JP2800596B2 - Heat pump type air conditioner for vehicles - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump type air conditioner for a vehicle having a vapor compression cycle for circulating a refrigerant to a heat exchanger outside a vehicle compartment and a heat exchanger inside a vehicle compartment by driving a compressor.

[0002]

2. Description of the Related Art A conventional heat pump type air conditioner for a vehicle is disclosed in Japanese Unexamined Patent Publication No. Hei.
As disclosed in JP-A-130808, the flow of the refrigerant is reversed between a heating operation and a refrigerant operation by a four-way valve. During the heating operation, the heat exchanger outside the vehicle compartment is used as a heat absorber, Using a heat exchanger as a radiator,
It is known that, during a cooling operation, the heat exchanger outside the vehicle compartment is used as a radiator and the heat exchanger inside the vehicle compartment is used as a heat absorber.

[0003] Specifically, Japanese Patent Application Laid-Open No. 2-290475
The cooling and heating device disclosed in Japanese Patent Laid-Open Publication No. HEI 7-26511 will be described with reference to FIG. That is, during the heating operation, the four-way valve 2 is switched as shown by the solid line, and the refrigerant is supplied from the compressor 1 to the four-way valve 2.
→ 1st interior heat exchanger 3 → heating heat exchanger 4 → 2nd interior heat exchanger 5 → expansion valve 6 → exterior heat exchanger 7 → four-way valve 2
→ The receiver 8 → circulates with the compressor 1, and the first vehicle interior heat exchanger 3 radiates the heat of the high-temperature refrigerant discharged from the compressor 1 to the air introduced by the blower fan 9 to generate warm air for vehicle interior heating. And heat exchanger 4 for heating is engine 1
The second heat exchanger 5 absorbs the waste heat from the refrigerant into the air, and the second heat exchanger 5 radiates the heat of the refrigerant to the air introduced by the blower fan 11 to generate warm air for heating the vehicle interior. The exchanger 7 absorbs the heat of the outside air introduced by the fan 12 into the refrigerant. During the cooling operation, the four-way valve 2 is switched as indicated by the dotted line, and the refrigerant is compressed 1 → the exterior heat exchanger 7 → the expansion valve 6 → the second interior heat exchanger 5 → the first interior heat exchanger 3 → The four-way valve 2 → the receiver 8 → the compressor 1 circulates, and the exterior heat exchanger 7 radiates the heat of the high-temperature refrigerant discharged from the compressor 1 to the outside air, and the first and second interior heat exchangers 3.
5 radiates the heat of the air introduced by the blower fans 9 and 11 to the refrigerant to create cold air for cooling the vehicle interior.

[0004]

In this conventional example, the flow of the refrigerant is reversed by the four-way valve 2 during the heating operation and during the refrigerant operation. During the heating operation, the heat exchanger 7 outside the vehicle compartment is connected to the heat absorber. As well as using the vehicle interior heat exchangers 3 and 5 as radiators to generate warm air for vehicle interior heating. During cooling operation, the vehicle exterior heat exchanger 7 is used as a radiator and Since the heat exchangers 3 and 5 are used as heat absorbers to generate cold air for cooling the vehicle interior, it can be used in climatic conditions such as when the outside air temperature is low, when running, when it rains, and when it snows. When the heating operation is performed, the amount of heat absorbed by the heat exchanger 7 outside the vehicle compartment decreases. Then, assuming that the work amount of the compressor 1 is constant, the heat radiation amount in the vehicle interior heat exchangers 3 and 5, which radiates the total heat amount of the heat absorption amount from the external heat exchanger 7 and the work amount of the compressor 1 Decreases,
Heating capacity decreases. In addition, under the above climatic conditions, a frost phenomenon is likely to occur, and the number of times of the defrost operation is increased, so that a stable heating operation may not be obtained.

Further, since the flow direction of the refrigerant changes between the cooling operation and the heating operation, both the pipes on the exterior heat exchanger 7 side and the interior heat exchangers 3, 5 endure high temperature and high pressure. It was necessary to change the pipe diameter and the like.

Further, during the heating operation, since waste heat from the engine 10 is absorbed to generate warm air for heating the vehicle interior, it is not suitable for a vehicle having no large heat source such as a solar car or an electric car.

On the other hand, the applicant of the present application has filed Japanese Patent Application No. 3-34.
No. 5950 proposes a new heat pump type air conditioner for vehicles. In this device, a heat-dissipating vehicle interior heat exchanger is provided in addition to a heat-absorbing vehicle interior heat exchanger, and switching is performed by a three-way valve. According to such a device, it is possible to improve the cooling and heating capacity with stable control irrespective of climatic conditions outside the vehicle compartment, without requiring a significant design change, suitable for electric vehicles, etc., and to perform dehumidifying heating. Can be.

[0008] More specifically, as shown in Fig. 26, the three-way valve 32 is switched as shown by the solid line during the heating operation, and the refrigerant flows from the compressor 31 → the three-way valve 32 → the heat exchanger 33 for radiating the vehicle to the liquid. The air circulated through the tank 36 → the expansion valve 34 → the heat absorbing vehicle interior heat exchanger 35 → the compressor 31, and the air introduced by the blower fan was cooled by heat exchange in the heat absorbing vehicle interior heat exchanger 35 to be cooled and dehumidified. Thereafter, the air is heated by heat exchange in the heat-dissipating vehicle interior heat exchanger 33 to generate warm air for vehicle interior heating.

During the cooling operation, the three-way valve 32 is switched as shown by the dotted line, and the refrigerant is supplied from the compressor 31 → the three-way valve 32 → the heat exchanger 38 outside the vehicle interior → the check valve 70 → the heat exchanger 33 for heat radiation inside the vehicle. → Liquid tank 36 → Expansion valve 34 → Heat-absorbing vehicle interior heat exchanger 35 → Circuit 31 circulates, and vehicle exterior heat exchanger 38 radiates heat of the high-temperature refrigerant discharged from compressor 1 to the outside air, and blower fan Is introduced into the heat exchanger 35, the heat is exchanged by the heat absorbing vehicle interior heat exchanger 35 to be cooled, and cool air for vehicle interior cooling is produced.

[0010] The refrigerating capacity of such a cooling and heating device is related to the amount of circulating refrigerant, and it is important to increase the amount of circulating refrigerant to improve the cooling capacity and dehumidifying and heating capacity. By the way, the amount of the circulated refrigerant is related to the volumetric efficiency of the compressor 31 and the specific volume of the suction gas. However, there is no particular means for positively increasing the volumetric efficiency, and there is a limit in improving the refrigerating capacity.

In addition, when the compressor discharge temperature is high or when the compressor motor rotation speed is high and the compressor discharge temperature is likely to be high, the operation of the apparatus must be stopped, and the heating capacity can be maximized. There was a risk of disappearing.

Therefore, the present invention can improve the cooling and heating performance with stable control without being influenced by the climatic conditions outside the vehicle compartment, does not require a significant design change, and enables dehumidifying heating suitable for automobiles and the like. Further, it is an object of the present invention to provide a heat pump type cooling / heating device for a vehicle which can further improve the refrigeration capacity and maximize the heating capacity.

[0013]

According to a first aspect of the present invention, there is provided a compressor for adding work to a refrigerant, and the compressor is connected to a refrigerant discharge side of the compressor to transfer heat of the refrigerant to outside air. A heat exchanger outside the vehicle compartment that radiates heat to the refrigerant, a heat exchanger that is connected to the refrigerant discharge side of the compressor, and that exchanges heat of the refrigerant with air introduced by the blowing means to generate warm conditioned air; Expansion means connected to the refrigerant outflow side of the heat-radiating vehicle interior heat exchanger; connected to the refrigerant outflow side of the expansion means and the refrigerant suction side of the compressor; A heat absorbing vehicle interior heat exchanger for exchanging heat with a refrigerant supplied from at least one of the vehicle exterior heat exchanger and the heat radiating vehicle interior heat exchanger through the expansion means to produce cold conditioned air; The refrigerant that is provided between the outlet side and the refrigerant inflow side of the exterior heat exchanger and the heat radiation interior heat exchanger and that is discharged from the compressor is introduced into at least the exterior heat exchanger during cooling operation. A refrigerant flow switching means for avoiding the heat exchanger outside the vehicle compartment during the heating operation and introducing the refrigerant into the heat exchanger inside the heat radiator, and a refrigerant inflow side of the heat exchanger outside the vehicle compartment and the compressor during the heating operation. A heating return flow path connecting between the refrigerant suction side and a refrigerant outflow side of the vehicle exterior heat exchanger or a refrigerant outflow side of the heat radiation interior vehicle heat exchanger and a refrigerant suction side of the compressor during cooling operation. At least one of a cooling return flow path that connects between the air conditioner and a part of the refrigerant flowing from the refrigerant flow path switching means to the heat radiating vehicle interior heat exchanger during the heating operation. Via return channel Means for allowing leakage to be supplied to the refrigerant suction side of the compressor, and from the heat exchanger outside the vehicle compartment to the heat exchanger for heat radiation and the heat exchanger for heat absorption during cooling operation. At least one of cooling leakage permitting means for permitting a part of the refrigerant to be supplied to the refrigerant suction side of the compressor via a cooling return flow path is provided.

According to a second aspect of the present invention, there is provided the heat pump type cooling / heating device for a vehicle according to the first aspect, wherein the pressure which allows the refrigerant allowed to leak by the heating leak permitting means or the cooling leak permitting means to pass therethrough. It is characterized in that a resistor is interposed.

According to a third aspect of the present invention, in the heat pump type cooling and heating apparatus for a vehicle according to the first or second aspect, the heating leak permitting means or the cooling leak permitting means controls a forward flow. The check valve is a check valve that allows a specified amount of refrigerant leakage in the reverse direction.

According to a fourth aspect of the present invention, there is provided the heat pump type cooling and heating apparatus according to the first or second aspect, wherein the heating leakage permitting means or the cooling leak permitting means is a control valve. It is characterized by.

According to a fifth aspect of the present invention, a compressor for adding work to the refrigerant, an external heat exchanger connected to the refrigerant discharge side of the compressor and radiating heat of the refrigerant to the outside air, and a refrigerant for the compressor A heat-exchange vehicle interior heat exchanger that is connected to the discharge side and exchanges heat of the refrigerant with the air introduced by the blowing means to produce warm air-conditioned air, and is connected to the refrigerant outflow side of this heat-exchange vehicle interior heat exchanger The expansion means, and the refrigerant outflow side of the expansion means and the refrigerant suction side of the compressor, and the heat of the air introduced by the air blowing means is supplied to the outside heat exchanger and the heat release heat exchanger. Heat exchange with the refrigerant supplied from at least one of the expansion means through the expansion means to generate cold conditioned air; a heat-absorbing vehicle interior heat exchanger; a refrigerant discharge side of the compressor; the vehicle exterior heat exchanger; The refrigerant that is provided between the refrigerant inflow side of the vehicle interior heat exchanger and that is discharged from the compressor is introduced into at least the exterior heat exchanger during the cooling operation, and avoids the exterior heat exchanger during the heating operation. And a refrigerant flow switching means for introducing the refrigerant into the heat radiating vehicle interior heat exchanger, wherein the refrigerant flow switching means is a four-way valve, and the refrigerant in the vehicle exterior heat exchanger through the four-way valve during a heating operation. A flow path is provided to allow connection between the inflow side and the refrigerant suction side of the compressor, and the outside heat of the vehicle is provided between the refrigerant outflow side of the outside heat exchanger and the four-way valve and the heat radiation interior heat exchanger. An outflow-side check valve that allows a predetermined amount of refrigerant to leak in the reverse direction is provided, with the outflow direction from the exchanger being the forward direction.

According to the present invention, a compressor for adding work to the refrigerant, an external heat exchanger connected to the refrigerant discharge side of the compressor and radiating heat of the refrigerant to the outside air, a refrigerant of the compressor A heat-exchange vehicle interior heat exchanger that is connected to the discharge side and exchanges heat of the refrigerant with the air introduced by the blowing means to produce warm air-conditioned air, and is connected to the refrigerant outflow side of this heat-exchange vehicle interior heat exchanger The expansion means, and the refrigerant outflow side of the expansion means and the refrigerant suction side of the compressor, and the heat of the air introduced by the air blowing means is supplied to the outside heat exchanger and the heat release heat exchanger. Heat exchange with the refrigerant supplied from at least one of the expansion means through the expansion means to generate cold conditioned air; a heat-absorbing vehicle interior heat exchanger; a refrigerant discharge side of the compressor; the vehicle exterior heat exchanger; The refrigerant that is provided between the refrigerant inflow side of the vehicle interior heat exchanger and that is discharged from the compressor is introduced into at least the exterior heat exchanger during the cooling operation, and avoids the exterior heat exchanger during the heating operation. And a refrigerant flow switching means for introducing the refrigerant into the heat radiating vehicle interior heat exchanger, wherein the refrigerant flow switching means is a four-way valve, and the refrigerant in the vehicle exterior heat exchanger through the four-way valve during a heating operation. A flow path is provided to enable connection between an inflow side and a refrigerant suction side of the compressor, and an outflow side control is provided between the refrigerant outflow side of the exterior heat exchanger and the four-way valve and the heat radiation interior heat exchanger. A valve is provided.

According to a seventh aspect of the present invention, there is provided a compressor for adding work to the refrigerant, a vehicle exterior heat exchanger connected to the refrigerant discharge side of the compressor for radiating heat of the refrigerant to the outside air, and a refrigerant for the compressor. A heat-exchange vehicle interior heat exchanger that is connected to the discharge side and exchanges heat of the refrigerant with the air introduced by the blowing means to produce warm air-conditioned air, and is connected to the refrigerant outflow side of this heat-exchange vehicle interior heat exchanger The expansion means, and the refrigerant outflow side of the expansion means and the refrigerant suction side of the compressor, and the heat of the air introduced by the air blowing means is supplied to the outside heat exchanger and the heat release heat exchanger. Heat exchange with the refrigerant supplied from at least one of the expansion means through the expansion means to generate cold conditioned air; a heat-absorbing vehicle interior heat exchanger; a refrigerant discharge side of the compressor; the vehicle exterior heat exchanger; The refrigerant that is provided between the refrigerant inflow side of the vehicle interior heat exchanger and that is discharged from the compressor is introduced into at least the exterior heat exchanger during the cooling operation, and avoids the exterior heat exchanger during the heating operation. Refrigerant flow switching means for introducing the heat radiation into the vehicle interior heat exchanger, the refrigerant flow switching means as a four-way valve, during heating operation of the vehicle exterior heat exchanger through the four-way valve A flow path that enables connection between the refrigerant inflow side and the refrigerant inflow side of the compressor, and enables connection between the refrigerant outflow side of the exterior heat exchanger and the refrigerant inflow side of the compressor via the four-way valve during cooling operation. Provided, between the refrigerant outflow side of the exterior heat exchanger and the four-way valve and the heat radiation interior heat exchanger, an outflow side bypass flow path that bypasses the flow of the refrigerant via a pressure resistor,
A bypass flow path is provided between the four-way valve and the refrigerant outflow side of the vehicle exterior heat exchanger and the refrigerant inflow side of the heat radiation interior vehicle heat exchanger via a pressure resistor to bypass the refrigerant flow, An outflow-side check valve that sets the outflow direction from the heat exchanger outside the vehicle to a forward direction is provided in a flow path parallel to the outflow-side bypass flow path, and the outflow from the four-way valve is provided in a flow path that is aligned with the bypass flow path. A non-return valve having a forward direction is provided.

According to the present invention, a compressor for adding work to the refrigerant, an external heat exchanger connected to the refrigerant discharge side of the compressor and radiating heat of the refrigerant to the outside air, a refrigerant of the compressor A heat-exchange vehicle interior heat exchanger that is connected to the discharge side and exchanges heat of the refrigerant with the air introduced by the blowing means to produce warm air-conditioned air, and is connected to the refrigerant outflow side of this heat-exchange vehicle interior heat exchanger The expansion means, and the refrigerant outflow side of the expansion means and the refrigerant suction side of the compressor, and the heat of the air introduced by the air blowing means is supplied to the outside heat exchanger and the heat release heat exchanger. Heat exchange with the refrigerant supplied from at least one of the expansion means through the expansion means to generate cold conditioned air; a heat-absorbing vehicle interior heat exchanger; a refrigerant discharge side of the compressor; the vehicle exterior heat exchanger; The refrigerant that is provided between the refrigerant inflow side of the vehicle interior heat exchanger and that is discharged from the compressor is introduced into at least the exterior heat exchanger during the cooling operation, and avoids the exterior heat exchanger during the heating operation. And a refrigerant flow switching means for introducing the heat radiation into the heat exchanger of the vehicle interior, wherein the refrigerant flow switching means is a three-way valve, and a refrigerant inflow side of the heat exchanger outside the vehicle and a refrigerant suction side of the compressor. An outflow side that provides a connectable flow path and bypasses the flow of the refrigerant through a pressure resistor between the refrigerant outflow side of the exterior heat exchanger and the three-way valve and the heat radiation interior heat exchanger. A bypass flow path is provided, and a refrigerant outflow side of the heat dissipation vehicle interior heat exchanger and a refrigerant suction side of the compressor are connected by a flow path including a pressure resistor, and are arranged in line with the outflow side detour flow path. In the flow path, the outflow direction from the exterior heat exchanger is forward Characterized in that a outlet-side check valve to be.

According to the ninth aspect of the present invention, a compressor for adding work to the refrigerant, an external heat exchanger connected to the refrigerant discharge side of the compressor and radiating heat of the refrigerant to the outside air, a refrigerant of the compressor A heat-exchange vehicle interior heat exchanger that is connected to the discharge side and exchanges heat of the refrigerant with the air introduced by the blowing means to produce warm air-conditioned air, and is connected to the refrigerant outflow side of this heat-exchange vehicle interior heat exchanger The expansion means, and the refrigerant outflow side of the expansion means and the refrigerant suction side of the compressor, and the heat of the air introduced by the air blowing means is supplied to the outside heat exchanger and the heat release heat exchanger. Heat exchange with the refrigerant supplied from at least one of the expansion means through the expansion means to generate cold conditioned air; a heat-absorbing vehicle interior heat exchanger; a refrigerant discharge side of the compressor; the vehicle exterior heat exchanger; The refrigerant that is provided between the refrigerant inflow side of the vehicle interior heat exchanger and that is discharged from the compressor is introduced into at least the exterior heat exchanger during the cooling operation, and avoids the exterior heat exchanger during the heating operation. Means for switching the refrigerant flow path to be introduced into the heat exchanger for heat dissipation, and a pressure resistor between the refrigerant outlet side of the heat exchanger for heat dissipation and the refrigerant suction side of the compressor. Characterized in that they are connected by a flow path.

According to a tenth aspect of the present invention, in the heat pump type cooling / heating device for a vehicle according to the fourth or sixth aspect, an element relating to at least one of a suction refrigerant temperature and a discharge refrigerant temperature of the compressor is detected. And a control means for controlling the control valve in accordance with the detection of the detection means.

[0023]

According to the first aspect of the present invention, the refrigerant flows from the compressor through the refrigerant flow switching means, the heat radiating vehicle interior heat exchanger, the expansion means, and the heat absorbing vehicle interior heat exchanger by the driving of the compressor during the heating operation. And circulates to the compressor, and the heat-dissipating cabin heat exchanger radiates the heat of the high-temperature refrigerant discharged from the compressor to the air introduced by the blowing means to produce warm air. The heat of the air introduced by the blowing means is absorbed by the refrigerant to produce cool air. During cooling operation, the compressor drives the refrigerant to move the refrigerant from the compressor to the refrigerant flow path switching means, only the heat exchanger outside the vehicle compartment, or both the heat exchanger outside the vehicle compartment and the heat exchanger inside the vehicle for heat dissipation, expansion means, heat exchange inside the vehicle compartment for heat absorption. The heat exchanger circulates through the heat exchanger in order to the compressor, the heat exchanger inside the vehicle radiates the heat of the high-temperature refrigerant discharged from the compressor to the outside air, and the heat exchanger inside the heat absorbing vehicle heats the air introduced by the blowing means. Absorbs heat into the refrigerant to create cold air.

During the heating operation, a part of the refrigerant is supplied to the refrigerant suction side of the compressor via the outside heat exchanger side and the heating return flow path, or the outside heat exchanger side or the heat radiation side during the cooling operation. A part of the refrigerant is supplied to the refrigerant suction side of the compressor via the passenger compartment heat exchanger side and the cooling return flow path.

Therefore, during at least one of heating and cooling, the leakage refrigerant supplied to the refrigerant suction side of the compressor adiabatically expands to take heat from the surroundings, and the temperature of the refrigerant sucked into the compressor is reduced. Done, increasing the volumetric efficiency.

According to the second aspect of the present invention, a part of the refrigerant is supplied to the refrigerant suction side of the compressor via the pressure resistor, whereby adiabatic expansion is further promoted, and the temperature drop of the refrigerant sucked into the compressor is further promoted. Can be done.

According to the third aspect of the present invention, a predetermined amount of refrigerant leakage is allowed by the check valve, and can be used for injection.

According to the fourth aspect of the present invention, a predetermined amount of refrigerant leakage is allowed by the control valve, and can be used for injection. Further, the amount of refrigerant used for injection and the timing of injection can be adjusted by adjusting the control valve.

According to the fifth aspect of the present invention, during the heating operation, a part of the refrigerant flowing from the four-way valve to the heat-radiating vehicle interior heat exchanger leaks a predetermined amount from the outflow-side reverse valve, and the heat radiation in the vehicle exterior heat exchanger. Is cooled and liquefied, and supplied to the refrigerant suction side of the compressor to perform injection.

According to the sixth aspect of the present invention, during the heating operation, a part of the refrigerant flowing from the four-way valve to the heat-radiating vehicle interior heat exchanger leaks by a predetermined amount under the control of the outflow side control valve, and the refrigerant flows outside the vehicle interior heat exchanger. Cooled and liquefied, supplied to the refrigerant suction side of the compressor, and injected.

According to the seventh aspect of the present invention, during the heating operation, a part of the refrigerant flowing from the four-way valve to the heat-radiating vehicle interior heat exchanger flows from the outflow-side bypass flow path through the pressure resistor and the vehicle exterior heat exchanger. Is supplied to the refrigerant suction side of the compressor to perform injection. Also, during the cooling operation, part of the refrigerant flowing from the four-way valve to the heat-radiating vehicle interior heat exchanger through the exterior heat exchanger passes from the bypass flow path to the pressure resistor and the refrigerant suction side of the compressor through the four-way valve. Inflow is performed and injection is performed. Therefore, the injection can be performed in any case of cooling and heating.

According to the eighth aspect of the invention, during the heating operation, a part of the refrigerant flowing from the three-way valve to the heat-radiating vehicle interior heat exchanger flows from the outflow-side bypass flow path through the pressure resistor and the vehicle exterior heat exchanger. And flows into the refrigerant suction side of the compressor to perform injection. Further, during the cooling operation, a part of the refrigerant flowing from the heat-radiating vehicle interior heat exchanger to the heat-absorbing vehicle interior heat exchanger is supplied to the refrigerant suction side of the compressor via the pressure resistor, and injection is performed. Therefore, the injection can be performed in any of the cooling and heating.

According to the ninth aspect of the present invention, a part of the refrigerant flowing from the heat-radiating vehicle interior heat exchanger to the heat-absorbing vehicle interior heat exchanger flows into the refrigerant suction side of the compressor via the pressure resistor, and is injected. Is performed. Therefore, the injection can be performed during the cooling operation or the heating operation.

According to the tenth aspect of the present invention, the control valve can be controlled in accordance with at least one of the suction refrigerant temperature and the discharge refrigerant temperature of the compressor, and accurate control of the control valve can be performed.

[0035]

Embodiments of the present invention will be described below.

FIG. 1 is a schematic configuration diagram of a vehicle heat pump type air conditioner according to a first embodiment of the present invention, and FIG. 2 is a schematic configuration diagram showing only a refrigeration cycle.

As shown in FIGS. 1 and 2, the compressor 31 is provided outside the vehicle compartment such as an engine room.
The input value can be directly changed like an electric compressor or a hydraulic drive compressor. A heat exchanger 38 outside the vehicle compartment and a heat exchanger 33 inside the vehicle compartment for heat dissipation are connected to the discharge side of the compressor 31 via a four-way valve 90 as a flow path switching means.

The outside heat exchanger 38 is provided outside the vehicle room such as an engine room, and serves as a vehicle outside condenser for radiating the heat of the refrigerant discharged from the compressor 31 to the outside air.

The heat-dissipating vehicle interior heat exchanger 33 is provided in a duct 39 serving as an apparatus body disposed at the front of the vehicle interior such as the back side of the instrument panel. Is a heat radiation type vehicle interior condenser that radiates heat to air introduced by a blower fan 37 as a blowing means.

The four-way valve 90 is switched to a flow path as shown by the solid line during the heating operation, and connects the discharge side of the compressor 31 to the refrigerant inflow side of the heat-exchanging interior heat exchanger 33 via the check valve 92. At the same time, the refrigerant suction side of the compressor 31 is connected to the refrigerant inflow side of the exterior heat exchanger 38 via the flow path 100 and the inflow side check valve 91. The flow channel 100
Comprises a pressure resistor 101 such as a capillary tube and constitutes a heating return flow path.

During the cooling operation, the four-way valve 90 switches the flow path as shown by the dotted line, and connects the discharge side of the compressor 31 to the check valve 91, the heat exchanger 38 outside the vehicle compartment, and the outflow-side check valve 70. Is connected to the refrigerant inflow side of the heat dissipation vehicle interior heat exchanger 33, and the refrigerant suction side of the compressor 31 is connected to the refrigerant inflow side of the heat dissipation interior heat exchanger 33 through the flow path 100 and the check valve 92. Connect to

The check valve 91 allows a forward flow of the refrigerant from the four-way valve 90 to the outside heat exchanger 38, and a predetermined amount in the reverse direction from the outside heat exchanger 38 to the flow path 100. Allow refrigerant leakage. The check valve 70 allows a forward refrigerant flow from the exterior heat exchanger 38 to the heat radiation interior heat exchanger 33 side, and allows a specified amount of refrigerant leakage in the reverse direction to the exterior heat exchanger 38. I do. These check valves 91 and 70 constitute a heating leak permitting means.

On the refrigerant outflow side of the heat radiating vehicle interior heat exchanger 33, the refrigerant inflow side of the heat absorbing vehicle interior heat exchanger 35 provided on the upstream side in the duct 39 is provided outside the liquid tank 36 and the vehicle interior. The expansion means is connected via an expansion valve 34 which adiabatically expands the liquid refrigerant to form a mist.

The heat absorbing vehicle interior heat exchanger 35 supplies the heat of the air introduced by the blower fan 37 from at least one of the vehicle exterior heat exchanger 38 and the heat radiation vehicle interior heat exchanger 33 through the expansion valve 34. This is an endothermic evaporator that absorbs heat into the cooled refrigerant to produce cool air. A refrigerant suction side of the compressor 31 is connected to a refrigerant outflow side of the heat absorbing vehicle interior heat exchanger 35.

An auxiliary heater 76 is provided on the air inlet side of the heat exchanger 33 for heat dissipation. The auxiliary heater 76 is a variable-type electric heater whose output can be arbitrarily set according to the input voltage. The input voltage is controlled by the controller 43. When the auxiliary heater 76 is turned on, the air passing through the heat dissipation vehicle interior heat exchanger 33 is heated, and the temperature of the refrigerant flowing through the heat dissipation vehicle interior heat exchanger 33 increases.

On the upstream side of the heat absorbing heat exchanger 35 in the duct 39, an inside air introducing pipe 40 for introducing the air inside the vehicle and an outside air introducing pipe 41 for introducing the outside air by receiving the traveling wind pressure. It is connected. The blower fan 37 is arranged between the air outlet side (downstream of the air flow) between the inside air introduction pipe 40 and the outside air introduction pipe 41 and the heat absorbing vehicle interior heat exchanger 35, and is rotated by a blower fan motor 44. It is designed to be driven.

An air mixing door 46 is provided on the upstream side of the heat exchanger 33 for heat dissipation. The air mixing door 46 is driven by an air mixing door actuator (not shown) driven by the control device 43, and cools the air passing through the heat absorbing vehicle interior heat exchanger 35 and dissipating the heat. Open / close so as to adjust the ratio (distribution of air volume between cold air and hot air) that separates cold air that stays cold by avoiding the air 33 and hot air that has passed through the heat exchanger 33 and that has been heated. . The air mix door opening Xdsc, which is the opening of the air mix door 46, is
Is the position indicated by the dashed line, and when the air volume distribution between the cold air and the hot air becomes 100% cold air, the air mix door opening Xds
When c = 0% (fully closed), the air mix door 46 is positioned as indicated by the two-dot chain line, and when the air volume distribution between the cool air and the hot air is 100%, the air mix door opening Xdsc =
100% (fully open) is set.

The heat exchanger 3 for radiating heat in the duct 39
Downstream from 3, an air mix chamber 47 is provided as a room for creating a temperature-conditioned conditioned air by improving the mixing of the cold air and the hot air. In the air mix chamber 47, a ventilator outlet 51 (51a, 51b) that blows out conditioned air toward the upper body of the target occupant.
b, 51c, 51d), a foot outlet 52 (52a) for blowing conditioned air toward the feet of the target occupant, and a defroster outlet 53 (53a) for blowing conditioned air toward the front window. I have. In the air mixing chamber 47, a ventilator door 55 and a foot door 5 are provided.
6 and a defroster door 57 are provided. The ventilator door 55 opens and closes the ventilator outlet 51 with a ventilator door actuator (not shown) driven by the control device 43. The foot door 56 opens and closes the foot outlet 52 by an unillustrated foot door actuator driven by the control device 43. The defroster door 57 opens and closes the defroster outlet 53 by a defroster door actuator (not shown) driven by the control device 43.

A circulation passage 71 communicating with the inside air introduction pipe 40 is connected to the air mix chamber 47. An opening 72 from the circulation passage 71 to the air mixing chamber 47 is provided with an entrance-side door 74 of the circulation passage 71, and a branch portion 73 between the circulation passage 71 and the inside air introduction pipe 40.
Is provided with an exit-side door 75. Entrance side door 7
4, the opening 72 is opened and closed by an entrance door actuator (not shown) driven by the control device 43, and the exit door 75
Switches the branch portion 73 by an outlet door actuator (not shown) driven by the control device 43. That is, in a state where the entrance side door 74 and the exit side door 75 are open (the exit side door 75 closes the inside air introduction pipe 40), the temperature-controlled air circulates from the air mix chamber 47 to the upstream side of the blower fan 37.

The control device 43 includes a heat absorbing suction air temperature sensor 58, a heat absorbing blower air temperature sensor 59, a ventilator outlet air temperature sensor 60, and a solar radiation sensor 61. And the outside air temperature sensor 62,
A room temperature sensor 63 and a room temperature setting unit 64 provided on the air conditioning setting panel 89 (in FIG. 1, shown by signal lines for convenience).
The air mix door is opened based on the thermal environment information of the air outlet mode switch 65 (same), the blower fan switch 66 (same), the refrigerant temperature sensor 67, and the air temperature sensor 68 for the air outlet of the heat exchanger. calculates a target air conditioning conditions such degrees Xdsc input value W _comp and the amount of air passing through V _eva passing heat-absorbing inner heat exchanger 35 target air temperature T _o of the compressor 31, the passenger compartment heating and cooling conditions are the arithmetic Compressor 31 so as to maintain the target cooling and heating conditions.
And a blower fan motor 44, an air mix door actuator, a ventilator door actuator, a foot door actuator, a defroster door actuator, and the like. The thermal environment information includes the air inlet temperature T _suc of the heat absorbing passenger compartment heat exchanger 35, the outlet air temperature T _out of the heat absorbing passenger compartment heat exchanger 35, and the outlet air temperature of the heat releasing passenger compartment heat exchanger 33. T _v , the air temperature T _{vent from} the ventilator outlet 51, and the solar radiation Q _{sun of the} vehicle
In such a vehicle exterior of the outside air temperature T _amb and the passenger compartment of the detection room (passenger compartment air temperature) T _{ro om} and cabin set temperature T _ptc and refrigerant temperature of the heat-radiating inner heat exchanger 33 outlet T _{re f} is there.

The heat pump cooling and heating apparatus for a vehicle according to the above embodiment is controlled based on the flowcharts shown in FIGS.

The process is started when the switch of the air conditioner is turned on and the control device is operated, and in step S1, the constants (A to H, P,
The setting of Q) is performed. That is, the target outlet temperature T _of
, F, G, H used in the formula for calculating the opening degree X of the air mix door, and P, Q used for correcting the set room temperature.

In step S2, various sensor outputs are read. That is, the vehicle interior temperature T _room which is the output of the room temperature sensor 63, and the solar radiation amount Q which is the output of the solar radiation sensor 61
_{It reads the sun} , the outside air temperature T _amb output from the outside air temperature sensor 62, the set room temperature T _ptc in the vehicle cabin output from the room temperature setting device 64, and the fan switch setting V _{fan, set} .

In step S3, in order to control the air volume of the blower fan by the applied voltage, conditioned air is generated according to the deviation (T _room -T _ptc ) between the room temperature set value T _ptc set by the occupant and the room temperature T _room. Set the applied voltage V _fan of the blower fan. Specifically, the applied voltage is increased as the deviation is larger, and the room temperature is quickly brought closer to the set room temperature.

In step S4, the set room temperature T _ptc is corrected. This correction is performed using the constants P and Q and the outside air temperature _{Tamb according} to the following equation.

T _ptc ′ = T _ptc + P × T _amb + Q Specifically, when the outside air temperature is low, the set room temperature is raised, and when the outside air temperature is high, the set room temperature is lowered. Normally, in human experience, lowering the room temperature in a hot environment gives a sense of warmth and coolness, such as "cool". Conversely, raising the room temperature in a cold surroundings gives a sense of warmth, such as "warm". Is obtained. By setting the temperature to be inversely proportional to the ambient temperature in this way, the sense of warmth and cold is stimulated and the user becomes comfortable.

In step S5, a target outlet temperature T _of is calculated. This calculation includes constants A, B, C, D, and E, an outside temperature T _amb , a room temperature T _room , a correction set room temperature T ′ _ptc , and a solar radiation amount Q.
_It is calculated by the following equation using _sun .

[0058]

In Equation 1] _{T of = A × T amb +} B × T room + C × T 'ptc + D × Q sun + E step S6, to calculate the degree of opening X of the air mixing door on the basis of the target outlet air temperature T _of. This calculation is a constant F,
This is performed by the following equation using G and H.

X = F × T _of ² + G × T _of + H In step S7, the blow mode is determined based on the target blow temperature T _of . That is, if the target outlet temperature is high, FOOT (foot mode) mainly blows out to the feet of the front seat occupant, if the target outlet temperature is medium, BI-LEVEL (bi-level mode) blows out to the chest and feet of the front seat occupant; Select VENT (vent mode) that blows out to the chest of the seat occupant.

In step S8, it is determined whether or not the occupant has pressed the manual fan switch. If the manual fan switch has been pressed, the fan set value V _fan ′ = V in step S9 to respond to the operation.
_{Let fan, set} be the final blower fan voltage. If the manual fan switch has not been pressed, step S1
At 0, the blower fan voltage automatically determined in the previous step S3 is used as it is.

In step S11, the blower fan voltage determined in step S9 or S10 is output to the blower fan motor 44.

In step S12, the output is output to each door actuator, and the door is automatically set at a predetermined position.

In step S13, the compressor and the compressor motor are controlled. This control is shown in FIGS.
This will be described later with reference to FIG.

When one loop is completed, the process returns to step S2, and the above steps are repeated.

During the heating operation, the four-way valve 90 is switched as shown by the solid line in FIGS. 1 and 2, and the refrigerant is supplied from the compressor 31 → the four-way valve 90 → the check valve 92 → the heat exchanger 33 for the heat radiation inside the vehicle → The liquid circulates through the liquid tank 36, the expansion valve 34, the heat absorbing heat exchanger 35, and the compressor 31. The heat dissipating heat exchanger 33 introduces the heat of the high-temperature refrigerant discharged from the compressor 31 by the blower fan 37. Heat is generated by radiating heat to the introduced air or air introduced by the ram pressure when the vehicle is running, and the heat absorbing vehicle interior heat exchanger 35 is connected to the blower fan 3.
The heat of the air introduced at 7 or the air introduced by the ram pressure during running of the vehicle is absorbed by the refrigerant to produce cool air.

During the cooling operation, the four-way valve 90 is switched as shown by the dotted line in FIG.
1 → four-way valve 90 → outside heat exchanger 38 → check valve 70 → radiation inside heat exchanger 33 → liquid tank 36 → expansion valve 34 →
The heat absorption heat exchanger 35 circulates from the heat exchanger 35 to the compressor 31, and the heat exchanger 38 outside the heat chamber radiates the heat of the high-temperature refrigerant discharged from the compressor 31 to the outside air, and the remaining heat to the heat exchanger inside the heat radiator. 33 radiates heat to the air introduced by the blower fan 37 or the air introduced by the ram pressure during traveling of the vehicle to generate warm air, and the heat absorbing vehicle interior heat exchanger 35 transmits the air or the vehicle introduced by the blower fan 37. The heat of the air introduced by the ram pressure during traveling is radiated to the refrigerant to produce cool air.

On the other hand, as shown in FIG.
A part of the refrigerant passing through the check valve 92 and flowing toward the heat-dissipating interior heat exchanger 33 leaks from the check valve 70 set to a predetermined leakage amount, and flows into the exterior heat exchanger 38. In the vehicle exterior heat exchanger 38, the refrigerant is cooled and liquefied by heat radiation to the outside air, and reaches the check valve 91. The check valve 91 is also set to a specified leakage amount, and the refrigerant leaking from the check valve 91 flows into the flow path 100, passes through the pressure resistor 101, and passes through the compressor 31.
Is supplied to the refrigerant suction side. Thus, the pressure resistor 10
The refrigerant in the liquid state supplied to the refrigerant suction side of the compressor 31 via 1 adiabatically expands and removes heat from the surroundings, lowers the refrigerant suction temperature of the compressor 31 and performs injection.

[0068] or if the compressor discharge temperature T _d is high by this injection, the likely condition increases compressor motor rotational speed N _c is higher T _d is, lowers the T _d, T _d when it is desired to exert the maximum heating capacity The problem of being unable to operate due to high heating can be solved, and the heating capacity can be improved. In particular, in the case of an electric compressor with a built-in motor which is easy to control, since the relatively low-temperature suction refrigerant is used for cooling the motor, the suction refrigerant is heated and, consequently, _Td is increased. The heating capacity can be improved by further increasing the number and increasing the refrigerant flow rate.

The decrease in the temperature of the refrigerant sucked into the compressor 31 means that the volumetric efficiency is improved and the amount of the circulating refrigerant is increased, so that the heat radiation in the heat exchanger 33 for heat dissipation and the heat exchanger for heat absorption in the car interior are improved. The heat absorption at 35 can be improved and the heating capacity can be significantly increased while maintaining the dehumidifying performance. Therefore, a comfortable vehicle interior environment can be created by sufficient heating while maintaining the anti-fog performance of the windshield.

The flow direction of the four-way valve 90 is normally switched by using an electromagnetic force. However, the electromagnetic force for switching is reduced by providing a pressure difference in the switched flow direction. That is, during the heating operation, the compressor 3
The refrigerant flowing to the heat-radiating vehicle interior heat exchanger 33 and the refrigerant slightly leaking through the check valve 70, the vehicle exterior heat exchanger 38, and the check valve 91 avoiding the heat exchanger 38 outside the vehicle compartment from 1. The pressure of the latter is lower by the amount of passing through the resistors such as the check valves 70 and 91. Due to this pressure difference, when switching to the cooling operation, the four-way valve 90 can be switched with a small electromagnetic force. During the cooling operation, the refrigerant flowing from the compressor 31 to the heat exchanger 38 outside the vehicle compartment and a part of the refrigerant flowing from the heat exchanger 38 outside the vehicle to the heat exchanger 33 for heat radiation inside the heat exchanger 33 pass through the check valve 92 in all directions. The pressure of the refrigerant slightly leaking to the valve 90 is lower in the latter.
Therefore, when switching to the heating operation using the pressure difference, the four-way valve 90 can be switched with a small electromagnetic force.

The presence of the check valve 91 can prevent the pressure resistor 101 from vibrating. That is, if the operation is switched from the cooling operation to the heating operation without the check valve 91, a large amount of refrigerant in the heat exchanger 38 outside the vehicle compartment may flow into the pressure resistor 101 as it is, causing vibration of the pressure resistor 101. However, the set amount of leakage flows into the pressure resistor 101 by the check valve 91, and the vibration can be suppressed.

FIGS. 6 to 8 show steps S1 of FIG.
3 shows a flowchart for executing Step 3.

First, FIG. 6 shows a flowchart for selecting between the cooling operation and the heating operation.

At step S131, various data are read. The reading here is performed in step S in FIG.
Read data other than the data read in step 2. That is, the output air temperature T _out of the heat absorbing vehicle interior heat exchanger 35 which is the output of the wind temperature sensor 59, the heat absorbing air temperature T _suc which is the output of the wind temperature sensor 58,
The heat-dissipating vehicle interior heat exchanger 33 which is the output of the wind temperature sensor 67
With the blown air temperature T _v and the physical quantity V _comp representing the compressor work, the compressor discharge increases and the compressor work increases in proportion to V _comp (corresponding to the frequency when using an electric compressor).

In step S132, it is determined whether or not the defroster switch is ON. If the defroster switch is ON, the process proceeds to step S133,
If the defroster switch has been turned off, the process proceeds to step S134.

In step S133, a correction term for the case where the defroster switch is ON is given to the target cooling state of the heat absorbing vehicle interior heat exchanger 35. ? T _c is a correction term air temperature balloon heat-absorbing inner heat exchanger as a target during the cooling operation,? T _H is the correction term of the upper limit cooling temperature of the heating operation (window sunny temperature), the defroster switch is ON In this case, the target cooling state in the heat absorbing vehicle interior heat exchanger 35 is set lower to increase the amount of dehumidification, and the reheating amount in the heat releasing vehicle interior heat exchanger 33 is increased. Air-conditioned air is blown into the cabin at the target blow-out temperature. Similarly, in step S134, the defroster switch is
A correction term for the target cooling state of the heat absorbing vehicle interior heat exchanger 35 when N is not set is given.

In step S135, step S133 is executed.
Using the correction term given in step S134 and step S134, a comparison is made between the cooling state in the heat-absorbing vehicle interior heat exchanger 35 in the cooling operation and the heating operation, and the cooling state in the cooling operation is When the temperature is lower than the case where the operation is performed, the process proceeds to step S136 to perform the cooling operation. Conversely, when the cooling state during the heating operation is lower than the case where the cooling operation is performed, the process proceeds to step S137 and the heating is performed. Execute the operation.

FIG. 7 shows a flowchart of compressor control at the time of heating temperature adjustment. When the heating operation is performed,
In step S1371, it is determined whether the defroster switch is ON.

If the defroster switch is ON in step S1371, on the other hand, if the defroster switch is OFF, in step S1373, the upper limit cooling of the heat absorbing indoor heat exchanger 35 during the heating operation is performed in step S1373. It gives a correction temperature δT _H with respect to the temperature. Here, the correction is made only for ON / OFF of the defroster switch, but the heat load condition of the vehicle, for example,
Correction may be made for solar radiation, vehicle interior temperature, outside air temperature, and air outlet temperature.

[0080] In step S1374, by comparing the low outside air temperature at the set upper limit cooling temperature T ₅ and the outside air temperature T _amb temperature upper cooling based on a (T _amb -δT _H), whichever is in the heating operation greater Set as the upper limit cooling temperature (upper limit _T'int ). Here, the outside air temperature is represented as one of the factors for determining the upper limit cooling temperature. However, other than the outside air temperature, a thermal environment condition of the vehicle, a window fogging sensor output, or the like may be used.

[0081] In step S1375, setting the temperature T _{se to} (T ₆₎ based on the freezing of the heat-absorbing inner heat exchanger 35 as the lower limit cooling temperature (the lower limit T _'int).

[0082] In step S1376, it is determined whether a lower or not than the lower limit cooling temperature to air temperature T _out balloon heat-absorbing inner heat exchanger has been set in step S1375 (lower T _'int). In the case of T _out <lower limit T ′ _int , the heat absorbing vehicle interior heat exchanger 35 may freeze in this state,
Proceeding to step S1382, the work amount of the compressor 31 is reduced by ΔV _c , and the temperature of the heat-exhaust-compartment heat exchanger blow-out temperature is increased to fall within the vertical cooling temperature. At this time, although not shown in the drawing, at the same time, control is performed to increase the suction air temperature of the heat absorbing vehicle interior heat exchanger, thereby preventing a decrease in the blow-out temperature accompanying a decrease in the work load of the compressor 31.

If it is determined in step S1376 that T _out ≧ lower limit T ′ _int , the process proceeds to step S1377, in which the temperature of the heat-exhausting indoor heat exchanger blown air T _out is set to the upper limit cooling temperature (upper limit T ′) set in step S1374. _int ).

If it is determined in step S1377 that T _out > upper limit T ′ _int , the flow advances to step S1380 to increase the work of the compressor 31 by ΔV _{c, and} to reduce the amount of heat absorbing vehicle in order to secure the dehumidification amount of the conditioned air. Reduce the temperature of the indoor heat exchanger. Conversely, in the case of T _{ou t} ≦ upper _T'int, the process proceeds to step S1378, and calculates the deviation △ theta target conditioned air temperature T _of the balloon heat-radiating inner heat exchanger air-conditioning temperature T _v.

In step S1379, if △ θ> S, the blow-out temperature has not reached the target air-conditioning air temperature T _of , so the flow proceeds to step S1380, where the compressor 31
Is increased by ΔV _{c to} increase the outlet temperature.
In the case of Δθ <−S, since the air temperature of the heat-exhausting indoor heat exchanger blown air is higher than the target blown air temperature, step S138 is performed.
Proceeding to 2, the work amount of the compressor 31 is decreased by ΔV _c to lower the blowout temperature. Under other conditions, the process proceeds to step S1381 to maintain the current compressor work.

In the conventional vehicle heat pump air conditioner, the blowout temperature can be controlled by changing the work amount of the compressor. Therefore, the temperature change amount of the vehicle greatly differs, and stable vehicle interior temperature control is difficult.

However, in the heating operation of the vehicle air conditioner according to the embodiment of the present invention, continuous heating operation can be performed without being affected by the outside air temperature. Irrespective of the driving conditions, the air temperature always appears as a predetermined amount of change in the outlet temperature (change in the amount of heat released into the vehicle interior). In addition, the dehumidification (cooling) always occurs in the heat absorbing heat exchanger 35 during the heating operation. Due to such a characteristic, the vehicle interior dehumidification temperature control without instability can be performed by the compressor control as shown in FIG.

FIG. 8 shows a flowchart of the compressor control during the cooling operation. When the cooling operation is performed, it is determined in step S1361 whether or not venting is performed.

In the case of vent blowing, it is the most energy-saving to cool the temperature of the air flowing into the heat absorbing vehicle interior heat exchanger 35 to the target blowing temperature and then blow the air into the vehicle interior, so the process proceeds to step S1362. Target outlet temperature X
_M (T _of ) is set to the target temperature T ′ _int of the air temperature blown out from the heat-exchanger interior heat exchanger.

If it is determined in step S1361 that it is other than vent blowing, the flow advances to step S1363 to determine whether or not the mode is the bi-level mode.

In the case of the bi-level mode, step S
1365, otherwise, to step S13.
Proceeds to 64, providing a corrected temperature? T _c of air temperature balloon heat-absorbing inner heat exchanger. This correction temperature is set to a larger value as the amount of reheat in the heat-radiating vehicle interior heat exchanger 33 increases.

[0092] In step S1366, correction of the target temperature T _'int the air temperature balloon heat-absorbing inner heat exchanger, the temperature T ₅ used in the step S1374, gave target outlet air temperature T _of Step S1364 or Step S1365 The temperature is set to the larger _of the temperature (T _of −δT _c ) corrected in the term.

At step S1367, at step S13
62 or the target temperature T ′ calculated in step S1366.
the difference between the _int and the air temperature balloon heat-absorbing inner heat exchanger T _out to calculate the θ.

In step S1368, step S13
If the value of θ calculated in step 67 is θ <−S _o , the process proceeds to step S1369, and the work amount of the compressor 31 is set to ΔV
_{c to} increase the temperature of the air blown from the heat-exchanger interior heat exchanger. If θ> _So , the compressor 31
It is determined that the amount of work has increased, and step S1
Proceeding to 391, the work of the compressor 31 is reduced by ΔV _c , otherwise the current compressor work is maintained.

Therefore, during the heating operation, the compressor 3
When the engine 1 starts, the heat absorption amount of the heat-absorbing vehicle interior heat exchanger 35 and the work amount corresponding to the actual input value W _comp of the compressor 31 are _radiated in the heat-radiating vehicle interior heat exchanger 33, so that the heat is absorbed into the vehicle interior. The air having a higher temperature than the suction air temperature T _suc of the heat absorbing vehicle interior heat exchanger 35 is blown out, and as the operation time elapses, the vehicle interior temperature, that is, the suction air temperature T _suc of the heat absorbing vehicle interior heat exchanger 35 is increased. Rise, and the actual input value W _comp of the compressor 31 can be increased accordingly, so that the vehicle interior is warmed up at an accelerated rate. Further, the air that has flowed into the heat-absorbing vehicle interior heat exchanger 35 flows into the heat-dissipating vehicle interior heat exchanger 33, so that the heat-absorbing vehicle interior heat exchanger 35
The actual input value W _comp of the compressor 31 is determined within a range where the heat load of the air flowing into the compressor 31 is not frozen in the heat absorbing vehicle interior heat exchanger 35, so that the compressor 3
1 is optimal.

FIG. 9 shows a configuration diagram of a refrigeration cycle according to the second embodiment. Since the basic configuration is the same as that of the embodiment shown in FIG. 2, the same reference numerals are given and duplicate explanations are omitted.

In this embodiment, the flow path 100
To control the flow rate of refrigerant leaking into the That is, in this embodiment, refrigerant flow opening / closing valves 93 and 94 are provided as control valves instead of the check valves 70 and 91 in FIG.
The refrigerant flow switching valves 93 and 94 are controlled by a control device 43 as control means shown in FIG.

The outside heat exchanger 38 is provided with an outside heat exchanger temperature detector 96 for detecting its temperature.
On the discharge side of the compressor 31, the compressor discharge temperature T
A compressor discharge temperature detector 97 for detecting _d is provided. The detection signals from the vehicle exterior heat exchanger temperature detector 96 and the compressor discharge temperature detector 97 are input to the control device 43.

FIGS. 10 and 11 show flowcharts of the embodiment shown in FIG.

FIG. 10 shows only a part of the flowcharts shown in FIGS. 3 and 4, that is, only the parts corresponding to FIG. 4. In this embodiment, the same flowcharts as those shown in FIG. 3 are provided. I have. Therefore, basic control is basically performed by a combination of the flowcharts of FIGS.

Then, in order to actively perform the injection control, the injection control is added as a step S14 after the control of the compressor and the compressor motor in the step S13. Other steps S8 to S13
The steps up to this are the same as those in FIG.

The injection control in step S14 is executed according to the flowchart shown in FIG.

When the injection control starts,
First, in step S141, it is determined whether or not the apparatus is in a heating operation in order to determine whether or not to perform injection control. If the heating operation is being performed, the process proceeds to step S142, and if the cooling operation is being performed, the process proceeds to step S143.

In step S143, since the compressor discharge temperature T _d and the compressor motor speed _Nc are both low and the refrigerant flow rate in the refrigeration cycle is small, the injection is not performed by closing the valves 93 and 94, and the operating refrigeration cycle The shortage of working refrigerant on the side is prevented.

In step S142, it is determined whether or not the compressor discharge temperature _Td is higher than a predetermined set discharge temperature _{Td, set} in order to determine whether or not to perform injection. If T _d is higher than T _{d, set} , step S
The flow shifts to 144, where the injection is performed by controlling the open / close state of the refrigerant flow opening / closing valves 93, 94. If _Td is equal to or _smaller than _{Td, set} , the process proceeds to step S145.

In step S144, the refrigerant is guided to the refrigerant suction side of the compressor 31 by opening the valves 93 and 94, and the refrigerant is cooled by adiabatic expansion to perform injection.

At step S145, it is determined whether or not the compressor speed is high and injection is required. The compressor speed _Nc is equal to a predetermined set speed N
when the _c, higher than _{se t} performs injection and proceeds to step S144. If lower, step S146
Migrated, the refrigerant flow-off valve 93 in accordance with the detected outer heat exchanger temperature T _cond in the outer heat exchanger temperature detector 96 to,
94 is controlled to open and close. That is, when T _{cond approaches} 0 ° C., the valves 93 and 94 are opened. In this case, the same state as when the injection is performed, and the high-temperature and high-pressure refrigerant flows in the exterior heat exchanger 38, the refrigerant remaining in the exterior heat exchanger 38 is expelled, and the operating refrigeration cycle Shortage of the refrigerant amount on the side can be prevented. If T _cond is around 10 ° C., valves 93, 9
4 is closed. Also, if it is in the middle temperature range,
The valve 93 is opened to allow the refrigerant to enter the exterior heat exchanger 38, and the pressure and temperature inside the exterior heat exchanger 38 are increased,
Similarly, shortage of the working refrigerant amount can be prevented.

When the above injection control is completed, the flow shifts to step S2 shown in FIG. 3, and similar steps are repeated.

In this manner, as shown in FIG. 12, during the heating operation by controlling the refrigerant flow opening / closing valves 93 and 94, an appropriate amount of refrigerant flows into the flow path 100, and the refrigerant is supplied to the compressor 31 through the pressure resistor 101. It can be supplied to the suction side. Therefore, the amount of refrigerant to be injected can be adjusted in a larger range.For example, the amount of refrigerant to be injected can be adjusted according to the compressor discharge temperature _Td , and the refrigerant discharge refrigerant temperature can be more accurately reduced. it can.

That is, when the compressor discharge temperature _Td is high or when the compressor motor speed _Nc is high and _Td is likely to be high, the injection is performed to reduce _Td , and the _Td is too high to operate. , And the heating capacity can be maximized to improve the capacity.

FIG. 13 shows a configuration diagram of a refrigeration cycle according to the third embodiment. Since the basic configuration is almost the same as that of the first embodiment, the same reference numerals are given and the duplicated explanation is omitted.

In this embodiment, the injection control is performed in both the cooling and heating. Therefore, in order to form a heating return flow path, a flow path 111 connecting the four-way valve 90 and the refrigerant inflow side of the compressor 31 is provided, and the four-way valve 90 and the refrigerant outflow side of the outside heat exchanger 38 and the heat radiation Outflow side detour channel 11 between the vehicle interior heat exchanger 33
2 are provided. The outflow side detour channel 112 is provided with a pressure resistor 102.

In order to constitute the heating leakage permitting means, an outflow-side check valve 70 is provided in a flow passage arranged in line with the outflow-side bypass flow passage 112, and the four-way valve 90 is connected to the refrigerant inflow side of the heat exchanger 38 outside the vehicle compartment. A refrigerant flow on-off valve 94 is interposed as an inflow-side control valve therebetween.

In order to form the cooling return flow path,
The flow path 111 is provided, and a bypass flow path 113 is provided between the four-way valve 90, the refrigerant outflow side of the exterior heat exchanger 38, and the heat radiation interior heat exchanger 33. The bypass flow path 113 is provided with a pressure resistor 103.

In order to constitute the cooling leakage permitting means,
A check valve 92 arranged in parallel with the bypass flow path 113;
A refrigerant flow opening / closing valve 110 is provided as a control valve provided between the zero and the bypass flow path 113.

FIG. 14 is a flowchart showing a control example of the third embodiment.

This flowchart is similar to that of FIG.
Corresponds to the flowchart shown in FIG. Therefore, also in this embodiment, the basic control is performed according to the flowcharts shown in FIGS.

In this embodiment, when the injection control is started, first, in step S161 in FIG. 14, it is determined whether the operation state of the apparatus is the cooling operation.
It is determined whether the operation is the heating operation. If the operation is the cooling operation, the process proceeds to step S162. If the operation is the heating operation, the process proceeds to step S16.
Move to 3.

In step S162, since the cooling operation is being performed, the valve 110 is closed and the valve 94 is opened. Step S163
On the contrary, since the heating operation is performed, the valve 94 is closed and the valve 11 is closed.
Open 0.

Next, in step S164, it is determined whether or not the compressor discharge temperature _Td is higher than a predetermined set discharge temperature _{Td, set} and injection is necessary.
If _Td is higher than _{Td, set} , injection is required, and the valve 110 is opened in step S165.
Therefore, a part of the refrigerant flowing from the exterior heat exchanger 38 to the heat radiation interior heat exchanger 33 passes through the bypass flow path 113, the pressure resistor 103, the valve 110, and the flow path 111, and flows into the refrigerant suction side of the compressor 31. Supplied to the adiabatic expansion. Therefore,
The temperature of the refrigerant sucked into the compressor 31 is reduced, the volumetric efficiency is improved, the refrigerant circulation amount in the cycle is increased, and the cooling capacity can be improved.

In step S164, T _d is _set to T _{d, set}
If it is determined that it is below, the process proceeds to step S166. In step S166, it is determined whether the motor rotation speed _Nc is high and injection is necessary. That is, by comparing the compressor motor rotational speed N _c predetermined set rotational speed N _c, and _{The set,} N _c is higher than N _{c, The set,} the process proceeds to step S165, the same injection is performed.

In step S166, N _c becomes N _{c, set}
If it is determined that it is below, the process proceeds to step S167,
Valve 110 is closed. Therefore, if the discharge temperature of the compressor 31 is low and the number of revolutions is low, the injection is not performed, the working refrigerant amount of the cycle is properly secured, and the cooling capacity can be improved.

At the time of the heating operation, the process proceeds from step S163 to step S168, and T _d is set in the same manner as in step S164.
And T _{d, set} are compared. Step S16
In step 9, _Nc is compared with _{Nc, set in the same} manner as in step S166. If T _d is higher than T _{d, set} , N _c
Is higher than _{Nc, set, the} injection is necessary, so the process proceeds to step S170, and the valve 94 is opened.

If the compressor discharge temperature _Td is low and the compressor motor speed _Nc is low, step S17 is performed.
Move to 1.

In step S171, it is determined whether the outside air temperature is low and the liquid refrigerant accumulates in the vehicle exterior heat exchanger 38 and the amount of working refrigerant on the refrigeration cycle side is insufficient. Therefore, the temperature T _cond in the heat exchanger 38 outside the vehicle _compartment is _equal to the predetermined set temperature T
If it is lower than _{cond, set} , perform injection control,
The process proceeds to step S170 to supply the high-temperature and high-pressure refrigerant to the exterior heat exchanger 38. Temperature T of outside heat exchanger 38
_{If cond} is equal to or greater than T _{cond, set} , the process proceeds to step S172, and the valve 94 is closed.

When the above injection control is completed, the flow shifts to step S2 shown in FIG. 3, and similar steps are repeated.

With such control, during the heating operation,
As shown in FIG. 15, a part of the refrigerant flowing from the compressor 31 to the heat-radiating vehicle interior heat exchanger 33 flows into the vehicle exterior heat exchanger 38 via the pressure resistor 102 of the outflow-side bypass flow path 112, and is sufficient here. It is cooled to become a liquid refrigerant. The liquid refrigerant flows to the flow path 111 via the open valve 94 and the four-way valve 90, and flows into the refrigerant suction side of the compressor 31 from the flow path 111. The liquid refrigerant flowing into the refrigerant suction side of the compressor 31 is adiabatically expanded to reduce the refrigerant suction temperature and, consequently, the refrigerant discharge temperature. Therefore, the heating capacity can be improved as described above.

Further, in this embodiment, during the cooling operation,
As shown in FIG. 16, a part of the refrigerant flowing from the compressor 31 to the heat exchanger 38 outside the vehicle compartment and further flowing to the heat exchanger 33 for heat release inside the pressure resistor 103 of the bypass channel 113, the valve 110 in the open state, It flows into the flow path 111 via the four-way valve 90 and flows into the refrigerant suction side of the compressor 31. Therefore, by reducing the temperature of the suction refrigerant, the compressor 31 can improve the volumetric efficiency at the time of suctioning the refrigerant, and can also improve the cooling capacity.

FIG. 17 shows a configuration diagram of a refrigeration cycle according to the fourth embodiment. Since the basic configuration is almost the same as the configuration of the first embodiment shown in FIG. 2, the same reference numerals are given and the duplicated description is omitted.

In this embodiment, as in the third embodiment, the injection can be performed in any of the cooling and heating. The three-way valve 32 is used as the refrigerant flow switching means.

In order to form a heating return flow path, a flow path 114 connecting the refrigerant inflow side of the exterior heat exchanger 38 and the refrigerant suction side of the compressor is provided.
Refrigerant outlet side, three-way valve 32 and heat-radiating vehicle interior heat exchanger 3
3, an outflow-side detour channel 112 including the pressure resistor 102 is provided.

In order to form a cooling return flow path, the refrigerant outlet side of the heat-radiating vehicle interior heat exchanger 33, specifically, the outlet side of the liquid tank 36 and the refrigerant inlet side of the compressor 31 are connected. And the flow path 1 including the pressure resistor 104.
15 are provided.

In order to constitute the heating leakage permitting means, an outflow-side check valve 70 is provided in a flow passage arranged in line with the outflow-side bypass flow passage 112, and a refrigerant flow opening / closing valve 95 is provided in the flow passage 114 as a control valve. Has been established.

In order to constitute a cooling leakage permitting means, a refrigerant flow opening / closing valve 98 is provided in the flow passage 115 as a control valve.

FIG. 18 is a flowchart showing a control example of the fourth embodiment.

The control contents of this flowchart are almost the same as those of the third embodiment shown in FIG.

Therefore, step S181 corresponds to step S161 in FIG. 14, and hereinafter, step S182 will be the same as step S162, and step S183 will be the same as step S1.
63, step S184 to step S164, step S185 to step S165, step S1
86 corresponds to step S166, step S187 corresponds to step S167, and step S188 corresponds to step S1.
68, step S189 corresponds to step S169, step S190 corresponds to step S170, and step S1
Reference numeral 92 corresponds to step S172.

However, in the flowchart of FIG. 18, FIG.
The control valve is different from the flowchart of FIG.
That is, during the cooling operation, the valve 95 is closed in step S182, and the opening and closing of the valve 98 is controlled in steps S185 and S187. In the heating operation, step S
In step 183, the valve 98 is closed, and steps S190 and S19 are performed.
2, the valve 95 is controlled to open and close.

Therefore, during the heating operation, as shown in FIG.
Part of the refrigerant flowing from the compressor 31 through the three-way valve 32 to the heat-dissipating interior heat exchanger 33 flows into the exterior heat exchanger 38 via the pressure resistor 102 and becomes a liquid refrigerant.
Then, the refrigerant is supplied to the suction side of the compressor 31 through the valve 95 in the open state, and similarly to the above, the adiabatic expansion lowers the suction refrigerant temperature of the compressor 31 and eventually the discharge refrigerant temperature. Therefore, the heating capacity can be improved as described above.

In the cooling operation, as shown in FIG. 20, a part of the refrigerant flowing out of the liquid tank 36 is opened.
8. The air is similarly sucked into the suction side of the compressor 31 via the pressure resistor 104, so that the volume efficiency at the time of sucking the refrigerant can be improved, and the cooling capacity can be improved.

FIG. 21 shows a configuration diagram of a refrigeration cycle according to the fifth embodiment. Since the basic configuration is almost the same as that of the fourth embodiment shown in FIG. 20, the same reference numerals are given and duplicate explanations are omitted.

In this embodiment, the cooling and heating injection is performed with a simple structure. That is, the outflow side detour channel 112 and the channel 114 of the fourth embodiment are omitted. Therefore, the injection at the time of heating is performed as shown in FIG. 22, and the injection at the time of cooling is performed as shown in FIG. 23. Part of the refrigerant is supplied to the refrigerant suction side of the compressor 31 via the compressor.

Therefore, in this embodiment, the device can be manufactured at low cost.

FIG. 24 is a control diagram showing a case where the injection is properly switched between the injection and the non-injection based on the physical quantity such as the compressor refrigerant discharge temperature or the refrigerant suction temperature or the pressure related thereto. That is, in this example, when the compressor refrigerant discharge temperature is equal to or lower than the predetermined temperature, the injection is not performed because the refrigeration performance is improved by maintaining the amount of the refrigerant flowing through the heat-absorbing interior heat exchanger rather than by the injection. In addition, when the refrigerant discharge temperature is equal to or higher than a predetermined temperature, the temperature of the discharged refrigerant can be reduced by injection, and the refrigeration capacity can be improved by maximizing the compressor capacity.

[0145]

As is apparent from the above, according to the first aspect of the present invention, the refrigerant does not flow backward due to the flow path switching operation of the flow path switching means, and the refrigerant does not flow backward during the heating operation. In addition to radiating heat, heat is absorbed by the heat absorbing interior heat exchanger, and during cooling operation, heat is radiated by the exterior heat exchanger or both the exterior heat exchanger and the heat radiating interior heat exchanger. Since the heat is absorbed by the heat exchanger, the amount of heat absorbed by the heat absorbing vehicle interior heat exchanger and the work heat of the compressor during the heating operation are radiated by the heat releasing vehicle interior heat exchanger to improve the heating capacity and the weather conditions of the outside air. It is possible to operate even at a low outside temperature without being influenced by the above, and stable control is possible. After dehumidification by the heat absorbing vehicle interior heat exchanger, heating is performed by the heat radiating vehicle interior heat exchanger, so that dehumidifying and heating becomes possible. Reheating after the dehumidification of the conditioned air does not require the use of an electric heater or the like, thereby reducing power consumption. Since heating can be efficiently performed without using an electric heater or exhaust heat of an engine, the present invention can be applied not only to a car having an engine but also to a case where a large heat source such as a solar car or an electric car is not provided. Since the flow direction of the refrigerant is the same between the cooling and the heating, the cooling and heating device currently used for the vehicle can be applied without much change, which is advantageous in design.

In addition, the injection can be performed during at least one of the heating operation and the cooling operation. Therefore, the temperature of the refrigerant sucked into the compressor and, consequently, the temperature of the discharged refrigerant can be lowered, so that the maximum heating performance can be obtained. Can be improved. Therefore, the capacity can be improved without increasing the compressor input or the like, and a more economical device can be obtained.

According to the second aspect of the present invention, the adiabatic expansion of the refrigerant flowing into the compressor is promoted by the pressure resistor, and the injection can be performed with a small amount of the refrigerant.

According to the third aspect of the present invention, the injection can be achieved with a simple structure by using a check valve as the leak permitting means for heating or the leak permitting means for cooling, and the apparatus becomes inexpensive.

According to the fourth aspect of the present invention, the injection can be controlled by using a control valve as the heating leak permitting means or the cooling leak permitting means. Therefore, more accurate injection becomes possible.

According to the fifth aspect of the present invention, the injection can be performed during the heating operation, and the temperature of the refrigerant sucked into the compressor and, consequently, the temperature of the discharged refrigerant can be reduced. Therefore, the heating performance can be significantly improved, and the volumetric efficiency of the compressor is improved, so that the refrigerant flow rate of the cycle is increased, and the refrigeration capacity is also improved, so that the dehumidifying heating performance can be improved.

According to the sixth aspect of the present invention, the injection can be controlled, and the injection can be accurately performed while improving the dehumidifying and heating performance. Accordingly, the heating performance can be improved while accurately maintaining the anti-fog performance and the like of the windshield.

According to the seventh aspect of the present invention, the injection can be performed in any of the cooling and heating modes, and both the dehumidifying and heating performance and the cooling capacity can be improved.

According to the eighth aspect of the present invention, the injection can be performed in any of the cooling and heating.
Moreover, since a three-way valve is used as the refrigerant flow switching means, it can be manufactured at low cost.

According to the ninth aspect of the present invention, the injection can be performed in any of the cooling and heating. In addition, since the three-way valve is used and the refrigerant return flow path is shared for cooling and heating, the structure is extremely simple.

According to the tenth aspect of the present invention, the control valve can be controlled in accordance with the detection of the detecting means, so that an accurate injection is performed in accordance with at least one of the suction refrigerant temperature and the discharge refrigerant temperature of the compressor. Can be.

[Brief description of the drawings]

FIG. 1 is a block diagram according to a first embodiment of the present invention.

FIG. 2 is a configuration diagram of a refrigeration cycle according to a first embodiment of the present invention.

FIG. 3 is a flowchart according to the first embodiment of the present invention.

FIG. 4 is a flowchart according to the first embodiment of the present invention.

FIG. 5 is an operation explanatory view.

FIG. 6 is a flowchart according to the first embodiment of the present invention.

FIG. 7 is a flowchart according to the first embodiment of the present invention.

FIG. 8 is a flowchart according to the first embodiment of the present invention.

FIG. 9 is a configuration diagram of a refrigeration cycle according to a second embodiment of the present invention.

FIG. 10 is a flowchart according to a second embodiment of the present invention.

FIG. 11 is a flowchart according to a second embodiment of the present invention.

FIG. 12 is an operation explanatory view.

FIG. 13 is a configuration diagram of a refrigeration cycle according to a third embodiment of the present invention.

FIG. 14 is a flowchart according to a third embodiment of the present invention.

FIG. 15 is an operation explanatory view.

FIG. 16 is an operation explanatory view.

FIG. 17 is a configuration diagram of a refrigeration cycle according to a fourth embodiment of the present invention.

FIG. 18 is a flowchart according to a fourth embodiment of the present invention.

FIG. 19 is an operation explanatory view.

FIG. 20 is an operation explanatory view.

FIG. 21 is a configuration diagram of a refrigeration cycle according to a fifth embodiment of the present invention.

FIG. 22 is an operation explanatory view.

FIG. 23 is an operation explanatory view.

FIG. 24 is a control diagram illustrating an example of injection control.

FIG. 25 is a configuration diagram of a refrigeration cycle according to a conventional example.

FIG. 26 is a configuration diagram of a refrigeration cycle of a new heat pump type cooling / heating device for a vehicle.

[Explanation of symbols]

 Reference Signs List 31 compressor 32 three-way valve (refrigerant flow path switching means) 33 heat-exchange vehicle interior heat exchanger 34 expansion valve (expansion means) 35 heat-absorption vehicle interior heat exchanger 37 blower fan (blowing means) 38 exterior heat exchanger 43 control Device 70 Outflow-side check valve (leakage permitting means for heating) 90 Four-way valve (refrigerant flow path switching means) 93 Refrigerant flow on-off valve (outflow-side control valve) 98, 99 Refrigerant flow on-off valve (control valve) 100, 111, 114, 115 Flow paths 101, 102, 103, 104 Pressure resistor 112 Outflow side detour channel 113 Detour channel

Claims (10)

(57) [Claims] A compressor that adds work to the refrigerant; a vehicle exterior heat exchanger that is connected to a refrigerant discharge side of the compressor and radiates heat of the refrigerant to the outside air; and a refrigerant that is connected to a refrigerant discharge side of the compressor. A heat-exchange vehicle interior heat exchanger for exchanging heat with air introduced by a blower to generate warm air-conditioned air; an expansion device connected to a refrigerant outflow side of the heat-exchange vehicle interior heat exchanger; The expansion unit is connected to the refrigerant outlet side of the expansion unit and the refrigerant suction side of the compressor, and transfers the heat of the air introduced by the blowing unit to the expansion unit from at least one of the exterior heat exchanger and the heat radiation interior heat exchanger. A heat absorbing interior heat exchanger for exchanging heat with the refrigerant supplied through the heat exchanger to produce cold conditioned air; a refrigerant discharging side of the compressor, a refrigerant for the exterior heat exchanger and a refrigerant for the heat radiation interior heat exchanger. The refrigerant discharged from the compressor, which is provided between the heat exchanger and the inlet side, is introduced into at least the exterior heat exchanger during the cooling operation, and is bypassed from the exterior heat exchanger during the heating operation to avoid the heat release from the interior of the vehicle. A refrigerant flow switching means to be introduced into the exchanger, a heating return flow path connecting between a refrigerant inflow side of the exterior heat exchanger and a refrigerant suction side of the compressor during a heating operation, and a cooling return operation during a cooling operation. At least one of a cooling return flow path that connects between a refrigerant outflow side of the vehicle exterior heat exchanger or a refrigerant outflow side of the heat radiation interior vehicle heat exchanger and a refrigerant suction side of the compressor is provided. A part of the refrigerant flowing from the refrigerant flow switching means to the heat-radiating vehicle interior heat exchanger is allowed to be supplied to the refrigerant suction side of the compressor via the vehicle exterior heat exchanger and the heating return flow path. For heating Leakage permitting means, and a part of the refrigerant flowing from the exterior heat exchanger to the heat radiation interior heat exchanger and the heat absorption interior heat exchanger during the cooling operation through the cooling return flow path. A heat pump type cooling / heating apparatus for a vehicle, wherein at least one of cooling air leakage permitting means for permitting supply to a suction side is provided. 2. The heat pump type cooling and heating apparatus for a vehicle according to claim 1, wherein a pressure resistor is provided for passing the refrigerant allowed to leak by the heating leak permitting means or the cooling leak permitting means. A heat pump type cooling / heating device for vehicles. 3. The heat pump type cooling / heating device for a vehicle according to claim 1, wherein the heating leak permitting means or the cooling leak permitting means allows a forward flow and a reverse flow. A heat pump type cooling / heating device for a vehicle, characterized in that the check valve is a check valve that allows a specified amount of refrigerant leakage. 4. The heat pump type cooling / heating apparatus for a vehicle according to claim 1, wherein the heating leak permitting means or the cooling leak permitting means is a control valve. Type air conditioner. 5. A compressor for adding work to the refrigerant, a vehicle exterior heat exchanger connected to the refrigerant discharge side of the compressor and radiating heat of the refrigerant to the outside air, and a refrigerant connected to the refrigerant discharge side of the compressor. A heat-exchange vehicle interior heat exchanger for exchanging heat with air introduced by a blower to generate warm air-conditioned air; an expansion device connected to a refrigerant outflow side of the heat-exchange vehicle interior heat exchanger; The expansion unit is connected to the refrigerant outlet side of the expansion unit and the refrigerant suction side of the compressor, and transfers the heat of the air introduced by the blowing unit to the expansion unit from at least one of the exterior heat exchanger and the heat radiation interior heat exchanger. A heat absorbing interior heat exchanger for exchanging heat with the refrigerant supplied through the air to generate cold conditioned air; a refrigerant discharging side of the compressor, a refrigerant of the exterior heat exchanger and a refrigerant of the heat radiation interior heat exchanger. The refrigerant discharged from the compressor, which is provided between the heat exchanger and the inlet side, is introduced into at least the exterior heat exchanger during the cooling operation, and is bypassed from the exterior heat exchanger during the heating operation to avoid the heat release from the interior of the vehicle. A refrigerant flow switching means for introducing the refrigerant into the heat exchanger, wherein the refrigerant flow switching means is a four-way valve, and a refrigerant inflow side of the exterior heat exchanger and the refrigerant of the compressor via the four-way valve during a heating operation. Providing a flow path that can be connected to the suction side, between the refrigerant outflow side of the exterior heat exchanger and the four-way valve and the heat radiation interior heat exchanger, the outflow direction from the exterior heat exchanger A heat pump type cooling / heating device for a vehicle, comprising an outflow-side check valve for allowing a specified amount of refrigerant to leak in a forward direction and in a reverse direction. 6. A compressor that adds work to the refrigerant, a vehicle exterior heat exchanger connected to the refrigerant discharge side of the compressor and radiating heat of the refrigerant to the outside air, and a refrigerant connected to the refrigerant discharge side of the compressor. A heat-exchange vehicle interior heat exchanger for exchanging heat with air introduced by a blower to generate warm air-conditioned air; an expansion device connected to a refrigerant outflow side of the heat-exchange vehicle interior heat exchanger; The expansion unit is connected to the refrigerant outlet side of the expansion unit and the refrigerant suction side of the compressor, and transfers the heat of the air introduced by the blowing unit to the expansion unit from at least one of the exterior heat exchanger and the heat radiation interior heat exchanger. A heat absorbing interior heat exchanger for exchanging heat with the refrigerant supplied through the air to generate cold conditioned air; a refrigerant discharging side of the compressor, a refrigerant of the exterior heat exchanger and a refrigerant of the heat radiation interior heat exchanger. The refrigerant discharged from the compressor, which is provided between the heat exchanger and the inlet side, is introduced into at least the exterior heat exchanger during the cooling operation, and is bypassed from the exterior heat exchanger during the heating operation to avoid the heat release from the interior of the vehicle. A refrigerant flow switching means for introducing the refrigerant into the heat exchanger, wherein the refrigerant flow switching means is a four-way valve, and a refrigerant inflow side of the exterior heat exchanger and the refrigerant of the compressor via the four-way valve during a heating operation. A flow path enabling connection with the suction side is provided, and an outflow side control valve is provided between the refrigerant outflow side of the exterior heat exchanger and the four-way valve and the heat radiation interior heat exchanger. Heat pump type air conditioner for vehicles. 7. A compressor for adding work to the refrigerant, a vehicle exterior heat exchanger connected to the refrigerant discharge side of the compressor and radiating heat of the refrigerant to the outside air, and a refrigerant connected to the refrigerant discharge side of the compressor. A heat-exchange vehicle interior heat exchanger for exchanging heat with air introduced by a blower to generate warm air-conditioned air; an expansion device connected to a refrigerant outflow side of the heat-exchange vehicle interior heat exchanger; The expansion unit is connected to the refrigerant outlet side of the expansion unit and the refrigerant suction side of the compressor, and transfers the heat of the air introduced by the blowing unit to the expansion unit from at least one of the exterior heat exchanger and the heat radiation interior heat exchanger. A heat absorbing interior heat exchanger for exchanging heat with the refrigerant supplied through the air to generate cold conditioned air; a refrigerant discharging side of the compressor, a refrigerant of the exterior heat exchanger and a refrigerant of the heat radiation interior heat exchanger. The refrigerant discharged from the compressor, which is provided between the heat exchanger and the inlet side, is introduced into at least the exterior heat exchanger during the cooling operation, and is bypassed from the exterior heat exchanger during the heating operation to avoid the heat release from the interior of the vehicle. A refrigerant flow switching means for introducing the heat exchanger into a heat exchanger, wherein the refrigerant flow switching means is a four-way valve, and during the heating operation, the refrigerant inflow side of the exterior heat exchanger and the compressor through the four-way valve. A flow path that enables connection with a refrigerant inflow side and that can connect a refrigerant outflow side of the exterior heat exchanger and a refrigerant inflow side of the compressor via the four-way valve during cooling operation; An outflow-side bypass flow path for bypassing the flow of the refrigerant via a pressure resistor is provided between the refrigerant outflow side of the exchanger and the four-way valve and the heat-radiating vehicle interior heat exchanger, and the four-way valve and the outside of the vehicle interior are provided. The refrigerant outlet side of the heat exchanger and the discharge A bypass flow path for bypassing the refrigerant flow via the pressure resistor between the refrigerant inflow side of the vehicle interior heat exchanger, and a flow path parallel to the outflow side bypass flow path, wherein the exterior heat exchanger An outflow-side check valve having an outflow direction from the forward direction as a forward direction is provided, and a check valve having an outflow direction from the four-way valve as a forward direction is provided in a flow path parallel to the bypass flow path. Heat pump type air conditioner for vehicles. 8. A compressor for adding work to the refrigerant, a vehicle exterior heat exchanger connected to the refrigerant discharge side of the compressor and radiating heat of the refrigerant to the outside air, and a refrigerant connected to the refrigerant discharge side of the compressor. A heat-exchange vehicle interior heat exchanger for exchanging heat with air introduced by a blower to generate warm air-conditioned air; an expansion device connected to a refrigerant outflow side of the heat-exchange vehicle interior heat exchanger; The expansion unit is connected to the refrigerant outlet side of the expansion unit and the refrigerant suction side of the compressor, and transfers the heat of the air introduced by the blowing unit to the expansion unit from at least one of the exterior heat exchanger and the heat radiation interior heat exchanger. A heat absorbing interior heat exchanger for exchanging heat with the refrigerant supplied through the air to generate cold conditioned air; a refrigerant discharging side of the compressor, a refrigerant of the exterior heat exchanger and a refrigerant of the heat radiation interior heat exchanger. The refrigerant discharged from the compressor, which is provided between the heat exchanger and the inlet side, is introduced into at least the exterior heat exchanger during the cooling operation, and is bypassed from the exterior heat exchanger during the heating operation to avoid the heat release from the interior of the vehicle. A refrigerant flow switching means for introducing the refrigerant into the heat exchanger, wherein the refrigerant flow switching means is a three-way valve, and a flow path enabling connection between a refrigerant inflow side of the exterior heat exchanger and a refrigerant suction side of the compressor. An outflow-side bypass flow path that bypasses the flow of the refrigerant via a pressure resistor is provided between the refrigerant outflow side of the exterior heat exchanger and the three-way valve and the heat radiation interior heat exchanger, A refrigerant outlet side of the heat-radiating vehicle interior heat exchanger and a refrigerant intake side of the compressor are connected by a flow path including a pressure resistor. An outflow check valve with the outflow direction from the heat exchanger as the forward direction A heat pump type air conditioner for a vehicle, wherein the air conditioner is provided. 9. A compressor that adds work to the refrigerant, a vehicle exterior heat exchanger connected to the refrigerant discharge side of the compressor and radiating heat of the refrigerant to the outside air, and a refrigerant connected to the refrigerant discharge side of the compressor. A heat-exchange vehicle interior heat exchanger for exchanging heat with air introduced by a blower to generate warm air-conditioned air; an expansion device connected to a refrigerant outflow side of the heat-exchange vehicle interior heat exchanger; The expansion unit is connected to the refrigerant outlet side of the expansion unit and the refrigerant suction side of the compressor, and transfers the heat of the air introduced by the blowing unit to the expansion unit from at least one of the exterior heat exchanger and the heat radiation interior heat exchanger. A heat absorbing interior heat exchanger for exchanging heat with the refrigerant supplied through the air to generate cold conditioned air; a refrigerant discharging side of the compressor, a refrigerant of the exterior heat exchanger and a refrigerant of the heat radiation interior heat exchanger. The refrigerant discharged from the compressor, which is provided between the heat exchanger and the inlet side, is introduced into at least the exterior heat exchanger during the cooling operation, and is bypassed from the exterior heat exchanger during the heating operation to avoid the heat release from the interior of the vehicle. A refrigerant flow switching means for introducing the refrigerant into the heat exchanger, wherein a refrigerant outflow side of the heat radiation interior heat exchanger and a refrigerant suction side of the compressor are connected by a flow path having a pressure resistor. A heat pump type cooling / heating device for vehicles. 10. The heat pump type cooling and heating apparatus for a vehicle according to claim 4, wherein said detecting means detects an element related to at least one of a suction refrigerant temperature and a discharge refrigerant temperature of said compressor; And a control means for controlling the control valve in accordance with the detection of the means.