EP2538159A2 - Kältekreislaufvorrichtung und Hydronik-Heizgerät mit Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung und Hydronik-Heizgerät mit Kältekreislaufvorrichtung Download PDF

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Publication number
EP2538159A2
EP2538159A2 EP12172951A EP12172951A EP2538159A2 EP 2538159 A2 EP2538159 A2 EP 2538159A2 EP 12172951 A EP12172951 A EP 12172951A EP 12172951 A EP12172951 A EP 12172951A EP 2538159 A2 EP2538159 A2 EP 2538159A2
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EP
European Patent Office
Prior art keywords
refrigeration cycle
flow rate
bypass pipe
rate adjusting
cycle apparatus
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Withdrawn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
EP12172951A
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English (en)
French (fr)
Inventor
Michiyoshi Kusaka
Shigeo Aoyama
Shunji Moriwaki
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Panasonic Corp
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Panasonic Corp
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Filing date
Publication date
Application filed by Panasonic Corp filed Critical Panasonic Corp
Publication of EP2538159A2 publication Critical patent/EP2538159A2/de
Withdrawn legal-status Critical Current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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/08—Exceeding a certain temperature value in a refrigeration component or 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • 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
    • F25B2600/2513—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

Definitions

  • the present invention relates to a refrigeration cycle apparatus and a hydronic heater having the 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 the compressor or connected to the portion of the pipe extending from the evaporator to the compressor, 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, one end of the second bypass pipe is
  • a liquid refrigerant which sufficiently secures a supercooled state in a high pressure liquid pipe can be made to directly bypass the compressor suction pipe through the second bypass pipe. It is possible to vary an amount of a refrigerant flowing through the decompressing means in accordance with a variation in the amount of the refrigerant flowing through the second bypass pipe such that a total sum of amounts of refrigerants flowing through the decompressing means and the second bypass pipe is constantly maintained.
  • the control means when a temperature detected by the temperature sensor is higher than a first predetermined value, the control means operates the decompressing means in its closing direction and operates the second flow rate adjusting means in its opening direction.
  • the configuration of the refrigeration cycle apparatus of the second aspect it is possible to reduce an amount of a refrigerant flowing through the decompressing means in accordance with an increased amount of the refrigerant flowing through the second bypass pipe such that the total sum of amounts of the refrigerants flowing through the decompressing means and the second bypass pipe is constantly maintained.
  • the discharge temperature from the compressor abruptly increases, it is possible to swiftly lower the discharge temperature by the bypassing operation of liquid, and reliability can be enhanced.
  • the control means when a temperature detected by the temperature sensor is lower than a second predetermined value, the control means operates the decompressing means in its opening direction and operates the second flow rate adjusting means in its closing direction.
  • the configuration of the refrigeration cycle apparatus of the third aspect it is possible to increase the amount of a refrigerant flowing through the decompressing means in accordance with a reduction amount of the refrigerant flowing through the second bypass pipe such that the total sum of the amounts of the refrigerants flowing through the decompressing means and the second bypass pipe is constantly maintained. As a result, it is possible to restrain a liquid refrigerant from returning to the compressor which configures the refrigerant circuit.
  • the radiator in the refrigeration cycle apparatus is a heat exchanger which heats water by exchanging heat between a refrigerant and water. Therefore, the present invention can be applied not only to a case where the radiator is a heat exchanger between refrigerant and air, but also to a case where the radiator is a heat exchanger between refrigerant and water. In addition, the same effect as that of the first or second aspect can be obtained. Further, 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.
  • 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 (radiator) 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 (radiator) 5 when the indoor unit 2 is used for
  • 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.
  • the other end of the first bypass pipe 9 may be connected to a compression chamber of 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.
  • the other end of the second bypass pipe 13 may be connected to the compression chamber of 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 discharge 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 - of the second flow rate adjusting valve 12 and an opening degree of the expansion valve 6 in accordance with a temperature detected by the discharge temperature sensor 15.
  • the opening degree of the expansion valve 6 is controlled in accordance with a controlled amount of the opening degree of the second flow rate adjusting valve 12.
  • 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 adjusts an opening degree of the first flow rate adjusting valve 11 such that an outlet state of the first bypass pipe 9 becomes a saturated gas refrigerant. According to this adjustment, performance of the supercooling heat exchanger 8 is sufficiently exerted, and the supercooled state of a liquid refrigerant in the refrigerant pipe which connects the supercooling heat exchanger 8 and the expansion valve 6 to each other is sufficiently secured.
  • the second bypass pipe 13 which branches off from between the supercooling heat exchanger 8 and the decompressing means (expansion valve 6), and which is connected to a portion between the compressor 3 and the evaporator 7 through second flow rate adjusting means (second flow rate adjusting valve 12), a discharge temperature of the compressor 3 is detected by a discharge temperature sensor 15 disposed in the discharge pipe 14, and when the discharge temperature becomes equal to or higher than a preset predetermined temperature, the second flow rate adjusting valve 12 disposed at the second bypass pipe 13 is opened by a predetermined opening degree by the control means 16, and the expansion valve 6 is closed by a predetermined opening degree by the control means 16 in accordance with the opening degree of the second flow rate adjusting valve 12.
  • a discharge temperature of the compressor 3 is detected by the discharge temperature sensor 15 disposed in the discharge pipe 14, and when the discharge temperature becomes equal to or lower than a preset predetermined temperature, the second flow rate adjusting valve 12 disposed at the second bypass pipe 13 is closed by a predetermined opening degree by the control means 16, and the expansion valve 6 is opened by a predetermined opening degree by the control means 16 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 discharge temperature sensor 15 (step 101).
  • a refrigerant in the pipe which connects the supercooling heat exchanger 8 and the expansion valve 6 to each other is sufficiently supercooled by the supercooling heat exchanger 8.
  • 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.
  • the second flow rate adjusting valve 12 is opened by the predetermined opening degree, and the expansion valve 6 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 expansion valve 6 and the second flow rate adjusting valve 12, and 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 PLSLO to a predetermined opening degree PLSL1.
  • An opening operation of the expansion valve 6 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 PLSLO to PLSL1. Therefore, the expansion valve 6 is closed by varying the opening degree from PLSSO 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 expansion valve 6 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 expansion valve 6 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 into the closing direction by the predetermined opening degree.
  • the expansion valve 6 is controlled into the opening direction by the predetermined opening degree. That is, the second flow rate adjusting valve 12 is closed by ⁇ G1 from the opening degree PLSL1 to the opening degree PLSL2.
  • the expansion valve 6 is opened by ⁇ Gs from the opening degree PLSS1 to PLSS2 so that the flow rate variation amount of the expansion valve 6 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 expansion valve 6 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 expansion valve 6 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 bypass the liquid refrigerant from the high pressure liquid refrigerant pipe between the radiator 5 and the decompressing means 6 to the suction pipe of the compressor 3 by the second bypass pipe 13. Hence, it is possible to swiftly lower the discharge temperature.
  • the second flow rate adjusting valve 12 is controlled into the closing direction and the expansion valve 6 is controlled into the opening direction. Therefore, it is possible to prevent a liquid refrigerant from returning to the compressor, and to enhance the reliability.
  • a refrigerant state at an inlet of the second bypass pipe 13 is a liquid refrigerant whose supercooled state is sufficiently secured after the refrigerant passes through the supercooling heat exchanger 8. Therefore, even under a low outside air temperature condition of even when a heating load is abruptly increased, it is possible to bypass the liquid refrigerant from the high pressure liquid refrigerant pipe between the condenser 5 and the decompressing means 6 to the suction pipe of the compressor 3. Hence, it is possible to lower the discharge temperature in a wide operation range, and to enhance the reliability of the compressor 3.
  • the expansion valve 6 is controlled into 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 rates of a refrigerants flowing through the expansion valve 6 and the 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 of the refrigeration cycle apparatus of the present application to the minimum.
  • the first bypass pipe 9 branches off from between the supercooling heat exchanger 8 and the expansion valve 6, and the first bypass pipe 9 may branch off from the refrigerant circuit 2 between the radiator 5 and the supercooling heat exchanger 8. It is not absolutely necessary that a connected portion of the first bypass pipe 9 is the suction pipe of the compressor 3. In the case of a compressor having an injection mechanism, the first bypass pipe 9 may be connected to an injection port.
  • 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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
EP12172951A 2011-06-22 2012-06-21 Kältekreislaufvorrichtung und Hydronik-Heizgerät mit Kältekreislaufvorrichtung Withdrawn EP2538159A2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2011137970A JP2013002800A (ja) 2011-06-22 2011-06-22 冷凍サイクル装置及びそれを備えた温水暖房装置

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EP2538159A2 true EP2538159A2 (de) 2012-12-26

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CN104061713A (zh) * 2014-06-03 2014-09-24 东莞市新时代新能源科技有限公司 温度调节系统
ITVI20130257A1 (it) * 2013-10-18 2015-04-19 Carel Ind Spa Metodo di azionamento di una macchina frigorifera dotata di apparato economizzatore
CN106766416A (zh) * 2016-12-26 2017-05-31 广东美的制冷设备有限公司 定频机调节系统及其调节方法和定频空调机

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Cited By (7)

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Publication number Priority date Publication date Assignee Title
ITVI20130257A1 (it) * 2013-10-18 2015-04-19 Carel Ind Spa Metodo di azionamento di una macchina frigorifera dotata di apparato economizzatore
CN104567157A (zh) * 2013-10-18 2015-04-29 卡雷尔工业股份公司 设置有经济器装置的制冷机的驱动方法
CN104567157B (zh) * 2013-10-18 2018-10-09 卡雷尔工业股份公司 设置有经济器装置的制冷机的驱动方法
US10184705B2 (en) 2013-10-18 2019-01-22 Carel Industries S.p.A. Actuation method of a refrigerating machine provided with an economizer apparatus
CN104061713A (zh) * 2014-06-03 2014-09-24 东莞市新时代新能源科技有限公司 温度调节系统
CN106766416A (zh) * 2016-12-26 2017-05-31 广东美的制冷设备有限公司 定频机调节系统及其调节方法和定频空调机
CN106766416B (zh) * 2016-12-26 2024-04-26 广东美的制冷设备有限公司 定频机调节系统及其调节方法和定频空调机

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