WO2018088033A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2018088033A1
WO2018088033A1 PCT/JP2017/033618 JP2017033618W WO2018088033A1 WO 2018088033 A1 WO2018088033 A1 WO 2018088033A1 JP 2017033618 W JP2017033618 W JP 2017033618W WO 2018088033 A1 WO2018088033 A1 WO 2018088033A1
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Prior art keywords
refrigerant
gas
compressor
pressure
air
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PCT/JP2017/033618
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English (en)
Japanese (ja)
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浩太郎 福田
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株式会社デンソー
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Publication of WO2018088033A1 publication Critical patent/WO2018088033A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle

Definitions

  • This disclosure relates to a refrigeration cycle apparatus including a two-stage compression type compressor.
  • Patent Document 1 describes a refrigeration cycle apparatus including a compressor, an indoor condenser, a gas-liquid separator, a high stage side expansion valve, a fixed throttle, an outdoor heat exchanger, a differential pressure valve, and the like.
  • the high-pressure refrigerant discharged from the compressor discharge port flows into the indoor condenser.
  • the refrigerant flowing into the indoor condenser radiates heat by exchanging heat with the air blown into the passenger compartment. Thereby, the air blown into the passenger compartment is heated.
  • the refrigerant that has flowed out of the indoor condenser is decompressed and expanded in an enthalpy manner until it becomes an intermediate-pressure refrigerant by a high-stage expansion valve that is in a throttled state.
  • the intermediate-pressure refrigerant decompressed by the high stage side expansion valve flows into the gas-liquid separation unit and is gas-liquid separated.
  • the liquid phase refrigerant separated in the gas-liquid separation unit is decompressed and expanded in an enthalpy manner until it becomes a low-pressure refrigerant in a fixed throttle.
  • the refrigerant decompressed and expanded by the fixed throttle flows into the outdoor heat exchanger and exchanges heat with the outside air to absorb heat.
  • the refrigerant flowing out of the outdoor heat exchanger is sucked from the suction port of the compressor and compressed again.
  • the pressure of the low-pressure refrigerant decompressed by the fixed throttle is guided to the differential pressure valve, so the differential pressure valve opens.
  • separated in the gas-liquid separation part flows in into the intermediate pressure port side of a compressor.
  • the intermediate-pressure gas-phase refrigerant that has flowed into the intermediate-pressure port joins with the refrigerant sucked from the suction port of the compressor and compressed by the low-stage compression mechanism, and is compressed by the high-stage compression mechanism.
  • the heat of the refrigerant discharged from the compressor by the indoor condenser can be dissipated to the air blown into the vehicle interior, and the heated air can be blown out into the vehicle interior.
  • heating of a vehicle interior is realizable.
  • the low-pressure refrigerant decompressed by the fixed throttle is sucked from the suction port of the compressor, and the intermediate-pressure refrigerant decompressed by the high stage side expansion valve is introduced into the intermediate pressure port of the compressor to increase the pressure.
  • a gas injection cycle (in other words, an economizer refrigeration cycle) that merges with the refrigerant in the process can be configured.
  • the refrigerant mixture having a low temperature can be sucked into the high-stage compression mechanism of the compressor, the compression efficiency of the high-stage compression mechanism can be improved, and the low-stage compression mechanism and the high-stage side can be improved.
  • the compression efficiency of both compression mechanisms can be improved.
  • the coefficient of performance (so-called COP) of the entire refrigeration cycle can be improved during the heating mode in which the difference between the high and low pressures of the cycle becomes large.
  • the gas-phase refrigerant separated by the gas-liquid separator passes from the intermediate pressure port to the compressor through the differential pressure valve. It flows in and flows back to the suction port side where the pressure is lower than the intermediate pressure port side.
  • the scroll of the compressor may reversely rotate and collide with the wall of the compression chamber irregularly, which may cause abnormal noise.
  • a refrigeration cycle apparatus is: A compressor that sucks and compresses refrigerant from the suction port and discharges it from the discharge port; A high-pressure side heat exchanger that exchanges heat between the refrigerant discharged from the discharge port; A high-stage decompression section that decompresses the refrigerant flowing out of the high-pressure side heat exchanger; A gas-liquid separator for separating the gas-liquid of the refrigerant decompressed in the high-stage decompression unit; The low-stage decompression unit that decompresses the liquid-phase refrigerant separated by the gas-liquid separation unit, the evaporator that evaporates the refrigerant decompressed by the low-stage decompression unit, and the gas-liquid separation unit A gas-phase refrigerant passage through which a gas-phase refrigerant flows; A differential pressure valve that opens and closes the gas-phase refrigerant passage by a pressure difference between the refrigerant decompressed by the low-stage
  • the compressor has an intermediate pressure port through which the refrigerant flowing through the gas-phase refrigerant passage flows, and the refrigerant flowing in from the intermediate pressure port is joined to the refrigerant in the compression process sucked from the suction port.
  • the low-stage decompression unit has an adjustment mechanism that adjusts the decompression amount of the refrigerant.
  • the refrigeration cycle apparatus performs a compressor stop delay control for stopping the compressor after controlling the low-stage decompression unit so that the decompression amount of the refrigerant decreases.
  • the pressure of the low-pressure refrigerant on the suction port side increases due to the decrease in the amount of decompression of the refrigerant in the low-stage decompression section, so the pressure difference between the intermediate pressure port and the suction port becomes small.
  • the gas-phase refrigerant separated by the gas-liquid separator can be prevented from flowing to the low pressure side of the compressor through the differential pressure valve. As a result, it is possible to prevent the compressor from rotating backward and generating vibrations and abnormal noise.
  • the heat pump cycle 10 is applied to the vehicle air conditioner 1 of a hybrid vehicle that obtains a driving force for traveling from an engine (in other words, an internal combustion engine) and a traveling electric motor.
  • the heat pump cycle 10 is a vapor compression refrigeration cycle.
  • the heat pump cycle 10 serves to cool or heat the air blown into the vehicle interior, which is the air-conditioning target space, in the vehicle air conditioner 1. Therefore, the air-conditioning target space of this embodiment is a vehicle interior, and the heat exchange target fluid of this embodiment is air blown into the vehicle interior.
  • the heat pump cycle 10 is configured to be able to switch between the cooling circuit shown in FIG. 1, the serial dehumidifying and heating mode shown in FIG. 1, the parallel dehumidifying and heating mode shown in FIG. 2, or the heating mode shown in FIG. 1 to 3, the flow of the refrigerant in each operation mode is indicated by solid arrows.
  • the cooling mode is a cooling operation mode in which the air blown into the passenger compartment is cooled to cool the passenger compartment.
  • the series dehumidification heating mode and the parallel dehumidification heating mode are dehumidification heating operation modes in which the air blown into the vehicle interior is dehumidified and then heated to dehumidify and heat the vehicle interior.
  • the heating mode is a heating operation mode in which air blown into the passenger compartment is heated to heat the passenger compartment.
  • the heat pump cycle 10 employs an HFC refrigerant (specifically, R134a) as a refrigerant, and constitutes a vapor compression subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant.
  • An HFO refrigerant for example, R1234yf
  • Refrigerating machine oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.
  • Compressor 11 of heat pump cycle 10 sucks in refrigerant, compresses it, and discharges it.
  • the compressor 11 is arrange
  • the compressor 11 houses two compression mechanisms, a low-stage compression mechanism and a high-stage compression mechanism, and an electric motor that rotationally drives both compression mechanisms in a housing that forms the outer shell. This is a two-stage booster type electric compressor configured.
  • the housing of the compressor 11 has a suction port 11a for sucking low-pressure refrigerant from the outside of the housing into the low-stage compression mechanism, and an intermediate-pressure refrigerant flows from the outside of the housing to the inside of the housing to compress from low pressure to high pressure.
  • An intermediate pressure port 11b for joining the refrigerant and a discharge port 11c for discharging the high-pressure refrigerant discharged from the high-stage compression mechanism to the outside of the housing are provided.
  • the intermediate pressure port 11b is connected to the refrigerant discharge port side of the low-stage compression mechanism (that is, the refrigerant suction port side of the high-stage compression mechanism).
  • Various types such as a scroll-type compression mechanism, a vane-type compression mechanism, and a rolling piston-type compression mechanism can be adopted as the low-stage side compression mechanism and the high-stage side compression mechanism.
  • the rotation speed of the electric motor of the compressor 11 is controlled by a control signal output from the control device 40.
  • the electric motor either an AC motor or a DC motor may be adopted.
  • the refrigerant discharge capacity of the compressor 11 is changed by controlling the rotational speed of the electric motor. Therefore, the electric motor is a discharge capacity changing unit of the compressor 11.
  • the compressor 11 in which two compression mechanisms are accommodated in one housing is adopted, but the type of the compressor is not limited to this. That is, if the intermediate pressure refrigerant can be introduced from the intermediate pressure port 11b and merged with the refrigerant in the compression process from low pressure to high pressure, one fixed capacity type compression mechanism and the compression mechanism are provided inside the housing.
  • An electric compressor configured to accommodate an electric motor that rotationally drives the motor may be used.
  • Two compressors are connected in series, and the suction port of the low-stage compression mechanism disposed on the low-stage side is defined as the suction port 11a, and the discharge port of the high-stage compression mechanism disposed on the high-stage side is the discharge port.
  • an intermediate pressure port 11b is provided at a connection portion that connects the discharge port of the low-stage compression mechanism and the suction port of the high-stage compression mechanism, and is provided by both the low-stage compression mechanism and the high-stage compression mechanism.
  • One two-stage booster compressor may be configured.
  • the refrigerant inlet side of the indoor condenser 12 is connected to the discharge port 11 c of the compressor 11.
  • the indoor condenser 12 is disposed in the air conditioning case 31 of the indoor air conditioning unit 30 of the vehicle air conditioner 1 and dissipates heat from the high-temperature and high-pressure refrigerant discharged from the high-stage compression mechanism of the compressor 11 (in other words, , An air heating heat exchanger that functions as a high pressure side heat exchanger and heats the air that has passed through the indoor evaporator 23.
  • the inlet side of the high stage side expansion valve 13 is connected to the refrigerant outlet side of the indoor condenser 12.
  • the high-stage expansion valve 13 is a high-stage decompression unit that decompresses the high-pressure refrigerant flowing out of the indoor condenser 12 until it becomes an intermediate-pressure refrigerant.
  • the high stage side expansion valve 13 is a first pressure reducing unit.
  • the high-stage side expansion valve 13 is an electrically variable type that includes a valve body that can change the throttle opening degree and an electric actuator that includes a stepping motor that changes the throttle opening degree of the valve body.
  • An aperture mechanism that includes a valve body that can change the throttle opening degree and an electric actuator that includes a stepping motor that changes the throttle opening degree of the valve body.
  • the high stage side expansion valve 13 may be configured so that the throttle opening is fully opened and the refrigerant decompression action is not exerted.
  • the operation of the high stage side expansion valve 13 is controlled by a control signal output from the control device 40.
  • a refrigerant inflow port 14 a of the gas-liquid separator 14 is connected to the outlet side of the high stage side expansion valve 13.
  • the gas-liquid separator 14 is a gas-liquid separation unit that separates the gas-liquid of the intermediate pressure refrigerant that has flowed out of the indoor condenser 12 and decompressed by the high-stage expansion valve 13.
  • the gas-liquid separator 14 is of a centrifugal separation type that separates the gas-liquid refrigerant by the action of centrifugal force.
  • the intermediate pressure port 11 b of the compressor 11 is connected to the gas phase refrigerant outflow port 14 b of the gas-liquid separator 14 via the intermediate pressure refrigerant passage 15.
  • a gas-phase refrigerant side on-off valve 16 is disposed in the intermediate pressure refrigerant passage 15.
  • the intermediate pressure refrigerant passage 15 is a gas phase refrigerant passage through which the gas phase refrigerant flowing out from the gas phase refrigerant outlet port 14b of the gas-liquid separator 14 flows.
  • the gas phase refrigerant side on-off valve 16 is a differential pressure valve that is displaced by a pressure difference between the refrigerant pressure in the pressure introduction passage 19 and the refrigerant pressure in the intermediate pressure refrigerant passage 15.
  • the refrigerant pressure on the inlet side of the outdoor heat exchanger 20 is guided to the gas-phase refrigerant side on-off valve 16 through the pressure introduction passage 19.
  • the liquid refrigerant side opening / closing valve 18a opens the fixed throttle bypass passage 18 and the refrigerant bypasses the fixed throttle 17 and is guided to the outdoor heat exchanger 20 side and the refrigerant is not decompressed by the fixed throttle 17, the pressure introduction passage 19 Since the pressure difference between the refrigerant pressure and the refrigerant pressure in the intermediate pressure refrigerant passage 15 becomes small, the gas phase refrigerant side on-off valve 16 closes the intermediate pressure refrigerant passage 15.
  • the gas-phase refrigerant side on / off valve 16 functions to switch the refrigerant flow path of the heat pump cycle 10 by opening and closing the intermediate pressure refrigerant passage 15. Accordingly, the gas-phase refrigerant side on-off valve 16 constitutes a refrigerant flow path switching unit that switches the refrigerant flow path of the refrigerant circulating in the cycle.
  • the inlet side of the fixed throttle 17 is connected to the liquid-phase refrigerant outlet port 14 c of the gas-liquid separator 14, and the refrigerant inlet side of the outdoor heat exchanger 20 is connected to the outlet side of the fixed throttle 17.
  • the fixed throttle 17 is a low-stage decompression unit that decompresses the liquid-phase refrigerant separated by the gas-liquid separator 14 until it becomes a low-pressure refrigerant.
  • a nozzle or an orifice having a fixed throttle opening can be employed as the fixed throttle 17, a nozzle or an orifice having a fixed throttle opening can be employed.
  • the area of the throttle passage is suddenly reduced or expanded rapidly, so that the refrigerant passing through the fixed throttle is changed with the change in the pressure difference between the upstream side and the downstream side (that is, the differential pressure between the inlet and outlet).
  • the flow rate and the dryness of the fixed throttle upstream refrigerant can be self-adjusted.
  • a fixed-throttle bypass passage 18 that guides the liquid-phase refrigerant separated by the gas-liquid separator 14 to the outdoor heat exchanger 20 side is bypassed at the liquid-phase refrigerant outlet port 14c of the gas-liquid separator 14. It is connected.
  • a liquid-phase refrigerant side opening / closing valve 18 a is disposed in the fixed throttle bypass passage 18.
  • the liquid-phase refrigerant side opening / closing valve 18 a is an electromagnetic valve that opens and closes the fixed throttle bypass passage 18, and its opening / closing operation is controlled by a control signal output from the control device 40.
  • the pressure loss that occurs when the refrigerant passes through the liquid-phase refrigerant side opening / closing valve 18 a is extremely small compared to the pressure loss that occurs when the refrigerant passes through the fixed throttle 17. Accordingly, the refrigerant flowing out of the indoor condenser 12 flows into the outdoor heat exchanger 20 via the fixed throttle bypass passage 18 side when the liquid phase refrigerant side opening / closing valve 18a is open, and the liquid phase refrigerant side opening / closing valve. When 18 a is closed, it flows into the outdoor heat exchanger 20 through the fixed throttle 17.
  • the liquid-phase refrigerant side on-off valve 18a can switch the refrigerant flow path of the heat pump cycle 10. Therefore, the liquid phase refrigerant side opening / closing valve 18a of the present embodiment, together with the gas phase refrigerant side opening / closing valve 16, constitutes a refrigerant channel switching unit that switches the refrigerant channel of the refrigerant circulating in the cycle.
  • a refrigerant circuit that connects the liquid phase refrigerant outflow port 14c outlet side of the gas-liquid separator 14 and the fixed throttle 17 inlet side, and the liquid phase refrigerant outflow port 14c outlet side and the fixed throttle bypass.
  • An electric three-way valve or the like that switches the refrigerant circuit connecting the inlet side of the passage 18 may be adopted.
  • the fixed throttle bypass passage 18 and the liquid-phase refrigerant side on-off valve 18a are adjustment mechanisms that adjust the amount of refrigerant reduced in the fixed throttle 17.
  • the refrigerant inlet side of the outdoor heat exchanger 20 is connected to the outlet side of the fixed throttle 17 and the fixed throttle bypass passage 18.
  • the outdoor heat exchanger 20 is disposed in the hood, and exchanges heat between the refrigerant circulating inside and the outside air blown from the blower fan 21.
  • the outdoor heat exchanger 20 functions as an evaporator that evaporates low-pressure refrigerant and exerts an endothermic action at least in the heating mode, and functions as a radiator that radiates heat from the high-pressure refrigerant in the cooling mode and the like. It is.
  • the refrigerant inlet side of the cooling expansion valve 22 as the second decompression unit is connected to the refrigerant outlet side of the outdoor heat exchanger 20.
  • the cooling expansion valve 22 depressurizes the refrigerant that flows out of the outdoor heat exchanger 20 and flows into the indoor evaporator 23 in the cooling operation mode or the like.
  • the basic configuration of the cooling expansion valve 22 is the same as that of the high-stage expansion valve 13, and its operation is controlled by a control signal output from the control device 40.
  • the refrigerant inlet side of the indoor evaporator 23 is connected to the outlet side of the cooling expansion valve 22.
  • the indoor evaporator 23 is disposed on the air flow upstream side of the indoor condenser 12 in the air conditioning case 31 of the indoor air conditioning unit 30, and evaporates the refrigerant that circulates in the cooling operation mode and the dehumidifying heating operation mode.
  • the heat exchanger functions as an evaporator (in other words, an air cooling heat exchanger) that cools the air blown into the vehicle interior by exerting an endothermic action.
  • the inlet side of the accumulator 24 is connected to the outlet side of the indoor evaporator 23.
  • the accumulator 24 is a low-pressure side gas-liquid separator that separates the gas-liquid refrigerant flowing into the accumulator 24 and stores excess refrigerant.
  • the suction port 11 a of the compressor 11 is connected to the gas phase refrigerant outlet of the accumulator 24. Therefore, the indoor evaporator 23 is connected so as to flow out to the suction port 11 a side of the compressor 11.
  • the low-pressure side bypass passage 25 that guides the refrigerant flowing out of the outdoor heat exchanger 20 to the inlet side of the accumulator 24 while bypassing the cooling expansion valve 22 and the indoor evaporator 23. Is connected.
  • a low pressure side bypass passage opening / closing valve 26 is arranged in the low pressure side bypass passage 25.
  • the low pressure side bypass passage opening / closing valve 26 is an electromagnetic valve that opens and closes the low pressure side bypass passage 25, and its opening / closing operation is controlled by a control voltage output from the control device 40. Further, the pressure loss that occurs when the refrigerant passes through the low pressure side bypass passage opening / closing valve 26 is extremely small compared to the pressure loss that occurs when the refrigerant passes through the cooling expansion valve 22.
  • the refrigerant flowing out of the outdoor heat exchanger 20 flows into the accumulator 24 through the low pressure side bypass passage 25 when the low pressure side bypass passage opening / closing valve 26 is open. At this time, the throttle opening degree of the cooling expansion valve 22 may be fully closed.
  • the low pressure side bypass passage opening / closing valve 26 when the low pressure side bypass passage opening / closing valve 26 is closed, it flows into the indoor evaporator 23 through the cooling expansion valve 22. Thereby, the low pressure side bypass passage opening / closing valve 26 can switch the refrigerant flow path of the heat pump cycle 10. Therefore, the low pressure side bypass passage opening / closing valve 26 of the present embodiment constitutes a refrigerant flow path switching unit that switches the refrigerant flow path of the refrigerant circulating in the cycle.
  • a constant pressure valve 27 is disposed on the outlet side of the indoor evaporator 23 and on the inlet side of the accumulator 24.
  • the constant pressure valve 27 is a constant pressure adjusting unit that maintains the refrigerant pressure at the outlet side of the indoor evaporator 23 at a predetermined pressure.
  • the high-pressure side bypass passage 28 passes the refrigerant in the range from the outlet side of the indoor condenser 12 to the inlet side of the high-stage expansion valve 13 from the outlet side of the outdoor heat exchanger 20 to the inlet side of the cooling expansion valve 22. It is a refrigerant passage leading to the range.
  • the high-pressure side bypass passage 28 is a refrigerant passage that guides the refrigerant flowing out of the indoor condenser 12 to the inlet side of the cooling expansion valve 22 by bypassing the high-stage side expansion valve 13 and the outdoor heat exchanger 20. .
  • the high pressure side bypass passage 28 is provided with a high pressure side bypass passage opening / closing valve 28a.
  • the high pressure side bypass passage opening / closing valve 28 a is an electromagnetic valve that opens and closes the high pressure side bypass passage 28, and its operation is controlled by a control signal output from the control device 40.
  • the high pressure side bypass passage opening / closing valve 28a functions to switch the cycle configuration (in other words, the refrigerant passage) by opening and closing the high pressure side bypass passage 28. Therefore, the high-pressure side bypass passage opening / closing valve 28a constitutes a refrigerant flow path switching unit that switches the refrigerant flow path of the refrigerant circulating in the cycle.
  • a check valve 29 is disposed on the outlet side of the outdoor heat exchanger 20.
  • the check valve 29 allows the refrigerant to flow from the outlet side of the outdoor heat exchanger 20 to the inlet side of the cooling expansion valve 22 and from the inlet side of the cooling expansion valve 22 to the outlet side of the outdoor heat exchanger 20. It is a backflow prevention part which prohibits the flow of the refrigerant
  • the check valve 29 can prevent the refrigerant flowing through the high-pressure side bypass passage 28 from flowing back to the outdoor heat exchanger 20 side.
  • the indoor air conditioning unit 30 is disposed inside the instrument panel at the foremost part of the vehicle interior, forms an outer shell of the indoor air conditioning unit 30, and forms an air passage for air blown into the vehicle interior in the interior. 31. And the air blower 32, the indoor condenser 12, the indoor evaporator 23, etc. are accommodated in this air passage.
  • Inside / outside air switching device 33 for switching between the inside air and the outside air is arranged on the most upstream side of the air flow of air conditioning case 31.
  • the inside / outside air switching device 33 continuously adjusts the opening area of the inside air introduction port for introducing the inside air into the air conditioning case 31 and the outside air introduction port for introducing the outside air by the inside / outside air switching door, so that the air volume of the inside air and the outside air are adjusted.
  • the air volume ratio with the air volume is continuously changed.
  • a blower 32 that blows the air sucked through the inside / outside air switching device 33 toward the vehicle interior is arranged on the downstream side of the air flow of the inside / outside air switching device 33.
  • the blower 32 is an electric blower that drives a centrifugal multiblade fan by an electric motor, and the number of rotations (in other words, the amount of blown air) is controlled by a control voltage output from the control device 40.
  • the indoor evaporator 23 and the indoor condenser 12 are arranged in the order of the indoor evaporator 23 ⁇ the indoor condenser 12 with respect to the flow of air blown into the vehicle interior.
  • the indoor evaporator 23 is disposed on the upstream side of the air flow with respect to the indoor condenser 12.
  • a heater core (not shown) is arranged between the indoor evaporator 23 and the indoor condenser 12.
  • the heater core is an auxiliary heating heat exchanger that auxiliary heats the air by exchanging heat between the engine coolant and the air that has passed through the indoor evaporator 23.
  • a bypass passage 35 is provided in the air conditioning case 31 to flow the air that has passed through the indoor evaporator 23, bypassing the heater core and the indoor condenser 12, and is downstream of the air flow of the indoor evaporator 23.
  • an air mix door 34 is disposed on the upstream side of the air flow of the heater core and the indoor condenser 12.
  • the air mix door 34 adjusts the air volume ratio between the air volume passing through the heater core and the indoor condenser 12 and the air volume passing through the bypass passage 35 in the air after passing through the indoor evaporator 23, thereby condensing the indoor air. It is a flow rate adjusting unit that adjusts the flow rate of air flowing into the condenser 12 (in other words, the air volume), and functions to adjust the heat exchange capacity of the indoor condenser 12.
  • an opening hole through which the air merged in the merge space 36 is blown out into the vehicle interior which is the space to be cooled is arranged.
  • a defroster opening hole 37a that blows conditioned air toward the inner side surface of the vehicle front window glass
  • a face opening hole 37b that blows conditioned air toward the upper body of the passenger in the passenger compartment
  • the foot opening hole 37c which blows air-conditioning wind toward is provided.
  • the air mix door 34 adjusts the air volume ratio between the air volume that passes through the indoor condenser 12 and the air volume that passes through the bypass passage 35, thereby adjusting the temperature of the air in the merging space 36.
  • the air mix door 34 is driven by a servo motor (not shown) whose operation is controlled by a control signal output from the control device 40.
  • the opening areas of the defroster door 38a and the face opening hole 37b for adjusting the opening area of the defroster opening hole 37a are adjusted.
  • a foot door 38c for adjusting the opening area of the face door 38b and the foot opening hole 37c is disposed.
  • the defroster door 38a, the face door 38b, and the foot door 38c constitute an air outlet mode switching unit that opens and closes the respective opening holes 37a to 37c and switches the air outlet mode. It is driven by a servo motor (not shown) whose operation is controlled by a control signal output from the control device 40.
  • the air flow downstream side of the defroster opening hole 37a, the face opening hole 37b, and the foot opening hole 37c is respectively connected to a face air outlet, a foot air outlet, and a defroster air outlet provided in the vehicle interior via ducts that form air passages. Connected to the exit.
  • the face opening hole 37b is fully opened and air is blown out from the face air outlet toward the upper body of the passenger in the vehicle. Both the face opening hole 37b and the foot opening hole 37c are opened.
  • a bi-level mode that blows air toward the upper body and feet of an indoor occupant, a foot mode in which the foot opening hole 37c is fully opened and the defroster opening hole 37a is opened by a small opening, and air is mainly blown out from the foot outlet. is there.
  • the control device 40 is composed of a well-known microcomputer including a CPU, a ROM, a RAM and the like and its peripheral circuits, performs various calculations and processing based on an air conditioning control program stored in the ROM, and is connected to the output side.
  • Various air conditioning control devices specifically, compressor 11, high stage side expansion valve 13, liquid phase refrigerant side opening / closing valve 18a, blower fan 21, cooling expansion valve 22, low pressure side bypass passage opening / closing valve 26, high pressure side The operation of the bypass passage opening / closing valve 28a, the blower 32 and the like is controlled.
  • an inside air sensor that detects the temperature inside the vehicle
  • an outside air sensor that detects the outside air temperature
  • a solar radiation sensor that detects the amount of solar radiation inside the vehicle
  • the temperature of air blown from the indoor evaporator 23 in other words An evaporator temperature sensor for detecting the evaporator temperature
  • a discharge pressure sensor for detecting the high-pressure refrigerant pressure discharged from the compressor 11
  • a condenser temperature sensor for detecting the temperature of the refrigerant flowing out of the indoor condenser 12
  • Various air-conditioning control sensor groups 41 such as a suction pressure sensor for detecting the suction refrigerant pressure sucked in are connected.
  • the input side of the control device 40 is connected to an operation panel (not shown) disposed near the instrument panel in the front of the passenger compartment, and operation signals from various air conditioning operation switches provided on the operation panel are input.
  • various air conditioning operation switches provided on the operation panel include an operation switch of the vehicle air conditioner 1, a vehicle interior temperature setting switch for setting the vehicle interior temperature, a cooling operation mode, a dehumidifying heating operation mode, and a heating operation mode.
  • a mode selection switch or the like for selecting is provided.
  • the control device 40 is configured such that a control unit that controls the operation of various air-conditioning control devices connected to the output side thereof is integrally configured. However, the control device 40 is configured to control the operation of each control target device (specifically, Hardware and software) constitute a control unit that controls the operation of each control target device.
  • each control target device specifically, Hardware and software
  • a configuration (specifically, hardware and software) that controls the operation of the electric motor of the compressor 11 constitutes the discharge capacity control unit.
  • the configuration (specifically, hardware and software) that controls the operation of the liquid-phase refrigerant side opening / closing valve 18a, the low pressure side bypass passage opening / closing valve 26, and the high pressure side bypass passage opening / closing valve 28a is refrigerant circuit control.
  • the discharge capacity control unit, the refrigerant circuit control unit, and the like may be configured as separate control devices for the control device 40.
  • the operation of the vehicle air conditioner 1 of the present embodiment having the above configuration will be described.
  • switching to the cooling operation mode for cooling the vehicle interior, the heating operation mode for heating the vehicle interior, and the dehumidification heating mode for heating while dehumidifying the vehicle interior is possible. it can.
  • This air conditioning control program is executed when the auto switch of the operation panel is turned on (in other words, turned on).
  • TAO Kset ⁇ Tset ⁇ Kr ⁇ Tr ⁇ Kam ⁇ Tam ⁇ Ks ⁇ As + C (F1)
  • Tset is the vehicle interior set temperature set by the temperature setting switch
  • Tr is the vehicle interior temperature detected by the internal air sensor (in other words, the internal air temperature)
  • Tam is the external air temperature detected by the external air sensor
  • As is solar radiation. The amount of solar radiation detected by the sensor.
  • Kset, Kr, Kam, Ks are control gains
  • C is a correction constant.
  • the operation in the cooling mode is executed. Also, when the target switch temperature TAO is equal to or higher than the cooling reference temperature ⁇ and the outside air temperature Tam is higher than the predetermined dehumidifying heating reference temperature ⁇ with the cooling switch on the operation panel turned on. The operation in the series dehumidifying and heating mode is executed.
  • the target switch temperature TAO is equal to or higher than the cooling reference temperature ⁇ and the outside air temperature Tam is equal to or lower than the dehumidifying heating reference temperature ⁇ in a state where the cooling switch of the operation panel is turned on
  • the parallel operation is performed. Run in dehumidifying heating mode. When the cooling switch is not turned on, the operation in the heating mode is executed.
  • the cooling mode is executed when the outside air temperature is relatively high, mainly in summer.
  • the series dehumidifying heating mode is executed mainly in spring or autumn.
  • the parallel dehumidifying heating mode is executed when the air needs to be heated with a higher heating capacity than the serial dehumidifying heating mode, mainly in early spring or late autumn. Furthermore, the heating mode can be executed mainly at low outdoor temperatures in winter.
  • (A) Cooling mode In the cooling mode, the control device 40 opens the high stage side expansion valve 13, opens the liquid phase refrigerant side opening / closing valve 18 a, and opens the cooling expansion valve 22 with a pressure reducing action. Further, the low pressure side bypass passage opening / closing valve 26 is closed, and the high pressure side bypass passage opening / closing valve 28a is closed.
  • the refrigerant circulates in the order of the compressor 11 ⁇ the outdoor heat exchanger 20 ⁇ the cooling expansion valve 22 ⁇ the indoor evaporator 23 ⁇ the constant pressure valve 27 ⁇ the accumulator 24 ⁇ the compressor 11.
  • a vapor compression refrigeration cycle is configured.
  • the control device 40 controls the operation of the compressor 11 so that the air blown out from the indoor evaporator 23 becomes the target evaporator temperature TEO.
  • the target evaporator temperature TEO is determined so as to decrease as the target outlet temperature TAO decreases.
  • the target evaporator temperature TEO is determined within a range in which frost formation of the indoor evaporator 23 can be suppressed.
  • control device 40 controls the operation of the cooling expansion valve 22 so that the COP of the cycle approaches the maximum value based on the pressure of the refrigerant flowing into the cooling expansion valve 22. Further, the control device 40 displaces the air mix door 34 so that the ventilation path on the indoor condenser 12 side is fully closed.
  • the outdoor heat exchanger 20 functions as a radiator and the indoor evaporator 23 functions as an evaporator.
  • the heat absorbed from the air when the refrigerant evaporates in the indoor evaporator 23 is radiated to the outside air in the outdoor heat exchanger 20. Thereby, air can be cooled.
  • the vehicle interior can be cooled by blowing the air cooled by the indoor evaporator 23 into the vehicle interior.
  • (B) Series dehumidifying and heating mode In the series dehumidifying and heating mode, the control device 40 sets the high-stage expansion valve 13 to a throttled state that exerts a pressure reducing action, sets the liquid-phase refrigerant side on-off valve 18a to a fully open state, and sets the cooling expansion valve 22 is set to a throttle state that exerts a pressure reducing action, the low pressure side bypass passage opening / closing valve 26 is closed, and the high pressure side bypass passage opening / closing valve 28a is closed.
  • the compressor 11 in the series dehumidifying and heating mode, the compressor 11 ⁇ the indoor condenser 12 ⁇ the high stage side expansion valve 13 ⁇ the outdoor heat exchanger 20 ⁇ the cooling expansion valve 22 ⁇ the indoor evaporator 23 ⁇ the constant.
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the pressure valve 27 ⁇ accumulator 24 ⁇ compressor 11 is configured. That is, a refrigeration cycle in which the outdoor heat exchanger 20 and the indoor evaporator 23 are connected in series to the refrigerant flow is configured.
  • the control device 40 controls the operation of the compressor 11 as in the cooling mode. Further, the control device 40 controls the operations of the high-stage expansion valve 13 and the cooling expansion valve 22 based on the pressure of the refrigerant flowing into the high-stage expansion valve 13 so that the COP of the cycle approaches the maximum value. . At this time, the control device 40 decreases the throttle opening of the high stage side expansion valve 13 and increases the throttle opening of the cooling expansion valve 22 as the target blowing temperature TAO increases. In addition, the control device 40 displaces the air mix door 34 so that the ventilation path on the indoor condenser 12 side is fully opened.
  • the indoor condenser 12 is caused to function as a radiator, and the indoor evaporator 23 is caused to function as an evaporator. Furthermore, when the saturation temperature of the refrigerant in the outdoor heat exchanger 20 is higher than the outside air, the outdoor heat exchanger 20 is caused to function as a radiator, and the saturation temperature of the refrigerant in the outdoor heat exchanger 20 is lower than the outside air. Makes the outdoor heat exchanger 20 function as an evaporator.
  • the saturation temperature of the refrigerant in the outdoor heat exchanger 20 is higher than the outside air, the saturation temperature of the refrigerant in the outdoor heat exchanger 20 is lowered as the target blowing temperature TAO increases, and the outdoor heat exchanger 20 The amount of heat released from the refrigerant at 20 can be reduced. Thereby, the thermal radiation amount of the refrigerant
  • the saturation temperature of the refrigerant in the outdoor heat exchanger 20 is lower than the outside air, the saturation temperature of the refrigerant in the outdoor heat exchanger 20 is decreased as the target blowing temperature TAO rises, and the outdoor heat exchanger 20.
  • the amount of heat absorbed by the refrigerant can be increased.
  • coolant in the indoor condenser 12 can be increased, and a heating capability can be improved.
  • the air that has been cooled and dehumidified by the indoor evaporator 23 is reheated by the indoor condenser 12 and blown out into the vehicle interior, thereby performing dehumidification heating in the vehicle interior.
  • the heating capacity of the air in the indoor condenser 12 can be adjusted by adjusting the throttle opening degree of the high stage side expansion valve 13 and the cooling expansion valve 22.
  • (C) Parallel dehumidifying and heating mode In the parallel dehumidifying and heating mode, the control device 40 sets the high-stage side expansion valve 13 to a throttled state that exerts a pressure reducing action, sets the liquid-phase refrigerant side on-off valve 18a to a fully open state, and sets the cooling expansion valve. 22 is set to a throttle state that exerts a pressure reducing action, the low pressure side bypass passage opening / closing valve 26 is fully opened, and the high pressure side bypass passage opening / closing valve 28a is fully opened.
  • the refrigerant circulates in the order of the compressor 11 ⁇ the indoor condenser 12 ⁇ the high stage side expansion valve 13 ⁇ the outdoor heat exchanger 20 ⁇ the accumulator 24 ⁇ the compressor 11.
  • a vapor compression refrigeration cycle is formed in which the refrigerant circulates in the order of the compressor 11 ⁇ the indoor condenser 12 ⁇ the cooling expansion valve 22 ⁇ the indoor evaporator 23 ⁇ the constant pressure valve 27 ⁇ the accumulator 24 ⁇ the compressor 11. That is, a refrigeration cycle in which the outdoor heat exchanger 20 and the indoor evaporator 23 are connected in parallel to the refrigerant flow is configured.
  • the control device 40 controls the operation of the compressor 11 as in the cooling mode. Further, the control device 40 controls the operations of the high-stage expansion valve 13 and the cooling expansion valve 22 based on the pressure of the refrigerant flowing into the high-stage expansion valve 13 so that the COP of the cycle approaches the maximum value. . At this time, the control device 40 decreases the throttle opening of the high stage side expansion valve 13 and increases the throttle opening of the cooling expansion valve 22 as the target blowing temperature TAO increases. In addition, the control device 40 displaces the air mix door 34 so that the ventilation path on the indoor condenser 12 side is fully opened.
  • the indoor condenser 12 functions as a radiator, and the outdoor heat exchanger 20 and the indoor evaporator 23 function as an evaporator.
  • coolant saturation temperature of the outdoor heat exchanger 20 can be lowered
  • coolant in the indoor condenser 20 can be increased, and a heating capability can be improved.
  • the air that has been cooled and dehumidified by the indoor evaporator 23 is reheated by the indoor condenser 12 and blown out into the vehicle interior, thereby performing dehumidification heating in the vehicle interior.
  • the refrigerant saturation temperature (in other words, the evaporation temperature) in the outdoor heat exchanger 20 can be made lower than the refrigerant saturation temperature (in other words, the evaporation temperature) in the indoor evaporator 23.
  • the air heating capacity can be increased.
  • (D) Heating Mode In the heating mode, the control device 40 sets the high stage side expansion valve 13 to a throttle state that exerts a pressure reducing action, sets the liquid phase refrigerant side on-off valve 18a to a closed state, and closes the cooling expansion valve 22. Further, the low pressure side bypass passage opening / closing valve 26 is fully opened, and the high pressure side bypass passage opening / closing valve 28a is closed.
  • the refrigerant circulates in the order of the outdoor heat exchanger 20 ⁇ the suction port 11 a of the compressor 11, and the refrigerant circulates in the order of the gas-phase refrigerant outflow port 14 b of the gas-liquid separator 14 ⁇ the intermediate pressure port 11 b of the compressor 11.
  • a so-called gas injection cycle is configured.
  • the control device 40 controls the operation of the compressor 11 so that the refrigerant flowing into the indoor condenser 12 becomes the target condenser temperature TCO.
  • the target condenser temperature TCO is determined so as to increase as the target blowing temperature TAO increases.
  • the control device 40 controls the operation of the high stage side expansion valve 13 so that the COP of the cycle approaches the maximum value based on the pressure of the refrigerant flowing into the high stage side expansion valve 13.
  • the control device 40 displaces the air mix door 34 so that the ventilation path on the indoor condenser 12 side is fully opened.
  • the indoor condenser 12 functions as a radiator and the outdoor heat exchanger 20 functions as an evaporator. Then, the heat absorbed from the outside air when the refrigerant evaporates in the outdoor heat exchanger 20 is radiated to the air in the indoor condenser 12. Thereby, air can be heated.
  • the vehicle interior can be heated by blowing the air heated by the indoor condenser 12 into the vehicle interior.
  • engine waste heat may be insufficient as a heating heat source. Therefore, it is extremely effective that a high COP can be exhibited regardless of the heating load in the heating operation mode as in the heat pump cycle 10 of the present embodiment.
  • the gas-phase refrigerant side on-off valve 16 since a differential pressure valve that is displaced by a pressure difference is employed as the gas-phase refrigerant side on-off valve 16, there is no need to provide an electromagnetic mechanism or the like for displacing the gas-phase refrigerant side on-off valve 16.
  • the gas phase refrigerant side on / off valve 16 can be easily displaced to open and close the intermediate pressure refrigerant passage 15.
  • the indoor evaporator 23 can be switched to a cycle configuration that functions as an evaporator for evaporating the refrigerant.
  • the indoor condenser 12 functions as a radiator that radiates the refrigerant, and the outdoor heat exchanger 20 evaporates the refrigerant. It is possible to easily configure a heat pump cycle configured to be switchable to a cycle configuration as a gas injection cycle that functions as a gas injection cycle.
  • Control device 40 performs compressor stop delay control for delaying stop of compressor 11 when it is determined to stop operation of heat pump cycle 10 in the heating mode.
  • the case where it is determined to stop the operation of the heat pump cycle 10 is, for example, a case where the air conditioning stop switch on the operation panel is pressed, or a case where the ignition switch of the vehicle is turned off.
  • the control device 40 when it is determined that the operation of the heat pump cycle 10 is stopped in the heating mode, the control device 40 first opens the liquid-phase refrigerant side on-off valve 18a. .
  • the liquid-phase refrigerant separated by the gas-liquid separator 14 bypasses the fixed throttle 17, flows through the fixed throttle bypass passage 18, and flows to the outdoor heat exchanger 20, so that the refrigerant pressure in the pressure introduction passage 19 increases.
  • the differential pressure between the refrigerant pressure in the intermediate pressure refrigerant passage 15 and the refrigerant pressure in the pressure introduction passage 19 is reduced.
  • the opening degree of the gas-phase refrigerant side opening / closing valve 16 is reduced.
  • the compressor 11 is stopped after a predetermined time has elapsed since the liquid-phase refrigerant side on-off valve 18a is opened. Thereby, even if the compressor 11 is stopped, the gas-phase refrigerant separated by the gas-liquid separator 14 passes through the gas-phase refrigerant-side on-off valve 16 and flows into the compressor 11 from the intermediate pressure port 11b, and the suction port 11a. Backflowing to the side can be suppressed.
  • the predetermined time is 600 ms. Since the differential pressure between the refrigerant pressure in the intermediate pressure refrigerant passage 15 and the refrigerant pressure in the pressure introduction passage 19 becomes smaller as the predetermined time is longer, the reverse flow of the refrigerant in the compressor 11 can be further suppressed.
  • the control device 40 has an abnormality in the compressor 11 during the compressor stop delay control (specifically, from when the liquid-phase refrigerant side on-off valve 18a is opened until a predetermined time elapses). In such a case, the compressor 11 is stopped urgently. For example, when the drive voltage of the compressor 11 is out of the normal range, it is determined that an abnormality has occurred in the compressor 11.
  • a safety function can be provided against delaying the stop of the compressor 11. For example, when the air conditioning stop switch on the operation panel is pressed during maintenance or the ignition switch of the vehicle is turned off, the compressor 11 may be mistakenly stopped and may touch the compressor 11 or its peripheral devices. Therefore, in such a case, safety can be ensured by urgently stopping the compressor 11.
  • the control device 40 performs compressor stop delay control when it is determined to stop the compressor 11. Specifically, in the compressor stop delay control, the control device 40 stops the compressor 11 after controlling the liquid-phase refrigerant side on-off valve 18a so that the amount of decompression of the refrigerant decreases. For example, in the compressor stop delay control, the control device 40 stops the compressor 11 when a predetermined time elapses after controlling the liquid-phase refrigerant side opening / closing valve 18a so that the amount of decompression of the refrigerant decreases.
  • the gas-phase refrigerant separated by the gas-liquid separator 14 can be prevented from flowing through the differential pressure valve 16 to the low pressure side of the compressor 11. As a result, it is possible to prevent the compressor 11 from rotating backward and generating vibrations and abnormal noise.
  • control device 40 causes the compressor 11 to stop urgently if an abnormality occurs in the compressor 11 during the compressor stop delay control. According to this, a safety function can be provided against delaying the stop of the compressor 11.
  • the heat pump cycle 10 is used for vehicle travel in this embodiment, for example. You may apply to the vehicle air conditioner 1 of the electric vehicle which obtains the driving force for vehicle travel from an electric motor.
  • the heat pump cycle 10 may be applied to a stationary air conditioner or the like.
  • the gas-liquid separator 14, the gas-phase refrigerant side on-off valve 16, the fixed throttle 17, the fixed throttling bypass passage 18, the liquid-phase refrigerant side on-off valve 18 a, and the pressure introduction passage 19 are integrally configured.
  • the integrated valve may be used.
  • This integrated valve is an integral part of the components required to make the heat pump cycle 10 function as a gas injection cycle, and further, a refrigerant circuit switching unit that switches a refrigerant circuit of refrigerant circulating in the cycle It fulfills the function as.
  • each operation mode is switched by executing an air conditioning control program
  • switching between each operation mode is not limited to this.
  • each operation mode may be switched on the basis of the target blowing temperature TAO and the outside air temperature Tam with reference to a control map stored in advance in the control device.
  • an operation mode setting switch for setting each operation mode is provided on the operation panel, and the cooling mode, the series dehumidifying heating mode, the parallel dehumidifying heating mode, and the heating mode are switched according to an operation signal of the operation mode setting switch. Also good.
  • the compressor 11 is stopped after a predetermined time has elapsed since the liquid-phase refrigerant side opening / closing valve 18a is opened, but the liquid-phase refrigerant side opening / closing valve 18a is opened.
  • the compressor 11 may be stopped when the differential pressure between the refrigerant pressure in the intermediate pressure refrigerant passage 15 and the refrigerant pressure in the pressure introduction flow path 19 becomes smaller than a threshold value.
  • the intermediate pressure refrigerant passage 15 forms a gas phase refrigerant passage through which the gas phase refrigerant separated by the gas-liquid separator 14 flows.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne un dispositif à cycle de réfrigération comprenant: un séparateur gaz-liquide (14) pour séparer un gaz et un réfrigérant liquide décompressés dans une unité de décompression côté étage supérieur; des unités de décompression côté étage inférieur (17, 18, 18a) pour décompresser le réfrigérant dans une phase liquide séparée par le séparateur gaz-liquide; un évaporateur (20) pour évaporer le réfrigérant décomprimé dans les unités de décompression côté étage inférieur; un trajet de réfrigérant en phase gazeuse (15) à travers lequel s'écoule le réfrigérant dans une phase gazeuse séparée par le séparateur gaz-liquide; et une soupape de pression différentielle (16) qui ouvre/ferme le trajet de réfrigérant en phase gazeuse à l'aide de la différence de pression entre le réfrigérant décomprimé par les unités de décompression côté étage inférieur et le réfrigérant s'écoulant à travers le trajet de réfrigérant en phase gazeuse. Les unités de décompression côté étage inférieur comprennent des mécanismes de réglage (18, 18a) pour ajuster la quantité de décompression du réfrigérant. Le dispositif à cycle de réfrigération est également pourvu d'un dispositif de commande (40) qui, lorsqu'il est déterminé qu'un compresseur doit être arrêté, commande les unités de décompression côté étage inférieur de façon à réduire la quantité de décompression du réfrigérant et réalise ensuite une commande de retardement d'arrêt de compresseur pour arrêter le compresseur.
PCT/JP2017/033618 2016-11-09 2017-09-18 Dispositif à cycle de réfrigération WO2018088033A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016218792A JP2018077004A (ja) 2016-11-09 2016-11-09 冷凍サイクル装置
JP2016-218792 2016-11-09

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WO2018088033A1 true WO2018088033A1 (fr) 2018-05-17

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11117445B2 (en) 2016-11-25 2021-09-14 Denso Corporation Vehicle air conditioning device

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002130850A (ja) * 2000-10-26 2002-05-09 Hitachi Ltd 冷凍装置
JP2013092355A (ja) * 2011-10-05 2013-05-16 Denso Corp 統合弁およびヒートポンプサイクル

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002130850A (ja) * 2000-10-26 2002-05-09 Hitachi Ltd 冷凍装置
JP2013092355A (ja) * 2011-10-05 2013-05-16 Denso Corp 統合弁およびヒートポンプサイクル

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11117445B2 (en) 2016-11-25 2021-09-14 Denso Corporation Vehicle air conditioning device

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