Thermal management integrated module and vehicle thermal management system

Abstract

This disclosure provides a thermal management integrated module and an on-board thermal management system. The thermal management integrated module includes a compressor and a fluid management device. The compressor includes a housing assembly with an intake port and an exhaust port, the housing assembly having first and second flow channel junctions. Refrigerant discharged from the exhaust port flows to the first flow channel junction; refrigerant leaving the second flow channel junction flows to the intake port. The housing assembly also has a bypass channel defined by the first and second flow channel junctions, and the fluid management device is disposed on the bypass channel. The above-described configuration of this disclosure allows the refrigerant discharged from the exhaust port to flow to the first flow channel junction, and then to the second flow channel junction via the bypass channel, and then back to the compressor via the intake port, forming a hot gas bypass loop for the refrigerant. This also avoids the need for excessive flow channels, improving the integration of the thermal management integrated module.

Description

Technical Field

[0001] This disclosure relates to a thermal management integrated module and an on-board thermal management system including the thermal management integrated module. Background Technology

[0002] As the market penetration rate of new energy vehicles increases and price wars intensify, there are increasingly higher requirements for modularization, lightweighting, standardization, and cost reduction in vehicle thermal management.

[0003] Existing thermal management systems typically consist of multiple independent components such as compressors, heat exchangers, electronic expansion valves, and sensors. These components are usually distributed across different locations on the vehicle body and connected by piping to achieve thermal management of the target object. However, this setup is complex, has low integration, occupies a large space, is costly, and carries a high risk of fluid leakage.

[0004] Therefore, those skilled in the art are dedicated to developing a new integrated thermal management module to address the aforementioned deficiencies in the prior art. Summary of the Invention

[0005] The purpose of this disclosure is to provide a thermal management integrated module, which includes a compressor with a housing assembly and a first heat exchanger and a second heat exchanger disposed on both sides of the compressor. By installing the first heat exchanger on the side closer to the control cavity, the control cavity can be effectively cooled, thereby dissipating heat from the electronic components inside. Furthermore, the end plate of the first heat exchanger can also serve as a cover plate for the control cavity, which further improves the integration of the thermal management integrated module and brings the first heat exchanger closer to the control cavity, further enhancing the cooling effect of the first heat exchanger on the electronic components within the control cavity / control section. Moreover, the main channel in the housing assembly of this disclosure includes a gas-liquid separation chamber, meaning that the drying bottle of this disclosure can be integrated into the housing assembly. This not only improves the integration of the thermal management integrated module and avoids the problems of high cost and high fluid leakage risk caused by additional drying bottles, but also enables gas-liquid separation of the refrigerant, preventing liquid slugging in the compressor. This disclosure arranges at least a portion of the gas-liquid separation chamber upstream of the compression component, meaning that at least a portion of the gas-liquid separation chamber and the suction port are located on the same side of the compression component along the compressor's axial direction. This allows the high-temperature refrigerant in the gas-liquid separation chamber to exchange heat with the low-temperature refrigerant in the compressor body cavity. In this case, the gas-liquid separation chamber and the upstream side of the compression component within the compressor body cavity can cooperate as an internal heat exchanger, further effectively improving the integration of the thermal management module. Furthermore, the top of the drying bottle can be provided with a vent connecting the gas-liquid separation chamber and the suction port, allowing the gaseous refrigerant after gas-liquid separation to flow back into the compressor body cavity through this vent, mix with the refrigerant drawn in through the suction port, and be further compressed by the compression component, thus achieving the compressor's gas replenishment and enthalpy increase function. In addition, the compressor housing assembly may also be provided with a first flow channel junction point for diverting flow and a second flow channel junction point for merging flow. The first flow channel junction point may be the junction point of the first exhaust flow channel, the second exhaust flow channel and the bypass channel, so that the refrigerant discharged from the exhaust port can reach the first flow channel junction point through the first exhaust flow channel and be diverted to the second exhaust flow channel and the bypass channel respectively. The second flow channel junction point may be the junction point of the main flow channel, the bypass channel and the inlet flow channel, so that the refrigerant in the bypass channel and the main flow channel can merge and flow into the inlet flow channel at the second flow channel junction point. This configuration can avoid setting too many flow channels and further improve the integration of the thermal management integrated module.

[0006] This disclosure provides a thermal management integrated module, which includes a compressor and a fluid management device. The compressor includes a housing assembly having an intake port and an exhaust port. The housing assembly further has a first flow channel junction and a second flow channel junction. Refrigerant discharged from the exhaust port flows to the first flow channel junction; refrigerant leaving the second flow channel junction flows to the intake port. The housing assembly also has a bypass channel defined by the first flow channel junction and the second flow channel junction. The fluid management device is disposed on the bypass channel.

[0007] The thermal management integrated module according to this disclosure may also have one or more of the following features, individually or in combination.

[0008] In one or more embodiments, the thermal management integrated module further includes a first heat exchanger, and the second flow channel junction is connected to the intake port via the first heat exchanger.

[0009] In one or more embodiments, the first flow channel junction is connected to the exhaust port via a first exhaust flow channel; the first flow channel junction also defines a first end of the bypass channel; and the first flow channel junction is also connected to a first fluid inlet of the second heat exchanger via a second exhaust flow channel.

[0010] In one or more embodiments, the second flow channel junction is connected to a first fluid outlet of the second heat exchanger via a main flow channel; the second flow channel junction also defines a second end of the bypass channel; and the second flow channel junction is also connected to a first fluid inlet of the first heat exchanger via an inlet flow channel.

[0011] In one or more embodiments, the secondary flow channel of the bypass flow channel has a first portion, a second portion, and a mounting cavity; the first portion and the second portion are respectively connected to and communicate with the mounting cavity; the fluid management device is installed in the mounting cavity.

[0012] In one or more embodiments, the first portion and the second portion extend parallel to the axis of the compressor and are offset along the centerline of the mounting cavity.

[0013] In one or more embodiments, the second portion extends along the centerline of the mounting cavity.

[0014] In one or more embodiments, the housing assembly includes an intake housing and an exhaust housing; the intake housing has the intake port and the exhaust housing has the exhaust port.

[0015] In one or more embodiments, the housing assembly further includes a control housing; the intake housing and the control housing define an auxiliary flow path for the bypass channel.

[0016] This disclosure also provides an on-board thermal management system, which includes the aforementioned thermal management integration module. Attached Figure Description

[0017] Figure 1 This is a perspective view of the thermal management integrated module according to the first embodiment of the present disclosure, wherein solid arrows indicate the fluid communication path of the refrigerant main circuit and dashed arrows indicate the fluid communication path of the hot gas bypass circuit.

[0018] Figure 2 This is a perspective view of a compressor according to a first embodiment of the present disclosure from a first perspective.

[0019] Figure 3 This is a perspective view of a compressor according to a first embodiment of the present disclosure from a second perspective, wherein the arrows indicate the flow direction of fluid in the bypass channel;

[0020] Figure 4 This is a first cross-sectional schematic diagram of a compressor according to a first embodiment of the present disclosure, showing the compressor's intake port and omitting the control board inside the control chamber;

[0021] Figure 5 This is a second cross-sectional schematic diagram of a compressor according to a first embodiment of the present disclosure, showing the outlet flow path;

[0022] Figure 6 This is a third cross-sectional schematic diagram of a compressor according to a first embodiment of the present disclosure, showing the inlet flow path;

[0023] Figure 7 for Figure 4 Another perspective diagram showing the compressor's exhaust port;

[0024] Figure 8 This is a schematic diagram of a first heat exchanger installed on the control unit of a compressor according to a first embodiment of the present disclosure;

[0025] Figure 9 A perspective view of the first heat exchanger according to the first embodiment of this disclosure from a first perspective;

[0026] Figure 10 This is a perspective view of the first heat exchanger according to the first embodiment of the present disclosure from a second perspective.

[0027] Figure 11 This is a perspective view of the control unit of a compressor according to the first embodiment of the present disclosure from a first perspective.

[0028] Figure 12 This is a perspective view of the control unit of the compressor according to the first embodiment of the present disclosure from a second perspective.

[0029] Figure 13 This is a perspective view of the compressor body according to the first embodiment of the present disclosure from a first perspective, showing the side of the compressor body facing the control unit;

[0030] Figure 14 This is a perspective view of the compressor body according to the first embodiment of the present disclosure from a second perspective, showing the flow direction of fluid in the bypass channel;

[0031] Figure 15 This is a cross-sectional view of the compressor body according to a first embodiment of the present disclosure, showing a first portion of the secondary flow channel;

[0032] Figure 16 This is another cross-sectional view of the compressor body according to the first embodiment of the present disclosure, showing a second portion of the secondary flow channel;

[0033] Figure 17 This is a perspective view of the compressor body according to the first embodiment of the present disclosure from a third perspective, in which a drying bottle is shown;

[0034] Figure 18 A perspective view of the compressor body according to the first embodiment of the present disclosure from a fourth perspective, showing the cover of the drying bottle;

[0035] Figure 19 This is a perspective view of the compressor body according to a first embodiment of the present disclosure, showing the gas-liquid separation chamber of the drying bottle;

[0036] Figure 20 This is a partial enlarged view of the compressor body at the drying bottle according to the first embodiment of this disclosure, showing the chamber inlet;

[0037] Figure 21 This is a partial enlarged view of the compressor body at the drying bottle according to the first embodiment of this disclosure, showing the chamber outlet;

[0038] Figure 22 This is a perspective view of the exhaust section of a compressor according to the first embodiment of this disclosure;

[0039] Figure 23 This is a perspective view of the second heat exchanger according to the first embodiment of this disclosure;

[0040] Figure 24 This is a schematic diagram of a second heat exchanger installed on the exhaust section of a compressor according to a first embodiment of the present disclosure;

[0041] Figure 25This is a cross-sectional view of a second heat exchanger installed on a compressor body according to a first embodiment of the present disclosure, showing the first flow channel junction.

[0042] Figure 26 for Figure 25 A magnified view of a portion at point A, showing the first flow channel junction;

[0043] Figure 27 This is a cross-sectional view of a first heat exchanger installed on a compressor according to a first embodiment of the present disclosure, showing the second flow channel junction.

[0044] Figure 28 for Figure 27 A magnified view at point B, showing the second flow channel junction;

[0045] Figure 29 This is a schematic diagram of the second flow channel junction according to the first embodiment of the present disclosure in another cross section;

[0046] Figure 30 This is a perspective view of a compressor according to a first embodiment of the present disclosure from a third perspective, showing the main throttling device;

[0047] Figure 31 This is a perspective view of a compressor according to a first embodiment of the present disclosure from a fourth perspective, in which the auxiliary throttling device is shown;

[0048] Figure 32 A three-dimensional representation of a thermal management integrated module according to a second embodiment of this disclosure;

[0049] Figure 33 This is a perspective view of the intake section of a compressor according to a second embodiment of the present disclosure, wherein the components of the compressor installed in the intake section are omitted, and the side of the intake section housing facing the exhaust section is shown.

[0050] Figure 34 This is a perspective view of the exhaust section of a compressor according to a second embodiment of the present disclosure, showing the side of the exhaust section housing facing the intake section;

[0051] Figure 35 This is a perspective view of the compressor body according to the second embodiment of the present disclosure from a first perspective;

[0052] Figure 36 This is a perspective view of the compressor body according to a second embodiment of the present disclosure from a second perspective, wherein the arrows indicate the flow direction of the fluid flowing through the drying bottle;

[0053] Figure 37 This is a schematic cross-sectional view of the compressor body according to a second embodiment of the present disclosure, showing the second flow channel junction;

[0054] Figure 38 A first-view perspective view of the thermal management integrated module according to the third embodiment of this disclosure;

[0055] Figure 39 A perspective view of the thermal management integrated module according to the third embodiment of this disclosure from a second perspective;

[0056] Figure 40 A perspective view of a thermal management integrated module according to a fourth embodiment of this disclosure;

[0057] Figure 41 A perspective view of a compressor according to the fourth embodiment of this disclosure;

[0058] Figure 42 This is a cross-sectional schematic diagram of a compressor according to a fourth embodiment of the present disclosure, showing the various components inside the compressor;

[0059] Figure 43 This is a perspective view of the intake housing according to the fourth embodiment of this disclosure;

[0060] Figure 44 This is a perspective view of the exhaust housing according to the fourth embodiment of this disclosure;

[0061] Figure 45 This is a schematic diagram of the working principle of the thermal management integrated module according to the first embodiment of this disclosure;

[0062] Figure 46 This is a schematic diagram of the working principle of the thermal management integrated module according to the second embodiment of this disclosure;

[0063] Figure 47 This is a schematic diagram of the working principle of the thermal management integrated module according to the third and fourth embodiments of this disclosure. Detailed Implementation

[0064] The following specific embodiments illustrate the implementation of this disclosure. Those skilled in the art can easily understand other advantages and effects of this disclosure from the content disclosed in this specification.

[0065] It should be understood that the structures, proportions, sizes, etc., depicted in the accompanying drawings are merely for illustrative purposes to aid those skilled in the art in understanding and reading the content disclosed herein, and are not intended to limit the implementation conditions of this disclosure. Therefore, they have no substantial technical significance. Any modifications to the structure, changes in proportions, or adjustments to the size, without affecting the effectiveness and purpose of this disclosure, should still fall within the scope of the technical content disclosed herein. Furthermore, the terms such as "above" and "a" used in this specification are merely for clarity of description and are not intended to limit the scope of this disclosure. Changes or adjustments to their relative relationships, without substantially altering the technical content, should also be considered within the scope of this disclosure's implementation.

[0066] This disclosure provides a thermal management integrated module. Specific embodiments of this disclosure are described below with reference to the accompanying drawings.

[0067] Please see Figures 1 to 3 The thermal management integrated module 1 includes a compressor 2 for converting a low-temperature, low-pressure refrigerant in a refrigerant circuit into a high-temperature, high-pressure refrigerant. In one embodiment, the compressor 2 includes a compressor body 20 and a control unit 10 connected to one end of the compressor body 20. The end of the compressor body 20 and the control unit 10 may define an auxiliary flow channel 1031 (e.g., Figure 3 and Figure 13 As shown in the figure, this configuration can effectively improve the integration of the thermal management integrated module 1 and avoid problems such as large space occupation, difficulty in assembly, and high risk of fluid leakage caused by additional piping.

[0068] Specifically, please refer to the following: Figures 2 to 7 The compressor body 20 includes an intake section 21 and an exhaust section 22 connected to the intake section 21, wherein the intake section 21 has an intake port 101 and the exhaust section 22 has an exhaust port 102. The control section 10 of the compressor 2 is connected to the end of the intake section 21 away from the exhaust section 22, that is, the intake section 21 is connected between the control section 10 and the exhaust section 22.

[0069] More specifically, the compressor 2 has a housing assembly H, which may include a control housing H1, an intake housing H2, and an exhaust housing H3 connected sequentially along the compressor's axis X (that is, the control housing H1 and the exhaust housing H3 are connected at both ends of the intake housing H2 along the compressor 2's axis X), wherein the interior of the housing assembly H, particularly the interior of the control housing H1, defines a control cavity 1000 (e.g., Figure 4As shown), the control cavity 1000 can accommodate electronic components, such as inverters, microcontrollers, etc., to form the control unit 10 of the compressor 2, mainly used for controlling the starting, operation, and protection of the compressor body 20. The control cavity 1000 has a cavity opening 1001 (as shown). Figure 11 As shown, multiple electronic components can be fixedly installed into the control cavity 1000 through the cavity opening 1001. During the operation of the compressor 2, the electronic components generate a large amount of heat, causing the temperature of the control cavity 1000 to rise.

[0070] In one embodiment, multiple electronic components may be disposed on a printed circuit board to form a control board 100 (e.g., Figure 5 and Figure 6 As shown), the control panel 100 can enter the control cavity 1000 through the cavity opening 1001 and is fixed in the control cavity 1000. The interior of the housing assembly H also defines a body cavity 2000 (i.e., the inner cavity of the compressor body 20, such as...). Figure 4 and Figure 7 As shown), it is used to house the stator 210, rotor 220, bearing 230, shaft 240, and compression components 250 of the compressor 2 (please refer to...). Figure 42 The compression component 250 may include a moving scroll plate 251 and a stationary scroll plate 252. The stator 210, rotor 220, bearing 230, shaft 240, and compression component 250 of the compressor 2 are housed within the intake housing H2, and an intake port 101 is formed in the intake housing H2 (e.g., ...). Figure 4 As shown), specifically, the suction port 101 can be formed on the inner wall of the suction section housing H2, and this inner wall of the suction section housing H2 is used to define at least a portion of the body cavity 2000 to form the suction section 21 of the compressor body 20. This section is mainly used to draw low-temperature, low-pressure gaseous refrigerant from the refrigerant circuit into the compressor body 20 (i.e., into the body cavity 2000), and then flow to the periphery of the stationary scroll plate 252. As the shaft 240 rotates, the gaseous refrigerant is gradually compressed into a high-temperature, high-pressure refrigerant in the compression chamber formed by the meshing of the moving scroll plate 251 and the stationary scroll plate 252, and then flows through the axial hole in the center of the stationary scroll plate 252 into the exhaust section housing H3. An exhaust port 102 is formed in the exhaust section housing H3 (as shown). Figure 7 As shown, specifically, the exhaust port 102 may be formed on the inner wall of the exhaust housing H3, and this inner wall of the exhaust housing H3 serves to define at least another part of the body cavity 2000 to form the exhaust section 22 of the compressor body 20, mainly for discharging the compressed high-temperature and high-pressure refrigerant through the exhaust port 102. The rotating shaft 240 can rotate about the axis X of the compressor 2. In a variant embodiment (not shown), the suction housing H2 may be composed of multiple sub-housings joined together, and / or the exhaust housing H3 may be composed of multiple sub-housings joined together.

[0071] Please refer to the above. Figure 12 and Figure 13 In one embodiment, a groove 200 is formed at one end of the intake housing H2 near the control housing H1. The control housing H1 has a first side away from the intake housing H2 (e.g., Figure 11 (as shown) and the second side near the intake housing H2 (as shown) Figure 12 As shown), the first side and the second side are arranged along the X-axis of the compressor 2. When the control housing H1 (especially its second side) is fixedly installed on the suction housing H2, the control housing H1 will block the opening of the groove 200 at the end of the suction housing H2 to form an auxiliary flow channel 1031.

[0072] Specifically, the groove 200 can be generally arc-shaped and formed at the outer edge of the intake housing H2 near the control housing H1. Correspondingly, the second side of the control housing H1 has an outer edge sidewall 22, which can block the opening of the arc-shaped groove 200 to form an arc-shaped auxiliary flow channel 1031, thereby effectively reducing the flow resistance of the fluid. A first inlet 201 and a second inlet 202 are formed on the bottom wall of the groove 200, allowing fluid (e.g., refrigerant) to enter. The first inlet 201 is used for fluid communication with the main flow channel 1300 on the housing assembly H (e.g., refrigerant). Figure 18 The dotted lines shown (described later) allow fluid in the main flow channel 1300 to flow into the auxiliary flow channel 1031 via the first inlet 201; the second inlet 202 is used for fluid communication with the secondary flow channel 1032 on the housing assembly H (e.g., Figure 3 and Figure 14 As shown (described later), this allows fluid in the secondary flow channel 1032 to flow into the auxiliary flow channel 1031 via the second inlet 202. Preferably, a sealing element may be provided between the control housing H1 and the intake housing H2 to prevent fluid leakage at their joint.

[0073] Of course, this disclosure is not limited to the above-described structure and shape of the auxiliary flow channel 1031. For example, the groove can also be any suitable shape formed on the second side of the control housing H1 near the intake housing H2, and its opening can be blocked by the intake housing H2 to form an auxiliary flow channel; or the groove can also be any suitable shape formed on the ends of the control housing H1 and the intake housing H2 that are close to each other, and the two grooves face each other and cooperate to form an auxiliary flow channel.

[0074] Please refer to the above. Figure 3 , Figures 14 to 16The housing assembly H is also provided with a secondary flow channel 1032, one end of which is fluidly connected to the auxiliary flow channel 1031 via the second inlet 202, and the other end is fluidly connected to the exhaust port 102 of the compressor 2. That is to say, the auxiliary flow channel 1031 can be fluidly connected to the exhaust port 102 of the compressor 2 via the second inlet 202 and the secondary flow channel 1032.

[0075] Specifically, the secondary flow channel 1032 may include a mounting cavity 810 for mounting a fluid management device, and a first portion 1032a and a second portion 1032b located on both sides of the mounting cavity 810 and in fluid communication with it, respectively. The first portion 1032a may be a straight channel extending generally along the X-axis of the compressor 2, formed in the intake housing H2 and the exhaust housing H3, with one end in fluid communication with the exhaust port 102 and the other end in fluid communication with the mounting cavity 810. The second portion 1032b may also be a straight channel extending generally along the X-axis of the compressor 2, and may be offset from the first portion 1032a in the direction along the centerline X0 of the mounting cavity 810, wherein the centerline X0 may be generally perpendicular to the height direction of the compressor 2. The second part 1032b is formed in the suction housing H2, with one end in fluid communication with the mounting cavity 810 and the other end in fluid communication with the auxiliary flow channel 1031 via the second inlet 202, so that the refrigerant discharged from the discharge port 102 of the compressor 2 can flow to the auxiliary flow channel 1031 via the secondary flow channel 1032 and the second inlet 202. The height direction Y is perpendicular to the mounting plane of the compressor 2, and the mounting plane can be defined by the four mounting feet 99 of the compressor.

[0076] The thermal management integrated module 1 may further include a fluid management device mounted on the housing assembly H. For example, the fluid management device may be at least partially mounted in the mounting cavity 810 and can be used to manage the opening and closing, flow direction, flow rate, and / or temperature of the fluid in the secondary flow channel 1032. In one embodiment, the fluid management device may include a throttling device 80, which includes a secondary throttling device 81 (e.g., an electronic expansion valve). The secondary throttling device 81 may be at least partially mounted in the mounting cavity 810 and fluidly connected to the secondary flow channel 1032 to regulate the flow rate, pressure, etc. of the fluid in the secondary flow channel 1032. Preferably, the secondary throttling device 81 may be configured such that the direction of its axis X1 is perpendicular to the height direction Y of the compressor 2 (e.g., ...). Figure 31 (as shown), to further reduce the overall package size of the thermal management integrated module 1.

[0077] It should be noted that the auxiliary flow channel 1031 and the secondary flow channel 1032 in the housing assembly H of compressor 2 can together form a bypass channel 103, mainly used to cooperate with the refrigerant main circuit (such as... Figure 1As shown by the solid line in the diagram (the specific circuit will be described later), the compressor in the thermal management system operates in a low-temperature heating mode. The first end of the bypass channel 103 (i.e., the end of the secondary flow channel 1032 furthest from the auxiliary flow channel 1031) is fluidly connected to the exhaust port 102, and the second end (i.e., the end of the auxiliary flow channel 1031 furthest from the secondary flow channel 1032) is fluidly connected to the suction port 101 of the compressor 2 (described later), thus forming a hot gas bypass circuit (e.g., as shown by the solid line in the diagram). Figure 1 As shown by the dotted line in the diagram, this enables stable operation and rapid heating of compressor 2 in low-temperature environments. Specifically, when the ambient temperature is low (e.g., below -20°C), the refrigerant in the first heat exchanger 30 may be difficult to evaporate in the heat pump mode to absorb heat from the outside, or the compressor suction density may be too low, making it difficult for compressor 2 to operate normally. In this case, the compressor can be operated in a low-temperature heating mode, where the hot gas bypass circuit and the refrigerant main circuit operate simultaneously. Since the high-temperature refrigerant in the hot gas bypass circuit mixes with the liquid refrigerant in the refrigerant main circuit, the liquid refrigerant in the refrigerant main circuit evaporates, preventing liquid refrigerant from directly entering compressor 2 and causing liquid slugging. This ensures the normal and stable operation of the compressor in low-temperature heating mode. At the same time, since the bypass channel 103 is formed on / integrated into the housing assembly H of compressor 2, it can effectively improve the integration of the thermal management integrated module 1, simplify the structure, and avoid problems such as large space occupation, difficult assembly, and high risk of fluid leakage caused by additional connecting pipes. Furthermore, the secondary throttling device 81 installed in the bypass channel 103 can throttle and reduce the pressure of the high-temperature and high-pressure refrigerant discharged from the exhaust port 102, so as to regulate the flow rate and pressure of the fluid in the hot gas bypass circuit.

[0078] Please refer to the above. Figure 1 , Figures 6 to 11 The thermal management integrated module 1 also includes a first heat exchanger 30 (e.g., a cooler) connected to the end of the control unit 10 of the compressor 2 away from the suction unit 21, so as to exchange heat with the control unit 10, especially with the electronic components in the control cavity 1000, thereby effectively cooling / dissipating heat from them.

[0079] In one embodiment, the first heat exchanger 30 may be a plate heat exchanger. Specifically, the first heat exchanger 30 has a first fluid inlet 301, a first fluid outlet 302, a second fluid inlet 303, a second fluid outlet 304, a first heat exchange channel, and a second heat exchange channel. The first heat exchange channel is formed between the first fluid inlet 301 and the first fluid outlet 302, and the second heat exchange channel is formed between the second fluid inlet 303 and the second fluid outlet 304. The first heat exchange channel may be a refrigerant heat exchange channel, and the second heat exchange channel may be a coolant heat exchange channel. The refrigerant in the first heat exchange channel exchanges heat with the coolant in the second heat exchange channel.

[0080] Please continue reading Figures 6 to 11The first heat exchanger 30 includes a main body 300 and an end plate 305 connected to one side of the main body 300. The main body 300 is a whole formed by stacking and welding heat exchange plates. The end plate 305 can be welded to the main body 300 and can be connected to the housing assembly H by fastening elements such as screws. In a specific embodiment, the first fluid inlet 301 and the first fluid outlet 302 are tubular, communicating with the main body 300 and located on the side of the main body 300 near the end plate 305; the second fluid inlet 303 and the second fluid outlet 304 are tubular, communicating with the main body 300 and located on the side of the main body 300 away from the end plate 305. The end plate 305 is provided with a through hole allowing the first fluid inlet 301 and the first fluid outlet 302 to pass through, and the tubular first fluid inlet 301 and the first fluid outlet 302 can pass through the through hole and protrude from the end plate 305.

[0081] In another embodiment, the tubular first fluid inlet 301 and first fluid outlet 302 are mounted on the end plate 305, for example, integrally formed with the end plate 305 to protrude from the end plate 305.

[0082] A first fluid (e.g., refrigerant) may enter the first heat exchange channel of the first heat exchanger 30 through the first fluid inlet 301 and flow out through the first fluid outlet 302. A second fluid (e.g., coolant) may enter the second heat exchange channel of the first heat exchanger 30 through the second fluid inlet 303 and flow out through the second fluid outlet 304. During its flow within the first heat exchanger 30, the second fluid may exchange heat sufficiently with the first fluid within the first heat exchanger 30.

[0083] The first fluid inlet 301 of the first heat exchanger 30 can be fluidly connected to the auxiliary flow channel 1031, and the first fluid outlet 302 can be fluidly connected to the suction port 101 of the compressor 2. In this way, the refrigerant discharged from the discharge port 102 of the compressor 2 can flow back to the suction port 101 of the compressor 2 via the bypass channel 103 (i.e., the secondary flow channel 1032 and the auxiliary flow channel 1031) and the first heat exchanger 30, thereby realizing the hot gas bypass of the compressor 2.

[0084] Specifically, please see Figure 5 and Figure 6The housing assembly H is further provided with an inlet channel 1100 and an outlet channel 1200, which are fluidly connected to the first heat exchange channel (e.g., the refrigerant heat exchange channel) of the first heat exchanger 30, respectively. One end of the inlet channel 1100 is fluidly connected to the auxiliary channel 1031, and the other end is fluidly connected to the first fluid inlet 301 of the first heat exchanger 30, so that the fluid in the auxiliary channel 1031 (or bypass channel 103) can enter the first heat exchange channel of the first heat exchanger 30 through the inlet channel 1100 and the first fluid inlet 301. One end of the outlet channel 1200 is fluidly connected to the first fluid outlet 302 of the first heat exchanger 30, and the other end is fluidly connected to the suction port 101 of the compressor 2, so that the fluid in the first heat exchange channel of the first heat exchanger 30 can flow back to the suction port 101 of the compressor 2 through the first fluid outlet 302 and the outlet channel 1200.

[0085] To facilitate the installation and connection of the first fluid inlet 301 and the first fluid outlet 302 of the first heat exchanger 30 to the inlet flow channel 1100 and the outlet flow channel 1200, the inlet flow channel 1100 may include an inlet extension 1110 disposed in the control unit housing H1, such as... Figure 11 As shown, the inlet extension 1110 can extend from the first side of the control housing H1 along an axis X parallel to the compressor 2 (e.g., ...). Figure 5 The flow channel 1200 extends in the direction shown to the second side of the control housing H1 and has a first port 1111 capable of docking with the first fluid inlet 301 of the first heat exchanger 30; the outlet flow channel 1200 may include an outlet extension 1210 disposed in the control housing H1, such as Figure 11 As shown, the outlet extension 1210 can also extend from the first side of the control unit housing H1 along a direction parallel to the axis X of the compressor 2 to the second side of the control unit housing H1, and has a second port 1211 that can be connected to the first fluid outlet 302 of the first heat exchanger 30. This arrangement allows the first fluid inlet 301 and the first fluid outlet 302 of the first heat exchanger 30 to be directly connected to the first port 1211 and the second port 1211, respectively, which facilitates installation and saves installation time.

[0086] To further enhance the integration of the thermal management integrated module 1 and improve the heat dissipation effect on the electronic components within the control unit 10, the end plate 305 of the first heat exchanger 30 can also serve as a cover plate for the control unit 10. Specifically, as shown in... Figure 10 and Figure 11As shown, the area of ​​the end plate 305 can be larger than the projected area of ​​the main body 300 on the plane where the end plate 305 is located. The first side of the control housing H1 facing the first heat exchanger 30 can be configured to be open, that is, the control cavity 1000 has a cavity opening 1001 to facilitate the placement of electronic components. The cavity opening 1001 and the first port 1111 and the second port 1211 can be respectively formed on the end face 13 of the first side of the housing assembly H (especially the control housing H1) (e.g., Figure 11 As shown, the end face 13 is perpendicular to the axis X of the compressor 2, and is closer to the suction port 101 than the discharge port 102 of the compressor 2. The first heat exchanger 30, especially its end plate 305, can be aligned with the end face 13 along the axis X of the compressor 2, so that the end plate 305 can close the cavity opening 1001, and the first fluid inlet 301 and the first fluid outlet 302 are respectively aligned with the first port 1111 and the second port 1211; in a specific embodiment, the tubular first fluid inlet 301 and the first fluid outlet 302 are respectively inserted into the first port 1111 and the second port 1211 to realize the alignment process. When the first heat exchanger 30 is installed on the control unit 10 (or the first heat exchanger 30 is docked to the end face 13), the first heat exchanger 30, especially its end plate 305, can close the cavity opening 1001, so that the end plate 305 of the first heat exchanger 30 can also serve as the cover plate of the control unit 10. This not only improves the integration of the thermal management integrated module 1, simplifies the structure, makes it occupy less space and has a lower cost, but also allows the first heat exchanger 30 to be closer to the control cavity 1000. Since the first heat exchanger 30 can be directly opposite to the electronic components in the control cavity 100 (or the electronic components on the control board 100), the heat on the electronic components (e.g., its temperature is about 70°C-80°C) can be directly transferred to the end plate 305 of the first heat exchanger 30 (e.g., its temperature is about 20°C) through radiation heat transfer, thereby effectively improving the cooling effect of the first heat exchanger 30 on the electronic components in the control cavity 1000 / control unit 10.

[0087] Preferably, a sealing element (not shown) is provided between the end plate 305 of the first heat exchanger 30 and the end face 13 of the control unit housing H1. This sealing element can be configured to surround the cavity opening 1001, and on the end face 13, the sealing element can separate the cavity opening 1001 from the first port 1111 and the second port 1211. This prevents fluid leakage at the junction of the first port 1111 and / or the second port 1211 with the first fluid inlet 301 and the second fluid outlet 302 of the first heat exchanger 30 from entering the control cavity 1000 and damaging electronic components. Of course, this disclosure is not limited to this; for example, the sealing element can also be configured to surround the first port 1111 and the second port 1211, as long as fluid leakage from the first port 1111 and the second port 1211 into the control cavity 1000 is prevented.

[0088] This disclosure is not limited to the above-described arrangement of the first heat exchanger 30 and the control unit 10. For example, the compressor 2 may also include a control chamber cover made of a thermally conductive material, which is mounted on the control unit housing H1 to close the cavity opening 1001. The first heat exchanger 30, especially its end plate, may be mounted on the control unit 10 and directly contact the control chamber cover. With this arrangement, the first heat exchanger 30 can indirectly cool the control cavity 1000 and its internal electronic components by cooling the control chamber cover.

[0089] Please refer to the above. Figure 1 as well as Figures 22 to 24 The thermal management integrated module 1 also includes a second heat exchanger 40 (e.g., a water-cooled condenser) connected to the end of the exhaust housing H3 away from the intake housing H2. In this embodiment, the heat generated by the compressor 2 compressing the refrigerant can be transferred to the coolant circuit (not shown) via the second heat exchanger 40, and further transferred by the coolant back to target objects requiring heat, such as the passenger compartment.

[0090] In one embodiment, the second heat exchanger 40 may be a plate heat exchanger, having a first heat exchange channel and a second heat exchange channel. The first heat exchange channel may be a refrigerant heat exchange channel, and the second heat exchange channel may be a coolant heat exchange channel. The refrigerant in the first heat exchange channel exchanges heat with the coolant in the second heat exchange channel.

[0091] Please continue reading Figure 23 and Figure 24 The second heat exchanger 40 includes a first fluid inlet 401 and a first fluid outlet 402 communicating with the first heat exchange channel, and a second fluid inlet 403 and a second fluid outlet 404 communicating with the second heat exchanger channel. The first fluid inlet 401 and the first fluid outlet 402 are located at the end of the second heat exchanger 40 closer to the compressor 2. A first fluid (e.g., refrigerant) can enter the first heat exchange channel of the second heat exchanger 40 through the first fluid inlet 401 and flow out through the first fluid outlet 402. The second fluid inlet 403 and the second fluid outlet 404 are located at the end of the second heat exchanger 40 away from the compressor 2. A second fluid (e.g., coolant) can enter the second heat exchange channel of the second heat exchanger 40 through the second fluid inlet 403 and flow out through the second fluid outlet 404. During its flow within the second heat exchanger 40, the second fluid can fully exchange heat with the first fluid within the second heat exchanger 40.

[0092] The first fluid inlet 401 of the second heat exchanger 40 can be fluidly connected to the exhaust port 102 of the compressor 2, and the first fluid outlet 402 can be fluidly connected to the first inlet 201 on the bottom wall of the groove 200 (e.g., Figure 13As shown), the refrigerant discharged from the discharge port 102 of the compressor 2 can flow back to the suction port 101 of the compressor 2 via the second heat exchanger 40, the first inlet 201, the inlet flow channel 1100, the first heat exchanger 30, and the outlet flow channel 1200, forming the main refrigerant circuit. Figure 1 As shown by the solid arrow in the image.

[0093] Specifically, please see Figure 18 The housing assembly H also includes an exhaust channel 1400 (e.g., Figure 18 (as indicated by the arrow at the top center) and the main channel 1300 (as shown) Figure 18 As indicated by the arrow in the lower middle section, the first heat exchange passage (e.g., the refrigerant heat exchange passage) of the second heat exchanger 40 can be fluidly connected to the first heat exchange passage of the second heat exchanger 40. One end of the exhaust passage 1400 is fluidly connected to the exhaust port 102 of the compressor 2, and the other end is fluidly connected to the first fluid inlet 401 of the second heat exchanger 40, so that the first fluid discharged from the exhaust port 102 of the compressor 2 can enter the first heat exchange passage of the second heat exchanger 40. One end of the main flow channel 1300 (or the inlet of the main flow channel 1300) is fluidly connected to the first fluid outlet 402 of the second heat exchanger 40, and the other end (or the outlet of the main flow channel 1300) is fluidly connected to the auxiliary flow channel 1031, so that the fluid in the first heat exchange channel of the second heat exchanger 40 can be fluidly connected to the auxiliary flow channel 1031 via the main flow channel 1300, and the auxiliary flow channel 1031 can flow back to the suction port 101 of the compressor 2 via the inlet flow channel 1100, the first heat exchanger 30 and the outlet flow channel 1200, thus forming the refrigerant main circuit from the discharge port 102 to the suction port 101 of the compressor 2.

[0094] To facilitate the installation and connection of the first fluid inlet 401 and the first fluid outlet 402 of the second heat exchanger 40 to the exhaust flow channel 1400 and the main flow channel 1300, the exhaust flow channel 1400 may include an inlet connection portion 1410 disposed in the exhaust housing H3, such as... Figure 22 As shown, the inlet connection 1410 can be connected from one side of the exhaust housing H3 along an axis X parallel to the compressor 2 (e.g., ...). Figure 5 The main channel 1300 extends in the direction shown to the other side of the exhaust housing H3 and has a first connection port 1411 capable of docking with the first fluid inlet 401 of the second heat exchanger 40; the main channel 1300 may include an outlet connection portion 1310 disposed in the exhaust housing H3, such as Figure 22As shown, the outlet connection 1310 can also extend from one side of the exhaust housing H3 along a direction parallel to the axis X of the compressor 2 to the other side of the exhaust housing H3, and has a second connection port 1311 that can dock with the first fluid outlet 402 of the second heat exchanger 40 (the connection port 1311 is also the inlet of the main flow channel 1300 mentioned above). This arrangement allows the first fluid inlet 401 and the first fluid outlet 402 of the second heat exchanger 40 to directly dock with the first connection port 1411 and the second connection port 1311 along the axis X of the compressor 2, respectively, which facilitates installation and saves installation time.

[0095] In one embodiment, such as Figure 18 As shown, the exhaust flow channel 1400 may include a first exhaust flow channel 1401 and a second exhaust flow channel 1402 disposed in the exhaust housing H3 and connected to each other. The first exhaust flow channel 1401 may extend in a direction perpendicular to the axis X of the compressor 2, and one end of it is connected to the exhaust port 102 of the compressor 2, and the other end is connected to the second exhaust flow channel 1402. The second exhaust flow channel 1402 may extend in a direction parallel to the axis X of the compressor 2, and one end of it is connected to the first exhaust flow channel 1401, and the other end is connected to the first fluid inlet 401 of the second heat exchanger 40. The second exhaust flow channel 1402 includes the aforementioned inlet connection portion 1410 that is connected to the first fluid inlet 401 of the second heat exchanger 40.

[0096] To securely mount the second heat exchanger 40 onto the exhaust housing H3, the exhaust housing H3 is provided with a plurality of brackets 220 (four are described herein, but not limited thereto) along its circumferential direction. Each bracket 220 has mounting holes 2200 for fixing the second heat exchanger 40. An outlet connection portion 1310 is provided on one of the brackets 220, for example... Figure 22 On the bracket 220 at the lower left corner. Correspondingly, the second heat exchanger 40 has multiple outwardly protruding mounting holes 400 on the end plate near the exhaust housing H3, such as... Figure 23 As shown. When the second heat exchanger 40 is installed on the exhaust housing H3, the mounting hole 400 on the second heat exchanger 40 is aligned with the mounting hole 2200 on the bracket 220, and the two can be fixed together by fastening elements (such as screws). Of course, this disclosure is not limited to this. For example, the second heat exchanger 40 can also be directly welded to the exhaust housing H3, as long as the second heat exchanger 40 is connected to the exhaust housing H3.

[0097] Please refer to the above. Figures 17 to 19 The throttling device 80 may also include a main throttling device 82 (e.g., an electronic expansion valve). At least one main throttling device 82 is provided on the main flow channel 1300 to regulate the flow rate and pressure of the fluid in the main refrigerant circuit.

[0098] Specifically, the main flow channel 1300 has a mounting cavity 820, which is disposed on the housing assembly H, particularly on the suction housing H2. A main throttling device 82 can be at least partially installed within the mounting cavity 820 and is fluidly connected to the main flow channel 1300 to regulate the flow rate and pressure of the fluid in the main flow channel 1300. More specifically, the refrigerant flowing into the main flow channel 1300 from the first fluid outlet 402 of the second heat exchanger 40 can be throttled and depressurized by the main throttling device 82, making it a low-temperature, low-pressure gas-liquid mixture refrigerant, which then enters the first heat exchanger 30 to evaporate and absorb heat from the coolant, before flowing back to the suction port 101. Preferably, the main throttling device 82 can be configured such that its axis X2 is perpendicular to the height direction Y of the compressor 2 (e.g., ...). Figure 30 (as shown), to further reduce the overall package size of the thermal management integrated module 1.

[0099] Please continue reading Figure 19 The main channel 1300 may also have a gas-liquid separation chamber 50, which is located upstream of the mounting chamber 820 (or the main throttling device 82) to separate the gas-liquid mixture refrigerant flowing out from the first fluid outlet 402 of the second heat exchanger 40.

[0100] In one embodiment, the gas-liquid separation chamber 50 may be formed on the suction housing H2 and has an opening 54 that opens toward the outside of the suction housing H2. Correspondingly, the housing assembly H may also include a cover plate 51 (e.g., Figure 18 As shown, the cover plate 51 can be connected to the intake housing H2 via a fastening element (e.g., screws) and closes the opening 54 of the gas-liquid separation chamber 50, forming a drying bottle 5. That is, the drying bottle 5 may include a gas-liquid separation chamber 50 formed on / integrated into the intake housing H2 and a cover plate 51 that closes the opening 54 of the gas-liquid separation chamber 50. The cover plate 51 is configured to connect to the intake housing H2 in a direction perpendicular to the axis X2 and perpendicular to the height direction Y of the compressor 2.

[0101] Please see Figure 20 and Figure 21 A cavity inlet 510 and a cavity outlet 520 may be provided on the side wall of the gas-liquid separation chamber 50. The cavity inlet 510 and the cavity outlet 520 may be located at the bottom of the gas-liquid separation chamber 50. Fluid can enter the gas-liquid separation chamber 50 through the cavity inlet 510 and exit through the cavity outlet 520. A first partition 503 and a second partition 504 are provided inside the gas-liquid separation chamber 50. The first partition 503 is arranged from bottom to top on the side wall of the gas-liquid separation chamber 50, and the second partition 504 is arranged from top to bottom on the side wall of the gas-liquid separation chamber 50. The first partition 503 is closer to the cavity inlet 510 than the second partition 504.

[0102] The first partition 503 and the second partition 504 are offset by a certain distance D along the axis X of the compressor 2, and along the height direction Y of the compressor 2, the first partition 503 and the second partition 504 have an overlapping portion W, thereby forming a connecting portion 505 between the first partition 503 and the second partition 504. The width of the connecting portion 505 is defined by the aforementioned distance D, and the height of the connecting portion 505 is defined by the aforementioned overlapping portion W. The depth of the connecting portion 505 is the depth of the gas-liquid separation chamber 50.

[0103] The second partition 504, the connecting portion 505, and the first partition 503 are arranged from top to bottom to divide the gas-liquid separation chamber 50 into a first chamber 501 and a second chamber 502 arranged along the axis X of the compressor 2. The first chamber 501 is located upstream of the second chamber 502, meaning that the chamber inlet 510 can be located on the side wall of the first chamber 501, and the chamber outlet 520 can be located on the side wall of the second chamber 502. The drying bottle 5 also includes a drying pack 3 for absorbing moisture from the gas-liquid mixture refrigerant flowing into the gas-liquid separation chamber 50 from the chamber inlet 510. In this embodiment, the drying pack 3 is located close to the chamber inlet 510, or in other words, the drying pack 3 is located inside the first chamber 501. Preferably, the drying pack 3 can be placed vertically so that the gas-liquid mixture refrigerant flowing in from the chamber inlet 510 can come into contact with the desiccant in the drying pack 3 over a longer path, and thus be fully dried by it. The connecting portion 505 is located between the first cavity 501 and the second cavity 502 along the refrigerant flow direction, and connects the first cavity 501 and the second cavity 502 respectively.

[0104] As described above, a partition structure can be provided inside the gas-liquid separation chamber 50. This partition structure divides the gas-liquid separation chamber 50 into a first chamber 501 and a second chamber 502, and is configured to connect the first chamber 501 and the second chamber 502 to allow refrigerant to flow from the first chamber 501 to the second chamber 502. The partition structure extends from top to bottom along the height direction Y of the compressor 2. Specifically, in Figure 20 In the embodiment shown, the partition structure includes the first partition 503, the second partition 504, and the connecting portion 505 described above.

[0105] Please continue reading Figure 20 and Figure 21 The housing assembly H, especially the bottom wall of the gas-liquid separation chamber 50 opposite to the opening 54, may be provided with a vent 500. The vent 500 is in fluid communication with the gas-liquid separation chamber 50 and the main body cavity 2000 of the housing assembly H. In the direction of the axis X of the compressor 2, the vent 500 and the compressor intake port 101 are located on the same side of the compression component 250 (i.e., the moving scroll plate 251 and the stationary scroll plate 252), that is, on the upstream side of the compression component 250, so as to realize the gas replenishment and enthalpy increase function of the thermal management system.

[0106] Specifically, the pore size of the vent 500 can be, for example, approximately 1mm-2mm, and the vent 500 can be disposed on the bottom wall of the first cavity 501 opposite to the opening 54, and located at the top of the gas-liquid separation chamber 50. Under the action of gravity, the gaseous refrigerant dried by the drying package 3 flows upward (e.g., Figure 19 (The middle arrow points to the vent 500), the liquid refrigerant remains at the bottom of the first cavity 501, and when the height of the liquid refrigerant is greater than the height of the first partition 503, the liquid refrigerant flows into the second cavity 502 through the connecting part 505 (as shown in the image). Figure 19 (The arrow pointing to the left is located above the first partition 503). The upward-flowing gaseous refrigerant can enter the upstream side of the compression component 250 in the main body cavity 2000 through the vent 500, and mix with the refrigerant drawn in from the suction port 101, and then be further compressed by the compression component 250. This can increase the discharge volume and discharge temperature of the compressor 2, increase the heating capacity and energy efficiency ratio of the thermal management system, and realize the function of gas replenishment and enthalpy increase. At the same time, since the gaseous refrigerant entering the main body cavity 2000 through the vent 500 has been fully dried by the drying package 3, the problem of liquid slugging in the compressor 2, which would damage the components inside the compressor, can be avoided.

[0107] In one embodiment, a stop 55 may also be provided in the gas-liquid separation chamber 50 to stop the gas-liquid mixed refrigerant, so that the gaseous refrigerant flowing in from the chamber inlet 510 must pass through the drying pack 3 before entering the main body chamber 200 through the air hole 500. This further effectively avoids the gaseous refrigerant from flowing directly into the main body chamber 2000 through the air hole 500 without being dried by the drying pack 3, which would cause liquid slugging in the compressor 2.

[0108] Please continue reading Figure 20 and Figure 21 The second chamber 502 of the gas-liquid separation chamber 50 is located upstream of the compression component 250, and is equipped with multiple heat exchange fins 52. This arrangement allows the high-temperature liquid refrigerant flowing into the second chamber 502 to exchange heat with the low-temperature gaseous refrigerant located upstream of the compression component 250 in the compressor body cavity 2000, thereby increasing the temperature of the low-temperature gaseous refrigerant in the body cavity 2000 and improving the efficiency of the compressor 2. Correspondingly, the temperature of the high-temperature liquid refrigerant in the second chamber 502 will decrease, allowing the part containing the drying bottle 5 to simultaneously function as an internal heat exchanger (e.g., Figure 45 The portion within the gas-liquid separation chamber 50, designated as 9), can serve as the high-pressure side of the internal heat exchanger (e.g., ...). Figure 45 The portion of the body cavity 2000 located upstream of the compression component 250 can serve as the low-pressure side of the internal heat exchanger (e.g., 9H as indicated in the diagram), and the portion of the body cavity 2000 located upstream of the compression component 250 can serve as the low-pressure side of the internal heat exchanger (e.g., 9H as indicated in the diagram). Figure 45The 9L symbol further enhances the integration of the thermal management integrated module 1, while simplifying the structure and reducing costs, avoiding problems such as high cost, complex structure, and low integration caused by additional internal heat exchangers.

[0109] To further improve the heat exchange effect between the refrigerant in the second cavity 502 and the refrigerant in the corresponding main cavity 2000, a baffle 53 (such as...) can also be provided in the second cavity 502. Figure 20 and Figure 21 As shown), a tortuous flow channel is formed within the second cavity 502, and heat exchange fins 52 can be arranged along this tortuous flow channel. This extends the flow path of the liquid refrigerant within the second cavity 502, thereby enabling sufficient heat exchange with the refrigerant within the main body cavity 2000. In an embodiment not shown, two baffles 53 may be provided within the second cavity 502. The baffle 53 near the partition 503 extends from the side wall at the top of the gas-liquid separation chamber 50 towards the bottom and is a certain distance from the bottom; the baffle 53 near the cavity outlet 520 extends from the side wall at the bottom of the gas-liquid separation chamber 50 towards the top and is a certain distance from the top, thus forming a tortuous flow channel within the second cavity 502. In another embodiment, as shown... Figure 20 As shown, a baffle plate 53 may be provided in the second cavity 502. The baffle plate 53 extends from the side wall at the bottom of the gas-liquid separation chamber 50 toward the top and is a certain distance from the top to form a tortuous flow channel in the second cavity 502. Of course, this disclosure is not limited to the number of baffle plates 53 mentioned above. For example, three or more baffle plates 53 may be provided in the second cavity 502, and the extension direction of the baffle plates 53 is not particularly limited, as long as the fluid entering the second cavity 502 can flow along the tortuous flow channel.

[0110] To further enhance the integration of the thermal management integrated module 1 and avoid setting too many flow channels in the housing assembly H, the housing assembly H also has a first flow channel junction 6 and a second flow channel junction 7. The refrigerant discharged from the exhaust port 102 of the compressor 2 flows to the first flow channel junction 6, and the refrigerant leaving from the second flow channel junction 7 flows to the suction port 101 of the compressor 2. The first flow channel junction 6 and the second flow channel junction 7 can be defined as the first end and the second end of the bypass channel 103, respectively (or, the bypass channel 103 can be defined by the first flow channel junction 6 and the second flow channel junction 7). The second flow channel junction 7 can be connected to the suction port 101 of the compressor 2 via the first heat exchanger 30.

[0111] Specifically, such as Figure 25 and Figure 26As shown, the first flow channel junction 6 is located in the control unit housing H3. This first flow channel junction 6 can be the junction of the first exhaust flow channel 1401, the second exhaust flow channel 1402, and the bypass channel 103 (or secondary flow channel 1302), and can serve as one end of the aforementioned three flow channels. The first flow channel junction 6 can be connected to the exhaust port 102 of the compressor 2 through the first exhaust flow channel 1401, connected to the first fluid inlet 401 of the second heat exchanger 40 through the second exhaust flow channel 1402, and connected to the second flow channel junction 7 through the bypass channel 103. This allows the refrigerant flowing out of the exhaust port 102 to reach the first flow channel junction 6 via the first exhaust flow channel 1401, where it splits into two branches: the first branch flows to the second heat exchanger 40 via the second exhaust flow channel 1402; the second branch flows to the second flow channel junction 7 via the bypass channel 103 (see also [reference]). Figure 25 , Figure 26 and Figure 27 (As indicated by the arrow in the image).

[0112] Please see Figure 27 , Figure 28 and Figure 29 The second flow channel junction 7 is located in the suction section housing H2. This second flow channel junction 7 can be the junction of the main flow channel 1300, the bypass channel 103 (or auxiliary flow channel 1031), and the inlet flow channel 1100, and can serve as one end of these three flow channels. The second flow channel junction 7 can be connected to the first fluid outlet 402 of the second heat exchanger 40 via the main flow channel 1300, to the first flow channel junction 6 via the bypass channel 103, and to the first fluid inlet 301 of the first heat exchanger 30 via the inlet flow channel 1100. This allows the refrigerant flowing from the first fluid outlet 402 of the second heat exchanger 40 and through the main flow channel 1300 to the second flow channel junction 7 to merge with the refrigerant flowing from the bypass channel 103 to the second flow channel junction 7 at the second flow channel junction 7. The merged refrigerant can then flow through the inlet flow channel 1100 to the first heat exchanger 30 and finally return to the compressor's suction port 101 (see also [reference]). Figure 1 , Figures 27 to 29 (As indicated by the arrow in the image).

[0113] The above structure and combination Figure 1 and Figure 45As can be seen, the above-described arrangement of this disclosure allows the refrigerant discharged from the exhaust port 102 of the compressor 2 to flow to the first flow channel junction 6, where it splits into two branches. The first branch flows through the second heat exchanger 40 to the main flow channel 1300 and then to the second flow channel junction 7; the second branch flows through the bypass channel 103 to the second flow channel junction 7, causing the first and second branches to merge at the second flow channel junction 7. The merged refrigerant can then flow back through the first heat exchanger 30 to the suction port 101 of the compressor 2. It should be noted that the second branch is only used when the thermal management system is in the compressor's low-temperature heating mode. Furthermore, the fluid from the first branch undergoes gas-liquid separation after entering the gas-liquid separation chamber 50 of the drying bottle 5. The gaseous refrigerant can then flow directly back through the vent 500 to the suction section 21 of the compressor 2, where it mixes with the refrigerant drawn in from the suction port 101 and is recompressed (e.g., Figure 45 (As shown by the dotted line in the lower left corner), it realizes the function of replenishing qi and increasing enthalpy.

[0114] Preferably, in order to monitor the operating status of compressor 2 and optimize the precise control of compressor 2, the fluid management device may further include a sensing device 90, such as... Figure 1 and Figure 12 As shown, the sensing device 90 may include a first sensor 91 and a second sensor 92. The first sensor 91 is disposed near the exhaust port 102 and is used to sense the temperature and / or pressure of the refrigerant discharged from the exhaust port 102. The second sensor 92 is disposed near the suction port 101 and is used to sense the temperature and / or pressure of the refrigerant drawn into the suction port 101. In one embodiment, the first sensor 91 may be mounted on the exhaust housing H3 and fluidly connected to the exhaust port 102, and the second sensor 92 may be disposed on the suction housing H2 and fluidly connected to the suction port 101. This arrangement allows for accurate sensing of the temperature and / or pressure at the suction port 101 and the exhaust port 102, providing a more precise basis for the control of the compressor 2 and monitoring the operating status of the compressor 2, which helps technicians to promptly identify potential faults.

[0115] The following description will focus on different embodiments of this disclosure. For simplicity, the differences between the embodiments will be detailed, while similarities will not be repeated. Furthermore, identical elements in the embodiments of this disclosure are designated with the same reference numerals to facilitate comparison between the embodiments.

[0116] Figures 32 to 37 A second embodiment of the thermal management integrated module 1 of this disclosure is shown, the main difference between the second embodiment and the first embodiment being the related settings of the drying bottle 5.

[0117] Specifically, the drying bottle 5 includes a gas-liquid separation chamber 50 and a drying package (not shown) disposed within the gas-liquid separation chamber 50. The gas-liquid separation chamber 50 is also part of the main flow channel 1300, but it is defined by the intake housing H2 and the exhaust housing H3. In one embodiment, as... Figure 33 and Figure 34 As shown, the gas-liquid separation chamber 50 may include a first sub-chamber 55 and a second sub-chamber 56. The first sub-chamber 55 may be formed at the outer edge of the intake housing H2, generally in the shape of a groove and having an opening facing the exhaust housing H3; the second sub-chamber 56 may be formed at the outer edge of the exhaust housing H3, generally in the shape of a groove and having an opening facing the intake housing H2 (that is, the first sub-chamber 55 and the second sub-chamber 56 are open to each other). When the intake housing H2 and the exhaust housing H3 are fixedly installed, the first sub-chamber 55 and the second sub-chamber 56 can close their openings and jointly define a sealed chamber, namely the gas-liquid separation chamber 50. This arrangement simplifies the structure of the drying bottle 5 and avoids the problem of complicated installation caused by the additional cover plate. Preferably, the thermal management integrated module 1 may also include a sealing element surrounding the first sub-chamber 55 and the second sub-chamber 56 and sandwiched between the intake housing H2 and the exhaust housing H3 to prevent fluid leakage.

[0118] Please continue reading Figure 33 and Figure 34 The gas-liquid separation chamber 50 has a chamber inlet 510 and a chamber outlet 520. The gas-liquid mixed refrigerant can enter the gas-liquid separation chamber 50 of the dryer bottle 5 through the chamber inlet 510 for gas-liquid separation. The separated liquid refrigerant can be discharged from the dryer bottle 5 through the chamber outlet 520. The chamber inlet 510 can be located on the exhaust housing H3, particularly on the bottom wall of the second sub-chamber 56 opposite to the opening (e.g.,...). Figure 34 As shown), and fluidly connected to the inlet of the main flow channel 1300 (i.e., the second connection port 1311 that is connected to the first fluid outlet 402 of the second heat exchanger 40, as shown). Figure 36 (As shown). The cavity outlet 520 can be provided on the intake housing H2, especially on the bottom wall of the first sub-chamber 55 opposite to the opening (e.g. Figure 33 (As shown by the dashed line in the diagram), and fluidly connected to the outlet of the main flow channel 1300 (i.e., at the junction of the second flow channel 7, as shown in the diagram). Figure 37(As shown). With this configuration, the gas-liquid mixed refrigerant flowing from the first fluid outlet 402 of the second heat exchanger 40 can enter the main flow channel 1300 via the second connection port 1311, and then enter the gas-liquid separation chamber 50 at a certain speed via the cavity inlet 510, impacting the inner wall of the drying bottle 5, thus promoting the separation of the gaseous and liquid refrigerants. The liquid refrigerant flows to the bottom of the gas-liquid separation chamber 50 under gravity and flows to the outlet of the main flow channel 1300 via the cavity outlet 520, as shown. Figure 36 As indicated by the arrow in the diagram. The gaseous refrigerant flows to the top of the gas-liquid separation chamber 50, thereby achieving gas-liquid separation.

[0119] In one embodiment, such as Figure 36 As shown, the main channel 1300 may include an inclined channel 1320, one end of which (i.e., the inlet of the inclined channel 1320) is connected to the inlet of the main channel 1300 (i.e., the second connection port 1311), and this end and the cavity outlet 520 of the gas-liquid separation chamber 50 may be arranged coaxially. The other end (i.e., the outlet of the inclined channel 1320) is connected to the cavity inlet 510. The gas-liquid mixed refrigerant can impact the inner wall of the gas-liquid separation chamber 50 under the guidance of the inclined channel 1320, promoting gas-liquid separation and preventing the gas-liquid mixed refrigerant from directly rushing to the cavity outlet 520. At the same time, it can also prevent the dryer package from impacting the cavity outlet 520 and causing blockage and refrigerant flow resistance.

[0120] A drying pack (not shown) is provided inside the gas-liquid separation chamber 50 to absorb moisture from the gas-liquid mixture of refrigerant flowing into the gas-liquid separation chamber 50 from the chamber inlet 510. In this embodiment, the drying pack can be placed horizontally and extends from near the chamber inlet 510 of the second sub-chamber 56 to near the chamber outlet 520 of the first sub-chamber 55 to fully dry the refrigerant entering the gas-liquid separation chamber 50.

[0121] In this embodiment, the portion containing the drying bottle 5 can be used as an internal heat exchanger (e.g., ...). Figure 46 Use the 9) marked in the middle.

[0122] Specifically, when at least a portion of the first sub-chamber 55 of the gas-liquid separation chamber 50 is located upstream of the compression component 250, the high-temperature, high-pressure refrigerant in the gas-liquid mixture within that portion of the first sub-chamber 55 can exchange heat with the low-temperature gaseous refrigerant located upstream of the compression component 250 within the compressor body cavity 2000. This causes the temperature of the low-temperature gaseous refrigerant within the body cavity 2000 to rise, and causes more of the gaseous refrigerant in the gas-liquid mixture within the first sub-chamber 55 to condense into liquid refrigerant, thus realizing the function of the internal heat exchanger 9. At least a portion of the first sub-chamber 55 can serve as the high-pressure side of the internal heat exchanger (e.g., Figure 46The portion of the body cavity 2000 located upstream of the compression component 250 (as indicated by 9H in the diagram) can serve as the low-pressure side of the internal heat exchanger (e.g., the portion marked 9H in the diagram). Figure 46 The 9L symbol further enhances the integration of the thermal management integrated module 1, while simplifying the structure and reducing costs. This avoids problems such as high cost, complex structure, and low integration caused by additional internal heat exchangers. At this time, a vent (not shown) can also be provided on the side wall of the first sub-chamber 55 of the gas-liquid separation chamber 50. This vent connects the gas-liquid separation chamber 50 and the main body chamber 2000, and is located upstream of the compression component 250 in the direction of the X axis of the compressor 2. This arrangement enables the gas replenishment and enthalpy increase function of the thermal management system. The specific principle is as described in the first embodiment, and therefore will not be repeated here.

[0123] When the position of the first sub-chamber 55 of the gas-liquid separation chamber 50 corresponds to the position of the compression component 250 (no part of the first sub-chamber 55 is located upstream of the compression component 250), the temperature difference between the refrigerant in the gas-liquid separation chamber 50 and the refrigerant at the compression component 250 in the main body chamber 2000 is small. At this time, the part where the drying bottle 5 is located is usually not used as an internal heat exchanger.

[0124] Furthermore, another difference between the thermal management integrated module 1 of the second embodiment and the first embodiment is that the placement position of the first sensor 91 is different.

[0125] Specifically, such as Figure 32 and Figure 35 As shown, in this embodiment, the first sensor 91 can be disposed on the main flow channel 1300 to sense the temperature and / or pressure of the refrigerant there. More specifically, in addition to the gas-liquid separation chamber 50 and the mounting chamber 820 for mounting the main throttling device 82, the main flow channel 1300 also has another mounting chamber 910, such as... Figure 35 As shown, the mounting cavity 910 can be located downstream of the gas-liquid separation cavity 50 and upstream of the mounting cavity 820. The first sensor 91 can be at least partially mounted within the mounting cavity 920 and fluidly connected to the main flow channel 1300 to sense the temperature and / or pressure of the refrigerant there. Since the first sensor 91 is located upstream of the main throttling device 82 for throttling and pressure reduction, and relatively close to the exhaust port 102 of the compressor 2, the sensed value of the first sensor 91 can roughly reflect the pressure and / or temperature at the exhaust port 102. Of course, this disclosure is not limited to this; for example, the first sensor can also be located upstream of the second heat exchanger 40, thus more accurately reflecting the pressure and / or temperature at the exhaust port 2. Preferably, the first sensor 91 can be configured such that its axis is perpendicular to the height direction Y of the compressor 2 to further reduce the overall package volume of the thermal management integrated module 1.

[0126] The above structure and combination Figure 32and Figure 46 As can be seen, the above-mentioned arrangement in this embodiment allows the refrigerant discharged from the exhaust port 102 of the compressor 2 to flow to the first flow channel junction point 6, and to split into two branches at the first flow channel junction point 6. The first branch can flow to the main flow channel 1300 via the second heat exchanger 40 and then to the second flow channel junction point 7. The second branch can flow to the second flow channel junction point 7 via the bypass channel 103, so that the first branch and the second branch merge at the second flow channel junction point 7. The merged refrigerant can flow back to the suction port 101 of the compressor 2 via the first heat exchanger 30. It should be noted that the second branch is only used when the thermal management system is in the compressor low-temperature heating mode.

[0127] In the two embodiments described above, the first fluid / refrigerant in the thermal management integrated module 1 can be a flammable refrigerant (e.g., R290). To avoid safety hazards, this refrigerant does not enter the air conditioning unit. In this case, the thermal management system needs to use a coolant circuit for cooling. However, when the refrigerant used in the thermal management integrated module 1 is a non-flammable refrigerant, the thermal management integrated module 1 can be connected to an external evaporator, and this external evaporator can be installed inside the air conditioning unit. That is, the refrigerant can enter the air conditioning unit, and in this case, the management system 1 can use a refrigerant circuit for cooling.

[0128] The following will describe the specific implementation of the thermal management integrated module 1, which can be connected to an external evaporator, through the third embodiment.

[0129] Figure 38 and Figure 39 A third embodiment of the thermal management integrated module 1 of this disclosure is shown. The main difference between this third embodiment and the first embodiment is that the thermal management integrated module 1 of this embodiment can be connected to an external evaporator.

[0130] Specifically, the housing assembly H may also be provided with a first external interface 93 and a second external interface 94 for connecting an external evaporator 8 (such as...). Figure 47 (As shown). For ease of installation, the first external interface 93 may be located on the cover plate 51 and near the cavity outlet 520 (see Figure 520). Figure 21 The first external interface 93 is located at the location of the compressor 2's exhaust port 102, which is fluidly connected to the external evaporator 8 (e.g., it can be connected to the external evaporator 8's inlet via a pipeline). It is understood that the external evaporator 8's inlet can be equipped with a throttling device, such as an expansion valve. However, this disclosure is not limited to this. For example, the first external interface 93 can also be located on the housing assembly H between the downstream of the drying bottle 5 and the upstream of the first heat exchanger 30, and fluidly connected to the main flow channel 1300 (or fluidly connected to the compressor 2's exhaust port 102). The second external interface 94 can be located on the suction housing H2 (e.g., ...). Figure 39As shown), and fluidly connected to the suction port 101 of the compressor 2, it is mainly used to connect to the outlet of the external evaporator 8 (for example, it can be connected and connected to the outlet of the external evaporator 8 via a pipeline). This arrangement allows the refrigerant discharged from the discharge port 102 of the compressor 2 to circulate to the external evaporator 8 via the first external interface 93 after flowing through the second evaporator 40 and the gas-liquid separation chamber 50 of the main flow channel 1300, and then back to the suction port 101 of the compressor 2 via the second external interface 94 (see reference). Figure 38 and Figure 47 This is used to realize the cooling mode of the thermal management system.

[0131] The above structure and combination Figure 38 , Figure 39 and Figure 47 As can be seen, the above-described configuration in this embodiment allows the refrigerant discharged from the exhaust port 102 of the compressor 2 to flow to the first flow channel junction 6, where it splits into two branches. The first branch flows into the main flow channel 1300 via the second heat exchanger 40 and then to the drying bottle 5 for gas-liquid separation. Subsequently, a portion of the liquid refrigerant can circulate to the external evaporator 8 via the first external interface 93 and return to the suction port 101 of the compressor 2 via the second external interface 94 (e.g., ...). Figure 47 (As shown by the dotted line in the lower left corner), another part of the liquid refrigerant can flow to the second flow channel junction 7; the second branch can flow to the second flow channel junction 7 via the bypass channel 103, so that the other part of the first branch and the second branch merge at the second flow channel junction 7, and the merged refrigerant can flow back to the suction port 101 of the compressor 2 via the first heat exchanger 30. It should be noted that the above-mentioned second branch is only used when the thermal management system is in the compressor low-temperature heating mode.

[0132] Preferably, such as Figure 47 As shown, a throttling device 83 (e.g., an electronic expansion valve) can be installed in the circuit where the external evaporator 8 is located, located between the downstream of the first external interface 93 and the upstream of the external evaporator 8, to throttle and reduce the pressure of the refrigerant flowing out from the external interface 93.

[0133] In addition, it should be noted that, Figure 47 The schematic diagram shows that the bottom wall of the gas-liquid separation chamber 50 of the thermal management integrated module 1 does not have vents 500. However, this disclosure is not limited to this; for example, vents 500 may also be provided on the bottom wall of the gas-liquid separation chamber 50 (see [reference]). Figures 19 to 21This allows the gaseous refrigerant after gas-liquid separation to enter the upstream side of the compression component 250 in the main body cavity 2000 through the vent 500, and mix with the refrigerant drawn in from the suction port 101. Then it is further compressed by the compression component 250 to increase the discharge volume and discharge temperature of the compressor 2, increase the heating capacity and energy efficiency ratio of the thermal management system, and realize the function of gas replenishment and enthalpy increase.

[0134] The following will combine Figures 40 to 44 The thermal management integrated module 1 of the fourth embodiment of this disclosure will now be introduced.

[0135] The main difference between the thermal management integrated module 1 in the fourth embodiment and the third embodiment is that, in this embodiment, the housing assembly H of the compressor 2 only includes the suction housing H2 and the exhaust housing H3, and no longer has a separately provided control housing H1. Alternatively, it can be considered that the suction housing and the control housing in this embodiment are integrally formed and collectively referred to as the suction housing H2. This arrangement can further improve the integration of the thermal management integrated module 1, save installation time, and further reduce the risk of fluid leakage.

[0136] Specifically, such as Figures 40 to 43 As shown, in this embodiment, the intake housing H2 has a control cavity 1000 at one end near the first heat exchanger 30. This cavity houses electronic components, such as inverters and microcontrollers, and is primarily used to control the compressor's start-up, operation, and protection. The control cavity 1000 has a cavity opening 1001 on the side facing the first heat exchanger 30 (e.g., ...). Figure 43 As shown, multiple electronic components can be fixedly installed into the control cavity 1000 through the cavity opening 1001.

[0137] In one embodiment, multiple electronic components may be disposed on a printed circuit board to form a control board 100 (e.g., Figure 41 and Figure 42 As shown, the control plate 100 can enter the control cavity 1000 through the cavity opening 1001 and be fixed in the control cavity 1000. The cavity opening 1001 can be closed by the end plate of the first heat exchanger 30, or it can be closed by an independent control cavity cover plate made of thermally conductive material. For details, please refer to the relevant description in the first embodiment, which will not be repeated here.

[0138] As mentioned above, this embodiment no longer has a separately provided control housing H1, therefore, this embodiment does not have the auxiliary flow channel 1031 defined by the control housing H1 and the intake housing H2 as in the previous embodiments. That is, in this embodiment, the bypass channel 103 provided in the housing assembly H only includes the secondary flow channel 1032, one end of which is connected to the first flow channel junction point 6, and the other end is connected to the second flow channel junction point 7 (e.g., ...). Figure 40As shown by the dotted line in the diagram, the refrigerant flowing out of the discharge port 102 of the compressor 2 flows into the secondary flow channel 1032 (or bypass channel 103) through the first flow channel junction 6, and then flows to the second flow channel junction 7. After passing through the first heat exchanger 30, it flows back to the suction port 101 of the compressor 2 to realize the hot gas bypass function of the compressor.

[0139] Specifically, such as Figures 40 to 43 As shown, the secondary flow channel 1032 may include: a mounting cavity 810 for mounting a fluid management device; a first portion 1032a and a second portion 1032b located on both sides of the mounting cavity 810 and in fluid communication with it respectively; and a third portion 1032c connecting the second portion 1032b to the second flow channel junction 7. The first portion 1032a may be a generally straight channel extending along the X-axis of the compressor 2, formed in the intake housing H2 and the exhaust housing H3, with one end in fluid communication with the first flow channel junction 6 and the other end in fluid communication with the mounting cavity 810. The second portion 1032b may be a generally straight channel extending along the X0-axis of the mounting cavity 810, with the angle between the straight channel and the straight channel of the first portion 1032a being approximately an obtuse angle. The second portion 1032b is formed in the intake housing H2, with one end in fluid communication with the mounting cavity 810 and the other end in fluid communication with the third portion 1032c. The third part 1032c can be generally a straight channel extending along the height direction of the compressor 2, and the angle between this straight channel and the straight channel of the second part 1032b is approximately an obtuse angle. The third part 1032c is formed in the suction housing H2, and one end of it is fluidly connected to the second part 1032b, and the other end is fluidly connected to the second flow channel junction 7. This arrangement allows the refrigerant discharged from the discharge port 102 of the compressor 2 to flow through the first flow channel junction 6 to the secondary flow channel 1032, and then to the second flow channel junction 7, and then back to the suction port 101 of the compressor 2 via the first heat exchanger 30, realizing the hot gas bypass function of the compressor.

[0140] A fluid management device may be at least partially installed in the mounting cavity 810 for managing the opening and closing, flow direction, flow rate, and / or temperature of the fluid in the bypass channel 103 / secondary flow channel 1032. In this embodiment, the fluid management device may include a throttling device 80, which includes a secondary throttling device 81 (e.g., an electronic expansion valve). The secondary throttling device 81 may be at least partially installed in the mounting cavity 810 and is in fluid communication with the secondary flow channel 1032 for regulating the flow rate, pressure, etc. of the fluid in the secondary flow channel 1032.

[0141] Please continue to refer to this. Figure 43In this embodiment, both the inlet channel 1100 and the outlet channel 1200 are formed only in the suction section housing H2 and are fluidly connected to the first heat exchange channel (e.g., the refrigerant heat exchange channel) of the first heat exchanger 30. One end of the inlet channel 1100 is fluidly connected to the second channel junction 7, and the other end is fluidly connected to the first fluid inlet 301 of the first heat exchanger 30, so that the fluid in the secondary channel 1032 (or bypass channel 103) can enter the first heat exchange channel of the first heat exchanger 30 via the second channel junction 7, the inlet channel 1100, and the first fluid inlet 301. One end of the outlet channel 1200 is fluidly connected to the first fluid outlet 302 of the first heat exchanger 30, and the other end is fluidly connected to the suction port 101 of the compressor 2, so that the fluid in the first heat exchange channel of the first heat exchanger 30 can flow back to the suction port 101 of the compressor 2 via the first fluid outlet 302 and the outlet channel 1200.

[0142] The above structure and combination Figures 40 to 44 , Figure 47 As can be seen, the above-described configuration in this embodiment allows the refrigerant discharged from the exhaust port 102 of the compressor 2 to flow to the first flow channel junction 6, where it splits into two branches. The first branch flows into the main flow channel 1300 via the second heat exchanger 40 and then to the drying bottle 5 for gas-liquid separation. Subsequently, a portion of the liquid refrigerant can circulate to the external evaporator 8 via the first external interface 93 and return to the suction port 101 of the compressor 2 via the second external interface 94 (e.g., ...). Figure 47 (As shown by the dotted line in the lower left corner), another part of the liquid refrigerant can flow to the second flow channel junction 7; the second branch can flow to the second flow channel junction 7 through the bypass channel 103, so that the other part of the first branch and the second branch merge at the second flow channel junction 7, and the merged refrigerant can flow back to the suction port 101 of the compressor 2 through the first heat exchanger 30.

[0143] In summary, this disclosure provides a thermal management integrated module, which includes a compressor with a housing assembly and a first heat exchanger and a second heat exchanger disposed on both sides of the compressor. The compressor housing assembly includes an intake port, an exhaust port, a main flow channel, a bypass channel, an inlet flow channel, an outlet flow channel, and an exhaust flow channel. The first heat exchanger has a first heat exchange channel that is fluidly connected to both the inlet and outlet flow channels, and the second heat exchanger has a first heat exchange channel that is fluidly connected to both the exhaust channel and the main flow channel. Refrigerant discharged from the compressor's exhaust port can sequentially flow through the exhaust channel, the first heat exchange channel of the second heat exchanger, the main flow channel, the inlet channel, the first heat exchange channel of the first heat exchanger, and the outlet flow channel, before returning to the compressor via the intake port, thus forming the main refrigerant circuit. Furthermore, refrigerant discharged from the compressor's exhaust port can also sequentially flow through a portion of the exhaust channel (i.e., the first exhaust channel), the bypass channel, the inlet channel, the first heat exchange channel of the first heat exchanger, and the outlet flow channel, before returning to the compressor via the intake port, thus forming a hot gas bypass circuit for the refrigerant. The aforementioned structural configuration of the thermal management integrated module effectively improves integration, reduces space occupation, lowers costs, and reduces the risk of fluid leakage. Furthermore, the compressor housing assembly has a control cavity for housing electronic components, etc. The first heat exchanger is installed near the control cavity, effectively cooling the control cavity and thus dissipating heat from the electronic components. Further, the end plate of the first heat exchanger can also serve as a cover plate for the control cavity, further improving the integration of the thermal management integrated module and bringing the first heat exchanger closer to the control cavity, further enhancing the cooling effect of the first heat exchanger on the electronic components within the control cavity / control section. Moreover, the main flow channel includes a gas-liquid separation chamber, meaning that the drying bottle of this disclosure can be integrated into the housing assembly H. This not only improves the integration of the thermal management integrated module and avoids the problems of high cost and high fluid leakage risk caused by additional drying bottles, but also achieves gas-liquid separation of the refrigerant, preventing liquid slugging in the compressor. This disclosure arranges at least a portion of the gas-liquid separation chamber upstream of the compression component, i.e., along the compressor's axial direction, at least a portion of the gas-liquid separation chamber is located on the same side of the compression component as the suction port. This allows the high-temperature refrigerant in the gas-liquid separation chamber to exchange heat with the low-temperature refrigerant in the compressor's internal cavity. In this case, the gas-liquid separation chamber can cooperate with the upstream of the compression component within the compressor body cavity as an internal heat exchanger, further effectively improving the integration of the thermal management integrated module. Furthermore, the top of the drying bottle can be provided with a vent connecting the gas-liquid separation chamber and the suction port, allowing the gaseous refrigerant after gas-liquid separation to flow back into the compressor's internal cavity through this vent, mix with the refrigerant drawn in through the suction port, and be further compressed by the compression component, thus achieving the compressor's gas replenishment and enthalpy increase function.In addition, the compressor housing assembly may also be provided with a first flow channel junction point for diverting flow and a second flow channel junction point for merging flow. The first flow channel junction point may be the junction point of the first exhaust flow channel, the second exhaust flow channel and the bypass channel, so that the refrigerant discharged from the exhaust port can reach the first flow channel junction point through the first exhaust flow channel and be diverted to the second exhaust flow channel and the bypass channel respectively. The second flow channel junction point may be the junction point of the main flow channel, the bypass channel and the inlet flow channel, so that the refrigerant in the bypass channel and the main flow channel can merge and flow into the inlet flow channel at the second flow channel junction point. This configuration can avoid setting too many flow channels and further improve the integration of the thermal management integrated module.

[0144] This disclosure also provides an on-board thermal management system, which may include the aforementioned thermal management integration module.

[0145] The foregoing description of exemplary embodiments of the thermal management integrated module and vehicle thermal management system provided by this disclosure refers to preferred embodiments. However, those skilled in the art will understand that various modifications and alterations can be made to the above specific embodiments without departing from the spirit of this disclosure, and various combinations can be made to the various technical features and structures proposed in this disclosure without exceeding the protection scope of this disclosure, which is determined by the appended claims.

Claims

1. A thermal management integrated module (1), the thermal management integrated module (1) comprising a compressor (2) and a fluid management device, characterized in that, The compressor (2) includes a housing assembly (H) having an intake port (101) and an exhaust port (102); The housing assembly (H) further includes a first flow channel joint (6), a second flow channel joint (7), and a bypass channel (103); wherein the bypass channel (103) is defined by the first flow channel joint (6) and the second flow channel joint (7); The fluid management device is located on the bypass channel (103).

2. The thermal management integrated module (1) as described in claim 1, characterized in that, The thermal management integrated module (1) further includes a first heat exchanger (30), and the second flow channel junction (7) is connected to the air intake (101) via the first heat exchanger (30).

3. The thermal management integrated module (1) as described in claim 2, characterized in that, The first flow channel junction (6) is connected to the exhaust port (102) through the first exhaust flow channel (1401); The first flow channel junction (6) also defines a first end of the bypass channel (103); and The first flow channel junction (6) is also connected to the first fluid inlet (401) of the second heat exchanger (40) via the second exhaust flow channel (1402).

4. The thermal management integrated module (1) as described in claim 3, characterized in that, The second flow channel junction (7) is connected to the first fluid outlet (402) of the second heat exchanger (40) via the main flow channel (1300); The second flow channel junction (7) also defines a second end of the bypass channel (103); and The second flow channel junction (7) is also connected to the first fluid inlet (301) of the first heat exchanger (30) via the inlet flow channel (1100).

5. The thermal management integrated module (1) as described in claim 1, characterized in that, The secondary channel (1032) of the bypass channel (103) has a first part (1032a), a second part (1032b) and a mounting cavity (810); the first part (1032a) and the second part (1032b) are respectively connected to and communicate with the mounting cavity (810); The fluid management device is installed in the mounting cavity (810).

6. The thermal management integrated module (1) as described in claim 5, characterized in that, The first portion (1032a) and the second portion (1032b) extend parallel to the axis (X) of the compressor (2) and are offset along the center line (X0) of the mounting cavity (810).

7. The thermal management integrated module (1) as described in claim 5, characterized in that, The second portion (1032b) extends along the centerline (X0) of the mounting cavity (810).

8. The thermal management integrated module (1) as described in claim 1, characterized in that, The housing assembly (H) includes an intake housing (H2) and an exhaust housing (H3); the intake housing (H2) has the intake port (101), and the exhaust housing (H3) has the exhaust port (102).

9. The thermal management integrated module (1) as described in claim 8, characterized in that, The housing assembly (H) further includes a control housing (H1); the intake housing (H2) and the control housing (H1) define an auxiliary flow channel (1031) for the bypass channel (103).

10. A vehicle-mounted thermal management system, characterized in that, The vehicle-mounted thermal management system includes a thermal management integrated module (1) as described in any one of claims 1-9.

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