EP3736514A1 - Dispositif à cycle de réfrigération et dispositif de chauffage de liquide le comprenant - Google Patents

Dispositif à cycle de réfrigération et dispositif de chauffage de liquide le comprenant Download PDF

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Publication number
EP3736514A1
EP3736514A1 EP20156001.8A EP20156001A EP3736514A1 EP 3736514 A1 EP3736514 A1 EP 3736514A1 EP 20156001 A EP20156001 A EP 20156001A EP 3736514 A1 EP3736514 A1 EP 3736514A1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
side heat
usage
operation mode
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP20156001.8A
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German (de)
English (en)
Inventor
Naoki Yoshida
Yuki YAMAOKA
Tsuneko Imagawa
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Publication of EP3736514A1 publication Critical patent/EP3736514A1/fr
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the 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
    • 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
    • F25B2313/027—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
    • 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
    • F25B2400/13—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
    • F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
    • 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
    • F25B2600/23—Time delays
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge 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
    • F25B2700/193—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
    • F25B2700/21—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
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet

Definitions

  • the present invention relates to a refrigeration cycle device and a liquid heating device having the same.
  • a refrigeration cycle device of this kind there is conventionally disclosed a refrigeration cycle device having a two-stage compression mechanism in which a portion of refrigerant is expanded from a downstream side of a usage-side heat exchanger, and intermediate refrigerant is bypassed to a middle stage location of compression of the two-stage compression mechanism (see patent document 1 for example).
  • Fig. 4 shows the conventional refrigeration cycle device described in patent document 1.
  • the refrigeration cycle device 100 includes a refrigerant circuit 110 through which refrigerant is circulated, and a rear stage-side injection pipe 120.
  • a compression mechanism 111 having a plurality of compression rotation elements which are connected to one another in series, a heat source-side heat exchanger 112, expansion mechanisms 113a and 113b and a usage-side heat exchanger 114 are annularly connected to the refrigerant circuit 110 through a pipe.
  • the refrigerant circuit 110 includes a switching mechanism 115 for switching over between a heating operation and a cooling operation.
  • the refrigeration cycle device 100 is provided with an intermediate refrigerant pipe 116 for allowing refrigerant discharged from a front stage-side compression rotation element to be sucked into a rear stage-side compression rotation element.
  • the intermediate refrigerant pipe 116 is provided with an intermediate cooler 117 which functions as a cooler of refrigerant discharged from the front stage-side compression rotation element and sucked into the rear stage-side compression rotation element.
  • the intermediate refrigerant pipe 116 is provided with an intermediate cooler bypass pipe 130.
  • the intermediate cooler bypass pipe 130 is connected such that refrigerant discharged from the front stage-side compression rotation element bypasses the intermediate cooler 117.
  • the rear stage-side injection pipe 120 is connected such that refrigerant which branches off from the refrigerant circuit 110 between the heat source-side heat exchanger 112 and the usage-side heat exchanger 114 returns to the rear stage-side compression rotation element of the compression mechanism 111.
  • the injection pipe 120 is provided with a rear stage-side injection valve 121 whose opening degree can be controlled.
  • the refrigeration cycle device 100 carries out a reverse cycle defrosting operation for defrosting the heat source-side heat exchanger 112 by switching the switching mechanism 115 into the cooling operation.
  • refrigerant is made to flow into the heat source-side heat exchanger 112, the intermediate cooler 117 and the rear stage-side injection pipe 120. If it is detected that the defrosting operation of the intermediate cooler 117 is completed during the reverse cycle defrosting operation, control is performed such that refrigerant does not flow into the intermediate cooler 117 using the intermediate cooler bypass pipe 130, and control is performed such that the opening degree of the rear stage-side injection valve 121 is increased.
  • Patent Document1 Japanese Patent Application Laid-open No. 2009-133581
  • the present invention has been accomplished to solve the above-described conventional problem, and it is an object of the invention to provide a refrigeration cycle device and a liquid heating device having the same capable of suppressing deterioration of the heating ability in the usage-side heat exchanger also when the heating operation in the usage-side heat exchanger is executed after the defrosting operation of the heat source-side heat exchanger is completed.
  • the present invention provides a refrigeration cycle device including: a main refrigerant circuit formed by sequentially connecting, to one another through a pipe, a compression mechanism composed of compression rotation elements, a usage-side heat exchanger for heating usage-side heat medium by refrigerant discharged from the compression rotation element, an intermediate heat exchanger, a first expansion device and a heat source-side heat exchanger; a bypass refrigerant circuit which exchanges heat with refrigerant flowing through the main refrigerant circuit by the intermediate heat exchanger after refrigerant branching off from the pipe between the usage-side heat exchanger and the first expansion device is decompressed by the second expansion device, the bypass refrigerant circuit joining up with refrigerant which is being compressed of the compression rotation element; a blowing device for supplying air to the heat source-side heat exchanger; and a control device, wherein the refrigeration cycle device further includes a heating operation mode for heating the usage-side heat medium in the usage-side heat exchanger by refrigerant discharged from
  • the temperature of the refrigerant discharged from the compression mechanism can be increased.
  • the control device can secure the flow rate of the refrigerant flowing through the usage-side heat exchanger while rising the temperature of the refrigerant discharged from the compression rotation element by setting the opening degree of the first expansion device and the opening degree of the second expansion device to such a value that the flow rate of the refrigerant flowing through the first expansion device becomes greater than the flow rate of the refrigerant flowing through the second expansion device at least during a predetermined period, and it is possible to suppress the deterioration of the heating ability in the usage-side heat exchanger in the heating operation mode which is executed after the defrosting operation mode is completed.
  • blowing device which supplies air to the heat source-side heat exchanger, it is possible to enhance the heat absorbing effect in the heat source-side heat exchanger, and to enhance the heating ability in the usage-side heat exchanger.
  • a refrigeration cycle device and a liquid heating device having the same capable of suppressing the deterioration of the heating ability in the usage-side heat exchanger even when the heating operation in the usage-side heat exchanger is executed after the defrosting operation of the heat source-side heat exchanger is completed.
  • a first aspect of the present invention provides a refrigeration cycle device including: a main refrigerant circuit formed by sequentially connecting, to one another through a pipe, a compression mechanism composed of compression rotation elements, a usage-side heat exchanger for heating usage-side heat medium by refrigerant discharged from the compression rotation element, an intermediate heat exchanger, a first expansion device and a heat source-side heat exchanger; a bypass refrigerant circuit which exchanges heat with refrigerant flowing through the main refrigerant circuit by the intermediate heat exchanger after refrigerant branching off from the pipe between the usage-side heat exchanger and the first expansion device is decompressed by the second expansion device, the bypass refrigerant circuit joining up with refrigerant which is being compressed of the compression rotation element; a blowing device for supplying air to the heat source-side heat exchanger; and a control device, wherein the refrigeration cycle device further includes a heating operation mode for heating the usage-side heat medium in the usage-side heat exchanger by refrigerant discharged from the compression rotation element,
  • the temperature of the refrigerant discharged from the compression mechanism can be increased.
  • the control device can secure the flow rate of the refrigerant flowing through the usage-side heat exchanger while rising the temperature of the refrigerant discharged from the compression rotation element by setting the opening degree of the first expansion device and the opening degree of the second expansion device to such a value that the flow rate of the refrigerant flowing through the first expansion device becomes greater than the flow rate of the refrigerant flowing through the second expansion device at least during a predetermined period, and it is possible to suppress the deterioration of the heating ability in the usage-side heat exchanger in the heating operation mode which is executed after the defrosting operation mode is completed.
  • blowing device which supplies air to the heat source-side heat exchanger, it is possible to enhance the heat absorbing effect in the heat source-side heat exchanger, and to enhance the heating ability in the usage-side heat exchanger.
  • the heating ability can be enhanced even in the heating operation mode after the defrosting operation mode under a high humidity outside air temperature condition having a high frosting amount is executed, and it is possible to provide a refrigeration cycle device capable of to suppress the deterioration of the heating ability of the heating operation.
  • the refrigeration cycle device further includes a high pressure side detecting section for detecting temperature of refrigerant on a high pressure side of the main refrigerant circuit or pressure of refrigerant on the high pressure side of the main refrigerant circuit, wherein the predetermined period is such a period that a detected value of the high pressure side detecting section is equal to or smaller than a predetermined value.
  • the opening degree of the first expansion device and the opening degree of the second expansion device are set to such a value that the flow rate of the refrigerant flowing through the first expansion device becomes greater than the flow rate of the refrigerant flowing through the second expansion device.
  • the predetermined period is time elapsed after the heating operation mode is started.
  • the predetermined period is set as time which is started when the heating operation mode is started and which is elapsed when the opening degree of the first expansion device and the opening degree of the second expansion device are set to such a value that the flow rate of the refrigerant flowing through the first expansion device becomes greater than the flow rate of the refrigerant flowing through the second expansion device.
  • refrigerant discharge from the compression rotation element flows through the usage-side heat exchanger, the first expansion device and the heat source-side heat exchanger in this order.
  • carbon dioxide is used as the refrigerant.
  • a sixth aspect of the invention provides a liquid heating device including the refrigeration cycle device according to any one of the first to fifth aspects, and a usage-side heat medium circuit through which the usage-side heat medium is circulated by a conveying device.
  • Fig. 1 is a block diagram of a liquid heating device in an embodiment of the present invention.
  • the liquid heating device is composed of a refrigeration cycle device 1, a usage-side heat medium circuit 5 and a control device 4 which controls an operation of the liquid heating device.
  • the refrigeration cycle device 1 is composed of a main refrigerant circuit 2 and a bypass refrigerant circuit 3.
  • the main refrigerant circuit 2 is formed by connecting, to one another through pipes 16, a compression mechanism 21, a usage-side heat exchanger 22 which is a radiator, an intermediate heat exchanger 26 which is a cooling heat exchanger, a first expansion device 23 which is a main expansion valve, and a heat source-side heat exchanger 24 which is an evaporator.
  • Carbon dioxide (CO2) is used as refrigerant.
  • a blowing device 29 supplies air to the heat source-side heat exchanger 24.
  • carbon dioxide is most suitable as the refrigerant, but it is also possible to use non-azeotropic refrigerant mixture such as R407, pseudoazeotropic refrigerant mixture such as R410A, and single refrigerant such as R32.
  • non-azeotropic refrigerant mixture such as R407
  • pseudoazeotropic refrigerant mixture such as R410A
  • single refrigerant such as R32.
  • the compression mechanism 21 which compresses refrigerant is composed of a low stage-side compression rotation element 21a and a high stage-side compression rotation element 21b.
  • the usage-side heat exchanger 22 heats the usage-side heat medium by refrigerant which is discharged from the high stage-side compression rotation element 21b.
  • a position where refrigerant from the bypass refrigerant circuit 3 joins up is defined as a middle stage location of compression of a compression rotation element
  • a compression rotation element up to the position where the refrigerant from the bypass refrigerant circuit 3 joins up is defined as the low stage-side compression rotation element 21a
  • a compression rotation element after the former position where the refrigerant from the bypass refrigerant circuit 3 joins up is defined as the high stage-side compression rotation element 21b.
  • the compression mechanism 21 may be composed of the low stage-side compression rotation element 21a and the high stage-side compression rotation element 21b each of which is composed of two compressors.
  • the bypass refrigerant circuit 3 branches off from the pipe 16 between the usage-side heat exchanger 22 and the first expansion device 23, and is connected to the pipe 16 between the low stage-side compression rotation element 21a and the high stage-side compression rotation element 21b.
  • the bypass refrigerant circuit 3 is provided with a second expansion device 31 which is a bypass expansion valve.
  • a portion of high pressure refrigerant after it passes through the usage-side heat exchanger 22 or a portion of high pressure refrigerant after it passes through the intermediate heat exchanger 26 is decompressed by the second expansion device 31 and becomes intermediate pressure refrigerant. Thereafter, the intermediate pressure refrigerant exchanges heat with high pressure refrigerant which flows through the main refrigerant circuit 2 in the intermediate heat exchanger 26, and joins up with refrigerant between the low stage-side compression rotation element 21a and the high stage-side compression rotation element 21b.
  • a heat medium returning pipe 53 and a heat medium going pipe 54 are connected to the usage-side heat exchanger 22.
  • the heat medium returning pipe 53 is provided with a conveying device 55 which is a conveying pump.
  • usage-side heat medium is supplied to the usage-side heat exchanger 22 through the heat medium returning pipe 53, usage-side heat medium heated by the usage-side heat exchanger 22 is supplied from the heat medium going pipe 54 to a hot water tank (not shown) or a heater (not shown) of a floor heating for example.
  • a room is heated or hot water is supplied. Thereafter, the usage-side heat medium again returns to the usage-side heat exchanger 22 through the heat medium returning pipe 53. Water or antifreeze liquid is used as the usage-side heat medium.
  • the pipe 16 on the high pressure side of the main refrigerant circuit 2 which connects a discharge side of the compression mechanism 21 and the first expansion device 23 to each other is provided with a high pressure side pressure sensor 52.
  • the high pressure side pressure sensor 52 detects evaporating pressure on the high pressure side as a high pressure side detecting section.
  • a discharge temperature thermistor (not shown) may be used as the high pressure side detecting section.
  • the discharge temperature thermistor is provided in the pipe 16 on the high pressure side of the main refrigerant circuit 2 which connects a discharge side of the compression mechanism 21 of the main refrigerant circuit 2 and the usage-side heat exchanger 22 to each other, and detects temperature of refrigerant which is discharged from the compression mechanism 21.
  • the pipe 16 on the low pressure side of the main refrigerant circuit 2 which connects a downstream side of the first expansion device 23 and a suction side of the compression mechanism 21 is provided with a low pressure side pressure sensor 51.
  • the low pressure side pressure sensor 51 detects low pressure side evaporating pressure as the low pressure side detecting section.
  • An evaporating temperature thermistor (not shown) may be used as the low pressure side detecting section.
  • the evaporating temperature thermistor is provided in the pipe 16 on the low pressure side of the main refrigerant circuit 2 which connects the downstream side of the first expansion device 23 and the suction side of the compression mechanism 21 to each other, and detects evaporating temperature of refrigerant which is in a low pressure side gas-liquid two-layer state.
  • a temperature thermistor 28 is provided around the heat source-side heat exchanger 24. By operating the blowing device 29, the temperature thermistor 28 detects temperature of air which supplies heat to the heat source-side heat exchanger 24.
  • the refrigeration cycle device 1 of the embodiment includes a heating operation mode which is a normal operation mode.
  • the heating operation mode operates the conveying device 55, allows the usage-side heat medium to circulate in the usage-side heat medium circuit 5, and heats the usage-side heat medium in the usage-side heat exchanger 22 by refrigerant discharged from the high stage-side compression rotation element 21b of the compression mechanism 21.
  • the refrigeration cycle device 1 also includes a defrosting operation mode for defrosting the heat source-side heat exchanger 24 by refrigerant discharged from the high stage-side compression rotation element 21b of the compression mechanism 21.
  • the defrosting operation mode when pressure detected by the low pressure side pressure sensor 51 becomes equal to or lower than a first predetermined value or temperature detected by the evaporating temperature thermistor becomes equal to or lower than a second predetermined value, or when execution time of the heating operation mode is continued for predetermined time or longer in a state where temperature of air which supplies heat to the heat source-side heat exchanger 24 detected by the temperature thermistor 28 is equal to or lower than a third predetermined value, it is determined that the heat source-side heat exchanger 24 is frosted.
  • frost which is adhered to the heat source-side heat exchanger 24 is melted and removed by heat of refrigerant discharged from the high stage-side compression rotation element 21b of the compression mechanism 21.
  • Fig. 1 solid arrows show flowing directions of refrigerant when the normal heating operation mode is executed. Variation of a state of refrigerant when the normal heating operation mode is executed will be described below.
  • High pressure refrigerant discharged from the compression mechanism 21 flows into the usage-side heat exchanger 22, and releases heat to the usage-side heat medium which passes through the usage-side heat exchanger 22.
  • High pressure refrigerant which flows out from the usage-side heat exchanger 22 is distributed to the intermediate heat exchanger 26 and the second expansion device 31.
  • High pressure refrigerant which flows into the intermediate heat exchanger 26 is cooled by the intermediate pressure refrigerant which is decompressed by the second expansion device 31.
  • the high pressure refrigerant distributed to the first expansion device 23 is decompressed and expanded by the first expansion device 23 and thereafter, the refrigerant flows into the heat source-side heat exchanger 24.
  • the low pressure refrigerant which flows into the heat source-side heat exchanger 24 exchanges heat with air supplied into the heat source-side heat exchanger 24 by the blowing device 29 and absorbs heat.
  • the high pressure refrigerant distributed to the second expansion device 31 is decompressed and expanded by the second expansion device 31 and thereafter, the refrigerant flows into the intermediate heat exchanger 26.
  • the intermediate pressure refrigerant which flows into the intermediate heat exchanger 26 is heated by high pressure refrigerant which flows out from the usage-side heat exchanger 22.
  • intermediate pressure refrigerant which flows out from the intermediate heat exchanger 26 joins up with intermediate pressure refrigerant which is discharged from the low stage-side compression rotation element 21a of the compression mechanism 21, and is sucked into the high stage-side compression rotation element 21b.
  • a portion of high pressure refrigerant bypasses through the intermediate heat exchanger 26 at the time of the heating operation, and a compressing force of the low stage-side compression rotation element 21a is reduced.
  • Density of refrigerant is increased by reduction in enthalpy of suction refrigerant of the high stage-side compression rotation element 21b of the compression mechanism 21, and this increase of density increases a flow rate of refrigerant flowing through the usage-side heat exchanger 22, and enhances heating ability or coefficient of performance.
  • the heating operation mode is executed in this manner, moisture and the like in air is frozen and frost is generated in the heat source-side heat exchanger 24, and heating ability or the coefficient of performance is deteriorated by deterioration of heat conductivity of the heat source-side heat exchanger 24.
  • a reverse cycle defrosting type defrosting operation mode As a typical defrosting operation mode, there is a reverse cycle defrosting type defrosting operation mode.
  • flow paths with which a four-way valve is in communication are switched when the heating operation mode is executed, thereby reversing a circulation direction of refrigerant. That is, high temperature and high pressure refrigerant discharged from the compression mechanism 21 is made to flow into the heat source-side heat exchanger 24, and frost of the heat source-side heat exchanger 24 is melted by condensation heat of the high temperature and high pressure refrigerant.
  • hot gas defrosting type defrosting operation mode in which a four-way valve is not switched and the same flow path as that when the heating operation mode is executed is used, and high temperature and high pressure refrigerant discharged from the compression mechanism 21 is made to flow into the usage-side heat exchanger 22.
  • a valve opening degree of the first expansion device 23 is made large, high temperature and high pressure gas refrigerant discharged from the compression mechanism 21 is made to pass through the first expansion device 23 without decompressing the gas refrigerant and thereafter, the gas refrigerant is made to flow into the heat source-side heat exchanger 24 to melt frost of the heat source-side heat exchanger 24.
  • the defrosting operation mode is executed using the hot gas defrosting type defrosting operation mode. Variation of a state of refrigerant in this case will be described below using Fig. 1 .
  • FIG. 1 show flowing directions of refrigerant when the defrosting operation mode is executed using the hot gas defrosting type defrosting operation mode.
  • High pressure refrigerant discharged from the compression mechanism 21 flows into the usage-side heat exchanger 22, the refrigerant which flows out from the usage-side heat exchanger 22 passes through the first expansion device 23 and then, the refrigerant flows into the heat source-side heat exchanger 24, releases heat to deposited frost and melts the frost. Thereafter, the refrigerant flows out from the heat source-side heat exchanger 24 and again returns to the compression mechanism 21.
  • circulation of the usage-side heat medium which flows through the usage-side heat exchanger 22 is stopped. That is, the operation of the conveying device 55 is stopped or the number of operational rotations of the conveying device 55 is reduced, and a flow rate of the usage-side heat medium flowing through the usage-side heat exchanger 22 is reduced.
  • a valve opening degree of the first expansion device 23 is increased and a decompression amount is reduced.
  • the defrosting operation mode is absolutely necessary to stably continue the heating operation mode as described above.
  • the control device 4 adjusts valve opening degrees of the first expansion device 23 and the second expansion device 31 such that a flow rate of refrigerant flowing through the first expansion device 23 becomes greater than a flow rate of refrigerant flowing through second expansion device 31.
  • enthalpy of refrigerant sucked into the high stage-side compression rotation element 21b of the compression mechanism 21 increases from a point b to a point b', and enthalpy of refrigerant discharged from the high stage-side compression rotation element 21b also increases from a point c to a point c' as shown in Fig. 2 .
  • discharge temperature rises, and a temperature difference with respect to the usage-side heat medium increases.
  • control device 4 appropriately adjusts a flow rate ratio of a flow rate of refrigerant flowing through the first expansion device 23 and a flow rate of refrigerant flowing through the second expansion device 31.
  • the heating ability rises, it is possible to immediately rise the heating ability in the heating operation mode which is executed after the defrosting operation mode is completed in a state where deterioration of coefficient of performance is suppressed.
  • control device 4 executes the defrosting operation mode to melt frost adhering to the heat source-side heat exchanger 24 and thereafter, the execution of the defrosting operation mode is completed (step S1).
  • step S2 an operating state of the blowing device 29 is detected (step S2).
  • step S3 an operating state of the blowing device 29 is detected (step S2).
  • valve opening degree of the first expansion device 23 and the valve opening degree of the second expansion device 31 are set in a state where the compression mechanism 21 is operated such that these valve opening degrees respectively become Om and Ob which are previously set in the control device 4 (step S4).
  • valve opening degree Om of the first expansion device 23 and the valve opening degree Ob of the second expansion device 31 are such opening degrees that a flow rate Gm of refrigerant flowing through the first expansion device 23 becomes greater than a flow rate Gb of refrigerant flowing through the second expansion device 31 (step S4).
  • valve opening degree of the first expansion device 23 is set substantially maximum and the valve opening degree of the second expansion device 31 is set substantially minimum, and high temperature and high pressure gas refrigerant discharged from the compression mechanism 21 is made to flow into the heat source-side heat exchanger 24.
  • control device 4 operates the valve opening degree of the first expansion device 23 into a closing direction and operates the valve opening degree of the second expansion device 31 into an opening direction or does not operate the second expansion device 31 and maintains its substantially minimum opening degree.
  • the control device 4 sets the valve opening degrees of the first expansion device 23 and the second expansion device 31 such that the flow rate of refrigerant flowing through the first expansion device 23 becomes greater than the flow rate of refrigerant flowing through the second expansion device 31.
  • control device 4 may normally operate the conveying device 55 and start the heating operation mode after the valve opening degrees of the first expansion device 23 and the second expansion device 31 are set such that the flow rate of refrigerant flowing through the first expansion device 23 becomes greater than the flow rate of refrigerant flowing through the second expansion device 31.
  • control device 4 detects high pressure side pressure Pd of the main refrigerant circuit 2 by the high pressure side pressure sensor 52 which is the high pressure side detecting section (step S5).
  • the high pressure side pressure sensor 52 detects the high pressure side pressure Pd of the main refrigerant circuit 2, i.e., detects discharge pressure of the compression mechanism 21 (discharge pressure of high stage-side compression rotation element 21b), and it is determined whether the detected value is equal to or smaller than a preset fourth predetermined value (predetermined pressure Pdt) (step S6) .
  • step S6 i.e., when the discharge pressure Pd is equal to or smaller than Pdt which is a second predetermined value, the valve opening degree of the first expansion device 23 and the valve opening degree of the second expansion device 31 are maintained as Om and Ob which are previously set in the control device 4.
  • step S6 When NO in step S6 on the other hand, i.e., when the discharge pressure Pd is higher than Pdt which is the second predetermined value, the control for making the valve opening degrees of the first expansion device 23 and the second expansion device 31 equal to Om and Ob which are previously set in the control device 4 is dissolved.
  • control is shifted to operation control of the valve opening degree of the first expansion device 23 and the valve opening degree of the second expansion device 31 in the normal heating operation mode, and the heating operation mode is continued.
  • a discharge temperature thermistor (not shown) which detects temperature of refrigerant discharged from the compression mechanism 21 may be used instead of the high pressure side pressure sensor 52.
  • the discharge temperature thermistor is provided in the pipe 16 on the high pressure side of the main refrigerant circuit 2 which connects the discharge side of the compression mechanism 21 of the main refrigerant circuit 2 and the usage-side heat exchanger 22 to each other.
  • valve opening degrees of the first expansion device 23 and the second expansion device 31 are set such that the flow rate of refrigerant flowing through the first expansion device 23 becomes greater than the flow rate of refrigerant flowing through the second expansion device 31.
  • valve opening degrees of the first expansion device 23 and the second expansion device 31 may be set such that the flow rate of refrigerant flowing through the first expansion device 23 becomes greater than the flow rate of refrigerant flowing through the second expansion device 31.
  • control is shifted to the operation control of the valve opening degrees of the first expansion device 23 and the second expansion device 31 in the normal heating operation mode, and the heating operation mode is continued.
  • valve opening degree Om of the first expansion device 23 and the valve opening degree Ob of the second expansion device 31 are previously set in the control device 4, but the flow rates may be actually detected and control may be performed such that the flow rate Gm of the main refrigerant becomes greater than the flow rate Gb of the bypass refrigerant.
  • flowmeters may be provided in a refrigerant circuit and a bypass path on the side of the first expansion device 23, or flow rates of refrigerants may be calculated from functions of a pressure difference and opening degrees of outlet and inlet ports of the expansion valves.
  • bypass refrigerant circuit 3 is branched off from the main refrigerant circuit 2 between the usage-side heat exchanger 22 and the intermediate heat exchanger 26, and the bypass refrigerant circuit 3 may be branched off from the main refrigerant circuit 2 between the intermediate heat exchanger 26 and the first expansion device 23.
  • first expansion device 23 and the second expansion device 31 in this embodiment are expansion valves, and these devices 23 and 31 may be expanders which collect power from expanding refrigerant.
  • a load may be changed by a dynamo-electric generator which is connected to the expander, and the number of rotations of the expander may be controlled.
  • the refrigeration cycle device of the present invention is composed of the main refrigerant circuit having the intermediate heat exchanger and the bypass refrigerant circuit, and the refrigeration cycle device can suppress the deterioration in the heating ability even when heating operation is executed after the defrosting operation of the heat source-side heat exchanger is completed. Therefore, the invention useful for a freezing device, an air conditioner, a hot water supplying device and a heating device using the refrigeration cycle device.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP20156001.8A 2019-05-09 2020-02-07 Dispositif à cycle de réfrigération et dispositif de chauffage de liquide le comprenant Pending EP3736514A1 (fr)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009133581A (ja) 2007-11-30 2009-06-18 Daikin Ind Ltd 冷凍装置
US20160273816A1 (en) * 2015-03-20 2016-09-22 Daikin Industries, Ltd. Refrigeration apparatus
WO2018097154A1 (fr) * 2016-11-24 2018-05-31 ダイキン工業株式会社 Dispositif de réfrigération

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2528846B2 (ja) * 1986-12-17 1996-08-28 株式会社日立製作所 空気調和機
JP2011137602A (ja) * 2009-12-28 2011-07-14 Daikin Industries Ltd ヒートポンプユニットおよび暖房システム
US10018389B2 (en) * 2011-12-22 2018-07-10 Mitsubishi Electric Corporation Air-conditioning apparatus
JP2013178046A (ja) * 2012-02-29 2013-09-09 Hitachi Appliances Inc 空気調和装置
JP2014105891A (ja) * 2012-11-26 2014-06-09 Panasonic Corp 冷凍サイクル装置及びそれを備えた温水生成装置
JP5677472B2 (ja) * 2013-01-08 2015-02-25 三菱電機株式会社 冷凍装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009133581A (ja) 2007-11-30 2009-06-18 Daikin Ind Ltd 冷凍装置
EP2230474A1 (fr) * 2007-11-30 2010-09-22 Daikin Industries, Ltd. Dispositif de refroidissement
US20160273816A1 (en) * 2015-03-20 2016-09-22 Daikin Industries, Ltd. Refrigeration apparatus
WO2018097154A1 (fr) * 2016-11-24 2018-05-31 ダイキン工業株式会社 Dispositif de réfrigération

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