JP2000283611A - Heat pump type air conditioning apparatus - Google Patents

Heat pump type air conditioning apparatus

Info

Publication number
JP2000283611A
JP2000283611A JP11089784A JP8978499A JP2000283611A JP 2000283611 A JP2000283611 A JP 2000283611A JP 11089784 A JP11089784 A JP 11089784A JP 8978499 A JP8978499 A JP 8978499A JP 2000283611 A JP2000283611 A JP 2000283611A
Authority
JP
Japan
Prior art keywords
heat exchanger
temperature
outdoor heat
air
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP11089784A
Other languages
Japanese (ja)
Other versions
JP4134433B2 (en
Inventor
Keita Honda
桂太 本多
Original Assignee
Denso Corp
株式会社デンソー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Corp, 株式会社デンソー filed Critical Denso Corp
Priority to JP08978499A priority Critical patent/JP4134433B2/en
Publication of JP2000283611A publication Critical patent/JP2000283611A/en
Application granted granted Critical
Publication of JP4134433B2 publication Critical patent/JP4134433B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60HARRANGEMENTS OR ADAPTATIONS OF HEATING, COOLING, VENTILATING, OR OTHER AIR-TREATING DEVICES SPECIALLY FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00Heating, cooling or ventilating [HVAC] devices
    • B60H1/32Cooling devices
    • B60H1/3204Cooling devices using compression
    • B60H1/3205Control means therefor
    • B60H1/321Control means therefor for preventing the freezing of a heat exchanger

Abstract

(57) [Problem] To prevent frost formation on the outdoor heat exchanger (18). SOLUTION: The refrigerant discharged from a compressor 13 and the conditioned air exchange heat in a condenser 9, and the refrigerant condensed in the condenser 9 is decompressed by a decompressor 19, and the decompressed refrigerant and outdoor air In the air conditioner that exchanges heat with the outdoor heat exchanger 18, the temperature of the outdoor heat exchanger 18 is controlled such that the temperature difference between the outside air temperature and the temperature of the outdoor heat exchanger 18 falls within a predetermined range. As a result, it is possible to prevent the temperature of the outdoor heat exchanger 18 from dropping more than necessary, so that the possibility that the temperature of the outdoor heat exchanger 18 decreases to the frost temperature range is reduced. Will be possible.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump type air conditioner, and more particularly to prevention of frost formation on an outdoor heat exchanger.

[0002]

2. Description of the Related Art In a conventional heat pump air conditioner, a gas discharge refrigerant (hot gas) discharged from a compressor is directly introduced into an indoor heat exchanger, and the indoor heat exchanger radiates heat from the gas refrigerant to conditioned air to provide a heating function. Can be demonstrated.
Further, the refrigerant condensed in the indoor heat exchanger is decompressed and then introduced into the outdoor heat exchanger. After the outdoor heat exchanger absorbs heat from the conditioned air into the refrigerant, the refrigerant is returned to the compressor.

[0003] In this type of heat pump type air conditioner, frost formation on the outdoor heat exchanger becomes a problem, and as a countermeasure, for example, there is one described in Japanese Patent Application Laid-Open No. Hei 10-71850. In this conventional apparatus, a bypass circuit for hot gas is provided that bypasses the condenser from the compressor discharge side and directly communicates with the outdoor heat exchanger inlet side, and a solenoid valve is provided in this bypass circuit, and further, the outdoor heat exchanger A temperature sensor for detecting a temperature is provided.

When the temperature of the outdoor heat exchanger becomes lower than a predetermined temperature, it is determined that a frost is formed, and a solenoid valve is controlled to be turned on and off at a predetermined duty ratio so that the hot gas discharged from the compressor is discharged to the outdoor heat exchanger. The frost adhering to the surface of the outdoor heat exchanger is melted by being introduced into the exchanger.

[0005]

However, in the above-mentioned conventional apparatus, hot gas is only introduced into the outdoor heat exchanger after frost formation for defrosting, and frost formation cannot be prevented beforehand. There's a problem. In addition, since the solenoid valve is on / off controlled, hot gas flows into the outdoor heat exchanger intermittently, and as a result, the flow rate of the refrigerant flowing through the indoor heat exchanger during defrosting fluctuates greatly, and therefore, There is also a problem that the air blowing temperature hunts.

[0006] The present invention has been made in view of the above points, and has as its object to prevent frost on an outdoor heat exchanger. Another object of the present invention is to stabilize the indoor air blowing temperature during the prevention of frost formation.

[0007]

In order to achieve the above object, according to the first to fourth aspects of the present invention, an outdoor heat exchanger (evaporating the refrigerant by exchanging heat between the depressurized refrigerant and the outdoor air during heating is provided. 18), so that the temperature difference between the outside air temperature and the temperature of the outdoor heat exchanger (18) falls within a predetermined range.
The temperature of the outdoor heat exchanger (18) is controlled.

According to this, since the temperature of the outdoor heat exchanger (18) can be prevented from lowering more than necessary, the outdoor heat exchanger (1)
The possibility that the temperature of 8) is lowered to the frost temperature range is reduced, so that frost formation can be prevented beforehand. As in the second aspect of the present invention, the bypass circuit (30) for guiding the refrigerant discharged from the compressor (13) to the outdoor heat exchanger (18) and the amount of the refrigerant flowing through the bypass circuit (30) are adjusted. And a control means (24) for controlling the operation of the bypass control valve (31) so as to control the temperature difference within a predetermined range.

In the invention according to claim 3, the control means (2
4) When the state in which the temperature of the outdoor heat exchanger (18) is lower than the outside air temperature by a predetermined value or more continues for a predetermined time, it is determined that the frost is formed, and the open state of the bypass control valve (31) is changed to the defrosting state It is characterized in that it is continued until it is determined to be in the completed state. According to this, defrosting can be reliably performed even when a frosted state is reached.

[0010] The invention according to claim 4 is characterized in that the bypass control valve (31) can continuously adjust the amount of refrigerant flowing through the bypass circuit (30). According to this, since the change in the refrigerant flow rate on the bypass circuit (30) side can be moderated, rapid fluctuations in the refrigerant flow rate on the indoor heat exchanger (9) side are prevented, and the indoor air blowing temperature can be stabilized. it can.

The reference numerals in parentheses of the above means indicate the correspondence with the specific means described in the embodiments described later.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows an embodiment in which the present invention is applied to an air conditioner for an electric vehicle.
Is installed in the cabin of the electric vehicle and its air conditioning duct 2
Constitutes an air-conditioned air passage for guiding conditioned air into the vehicle interior. At one end of the air-conditioning duct 2, there is provided an inside air suction port 3 for sucking inside air and an outside air suction port 4 for sucking outside air. .

A blower 6 for blowing air into the air-conditioning duct 2 is provided adjacent to the inlets 3 and 4, and the blower 6 is constituted by a centrifugal fan driven by a motor 7. In the air conditioning duct 2, a heating condenser 9 is provided on the air blowing side of the blower 6. The heating condenser 9 is an indoor heat exchanger that constitutes a part of a refrigeration cycle, and performs a heating cycle described later.
It functions as a heater that heats the air in the air conditioning duct 2 by the heat radiation effect of the refrigerant flowing inside.

In the air conditioning duct 2, a heating condenser 9 is provided.
A bypass passage 10 for bypassing the heating condenser 9 and allowing air to flow therethrough is provided at the side of the plate-shaped switching door 11 for switching between the ventilation passage of the heating condenser 9 and the bypass passage 10. It is provided as possible. The switching door 11 is operated at a solid line position where the ventilation passage of the heating condenser 9 is fully opened and the bypass passage 10 is fully closed at the time of heating.
It is operated to the position indicated by the broken line where the ventilation passage of the heating condenser 9 is fully closed and the bypass passage 10 is fully opened.

A cooling evaporator 8 is provided downstream of the heating condenser 9 in the air. The cooling evaporator 8 is an indoor heat exchanger that constitutes a part of a refrigeration cycle. Sometimes, due to the endothermic effect of the refrigerant flowing inside,
It functions as a cooler that cools and dehumidifies the air in the air conditioning duct 2. In the air-conditioning duct 2, downstream of the air from the cooling evaporator 8, a foot outlet 94 that blows out the conditioned air toward the feet of the passenger in the passenger compartment, and a face blower that discharges the conditioned air toward the upper body of the passenger in the passenger compartment. An outlet 95 and a defroster outlet 96 for blowing conditioned air to the inner surface of the vehicle window glass are provided. The plurality of outlets 94 to 96 are selectively opened and closed by outlet mode doors 97, 98, and 99.

Next, the refrigeration cycle 12 including the cooling evaporator 8 and the heating condenser 9 will be described. The refrigeration cycle 12 is configured as a heat pump refrigeration cycle for cooling and heating the vehicle interior. , A motor-driven refrigerant compressor 13. In the flow path between the discharge side of the compressor 13 and the condenser 9, a pressure sensor 14 for detecting a discharge pressure (cycle high pressure) is arranged.

The refrigeration cycle 12 includes a cooling solenoid valve 15, a heating solenoid valve 16, a dehumidification solenoid valve 17, an outdoor heat exchanger 18, a first decompressor 19, a second decompressor 20, a refrigerant gas. An accumulator 21 that separates the liquid, stores the liquid refrigerant, and discharges the gas refrigerant is provided. Further, a bypass circuit 30 branched from between the discharge side of the compressor 13 and the condenser 9 is connected to the inlet side of the outdoor heat exchanger 18. A bypass control valve 31 capable of continuously adjusting the opening is provided.

The bypass control valve 31 uses, for example, a valve of a type in which a conical valve body is moved in and out of a circular opening serving as a refrigerant passage to adjust the opening degree. Drive with. The outdoor heat exchanger 18 is installed outside the vehicle compartment of the electric vehicle, and exchanges heat with the outside air blown by the electric outdoor fan 18a. An outdoor unit temperature sensor 32 is disposed in the outdoor heat exchanger 18,
The outdoor unit temperature sensor 32 detects the temperature of the pipe on the outlet side (the heating electromagnetic valve 16 side) of the outdoor heat exchanger 18 in the refrigerant flow during heating. An outside air temperature sensor 33 that detects the temperature of the air (outside air) flowing into the outdoor heat exchanger 18 is arranged on the air inlet side of the outdoor heat exchanger 18.

The refrigerant compressor 13 is an electric compressor. An electric motor (AC motor) (not shown) is built in a sealed case integrally, and driven by this motor to suck, compress, and remove the refrigerant. Discharge is performed. This refrigerant compressor 13
An AC voltage is applied to the AC motor by an inverter 22, and the frequency of the AC voltage is adjusted by the inverter 22 to continuously change the motor rotation speed. Accordingly, the inverter 22 serves as a means for adjusting the rotation speed of the compressor 13, and a DC voltage is applied to the inverter 22 from the vehicle-mounted battery 23.

The inverter 22 is energized by an air-conditioning control device (control means) 24. The air-conditioning control device 24 is an electronic control device including a microcomputer and its peripheral circuits, and controls the operations of the solenoid valves 15 to 17 and the bypass control valve 31 in addition to the inverter 22. Further, the operation of devices such as the inside / outside air switching door 5 of the air conditioning unit 1, the 6 motor 7 of the blower, the aeromic door 11, and the outdoor fan 18a is controlled by the control device 24.

The control unit 24 includes, in addition to the pressure sensor 14, the outdoor unit temperature sensor 32, and the outside air temperature sensor 33, an inside air sensor for detecting the temperature inside the vehicle, and the evaporator 8 for cooling.
Sensor signals are input from an air conditioning sensor group 25 including an evaporator temperature sensor for detecting the air temperature immediately after the air blows out, a solar radiation sensor for detecting the amount of solar radiation into the vehicle interior, and the like. Further, signals (temperature setting signals and the like) from the levers and switches 27 of the air conditioning operation panel 26 provided near the driver's seat in the vehicle cabin are also input to the control device 24.

Next, the operation of this embodiment in the above configuration will be described. First, during the heating operation, the cooling electromagnetic valve 15 and the dehumidifying electromagnetic valve 17 of the refrigeration cycle 12 are closed and the heating electromagnetic valve 16 is opened by the output of the control device 24. Thereby, when the compressor 13 operates, the path shown by the thick line in FIG. 1, that is, the compressor 13 → the condenser 9 → the first depressurizer 19 → the outdoor heat exchanger 18 → the heating electromagnetic valve 18 → the accumulator 21 → the compression. The refrigerant flows through the path of the machine 13.

Therefore, the outdoor heat exchanger 18 becomes an evaporator, and the heat absorbed by the outdoor heat exchanger 18 and the heat generated by the compression work can be radiated as condensation heat in the indoor condenser 9 in the air conditioning unit 1. it can. Therefore, the switching door 1
1 is opened as shown by the solid line in FIG.
Blown air passes through the condenser 9 and is heated to become hot air, so that the vehicle interior can be heated.

Then, the target pressure of the cycle high pressure is calculated based on the target outlet air temperature and the like, and the number of revolutions of the compressor 13 is controlled so as to reach the target pressure, thereby adjusting the outlet air temperature. On the other hand, during the cooling operation, the control device 24
, The cooling electromagnetic valve 15 of the refrigeration cycle 12 is opened, and the heating electromagnetic valve 16 and the dehumidifying electromagnetic valve 17 are closed. Therefore, when the compressor 13 operates, the compressor 13 →
Condenser 9 → cooling solenoid valve 15 → outdoor heat exchanger 18 → second
The refrigerant flows through the route of the pressure reducer 20 → the evaporator 8 → the accumulator 21 → the compressor 13. Also, during cooling,
By operating the switching door 11 to the position indicated by the broken line in FIG. 1, the ventilation passage of the condenser 9 is fully closed, and the bypass passage 10 is fully opened. Therefore, all the air blown by the blower 6 passes through the bypass passage 10 and does not pass through the condenser 9. As a result, the condenser 9 becomes a mere refrigerant passage and does not perform a condensing operation.

Then, the outdoor heat exchanger 18 becomes a condenser, and the refrigerant radiated and condensed by the outdoor heat exchanger 18 flows into the evaporator 8 after being depressurized by the second decompressor 20. Here, the low-pressure refrigerant evaporates and cools the blown air. The cooled cold air passes through the bypass passage 10 and is blown into the vehicle interior to perform cooling. Next, the frost prevention control and the defrost control of the outdoor heat exchanger 18 during the heating operation, which are features of the present embodiment, will be described. FIG. 2 shows a control routine executed by the control device 24 to perform these controls, and will be described below with reference to FIGS.

During the heating operation, a part of the high-temperature and high-pressure gas refrigerant discharged from the compressor 13 as shown by a dashed line in FIG. 1 is used, except when the bypass control valve 31 is controlled to the fully closed position. The outdoor heat exchanger 18 via the bypass circuit 30
During the heating operation, the opening degree of the bypass control valve 31 is controlled in accordance with the control routine of FIG.

If it is within 10 minutes after the start of the heating operation (step S100: YES), the bypass control valve 31 is controlled to the fully closed position (step S101), and the refrigerant discharged from the compressor 13 is introduced into the full condenser 9. To maximize the heating capacity. After 10 minutes have passed since the start of the heating operation (step S1)
00 is NO), the outdoor air temperature detected by the outdoor air temperature sensor 33 and the outdoor heat exchanger 18 detected by the outdoor air temperature sensor 32.
Of the temperature difference ΔT from the temperature (step S10)
2). Here, ΔT = outside air temperature−outdoor heat exchanger temperature.

If the temperature difference ΔT is within the target temperature range, that is, 0 ° C <ΔT <5 ° C, the heating operation is continued with the bypass control valve 31 fully closed. On the other hand, ΔT ≧
If it is 5 ° C., the process proceeds to step S103, where ΔT <20 °
C, or if the state of ΔT ≧ 20 ° C. is less than 10 minutes, the determination in step S103 is NO, and the determination in step S103 is NO.
At 104, the bypass control valve 31 is opened by 1%.

As a result, a part of the gas refrigerant discharged from the compressor 13 is introduced into the outdoor heat exchanger 18 via the bypass circuit 30, and the gas refrigerant discharges the outdoor heat exchanger 18
Is warmed. Therefore, the temperature of the outdoor heat exchanger 18 is increased, or the temperature of the outdoor heat exchanger 18 is prevented from decreasing. While ΔT ≧ 5 ° C. and the state of NO in step S103 continues, the opening of the bypass control valve 31 is increased by 1% in step S104, and the amount of gas refrigerant introduced into the outdoor heat exchanger 18 increases. Then, the temperature of the outdoor heat exchanger 18 rises.

When the temperature of the outdoor heat exchanger 18 rises under the control of steps S102 to S104 and the temperature difference ΔT is adjusted to the target temperature range (0 ° C <ΔT <5 ° C), the bypass at that time is set. The heating operation is continued while the opening of the control valve 31 is maintained. If the temperature of the outdoor heat exchanger 18 exceeds the outside air temperature (ΔT <0 ° C.), step S10
From 2, the process proceeds to step S <b> 105, where the opening of the bypass control valve 31 is reduced by 1%, and the amount of gas refrigerant introduced into the outdoor heat exchanger 18 is reduced.

While the state of ΔT <0 ° C. continues, the opening of the bypass control valve 31 is reduced by 1% in step S105, and the amount of gas refrigerant introduced into the outdoor heat exchanger 18 is reduced. Then, the temperature of the outdoor heat exchanger 18 decreases. Next, the defrost control will be described. If the state of ΔT ≧ 20 ° C. continues for 10 minutes or more, it is determined that a frost is formed (step S10).
3 is YES), in step S106, the bypass control valve 31
Is opened by 1% to start defrost control.

If the temperature Toh of the outdoor heat exchanger 18 is lower than 0 ° C., or if the condition of Toh> 0 ° C. is less than 5 minutes, step S107 becomes NO, and the bypass control valve is turned on at step S106. 31 is increased by 1%, the amount of gas refrigerant introduced into the outdoor heat exchanger 18 is increased, and defrosting is performed. As a result, if the state of Toh> 0 ° C. continues for 5 minutes or more, it is determined that the defrosting is completed (step S
107 is YES), the defrost control ends.

If the cycle of steps S102 to S104, the cycle of steps S102 and S105, and the cycle of steps S106 and S107 are each set to 1 second, the opening of the bypass control valve 31 is changed from fully closed to fully opened in 100 seconds. Can be varied up to According to the above-described embodiment, by adjusting the temperature difference ΔT to the target temperature range, it is possible to prevent the temperature of the outdoor heat exchanger 18 from dropping more than necessary, and accordingly, the temperature of the outdoor heat exchanger 18 is reduced to the frost formation temperature range. The possibility of lowering is reduced, and frost formation can be prevented.

Also, since the amount of gas refrigerant introduced into the outdoor heat exchanger 18 is controlled continuously, not on / off, a rapid change in the flow rate of the refrigerant flowing through the condenser 9 is prevented. The indoor air blowing temperature can be stabilized. Further, when it is determined that the frost is formed, the amount of the gas refrigerant flowing through the bypass circuit 30 is increased, so that the defrost can be quickly and reliably performed. (Other Embodiments) The present invention is not limited to the vehicle as in the above embodiment, but can be applied to air conditioners for various uses.

Even if the bypass control valve 31 is of a type that opens and closes the bypass circuit 30 in an on-off manner, frost formation and defrosting can be performed as in the above embodiment. In an air conditioner that does not include the bypass circuit 30 and the bypass control valve 31, the compressor 13 is used instead of controlling the opening of the bypass control valve 31.
By controlling the rotation speed of the compressor or the on / off of the compressor 13 to control the temperature of the outdoor heat exchanger 18, frost formation and defrosting can be performed in the same manner as in the above embodiment.

[Brief description of the drawings]

FIG. 1 is an overall system diagram of an embodiment of the present invention.

FIG. 2 is a flowchart for explaining the operation of an embodiment of the present invention.

[Explanation of symbols]

2 ... air conditioning duct, 9 ... condenser (indoor heat exchanger), 13 ...
Compressor, 18 outdoor heat exchanger, 19 pressure reducer (pressure reducing means), 24 air conditioning control device (control means), 30 bypass circuit, 31 bypass control valve.

Claims (4)

[Claims]
1. An air conditioning duct (2) forming a passage for air-conditioned air blown into a room, a compressor (13) for compressing and discharging a refrigerant, and arranged in the air conditioning duct (2) for heating. An indoor heat exchanger (9) for exchanging heat between the refrigerant discharged from the compressor (13) and the conditioned air to condense the refrigerant, and a decompression for decompressing the refrigerant condensed in the indoor heat exchanger (9). Means (19), and an outdoor heat exchanger (18) which is disposed outdoors and heat-exchanges the refrigerant and outdoor air depressurized by the pressure reducing means (19) during heating to evaporate the refrigerant. The outdoor heat exchanger (18) such that a temperature difference between the temperature of the outdoor heat exchanger (18) and the temperature of the outdoor heat exchanger (18) is within a predetermined range.
A heat pump air conditioner characterized by controlling the temperature of the air.
2. A bypass circuit (3) for guiding refrigerant discharged from said compressor (13) to said outdoor heat exchanger (18).
0), a bypass control valve (31) for adjusting the amount of refrigerant flowing through the bypass circuit (30), and an operation of the bypass control valve (31) so as to control the temperature difference within a predetermined range. The heat pump type air conditioner according to claim 1, further comprising a control means (24).
3. The control means (24) determines that a frosting state has occurred when the temperature of the outdoor heat exchanger (18) has been lower than the outside air temperature by a predetermined value or more for a predetermined time. The heat pump air conditioner according to claim 2, wherein the valve opening state of (31) is continued until it is determined that the defrosting is completed.
4. The heat pump air conditioner according to claim 2, wherein the bypass control valve (31) is capable of continuously adjusting the amount of refrigerant flowing through the bypass circuit (30).
JP08978499A 1999-03-30 1999-03-30 Heat pump air conditioner Expired - Fee Related JP4134433B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP08978499A JP4134433B2 (en) 1999-03-30 1999-03-30 Heat pump air conditioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP08978499A JP4134433B2 (en) 1999-03-30 1999-03-30 Heat pump air conditioner

Publications (2)

Publication Number Publication Date
JP2000283611A true JP2000283611A (en) 2000-10-13
JP4134433B2 JP4134433B2 (en) 2008-08-20

Family

ID=13980319

Family Applications (1)

Application Number Title Priority Date Filing Date
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Country Status (1)

Country Link
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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011011686A (en) * 2009-07-03 2011-01-20 Denso Corp Control method for vehicular air conditioner
CN103204044A (en) * 2012-01-16 2013-07-17 杭州三花研究院有限公司 Vehicle air-conditioning system
JP2013178032A (en) * 2012-02-28 2013-09-09 Mitsubishi Heavy Ind Ltd Vehicle heat pump air conditioner and method for operating the same
CN103568782A (en) * 2012-08-10 2014-02-12 本田技研工业株式会社 Air conditioner for vehicle
JP2015116934A (en) * 2013-12-18 2015-06-25 株式会社デンソー Heat pump cycle device
US9829237B2 (en) 2012-03-05 2017-11-28 Hanon Systems Heat pump system for vehicle and method of controlling the same
CN108488920A (en) * 2018-04-26 2018-09-04 广东美的制冷设备有限公司 Air conditioner and its control method, device

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5747709B2 (en) * 2011-07-22 2015-07-15 株式会社富士通ゼネラル Air conditioner
CN107356023B (en) * 2016-05-10 2019-12-10 比亚迪股份有限公司 Heat pump air conditioning system and electric automobile

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011011686A (en) * 2009-07-03 2011-01-20 Denso Corp Control method for vehicular air conditioner
CN103204044A (en) * 2012-01-16 2013-07-17 杭州三花研究院有限公司 Vehicle air-conditioning system
JP2013178032A (en) * 2012-02-28 2013-09-09 Mitsubishi Heavy Ind Ltd Vehicle heat pump air conditioner and method for operating the same
US9829237B2 (en) 2012-03-05 2017-11-28 Hanon Systems Heat pump system for vehicle and method of controlling the same
CN103568782A (en) * 2012-08-10 2014-02-12 本田技研工业株式会社 Air conditioner for vehicle
EP2695758A1 (en) 2012-08-10 2014-02-12 Honda Motor Co., Ltd. Air conditioner for vehicle
JP2014034371A (en) * 2012-08-10 2014-02-24 Honda Motor Co Ltd Vehicle air conditioner
US9707930B2 (en) 2012-08-10 2017-07-18 Honda Motor Co., Ltd. Air conditioner for vehicle
JP2015116934A (en) * 2013-12-18 2015-06-25 株式会社デンソー Heat pump cycle device
CN108488920A (en) * 2018-04-26 2018-09-04 广东美的制冷设备有限公司 Air conditioner and its control method, device

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