JP2021188790A - Refrigeration cycle device - Google Patents

Abstract

To suppress fluctuation of a blowout air temperature.SOLUTION: A refrigeration cycle device includes: an air-conditioning expansion valve 14b decompressing a refrigerant of which heat has been radiated by a heat radiation part; an indoor evaporator 18 evaporating the refrigerant and cooling air by exchanging heat between the refrigerant decompressed by the air-conditioning expansion valve and the air; cooling expansion valves 14c, 14d disposed in parallel with the air-conditioning expansion valve in a flow of the refrigerant and decompressing the refrigerant of which heat has been radiated by the heat radiation part; cooling parts 19a, 19b cooling a cooling object by evaporating the refrigerant decompressed by the cooling expansion valves by using heat of the cooling object; and a control section 60 performing fluctuation suppression control for controlling at least one of refrigerant discharge capacity of a compressor and openings of the cooling expansion valves to suppress fluctuation of a flow rate of the refrigerant in the indoor evaporator when a first mode in which the refrigerant flows in the indoor evaporator and the refrigerant does not flow in the cooling parts is shifted to a second mode in which the refrigerant flows in the indoor evaporator and the cooling parts.SELECTED DRAWING: Figure 9

Description

The present invention relates to a refrigeration cycle device that cools air and objects to be cooled.

Conventionally, the battery temperature control device described in Patent Document 1 has a refrigeration cycle device. In this refrigeration cycle device, the refrigerant flows in parallel with the indoor evaporator and the chiller. The indoor evaporator cools the air blown into the vehicle interior with a low-pressure refrigerant. The chiller cools the cooling water for cooling the battery with a low-pressure refrigerant. Therefore, this battery temperature control device also functions as an air conditioner.

The low-pressure refrigerant (that is, low-temperature refrigerant) decompressed by the cooling expansion valve flows into the indoor evaporator. The low-pressure refrigerant decompressed by the endothermic expansion valve flows into the chiller. By opening and closing the endothermic expansion valve, the cooling mode and the cooling cooling mode can be switched. The cooling mode is an operation mode in which the air blown into the vehicle interior is cooled and the battery is not cooled. The cooling cooling mode is an operation mode in which the air blown into the vehicle interior is cooled and the battery is also cooled. By fully closing the opening degree of the endothermic expansion valve, the cooling mode can be switched, and by setting the opening degree of the endothermic expansion valve to the throttle opening, the cooling mode can be switched.

Refrigerant oil that lubricates the compressor is mixed in the refrigerant. The refrigerating machine oil circulates together with the refrigerant in the refrigerant circuit of the refrigerating cycle device.

Japanese Unexamined Patent Publication No. 2020-004484

According to the above-mentioned conventional technique, when the cooling mode is switched to the cooling cooling mode, the flow velocity and the flow rate of the refrigerant branched to the indoor evaporator side and the chiller side decrease, and the refrigerating machine oil stays in the refrigerant pipe or the heat exchanger. It will be easier to do. Therefore, as a countermeasure for this, it is conceivable to control the lower limit rotation speed of the compressor to be higher in the cooling mode than in the cooling mode.

However, if the rotation speed of the compressor suddenly increases when the cooling mode is switched to the cooling cooling mode, the temperature fluctuation of the air blown out from the indoor evaporator becomes large.

For example, when the rotation speed of the compressor increases at a stretch, the cooling capacity of the indoor evaporator becomes excessive, and the cooling expansion valve is closed in order to reduce the cooling capacity of the indoor evaporator. Then, the refrigerant of the indoor evaporator is pulled by the suction pressure of the compressor, and the temperature drops (so-called undershoot). As the refrigerant in the indoor evaporator evaporates while the refrigerant in the indoor evaporator is drawn in this way, the temperature of the indoor evaporator rises sharply. Then, the expansion valve for cooling is opened again and the refrigerant flows out to the indoor evaporator, but the temperature rise cannot be suppressed and the temperature of the indoor evaporator becomes too high (so-called overshoot). As a result, the temperature fluctuation of the air blown out from the indoor evaporator becomes large (see FIG. 8 described later).

In view of the above points, it is an object of the present invention to suppress fluctuations in the temperature of blown air.

In order to achieve the above object, the refrigeration cycle apparatus according to claim 1 is used.
A compressor (11) that compresses and discharges the refrigerant,
A heat radiating unit (16) that dissipates heat from the refrigerant discharged from the compressor,
A cooling expansion valve (14b) that reduces the pressure of the refrigerant dissipated in the heat dissipation section, and
An indoor evaporator (18) that evaporates the refrigerant and cools the air by exchanging heat between the refrigerant decompressed by the expansion valve for cooling and the air.
Cooling expansion valves (14c, 14d) that are arranged in parallel with the cooling expansion valve in the flow of the refrigerant and reduce the pressure of the refrigerant dissipated in the heat dissipation section.
Cooling units (19a, 19b) that cool the object to be cooled by evaporating the refrigerant decompressed by the expansion valve for cooling with the heat of the object to be cooled.
When switching from the first mode in which the refrigerant flows through the indoor evaporator and the refrigerant does not flow in the cooling section to the second mode in which the refrigerant flows through the indoor evaporator and the cooling section, compression is performed so as to suppress fluctuations in the flow rate of the refrigerant in the indoor evaporator. It is provided with a control unit (60) that controls fluctuation suppression to control at least one of the refrigerant discharge capacity of the machine and the opening degree of the cooling expansion valve.

According to this, since the fluctuation of the flow rate of the refrigerant in the indoor evaporator is suppressed when the mode is switched from the first mode to the second mode, the fluctuation of the temperature of the blown air from the indoor evaporator can be suppressed.

The reference numerals in parentheses of each means described in this column and the scope of claims indicate the correspondence with the specific means described in the embodiments described later.

It is an overall block diagram of the air conditioner for a vehicle of 1st Embodiment. It is a block diagram which shows the electric control part of the air-conditioning apparatus for a vehicle of 1st Embodiment. It is a flowchart which shows a part of the control process of the control program of 1st Embodiment. It is a flowchart which shows another part of the control process of the control program of 1st Embodiment. It is a flowchart which shows the control process of the cooling mode of 1st Embodiment. It is a flowchart which shows the control process of the cooling cooling mode of 1st Embodiment. It is a flowchart which shows the control process of the cooling cooling mode of 1st Embodiment. It is a time chart which shows the operation example of the air conditioner for a vehicle in the comparative example. It is a time chart which shows the operation example of the air conditioner for a vehicle in 1st Embodiment. It is an overall block diagram of the air conditioner for a vehicle of 2nd Embodiment.

(First Embodiment)
The first embodiment of the present invention will be described with reference to FIGS. 1 to 7. In the present embodiment, the refrigeration cycle device 10 according to the present invention is applied to a vehicle air conditioner 1 mounted on an electric vehicle that obtains a driving force for traveling from an electric motor. The vehicle air conditioner 1 is an air conditioner with a battery temperature adjusting function. The vehicle air conditioner 1 air-conditions the interior of the vehicle, which is the space to be air-conditioned, and adjusts the temperature of the battery.

The battery is a secondary battery that stores electric power supplied to an in-vehicle device such as an electric motor. The battery of this embodiment is a lithium ion battery. The battery is a so-called assembled battery formed by stacking a plurality of battery cells 81 and electrically connecting the battery cells 81 in series or in parallel.

The output of this type of battery tends to decrease at low temperatures, and deterioration tends to progress at high temperatures. Therefore, the temperature of the battery needs to be maintained within an appropriate temperature range (in this embodiment, 15 ° C. or higher and 55 ° C. or lower) in which the charge / discharge capacity of the battery can be fully utilized.

Therefore, in the vehicle air conditioner 1, the battery can be cooled by the cold heat generated by the refrigeration cycle device 10. The objects to be cooled in the refrigeration cycle device 10 of the present embodiment are air and a battery.

As shown in the overall configuration diagram of FIG. 1, the vehicle air conditioner 1 includes a refrigerating cycle device 10, an indoor air conditioner unit 30, a high temperature side heat medium circuit 40, and the like.

The refrigerating cycle device 10 cools the air blown into the vehicle interior and heats the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40 in order to perform air conditioning in the vehicle interior.

The refrigerating cycle device 10 can switch the refrigerant circuits for various operation modes in order to perform air conditioning in the vehicle interior. For example, the refrigerant circuit in the cooling mode, the refrigerant circuit in the dehumidifying / heating mode, the refrigerant circuit in the heating mode, and the like can be switched. The refrigeration cycle device 10 can switch between an operation mode in which the battery is cooled and an operation mode in which the battery is not cooled in each operation mode for air conditioning.

The refrigeration cycle apparatus 10 employs an HFO-based refrigerant (specifically, R1234yf) as the refrigerant, and the pressure of the discharged refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant, which is a steam compression type subcritical. It constitutes a refrigeration cycle. Refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant. Some of the refrigerating machine oil circulates in the cycle together with the refrigerant.

Among the constituent devices of the refrigerating cycle device 10, the compressor 11 sucks the refrigerant in the refrigerating cycle device 10, compresses it, and discharges it. The compressor 11 is arranged in front of the vehicle interior and is arranged in the drive unit room in which the electric motor and the like are housed. The compressor 11 is an electric compressor that rotationally drives a fixed-capacity compression mechanism having a fixed discharge capacity by an electric motor. The number of revolutions (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the cycle control device 60.

The inlet side of the refrigerant passage of the water-refrigerant heat exchanger 12 is connected to the discharge port of the compressor 11. The water-refrigerant heat exchanger 12 has a refrigerant passage for circulating the high-pressure refrigerant discharged from the compressor 11 and a water passage for circulating the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40. The water refrigerant heat exchanger 12 is a heat exchanger for heating that heats the high temperature side heat medium by exchanging heat between the high pressure refrigerant flowing through the refrigerant passage and the high temperature side heat medium flowing through the water passage.

The inlet side of the first three-way joint 13a having three inflow outlets communicating with each other is connected to the outlet of the refrigerant passage of the water refrigerant heat exchanger 12. As such a three-way joint, one formed by joining a plurality of pipes or one formed by providing a plurality of refrigerant passages in a metal block or a resin block can be adopted.

The refrigeration cycle device 10 includes second to eighth three-way joints 13b to 13h. The basic configuration of the second to eighth three-way joints 13b to 13h is the same as that of the first three-way joint 13a.

The inlet side of the heating expansion valve 14a is connected to one of the outlets of the first three-way joint 13a. One inflow port side of the second three-way joint 13b is connected to the other outflow port of the first three-way joint 13a via a bypass passage 22a. A dehumidifying on-off valve 15a is arranged in the bypass passage 22a.

The dehumidifying on-off valve 15a is a solenoid valve that opens and closes a refrigerant passage connecting the other outlet side of the first three-way joint 13a and the one inlet side of the second three-way joint 13b. The refrigeration cycle device 10 includes a heating on-off valve 15b. The basic configuration of the heating on-off valve 15b is the same as that of the dehumidifying on-off valve 15a.

The dehumidifying on-off valve 15a and the heating on-off valve 15b can switch the refrigerant circuit of each operation mode by opening and closing the refrigerant passage. The dehumidifying on-off valve 15a and the heating on-off valve 15b are refrigerant circuit switching units that switch the refrigerant circuit of the cycle. The dehumidifying on-off valve 15a and the heating on-off valve 15b are controlled by a control voltage output from the cycle control device 60.

The heating expansion valve 14a reduces the pressure of the high-pressure refrigerant flowing out from the refrigerant passage of the water refrigerant heat exchanger 12 at least in the operation mode of heating the vehicle interior, and reduces the flow rate (mass flow rate) of the refrigerant flowing out to the downstream side. It is a decompression unit for heating to be adjusted. The heating expansion valve 14a is an electric variable throttle mechanism having a valve body configured to change the throttle opening degree and an electric actuator for changing the throttle opening degree.

The refrigeration cycle device 10 includes a cooling expansion valve 14b, a first cooling expansion valve 14c, and a second cooling expansion valve 14d. The basic configurations of the cooling expansion valve 14b, the first cooling expansion valve 14c, and the second cooling expansion valve 14d are the same as those of the heating expansion valve 14a.

The heating expansion valve 14a, the cooling expansion valve 14b, the first cooling expansion valve 14c, and the second cooling expansion valve 14d exert almost all the flow rate adjusting action and the refrigerant depressurizing action by fully opening the valve opening. It has a fully open function that functions as a mere refrigerant passage, and a fully closed function that closes the refrigerant passage by fully closing the valve opening.

With the fully open function and the fully closed function, the heating expansion valve 14a, the cooling expansion valve 14b, the first cooling expansion valve 14c, and the second cooling expansion valve 14d can switch the refrigerant circuit in each operation mode. The heating expansion valve 14a, the cooling expansion valve 14b, the first cooling expansion valve 14c, and the second cooling expansion valve 14d function as a refrigerant circuit switching unit. The heating expansion valve 14a, the cooling expansion valve 14b, the first cooling expansion valve 14c, and the second cooling expansion valve 14d are controlled by a control signal (control pulse) output from the cycle control device 60.

The refrigerant inlet side of the outdoor heat exchanger 16 is connected to the outlet of the heating expansion valve 14a. The outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the refrigerant flowing out from the heating expansion valve 14a and the outside air blown by a cooling fan (not shown). The outdoor heat exchanger 16 is arranged on the front side in the drive device room. Therefore, when the vehicle is running, the running wind can be applied to the outdoor heat exchanger 16.

The inlet side of the third three-way joint 13c is connected to the refrigerant outlet of the outdoor heat exchanger 16. One inflow port side of the fourth three-way joint 13d is connected to one outflow port of the third three-way joint 13c via a heating passage 22b. A heating on-off valve 15b for opening and closing the refrigerant passage is arranged in the heating passage 22b.

The other inlet side of the second three-way joint 13b is connected to the other outlet of the third three-way joint 13c. A check valve 17 is arranged in the refrigerant passage connecting the other outlet side of the third three-way joint 13c and the other inlet side of the second three-way joint 13b. The check valve 17 allows the refrigerant to flow from the third three-way joint 13c side to the second three-way joint 13b side, and prohibits the refrigerant from flowing from the second three-way joint 13b side to the third three-way joint 13c side.

The inlet side of the fifth three-way joint 13e is connected to the outlet of the second three-way joint 13b. The inlet side of the cooling expansion valve 14b is connected to one of the outlets of the fifth three-way joint 13e. The inlet side of the 7th three-way joint 13g is connected to the other outlet of the fifth three-way joint 13e.

The cooling expansion valve 14b is a cooling expansion valve that reduces the pressure of the refrigerant flowing out from the outdoor heat exchanger 16 and adjusts the flow rate of the refrigerant flowing out to the downstream side at least in the operation mode for cooling the vehicle interior.

The refrigerant inlet side of the indoor evaporator 18 is connected to the outlet of the cooling expansion valve 14b. The indoor evaporator 18 is arranged in the air conditioning case 31 of the indoor air conditioning unit 30. The indoor evaporator 18 exchanges heat between the low-pressure refrigerant decompressed by the cooling expansion valve 14b and the air blown from the blower 32 to evaporate the low-pressure refrigerant, and causes the low-pressure refrigerant to exert a heat absorbing action to absorb air. It is an indoor evaporator that cools.

The inlet side of the evaporation pressure adjusting valve 20 is connected to the refrigerant outlet of the indoor evaporator 18. The evaporation pressure adjusting valve 20 maintains the refrigerant evaporation pressure in the indoor evaporator 18 at a predetermined reference pressure or higher in order to suppress frost formation in the indoor evaporator 18. The evaporation pressure adjusting valve 20 is a mechanical variable throttle mechanism that increases the valve opening degree as the pressure of the refrigerant on the outlet side of the indoor evaporator 18 increases. As a result, the evaporation pressure adjusting valve 20 maintains the refrigerant evaporation temperature in the indoor evaporator 18 at a frost formation suppression temperature (1 ° C. in the present embodiment) that can suppress frost formation in the indoor evaporator 18. ..

One inflow port side of the sixth three-way joint 13f is connected to the outlet of the evaporation pressure adjusting valve 20.

The inlet side of the first cooling expansion valve 14c is connected to one of the outlets of the seventh three-way joint 13g. The inlet side of the second cooling expansion valve 14d is connected to the other outlet of the seventh three-way joint 13g.

The first cooling expansion valve 14c and the second cooling expansion valve 14d reduce the pressure of the refrigerant flowing out of the outdoor heat exchanger 16 at least in the operation mode for cooling the battery, and reduce the flow rate of the refrigerant flowing out to the downstream side. It is a cooling expansion valve to be adjusted.

The inlet side of the refrigerant passage of the first battery cooler 19a is connected to the outlet of the first cooling expansion valve 14c. The first battery cooler 19a has a refrigerant passage through which a low-pressure refrigerant decompressed by the first cooling expansion valve 14c flows. The first battery cooler 19a is an evaporation unit that evaporates the low-pressure refrigerant flowing through the refrigerant passage by the heat of the battery to exert an endothermic action. One inflow port side of the eighth three-way joint 13h is connected to the outlet of the refrigerant passage of the first battery cooler 19a.

The inlet side of the refrigerant passage of the second battery cooler 19b is connected to the outlet of the second cooling expansion valve 14d. The second battery cooler 19b has a refrigerant passage through which the low-pressure refrigerant decompressed by the second cooling expansion valve 14d flows. The second battery cooler 19b is an evaporation unit that evaporates the low-pressure refrigerant flowing through the refrigerant passage by the heat of the battery to exert an endothermic action. The other inflow port side of the eighth three-way joint 13h is connected to the outlet of the refrigerant passage of the second battery cooler 19b.

For example, the first battery cooler 19a and the second battery cooler 19b are heat exchangers that absorb heat from the battery via a heat medium such as air or cooling water. The first battery cooler 19a and the second battery cooler 19b may be coolers that directly absorb heat from the battery by heat conduction without using a heat medium such as air or cooling water.

The other inlet side of the sixth three-way joint 13f is connected to the outlet of the eighth three-way joint 13h. The other inlet side of the fourth three-way joint 13d is connected to the outlet of the sixth three-way joint 13f. The inlet side of the accumulator 21 is connected to the outlet of the fourth three-way joint 13d. The accumulator 21 is a gas-liquid separation unit that separates the gas-liquid of the refrigerant that has flowed into the inside and stores the excess liquid-phase refrigerant in the cycle. The suction port side of the compressor 11 is connected to the gas phase refrigerant outlet of the accumulator 21.

The accumulator 21 is formed with an oil return hole for returning the refrigerating machine oil mixed in the separated liquid phase refrigerant to the compressor 11. The refrigerating machine oil in the accumulator 21 is returned to the compressor 11 together with a small amount of liquid phase refrigerant.

The fifth three-way joint 13e of the present embodiment is a branch portion for branching the flow of the refrigerant flowing out from the outdoor heat exchanger 16. The sixth three-way joint 13f merges the flow of the refrigerant flowing out from the indoor evaporator 18 with the flow of the refrigerant flowing out from the first battery cooler 19a and the second battery cooler 19b, and moves to the suction side of the compressor 11. It is a confluence part to be discharged.

The first battery cooler 19a and the second battery cooler 19b are connected to the indoor evaporator 18 in parallel with each other in the refrigerant flow. The bypass passage 22a guides the refrigerant flowing out of the refrigerant passage of the water refrigerant heat exchanger 12 to the upstream side of the branch portion. The heating passage 22b guides the refrigerant flowing out of the outdoor heat exchanger 16 to the suction port side of the compressor 11.

The high temperature side heat medium circuit 40 is a heat medium circulation circuit that circulates the high temperature side heat medium. As the high temperature side heat medium, a solution containing ethylene glycol, dimethylpolysiloxane, a nanofluid, or the like, an antifreeze solution, or the like can be adopted. In the high temperature side heat medium circuit 40, a water passage of the water refrigerant heat exchanger 12, a high temperature side heat medium pump 41, a heater core 42, and the like are arranged.

The high temperature side heat medium pump 41 is a water pump that pumps the high temperature side heat medium to the inlet side of the water passage of the water refrigerant heat exchanger 12. The high temperature side heat medium pump 41 is an electric pump whose rotation speed (that is, pumping capacity) is controlled by a control voltage output from the cycle control device 60.

The heat medium inlet side of the heater core 42 is connected to the outlet of the water passage of the water refrigerant heat exchanger 12. The heater core 42 is a heat exchanger that heats the air by exchanging heat between the high temperature side heat medium heated by the water refrigerant heat exchanger 12 and the air that has passed through the indoor evaporator 18. The heater core 42 is arranged in the air conditioning case 31 of the indoor air conditioning unit 30. The suction port side of the high temperature side heat medium pump 41 is connected to the heat medium outlet of the heater core 42.

In the high temperature side heat medium circuit 40, the high temperature side heat medium pump 41 adjusts the flow rate of the high temperature side heat medium flowing into the heater core 42 to dissipate heat of the high temperature side heat medium in the heater core 42 to the air (that is, the heater core). The amount of heat of air in 42) can be adjusted.

Each component of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 is a heating unit that heats air using the refrigerant discharged from the compressor 11 as a heat source.

The indoor air-conditioning unit 30 is for blowing out air whose temperature has been adjusted by the refrigeration cycle device 10 into the vehicle interior. The indoor air conditioning unit 30 is arranged inside the instrument panel (instrument panel) at the front of the vehicle interior.

The indoor air conditioning unit 30 accommodates a blower 32, an indoor evaporator 18, a heater core 42, and the like in an air passage formed in an air conditioning case 31 forming an outer shell thereof.

The air conditioning case 31 forms an air passage for air to be blown into the vehicle interior. The air conditioning case 31 is made of a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength.

An inside / outside air switching device 33 is arranged on the most upstream side of the air flow of the air conditioning case 31. The inside / outside air switching device 33 switches and introduces the inside air (that is, the vehicle interior air) and the outside air (that is, the vehicle interior outside air) into the air conditioning case 31.

The inside / outside air switching device 33 continuously adjusts the opening areas of the inside air introduction port for introducing the inside air into the air conditioning case 31 and the outside air introduction port for introducing the outside air by the inside / outside air switching door, and the introduction air volume of the inside air and the outside air. Change the introduction ratio with the introduction air volume. The inside / outside air switching door is driven by an electric actuator for the inside / outside air switching door. The electric actuator for the inside / outside air switching door is controlled by a control signal output from the cycle control device 60.

A blower 32 is arranged on the downstream side of the air flow of the inside / outside air switching device 33. The blower 32 blows the air sucked through the inside / outside air switching device 33 toward the vehicle interior. The blower 32 is an electric blower that drives a centrifugal multi-blade fan with an electric motor. The rotation speed (that is, the blowing capacity) of the blower 32 is controlled by the control voltage output from the cycle control device 60.

On the downstream side of the air flow of the blower 32, the indoor evaporator 18 and the heater core 42 are arranged in this order with respect to the air flow. The indoor evaporator 18 is arranged on the upstream side of the air flow with respect to the heater core 42.

The air-conditioning case 31 is provided with a cold air bypass passage 35 that allows air after passing through the indoor evaporator 18 to bypass the heater core 42. An air mix door 34 is arranged on the downstream side of the air flow of the indoor evaporator 18 in the air conditioning case 31 and on the upstream side of the air flow of the heater core 42.

The air mix door 34 is an air volume ratio adjusting unit that adjusts the air volume ratio between the air volume of the air passing through the heater core 42 side and the air volume of the air passing through the cold air bypass passage 35 among the air after passing through the indoor evaporator 18. .. The air mix door 34 is driven by an electric actuator for the air mix door. This electric actuator is controlled by a control signal output from the cycle control device 60.

A mixing space is arranged on the downstream side of the air flow of the heater core 42 and the cold air bypass passage 35 in the air conditioning case 31. The mixing space is a space in which the air heated by the heater core 42 and the unheated air passing through the cold air bypass passage 35 are mixed.

In the downstream portion of the air flow of the air conditioning case 31, an opening hole for blowing out the air mixed in the mixing space (that is, the air conditioning air) into the vehicle interior, which is the air conditioning target space, is arranged.

As the opening hole, a face opening hole, a foot opening hole, and a defroster opening hole (none of which are shown) are provided. The face opening hole is an opening hole for blowing air-conditioning air toward the upper body of the occupant in the vehicle interior. The foot opening hole is an opening hole for blowing air-conditioning air toward the feet of the occupant. The defroster opening hole is an opening hole for blowing air conditioning air toward the inner side surface of the front window glass of the vehicle.

These face opening holes, foot opening holes, and defroster opening holes are the face outlets, foot outlets, and defroster outlets (none of which are shown) provided in the vehicle interior via ducts forming air passages, respectively. )It is connected to the.

The temperature of the conditioned air mixed in the mixing space is adjusted by adjusting the air volume ratio between the air volume passing through the heater core 42 and the air volume passing through the cold air bypass passage 35 by the air mix door 34. As a result, the temperature of the air (air-conditioning air) blown from each outlet into the vehicle interior is adjusted.

A face door, a foot door, and a defroster door (none of which are shown) are arranged on the upstream side of the air flow of the face opening hole, the foot opening hole, and the defroster opening hole, respectively. The face door adjusts the opening area of the face opening hole. The foot door adjusts the opening area of the foot opening hole. The defroster door adjusts the opening area of the defroster opening hole.

These face doors, foot doors, and defroster doors constitute an outlet mode switching device for switching the outlet mode. These doors are connected to an electric actuator for driving the outlet mode door via a link mechanism or the like, and are rotated in conjunction with each other. The operation of this electric actuator is also controlled by a control signal output from the cycle control device 60.

Specific examples of the outlet mode that can be switched by the outlet mode switching device include a face mode, a bi-level mode, and a foot mode.

The face mode is an outlet mode in which the face outlet is fully opened and air is blown from the face outlet toward the upper body of the passenger in the passenger compartment. The bi-level mode is an outlet mode in which both the face outlet and the foot outlet are opened to blow air toward the upper body and feet of the passengers in the passenger compartment. The foot mode is an outlet mode in which the foot outlet is fully opened and the defroster outlet is opened by a small opening, and air is mainly blown out from the foot outlet.

The occupant can also switch to the defroster mode by manually operating the blowout mode changeover switch provided on the operation panel 70. The defroster mode is an outlet mode in which the defroster outlet is fully opened and air is blown from the defroster outlet to the inner surface of the front window glass.

Next, the outline of the electric control unit of this embodiment will be described. The cycle control device 60 includes a well-known microcomputer including a CPU, ROM, RAM, and the like, and peripheral circuits thereof. Then, various calculations and processes are performed based on the control program stored in the ROM, and the operation of various controlled target devices 11, 14a to 14d, 15a, 15b, 32, 41, etc. connected to the output side is controlled. do.

On the input side of the cycle control device 60, as shown in the block diagram of FIG. 2, the inside temperature sensor 61, the outside temperature sensor 62, the solar radiation sensor 63, the first to eighth refrigerant temperature sensors 64a to 64h, and the evaporator temperature sensor 64i, first and second refrigerant pressure sensors 65a to 65b, high temperature side heat medium temperature sensor 66a, battery control device 69 and the like are connected. Then, the detection signals of these sensor groups are input to the cycle control device 60.

The internal air temperature sensor 61 is an internal air temperature detecting unit that detects the internal air temperature Tr (that is, the vehicle interior temperature). The outside air temperature sensor 62 is an outside air temperature detection unit that detects the outside air temperature Tam (that is, the outside air temperature of the vehicle interior). The solar radiation sensor 63 is a solar radiation amount detection unit that detects the solar radiation amount Ts applied to the vehicle interior.

The first refrigerant temperature sensor 64a is a discharge refrigerant temperature detection unit that detects the temperature T1 of the refrigerant discharged from the compressor 11. The second refrigerant temperature sensor 64b is a second refrigerant temperature detecting unit that detects the temperature T2 of the refrigerant flowing out from the refrigerant passage of the water refrigerant heat exchanger 12. The third refrigerant temperature sensor 64c is a third refrigerant temperature detecting unit that detects the temperature T3 of the refrigerant flowing out from the outdoor heat exchanger 16. The fourth refrigerant temperature sensor 64d is a fourth refrigerant temperature detecting unit that detects the temperature T4 of the refrigerant flowing out of the indoor evaporator 18.

The fifth refrigerant temperature sensor 64e is a fifth refrigerant temperature detecting unit that detects the temperature T5 of the refrigerant flowing into the refrigerant passage of the first battery cooler 19a. The sixth refrigerant temperature sensor 64f is a sixth refrigerant temperature detecting unit that detects the temperature T6 of the refrigerant flowing out from the refrigerant passage of the first battery cooler 19a. The seventh refrigerant temperature sensor 64g is a seventh refrigerant temperature detecting unit that detects the temperature T7 of the refrigerant flowing into the refrigerant passage of the second battery cooler 19b. The eighth refrigerant temperature sensor 64h is an eighth refrigerant temperature detecting unit that detects the temperature T8 of the refrigerant flowing out from the refrigerant passage of the second battery cooler 19b.

The evaporator temperature sensor 64i is an evaporator temperature detection unit that detects the evaporator temperature Tefin, which is the refrigerant evaporation temperature in the indoor evaporator 18. The evaporator temperature sensor 64i of the present embodiment detects the heat exchange fin temperature of the indoor evaporator 18.

The first refrigerant pressure sensor 65a is a first refrigerant pressure detecting unit that detects the pressure P1 of the refrigerant flowing out from the refrigerant passage of the water refrigerant heat exchanger 12. The second refrigerant pressure sensor 65b is a second refrigerant pressure detecting unit that detects the pressure P2 of the refrigerant flowing out from the refrigerant passage of the first battery cooler 19a and the refrigerant passage of the second battery cooler 19b.

The high temperature side heat medium temperature sensor 66a is a high temperature side heat medium temperature detection unit that detects the high temperature side heat medium temperature TWH, which is the temperature of the high temperature side heat medium flowing out from the water passage of the water refrigerant heat exchanger 12.

The battery control device 69 is a battery control unit that controls the input / output of the battery. A detection signal from the battery temperature sensor 69a is input to the battery control device 69.

The battery temperature sensor 69a is a battery temperature detecting unit that detects the battery temperature TB (that is, the battery temperature). The battery temperature sensor 69a of the present embodiment has a plurality of temperature sensors and detects the temperature of a plurality of points of the battery. Therefore, the cycle control device 60 can also detect the temperature difference of each part of the battery. As the battery temperature TB, the average value of the detected values of a plurality of temperature sensors is adopted.

Information such as the time when the rapid charging of the battery is started and the battery temperature TB is input from the battery control device 69 to the cycle control device 60.

An operation panel 70 arranged near the instrument panel at the front of the vehicle interior is connected to the input side of the cycle control device 60, and operation signals from various operation switches provided on the operation panel 70 are input.

Specific examples of the various operation switches provided on the operation panel 70 include an auto switch that sets or cancels the automatic control operation of the vehicle air conditioner, an air conditioner switch that requires the indoor evaporator 18 to cool the air, and the like. There are an air volume setting switch for manually setting the air volume of the blower 32, a temperature setting switch for setting the target temperature Tset in the vehicle interior, a blow mode changeover switch for manually setting the blow mode, and the like.

The cycle control device 60 of the present embodiment is integrally configured with a control unit that controls various controlled devices connected to the output side of the cycle control device 60. The configuration (hardware and software) that controls the operation of each of the control target devices in the cycle control device 60 is a control unit that controls the operation of each control target device.

For example, in the cycle control device 60, the configuration for controlling the refrigerant discharge capacity of the compressor 11 (specifically, the rotation speed of the compressor 11) is the compressor control unit 60a. Further, the configuration for controlling the operation of the heating expansion valve 14a, the cooling expansion valve 14b, the first cooling expansion valve 14c, and the second cooling expansion valve 14d is the expansion valve control unit 60b. The configuration that controls the operation of the dehumidifying on-off valve 15a and the heating on-off valve 15b is the refrigerant circuit switching control unit 60c.

The configuration for controlling the pumping capacity of the high temperature side heat medium of the high temperature side heat medium pump 41 is the high temperature side heat medium pump control unit 60d.

Next, the operation of the present embodiment in the above configuration will be described. The vehicle air conditioner 1 of the present embodiment air-conditions the interior of the vehicle and adjusts the temperature of the battery. In the refrigerating cycle device 10, the refrigerant circuit can be switched to operate in the following 11 types of operation modes.

(1) Cooling mode: The cooling mode is an operation mode in which the inside of the vehicle is cooled by cooling the air and blowing it into the vehicle interior without cooling the battery.

(2) Series dehumidification / heating mode: The series dehumidification / heating mode is an operation mode in which the inside of the vehicle is dehumidified and heated by reheating the cooled and dehumidified air and blowing it into the vehicle interior without cooling the battery. be.

(3) Parallel dehumidification / heating mode: The parallel dehumidification / heating mode reheats the cooled and dehumidified air with a higher heating capacity than the series dehumidification / heating mode and blows it into the vehicle interior without cooling the battery. This is an operation mode for dehumidifying and heating the interior of the vehicle.

(4) Heating mode: The heating mode is an operation mode in which the interior of the vehicle is heated by heating the air and blowing it into the vehicle interior without cooling the battery.

(5) Cooling cooling mode: The cooling cooling mode is an operation mode in which the inside of the vehicle is cooled by cooling the battery and cooling the air to the inside of the vehicle.

(6) Series dehumidification / heating / cooling mode: The series dehumidification / heating / cooling mode is an operation mode in which the battery is cooled and the cooled and dehumidified air is reheated and blown into the vehicle interior to perform dehumidification / heating. Is.

(7) Parallel dehumidifying / heating / cooling mode: The parallel dehumidifying / heating / cooling mode cools the battery and reheats the cooled and dehumidified air with a higher heating capacity than the series dehumidifying / heating / cooling mode and blows it into the vehicle interior. This is an operation mode in which dehumidifying and heating the interior of the vehicle is performed.

(8) Heating / cooling mode: The heating / cooling mode is an operation mode in which the battery is cooled and the interior of the vehicle is heated by heating the air and blowing it into the vehicle interior.

(9) Heating series cooling mode: The heating series cooling mode is an operation mode in which the battery is cooled and the interior of the vehicle is heated by heating the air with a heating capacity higher than that of the heating / cooling mode and blowing it into the vehicle interior. be.

(10) Heating parallel cooling mode: The heating parallel cooling mode is an operation mode in which the battery is cooled and the interior of the vehicle is heated by heating the air with a higher heating capacity than the heating series cooling mode and blowing it into the vehicle interior. Is.

(11) Cooling mode: An operation mode in which the battery is cooled without air-conditioning the interior of the vehicle.

Switching between these operation modes is performed by executing a control program. The control program is executed when the auto switch of the operation panel 70 is turned on (ON) by the operation of the occupant and the automatic control in the vehicle interior is set. The control program will be described with reference to FIGS. 3 to 7. Further, each control step shown in the flowchart of FIG. 3 or the like is a function realization unit included in the cycle control device 60.

First, in step S10 of FIG. 3, the detection signal of the sensor group described above and the operation signal of the operation panel 70 are read. In the following step S20, the target blowout temperature TAO, which is the target temperature of the air blown into the vehicle interior, is determined based on the detection signal and the operation signal read in step S10. Therefore, step S20 is a target blowout temperature determination unit.

Specifically, the target blowout temperature TAO is calculated by the following mathematical formula F1.
TAO = Kset x Tset-Kr x Tr-Kam x Tam-Ks x Ts + C ... (F1)
In addition, Tset is the vehicle interior set temperature set by the temperature setting switch. Tr is the vehicle interior temperature detected by the inside air sensor. Tam is the temperature outside the vehicle interior detected by the outside air sensor. Ts is the amount of solar radiation detected by the solar radiation sensor. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

Next, in step S30, it is determined whether or not the air conditioner switch is turned on. The fact that the air conditioner switch is turned on means that the occupant is requesting cooling or dehumidification of the passenger compartment. In other words, turning on the air conditioner switch means that it is required to cool the air with the indoor evaporator 18.

If it is determined in step S30 that the air conditioner switch is turned on, the process proceeds to step S40. If it is determined in step S30 that the air conditioner switch is not turned on, the process proceeds to step S160.

In step S40, it is determined whether or not the outside air temperature Tam is equal to or higher than the predetermined standard non-standard air temperature KA (0 ° C. in this embodiment). The non-standard air temperature KA is set so that cooling the air with the indoor evaporator 18 is effective for cooling or dehumidifying the air-conditioned space.

More specifically, in the present embodiment, in order to suppress the frost formation of the indoor evaporator 18, the evaporation pressure adjusting valve 20 sets the refrigerant evaporation temperature in the indoor evaporator 18 to the frost formation suppression temperature (1 ° C. in the present embodiment). ) More than that. Therefore, the indoor evaporator 18 cannot cool the air to a temperature lower than the frost formation suppression temperature.

That is, when the temperature of the air flowing into the indoor evaporator 18 is lower than the temperature of the frost formation suppression temperature, it is not effective to cool the air with the indoor evaporator 18. Therefore, the non-standard air temperature KA is set to a value lower than the frost formation suppression temperature, and when the outside air temperature Tam is lower than the standard non-standard air temperature KA, the air is not cooled by the indoor evaporator 18.

If it is determined in step S40 that the outside air temperature Tam is equal to or higher than the standard non-standard air temperature KA, the process proceeds to step S50. If it is determined in step S40 that the outside air temperature Tam is not equal to or higher than the standard non-standard air temperature KA, the process proceeds to step S160.

In step S50, it is determined whether or not the target blowing temperature TAO is equal to or lower than the cooling reference temperature α1. The cooling reference temperature α1 is determined by the cycle control device 60.

If it is determined in step S50 that the target blowing temperature TAO is equal to or lower than the cooling reference temperature α1, the process proceeds to step S60. If it is determined in step S50 that the target blowing temperature TAO is not equal to or lower than the cooling reference temperature α1, the process proceeds to step S90.

In step S60, it is determined whether or not the battery needs to be cooled. Specifically, in the present embodiment, the battery is cooled when the battery temperature TB detected by the battery temperature sensor 69a is equal to or higher than the predetermined reference cooling temperature KTB (35 ° C. in the present embodiment). Determined to be necessary. Further, when the battery temperature TB is lower than the reference cooling temperature KTB, it is determined that the battery does not need to be cooled.

If it is determined in step S60 that the battery needs to be cooled, the process proceeds to step S70, and (5) cooling cooling mode is selected as the operation mode. If it is determined in step S60 that the battery does not need to be cooled, the process proceeds to step S80, and (1) cooling mode is selected as the operation mode.

In step S90, it is determined whether or not the target blowing temperature TAO is equal to or lower than the dehumidifying reference temperature β1. The dehumidifying reference temperature β1 is determined by the cycle control device 60. The dehumidifying reference temperature β1 is determined to be higher than the cooling reference temperature α1.

If it is determined in step S90 that the target blowing temperature TAO is equal to or lower than the dehumidifying reference temperature β1, the process proceeds to step S100. If it is determined in step S90 that the target blowout temperature TAO is not equal to or lower than the dehumidification reference temperature β1, the process proceeds to step S130.

In step S100, as in step S60, it is determined whether or not the battery needs to be cooled.

If it is determined in step S100 that the battery needs to be cooled, the process proceeds to step S110, and (6) series dehumidification / heating / cooling mode is selected as the operation mode of the refrigeration cycle device 10. If it is determined in step S100 that the battery does not need to be cooled, the process proceeds to step S120, and (2) series dehumidification / heating mode is selected as the operation mode.

In step S130, as in step S60, it is determined whether or not the battery needs to be cooled.

If it is determined in step S130 that the battery needs to be cooled, the process proceeds to step S140, and (7) parallel dehumidification / heating / cooling mode is selected as the operation mode of the refrigeration cycle device 10. If it is determined in step S100 that the battery does not need to be cooled, the process proceeds to step S150, and (3) parallel dehumidification / heating mode is selected as the operation mode.

Subsequently, a case where the process proceeds from step S30 or step S40 to step S160 will be described. When the process proceeds from step S30 or step S40 to step S160, it is a case where it is determined that it is not effective to cool the air with the indoor evaporator 18. In step S160, as shown in FIG. 4, it is determined whether or not the target blowing temperature TAO is equal to or higher than the heating reference temperature γ.

The heating reference temperature γ is determined by the cycle control device 60. The heating reference temperature γ is set so that heating the air with the heater core 42 is effective for heating the air-conditioned space.

If it is determined in step S160 that the target outlet temperature TAO is equal to or higher than the heating reference temperature γ, it is necessary to heat the air with the heater core 42, and the process proceeds to step S170. If it is determined in step S160 that the target outlet temperature TAO is not equal to or higher than the heating reference temperature γ, it is not necessary to heat the air with the heater core 42, and the process proceeds to step S240.

In step S170, as in step S60, it is determined whether or not the battery needs to be cooled.

If it is determined in step S170 that the battery needs to be cooled, the process proceeds to step S180. If it is determined in step S170 that the battery does not need to be cooled, the process proceeds to step S230, and (4) heating mode is selected as the operation mode.

Here, when it is determined in step S170 that the battery needs to be cooled and the process proceeds to step S180, it is necessary to both heat the vehicle interior and cool the battery. Therefore, in the refrigerating cycle device 10, the amount of heat dissipated by the refrigerant to the high-temperature side heat medium in the water-refrigerant heat exchanger 12 and the amount of heat absorbed by the refrigerant from the batteries in the first battery cooler 19a and the second battery cooler 19b. It is necessary to properly adjust the amount of heat absorbed.

Therefore, in the refrigerating cycle device 10 of the present embodiment, when it is necessary to perform both heating of the vehicle interior and cooling of the battery, as shown in steps S180 to S220 of FIG. 4, (8) heating / cooling mode , (9) Heating series cooling mode and (10) Heating parallel cooling mode are switched.

First, in step S180, it is determined whether or not the target blowing temperature TAO is equal to or lower than the low temperature side cooling reference temperature α2. The low temperature side cooling reference temperature α2 is determined by the cycle control device 60. The cooling reference temperature α2 on the low temperature side is determined to be higher than the cooling reference temperature α1 and lower than the dehumidifying reference temperature β1.

If it is determined in step S180 that the target outlet temperature TAO is the low temperature side cooling reference temperature α2 or less, the process proceeds to step S190, and (8) heating / cooling mode is selected as the operation mode. If it is determined in step S180 that the target blowing temperature TAO is not equal to or lower than the low temperature side cooling reference temperature α2, the process proceeds to step S200.

In step S200, it is determined whether or not the target blowing temperature TAO is equal to or lower than the high temperature side cooling reference temperature β2. The high temperature side cooling reference temperature β2 is determined by the cycle control device 60. The high temperature side cooling reference temperature β2 is determined to be higher than the dehumidifying reference temperature β1.

If it is determined in step S200 that the target outlet temperature TAO is equal to or lower than the high temperature side cooling reference temperature β2, the process proceeds to step S210, and (9) heating series cooling mode is selected as the operation mode. If it is determined in step S200 that the target outlet temperature TAO is not equal to or lower than the high temperature side cooling reference temperature β2, the process proceeds to step S220, and (10) heating parallel cooling mode is selected as the operation mode.

Subsequently, a case where the process proceeds from step S160 to step S240 will be described. When the process proceeds from step S160 to step S240, it is not necessary to heat the air with the heater core 42. Therefore, in step S240, it is determined whether or not the battery needs to be cooled, as in step S60.

If it is determined in step S240 that the battery needs to be cooled, the process proceeds to step S250, and (11) cooling mode is selected as the operation mode. If it is determined in step S200 that the battery does not need to be cooled, the process proceeds to step S260, the ventilation mode is selected as the operation mode, and the process returns to step S10.

The blower mode is an operation mode in which the compressor 11 is stopped and the blower 32 is operated according to the setting signal set by the air volume setting switch. If it is determined in step S240 that the battery does not need to be cooled, it is not necessary to operate the refrigerating cycle device 10 for air conditioning in the vehicle interior and cooling of the battery.

In the control program of the present embodiment, the operation mode of the refrigerating cycle device 10 is switched as described above. Further, this control program controls not only the operation of each component of the refrigeration cycle device 10, but also the operation of the high temperature side heat medium pump 41 of the high temperature side heat medium circuit 40 constituting the heating unit.

Specifically, the cycle control device 60 operates the high temperature side heat medium pump 41 so as to exhibit the reference pumping capacity for each predetermined operation mode regardless of the operation mode of the refrigeration cycle device 10 described above. Control.

Therefore, in the high temperature side heat medium circuit 40, when the high temperature side heat medium is heated in the water passage of the water refrigerant heat exchanger 12, the heated high temperature side heat medium is pressure-fed to the heater core 42. The high temperature side heat medium flowing into the heater core 42 exchanges heat with air. This heats the air. The high temperature side heat medium flowing out of the heater core 42 is sucked into the high temperature side heat medium pump 41 and pumped to the water refrigerant heat exchanger 12.

The detailed operation of the vehicle air conditioner 1 in each operation mode will be described below. In each operation mode, the cycle control device 60 executes the control flow of each operation mode.

(1) Cooling mode In the cooling mode, the control device 60 executes the control flow of the cooling mode shown in FIG. First, in step S600, the target evaporator temperature TEO is determined. The target evaporator temperature TEO is determined based on the target blowout temperature TAO with reference to the control map stored in the cycle control device 60. In the control map of the present embodiment, it is determined that the target evaporator temperature TEO increases as the target blowout temperature TAO increases.

In step S610, the amount of increase / decrease ΔIVO in the rotation speed of the compressor 11 is determined. The increase / decrease amount ΔIVO is set so that the evaporator temperature Tefin approaches the target evaporator temperature TEO by the feedback control method based on the deviation between the target evaporator temperature TEO and the evaporator temperature Tefin detected by the evaporator temperature sensor 64i. It is determined.

When the rotation speed of the compressor 11 is increased or decreased by the increase / decrease amount ΔIVO and the rotation speed of the compressor 11 is less than the lower limit rotation speed Ncmin (1000 rpm in this embodiment), the compressor 11 is stopped.

In step S620, the target supercooling degree SCO1 of the refrigerant flowing out from the outdoor heat exchanger 16 is determined. The target supercooling degree SCO1 is determined with reference to the control map, for example, based on the outside air temperature Tam. In the control map of the present embodiment, the target supercooling degree SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.

In step S630, the amount of increase / decrease ΔEVC in the throttle opening of the cooling expansion valve 14b is determined. The increase / decrease amount ΔEVC is the supercooling degree of the outlet side refrigerant of the outdoor heat exchanger 16 by the feedback control method based on the deviation between the target supercooling degree SCO1 and the supercooling degree SC1 of the outlet side refrigerant of the outdoor heat exchanger 16. SC1 is determined to approach the target supercooling degree SCO1.

The degree of supercooling SC1 of the outlet side refrigerant of the outdoor heat exchanger 16 is calculated based on the temperature T3 detected by the third refrigerant temperature sensor 64c and the pressure P1 detected by the first refrigerant pressure sensor 65a.

In step S640, the opening SW of the air mix door 34 is calculated using the following mathematical formula F2.
SW = {TAO + (Tefin + C2)} / {TWH + (Tefin + C2)}
… (F2)
The TWH is the high temperature side heat medium temperature detected by the high temperature side heat medium temperature sensor 66a. C2 is a constant for control.

In step S650, in order to switch the refrigerating cycle device 10 to the cooling mode refrigerant circuit, the heating expansion valve 14a is set to the fully open state, the cooling expansion valve 14b is set to the throttle state that exerts the refrigerant depressurizing action, and the first cooling expansion is performed. The valve 14c and the second cooling expansion valve 14d are fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, the control signal or the control voltage is output to each controlled device so that the control state determined in the above step can be obtained, and the process returns to step S10.

Therefore, in the refrigerating cycle device 10 in the cooling mode, the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, the indoor evaporator 18, A steam compression type refrigeration cycle in which the refrigerant circulates in the order of the evaporative pressure regulating valve 20, the accumulator 21, and the compressor 11 is configured.

That is, in the refrigerating cycle device 10 in the cooling mode, the water refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a radiator (in other words, a radiator) for dissipating the refrigerant discharged from the compressor 11 for cooling. A steam compression type refrigeration cycle is configured in which the expansion valve 14b functions as a pressure reducing unit for reducing the pressure of the refrigerant, and the indoor evaporator 18 functions as an evaporator.

According to this, the air can be cooled by the indoor evaporator 18, and the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12.

Therefore, in the vehicle air conditioner 1 in the cooling mode, a part of the air cooled by the indoor evaporator 18 is reheated by the heater core 42 by adjusting the opening degree of the air mix door 34, and approaches the target blowing temperature TAO. By blowing out the air whose temperature has been adjusted so as to be blown into the vehicle interior, the vehicle interior can be cooled.

(2) Series dehumidification / heating mode In the control flow of the series dehumidification / heating mode, the target evaporator temperature TEO is determined in the first step as in the cooling mode. In the next step, as in the cooling mode, the amount of increase / decrease ΔIVO in the rotation speed of the compressor 11 is determined.

When the rotation speed of the compressor 11 is increased or decreased by the increase / decrease amount ΔIVO and the rotation speed of the compressor 11 is less than the lower limit rotation speed Ncmin (1000 rpm in this embodiment), the compressor 11 is stopped.

In the next step, the target high temperature side heat medium temperature TWHO of the high temperature side heat medium is determined so that the air can be heated by the heater core 42. The target high temperature side heat medium temperature TWHO is determined with reference to the control map based on the target blowout temperature TAO and the efficiency of the heater core 42. In the control map of the present embodiment, it is determined that the target high temperature side heat medium temperature TWHO increases as the target blowout temperature TAO increases.

In the next step, the throttle opening of the heating expansion valve 14a and the throttle opening of the cooling expansion valve 14b are determined. Specifically, in the series dehumidifying and heating mode, as the target outlet temperature TAO rises, the throttle opening of the heating expansion valve 14a decreases, and the throttle opening of the cooling expansion valve 14b increases.

In the next step, the opening SW of the air mix door 34 is calculated in the same manner as in the cooling mode. Here, in the series dehumidifying / heating mode, the target blowing temperature TAO is higher than in the cooling mode, so that the opening SW of the air mix door 34 approaches 100%. Therefore, in the series dehumidifying / heating mode, the opening degree of the air mix door 34 is determined so that almost the entire flow rate of the air after passing through the indoor evaporator 18 passes through the heater core 42.

In the next step, in order to switch the refrigerating cycle device 10 to the refrigerant circuit in the series dehumidifying and heating mode, the heating expansion valve 14a is set to the throttle state, the cooling expansion valve 14b is set to the throttle state, and the first cooling expansion valve 14c and The second cooling expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, the control signal or the control voltage is output to each controlled device so that the control state determined in the above step can be obtained, and the process returns to step S10.

Therefore, in the refrigerating cycle device 10 in the series dehumidifying / heating mode, the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, and the indoor evaporator. A steam compression type refrigeration cycle in which the refrigerant circulates in the order of 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 is configured.

That is, in the refrigerating cycle device 10 in the series dehumidifying and heating mode, the water-refrigerant heat exchanger 12 functions as a radiator (in other words, a radiator) that dissipates the refrigerant discharged from the compressor 11, and the heating expansion valve 14a and A steam compression type refrigeration cycle is configured in which the expansion valve 14b for cooling functions as a pressure reducing unit and the indoor evaporator 18 functions as an evaporator.

Further, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, a cycle is configured in which the outdoor heat exchanger 16 functions as a radiator (in other words, a radiator). .. When the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, a cycle in which the outdoor heat exchanger 16 functions as an evaporator is configured.

According to this, the air can be cooled by the indoor evaporator 18, and the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the series dehumidifying / heating mode, the air cooled by the indoor evaporator 18 and dehumidified is reheated by the heater core 42 and blown out into the vehicle interior to dehumidify and heat the vehicle interior. It can be carried out.

(3) Parallel dehumidifying and heating mode In the first step of the control flow of the parallel dehumidifying and heating mode, the target high temperature side heat medium temperature of the high temperature side heat medium is the same as in the series dehumidifying and heating mode so that the air can be heated by the heater core 42. TWHO is determined.

In the next step, the amount of increase / decrease ΔIVO in the rotation speed of the compressor 11 is determined. When the rotation speed of the compressor 11 is increased or decreased by the increase / decrease amount ΔIVO and the rotation speed of the compressor 11 is less than the lower limit rotation speed Ncmin (1000 rpm in this embodiment), the compressor 11 is stopped.

In the parallel dehumidifying / heating mode, the increase / decrease amount ΔIVO is based on the deviation between the target high temperature side heat medium temperature TWHO and the high temperature side heat medium temperature TWH, and the high temperature side heat medium temperature TWH is the target high temperature side heat medium temperature by the feedback control method. Determined to approach TWHO.

In the next step, the target superheat degree SHEO of the outlet side refrigerant of the indoor evaporator 18 is determined. As the target superheat degree SHEO, a predetermined constant (5 ° C. in this embodiment) can be adopted.

In the next step, the throttle opening of the heating expansion valve 14a and the throttle opening of the cooling expansion valve 14b are determined. In the parallel dehumidification / heating mode, the superheat degree SH is determined to approach the target superheat degree SHEO by the feedback control method based on the deviation between the target superheat degree SHEO and the superheat degree SHE of the outlet side refrigerant of the indoor evaporator 18. ..

The degree of superheat SHE of the outlet-side refrigerant of the indoor evaporator 18 is calculated based on the temperature T4 and the evaporator temperature Tefin detected by the fourth refrigerant temperature sensor 64d.

In the next step, the opening SW of the air mix door 34 is calculated in the same manner as in the cooling mode. Here, in the parallel dehumidifying / heating mode, the target outlet temperature TAO is higher than in the cooling mode, so that the opening SW of the air mix door 34 approaches 100% as in the series dehumidifying / heating mode. Therefore, in the parallel dehumidifying / heating mode, the opening degree of the air mix door 34 is determined so that almost the entire flow rate of the air after passing through the indoor evaporator 18 passes through the heater core 42.

In the next step, in order to switch the refrigerating cycle device 10 to the refrigerant circuit in the parallel dehumidifying and heating mode, the heating expansion valve 14a is set to the throttle state, the cooling expansion valve 14b is set to the throttle state, and the first cooling expansion valve 14c and The second cooling expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is opened, and the heating on-off valve 15b is opened. Further, the control signal or the control voltage is output to each controlled device so that the control state determined in the above step can be obtained, and the process returns to step S10.

Therefore, in the refrigerating cycle device 10 in the parallel dehumidifying / heating mode, the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the compressor 11 are in that order. Circulates, and the refrigerant circulates in the order of the compressor 11, the water refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure adjusting valve 20, the accumulator 21, and the compressor 11. A compression refrigeration cycle is constructed.

That is, in the refrigeration cycle device 10 in the parallel dehumidifying / heating mode, the water-refrigerant heat exchanger 12 functions as a radiator (in other words, a radiator) for dissipating the refrigerant discharged from the compressor 11, and the heating expansion valve 14a is used. The outdoor heat exchanger 16 functions as a decompression unit, and the heating expansion valve 14a and the cooling expansion valve 14b connected in parallel to the outdoor heat exchanger 16 function as a decompression unit. , A refrigeration cycle is configured in which the indoor evaporator 18 functions as an evaporator.

According to this, the air can be cooled by the indoor evaporator 18, and the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the parallel dehumidifying / heating mode, the air cooled by the indoor evaporator 18 and dehumidified is reheated by the heater core 42 and blown out into the vehicle interior to dehumidify and heat the vehicle interior. It can be carried out.

(4) Heating mode In the first step of the control flow of the heating mode, the target high temperature side heat medium temperature TWHO of the high temperature side heat medium is determined as in the parallel dehumidifying heating mode. In the next step, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11 is determined as in the parallel dehumidification / heating mode. When the rotation speed of the compressor 11 is increased or decreased by the increase / decrease amount ΔIVO and the rotation speed of the compressor 11 is less than the lower limit rotation speed Ncmin (1000 rpm in this embodiment), the compressor 11 is stopped.

In the next step, the target supercooling degree SCO2 of the refrigerant flowing out from the refrigerant passage of the water refrigerant heat exchanger 12 is determined. The target supercooling degree SCO2 is determined with reference to the control map based on the suction temperature of the air flowing into the indoor evaporator 18 or the outside air temperature Tam. In the control map of the present embodiment, the target supercooling degree SCO2 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.

In the next step, the amount of increase / decrease ΔEVH in the throttle opening of the heating expansion valve 14a is determined. The increase / decrease amount ΔEVH is the refrigerant passage of the water refrigerant heat exchanger 12 by the feedback control method based on the deviation between the target supercooling degree SCO2 and the overcooling degree SC2 of the refrigerant flowing out from the refrigerant passage of the water refrigerant heat exchanger 12. The degree of supercooling SC2 of the refrigerant flowing out from is determined to approach the target degree of supercooling SCO2.

The degree of supercooling SC2 of the refrigerant flowing out from the refrigerant passage of the water refrigerant heat exchanger 12 is calculated based on the temperature T2 detected by the second refrigerant temperature sensor 64b and the pressure P1 detected by the first refrigerant pressure sensor 65a. To.

In the next step, the opening SW of the air mix door 34 is calculated in the same manner as in the cooling mode. Here, in the heating mode, the target outlet temperature TAO is higher than in the cooling mode, so that the opening SW of the air mix door 34 approaches 100%. Therefore, in the heating mode, the opening degree of the air mix door 34 is determined so that substantially the entire flow rate of the air after passing through the indoor evaporator 18 passes through the heater core 42.

In the next step, in order to switch the refrigerating cycle device 10 to the refrigerant circuit in the heating mode, the heating expansion valve 14a is set to the throttled state, the cooling expansion valve 14b is set to the fully closed state, and the first cooling expansion valve 14c and the first 2 The cooling expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is opened. Further, the control signal or the control voltage is output to each controlled device so that the control state determined in the above step can be obtained, and the process returns to step S10.

Therefore, in the refrigerating cycle device 10 in the heating mode, the refrigerant circulates in the order of the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the compressor 11. A steam compression type refrigeration cycle is constructed.

That is, in the refrigeration cycle device 10 in the heating mode, the water-refrigerant heat exchanger 12 functions as a radiator (in other words, a radiator) that dissipates heat from the refrigerant discharged from the compressor 11, and the heating expansion valve 14a is a decompression unit. A refrigeration cycle is configured in which the outdoor heat exchanger 16 functions as an evaporator.

According to this, the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the heating mode, the interior of the vehicle can be heated by blowing out the air heated by the heater core 42 into the interior of the vehicle.

(5) Cooling Cooling Mode In the cooling cooling mode, the control device 60 executes the control flow in the cooling cooling mode shown in FIGS. 6 to 7. First, in step S1100, it is determined whether or not the rotation speed Nc0 before switching is 3000 rpm or less. The rotation speed Nc0 before switching is the rotation speed of the compressor 11 before switching to the cooling / cooling mode.

If it is determined in step S1100 that the rotation speed Nc0 before switching is 3000 rpm or less, the process proceeds to step S1110. If it is determined in step S1100 that the rotation speed Nc0 before switching is not 3000 rpm or less, the process proceeds to step S1140.

In step S1110, it is determined whether or not the battery is in the initial stage of cooling. In the present embodiment, when the elapsed time ct after switching to the cooling cooling mode is within a predetermined time tcO (for example, 100 seconds), it is determined that the battery is in the initial stage of cooling. When the elapsed time tc after switching to the cooling cooling mode exceeds the predetermined time tcO, it is determined that the battery is not in the initial stage of cooling start.

If it is determined in step S1110 that the battery is in the initial stage of cooling, the process proceeds to step S1120. If it is determined in step S60 that it is not the initial stage of cooling the battery, the process proceeds to step S1130.

In step S1120, the control execution flag is turned ON and the process proceeds to step S1140. In step S1130, the control execution flag is turned off and the process proceeds to step S1140.

The control execution flag is a flag for controlling the blowout temperature fluctuation of the indoor evaporator 18 when (1) the cooling mode or the like is switched to (5) the cooling cooling mode.

In step S1140, the lower limit rotation speed Ncmin of the compressor 11 is determined to be higher than the other operation modes. In other words, the lower limit of the refrigerant discharge capacity of the compressor 11 is determined to be higher than that of other operation modes.

Specifically, while (1) the lower limit rotation speed Ncmin is 1000 rpm in the cooling mode or the like, (5) the lower limit rotation speed Ncmin is increased to 3000 rpm in the cooling cooling mode. However, the lower limit rotation speed Ncmin is not increased all at once to 3000 rpm, but is gradually increased with the passage of time. Specifically, the rotation speed obtained by adding a predetermined rotation speed to the previous lower limit rotation speed Ncmin is defined as the current lower limit rotation speed Ncmin. When the rotation speed obtained by adding the predetermined rotation speed to the previous lower limit rotation speed Ncmin is 3000 rpm or more, the lower limit rotation speed Ncmin is set to 3000 rpm.

In steps S1150 to S1190, the target evaporator temperature TEO, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11, the increase / decrease amount ΔEVC of the throttle opening of the cooling expansion valve 14b, and the air mix are the same as in steps S600 to S640 of the cooling mode. The opening SW of the door 34 is determined.

Next, in step S1200, the target superheat degree SHCO of the refrigerant on the outlet side of the refrigerant passage of the first battery cooler 19a and the second battery cooler 19b is determined. As the target superheat degree SHCO, a predetermined constant (5 ° C. in this embodiment) can be adopted.

In step S1210, the increase / decrease amount ΔEVB1 of the throttle opening of the first cooling expansion valve 14c and the increase / decrease amount ΔEVB2 of the throttle opening of the second cooling expansion valve 14d are determined.

In the cooling cooling mode, the increase / decrease amount ΔEVB1 of the throttle opening of the first cooling expansion valve 14c is based on the deviation between the target superheat degree SHCO and the superheat degree SHC1 of the refrigerant flowing out from the refrigerant passage of the first battery cooler 19a. The feedback control method determines that the overheating degree SHC1 of the refrigerant flowing out of the refrigerant passage of the first battery cooler 19a approaches the target overheating degree SHCO.

The degree of superheat SHC1 of the refrigerant flowing out from the refrigerant passage of the first battery cooler 19a is calculated based on the temperature T5 detected by the fifth refrigerant temperature sensor 64e and the pressure P2 detected by the second refrigerant pressure sensor 65b. ..

In the cooling cooling mode, the increase / decrease amount ΔEVB2 of the throttle opening of the second cooling expansion valve 14c is based on the deviation between the target overheating degree SHCO and the overheating degree SHC2 of the refrigerant flowing out from the refrigerant passage of the second battery cooler 19b. The feedback control method determines that the overheating degree SHC2 of the refrigerant flowing out of the refrigerant passage of the second battery cooler 19b approaches the target overheating degree SHCO.

The degree of superheat SHC2 of the refrigerant flowing out from the refrigerant passage of the second battery cooler 19b is calculated based on the temperature T7 detected by the seventh refrigerant temperature sensor 64g and the pressure P2 detected by the second refrigerant pressure sensor 65b. ..

Next, in step S1220, it is determined whether or not the evaporator temperature Tefin has reached the target evaporator temperature TEO. If it is determined in step S1220 that the evaporator temperature Tefin has reached the target evaporator temperature TEO, the process proceeds to step S1230. If it is determined in step S1220 that the evaporator temperature Tefin has not reached the target evaporator temperature TEO, the process proceeds to step S1270.

In step S1230, it is determined whether or not the control execution flag is turned ON. If it is determined in step S1230 that the control execution flag is not turned ON, the process proceeds to step S1240. If it is determined in step S1230 that the control execution flag is ON, the process proceeds to step S1270.

In step S1240, it is determined whether or not the battery temperature TB has reached the target battery temperature TBO. That is, it is determined whether or not the battery needs to be cooled. If it is determined in step S1240 that the battery temperature TB has reached the target battery temperature TBO, that is, if it is not necessary to cool the battery, the process proceeds to step S1250. If it is determined in step S1240 that the battery temperature TB has not reached the target battery temperature TBO, that is, if it is necessary to cool the battery, the process proceeds to step S1260.

In step S1240, it may be determined whether or not the battery needs to be cooled based on whether or not the temperature of the first battery cooler 19a and the temperature of the second battery cooler 19b have reached the target temperature.

In step S1250, it is decided to stop the compressor 11, and the process proceeds to step S1330. In step S1260, it is determined that the cooling expansion valve 14b is fully closed, and the process proceeds to step S1330.

In step S1270, it is determined whether or not the battery temperature TB has reached the target battery temperature TBO. If it is determined in step S1270 that the battery temperature TB has reached the target battery temperature TBO, the process proceeds to step S1280. If it is determined in step S1270 that the battery temperature TB has not reached the target battery temperature TBO, the process proceeds to step S1300.

In step S1280, it is determined whether or not the control execution flag is turned ON. If it is determined in step S1280 that the control execution flag is not turned ON, the process proceeds to step S1290. If it is determined in step S1280 that the control execution flag is ON, the process proceeds to step S1300.

In step S1290, it is determined that the first cooling expansion valve 14c and the second cooling expansion valve 14d are fully closed, and the process proceeds to step S1330.

In step S1300, it is determined whether or not the control execution flag is turned ON. If it is determined in step S1300 that the control execution flag is ON, the process proceeds to step S1320. If it is determined in step S1300 that the control execution flag is not turned ON, the process proceeds to step S1330.

In step S1320, the throttle opening of the first cooling expansion valve 14c and the throttle opening of the second cooling expansion valve 14d are determined to be larger than the throttle opening determined in step S1210. For example, the aperture opening is determined to be 2.5 times the aperture opening determined in step S1210.

In step S1330, in order to switch the refrigerating cycle device 10 to the refrigerant circuit in the cooling cooling mode, the heating expansion valve 14a is set to the fully open state, the cooling expansion valve 14b is set to the throttle state, and the first cooling expansion valve 14c and the second are set. The cooling expansion valve 14d is in a throttled state, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or a control voltage is output to each device to be controlled so that the control state determined in steps S1140, S1160, S1180, S1190, S1210, S1250, S1260, S1290, and S1320 can be obtained, and the step. Return to S10.

Therefore, in the refrigerating cycle device 10 in the cooling cooling mode, the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, and the indoor evaporator 18 Refrigerant circulates in the order of the evaporation pressure adjusting valve 20, the accumulator 21, the compressor 11, and the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, and the first. 1 A steam compression type refrigeration cycle in which the refrigerant circulates in the order of the cooling expansion valve 14c, the second cooling expansion valve 14d, the first battery cooler 19a and the second battery cooler 19b, the accumulator 21, and the compressor 11 is configured. To.

That is, in the refrigerating cycle device 10 in the cooling cooling mode, the water refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as radiators to dissipate the refrigerant discharged from the compressor 11, and the cooling expansion valve 14b is the decompression unit. The indoor evaporator 18 functions as an evaporator, and the first cooling expansion valve 14c and the second cooling expansion valve 14d connected in parallel to the cooling expansion valve 14b and the indoor evaporator 18 Functions as a decompression unit, and a refrigerating cycle in which the first battery cooler 19a and the second battery cooler 19b function as an evaporator is configured.

According to this, the blown air can be cooled by the indoor evaporator 18, and the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12.

Therefore, in the vehicle air conditioner 1 in the cooling / cooling mode, a part of the blown air cooled by the indoor evaporator 18 is reheated by the heater core 42 by adjusting the opening degree of the air mix door 34, and the target blowing temperature TAO. The interior of the vehicle can be cooled by blowing out the blown air whose temperature has been adjusted so as to approach.

Further, the battery can be cooled by the first battery cooler 19a and the second battery cooler 19b.

When the rotation speed Nc of the compressor 11 is switched to the cooling cooling mode at a low load of 3000 rpm or less, the lower limit rotation speed Ncmin of the compressor 11 is gradually increased from 1000 rpm to 3000 rpm in step S1140.

According to this, it is possible to suppress that the flow rate of the refrigerant flowing into the indoor evaporator 18 suddenly increases when the cooling / cooling mode is switched to, and the temperature of the air blown out from the indoor evaporator 18 fluctuates significantly.

When the rotation speed Nc of the compressor 11 is switched to the cooling cooling mode at a low load of 3000 rpm or less, the first cooling expansion valve 14c is performed in step S1320 during the period from the switching to the cooling cooling mode to tcO for a predetermined time. And the throttle opening of the second cooling expansion valve 14d is made larger than that in the normal control.

According to this, it is possible to suppress that the flow rate of the refrigerant flowing into the indoor evaporator 18 suddenly increases when the cooling / cooling mode is switched to, and the temperature of the air blown out from the indoor evaporator 18 fluctuates significantly.

When the rotation speed Nc of the compressor 11 is switched to the cooling cooling mode at a low load of 3000 rpm or less, the evaporator temperature Tefin becomes the target evaporator temperature TEO during the predetermined time tcO after switching to the cooling cooling mode. Even if it reaches, the cooling expansion valve 14b is not fully closed by step S1230.

According to this, since the undershoot and overshoot in the indoor evaporator 18 can be suppressed, it is possible to suppress a large fluctuation in the temperature of the blown air from the indoor evaporator 18.

When the rotation speed Nc of the compressor 11 is switched to the cooling cooling mode at a low load of 3000 rpm or less, the battery temperature TB reaches the target battery temperature TBO during the predetermined time tcO after switching to the cooling cooling mode. However, the first cooling expansion valve 14c and the second cooling expansion valve 14d are not fully closed by step S1280.

According to this, when the battery temperature TB reaches the target battery temperature TBO, the flow rate of the refrigerant flowing into the indoor evaporator 18 suddenly increases, and it is possible to prevent the temperature of the blown air from the indoor evaporator 18 from fluctuating significantly.

(6) In-series dehumidifying / heating / cooling mode In the first step of the control flow of the in-series dehumidifying / heating / cooling mode, the target evaporator temperature TEO, the amount of increase / decrease in the number of revolutions of the compressor 11 ΔIVO, and the target high temperature side are the same as in the series dehumidifying / heating mode. The heat medium temperature TWHO, the throttle opening degree of the heating expansion valve 14a, the throttle opening degree of the cooling expansion valve 14b, and the opening degree SW of the air mix door 34 are determined.

In the next step, as in the cooling cooling mode, the target superheat degree SHEO, the increase / decrease amount ΔEVB1 of the throttle opening of the first cooling expansion valve 14c, and the increase / decrease amount ΔEVB2 of the throttle opening of the second cooling expansion valve 14d are determined. do.

In the next step, in order to switch the refrigerating cycle device 10 to the refrigerant circuit in the series dehumidifying / heating / cooling mode, the heating expansion valve 14a is set to the throttle state, the cooling expansion valve 14b is set to the throttle state, and the first cooling expansion valve 14c is set. The second cooling expansion valve 14d is set to the throttled state, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed.

Further, the control signal or the control voltage is output to each controlled device so that the control state determined in the above step can be obtained, and the process returns to step S10.

Therefore, in the series dehumidifying / heating / cooling mode, the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, the indoor evaporator 18, and the evaporation pressure. The refrigerant circulates in the order of the regulating valve 20, the accumulator 21, the compressor 11, and the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, and the first cooling. A steam compression type refrigeration cycle in which the refrigerant circulates in the order of the expansion valve 14c, the second cooling expansion valve 14d, the first battery cooler 19a and the second battery cooler 19b, the accumulator 21, and the compressor 11 is configured.

That is, in the refrigerating cycle device 10 in the series dehumidifying / heating / cooling mode, the water-refrigerant heat exchanger 12 functions as a radiator (in other words, a radiator), the indoor evaporator 18, the first cooling expansion valve 14c, and the second cooling. A steam compression type refrigeration cycle is configured in which the expansion valve 14d functions as an evaporator.

That is, in the refrigeration cycle device 10 in the series dehumidifying / heating mode, the water-refrigerant heat exchanger 12 functions as a radiator (in other words, a radiator) that dissipates the refrigerant discharged from the compressor 11, and the heating expansion valve 14a is used. It functions as a decompression unit, and further, the cooling expansion valve 14b functions as a decompression unit, the indoor evaporator 18 functions as an evaporator, and is connected in parallel to the cooling expansion valve 14b and the indoor evaporator 18. A refrigeration cycle is configured in which the first cooling expansion valve 14c and the second cooling expansion valve 14d function as a pressure reducing unit, and the first battery cooler 19a and the second battery cooler 19b function as an evaporator.

Further, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, a cycle is configured in which the outdoor heat exchanger 16 functions as a radiator (in other words, a radiator). .. When the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, a cycle in which the outdoor heat exchanger 16 functions as an evaporator is configured.

According to this, the air can be cooled by the indoor evaporator 18, and the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12.

Therefore, in the refrigerating cycle device 10 in the series dehumidifying / heating / cooling mode, the air cooled by the indoor evaporator 18 and dehumidified is reheated by the heater core 42 and blown out into the vehicle interior to dehumidify and heat the vehicle interior. It can be carried out.

Further, the battery can be cooled by the first battery cooler 19a and the second battery cooler 19b.

(7) Parallel dehumidifying / heating / cooling mode In the first step of the control flow of the parallel dehumidifying / heating / cooling mode, as in the parallel dehumidifying / heating mode, the target high-temperature side heat medium temperature TWHO, the amount of increase / decrease in the rotation speed of the compressor 11 ΔIVO, and the target. The degree of superheat SHEO, the throttle opening of the heating expansion valve 14a, the throttle opening of the cooling expansion valve 14b, and the opening SW of the air mix door 34 are determined.

In the next step, as in the cooling cooling mode, the target superheat degree SHEO, the increase / decrease amount ΔEVB1 of the throttle opening of the first cooling expansion valve 14c, and the increase / decrease amount ΔEVB2 of the throttle opening of the second cooling expansion valve 14d are determined. do.

In the next step, in order to switch the refrigerating cycle device 10 to the refrigerant circuit in the parallel dehumidifying / heating / cooling mode, the heating expansion valve 14a is set to the throttle state, the cooling expansion valve 14b is set to the throttle state, and the first cooling expansion valve 14c is set. The second cooling expansion valve 14d is set to the throttled state, the dehumidifying on-off valve 15a is opened, and the heating on-off valve 15b is opened.

Further, the control signal or the control voltage is output to each controlled device so that the control state determined in the above step can be obtained, and the process returns to step S10.

Therefore, in the refrigeration cycle device 10 in the parallel dehumidifying / heating / cooling mode, the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the compressor 11 are in this order. As the refrigerant circulates, the refrigerant circulates in the order of the compressor 11, the water refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure adjusting valve 20, the accumulator 21, and the compressor 11. Further, a compressor 11, a water refrigerant heat exchanger 12, a bypass passage 22a, a first cooling expansion valve 14c and a second cooling expansion valve 14d, a first battery cooler 19a and a second battery cooler 19b, an accumulator 21. , A steam compression type refrigeration cycle in which the refrigerant circulates in the order of the compressor 11 is configured.

That is, in the refrigeration cycle device 10 in the parallel dehumidifying / heating / cooling mode, the water-refrigerant heat exchanger 12 functions as a radiator (in other words, a radiator) that dissipates the refrigerant discharged from the compressor 11, and the heating expansion valve 14a. Functions as a pressure reducing unit, the outdoor heat exchanger 16 functions as an evaporator, and the cooling expansion valve 14a connected in parallel to the heating expansion valve 14a and the outdoor heat exchanger 16 functions as a pressure reducing unit. The indoor evaporator 18 functions as an evaporator, and the first cooling expansion valve 14c and the second cooling expansion valve 14d connected in parallel to the heating expansion valve 14a and the outdoor heat exchanger 16 Functions as a decompression unit, and a refrigeration cycle in which the first battery cooler 19a and the second battery cooler 19b function as an evaporator is configured.

According to this, the air can be cooled by the indoor evaporator 18, and the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12.

Therefore, in the vehicle air conditioner 1 in the parallel dehumidifying / heating / cooling mode, the air cooled by the indoor evaporator 18 and dehumidified is reheated by the heater core 42 and blown out into the vehicle interior to dehumidify and heat the vehicle interior. It can be performed. At this time, by lowering the refrigerant evaporation temperature in the outdoor heat exchanger 16 to be lower than the refrigerant evaporation temperature in the indoor evaporator 18, the air can be reheated with a heating capacity higher than that in the series dehumidifying / heating / cooling mode.

Further, the battery can be cooled by the first battery cooler 19a and the second battery cooler 19b.

(8) Heating / cooling mode In the first step of the control flow of the heating / cooling mode, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11 is determined. In the heating / cooling mode, the increase / decrease amount ΔIVO is determined so that the battery temperature TB approaches the target battery temperature TBO by the feedback control method based on the deviation between the battery temperature TB and the target battery temperature TBO. The target battery temperature TBO is determined with reference to the control map based on the calorific value of the battery and the outside air temperature Tam.

When the rotation speed of the compressor 11 is increased or decreased by the increase / decrease amount ΔIVO and the rotation speed of the compressor 11 is less than the lower limit rotation speed Ncmin (1000 rpm in this embodiment), the compressor 11 is stopped.

In the next step, the target supercooling degree SCO1 of the refrigerant flowing out from the outdoor heat exchanger 16 is determined. The target supercooling degree SCO1 of the heating / cooling mode is determined with reference to the control map based on the outside air temperature Tam. In the control map of the present embodiment, the target supercooling degree SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.

In the next step, the amount of increase / decrease ΔEVB in the throttle opening of the cooling expansion valve 14c is determined. The increase / decrease amount ΔEVB is the supercooling degree of the outlet side refrigerant of the outdoor heat exchanger 16 by the feedback control method based on the deviation between the target supercooling degree SCO1 and the supercooling degree SC1 of the outlet side refrigerant of the outdoor heat exchanger 16. SC1 is determined to approach the target supercooling degree SCO1. The supercooling degree SC1 is calculated in the same manner as in the cooling mode.

In the next step, the opening SW of the air mix door 34 is calculated in the same manner as in the cooling mode.

In the next step, in order to switch the refrigerating cycle device 10 to the refrigerant circuit in the heating / cooling mode, the heating expansion valve 14a is fully opened, the cooling expansion valve 14b is fully closed, and the first cooling expansion valve 14c and The second cooling expansion valve 14d is set to the throttled state, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or a control voltage is output to each controlled device so that the control state determined in the above step can be obtained, and the process returns to step S10.

Therefore, in the refrigerating cycle device 10 in the heating / cooling mode, the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the first cooling expansion valve 14c and the second. A steam compression type refrigeration cycle in which the refrigerant circulates in the order of the cooling expansion valve 14d, the first battery cooler 19a and the second battery cooler 19b, the evaporation pressure adjusting valve 20, the accumulator 21, and the compressor 11 is configured.

That is, in the refrigerating cycle device 10 in the heating / cooling mode, the water refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a radiator (in other words, a radiator) that dissipates the refrigerant discharged from the compressor 11. A steam compression type refrigeration cycle in which the 1st cooling expansion valve 14c and the 2nd cooling expansion valve 14d function as a pressure reducing unit for reducing the pressure of the refrigerant, and the 1st battery cooler 19a and the 2nd battery cooler 19b function as an evaporator. Is configured.

According to this, the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the heating / cooling mode, the interior of the vehicle can be heated by blowing out the air heated by the heater core 42 into the interior of the vehicle. Further, the battery can be cooled by the first battery cooler 19a and the second battery cooler 19b.

(9) Heating series cooling mode In the first step of the control flow of the heating series cooling mode, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11 is determined as in the heating / cooling mode.

When the rotation speed of the compressor 11 is increased or decreased by the increase / decrease amount ΔIVO and the rotation speed of the compressor 11 is less than the lower limit rotation speed Ncmin (1000 rpm in this embodiment), the compressor 11 is stopped.

In the next step, the target high temperature side heat medium temperature TWHO of the high temperature side heat medium is determined as in the series dehumidification heating mode.

In the next step, the throttle opening of the heating expansion valve 14a, the throttle opening of the first cooling expansion valve 14c, and the throttle opening of the second cooling expansion valve 14d are determined. Specifically, in the heating series cooling mode, as the target outlet temperature TAO rises, the throttle opening of the heating expansion valve 14a is reduced, and the first cooling expansion valve 14c and the second cooling expansion valve 14d are reduced. Increase the aperture opening of.

In the next step, the opening SW of the air mix door 34 is calculated in the same manner as in the cooling mode.

In the next step, in order to switch the refrigerating cycle device 10 to the refrigerant circuit in the heating series cooling mode, the heating expansion valve 14a is set to the throttled state, the cooling expansion valve 14b is set to the fully closed state, and the first cooling expansion valve 14c is set. The second cooling expansion valve 14d is set to the throttled state, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or a control voltage is output to each controlled device so that the control state determined in the above step can be obtained, and the process returns to step S10.

Therefore, in the refrigerating cycle device 10 in the heating series cooling mode, the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the first cooling expansion valve 14c and the first. 2. A steam compression type refrigeration cycle in which the refrigerant circulates in the order of the cooling expansion valve 14d, the first battery cooler 19a and the second battery cooler 19b, the accumulator 21, and the compressor 11 is configured.

That is, in the refrigerating cycle device 10 in the heating series cooling mode, the water refrigerant heat exchanger 12 functions as a radiator (in other words, a radiator) that dissipates the refrigerant discharged from the compressor 11, and the heating expansion valve 14a, A steam compression type refrigeration cycle is configured in which the first cooling expansion valve 14c and the second cooling expansion valve 14d function as a pressure reducing unit, and the first battery cooler 19a and the second battery cooler 19b function as an evaporator. To.

Further, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, a cycle is configured in which the outdoor heat exchanger 16 functions as a radiator (in other words, a radiator). .. When the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, a cycle in which the outdoor heat exchanger 16 functions as an evaporator is configured.

According to this, the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the heating series cooling mode, the interior of the vehicle can be heated by blowing out the air heated by the heater core 42 into the interior of the vehicle. Further, the battery can be cooled by the first battery cooler 19a and the second battery cooler 19b.

(10) Heating parallel cooling mode In the first step of the control flow of the heating parallel cooling mode, the target high temperature side heat medium temperature of the high temperature side heat medium is the same as in the series dehumidifying heating mode so that the air can be heated by the heater core 42. TWHO is decided.

In the next step, the amount of increase / decrease ΔIVO in the rotation speed of the compressor 11 is determined. In the heating parallel cooling mode, the increase / decrease amount ΔIVO is the high temperature side heat medium temperature by the feedback control method based on the deviation between the target high temperature side heat medium temperature TWHO and the high temperature side heat medium temperature TWH, as in the series dehumidification heating mode. The TWH is determined to approach the target high temperature side heat medium temperature TWHO.

When the rotation speed of the compressor 11 is increased or decreased by the increase / decrease amount ΔIVO and the rotation speed of the compressor 11 is less than the lower limit rotation speed Ncmin (1000 rpm in this embodiment), the compressor 11 is stopped.

In the next step, the target superheat degree SHCO of the outlet side refrigerant of the refrigerant passage of the first battery cooler 19a and the target superheat degree SHCO of the outlet side refrigerant of the refrigerant passage of the second battery cooler 19b are determined. As the target superheat degree SHCO, a predetermined constant (5 ° C. in this embodiment) can be adopted.

In the next step, the throttle opening of the heating expansion valve 14a, the throttle opening of the first cooling expansion valve 14c, and the throttle opening of the second cooling expansion valve 14d are determined. In the heating parallel cooling mode, the deviation between the target superheat degree SHCO and the superheat degree SHC1 of the refrigerant on the outlet side of the refrigerant passage of the first battery cooler 19a, and the target superheat degree SHCO and the outlet side of the refrigerant passage of the first battery cooler 19b. Based on the deviation from the superheat degree SHC2 of the refrigerant, the superheat degree SHC1 and SHC2 are determined to approach the target superheat degree SHCO by the feedback control method.

In the next step, the opening SW of the air mix door 34 is calculated in the same manner as in the cooling mode. In the next step, in order to switch the refrigerating cycle device 10 to the refrigerant circuit in the heating parallel cooling mode, the heating expansion valve 14a is set to the throttled state, the cooling expansion valve 14b is set to the fully closed state, and the first cooling expansion valve 14c is set. The second cooling expansion valve 14d is set to the throttled state, the dehumidifying on-off valve 15a is opened, and the heating on-off valve 15b is opened.

Further, the control signal or the control voltage is output to each controlled device so that the control state determined in the above step can be obtained, and the process returns to step S10.

Therefore, in the refrigerating cycle device 10 in the heating parallel cooling mode, the refrigerant is in the order of the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the compressor 11. Along with the circulation, the compressor 11, the water refrigerant heat exchanger 12, the bypass passage 22a, the first cooling expansion valve 14c and the second cooling expansion valve 14d, the first battery cooler 19a and the second battery cooler 19b, A steam compression type refrigeration cycle in which the refrigerant circulates in the order of the accumulator 21 and the compressor 11 is configured.

That is, in the refrigeration cycle device 10 in the heating parallel cooling mode, the water refrigerant heat exchanger 12 functions as a radiator (in other words, a radiator) for dissipating the refrigerant discharged from the compressor 11, and the heating expansion valve 14a is used. It functions as a decompression unit, the outdoor heat exchanger 16 functions as an evaporator, and the first cooling expansion valve 14c and the second cooling connected in parallel to the heating expansion valve 14a and the outdoor heat exchanger 16. A refrigeration cycle is configured in which the expansion valve 14d functions as a pressure reducing unit, and the first battery cooler 19a and the second battery cooler 19b function as an evaporator.

According to this, the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the heating parallel cooling mode, the interior of the vehicle can be heated by blowing out the air heated by the heater core 42 into the interior of the vehicle. Further, the battery can be cooled by the first battery cooler 19a and the second battery cooler 19b.

(11) Cooling mode In the first step of the control flow of the cooling mode, the amount of increase / decrease in the rotation speed of the compressor 11 ΔIVO, the target supercooling degree SCO1, the target supercooling degree SCO2, and the first cooling are the same as in the heating cooling mode. The amount of increase / decrease in the throttle opening of the expansion valve 14c ΔEVB1, the amount of increase / decrease in the throttle opening of the second cooling expansion valve 14d ΔEVB2, and the opening SW of the air mix door 34 are determined.

Here, in the cooling mode, the target outlet temperature TAO is lower than the heating reference temperature γ, so that the opening SW of the air mix door 34 approaches 0%. Therefore, in the cooling mode, the opening degree of the air mix door 34 is determined so that substantially the entire flow rate of the air after passing through the indoor evaporator 18 passes through the cold air bypass passage 35.

In the next step, in order to switch the refrigeration cycle device 10 to the cooling mode refrigerant circuit, the heating expansion valve 14a is fully opened, the cooling expansion valve 14b is fully closed, and the first cooling expansion valve 14c and the first cooling expansion valve 14c are fully closed. 2 The cooling expansion valve 14d is set to the throttled state, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, the control signal or the control voltage is output to each controlled device so that the control state determined in the above step can be obtained, and the process returns to step S10.

Therefore, in the refrigerating cycle device 10 in the cooling mode, the compressor 11, the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the first cooling expansion valve 14c, and the second cooling A steam compression type refrigeration cycle in which the refrigerant circulates in the order of the expansion valve 14d, the first battery cooler 19a and the second battery cooler 19b, the accumulator 21, and the compressor 11 is configured.

That is, in the refrigerating cycle device 10 in the cooling mode, the outdoor heat exchanger 16 functions as a radiator (in other words, a radiator) that dissipates the refrigerant discharged from the compressor 11, and the first cooling expansion valve 14c and the first. 2 A steam compression type refrigeration cycle is configured in which the cooling expansion valve 14d functions as a pressure reducing unit, and the first battery cooler 19a and the second battery cooler 19b function as an evaporator.

According to this, the battery can be cooled by the first battery cooler 19a and the second battery cooler 19b.

As described above, in the refrigerating cycle apparatus 10 of the present embodiment, various operation modes can be switched. As a result, the vehicle air conditioner 1 can realize comfortable air conditioning in the vehicle interior while appropriately adjusting the temperature of the battery.

In the present embodiment, fluctuation suppression control is performed in order to suppress fluctuations in the temperature of the blown air from the indoor evaporator 18 when the cooling mode is switched to the cooling cooling mode. Specifically, the above-mentioned steps S1140, S1230, S1280, and S1320 are controlled. Hereinafter, the action and effect of the fluctuation suppression control of the present embodiment will be described.

FIG. 8 is a time chart showing an operation example of a comparative example, and FIG. 9 is a time chart showing an operation example of the present embodiment. 8 to 9 show the rotation speed Nc of the compressor 11 before and after switching from the cooling mode to the cooling cooling mode, the opening EVC of the cooling expansion valve 14b, and the first and second cooling expansion valves 14c to 14d. The time transition of the opening EVB and the evaporator temperature Tefin is shown.

In the comparative example shown in FIG. 8, the fluctuation suppression control of the present embodiment is not performed. Therefore, in the comparative example shown in FIG. 8, when the cooling mode is switched to the cooling cooling mode, the lower limit rotation speed Ncmin of the compressor 11 is not gradually increased but is increased at once from 1000 rpm to 3000 rpm. The rotation speed Nc also increases at once from 1000 rpm to 3000 rpm. As a result, the flow rate of the refrigerant flowing into the indoor evaporator 18 increases, the evaporator temperature Tefin decreases, and the target evaporator temperature TEO is reached. When the evaporator temperature Tefin reaches the target evaporator temperature TEO, the cooling expansion valve 14b is fully closed. When the cooling expansion valve 14b is fully closed, the refrigerant in the indoor evaporator 18 is pulled by the suction pressure of the compressor 11, and the evaporator temperature Tefin falls below the target evaporator temperature TEO (so-called undershoot). .. Then, the refrigerant in the indoor evaporator 18 evaporates, the evaporator temperature Tefin rises sharply, and the target evaporator temperature TEO is reached. When the evaporator temperature Tefin rises and reaches the target evaporator temperature TEO, the cooling expansion valve 14b is opened again and the refrigerant flows out to the indoor evaporator 18, but the rise in the evaporator temperature Tefin cannot be suppressed and the evaporator temperature. Tefin soars and exceeds the target evaporator temperature TEO (so-called overshoot). Due to such undershoot and overshoot, the fluctuation of the evaporator temperature Tefin becomes large, and the fluctuation of the blown air from the indoor evaporator 18 becomes large.

On the other hand, in the present embodiment shown in FIG. 9, since the fluctuation suppression control is performed, the lower limit rotation speed Ncmin of the compressor 11 is gradually increased from 1000 rpm to 3000 rpm when the cooling mode is switched to the cooling cooling mode, and the first The throttle opening of the 1 cooling expansion valve 14c and the 2nd cooling expansion valve 14d is made larger than that in the normal control. As a result, the increase in the flow rate of the refrigerant flowing into the indoor evaporator 18 is suppressed, and the decrease in the evaporator temperature Tefin becomes gradual. Further, even if the evaporator temperature Tefin reaches the target evaporator temperature TEO, the cooling expansion valve 14b is not fully closed, so that undershoot and overshoot in the indoor evaporator 18 can be suppressed. Then, when the elapsed time ct from the start of cooling of the battery exceeds the predetermined time tcO, the throttle opening of the first cooling expansion valve 14c and the second cooling expansion valve 14d is returned to the throttle opening at the time of normal control. Is done. As described above, in the present embodiment, the fluctuation of the evaporator temperature Tefin can be suppressed by performing the fluctuation suppression control, and thus the fluctuation of the blown air from the indoor evaporator 18 can be suppressed.

In the present embodiment, the control device 60 performs fluctuation suppression control when switching from the cooling mode to the cooling cooling mode. In the fluctuation suppression control, the rotation speed of the compressor 11 is controlled so as to suppress the flow rate fluctuation of the refrigerant in the indoor evaporator 18. Further, in the fluctuation suppression control, the first cooling expansion valve 14c and the second cooling expansion valve 14d are controlled so as to suppress the fluctuation of the flow rate of the refrigerant in the indoor evaporator 18.

According to this, since the fluctuation of the flow rate of the refrigerant in the indoor evaporator 18 is suppressed when the cooling mode is switched to the cooling cooling mode, the fluctuation of the temperature of the blown air from the indoor evaporator 18 can be suppressed.

In the fluctuation suppression control of the present embodiment, as described in step S1140, the ascending speed of the lower limit rotation speed Ncmin of the compressor 11 is set to a predetermined speed or less. Thereby, when the cooling mode is switched to the cooling cooling mode, the fluctuation of the flow rate of the refrigerant in the indoor evaporator 18 can be surely suppressed. In particular, it is possible to prevent the cooling capacity of the indoor evaporator 18 from becoming excessive and closing the cooling expansion valve 14b due to the rapid increase in the rotation speed of the compressor 11. As a result, the fluctuation of the flow rate of the refrigerant in the indoor evaporator 18 can be reliably suppressed, so that the temperature fluctuation of the blown air from the indoor evaporator 18 can be suppressed.

In the present embodiment, as described in step S1230, when the elapsed time ct after switching from the cooling mode to the cooling cooling mode in the fluctuation suppression control is within the predetermined time ctO, it is necessary to cool the air with the indoor evaporator 18. The cooling expansion valve 14b is controlled so that the refrigerant continues to flow to the indoor evaporator 18 even if the air conditioner disappears.

According to this, when the cooling expansion valve 14b is closed, the refrigerant of the indoor evaporator 18 is pulled by the suction pressure of the compressor 11 and the temperature of the indoor evaporator 18 can be suppressed from rising sharply. Therefore, the indoor evaporator 18 can be prevented from rising rapidly. It is possible to suppress the temperature fluctuation of the blown air from.

In the present embodiment, as described in step S1280, when the elapsed time ct after switching from the cooling mode to the cooling cooling mode in the fluctuation suppression control is within the predetermined time tcO, the first battery cooler 19a and the second battery The first cooling expansion valve 14c and the second cooling expansion valve 14d are controlled so that the refrigerant continues to flow to the first battery cooler 19a and the second battery cooler 19b even if it is no longer necessary to cool the battery with the cooler 19b. do.

According to this, since the first cooling expansion valve 14c and the second cooling expansion valve 14d are closed, it is possible to suppress a rapid increase in the flow rate of the refrigerant in the indoor evaporator 18, so that the air is blown out from the indoor evaporator 18. The temperature fluctuation of air can be suppressed. Further, when the first cooling expansion valve 14c and the second cooling expansion valve 14d are closed, the refrigerants of the first battery cooler 19a and the second battery cooler 19b are pulled by the suction pressure of the compressor 11 and the first. It is possible to prevent the temperature of the battery cooler 19a and the second battery cooler 19b from rising sharply. Therefore, the temperature fluctuation of the battery can be suppressed.

In the present embodiment, as described in step S1320, when the rotation speed of the compressor 11 when switching from the cooling mode to the cooling cooling mode in the fluctuation suppression control is lower than the predetermined rotation speed (specifically, 3000 rpm). The opening degree of the first cooling expansion valve 14c and the second cooling expansion valve 14d is increased as compared with the normal control.

As a result, when the rotation speed of the compressor 11 increases in the fluctuation suppression control, the refrigerant easily flows to the first battery cooler 19a and the second battery cooler 19b, so that the increase in the flow rate of the refrigerant in the indoor evaporator 18 can be suppressed. .. As a result, it is possible to suppress the cooling capacity of the indoor evaporator 18 from becoming excessive and closing the cooling expansion valve 14b, so that the temperature fluctuation of the blown air from the indoor evaporator 18 can be suppressed.

(Second Embodiment)
In the first embodiment, the cooling expansion valve 14b, the first cooling expansion valve 14c, and the second cooling expansion valve 14d have a fully closed function of closing the refrigerant passage by fully closing the valve opening. However, in the present embodiment, as shown in FIG. 10, the refrigerating cycle device 10 has a cooling on-off valve 15c and a cooling on-off valve 15d, and has a cooling on-off valve 14b and a first cooling on-off valve. The fully closed function of 14c and the second cooling expansion valve 14d is abolished.

The basic configuration of the cooling on-off valve 15c and the cooling on-off valve 15d is the same as that of the high-pressure side on-off valve 15a. The cooling on-off valve 15c and the cooling on-off valve 15d can switch the refrigerant circuit of each operation mode by opening and closing the refrigerant passage. The cooling on-off valve 15c and the cooling on-off valve 15d are refrigerant circuit switching units that switch the refrigerant circuit of the cycle. The cooling on-off valve 15c and the cooling on-off valve 15d are controlled by a control voltage output from the cycle control device 60.

The cooling on-off valve 15c has a cooling on-off valve 15c arranged in a refrigerant passage connecting one outlet side of the fifth three-way joint 13e and the inlet side of the cooling expansion valve 14b, and opens and closes the refrigerant passage. do.

The cooling on-off valve 15d is arranged in a refrigerant passage connecting the other outlet side of the fifth three-way joint 13e and the inlet side of the seventh three-way joint 13g, and opens and closes the refrigerant passage.

In the present embodiment, the second check valve 17b is arranged in the refrigerant passage connecting the outlet side of the eighth three-way joint 13h and the other inlet side of the sixth three-way joint 13f. The second check valve 17b allows the refrigerant to flow from the 6th three-way joint 13f side to the 8th three-way joint 13h side, and prohibits the refrigerant from flowing from the 8th three-way joint 13h side to the 6th three-way joint 13f side. do.

Also in this embodiment, the same action and effect as those of the first embodiment can be obtained.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention. In addition, the means disclosed in each of the above embodiments may be appropriately combined to the extent feasible.

(A) In the above-described embodiment, the refrigeration cycle device 10 capable of switching to a plurality of operation modes has been described, but the switching of the operation mode of the refrigeration cycle device 10 is not limited to this. At least, the first mode in which the air is cooled by the indoor evaporator 18 and the batteries are not cooled by the first battery cooler 19a and the second battery cooler 19b, and the first mode in which the air is cooled by the indoor evaporator 18 and the first battery cooler 19a and It suffices if the second battery cooler 19b can switch between the second mode for cooling the battery and the second mode. Then, the fluctuation suppression control may be performed when switching from the first mode to the second mode.

Further, the detailed control of each operation mode is not limited to that disclosed in the above-described embodiment. For example, the blower mode described in step S260 may be a stop mode for stopping not only the compressor 11 but also the blower 32.

(B) In step S1260 of the above-described embodiment, the rotation speed of the compressor 11 may be reduced instead of fully closing the cooling expansion valve 14b. That is, when the control device 60 does not need to cool the air in the indoor evaporator 18 in the fluctuation suppression control and prevents the refrigerant from flowing to the indoor evaporator 18, the rotation speed of the compressor 11 is temporarily lowered. You may do so.

According to this, even if the cooling expansion valve 14b is closed, the refrigerant of the indoor evaporator 18 can be suppressed from being pulled by the suction pressure of the compressor 11, so that the temperature of the indoor evaporator 18 can be suppressed from rising sharply. As a result, the temperature fluctuation of the blown air from the indoor evaporator 18 can be suppressed.

(C) In step S1290 of the above-described embodiment, the rotation speed of the compressor 11 may be reduced instead of fully closing the first cooling expansion valve 14c and the second cooling expansion valve 14d. That is, the control device 60 does not need to cool the battery with the refrigerant of the first battery cooler 19a and the second battery cooler 19b in the fluctuation suppression control, and the refrigerant is added to the first battery cooler 19a and the second battery cooler 19b. When the flow is prevented from flowing, the rotation speed of the compressor 11 may be temporarily lowered.

According to this, even if the first cooling expansion valve 14c and the second cooling expansion valve 14d are fully closed, it is possible to suppress a rapid increase in the flow rate of the refrigerant in the indoor evaporator 18, so that the indoor evaporator 18 can be suppressed. It is possible to suppress the temperature fluctuation of the blown air from. Further, even if the first cooling expansion valve 14c and the second cooling expansion valve 14d are fully closed, the refrigerants of the first battery cooler 19a and the second battery cooler 19b are drawn by the suction pressure of the compressor 11. Since this can be suppressed, it is possible to prevent the temperatures of the first battery cooler 19a and the second battery cooler 19b from rising sharply.

(D) In step S1140 of each of the above-described embodiments, the lower limit rotation speed Ncmin of the compressor 11 is set higher in the cooling mode than in the cooling mode, but the cooling mode is switched to the cooling cooling mode in the fluctuation suppression control of the cooling cooling mode. When the elapsed time ct from the time is within the predetermined time tcO, it may be prohibited to set the lower limit rotation speed Ncmin of the compressor 11 to be higher than that in the cooling mode.

As a result, it is possible to prevent the indoor evaporator 18 from becoming excessive in cooling capacity due to an increase in the rotation speed of the compressor 11 immediately after switching from the cooling mode to the cooling cooling mode. Therefore, since the cooling expansion valve 14b is closed and the fluctuation of the flow rate of the refrigerant in the indoor evaporator 18 can be suppressed, the temperature fluctuation of the blown air from the indoor evaporator 18 can be suppressed.

(E) The components of the refrigeration cycle apparatus are not limited to those disclosed in the above-described embodiment. A plurality of cycle components may be integrated so that the above-mentioned effects can be exhibited. For example, a four-way joint structure in which two three-way joints are integrated, such as a second three-way joint 13b and a fifth three-way joint 13e, a fourth three-way joint 13d and a sixth three-way joint 13f, may be adopted. Further, as the cooling expansion valve 14b, the first cooling expansion valve 14c, and the second cooling expansion valve 14d, those in which the electric expansion valve having no fully closed function and the on-off valve are directly connected are adopted. May be good.

Further, in the above-described embodiment, the example in which R1234yf is adopted as the refrigerant has been described, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may be adopted. Alternatively, a mixed refrigerant or the like in which a plurality of types of these refrigerants are mixed may be adopted. Further, carbon dioxide may be adopted as the refrigerant to form a supercritical refrigeration cycle in which the pressure of the refrigerant on the high pressure side is equal to or higher than the critical pressure of the refrigerant.

(F) The configuration of the heating unit is not limited to that disclosed in the above-described embodiment. For example, a three-way valve and a high-temperature side radiator may be added to the high-temperature side heat medium circuit 40 described in the first embodiment to dissipate excess heat to the outside air. Further, in a vehicle equipped with an internal combustion engine (engine) such as a hybrid vehicle, engine cooling water may be circulated in the high temperature side heat medium circuit 40.

(G) With respect to the first embodiment, the high temperature side heat medium circuit 40 may be abolished and an indoor condenser may be adopted. The indoor condenser is a heating unit that heats the air while condensing the refrigerant by exchanging heat between the high-temperature and high-pressure refrigerant discharged from the compressor 11 and the air cooled by the indoor evaporator 18. The indoor condenser may be arranged in the air conditioning case 31 of the indoor air conditioning unit 30 instead of the heater core 42 described in the first embodiment.

(H) In the above-described embodiment, the example in which the cooling target to be cooled by the cooling unit is a battery has been described, but the cooling target is not limited to this. An inverter that converts direct current and alternating current, a charger that charges the battery, and a motor generator that outputs driving force for driving by supplying electric power and generates regenerative electric power during deceleration. As described above, it may be an electric device that generates heat during operation.

(I) In each of the above-described embodiments, the refrigeration cycle device 10 according to the present invention is applied to the vehicle air conditioner 1, but the application of the refrigeration cycle device 10 is not limited to this. For example, it may be applied to an air conditioner having a battery cooling function that air-conditions a room while appropriately adjusting the temperature of a stationary battery.

(J) In each of the above-described embodiments, the method for cooling the battery may be a direct cooling type, an air cooling type, or a water cooling type. The direct cooling type is a method in which the first battery cooler 19a and the second battery cooler 19b directly absorb heat from the battery by heat conduction without using a heat medium such as air or cooling water. The air-cooled type is a method in which the first battery cooler 19a and the second battery cooler 19b cool the air, and the battery is cooled by the air cooled by the first battery cooler 19a and the second battery cooler 19b. The water-cooled type is a method in which the first battery cooler 19a and the second battery cooler 19b cool the cooling water, and the cooling water cooled by the first battery cooler 19a and the second battery cooler 19b cools the battery. be.

11 Compressor 14b Cooling expansion valve 14c First cooling expansion valve (cooling expansion valve)
14d 1st cooling expansion valve (cooling expansion valve)
16 Outdoor heat exchanger (heat dissipation part)
18 Indoor evaporator (indoor evaporator)
19a 1st battery cooler (cooling unit)
19b 2nd battery cooler (cooling unit)
60 Control device (control unit)

Claims (8)

A compressor (11) that compresses and discharges the refrigerant,
A heat radiating unit (16) that dissipates heat from the refrigerant discharged from the compressor, and
A cooling expansion valve (14b) for reducing the pressure of the refrigerant radiated by the heat radiating portion, and a cooling expansion valve (14b).
An indoor evaporator (18) that evaporates the refrigerant and cools the air by exchanging heat between the refrigerant decompressed by the cooling expansion valve and air.
Cooling expansion valves (14c, 14d) arranged in parallel with the cooling expansion valve in the flow of the refrigerant and reducing the pressure of the refrigerant radiated by the heat radiating portion.
Cooling units (19a, 19b) that cool the cooling object by evaporating the refrigerant decompressed by the cooling expansion valve with the heat of the cooling object.
When switching from the first mode in which the refrigerant flows in the indoor evaporator and the refrigerant does not flow in the cooling unit to the second mode in which the refrigerant flows in the indoor evaporator and the cooling unit, the refrigerant in the indoor evaporator A refrigerating cycle device including a control unit (60) that controls fluctuation suppression control that controls at least one of the refrigerant discharge capacity of the compressor and the opening degree of the cooling expansion valve so as to suppress fluctuations in the flow rate of the refrigerator. The control unit
The refrigerant discharge capacity of the compressor is controlled so that the temperature (TE) of the indoor evaporator approaches the target temperature (TEO).
In the second mode, the lower limit capacity (Ncmin) of the refrigerant discharge capacity of the compressor is made higher than that in the first mode.
The refrigeration cycle apparatus according to claim 1, wherein in the fluctuation suppression control, the ascending speed of the lower limit capacity is set to a predetermined speed or less. The control unit
When it is no longer necessary to cool the air with the indoor evaporator in the second mode, the refrigerant is prevented from flowing to the indoor evaporator.
When the elapsed time (tc) after switching from the first mode to the second mode in the fluctuation suppression control is within a predetermined time (tcO), it is not necessary to cool the air with the indoor evaporator. The refrigerating cycle apparatus according to claim 1 or 2, wherein the refrigerant continues to flow in the indoor evaporator. When the control unit does not need to cool the air in the indoor evaporator in the fluctuation suppression control and prevents the refrigerant from flowing to the indoor evaporator, the control unit temporarily increases the refrigerant discharge capacity of the compressor. The refrigeration cycle apparatus according to claim 3. The control unit
When it is no longer necessary to cool the object to be cooled by the cooling unit in the second mode, the refrigerant is prevented from flowing to the cooling unit.
When the elapsed time (tc) after switching from the first mode to the second mode in the fluctuation suppression control is within a predetermined time (tcO), it is no longer necessary to cool the object to be cooled by the cooling unit. The refrigeration cycle apparatus according to claim 1 or 2, wherein the refrigerant continues to flow in the cooling unit. When the control unit does not need to cool the object to be cooled by the cooling unit in the fluctuation suppression control and prevents the refrigerant from flowing to the cooling unit, the control unit temporarily increases the refrigerant discharge capacity of the compressor. The refrigeration cycle apparatus according to claim 5. The control unit
Normal control is performed to control the cooling expansion valve so that the superheat degree (SHC1, SHC2) of the refrigerant flowing out of the cooling unit approaches the target superheat degree (SHCO).
When the refrigerant discharge capacity of the compressor when switching from the first mode to the second mode in the fluctuation suppression control is less than the predetermined capacity, the opening degree of the cooling expansion valve is compared with the normal control. The refrigeration cycle apparatus according to any one of claims 1 to 6. The control unit
The refrigerant discharge capacity of the compressor is controlled so that the temperature (TE) of the indoor evaporator approaches the target temperature (TEO).
In the second mode, the lower limit of the refrigerant discharge capacity of the compressor is made higher than that in the first mode.
In the fluctuation suppression control, when the elapsed time (tc) after switching from the first mode to the second mode is within a predetermined time (tcO), it is prohibited to make the lower limit capacity higher than that of the first mode. The refrigeration cycle apparatus according to claim 1.

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