EP2525168B1 - Pompe à chaleur à compression de vapeur supercritique et unité d'alimentation en eau chaude - Google Patents

Pompe à chaleur à compression de vapeur supercritique et unité d'alimentation en eau chaude Download PDF

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Publication number
EP2525168B1
EP2525168B1 EP12167898.1A EP12167898A EP2525168B1 EP 2525168 B1 EP2525168 B1 EP 2525168B1 EP 12167898 A EP12167898 A EP 12167898A EP 2525168 B1 EP2525168 B1 EP 2525168B1
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Prior art keywords
refrigerant
gas
stage compressor
pressure
heat exchanger
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EP12167898.1A
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German (de)
English (en)
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EP2525168A1 (fr
Inventor
Taku Hokamura
Takuya Okada
Ken Watanabe
Shigeru Yoshida
Minemasa Omura
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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    • 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
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B2400/13—Economisers

Definitions

  • the present invention relates to a supercritical steam compression heat pump employing CO 2 refrigerant and to a hot-water supply unit to which the heat pump is applied.
  • heat-pump hot-water supply units in which refrigerant/water heat exchangers are employed as heat sinks thereof and in which heat exchange between the refrigerant and water is performed at the refrigerant/water heat exchangers, thereby heating water to produce hot water, have been known in the related art, as exemplified by Patent Literatures 1 and 2 or the like.
  • the discharge temperature from the compressor increases, as indicated by a broken line in Fig. 2 .
  • the discharge temperature is restricted to about 140 °C.
  • the present invention has been conceived in light of the above-described circumstances, and an object thereof is to provide, for a supercritical steam compression heat pump employing CO 2 refrigerant that utilizes heat exchange on a high-pressure side, as in supplying hot water or the like, a supercritical steam compression heat pump and a hot-water supply unit whose heating capacity can be increased by enabling the operation thereof without reducing the high pressure.
  • Document JP 2010 127563 discloses a supercritical steam compression heat pump according to the preamble of claim 1.
  • the low-pressure gas/liquid separator in the supercritical steam compression heat pump employing CO 2 refrigerant is disposed in the intake pipe that connects the outlet side of the internal heat exchanger and the compressor, by bringing the low-pressure refrigerant at the outlet of the internal heat exchanger to a saturated state, it is possible to control superheating of the refrigerant that is taken into the compressor via the low-pressure gas/liquid separator to be a comparatively small level as compared with a unit in which the low-pressure gas/liquid separator is provided between the evaporator and the internal heat exchanger, which makes it possible to suppress an increase in the discharge temperature of the compressor. Therefore, even if the discharge temperature of the compressor is restricted, by increasing the heating capacity by performing the operation where the high-pressure pressure is set comparatively high but so as not to exceed the temperature limit, it is possible to achieve a performance enhancement for the heat pump.
  • intermediate-pressure depressurizing means and an intermediate-pressure gas/liquid separator are provided between the heat sink and the internal heat exchanger, and a gas injection circuit for injecting refrigerant gas separated at the intermediate-pressure gas/liquid separator into the compressor is provided.
  • the intermediate-pressure depressurizing means and the intermediate-pressure gas/liquid separator are provided between the heat sink and the internal heat exchanger, and because the gas injection circuit for injecting the refrigerant gas separated at the intermediate-pressure gas/liquid separator into the compressor is provided, it is possible to enhance the COP (coefficient of performance) and to enhance the heating capacity through the supercooling effect of the refrigerant achieved by means of the internal heat exchanger and the gas injection effect (economizer effect) achieved by means of the gas injection circuit. Therefore, a further performance enhancement can be achieved for the heat pump.
  • a two-stage compressor in which a lower-stage compressor and a higher-stage compressor are provided in a sealed housing is employed as the compressor, and the refrigerant gas from the gas injection circuit is injected into intermediate-pressure refrigerant that is taken into the higher-stage compressor.
  • the two-stage compressor in which the lower-stage compressor and the higher-stage compressor are provided in the sealed housing is employed as the compressor, and because the refrigerant gas from the gas injection circuit is injected into the intermediate-pressure refrigerant gas that is taken into the higher-stage compressor, pressure loss can be kept to a minimum for the intermediate-pressure refrigerant gas that is separated at the intermediate-pressure gas/liquid separator and used for the gas injection via the gas injection circuit, thus making it possible to achieve a high heating capacity and a high COP (coefficient of performance) through the gas injection effect. Therefore, it is possible to achieve a further performance enhancement for the heat pump through the efficiency enhancement achieved by the two-stage compression and the gas injection effect.
  • a refrigerant/water heat exchanger that heats water by performing heat exchange between refrigerant and water is employed as the heat sink in the supercritical steam compression heat pump according to any one of Claims 1 or 2 and hot water can be produced by means of the refrigerant/water heat exchanger.
  • a refrigerant/water heat exchanger that performs heat exchange between the refrigerant and water to heat the water is employed as the heat sink in any one of the supercritical steam compression heat pumps described above, and because hot water can be produced via the refrigerant/water heat exchanger, it is possible to increase the capacity for heating water with the refrigerant at the refrigerant/water heat exchanger due to the fact that operation is possible while maintaining the high-pressure pressure comparatively high on the heat pump side during the hot-water supplying operation, in which hot water is produced by operating the supercritical steam compression heat pump. Therefore, it is possible to enhance the hot-water supply capacity and to achieve a performance enhancement for the hot-water supply unit.
  • a supercritical steam compression heat pump of the present invention by bringing low-pressure refrigerant at an outlet of an internal heat exchanger to a saturated state, it is possible to control superheating of refrigerant that is taken into a compressor via the low-pressure gas/liquid separator to a comparatively small level as compared with a unit in which the low-pressure gas/liquid separator is provided between the evaporator and the internal heat exchanger, which makes it possible to suppress an increase in the discharge temperature of the compressor; therefore, even if the discharge temperature of the compressor is restricted, by increasing the heating capacity by performing the operation where the high-pressure pressure is set comparatively high but so as not to exceed the temperature limit, it is possible to achieve a performance enhancement for the heat pump.
  • a hot-water supply unit of the present invention because it is possible to increase the capacity for heating water with refrigerant at a refrigerant/water heat exchanger due to the fact that the operation is possible while maintaining the high-pressure pressure comparatively high on a heat-pump side during the hot-water supplying operation, in which hot water is produced by operating a supercritical steam compression heat pump, it is possible to enhance the hot-water supply capacity and to achieve a performance enhancement for the hot-water supply unit.
  • Fig. 1 is a diagram showing, in outline, the configuration of a hot-water supply unit employing a supercritical steam compression heat pump according to the embodiment of the present invention
  • Fig. 2 is a Mollier diagram for that heat pump.
  • a hot-water supply unit 1 is provided with a supercritical steam compression heat pump 2 employing CO 2 refrigerant and a water circulation pathway 3 that is connected to a hot-water storage tank unit (not shown).
  • the water circulation pathway 3 is provided with a water supply-side pathway 3A that is connected to a water-side flow path of a heat sink (refrigerant/water heat exchanger) 11 in the supercritical steam compression heat pump 2 and a hot-water extraction-side pathway 3B for extracting hot water produced at the refrigerant/water heat exchanger 11, and the water supply-side pathway 3A is provided with a water pump 4 and a flow-volume control valve 5.
  • the above-described heat pump 2 is provided with a closed-cycle refrigerant circulation circuit 18 where a two-stage compressor (compressor) 9 in which a lower-stage compressor 7 and a higher-stage compressor 8 are built into a sealed housing 6; an oil separator 10 that separates lubricant contained in refrigerant gas; the heat sink (refrigerant/water heat exchanger) 11 that releases the heat of the refrigerant gas; an electronic expansion valve (intermediate-pressure depressurizing means) 12 that depressurizes the refrigerant to intermediate pressure; an intermediate-pressure receiver (intermediate-pressure gas/liquid separator) 13 equipped with a gas/liquid separating function; an internal heat exchanger 14 that performs heat exchange between intermediate-pressure refrigerant and low-pressure refrigerant that is taken into the two-stage compressor 9; main electronic expansion valves (depressurizing means) 15A and 15B that depressurize the intermediate-pressure refrigerant to low-temperature, low-pressure gas/liquid two-phase
  • the heat sink 11 of the heat pump 2 described above serves as a refrigerant/water heat exchanger in which heat exchange is performed between water and the refrigerant gas by making high-temperature, high-pressure refrigerant gas discharged from the two-stage compressor 9 circulate in a refrigerant-side flow path on one side thereof and making water circulate in the water-side flow path on the other side via the water circulation pathway 3. Then, water is heated by the high-temperature, high-pressure refrigerant gas at this refrigerant/water heat exchanger 11, thus producing hot water.
  • the above-described heat pump 2 is provided with an oil-return circuit 19 that returns oil separated at the oil separator 10 to an intake pipe 18A side in the two-stage compressor 9, and this oil-return circuit 19 is provided with a double-pipe heat exchanger 20 and an oil-level adjusting mechanism 21 formed of an electromagnetic valve, a capillary tube, and so forth. Furthermore, the above-described heat pump 2 is provided with a hot-gas bypass circuit 22 for removing frost by introducing the high-temperature, high-pressure hot gaseous refrigerant discharged from the two-stage compressor 9 into the evaporators 17A and 17B in the event of frost forming on surfaces of the evaporators 17A and 17B during operation at a low outside air temperature.
  • the hot-gas bypass circuit 22 is provided with an electromagnetic valve 23 that is opened/closed by detecting the frost formation.
  • the above-described heat pump 2 is provided with a gas injection circuit 24 for injecting the intermediate-pressure refrigerant gas separated at the intermediate-pressure receiver (intermediate-pressure gas/liquid separator) 13 equipped with the gas/liquid separating function into the sealed housing 6 in which the atmosphere is of the intermediate-pressure gas that is taken into the higher-stage compressor 8 in the two-stage compressor 9 via the double-pipe heat exchanger 20 provided in the oil-return circuit 19.
  • This gas injection circuit 24 is provided with an electromagnetic valve 25 so that the gas injection circuit 24 can be opened/closed as needed.
  • the above-described refrigerant circulation circuit 18 has a configuration in which a low-pressure gas/liquid separator (accumulator) 26 is disposed in an intake pipe 18A that connects the outlet side of the internal heat exchanger 14 and the two-stage compressor 9.
  • This low-pressure gas/liquid separator (accumulator) 26 functions so that a liquid component contained in the low-pressure refrigerant gas is separated therein and only the gaseous refrigerant is taken into the two-stage compressor 9.
  • this embodiment affords the following operational advantages.
  • the supercritical steam compression heat pump 2 employing CO 2 refrigerant is activated in the above-described hot-water supply unit 1, the high-temperature, high-pressure refrigerant gas that has undergone the two-stage compression at the two-stage compressor 9 is introduced into the heat sink (refrigerant/water heat exchanger) 11 after the oil contained in the refrigerant is separated at the oil separator 10, and the refrigerant gas undergoes heat exchange therein with water that is circulated in the water-side flow path from the water supply-side pathway 3A of the water circulation pathway 3.
  • This water is heated and increased in temperature by the heat released from the high-temperature, high-pressure refrigerant gas and is subsequently returned to the hot-water storage tank (not shown) via the how-water extraction-side pathway 3B; and the heat exchange between the refrigerant and water is continued at the heat sink (refrigerant/water heat exchanger) 11 continuously until the hot-water storage level in the hot-water storage tank reaches a predetermined level, and the hot-water storing operation is ended when the hot-water storage level reaches the predetermined level.
  • the refrigerant that has been cooled by means of heat exchange with water at the heat sink 11 is depressurized at the intermediate-pressure electronic expansion valve (intermediate-pressure depressurizing means) 12, reaches the intermediate-pressure receiver 13, and undergoes gas/liquid separation therein.
  • the intermediate-pressure gaseous refrigerant separated at the intermediate-pressure receiver 13 passes through the electromagnetic valve 25 and the double-pipe heat exchanger 20, is injected into the intermediate-pressure refrigerant gas in the sealed housing 6 of the two-stage compressor 9 by means of the gas injection circuit 24, and is taken into the higher-stage compressor 8 where it is recompressed.
  • the hot-water supply capacity can be increased by enhancing the heating capacity and the coefficient of performance (COP) of the heat pump 2 by means of the economizer effect due to this gas injection.
  • the liquid refrigerant separated at the intermediate-pressure receiver 13 is supercooled by means of heat exchange with the low-pressure refrigerant gas evaporated at the evaporators 17A and 17B at the internal heat exchanger 14, is subsequently depressurized at the main electronic expansion valves (depressurizing means) 15A and 15B, and flows into the evaporators (air heat exchangers) 17A and 17B in the form of low-temperature, low-pressure, gas/liquid two-phase refrigerant.
  • the gaseous refrigerant from which the liquid component has been separated is taken into the two-stage compressor 9 and is recompressed therein. Thereafter, the refrigerant is utilized to produce hot water by repeating the same operation.
  • this embodiment is configured such that the low-pressure gas/liquid separator 26 that allows the two-stage compressor 9 to take in only the gaseous refrigerant by performing gas/liquid separation of the refrigerant evaporated at the evaporators 17A and 17B is disposed in the intake pipe 18A that connects the two-stage compressor 9 and the low-pressure-refrigerant outlet side of the internal heat exchanger 14 that is provided in the intake pipe 18A on the downstream side of the evaporators 17A and 17B.
  • the refrigerant can be brought to a substantially saturated state at an inlet point A and an outlet point B of the internal heat exchanger 14 and an intake point C of the two-stage compressor 9 in the supercritical cycle in Fig.
  • intermediate-pressure electronic expansion valve (intermediate-pressure depressurizing means) 12 and the intermediate-pressure receiver (intermediate-pressure gas/liquid separator) 13 equipped with the gas/liquid separating function are provided between the heat sink (refrigerant/water heat exchanger) 11 and the internal heat exchanger 14, and because the gas injection circuit 24 for injecting the refrigerant gas separated at the intermediate-pressure receiver 13 into the two-stage compressor 9 is provided, it is possible to enhance the COP (coefficient of performance) and to enhance the heating capacity through a supercooling effect of the refrigerant achieved by means of the internal heat exchanger 14 and the gas injection effect (economizer effect) achieved by means of the gas injection circuit 24. Therefore, it is possible to achieve a further performance enhancement for the supercritical steam compression heat pump 2 and the hot-water supply unit 1.
  • the two-stage compressor 9 in which the lower-stage compressor 7 and the higher-stage compressor 8 are provided in the sealed housing 6 is employed as the compressor applied to the heat pump 2, and the refrigerant gas from the gas injection circuit 24 is injected into the intermediate-pressure refrigerant gas that is taken into the higher-stage compressor 8. Because of this, pressure loss can be kept to a minimum for the intermediate-pressure refrigerant gas that is separated at the intermediate-pressure receiver (intermediate-pressure gas/liquid separator) 13 and used for gas injection via the gas injection circuit 24, thus making it possible to achieve a high heating capacity and a high COP (coefficient of performance) through the gas injection effect. Therefore, it is possible to achieve further performance enhancement for the supercritical steam compression heat pump 2 and the hot-water supply unit 1 through the efficiency enhancement achieved by the two-stage compressor 9 and the gas injection effect.

Claims (3)

  1. Pompe à chaleur à compression de vapeur supercritique dans laquelle un fluide frigorigène à base de CO2 est utilisé en tant que milieu de travail comprenant :
    un compresseur à deux étages (9) qui comprime le fluide frigorigène ;
    un dissipateur de chaleur (11) qui libère la chaleur du fluide frigorigène à haute pression à haute température ;
    des premiers moyens de réduction de pression (12) pour réduire la pression du fluide frigorigène qui est passé à travers le dissipateur de chaleur (11) ;
    un séparateur gaz/liquide de pression intermédiaire (13) pour effectuer la séparation gaz/liquide du fluide frigorigène dont la pression a été réduite par les premiers moyens de réduction de pression (12) ;
    un premier échangeur de chaleur interne (14) qui effectue un échange de chaleur entre le fluide frigorigène qui s'est écoulé hors du dissipateur de chaleur et le fluide frigorigène à basse pression qui est amené dans le compresseur à deux étages ;
    des deuxièmes moyens de réduction de pression (15A, 15B) pour réduire la pression du fluide frigorigène qui est passé à travers le premier échangeur de chaleur interne (14) ;
    un évaporateur (17A, 17B) qui évapore le fluide frigorigène à deux phases gazeuse et liquide dont la pression a été réduite par les deuxièmes moyens de réduction de pression (15A, 15B) ; et
    un séparateur gaz/liquide basse pression (26) qui permet au compresseur à deux étages (9) de recevoir uniquement le fluide frigorigène gazeux en effectuant la séparation gaz/liquide du fluide frigorigène qui a été évaporé au niveau de l'évaporateur (17A, 17B) ;
    dans laquelle un circuit de circulation de fluide frigorigène est formé dans lequel le compresseur à deux étages (9), le dissipateur de chaleur (11), les premiers moyens de réduction de pression (12), le séparateur gaz/liquide de pression intermédiaire (13), le premier échangeur de chaleur interne (14), les deuxièmes moyens de réduction de pression (15A, 15B), l'évaporateur (17A, 17B), et le séparateur gaz/liquide basse pression (26) sont reliés par des tuyaux dans cet ordre,
    dans laquelle le séparateur gaz/liquide basse pression (26) est disposé dans un tuyau d'admission qui relie un côté de sortie du premier échangeur de chaleur interne (14) et le compresseur à deux étages (9),
    la pompe à chaleur à compression de vapeur supercritique étant caractérisée en ce qu'elle comprend en outre :
    un séparateur d'huile (10) pour séparer le lubrifiant contenu dans le fluide frigorigène qui est passé à travers le compresseur à deux étages (9) ;
    un circuit de dérivation de gaz chaud (22) configuré pour retirer le givre en introduisant le fluide frigorigène gazeux refoulé du compresseur à deux étages (9) dans l'évaporateur (17A ; 17B)
    un circuit d'injection de gaz (24) comprenant une première électrovanne (25) pour permettre l'ouverture et la fermeture du circuit d'injection de gaz (24), et configuré pour injecter le fluide frigorigène séparé au niveau du séparateur gaz/liquide de pression intermédiaire (13) dans le compresseur à deux étages (9) ; et
    un deuxième échangeur de chaleur (20) prévu en tant qu'échangeur de chaleur à tuyau double et un mécanisme d'ajustement de niveau d'huile (21) constitué d'au moins une deuxième électrovanne et d'un tube capillaire, le deuxième échangeur de chaleur étant configuré pour effectuer un échange de chaleur avec le circuit d'injection de gaz (24), le deuxième échangeur de chaleur (20) étant prévu dans un circuit de retour d'huile (19) qui renvoie l'huile séparée au niveau du séparateur d'huile (10) vers le compresseur à deux étages (9).
  2. Pompe à chaleur à compression de vapeur supercritique selon la revendication 1, dans laquelle le compresseur à deux étages comprend un compresseur d'étage inférieur (7) et un compresseur d'étage supérieur (8) qui sont prévus dans un logement fermé hermétiquement (6), et le fluide frigorigène gazeux provenant du circuit d'injection de gaz (24) est injecté dans le fluide frigorigène gazeux de pression intermédiaire qui est amené dans le compresseur d'étage supérieur (8).
  3. Unité d'alimentation en eau chaude dans laquelle un échangeur de chaleur fluide frigorigène/eau (11) qui chauffe de l'eau en effectuant un échange de chaleur entre le fluide frigorigène et l'eau est utilisé en tant que dissipateur de chaleur dans la pompe à chaleur à compression de vapeur supercritique selon l'une quelconque des revendications 1 et 2 et de l'eau chaude peut être produite au moyen de l'échangeur de chaleur fluide frigorigène/eau (11).
EP12167898.1A 2011-05-18 2012-05-14 Pompe à chaleur à compression de vapeur supercritique et unité d'alimentation en eau chaude Active EP2525168B1 (fr)

Applications Claiming Priority (1)

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JP2011111747A JP2012241967A (ja) 2011-05-18 2011-05-18 超臨界蒸気圧縮式ヒートポンプおよび給湯機

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EP2525168A1 EP2525168A1 (fr) 2012-11-21
EP2525168B1 true EP2525168B1 (fr) 2019-08-07

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JP6228798B2 (ja) * 2013-09-30 2017-11-08 三菱重工サーマルシステムズ株式会社 ヒートポンプシステム、及び、ヒートポンプ式給湯器
CN109297213B (zh) * 2018-08-24 2019-12-31 珠海格力电器股份有限公司 空调系统及压缩机补气控制方法

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JPH06337171A (ja) * 1993-03-30 1994-12-06 Mitsubishi Heavy Ind Ltd 冷凍装置
JPH07190520A (ja) * 1993-12-27 1995-07-28 Kobe Steel Ltd 冷凍装置
JP2006077998A (ja) * 2004-09-07 2006-03-23 Matsushita Electric Ind Co Ltd 冷凍サイクル装置および制御方法
JP4595717B2 (ja) * 2005-05-24 2010-12-08 株式会社デンソー エジェクタを用いた蒸気圧縮式冷凍サイクル
JP4657087B2 (ja) * 2005-11-14 2011-03-23 三洋電機株式会社 ヒートポンプ式給湯機
JP2008089268A (ja) * 2006-10-04 2008-04-17 Sanden Corp 車両用冷房装置
JP2010127563A (ja) * 2008-11-28 2010-06-10 Sanden Corp 冷凍システム
JP4833330B2 (ja) * 2009-11-27 2011-12-07 三菱電機株式会社 超臨界蒸気圧縮式冷凍サイクルおよびこれを用いる冷暖房空調設備とヒートポンプ給湯機
JP5264874B2 (ja) * 2010-12-24 2013-08-14 三菱電機株式会社 冷凍装置

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EP2525168A1 (fr) 2012-11-21
JP2012241967A (ja) 2012-12-10

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