An internally cooled integrated thermal management compressor
Patent Information
- Application Number
- CN202522525652.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-11-28
- Publication Date
- 2026-09-29
- Estimated Expiration
- 2035-11-28
AI Technical Summary
[0005]然而，现有集成式热管理系统及配套压缩机仍存在诸多技术缺陷：其一，普通集成系统缺乏高效制热辅助结构，在低温环境下制热量显著不足，且压缩机排气温度过高，影响系统在极端低温工况下的稳定运行；其二，压缩机工作时，功率模块会产生大量热量，这些热量需通过低压盖向内部传递散热，但现有结构的内部散热面均为平面设计，散热面积小、导热能力弱，在环境温度较高、压缩机转速较低、压缩比大或吸气过热度较高等严苛工况下，极易因温升过高导致压缩机无法持续工作
[0015]本实用新型的有益效果在于：这种集成热管理压缩机能构建高效冷媒循环散热回路，扩大换热面积、强化散热，适配各种严苛工况，有效保障压缩机稳定运行。
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Figure CN224813930U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to vehicle thermal management technology, and in particular to an integrated thermal management compressor with internal cooling. Background Technology
[0002] With the rapid development of the new energy vehicle industry, the demand for vehicle thermal management has evolved from simple refrigeration to diversified and complex needs, covering scenarios such as refrigeration, heating, battery thermal management, small-scale refrigeration, and simultaneous refrigeration and heating of multiple units. The structure and function of traditional distributed air conditioning systems are no longer able to match the above-mentioned complex usage needs and cannot meet the stringent requirements of vehicles for thermal management efficiency.
[0003] At the same time, air conditioning system refrigerants are facing updates and iterations. The traditionally used R134a refrigerant has been included in the phase-out schedules of various countries. R290 refrigerant, which has flammable and explosive properties, has gradually become the mainstream choice in the industry due to its environmental advantages. However, the structural design of traditional distributed air conditioning systems cannot guarantee the safety of using R290 refrigerant. This situation has further promoted the widespread application of integrated thermal management systems in new energy vehicles.
[0004] Currently, integrated thermal management systems generally adopt a secondary heat exchange method between the refrigerant system and the external water system to achieve thermal management objectives. The main components are the compressor, condenser, expansion valve, and evaporator, which are integrated and installed on the same base plate. Typically, LCC plate heat exchangers are selected as condensers and chiiller plate heat exchangers as evaporators. Cold and heat sources are supplied to external heat units through the water side. The external heat units switch between cold and heat sources according to the control strategy to achieve thermal management objectives.
[0005] However, existing integrated thermal management systems and their associated compressors still have many technical defects: First, ordinary integrated systems lack efficient heating auxiliary structures, resulting in significantly insufficient heating capacity in low-temperature environments, and excessively high compressor discharge temperatures, affecting the stable operation of the system under extreme low-temperature conditions; Second, when the compressor is working, the power module generates a large amount of heat, which needs to be transferred to the interior through the low-pressure cover for heat dissipation. However, the internal heat dissipation surfaces of existing structures are all planar designs, with small heat dissipation area and weak thermal conductivity. Under harsh conditions such as high ambient temperature, low compressor speed, high compression ratio, or high suction superheat, the compressor is prone to failure to operate continuously due to excessive temperature rise. Utility Model Content
[0006] The technical problem to be solved by this utility model is to provide an integrated thermal management compressor with internal cooling. This integrated thermal management compressor can build an efficient refrigerant circulation heat dissipation circuit, expand the heat exchange area, enhance heat dissipation, adapt to various harsh working conditions, and effectively ensure the stable operation of the compressor.
[0007] To solve the above technical problems, the following technical solution is adopted: An integrated thermal management compressor with internal cooling includes an electrical cover, a low-pressure cover, a housing, a frame, a pump body, and a high-pressure cover connected sequentially from front to back. The housing has an intake port communicating with the interior on its outer side wall, and the high-pressure cover has an exhaust port communicating with the interior on its outer side wall. A drive shaft, a stator, and a rotor are disposed within the housing. The drive shaft passes axially through the housing and is rotatably mounted on the low-pressure cover via bearings. The stator is fixedly mounted on the inner wall of the housing, and the rotor is mounted on the drive shaft and corresponds to the position of the stator. The low-pressure cover has a first groove in the middle of its rear side wall, and the drive shaft is mounted at the rear of the first groove. The drive shaft has an axial hole that passes through it axially, and a radial hole that passes through it at its front end. The axial hole, the radial hole, and the first groove are connected and form a cooling circulation space. The rear side wall of the low-pressure cover has multiple heat dissipation fins.
[0008] Typically, power modules in thermal management systems achieve heat conduction by making close contact with the outer end face of the low-pressure cover using thermally conductive silicone grease. In the aforementioned integrated thermal management compressor, when the rotor drives the drive shaft to rotate, the radial holes generate negative pressure due to centrifugal force. This pressure actively guides the mixture of low-temperature refrigerant and refrigeration oil entering from the suction port, allowing it to seep into the first groove between the inner and outer rings of the bearing. As it flows through the heat dissipation fins, it fully absorbs the heat transferred from the power module through the low-pressure cover and is then discharged through the axial and radial holes. Because the first groove provides a cavity for the accumulation and flow of the low-temperature mixture, and together with the axial and radial holes of the drive shaft, it forms a cooling circulation space, enabling the low-temperature mixture to achieve efficient heat dissipation through efficient circulation within this space. Secondly, the rear wall of the low-pressure cover is equipped with multiple heat dissipation fins, which can significantly increase the heat dissipation area compared with the traditional planar heat dissipation structure. This allows the low-temperature mixture to more fully absorb the heat transferred from the power module through the low-pressure cover when it flows through the heat dissipation fins, quickly reducing the IGBT temperature. This effectively solves the problem of excessive temperature rise of the compressor under high temperature environment, low speed, high compression ratio or high suction superheat conditions, widens the operating temperature range, and ensures the stable operation of the compressor and integrated thermal management system.
[0009] In the aforementioned front-to-back direction, the direction of the compressor's intake and exhaust is used to determine the direction, with the intake position being front and the exhaust position being back.
[0010] In a preferred embodiment, each of the heat dissipation fins extends from front to back along the axial direction of the housing. The axially extending heat dissipation fins can be perpendicular to the flow direction of the cryogenic mixture, thereby disturbing the flow of the cryogenic mixture as much as possible and further enhancing the heat dissipation capacity.
[0011] In the preferred embodiment, each of the heat dissipation fins includes multiple first heat dissipation fins and multiple second heat dissipation fins. Each first heat dissipation fin is circumferentially arranged around the front end of the drive shaft, and each second heat dissipation fin is disposed in the first groove. The first and second heat dissipation fins can achieve full coverage of the heat dissipation area. The first heat dissipation fins, circumferentially arranged around the front end of the drive shaft, can directly cool the bearing and the high-temperature area around the drive shaft. The second heat dissipation fins, disposed in the first groove, can directly contact the low-temperature mixture accumulated in the second groove, enhancing local heat exchange. The two sets of heat dissipation fins work together to further improve the heat dissipation area and heat exchange uniformity, avoid local heat accumulation, and significantly widen the compressor's operating temperature range.
[0012] In a preferred embodiment, a counterweight is fixedly mounted on the front end face of the rotor. The counterweight can balance the inertial force when the rotor rotates, reduce the vibration of the drive shaft, and improve the operating stability and service life of the compressor; at the same time, the counterweight rotates at high speed with the rotor, which can aggravate the airflow disturbance of the low-temperature mixture, accelerate the speed of fluid flowing through the heat dissipation fins, and enhance the convective heat transfer effect.
[0013] In a further preferred embodiment, the cross-section of the counterweight is a fan-shaped ring with a central angle of 180°. The 180° fan-shaped ring structure can adapt to the installation space at the front end of the rotor, and its arc-shaped air-facing surface conforms to the characteristics of airflow dynamics. When rotating, it can generate a stronger airflow pushing force, expand the disturbance range, and allow the low-temperature mixture to more fully scour the heat dissipation fins, thereby improving the overall heat exchange efficiency.
[0014] In a further preferred embodiment, a second groove is formed on the outer front side of the counterweight at the middle position. The second groove increases the surface area of the counterweight, expanding the contact area with the cryogenic mixture. With the direction of rotation, the wall of the second groove and the side wall of the counterweight can jointly contact the cryogenic mixture head-on, increasing the airflow speed and creating turbulence as the cryogenic mixture flows through. This allows the high-speed airflow to quickly exchange heat with the heat dissipation fins, significantly improving heat exchange efficiency and enabling the IGBT to cool down rapidly.
[0015] The beneficial effects of this utility model are as follows: This integrated thermal management compressor can construct an efficient refrigerant circulation heat dissipation circuit, expand the heat exchange area, enhance heat dissipation, adapt to various harsh working conditions, and effectively ensure the stable operation of the compressor. Attached Figure Description
[0016] Figure 1 This is a partial cross-sectional view of the integrated thermal management compressor in an embodiment of this utility model; Figure 2 for Figure 1 A magnified view of position A in the middle; Figure 3 This is a side view of the drive shaft, rotor, and counterweight in an embodiment of the present invention. Detailed Implementation
[0017] The present invention will be further described below with reference to the accompanying drawings and specific embodiments: like Figure 1-3 The illustrated integrated thermal management compressor with internal cooling includes, from front to back, an electrical cover 1, a low-pressure cover 2, a housing 3, a frame 4, a pump body 5, and a high-pressure cover 6. The housing 3 has an intake port 301 communicating with the interior on its outer side wall, and the high-pressure cover 6 has an exhaust port 601 communicating with the interior on its outer side wall. The housing 3 houses a drive shaft 7, a rotor 8, and a stator 9. The drive shaft 7 is axially inserted into the housing 3 and is rotatably mounted on the low-pressure cover 2 via bearings. The stator 9 is fixedly mounted on the housing. On the inner wall of 3, the rotor 8 is mounted on the drive shaft 7 and corresponds to the position of the stator 9; a first groove 201 is opened in the middle of the rear side wall of the low-pressure cover 2, and the drive shaft 7 is installed at the rear of the first groove 201; an axial hole 701 is opened on the drive shaft 7, and a radial hole 702 is opened at the front end of the drive shaft 7; the axial hole 701, the radial hole 702 and the first groove 201 are connected and form a cooling circulation space; a plurality of heat dissipation fins 10 are provided on the rear side wall of the low-pressure cover 2.
[0018] Typically, in a thermal management system, the power module is in close contact with the outer end face of the low-pressure cover 2 via thermally conductive silicone grease to achieve heat conduction. In the aforementioned integrated thermal management compressor, when the rotor 8 drives the drive shaft 7 to rotate, the radial hole 702 generates negative pressure due to centrifugal force. This pressure actively guides the low-temperature refrigerant and refrigeration oil mixture entering from the suction port 301 to seep into the first groove 201 between the inner and outer rings of the bearing. As it flows through the heat dissipation fins 10, it fully absorbs the heat transferred from the power module through the low-pressure cover 2, and then discharges through the axial hole 701 and radial hole 702 (flow direction as shown). Figure 2 (As indicated by the arrow) Because the first groove 201 provides a cavity for the accumulation and flow of the cryogenic mixture, and together with the axial hole 701 and radial hole 702 of the drive shaft 7, it forms a cooling circulation space, enabling the cryogenic mixture to achieve efficient heat dissipation in the cooling circulation space. Secondly, multiple heat dissipation fins 10 are provided on the rear side wall of the low-pressure cover 2. Compared with the traditional planar heat dissipation structure, this can significantly increase the heat dissipation area, allowing the cryogenic mixture to more fully absorb the heat transferred by the power module through the low-pressure cover 2 when flowing through the heat dissipation fins 10, quickly reducing the IGBT temperature, effectively solving the problem of excessive temperature rise of the compressor under high temperature environment, low speed, high compression ratio or high suction superheat conditions, widening the operating temperature range, and ensuring the stable operation of the compressor and integrated thermal management system.
[0019] In the aforementioned front-to-back direction, the direction of the compressor's intake and exhaust is used to determine the direction, with the intake position being front and the exhaust position being back.
[0020] Each heat dissipation fin 10 extends from front to back along the axial direction of the housing 3. The heat dissipation fins 10 extending along the axial direction can be perpendicular to the flow direction of the low-temperature mixture, thereby disturbing the flow of the low-temperature mixture as much as possible and further enhancing the heat dissipation capacity.
[0021] Each heat dissipation fin 10 includes multiple first heat dissipation fins 1001 and multiple second heat dissipation fins 1002. Each first heat dissipation fin 1001 is circumferentially arranged around the front end of the drive shaft 7, and each second heat dissipation fin 1002 is disposed in a first groove 201. The first heat dissipation fins 1001 and the second heat dissipation fins 1002 can achieve full coverage of the heat dissipation area. The first heat dissipation fins 1001, which are circumferentially arranged around the front end of the drive shaft 7, can directly cool the bearing and the high-temperature area around the drive shaft 7. The second heat dissipation fins 1002, which are disposed in the first groove 201, can directly contact the low-temperature mixture accumulated in the second groove 201, thereby enhancing local heat exchange. The two sets of heat dissipation fins 10 work together to further improve the heat dissipation area and heat exchange uniformity, avoid local heat accumulation, and significantly widen the operating temperature range of the compressor.
[0022] A counterweight 11 is fixedly installed on the front end face of the rotor 8. The counterweight 11 can balance the inertial force when the rotor 8 rotates, reduce the vibration of the drive shaft 7, and improve the operating stability and service life of the compressor. At the same time, the counterweight 11 rotates at high speed with the rotor 8, which can aggravate the airflow disturbance of the low temperature mixture, accelerate the speed of the fluid flowing through the heat dissipation fins 10, and enhance the convective heat transfer effect.
[0023] The counterweight 11 has a fan-shaped annular cross-section with a central angle of 180°. The 180° fan-shaped annular structure can fit the installation space at the front end of the rotor 8. Its arc-shaped air-facing surface conforms to the characteristics of airflow dynamics. When rotating, it can generate a stronger airflow pushing force, expand the disturbance range, and allow the low-temperature mixture to more fully scour the heat dissipation fins 10, thereby improving the overall heat exchange efficiency.
[0024] A second groove 1101 is formed on the outer front side of the middle position of the counterweight 11. The second groove 1101 increases the surface area of the counterweight 11, expanding the contact area with the low-temperature mixture, and with the rotation direction (i.e., along such...). Figure 3 When rotating in the direction indicated by the arrow, the wall 11011 of the second groove 1101 and the side wall 1102 of the counterweight 11 can come into direct contact with the low-temperature mixture, which intensifies the airflow speed and causes the low-temperature mixture to form turbulence when it flows through. This allows the high-speed airflow to quickly exchange heat with the heat dissipation fins 10, significantly improving the heat exchange efficiency and enabling the IGBT to cool down rapidly.
Claims
1. An integrated thermal management compressor with internal cooling, comprising, from front to back, an electrical cover, a low-pressure cover, a housing, a frame, a pump body, and a high-pressure cover; the outer side wall of the housing has an intake port communicating with the interior, and the outer side wall of the high-pressure cover has an exhaust port communicating with the interior; a drive shaft, a stator, and a rotor are disposed within the housing; the drive shaft passes axially through the housing and is rotatably mounted on the low-pressure cover via bearings; the stator is fixedly mounted on the inner wall of the housing; and the rotor is mounted on the drive shaft and corresponds in position to the stator; characterized in that: The low-pressure cover has a first groove in the middle of its rear sidewall, and the drive shaft is installed at the rear of the first groove. The drive shaft has an axial hole that runs through the shaft, and a radial hole that runs through the front end of the drive shaft. The axial hole, the radial hole, and the first groove are connected and form a cooling circulation space. The rear sidewall of the low-pressure cover is provided with multiple heat dissipation fins.
2. The integrated thermal management compressor with internal cooling as described in claim 1, characterized in that: Each of the heat dissipation fins extends from front to back along the axial direction of the housing.
3. The integrated thermal management compressor with internal cooling as described in claim 1, characterized in that: Each of the heat dissipation fins includes multiple first heat dissipation fins and multiple second heat dissipation fins. Each first heat dissipation fin is circumferentially arranged around the front end of the drive shaft, and each second heat dissipation fin is disposed in the first groove.
4. The integrated thermal management compressor with internal cooling as described in claim 1, characterized in that: A counterweight is fixedly installed on the front end face of the rotor.
5. An integrated thermal management compressor with internal cooling as described in claim 4, characterized in that: The cross-section of the counterweight is a fan-shaped ring with a central angle of 180°.
6. The integrated thermal management compressor with internal cooling as described in claim 5, characterized in that: A second groove is formed on the outer front side of the middle position of the counterweight.