JP2013189179A - Vehicle air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicle air conditioner configured to prevent a reduction in the amount of refrigerant to be ejected from a compressor under a low outside temperature condition, to obtain required heating performance during heating operation, and to remove moisture without reducing the heating performance during dehumidified heating operation.SOLUTION: A vehicle air conditioner includes: a bypass circuit 31 (refrigerant passages 20l, 20m) for allowing a part of liquid refrigerant flowing from a receiver tank 30 to be sucked in a part where refrigerant being compressed in a compressor 21 passes, during heating operation, or dehumidified heating operation; a second inside heat-exchanger expansion valve 29 for decompressing the refrigerant passing through the bypass circuit 31; and a second inside heat exchanger 25 that exchanges heat between the gas-liquid two-phase refrigerant passing through the bypass circuit 31 and the other liquid refrigerant flowing from the receiver tank 30 by decompression by means of the second inside heat-exchanger expansion valve 29.

Description

  The present invention relates to a vehicle air conditioner applicable to, for example, an electric vehicle.

  Conventionally, in this type of vehicle air conditioner, a compressor that compresses and discharges a refrigerant, a radiator that dissipates the refrigerant, a heat absorber that absorbs heat from the refrigerant, and an outdoor heat exchanger that dissipates or absorbs heat from the refrigerant, Are known (for example, see Patent Document 1).

  In the vehicle air conditioner, the refrigerant discharged from the compressor is caused to flow into the radiator to dissipate heat, and the refrigerant that has circulated through the radiator is caused to flow into the outdoor heat exchanger via the first expansion valve to absorb heat. The heating operation is performed by causing the compressor to suck the refrigerant that has passed through the heat exchanger.

  Further, in the vehicle air conditioner, the refrigerant discharged from the compressor is caused to flow into the radiator to dissipate heat, and a part of the refrigerant flowing through the radiator is caused to flow into the outdoor heat exchanger via the first expansion valve. Dehumidification heating is performed by allowing the other refrigerant flowing through the radiator to flow into the heat absorber through the second expansion valve to absorb the heat and sucking the refrigerant flowing through the outdoor heat exchanger and the heat absorber into the compressor. There is something to drive.

JP 2000-25446 A

  In the vehicle air conditioner, when a heating operation or a dehumidifying heating operation is performed in an environment where the outside air temperature is low (for example, below 10 ° C. below zero), the refrigerant flowing through the outdoor heat exchanger hardly absorbs heat from the outside air, There is a case where the heat absorption amount in the outdoor heat exchanger is insufficient. In the vehicle air conditioner, if the compressor is operated with insufficient heat absorption in the outdoor heat exchanger, the amount of refrigerant circulating in the refrigerant circuit decreases and the amount of heat released from the radiator decreases, which is necessary. It may be difficult to obtain a sufficient heating capacity.

  The object of the present invention is to prevent a decrease in the refrigerant discharge amount from the compressor in an environment of low outside air temperature, to obtain the heating capacity necessary during the heating operation, and to improve the heating capacity during the dehumidifying heating operation. An object of the present invention is to provide a vehicle air conditioner that can be dehumidified without being lowered.

  In order to achieve the above object, the present invention provides a compressor that compresses and discharges a refrigerant, a radiator that radiates heat from the refrigerant, a heat absorber that absorbs heat from the refrigerant, and an outdoor heat exchanger that radiates or absorbs heat from the refrigerant. The refrigerant that flows out of the radiator is stored and separated into gas and liquid, and the receiver tank that allows the liquid refrigerant to flow out, and the refrigerant discharged by the compressor flows into the radiator to dissipate the heat and circulates the radiator The refrigerant flowing into the receiver tank flows into the outdoor heat exchanger via the first expansion valve to absorb the heat, and the refrigerant flowing through the outdoor heat exchanger is sucked into the compressor. The refrigerant discharged from the compressor and the refrigerant circuit for heating flow into the radiator to dissipate heat, the refrigerant flowing through the radiator flows into the receiver tank, and a part of the liquid refrigerant flowing out of the receiver tank is first expanded. The refrigerant flows into the outdoor heat exchanger through the valve to absorb heat, and the other liquid refrigerant flowing out of the receiver tank flows into the heat absorber through the second expansion valve to absorb heat, and the outdoor heat exchanger and heat absorber are In the dehumidifying and heating refrigerant circuit that causes the refrigerant to be sucked into the compressor, and in the heating refrigerant circuit and the dehumidifying and heating refrigerant circuit, the refrigerant in the middle of compression of the compressor flows through a part of the liquid refrigerant flowing out from the receiver tank. A bypass circuit to be sucked into the part, a third expansion valve that depressurizes the refrigerant flowing through the bypass circuit, a refrigerant that flows through the bypass circuit depressurized by the third expansion valve, and other liquid refrigerant that has flowed out of the receiver tank An internal heat exchanger to be replaced.

  As a result, a part of the liquid refrigerant flowing out from the receiver tank is decompressed by the third expansion valve and sucked into the portion where the refrigerant in the middle of compression of the compressor flows, thereby increasing the refrigerant discharge amount of the compressor. Thus, it is possible to increase the heat radiation amount in the radiator.

  In order to achieve the above object, the present invention provides a compressor that compresses and discharges a refrigerant, a radiator that dissipates heat from the refrigerant, a heat absorber that absorbs heat from the refrigerant, and an outdoor heat exchange that dissipates or absorbs heat from the refrigerant. The refrigerant discharged from the compressor and the compressor flows into the radiator to dissipate heat, and the refrigerant flowing through the radiator flows into the outdoor heat exchanger via the first expansion valve to absorb heat, and flows through the outdoor heat exchanger Refrigerant circuit for heating that causes the refrigerant to be sucked into the compressor, and the refrigerant discharged from the compressor to flow into the radiator to dissipate heat, and a part of the refrigerant that has circulated through the radiator passes through the first expansion valve for outdoor heat exchange The other refrigerant flowing through the radiator is absorbed by the refrigerant and flows through the second expansion valve into the heat absorber to absorb the heat, and the refrigerant flowing through the outdoor heat exchanger and the heat absorber is sucked into the compressor. Dehumidifying and heating refrigerant circuit, heating refrigerant circuit and dehumidification A bypass circuit that sucks a portion of the refrigerant that has flowed out of the radiator into a portion through which the refrigerant that is being compressed flows, a third expansion valve that depressurizes the refrigerant flowing through the bypass circuit, A refrigerant flow path in which the refrigerant flowing through the bypass circuit decompressed by the expansion valve and the internal heat exchanger that exchanges heat between the refrigerant flowing out of the radiator and the refrigerant flowing out of the radiator of the internal heat exchanger flows Is provided with a receiver tank section that stores the refrigerant and separates it into a gas and a liquid and allows the liquid refrigerant to flow out.

  As a result, a part of the liquid refrigerant flowing out from the receiver tank part of the internal heat exchanger is decompressed by the third expansion valve, and is sucked into the part where the refrigerant in the middle of the compression flows. It becomes possible to increase the heat radiation amount in the radiator by increasing the refrigerant discharge amount.

  According to the present invention, by increasing the refrigerant discharge amount of the compressor, the heat radiation amount in the radiator can be increased, so that the heating capability can be improved during the heating operation, and the heating is performed during the dehumidifying heating operation. Dehumidification is possible without reducing the capacity. Further, by adjusting the degree of superheat of the refrigerant sucked in the compressor, the refrigerant sucked into the compressor can be reliably made into a gas refrigerant, and damage due to liquid compression of the compressor can be avoided. Furthermore, the heating capacity does not require complicated control, and can be controlled only by adjusting the refrigerant flow rate sucked into the compressor via the bypass circuit. Further, since the receiver function is provided on the downstream side of the radiator in the refrigerant flow direction, the refrigerant flow rate in the refrigerant circuit can be easily adjusted.

It is a schematic block diagram of the vehicle air conditioner which shows 1st Embodiment of this invention. It is a schematic block diagram of the air conditioning apparatus for vehicles which shows a cooling operation and a dehumidification cooling operation. It is a schematic block diagram of the vehicle air conditioner which shows heating operation. It is a schematic block diagram of the vehicle air conditioner which shows 1st dehumidification heating operation. It is a schematic block diagram of the air conditioning apparatus for vehicles which shows 2nd dehumidification heating operation. It is a schematic block diagram of the vehicle air conditioner which shows the state which open | released the expansion valve for 2nd internal heat exchangers during heating operation. It is a schematic block diagram of the vehicle air conditioner which shows 2nd Embodiment of this invention. It is a schematic block diagram of a 2nd internal heat exchanger. It is a schematic block diagram of the vehicle air conditioner which shows the state which open | released the expansion valve for 2nd internal heat exchangers during heating operation. It is a schematic block diagram of the vehicle air conditioner which shows 3rd Embodiment of this invention. It is a schematic block diagram of the vehicle air conditioning apparatus which shows the other example of the attachment position of an electric heater. It is a schematic block diagram of the vehicle air conditioner which shows 4th Embodiment of this invention. It is a schematic block diagram of the air conditioning apparatus for vehicles which shows the other example of this invention. It is a schematic block diagram of the air conditioning apparatus for vehicles which shows the other example of this invention.

  1 to 6 show a first embodiment of the present invention.

  As shown in FIG. 1, the vehicle air conditioner of the present invention includes an air conditioning unit 10 provided in a vehicle interior, and a refrigerant circuit 20 configured across the vehicle interior and the exterior of the vehicle interior.

  The air conditioning unit 10 has an air flow passage 11 for circulating air supplied into the vehicle interior. On one end side of the air flow passage 11, an outside air intake port 11 a for allowing the air outside the vehicle interior to flow into the air flow passage 11, an inside air intake port 11 b for allowing the air inside the vehicle interior to flow into the air flow passage 11, Is provided. Further, on the other end side of the air flow passage 11, a foot outlet 11 c that blows out air flowing through the air flow passage 11 toward the feet of the passengers in the passenger compartment, and air flowing through the air flow passage 11 are supplied to the vehicle. A vent outlet 11d that blows out toward the upper body of the passenger in the room, and a differential outlet 11e that blows out the air flowing through the air flow passage 11 toward the surface of the vehicle windshield toward the vehicle interior side. ing.

  An indoor blower 12 such as a sirocco fan for circulating air from one end side to the other end side of the air flow passage 11 is provided on one end side in the air flow passage 11.

  On one end side of the air flow passage 11, there is provided an inlet switching damper 13 that can open one of the outside air inlet 11 a and the inside air inlet 11 b and close the other. When the inside air suction port 11b is closed by the suction port switching damper 13 and the outside air suction port 11a is opened, an outside air supply mode in which air flows from the outside air suction port 11a into the air flow passage 11 is set. Further, when the outside air suction port 11a is closed by the suction port switching damper 13 and the inside air suction port 11b is opened, the inside air circulation mode in which air flows from the inside air suction port 11b into the air flow passage 11 is set. Further, when the suction port switching damper 13 is positioned between the outside air suction port 11a and the inside air suction port 11b, and the outside air suction port 11a and the inside air suction port 11b are opened, the outside air suction port 11a by the suction port switching damper 13 is opened. And the inside / outside air suction mode in which air flows into the air flow passage 11 from the outside air suction port 11a and the inside air suction port 11b at a ratio corresponding to the respective opening ratios of the inside air suction port 11b.

  The outlet switching dampers 13b, 13c, and 13d for opening and closing the outlets 11c, 11d, and 11e are provided at the foot outlet 11c, the vent outlet 11d, and the differential outlet 11e on the other end side of the air flow passage 11, respectively. Is provided. The outlet switching dampers 13b, 13c, and 13d are configured to be interlocked by a link mechanism (not shown). Here, when the foot outlet 11c is opened by the outlet switching dampers 13b, 13c, and 13d, the vent outlet 11d is closed, and the differential outlet 11e is slightly opened, the air flowing through the air flow passage 11 is reduced. Most of the air is blown from the foot outlet 11c and the remaining air is blown from the differential outlet 11e. When the foot outlet 11c and the differential outlet 11e are closed by the outlet switching dampers 13b, 13c, and 13d and the vent outlet 11d is opened, all of the air flowing through the air flow passage 11 is vented 11d. It becomes the vent mode blown out from. Further, when the foot outlet 11c and the vent outlet 11d are opened by the outlet switching dampers 13b, 13c, and 13d and the differential outlet 11e is closed, the air flowing through the air flow passage 11 is moved to the foot outlet 11c and the vent. It becomes the bilevel mode which blows off from the blower outlet 11d. When the foot outlet 11c and the vent outlet 11d are closed by the outlet switching dampers 13b, 13c, and 13d and the differential outlet 11e is opened, the air flowing through the air flow passage 11 is blown out from the differential outlet 11e. It becomes the differential mode. When the vent outlet 11d is closed by the outlet switching dampers 13b, 13c, and 13d and the foot outlet 11c and the differential outlet 11e are opened, the air flowing through the air flow passage 11 is transferred to the foot outlet 11c and the differential outlet 11c. It becomes the differential foot mode which blows off from the blower outlet 11e. In the air flow passage 11, the foot outlet 11c, the vent outlet 11d, the heat absorber and the radiator described later, the temperature of the air blown from the foot outlet 11c is blown out from the vent outlet 11d in the bi-level mode. The positional relationship and the structure are such that a temperature difference that is higher than the temperature of the air is generated.

  The air flow passage 11 on the downstream side in the air flow direction of the indoor blower 12 is provided with a heat absorber 14 for cooling and dehumidifying the air flowing through the air flow passage 11. A heat radiator 15 for heating the air flowing through the air flow passage 11 is provided in the air flow passage 11 on the downstream side in the air flow direction of the heat absorber 14. The heat absorber 14 and the heat radiator 15 are heat exchangers including fins and tubes for exchanging heat between the refrigerant flowing through the interior and the air flowing through the air flow passage 11.

  The air flow path 11 between the heat absorber 14 and the heat radiator 15 is provided with an air mix damper 16 for adjusting a ratio of air heated by the heat radiator 15 flowing through the air flow path 11. By moving the air mix damper 16 in the direction of closing the upstream side of the radiator 15 in the air flow passage 11, the ratio of the air to be heat exchanged in the radiator 15 is reduced, and other than the radiator 15 in the air flow passage 11. By moving to the partial side, the proportion of air that exchanges heat in the radiator 15 increases. The air mix damper 16 closes the upstream side of the radiator 15 in the air flow passage 11 and opens the portion other than the radiator 15 so that the opening degree becomes 0%, and the upstream side of the radiator 15 in the air flow passage 11. Is opened and the opening is 100% with the portion other than the radiator 15 closed.

  The refrigerant circuit 20 includes the heat absorber 14, the radiator 15, a compressor 21 for compressing the refrigerant, an outdoor heat exchanger 22 for exchanging heat between the refrigerant and air outside the passenger compartment, the radiator 15, and outdoor heat. The first internal heat exchanger 23 for exchanging heat between at least the refrigerant flowing out of the radiator 15 and the refrigerant flowing out of the heat absorber 14 of the exchanger 22, an expansion means as a first expansion valve, and a condensation pressure adjusting means The first control valve 24 having a refrigerant flow path that can be switched to the expansion means side or the condensation pressure adjustment means side, heat exchange between a part of the refrigerant flowing out of the radiator 15 and other refrigerant flowing out of the radiator 15 The second internal heat exchanger 25, the first electromagnetic valve 26a, the second electromagnetic valve 26b, the third electromagnetic valve 26c, the first to second check valves 27a and 27b, and the expansion for the heat absorber as the second expansion valve Cooling out of valve 28 and radiator 15 Second internal heat exchanger expansion valve 29 as a third expansion valve for decompressing a part of the refrigerant, a receiver for storing surplus refrigerant and separating the refrigerant into gas and liquid and allowing the liquid refrigerant to flow out A tank 30 is connected to each other by a copper tube or an aluminum tube.

  Specifically, the refrigerant flow path 20 a is provided by connecting the refrigerant inflow side of the radiator 15 to the refrigerant discharge side of the compressor 21. In addition, a refrigerant flow passage 20b is provided on the refrigerant outflow side of the radiator 15 by connecting the high-pressure refrigerant inflow side of the second internal heat exchanger 25. A receiver tank 30 is provided in the refrigerant flow passage 20b. A refrigerant flow passage 20 c is provided on the high-pressure refrigerant outflow side of the second internal heat exchanger 25 by connecting the refrigerant inflow side of the first control valve 24. A refrigerant flow passage 20d is provided on the refrigerant outflow side of the first control valve 24 on the expansion means side by connecting one end side of the outdoor heat exchanger 22. A first check valve 27a is provided in the refrigerant flow passage 20d. In addition, a refrigerant flow passage 20e is provided on the refrigerant outflow side of the first control valve 24 on the side of the condensing pressure adjusting means, to which the other end side of the outdoor heat exchanger 22 is connected. A refrigerant flow passage 20f is provided on the other end side of the outdoor heat exchanger 22 by connecting the refrigerant suction side of the compressor 21 in parallel with the refrigerant flow passage 20e. A first electromagnetic valve 26a is provided in the refrigerant flow passage 20f. The refrigerant flow passage 20c is provided with a refrigerant flow passage 20g by connecting the high-pressure refrigerant inflow side of the first internal heat exchanger 23 to the refrigerant flow passage 20c. A second electromagnetic valve 26b is provided in the refrigerant flow passage 20g. A refrigerant flow passage 20h is provided on the high-pressure refrigerant outflow side of the first internal heat exchanger 23 by connecting the refrigerant inflow side of the heat absorber 14. A heat absorber expansion valve 28 is provided in the refrigerant flow passage 20h. A refrigerant flow passage 20 i is provided on the refrigerant outflow side of the heat absorber 14 by connecting the low-pressure refrigerant inflow side of the first internal heat exchanger 23. A refrigerant flow passage 20j is provided on the low-pressure refrigerant outflow side of the first internal heat exchanger 23 by connecting the downstream side of the refrigerant flow passage 20f in the refrigerant flow direction of the first electromagnetic valve 26a. A refrigerant flow passage 20k is provided on one end side of the outdoor heat exchanger 22 by connecting the downstream side in the refrigerant flow direction of the second electromagnetic valve 26b of the refrigerant flow passage 20g in parallel with the refrigerant flow passage 20d. Yes. A third electromagnetic valve 26c and a second check valve 27b are provided in the refrigerant flow passage 20k in order from the upstream side in the refrigerant flow direction. The refrigerant flow passage 20b is provided with a refrigerant flow passage 20l by branching and connected to the low-pressure refrigerant inflow side of the second internal heat exchanger 25. A second internal heat exchanger expansion valve 29 is provided in the refrigerant flow passage 20l. A refrigerant flow passage 20m is provided on the low-pressure refrigerant outflow side of the second internal heat exchanger 25 by being connected to the refrigerant suction side of the compressor 21. Here, the bypass circuit 31 is configured by the refrigerant flow path 201, the low-pressure side of the second internal heat exchanger 25, and the refrigerant flow path 20m.

  The compressor 21 and the outdoor heat exchanger 22 are disposed in an engine room outside the vehicle compartment.

  The compressor 21 is provided with a pair of refrigerant inlets, one refrigerant inlet is connected to the refrigerant flow passage 20f, and the other refrigerant inlet is connected to the refrigerant flow passage 20m. The other refrigerant inlet connected to the refrigerant flow passage 20m communicates with a portion through which the refrigerant in the middle of compression flows. The compressor 21 is driven by an electric motor, and the rotation speed can be adjusted by inverter control.

  The outdoor heat exchanger 22 is a heat exchanger composed of fins, tubes, and the like for exchanging heat between the refrigerant circulating inside and the air outside the vehicle compartment. When the outdoor heat exchanger 22 functions as a heat absorber, the refrigerant flows from one end side of the refrigerant flow path, and when the outdoor heat exchanger 22 functions as a radiator, the refrigerant flows from the other end side of the refrigerant flow path. On one end side of the refrigerant flow path of the outdoor heat exchanger 22, a gas-liquid separation unit 22a capable of storing a liquid refrigerant when functioning as a radiator, and a liquid refrigerant flowing out of the gas-liquid separation unit 22a are supercooled. And a supercooling portion 22b for providing the above state. The outdoor heat exchanger 22 is provided with an outdoor blower 22c for exchanging heat between air outside the passenger compartment and the refrigerant when the vehicle is stopped.

  The first internal heat exchanger 23 is, for example, a double-pipe type or a stacked type heat exchanger, and exchanges heat between the refrigerant and the refrigerant.

  The first control valve 24 decompresses the refrigerant flowing into the outdoor heat exchanger 22 during the heating operation and the first dehumidifying heating operation on the expansion means side. The first control valve 24 controls the condensation pressure of the refrigerant in the radiator 15 during the dehumidifying and cooling operation on the condensation pressure adjusting means side. The first control valve 24 has a stepping motor for switching the refrigerant flow path to the expansion means side or the condensation pressure adjusting means side and adjusting the opening degree of each refrigerant flow path.

  The second internal heat exchanger 25 is, for example, a double-pipe type or a laminated type heat exchanger, and exchanges heat between the refrigerant and the refrigerant.

  The heat absorber expansion valve 28 is a temperature expansion valve whose valve opening can be adjusted according to the temperature of the refrigerant flowing out of the heat absorber 14. As the temperature expansion valve, for example, an outflow refrigerant passage through which the refrigerant flowing out from the heat absorber flows, a temperature sensing rod for detecting the temperature through the outflow refrigerant passage, and a diaphragm for moving the valve body, An integrally formed box-type temperature expansion valve is used.

  The second internal heat exchanger expansion valve 29 is an electronic expansion valve, and the controller switches the opening and closing of the valve based on, for example, the temperature outside the passenger compartment, and adjusts the valve opening.

  In the vehicle air conditioner configured as described above, a cooling operation, a dehumidifying and cooling operation, a heating operation, a first dehumidifying and heating operation, and a second dehumidifying and heating operation are performed. Hereinafter, each operation will be described.

In the cooling operation and the dehumidifying and cooling operation, in the refrigerant circuit 20, the refrigerant flow path of the first control valve 24 is set on the condensation pressure adjusting means side, the third electromagnetic valve 26c is opened, and the first and second electromagnetic valves 26a. 26b are closed, the expansion valve 29 for the second internal heat exchanger is closed, and the compressor 21 is operated.
Thereby, the refrigerant discharged from the compressor 21 is, as shown in FIG. 2, the refrigerant flow passage 20a, the radiator 15, the refrigerant flow passage 20b, the high-pressure side of the second internal heat exchanger 25, the refrigerant flow passage 20c, 20e, outdoor heat exchanger 22, refrigerant flow passages 20k, 20g, high pressure side of first internal heat exchanger 23, refrigerant flow passage 20h, heat absorber 14, refrigerant flow passage 20i, low pressure side of first internal heat exchanger 23 Then, the refrigerant flows in the order of the refrigerant flow paths 20j and 20f and is sucked into the compressor 21. In the cooling operation, the refrigerant flowing through the refrigerant circuit 20 dissipates heat in the outdoor heat exchanger 22 and absorbs heat in the heat absorber 14. In the dehumidifying and cooling operation, as shown by the one-dot chain line in FIG. 2, when the air mix damper 16 is opened, the refrigerant flowing through the refrigerant circuit 20 also radiates heat in the radiator 15. Moreover, the refrigerant | coolant which distribute | circulates the outdoor heat exchanger 22 will be in the state of supercooling by flowing through the gas-liquid separation part 22a and the supercooling part 22b, and will flow into the refrigerant | coolant flow path 20k.

  At this time, in the air-conditioning unit 10 in the cooling operation, the air in the air flow passage 11 circulated by operating the indoor blower 12 is cooled by exchanging heat with the refrigerant in the heat absorber 14, and the temperature in the vehicle interior is set as a target. In order to obtain the temperature Tset, the air is blown into the vehicle interior as the target air temperature TAO, which is the temperature of the air to be blown out from the air outlets 11c, 11d, and 11e.

  The target blowing temperature TAO is calculated based on the detected environmental conditions and the target set temperature Tset by detecting environmental conditions such as the temperature Tam outside the passenger compartment, the temperature Tr inside the passenger compartment, and the amount of solar radiation Ts.

  Further, in the air conditioning unit 10 during the dehumidifying and cooling operation, the air in the air flow passage 11 circulated by operating the indoor fan 12 is dehumidified by being cooled by exchanging heat with the refrigerant that absorbs heat in the heat absorber 14. . The air dehumidified in the heat absorber 14 is heated by exchanging heat with the refrigerant that dissipates heat in the radiator 15 and is blown into the passenger compartment as air at the target blowing temperature TAO.

In the heating operation, in the refrigerant circuit 20, the refrigerant flow path of the first control valve 24 is set on the expansion means side, the first electromagnetic valve 26a is opened, and the second and third electromagnetic valves 26b and 26c are closed, The compressor 21 is operated with the second internal heat exchanger expansion valve 29 closed.
As a result, the refrigerant discharged from the compressor 21 is, as shown in FIG. 3, the refrigerant flow passage 20a, the radiator 15, the refrigerant flow passage 20b, the high-pressure side of the second internal heat exchanger 25, the refrigerant flow passage 20c, 20d, the outdoor heat exchanger 22, and the refrigerant flow passage 20f are circulated in this order and sucked into the compressor 21. The refrigerant flowing through the refrigerant circuit 20 dissipates heat in the radiator 15 and absorbs heat in the outdoor heat exchanger 22. The refrigerant sucked into the compressor 21 is adjusted to a predetermined degree of superheat by controlling the opening degree of the first control valve 24 on the expansion means side.

  At this time, in the air conditioning unit 10, the air in the air flow passage 11 circulated by operating the indoor fan 12 is heated by exchanging heat with the refrigerant in the radiator 15 without exchanging heat with the refrigerant in the heat absorber 14. Then, the air becomes the target blowing temperature TAO and is blown into the passenger compartment.

In the first dehumidifying and heating operation, in the refrigerant circuit 20, the refrigerant flow path of the first control valve 24 is set on the expansion means side, the first and second electromagnetic valves 26a and 26b are opened, and the third electromagnetic valve 26c is set. The compressor 21 is operated by closing the second internal heat exchanger expansion valve 29.
As a result, the refrigerant discharged from the compressor 21 passes through the refrigerant flow passage 20a, the radiator 15, the refrigerant flow passage 20b, the high-pressure side of the second internal heat exchanger 25, and the refrigerant flow passage 20c as shown in FIG. Circulate in order. Part of the refrigerant flowing through the refrigerant flow passage 20c flows through the refrigerant flow passage 20d, the outdoor heat exchanger 22, and the refrigerant flow passage 20f in this order, and is sucked into the compressor 21. Other refrigerants flowing through the refrigerant flow passage 20c are the refrigerant flow passage 20g, the high-pressure side of the first internal heat exchanger 23, the refrigerant flow passage 20h, the heat absorber 14, the refrigerant flow passage 20i, and the first internal heat exchanger. The refrigerant flows in the order of the low pressure side 23 and the refrigerant flow passages 20j and 20f, and is sucked into the compressor 21. The refrigerant flowing through the refrigerant circuit 20 radiates heat in the radiator 15 and absorbs heat in the heat absorber 14 and the outdoor heat exchanger 22. The refrigerant sucked into the compressor 21 is adjusted to a predetermined degree of superheat by controlling the opening degree of the first control valve 24 on the expansion means side.

  At this time, in the air conditioning unit 10, the air in the air flow passage 11 circulated by operating the indoor blower 12 is dehumidified by being cooled by heat exchange with the refrigerant in the heat absorber 14. The air dehumidified in the heat absorber 14 is heated when a part of the air exchanges heat with the refrigerant in the radiator 15, and is blown into the vehicle interior as air at the target blowing temperature TAO.

In the second dehumidifying and heating operation, the refrigerant circuit 20 closes the refrigerant flow path of the first control valve 24, opens the second electromagnetic valve 26b, closes the first and third electromagnetic valves 26a and 26c, (2) The internal heat exchanger expansion valve 29 is closed and the compressor 21 is operated.
Thereby, the refrigerant discharged from the compressor 21 is, as shown in FIG. 5, the refrigerant flow passage 20a, the radiator 15, the refrigerant flow passage 20b, the high pressure side of the second internal heat exchanger 25, the refrigerant flow passage 20c, 20 g, the high pressure side of the first internal heat exchanger 23, the refrigerant flow passage 20 h, the heat absorber 14, the refrigerant flow passage 20 i, the low pressure side of the first internal heat exchanger 23, and the refrigerant flow passages 20 j and 20 f in this order and compressed Inhaled by the machine 21. The refrigerant flowing through the refrigerant circuit 20 dissipates heat in the radiator 15 and absorbs heat in the heat absorber 14.

  At this time, in the air conditioning unit 10, the air in the air flow passage 11 circulated by operating the indoor blower 12 is cooled by exchanging heat with the refrigerant in the heat absorber 14 as in the first dehumidifying heating operation. Is dehumidified. The air dehumidified in the heat absorber 14 is heated when a part of the air exchanges heat with the refrigerant in the radiator 15, and is blown into the vehicle interior at the target blowing temperature TAO.

  When the auto air conditioner switch is set to the on state, the cooling operation, the dehumidifying and cooling operation, the heating operation, the first dehumidifying and heating operation, and the second dehumidifying and heating operation are performed as follows. It is switched based on environmental conditions such as the humidity outside the passenger compartment, the humidity Th inside the passenger compartment, and the amount of solar radiation Ts.

  Moreover, the mode of the blower outlets 11c, 11d, and 11e is switched by the blower outlet switching dampers 13b, 13c, and 13d. The opening degree of the air mix damper 16 is adjusted so that the temperature of the air blown from the blowout ports 11c, 11d, and 11e becomes the target blowout temperature TAO.

  Further, in each operation, switching between the foot mode, the vent mode, and the bi-level mode is performed according to the target blowing temperature TAO. Specifically, the foot mode is set when the target blowing temperature TAO is a high temperature such as 40 ° C. or higher. Further, the vent mode is set when the target blowing temperature TAO is low, for example, less than 25 ° C. Further, when the target blowing temperature TAO is a temperature between the target blowing temperature TAO where the foot mode is set and the target blowing temperature TAO where the vent mode is set, the bi-level mode is set.

  Further, during the heating operation or the first dehumidifying heating operation, when the temperature of the air outside the vehicle compartment becomes low (for example, 10 degrees or less below zero), it is difficult for the refrigerant flowing through the outdoor heat exchanger 22 to absorb heat. During the heating operation or the first dehumidifying heating operation, if the heat absorption amount in the outdoor heat exchanger 22 is insufficient, the circulation amount of the refrigerant in the refrigerant circuit 20 is reduced, the heat radiation amount from the radiator 15 is reduced, and the heating capacity is reduced. There may be a shortage.

  For this reason, when the temperature of the air outside the passenger compartment becomes low during the heating operation or the first dehumidifying heating operation, the second internal heat exchanger expansion valve 29 is opened to increase the heat radiation amount in the radiator 15. To do.

  When the second internal heat exchanger expansion valve 29 is opened during the heating operation or the first dehumidifying heating operation, a part of the refrigerant flowing out of the radiator 15 is, as shown in FIG. The refrigerant flows through the low-pressure side of the internal heat exchanger 25 and the refrigerant flow passage 20m in this order, and is sucked into the compressor 21.

  At this time, the refrigerant that has flowed out of the radiator 15 flows into the receiver tank 30 and is stored and separated into gas and liquid, and only the liquid refrigerant flows out. The refrigerant flowing through the refrigerant flow passage 20l is decompressed by the second internal heat exchanger expansion valve 29 to be in a gas-liquid two-phase state and flows into the low pressure side of the second internal heat exchanger 25. The refrigerant flowing through the low-pressure side of the second internal heat exchanger 25 flows out of the radiator 15 and exchanges heat with the refrigerant flowing through the high-pressure side of the second internal heat exchanger 25 to absorb heat, and is in a gas-liquid two-phase state. Thus, the refrigerant is sucked into the portion where the refrigerant in the middle of compression of the compressor 21 circulates. The refrigerant flowing through the high-pressure side of the second internal heat exchanger 25 exchanges heat with the refrigerant flowing through the low-pressure side of the second internal heat exchanger 25 to dissipate heat and become supercooled. It distribute | circulates toward the heat exchanger 22, and distribute | circulates toward each of the outdoor heat exchanger 22 and the heat absorber 14 during the 1st dehumidification heating operation.

  Thereby, since the compressor 21 sucks the gas-liquid two-phase refrigerant into the portion where the refrigerant in the middle of compression flows, the refrigerant discharge amount even if the heat absorption amount in the outdoor heat exchanger 22 is small Will increase. When the refrigerant discharge amount of the compressor 21 increases, the heat dissipation amount in the radiator 15 increases.

  Further, since the refrigerant in the gas-liquid two-phase state is sucked into the compressor 21, it is possible to ensure the return amount of the lubricating oil necessary for lubricating the compressor 21.

  Moreover, since the refrigerant | coolant which distribute | circulated the high voltage | pressure side of the 2nd internal heat exchanger 25 will be in a supercooling state, the heat absorption amount in the outdoor heat exchanger 22 will increase during heating operation, and it will be outdoor during 1st dehumidification heating operation. The amount of heat absorption in each of the heat exchanger 22 and the heat absorber 14 increases.

  Thus, according to the vehicle air conditioner of the present embodiment, during the heating operation or the dehumidifying heating operation, the refrigerant in the middle of the compression of the compressor 21 flows through a part of the liquid refrigerant flowing out from the receiver tank 30. The pressure is reduced by a bypass circuit 31 (refrigerant flow passages 20l and 20m) that is sucked into a portion to be discharged, a second internal heat exchanger expansion valve 29 that depressurizes the refrigerant flowing through the bypass circuit 31, and a second internal heat exchanger expansion valve 29. And a second internal heat exchanger 25 that exchanges heat between the refrigerant flowing through the bypass circuit 31 that has become a gas-liquid two-phase state and the other liquid refrigerant flowing out of the receiver tank 30. Thereby, when the temperature of the air outside the passenger compartment becomes low during the heating operation or the first dehumidifying heating operation, the refrigerant discharge amount from the compressor 21 is opened by opening the second internal heat exchanger expansion valve 29. Since the amount of heat radiation in the radiator 15 can be increased, the heating capacity during heating operation can be improved, and dehumidification can be performed without reducing the heating capacity during the first dehumidifying heating operation. . Further, since the refrigerant in the gas-liquid two-phase state is sucked into the compressor 21, it is possible to ensure the return amount of the lubricating oil necessary for lubricating the compressor 21. Further, since the liquid refrigerant flowing out of the receiver tank 30 is decompressed by the second internal heat exchanger expansion valve 29 and flows into the low pressure side of the second internal heat exchanger 25, the refrigerant is gas-liquid 2. The adjustment to the phase state is facilitated, and the refrigerant in the gas-liquid two-phase state can be reliably sucked into the portion where the refrigerant in the middle of compression of the compressor 21 flows.

  7 to 9 show a second embodiment of the present invention. In addition, the same code | symbol is attached | subjected and shown to the component similar to the said embodiment.

  As shown in FIG. 7, the vehicle air conditioner is provided with a second internal heat exchanger 32 that does not have a receiver tank 30 in the refrigerant flow passage 20 b and has a function of a receiver tank.

  The bypass circuit 31 is branched from the refrigerant flow passage 20c (downstream of the second internal heat exchanger 32 in the refrigerant flow direction) instead of the refrigerant flow passage 20l of the first embodiment, and the second internal heat exchanger 32. The refrigerant flow passage 20n is connected to the low-pressure refrigerant inflow side.

  As shown in FIG. 8, the second internal heat exchanger 32 can store the refrigerant that has flowed out of the radiator 15, and the receiver tank portion 32 a that separates the refrigerant into gas and liquid and causes the liquid refrigerant to flow out; The low-pressure refrigerant circulation part 32b that distributes the refrigerant decompressed by the expansion valve 29 for the second internal heat exchanger, and the heat exchange part that can exchange heat between the refrigerant that circulates through the receiver tank part 32a and the refrigerant that circulates through the low-pressure refrigerant circulation part 32b. 32c.

  The receiver tank part 32a is provided such that the refrigerant flow path extends in the vertical direction, the refrigerant flow path 20b is connected to the upper part, and the refrigerant flow path 20c is connected to the lower part. In the receiver tank portion 32a, the refrigerant that has flowed out of the radiator 15 flows in from the top and is stored, and is separated into gas and liquid. In addition, liquid refrigerant flows out from the lower part from the receiver tank part 32a.

  The low-pressure refrigerant circulation part 32b is provided so that the refrigerant flow path extends in the vertical direction, the refrigerant flow path 20n is connected to the upper side, and the refrigerant flow path 20m is connected to the lower side. In the low-pressure refrigerant circulation part 32b, the refrigerant mixed with the lubricating oil flowing out from the receiver tank part 32a flows in from the upper part, and the refrigerant flows out from the lower part together with the lubricating oil.

  The heat exchange part 32c is provided between the receiver tank part 32a and the low-pressure refrigerant circulation part 32b, and the refrigerant that circulates each is provided so as to be able to exchange heat with each other. The second internal heat exchanger 32 is a plate-type heat exchanger as long as heat exchange between the refrigerant flowing through the receiver tank section 32a and the refrigerant flowing through the low-pressure refrigerant circulation section 32b is possible in the heat exchange section 32c. Alternatively, a multi-tube heat exchanger may be used.

  In the vehicle air conditioner configured as described above, when the second internal heat exchanger expansion valve 29 is opened during heating operation or dehumidifying heating operation, the refrigerant flowing out of the radiator 15 is as shown in FIG. After flowing through the receiver tank portion 32a of the second internal heat exchanger 32, a part of the refrigerant flow passage 20n, the low-pressure refrigerant flow portion 32b of the second internal heat exchanger 32, and the refrigerant flow passage 20m are circulated and compressed in this order. The refrigerant is sucked into the part where the refrigerant in the middle of compression of the machine 21 flows.

  At this time, the refrigerant flowing out of the radiator 15 flows into the receiver tank portion 32a of the second internal heat exchanger 32 and is separated into gas and liquid, and the liquid refrigerant flows out. The refrigerant flowing through the refrigerant flow passage 20n is decompressed by the second internal heat exchanger expansion valve 29 to be in a gas-liquid two-phase state and flows into the low-pressure refrigerant circulation portion 32b of the second internal heat exchanger 32. The refrigerant flowing through the low-pressure refrigerant circulation part 32b absorbs heat by exchanging heat with the refrigerant flowing out of the radiator 15 and flowing through the receiver tank part 32a of the second internal heat exchanger 32, and is compressed in a gas-liquid two-phase state. The refrigerant is sucked into the part where the refrigerant in the middle of compression of the machine 21 flows. In addition, the refrigerant flowing through the receiver tank portion 32a dissipates heat by exchanging heat with the refrigerant flowing through the low-pressure refrigerant circulation portion 32b, and is in a supercooled state, and flows toward the outdoor heat exchanger 22 during heating operation. During the first dehumidifying and heating operation, the refrigerant flows toward each of the outdoor heat exchanger 22 and the heat absorber 14.

  Thereby, since the compressor 21 sucks the gas-liquid two-phase refrigerant into the portion where the refrigerant in the middle of compression flows, the refrigerant discharge amount even if the heat absorption amount in the outdoor heat exchanger 22 is small Will increase. When the refrigerant discharge amount of the compressor 21 increases, the heat dissipation amount in the radiator 15 increases.

  Further, since the refrigerant in the gas-liquid two-phase state is sucked into the compressor 21, it is possible to ensure the return amount of the lubricating oil necessary for lubricating the compressor 21.

  Moreover, since the refrigerant | coolant which distribute | circulated the receiver tank part 32a will be in a supercooled state, the heat absorption amount in the outdoor heat exchanger 22 will increase during heating operation, and the outdoor heat exchanger 22 and heat absorption during 1st dehumidification heating operation. The amount of heat absorption in each of the vessels 14 increases.

  As described above, according to the vehicle air conditioner of the present embodiment, a part of the refrigerant flowing out of the radiator 15 flows through a part of the refrigerant flowing out of the radiator 15 during the heating operation or the dehumidifying heating operation. The pressure is reduced by the bypass circuit 31 (refrigerant flow passages 20n, 20m) to be sucked into the second internal heat exchanger, the second internal heat exchanger expansion valve 29 for reducing the pressure of the refrigerant flowing through the bypass circuit 31, and the second internal heat exchanger expansion valve 29. And a second internal heat exchanger 32 for exchanging heat between the refrigerant flowing through the bypass circuit 31 in a gas-liquid two-phase state and the refrigerant flowing out of the radiator 15, and dissipating heat from the second internal heat exchanger 32. The refrigerant flow path through which the refrigerant that has flowed out of the vessel 15 flows is provided with a receiver tank portion 32a that stores the refrigerant and separates it into gas and liquid, and allows the liquid refrigerant to flow out. Thereby, when the temperature of the air outside the passenger compartment becomes low during the heating operation or the first dehumidifying heating operation, the refrigerant discharge amount from the compressor 21 is opened by opening the second internal heat exchanger expansion valve 29. Since the amount of heat radiation in the radiator 15 can be increased, the heating capacity during heating operation can be improved, and dehumidification can be performed without reducing the heating capacity during the first dehumidifying heating operation. . Further, since the refrigerant in the gas-liquid two-phase state is sucked into the compressor 21, it is possible to ensure the return amount of the lubricating oil necessary for lubricating the compressor 21. Further, the liquid refrigerant flowing out from the receiver tank portion 32 a of the second internal heat exchanger 32 is decompressed by the second internal heat exchanger expansion valve 29 and flows into the low-pressure refrigerant circulation portion 32 b of the second internal heat exchanger 32. Therefore, the adjustment of the refrigerant to the gas-liquid two-phase state is facilitated, and the gas-liquid two-phase refrigerant can be reliably sucked into the portion where the refrigerant in the middle of compression of the compressor 21 flows. Become.

  In the receiver tank portion 32a of the second internal heat exchanger 32, the refrigerant flows in from the upper side, and the refrigerant flows out from the lower side. As a result, since the liquid refrigerant that accumulates on the lower side of the receiver tank portion 32a can be caused to flow out of the receiver tank portion 32a by gravity, it is possible to configure the receiver tank portion 32a with a simple structure and reduce the manufacturing cost. Can be achieved.

  Further, in the low-pressure refrigerant circulation part 32b of the second internal heat exchanger 32, the refrigerant flows in from the upper side and the refrigerant flows out from the lower side. Thereby, since the lubricating oil mixed in the refrigerant flowing into the low-pressure refrigerant circulation part 32b can be caused to flow out of the low-pressure refrigerant circulation part 32b by gravity, it is possible to prevent a reduction in the circulation amount of the lubricating oil in the refrigerant circuit 20. It is possible to improve the operation efficiency of the compressor 21 and reduce the occurrence of failure.

  FIG. 10 shows a third embodiment of the present invention. In addition, the same code | symbol is attached | subjected and shown to the component similar to the said embodiment.

  In this vehicle air conditioner, as shown in FIG. 10, instead of the radiator 15 of the second embodiment, a refrigerant radiator 33 as a radiator that exchanges heat between water and a refrigerant as a heat medium is air. It is provided outside the flow passage 11.

  A water circuit 40 serving as a heat medium circuit through which water flows is connected to the heat exchanging portion 33a for exchanging heat of the water in the refrigerant radiator 33 with the refrigerant. The water circuit 40 includes a water pump 41 that discharges water, a heater core 42 that serves as a heat medium radiator for exchanging heat between the air that flows through the air flow passage 11 and water, and heat that is discharged from an engine for traveling the vehicle. A radiator 43 as an exhaust heat absorption part for absorbing water into water and an electric heater 44 for heating water are connected.

  In the vehicle air conditioner configured as described above, the refrigerant can be circulated as in the second embodiment, and the gas-liquid two-phase refrigerant can be sucked into the compressor 21. is there.

  In the water circuit 40, the water pump 41 is operated to distribute water during the dehumidifying and cooling operation, the heating operation, the first dehumidifying and heating operation, and the second dehumidifying and heating operation.

  The water flowing through the water circuit 40 absorbs heat from the refrigerant in the refrigerant radiator 33, and dissipates heat by exchanging heat with the air flowing through the air flow passage 11 in the heater core 42. The water flowing through the water circuit 40 is heated by the heat discharged from the engine in the radiator 43 in addition to being heated in the refrigerant radiator 33. When the heating amount of the air flowing through the air flow passage 11 is insufficient, the insufficient heating amount can be compensated by heating the water flowing through the water circuit 40 with the electric heater 44.

  Thus, in the vehicle air conditioner of the present embodiment, as in the second embodiment, when the temperature of the air outside the vehicle compartment becomes low during the heating operation or the first dehumidifying heating operation, By opening the expansion valve 29 for the internal heat exchanger, the amount of refrigerant discharged from the compressor 21 can be increased and the amount of heat released from the radiator 15 can be increased, so that the heating capacity during heating operation can be improved. It is possible to perform dehumidification without reducing the heating capacity during the first dehumidifying heating operation. Further, since the refrigerant in the gas-liquid two-phase state is sucked into the compressor 21, it is possible to ensure the return amount of the lubricating oil necessary for lubricating the compressor 21. Further, the liquid refrigerant flowing out from the receiver tank portion 32 a of the second internal heat exchanger 32 is decompressed by the second internal heat exchanger expansion valve 29 and flows into the low-pressure refrigerant circulation portion 32 b of the second internal heat exchanger 32. Therefore, the adjustment of the refrigerant to the gas-liquid two-phase state is facilitated, and the gas-liquid two-phase refrigerant can be reliably sucked into the portion where the refrigerant in the middle of compression of the compressor 21 flows. Become.

  Further, a radiator 43 for heating water flowing through the water circuit 40 by heat discharged from the engine is connected to the water circuit 40. As a result, heating operation and first dehumidifying heating operation can be performed by heating the water in the water circuit 40 with the heat discharged from the engine, so the energy consumption can be reduced by effectively using the exhaust heat of the engine. It becomes possible to reduce.

  In addition, an electric heater 44 for heating water flowing through the water circuit 40 is provided. As a result, it is possible to compensate for the insufficient amount of heat in the heating capacity during the heating operation or the first dehumidifying heating operation, so that the interior of the vehicle can be maintained at the required temperature.

  In the third embodiment, the amount of heat in the heating capacity during the heating operation or the first dehumidifying heating operation is shown by heating the water flowing through the water circuit 40 by the electric heater 44. It is not limited to. For example, as shown in FIG. 11, an electric heater 44 may be provided in the refrigerant flow passage 20 f on the suction side of the compressor 21, and the refrigerant flowing through the refrigerant circuit 20 may be heated by the electric heater 44. Further, the attachment position of the electric heater 44 with respect to the refrigerant circuit 20 is not limited to the refrigerant flow passage 20 f on the suction side of the compressor 21. For example, the electric heater 44 may be provided between the second internal heat exchanger 32 and the compressor 21 in the bypass circuit 31, or may be provided between the discharge side of the compressor 21 and the refrigerant radiator 33. Good. In addition, an electric heater 44 may be provided in each of the water circuit 40 and the refrigerant circuit 20 so that the water flowing through the water circuit 40 and the refrigerant flowing through the refrigerant circuit 20 are simultaneously heated by the electric heater 44.

  Moreover, in the said 3rd Embodiment, although the water circuit 40 which distribute | circulates water as a heat medium was shown, it is not restricted to this, For example, the antifreezing liquid which has ethylene glycol as a main component can also be used as a heat medium. is there.

  In the third embodiment, the water circuit 40 is connected to the radiator 43 for absorbing the heat discharged from the engine into the water. However, the present invention is not limited to this. For example, heat that is discharged when the vehicle travels, such as heat that is discharged from an electric motor or a battery provided in the vehicle, may be absorbed by water flowing through the water circuit 40.

  In the third embodiment, the water circuit 40 is applied to the refrigerant circuit 20 of the second embodiment. However, the present invention is not limited to this, and the refrigerant circuit 20 of the first embodiment has water. The circuit 40 may be applied.

  FIG. 12 shows a fourth embodiment of the present invention. In addition, the same code | symbol is attached | subjected and shown to the component similar to the said embodiment.

  As shown in FIG. 12, the refrigerant circuit 20 of this vehicle air conditioner is provided with one refrigerant inlet and one refrigerant outlet in place of the first control valve 24 in the first embodiment. And a second control valve 34 capable of adjusting the valve opening in the respective ranges of the condensation pressure adjustment region.

  Specifically, the refrigerant flow path 20 a is provided by connecting the refrigerant inflow side of the radiator 15 to the refrigerant discharge side of the compressor 21. In addition, a refrigerant flow passage 20b is provided on the refrigerant outflow side of the radiator 15 by connecting the high-pressure refrigerant inflow side of the second internal heat exchanger 32. A refrigerant flow passage 20 c is provided on the high-pressure refrigerant outflow side of the second internal heat exchanger 32 by connecting the refrigerant inflow side of the second control valve 34. A refrigerant flow passage 20 d is provided on the refrigerant outflow side of the second control valve 34 by connecting the refrigerant inflow side of the outdoor heat exchanger 22. Further, a refrigerant flow passage 20e is provided on the refrigerant outflow side of the outdoor heat exchanger 22 by connecting the refrigerant intake side of the compressor 21. A first electromagnetic valve 26a is provided in the refrigerant flow passage 20e. The refrigerant flow passage 20c is provided with a refrigerant flow passage 20f by connecting the high-pressure refrigerant inflow side of the first internal heat exchanger 23 to the refrigerant flow passage 20c. In the refrigerant flow passage 20f, a second electromagnetic valve 26b and a first check valve 27a are provided in order from the upstream side in the refrigerant flow direction. A refrigerant flow passage 20 g is provided on the high-pressure refrigerant outflow side of the first internal heat exchanger 23 by connecting the refrigerant inflow side of the heat absorber 14. A heat absorber expansion valve 28 is provided in the refrigerant flow passage 20g. A refrigerant flow passage 20 h is provided on the refrigerant outflow side of the heat absorber 14 by connecting the low-pressure refrigerant inflow side of the first internal heat exchanger 23. A refrigerant flow passage 20i is provided on the low-pressure refrigerant outflow side of the first internal heat exchanger 23 by connecting the refrigerant flow direction downstream side of the first electromagnetic valve 26a of the refrigerant flow passage 20e. A refrigerant flow passage 20j is provided on the refrigerant outflow side of the outdoor heat exchanger 22 by connecting the refrigerant inflow side of the gas-liquid separator 22a in parallel with the refrigerant flow passage 20e. A third electromagnetic valve 26c is provided in the refrigerant flow passage 20j. A refrigerant flow passage 20k is provided on the refrigerant outflow side of the gas-liquid separation unit 22a by connecting the downstream side in the refrigerant flow direction of the first check valve 27a of the refrigerant flow passage 20f via the supercooling unit 22b. Yes. A second check valve 27b is provided in the refrigerant flow passage 20k. The refrigerant flow passage 20c is branched and connected to the low-pressure refrigerant inflow side of the second internal heat exchanger 32, thereby providing a refrigerant flow passage 20n. A second internal heat exchanger expansion valve 29 is provided in the refrigerant flow passage 20n. A refrigerant flow passage 20m is provided on the low-pressure refrigerant outflow side of the second internal heat exchanger 32 by connecting the refrigerant suction side of the compressor 21. Here, the bypass circuit 31 is configured by the refrigerant flow passage 20n, the low-pressure side of the second internal heat exchanger 32, and the refrigerant flow passage 20m.

In the heating operation of the vehicle air conditioner configured as described above, in the refrigerant circuit 20, the refrigerant flow path of the second control valve 34 is set on the expansion means side, the first electromagnetic valve 26a is opened, and the first The second to third electromagnetic valves 26b and 26c are closed, the second internal heat exchanger expansion valve 29 is closed, and the compressor 21 is operated.
As a result, the refrigerant discharged from the compressor 21 passes through the refrigerant flow passage 20a, the radiator 15, the refrigerant flow passage 20b, the high-pressure side of the second internal heat exchanger 32, the refrigerant flow passages 20c and 20d, and the outdoor heat exchanger 22. Then, the refrigerant flows in the order of the refrigerant flow passage 20e and is sucked into the compressor 21. The refrigerant flowing through the refrigerant circuit 20 dissipates heat in the radiator 15 and absorbs heat in the outdoor heat exchanger 22.

In the first dehumidifying and heating operation, in the refrigerant circuit 20, the refrigerant flow path of the second control valve 34 is set on the expansion means side, the first and second electromagnetic valves 26a and 26b are opened, and the third electromagnetic valve 26 c is closed, the second internal heat exchanger expansion valve 29 is closed, and the compressor 21 is operated.
Thereby, the refrigerant discharged from the compressor 21 flows in order through the refrigerant flow passage 20a, the radiator 15, the refrigerant flow passage 20b, the high-pressure side of the second internal heat exchanger 32, and the refrigerant flow passage 20c. A part of the refrigerant flowing through the refrigerant flow passage 20c flows in the order of the refrigerant flow passage 20d, the outdoor heat exchanger 22, and the refrigerant flow passage 20e and is sucked into the compressor 21. Other refrigerants flowing through the refrigerant flow passage 20c include the refrigerant flow passage 20f, the high-pressure side of the first internal heat exchanger 23, the refrigerant flow passage 20g, the heat absorber 14, the refrigerant flow passage 20h, and the first internal heat exchanger. The refrigerant flows in the order of the low pressure side 23 and the refrigerant flow passages 20 i and 20 e and is sucked into the compressor 21. The refrigerant flowing through the refrigerant circuit 20 radiates heat in the radiator 15 and absorbs heat in the heat absorber 14 and the outdoor heat exchanger 22.

  When the expansion valve 29 for the second internal heat exchanger is opened during the heating operation or the first dehumidifying heating operation, the refrigerant flowing out from the radiator 15 is received by the receiver of the second internal heat exchanger 32 as in the second embodiment. After flowing through the tank portion 32a, a part of the refrigerant flows through the refrigerant flow passage 20n, the low-pressure refrigerant flow portion 32b of the second internal heat exchanger 32, and the refrigerant flow passage 20m in this order, and the refrigerant being compressed by the compressor 21 flows. Inhaled into the part.

  As described above, according to the vehicle air conditioner of the present embodiment, when the temperature of the air outside the passenger compartment becomes low during the heating operation or the first dehumidifying heating operation, as in the above embodiment, the second By opening the expansion valve 29 for the internal heat exchanger, the amount of refrigerant discharged from the compressor 21 can be increased and the amount of heat released from the radiator 15 can be increased, so that the heating capacity during heating operation can be improved. It is possible to perform dehumidification without reducing the heating capacity during the first dehumidifying heating operation. Further, since the refrigerant in the gas-liquid two-phase state is sucked into the compressor 21, it is possible to ensure the return amount of the lubricating oil necessary for lubricating the compressor 21. Further, the liquid refrigerant flowing out from the receiver tank portion 32 a of the second internal heat exchanger 32 is decompressed by the second internal heat exchanger expansion valve 29 and flows into the low-pressure refrigerant circulation portion 32 b of the second internal heat exchanger 32. Therefore, the adjustment of the refrigerant to the gas-liquid two-phase state is facilitated, and the gas-liquid two-phase refrigerant can be reliably sucked into the portion where the refrigerant in the middle of compression of the compressor 21 flows. Become.

  The refrigerant circuit 20 according to the fourth embodiment can be applied to a circuit including the bypass circuit 31 according to the first embodiment and a circuit including the water circuit 40 according to the third embodiment.

  In the embodiment, the expansion means for decompressing the refrigerant flowing into the outdoor heat exchanger 22 during the heating operation and the first dehumidifying heating operation and the refrigerant condensing pressure in the radiator 15 during the dehumidifying and cooling operation are controlled. Although the 1st control valve 24 and the 2nd control valve 34 which have a condensing pressure adjustment means were shown, it is not restricted to this. For example, in the refrigerant circuit 20, instead of the first control valve 24 and the second control valve 34, an expansion means having a variable opening and a condensation pressure adjustment means may be configured separately.

  Moreover, although the said embodiment showed what connected the bypass circuit 31 to the partial refrigerant | coolant inlet port through which the refrigerant | coolant in the middle of compression of the compressor 21 provided with a pair of refrigerant | coolant inlet port distribute | circulated, it is restricted to this. It is not a thing. For example, when the compressor 21 is a two-stage compressor, the bypass circuit 31 may be connected to the refrigerant flow passage between the first stage and the second stage.

  Moreover, although the said embodiment showed what used the expansion valve 29 for 2nd internal heat exchangers as the electronic expansion valve which can open and close a valve, and adjustment of a valve opening degree, it is not restricted to this. For example, the bypass circuit 31 may be provided with a temperature expansion valve as an expansion valve for the second internal heat exchanger and an opening / closing valve such as an electromagnetic valve capable of opening / closing the bypass circuit 31.

  In the first embodiment, the second internal heat exchanger 25 and the second internal heat exchanger expansion valve 29 are connected to the bypass circuit 31, respectively. In the second embodiment, the second internal heat exchanger 32 and Although the second internal heat exchanger expansion valve 29 is shown as being connected to the bypass circuit 31, it is not limited thereto. As shown in FIG. 13, the second internal heat exchanger 25 and the second internal heat exchanger expansion valve 29 may be formed integrally, or as shown in FIG. 14, the second internal heat exchanger 32. And the second internal heat exchanger expansion valve 29 may be integrally formed. Thereby, it becomes possible to reduce the number of parts at the time of assembling to the vehicle, and to reduce the manufacturing cost.

DESCRIPTION OF SYMBOLS 10 ... Air conditioning unit, 14 ... Heat absorber, 15 ... Radiator, 20 ... Refrigerant circuit,
DESCRIPTION OF SYMBOLS 21 ... Compressor, 22 ... Outdoor heat exchanger, 24 ... 1st control valve, 25 ... 2nd internal heat exchanger, 26a, 26b, 26c ... 1st-3rd solenoid valve, 29 ... For 2nd internal heat exchanger Expansion valve, 30 ... receiver tank, 31 ... bypass circuit, 32 ... second internal heat exchanger, 32a ... receiver tank section, 32b ... low-pressure refrigerant circulation section, 33 ... refrigerant radiator, 33a ... heat exchange section, 40 ... water Circuit 41 ... Water pump 42 ... Heater core 43 ... Radiator 44 ... Electric heater

Claims (10)

A compressor that compresses and discharges the refrigerant;
A radiator that dissipates the refrigerant,
A heat absorber that absorbs the refrigerant;
An outdoor heat exchanger that radiates or absorbs refrigerant,
A receiver tank that stores the refrigerant that has flowed out of the radiator and separates it into gas and liquid, and that causes the liquid refrigerant to flow out,
The refrigerant discharged from the compressor is caused to flow into the radiator to dissipate the heat, the refrigerant flowing through the radiator is caused to flow into the receiver tank, and the liquid refrigerant flowing out of the receiver tank is transferred to the outdoor heat exchanger via the first expansion valve. A refrigerant circuit for heating that causes the compressor to suck the refrigerant flowing through the outdoor heat exchanger,
The refrigerant discharged from the compressor flows into the radiator to dissipate the heat, the refrigerant flowing through the radiator flows into the receiver tank, and a part of the liquid refrigerant flowing out of the receiver tank is heated to the outdoor heat via the first expansion valve. The refrigerant that has flowed into the exchanger to absorb heat and that has flowed out of the receiver tank into the heat absorber via the second expansion valve absorbs heat, and the refrigerant that has flowed through the outdoor heat exchanger and the heat absorber is compressed by the compressor. A refrigerant circuit for dehumidifying and heating to be inhaled,
In the refrigerant circuit for heating and the refrigerant circuit for dehumidifying heating, a bypass circuit that sucks a part of the liquid refrigerant flowing out of the receiver tank into a portion where the refrigerant in the middle of compression of the compressor flows,
A third expansion valve that depressurizes the refrigerant flowing through the bypass circuit;
An air conditioner for vehicles, comprising: an internal heat exchanger for exchanging heat between the refrigerant flowing through the bypass circuit decompressed by the third expansion valve and the refrigerant of the other liquid flowing out from the receiver tank. A compressor that compresses and discharges the refrigerant;
A radiator that dissipates the refrigerant,
A heat absorber that absorbs the refrigerant;
An outdoor heat exchanger that radiates or absorbs refrigerant,
The refrigerant discharged from the compressor flows into the radiator to dissipate heat, and the refrigerant that has flowed through the radiator flows into the outdoor heat exchanger through the first expansion valve to absorb heat, and the refrigerant that has flowed through the outdoor heat exchanger is A heating refrigerant circuit to be sucked into the compressor;
The refrigerant discharged from the compressor flows into the radiator to dissipate the heat, and a part of the refrigerant flowing through the radiator flows into the outdoor heat exchanger via the first expansion valve to absorb heat, and the other circulating through the radiator A refrigerant circuit for dehumidification heating that causes the refrigerant to flow into the heat absorber via the second expansion valve to absorb heat, and to suck the refrigerant that has passed through the outdoor heat exchanger and the heat absorber into the compressor,
In the refrigerant circuit for heating and the refrigerant circuit for dehumidifying heating, a bypass circuit that sucks a part of the refrigerant flowing out of the radiator into a portion where the refrigerant in the middle of compression of the compressor flows,
A third expansion valve that depressurizes the refrigerant flowing through the bypass circuit;
An internal heat exchanger for exchanging heat between the refrigerant flowing through the bypass circuit decompressed by the third expansion valve and the refrigerant flowing out of the radiator,
The refrigerant flow path through which the refrigerant flowing out of the radiator of the internal heat exchanger circulates is provided with a receiver tank section that stores the refrigerant and separates it into gas and liquid, and outflows the liquid refrigerant. A vehicle air conditioner. The vehicle air conditioner according to claim 2, wherein the receiver tank unit receives refrigerant from an upper side and flows out from a lower side. 4. The vehicle air according to claim 2, wherein the refrigerant flow path through which the refrigerant flowing through the bypass circuit of the internal heat exchanger flows flows from the upper side and flows out from the lower side. Harmony device. The vehicle air conditioner according to any one of claims 1 to 4, wherein the third expansion valve is formed integrally with the internal heat exchanger. A heat medium pump for discharging the heat medium;
A heat exchanging unit that is provided in the radiator and exchanges heat between the refrigerant flowing through the radiator and the heat medium;
A heat medium radiator that dissipates the heat medium;
The heat medium discharged from the heat medium pump flows into the heat exchange part to absorb heat, the heat medium that has passed through the heat exchange part flows into the heat medium radiator to dissipate heat, and the heat medium that has circulated through the heat medium radiator A vehicle air conditioner according to any one of claims 1 to 5, further comprising a heat medium circuit that is sucked into the heat medium pump. The vehicle air conditioner according to claim 6, further comprising a heat medium heating means for heating the heat medium flowing through the heat medium circuit. The vehicle air conditioner according to claim 7, wherein the heat medium heating means is an electric heater capable of heating the heat medium flowing through the heat medium circuit. The heat medium heating means is an exhaust heat absorption part that is provided in the heat medium circuit and absorbs heat discharged from other devices to the heat medium that circulates through the heat medium circuit. Air conditioner for vehicles. The vehicle air conditioner according to any one of claims 1 to 9, further comprising refrigerant heating means for heating the refrigerant flowing through the heating refrigerant circuit and the dehumidifying heating refrigerant circuit.

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