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EP3217118B1 - Heat pump apparatus - Google Patents

Heat pump apparatus Download PDF

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Publication number
EP3217118B1
EP3217118B1 EP16186105.9A EP16186105A EP3217118B1 EP 3217118 B1 EP3217118 B1 EP 3217118B1 EP 16186105 A EP16186105 A EP 16186105A EP 3217118 B1 EP3217118 B1 EP 3217118B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
evaporator
refrigeration circuit
heat exchanger
pressure
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.)
Active
Application number
EP16186105.9A
Other languages
German (de)
French (fr)
Other versions
EP3217118A1 (en
Inventor
Akihiro Shigeta
Masaru Matsui
Seishi Iitaka
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
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Panasonic Intellectual Property Management Co Ltd
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Publication of EP3217118A1 publication Critical patent/EP3217118A1/en
Application granted granted Critical
Publication of EP3217118B1 publication Critical patent/EP3217118B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/18—Hot-water central heating systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way 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
    • 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
    • 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
    • F25B2313/02791—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using shut-off 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
    • 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
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/06—Several compression cycles arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures of 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the present invention relates to a heat pump apparatus which adjusts the pressure of a refrigerant in an evaporator in the lower-stage cycle of a binary refrigeration cycle.
  • a conventional heat pump apparatus includes two refrigeration circuits of an air-conditioning refrigeration cycle 59 and a hot water supply refrigeration cycle 63.
  • the air-conditioning refrigeration cycle 59 is configured such that an air-conditioning compressor 50, an outdoor heat exchanger 51, each of outdoor heat exchanger opening/closing means 52a and 52b, outdoor heat exchanger diaphragm means 53, an indoor heat exchanger 54, each of indoor heat exchanger opening/closing means 55a and 55b, and an indoor heat exchanger diaphragm means 56 are connected in series, and such that a refrigerant-refrigerant heat exchanger 57 and a hot water heat source diaphragm means 58, which are connected in series, are connected in parallel with the indoor heat exchanger 54, each of the indoor heat exchanger opening/closing means 55a and 55b, and the indoor heat exchanger diaphragm means 56.
  • an air-conditioning refrigerant is made to circulate through the air-conditioning refrigeration cycle 59.
  • the hot water supply refrigeration cycle 63 includes a hot-water supply compressor 60, a heat medium-refrigerant heat exchanger 61, hot water supply diaphragm means 62, and the refrigerant-refrigerant heat exchanger 57, all of which are connected in series. With this configuration, a hot water refrigerant is made to circulate through the hot-water supply refrigeration cycle 63.
  • the air-conditioning refrigeration cycle 59 and the hot-water supply refrigeration cycle 63 are connected to each other so that the air conditioning refrigerant and the hot-water supply refrigerant are heat-exchanged with each other in the refrigerant-refrigerant heat exchanger 57. Thereby, the cooling or heating operation in the air-conditioning refrigeration cycle 59, and the heating operation with hot water supply heat medium in the hot water supply refrigeration cycle 63 can be performed simultaneously (see, for example, International Publication No. WO 2009/098751 ).
  • the condensation temperature in the air-conditioning refrigeration cycle 59 is high, and thereby, the evaporation temperature in the hot water supply refrigeration cycle 63 also become high in the refrigerant-refrigerant heat exchanger 57.
  • Document EP-A-2 846 111 discloses a heat pump apparatus according to the preamble of claim 1.
  • An object of the present invention is to a heat pump apparatus which can reduce the discharge temperature of the compressor to improve the reliability of the compressor, even at the time of heating operation under the condition that the heating load is high, or at the time of cooling operation under the condition that the outside air temperature is high.
  • a heat pump apparatus includes the features of claim 1.
  • the high pressure-side pressure of the second refrigerant in the evaporator is reduced, that the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator is reduced, and that the degree of superheat of the first refrigerant at the outlet of the evaporator is reduced. Therefore, the discharge temperature of the compressor can also be reduced. Further, the high pressure-side pressure of the second refrigerant in the evaporator can be adjusted to a desired value.
  • the discharge temperature of the compressor can be reduced, and thereby, the reliability of the compressor can be improved.
  • the heat exchanger for example, an air-conditioning indoor unit, which is installed in the circuit in parallel with the evaporator, performs high-temperature-air heating operation which requires a high condensation temperature
  • the operation in the first refrigeration circuit can be performed simultaneously with the operation in the second refrigeration circuit.
  • the heat pump apparatus includes : a first refrigeration circuit in which a compressor, a condenser, first diaphragm means, and an evaporator are connected by a pipe, and which circulates a first refrigerant therethrough; a second refrigeration circuit which circulated a second refrigerant therethrough and performs heat exchange with the first refrigeration circuit in the evaporator; second diaphragm means and third diaphragm means which are respectively arranged at an inlet and an outlet of the evaporator of the second refrigeration circuit; and a control section which controls the opening degrees of the second diaphragm means and the third diaphragm means, wherein the control section has a first refrigeration circuit discharge temperature suppression mode which reduces the opening degree of the second diaphragm means so that the pressure of the second refrigerant in the evaporator is not more than a predetermined value.
  • the high pressure-side pressure of the second refrigerant in the evaporator is reduced, and thereby, the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator is reduced, so that the degree of superheat of the first refrigerant at the outlet of the evaporator is reduced. Therefore, the discharge temperature of the compressor can be reduced.
  • the high pressure-side pressure of the second refrigerant in the evaporator can be adjusted to a desired value.
  • the condensation temperature of the second refrigeration circuit is high and thereby a heating load is high, or when cooling operation is performed at a high outside air temperature, the discharge temperature of the compressor can be reduced, and thereby, the reliability of the compressor can be improved.
  • a heat exchanger for example, an air conditioning indoor unit, which is installed in the circuit in parallel with the evaporator, performs high-temperature-air heating operation which requires a high condensation temperature
  • the operation in the first refrigeration circuit can be performed simultaneously with the operation in the second refrigeration circuit.
  • the first refrigeration circuit discharge temperature suppression mode further includes control of the opening and closing of the third diaphragm means on the basis of the supercooling degree of the second refrigerant at the outlet of the evaporator.
  • the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator can be reduced, and thereby, the degree of superheat of the first refrigerant at the outlet of the evaporator can be reduced.
  • FIG. 1 is a refrigerant circuit diagram of a heat pump apparatus in a first embodiment of the present invention 1.
  • the heat pump apparatus includes two refrigeration circuits of a first refrigeration circuit 5 and a second refrigeration circuit 20.
  • the first refrigeration circuit 5 is configured by connecting in series a compressor 1, a condenser 2, first diaphragm means 3, and an evaporator 4 by a refrigerant pipe 40. A first refrigerant is circulated in the first refrigeration circuit 5.
  • compressor discharge temperature detection means 6 which detects the temperature of the first refrigerant discharged from the compressor 1, is arranged at the discharge side of the compressor 1.
  • compressor suction temperature detection means 31 which detects the temperature of the first refrigerant sucked into the compressor 1, is arranged at the suction side of the compressor 1.
  • compressor suction pressure detection means 32 which detects the pressure of the first refrigerant sucked into the compressor 1, is arranged at the suction side of the compressor 1.
  • second refrigeration circuit evaporator intermediate temperature detection means 30, which detects intermediate temperature of the evaporator 4 in the second refrigeration circuit 20, is arranged in the evaporator 4.
  • the second refrigeration circuit 20 is configured by connecting, by a second refrigerant pipe 41, a second compressor 11, an outdoor heat exchanger 15 which performs heat exchange with outdoor air, two indoor heat exchangers 12a and 12b which perform heat exchange with indoor air, and the evaporator 4.
  • the indoor heat exchangers 12a and 12b are provided in parallel with each other.
  • a discharge refrigerant pipe 42 which is connected to the discharge side of the second compressor 11, is connected in a branching manner at one inlet side of each of the indoor heat exchangers 12a and 12b.
  • a suction refrigerant pipe 43 which is connected to the suction side of the second compressor 11, is connected in a branching manner at the one inlet side of each of the indoor heat exchangers 12a and 12b.
  • Indoor heat exchanger opening/closing means 13b and 13d are connected to the discharge refrigerant pipe 42, and indoor heat exchanger opening/closing means 13a and 13c are connected to the suction refrigerant pipe 43.
  • indoor heat exchanger diaphragm means 14a and 14b are respectively provided at the other inlet sides of the indoor heat exchangers 12a and 12b.
  • the evaporator 4 is connected in parallel with each of the indoor heat exchangers 12a and 12b.
  • the inlet side of the evaporator 4 is connected to the discharge refrigerant pipe 42, and the outlet side of the evaporator 4 is connected to the second refrigerant pipe 41.
  • Second diaphragm means 18 is provided at the inlet side of the evaporator 4
  • third diaphragm means 19 is provided at the outlet side of the evaporator 4.
  • the suction refrigerant pipe 43 which is connected at the suction side of the compressor 11, is connected at one of two branches at the one inlet side of each of the indoor heat exchangers 12a and 12b.
  • the discharge refrigerant pipe 42 which is connected at the discharge side of the second compressor 11, is connected at the other of the two branches at the one inlet side of each of the indoor heat exchangers 12a and 12b.
  • Each of outdoor heat exchanger opening/closing means 16a and 16b is provided between the outdoor heat exchanger 15 and the second compressors 11.
  • Outdoor heat exchanger diaphragm means 17 is provided at the other inlet side of the outdoor heat exchanger 15.
  • the second refrigerant is circulated in the second refrigeration circuit 20 configured in this way.
  • a natural refrigerant such as carbon dioxide (CO2)
  • CO2 carbon dioxide
  • a fluorocarbon-based refrigerant such as R22, R410A, R407C, R32 and R134a
  • second compressor discharge pressure detection means 21, which detects the pressure of the second refrigerant discharged from the second compressor 11, is provided at the discharge side of the second compressor 11.
  • second compressor suction pressure detection means 22, which detects the pressure of the second refrigerant sucked into the second compressor 11, is provided at the suction side of the second compressor 11.
  • Indoor heat exchanger first temperature detection means 23a which detects the temperature of the second refrigerant, is provided between the indoor heat exchanger 12a and the indoor heat exchanger opening/closing means 13a and 13b. Also, indoor heat exchanger first temperature detection means 23b, which detects the temperature of the second refrigerant, is provided between the indoor heat exchanger 12b and the indoor heat exchanger opening/closing means 13c and 13d. Further, indoor heat exchanger second temperature detection means 24a, which detect the temperature of the second refrigerant, is provided between the indoor heat exchanger 12a and the indoor heat exchanger diaphragm means 14a. Also, indoor heat exchanger second temperature detection means 24b, which detect the temperature of the second refrigerant, is provided between the indoor heat exchanger 12b and the indoor heat exchanger diaphragm means 14b.
  • outdoor heat exchanger first temperature detection means 25 which detects the temperature of the second refrigerant, is provided between the outdoor heat exchanger 15 and each of the outdoor heat exchanger opening/closing means 16a and 16b.
  • outdoor heat exchanger second temperature detection means 26 which detects the temperature of the second refrigerant, is provided between the outdoor heat exchanger 15 and the outdoor heat exchanger diaphragm means 17.
  • second refrigeration circuit evaporator inlet pressure detection means 27 which detects the pressure of the second refrigerant flowing into the evaporator 4, is provided between the second diaphragm means 18 and the evaporators 4.
  • second refrigeration circuit evaporator outlet temperature detection means 28 which detects the temperature of the second refrigerant flowing out from the evaporator 4, is provided between the evaporator 4 and the third diaphragm means 19.
  • the heat pump apparatus of the present embodiment includes a control section 29 as control means for controlling the first refrigeration circuit 5 and the second refrigeration circuit 20.
  • the control section 29 centrally controls respective portions of the heat pump apparatus, and includes: a CPU; a ROM storing, in a non-volatile manner, an executable basic control program, data relating to the basic control program, and the like; a RAM temporarily storing a program executed by the CPU, predetermined data, and the like; and other peripheral circuits, and the like.
  • the control section 29 is configured to perform, in the first refrigeration circuit 5, drive control of the compressor 1, and control of the degree of opening of the first diaphragm means 3, on the basis of the detection results of the compressor discharge temperature detection means 6, the compressor suction temperature detection means 31, and the compressor suction pressure detection means 32.
  • control section 29 is configured to perform, in the second refrigeration circuit 20, drive control of the second compressor 11, and control of the degree of opening of each of the second diaphragm means 18, the third diaphragm means 19, the indoor heat exchanger diaphragm means 14a and 14b, and the outdoor heat exchanger diaphragm means 17, on the basis of the detection results of the second compressor discharge pressure detection means 21, and the second compressor suction pressure detection means 22, and on the basis of the detection results of the indoor heat exchanger first temperature detection means 23a and 23b, the indoor heat exchanger second temperature detection means 24a and 24b, the outdoor heat exchanger first temperature detection means 25, the outdoor heat exchanger second temperature detection means 26, the second refrigeration circuit evaporator inlet pressure detection means 27, and the second refrigeration circuit evaporator outlet temperature detection means 28.
  • control which is performed by the control section 29, is provided with the first refrigeration circuit discharge temperature suppression mode which reduces the degree of opening of the second diaphragm means 18 so that the pressure of the second refrigerant in the evaporator 4 is not more than a predetermined value.
  • the first refrigeration circuit discharge temperature suppression mode is controlled on the basis of the pressure Peva_r 2 of the second refrigerant, which is detected by the second refrigeration circuit evaporator inlet pressure detection means 27.
  • control section 29 determines whether or not the pressure Peva_r 2 of the second refrigerant is more than a predetermined value (for example, 3.0 MPa). When the pressure Peva_r 2 of the second refrigerant is more than the predetermined value, the control section 29 performs control to reduce the degree of opening of the second diaphragm means 18. The control section 29 determines whether or not the pressure Peva_r 2 of the second refrigerant is within a range of a predetermined value (for example, the range not less than 2.6 MPa and not more than 3.0 MPa).
  • a predetermined value for example, 3.0 MPa
  • the control section 29 When the pressure Peva_r 2 of the second refrigerant is within the range of the predetermined value, the control section 29 performs control to maintain the degree of opening of the second diaphragm means 18. Further, the control section 29 determines whether or not the Pressure Peva_r 2 of the second refrigerant is less than a predetermined value (for example, 2.6 MPa). When the Pressure Peva_r 2 of the second refrigerant is less than the predetermined value, the control section 29 performs control to increase the degree of opening of the second diaphragm means 18.
  • a predetermined value for example, 2.6 MPa
  • control section 29 can reduce the high pressure-side pressure of the second refrigerant in the evaporator 4.
  • control section 29 controls the first refrigeration circuit discharge temperature suppression mode, on the basis of the supercooling degree SCeva_o_r 2 of the second refrigerant at the outlet of the evaporator 4 of the second refrigeration circuit 20.
  • the supercooling degree SCeva_o_r 2 of the second refrigerant can be obtained from the difference between the condensation temperature calculated on the basis of the pressure Peva_r 2 of the second refrigerant, and the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28 (that is, the condensation temperature calculated on the basis of the pressure Peva_r 2 of the second refrigerant minus the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28).
  • the control section 29 determines whether or not the supercooling degree SCeva_o_r 2 of the second refrigerant is within a range of a predetermined value (for example, 3K ⁇ SCeva_o_r 2 ⁇ 7K). When the supercooling degree SCeva_o_r 2 of the second refrigerant is within the predetermined value, the control section 29 performs control to maintain the degree of opening of the third diaphragm means 19. Further, the control section 29 determines whether or not the supercooling degree SCeva_o_r 2 of the second refrigerant is more than a predetermined value (for example, 7 K). When the supercooling degree SCeva_o_r 2 of the second refrigerant is more than the predetermined value, the control section 29 performs control to increase the degree of opening of the third diaphragm means 19.
  • a predetermined value for example, 3K ⁇ SCeva_o_r 2 ⁇ 7K
  • control section 29 determines whether or not the supercooling degree SCeva_o_r 2 of the second refrigerant is less than a predetermined value (for example, 3 K). When the supercooling degree SCeva_o_r 2 of the second refrigerant is less than the predetermined value, the control section 29 performs control to reduce the degree of opening of the third diaphragm means 19.
  • a predetermined value for example, 3 K.
  • control section 29 can reduce the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator 4, and can reduce the degree of superheat of the first refrigerant at the outlet of the evaporator 4.
  • FIG. 2 is a circuit diagram showing an example when the heating operation of the second refrigeration circuit 20 is performed by using the indoor heat exchangers 12a and 12b are used as condensers, and when the first refrigeration circuit 5 is also operated. It should be noted that each of the blackened opening/closing means in FIG. 2 indicates that it is closed.
  • the second refrigerant which is discharged from the second compressor 11, flows into the indoor heat exchangers 12a and 12b and dissipates heat to the indoor air.
  • the first refrigerant which is discharged from the compressor 1, discharges heat into the condenser 2.
  • the first refrigerant which is limited by the first diaphragm means 3 on the basis of the temperature detected by the compressor discharge temperature detection means 6, is made to flow into the evaporator 4, and absorbs heat from the second refrigerant, the pressure of which is adjusted by the second diaphragm means 18 on the basis of the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27. Then, the first refrigerant is sucked into the compressor 1.
  • the second refrigerant the heat of which is absorbed by the first refrigerant in the evaporator 4 is limited by the third diaphragm means 19 on the basis of the supercooling degree obtained from the difference between the condensation temperature calculated from the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27, and the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28.
  • the second refrigerant flowing out from each of the indoor heat exchangers 12a and 12b is limited by each of the indoor heat exchanger diaphragm means 14a and 14b, on the basis of the supercooling degrees obtained from the difference between the condensation temperature calculated from the pressure detected by the second compressor discharge pressure detection means 21, and each of the temperatures detected by the indoor heat exchanger second temperature detection means 24a and 24b.
  • the second refrigerant limited by the third diaphragm means 19, and the second refrigerant limited the indoor heat exchanger diaphragm means 14a and 14b, are mixed with each other, and then absorb heat from the outdoor air in the outdoor heat exchanger 15.
  • the outdoor heat exchanger diaphragm means 17 adjusts the second refrigerant flowing through the outdoor heat exchanger 15, on the basis of the degree of superheat obtained from the difference between the evaporation temperature calculated from the pressure detected by the second compressor suction pressure detection means 22, and the temperature detected by the outdoor heat exchanger first temperature detection means 25.
  • the second refrigerant flowing out from the outdoor heat exchanger 15 is sucked into the second compressor 11 through the outdoor heat exchanger opening/closing means 16a which is opened.
  • the indoor heat exchanger opening/closing means 13a and 13c and the outdoor heat exchanger opening/closing means 16b are closed, and hence the second refrigerant does not flow through each of the opening/closing means.
  • FIG. 3 is a circuit diagram showing an example when the cooling operation of the second refrigeration circuit 20 is performed by using the indoor heat exchangers 12a and 12b as evaporators, and when the first refrigeration circuit 5 is also operated. It should be noted that each of the blackened opening/closing means in FIG. 3 indicates that it is closed.
  • the second refrigerant discharged from the second compressor 11 flows into the outdoor heat exchanger 15 and dissipates heat to the indoor air.
  • the first refrigeration circuit 5 similar to the case of heating operation in the second refrigeration circuit 20, the first refrigerant discharged from the compressor 1 discharges heat in the condenser 2. Then, the first refrigerant, which is limited by the first diaphragm means 3 on the basis of the temperature detected by the compressor discharge temperature detection means 6, flows into the evaporator 4.
  • the first refrigerant absorbs heat from the second refrigerant, the pressure of which is adjusted by the second diaphragm means 18 on the basis of the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27, and is sucked into the compressor 1.
  • the second refrigerant the heat of which is absorbed by the first refrigerant in the evaporator 4 is limited by the third diaphragm means 19, on the basis of the supercooling degree obtained from the difference between the condensation temperature calculated from the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27, and the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28.
  • the second refrigerant flowing out from the outdoor heat exchanger 15 is limited by the outdoor heat exchanger diaphragm means 17, on the basis of the supercooling degree obtained from the difference between the condensation temperature calculated from the pressure detected by the second compressor discharge pressure detection means 21, and the temperature detected by the outdoor heat exchanger second temperature detection means 26.
  • the second refrigerant limited by the third diaphragm means 19 and the second refrigerant limited by the outdoor heat exchanger diaphragm means 17 are mixed with each other and absorb heat from the indoor air in the indoor heat exchangers 12a and 12b.
  • the second refrigerant flowing through each of the indoor heat exchangers 12a and 12b is adjusted by each of the indoor heat exchanger diaphragm means 14a and 14b, on the basis of the degree of superheat which is obtained from the difference between the evaporation temperature calculated from the pressure detected by the second compressor suction pressure detection means 22, and the temperature detected by each of the indoor heat exchanger first temperature detection means 23a and 23b.
  • the second refrigerant flowing out from the indoor heat exchangers 12a and 12b is sucked into the second compressor 11 through the indoor heat exchanger opening/closing means 13a and 13c which are opened.
  • the indoor heat exchanger opening/closing means 13b and 13d and the outdoor heat exchanger opening/closing means 16a are closed, and hence the second refrigerant is not made to flow through the indoor and outdoor heat exchanger opening/closing means.
  • FIG. 4 is a circuit diagram showing an example in the case where the indoor heat exchanger 12a and the indoor heat exchanger 12b are respectively used as a condenser and an evaporator, and where cooling operation and heating operation are performed at the same time in the second refrigeration circuit 20, and also the first refrigeration circuit 5 is operated. It should be noted that each of the blackened opening/closing means in FIG. 4 indicates that it is closed.
  • the second refrigerant discharged from the second compressor 11 flows into the indoor heat exchanger 12a through the indoor heat exchanger opening/closing means 13b in an opened state, and discharges heat to the indoor air.
  • the first refrigerant discharged from the compressor 1 discharges heat in the condenser 2. Then, the first refrigeration is limited by the first diaphragm means 3 on the basis of the temperature detected by the compressor discharge temperature detection means 6, and flows into the evaporator 4.
  • the first refrigeration absorbs heat from the second refrigerant, the pressure of which is adjusted by the second diaphragm means 18 on the basis of the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27, and is sucked into the compressor 1.
  • the second refrigerant the heat of which is absorbed by the first refrigerant, is limited by the third diaphragm means 19 on the basis of the supercooling degree obtained from the difference between the condensation temperature calculated from the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27, and the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28.
  • the second refrigerant flowing out from the indoor heat exchanger 12a is limited by the indoor heat exchanger diaphragm means 14a on the basis of the supercooling degree obtained from the difference between the condensation temperature calculated from the pressure detected by the second compressor discharge pressure detection means 21, and the temperature detected by the indoor heat exchanger second temperature detection means 24a.
  • the second refrigerant limited by the third diaphragm means 19, and the second refrigerant limited by the indoor heat exchanger diaphragm means 14a are mixed with each other, to absorb heat from indoor air in the indoor heat exchanger 12b and from outdoor air in the outdoor heat exchanger 15.
  • Each of the indoor heat exchanger diaphragm means 14b and the outdoor heat exchanger diaphragm means 17 adjusts the second refrigerant flowing into each of the indoor heat exchanger 12b and the outdoor heat exchanger 15, on the basis of the degree of superheat obtained from the difference between the evaporation temperature calculated from the pressure detected by the second compressor suction pressure detection means 22, and the temperature detected by each of the indoor heat exchanger first temperature detection means 23b and the outdoor heat exchanger first temperature detection means 25.
  • the second refrigerant which flows out from each of the indoor heat exchanger 12b and the outdoor heat exchanger 15, is sucked into the second compressor 11 through each of the indoor heat exchanger opening/closing means 13c and the outdoor heat exchanger opening/closing means 16a which are opened.
  • the indoor heat exchanger opening/closing means 13a and 13d, and the outdoor heat exchanger opening/closing means 16b are closed, and hence, the second refrigerant does not flow through each of the indoor and outdoor heat exchanger opening/closing means.
  • FIG. 5 is a circuit diagram showing an example in the case where cooling operation and heating operation are performed at the same time in the second refrigeration circuit 20 by respectively using the indoor heat exchanger 12a and the indoor heat exchanger 12b as an evaporator and a condenser, and where the first refrigeration circuit 5 is also operated. It should be noted that each of the blackened opening/closing means in FIG. 5 indicates that it is closed.
  • the operation is performed without changing the opening and closing states of the outdoor heat exchanger opening/closing means 16a and 16b.
  • the second refrigeration circuit 20 when, in the heating operation, the second refrigeration circuit 20 requires a large amount of heat to be discharged to indoor air (for example, the indoor temperature is 5°C, and the set temperature is 30°C), or when, in the cooling operation, the temperature of outdoor air is highly (for example, 40°C) so that the temperature of the second refrigerant flowing into the outdoor heat exchanger 15 needs to be not less than the temperature of outdoor air, the high pressure-side pressure of the second refrigeration circuit 20 becomes high.
  • the pressure of the second refrigerant flowing into the evaporator 4 also becomes high, the condensation temperature becomes high (for example, 50°C), and hence, the evaporation temperature of the first refrigeration circuit 5 also becomes high.
  • the degree of superheat of the first refrigerant flowing out from the evaporator 4 becomes larger.
  • control section 29 performs control by the first refrigeration circuit discharge temperature suppression mode.
  • FIG. 6 is a flowchart showing the operation by the first refrigeration circuit discharge temperature suppression mode.
  • the control section 29 determines whether or not the pressure Peva_r 2 of the second refrigerant, which is detected by the second refrigeration circuit evaporator inlet pressure detection means 27, is more than 3.0 MPa (ST1). Then, when determining that the pressure Peva_r 2 of the second refrigerant is more than 3.0 MPa (ST1: YES), the control section 29 reduces the opening degree of the second diaphragm means 18 (ST2).
  • control section 29 determines whether or not the supercooling degree SCeva_o_r 2 of the second refrigerant at the outlet of the evaporator 4 of the second refrigeration circuit 20 is in the range of 3 K ⁇ SCeva_o_r 2 ⁇ 7K (ST3). Then, when determining that the supercooling degree SCeva_o_r 2 of the second refrigerant is in the predetermined range (ST3: YES), the control section 29 performs control to maintain the opening degree of the third diaphragm means 19 (ST4).
  • the control section 29 performs control to increase the opening degree of the third diaphragm means 19 (ST6).
  • the control section 29 performs control to reduce the opening degree of the third diaphragm means 19 (ST7).
  • control section 29 determines whether or not the pressure Peva_r 2 of the second refrigerant is more than 2.6 MPa which is the lower limit value of the pressure Peva_r2 of the second refrigerant (ST8).
  • the control section 29 performs control to maintain the opening degree of the second diaphragm means 18 (ST9).
  • the control section 29 performs control to increase the opening degree of the second diaphragm means 18 (ST10).
  • control section 29 performs control of the third diaphragm means 19 on the basis of the flow of ST3 to ST7.
  • the control section 29 is provided with the first refrigeration circuit discharge temperature suppression mode which reduces the opening degree of the second diaphragm means 18 for preventing the pressure of the second refrigerant in the evaporator 4 from being more than the predetermined value.
  • the high pressure-side pressure of the second refrigerant in the evaporator 4 can be reduced, and the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator 4 can be reduced.
  • the degree of superheat of the first refrigerant at the outlet of the evaporator 4 can be reduced, and the discharge temperature of the compressor 1 can be reduced.
  • the condensation temperature of the second refrigeration circuit 20 is high, and thereby the heating load is high, or even when cooling operation is performed under the condition of high outdoor-air temperature, the discharge temperature of the compressor 1 can be reduced, and thereby, the reliability of the compressor 1 can be improved.
  • the pressures of the second refrigerant in the evaporator 4 can be individually controlled.
  • the high-temperature-air heating operation in which high condensation temperature is required at indoor heat exchangers 12a and 12b, and the operation in the first refrigeration circuit 5 can be simultaneously performed.
  • the opening degree of the second diaphragm means 18 is adjusted on the basis of the pressure obtained by detecting the pressure of the second refrigerant in the evaporator 4 by the second refrigeration circuit evaporator inlet pressure detection means 27.
  • the opening degree of the second diaphragm means 18 can also be adjusted on the basis of the temperature detected by the second refrigeration circuit evaporator intermediate temperature detection means 30, the temperature detected by the compressor suction temperature detection means 31, or the pressure detected by the compressor suction pressure detection means 32.
  • the opening degree of the third diaphragm means 19 is adjusted on the basis of the supercooling degree SCeva_o_r 2. However, it is also possible to perform control such that the opening degree of the third diaphragm means 19 is adjusted on the basis of the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28, so that the suction temperature of the compressor 1 does not exceed the upper limit.
  • the heat pump apparatus is configured to suppress the increase of the compressor discharge temperature of the high-stage-side refrigeration circuit in the binary refrigeration cycle, and can be applied to applications, such as an air conditioner, a chiller, a drier, a hot water supply air conditioning composite apparatus, a hot water heater, and the like.

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Description

    BACKGROUND OF THE INVENTION Field of the Invention
  • The present invention relates to a heat pump apparatus which adjusts the pressure of a refrigerant in an evaporator in the lower-stage cycle of a binary refrigeration cycle.
    • Description of the Related Art
  • As shown in FIG. 7, a conventional heat pump apparatus includes two refrigeration circuits of an air-conditioning refrigeration cycle 59 and a hot water supply refrigeration cycle 63.
  • The air-conditioning refrigeration cycle 59 is configured such that an air-conditioning compressor 50, an outdoor heat exchanger 51, each of outdoor heat exchanger opening/closing means 52a and 52b, outdoor heat exchanger diaphragm means 53, an indoor heat exchanger 54, each of indoor heat exchanger opening/closing means 55a and 55b, and an indoor heat exchanger diaphragm means 56 are connected in series, and such that a refrigerant-refrigerant heat exchanger 57 and a hot water heat source diaphragm means 58, which are connected in series, are connected in parallel with the indoor heat exchanger 54, each of the indoor heat exchanger opening/closing means 55a and 55b, and the indoor heat exchanger diaphragm means 56. With this configuration, an air-conditioning refrigerant is made to circulate through the air-conditioning refrigeration cycle 59.
  • Further, the hot water supply refrigeration cycle 63 includes a hot-water supply compressor 60, a heat medium-refrigerant heat exchanger 61, hot water supply diaphragm means 62, and the refrigerant-refrigerant heat exchanger 57, all of which are connected in series. With this configuration, a hot water refrigerant is made to circulate through the hot-water supply refrigeration cycle 63.
  • The air-conditioning refrigeration cycle 59 and the hot-water supply refrigeration cycle 63 are connected to each other so that the air conditioning refrigerant and the hot-water supply refrigerant are heat-exchanged with each other in the refrigerant-refrigerant heat exchanger 57. Thereby, the cooling or heating operation in the air-conditioning refrigeration cycle 59, and the heating operation with hot water supply heat medium in the hot water supply refrigeration cycle 63 can be performed simultaneously (see, for example, International Publication No. WO 2009/098751 ).
  • However, in the above-described conventional configuration, under a condition that the condensation temperature is high (for example, 50°C), as in the case where the heating load is high in the air-conditioning refrigeration cycle 59, or where cooling operation is performed under a condition that the outside air temperature is high, the evaporation temperature in the air-conditioning refrigeration cycle 59 is high, and thereby, the evaporation temperature in the hot water supply refrigeration cycle 63 also become high in the refrigerant-refrigerant heat exchanger 57. Therefore, when the enthalpy difference, which is equivalent to that in the case where the evaporation temperature is low, is secured, the degree of superheat of the hot water supply refrigerant becomes large at the outlet of the refrigerant-refrigerant heat exchanger 57.
  • In this case, there is a problem that the temperature of the hot water supply refrigerant discharged from the hot water supply compressor 60 is increased excessively, and thereby, the reliability of the hot water supply compressor 60 is reduced as compared with the case where the degree of superheat is small. Document EP-A-2 846 111 discloses a heat pump apparatus according to the preamble of claim 1.
  • The present invention has been made in view of the above-described problem. An object of the present invention is to a heat pump apparatus which can reduce the discharge temperature of the compressor to improve the reliability of the compressor, even at the time of heating operation under the condition that the heating load is high, or at the time of cooling operation under the condition that the outside air temperature is high.
    • SUMMARY OF THE INVENTION
  • To solve the above-described problems, a heat pump apparatus according to the present invention includes the features of claim 1.
  • Thereby, it is possible that the high pressure-side pressure of the second refrigerant in the evaporator is reduced, that the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator is reduced, and that the degree of superheat of the first refrigerant at the outlet of the evaporator is reduced. Therefore, the discharge temperature of the compressor can also be reduced. Further, the high pressure-side pressure of the second refrigerant in the evaporator can be adjusted to a desired value.
  • According to the heat pump apparatus of the present invention, even in the case where the heating load is high due to a high condensation temperature of the second refrigeration circuit, or where cooling operation is performed under a high outdoor air temperature, the discharge temperature of the compressor can be reduced, and thereby, the reliability of the compressor can be improved.
  • Further, even when, in the second refrigeration circuit, the heat exchanger, for example, an air-conditioning indoor unit, which is installed in the circuit in parallel with the evaporator, performs high-temperature-air heating operation which requires a high condensation temperature, the operation in the first refrigeration circuit can be performed simultaneously with the operation in the second refrigeration circuit.
    • BRIEF DESCRIPTION OF THE DRAWINGS
    • FIG. 1 is a refrigerant circuit diagram of a heat pump apparatus in an embodiment 1 of the present invention;
    • FIG. 2 is a refrigerant circuit diagram when, in the embodiment 1 of the present invention, the heating operation of a second refrigeration circuit of the heat pump apparatus is performed, and also a first refrigeration circuit is operated;
    • FIG. 3 is a refrigerant circuit diagram when, in the embodiment 1 of the present invention, the cooling operation of the second refrigeration circuit of the heat pump apparatus is performed, and also the first refrigeration circuit is operated;
    • FIG. 4 is a refrigerant circuit diagram when, in the embodiment 1 of the present invention, the heating operation and cooling operation of the second refrigeration circuit of the heat pump apparatus are simultaneously performed, and also the first refrigeration circuit is operated;
    • FIG. 5 is a refrigerant circuit diagram when, in the embodiment 1 of the present invention, an indoor heat exchanger of the second refrigeration circuit of the heat pump apparatus is changed to simultaneously perform the heating operation and cooling operation, and the first refrigeration circuit is operated;
    • FIG. 6 is a flowchart showing control operation in the embodiment 1 of the present invention; and
    • FIG. 7 is a refrigerant circuit diagram of a conventional heat pump apparatus.
    DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
  • The heat pump apparatus according to the invention includes : a first refrigeration circuit in which a compressor, a condenser, first diaphragm means, and an evaporator are connected by a pipe, and which circulates a first refrigerant therethrough; a second refrigeration circuit which circulated a second refrigerant therethrough and performs heat exchange with the first refrigeration circuit in the evaporator; second diaphragm means and third diaphragm means which are respectively arranged at an inlet and an outlet of the evaporator of the second refrigeration circuit; and a control section which controls the opening degrees of the second diaphragm means and the third diaphragm means, wherein the control section has a first refrigeration circuit discharge temperature suppression mode which reduces the opening degree of the second diaphragm means so that the pressure of the second refrigerant in the evaporator is not more than a predetermined value.
  • Thereby, the high pressure-side pressure of the second refrigerant in the evaporator is reduced, and thereby, the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator is reduced, so that the degree of superheat of the first refrigerant at the outlet of the evaporator is reduced. Therefore, the discharge temperature of the compressor can be reduced.
  • Further, the high pressure-side pressure of the second refrigerant in the evaporator can be adjusted to a desired value.
  • Therefore, even when the condensation temperature of the second refrigeration circuit is high and thereby a heating load is high, or when cooling operation is performed at a high outside air temperature, the discharge temperature of the compressor can be reduced, and thereby, the reliability of the compressor can be improved.
  • Further, even when, in the second refrigeration circuit, a heat exchanger, for example, an air conditioning indoor unit, which is installed in the circuit in parallel with the evaporator, performs high-temperature-air heating operation which requires a high condensation temperature, the operation in the first refrigeration circuit can be performed simultaneously with the operation in the second refrigeration circuit.
  • According to the heat pump apparatus of the invention, the first refrigeration circuit discharge temperature suppression mode further includes control of the opening and closing of the third diaphragm means on the basis of the supercooling degree of the second refrigerant at the outlet of the evaporator.
  • Thereby, the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator can be reduced, and thereby, the degree of superheat of the first refrigerant at the outlet of the evaporator can be reduced.
  • In the following, an embodiment according to the present invention will be described with reference to the accompanying drawings. It should be noted that the present invention is not limited by the embodiment.
    • (Embodiment 1)
  • FIG. 1 is a refrigerant circuit diagram of a heat pump apparatus in a first embodiment of the present invention 1. In FIG. 1, the heat pump apparatus includes two refrigeration circuits of a first refrigeration circuit 5 and a second refrigeration circuit 20.
  • The first refrigeration circuit 5 is configured by connecting in series a compressor 1, a condenser 2, first diaphragm means 3, and an evaporator 4 by a refrigerant pipe 40. A first refrigerant is circulated in the first refrigeration circuit 5.
  • Further, compressor discharge temperature detection means 6, which detects the temperature of the first refrigerant discharged from the compressor 1, is arranged at the discharge side of the compressor 1. Further, compressor suction temperature detection means 31, which detects the temperature of the first refrigerant sucked into the compressor 1, is arranged at the suction side of the compressor 1. Further, compressor suction pressure detection means 32, which detects the pressure of the first refrigerant sucked into the compressor 1, is arranged at the suction side of the compressor 1. Further, second refrigeration circuit evaporator intermediate temperature detection means 30, which detects intermediate temperature of the evaporator 4 in the second refrigeration circuit 20, is arranged in the evaporator 4.
  • On the other hand, the second refrigeration circuit 20 is configured by connecting, by a second refrigerant pipe 41, a second compressor 11, an outdoor heat exchanger 15 which performs heat exchange with outdoor air, two indoor heat exchangers 12a and 12b which perform heat exchange with indoor air, and the evaporator 4.
  • The indoor heat exchangers 12a and 12b are provided in parallel with each other. A discharge refrigerant pipe 42, which is connected to the discharge side of the second compressor 11, is connected in a branching manner at one inlet side of each of the indoor heat exchangers 12a and 12b. A suction refrigerant pipe 43, which is connected to the suction side of the second compressor 11, is connected in a branching manner at the one inlet side of each of the indoor heat exchangers 12a and 12b. Indoor heat exchanger opening/closing means 13b and 13d are connected to the discharge refrigerant pipe 42, and indoor heat exchanger opening/closing means 13a and 13c are connected to the suction refrigerant pipe 43. Further, indoor heat exchanger diaphragm means 14a and 14b are respectively provided at the other inlet sides of the indoor heat exchangers 12a and 12b.
  • Further, the evaporator 4 is connected in parallel with each of the indoor heat exchangers 12a and 12b. The inlet side of the evaporator 4 is connected to the discharge refrigerant pipe 42, and the outlet side of the evaporator 4 is connected to the second refrigerant pipe 41. Second diaphragm means 18 is provided at the inlet side of the evaporator 4, and third diaphragm means 19 is provided at the outlet side of the evaporator 4.
  • The suction refrigerant pipe 43, which is connected at the suction side of the compressor 11, is connected at one of two branches at the one inlet side of each of the indoor heat exchangers 12a and 12b. The discharge refrigerant pipe 42, which is connected at the discharge side of the second compressor 11, is connected at the other of the two branches at the one inlet side of each of the indoor heat exchangers 12a and 12b. Each of outdoor heat exchanger opening/closing means 16a and 16b is provided between the outdoor heat exchanger 15 and the second compressors 11.
  • Outdoor heat exchanger diaphragm means 17 is provided at the other inlet side of the outdoor heat exchanger 15. The second refrigerant is circulated in the second refrigeration circuit 20 configured in this way.
  • Further, as the first refrigerant and the second refrigerant, a natural refrigerant, such as carbon dioxide (CO2), is used in addition to a fluorocarbon-based refrigerant, such as R22, R410A, R407C, R32 and R134a, and especially, each of R407C, R134a and carbon dioxide (CO2), which are widely used in high temperature applications, is desirable as the first refrigerant.
  • Further, second compressor discharge pressure detection means 21, which detects the pressure of the second refrigerant discharged from the second compressor 11, is provided at the discharge side of the second compressor 11. Also, second compressor suction pressure detection means 22, which detects the pressure of the second refrigerant sucked into the second compressor 11, is provided at the suction side of the second compressor 11.
  • Indoor heat exchanger first temperature detection means 23a, which detects the temperature of the second refrigerant, is provided between the indoor heat exchanger 12a and the indoor heat exchanger opening/closing means 13a and 13b. Also, indoor heat exchanger first temperature detection means 23b, which detects the temperature of the second refrigerant, is provided between the indoor heat exchanger 12b and the indoor heat exchanger opening/closing means 13c and 13d. Further, indoor heat exchanger second temperature detection means 24a, which detect the temperature of the second refrigerant, is provided between the indoor heat exchanger 12a and the indoor heat exchanger diaphragm means 14a. Also, indoor heat exchanger second temperature detection means 24b, which detect the temperature of the second refrigerant, is provided between the indoor heat exchanger 12b and the indoor heat exchanger diaphragm means 14b.
  • Further, outdoor heat exchanger first temperature detection means 25, which detects the temperature of the second refrigerant, is provided between the outdoor heat exchanger 15 and each of the outdoor heat exchanger opening/closing means 16a and 16b. Also, outdoor heat exchanger second temperature detection means 26, which detects the temperature of the second refrigerant, is provided between the outdoor heat exchanger 15 and the outdoor heat exchanger diaphragm means 17.
  • Further, second refrigeration circuit evaporator inlet pressure detection means 27, which detects the pressure of the second refrigerant flowing into the evaporator 4, is provided between the second diaphragm means 18 and the evaporators 4. Also, second refrigeration circuit evaporator outlet temperature detection means 28, which detects the temperature of the second refrigerant flowing out from the evaporator 4, is provided between the evaporator 4 and the third diaphragm means 19.
  • Further, the heat pump apparatus of the present embodiment includes a control section 29 as control means for controlling the first refrigeration circuit 5 and the second refrigeration circuit 20. The control section 29 centrally controls respective portions of the heat pump apparatus, and includes: a CPU; a ROM storing, in a non-volatile manner, an executable basic control program, data relating to the basic control program, and the like; a RAM temporarily storing a program executed by the CPU, predetermined data, and the like; and other peripheral circuits, and the like.
  • The control section 29 is configured to perform, in the first refrigeration circuit 5, drive control of the compressor 1, and control of the degree of opening of the first diaphragm means 3, on the basis of the detection results of the compressor discharge temperature detection means 6, the compressor suction temperature detection means 31, and the compressor suction pressure detection means 32.
  • Further, the control section 29 is configured to perform, in the second refrigeration circuit 20, drive control of the second compressor 11, and control of the degree of opening of each of the second diaphragm means 18, the third diaphragm means 19, the indoor heat exchanger diaphragm means 14a and 14b, and the outdoor heat exchanger diaphragm means 17, on the basis of the detection results of the second compressor discharge pressure detection means 21, and the second compressor suction pressure detection means 22, and on the basis of the detection results of the indoor heat exchanger first temperature detection means 23a and 23b, the indoor heat exchanger second temperature detection means 24a and 24b, the outdoor heat exchanger first temperature detection means 25, the outdoor heat exchanger second temperature detection means 26, the second refrigeration circuit evaporator inlet pressure detection means 27, and the second refrigeration circuit evaporator outlet temperature detection means 28.
  • Further, in the present embodiment, the control, which is performed by the control section 29, is provided with the first refrigeration circuit discharge temperature suppression mode which reduces the degree of opening of the second diaphragm means 18 so that the pressure of the second refrigerant in the evaporator 4 is not more than a predetermined value.
  • The first refrigeration circuit discharge temperature suppression mode is controlled on the basis of the pressure Peva_r 2 of the second refrigerant, which is detected by the second refrigeration circuit evaporator inlet pressure detection means 27.
  • For example, the control section 29 determines whether or not the pressure Peva_r 2 of the second refrigerant is more than a predetermined value (for example, 3.0 MPa). When the pressure Peva_r 2 of the second refrigerant is more than the predetermined value, the control section 29 performs control to reduce the degree of opening of the second diaphragm means 18. The control section 29 determines whether or not the pressure Peva_r 2 of the second refrigerant is within a range of a predetermined value (for example, the range not less than 2.6 MPa and not more than 3.0 MPa). When the pressure Peva_r 2 of the second refrigerant is within the range of the predetermined value, the control section 29 performs control to maintain the degree of opening of the second diaphragm means 18. Further, the control section 29 determines whether or not the Pressure Peva_r 2 of the second refrigerant is less than a predetermined value (for example, 2.6 MPa). When the Pressure Peva_r 2 of the second refrigerant is less than the predetermined value, the control section 29 performs control to increase the degree of opening of the second diaphragm means 18.
  • By performing control in this way, the control section 29 can reduce the high pressure-side pressure of the second refrigerant in the evaporator 4.
  • Further, the control section 29 controls the first refrigeration circuit discharge temperature suppression mode, on the basis of the supercooling degree SCeva_o_r 2 of the second refrigerant at the outlet of the evaporator 4 of the second refrigeration circuit 20.
  • The supercooling degree SCeva_o_r 2 of the second refrigerant can be obtained from the difference between the condensation temperature calculated on the basis of the pressure Peva_r 2 of the second refrigerant, and the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28 (that is, the condensation temperature calculated on the basis of the pressure Peva_r 2 of the second refrigerant minus the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28).
  • The control section 29 determines whether or not the supercooling degree SCeva_o_r 2 of the second refrigerant is within a range of a predetermined value (for example, 3K ≤ SCeva_o_r 2 ≤ 7K). When the supercooling degree SCeva_o_r 2 of the second refrigerant is within the predetermined value, the control section 29 performs control to maintain the degree of opening of the third diaphragm means 19. Further, the control section 29 determines whether or not the supercooling degree SCeva_o_r 2 of the second refrigerant is more than a predetermined value (for example, 7 K). When the supercooling degree SCeva_o_r 2 of the second refrigerant is more than the predetermined value, the control section 29 performs control to increase the degree of opening of the third diaphragm means 19.
  • Further, the control section 29 determines whether or not the supercooling degree SCeva_o_r 2 of the second refrigerant is less than a predetermined value (for example, 3 K). When the supercooling degree SCeva_o_r 2 of the second refrigerant is less than the predetermined value, the control section 29 performs control to reduce the degree of opening of the third diaphragm means 19.
  • By performing control in this way, the control section 29 can reduce the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator 4, and can reduce the degree of superheat of the first refrigerant at the outlet of the evaporator 4.
  • In the following, the operation and effect of the heat pump apparatus, configure described above, will be described.
    FIG. 2 is a circuit diagram showing an example when the heating operation of the second refrigeration circuit 20 is performed by using the indoor heat exchangers 12a and 12b are used as condensers, and when the first refrigeration circuit 5 is also operated. It should be noted that each of the blackened opening/closing means in FIG. 2 indicates that it is closed.
  • As shown in FIG. 2, through the indoor heat exchanger opening/closing means 13b and 13d which are opened, the second refrigerant, which is discharged from the second compressor 11, flows into the indoor heat exchangers 12a and 12b and dissipates heat to the indoor air.
  • Further, in the first refrigeration circuit 5, the first refrigerant, which is discharged from the compressor 1, discharges heat into the condenser 2. The first refrigerant, which is limited by the first diaphragm means 3 on the basis of the temperature detected by the compressor discharge temperature detection means 6, is made to flow into the evaporator 4, and absorbs heat from the second refrigerant, the pressure of which is adjusted by the second diaphragm means 18 on the basis of the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27. Then, the first refrigerant is sucked into the compressor 1.
  • Further, the second refrigerant, the heat of which is absorbed by the first refrigerant in the evaporator 4, is limited by the third diaphragm means 19 on the basis of the supercooling degree obtained from the difference between the condensation temperature calculated from the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27, and the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28. On the other hand, the second refrigerant flowing out from each of the indoor heat exchangers 12a and 12b is limited by each of the indoor heat exchanger diaphragm means 14a and 14b, on the basis of the supercooling degrees obtained from the difference between the condensation temperature calculated from the pressure detected by the second compressor discharge pressure detection means 21, and each of the temperatures detected by the indoor heat exchanger second temperature detection means 24a and 24b.
  • The second refrigerant limited by the third diaphragm means 19, and the second refrigerant limited the indoor heat exchanger diaphragm means 14a and 14b, are mixed with each other, and then absorb heat from the outdoor air in the outdoor heat exchanger 15.
  • The outdoor heat exchanger diaphragm means 17 adjusts the second refrigerant flowing through the outdoor heat exchanger 15, on the basis of the degree of superheat obtained from the difference between the evaporation temperature calculated from the pressure detected by the second compressor suction pressure detection means 22, and the temperature detected by the outdoor heat exchanger first temperature detection means 25.
  • Then, the second refrigerant flowing out from the outdoor heat exchanger 15 is sucked into the second compressor 11 through the outdoor heat exchanger opening/closing means 16a which is opened. In this case, the indoor heat exchanger opening/closing means 13a and 13c and the outdoor heat exchanger opening/closing means 16b are closed, and hence the second refrigerant does not flow through each of the opening/closing means.
  • FIG. 3 is a circuit diagram showing an example when the cooling operation of the second refrigeration circuit 20 is performed by using the indoor heat exchangers 12a and 12b as evaporators, and when the first refrigeration circuit 5 is also operated. It should be noted that each of the blackened opening/closing means in FIG. 3 indicates that it is closed.
  • As shown in FIG. 3, through the outdoor heat exchanger opening/closing means 16b which is opened, the second refrigerant discharged from the second compressor 11 flows into the outdoor heat exchanger 15 and dissipates heat to the indoor air. Further, in the first refrigeration circuit 5, similar to the case of heating operation in the second refrigeration circuit 20, the first refrigerant discharged from the compressor 1 discharges heat in the condenser 2. Then, the first refrigerant, which is limited by the first diaphragm means 3 on the basis of the temperature detected by the compressor discharge temperature detection means 6, flows into the evaporator 4. In the evaporator 4, the first refrigerant absorbs heat from the second refrigerant, the pressure of which is adjusted by the second diaphragm means 18 on the basis of the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27, and is sucked into the compressor 1.
  • Further, the second refrigerant, the heat of which is absorbed by the first refrigerant in the evaporator 4, is limited by the third diaphragm means 19, on the basis of the supercooling degree obtained from the difference between the condensation temperature calculated from the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27, and the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28.
  • On the other hand, the second refrigerant flowing out from the outdoor heat exchanger 15 is limited by the outdoor heat exchanger diaphragm means 17, on the basis of the supercooling degree obtained from the difference between the condensation temperature calculated from the pressure detected by the second compressor discharge pressure detection means 21, and the temperature detected by the outdoor heat exchanger second temperature detection means 26.
  • The second refrigerant limited by the third diaphragm means 19 and the second refrigerant limited by the outdoor heat exchanger diaphragm means 17 are mixed with each other and absorb heat from the indoor air in the indoor heat exchangers 12a and 12b. The second refrigerant flowing through each of the indoor heat exchangers 12a and 12b is adjusted by each of the indoor heat exchanger diaphragm means 14a and 14b, on the basis of the degree of superheat which is obtained from the difference between the evaporation temperature calculated from the pressure detected by the second compressor suction pressure detection means 22, and the temperature detected by each of the indoor heat exchanger first temperature detection means 23a and 23b.
  • Further, the second refrigerant flowing out from the indoor heat exchangers 12a and 12b is sucked into the second compressor 11 through the indoor heat exchanger opening/closing means 13a and 13c which are opened. In this case, the indoor heat exchanger opening/closing means 13b and 13d and the outdoor heat exchanger opening/closing means 16a are closed, and hence the second refrigerant is not made to flow through the indoor and outdoor heat exchanger opening/closing means.
  • FIG. 4 is a circuit diagram showing an example in the case where the indoor heat exchanger 12a and the indoor heat exchanger 12b are respectively used as a condenser and an evaporator, and where cooling operation and heating operation are performed at the same time in the second refrigeration circuit 20, and also the first refrigeration circuit 5 is operated. It should be noted that each of the blackened opening/closing means in FIG. 4 indicates that it is closed.
  • As shown in FIG. 4, the second refrigerant discharged from the second compressor 11 flows into the indoor heat exchanger 12a through the indoor heat exchanger opening/closing means 13b in an opened state, and discharges heat to the indoor air. Further, in the first refrigeration circuit 5, the first refrigerant discharged from the compressor 1 discharges heat in the condenser 2. Then, the first refrigeration is limited by the first diaphragm means 3 on the basis of the temperature detected by the compressor discharge temperature detection means 6, and flows into the evaporator 4. In the evaporator 4, the first refrigeration absorbs heat from the second refrigerant, the pressure of which is adjusted by the second diaphragm means 18 on the basis of the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27, and is sucked into the compressor 1.
  • Further, in the evaporator 4, the second refrigerant, the heat of which is absorbed by the first refrigerant, is limited by the third diaphragm means 19 on the basis of the supercooling degree obtained from the difference between the condensation temperature calculated from the pressure detected by the second refrigeration circuit evaporator inlet pressure detection means 27, and the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28.
  • On the other hand, the second refrigerant flowing out from the indoor heat exchanger 12a is limited by the indoor heat exchanger diaphragm means 14a on the basis of the supercooling degree obtained from the difference between the condensation temperature calculated from the pressure detected by the second compressor discharge pressure detection means 21, and the temperature detected by the indoor heat exchanger second temperature detection means 24a.
  • The second refrigerant limited by the third diaphragm means 19, and the second refrigerant limited by the indoor heat exchanger diaphragm means 14a are mixed with each other, to absorb heat from indoor air in the indoor heat exchanger 12b and from outdoor air in the outdoor heat exchanger 15.
  • Each of the indoor heat exchanger diaphragm means 14b and the outdoor heat exchanger diaphragm means 17 adjusts the second refrigerant flowing into each of the indoor heat exchanger 12b and the outdoor heat exchanger 15, on the basis of the degree of superheat obtained from the difference between the evaporation temperature calculated from the pressure detected by the second compressor suction pressure detection means 22, and the temperature detected by each of the indoor heat exchanger first temperature detection means 23b and the outdoor heat exchanger first temperature detection means 25.
  • Further, the second refrigerant, which flows out from each of the indoor heat exchanger 12b and the outdoor heat exchanger 15, is sucked into the second compressor 11 through each of the indoor heat exchanger opening/closing means 13c and the outdoor heat exchanger opening/closing means 16a which are opened. In this case, the indoor heat exchanger opening/closing means 13a and 13d, and the outdoor heat exchanger opening/closing means 16b are closed, and hence, the second refrigerant does not flow through each of the indoor and outdoor heat exchanger opening/closing means.
  • FIG. 5 is a circuit diagram showing an example in the case where cooling operation and heating operation are performed at the same time in the second refrigeration circuit 20 by respectively using the indoor heat exchanger 12a and the indoor heat exchanger 12b as an evaporator and a condenser, and where the first refrigeration circuit 5 is also operated. It should be noted that each of the blackened opening/closing means in FIG. 5 indicates that it is closed.
  • As shown in FIG. 5, in the state where the indoor heat exchanger opening/closing means 13a and 13d are opened, and where the indoor heat exchanger opening/closing means 13b and 13c are closed, the operation is performed without changing the opening and closing states of the outdoor heat exchanger opening/closing means 16a and 16b.
  • In the operation state described above, when, in the heating operation, the second refrigeration circuit 20 requires a large amount of heat to be discharged to indoor air (for example, the indoor temperature is 5°C, and the set temperature is 30°C), or when, in the cooling operation, the temperature of outdoor air is highly (for example, 40°C) so that the temperature of the second refrigerant flowing into the outdoor heat exchanger 15 needs to be not less than the temperature of outdoor air, the high pressure-side pressure of the second refrigeration circuit 20 becomes high.
  • Therefore, since the pressure of the second refrigerant flowing into the evaporator 4 also becomes high, the condensation temperature becomes high (for example, 50°C), and hence, the evaporation temperature of the first refrigeration circuit 5 also becomes high. At this time, in the case where the enthalpy difference, which is equivalent to that when the evaporation temperature is low, is secured, the degree of superheat of the first refrigerant flowing out from the evaporator 4 becomes larger.
  • In such case, in the present embodiment, the control section 29 performs control by the first refrigeration circuit discharge temperature suppression mode.
  • FIG. 6 is a flowchart showing the operation by the first refrigeration circuit discharge temperature suppression mode.
  • As shown in FIG. 6, when starting the operation, the control section 29 determines whether or not the pressure Peva_r 2 of the second refrigerant, which is detected by the second refrigeration circuit evaporator inlet pressure detection means 27, is more than 3.0 MPa (ST1). Then, when determining that the pressure Peva_r 2 of the second refrigerant is more than 3.0 MPa (ST1: YES), the control section 29 reduces the opening degree of the second diaphragm means 18 (ST2).
  • Next, the control section 29 determines whether or not the supercooling degree SCeva_o_r 2 of the second refrigerant at the outlet of the evaporator 4 of the second refrigeration circuit 20 is in the range of 3 K ≤ SCeva_o_r 2 ≤ 7K (ST3). Then, when determining that the supercooling degree SCeva_o_r 2 of the second refrigerant is in the predetermined range (ST3: YES), the control section 29 performs control to maintain the opening degree of the third diaphragm means 19 (ST4).
  • Further, when the supercooling degree SCeva_o_r 2 of the second refrigerant is not in the predetermined range (ST3: NO), and when the supercooling degree SCeva_o_r 2 of the second refrigerant is larger than 7 K (ST5: YES), the control section 29 performs control to increase the opening degree of the third diaphragm means 19 (ST6). On the contrary, when the supercooling degree SCeva_o_r 2 of the second refrigerant is less than 3 K (ST5: NO), the control section 29 performs control to reduce the opening degree of the third diaphragm means 19 (ST7).
  • On the other hand, when the control section 29 determines that the pressure Peva_r 2 of the second refrigerant is not more than 3.0 MPa, then in order to prevent the pressure Peva_r 2 of the second refrigerant from being excessively reduced, the control section 29 determines whether or not the pressure Peva_r 2 of the second refrigerant is more than 2.6 MPa which is the lower limit value of the pressure Peva_r2 of the second refrigerant (ST8).
  • Then, when the pressure Peva_r 2 of the second refrigerant is more than 2.6 MPa as the lower limit value (ST8: YES), the control section 29 performs control to maintain the opening degree of the second diaphragm means 18 (ST9). On the contrary, when the pressure Peva_r 2 of the second refrigerant is less than 2.6 MPa as the lower limit value (ST8: NO), the control section 29 performs control to increase the opening degree of the second diaphragm means 18 (ST10).
  • Then, after performing the control of the second diaphragm means 18, the control section 29 performs control of the third diaphragm means 19 on the basis of the flow of ST3 to ST7.
  • When the above-described control is performed, it is possible that the high pressure-side pressure of the second refrigerant in the evaporator 4 is reduced, that the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator 4 is reduced, and that the degree of superheat of the first refrigerant at the outlet of the evaporator 4 is reduced. Thereby, the discharge temperature of the compressor 1 can also be reduced.
  • As described above, in the present embodiment, the control section 29 is provided with the first refrigeration circuit discharge temperature suppression mode which reduces the opening degree of the second diaphragm means 18 for preventing the pressure of the second refrigerant in the evaporator 4 from being more than the predetermined value. Thereby, the high pressure-side pressure of the second refrigerant in the evaporator 4 can be reduced, and the amount of heat exchange between the first refrigerant and the second refrigerant in the evaporator 4 can be reduced. Further, the degree of superheat of the first refrigerant at the outlet of the evaporator 4 can be reduced, and the discharge temperature of the compressor 1 can be reduced.
  • Thereby, even when the condensation temperature of the second refrigeration circuit 20 is high, and thereby the heating load is high, or even when cooling operation is performed under the condition of high outdoor-air temperature, the discharge temperature of the compressor 1 can be reduced, and thereby, the reliability of the compressor 1 can be improved.
  • Further, regardless of the condensation temperature of the second refrigeration circuit 20, the pressures of the second refrigerant in the evaporator 4 can be individually controlled. For example, the high-temperature-air heating operation in which high condensation temperature is required at indoor heat exchangers 12a and 12b, and the operation in the first refrigeration circuit 5 can be simultaneously performed.
  • It should be noted that, in the present embodiment, the opening degree of the second diaphragm means 18 is adjusted on the basis of the pressure obtained by detecting the pressure of the second refrigerant in the evaporator 4 by the second refrigeration circuit evaporator inlet pressure detection means 27. However, as shown in FIG. 1, the opening degree of the second diaphragm means 18 can also be adjusted on the basis of the temperature detected by the second refrigeration circuit evaporator intermediate temperature detection means 30, the temperature detected by the compressor suction temperature detection means 31, or the pressure detected by the compressor suction pressure detection means 32.
  • Further, in the present embodiment, the opening degree of the third diaphragm means 19 is adjusted on the basis of the supercooling degree SCeva_o_r 2. However, it is also possible to perform control such that the opening degree of the third diaphragm means 19 is adjusted on the basis of the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means 28, so that the suction temperature of the compressor 1 does not exceed the upper limit.
  • As described above, the heat pump apparatus according to the present invention is configured to suppress the increase of the compressor discharge temperature of the high-stage-side refrigeration circuit in the binary refrigeration cycle, and can be applied to applications, such as an air conditioner, a chiller, a drier, a hot water supply air conditioning composite apparatus, a hot water heater, and the like.
    • REFERENCE SIGNS LIST
    • 1
    Compressor
    2
    Condenser
    3
    First diaphragm means
    4
    Evaporator
    5
    First refrigeration circuit
    18
    Second diaphragm means
    19
    Third diaphragm means
    20
    Second refrigeration circuit
    29
    Control section

Claims (1)

  1. A heat pump apparatus comprising:
    a first refrigeration circuit (5) comprising a compressor (1), a condenser (2), first diaphragm means (3), and an evaporator (4), connected by a pipe to allow a first refrigerant to circulate there through;
    a second refrigeration circuit (20) comprising a second compressor (11), an outdoor heat exchanger (15) that performs heat exchange with outdoor air, two indoor heat exchangers (12a, 12b) that perform heat exchange with indoor air, and the evaporator (4), connected by a second refrigerant pipe (41) to allow a second refrigerant to circulate there through and to perform heat exchange with the first refrigeration circuit (5) in the evaporator (4);
    second diaphragm means (18) and third diaphragm means (19) which are respectively arranged at an inlet and an outlet of the evaporator (4) of the second refrigeration circuit (20); and
    a control section (29) which is configured to control the degree of opening of each of the second diaphragm means (18) and the third diaphragm means (19),
    characterized in that the second refrigeration circuit comprises a second refrigeration circuit evaporator inlet pressure detection means and a second refrigeration circuit evaporator outlet temperature detection means,
    the control section (19) has a first refrigeration circuit discharge temperature suppression mode,
    in the first refrigeration circuit temperature suppression mode,
    the control section (29) is configured to perform control to reduce the degree of opening of the second diaphragm means (18) when the pressure of the second refrigerant in the evaporator (4) is more than a first predetermined pressure value or control to maintain the degree of opening of the second diaphragm means (18) when the pressure of the second refrigerant is within a range of predetermined pressure value or control to increase the degree of opening of the second diaphragm means (18) when the pressure of the second refrigerant is less than a second predetermined pressure value, the pressure of the second refrigerant being detected by the
    second refrigeration circuit evaporator inlet pressure detection means (27), and
    in that the control section (29) is configured to perform control to maintain the degree of opening of the third diaphragm means (19) when the supercooling degree of the second refrigerant at the outlet of the evaporator (4) is within a range of predetermined supercooling degree value or control to increase the degree of opening of the third diaphragm means (19) when the supercooling degree of the second refrigerant is more than a first predetermined supercooling degree value or control to reduce the degree of opening of the third diaphragm means (19) when the supercooling degree of the second refrigerant is less than a second predetermined supercooling degree value, the supercooling degree of the second refrigerant being obtained from the difference between the condensation temperature calculated on the basis of the pressure of the second refrigerant, and the temperature detected by the second refrigeration circuit evaporator outlet temperature detection means (28).
EP16186105.9A 2016-03-07 2016-08-29 Heat pump apparatus Active EP3217118B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2016042968A JP2017161085A (en) 2016-03-07 2016-03-07 Heat pump device

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EP3217118A1 EP3217118A1 (en) 2017-09-13
EP3217118B1 true EP3217118B1 (en) 2022-10-05

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EP (1) EP3217118B1 (en)
JP (1) JP2017161085A (en)
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Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4116645B2 (en) * 2006-01-30 2008-07-09 三菱電機株式会社 Heat pump water heater
JP4592617B2 (en) * 2006-02-27 2010-12-01 三洋電機株式会社 Cooling and heating device
EP2184563A4 (en) 2008-02-04 2016-02-17 Mitsubishi Electric Corp Air-conditioning and water-heating complex system
ES2877210T3 (en) * 2010-04-05 2021-11-16 Mitsubishi Electric Corp Composite air conditioning and hot water supply system
KR101203579B1 (en) * 2010-11-05 2012-11-21 엘지전자 주식회사 Speed heating apparatus with air conditioner and Control process of the same
JP2013104606A (en) * 2011-11-14 2013-05-30 Panasonic Corp Refrigeration cycle apparatus and hot water producing apparatus
JP5791785B2 (en) * 2012-03-27 2015-10-07 三菱電機株式会社 Air conditioner
IN2014DN08932A (en) * 2012-04-25 2015-05-22 Hitachi Ltd
JP5893151B2 (en) * 2012-09-25 2016-03-23 三菱電機株式会社 Air conditioning and hot water supply complex system

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EP3217118A1 (en) 2017-09-13
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