WO2007022777A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2007022777A1
WO2007022777A1 PCT/DK2006/000458 DK2006000458W WO2007022777A1 WO 2007022777 A1 WO2007022777 A1 WO 2007022777A1 DK 2006000458 W DK2006000458 W DK 2006000458W WO 2007022777 A1 WO2007022777 A1 WO 2007022777A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
flow
flow channel
channel
refrigerant
Prior art date
Application number
PCT/DK2006/000458
Other languages
English (en)
Inventor
Finn Guldager Christensen
Original Assignee
Knudsen Køling A/S
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 Knudsen Køling A/S filed Critical Knudsen Køling A/S
Publication of WO2007022777A1 publication Critical patent/WO2007022777A1/fr

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Classifications

    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/082—Heat exchange elements made from metals or metal alloys from steel or ferrous alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • F28F21/085—Heat exchange elements made from metals or metal alloys from copper or copper alloys
    • 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
    • F25B2400/24—Storage receiver heat
    • 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
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F28D20/021—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat the latent heat storage material and the heat-exchanging means being enclosed in one container

Definitions

  • the present invention relates to a heat exchanger, and in particular the present invention relates to a heat exchanger for a transcritical refrigeration system.
  • heat release from the refrigerant is based on condensation of the refrigerant.
  • the "real life" upper limit for heat release based on condensation of CO 2 will be around 20 0 C ambient temperature. Below this temperature, the CO 2 stays below the critical point and the refrigeration system operates in subcritical cycles.
  • cooling of the CO 2 is a single-phase cooling, namely a gas cooling.
  • CO 2 is above the critical point at the high- pressure side of the system, and the refrigeration system operates in transcritical cycles.
  • the efficiency and cooling capacity of the refrigeration system is lower in transcritical operation than in subcritical operation.
  • a transcritical refrigeration system with improved performance during transcritical operation is provided by incorporation of one or more heat exchangers.
  • the high and low pressure generated by the compressor in a transcritical refrigeration system with CO 2 refrigerant are approximately 120 bar and 40 bar, respectively.
  • a heat exchanger with a first flow channel positioned in thermal contact with a second flow channel for heat exchange between a first fluid flowing in the first channel and a second fluid flowing in the second channel.
  • the first and second flow channels are tubular flow channels and the first flow channel is positioned within and enclosed by the second flow channel whereby a good thermal contact between the flow channels is provided facilitating heat exchange between fluids flowing in the flow channels.
  • the tubular flow channels have a circular cross-section for low manufacturing cost.
  • the outer surface of the inner flow channel may be corrugated or have fins so that the surface area is increased and the heat transfer enhanced.
  • the first tubular flow channel may be substantially concentric with the second tubular flow channel so that the fluid flow in the second channel is substantially uniform and symmetric for the best heat exchange.
  • the heat exchanger comprises two linear tubes with circular cross-sections extending along the same longitudinal axis.
  • the heat exchanger comprises two linear tubes with circular cross-sections extending along the same longitudinal axis that are bend into a meander shape with linear sections interconnected by bended sections, preferably turning the flow direction 180°.
  • a bended section is formed without thermal contact between the fluid channels so that no heat exchange takes place in the bended section for ease of manufacturing.
  • the heat exchanger comprises two linear tubes with circular cross-sections extending along the same longitudinal axis that are bend into a spiral.
  • the first channel is formed by a tube made of stainless steel capable of sustaining the pressure of the high-pressure side of the compressor, typically 120 bar.
  • the second channel is preferably formed by a tube made of copper that is silver soldered around the stainless steel tube and having copper fittings forming the flow inlet and outlet.
  • the copper tube is capable of sustaining the pressure of the low-pressure side of the compressor, typically 40 bar.
  • a heat exchanger is utilized in a transcritical refrigeration system comprising a refrigerant flow circuit for recirculation of a refrigerant, the refrigerant flow circuit comprising a compressor for generation of a refrigerant flow from a low-pressure side to a high-pressure side of the compressor and, in the order defined by the flow direction, connected in series with a gas cooler for cooling of the refrigerant towards the ambient temperature, a pressure reducing device, such as a reduction valve, separating the low-pressure side and the high pressure side of the compressor, and a first evaporator for evaporation of the refrigerant, e.g. in a cooling furniture.
  • the heat exchanger has its first channel connected in the refrigerant flow circuit between the gas cooler and the pressure-reducing device so that the first channel is incorporated in the refrigerant flow channel.
  • the second channel of the heat exchanger is used for a thermal medium flow.
  • the second channel is connected in series with a storage tank for storage of the thermal medium, e.g. water, the storage tank further comprising a second evaporator connected with the refrigerant flow circuit in parallel with the first evaporator for cooling of the thermal medium.
  • the cooling capacity of the system that is available at low ambient temperatures, i.e. during subcritical operation of the system, may be stored in the storage tank for later use, such as for use during transcritical operation of the system, when the system without the stored cooling capability would operate with a lowered performance.
  • the thermal medium is water, and preferably the water is cooled to ice in the storage tank during subcritical operation of the system.
  • the thermal storage tank may also comprise a thermal medium flow path connected in series with the thermal medium flow path of the heat exchanger so that the thermal medium flows into thermal contact with a second thermal medium, e.g. water, stored in the thermal storage tank and cooled by the second evaporator during subcritical operation of the system.
  • the second thermal medium may undergo a phase transition, e.g. water to ice, during cooling.
  • a phase transition e.g. from water to ice, makes it possible to store a large cooling capacity in the storage tank.
  • a second pressure reducing device may be connected in series with and between the gas cooler and the heat exchanger for adjustment of a desired pressure in the gas cooler.
  • the second pressure reducing device may alternatively be connected between the heat exchanger and the receiver.
  • an optimum gas cooler pressure exists during transcritical operation of the system.
  • the second pressure reducing device such as an expansion valve, may be controlled so that the gas cooler pressure attains the optimum value or approximately the optimum value.
  • the heat exchanger also causes a pressure reduction from the input to the output of the heat exchanger as a result of the cooling of the refrigerant.
  • the heat exchanger may also function as the second pressure reducing device and the flow of thermal medium through the heat exchanger may be controlled so that the gas cooler pressure attains the optimum value or approximately the optimum value.
  • a heat exchanger according to the present invention may have the first flow channel connected with the refrigerant flow circuit between the compressor and the gas cooler and with the second flow channel connected with the above-mentioned storage tank for fluid flow of the thermal medium so that heat exchange between the refrigerant at the high pressure side of the compressor and the thermal medium can take place for heating of the thermal medium and storage of the heated medium in the thermal storage tank.
  • the heated medium may be used for heating purposes.
  • the thermal storage tank may also comprise a thermal medium flow path connected in series with the thermal medium flow path of the second heat exchanger so that the thermal medium flows into thermal contact with a second thermal medium, e.g. water, stored in the thermal storage tank.
  • a second thermal medium e.g. water
  • a heat exchanger according to the present invention may be used for heat exchange between the high-pressure side and the low-pressure side of the compressor for improved efficiency of the refrigeration system.
  • the first flow channel may be connected in the refrigerant flow circuit between the compressor and the gas cooler, or between the gas cooler and the second pressure reducing device, or between the second pressure reducing device and the receiver.
  • the second flow channel may be connected in the refrigerant flow circuit between the evaporator and the compressor.
  • Fig. 1 is a blocked schematic of a first embodiment of a transcritical cooling system according to the present invention
  • Fig. 2 is a plot of a subcritical cooling cycle
  • Fig. 3 is a plot of a transcritical cooling cycle
  • Fig. 4 is a plot illustrating control of gas cooler pressure
  • Fig. 5 is a blocked schematic of a second embodiment of a transcritical cooling system according to the present invention.
  • Fig. 6 shows a longitudinal cross-section of a first and a second embodiment of a heat exchanger according to the present invention
  • Fig. 7 illustrates various positions of a heat exchanger in a refrigeration system according to the present invention.
  • Fig. 1 is a blocked schematic of a first embodiment 10 of a transcritical cooling system according to the present invention.
  • the system 10 comprises a refrigerant flow circuit for recirculation of CO 2 refrigerant 12, the refrigerant flow circuit comprising a compressor 14 for generation of a refrigerant flow in the direction of the arrow 16 from a low-pressure side to a high-pressure side of the compressor 14 and, in the order defined by the flow direction, connected in series with a gas cooler 18 for cooling of the refrigerant 12 towards the ambient temperature, a valve 20 for pressure reduction as will be further explained below, a heat exchanger 22 with the first flow channel 24 connected in the refrigerant flow circuit between the gas cooler 18 and a receiver 26 for accommodation of CO 2 refrigerant 12.
  • the receiver 26 is connected to an expansion valve 28 separating the low-pressure side and the high- pressure side of the compressor 14, and a first evaporator 30 for evaporation of the CO 2 refrigerant.
  • Fig. 2 illustrates subcritical operation of the system 10 in a conventional Log (p), h (enthalpy) diagram.
  • the compressor 14 compresses the CO 2 refrigerant, and subsequently heat is released from the refrigerant from point 2 to 3 below the critical point 32 by condensation of the refrigerant in the gas cooler (condenser) 18 at a constant pressure.
  • Fig. 3 illustrates transcritical operation of the system 10.
  • the most important difference between the plot of Fig. 3 and the plot of Fig. 2 is that the CO 2 refrigerant is above the critical point 32 at the high-pressure side of the compressor 14 and thus, heat is released from the refrigerant by CO 2 gas cooling in the gas cooler 18.
  • the coefficient of performance (COP) of the system 10 is less for transcritical cycles than for subcritical cycles due to the lacking phase transition, i.e. no condensation, during heat release.
  • the expansion from point 3 to 4 takes place in two steps, namely from point 3 to 5, and subsequently from point 5 to 4.
  • the valve 20 reduces the pressure from point 3 to point 5 so that CO 2 in the liquid phase enters the heat exchanger 22 and is collected in the receiver 26. Further, the valve 20 is controlled in such a way that the pressure in the gas cooler 18 attains a value that gives substantially the best possible COP. This is further illustrated in Fig. 4. In addition to the transcritical cooling cycle, Fig. 4 shows two isotherms 34, 36.
  • the COP decreases for increased gas cooler pressure.
  • the valve 20 is adjusted in such a way that the gas cooler pressure attains, at least approximately, this optimum pressure value.
  • the gas cooler pressure is app. 120 bar while the pressure at the low-pressure side of the compressor 14 is app. 40 bar.
  • the heat exchanger 22 also comprises a thermal medium flow channel 38 for a thermal medium flow and connected in series with a storage tank 40 for storage of water and ice.
  • the storage tank 30 further comprises an evaporator 42 connected to an expansion valve 44 so that the evaporator 42 is connected in the refrigerant flow circuit in parallel with the first evaporator 30.
  • the evaporator 42 operates in parallel with the evaporator 30 so that the water in the storage tank 20 is cooled to ice.
  • the pump 46 is operated and the three-way valve 50 is opened to pump water at the freezing point through the thermal medium flow channel 38 for further cooling of the CO 2 refrigerant whereby the capacity of the system 10 is increased during transcritical operation.
  • the embodiment of Fig. 5 corresponds to the embodiment of Fig. 1 with a further heat exchanger 50 inserted in the refrigerant flow circuit between the compressor 14 and the gas cooler 18.
  • the heat exchanger 50 has a refrigerant flow channel 52 connected in the refrigerant flow circuit between the compressor 14 and the gas cooler 18.
  • the heat exchanger 50 also comprises a thermal medium flow channel 54 for a thermal medium flow and connected in series with the storage tank 40 for storage of water and ice.
  • valves 48, 56, 58 are opened allowing the pump 46 to pump water from the storage tank 40 through the heat exchanger 50 for heating of the water, and back into the storage tank.
  • the storage tank may further be connected to a heating system (not shown) that utilizes the heated water.
  • the water is cooled to ice, when the system 10 operates in subcritical cycles and the ice water is used for cooling of the refrigerant in the heat exchanger 22 when the system 10 operates in transcritical cycles as described above with reference to Fig. 1.
  • Fig. 6 shows a longitudinal cross-section of a first and a second embodiment of a heat exchanger according to the present invention.
  • the heat exchanger 100 has a first flow channel 102 positioned in thermal contact with a second flow channel 104 for heat exchange between a first fluid flowing in the first channel 102 and a second fluid counter-flowing in the second channel 104.
  • the first flow channel is defined within a stainless steel tube 106 with a circular cross-section that is capable of sustaining high pressures, such as the pressure of the high-pressure side of the compressor, e.g. 120 bar.
  • the second channel is defined within a copper tube 108 between the inner wall of the copper tube 108 and the outer wall of the stainless steel tube 106 that is positioned inside the copper tube 108. Heat exchange takes place through the stainless steel wall of the stainless steel tube 108 having good heat conducting properties and a large contact surface with the fluid in the copper tube 108.
  • the inlet 110 and outlet 112 of the copper tube are formed by copper fittings.
  • the stainless steel tube 106 and the copper tube 108 are silver soldered together at the ends 114, 116 of the copper tube and extend concentrically along
  • the heat exchanger 100 comprises two linear tubes 106, 108 with circular cross-sections extending along the same longitudinal axis that are bend into a meander-like shape with two linear sections 118, 120 interconnected by a bended section 122 turning the flow direction 180°.
  • the heat exchanger may have more than two linear sections with a corresponding number of bended sections.
  • Fig. 7 illustrates various positions of a heat exchanger in a refrigeration system according to the present invention.
  • a heat exchanger according to the present invention is used for heat exchange between the high-pressure side and the low-pressure side of the compressor for improved efficiency of the refrigeration system.
  • the first flow channel is connected in the refrigerant flow circuit between the gas cooler and the second pressure reducing device.
  • the second flow channel is connected in the refrigerant flow circuit between the evaporator and the compressor.
  • Position 2 corresponds to the position of the heat exchanger in Fig. 1.
  • the heat exchanger may also be positioned upstream the second pressure reducing device.
  • Position 3 corresponds to the position of the second heat exchanger in Fig. 5.
  • An embodiment of the invention may have one heat exchanger in any of the positions shown in Fig. 7 or upstream the second pressure reducing device as required. Another embodiment may have two heat exchangers in any combination of the positions in Fig. 7 or upstream the second pressure reducing device as required. Yet another embodiment may have three heat exchangers in the positions shown in Fig. 7 or upstream the second pressure reducing device as previously mentioned.

Abstract

La présente invention vise un échangeur de chaleur (22,100), en particulier pour un système de réfrigération transcritique (10) avec un premier circuit d’écoulement (24,102) positionné en contact thermique avec un deuxième circuit d’écoulement (38,104) destiné à échanger de la chaleur entre un premier écoulement de fluide dans le premier circuit et un deuxième écoulement de fluide dans le deuxième circuit. Les premier et deuxième circuits d’écoulement sont des circuits d’écoulement tubulaires, le premier circuit d’écoulement étant positionné à l’intérieur du deuxième circuit d’écoulement et enclos dans celui-ci. Ceci assure un bon contact thermique entre les circuits d’écoulement et facilite l’échange de chaleur entre les fluides passant dans les circuits d’écoulement. Le premier circuit d’écoulement tubulaire peut être sensiblement concentrique au deuxième circuit d’écoulement tubulaire de façon à ce que l’écoulement de fluide dans le deuxième circuit soit sensiblement uniforme et symétrique pour un échange de chaleur optimal. Dans un mode de réalisation simple préféré, l’échangeur de chaleur comporte deux tubes linéaires dont les coupes circulaires se prolongent sur le même axe longitudinal.
PCT/DK2006/000458 2005-08-25 2006-08-24 Échangeur de chaleur WO2007022777A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA200501185 2005-08-25
DKPA200501185 2005-08-25

Publications (1)

Publication Number Publication Date
WO2007022777A1 true WO2007022777A1 (fr) 2007-03-01

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2205910A1 (fr) * 2007-11-05 2010-07-14 Alfa Laval Corporate AB Séparateur de liquide pour un système d'évaporateur
WO2012109057A3 (fr) * 2011-02-08 2012-10-11 Carrier Corporation Echangeur de chaleur a rejet de chaleur refroidi par l'eau
US20120312041A1 (en) * 2011-06-10 2012-12-13 Jordan Kantchev Suction compressor temperature regulator device for transcritical and subcritical r-744 compressors
US9194615B2 (en) 2013-04-05 2015-11-24 Marc-Andre Lesmerises CO2 cooling system and method for operating same
US10690389B2 (en) 2008-10-23 2020-06-23 Toromont Industries Ltd CO2 refrigeration system
US11656005B2 (en) 2015-04-29 2023-05-23 Gestion Marc-André Lesmerises Inc. CO2 cooling system and method for operating same

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DE33168C (fr) *
GB118866A (en) * 1917-07-24 1918-08-26 Reginald Martin Mckech Dickson Improvements in Refrigerating Machines.
GB151258A (en) * 1919-09-19 1921-07-07 Fritz Wilhelm Improvements in surface apparatus for effecting transfer of heat
GB230586A (en) * 1924-01-16 1925-03-19 William George Brettell Improvements in and connected with refrigeration systems in which gases are liquefied by compression and the liquid evaporated
GB230922A (en) * 1923-12-20 1925-03-20 William George Brettell Improvements in and connected with refrigeration systems in which gases are liquified by compression and the liquid evaporated
US1795872A (en) * 1928-09-29 1931-03-10 Frigidaire Corp Refrigerating apparatus
FR1082615A (fr) * 1952-01-11 1954-12-30 Soutirage de froid pour faciliter la condensation des fluides frigorifiques
US4210199A (en) * 1978-06-14 1980-07-01 Doucette Industries, Inc. Heat exchange system
EP0837291A2 (fr) * 1996-08-22 1998-04-22 Denso Corporation Système frigorifique du type à compression de vapeur
JPH11142007A (ja) * 1997-11-06 1999-05-28 Nippon Soken Inc 冷凍サイクル
JP2000356419A (ja) * 1999-06-17 2000-12-26 Japan Climate Systems Corp 車両用空調装置
US20020046830A1 (en) * 2000-10-25 2002-04-25 Holger Ulrich Air conditioner with internal heat exchanger and heat exchanger tube therefor
JP2002156162A (ja) * 2000-11-16 2002-05-31 Mitsubishi Heavy Ind Ltd インタークーラ及び車両用ｃｏ２冷媒空調装置
JP2003194421A (ja) * 2001-12-28 2003-07-09 Matsushita Electric Ind Co Ltd 冷凍サイクル
JP2004093037A (ja) * 2002-08-30 2004-03-25 Toyo Radiator Co Ltd 二重管型熱交換器
WO2004054827A1 (fr) * 2002-12-16 2004-07-01 Daimlerchrysler Ag Installation de climatisation conçue en particulier pour des vehicules automobiles
EP1462281A2 (fr) * 2003-02-15 2004-09-29 Volkswagen Aktiengesellschaft Appareil de climatisation avec plusieurs évaporateurs pour véhicule à moteur

Patent Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE33168C (fr) *
GB118866A (en) * 1917-07-24 1918-08-26 Reginald Martin Mckech Dickson Improvements in Refrigerating Machines.
GB151258A (en) * 1919-09-19 1921-07-07 Fritz Wilhelm Improvements in surface apparatus for effecting transfer of heat
GB230922A (en) * 1923-12-20 1925-03-20 William George Brettell Improvements in and connected with refrigeration systems in which gases are liquified by compression and the liquid evaporated
GB230586A (en) * 1924-01-16 1925-03-19 William George Brettell Improvements in and connected with refrigeration systems in which gases are liquefied by compression and the liquid evaporated
US1795872A (en) * 1928-09-29 1931-03-10 Frigidaire Corp Refrigerating apparatus
FR1082615A (fr) * 1952-01-11 1954-12-30 Soutirage de froid pour faciliter la condensation des fluides frigorifiques
US4210199A (en) * 1978-06-14 1980-07-01 Doucette Industries, Inc. Heat exchange system
EP0837291A2 (fr) * 1996-08-22 1998-04-22 Denso Corporation Système frigorifique du type à compression de vapeur
JPH11142007A (ja) * 1997-11-06 1999-05-28 Nippon Soken Inc 冷凍サイクル
JP2000356419A (ja) * 1999-06-17 2000-12-26 Japan Climate Systems Corp 車両用空調装置
US20020046830A1 (en) * 2000-10-25 2002-04-25 Holger Ulrich Air conditioner with internal heat exchanger and heat exchanger tube therefor
JP2002156162A (ja) * 2000-11-16 2002-05-31 Mitsubishi Heavy Ind Ltd インタークーラ及び車両用ｃｏ２冷媒空調装置
JP2003194421A (ja) * 2001-12-28 2003-07-09 Matsushita Electric Ind Co Ltd 冷凍サイクル
JP2004093037A (ja) * 2002-08-30 2004-03-25 Toyo Radiator Co Ltd 二重管型熱交換器
WO2004054827A1 (fr) * 2002-12-16 2004-07-01 Daimlerchrysler Ag Installation de climatisation conçue en particulier pour des vehicules automobiles
EP1462281A2 (fr) * 2003-02-15 2004-09-29 Volkswagen Aktiengesellschaft Appareil de climatisation avec plusieurs évaporateurs pour véhicule à moteur

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EP2205910A1 (fr) * 2007-11-05 2010-07-14 Alfa Laval Corporate AB Séparateur de liquide pour un système d'évaporateur
EP2205910A4 (fr) * 2007-11-05 2013-03-20 Alfa Laval Corp Ab Séparateur de liquide pour un système d'évaporateur
US10036583B2 (en) 2007-11-05 2018-07-31 Alfa Laval Corporated Ab Liquid separator for an evaporator system
US10690389B2 (en) 2008-10-23 2020-06-23 Toromont Industries Ltd CO2 refrigeration system
WO2012109057A3 (fr) * 2011-02-08 2012-10-11 Carrier Corporation Echangeur de chaleur a rejet de chaleur refroidi par l'eau
US10401094B2 (en) 2011-02-08 2019-09-03 Carrier Corporation Brazed plate heat exchanger for water-cooled heat rejection in a refrigeration cycle
US20120312041A1 (en) * 2011-06-10 2012-12-13 Jordan Kantchev Suction compressor temperature regulator device for transcritical and subcritical r-744 compressors
US9194615B2 (en) 2013-04-05 2015-11-24 Marc-Andre Lesmerises CO2 cooling system and method for operating same
US11656005B2 (en) 2015-04-29 2023-05-23 Gestion Marc-André Lesmerises Inc. CO2 cooling system and method for operating same

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