temperatures
Leaving chilled-water and entering condenser-water temperature selection can
be considered independently of their respective flow rates. However,
temperatures and flow rates should be selected together to design an efficient
and flexible chilled-water-system.
Standard rating temperatures
Currently, the standard-rating-condition temperatures in ARI 550/590
1
and
ARI 560
2
are:
n Evaporator leaving water temperature: 44°F [6.7°C]
n Water-cooled-condenser, entering-water temperature: 85°F [29.4°C]
n Air-cooled-condenser, entering-air dry bulb: 95°F [35.0°C]
For years, these temperature definitions were the benchmarks in system
designs. Today, designers apply a variety of different temperatures.
ARI 550/590 reflects this trend by allowing the chilled-water and condenser-
water temperatures to be selected at non-standard points and the chiller to be
tested as specified by the standard.
Refer to ARI Standard 550/590–1998,
Standard for Water Chilling Packages
Using the Vapor Compression Cycle and
the ARI Standard 560–1992, Standard for
Absorption Water Chiller and Water
Heating Package, for additional
information. Both are published by the
Air-Conditioning & Refrigeration Institute.
(www.ari.org)

SYS-APM001-EN
14
Chilled-water temperatures
Currently, comfort cooling systems are designed with chilled-water-supply
temperatures that range from 44°F [6.7°C] to 38°F [3.3°C], and, in some cases,
as low as 34°F [1.1°C]. Reasons to decrease the chilled-water temperature
include these:
n The system design more readily accommodates wider temperature
differences (lower flow rates) than the standard rating conditions (see the
subsection Selecting flow rates, page 16).
n Lower water temperature allows lower air temperatures (and flows) to be
selected resulting in reduced airside installed and operating costs.
n Colder water in the same chilled-water coil may provide better
dehumidification.
n Colder water can be used to increase the capacity of an existing chilled-
water distribution system. In some instances, this can save significant
capital expenditures to add capacity to large central plants that have
reached their flow limits.
Some system designers hesitate to use lower chilled-water temperatures,
concerned that:
n the chiller will become less efficient. As discussed earlier, lower chilled-
water temperature makes the chiller work harder. However, while the lower
water temperature increases chiller energy consumption, reducing the
chilled-water flow rate reduces pump energy. This combination often lowers
system energy consumption.
n lower chilled-water temperatures may require more insulation on piping to
prevent condensation (“sweating”). Ensure that pipes are properly insulated
at all water temperatures. Lower temperature water will not always require
more insulation.
Condenser-water temperatures
Today’s chillers can run at various entering condenser-water temperatures,
varying from design temperature to the lowest-allowable temperature for that
particular chiller design. However, many existing older chillers are limited in
their allowable condenser-water temperatures. Contact the chiller manufacturer
for these limits. Optimal condenser-water-temperature control is discussed in
the section, Condenser-System Variations, page 69.
Chilled water (without antifreeze) at 34°F
(1.1°C) is possible with some chillers that
use sophisticated evaporator-design and
chiller-control methods.

SYS-APM001-EN 15
Chilled- and condenser-water flow rates
The selection of chilled-water and condenser-water flow rates is a powerful tool
that designers have at their disposal. Kelly and Chan5
, and Schwedler and
Nordeen6
, found that reducing flow rates can reduce the costs of chilled-water-
system installation and/or operation.
Standard-rating flow rates
Presently, the standard-rating-condition flow rates in ARI 550/590 are:
n 2.4 gpm/ton [0.043 lps/kW] for evaporator
n 3.0 gpm/ton [0.054 lps/kW] for condenser
This evaporator flow rate corresponds to a 10°F [5.6°C] temperature difference.
Depending on the compressor efficiency, the corresponding condenser
temperature difference is 9.1°F to 10°F [5.1°C to 5.6°C].
Absorption chillers are rated using ARI Standard 560–1992, Standard for
Absorption Water Chiller and Water Heating Package2
. The evaporator flow
rates are the same as those used in ARI 550/590; however, condenser (often
called cooling water) flow rates differ depending on the absorption chiller
design. Table 2 shows the standard rating conditions for various absorption
chillers.
Table 2 Standard rating conditions for absorption chillers
Absorption Chiller Type
Condenser Flow Rate
gpm/tonkkkkk lps/kW
Single Effect 3.60 0.065
Double Effect
Steam or hot water 4.00 0.072
Direct fired 4.50 0.081

SYS-APM001-EN
16
Selecting flow rates
Designers may use the standard rating conditions to compare manufacturers’
performances at exactly the same conditions. However, these standards allow
any flow rates to be used and certified comparisons to be made at those
conditions. For a given load, as flow rate decreases, the temperature differential
increases. Table 3 reflects a 450-ton [1,580-kW refrigeration] chilled-water
system, both as a base case and with low flow.
In this example, notice that the leaving-chilled-water temperature decreases
and the leaving-condenser-water temperature increases. This means that the
chiller’s compressor must provide more lift and use more power. How does this
impact system energy consumption? Using the following assumptions, we can
calculate system energy usage:
n 80 feet of water [239 kPa] pressure drop through chilled-water piping
n 30 feet of water [89.7 kPa] pressure drop through condenser-water piping
n 78°F [25.6°C] design wet bulb
n 93 percent motor efficiency for pumps and tower
n 75 percent pump efficiency
n Identical pipe size in chilled- and condenser-water loops (either a design
decision, or indicating changing flows in an existing system)
The pressure drop through the chiller will change. When using the same size
pipe, the pressure drop changes with nearly the square of the flow rate. While
this is true for straight piping, the pressure drop does not follow this exact
relationship for control valves or branches serving loads of varying diversity.
Table 3 Standard rating conditions for chilled-water systems
Chilled Water System Base Case Low Flow
Evaporator flow rate, gpm [lps] 1,080 [68.1] 675 [42.6]
Chilled water
temperature °F [°C]
Entering 54.0 [12.2] 57.0 [13.9]
Leaving 44.0 [6.7] 41.0 [5.0]
Condenser flow rate, gpm [lps] 1,350 [85.2] 900 [56.8]
Condenser water
temperature °F [°C]
Entering 85.0 [29.4] 85.0 [29.4]
Leaving 94.3 [34.6] 99.1 [37.3]
Chiller power, kW 256.0 292.0

SYS-APM001-EN 17
Be sure to calculate the actual pressure drop throughout the system. Hazen–
Williams and Darcy–Weisbach calculate the change is to the 1.85 and 1.90
power, respectively. The examples here use the more conservative 1.85 power:
DP2/DP1 = (Flow2)/(Flow1)
1.85
Given different flow rates and entering water temperatures, a different cooling
tower can be selected for the low-flow condition:
Table 4 Low-flow conditions for chilled-water pump
Base Case Low Flow
Flow rate, gpm [lps] 1,080 [68.1] 675 [42.6]
System pressure drop, ft water [kPa] 80.0 [239] 33.5 [100]
Evaporator-bundle pressure drop, ft water [kPa] 29.7 [88.8] 12.6 [37.7]
Pump power output, hp [kW] 39.9 [29.8] 10.5 [7.80]
Pump electrical power input, kW 32.0 8.4
Table 5 Low-flow conditions for cooling tower
Base Case Low Flow
Flow rate, gpm [lps] 1,350 [85.2] 900 [56.8]
Static head, ft water [kPa] 19.1 [57.1] 12.6 [37.7]
Tower fan power output, hp [kW] 30.0 [22.4] 20.0 [14.9]
Tower fan electrical power input, kW 24.1 16.0
Table 6 Low-flow conditions for condenser-water pump
Base Case Low Flow
Flow rate, gpm [lps] 1,350 [85.2] 900 [56.8]
System pressure drop, ft water [kPa] 30 [89.7] 14.2 [42.5]
Condenser-bundle pressure drop, ft water [kPa] 19.9 [59.5] 9.6 [28.7]
Tower static lift, ft water [kPa] 19.1 [57.1] 12.6 [37.7]
Pump electrical input, kW 25.2 8.8

SYS-APM001-EN
18
The total system power is now as follows:
It becomes clear that flow rates can affect full-load system power. Even though
the chiller requires more power in the low-flow system, the power reductions
experienced by the pumps and cooling tower result in an overall savings for the
system. What happens at part-load conditions? Figure 5 shows the part-load
performance based on the following assumptions:
n The chilled-water pump includes a variable-frequency drive
n The condenser-water pump remains at constant power
n The cooling tower is controlled to produce water temperatures lower
than design
Table 7 Total system power
Component Power (kW) Base Case Low Flow
Chiller 256.0 292.0
Chilled-water pump 32.0 8.4
Condenser-water pump 25.2 8.8
Cooling tower 24.1 16.0
Total power for chilled-water system 337.3 325.2

SYS-APM001-EN 19
Figure 5 Chilled-water-system performance at part load
While the magnitude of the benefit of low-flow changes depends on the chiller
type used (centrifugal, absorption, helical-rotary, scroll), all chilled-water
systems can benefit from judicious use of reduced flow rates.
Coil response to decreased entering water temperature
A coil is a simple heat exchanger. If we want it to deliver the same sensible and
latent capacity while we supply it with cooler water, the coil's controls respond
by reducing the amount of water passing through it. Because the amount of
water decreases while the amount of heat exchanged remains constant, the
leaving water temperature increases. Thus, by producing cooler water, a low-
flow system can be applied to an existing building. In a retrofit application it is
wise to reselect the coil, using the manufacturer’s selection program, at a new
chilled-water temperature to ensure its performance will meet requirements.
When coil performance data is not available from the original manufacturer,
some designers use this approximation. For each 1°F –1.5°F [0.6°C–1.1°C] the
water temperature entering the coil decreases, the water returns 1°F [0.6°C]
warmer and gives about the same sensible and total capacities.
For example, consider a coil operating at 44°F [6.7°C] entering temperature and
54°F [12.2°C] leaving temperature. By changing the entering-water temperature
to 41°F [5.0°C] the coil-leaving temperature will be approximately 56°F –57°F
[13.3°C–13.9°C]. Let’s look at this example in a table.
0.0
50.0
100.0
150.0
200.0
250.0
300.0
350.0
25% Load 50% Load 75% Load Full Load
kW
Base
Low Flow

SYS-APM001-EN
20
One possible concern of low-supply water temperatures is the ability of the
valve to control flow properly at low-load conditions. A properly-sized valve
with good range can work well in low-flow systems. In existing systems, valves
may need to be replaced if they cannot operate with the new range of flows, but
the coils do not need to be replaced.
Cooling-tower options with low flow
Smaller tower
Like coils, cooling towers are heat exchangers—although often misunderstood
heat exchangers. The tower exchanges heat between the entering (warmest)
water temperature and the ambient wet-bulb temperature. Therefore, in a new
system or when a cooling tower is replaced, a low-flow system design allows a
smaller, more efficient cooling tower to be selected. How is this possible?
Since the amount of heat rejection is approximately the same in standard-
rating-condition and low-flow systems, we can estimate the heat exchange area
necessary to reject the heat:
Q = U A1 ∆T1, where A = area, U = coefficient of heat transfer, and
lnnn.∆T = temperature difference
= U A2 ∆T2 or A1 ∆T1 = A2 ∆T2
Using standard rating conditions, the temperature difference between tower
entering temperature and ambient wet bulb for ∆T1 is:
∆T1 = 94.2 – 78 = 16.2°F [34.6 – 25.6 = 9.0°C]
while at typical low-flow conditions for ∆T2 it is:
∆T2 = 99.1 – 78 = 21.1°F [37.3 – 25.6 = 11.7°C]
Therefore:
A1 × 16.2 = A2 × 21.1 or A2 = 0.77 A1
Table 8 Effect of decreased water temperature
Original
Selection
°F [°C]
Chilled-water reduction
for each 1° return water
increase °F [°C]
Coil water
temperature
Entering 44 [6.7]
1°
41 [5.0]
1.5°
41 [5.0]
Leaving 54 [12.2] 57 [13.9] 56 [13.3]

SYS-APM001-EN 21
In a cooling tower, the heat exchange capacity can be changed by either surface
area or airflow, or some combination of the two. A cooling-tower
manufacturer's selection program can give the exact size and power
requirements. In the example on pages 16–18, both the cooling-tower size and
airflow (hence, required fan power) were reduced.
Same tower, smaller approach
Another option is to use the same cooling tower at a lower flow rate. In a new
system, this is a design decision, but in an existing system, it is often a
constraint. Given the same heat-rejection load, the low-flow system allows the
cooling tower to return colder water; that is, the tower's approach to the
ambient wet-bulb temperature decreases. In the previous example of 450 tons
[1580 kW], the same cooling tower would have resulted in an entering
condenser-water temperature of 83.5°F [28.6°C] instead of the 85°F [29.4°C]
with the smaller cooling tower. It is important to realize that the entering
temperature for the tower would be approximately 97.6°F [36.4°C]. Therefore,
the effect of reduced flow rate on chiller energy consumption is partially offset
by the lower entering- condenser water temperature.
Same tower, larger chiller
One retrofit option that benefits many building owners is installing a new,
larger chiller and using the existing cooling tower, condenser-water pump, and
condenser-water pipes. In many cases, this allows the building owner to
increase the chilled-water-system capacity for an expansion, with a limited
budget. Table 9 shows the conditions for an existing 450-ton [1,580-kW] chiller
replaced by a 675-ton [2,370-kW] chiller. This is a capacity increase of 50
percent. A more extensive discussion of this example is contained in the next
section, System Configurations. It is important to select the new chiller based
on the new conditions.
Table 9 Retrofit capacity changes
Present
Expansion
retrofit
Capacity, tons
[kW refrigeration]
450 [1,580] 675 [2,370]
Cooling tower
Flow rate, gpm [l/s] 1350 [85.2] 1,350 [85.2]
Entering temperature, °F [°C] 94.3 [34.6] 103 [39.4]
Leaving temperature, °F [°C] 85 [29.4] 88 [31.1]
Ambient wet-bulb
temperature, °F [°C]
78 [25.6] 78 [25.6]

SYS-APM001-EN
22
Cost implications
By reducing either chilled- or condenser-water flow rates alone, the following
installed-cost reductions are possible:
n Reduced pump size, valves, strainers, fittings, electrical connections
n In new systems, reduced pipe sizes
n In existing systems, more capacity from existing chilled-water piping
systems
n Reduced cooling-tower size, footprint, and fan power
Alternatively, a physically-smaller cooling tower may be selected using low
flow. A reduced footprint can benefit building owners in a number of ways:
n Reduced real estate requirements (often more important than realized)
n Reduced structural requirement, since the amount of tower water is reduced
n Reduced excavation and material costs in the case of a large, built-up tower
with a concrete sump
n Improved aesthetics because of the reduced tower height
In addition to reducing installation costs, operating cost reductions for the
whole system are also available. Due to a smaller pump and/or tower, the pump
and tower operating costs can be reduced substantially with less adverse
impact on the chiller operating cost. Analysis programs such as DOE 2.1,
TRACE®
, or System Analyzer™ software can be used to determine annual
operating costs. Nordeen and Schwedler6
showed that operating costs for
chilled-water systems using absorption chillers can benefit greatly from
reduced condenser-water flow. Figure 6 shows operating costs as generated
with System Analyzer™ analysis software.
Several considerations should be kept in
mind when determining sizes for new
systems. As pipe size is decreased, so are
valve and specialty sizes and costs.
Remember that reducing pipe size
increases pressure drop. Keep a balance
between first cost and operating costs.
This can significantly reduce the system
retrofit costs since existing pipes may be
used.

SYS-APM001-EN 23
Figure 6 Annual system operating costs
Kelly and Chan5
compare the operational costs of chilled-water-system designs
in site locations. Their summary states:
In conclusion, there are times you can “have your cake and eat it too.”
In most cases, larger ∆T’s and the associated lower flow rates will not
only save installation cost but will usually save energy over the course
of the year. This is especially true if a portion of the first cost savings is
reinvested in more efficient chillers. With the same cost chillers, at
worst, the annual operating cost with the lower flows will be about
equal to “standard” flows but still at a lower first cost.
$-
$5,000
$10,000
$15,000
$20,000
$25,000
$30,000
$35,000
$40,000
4.45 gpm/ton 3.60 gpm/ton 3.09 gpm/ton

SYS-APM001-EN
24
Misconceptions about low-flow rates
Some common misconceptions about low-flow systems include:
1 Low flow is only good for long piping runs
2 Low flow only works well for specific manufacturers’ chillers
3 Low flow can only be applied to new chilled-water systems
Let’s discuss each of these three misconceptions.
Misconception 1—Low flow is only good for long
piping runs.
One way to examine this claim is to use our previous example, but to
concentrate on the condenser-water side. We’ll start with the example covered
on pages 16–18. Using the same chiller, but a smaller cooling tower and a more
conservative zero condenser-water-pipe pressure drop, we can examine the
effect of reducing flow rates.
Table 10 Reduced flow-rate effect
Condenser Water Pump Base Case Low Flow
Flow rate, gpm [lps] 1350 [85.2] 900 [56.8]
System pressure drop, ft water [kPa] 0 0
Condenser bundle pressure drop, ft water [kPa] 19.9 [59.5] 9.6 [28.7]
Tower static lift, ft water [kPa] 19.1 [57.1] 12.6 [37.7]
Pump fan electrical input, kW 14.2 5.4

SYS-APM001-EN 25
Figure 7 System energy comparison (no pipe)
Energy consumption for the chiller, condenser-water pump, and cooling-tower
fans is shown in Figure 7. Note that only at full load does the total power of the
chilled-water plant increase. Recall that this is with absolutely no pressure drop
through the condenser-water piping, valves, or fittings. It is interesting to note
that the break-even point at full load is approximately 8 feet of head (water)
[23.9 kPa]. Also note that at all part-load conditions, the total power of the low-
flow system is less than that of the base system. It is easy to see that even for
short piping runs, reducing flow rates can improve plant energy consumption.
Misconception 2—Low flow only works for specific
manufacturers’ chillers.
Demirchian, et al.
3
, Eley
4
, and Schwedler and Nordeen
6
independently showed
that system energy consumption can be reduced by reducing flow rates. It is
interesting to note that in the systems studied, three different chiller
manufacturer’s chillers were examined, yet the energy savings only varied from
2.0 to 6.5 percent. In all cases, regardless of which manufacturer’s chillers were
used, the system energy consumption was reduced. In addition, Demirchian, et
al.
2
, and Schwedler and Nordeen
6
also noted reduced first costs.
0.0
50.0
1
00.0
1
50.0
200.0
250.0
300.0
350.0
25% 50% 75% 1
00%
System Load
System
Energy
Consumption
(kWh)
3.0 gpm/ton 2.0 gpm/ton

SYS-APM001-EN
26
Misconception 3—Low flow can only be applied to new
chilled-water systems.
As previously discussed in the manual in the sub-sections Coil response to
decreased entering water temperature and Cooling tower options with low
flow, there are distinct opportunities to use existing infrastructure (pumps,
pipes, coils, and cooling towers) to either expand available cooling capacity
and/or reduce system energy costs by using lower-flow rates.
Upon examination, it is clear that low-flow systems allow savings even on short
piping runs, work with all manufacturers’ chillers, and can be used in retrofit
applications. As a designer, remember to review the benefits to the building
owner. Often, reducing flow rates can provide significant value.
Chapter references
1 ARI Standard 550/590–1998, Standard for Water Chilling Packages Using the
Vapor Compression Cycle, Air-Conditioning & Refrigeration Institute.
2 ARI Standard 560–1992, Standard for Absorption Water Chiller and Water
Heating Package, Air-Conditioning & Refrigeration Institute.
3 Demirchian, G.H. PE and Maragareci, M.A. PE.: “The benefits of higher
condenser-water ∆T at Logan International Airport central chilled-water
plant.” IDEA 88th Annual Conference Proceedings, 1997, pp. 291–300.
4 Eley, C.: “Energy analysis–replacement of chillers for buildings 43, 47, and
48.”Eley Associates, CA, April 1997.
5 Kelly, D.W. and Chan, T.; “Optimizing chilled-water plants,” Heating/Piping/
Air Conditioning, January 1999, pp. 145-7.
6 Schwedler, M., P
.E. and Nordeen, A.; “Low flow works for absorbers too!”
Contracting Business, November 1998, pp. 108-112.

SYS-APM001-EN 27
System Configurations
Multiple-chiller systems are more common than single-chiller systems for the
same reason that most commercial airplanes have more than one engine—the
balance of reliability and cost. The most typical system configuration, by far,
has two chillers. Since system loads can vary throughout a wide spectrum,
multiple-chiller systems can often operate with one chiller. During these
periods, if the system is designed properly, the energy required to operate a
second chiller and its auxiliaries can be conserved.
Parallel chillers
Figure 8 shows a system with two chillers piped in parallel, using a single
chilled-water pump.
Figure 8 Parallel chillers with single, common chiller pump
With constant flow loads, water flows in both chillers continually, whether the
chiller is operating or not. Clearly, this can disrupt the supply chilled-water
temperature when only one chiller is operating. The temperatures indicated in
Figure 8 show how the supply water temperature rises when one chiller is
cycled off in response to a part-load condition. This may result in inadequate
dehumidification capabilities or the inability to satisfy specific loads.
Alternatively, the running chiller can be reset to produce a lower supply
temperature at this condition. In this way, the mixed system-supply-water
temperature may be maintained at a more acceptable temperature. This
complicates the control system and presents the possibility of increasing chiller
energy consumption due to the requirement for lower-temperature water.
There will also be a low limit to this water temperature, dependent on the
chiller’s low pressure cut out control, low-evaporator-refrigerant-temperature
limits, or low leaving-chilled-water limits.
Constant
Flow
Chiller 2 (Off)
Chiller 1 (On)
54°F [12.2°C] 54°F [12.2°C]
44°F [6.6°C]
49°F [9.4°C]

SYS-APM001-EN
28
Figure 9 Parallel chillers with separate, dedicated chiller pumps
If separate, dedicated chiller pumps are used (Figure 9), a chiller–pump pair can
be cycled together. This solves the flow mixing problem described above, but
presents a new problem. With only one pump operating, total system water
flow will decrease significantly, according to the pump–system curve
relationship. All the load terminals in the system will receive less water,
regardless of their need. Consequently, it is possible to starve some loads that
are still high, perhaps those serving internal spaces with constant loads, or to
starve the loads farthest from the pump.
Off
On
Chiller 1 (On)
Chiller 2 (Off)
Partial Flow
(Starved Coils)

SYS-APM001-EN 29
Series chillers
If chillers are piped in series, as in Figure 10, the mixing problem disappears
and the starving coils problem, when one of the pumps is not running, is
resolved. Series flow presents a new set of temperature and flow control
challenges.
Figure 10 Series chillers
The flow rate through each chiller is the entire system flow, that is, double the
individual flow rate of the parallel chillers (two chillers). This means that the
chiller evaporator must accommodate the doubled water quantity. All things
being equal, this results in fewer water passes and decreased chiller efficiency.
However, this efficiency loss is more than offset by increased chiller efficiency
because the upstream chiller operates at warmer temperatures. Also, pressure
losses are additive when the chillers are piped in series. This may increase total
system pressure loss significantly. On the other hand, series chillers may work
very well in low-flow systems, where the system temperature difference is
greater than 16°F [9°C], resulting in less pressure loss. Low-flow systems are
discussed in detail beginning on page 16.
Chiller 2
Set Point = 44°F [6.6°C] Chiller 1
Set Point = 44°F [6.6°C]
54°F [12.2°C]
Coil Loads
49°F [9.4°C]
44°F [6.6°C]

SYS-APM001-EN
30
Temperature control can be executed in several ways. Figure 10 shows a
strategy where the controller on each chiller is set at the system design set
point. Either chiller can be used to meet the system demand for up to
50 percent of the system load. At system loads greater than 50 percent, the
upstream chiller is preferentially loaded because it will attempt to produce the
design leaving chilled-water temperature. Any portion of the load that remains
is directed to the downstream chiller.
If chiller set points are staggered (upstream at 49°F [9.4°C] and downstream at
44°F [6.7°C]), the downstream chiller is loaded first. The upstream machine then
meets any portion of the system load that the downstream chiller cannot meet.
This control strategy offers several benefits. The first is that the upstream chiller
is always operating at an elevated temperature. This allows it to operate at a
higher efficiency. Also, placing an absorption chiller in the upstream position
increases its capacity. As an example, an absorption chiller that can produce
500 tons [1,760-kW] at a leaving chilled-water temperature of 44°F [6.7°C] may
produce 600 tons [2,110-kW] at 50°F [10°C]. Centrifugal, helical-rotary,
reciprocating, and scroll chillers experience capacity and efficiency changes to
a lesser degree. By judicious use of the series configuration, these benefits can
provide reduced installed cost and fuel flexibility to the building owner.
Equal loading of the two chillers may be accomplished by using a chiller plant
management system to reset the upstream chiller’s set point in response to
changes in system load.

SYS-APM001-EN 31
Primary–secondary (decoupled) systems
The root cause of essentially all of the difficulties with parallel chiller control is
the fixed relationship between chiller and system flow rates. If, instead, we can
hydraulically decouple the production (chiller) piping from the distribution
(load) piping, it is possible to control them separately. The fixed relationships
are then broken apart.
System basics
Hydraulic decoupling
Figure 11 shows the basic decoupled system. This strategy is also referred to as
a primary–secondary pumping arrangement. Separate pumps are dedicated to
production and distribution. While the same water is pumped twice (by
different pumps), there is no duplication of pumping energy. This is because
the production pumps overcome only the chiller and production-side pressure
drop while the distribution pumps overcome only the distribution system
pressure drops.
Figure 11 Decoupled arrangement
Chiller 3
Chiller 2
Chiller 1
Bypass Line
Supply
Production
Distribution

SYS-APM001-EN
32
The unrestricted bypass line hydraulically decouples the production and
distribution pumps so that they cannot operate in a series coupled pumping
arrangement.
Although the two pumping systems are independent, they have three things in
common:
n bypass piping,
n no-flow static head (from the building water column), and
n water.
Changes in flows or pressures, due to variations in dynamic head or the
number of chillers operating, cannot cross the bypass line.
The extent of decoupling depends solely on the restriction (or lack of
restriction) in the bypass pipe. Total decoupling is accomplished only if the
bypass piping has zero pressure loss at any flow. Since this is not possible,
some insignificant pump coupling will exist. The important issue is to keep the
bypass piping free of unnecessary restrictions such as check valves. See Check
valve in the bypass line, page 63, for further discussion.
Production
An individual production (chiller) pump need only pump water from the return
bypass tee (point A in Figure 12), through its chiller, and into the tee at the
supply-end of the bypass line (point B in Figure 12). This represents a relatively
small pressure differential and a low pumping-power requirement. In addition,
each individual pump operates only when its corresponding chiller runs.
Production loops are independent, one from another, as well as from the
distribution loop. They may consist of pump–chiller pairs that act as
independent chillers. Or, manifolded and stepped pumps can be teamed with
automatic, two-position chiller valves to operate in the same way as pump–
chiller pairs. Figure 12 shows the latter arrangement. Temperature control is
also independent. The conventional, chilled-water temperature controller
furnished with the chiller, serves this function.

SYS-APM001-EN 33
Figure 12 Production loop
Chillers may be of any type, age, size, or manufacturer. System operation is
simplest, however, if all of the chillers are designed to operate with the same
leaving chilled-water temperature and through the same system temperature
rise (temperature difference) across the chiller.
It is interesting to note that if the chillers in a decoupled system make the same
chilled-water temperature, then all the operating chillers are loaded to equal
percentages. There may be times when preferentially loading a chiller is
desired. This is discussed in the section Chilled-Water-System Variations, page
54.
Production
Pumps
Chiller 3
Chiller 2
Chiller 1
Bypass Line
Return
Production
Distribution
Supply
A B
Automated Isolation
Valves

SYS-APM001-EN
34
Distribution
Distribution pumps take water from the supply water tee (point B in Figure 12),
push it through all the distribution piping and load terminals, and then on to the
return water tee (point A in Figure 12). This pump can (and should) allow
variable flow.
Figure 13 Distribution loop
By itself, the distribution system is easy to understand. Figure 13 shows a
simplified distribution system consisting of multiple cooling coils, each
controlled by a valve that regulates the flow in its respective coil. In this case,
the flow control valves should not be three-way because a constant flow is not
desired. Instead, two-way modulating valves are used. As the aggregate loads
change system flow, a constant speed pump would “ride” its flow-rate-versus-
head-pressure. This means that in response to the change of flow required, the
pump will find a new equilibrium point along its operating curve. An example
pump curve is shown in Figure 13.
Alternatively, multiple pumps or variable-speed pumps can be used to limit the
dynamic pumping head, similar to VAV fan control. Properly designed, part-
load pumping power can approach the theoretical cubic relationship to flow,
thus reducing energy consumption significantly. Today, most decoupled
systems use a variable-speed drive on the distribution pump.
Distribution basics The distribution system benefits from the ability to
accommodate load diversity, the fact that system flow is variable, and (in a
properly operating system) the fact that return water is maintained at
temperatures near design. The last assumption is further discussed in the
subsection Low ∆T syndrome, page 63.
Supply
Return
Bypass Line
Loads
Distribution
Pump Curve
Head
Flow

SYS-APM001-EN 35
Load diversity Not all chilled-water loads peak simultaneously. Therefore,
the quantity of water that flows at any one time is reduced from the “sum of the
peaks” load that would be required in a constant-flow-distribution loop. This
presents the possibility of reducing chiller, pump, and pipe sizes significantly.
Variable flow Only the water that the loads actually use is pumped. Most of
the time, this means a significantly reduced flow rate, accompanied by an even
more significant reduction in pumping energy.
Elevated return-water temperatures Because unused chilled water does
not bypass the cooling coils, all water that is returned accomplishes some
cooling. Theoretically, the return-water temperature will always be at least as
high as it is at full load. From a practical standpoint, this is not always possible,
but it is closely approached in a properly operating system. In fact, at most part-
load conditions, water returns from properly functioning air-conditioning coils
at higher-than-design temperatures. In systems that use counterflow cooling
coils, this occurs because the water leaving the coil tries to approach the
temperature of the entering air stream.
Warm return water provides advantages in system design. It permits
“preferential” loading of chillers, for example. Warmer return water is useful
with all systems, but particularly so with heat recovery and free cooling
applications. The section Chilled-Water System Variations, page 54 has further
information.

SYS-APM001-EN
36
Pumping Arrangements
Common
A variety of distribution system arrangements is possible. A single, large
pumping station, as shown in Figure 12, can be used. The station may consist
of single or multiplexed pumps sequenced on or off.
Figure 14 Campus pumping
ffft f f f f f ttfarrangement
Campus
Alternatively, each of several secondary distribution systems can be piped in
parallel. For example, Figure 14 shows separate distribution systems for each of
three loads. Clearly, this arrangement lends itself to the possibility of plant
expansion by simply adding secondary distribution pumps to the existing plant.
Tertiary or distributed
Tertiary pumping is an extension of primary–secondary pumping when the
distribution or secondary pump must overcome diverse and severe pumping
requirements.
System loads can also be decoupled from the secondary distribution system.
This is frequently done with very large systems. Figure 15 shows one method of
providing “tertiary pumping” at the loads. A “load” may be something as large
as an entire building, or as small as an individual cooling coil. When one or
more loads have extreme head requirements, the degree of rangability of the
distribution pump is severely curtailed. Tertiary pumping allows the excess
pumping requirements to be placed on a third pumping system thus shielding
the distribution pump from divergent pressure requirements.
Most importantly, the loads must be controlled so that only the water needed to
perform cooling is taken from the distribution loop. Water must not be allowed
to flow into the return piping until it has sustained a specific temperature rise.
Tertiary pumps can be either constant flow or variable flow, to best meet the
terminal load requirements.
Return Supply
Secondary
Distribution Pumps
Bypass Line

SYS-APM001-EN 37
Figure 15 Tertiary pumping arrangement
Decoupled system–principle of operation
Figure 16 Decoupled system supply
oooooooto tee
At the tee connecting the supply and bypass lines, a supply–demand
relationship exists, as shown in Figure 16. Think of the total flow rate from all
operating pump–chiller pairs as supply. Demand is the distribution system flow
required to meet loads. Whenever supply and demand flows are unequal, water
will flow into, or out of, the bypass line. Flow can be sensed directly or inferred
from the bypass-water temperature.
An inadequate supply to meet demand causes return water to flow out of the
bypass leg of the tee, into the distribution system. The mixture of chiller-supply
and warm system-return water, then, flows into the distribution loop. Supply-
water temperature control is compromised when this happens. If the bypass-
line flow into the supply tee (Figure 16) can be sensed, its presence can be used
to energize another pump–chiller pair. The increase in supply water flow from
the additional pump changes the supply–demand relationship at the tee,
eliminating return-water mixing. As long as return-water mixing does not occur
at the supply tee, no additional chiller capacity is required. When mixing does
occur, an additional chiller may be needed, depending on the amount of mixing
that can be tolerated.
Chiller 1
Chiller 2
Check Valve
Variable-Speed
Drive
Control
Differential
Pressure
Transmitter
Valve
Loads Loads
Excess
Inadequate
Supply
Production
Distribution
Supply
Supply
Return
Bypass

SYS-APM001-EN
38
Much of the time, supply exceeds demand and the surplus flows to the return
tee. If a chiller pump is stopped prematurely, the bypass-line flow will again
show a deficit and the pump will be cycled on again. The amount of surplus
flow necessary depends on the size of the chiller to be shut off. The surplus flow
must exceed a certain quantity before shutting off a chiller–pump pair. This is
discussed in Chiller sequencing, page 39. If all chillers are equal in size, the
surplus-flow signal can be constant.
Control of the number of chillers is accomplished by simply noting the direction
of flow in the bypass line. Thus, the system operates as a flow-based demand
system, not a temperature-based demand system.
Flow-based control
To properly operate a primary–secondary system, an indication of direction of
flow and the flow rate through the bypass line is necessary. This may be done
either directly or indirectly. When bypass flow is from supply to return, it is
called surplus. Bypass flow moving from return to supply is termed deficit.
Flow-sensing
Direct flow-sensing in the bypass line can be accomplished in several ways. A
number of flow-metering technologies have been used successfully. These
include Pitot tube, Venturi, orifice plate, differential pressure, turbine, impeller,
vortex, magnetic, and ultrasonic transit-time. The accuracy, ease of installation,
maintainability, and cost of meter technologies vary widely. To give accurate
results, a flow meter must be calibrated periodically, with some flow meters
requiring more-frequent calibration than others. When using flow-sensing
devices, it is important to understand the range of flows a device can properly
measure and its calibration requirements. The readings will only be as good as
the instrumentation. Also note that many flow-measurement devices require
several diameters of straight pipe for accurate readings.
Figure 17 Temperature-sensing Temperature-sensing
Mixed water streams at the outlets of the supply- and return-water tees,
Figure 17, can be used to indirectly determine the supply–demand relationship.
Standard temperature-mixing equations can be used to determine the exact
amount of surplus or deficit flow in the bypass line.
The five temperatures sensed—at points A, B, C, D, and E—are received by a
programmable controller. (Some control systems use only two sensors, at
points B and D, in conjunction with “pre-programmed” algebraic mixing
equations.) Processing software applies the classic mixing equations and
determines the resulting action to properly control the chilled-water system.
E (Optional)
D (Required)
(Optional)
(Required) B
(Optional) A
Return Main Supply Main
C

SYS-APM001-EN 39
Note that sensor D needs to be very accurate, especially if there are many
chillers, since small temperature changes may warrant chiller sequencing.
Either temperature-sensing strategy has a cost and flexibility advantage if a
building or chiller-plant management system already exists, or is planned.
Chiller sequencing
Given the amount and direction of flow in the bypass line, chillers can be added
or subtracted.
Adding a chiller
When there is deficit flow in the bypass line, the system is receiving water at a
temperature above the system design temperature. (Also see the Low ∆T
syndrome discussion, page 63.) At this point in time, a chiller and pump may be
added. Many operators sense deficit flow for a particular amount of time (for
example, 15 minutes) to ensure that the deficit flow is not a result of system
transients. This reduces the chances of cycling a chiller; that is, turning on a
chiller and then turning it off after a short time.
Subtracting a chiller
A chiller may be turned off when enough surplus water is flowing through the
bypass line. How much is enough? Enough so that the chiller does not cycle on
again in a short time period. Many system operators compare the amount of
surplus flow with the flow rate of the chiller they are considering turning off. If
this ratio is 110 to 115 percent, they turn the chiller off. Let’s look at an example:
Chiller 1 can make 960 gpm [60.6 lps] of 40°F [4.4°C] chilled-water,
while Chiller 2 can make 1,440 gpm [90.8 lps]. At present, there is 1,100 gpm
[69.4 lps] of surplus flow in the bypass line.
n The surplus bypass flow is presently 115 percent of Chiller 1’s flow. If we
turn Chiller 1 off, we will have 140 gpm [8.8 lps] of surplus flow left.
n Note that the surplus bypass flow is presently only 76 percent of Chiller 2’s
flow. If we turn Chiller 2 off, we will have 340 gpm [21.5 lps] of deficit flow. It
is clear that we would have to cycle that chiller back on soon.
In this case, we could turn Chiller 1 off, but leave Chiller 2 on for the most
efficient use of the chillers.

SYS-APM001-EN
40
Variable-Primary-Flow Systems
Another method for balancing the production and distribution flows is to make
them equal. Variable-flow systems require chillers that can operate properly
when evaporator flow varies.
Conceptually, the variable-primary-flow (VPF) system resembles the familiar
constant primary–variable secondary design more commonly known as the
decoupled” system.
1
For example, both require a bypass. The bypass line for a
VPF system is required to ensure that minimum flow through chillers can be
maintained. Each chiller in the arrangement shown has a dedicated pump
whose operation coincides with the chiller it serves.
Figure 18 Variable-primary-flow system
In a VPF system, water flow varies throughout the entire system—through the
evaporator of each operating chiller as well as through the cooling coils.
Two-way control valves on coils, check (or isolation) valves on chillers, and a
bypass pipe with a control valve are required to implement a VPF system.
However:
n variable-flow chiller pumps eliminate the need for a separate
distribution pump.
n the bypass can be positioned either upstream or downstream of the
cooling coils.
n a control valve in the bypass ensures that the amount of flow through the
operating chiller(s) never falls below the minimum limit.
Chiller 2
Chiller 1
Variable-Flow-
Chiller Pumps
Control Valve
System Coils,
Two-Way Control Valves
Multiple
Valves May Be
Three-Way
Required
Optional
“Bypass”
Check
Valves
For Minimum Chiller Flow

SYS-APM001-EN 41
VPF advantages
VPF systems present building owners with several cost-saving benefits that are
directly related to the pumps. The most obvious cost savings result from
eliminating the secondary distribution pump, which, in turn, avoids the material
and labor expenses incurred with the associated piping connections, electrical
service, and variable-frequency drive. Although the number of pumps is
reduced, the sizes of both the pumps and the variable-frequency drives increase
since the pumps must be sized to overcome the entire system’s pressure drop.
This offsets some of the installed cost savings due to fewer pumps.
Building owners often cite pump-related energy savings as the reason that
prompted them to install a VPF system. With the help of a software analysis tool
such as System Analyzer™, TRACE®
600, or DOE 2.1, you can determine
whether the anticipated energy savings justify the use of variable-primary flow
in a particular application.
It may be easier to apply a variable-primary-flow system rather than a primary–
secondary system to an existing chilled-water plant. Unlike the primary–
secondary design, the bypass can be positioned almost anywhere in the chilled-
water loop and an additional pump is unnecessary.
VPF caveats
Sequencing chillers requires a thorough understanding of system dynamics
since flow rates will vary through every operating chiller. The control strategy
needed to avoid cycling, or restarting the chiller too soon, becomes
complicated as the number of chillers or the capacities of the different chillers
increases. The system designer must thoroughly define the control sequence
early in the design process and clearly communicate it to the controls provider.
Better yet, on such a system, a partnership among owner, operator, designer,
and chiller plant provider (including controls) can be formed.
Controlling the flow rate fluctuation is critical. Confirm the allowable flow
fluctuations with the chiller manufacturer and design the system so that the rate
of flow change is never exceeded. Operators must understand how VPF
systems work, therefore training is mandatory. The success of a system design
is directly related to the operator’s ability to carry out the design intent.
An important consideration when investigating variable-primary-flow systems
is the fact that VPF systems take more time and planning than other systems to
design and commission properly. If this time and planning can’t, or won’t, be
invested, you will probably have better results with the use of systems other
than VPF
.
Dispelling A Common Misconception
True or false: “Chillers operate more
efficiently in a system with variable rather
than constant primary flow because of the
greater log mean temperature difference
(LMTD).”
It is true that the return water temperature
in a properly operating VPF system
remains constant as the amount of flow
changes. It is also true that the LMTD can
be increased by changing the production
(primary) side of the chilled-water loop
from constant to variable flow. But there
are other facts to consider.
In a system with constant primary flow:
• Entering-evaporator temperature and
uLMTD fall as the cooling load diminishes.
• The convective heat transfer coefficient,
ulike the primary flow, remains constant
udespite reductions in load.
In a system with variable primary flow:
• The convective heat transfer coefficient in
uthe chiller evaporator decreases with a
ureduction in flow.
• Reduced flow decreases the overall heat-
utransfer effectiveness of the chiller
uevaporator.
The net effect is that the power
consumption for a given chiller is virtually
the same whether the chiller’s evaporator
flow is variable or constant.

SYS-APM001-EN
42
Limits
Evaporator flow rates change as system demand changes. However, there are
limits to absolute flow rate and allowable rate of change. Exceeding those limits
may cause chiller-control instability or catastrophic failure.
Absolute flow limits
Maintain the evaporator flow between the minimum and maximum limits.
Today, the cataloged water velocity range for many chillers is 3–11 fps
[0.9–3.4 m/s], although some manufacturers now allow selections in the 1.5–2.0
fps [0.46–0.61 m/s] range. Ask the chiller manufacturer for the actual flow-rate-
limit values (gpm [lps]) for your machine. The upper limit is generally set to
avoid tube erosion problems, while the lower limit maintains control stability.
Rate of change
If a chiller's control system can not respond properly, the chiller might actually
respond to rapid flow-rate changes by turning off or locking out on a safety trip.
To ensure that chillers stay on line, keep changes in evaporator flow rate within
manufacturer-set limits. This may require the use of slow-acting, modulating
control valves at each chiller to reduce flow variation as chillers are sequenced,
especially if pumps are manifolded.
Bypass flow control
Just as in a primary–secondary system, VPF systems respond to load changes
by modulating flow. As the system demand nears the minimum flow rate for a
single chiller, water must be bypassed to keep the flow rate through the chiller
evaporator above that minimum.
Methods
n Bypass line with valve As previously discussed, bypass may either be
controlled at a central location or be ensured through the use of three-way
valves. When a bypass line and valve are used, the valve must be slow
acting and modulate open when the flow rate nears the minimum of any
chiller on-line. When the flow rate rises above the chiller’s minimum by a
preset limit, the valve may close.
n Three-way valve An alternative is to provide three-way valves in distant
portions of the system. The pump must be controlled so these valves always
keep the total of their flow above the chiller’s minimum. One method to
ensure this flow rate is to control the pump to maintain a pressure
differential at this valve, thus ensuring nearly constant flow at this point in
the system.
Application note
While flow through a chiller’s evaporator is
now allowed to change, chillers with
advanced controls may react by
temporarily unloading. This results in an
elevated leaving chilled-water
temperature—generally only for a short
time. For applications that require strict
chilled-water temperature control, check
with the chiller manufacturer for
recommendations concerning the use of
variable-evaporator flow.
As of this manual’s writing, the most
advanced chiller controls can provide close
temperature control if flow fluctuations are
limited to less than 10 percent of design
chiller flow per minute. For some
advanced controls, relaxing this limit to
30 percent of design flow per minute is
permissible in most comfort-cooling
applications since the leaving-evaporator
water temperature will not deviate from
set point for more than a few minutes,
if at all. Again, check with the chiller
manufacturer for base limits

SYS-APM001-EN 43
Evaporator flow measurement
Measurements of evaporator flow are critical to VPF control. One common
practice relies on direct measurement using flow meters. (Be aware that some
flow meters require, but seldom receive, frequent calibration.) Another
measures water pressure drop through the evaporator bundle and estimates
evaporator flow based on manufacturer data.
Bypass locations
A bypass is required whether the primary flow is constant or variable. In a
primary–secondary system the decoupler allows excess primary water to be
bypassed. In the VPF system the bypass allows system control to maintain the
flows to chillers' minimum flow requirements.
There are three common locations for the VPF bypass line:
n Place the smaller bypass required for a VPF system in the same position as
the bypass in a “decoupled” system. A variable-speed drive on the pump
located near the chillers reduces flow and allows substantial energy and
operating cost savings. One drawback is that the valve must work against
higher pressures—possibly causing wear and lack of controllability.
n Use three-way valves at some of the system coils. While this approach
ensures minimum chiller flow, it reduces the pump operating cost-savings,
due to the increased system flow and decreased return-water temperature.
n Locate a bypass line and valve near the end of the piping run. The bypass
control valve sees a lower operating pressure and stable control. Some
operating cost savings may be sacrificed to maintain the pump-operating
pressure at a higher level with the bypass located away from the chillers.
The line sizes must be large enough to allow the minimum flow rate.
Chiller sequencing
Variable-primary-flow systems have more complex chiller sequencing
requirements than primary–secondary systems. In fact, it is the time and
thought put into chiller sequencing that will ultimately allow a VPF system to
work well—or cause it to fail. System designers must think through the
process, communicate the sequence of operation to those providing system-
level programming and make sure the system operator understands the system
function for it to have any chance to work.

SYS-APM001-EN
44
Adding a chiller in a VPF system
When the chiller(s) already on-line can no longer increase their flow rate—due
either to the pump capacity or the maximum allowable evaporator-flow rate—
or when chillers cannot meet the system-chilled-water set point, a chiller may
be added. In a properly operating system the supply-water temperature is
monitored. When the temperature exceeds the design setpoint by a certain
amount (for example, 1.5°F [0.8³C]) for a set time (for example, 15 minutes) an
additional chiller starts.
As chillers are brought on-line, flow rates may fluctuate substantially. This is
especially true in a system with two chillers. An example will help explain the
challenges.
At a point in time, Chiller 1 is active and has 1,100 gpm [69.4 lps] flowing
through its evaporator. It can no longer satisfy the required system supply
temperature. What happens if Chiller 2’s valve is opened with no other action
taken? If we assume that pressure drops are equal, 550 gpm [34.7 lps] will flow
through each chiller. This means Chiller 1’s flow rate drops by 50 percent
instantaneously (probably beyond what its controls can respond to) and we are
below each chiller’s minimum flow rate. Be aware that this could become an
issue since chiller controls may protect the chiller by shutting it off. The result is
that some combination of pump speed, bypass valve control, and slow-acting
valves at the chillers must do two things:
n Keep change in flow rate within the equipment limitations
n Keep each chiller’s flow rate above its minimum
The bottom line is that control of VPF systems MUST be considered during
system design.
Table 11 Flow-rate-fluctuation examples
Design
flow rate
gpm [lps]
Minimum
flow rate
gpm [lps]
Maximum
flow rate
gpm [lps]
Chiller 1 960 [60.6] 576 [36.3] 2,110 [133.1]
Chiller 2 1,440 [90.8] 675 [42.6] 2,474 [156.1]

SYS-APM001-EN 45
Subtracting a chiller in a VPF system
Subtracting a chiller in a VPF system is not simple, either. As an example,
suppose that both chillers are running near their minimum flow. Chiller 1 is at
650 gpm [41.0 lps] and Chiller 2 is at 760 gpm [47.9 lps], so the system total is
1,410 gpm [88.9 lps].
Choice 1
Turn off Chiller 1: It is obvious that we should be able to turn Chiller 1 off
and satisfy system load as long as the flow rate doesn’t increase too rapidly.
However, the system flow rate is close to the Chiller 2’s design flow rate, and if
the system flow increases, we may need restart Chiller 1.
Choice 2
Turn off Chiller 2: If Chiller 1 has a condenser water temperature lower than
design, its capacity has increased. Could we turn off Chiller 2? Chiller 1’s flow is
certainly within the allowable limits, but it may or may not be able to supply the
required capacity. In this case, the dilemma is to ensure that there is enough
chilled water capacity after a chiller is turned off.
Obviously, control is an extremely important aspect of a VPF system. In many
chilled-water systems with between two and five chillers, system designers
elect to use a primary–secondary system design to minimize control
complexity.
“Overpumping” a chiller in a VPF system
Some VPF practitioners use manifolded pumps, allowing them to “overpump”
a chiller. As used here, overpump means to pump more water through a chiller
than was specified in the original design. In the previous example, Chiller 1
would be “overpumped” any time its evaporator water flow exceeds 960 gpm
[60.6 lps]; however, the flow rate must still be less than the maximum
allowable. Recall that pressure drop through the evaporator will increase
roughly with the square of the flow. There are two reasons one might want to
overpump a chiller.
As the condenser water temperature is allowed to fall, the chiller could produce
more cooling—if allowed. The only way to actually get that increased capacity
is to increase either the flow rate or the temperature difference. The return
water temperature is set, so now the only choices are to decrease the leaving
water temperature or increase the flow. Changing water temperature
complicates the system operation, but increasing water flow may be fairly
simple in a VPF system. By increasing the evaporator flow rate, the chiller can
provide more cooling.

SYS-APM001-EN
46
Some system operators overpump a chiller as a “band-aid” for systems
experiencing low ∆T syndrome (see page 61). An example of low ∆T syndrome
is receiving a depressed (for example, 49°F [9.4°C]) return-water temperature
rather than the design (for example, 56°F [13.3°C]) return-water temperature.
Again, the only methods to load the chiller are to decrease the chilled-water
temperature or to increase the flow. If the pumping power and speed allows,
the operator may be able to increase the chiller’s flow rate and capacity. Do not
exceed the pump’s operating envelope.
Critical VPF system requirements
While they do have benefits, variable-primary-flow systems
1
should not be
used on all systems. Understanding and accounting for the following
prerequisites are critical for a successful VPF system.
n Chiller controls must adequately regulate temperature as flows vary
n System level controls must adequately regulate both temperature and flow
as system demand varies
n Adequate time must be budgeted to design and program the system control
sequence
n The system operator must understand the intended operation
n The system must include a means of assuring all chiller minimum-flow
requirements, normally one of the bypass methods previously discussed.
VPF complicates all aspects of system design and operation. Consequently,
there are many steps that must be taken to allow a VPF system to work well.
Chapter references
1 Schwedler, M., PE and Bradley, B.; “An Idea for Chilled-Water Plants Whose

SYS-APM001-EN 47
Chilled-Water-Control Options
Chilled water reset—raising and lowering
Many chilled-water plants use chilled water reset, that is, changing the chiller's
control setpoint, in an effort to reduce chiller energy consumption. As discussed
in the first section Chilled-Water Plant Basics, page 3, raising chilled-water
temperature reduces chiller energy consumption. In a constant-volume
pumping system, this may reduce system energy consumption as long as
humidity control is not lost. Humidity control may be lost if, as chilled-water
temperature is increased, the air temperature leaving the coil increases to a
point where it no longer performs adequate dehumidification.
In a variable-volume pumping system, however, raising the chilled-water
temperature increases pump energy, often substantially, and typically increases
total system energy. Before considering increased chilled-water temperature,
the system operator should calculate the increased pumping energy and
compare it with the chiller energy savings. It should be noted that ASHRAE/
IESNA Standard 90.1–19991
requires chilled-water reset for constant-volume
systems—with exceptions—but exempts variable-volume systems from this
requirement for the reasons discussed.
An often overlooked method of decreasing system energy consumption is to
reduce the chilled-water temperature, thereby decreasing pumping energy but
increasing chiller energy. This strategy is possible with adequate chiller capacity
and lift capability. Reducing chilled-water temperature may also improve
dehumidification in the building. Another result of reducing the chilled-water
temperature is increased chiller capacity during times when the condenser
water temperature is cooler than design. This allows more time before another
chiller and its ancillary equipment are started. This option is more fully
discussed in Low ∆T syndrome, page 63.
Be aware that any change in chilled-water set point requires changes to be
made to the system chiller-sequencing algorithms to ensure that system
capacity is met. This added complication may not be warranted.

SYS-APM001-EN
Chilled-Water-Control Options
48
Critical valve reset
Often, pumps are controlled to maintain a constant-pressure differential at a
remote coil. Unless this coil serves the zone requiring the most cooling (the
critical zone), the pump provides more pressure than necessary and consumes
more power than necessary. Systems that have integrated air-side and chiller
plant control systems and contain valves with direct digital controls present an
opportunity for further pump operating-cost reduction. If a system is monitored
to determine the critical valve at each point in time, the pump’s operating
pressure can be reset so that the critical zone’s control valve is nearly open.
Integrated control allows a system-level controller to determine the critical zone
and reset the pump’s set point dynamically, therefore reducing pump operating
costs.
The controllers know the position of their individual valves, which modulate to
maintain the required water flow through the coil. The building automation
system continually monitors the valve controllers, looking for the most open
valve. The controller resets the pump set point so that at least one valve, the
one requiring the highest inlet pressure, is nearly wide open. The result is that
the pump generates only enough pressure to get the required water flow
through this “critical” valve, thus saving pumping energy.
Chapter references
1 BSR/ASHRAE/IESNA 90.1–1999, “Energy standard for buildings except low-
rise residential buildings,” Illuminating Engineering Society of North
America and American Society of Heating, Refrigerating and Air-
Conditioning Engineers, Inc., 1999.

SYS-APM001-EN 49
Design Considerations
Chilled-water-pump configuration
Pumps may be either on the inlet or the outlet of the chiller, as long as the inlet
of the pump experiences an adequate, positive suction pressure. In applications
where there is a significant liquid column head (for example, a high-rise
building), the pump is often located at the chiller’s outlet so that the evaporator
bundle is subject to the static head rather than the static-plus-dynamic (added
by the pump) head. The need for high-pressure water boxes on the chiller can
be eliminated.
An additional advantage of locating the pump upstream of the chiller is that if
the pump motor rejects its heat to the water, the heat can be removed directly
by the chiller. The chiller does not need to compensate for the pump heat by
making colder water.
Pump per chiller
In either a primary–secondary or variable-primary-flow system, using one
pump per chiller simplifies system hydraulics. The pump can be selected to
produce the flow and pressure drop necessary for the specific chiller. Bringing
additional pumps on changes system hydraulics, but only minimally. One
drawback of such a system is a lack of redundancy, since the pump and chiller
are dedicated to one another. This may be overcome by using a spare pump,
pipes, and valves so that the spare pump could work with any chiller during
emergency conditions.
Manifolded pumps
In an effort to resolve the redundancy consideration, some designers prefer to
manifold pumps and provide n+1 pumps, where n is the number of chillers.
Such an arrangement allows any pump to be used with any chiller. However,
system hydraulics become more complicated. Unless all piping runs and
evaporator pressure drops are equal, the amount of water flowing to each
chiller will differ. As discussed with the variable-primary-flow system,
manifolded pumps present a control challenge when chillers are sequenced.
Either pump configuration can be successful; one pump per chiller simplifies
the hydraulics, while manifolded pumps allow redundancy.

SYS-APM001-EN
50
Bypass-line sizing
Bypass lines are required in both primary–secondary and variable-primary-flow
systems. In a decoupled system, the bypass line should be sized for 110 to 115
percent of the largest chiller's design flow rate. In a VPF system, the bypass line
should be sized for the largest chiller’s minimum flow rate.
While minimal pressure loss is desirable, substantial water velocity can be
accommodated without significant pressure loss in the relatively short length of
bypass piping. The bypass line must be of sufficient length to prevent random
mixing of the supply and return water streams; a minimum length of five to ten
pipe diameters is recommended.
Amount of fluid in the loop
Two questions must be answered when determining how much fluid is
necessary to maintain proper chilled-water-system control.
n How fast can the specific chiller respond to changing conditions?
n How fast can the system respond to changing conditions?
The amount of fluid the loop requires to operate properly is related to the larger
of these two answers. Note that both answers describe an amount of time.
Required Volume = Flow Rate × Loop Time
Where:
n Required Volume = the amount of fluid in the coil, pipes, evaporator barrel,
storage tank, etc., in gallons [liters]
n Flow Rate = the system flow rate, in gpm [lps]
n Loop Time = the time it takes for fluid to leave the chiller, move through the
system and return to the chiller, and allow for stable system operation, in
minutes [seconds]

SYS-APM001-EN 51
Chiller response to changing conditions
Follow the manufacturer's advice for the specific chiller being considered. This
determines the absolute minimum amount of water the loop requires. However,
this is the chiller minimum, not the system minimum, as discussed in the next
section. Many of today's chillers have controls that respond quickly to changing
conditions. Some chillers can react to a change in return water temperature in
one minute; other chillers may require five or more minutes to react. The
response varies, depending on chiller type and design.
System response to changing conditions
It is important to understand that even if a chiller can respond to rapidly
changing conditions, the interaction between the chiller, system pumps, and
control valves may define the minimum loop time. These components may
“hunt” if the system conditions change too rapidly. Review these interactions to
ensure that system control will be stable.
Example:
A specific chiller requires at least two minutes of water in the loop to operate
properly. However, after considering the system interaction, it’s decided that a
five-minute loop time will work best. The system flow rate is 960 gpm [60.6 lps].
Required Volume (R.V.) = 960 gpm × 5 minutes = 4,800 gallons
[R.V. = 60 lps × 5 minutes × (60 seconds/1 minute) = 18,180 liters]
If the volume of fluid in the evaporator bundle, piping, and coils is less than the
required volume, a tank should be added to increase loop volume. For optimal
stability, the tank should be placed in the return water position and be designed
to mix the returning-water stream with the water currently in the tank.
Plant expansion
Plant expansion can be performed easily in either a primary–secondary or
variable-primary-flow system by adding another chiller and pump to the
system. The two major considerations will be whether the chilled-water
distribution pipes will be able to handle the flow and how to install the new
chiller while other chillers are still providing cooling. When the new system
flow rate complies with good piping practice and the pumps can deliver the
water, the process works well. To maintain chilled-water flow during installation
of a new chiller, some plants are constructed with piping stubs in place for the
new chiller. In this way, the new chiller can be installed while the system is still
operating, then the valves in the stubs can be opened.

SYS-APM001-EN
52
When decoupled systems are used on large campus-type systems, added loads
are often located some distance away from the original loads. Yet, planners like
the idea of somehow hooking the new loads to the existing system. The double-
ended system shown in Figure 19 is one way of handling this requirement. A
second production facility is placed at a convenient location in the new part of
the campus. Its distribution plant is laid out as a mirror image of the original
piping, and connects to it at the ends of each system.
This way, either production loop can feed into the now common distribution
loop. The point of no-flow simply floats as the two production plants are
loaded. If, at very low seasonal loads, the operators want to secure one entire
production loop, it is not a problem if the on-line plant has adequate production
and distribution capacity. With full-time plants, this tactic can be used to reduce
operating expenses significantly for many weeks of the year. Further, it permits
preferential loading of the newer, more efficient machinery.

SYS-APM001-EN 53
Figure 19 Double-ended decoupled system
Chiller 2
Chiller 1
Chiller 3
Check Valves
Existing Plant
New Plant
Loads
Existing Bypass Line
New Bypass Line
Production
Distribution

SYS-APM001-EN
54
Chilled-Water System Variations
A number of chilled-water system variations can and should be used when
appropriate. Each configuration offers specific advantages to solve problems
and add value to the system.
Heat recovery
ASHRAE/IESNA Standard 90.1–19991
now requires heat recovery in specific
applications. Indoor air quality concerns have spurred the use of systems that
subcool supply air to dehumidify, then temper, the air to satisfy space
conditions. ASHRAE/IESNA Standard 90.1–1999 also limits the amount of new
reheat energy used in these applications. With these drivers, and energy costs,
there has been a resurgence of heat recovery chillers. The example on page 57
describes a cost-effective recovered-heat scheme. This scheme is commonly
used for service-water heating in resort hotels and for certain process loads.
Preferential loading
Preferential loading is desirable for systems that use heat recovery since the
heat recovery chiller may remain more fully loaded, thus producing more heat
that can be recovered for the desired process. Preferential loading may also be
beneficial for use with either a high-efficiency chiller that should be fully loaded
whenever possible, or a chiller using a fuel other than electricity, such as an
absorption chiller using waste steam from a cogeneration plant or a chiller
coupled with an engine that generates electricity. When used with the latter, the
system is able to preferentially load the alternate fuel chiller when the cost of
electricity is high.

SYS-APM001-EN 55
Parallel arrangement
If a chiller, in a decoupled system, is moved to the distribution side of the
bypass line, system hydraulics, and temperatures, the chiller is preferentially
loaded when it is turned on. As shown in Figure 20, Chiller 1 always sees the
warmest system water and is preferentially loaded. As previously discussed,
chillers on the production side of the bypass line (Chillers 2 and 3) will be
loaded to equal percentages.
Figure 20 Parallel preferential loading arrangement
One caveat when applying this arrangement is that chillers on the production
side of the bypass line will run more often at low part-load conditions. Older
chillers or newer chillers that have a high cycle point may not have this
capability.
Chiller 3
Chiller 2 Production
Distribution
Bypass Line
Chiller 1
Preferential
Loading
Loading
Equal
Percentage

SYS-APM001-EN
56
Sidestream arrangement
Figure 21 Sidestream preferential
aaaaaaaa aaloading arrangement
Figure 21 shows a simple modification to the traditional decoupled
arrangement. The sidestream arrangement assures that the chiller piped in the
sidestream position receives the warmest entering-water temperature and can
fully load it whenever the chiller plant operates.
This arrangement is unique because it not only allows preferential loading, but
it also permits the cooling device (chiller, heat exchanger, etc.) in the sidestream
position to operate at any temperature change. This configuration precools the
system-return water for the chillers downstream, reduces their loads and
energy consumption, and decreases the overall operating cost of the chilled-
water plant.
When cooling devices are located in the return piping of the distribution loop,
they do not contribute to system demands for flow. They simply reduce the
temperature of return water to the production loop. While this is counter-
productive to the principle of striving for the highest possible return water
temperature, it is often the best way to obtain free cooling, specialized heat
recovery, or reduce the capital cost of ice storage equipment.
Sidestream, decoupled applications are usually most economical when the
sidestream chiller is smaller than those on the production side of the bypass
line. Since pumping requirements and energy consumption change with
modifications to the system arrangement, it is best to use a computerized
analysis tool to model the economic effects.
Following are three different system configurations that can benefit from the
sidestream application.
Chiller 3
Production
Distribution
Chiller 2
Bypass Line
Chiller 1
Sidestream position receives
the warmest return water.

SYS-APM001-EN 57
Figure 22 Plate-and-frame heat
ffffffffffffhhfffexchanger
Plate-and-frame heat exchanger
A free-cooling heat exchanger8
may be capable of chilling water to only 48°F
[8.9°C] during some periods. Rather than overlook this portion of cooling
capacity assistance, the heat exchanger does whatever it can to its portion of
the total return stream. Chillers operating downstream can reduce chiller-water
temperature further, allowing simultaneous free cooling and mechanical
cooling. This configuration increases the hours that the heat exchanger may be
used. Since this capacity is brought to bear on the warmest water in the
system, it has the greatest impact.
Heat recovery
A similar situation occurs if a heat-recovery chiller is placed in this sidestream
position
5
(see Figure 22). This chiller may be equipped with a heat recovery
condenser or it could be a standard, single-condenser chiller operating as a
heat pump. The chiller may not be capable of cooling water to the system
supply temperature. That is unimportant with this configuration. Think of the
machine as a heater instead of a chiller. Its primary function is heating, and
cooling is a beneficial by-product. The passing return-chilled-water stream
appears as an infinite heat source to the heat recovery chiller. The chiller only
cools its evaporator water enough to satisfy the heating demand. This avoids
the control predicament of deciding how to reject surplus condenser heat when
the cooling and heating loads of a chiller do not strike a perfect heat balance.
Optional fuels
An absorption chiller may be applied in a sidestream location. This allows the
chiller to be loaded whenever utility rates make it beneficial. It also ensures the
absorption water chiller the warmest entering-water temperature, allowing it to
operate more efficiently and produce more cooling.
System control
The flexibility of sidestream applications is increased by the fact that the
devices are used to precool return water, not to produce the system chilled-
water temperature. This means that they may be loaded by a different signal. In
the case of a plate-and-frame heat exchanger, as long as return water is being
cooled, there is an advantage to using it. A heat-recovery chiller can be loaded
to produce just the amount of hot water necessary using the condenser-water
leaving temperature as a signal. If preferential loading is used with an
absorption chiller, it may be loaded simply by decreasing its leaving-water
temperature.
Chiller 2
Chiller 1
Plate-and-frame
Bypass Line
heat exchanger
Distribution
Production

SYS-APM001-EN
58
Unequal chiller sizing
Many designers seem to default to using the same capacity chillers within a
chilled-water plant.2,3
There are benefits to sizing chillers to meet the system
loads. One is that when a chiller is brought on line, so is its ancillary equipment,
thus increasing system energy consumption. In general, the smaller the chiller,
the smaller the ancillary equipment. Another is being able to ensure that
chillers are efficiently loaded. Many times this can be accomplished by using
chillers that do not have the same capacity. Examine the use of 60/40 splits (one
chiller at 60 percentage system capacity, the other at 40 percent) or 1/3–2/3
splits (one chiller at 1/3 of system capacity the other at 2/3). The benefit is that
the system load can be more closely matched with the total chiller capacity,
increasing total system efficiency.
Series–counterflow application
Another system configuration that can be very energy efficient incorporates the
previously described series application, but does so for both the chilled water
and condenser water. Figure 23 shows such a configuration.
Note that the downstream machine, in this case, produces 40°F [4.4°C] chilled
water, while the upstream machine produces 50°F [10°C] chilled water. The
downstream machine receives 85°F [29.4°C] condenser water, while the
upstream machine receives 95°F [35°C] condenser water. Therefore, the
pumping requirements are only 1.2 gpm/ton on the chilled water side and 1.5
gpm/ton on the condenser water side—greatly reducing pumping costs.
The configuration has the effect of equalizing each chiller’s required lift, as
shown in Figure 23a. The chilled- and condenser-water flow directions are
opposite, or counter, to one another. Thus the name, series-counterflow.
The series–counterflow configuration
can work with all types of chillers.
Duplex chillers are shown in Figure 23.
A single large chiller may be built as a
duplex machine. The evaporator and
condenser water circuits are common
to both halves of the duplex. Increased
efficiency comes from the separation
of the compressors and refrigerant
circuits. Thus, each half is redundant
for increased system reliability.

SYS-APM001-EN 59
Figure 23 Series–counterflow arrangement
Figure 23a jjjEqual lift concept
Upstream Chiller Downstream Chiller
95 °F [35°C]
105 °F [40.6°C]
60 °F [15.5°C]
85 °F [29.4 °C]
40 °F [4.4°C]
50 °F [10°C]
}
40°F
40°F
Series-
Single
Compressor
Chiller
95°F
105°F
Upstream Chiller
Downstream Chiller
105°F
65°F [36.1°C]
55°F [30.6°C]
55°F [30.6°C]
50°F
[40.6°C]
[40.6°C]
[10°C]
[4.4°C]
[35°C]
[4.4°C]
Arrangement
Counterflow

SYS-APM001-EN
60
Applications outside the chiller’s range
Designers may wish to use chillers to provide cooling for which the flow rate or
temperature requirements are not within the ranges of a particular chiller, even
though the chiller has adequate capacity. This often occurs with manufacturing
processes. Let’s look at two examples showing system designs that can satisfy
the desired conditions.
Flow rate out of range
A plastic injection molding process requires 80 gpm [5.1 lps] of 50°F [10°C]
water and returns that water at 60°F [15.6°C]. The selected chiller can operate at
these temperatures, but has a minimum flow rate of 120 gpm [7.6 lps]. The
following system in Figure 24 can satisfy the process. Decoupling the chiller
from the process load allows the water flow to be different, ensuring that the
flow through the chiller is within acceptable limits. With a single chiller system,
one pump and a three-way valve gives the same results.
Figure 24 Flow rate out of range for equipment
Constant Volume Pump
50°F [10°C]
40 gpm [2.3 lps]
56.7°F [13.7°C]
50°F [10°C]
120 gpm [7.6 lps]
120 gpm [7.6 lps]
80 gpm [5.1 lps]
120 gpm [7.6 lps]
50°F [10°C]
Constant Volume Pump
80 gpm [5.1 lps]
Process
Load
Chiller
Bypass
Pipe
60°F [15.6°C]

SYS-APM001-EN 61
Temperatures out of range
A laboratory load requires 120 gpm [7.6 lps] of water entering the process at
85°F [29.4°C] and returning at 95°F [35°C]. The accuracy required is more
precise than the cooling tower can provide. The selected chiller has adequate
capacity, but a maximum leaving-chilled-water temperature of 60°F [15.6°C].
Using a pair of bypass pipes allows the mixing valve to supply the proper
temperature to the process load and maintains acceptable water flow rates and
temperatures through the chiller. In the example shown in Figure 25, the chiller
and process flow rates are equal, although this is not a requirement. For
example, if the chiller had a higher flow rate, more water would bypass and mix
with the warm return water.
Figure 25 Temperatures out of range for equipment
An example of a process application layout where the required temperature
control tolerance is more precise than the chiller controls allow is shown in the
Figure 26.
For example, when Chiller 2 is turned on, it takes a certain amount of time to
reach its supply-temperature setpoint. The dedicated control valve remains
closed and water is bypassed until Chiller 2 reaches its setpoint, which keeps
the water temperature supplied to the process within tolerance. When Chiller 2
reaches its setpoint, the control valve opens.
This design requires a different chiller-sequencing strategy than the standard
decoupled system. Water must not be allowed to bypass from the return side to
the supply side, since this will cause the temperature of the water supplied to
the process to vary outside the tolerance. Set the system controls to turn on
Chiller 2 before deficit flow occurs.
Constant Volume
Constant Volume
60°F [15.6°C]
120 gpm
70°F [°C]
120 gpm
95°F [35°C]
120 gpm [7.6 lps]
120 gpm [7.6 lps]
120 gpm [7.6 lps]
85°F [29.4°C]
35 gpm [2.2 lps]
95°F[35°C]
60°F [15.6°C]
95°F[35°C]
85 gpm [5.4 lps]
85 gpm
60°F[15.6°C]
35 gpm [2.2 lps]
Process
[7.6 lps]
[7.6 lps]
5.4 lps]
Load
Chiller
Pump
Pump
Mixing
Valve
Bypass
Pipes

SYS-APM001-EN
62
Figure 26 Precise temperature control, multiple chillers
Chapter references
1 BSR/ASHRAE/IESNA 90.1–1999, “Energy standard for buildings except low-
rise residential buildings,” Illuminating Engineering Society of North
America and American Society of Heating, Refrigerating and Air-
Conditioning Engineers, Inc., 1999.
2 Eppelheimer, D., P
.E. and Bradley, B.; “Chilled-Water Plants
and…Asymmetry as a Basis of Design,”Engineers Newsletter, Volume 28,
No. 4, The Trane Company, October 1999.
3 Landman, W. and Bradley, B.; “Off-Design Chiller Performance,” Engineers
Newsletter, Volume 25, No. 5, The Trane Company, December 1996.
4 Trane Applications Engineering Group, “A New Era of Free Cooling,”
Engineers Newsletter, Volume 20, No. 3, The Trane Company, 1991.
5 Trane Applications Engineering Group, “Two Good Old Ideas Combine to
Form One New Great Idea,” Engineers Newsletter, Volume 20, No. 1, The
Trane Company, 1991.
Chiller 2 Chiller 1
Variable-Speed
Pump
Bypass
Process
Control
Valves
Load

SYS-APM001-EN 63
Chilled-Water System Issues
Low ∆T syndrome
During the past several years the “low ∆T syndrome” debate has raged.1,3
The
symptom of the problem is that, in large systems, return-water temperature is
too low, thus not allowing the chillers to fully load. Many system operators
simply turn on more chillers to satisfy flow requirements. Some system
designers advocate putting a check valve in the bypass line—thus putting
chilled-water primary and secondary pumps in series and varying the flow
through chiller evaporators. Other designers install primary pumps that are
larger than necessary and “overpump” chillers at part-load conditions. These
solutions are all “band-aids” and do not treat the source of the problem.
Coad2
points to the fact that a properly operating hydraulic system will work as
designed and explains the fallacies in the check valve and overpumping
approaches. Taylor5
recommends that a number of mitigating procedures be
implemented to eliminate the problem. They include:
n Eliminate three-way valves
n Ensure that airside control is not causing the problem
n Properly maintain the system, including regular air filter changes, coil
cleaning, control calibration, and proper setpoints
Before applying band-aid approaches to “fix” symptoms such as low ∆T
syndrome, ensure that the system is operating properly using some or all of the
procedures Taylor5
discusses. In addition to these procedures, simply reducing
the chilled-water supply temperature will have the effect of raising the system
return-water temperature in systems using two-way valves.
Check valve in the bypass line
Some designers recommend the installation of a check valve in the bypass line
of a primary–secondary system to eliminate the possibility of deficit flow in the
bypass line. The premise is that if there is a system problem (low temperature
differential), the check valve will put the primary and secondary pumps in series
and pump more water through the chiller, thus balancing the primary and
secondary flow requirements. This is not universally accepted. Coad
2
states,
One constraint is that if the system is designed as variable flow and is
experiencing operating problems related to low return water
temperatures, the solution is not in the plant but rather in the load.
and

SYS-APM001-EN
64
One solution that has been suggested is to install a check valve in the
plant common pipe or decoupling line circuit … However, to be
realistic, all that the check valve can do is assure that no water
bypasses the chillers, which in turn has the effect of increasing flow in
the chiller. Thus with the installation of the check valve must be an
algorithm to either slow down system pump(s) when flow increases
beyond the design maximum for the on chiller or turn on additional
chillers. Thus the check valve solution offers its own problems and
many designers feel very uncomfortable with forcing pumps into
series operation without the benefit of understanding the full impact
thereof.
This manual does not recommend the use of check valves in the bypass line.
Failure recovery
Figure 27 Failure recovery With all the varied approaches available to potential customers, it sometimes
seems that the main idea gets lost. People purchase chilled-water plants to
reliably produce chilled water to satisfy another need, such as comfort or
process cooling. Therefore when the plant operates there must be a process in
place to recover from the failure of a chilled- or condenser-water pump, cooling
tower, or chiller. Failure recovery should be integral to the chilled-water plant
control system. Refer to Figure 27. If the control sequence tries to start Chiller 2
and its pump, but the pump has an electrical malfunction, the sequence should
immediately lock out Chiller 2 and its pump. The control system should then
attempt to start Chiller 3 and its pump. At the same time, the control system
should send a pump malfunction alarm to the system operator.
Alternative energy sources
Energy source redundancy is receiving increased attention due to rate
variations and reliability issues brought about by the deregulation of electrical
utilities across the country. There are two basic approaches to meet these
issues:
n Provide an alternate source of internally-generated electricity to serve a
system in the event of general failure or an unacceptably high temporary
cost of electricity (time-of-day rates).
n Provide an alternate source of chilled-water producing capability, possibly
fueled by natural gas, another fossil fuel, or even using low cost electricity
as an alternative energy source.
Chiller 3 Start
Chiller 2 Unavailable
Chiller 1 Running
Bypass Line
Return Supply

SYS-APM001-EN 65
Electricity generation
The design, construction, and operation of full-capacity, electrical-generation
systems is well understood. The electrical-generation capacity can be sized to
allow an entire facility to operate or it can be sized for an emergency situation.
Electrical generation can be outsourced to avoid internal capitalization.
A variation of electrical generation uses an engine indirectly- or directly-
coupled to a chiller. Either variation produces chilled water using an alternative
fuel such as natural gas or fuel oil. The indirect-coupling method allows the
chiller to operate using an alternative fuel or electricity from the grid. An engine
directly-coupled to a chiller can only run using the alternative fuel.
Alternative fuel
Some designers prefer to employ chillers that use fossil fuels. Examples are
absorption chillers using natural gas, steam, or hot water. Plants with these
chillers, discussed in detail elsewhere
4
, allow the owner to take advantage of
permanently expected fuel rate separations.
Thermal storage
Another successfully applied alternative-energy source is thermal storage.
Chillers make either ice or chilled water during times of decreased electricity
costs. The energy is stored in tanks and then discharged to satisfy cooling loads
during times of high electrical costs. Other manuals describe the use of thermal
storage in detail. 6,7,8,9
Use any of these technologies to provide value to the building owner through
judicious use of alternative fuels.

SYS-APM001-EN
66
Contingency
In addition to failure recovery, it may be wise for plant designers to work with
building owners to develop a contingency plan for chilled water in the case of
emergency shutdown or an extended breakdown. Often this is critical for
process cooling applications. Such a plan can include working with suppliers to
establish a short lead-time on equipment leasing. When equipment leasing is
combined with, for example, piping stubs built into the chilled-water system for
quick connection, a contingency plan can be put into action quickly and the
system can produce chilled water again in a short period of time.
Cooling contingency planning
Today, many organizations have contingency plans for critical areas of their
business. Some deal with natural disasters and others with the loss of power in
critical areas. However, few have actually taken the time to think about what a
loss of cooling would mean to their facility. If the cooling system failed or was
suddenly grossly undersized due to weather, etc., how would that affect
business? What financial risk would be involved with a loss of cooling?
Cooling contingency planning is intended to minimize the losses a facility may
incur as a result of a total or partial loss of cooling. It allows a building owner to
act more quickly by having a plan in place and by proactively preparing his or
her facility to accept temporary equipment. Although a number of facilities are
prepared after the construction phase, the construction phase provides an easy
and cost-effective opportunity to prepare a facility and is a logical time to
provide water stubouts and electrical connections. This helps to keep costs
down and reduces the need to shut down existing equipment to make
necessary building preparations.
Cooling contingency planning is the process of preparing for a loss of cooling
while in a nonemergency situation. This allows common sense, rather than
panic, to prevail during a critical event. The following topics are general and
broad in scope. They provide a sense of what is involved in the planning
process. Contingency planning itself is very detailed and situation-specific.
Minimum capacity required It is important to first identify the minimum
capacity required. With multiple chillers in a facility, it may be acceptable to
have less tonnage in an emergency situation. For example, a facility’s chiller
plant may consist of 1,800 tons [6,330 kW], but the minimum tonnage required
may only be 1,200 tons [4,220 kW]. Therefore, it is also important to identify the
plan of action if Chiller 1 fails, if Chiller 2 fails, if Chillers 2 and 3 fail, and so on.

SYS-APM001-EN 67
Type and size of chiller The type and size of contingency cooling required
by a facility are determined by several factors. In turn, the choice of chiller
determines how the facility is prepared. Examples of parameters that determine
the chiller are:
n Electrical requirements
n Ease of installation (air-cooled chillers are easier to set up)
n Location or available space
n Comfort or process cooling
Location of equipment Location can be a major factor in contingency
planning. When selecting the location of the temporary equipment it is
important to consider:
n Water and electrical connections location
n Sound sensitive areas in the facility
n Location easily accessible to service staff
n Equipment separated from the public
Water and electrical connections
n Water connection size requirements
n External stubout locations
n Sufficient power to run the temporary unit
n Possible generator requirement
Ancillary equipment
n Pumping system requirements
n Temporary hose requirements
n Electrical cable requirements
This section briefly describes some of the items to consider when establishing a
cooling contingency plan. Keep in mind that there may be other considerations,
depending on the application.

SYS-APM001-EN
68
Chapter references
1 Avery, G., P
.E.; “Controlling Chillers in Variable-Flow System,” ASHRAE
Journal, February 1998. pp. 42-45.
2 Coad, W.J., P
.E.; “A Fundamental Perspective on Chilled-Water Systems,”
Heating/Piping/Air Conditioning, August 1998, pp. 59-66.
3 Kirsner, W.; “The Demise of the Primary-Secondary Pumping Paradigm for
Chilled-Water Plant Design,” Heating/Piping/Air Conditioning, November
1996.
4 Schwedler, M., PE and Brunsvold, D., Absorption Chiller System Design,
SYS-AM-13, The Trane Company, May 1999.
5 Taylor, S. T.; “Degrading Delta-T in New and Existing Chilled Water Plants,”
Cool $ense National Forum on Integrated Chiller Retrofits, Lawrence
Berkeley National Laboratory and Pacific Gas & Electric, September 1997.
6 Trane Applications Engineering Group, “Thermal Storage - Understanding
Its Economics,” Ice Storage Systems, Engineered Systems Clinics. ISS-CLC-
1, The Trane Company, 1991.
the Choices,” Ice Storage Systems, Engineered Systems Clinics. ISS-CLC-2,
The Trane Company, 1991.
System Design,” Ice Storage Systems, Engineered Systems Clinics. ISS-
CLC-3, The Trane Company, 1991.
9 Trane Applications Engineering Group, “Thermal Storage–Understanding
Control Strategies,” Ice Storage Systems, Engineered Systems Clinics. ISS-

SYS-APM001-EN 69
Condenser-System Variations
Water-cooled chillers require condenser-water-system variations to be
considered. For a discussion of condenser-water temperatures and flow rates
refer to the section, Chilled-Water-Plant Basics, page 3. Since air-cooled-chiller
condenser controls are part of the chiller design, they are not discussed in this
manual.
To ensure optimum heat transfer performance, the condenser-heat transfer
surfaces must be kept free of scale and sludge. Even a thin deposit of scale can
substantially reduce heat transfer capacity and chiller efficiency. Specifics of
cooling-tower-water treatment are not discussed in this manual. Engage the
services of a qualified water treatment specialist to determine the level of water
treatment required to remove contaminants from the cooling tower water.
Condenser flow configurations
Most importantly, the inlet to the pump must be under sufficient net positive
head. This often means locating the pump below the cooling-tower sump.
Single tower per chiller
In some applications each chiller has a dedicated cooling tower. This is most
likely to occur when chillers, and their accompanying towers are purchased at
different times during the facility’s life—such as when additions are made.
Figure 28 Manifolded condenser-
aaaaaaaaaawater pumps
Manifolded pumps
A much-used pumping arrangement has a single cooling-tower sump with
manifolded pumps, one condenser water line, and separate, smaller, pipes for
each chiller as shown in Figure 28. This provides a number of advantages:
n Pumping redundancy
n If cooling towers cells can be isolated, any cooling-tower cell runs with
any chiller
n Hydraulics are generally less problematic than on the chilled-water side
n Cooling towers can be located remotely from chillers, with only a single
supply and return pipe to connect them
Manifolded
Load
Cooling
Pumps
Towers

SYS-APM001-EN
70
Condenser water control for transient conditions
Every chiller requires a pressure differential between the evaporator and
condenser in order to operate. The chiller must develop its pressure differential
within a manufacturer-specified time or its controls will shut it off. During some
start-up conditions, this pressure differential may be hard to produce within the
time limitation.
An example of such a condition is an office building that has been unoccupied
during a cool, clear, fall weekend. The tower sump water is at 40 °F [4.4 °C].
Monday is sunny and warm, which requires a chiller to be turned on. Since the
chiller is lightly loaded and the tower sump is large, the pressure differential
can not be reached before the chiller turns off. If the condenser flow rate for a
given chiller can be reduced, this scenario is less likely to occur. The lower flow
rate increases the leaving condenser-water temperature, condenser-refrigerant
temperature, and refrigerant pressure.
The flow reduction options include:
n Cooling tower bypass
n Chiller bypass
n One or two throttling valves in the condenser-water pipe with the pump
riding its curve
n A variable-speed condenser water pump
After the minimum-pressure differential is reached, the flow may be increased
as long as that minimum-pressure difference is maintained. Some designers
and operators become concerned with possible fouling of condenser-water
tubes during these start-up conditions. There is little to fear due to the short
duration of reduced flow operation and the limited occurrences. The
advantages and disadvantages of these options are discussed in a variety of
publications.
1,5

SYS-APM001-EN 71
Cooling-tower-fan control methods
Cooling towers operate to produce the sump water temperature. As the heat-
rejection load and ambient wet-bulb tempersture change, the cooling tower
fans must move more or less air to produce the desired water temperature.
Cycling a single fan
Cycling a single fan on and off is one method to maintain rough water
temperature control. Since airflow changes greatly between fan speeds, so
does heat rejection. Temperature swings of 7 °F to 10 °F [3.9°C to 5.6°C] are not
uncommon. Some chillers, especially older chillers with pneumatic controls,
may operate poorly in response to these changing temperatures. Care must
also be taken to ensure that the fan does not cycle too often and damage the
motor, drive, or fan assembly.
Two-speed fans
The installation of two-speed cooling tower fans is an option used frequently to
reduce temperature swings. Typically, the low fan speed is between 50 and 70
percent of full speed. Since the heat rejection changes roughly in proportion
with the fan speed, the temperature swing will be only 50 to 75 percent of
cycling a single fan. Again, care should be taken not to cycle too often between
speeds—or the gear box may incur excessive wear and fail. A distinct
advantage of two-speed fans is that at low speed, the fan power is greatly
reduced. Since the fan power varies with the cube of the speed (approximately)
the power at half speed is about 15 percent of full speed.
“Pony” motors
Another option offered by cooling-tower manufacturers is to have two separate
motors available to drive the fan. The smaller motor is referred to as a “pony”
motor. It operates at two-thirds of the full speed and uses about 30 percent of
the full speed power. While controlling the tower, it is important to minimize
cycling between speeds.
Variable-speed drives
Using variable-speed drives on cooling-tower fans offers two distinct benefits.
First, the tower-water-temperature control is extremely good. Second, the fan
power varies with the cube of the speed, so there is great potential for energy
savings. Variable-speed drives also allow the fan speed to be changed without
fear of gear box or motor wear. They may also offer acoustical advantages by
significantly lowering sound power at reduced speeds.

SYS-APM001-EN
72
Plate-and-frame heat exchanger
As previously discussed in the section Chilled-Water-System Variations, page
57, a plate-and-frame heat exchanger may be used in conjunction with a cooling
tower to provide cooling during very low wet-bulb temperature conditions.
When it is to be used for these purposes, designers often specify a cooling
tower larger than necessary for design conditions so that it can be used for
many hours with the plate-and- frame heat exchanger.
Well, river, or lake water
There are times when well, river, or lake water will be pumped through the
condenser. In these cases, an examination should be undertaken to balance the
cost of pumping the water with the benefit the chiller gets when more water
passes through its condenser. The environmental limitations imposed by local
codes are another consideration. Some locales will not allow well water to be
dumped after being used. Other local authorities limit the maximum water
temperature that may be returned to a body of water. Flow rates need to be
carefully selected to balance the economic and environmental requirements.
Condenser-water temperature control
Chiller–tower energy balance
The subject of condenser-water temperature control has been studied by a
number of people. In recent years, Braun and Didderich
2
; Hydeman, Gillespie,
and Kammerud
3
; and Schwedler
4
have all independently noted that balancing
chiller and cooling-tower energy is important. Hydeman, et al., showed that at
various loads and ambient conditions, the optimal condenser-water
temperature for a specific chilled-water plant depends on both chiller load and
ambient conditions, see Figure 29. All the studies showed that during many
points of operation, the optimal condition is not the lowest water temperature
the cooling tower can produce. It is important for the system designer and
operator to examine the use of system-level controls to set the tower-sump-
temperature setpoint to reduce the sum of chiller-plus-tower energy. This
optimal chiller-tower control can be automated by a chiller-plant management
system.

SYS-APM001-EN 73
Figure 29 Chiller–tower energy consumption
Figure 29 from Hydeman, et al., used with permission.
Condenser-water pump options
Chiller–pump balance
There are times when a system designer may choose to vary the condenser
water flow in addition to, or instead of, the cooling-tower fan speed. This may
be beneficial in systems with high pumping power. If a variable-speed drive is
installed, the flow may be reduced and the pump power can be reduced
substantially— approximately with the cube of the speed. Attempting to vary
both the pump and the tower fan speeds is complex and requires adequate
time for design and implementation.
Coldest condenser water that the
tower can produce at this load
and wet-bulb temperature
Highest cooling capacity
available at this condenser-
water temperature

SYS-APM001-EN
74
Variable flow limitations
Care should be taken to keep the flow through the condenser above the
minimum allowable flow rate for the chiller’s condenser. The operator should
regularly log the condenser approach temperature (the temperature difference
between the condenser’s refrigerant temperature and the condenser-water
leaving temperature) to ensure that the tubes are not becoming fouled. The
approach temperature may be monitored using a chiller plant management
system.
Tower and/or tower nozzle design can affect the allowable condenser-water
flow. If the flow drops below the manufacturer’s specified limit, the water is no
longer evenly distributed over the tower fill. This results in a decrease in
cooling-tower heat-transfer effectiveness. In extreme cases, it can also result in
water freezing in the cooling tower. If variable tower flow is a consideration,
contact the cooling-tower manufacturer to determine the flow limit and
possibly choose nozzles or cooling-tower configurations that can handle
variable-water flow.
Figure 30 Decoupled condenser-
XXXXXXXXwater system
Decoupled condenser-water system
To overcome possible problems with variable-water flow across a cooling
tower, some designers decouple the condenser-water system as shown in
Figure 30. This arrangement allows energy optimization through a reduction of
pumping power without excessively complicating the system. Because cooling
towers work best with full water flow over the transfer media, a separate
wetting (recirculation) pump provides a constant flow of water through the
tower. This is a low energy pump, as very little lift is required.
Dedicated, variable-flow condenser pumps (CDWP-1 and CDWP-2) permit a
reduction in the pumping energy whenever the temperature of condenser
water results in an unproductive reduction of condenser refrigerant pressure.
While the number of dedicated pumps may seem complicated at first,
remember the number of valves and controls that are eliminated.
Cooling Tower Fan (Inverter)
Cooling
Tower
Water Sump
Tower Water
Recirculation
Pump
Chiller 2
Chiller 1
(Inverter)
(Inverter)
CDWP-1
CDWP-2

SYS-APM001-EN 75
Retrofit opportunities
A tremendous retrofit opportunity can be realized if the low-flow concepts
discussed earlier in the section Chilled-Water-System Options, page 20, are
utilized. Building owners may need to increase the capacity of an existing
system, for example in response to a building addition. In many of these
buildings, the condenser water system (piping, pump, and tower) is in good
condition, but is considered to be too small. By changing from traditional
design conditions, the existing infrastructure can often be used while still
providing additional capacity.
Keep in mind that a cooling tower is not limited to a specific tonnage. A cooling
tower is a heat exchanger that exchanges heat between the entering water
temperature and the ambient wet bulb. By varying the flow or the temperature,
the tower capacity can be changed—often increased. An example can easily
show this.
Example A hospital presently has a 450-ton [1,580-kW] refrigeration] chiller
that needs to be replaced. The condenser water flow is 1,350 gpm [85.2 lps].
The cooling-tower selection conditions are
n entering water temperature: 95°F[35°C]
n leaving water temperature: 85°F[29.4°C]
n ambient wet bulb: 78°F [25.6°C]
Recently, the cooling-tower fill was replaced. The tower, condenser water
piping, and pump are in good condition. The hospital is planning an addition
with 50 percent more load for a total of 675-tons [2,370-kW]. Must the hospital
replace the condenser water system? The answer is “no”
, as long as the chiller
is selected properly.
How is this possible? As long as the new chiller’s condenser-water pressure
drop is at or below that of the present chiller, the same amount of water can still
be pumped. With the same flow rate, a 675-ton [2,370-kW] chiller may be
selected with a condenser-water-temperature rise of approximately15°F [8.3°C].
Using the cooling- tower manufacturer’s selection software, the same cooling
tower can be selected at the elevated temperature difference. As shown in
Figure 31, the new selection point will be:
n entering water temperature: 103°F [39.4°C]
n leaving water temperature: 88°F [31.1°C]
n ambient wet bulb: 78°F [25.6°C]

SYS-APM001-EN
76
It quickly becomes evident that the same cooling tower and flow rate are
adequate to reject more heat, in this case, approximately 50 percent more heat.
The design engineer can often help reduce total project costs using the existing
infrastructure and selecting a chiller with a higher temperature differential.
Figure 31 Chiller–tower selection with different chiller capacities
:
:
:
Water Temperature (°F)
90
85
80
75
70
65
60 70 80
55 65 75
10°F [5.6°C] ∆
15°F [8.3°C] ∆
Cooling-Tower
15°F [8.3°C] Range
10°F [5.6°C] Range
Design Point
Wet-Bulb Temperature (°F)

SYS-APM001-EN 77
Chapter references
1 “Condenser-Water Temperature Control for CenTraVac™ Centrifugal Chiller
Systems,” CTV-EB-84, The Trane Company, May 1997.
2 Braun, J.E. and Diderrich, G.T. “Near Optimal Control of Cooling Towers for
Chilled-Water Systems.” ASHRAE Transactions, 96(2):806-13.1990.
3 Hydeman, M., Gillespie, K., and Kammerud, R. “CoolTools Project: A Toolkit
to Improve Evaluation and Operation of Chilled Water Plants.” Cool $ense
National Forum on Integrated Chiller Retrofits, Lawrence Berkeley National
Laboratory and Pacific Gas & Electric, September 1997.
4 Schwedler, M., PE, and Bradley, B.; “Tower Water Temperature–Control It
How???” Engineers Newsletter, Volume 24, No. 1, The Trane Company,
1995.
5 “Water-Cooled Series R Chiller - Models RTHB & RTHC Condenser Water
Control,” RLC-EB-4, The Trane Company, August 1999.

SYS-APM001-EN
78
Conclusion
Since most chilled water systems incorporate more than one chiller, it is vital to
have a clear understanding of multiple-chiller concepts and their application.
There is nothing particularly complex about the principles involved. Instead,
system design is simply a matter of exercising a few key rules of applied
physics.
A myriad of choices are available for the design and operation of chilled water
systems. These choices include flow rates, temperatures, system
configurations, and control options. After determining the needs and wants of
the building owner and chiller plant operator, judicious use of these choices
allows designers to provide solutions that add real value.
When applying the principles in this manual, it is important to remember the
following rules:
n Rule 1 Strive for simplicity. Simple does not always mean using the fewest
components. Simplicity is usually elegant in its ability to be universally
understood.
n Rule 2 If the system designer can explain how a design works, there is a
good chance that the system will function well. If the designer can’t explain
how the design works, there is no chance that the system will operate
efficiently.
n Rule 3 If the system operator understands the designer’s explanation of
how the system works, there is a good chance that the system will work. If
the system operator doesn’t understand the explanation, there is no chance
that the system will operate efficiently.

SYS-APM001-EN 79
Glossary
ASHRAE American Society of Heating, Refrigerating and Air-Conditioning
Engineers.
building automation system A combination of controllers and other software
products which communicate and control various mechanical systems to
enable building management. These include the heating, ventilation, and air
conditioning (HVAC) systems as well as lighting systems, access control, and
miscellaneous other devices within a building. Also called a building
management system (BMS).
chilled water Also know as leaving-chilled-water or leaving-evaporator-water;
the cold water produced by the chiller (flowing through the tube bundle in the
evaporator) and pumped to the air handler coils throughout the building.
Within the evaporator, refrigerant surrounds the tube bundle and accepts heat
from the return chilled water.
chiller An air-conditioning system that circulates chilled water to various
cooling coils in an installation.
coil An evaporator or condenser made up of tubing either with or without
extended surfaces (fins).
condenser The region of the chiller where refrigerant vapor is converted to
liquid so that the temperature and pressure can be decreased as the refrigerant
goes into the evaporator.
condenser water, leaving See cooling water.
cooling tower water See cooling water.
cooling water Also known as tower water, leaving-cooling water, leaving-
condenser water, entering-absorber water, condenser-absorber water, entering-
cooling water, or cooling tower water; obtained from the source (tower, river,
pond, etc.) to which heat is rejected, flows through the tubes that run through
the absorber and the condenser, and is returned to the source.
In electrically driven chillers, the cooling water picks up heat only from the
condenser. In an absorption chiller, the cooling water also has to pick up heat
from the absorber. The water typically flows from the source at 85°F [29.4°C],
first to the absorber and then to the condenser (series flow). Associated water
temperatures are referred to as entering-absorber-water temperature (or
leaving-tower-water temperature) and leaving-condenser-water temperature
(or entering-tower-water temperature).
COP Coefficient of Performance; cooling effect divided by heat input
(dimensionless); the reciprocal of efficiency.
direct digital control Programming used by building control systems to
control variable outputs, such as valves or actuators. In the HVAC industry, DDC
means direct digital control by a microprocessor controller with no
intermediate device.

SYS-APM001-EN
Glossary
80
evaporator The region in the chiller where the system chilled water is
continuously cooled down by flashing the refrigerant to vapor in a deep
vacuum as it picks up heat from the returning system water.
fouling Deposits of foreign material in the water side of tubing in refrigeration
condensers or chillers which affect the transfer of heat.
heat exchanger A device used to transfer heat between two physically
separated fluids.
heat transfer The movement of heat from one body or substance to another.
The three methods of heat transfer are conduction, convection and radiation.
load Any one of several output devices that are to be controlled by a building
management panel.
mechanical-compression refrigeration cycle The electrically driven chiller
makes use of an electric motor, driving a compressor to produce chilled water
for cooling. It does this via a mechanical process that uses a refrigerant for a
working fluid. Inside the vessel are pressure and temperature differentials,
where heat is absorbed at a low temperature and then rejected at a higher
temperature.
psychrometric chart A chart that shows the relationship between the
temperature, pressure, and moisture content of the air.
psychrometric measurement The measurement of temperature, pressure,
and humidity of air using a psychrometric chart.
pumps (system)
chilled water Circulates the chilled water through the evaporator section
of the chiller and then through the building coils.
cooling water Circulates the cooling water from the source through the
chiller, condenser, and back to the source.
shell-and-tube A designation for a type of heat exchangers consisting of a
tube bundle within a shell or casing. Often used in chiller condensers and
evaporators.
shell-and-tube flooded evaporators Evaporators that use water flow through
tubes built into a cylindrical evaporator with refrigerant on the outside of the
tubes.
temperature, ambient The temperature of the air surrounding the object
under consideration
temperature, wet-bulb A measure of the degree of moisture in the air. It is the
temperature of evaporation for an air sample, measured with a thermometer
that has its bulb covered by a moistened wick.
tower water See cooling water.

Glossary
SYS-APM001-EN 81
three-way valve A flow-control valve with three fluid-flow openings. It
controls constant flow through or around the load.
two-way valve A flow-control valve with two fluid-flow openings.
valve, throttling A small valve used primarily in gauge lines to shut off the
line between readings, and to throttle the line to prevent fluctuations during
readings.

SYS-APM001-EN
82
References
2000 ASHRAE HVAC Systems and Equipment Handbook, Chapter 12, Hydronic
Heating and Cooling System Design. American Society of Heating,
Refrigeration and Air-Conditioning Engineers.
2000 ASHRAE HVAC Systems and Equipment Handbook, Chapter 36, Cooling
Towers. American Society of Heating, Refrigeration and Air-Conditioning
Engineers.
ARI Standard 550/590–1998, Standard for Water Chilling Packages Using the
Vapor Compression Cycle, Air-Conditioning & Refrigeration Institute.
ARI Standard 560–1992, Standard for Absorption Water Chiller and Water
Heating Package, Air-Conditioning & Refrigeration Institute.
Avery, G., PE; “Controlling Chillers in Variable Flow System,” ASHRAE Journal,
February 1998. pp. 42–45.
Braun, J.E. and Diderrich, G.T.; “Near Optimal Control of Cooling Towers for
Chilled-Water Systems.” ASHRAE Transactions, 1990, 96(2):806–13.
BSR/ASHRAE/IESNA 90.1–1999, “Energy Standard for Buildings Except Low-
Rise Residential Buildings,” Illuminating Engineering Society of North America
and American Society of Heating, Refrigerating and Air-Conditioning Engineers,
Inc., 1999.
Coad, W.J., PE; “A Fundamental Perspective on Chilled Water Systems,”
Heating/Piping/Air Conditioning, August 1998, pp. 59–66.
“Condenser Water Temperature Control For CenTraVac™ Centrifugal Chiller
Systems,” CTV-EB-84, The Trane Company, May 1997.
Demirchian, G. H. PE and Maragareci, M. A. PE; “The Benefits of Higher
Condenser Water ∆T at Logan International Airport Central Chilled Water Plant.”
IDEA 88th Annual Conference Proceedings, 1997, pp. 291–300.
Eley, C.: Energy Analysis—Replacement of Chillers For Buildings 43, 47, and 48.
Eley Associates, CA, April 1997.
* Eppelheimer, D., PE and Bradley, B.; “Chilled Water Plants and…Asymmetry
as a Basis of Design,” Engineers Newsletter, Volume 28, No. 4, The Trane
Company, 1999.
Hougton, D., PE; “Know Your Flow, a Market Survey of Liquid Flow Meters,”
Tech Update, E SOURCE, INC., March 1996
Refer to www.trane.com/commercial/
library/newsletters.asp for copies of
newsletters with an * symbol.

References
SYS-APM001-EN 83
Hydeman, M., Gillespie, K., and Kammerud, R. “CoolTools Project: A Toolkit to
Improve Evaluation and Operation of Chilled Water Plants.” Cool $ense
National Forum on Integrated Chiller Retrofits, Lawrence Berkeley National
Laboratory and Pacific Gas & Electric, September 1997.
Kelly, D.W. and Chan, T., “Optimizing Chilled Water Plants,” Heating/Piping/Air
Conditioning, January 1999, pp. 145–7.
Kirsner, W.; “The Demise of the Primary-Secondary Pumping Paradigm for
Chilled Water Plant Design,” Heating/Piping/Air Conditioning, November 1996.
Landman, W. and Bradley, B.; “Off-Design Chiller Performance,” Engineers
Newsletter, Volume 25, No. 5, The Trane Company, December 1996.
Schwedler, M, PE, “Take It To the Limit…Or Just Halfway?” ASHRAE Journal,
July 1998, pp. 32–9.
* Schwedler, M., PE and Bradley, B.; “An Idea for Chilled-Water Plants Whose
* Schwedler, M., PE and Bradley, B.; “How Low Flow Systems Can Help You
Give Your Customers What They Want,” Engineers Newsletter, Volume 26, No.
2, The Trane Company, 1997.
* Schwedler, M., PE and Bradley, B.; “Tower Water Temperature - Control It
How???” Engineers Newsletter, Volume 24, No. 1, The Trane Company, 1995.
Schwedler, M., PE and Brunsvold, D., Absorption Chiller System Design, SYS-
AM-13, The Trane Company, May 1999.
Schwedler, M., PE and Nordeen, A.; “Low Flow Works for Absorbers Too!”
Contracting Business, November 1998, pp. 108-112.
Schwedler, M., PE, Letter to the Editor, ASHRAE Journal, April 1998, p. 30.
Taylor, S. T.; “Degrading Delta-T in New and Existing Chilled Water Plants,”
Cool $ense National Forum on Integrated Chiller Retrofits, Lawrence Berkeley
National Laboratory and Pacific Gas & Electric, September 1997.
Trane Applications Engineering Group; “A New Era of Free Cooling,” Engineers
Newsletter, Volume 20, No. 3, The Trane Company, 1991.
Trane Applications Engineering Group; “Two Good Old Ideas Combine to Form
One New Great Idea,” Engineers Newsletter, Volume 20, No. 1, The Trane
Company, 1991.

SYS-APM001-EN
References
84
Trane Applications Engineering Group, “Thermal Storage - Understanding Its
Economics,” Ice Storage Systems, Engineered Systems Clinics. ISS-CLC-1, The
Trane Applications Engineering Group, “Thermal Storage - Understanding the
Choices,” Ice Storage Systems, Engineered Systems Clinics. ISS-CLC-2, The
Trane Applications Engineering Group, “Thermal Storage - Understanding
System Design,” Ice Storage Systems, Engineered Systems Clinics. ISS-CLC-3,
The Trane Company, 1991.
Trane Applications Engineering Group, “Thermal Storage–Understanding
Control Strategies,” Ice Storage Systems, Engineered Systems Clinics. ISS-
Waltz, J. P
., PE, CEM; “Don't Ignore Variable Flow,” Contracting Business, July
1997, pp. 133–144.
“Water-Cooled Series R Chiller—Models RTHB & RTHC Condenser Water
Control;” RLC-EB-4, The Trane Company, August 1999.
Webb, R.L. and Li, W.; “Fouling in Enhanced Tubes Using Cooling Tower Water,
Part I: Long-Term Fouling Data,” International Journal of Heat and Mass
Transfer, 2000.

SYS-APM001-EN 85
Index
A
ambient conditions, effect of 10
arrangement, parallel 55
B
bypass flow control 42
bypass-line sizing 50
bypass line with check valve 63
bypass locations 43
C
chilled- and condenser-water flow rates 15
chilled- and condenser-water temperatures 13
chilled-water distribution system 7
chilled-water flow rate, effect of 3
chilled-water plants 2
chilled-water pump 8
chilled-water-pump configuration 49
chilled-water reset 47
chilled-water-system, issues 63
chilled-water temperatures 14
chilled-water temperature, effect of 3
chiller, air-cooled 2
chiller, adding a 39
chiller, adding in a VPF system 44
chiller production 32
chiller–pump balance 73
chiller range, applications outside 59
chiller response to changing conditions 61

SYS-APM001-EN
Index
86
chiller sequencing 39, 43
chiller, subtracting 39
chiller, subtracting in a VPF system 45
chiller–tower energy balance 72
chiller, unequal sizing 58
chiller, water-cooled 2
chillers, parallel 27
chillers, series, 29
coil response 28
coils, uncontrolled 6,7
condenser, air-cooled 5
condenser flow configurations 69
condenser-water-control options for transient conditions 70
condenser-water flow rate, effect of 4
condenser, water-cooled 4
condenser-water system 10
condenser-water system, decoupled 74
condenser-water temperature, effect of 4
condenser-water temperatures 14
condenser-water temperature control 72
connections, electrical and water 67
controls 11
control, chiller 11
control, flow-based 38
control, pump 12

Index
SYS-APM001-EN 87
control, system 57
cooling contingency planning 66
cooling-tower-fan control methods 71
cooling-tower options with low flow 20
D
Darcy–Weisbach 17
decoupled system–principle of operation 37
decoupling, hydraulic 31
deficit 38
design considerations 49
distribution basics, 34
E
energy sources, alternative 64
equipment, ancillary 67
expansion, plant 51
evaporator 3
F
failure recovery 64
fan, cycling a single 71
fans, two-speed 71
flow limits, absolute 42
flow rate, out of range 60
flow rates, cost implications 22
flow rates, different 38
flow rates, standard-rating 15
flow rates, selecting 16
flow-sensing 38

SYS-APM001-EN
Index
88
flow, variable 35
flow limitations, variable 73
fluid in the loop, amount of 50
fuels, optional 57
H
Hazen–Williams 17
heat exchanger, plate-and-frame 57, 72
heat recovery 54
L
limits 42
load, diversity 35
load, effect of 10
loads 5
loading, preferential 54
low ∆ T syndrome 63
low-flow rates, misconceptions about 24-26
M
motors, pony 71
P
parallel arrangement 55
piping, distribution 9
plant expansion 51
pump option, condenser water 73
pumping arrangements, campus 36
pumping arrangements, common 36
pumping arrangements, tertiary 36
pumps, distribution 34

Index
SYS-APM001-EN 89
pump per chiller 49
pumps, manifolded 49, 69
R
rate of change 51
retrofit capacity changes 21
retrofit opportunities 75
S
series–counterflow application 58
sidestream arrangement 56
software analysis tools 41
surplus flow 38
system control 57
system supply and demand 38
systems, low-flow 24
systems, primary–secondary 31
systems, variable-primary-flow 40
system response to changing conditions 51
T
temperature control 38
temperature, coil response to decreased entering water 19
temperature, elevated return-water 35
temperatures, out of range 61
temperature-sensing 38
temperatures, standard rating 13
tower, cooling 10
tower per chiller, single 69
tower, smaller 21

SYS-APM001-EN
Index
90
tower, larger 21
V
valve, check 63
valve, check in the bypass line 63
valve, three-way 6,7
valve, two-way 6,7
valve reset, critical 48
variable flow limitations 74
variable-primary-flow systems 40
variable-speed drives 71
variable-speed pump 6,7
VPF advantages 41
VPF caveats 41
VPF system, adding a chiller 44
VPF system, critical requirements 46
VPF system, “overpumping” a chiller 45
VPF system, subtracting a chiller 45
W
water, well or river 72

Since The Trane Company has a policy of continuous product and product data improvement, it
reserves the right to change design and specifications without notice.
The Trane Company
An American Standard Company
www.trane.com
For more information contact
your local district office or
e-mail us at comfort@trane.com
Literature Order Number SYS-APM001-EN (March 2001)
File Number PL-000-SYS-APM001-EN
Supersedes CON-AM-21 (May 1987)
Stocking Location La Crosse

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