WO2016148077A1 - ヒートポンプ - Google Patents
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- WO2016148077A1 WO2016148077A1 PCT/JP2016/057838 JP2016057838W WO2016148077A1 WO 2016148077 A1 WO2016148077 A1 WO 2016148077A1 JP 2016057838 W JP2016057838 W JP 2016057838W WO 2016148077 A1 WO2016148077 A1 WO 2016148077A1
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- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat exchanger
- temperature
- expansion valve
- flow rate
- Prior art date
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Classifications
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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
- 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
- F25B49/027—Condenser control arrangements
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/005—Outdoor unit expansion valves
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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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
- F25B2600/00—Control issues
- F25B2600/17—Control issues by controlling the pressure of the condenser
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2515—Flow valves
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
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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
- 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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
Definitions
- the present invention relates to a heat pump.
- an expansion valve in which the opening degree can be adjusted in the refrigerant flow path between the condenser (first heat exchanger) and the evaporator (second heat exchanger) to adjust the flow rate of the refrigerant.
- a heat pump comprising:
- the heat pump described in Patent Document 1 includes a temperature type automatic expansion valve.
- the temperature type automatic expansion valve adjusts the opening degree based on the temperature (superheat degree) of the refrigerant just before entering the compressor. Thereby, the flow rate of the refrigerant passing through the expansion valve is kept constant.
- Patent Document 1 also discloses that a temperature type automatic expansion valve can be replaced with an electronically controlled expansion valve.
- the present invention maintains an optimum condensing pressure by adjusting the flow coefficient of the condenser outlet side path to a value commensurate with the refrigerant flow rate when the refrigerant flow rate required by the evaporator changes in the heat pump. It is an object to improve the condensing action of.
- a compressor that compresses and discharges the refrigerant;
- a first heat exchanger for condensing refrigerant from the compressor;
- a flow control valve for adjusting the flow rate of the refrigerant condensed by the first heat exchanger;
- a second heat exchanger that cools the temperature adjustment target using the refrigerant decompressed by the expansion valve;
- the opening of the expansion valve is controlled based on the temperature difference between the temperature of the refrigerant flowing into the second heat exchanger and the temperature of the refrigerant flowing out of the second heat exchanger, and the second heat exchanger
- a control device that controls the opening degree of the flow rate control valve based on the refrigerant flow rate supplied to the heat pump.
- the refrigerant in the heat pump, when the refrigerant flow rate required by the evaporator changes, the refrigerant is maintained at the optimum condensing pressure by adjusting the flow coefficient of the condenser outlet side path to a value commensurate with the refrigerant flow rate.
- the condensation action of can be improved.
- the degree of supercooling of the condenser can be adjusted depending on the operating conditions, and the efficiency of the refrigeration cycle is improved.
- FIG. 1 is a circuit diagram showing a configuration of a heat pump according to an embodiment of the present invention.
- a heat pump is a heat pump incorporated in the air conditioner.
- a solid line indicates a refrigerant flow path (refrigerant pipe) through which the refrigerant flows.
- components of the heat pump such as a filter are omitted in order to simplify the description.
- the heat pump 10 includes an outdoor unit 12 that exchanges heat with outside air, and at least one indoor unit 14 that exchanges heat with indoor air.
- the heat pump 10 has two indoor units 14.
- the outdoor unit 12 includes a compressor 16 that compresses and discharges the refrigerant, a heat exchanger (first heat exchanger) 18 that performs heat exchange between the refrigerant and the outside air, and a four-way valve 20.
- the indoor unit 14 includes a heat exchanger 22 that performs heat exchange between the refrigerant and the room air.
- Compressor 16 is driven by gas engine 24.
- gas engine 24 In the case of the present embodiment, two compressors 16 and one gas engine 24 are mounted on the outdoor unit 12. Further, at least one of the compressors 16 is selectively driven by one gas engine 24.
- the drive source for driving the compressor 16 is not limited to the gas engine 24 but may be, for example, a motor or a gasoline engine.
- the high-temperature and high-pressure gaseous refrigerant discharged from the discharge port 16 a of the compressor 16 is directed to the heat exchanger 18 of the outdoor unit 12 or the heat exchanger 22 of the indoor unit 14 by the four-way valve 20.
- the gaseous refrigerant discharged from the compressor 16 is sent to the heat exchanger 22 of the indoor unit 14.
- the gaseous refrigerant is sent to the heat exchanger 18 of the outdoor unit 12.
- An oil separator 30 that separates oil contained in the refrigerant is provided on the discharge path of the compressor 16, that is, on the refrigerant flow path between the discharge port 16 a of the compressor 16 and the four-way valve 20.
- the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 16 and passing through the four-way valve 20 (solid line) is indoor air (temperature adjustment target) in the heat exchanger 22 of at least one indoor unit 14. And heat exchange. That is, heat is transferred from the refrigerant to the room air via the heat exchanger 22. As a result, the refrigerant is brought into a low-temperature and high-pressure liquid state.
- Each indoor unit 14 includes an expansion valve 32 whose opening degree can be adjusted.
- the expansion valve 32 is provided in the indoor unit 14 so as to be positioned between the heat exchanger 22 of the indoor unit 14 and the heat exchanger 18 of the outdoor unit 12 on the refrigerant flow path. When the expansion valve 32 is in the open state, the refrigerant can pass through the heat exchanger 22 of the indoor unit 14. When the indoor unit 14 is stopped, the expansion valve 32 is closed.
- a receiver 34 is provided in the outdoor unit 12. During the heating operation, the receiver 34 is a buffer tank that temporarily stores low-temperature and high-pressure liquid refrigerant after heat exchange with room air by the heat exchanger 22 of the indoor unit 14. The liquid refrigerant flowing out of the heat exchanger 22 of the indoor unit 14 passes through the check valve 36 and flows into the receiver 34.
- the low-temperature and high-pressure liquid refrigerant in the receiver 34 is sent to the heat exchanger 18 of the outdoor unit 12.
- a check valve 38 and an expansion valve 40 are provided in the refrigerant flow path between the receiver 34 and the heat exchanger 18.
- the expansion valve 40 is an expansion valve whose opening degree can be adjusted.
- the expansion valve 40 controls the opening degree so that the refrigerant superheat degree of the suction port 16b of the compressor 16 is equal to or higher than a predetermined temperature.
- the refrigerant superheat degree of the suction port 16b is a temperature difference between the saturated vapor temperature corresponding to the pressure detected by the pressure sensor 68 and, for example, the refrigerant temperature detected by the temperature sensor 66, and the detected refrigerant temperature is saturated. It controls so that it may become more than predetermined temperature (for example, 5 degreeC) rather than steam temperature.
- the low-temperature and high-pressure liquid refrigerant that has flowed out of the receiver 34 is expanded (depressurized) by the expansion valve 40 and is brought into a low-temperature and low-pressure liquid state (mist state).
- the low-temperature and low-pressure liquid refrigerant that has passed through the expansion valve 40 exchanges heat with the outside air in the heat exchanger 18 of the outdoor unit 12. That is, heat is transferred from the outside air to the refrigerant through the heat exchanger 18. As a result, the refrigerant is brought into a low-temperature and low-pressure gas state.
- the accumulator 42 is provided in the outdoor unit 12. During the heating operation, the accumulator 42 temporarily stores the low-temperature and low-pressure gaseous refrigerant after heat exchange with the outside air in the heat exchanger 18 of the outdoor unit 12.
- the accumulator 42 is provided in the suction path of the compressor 16 (the refrigerant flow path between the suction port 16b of the compressor 16 and the four-way valve 20).
- the low-temperature and low-pressure gaseous refrigerant in the accumulator 42 is sucked into the compressor 16 and compressed. As a result, the refrigerant is brought into a high-temperature and high-pressure gas state, and is sent again toward the heat exchanger 22 of the indoor unit 14 during the heating operation.
- the on-off valve 62 is opened in a normal air conditioning operation.
- the on-off valve 62 is closed during a period when the liquid refrigerant is present, such as when it is stopped, at the beginning of activation, or when the air conditioning load is suddenly reduced, and the liquid refrigerant is stored in the accumulator 42.
- the heat pump 10 has an evaporation assisting heat exchanger 64 in parallel with the heat exchanger 18 in the refrigerant flow during the heating operation.
- the evaporation assisting heat exchanger 64 is connected to the receiver 34.
- the receiver 34 Pour liquid refrigerant.
- an expansion valve 70 whose opening degree can be adjusted is provided between the receiver 34 and the evaporation assisting heat exchanger 64.
- the control device (not shown) of the heat pump 10 opens the expansion valve 70 when the refrigerant superheat degree of the suction port 16b is equal to or lower than a predetermined temperature.
- the expansion valve 70 When the expansion valve 70 is opened, at least a part of the liquid refrigerant flows from the receiver 34 toward the evaporation assisting heat exchanger 64 and flows through the expansion valve 70 into a low-temperature / low-pressure mist.
- the mist-like refrigerant that has passed through the expansion valve 70 is heated by, for example, the high-temperature exhaust gas or coolant of the gas engine 24 (that is, waste heat of the gas engine 24) in the evaporation assisting heat exchanger 64.
- the mist-like refrigerant that has passed through the expansion valve 70 and has flowed into the evaporation assisting heat exchanger 64 is brought into a high-temperature and low-pressure gas state.
- the high-temperature gaseous refrigerant heated by the evaporation assisting heat exchanger 64 has a higher superheat degree than the refrigerant that has passed through the heat exchanger 18 and joins the refrigerant flow path between the four-way valve 20 and the accumulator 42.
- the high-temperature and high-pressure gaseous refrigerant discharged from the discharge port 16a of the compressor 16 moves to the heat exchanger 18 of the outdoor unit 12 via the four-way valve 20 (two-dot chain line).
- the refrigerant is brought into a low-temperature and high-pressure liquid state.
- the refrigerant that has flowed out of the heat exchanger 18 passes through the on-off valve 50 and the check valve 52 and flows into the receiver 34.
- the on-off valve 50 is closed during heating operation.
- the refrigerant that has flowed out of the heat exchanger 18 passes only through the on-off valve 50 and the check valve 52, or in addition thereto, the expansion valve 40 and the reverse valve.
- the stop valve 54 also passes through and flows into the receiver 34.
- the refrigerant flowing into the receiver 34 passes through the check valve 56 and passes through the expansion valve 32 of the indoor unit 14.
- the expansion valve 32 controls the opening degree as will be described later so that the degree of refrigerant superheat at the outlet of the heat exchanger 22 is equal to or greater than a predetermined value.
- the refrigerant is decompressed to a cold / low pressure liquid state (mist state).
- the refrigerant that has passed through the expansion valve 32 passes through the heat exchanger 22 of the indoor unit 14 where it exchanges heat with the indoor air. Thereby, the refrigerant takes heat from the room air (cools the room air). As a result, the refrigerant is brought into a low-temperature and low-pressure gas state.
- the refrigerant flowing out of the heat exchanger 22 passes through the four-way valve 20 and the accumulator 42 and returns to the compressor 16.
- the heat pump 10 has a cooling heat exchanger 58 for cooling the refrigerant from the receiver 34 toward the check valve 56.
- the cooling heat exchanger 58 is configured so that heat exchange is performed between the liquid refrigerant and the mist refrigerant from the receiver 34 toward the check valve 56, that is, the liquid refrigerant is cooled with the mist refrigerant. Yes.
- This mist-like refrigerant is obtained by forming a part of the liquid refrigerant from the cooling heat exchanger 58 toward the check valve 56 into a mist (depressurized) by the expansion valve 60.
- the expansion valve 60 is a valve whose opening degree can be adjusted in order to selectively cool the liquid refrigerant by the cooling heat exchanger 58.
- the control device (not shown) of the heat pump 10 controls the expansion valve 60 so that the expansion valve 60 is at least partially opened, it passes through the cooling heat exchanger 58 and before the check valve 56. A part of the liquid refrigerant passes through the expansion valve 60 and is atomized (depressurized). The refrigerant atomized by the expansion valve 60 flows into the cooling heat exchanger 58, takes out heat from the liquid refrigerant before flowing out of the receiver 34 and passing through the check valve 56, and is thereby gasified. . As a result, a low-temperature liquid refrigerant flows into the heat exchanger 22 of the indoor unit 14 as compared with when the expansion valve 60 is closed.
- the gaseous refrigerant that has flowed out of the receiver 34 and deprived of heat from the liquid refrigerant before passing through the check valve 56 is directly returned to the compressor 16 from the cooling heat exchanger 58.
- each of the plurality of indoor units 14 includes a temperature sensor 82 that detects the temperature of the refrigerant.
- the temperature sensor 82 detects the temperature of the refrigerant downstream of the indoor unit 14 with respect to the heat exchanger 22 during the cooling operation, that is, detects the temperature of the refrigerant flowing out of the heat exchanger 22.
- the control device of the heat pump 10 expands the indoor unit 14 so that the refrigerant temperature detected by the temperature sensor 82 is equal to or higher than a predetermined temperature (for example, 5 ° C.) with respect to the saturated vapor temperature corresponding to the pressure detected by the pressure sensor 68.
- a predetermined temperature for example, 5 ° C.
- the opening degree of the valve 32 is controlled.
- control device of the heat pump 10 will explain the opening degree control of the expansion valve 40 based on the flow rate of the refrigerant supplied to the heat exchanger 22 of the indoor unit 14.
- the expansion valve 40 is selected so that the flow coefficient matches the refrigerant flow rate of the rated cooling operation.
- the rated cooling operation is a situation in which, for example, all the indoor units 14 connected at an outside air temperature of 35 ° C. are required to perform the cooling operation.
- the control device of the heat pump 10 reduces the refrigerant flow rate by making the number of operation and the number of rotations of the compressors 16 smaller than the rated operation accordingly.
- the control device of the heat pump 10 decreases the opening degree of the expansion valve 40 according to the number of operating compressors 16 and the number of rotations. For example, assuming that the opening degree of the expansion valve 40 during rated operation is 100%, the optimum condensing pressure cannot be maintained as the refrigerant circulation rate decreases, and the performance deteriorates. Is reduced to the optimum expansion valve opening degree with respect to the refrigerant flow rate corresponding to.
- the opening degree of the expansion valve 40 is controlled based on the flow rate of the refrigerant supplied to the heat exchanger 22 of the indoor unit 14 (that is, based on the number of operating and the number of rotations of the compressor 16).
- the expansion valve 40 to function as a flow rate control valve, the optimum condensing pressure can be maintained and the refrigerant condensing action can be improved.
- the degree of supercooling of the condenser can be adjusted according to the operating conditions, and the cooling efficiency of the heat pump 10 can be improved.
- the expansion valve 40 functions as a pressure reducing valve that depressurizes the refrigerant during the heating operation, and functions as a flow rate adjustment valve that adjusts the refrigerant flow rate during the cooling operation.
- the embodiment of the present invention is not limited to this.
- a refrigerant flow path that bypasses the expansion valve 40 may be provided, and a flow rate adjustment valve and an on-off valve may be provided in the bypass flow path.
- the heat pump 10 is an air conditioner that controls the temperature of room air as a temperature adjustment target, but the embodiment of the present invention is not limited thereto.
- the heat pump according to the embodiment of the present invention may be, for example, a chiller that adjusts the temperature of water using a refrigerant.
- a water / refrigerant heat exchanger is provided instead of the heat exchanger 22 of the indoor unit 14. That is, in a broad sense, the heat pump according to the present invention is condensed by the compressor that compresses and discharges the refrigerant, the first heat exchanger that condenses the refrigerant from the compressor, and the first heat exchanger.
- a flow rate adjusting valve for adjusting the flow rate of the refrigerant an expansion valve capable of adjusting the opening for reducing the pressure of the refrigerant that has passed through the flow rate adjusting valve, and second heat for cooling the temperature adjustment target using the refrigerant reduced in pressure by the expansion valve
- the opening degree of the expansion valve is controlled based on the temperature difference between the exchanger and the temperature of the refrigerant flowing into the second heat exchanger and the temperature of the refrigerant flowing out of the second heat exchanger.
- the present invention is applicable to a heat pump including an expansion valve capable of adjusting an opening between two heat exchangers.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Description
冷媒を圧縮して吐出する圧縮機と、
圧縮機からの冷媒を凝縮する第1の熱交換器と、
第1の熱交換器によって凝縮された冷媒の流量を調節する流量調節弁と、
流量調節弁を通過した冷媒を減圧する開度調節可能な膨張弁と、
膨張弁によって減圧された冷媒を用いて温度調節対象を冷却する第2の熱交換器と、
第2の熱交換器に流入する冷媒の温度と第2の熱交換器から流出する冷媒の温度との間の温度差に基づいて膨張弁の開度を制御するとともに、第2の熱交換器に供給する冷媒流量に基づいて流量調節弁の開度を制御する制御装置と、を有するヒートポンプが提供される。
16 圧縮機
18 第1の熱交換器
22 第2の熱交換器
32 膨張弁
40 流量調節弁(膨張弁)
Claims (1)
- 冷媒を圧縮して吐出する圧縮機と、
圧縮機からの冷媒を凝縮する第1の熱交換器と、
第1の熱交換器によって凝縮された冷媒の流量を調節する流量調節弁と、
流量調節弁を通過した冷媒を減圧する開度調節可能な膨張弁と、
膨張弁によって減圧された冷媒を用いて温度調節対象を冷却する第2の熱交換器と、
第2の熱交換器に流入する冷媒の温度と第2の熱交換器から流出する冷媒の温度との間の温度差に基づいて膨張弁の開度を制御するとともに、第2の熱交換器に供給する冷媒流量に基づいて流量調節弁の開度を制御する制御装置と、を有するヒートポンプ。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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US15/559,011 US10816251B2 (en) | 2015-03-17 | 2016-03-11 | Heat pump |
EP16764907.8A EP3273182B1 (en) | 2015-03-17 | 2016-03-11 | Heat pump |
CN201680007055.2A CN108027178B (zh) | 2015-03-17 | 2016-03-11 | 热泵 |
KR1020177025595A KR102017405B1 (ko) | 2015-03-17 | 2016-03-11 | 히트 펌프 |
Applications Claiming Priority (2)
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JP2015053176A JP6339036B2 (ja) | 2015-03-17 | 2015-03-17 | ヒートポンプ |
JP2015-053176 | 2015-03-17 |
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WO2016148077A1 true WO2016148077A1 (ja) | 2016-09-22 |
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PCT/JP2016/057838 WO2016148077A1 (ja) | 2015-03-17 | 2016-03-11 | ヒートポンプ |
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US (1) | US10816251B2 (ja) |
EP (1) | EP3273182B1 (ja) |
JP (1) | JP6339036B2 (ja) |
KR (1) | KR102017405B1 (ja) |
CN (1) | CN108027178B (ja) |
WO (1) | WO2016148077A1 (ja) |
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EP3361192B1 (en) * | 2017-02-10 | 2019-09-04 | Daikin Europe N.V. | Heat source unit and air conditioner having the heat source unit |
US10782034B2 (en) * | 2017-12-13 | 2020-09-22 | RK Mechanical, Inc. | System for conditioning an airflow using a portable closed loop cooling system |
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JPS6334459A (ja) * | 1986-07-29 | 1988-02-15 | 株式会社東芝 | 空気調和機 |
JPH0264361A (ja) * | 1988-08-30 | 1990-03-05 | Ulvac Corp | 冷凍・冷却用膨張弁の制御方法 |
JPH04366365A (ja) * | 1991-06-12 | 1992-12-18 | Daikin Ind Ltd | 冷凍装置の運転制御装置 |
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- 2016-03-11 CN CN201680007055.2A patent/CN108027178B/zh active Active
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Also Published As
Publication number | Publication date |
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US10816251B2 (en) | 2020-10-27 |
KR20170116139A (ko) | 2017-10-18 |
CN108027178A (zh) | 2018-05-11 |
JP2016173200A (ja) | 2016-09-29 |
JP6339036B2 (ja) | 2018-06-06 |
CN108027178B (zh) | 2020-12-18 |
KR102017405B1 (ko) | 2019-09-02 |
EP3273182A1 (en) | 2018-01-24 |
EP3273182A4 (en) | 2018-11-07 |
US20180080697A1 (en) | 2018-03-22 |
EP3273182B1 (en) | 2022-05-04 |
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