Cooling device for automotive air conditioning system

Abstract

The present invention discloses a cooling device for an automotive air-conditioning system, which includes a flow-dividing cavity and a flow-merging cavity. A plurality of pressure pipes are vertically connected between the flow-dividing cavity and the flow-merging cavity; a refrigerant inlet for refrigerant to flow in is provided on the flow-dividing cavity, and a refrigerant outlet for refrigerant to flow out is provided on the flow-merging cavity; heat exchange fins are arranged in the vertical direction between the pressure pipes; pressure control valves for controlling the opening and closing of the lower pipe orifice parts of the respective pressure pipes are respectively arranged at the bottoms of the plurality of pressure pipes, and the pressure values of the pressure control valves are set in grades; a flow-dividing device is further included, and the flow-dividing device can selectively open or close the pipelines of the corresponding pressure pipes according to the pressure of the refrigerant flowing into the flow-dividing cavity; the energy possessed by the pressure change of the air-conditioning system is recycled to increase the subcooling degree of the refrigerant, thereby improving the refrigeration effect of the air-conditioning system.

Description

Technical Field

[0001] The present invention belongs to the technical field of automotive air conditioning systems, and particularly relates to a cooling device for an automotive air conditioning system. Background Art

[0002] An automotive air conditioning system generally includes components such as a compressor, an evaporator, an expansion unit, and a condenser. Among them, the condenser is crucial in the refrigeration cycle of the automotive air conditioning system. The condenser exchanges heat with the surrounding environment to cool the high-temperature and high-pressure refrigerant vapor discharged by the compressor, causing it to condense into a high-pressure refrigerant liquid, providing a certain degree of subcooling for the liquid refrigerant, and then supplying it to the expansion valve and the evaporator to ultimately cool the air in the vehicle compartment.

[0003] The subcooled condenser is an improved and upgraded version of the condenser, a component of the vehicle air conditioner. It integrates the parallel-flow condenser and the liquid receiver dryer, eliminating the refrigerant pipe connecting the parallel-flow condenser and the liquid receiver dryer, with a compact structure; the high-pressure gaseous refrigerant is cooled to a high-pressure liquid in the condensation zones in the upper and middle parts of the condenser and then passes through the integrated liquid receiver dryer, and finally is further cooled in the subcooling zone in the lower part of the condenser to increase the subcooling degree, thereby improving the air conditioning performance and being widely used in current vehicle air conditioning systems. However, when the air conditioning system operates under conditions such as high temperature, idling, and traffic jams, the subcooling degree of the refrigerant obtained from the condenser is still not deep enough, which in turn affects the refrigeration effect of the entire air conditioning system. Therefore, how to increase the subcooling degree of the refrigerant has become a problem to be solved; in the prior art, generally, methods such as increasing the heat dissipation area of the condenser or increasing the air volume of the condenser fan are used to increase the subcooling degree of the refrigeration medium, thereby improving the refrigeration effect of the automotive air conditioner; increasing the heat dissipation area of the condenser will correspondingly increase the structural size of the condenser, resulting in a poor arrangement of the entire air conditioner in the front compartment of the vehicle; increasing the air volume of the condenser fan will increase power consumption and the noise of the condenser fan; obviously, such methods all have certain defects.

[0004] Therefore, it is necessary to consider other aspects to increase the subcooling degree of the refrigerant. To adapt to different working conditions, the compressor consumes different powers, and the pressure of the air conditioning system generally fluctuates between 22 bar and 10 bar. Different system pressures have different pressure potentials, and the corresponding liquid refrigerants have different saturation temperatures. The change in the air conditioning system pressure has a certain amount of energy, and this part of the energy has not been reasonably utilized in the current air conditioning system. Therefore, it can be considered to further cool the refrigerant by recovering and utilizing the pressure energy generated by the pressure change and the internal energy of the saturated refrigerant corresponding to different pressures in the air conditioning system to increase the subcooling degree of the refrigerant, thereby improving the refrigeration effect of the air conditioning system. Summary of the Invention

[0005] In view of this, the present invention provides a cooling device for an automotive air-conditioning system. By adopting a flow splitting device to control the flow direction of refrigerants with different pressures to different pressure pipes, the refrigerants in each stage of pressure pipes have different pressure potential energies and saturation temperatures. Heat exchange fins are arranged between the pressure pipes at each stage. During operation, the further cooling of the refrigerants is completed by utilizing the changing pressure potential energy of the system and the internal energy of the saturated refrigerants corresponding to different pressures.

[0006] To achieve the above object, the present invention provides the following technical solution: A cooling device for an automotive air-conditioning system includes a flow splitting cavity and a flow combining cavity. A plurality of pressure pipes are vertically connected between the flow splitting cavity and the flow combining cavity; A refrigerant inlet for the refrigerant to flow in is provided on the flow splitting cavity, and a refrigerant outlet for the refrigerant to flow out is provided on the flow combining cavity; Heat exchange fins are arranged in the vertical direction between the pressure pipes; At the bottoms of the plurality of pressure pipes, pressure control valves for controlling the opening and closing of the lower pipe orifice parts of their respective pressure pipes are respectively provided, and the pressure values of the pressure control valves are set in stages;

[0007] It further includes a flow splitting device, and the flow splitting device can selectively open or close the pipelines of the corresponding pressure pipes according to the pressure of the refrigerant flowing into the flow splitting cavity.

[0008] Furthermore, the cooling device can be arranged in the transition section between the condensation area and the subcooling area of the subcooled condenser of the air-conditioning system. The outflow end of the condensation area and the inflow end of the subcooling area are respectively connected to the refrigerant inlet and the refrigerant outlet. Of course, it can also be arranged at the refrigerant outflow end of the subcooled condenser (or non-subcooled condenser) of the air-conditioning system, or in a pipeline with pressure changes.

[0009] Furthermore, the flow splitting device includes a flow splitting valve plate, a rotating shaft and a driving motor; The flow splitting valve plate is arranged in the flow splitting cavity, the rotating shaft is fixedly connected to the upper end surface of the flow splitting valve plate, and its upper end penetrates and exposes the top of the flow splitting cavity. A driven gear is provided on a section of the rotating shaft exposed from the top of the flow splitting cavity, and a driving gear is provided at the output end of the driving motor. The driving gear is meshed with the driven gear; The flow splitting valve plate is provided with a flow splitting port for opening the pipeline of the pressure pipe, and the flow splitting valve plate drives the rotation through the driving motor to control the opening and closing of the pipelines of each pressure pipe;

[0010] During use, the driving motor drives the flow splitting valve plate to rotate by a certain angle according to the signal given by the original pressure sensor of the air-conditioning system to selectively open or close the pipelines of the multiple pressure pipes.

[0011] Furthermore, the flow splitting valve plate is a circular sheet structure, and the flow splitting ports are arranged in a fan-shaped opening shape with the center line of the flow splitting valve plate as the center.

[0012] Furthermore, the drive motor is a servo motor.

[0013] Furthermore, the plurality of pressure pipes are uniformly arranged at equal angular intervals in the circumferential direction.

[0014] Furthermore, the inner and outer diameters of the plurality of pressure pipes are the same respectively.

[0015] Furthermore, the heat exchange fins are rectangular fins, serrated fins or corrugated fins, and are arranged in a laminated structure along the vertical direction of the pressure pipes.

[0016] Furthermore, the flow dividing cavity is a tubular structure sealed at both the upper and lower ends.

[0017] Furthermore, the flow combining cavity is a funnel-shaped structure sealed at the top.

[0018] The present invention has at least one of the following beneficial effects:

[0019] 1. The cooling device for an automotive air conditioning system provided by the present invention controls the flow of refrigerants with different pressures to different pipes by using a flow dividing device. The refrigerants in each stage of pressure pipes have different pressure potentials and saturation temperatures. During operation, different pressures correspond to different saturation temperatures, so there is a temperature difference between the pressure pipes, enabling heat exchange between the pipes through the fins, recovering the latent heat and sensible heat of the corresponding refrigerants, effectively increasing the subcooling degree of the refrigerant, and thus improving the refrigeration effect of the air conditioning system.

[0020] 2. The cooling device for an automotive air conditioning system provided by the present invention can be arranged at the transition section between the condensation area and the subcooling area of a subcooled condenser in the air conditioning system, or at the refrigerant outlet end of a subcooled condenser (or a non-subcooled condenser) in the air conditioning system. It can be integrated on the existing automotive condenser, with a small overall structure occupying little space and having no impact on the layout of the existing air conditioning system.

[0021] Other advantages, objectives and features of the present invention will be described to some extent in the subsequent specification, and to some extent, will be obvious to those skilled in the art based on the study of the following text, or can be taught from the practice of the present invention. The objectives and other advantages of the present invention can be realized and obtained through the following specification. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 is a schematic structural diagram of the present invention

[0023] Figure 2 is an axonometric schematic diagram after the flow dividing valve plate and the rotating shaft are connected

[0024] Reference numerals: 1 - flow - dividing cavity, 2 - pressure pipe, 201 - low - pressure pipe, 202 - medium - pressure pipe, 203 - high - pressure pipe, 3 - flow - combining cavity, 4 - heat - exchange fins, 5 - pressure control valve, 6 - refrigerant inlet, 7 - refrigerant outlet, 8 - flow - dividing valve plate, 9 - rotating shaft, 10 - driven gear, 11 - driving motor, 12 - driving gear. Detailed implementation manners

[0025] The following uses specific examples to illustrate the implementation manners of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through other different specific implementation manners. Various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that the diagrams provided in the following embodiments are only used to illustrate the basic concept of the present invention. Without conflict, the following embodiments and the features in the embodiments can be combined with each other.

[0026] Among them, the drawings are only for illustrative purposes, showing only schematic diagrams, not physical diagrams, and should not be construed as a limitation to the present invention; in order to better illustrate the embodiments of the present invention, some components in the drawings will be omitted, enlarged or reduced, which does not represent the size of the actual product; for those skilled in the art, it is understandable that some well - known structures and their descriptions in the drawings may be omitted.

[0027] Please refer to Figure 1-2, A cooling device for an automotive air-conditioning system, comprising a shunt cavity 1 and a confluence cavity 3. A number of pressure pipes 2 are vertically connected between the shunt cavity 1 and the confluence cavity 3. A refrigerant inlet 6 for refrigerant inflow is provided on the shunt cavity 1. The inlet has a tubular structure. Here, both the shunt cavity 1 and the confluence cavity 3 are vertically arranged, and the refrigerant inlet 6 is provided at the upper end of the shunt cavity 1. A refrigerant outlet 7 for refrigerant outflow is provided on the confluence cavity 3. The outlet has a tubular structure, and the refrigerant outlet 7 is provided at the lower end of the confluence cavity 3. Heat exchange fins 4 are arranged in the vertical direction between the pressure pipes 2. Pressure control valves 5 for controlling the opening and closing of the lower pipe orifices of their respective pressure pipes are respectively provided at the bottoms of the pressure pipes 2. Here, the pressure control valve 5 can be a spring valve, including a valve plate covering the bottom of the pressure pipe. The valve plate is connected to the outer wall of the pressure pipe through a torsion spring. The elastic modulus of the torsion spring is selected according to the pressure grade. Of course, a tubular overflow valve can also be used. These are all prior arts and will not be elaborated here. The pressure values of the pressure control valves are set in grades, and the pressure values of each pipe can be set according to the following principle: the gravity of the refrigerant in the semi-liquid state < the valve opening pressure value < the gravity of the refrigerant in the full-liquid state, less than the pressure value at which all the refrigerant in the semi-liquid state evaporates. It can be known that the pressure loss in the entire pipeline is not large, and the original pressure values of the system before and after each pipeline valve are relatively balanced. Therefore, it is feasible to calculate and set the valve opening pressure value based on gravity here;

[0028] It further includes a shunt device. The shunt device can selectively open or close the pipelines of the corresponding pressure pipes 2 according to the pressure of the refrigerant flowing into the shunt cavity 1. During use, the cooling device can be arranged in the transition section between the condensation area and the subcooling area of the subcooled condenser in the air-conditioning system. The outflow end of the condensation area and the inflow end of the subcooling area are respectively connected to the refrigerant inlet 6 and the refrigerant outlet 7, which can be connected through pipelines. Of course, it can also be arranged at the refrigerant outflow end of the subcooled condenser or non-subcooled condenser in the air-conditioning system, as long as it is in a pipeline with pressure changes;

[0029] By using the shunt device to control the flow of refrigerants with different pressures to different pipelines, the refrigerants in each pressure pipe 2 have different pressure potential energies and saturation temperatures. During operation, the refrigerants in each pressure pipe 2 can exchange heat with each other through the heat exchange fins 4. Through the corresponding cooling between the pipes, the pressure energy generated by the pressure change and the internal energy of the saturated refrigerant corresponding to different pressures in the air-conditioning system are reasonably recovered and utilized, which can effectively increase the subcooling degree of the refrigerant and thus improve the refrigeration effect of the air-conditioning system.

[0030] In this embodiment, the cooling device can be arranged at the transition section between the condensation area and the subcooling area of the subcooled condenser in the air-conditioning system. The outflow end of the condensation area and the inflow end of the subcooling area are respectively connected to the refrigerant inlet 6 and the refrigerant outlet 7, such as by pipeline connection. Of course, it can also be arranged at the refrigerant outflow end of the subcooled condenser (or non-subcooled condenser) in the air-conditioning system. The refrigerant inlet 6 is connected to the refrigerant outflow end of the subcooled condenser (or non-subcooled condenser) in the air-conditioning system through a pipeline, and the refrigerant inlet 6 is connected to the subsequent air-conditioning pipeline. The subcooled condenser and the non-subcooled condenser here are prior arts and will not be elaborated here. During installation, it can be integrated on the existing automotive condenser, such as beside the liquid storage and dryer of the subcooled condenser. The overall structure occupies little space and will not affect the layout of the existing air-conditioning system.

[0031] In this embodiment, the flow dividing device includes a flow dividing valve plate 8, a rotating shaft 9 and a driving motor 11. The flow dividing valve plate 8 is arranged in the flow dividing cavity 1, here at the bottom inside the flow dividing cavity 1, and covers the upper pipe orifice parts of each pressure pipe 2 to achieve the blocking of the pipelines of each pressure pipe 2. The rotating shaft 9 is fixedly connected to the upper end surface of the flow dividing valve plate 8, or it can be an integral structure. Its upper end penetrates and exposes the top of the flow dividing cavity 1. A driven gear 10 is provided on a section of the rotating shaft 9 that exposes the top of the flow dividing cavity 1. The output end of the driving motor 11 is provided with a driving gear 12, and the driving gear 12 is meshed and connected with the driven gear 11. The flow dividing valve plate 8 is provided with a flow dividing opening for opening the pipeline of the pressure pipe 2. The flow dividing opening ensures that only one pressure pipe orifice is opened at a specific moment. The flow dividing valve plate 8 is driven to rotate by the driving motor 11 to control the opening and closing of the pipelines of each pressure pipe 2. During use, the driving motor 11 drives the flow dividing valve plate 8 to rotate at a fixed angle according to the signal given by the original pressure sensor in the air-conditioning system to achieve the selective opening or closing of the pipelines of the multiple pressure pipes 2. The structure of this flow dividing device is simple to control and occupies little space.

[0032] In this embodiment, the flow dividing valve plate 8 is a circular sheet-like structure, and the flow dividing opening is arranged in a fan-shaped opening shape with the center line of the flow dividing valve plate as the center. It is convenient to process and has a simple structure. Of course, it can also be a circular opening, etc.

[0033] In this embodiment, the driving motor 11 is a servo motor. Here, a micro servo motor is used, which has a small volume and precise angle rotation control.

[0034] In this embodiment, the several pressure pipes 2 are evenly arranged at equal angular intervals along the circumferential direction, and the structure is simple.

[0035] In this embodiment, the inner and outer diameters of the multiple pressure pipes 2 are the same respectively, which is convenient for arrangement and convenient for the flow dividing opening on the flow dividing valve plate 8 to achieve the opening and closing control of each pressure pipe 2, etc.

[0036] In this embodiment, the heat exchange fins 4 are rectangular fins, serrated fins or corrugated fins, and are arranged in a laminated structure along the vertical direction of the pressure pipe 2 to ensure the heat dissipation effect.

[0037] In this embodiment, the flow dividing cavity 1 is a tubular structure with closed upper and lower ends, which can be cylindrical or square tubular, etc. It has a simple structure and occupies a small space.

[0038] In this embodiment, the flow combining cavity 3 is a funnel-shaped structure with a closed top, which is convenient for liquid flow. Of course, it can also be a columnar structure or the like.

[0039] Now, taking the case where the device is arranged in the transition section between the condensation area and the subcooling area of a subcooled condenser, and when there are three pressure pipes 2 and a spring valve is used, and the system pressure change range is 8 - 22 bar as an example, the implementation principle of the present invention is described as follows:

[0040] Here, the multi-stage pressure pipes are divided into a low-pressure pipe 201, a medium-pressure pipe 202, and a high-pressure pipe 203. The inflow pressure value ranges of each pipe can be set as follows: the pressure of the low-pressure pipe is 8 bar - 13 bar, the pressure of the medium-pressure pipe is 13 bar - 18 bar, and the pressure of the high-pressure pipe is 18 bar - 22 bar; the pressure value of the spring valve is adaptively selected according to the gravity of the refrigerant in the semi-liquid state < the valve opening pressure value < the gravity of the refrigerant in the full-liquid state, and the pressure value of the semi-liquid state when all the refrigerant in the semi-liquid state evaporates. The semi-liquid state refers to the state when half of the liquid refrigerant is stored in the pipe, and the full-liquid state refers to the state when the pipe is filled with liquid refrigerant. Here, the gravity can be calculated according to the density and volume. The elastic force value of the spring valve is calculated by the spring elastic modulus. The calculation methods here are all well-known prior arts and will not be elaborated here; the pressure sensor of the original air-conditioning system is used to measure the pressure of the refrigerant flowing into the flow dividing cavity 1. For different ranges of system pressure, the servo motor 11 has different rotation angles, and the servo motor 11 drives the flow dividing valve plate 8 to rotate, so that the pipes with different pressure values are opened or closed; corresponding spring valves are also provided at the bottoms of different pressure pipes 2, and the opening and closing of the corresponding spring valves are controlled by the pressure of the refrigerant liquid retained in the pressure pipe 2 and the gravity of the refrigerant liquid itself.

[0041] When the system is at low pressure, the flow dividing valve plate 8 opens the low-pressure pipe 201. The low-pressure refrigerant enters the low-pressure pipe 201 from the condensation section of the condenser. When the gravity of the refrigerant liquid itself in the pipe exceeds the set value of the corresponding spring valve, the low-pressure refrigerant pipe is unblocked, and the refrigerant enters the subcooling section of the condenser for subcooling.

[0042] When the system pressure rises, the flow dividing valve plate 8 rotates, gradually closing the low-pressure pipe 201. However, there is still some low-pressure and low-temperature refrigerant remaining in it. After the medium-pressure pipe 202 is opened, the refrigerant passes through the medium-pressure pipe 202, and the saturated pressure and saturated temperature of the refrigerant in the medium-pressure pipe 202 are relatively high. At this time, the low-pressure and low-temperature refrigerant remaining in the low-pressure pipe 201 can cool the medium-pressure refrigerant through the fins 4 between the pressure pipes 2, further reducing the temperature of the refrigerant in the medium-pressure pipe 202, reducing the load of the subcooling section of the condenser, and at the same time recovering the cold energy in the low-pressure pipe 201. Meanwhile, the low-pressure and low-temperature refrigerant in the low-pressure pipe 201 expands due to heat. When the pressure inside the pipe is greater than the set pressure value of the bottom spring valve, the bottom valve opens, and the refrigerant in the gas-liquid mixed state has the same temperature as the refrigerant flowing out of the medium-pressure pipe (after heat exchange, thermal equilibrium is reached in the medium- and low-pressure pipes). After the two are mixed, they enter the subcooling section of the condenser for subcooling. At this time, the refrigerant flow rate of the system does not change either. At the same time, it is a dynamic process inside the low-pressure pipe 201. When the pressure inside the pipe (the gravity of the refrigerant and the pressure potential energy of thermal expansion) is less than the valve set value, the valve closes, and some refrigerant remains in the pipe, reducing the refrigerant flow rate of the system and also being able to reduce the system pressure;

[0043] When the system pressure continues to rise, the stroke of the flow dividing valve plate 8 increases, the high-pressure pipe 203 opens, the refrigerant enters the high-pressure pipe 203, and the refrigerant in the medium-pressure pipe 201 and the low-pressure pipe 202 will also cool the high-pressure pipe through the fins 4;

[0044] When the system pressure decreases, the stroke of the flow dividing valve plate 8 decreases, the high-pressure pipe 203 closes, and the medium-pressure pipe 202 opens. At this time, the pressure and temperature of the refrigerant remaining in the high-pressure pipe 203 are relatively high. At this time, the gravity of the refrigerant in the high-pressure pipe plus the pressure potential energy is still greater than the set value of the corresponding spring valve at the bottom, and the bottom valve is still open. The high-pressure refrigerant leaks, the pressure decreases, and at this time, the saturated high-pressure refrigerant will undergo a phase change and absorb heat, releasing its latent heat, and then further reducing the temperature of the medium-pressure pipe through the fins 4. After leakage, the high-pressure refrigerant reaches the medium pressure and mixes with the refrigerant flowing out of the medium-pressure pipe 202 and enters the subcooling section of the condenser for subcooling. In this process, the latent heat of the high-pressure refrigerant is much greater than the sensible heat, so the overall temperature will also decrease;

[0045] As the system pressure continuously changes, the multi-stage pressure pipes 2 open and close according to the established logic, recovering the system pressure potential energy and the internal energy of the saturated refrigerant corresponding to different pressures for refrigerant cooling.

[0046] This cooling device has good beneficial effects, which can be reflected through the following calculations:

[0047] Assume,

[0048] Refrigerant in the high-pressure pipe: Pressure 20 bar, temperature 68 °C, enthalpy of liquid 300 kj / kg, enthalpy of gas 428 kj / kg, specific heat at constant pressure of liquid 1.7691 kj / kg.°C, specific heat at constant pressure of gas 1.5518 kj / kg.°C, liquid density 1008 kg / m3;

[0049] Refrigerant in the medium-pressure pipe: 15 bar, temperature 55 °C, enthalpy of liquid 279 kj / kg, enthalpy of gas 425 kj / kg, specific heat at constant pressure of liquid 1.6089 kj / kg.°C, specific heat at constant pressure of gas 1.3099 kj / kg.°C, liquid density 1078.3 kg / m3;

[0050] Refrigerant in the low-pressure pipe: 10 bar, temperature 39 °C, enthalpy of liquid 254 kj / kg, enthalpy of gas 418 kj / kg, specific heat at constant pressure of liquid 1.4926 kj / kg.°C, specific heat at constant pressure of gas 1.1358 kj / kg.°C, liquid density 1150.9 kg / m3;

[0051] Assume the set volume of a single pressure pipe: A cylindrical pipe with a height of 22 cm and a diameter of 2 cm:

[0052] The mass of the remaining high-pressure refrigerant is 0.0696 kg, the mass of the medium-pressure refrigerant is 0.074 kg, the mass of the remaining low-pressure refrigerant is 0.0795 kg, and the fin heat transfer efficiency is set to 0.8;

[0053] Therefore, the heat transfer Q between high and medium pressures: (300 - 279) * 0.074 = 1.554 kj, which reduces the temperature of the high-pressure liquid refrigerant of the same volume by 0.8 * 1.554 / (1.7691 * 0.0696) = 10 °C, with significant benefits;

[0054] The heat transfer Q between medium and low pressures: (279 - 254) * 0.0795 = 1.9875 kj, which reduces the temperature of the medium-pressure liquid refrigerant of the same volume by 0.8 * 1.9875 / (1.6089 * 0.074) = 13.3 °C, with significant benefits.

[0055] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit them. Although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the technical solutions of the present invention can be modified or equivalently replaced without departing from the purpose and scope of the technical solutions of the present invention, and they should all be covered by the scope of the claims of the present invention.

Claims

1. A cooling device for an automotive air conditioning system, characterized in that: It includes a shunt cavity and a confluence cavity, and a number of pressure pipes are vertically connected between the shunt cavity and the confluence cavity; a refrigerant inlet for refrigerant inflow is provided on the shunt cavity, and a refrigerant outlet for refrigerant outflow is provided on the confluence cavity; heat exchange fins are arranged in the vertical direction between the pressure pipes; at the bottoms of the pressure pipes, pressure control valves for controlling the opening and closing of the lower pipe orifices of the respective pressure pipes are provided, and the pressure values of the pressure control valves are set in grades; It further includes a shunt device, and the shunt device can selectively open or close the pipelines of the corresponding pressure pipes according to the pressure of the refrigerant flowing into the shunt cavity; The cooling device is arranged in the transition section between the condensation area and the subcooling area of the subcooled condenser of the air conditioning system; or arranged at the refrigerant outlet end of the subcooled condenser of the air conditioning system; The shunt device includes a shunt valve plate, a rotating shaft and a driving motor; the shunt valve plate is arranged in the shunt cavity, the rotating shaft is fixedly connected to the upper end surface of the shunt valve plate, and its upper end penetrates and exposes the top of the shunt cavity. A driven gear is provided on a section of the rotating shaft exposed above the top of the shunt cavity, and a driving gear is provided at the output end of the driving motor. The driving gear is meshed with the driven gear; a shunt port for opening the pipeline of the pressure pipe is provided on the shunt valve plate, and the shunt valve plate drives the rotation through the driving motor to control the opening and closing of the pipelines of the pressure pipes.

2. The cooling device for an automotive air conditioning system according to claim 1, characterized in that: The shunt valve plate is a circular sheet structure, and the shunt ports are arranged in a fan-shaped opening shape with the center line of the shunt valve plate as the center.

3. The cooling device for an automotive air conditioning system according to claim 1, characterized in that: The driving motor is a servo motor.

4. The cooling device for an automotive air conditioning system according to claim 1, characterized in that: The pressure pipes are evenly arranged at equal angles along the circumferential direction.

5. The cooling device for an automotive air conditioning system according to claim 1, characterized in that: The inner and outer diameters of the pressure pipes are the same respectively.

6. The cooling device for an automotive air conditioning system according to claim 1, characterized in that: The heat exchange fins are rectangular fins, serrated fins or corrugated fins, and are arranged in a laminated structure along the vertical direction of the pressure pipes.

7. The cooling device for an automotive air conditioning system according to claim 1, characterized in that: The shunt cavity is a tubular structure with upper and lower ends sealed.

8. The cooling device for an automotive air conditioning system according to claim 1, characterized in that: The confluence cavity is a funnel-shaped structure with the top sealed.

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