WO2006033378A1 - エジェクタ式冷凍サイクル装置 - Google Patents
エジェクタ式冷凍サイクル装置 Download PDFInfo
- Publication number
- WO2006033378A1 WO2006033378A1 PCT/JP2005/017447 JP2005017447W WO2006033378A1 WO 2006033378 A1 WO2006033378 A1 WO 2006033378A1 JP 2005017447 W JP2005017447 W JP 2005017447W WO 2006033378 A1 WO2006033378 A1 WO 2006033378A1
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- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- evaporator
- ejector
- compressor
- radiator
- Prior art date
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3286—Constructional features
- B60H2001/3298—Ejector-type refrigerant circuits
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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
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0012—Ejectors with the cooled primary flow at high pressure
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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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
- F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
Definitions
- the present invention relates to a defrosting operation of an ejector refrigeration cycle apparatus having an ejector that serves as a refrigerant decompression means and a refrigerant circulation means.
- the present invention is applied to a refrigeration cycle of an air conditioning refrigeration apparatus for a vehicle. It is effective.
- Patent Document 1 has already proposed a defrosting operation of an ejector-type refrigeration cycle apparatus.
- a gas-liquid separator is arranged on the downstream side of an ejector, and an evaporator is provided between the liquid-phase refrigerant outlet side of the gas-liquid separator and the refrigerant suction port side of the ejector.
- a bypass passage that directly connects the discharge side passage to the upstream passage of the evaporator is provided, and a shut mechanism is provided in the bypass passage.
- the high-temperature refrigerant from the bypass passage is between the coupling portion between the upstream flow path of the evaporator and the bypass passage and the liquid-phase coolant outlet of the gas-liquid separator.
- a mechanism for example, a throttle and a check valve is provided to prevent the directing of the force toward the refrigerant outlet.
- the present invention relates to a defrosting hand in an ejector-type refrigeration cycle apparatus including a plurality of evaporators.
- the purpose is to provide a stage.
- an ejector-type refrigeration cycle apparatus includes a compressor (12) that sucks and compresses refrigerant,
- a radiator (13) that dissipates heat of the high-pressure refrigerant discharged from the compressor (12); a nozzle part (14a) that decompresses and expands the refrigerant on the downstream side of the radiator (13); and the nozzle part
- An ejector (14) having a refrigerant suction port (14c) through which a refrigerant is sucked by a high-speed refrigerant flow ejected from (14a);
- a refrigerant flow is branched on the upstream side of the first evaporator (15) connected to the suction side of the compressor (12) and the ejector (14) on the refrigerant outflow side, and the refrigerant flow is divided into the refrigerant suction port.
- a first throttle means (18) disposed in the first branch passage (17) for decompressing and expanding the refrigerant, and disposed downstream of the first throttle means (18) in the first branch passage (17).
- the refrigerant evaporation pressure of the second evaporator (19) is lower than the refrigerant evaporation pressure of the first evaporator (15),
- the first throttle means (18) has a structure with a fully open function for fully opening the first branch passage (17) when the second evaporator (19) is defrosted.
- the first evaporator (15) having a high refrigerant evaporation pressure can exhibit the cooling ability in the high temperature region, and the refrigerant having a low refrigerant evaporation pressure! Can demonstrate ability.
- the first throttling means (18) is operated to the fully open position of the first branch passage (17), so that the high-temperature and high-pressure at the outlet of the radiator (13)
- the refrigerant can be directly introduced into the second evaporator (19) through the first branch passage (17).
- the second evaporator (19) can be defrosted satisfactorily.
- the first throttle means (18) which normally reduces the pressure of the cooling medium, is fully opened during defrosting, and the second evaporator ( 19) can be defrosted.
- the refrigerant on the downstream side of the radiator (13) flows into the second evaporator (19) through the throttle means (18). Therefore, the refrigerant flow rate of the second evaporator (19) during normal operation can be easily adjusted to a value according to the heat load by the throttle means (18).
- the "full open function for fully opening the first branch passage (17)” means not only the case where the first branch passage (17) is fully opened, but also the case where the first branch passage (17) is opened while being slightly reduced in area. Including. That is, there is a case where it is necessary to make the i-th throttling means ( 18 ) open while reducing the area of the i-th branch passage ( 17 ) by a slight amount.
- an ejector-type refrigeration cycle apparatus includes a compressor (12) that sucks and compresses refrigerant,
- a radiator (13) that dissipates heat of the high-pressure refrigerant discharged from the compressor (12); a nozzle part (14a) that decompresses and expands the refrigerant on the downstream side of the radiator (13); and the nozzle part
- An ejector (14) having a refrigerant suction port (14c) through which a refrigerant is sucked by a high-speed refrigerant flow ejected from (14a);
- a refrigerant flow is branched on the upstream side of the first evaporator (15) connected to the suction side of the compressor (12) and the ejector (14) on the refrigerant outflow side, and the refrigerant flow is divided into the refrigerant suction port.
- a first throttle means (180) disposed in the first branch passage (17) for decompressing and expanding the refrigerant, and disposed downstream of the first throttle means (180) in the first branch passage (17).
- the refrigerant evaporation pressure of the second evaporator (19) is lower than the refrigerant evaporation pressure of the first evaporator (15),
- the shut mechanism (24) has a normally closed configuration that opens the bypass passage (23) when the second evaporator (19) is defrosted.
- the defrosting means of the second evaporator (19) is changed from the first example. That is, in the second example of the present invention, when the second evaporator (19) is defrosted, the high-temperature and high-pressure refrigerant on the discharge side of the compressor (12) is directly passed to the second evaporator (19) through the bypass passage (23). Introduction Thus, the second evaporator (19) can be defrosted.
- the first diaphragm means (180) does not need to be set to the fully open function, so that a normal fixed diaphragm or variable diaphragm can be used as the first diaphragm means (180) as it is.
- the other effects of the second example of the present invention are the same as those of the first example.
- an ejector-type refrigeration cycle apparatus includes a compressor (12) that sucks and compresses refrigerant,
- a radiator (13) that dissipates heat of the high-pressure refrigerant discharged from the compressor (12); a nozzle part (14a) that decompresses and expands the refrigerant on the downstream side of the radiator (13); and the nozzle part
- An ejector (14) having a refrigerant suction port (14c) through which a refrigerant is sucked by a high-speed refrigerant flow ejected from (14a);
- a refrigerant flow is branched on the upstream side of the first evaporator (15) connected to the suction side of the compressor (12) and the ejector (14) on the refrigerant outflow side, and the refrigerant flow is divided into the refrigerant suction port.
- First throttling means (180) disposed in the first branch passage (17) and decompressing and expanding the refrigerant on the radiator (13) downstream side;
- the refrigerant evaporation pressure of the second evaporator (19) is lower than the refrigerant evaporation pressure of the first evaporator (15),
- the shut mechanism (34) has a normally closed configuration that opens the bypass passage (33) when the second evaporator (19) is defrosted.
- the bypass passage (33) of the first throttle means (180) is opened by the shut mechanism (34).
- the high-temperature and high-pressure refrigerant at the outlet of the radiator (13) can be directly introduced into the second evaporator (19) through the bypass passage (33).
- the first drawing means Since (180) does not need to be set to the fully open function, a normal fixed aperture or variable aperture can be used as the first aperture means (180) as it is.
- the ejector-type refrigeration cycle apparatus may include a third evaporator (27) that exhibits a cooling capacity by evaporating the refrigerant in the same temperature range as the first evaporator (15).
- a refrigerant flow is branched from an upstream portion of the first throttle means (18, 180) in the first branch passage (17), and the refrigerant flow is divided into refrigerant in the first evaporator (15).
- a second branch passage (25) joined between the outflow side and the suction side of the compressor (12);
- the third evaporator (27) can be arranged.
- the third evaporator (27) specifically forms the second branch passage (25) and is disposed in the second branch passage (25).
- the first evaporator (15) may be connected to the refrigerant outflow side of the ejector (14)!
- a third throttle means (30) is provided between the refrigerant outlet side of the radiator (13) and the refrigerant inlet side of the first evaporator (15), and the ejector (14) is connected to the third throttle. It can be provided in parallel with the means (30).
- the third throttle means (30) dedicated for the first evaporator (15) is provided, the refrigerant flow rate of the first evaporator (15) is adjusted in the ejector (14). There is no need to share functions. For this reason, the ejector (14) can specialize in the pump function for creating a pressure difference between the first and second evaporators (15, 19).
- the upstream portion of the ejector (14) is shut. If the shut mechanism (31) is provided, the high-pressure refrigerant flow flowing into the ejector (14) from the refrigerant outflow side of the radiator (13) when the second evaporator (19) is defrosted is blocked.
- the defrosting performance can be improved by increasing the amount of high-pressure refrigerant flowing into the evaporator (19).
- the ejector-type refrigeration cycle apparatus includes a shut mechanism (32) for shutting the upstream portion of the radiator (13) when the second evaporator (19) is defrosted. If this is done, the defrosting performance can be improved by increasing the amount of high-pressure refrigerant flowing into the second evaporator (19) when the second evaporator (19) is defrosted.
- an ejector-type refrigeration cycle apparatus includes a compressor (12) for sucking and compressing refrigerant,
- a radiator (13) that dissipates heat of the high-pressure refrigerant discharged from the compressor (12); a nozzle part (14a) that decompresses and expands the refrigerant on the downstream side of the radiator (13); and the nozzle part
- An ejector (14) having a refrigerant suction port (14c) through which a refrigerant is sucked by a high-speed refrigerant flow ejected from (14a);
- Throttle means (180) disposed in the branch passage (36) and decompressing and expanding the liquid refrigerant flowing out of the gas-liquid separator (35);
- the refrigerant evaporation pressure of the second evaporator (19) is lower than the refrigerant evaporation pressure of the first evaporator (15),
- the shut mechanism (24) has a normally closed configuration that opens the bypass passage (23) when the second evaporator (19) is defrosted.
- the gas-liquid separator (35) includes a branch passage (36) for connecting the outlet of the liquid-phase refrigerant to the refrigerant suction port (14c), and the throttle means (180) is provided in the branch passage (36).
- a second evaporator (19) may be provided.
- the refrigerant evaporates at a lower temperature than the first evaporator (15).
- the second evaporator (19) is defrosted, the high-pressure refrigerant on the discharge side of the compressor (12) is removed. By introducing it directly into the second evaporator (19), the second evaporator (19) can be defrosted well.
- an ejector-type refrigeration cycle apparatus includes a compressor (12) that sucks and compresses refrigerant,
- a radiator (13) that dissipates heat of the high-pressure refrigerant discharged from the compressor (12); a nozzle part (14a) that decompresses and expands the refrigerant on the downstream side of the radiator (13); and the nozzle part
- An ejector (14) having a refrigerant suction port (14c) through which a refrigerant is sucked by a high-speed refrigerant flow ejected from (14a);
- the low-pressure refrigerant evaporates in the first evaporator (15) and the second evaporator (19) by controlling the opening degree of the first throttle mechanism (38) and the second throttle mechanism (18).
- the high-pressure high-temperature refrigerant on the discharge side of the compressor (12) is introduced into both the second evaporator (19) and the first evaporator (15), and the both evaporators (15, 19) are introduced.
- the first throttle mechanism (38) is specifically set to a predetermined throttle opening state, 2
- the diaphragm mechanism (18) may be fully opened.
- an ejector-type refrigeration cycle apparatus includes a compressor (12) that sucks and compresses refrigerant,
- a radiator (13) that dissipates heat of the high-pressure refrigerant discharged from the compressor (12); a nozzle part (14a) that decompresses and expands the refrigerant on the downstream side of the radiator (13); and the nozzle part
- An ejector (14) having a refrigerant suction port (14c) through which a refrigerant is sucked by a high-speed refrigerant flow ejected from (14a);
- the low-pressure refrigerant evaporates in the first evaporator (15) and the second evaporator (19) by controlling the opening degree of the first throttle mechanism (18) and the second throttle mechanism (39).
- the high-pressure high-temperature refrigerant on the discharge side of the compressor (12) is introduced into the second evaporator (19) to defrost the second evaporator (19);
- the high-pressure refrigerant that has passed through the second evaporator (19) is depressurized by the second throttling mechanism (39), and the low-pressure refrigerant after this depressurization is introduced into the first evaporator (15), whereby the first evaporator
- the evaporator (15) has a cooling function.
- the high-pressure high-temperature refrigerant on the discharge side of the compressor (12) is introduced into the second evaporator (19) and the second evaporator (19) 19) can be defrosted, and at the same time, the high-pressure refrigerant that has passed through the second evaporator (19) is depressurized by the second throttling mechanism (39). ),
- the first evaporator (15) can perform the cooling function. Therefore, the defrosting function of the second evaporator (19) and the cooling function of the first evaporator (15) can be constantly and simultaneously performed.
- the first throttle mechanism (18) may be fully opened, and the second throttle mechanism (39) may be in a predetermined throttle opening state.
- the cycle behavior in the defrosting / cooling operation mode illustrated in FIG. 22 can be realized, and the simultaneous operation of the defrosting function and the cooling function can be constantly performed.
- an ejector-type refrigeration cycle apparatus includes a compressor (12) that sucks and compresses refrigerant,
- a radiator (13) that dissipates heat of the high-pressure refrigerant discharged from the compressor (12); a nozzle part (14a) that decompresses and expands the refrigerant on the downstream side of the radiator (13); and the nozzle part
- An ejector (14) having a refrigerant suction port (14c) through which a refrigerant is sucked by a high-speed refrigerant flow ejected from (14a);
- a state in which the refrigerant dissipates heat in the radiator (13) is set, a normal operation mode in which low-pressure refrigerant evaporates in the first evaporator (15) and the second evaporator (19), and the radiator ( 13)
- the refrigerant does not release heat!
- the refrigerant on the discharge side of the compressor (12) flows into the throttle mechanism (181) while being in a high-pressure and high-temperature state and is depressurized, and the low-pressure high-temperature gas-phase refrigerant after passing through the throttle mechanism (181) is removed. It is introduced into both the first evaporator (15) and the second evaporator (19).
- the low-pressure high-temperature gas-phase refrigerant decompressed by the throttle mechanism (181) is supplied to the first evaporator (15) and the second evaporator (19 ) To defrost both evaporators (15, 19) at the same time. Therefore, the steady defrosting function of both evaporators (15, 19) by the operation of the compressor (12) can be satisfactorily performed.
- the opening degree in the defrosting operation mode is made larger than the opening degree in the normal operation mode of the throttle mechanism (181), the necessary refrigerant flow rate can be secured even in the defrosting operation mode.
- the defrosting operation mode is set.
- the high-pressure and high-temperature gas-phase refrigerant on the discharge side of the compressor (12) is decompressed by the throttle mechanism (181), and the density of the gas-phase refrigerant is smaller than the density of the liquid-phase refrigerant. Since the opening of (181) is larger in the defrosting operation mode than in the normal operation mode, the required refrigerant flow rate even in the defrosting operation mode in which the refrigerant is decompressed by the throttle mechanism (181) Can be ensured.
- the radiator (13) may be provided with a blowing means (13a) for blowing cooling air, and the blowing means (13a) may be stopped during the defrosting operation mode.
- the evaporator defrosting function can be exhibited with a simple refrigerant passage configuration that does not require a refrigerant passage or the like that bypasses the radiator (13).
- a bypass shut mechanism (41) provided in the radiator bypass passage (40). By opening the bypass shut mechanism (41) in the defrosting operation mode, the compressor (12) discharge side Of high pressure and high temperature refrigerant through the radiator bypass passage (40)
- the high-pressure high-temperature refrigerant on the discharge side of the compressor (12) is introduced into the throttle mechanism (181) through the radiator bypass passage (40) while the blowing means (13a) of the radiator (13) is operated. can do.
- a radiator shut mechanism (42) is provided in parallel with the bypass shut mechanism (41) at the refrigerant outlet of the radiator (13), and a blower for blowing cooling air to the radiator (13).
- a step (13a) is provided;
- bypass shut mechanism (41) In the defrosting operation mode, the bypass shut mechanism (41) is opened, the radiator shut mechanism (42) is closed, and the air blowing means (13a) is operated. Can do.
- the radiator (13) is connected to the compressor (12) discharge side at high pressure and high temperature.
- the liquid storage function for condensing and storing the gas-phase refrigerant can be exhibited. Therefore, when the gas-liquid separator (35) is arranged on the refrigerant outflow side (compressor (12) suction side) of the first evaporator (15), the tank capacity of the gas-liquid separator (35) can be reduced. .
- an ejector shut mechanism (31) is provided in the upstream side passage of the ejector (14), and the defrosting operation mode and the defrosting / cooling operation mode are provided.
- the upstream passage of the ejector (14) may be closed by the ejector shut mechanism (31).
- the upstream passage of the ejector (14) is closed to prevent the coolant from flowing into the upstream passage force ejector (14), and the second evaporator (19) side
- the flow rate of the high-temperature refrigerant flowing into the can be increased, and the defrosting ability can be improved.
- the gas-liquid of the refrigerant is separated and the liquid-phase refrigerant is stored on the refrigerant outlet side of the first evaporator (15), and the gas-phase refrigerant is compressed.
- a gas-liquid separator (35) that flows out to the suction side of the machine (12) may be provided. In this case, liquid refrigerant return to the compressor (12) can be reliably prevented during the defrosting operation mode and the defrosting / cooling operation mode.
- FIG. 1 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a first embodiment of the present invention.
- FIG. 2 (a) and (b) are schematic operation explanatory views of the throttle mechanism with a fully open function in the first embodiment.
- FIG. 3 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a second embodiment.
- FIG. 4 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a third embodiment.
- FIG. 5 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a fourth embodiment.
- FIG. 6 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a fifth embodiment.
- FIG. 7 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a sixth embodiment.
- FIG. 8 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a seventh embodiment.
- FIG. 9 is a cycle diagram showing an ejector refrigeration cycle apparatus according to an eighth embodiment.
- 10 A cycle diagram showing an ejector-type refrigeration cycle apparatus according to the ninth embodiment.
- 11 A cycle diagram showing an ejector refrigeration cycle apparatus according to a tenth embodiment.
- 12 A cycle diagram showing an ejector refrigeration cycle apparatus according to an eleventh embodiment.
- 13 A cycle diagram showing an ejector refrigeration cycle apparatus according to a twelfth embodiment.
- 14 A cycle diagram showing an ejector refrigeration cycle apparatus according to a thirteenth embodiment.
- 15 A cycle diagram showing an ejector refrigeration cycle apparatus according to a fourteenth embodiment. ⁇ 16] A chart collectively showing operations of various devices according to the fourteenth embodiment.
- FIG. 20 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a sixteenth embodiment.
- FIG. 21 is a chart collectively showing operations of various devices according to the sixteenth embodiment.
- FIG. 22 is a Mollier diagram showing the operation during the defrosting / cooling operation according to the sixteenth embodiment.
- FIG. 23 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a seventeenth embodiment. ⁇ 24] It is a schematic operation explanatory view of the aperture mechanism in the seventeenth embodiment.
- FIG. 25 is a chart collectively showing operations of various devices according to the seventeenth embodiment.
- FIG. 26 is a Mollier diagram showing the operation during the defrosting operation according to the seventeenth embodiment.
- FIG. 27 is a cycle diagram showing an ejector refrigeration cycle apparatus according to an eighteenth embodiment.
- FIG. 28 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a nineteenth embodiment.
- FIG. 29 is a chart collectively showing operations of various devices according to the nineteenth embodiment.
- FIG. 30 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a twentieth embodiment.
- FIG. 31 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a twenty-first embodiment.
- FIG. 32 is a chart summarizing operations of various devices according to the twenty-first embodiment.
- FIG. 33 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a twenty-second embodiment.
- 34 A cycle diagram showing an ejector refrigeration cycle apparatus according to a twenty-third embodiment.
- FIG. 35 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a twenty-fourth embodiment.
- FIG. 36 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a twenty-fifth embodiment.
- FIG. 37 is a cycle diagram showing an ejector refrigeration cycle apparatus according to a twenty-sixth embodiment.
- FIG. 1 shows an example in which an ejector-type refrigeration cycle apparatus according to a first embodiment of the present invention is applied to a refrigeration cycle of a vehicle air-conditioning refrigeration apparatus.
- the ejector-type refrigeration cycle apparatus 10 includes a refrigerant circulation path 11.
- the refrigerant circulation path 11 is provided with a compressor 12 that sucks and compresses the refrigerant.
- the compressor 12 is driven to rotate by a vehicle travel engine (not shown) via a belt or the like.
- a variable capacity compressor capable of adjusting the refrigerant discharge capacity by changing the discharge capacity is used.
- the discharge capacity corresponds to the refrigerant discharge amount per rotation, and the discharge capacity can be changed by changing the suction volume of the refrigerant.
- variable capacity compressor 12 is typically a swash plate type. Specifically, the piston suction stroke is changed by changing the piston stroke by changing the angle of the swash plate.
- the angle of the swash plate can be electrically controlled from the outside by changing the pressure (control pressure) of the swash plate chamber by the electromagnetic pressure control device 12a constituting the capacity control mechanism.
- a radiator 13 is disposed on the downstream side of the refrigerant flow of the compressor 12.
- the radiator 13 cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 12 and outside air blown by a cooling fan (not shown).
- An ejector 14 is disposed at a further downstream side of the refrigerant flow than the radiator 13.
- the ejector 14 is a depressurizing means for depressurizing the refrigerant, and is a momentum transporting pump that transports fluid by suction action of a refrigerant flow ejected at high speed.
- the ejector 14 is connected to a nozzle portion 14a for reducing the passage area of the high-pressure refrigerant flowing from the radiator 13 to be small and isentropically decompressed and expanded, and to a refrigerant outlet of the nozzle portion 14a. And a suction port 14c for sucking a refrigerant from the second evaporator 19, which will be described later.
- a diffuser portion 14b serving as a pressure increasing portion is disposed at the downstream side of the refrigerant flow of the nozzle portion 14a and the suction port 14c.
- the diffuser part 14b is formed in a shape that gradually increases the passage area of the refrigerant, and decelerates the refrigerant flow to increase the refrigerant pressure. In other words, it acts to convert the velocity energy of the refrigerant into pressure energy.
- the first evaporator 15 is installed, for example, in a ventilation path of a vehicle interior air conditioning unit (not shown) and performs a cooling action for vehicle interior cooling.
- the air-conditioning air in the vehicle interior is blown to the first evaporator 15 by the electric blower (first blower) 16 of the vehicle interior air-conditioning unit, and the low-pressure refrigerant decompressed by the ejector 14 is supplied to the first evaporator.
- heat is absorbed from the conditioned air in the passenger compartment and evaporates, thereby cooling the conditioned air in the passenger compartment and exerting cooling performance.
- the gas-phase refrigerant evaporated in the first evaporator 15 is sucked into the compressor 12 and circulates again through the refrigerant circulation path 11.
- a branch is made at a portion between the radiator 13 and the ejector 14 in the refrigerant circulation path 11, and the refrigerant circulation path 11 is made at the suction port 14 c of the ejector 14.
- a branch passage 17 is formed to join the two.
- a throttle mechanism 18 for adjusting the flow rate of the refrigerant and depressurizing the refrigerant is disposed.
- the aperture mechanism 18 is constituted by an aperture mechanism with a fully open function.
- FIG. 2 is a schematic cross-sectional view showing a specific example of the throttle mechanism 18 with the fully open function.
- the throttle mechanism 18 has a throttle hole 18a constituting a fixed throttle and a full opening for fully opening the branch passage 17.
- a movable plate member 18c having an opening with a hole 18b is provided.
- the fully open hole 18b is designed to have a cross-sectional area equivalent to the cross-sectional area of the flow path (pipe) of the branch passage 20.
- the throttle mechanism 18 fulfills the function of fully opening the branch passage 20.
- the movable plate member 18c is arranged so as to be movable in the transverse direction of the branch passage 17 (in the direction orthogonal to the refrigerant flow direction a), and the movable plate member 18c is an electric type constituted by a servo motor or the like. It is driven by the actuator 18d.
- FIG. 2 (a) shows a normal time when the throttle hole 18a acts as a fixed throttle
- FIG. 2 (b) shows a defrosting operation in which the branch channel 17 is fully opened by the fully open hole 18b.
- a second evaporator 19 is arranged at a downstream side of the refrigerant flow with respect to the throttle mechanism 18.
- the second evaporator 19 is installed in a refrigerator (not shown) mounted on a vehicle, for example, and is refrigerated. Performs cooling in the cabinet.
- the air in the refrigerator is blown to the second evaporator 19 by an electric blower (second blower) 20.
- the electromagnetic pressure control device 12a, the first and second blowers 16, 20, the throttle mechanism 18 and the like of the variable capacity compressor 12 are from the electric control device (hereinafter abbreviated as ECU) 21. It is electrically controlled by the control signal.
- ECU electric control device
- a temperature sensor 22 is disposed at a predetermined position in the vicinity of the second evaporator 19, and the temperature sensor 22 detects the air temperature in the vicinity of the second evaporator 19. The detection signal of the temperature sensor 22 is input to the ECU 21.
- the compressor 12 When the compressor 12 is driven by the vehicle engine, the refrigerant that has been compressed by the compressor 12 and brought into a high-temperature and high-pressure state flows into the radiator 13 and is cooled and condensed by the outside air.
- the high-pressure liquid refrigerant that has flowed out of the radiator 13 is divided into a flow that flows through the refrigerant circulation path 11 and a flow that flows through the branch path 17.
- the throttle mechanism 18 of the branch passage 17 is placed in the normal state of Fig. 2 (a) by the control signal of the ECU 21.
- the throttle hole 18a is located in the branch passage 17. For this reason, since the throttle hole 18a acts as a fixed throttle, the refrigerant flowing through the branch passage 17 is decompressed by the throttle mechanism 18 to be in a low pressure state.
- This low-pressure refrigerant absorbs heat from the air in the refrigerator blown by the second blower 20 in the second evaporator 19 and evaporates. Thereby, the 2nd evaporator 19 exhibits the cooling effect
- the flow rate of the refrigerant passing through the first branch passage 17 and flowing into the second evaporator 19 can be adjusted by the opening degree of the throttle hole 18 a of the throttle mechanism 18.
- the ECU 21 can control the cooling capacity of the cooling target space (specifically, the space in the refrigerator) exhibited by the second evaporator 19 by controlling the rotation speed (air flow rate) of the second blower 20.
- the refrigerant flow flowing through the refrigerant circulation path 11 flows into the ejector 14 and is decompressed and expanded by the nozzle portion 14a. Accordingly, the pressure energy of the refrigerant is converted into the velocity energy at the nozzle portion 14a, and the refrigerant becomes a high velocity and is ejected from the nozzle. Due to the pressure drop in the vicinity of the nozzle nozzle generated at this time, the vapor-phase refrigerant evaporated in the second evaporator 19 is sucked from the suction port 14c.
- the refrigerant absorbs heat from the conditioned air blown into the passenger compartment and evaporates.
- the vapor phase refrigerant after the evaporation is sucked and compressed by the compressor 12 and circulates again through the refrigerant circulation path 11.
- the ECU 21 can control the capacity of the compressor 12 to control the refrigerant discharge capacity of the compressor 12.
- the refrigerant flow rate to the first evaporator 15 is adjusted, and the rotation speed (air flow rate) of the first blower 26 is controlled to cool the cooling target space exhibited by the first evaporator 15.
- Capability, specifically, cooling capacity in the passenger compartment can be controlled.
- the refrigerant evaporation pressure of the first evaporator 15 is the pressure after being increased by the diffuser portion 14b, while the outlet side of the second evaporator 19 is connected to the suction port 14c of the ejector 14. Therefore, the lowest pressure immediately after depressurization at the nozzle portion 14 a can be applied to the second evaporator 19.
- the refrigerant evaporation pressure (refrigerant evaporation temperature) of the second evaporator 19 can be made lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the first evaporator 15. Therefore, the first evaporator 15 can exhibit a cooling action in a relatively high temperature range suitable for cooling the passenger compartment, and the second evaporator 19 can exhibit a cooling action in a low temperature range suitable for cooling in the refrigerator. .
- the second evaporator 19 may be operated under a condition where the refrigerant evaporation temperature is lower than 0 ° C., the cooling performance is reduced due to the frost (with frost) of the second evaporator 19. It becomes a problem.
- the temperature sensor 22 is disposed in the vicinity of the second evaporator 19, and the ECU 21 determines whether the second evaporator 19 is frosted based on the detected temperature of the temperature sensor 22.
- the second evaporator 19 is automatically defrosted! /.
- the ECU 21 determines the frost state of the second evaporator 19. Then, a control signal is output to the electric actuator 18d of the throttle mechanism 18 with the fully open function, and the movable plate member 18c is moved to the normal state as shown in FIG. Move from the position to the defrosting position in Fig. 2 (b).
- the fully opening hole 18b of the movable plate member 18c is overlapped with the entire passage of the branch passage 17, and the branch passage 17 is fully opened.
- the high-temperature and high-pressure liquid refrigerant at the outlet of the radiator 13 can be directly led to the second evaporator 19 through the branch passage 17.
- the frost adhering to the surface of the second evaporator 19 can be melted, and the defrosting operation of the second evaporator 19 can be performed with a very simple configuration.
- the electric actuator 18d returns the movable plate member 18c to the normal position shown in FIG. 2 (a) when the defrosting position force shown in FIG. 2 (b). Therefore, since the throttle mechanism 18 again exhibits the action of the fixed throttle by the throttle hole 18a, the second evaporator 19 returns to the state in which the cooling action is also exhibited.
- FIG. 3 shows the second embodiment, and the same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.
- a bypass passage 23 that directly connects the discharge side passage of the compressor 12 and the inlet of the second evaporator 19 is formed, and a shut mechanism 24 is provided in the bypass passage 23.
- the shut mechanism 24 can be constituted by a normally closed solenoid valve that opens only when energized.
- the shut mechanism 24 is maintained in the shut state by a control signal from the ECU 21 during normal times (when it is not necessary to defrost the second evaporator 19). Therefore, since the refrigerant does not flow into the bypass passage 23, the operation of the compressor 12 performs the same refrigeration cycle operation as in the first embodiment, and the first evaporator 15 has a relatively high temperature range suitable for cooling the vehicle interior. At the same time that the cooling action can be exerted, the second evaporator 19 can exert a cooling action in a lower temperature region suitable for cooling in the refrigerator.
- the ECU 21 determines that the second evaporator 19 is in a frost state. Is output, a control signal is output to the shut mechanism 24, and the shut mechanism 24 is opened.
- the defrosting operation of the second evaporator 19 can be performed with an extremely simple configuration.
- the end of the defrosting operation may be determined in the same manner as in the first embodiment, and the shut mechanism 24 may be returned to the shut state.
- the throttle mechanism 180 of the branch passage 17 according to the second embodiment can be configured by using a normal fixed throttle or variable throttle from V which does not require the fully open function to be set.
- FIG. 4 shows a third embodiment, which is a modification of the first embodiment. That is, in the third embodiment, in addition to the configuration of the first embodiment, the upstream portion of the throttle mechanism 18 with a fully open function in the branch passage 17 and the portion between the first evaporator 15 and the compressor 12 are provided. A second branch passage 25 is added to connect with.
- a throttle mechanism 26 for reducing the pressure of the refrigerant and a third evaporator 27 positioned downstream of the throttle mechanism 26 relative to the refrigerant flow are arranged. Since the aperture mechanism 26 does not need to be set to a fully open function, it can be configured using a normal fixed aperture or variable aperture. Air in the space to be cooled is blown to the third evaporator 27 by an electric blower (third blower) 28. The operation of the third blower 28 is also controlled by the ECU 21. Third evaporator 27
- the downstream side of the third evaporator 27 joins the downstream side of the first evaporator 15 and is connected to the suction side of the compressor 12, the first and third evaporators 15
- the refrigerant evaporation pressure of 27 is almost the same as the suction pressure of the compressor 12. Accordingly, the refrigerant evaporating temperatures of the first and third evaporators 15 and 27 are also the same temperature, so that the first and third evaporators 15 and 27 perform a cooling operation in the same temperature range.
- the refrigerant evaporation temperature of the second evaporator 19 is lower than the refrigerant evaporation temperature of the first and third evaporators 15 and 27, but the defrosting of the second evaporator 19 is performed. Can be performed in the same manner as in the first embodiment by opening the aperture mechanism 18 with the fully open function.
- the first evaporator 15 is used to cool the front seat side area of the vehicle interior, By evaporator 27 The rear seat side area of the passenger compartment is cooled, and the interior of the refrigerator is cooled by the second evaporator 19.
- FIG. 5 shows a fourth embodiment, which is a modification of the second embodiment (FIG. 3). That is, in the fourth embodiment, in addition to the configuration of the second embodiment, the upstream portion of the throttle mechanism 180 in the branch passage 17 and the portion between the first evaporator 15 and the compressor 12 are connected. Following 2 branch passages 25. A throttle mechanism 26 and a third evaporator 27 are disposed in the second branch passage 25. The throttle mechanism 26 and the third evaporator 27 are the same as those in the third embodiment.
- the defrosting of the second evaporator 19 can be performed by the bypass passage 23 and the shut mechanism 24 in the same manner as in the second embodiment, and the cooling action by the third evaporator 27 is achieved. Can be performed in the same manner as in the third embodiment.
- FIG. 6 shows a fifth embodiment, which is a modification of the first embodiment. That is, in the fifth embodiment, a dedicated throttle mechanism 30 is added upstream of the first evaporator 15, and accordingly, the ejector 14 is arranged in parallel with the throttle mechanism 30.
- Various throttle mechanisms 30 can be used. For example, a temperature-type expansion valve that controls the degree of superheat of the outlet refrigerant of the first evaporator 15 to a predetermined value is preferable.
- a throttling mechanism 18 with a fully-opening function is disposed upstream of the second evaporator 19, and when the defrosting of the second evaporator 19 is necessary, the throttling mechanism 18 is fully opened to remove the second evaporator 19. Executing the frost operation is the same as in the first embodiment.
- the ejector 14 and the first evaporator 15 are connected in series.
- the ejector 14 functions as a refrigerant flow rate adjusting function of the first evaporator 15 and also functions as a pump that creates a refrigerant pressure difference between the first evaporator 15 and the second evaporator 19.
- the ejector 14 when designing the ejector 14, it is necessary to satisfy both the required specifications of the refrigerant flow rate adjusting function and the pump function, and the first evaporator 15 has the first function to secure the refrigerant flow rate adjusting function.
- the design must depend on the evaporator 15. As a result, there is a problem that it becomes difficult to operate the eddy-type refrigeration cycle apparatus with high efficiency.
- a dedicated throttle is provided in the upstream portion of the first evaporator 15.
- the mechanism 30 is arranged so that the ejector 14 does not share the refrigerant flow rate adjusting function of the first evaporator 15. For this reason, the ejector 14 can specialize only in a pump function that creates a refrigerant pressure difference between the first evaporator 15 and the second evaporator 19.
- the shape of the ejector 14 is optimized so that a predetermined pressure difference is provided between the first and second evaporators 15 and 19, in other words, the passing flow rate of the ejector 14 is a predetermined flow rate. It becomes possible to design. As a result, the ejector-type refrigeration cycle apparatus can be operated efficiently even with a wide range of fluctuations in cycle operating conditions (compressor speed, outside air temperature, cooling target space temperature, etc.).
- FIG. 7 shows a sixth embodiment, which is a modification of the second embodiment (FIG. 3). That is, in the sixth embodiment, in the cycle configuration having the bypass passage 23 and the shut mechanism 24 for the defrosting operation of the second evaporator 19 as in the second embodiment, the upstream side of the first evaporator 15 is provided. A special throttle mechanism 30 is added, and the ejector 14 is connected in parallel to the throttle mechanism 30.
- FIG. 8 shows a seventh embodiment, which is a modification of the third embodiment (FIG. 4). That is, in the seventh embodiment, as in the third embodiment, the throttling mechanism 18 with a fully opening function for the defrosting operation is arranged upstream of the second evaporator 19, and the throttling mechanism 26 and the third throttling mechanism are arranged. In the cycle configuration having the evaporator 27, a dedicated throttle mechanism 30 is added upstream of the first evaporator 15, and the ejector 14 is connected in parallel to the throttle mechanism 30.
- FIG. 9 shows an eighth embodiment, which is a modification of the fourth embodiment (FIG. 5). That is, the eighth embodiment includes the bypass passage 23 and the shut mechanism 24 for the defrosting operation of the second evaporator 19 as in the fourth embodiment, and the throttle mechanism 26 and the third evaporator 27. Cycle with In the configuration, a dedicated throttle mechanism 30 is added upstream of the first evaporator 15, and the ejector 14 is connected in parallel to the throttle mechanism 30.
- the parallel connection of the ejectors 14 is the same as that of the fifth embodiment (FIG. 6). Therefore, the eighth embodiment can exhibit the action and effect obtained by combining the fourth embodiment and the fifth embodiment.
- FIG. 10 shows a ninth embodiment, which is a modification of the first embodiment. That is, in the ninth embodiment, the shut mechanism 31 is provided in the upstream portion of the ejector 14 in the refrigerant circulation passage 11 in the cycle configuration of the first embodiment. Specifically, the shut mechanism 31 can be constituted by a normally open solenoid valve that closes only when energized.
- the ECU 21 sends a control signal to the shut mechanism 31. Outputs the shut mechanism 31 to the shut (fully closed) state. At the same time, the ECU 21 outputs a control signal to the throttle mechanism 18 with the fully open function, and the throttle mechanism 18 is fully opened.
- the refrigerant circulation passage 11 is shut by the shut mechanism 31, so that the entire amount of the high-temperature high-pressure refrigerant at the outlet of the radiator 13 passes through the throttle mechanism 18 and flows into the second evaporator 19. To do.
- a defrost capability can be improved and the defrost of the 2nd evaporator 19 can be complete
- FIG. 11 shows a tenth embodiment, which is a modification of the second embodiment (FIG. 3). That is, in the cycle configuration of the second embodiment, the tenth embodiment is provided with a shut mechanism 31 in the refrigerant circulation passage 11 upstream of the ejector 14. Specifically, the shut mechanism 31 can be constituted by a normally open solenoid valve that closes only when energized.
- the ECU 21 sends a control signal to the shut mechanism 31. Outputs the shut mechanism 31 to the shut (fully closed) state. At the same time, the ECU 21 outputs a control signal to the shut mechanism 24 in the bypass passage 23 to fully open the shut mechanism 24.
- the refrigerant circulation passage 11 is shut by the shut mechanism 31. Therefore, the compressor 12 that passes through the bypass passage 23 and flows into the second evaporator 19 has a high temperature and high pressure on the discharge side. The amount of gas phase refrigerant increases. Thereby, compared with 2nd Embodiment, a defrosting capability can be improved and the defrosting of the 2nd evaporator 19 can be complete
- FIG. 12 shows an eleventh embodiment, which is a modification of the tenth embodiment (FIG. 11). That is, in the eleventh embodiment, a shut mechanism 32 corresponding to the shut mechanism 31 of the tenth embodiment is provided in the upstream portion of the radiator 13. Specifically, the shut mechanism 32 can also be constituted by a normally open solenoid valve, similarly to the shut mechanisms 31 of the ninth and tenth embodiments.
- the ECU 21 when the frost state force 3 ⁇ 4cu21 of the second evaporator 19 is determined based on the air temperature in the vicinity of the second evaporator 19, the ECU 21 outputs a control signal to the shut mechanism 32. , Set the shut mechanism 32 to the shut (fully closed) state. At the same time, the ECU 21 outputs a control signal to the shut mechanism 24 in the bypass passage 23 so that the shut mechanism 24 is fully opened.
- the upstream passage of the radiator 13 is shut by the shut mechanism 32, so that the entire amount of the high-temperature and high-pressure gas-phase refrigerant on the discharge side of the compressor 12 passes through the bypass passage 23. It flows into the second evaporator 19. Thereby, the defrosting capability can be further improved as compared with the tenth embodiment.
- the two shut mechanisms 24, 32 may be configured by a single passage switching mechanism of a three-way valve type! / ⁇ .
- FIG. 13 shows a twelfth embodiment, which is a modification of the first embodiment. That is, the twelfth embodiment In this state, instead of the aperture mechanism 18 with the fully open function of the first embodiment, an aperture mechanism 180 including a normal fixed aperture and a variable aperture without setting the fully open function is used.
- a binos passage 33 is provided in parallel with the throttle mechanism 180, and a shut mechanism 34 is provided in the bypass passage 33.
- the shut mechanism 34 can be constituted by a normally closed solenoid valve that opens only when energized.
- the amount of refrigerant flowing into the second evaporator 19 is adjusted by the throttle mechanism 180.
- the shut mechanism 34 shifts to the fully open state by the control signal of the ECU 21.
- the high-temperature and high-pressure liquid refrigerant at the outlet of the radiator 13 passes through the bypass passage 33 and flows into the second evaporator 19, so that the second evaporator 19 can be defrosted.
- the twelfth embodiment is described as a modification of the first embodiment, in addition to the first embodiment, another embodiment (third, In each of the fifth, seventh, and ninth embodiments), instead of the throttle mechanism 18 with the fully open function, by providing a normal throttle mechanism 180, a binos passage 33, and a shut mechanism 34 that do not set the fully open function, The concept of the twelfth embodiment can be similarly implemented.
- the radiator 13 is branched at the outlet side to form a branch passage 17 connected to the suction port 14c of the ejector 14.
- the throttle mechanisms 18, 18 are arranged at the outlet side to form a branch passage 17 connected to the suction port 14c of the ejector 14.
- the second evaporator 1 0 and the second evaporator 19 are arranged.
- the second evaporator 1 0 and the second evaporator 19 are arranged.
- the gas-liquid separator 35 for separating the liquid phase refrigerant and storing the liquid-phase refrigerant is arranged, the gas-phase refrigerant separated by the gas-liquid separator 35 is led out to the suction side of the compressor 12, and separated by the gas-liquid separator 35 The liquid phase refrigerant thus led out to the branch passage 36 side.
- This branch passage 36 is a liquid refrigerant outlet near the bottom of the gas-liquid separator 35 and the suction of the ejector 14.
- a throttle mechanism 180 is provided on the upstream side of the branch path 36, and the second evaporator 19 is disposed on the downstream side of the throttle mechanism 180.
- the aperture mechanism 180 consists of a normal fixed aperture or variable aperture that does not set the fully open function.
- the refrigerant evaporation pressure (refrigerant evaporation temperature) of the second evaporator 19 is lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the first evaporator 15.
- 1 evaporator 15 provides a cooling effect in the high temperature range
- 2nd evaporator 19 provides a cooling effect in the low temperature range.
- the shut mechanism 24 of the bypass passage 23 is opened by the control signal of the ECU 21.
- the high-temperature and high-pressure gas-phase refrigerant on the discharge side of the compressor 12 passes through the binos passage 23 and flows into the second evaporator 19, so that the second evaporator 19 can be defrosted.
- FIG. 15 shows a fourteenth embodiment, and a gas-liquid separator 35 is added to the first embodiment shown in FIG.
- the gas-liquid separator 35 is connected to the downstream side of the first evaporator 15, separates the gas-liquid at the outlet refrigerant of the first evaporator 15, stores the liquid-phase refrigerant, and stores the gas-phase refrigerant in the compressor 12. It flows out to the inhalation side.
- a common space to be cooled (specifically, the space in the refrigerator of the vehicle-mounted refrigerator) by the first evaporator 15 and the second evaporator 19.
- the first evaporator 15 is disposed on the upstream side of the air flow of the electric blower 16
- the second evaporator 19 is disposed on the downstream side of the air flow of the first evaporator 15, and the second evaporation is performed. Cooling air after passing through the container 19 is blown out to the space to be cooled (inside the space).
- the first evaporator 15 and the second evaporator 19 may be integrally configured by means such as brazing.
- the first evaporator 15 and the second evaporator 19 cool the common cooling target space (the interior space) to a low temperature of 0 ° C or lower. It is necessary to perform a defrosting operation on both the second evaporators 19.
- FIG. 16 summarizes the operation of the various devices of the fourteenth embodiment. During normal operation, the compressor 12, the electric cooling fan 13a of the radiator 13, and the electric blower 16 of the cooling unit 37 are in an operating state. Then, the throttle mechanism 18 with the fully open function is controlled to a predetermined throttle state.
- the blown air of the electric blower 16 can be cooled by the heat absorption action accompanying the refrigerant evaporation in the first evaporator 15 and the second evaporator 19, and the cooling target space of the cooling unit 37 can be cooled. . That is, a normal cooling operation can be executed.
- the control device 21 determines the frost state of the first and second evaporators 15 and 19 to defrost each device in the refrigeration cycle 10. Switch to operation mode. That is, the control device 21 controls the throttle mechanism 18 with the fully open function to the fully open state, and simultaneously stops the compressor 12 and the electric blower 16 for the evaporator.
- the control device 21 controls the throttle mechanism 18 with the fully open function to the fully open state, and simultaneously stops the compressor 12 and the electric blower 16 for the evaporator.
- the stopped state of the compressor 12 is the electromagnetic pressure control. This means that the discharge capacity is set to the minimum capacity of around 0% by the device 12a.
- the electromagnetic clutch may be shut off and the compressor 12 may be stopped.
- the radiator cooling fan 13a may be in the stopped or activated state during defrosting operation.
- the throttling mechanism 18 When the throttling mechanism 18 is fully opened during the defrosting operation, the high-temperature liquid refrigerant at the outlet side of the radiator 13 flows directly into the second evaporator 19, and further, the second evaporator 19 dissipates heat to a predetermined amount.
- the medium-temperature liquid refrigerant whose temperature has decreased passes through the refrigerant suction port 14 c of the ejector 14 and flows into the first evaporator 15. In this way, the high-temperature liquid refrigerant on the outlet side of the radiator 13 flows in the order of the second evaporator 19 ⁇ the first evaporator 15, and the second evaporator 19 and the first evaporator 15 are defrosted simultaneously.
- the first and second evaporators 15 and 19 are temporarily defrosted using the high-temperature liquid refrigerant on the radiator 13 side that is present when the compressor 12 is in operation. Therefore, the compressor 12 is stopped during the defrosting operation. That is, when the first and second evaporators 15 and 19 are small in size and have a small required cooling capacity, the high-temperature liquid coolant on the radiator 13 side that is present when the compressor 12 is operating is The first and second evaporators 15 and 19 can be removed by allowing them to flow into the evaporators 15 and 19. Frost can be done.
- FIG. 17 shows a fifteenth embodiment, in which a shut mechanism 31 on the upstream side of the ejector 14 and a throttle mechanism 38 on the outlet side of the gas-liquid separator 35 are added to the fourteenth embodiment.
- the shut mechanism 31 may be the same as described in FIG.
- the throttle mechanism 38 has a function of fully opening the outlet side passage (compressor suction side passage) of the gas-liquid separator 35 and may have the same configuration as the throttle mechanism 18. However, the throttle mechanism 38 is controlled by the control device 21 so as to be fully opened during normal operation and to have a predetermined throttle opening degree during defrosting operation.
- FIG. 18 summarizes the operation of the various devices of the fifteenth embodiment.
- the compressor 12, the electric cooling fan 13a of the radiator 13, and the electric blower 16 of the cooling unit 37 are in an operating state. It becomes.
- the throttle mechanism 18 with the fully open function is controlled to a predetermined throttle opening state
- the throttle mechanism 38 with the fully open function is controlled to the fully open state
- the shut mechanism 31 is controlled to the fully open state.
- the cooling air of the electric blower 16 can be cooled by the cooling (heat absorption) action of the first and second evaporators 15 and 19, and the cooling target space of the cooling unit 37 can be cooled. That is, a normal cooling operation can be performed.
- the control device 21 controls each device as follows in order to execute the defrosting operation.
- the cooling fan 13a for the radiator and the electric blower 16 for the evaporator are respectively stopped.
- the throttle mechanism 18 is controlled to be fully opened, the throttle mechanism 38 is controlled to a predetermined throttle opening state, and the shut mechanism 31 is controlled to be fully closed.
- the medium-temperature and high-pressure gas-phase refrigerant passes through the refrigerant suction port 14c portion of the ejector 14. It flows into the first evaporator 15. In this way, the high-pressure and high-temperature gas-phase refrigerant flows in the order of the second evaporator 19 ⁇ the first evaporator 15, and the second evaporator 19 and the first evaporator 15 are defrosted simultaneously.
- the high-pressure refrigerant that has flowed out of the first evaporator 15 is gas-liquid separated in the gas-liquid separator 35, and the high-pressure gas-phase refrigerant that has flowed out of the gas-liquid separator 35 is decompressed to a predetermined low-pressure state by the throttle mechanism 38. Then, it is sucked into the compressor 12 as a low-temperature and low-pressure gas-phase refrigerant.
- FIG. 19 is a Mollier diagram showing the cycle behavior during the defrosting operation of the fifteenth embodiment.
- FIG. 20 shows a sixteenth embodiment.
- a gas-liquid separator 35 is added to the outlet side of the first evaporator 15 and a fully open function is provided on the outlet side of the second evaporator 19 with respect to the first embodiment of FIG.
- the aperture mechanism with 39 is added.
- the diaphragm mechanism 39 may have the same configuration as the diaphragm mechanism 18. However, the throttle mechanism 39 is controlled by the control device 21 so as to be fully opened during normal operation and to have a predetermined throttle opening degree during defrosting / cooling operation.
- the first evaporator 15 is provided for air conditioning in the vehicle interior, while the second evaporator 19 is provided for cooling in the refrigerator mounted on the vehicle, and each of the separate electric blowers 16, 20 is provided. I started to cool the air!
- FIG. 21 summarizes the operation of the various devices of the sixteenth embodiment.
- the electric cooling fans of the compressor 12 and the radiator 13 are shown.
- Ann 13a and electric blowers 16, 20 are activated.
- the throttle mechanism 18 on the inlet side of the second evaporator 19 is controlled to a predetermined throttle opening state, and conversely, the throttle mechanism 39 on the outlet side of the second evaporator 19 is controlled to be fully opened.
- the low-pressure refrigerant that has been depressurized after passing through the ejector 14 evaporates, so that the air blown from the electric blower 16 is cooled by the cooling (heat absorption) action of the first evaporator 15. Cool the passenger compartment.
- the low-pressure refrigerant that has been reduced in pressure through the throttle mechanism 18 evaporates, so the air blown from the electric blower 20 is cooled by the cooling (heat absorption) action of the second evaporator 19, Cool down the refrigerator.
- cooling in the passenger compartment and cooling in the refrigerator can be performed simultaneously.
- control device 21 controls each device as follows in order to execute the defrosting / cooling operation mode.
- the electric blower 20 for the second evaporator is brought into a stopped state.
- the throttle mechanism 18 on the inlet side of the second evaporator 19 is controlled to a fully open state, and conversely, the throttle mechanism 39 on the outlet side of the second evaporator 19 is controlled to a predetermined throttle opening state.
- the liquid-phase refrigerant on the outlet side of the radiator 13 flows into the second evaporator 19 in a high temperature and high pressure state, and the second evaporator 19 is defrosted.
- the high-pressure refrigerant dissipates heat in the second evaporator 19 and becomes a high pressure state of medium temperature.
- the high-pressure refrigerant is decompressed by the throttle mechanism 39, and enters a low-temperature and low-pressure gas-liquid two-phase state.
- This low-pressure refrigerant passes through the refrigerant suction port 14 c of the ejector 14 and flows into the first evaporator 15.
- the suction-side low-pressure refrigerant from the refrigerant suction port 14c and the low-pressure refrigerant that has passed through the nozzle 14a of the ejector 14 join together and flow into the first evaporator 15, and exhibit the cooling (heat absorption) action of the first evaporator 15. it can.
- FIG. 22 is a Mollier diagram showing the cycle behavior in the defrosting / cooling operation mode according to the sixteenth embodiment.
- FIG. 17 In the fifteenth embodiment (FIG. 17), as shown in FIG. The generators 15 and 19 are defrosted. In the seventeenth embodiment (FIG. 23), the low-pressure and high-temperature refrigerant is defrosted from the first and second evaporators 15 and 19 as shown in FIG. I do.
- a variable throttle mechanism 181 that does not have a fully open function is provided at the inlet of the second evaporator 19.
- FIG. 24 shows a specific example of the variable throttle mechanism 181.
- the first throttle hole 181a having a small throttle opening and the second throttle hole 18 lb having a larger throttle opening than the first throttle hole 181a are shown in FIG.
- the movable plate member opens in parallel with 18 lc.
- the movable plate member 181c is arranged so as to be movable in the transverse direction of the branch passage 17 (in the direction orthogonal to the refrigerant flow direction a), and the movable plate member 181c is constituted by a servo motor or the like. It is driven by 181d.
- the movable plate member 181c is moved to the position shown in Fig. 24 (a), and the first throttle hole 18 8 la is positioned in the branch passage 17, whereas, during the defrosting operation, the movable plate member 181c is moved. 181c is moved to the position shown in FIG. 24 (b), and the second throttle hole 181b is positioned in the branch passage 17.
- FIG. 25 summarizes the operation of the various devices of the seventeenth embodiment.
- the compressor 12, the radiator cooling fan 13a, and the evaporator blower 16 are operated, and the shut mechanism 31 is fully opened. Put it in a state.
- variable throttle mechanism 181 the electric actuator 181 d is controlled by the ECU 21 to move the movable plate member 181 c to the position shown in FIG. 24 (a), and the first throttle hole 181 a is positioned in the branch passage 17.
- the throttle opening by the first throttle hole 181a is set to a small state, and the low-pressure refrigerant depressurized by the first throttle hole 181a flows into the second evaporator 19 and enters the second evaporator 19. 2 Cooling (endothermic) action of the evaporator 19 is exhibited.
- the high-pressure refrigerant flows into the ejector 14 through the shut mechanism 31 in the fully opened state, is depressurized by the nozzle portion 14a, passes through the low-pressure refrigerant depressurized by the nozzle portion 14a, and the second evaporator 19, and then is The low-pressure refrigerant sucked into the suction port 14c flows into the first evaporator 15, and the cooling (heat absorption) action of the first evaporator 15 is exhibited.
- the air blown by the electric blower 16 can be cooled by the combination of the cooling (heat absorption) actions of the first and second evaporators 15 and 19, and the cooling target space of the cooling unit 37 can be cooled. The That is, a normal cooling operation is performed.
- the control device 21 controls each device as follows in order to execute the defrosting operation.
- variable throttle mechanism 181 the electric actuator 181 d is controlled by the ECU 21 to move the movable plate member 181 c to the position shown in FIG. 24 (b), and the second throttle hole 18 lb is positioned in the branch passage 17. Let Thereby, the state of the throttle opening degree: large by the second throttle hole 181b is set.
- the heat dissipation of the refrigerant in the radiator 13 is substantially stopped by stopping the radiator cooling fan 13a. Therefore, the refrigerant on the discharge side of the compressor 12 is released in a high-temperature and high-pressure gas phase state. It passes through the heater 13 and reaches the inlet side of the variable throttle mechanism 181. Here, since the shut mechanism 31 is fully closed during the defrosting operation, the entire amount of the gas-phase refrigerant on the discharge side of the compressor 12 flows into the variable throttle mechanism 181.
- the second throttle hole 181b having a larger throttle opening than the first throttle hole 181a exerts a pressure reducing action. Due to this depressurization action, the high-temperature and high-pressure gas-phase refrigerant becomes a low-pressure and high-temperature gas-phase refrigerant, and this low-pressure and high-temperature gas-phase refrigerant first flows into the second evaporator 19 to defrost the second evaporator 19. Do.
- the low-pressure and high-temperature gas-phase refrigerant flows into the first evaporator 15, and defrosts the first evaporator 15.
- the refrigerant that has passed through the first evaporator 15 is gas-liquid separated in the gas-liquid separator 35, and the gas-phase refrigerant in the gas-liquid separator 35 is sucked into the compressor 12 and compressed again.
- FIG. 26 is a Mollier diagram showing the cycle behavior during the defrosting operation of the seventeenth embodiment.
- the shut-off mechanism 31 is fully closed so that the entire amount of the high-temperature and high-pressure gas-phase refrigerant is reduced by the variable throttle mechanism 181 and then flows into the second evaporator 19. Then, the refrigerant that has passed through the second evaporator 19 is caused to flow into the first evaporator 15. Thereby, the defrosting of the second evaporator 19 and the first evaporator 15 can be performed constantly using the low-pressure high-temperature refrigerant.
- variable throttle mechanism 181 depressurizes the liquid-phase refrigerant condensed in the radiator 13 during normal operation, while depressurizing the gas-phase refrigerant on the discharge side of the compressor 12 during defrosting operation.
- density of the gas-phase refrigerant is significantly smaller than that of the liquid-phase refrigerant
- the throttle opening during the defrosting operation of the variable throttle mechanism 181 is made larger than that during the normal operation, and the cycle circulation refrigerant during the defrosting operation is increased. Ensure that the flow rate is secured.
- the shut mechanism 31 is a fully open and fully closed on-off valve type.
- Force shut mechanism 31 is a flow rate adjustment type valve mechanism capable of continuously adjusting the passage area, and defrosting operation is performed. Occasionally, a predetermined flow rate of high-temperature gas-phase refrigerant may be allowed to flow into the ejector 14 side. Also, adjust the refrigerant flow rate to the ejector 14 side during normal operation with the flow adjustment type short mechanism 31.
- the shut mechanism 31 may be configured as a flow rate adjusting type valve mechanism, as is the case with the shut mechanisms in other embodiments.
- FIG. 27 shows an eighteenth embodiment.
- the shut mechanism 31 of the seventeenth embodiment (FIG. 23) is eliminated, and the upstream portion of the ejector 14 is directly connected to the outlet portion of the radiator 13.
- the other points of the eighteenth embodiment are the same as those of the seventeenth embodiment. Accordingly, in FIG. 25, the switching of the operation between the normal operation and the defrosting operation of the other devices is as shown in FIG.
- a predetermined proportion of the high-temperature and high-pressure gas-phase refrigerant that has passed through the radiator 13 during the defrosting operation is depressurized by the variable throttle mechanism 181 so that the low-pressure high-temperature gas-phase refrigerant is This low-pressure high-temperature gas-phase refrigerant flows into the second evaporator 19 and defrosts the second evaporator 19.
- the remainder of the high-temperature and high-pressure gas-phase refrigerant that has passed through the radiator 13 flows into the ejector 14 and is depressurized, so that it becomes a low-pressure high-temperature gas-phase refrigerant.
- This low-pressure high-temperature gas-phase refrigerant and the low-pressure gas-phase refrigerant after passing through the second evaporator 19 merge at the ejector 14, and the low-pressure high-temperature gas-phase refrigerant after this merge flows into the first evaporator 15. Then, the first evaporator 15 is defrosted.
- the low-pressure high-temperature gas-phase refrigerant that has been depressurized after passing through the ejector 14 flows directly into the first evaporator 15, so that the first evaporator 15 is compared with the seventeenth embodiment.
- the defrosting ability of the first evaporator 15 can be increased by increasing the temperature (heat amount) of the inflowing gas phase refrigerant.
- FIG. 28 shows the nineteenth embodiment. Compared to the seventeenth embodiment (FIG. 23), the bypass passage 40 of the radiator 13, the shut mechanism 41 of the bypass passage 40, and the shut of the outlet portion of the radiator 13. Mechanism 42 is added. The shut mechanism 41 and the shut mechanism 42 are arranged in parallel.
- FIG. 29 shows the operation switching between the normal operation and the defrost operation of each device in the nineteenth embodiment.
- the shut mechanism 31 and the shut mechanism 42 are fully opened, while the shut mechanism 41 is fully closed to block the bypass passage 40.
- the same operation as that in the seventeenth embodiment is performed during normal operation.
- shut mechanism 31 and the shut mechanism 42 are fully closed, while the shut mechanism 41 is fully open to open the bypass passage 40.
- the high-pressure and high-temperature discharged gas-phase refrigerant of the compressor 12 flows through the bypass passage 40 and bypasses the radiator 13.
- the total amount of high-pressure and high-temperature discharged gas-phase refrigerant that bypasses the radiator 13 is reduced in pressure by the variable throttle mechanism 181, and becomes low-pressure high-temperature gas-phase refrigerant.
- This low-pressure high-temperature gas-phase refrigerant flows in the order of the second evaporator 19 ⁇ the ejector 14 ⁇ the first evaporator 15, and defrosts the second evaporator 19 and the first evaporator 15.
- the radiator cooling fan 13a is maintained in the operating state with the shut mechanism 42 at the outlet of the radiator 13 being fully closed during the defrosting operation.
- a part of the gas-phase refrigerant discharged from the compressor 12 can be cooled and condensed by the outside air, and the liquid-phase refrigerant can be stored inside the radiator 13. For this reason, since the amount of the liquid-phase refrigerant that accumulates in the gas-liquid separator 35 during the defrosting operation can be reduced, there is an advantage that the tank capacity of the gas-liquid separator 35 can be reduced.
- FIG. 30 shows a twentieth embodiment, in which the shut mechanism 31 in the nineteenth embodiment (FIG. 28) is eliminated. Accordingly, the twentieth embodiment is the same as the cycle configuration of the eighteenth embodiment (FIG. 27) in that the shut mechanism 31 is eliminated. For this reason, the twentieth embodiment can exhibit the operational effects obtained by combining the eighteenth embodiment and the nineteenth embodiment.
- FIG. 31 shows a twenty-first embodiment, which is a cycle configuration in which three or more evaporators are combined.
- the twenty-first embodiment is based on the cycle configuration of the seventeenth embodiment (FIG. 23), and a second branch passage 25 is added thereto.
- the second branch passage 25 is the same as that of the third embodiment (FIG. 4), is branched on the upstream side of the variable throttle mechanism 181 of the first branch passage 17, and is connected to the outlet side of the first evaporator 15.
- variable throttle mechanism 182 is provided on the upstream side of the second branch passage 25, and a third evaporator 27 is provided on the downstream side of the variable throttle mechanism 182.
- the variable throttle mechanism 182 includes a first throttle hole with a small throttle opening and a second throttle hole with a throttle opening larger than the first throttle hole. It is the structure opened in parallel.
- variable throttle mechanism 182 can set the throttle opening by the first throttle hole: small state during normal operation, and can set the throttle opening: large state by the second throttle hole during defrosting operation. It is like this.
- the third evaporator 27 constitutes an independent cooling unit 43 together with the electric blower 28.
- the first cooling unit 37 cools the interior space (the cooling target space) of the first refrigerator to a low temperature of 0 ° C. or lower
- the second cooling unit 43 cools the second refrigerator compartment.
- the inner space (space to be cooled) is cooled to a low temperature below 0 ° C!
- the refrigerant evaporation pressure (refrigerant evaporation temperature) of the third evaporator 27 is the same as that of the first evaporator 15. Become equivalent. Therefore, the cooling temperature of the second cooling unit 43 is higher than the cooling temperature of the first cooling unit 37.
- the blown air of the electric blower 28 is cooled by the third evaporator 27, and the cooled air is blown out to the space to be cooled.
- the cooling temperature of the second cooling unit 43 is also a low temperature of 0 ° C. or less, the third evaporator 27 also needs to be defrosted.
- a temperature sensor 22a is installed in the vicinity of the third evaporator 27, the temperature in the vicinity of the third evaporator 27 is detected by the temperature sensor 22a, and the detected signal force is input to the CU21.
- the ECU 21 issues a defrosting operation command based on the detected temperatures of the temperature sensor 22 of the first cooling unit 37 and the temperature sensor 22a of the second cooling unit 43.
- Fig. 32 shows the operation switching between the normal operation and the defrosting operation of each device in the twenty-first embodiment. Show.
- the gas-phase refrigerant on the discharge side of the compressor 12 passes through the radiator 13 while being in a high-temperature and high-pressure state, and is depressurized by the variable throttle mechanisms 181 and 182 to become a low-pressure high-temperature gas-phase refrigerant.
- the low-pressure high-temperature gas-phase refrigerant in the first branch passage 17 flows in the order of the second evaporator 19 ⁇ the first evaporator 15, and defrosts both the evaporators 19 and 15.
- the low-pressure high-temperature gas-phase refrigerant in the second branch passage 25 flows into the third evaporator 27, and the third evaporator 27 is defrosted.
- the shut mechanism 31 is provided upstream of the ejector 14, and the force that fully closes the shut mechanism 31 during the defrosting operation. Good. That is, in the cycle configuration of the eighteenth embodiment (FIG. 27), the second branch passage 25 having the variable throttle mechanism 182 and the third evaporator 27 may be combined.
- FIG. 33 shows a twenty-second embodiment in which a second branch passage 25 having a variable throttle mechanism 182 and a third evaporator 27 is combined in the cycle configuration of the nineteenth embodiment (FIG. 28).
- a shut mechanism 31 is provided on the upstream side of the ejector 14, and the force for fully closing the shut mechanism 31 during the defrosting operation is shown in FIG. It can be abolished as in 30).
- FIG. 34 shows a 23rd embodiment.
- a dedicated throttle mechanism 30 is added upstream of the first evaporator 15, and the ejector 14 is connected to this throttle.
- a cycle configuration arranged in parallel with mechanism 30 is adopted.
- the cooling unit 37, the shut mechanism 31, and the variable throttle mechanism 181 in the seventeenth embodiment are combined in such a cycle configuration of the parallel arrangement of the radiators.
- a shut mechanism 31 may be provided upstream of the ejector 14, and the shut mechanism 31 may be completely closed during the defrosting operation.
- the shut mechanism 31 may be eliminated.
- FIG. 35 shows a twenty-fourth embodiment, which employs a cycle configuration with an ejector arranged in parallel in the nineteenth embodiment (FIG. 28).
- the operation switching of each device during the normal operation and the defrosting operation in the 24th embodiment is the same as that in the 19th embodiment, and the operation switching of each device may be performed as shown in FIG.
- shut mechanism 31 upstream of the ejector 14 may be eliminated.
- FIG. 36 shows a twenty-fifth embodiment, which adopts a cycle configuration with an ejector arranged in parallel in the twenty-first embodiment (FIG. 31).
- the shut mechanism 31 on the upstream side of the ejector 14 may be eliminated.
- FIG. 37 shows a twenty-sixth embodiment, which employs a cycle configuration with an ejector arranged in parallel in the twenty-second embodiment (FIG. 33).
- the shut mechanism 31 on the upstream side of the ejector 14 may be eliminated.
- the air temperature in the vicinity of the second evaporator 19 and the third evaporator 27 is detected by the temperature sensors 22 and 22a, and the defrosting operation is automatically performed.
- the automatic control of the defrosting operation can be variously modified.
- the surface temperature of the second and third evaporators 19 and 27 is detected by the temperature sensors 22 and 22a to automatically control the defrosting operation. May be performed.
- a refrigerant temperature sensor for detecting the refrigerant temperature is provided in the refrigerant passage in the vicinity of the second and third evaporators 19 and 27, and the refrigerant temperature is divided based on the refrigerant temperature in the vicinity of the second and third evaporators 19 and 27. Automatic control of frost operation may be performed.
- a refrigerant pressure sensor for detecting the refrigerant pressure in the vicinity of the second and third evaporators 19 and 27 is provided.
- Second, Automatic control of the defrosting operation may be performed based on the refrigerant pressure in the vicinity of the third evaporators 19 and 27.
- FIG. 2 As the throttle mechanism 18 with a fully open function, a movable plate member 18c having a throttle hole 18a constituting a fixed throttle and a full opening hole 18b for fully opening the branch passage 17 is shown.
- An electric expansion valve that continuously changes the opening of the valve body with an electric actuator such as a servo motor is used as a throttling mechanism 18 with a fully-open function that shows a type driven by an electric actuator 18d.
- variable throttle mechanism 181 is movable with a first throttle hole 181a having a small throttle opening and a second throttle hole 181b having a larger throttle opening than the first throttle hole 181a opened in parallel.
- a force mechanism shown in a specific example in which the plate member 181c is driven by the electric actuator 181d may be a valve mechanism capable of continuously adjusting the throttle opening as the variable throttle mechanism 181.
- Both of the second evaporators 19 may be used for cooling in the refrigerator. That is, the first evaporator 15 with the refrigerant evaporation temperature on the high temperature side cools the refrigerator compartment in the refrigerator, and the second evaporator 19 with the refrigerant evaporation temperature on the low temperature side cools the freezer compartment in the refrigerator. Also good.
- the first evaporator 15 and the second evaporator 19 constitute one cooling unit 37, and the inside of one refrigerator is constituted by the cooling unit 37.
- the first evaporator 15 and the second evaporator 19 are arranged in separate refrigerators, and the first refrigerator 15 and the second evaporator 19 cool the separate refrigerators. Good.
- FIG. 15 In the fourteenth embodiment (FIG. 15) and the like, an example in which the gas-liquid separator 35 is arranged on the outlet side of the first evaporator 15 is shown. If a liquid separator (Resino is installed, and the cycle refrigerant flow rate is controlled so that the outlet refrigerant of the first evaporator 15 has a predetermined degree of superheat during normal operation, the gas-liquid separator 35 during normal operation is used. Is the passage of superheated gas refrigerant It becomes. Therefore, the gas-liquid separator 35 serves to store the liquid-phase refrigerant by separating the gas-liquid refrigerant only during the defrosting operation.
- a liquid separator Resino
- the cycle refrigerant flow rate is controlled so that the outlet refrigerant of the first evaporator 15 has a predetermined degree of superheat during normal operation
- the gas-liquid separator 35 during normal operation is used. Is the passage of superheated gas refrigerant It becomes. Therefore
- the type of refrigerant was not specified.
- the refrigerant can be applied to a vapor compression refrigeration cycle such as chlorofluorocarbon-based, HC-based alternative chlorofluorocarbon, and carbon dioxide (C02).
- chlorofluorocarbon is a general term for organic compounds such as carbon, fluorine, chlorine, and hydrogen, and is widely used as a refrigerant.
- Fluorocarbon refrigerants include HCFC (Hide mouth / Fluoro mouth carbon) refrigerant, HFC (Hide mouth / Fluoro carbon) refrigerant, etc., which do not destroy the ozone layer. It is a refrigerant called alternative chlorofluorocarbon.
- the HC (hydrocarbon) refrigerant is a refrigerant substance that contains hydrogen and carbon and exists in nature.
- These HC refrigerants include R600a (isobutane) and R290 (propane).
- variable displacement compressor is used as the compressor 12, and the capacity of the variable displacement compressor 12 is controlled by the ECU 21 to control the refrigerant discharge capacity of the compressor 12.
- a fixed-capacity compressor is used as the compressor 12, and the operation of the fixed-capacity compressor 12 is controlled by an electromagnetic clutch, and the compression ratio is controlled by controlling the ratio of the on-off operation of the compressor 12.
- the refrigerant discharge capacity of the machine 12 may be controlled.
- the refrigerant discharge capacity can be controlled by controlling the rotational speed of the electric compressor 12.
- each evaporator is an indoor heat exchanger that is a use side heat exchanger.
- the configuration of the above-described embodiment can also be applied to a cycle in which outdoor heat exchange called non-use side heat exchange or heat source side heat exchanger is used as each of the above-described evaporators.
- a cycle called a heat pump such as a heating refrigeration cycle in which each evaporator is an outdoor heat exchanger and a condenser is an indoor heat exchanger, or a refrigeration cycle for hot water supply in which water is heated by a condenser.
- the above-described embodiment can be applied.
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- Defrosting Systems (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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CN2005800022688A CN1910410B (zh) | 2004-09-22 | 2005-09-22 | 喷射式制冷剂循环装置 |
DE112005000931.9T DE112005000931B4 (de) | 2004-09-22 | 2005-09-22 | Ejektorpumpen-Kühlkreisvorrichtung |
US10/581,088 US7757514B2 (en) | 2004-09-22 | 2005-09-22 | Ejector-type refrigerant cycle device |
US12/802,239 US8186180B2 (en) | 2004-09-22 | 2010-06-02 | Ejector-type refrigerant cycle device |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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JP2004-275152 | 2004-09-22 | ||
JP2004275152 | 2004-09-22 | ||
JP2005225189A JP4984453B2 (ja) | 2004-09-22 | 2005-08-03 | エジェクタ式冷凍サイクル |
JP2005-225189 | 2005-08-03 |
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Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/581,088 A-371-Of-International US7757514B2 (en) | 2004-09-22 | 2005-09-22 | Ejector-type refrigerant cycle device |
US12/802,239 Division US8186180B2 (en) | 2004-09-22 | 2010-06-02 | Ejector-type refrigerant cycle device |
Publications (1)
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WO2006033378A1 true WO2006033378A1 (ja) | 2006-03-30 |
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PCT/JP2005/017447 WO2006033378A1 (ja) | 2004-09-22 | 2005-09-22 | エジェクタ式冷凍サイクル装置 |
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Country | Link |
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US (2) | US7757514B2 (ja) |
JP (1) | JP4984453B2 (ja) |
KR (1) | KR100798395B1 (ja) |
CN (1) | CN1910410B (ja) |
DE (1) | DE112005000931B4 (ja) |
WO (1) | WO2006033378A1 (ja) |
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Also Published As
Publication number | Publication date |
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KR100798395B1 (ko) | 2008-01-28 |
CN1910410A (zh) | 2007-02-07 |
US20100257893A1 (en) | 2010-10-14 |
KR20070029132A (ko) | 2007-03-13 |
JP4984453B2 (ja) | 2012-07-25 |
JP2006118849A (ja) | 2006-05-11 |
DE112005000931B4 (de) | 2019-05-09 |
US8186180B2 (en) | 2012-05-29 |
DE112005000931T5 (de) | 2007-04-26 |
US20070119207A1 (en) | 2007-05-31 |
CN1910410B (zh) | 2010-05-05 |
US7757514B2 (en) | 2010-07-20 |
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