WO2012104890A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2012104890A1 WO2012104890A1 PCT/JP2011/000510 JP2011000510W WO2012104890A1 WO 2012104890 A1 WO2012104890 A1 WO 2012104890A1 JP 2011000510 W JP2011000510 W JP 2011000510W WO 2012104890 A1 WO2012104890 A1 WO 2012104890A1
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- refrigerant
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- heat exchanger
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
- F24F3/065—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units with a plurality of evaporators or condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
- F24F3/08—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units with separate supply and return lines for hot and cold heat-exchange fluids i.e. so-called "4-conduit" system
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
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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
- 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
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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
- 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
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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
- 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
- F25B2313/02732—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two three-way valves
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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
- 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
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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
- 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
- F25B2400/12—Inflammable refrigerants
- F25B2400/121—Inflammable refrigerants using R1234
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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
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
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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
- F25B2500/00—Problems to be solved
- F25B2500/08—Exceeding a certain temperature value in a refrigeration component or cycle
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
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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
- 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
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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
- F25B41/00—Fluid-circulation arrangements
Definitions
- the present invention relates to an air conditioner applied to, for example, a building multi air conditioner.
- an air conditioner such as a multi air conditioning system for buildings
- a refrigerant is circulated from an outdoor unit to a relay unit (relay unit)
- a heat medium such as water is circulated from the relay unit to the indoor unit.
- an air conditioner that reduces the conveyance power of the heat medium while circulating the medium and realizes the mixed operation of cooling and heating (for example, Patent Document 1).
- a compressor high-pressure shell compression that uses R32, which has a relatively low global warming potential (GWP), as the refrigerant, and that has a discharge pressure atmosphere from the outlet side of the gas-liquid separator in the high-pressure liquid pipe of the refrigeration cycle.
- GWP global warming potential
- Patent Document 1 In an air conditioner such as a building multi-air conditioner described in Patent Document 1, there is no problem when a refrigerant such as R410A is used as a refrigerant. For example, when R32 or the like is used as a refrigerant, In some cases, the discharge temperature of the compressor becomes too high during heating at a low outside air temperature. For this reason, there existed a subject that a refrigerant
- a throttle device such as an electronic expansion valve that depressurizes the refrigerant is installed in a relay machine or an indoor unit away from the outdoor unit.
- Patent Document 3 In the air conditioning apparatus described in Patent Document 3, a method is disclosed in which a plurality of check valves are used to inject from a high-pressure liquid pipe during cooling and during heating.
- a throttle device such as an electronic expansion valve
- the compressor in Patent Document 3 uses a high-pressure shell structure. In addition, it does not support mixed operation of cooling and heating.
- the present invention has been made to solve the above-described problem, and a throttle device such as an electronic expansion valve for decompressing the refrigerant is installed in a relay machine or indoor unit away from the outdoor unit. It is a system that is in a two-phase state (gas-liquid two-phase) or a liquid state from a repeater or indoor unit, such that a low-pressure or medium-pressure refrigerant returns to the outdoor unit, and uses a compressor with a low-pressure shell structure
- an air conditioner having a refrigerant circuit that is controlled so as to ensure that the discharge temperature does not become excessively high and prevents deterioration of the refrigerant and the refrigerating machine oil is obtained.
- An air conditioner according to the present invention has a compression chamber provided with an opening into which refrigerant flowing through an injection pipe flows in a sealed container, the inside of the sealed container is set to a low-pressure refrigerant pressure atmosphere, and the low-pressure refrigerant in the sealed container is
- a compressor having a low-pressure shell structure that flows into the compression chamber for compression; a first heat exchanger for evaporating or condensing the refrigerant; and one or more second heat exchangers; and one or more first heat exchangers for depressurizing the refrigerant.
- a refrigerant flow switching device that switches the flow path, and a medium pressure that is smaller than the high pressure and larger than the low pressure is the refrigerant that passes through the first expansion device and flows from the second heat exchanger side to the first heat exchanger side.
- the first heat exchanger is an evaporator
- a part of the high-pressure refrigerant flowing from the first to the second heat exchanger side can be made to flow to the injection pipe.
- the refrigerant discharge temperature of the compressor is able to flow through the injection pipe, even when a refrigerant such as R32, which tends to be high in temperature, is used. Is controlled so that it does not become too high, deterioration of the refrigerant and refrigerating machine oil can be prevented, and safe operation can be achieved.
- the air conditioner according to the present invention has a compressor regardless of the operation using the first heat exchanger as a condenser or the operation using an evaporator even when a refrigerant such as R32 that increases the discharge temperature of the compressor is used. Since the refrigerant can be injected into the compression chamber, it can be controlled so that the discharge temperature does not become too high, and deterioration of the refrigerant and refrigerating machine oil can be prevented, and an air conditioner capable of safe operation can be obtained. .
- FIG. 2 is a ph diagram (pressure-enthalpy diagram) during a cooling only operation of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- FIG. 2 is a ph diagram (pressure-enthalpy diagram) during a cooling only operation of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- FIG. 2 is a ph diagram (pressure-enthalpy diagram) during cooling main operation of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- the ph diagram pressure-enthalpy diagram at the time of heating main operation of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- BRIEF DESCRIPTION OF THE DRAWINGS Schematic of the structure of the aperture apparatus of the air conditioning apparatus which concerns on Embodiment 1 of this invention.
- operation of the air conditioning apparatus which concerns on Embodiment 1 of this invention.
- the circuit block diagram of the air conditioning apparatus which concerns on Embodiment 2 of this invention.
- FIG. 7 is a ph diagram (pressure-enthalpy diagram) during a cooling only operation of the air-conditioning apparatus according to Embodiment 2 of the present invention.
- FIG. 7 is a ph diagram (pressure-enthalpy diagram) during a cooling only operation of the air-conditioning apparatus according to Embodiment 2 of the present invention.
- Embodiment 1 FIG. Embodiment 1 of the present invention will be described with reference to the drawings.
- FIG. 1 is a schematic diagram showing an installation example of an air-conditioning apparatus according to an embodiment of the present invention. Based on FIG. 1, the installation example of an air conditioning apparatus is demonstrated.
- This air conditioner uses the refrigeration cycle (refrigerant circulation circuit A, heat medium circulation circuit B) for circulating the heat source side refrigerant and the heat medium, so that each indoor unit 2 can freely set the cooling mode or the heating mode as the operation mode. You can choose.
- the size relationship of each component may be different from the actual one.
- the temperature and pressure levels described below are not based on absolute values, but are based on relationships that are relatively determined in terms of the state and operation of the device. Suppose you are.
- the air conditioner according to the present embodiment includes an outdoor unit 1 that is an outdoor unit (heat source unit), a plurality of indoor units 2, and an outdoor unit 1 and an indoor unit 2. And a heat medium relay unit 3 serving as a relay unit (relay machine) interposed between the two.
- the heat medium relay unit 3 performs heat exchange between the heat source side refrigerant and the heat medium.
- the outdoor unit 1 and the heat medium relay unit 3 are connected by a refrigerant pipe 4 that conducts the heat source side refrigerant.
- the heat medium relay unit 3 and the indoor unit 2 are connected by a pipe (heat medium pipe) 5 that conducts the heat medium.
- the cold or warm heat generated by the outdoor unit 1 is delivered to the indoor unit 2 via the heat medium converter 3.
- the outdoor unit 1 is usually disposed in an outdoor space 6 that is a space outside a building 9 such as a building (for example, a rooftop), and supplies cold or hot heat to the indoor unit 2 via the heat medium converter 3. It is.
- the indoor unit 2 is arranged at a position where cooling air or heating air can be supplied to the indoor space 7 that is a space (for example, a living room) inside the building 9, and the cooling air is supplied to the indoor space 7 that is the air-conditioning target space. Alternatively, heating air is supplied.
- the heat medium relay unit 3 is configured as a separate housing from the outdoor unit 1 and the indoor unit 2 so as to be installed at a position different from the outdoor space 6 and the indoor space 7.
- the outdoor unit 1 and the indoor unit 2 are connected to each other by a refrigerant pipe 4 and a pipe 5, respectively, and transmit cold heat or hot heat supplied from the outdoor unit 1 to the indoor unit 2.
- each unit (outdoor unit 1, indoor unit 2, and heat medium converter 3) is connected using two pipes (refrigerant pipe 4, pipe 5). Therefore, construction is easy.
- the heat medium converter 3 is installed in a space (hereinafter simply referred to as a space 8) such as the back of the ceiling, which is inside the building 9 but is different from the indoor space 7.
- the state is shown as an example.
- the heat medium relay 3 can also be installed in a common space where there is an elevator or the like.
- the indoor unit 2 is a ceiling cassette type
- mold is shown as an example, it is not limited to this, It is directly or directly in the indoor space 7, such as a ceiling embedded type and a ceiling suspended type. Any type of air can be used as long as heating air or cooling air can be blown out by a duct or the like.
- the outdoor unit 1 may be installed in the outdoor space 6 as an example, it is not limited to this.
- the outdoor unit 1 may be installed in an enclosed space such as a machine room with a ventilation opening.
- the waste heat can be exhausted outside the building 9 by the exhaust duct, it may be installed inside the building 9 or installed inside the building 9 using the water-cooled outdoor unit 1. You may do it. No matter what place the outdoor unit 1 is installed, no particular problem occurs.
- the heat medium converter 3 can also be installed in the vicinity of the outdoor unit 1. However, it should be noted that if the distance from the heat medium converter 3 to the indoor unit 2 is too long, the heat medium transfer power becomes considerably large, and the energy saving effect is diminished. Furthermore, the number of connected outdoor units 1, indoor units 2, and heat medium converters 3 is not limited to the number illustrated in FIG. 1 and the like, and the building 9 in which the air conditioner according to the present embodiment is installed. The number of units may be determined according to.
- FIG. 2 is a schematic circuit configuration diagram illustrating an example of a circuit configuration of the air-conditioning apparatus according to Embodiment 1 (hereinafter referred to as the air-conditioning apparatus 100). Based on FIG. 2, the detailed structure of the air conditioning apparatus 100 is demonstrated. As shown in FIG. 2, the outdoor unit 1 and the heat medium relay unit 3 are a heat exchanger 15 a between the heat medium and a heat medium heat exchanger that serve as a second heat exchanger provided in the heat medium relay unit 3.
- the refrigerant pipe 4 is connected via the vessel 15b.
- the heat medium converter 3 and the indoor unit 2 are also connected by a pipe 5 via a heat exchanger related to heat medium 15a and a heat exchanger related to heat medium 15b.
- the refrigerant pipe 4 will be described in detail later.
- the outdoor unit 1 includes a compressor 10, a first refrigerant flow switching device 11 such as a four-way valve, a heat source side heat exchanger 12 serving as a first heat exchanger, and an accumulator 19. It is mounted connected in series.
- the outdoor unit 1 is provided with a first connection pipe 4a, a second connection pipe 4b, a check valve 13a, a check valve 13b, a check valve 13c, and a check valve 13d. Regardless of the operation that the indoor unit 2 requires, heat is provided by providing the first connection pipe 4a, the second connection pipe 4b, the check valve 13a, the check valve 13b, the check valve 13c, and the check valve 13d.
- the flow of the heat source side refrigerant flowing into and out of the medium converter 3 can be set in a certain direction.
- the compressor 10 sucks the heat source side refrigerant and compresses the heat source side refrigerant to a high temperature and high pressure state.
- the compressor 10 may be composed of an inverter compressor capable of capacity control. The structure of the compressor 10 will be described later.
- the first refrigerant flow switching device 11 is used in the heating operation (in the heating only operation mode and in the heating main operation mode) and in the cooling operation (in the cooling only operation mode and the cooling main operation mode).
- the flow of the heat source side refrigerant is switched.
- the heat source side heat exchanger 12 functions as an evaporator during heating operation, functions as a condenser (or radiator) during cooling operation, and exchanges heat between air supplied from a blower (not shown) and the heat source side refrigerant.
- the heat source side refrigerant is converted into evaporative gas or condensed liquid.
- the accumulator 19 is provided on the suction side of the heat source side refrigerant in the compressor 10 and stores excess heat source side refrigerant.
- the check valve 13d is provided in the refrigerant pipe 4 between the heat medium converter 3 and the first refrigerant flow switching device 11, and only in a predetermined direction (direction from the heat medium converter 3 to the outdoor unit 1).
- the flow of the heat source side refrigerant is allowed.
- the check valve 13 a is provided in the refrigerant pipe 4 between the heat source side heat exchanger 12 and the heat medium converter 3, and only on a heat source side in a predetermined direction (direction from the outdoor unit 1 to the heat medium converter 3).
- the refrigerant flow is allowed.
- the check valve 13b is provided in the first connection pipe 4a, and causes the heat source side refrigerant discharged from the compressor 10 to flow to the heat medium converter 3 during the heating operation.
- the check valve 13 c is provided in the second connection pipe 4 b and causes the heat source side refrigerant returned from the heat medium relay unit 3 to flow to the suction side of the compressor 10 during the heating operation.
- the first connection pipe 4a is a refrigerant pipe 4 between the first refrigerant flow switching device 11 and the check valve 13d, and a refrigerant between the check valve 13a and the heat medium relay unit 3.
- the pipe 4 is connected.
- the second connection pipe 4b includes a refrigerant pipe 4 between the check valve 13d and the heat medium relay unit 3, and a refrigerant pipe 4 between the heat source side heat exchanger 12 and the check valve 13a. Are connected to each other.
- an upper limit temperature is set.
- this upper limit temperature is set to 120 ° C. Since the temperature of the heat source side refrigerant that is highest in the refrigeration circuit A is the temperature (discharge temperature) on the discharge side of the compressor 10, control is performed so that the discharge temperature is not higher than 120 ° C. as much as possible. For example, when a refrigerant such as R410A is used as the heat source side refrigerant, the discharge temperature rarely reaches 120 ° C. during normal operation.
- the outdoor unit 1 includes a branching device, a distributor, and the like.
- the branching portion 27a serving as the first branching device
- the branching portion 27b serving as the second branching device
- the injection opening / closing device 24 A backflow prevention device 20
- a throttling device 14a serving as a second throttling device
- a throttling device 14b serving as a third throttling device
- an injection pipe 4c and a branch pipe 4d are provided.
- An injection circuit is constituted in the refrigerant circuit A by these devices and piping. Further, it includes an intermediate pressure detection device 32, a discharge refrigerant temperature detection device 37, an intake refrigerant temperature detection device 38, and a high pressure detection device 39. Furthermore, it has the control apparatus 50 for performing refrigerant temperature control etc.
- the compressor 10 has a compression chamber in a sealed container, the inside of the sealed container has a low-pressure refrigerant pressure atmosphere, and has a low-pressure shell structure that sucks and compresses the low-pressure refrigerant in the sealed container in the compression chamber. .
- An opening is provided in a part of the compression chamber of the compressor 10. And it has the injection piping 4c which introduces a heat source side refrigerant
- the temperature of the heat source side refrigerant discharged from the compressor 10 or the degree of superheat of the heat source side refrigerant discharged from the compressor 10 (discharge superheat) by introducing the heat source side refrigerant into the compression chamber through the opening from the injection pipe 4c. ) Can be reduced.
- the control device 50 controls the injection opening / closing device 24, the expansion device 14a, the expansion device 14b, etc., thereby controlling the introduction of the heat source side refrigerant from the injection pipe 4c and lowering the discharge temperature of the compressor 10. Can be driven safely.
- a specific control operation will be described in the description for each operation mode described later.
- the control device 50 is configured by a microcomputer or the like, and controls each device based on detection information from various detection devices and instructions from a remote controller.
- the driving frequency of the compressor 10 the rotation speed of the blower (including ON / OFF), the switching of the first refrigerant flow switching device 11 and the like are controlled, and each operation mode described later is executed. It is supposed to be.
- the difference in discharge temperature between when R410A is used as the heat source side refrigerant and when R32 is used will be further described.
- the evaporation temperature of the refrigeration cycle is 0 ° C.
- the condensation temperature is 49 ° C.
- the superheat (superheat degree) of the compressor suction refrigerant is 0 ° C.
- the discharge temperature of the compressor 10 is about 70 ° C. due to the physical properties of the refrigerant.
- the discharge temperature of the compressor 10 is about 86 ° C. due to the physical properties of the refrigerant. From the above, when R32 is used as the heat source side refrigerant, the discharge temperature increases by about 16 ° C. compared to the case where R410A is used. In actual operation, the compressor 10 performs polytropic compression, which is an operation that is less efficient than adiabatic compression, so that the discharge temperature is further higher than the above value. For example, even when R410A is used, it frequently occurs that the operation is performed with the discharge temperature exceeding 100 ° C. Under the condition that the discharge temperature is higher than 104 ° C. in R410A, the discharge temperature limit needs to be lowered because the discharge temperature limit of 120 ° C. is exceeded in R32.
- the discharge temperature can be lowered by sucking the heat source side refrigerant in the phase state into the compression chamber of the compressor.
- a low-pressure shell structure such as the compressor 10
- the liquid refrigerant only accumulates in the shell of the compressor 10 and the two-phase in the compression chamber.
- the refrigerant is not inhaled. Accordingly, in order to lower the discharge temperature when using the compressor 10 having a low-pressure shell structure and using R32 or the like that increases the discharge temperature, a low-temperature heat source is provided from the outside to the compression chamber in the middle of compression.
- the side refrigerant is injected to lower the temperature of the heat source side refrigerant.
- the discharge temperature is lowered by introducing the refrigerant from the injection pipe 4c.
- the discharge temperature is controlled to be a target value (for example, 100 ° C.), and the control target value is changed according to the outside air temperature. It may be.
- the injection may be performed before the discharge temperature exceeds a predetermined value (for example, 110 ° C.), and if it is lower than that, the injection may be controlled not to be performed.
- control is performed so that the discharge temperature is within the target range (for example, 80 ° C to 100 ° C).
- the target range for example, 80 ° C to 100 ° C.
- discharge superheat degree is calculated using the pressure on the high pressure side detected by the high pressure detection device 39 and the discharge temperature detected by the discharge refrigerant temperature detection device 37.
- the injection amount may be controlled so that the discharge superheat becomes a target value (for example, 30 ° C.), and the control target value may be changed according to the outside air temperature.
- the injection may be performed before the discharge superheat exceeds a predetermined value (for example, 40 ° C.), and when it is lower than that, the injection may be controlled not to be performed. Furthermore, control is performed so that the discharge superheat falls within the target range (for example, 10 ° C. to 40 ° C.), and when the discharge superheat is likely to exceed the upper limit of the target range, the injection amount is increased. You may control so that the amount of injection may be reduced when it is likely to fall below a minimum.
- a predetermined value for example, 40 ° C.
- the heat source side refrigerant circulating in the refrigerant circuit A is R32
- the conventional R410A condensing temperature, evaporation temperature, superheat (superheat degree), subcool (supercool degree)
- any refrigerant whose discharge temperature is higher than R410A can reduce the discharge temperature by the configuration of the present embodiment, and the same effect can be obtained. Play.
- a heat source side refrigerant that is 3 ° C. or higher than R410A is more effective.
- FIG. 3 is a diagram showing a change in discharge temperature with respect to the mass ratio of R32 in the mixed refrigerant of R32 and HFO1234yf.
- HFO1234yf is a tetrafluoropropene refrigerant having a small global warming potential and a chemical formula represented by CF 3 CF ⁇ CH 2 . Then, the discharge temperature is estimated on the assumption that adiabatic compression (isentropic compression) is performed in the same manner as described above.
- the discharge temperature is calculated in the same manner as described above.
- the discharge temperature is approximately 70 ° C., which is substantially the same as that of R410A.
- the discharge temperature is approximately 73 ° C., which is 3 ° C. higher than the discharge temperature of R410A.
- the refrigerant type in the mixed refrigerant is not limited to two kinds, and even if it is three or more kinds of mixed refrigerants containing a small amount of other refrigerant components, there is no significant influence on the discharge temperature, so the same effect is achieved. .
- it can be used in a mixed refrigerant containing a small amount of R32, HFO1234yf, and other refrigerants.
- the calculation here is based on the assumption of adiabatic compression, and since actual compression is performed by polytropic compression, it is several tens of degrees higher than the temperature described here, for example, 20 ° C. This is a high value.
- Each indoor unit 2 is equipped with a use side heat exchanger 26.
- the use side heat exchanger 26 is connected to the heat medium flow control device 25 and the second heat medium flow switching device 23 of the heat medium converter 3 by the pipe 5.
- This use side heat exchanger 26 performs heat exchange between air supplied from a blower (not shown) and a heat medium, and generates heating air or cooling air to be supplied to the indoor space 7. is there.
- FIG. 2 shows an example in which four indoor units 2 are connected to the heat medium relay unit 3, and are illustrated as an indoor unit 2a, an indoor unit 2b, an indoor unit 2c, and an indoor unit 2d from the bottom of the page. Show.
- the use side heat exchanger 26 also uses the use side heat exchanger 26a, the use side heat exchanger 26b, the use side heat exchanger 26c, and the use side heat exchange from the lower side of the drawing. It is shown as a container 26d.
- the number of connected indoor units 2 is not limited to four as shown in FIG.
- the heat medium relay unit 3 is equipped with two heat exchangers 15 between heat mediums, two expansion devices 16, two opening / closing devices 17, and two second refrigerant flow switching devices 18. .
- two pumps 21, four first heat medium flow switching devices 22, four second heat medium flow switching devices 23, and four heat medium flow control devices 25 are mounted.
- the two heat exchangers 15 between heat mediums (heat medium heat exchanger 15a, heat medium heat exchanger 15b) serving as the second heat exchangers are condensers (radiators) or evaporators in the refrigerant circuit A. Function as. Heat exchange is performed between the heat source side refrigerant and the heat medium, and the cold or warm heat generated in the outdoor unit 1 and stored in the heat source side refrigerant is transmitted to the heat medium.
- the heat exchanger related to heat medium 15a is provided between the expansion device 16a and the second refrigerant flow switching device 18a in the refrigerant circuit A, and serves to cool the heat medium in the cooling / heating mixed operation mode described later. Is.
- the heat exchanger related to heat medium 15b is provided between the expansion device 16b and the second refrigerant flow switching device 18b in the refrigerant circuit A, and heats the heat medium in the cooling / heating mixed operation mode described later. It is for use.
- the two expansion devices 16 (the expansion device 16a and the expansion device 16b) serving as the first expansion devices have functions as pressure reducing valves and expansion valves, and expand the heat source side refrigerant by reducing the pressure.
- the expansion device 16a is provided on the upstream side of the heat exchanger related to heat medium 15a in the flow of the heat source side refrigerant during the cooling operation.
- the expansion device 16b is provided on the upstream side of the heat exchanger related to heat medium 15b in the flow of the heat source side refrigerant during the cooling operation.
- the two throttling devices 16 may be configured such that the opening degree (opening area) can be variably controlled, such as an electronic expansion valve.
- the two opening / closing devices 17 are constituted by two-way valves or the like, and open / close the refrigerant pipe 4.
- the opening / closing device 17a is provided in the refrigerant pipe 4 on the inlet side of the heat source side refrigerant.
- the opening / closing device 17b is provided in a pipe connecting the refrigerant pipe 4 on the inlet side and the outlet side of the heat source side refrigerant.
- the two second refrigerant flow switching devices 18 (second refrigerant flow switching device 18a and second refrigerant flow switching device 18b) are constituted by four-way valves or the like, and switch the flow of the heat source side refrigerant according to the operation mode.
- the second refrigerant flow switching device 18a is provided on the downstream side of the heat exchanger related to heat medium 15a in the flow of the heat source side refrigerant during the cooling operation.
- the second refrigerant flow switching device 18b is provided on the downstream side of the heat exchanger related to heat medium 15b in the flow of the heat source side refrigerant during the cooling only operation.
- the two pumps 21 (pump 21a and pump 21b) circulate a heat medium that conducts through the pipe 5.
- the pump 21 a is provided in the pipe 5 between the heat exchanger related to heat medium 15 a and the second heat medium flow switching device 23.
- the pump 21 b is provided in the pipe 5 between the heat exchanger related to heat medium 15 b and the second heat medium flow switching device 23.
- the two pumps 21 may be constituted by, for example, pumps capable of capacity control.
- the four first heat medium flow switching devices 22 are configured by three-way valves or the like, and switch the heat medium flow channels. Is.
- the first heat medium flow switching device 22 is provided in a number (here, four) according to the number of indoor units 2 installed. In the first heat medium flow switching device 22, one of the three sides is in the heat exchanger 15a, one of the three is in the heat exchanger 15b, and one of the three is in the heat medium flow rate.
- Each is connected to the adjusting device 25 and provided on the outlet side of the heat medium flow path of the use side heat exchanger 26. In FIG.
- the first heat medium flow switching device 22a the first heat medium flow switching device 22b, the first heat medium flow switching device 22c, and the first heat medium corresponding to the indoor unit 2 from the lower side of the drawing. It is illustrated as a flow path switching device 22d (the same applies to the following drawings).
- the four second heat medium flow switching devices 23 are configured by three-way valves or the like, and switch the flow path of the heat medium. Is.
- the number of the second heat medium flow switching devices 23 is set according to the number of installed indoor units 2 (here, four).
- the heat exchanger is connected to the exchanger 26 and provided on the inlet side of the heat medium flow path of the use side heat exchanger 26. In FIG.
- the second heat medium flow switching device 23a, the second heat medium flow switching device 23b, the second heat medium flow switching device 23c, and the second heat medium are associated with the indoor unit 2 from the lower side of the drawing. It is illustrated as a flow path switching device 23d (the same applies to the following drawings).
- the four heat medium flow control devices 25 are configured by a two-way valve or the like that can control the opening area, and controls the flow rate flowing through the pipe 5. is there.
- the number of the heat medium flow control devices 25 is set according to the number of indoor units 2 installed (four in this case).
- One of the heat medium flow control devices 25 is connected to the use side heat exchanger 26 and the other is connected to the first heat medium flow switching device 22, and is connected to the outlet side of the heat medium flow channel of the use side heat exchanger 26. Is provided. In FIG.
- the heat medium flow control device 25a, the heat medium flow control device 25b, the heat medium flow control device 25c, and the heat medium flow control device 25d are illustrated from the lower side of the drawing. The same applies to the following drawings). Further, the heat medium flow control device 25 may be provided on the inlet side of the heat medium flow path of the use side heat exchanger 26.
- the heat exchanger 3 includes two heat exchanger outlet temperature detection devices 31 (hereinafter referred to as first temperature sensors 31) and four heat exchanger outlet temperature detection devices 34 (hereinafter referred to as first temperature sensors). (Referred to as two temperature sensors 34), four heat medium heat exchanger refrigerant temperature detection devices 35 (hereinafter referred to as third temperature sensors 35), and two heat medium heat exchanger refrigerant pressure detection devices 36 (hereinafter referred to as pressure). Sensor 36) is provided. Information (temperature information, pressure information) detected by these detection devices is sent to the control device 50 described above, and the drive frequency of the compressor 10, the rotational speed of the blower (not shown), and the first refrigerant flow switching device 11 are displayed. Switching, switching of the driving frequency of the pump 21, switching of the second refrigerant flow switching device 18, switching of the flow path of the heat medium, and the like.
- the two first temperature sensors 31 are the heat medium flowing out from the heat exchanger related to heat medium 15, that is, the temperature of the heat medium at the outlet of the heat exchanger related to heat medium 15.
- a thermistor may be used.
- the first temperature sensor 31a is provided in the pipe 5 on the inlet side of the pump 21a.
- the first temperature sensor 31b is provided in the pipe 5 on the inlet side of the pump 21b.
- the four second temperature sensors 34 are provided between the first heat medium flow switching device 22 and the heat medium flow control device 25, and use side heat exchangers.
- the temperature of the heat medium that has flowed out of the heater 26 is detected, and it may be constituted by a thermistor or the like.
- the number of the second temperature sensors 34 (four here) according to the number of indoor units 2 installed is provided. In correspondence with the indoor unit 2, the second temperature sensor 34a, the second temperature sensor 34b, the second temperature sensor 34c, and the second temperature sensor 34d are illustrated from the lower side of the drawing.
- the four third temperature sensors 35 are provided on the inlet side or the outlet side of the heat source side refrigerant of the heat exchanger related to heat medium 15, and the heat exchanger related to heat medium 15
- the temperature of the heat source side refrigerant flowing into the heat source or the temperature of the heat source side refrigerant flowing out of the heat exchanger related to heat medium 15 is detected, and may be composed of a thermistor or the like.
- the third temperature sensor 35a is provided between the heat exchanger related to heat medium 15a and the second refrigerant flow switching device 18a.
- the third temperature sensor 35b is provided between the heat exchanger related to heat medium 15a and the expansion device 16a.
- the third temperature sensor 35c is provided between the heat exchanger related to heat medium 15b and the second refrigerant flow switching device 18b.
- the third temperature sensor 35d is provided between the heat exchanger related to heat medium 15b and the expansion device 16b.
- the pressure sensor 36b is provided between the heat exchanger related to heat medium 15b and the expansion device 16b, and between the heat exchanger related to heat medium 15b and the expansion device 16b.
- the pressure of the flowing heat source side refrigerant is detected.
- the pressure sensor 36a is provided between the heat exchanger related to heat medium 15a and the second refrigerant flow switching device 18a, and is connected to the heat exchanger related to heat medium 15a and the second heat exchanger 15a.
- the pressure of the heat source side refrigerant flowing between the refrigerant flow switching device 18a is detected.
- the heat medium relay unit 3 is provided with a control device (not shown) constituted by a microcomputer or the like. Based on detection information from various detection devices and instructions from the remote controller, driving of the pump 21, opening of the expansion device 16, opening / closing of the opening / closing device 17, switching of the second refrigerant flow switching device 18, first heat medium flow Control each device of the heat medium relay 3 such as switching the path switching device 22, switching the second heat medium flow switching device 23, opening degree of the heat medium flow control device 25, etc., and execute each operation mode to be described later It is like that.
- a separate control device for controlling each device of the heat medium relay 3 is provided, but it is provided in only one of the outdoor unit 1 and the heat medium relay device 3 integrally with the control device 50 described above. May be.
- the pipe 5 that conducts the heat medium is composed of one that is connected to the heat exchanger related to heat medium 15a and one that is connected to the heat exchanger related to heat medium 15b.
- the pipe 5 is branched (here, four branches each) according to the number of indoor units 2 connected to the heat medium relay unit 3.
- the pipe 5 is connected by a first heat medium flow switching device 22 and a second heat medium flow switching device 23.
- the first heat medium flow switching device 22 and the second heat medium flow switching device 23 By controlling the first heat medium flow switching device 22 and the second heat medium flow switching device 23, the heat medium from the heat exchanger related to heat medium 15a flows into the use-side heat exchanger 26, or the heat medium Whether the heat medium from the intermediate heat exchanger 15b flows into the use side heat exchanger 26 is determined.
- the refrigerant in the compressor 10 the first refrigerant flow switching device 11, the heat source side heat exchanger 12, the switching device 17, the second refrigerant flow switching device 18, and the heat exchanger related to heat medium 15a.
- the flow path, the expansion device 16 and the accumulator 19 are connected by the refrigerant pipe 4 to constitute the refrigerant circuit A.
- the switching device 23 is connected by a pipe 5 to constitute a heat medium circulation circuit B.
- a plurality of use side heat exchangers 26 are connected in parallel to each of the heat exchangers 15 between heat mediums, and the heat medium circulation circuit B can be made into a plurality of systems by switching by the flow path switching device. It is.
- the outdoor unit 1 and the heat medium relay unit 3 are connected via the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b provided in the heat medium converter 3.
- the heat medium relay unit 3 and the indoor unit 2 are also connected to each other via the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b.
- the heat source side refrigerant circulating in the refrigerant circuit A and the heat medium circulating in the heat medium circuit B exchange heat in the intermediate heat exchanger 15a and the intermediate heat exchanger 15b. I can do it.
- the air conditioner 100 can select a cooling operation or a heating operation in each indoor unit 2 based on an instruction from each indoor unit 2. For this reason, the air conditioner 100 is configured such that all the indoor units 2 being operated can perform the same operation, and each of the indoor units 2 can be operated differently.
- each operation mode In the operation mode executed by the air conditioner 100, all the indoor units 2 being operated are in the cooling operation and only the cooling load is generated, and all the indoor units 2 being operated are in the cooling mode. There is an all-heating operation mode when only heating load occurs when heating operation is performed. Further, there are a cooling main operation mode when each indoor unit 2 operates differently and the cooling load is larger, and a heating main operation mode when the heating load is larger.
- each operation mode will be described together with the flow of the heat source side refrigerant and the heat medium.
- FIG. 4 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the cooling only operation mode.
- the cooling only operation mode will be described by taking as an example a case where a cooling load is generated only in the use side heat exchanger 26a and the use side heat exchanger 26b.
- a pipe represented by a thick line indicates a pipe through which the refrigerant (heat source side refrigerant and heat medium) flows.
- the flow direction of the heat source side refrigerant is indicated by solid line arrows
- the flow direction of the heat medium is indicated by broken line arrows.
- the first refrigerant flow switching device 11 is switched so that the heat source side refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12.
- the pump 21a and the pump 21b are driven, the heat medium flow control device 25a and the heat medium flow control device 25b are opened, and the heat medium flow control device 25c and the heat medium flow control device 25d are fully closed.
- the heat medium circulates between the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b and the use side heat exchanger 26a and the use side heat exchanger 26b.
- the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the first refrigerant flow switching device 11. Then, the heat source side heat exchanger 12 condenses and liquefies while radiating heat to the outdoor air, and becomes a high-pressure liquid refrigerant.
- the high-pressure liquid refrigerant that has flowed out of the heat source side heat exchanger 12 flows out of the outdoor unit 1 through the check valve 13a, the branch part 27a, and flows into the heat medium relay unit 3 through the refrigerant pipe 4. .
- the high-pressure liquid refrigerant flowing into the heat medium relay unit 3 is branched after passing through the opening / closing device 17a and expanded by the expansion device 16a and the expansion device 16b to become a low-temperature low-pressure two-phase refrigerant.
- This two-phase refrigerant flows into each of the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b acting as an evaporator, and absorbs heat from the heat medium circulating in the heat medium circulation circuit B. It becomes a low-temperature and low-pressure gas refrigerant while cooling.
- the gas refrigerant flowing out from the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b flows out from the heat medium converter 3 via the second refrigerant flow switching device 18a and the second refrigerant flow switching device 18b.
- the refrigerant flows into the outdoor unit 1 again through the refrigerant pipe 4.
- the heat-source-side refrigerant that has flowed into the outdoor unit 1 is sucked into the compressor 10 again via the branch portion 27b, the check valve 13d, the first refrigerant flow switching device 11 and the accumulator 19. .
- the expansion device 16a has an opening degree (superheat) so that the superheat (superheat degree) obtained as a difference between the temperature detected by the third temperature sensor 35a and the temperature detected by the third temperature sensor 35b becomes constant. Opening area) is controlled. Similarly, the opening degree of the expansion device 16b is controlled so that the superheat obtained as the difference between the temperature detected by the third temperature sensor 35c and the temperature detected by the third temperature sensor 35d is constant.
- the opening / closing device 17a is open and the opening / closing device 17b is closed.
- FIG. 5 is a diagram showing a ph diagram (pressure-enthalpy diagram) in the cooling only operation mode according to the first embodiment.
- the air conditioner 100 performs an operation of lowering the discharge temperature using the injection circuit. The operation at this time will be described with reference to FIGS.
- the low-temperature and low-pressure gas refrigerant sucked from the suction port of the compressor 10 is introduced into the sealed container, and the low-temperature and low-pressure gas refrigerant filled in the sealed container is sucked into the compression chamber (not shown). Is done. While the compression chamber is rotated 0 to 360 degrees by a motor (not shown), the internal volume decreases, and the internal heat source side refrigerant is compressed and the pressure and temperature rise. When the rotation angle of the motor reaches a certain angle, the opening opens (the state at this time is point F in FIG. 5), and the inside of the compression chamber and the injection pipe 4c outside the compressor 10 communicate with each other. It has become.
- the heat-source-side refrigerant compressed by the compressor 10 is condensed and liquefied by the heat-source-side heat exchanger 12 to become a high-pressure liquid refrigerant (point J in FIG. 5).
- a high-pressure liquid refrigerant point J in FIG. 5
- the injection opening / closing device 24 is opened, and this high-pressure liquid refrigerant is branched at the branching portion 27a, flows into the injection piping 4c via the injection opening / closing device 24 and the branching piping 4d, and is reduced in pressure by the expansion device 14b.
- a two-phase refrigerant with pressure (point K in FIG. 5) is caused to flow into the compression chamber through an opening provided in the compression chamber of the compressor 10.
- the medium-pressure gas refrigerant (point F in FIG. 5) and the low-temperature medium-pressure two-phase refrigerant (point K in FIG. 5) are mixed, and the temperature of the heat source side refrigerant is lowered.
- the temperature at this time is a temperature corresponding to the point H in FIG.
- the discharge temperature of the heat source side refrigerant discharged from the compressor 10 decreases.
- the discharge temperature of the compressor 10 is a temperature corresponding to the point I in FIG.
- the discharge temperature of the compressor 10 when the injection is not performed is a temperature corresponding to the point G in FIG. From the above, it can be seen that by performing the injection, the discharge temperature is lowered from the temperature corresponding to the point G to the temperature corresponding to the point I.
- the heat source side refrigerant in the flow path from the injection opening / closing device 24 of the branch pipe 4d to the backflow prevention device 20 is a high-pressure refrigerant, and returns from the heat medium converter 3 to the outdoor unit 1 via the refrigerant pipe 4 to branch.
- the heat source side refrigerant reaching the portion 27b is a low pressure refrigerant.
- the backflow prevention device 20 prevents the heat-source-side refrigerant flowing from the branch pipe 4d to the branch portion 27b, and the action of the backflow prevention device 20 prevents the high-pressure refrigerant in the branch pipe 4d from mixing with the low-pressure refrigerant in the branch portion 27b. It is preventing.
- the injection opening / closing device 24 may be one that can change the opening area of an electronic expansion valve or the like as long as it can switch the passage or non-passage of the refrigerant, in addition to the one that can switch the opening and closing of a solenoid valve or the like.
- the backflow prevention device 20 may be a check valve, or may be one that can switch opening and closing of an electromagnetic valve or the like, or one that can change opening and closing of a flow path by changing the opening area of an electronic expansion valve or the like. In the cooling only operation, since the heat source side refrigerant does not flow through the expansion device 14a, the opening degree may be set to an arbitrary degree.
- the control device 50 prevents the discharge temperature of the compressor 10 detected by the discharge refrigerant temperature detection device 37 from becoming too high.
- the opening area of the diaphragm device 14b is controlled.
- a control method when it is determined that the discharge temperature exceeds a certain value (for example, 110 ° C., etc.), it may be controlled to open by a certain degree of opening, for example, 10 pulses, or the discharge temperature is a target value. You may make it control the opening degree of the expansion device 14b so that it may become (for example, 100 degreeC).
- the expansion device 14b may be a capillary tube, and an amount of the heat source side refrigerant corresponding to the pressure difference may be injected.
- the flow of the heat medium in the heat medium circuit B will be described.
- the cold heat of the heat source side refrigerant is transmitted to the heat medium in both the heat exchanger 15a and the heat exchanger 15b, and the cooled heat medium is piped 5 by the pump 21a and the pump 21b.
- the inside will be allowed to flow.
- the heat medium pressurized and discharged by the pump 21a and the pump 21b passes through the second heat medium flow switching device 23a and the second heat medium flow switching device 23b, and the use side heat exchanger 26a and the use side heat exchange. Flows into the vessel 26b.
- the heat medium absorbs heat from the indoor air in the use side heat exchanger 26a and the use side heat exchanger 26b, thereby cooling the indoor space 7.
- the heat medium flows out of the use-side heat exchanger 26a and the use-side heat exchanger 26b and flows into the heat medium flow control device 25a and the heat medium flow control device 25b.
- the heat medium flow control device 25a and the heat medium flow control device 25b are operated to control the flow rate of the heat medium to a flow rate necessary to cover the air conditioning load required indoors, so that the use side heat exchanger 26a. And it flows into the use side heat exchanger 26b.
- the heat medium flowing out of the heat medium flow control device 25a and the heat medium flow control device 25b passes through the first heat medium flow switching device 22a and the first heat medium flow switching device 22b, and the heat exchanger related to heat medium 15a. And flows into the heat exchanger related to heat medium 15b, and is sucked into the pump 21a and the pump 21b again.
- the heat medium is directed from the second heat medium flow switching device 23 to the first heat medium flow switching device 22 via the heat medium flow control device 25.
- the air conditioning load required in the indoor space 7 includes the temperature detected by the first temperature sensor 31a, the temperature detected by the first temperature sensor 31b, and the temperature detected by the second temperature sensor 34. It is possible to cover by controlling so that the difference between the two is kept at the target value.
- the outlet temperature of the heat exchanger related to heat medium 15 either the temperature of the first temperature sensor 31a or the first temperature sensor 31b may be used, or the average temperature thereof may be used.
- the first heat medium flow switching device 22 and the second heat medium flow switching device 23 ensure a flow path that flows to both the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b.
- the intermediate opening is set.
- FIG. 6 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the heating only operation mode.
- the heating only operation mode will be described by taking as an example a case where a thermal load is generated only in the use side heat exchanger 26a and the use side heat exchanger 26b.
- tube represented by the thick line has shown the piping through which a refrigerant
- the flow direction of the heat source side refrigerant is indicated by solid line arrows, and the flow direction of the heat medium is indicated by broken line arrows.
- the first refrigerant flow switching device 11 causes the heat source side refrigerant discharged from the compressor 10 to heat without passing through the heat source side heat exchanger 12. It switches so that it may flow into the media converter 3.
- the pump 21a and the pump 21b are driven, the heat medium flow control device 25a and the heat medium flow control device 25b are opened, and the heat medium flow control device 25c and the heat medium flow control device 25d are fully closed.
- the heat medium circulates between the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b and the use side heat exchanger 26a and the use side heat exchanger 26b.
- the low-temperature and low-pressure heat source side refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, conducts through the first connection pipe 4 a, passes through the check valve 13 b and the branch portion 27 a, and then from the outdoor unit 1. leak.
- the high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit 1 flows into the heat medium relay unit 3 through the refrigerant pipe 4.
- the high-temperature and high-pressure gas refrigerant that has flowed into the heat medium relay unit 3 is branched and passes through the second refrigerant flow switching device 18a and the second refrigerant flow switching device 18b, and between the heat exchangers 15a and the heat medium. It flows into each of the heat exchangers 15b.
- the high-temperature and high-pressure gas refrigerant that has flowed into the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b is condensed and liquefied while dissipating heat to the heat medium circulating in the heat medium circuit B, and becomes a high-pressure liquid refrigerant.
- the liquid refrigerant that has flowed out of the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b is expanded by the expansion device 16a and the expansion device 16b, and becomes a two-phase refrigerant or liquid refrigerant of medium temperature and intermediate pressure.
- the two-phase refrigerant or liquid refrigerant flows out of the heat medium relay unit 3 through the opening / closing device 17b, and flows into the outdoor unit 1 through the refrigerant pipe 4 again.
- the heat-source-side refrigerant that has flowed into the outdoor unit 1 flows into the second connection pipe 4b via the branching portion 27b, passes through the expansion device 14a, is throttled by the expansion device 14a, and becomes a low-temperature and low-pressure two-phase refrigerant. It passes through the valve 13c and flows into the heat source side heat exchanger 12 acting as an evaporator.
- the heat source side refrigerant flowing into the heat source side heat exchanger 12 absorbs heat from the outdoor air in the heat source side heat exchanger 12 and becomes a low-temperature and low-pressure gas refrigerant.
- the low-temperature and low-pressure gas refrigerant flowing out from the heat source side heat exchanger 12 is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
- the expansion device 16a has a constant subcool (degree of subcooling) obtained as a difference between a value obtained by converting the pressure detected by the pressure sensor 36 into a saturation temperature and a temperature detected by the third temperature sensor 35b.
- the opening degree is controlled.
- the expansion device 16b has an opening degree so that a subcool obtained as a difference between a value obtained by converting the pressure detected by the pressure sensor 36 into a saturation temperature and a temperature detected by the third temperature sensor 35d is constant. Be controlled.
- the opening / closing device 17a is closed and the opening / closing device 17b is open.
- the temperature at the intermediate position may be used instead of the pressure sensor 36, and the system can be configured at low cost.
- FIG. 7 is a diagram showing a ph diagram (pressure-enthalpy diagram) in the heating only operation mode according to the first embodiment.
- the cooling only operation mode when the heat source side refrigerant is R32, the discharge temperature of the compressor 10 is high, and thus the air conditioner 100 performs an operation of lowering the discharge temperature using the injection circuit. The operation at this time will be described with reference to FIGS.
- the low-temperature and low-pressure gas refrigerant sucked from the suction port of the compressor 10 is introduced into the sealed container, and the low-temperature and low-pressure gas refrigerant filled in the sealed container is sucked into the compression chamber (not shown). Is done. While the compression chamber is rotated 0 to 360 degrees by a motor (not shown), the internal volume decreases, and the internal heat source side refrigerant is compressed and the pressure and temperature rise. When the rotation angle of the motor reaches a certain angle, the opening opens (the state at this time is point F in FIG. 7), and the inside of the compression chamber communicates with the injection pipe 4c outside the compressor 10. It has become.
- the heat-source-side refrigerant that returns from the heat medium relay unit 3 to the outdoor unit 1 via the refrigerant pipe 4 flows to the expansion device 14a via the branch portion 27b.
- the pressure of the heat source side refrigerant on the upstream side of the expansion device 14a is controlled to an intermediate pressure state (point J in FIG. 7).
- the two-phase refrigerant or liquid refrigerant that has been brought into an intermediate pressure state by the expansion device 14 a is branched by the branching portion 27 b, flows into the branch pipe 4 d, and flows into the injection pipe 4 c through the backflow prevention device 20.
- the refrigerant is decompressed by the expansion device 14b and becomes a low-temperature / medium-pressure two-phase refrigerant whose pressure is slightly reduced (point K in FIG. 7), and flows into the compression chamber from the opening provided in the compression chamber of the compressor 10.
- the medium-pressure gas refrigerant (point F in FIG. 7) and the low-temperature medium-pressure two-phase refrigerant (point K in FIG. 7) are mixed, thereby lowering the temperature of the heat source side refrigerant.
- the temperature at this time is a temperature corresponding to the point H in FIG. Thereby, the discharge temperature of the heat source side refrigerant discharged from the compressor 10 decreases.
- the discharge temperature of the compressor 10 is a temperature corresponding to the point I in FIG. Further, the discharge temperature of the compressor 10 when the injection is not performed is a temperature corresponding to the point G in FIG. From the above, it can be seen that by performing the injection, the discharge temperature is lowered from the temperature corresponding to the point G to the temperature corresponding to the point I.
- the branching portion 27b has a structure and an arrangement of the branching portion 27b that diverts the heat source side refrigerant in a state where the heat source side refrigerant flows in the direction opposite to the direction of gravity. By doing so, the two-phase refrigerant can be uniformly distributed.
- the injection opening / closing device 24 is closed, and the high-pressure heat-source-side refrigerant is mixed with the intermediate-pressure heat-source-side refrigerant that has passed through the backflow prevention device 20 from the branch portion 27a. Is prevented.
- the injection opening / closing device 24 may be one that can change the opening area of an electronic expansion valve or the like as long as it can switch the passage or non-passage of the refrigerant, as well as the one that can switch the opening and closing of an electromagnetic valve or the like.
- the backflow prevention device 20 may be a check valve, or may be one that can switch opening and closing of an electromagnetic valve or the like, or one that can change opening and closing of a flow path by changing the opening area of an electronic expansion valve or the like. Further, it is desirable that the expansion device 14a can change the opening area of an electronic expansion valve or the like. If an electronic expansion valve is used, the intermediate pressure upstream of the expansion device 14a can be controlled to an arbitrary pressure. For example, if the intermediate pressure detected by the intermediate pressure detection device 32 is controlled to be a constant value, the discharge temperature control by the expansion device 14b is stabilized. However, the expansion device 14a is not limited to the electronic expansion valve.
- a plurality of opening areas may be selected by combining open / close valves such as small solenoid valves, or a medium pressure may be formed according to the pressure loss of the heat source side refrigerant by using a capillary tube.
- open / close valves such as small solenoid valves
- a medium pressure may be formed according to the pressure loss of the heat source side refrigerant by using a capillary tube.
- the controllability is slightly deteriorated, but the discharge temperature can be controlled to the target.
- the intermediate pressure detection device 32 may calculate the intermediate pressure by, for example, the control device 50 based on the temperature detected using not only the pressure sensor but also the temperature sensor. Further, when the opening area of the expansion device 14b can be changed, such as an electronic expansion valve, the control device 50 does not cause the discharge temperature of the compressor 10 detected by the discharge refrigerant temperature detection device 37 to be too high. Thus, the opening area of the diaphragm device 14b is controlled. As a control method, when it is determined that the discharge temperature exceeds a certain value (for example, 110 ° C., etc.), it may be controlled to open by a certain degree of opening, for example, 10 pulses, or the discharge temperature is a target value.
- a certain value for example, 110 ° C., etc.
- the expansion device 14b may be a capillary tube, and an amount of the heat source side refrigerant corresponding to the pressure difference may be injected.
- the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b both heat the heat medium.
- the pressure (medium pressure) of the heat source side refrigerant on the upstream side of the expansion device 14a may be controlled to be higher. If the control is performed so that the intermediate pressure is increased, the differential pressure from the pressure in the compression chamber can be increased, so that the amount of the heat-source-side refrigerant injected into the compression chamber can be increased. Therefore, even when the outside air temperature is low, a sufficient injection amount can be supplied to the compression chamber to lower the discharge temperature.
- control of the diaphragm device 14a and the diaphragm device 14b by the control device 50 is not limited to this.
- the expansion device 14b may be fully opened, and the discharge temperature of the compressor 10 may be controlled only by the expansion device 14a. In this way, control is simplified, and there is an advantage that an inexpensive device can be used for the expansion device 14b.
- the heat of the heat source side refrigerant is transmitted to the heat medium in both the heat exchanger 15a and the heat exchanger 15b, and the heated heat medium is piped 5 by the pump 21a and the pump 21b.
- the inside will be allowed to flow.
- the heat medium pressurized and discharged by the pump 21a and the pump 21b passes through the second heat medium flow switching device 23a and the second heat medium flow switching device 23b, and the use side heat exchanger 26a and the use side heat exchange. Flows into the vessel 26b.
- the heat medium radiates heat to the indoor air by the use side heat exchanger 26a and the use side heat exchanger 26b, thereby heating the indoor space 7.
- the heat medium flows out of the use-side heat exchanger 26a and the use-side heat exchanger 26b and flows into the heat medium flow control device 25a and the heat medium flow control device 25b.
- the heat medium flow control device 25a and the heat medium flow control device 25b are operated to control the flow rate of the heat medium to a flow rate necessary to cover the air conditioning load required indoors, so that the use side heat exchanger 26a. And it flows into the use side heat exchanger 26b.
- the heat medium flowing out of the heat medium flow control device 25a and the heat medium flow control device 25b passes through the first heat medium flow switching device 22a and the first heat medium flow switching device 22b, and the heat exchanger related to heat medium 15a. And flows into the heat exchanger related to heat medium 15b, and is sucked into the pump 21a and the pump 21b again.
- the heat medium is directed from the second heat medium flow switching device 23 to the first heat medium flow switching device 22 via the heat medium flow control device 25.
- the air conditioning load required in the indoor space 7 includes the temperature detected by the first temperature sensor 31a, the temperature detected by the first temperature sensor 31b, and the temperature detected by the second temperature sensor 34. It is possible to cover by controlling so that the difference between the two is kept at the target value.
- the outlet temperature of the heat exchanger related to heat medium 15 either the temperature of the first temperature sensor 31a or the first temperature sensor 31b may be used, or the average temperature thereof may be used.
- the first heat medium flow switching device 22 and the second heat medium flow switching device 23 ensure a flow path that flows to both the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b.
- the intermediate opening is set.
- the usage-side heat exchanger 26a should be controlled by the temperature difference between the inlet and the outlet, but the temperature of the heat medium on the inlet side of the usage-side heat exchanger 26 is detected by the first temperature sensor 31b. By using the first temperature sensor 31b, the number of temperature sensors can be reduced and the system can be configured at low cost.
- FIG. 8 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the cooling main operation mode.
- the cooling main operation mode will be described by taking as an example a case where a cooling load is generated in the use side heat exchanger 26a and a heating load is generated in the use side heat exchanger 26b.
- a pipe represented by a thick line shows a pipe through which the refrigerant (heat source side refrigerant and heat medium) circulates.
- the flow direction of the heat source side refrigerant is indicated by solid line arrows, and the flow direction of the heat medium is indicated by broken line arrows.
- the first refrigerant flow switching device 11 is switched so that the heat source side refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12.
- the pump 21a and the pump 21b are driven, the heat medium flow control device 25a and the heat medium flow control device 25b are opened, and the heat medium flow control device 25c and the heat medium flow control device 25d are fully closed.
- the heat medium is circulated between the heat exchanger related to heat medium 15a and the use side heat exchanger 26a, and between the heat exchanger related to heat medium 15b and the use side heat exchanger 26b.
- the low-temperature and low-pressure heat source side refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the first refrigerant flow switching device 11. Then, the heat source side heat exchanger 12 condenses while radiating heat to the outdoor air, and becomes a two-phase refrigerant.
- the two-phase refrigerant that has flowed out of the heat source side heat exchanger 12 flows out of the outdoor unit 1 through the check valve 13a, the branching portion 27a, and flows into the heat medium relay unit 3 through the refrigerant pipe 4. .
- the two-phase refrigerant that has flowed into the heat medium relay unit 3 flows into the heat exchanger related to heat medium 15b that acts as a condenser through the second refrigerant flow switching device 18b.
- the two-phase refrigerant that has flowed into the heat exchanger related to heat medium 15b is condensed and liquefied while dissipating heat to the heat medium circulating in the heat medium circuit B, and becomes liquid refrigerant.
- the liquid refrigerant flowing out of the heat exchanger related to heat medium 15b is expanded by the expansion device 16b and becomes a low-pressure two-phase refrigerant. This low-pressure two-phase refrigerant flows into the heat exchanger related to heat medium 15a acting as an evaporator via the expansion device 16a.
- the low-pressure two-phase refrigerant that has flowed into the heat exchanger related to heat medium 15a absorbs heat from the heat medium circulating in the heat medium circuit B, and becomes a low-pressure gas refrigerant while cooling the heat medium.
- the gas refrigerant flows out of the heat exchanger related to heat medium 15a, flows out of the heat medium converter 3 via the second refrigerant flow switching device 18a, and flows into the outdoor unit 1 again through the refrigerant pipe 4.
- the heat-source-side refrigerant that has flowed into the outdoor unit 1 is sucked into the compressor 10 again via the branch portion 27b, the check valve 13d, the first refrigerant flow switching device 11 and the accumulator 19. .
- the opening degree of the expansion device 16b is controlled so that the superheat obtained as the difference between the temperature detected by the third temperature sensor 35a and the temperature detected by the third temperature sensor 35b becomes constant.
- the expansion device 16a is fully open, the opening / closing device 17a is closed, and the opening / closing device 17b is closed.
- the expansion device 16b controls the opening degree so that a subcool obtained as a difference between a value obtained by converting the pressure detected by the pressure sensor 36 into a saturation temperature and a temperature detected by the third temperature sensor 35d is constant. May be.
- the expansion device 16b may be fully opened, and the superheat or subcool may be controlled by the expansion device 16a.
- FIG. 9 is a diagram showing a ph diagram (pressure-enthalpy diagram) in the cooling main operation mode according to the first embodiment.
- the air conditioner 100 performs an operation of lowering the discharge temperature using the injection circuit. The operation at this time will be described with reference to FIGS.
- the low-temperature and low-pressure gas refrigerant sucked from the suction port of the compressor 10 is introduced into the sealed container, and the low-temperature and low-pressure gas refrigerant filled in the sealed container is sucked into the compression chamber (not shown). Is done. While the compression chamber is rotated 0 to 360 degrees by a motor (not shown), the internal volume decreases, and the internal heat source side refrigerant is compressed and the pressure and temperature rise. When the rotation angle of the motor reaches a certain angle, the opening opens (the state at this time is point F in FIG. 9), and the inside of the compression chamber and the injection pipe 4c outside the compressor 10 communicate with each other. It has become.
- the heat-source-side refrigerant compressed by the compressor 10 is condensed in the heat-source-side heat exchanger 12 to become a high-pressure two-phase refrigerant (point J in FIG. 9), and passes through the check valve 13a.
- the injection opening / closing device 24 is opened, and this high-pressure two-phase refrigerant is branched at the branching portion 27a, flows into the injection piping 4c via the injection opening / closing device 24 and the branching piping 4d, and is decompressed by the expansion device 14b to be low temperature.
- the medium-pressure two-phase refrigerant is used (point K in FIG. 9), and flows into the compression chamber from the opening provided in the compression chamber of the compressor 10.
- the medium-pressure gas refrigerant (point F in FIG. 9) and the low-temperature medium-pressure two-phase refrigerant (point K in FIG. 9) are mixed, so that the temperature of the heat source side refrigerant decreases.
- the temperature at this time is a temperature corresponding to the point H in FIG.
- the discharge temperature of the heat source side refrigerant discharged from the compressor 10 decreases.
- the discharge temperature of the compressor 10 is a temperature corresponding to the point I in FIG.
- the discharge temperature of the compressor 10 when the injection is not performed is a temperature corresponding to the point G in FIG. From the above, it can be seen that by performing the injection, the discharge temperature is lowered from the temperature corresponding to the point G to the temperature corresponding to the point I.
- the branching portion 27a has a structure and an arrangement of the branching portion 27a that diverts the heat source side refrigerant in a state in which the heat source side refrigerant flows in the direction opposite to the gravity direction. By doing so, the two-phase refrigerant can be uniformly distributed.
- the heat-source-side refrigerant in the flow path from the injection opening / closing device 24 of the branch pipe 4d to the backflow prevention device 20 is a high-pressure refrigerant, and returns to the outdoor unit 1 from the heat medium converter 3 via the refrigerant pipe 4.
- the heat source side refrigerant reaching the portion 27b is a low pressure refrigerant.
- the backflow prevention device 20 prevents the heat-source-side refrigerant flowing from the branch pipe 4d to the branch portion 27b, and the action of the backflow prevention device 20 prevents the high-pressure refrigerant in the branch pipe 4d from mixing with the low-pressure refrigerant in the branch portion 27b. It is preventing.
- the injection opening / closing device 24 may be one that can change the opening area of an electronic expansion valve or the like as long as it can switch the passage or non-passage of the refrigerant, in addition to the one that can switch the opening and closing of a solenoid valve or the like.
- the backflow prevention device 20 may be a check valve, or may be one that can switch opening and closing of an electromagnetic valve or the like, or one that can change opening and closing of a flow path by changing the opening area of an electronic expansion valve or the like. Further, even in the cooling main operation, since the heat source side refrigerant does not flow through the expansion device 14a, an arbitrary opening degree may be set.
- the control device 50 prevents the discharge temperature of the compressor 10 detected by the discharge refrigerant temperature detection device 37 from becoming too high.
- the opening area of the diaphragm device 14b is controlled.
- a control method when it is determined that the discharge temperature exceeds a certain value (for example, 110 ° C., etc.), it may be controlled to open by a certain degree of opening, for example, 10 pulses, or the discharge temperature is a target value. You may make it control the opening degree of the expansion device 14b so that it may become (for example, 100 degreeC).
- the expansion device 14b may be a capillary tube, and an amount of the heat source side refrigerant corresponding to the pressure difference may be injected.
- the heat of the heat source side refrigerant is transmitted to the heat medium in the heat exchanger related to heat medium 15b, and the heated heat medium is caused to flow in the pipe 5 by the pump 21b.
- the cold heat of the heat source side refrigerant is transmitted to the heat medium by the heat exchanger related to heat medium 15a, and the cooled heat medium is caused to flow in the pipe 5 by the pump 21a.
- the heat medium pressurized and discharged by the pump 21a and the pump 21b passes through the second heat medium flow switching device 23a and the second heat medium flow switching device 23b, and the use side heat exchanger 26a and the use side heat exchange. Flows into the vessel 26b.
- the heat medium radiates heat to the indoor air, thereby heating the indoor space 7. Further, in the use side heat exchanger 26a, the heat medium absorbs heat from the indoor air, thereby cooling the indoor space 7.
- the heat medium flow control device 25a and the heat medium flow control device 25b are operated to control the flow rate of the heat medium to a flow rate necessary to cover the air conditioning load required indoors, so that the use side heat exchanger 26a. And it flows into the use side heat exchanger 26b.
- the heat medium whose temperature has slightly decreased after passing through the use side heat exchanger 26b flows into the heat exchanger related to heat medium 15b through the heat medium flow control device 25b and the first heat medium flow switching device 22b, and again.
- the heat medium whose temperature has slightly increased after passing through the use side heat exchanger 26a flows into the heat exchanger related to heat medium 15a through the heat medium flow control device 25a and the first heat medium flow switching device 22a, and again. It is sucked into the pump 21a.
- the warm heat medium and the cold heat medium are not mixed by the action of the first heat medium flow switching device 22 and the second heat medium flow switching device 23, and the use side has a heat load and a heat load, respectively. It is introduced into the heat exchanger 26.
- the first heat medium flow switching device 22 from the second heat medium flow switching device 23 via the heat medium flow control device 25 on both the heating side and the cooling side.
- the heat medium is flowing in the direction to
- the air conditioning load required in the indoor space 7 is the difference between the temperature detected by the first temperature sensor 31b on the heating side and the temperature detected by the second temperature sensor 34 on the heating side, This can be covered by controlling the difference between the temperature detected by the two temperature sensor 34 and the temperature detected by the first temperature sensor 31a so as to keep the target value.
- FIG. 10 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the heating main operation mode.
- the heating main operation mode will be described by taking as an example a case where a heat load is generated in the use side heat exchanger 26a and a heat load is generated in the use side heat exchanger 26b.
- a pipe represented by a thick line indicates a pipe through which the refrigerant (heat source side refrigerant and heat medium) circulates.
- the flow direction of the heat source side refrigerant is indicated by a solid line arrow, and the flow direction of the heat medium is indicated by a broken line arrow.
- the first refrigerant flow switching device 11 causes the heat source side refrigerant discharged from the compressor 10 to heat without passing through the heat source side heat exchanger 12. It switches so that it may flow into the media converter 3.
- the pump 21a and the pump 21b are driven, the heat medium flow control device 25a and the heat medium flow control device 25b are opened, and the heat medium flow control device 25c and the heat medium flow control device 25d are fully closed.
- the heat medium circulates between the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b and between the use side heat exchanger 26b and the use side heat exchanger 26a.
- the low-temperature and low-pressure heat source side refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, conducts through the first connection pipe 4a, passes through the check valve 13b, and passes through the branch portion 27a to the outdoor. Out of machine 1.
- the high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit 1 flows into the heat medium relay unit 3 through the refrigerant pipe 4.
- the high-temperature and high-pressure gas refrigerant that has flowed into the heat medium relay unit 3 flows into the heat exchanger related to heat medium 15b that acts as a condenser through the second refrigerant flow switching device 18b.
- the gas refrigerant flowing into the heat exchanger related to heat medium 15b is condensed and liquefied while dissipating heat to the heat medium circulating in the heat medium circuit B, and becomes liquid refrigerant.
- the liquid refrigerant that has flowed out of the heat exchanger related to heat medium 15b is expanded by the expansion device 16b and becomes a medium-pressure two-phase refrigerant.
- This medium pressure two-phase refrigerant flows into the heat exchanger related to heat medium 15a acting as an evaporator via the expansion device 16a.
- the medium-pressure two-phase refrigerant that has flowed into the heat exchanger related to heat medium 15a evaporates by absorbing heat from the heat medium circulating in the heat medium circuit B, thereby cooling the heat medium.
- This low-pressure two-phase refrigerant flows out of the heat exchanger related to heat medium 15a, flows out of the heat medium converter 3 via the second refrigerant flow switching device 18a, and flows again into the outdoor unit 1 through the refrigerant pipe 4. To do.
- the heat-source-side refrigerant that has flowed into the outdoor unit 1 flows into the second connection pipe 4b via the branching portion 27b, passes through the expansion device 14a, is throttled by the expansion device 14a, and becomes a low-temperature and low-pressure two-phase refrigerant. It flows into the heat source side heat exchanger 12 which acts as an evaporator through the valve 13c. Then, the heat source side refrigerant flowing into the heat source side heat exchanger 12 absorbs heat from the outdoor air by the heat source side heat exchanger 12 and becomes a low-temperature and low-pressure gas refrigerant. The low-temperature and low-pressure gas refrigerant flowing out from the heat source side heat exchanger 12 is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
- the expansion device 16b has an opening degree so that a subcool obtained as a difference between a value obtained by converting the pressure detected by the pressure sensor 36 into a saturation temperature and a temperature detected by the third temperature sensor 35b is constant. Be controlled.
- the expansion device 16a is fully open, the opening / closing device 17a is closed, and the opening / closing device 17b is closed. Note that the expansion device 16b may be fully opened, and the subcooling may be controlled by the expansion device 16a.
- FIG. 11 is a diagram showing a ph diagram (pressure-enthalpy diagram) in the heating main operation mode according to the first embodiment.
- the air conditioning apparatus 100 performs an operation of lowering the discharge temperature using the injection circuit. The operation at this time will be described with reference to FIGS.
- the low-temperature and low-pressure gas refrigerant sucked from the suction port of the compressor 10 is introduced into the sealed container, and the low-temperature and low-pressure gas refrigerant filled in the sealed container is sucked into the compression chamber (not shown). Is done. While the compression chamber is rotated 0 to 360 degrees by a motor (not shown), the internal volume decreases, and the internal heat source side refrigerant is compressed and the pressure and temperature rise. When the rotation angle of the motor reaches a certain angle, the opening opens (the state at this time is point F in FIG. 11), and the inside of the compression chamber and the injection pipe 4c outside the compressor 10 communicate with each other. It has become.
- the heat-source-side refrigerant that returns from the heat medium relay unit 3 to the outdoor unit 1 via the refrigerant pipe 4 flows to the expansion device 14a via the branch portion 27b.
- the pressure of the heat source side refrigerant on the upstream side of the expansion device 14a is controlled to an intermediate pressure state (point J in FIG. 11).
- the two-phase refrigerant that has been brought into the intermediate pressure state by the expansion device 14a is branched by the branch portion 27b, flows into the branch pipe 4d, and flows to the injection pipe 4c through the backflow prevention device 20.
- the pressure is reduced by the expansion device 14b to become a low-temperature / medium-pressure two-phase refrigerant whose pressure is slightly reduced (point K in FIG. 11), and flows into the compression chamber from the opening provided in the compression chamber of the compressor 10.
- the medium-pressure gas refrigerant point F in FIG. 11
- the low-temperature medium-pressure two-phase refrigerant point K in FIG. 11
- the temperature at this time is a temperature corresponding to the point H in FIG.
- the discharge temperature of the heat source side refrigerant discharged from the compressor 10 decreases.
- the discharge temperature of the compressor 10 is a temperature corresponding to the point I in FIG. Further, the discharge temperature of the compressor 10 when the injection is not performed is a temperature corresponding to the point G in FIG. From the above, it can be seen that by performing the injection, the discharge temperature is lowered from the temperature corresponding to the point G to the temperature corresponding to the point I.
- the branching portion 27b has a structure and an arrangement of the branching portion 27b that diverts the heat source side refrigerant in a state where the heat source side refrigerant flows in the direction opposite to the direction of gravity. By doing so, the two-phase refrigerant can be uniformly distributed.
- the injection opening / closing device 24 In the heating main operation mode, the injection opening / closing device 24 is closed, and the high-pressure heat-source-side refrigerant is mixed with the intermediate-pressure heat-source-side refrigerant that has passed through the backflow prevention device 20 from the branch portion 27a. Is prevented.
- the injection opening / closing device 24 may be one that can change the opening area of an electronic expansion valve or the like as long as it can switch the passage or non-passage of the refrigerant, as well as the one that can switch the opening and closing of an electromagnetic valve or the like.
- the backflow prevention device 20 may be a check valve, or may be one that can switch opening and closing of an electromagnetic valve or the like, or one that can change opening and closing of a flow path by changing the opening area of an electronic expansion valve or the like. Further, it is desirable that the expansion device 14a can change the opening area of an electronic expansion valve or the like. If an electronic expansion valve is used, the intermediate pressure upstream of the expansion device 14a can be controlled to an arbitrary pressure. For example, if the intermediate pressure detected by the intermediate pressure detection device 32 is controlled to be a constant value, the discharge temperature control by the expansion device 14b is stabilized. However, the expansion device 14a is not limited to the electronic expansion valve.
- a plurality of opening areas may be selected by combining open / close valves such as small solenoid valves, or a medium pressure may be formed according to the pressure loss of the heat source side refrigerant by using a capillary tube.
- open / close valves such as small solenoid valves
- a medium pressure may be formed according to the pressure loss of the heat source side refrigerant by using a capillary tube.
- the controllability is slightly deteriorated, but the discharge temperature can be controlled as a target.
- the intermediate pressure detection device 32 may calculate the intermediate pressure by, for example, the control device 50 based on the temperature detected using not only the pressure sensor but also the temperature sensor. Further, when the opening area of the expansion device 14b can be changed, such as an electronic expansion valve, the control device 50 does not cause the discharge temperature of the compressor 10 detected by the discharge refrigerant temperature detection device 37 to be too high. Thus, the opening area of the diaphragm device 14b is controlled. As a control method, when it is determined that the discharge temperature exceeds a certain value (for example, 110 ° C., etc.), it may be controlled to open by a certain degree of opening, for example, 10 pulses, or the discharge temperature is a target value.
- a certain value for example, 110 ° C., etc.
- the expansion device 14b may be a capillary tube, and an amount of the heat source side refrigerant corresponding to the pressure difference may be injected.
- the heat medium is cooled in the heat exchanger related to heat medium 15a.
- the pressure (medium pressure) of the heat source side refrigerant on the upstream side of the expansion device 14a cannot be controlled so high. If the intermediate pressure cannot be increased, the amount of heat source side refrigerant injected into the compression chamber is reduced, and the amount of decrease in the discharge temperature is reduced.
- the operation in the heating main operation mode is not performed when the outside air temperature is low (for example, the outside air temperature is ⁇ 5 ° C. or lower). Further, when the outside air temperature is high, the discharge temperature is not so high. For this reason, there is no problem because the injection amount need not be so large.
- the expansion device 14a can cool the heat medium with the heat exchanger 15a between heat mediums, and the injection amount can be safely set to an intermediate pressure that can supply a sufficient amount to the compression chamber to lower the discharge temperature. You can drive.
- control of the diaphragm device 14a and the diaphragm device 14b by the control device 50 is not limited to this.
- the expansion device 14b may be fully opened, and the discharge temperature of the compressor 10 may be controlled only by the expansion device 14a. In this way, control is simplified, and there is an advantage that an inexpensive device can be used for the expansion device 14b.
- the intermediate pressure cannot be freely controlled, and it is necessary to control the expansion device 14a in consideration of both the intermediate pressure and the discharge temperature.
- the heat of the heat source side refrigerant is transmitted to the heat medium in the heat exchanger related to heat medium 15b, and the heated heat medium is caused to flow in the pipe 5 by the pump 21b.
- the cold heat of the heat source side refrigerant is transmitted to the heat medium by the heat exchanger related to heat medium 15a, and the cooled heat medium is caused to flow in the pipe 5 by the pump 21a.
- the heat medium pressurized and discharged by the pump 21a and the pump 21b passes through the second heat medium flow switching device 23a and the second heat medium flow switching device 23b, and the use side heat exchanger 26a and the use side heat exchange. Flows into the vessel 26b.
- the heat medium absorbs heat from the indoor air, thereby cooling the indoor space 7. Further, in the use side heat exchanger 26a, the heat medium radiates heat to the indoor air, thereby heating the indoor space 7.
- the heat medium flow control device 25a and the heat medium flow control device 25b are operated to control the flow rate of the heat medium to a flow rate necessary to cover the air conditioning load required indoors, so that the use side heat exchanger 26a. And it flows into the use side heat exchanger 26b.
- the heat medium that has passed through the use-side heat exchanger 26b and has risen slightly in temperature passes through the heat medium flow control device 25b and the first heat medium flow switching device 22b, flows into the heat exchanger related to heat medium 15a, and again It is sucked into the pump 21a.
- the heat medium that has passed through the use-side heat exchanger 26a and whose temperature has slightly decreased flows through the heat medium flow control device 25a and the first heat medium flow switching device 22a into the heat exchanger related to heat medium 15b, and again It is sucked into the pump 21b.
- the warm heat medium and the cold heat medium are not mixed by the action of the first heat medium flow switching device 22 and the second heat medium flow switching device 23, and the use side has a heat load and a heat load, respectively. It is introduced into the heat exchanger 26.
- the first heat medium flow switching device 22 from the second heat medium flow switching device 23 via the heat medium flow control device 25 on both the heating side and the cooling side.
- the heat medium is flowing in the direction to
- the air conditioning load required in the indoor space 7 is the difference between the temperature detected by the first temperature sensor 31b on the heating side and the temperature detected by the second temperature sensor 34 on the heating side, This can be covered by controlling the difference between the temperature detected by the two temperature sensor 34 and the temperature detected by the first temperature sensor 31a so as to keep the target value.
- aperture device 14a and / or aperture device 14b The operation in each operation mode and the injection into the compression chamber of the compressor 10 are performed as described above. Accordingly, the refrigerant in the two-phase state flows into the expansion device 14a in the heating only operation mode and the heating main operation mode. Further, liquid refrigerant flows into the expansion device 14b when in the cooling only operation mode, and heat source side refrigerant in a two-phase state flows during the cooling main operation mode, the heating only operation mode, and the heating main operation mode.
- the expansion device 14 When an electronic expansion valve is used as the expansion device 14a and / or the expansion device 14b (herein referred to as the expansion device 14), when the two-phase heat source side refrigerant flows in, the gas refrigerant and the liquid refrigerant are separated. In this case, the state in which the gas flows through the throttling portion and the state in which the liquid flows separately occur, and the pressure on the outlet side of the throttling device may not be stable. In particular, when the dryness is small, separation between the gas refrigerant and the liquid refrigerant occurs, and the pressure tends to become unstable.
- FIG. 12 is a diagram showing the structure of the expansion device 14a and / or the expansion device 14b.
- each throttle device 14 includes an inflow pipe 41, an outflow pipe 42, a throttle part (medium pressure refrigerant throttle part, injection refrigerant throttle part) 43, a valve body 44, a motor 45, and a stirring device 46.
- a stirrer (medium pressure refrigerant stirrer, injection refrigerant stirrer) 46 is inserted into the inflow pipe 41.
- the two-phase refrigerant that has flowed in from the inflow pipe 41 reaches the agitating device 46, and the gas refrigerant and the liquid refrigerant are agitated almost uniformly by the action of the agitating device 46.
- the two-phase refrigerant in which the gas refrigerant and the liquid refrigerant are almost uniformly mixed is squeezed by the valve body 44 at the throttle portion 43, depressurized, and flows out from the outflow pipe 42.
- the position of the valve body 44 is controlled by the motor 45, and the throttle amount at the throttle unit 43 is controlled.
- the control device 50 controls the motor 45.
- the stirring device 46 may be any device as long as it can create a state in which the gas refrigerant and the liquid refrigerant are almost uniformly mixed.
- foam metal is a porous metal having the same three-dimensional network structure as a resin foam such as sponge, and has the highest porosity (porosity) among the metal porous bodies (80% to 97%). Is.
- the inner diameter of the pipe is D and the length of the pipe is L
- the flow inside the pipe reaches a distance where the L / D is 8 to 10 from a portion having a structure that disturbs the flow. It has been clarified in the field of fluid dynamics that the influence of turbulence is eliminated and the flow is restored. Therefore, the inner diameter of the inflow pipe of the expansion device 14 is D, the length from the agitation device 46 to the expansion unit 43 is L, and the agitation device 46 is installed at a position where L / D is 6 or less.
- the two-phase refrigerant stirred by the stirring device 46 can reach the throttle portion 43 while being stirred, and the control can be stabilized.
- the air conditioner 100 has several operation modes. In these operation modes, the heat source side refrigerant flows through the refrigerant pipe 4 that connects the outdoor unit 1 and the heat medium relay unit 3.
- a heat medium such as water or antifreeze liquid flows through the pipe 5 connecting the heat medium converter 3 and the indoor unit 2.
- the defrosting operation will be described.
- the low-temperature and low-pressure heat-source-side refrigerant below the freezing point flows in the piping of the heat-source-side heat exchanger 12 serving as an evaporator.
- frost forms on the heat source side heat exchanger 12 and the surroundings.
- frost formation occurs in the heat source side heat exchanger 12
- the frost layer becomes a thermal resistance, and the flow path around which the air around the heat source side heat exchanger 12 flows becomes narrow and the air hardly flows.
- FIG. 13 is a refrigerant circuit diagram illustrating a refrigerant flow in the defrosting operation of the air conditioner 100.
- the defrosting operation in this Embodiment is demonstrated based on FIG.
- the heat source side refrigerant is compressed by the compressor 10, heated, discharged from the compressor 10, and flows into the heat source side heat exchanger 12 through the first refrigerant flow switching device 11. Then, heat is radiated by the heat source side heat exchanger 12 to melt the frost adhering to the surroundings.
- the heat-source-side refrigerant that has flowed out of the heat-source-side heat exchanger 12 passes through the check valve 13a, reaches the branching portion 27a, and is branched at the branching portion 27a.
- One flow branched in the branching portion 27 a flows out of the outdoor unit 1 and flows into the heat medium relay unit 3 through the refrigerant pipe 4.
- the heat-source-side refrigerant flowing into the heat medium relay unit 3 flows out of the heat medium relay unit 3 through the open / close device 17a and the open switch device 17b, and passes through the refrigerant pipe 4. Then flows into the outdoor unit 1 again.
- the heat-source-side refrigerant that has flowed into the outdoor unit 1 is sucked into the compressor 10 again via the branch portion 27b, the check valve 13d, the first refrigerant flow switching device 11 and the accumulator 19. .
- the expansion device 16a and the expansion device 16b are fully closed or have a small opening at which the heat source side refrigerant does not flow, and the heat medium side heat exchanger 15a and the heat medium heat exchanger 15b include the heat source side refrigerant. Is prevented from flowing.
- the other flow divided by the branch portion 27a flows into the branch pipe 4d, flows into the injection pipe 4c through the open injection opening / closing device 24, and passes through the throttle device 14b in the fully open state. 10 is injected into the compression chamber 10, and merges with the heat source side refrigerant (one flow divided by the branching portion 27 a) sucked into the compressor 10 through the accumulator 19.
- the pump 21b is operated to circulate the heat medium to the use side heat exchanger 26 (26a and 26b) having a heating request.
- the heating operation can be continued by the warm heat stored in the heat medium.
- the pump 21a may be operated, or during the defrosting operation, the pump 21a and the pump 21b may be stopped to stop the heating operation.
- the heat source side refrigerant is branched at the branching portion 27a, and a part of the heat source side refrigerant is transferred to the compressor 10. Injection into the compression chamber. In this way, it is possible to easily transfer the residual heat of the compressor 10 directly to the heat source side refrigerant, and an efficient defrosting operation can be performed. Moreover, since the refrigerant
- the expansion devices 14a, 14b, etc. are used for the cooling only operation with the heat source side heat exchanger as the condenser, the cooling main operation, the heating only operation with the evaporator, and heating.
- the heat source side refrigerant can be injected into the compressor 1 having the low-pressure shell structure by passing through the injection pipe 4c.
- any operation mode operation mode
- the mixed refrigerant includes a mixed refrigerant containing HFO1234yf having a lower global warming potential than R410A and having an environmentally effective mass ratio of R32 and R32 of 62% or more, or HFO1234ze having a mass ratio of R32 of 43% or more.
- a mixed refrigerant it is effective for a heat source side refrigerant whose discharge temperature is higher than that of R410A.
- the branch portions 27a and 27b allow the heat source side refrigerant to flow from the heat source side heat exchanger 12 side to the heat medium converter 3 (inter-heat medium heat exchanger 15) side, and from the heat medium converter 3 side to the heat source side heat exchanger 12 side.
- the heat source side refrigerant flowing into the flow path and flowing into the injection pipe 4c via the branch pipe 4d, the heat source side refrigerant can be injected regardless of the operation mode.
- coolant can be branched more uniformly.
- the two-phase refrigerant can be stirred by providing the stirring device 46 for the expansion devices 14a and 14b.
- the throttle device 14 can be passed while maintaining the stirring effect.
- the stirring apparatus 46 has a porous metal (foamed metal) with a porosity of 80% or more, the heat source side refrigerant can be stirred with a simple configuration.
- the heat source side refrigerant can be circulated through the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b without flowing, the heat medium on the heat medium circuit B side even during the defrosting operation.
- the heating operation can be continued by the heat stored in the.
- the pressure sensor 36a is installed in a flow path between the heat exchanger related to heat medium 15a acting as the cooling side in the cooling / heating mixed operation and the second refrigerant flow switching device 18a, and the pressure sensor 36b is mixed in the cooling / heating combination.
- movement, and the expansion apparatus 16b was demonstrated.
- the saturation temperature can be calculated with high accuracy.
- the pressure sensor 36b may be installed in the flow path between the heat exchanger related to heat medium 15b and the expansion device 16b, and the calculation accuracy does not deteriorate so much.
- the pressure sensor 36a is connected to the heat medium heat exchanger when the amount of pressure loss can be estimated or the heat medium heat exchanger with a small pressure loss is used. You may install in the flow path between 15a and the 2nd refrigerant flow switching device 18a.
- the air conditioning apparatus 100 when only the heating load or the cooling load is generated in the use side heat exchanger 26, the corresponding first heat medium flow switching device 22 and second heat medium flow switching device 23 are connected.
- the intermediate opening degree is set so that the heat medium flows through both the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b.
- each indoor unit 2 performs heating operation and cooling operation. It can be done freely.
- the first heat medium flow switching device 22 and the second heat medium flow switching device 23 described in the embodiment are capable of switching a three-way flow path such as a three-way valve, or a two-way flow path such as an on-off valve. What is necessary is just to switch a flow path, such as combining two things to open and close.
- the first heat medium can be obtained by combining two things, such as a stepping motor driven mixing valve, which can change the flow rate of the three-way flow path, and two things, such as an electronic expansion valve, which can change the flow rate of the two-way flow path.
- the flow path switching device 22 and the second heat medium flow path switching device 23 may be used. In this case, it is possible to prevent water hammer due to sudden opening and closing of the flow path.
- the case where the heat medium flow control device 25 is a two-way valve has been described as an example. You may make it do.
- the heat medium flow control device 25 may be a stepping motor driven type that can control the flow rate flowing through the flow path, and may be a two-way valve or a one-way valve with one end closed. Further, as the heat medium flow control device 25, a device that opens and closes a two-way flow path such as an open / close valve may be used, and the average flow rate may be controlled by repeating ON / OFF.
- coolant flow path switching device 18 was shown as if it were a four-way valve, it is not restricted to this, A two-way flow-path switching valve and a plurality of three-way flow-path switching valves are used similarly. You may comprise so that a heat source side refrigerant
- the heat medium for example, brine (antifreeze), water, a mixture of brine and water, a mixture of water and an additive having a high anticorrosive effect, or the like can be used. Therefore, in the air conditioning apparatus 100, even if the heat medium leaks into the indoor space 7 through the indoor unit 2, it contributes to the improvement of safety because a highly safe heat medium is used. Become.
- the heat source side heat exchanger 12 and the use side heat exchangers 26a to 26d are equipped with a blower, and in many cases, condensation or evaporation is promoted by blowing, but this is not restrictive.
- a blower for example, as the use side heat exchangers 26a to 26d, a panel heater using radiation can be used, and as the heat source side heat exchanger 12, a water-cooled type in which heat is transferred by water or antifreeze liquid. Any material can be used as long as it can dissipate heat or absorb heat.
- the number of pumps 21a and 21b is not limited to one, and a plurality of small capacity pumps may be arranged in parallel.
- FIG. FIG. 14 is a schematic circuit configuration diagram illustrating an example of a circuit configuration of the air-conditioning apparatus 100 according to Embodiment 2.
- a refrigerant-refrigerant heat exchanger (inter-refrigerant heat exchanger) 28 is attached to an injection pipe 4c connected to an opening of a compression chamber of the compressor 10.
- the refrigerant-refrigerant heat exchanger 28 performs heat exchange between the heat source side refrigerant before being decompressed by the expansion device 14b and the heat source side refrigerant after being decompressed.
- FIG. 15 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 according to Embodiment 2 is in the cooling only operation mode.
- the low-temperature and low-pressure heat source side refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the first refrigerant flow switching device 11. Then, the heat source side heat exchanger 12 condenses and liquefies while radiating heat to the outdoor air, and becomes a high-pressure liquid refrigerant.
- the high-pressure liquid refrigerant that has flowed out of the heat source side heat exchanger 12 flows out of the outdoor unit 1 through the check valve 13a, the branch part 27a, and flows into the heat medium relay unit 3 through the refrigerant pipe 4. .
- the high-pressure liquid refrigerant flowing into the heat medium relay unit 3 is branched after passing through the opening / closing device 17a and expanded by the expansion device 16a and the expansion device 16b to become a low-temperature low-pressure two-phase refrigerant.
- This two-phase refrigerant flows into each of the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b acting as an evaporator, and absorbs heat from the heat medium circulating in the heat medium circulation circuit B. It becomes a low-temperature and low-pressure gas refrigerant while cooling.
- the gas refrigerant flowing out from the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b flows out from the heat medium converter 3 via the second refrigerant flow switching device 18a and the second refrigerant flow switching device 18b.
- the refrigerant flows into the outdoor unit 1 again through the refrigerant pipe 4.
- the heat-source-side refrigerant that has flowed into the outdoor unit 1 is sucked into the compressor 10 again via the branch portion 27b, the check valve 13d, the first refrigerant flow switching device 11 and the accumulator 19. .
- FIG. 16 is a diagram showing a ph diagram (pressure-enthalpy diagram) in the cooling only operation mode according to the second embodiment.
- movement etc. in which the air conditioning apparatus 100 reduces discharge temperature using an injection circuit are demonstrated using FIG. 15 and FIG.
- the internal volume decreases, and the internal heat source side refrigerant is compressed. Increase in pressure and temperature.
- the opening opens (the state at this time is point F in FIG. 16), and the inside of the compression chamber communicates with the injection pipe 4c outside the compressor 10.
- the heat-source-side refrigerant compressed by the compressor 10 is condensed and liquefied by the heat-source-side heat exchanger 12 to become a high-pressure liquid refrigerant (point J in FIG. 16), and enters the branching portion 27a via the check valve 13a. It reaches.
- the injection opening / closing device 24 is opened, and the high-pressure liquid refrigerant is branched at the branching portion 27a and flows into the injection pipe 4c via the injection opening / closing device 24 and the branching pipe 4d. Then, the pressure is reduced by the expansion device 14b via the refrigerant-refrigerant heat exchanger 28 to obtain a low-temperature / medium-pressure two-phase refrigerant.
- the refrigerant-refrigerant heat exchanger 28 performs heat exchange between the heat source side refrigerant before being decompressed by the expansion device 14b and the heat source side refrigerant after being decompressed.
- the heat source side refrigerant before flowing into the expansion device 14b is cooled by the heat source side refrigerant whose pressure and temperature are reduced by the refrigerant-refrigerant heat exchanger 28 (the temperature corresponds to the point J 'in FIG. 16). Temperature).
- the refrigerant-refrigerant heat exchanger 28 After being depressurized by the expansion device 14b (point K ′ in FIG. 16), the refrigerant-refrigerant heat exchanger 28 is heated by the heat source side refrigerant before decompression (point K in FIG. 16) and flows into the compression chamber.
- the expansion device 14b may not be able to perform stable control. By doing in this way, even if the subcooling (supercooling degree) at the outlet of the heat source side heat exchanger 12 is small due to a small amount of the refrigerant enclosed, the liquid refrigerant is reliably supplied to the expansion device 14b. And stable control becomes possible.
- FIG. 17 is a refrigerant circuit diagram illustrating the refrigerant flow when the air-conditioning apparatus 100 is in the heating only operation mode.
- the low-temperature and low-pressure heat source side refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, conducts through the first connection pipe 4 a, passes through the check valve 13 b and the branch portion 27 a, and then from the outdoor unit 1. leak.
- the high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit 1 flows into the heat medium relay unit 3 through the refrigerant pipe 4.
- the high-temperature and high-pressure gas refrigerant that has flowed into the heat medium relay unit 3 is branched and passes through the second refrigerant flow switching device 18a and the second refrigerant flow switching device 18b, so that the heat exchanger related to heat medium 15a and the heat medium are heated. It flows into each of the heat exchangers 15b.
- the high-temperature and high-pressure gas refrigerant that has flowed into the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b is condensed and liquefied while dissipating heat to the heat medium circulating in the heat medium circuit B, and becomes a high-pressure liquid refrigerant.
- the liquid refrigerant that has flowed out of the heat exchanger related to heat medium 15a and the heat exchanger related to heat medium 15b is expanded by the expansion device 16a and the expansion device 16b, and becomes a two-phase refrigerant or liquid refrigerant of medium temperature and intermediate pressure.
- the two-phase refrigerant or liquid refrigerant flows out of the heat medium relay unit 3 through the opening / closing device 17b, and flows into the outdoor unit 1 through the refrigerant pipe 4 again.
- the heat-source-side refrigerant that has flowed into the outdoor unit 1 flows into the second connection pipe 4b via the branching portion 27b, passes through the expansion device 14a, is throttled by the expansion device 14a, and becomes a low-temperature and low-pressure two-phase refrigerant. It passes through the valve 13c and flows into the heat source side heat exchanger 12 acting as an evaporator.
- the heat source side refrigerant flowing into the heat source side heat exchanger 12 absorbs heat from the outdoor air in the heat source side heat exchanger 12 and becomes a low-temperature and low-pressure gas refrigerant.
- the low-temperature and low-pressure gas refrigerant flowing out from the heat source side heat exchanger 12 is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
- FIG. 18 is a diagram showing a ph diagram (pressure-enthalpy diagram) in the heating only operation mode according to the second embodiment.
- movement etc. in which the air conditioning apparatus 100 reduces discharge temperature using an injection circuit are demonstrated using FIG. 17 and FIG.
- the internal volume decreases, and the internal heat source side refrigerant is compressed. Increase in pressure and temperature.
- the opening opens (the state at this time is point F in FIG. 18), and the inside of the compression chamber communicates with the injection pipe 4c outside the compressor 10.
- the pressure of the flow of the heat source side refrigerant in the air conditioner 100 is controlled to an intermediate pressure state (point J in FIG. 18).
- the two-phase refrigerant or liquid refrigerant brought into the intermediate pressure state by the expansion device 14a is branched by the branching portion 27b, flows into the branch pipe 4d, and flows to the injection pipe 4c through the backflow prevention device 20.
- the refrigerant flows into the expansion device 14b via the refrigerant-refrigerant heat exchanger 28 and is depressurized to become a low-temperature / medium-pressure two-phase refrigerant whose pressure is slightly reduced.
- the refrigerant-refrigerant heat exchanger 28 performs heat exchange between the heat source side refrigerant before being decompressed by the expansion device 14b and the heat source side refrigerant after being decompressed.
- the heat-source-side refrigerant before flowing into the expansion device 14b is cooled by the heat-source-side refrigerant whose pressure and temperature are reduced by the refrigerant-refrigerant heat exchanger 28 (the temperature corresponds to the point J ′ in FIG. 18). Temperature).
- the refrigerant-refrigerant heat exchanger 28 After being depressurized by the expansion device 14b (point K ′ in FIG. 18), the refrigerant-refrigerant heat exchanger 28 is heated by the heat source side refrigerant before decompression (point K in FIG. 18) and flows into the compression chamber. If the heat source side refrigerant in the two-phase state flows in, the expansion device 14b may not be able to perform stable control. In this way, the medium-pressure two-phase heat source side refrigerant can be changed to a medium-pressure liquid refrigerant and flowed into the expansion device 14b, and stable control can be performed.
- FIG. 19 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the cooling main operation mode.
- the low-temperature and low-pressure heat source side refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the first refrigerant flow switching device 11. Then, the heat source side heat exchanger 12 condenses while radiating heat to the outdoor air, and becomes a two-phase refrigerant.
- the two-phase refrigerant that has flowed out of the heat source side heat exchanger 12 flows out of the outdoor unit 1 through the check valve 13a, the branching portion 27a, and flows into the heat medium relay unit 3 through the refrigerant pipe 4. .
- the two-phase refrigerant that has flowed into the heat medium relay unit 3 flows into the heat exchanger related to heat medium 15b that acts as a condenser through the second refrigerant flow switching device 18b.
- the two-phase refrigerant that has flowed into the heat exchanger related to heat medium 15b is condensed and liquefied while dissipating heat to the heat medium circulating in the heat medium circuit B, and becomes liquid refrigerant.
- the liquid refrigerant flowing out of the heat exchanger related to heat medium 15b is expanded by the expansion device 16b and becomes a low-pressure two-phase refrigerant. This low-pressure two-phase refrigerant flows into the heat exchanger related to heat medium 15a acting as an evaporator via the expansion device 16a.
- the low-pressure two-phase refrigerant that has flowed into the heat exchanger related to heat medium 15a absorbs heat from the heat medium circulating in the heat medium circuit B, and becomes a low-pressure gas refrigerant while cooling the heat medium.
- the gas refrigerant flows out of the heat exchanger related to heat medium 15a, flows out of the heat medium converter 3 via the second refrigerant flow switching device 18a, and flows into the outdoor unit 1 again through the refrigerant pipe 4.
- the heat-source-side refrigerant that has flowed into the outdoor unit 1 is sucked into the compressor 10 again via the branch portion 27b, the check valve 13d, the first refrigerant flow switching device 11 and the accumulator 19. .
- FIG. 20 is a diagram showing a ph diagram (pressure-enthalpy diagram) in the cooling main operation mode according to the second embodiment.
- movement etc. in which the air conditioning apparatus 100 reduces discharge temperature using an injection circuit are demonstrated using FIG. 19 and FIG.
- the internal volume decreases, and the internal heat source side refrigerant is compressed. Increase in pressure and temperature.
- the opening opens (the state at this time is point F in FIG. 20), and the inside of the compression chamber communicates with the injection pipe 4c outside the compressor 10.
- the heat-source-side refrigerant compressed by the compressor 10 is condensed by the heat-source-side heat exchanger 12 to become a high-pressure two-phase refrigerant (point J in FIG. 20), and reaches the branching portion 27a via the check valve 13a.
- the injection opening / closing device 24 is opened, and the high-pressure two-phase refrigerant is branched at the branching portion 27a and flows into the injection piping 4c via the injection switching device 24 and the branch piping 4d. Then, the pressure is reduced by the expansion device 14b via the refrigerant-refrigerant heat exchanger 28 to obtain a low-temperature / medium-pressure two-phase refrigerant.
- the refrigerant-refrigerant heat exchanger 28 performs heat exchange between the heat source side refrigerant before being decompressed by the expansion device 14b and the heat source side refrigerant after being decompressed.
- the heat-source-side refrigerant before flowing into the expansion device 14b is cooled by the heat-source-side refrigerant whose pressure and temperature are reduced by the refrigerant-refrigerant heat exchanger 28 (the temperature corresponds to the point J ′ in FIG. 20). Temperature).
- the refrigerant-refrigerant heat exchanger 28 After being depressurized by the expansion device 14b (point K ′ in FIG. 20), the refrigerant-refrigerant heat exchanger 28 is heated by the heat source side refrigerant before decompression (point K in FIG.
- the expansion device 14b may not be able to perform stable control. By doing so, the high-pressure two-phase heat-source-side refrigerant can be converted into a high-pressure liquid refrigerant and flowed into the expansion device 14b, thereby enabling stable control.
- FIG. 21 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the heating main operation mode.
- the low-temperature and low-pressure heat source side refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, conducts through the first connection pipe 4a, passes through the check valve 13b, and passes through the branch portion 27a to the outdoor. Out of machine 1.
- the high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit 1 flows into the heat medium relay unit 3 through the refrigerant pipe 4.
- the high-temperature and high-pressure gas refrigerant that has flowed into the heat medium relay unit 3 flows into the heat exchanger related to heat medium 15b that acts as a condenser through the second refrigerant flow switching device 18b.
- the gas refrigerant flowing into the heat exchanger related to heat medium 15b is condensed and liquefied while dissipating heat to the heat medium circulating in the heat medium circuit B, and becomes liquid refrigerant.
- the liquid refrigerant that has flowed out of the heat exchanger related to heat medium 15b is expanded by the expansion device 16b and becomes a medium-pressure two-phase refrigerant.
- This medium pressure two-phase refrigerant flows into the heat exchanger related to heat medium 15a acting as an evaporator via the expansion device 16a.
- the medium-pressure two-phase refrigerant that has flowed into the heat exchanger related to heat medium 15a evaporates by absorbing heat from the heat medium circulating in the heat medium circuit B, thereby cooling the heat medium.
- the medium pressure two-phase refrigerant flows out of the heat exchanger related to heat medium 15a, flows out of the heat medium converter 3 via the second refrigerant flow switching device 18a, passes through the refrigerant pipe 4 and returns to the outdoor unit 1 again. Inflow.
- the heat-source-side refrigerant that has flowed into the outdoor unit 1 flows into the second connection pipe 4b via the branching portion 27b, passes through the expansion device 14a, is throttled by the expansion device 14a, and becomes a low-temperature and low-pressure two-phase refrigerant. It flows into the heat source side heat exchanger 12 which acts as an evaporator through the valve 13c. Then, the heat source side refrigerant flowing into the heat source side heat exchanger 12 absorbs heat from the outdoor air by the heat source side heat exchanger 12 and becomes a low-temperature and low-pressure gas refrigerant. The low-temperature and low-pressure gas refrigerant flowing out from the heat source side heat exchanger 12 is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
- FIG. 22 is a diagram showing a ph diagram (pressure-enthalpy diagram) in the heating main operation mode according to the second embodiment.
- movement etc. in which the air conditioning apparatus 100 reduces discharge temperature using an injection circuit are demonstrated using FIG. 21 and FIG.
- the internal volume decreases, and the internal heat source side refrigerant is compressed. Increase in pressure and temperature.
- the opening opens (the state at this time is a point F in FIG. 22), and the inside of the compression chamber communicates with the injection pipe 4c outside the compressor 10.
- the pressure of the flow of the heat source side refrigerant in the air conditioner 100 is controlled to an intermediate pressure state (point J in FIG. 22).
- the two-phase refrigerant that has been brought into the intermediate pressure state by the expansion device 14a is branched by the branch portion 27b, flows into the branch pipe 4d, and flows into the injection pipe 4c through the backflow prevention device 20.
- the refrigerant flows into the expansion device 14b through the refrigerant-refrigerant heat exchanger 28 and is depressurized to become a low-temperature / medium-pressure two-phase refrigerant with a reduced pressure.
- the refrigerant-refrigerant heat exchanger 28 performs heat exchange between the heat source side refrigerant before being decompressed by the expansion device 14b and the heat source side refrigerant after being decompressed.
- the heat-source-side refrigerant before flowing into the expansion device 14b is cooled by the heat-source-side refrigerant whose pressure and temperature are reduced by the refrigerant-refrigerant heat exchanger 28 (the temperature corresponds to the point J ′ in FIG. 22).
- the refrigerant-refrigerant heat exchanger 28 After being depressurized by the expansion device 14b (point K ′ in FIG. 22), the refrigerant-refrigerant heat exchanger 28 is heated by the heat source side refrigerant before decompression (point K in FIG. 22) and flows into the compression chamber. If the heat source side refrigerant in the two-phase state flows in, the expansion device 14b may not be able to perform stable control. In this way, the medium-pressure two-phase heat source side refrigerant can be changed to a medium-pressure liquid refrigerant and flowed into the expansion device 14b, and stable control can be performed.
- the refrigerant-refrigerant heat exchanger 28 is provided so that the refrigerant flowing into the expansion device 14b becomes a liquid refrigerant. As a result, hunting and the like can be prevented and stable control becomes possible.
- Embodiment 3 FIG.
- the compressor 10, the first refrigerant flow switching device 11, the heat source side heat exchanger 12, the expansion device 14 a, the expansion device 14 b, the switching device 17, and the backflow prevention device 20 are accommodated in the outdoor unit 1. did.
- the use side heat exchanger 26 was accommodated in the indoor unit 2, and the heat exchanger related to heat medium 15 and the expansion device 16 were accommodated in the heat medium converter 3.
- the outdoor unit 1 and the heat medium converter 3 are connected by a set of two pipes, the heat source side refrigerant is circulated between the outdoor unit 1 and the heat medium converter 3, and the indoor unit 2 and the heat medium
- the medium converter 3 is connected to each other by a pair of pipes, the heat medium is circulated between the indoor unit 2 and the heat medium converter 3, and the heat source side refrigerant and
- the system for exchanging heat with the heat medium has been described as an example, but the present invention is not limited to this.
- FIG. 23 is a diagram illustrating the configuration of the air-conditioning apparatus according to Embodiment 3.
- the compressor 10, the first refrigerant flow switching device 11, the heat source side heat exchanger 12, the expansion device 14 a, the expansion device 14 b, the opening / closing device 17 and the backflow prevention device 20 are accommodated in the outdoor unit 1.
- the load-side heat exchanger 26 and the expansion device 16 that serve as an evaporator or a condenser to exchange heat between the air in the air-conditioning target space and the refrigerant are accommodated in the indoor unit 2, and are separated from the outdoor unit 1 and the indoor unit 2.
- a relay unit 3A serving as a formed relay unit is provided, the outdoor unit 1 and the relay unit 3A are connected by a set of two pipes, and the indoor unit 2 and the relay unit 3A are each set of two sets.
- Direct expansion that can be connected by a pipe and circulates refrigerant between the outdoor unit 1 and the indoor unit 2 via the relay unit 3A to perform a cooling only operation, a heating only operation, a cooling main operation, or a heating main operation. It can also be applied to the system and has the same effect.
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- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
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Abstract
Description
この発明の実施の形態1について、図面に基づいて説明する。
室外機1には、圧縮機10と、四方弁等の第1冷媒流路切替装置11と、第一の熱交換器となる熱源側熱交換器12と、アキュムレーター19とが冷媒配管4で直列に接続されて搭載されている。また、室外機1には、第1接続配管4a、第2接続配管4b、逆止弁13a、逆止弁13b、逆止弁13c、および、逆止弁13dが設けられている。第1接続配管4a、第2接続配管4b、逆止弁13a、逆止弁13b、逆止弁13c、および、逆止弁13dを設けることで、室内機2の要求する運転に関わらず、熱媒体変換機3に流入出する熱源側冷媒の流れを一定方向にすることができる。
室内機2には、それぞれ利用側熱交換器26が搭載されている。この利用側熱交換器26は、配管5によって熱媒体変換機3の熱媒体流量調整装置25と第2熱媒体流路切替装置23に接続するようになっている。この利用側熱交換器26は、図示省略の送風機から供給される空気と熱媒体との間で熱交換を行い、室内空間7に供給するための暖房用空気あるいは冷房用空気を生成するものである。
熱媒体変換機3には、2つの熱媒体間熱交換器15と、2つの絞り装置16と、2つの開閉装置17と、2つの第2冷媒流路切替装置18と、が搭載されている。また、2つのポンプ21と、4つの第1熱媒体流路切替装置22と、4つの第2熱媒体流路切替装置23と、4つの熱媒体流量調整装置25と、が搭載されている。
図4は、空気調和装置100の全冷房運転モード時における冷媒の流れを示す冷媒回路図である。この図4では、利用側熱交換器26aおよび利用側熱交換器26bでのみ冷熱負荷が発生している場合を例に全冷房運転モードについて説明する。なお、図4では、太線で表された配管が冷媒(熱源側冷媒および熱媒体)の流れる配管を示している。また、図4では、熱源側冷媒の流れ方向を実線矢印で、熱媒体の流れ方向を破線矢印で示している。
低温低圧の冷媒が圧縮機10によって圧縮され、高温高圧のガス冷媒となって吐出される。圧縮機10から吐出された高温高圧のガス冷媒は、第1冷媒流路切替装置11を介して熱源側熱交換器12に流入する。そして、熱源側熱交換器12で室外空気に放熱しながら凝縮液化し、高圧液冷媒となる。熱源側熱交換器12から流出した高圧液冷媒は、逆止弁13aを通って、分岐部27aを介して、室外機1から流出し、冷媒配管4を通って熱媒体変換機3に流入する。熱媒体変換機3に流入した高圧液冷媒は、開閉装置17aを経由した後に分岐されて絞り装置16aおよび絞り装置16bで膨張させられて、低温低圧の二相冷媒となる。
全冷房運転モードでは、熱媒体間熱交換器15aおよび熱媒体間熱交換器15bの双方で熱源側冷媒の冷熱が熱媒体に伝えられ、冷やされた熱媒体がポンプ21aおよびポンプ21bによって配管5内を流動させられることになる。ポンプ21aおよびポンプ21bで加圧されて流出した熱媒体は、第2熱媒体流路切替装置23aおよび第2熱媒体流路切替装置23bを介して、利用側熱交換器26aおよび利用側熱交換器26bに流入する。そして、熱媒体が利用側熱交換器26aおよび利用側熱交換器26bで室内空気から吸熱することで、室内空間7の冷房を行う。
図6は、空気調和装置100の全暖房運転モード時における冷媒の流れを示す冷媒回路図である。この図6では、利用側熱交換器26aおよび利用側熱交換器26bでのみ温熱負荷が発生している場合を例に全暖房運転モードについて説明する。なお、図6では、太線で表された配管が冷媒(熱源側冷媒および熱媒体)の流れる配管を示している。また、図6では、熱源側冷媒の流れ方向を実線矢印で、熱媒体の流れ方向を破線矢印で示している。
低温低圧の熱源側冷媒が圧縮機10によって圧縮され、高温高圧のガス冷媒となって吐出される。圧縮機10から吐出された高温高圧のガス冷媒は、第1冷媒流路切替装置11を通り、第1接続配管4aを導通し、逆止弁13b、分岐部27aを通過し、室外機1から流出する。室外機1から流出した高温高圧のガス冷媒は、冷媒配管4を通って熱媒体変換機3に流入する。熱媒体変換機3に流入した高温高圧のガス冷媒は、分岐されて第2冷媒流路切替装置18aおよび第2冷媒流路切替装置18bを通って、熱媒体間熱交換器15aおよび熱媒体間熱交換器15bのそれぞれに流入する。
全暖房運転モードでは、熱媒体間熱交換器15aおよび熱媒体間熱交換器15bの双方で熱源側冷媒の温熱が熱媒体に伝えられ、暖められた熱媒体がポンプ21aおよびポンプ21bによって配管5内を流動させられることになる。ポンプ21aおよびポンプ21bで加圧されて流出した熱媒体は、第2熱媒体流路切替装置23aおよび第2熱媒体流路切替装置23bを介して、利用側熱交換器26aおよび利用側熱交換器26bに流入する。そして、熱媒体が利用側熱交換器26aおよび利用側熱交換器26bで室内空気に放熱することで、室内空間7の暖房を行う。
図8は、空気調和装置100の冷房主体運転モード時における冷媒の流れを示す冷媒回路図である。この図8では、利用側熱交換器26aで冷熱負荷が発生し、利用側熱交換器26bで温熱負荷が発生している場合を例に冷房主体運転モードについて説明する。なお、図8では、太線で表された配管が冷媒(熱源側冷媒および熱媒体)の循環する配管を示している。また、図8では、熱源側冷媒の流れ方向を実線矢印で、熱媒体の流れ方向を破線矢印で示している。
低温低圧の熱源側冷媒が圧縮機10によって圧縮され、高温高圧のガス冷媒となって吐出される。圧縮機10から吐出された高温高圧のガス冷媒は、第1冷媒流路切替装置11を介して熱源側熱交換器12に流入する。そして、熱源側熱交換器12で室外空気に放熱しながら凝縮し、二相冷媒となる。熱源側熱交換器12から流出した二相冷媒は、逆止弁13aを通って、分岐部27aを介して、室外機1から流出し、冷媒配管4を通って熱媒体変換機3に流入する。熱媒体変換機3に流入した二相冷媒は、第2冷媒流路切替装置18bを通って凝縮器として作用する熱媒体間熱交換器15bに流入する。
冷房主体運転モードでは、熱媒体間熱交換器15bで熱源側冷媒の温熱が熱媒体に伝えられ、暖められた熱媒体がポンプ21bによって配管5内を流動させられることになる。また、冷房主体運転モードでは、熱媒体間熱交換器15aで熱源側冷媒の冷熱が熱媒体に伝えられ、冷やされた熱媒体がポンプ21aによって配管5内を流動させられることになる。ポンプ21aおよびポンプ21bで加圧されて流出した熱媒体は、第2熱媒体流路切替装置23aおよび第2熱媒体流路切替装置23bを介して、利用側熱交換器26aおよび利用側熱交換器26bに流入する。
図10は、空気調和装置100の暖房主体運転モード時における冷媒の流れを示す冷媒回路図である。この図10では、利用側熱交換器26aで温熱負荷が発生し、利用側熱交換器26bで冷熱負荷が発生している場合を例に暖房主体運転モードについて説明する。なお、図10では、太線で表された配管が冷媒(熱源側冷媒および熱媒体)の循環する配管を示している。また、図10では、熱源側冷媒の流れ方向を実線矢印で、熱媒体の流れ方向を破線矢印で示している。
低温低圧の熱源側冷媒が圧縮機10によって圧縮され、高温高圧のガス冷媒となって吐出される。圧縮機10から吐出された高温高圧のガス冷媒は、第1冷媒流路切替装置11を通り、第1接続配管4aを導通し、逆止弁13bを通過し、分岐部27aを介して、室外機1から流出する。室外機1から流出した高温高圧のガス冷媒は、冷媒配管4を通って熱媒体変換機3に流入する。熱媒体変換機3に流入した高温高圧のガス冷媒は、第2冷媒流路切替装置18bを通って凝縮器として作用する熱媒体間熱交換器15bに流入する。
暖房主体運転モードでは、熱媒体間熱交換器15bで熱源側冷媒の温熱が熱媒体に伝えられ、暖められた熱媒体がポンプ21bによって配管5内を流動させられることになる。また、暖房主体運転モードでは、熱媒体間熱交換器15aで熱源側冷媒の冷熱が熱媒体に伝えられ、冷やされた熱媒体がポンプ21aによって配管5内を流動させられることになる。ポンプ21aおよびポンプ21bで加圧されて流出した熱媒体は、第2熱媒体流路切替装置23aおよび第2熱媒体流路切替装置23bを介して、利用側熱交換器26aおよび利用側熱交換器26bに流入する。
各運転モードの動作および圧縮機10の圧縮室へのインジェクションは以上のように行われる。従って、絞り装置14aには、全暖房運転モードおよび暖房主体運転モードのときに、二相状態の冷媒が流れ込む。また、絞り装置14bには、全冷房運転モードのときに液冷媒が流れ込み、冷房主体運転モード、全暖房運転モードおよび暖房主体運転モードのときに二相状態の熱源側冷媒が流れ込む。絞り装置14aまたは/および絞り装置14b(ここでは絞り装置14と記載する)として、電子式膨張弁を使用した場合、二相状態の熱源側冷媒が流入すると、ガス冷媒と液冷媒とが分離して流れている場合に、絞り部にガスが流れる状態と液が流れる状態とが別々に発生して、絞り装置の出口側の圧力が安定しない場合がある。特に、乾き度が小さい場合に、ガス冷媒と液冷媒との分離が発生し、圧力が不安定になる傾向が強い。
以上説明したように、本実施の形態に係る空気調和装置100は、幾つかの運転モードを具備している。これらの運転モードにおいては、室外機1と熱媒体変換機3とを接続する冷媒配管4には熱源側冷媒が流れている。
本実施の形態に係る空気調和装置100が実行する幾つかの運転モードにおいては、熱媒体変換機3と室内機2を接続する配管5には水や不凍液等の熱媒体が流れている。
全暖房運転モードおよび暖房主体運転モードにおいては、蒸発器となる熱源側熱交換器12の配管の内部に氷点下の低温低圧の熱源側冷媒が流れる。このため、熱源側熱交換器12の周囲の空気温度が低い場合、熱源側熱交換器12、周囲に着霜が起きる。熱源側熱交換器12に着霜が起きると、霜層が熱抵抗となり、かつ、熱源側熱交換器12の周囲の空気が流動する流路が狭くなり空気が流れ難くなる。このため、熱源側冷媒と空気との熱交換が阻害され、機器の暖房能力および運転効率が低下する。そこで、熱源側熱交換器12の着霜が増加した場合、熱源側熱交換器12、周囲の霜を融かす除霜運転を行う。
熱源側冷媒は圧縮機10によって圧縮され、加熱されて、圧縮機10から吐出され、第1冷媒流路切替装置11を介して熱源側熱交換器12に流入する。そして、熱源側熱交換器12で放熱し、周囲に付着した霜を融かす。熱源側熱交換器12から流出した熱源側冷媒は、逆止弁13aを通って、分岐部27aに至り、分岐部27aで分流される。
図14は、実施の形態2に係る空気調和装置100の回路構成の一例を示す概略回路構成図である。発明の実施の形態2について、各図面に基づいて説明する。以下、実施の形態1と異なる部分を中心に説明する。本実施の形態の空気調和装置100には、圧縮機10の圧縮室の開口部に繋がるインジェクション配管4cに、冷媒-冷媒熱交換器(冷媒間熱交換器)28が取り付けられている。冷媒-冷媒熱交換器28は、絞り装置14bで減圧される前の熱源側冷媒と減圧された後の熱源側冷媒との熱交換を行う。
図15は、実施の形態2の空気調和装置100の全冷房運転モード時における冷媒の流れを示す冷媒回路図である。図15に示すように、低温低圧の熱源側冷媒が圧縮機10によって圧縮され、高温高圧のガス冷媒となって吐出される。圧縮機10から吐出された高温高圧のガス冷媒は、第1冷媒流路切替装置11を介して熱源側熱交換器12に流入する。そして、熱源側熱交換器12で室外空気に放熱しながら凝縮液化し、高圧液冷媒となる。熱源側熱交換器12から流出した高圧液冷媒は、逆止弁13aを通って、分岐部27aを介して、室外機1から流出し、冷媒配管4を通って熱媒体変換機3に流入する。熱媒体変換機3に流入した高圧液冷媒は、開閉装置17aを経由した後に分岐されて絞り装置16aおよび絞り装置16bで膨張させられて、低温低圧の二相冷媒となる。
図17は、空気調和装置100の全暖房運転モード時における冷媒の流れを示す冷媒回路図である。低温低圧の熱源側冷媒が圧縮機10によって圧縮され、高温高圧のガス冷媒となって吐出される。圧縮機10から吐出された高温高圧のガス冷媒は、第1冷媒流路切替装置11を通り、第1接続配管4aを導通し、逆止弁13b、分岐部27aを通過し、室外機1から流出する。室外機1から流出した高温高圧のガス冷媒は、冷媒配管4を通って熱媒体変換機3に流入する。熱媒体変換機3に流入した高温高圧のガス冷媒は、分岐されて第2冷媒流路切替装置18aおよび第2冷媒流路切替装置18bを通って、熱媒体間熱交換器15aおよび熱媒体間熱交換器15bのそれぞれに流入する。
図19は、空気調和装置100の冷房主体運転モード時における冷媒の流れを示す冷媒回路図である。低温低圧の熱源側冷媒が圧縮機10によって圧縮され、高温高圧のガス冷媒となって吐出される。圧縮機10から吐出された高温高圧のガス冷媒は、第1冷媒流路切替装置11を介して熱源側熱交換器12に流入する。そして、熱源側熱交換器12で室外空気に放熱しながら凝縮し、二相冷媒となる。熱源側熱交換器12から流出した二相冷媒は、逆止弁13aを通って、分岐部27aを介して、室外機1から流出し、冷媒配管4を通って熱媒体変換機3に流入する。熱媒体変換機3に流入した二相冷媒は、第2冷媒流路切替装置18bを通って凝縮器として作用する熱媒体間熱交換器15bに流入する。
図21は、空気調和装置100の暖房主体運転モード時における冷媒の流れを示す冷媒回路図である。低温低圧の熱源側冷媒が圧縮機10によって圧縮され、高温高圧のガス冷媒となって吐出される。圧縮機10から吐出された高温高圧のガス冷媒は、第1冷媒流路切替装置11を通り、第1接続配管4aを導通し、逆止弁13bを通過し、分岐部27aを介して、室外機1から流出する。室外機1から流出した高温高圧のガス冷媒は、冷媒配管4を通って熱媒体変換機3に流入する。熱媒体変換機3に流入した高温高圧のガス冷媒は、第2冷媒流路切替装置18bを通って凝縮器として作用する熱媒体間熱交換器15bに流入する。
上述の実施の形態では、圧縮機10、第一の冷媒流路切替装置11、熱源側熱交換器12、絞り装置14a、絞り装置14b、開閉装置17および逆流防止装置20を室外機1に収容した。さらに、利用側熱交換器26を室内機2に収容し、熱媒体間熱交換器15および絞り装置16を熱媒体変換機3に収容した。そして、室外機1と熱媒体変換機3との間を2本一組の配管で接続し、室外機1と熱媒体変換機3との間で熱源側冷媒を循環させ、室内機2と熱媒体変換機3との間をそれぞれ2本一組の配管で接続し、室内機2と熱媒体変換機3との間で熱媒体を循環させ、熱媒体間熱交換器15で熱源側冷媒と熱媒体とを熱交換させるシステムを例に説明を行ったが、これに限るものではない。
Claims (20)
- インジェクション配管を流れる冷媒が流入する開口部を設けた圧縮室を密閉容器内に有し、前記密閉容器内を低圧の冷媒圧雰囲気として、前記密閉容器内の低圧冷媒を前記圧縮室に流入させて圧縮する低圧シェル構造の圧縮機と、
冷媒を蒸発または凝縮させるための第一の熱交換器及び1以上の第二の熱交換器と、
前記冷媒を減圧する1以上の第一の絞り装置と、
前記第一の熱交換器に高圧の冷媒を通過させて凝縮器として機能させる場合と、前記第一の熱交換器に低圧の冷媒を通過させて蒸発器として機能させる場合とで流路を切り替える冷媒流路切替装置と、
前記第一の絞り装置を通過して前記第二の熱交換器側から前記第一の熱交換器側に流れる冷媒を、前記高圧よりも小さく前記低圧よりも大きい中圧の冷媒にするための第二の絞り装置と
を配管接続して冷媒循環回路を構成し、
前記インジェクション配管から前記圧縮室に流入させる前記冷媒の量を制御する制御装置を備え、
前記第一の熱交換器が凝縮器となる場合においては、前記第一の熱交換器側から前記第二の熱交換器側に流れる前記高圧の冷媒の一部をインジェクション配管に流すことができるようにし、前記第一の熱交換器が蒸発器となる場合においては、前記第二の絞り装置により前記中圧にした前記冷媒の一部をインジェクション配管に流すことができるようにする空気調和装置。 - 前記第一の熱交換器が凝縮器となる場合においては、前記冷媒は前記第二の絞り装置を通らずに前記第一の熱交換器と前記第二の熱交換器との間を流動し、前記高圧側から前記冷媒を前記開口部に導入し、前記第一の熱交換器が蒸発器となる場合においては、前記冷媒は前記第二の熱交換器から前記第二の絞り装置を通って前記第一の熱交換器側へ流れ、前記第二の絞り装置によって生成された前記中圧側からの前記冷媒を前記開口部に導入することを特徴とする請求項1に記載の空気調和装置。
- R32、R32およびHFO1234yfを含み、前記R32の質量比率が62%以上である混合冷媒、または、R32およびHFO1234zeを含み、前記R32の質量比率が43%以上である混合冷媒を、前記冷媒とする請求項1または請求項2に記載の空気調和装置。
- 前記第一の熱交換器が凝縮器となる場合の冷媒の流れにおいて前記第一の熱交換器と前記第一の絞り装置との間の流路に設置され、前記冷媒の一部を分流する第一の冷媒分岐手段と、
前記第一の熱交換器が蒸発器となる場合の冷媒の流れにおいて前記第二の熱交換器と前記第二の絞り装置との間の流路に設置され、前記冷媒の一部を分流する第二の冷媒分岐手段と、
前記第一の分岐手段と前記第二の分岐手段とを接続し、前記インジェクション配管との接続口を介して、分流に係る前記冷媒を前記インジェクション配管に流すための分岐配管と、
前記分岐配管に設置され、前記第一の分岐手段から前記インジェクション配管に前記冷媒を通過させるか否かを制御する開閉装置と、
前記分岐配管において、前記接続口と前記第二の分岐手段との間の流路に設置された逆流防止装置と、
前記インジェクション配管に設置された第三の絞り装置と
をさらに備える請求項1から請求項3のいずれかに記載の空気調和装置。 - 重力方向に対して反対の方向に冷媒の流れを形成して分流させるように、前記第一の分岐手段および前記第二の分岐手段を配置することを特徴とする請求項4に記載の空気調和装置。
- 前記第三の絞り装置は、
前記制御装置の指示に基づいて流路における開口面積を変化させるインジェクション冷媒絞り部と、
前記インジェクション冷媒絞り部より冷媒流入側において、二相状態の冷媒を攪拌させるインジェクション冷媒攪拌装置と
を備える請求項4または請求項5に記載の空気調和装置。 - 前記インジェクション冷媒絞り部と前記インジェクション冷媒攪拌装置との距離は、前記第三の絞り装置の前記冷媒流入側における配管の内径の6倍以下である請求項6に記載の空気調和装置。
- 前記インジェクション冷媒攪拌装置は、気孔率が80%以上の多孔質金属を有する請求項6または請求項7に記載の空気調和装置。
- 前記インジェクション配管に設置され、前記第三の絞り装置に流入する前記冷媒と前記第三の絞り装置から流出する前記冷媒とを熱交換させる冷媒-冷媒熱交換器をさらに備える請求項4から請求項8のいずれかに記載の空気調和装置。
- 前記第二の絞り装置は、
前記制御装置の指示に基づいて流路における開口面積を変化させる中圧冷媒絞り部と、
前記中圧冷媒絞り部より冷媒流入側に、二相状態の冷媒を攪拌させる中圧冷媒攪拌装置と
を備える請求項1から請求項9のいずれかに記載の空気調和装置。 - 前記中圧冷媒絞り部と前記中圧冷媒攪拌装置との距離は、前記第二の絞り装置の前記冷媒流入側における配管の内径の6倍以下である請求項10に記載の空気調和装置。
- 前記中圧冷媒攪拌装置は、気孔率が80%以上の多孔質金属を有する請求項10または請求項11に記載の空気調和装置。
- 前記中圧となる圧力を検出可能な位置に設置されて、圧力または温度を検出する中圧検出装置をさらに備え、
前記制御装置は、前記中圧検出装置の検出に係る圧力、前記中圧検出装置の検出に係る温度の飽和圧力、または、前記中圧検出装置の検出に係る温度若しくは圧力に基づく飽和温度が、目標に近づくように、または、目標とする範囲に収まるように、前記第二の絞り装置の駆動を制御する請求項1から請求項12のいずれかに記載の空気調和装置。 - 前記圧縮機、前記冷媒流路切替装置及び前記第一の熱交換器を収容する室外ユニットと、前記第一の絞り装置及び前記第二の熱交換器を収容する中継ユニットとを2本の冷媒配管で接続し、
さらに、前記中継ユニットと空調対象空間の空気を加熱または冷却する複数の室内機とを前記冷媒と異なる熱媒体を循環させるための配管で接続し、
前記2本の冷媒配管の一方に高圧の液冷媒が流れ、他方に低圧のガス冷媒が流れる全冷房運転モードと、前記2本の冷媒配管の一方に高圧のガス冷媒が流れ、他方に中圧の二相冷媒または中圧の液冷媒が流れる全暖房運転モードとを運転形態として有し、
前記制御装置は、
前記全冷房運転モードでの運転を行うときには、前記開閉装置を開にさせて、前記第一の分岐手段から前記開閉装置を介して前記インジェクション配管に高圧の液冷媒を流入させ、
前記全暖房運転モードでの運転を行うときには、前記開閉装置を閉にさせて、前記第二の分岐手段から前記インジェクション配管に前記中圧の二相冷媒または中圧の液冷媒を流入させる請求項4から請求項13のいずれかに記載の空気調和装置。 - 前記2本の冷媒配管の一方に高圧の二相冷媒が流れ、他方に低圧のガス冷媒が流れる冷房主体運転モードと、前記2本の冷媒配管の一方に高圧のガス冷媒が流れ、他方に中圧の二相冷媒が流れる暖房主体運転モードとを運転形態としてさらに有し、
前記制御装置は、
前記冷房主体運転モードでの運転を行うときには、前記開閉装置を開にさせて、前記第一の分岐手段から前記開閉装置を介して前記インジェクション配管に高圧の二相冷媒を流入させ、
前記暖房主体運転モードでの運転を行うときには、前記開閉装置を閉にさせて、前記第二の分岐手段から前記インジェクション配管に中圧の二相冷媒を流入させる請求項14に記載の空気調和装置。 - 前記圧縮機の吐出温度を検出するための吐出温度検出装置をさらに備え、
前記制御装置は、
前記第一の熱交換器を凝縮器として機能させる場合においては、前記吐出温度検出装置の検出温度が目標温度に近づくように、または、目標温度を超えないように、または、目標範囲に収まるように前記第三の絞り装置を制御し、
前記第一の熱交換器を蒸発器として機能させる場合においては、前記吐出温度検出装置の検出温度が目標温度に近づくように、または、目標温度を超えないように、または、目標範囲に収まるように前記第三の絞り装置、または、前記第二の絞り装置および前記第三の絞り装置を制御するものである請求項4から請求項15のいずれかに記載の空気調和装置。 - 前記圧縮機の吐出温度を検出するための吐出温度検出装置および前記圧縮機の高圧を検出するための高圧検出装置をさらに備え、
前記制御装置は、
前記第一の熱交換器を凝縮器として機能させる場合においては、前記吐出温度検出装置の検出温度および前記高圧検出装置の検出圧力から算出した吐出過熱度が目標過熱度に近づくように、または、目標過熱度を超えないように、または、目標範囲に収まるように前記第三の絞り装置を制御し、
前記第一の熱交換器を蒸発器として機能させる場合においては、前記吐出温度検出装置の検出温度および前記高圧検出装置の検出圧力から算出した吐出過熱度が目標過熱度に近づくように、または、目標過熱度を超えないように、または、目標範囲に収まるように前記第三の絞り装置、または、前記第二の絞り装置および前記第三の絞り装置を制御するものである請求項4から請求項15のいずれかに記載の空気調和装置。 - 前記制御装置は、前記第一の熱交換器の周囲に付着した霜を融かす除霜運転において、前記第一の熱交換器を通過して冷却された前記冷媒を、前記インジェクション配管を経由して前記圧縮室に流入させるように、前記第三絞り装置を制御する請求項1から請求項12、請求項14または請求項15のいずれかに記載の空気調和装置。
- 空調対象空間を空調可能な位置に設置され前記空調対象空間の空気と熱交換をする前記第二の熱交換器および前記第一の絞り装置を収容する室内機と、
前記圧縮機、前記冷媒流路切替装置、前記第一の熱交換器、前記第二の絞り装置、前記第三の絞り装置、前記開閉装置および前記逆流防止装置を収容し、室外または機械室に設置される室外ユニットと、
前記室外ユニットおよび前記室内機とは別体に形成される中継ユニットと、
前記室内機と前記中継ユニットとの間、および、前記室外ユニットと前記中継ユニットとの間を接続し、前記中継ユニットを介して前記室外ユニットと前記室内機との間に前記冷媒を循環させる2本1組の配管と
を備える請求項1から請求項18のいずれかに記載の空気調和装置。 - 空調対象空間を空調可能な位置に設置され前記空調対象空間の空気と熱交換をする利用側熱交換器を収容する室内機と、
前記圧縮機、前記冷媒流路切替装置、前記第一の熱交換器、前記第二の絞り装置、前記第三の絞り装置、前記開閉装置および前記逆流防止装置を収容し室外または機械室に設置される室外ユニットと、
前記第二の熱交換器および前記第一の絞り装置を収容し前記室外ユニットおよび前記室内機とは別体に形成される熱媒体変換機と、
前記室外ユニットと前記熱媒体変換機との間を接続し、前記冷媒を循環させる2本1組の配管と、
前記室内機と前記熱媒体変換機との間を接続し、前記冷媒とは異なる熱媒体を循環させる2本1組の配管とを備え、
前記冷媒と前記熱媒体とを前記第二の熱交換器で熱交換させる請求項1から請求項18のいずれかに記載の空気調和装置。
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014080463A1 (ja) * | 2012-11-21 | 2014-05-30 | 三菱電機株式会社 | 空気調和装置 |
WO2014080464A1 (ja) * | 2012-11-21 | 2014-05-30 | 三菱電機株式会社 | 空気調和装置 |
WO2014137968A3 (en) * | 2013-03-04 | 2014-11-06 | Johnson Controls Technology Company | A modular liquid based heating and cooling system |
WO2015001613A1 (ja) * | 2013-07-02 | 2015-01-08 | 三菱電機株式会社 | 冷凍サイクル装置 |
Families Citing this family (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9732992B2 (en) * | 2011-01-27 | 2017-08-15 | Mitsubishi Electric Corporation | Air-conditioning apparatus for preventing the freezing of non-azeotropic refrigerant |
JP5594267B2 (ja) * | 2011-09-12 | 2014-09-24 | ダイキン工業株式会社 | 冷凍装置 |
EP2863139B1 (en) * | 2012-04-23 | 2020-07-08 | Mitsubishi Electric Corporation | Air conditioning system |
EP2980408A4 (en) * | 2013-03-29 | 2016-12-21 | Johnson Controls-Hitachi Air Conditioning Tech (Hong Kong) Ltd | SCROLL COMPRESSORS |
JP6271195B2 (ja) * | 2013-09-18 | 2018-01-31 | サンデンホールディングス株式会社 | 車両用空気調和装置 |
EP3062040B1 (en) * | 2013-10-25 | 2021-12-15 | Mitsubishi Electric Corporation | Refrigeration cycle device |
US9883616B2 (en) * | 2014-09-29 | 2018-01-30 | International Business Machines Corporation | Manifold heat exchanger |
JP6482826B2 (ja) * | 2014-11-12 | 2019-03-13 | 三菱重工サーマルシステムズ株式会社 | 熱源システム及びその制御装置並びに制御方法 |
CN107532823A (zh) * | 2015-05-13 | 2018-01-02 | 三菱电机株式会社 | 制冷循环装置 |
CN109556327B (zh) * | 2017-09-26 | 2022-01-04 | 开利公司 | 节流分配组件和制冷*** |
GB201811307D0 (en) | 2018-07-10 | 2018-08-29 | Easy Airconditioning Ltd | Air conditioning system |
CN110857806B (zh) * | 2018-08-24 | 2022-07-22 | 广东松下环境***有限公司 | 送风装置的控制方法及应用其的送风装置 |
CN109386987B (zh) * | 2018-10-22 | 2020-12-29 | 广东美的暖通设备有限公司 | 两管制热回收多联机***及其空调室外机 |
CN111271892B (zh) * | 2018-12-05 | 2021-11-05 | 约克广州空调冷冻设备有限公司 | 制冷*** |
EP3911897A4 (en) | 2019-03-17 | 2022-03-16 | Ralph Feria | VALVE SYSTEM AND PROCESS |
KR20210096785A (ko) * | 2020-01-29 | 2021-08-06 | 엘지전자 주식회사 | 공기조화장치 및 그 제어방법 |
JP2021162205A (ja) * | 2020-03-31 | 2021-10-11 | ダイキン工業株式会社 | 空気調和装置 |
CN114427760B (zh) * | 2020-10-29 | 2023-08-22 | 深圳麦克维尔空调有限公司 | 空调机组及其控制方法 |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002107002A (ja) * | 2000-09-29 | 2002-04-10 | Mitsubishi Electric Corp | 冷凍装置 |
JP2003314930A (ja) * | 2002-04-19 | 2003-11-06 | Daikin Ind Ltd | 多室型空気調和機 |
JP2005282972A (ja) | 2004-03-30 | 2005-10-13 | Hitachi Ltd | 冷凍装置 |
JP2007263443A (ja) * | 2006-03-28 | 2007-10-11 | Mitsubishi Electric Corp | 空気調和装置 |
JP2008138921A (ja) * | 2006-11-30 | 2008-06-19 | Mitsubishi Electric Corp | 空気調和装置 |
JP2009127902A (ja) | 2007-11-21 | 2009-06-11 | Mitsubishi Electric Corp | 冷凍装置及び圧縮機 |
WO2009154149A1 (ja) * | 2008-06-16 | 2009-12-23 | 三菱電機株式会社 | 非共沸混合冷媒及び冷凍サイクル装置 |
WO2010049998A1 (ja) | 2008-10-29 | 2010-05-06 | 三菱電機株式会社 | 空気調和装置及び中継装置 |
JP2010112579A (ja) * | 2008-11-04 | 2010-05-20 | Daikin Ind Ltd | 冷凍装置 |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5585853A (en) * | 1978-12-20 | 1980-06-28 | Tokyo Shibaura Electric Co | Refrigeration cycle |
JPS57198941A (en) * | 1981-05-29 | 1982-12-06 | Sanyo Electric Co Ltd | Air conditioner |
JP3277665B2 (ja) * | 1993-12-29 | 2002-04-22 | ダイキン工業株式会社 | 空気調和機 |
JPH08313120A (ja) * | 1995-05-15 | 1996-11-29 | Matsushita Electric Ind Co Ltd | 3成分混合冷媒充填装置および充填方法 |
JPH1130445A (ja) * | 1997-07-10 | 1999-02-02 | Denso Corp | 冷凍サイクル装置 |
JP3980186B2 (ja) * | 1997-10-23 | 2007-09-26 | カルソニックカンセイ株式会社 | ヒートポンプ式自動車用空気調和装置 |
JP3379426B2 (ja) * | 1998-03-04 | 2003-02-24 | 株式会社日立製作所 | 蓄熱式空気調和機 |
JP3094997B2 (ja) * | 1998-09-30 | 2000-10-03 | ダイキン工業株式会社 | 冷凍装置 |
JP4123829B2 (ja) * | 2002-05-28 | 2008-07-23 | 三菱電機株式会社 | 冷凍サイクル装置 |
JP2004218964A (ja) * | 2003-01-16 | 2004-08-05 | Matsushita Electric Ind Co Ltd | 冷凍装置 |
JP4613526B2 (ja) * | 2004-06-23 | 2011-01-19 | 株式会社デンソー | 超臨界式ヒートポンプサイクル装置 |
JP4459776B2 (ja) * | 2004-10-18 | 2010-04-28 | 三菱電機株式会社 | ヒートポンプ装置及びヒートポンプ装置の室外機 |
JP4715561B2 (ja) * | 2006-03-06 | 2011-07-06 | ダイキン工業株式会社 | 冷凍装置 |
JP2007263433A (ja) * | 2006-03-28 | 2007-10-11 | Sanyo Electric Co Ltd | 冷媒サイクル装置及び冷媒サイクル装置用熱交換器 |
JP2008106738A (ja) * | 2006-09-29 | 2008-05-08 | Fujitsu General Ltd | ロータリ圧縮機およびヒートポンプシステム |
JP5132354B2 (ja) * | 2008-02-21 | 2013-01-30 | 三菱電機株式会社 | 空気調和装置 |
JP4989511B2 (ja) * | 2008-02-22 | 2012-08-01 | 三菱電機株式会社 | 空気調和装置 |
JP4931848B2 (ja) * | 2008-03-31 | 2012-05-16 | 三菱電機株式会社 | ヒートポンプ式給湯用室外機 |
JP2010078164A (ja) * | 2008-09-24 | 2010-04-08 | Fujitsu General Ltd | 冷凍空調装置 |
JP5277854B2 (ja) | 2008-10-14 | 2013-08-28 | ダイキン工業株式会社 | 空気調和装置 |
EP2416081B1 (en) | 2009-04-01 | 2024-03-20 | Mitsubishi Electric Corporation | Air-conditioning device |
JP4906894B2 (ja) * | 2009-08-21 | 2012-03-28 | 三菱電機株式会社 | ヒートポンプ装置及びヒートポンプ装置の室外機 |
-
2011
- 2011-01-31 EP EP11857510.9A patent/EP2672199B1/en active Active
- 2011-01-31 AU AU2011358037A patent/AU2011358037B2/en active Active
- 2011-01-31 JP JP2012555548A patent/JP5657030B2/ja active Active
- 2011-01-31 US US13/885,457 patent/US9671119B2/en active Active
- 2011-01-31 CN CN201180058104.2A patent/CN103238034B/zh active Active
- 2011-01-31 WO PCT/JP2011/000510 patent/WO2012104890A1/ja active Application Filing
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002107002A (ja) * | 2000-09-29 | 2002-04-10 | Mitsubishi Electric Corp | 冷凍装置 |
JP2003314930A (ja) * | 2002-04-19 | 2003-11-06 | Daikin Ind Ltd | 多室型空気調和機 |
JP2005282972A (ja) | 2004-03-30 | 2005-10-13 | Hitachi Ltd | 冷凍装置 |
JP2007263443A (ja) * | 2006-03-28 | 2007-10-11 | Mitsubishi Electric Corp | 空気調和装置 |
JP2008138921A (ja) * | 2006-11-30 | 2008-06-19 | Mitsubishi Electric Corp | 空気調和装置 |
JP2009127902A (ja) | 2007-11-21 | 2009-06-11 | Mitsubishi Electric Corp | 冷凍装置及び圧縮機 |
WO2009154149A1 (ja) * | 2008-06-16 | 2009-12-23 | 三菱電機株式会社 | 非共沸混合冷媒及び冷凍サイクル装置 |
WO2010049998A1 (ja) | 2008-10-29 | 2010-05-06 | 三菱電機株式会社 | 空気調和装置及び中継装置 |
JP2010112579A (ja) * | 2008-11-04 | 2010-05-20 | Daikin Ind Ltd | 冷凍装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2672199A4 |
Cited By (23)
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EP2924367A4 (en) * | 2012-11-21 | 2016-08-24 | Mitsubishi Electric Corp | AIR CONDITIONING |
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JPWO2014080464A1 (ja) * | 2012-11-21 | 2017-01-05 | 三菱電機株式会社 | 空気調和装置 |
WO2014080464A1 (ja) * | 2012-11-21 | 2014-05-30 | 三菱電機株式会社 | 空気調和装置 |
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US11079122B2 (en) | 2013-03-04 | 2021-08-03 | Johnson Controls Technology Company | Modular liquid based heating and cooling system |
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CN105190188A (zh) * | 2013-03-04 | 2015-12-23 | 江森自控科技公司 | 模块化液基加热和冷却*** |
GB2530453A (en) * | 2013-07-02 | 2016-03-23 | Mitsubishi Electric Corp | Refrigeration cycle device |
JPWO2015001613A1 (ja) * | 2013-07-02 | 2017-02-23 | 三菱電機株式会社 | 冷凍サイクル装置 |
GB2530453B (en) * | 2013-07-02 | 2018-02-14 | Mitsubishi Electric Corp | Refrigeration cycle device |
WO2015001613A1 (ja) * | 2013-07-02 | 2015-01-08 | 三菱電機株式会社 | 冷凍サイクル装置 |
Also Published As
Publication number | Publication date |
---|---|
EP2672199A1 (en) | 2013-12-11 |
US20130233008A1 (en) | 2013-09-12 |
EP2672199B1 (en) | 2019-04-10 |
JPWO2012104890A1 (ja) | 2014-07-03 |
EP2672199A4 (en) | 2016-12-14 |
AU2011358037A1 (en) | 2013-06-13 |
US9671119B2 (en) | 2017-06-06 |
AU2011358037B2 (en) | 2015-01-22 |
JP5657030B2 (ja) | 2015-01-21 |
CN103238034B (zh) | 2015-04-01 |
CN103238034A (zh) | 2013-08-07 |
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