WO2016010006A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2016010006A1 WO2016010006A1 PCT/JP2015/070080 JP2015070080W WO2016010006A1 WO 2016010006 A1 WO2016010006 A1 WO 2016010006A1 JP 2015070080 W JP2015070080 W JP 2015070080W WO 2016010006 A1 WO2016010006 A1 WO 2016010006A1
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- heat
- flow rate
- heat medium
- heat source
- heat exchanger
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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
- 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
- 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
- F24F11/84—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 using valves
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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
- F24F11/89—Arrangement or mounting of control or safety devices
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
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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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
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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
- 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
- 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
- F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
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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
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
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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
- F25B2313/02741—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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0312—Pressure sensors near the indoor 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0313—Pressure sensors near the outdoor 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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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
- F25B2313/031—Sensor arrangements
- F25B2313/0315—Temperature sensors near the outdoor 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
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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
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
Definitions
- the present invention relates to an air conditioner in which a plurality of indoor units are connected and air conditioning can be performed selectively or simultaneously for each indoor unit.
- a refrigerant circuit that circulates the refrigerant is configured by connecting a load side unit (such as an indoor unit) having a machine side heat exchanger with a refrigerant pipe. Then, in the indoor unit side heat exchanger, when the refrigerant evaporates and condenses, the heat, heat is released from the air in the air-conditioning target space to be heat exchanged, and the pressure, temperature, etc. related to the refrigerant in the refrigerant circuit are changed. Air conditioning is performed while changing.
- cooling and heating are automatically determined, respectively.
- an air conditioner that can perform heating and cooling simultaneous operation (cooling and heating mixed operation) that can perform heating (see, for example, Patent Document 1).
- a target value of the outlet temperature of the heat medium is obtained by a predetermined relationship from the inlet temperature of the heat medium supplied to the heat source device side heat exchanger and the frequency of the compressor, and the heat medium transporter is matched to this target value.
- an air conditioner that controls the frequency of a water pump (for example, a water pump) (see, for example, Patent Document 2).
- the air conditioning load ratio of the cooling and heating is substantially equal, and when performing the complete heat recovery operation, It is necessary to reduce the amount of heat exchange in the outdoor heat exchanger. In other words, in order to improve the comfort and energy saving of the air conditioner in heat recovery operation, it is necessary to bring the heat dissipation amount closer to zero if it is cooling-dominated operation, and it is necessary to bring the heat absorption amount closer to zero in the heating-dominated operation. . However, it is necessary to secure the compression ratio to a predetermined value or more (for example, 2 or more) for the equipment reliability of the compressor.
- AK the value needs to be lowered.
- it is an air heat exchanger, it is necessary to secure an outdoor fan above a certain level for cooling the electronic base of the outdoor unit, and if it is a water heat exchanger, the water flow rate is kept above a certain level due to pitting corrosion.
- the AK value cannot be reduced to a desired AK value, and the low pressure of the refrigeration cycle is reduced.
- the evaporation temperature needs to be kept at 0 ° C or higher to prevent the indoor unit from freezing.
- the equipment must be stopped to prevent the indoor unit from freezing.
- the present invention has been made in order to cope with the above-described problems, and during cooling and heating simultaneous operation performed by circulating a refrigerant between a heat source machine side heat exchanger and a use side heat exchanger, cooling operation or heating. Even when there are multiple usage-side heat exchangers in operation, stable control can be performed, and heat source-side heat exchange that exchanges heat with refrigerant according to the usage-side heat exchanger capacity
- An object of the present invention is to provide a highly efficient air conditioner by controlling the flow rate of the heat medium supplied to the chamber, thereby reducing the power consumption accompanying the heat medium supply.
- the air conditioner of the present invention is A compressor that compresses and discharges the refrigerant; A heat source machine side heat exchanger for exchanging heat between the refrigerant and the heat medium different from the refrigerant; A plurality of use side heat exchangers for exchanging heat between the refrigerant and the surrounding use medium; Provided between the heat source unit side heat exchanger and the plurality of use side heat exchangers, switching a part of the plurality of use side heat exchangers to a cooling operation, of the plurality of use side heat exchangers A repeater that switches a part to heating operation,
- a heat medium system capable of adjusting the flow rate of the heat medium supplied to the heat source machine side heat exchanger, it comprises at least one heat medium transporter, a heat medium flow controller, and a heat medium flow controller.
- the compressor and the heat source machine side heat exchanger are arranged in a heat source machine, and the use side heat exchanger is arranged in an indoor unit, According to a control command, each of the plurality of usage-side heat exchangers is switched to the cooling operation and the heating operation, and is an air conditioner that performs a cooling and heating simultaneous operation,
- a refrigerant is flowed according to a ratio of a total cooling capacity and a total heating capacity of the plurality of use side heat exchangers
- the heat medium flow control device controls the heat medium flow regulator using the heat medium inflow temperature to the heat source unit side heat exchanger and the heat medium outflow temperature from the heat source unit side heat exchanger, A heat medium flow rate supplied to the heat source unit side heat exchanger is controlled.
- the air conditioner of the present invention comfort can be maintained even when there are a plurality of use side heat exchangers performing cooling operation or heating operation during simultaneous cooling and heating operation. Further, by controlling the flow rate of the heat medium supplied to the heat source device based on the heat medium temperature difference calculated from the heat medium temperature detected by the heat medium temperature detecting means provided in the heat source device, according to the use side heat exchanger capacity The heat medium flow rate can be reduced, and the power consumption of the heat medium transporter (for example, a water pump) can also be reduced. Therefore, this configuration has an effect that a highly efficient simultaneous cooling and heating operation can be performed.
- the heat medium transporter for example, a water pump
- Embodiment 1 of this invention It is a figure which shows the structural example of the air conditioning apparatus in Embodiment 1 of this invention. It is a cooling-heating simultaneous operation in Embodiment 1 of this invention, Comprising: It is a figure which shows the structural example of the air conditioning apparatus 1 explaining the driving
- Embodiment 2 of this invention It is a figure explaining an example of the flowchart of the heat medium flow volume adjustment control in Embodiment 2 of this invention. It is a figure explaining an example of four patterns of the heat medium flow volume adjustment state in Embodiment 2 of this invention. It is a figure explaining an example of the relationship between the utilization side heat exchanger capacity
- FIG. 1 is a diagram illustrating a configuration example of an air-conditioning apparatus 1 according to Embodiment 1 of the present invention.
- the air conditioner 1 includes a heat source unit A, a relay unit B, an indoor unit C, and an indoor unit D, and includes a four-way valve 102, check valves 118 to 121, and the like.
- a cooling refrigeration cycle and a heating refrigeration cycle are formed, and a refrigerant is circulated to perform simultaneous cooling and heating operations.
- the pressure detected by the pressure detection means 126 and 127 and the temperature of the heat source machine detected by the temperature detection means 128 and 129 By controlling the temperature, the temperature of the refrigerant flowing into the individual use side heat exchangers 105c and 105d (sometimes collectively referred to as the use side heat exchanger 105) provided in each of the indoor units C and D is within a certain range. Keep inside. As a result, even when the cooling operation capacity and the heating operation capacity change during the simultaneous cooling and heating operation, the stable cooling and heating operation is continued at a low cost. In addition, it is good also as a structure provided with combined heat source machine A1, A2 as a heat source machine.
- the configuration of the heat source devices A1 and A2 may be the same as that of the heat source device A, for example.
- the relay unit B is provided between the heat source unit A, the indoor unit C, and the indoor unit D.
- the heat source machine A and the relay machine B are connected by a first connection pipe 106 and a second connection pipe 107 having a smaller pipe diameter than the first connection pipe 106.
- the relay machine B and the indoor unit C are connected by the 3rd connection piping 106c and the 4th connection piping 107c.
- the relay machine B and the indoor unit D are connected by the 5th connection piping 106d and the 6th connection piping 107d.
- the heat source machine A includes a compressor 101, a four-way valve 102, a heat source machine side heat exchanger 103, and an accumulator 104.
- the heat source machine A includes a check valve 118, a check valve 119, a check valve 120, and a check valve 121.
- the heat source machine A includes a fourth flow rate regulator 122, a gas-liquid separator 123, a fifth flow rate regulator 124, a switching valve 125, and a control unit 141.
- the heat source machine A includes first pressure detection means 126, second pressure detection means 127, and temperature detection means 128 and 129 on the refrigerant inlet side or the refrigerant outlet side of the heat source machine side heat exchanger 103, thereby The detected pressure and temperature are supplied to the control unit 141.
- the four-way valve 102 includes four ports. Each port includes a discharge side of the compressor 101, a heat source unit side heat exchanger 103, an accumulator 104, an outlet side of the check valve 119, and an inlet of the check valve 120. And the refrigerant flow path is switched.
- One of the heat source device side heat exchangers 103 is connected to the four-way valve 102, and the other is connected to a pipe connected to the fourth flow rate regulator 122 and the gas-liquid separator 123.
- the switching valve 125 is a valve that can be opened and closed, and is arranged in a circuit that bypasses the heat source apparatus side heat exchanger 103 and the fourth flow rate regulator 122.
- heat exchange with the refrigerant flowing in the refrigerant circuit therein is a heat medium different from the refrigerant, and is, for example, water or brine.
- the accumulator 104 is connected between the four-way valve 102 and the suction side of the compressor 101, separates the liquid refrigerant, and supplies the gas refrigerant to the compressor 101.
- the fifth flow rate regulator 124 is connected between the accumulator 104 and the gas-liquid separator 123, and regulates the refrigerant flowing into the heat source unit side heat exchanger 103.
- the compressor 101, the four-way valve 102, and the heat source device side heat exchanger 103 described above constitute a part of the refrigerant circuit.
- the check valve 118 is provided between the fourth flow rate regulator 122 connected to the heat source apparatus side heat exchanger 103 and the outlet side of the second connection pipe 107 and the check valve 120.
- the inlet side of the check valve 118 is connected to a pipe connected to the fourth flow regulator 122.
- the outlet side of the check valve 118 is connected to the second connection pipe 107 and a pipe connected to the outlet side of the check valve 120.
- the check valve 118 allows the refrigerant to flow only from one direction to the second connection pipe 107 via the fourth flow rate regulator 122 from the heat source apparatus side heat exchanger 103.
- the check valve 119 is provided between the inlet side of the four-way valve 102 and the check valve 120 and the inlet side of the first connection pipe 106 and the check valve 121.
- the inlet side of the check valve 119 is connected to a pipe connected to the first connection pipe 106 and the inlet side of the check valve 121.
- the outlet side of the check valve 119 is connected to a pipe connected to the four-way valve 102 and the inlet side of the check valve 120.
- the check valve 119 allows the refrigerant to flow only from one direction from the first connection pipe 106 to the four-way valve 102.
- the check valve 120 is provided between the outlet side of the four-way valve 102 and the check valve 119, the outlet side of the check valve 118, and the second connection pipe 107.
- the inlet side of the check valve 120 is connected to piping connected to the four-way valve 102 and the outlet side of the check valve 119.
- the outlet side of the check valve 120 is connected to a pipe connected to the outlet side of the check valve 118 and the second connection pipe 107.
- the check valve 120 allows the refrigerant to flow from the four-way valve 102 to the second connection pipe 107 only from one direction.
- the check valve 121 is provided between the inlet side of the check valve 119 and the first connection pipe 106 and the gas-liquid separator 123 connected to the heat source device side heat exchanger 103.
- the inlet side of the check valve 121 is connected to a pipe connected to the inlet side of the check valve 119 and the first connection pipe 106.
- the outlet side of the check valve 121 is connected to a pipe connected to the gas-liquid separator 123.
- the check valve 121 allows the refrigerant to flow only from one direction from the first connection pipe 106 to the gas-liquid separator 123.
- the check valve 118 to the check valve 121 described above constitute a flow path switching valve of the refrigerant circuit.
- the flow path switching valve and the relay unit B described later make it possible to form a refrigeration cycle for cooling operation and a refrigeration cycle for heating operation in the refrigerant circuit during simultaneous cooling and heating operation.
- One end of the fourth flow rate regulator 122 is connected to the inlet side of the check valve 118, and the other end is connected to the outlet side of the heat source device side heat exchanger 103 and the gas-liquid separator 123.
- the outlet side of the check valve 118 is connected to one end of the second connection pipe 107.
- the other end of the second connection pipe 107 is connected to the relay machine B.
- One end of the switching valve 125 is connected to the heat source apparatus side heat exchanger 103, and the other end is connected to the fourth flow rate regulator 122.
- the fourth flow rate regulator 122 and the switching valve 125 are each connected in series with the relay B, and the refrigerant is supplied to the relay B.
- the fourth flow rate regulator 122 is a flow rate control device with a variable opening. Therefore, the amount of refrigerant flowing into the heat source unit side heat exchanger 103 is controlled by adjusting the opening of the fourth flow rate regulator 122, and the refrigerant that has passed through the fourth flow rate regulator 122 passes through the switching valve 125.
- the refrigerant is combined with the refrigerant and the refrigerant is supplied to the relay unit B.
- the fifth flow regulator 124 is provided between the gas-liquid separator 123 and the accumulator 104, one end is connected to one outlet side of the gas-liquid separator 123, and the other end is connected to the inlet side of the accumulator 104. Connected. The other outlet side of the gas-liquid separator 123 is connected to the heat source machine side heat exchanger 103. The inlet side of the gas-liquid separator 123 is connected to the outlet side of the check valve 121, and the inlet side of the check valve 121 is connected to one end of the first connection pipe 106. The other end of the first connection pipe 106 is connected to the repeater B.
- the fifth flow rate regulator 124 and the heat source unit side heat exchanger 103 are each connected in series with the relay unit B, and the refrigerant is supplied from the relay unit B.
- the fifth flow rate regulator 124 is a flow rate control device with a variable opening. Therefore, the amount of refrigerant flowing from the relay B is controlled by adjusting the opening of the fifth flow rate regulator 124, and the refrigerant is supplied to the heat source device side heat exchanger 103 in a state where the amount of refrigerant is controlled.
- the pressure detection means 126 and 127 are formed by sensors, for example.
- the first pressure detecting means 126 measures the pressure of the refrigerant discharged from the compressor 101
- the second pressure detecting means 127 is the outlet side of the heat source unit side heat exchanger 103 (or the suction side of the compressor 101).
- Measure the refrigerant pressure Those measurement results are supplied to the control unit 141.
- the pressure detection means 126 and 127 may supply the measurement result to the control unit 141 as it is, or may supply the measurement result accumulated after a certain period of accumulation to the control unit 141 at a predetermined cycle interval.
- the pressure detection means 126, 127 may be any means as long as it can detect the refrigerant pressure, and the type is not limited.
- the temperature detection means 128 and 129 are formed of, for example, a thermistor.
- the temperature detectors 128 and 129 measure the refrigerant temperature on the inlet side and the outlet side of the heat source unit side heat exchanger 103 (inlet and outlet change depending on the operation mode). Those measurement results are supplied to the control unit 141.
- the temperature detection units 128 and 129 may supply the measurement results to the control unit 141 as they are, or may supply the measurement results accumulated after a certain period of accumulation to the control unit 141 at a predetermined cycle interval.
- the temperature detection means 128 and 129 are described as an example of thermistors. However, the temperature detection means 128 and 129 are not particularly limited thereto.
- the control unit 141 is configured mainly with a microprocessor unit, for example, and performs overall control of the heat source unit A and communication with an external device, for example, the relay unit B, based on the measurement result of each detection unit. Further, in the overall control of the heat source machine A, the necessary arithmetic processing is executed.
- the relay B includes a first branching unit 110, a second branching unit 111, a gas-liquid separator 112, a second flow rate regulator 113, a third flow rate regulator 115, a first heat exchanger 116, a first 2 heat exchanger 117, temperature detection means 132, third pressure detection means 130 a, fourth pressure detection means 130 b, and control unit 151.
- the relay machine B is connected to the heat source machine A via the first connection pipe 106 and the second connection pipe 107.
- the relay unit B is connected to the indoor unit C through the third connection pipe 106c and the fourth connection pipe 107c.
- the relay unit B is connected to the indoor unit D via the fifth connection pipe 106d and the sixth connection pipe 107d.
- the first branching unit 110 includes an electromagnetic valve 108a and an electromagnetic valve 108b.
- the solenoid valve 108a and the solenoid valve 108b are connected to the indoor unit C through the third connection pipe 106c. Further, the electromagnetic valve 108a and the electromagnetic valve 108b are connected to the indoor unit D through the fifth connection pipe 106d.
- the solenoid valve 108a is a valve that can be opened and closed, and has one end connected to the first connection pipe 106 and the other end connected to one terminal of the third connection pipe 106c, the fifth connection pipe 106d, and the solenoid valve 108b. It is connected.
- the solenoid valve 108b is a valve that can be opened and closed, and one end is connected to the second connection pipe 107 having the gas-liquid separator 112, and the other end is connected to the third connection pipe 106c, the fifth connection pipe 106d, and the electromagnetic valve. It is connected to one terminal of the valve 108a.
- the first branch part 110 is connected to the indoor unit C via the third connection pipe 106c.
- the first branch part 110 is connected to the indoor unit D via the fifth connection pipe 106d.
- the first branch part 110 is connected to the heat source machine A through the first connection pipe 106 and the second connection pipe 107.
- the first branching unit 110 connects the third connection pipe 106c to either the first connection pipe 106 or the second connection pipe 107 using the electromagnetic valve 108a and the electromagnetic valve 108b.
- the first branching section 110 connects the fifth connection pipe 106d with either the first connection pipe 106 or the second connection pipe 107 using the electromagnetic valve 108a and the electromagnetic valve 108b.
- the second branch portion 111 includes a check valve 131a and a check valve 131b.
- the check valve 131a and the check valve 131b are connected to each other in an antiparallel relationship.
- the input side of the check valve 131a and the output side of the check valve 131b are connected to the indoor unit C through the fourth connection pipe 107c, and are connected to the indoor unit D through the sixth connection pipe 107d. .
- the output side of the check valve 131a is connected to the meeting part 131a_all.
- the input side of the check valve 131b is connected to the meeting part 131b_all.
- the meeting part 131a_all and the meeting part 131b_all are clearly shown in FIGS.
- the second branch portion 111 is connected to the indoor unit C through the fourth connection pipe 107c.
- the second branch portion 111 is connected to the indoor unit D via the sixth connection pipe 107d.
- the second branch part 111 is connected to the second flow rate regulator 113 and the first heat exchanger 116 via the meeting part 131a_all.
- the second branch portion 111 is connected to the third flow rate regulator 115 and the first heat exchanger 116 via the meeting portion 131b_all.
- the gas-liquid separator 112 is provided in the middle of the second connection pipe 107, the gas phase portion is connected to the electromagnetic valve 108b of the first branching portion 110, and the liquid phase portion is the first heat exchange.
- the second branch unit 111 is connected to the second branch unit 111 through the second unit 116, the second flow rate regulator 113, and the second heat exchanger 117.
- the second flow rate regulator 113 has one end connected to the first heat exchanger 116 and the other end connected to one end of the second heat exchanger 117 and the meeting part 131a_all of the second branching part 111. .
- the piping between the first heat exchanger 116 and the second flow rate regulator 113 is provided with a third pressure detection means 130a.
- a fourth pressure detector 130b is provided in the pipe between the second flow rate regulator 113, the second heat exchanger 117, and the meeting portion 131a_all.
- the second flow rate regulator 113 is a flow rate regulator whose opening degree can be adjusted, and the difference between the pressure value detected by the third pressure detection means 130a and the pressure value detected by the fourth pressure detection means 130b. Adjust the opening so that becomes constant.
- the third flow rate regulator 115 is a flow rate regulator whose opening degree can be adjusted, and any one of the temperature detection means 132, the third pressure detection means 130a, the fourth pressure detection means 130b, or a plurality thereof. The opening is adjusted by matching.
- the bypass pipe 114 has one end connected to the first connection pipe 106 and the other end connected to the third flow rate regulator 115. Therefore, the amount of refrigerant supplied to the heat source unit A varies depending on the opening of the third flow rate regulator 115.
- the first heat exchanger 116 is provided between the gas-liquid separator 112, the second heat exchanger 117, and the second flow rate regulator 113, and includes a bypass pipe 114, the gas-liquid separator 112, and the first heat exchanger 116. Heat exchange is performed with a pipe provided between the two flow rate regulators 113.
- the third pressure detecting means 130a measures the pressure of the refrigerant flowing in the pipe provided between the first heat exchanger 116 and the second flow rate regulator 113, and sends the measurement result to the control unit 151. Supply.
- the fourth pressure detection means 130b measures the pressure of the refrigerant flowing in the pipe provided between the second flow rate regulator 113, the second heat exchanger 117, and the second branch portion 111, The measurement result is supplied to the control unit 151.
- the third pressure detection unit 130a and the fourth pressure detection unit 130b are collectively referred to as the pressure detection unit 130.
- the pressure detection unit 130 may supply the measurement result to the control unit 151 as it is, or may supply the measurement result accumulated after a certain period of accumulation to the control unit 151 at a predetermined cycle interval.
- the pressure detecting means 130 may be any means as long as it can detect the refrigerant pressure, and the type is not limited.
- the control unit 151 is configured mainly with a microprocessor unit, for example, and based on the measurement result of each detection unit, the control of the relay unit B and external devices such as the heat source unit A and the indoor units C and D are performed. Communicate with. Further, in the overall control of the repeater B, the necessary arithmetic processing is executed.
- the indoor unit C includes a use side heat exchanger 105c and a first flow rate regulator 109c.
- a plurality of use side heat exchangers 105c are provided.
- a liquid pipe temperature detecting means 133 for detecting the temperature of the pipe is provided between the use side heat exchanger 105c and the first flow rate regulator 109c.
- a gas pipe temperature detecting means 134 for detecting the temperature of the pipe is provided between the use side heat exchanger 105c and the first branching section 110.
- the liquid pipe temperature detecting means 133 and the gas pipe temperature detecting means 134 are displayed only for one of the use side heat exchangers 105d of the indoor unit D due to space limitations.
- the temperature detecting means is provided in all the use side heat exchangers of the indoor unit C and the indoor unit D, respectively.
- the utilization side heat exchanger 105c and the first flow rate regulator 109c described above constitute a part of the refrigerant circuit.
- the indoor unit D includes a use side heat exchanger 105d and a first flow rate regulator 109d.
- a plurality of use side heat exchangers 105d are provided.
- a liquid pipe temperature detecting means 133 for detecting the temperature of the pipe is provided between the use side heat exchanger 105d and the first branching part 110.
- a gas pipe temperature detecting means 134 for detecting the temperature of the pipe is provided between the use side heat exchanger 105d and the first branching part 110.
- the utilization side heat exchanger 105d and the first flow rate regulator 109d described above constitute a part of the refrigerant circuit.
- the heat medium system is for supplying the heat source apparatus side heat exchanger 103 with a heat medium different from the refrigerant such as water or brine that exchanges heat with the refrigerant flowing through the heat source apparatus side heat exchanger 103.
- a heat medium flow controller 201 As components of the system, there are a heat medium flow controller 201, a heat medium transporter 202, a heat medium inflow temperature detection means 203, a heat medium outflow temperature detection means 204, and a heat medium flow control device 250.
- the heat medium system is usually configured so that the temperature of the heat medium can also be adjusted.
- the heat medium flow controller 201 adjusts the flow rate of the heat medium flowing through the heat source apparatus side heat exchanger 103, and includes a valve or the like.
- the heat medium transporter 202 sends out a heat medium, and includes a pump or the like.
- the heat medium inflow temperature detecting means 203 and the heat medium outflow temperature detecting means 204 are temperature sensors that measure the temperature of the heat medium on the inlet side and the outlet side of the heat source apparatus side heat exchanger 103, respectively.
- the heat medium flow controller 201 and the heat medium transporter 202 are controlled by the heat medium flow control device 250 based on the detection values of the heat medium inflow temperature detection means 203 and the heat medium outflow temperature detection means 204.
- the heat medium flow control device 250 includes a heat source unit operation mode detection unit 205 that determines whether the compressors of the heat source unit A and the combined heat source unit are stopped or in operation, and cooling operation and heating operation of the plurality of use side heat exchangers 105 Are provided with an indoor unit operation mode detection means 210 for detecting the total of the indoor unit cooling operation capacity, which is the sum of the capacities in each case, and the total of the indoor unit heating operation capacity. Furthermore, a heat medium temperature difference calculating means 251 is provided for calculating a difference between measured values of the heat medium inflow temperature detecting means 203 and the heat medium outflow temperature detecting means 204.
- the heat medium flow control device 250 calculates the flow rate of the heat medium supplied to the heat source apparatus side heat exchanger 103 based on the result of the heat medium temperature difference calculation means 251. Further, the heat medium flow control device 250 determines the heat source unit from the total indoor unit cooling operation capacity, the total indoor unit heating operation capacity, and the total operation capacity of the heat source unit combined with the heat source unit A (heat source unit operation capacity). The flow rate of the heat medium supplied to the side heat exchanger 103 is also calculated. In addition, the heat medium flow control device 250 includes a setting switch 252 that can input a heat medium flow value. Note that the heat medium flow control device 250 may be included in the control unit 141 of the heat source machine A.
- FIG. 2 is a diagram illustrating a configuration example of the air-conditioning apparatus 1 for explaining an operation state in the cooling-heating simultaneous operation according to the first embodiment of the present invention and mainly in a cooling operation.
- a cooling operation is set for the indoor unit C and a heating operation is set for the indoor unit D, and the operation of the air conditioner 1 is performed mainly by the cooling.
- the indoor unit C side is opened among the solenoid valves 108a, and the indoor unit D side is closed. Moreover, in the 1st branch part 110, the indoor unit C side is closed among the solenoid valves 108b, and the indoor unit D side is opened.
- the opening degree of the second flow rate regulator 113 is controlled so that the differential pressure between the third pressure detection means 130a and the fourth pressure detection means 130b becomes an appropriate value.
- the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 101 flows into the heat source unit side heat exchanger 103 through the four-way valve 102.
- the heat source device side heat exchanger 103 exchanges heat with a heat medium such as water.
- the heat-exchanged high-temperature and high-pressure gas refrigerant becomes a gas-liquid two-phase high-temperature and high-pressure refrigerant.
- the gas-liquid two-phase high-temperature and high-pressure refrigerant passes through the fourth connection regulator 107 and the check valve 118, passes through the second connection pipe 107, and is supplied to the gas-liquid separator 112 of the relay B.
- the switching valve 125 is controlled to a predetermined opening according to the difference between the temperature obtained from the detected pressure value of the first pressure detecting means 126 and the target value.
- the gas-liquid separator 112 separates the gas-liquid two-phase high-temperature and high-pressure refrigerant into a gaseous refrigerant and a liquid refrigerant.
- the separated gaseous refrigerant flows into the first branch part 110.
- the gaseous refrigerant that has flowed into the first branching section 110 is supplied to the indoor unit D in which the heating operation is set, through the open solenoid valve 108b and the fifth connection pipe 106d.
- the use side heat exchanger 105d exchanges heat with a use medium such as air, and condenses and liquefies the supplied gaseous refrigerant.
- the usage-side heat exchanger 105d is controlled by the first flow rate regulator 109d based on the degree of supercooling at the outlet of the usage-side heat exchanger 105d.
- the first flow controller 109d depressurizes the liquid refrigerant condensed and liquefied by the use side heat exchanger 105d, and converts it to an intermediate pressure refrigerant that is an intermediate pressure between the high pressure and the low pressure.
- the refrigerant having the intermediate pressure flows into the second branch portion 111.
- the first connection pipe 106 has a low pressure
- the second connection pipe 107 has a high pressure. Therefore, due to the pressure difference between them, the refrigerant flows to the check valve 118 and the check valve 119, while the refrigerant does not flow to the check valve 120 and the check valve 121.
- the liquid refrigerant separated by the gas-liquid separator 112 passes through the second flow rate regulator 113 that controls the pressure difference between the high pressure and the intermediate pressure to be constant, and flows into the second branch portion 111.
- the supplied liquid refrigerant passes through the check valve 131b connected to the indoor unit C side, and flows into the indoor unit C through the fourth connection pipe 107c.
- the inflowing liquid refrigerant is decompressed to a low pressure by using the first flow rate regulator 109c controlled according to the degree of superheat at the outlet of the utilization side heat exchanger 105c of the indoor unit C. It is supplied to the heat exchanger 105c.
- the supplied liquid refrigerant is evaporated and gasified by exchanging heat with a use medium such as air.
- the refrigerant that has been gasified to become a gas refrigerant passes through the third connection pipe 106 c and flows into the first branch portion 110.
- the solenoid valve 108a on the side connected to the indoor unit C is open. Therefore, the gas refrigerant that has flowed in passes through the electromagnetic valve 108 a on the side connected to the indoor unit C, and flows into the first connection pipe 106.
- the gas refrigerant flows into the check valve 119 having a lower pressure than the check valve 121, and is sucked into the compressor 101 through the four-way valve 102 and the accumulator 104. With such an operation, a refrigeration cycle is formed and a cooling main operation is performed.
- the refrigerants that have been separated by the gas-liquid separator 112 and have flowed into the second branch portion 111 there are refrigerants that have not flowed into the indoor unit C.
- Such liquid refrigerant passes through the second flow rate regulator 113, passes through the second heat exchanger 117, does not flow into the second branch portion 111, and flows into the third flow rate regulator 115.
- the third flow rate regulator 115 depressurizes the inflowing liquid refrigerant to a low pressure to lower the refrigerant evaporation temperature.
- the liquid refrigerant whose evaporation temperature has decreased passes through the bypass pipe 114 and exchanges heat with the liquid refrigerant mainly supplied from the second flow rate regulator 113.
- the first heat exchanger 116 heat exchange with the high-temperature and high-pressure liquid refrigerant supplied from the gas-liquid separator 112 becomes a gas refrigerant, and the first connection It flows into the pipe 106.
- FIG. 3 is a diagram showing a configuration example of the air-conditioning apparatus 1 for explaining an operation state in the case of heating and cooling simultaneous operation in Embodiment 1 of the present invention and mainly heating.
- a heating operation is set for the indoor unit C and a cooling operation is set for the indoor unit D, and the operation of the air conditioner 1 is performed mainly by heating.
- the indoor unit C side is closed among the solenoid valves 108a, and the indoor unit D side is opened. Moreover, among the electromagnetic valves 108b, the indoor unit C side is opened, and the indoor unit D side is closed.
- the opening degree of the second flow rate regulator 113 is controlled so that the differential pressure between the third pressure detection means 130a and the fourth pressure detection means 130b becomes an appropriate value.
- the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 101 passes through the four-way valve 102, the check valve 120, the second connection pipe 107, and the relay machine.
- B gas-liquid separator 112 is supplied.
- the gas-liquid separator 112 supplies a high-temperature and high-pressure gas refrigerant to the first branch part 110.
- the gas refrigerant supplied to the first branch part 110 is supplied to the indoor unit C in which the heating operation is set, through the open solenoid valve 108b and the third connection pipe 106c.
- the use side heat exchanger 105c exchanges heat with a use medium such as air, and the supplied gas refrigerant is condensed and liquefied.
- the use side heat exchanger 105c is controlled by the first flow rate regulator 109c based on the degree of supercooling at the outlet of the use side heat exchanger 105c.
- the first flow controller 109c depressurizes the liquid refrigerant condensed and liquefied by the use side heat exchanger 105c, and converts it to an intermediate pressure liquid refrigerant that is an intermediate pressure between the high pressure and the low pressure.
- the liquid refrigerant having the intermediate pressure flows into the second branch portion 111 through the fourth connection pipe 107c.
- the liquid refrigerant that has flowed into the second branch portion 111 joins at the meeting portion 131a_all.
- the liquid refrigerant merged at the meeting part 131a_all passes through the second heat exchanger 117.
- part of the liquid refrigerant that has passed through the second heat exchanger 117 passes through the third flow rate regulator 115 and flows into the second heat exchanger 117 in a decompressed state. Yes. Therefore, in the second heat exchanger 117, the intermediate-pressure liquid refrigerant and the low-pressure liquid refrigerant are heat-exchanged, and the low-pressure liquid refrigerant has a low evaporation temperature, so that it becomes a gas refrigerant and passes through the bypass pipe 114.
- the intermediate-pressure liquid refrigerant reaches the meeting part 131b_all, passes through the check valve 131b connected to the indoor unit D, flows into the indoor unit D through the sixth connection pipe 107d.
- the liquid refrigerant that has flowed into the indoor unit D is depressurized to a low pressure using the first flow rate regulator 109d that is controlled according to the degree of superheat at the outlet of the use side heat exchanger 105d of the indoor unit D, and evaporates.
- the use side heat exchanger 105d In the state where temperature is low, it is supplied to the use side heat exchanger 105d.
- the supplied liquid refrigerant having a low evaporation temperature is evaporated and gasified by exchanging heat with a use medium such as air.
- the refrigerant that has been gasified and becomes a gas refrigerant passes through the fifth connection pipe 106d and flows into the first branch 110.
- the solenoid valve 108a by the side connected with the indoor unit D is opening. Therefore, the gas refrigerant that has flowed in passes through the electromagnetic valve 108 a on the side connected to the indoor unit D, and flows into the first connection pipe 106.
- the gas refrigerant flows into the check valve 121 side having a lower pressure than the check valve 119, and the liquid refrigerant that has passed through the gas-liquid separator 123 flows into the heat source unit side heat exchanger 103 and evaporates.
- the gas enters a gas state and is sucked into the compressor 101 through the four-way valve 102 and the accumulator 104.
- the gas refrigerant that has passed through the gas-liquid separator 123 passes through the fifth flow rate regulator 124 and is sucked into the compressor 101 via the accumulator 104. With such an operation, a refrigeration cycle is formed, and a heating main operation is performed.
- the first connection pipe 106 has a low pressure
- the second connection pipe 107 has a high pressure. Therefore, due to the pressure difference between them, the refrigerant flows to the check valve 120 and the check valve 121, while the refrigerant does not flow to the check valve 118 and the check valve 119.
- the ratio between the cooling operation capacity and the heating operation capacity changes during the cooling and heating simultaneous operation and during the cooling main operation.
- the state of the refrigerant flowing into the repeater B needs to have a high dryness.
- the condensation temperature of the heat source device side heat exchanger 103 provided in the heat source device A that is, the high pressure is also lowered. Due to this phenomenon, the liquid pipe temperature detected by the liquid pipe temperature detecting means 133 of the indoor unit C that is performing the cooling operation is lowered.
- the air conditioner 1 cannot maintain the continued cooling operation, and further, the condensation temperature is low and the heating capacity is reduced. The user who uses the device 1 becomes uncomfortable.
- the indoor unit C In order to prevent the indoor unit C from starting and stopping, it is necessary to raise the liquid pipe temperature detected by the liquid pipe temperature detection means 133 of the indoor unit C to a predetermined value or more.
- the liquid pipe temperature detected by the liquid pipe temperature detection means 133 of the indoor unit C is different for each use side heat exchanger 105c of the indoor unit C. Therefore, when performing the process which raises liquid tube temperature, according to each utilization side heat exchanger 105c, it was necessary to control liquid tube temperature separately, and control was complicated. Further, in order to ensure the heating capacity, it is necessary to set the condensation temperature of the heat source unit side heat exchanger 103, that is, the high pressure, to a predetermined value.
- the amount of refrigerant flowing through the heat source unit side heat exchanger 103 and the amount of refrigerant bypassing the heat source unit side heat exchanger 103 via the switching valve 125 are the cooling operation capacity (indoor unit C) and the heating operation capacity (indoor unit D). ) And the ratio.
- FIG. 4 is a diagram illustrating an example of the relationship between the CV value of the switching valve 125 and the opening ratio of the fourth flow rate regulator 122 during cooling according to Embodiment 1 of the present invention.
- the horizontal axis is assumed to be the CV value of the switching valve 125, and the vertical axis is assumed to be the opening ratio of the fourth flow rate regulator 122 that controls the flow rate of the heat source apparatus side heat exchanger 103. Further, it is assumed that ⁇ Qjc is the total heat amount during cooling, and ⁇ Qjh is the total heat amount during heating.
- the pressure detected by the first pressure detection unit 126 decreases, so the dryness of the refrigerant is increased. If the ratio between the indoor unit C and the indoor unit D is the same, the unit moves on the same dryness line.
- the compressor frequency is determined by the cooling total heat amount ⁇ Qjc
- the CV value of the switching valve 125 is determined by the heating total heat amount ⁇ Qjh.
- the opening degree of the fourth flow rate regulator 122 is determined by the measured value of the first pressure detecting means 126 and the measured values of the refrigerant temperature detecting means 128 and 129 at the inlet / outlet of the heat source apparatus side heat exchanger 103.
- the characteristic line for the switching valve 125 has an upward slope.
- the difference between the temperature obtained from the pressure detected by the first pressure detection means 126 and the target control temperature is calculated by using the CV value of the switching valve 125 and the fourth flow regulator 122. What is necessary is just to control by the opening ratio and the frequency of the compressor 101. Because of this operation, it is not necessary to individually set the target control temperature for each temperature of the indoor unit, and control may be performed based on the detection result of the first pressure detection means 126 of the heat source unit A.
- the fourth flow rate regulator 122 that controls the flow rate of the heat source unit side heat exchanger 103 of the heat source unit A and the switching valve 125 that opens and closes the bypass circuit that bypasses the heat source unit side heat exchanger 103 are provided.
- the pressure detected by the first pressure detector 126 provided in the heat source device A there are a plurality of use side heat exchangers 105 that are performing cooling operation or heating operation during simultaneous cooling and heating operation.
- stable control can be simplified. Therefore, comfort can be maintained at low cost.
- Inlet pressure (discharge pressure of the compressor 101) of the heat source device side heat exchanger 103, refrigerant inlet and outlet temperatures of the heat source device side heat exchanger 103, cooling operation capacity and heating of the plurality of usage side heat exchangers 105 Based on the ratio to the operating capacity, the target control temperature of the heat source unit side heat exchanger 103 is obtained, and the fourth flow rate regulator 122 and the switching valve 125 are adjusted according to the target control temperature, and the heat source unit side heat exchange is performed.
- the flow rate of the vessel 103 is controlled.
- FIG. FIG. 5 is a flowchart illustrating a flow of the heat medium flow rate adjustment control executed by the heat medium flow control device 250 according to the second embodiment. Based on FIG. 5, the flow from when the heat medium flow control device 250 outputs an electric signal to the heat medium flow controller 201 after acquiring the input value will be described.
- the heat medium flow rate adjustment is started (step S101). After starting the heat medium flow rate adjustment, it is determined whether or not a predetermined time T1 seconds (30 seconds here) has been set (step S102). Get the required input values.
- the heat source machine operation mode detection means 205 measures the operation state of the heat source machine A (whether the compressor 101 is stopped or operating), the heat medium inflow temperature detection means 203 and the heat medium outflow temperature detection means 204.
- a heat medium temperature difference from the heat medium temperature difference calculation means 251 based on the value is acquired (step S103).
- the heat medium flow control device 250 determines a heat medium flow adjustment state pattern (patterns A, B, C, and D) from the operation state of the heat source unit A using the relationship shown in FIG. 6 (step S104). ).
- step S105 After calculating the required flow rate of the heat medium, it is output as an electric signal to the heat medium flow rate regulator 201.
- the voltage signal is in the range of 0 to 10V, and 0V is fully open and 10V is fully closed, so 10V is output (step S111).
- 0V may correspond to fully closed and 10V may correspond to fully open, but from the viewpoint of safety, it is preferable that 0V correspond to fully open and 10V correspond to fully closed.
- the description is based on the voltage signal here, it may be a current signal.
- Step S106 After calculating the required flow rate of the heat medium, it is output as an electric signal to the heat medium flow rate regulator 201.
- T2 seconds in consideration of the opening / closing speed of the heat medium flow rate regulator 201) Compared to 120 seconds here).
- step S107 When the elapsed time from the previous output is equal to or longer than the predetermined time T2 seconds (step S107; YES), an electric signal is output to the heat medium flow controller 201.
- the voltage signal is in the range of 0 to 10 V, and 0 V is fully open and 10 V is fully closed, so it is between 0 and 10 V, but here it is assumed that it is 5 V (step) S111).
- step S107; NO when the elapsed time from the previous output is shorter than the elapsed time T2 seconds (step S107; NO), the process returns to the start of the heat medium flow rate adjustment (step S101), and steps are taken again.
- the compressor 101 of the heat source device A is in operation and the compressor operation time is longer than a predetermined time T0 minutes (here, 5 minutes). For this reason, the required heat medium flow rate to be supplied to the heat source apparatus side heat exchanger 103 is determined by calculating the heat medium flow rate change amount dGw (step S108). After calculating the required heat medium flow rate, it is output as an electrical signal to the heat medium flow rate regulator 201. The elapsed time from the previous output and a predetermined time T2 in consideration of the opening / closing speed of the heat medium flow rate regulator 201. Compare with seconds (120 seconds here).
- step S109 When the elapsed time from the previous output is equal to or longer than the predetermined time T2 seconds (step S109; YES), an electric signal is output to the heat medium flow controller 201.
- the voltage signal is in the range of 0 to 10 V, 0 V is fully open, 10 V is fully closed, and the lower limit flow rate is 5 V, so that the voltage signal is output between 0 and 5 V (step S111).
- step S109; NO when the elapsed time from the previous output is shorter than the elapsed time T2 seconds (step S109; NO), the process returns to the start of the heat medium flow rate adjustment (step S101) and steps are taken again.
- the “heat medium flow rate change amount dGw” calculated by the pattern C is calculated using the temperature difference between the heat medium inflow temperature and the heat medium outflow temperature in the heat source apparatus side heat exchanger 103 and the target value of the temperature difference.
- the medium flow control device 250 calculates from the equation shown in FIG.
- the heat medium flow rate Gw represents a current value.
- the heat medium flow rate Gw is a rated flow rate.
- the heat medium temperature difference target value is 5 ° C., but this heat medium temperature difference target value is determined by the specifications of the heat exchanger and is not limited to 5 ° C.
- the compressor 101 of the heat source device A is in operation, and the compressor operation time is shorter than a predetermined time T0 minutes (here, 5 minutes). For this reason, assuming the compressor starting state, the rated flow rate (maximum flow rate) of the heat medium flow rate regulator 201 is supplied to the heat source device side heat exchanger 103 as the heat medium (step S110). Since the pressure in the refrigerant system is not stable at the time of starting the compressor, the heat medium flow rate adjustment control is performed here to promote the pressure fluctuation in the refrigerant system. For this reason, the opening degree change of the heat medium flow controller 201 becomes frequent, and there is a possibility that pressure fluctuations in the heat medium system occur.
- the rated flow rate is set in consideration of the high pressure rise at the time of starting compression or the prevention of freezing of the heat medium heat exchanger.
- the required flow rate of the heat medium it is output as an electric signal to the heat medium flow controller 201.
- the voltage signal is in the range of 0 to 10 V, 0 V is fully open, and 10 V is fully closed, so 0 V is output (step S 111).
- the required heat medium flow rate is calculated as described above (steps S105 to 110), the calculated heat medium required flow rate is converted into an electric signal output value (step S111), and the signal is output to the heat medium flow rate regulator 201 (step S111). S112). After the electrical signal is output to the heat medium flow controller 201, the timer of the elapsed time from the previous output is reset (step S113), the process returns to the heat medium flow adjustment start (step S101), and the steps are taken again. .
- the above control by the heat medium flow control device 250 can be summarized as shown in FIG. That is, the heat medium supplied to the heat source apparatus side heat exchanger 103 is 0 (zero) in the pattern A, the lower limit flow rate defined by the heat source apparatus A in the pattern B, and the rated flow rate of the heat medium flow controller 201 in the pattern D.
- the flow rate is calculated based on the temperature difference at the inlet / outlet of the heat medium of the heat source device side heat exchanger 103 and the temperature difference target value. .
- the following measures are taken in controlling the heat medium flow rate.
- the heat medium flow control device 250 sets the lower limit flow rate of the heat medium determined by the heat source device A as a lower limit value, and sets the flow rate (rated flow rate) corresponding to the maximum opening of the heat medium flow regulator 201 as an upper limit value.
- the flow control device 250 controls the heat medium flow rate between the lower limit value and the upper limit value.
- a plurality of lower limit values are preferably set so that they can be selected according to the characteristics of the heat medium flow controller 201.
- the lower limit value is an amount that does not hinder the operation of the heat source unit A, and may be selected from the flow rate required from the viewpoint of preventing pitting corrosion or freezing of the heat source unit side heat exchanger 103. Good.
- the heat medium flow control device 250 may include a plurality of switches 252 or buttons for setting a lower limit value.
- the switch 252 or the like is not used to change the lower limit value itself (minimum flow rate), but the heat source side heat exchange is performed even if the specification (rated Cv value) of the heat medium flow regulator 201 is different. It is used to set the minimum flow rate supplied to the vessel 103 to be the same.
- the heat medium flow control device 250 controls the heat medium flow controller 201 so that the maximum flow rate is ensured after the compressor 101 included in the heat source device A is started, and the operation flow shifts to a calculation flow pattern C after a predetermined time. It is preferable to do this. From the viewpoint of promptly shifting to the stable state to the pattern C or avoiding the twisting of the valve of the heat medium flow regulator 201, the opening degree of the heat medium flow regulator 201 is determined when determining the maximum flow rate of the pattern D. It is better to set the opening slightly smaller than the rated maximum opening.
- the heat medium flow rate The controller 250 preferably sets the flow rate of the heat medium supplied to the heat medium flow rate regulator 201 to the lower limit value.
- the heat medium flow control device 250 sets the flow rate of the heat medium supplied to the heat medium flow controller 201 to zero.
- Pattern C when the heat medium temperature difference between the heat medium inflow side and the outflow side of the heat source apparatus side heat exchanger 103 is larger than the target temperature difference, the flow rate of the heat medium supplied to the heat medium flow controller 201 is increased.
- the heat source apparatus side heat exchanger 103 is supplied to the heat medium flow rate regulator 201 in proportion to the difference between the target temperature difference of the heat medium on the heat medium inflow side and the outflow side and the actual temperature difference. Increase the amount of heat medium to be changed.
- the command electric power to the heat medium flow rate regulator 201 is secured. It is preferable that the flow rate is small or the lower limit value when the output value is large, and the flow rate is large or the rated flow rate when the command electric output value is small.
- the heat source apparatus A is controlled based on the heat medium temperature difference calculated from the temperatures detected by the heat medium temperature detecting means 203 and 204 provided in the heat source apparatus A.
- the heat medium flow rate is reduced according to the capacity of the use side heat exchanger, and while maintaining the comfort as the air conditioner 1, the heat medium transporter 202 (for example, a water pump) ) Can also be reduced. Therefore, with this configuration, it is possible to obtain an effect that a highly efficient simultaneous cooling and heating operation can be performed.
- FIG. 8 is a flowchart illustrating the flow of heat medium flow rate adjustment control executed by the heat medium flow control device 250 according to the third embodiment.
- FIG. 9 is a diagram for explaining another example of the flowchart of the heat medium flow rate adjustment control in the third embodiment of the present invention.
- FIG. 10 is a diagram for explaining an example of four patterns (the pattern D has already been described and is omitted) in the heat medium flow rate adjustment state according to the third embodiment of the present invention.
- the patterns C, C-1, and C-2 (computed flow rate) will be described with reference to FIGS.
- the same processing as in the second embodiment is omitted.
- the pattern C in FIG. 8 is the same as the pattern C-2 in FIGS. 9 and 10
- the pattern C-1 in FIGS. 9 and 10 is the same as the pattern C in FIGS.
- FIG. 8 differs from FIG. 5 and FIG. 6 in pattern C.
- the “heat medium flow rate Gw” includes the heat medium rated flow rate, the operating frequency of the compressor of the heat source unit A, the maximum frequency of the compressor of the heat source unit A, and the minimum of the compressor of the heat source unit A.
- the heat medium flow control device 250 calculates from the equation shown in the pattern C-2 in FIG. The heat medium flow control device 250 increases the flow rate of the heat medium supplied to the heat medium flow controller 201 when the operating frequency of the compressor of the heat source apparatus A is higher than the minimum frequency of the compressor of the heat source apparatus.
- the “heat medium flow rate Gw” uses the temperature difference between the heat medium inflow temperature and the heat medium outflow temperature in the heat source apparatus side heat exchanger 103 and the target value of these temperature differences according to the pattern C-1.
- the operation frequency of the compressor of the heat source machine A, the maximum frequency of the compressor of the heat source machine A, and the minimum frequency of the compressor of the heat source machine A according to the first calculated flow rate calculated in the above and the pattern C-2 are used. Is calculated and determined based on the calculated second calculated flow rate (step S116, step S117).
- step S116 the first calculation flow rate is calculated based on the temperature difference between the heat medium inflow temperature and the heat medium outflow temperature data-nn degrees in the heat source apparatus side heat exchanger 103 and the target value of the temperature difference.
- the required heat medium flow rate Gw ′ current heat medium flow rate Gw + change amount dGw.
- the second calculation flow rate is calculated based on the operating frequency of the compressor of the heat source machine A, the maximum frequency of the compressor of the heat source machine A, and the minimum frequency of the compressor of the heat source machine A.
- step S118 the heat medium flow control device 250 sets the larger one of the first calculated flow rate and the second calculated flow rate as the flow rate of the heat medium supplied to the heat medium flow rate regulator 201.
- the heat medium rated flow rate may be divided into Steps within a certain range, and the representative flow rate may be output with respect to a numerical value within the Step range.
- the minimum flow rate 2m 3 / h when the rated flow 6m 3 / h, Step1: 2m 3 / h, Step2: 3m 3 / h (2m 3 / h ⁇ 3m 3 / h), Step3: 4m 3 / h (3 m 3 / h to 4 m 3 / h), Step 4: 5 m 3 / h (4 m 3 / h to 5 m 3 / h) may be used.
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Abstract
Description
ここで、例えば、室内機に供え付けられたリモコンの設定温度と室内機周辺の気温とに応じて、複数の室内機において、それぞれ冷房、暖房を自動的に判断し、室内機ごとに冷房、暖房を行うことができる冷暖房同時運転(冷暖房混在運転)が可能な空気調和装置があった(例えば、特許文献1参照)。
また、熱源機側熱交換器に供給する熱媒体の入口温度と圧縮機の周波数から、予め定められた関係によって熱媒体の出口温度の目標値を求め、この目標値に合わせて熱媒体搬送器(例えば水ポンプ)の周波数を制御する空気調和装置があった(例えば、特許文献2参照)。
また、特許文献1に記載の冷暖房混在運転可能な空調機では、室内機間で熱回収運転となるため、冷房と暖房の空調負荷比率がほぼ同等であり、完全熱回収運転を行う場合は、室外熱交換器での熱交換量を低減する必要がある。つまり、熱回収運転での空調機の快適性および省エネ性を向上するには、冷房主体運転であれば、放熱量ゼロに近づける必要があり、暖房主体運転では吸熱量をゼロに近づける必要がある。
しかしながら、圧縮機の機器信頼性上、圧縮比を所定値以上(例えば2以上)に確保する必要があるため、冷房運転時であれば、低外気もしくは低圧縮機運転容量での運転では、AK値を低下させる必要がある。しかし、空気熱交換器であれば、室外機の電子基盤冷却のために室外ファンを一定以上に確保する必要があり、水熱交換器であれば、孔食のため水流速を一定以上に保つ必要がある。そのため、AK値を所望のAK値まで低下させることができず、冷凍サイクルの低圧が低下する。冷房時は、室内機の凍結防止のため蒸発温度を0℃以上に確保する必要があるが、低圧が低下した場合は、室内機の凍結防止のため機器を停止する必要があり、機器の発停が頻発し、室内の快適性や、省エネ性が悪化するという課題があった。
また、特許文献2に記載の空気調和装置では、圧縮機の周波数に応じて熱媒体搬送器の周波数を制御するため、利用側熱交換器容量の変化等、冷媒系統側の過渡的な変化に追従して熱媒体搬送器の周波数が変化し、熱媒体系統側の運転の安定に時間がかかる。また、冷暖房混在運転時に利用側熱交換器容量は高いが冷房と暖房の運転容量が同等な場合、熱源機側熱交換器へ供給する熱媒体流量を低減させることができるが、圧縮機周波数が高いため熱媒体搬送機の周波数を高くし省エネ性を悪化させるという課題があった。
冷媒を圧縮して吐出する圧縮機と、
前記冷媒と前記冷媒とは異なる熱媒体との間で熱交換する熱源機側熱交換器と、
前記冷媒と周囲の利用媒体との間で熱交換する複数の利用側熱交換器と、
前記熱源機側熱交換器と、前記複数の利用側熱交換器との間に設けられ、前記複数の利用側熱交換器の一部を冷房運転に切り換え、前記複数の利用側熱交換器の一部を暖房運転に切り換える中継機と、
前記熱源機側熱交換器に供給する前記熱媒体の流量を調整可能な熱媒体システムとして、少なくとも1系統の熱媒体搬送器、熱媒体流量調整器、および熱媒体流量制御装置を備え、
前記圧縮機と前記熱源機側熱交換器が熱源機に配置され、前記利用側熱交換器が室内機に配置され、
制御指令に応じて、前記複数の利用側熱交換器のそれぞれを前記冷房運転と前記暖房運転とに切り換え、冷暖房同時運転を行う空気調和装置であって、
前記熱源機側熱交換器には、前記複数の利用側熱交換器の総冷房容量と総暖房容量との比率に応じて冷媒が流され、
前記熱媒体流量制御装置が、前記熱源機側熱交換器への熱媒体流入温度と、前記熱源機側熱交換器からの熱媒体流出温度とを利用して熱媒体流量調整器を制御し、前記熱源機側熱交換器に供給する熱媒体流量を制御するように構成されている。
図1は本発明の実施の形態1における空気調和装置1の構成例を示す図である。図1に示すように、空気調和装置1は、熱源機A、中継機B、室内機C、室内機Dを備え、四方弁102及び逆止弁118~121等を用い、空気調和装置1内に、冷房用冷凍サイクルと、暖房用冷凍サイクルとを形成し、冷媒を循環させて冷暖房同時運転を行う。
冷暖房同時運転時に冷房運転容量と暖房運転容量が変化した場合には、熱源機A側では、圧力検出手段126,127で検出される圧力、温度検出手段128,129で検出される熱源機の温度を制御することで、各室内機C,Dに設けられた個々の利用側熱交換器105c,105d(まとめて利用側熱交換器105と称する場合もある)に流入する冷媒の温度を一定範囲内に保つ。
この結果、冷暖房同時運転中に冷房運転容量と暖房運転容量が変化した場合であっても、低コストで、安定した冷暖房運転を継続させる。
なお、熱源機として組合わせ熱源機A1,A2を備える構成としてもよい。熱源機A1,A2の構成はたとえば熱源機Aと同じでもよい。
以下、上述した内容の詳細について順に説明する。
なお、以下では、熱源機Aが1台、中継機Bが1台、室内機C,Dが2台の場合の一例について説明するが、これに限定されるものではない。例えば、室内機が2台以上の複数台の場合であってもよい。また、例えば、熱源機や中継機が複数台であってもよい。
なお、熱源機側熱交換器103において、その中の冷媒回路を流れる冷媒と熱交換するのは、冷媒と異なる熱媒体であり、それは例えば、水若しくはブラインである。
また、第5の流量調整器124は、アキュムレータ104と気液分離器123との間に接続され、熱源機側熱交換器103に流入する冷媒を調整する。
切換弁125は、一端が熱源機側熱交換器103に接続され、他端が第4の流量調整器122に接続されている。
したがって、第4の流量調整器122の開度を調整することで熱源機側熱交換器103へ流入する冷媒量を制御し、第4の流量調整器122を通過した冷媒を切換弁125を通過した冷媒と合流させて、冷媒を中継機Bへ供給する。
したがって、第5の流量調整器124の開度を調整することで中継機Bから流入する冷媒量を制御し、冷媒量を制御した状態で冷媒を熱源機側熱交換器103に供給する。
なお、圧力検出手段126,127は、冷媒圧力を検出できるものであればよく、種類などは限定されない。
なお、上記の説明では、温度検出手段128,129は、サーミスタで形成される一例について説明したが、特にこれに限定しない。
中継機Bは、第1の接続配管106及び第2の接続配管107を介して、熱源機Aと接続されている。また、中継機Bは、第3の接続配管106c及び第4の接続配管107cを介して、室内機Cと接続されている。さらに、中継機Bは、第5の接続配管106d及び第6の接続配管107dを介して、室内機Dと接続されている。
電磁弁108aは、開閉可能な弁であり、一端が第1の接続配管106に接続され、他端が第3の接続配管106c、第5の接続配管106d、及び電磁弁108bの一方の端子と接続されている。電磁弁108bは、開閉可能な弁であり、一端が気液分離器112を有する第2の接続配管107に接続され、他端が第3の接続配管106c、第5の接続配管106d、及び電磁弁108aの一方の端子と接続されている。
第2の流量調整器113は、開度が調整可能な流量調整器であり、第3の圧力検出手段130aで検出した圧力値と、第4の圧力検出手段130bで検出した圧力値との差が一定となるように開度を調整する。
また、バイパス配管114は、一端が第1の接続配管106に接続され、他端が第3の流量調整器115に接続されている。
したがって、第3の流量調整器115の開度に応じて、熱源機Aへ供給する冷媒量は変動する。
なお、上記の説明では、温度検出手段132は、サーミスタで形成される一例について説明したが、特にこれに限定しない。
第4の圧力検出手段130bは、第2の流量調整器113と、第2の熱交換器117及び第2の分岐部111との間に設けられた配管内を流れる冷媒の圧力を測定し、測定結果を制御部151に供給する。
なお、第3の圧力検出手段130a及び第4の圧力検出手段130bを総称して、圧力検出手段130と称する。圧力検出手段130は、測定結果をそのまま制御部151に供給してもよく、一定期間測定結果を蓄積後に蓄積した測定結果を所定の周期間隔で制御部151に供給してもよい。圧力検出手段130は冷媒圧力を検出できるものであればよく、種類などは限定されない。
上記で説明した利用側熱交換器105c及び第1の流量調整器109cで、冷媒回路の一部が構成される。
上記で説明した利用側熱交換器105d及び第1の流量調整器109dで、冷媒回路の一部が構成される。
該熱媒体システムは、熱源機側熱交換器103を流れる冷媒と熱交換を行う水やブラインなどの冷媒とは異なる熱媒体を、熱源機側熱交換器103に供給するためのものである。そのシステムの構成要素として、熱媒体流量調整器201、熱媒体搬送器202、熱媒体流入温度検出手段203、熱媒体流出温度検出手段204、および熱媒体流量制御装置250がある。該熱媒体システムは、通常、熱媒体の温度も調整できるように構成されている。
熱媒体流量制御装置250は、熱源機Aおよび組合せ熱源機の圧縮機の停止中または稼働中を判定する熱源機運転モード検知手段205と、複数の利用側熱交換器105の冷房運転と暖房運転のそれぞれの場合の容量の合計である室内機冷房運転容量の合計と、室内機暖房運転容量の合計とを検出する室内機運転モード検知手段210を備える。さらに、熱媒体流入温度検出手段203と熱媒体流出温度検出手段204の測定値の差を算出する、熱媒体温度差演算手段251を備える。
熱媒体流量制御装置250は、熱媒体温度差演算手段251での結果をもとに、熱源機側熱交換器103に供給する熱媒体の流量を算出する。
また、熱媒体流量制御装置250は、室内機冷房運転容量の合計、室内機暖房運転容量の合計、および熱源機Aと組合わせ熱源機の運転容量の合計(熱源機運転容量)から、熱源機側熱交換器103に供給する熱媒体の流量も算出する。
加えて、熱媒体流量制御装置250は、熱媒体流量値を入力できる設定スイッチ252を備えている。
なお、熱媒体流量制御装置250は、熱源機Aの制御部141に含められてもよい。
前提条件として、室内機Cには冷房運転、室内機Dには暖房運転がそれぞれ設定され、冷房主体で空気調和装置1の運転が行われると想定する。
第2の流量調整器113の開度は、第3の圧力検出手段130aと第4の圧力検出手段130bとの差圧が適度な値になるように制御される。
熱源機側熱交換器103は、水等の熱媒体と熱交換する。熱交換した高温高圧のガス冷媒は、気液二相の高温高圧の冷媒となる。次に、気液二相の高温高圧の冷媒は、第4の流量調整器122、逆止弁118を経て、第2の接続配管107を通過し、中継機Bの気液分離器112へ供給される。このとき、第1の圧力検出手段126の検出圧力値から得られる温度とその目標値との差に応じて切換弁125が所定の開度に制御される。
気液分離器112は、気液二相の高温高圧の冷媒を、ガス状冷媒と、液状冷媒とに分離する。
分離されたガス状冷媒は、第1の分岐部110へ流入する。第1の分岐部110へ流入したガス状冷媒は、開口している側の電磁弁108b、第5の接続配管106dを経て、暖房運転が設定されている室内機Dへ供給される。
また、利用側熱交換器105dは、利用側熱交換器105dの出口の過冷却度に基づいて、第1の流量調整器109dで制御される。
第1の流量調整器109dは、利用側熱交換器105dで凝縮液化された液冷媒を減圧し、高圧と、低圧との中間の圧力である中間圧の冷媒にする。
中間圧となった冷媒は、第2の分岐部111に流入される。
次に、第2の分岐部111では、供給された液状冷媒は、室内機C側に接続されている逆止弁131bを通過し、第4の接続配管107cを通って室内機Cへ流入する。
次に、流入した液状冷媒は、室内機Cの利用側熱交換器105cの出口の過熱度に応じて制御される第1の流量調整器109cを用いて低圧まで減圧された状態で、利用側熱交換器105cに供給される。
利用側熱交換器105cでは、供給された液状冷媒は、空気等の利用媒体と熱交換することで、蒸発してガス化する。
ガス化してガス冷媒となった冷媒は、第3の接続配管106cを通過し、第1の分岐部110へ流入する。第1の分岐部110では、室内機Cと接続された側の電磁弁108aが開口している。そこで、流入したガス冷媒は、室内機Cと接続された側の電磁弁108aを通過し、第1の接続配管106へ流入する。
次に、ガス冷媒は、逆止弁121よりも低圧の逆止弁119側へ流入し、四方弁102、アキュムレータ104を経て、圧縮機101へ吸入される。
このような動作で、冷凍サイクルが形成され、冷房主体運転が行われる。
前提条件として、室内機Cには暖房運転、室内機Dには冷房運転がそれぞれ設定され、暖房主体で空気調和装置1の運転が行われると想定する。
第2の流量調整器113の開度は、第3の圧力検出手段130aと第4の圧力検出手段130bとの差圧が適度な値になるように制御される。
気液分離器112は、高温高圧のガス冷媒を、第1の分岐部110へ供給する。第1の分岐部110へ供給されたガス冷媒は、開口している側の電磁弁108b、第3の接続配管106cを経て、暖房運転が設定されている室内機Cへ供給される。
また、利用側熱交換器105cは、利用側熱交換器105cの出口の過冷却度に基づいて、第1の流量調整器109cで制御される。
第1の流量調整器109cは、利用側熱交換器105cで凝縮液化された液冷媒を減圧し、高圧と、低圧との中間の圧力である中間圧の液冷媒にする。
中間圧となった液冷媒は、第4の接続配管107cを通って第2の分岐部111に流入される。
次に、室内機Dに流入した液状冷媒は、室内機Dの利用側熱交換器105dの出口の過熱度に応じて制御される第1の流量調整器109dを用いて低圧まで減圧されて蒸発温度が低い状態で、利用側熱交換器105dに供給される。
利用側熱交換器105dでは、供給された蒸発温度の低い液状冷媒は、空気等の利用媒体と熱交換することで、蒸発してガス化する。
次に、ガス冷媒は、逆止弁119よりも低圧の逆止弁121側へ流入し、気液分離器123を通過した液冷媒は、熱源機側熱交換器103に流入して蒸発してガス状態となり、四方弁102、アキュムレータ104を経て圧縮機101へ吸入される。また、気液分離器123を通過したガス冷媒は、第5の流量調整器124を通り、アキュムレータ104を経て圧縮機101へ吸入される。
このような動作で、冷凍サイクルが形成され、暖房主体運転が行われる。
暖房運転容量が大きくなるにつれ、中継機Bへ流入する冷媒の状態として、乾き度が大きい状態とする必要がある。この結果、熱源機Aが備える熱源機側熱交換器103の凝縮温度、すなわち、高圧圧力も低下していく。この現象のため、冷房運転している室内機Cの液管温度検出手段133が検出する液管温度は低下する。この結果、室内機Cは発停を繰り返すことになるため、空気調和装置1は、継続した冷房運転を維持することができなくなり、さらに、凝縮温度が低く、暖房能力が低下するため、空気調和装置1を利用するユーザーは不快な状態になる。
また、暖房能力を確保するには、熱源機側熱交換器103の凝縮温度、すなわち高圧圧力を所定値にする必要がある。
したがって、熱源機側熱交換器103を流れる冷媒量と切換弁125を介して熱源機側熱交換器103をバイパスする冷媒量は、冷房運転容量(室内機C)と暖房運転容量(室内機D)との比率により決定される。
横軸が切換弁125のCV値であると想定し、縦軸が熱源機側熱交換器103の流量を制御する第4の流量調整器122の開度比と想定する。また、ΣQjcは冷房時総熱量、ΣQjhは暖房時総熱量であるとそれぞれ想定する。
第4の流量調整器122の開度は、第1の圧力検出手段126の測定値と、熱源機側熱交換器103の出入口の冷媒温度検出手段128,129の測定値とにより決定される。また、熱源機側熱交換器103に流れる冷媒流量が多い領域では、過冷却度が小さくなり、熱源機側熱交換器103の出口乾き度が大きくなる。そのため、切換弁125に対する特性線は右上がりの傾きとなる。
なお、上記の説明では、室内機Dが増加した場合について説明したが、室内機Dが減少した場合についても同様に処理できる。よって、室内機Dが減少した場合には熱源機Aの第1の圧力検出手段126が検出する温度は大きくなる。つまり、上述した処理と逆のことをすればよい。
熱源機側熱交換器103と、
複数の利用側熱交換器105と、
熱源機側熱交換器103と複数の利用側熱交換器105との間に設けられ、複数の利用側熱交換器105の一部を冷房運転側に切り換え、複数の利用側熱交換器105の一部を暖房運転側に切り換える中継機Bと、
熱源機側熱交換器103に流入する冷媒の流量を調整する第4の流量調整器122と、
熱源機側熱交換器103をバイパスする流路に配置された切換弁125と、
第4の流量調整器122と切換弁125を調整する制御部141とを備え、
制御指令に応じて、複数の利用側熱交換器105のそれぞれを冷房運転側と暖房運転側とに切り換え、冷暖房同時運転を行う空気調和装置1であって、
熱源機側熱交換器103の入口圧力(圧縮機101の吐出圧力)と、熱源機側熱交換器103の冷媒の入口及び出口温度と、複数の利用側熱交換器105の冷房運転容量と暖房運転容量との比率に基づいて、熱源機側熱交換器103の目標制御温度を求め、目標制御温度に応じて、第4の流量調整器122及び切換弁125を調整し、熱源機側熱交換器103の流量を制御する。これにより、冷暖房同時運転中、冷房運転を行っている利用側熱交換器が複数存在する場合であっても、冷房運転もしくは暖房運転を行う制御を簡易にすることができる。この構成のため、低コストで、安定した冷暖房同時運転を継続させることができる。
図5は、実施の形態2に係わる熱媒体流量制御装置250が実行する熱媒体流量調整制御の流れを示すフローチャートを表す図である。図5に基づいて、熱媒体流量制御装置250が、入力値取得から熱媒体流量調整器201へ電気信号を出力するまでの流れを説明する。
熱源機Aが稼動できる状態になると熱媒体流量調整を開始する(ステップS101)。熱媒体流量調整を開始後、予め設定している所定時間T1秒(ここでは30秒とする)の経過を判断し(ステップS102)、経過していれば、次に進んで熱媒体流量調整に必要な入力値を取得する。入力値としては、熱源機運転モード検知手段205により熱源機Aの運転状態と(圧縮機101が停止中か動作中か)、熱媒体流入温度検出手段203および熱媒体流出温度検出手段204の測定値に基づく熱媒体温度差演算手段251からの熱媒体温度差と、を取得する(ステップS103)。続いて、熱媒体流量制御装置250は、熱源機Aの運転状態から、図6に示す関係を用いて熱媒体流量調整状態のパターン(パターンA、B、C、D)を決定する(ステップS104)。
また、ここでは電圧信号をベースに説明をしているが、電流信号であってもよい。
パターンCで算出する「熱媒体流量変化量dGw」は、熱源機側熱交換器103における熱媒体流入温度と熱媒体流出温度との温度差およびそれらの温度差の目標値を利用して、熱媒体流量制御装置250が図6に示す式から算出する。この式で、熱媒体流量Gwは現在値を表しており、たとえばパターンDからパターンCへの移行時では、熱媒体流量Gwは定格流量である。
なお、ここでは、熱媒体温度差目標値を5℃としているが、この熱媒体温度差目標値は熱交換器の仕様により決定されるものであり、5℃に限定されるものではない。
また、上記の熱媒体流量Gwは、組合わせ熱源を含めても、熱媒体流量調整器201が1台の場合のものである。組合わせ熱源の各熱源機が熱媒体流量調整器201をそれぞれ備える場合は、各熱源機の熱媒体流量は、Gw/nとなる(n=組合わせ熱源の台数)。
また、図6中のゲイン比率βは、一度の操作で必要なゲインに対して、制御間隔を考慮して設定する。例えば、整定時間最小となるゲイン比率は、制御間隔を2分、時定数(冷媒封入量/循環量)[秒]を4分=240秒としたとき、βは約0.19となる。
なお、下限値は、熱媒体流量調整器201の特性に応じて選択できるように複数設定されるのが好ましい。また、下限値は、熱源機Aの運転に支障をきたさない量であって、熱源機側熱交換器103の孔食防止または凍結防止のいずれからの観点から要求される流量から選択されてもよい。
熱媒体流量制御装置250は、下限値を設定する複数のスイッチ252またはボタンを備えるようにしてもよい。この場合のスイッチ252等は、下限値自体(最小流量)を変更するのに使用されるのではなく、熱媒体流量調整器201の仕様(定格Cv値)が異なっても、熱源機側熱交換器103に供給される最小流量が同じになるように設定するのに用いられる。
なお、パターンCへの安定状態に早く移行したいこと、または熱媒体流量調整器201の弁のこじりを避ける観点からは、パターンDの最大流量を定めるに際しては、熱媒体流量調整器201の開度は定格である最大開度より少し小さな開度とするのが良い。
熱源機Aが他の熱源機と組合わせて利用されるものであり、熱源機Aの圧縮機101が停止しているが、他の熱源機の圧縮機が運転している場合、熱媒体流量制御装置250は、熱媒体流量調整器201に供給する熱媒体の流量を上記下限値とするのが好ましい。
熱源機Aが他の熱源機と組合わせて利用されるものであり、熱源機Aの圧縮機101が停止し、かつ他の熱源機の圧縮機も停止している場合、熱媒体流量制御装置250は、熱媒体流量調整器201に供給する熱媒体の流量をゼロとする。
また、パターンCでは、熱源機側熱交換器103の熱媒体の流入側と流出側における熱媒体の目標温度差と実際の温度差からの差に比例して、熱媒体流量調整器201に供給する熱媒体の変更量を増大させる。
また、パターンCでは、熱源機側熱交換器103の熱媒体の流入側と流出側における熱媒体の目標温度差からの差が予め定めた値以下の場合には熱媒体の供給流量の変更量をゼロとする。
なお、熱媒体流量制御装置250と熱媒体流量調整器201との間の通信が切断されても熱源機Aに供給される熱媒体流量を確保するため、熱媒体流量調整器201への指令電気出力値が大の場合に流量小又は下限値とし、指令電気出力値が小の場合に流量大または定格流量となる組合せとするのが好ましい。
図8は実施の形態3に係わる熱媒体流量制御装置250が実行する熱媒体流量調整制御の流れを示すフローチャートを表す図である。図9は本発明の実施の形態3における熱媒体流量調整制御のフローチャートの別の一例を説明する図である。図10は本発明の実施の形態3における熱媒体流量調整状態の4つのパターン(パターンDは既に説明済みなので省略)の一例を説明する図である。図8~図10に基づいて、パターンC、C-1、及びC-2(演算流量)について説明する。なお、実施の形態3においては、実施の形態2と同一の処理については割愛する。また、図8のパターンCは、図9、図10のパターンC-2と同じであり、図9、図10のパターンC-1は、は図5、図6のパターンCと同じである。
ステップS117において、熱源機Aの圧縮機の運転周波数と、熱源機Aの圧縮機の最大周波数と、熱源機Aの圧縮機の最小周波数とに基づいて第2演算流量を算出する。ステップS118において、熱媒体流量制御装置250は、第1演算流量及び第2演算流量のうち大きい方を熱媒体流量調整器201に供給する熱媒体の流量とする。
Claims (20)
- 冷媒を圧縮して吐出する圧縮機と、
前記冷媒と前記冷媒とは異なる熱媒体との間で熱交換する熱源機側熱交換器と、
前記冷媒と周囲の利用媒体との間で熱交換する複数の利用側熱交換器と、
前記熱源機側熱交換器と、前記複数の利用側熱交換器との間に設けられ、前記複数の利用側熱交換器の一部を冷房運転に切り換え、前記複数の利用側熱交換器の一部を暖房運転に切り換える中継機と、
前記熱源機側熱交換器に供給する前記熱媒体の流量を調整可能な熱媒体システムとして、少なくとも1系統の熱媒体搬送器、熱媒体流量調整器、および熱媒体流量制御装置を備え、
前記圧縮機と前記熱源機側熱交換器が熱源機に配置され、前記利用側熱交換器が室内機に配置され、
制御指令に応じて、前記複数の利用側熱交換器のそれぞれを前記冷房運転と前記暖房運転とに切り換え、冷暖房同時運転を行う空気調和装置であって、
前記熱源機側熱交換器には、前記複数の利用側熱交換器の総冷房容量と総暖房容量との比率に応じて前記冷媒が流され、
前記熱媒体流量制御装置が、前記熱源機側熱交換器への熱媒体流入温度と、前記熱源機側熱交換器からの熱媒体流出温度とを利用して、前記熱源機側熱交換器に供給する前記熱媒体流量を制御するように構成されている空気調和装置。 - 前記熱源機によって定められた前記熱媒体の下限流量を下限値とし、前記熱媒体流量調整器の最大開度に対応した流量を上限値とし、
前記熱媒体流量制御装置は、前記下限値と前記上限値の間で前記熱媒体流量を制御する請求項1に記載の空気調和装置。 - 前記下限値は、前記熱媒体流量調整器の特性に応じて選択できるように複数設定されている請求項2に記載の空気調和装置。
- 前記下限値は、前記熱源機の運転に支障をきたさない、熱源機側熱交換器の孔食防止または凍結防止のいずれからの流量から選択される請求項2に記載の空気調和装置。
- 前記下限値を設定する複数のスイッチまたはボタンを備える請求項2~4のいずれか1項に記載の空気調和装置。
- 前記熱媒体流量制御装置は、前記熱源機の運転モードに応じて、前記熱媒体流量調整器を、熱媒体を流さない「流量ゼロ」、前記熱源機によって定められた最小流量である「下限流量」、前記熱媒体流入温度と、前記熱媒体流出温度と、該流入温度と該流出温度との目標差である熱媒体温度差目標値とに基づいて算出決定する「演算流量」、および前記熱媒体流量調整器の定格流量に対応する「最大流量」の4つのパターンで制御する請求項1~5のいずれか1項に記載の空気調和装置。
- 前記熱媒体流量制御装置は、前記熱源機が有する前記圧縮機が起動してからは前記最大流量とし、所定時間経過後に前記演算流量のパターンに移行するように、前記熱媒体流量調整器を制御する請求項6に記載の空気調和装置。
- 前記熱源機が他の熱源機と組合わせて利用されるものであり、前記熱源機の前記圧縮機が停止しているが、前記他の熱源機の圧縮機が運転している場合、
前記熱媒体流量制御装置は、前記熱媒体流量調整器に供給する前記熱媒体の流量を前記下限流量とする請求項6または7に記載の空気調和装置。 - 前記熱源機が他の熱源機と組合わせて利用されるものであり、前記熱源機の前記圧縮機が停止し、かつ前記他の熱源機の全ての圧縮機が停止している場合、
前記熱媒体流量制御装置は、前記熱媒体流量調整器に供給する前記熱媒体を前記流量ゼロとする請求項6または7に記載の空気調和装置。 - 前記演算流量のパターンでは、前記熱源機側熱交換器の前記熱媒体の流入側と流出側における熱媒体温度差が前記熱媒体温度差目標値より大きい時、前記熱媒体流量調整器に供給する前記熱媒体の流量を増大させる請求項6~9のいずれか1項に記載の空気調和装置。
- 前記演算流量のパターンでは、前記熱源機側熱交換器の前記熱媒体の流入側と流出側における前記熱媒体温度差目標値と実際の温度差からの差に比例して、前記熱媒体流量調整器に供給する前記熱媒体の変更量を増大させる請求項6~10のいずれか1項に記載の空気調和装置。
- 前記演算流量のパターンでは、前記熱媒体温度差目標値からの差が予め定めた値以下の場合には前記熱媒体の供給流量の変更量をゼロとする請求項6~11のいずれか1項に記載の空気調和装置。
- 前記熱媒体流量調整器に出力する開度指令の電気出力値は、前記最大流量に対応する出力値が前記下限流量に対応する出力値に対して小さくなるように設定されている請求項6~12のいずれか1項に記載の空気調和装置。
- 前記熱源機側熱交換器の熱媒体流入側と熱媒体流出側に前記熱媒体の温度を検出する熱媒体温度検出手段を備え、
熱媒体流量制御装置は、各熱媒体温度検出手段の検出結果に基づいて、前記流入側と前記流出側の前記熱媒体の温度差を求める熱媒体温度差演算手段を備える請求項1~13のいずれか1項に記載の空気調和装置。 - 冷媒を圧縮して吐出する圧縮機と、
前記冷媒と前記冷媒とは異なる熱媒体との間で熱交換する熱源機側熱交換器と、
前記冷媒と周囲の利用媒体との間で熱交換する複数の利用側熱交換器と、
前記熱源機側熱交換器と、前記複数の利用側熱交換器との間に設けられ、前記複数の利用側熱交換器の一部を冷房運転に切り換え、前記複数の利用側熱交換器の一部を暖房運転に切り換える中継機と、
前記熱源機側熱交換器に供給する前記熱媒体の流量を調整可能な熱媒体システムとして、少なくとも1系統の熱媒体搬送器、熱媒体流量調整器、および熱媒体流量制御装置を備え、
前記圧縮機と前記熱源機側熱交換器が熱源機に配置され、前記利用側熱交換器が室内機に配置され、
制御指令に応じて、前記複数の利用側熱交換器のそれぞれを前記冷房運転と前記暖房運転とに切り換え、冷暖房同時運転を行う空気調和装置であって、
前記熱源機の前記圧縮機の運転周波数と、前記熱源機の前記圧縮機の最大周波数と、前記熱源機の前記圧縮機の最小周波数とを利用して、前記熱源機側熱交換器に供給する熱媒体流量を制御するように構成されている空気調和装置。 - 前記熱媒体流量制御装置は、前記熱源機の運転モードに応じて、前記熱媒体流量調整器を、熱媒体を流さない「流量ゼロ」、前記熱源機によって定められた最小流量である「下限流量」、前記熱源機の前記圧縮機の運転周波数と、前記熱源機の前記圧縮機の最大周波数と、前記熱源機の前記圧縮機の最小周波数とに基づいて算出決定する「演算流量」、および前記熱媒体流量調整器の定格流量に対応する「最大流量」の4つのパターンで制御する請求項15に記載の空気調和装置。
- 前記演算流量のパターンでは、前記熱媒体流量制御装置は、前記熱源機の前記圧縮機の運転周波数が前記熱源機の前記圧縮機の最小周波数より大きいとき、前記熱媒体流量調整器に供給する前記熱媒体の流量を増大させる請求項16に記載の空気調和装置。
- 前記熱源機の前記圧縮機の運転周波数と、前記熱源機の前記圧縮機の最大周波数と、前記熱源機の前記圧縮機の最小周波数とを利用して、前記熱源機側熱交換器に供給する熱媒体流量を制御するように構成されている請求項1に記載の空気調和装置。
- 前記熱媒体流量制御装置は、前記熱源機の運転モードに応じて、前記熱媒体流量調整器を、熱媒体を流さない「流量ゼロ」、前記熱源機によって定められた最小流量である「下限流量」、前記熱源機側熱交換器への熱媒体流入温度と、前記熱源機側熱交換器からの熱媒体流出温度とに基づいて算出される第1演算流量、及び、前記熱源機の前記圧縮機の運転周波数と、前記熱源機の前記圧縮機の最大周波数と、前記熱源機の前記圧縮機の最小周波数とに基づいて第2演算流量に基づいて算出決定する「演算流量」、並びに前記熱媒体流量調整器の定格流量に対応する「最大流量」の4つのパターンで制御する請求項18に記載の空気調和装置。
- 前記演算流量のパターンでは、熱媒体流量制御装置は、前記第1演算流量及び前記第2演算流量のうち大きい方を前記熱媒体流量調整器に供給する前記熱媒体の流量とする請求項19に記載の空気調和装置。
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