Thermal management module and vehicle
By setting adjacent first and second flow paths in the manifold of the heat management module, heat exchange between high-pressure refrigerant and low-pressure refrigerant is achieved, solving the problem of increasing costs by setting up heat exchanger components separately, increasing the overheating of the refrigerant at the suction end of the compressor and reducing system costs.
Patent Information
- Application Number
- CN202420421122.7
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-03-05
- Publication Date
- 2025-06-10
- Estimated Expiration
- 2034-03-05
AI Technical Summary
In the vehicle thermal management system, the separate heat exchanger component is provided to increase the cost of the thermal management module, and it is difficult to achieve effective heat exchange between the high-pressure refrigerant and the low-pressure refrigerant to increase the overheating of the refrigerant at the suction end of the compressor.
By providing the first and second runners in the manifold of the heat management module, at least partially adjacent, to achieve heat exchange between the high-pressure refrigerant and the low-pressure refrigerant, the increase in the cost of setting up the heat exchanger components alone is avoided.
The heat exchange between high-pressure refrigerant and low-pressure refrigerant is realized, the overheating of the refrigerant at the suction end of the compressor is improved, the cost of the thermal management module is reduced, and the overall performance of the system is improved.
Smart Images
Figure CN222964159U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to a thermal management module and a vehicle, and more particularly, to a thermal management module with a relatively low cost. Background Art
[0002] In a refrigeration cycle, in order to increase the superheat degree of the refrigerant at the suction end of the compressor, an internal heat exchanger is usually configured in the vehicle thermal management system. The high-pressure refrigerant at the exhaust end of the compressor and the low-pressure refrigerant at the suction end of the compressor exchange heat through the internal heat exchanger to increase the superheat degree of the refrigerant at the suction end of the compressor, thereby improving the performance of the thermal management system. However, the separate setting of the heat exchanger component also increases the cost of the thermal management module.
[0003] Therefore, it is desirable to propose a thermal management module that can not only achieve the heat exchange between the high-pressure refrigerant and the low-pressure refrigerant to increase the superheat degree of the refrigerant at the suction end of the compressor, but also avoid the cost increase caused by the separate setting of the heat exchanger component. Summary of the Utility Model
[0004] According to a first aspect of the present utility model, a thermal management module is proposed, which includes a manifold having a plate-shaped main body and a first flow channel and a second flow channel provided on the plate-shaped main body; a thermal management element provided on the manifold and communicating with the first flow channel and / or the second flow channel; wherein, the first flow channel and the second flow channel are arranged to be at least partially adjacent so that the fluid in the first flow channel and the fluid in the second flow channel can exchange heat.
[0005] According to this solution, through the adjacent arrangement of the first flow channel and the second flow channel, the fluids in the first flow channel and the second flow channel can exchange heat while flowing between the thermal management elements, without having to exchange heat through a specially provided heat exchange component, reducing the cost increase caused by the setting of the heat exchange component.
[0006] In some solutions, the projections of the first flow channel and the second flow channel along the thickness direction of the plate-shaped main body may at least partially overlap.
[0007] In some solutions, the projections of the first flow channel and the second flow channel along the thickness direction of the plate-shaped main body may completely overlap.
[0008] In some solutions, the plate-shaped main body may include a first plate, a second plate, and a third plate arranged in sequence along its thickness direction. The first plate and the second plate cooperate to form the second flow channel, and the second plate and the third plate cooperate to form the first flow channel.
[0009] In some solutions, the projections of the first flow channel and the second flow channel in the direction perpendicular to the thickness direction of the plate-shaped main body may at least partially overlap.
[0010] In some solutions, the projections of the first flow channel and the second flow channel in a direction perpendicular to the thickness direction of the plate-shaped body may completely coincide.
[0011] In some solutions, the plate-shaped body may include a groove and a cover plate, and the first flow channel and the second flow channel are formed by the cooperation of the groove and the cover plate.
[0012] In some solutions, the first flow channel may be a circuit for low-pressure refrigerant, and the second flow channel may be a circuit for high-pressure refrigerant.
[0013] In some solutions, the thermal management element may include at least one of a water-cooled condenser, a cooler, and a dryer bottle.
[0014] According to a second aspect of the present invention, a vehicle is provided, including the thermal management module according to the first aspect of the present invention. Description of the Drawings
[0015] Figure 1 Shows a framework diagram of the thermal management module according to an embodiment of the present invention;
[0016] Figure 2 Shows a schematic diagram of the thermal management module according to an embodiment of the present invention;
[0017] Figure 3 Shows a schematic diagram of the manifold according to the first embodiment of the present invention;
[0018] Figure 4 Shows a schematic diagram of the manifold according to the second embodiment of the present invention.
[0019] Reference Signs: 100 Thermal Management Module, 110 Manifold, 111 First Plate, 112 Second Plate, 113 Third Plate, 114 First Flow Channel, 116 Second Flow Channel, 120 Water-Cooled Condenser, 130 Dryer Bottle, 140 Cooler, 150 Bracket, 160 Compressor, 210 Manifold, 212 Plate-Shaped Body, 214 First Flow Channel, 216 Second Flow Channel. Detailed Description of the Embodiments
[0020] In order to make the objectives, solutions, and advantages of the technical solutions of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the drawings of the specific embodiments of the present invention. Unless otherwise specified, the terms used herein have the ordinary meanings in the art. The same reference signs in the drawings represent the same components.
[0021] Figure 1 and Figure 2The framework diagram and schematic diagram of the thermal management module 100 according to an embodiment of the present utility model are respectively shown. The thermal management module 100 mainly includes a manifold 110, a water-cooled condenser 120, a dryer bottle 130, a cooler 140, and a bracket 150. The manifold 110 is disposed on the bracket 150.
[0022] As Figure 1 shown, the high-temperature and high-pressure refrigerant discharged by the compressor 160 sequentially flows through the water-cooled condenser 120, the dryer bottle 130, the second flow channel 116 of the internal heat exchanger, an electronic expansion valve (not shown), the cooler 140, the first flow channel 114 of the internal heat exchanger, and returns to the compressor 160. Among them, the high-temperature and high-pressure refrigerant releases heat when flowing through the water-cooled condenser 120 and becomes a medium-temperature and high-pressure refrigerant. The dryer bottle 130 is used to store the refrigerant and achieve the gas-liquid separation of the refrigerant to discharge the liquid refrigerant. The refrigerant in the first flow channel 114 of the internal heat exchanger exchanges heat with the refrigerant in the second flow channel 116. The refrigerant is throttled and depressurized when flowing through the electronic expansion valve and evaporates and absorbs heat in the cooler 140. Through the above-mentioned heat cycle of the refrigerant in the flow channels (to be described in detail below) of the manifold 110, the thermal management function of the thermal management module 100 is realized. It should be understood that the water-cooled condenser 120, the dryer bottle 130, and the cooler 140 as thermal management elements are only examples. The present utility model is not intended to limit the specific types of thermal management elements, but includes any other suitable thermal management elements that achieve the thermal management function through the heat cycle between high-pressure refrigerant and low-pressure refrigerant.
[0023] To increase the superheat degree of the refrigerant at the suction end of the compressor 160, an internal heat exchanger is usually configured in the thermal management module 100. When the thermal management module 100 operates, the low-pressure refrigerant fluid at the suction end of the compressor 160 and the high-pressure refrigerant fluid at the discharge end of the compressor 160 exchange heat in the internal heat exchanger, increasing the superheat degree of the refrigerant at the suction end of the compressor 160 to improve the system performance. In the prior art, the heat exchange between the above-mentioned low-pressure refrigerant and high-pressure refrigerant is realized through a separate heat exchanger component. However, the separate heat exchanger component increases the cost of the thermal management module 100.
[0024] To avoid increasing the cost of the thermal management module 100 due to separate heat exchanger components while still enabling heat exchange between the high-pressure refrigerant and the low-pressure refrigerant, thereby increasing the superheat of the refrigerant at the suction end of the compressor 160, the first flow channels 114, 214 and the second flow channels 116, 216 in the manifold 110 of the thermal management module 100 of the present utility model are arranged to be at least partially adjacent so that the fluid in the first flow channels 114, 214 can exchange heat with the fluid in the second flow channels 116, 216. For convenience of description, in the following description herein, the low-pressure refrigerant flows through the first flow channels 114, 214, while the high-pressure refrigerant flows through the second flow channels 116, 216. It should be understood that the correspondence between the first (second) flow channels and the low (high)-pressure refrigerant is merely exemplary, and it is also possible to have the high-pressure refrigerant flow through the first flow channels 114, 214 and the low-pressure refrigerant flow through the second flow channels 116, 216.
[0025] Optionally, the internal heat exchange part has five openings (i.e., the high-pressure flow channel has one inlet and one outlet, and the low-pressure flow channel has two inlets and one outlet). Correspondingly, the corresponding heat exchange channels in the manifold 110 also form the feature of "five openings", that is, there are two low-pressure flow channels and one high-pressure flow channel, and each of the two low-pressure flow channels exchanges heat with the high-pressure flow channel. It should be understood that the present utility model is not intended to limit the number of the low-pressure flow channels and the high-pressure flow channels, but may include any number of low-pressure flow channels and high-pressure flow channels that can exchange heat with each other. Specifically, the first flow channel 114 is a low-pressure flow channel, and the second flow channel 116 is a high-pressure flow channel.
[0026] Optionally, as Figure 3As shown, the projections of the first flow channel 114 and the second flow channel 116 in the thickness direction of the plate-like main bodies 111, 112, 113 may at least partially overlap. Preferably, the projections of the first flow channel 114 and the second flow channel 116 in the thickness direction of the plate-like main bodies 111, 112, 113 may completely overlap. Specifically, the plate-like main bodies 111, 112, 113 may include a first plate 111, a second plate 112, and a third plate 113 arranged in sequence along their thickness direction. The first plate 111 and the second plate 112 cooperate to form the second flow channel 116, and the second plate 112 and the third plate 113 cooperate to form the first flow channel 114. For example, grooves are respectively formed on the first plate 111 and the third plate 113, the second plate 112 has a flat plate shape, the groove of the first plate 111 and the flat plate shape of the second plate 112 cooperate to form the second flow channel 116, and the groove of the third plate 113 and the flat plate shape of the second plate 112 cooperate to form the first flow channel 114. In this case, the second plate 112 can serve as the common pipe wall of the first flow channel 114 and the second flow channel 116, and the low-pressure refrigerant in the first flow channel 114 and the high-pressure refrigerant in the second flow channel 116 can perform heat exchange via the second plate 112. It should be understood that the present utility model is not intended to limit the specific cooperation form of the first plate 111 and the third plate 113 with the second plate 112 to form the flow channel, and the first plate 111 and the third plate 113 and the second plate 112 can also adopt any other suitable cooperation method to form the flow channel. For example, grooves for forming the flow channel can also be provided on the second plate 112.
[0027] Preferably, the first flow channel 114 and / or the second flow channel 116 can extend in a curved manner, such as extending in a U shape or an S shape or any other suitable shape, so as to increase the distance along which heat exchange can occur between the first flow channel 114 and the second flow channel 116, thereby increasing the heat exchange efficiency between the low-pressure refrigerant in the first flow channel 114 and the high-pressure refrigerant in the second flow channel 116, further increasing the superheat degree of the refrigerant at the suction end of the compressor 160, and further improving the performance of the thermal management module 100.
[0028] Preferably, the second flow channel 116 includes two parallel pipe segments to increase the contact area between the second flow channel 116 and the first plate 111, thereby improving the heat exchange capacity between the second flow channel 116 and the first flow channel 114. The number of parallel pipe segments can be set as required, not limited to two, for example, it can also be three, four, etc.; the parallel pipe segments can also be formed by setting the second flow channel 116 in a flat shape and arranging parallel partition plates inside the second flow channel 116; the first flow channel 114 can also adopt a similar structure to improve the heat exchange performance.
[0029] Optionally, as Figure 4As shown, the projections of the first flow channel 214 and the second flow channel 216 in a direction perpendicular to the thickness direction of the plate-like main body 212 (i.e., parallel to the extension direction of the manifold 210) can at least partially overlap. Preferably, the projections of the first flow channel 214 and the second flow channel 216 in a direction perpendicular to the thickness direction of the plate-like main body 212 can completely overlap. For example, the plate-like main body 212 can include a groove and a cover plate, and the first flow channel 214 and the second flow channel 216 are formed by the cooperation of the groove and the cover plate. In this way, the first flow channel 214 and the second flow channel 216 have a common wall perpendicular to the plate-like main body 212, so that while the low-pressure refrigerant and the high-pressure refrigerant circulate in the first flow channel 214 and the second flow channel 216, the low-pressure refrigerant can absorb heat from the high-pressure refrigerant to increase the superheat degree of the refrigerant at the suction end of the compressor 160, thereby improving the performance of the thermal management module 100.
[0030] Preferably, the thermal management module 100 is configured such that in a portion where the projections of the first flow channel 214 and the second flow channel 216 in a direction parallel to the extension direction of the manifold 210 overlap (i.e., a portion where the low-pressure refrigerant in the first flow channel 214 exchanges heat with the high-pressure refrigerant in the second flow channel 216), the flow direction of the low-pressure refrigerant in the first flow channel 214 is opposite to the flow direction of the high-pressure refrigerant in the second flow channel 216. This is beneficial to increasing the heat exchange efficiency between the low-pressure refrigerant in the first flow channel 214 and the high-pressure refrigerant in the second flow channel 216, further increasing the superheat degree of the refrigerant at the suction end of the compressor 160, so as to further improve the performance of the thermal management module 100.
[0031] The thermal management module 100 of the present utility model can be used in vehicles. Since the thermal management module 100 does not need to use a separate heat exchange component, the cost of the thermal management module is lower and the integration degree is higher, so that the cost of the vehicle using the thermal management module 100 is lower and the layout of the thermal management system is more flexible.
[0032] In this article, multiple exemplary embodiments of the present utility model have been described in detail with reference to preferred embodiments. However, those skilled in the art can understand that without departing from the concept of the present utility model, various modifications and changes can be made to the above specific embodiments, and various technical features and structures proposed by the present utility model can also be combined, without exceeding the protection scope of the present utility model. The protection scope of the present utility model is determined by the appended claims.
Claims
1. A thermal management module (100), characterized in that: include: A manifold (110, 210) having a plate-shaped body (111, 112, 113; 212) and a first flow channel (114, 214) and a second flow channel (116, 216) arranged on the plate-shaped body (212); A thermal management element (120, 130, 140) is disposed on the manifold (110, 210) and is in communication with the first flow channel (114, 214) and / or the second flow channel (116, 216); The first flow channel (114, 214) and the second flow channel (116, 216) are arranged to be at least partially adjacent to each other so that the fluid in the first flow channel (114, 214) and the fluid in the second flow channel (116, 216) can perform heat exchange.
2. The thermal management module (100) according to claim 1, characterized in that: Projections of the first flow channel (114) and the second flow channel (116) along the thickness direction of the plate-like body (111, 112, 113) at least partially overlap.
3. The thermal management module (100) according to claim 2, characterized in that: The projections of the first flow channel (114) and the second flow channel (116) along the thickness direction of the plate-like body (111, 112, 113) completely overlap.
4. The thermal management module (100) according to claim 2, characterized in that: The plate-like body (111, 112, 113) comprises a first plate, a second plate and a third plate which are sequentially arranged along the thickness direction thereof; the first plate cooperates with the second plate to form the second flow channel (116); the second plate cooperates with the third plate to form the first flow channel (114).
5. The thermal management module (100) according to claim 1, characterized in that: Projections of the first flow channel (214) and the second flow channel (216) in a direction perpendicular to the thickness direction of the plate-like body (212) at least partially overlap.
6. The thermal management module (100) according to claim 4, characterized in that: Projections of the first flow channel (214) and the second flow channel (216) in a direction perpendicular to the thickness direction of the plate-like body (212) completely overlap.
7. The thermal management module (100) according to claim 5 or 6, characterized in that: The plate-shaped body (212) comprises a groove and a cover plate, and the first flow channel (214) and the second flow channel (216) are formed by the cooperation of the groove and the cover plate.
8. The thermal management module (100) according to claim 1, characterized in that: The first flow passage (114, 214) is a circuit for low-pressure refrigerant, and the second flow passage (116, 216) is a circuit for high-pressure refrigerant.
9. The thermal management module (100) according to claim 1, characterized in that: The thermal management element (120, 130, 140) includes at least one of a water-cooled condenser, a drying bottle, and a cooler.
10. A vehicle, characterized in that: It comprises a thermal management module (100) according to any one of claims 1 to 9.