JP6340279B2 - Air conditioner for vehicles - Google Patents

Description

  The present invention relates to a vehicle air conditioner mounted on, for example, an automobile.

  2. Description of the Related Art Conventionally, a vehicle air conditioner that includes a heat pump device and a heater core to which engine cooling water is supplied is known (see, for example, Patent Document 1). The heat pump device of Patent Document 1 includes a compressor that compresses a refrigerant, a vehicle exterior heat exchanger that is disposed outside the vehicle, a pressure reducing valve that depressurizes the pressure of the refrigerant, and an air conditioning casing that is disposed inside the vehicle. The vehicle interior heat exchanger for cooling and the vehicle interior heat exchanger for heating. In the cooling operation mode, the refrigerant discharged from the compressor flows through the heating vehicle interior heat exchanger and the vehicle exterior heat exchanger to dissipate the heat, and then the pressure is reduced by the pressure reducing valve and flows to the cooling vehicle interior heat exchanger. On the other hand, in the heating operation mode, the refrigerant discharged from the compressor is allowed to flow to the heating vehicle interior heat exchanger, and then flows to the vehicle exterior heat exchanger to be sucked into the compressor.

  Moreover, in patent document 1, the warm air path through which the air which passes a heating vehicle interior heat exchanger distribute | circulates inside the air-conditioning casing, and the bypass channel through which the air which does not pass a heating vehicle interior heat exchanger distribute | circulates. The temperature of the conditioned air is adjusted by adjusting the air volume ratio between the hot air passage and the bypass passage with an air mix door. A heater core is disposed inside the warm air passage on the downstream side in the air flow direction of the air mix door and on the upstream side in the air flow direction of the heating interior heat exchanger.

JP 2009-202736 A

  By the way, in the air conditioning casing, in addition to the hot air passage, a bypass passage is formed in parallel, and further downsizing of the air conditioning casing is desired. It is difficult to secure. In Patent Document 1, since the heater core is disposed inside the hot air passage on the downstream side of the air flow of the air mix door, the size of the heater core must be accommodated in the hot air passage. Difficult to make. In addition, the heater core generally includes a header tank that does not directly contribute to heat exchange, and the presence of this header tank cuts the air passage surface effective for heat exchange, and consequently the heating performance of the heater core is reduced. .

  Moreover, at the time of heating operation, there is a demand for reducing the energy consumed by heating as much as possible by effectively using the heat generated by the equipment mounted on the vehicle.

  This invention is made | formed in view of this point, The place made into the objective is to reduce the energy consumed by heating, improving the heating performance of the air in heating operation mode.

  In order to achieve the above object, in the present invention, an air heater to which a heat exchange medium is supplied from a device that generates heat from a vehicle is provided so as to face the hot air passage and the bypass passage, and the amount of heat supplied to the air heater is reduced. It was made possible to change.

The first invention is
A compressor for compressing the refrigerant;
An outdoor heat exchanger disposed outside the vehicle;
A first vehicle interior heat exchanger disposed in the vehicle interior;
A second vehicle interior heat exchanger disposed downstream of the first vehicle interior heat exchanger in the flow direction of air-conditioning air in the vehicle interior;
A first and a second pressure reducing valve;
In the cooling operation mode, the refrigerant discharged from the compressor flows through the second vehicle interior heat exchanger and the vehicle exterior heat exchanger, and is then decompressed by the second pressure reducing valve, so that the first vehicle interior heat exchanger is used. In the heating operation mode, the refrigerant discharged from the compressor is flowed to the second vehicle interior heat exchanger, and then the pressure is reduced by the first pressure reducing valve to exchange the heat outside the vehicle. In a vehicle air conditioner equipped with a heat pump device configured to flow into a container and suck into the compressor,
Inside the air conditioning casing that houses the first vehicle interior heat exchanger and the second vehicle interior heat exchanger, a hot air passage through which the air that has passed through the second vehicle interior heat exchanger flows, and the air 2. A bypass passage that flows by bypassing the vehicle interior heat exchanger, and an air heater that is disposed so as to face the hot air passage and the bypass passage and that is supplied with a heat exchange medium from a device that generates heat from the vehicle is provided. And
A heat supply variable means for changing the heat supply supplied to the air heater, and a controller for controlling the heat pump device and the heat supply variable means,
When the control device is operating the heat pump device in the heating operation mode, if the air temperature in the passenger compartment becomes equal to or higher than the target blowing air temperature to the passenger compartment, the heating operation capability of the heat pump device is reduced. The heat supply amount to the air heater by the supply heat amount varying means is reduced.

  According to this configuration, in the cooling operation mode, the second vehicle interior heat exchanger and the vehicle exterior heat exchanger serve as radiators, and the first vehicle interior heat exchanger serves as a heat absorber. Air-conditioning air is cooled by the first vehicle interior heat exchanger.

  On the other hand, in the heating operation mode, the second vehicle interior heat exchanger serves as a radiator, and the vehicle exterior heat exchanger serves as a heat absorber. The air is heated by an air heater to which a heat exchange medium is supplied from a device that generates heat from the vehicle, and then heated by a second vehicle interior heat exchanger. At this time, since the air heater is disposed so as to face the bypass passage and the hot air passage, a wide air passage area of the air heater is ensured. Thereby, the heating performance of the air by an air heater increases.

  Moreover, since the air heater is located upstream of the second vehicle interior heat exchanger, the temperature of the air flowing into the second vehicle interior heat exchanger becomes high. Therefore, the amount of energy consumed by the compressor during the heating operation mode can be reduced.

  Furthermore, when the air temperature in the passenger compartment becomes equal to or higher than the target blowing air temperature in the heating operation mode, the heating operation capability of the heat pump device is reduced first, so that the amount of energy consumed by the compressor can be reduced.

According to a second invention, in the first invention,
The supply heat amount varying means is switched between a supply state in which a heat exchange medium is supplied to the air heater and a bypass state in which the air heater is bypassed and allowed to flow.

  According to this configuration, in the cooling operation mode, the heat exchange medium is not supplied to the air heater by setting the supply heat amount variable means to the bypass state. Thereby, the cooling performance is improved.

According to a third invention, in the first invention,
The supply heat amount variable means includes a variable flow pump that changes a flow rate of a heat exchange medium supplied to the air heater.

  According to this configuration, it is possible to finely adjust the amount of heat supplied to the air heater.

According to a fourth invention, in the first invention,
The controller controls the outside heat exchanger outside the vehicle to an intermediate pressure of a heat pump cycle so that the first vehicle interior heat exchanger serves as a heat absorber, and the second vehicle interior heat exchanger serves as a radiator. The heat pump device is controlled so as to be in a mode, and a heat exchange medium is supplied to the air heater in the dehumidifying heating operation mode.

  According to this configuration, in the dehumidifying and heating operation mode, it is possible to reduce the capacity of the heat pump device on the heating side using the heat source of the vehicle.

A fifth invention is the fourth invention,
When operating the heat pump device in the dehumidifying and heating operation mode, the control device reduces the heating operation capability of the heat pump device when the air temperature in the vehicle compartment is equal to or higher than the target blown air temperature to the vehicle compartment. Then, it is comprised so that the amount of heat supplied to the said air heater by the said supply heat amount variable means may be reduced.

  According to this configuration, when the air temperature in the passenger compartment becomes equal to or higher than the target blowing air temperature in the dehumidifying heating operation mode, the heating operation capacity of the heat pump device is reduced first, so that the amount of energy consumed by the compressor can be reduced. Become.

A sixth invention is the first or fifth invention, wherein
An air mix door for adjusting the air volume ratio of the hot air passage and the bypass passage;
When the air temperature in the passenger compartment becomes equal to or higher than the target air temperature to the passenger compartment while the heat pump device is operating in the heating operation mode, the control device sets the air volume ratio of the bypass passage by the air mix door. After the increase, the supply heat amount to the air heater by the supply heat amount varying means is reduced.

  According to this configuration, it is possible to reduce the amount of energy consumed by the heat pump device.

A seventh invention is the first or fifth invention, wherein
In the air conditioning casing, an electric heater for heating the air conditioning air is disposed,
When the air temperature in the passenger compartment is equal to or higher than the target air temperature for the passenger compartment when the heat pump device is operating in the heating operation mode, the control device is configured to reduce the heating operation capability of the heat pump device. In addition, the heating capacity of the electric heater is reduced before the amount of heat supplied to the air heater by the supply heat amount varying means is reduced.

  According to this configuration, the amount of energy consumption can be reduced by preferentially reducing the heating capacity of the electric heater.

  According to the first aspect of the present invention, the hot air passage and the bypass passage are formed in the air conditioning casing that houses the first heat exchanger and the second heat exchanger of the heat pump device, and heat is generated from the heat generating device of the vehicle. Since the air heater to which the exchange medium is supplied is provided so as to face the hot air passage and the bypass passage, the air heater having a wide air passage surface can be obtained, and thus the air heating performance can be improved. . Moreover, since the temperature of the air flowing into the second vehicle interior heat exchanger becomes high, the amount of energy consumed by the compressor in the heating operation mode can be reduced. Furthermore, when the air temperature in the passenger compartment becomes equal to or higher than the target blowing air temperature in the heating operation mode, the heating operation capacity of the heat pump device can be reduced first, which also reduces the amount of energy consumed by the compressor. it can.

  According to the second invention, since the heat exchange medium can be prevented from being supplied to the air heater during the cooling operation mode, the cooling performance can be improved.

  According to the third invention, since the flow rate of the heat exchange medium supplied to the air heater can be changed by the variable flow pump, the amount of heat supplied to the air heater can be finely adjusted.

  According to the fourth invention, since the heat exchange medium is supplied to the air heater in the dehumidifying and heating operation mode, the capacity on the heating side can be reduced using the heat source of the vehicle, and the energy consumption is reduced. be able to.

  According to the fifth invention, when the air temperature in the passenger compartment becomes higher than the target blown air temperature in the dehumidifying heating operation mode, the heating operation capacity of the heat pump device is reduced first, so that the amount of energy consumed by the compressor is reduced. Can do.

  According to the sixth aspect of the invention, when the air temperature in the passenger compartment becomes equal to or higher than the target blowing air temperature in the heating operation mode, the air volume ratio of the bypass passage by the air mix door is increased, so that the amount of energy consumption can be reduced.

  According to the seventh aspect of the present invention, when the air temperature in the passenger compartment becomes equal to or higher than the target blowing air temperature in the heating operation mode, the heating capacity of the electric heater can be preferentially reduced, so that the amount of energy consumption can be reduced. it can.

It is the schematic of the vehicle air conditioner which concerns on embodiment. It is a block diagram of a vehicle air-conditioning control device. FIG. 2 is a view corresponding to FIG. 1 in a heating operation mode. FIG. 2 is a view corresponding to FIG. 1 in a dehumidifying and heating operation mode. FIG. 2 is a view corresponding to FIG. 1 in a dehumidifying operation mode. FIG. 2 is a view corresponding to FIG. 1 in a cooling operation mode. It is a flowchart which shows the control procedure of the main routine by a control apparatus. It is a flowchart which shows the control procedure of heating operation mode. It is a flowchart which shows the control procedure of dehumidification heating operation mode. It is a flowchart which shows the control procedure of dehumidification operation mode. It is a flowchart which shows the control procedure of air_conditionaing | cooling operation mode.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. It should be noted that the following description of the preferred embodiment is merely illustrative in nature, and is not intended to limit the present invention, its application, or its use.

  FIG. 1 is a diagram showing a schematic configuration of a vehicle air conditioner 1 according to an embodiment of the present invention, and FIG. 2 is a block diagram of a control device 12 of the vehicle air conditioner 1 according to an embodiment of the present invention. The vehicle air conditioner 1 includes an air conditioning unit 10, a heat pump device H, a heater core (air heater) 11, and a control device 12. The heater core 11 is supplied with engine coolant (heat exchange medium) from the engine E of the vehicle.

  That is, the engine E is mounted on the vehicle. The water jacket (not shown) formed in the cylinder block of the engine E includes an engine cooling water outflow pipe 2 through which engine cooling water flows out and engine cooling water outflowed from the engine cooling water outflow pipe 2 into the water jacket. A return return pipe 3 is connected. The engine E is provided with a cooling water pump 17 for sending engine cooling water to the engine cooling water outflow pipe 2. The cooling water pump 17 is composed of an electric pump (variable flow rate pump) controlled by the control device 12 as shown in FIG. 2, and the amount of engine cooling water supplied per unit time can be arbitrarily changed. It can be done. The cooling water pump 17 may be a pump that is driven by the power of the engine E.

  The downstream side of the engine cooling water outflow pipe 2 is connected to the engine cooling water inflow portion of the heater core 11. A first radiator pipe 4 is connected to the engine coolant outflow portion of the heater core 11. The first radiator pipe 4 is connected to a radiator A of the vehicle. A return pipe 3 is connected to the middle part of the first radiator pipe 4. Cooling air is sent to the radiator A by the electric fan F.

  The radiator A is connected to a second radiator pipe 5. The second radiator pipe 5 is connected to the middle part of the engine coolant outflow pipe 2 via a thermostat device B. The thermostat device B causes the engine cooling water in the engine cooling water outflow pipe 2 to flow through the second radiator pipe 5 when the temperature of the engine cooling water exceeds a predetermined temperature, and the second radiator pipe 5 when the temperature is lower than the predetermined temperature. It is a well-known thing comprised so that it may not flow. The predetermined temperature can be set to, for example, a temperature at which the engine E has been warmed up. The thermostat device B is configured to constantly flow engine cooling water to the heater core 11 side.

  A hot water valve C is provided closer to the heater core 11 than the thermostat device B of the engine coolant outlet pipe 2. The hot water valve C is connected to a bypass pipe 4 a that branches off from a middle part of the first radiator pipe 4. The hot water valve C is configured by a known electric flow control valve and is controlled by the control device 12. The hot water valve C is supplied by the control device 12 to supply the engine cooling water in the engine cooling water outflow pipe 2 to the heater core 11 and does not flow into the bypass pipe 4a (open state of the hot water valve C), and the engine cooling water outflow pipe 2 can be switched to a bypass state (the closed state of the hot water valve C) that flows to the bypass pipe 4a without flowing the engine coolant in the heater core 11, and the amount of engine coolant that flows to the heater core 11 in an intermediate state between them. Can be adjusted. That is, increasing the amount of engine cooling water flowing to the heater core 11 increases the amount of heat supplied to the heater core 11, while reducing the amount of engine cooling water flowing to the heater core 11 supplies it to the heater core 11. Since the supply heat amount decreases, the hot water valve C is a supply heat amount variable means for changing the supply heat amount supplied to the heater core 11.

  Further, since the electric cooling water pump 17 described above is provided in the engine E of this vehicle, the discharge amount of the cooling water pump 17 can be changed. Increasing the discharge amount of the cooling water pump 17 increases the supply heat amount (engine cooling water amount) supplied to the heater core 11, while the supply amount supplied to the heater core 11 by decreasing the discharge amount of the cooling water pump 17. Since the amount of heat decreases, the cooling water pump 17 also serves as a supply heat amount variable means for changing the supply heat amount supplied to the heater core 11.

  Although not shown, the heater core 11 is a tube-and-fin type heat exchanger configured by stacking a plurality of tubes and fins. Header tanks (not shown) are respectively provided at both ends of the tubes, and the engine coolant outflow pipe 2 and the first radiator pipe 4 are connected to the header tanks so that the engine coolant is heated by the heater core. After being supplied to the heater 11, the heater core 11 is discharged. The air passage portion of the heater core 11 is a portion where fins are disposed except for the header tank.

  The heat pump device H includes a compressor 20 that compresses a refrigerant, a vehicle exterior heat exchanger 21 that is disposed outside the vehicle, and an upstream vehicle interior heat exchanger (first vehicle interior heat) that is disposed in the vehicle interior. Exchanger) 22 and a downstream vehicle interior heat exchanger (second vehicle interior heat exchanger) 23 disposed downstream of the upstream vehicle interior heat exchanger 22 in the flow direction of the air-conditioning air in the vehicle interior. And a first pressure reducing valve 24, a second pressure reducing valve 25, a liquid receiver 26, and a refrigerant flow switching valve 27.

  The compressor 20 is an electric compressor that operates by being supplied with electric power from a battery (not shown) mounted on the vehicle, for example, and can be configured to change the refrigerant discharge amount per unit time by increasing or decreasing the rotation speed. Has been. When the rotation speed of the compressor 20 is zero, the refrigerant discharge amount becomes zero. The vehicle exterior heat exchanger 21 is disposed so as to overlap the radiator A in the front-rear direction at the front end of the engine room of the vehicle. Details of the upstream side vehicle interior heat exchanger 22 and the downstream side vehicle interior heat exchanger 23 will be described later.

  The heat pump device H includes first to fourth refrigerant pipes 31 to 34 through which refrigerant flows. The first refrigerant pipe 31 extends from the refrigerant discharge portion of the compressor 20 to the refrigerant inflow portion of the downstream vehicle interior heat exchanger 23. The refrigerant inflow part of the downstream side vehicle interior heat exchanger 23 is located downstream of the refrigerant outflow part in the air flow direction. The second refrigerant pipe 32 extends from the refrigerant outflow portion of the downstream-side vehicle interior heat exchanger 23 to the refrigerant inflow portion of the vehicle exterior heat exchanger 21. The third refrigerant pipe 33 extends from the refrigerant outflow portion of the vehicle exterior heat exchanger 21 to the refrigerant inflow portion of the upstream vehicle interior heat exchanger 22. A branch pipe 33 a is provided in the middle of the third refrigerant pipe 33. The refrigerant inflow portion of the upstream side vehicle interior heat exchanger 22 is located downstream of the refrigerant outflow portion in the air flow direction. The fourth refrigerant pipe 34 extends from the refrigerant outflow portion of the upstream side vehicle interior heat exchanger 22 to the refrigerant suction portion of the compressor 20. The liquid receiver 26 is disposed at a location near the compressor 20 in the middle of the fourth refrigerant pipe 34.

  The first pressure reducing valve 24 is disposed in the middle of the second refrigerant pipe 32. The second pressure reducing valve 25 is disposed at a position closer to the upstream side interior heat exchanger 22 than the branch pipe 33 a of the third refrigerant pipe 33. The first pressure-reducing valve 24 and the second pressure-reducing valve 25 are well-known electric types, and are controlled by the control device 12 to be fully closed from the state where the second refrigerant pipe 32 and the third refrigerant pipe 33 are fully opened, respectively. It is comprised so that it can be set as the arbitrary opening to the state made into.

  The refrigerant flow switching valve 27 is disposed in the middle of the fourth refrigerant pipe 34, and the branch pipe 33 a of the third refrigerant pipe 33 is connected to the refrigerant flow switching valve 27. The refrigerant flow switching valve 27 is an electric switching valve controlled by the control device 12, and the refrigerant flowing through the third refrigerant pipe 33 from the refrigerant outflow portion of the vehicle exterior heat exchanger 21 is transferred to the upstream vehicle interior heat. It is configured so that it can be switched between a state in which it flows through the exchanger 22 and does not flow through the fourth refrigerant pipe 34 and a state in which it flows through the fourth refrigerant pipe 34 without flowing through the upstream side heat exchanger 22. Yes.

  The air conditioning unit 10 includes an air conditioning casing 13 that houses an upstream side passenger compartment heat exchanger 22, a downstream side passenger compartment heat exchanger 23, and a heater core 11. An inside / outside air switching unit 14 is provided upstream of the air conditioning casing 13 in the air flow direction. The inside / outside air switching unit 14 includes an outside air introduction port 14a for introducing air outside the vehicle compartment (outside air) and an inside air introduction port 14b for introducing air inside the vehicle compartment (inside air). Inside the inside / outside air switching unit 14 is provided an inside / outside air switching door 14c for opening and closing the outside air introduction port 14a and the inside air introduction port 14b. The inside / outside air switching door 14c is driven by an inside / outside air switching actuator 14d controlled by the control device 12 shown in FIG. As shown in FIG. 1, the inside / outside air switching unit 14 has an inside air introduction mode in which the outside air introduction port 14a is fully closed and the inside air introduction port 14b is fully opened, and although not shown, the outside air introduction port 14a is fully opened and the inside air introduction port 14b. Can be switched to the outside air introduction mode in which is fully closed.

  The inside / outside air switching unit 14 is provided with a blower 15. The blower 15 includes a fan 15a and a blower motor 15b that rotationally drives the fan 15a. Air for air conditioning is taken in from the outside air inlet 14a or the inside air inlet 14b by the rotation of the fan 15a.

  Inside the air conditioning casing 13, an upstream passage R <b> 1 is formed to communicate with the inside / outside air switching unit 14 on the downstream side of the inside / outside air switching unit 14 in the air flow direction. The upstream side passage R1 is provided with the upstream side passenger compartment heat exchanger 22 and the heater core 11. The upstream side vehicle interior heat exchanger 22 is located upstream of the heater core 11 in the air flow direction.

  The upstream side vehicle interior heat exchanger 22 is configured by a tube and fin type heat exchanger similar to the heater core 11. The upstream vehicle interior heat exchanger 22 and the heater core 11 are both disposed so as to cross the entire upstream passage R1, and most of the air flowing through the upstream passage R1 is upstream of the upstream vehicle interior heat exchanger 22 and the heater core. 11 is passed. The air passage portion of the heater core 11 is disposed so as to face the air passage portion of the upstream side vehicle interior heat exchanger 22 from the downstream side in the air flow direction.

  Inside the air conditioning casing 13, a hot air passage R2 and a bypass passage R3 are formed downstream of the upstream passage R1 in the air flow direction. That is, the hot air passage R2 and the bypass passage R3 communicate with the downstream side of the upstream passage R1, and the air flowing through the upstream passage R1 can flow into the hot air passage R2 and the bypass passage R3. ing. The cross-sectional area of the hot air passage R2 and the cross-sectional area of the bypass passage R3 are set to be narrower than the cross-sectional area of the upstream-side passage R1. In this embodiment, the total cross-sectional area of the hot air passage R2 and the bypass passage R3 is set to be approximately the same as the cross-sectional area of the upstream passage R1.

  The air passage portion of the heater core 11 is disposed so as to face from the upstream end opening of the hot air passage R2 to the upstream end opening of the bypass passage R3. Therefore, the air that has passed through the heater core 11 flows into both the hot air passage R2 and the bypass passage R3.

  A downstream side passenger compartment heat exchanger 23 is disposed in the warm air passage R2. The downstream-side vehicle interior heat exchanger 23 is configured by a tube-and-fin type heat exchanger similar to the heater core 11. The downstream-side vehicle interior heat exchanger 23 is disposed so as to cross the entire warm air passage R2, and most of the air flowing through the hot air passage R2 passes through the downstream-side vehicle interior heat exchanger 23. ing. That is, the air that has passed through the downstream side heat exchanger 23 flows through the warm air passage R2.

  In the warm air passage R2, an electric heater 16 is disposed downstream of the downstream side passenger compartment heat exchanger 23 in the air flow direction. The electric heater 16 has a structure that generates heat when supplied with electric power. For example, the electric heater 16 includes an electric heater using a PTC element, and can heat the air-conditioning air inside the air-conditioning casing 13. It has become. As shown in FIG. 2, the electric heater 16 is controlled by the control device 12, and the heating capacity can be adjusted by changing the power supplied to the electric heater 16.

  The bypass passage R3 is a passage through which air that bypasses the downstream-side vehicle interior heat exchanger 23 flows. An air mix door 18 is disposed at upstream ends of the hot air passage R2 and the bypass passage R3 in the air flow direction. Therefore, the heater core 11 is disposed upstream of the air mix door 18 in the air flow direction.

  The air mix door 18 is disposed between the upstream side passenger compartment heat exchanger 22 and the downstream side passenger compartment heat exchanger 23, and the upstream end opening of the hot air passage R2 and the upstream end opening of the bypass passage R3. Is adjusted to adjust the ratio of the amount of air flowing through the warm air passage R2 and the amount of air flowing through the bypass passage R3. When the air mix door 18 fully closes the upstream end opening of the hot air passage R2 and fully opens the upstream end opening of the bypass passage R3, the air does not flow into the hot air passage R2 and reaches a maximum cooling state. When the upstream end opening of the passage R2 is fully opened and the upstream end opening of the bypass passage R3 is fully closed, air does not flow through the bypass passage R3 and the maximum heating state is established. The air mix door 18 is driven by an air mix actuator 18 a controlled by the control device 12. The opening degree of the warm air passage R2 and the bypass passage R3 by the air mix door 18 can be arbitrarily adjusted.

  In this embodiment, “the opening degree of the air mix door 18 is large” means that the opening degree of the bypass passage R3 is increased (the opening degree of the hot air passage R2 is reduced). “The opening is small” means that the opening of the bypass passage R3 is reduced (the opening of the hot air passage R2 is increased).

  Inside the air conditioning casing 13, an air mix space R <b> 4 communicating with the hot air passage R <b> 2 and the bypass passage R <b> 3 on the downstream side in the air flow direction is provided. The air mix space R4 is for collecting and mixing the air flowing through the hot air passage R2 and the bypass passage R3, and conditioned air is generated in the air mix space R4.

  A defroster air outlet 13a, a vent air outlet 13b, and a heat air outlet 13c are formed downstream of the air mix space R4 of the air conditioning casing 13 in the air flow direction so as to communicate with the air mix space R4. The defroster outlet 13a is for supplying conditioned air to the inner surface of the windshield (not shown), and is connected to a defroster nozzle (not shown) of the instrument panel. The vent outlet 13b is for supplying conditioned air to the upper body of the occupant and is connected to a vent nozzle (not shown) of the instrument panel. Further, the heat outlet 13c is opened in the vicinity of the foot of the passenger.

  The defroster outlet 13a is opened and closed by a defroster door 13d, the vent outlet 13b is opened and closed by a vent door 13e, and the heat outlet 13c is opened and closed by a heat door 13f. The defroster door 13d, the vent door 13e, and the heat door 13f are actuated by a blowing direction switching actuator 13g. The blowing direction switching actuator 13g is controlled by the control device 12. The blowing mode of the conditioned air is switched by opening / closing operations of the defroster door 13d, the vent door 13e, and the heat door 13f. For example, any one of a plurality of modes such as a defroster mode, a vent mode, a heat mode, and a bi-level mode is selected. Can be switched.

  As shown in FIG. 2, the air conditioner 1 is provided with an outside air temperature sensor 40, an inside air temperature sensor 41, a solar radiation amount sensor 42, a cooling water temperature sensor 43, an evaporator sensor 44, and an operation switch 45. The sensors 40 to 44 are connected to the control device 12 and output signals to the control device 12. The operation switch 45 is also connected to the control device 12 so that the control device 12 can detect the operation state by the passenger.

  The outside air temperature sensor 40 is a sensor for detecting the temperature of outside air, for example, disposed outside the passenger compartment at the front or side of the vehicle. The inside air temperature sensor 41 is disposed, for example, in the vicinity of the instrument panel in the passenger compartment, and is a sensor for detecting the temperature of the inside air. The solar radiation amount sensor 42 is a sensor for detecting the amount of solar radiation irradiated to the passenger compartment. The coolant temperature sensor 43 is a sensor for detecting the temperature of the engine coolant. The evaporator sensor 44 is disposed on the downstream side in the air flow direction of the upstream vehicle interior heat exchanger 22 and is a sensor for detecting the surface temperature of the upstream vehicle interior heat exchanger 22. The operation switch 45 is disposed, for example, on an instrument panel or the like. For example, an ON / OFF switch for the air conditioner 1, an air volume switch for increasing or decreasing the air flow, a temperature setting switch for setting the temperature of the passenger compartment, It is composed of an inside / outside air switching switch for switching between inside air circulation, outside air introduction and inside / outside air mixing modes, an auto switch for selecting whether or not to use auto air conditioner control, a blowing mode switching switch for switching the blowing direction, a defroster switch, and the like.

  Based on the signals (output values) output from the sensors 40 to 44 and the operation state of the operation switch 45, the control device 12 uses the inside / outside air switching actuator 14d, the air mix actuator 18a, the blowing direction switching actuator 13g, and the blower. The motor 15b, the electric heater 16, the compressor 20, the first pressure reducing valve 24, the second pressure reducing valve 25, the refrigerant flow switching valve 27, and the hot water valve C are controlled.

  That is, when the automatic air conditioner control is selected by the auto switch of the operation switch 45, the temperature outside the passenger compartment, the temperature inside the passenger compartment, the amount of solar radiation, the engine coolant temperature, the surface temperature of the upstream passenger compartment heat exchanger 22, Based on the set temperature or the like, the target blown air temperature of the conditioned air to be supplied into the vehicle interior is determined, the opening degree of the air mix door 18 is calculated so as to be the target blown air temperature, and the air mix door 18 The air mix door 18 is rotated by controlling the air mix actuator 18a so that the opening degree is reached. Further, the control of the heating capacity of the electric heater 16, the change of the rotation speed of the compressor 20, the change of the opening of the first pressure reducing valve 24 and the second pressure reducing valve 25, the opening of the refrigerant flow switching valve 27 and the hot water valve C are controlled. Make a change.

  A specific control procedure by the control device 12 will be described with reference to flowcharts shown in FIGS. The flowchart in FIG. 7 shows the main routine. In step SA1 after the start in this flowchart, the air conditioning mode is determined according to a known method. In this embodiment, the air conditioning mode basically has four modes of a heating operation mode, a dehumidifying heating operation mode, a dehumidifying operation mode, and a cooling mode. For example, when the outside heat exchanger 21 is frosted, the defrosting operation mode is selected. And so on. The air conditioning mode determination is performed based on a result of estimating which operation mode the occupant desires based on conditions such as the outside air temperature, the internal air temperature, and the set temperature by the occupant.

  If it determines with it being heating operation mode by step SA1, it will progress to step SA2 and will progress to step SA3, and heating operation control will be performed. The control procedure of the heating operation is shown in the flowchart of FIG. If it determines with it being dehumidification heating operation mode by step SA1, it will progress to step SA4 and will progress to step SA5, and dehumidification heating operation control will be performed. The control procedure of the dehumidifying and heating operation is shown in the flowchart of FIG. If it is determined in step SA1 that the dehumidifying operation mode is selected, the process proceeds to step SA6, and then proceeds to step SA7 where dehumidifying operation control is performed. The control procedure of the dehumidifying operation is shown in the flowchart of FIG. If it is determined in step SA1 that the cooling operation mode is set, the process proceeds to step SA8, and then proceeds to step SA9 to perform cooling operation control. The control procedure of the cooling operation is shown in the flowchart of FIG.

  A control procedure of the heating operation shown in the flowchart of FIG. 8 will be described. In step SB1, the air mix door 18 is fully heated, that is, the upstream end opening of the hot air passage R2 is fully opened, and the upstream end opening of the bypass passage R3 is fully closed.

  Then, the process proceeds to step SB2, and the hot water valve C is opened, that is, the engine cooling water in the engine cooling water outflow pipe 2 flows into the heater core 11. In step SB3 following step SB2, the heat pump device H is started to operate in the heating operation mode. In the heating operation mode shown in FIG. 3, the compressor 20 is operated, and the first pressure reducing valve 24 is set to an opening degree that exerts a pressure reducing action. Further, the refrigerant flow switching valve 27 is switched so that the refrigerant does not flow to the upstream side vehicle interior heat exchanger 22. Thereby, since the refrigerant | coolant of the high temperature state discharged from the compressor 20 flows into the downstream vehicle interior heat exchanger 23, the downstream vehicle interior heat exchanger 23 acts as a heat radiator. Moreover, since the refrigerant | coolant after pressure reduction flows into the vehicle exterior heat exchanger 21, the vehicle exterior heat exchanger 21 acts as a heat absorber. The refrigerant that has absorbed heat by the vehicle exterior heat exchanger 21 is sucked into the compressor 20. Further, the electric heater 16 is turned on.

  The air introduced into the air conditioning casing 13 first flows into the upstream side passage R1 and passes through the upstream side interior heat exchanger 22. Since the refrigerant does not flow through the upstream side vehicle interior heat exchanger 22, the air passing through the upstream side vehicle interior heat exchanger 22 is neither heated nor cooled. Thereafter, the air passes through the heater core 11. Since engine cooling water flows through the heater core 11, the engine cooling water and air exchange heat to heat the air.

  Then, the air flows into the warm air passage R2 and passes through the downstream-side vehicle interior heat exchanger 23. Since the high-temperature refrigerant flows through the downstream side vehicle interior heat exchanger 23, the air passing through the downstream side vehicle interior heat exchanger 23 is heated. The air that has passed through the downstream side heat exchanger 23 is also heated by the electric heater 16. The air heated by the electric heater 16 is supplied to the vehicle compartment from the air outlet corresponding to the air outlet mode through the air mix space R4. If light heating is sufficient, the heating capacity of the electric heater 16 is reduced or reduced to 0 before the rotation speed of the compressor 20 is reduced and before the opening degree of the air mix door 18 is adjusted. To do. Thereby, the energy consumption of the electric heater 16 can be reduced.

  In step SB4 following step SB3, compressor control is performed. The compressor control is control for changing the refrigerant discharge amount per unit time of the compressor 20, that is, the rotation speed of the compressor 20. In the compressor control, the current rotation speed of the compressor 20 is Nc. Nc is basically set according to conditions such as the outside air temperature, the inside air temperature, and the temperature set by the occupant. For example, Nc is raised when strong heating is desired. Specifically, when the air temperature (actual internal air temperature) in the vehicle compartment is lower than the target blown air temperature (target temperature) to the vehicle compartment, the rotation of the compressor 20 is determined by adding Nc to the current Nc by α. Increase the number. Thereby, the heating capability of the heat pump apparatus H increases. On the other hand, when the actual inside air temperature becomes equal to or higher than the target temperature, the rotational speed of the compressor 20 is reduced by setting Nc to a value obtained by subtracting α from the current Nc. Thereby, the heating capability of the heat pump apparatus H falls. The target temperature is calculated by the control device 12 according to a known method based on the outside air temperature, the inside air temperature, the set temperature by the occupant, and the like. The actual room temperature is a temperature detected by the room temperature sensor 41.

  When the process proceeds to step SB5 through step SB4, it is determined whether or not the rotational speed Nc of the compressor 20 has become zero. If it is determined NO in step SB5 and the rotation speed Nc of the compressor 20 is not 0, it is necessary to perform heating by the heat pump device H, so the process returns to step SB4 and the compressor control is repeated. When it is determined YES in step SB5 and the rotation speed Nc of the compressor 20 is 0, for example, the air temperature in the passenger compartment has increased until the heating by the heat pump device H becomes unnecessary, or the set temperature by the passenger Can be estimated. In this case, it progresses to step SB6 and hot water valve control is performed.

  The hot water valve control is open / close control of the hot water valve C. In the hot water valve control, the current opening degree of the hot water valve C (the engine coolant flow rate toward the heater core 11) is Qw. Qw is basically set according to conditions such as the outside air temperature, the inside air temperature, and the temperature set by the occupant. For example, when strong heating is desired, Qw is increased and the heater core 11 side is set. Increase engine coolant flow to Specifically, when the actual inside air temperature is lower than the target temperature, the engine coolant flow rate to the heater core 11 side is increased by setting Qw to a value obtained by adding β to the current Qw. Thereby, the heating capability of the heater core 11 increases. On the other hand, when the actual inside air temperature becomes equal to or higher than the target temperature, the flow rate of the engine coolant to the heater core 11 is decreased by setting Qw to a value obtained by subtracting β from the current Qw. Thereby, the heating capability of the heater core 11 falls.

  If it progresses to step SB7 through step SB6, it will be determined whether target temperature is higher than actual internal air temperature. If it is determined as YES in step SB7 and the target temperature is higher than the actual inside air temperature, the process proceeds to step SB8, where it is determined whether or not the opening degree Qw of the hot water valve C is the maximum (Max). If it determines with YES by step SB8 and it determines with the opening degree Qw of the hot water valve C being the maximum, it will return to step SB4 and will repeat compressor control. On the other hand, if it is determined NO in step SB8, the opening degree Qw of the hot water valve C is not the maximum, so the process returns to step SB6 and the hot water valve control is repeated.

  If it is determined as NO in step SB7, the process proceeds to step SB9, and it is determined whether or not the opening degree Qw of the hot water valve C is minimum (Min). If it is determined YES in step SB9 and the opening degree Qw of the hot water valve C is determined to be the minimum, the process proceeds to step SB10. On the other hand, if NO is determined in step SB9, the opening degree Qw of the hot water valve C is determined. Since it is not minimum, it returns to step SB6 and repeats warm water valve control.

  In step SB10, the current opening degree Md of the air mix door 18 is changed. That is, the opening degree Md is increased by adding the opening degree to the current opening degree Md of the air mix door 18 by θ. Thereby, since the opening degree of bypass passage R3 becomes large, it adjusts in the direction in which blowing air temperature falls.

  In step SB11 following step SB10, it is determined whether or not the target temperature is lower than the actual inside air temperature. When YES is determined in step SB11 and the target temperature is lower than the actual room air temperature, the process returns to step SB10 and the opening degree of the air mix door 18 is adjusted. If NO is determined in step SB11, the process proceeds to the return of the main routine shown in FIG.

  Next, the control procedure of the dehumidifying heating operation shown in the flowchart of FIG. 9 will be described. In step SC1, the air mix door 18 is fully opened, that is, the upstream end opening of the hot air passage R2 is fully opened, and the upstream end opening of the bypass passage R3 is fully closed.

  Then, the process proceeds to step SC <b> 2, and the hot water valve C is opened, that is, the engine cooling water in the engine cooling water outflow pipe 2 flows into the heater core 11. In step SC3 following step SC2, the heat pump device H is started to operate in the dehumidifying and heating operation mode.

  In the dehumidifying and heating operation mode shown in FIG. 4, the compressor 20 is operated, and the first pressure reducing valve 24 is set to an opening degree that exerts a pressure reducing action. Further, the refrigerant flow switching valve 27 is switched so that the refrigerant flows to the upstream side vehicle interior heat exchanger 22. The second pressure reducing valve 25 has an opening that does not exert a pressure reducing action. Thereby, since the refrigerant | coolant of the high temperature state discharged from the compressor 20 flows into the downstream vehicle interior heat exchanger 23, the downstream vehicle interior heat exchanger 23 acts as a heat radiator. Moreover, since the refrigerant | coolant after pressure reduction flows into the vehicle exterior heat exchanger 21 and the upstream vehicle interior heat exchanger 22, the vehicle exterior heat exchanger 21 and the upstream vehicle interior heat exchanger 22 act as a heat absorber. The refrigerant that has absorbed heat by the vehicle exterior heat exchanger 21 and the upstream vehicle interior heat exchanger 22 is sucked into the compressor 20. The electric heater 16 is turned on / off according to the degree of heating requirement.

  The air introduced into the air conditioning casing 13 first flows into the upstream side passage R1 and passes through the upstream side interior heat exchanger 22. Since the refrigerant after decompression flows through the upstream side interior heat exchanger 22, the air passing through the upstream side interior heat exchanger 22 is cooled and dehumidified thereby. Thereafter, the air passes through the heater core 11 and is heated.

  Then, the air flows into the hot air passage R2 and passes through the downstream side vehicle interior heat exchanger 23 to be heated. The air that has passed through the downstream side interior heat exchanger 23 is also heated by the electric heater 16 when the electric heater 16 is ON. The heated air passes through the air mix space R4 and is supplied to the vehicle compartment from the air outlet corresponding to the air outlet mode.

  In step SC4 following step SC3, compressor control and pressure reducing valve control are performed. The compressor control is the same as step SB4 described above, and is a control for changing the rotation speed of the compressor 20 according to conditions such as the outside air temperature, the inside air temperature, and the set temperature by the occupant. The pressure reducing valve control is a control in which the opening degree of the first pressure reducing valve 24 is changed to control the vehicle exterior heat exchanger 21 to the intermediate pressure of the heat pump cycle to change the heat absorption amount of the upstream vehicle interior heat exchanger 22. is there.

  In step SC5 following step SC4, it is determined whether or not the rotational speed Nc of the compressor 20 has become zero. If it is determined NO in step SC5 and the rotation speed Nc of the compressor 20 is not 0, the heating by the heat pump device H is necessary, so that the process returns to step SC4 and the compressor control and the pressure reducing valve control are repeated. If it is determined as YES in step SC5 and the rotation speed Nc of the compressor 20 is 0, it can be estimated that the air temperature in the passenger compartment has increased until heating by the heat pump device H becomes unnecessary. In this case, it progresses to step SC6 and hot water valve control is performed. The hot water valve control is the same as in step SB6.

  In step SC7 following step SC6, it is determined whether or not the target temperature is higher than the actual inside air temperature. If it is determined as YES in step SC7 and the target temperature is higher than the actual room air temperature, the process proceeds to step SC8, and it is determined whether or not the opening degree Qw of the hot water valve C is the maximum (Max). If it determines with YES by step SC8 and it determines with the opening degree Qw of the hot water valve C being the maximum, it will return to step SC4 and will repeat compressor control and pressure-reduction valve control. On the other hand, if NO is determined in step SC8, the opening degree Qw of the hot water valve C is not the maximum, so the process returns to step SC6 and the hot water valve control is repeated.

  When it is determined NO in step SC7, the process proceeds to step SC9, and it is determined whether or not the opening degree Qw of the hot water valve C is the minimum (Min). If it is determined YES in step SC9 and it is determined that the opening degree Qw of the hot water valve C is minimum, the process proceeds to step SC10. On the other hand, if NO is determined in step SC9, the opening degree Qw of the hot water valve C is determined. Since it is not the minimum, it returns to step SC6 and repeats warm water valve control.

  In step SC10, the current opening degree Md of the air mix door 18 is changed. That is, the opening degree Md is increased by adding the opening degree to the current opening degree Md of the air mix door 18 by θ. Thereby, since the opening degree of bypass passage R3 becomes large, it adjusts in the direction in which blowing air temperature falls.

  In step SC11 following step SC10, it is determined whether or not the target temperature is lower than the actual inside air temperature. If YES is determined in step SC11 and the target temperature is lower than the actual indoor air temperature, the process returns to step SC10, and the opening degree of the air mix door 18 is adjusted. If NO is determined in step SC11, the process proceeds to the return of the main routine shown in FIG.

  Next, the control procedure of the dehumidifying operation shown in the flowchart of FIG. 10 will be described. In step SD1, the temperature of the blown air is adjusted by changing the opening of the air mix door 18. Thereafter, the process proceeds to step SD2 in which the hot water valve C is closed, that is, the engine cooling water in the engine cooling water outflow pipe 2 does not flow into the heater core 11.

  In step SD3 following step SD2, the heat pump device H is started to operate in the dehumidifying operation mode. In the dehumidifying operation mode shown in FIG. 5, the compressor 20 is operated, and the first pressure reducing valve 24 is set to an opening degree that does not exert a pressure reducing action. Further, the refrigerant flow switching valve 27 is switched so that the refrigerant flows to the upstream side vehicle interior heat exchanger 22. The second pressure reducing valve 25 has an opening degree that exerts a pressure reducing action. As a result, the high-temperature refrigerant discharged from the compressor 20 flows to the downstream side vehicle interior heat exchanger 23 and the vehicle exterior heat exchanger 21, so that the downstream vehicle interior heat exchanger 23 and the vehicle exterior heat exchanger 21 are connected to the radiator. Acts as Moreover, since the refrigerant | coolant after pressure reduction flows through the upstream vehicle interior heat exchanger 22, the upstream vehicle interior heat exchanger 22 acts as a heat absorber. The refrigerant that has absorbed heat by the upstream side vehicle interior heat exchanger 22 is sucked into the compressor 20. Further, the electric heater 16 is turned off.

  The air introduced into the air conditioning casing 13 first flows into the upstream side passage R1 and passes through the upstream side interior heat exchanger 22. Since the refrigerant after decompression flows through the upstream side interior heat exchanger 22, the air passing through the upstream side interior heat exchanger 22 is cooled and dehumidified thereby. Thereafter, the air passes through the heater core 11, but since the engine cooling water does not flow through the heater core 11, the air is not heated.

  And air flows into warm air passage R2 and bypass passage R3 by the opening of air mix door 18. The air flowing into the warm air passage R2 passes through the downstream side vehicle interior heat exchanger 23 and is heated. The air that has passed through the downstream side vehicle interior heat exchanger 23 flows into the air mix space R4. The air flowing through the bypass passage R3 also flows into the air mix space R4, and is mixed with warm air in the air mix space R4 to become conditioned air at a desired temperature. This conditioned air is supplied to the passenger compartment from the outlet corresponding to the blowing mode.

  In step SD4 following step SD3, air mix door control, electric heater control, and compressor control are performed. The air mix door control is a control for adjusting the temperature of the blown air by changing the opening degree of the air mix door 18. The electric heater control is control for adjusting the heating capacity by changing the power supplied to the electric heater 16. The air mix door control and the electric heater control are controls that can increase the temperature of the air-conditioning air that has been cooled by passing through the upstream side vehicle interior heat exchanger 22, and are also referred to as hot air control. In the compressor control, when the rotational speed of the compressor 20 is increased, the dehumidifying capacity of the upstream side vehicle interior heat exchanger 22 is increased, and when the rotational speed of the compressor 20 is decreased, the dehumidifying capacity of the upstream side vehicle interior heat exchanger 22 is decreased. . That is, the compressor control is dehumidification control for adjusting the dehumidification amount. After step SD4, the process proceeds to the return of the main routine shown in FIG.

  Next, the control procedure of the cooling operation shown in the flowchart of FIG. 11 will be described. In step SE1, the air mix door 18 is fully cooled, that is, the upstream end opening of the warm air passage R2 is fully closed, and the upstream end opening of the bypass passage R3 is fully opened. Thereafter, the process proceeds to step SE2 where the hot water valve C is closed, that is, the engine cooling water in the engine cooling water outflow pipe 2 does not flow into the heater core 11. In step SE3 following step SE2, the heat pump device H is started to operate in the cooling operation mode. The cooling operation mode shown in FIG. 6 is the same as the dehumidifying operation mode.

  The air introduced into the air conditioning casing 13 first flows into the upstream side passage R1 and passes through the upstream side interior heat exchanger 22. Since the refrigerant after decompression flows through the upstream side vehicle interior heat exchanger 22, the air passing through the upstream side vehicle interior heat exchanger 22 is cooled. Thereafter, the air passes through the heater core 11, but since the engine cooling water does not flow through the heater core 11, the air is not heated. And after flowing in air mix space R4 through bypass passage R3, air is supplied to a compartment from a blower outlet corresponding to blowout mode.

  Thereafter, the process proceeds to step SE4 to perform compressor control. In the compressor control, when the rotation speed of the compressor 20 is increased, the degree of heat absorption of the upstream side vehicle interior heat exchanger 22 is increased, and when the rotation number of the compressor 20 is decreased, the degree of heat absorption of the upstream side vehicle interior heat exchanger 22 is decreased. . That is, the compressor control is cold air control that adjusts the temperature of the cold air. After step SE4, the process proceeds to the return of the main routine shown in FIG.

  It should be noted that the engine cooling water supplied to the heater core 11 is blocked by the hot water valve C when the air mix door 18 is in an operating state other than the operating state in which the air volume ratio of the hot air passage R2 is the maximum ratio. Also good.

  In the above embodiment, the amount of heat supplied to the heater core 11 is changed by adjusting the opening of the hot water valve C in step SB6 in the heating operation mode and step SC6 in the dehumidifying heating operation mode. For example, the amount of heat supplied to the heater core 11 may be changed by adjusting the supply amount of the cooling water pump 17. By adjusting with the cooling water pump 17, the operating frequency of the hot water valve C can be lowered to improve the durability of the hot water valve C, and the amount of heat supplied to the heater core 11 can be finely controlled.

  Further, when the air temperature in the passenger compartment becomes equal to or higher than the target blown air temperature to the passenger compartment while the heat pump device H is operating in the heating operation mode, the control device 12 has an air volume of the bypass passage R3 by the air mix door 18. After increasing the ratio, step SB6 in FIG. 8 may be performed to reduce the amount of heat supplied to the heater core 11.

  In addition, when the control device 12 is operating the heat pump device H in the heating operation mode, if the air temperature in the passenger compartment becomes equal to or higher than the target blowing air temperature to the passenger compartment, the heating operation capability of the heat pump device H is reduced. You may comprise so that the heating capability of the electric heater 16 may be reduced before reducing the rotation speed of the compressor 20 and before reducing the amount of heat supplied to the heater core 11.

  As described above, according to this embodiment, in the cooling operation mode, the vehicle exterior heat exchanger 21 and the downstream vehicle interior heat exchanger 23 serve as radiators, and the upstream vehicle interior heat exchanger 22 serves as a heat absorber. Therefore, the air for air conditioning is cooled by the upstream side vehicle interior heat exchanger 22.

  On the other hand, in the heating operation mode, the downstream-side vehicle interior heat exchanger 23 serves as a radiator, and the vehicle interior heat exchanger 21 serves as a heat absorber. The air is heated by the heater core 11 to which engine cooling water is supplied from the engine E, which is a device that generates heat from the vehicle, and is also heated by the downstream side interior heat exchanger 23. At this time, the heater core 11 is disposed upstream of the air mix door 18 in the air flow direction, that is, upstream of the warm air passage R2. The upstream passage R1 upstream of the hot air passage R2 has a cross-sectional area that combines the bypass passage R3 and the hot air passage R2, and a wide cross-sectional area is secured. Therefore, the heater core 11 having a wide air passage surface is provided. Can be arranged. Thereby, the heating performance of the air by the heater core 11 can be improved. Further, since the heater core 11 is not provided between the air mix door 18 and the downstream-side vehicle interior heat exchanger 23, the thickness dimension of the downstream-side vehicle interior heat exchanger 23 can also be increased. The heating performance can be improved.

  Further, since the heater core 11 is located on the upstream side of the downstream-side vehicle interior heat exchanger 23, the temperature of the air flowing into the downstream-side vehicle interior heat exchanger 23 becomes high. Therefore, it is possible to reduce the amount of energy consumed by the compressor 20 in the heating operation mode.

  Further, since the heater core 11 is disposed so as to face both the hot air passage R2 and the bypass passage R3, the air passage portion of the heater core 11 can be widened, and both the heating performance improvement and the thinning of the heater core 11 are achieved. Thus, it is possible to reduce the pressure loss of the air, and it is possible to prevent the air volume from being reduced and the blower 15 from being enlarged.

  Further, when the actual inside air temperature becomes equal to or higher than the target temperature in the heating operation mode, the heating operation capacity of the heat pump device H is reduced before the heating capacity of the heater core 11 is reduced by reducing the rotation speed of the compressor 20. The amount of energy consumed by 20 can be reduced.

  Further, the engine cooling water can be prevented from being supplied to the heater core 11 in the cooling operation mode, so that the cooling performance can be improved.

  In addition, in the said embodiment, although the air passage part of the heater core 11 is arrange | positioned so that it may oppose from the air flow direction downstream with respect to the air passage part of the upstream vehicle interior heat exchanger 22, it is not restricted to this, For example, the air passage portion of the heater core 11 may be disposed so as to face the air passage portion of the upstream vehicle interior heat exchanger 22 from the upstream side in the air flow direction. In this case, for example, when the evaporator sensor 44 is mounted on the downstream side in the air flow direction of the upstream vehicle interior heat exchanger 22, the heater core 11 is not provided on the downstream side in the air flow direction of the upstream vehicle interior heat exchanger 22. The sensor 44 can be easily attached to the upstream side interior heat exchanger 22 from the downstream side in the air flow direction.

  In the above embodiment, the heat of the engine is supplied to the heater core 11. However, the present invention is not limited to this. For example, electric components (devices that generate heat from the vehicle) such as a running motor, a battery, and an inverter device are cooled. For this purpose, cooling water may be supplied to the heater core 11.

  The above-described embodiment is merely an example in all respects and should not be interpreted in a limited manner. Further, all modifications and changes belonging to the equivalent scope of the claims are within the scope of the present invention.

  As described above, the vehicle air conditioner according to the present invention can be mounted, for example, in an automobile.

1 Vehicle air conditioner 11 Heater core (air heater)
12 Control device 13 Air conditioning casing 16 Electric heater (electric heater)
17 Cooling water pump (Variable heat supply means)
18 Air Mix Door 20 Compressor 21 Outside Heat Exchanger 22 Upstream Car Interior Heat Exchanger (First Car Interior Heat Exchanger)
23 Downstream passenger compartment heat exchanger (second passenger compartment heat exchanger)
24 1st pressure reducing valve 25 2nd pressure reducing valve C Hot water valve (Supply heat amount variable means)
E Engine H Heat pump device R2 Hot air passage R3 Bypass passage

Claims (7)

A compressor for compressing the refrigerant;
An outdoor heat exchanger disposed outside the vehicle;
A first vehicle interior heat exchanger disposed in the vehicle interior;
A second vehicle interior heat exchanger disposed downstream of the first vehicle interior heat exchanger in the flow direction of air-conditioning air in the vehicle interior;
A first and a second pressure reducing valve;
In the cooling operation mode, the refrigerant discharged from the compressor flows through the second vehicle interior heat exchanger and the vehicle exterior heat exchanger, and is then decompressed by the second pressure reducing valve, so that the first vehicle interior heat exchanger is used. In the heating operation mode, the refrigerant discharged from the compressor is flowed to the second vehicle interior heat exchanger, and then the pressure is reduced by the first pressure reducing valve to exchange the heat outside the vehicle. In a vehicle air conditioner equipped with a heat pump device configured to flow into a container and suck into the compressor,
Inside the air conditioning casing that houses the first vehicle interior heat exchanger and the second vehicle interior heat exchanger, a hot air passage through which the air that has passed through the second vehicle interior heat exchanger flows, and the air 2. A bypass passage that flows by bypassing the vehicle interior heat exchanger, and an air heater that is disposed so as to face the hot air passage and the bypass passage and that is supplied with a heat exchange medium from a device that generates heat from the vehicle is provided. And
A heat supply variable means for changing the heat supply supplied to the air heater, and a controller for controlling the heat pump device and the heat supply variable means,
When the control device is operating the heat pump device in the heating operation mode, if the air temperature in the passenger compartment becomes equal to or higher than the target blowing air temperature to the passenger compartment, the heating operation capability of the heat pump device is reduced. The vehicle air conditioner is configured to reduce the amount of heat supplied to the air heater by the supply heat amount varying means. In the vehicle air conditioner according to claim 1,
The vehicle air conditioner characterized in that the supply heat amount varying means is switched between a supply state in which a heat exchange medium is supplied to the air heater and a bypass state in which the air heater is bypassed to flow. In the vehicle air conditioner according to claim 1,
The vehicle air conditioner characterized in that the supply heat amount varying means includes a variable flow pump for changing a flow rate of a heat exchange medium supplied to the air heater. In the vehicle air conditioner according to claim 1,
The controller controls the outside heat exchanger outside the vehicle to an intermediate pressure of a heat pump cycle so that the first vehicle interior heat exchanger serves as a heat absorber, and the second vehicle interior heat exchanger serves as a radiator. A vehicle air conditioner configured to control the heat pump device so as to be in a mode and to supply a heat exchange medium to the air heater in a dehumidifying heating operation mode. The vehicle air conditioner according to claim 4,
When operating the heat pump device in the dehumidifying and heating operation mode, the control device reduces the heating operation capability of the heat pump device when the air temperature in the vehicle compartment is equal to or higher than the target blown air temperature to the vehicle compartment. Thereafter, the vehicle air conditioner is configured to reduce the amount of heat supplied to the air heater by the supply heat amount varying means. In the vehicle air conditioner according to claim 1 or 5,
An air mix door for adjusting the air volume ratio of the hot air passage and the bypass passage;
When the air temperature in the passenger compartment becomes equal to or higher than the target air temperature to the passenger compartment while the heat pump device is operating in the heating operation mode, the control device sets the air volume ratio of the bypass passage by the air mix door. A vehicle air conditioner configured to reduce the amount of heat supplied to the air heater by the supply heat amount variable means after the increase. In the vehicle air conditioner according to claim 1 or 5,
In the air conditioning casing, an electric heater for heating the air conditioning air is disposed,
When the air temperature in the passenger compartment is equal to or higher than the target air temperature for the passenger compartment when the heat pump device is operating in the heating operation mode, the control device is configured to reduce the heating operation capability of the heat pump device. The vehicle air conditioner is configured to reduce the heating capacity of the electric heater before reducing the amount of heat supplied to the air heater by the supply heat amount varying means. .

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