EP2482013A2 - Appareil à cycle de réfrigération - Google Patents

Appareil à cycle de réfrigération Download PDF

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Publication number
EP2482013A2
EP2482013A2 EP12152877A EP12152877A EP2482013A2 EP 2482013 A2 EP2482013 A2 EP 2482013A2 EP 12152877 A EP12152877 A EP 12152877A EP 12152877 A EP12152877 A EP 12152877A EP 2482013 A2 EP2482013 A2 EP 2482013A2
Authority
EP
European Patent Office
Prior art keywords
flow rate
rate adjusting
refrigeration cycle
bypass pipe
adjusting means
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.)
Withdrawn
Application number
EP12152877A
Other languages
German (de)
English (en)
Other versions
EP2482013A3 (fr
Inventor
Michiyoshi Kusaka
Shunji Moriwaki
Shigeo Aoyama
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.)
Panasonic Corp
Original Assignee
Panasonic Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Panasonic Corp filed Critical Panasonic Corp
Publication of EP2482013A2 publication Critical patent/EP2482013A2/fr
Publication of EP2482013A3 publication Critical patent/EP2482013A3/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for the 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • 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
    • F25B2700/21—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
    • 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
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid

Definitions

  • the present invention relates to a refrigeration cycle apparatus.
  • a discharge temperature of a compressor extremely rises in the case of a general refrigeration cycle apparatus because an evaporating pressure is reduced and a high condensation temperature is required.
  • the apparatus receives an influence of uneven distribution of refrigerant in the refrigeration cycle or an amount of operation of an opening degree of an expansion valve, and a temperature of a refrigerant (discharge temperature) discharged from the compressor abruptly rises until the refrigeration cycle is stabilized in some cases.
  • a refrigerant pipe extending from a condenser to an expansion valve and a suction refrigerant pipe of a compressor are connected to each other by means of a bypass pipe through the expansion valve and a supercooling heat exchanger, and the compressor sucks a liquid refrigerant.
  • Fig. 6 shows a conventional refrigeration cycle apparatus described in patent document 1.
  • the condenser 103 is connected to a first input terminal of the bridge circuit 104.
  • One of first output terminals of the bridge circuit 104 is connected to a second input terminal of the bridge circuit 104 through a supercooling heat exchanger 106 and decompressing means 107, and a second output terminal of the bridge circuit 104 is connected to the evaporator 105.
  • the other first output terminal of the bridge circuit 104 is connected to a suction refrigerant pipe of the compressor 101 by means of a bypass pipe 108 through the supercooling heat exchanger 106.
  • a flow rate adjusting valve 109 for the supercooling heat exchanger is connected to the bypass pipe 108 at a location upstream of the supercooling heat exchanger 106.
  • a discharge pipe of the compressor 101 includes a discharge temperature sensor 110. An opening degree of the flow rate adjusting valve 109 is adjusted based on a discharge temperature detected by the discharge temperature sensor 110, and an amount of a refrigerant flowing to the bypass pipe 108 is controlled.
  • Patent Document 1 Japanese Patent Publication No. 3440910
  • the present invention has been accomplished to solve the problem, and it is an object of the invention to provide a refrigeration cycle apparatus capable of swiftly suppressing the abrupt discharge temperature rise while maintaining a stable operation of the refrigeration cycle.
  • the present invention provides a refrigeration cycle apparatus in which a compressor, a condenser, decompressing means and an evaporator are annularly connected to one another through pipes in order, thereby forming a refrigeration cycle, a supercooling heat exchanger is disposed between the condenser and the decompressing means, one end of a first bypass pipe is connected to a portion of the pipe extending from the supercooling heat exchanger to the decompressing means, first flow rate adjusting means is connected to the first bypass pipe, heat of a refrigerant which flows out from the first flow rate adjusting means is exchanged with heat of a refrigerant which flows through the supercooling heat exchanger, the other end of the first bypass pipe is connected to a portion of the pipe extending from the evaporator to the compressor, and the refrigeration cycle apparatus also includes a temperature sensor which detects a discharge temperature of the compressor, characterized in that the refrigeration cycle apparatus further comprises a second bypass pipe and control means, one end of the second bypass pipe is
  • the refrigeration cycle apparatus of the invention is characterized in that when a temperature detected by the temperature sensor become higher than a first predetermined value, the control means operates the first flow rate adjusting means in its closing direction and operates the second flow rate adjusting means in its opening direction.
  • a liquid refrigerant whose heat is not exchanged with a refrigerant flowing through the supercooling heat exchanger is made to flow into the compressor suction pipe by the second bypass pipe, and it is possible to reduce a flow rate of a refrigerant which flows through the first bypass pipe in accordance with an increased amount of a refrigerant which flows through the second bypass pipe.
  • a liquid refrigerant can sufficiently flow into the compressor suction pipe.
  • the refrigeration cycle apparatus of the invention is characterized in that the control means controls such that a flow rate variation amount Gs generated by the closing operation of the first flow rate adjusting means becomes equal to a flow rate variation amount Gl generated by the opening operation of the second flow rate adjusting means. According to this, it is possible to constantly maintain a total sum of an amount of a refrigerant which flows through the first bypass pipe and the second bypass pipe, and it is possible to suppress a variation in a refrigeration cycle generated by bypassing.
  • the refrigeration cycle apparatus of the invention is characterized in that when a temperature detected by the temperature sensor becomes lower than a first predetermined value, the control means operates the first flow rate adjusting means in its opening direction and operates the second flow rate adjusting means in its closing direction.
  • a liquid refrigerant whose heat is not exchanged with a refrigerant flowing through the supercooling heat exchanger is made to flow into the compressor suction pipe by the second bypass pipe, and it is possible to increase a flow rate of a refrigerant which flows through the first bypass pipe in accordance with a reduced amount of a refrigerant which flows through the second bypass pipe. As a result, it is possible to prevent a liquid refrigerant from returning to the compressor.
  • the refrigeration cycle apparatus of the invention is characterized in that the control means controls such that a flow rate variation amount ⁇ Gs generated by the opening operation of the first flow rate adjusting means becomes equal to a flow rate variation amount ⁇ Gl generated by the closing operation of the second flow rate adjusting means. According to this, it is possible to constantly maintain a total sum of an amount of a refrigerant which flows through the first bypass pipe and the second bypass pipe, and to suppress a variation in a circulation amount of a refrigerant which flows through the refrigeration cycle.
  • the refrigeration cycle apparatus of the invention is characterized in that the condenser is a heat exchanger which heats water by exchanging heat between the refrigerant and the water, and hot water heated by the condenser is used for heating a room.
  • the refrigeration cycle apparatus of the invention can also be applied to a hydronic heater not only when the condenser is a heat exchanger which exchanges heat between a refrigerant and air but also when the condenser is a heat exchanger which exchanges heat between a refrigerant and water.
  • Fig. 1 is a circuit diagram of a refrigeration cycle apparatus according to a first embodiment of the present invention.
  • Fig. 2 is a control flowchart of a flow rate adjusting valve.
  • Fig. 3 is a control conceptual diagram when control of the flow rate adjusting valve is started.
  • Fig. 4 is a control conceptual diagram of a variation in a discharge temperature and control of an opening degree of the flow rate adjusting valve.
  • Fig. 5 is a control conceptual diagram during control of the flow rate adjusting valve.
  • a refrigerant it is possible to use a zeotropic refrigerant mixture such as R407C, a pseudo-azeotropic refrigerant mixture such as R410A or a single refrigerant.
  • the refrigeration cycle apparatus of the embodiment includes an outdoor unit 1 and an indoor unit 2.
  • the refrigeration cycle is formed by annularly connecting the following members to one another through pipes: that is, a compressor 3 which compresses a refrigerant, a four-way valve 4 which switches between flowing directions of the refrigerant, a condenser 5 (when the indoor unit 2 is used for a heating operation) which condenses and liquefies a high-temperature and high-pressure refrigerant, and expansion valve 6 (decompressing means) which decompresses and expands a high-pressure liquid refrigerant, and an evaporator 7 (when the indoor unit 2 is used for the heating operation) which evaporates and vaporizes a low-temperature two-phase refrigerant.
  • a compressor 3 which compresses a refrigerant
  • a four-way valve 4 which switches between flowing directions of the refrigerant
  • a condenser 5 when the indoor unit 2 is used for a heating operation
  • the indoor unit 2 includes the condenser 5, and the outdoor unit 1 includes the compressor 3, the four-way valve 4, the expansion valve 6 and the evaporator 7.
  • the four-way valve 4 By switching the four-way valve 4, it is possible to switch a normal heating operation to a cooling operation, or from the normal heating operation to a defrosting operation.
  • a supercooling heat exchanger 8 is disposed between the condenser 5 and the expansion valve 6.
  • the outdoor unit 1 includes the supercooling heat exchanger 8.
  • One end of a first bypass pipe 9 is connected to a pipe extending from the supercooling heat exchanger 8 to the expansion valve 6.
  • First flow rate adjusting means 11 is connected to the first bypass pipe 9.
  • the first flow rate adjusting valve 11 adjusts a bypassing amount of a refrigerant flowing to the first bypass pipe 9.
  • the other end of the first bypass pipe 9 is connected to a pipe extending from the evaporator 7 to the compressor 3.
  • a refrigerant which flows out from the first flow rate adjusting valve 11 exchanges heat with a refrigerant which flows through the supercooling heat exchanger 8 and then, the refrigerant is supplied to a suction pipe 10 of the compressor 3.
  • the supercooling heat exchanger 8 heat is exchanged between a high-pressure refrigerant which flows out from the condenser 5 and a low-pressure bypassing refrigerant which flows out from the first flow rate adjusting valve 11.
  • a second bypass pipe 13 is connected to a pipe extending from the supercooling heat exchanger 8 to the expansion valve 6.
  • a second flow rate adjusting valve 12 is connected to the second bypass pipe 13.
  • the second flow rate adjusting valve 12 adjusts a bypassing amount of a refrigerant which flows to the second bypass pipe 13.
  • the other end of the second bypass pipe 13 is connected to a pipe extending from the evaporator 7 to the compressor 3.
  • a refrigerant which flows out from the second bypass pipe 13 is supplied to the suction pipe 10 of the compressor 3 without exchanging heat with a refrigerant which flows through the supercooling heat exchanger 8.
  • a temperature sensor 15 which detects a discharge temperature of the compressor 3 is connected to the discharge pipe 14 of the compressor 3.
  • Control means 16 controls an opening degree of the first flow rate adjusting valve 11 and an opening degree of the second flow rate adjusting valve 12 in accordance with a temperature detected by the temperature sensor 15.
  • a high-pressure gas refrigerant discharged from the compressor 3 flows from the discharge pipe 14 and reaches the four-way valve 4.
  • the high-pressure gas refrigerant flows into the condenser 5, radiates heat, and is condensed and liquefied.
  • the condensed and liquefied high-pressure liquid refrigerant is supercooled by the supercooling heat exchanger 8, the refrigerant is decompressed and expanded by the expansion valve 6 and becomes a low-temperature and low-pressure two-phase refrigerant.
  • the low-temperature low-pressure two-phase refrigerant flows into the evaporator 7, and evaporates and vaporizes. Thereafter, the refrigerant again passes through the four-way valve 4 and is sucked from the suction pipe 10 into the compressor 3.
  • the control means 16 When a temperature detected by the temperature sensor 15 becomes higher than a first predetermined value, the control means 16 operates the first flow rate adjusting valve 11 in its closing direction and operates the second flow rate adjusting valve 12 in its opening direction. More specifically, when the temperature detected by the temperature sensor 15 becomes higher than the first predetermined value, the second flow rate adjusting valve 12 is opened by the predetermined opening degree, and the first flow rate adjusting valve 11 is closed by the predetermined opening degree in accordance with the opening degree of the second flow rate adjusting valve 12. When the temperature detected by the temperature sensor 15 becomes lower than the first predetermined value, the control means 16 operates the first flow rate adjusting valve 11 in its opening direction and operates the second flow rate adjusting valve 12 in its closing direction. More specifically, the second flow rate adjusting valve 12 is closed by the predetermined opening degree, and the first flow rate adjusting valve 11 is opened by the predetermined opening direction in accordance with the opening degree of the second flow rate adjusting valve 12.
  • a bypassing refrigerant is made to flow to the first bypass pipe 9 at the time of a normal operation, thereby carrying out the operation using the supercooling heat exchanger 8.
  • a discharge temperature Td is detected by the temperature sensor 15 (step 101).
  • a discharge temperature Td and a previously set first set temperature TdH are compared with each other (step 102).
  • the first set temperature TdH is set in accordance with a specification of the compressor 3. It is preferable that the first set temperature TdH is set to a normal discharge temperature, or a temperature which is lower than an upper limit discharge temperature by a predetermined temperature, i.e., a temperature at which reliability of the compressor 3 can not be deteriorated when the compressor 3 is used.
  • a predetermined temperature i.e., a temperature at which reliability of the compressor 3 can not be deteriorated when the compressor 3 is used.
  • step 104 If the detected discharge temperature Td is equal to or higher than the first set temperature TdH, the second flow rate adjusting valve 12 is opened by the predetermined opening degree, and the first flow rate adjusting valve 11 is closed by the predetermined opening degree in accordance with the opening degree of the second flow rate adjusting valve 12 (step 104).
  • the operation in step 104 is shown in Fig. 3 .
  • a lateral axis shows valve opening degrees of the first flow rate adjusting valve 11 and the second flow rate adjusting valve 12
  • a vertical axis shows refrigerant flow rates of these valves 11 and 12.
  • the second flow rate adjusting valve 12 is opened from a closed state PLSL0 to a predetermined opening degree PLSL1.
  • An opening operation of the first flow rate adjusting valve 11 is carried out simultaneously with the opening operation of the second flow rate adjusting valve 12.
  • a flow rate variation amount Gl is generated when the opening degree of the second flow rate adjusting valve 12 is varied from PLSL0 to PLSL1. Therefore, the first flow rate adjusting valve 11 is closed by varying the opening degree from PLSS0 to PLSS1 so that a flow rate variation amount Gs (absolute value) which is equal to the flow rate variation amount Gl is generated.
  • step 105 a variation state of the discharge temperature generated by operation of step 103 is determined (step 105).
  • step 105 in a state where the discharge temperature Td is equal to or higher than a set temperature TdH, if the discharge temperature Td is rising, the second flow rate adjusting valve 12 is opened by the predetermined opening degree, and the first flow rate adjusting valve 11 is closed by the predetermined opening degree (step 106). If the discharge temperature Td is lowering in step 105 on the contrary, the second flow rate adjusting valve 12 is closed by the predetermined opening degree and the first flow rate adjusting valve 11 is opened by the predetermined opening degree (step 107).
  • Fig. 4 shows a variation in the discharge temperature. A case where the discharge temperature Td is lowering will be explained. As shown in Fig.
  • a discharge temperature Td before a predetermined time discharge temperature and a variation amount dTd of the discharge temperature Td after the predetermined time dT are compared with each other, and if the variation amount is lower than 0°C, it is determined that the discharge temperature Td is lowering.
  • step 107 An operation in step 107 is shown in Fig. 5 .
  • the second flow rate adjusting valve 12 is controlled in the closing direction by the predetermined opening degree.
  • the first flow rate adjusting valve 11 is controlled in the opening direction by the predetermined opening degree. That is, the second flow rate adjusting valve 12 is closed by ⁇ Gl from the opening degree PLSL1 to the opening degree PLSL2.
  • the first flow rate adjusting valve 11 is opened by ⁇ Gs from the opening degree PLSS1 to PLSS2 so that the flow rate variation amount of the first flow rate adjusting valve 11 becomes equal to a reverse direction of the flow rate variation amount of the second flow rate adjusting valve 12.
  • step 108 the discharge temperature Td is detected, and this is compared with a second set temperature TdL (step 108). If the discharge temperature Td is equal to or higher than the second set temperature TdL in step 108, operations from step 105 to step 107 are repeated. If the discharge temperature Td is lower than the second set temperature TdL, a variation state of the discharge temperature Td is determined (step 109). This determining operation of the variation state in step 109 is the same as that in step 105. If the discharge temperature Td is in the lowering state based on the determination result in step 109, the second flow rate adjusting valve 12 is closed by the predetermined opening degree. The first flow rate adjusting valve 11 is opened by the predetermined opening degree (step 110).
  • step 110 operation in step 103 is checked, and if the operation is stopped, the control is completed. If the discharge temperature Td is in the rising state on the contrary, the second flow rate adjusting valve 12 is opened by the predetermined opening degree. The first flow rate adjusting valve 11 is closed by the predetermined opening degree (step 111). After step 111, the operation in step 103 is checked, and if the operation is stopped, the control is completed.
  • step 101 By repeating the operations from step 101 to step 111, even if the discharge temperature abruptly rises when a load is varied, it is possible to more swiftly lower the discharge temperature by the second bypass pipe 13. Even when the refrigerant flow rate of the second bypass pipe 13 becomes excessively large, the second flow rate adjusting valve 12 is controlled in the closing direction and the first flow rate adjusting valve 11 is controlled in the opening direction. Therefore, it is possible to prevent a liquid refrigerant from returning to the compressor, and to enhance the reliability.
  • the first flow rate adjusting valve 11 of the first bypass pipe 9 is controlled in the reverse direction in accordance with a refrigerant flow rate of the second flow rate adjusting valve 12 of the second bypass pipe 13, and it is possible to reduce a variation amount of a total sum of the flow rate of a refrigerant flowing through the first bypass pipe 9 and second bypass pipe 13. Therefore, it is possible to suppress a variation in high and low pressures at the time of the bypassing operation, to stably maintain the refrigeration cycle, and to suppress the deterioration in efficiency to the minimum.
  • the condenser 5 function as a heat exchanger for heating water by heat exchange between a refrigerant and water, and to use hot water heated by the condenser 5 for heating a room. Therefore, the present invention can also be applied to a hydronic heater not only when the condenser 5 is a heat exchanger which exchanges heat between a refrigerant and air but also when the condenser 5 is a heat exchanger which exchanges heat between a refrigerant and water.
  • the refrigeration cycle apparatus of the invention even when a discharge temperature abruptly rises when a load is varied, it is possible to suppress a discharge temperature rise while stably maintaining the refrigeration cycle. Therefore, the refrigeration cycle apparatus can also be applied to a general air conditioner, a heat pump hydronic heater, a professional-use freezing machine, and a heat pump hot water supply apparatus.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP12152877A 2011-01-27 2012-01-27 Appareil à cycle de réfrigération Withdrawn EP2482013A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2011014959A JP5278452B2 (ja) 2011-01-27 2011-01-27 冷凍サイクル装置及びそれを用いた温水暖房装置

Publications (2)

Publication Number Publication Date
EP2482013A2 true EP2482013A2 (fr) 2012-08-01
EP2482013A3 EP2482013A3 (fr) 2013-01-02

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EP12152877A Withdrawn EP2482013A3 (fr) 2011-01-27 2012-01-27 Appareil à cycle de réfrigération

Country Status (3)

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EP (1) EP2482013A3 (fr)
JP (1) JP5278452B2 (fr)
CN (1) CN102620458A (fr)

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JP2015001326A (ja) * 2013-06-14 2015-01-05 パナソニックＩｐマネジメント株式会社 温水生成装置
CN104633979B (zh) * 2013-11-13 2017-03-29 珠海格力电器股份有限公司 空调器及其控制方法
CN104729161B (zh) * 2013-12-19 2018-08-24 珠海格力电器股份有限公司 空调器及其控制方法
CN107843037B (zh) * 2017-10-31 2021-02-23 广东美的暖通设备有限公司 多联机系统及其过冷控制装置和方法
CN108375255B (zh) * 2017-12-29 2019-12-06 青岛海尔空调器有限总公司 空调器系统
CN110173913A (zh) * 2019-04-24 2019-08-27 同济大学 一种超大过冷度的蒸气压缩高温热泵机组
CN110173796B (zh) * 2019-05-29 2020-12-22 南京天加环境科技有限公司 一种防止多联式空调室内机制冷剂回液的控制方法
JP7436789B2 (ja) * 2019-11-01 2024-02-22 ダイキン工業株式会社 プレート型冷媒配管、及び、冷凍装置
CN115493320B (zh) * 2022-08-31 2024-05-10 青岛海尔空调电子有限公司 空气源热泵系统及其控制方法

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JP3440910B2 (ja) 2000-02-17 2003-08-25 ダイキン工業株式会社 冷凍装置

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EP2482013A3 (fr) 2013-01-02
CN102620458A (zh) 2012-08-01
JP5278452B2 (ja) 2013-09-04
JP2012154575A (ja) 2012-08-16

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