KR20240000663A - Automotive air conditioning system - Google Patents

Abstract

The present invention includes a compressor that compresses the introduced refrigerant and discharges it in a high-temperature, high-pressure gaseous state; an indoor condenser connected to the compressor through a first flow path, into which the refrigerant discharged from the compressor flows and heat-exchanging the introduced refrigerant with air flowing into the air conditioning case to heat the vehicle interior in a heating mode; a water-cooled condenser connected to the indoor condenser through a second flow path, which draws in the refrigerant discharged from the indoor condenser and condenses the refrigerant through heat exchange with cooling water; an outdoor condenser connected to the water-cooled condenser through a third flow path, and receiving the refrigerant discharged from the water-cooled condenser and condensing the refrigerant through heat exchange with external air supplied from outside; An evaporator connected to the outdoor condenser through a fourth flow path, and in the cooling mode, takes in the refrigerant discharged from the outdoor condenser, evaporates the refrigerant, and cools the vehicle interior by exchanging heat with air supplied to the vehicle interior through the air conditioning case; A first branch passage connected to the evaporator and the fifth passage and connected to the compressor by a sixth passage, refrigerant supplied from the evaporator in each mode, and branched from the third passage and connected to the fifth passage. an accumulator that temporarily stores the refrigerant supplied from the water-cooled condenser, separates the stored refrigerant into liquid refrigerant and gaseous refrigerant, and then supplies the gaseous refrigerant to the compressor; a battery chiller that is provided on a bypass passage branched from the fourth passage and connected to the fifth passage, and cools the battery coolant by exchanging heat with the refrigerant in a cooling battery cooperation mode; A second branch passage is provided on the second passage and the fourth passage to depressurize the refrigerant moving to the second passage and the fourth passage, and is branched from the bypass passage and connected to the fourth passage. An expansion valve unit provided at a point branching from the bypass passage to selectively depressurize the moving refrigerant while switching the flow of the refrigerant moving into the bypass passage; A point where the first branch flow path branched from the third flow path and connected to the fifth flow path branches off from the third flow path, on the third branch flow path branched from the second flow path and connected to the fourth flow path, An opening/closing valve unit provided at the front of the point where the third branch flow path is connected on the fourth flow path to change the flow of refrigerant, selectively open and close the third branch flow path, and prevent the refrigerant from flowing back into the fourth flow path; It is provided on the sixth passage adjacent to the compressor and the first passage adjacent to the indoor condenser and adjacent to the outdoor condenser to measure the pressure and temperature of the refrigerant moving to the sixth passage and the first passage and the temperature of the outside air. sensor unit; And it is connected to the expansion valve unit, the sensor unit, and the opening/closing valve unit, and controls the operation of the expansion valve unit in response to each mode based on the pressure and temperature of the refrigerant and the temperature of the outside air measured by the sensor unit, while controlling the opening and closing of the expansion valve unit. Provided is a cooling and heating system for a vehicle that includes a control unit that controls the opening and closing direction and opening and closing of the valve unit.

Description

Automotive air conditioning system {Automotive air conditioning system}

The present invention relates to a vehicle cooling and heating system, and more specifically, to a vehicle cooling and heating system that cools and heats the vehicle using a refrigerant that exchanges heat with coolant in a water-cooled condenser.

An air conditioning system for a vehicle typically includes a cooling system for cooling the interior of the vehicle and a heating system for heating the interior of the vehicle. The cooling system is configured to cool the interior of the vehicle by converting air passing through the outside of the evaporator on the evaporator side of the refrigerant cycle into cold air by exchanging heat with the refrigerant flowing inside the evaporator, and the heating system is configured to cool the vehicle interior by using a heater on the heater core side of the coolant cycle. It is configured to heat the vehicle interior by converting the air passing through the outside of the core into warmth by exchanging heat with the coolant flowing inside the heater core.

Meanwhile, different from the above-mentioned vehicle air conditioning system, a heat pump system that can selectively perform cooling and heating by changing the flow direction of the refrigerant using one refrigerant cycle is being applied, for example, two heat exchangers. (i.e., an indoor heat exchanger installed inside the air conditioning case to exchange heat with the air blown into the vehicle interior, and an outdoor heat exchanger to exchange heat outside the air conditioning case) and a direction control valve that can change the flow direction of the refrigerant. do. Therefore, when the cooling mode is operated according to the flow direction of the refrigerant by the direction control valve, the outdoor heat exchanger serves as a condenser for cooling, and when the heating mode is operated, the outdoor heat exchanger functions as an evaporator for heating. do.

Various types of vehicle heat pump systems have been proposed, a representative example of which is shown in FIG. 1.

The vehicle heat pump system shown in FIG. 1 is installed in parallel with a compressor 30 that compresses and discharges refrigerant, and a high-pressure side heat exchanger 32 that dissipates heat from the refrigerant discharged from the compressor 30. A first expansion valve 34 and a first bypass valve 36 that selectively pass the refrigerant that has passed through the high-pressure side heat exchanger 32, and the first expansion valve 34 or the first bypass valve 36 ) an outdoor heat exchanger (48) that heat-exchanges the refrigerant that has passed through the outdoor heat exchanger (48), a low-pressure side heat exchanger (60) that evaporates the refrigerant that has passed through the outdoor heat exchanger (48), and the low-pressure side heat exchanger (60). An accumulator (62) that separates the passed refrigerant into gas phase and liquid refrigerant, and an intermediate heat exchanger (50) that exchanges heat between the refrigerant supplied to the low pressure side heat exchanger (60) and the refrigerant returning to the compressor (30). ) and a second expansion valve (56) that selectively expands the refrigerant supplied to the low-pressure side heat exchanger (60), and is installed in parallel with the second expansion valve (56) to form the outdoor heat exchanger (48) It includes a second bypass valve 58 that selectively connects the outlet side of and the inlet side of the accumulator 62.

In FIG. 1, reference numeral 10 refers to an air conditioning case in which the high-pressure side heat exchanger 32 and the low-pressure side heat exchanger 60 are built-in, reference number 12 refers to a temperature control door that controls the mixing amount of cold and warm air, and reference number 20 refers to the above-mentioned air conditioning case. Each blower installed at the entrance of the air conditioning case is shown.

According to the conventional vehicle heat pump system configured as described above, when the heat pump mode (heating mode) is operated, the first bypass valve 36 and the second expansion valve 56 are closed, and the first expansion valve ( 34) and the second bypass valve 58 are opened. Additionally, the temperature control door 12 operates as shown in FIG. 1. Therefore, the refrigerant discharged from the compressor 30 is the high pressure side heat exchanger 32, the first expansion valve 34, the outdoor heat exchanger 48, the high pressure part 52 of the intermediate heat exchanger 50, and the second bypass. It returns to the compressor 30 through the valve 58, the accumulator 62, and the low pressure part 54 of the intermediate heat exchanger 50 in that order. That is, the high-pressure side heat exchanger 32 functions as a heater, and the outdoor heat exchanger 48 functions as an evaporator.

When the air conditioner mode (cooling mode) is activated, the first bypass valve 36 and the second expansion valve 56 are opened, and the first expansion valve 34 and the second bypass valve 58 are closed. do. Additionally, the temperature control door 12 closes the passage of the high pressure side heat exchanger 32. Therefore, the refrigerant discharged from the compressor 30 is the high pressure side heat exchanger 32, the first bypass valve 36, the outdoor heat exchanger 48, the high pressure part 52 of the intermediate heat exchanger 50, and the second expansion. It returns to the compressor 30 through the valve 56, the low-pressure side heat exchanger 60, the accumulator 62, and the low-pressure part 54 of the intermediate heat exchanger 50 in that order. That is, the low-pressure side heat exchanger 60 functions as an evaporator, and the high-pressure side heat exchanger 32 closed by the temperature control door 12 functions as a heater in the same way as in the heat pump mode. do.

For conventional technology, refer to Korean Patent Publication No. 10-2013-0101254 (2013.09.13.).

The conventional vehicle heat pump system uses an intermediate heat exchanger (50) to improve cooling performance during cooling, dissipating heat through conduction of high-temperature refrigerant to low-temperature refrigerant, thereby making it possible to secure an additional subcooling section, thereby increasing cooling performance. In the electric vehicle heat pump system that secures heating performance through refrigerant, it is necessary to secure a subcooling section of the refrigerant, and after expansion in the electronic expansion valve, it is necessary to secure superheat through heat absorption in the low-pressure side heat exchanger (60), but the outdoor heat exchanger (48) ), a problem occurred in which the stability of the system became increasingly insufficient due to low subcooling due to insufficient capacity and insufficient superheating due to lack of heat source.

In addition, the conventional second expansion valve 56 is composed of a 2-way internal flow path, so it can only block refrigerant flow in both directions and expand through step control of the orifice hole, which causes refrigerant expansion and expansion in the entire heat pump system circuit. When changing the flow path, a separate line must be constructed, and each line configuration causes the overall circuit configuration to be complicated, and is also a very disadvantageous factor in utilizing space in the limited power electronic component room.

The present invention was created to solve the above problems, and allows refrigerant to pass through an intermediate heat exchanger used for cooling even in heating mode, thereby securing a supercooling section and superheating during heating, and making it possible to secure a supercooling section and a degree of superheating during heating. By allowing online refrigerants to exchange heat with each other, it is possible to secure subcooling before expansion and a margin for compressor superheating in the electronic expansion valve, and the integrated expansion valve provided at the point where the second branch flow path branches off on the bypass flow path is used to expand the refrigerant. The purpose is to provide a cooling and heating system for vehicles that can simplify the circuit configuration of the entire heat pump system by simultaneously expanding the refrigerant while changing the flow direction.

In order to achieve the above object, the present invention includes a compressor that compresses the introduced refrigerant and discharges it in a high-temperature, high-pressure gaseous state; an indoor condenser connected to the compressor through a first flow path, into which the refrigerant discharged from the compressor flows and heat-exchanging the introduced refrigerant with air flowing into the air conditioning case to heat the vehicle interior in a heating mode; a water-cooled condenser connected to the indoor condenser through a second flow path, which draws in the refrigerant discharged from the indoor condenser and condenses the refrigerant through heat exchange with cooling water; an outdoor condenser connected to the water-cooled condenser through a third flow path, and receiving the refrigerant discharged from the water-cooled condenser and condensing the refrigerant through heat exchange with external air supplied from outside; An evaporator connected to the outdoor condenser through a fourth flow path, and in the cooling mode, takes in the refrigerant discharged from the outdoor condenser, evaporates the refrigerant, and cools the vehicle interior by exchanging heat with air supplied to the vehicle interior through the air conditioning case; A first branch passage connected to the evaporator and the fifth passage and connected to the compressor by a sixth passage, refrigerant supplied from the evaporator in each mode, and branched from the third passage and connected to the fifth passage. an accumulator that temporarily stores the refrigerant supplied from the water-cooled condenser, separates the stored refrigerant into liquid refrigerant and gaseous refrigerant, and then supplies the gaseous refrigerant to the compressor; a battery chiller that is provided on a bypass passage branched from the fourth passage and connected to the fifth passage, and cools the battery coolant by exchanging heat with the refrigerant in a cooling battery cooperation mode; A second branch passage is provided on the second passage and the fourth passage to depressurize the refrigerant moving to the second passage and the fourth passage, and is branched from the bypass passage and connected to the fourth passage. An expansion valve unit provided at a point branching from the bypass passage to selectively depressurize the moving refrigerant while switching the flow of the refrigerant moving into the bypass passage; A point where the first branch flow path branched from the third flow path and connected to the fifth flow path branches off from the third flow path, on the third branch flow path branched from the second flow path and connected to the fourth flow path, An opening/closing valve unit provided at the front of the point where the third branch flow path is connected on the fourth flow path to change the flow of refrigerant, selectively open and close the third branch flow path, and prevent the refrigerant from flowing back into the fourth flow path; It is provided on the sixth passage adjacent to the compressor and the first passage adjacent to the indoor condenser and adjacent to the outdoor condenser to measure the pressure and temperature of the refrigerant moving to the sixth passage and the first passage and the temperature of the outside air. sensor unit; And it is connected to the expansion valve unit, the sensor unit, and the opening/closing valve unit, and controls the operation of the expansion valve unit in response to each mode based on the pressure and temperature of the refrigerant and the temperature of the outside air measured by the sensor unit, while controlling the opening and closing of the expansion valve unit. Provided is a cooling and heating system for a vehicle that includes a control unit that controls the opening and closing direction and opening and closing of the valve unit.

The cooling and heating system for a vehicle according to the present invention may further include an intermediate heat exchanger that exchanges heat between the refrigerant moving to the fourth flow path and the refrigerant moving to the fifth flow path.

In the cooling and heating system for a vehicle according to the present invention, the intermediate heat exchanger may have one of the forms of a double pipe structure, a spiral double pipe structure, a plate stacked structure, and a plate-shaped tube joint structure, and can be used in a cooling mode, a heating mode, a heating dehumidification mode, and a cooling battery. In cooperative mode, heat can be exchanged in the intermediate heat exchanger.

The accumulator may be provided with a heater rod made of carbon exothermic composite material that vaporizes the supplied liquid refrigerant, and the degree of superheating of the refrigerant supplied to the compressor may be increased by the heater rod.

The expansion valve unit is provided at a front end of the water-cooled condenser on the second flow path and includes a first electronic expansion valve that expands and depressurizes the refrigerant moved from the indoor condenser to the water-cooled condenser during heating mode and heating dehumidification mode, and A solenoid expansion valve provided at the front of the evaporator on the 4th flow path and expanding and depressurizing the refrigerant supplied to the evaporator through the 4th flow path during the cooling mode and cooling battery cooperation mode, and the second branch flow path on the bypass flow path It is provided at the branch point, and in the heating dehumidification mode, the flow of the refrigerant moving to the bypass passage is converted to the fourth passage while expanding and depressurizing the refrigerant supplied to the fourth passage, and in the cooling battery cooperation mode, the It may include an integrated expansion valve that expands and depressurizes the refrigerant supplied to the battery chiller through a bypass passage. The integrated expansion valve is closed in the cooling mode and opens in the direction of the fourth passage in the heating mode and heating dehumidification mode. It can be opened toward the battery chiller in the cooling battery cooperation mode.

The integrated expansion valve may be a 3-way valve, and the ball provided inside the integrated expansion valve has an inlet through which refrigerant is injected from the outdoor condenser, and an outlet through which the refrigerant injected into the battery chiller and the evaporator is discharged. A discharge slit may be formed on one side of the discharge port to expand and depressurize the discharged refrigerant.

The injection port and the discharge port may communicate with each other and be arranged at right angles to each other, one side and the other side of the discharge port may have different lengths, and the length (L1) of one side where the discharge slit is formed is the length of the other side. It may be smaller than the length (L2) of .

The on/off valve unit includes a first on/off valve provided at a point where the first branch flow path diverges from the third flow path to switch the flow of refrigerant moving to the third flow path, and a first on/off valve provided on the third branch flow path. A second opening/closing valve that selectively opens and closes the third branch flow path, and is provided at the front end of the point where the third branch flow path is connected on the fourth flow path to prevent the refrigerant moving to the fourth flow path from flowing back toward the outdoor condenser. It may include a check valve that prevents the operation, and the first on-off valve may be a 3-way valve and the second on-off valve may be a 2-way valve.

The sensor unit includes a PT sensor provided on a sixth passage adjacent to the compressor and a first passage adjacent to the indoor condenser to measure the pressure and temperature of the refrigerant moving into the sixth passage and the first passage, the outdoor condenser, and It may include an outdoor temperature sensor provided adjacently to measure the temperature of the outdoor air.

In the cooling mode, the first on-off valve of the on-off valve unit provided at the rear end of the water-cooled condenser may be opened in the direction of the outdoor condenser, and the second on-off valve of the on-off valve unit provided on the third branch flow path may be closed. The first electronic expansion valve of the expansion valve part provided on the second flow path may be fully opened, and the solenoid expansion valve of the expansion valve part provided at the front of the evaporator on the fourth flow path may be opened to evaporate the evaporator. The refrigerant supplied to can be expanded, and the discharge port and the discharge slit of the integrated expansion valve of the expansion valve unit provided at the point where the second branch flow path branches on the bypass flow path can be closed.

In the heating mode and heating dehumidification mode, the first opening/closing valve of the switching valve unit provided at the rear end of the water-cooled condenser may be opened in the direction of the first branch flow path connected to the fifth flow path, and may be opened on the third branch flow path. The second on-off valve provided in the on-off valve part may be opened, and the check valve provided on the fourth flow path may operate so that the refrigerant moved to the fourth flow path through the second branch flow path flows back toward the outdoor condenser. The first electronic expansion valve of the expansion valve unit provided on the second flow path can expand the refrigerant supplied to the water-cooled condenser by opening, and is provided at the front of the evaporator on the fourth flow path. The solenoid expansion valve of the expansion valve part may be closed, and the integrated expansion valve of the expansion valve part provided at a point where the second branch flow path branches on the bypass flow path may cause the ball to rotate in the direction of the second branch flow path. As the discharge slit is gradually opened, the refrigerant supplied to the second branch flow path can be expanded, and when the outside air temperature measured by the outside air temperature sensor of the sensor unit is below 0°C, it can be switched to heating mode, and the outside air temperature If the outside temperature measured by the sensor is between 0℃ and 15℃, it can be switched to heating and dehumidification mode.

In the cooling battery cooperation mode, the first on-off valve of the on-off valve unit provided at the rear end of the water-cooled condenser may be opened in the direction of the outdoor condenser, and the second on-off valve of the on-off valve unit provided on the third branch flow path can be closed, the first electronic expansion valve of the expansion valve part provided on the second flow path can be fully opened, and the solenoid expansion valve of the expansion valve part provided at the front of the evaporator on the fourth flow path is opened. The refrigerant supplied to the evaporator can be expanded, and the integrated expansion valve of the expansion valve unit provided at the point where the second branch flow path branches on the bypass flow path rotates the ball to open the discharge slit in the direction of the battery chiller. As this is gradually opened, the refrigerant supplied to the battery chiller can be expanded.

According to the cooling and heating system for a vehicle according to the present invention, it is possible to secure a subcooling section by allowing the refrigerant to pass through the intermediate heat exchanger used during cooling even in the heating mode, and the refrigerant in the fourth passage, which is the high temperature line, and the fifth passage, which is the low temperature line, are By allowing heat exchange with each other, it is possible to secure a margin for superheating of the compressor, and by securing subcooling in the heating and dehumidifying mode, optimal expansion conditions for the integrated expansion valve are possible, maximizing the vehicle's interior dehumidification ability through the evaporator.

In addition, the integrated expansion valve provided at the point where the second branch flow path branches off on the bypass flow path can change the flow direction of the refrigerant and simultaneously expand the refrigerant discharged through the discharge port, simplifying the circuit configuration of the entire heat pump system. This can solve the problem of being a disadvantage in utilizing space in a limited room for power electronic components.

1 is a configuration diagram showing a conventional vehicle heat pump system.
Figure 2 is a configuration diagram showing a vehicle cooling and heating system according to an embodiment of the present invention.
FIG. 3 is a diagram illustrating a state in which refrigerant is circulated in the cooling mode of the vehicle cooling and heating system shown in FIG. 2.
FIG. 4 is a diagram illustrating a state in which refrigerant is circulated in the heating mode of the vehicle cooling and heating system shown in FIG. 2.
FIG. 5 is a diagram illustrating a state in which refrigerant is circulated in the heating and dehumidifying mode of the vehicle cooling and heating system shown in FIG. 2.
FIG. 6 is a diagram illustrating a state in which refrigerant is circulated in the cooling battery coordination mode of the vehicle cooling and heating system shown in FIG. 2.
Figure 7 is a diagram showing the flow state of refrigerant through the integrated expansion valve in cooling mode.
Figure 8 is a diagram showing the open and closed states of the integrated expansion valve in the heating mode and heating dehumidification mode.
Figure 9 is a diagram showing the flow state of refrigerant through the integrated expansion valve in the heating mode and heating dehumidification mode.
Figure 10 is a diagram showing the open and closed states of the integrated expansion valve in the cooling battery cooperation mode.
Figure 11 is a diagram showing the flow state of refrigerant through the integrated expansion valve in the cooling battery cooperation mode.

Hereinafter, preferred embodiments according to the present invention will be described in detail with reference to the attached drawings. Prior to this, the terms or words used in this specification and claims should not be construed as limited to their usual or dictionary meanings, and the inventor should appropriately define the concept of terms in order to explain his or her invention in the best way. It must be interpreted as meaning and concept consistent with the technical idea of the present invention based on the principle of definability.

2 to 11, the vehicle cooling and heating system 100 according to an embodiment of the present invention includes a compressor 1100, an indoor condenser 1200, a water-cooled condenser 1300, an outdoor condenser 1400, It includes an evaporator 1500, an accumulator 1600, a battery chiller 1700, an expansion valve unit 1800, an on/off valve unit 1900, a sensor unit 2000, and a control unit 2100, It may further include an intermediate heat exchanger (2200).

Referring to FIG. 2, the vehicle cooling and heating system 100 according to an embodiment of the present invention includes a compressor 1100, an indoor condenser 1200, a water-cooled condenser 1300, and an outdoor condenser 1400 on the refrigerant circulation line in which the refrigerant circulates. , the evaporator 1500 is connected, and is preferably applied to an electric vehicle or hybrid vehicle.

The compressor 1100 draws in and compresses the refrigerant through an input terminal connected to a passage through which the refrigerant flows, and then discharges the compressed refrigerant into the passage through the output terminal. At this time, the discharged refrigerant is a high-temperature, high-pressure refrigerant (refrigerant gas; gas). ) is discharged.

The output end of the compressor 1100 is connected to the first flow path (R1), and the input end of the indoor condenser 1200 and the output end of the compressor 1100 are connected through the first flow path (R1), so that the compressor 1100 ) The high-temperature, high-pressure refrigerant (gas) compressed in ) is output to the indoor condenser (1200).

The indoor condenser 1200 is provided in an air conditioning case (not shown), and the indoor condenser 1200 introduces the refrigerant (gas) discharged from the compressor 1100 through the first flow path (R1). The indoor condenser 1200 condenses the high-temperature, high-pressure refrigerant (gas) flowing inside through heat exchange with air supplied into the vehicle interior through an air conditioning case (not shown) and heats the air with the heat of condensation, thereby heating the interior of the vehicle. Ensure that heating is provided.

It is preferable that a PTC heater (PTC) is provided adjacent to the indoor condenser 1200, and the PTC heater (PTC) is provided inside the air conditioning case (not shown) to supply insufficient heating heat source.

The structure of the air conditioning case (not shown) and the process of supplying the heat-exchanged air to the interior of the vehicle to provide heating after the air conditioning case (not shown) takes in air are well-known technologies, and detailed description thereof is omitted. I decided to do it.

The output terminal of the indoor condenser (1200) is connected to the second flow path (R2), and the second flow path (R2) is connected to the water-cooled condenser (1300). The water-cooled condenser 1300 draws in the refrigerant discharged from the indoor condenser 1200 through the second flow path (R2) and condenses the refrigerant during cooling by exchanging heat with the coolant flowing in the coolant line (not shown) and providing heating. It serves to evaporate the refrigerant, and it is preferable that the first electronic expansion valve 1810 of the expansion valve unit 1800, which will be described later, is provided on the second flow passage R2.

The water-cooled condenser 1300 is connected to the outdoor condenser 1400 through a third flow path (R3). The outdoor condenser 1400 condenses the refrigerant introduced through the third flow path (R3) through heat exchange with external air and then discharges it to the fourth flow path (R4) through the output terminal. The fourth flow path (R4) is connected to the evaporator 1500 and supplies the refrigerant output after condensing in the outdoor condenser 1400 to the evaporator 1500.

The outdoor condenser 1400 draws refrigerant from the water-cooled condenser 1300 and condenses the refrigerant through heat exchange with external air. The outdoor condenser 1400 is a radiator unit provided in the vehicle drive unit (drive motor, not shown). It is placed close to (not shown), and the refrigerant introduced through the input side is condensed by heat exchange with external air and then discharged to the fourth flow path (R4).

The fourth flow path (R4) is connected to the evaporator 1500 and supplies the refrigerant output after condensing in the outdoor condenser 1400 to the evaporator 1500, and the evaporator 1500 vaporizes the introduced refrigerant. It serves to cool the vehicle interior by exchanging heat with air supplied into the vehicle interior through an air conditioning case (not shown).

The evaporator 1500 is connected to the accumulator 1600 through a fifth flow path (R5), and the accumulator 1600 is provided between the evaporator 1500 and the compressor 1100 and supplied from the evaporator 1500. Temporarily storing the refrigerant and the refrigerant supplied from the water-cooled condenser 1300 through the first branch flow path (QR1) branched from the third flow path (R3) and connected to the fifth flow path (R5) The liquid refrigerant is separated into a gaseous refrigerant, and the separated gaseous refrigerant is supplied to the compressor 1100 through the sixth flow path (R6).

The accumulator 1600 may be provided with a heater rod (not shown) made of carbon heat-generating composite material that vaporizes the supplied liquid refrigerant. A heater rod (not shown) may be provided inside the accumulator 1600. Accordingly, the degree of superheating of the refrigerant supplied to the compressor 1100 can be increased, thereby improving heating efficiency.

A bypass branched from the fourth passage (R4) connecting the outdoor condenser (1400) and the evaporator (1500) and connected to the fifth passage (R5) connecting the evaporator (1500) and the accumulator (1600). A battery chiller 1700 is provided on the flow path (BR).

The battery chiller 1700 serves to cool the battery (not shown) by heat exchanging the refrigerant flowing through the coolant line (not shown) and the bypass passage (BR) in the cooling battery cooperation mode. In the cooling battery coordination mode described later, the refrigerant flows into the bypass passage (BR), and at this time, the battery chiller 1700 mixes the refrigerant flowing into the bypass passage (BR) and the battery coolant flowing into the coolant line. By cooling the coolant through heat exchange, heat management of the battery (not shown) is possible.

The second flow path (R2), the fourth flow path (R4), and the second branch flow path (QR2) branched from the bypass flow path (BR) and connected to the fourth flow path (R4) are connected to the bypass flow path (BR). ) is provided at a point branching from the expansion valve unit 1800, and the expansion valve unit 1800 depressurizes the refrigerant moving to the second flow path (R2) and the fourth flow path (R4), and the bypass It serves to selectively depressurize the moving refrigerant by switching the flow of the refrigerant moving into the flow path (BR).

The expansion valve unit 1800 includes a first electronic expansion valve 1810, a solenoid expansion valve 1820, and an integrated expansion valve 1830. The first electronic expansion valve 1810 is provided on the second flow path (R2) and expands the refrigerant that passes through the indoor condenser 1200 and moves to the second flow path (R2) in the heating mode and heating dehumidification mode. It serves to reduce pressure.

The solenoid expansion valve 1820 is provided on the fourth flow path (R4) adjacent to the evaporator 1500, and passes through the outdoor condenser 1400 in the cooling mode and cooling battery cooperation mode and is supplied to the evaporator 1500. It serves to expand the refrigerant and reduce its pressure.

The integrated expansion valve 1830 is provided at a point where the second branch flow path (QR2) branches on the bypass flow path (BR), and the refrigerant flow moves to the bypass flow path (BR) in the heating and dehumidifying mode. While switching to the fourth flow path (R4), the refrigerant supplied to the fourth flow path (R4) is expanded and decompressed, and in the cooling battery cooperation mode, it is supplied to the battery chiller (1700) through the bypass flow path (BR). It serves to expand the supplied refrigerant and reduce its pressure.

The integrated expansion valve 1830 is closed in the cooling mode, and in the heating mode and heating dehumidification mode, the refrigerant moving to the bypass passage (BR) is supplied to the fourth passage (R4) in the direction of the fourth passage (R4). ) direction, and in the cooling battery cooperation mode, it opens in the direction of the battery chiller (1700) so that the refrigerant moving to the bypass passage (BR) is supplied to the battery chiller (1700).

Referring to FIGS. 7 to 11, the integrated expansion valve 1830 is a 3-way valve, and the ball 1831 provided therein has an inlet 1832 through which refrigerant is injected from the outdoor condenser 1400. , an outlet 1834 is formed that communicates with the inlet 1832 and discharges the refrigerant introduced through the inlet 1832 to the evaporator 1500 and the battery chiller 1700. The injection port 1832 and the discharge port 1834 are arranged at right angles to each other, and a discharge slit 1834a is formed on one side of the discharge port 1834. As the discharge port 1834 rotates around the injection port 1832, the discharge port 1834 is connected to the evaporator 1500 and the battery chiller 1700. One side and the other side of the discharge port 1834 have different lengths, and the length L1 of one side where the discharge slit 1834a is formed is longer than the length L2 of the other side. It is desirable to have a small length, and the refrigerant is discharged through the discharge slit (1834a) to reduce pressure.

The first branch flow path (QR1), which branches off from the third flow path (R3) and is connected to the fifth flow path (R5), branches off from the third flow path (R3) and branches off from the second flow path (R2). On the third branch flow path (QR3) connected to the fourth flow path (R4), an opening/closing valve unit 1900 is provided at the front end of the point where the third branch flow path (QR3) is connected to the fourth flow path (R4). do. The on-off valve unit 1900 switches the flow of refrigerant, selectively opens and closes the third branch flow path (QR3), and prevents the refrigerant from flowing back into the fourth flow path (R4).

The on-off valve unit 1900 includes a first on-off valve 1910, a second on-off valve 1920, and a check valve 1930. The first on/off valve 1910 is provided on the third flow path (R3) at a point where the first branch flow path (QR1) branches off from the third flow path (R3) and is connected to the fifth flow path (R5). It serves to change the flow direction of the refrigerant moving to the third flow path (R3), and it is preferable that a three-way valve is used as the first opening/closing valve (1910).

The second on/off valve (1920) is provided on the third branch flow path (QR3) and serves to selectively open and close the third branch flow path (QR3). The second on/off valve (1920) is a two-way valve. It is desirable to use.

The check valve 1930 is provided at the front of the point where the third branch flow path (QR3) is connected on the fourth flow path (R4) and moves from the third branch flow path (QR3) to the fourth flow path (R4). It serves to prevent the refrigerant from flowing back toward the outdoor condenser 1400, and the first on-off valve 1910 and the second on-off valve 1920 are connected to the control unit 2100, which will be described later, to the control unit 2100. It is desirable to operate by

A sensor unit 2000 is provided on the sixth flow path (R6) adjacent to the compressor 1100 and the first flow path (R1) adjacent to the indoor condenser 1200 and adjacent to the outdoor condenser 1400, The sensor unit 2000 serves to measure the pressure and temperature of the refrigerant moving to the sixth flow path (R6) and the first flow path (R1) and the temperature of the outdoor air adjacent to the outdoor condenser (1400).

The sensor unit 2000 includes a PT sensor 2010 and an outside temperature sensor 2020. The PT sensor 2010 is provided on the sixth flow path (R6) adjacent to the compressor 1100 and the first flow path (R1) adjacent to the indoor condenser 1200, and is connected to the compressor through the sixth flow path (R6). It serves to measure the pressure and temperature of the refrigerant supplied to (1100) and the refrigerant supplied to the indoor condenser (1200), and the outdoor temperature sensor (2020) is provided adjacent to the outdoor condenser (1400) to measure the outdoor air temperature sensor (2020). It serves to measure temperature, and the sensor unit 2000 is connected to a control unit 2100, which will be described later.

The control unit 2100 selectively opens and closes the expansion valve unit 1800 in response to each mode based on the pressure and temperature of the refrigerant and the temperature of the external air measured by the sensor unit 2000, thereby opening and closing the expansion valve unit 1900. ) plays a role in controlling the operation of.

The high-temperature, high-pressure refrigerant moving to the fourth flow path (R4) and the low-temperature, low-pressure refrigerant moving to the fifth flow path (R5) exchange heat by the intermediate heat exchanger (2200), and ensure a degree of subcooling in the heating mode described later. It is possible to secure a margin for superheat of the compressor 1100. The intermediate heat exchanger 2200 may have various structures such as a double pipe structure, a spiral double pipe structure, a plate stacked structure, and a plate-tube joint structure. For example, when the intermediate heat exchanger (2200) has a double pipe structure, it exchanges heat between the refrigerant flowing through the inner pipe provided on the inside and the refrigerant flowing into the outer pipe surrounding the inner pipe. The structure of the intermediate heat exchanger (2200) is general. Since this is the case, detailed description thereof will be omitted.

Referring to Figures 3 and 7, the flow of refrigerant in cooling mode is compressor 1100, indoor condenser 1200, water-cooled condenser 1300, outdoor condenser 1400, evaporator 1500, accumulator 1600, and compressor. It circulates to (1100) to cool the vehicle interior.

In the cooling mode, the first opening/closing valve 1910 provided at the rear end of the water-cooled condenser 1300 on the third flow path (R3) opens toward the outdoor condenser 1400 and discharges the water from the water-cooled condenser 1300. Refrigerant is supplied to the outdoor condenser (1400).

The first electronic expansion valve 1810 provided at the front of the water-cooled condenser 1300 on the second flow path (R2) is fully opened and supplies the refrigerant moving to the second flow path (R2) to the water-cooled condenser (1300). And, the second opening/closing valve 1920 provided on the third branch flow path (QR3) branched from the second flow path (R2) is closed so that the refrigerant moving to the second flow path (R2) flows into the third branch flow path ( Make sure it is not moved to QR3).

The integrated expansion valve 1830 provided at the point where the second branch flow path (QR2) branches off on the bypass flow path (BR) branching from the fourth flow path (R4) has the discharge port 1834 and the discharge slit 1834a. ) are all closed to prevent the refrigerant moving to the fourth flow path (R4) from moving to the evaporator 1500 and the battery chiller 1700 through the bypass flow path (BR).

The solenoid expansion valve 1820 provided at the front of the evaporator 1500 on the fourth passage R4 expands the refrigerant moving to the fourth passage R4 and then supplies it to the evaporator 1500, and the solenoid The expansion valve 1820 is preferably opened to supply refrigerant to the evaporator 1500. The refrigerant that has passed through the evaporator 1500 is supplied to the accumulator 1600 through the intermediate heat exchanger 2200 and is separated into liquid refrigerant and gaseous refrigerant, and the separated gaseous refrigerant is circulated to the compressor 1100.

Referring to FIGS. 4, 8, and 9, in the heating mode, the flow of refrigerant passes through the compressor 1100 and the indoor condenser 1200, and then most of the refrigerant, except for some minimum flow rates, flows through the water-cooled condenser 1300 and the accumulator ( 1600), the refrigerant with the minimum flow rate among the refrigerants that have passed through the indoor condenser 1200 circulates to the evaporator 1500, the accumulator 1600, and the compressor 1100 through the third branch flow path (QR3). It is also possible to secure the superheat of the refrigerant while doing so, and when the outside temperature measured by the outside temperature sensor 2020 of the sensor unit 2000 is below 0°C, the heating mode is switched.

In the heating mode, the first opening/closing valve 1910 provided at the rear end of the water-cooled condenser 1300 on the third flow path (R3) is opened toward the first branch flow path (QR1) and discharges water from the water-cooled condenser (1300). The refrigerant is supplied to the accumulator (1600) through the first branch flow path (QR1).

The first electronic expansion valve 1810 provided at the front of the water-cooled condenser 1300 on the second flow path (R2) opens and supplies the refrigerant moving to the second flow path (R2) to the water-cooled condenser 1300. The refrigerant supplied to the water-cooled condenser 1300 is expanded.

The check valve 1930 provided on the fourth flow path (R4) operates to prevent the refrigerant moved to the third branch flow path (QR3) from flowing back toward the outdoor condenser 1400 through the fourth flow path (R4). do.

The solenoid expansion valve 1820 provided at the front of the evaporator 1500 on the fourth passage R4 is closed to prevent the refrigerant moving to the fourth passage R4 from being supplied to the evaporator 1500, The integrated expansion valve 1830 provided at a point where the second branch flow path (QR2) branches off on the bypass flow path (BR) branching from the fourth flow path (R4) causes the ball 1831 to rotate to form the second branch. The discharge slit (1834a) is gradually opened in the direction of the flow path (QR2) to expand the refrigerant supplied to the second branch flow path (QR2), and then the discharge port (1834) is completely opened in the direction of the second branch flow path (QR2). It is opened to supply refrigerant to the evaporator (1500).

Accordingly, low-temperature refrigerant is introduced into the evaporator 1500, and low-humidity air is discharged into the room through heat exchange with air flowing in from the outside, thereby enabling dehumidification of the room.

The refrigerant of the minimum flow rate moved to the third branch flow path (QR3) and controlled for expansion by the integrated expansion valve (1830) is supplied to the accumulator (1600) through the evaporator (1500), and the water-cooled condenser (1300) The refrigerant supplied to the accumulator 1600 through the evaporator 1500 is separated into liquid refrigerant and gaseous refrigerant, and the separated gaseous refrigerant is circulated to the compressor 1100.

Referring to FIGS. 5, 8, and 9, in the heating and dehumidifying mode, the flow of refrigerant passes through the compressor 1100 and the indoor condenser 1200, and then some of the refrigerant flows into the water-cooled condenser 1300, the accumulator 1600, and the compressor ( 1100), and some of the refrigerant that has passed through the indoor condenser 1200 circulates through the third branch flow path (QR3) to the evaporator 1500, accumulator 1600, and compressor 1100 to heat and dehumidify the vehicle interior. is performed, and when the outside temperature measured by the outside temperature sensor 2020 of the sensor unit 2000 is above 0°C and below 15°C, the mode is switched to heating and dehumidification mode.

In the heating dehumidification mode, the first opening/closing valve (1910) opens toward the accumulator (1600), the second opening/closing valve (1920) opens, the check valve (1930) operates, and the first electronic expansion valve (1810) opens. The solenoid expansion valve 1920 is closed, and the ball 1831 rotates to gradually open the discharge slit 1834a in the direction of the second branch flow path QR2, and the integrated expansion valve 1830 opens the second branch flow path QR2. After expanding the refrigerant supplied to (QR2), the discharge port 1834 is completely opened in the direction of the second branch flow path (QR2), which is the same as the heating mode shown in FIG. 4, but the integrated expansion valve 1830 In the heating mode, it opens to allow the minimum flow rate to pass, but in the heating and dehumidification mode, it is different from the heating mode in that the evaporator 1500 controls the flow rate to ensure dehumidification performance rather than the minimum flow rate.

6, 10, and 11, in the cooling battery coordination mode, the refrigerant flows through the compressor 1100, the indoor condenser 1200, the water-cooled condenser 1300, and the outdoor condenser 1400, and then some of the refrigerant is It circulates through the evaporator 1500, accumulator 1600, and compressor 1100, and some of the other refrigerant circulates through the battery chiller 1700, accumulator 1600, and compressor 1100 to cool the vehicle interior.

In the cooling battery cooperation mode, the first opening/closing valve 1910 provided at the rear end of the water-cooled condenser 1300 on the third flow path (R3) is opened toward the outdoor condenser 1400 to open the water-cooled condenser 1300. The discharged refrigerant is supplied to the outdoor condenser (1400).

The first electronic expansion valve 1810 provided at the front of the water-cooled condenser 1300 on the second flow path (R2) is fully opened and supplies the refrigerant moving to the second flow path (R2) to the water-cooled condenser (1300). And, the second opening/closing valve 1920 provided on the third branch flow path (QR3) branched from the second flow path (R2) is closed so that the refrigerant moving to the second flow path (R2) flows into the third branch flow path ( Make sure it is not moved to QR3).

The solenoid expansion valve 1820 provided at the front of the evaporator 1500 on the fourth passage R4 expands the refrigerant moving to the fourth passage R4 and then supplies it to the evaporator 1500. The integrated expansion valve 1830 provided at the point where the second branch flow path (QR2) branches off on the bypass flow path (BR) branching from the fourth flow path (R4) is opened in the direction of the battery chiller (1700). The refrigerant moved to the battery chiller 1700 through the bypass passage (BR) is expanded and then supplied to the battery chiller 1700.

The refrigerant that has passed through the evaporator 1500 and the battery chiller 1700 is supplied to the accumulator 1600 through the intermediate heat exchanger 2200 and is separated into liquid refrigerant and gaseous refrigerant, and the separated gaseous refrigerant is sent to the compressor ( 1100).

Therefore, even in the heating mode, the refrigerant passes through the intermediate heat exchanger (2200) used during cooling, making it possible to secure the subcooling section and the degree of superheating, and the fourth flow path (R4), which is the high temperature line, and the fifth flow path, which is the low temperature line. By allowing the refrigerants in (R5) to exchange heat with each other, it is possible to secure a margin for superheating of the compressor (1100), and by securing subcooling in the heating and dehumidifying mode, optimal expansion conditions for the integrated expansion valve (1830) are possible, thereby increasing the evaporator (1100). 1500), the vehicle's interior dehumidification ability can be maximized.

The present invention has been described with reference to the embodiments shown in the drawings, but these are merely illustrative, and those skilled in the art will understand that various modifications and equivalent other embodiments are possible therefrom. Therefore, the true scope of technical protection of the present invention should be determined by the technical spirit of the attached patent claims.

100: Vehicle cooling and heating system 1100: Compressor
1200: Indoor condenser 1300: Water-cooled condenser
1400: Outdoor condenser 1500: Evaporator
1600: Accumulator 1700: Battery chiller
1800: Expansion valve unit 1810: First electronic expansion valve
1820: Solenoid expansion valve 1830: Integrated expansion valve
1831: Ball 1832: Inlet
1834: discharge port 1834a: discharge slit
1900: Open/close valve unit 1910: First open/close valve
1920: Second opening/closing valve 1930: Check valve
2000: Sensor unit 2010: PT sensor
2020: Outdoor temperature sensor 2100: Control unit

Claims (12)

A compressor that compresses the introduced refrigerant and discharges it in a high-temperature, high-pressure gaseous state;
an indoor condenser connected to the compressor through a first flow path, into which the refrigerant discharged from the compressor flows and heat-exchanging the introduced refrigerant with air flowing into the air conditioning case to heat the vehicle interior in a heating mode;
a water-cooled condenser connected to the indoor condenser through a second flow path, which draws in the refrigerant discharged from the indoor condenser and condenses the refrigerant through heat exchange with cooling water;
an outdoor condenser connected to the water-cooled condenser through a third flow path, and receiving the refrigerant discharged from the water-cooled condenser and condensing the refrigerant through heat exchange with external air supplied from outside;
An evaporator connected to the outdoor condenser through a fourth flow path, and in the cooling mode, takes in the refrigerant discharged from the outdoor condenser, evaporates the refrigerant, and cools the vehicle interior by exchanging heat with air supplied to the vehicle interior through the air conditioning case;
A first branch passage connected to the evaporator and the fifth passage and connected to the compressor by a sixth passage, refrigerant supplied from the evaporator in each mode, and branched from the third passage and connected to the fifth passage. an accumulator that temporarily stores the refrigerant supplied from the water-cooled condenser, separates the stored refrigerant into liquid refrigerant and gaseous refrigerant, and then supplies the gaseous refrigerant to the compressor;
a battery chiller that is provided on a bypass passage branched from the fourth passage and connected to the fifth passage, and cools the battery coolant by exchanging heat with the refrigerant in a cooling battery cooperation mode;
A second branch passage is provided on the second passage and the fourth passage to depressurize the refrigerant moving to the second passage and the fourth passage, and is branched from the bypass passage and connected to the fourth passage. An expansion valve unit provided at a point branching from the bypass passage to selectively depressurize the moving refrigerant while switching the flow of the refrigerant moving into the bypass passage;
A point where the first branch flow path branched from the third flow path and connected to the fifth flow path branches off from the third flow path, on the third branch flow path branched from the second flow path and connected to the fourth flow path, An opening/closing valve unit provided at the front of the point where the third branch flow path is connected on the fourth flow path to change the flow of refrigerant, selectively open and close the third branch flow path, and prevent the refrigerant from flowing back into the fourth flow path;
It is provided on the sixth passage adjacent to the compressor and the first passage adjacent to the indoor condenser and adjacent to the outdoor condenser to measure the pressure and temperature of the refrigerant moving to the sixth passage and the first passage and the temperature of the outside air. sensor unit; and
It is connected to the expansion valve unit, the sensor unit, and the on-off valve unit, and controls the operation of the expansion valve unit in response to each mode based on the pressure and temperature of the refrigerant and the temperature of the outside air measured by the sensor unit, and the on-off valve A cooling and heating system for a vehicle including a control unit that controls the opening and closing direction and opening and closing of the unit.
In claim 1,
A cooling and heating system for a vehicle further comprising an intermediate heat exchanger that exchanges heat between the refrigerant moved to the fourth flow path and the refrigerant moved to the fifth flow path.
In claim 2,
The intermediate heat exchanger has one of the following forms: a double-tube structure, a spiral double-tube structure, a plate-stacked structure, and a plate-tube joint structure,
A cooling and heating system for a vehicle, characterized in that heat is exchanged in the intermediate heat exchanger in cooling mode, heating mode, heating dehumidification mode, and cooling battery cooperation mode.
In claim 1,
A heating and cooling system for a vehicle, wherein the accumulator is provided with a heater rod made of carbon heat-generating composite material that vaporizes the supplied liquid refrigerant, and the degree of superheat of the refrigerant supplied to the compressor is increased by the heater rod.
In claim 1,
The expansion valve part,
A first electronic expansion valve provided in front of the water-cooled condenser on the second flow path and expanding and depressurizing the refrigerant moving from the indoor condenser to the water-cooled condenser during heating mode and heating dehumidification mode;
A solenoid expansion valve provided at the front of the evaporator on the fourth passage and expanding and depressurizing the refrigerant supplied to the evaporator through the fourth passage in the cooling mode and cooling battery cooperation mode;
It is provided at a point where the second branch flow path branches on the bypass flow path, and in the heating and dehumidifying mode, the flow of refrigerant moving to the bypass flow path is converted to the fourth flow path and the refrigerant supplied to the fourth flow path is expanded. It includes an integrated expansion valve that expands and reduces the pressure of the refrigerant supplied to the battery chiller through the bypass passage in the cooling battery cooperation mode,
The integrated expansion valve is closed in the cooling mode, opens in the direction of the fourth flow path in the heating mode and heating dehumidification mode, and opens in the direction of the battery chiller in the cooling battery cooperation mode.
In claim 5,
The integrated expansion valve is a 3-way valve,
The ball provided inside the integrated expansion valve is formed with an inlet through which refrigerant is injected from the outdoor condenser and an outlet through which the refrigerant injected into the battery chiller and the evaporator is discharged,
A vehicle cooling and heating system in which a discharge slit is formed on one side of the discharge port to expand and depressurize the discharged refrigerant.
In claim 6,
The injection port and the discharge port communicate with each other and are arranged at right angles to each other, one side and the other side of the discharge port have different lengths, and the length (L1) of one side where the discharge slit is formed is the length (L2) of the other side. ) A vehicle cooling and heating system characterized by a smaller size.
In claim 1,
The opening/closing valve part,
A first opening/closing valve provided at a point where the first branch flow path branches off from the third flow path to switch the flow of refrigerant moving to the third flow path;
A second opening/closing valve provided on the third branch flow path to selectively open and close the third branch flow path,
It includes a check valve provided at the front of the point where the third branch flow path is connected on the fourth flow path to prevent the refrigerant moving into the fourth flow path from flowing back toward the outdoor condenser,
A cooling and heating system for a vehicle, wherein the first on/off valve is a 3-way valve and the second on/off valve is a 2-way valve.
In claim 1,
The sensor unit,
A PT sensor provided on a sixth passage adjacent to the compressor and a first passage adjacent to the indoor condenser to measure the pressure and temperature of the refrigerant moving into the sixth passage and the first passage,
A cooling and heating system for a vehicle including an outdoor temperature sensor provided adjacent to the outdoor condenser to measure the temperature of the outdoor air.
In claim 7,
In the cooling mode, the first on-off valve of the on-off valve unit provided at the rear end of the water-cooled condenser is opened in the direction of the outdoor condenser, and the second on-off valve of the on-off valve unit provided on the third branch flow path is closed,
The first electronic expansion valve of the expansion valve part provided on the second flow path is fully opened, and the solenoid expansion valve of the expansion valve part provided at the front of the evaporator on the fourth flow path is opened to allow the refrigerant supplied to the evaporator. A cooling and heating system for a vehicle, wherein the integrated expansion valve of the expansion valve unit, which is provided at a point where the second branch flow path branches on the bypass flow path, closes the discharge port and the discharge slit.
In claim 7,
In the heating mode and heating dehumidification mode, the first opening/closing valve of the on-off valve unit provided at the rear end of the water-cooled condenser is opened in the direction of the first branch passage connected to the fifth passage, and is provided on the third branch passage. The second on-off valve of the on-off valve part is opened, and the check valve provided on the fourth passage operates to prevent the refrigerant moved to the fourth passage through the second branch passage from flowing back toward the outdoor condenser. do,
The first electronic expansion valve of the expansion valve part provided on the second flow path opens to expand the refrigerant supplied to the water-cooled condenser, and the solenoid expansion valve of the expansion valve part provided in the front of the evaporator on the fourth flow path is Closed, the integrated expansion valve of the expansion valve unit provided at the point where the second branch flow path branches on the bypass flow path rotates the ball and gradually opens the discharge slit in the direction of the second branch flow path, thereby expanding the second branch flow path. Expands the refrigerant supplied to the branch flow path,
When the outdoor temperature measured by the outdoor temperature sensor of the sensor unit is 0 ℃ or less, the heating mode is switched, and when the outdoor temperature measured by the outdoor temperature sensor is 0 ℃ or more and 15 ℃ or lower, the heating mode is switched to the heating dehumidification mode. A cooling and heating system for vehicles.
In claim 7,
In the cooling battery cooperation mode, the first on-off valve of the on-off valve unit provided at the rear end of the water-cooled condenser is opened in the direction of the outdoor condenser, and the second on-off valve of the on-off valve unit provided on the third branch flow path is closed. And,
The first electronic expansion valve of the expansion valve part provided on the second flow path is fully opened, and the solenoid expansion valve of the expansion valve part provided at the front of the evaporator on the fourth flow path is opened to allow the refrigerant supplied to the evaporator. Inflated, the integrated expansion valve of the expansion valve unit provided at the point where the second branch flow path branches on the bypass flow path rotates the ball to gradually open the discharge slit in the direction of the battery chiller to the battery chiller. A vehicle cooling and heating system characterized by expanding the supplied refrigerant.

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