US20080202140A1 - High Side Pressure Regulation For Transcritical Vapor Compression System - Google Patents

High Side Pressure Regulation For Transcritical Vapor Compression System Download PDF

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Publication number
US20080202140A1
US20080202140A1 US11/908,629 US90862907A US2008202140A1 US 20080202140 A1 US20080202140 A1 US 20080202140A1 US 90862907 A US90862907 A US 90862907A US 2008202140 A1 US2008202140 A1 US 2008202140A1
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United States
Prior art keywords
heat exchanger
compressor
flow path
refrigerant
expansion device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US11/908,629
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English (en)
Inventor
Tobias H. Sienel
Yu Chen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Taylor Commercial FoodService LLC
Original Assignee
Carrier Comercial Refrigeration Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Comercial Refrigeration Inc filed Critical Carrier Comercial Refrigeration Inc
Priority to US11/908,629 priority Critical patent/US20080202140A1/en
Assigned to CARRIER COMMERCIAL REFRIGERATION, INC. reassignment CARRIER COMMERCIAL REFRIGERATION, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHEN, YU, SIENEL, TOBIAS H.
Publication of US20080202140A1 publication Critical patent/US20080202140A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/17—Control issues by controlling the pressure of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F25D19/02—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors plug-in type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D31/00—Other cooling or freezing apparatus
    • F25D31/006—Other cooling or freezing apparatus specially adapted for cooling receptacles, e.g. tanks
    • F25D31/007—Bottles or cans

Definitions

  • the invention relates to refrigeration. More particularly, the invention relates to beverage coolers.
  • FIG. 1 schematically shows transcritical vapor compression system 20 utilizing CO 2 as working fluid.
  • the system comprises a compressor 22 , a gas cooler 24 , an expansion device 26 , and an evaporator 28 .
  • the exemplary gas cooler and evaporator may each take the form of a refrigerant-to-air heat exchanger. Airflows across one or both of these heat exchangers may be forced. For example, one or more fans 30 and 32 may drive respective airflows 34 and 36 across the two heat exchangers.
  • a refrigerant flow path 40 includes a suction line extending from an outlet of the evaporator 28 to an inlet 42 of the compressor 22 .
  • a discharge line extends from an outlet 44 of the compressor to an inlet of the gas cooler. Additional lines connect the gas cooler outlet to expansion device inlet and expansion device outlet to evaporator inlet.
  • the evaporator may be essentially at the cooler interior temperature. It is typically desired to maintain this temperature in a very narrow range regardless of external condition. For example, it may be desired to maintain the interior very close to 37° F. This temperature essentially fixes the steady state compressor suction pressure.
  • the energy efficiency of a vapor compression system is usually expressed as a ratio of the system capacity to the energy consumed. Because an increase in pressure typically produces both a higher capacity and a higher energy consumption, the balance between the two will dictate the overall COP. Therefore, there is typically an optimal pressure which yields the highest possible performance.
  • An electronic expansion valve is usually used as the device 26 to control the high side pressure to optimize the COP of the CO 2 vapor compression system.
  • An electronic expansion valve typically comprises a stepper motor attached to a needle valve to vary the effective valve opening or flow capacity to a large number of possible positions (typically over one hundred). This provides good control of the high side pressure over a large range of operating conditions.
  • the opening of the valve is electronically controlled by a controller 50 to match the actual high side pressure to the desired set point.
  • This pressure control strategy involves a fairly high cost valve, a sophisticated controller 50 , and a sensor 52 for measuring the high side pressure. This equipment adds a significant amount of cost to the CO 2 vapor compression system, causing the CO 2 vapor compression system to be less attractive compared to an HFC system.
  • a fixed expansion device e.g., a fixed orifice or capillary tube
  • a fixed expansion device can work well to regulate the system high side pressure to a near optimum pressure.
  • the flowrate through a fixed speed and displacement compressor can become relatively high. This high flowrate can cause the high side pressure to exceed a safe limit.
  • An expensive expansion device may be eliminated in favor of a less expensive pressure regulator in a CO 2 vapor compression system such as is used in a bottle cooler or small-capacity air conditioner, refrigerator, or other system.
  • the potential for overpressurization may be reduced by using an inexpensive, multi-step fixed expansion device based on one or more solenoid valves.
  • FIG. 1 is a schematic of a prior art vapor compression system.
  • FIG. 2 is a schematic of a first inventive CO 2 vapor compression system.
  • FIG. 3 is a schematic of a second inventive CO 2 vapor compression system.
  • FIG. 4 is a schematic of a third inventive CO 2 vapor compression system.
  • FIG. 5 is a schematic of a fourth inventive CO 2 vapor compression system.
  • FIG. 6 is a schematic of a fifth inventive CO 2 vapor compression system.
  • FIG. 7 is a schematic of a sixth inventive CO 2 vapor compression system.
  • FIG. 8 is a schematic of a seventh inventive CO 2 vapor compression system.
  • FIG. 9 is a side schematic view of a display case including a refrigeration and air management cassette.
  • FIG. 10 is a view of a refrigeration and air management cassette.
  • the current invention relates to high-side pressure optimization for a CO 2 vapor compression system.
  • a fixed expansion device e.g., an orifice or capillary tube
  • the preset value should be determined such that the CO 2 vapor compression system can achieve the best overall Coefficient of Performance (COP) for the entire operating envelope.
  • COP Coefficient of Performance
  • the compressor flowrate will be significantly higher than during steady state conditions.
  • the high-side pressure should be optimized such that the pulldown cooling capacity of the CO 2 vapor compression system can be maximized, but the flow through the pressure regulator does not exceed the flow through the compressor (so that the system pressure becomes too great).
  • This optimal high-side pressure for maximizing capacity is usually higher than the optimal high-side pressure for maximizing the overall COP.
  • the expansion device may be configured to have a larger flow capacity during pulldown conditions. A simple multi-position expansion device may provide this. There are a number of ways through which this can be achieved through the use of solenoid valves to enable a two or more position pressure control system.
  • FIG. 2 shows a system 60 in which the refrigerant flow path 62 is split into two parallel branches/segments 64 and 66 between the gas cooler 24 outlet and evaporator 28 inlet.
  • the first branch 64 has a first fixed expansion device 68 .
  • the second branch 66 includes, in series, a solenoid valve 70 and a second fixed expansion device 72 .
  • the exemplary solenoid valve 70 has two settings/conditions.
  • One setting/condition is a fully closed condition in which no flow may pass along the second branch 66 .
  • the second setting/condition is a fully open condition allowing flow to pass through the second branch 66 with a minimal pressure loss across the solenoid valve 70 .
  • the solenoid valve 70 is kept fully closed.
  • the compressor flowrate is relatively high.
  • the solenoid valve 70 is opened, allowing flow through the second fixed expansion device 72 .
  • the combination of both expansion devices 68 and 72 regulates the high-side pressure to avoid overpressurization while still delivering good system performance.
  • a pulldown condition may be detected by means of one or more temperature sensors 75 and pressure sensor 74 coupled to a controller 76 coupled to control the solenoid valve 70 .
  • the controller 76 may also be coupled to the compressor and/or fan(s) to control their respective operation.
  • the sensor and controller are not illustrated in the following examples although they may be present.
  • FIG. 3 shows a system 80 wherein the refrigerant flow path 82 has two segments/branches 84 and 86 in parallel upstream of a first fixed expansion device 88 .
  • the first branch 84 includes a solenoid valve 90 .
  • the second branch 86 includes a second fixed expansion device 92 .
  • the solenoid valve 90 is closed to prevent flow along the first branch 84 .
  • the second branch 86 acts as a bypass with restricted flow passing through the second fixed expansion device 92 before then passing through the first fixed expansion device 88 .
  • the solenoid valve 90 is open, allowing an essentially unrestricted flow along the first branch 84 .
  • a small additional flow may flow along the second branch 86 , with the combined flow then passing through the first expansion device 88 .
  • the first expansion device 88 may be upstream of the branching rather than downstream. Control methods and components (not shown) of this system and those discussed below may be similar to those of the system 60 .
  • FIG. 4 shows another system 100 wherein the flow path 102 has first and second segments/branches 104 and 106 between the gas cooler and evaporator.
  • a fixed expansion device 108 is located in the first branch 104 .
  • a solenoid valve 110 is located in the second branch 106 .
  • the solenoid valve 110 combines aspects of a solenoid valve and a fixed expansion device. Specifically, the open condition may still be relatively restricted compared with the open condition of the solenoid valve 90 . Therefore, the pulldown pressure drop through the solenoid valve 110 is significant and the high-side pressure of the system is controlled to the preset constant optimal value by the combination of the solenoid valve 110 and the fixed expansion device. For steady state operation, the solenoid valve 110 is fully closed and all flow passes through the expansion device 108 .
  • FIG. 5 shows a branch-less system 120 in which, along the flow path 122 , a solenoid valve 124 and fixed expansion device 126 are located in series.
  • the solenoid valve 124 combines aspects of the solenoid valve and a fixed expansion device differently from the valve 1 10 of FIG. 4 .
  • the valve element (e.g., the solenoid plunger) of the solenoid valve 124 may have a small orifice so that its closed condition is only a partially closed condition.
  • the open condition is an essentially fully open condition with low pressure drop.
  • the solenoid valve 124 is in its closed condition passing a relatively low flow and creating a substantial pressure drop (individually and combined with the expansion device 126 ).
  • the solenoid valve is open, permitting the flow rate to be dictated essentially solely by the expansion device 126 .
  • the series order may be reversed.
  • FIG. 6 shows a system 140 combining aspects of the systems 80 and 120 .
  • the flow path 142 has two segments/branches 144 and 146 in parallel upstream of a first fixed expansion device 148 .
  • the first branch 144 includes a solenoid valve 150 .
  • the second branch 146 includes a fixed expansion device 152 .
  • the exemplary solenoid valve 150 may, similar to the solenoid valve 124 , have a closed condition that is only partially closed. During pulldown conditions, the solenoid valve 150 is open. During steady state conditions, the valve 150 is closed. In the steady state condition, there is a relatively small flow along each of the branches. During pulldown conditions, a larger flow may pass along the first branch 144 , with a residual flow along the second branch 146 .
  • FIG. 7 shows another system 160 wherein the flow path 162 includes a solenoid valve 164 that combines solenoid valve and orifice functions.
  • the element of the solenoid valve 144 includes an orifice so that the closed condition is only partially closed.
  • the valve 144 is in its closed condition with the orifice passing the relatively small flow.
  • the valve is open so that a larger flow is passed.
  • FIG. 8 shows a system 180 wherein the flow path 182 includes segments/branches 184 and 186 between the gas cooler and the evaporator.
  • a solenoid valve 188 and 190 is located in each of the branches.
  • the elements of these solenoid valves may include orifices. Independent control over the valves may provide more than two alternative effective flow restrictions. For example, with different size orifices, the two valves provide up to four different effective restrictions.
  • a minimal restriction may be present with both valves open.
  • a maximal restriction may be present with both valves closed.
  • a pair of intermediate restrictions may be achieved with one of the valves closed and the other open.
  • the conduit of the branches may be sized or the valve sized or additional restriction may be present so that with only one valve open there is not essentially free flow.
  • An alternative embodiment could feature such valves in series rather than parallel.
  • a variety of sensor and/or user inputs may be used to control the solenoid valve(s).
  • Direct measurement of the high-side pressure may be made by the sensor 74 . When this pressure exceeds one or more associated thresholds, the controller 76 may cause the valve(s) to assume an associated relatively free-flow condition.
  • input may be received from an air temperature sensor.
  • the exemplary sensor 75 may be positioned to be exposed to air in or from the cooler interior (e.g., to the flow 36 upstream of the evaporator 28 ). The sensor 75 may form part of a control thermostat. Accordingly, use of such a sensor alone may permit cost savings through the elimination of the pressure sensor 52 or 74 .
  • the flow through the system is a direct function of the density of the refrigerant entering the compressor and, to a lesser extent, the pressure ratio of the compressor.
  • the inlet density is a direct function of the saturation temperature and superheat of the refrigerant.
  • These, in turn, are direct functions of the air temperature, system size, and charge.
  • these parameters may be determined in the design stage as a function of air temperature flowing through the evaporator. A correlation can be produced which matches the evaporator air temperature to the refrigerant inlet density.
  • the solenoid valve(s) would remain in the open position until the output of the evaporator temperature sensor 75 drops below a predetermined value.
  • the solenoid valve or one of the solenoid valves is closed. This can be repeated for systems having multiple solenoid valves further reducing the effective expansion orifice area as the temperature drops so as to maintain a mere optimal pressure in the high pressure portion of the system.
  • a high-side pressure is directly measured (e.g., by the sensor 74 ) a different correlation may be used.
  • the optimal high-side pressure may be known as a function of evaporator temperature and, optionally, the ambient temperature.
  • the solenoid valve or valves may be actuated to maintain the pressure within certain limits.
  • FIG. 9 shows an exemplary cooler 200 having a removable cassette 202 containing the refrigerant and air handling systems.
  • the exemplary cassette 202 is mounted in a compartment of a base 204 of a housing.
  • the housing has an interior volume 206 between left and right side walls, a rear wall/duct 216 , a top wall/duct 218 , a front door 220 , and the base compartment.
  • the interior contains a vertical array of shelves 222 holding beverage containers 224 .
  • the exemplary cassette 202 draws the air flow 34 through a front grille in the base 224 and discharges the air flow 34 from a rear of the base.
  • the cassette may be extractable through the base front by removing or opening the grille.
  • the exemplary cassette drives the air flow 36 on a recirculating flow path through the interior 206 via the rear duct 210 and top duct 218 .
  • FIG. 10 shows further details of an exemplary cassette 202 .
  • the heat exchanger 28 is positioned in a well 240 defined by an insulated wall 242 .
  • the heat exchanger i 28 is shown positioned mostly in an upper rear quadrant of the cassette and oriented to pass the air flow 36 generally rearwardly, with an upturn after exiting the heat exchanger so as to discharge from a rear portion o the cassette upper end, a drain 250 may extend through a bottom of the wall 242 to pass water condensed from the flow 36 to a drain pan 252 .
  • a water accumulation 254 is shown in the pan 252 .
  • the pan 252 is along an air duct 256 passing the flow 34 downstream of the heat exchanger 24 . Exposure of the accumulation 254 to the heated air in the flow 34 may encourage evaporation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
US11/908,629 2005-03-18 2005-12-30 High Side Pressure Regulation For Transcritical Vapor Compression System Abandoned US20080202140A1 (en)

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Application Number Priority Date Filing Date Title
US11/908,629 US20080202140A1 (en) 2005-03-18 2005-12-30 High Side Pressure Regulation For Transcritical Vapor Compression System

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US66396005P 2005-03-18 2005-03-18
PCT/US2005/047528 WO2006101566A1 (en) 2005-03-18 2005-12-30 High side pressure regulation for transcritical vapor compression
US11/908,629 US20080202140A1 (en) 2005-03-18 2005-12-30 High Side Pressure Regulation For Transcritical Vapor Compression System

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US (1) US20080202140A1 (zh)
EP (1) EP1963760A4 (zh)
JP (1) JP2008533428A (zh)
CN (1) CN101142450B (zh)
HK (1) HK1118600A1 (zh)
WO (1) WO2006101566A1 (zh)

Cited By (5)

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US20080256974A1 (en) * 2005-03-18 2008-10-23 Carrier Commercial Refrigeration, Inc. Condensate Heat Transfer for Transcritical Carbon Dioxide Refrigeration System
US20100300127A1 (en) * 2007-10-17 2010-12-02 Carrier Corporation Refrigerated Case
US20130233009A1 (en) * 2012-03-08 2013-09-12 Toromont Industries Ltd Co2 refrigeration system for ice-playing surface
US20150168036A1 (en) * 2013-12-17 2015-06-18 Lennox Industries Inc. Managing high pressure events in air conditioners
CN111351273A (zh) * 2020-04-13 2020-06-30 宁波奥克斯电气股份有限公司 一种节流机构、空调器及节流控制方法

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WO2010039630A2 (en) * 2008-10-01 2010-04-08 Carrier Corporation High-side pressure control for transcritical refrigeration system

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Publication number Priority date Publication date Assignee Title
US20080256974A1 (en) * 2005-03-18 2008-10-23 Carrier Commercial Refrigeration, Inc. Condensate Heat Transfer for Transcritical Carbon Dioxide Refrigeration System
US20100300127A1 (en) * 2007-10-17 2010-12-02 Carrier Corporation Refrigerated Case
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JP2008533428A (ja) 2008-08-21
HK1118600A1 (en) 2009-02-13
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EP1963760A4 (en) 2011-03-09
EP1963760A1 (en) 2008-09-03
CN101142450B (zh) 2011-06-22

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