EP3604972A1 - Hybrid chiller system - Google Patents
Hybrid chiller system Download PDFInfo
- Publication number
- EP3604972A1 EP3604972A1 EP19185716.8A EP19185716A EP3604972A1 EP 3604972 A1 EP3604972 A1 EP 3604972A1 EP 19185716 A EP19185716 A EP 19185716A EP 3604972 A1 EP3604972 A1 EP 3604972A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- outdoor unit
- ghp
- ehp
- control section
- refrigerant
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 103
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 70
- 238000004378 air conditioning Methods 0.000 claims description 55
- 238000001816 cooling Methods 0.000 claims description 24
- 238000010438 heat treatment Methods 0.000 claims description 23
- 239000003921 oil Substances 0.000 description 52
- 239000000498 cooling water Substances 0.000 description 27
- 238000004781 supercooling Methods 0.000 description 11
- 239000007788 liquid Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000005611 electricity Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
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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
- F25B27/00—Machines, plants or systems, using particular sources of energy
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
- 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
- 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
- F25B2313/003—Indoor unit with water as a heat sink or heat source
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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
- F25B2313/004—Outdoor unit with water as a heat sink or heat source
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2327/00—Refrigeration system using an engine for driving a 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/06—Several compression cycles arranged in parallel
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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
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
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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
- F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
Definitions
- the present invention relates to a hybrid chiller system, and more particularly relates to a hybrid chiller system in which a GHP outdoor unit and an EHP outdoor unit are for combined use.
- an air conditioner in which an indoor unit performs air conditioning by use of an outdoor unit in which a compressor to be driven by a gas engine or the like is mounted and an outdoor unit in which a compressor to be driven by electricity is mounted.
- an air conditioner including a second outdoor unit including a high-capacity compressor, a four-way valve and an outdoor heat exchanger, a first outdoor unit including a low-capacity compressor, a four-way valve and an outdoor heat exchanger, and an indoor unit connected to these outdoor units via one refrigerant system (e.g., see Japanese Patent Laid-Open No. 2017-150687 ).
- the above conventional air conditioner is an air heat exchange air conditioning system in which a GHP outdoor unit and an EHP outdoor unit are connected to an indoor unit, to exchange heat between a refrigerant and indoor air, thereby performing air conditioning.
- the present invention has been developed in view of the above described respects, and an object thereof is to provide a hybrid chiller system in which a chiller system can be constructed, and entrapment of a refrigerant or the like in the chiller system can be prevented.
- a hybrid chiller system including a GHP outdoor unit including a GHP compressor to be driven by a gas engine, an EHP outdoor unit including a compressor to be driven by a commercial power source, and a water heat exchanger that exchanges heat between a refrigerant and cold and hot water that are sent from the GHP outdoor unit and the EHP outdoor unit.
- the chiller system in which the water heat exchanger exchanges heat between the refrigerant and the cold and hot water by use of the GHP outdoor unit and the EHP outdoor unit.
- a hybrid chiller system of the present invention there can be constructed a chiller system in which a water heat exchanger exchanges heat with cold and hot water, by use of a GHP outdoor unit and an EHP outdoor unit.
- a hybrid chiller system in a first aspect of the present invention, includes a GHP outdoor unit including a GHP compressor to be driven by a gas engine, an EHP outdoor unit including a compressor to be driven by a commercial power source, and a water heat exchanger that exchanges heat between a refrigerant and cold and hot water that are sent from the GHP outdoor unit and the EHP outdoor unit.
- the chiller system in which the water heat exchanger exchanges heat with the cold and hot water by use of the GHP outdoor unit and the EHP outdoor unit.
- the hybrid chiller system includes a GHP control section that controls the GHP outdoor unit, an EHP control section that controls the EHP outdoor unit, and a controller control section that transmits a control instruction signal to each of the GHP control section and the EHP control section.
- the GHP control section can control the GHP outdoor unit
- the EHP control section can control the EHP outdoor unit
- the controller control section sets an upper limit horsepower based on an operation state of each of the GHP outdoor unit and the EHP outdoor unit, and transmits an instruction signal of this upper limit horsepower to each of the GHP control section and the EHP control section.
- air heat exchange air conditioning when an operation horsepower of the EHP outdoor unit does not satisfy an upper limit horsepower instruction of the EHP outdoor unit, the EHP control section notifies the GHP control section of the upper limit horsepower instruction not being satisfied, and the GHP control section performs control to lower rotation of the gas engine of the GHP outdoor unit.
- the GHP control section executes control so that the control to lower the rotation of the gas engine of the GHP outdoor unit is not performed.
- the GHP control section executes the control so that the control to lower the rotation of the gas engine of the GHP outdoor unit is not performed. Consequently, a water temperature fluctuation in the water heat exchanger can be decreased, and a stabilized operation can be performed.
- the GHP control section controls an opening degree of an electric valve based on a discharge temperature of the refrigerant of the GHP compressor.
- the GHP control section sets a threshold value of the discharge temperature of the refrigerant of the GHP compressor to be lower than when the air heat exchange air conditioning is performed, to execute the control.
- the threshold value of the discharge temperature of the refrigerant is set to be lower. Consequently, the opening degree of the electric valve can be controlled in such a tendency that the valve opens earlier. Furthermore, when the opening degree of the electric valve is controlled so that the valve opens earlier, rise of a high pressure or liquid seal can be prevented.
- the EHP control section when receiving an instruction signal of an upper limit horsepower of the EHP outdoor unit which is transmitted from the controller control section, raises the upper limit horsepower of the EHP outdoor unit to control the EHP outdoor unit.
- the EHP control section controls and raises the upper limit horsepower of the EHP outdoor unit. Consequently, stagnation of the refrigerant can be prevented, and the GHP outdoor unit can be prevented from running out of gas.
- the EHP control section controls and starts the EHP outdoor unit.
- the GHP control section opens an oil return valve of the GHP outdoor unit, and the EHP control section controls and opens a solenoid valve for a high pressure refrigerant, until the EHP outdoor unit starts. After the EHP outdoor unit starts, rotation of the gas engine of the GHP outdoor unit is controlled and inhibited.
- the EHP control section controls and starts the EHP outdoor unit.
- the GHP control section opens the oil return valve of the GHP outdoor unit, and the EHP control section controls and opens the solenoid valve for the high pressure refrigerant, until the EHP outdoor unit starts.
- the rotation of the gas engine of the GHP outdoor unit is controlled and inhibited. Consequently, refrigerant pressure balance between the GHP outdoor unit and the EHP outdoor unit can be acquired.
- the refrigerant that stagnates in the EHP outdoor unit can be supplied to the GHP outdoor unit, and the running out of the gas in the GHP outdoor unit can be solved.
- the GHP control section controls and maintains or lowers a rotation speed of the gas engine.
- the temperature difference between the inlet side temperature and the outlet side temperature of the water heat exchanger is large, control to increase the rotation speed of the gas engine is inhibited.
- Fig. 1 is a configuration diagram showing an embodiment of an air conditioner to which a hybrid chiller system according to the present invention is applied.
- an air conditioner 1 includes a GHP outdoor unit 2 including a GHP compressor 13 to be driven as a high capacity compressor by a gas engine 12, an EHP outdoor unit 3 including an EHP compressor 62 to be driven as a low capacity compressor by a commercial power source, and a water heat exchanger 8.
- the GHP outdoor unit 2, the EHP outdoor unit 3 and the water heat exchanger 8 are connected via an interunit pipe 5 and an oil balance pipe 6. Consequently, a refrigeration cycle circuit to perform an air conditioning operation is con stituted.
- the GHP outdoor unit 2 includes two external connection valves 10a and 10b to be connected to the external interunit pipe 5, and an oil connection valve 11 to be connected to the oil balance pipe 6.
- the gas engine 12 In the GHP outdoor unit 2, there are provided the gas engine 12, and a GHP compressor 13 that compresses a refrigerant by a drive force of the gas engine 12.
- the GHP compressor 13 is constituted of a first GHP compressor 13a and a second GHP compressor 13b that are provided in parallel.
- the gas engine 12 burns a mixed gas of a fuel such as a gas supplied through a fuel adjustment valve (not shown) and air supplied through a throttle valve (not shown) to generate the drive force.
- a fuel such as a gas supplied through a fuel adjustment valve (not shown) and air supplied through a throttle valve (not shown) to generate the drive force.
- a drive belt 14 is bridged between an output shaft of the gas engine 12 and a driven shaft of the GHP compressor 13, and the drive force of the gas engine 12 is transmitted via the drive belt 14, to drive the GHP compressor 13.
- An oil separator 15, a four-way valve 16 and two outdoor heat exchangers 17 and 17 are successively connected to a discharge side of the GHP compressor 13, and each outdoor heat exchanger 17 is connected to one external connection valve 10a via a refrigerant pipe 20.
- An outdoor fan 18 to exchange heat between the outdoor heat exchanger 17 and outdoor air is provided in the vicinity of the outdoor heat exchanger 17.
- the other external connection valve 10b is connected to the refrigerant pipe 20.
- a middle portion of this refrigerant pipe 20 is connected to a suction side of the GHP compressor 13 via the four-way valve 16 and an accumulator 19.
- Electric valves 24 and a check valve 25 are connected in parallel with the middle portion of the refrigerant pipe 20, and the refrigerant pipe 20 is connected to a liquid pipe 22 connected to an inflow side of the accumulator 19.
- a dry core 39 is provided between the outdoor heat exchanger 17 and the external connection valve 10a.
- a heat exchange refrigerant pipe 23 that connects the suction side of the GHP compressor 13 to the refrigerant pipe 20 is connected between the suction side of the GHP compressor 13 and the refrigerant pipe 20, and in this heat exchange refrigerant pipe 23, an electric valve 26 is provided.
- a plate type heat exchanger 27 is provided between the electric valve 26 of the heat exchange refrigerant pipe 23 and the suction side of the GHP compressor 13.
- the GHP outdoor unit 2 includes a bypass pipe 28 that connects a discharge side of the GHP compressor 13 to the suction side thereof.
- One end of the bypass pipe 28 is connected between the oil separator 15 and the four-way valve 16, and the other end of the bypass pipe 28 is connected between the accumulator 19 and the four-way valve 16.
- a part of the refrigerant on the discharge side of the GHP compressor 13 flows through the bypass pipe 28 to the suction side of the GHP compressor 13 due to a pressure difference.
- bypass valve 29 that adjusts a flow rate of the bypass pipe 28 is provided.
- the bypass valve 29 is an electric valve that can open and close stepwise.
- the GHP outdoor unit 2 includes an oil return pipe 30 that connects the oil separator 15 to the suction side of the GHP compressor 13. Lubricating oil stored in the oil separator 15 flows through the oil return pipe 30 to the suction side due to the pressure difference between the discharge side and the suction side of the GHP compressor 13.
- the oil return pipe 30 includes a first return pipe 31 that connects an oil outflow port of the oil separator 15 to the suction side of the GHP compressor 13, and a second return pipe 36 provided in parallel to the first return pipe 31.
- the first return pipe 31 includes a capillary tube 32.
- the second return pipe 36 is connected to the first return pipe 31 to pass by the capillary tube 32.
- One end of the second return pipe 36 is connected to an upstream side of the capillary tube 32 in the first return pipe 31, and the other end of the second return pipe 36 is connected to a downstream side of the capillary tube 32 in the first return pipe 31.
- the second return pipe 36 includes a capillary tube 33, and an oil return valve 34 provided on a downstream side of the capillary tube 33.
- the oil connection valve 11 is connected to an oil pipe 35.
- a middle portion of the oil pipe 35 is branched, so that one oil pipe is connected to the downstream side from the oil separator 15 of the refrigerant pipe 20, and the other oil pipe is connected between the capillary tube 33 of the second return pipe 36 and the oil return valve 34.
- the external connection valve 10a connected to the refrigerant pipe 20 is connected to one end of the water heat exchanger 8 via the interunit pipe 5. Furthermore, the other end of the water heat exchanger 8 is connected to the external connection valve 10b connected to the refrigerant pipe 20 via the interunit pipe 5.
- the water heat exchanger 8 is connected to a cold and hot water pipe, and the water heat exchanger 8 exchanges heat between the refrigerant sent from the GHP outdoor unit 2 and cold and hot water that flows through the cold and hot water pipe.
- a cold and hot water pipe 9 connected to the water heat exchanger 8 is connected to an unshown indoor unit, and configured to supply the cold and hot water to the indoor unit.
- the air conditioner 1 of the present embodiment includes a so-called hybrid outdoor unit including the GHP outdoor unit 2 and the EHP outdoor unit 3, and is considered as an air conditioner of the hybrid chiller system in which a chiller system performs the air conditioning by use of the GHP outdoor unit 2 and the EHP outdoor unit 3.
- an inlet temperature sensor 120 that detects an inlet side temperature of the refrigerant and an outlet temperature sensor 121 that detects an outlet side temperature of the refrigerant.
- the GHP outdoor unit 2 includes a cooling water circuit 50 of the gas engine 12.
- the cooling water circuit 50 includes a cooling water three-way valve 52, the plate type heat exchanger 27, a radiator 53 disposed close to the one outdoor heat exchanger 17, a cooling water pump 54, and an exhaust gas heat exchanger 55 of the gas engine 12, which are connected in order from the gas engine 12 via a cooling water pipe 51.
- the cooling water pump 54 is driven, to circulate cooling water through this circuit.
- the cooling water pipe 51 of the cooling water circuit 50 is shown by a double line in Fig. 1 , and flow of the cooling water is shown by a solid arrow line.
- the electric valve 26 is operated to heat the refrigerant that returns to the GHP compressor 13 with the cooling water that flows through the cooling water pipe 51. Consequently, a low pressure of the refrigerant rises, and a heating efficiency improves.
- the cooling water circuit 50 can form a first route in which the cooling water flows in order from the gas engine 12 through the cooling water three-way valve 52, the radiator 53, the cooling water pump 54, and the exhaust gas heat exchanger 55 to the gas engine 12.
- the cooling water circuit 50 can form a second route in which the cooling water flows in order from the gas engine 12 through the cooling water three-way valve 52, the plate type heat exchanger 27, the cooling water pump 54 and the exhaust gas heat exchanger 55 to the gas engine 12.
- a hot water three-way valve 56 is provided in a middle of the first route that connects the radiator 53 to the cooling water three-way valve 52.
- the hot water three-way valve 56 is connected to a hot water heat exchanger 57 that exchanges heat between the cooling water and hot water, and the cooling water that flows through the hot water heat exchanger 57 is returned to an upstream side of the cooling water pump 54.
- the EHP outdoor unit 3 includes two external connection valves 60 to be connected to the external interunit pipe 5 and an oil connection valve 61 to be connected to the oil balance pipe 6.
- the EHP outdoor unit 3 includes the EHP compressor 62 to be driven by the commercial power source. It is considered that an example of this EHP compressor 62 is an inverter type compressor that can vary an output.
- a discharge side of the EHP compressor 62 is connected to an oil separator 63, a four-way valve 64 and two outdoor heat exchangers 65 and 65 in order, and the outdoor heat exchanger 65 is connected to one external connection valve 60a via a refrigerant pipe 66.
- an outdoor fan 105 (see Fig. 2 ) is provided to exchange heat between the outdoor heat exchanger 65 and the outdoor air.
- a supercooling heat exchanger 90 is provided between the outdoor heat exchanger 65 and the external connection valve 60a.
- Two systems of pipe lines are formed in the outdoor heat exchanger 65, and the refrigerant pipe 66 on a four-way valve 64 side and the refrigerant pipe 66 on a supercooling heat exchanger 90 side are respectively branched and connected to the outdoor heat exchanger 65. Furthermore, outdoor electronic control valves 68 and 68 are provided in the refrigerant pipe 66 on the supercooling heat exchanger 90 side of the outdoor heat exchanger 65.
- the supercooling heat exchanger 90 includes two heat exchange units 91 and 91.
- the refrigerant pipe 66 on an outdoor heat exchanger 65 side and a refrigerant pipe 67 on an external connection valve 60a side are respectively branched and connected to each heat exchange unit 91 of the supercooling heat exchanger 90.
- each heat exchange unit 91 is a double pipe type heat exchanger. Outer pipes of the heat exchange units 91 are connected to the refrigerant pipe 66 on the outdoor heat exchanger 65 side and the refrigerant pipe 67 on the external connection valve 60a side, respectively.
- a middle portion of the refrigerant pipe 67 that connects the supercooling heat exchanger 90 to the external connection valve 60a is connected to a supercooling branch pipe 92.
- a middle portion of this supercooling branch pipe 92 is connected to an inner pipe 94 of each heat exchange unit 91 via a supercooling electronic control valve 93.
- the refrigerant that flows through the inner pipe 94 of the heat exchange unit 91 is returned to the refrigerant pipe 66 between the four-way valve 64 and an accumulator 69 via a supercooling refrigerant pipe 95.
- An external connection valve 60b on the other side is connected to a suction side of the EHP compressor 62 via the refrigerant pipe 66, and the four-way valve 64 and the accumulator 69 are provided in a middle portion of the refrigerant pipe 66.
- a middle portion of the refrigerant pipe 66 which is between the EHP compressor 62 and the oil separator 63 is provided with a refrigerant return pipe 70 branched and connected to the refrigerant pipe 66 between the EHP compressor 62 and the accumulator 69.
- a refrigerant returning solenoid valve 71 is provided in a middle portion of the refrigerant return pipe 70. Then, when the refrigerant returning solenoid valve 71 is opened, a part of the refrigerant does not circulate in a refrigeration cycle and is guided to the suction side of the EHP compressor 62.
- a lower portion of the oil separator 63 is connected to an oil pipe 72, and a middle portion of the oil pipe 72 is connected to an oil return pipe 73 connected to the suction side of the EHP compressor 62.
- the oil return pipe 73 includes two branch pipes 74 and 75 that branch from the oil pipe 72, one branch pipe 74 is provided with an oil return valve 76, and the other branch pipe 75 is provided with a capillary tube 78. Furthermore, a capillary tube 79 is provided between connection portions of the oil pipe 72 to the respective branch pipes 74 and 75.
- a middle portion of the refrigerant pipe 66 which is between the oil separator 63 and the four-way valve 64 is connected to a high pressure refrigerant pipe 80 midway branched and connected to a middle portion of the oil pipe 72.
- a middle portion of the high pressure refrigerant pipe 80 is provided with a solenoid valve 81 for a high pressure refrigerant.
- the accumulator 69 includes an inflow pipe 82 into which the refrigerant of the refrigerant pipe 66 flows, and an outflow pipe 83 that sends an inner gas refrigerant of the accumulator 69 to the EHP compressor 62.
- the outflow pipe 83 is configured to open in an inner upper portion of the accumulator 69, and to send, to the EHP compressor 62, a gas refrigerant accumulated in the inner upper portion of the accumulator 69.
- the EHP compressor 62 is connected to an overflow pipe 84 connected to the suction side of the EHP compressor 62.
- an overflow pipe 84 connected to the suction side of the EHP compressor 62.
- a strainer 85 and a throttle 86 to decompress oil are incorporated.
- the external connection valve 60a of the EHP outdoor unit 3 is connected to one end of the interunit pipe 5, and the other end of the interunit pipe 5 is connected to a middle portion of the interunit pipe 5 which connects the external connection valve 10a of the GHP outdoor unit 2 to the water heat exchanger 8.
- the external connection valve 60b connected to a refrigerant pipe of the EHP outdoor unit 3 is connected to one end of the interunit pipe 5, and the other end of the interunit pipe 5 is connected to a middle portion of the interunit pipe 5 which connects the external connection valve 10b of the GHP outdoor unit 2 to the water heat exchanger 8.
- the oil connection valve 61 of the EHP outdoor unit 3 is connected to the oil connection valve 11 of the GHP outdoor unit 2 via the oil balance pipe 6. Consequently, the GHP compressor 13 of the GHP outdoor unit 2 and the EHP compressor 62 of the EHP outdoor unit 3 can supply the oil to each other via the oil balance pipe 6, and balance of an oil amount can be held between the GHP compressor 13 of the GHP outdoor unit 2 and the EHP compressor 62 of the EHP outdoor unit 3.
- the refrigerant is supplied to an indoor heat exchanger of the indoor unit from the GHP outdoor unit 2 and the EHP outdoor unit 3 in place of the water heat exchanger 8. Consequently, an air conditioning system by air heat exchange can be constructed.
- the air conditioning that is performed by this air heat exchange is referred to as the air heat exchange air conditioning.
- Fig. 2 is a block diagram showing the control configuration in the present embodiment.
- the GHP outdoor unit 2 includes a GHP control section 100 as a control section
- the EHP outdoor unit 3 includes an EHP control section 101 as a control section.
- the air conditioner includes a controller 110 that sends a control instruction signal to each of the GHP outdoor unit 2 and the EHP outdoor unit 3.
- the controller 110 includes a controller control section 111 to generally control the GHP control section 100 and the EHP control section 101.
- Each of the GHP control section 100, the EHP control section 101 and the controller control section 111 includes, for example, a computation processing circuit such as a CPU, storage means such as ROM and RAM, and others, and executes a predetermined program to perform predetermined control.
- the GHP control section 100 is configured to perform drive control of the gas engine 12, the outdoor fan 18 and the cooling water pump 54 of the GHP outdoor unit 2, and to perform opening and closing control or opening degree control of the external connection valves 10a and 10b, the oil connection valve 11, the electric valve 24, the electric valve 26, the bypass valve 29, the oil return valve 34 and the cooling water three-way valve 52 of the GHP outdoor unit 2.
- the EHP control section 101 is configured to perform drive control of the EHP compressor 62 and the outdoor fan 105 of the EHP outdoor unit 3, and to perform opening and closing control or opening degree control of the external connection valves 60a and 60b, the oil connection valve 61, the outdoor electronic control valve 68, the refrigerant returning solenoid valve 71, the oil return valve 76, the solenoid valve 81 for the high pressure refrigerant and the supercooling electronic control valve 93 of the EHP outdoor unit 3.
- the GHP control section 100 is set to a master, and the EHP control section 101 and an indoor control section are set to slaves.
- the control instruction signal from the controller control section 111 is first transmitted to the GHP control section 100, and this control instruction signal is sequentially transmitted from the GHP control section 100 to the EHP control section 101 and the indoor control section.
- each of the GHP outdoor unit 2 and the EHP outdoor unit 3 adjusts an output in accordance with a cooling load. For example, when the cooling load is a low load, the EHP outdoor unit 3 is driven, and as the cooling load increases, the EHP outdoor unit 3 is stopped, and the GHP outdoor unit 2 is started. When the cooling load is a high load, the GHP outdoor unit 2 is driven, and additionally the EHP outdoor unit 3 is driven.
- the controller 110 controls the GHP outdoor unit 2 and the EHP outdoor unit 3 based on a number of indoor units to be operated, a set temperature, an outdoor air temperature, and the like. Consequently, a control signal is output to each of the GHP control section 100 and the EHP control section 101 so that an operation of the GHP outdoor unit 2 and an operation of the EHP outdoor unit 3 save energy most.
- the GHP control section 100 efficiently controls the operation of the GHP outdoor unit 2
- the EHP control section 101 efficiently controls the operation of the EHP outdoor unit 3.
- the controller control section 111 sets an upper limit horsepower based on an operation state of each of the GHP outdoor unit 2 and the EHP outdoor unit 3, transmits an instruction signal of this upper limit horsepower to the GHP control section 100, and transmits the signal to the EHP control section via the GHP control section 100. Then, each of the GHP control section 100 and the EHP control section 101 controls the operation in accordance with the upper limit horsepower set by the controller control section 111.
- the GHP control section 100 judges that an operation horsepower of the EHP outdoor unit 3 does not satisfy an upper limit horsepower instruction of the EHP outdoor unit 3, the GHP control section 100 performs control to lower rotation of the gas engine 12 of the GHP outdoor unit 2.
- the GHP control section 100 performs control so that the above described control to lower the rotation of the gas engine 12 of the GHP outdoor unit 2 is not performed.
- the GHP control section 100 controls an opening degree of the electric valve 24. That is, the GHP control section 100 controls suction super heat or discharge super heat based on a discharge temperature of the refrigerant of the GHP compressor 13.
- the GHP control section 100 sets a threshold value of the discharge temperature of the refrigerant of the GHP compressor 13 to be lower than when the air heat exchange air conditioning is performed, to execute the control.
- the threshold value is set to be lower. Consequently, the opening degree of the electric valves 24 can be controlled in such a tendency that the valve opens earlier. Therefore, when the chiller air conditioning is performed, the output is to be raised to acquire a necessary capacity.
- the opening degree of the electric valve 24 is small, there is concern that a high pressure rises or that liquid seal of the water heat exchanger 8 is generated.
- the opening degree of the electric valve 24 is controlled so that the valve opens earlier, the rise of the high pressure or the liquid seal can be prevented.
- the GHP control section 100 controls the opening degree of the electric valve 24 so that the valve opens earlier. Consequently, the rise of the high pressure or the liquid seal can be prevented.
- the EHP control section 101 raises the upper limit horsepower of the EHP outdoor unit 3 to control the EHP outdoor unit 3.
- the refrigerant may stagnate in the EHP outdoor unit 3.
- the GHP outdoor unit 2 runs out of gas.
- the EHP control section 101 controls and raises the upper limit horsepower of the EHP outdoor unit 3. Consequently, the refrigerant is prevented from stagnating, and the GHP outdoor unit 2 can be prevented from running out of gas.
- the upper limit horsepower of the EHP outdoor unit 3 is controlled and uniformly raised, for example, as much as a predetermined percentage set in advance.
- the GHP outdoor unit 2 runs out of gas, and oil runs short.
- the GHP control section 100 sends a start instruction to the EHP control section 101, and the EHP control section 101 starts the EHP outdoor unit 3, and controls the GHP outdoor unit 2 and the EHP outdoor unit 3 to operate.
- the GHP control section 100 judges that the gas runs out. In this case, the GHP control section 100 sends the start instruction to the EHP control section 101, and the EHP control section 101 controls and starts the EHP outdoor unit 3.
- the GHP control section 100 opens the oil return valve 34 of the GHP outdoor unit 2, and the EHP control section 101 controls and opens the solenoid valve 81 for the high pressure refrigerant, until the EHP outdoor unit 3 starts.
- the GHP control section 100 judges that the EHP outdoor unit 3 starts, the GHP control section 100 controls and inhibits the rotation of the gas engine 12 of the GHP outdoor unit 2. Such control can acquire balance in refrigerant pressure between the GHP outdoor unit 2 and the EHP outdoor unit 3. The refrigerant that stagnates in the EHP outdoor unit 3 can be supplied to the GHP outdoor unit 2, and the running out of the gas in the GHP outdoor unit 2 can be solved.
- the GHP outdoor unit 2 runs out of gas, based on a temperature difference between the inlet side temperature and the outlet side temperature of the water heat exchanger 8 and an opening degree of a water heat exchanging valve. That is, when the opening degree of the water heat exchanging valve is large and the temperature difference between the inlet side temperature and the outlet side temperature is large, it is determined that the gas runs out.
- the temperature difference is small between the inlet side temperature and the outlet side temperature of the water heat exchanger 8 which are detected by the inlet temperature sensor 120 and the outlet temperature sensor 121.
- the GHP control section 100 controls and maintains or lowers a rotation speed of the gas engine 12.
- the GHP control section 100 inhibits control to increase the rotation speed of the gas engine 12.
- Such control can prevent the temperature of the water heat exchanger 8 from extremely dropping during the cooling operation. As a result, delay in control to start the stopped EHP outdoor unit 3 can be prevented, and the GHP outdoor unit 2 can be prevented from running out of gas.
- the hybrid chiller system includes the GHP outdoor unit 2 including the GHP compressor 13 to be driven by the gas engine 12, the EHP outdoor unit 3 including the compressor to be driven by the commercial power source, and the water heat exchanger 8 that exchanges heat between the refrigerant and the cold and hot water that are sent from the GHP outdoor unit 2 and the EHP outdoor unit 3.
- the hybrid chiller system includes the GHP control section 100 that controls the GHP outdoor unit 2, the EHP control section 101 that controls the EHP outdoor unit 3, and the controller control section 111 that transmits the control instruction signal to each of the GHP control section 100 and the EHP control section 101.
- the GHP control section 100 can control the GHP outdoor unit 2
- the EHP control section 101 can control the EHP outdoor unit 3.
- the controller control section 111 sets the upper limit horsepower based on the operation state of each of the GHP outdoor unit 2 and the EHP outdoor unit 3, and transmits the instruction signal of this upper limit horsepower to each of the GHP control section 100 and the EHP control section.
- the EHP control section 101 notifies the GHP control section 100 of the upper limit horsepower instruction not being satisfied, and the GHP control section 100 performs control to lower the rotation of the gas engine 12 of the GHP outdoor unit 2.
- the GHP control section 100 executes control so that the control to lower the rotation of the gas engine 12 of the GHP outdoor unit 2 is not performed.
- the GHP control section 100 executes the control so that the control to lower the rotation of the gas engine 12 of the GHP outdoor unit 2 is not performed. Consequently, a water temperature fluctuation in the water heat exchanger 8 can be decreased, and a stabilized operation can be performed.
- the GHP control section 100 controls the opening degree of the electric valve 24 based on the discharge temperature of the refrigerant of the GHP compressor 13.
- the GHP control section 100 sets the threshold value of the discharge temperature of the refrigerant of the GHP compressor 13 to be lower than when the air heat exchange air conditioning is performed, to execute the control.
- the threshold value of the discharge temperature of the refrigerant is set to be lower. Consequently, the opening degree of the electric valve 24 can be controlled in such a tendency that the valve opens earlier. Furthermore, when the opening degree of the electric valve 24 is controlled so that the valve opens earlier, the rise of the high pressure or the liquid seal can be prevented.
- the EHP control section 101 raises the upper limit horsepower of the EHP outdoor unit 3 to control the EHP outdoor unit 3.
- the EHP control section 101 controls and raises the upper limit horsepower of the EHP outdoor unit 3. Consequently, the stagnation of the refrigerant can be prevented, and the GHP outdoor unit 2 can be prevented from running out of gas.
- the EHP control section 101 controls and starts the EHP outdoor unit 3.
- the GHP control section 100 opens the oil return valve 34 of the GHP outdoor unit 2, and the EHP control section 101 controls and opens the solenoid valve 81 for the high pressure refrigerant, until the EHP outdoor unit 3 starts. After the EHP outdoor unit 3 starts, the rotation of the gas engine 12 of the GHP outdoor unit 2 is controlled and inhibited.
- the EHP control section 101 controls and starts the EHP outdoor unit 3.
- the GHP control section 100 opens the oil return valve 34 of the GHP outdoor unit 2, and the EHP control section 101 controls and opens the solenoid valve for the high pressure refrigerant, until the EHP outdoor unit 3 starts.
- the rotation of the gas engine 12 of the GHP outdoor unit 2 is controlled and inhibited. Consequently, the refrigerant pressure balance between the GHP outdoor unit 2 and the EHP outdoor unit 3 can be acquired.
- the refrigerant that stagnates in the EHP outdoor unit 3 can be supplied to the GHP outdoor unit 2, and the running out of gas in the GHP outdoor unit 2 can be solved.
- the GHP control section 100 controls and maintains or lowers the rotation speed of the gas engine 12.
- the control to increase the rotation speed of the gas engine 12 is inhibited.
- the GHP control section 100 is set to the master, and the EHP control section 101 is set to the slave, but the present invention is not limited to this example.
- the EHP control section 101 may be set to a master, the GHP control section 100 may be set to a slave, and the control instruction signal from the controller control section 111 may be first transmitted to the EHP control section 101.
- the GHP control section 100, the EHP control section 101 and the indoor control section may be connected in parallel to the controller control section 111, and the controller control section 111 may individually transmit control instruction signals to the GHP control section 100, the EHP control section 101 and the indoor control section.
- the air conditioning is performed by using the chiller system
- the air conditioning is not restrictive.
- the present invention can be also applied to process cooling, heating application or the like.
- the hybrid chiller system according to the present invention can construct the chiller system, and can be preferably utilized as the hybrid chiller system that can prevent stagnation of the refrigerant in the chiller system.
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Abstract
Description
- The present invention relates to a hybrid chiller system, and more particularly relates to a hybrid chiller system in which a GHP outdoor unit and an EHP outdoor unit are for combined use.
- In general, there is known an air conditioner in which an indoor unit performs air conditioning by use of an outdoor unit in which a compressor to be driven by a gas engine or the like is mounted and an outdoor unit in which a compressor to be driven by electricity is mounted.
- As this air conditioner, there has been heretofore disclosed, for example, an air conditioner including a second outdoor unit including a high-capacity compressor, a four-way valve and an outdoor heat exchanger, a first outdoor unit including a low-capacity compressor, a four-way valve and an outdoor heat exchanger, and an indoor unit connected to these outdoor units via one refrigerant system (e.g., see Japanese Patent Laid-Open No.
2017-150687 - However, the above conventional air conditioner is an air heat exchange air conditioning system in which a GHP outdoor unit and an EHP outdoor unit are connected to an indoor unit, to exchange heat between a refrigerant and indoor air, thereby performing air conditioning.
- On the other hand, in recent years, there has been demand for a chiller system in which a GHP outdoor unit and an EHP outdoor unit are connected to a water heat exchanger, and heat is exchanged with a refrigerant by this water heat exchanger, to produce cold and hot water.
- Furthermore, when the chiller system is constructed, there is concern that a problem of entrapment of the refrigerant or deviation of the refrigerant occurs, because a heat exchange volume is not large and a refrigerant pipe is comparatively short differently from the air heat exchange air conditioner system.
- The present invention has been developed in view of the above described respects, and an object thereof is to provide a hybrid chiller system in which a chiller system can be constructed, and entrapment of a refrigerant or the like in the chiller system can be prevented.
- To achieve the above object, according to one aspect of the present invention, there is provided a hybrid chiller system including a GHP outdoor unit including a GHP compressor to be driven by a gas engine, an EHP outdoor unit including a compressor to be driven by a commercial power source, and a water heat exchanger that exchanges heat between a refrigerant and cold and hot water that are sent from the GHP outdoor unit and the EHP outdoor unit.
- According to this system, there can be constructed the chiller system in which the water heat exchanger exchanges heat between the refrigerant and the cold and hot water by use of the GHP outdoor unit and the EHP outdoor unit.
- According to a hybrid chiller system of the present invention, there can be constructed a chiller system in which a water heat exchanger exchanges heat with cold and hot water, by use of a GHP outdoor unit and an EHP outdoor unit.
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Fig. 1 is a configuration diagram of an air conditioner according to an embodiment of the present invention; and -
Fig. 2 is a block diagram showing a functional configuration of the air conditioner. - In a first aspect of the present invention, a hybrid chiller system includes a GHP outdoor unit including a GHP compressor to be driven by a gas engine, an EHP outdoor unit including a compressor to be driven by a commercial power source, and a water heat exchanger that exchanges heat between a refrigerant and cold and hot water that are sent from the GHP outdoor unit and the EHP outdoor unit.
- According to this system, it is possible to construct the chiller system in which the water heat exchanger exchanges heat with the cold and hot water by use of the GHP outdoor unit and the EHP outdoor unit.
- In a second aspect of the present invention, the hybrid chiller system includes a GHP control section that controls the GHP outdoor unit, an EHP control section that controls the EHP outdoor unit, and a controller control section that transmits a control instruction signal to each of the GHP control section and the EHP control section.
- According to this system, based on the control instruction signal from the controller control section, the GHP control section can control the GHP outdoor unit, and the EHP control section can control the EHP outdoor unit.
- In a third aspect of the present invention, the controller control section sets an upper limit horsepower based on an operation state of each of the GHP outdoor unit and the EHP outdoor unit, and transmits an instruction signal of this upper limit horsepower to each of the GHP control section and the EHP control section. In a case where air heat exchange air conditioning is performed, when an operation horsepower of the EHP outdoor unit does not satisfy an upper limit horsepower instruction of the EHP outdoor unit, the EHP control section notifies the GHP control section of the upper limit horsepower instruction not being satisfied, and the GHP control section performs control to lower rotation of the gas engine of the GHP outdoor unit. When chiller air conditioning is performed and a heating operation is performed, the GHP control section executes control so that the control to lower the rotation of the gas engine of the GHP outdoor unit is not performed.
- According to this system, when the chiller air conditioning is performed and the heating operation is performed, the GHP control section executes the control so that the control to lower the rotation of the gas engine of the GHP outdoor unit is not performed. Consequently, a water temperature fluctuation in the water heat exchanger can be decreased, and a stabilized operation can be performed.
- In a fourth aspect of the present invention, when air heat exchange air conditioning is performed and a heating operation is performed, the GHP control section controls an opening degree of an electric valve based on a discharge temperature of the refrigerant of the GHP compressor. When chiller air conditioning is performed and the heating operation is performed, the GHP control section sets a threshold value of the discharge temperature of the refrigerant of the GHP compressor to be lower than when the air heat exchange air conditioning is performed, to execute the control.
- According to this system, when the chiller air conditioning is performed and the heating operation is performed, the threshold value of the discharge temperature of the refrigerant is set to be lower. Consequently, the opening degree of the electric valve can be controlled in such a tendency that the valve opens earlier. Furthermore, when the opening degree of the electric valve is controlled so that the valve opens earlier, rise of a high pressure or liquid seal can be prevented.
- In a fifth aspect of the present invention, in a case where chiller air conditioning is performed and a cooling operation is performed by the GHP outdoor unit and the EHP outdoor unit, when receiving an instruction signal of an upper limit horsepower of the EHP outdoor unit which is transmitted from the controller control section, the EHP control section raises the upper limit horsepower of the EHP outdoor unit to control the EHP outdoor unit.
- According to this system, the EHP control section controls and raises the upper limit horsepower of the EHP outdoor unit. Consequently, stagnation of the refrigerant can be prevented, and the GHP outdoor unit can be prevented from running out of gas.
- In a sixth aspect of the present invention, in a case where chiller air conditioning is performed and a cooling operation is performed by the GHP outdoor unit, when the GHP control section judges that gas runs out, the EHP control section controls and starts the EHP outdoor unit. The GHP control section opens an oil return valve of the GHP outdoor unit, and the EHP control section controls and opens a solenoid valve for a high pressure refrigerant, until the EHP outdoor unit starts. After the EHP outdoor unit starts, rotation of the gas engine of the GHP outdoor unit is controlled and inhibited.
- According to this system, the EHP control section controls and starts the EHP outdoor unit. The GHP control section opens the oil return valve of the GHP outdoor unit, and the EHP control section controls and opens the solenoid valve for the high pressure refrigerant, until the EHP outdoor unit starts. After the EHP outdoor unit starts, the rotation of the gas engine of the GHP outdoor unit is controlled and inhibited. Consequently, refrigerant pressure balance between the GHP outdoor unit and the EHP outdoor unit can be acquired. The refrigerant that stagnates in the EHP outdoor unit can be supplied to the GHP outdoor unit, and the running out of the gas in the GHP outdoor unit can be solved.
- In a seventh aspect of the present invention, in a case where chiller air conditioning is performed and a cooling operation is performed, when a temperature difference between an inlet side temperature and an outlet side temperature of the water heat exchanger is small, the GHP control section controls and maintains or lowers a rotation speed of the gas engine. When the temperature difference between the inlet side temperature and the outlet side temperature of the water heat exchanger is large, control to increase the rotation speed of the gas engine is inhibited.
- According to this system, when the temperature difference between the inlet side temperature and the outlet side temperature of the water heat exchanger is large, the control to increase the rotation speed of the gas engine is inhibited. Consequently, the temperature of the water heat exchanger can be prevented from extremely dropping during the cooling operation. As a result, delay in control to start the stopped EHP outdoor unit can be prevented, and the GHP outdoor unit can be prevented from running out of gas.
- Hereinafter, description will be made as to an embodiment of the present invention with reference to the drawing.
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Fig. 1 is a configuration diagram showing an embodiment of an air conditioner to which a hybrid chiller system according to the present invention is applied. - As shown in
Fig. 1 , an air conditioner 1 includes a GHPoutdoor unit 2 including aGHP compressor 13 to be driven as a high capacity compressor by agas engine 12, an EHPoutdoor unit 3 including an EHPcompressor 62 to be driven as a low capacity compressor by a commercial power source, and awater heat exchanger 8. The GHPoutdoor unit 2, the EHPoutdoor unit 3 and thewater heat exchanger 8 are connected via aninterunit pipe 5 and anoil balance pipe 6. Consequently, a refrigeration cycle circuit to perform an air conditioning operation is con stituted. - The GHP
outdoor unit 2 includes twoexternal connection valves external interunit pipe 5, and anoil connection valve 11 to be connected to theoil balance pipe 6. - In the GHP
outdoor unit 2, there are provided thegas engine 12, and aGHP compressor 13 that compresses a refrigerant by a drive force of thegas engine 12. The GHPcompressor 13 is constituted of afirst GHP compressor 13a and asecond GHP compressor 13b that are provided in parallel. - The
gas engine 12 burns a mixed gas of a fuel such as a gas supplied through a fuel adjustment valve (not shown) and air supplied through a throttle valve (not shown) to generate the drive force. - A
drive belt 14 is bridged between an output shaft of thegas engine 12 and a driven shaft of theGHP compressor 13, and the drive force of thegas engine 12 is transmitted via thedrive belt 14, to drive theGHP compressor 13. - An
oil separator 15, a four-way valve 16 and twooutdoor heat exchangers GHP compressor 13, and eachoutdoor heat exchanger 17 is connected to oneexternal connection valve 10a via arefrigerant pipe 20. Anoutdoor fan 18 to exchange heat between theoutdoor heat exchanger 17 and outdoor air is provided in the vicinity of theoutdoor heat exchanger 17. - Furthermore, the other
external connection valve 10b is connected to therefrigerant pipe 20. A middle portion of thisrefrigerant pipe 20 is connected to a suction side of theGHP compressor 13 via the four-way valve 16 and anaccumulator 19. -
Electric valves 24 and acheck valve 25 are connected in parallel with the middle portion of therefrigerant pipe 20, and therefrigerant pipe 20 is connected to aliquid pipe 22 connected to an inflow side of theaccumulator 19. Adry core 39 is provided between theoutdoor heat exchanger 17 and theexternal connection valve 10a. - Furthermore, a heat
exchange refrigerant pipe 23 that connects the suction side of theGHP compressor 13 to therefrigerant pipe 20 is connected between the suction side of theGHP compressor 13 and therefrigerant pipe 20, and in this heatexchange refrigerant pipe 23, anelectric valve 26 is provided. A platetype heat exchanger 27 is provided between theelectric valve 26 of the heatexchange refrigerant pipe 23 and the suction side of theGHP compressor 13. - The GHP
outdoor unit 2 includes abypass pipe 28 that connects a discharge side of theGHP compressor 13 to the suction side thereof. One end of thebypass pipe 28 is connected between theoil separator 15 and the four-way valve 16, and the other end of thebypass pipe 28 is connected between theaccumulator 19 and the four-way valve 16. A part of the refrigerant on the discharge side of theGHP compressor 13 flows through thebypass pipe 28 to the suction side of theGHP compressor 13 due to a pressure difference. - In the
bypass pipe 28, abypass valve 29 that adjusts a flow rate of thebypass pipe 28 is provided. Thebypass valve 29 is an electric valve that can open and close stepwise. - The GHP
outdoor unit 2 includes anoil return pipe 30 that connects theoil separator 15 to the suction side of theGHP compressor 13. Lubricating oil stored in theoil separator 15 flows through theoil return pipe 30 to the suction side due to the pressure difference between the discharge side and the suction side of theGHP compressor 13. - The
oil return pipe 30 includes afirst return pipe 31 that connects an oil outflow port of theoil separator 15 to the suction side of theGHP compressor 13, and asecond return pipe 36 provided in parallel to thefirst return pipe 31. - The
first return pipe 31 includes acapillary tube 32. - The
second return pipe 36 is connected to thefirst return pipe 31 to pass by thecapillary tube 32. One end of thesecond return pipe 36 is connected to an upstream side of thecapillary tube 32 in thefirst return pipe 31, and the other end of thesecond return pipe 36 is connected to a downstream side of thecapillary tube 32 in thefirst return pipe 31. - The
second return pipe 36 includes acapillary tube 33, and anoil return valve 34 provided on a downstream side of thecapillary tube 33. - The
oil connection valve 11 is connected to anoil pipe 35. A middle portion of theoil pipe 35 is branched, so that one oil pipe is connected to the downstream side from theoil separator 15 of therefrigerant pipe 20, and the other oil pipe is connected between thecapillary tube 33 of thesecond return pipe 36 and theoil return valve 34. - The
external connection valve 10a connected to therefrigerant pipe 20 is connected to one end of thewater heat exchanger 8 via theinterunit pipe 5. Furthermore, the other end of thewater heat exchanger 8 is connected to theexternal connection valve 10b connected to therefrigerant pipe 20 via theinterunit pipe 5. - The
water heat exchanger 8 is connected to a cold and hot water pipe, and thewater heat exchanger 8 exchanges heat between the refrigerant sent from the GHPoutdoor unit 2 and cold and hot water that flows through the cold and hot water pipe. - A cold and
hot water pipe 9 connected to thewater heat exchanger 8 is connected to an unshown indoor unit, and configured to supply the cold and hot water to the indoor unit. - That is, the air conditioner 1 of the present embodiment includes a so-called hybrid outdoor unit including the GHP
outdoor unit 2 and the EHPoutdoor unit 3, and is considered as an air conditioner of the hybrid chiller system in which a chiller system performs the air conditioning by use of the GHPoutdoor unit 2 and the EHPoutdoor unit 3. - Furthermore, in the refrigerant pipe connected to the
water heat exchanger 8, there are provided aninlet temperature sensor 120 that detects an inlet side temperature of the refrigerant and anoutlet temperature sensor 121 that detects an outlet side temperature of the refrigerant. - Furthermore, the GHP
outdoor unit 2 includes a coolingwater circuit 50 of thegas engine 12. - The cooling
water circuit 50 includes a cooling water three-way valve 52, the platetype heat exchanger 27, a radiator 53 disposed close to the oneoutdoor heat exchanger 17, a coolingwater pump 54, and an exhaustgas heat exchanger 55 of thegas engine 12, which are connected in order from thegas engine 12 via a coolingwater pipe 51. The coolingwater pump 54 is driven, to circulate cooling water through this circuit. - The cooling
water pipe 51 of the coolingwater circuit 50 is shown by a double line inFig. 1 , and flow of the cooling water is shown by a solid arrow line. - In the radiator 53, heat is exchanged between the outdoor air and the cooling water.
- Furthermore, in the plate
type heat exchanger 27, theelectric valve 26 is operated to heat the refrigerant that returns to theGHP compressor 13 with the cooling water that flows through the coolingwater pipe 51. Consequently, a low pressure of the refrigerant rises, and a heating efficiency improves. - The cooling
water circuit 50 can form a first route in which the cooling water flows in order from thegas engine 12 through the cooling water three-way valve 52, the radiator 53, the coolingwater pump 54, and the exhaustgas heat exchanger 55 to thegas engine 12. - Furthermore, the cooling
water circuit 50 can form a second route in which the cooling water flows in order from thegas engine 12 through the cooling water three-way valve 52, the platetype heat exchanger 27, the coolingwater pump 54 and the exhaustgas heat exchanger 55 to thegas engine 12. - In a middle of the first route that connects the radiator 53 to the cooling water three-
way valve 52, a hot water three-way valve 56 is provided. The hot water three-way valve 56 is connected to a hotwater heat exchanger 57 that exchanges heat between the cooling water and hot water, and the cooling water that flows through the hotwater heat exchanger 57 is returned to an upstream side of the coolingwater pump 54. - Next, description will be made as to the EHP
outdoor unit 3. - The EHP
outdoor unit 3 includes twoexternal connection valves 60 to be connected to theexternal interunit pipe 5 and anoil connection valve 61 to be connected to theoil balance pipe 6. - The EHP
outdoor unit 3 includes theEHP compressor 62 to be driven by the commercial power source. It is considered that an example of thisEHP compressor 62 is an inverter type compressor that can vary an output. - A discharge side of the
EHP compressor 62 is connected to anoil separator 63, a four-way valve 64 and twooutdoor heat exchangers outdoor heat exchanger 65 is connected to oneexternal connection valve 60a via arefrigerant pipe 66. In the vicinity of theoutdoor heat exchanger 65, an outdoor fan 105 (seeFig. 2 ) is provided to exchange heat between theoutdoor heat exchanger 65 and the outdoor air. - A supercooling
heat exchanger 90 is provided between theoutdoor heat exchanger 65 and theexternal connection valve 60a. - Two systems of pipe lines are formed in the
outdoor heat exchanger 65, and therefrigerant pipe 66 on a four-way valve 64 side and therefrigerant pipe 66 on asupercooling heat exchanger 90 side are respectively branched and connected to theoutdoor heat exchanger 65. Furthermore, outdoorelectronic control valves refrigerant pipe 66 on thesupercooling heat exchanger 90 side of theoutdoor heat exchanger 65. - The supercooling
heat exchanger 90 includes twoheat exchange units refrigerant pipe 66 on anoutdoor heat exchanger 65 side and arefrigerant pipe 67 on anexternal connection valve 60a side are respectively branched and connected to eachheat exchange unit 91 of thesupercooling heat exchanger 90. - In the present embodiment, each
heat exchange unit 91 is a double pipe type heat exchanger. Outer pipes of theheat exchange units 91 are connected to therefrigerant pipe 66 on theoutdoor heat exchanger 65 side and therefrigerant pipe 67 on theexternal connection valve 60a side, respectively. - A middle portion of the
refrigerant pipe 67 that connects thesupercooling heat exchanger 90 to theexternal connection valve 60a is connected to a supercoolingbranch pipe 92. A middle portion of this supercoolingbranch pipe 92 is connected to aninner pipe 94 of eachheat exchange unit 91 via a supercoolingelectronic control valve 93. The refrigerant that flows through theinner pipe 94 of theheat exchange unit 91 is returned to therefrigerant pipe 66 between the four-way valve 64 and anaccumulator 69 via a supercoolingrefrigerant pipe 95. - An
external connection valve 60b on the other side is connected to a suction side of theEHP compressor 62 via therefrigerant pipe 66, and the four-way valve 64 and theaccumulator 69 are provided in a middle portion of therefrigerant pipe 66. - Furthermore, a middle portion of the
refrigerant pipe 66 which is between theEHP compressor 62 and theoil separator 63 is provided with arefrigerant return pipe 70 branched and connected to therefrigerant pipe 66 between theEHP compressor 62 and theaccumulator 69. A refrigerant returningsolenoid valve 71 is provided in a middle portion of therefrigerant return pipe 70. Then, when the refrigerant returningsolenoid valve 71 is opened, a part of the refrigerant does not circulate in a refrigeration cycle and is guided to the suction side of theEHP compressor 62. - Additionally, a lower portion of the
oil separator 63 is connected to anoil pipe 72, and a middle portion of theoil pipe 72 is connected to anoil return pipe 73 connected to the suction side of theEHP compressor 62. Theoil return pipe 73 includes twobranch pipes 74 and 75 that branch from theoil pipe 72, one branch pipe 74 is provided with anoil return valve 76, and theother branch pipe 75 is provided with acapillary tube 78. Furthermore, acapillary tube 79 is provided between connection portions of theoil pipe 72 to therespective branch pipes 74 and 75. - A middle portion of the
refrigerant pipe 66 which is between theoil separator 63 and the four-way valve 64 is connected to a high pressurerefrigerant pipe 80 midway branched and connected to a middle portion of theoil pipe 72. A middle portion of the high pressurerefrigerant pipe 80 is provided with asolenoid valve 81 for a high pressure refrigerant. - Furthermore, the
accumulator 69 includes aninflow pipe 82 into which the refrigerant of therefrigerant pipe 66 flows, and anoutflow pipe 83 that sends an inner gas refrigerant of theaccumulator 69 to theEHP compressor 62. Theoutflow pipe 83 is configured to open in an inner upper portion of theaccumulator 69, and to send, to theEHP compressor 62, a gas refrigerant accumulated in the inner upper portion of theaccumulator 69. - Additionally, the
EHP compressor 62 is connected to anoverflow pipe 84 connected to the suction side of theEHP compressor 62. In thisoverflow pipe 84, astrainer 85 and athrottle 86 to decompress oil are incorporated. - The
external connection valve 60a of the EHPoutdoor unit 3 is connected to one end of theinterunit pipe 5, and the other end of theinterunit pipe 5 is connected to a middle portion of theinterunit pipe 5 which connects theexternal connection valve 10a of the GHPoutdoor unit 2 to thewater heat exchanger 8. Theexternal connection valve 60b connected to a refrigerant pipe of the EHPoutdoor unit 3 is connected to one end of theinterunit pipe 5, and the other end of theinterunit pipe 5 is connected to a middle portion of theinterunit pipe 5 which connects theexternal connection valve 10b of the GHPoutdoor unit 2 to thewater heat exchanger 8. - Furthermore, the
oil connection valve 61 of the EHPoutdoor unit 3 is connected to theoil connection valve 11 of the GHPoutdoor unit 2 via theoil balance pipe 6. Consequently, theGHP compressor 13 of the GHPoutdoor unit 2 and theEHP compressor 62 of the EHPoutdoor unit 3 can supply the oil to each other via theoil balance pipe 6, and balance of an oil amount can be held between theGHP compressor 13 of the GHPoutdoor unit 2 and theEHP compressor 62 of the EHPoutdoor unit 3. - Then, when the cooling operation is performed, the refrigerant flows as shown by a solid arrow line in
Fig. 1 , and when the heating operation is performed, the refrigerant flows as shown by a broken arrow line inFig. 1 . - Note that the refrigerant is supplied to an indoor heat exchanger of the indoor unit from the GHP
outdoor unit 2 and the EHPoutdoor unit 3 in place of thewater heat exchanger 8. Consequently, an air conditioning system by air heat exchange can be constructed. Hereinafter, the air conditioning that is performed by this air heat exchange is referred to as the air heat exchange air conditioning. - Next, description will be made as to a control configuration of the air conditioner of the present embodiment.
Fig. 2 is a block diagram showing the control configuration in the present embodiment. - As shown in
Fig. 2 , in the present embodiment, the GHPoutdoor unit 2 includes aGHP control section 100 as a control section, and the EHPoutdoor unit 3 includes anEHP control section 101 as a control section. - Furthermore, in the present embodiment, the air conditioner includes a
controller 110 that sends a control instruction signal to each of the GHPoutdoor unit 2 and the EHPoutdoor unit 3. - The
controller 110 includes acontroller control section 111 to generally control theGHP control section 100 and theEHP control section 101. - Each of the
GHP control section 100, theEHP control section 101 and thecontroller control section 111 includes, for example, a computation processing circuit such as a CPU, storage means such as ROM and RAM, and others, and executes a predetermined program to perform predetermined control. - The
GHP control section 100 is configured to perform drive control of thegas engine 12, theoutdoor fan 18 and the coolingwater pump 54 of the GHPoutdoor unit 2, and to perform opening and closing control or opening degree control of theexternal connection valves oil connection valve 11, theelectric valve 24, theelectric valve 26, thebypass valve 29, theoil return valve 34 and the cooling water three-way valve 52 of the GHPoutdoor unit 2. - The
EHP control section 101 is configured to perform drive control of theEHP compressor 62 and theoutdoor fan 105 of the EHPoutdoor unit 3, and to perform opening and closing control or opening degree control of theexternal connection valves oil connection valve 61, the outdoorelectronic control valve 68, the refrigerant returningsolenoid valve 71, theoil return valve 76, thesolenoid valve 81 for the high pressure refrigerant and the supercoolingelectronic control valve 93 of the EHPoutdoor unit 3. - These control operations of the
GHP control section 100 and theEHP control section 101 are performed based on the control instruction signal sent from thecontroller control section 111. - At this time, in the present embodiment, the
GHP control section 100 is set to a master, and theEHP control section 101 and an indoor control section are set to slaves. The control instruction signal from thecontroller control section 111 is first transmitted to theGHP control section 100, and this control instruction signal is sequentially transmitted from theGHP control section 100 to theEHP control section 101 and the indoor control section. - In the present embodiment, each of the GHP
outdoor unit 2 and the EHPoutdoor unit 3 adjusts an output in accordance with a cooling load. For example, when the cooling load is a low load, the EHPoutdoor unit 3 is driven, and as the cooling load increases, the EHPoutdoor unit 3 is stopped, and the GHPoutdoor unit 2 is started. When the cooling load is a high load, the GHPoutdoor unit 2 is driven, and additionally the EHPoutdoor unit 3 is driven. - The
controller 110 controls the GHPoutdoor unit 2 and the EHPoutdoor unit 3 based on a number of indoor units to be operated, a set temperature, an outdoor air temperature, and the like. Consequently, a control signal is output to each of theGHP control section 100 and theEHP control section 101 so that an operation of the GHPoutdoor unit 2 and an operation of the EHPoutdoor unit 3 save energy most. In consequence, theGHP control section 100 efficiently controls the operation of the GHPoutdoor unit 2, and theEHP control section 101 efficiently controls the operation of the EHPoutdoor unit 3. - Next, description will be made as to the control in the present embodiment in detail.
- When the air heat exchange air conditioning is performed, the
controller control section 111 sets an upper limit horsepower based on an operation state of each of the GHPoutdoor unit 2 and the EHPoutdoor unit 3, transmits an instruction signal of this upper limit horsepower to theGHP control section 100, and transmits the signal to the EHP control section via theGHP control section 100. Then, each of theGHP control section 100 and theEHP control section 101 controls the operation in accordance with the upper limit horsepower set by thecontroller control section 111. - In this case, when the
GHP control section 100 judges that an operation horsepower of the EHPoutdoor unit 3 does not satisfy an upper limit horsepower instruction of the EHPoutdoor unit 3, theGHP control section 100 performs control to lower rotation of thegas engine 12 of the GHPoutdoor unit 2. - Specifically, when the operation horsepower of the EHP
outdoor unit 3 does not satisfy the upper limit horsepower, the rotation of thegas engine 12 of the GHPoutdoor unit 2 is lowered. Consequently, the horsepower of the EHPoutdoor unit 3 is easy to rise, and the operation of each of the GHPoutdoor unit 2 and the EHPoutdoor unit 3 can be more efficiently performed. - Furthermore, when chiller air conditioning is performed and a heating operation is performed, the
GHP control section 100 performs control so that the above described control to lower the rotation of thegas engine 12 of the GHPoutdoor unit 2 is not performed. - In this case, when the chiller air conditioning is performed and the heating operation is performed, the control to lower the rotation of the
gas engine 12 of the GHPoutdoor unit 2 is performed. Then, a water temperature fluctuation in thewater heat exchanger 8 increases, and the operation is not stabilized. - When the air heat exchange air conditioning is performed, during the heating operation, the
GHP control section 100 controls an opening degree of theelectric valve 24. That is, theGHP control section 100 controls suction super heat or discharge super heat based on a discharge temperature of the refrigerant of theGHP compressor 13. - Furthermore, when the chiller air conditioning is performed and the heating operation is performed, the
GHP control section 100 sets a threshold value of the discharge temperature of the refrigerant of theGHP compressor 13 to be lower than when the air heat exchange air conditioning is performed, to execute the control. - In consequence, when the chiller air conditioning is performed and the heating operation is performed, the threshold value is set to be lower. Consequently, the opening degree of the
electric valves 24 can be controlled in such a tendency that the valve opens earlier. Therefore, when the chiller air conditioning is performed, the output is to be raised to acquire a necessary capacity. However, when the opening degree of theelectric valve 24 is small, there is concern that a high pressure rises or that liquid seal of thewater heat exchanger 8 is generated. However, when the opening degree of theelectric valve 24 is controlled so that the valve opens earlier, the rise of the high pressure or the liquid seal can be prevented. - In this case, when the air heat exchange air conditioning is performed, a place where the GHP
outdoor unit 2 and the EHPoutdoor unit 3 are installed is often distant from a place where the indoor unit is installed. When the refrigerant pipe lengthens, the pipe reaches several hundred meters sometimes. Therefore, it is possible to sufficiently acquire a place where a surplus refrigerant stagnates. - On the other hand, when the chiller air conditioning is performed, a distance from the installation place of the GHP
outdoor unit 2 and the EHPoutdoor unit 3 to the installation place of thewater heat exchanger 8 is comparatively short. Additionally, in the present embodiment, for example, a receiver tank to store the surplus refrigerant is not installed in the EHPoutdoor unit 3. Therefore, when the chiller air conditioning is performed, a place to store the surplus refrigerant cannot be acquired, and hence there is a tendency that the refrigerant is easy to accumulate in thewater heat exchanger 8. - As described above, when the chiller air conditioning is performed and the heating operation is performed, the
GHP control section 100 controls the opening degree of theelectric valve 24 so that the valve opens earlier. Consequently, the rise of the high pressure or the liquid seal can be prevented. - In a case where the chiller air conditioning is performed and the GHP
outdoor unit 2 and the EHPoutdoor unit 3 perform the cooling operation, when receiving the instruction signal of the upper limit horsepower of the EHPoutdoor unit 3 which is transmitted from thecontroller control section 111 via theGHP control section 100, theEHP control section 101 raises the upper limit horsepower of the EHPoutdoor unit 3 to control the EHPoutdoor unit 3. - That is, when the GHP
outdoor unit 2 and the EHPoutdoor unit 3 operate during the chiller air conditioning, and when the operation horsepower of the EHPoutdoor unit 3 is suppressed, the refrigerant may stagnate in the EHPoutdoor unit 3. There is also concern that the GHPoutdoor unit 2 runs out of gas. As in the present embodiment, theEHP control section 101 controls and raises the upper limit horsepower of the EHPoutdoor unit 3. Consequently, the refrigerant is prevented from stagnating, and the GHPoutdoor unit 2 can be prevented from running out of gas. - The upper limit horsepower of the EHP
outdoor unit 3 is controlled and uniformly raised, for example, as much as a predetermined percentage set in advance. - When the air heat exchange air conditioning is performed, during the cooling operation, the GHP
outdoor unit 2 runs out of gas, and oil runs short. In this case, theGHP control section 100 sends a start instruction to theEHP control section 101, and theEHP control section 101 starts the EHPoutdoor unit 3, and controls the GHPoutdoor unit 2 and the EHPoutdoor unit 3 to operate. - Furthermore, when the chiller air conditioning is performed and the GHP
outdoor unit 2 performs the cooling operation, theGHP control section 100 judges that the gas runs out. In this case, theGHP control section 100 sends the start instruction to theEHP control section 101, and theEHP control section 101 controls and starts the EHPoutdoor unit 3. TheGHP control section 100 opens theoil return valve 34 of the GHPoutdoor unit 2, and theEHP control section 101 controls and opens thesolenoid valve 81 for the high pressure refrigerant, until the EHPoutdoor unit 3 starts. - When the
GHP control section 100 judges that the EHPoutdoor unit 3 starts, theGHP control section 100 controls and inhibits the rotation of thegas engine 12 of the GHPoutdoor unit 2. Such control can acquire balance in refrigerant pressure between the GHPoutdoor unit 2 and the EHPoutdoor unit 3. The refrigerant that stagnates in the EHPoutdoor unit 3 can be supplied to the GHPoutdoor unit 2, and the running out of the gas in the GHPoutdoor unit 2 can be solved. - Note that it is determined that the GHP
outdoor unit 2 runs out of gas, based on a temperature difference between the inlet side temperature and the outlet side temperature of thewater heat exchanger 8 and an opening degree of a water heat exchanging valve. That is, when the opening degree of the water heat exchanging valve is large and the temperature difference between the inlet side temperature and the outlet side temperature is large, it is determined that the gas runs out. - In the case where the chiller air conditioning is performed, during the cooling operation, the temperature difference is small between the inlet side temperature and the outlet side temperature of the
water heat exchanger 8 which are detected by theinlet temperature sensor 120 and theoutlet temperature sensor 121. In this case, theGHP control section 100 controls and maintains or lowers a rotation speed of thegas engine 12. - Furthermore, when the temperature difference between the inlet side temperature and the outlet side temperature of the
water heat exchanger 8 is large, theGHP control section 100 inhibits control to increase the rotation speed of thegas engine 12. - Such control can prevent the temperature of the
water heat exchanger 8 from extremely dropping during the cooling operation. As a result, delay in control to start the stopped EHPoutdoor unit 3 can be prevented, and the GHPoutdoor unit 2 can be prevented from running out of gas. - As described above, in the present embodiment, the hybrid chiller system includes the GHP
outdoor unit 2 including theGHP compressor 13 to be driven by thegas engine 12, the EHPoutdoor unit 3 including the compressor to be driven by the commercial power source, and thewater heat exchanger 8 that exchanges heat between the refrigerant and the cold and hot water that are sent from the GHPoutdoor unit 2 and the EHPoutdoor unit 3. - According to this system, it is possible to construct the chiller system in which the
water heat exchanger 8 exchanges heat with the cold and hot water by use of the GHPoutdoor unit 2 and the EHPoutdoor unit 3. - Furthermore, in the present embodiment, the hybrid chiller system includes the
GHP control section 100 that controls the GHPoutdoor unit 2, theEHP control section 101 that controls the EHPoutdoor unit 3, and thecontroller control section 111 that transmits the control instruction signal to each of theGHP control section 100 and theEHP control section 101. - According to this system, based on the control instruction signal from the
controller control section 111, theGHP control section 100 can control the GHPoutdoor unit 2, and theEHP control section 101 can control the EHPoutdoor unit 3. - Additionally, in the present embodiment, the
controller control section 111 sets the upper limit horsepower based on the operation state of each of the GHPoutdoor unit 2 and the EHPoutdoor unit 3, and transmits the instruction signal of this upper limit horsepower to each of theGHP control section 100 and the EHP control section. In a case where the air heat exchange air conditioning is performed, when the operation horsepower of the EHPoutdoor unit 3 does not satisfy the upper limit horsepower instruction of the EHPoutdoor unit 3, theEHP control section 101 notifies theGHP control section 100 of the upper limit horsepower instruction not being satisfied, and theGHP control section 100 performs control to lower the rotation of thegas engine 12 of the GHPoutdoor unit 2. When the chiller air conditioning is performed and the heating operation is performed, theGHP control section 100 executes control so that the control to lower the rotation of thegas engine 12 of the GHPoutdoor unit 2 is not performed. - According to this system, when the chiller air conditioning is performed and the heating operation is performed, the
GHP control section 100 executes the control so that the control to lower the rotation of thegas engine 12 of the GHPoutdoor unit 2 is not performed. Consequently, a water temperature fluctuation in thewater heat exchanger 8 can be decreased, and a stabilized operation can be performed. - Furthermore, in the present embodiment, when the air heat exchange air conditioning is performed and the heating operation is performed, the
GHP control section 100 controls the opening degree of theelectric valve 24 based on the discharge temperature of the refrigerant of theGHP compressor 13. When the chiller air conditioning is performed and the heating operation is performed, theGHP control section 100 sets the threshold value of the discharge temperature of the refrigerant of theGHP compressor 13 to be lower than when the air heat exchange air conditioning is performed, to execute the control. - According to this system, when the chiller air conditioning is performed and the heating operation is performed, the threshold value of the discharge temperature of the refrigerant is set to be lower. Consequently, the opening degree of the
electric valve 24 can be controlled in such a tendency that the valve opens earlier. Furthermore, when the opening degree of theelectric valve 24 is controlled so that the valve opens earlier, the rise of the high pressure or the liquid seal can be prevented. - Additionally, in the present embodiment, in the case where the chiller air conditioning is performed and the cooling operation is performed by the GHP
outdoor unit 2 and the EHPoutdoor unit 3, when receiving the instruction signal of the upper limit horsepower of the EHPoutdoor unit 3 which is transmitted from thecontroller control section 111, theEHP control section 101 raises the upper limit horsepower of the EHPoutdoor unit 3 to control the EHPoutdoor unit 3. - According to this system, the
EHP control section 101 controls and raises the upper limit horsepower of the EHPoutdoor unit 3. Consequently, the stagnation of the refrigerant can be prevented, and the GHPoutdoor unit 2 can be prevented from running out of gas. - Furthermore, in the present embodiment, in the case where the chiller air conditioning is performed and the GHP
outdoor unit 2 performs the cooling operation, when theGHP control section 100 judges that the gas runs out, theEHP control section 101 controls and starts the EHPoutdoor unit 3. TheGHP control section 100 opens theoil return valve 34 of the GHPoutdoor unit 2, and theEHP control section 101 controls and opens thesolenoid valve 81 for the high pressure refrigerant, until the EHPoutdoor unit 3 starts. After the EHPoutdoor unit 3 starts, the rotation of thegas engine 12 of the GHPoutdoor unit 2 is controlled and inhibited. - According to this system, the
EHP control section 101 controls and starts the EHPoutdoor unit 3. TheGHP control section 100 opens theoil return valve 34 of the GHPoutdoor unit 2, and theEHP control section 101 controls and opens the solenoid valve for the high pressure refrigerant, until the EHPoutdoor unit 3 starts. After the EHPoutdoor unit 3 starts, the rotation of thegas engine 12 of the GHPoutdoor unit 2 is controlled and inhibited. Consequently, the refrigerant pressure balance between the GHPoutdoor unit 2 and the EHPoutdoor unit 3 can be acquired. The refrigerant that stagnates in the EHPoutdoor unit 3 can be supplied to the GHPoutdoor unit 2, and the running out of gas in the GHPoutdoor unit 2 can be solved. - Additionally, in the present embodiment, in the case where the chiller air conditioning is performed and the cooling operation is performed, when the temperature difference between the inlet side temperature and the outlet side temperature of the
water heat exchanger 8 is small, theGHP control section 100 controls and maintains or lowers the rotation speed of thegas engine 12. When the temperature difference between the inlet side temperature and the outlet side temperature of thewater heat exchanger 8 is large, the control to increase the rotation speed of thegas engine 12 is inhibited. - According to this system, when the temperature difference between the inlet side temperature and the outlet side temperature of the
water heat exchanger 8 is large, the control to increase the rotation speed of thegas engine 12 is inhibited. Consequently, the temperature of thewater heat exchanger 8 can be prevented from extremely dropping during the cooling operation. As a result, delay in control to start the stopped EHPoutdoor unit 3 can be prevented, and the GHPoutdoor unit 2 can be prevented from running out of gas. - Note that the above embodiment illustrates one aspect to which the present invention is applied, and the present invention is not limited to the above embodiment.
- In the above embodiment, there has been described the example where the
GHP control section 100 is set to the master, and theEHP control section 101 is set to the slave, but the present invention is not limited to this example. For example, theEHP control section 101 may be set to a master, theGHP control section 100 may be set to a slave, and the control instruction signal from thecontroller control section 111 may be first transmitted to theEHP control section 101. - Furthermore, without setting the master and the slave, the
GHP control section 100, theEHP control section 101 and the indoor control section may be connected in parallel to thecontroller control section 111, and thecontroller control section 111 may individually transmit control instruction signals to theGHP control section 100, theEHP control section 101 and the indoor control section. - Additionally, in the above embodiment, the case where the air conditioning is performed by using the chiller system has been described, but the air conditioning is not restrictive. For example, the present invention can be also applied to process cooling, heating application or the like.
- As described above, the hybrid chiller system according to the present invention can construct the chiller system, and can be preferably utilized as the hybrid chiller system that can prevent stagnation of the refrigerant in the chiller system.
-
- 1
- air conditioner
- 2
- GHP outdoor unit
- 3
- EHP outdoor unit
- 8
- water heat exchanger
- 12
- gas engine
- 13
- GHP compressor
- 15
- oil separator
- 17, 65
- outdoor heat exchanger
- 62
- EHP compressor
- 71
- refrigerant returning solenoid valve
- 100
- GHP control section
- 101
- EHP control section
- 110
- controller
- 111
- controller control section
- 120
- inlet temperature sensor
- 121
- outlet temperature sensor
Claims (7)
- A hybrid chiller system characterized by comprising:a GHP outdoor unit (2) including a GHP compressor (13) to be driven by a gas engine (12);an EHP outdoor unit (3) including a compressor to be driven by a commercial power source; anda water heat exchanger (8) that exchanges heat between a refrigerant and cold and hot water that are sent from the GHP outdoor unit and the EHP outdoor unit.
- The hybrid chiller system according to claim 1, comprising:a GHP control section (100) that controls the GHP outdoor unit;an EHP control section (101) that controls the EHP outdoor unit; anda controller control section (111) that transmits a control instruction signal to each of the GHP control section and the EHP control section.
- The hybrid chiller system according to claim 2, wherein the controller control section sets an upper limit horsepower based on an operation state of each of the GHP outdoor unit and the EHP outdoor unit, and transmits an instruction signal of this upper limit horsepower to each of the GHP control section and the EHP control section,
in a case where air heat exchange air conditioning is performed, when an operation horsepower of the EHP outdoor unit does not satisfy an upper limit horsepower instruction of the EHP outdoor unit, the EHP control section notifies the GHP control section of the upper limit horsepower instruction not being satisfied, and the GHP control section performs control to lower rotation of the gas engine of the GHP outdoor unit, and
when chiller air conditioning is performed and a heating operation is performed, the GHP control section executes control so that the control to lower the rotation of the gas engine of the GHP outdoor unit is not performed. - The hybrid chiller system according to claim 2 or 3, wherein when air heat exchange air conditioning is performed and a heating operation is performed, the GHP control section controls an opening degree of an electric valve (24) based on a discharge temperature of the refrigerant of the GHP compressor, and
when chiller air conditioning is performed and the heating operation is performed, the GHP control section sets a threshold value of the discharge temperature of the refrigerant of the GHP compressor to be lower than when the air heat exchange air conditioning is performed, to execute the control. - The hybrid chiller system according to any one of claims 2 to 4, wherein in a case where chiller air conditioning is performed and a cooling operation is performed by the GHP outdoor unit and the EHP outdoor unit, when receiving an instruction signal of an upper limit horsepower of the EHP outdoor unit which is transmitted from the controller control section, the EHP control section raises the upper limit horsepower of the EHP outdoor unit to control the EHP outdoor unit.
- The hybrid chiller system according to any one of claims 2 to 5, wherein in a case where chiller air conditioning is performed and a cooling operation is performed by the GHP outdoor unit, when the GHP control section judges that gas runs out, the EHP control section controls and starts the EHP outdoor unit; the GHP control section opens an oil return valve (34) of the GHP outdoor unit, and the EHP control section controls and opens a solenoid valve (81) for a high pressure refrigerant, until the EHP outdoor unit starts; and after the EHP outdoor unit starts, rotation of the gas engine of the GHP outdoor unit is controlled and inhibited.
- The hybrid chiller system according to any one of claims 2 to 6, wherein in a case where chiller air conditioning is performed and a cooling operation is performed, when a temperature difference between an inlet side temperature and an outlet side temperature of the water heat exchanger is small, the GHP control section controls and maintains or lowers a rotation speed of the gas engine; and when the temperature difference between the inlet side temperature and the outlet side temperature of the water heat exchanger is large, control to increase the rotation speed of the gas engine is inhibited.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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JP2018142633A JP7142314B2 (en) | 2018-07-30 | 2018-07-30 | Hybrid chiller system |
Publications (2)
Publication Number | Publication Date |
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EP3604972A1 true EP3604972A1 (en) | 2020-02-05 |
EP3604972B1 EP3604972B1 (en) | 2022-09-07 |
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EP19185716.8A Active EP3604972B1 (en) | 2018-07-30 | 2019-07-11 | Hybrid chiller system |
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JP (1) | JP7142314B2 (en) |
CN (1) | CN110779237B (en) |
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CN116033726A (en) * | 2023-03-28 | 2023-04-28 | 常州工程职业技术学院 | Outdoor cabinet heat dissipation and dust removal system and control method |
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CN114576881B (en) * | 2020-11-30 | 2023-10-31 | 上海本家空调***有限公司 | Gas heat pump air conditioning system |
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- 2019-07-22 CN CN201910660234.1A patent/CN110779237B/en active Active
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EP1288592A2 (en) * | 2001-08-31 | 2003-03-05 | Mitsubishi Heavy Industries, Ltd. | Gas heat pump type air conditioning device, engine-coolant-water heating device, and operating method for gas heat pump type air conditioning device |
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Also Published As
Publication number | Publication date |
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EP3604972B1 (en) | 2022-09-07 |
JP2020020490A (en) | 2020-02-06 |
JP7142314B2 (en) | 2022-09-27 |
CN110779237B (en) | 2022-09-23 |
CN110779237A (en) | 2020-02-11 |
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