EP2525168A1 - 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
EP2525168A1
EP2525168A1 EP12167898A EP12167898A EP2525168A1 EP 2525168 A1 EP2525168 A1 EP 2525168A1 EP 12167898 A EP12167898 A EP 12167898A EP 12167898 A EP12167898 A EP 12167898A EP 2525168 A1 EP2525168 A1 EP 2525168A1
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EP
European Patent Office
Prior art keywords
refrigerant
pressure
gas
compressor
heat exchanger
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.)
Granted
Application number
EP12167898A
Other languages
German (de)
English (en)
Other versions
EP2525168B1 (fr
Inventor
Taku Hokamura
Takuya Okada
Ken Watanabe
Shigeru Yoshida
Minemasa Omura
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Ltd
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Publication of EP2525168A1 publication Critical patent/EP2525168A1/fr
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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
    • 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.
  • a supercritical steam compression heat pump according to the present invention is a supercritical steam compression heat pump in which CO 2 refrigerant is employed as a working medium includes a compressor that compresses the refrigerant, a heat sink that releases the heat of high-temperature, high-pressure refrigerant, an internal heat exchanger that performs heat exchange between the refrigerant that has flowed out from the heat sink and low-pressure refrigerant that is taken into the compressor, depressurizing means for depressurizing the refrigerant that has passed through the internal heat exchanger, an evaporator that evaporates gas/liquid two-phase refrigerant that has been depressurized by the depressurizing means, and a low-pressure gas/liquid separator that allows the compressor to take in only gaseous refrigerant by performing gas/liquid separation of the refrigerant that has been evaporated at the
  • 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 to 3 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.
  • a heat sink refrigerant/water heat exchanger
  • 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.
  • the present invention is not limited to the invention according to the above-described embodiment, and appropriate modifications are possible within a range that does not depart from the spirit thereof.
  • the above-described embodiment has been described in terms of an example in which the two-stage compressor 9 is employed as the compressor, it is needless to mention that the present invention is similarly applicable to a unit in which a single-stage compressor is employed, and, furthermore, even in the case in which a single-stage compressor is employed, it is, of course, possible to provide the gas injection circuit 24 therein.

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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)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
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)

Application Number Priority Date Filing Date Title
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 true EP2525168A1 (fr) 2012-11-21
EP2525168B1 EP2525168B1 (fr) 2019-08-07

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EP (1) EP2525168B1 (fr)
JP (1) JP2012241967A (fr)
ES (1) ES2750032T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109297213A (zh) * 2018-08-24 2019-02-01 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

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1632733A2 (fr) * 2004-09-07 2006-03-08 Matsushita Electric Industrial Co., Ltd. Appareil à cycle de réfrigération et procédé de régulation
JP2007003166A (ja) * 2005-05-24 2007-01-11 Denso Corp エジェクタを用いた蒸気圧縮式冷凍サイクル
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

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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
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

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1632733A2 (fr) * 2004-09-07 2006-03-08 Matsushita Electric Industrial Co., Ltd. Appareil à cycle de réfrigération et procédé de régulation
JP2007003166A (ja) * 2005-05-24 2007-01-11 Denso Corp エジェクタを用いた蒸気圧縮式冷凍サイクル
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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109297213A (zh) * 2018-08-24 2019-02-01 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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EP2525168B1 (fr) 2019-08-07
ES2750032T3 (es) 2020-03-24
JP2012241967A (ja) 2012-12-10

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