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Economized Vapor Injection (EVI) Compressors
AE4-1327 R6 February 2011
Application Engineering
B U L L E T I N
1. Introduction
The refrigeration Economized Vapor Injection (EVI)compressor was developed to provide improvedcapacity and efficiency. EVI compressor systemsbenefit over standard refrigeration compressor systems
of equivalent horsepower due to the following:
Capacity Improvement - The capacity is improvedby increasing the h (change in enthalpy) in thesystem rather than increasing mass flow. Thisis accomplished without increasing compressordisplacement.
SECTION PAGE
1. Introduction ........................................................1
2. Theory of Operation ...........................................1
3. Nomenclature .................................................... 1
4. ARI Low Temperature Ratings ........................... 3
5. Approved Refrigerants ....................................... 3
6. Approved Oils .................................................... 3
7. Power Requirements ......................................... 3
8. Application Envelope ......................................... 3
9. Control Requirements ........................................ 410. Discharge Temperature Control ......................... 4
10.1 Thermistor ...............................................4
10.2 Discharge Line Thermostat .....................4
10.3 Copeland Scroll Demand Cooling ..... 5
11. TXV and Heat Exchanger ...................................8
12. System Configuration ......................................... 8
12.1 Downstream Extraction ........................... 8
12.2 Upstream Extraction ...............................8
12.3 Heat Exchanger Piping Arrangements .... 8
13. System Design Guidelines .................................9
13.1 Heat Exchanger Sizing ........................... 9
13.2 Line Sizing ............................................1013.3 Heat Exchanger TXV Sizing ................. 10
13.4 Solenoid Valve & Ball Valve .................. 10
13.5 Current Sensing Relay .......................... 10
13.6 Multiple Compressor Applications .........10
14. Controlling Liquid Out Temperature .................. 11
Increased Energy Efficiency Ratio (EER) - Theefficiency improves due to the fact that the gainin capacity is greater than the increase in powerthat the compressor consumes.
Cost and Energy Advantage - Because asmaller horsepower compressor can be used toachieve the same capacity as a larger horsepowercompressor, there is an inherent cost advantage.
2. Theory of Operation
Copeland EVI scroll compressors are equipped withan injection connection for Economizer Operation.Economizing is accomplished by utilizing a subcoolingcircuit similar to that shown in Figure 1. This mode ofoperation increases the refrigeration capacity and inturn the efficiency of the system. The benefits providedwill increase as the compression ratio increases, thus,more gains will be made in summer when increasedcapacity may actually be required.
The schematic shows a system configuration forthe economizer cycle. A heat exchanger is used to
provide subcooling to the refrigerant before it entersthe evaporator. This subcooling process provides theincreased capacity gain for the system, as describedabove. During the subcooling process a small amountof refrigerant is evaporated and superheated. Thissuperheated refrigerant is then injected into the midcompression cycle of the scroll compressor andcompressed to discharge pressure. This injectedvapor also provides cooling at higher compressionratios, similar to liquid injection of standard ZF Scrollcompressors.
3. Nomenclature
The EVI compressor has a model designation as follows,with the sixth digit shown as a "V": ZF18KVE-TFD.
The model numbers include the nominal capacitywithout the economizer cycle for R-404A refrigerantat 60 Hz Low Temperature ARI rating conditions. (SeeModel Designation diagram on Page 3.)
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The P-h diagram shows the theoretical gain in system performance achieved by using theeconomizer cycle. The extension outside of the vapor dome is what allows for the extra enthalpy
increase in the evaporator, enhancing system performance. Although power increases due to thevapor injection into the compressor, there is still an efficiency gain given that the capacity gainsexceed the power increase.
Definition(s) Description
Tc Condensing temperature
Tli Liquid temperature entering H/X
Tlo Subcooled liquid leaving H/X
Pi Intermediate Pressure
Tsi Saturated temperature at intermediate pressureTvo Vapor temperature leaving H/X
Tvi Vapor temperature entering H/X
Tsc Liquid subcooling in H/X
M Evaporator Mass Flow
I Vapor Injection Mass Flow
THX Liquid temp out H/X-Liquid-Saturated temperature at intermediate pressure
TSC Liquid temp in to H/X-subcooled liquid temp out H/X
Figure 1Circuit Diagram and Cycle for EVI
(Upstream extraction shown here. See Section 12 for details.)
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Model Designation
1 Z = Compressor Family: Z = Scroll2 F = Low Temperature3 Nominal Capacity [BTU/h] @ 60 Hz and ARI
low temperature conditions using multipliersK for 1000, without vapor injection
4 Vapor Injection for EVI Operation5 POE Oil6 Motor Version7 Bill of Material Number
The EVI rating curves have been developed toincorporate performance improvements while utilizingthe economizer cycle. The capacity displayed is
with maximum possible subcooling at the exit of thesubcooling heat exchanger. Compressor performanceinformation can be obtained by accessing theOnline Product Information (OPI) database at www.emersonclimate.com.
4. ARI Low Temperature Ratings(-25F/105F, R-404A)
Model With EVI* Without EVIZF13KVE 20,100 Btu/hr 13,000 Btu/hrZF18KVE 29,200 Btu/hr 18,000 Btu/hrZF24KVE 34,200 Btu/hr 24,000 Btu/hrZF33KVE 47,900 Btu/hr 33,000 Btu/hr
ZF40KVE 62,500 Btu/hr 40,000 Btu/hrZF48KVE 72,000 Btu/hr 48,000 Btu/hr
*Maximum possible subcooling
ARI Low Temperature Ratings(-25F/105F, R-407A)
Model With EVI1,2 Without EVI1
ZF13KVE 15,700 Btu/hr 12,000 Btu/hrZF18KVE 23,600 Btu/hr 17,600 Btu/hrZF24KVE 27,500 Btu/hr 20,800 Btu/hrZF33KVE 38,100 Btu/hr 29,000 Btu/hrZF40KVE 48,800 Btu/hr 37,000 Btu/hr
1Dew point pressures assumed
2Maximum possible subcooling
Note: For performance of ZF*KVE models with otherrefrigerants, refer to the Online Product Information atwww.emersonclimate.com
5. Approved Refrigerants
R404A, R507 and R407A are approved for use withCopeland EVI scroll compressors. R407A requiresthe use of Demand Cooling for low temp operation.
6. Approved Oils
Polyol Ester (POE) lubricants are the only lubricantsapproved for the EVI compressor. For a complete
list of approved POE lubricants, refer to Form 93-11,Emerson Accepted Refrigerants/Lubricants.
7. Power Requirements
EVI compressors are only available for three phase power.
8. Application Envelopes
Figure 2
Figure 3
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Medium Temperature ZF**KVE Envelope (R-404A/R-507)Condions: 65F Return Gas, 260F Max DLT
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* For other return gas conditions contact your Application Engineerfor Demand Cooling requirements.
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9. Control Requirements
See Figure 6 for a detailed schematic for this system(shown for a single compressor application). Thefigure also shows the upstream extraction method fortapping the liquid for the heat exchanger; see Section12 for additional details.
10. Discharge Temperature Control
A discharge temperature control is not required on allcompressors.
Models ZF24KVE-TW*, ZF33KVE-TW*, ZF40KVE-TW*, ZF48KVE-TW* have an internal temperaturesensor and no other discharge temperature controlis required for applications using R-404A or R-507.No thermistor or thermostat is required when usingCopeland Scroll Demand Cooling for low temperatureapplications.
For models ZF13KVE-TF*, ZF18KVE-TF* use one ofthe following two methods for discharge temperaturecontrol.
10.1 Thermistor
For low temperature applications with R-407A,Copeland ScrollDemand Cooling is required for useto run all conditions within the approved operatingenvelope. Additional information on Demand Coolingis discussed in Section 10.3.
A thermistor in the compressor control circuit is usedto protect against high discharge temperatures andmust be wired to the rack control systems. The cut outtemperature is to be set at 280F. The temperatureresistance values for the sensor can be found inAppendix A.
The thermistor must conform to the curve characteristicsoutlined in Appendix A. The table expresses the ratioof the resistance at the indicated temperature andthe resistance at 77F (25C). The resistance at 77F(25C) is 86Kohms nominal. The curve fit is Ratio =0.8685e-0.257x, where x = resistance at the indicatedtemperature.
NOTE: The system controller must open thecontactor when the discharge line temperatureexceeds 280F
10.2 Discharge Line ThermostatAnother method of discharge temperature control isthe use of a discharge line thermostat. It is requiredin the compressor control circuit. The thermostatshave a cut out setting that will insure discharge linetemperatures below the 260F (127C) maximum
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CondensingTemperature(C)
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Low Temperature ZF**KVE Envelope (R-407A)Condions: 65F Return Gas, 260F Max DLT
Figure 4
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Medium Temperature ZF**KVE Envelope (R-407A)Condions: 65F Return Gas, 260 F Max DLT
Figure 5
Figure 6
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limit. (This value differs from the cut out value set onthe thermistor because the temperature is measuredcloser to the discharge gas from the scroll when usingthe thermistor.) The discharge line thermostat shouldbe installed approximately 7 (178mm) inches from thedischarge tube outlet. If a service valve is installed at thedischarge tube outlet, the thermostat should be located5 (127mm) inches from the valve braze. For properfunctioning, it is recommended the thermostat should beinsulated to protect it from a direct air stream. Kits havebeen set up to include the TOD thermostat, retainer,and installation instructions. These thermostats mustbe used with " O.D. discharge lines to ensure properthermal transfer and temperature control. They workwith either 120 or 240 volt circuits, and are availablewith or without an alarm circuit capability. See Table 1for a list of discharge line thermostat kit numbers.
10.3 Copeland Scroll Demand Cooling
The Demand Cooling system uses modern electronicsto provide a reliable cost effective solution to highinternal discharge temperatures encountered in lowtemperature applications using R-407A. DemandCooling has traditionally been applied to the CopelandDiscus product line to control high internal dischargetemperatures that exceed the safe temperature limitfor long term stability of refrigeration oil. EmersonClimate Technologies has now approved the use ofDemand Cooling for the Copeland Economized VaporInjection (EVI) scroll product line using low temperatureR-407A. The integration of Demand Cooling with EVIscroll creates a wet-injection approach to dischargetemperature control. Emerson has approved the followingEVI scrolls for use in low temperature applications withDemand Cooling:
ZF13KVE
ZF(D)18KVE
ZF24KVE
ZF33KVE
ZF40KVE
The Demand Cooling module uses the signal of adischarge line temperature sensor to monitor dischargegas temperature. If a critical temperature is reached,
the module energizes a long life injection valve whichmeters a controlled amount of saturated refrigerantinto the vapor injection line. The injection will continueuntil the discharge line temperature reaches a lower
preset temperature. This process controls the dischargetemperature to a safe level. If, for some reason, thedischarge temperature rises above a preset maximumlevel, the Demand Cooling module will turn thecompressor off (requiring a manual reset) and actuateits alarm contact.
The injection valve orifice has been carefully chosen tobe large enough to provide the necessary cooling whenrequired but not so large that a dangerous amount ofliquid is injected, or that excessive system pressurefluctuation occurs during injection valve cycling. It isimportant to use the correct valve for the EVI scroll.
Performance data for Demand Cooling compressorsincludes the effects of injection when it is required. Theapproximate conditions where injection occurs are shownpreviously in Figure 5 for R-407A. At the conditionswhere Demand Cooling is operating, the performancevalues are time averages of the instantaneous values,since small fluctuations occur as the Demand Coolinginjection valve cycles.
The Demand Cooling system addresses the capacityand efficiency issues by limiting injection to those timeswhen it is required to control discharge temperaturesto safe levels. For most applications this will only be
during periods of high condensing temperatures, highreturn gas temperatures, or abnormally low suctionpressure. The Demand Cooling system has beendesigned to meet the same high reliability standardsas Scroll compressors.
Demand Cooling System Design
When Demand Cooling operates, it diverts refrigerationcapacity in the form of injected saturated refrigerantfrom the vapor injection circuit to the compressor (SeeFigure 7 for a typical single system schematic). DemandCooling injects a small amount of liquid to the vaporinjection stream to cool the discharge. This does notaffect the mass flow significantly. However, when the
valve injects the system will lose some capacity becausethe EVI pressure increases and thus decreases EVIperformance.
Note! A separate Demand Cooling kit is required foreach compressor.
The injection valve should be installed as close aspossible to the compressor vapor injection inlet, nomore than 3 feet. The line MUST be well insulated. If
Kit NumberConduit
ConnectorAlarm
Contact Lead
998-7022-02 Yes No
998-0540-00 No No
998-0541-00 No Yes
Table 1 - Discharge Line Thermostat Kit Numbers
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there is substantial heat gain along the vapor injectionline, injection may result in a substantial loss in vapor
injection capacity during Demand Cooling operation.In order to minimize this loss, good practice indicatesDemand Cooling operation be kept to a minimum throughproper system design and installation practices. Thereare three areas which can be addressed to minimize theimpact of Demand Cooling operation on performance:
1. Compressor Return Gas Temperature: Suctionlines should be well insulated to reduce suction lineheat gain. Return gas superheat should be as low aspossible consistent with safe compressor operation.
2. Condensing Temperatures: It is important whenusing R-407A as a low temperature refrigerant that
condensing temperatures be minimized to reducecompression ratios and compressor dischargetemperature.
3. Suction pressure: Evaporator design and systemcontrol settings should provide the maximum suctionpressure consistent with the application in order tohave as low a compression ratio as possible.
Demand Cooling With Copeland DigitalCompressor Controller
In order to control a Copeland Digital Scroll compressor,the Copeland Digital Compressor Controller (P/N943-0086-00) may be used in multiple compressorapplications. The digital compressor controller has itsown discharge temperature protection. However, forapplications requiring Demand Cooling, the DemandCooling module should have primary control of thetemperature protection.To ensure the Demand Coolingsystem functions appropriately, jumper the T1 andT2 inputs on the Copeland Digital CompressorController, with a 5kOhm, 1 Watt resistor.
Demand Cooling System Components
The Demand Cooling system consists of: the dischargeline temperature sensor, the Demand Cooling module,and the injection valve solenoid. The Emerson kit numbersfor each scroll model are shown in Table 3 (next page).
Demand Cooling SpecificationsDemand Cooling is designed to operate and protectthe compressor within the evaporating and condensingenvelope identified in Figure 5. Operating setpoints andcontrol actions are listed in Table 4.
Figure 7 - Typical Single Compressor System Schematic with Copeland ScrollDemand Cooling
CONDENSER
EVAPORATOR
M
L
A
S
DEMAND COOLING
CONTROL MODULE
ACCUMULATOR
SUCTION LINE
FILTER
COMPRESSOR
INJECTION
SOLENOID VALVESIGHT
GLASS
INJECTION
LINE
FILTER
INJECTION VALVE
ELECTRICAL
CONTROL LINE
TEMP SENSOR
LINE
MANUAL
SHUTOFF VALVE
VAPOR INJECTION LINE
LIQUID INJECTION LINE
RECEIVERLIQUID LINE
FILTER DRIER
HX
TXV
HX
TO CONTROL
CIRCUIT
TXV
TEMP SENSOR
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Figure 8 - Digital Compressor Controller Wiring Diagram
*
**
Protection controls such as high/low pressure controls andcompressor motor protection module go here.
Polarity must match system controller
Note: The Neutral to L1, M1, U1, V1 is connected together.
*
**
OR 5kOhm, 1W RESISTOR(for Demand Cooling Applications)
Note! Discharge line temperatures are measured externally and are for reference only.
Table 4
Discharge Line
Temperature
Demand Cooling Module
Operation
Approximate Sensor
ResistanceRising Through 258F Demand Cooling Solenoid ON 3,820
Falling Through 237F Demand Cooling Solenoid OFF 5,000
Rising Through 286F Alarm Contact Energized 2,620
At Room Temp (77F) Demand Cooling Solenoid OFF86,000 (when compressorhas cooled)
Kit Part Number
120V Demand Cooling for Copeland ScrollKit 998-1000-50
240V Demand Cooling for Copeland Scroll Kit 998-1000-51
Table 3 - Copeland Scroll Demand Cooling Kits
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Demand Cooling Wiring Schematic
The figure below shows a recommended wiringschematic for the Demand Cooling assembly.
12. System Configuration
There are two methods of controlling refrigerant flowat the heat exchanger - downstream and upstream
extraction.
12.1 Downstream Extraction
The downstream extraction is the preferred methodemployed in the United States. In downstreamextraction the TXV is placed between the liquid outletand vapor inlet of the heat exchanger. The advantageof downstream extraction is that subcooling is ensuredbecause the liquid is further subcooled as it flowsthrough the heat exchanger. Therefore, more subcooledliquid enters the TXV which increases the probabilitythat the valve will not hunt. The disadvantage with thismethod is that it is not as efficient as the upstreammethod; however, the difference is too small for
practical purposes. See Figure 10.
12.2 Upstream Extraction
In upstream extraction the TXV is placed betweenthe condenser and the heat exchanger. The TXVregulates the flow of subcooled refrigerant out of thecondenser and into the heat exchanger. With this typeof configuration there is a potential forflash gas whichwould cause the valve to hunt. See Figure 11.
12.3 Heat Exchanger Piping Arrangements
Best subcooling effect is assured if counterflow of gas
and liquid is provided as shown (see Figure 12). Inorder to guarantee optimum heat transfer, the plateheat exchanger should be mounted vertically andvapor should exit it at the top.
Figure 9
The normally closed (NC) contact of the alarm relay (L-M)should be wired in the compressor contactor control circuitso that opening this contact removes the compressorfrom the line and removes power to the CM.
11. Thermostatic Expansion Valve (TXV) & HeatExchanger
In order to properly use an Enhanced Vapor Injectioncompressor a thermostatic expansion valve (TXV) andheat exchanger are needed in the system. Emersonprovides a kit that has these components properly sizedfor the ZF13 and ZF18 single compressor applications,see Table 5. For multiple compressor applications, thesubcooling components may be designed using thesubcooling load and pressure and temperature dataprovided by the EVI calculator program.
Table 5
Model 24V 120V 240V Kits Include:
ZF13 985-
1500-00
985-
1500-01
985-
1500-02
TXV,
Solenoid Valve,
Current Sensing
Relay, Heat
Exchanger
ZF18 985-
1500-00
985-
1500-01
985-
1500-02
ZF24 N/A N/A N/A
ZF33 N/A N/A N/A
ZF40 N/A N/A N/A
ZF48 N/A N/A N/A
Heat
Exchanger
Vapor Outlet to
Compressor
Condenser
Outlet
TXV
LIT
VOT
SIT
UT
LOT
Figure 10 - Downstream Extraction
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13. System Design Guidelines:
NOTE: The following sections discuss system design
guidelines for the EVI product. Please refer to theEmerson Product Selection Software, which canbe found in the Online Product Information (OPI)database located at www.emersonclimate.com, forfurther information needed to accommodate yoursizing needs.
13.1 Heat Exchanger Sizing
Heat exchangers should be sized so that they haveadequate design margin for the entire range of systemoperation, but they should be optimized for normaloperating conditions. The parameters used to determinethe proper heat exchanger size are described below:
SIT = Heat Exchanger saturated evaporatingtemperature at its outlet pressure.
LIT = Liquid in Temp ~ Condensing Outlet LOT = Liquid Out Temp = SIT + TD VIT = Vapor In Temp ~ SIT + Loss VOT = Vapor Out Temp = SIT + Superheat H = Enthalpy Subcooling = LIT - LOT Superheat = VOT - SIT TD = LOT- SIT
The key parameter in determining the proper heatexchanger is the Saturated Injection Temperature(SIT). It is imperative the following procedure befollowed for optimized performance. The SIT has
been derived experimentally and can be approximatedby using Figure 13. After determining the SIT, a 10FCondenser Subcooling, TD, and Superheat are targeted.This is done in order to optimize system performancewhile at the same time maintaining system reliabilityand functionality. Once these parameters have beenestablished, the heat exchanger Btu/Hr capacitycan be established, which gives the required heatexchanger size.
Figure 13
Example of Heat Exchanger Sizing OptimizedZF18KVE 404A
Step 1 Know Conditions -25/105/0/65
Te/Tc / Cond SC / Suct RG
Step 2 Determine Flow Me 355 lb/hr
From Product Data
Step 3 Estimate SIT From Guideline 12
Step 4 Use the 10 Guidelines To Derive LIT = T
5901-
LOT = SIT + 10 22 HX SC = LIT - LO 73
= (T
- SIT-20) HX Btu/hr =M
x (Hft - Hlot) 9550
=355 x (47.0 - 20.1)
VO = Vapor temperature leaving H/X
VI = Vapor temperature entering H/X
LI = Liquid temperature entering H/X
LO = Subcooled liquid leaving H/X
Figure 12 - H/X Piping Arrangement
Figure 11 - Upstream Extraction
Vapor OutCond. Out
Liq. In
TXV
SIT
Liq. OutVapor In
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For multiple compressor applications the same processcan be used to determine the heat exchanger sizeneeded by adding together the individual heat exchangercapacities for each compressor.
13.2 Line Sizing
In single compressor applications, the vapor injectionline from the heat exchanger to the compressor shouldbe 3/8" - 1/2" and kept as short as possible in order tominimize pressure drop loss. The liquid line from the heatexchanger to the evaporator should be insulated and keptas short as possible in order to maximize the subcoolingat the evaporator. If a vapor injection header is used, theheader diameter should be such that the cross-sectionalarea is equal to the sum of the cross-sectional areas ofthe individual cross-sectional lines to the compressor.
For example, for four compressors, each with a 3/8"vapor injection line, the header tube diameter should bea 7/8" tube. In addition, the individual injection lines tothe compressors should tap into the header either ontop or on the sides of the header tube; a bottom tap willincrease the risk of returning liquid into the compressorthrough the vapor injection line.
13.3 Heat Exchanger TXV Sizing
TXV's should be sized so that they have adequate designmargin for the entire range of system operation, but theyshould be optimized for normal operating conditions.Select a TXV that is able to handle the Btu/hr capacity ofthe heat exchanger determined in the section above.
13.4 Solenoid Valve & Ball Valve
A solenoid valve is required to stop the flow ofvapor from the system to the compressor when thecompressor is in the off cycle. This must be a vapor
solenoid sized equivalent to or larger than the vaporinjection tube size. For minimum orifice sizes seeTable 6. For service purposes, a mechanical ball valve(not provided by Emerson) is also recommended in thevapor injection line.
Table 6
ModelMinimum
Orifice Size
Flow Control
Valve Series
ZF13 3/16" 200RB 3
ZF18 3/16" 200RB 3
ZF24 1/4" 200RB 4
ZF33 1/4" 200RB 4
ZF40 5/16" 200RB 5
ZF48 5/16" 200RB 5
13.5 Current Sensing Relay
To prevent the solenoid from remaining open during a"motor protector trip" a current sensing relay must beprovided that senses whenever the compressor is "off"and closes the solenoid to stop injection. See Table 5for a kit with the correct current sensing relay.
13.6 Multiple Compressor Applications
EVI can also be used in multiple compressorapplications. Unlike a standard compressor system, theEVI compressor system changes its delivered capacity
by changing the amount of sub-cooling provided at thesub-cooling heat exchanger. The result is that in highambient temperature conditions (summer operation)and in low ambient temperature conditions (winteroperation), the same number of compressors tend torun. It is important to note this since most personnelare used to seeing fewer compressors in operationin the cooler winter months compared to the hottersummer months; with EVI, almost the same number ofcompressors will be running in the summer and winter.
Multiple EVI compressors can be used with eithera single heat exchanger for each compressor or acommon heat exchanger for all compressors. In case
of a common heat exchanger, a solenoid valve shouldbe installed on each individual vapor injection line.Special care has to be given to the design of the heatexchanger and of the thermostatic expansion valve(TXV) to allow for part load operation. Good refrigerantdistribution is required in the common heat exchangeras well as sufficient velocities for oil return, even atpart load.
In the case of a large range of capacity modulation(more than 2 compressors in parallel), the use of an
Example of Heat Exchanger Sizing Fixed Liquid Temperature
ZF18KVE 404AStep 1 Know Conditions -25/105/0/65
Te/Tc / Cond SC / Suct RG
Step 2 Determine Flow M
355 lb/hr
From Product Data
Step 3 Use the 10 Guideline LIT = T
5901-
LOT user defined 50 HX SC = LIT - LO 45 HX [Btu/hr] = M
x (Hft - Hlot) 6140
= 355 x (47.0 - 29.7)
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Electronic Expansion Valve (EXV) or of two differentTXV(s) controlled by individual solenoid valves, mayimprove performance. For example, one at 100%full load and the second solenoid valve for 30% offull load. (See Figures 14and15). It is necessary toensure that the solenoid valves, vapor injection linesand header(s) are adequately sized in order to keeppressure drop to a minimum. At the same time, thelayout should be such that excessive amounts of oil donot accumulate in the header.
14. Controlling Liquid Out Temperature (LOT)
The LOT will typically be determined by the operatingcondition of the compressor. If the LOT needs to befixed at any specific value (for example, 50F) forpurposes of good system control, an EvaporatorPressure Regulator (EPR) valve may be introduced
at the vapor outlet of the subcooling heat exchanger.Table 7 shows approximate EPR settings for differentliquid temperature.
Emerson Climate Technologies Product SelectionSoftware can be used to determine the effect offixingLOT on the capacity and efficiency of the compressor.See Figures 15 and 16 on the following page.
Table 7
Figure 14
EVI Paralleling with HX Thermostatic valves of
different capacity
Figure 15
EVI Paralleling with HX Electronic Expansion
Valve (EXV)
R-407A (Based on Dew Point Properties)
Subcooler Liquid OutTemperature, F Approximate EPRSetting, psig (psia)
60 86.1 (100.8)
50 69.4 (84.1)
40 54.8 (69.5)
*Assumes a 10F DT across EVI Heat Exchanger
R-404A (Based on Dew Point Properties)
Subcooler Liquid OutTemperature, F
Approximate EPRSetting, psig (psia)
60 103.6 (118.3)
50 85.4 (100.1)
40 69.3 (84.0)
*Assumes a 10F DT across EVI Heat Exchanger
7/28/2019 AE1327
12/13
12 2010 Emerson Climate Technologies
Printed in the U.S.A.
AE-1327 R5
Application Engineering
B U L L E T I N
Economizer Settings
Defaults To AutomaticFor Maximum Sub-cooling
Maximum Sub-cooling
Obtained
Economizer Settings Is Set
To Constant Liquid
Temp. For Fixing Liquid
Out Temperature (LOT)
Liquid Temperature Is
Fixed At Input Value
Figure 16Screenshot of Emerson Climate Technologies Product Selection Software Showing the Maximum
Sub-cooling Obtained When the Default Automatic is Selected for Economizer Settings.
Figure 17Screenshot of the Product Selection Software Showing the Constant Liquid Temperature at Outlet of the
Subcooling Heat Exchanger.
7/28/2019 AE1327
13/13
13 2010 Emerson Climate Technologies
AE-1327 R5
Application Engineering
B U L L E T I N
7C 2.301308C 2.19180
9C 2.08830
10C 1.99030
11C 1.89720
12C 1.80900
13C 1.72550
14C 1.64640
15C 1.57140
16C 1.50000
17C 1.43230
18C 1.36810
19C 1.30710
20C 1.2493021C 1.19420
22C 1.14180
23C 1.09210
24C 1.04490
25C 1.00000
26C 0.95710
27C 0.91640
28C 0.87760
29C 0.84070
30C 0.80560
31C 0.77200
32C 0.74010
33C 0.7096034C 0.68060
35C 0.65300
36C 0.62660
37C 0.60140
38C 0.57740
39C 0.55460
40C 0.53270
41C 0.51170
42C 0.49180
43C 0.47270
44C 0.45440
45C 0.4370046C 0.42030
47C 0.40420
48C 0.38890
49C 0.37430
5C 2.53960
6C 2.41710
7C 2.30130
8C 2.191809C 2.08830
10C 1.99030
11C 1.89720
12C 1.80900
13C 1.72550
14C 1.64640
15C 1.57140
16C 1.50000
17C 1.43230
18C 1.36810
19C 1.30710
20C 1.24930
21C 1.1942022C 1.14180
23C 1.09210
24C 1.04490
25C 1.00000
26C 0.95710
27C 0.91640
28C 0.87760
29C 0.84070
30C 0.80560
31C 0.77200
32C 0.74010
33C 0.70960
34C 0.6806035C 0.65300
36C 0.62660
37C 0.60140
38C 0.57740
39C 0.55460
40C 0.53270
41C 0.51170
42C 0.49180
43C 0.47270
44C 0.45440
45C 0.43700
46C 0.4203047C 0.40420
48C 0.38890
49C 0.37430
95C 0.07870
96C 0.07641
97C 0.07420
98C 0.07206
99C 0.07000100C 0.06800
101C 0.06612
102C 0.06430
103C 0.06255
104C 0.06085
105C 0.05920
106C 0.05760
107C 0.05605
108C 0.05456
109C 0.05310
110C 0.05170
111C 0.05027
112C 0.04889113C O.04755
114C 0.04625
115C O.04500
116C 0.04372
117C 0.04248
118C 0.04128
119C 0.04012
120C O.03900
121C O.03793
122C 0.03690
123C 0.03590
124C 0.03494
125C 0.03400126C 0.03315
127C 0.03233
128C 0.03153
129C 0.03075
130C 0.03000
131C 0.02926
132C 0.02854
133C 0.02784
134C 0.02716
135C 0.02650
136C 0.02586
137C 0.02525138C 0.02465
139C 0.02407
140C 0.02350
141C 0.02295
142C 0.02242
143C 0.02190
144C 0.02139
145C 0.02090146C 0.02039
147C 0.01990
148C 0.01942
149C 0.01895
150C 0.01850
151C 0.01801
152C 0.01754
153C 0.01708
154C 0.01663
155C 0.01620
156C 0.01584
157C 0.01549
158C 0.01515159C 0.01482
160C 0.01450
161C 0.01418
162C 0.01388
163C 0.01358
164C 0.01328
165C 0.01300
166C 0.01275
167C 0.01250
168C 0.01226
169C 0.01203
170C 0.01180
171C 0.01157172C 0.01134
173C 0.01112
174C 0.01091
175C 0.01700
176C 0.01049
177C 0.01029
178C 0.10090
179C 0.00989
180C 0.00970
181C 0.00949
182C 0.00928
183C 0.00908184C 0.00889
185C 0.00870
186C 0.00853
187C 0.00837
188C 0.00821
189C 0.00805
190C 0.00790
-40C 33.60000-39C 31.44900
-38C 29.45200
-37C 27.59700
-36C 25.87300
-35C 24.27000
-34C 22.76100
-33C 21.35700
-32C 20.05100
-31C 18.83400
-30C 17.70000
-29C 16.63420
-28C 15.64040
-27C 14.71340-26C 13.84820
-25C 13.04020
-24C 12.28070
-23C 11.57100
-22C 10.90750
-21C 10.28680
-20C 9.70600
-19C 9.15880
-18C 8.64630
-17C 8.16620
-16C 7.71620
-15C 8.29400
-14C 6.89570-13C 6.52190
-12C 6.17110
-11C 5.84150
-10C 5.53190
-9C 5.23920
-8C 4.96400
-7C 4.70520
-6C 4.46170
-5C 4.23240
-4C 4.01530
-3C 3.81090
-2C 3.61820-1C 3.43670
0C 3.26540
1C 3.10300
2C 2.94980
3C 2.80520
4C 2.66860
5C 2.53960
6C 2.41710
Temp Ratio Temp Ratio Temp Ratio Temp Ratio Temp Ratio
Appendix A