EP4390269A1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP4390269A1
EP4390269A1 EP23217474.8A EP23217474A EP4390269A1 EP 4390269 A1 EP4390269 A1 EP 4390269A1 EP 23217474 A EP23217474 A EP 23217474A EP 4390269 A1 EP4390269 A1 EP 4390269A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
flows
side heat
refrigeration cycle
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.)
Pending
Application number
EP23217474.8A
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English (en)
French (fr)
Inventor
Kazuki KOISHIHARA
Yuki YAMAOKA
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 Intellectual Property Management Co Ltd
Original Assignee
Panasonic Intellectual Property Management Co Ltd
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 Intellectual Property Management Co Ltd filed Critical Panasonic Intellectual Property Management Co Ltd
Publication of EP4390269A1 publication Critical patent/EP4390269A1/de
Pending 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/004—Outdoor unit with water as a heat sink or heat source
    • 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
    • F25B2600/2509—Economiser valves

Definitions

  • the present invention relates to a refrigeration cycle device using propane as refrigerant.
  • Patent document 1 proposes an air conditioner including: a refrigeration cycle formed by connecting a compressor, an indoor heat exchanger, an upstream side expansion valve, an intermediate pressure receiver, a downstream side expansion valve and an outdoor heat exchanger to one another such that refrigerant flow these elements in this order at the time of a heating operation; an injection circuit for injecting refrigerant of the intermediate pressure receiver into the compressor; an injection expansion valve provided in the injection circuit to adjust an amount of refrigerant which is injected; and control means for controlling the upstream side expansion valve, the downstream side expansion valve and the injection expansion valve.
  • the control means includes a liquid accumulating determining section which determines whether liquid refrigerant is accumulated in the intermediate pressure receiver. If it is determined that the liquid refrigerant is accumulated in the intermediate pressure receiver, the injection expansion valve is opened to carry out the injection, thereby preventing variation in oil dilution degree in the compressor caused by unevenness of blowout temperature or reduction of discharge temperature.
  • Such a conventional technique is effective for enhancing the heating ability specially when outdoor air temperature is low or when refrigerant such as R290 having lower density as compared with R410A and R32 is used, and such an injection circuit is mounted in a hydronic heater.
  • Patent Document 1 Japanese Patent Application Laidopen No.2019-148394
  • a refrigeration cycle device of the present invention described in claim 1 including a main refrigerant circuit 10 formed by sequentially connecting, to one another through a refrigerant pipe 18, a compressor 11, a four-way valve 12, a use-side heat exchanger 13, an economizer 14, an internal heat exchanger 15, a first expansion device 16 and a heat source-side heat exchanger 17; and a bypass refrigerant circuit 20 in which refrigerant branches off from the refrigerant pipe 18 between the use-side heat exchanger 13 and the economizer 14, the branched refrigerant is decompressed by a second expansion device 21 and then, the branched refrigerant exchanges heat with the refrigerant which flows through the main refrigerant circuit 10 in the economizer 14, and the branched refrigerant joins up with the refrigerant which is in the middle of compression stroke of the compressor 11, wherein propane is used as the refrigerant, and when the use-side heat exchanger 13 is used as a condenser, in the internal
  • the high pressure refrigerant which flows through the internal heat exchanger 15 is the high pressure refrigerant after it flows through the economizer 14.
  • the high pressure refrigerant flowing through the internal heat exchanger 15 and the low pressure refrigerant flowing through the internal heat exchanger 15 are opposite flows.
  • the low pressure refrigerant flowing through the main refrigerant circuit 10 at a location upstream of the economizer 14 and the low pressure refrigerant before it is sucked into the compressor 11 at a location downstream of the four-way valve 12 exchange heat with each other.
  • a high pressure-side flow path 15a through which the high pressure refrigerant flows is made narrower than a low pressure-side flow path 15b through which the low pressure refrigerant flows.
  • a suction superheat degree of refrigerant which is sucked into a compressor can be increased, and even if propane is injected as refrigerant, it is possible to reliably secure a discharge superheat degree. Therefore, it is possible to stably control an expansion valve. Since discharge temperature from the compressor rises, a temperature difference between refrigerant and heat medium to be heated is increased in the condenser.
  • propane is used as the refrigerant
  • the use-side heat exchanger is used as a condenser, in the internal heat exchanger, high pressure refrigerant which flows through the main refrigerant circuit and low pressure refrigerant which flows out from the heat source-side heat exchanger and which flows through the main refrigerant circuit exchange heat with each other.
  • low pressure gas refrigerant having a large suction superheat degree in the compression chamber and refrigerant which is injected in the two-phase state are mixed with each other, and a rate occupied by the liquid refrigerant in the compression chamber is reduced. Therefore, reduction in viscosity of lubricant oil is suppressed, and reliability of the device is enhanced.
  • the high pressure refrigerant which flows through the internal heat exchanger is the high pressure refrigerant after it flows through the economizer.
  • an enthalpy difference in the heat source-side heat exchanger can further be increased, the endothermic energy amount is increased and therefore, energy saving performance of the device is enhanced.
  • the high pressure refrigerant flowing through the internal heat exchanger and the low pressure refrigerant flowing through the internal heat exchanger are opposite flows.
  • heat exchanging efficiency of the internal heat exchanger is enhanced because the high pressure refrigerant and the low pressure refrigerant flow oppositely, and discharge temperature further rises. Therefore, a radiation amount in the use-side heat exchanger further increases, and energy saving performance of the device is enhanced.
  • a fourth embodiment of the invention in the refrigeration cycle device of the first embodiment, when the use-side heat exchanger is used as an evaporator, in the internal heat exchanger, the low pressure refrigerant flowing through the main refrigerant circuit at a location upstream of the economizer and the low pressure refrigerant before it is sucked into the compressor at a location downstream of the four-way valve exchange heat with each other.
  • the use-side heat exchanger when the use-side heat exchanger is used as the evaporator by switching the four-way valve, in the internal heat exchanger, low pressure refrigerants which are radiated heat by the heat source-side heat exchanger, and which are decompressed by the first expansion device exchange heat with each other. Therefore, even if the internal heat exchanger is provided, temperature of refrigerant which flows into the heat source-side heat exchanger is not lowered at the time of cooling operation, and cooling performance is not deteriorated.
  • a high pressure-side flow path through which the high pressure refrigerant flows is made narrower than a low pressure-side flow path through which the low pressure refrigerant flows.
  • the high pressure-side flow path into which high density liquid refrigerant flows is made narrower than the low pressure-side flow path into which low density gas refrigerant flows. Therefore, flow speed of refrigerant becomes fast, and the heat transfer coefficient is enhanced.
  • the low pressure-side flow path into which the low density gas refrigerant flows is made wider than the high pressure-side flow path into which the high density liquid refrigerant flows. Therefore, pressure loss of refrigerant which flows through the low pressure-side flow path is reduced and thus, the energy saving performance of the device is enhanced.
  • Fig. 1 is a block diagram of a refrigeration cycle device of the embodiment, and shows a flow of refrigerant in a heating operation.
  • the refrigeration cycle device is composed of a main refrigerant circuit 10 and a bypass refrigerant circuit 20.
  • the refrigeration cycle device of the embodiment uses propane as refrigerant.
  • the main refrigerant circuit 10 is formed by sequentially connecting, to one another through a refrigerant pipe 18, a compressor 11 which compresses refrigerant, a four-way valve 12, a use-side heat exchanger 13 which functions as a radiator at the time of heating operation, an economizer 14 which functions as an intermediate heat exchanger, an internal heat exchanger 15, a first expansion device 16 which is a main expansion valve, and a heat source-side heat exchanger 17 which functions as an evaporator at the time of heating operation.
  • the four-way valve 12 is provided between the compressor 11 and the use-side heat exchanger 13.
  • the four-way valve 12 can change a direction of refrigerant which flows through the main refrigerant circuit 10. That is, by switching the four-way valve 12, at the time of cooling operation, refrigerant which is discharged from the compressor 11 flows through the heat source-side heat exchanger 17, the first expansion device 16, the internal heat exchanger 15, the economizer 14 and the use-side heat exchanger 13 in this order, and the refrigerant is sucked into the compressor 11.
  • the heat source-side heat exchanger 17 functions as a radiator
  • the use-side heat exchanger 13 functions as an evaporator.
  • the bypass refrigerant circuit 20 branches off from the refrigerant pipe 18 located between the use-side heat exchanger 13 and the economizer 14 (refrigerant branch point A), and the bypass refrigerant circuit 20 is connected to the compression chamber in the middle of compression stroke of the compressor 11.
  • the bypass refrigerant circuit 20 is provided with a second expansion device 21.
  • a portion of high pressure refrigerant after it passes through the use-side heat exchanger 13 is decompressed by the second expansion device 21 and becomes intermediate pressure refrigerant and then, it exchanges heat in the economizer 14 with high pressure refrigerant which flows through the main refrigerant circuit 10, and itis injected into the compressor 11.
  • the refrigerant which is injected into the compressor 11 joins up with refrigerant which is in the middle of compression stroke of the compressor 11.
  • the use-side heat medium circuit 30 is formed by connecting the use-side heat exchanger 13 the circulation pump 31 and the load termination 32 to one another through a heat medium pipe 33. Water or antifreeze liquid can be used as the use-side heat medium which flows through the use-side heat medium circuit 30.
  • the use-side heat exchanger 13 heats the use-side heat medium discharged from the compressor 11.
  • the use-side heat medium which is heated by the use-side heat exchanger 13 radiates heat in the load termination 32 and is utilized for heating a room, the use-side heat medium radiates heat in the load termination 32 and become low in temperature and the use-side heat medium low is again heated by the use-side heat exchanger 13.
  • the internal heat exchanger 15 is provided between the economizer 14 and the first expansion device 16.
  • Fig. 2 is a pressure-enthalpy diagram (P-h diagram) in the refrigeration cycle device of the embodiment. Points (a) to (h) in Fig. 2 correspond to points (a) to (h) in Fig. 1 .
  • Fig. 1 shows heating operation using the use-side heat exchanger 13 as a condenser.
  • high pressure refrigerant (a) discharged from the compressor 11 radiates heat in the use-side heat exchanger 13.
  • a partial high pressure refrigerant after it radiates heat in the use-side heat exchanger 13 branches off from the main refrigerant circuit 10 (refrigerant branch point A), it is decompressed to the intermediate pressure by the second expansion device 21 and becomes intermediate pressure refrigerant (g), and the intermediate pressure refrigerant exchanges heat in the economizer 14 with high pressure refrigerant which flows through the main refrigerant circuit 10.
  • the high pressure refrigerant which flows through the main refrigerant circuit 10 after it radiates heat in the use-side heat exchanger 13 is cooled by the intermediate pressure refrigerant (g) which flows through the bypass refrigerant circuit 20, and its enthalpy is reduced (b).
  • the refrigerant (d) decompressed by the first expansion device 16 is reduced in refrigerant dryness (weight rate occupied by gas-phase component in the entire refrigerant) when the refrigerant (d) flows into the heat source-side heat exchanger 17, liquid component of refrigerant is increased, the refrigerant (d) evaporates (e) in the heat source-side heat exchanger 17, the refrigerant (d) absorbs heat in the internal heat exchanger 15 and returns to a suction side (f) of the compressor 11.
  • intermediate pressure refrigerant (g) which is decompressed to the intermediate pressure by the second expansion device 21 is heated by high pressure refrigerant which flows through the main refrigerant circuit 10 in the economizer 14, and the intermediate pressure refrigerant (g) joins up (h) with refrigerant which is in the middle of compression stroke of the compressor 11 in a state where refrigerant enthalpy becomes high.
  • High pressure refrigerant which flows through the internal heat exchanger 15 is high pressure refrigerant after it flows through the economizer 14, and by exchanging heat between high pressure refrigerant after it flows through the economizer 14 and low pressure refrigerant which flows out from the heat source-side heat exchanger 17, an enthalpy difference in the heat source-side heat exchanger 17 can further be increased, and since the endothermic energy amount is increased, energy saving performance of the device is enhanced.
  • the high pressure refrigerant flowing through the internal heat exchanger 15 and the low pressure refrigerant flowing through the internal heat exchanger 15 are opposite flows. By making the opposite flows in this manner, heat exchanging efficiency of the internal heat exchanger 15 is enhanced, and discharge temperature further increased. Therefore, the radiation amount in the use-side heat exchanger 13 is further increased, and energy saving performance of the device is enhanced.
  • a high pressure-side flow path 15a through which high pressure refrigerant flows is made narrower than a low pressure-side flow path 15b through which low pressure refrigerant flows. That is, a flow path sectional area of the high pressure-side flow path 15a is made smaller than that of the low pressure-side flow path 15b. Since the high pressure-side flow path 15a into which high density liquid refrigerant flows is made narrower than the low pressure-side flow path 15b into which low density gas refrigerant flows as described above, the flow speed of refrigerant becomes faster, and the transfer coefficient is enhanced.
  • the low pressure-side flow path 15b into which the low density gas refrigerant flows is made wider than the high pressure-side flow path 15a into which high density liquid refrigerant flows, pressure loss of refrigerant which flows through the low pressure-side flow path 15b is reduced and thus, energy saving performance of the device is enhanced.
  • Fig. 3 is a block diagram of the refrigeration cycle device of the embodiment, and shows a flow of refrigerant in a cooling operation.
  • the use-side heat exchanger 13 is used as an evaporator.
  • High pressure refrigerant which is discharged from the compressor 11 radiates heat in the heat source-side heat exchanger 17 and then, the high pressure refrigerant is decompressed by the first expansion device 16, the high pressure refrigerant passes through the internal heat exchanger 15, the high pressure refrigerant evaporates in the economizer 14 and the use-side heat exchanger 13, and the high pressure refrigerant again passes through the internal heat exchanger 15 and returns to the suction side of the compressor 11.
  • the low pressure refrigerant flowing through the main refrigerant circuit 10 at a location upstream of the economizer 14 and the low pressure refrigerant before it is sucked into the compressor 11 at a location downstream of the four-way valve 12 exchange heat in the internal heat exchanger 15.
  • the use-side heat exchanger 13 is used as an evaporator by switching the four-way valve in this manner, in the internal heat exchanger 15, the low pressure refrigerants which are radiated heat by the heat source-side heat exchanger 17, and which are decompressed by the first expansion device 16 exchange heat with each other. Therefore, even if the internal heat exchanger 15 is provided, temperature of refrigerant which flows into the heat source-side heat exchanger 17 is not lowered at the time of cooling operation, and cooling performance is not deteriorated.
  • Refrigerant which branches off from the main refrigerant circuit 10 at the refrigerant branch point A is decompressed to the intermediate pressure by the second expansion device 21 and becomes intermediate pressure refrigerant, and the intermediate pressure refrigerant exchanges heat with high pressure refrigerant which flows through the main refrigerant circuit 10 in the economizer 14.
  • Figs. 4 are graphs comparing COP depending upon existence or non-existence of an internal heat exchanger and a discharge superheat degree with each other.
  • a case where the internal heat exchanger 15 exists shows the refrigeration cycle device illustrated in Figs. 1 to 3
  • a case where there is no internal heat exchanger 15 shows a comparative device using no internal heat exchanger 15 in the refrigeration cycle device illustrated in Figs. 1 to 3 .
  • propane is used as the refrigerant.
  • a lateral axis shows a bypass ratio and a vertical axis shows COP.
  • the refrigeration cycle device according to this embodiment having the internal heat exchanger 15 has higher COP as compared with the comparative device using no internal heat exchanger 15 where the bypass ratio is in a range of 0% to 40%.
  • a lateral axis shows the bypass ratio and a vertical axis shows a discharge superheat degree.
  • the refrigeration cycle device of this embodiment having the internal heat exchanger 15 has a higher discharge superheat degree as compared with the comparative device using no internal heat exchanger 15 where the bypass ratio is in a range of 0% to 20%.
  • Figs. 5 and 6 are T-h diagrams of a radiator (use-side heat exchanger) depending upon existence or non-existence of the internal heat exchanger.
  • a case where the internal heat exchanger 15 exists shows the refrigeration cycle device illustrated in Figs. 1 to 3
  • a case where there is no internal heat exchanger 15 shows a comparative device using no internal heat exchanger 15 in the refrigeration cycle device illustrated in Figs. 1 to 3 .
  • propane is used as the refrigerant.
  • Fig. 5(a) is a T-h diagram in a comparative device having no internal heat exchanger
  • Fig. 5(b) is T-h diagram in the refrigeration cycle device of this embodiment having the internal heat exchanger 15.
  • the refrigeration cycle device of this embodiment shown in Fig. 5(b) has a larger temperature difference between water and refrigerant as compared with the comparative device using no internal heat exchanger 15 shown in Fig. 5(a) .
  • a logarithm average temperature difference is 0.7K in the comparative device using no internal heat exchanger 15, and is 4.2K in the refrigeration cycle device of this embodiment.
  • the refrigeration cycle device of the embodiment is provided with the internal heat exchanger 15. According to this, discharge temperature rises, and a temperature difference between water and refrigerant is increased.
  • the suction superheat degree of refrigerant sucked into the compressor 11 can be increased, and even if injection is carried out using propane as the refrigerant, it is possible to reliably secure the discharge superheat degree, and COP is also enhanced. Since the discharge temperature from the compressor 11 rises, a temperature difference between refrigerant and heat medium to be heated is increased in the condenser (use-side heat exchanger 13). Therefore, a radiation amount from the condenser 13 is increased.
  • the refrigeration cycle device of the present invention even if injection is carried out using propane as the refrigerant, it is possible to sufficiently secure discharge SH, and to efficiently operate the device.

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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)
EP23217474.8A 2022-12-20 2023-12-18 Kältekreislaufvorrichtung Pending EP4390269A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2022203650A JP2024088461A (ja) 2022-12-20 2022-12-20 冷凍サイクル装置

Publications (1)

Publication Number Publication Date
EP4390269A1 true EP4390269A1 (de) 2024-06-26

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Application Number Title Priority Date Filing Date
EP23217474.8A Pending EP4390269A1 (de) 2022-12-20 2023-12-18 Kältekreislaufvorrichtung

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019148394A (ja) 2018-02-28 2019-09-05 株式会社富士通ゼネラル 空気調和機
EP3671049A1 (de) * 2018-12-17 2020-06-24 Panasonic Intellectual Property Management Co., Ltd. Wärmepumpensystem
WO2022208727A1 (ja) * 2021-03-31 2022-10-06 三菱電機株式会社 冷凍サイクル装置
EP4089345A1 (de) * 2021-05-12 2022-11-16 Panasonic Intellectual Property Management Co., Ltd. Kältekreislaufvorrichtung und flüssigkeitsheizvorrichtung damit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019148394A (ja) 2018-02-28 2019-09-05 株式会社富士通ゼネラル 空気調和機
EP3671049A1 (de) * 2018-12-17 2020-06-24 Panasonic Intellectual Property Management Co., Ltd. Wärmepumpensystem
WO2022208727A1 (ja) * 2021-03-31 2022-10-06 三菱電機株式会社 冷凍サイクル装置
EP4089345A1 (de) * 2021-05-12 2022-11-16 Panasonic Intellectual Property Management Co., Ltd. Kältekreislaufvorrichtung und flüssigkeitsheizvorrichtung damit

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