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WO2008130412A1 - Système de réfrigérant à co2 avec circuit intensificateur - Google Patents

Système de réfrigérant à co2 avec circuit intensificateur Download PDF

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Publication number
WO2008130412A1
WO2008130412A1 PCT/US2007/067168 US2007067168W WO2008130412A1 WO 2008130412 A1 WO2008130412 A1 WO 2008130412A1 US 2007067168 W US2007067168 W US 2007067168W WO 2008130412 A1 WO2008130412 A1 WO 2008130412A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
set forth
heat
compressor
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.)
Ceased
Application number
PCT/US2007/067168
Other languages
English (en)
Inventor
Michael F. Taras
Alexander Lifson
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.)
Carrier Corp
Original Assignee
Carrier Corp
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 Corp filed Critical Carrier Corp
Priority to EP07761081A priority Critical patent/EP2150755A4/fr
Priority to US12/596,846 priority patent/US20100043475A1/en
Priority to PCT/US2007/067168 priority patent/WO2008130412A1/fr
Priority to HK10109017.8A priority patent/HK1142662B/xx
Priority to CN200780053471.7A priority patent/CN101688695B/zh
Publication of WO2008130412A1 publication Critical patent/WO2008130412A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0234—Header boxes; End plates having a second heat exchanger disposed there within, e.g. oil cooler
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/074—Details of compressors or related parts with multiple cylinders
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Definitions

  • This application relates to refrigerant systems which utilize CO 2 refrigerant and are provided with a booster circuit to enhance operational performance.
  • Refrigerant systems are known in the HVAC&R (heating, ventilation, air conditioning and refrigeration) art, and operate to compress and circulate a refrigerant throughout a closed-loop refrigerant circuit, connecting a plurality of components, to condition a secondary fluid to be delivered to a climate-controlled space.
  • HVAC&R heating, ventilation, air conditioning and refrigeration
  • refrigerant is compressed in a compressor from a lower to a higher pressure and delivered to a downstream heat rejection heat exchanger, which is a so-called gas cooler, in transcritical applications, or a so-called condenser, in subcritical applications.
  • refrigerant flows to an expansion device where it is expanded to a lower pressure and temperature and then is routed to an evaporator, where refrigerant cools a secondary fluid to be delivered to the conditioned environment. From the evaporator, refrigerant is returned to the compressor.
  • refrigerant systems is an air conditioning system, which operates to condition (cool and often dehumidify) air to be delivered into a climate-controlled zone or space.
  • CO2 Due to its low critical point, CO2 often operates in a transcritical cycle (rejects heat above the two-phase dome or above the critical point) that has certain inherit inefficiencies associated with the heat rejection process. Therefore, refrigerant systems utilizing CO 2 as a refrigerant do not always operate at the efficiency levels of traditional refrigerant systems. Thus, it is desirable to provide design features enhancing CO 2 system performance to become comparable to the traditional refrigerant systems for a wide spectrum of operating and environmental conditions.
  • a separate closed-loop booster circuit is provided in combination with a main refrigerant circuit utilizing CO 2 as a refrigerant.
  • the booster circuit provides extra cooling for the high pressure refrigerant, in addition to the cooling provided in the heat rejection heat exchanger of the main CO 2 system.
  • the booster circuit may also utilize CO 2 as a refrigerant.
  • the booster system may cool the refrigerant in the main liquid line, in the main heat rejection heat exchanger, or in a separate heat exchanger positioned downstream of the main heat rejection heat exchanger, with respect to the refrigerant flow.
  • the heat rejection heat exchanger of the booster circuit can be combined with the heat rejection heat exchanger of the main circuit in a single construction, such that a single air management (fan) system may be utilized to move air over both heat exchangers. Both heat rejection heat exchangers are preferably positioned to provide a more efficient counterflow configuration, with respect to the airflow.
  • the compressor for the booster circuit may be combined with the main circuit compression system, such as, for instance, some of the cylinder banks of a multi-piston compressor system, or may comprise a separate compressor unit.
  • the booster circuit may be provided to enhance or assist with other features of the refrigerant system, such as an economizer function, "liquid-to-suction" heat exchanger, intercooling and liquid injection.
  • Figure 1 shows a first schematic of the present invention.
  • Figure 2 shows a second schematic of the present invention.
  • Figure 3 shows a third schematic of the present invention.
  • Figure 4 shows a fourth schematic of the present invention.
  • Figure 5 shows a fifth schematic of the present invention.
  • Figure 6 shows a sixth schematic of the present invention.
  • Figure 7 shows system performance improvement obtained by the present invention.
  • Refrigerant system 20 is illustrated in Figure 1 and includes a main closed-loop refrigerant circuit 21 and a booster closed-loop refrigerant circuit 32.
  • a main circuit compressor 22 compresses a refrigerant and delivers it downstream to a main circuit heat rejection heat exchanger 24, which is a so-called gas cooler in transcritical applications or a so-called condenser in subcritical applications.
  • a separate heat exchanger 26 is positioned downstream of the heat rejection heat exchanger 24, with respect to the refrigerant flow, to provide extra cooling to the main circuit refrigerant.
  • a main circuit expansion device 28 is positioned downstream of the heat exchanger 26, and a main circuit evaporator 30 is located downstream of the expansion device 26.
  • the evaporator 30 operates with an associated air-moving device, such as fan, to condition (cool and often dehumidify) air being delivered into a climate-controlled zone or space of the indoor environment.
  • a separate closed-loop booster circuit 32 is associated with the heat exchanger 26.
  • a booster circuit compressor 34 compresses refrigerant and delivers it to a booster circuit heat rejection heat exchanger 36, a booster circuit expansion device 38 and then through the heat accepting heat exchanger 26.
  • the main circuit 21 operates with CO 2 as a refrigerant.
  • CO 2 refrigerant has some challenges in providing adequate cooling performance levels, and in particular as compared to the cooling performance levels provided by the prior art traditional refrigerants. As noted above, since the CO 2 refrigerant has a low critical point, it quite often operates in a transcritical cycle, which has certain inherent inefficiencies, in comparison to a traditional subcritical vapor compression cycle.
  • the implementation of the heat exchanger 26 provides extra cooling for the main circuit refrigerant, prior to entering the expansion device 28, and a subsequent capacity boost in the evaporator 30 as well as potential thermodynamic efficiency augmentation for the entire refrigerant system 20.
  • the employment of the heat accepting heat exchanger 26 allows CO 2 refrigerant systems to enhance performance requirements (capacity and thermodynamic efficiency) of modern refrigerant systems, and, in particular, air conditioning systems.
  • the compressor 34 of the booster circuit 32 operates at much lower pressure ratios (as well as pressure differentials), in comparison to the compressor 22 of the main circuit 21, and should have better performance characteristics (isentropic and volumetric efficiencies).
  • booster circuit compressor 34 will take advantage of a steeper slope of constant entropy lines in its operational domain, translating into lower compressor power consumption. Both phenomena described above improve overall performance characteristics (capacity and thermodynamic efficiency) of the refrigerant system 20.
  • the booster circuit 32 may also operate with CO 2 as its refrigerant.
  • Refrigerant flows in the heat exchanger 26 are preferably arranged in a counterflow configuration, in order to improve the heat exchanger effectiveness.
  • the heat exchanger 26 could be incorporated into the design of the heat rejection heat exchanger 24.
  • a tube-and-shell heat exchanger 26 may be configured as an outlet manifold of the heat exchanger 24.
  • the heat exchanger 26 may be a separate heat exchange unit, such as a brazed plate heat exchanger.
  • the booster circuit heat rejection heat exchanger 36 is shown in Figure 1 as a separate unit, it may be combined with the main circuit heat rejection heat exchanger 24. In this case, a single air management (fan) system can be provided to move air over both heat exchangers 24 and 36 that are preferably arranged in a counterflow configuration, with respect to the airflow.
  • a single air management (fan) system can be provided to move air over both heat exchangers 24 and 36 that are preferably arranged in a counterflow configuration, with respect to the airflow.
  • another embodiment 44 provides tandem compressor stages 46 and 48 which circulate refrigerant through a main circuit 41, including a heat rejection heat exchanger 50, a heat exchanger 52, the expansion device 28, and the evaporator 30.
  • a separate compressor stage 54 compresses the refrigerant in a booster circuit 42 and circulates it through a heat rejection heat exchanger 56, the heat exchanger 52, an expansion device 43 and back to the compressor 54.
  • a fan system 57 may be designed to move air over both heat rejection heat exchangers 50 and 56. In this manner, there is not the requirement of a separate air-moving device for each heat exchanger.
  • heat rejection heat exchangers 50 and 56 are shown in a sequential arrangement, with respect to the airflow, they can also be positioned in a parallel configuration.
  • the tandem compressors 46 and 48 of the main circuit 41 and the compressor 54 of the booster circuit 42 may all be receiving power from the same source of energy or be driven by the same mechanism.
  • a common eccentric drive may be provided for a multi-piston reciprocating compressor arrangement.
  • the compressors 46, 48 and 54 although in general operating at different pressures, may be represented by separate compressor banks of the same reciprocating compressor.
  • Figure 2 embodiment provides similar benefits to the embodiment shown in Figure 1.
  • FIG 3 shows an embodiment 60, wherein the compressor 62 of the main circuit 61 delivers refrigerant sequentially to a heat rejection heat exchanger 64, a heat exchanger 66, an expansion device 68 and an evaporator 70.
  • the refrigerant in the main circuit 61 flows from the evaporator 70 back through the heat exchanger 66, before returning to the compressor 62.
  • the heat exchanger 66 performs a function similar to a "liquid-to-suction" heat exchanger function (since, in transcritical operation, there may not be any liquid at the exit of the heat rejection heat exchanger 64 of the main circuit 61).
  • the booster circuit 75 includes a compressor 74 circulating the refrigerant through a heat rejection heat exchanger 76 and the heat exchanger 66.
  • the booster circuit refrigerant in the heat rejection heat exchanger 76 is cooled by a separate secondary fluid flowing through a conduit 80.
  • this secondary fluid flowing through the conduit 80 which could be, for instance, water, may be utilized as a source of heat for other needs.
  • the booster circuit 75 enhances the "liquid-to-suction" heat exchanger function, providing augmentation in performance characteristics of the refrigerant system 60.
  • this embodiment is similar to the embodiment of Figure 1.
  • FIG. 4 An embodiment 90 is illustrated in Figure 4.
  • two sequential stages of compression 92 and 94 are associated with the main circuit 91.
  • these two compression stages 92 and 94 are depicted as separate compressor units, they may be represented as the two compression stages within the same compressor housing.
  • the heat rejection heat exchanger 96 is positioned downstream of the second stage 94.
  • a tap line 100 taps a portion of refrigerant from a liquid line 106 in the main refrigerant circuit 91 and passes this tapped portion of the refrigerant through an auxiliary expansion device 102, where it is expanded to a lower pressure and temperature.
  • the tapped refrigerant passes in heat exchanger relationship with the main refrigerant flow in an economizer heat exchanger 98, to provide additional cooling to the main refrigerant, as known.
  • the refrigerant flows in the lines 100 and 106 through the economizer heat exchanger 98 are shown in the same direction, in practice, they are preferably arranged in a counterflow configuration, to enhance the effectiveness of the heat exchanger 98.
  • a flash tank arrangement can be utilized to provide similar functionality. Refrigerant in the tap line 100 is returned through a vapor injection line 104 to an intermediate pressure point between the compressors 92 and 94.
  • the booster circuit 108 serves to enhance the economizer function and to provide additional cooling in the economizer heat exchanger 98 to the refrigerant in the main circuit 91. Therefore, the main circuit refrigerant would have a greater cooling thermal potential in the evaporator 107, while refrigerant in the vapor injection line would have a lower temperature, enhancing the compression process.
  • the refrigerant in the main circuit 91 continues through the expansion device 28 and the evaporator 107 and returns to the first compression stage 92.
  • the compressor 110 compresses the refrigerant and delivers it through a heat rejection heat exchanger 112.
  • the refrigerant passes through an expansion device 116 and through the economizer heat exchanger 98 and returns to the compressor 110.
  • the purpose of this arrangement would be to provide addition cooling of the CO 2 refrigerant in the main circuit 91 and to reduce the temperature of the refrigerant vapor in the vapor injection line 104.
  • the booster circuit 115 allows for the enhancement of the economizer function, due the two phenomena described above, and subsequent performance augmentation of the refrigerant system 90. It should be noted that, although only one economizer circuit and two compression stages are shown in Figure 4, there may be any number of economizer circuits, compression stages and associated booster circuits incorporated into a single refrigerant system design. Also, as known, there are many variations of the economizer circuit arrangement, all of which can benefit from the present invention.
  • FIG. 5 Another embodiment 120 is illustrated in Figure 5.
  • the main refrigerant circuit 121 there are two sequential stages of compression 122 and 124 that may or may not be represented by separate compressor units, a heat rejection heat exchanger 126, a heat accepting heat exchanger 128, and an evaporator 136.
  • a portion the refrigerant is selectively diverted through an auxiliary expansion device 132, and into a liquid injection point 134 intermediate the compression stages 122 and 124.
  • the overall temperature of the refrigerant reaching the second compression stage 124 can be controlled.
  • a booster circuit 138 provides additional cooling in the heat exchanger 128 for the refrigerant circulating through the main circuit 121.
  • the booster circuit 138 includes a compressor 140, a heat rejection heat exchanger 142 and an expansion device 144. Therefore, the main circuit refrigerant reaching the diversion point 130 has a lower temperature, allowing not only for the performance enhancement in the evaporator 136, but also providing a greater cooling potential for the refrigerant injected between the compression stages 122 and 124. As a result, compression process is improved, discharge temperature control is provided and operational envelope for the refrigerant system 120 is extended. It has to be noted that there could be more then two compression stages and more than a single liquid injection point incorporated into the design of the refrigerant system 120.
  • FIG. 6 Another embodiment 220 is illustrated in Figure 6.
  • a heat rejection heat exchanger 226 is located downstream of the second compression stage and a heat accepting heat exchanger 228 is positioned downstream of the heat rejection heat exchanger 226, both with respect to the refrigerant flow.
  • An expansion device 28 and then an evaporator 236 are located in series downstream of the heat accepting heat exchanger 228, also with respect to the refrigerant flow.
  • An intercooler is positioned between the compression stages 222 and 224 and is an integral part of the heat accepting heat exchanger 228.
  • the intercooler provides cooling to the refrigerant vapor compressed in the first compression stage 222 and routed to the second compression stage 224.
  • the compression process is improved and the discharge temperature at the exit of the second compression stage 224 does not exceed the specified limit.
  • the overall system performance can be maximized by the discharge temperature reduction.
  • the design of the heat accepting heat exchanger 228 has all three refrigerant streams arranged in parallel, in some embodiments, the two refrigerant streams of the main circuit may be configured in sequence with each other to provide sequential heat transfer interaction with the booster circuit, preferably in a counterflow manner. Further, in the latter arrangement, the heat exchanger 228 may be represented by two separate heat exchanger units.
  • the present invention discloses various schematics and techniques which can be utilized to provide a booster circuit for obtaining an extra cooling of a CO 2 refrigerant in a main refrigerant circuit.
  • the additional benefits of enhancement of other features of the refrigerant systems, such as an economizer function, "liquid-to-suction" heat exchanger, intercooling and liquid injection are also disclosed.
  • compressor types could be used in this invention.
  • scroll, screw, rotary, or reciprocating compressors can be employed.
  • the refrigerant systems that utilize this invention can be used in many different applications, including, but not limited to, air conditioning systems, heat pump systems, marine container units, refrigeration truck-trailer units, and supermarket refrigeration systems.
  • the booster circuit itself may have various performance enhancement features, if desired. While several embodiments are disclosed, a worker of ordinary skill in this art would recognize that certain modifications come within the scope of this invention. For that reason the following claims should be studied to determine the true scope and content of this invention.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention concerne un système de réfrigérant, qui utilise du CO2 comme réfrigérant, qui comprend un circuit de réfrigérant en boucle fermée principal et un circuit de réfrigérant en boucle fermée intensificateur. Un échangeur de chaleur acceptant de la chaleur, ce qui assure un refroidissement supplémentaire du réfrigérant circulant dans le circuit principal et améliore ainsi l'efficacité du système de réfrigérant, sert également de composant partagé couplant les deux circuits par interaction de transfert de chaleur. Divers schémas et configurations pour le circuit intensificateur, qui peuvent être combinés avec d'autres caractéristiques d'amplification de l'efficacité, sont proposés. Des bénéfices supplémentaires de fonction d'économie, d'échangeur de chaleur « liquide à aspiration », de refroidissement intermédiaire et d'injection de liquide sont également proposés. Le circuit intensificateur peut également contenir du réfrigérant à CO2.
PCT/US2007/067168 2007-04-23 2007-04-23 Système de réfrigérant à co2 avec circuit intensificateur Ceased WO2008130412A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP07761081A EP2150755A4 (fr) 2007-04-23 2007-04-23 Système de réfrigérant à co<sb>2</sb>avec circuit intensificateur
US12/596,846 US20100043475A1 (en) 2007-04-23 2007-04-23 Co2 refrigerant system with booster circuit
PCT/US2007/067168 WO2008130412A1 (fr) 2007-04-23 2007-04-23 Système de réfrigérant à co2 avec circuit intensificateur
HK10109017.8A HK1142662B (en) 2007-04-23 Co2 refrigerant system with booster circuit
CN200780053471.7A CN101688695B (zh) 2007-04-23 2007-04-23 带增强器回路的co2制冷剂系统

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2007/067168 WO2008130412A1 (fr) 2007-04-23 2007-04-23 Système de réfrigérant à co2 avec circuit intensificateur

Publications (1)

Publication Number Publication Date
WO2008130412A1 true WO2008130412A1 (fr) 2008-10-30

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2007/067168 Ceased WO2008130412A1 (fr) 2007-04-23 2007-04-23 Système de réfrigérant à co2 avec circuit intensificateur

Country Status (4)

Country Link
US (1) US20100043475A1 (fr)
EP (1) EP2150755A4 (fr)
CN (1) CN101688695B (fr)
WO (1) WO2008130412A1 (fr)

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WO2012012485A1 (fr) 2010-07-23 2012-01-26 Carrier Corporation Cycle frigorifique à éjecteur et dispositif frigorifique l'utilisant
EP2631564A1 (fr) * 2012-02-24 2013-08-28 Airbus Operations GmbH Système de refroidissement fiable pour fonctionnement avec réfrigérant à deux phases
EP2330368A3 (fr) * 2009-11-20 2015-04-22 LG ELectronics INC. Appareil de refroidissement/chauffage de type pompe à chaleur
WO2016018692A1 (fr) * 2014-07-31 2016-02-04 Carrier Corporation Système de refroidissement
EP2482005A4 (fr) * 2009-09-25 2016-12-21 Hitachi Ltd Systeme d'alimentation en conditionnement d'air/eau chaude et unite de pompe a chaleur
US9726404B2 (en) 2012-02-24 2017-08-08 Airbus Operations Gmbh Cooling system with a plurality of subcoolers
US9857101B2 (en) 2010-07-23 2018-01-02 Carrier Corporation Refrigeration ejector cycle having control for supercritical to subcritical transition prior to the ejector
IT202100002630A1 (it) 2021-02-05 2021-05-05 Aircodue S R L Impianto di condizionamento e riscaldamento ambientale
IT202100006896A1 (it) 2021-03-23 2022-09-23 Aircodue S R L Impianto di condizionamento e riscaldamento ambientale
WO2023079114A1 (fr) * 2021-11-05 2023-05-11 Maersk Container Industry A/S Système de réfrigération en cascade

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EP2679933A4 (fr) * 2011-02-22 2014-07-30 Hitachi Ltd Système de conditionnement d'air et d'alimentation en eau chaude
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CN106352608B (zh) 2015-07-13 2021-06-15 开利公司 经济器组件及具有其的制冷系统
CN105222385B (zh) * 2015-10-20 2018-01-19 西安交通大学 一种跨临界co2复合热泵系统
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CN109073285A (zh) 2016-05-03 2018-12-21 开利公司 喷射器增强型热回收制冷系统
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CN108253650B (zh) * 2018-01-18 2019-04-12 西安交通大学 一种跨临界二氧化碳复合热泵系统的控制方法
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CN101688695B (zh) 2014-07-23
EP2150755A1 (fr) 2010-02-10
CN101688695A (zh) 2010-03-31
HK1142662A1 (en) 2010-12-10
EP2150755A4 (fr) 2011-08-24
US20100043475A1 (en) 2010-02-25

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