EP2551612A2 - Pompe à chaleur à cycle supercritique - Google Patents

Pompe à chaleur à cycle supercritique Download PDF

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Publication number
EP2551612A2
EP2551612A2 EP12177749A EP12177749A EP2551612A2 EP 2551612 A2 EP2551612 A2 EP 2551612A2 EP 12177749 A EP12177749 A EP 12177749A EP 12177749 A EP12177749 A EP 12177749A EP 2551612 A2 EP2551612 A2 EP 2551612A2
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EP
European Patent Office
Prior art keywords
pressure
refrigerant
oil
viscosity
multistage 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.)
Granted
Application number
EP12177749A
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German (de)
English (en)
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EP2551612A3 (fr
EP2551612B1 (fr
Inventor
Youhei Hotta
Yoshiyuki Kimata
Hajime Sato
Toshiyuki Goto
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Publication of EP2551612A3 publication Critical patent/EP2551612A3/fr
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Publication of EP2551612B1 publication Critical patent/EP2551612B1/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
    • 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
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/16—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to a supercritical-cycle (CO 2 -cycle) heat pump employing CO 2 refrigerant.
  • Patent Literatures 5 and 6 there are concerns that, in compressors provided with the injection circuits, the oil will be separated in gas-liquid separators, causing the oil return from the injection circuits to also deteriorate in addition to that from the low-pressure side refrigerant circuits, which affects the lubrication performance of the compressors, and so on.
  • the polyol-ester-based oil has high compatibility with the refrigerant, which makes the occurrence of problems described above unlikely; however, there are concerns that the refrigerant will increase the dilution ratio, decrease the oil viscosity, and so on. Although these concerns are reduced in compressors employing multistage compressors with sealed housings, having intermediate pressure in the interior thereof, because of the temperature and pressure conditions in the intermediate-pressure housings, as compared with compressors with high-pressure housings or low-pressure housings, it is necessary to somehow restrict the effects in question because they are considered to affect the lubrication performance.
  • the above-described supercritical-cycle heat pump further includes an intermediate pressure sensor for detecting the pressure of the intermediate-pressure refrigerant to be injected from the injection circuit to the sealed housing of the multistage compressor; an intermediate temperature sensor for detecting the temperature of the intermediate-pressure refrigerant to be injected from the injection circuit to the sealed housing of the multistage compressor; an intake pressure sensor for detecting the pressure of intake refrigerant for the multistage compressor; an intake temperature sensor for detecting the temperature of the intake refrigerant for the multistage compressor, wherein the controller controls refrigerant superheating temperatures of the intermediate-pressure refrigerant and the intake refrigerant to respective target superheating temperatures with the first electronic expansion valve and the second electronic expansion valve.
  • the controller is configured to control refrigerant superheating temperatures of the intermediate-pressure refrigerant and the intake refrigerant to respective target superheating temperatures with the first electronic expansion valve and the second electronic expansion valve, by controlling the existing first electronic expansion valve and second electronic expansion valve, provided upstream and downstream of the gas-liquid separator connected to the injection circuit, the viscosity of the POE oil can be kept above the certain viscosity zone by merely changing the software for the controller without additionally providing new devices, which makes it possible to prevent an increase in the dilution ratio of the oil and a decrease in the oil viscosity. Therefore, it is possible to achieve improved lubrication performance in a simple manner by employing the POE oil, which has high compatibility, while avoiding an increase in complexity of the hardware configuration.
  • the capacity to return oil to a multistage compressor from a system side can be enhanced by employing polyol-ester-based oil having high compatibility with CO 2 refrigerant or mixed oil (POE oil) thereof, and also because an increase in the dilution ratio of oil and a decrease in the oil viscosity, which are affected by the pressure and temperature of the refrigerant, can be prevented by keeping the viscosity of the oil above the certain viscosity zone by controlling the pressure of intermediate-pressure refrigerant within a preset usage limit range, it is possible to eliminate a decrease in the lubrication performance caused by a lack of lubricant in the multistage compressor, an increase in the dilution ratio of the oil, a decrease in the viscosity thereof, and so forth, which makes it possible to ensure sufficient reliability.
  • POE oil mixed oil
  • FIG. 1 shows a diagram of a refrigerating cycle of a supercritical-cycle heat pump employing CO 2 refrigerant according to an embodiment of the present invention.
  • a supercritical-cycle heat pump (CO 2 cycle heat pump) 1 is provided with a multistage compressor 2, and a closed-cycle refrigerant circuit (refrigerating cycle) 10 is formed by sequentially connecting the multistage compressor 2, an oil separator 3, a radiator 4, a first electronic expansion valve 5, a gas-liquid separator 6, a second electronic expansion valve 7, and an evaporator 8 in this order via refrigerant pipes 9.
  • the above-described refrigerant circuit (refrigerating cycle) 10 is provided with an injection circuit 11 for injecting intermediate-pressure refrigerant gas separated by the gas-liquid separator 6 into a sealed housing 14, having intermediate pressure in the interior thereof, in the multistage compressor 2, and is also provided with an oil-return circuit 13 that returns lubricant separated from the refrigerant gas at the oil separator 3 to an intake refrigerant pipe 9A in the multistage compressor 2 after performing heat exchange thereof with the intermediate-pressure refrigerant gas via a heat exchanger 12 provided in the injection circuit 11.
  • the multistage compressor 2 has an electric motor (not shown) built into a single sealed housing 14 and is also provided with two compression mechanisms, that is, a lower-stage compression mechanism 15 and a higher-stage compression mechanism 16, that are driven by the electric motor.
  • the multistage compressor 2 is configured such that the lower-stage compression mechanism 15 takes in low-pressure refrigerant gas evaporated by the evaporator 8, compresses it to intermediate pressure, and discharges it into the sealed housing 14; and the higher-stage compression mechanism 16 takes in the intermediate-pressure refrigerant gas, performs tow-stage compression to high pressure, and discharges the high-pressure refrigerant gas to the oil separator 3 connected to the multistage compressor 2.
  • a single type or mixed types of compression mechanisms among the rotary type, scroll type, and various other types may be employed as the lower-stage compression mechanism 15 and the higher-stage compression mechanism 16.
  • polyol-ester-based oil (POE oil) which has high compatibility with CO 2 refrigerant, or mixed oil thereof (hereinafter, simply referred to as POE oil) is employed as the lubricant 17.
  • the oil separator 3 separates the lubricant 17 contained in the CO 2 refrigerant discharged from the multistage compressor 2 and returns it to the intake refrigerant pipe 9A in the multistage compressor 2 via the oil-return circuit 13.
  • the radiator 4 performs heat exchange between high-temperature, high-pressure refrigerant gas and a cooling medium, thus causing the refrigerant gas to release heat to reach a supercritical state or a condensed liquefied state, and thereby causes the refrigerant to flow out toward the first electronic expansion valve 5.
  • the first electronic expansion valve 5 depressurizes the high-pressure refrigerant to intermediate pressure and supplies it to the gas-liquid separator 6.
  • the gas-liquid separator 6 performs gas-liquid separation of gas-liquid two-phase CO 2 refrigerant which has been depressurized to the intermediate pressure, injects gaseous refrigerant into the sealed housing 14 of the multistage compressor 2 by making it pass through the injection circuit 11 from the gas-liquid separator 6, and also causes liquid refrigerant to flow out toward the second electronic expansion valve 7.
  • the second electronic expansion valve 7 depressurizes the intermediate-pressure liquid refrigerant, supplies it to the evaporator 8 as low-pressure, low-temperature gas-liquid two-phase refrigerant, measures the pressure and temperature of the low-pressure refrigerant gas to be taken into the multistage compressor 2, and controls the refrigerant superheating temperature at an outlet of the evaporator 8 to a target value.
  • a discharge pipe from the multistage compressor 2 is provided with a discharge pressure sensor 18 and a temperature sensor 19 that detect the pressure and temperature of the discharged refrigerant gas;
  • the intake refrigerant pipe 9A in the multistage compressor 2 is provided with an intake pressure sensor 20 and a temperature sensor 21 that detect the pressure and temperature of the intake refrigerant gas;
  • the injection circuit 11 is provided with an intermediate pressure sensor 22 and a temperature sensor 23 that detect the pressure and temperature of the intermediate-pressure refrigerant.
  • the sealed housing 14 in the multistage compressor 2 is provided, at the bottom portion thereof, with an oil temperature sensor 24 that detects the oil temperature of the lubricant 17.
  • Detected values from the discharge pressure sensor 18 and the temperature sensor 19 are used for high-pressure protection, discharge-temperature control, discharge-superheating temperature control, or the like, and the intake pressure sensor 20 and the temperature sensor 21 are employed for low-pressure protection and intake-superheating temperature control by the second electronic expansion valve 7. Furthermore, the detected values from the intermediate pressure sensor 22, the temperature sensor 23, and the oil temperature sensor 24 are used for the following control for keeping the viscosity of the POE oil, employed as the lubricant 17, in the certain viscosity zone.
  • the viscosity of the POE oil 17 is controlled in the following way via a controller 25.
  • the viscosity of the POE oil 17 depends on its solubility in the CO 2 refrigerant, which is determined by the pressure and temperature of the CO 2 refrigerant.
  • the solubility of the POE oil 17 in the CO 2 refrigerant has the characteristic that the solubility increases with an increase in pressure if the temperature is the same, and, in addition, the solubility increases with a decrease in temperature if the pressure is the same, as is clear from a pressure-solubility characteristic diagram shown in Fig. 3 , with temperature as a parameter; for example, when the pressure is 5.4 MPa, the solubility is 20 wt% if the temperature is 60 °C.
  • the viscosity of the POE oil 17 when dissolved in the CO 2 refrigerant has the characteristic that the viscosity decreases with an increase in the solubility if temperature of the POE oil 17 is the same and, in addition, the viscosity decreases with an increase in temperature of the POE oil 17 if the solubility is the same, as is clear from a temperature-viscosity characteristic diagram shown in Fig. 4 , with solubility as a parameter; for example, when the solubility is 20 wt%, as described above, the viscosity is 5.0 mPa•s if temperature is 40 °C.
  • the viscosity of the POE oil 17 filled in the sealed housing 14, having intermediate pressure in the interior thereof, in the multistage compressor 2 can be ascertained by measuring the pressure and temperature of the intermediate-pressure refrigerant, and this fact indicates that the viscosity of the POE oil 17 can he controlled by controlling the pressure and temperature of the intermediate-pressure refrigerant.
  • the pressure and temperature of the intermediate-pressure refrigerant are controlled by the controller 25 via the first electronic expansion valve 5 so that the viscosity of the POE oil 17 is kept above the certain viscosity zone so as to prevent an increase in the dilution ratio when the refrigerant dissolves in the POE oil 17, which has a high compatibility with the CO 2 refrigerant, as well as a resultant decrease in the viscosity of the oil.
  • the pressure and temperature of the intermediate-pressure refrigerant are measured by the intermediate pressure sensor 22 and the temperature sensor 23, the solubility of the POE oil in the CO 2 refrigerant under that pressure and temperature is determined by using Fig.
  • the controller 25 detects the pressure and temperature of the intermediate-pressure refrigerant to be injected into the sealed housing 14 from the injection circuit 11 and those of the intake refrigerant for the multistage compressor 2 with the intermediate pressure sensor 22, the temperature sensor 23, the intake pressure sensor 20, and the temperature sensor 21 respectively; controls refrigerant superheating temperatures of the intermediate-pressure refrigerant and the intake refrigerant to respective target superheating temperatures (for example, intermediate-pressure saturation temperature + ⁇ deg.
  • target superheating temperatures for example, intermediate-pressure saturation temperature + ⁇ deg.
  • the multistage compressor 2 of the supercritical-cycle heat pump 1 is a two-stage compressor, as pressure ranges in which it can be operated, a lower-stage usage limit range and a higher-stage usage limit range are preset on the basis of the relationship between the low pressure and intermediate pressure on the lower-stage side and the relationship between intermediate pressure and high pressure on the higher-stage side in consideration of the above-described points, as shown in Fig. 2 .
  • this embodiment affords the following operational advantages.
  • the CO 2 refrigerant compressed to the intermediate pressure at the lower-stage compression mechanism 15 of the multistage compressor 2 is discharged into the sealed housing 14 and is taken into the higher-stage compression mechanism 16 together with the intermediate-pressure refrigerant gas injected into the sealed housing 14 from the injection circuit 11.
  • This refrigerant undergoes two-stage compression to high pressure at the higher-stage compression mechanism 16, is discharged toward the refrigerant circuit (refrigerating cycle) 10, and is introduced into the radiator 4 after the lubricant 17 in the refrigerant is separated at the oil separator 3.
  • the refrigerant introduced into the radiator 4 reaches a supercritical state or a condensed liquefied state by releasing heat to the cooling medium, is depressurized to intermediate pressure by the first electronic expansion valve 5, thereby reaching the gas-liquid separator 6 in the gas-liquid two-phase state, and is separated therein into the intermediate-pressure liquid refrigerant and the intermediate-pressure gaseous refrigerant.
  • the separated intermediate-pressure gaseous refrigerant is injected into the sealed housing 14 of the multistage compressor 2 via the injection circuit 11, as described above.
  • the intermediate-pressure liquid refrigerant is depressurized again by the second electronic expansion valve 7, thereby being supplied to the evaporator 8 in the form of low-temperature, low-pressure gas-liquid two-phase refrigerant.
  • the controller 25 determines the viscosity of the POE oil 17 from the solubility and the temperature of the POE oil 17 on the basis of the solubility of the POE oil 17 in the CO 2 refrigerant under the pressure and the temperature of the intermediate-pressure refrigerant, controls the pressure and the temperature of the intermediate-pressure refrigerant via the first electronic expansion valve 5 so that the pressure thereof is controlled within the preset usage limit range in order to keep the viscosity of the POE oil 17 above the certain viscosity zone, and, by doing so, the viscosity of the POE oil 17 is kept above the certain viscosity zone by controlling the pressure of the intermediate-pressure refrigerant within the preset usage limit range, which thereby prevents an increase in the dilution ratio of the POE oil 17 and a decrease in the viscosity
  • controller 25 is configured so as to detect the pressure and the temperature of the intermediate-pressure refrigerant gas injected into the sealed housing 14 of the multistage compressor 2 via the injection circuit 11 and those of refrigerant gas that is taken into the multistage compressor 2; to control respective refrigerant superheating temperatures to the target superheating temperatures (for example, intermediate-pressure saturation temperature + ⁇ deg. and intake-pressure saturation temperature + ⁇ deg.) with the first electronic expansion valve 5 and the second electronic expansion valve 7; and to also control the pressure and the temperature of the intermediate-pressure refrigerant via the first electronic expansion valve 5 so that the pressure thereof is controlled within the preset usage limit range in order to keep the viscosity of the POE oil 17 above the certain viscosity zone.
  • target superheating temperatures for example, intermediate-pressure saturation temperature + ⁇ deg. and intake-pressure saturation temperature + ⁇ deg.
  • the viscosity of the POE oil 17 can be kept above the certain viscosity zone by merely changing software for the controller 25 without additionally providing new devices, which makes it possible to prevent an increase in the dilution ratio of the POE oil 17 and a decrease in the viscosity thereof. Therefore, it is possible to achieve improvements in the lubrication performance in a simple manner by employing the POE oil 17, which has high compatibility, while avoiding an increase in complexity of the hardware configuration.
  • the multistage compressor 2 is a two-stage compressor, and, as shown in Fig. 2 , the usage limit ranges are changed in accordance with the viscosity of the POE oil 17 in the sealed housing 14 in the lower-stage usage limit range and the higher-stage usage limit range, which are preset on the basis of the relationship between the low pressure and intermediate pressure on the lower-stage side and the relationship between the intermediate pressure and high pressure on the higher-stage side, thus enabling the operation in portions of limited pressure ranges even when the viscosity of the POE oil 17 does not reach the rated value (first threshold), so long as it reaches the second rated value (second threshold), which is lower than the rated value.
  • the supercritical-cycle heat pump 1 is applicable to a wide range of usages without limitation to air conditioners, hot-water supply units, and so forth; and it is, of course, applicable to a unit in which a four-way switching valve is provided between the discharge side and the intake side of the multistage compressor 2, which makes it possible to switch the refrigerant circuit (refrigerating cycle) 10 between a heating cycle and a cooling cycle.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP12177749.4A 2011-07-29 2012-07-25 Pompe à chaleur à cycle supercritique Active EP2551612B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2011166353A JP5798830B2 (ja) 2011-07-29 2011-07-29 超臨界サイクルヒートポンプ

Publications (3)

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EP2551612A2 true EP2551612A2 (fr) 2013-01-30
EP2551612A3 EP2551612A3 (fr) 2014-03-26
EP2551612B1 EP2551612B1 (fr) 2015-07-22

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CN103363749A (zh) * 2013-08-05 2013-10-23 上海理工大学 饱和等熵压缩排气温差控制制冷剂流量的方法
DE102014100093A1 (de) * 2014-01-07 2015-07-09 Kriwan Industrie-Elektronik Gmbh Kälteanlage und Verfahren zur Regelung der Überhitzung eines Kältemittels einer Kälteanlage
EP2952833A3 (fr) * 2014-05-16 2016-04-06 Lennox Industries Inc. Gestion de fonctionnement de compresseur dans des climatiseurs
EP3026370A1 (fr) * 2014-11-05 2016-06-01 Mitsubishi Heavy Industries, Ltd. Appareil à cycle de réfrigération à deux étages et dispositif et procédé de commande de l'appareil
CN107036331A (zh) * 2015-07-15 2017-08-11 艾默生环境优化技术(苏州)有限公司 空调系统及控制空调系统的压缩机的油池的加热的方法
CN107461955A (zh) * 2017-08-30 2017-12-12 广东美芝制冷设备有限公司 制冷系统
US10309704B2 (en) 2013-11-25 2019-06-04 The Coca-Cola Company Compressor with an oil separator between compressing stages
CN111306827A (zh) * 2019-12-30 2020-06-19 松下冷机系统（大连）有限公司 一种宽环温型co2空气源热泵系统
CN112303957A (zh) * 2020-10-15 2021-02-02 珠海格力电器股份有限公司 压缩机回油控制方法
CN114963528A (zh) * 2021-06-29 2022-08-30 青岛海尔新能源电器有限公司 冷媒检测方法、装置、设备及存储介质

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CN106225287B (zh) * 2016-08-09 2019-02-12 宁波阿诺丹机械有限公司 一种二氧化碳高效制冷系统
CN106766442A (zh) * 2016-11-16 2017-05-31 海信（山东）空调有限公司 一种可靠过热度的获取方法、控制方法和装置以及空调
US11073313B2 (en) 2018-01-11 2021-07-27 Carrier Corporation Method of managing compressor start for transport refrigeration system
CN109489293B (zh) * 2018-10-11 2019-11-08 珠海格力电器股份有限公司 空调系统
CN113719963B (zh) * 2020-05-25 2022-12-27 青岛海尔空调电子有限公司 多联机系统的回油控制方法
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CN103363749A (zh) * 2013-08-05 2013-10-23 上海理工大学 饱和等熵压缩排气温差控制制冷剂流量的方法
US10309704B2 (en) 2013-11-25 2019-06-04 The Coca-Cola Company Compressor with an oil separator between compressing stages
DE102014100093A1 (de) * 2014-01-07 2015-07-09 Kriwan Industrie-Elektronik Gmbh Kälteanlage und Verfahren zur Regelung der Überhitzung eines Kältemittels einer Kälteanlage
EP2952833A3 (fr) * 2014-05-16 2016-04-06 Lennox Industries Inc. Gestion de fonctionnement de compresseur dans des climatiseurs
US9482454B2 (en) 2014-05-16 2016-11-01 Lennox Industries Inc. Compressor operation management in air conditioners
EP3026370A1 (fr) * 2014-11-05 2016-06-01 Mitsubishi Heavy Industries, Ltd. Appareil à cycle de réfrigération à deux étages et dispositif et procédé de commande de l'appareil
CN107036331A (zh) * 2015-07-15 2017-08-11 艾默生环境优化技术(苏州)有限公司 空调系统及控制空调系统的压缩机的油池的加热的方法
CN107461955A (zh) * 2017-08-30 2017-12-12 广东美芝制冷设备有限公司 制冷系统
CN111306827A (zh) * 2019-12-30 2020-06-19 松下冷机系统（大连）有限公司 一种宽环温型co2空气源热泵系统
CN111306827B (zh) * 2019-12-30 2023-08-29 冰山冷热科技股份有限公司 一种宽环温型co2空气源热泵系统
CN112303957A (zh) * 2020-10-15 2021-02-02 珠海格力电器股份有限公司 压缩机回油控制方法
CN114963528A (zh) * 2021-06-29 2022-08-30 青岛海尔新能源电器有限公司 冷媒检测方法、装置、设备及存储介质
CN114963528B (zh) * 2021-06-29 2023-08-18 青岛海尔新能源电器有限公司 冷媒检测方法、装置、设备及存储介质

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