Three-phase copper bar heat dissipation power assembly and electric vehicle

Abstract

The invention discloses a three-phase copper bar heat dissipation power assembly and an electric vehicle, and relates to the technical field of electric vehicles, the power assembly comprises a driving motor and a three-phase copper bar, an oil cooling loop of the power assembly comprises a circumferential flow channel, a copper bar cooling flow channel and a stator cooling flow channel, the circumferential flow channel is used for receiving oil liquid subjected to heat exchange through a heat exchanger, and the copper bar cooling flow channel is used for cooling the stator cooling flow channel; the copper bar cooling flow channel is used for transmitting oil liquid to cool a three-phase copper bar, the stator cooling flow channel is used for transmitting oil liquid to cool a stator of the driving motor, the circumferential flow channels are distributed in the circumferential direction of the driving motor, and the positions where the circumferential flow channels are communicated with the copper bar cooling flow channel and the positions where the circumferential flow channels are communicated with the stator cooling flow channel are spaced. And the copper bar cooling flow channel and the stator cooling flow channel are used for shunting oil in the circumferential flow channel. According to the embodiment of the invention, the copper bar cooling flow channel bypasses the circumferential flow channel for cooling the motor stator to directly cool the three-phase copper bar, the length of an oil path is shortened, the copper bar cooling flow channel and the stator cooling flow channel are connected in parallel, and the cooling efficiency of the copper bar is improved.

Description

Technical Field

[0001] The present application relates to the technical field of electric vehicles, and in particular to a powertrain and an electric vehicle with three-phase copper busbar heat dissipation. Background Art

[0002] The powertrain of new energy vehicles circulates oil through an internal oil pump to cool heat-generating components such as the stator and reducer of the drive motor.

[0003] With the development of technology, powertrains are moving towards high speed, high integration and high efficiency, and the heat generation of some components is gradually increasing. However, the current powertrain has insufficient heat dissipation capacity for heat-generating components such as three-phase copper busbars, and the design of the internal cooling oil circuit of the powertrain needs to be improved. Summary of the Invention

[0004] The present application provides a powertrain with three-phase copper busbar heat dissipation, the powertrain including a drive motor and a three-phase copper busbar, the drive motor being used to receive alternating current output by a drive motor controller through the three-phase copper busbar, the oil cooling circuit of the powertrain including a circumferential flow channel, a copper busbar cooling flow channel and a stator cooling flow channel, the circumferential flow channel being used to receive oil after heat exchange in a heat exchanger, the copper busbar cooling flow channel being used to transfer oil to cool the three-phase copper busbar, and the stator cooling flow channel being used to transfer oil to cool the stator of the drive motor, wherein: the circumferential flow channel is distributed along the circumference of the drive motor, the position where the circumferential flow channel is connected to the copper busbar cooling flow channel and the position where the circumferential flow channel is connected to the stator cooling flow channel are spaced apart, and the copper busbar cooling flow channel and the stator cooling flow channel are used to divert the oil in the circumferential flow channel. The embodiment of the present application bypasses a copper bar cooling channel on the circumferential flow channel for cooling the motor stator to directly cool the three-phase copper bar, and uses the oil after heat exchange in the heat exchanger received by the circumferential flow channel to cool the three-phase copper bar, thereby improving the utilization efficiency of the oil channel in the powertrain, so that the circumferential flow channel can divert part of the oil to cool the three-phase copper bar; the copper bar cooling channel for cooling the three-phase copper bar in the present application is transferred through the circumferential flow channel to receive the oil after heat exchange in the heat exchanger, and the oil path between the circumferential flow channel and the heat exchanger can be utilized to shorten the oil path length, simplify the structure, and reduce the cost; and the oil in the circumferential flow channel is low-temperature oil that has been heat exchanged by the heat exchanger, and the copper bar cooling channel diverted by the circumferential flow channel is connected in parallel with the stator cooling channel, which prevents the heated oil in the stator cooling channel from entering the copper bar cooling channel and affecting the cooling efficiency of the three-phase copper bar, thereby improving the cooling efficiency of the copper bar.

[0005] In one possible implementation, the position where the circumferential flow channel is connected to the copper bar cooling flow channel and the position where the circumferential flow channel is used to receive the oil after heat exchange in the heat exchanger are spaced apart along the circumference of the drive motor. The radial inner wall of the circumferential flow channel will exchange heat with the stator, and the heat of the stator will gradually heat the flowing oil to appropriately increase the temperature of the oil flowing into the copper bar cooling flow channel from the circumferential flow channel, preventing the low-temperature oil after heat exchange in the heat exchanger from directly entering the copper bar cooling flow channel to cool the high-temperature three-phase copper bar. On the basis of satisfying the cooling of the three-phase copper bar, it prevents the temperature of the three-phase copper bar from changing suddenly and affecting the transmission stability of electric energy. In addition, the heated oil in the circumferential flow channel is also conducive to reducing the viscosity of the oil, improving the uniformity of the oil in the copper bar cooling flow channel sprayed on the three-phase copper bar, thereby improving the cooling efficiency of the three-phase copper bar.

[0006] In one possible implementation, the locations where the circumferential flow channel connects to the copper busbar cooling channel and the locations where the circumferential flow channel connects to the stator cooling channel are spaced apart along the circumference of the drive motor. The oil in the circumferential flow channel flows along the circumference of the stator. When the flow channel reaches the location of the first liquid port, it does not enter the second liquid port, but needs to flow a certain distance along the circumference before entering the second liquid port. This prevents the circumferential flow channel from diverting at the same location, resulting in insufficient oil being received by the copper busbar cooling channel and the stator cooling channel.

[0007] In one possible implementation, the circumferential flow channel is used to receive oil after heat exchange in the heat exchanger through multiple liquid inlet flow channels, and the locations where the multiple liquid inlet flow channels connect to the circumferential flow channel are spaced apart along the circumference of the drive motor. By providing multiple liquid inlet flow channels, and by spacing the third liquid ports connecting the multiple liquid inlet flow channels along the circumference of the drive motor, the amount of oil that the circumferential flow channel can receive after heat exchange in the heat exchanger through the liquid inlet flow channel can be increased, providing sufficient oil for the subsequent diversion copper busbar cooling flow channel and the stator cooling flow channel, and preventing insufficient oil in the circumferential flow channel from affecting the cooling of the stator and three-phase copper busbar.

[0008] In a possible implementation, the shell of the powertrain encloses the motor cavity and the copper bar cooling channel, the motor cavity is used to accommodate the stator of the drive motor, and the copper bar cooling channel is used to pass through the inner wall of the motor cavity and connect to the circumferential channel. The present application encloses the motor cavity and the copper bar cooling channel by the shell, and uses the thickness of the motor cavity wall to synchronously form the copper bar cooling channel. There is no need to make additional designs to the structure, shape and size of the shell, and the preparation cost of the copper bar cooling channel is lower. In addition, the copper bar cooling channel is arranged on the radial outside of the motor cavity and will not interfere with other channels, and there is no need to make changes to the position and structure of other channels.

[0009] In one possible implementation, the inner wall of the motor cavity and the stator of the drive motor enclose the circumferential flow channel, which is used to surround the stator along the circumference of the drive motor. The stator circumferential flow channel serves as a circumferential flow channel, and the formed housing simultaneously encloses a copper bar cooling channel to transport cooling oil to the copper bar. Improvements to the flow channel are all in the housing. For example, the copper bar cooling channel can be injection-molded at the same time as the motor cavity, simplifying the production process of the copper bar cooling channel and reducing production costs.

[0010] In one possible implementation, the circumferential flow channel along the circumference of the drive motor is configured to surround the end windings and spray oil into the end windings through a plurality of oil spray holes extending therethrough. The stator cooling channel is configured to receive oil sprayed from the oil spray holes. The stator winding oil spray ring encloses the circumferential flow channel. The circumferential flow channel receives oil from the heat exchanger, sprays oil to cool the end windings, and distributes oil to the copper busbar cooling channel to cool the three-phase copper busbars.

[0011] In one possible implementation, a portion of the copper bar cooling channel is used to connect to the circumferential channel along the radial direction of the stator, and another portion of the copper bar cooling channel is used to transmit oil along the axial direction of the stator to cool the three-phase copper bar. By extending a portion of the copper bar cooling channel along the radial direction of the stator, one side of the copper bar cooling channel can be close to the circumferential channel and connected to the circumferential channel, thereby ensuring that the oil in the circumferential channel can flow into the copper bar cooling channel. By extending another portion of the copper bar cooling channel along the axial direction of the stator, the copper bar cooling channel can penetrate the inner wall of the motor cavity, thereby allowing the oil in the circumferential channel to be transmitted to the three-phase copper bar through the copper bar cooling channel to dissipate heat for the three-phase copper bar.

[0012] In one possible implementation, the copper busbar cooling channel is used to be located on both sides of the powertrain's axial direction along with the heat exchanger. By locating the copper busbar cooling channel and the heat exchanger on both sides of the powertrain's axial direction to match the three-phase copper busbar configuration on one side of the powertrain, the oil is guided to flow smoothly toward the three-phase copper busbar, dissipating heat for the three-phase copper busbar. Furthermore, the three-phase copper busbar is located on the side of the heat exchanger closest to the motor stator, simplifying the copper busbar cooling channel configuration and avoiding the need for a longer copper busbar cooling channel due to the copper busbar cooling channel being far from the three-phase copper busbar.

[0013] In one possible implementation, the powertrain includes a motor bearing cooling channel, which receives oil from the circumferential channel and transfers the oil to cool the motor bearings of the drive motor. By providing the motor bearing cooling channel, which is in communication with the circumferential channel and the chamber containing the motor bearings, respectively, the oil in the circumferential channel can be transported through the motor bearing cooling channel to the motor bearings, dissipating heat and lubricating the motor bearings, thereby ensuring reliable operation of the motor bearings.

[0014] In one possible implementation, the position where the motor bearing cooling channel communicates with the circumferential channel and the position where the circumferential channel receives the oil after heat exchange in the heat exchanger are spaced apart along the circumference of the drive motor. By spacing the position where the motor bearing cooling channel communicates with the circumferential channel and the position where the circumferential channel receives the oil after heat exchange in the heat exchanger along the circumference of the drive motor, the low-temperature oil in the heat exchanger rises in temperature after flowing through the circumferential channel. The motor bearing cooling channel is used to receive the heated oil in the circumferential channel and transmit it to the motor bearings, thereby reducing the viscosity of the oil flowing through the motor bearings, thereby reducing the operating resistance of the oil to the motor bearings, and thereby improving the operating efficiency of the drive motor.

[0015] In one possible implementation, the motor bearing cooling channel is configured to separately receive the oil after heat exchange in the heat exchanger and the oil from the circumferential channel, and to merge the two oil streams to cool the motor bearing. By having the motor bearing cooling channel separately receive the low-temperature oil after heat exchange in the heat exchanger and the oil from the circumferential channel, and mixing the two oils at different temperatures before transmitting them to the motor bearing, the circumferential channel can be used to regulate the temperature of the oil in the motor bearing cooling channel, controlling the oil to lubricate and cool the motor bearing at an appropriate temperature, thereby achieving an optimal balance between temperature and viscosity.

[0016] In one possible implementation, the powertrain includes a resolver sensor, the motor shaft of the drive motor is fixedly connected to the resolver sensor, and the motor bearing is located on the same side of the drive motor stator as the resolver sensor. By locating the motor bearing and resolver sensor on the same side of the drive motor stator, the resolver sensor can detect the rotational speed of the motor bearing on that side. When the motor bearing rotates too fast, oil flows through the motor bearing cooling channel into the resolver-side motor bearing, ensuring lubrication and heat dissipation of the motor bearing.

[0017] In one possible implementation, the circumferential flow channel receives the oil after heat exchange in the heat exchanger through the liquid inlet channel, and the inner diameter of the copper bar cooling channel is smaller than the inner diameter of the liquid inlet channel. By making the inner diameter of the copper bar cooling channel smaller than the inner diameter of the liquid inlet channel, the inner diameter of the copper bar cooling channel is prevented from being too large and affecting the amount of oil in other liquid inlet channels connected to the circumferential flow channel, thereby improving the cooling efficiency of various components of the drive motor.

[0018] The present application also provides an electric vehicle, including a powertrain and a wheel, wherein the powertrain is used to drive the wheel to rotate. The present application provides a copper bar cooling channel and a stator cooling channel that are both connected to the circumferential channel, so that the oil in the circumferential channel can flow into the three-phase copper bar through the copper bar cooling channel, and flow into the motor stator through the stator cooling channel to improve the heat dissipation of the three-phase copper bar and the motor stator. The position where the copper bar cooling channel and the circumferential channel are connected, and the position where the stator cooling channel and the circumferential channel are connected are spaced apart, so that the circumferential channel distributes oil to the stator cooling channel and the copper bar cooling channel at different positions along the circumference of the drive motor, thereby ensuring that the amount of oil in the copper bar cooling channel and the stator cooling channel is sufficient to improve the heat dissipation effect of the drive motor and the three-phase copper bar, and realize lubrication of the drive motor with oil to improve the operating efficiency of the drive motor, thereby improving the overall performance of the electric vehicle. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 is a schematic diagram of an electric vehicle provided in an embodiment of the present application;

[0020] Figure 2 is a schematic diagram of a powertrain provided in an embodiment of the present application;

[0021] Figure 3 is a schematic diagram of a powertrain provided in an embodiment of the present application;

[0022] Figure 4 This is a schematic diagram of a stator provided in an embodiment of the present application;

[0023] Figure 5 1 is a schematic diagram of a powertrain provided in an embodiment of the present application;

[0024] Figure 6 is a cross-sectional view of a stator provided in an embodiment of the present application;

[0025] Figure 7 This is a schematic diagram of a powertrain with multiple liquid inlet channels connected in parallel, as provided in an embodiment of the present application;

[0026] Figure 8 This is a schematic diagram of a powertrain with multiple liquid inlet channels connected in parallel, as provided in an embodiment of the present application;

[0027] Figure 9 This is a schematic diagram of a stator provided in an embodiment of the present application;

[0028] Figure 10 This is a schematic diagram of a stator provided in an embodiment of the present application;

[0029] Figure 11 This is a schematic diagram of a stator provided in an embodiment of the present application;

[0030] Figure 12 This is a schematic diagram of a stator provided in an embodiment of the present application;

[0031] Figure 13 is a partial schematic diagram of a powertrain provided in an embodiment of the present application;

[0032] Figure 14 is a schematic diagram of a powertrain provided in an embodiment of the present application;

[0033] Figure 15 This is a schematic diagram of a stator provided in an embodiment of the present application;

[0034] Figure 16 is a schematic diagram of a powertrain provided in an embodiment of the present application;

[0035] Figure 17 is a schematic diagram of a powertrain provided in an embodiment of the present application;

[0036] Figure 18 1 is a schematic diagram of a powertrain with a resolver sensor provided in an embodiment of the present application;

[0037] Figure 19 It is a schematic diagram of a powertrain provided in an embodiment of the present application. DETAILED DESCRIPTION

[0038] The embodiments of the present application are described below in conjunction with the drawings in the embodiments of the present application.

[0039] During operation, motors experience frequent changes in operating conditions and generate significant heat, which increases motor temperature and impacts their lifespan and safety. Currently, an oil pump installed within the powertrain drives the oil flow within the powertrain. After cooling through a heat exchanger, the oil flows into the stator of the drive motor to cool it. The cooled oil then flows back into the reducer cavity, where it is absorbed by the oil pump and forms an oil circulation system. Currently, with the development of new energy vehicles, higher requirements are being placed on powertrain cooling efficiency. Currently, the cooling of the three-phase copper busbar is insufficient. The three-phase copper busbar generates heat when transmitting power from the power battery to the drive motor. Without effective heat dissipation, the service life of the busbar is shortened.

[0040] In response to the above problems, an embodiment of the present application provides a powertrain with three-phase copper busbar heat dissipation, wherein the powertrain includes a drive motor and a three-phase copper busbar, the drive motor is used to receive the alternating current output by the motor controller through the three-phase copper busbar, the oil cooling circuit of the powertrain includes a circumferential flow channel, a copper busbar cooling flow channel and a stator cooling flow channel, the circumferential flow channel is used to receive the oil after heat exchange in the heat exchanger, the copper busbar cooling flow channel is used to transfer oil to cool the three-phase copper busbar, and the stator cooling flow channel is used to transfer oil to cool the stator of the drive motor, wherein: the circumferential flow channel is distributed along the circumference of the drive motor, the position where the copper busbar cooling flow channel is connected to the circumferential flow channel and the position where the stator cooling flow channel is connected to the circumferential flow channel are spaced apart, and the copper busbar cooling flow channel and the stator cooling flow channel are used to divert the oil in the circumferential flow channel. The embodiment of the present application bypasses a copper bar cooling channel on the circumferential flow channel for cooling the motor stator to directly cool the three-phase copper bar, and uses the oil after heat exchange in the heat exchanger received by the circumferential flow channel to cool the three-phase copper bar, thereby improving the utilization efficiency of the oil channel in the powertrain, so that the circumferential flow channel can divert part of the oil to cool the three-phase copper bar; the copper bar cooling channel for cooling the three-phase copper bar in the present application is transferred through the circumferential flow channel to receive the oil after heat exchange in the heat exchanger, and the oil path between the circumferential flow channel and the heat exchanger can be utilized to shorten the oil path length, simplify the structure, and reduce the cost; and the oil in the circumferential flow channel is low-temperature oil that has been heat exchanged by the heat exchanger, and the copper bar cooling channel diverted by the circumferential flow channel is connected in parallel with the stator cooling channel, which prevents the heated oil in the stator cooling channel from entering the copper bar cooling channel and affecting the cooling efficiency of the three-phase copper bar, thereby improving the cooling efficiency of the copper bar.

[0041] An embodiment of the present application provides an electric vehicle. Figure 1 Schematic diagram of an electric vehicle 1 provided in an embodiment of the present application. Figure 1 As shown, the electric vehicle 1 includes a powertrain 10 and a plurality of wheels 20. The powertrain 10 is capable of providing power to the wheels 20 of the electric vehicle 1. The powertrain 10 and the wheels 20 are in transmission connection. The powertrain 10 is used to drive the plurality of wheels 20 to rotate, thereby driving the electric vehicle 1 forward or backward. In one embodiment, the electric vehicle 1 is a front-wheel drive vehicle or a rear-wheel drive vehicle, and the powertrain 10 is used to drive the front wheels or the rear wheels of the electric vehicle 1. In one embodiment, the electric vehicle 1 is a two-wheel drive vehicle or a four-wheel drive vehicle, and the powertrain 10 is used to drive two wheels 20 or four wheels 20 of the electric vehicle 1 to rotate.

[0042] In one embodiment, the electric vehicle 1 further includes a power battery 30, which is used to store electrical energy input from an external power source and also to power the powertrain 10. The powertrain 10 receives electrical energy from the power battery 30 and converts it into mechanical energy to drive the wheels 20 to rotate.

[0043] In the embodiment of the present application, the electric vehicle 1 includes a two-wheeled, three-wheeled, or four-wheeled vehicle. In the embodiment of the present application, the electric vehicle 1 includes a pure electric vehicle (BEV), a hybrid electric vehicle (HEV), and a range-extended electric vehicle (REEV). In one embodiment, the electric vehicle 1 is a vehicle, for example, a commercial vehicle, a passenger car, a motorcycle, or a flying vehicle.

[0044] An embodiment of the present application provides a powertrain 10 . Figure 2 Schematic diagram of the powertrain 10 provided in the embodiment of the present application. Figure 2 As shown, the powertrain 10 includes a housing 100, a drive motor 200, and a reducer 300. The housing 100 is used to enclose and fix the drive motor 200 and the reducer 300. The drive motor 200 is used to drive the reducer 300. The drive motor 200 is used to convert electrical energy into mechanical energy and drive the wheels 20 of the electric vehicle 1 through the reducer 300.

[0045] See also Figure 2 、 Figure 3 and Figure 4 , Figure 3 is a schematic diagram of a powertrain 10 provided in an embodiment of the present application. Figure 4 It is a schematic diagram of the stator 210 provided in an embodiment of the present application. In one embodiment, the housing 100 encloses a motor cavity 110 and a reducer cavity 120, the motor cavity 110 is used to accommodate the stator 210 and the rotor 220 of the drive motor 200, and the reducer cavity 120 is used to accommodate the transmission parts such as the transmission shaft and gears of the reducer 300. In one embodiment, a portion of the rotor 220 of the drive motor 200 along the axial direction of the power assembly 10 passes through the motor cavity 110 into the reducer cavity 120, and is rotatably connected to the input shaft of the reducer 300 in the reducer cavity 120, so as to drive the input shaft to rotate through the rotation of the rotor 220. In one embodiment, the input shaft of the reducer 300 along the axial direction of the power assembly 10 passes through the reducer cavity 120 into the motor cavity 110, and is rotatably connected to the rotor 220 of the drive motor 200 in the motor cavity 110, so as to drive the input shaft to rotate through the rotation of the rotor 220.

[0046] See also Figure 1 、 Figure 2 、 Figure 3 and Figure 5 , Figure 5It is a schematic diagram of the powertrain 10 provided in an embodiment of the present application. In one embodiment, the powertrain 10 includes an oil pump 400 and a heat exchanger 500. The oil pump 400 is used to recover the oil stored at the bottom of the reducer cavity 120 and provide a driving force to the oil to drive the oil to flow through the heat exchanger 500 for cooling. Driven by the oil pump 400, the cooled oil enters the stator 210 of the drive motor 200 and cools the stator 210. Under the action of gravity and the drive of the oil pump 400, the oil flowing through the stator 210 flows into the reducer cavity 120, and finally flows back to the oil pump 400, forming a circulating cooling of the stator 210 of the drive motor 200 in the powertrain 10.

[0047] In one embodiment, a portion of the oil recovered by the oil pump 400 flows into the stator 210 to cool the stator 210, and the other portion flows into the reducer cavity 120 to lubricate and cool the intermediate shaft and output shaft of the reducer 300. After lubrication and cooling, the oil falls to the bottom of the reducer cavity 120 under the action of gravity. The oil is recovered by the oil pump 400 to form circulating lubrication and cooling of the oil in the reducer cavity 120.

[0048] In one embodiment, the powertrain 10 further includes a motor controller 600 and a three-phase copper busbar 700. The motor controller 600 is used to receive power from the power battery 30, and the motor controller 600 is used to convert direct current into alternating current and transmit it to the drive motor 200. The drive motor 200 converts electrical energy into mechanical energy, and the drive motor 200 is used to transmit and connect the reducer 300. The three-phase copper busbar 700 is located at one end of the housing 100 and is used to electrically connect the motor controller 600 and the drive motor 200 so that the motor controller 600 can convert direct current into alternating current and transmit it to the drive motor 200. The power output by the drive motor 200 can be transmitted to the reducer 300, and after the deceleration and torque-increasing action of the reducer 300, it is output to the drive wheel 20 to drive the electric vehicle 1.

[0049] The powertrain 10 provided in the embodiment of the present application will be described in detail below. Figure 2 、 Figure 3 and Figure 4 In the figure, the axial direction of the power assembly 10 is the Y direction or a direction parallel to the Y direction, and the radial direction of the power assembly 10 is a direction perpendicular to the axial direction of the power assembly 10, which is the same as the following description.

[0050] See also Figure 2 、 Figure 3 、 Figure 4 and Figure 5In one embodiment, the oil cooling circuit of the powertrain 10 includes a circumferential flow channel 101, a copper busbar cooling flow channel 102, and a stator cooling flow channel 211. The circumferential flow channel 101 is used to receive oil after heat exchange in the heat exchanger 500, the copper busbar cooling flow channel 102 is used to transmit oil to cool the three-phase copper busbar 700, and the stator cooling flow channel 211 is used to transmit oil to cool the stator 210 of the drive motor 200.

[0051] In one embodiment, the circumferential channel 101, the copper bar cooling channel 102, and the stator cooling channel 211 are all used to contain and circulate oil, and the oil flows in each channel under the drive of the oil pump 400. In one embodiment, under the drive of the oil pump 400, the oil first flows through the shell channel 130 and flows to the heat exchanger 500. The shell channel 130 is formed by the shell 100. The shell channel 130 can be formed at the same time as the shell 100 is injection molded, or it can be formed by drilling in the shell 100 after the shell 100 is injection molded. In one embodiment, the shell 100 encloses an oil circuit of a heat exchanger 500, and the oil circuit of the heat exchanger 500 is used to be close to or in contact with the water-cooling flow channel of the heat exchanger 500. The oil flowing through the shell flow channel 130 enters the oil circuit of the heat exchanger 500. The oil in the oil circuit of the heat exchanger 500 is cooled to a lower temperature through the low-temperature water-cooled heat exchange of the heat exchanger 500, and is transmitted to the liquid inlet flow channel 103 enclosed by the shell 100. The liquid inlet flow channel 103 extends at least partially along the axial direction of the powertrain 10 to transmit the low-temperature oil from the side close to the reducer cavity 120 to the position where the stator 210 of the drive motor 200 is located.

[0052] See also Figure 3 、 Figure 3 and Figure 4 In one embodiment, the liquid inlet channel 103 extends in the cavity wall of the motor cavity 110 along the axial direction of the power assembly 10, and the liquid inlet channel 103 has an opening on the inner wall of the motor cavity 110, and the opening is used to transmit low-temperature oil to the circumferential channel 101 for cooling the drive motor. In one embodiment, the circumferential channel 101 is a channel with a certain accommodation space formed by the shell 100 and the stator 210, which is used to accommodate and circulate oil. A part of the inner wall of the circumferential channel 101 is the inner wall of the motor cavity 110, and the other part of the inner wall is the outer wall of the stator 210. In one embodiment, the circumferential channel 101 is formed by an independent shell, and the shell and the shell 100 are independent structures. The shell encloses a channel with a certain accommodation space for accommodating and circulating oil, and the shell is fixed in the motor cavity 110. For various specific implementation methods of the circumferential channel 101, please refer to the detailed description of the embodiments below.

[0053] See also Figure 3 and Figure 4In one embodiment, the circumferential flow channel 101 is distributed along the circumference of the drive motor. The position where the circumferential flow channel 101 is connected to the copper busbar cooling flow channel 102 and the position where the circumferential flow channel 101 is connected to the stator cooling flow channel 211 are spaced apart along the circumference of the drive motor. The copper busbar cooling flow channel 102 and the stator cooling flow channel 211 are used to divert the oil in the circumferential flow channel 101.

[0054] See also Figure 2 、 Figure 3 and Figure 4 In one embodiment, the circumferential flow channel 101 is used to surround the stator 210 or the end winding of the drive motor 200 along the circumference of the drive motor 200. This embodiment takes surrounding the stator 210 as an example. Two liquid ports are provided on the inner wall of the circumferential flow channel 101, and both liquid ports are used to penetrate the inner wall of the circumferential flow channel 101, wherein the first liquid port 1011 is used to connect the stator cooling flow channel 211, and at least part of the stator cooling flow channel 211 is used to extend along the axial direction of the stator 210 and penetrate the stator 210 along the axial direction of the stator 210. In one embodiment, the stator 210 is formed by stacking multiple layers of punching sheets 212, and each punching sheet 212 is provided with a through hole, and the through holes on any two adjacent layers of punching sheets 212 are opposite, and the through holes of the stacked multiple layers of punching sheets 212 are connected in sequence to form an axial flow channel 213, and the axial flow channel 213 is used to extend along the axial direction of the stator 210. In one embodiment, at least one radial flow channel 214 is provided along the radial direction of the stator 210 , and the radial flow channel 214 is used to communicate with the first liquid port 1011 .

[0055] In one embodiment, the stator cooling channel 211 includes an axial channel 213 and a radial channel 214. The number and position of the first liquid ports 1011 correspond to the number and position of the radial channel 214 openings on the outer circumferential surface of the stator. The oil flowing in the circumferential channel 101 enters the axial channel 213 through the radial channel 214. The axial channel 213 is used to contain oil to reduce the temperature of the stator 210. The oil flowing in the axial channel 213 flows out from one or both ends of the axial channel 213 to cool the end windings at one or both axial ends of the stator 210. In one embodiment, there are multiple axial channels 213, and the multiple axial channels 213 are spaced apart along the circumference of the drive motor 200. The number of radial channels 214 corresponds to the number of axial channels 213, and each axial channel 213 receives the oil transported by the circumferential channel 101 through the radial channel 214.

[0056] In one embodiment, the circumferential flow channel 101 is distributed along the circumference of the drive motor 200. The stator cooling flow channel 211 is located radially inward of the circumferential flow channel 101. A first liquid port 1011 for communicating with the radial flow channel 214 is located on the inner circumferential surface of the circumferential flow channel 101. The first liquid port 1011 is configured to penetrate the radial inner wall of the circumferential flow channel 101. The circumferential flow channel 101, the first liquid port 1011, and the radial flow channel 214 are sequentially connected along the radial direction of the stator 210.

[0057] See also Figure 3 and Figure 4 In one embodiment, the second of the two liquid ports 1012 is used to connect to the copper busbar cooling channel 102. A portion of the oil in the circumferential channel 101 flows through the second liquid port 1012 into the copper busbar cooling channel 102. The copper busbar cooling channel 102 then delivers the oil to the three-phase copper busbar 700 to cool it. In one embodiment, the outlet of the copper busbar cooling channel 102 is connected to an oil spray nozzle, which sprays the oil onto the surface of the three-phase copper busbar 700 to cool it.

[0058] In one embodiment, the circumferential flow channel 101 is used to receive low-temperature oil after heat exchange through the heat exchanger 500 and distribute the low-temperature oil to the stator cooling channel 211 and the copper busbar cooling channel 102. In one embodiment, the oil flowing through the stator cooling channel 211 is used to cool the stator 210, reducing the temperature of the stator 210. The cooled oil is discharged from the drive motor and returned to the reducer cavity. It is then recovered by the oil pump from the reducer cavity and heat exchanged again through the heat exchanger 500. The low-temperature oil after heat exchange re-enters the circumferential flow channel 101, forming a circulating cooling system. In one embodiment, the oil flowing through the copper busbar cooling channel 102 is used to cool the three-phase copper busbar 700, reducing the temperature of the three-phase copper busbar 700. The cooled oil is discharged from the receiving cavity of the three-phase copper busbar 700 and returned to the reducer cavity. It is then recovered by the oil pump from the reducer cavity and heat exchanged again through the heat exchanger 500. The low-temperature oil after heat exchange re-enters the circumferential flow channel 101, forming a circulating cooling system.

[0059] See also Figure 3 and Figure 4 In one embodiment, the circumferential flow channel 101 is connected to the copper busbar cooling flow channel 102 at the location of the second liquid port 1012, and is connected to the stator cooling flow channel 211 at the location of the first liquid port 1011. The first liquid port 1011 and the second liquid port 1012 are spaced apart. In one embodiment, the first liquid port 1011 and the second liquid port 1012 do not overlap or overlap. The oil flowing through the first liquid port 1011 does not enter the copper busbar cooling flow channel 102, and the oil flowing through the second liquid port 1012 does not enter the stator cooling flow channel 211.

[0060] In the embodiment of the present application, a copper bar cooling channel 102 is bypassed on the circumferential channel 101 for cooling the motor stator 210 to directly cool the three-phase copper bar 700, and the oil after heat exchange in the heat exchanger 500 received by the circumferential channel 101 is used to cool the three-phase copper bar 700, thereby improving the efficiency of the oil channel in the powertrain 10, so that the circumferential channel 101 can divert part of the oil to cool the three-phase copper bar 700; the copper bar cooling channel 102 for cooling the three-phase copper bar 700 of the present application is intermediately connected to the circumferential channel 101. By receiving the oil after heat exchange in the heat exchanger 500, the oil path between the circumferential flow channel 101 and the heat exchanger 500 can be utilized to shorten the oil path length, simplify the structure, and reduce costs; and the oil in the circumferential flow channel 101 is low-temperature oil that has undergone heat exchange in the heat exchanger 500. The copper bar cooling channel 102 and the stator cooling channel 211 branched out from the circumferential flow channel 101 are connected in parallel, preventing the heated oil in the stator cooling channel 211 from entering the copper bar cooling channel 102 and affecting the cooling efficiency of the three-phase copper bar, thereby improving the cooling efficiency of the three-phase copper bar 700.

[0061] In one embodiment, it should be noted that the above embodiment of the present application only uses the three-phase copper busbar 700 as an example, providing an embodiment in which low-temperature oil after heat exchange in the heat exchanger 500 is received from the circumferential flow channel 101 and diverted to the three-phase copper busbar 700 to cool the three-phase copper busbar 700. Based on the above embodiment, for other components that require cooling, such as bearings, a structure similar to the copper busbar cooling channel 102 can also be used for drainage and heat dissipation.

[0062] See also Figure 3 and Figure 6 , Figure 6 In one embodiment, the position where the circumferential channel 101 communicates with the copper bar cooling channel 102 and the position where the circumferential channel 101 receives the oil after heat exchange in the heat exchanger 500 are spaced apart along the circumference of the drive motor.

[0063] In one embodiment, a second liquid port 1012 is provided on the inner wall of the circumferential channel 101. The second liquid port 1012 is used to connect to the copper bar cooling channel 102. The oil in the circumferential channel 101 flows into the copper bar cooling channel 102 through the second liquid port 1012. The copper bar cooling channel 102 then delivers the oil to the three-phase copper bar 700 to cool it. In one embodiment, the outlet of the copper bar cooling channel 102 is connected to an oil spray nozzle, which sprays the oil onto the surface of the three-phase copper bar 700 to cool it.

[0064] In one embodiment, the liquid separation port provided on the inner wall of the circumferential flow channel 101 further includes a third liquid port 1013. The third liquid port 1013 is used to connect to a liquid inlet channel 103. The liquid inlet channel 103 is used to receive the oil after heat exchange in the heat exchanger 500 and transfer the low-temperature oil to the circumferential flow channel 101 through the third liquid port 1013. In one embodiment, the liquid inlet channel 103 extends along the axial direction of the powertrain 10 to transfer the low-temperature oil on the side of the powertrain 10 close to the reducer 300, which has been heat exchanged in the heat exchanger 500, to the circumferential flow channel 101 surrounding the outer periphery of the stator 210. In one embodiment, the liquid inlet channel 103 is located within the cavity wall of the motor cavity 110. The low-temperature oil flowing in the liquid inlet channel 103 can also reduce the temperature of the inner wall of the motor cavity and the medium in the motor cavity.

[0065] In one embodiment, the circumferential flow channel 101 is connected to the copper busbar cooling flow channel 102 at the position of the second liquid port 1012, and the circumferential flow channel 101 is connected to the liquid inlet flow channel 103 at the position of the third liquid port 1013 to receive the oil after heat exchange in the heat exchanger 500, and the second liquid port 1012 and the third liquid port 1013 are spaced apart along the circumference of the drive motor. In one embodiment, the second liquid port 1012 and the third liquid port 1013 do not overlap and do not coincide. In one embodiment, the second liquid port 1012 and the third liquid port 1013 are both located on the outer peripheral surface of the circumferential flow channel 101, the copper busbar cooling flow channel 102 and the liquid inlet flow channel 103 are both connected to the circumferential flow channel 101 along the radial direction of the stator 210, and the copper busbar cooling flow channel 102 and the liquid inlet flow channel 103 are both located radially outside the circumferential flow channel 101. The second liquid port 1012 and the third liquid port 1013 are spaced apart along the circumference of the circumferential flow channel 101. The low-temperature oil entering from the liquid inlet channel 103 will not immediately enter the copper bar cooling channel 102 in the circumferential flow channel 101, but will flow a certain distance along the circumference of the circumferential flow channel 101. The radial inner wall of the circumferential flow channel 101 will exchange heat with the stator 210. The heat of the stator 210 will gradually heat the flowing oil to appropriately increase the temperature of the oil flowing from the circumferential flow channel 101 into the copper bar cooling channel 102, preventing the low-temperature oil after heat exchange by the heat exchanger 500 from directly entering the copper bar cooling channel 102 to cool the three-phase copper bar 700 in a high-temperature state. On the basis of satisfying the cooling of the three-phase copper bar 700, the temperature of the three-phase copper bar 700 is prevented from changing suddenly, thereby affecting the transmission stability of electric energy. In addition, the heated oil in the circumferential flow channel 101 is also beneficial to reducing the viscosity of the oil, improving the uniformity of the oil in the copper busbar cooling flow channel 102 spraying on the three-phase copper busbar 700, thereby improving the cooling efficiency of the three-phase copper busbar 700.

[0066] See also Figure 3 and Figure 6In one embodiment, the position where the circumferential flow channel 101 is connected to the copper busbar cooling flow channel 102 and the position where the circumferential flow channel 101 is connected to the stator cooling flow channel 211 are spaced apart along the circumference of the drive motor.

[0067] In one embodiment, two liquid inlets are provided on the inner wall of the circumferential flow channel 101. Both liquid inlets are used to penetrate the inner wall of the circumferential flow channel 101. The first liquid inlet 1011 is used to connect to the stator cooling flow channel 211, and the second liquid inlet 1012 is used to connect to the copper bar cooling flow channel 102. The circumferential flow channel 101 is connected to the copper bar cooling flow channel 102 at the location of the second liquid inlet 1012, and the circumferential flow channel 101 is connected to the stator cooling flow channel 211 at the location of the first liquid inlet 1011. The first liquid inlet 1011 and the second liquid inlet 1012 are used to be spaced apart along the circumference of the stator 210. For example, along the radial direction of the stator 210, the projection of the first liquid port 1011 on the inner circumferential surface of the circumferential flow channel 101 and the projection of the second liquid port 1012 on the inner circumferential surface of the circumferential flow channel 101 do not overlap or coincide with each other. The oil in the circumferential flow channel 101 flows along the circumference of the stator 210. When the flow channel reaches the position of the first liquid port 1011, it will not enter the second liquid port 1012, but needs to flow along the circumferential direction for a distance before entering the second liquid port 1012, so as to prevent the circumferential flow channel 101 from being diverted at the same position, resulting in insufficient oil received by the copper busbar cooling channel 102 and the stator cooling channel 211.

[0068] In one embodiment, the first liquid port 1011 is located on the radial inner surface of the circumferential flow channel 101 , and the second liquid port 1012 is located on the radial outer surface of the circumferential flow channel 101 . The first liquid port 1011 and the second liquid port 1012 are spaced apart along the radial direction of the stator 210 .

[0069] In one embodiment, the position where the circumferential flow channel 101 is connected to the copper busbar cooling flow channel 102 and the position where the circumferential flow channel 101 is connected to the stator cooling flow channel 211 are spaced apart along the circumference of the drive motor, including the first liquid port 1011 and the second liquid port 1012 for being spaced apart in any direction along the radial and circumferential directions of the stator 210.

[0070] See also Figure 2 、 Figure 7 and Figure 8 , Figure 7 This is a schematic diagram of a powertrain 10 with multiple liquid inlet channels 103 connected in parallel, provided in an embodiment of the present application. Figure 8 This is a schematic diagram of a powertrain 10 with multiple parallel-connected fluid inlet channels 103, according to an embodiment of the present application. In one embodiment, the circumferential fluid channel 101 receives oil after heat exchange in the heat exchanger 500 through the multiple fluid inlet channels 103. The locations where the multiple fluid inlet channels 103 communicate with the circumferential fluid channel 101 are spaced apart along the circumference of the drive motor.

[0071] See also Figure 2 、 Figure 6 、 Figure 7 and Figure 8 In one embodiment, a third liquid port 1013 is provided on the inner wall of the circumferential flow channel 101. The third liquid port 1013 is used to connect to a liquid inlet channel 103. The liquid inlet channel 103 is used to receive the oil after heat exchange in the heat exchanger 500 and transfer the low-temperature oil to the circumferential flow channel 101 through the third liquid port 1013. In one embodiment, the liquid inlet channel 103 extends along the axial direction of the power assembly 10 to transfer the low-temperature oil on the side of the power assembly 10 close to the reducer 300 after heat exchange in the heat exchanger 500 to the circumferential flow channel 101 surrounding the outer periphery of the stator 210. In one embodiment, the liquid inlet channel 103 is located in the cavity wall of the motor cavity 110. The low-temperature oil flowing in the liquid inlet channel 103 can also reduce the temperature of the inner wall of the motor cavity 110 and the medium in the motor cavity 110.

[0072] In one embodiment, there are multiple liquid inlet channels 103, corresponding to multiple third liquid ports 1013. Each liquid inlet channel 103 is connected to the circumferential channel 101 through at least one third liquid port 1013. Multiple liquid inlet channels 103 are connected in parallel. The oil after heat exchange in the heat exchanger 500 enters the multiple liquid inlet channels 103 respectively, and flows into the circumferential channel 101 through the multiple liquid inlet channels 103.

[0073] In one embodiment, the liquid inlet channel 103 is connected to the circumferential channel 101 at the position of the third liquid port 1013 , and a plurality of third liquid ports 1013 are used to be spaced apart along the circumference of the drive motor.

[0074] In this embodiment, a plurality of liquid inlet channels 103 are provided, and the third liquid ports 1013 connected to the plurality of liquid inlet channels 103 are arranged at intervals along the circumference of the drive motor. This can increase the amount of oil obtained by the circumferential channel 101 through the liquid inlet channel 103 after heat exchange in the heat exchanger 500, provide sufficient oil for the subsequent diversion copper bar cooling channel 102 and the stator cooling channel 211, and prevent insufficient oil in the circumferential channel 101 from affecting the cooling of the stator 210 and the three-phase copper bar 700.

[0075] In one embodiment, among the multiple third liquid ports 1013, the spacing between any two adjacent third liquid ports 1013 along the circumference of the drive motor 200 is the same, so that the oil after heat exchange in the heat exchanger 500 can flow evenly into the circumferential flow channel 101, ensuring the uniformity of the oil amount in the circumferential flow channel 101 throughout the flow channel, so that the circumferential flow channel 101 provides oil stability to the copper busbar cooling channel 102 and the stator cooling channel 211.

[0076] See also Figure 2 、 Figure 3 、 Figure 4In one embodiment, the housing 100 of the powertrain 10 encloses a motor cavity 110 and a copper busbar cooling channel 102 . The motor cavity 110 is used to accommodate a stator 210 of a drive motor 200 . The copper busbar cooling channel 102 is used to penetrate the inner wall of the motor cavity 110 and connect to the circumferential channel 101 .

[0077] In one embodiment, the housing 100 includes a groove along the axial direction of the powertrain 10. The groove and a motor cover enclose the motor cavity 110. The stator 210 of the drive motor 200 is accommodated and fixed within the motor cavity 110, with the outer wall of the stator 210 fixedly connected to the inner wall of the motor cavity 110. The stator 210 is stationary within the motor cavity 110, and the rotor 220 passes through the stator 210 and rotates relative to the stator 210.

[0078] In one embodiment, the housing 100 also encloses a copper busbar cooling channel 102, which is a channel within the side wall of the motor cavity 110. The copper busbar cooling channel 102 can be formed while the motor cavity 110 of the housing 100 is formed. One end of the copper busbar cooling channel 102 passes through the inner wall surface of the motor cavity 110 to connect to the circumferential channel 101 within the motor cavity 110. In one embodiment, the outer wall surface of one axial end of the housing 100 has another groove, and the other groove is used to accommodate the three-phase copper busbar 700. While the motor cover encloses the motor cavity 110 with one groove, it also encloses the copper busbar accommodating cavity for accommodating the three-phase copper busbar 700 together with the other groove. In one embodiment, the other end of the copper busbar cooling channel 102 passes through the outer wall surface of one axial end of the housing 100 to connect to the copper busbar accommodating cavity for accommodating the three-phase copper busbar 700.

[0079] The present application utilizes a housing 100 to enclose the motor cavity 110 and the copper bar cooling channel 102, utilizing the thickness of the motor cavity 110 wall to simultaneously form the copper bar cooling channel 102. This eliminates the need for additional design of the structure, shape, and dimensions of the housing 100, resulting in lower production costs for the copper bar cooling channel 102. Furthermore, the copper bar cooling channel 102 is positioned radially outward from the motor cavity 110, preventing interference with other channels and eliminating the need for positional or structural changes to other channels.

[0080] See also Figure 2 、 Figure 3 、 Figure 4 、 Figure 9 and Figure 10 , Figure 9 is a schematic diagram of the stator 210 provided in an embodiment of the present application. Figure 10 1 is a schematic diagram of the stator 210 provided in an embodiment of the present application. In one embodiment, the inner wall of the motor cavity 110 and the stator 210 of the drive motor 200 enclose a circumferential flow channel 101. The circumferential flow channel 101 is used to surround the stator 210 along the circumference of the drive motor 200.

[0081] In one embodiment, the circumferential flow channel 101 is a stator circumferential flow channel, the outer diameter of the stator 210 is equal to the inner diameter of the motor cavity 110 , and the outer peripheral surface 215 of the stator 210 is in contact with the inner wall surface of the motor cavity 110 .

[0082] See also Figure 4 In one embodiment, the outer peripheral surface 215 of the stator 210 includes a circle of annular grooves 2151, and the inner wall surface of the motor cavity 110 and the inner wall surface of the annular groove 2151 enclose a circumferential flow channel 101. The radial outer wall surface of the circumferential flow channel 101 is the inner wall surface of the motor cavity 110, and the radial inner wall surface of the circumferential flow channel 101 is the bottom wall of the circle of annular grooves 2151.

[0083] See also Figure 9 In one embodiment, the inner wall surface of the motor cavity 110 includes another circle of annular grooves 111, the outer peripheral surface 215 of the stator 210 and the inner wall surface of the other circle of annular grooves 2151 enclose a circumferential flow channel 101, the radial outer wall surface of the circumferential flow channel 101 is the bottom wall of the other circle of annular grooves 111, and the radial inner wall surface of the circumferential flow channel 101 is the outer peripheral surface 215 of the stator 210.

[0084] See also Figure 10 In one embodiment, the outer circumferential surface 215 of the stator 210 includes a ring of annular grooves 2151, and the inner wall surface of the motor cavity 110 includes another ring of annular grooves 111. The outer circumferential surface 215 of the stator 210 and the inner wall surface of the motor cavity 110 are in contact with each other. The ring of annular grooves 2151 and the inner wall of the other ring of annular grooves 111 are radially opposed to each other in the stator 210. The inner wall of the ring of annular grooves 2151 and the inner wall of the other ring of annular grooves 111 together form a circumferential flow channel 101. The radial outer wall surface of the circumferential flow channel 101 serves as the bottom wall of the other ring of annular grooves 111, and the radial inner wall surface of the circumferential flow channel 101 serves as the bottom wall of the ring of annular grooves 2151.

[0085] See also Figure 9 and Figure 10 In one embodiment, the first liquid port 1011 is located on the radial inner wall surface of the circumferential flow channel 101, and at least one radial flow channel 214 is provided in the radial direction of the stator 210. The radial flow channel 214 is used to communicate with the first liquid port 1011 on the radial inner wall surface of the circumferential flow channel 101. The low-temperature oil received in the circumferential flow channel 101 enters the radial flow channel 214 through the first liquid port 1011, and further enters the axial flow channel 213 to cool the stator 210.

[0086] In one embodiment, the second liquid port 1012 is located on the radial outer wall surface of the circumferential flow channel 101, and diverts oil to the stator cooling channel 211 and the copper bar cooling channel 102 from the radial sides of the circumferential flow channel 101, thereby preventing crosstalk in the diversion and improving the efficiency of the diversion of the circumferential flow channel 101.

[0087] See also Figure 2 、 Figure 3 、 Figure 11 and Figure 12 , Figure 11 is a schematic diagram of the stator 210 provided in an embodiment of the present application. Figure 12 Figure 2 is a schematic diagram of a stator 210 provided in an embodiment of the present application. In one embodiment, along the circumference of the drive motor 200, a circumferential flow channel 101 surrounds the end windings 230. The circumferential flow channel 101 is used to spray oil into the end windings 230 through a plurality of oil injection holes 231 extending therethrough. The stator cooling flow channel 211 receives the oil sprayed from the oil injection holes 231.

[0088] In one embodiment, the oil injection ring 240 is used to enclose an annular groove 241, which is configured to engage with the axial end surface of the stator 210 and accommodate the end windings 230. The circumferential flow channel 101 is an annular flow channel formed by the outer circumferential surface of the oil injection ring 240, the outer circumferential surface of the stator 210, and the inner wall of the motor cavity 110. There are two oil injection rings 240, each fixed to the axial ends of the stator 210.

[0089] In one embodiment, the outer circumferences of the two oil injection rings 240 are stepped, with the outer circumference of the raised portion abutting the inner wall of the motor cavity 110, and the outer circumference of the recessed portion being spaced from the inner wall of the motor cavity 110. The inner wall of the raised portion, the inner wall of the motor cavity 110, the inner wall of the recessed portion, and the outer circumference of the stator 210 collectively enclose the circumferential flow channel 101. In one embodiment, both ends of the two oil injection rings 240 are sealed by end caps 250. The outer diameter of the end caps 250 is equal to the inner diameter of the motor cavity 110, and the outer diameter of the oil injection rings 240 is smaller than the inner diameter of the motor cavity 110. The inner wall of the end caps 250 that protrude from the outer circumference of the oil injection rings 240, the outer circumference of the oil injection rings 240, the inner wall of the motor cavity 110, and the outer circumference of the stator 210 collectively enclose the circumferential flow channel 101.

[0090] In one embodiment, the annular groove 241 formed by the oil injection ring 240 has at least one oil injection hole 231 on its radial outer peripheral surface, and the liquid outlet of the liquid inlet channel 103 on the inner wall of the motor cavity 110 is connected to the circumferential flow channel 101. The liquid inlet channel 103 receives the oil after heat exchange in the heat exchanger 500 and enters the circumferential flow channel 101. The oil in the circumferential flow channel 101 is sprayed onto the surface of the end winding 230 through the oil injection hole 231 under the action of pressure to cool the end winding 230.

[0091] This embodiment is directed to the structure of the oil injection ring 240. The circumferential flow channel 101 enclosed by the oil injection ring 240 surrounds the end winding 230. A portion of the oil delivered by the oil injection ring 240 for oil spray cooling to the end winding 230 is diverted to the three-phase copper busbar 700 for oil delivery and cooling.

[0092] See also Figure 2 、 Figure 3 、 Figure 4 and Figure 13 , Figure 13 This is a partial schematic diagram of a powertrain 10 provided in an embodiment of the present application. In one embodiment, a portion of the copper busbar cooling channel 102 is used to connect to the circumferential channel 101 in the radial direction of the stator 210, while another portion of the copper busbar cooling channel 102 is used to transmit oil in the axial direction of the stator 210 to cool the three-phase copper busbar 700.

[0093] In one embodiment, a portion of the copper bar cooling channel 102 extends radially along the stator 210. Figure 2 、 Figure 4 and Figure 13 In the X direction shown, one side of the copper bar cooling channel 102 can be close to the circumferential channel 101 and connected to the circumferential channel 101, thereby ensuring that the oil in the circumferential channel 101 can flow into the copper bar cooling channel 102. In one embodiment, another part of the copper bar cooling channel 102 extends along the axial direction of the stator 210, see Figure 2 、 Figure 3 、 Figure 4 and Figure 13 The Y direction shown allows the copper busbar cooling channel 102 to penetrate the inner wall of the motor cavity 110, thereby allowing the oil in the circumferential channel 101 to be transmitted to the three-phase copper busbar 700 through the copper busbar cooling channel 102, thereby dissipating heat for the three-phase copper busbar 700. In one embodiment, the copper busbar cooling channel 102 is formed during the injection molding of the housing 100, and the housing 100 encloses the copper busbar cooling channel 102 to ensure the sealing of the copper busbar cooling channel 102.

[0094] See also Figure 2 、 Figure 3 and Figure 7 In one embodiment, along the axial direction of the powertrain 10, see Figure 2 、 Figure 3 and Figure 7 In the Y direction shown, the copper bar cooling channel 102 is used to be located on both axial sides of the power assembly 10 together with the heat exchanger 500 .

[0095] In one embodiment, the three-phase copper busbar 700 and the heat exchanger 500 are located on either side of the motor stator 210 along the axial direction of the powertrain 10, facilitating connection between the motor stator 210 and the three-phase copper busbar 700, thereby enabling the motor stator 210 to receive AC power output from the motor controller 600 via the three-phase copper busbar 700. In one embodiment, the copper busbar cooling channel 102 extends along the side of the motor stator 210 facing away from the heat exchanger 500 to match the three-phase copper busbar 700 provided on the side of the drive motor 200 of the powertrain 10, guiding the oil in the heat exchanger 500 to flow smoothly toward the three-phase copper busbar 700, thereby dissipating heat from the three-phase copper busbar 700.

[0096] In one embodiment, the liquid inlet channel 103 passes through the housing 100 and connects to the heat exchanger 500 and the circumferential channel 101, respectively, to replenish the oil in the circumferential channel 101 of the motor stator 210, thereby ensuring the amount of oil in the copper busbar cooling channel 102 and achieving efficient heat dissipation of the three-phase copper busbar 700. In one embodiment, the heat exchanger 500 is located on the side of the housing near the reducer cavity 120 to ensure that the oil driven by the oil pump can flow through the heat exchanger along the cooling circuit and flow to the drive motor 200, thereby ensuring that the oil temperature entering the drive motor 200 is relatively low.

[0097] In one embodiment, the three-phase copper bar 700 is located on the side of the motor stator 210 away from the reducer cavity 120 to ensure that the three-phase copper bar 700 is close to the motor stator 210. A copper bar cooling channel 102 is provided on the side of the motor stator 210 away from the reducer cavity 120. In one embodiment, along the radial direction of the power assembly 10, refer to Figure 2 、 Figure 3 and Figure 7 In the Z direction shown, the three-phase copper busbar 700 is located between the motor controller 600 and the drive motor 200 , shortening the length of the connection between the motor controller 600 , the three-phase copper busbar 700 and the drive motor 200 .

[0098] See also Figure 2 、 Figure 3 、 Figure 14 、 Figure 15 , Figure 14 is a schematic diagram of a powertrain 10 provided in an embodiment of the present application. Figure 15 Schematic diagram of the stator 210 provided in an embodiment of the present application. In one embodiment, the powertrain 10 includes a bearing cooling channel 104 , which is used to receive oil from the circumferential channel 101 and transmit the oil to cool the motor bearings 260 of the drive motor 200 .

[0099] In one embodiment, the drive motor 200 includes a motor bearing 260, which is supported between the motor rotor and the housing 100 to ensure the stability of the operation of the drive motor 200. In one embodiment, when the drive motor 200 is in operation, the motor bearing 260 generates a large amount of heat due to friction. If this heat is not treated, the mechanical properties of the material of the motor bearing 260 will be degraded, thereby reducing the service life of the motor bearing 260.

[0100] In one embodiment, a fourth liquid port 1014 is provided on the inner wall of the circumferential channel 101, and the fourth liquid port 1014 is connected to both the circumferential channel 101 and the bearing cooling channel 104. The fourth liquid port 1014 is used to receive oil from the circumferential channel 101 and transmit it to the motor bearing 260 through the bearing cooling channel 104, so that the low-temperature oil after heat exchange in the heat exchanger 500 can flow into the motor bearing 260 through the bearing cooling channel 104, dissipating heat and lubricating the motor bearing 260, thereby ensuring the operating efficiency of the motor bearing 260. In one embodiment, the oil after heat exchange in the heat exchanger 500 is directedly transmitted to the motor bearing 260 through the bearing cooling channel 104. The oil has a lubricating effect on the motor bearing 260, reducing the friction of the motor bearing 260 during operation, and at the same time cooling the motor bearing 260, thereby improving the operating efficiency of the drive motor 200 and reducing energy loss.

[0101] In one embodiment, the bearing cooling channel 104 is enclosed by the housing 100 of the powertrain 10, thereby simplifying the manufacturing process and cost of the bearing cooling channel 104. In one embodiment, the bearing cooling channel 104 and the stator cooling channel 211 are both connected to the circumferential channel 101, and the position where the bearing cooling channel 104 and the circumferential channel 101 are connected is spaced apart from the position where the stator cooling channel 211 and the circumferential channel 101 are connected, to ensure that the amount of oil in the bearing cooling channel 104 and the stator cooling channel 211 is sufficient to support the lubrication and heat dissipation of the motor bearing 260 and the motor stator 210, thereby improving the operating efficiency of the drive motor 200.

[0102] See also Figure 14 and Figure 15In one embodiment, the bearing cooling channel 104, the stator cooling channel 211, and the copper busbar cooling channel 102 are arranged in parallel, and the oil in the circumferential channel 101 can flow into the above three cooling channels respectively, respectively dissipating heat for the motor bearing 260, the motor stator 210, and the three-phase copper busbar 700. In one embodiment, along the radial direction of the stator 210, the projection of the first liquid port 1011 on the inner circumferential surface of the circumferential channel 101 and the projection of the fourth liquid port 1014 on the inner circumferential surface of the circumferential channel 101 do not overlap or coincide. The oil in the circumferential channel 101 flows along the circumference of the stator 210, preventing the circumferential channel 101 from being diverted at the same position, resulting in insufficient oil received by the bearing cooling channel 104 and the stator cooling channel 211.

[0103] See also Figure 14 and Figure 15 In one embodiment, the position where the bearing cooling channel 104 is connected to the circumferential channel 101 and the position where the circumferential channel 101 is used to receive the oil after heat exchange in the heat exchanger 500 are spaced apart along the circumference of the drive motor 200.

[0104] In one embodiment, the location where the liquid inlet channel 103 and the circumferential channel 101 are connected is spaced apart from the location where the bearing cooling channel 104 and the circumferential channel 101 are connected, so that after the low-temperature oil heated by the heat exchanger 500 flows through the circumferential channel 101, the oil temperature increases accordingly and the oil viscosity decreases, thereby avoiding excessive resistance to the rotation of the motor bearing 260 due to excessive viscosity of the low-temperature oil, thereby ensuring the heat dissipation effect of the motor bearing 260 while improving the lubrication efficiency of the oil on the motor bearing 260. In one embodiment, the viscosity of the oil increases as the temperature of the oil decreases. The distance between the location where the liquid inlet channel 103 and the circumferential channel 101 are connected and the location where the bearing cooling channel 104 and the circumferential channel 101 are connected can be adjusted according to actual conditions to ensure the heat dissipation efficiency of the oil flowing through the motor bearing 260 for the motor bearing 260, while ensuring that the viscosity of the oil is low, thereby improving the efficiency of the motor bearing 260 during operation.

[0105] See also Figure 16 , Figure 16 In one embodiment, the bearing cooling channel 104 is used to receive the oil after heat exchange in the heat exchanger 500 and the oil in the circumferential channel 101 and merge the two oils to cool the motor bearing 260.

[0106] In one embodiment, the length of the bearing cooling channel 104 along the axial direction of the drive motor is greater than the length of the stator 210. An opening is provided on the sidewall of the bearing cooling channel 104 for communicating with the circumferential channel 101 to receive the low-temperature oil flowing within the circumferential channel 101. One end of the bearing cooling channel 104 passes over the stator 210 to directly receive the oil heated by the heat exchanger 500. The other end of the bearing cooling channel 104 is connected to the chamber where the motor bearing 260 is located. In one embodiment, a portion of the oil heated by the heat exchanger 500 enters the circumferential channel 101 and passes through the circumferential channel 101 from the middle of the bearing cooling channel 104 to cool the motor bearing 260. The remaining portion of the oil heated by the heat exchanger 500 does not enter the circumferential channel 101 but enters the bearing cooling channel 104 directly from the end of the bearing cooling channel 104 to cool the motor bearing 260.

[0107] In this embodiment, through the setting of the bearing cooling channel 104, the bearing cooling channel 104 can directly receive the low-temperature oil heated by the heat exchanger 500 to cool the motor bearing 260, and also synchronously receive the oil from the circumferential channel 101, so as to adjust the temperature of the oil in the bearing cooling channel 104 through the circumferential channel 101, control the oil to lubricate and cool the motor bearing 260 at a suitable temperature, and find the best balance point between temperature and viscosity.

[0108] See also Figure 17 , Figure 17 1 is a schematic diagram of the powertrain 10 provided in an embodiment of the present application. In one embodiment, the bearing cooling channel 104 includes a heat dissipation channel 1041, another heat dissipation channel 1042 and a third heat dissipation channel 1043. One heat dissipation channel 1041 is used to connect the circumferential channel 101 and the chamber containing the motor bearing 260. Another heat dissipation channel 1042 is used to connect the oil circuit of the heat exchanger 500 and the chamber containing the motor bearing 260. Along the axial direction of the powertrain 10, refer to Figure 17 In the Y direction shown, the third heat dissipation channel 1043 is located on one side of one heat dissipation channel 1041 and another heat dissipation channel 1042. The third heat dissipation channel 1043 is connected to both the one heat dissipation channel 1041 and the other heat dissipation channel 1042, so that the oil in the one heat dissipation channel 1041 and the oil in the other heat dissipation channel 1042 can converge and mix through the third heat dissipation channel 1043. In one embodiment, the oil exchanged in the heat exchanger 500 is cooled and flows into the circumferential channel 101. The oil is transported through the circumferential channel 101, causing the oil temperature to rise. The oil temperature in the circumferential channel 101 is higher than the oil temperature in the heat exchanger 500, that is, the oil temperature in the one heat dissipation channel 1041 is higher than the oil temperature in the other heat dissipation channel 1042.

[0109] In one embodiment, when the oil temperature is too low, the viscosity of the oil increases, resulting in increased resistance to the operation of the drive motor and poor lubrication. When the oil temperature is too high, the viscosity of the oil decreases, reducing the resistance to the operation of the drive motor. However, excessively high oil temperature does not effectively dissipate heat from the motor bearings 260, which can easily damage the motor bearings 260 due to the high temperature.

[0110] In one embodiment, the amount of oil in one heat dissipation channel 1041 and the amount of oil in another heat dissipation channel 1042 output to the motor bearing 260 is adjusted, thereby adjusting the oil temperature to reduce the resistance of the oil to the motor bearing 260 and lowering the temperature of the motor bearing 260 to ensure the reliability of the motor bearing 260.

[0111] In one embodiment, a valve 1045 is provided on a heat dissipation channel 1041 to control the amount of oil in the heat dissipation channel 1041 output to the motor bearing 260. Specifically, when the temperature of the motor bearing 260 is low, the motor bearing 260 does not need to be cooled by oil, and the valve 1045 is controlled to open. The oil with increased temperature flows into the third heat dissipation channel 1043 and is transmitted to the motor bearing 260 through the third heat dissipation channel 1043, thereby increasing the temperature of the oil in the motor bearing 260, reducing the viscosity of the oil, and improving the lubrication effect. Moreover, the temperature of the oil flowing through the circumferential flow channel 101 is higher than the oil after heat exchange in the heat exchanger 500. The higher temperature oil is used to lubricate the motor bearing 260, and the viscosity of the oil is lower, thereby reducing the resistance of the oil to the motor bearing 260 during operation, thereby improving the operating efficiency of the drive motor.

[0112] In one embodiment, another valve 1046 is provided on the other heat dissipation channel 1042 to control the amount of oil in the other heat dissipation channel 1042 that is delivered to the motor bearing 260. Specifically, when the temperature of the motor bearing 260 is high and the motor bearing 260 requires low-temperature oil for heat dissipation, the other valve 1046 is controlled to open. This allows the oil cooled by the heat exchanger 500 to flow directly into the motor bearing 260, dissipating heat from the motor bearing 260 and improving its reliability.

[0113] In one embodiment, one valve 1045 and another valve 1046 are opened simultaneously, and the flow rates of one valve 1045 and another valve 1046 can be controlled according to the actual operating conditions of the motor bearing 260 to control the ratio of the amount of oil entering the motor bearing 260 from the heat exchanger 500 and the circumferential flow channel 101, thereby achieving a balance between the heat dissipation effect on the motor bearing 260 and the resistance of the motor bearing 260 during operation. In one embodiment, the inner diameters of one heat dissipation channel 1041 and another heat dissipation channel 1042 are set according to different operating conditions, thereby regulating the ratio of oil of different temperatures in one heat dissipation channel 1041 and another heat dissipation channel 1042 entering the third heat dissipation channel 1043 to ensure the lubrication and heat dissipation effects of the oil on the motor bearing 260, thereby improving the operating efficiency of the powertrain 10.

[0114] See Figure 2 and Figure 18 , Figure 18 FIG2 is a schematic diagram of a powertrain 10 including a resolver sensor 800 according to an embodiment of the present application. In one embodiment, the powertrain 10 includes the resolver sensor 800. The motor shaft 270 of the drive motor 200 is fixedly connected to the resolver sensor 800. The motor bearing 260 is located on the same side of the stator 210 of the drive motor 200 as the resolver sensor 800.

[0115] In one embodiment, the powertrain 10 further includes a resolver sensor 800, which is located on the motor shaft 270 and is used to detect the position and speed of the drive motor 200 to ensure stable operation and efficiency of the drive motor 200. In one embodiment, when the resolver sensor 800 detects that the speed of the drive motor 200 is too high, which may easily cause the temperature of the motor bearing 260 on the resolver side to rise, the bearing cooling channel 104 connects the heat exchanger 500 and the motor bearing 260 on the resolver side, so that oil can be accurately transferred from the heat exchanger 500 to the motor bearing 260 on the resolver side, dissipating heat from the motor bearing 260 on the resolver side, thereby improving the heat dissipation efficiency of the motor bearing 260 on the resolver side. In one embodiment, the bearing cooling channel 104 can determine the actual temperature of the resolver-side motor bearing 260 based on the speed of the drive motor 200 detected by the resolver sensor 800. Based on the actual temperature, the amount of oil flowing from the heat exchanger 500 to the resolver-side motor bearing 260 is controlled. This ensures lubrication and heat dissipation of the resolver-side motor bearing 260 while reducing the resistance of the oil to the resolver-side motor bearing 260, thereby improving the operating efficiency of the powertrain 10. In one embodiment, the bearing cooling channel 104 is used to connect the circumferential channel 101 and the resolver-side motor bearing 260, allowing oil to be precisely transferred from the circumferential channel 101 to the resolver-side motor bearing 260, dissipating heat from the resolver-side motor bearing 260 and improving the heat dissipation efficiency of the resolver-side motor bearing 260.

[0116] See also Figure 19 , Figure 19 This is a schematic diagram of a powertrain 10 provided in an embodiment of the present application. In one embodiment, the circumferential channel 101 is used to receive the oil after heat exchange in the heat exchanger 500 through the liquid inlet channel 103. The inner diameter D2 of the copper busbar cooling channel 102 is smaller than the inner diameter D1 of the liquid inlet channel 103.

[0117] In one embodiment, part of the oil in the liquid inlet channel 103 flows into the copper bar cooling channel 102, and the other part of the oil flows into the stator cooling channel 211 or the bearing cooling channel 104. In one embodiment, the inner diameter D2 of the copper bar cooling channel 102 is smaller than the inner diameter D1 of the liquid inlet channel 103 to prevent the inner diameter of the copper bar cooling channel 102 from being too large and affecting the amount of oil in the above-mentioned liquid inlet channel. In one embodiment, the inner diameter of the bearing cooling channel 104 is smaller than the inner diameter of the liquid inlet channel 103. In one embodiment, the inner diameter of the stator cooling channel 211 is smaller than the inner diameter of the liquid inlet channel 103.

[0118] An embodiment of the present application also provides a powertrain having multiple liquid inlet channels, wherein the oil cooling circuit of the powertrain includes a circumferential channel and a liquid inlet channel, wherein the circumferential channel is used to receive the oil after heat exchange in the heat exchanger through the multiple liquid inlet channels, wherein: the circumferential channel is distributed along the circumference of the drive motor, and the positions where the multiple liquid inlet channels are connected to the circumferential channel are used to be spaced apart along the circumference of the drive motor, and the liquid inlet channel is used to provide oil to the circumferential channel. The embodiment of the present application provides oil to the circumferential flow channel for cooling the drive motor by providing an inlet flow channel between the circumferential flow channel and the heat exchanger, and allowing the oil to flow precisely from the heat exchanger to the circumferential flow channel, so that the circumferential flow channel can divert part of the oil to cool various locations of the drive motor; the number of inlet flow channels is set to multiple, and the locations where the multiple inlet flow channels are connected to the circumferential flow channel are spaced along the circumference of the drive motor, which can increase the amount of oil that the circumferential flow channel obtains after heat exchange in the heat exchanger through the inlet flow channel, cools various locations of the drive motor, and prevents insufficient oil in the circumferential flow channel from affecting the cooling effect of the drive motor. In addition, the oil in the circumferential flow channel is low-temperature oil that has been heat exchanged by the heat exchanger. The arrangement of multiple inlet flow channels in parallel can also ensure that the temperature of the oil in the circumferential flow channel is low, prevent the heated oil in the circumferential flow channel from entering the drive motor and affecting the cooling efficiency of the drive motor, and improve the cooling efficiency of the drive motor.

[0119] The powertrain 10 provided in an embodiment of the present application will be described in detail below.

[0120] See also Figure 2 、 Figure 3 and Figure 4 In one embodiment, the oil cooling circuit of the powertrain 10 includes a circumferential flow channel 101 and a liquid inlet flow channel 103. The circumferential flow channel 101 is used to receive the oil after heat exchange in the heat exchanger 500. The liquid inlet flow channel 103 is used to connect the heat exchanger 500 and the circumferential flow channel 101, so that the oil in the heat exchanger 500 can flow accurately into the circumferential flow channel 101 through the liquid inlet flow channel 103.

[0121] See also Figure 2 and Figure 5In one embodiment, the circumferential flow channel 101 and the liquid inlet flow channel 103 are both used to contain and circulate oil, and the oil flows in each flow channel under the drive of the oil pump 400. In one embodiment, under the drive of the oil pump 400, the oil first flows through the shell flow channel 130 and flows to the heat exchanger 500. The shell flow channel 130 is formed by the shell 100. The shell flow channel 130 can be formed at the same time as the shell 100 is injection molded, or it can be formed by drilling in the shell 100 after the shell 100 is injection molded. In one embodiment, the shell 100 encloses an oil circuit of a heat exchanger 500, and the oil circuit of the heat exchanger 500 is used to be close to or in contact with the water-cooling flow channel of the heat exchanger 500. The oil flowing through the shell flow channel 130 enters the oil circuit of the heat exchanger 500. The oil in the oil circuit of the heat exchanger 500 is cooled to a lower temperature through the low-temperature water-cooled heat exchange of the heat exchanger 500, and is transmitted to the liquid inlet flow channel 103 enclosed by the shell 100. The liquid inlet flow channel 103 extends at least partially along the axial direction of the powertrain 10 to transmit the low-temperature oil from the side close to the reducer cavity 120 to the position where the stator 210 of the drive motor 200 is located.

[0122] See also Figure 2 and Figure 4 In one embodiment, the liquid inlet channel 103 extends in the cavity wall of the motor cavity 110 along the axial direction of the power assembly 10, and the liquid inlet channel 103 has an opening on the inner wall of the motor cavity 110, and the opening is used to transmit low-temperature oil to the circumferential channel 101 for cooling the drive motor 200. In one embodiment, the circumferential channel 101 is a channel with a certain accommodation space formed by the shell 100 and the stator 210, which is used to accommodate and circulate oil. A part of the inner wall of the circumferential channel 101 is the inner wall of the motor cavity 110, and the other part of the inner wall is the outer wall of the stator 210. In one embodiment, the circumferential channel 101 is formed by an independent shell, and the shell and the shell 100 are independent structures. The shell encloses a channel with a certain accommodation space for accommodating and circulating oil, and the shell is fixed in the motor cavity 110. For various specific implementation methods of the circumferential channel 101, please refer to the detailed description of the embodiments below.

[0123] See also Figure 3 and Figure 6In one embodiment, a third liquid port 1013 is provided on the inner wall of the circumferential flow channel 101. The third liquid port 1013 is used to connect to a liquid inlet channel 103. The liquid inlet channel 103 is used to receive the oil after heat exchange in the heat exchanger 500 and transfer the low-temperature oil to the circumferential flow channel 101 through the third liquid port 1013. In one embodiment, the liquid inlet channel 103 extends along the axial direction of the power assembly 10 to transfer the low-temperature oil on the side of the power assembly 10 close to the reducer 300 after heat exchange in the heat exchanger 500 to the circumferential flow channel 101 surrounding the outer periphery of the stator 210. In one embodiment, the liquid inlet channel 103 is located in the cavity wall of the motor cavity 110. The low-temperature oil flowing in the liquid inlet channel 103 can also reduce the temperature of the inner wall of the motor cavity 110 and the medium in the motor cavity 110.

[0124] See also Figure 2 、 Figure 7 and Figure 8 In one embodiment, the circumferential flow channel 101 is distributed along the circumference of the drive motor 200. The positions where the circumferential flow channel 101 is connected to the multiple liquid inlet flow channels 103 are spaced apart along the circumference of the drive motor 200. The liquid inlet flow channel 103 is used to provide the circumferential flow channel 101 with low-temperature oil after heat exchange in the heat exchanger 500, so as to achieve cooling of the drive motor by the circumferential flow channel 101. In one embodiment, the number of liquid inlet flow channels 103 is multiple, corresponding to the number of third liquid ports 1013. Each liquid inlet flow channel 103 is connected to the circumferential flow channel 101 through at least one third liquid port 1013. The multiple liquid inlet flow channels 103 are connected in parallel. The oil after heat exchange in the heat exchanger 500 enters the multiple liquid inlet flow channels 103 respectively, and flows into the circumferential flow channel 101 through the multiple liquid inlet flow channels 103.

[0125] In one embodiment, the liquid inlet channel 103 is connected to the circumferential channel 101 at the location of the third liquid port 1013. Multiple third liquid ports 1013 are used to be spaced apart along the circumference of the drive motor 200. In one embodiment, the circumferential channel 101 is connected to the motor stator 210 at the location of the third liquid port 1013.

[0126] The embodiment of the present application sets a liquid inlet channel 103 between the circumferential channel 101 and the heat exchanger 500, and the liquid inlet channel is connected to the circumferential channel 101 and the heat exchanger 500, and is used to provide low-temperature oil to the circumferential channel 101 for cooling the drive motor 200, so that the circumferential channel 101 can divert part of the oil to cool various positions of the drive motor 200; by setting multiple liquid inlet channels 103, and the third liquid port 1013 connected to the multiple liquid inlet channels 103 is arranged at circumferential intervals along the drive motor 200, the amount of oil obtained by the circumferential channel 101 after heat exchange in the heat exchanger 500 through the liquid inlet channel 103 can be increased, so as to provide sufficient oil for subsequent diversion to various components of the drive motor 200 that need to be cooled, thereby preventing insufficient oil in the circumferential channel 101 from affecting the cooling of various components of the drive motor 200.

[0127] See also Figure 7 and Figure 8 In one embodiment, among the multiple third liquid ports 1013, the spacing between any two adjacent third liquid ports 1013 along the circumference of the drive motor 200 is the same, so that the oil after heat exchange in the heat exchanger 500 can flow evenly into the circumferential flow channel 101, ensuring the uniformity of the oil amount in the circumferential flow channel 101 throughout the flow channel, so that the circumferential flow channel 101 can provide oil stability to various components of the drive motor 200.

[0128] See also Figure 2 and Figure 5 In one embodiment, the circumferential flow channel 101 is used to receive low-temperature oil after heat exchange in the heat exchanger 500 and distribute the low-temperature oil to the drive motor 200. In one embodiment, the oil flowing through the circumferential flow channel 101 is used to cool the drive motor 200, reducing the temperature of various components of the drive motor 200 that require cooling. The cooled oil is discharged from the drive motor 200 and flows back into the reducer cavity. It is recovered from the reducer cavity by the oil pump and heat exchanged again through the heat exchanger 500. After heat exchange, the low-temperature oil re-enters the circumferential flow channel 101 through the liquid inlet flow channel 103, forming a circulating cooling.

[0129] See also Figure 3 、 Figure 4 and Figure 6In one embodiment, the oil cooling circuit of the powertrain 10 also includes a stator cooling channel 211, which is used to transfer oil and cool the stator 210 of the drive motor 200. In one embodiment, the stator cooling channel 211 is connected to the circumferential channel 101 and the stator 210, so that the oil can flow from the stator cooling channel 211 to the stator 210 to dissipate heat for the stator 210. In one embodiment, the liquid inlet channel 103, the circumferential channel 101 and the stator cooling channel 211 are all connected. The oil is transferred to the circumferential channel 101 through the liquid inlet channel 103, and then transferred to the stator 210 through the stator cooling channel 211 to ensure the precise transfer of oil to the stator 210 and achieve heat dissipation for the stator 210.

[0130] In one embodiment, the circumferential flow channel 101 is used to surround the stator 210 or the end winding of the drive motor 200 along the circumference of the drive motor 200. This embodiment takes surrounding the stator 210 as an example. A first liquid port 1011 is provided on the inner wall of the circumferential flow channel 101. The first liquid port 1011 is used to penetrate the inner wall of the circumferential flow channel 101 and to connect the stator cooling flow channel 211. At least a portion of the stator cooling flow channel 211 is used to extend along the axial direction of the stator 210 and penetrate the stator 210 along the axial direction of the stator 210. In one embodiment, the stator 210 is formed by stacking multiple layers of punching sheets 212. Each punching sheet 212 is provided with a through hole. The through holes on any two adjacent layers of punching sheets 212 are opposite to each other. The through holes of the stacked multiple layers of punching sheets 212 are connected in sequence to form an axial flow channel 213. The axial flow channel 213 is used to extend along the axial direction of the stator 210. In one embodiment, at least one radial flow channel 214 is provided along the radial direction of the stator 210 , and the radial flow channel 214 is used to communicate with the first liquid port 1011 .

[0131] See also Figure 4 、 Figure 6 、 Figure 8 、 Figure 9 and Figure 10 In one embodiment, the stator cooling channel 211 includes an axial channel 213 and a radial channel 214. The number and position of the first liquid ports 1011 correspond to the number and position of the openings of the radial channel 214 on the outer circumferential surface of the stator. The oil flowing in the circumferential channel 101 enters the axial channel 213 through the radial channel 214. The axial channel 213 is used to contain oil to reduce the temperature of the stator 210. The oil flowing in the axial channel 213 flows out from one or both ends of the axial channel 213 to cool the end windings at one or both axial ends of the stator 210. In one embodiment, there are multiple axial channels 213, and the multiple axial channels 213 are arranged at intervals along the circumference of the drive motor. The number of radial channels 214 corresponds to the number of axial channels 213, and each axial channel 213 receives the oil transported by the circumferential channel 101 through the radial channel 214.

[0132] In one embodiment, the circumferential flow channel 101 is distributed along the circumference of the drive motor, the stator cooling flow channel 211 is located radially inward of the circumferential flow channel 101, and the first liquid port 1011 for communicating with the radial flow channel 214 is located on the inner circumferential surface of the circumferential flow channel 101. The first liquid port 1011 is configured to penetrate the radial inner wall of the circumferential flow channel 101. In the radial direction of the stator 210, the circumferential flow channel 101, the first liquid port 1011, and the radial flow channel 214 are sequentially connected.

[0133] See also Figure 6 and Figure 8 In one embodiment, the first liquid port 1011 connecting the stator cooling channel 211 to the circumferential channel 101 and the third liquid port 1013 connecting the multiple liquid inlet channels 103 to the circumferential channel 101 are arranged at intervals to prevent the oil flowing into the circumferential channel 101 from all flowing into the stator cooling channel 211, resulting in insufficient oil in the circumferential channel 101.

[0134] See also Figure 3 、 Figure 4 、 Figure 7 、 Figure 9 and Figure 10 In one embodiment, the oil cooling circuit of the powertrain 10 also includes a copper busbar cooling channel 102, which is used to transmit oil and cool the three-phase copper busbar 700. In one embodiment, the copper busbar cooling channel 102 is connected to the circumferential channel 101 and the three-phase copper busbar 700, so that oil can flow from the copper busbar cooling channel 102 into the three-phase copper busbar 700 to dissipate heat for the three-phase copper busbar 700. In one embodiment, the liquid inlet channel 103, the circumferential channel 101 and the copper busbar cooling channel 102 are all connected. The oil is transmitted to the circumferential channel 101 through the liquid inlet channel 103, and then transmitted to the three-phase copper busbar 700 through the copper busbar cooling channel 102, thereby dissipating heat for the three-phase copper busbar 700.

[0135] See also Figure 4 、 Figure 9 and Figure 10 In one embodiment, a second liquid port 1012 is provided on the inner wall of the circumferential channel 101. The second liquid port 1012 is used to connect to the copper bar cooling channel 102. The oil in the circumferential channel 101 flows into the copper bar cooling channel 102 through the second liquid port 1012. The copper bar cooling channel 102 then delivers the oil to the three-phase copper bar 700 to cool it. In one embodiment, the outlet of the copper bar cooling channel 102 is connected to an oil spray nozzle, which sprays the oil onto the surface of the three-phase copper bar 700 to cool it.

[0136] See also Figure 2 、 Figure 3 、 Figure 6 、 Figure 7 and Figure 8 In one embodiment, the position where the circumferential flow channel 101 is connected to the copper busbar cooling flow channel 102 and the position where the circumferential flow channel 101 is used to receive the oil after heat exchange in the heat exchanger 500 are spaced apart along the circumference of the drive motor 200.

[0137] In one embodiment, the locations where the circumferential flow channel 101 communicates with the copper busbar cooling flow channel 102 and the locations where the circumferential flow channel 101 communicates with the liquid inlet flow channel 103 are spaced apart along the circumference of the drive motor 200. In one embodiment, the circumferential flow channel 101 communicates with the copper busbar cooling flow channel 102 at the location of the second liquid port 1012, and communicates with the liquid inlet flow channel 103 at the location of the third liquid port 1013 to receive the oil after heat exchange in the heat exchanger 500. The second liquid port 1012 and the third liquid port 1013 are spaced apart along the circumference of the drive motor 200.

[0138] In one embodiment, the second liquid port 1012 and the third liquid port 1013 do not overlap or overlap. In one embodiment, the second liquid port 1012 and the third liquid port 1013 are both located on the outer circumferential surface of the circumferential flow channel 101, the copper bar cooling flow channel 102 and the liquid inlet flow channel 103 are both connected to the circumferential flow channel 101 in the radial direction of the stator 210, and the copper bar cooling flow channel 102 and the liquid inlet flow channel 103 are both located radially outward of the circumferential flow channel 101. The second liquid port 1012 and the third liquid port 1013 are spaced apart along the circumference of the circumferential flow channel 101. The low-temperature oil entering from the liquid inlet channel 103 will not immediately enter the copper bar cooling channel 102 in the circumferential flow channel 101, but will flow a certain distance along the circumference of the circumferential flow channel 101. The radial inner wall of the circumferential flow channel 101 will exchange heat with the stator 210. The heat of the stator 210 will gradually heat the flowing oil to appropriately increase the temperature of the oil flowing from the circumferential flow channel 101 into the copper bar cooling channel 102, preventing the low-temperature oil after heat exchange by the heat exchanger 500 from directly entering the copper bar cooling channel 102 to cool the three-phase copper bar 700 in a high-temperature state. On the basis of satisfying the cooling of the three-phase copper bar 700, the temperature of the three-phase copper bar 700 is prevented from changing suddenly, thereby affecting the transmission stability of electric energy. In addition, the heated oil in the circumferential flow channel 101 is also beneficial to reducing the viscosity of the oil, improving the uniformity of the oil in the copper busbar cooling flow channel 102 spraying on the three-phase copper busbar 700, thereby improving the cooling efficiency of the three-phase copper busbar 700.

[0139] See also Figure 2 and Figure 14 In one embodiment, the power assembly 10 includes a bearing cooling channel 104 , which is used to receive oil from the circumferential channel 101 and to transmit oil to cool the motor bearing 260 of the drive motor 200 .

[0140] In one embodiment, the drive motor 200 includes a motor bearing 260, which is used to support and position the drive motor 200 to ensure the stability of the operation of the drive motor 200. In one embodiment, when the drive motor 200 is in operation, the motor bearing 260 generates a large amount of heat due to friction. If this heat is not treated, the mechanical properties of the material of the motor bearing 260 will be degraded, thereby reducing the service life of the motor bearing 260.

[0141] See also Figure 14 and Figure 15 In one embodiment, a fourth liquid port 1014 is provided in the circumferential flow channel 101. The fourth liquid port 1014 is connected to both the circumferential flow channel 101 and the bearing cooling flow channel 104. The fourth liquid port 1014 is used to receive oil from the circumferential flow channel 101 and transmit it to the motor bearing 260 through the bearing cooling flow channel 104. This allows the low-temperature oil that has undergone heat exchange in the heat exchanger 500 to flow through the bearing cooling flow channel 104 into the motor bearing 260, dissipating heat and lubricating the motor bearing 260, thereby ensuring the operating efficiency of the motor bearing 260.

[0142] See also Figure 14 and Figure 15 In one embodiment, the position where the bearing cooling channel 104 is connected to the circumferential channel 101 and the position where the circumferential channel 101 is used to receive the oil after heat exchange in the heat exchanger 500 are spaced apart along the circumference of the drive motor 200.

[0143] In one embodiment, the location where the inlet channel 103 and the circumferential channel 101 are connected is spaced apart from the location where the bearing cooling channel 104 and the circumferential channel 101 are connected, along the circumference of the drive motor 200. This allows the low-temperature oil, after heat exchanged by the heat exchanger 500, to flow through the circumferential channel 101, to increase its temperature and decrease its viscosity. This prevents the low-temperature oil from having excessive viscosity and causing excessive resistance to the rotation of the motor bearing 260. This ensures the heat dissipation effect of the motor bearing 260 while improving the lubrication efficiency of the oil on the motor bearing 260. In one embodiment, the viscosity of the oil increases as the temperature of the oil decreases. The distance between the location where the inlet channel 103 and the circumferential channel 101 are connected and the location where the bearing cooling channel 104 and the circumferential channel 101 are connected can be adjusted according to actual conditions to ensure the heat dissipation efficiency of the oil flowing through the motor bearing 260, while ensuring that the viscosity of the oil is low, thereby improving the efficiency of the motor bearing 260 during operation.

[0144] See also Figure 19 In one embodiment, the circumferential flow channel 101 is used to receive the oil after heat exchange in the heat exchanger 500 through the liquid inlet flow channel 103, and the inner diameter D2 of the copper busbar cooling flow channel 102 is smaller than the inner diameter D1 of the liquid inlet flow channel 103.

[0145] In one embodiment, part of the oil in the liquid inlet channel 103 flows into the copper bar cooling channel 102, and the other part of the oil flows into the stator cooling channel 211 or the bearing cooling channel 104. In one embodiment, the inner diameter D2 of the copper bar cooling channel 102 is smaller than the inner diameter D1 of the liquid inlet channel 103 to prevent the inner diameter of the copper bar cooling channel 102 from being too large and affecting the amount of oil in the above-mentioned liquid inlet channel. In one embodiment, the inner diameter of the bearing cooling channel 104 is smaller than the inner diameter of the liquid inlet channel 103. In one embodiment, the inner diameter of the stator cooling channel 211 is smaller than the inner diameter of the liquid inlet channel 103.

[0146] An embodiment of the present application also provides a powertrain for heat dissipation of motor bearings, wherein the oil cooling circuit of the powertrain includes a circumferential flow channel, a bearing cooling flow channel and a stator cooling flow channel, wherein the circumferential flow channel is used to receive oil after heat exchange in a heat exchanger, the bearing cooling flow channel is used to transmit oil to cool the bearings of the drive motor, and the stator cooling flow channel is used to transmit oil to cool the stator of the drive motor, wherein: the circumferential flow channel is distributed along the circumference of the drive motor, the position where the bearing cooling flow channel is connected to the circumferential flow channel and the position where the stator cooling flow channel is connected to the circumferential flow channel are spaced apart, and the bearing cooling flow channel and the stator cooling flow channel are used to divert the oil in the circumferential flow channel. The embodiment of the present application bypasses a bearing cooling channel on the circumferential channel for cooling the motor stator to directly cool the bearings of the drive motor, and uses the oil after heat exchange in the heat exchanger received by the circumferential channel to cool the motor bearings, thereby improving the utilization efficiency of the oil channel in the powertrain so that the circumferential channel can divert part of the oil to cool the bearings; the bearing cooling channel for cooling the motor bearings of the present application is transferred through the circumferential channel to receive the oil after heat exchange in the heat exchanger, and the oil path between the circumferential channel and the heat exchanger can be utilized to shorten the oil path length, simplify the structure, and reduce costs; and the oil in the circumferential channel is low-temperature oil heated by the heat exchanger, and the bearing cooling channel diverted from the circumferential channel and the stator cooling channel are connected in parallel, preventing the heated oil in the stator cooling channel from entering the bearing cooling channel and affecting the cooling efficiency of the motor bearings, thereby improving the cooling efficiency of the bearings.

[0147] The powertrain 10 provided in an embodiment of the present application will be described in detail below.

[0148] See also Figure 2 、 Figure 14 and Figure 15In one embodiment, the oil cooling circuit of the powertrain 10 includes a circumferential flow channel 101, a bearing cooling flow channel 104, and a stator cooling flow channel 211. The circumferential flow channel 101 is used to receive oil after heat exchange in the heat exchanger 500, the bearing cooling flow channel 104 is used to transmit oil to cool the motor bearings 260 of the drive motor 200, and the stator cooling flow channel 211 is used to transmit oil to cool the stator 210 of the drive motor 200.

[0149] In one embodiment, the drive motor 200 includes a motor bearing 260, which is supported between the motor rotor and the housing 100 to ensure the stability of the operation of the drive motor 200. In one embodiment, when the drive motor 200 is in operation, the motor bearing 260 generates a large amount of heat due to friction. If this heat is not treated, the mechanical properties of the material of the motor bearing 260 will be degraded, thereby reducing the service life of the motor bearing 260.

[0150] See also Figure 2 、 Figure 5 、 Figure 14 and Figure 15 In one embodiment, the circumferential flow channel 101, the bearing cooling flow channel 104, and the stator cooling flow channel 211 are all used to contain and circulate oil, and the oil flows in each flow channel under the drive of the oil pump 400. In one embodiment, under the drive of the oil pump 400, the oil first flows through the shell flow channel 130 and flows to the heat exchanger 500. The shell flow channel 130 is formed by the shell 100. The shell flow channel 130 can be formed at the same time as the shell 100 is injection molded, or it can be formed in the shell 100 by drilling after the shell 100 is injection molded. In one embodiment, the shell 100 encloses an oil circuit of a heat exchanger 500, and the oil circuit of the heat exchanger 500 is used to be close to or in contact with the water-cooling flow channel of the heat exchanger 500. The oil flowing through the shell flow channel 130 enters the oil circuit of the heat exchanger 500. The oil in the oil circuit of the heat exchanger 500 is cooled to a lower temperature through the low-temperature water-cooled heat exchange of the heat exchanger 500, and is transmitted to the liquid inlet flow channel 103 enclosed by the shell 100. The liquid inlet flow channel 103 extends at least partially along the axial direction of the powertrain 10 to transmit the low-temperature oil from the side close to the reducer cavity 120 to the position where the stator 210 of the drive motor 200 is located.

[0151] In one embodiment, the liquid inlet channel 103 extends in the cavity wall of the motor cavity 110 along the axial direction of the power assembly 10, and the liquid inlet channel 103 has an opening on the inner wall of the motor cavity 110, and the opening is used to transmit low-temperature oil to the circumferential channel 101 for cooling the drive motor 200. In one embodiment, the circumferential channel 101 is a channel with a certain accommodation space formed by the shell 100 and the stator 210, which is used to accommodate and circulate oil. A part of the inner wall of the circumferential channel 101 is the inner wall of the motor cavity 110, and the other part of the inner wall is the outer wall of the stator 210. In one embodiment, the circumferential channel 101 is formed by an independent shell, and the shell and the shell 100 are independent structures. The shell encloses a channel with a certain accommodation space for accommodating and circulating oil, and the shell is fixed in the motor cavity 110. For various specific implementation methods of the circumferential channel 101, please refer to the detailed description of the embodiments below.

[0152] In one embodiment, the circumferential flow channel 101 is distributed along the circumference of the drive motor 200, and the position where the circumferential flow channel 101 is connected to the bearing cooling flow channel 104 and the position where the circumferential flow channel 101 is connected to the stator cooling flow channel 211 are spaced apart along the circumference of the drive motor 200. The bearing cooling flow channel 104 and the stator cooling flow channel 211 are used to divert the oil in the circumferential flow channel 101.

[0153] See also Figure 4 、 Figure 14 and Figure 15 In one embodiment, the circumferential flow channel 101 is used to surround the stator 210 or the end winding of the drive motor 200 along the circumference of the drive motor 200. This embodiment takes surrounding the stator 210 as an example. Two liquid ports are provided on the inner wall of the circumferential flow channel 101, and both liquid ports are used to penetrate the inner wall of the circumferential flow channel 101, wherein the first liquid port 1011 is used to connect the stator cooling flow channel 211, and at least part of the stator cooling flow channel 211 is used to extend along the axial direction of the stator 210 and penetrate the stator 210 along the axial direction of the stator 210. In one embodiment, the stator 210 is formed by stacking multiple layers of punching sheets 212, and each punching sheet 212 is provided with a through hole, and the through holes on any two adjacent layers of punching sheets 212 are opposite, and the through holes of the stacked multiple layers of punching sheets 212 are connected in sequence to form an axial flow channel 213, and the axial flow channel 213 is used to extend along the axial direction of the stator 210. In one embodiment, at least one radial flow channel 214 is provided along the radial direction of the stator 210 , and the radial flow channel 214 is used to communicate with the first liquid port 1011 .

[0154] See also Figure 13In one embodiment, the stator cooling channel 211 includes an axial channel 213 and a radial channel 214. The number and position of the first liquid ports 1011 correspond to the number and position of the openings of the radial channel 214 on the outer circumferential surface of the stator. The oil flowing in the circumferential channel 101 enters the axial channel 213 through the radial channel 214. The axial channel 213 is used to contain oil to reduce the temperature of the stator 210. The oil flowing in the axial channel 213 flows out from one or both ends of the axial channel 213 to cool the end windings at one or both axial ends of the stator 210. In one embodiment, there are multiple axial channels 213, and the multiple axial channels 213 are arranged at intervals along the circumference of the drive motor. The number of radial channels 214 corresponds to the number of axial channels 213, and each axial channel 213 receives the oil transported by the circumferential channel 101 through the radial channel 214.

[0155] In one embodiment, the circumferential flow channel 101 is distributed along the circumference of the drive motor 200. The stator cooling flow channel 211 is located radially inward of the circumferential flow channel 101. A first liquid port 1011 for communicating with the radial flow channel 214 is located on the inner circumferential surface of the circumferential flow channel 101. The first liquid port 1011 is configured to penetrate the radial inner wall of the circumferential flow channel 101. The circumferential flow channel 101, the first liquid port 1011, and the radial flow channel 214 are sequentially connected along the radial direction of the stator 210.

[0156] See also Figure 14 and Figure 15 In one embodiment, a fourth liquid port 1014 is further provided in the circumferential channel 101. The fourth liquid port 1014 is used to connect to the bearing cooling channel 104. A portion of the oil in the circumferential channel 101 flows through the fourth liquid port 1014 into the bearing cooling channel 104. The bearing cooling channel 104 then delivers the oil to the motor bearing 260 to cool the motor bearing 260. In one embodiment, the outlet of the bearing cooling channel 104 is connected to an oil spray nozzle, which sprays the oil onto the surface of the motor bearing 260 to cool the motor bearing 260.

[0157] See also Figure 2 、 Figure 5 、 Figure 14 and Figure 15In one embodiment, the circumferential flow channel 101 is used to receive low-temperature oil after heat exchange in the heat exchanger 500 and distribute the low-temperature oil to the stator cooling channel 211 and the bearing cooling channel 104. In one embodiment, the oil flowing through the stator cooling channel 211 is used to cool the stator 210, reducing the temperature of the stator 210. The cooled oil is discharged from the drive motor 200 and flows back into the reducer cavity 120. From the reducer cavity 120, it is recovered by the oil pump 400 and again heat exchanged through the heat exchanger 500. After heat exchange, the low-temperature oil re-enters the circumferential flow channel 101, forming a circulating cooling. In one embodiment, the oil flowing through the bearing cooling channel 104 is used to cool the motor bearing 260, thereby reducing the temperature of the motor bearing 260. The cooled oil is discharged from the accommodating cavity of the motor bearing 260 and flows back into the reducer cavity 120. The oil is recovered from the reducer cavity 120 by the oil pump 400 and is heat exchanged again through the heat exchanger 500. The low-temperature oil after heat exchange re-enters the circumferential channel 101, thereby forming circulating cooling.

[0158] In one embodiment, the circumferential flow channel 101 is connected to the bearing cooling flow channel 104 at the location of the fourth liquid port 1014, and is connected to the stator cooling flow channel 211 at the location of the first liquid port 1011. The first liquid port 1011 and the fourth liquid port 1014 are spaced apart. In one embodiment, the first liquid port 1011 and the fourth liquid port 1014 do not overlap or overlap. The oil flowing through the first liquid port 1011 does not enter the bearing cooling flow channel 104, and the oil flowing through the fourth liquid port 1014 does not enter the stator cooling flow channel 211.

[0159] The embodiment of the present application bypasses a bearing cooling channel 104 on the circumferential channel 101 for cooling the motor stator 210 to directly cool the motor bearing 260, and uses the oil after heat exchange in the heat exchanger 500 received by the circumferential channel 101 to cool the motor bearing 260, thereby improving the efficiency of the oil channel in the powertrain 10, so that the circumferential channel 101 can divert part of the oil to cool the motor bearing 260; the bearing cooling channel 104 for cooling the motor bearing 260 of the present application is transferred through the circumferential channel 101 By receiving the oil after heat exchange in the heat exchanger 500, the oil path between the circumferential flow channel 101 and the heat exchanger 500 can be utilized to shorten the oil path length, simplify the structure, and reduce costs; and the oil in the circumferential flow channel 101 is low-temperature oil that has been heat exchanged by the heat exchanger 500, and the bearing cooling channel 104 and the stator cooling channel 211 branched out from the circumferential flow channel 101 are connected in parallel, preventing the heated oil in the stator cooling channel 211 from entering the bearing cooling channel 104 and affecting the cooling efficiency of the motor bearing 260, thereby improving the cooling efficiency of the motor bearing 260.

[0160] In one embodiment, it should be noted that the above embodiment of the present application only uses the motor bearing 260 as an example to provide an embodiment in which low-temperature oil after heat exchange in the heat exchanger 500 is received from the circumferential flow channel 101 and diverted to the motor bearing 260 to cool the motor bearing 260. Based on the above embodiment, for other components that need to be cooled, such as three-phase copper busbars, a structure similar to the bearing cooling channel 104 can also be used for drainage and heat dissipation.

[0161] See also Figure 14 and Figure 15 In one embodiment, the position where the bearing cooling channel 104 is connected to the circumferential channel 101 and the position where the circumferential channel 101 is used to receive the oil after heat exchange in the heat exchanger 500 are spaced apart along the circumference of the drive motor 200.

[0162] In one embodiment, the location where the inlet channel 103 and the circumferential channel 101 are connected is spaced apart from the location where the bearing cooling channel 104 and the circumferential channel 101 are connected, along the circumference of the drive motor 200. This allows the low-temperature oil, after heat exchanged by the heat exchanger 500, to flow through the circumferential channel 101, to increase its temperature and decrease its viscosity. This prevents the low-temperature oil from having excessive viscosity and causing excessive resistance to the rotation of the motor bearing 260. This ensures the heat dissipation effect of the motor bearing 260 while improving the lubrication efficiency of the oil on the motor bearing 260. In one embodiment, the viscosity of the oil increases as the temperature of the oil decreases. The distance between the location where the inlet channel 103 and the circumferential channel 101 are connected and the location where the bearing cooling channel 104 and the circumferential channel 101 are connected can be adjusted according to actual conditions to ensure the heat dissipation efficiency of the oil flowing through the motor bearing 260, while ensuring that the viscosity of the oil is low, thereby improving the efficiency of the motor bearing 260 during operation.

[0163] See also Figure 16 In one embodiment, the bearing cooling channel 104 is used to receive the oil after heat exchange in the heat exchanger 500 and the oil in the circumferential channel 101 respectively and merge the two oils to cool the motor bearing 260.

[0164] In one embodiment, the length of the bearing cooling channel 104 along the axial direction of the drive motor 200 is greater than the length of the stator 210. An opening is provided on the sidewall of the bearing cooling channel 104 for communicating with the circumferential channel 101 to receive the low-temperature oil flowing within the circumferential channel 101. One end of the bearing cooling channel 104 passes over the stator 210 to directly receive the oil heated by the heat exchanger 500. The other end of the bearing cooling channel 104 is connected to the chamber where the motor bearing 260 is located. In one embodiment, a portion of the oil heated by the heat exchanger 500 enters the circumferential channel 101 and passes through the circumferential channel 101 into the bearing cooling channel 104 from its center to cool the motor bearing 260. The remaining portion of the oil heated by the heat exchanger 500 does not enter the circumferential channel 101 but enters the bearing cooling channel 104 directly from its end to cool the motor bearing 260.

[0165] In this embodiment, through the setting of the bearing cooling channel 104, the bearing cooling channel 104 can directly receive the low temperature heat exchanged by the heat exchanger 500 to cool the motor bearing 260, and also synchronously receive the oil from the circumferential channel 101, so as to adjust the temperature of the oil in the bearing cooling channel 104 through the circumferential channel 101, control the oil to lubricate and cool the motor bearing 260 at a suitable temperature, and find the best balance point between temperature and viscosity.

[0166] See also Figure 17 In one embodiment, the bearing cooling channel 104 includes a heat dissipation channel 1041, another heat dissipation channel 1042, and a third heat dissipation channel 1043. One heat dissipation channel 1041 is used to connect the circumferential channel 101 and the chamber containing the motor bearing 260. Another heat dissipation channel 1042 is used to connect the oil circuit of the heat exchanger 500 and the chamber containing the motor bearing 260. Along the axial direction of the power assembly 10, refer to Figure 17 In the Y direction shown, the third heat dissipation channel 1043 is located on one side of one heat dissipation channel 1041 and another heat dissipation channel 1042. The third heat dissipation channel 1043 is connected to both the one heat dissipation channel 1041 and the other heat dissipation channel 1042, so that the oil in the one heat dissipation channel 1041 and the oil in the other heat dissipation channel 1042 can converge and mix through the third heat dissipation channel 1043. In one embodiment, the oil exchanged in the heat exchanger 500 is cooled and flows into the circumferential channel 101. The oil is transported through the circumferential channel 101, causing the oil temperature to rise. The oil temperature in the circumferential channel 101 is higher than the oil temperature in the heat exchanger 500, that is, the oil temperature in the one heat dissipation channel 1041 is higher than the oil temperature in the other heat dissipation channel 1042.

[0167] In one embodiment, when the oil temperature is too low, the viscosity of the oil increases, resulting in increased resistance to the operation of the drive motor and poor lubrication. When the oil temperature is too high, the viscosity of the oil decreases, reducing the resistance to the operation of the drive motor. However, excessively high oil temperature does not effectively dissipate heat from the motor bearings 260, which can easily damage the motor bearings 260 due to the high temperature.

[0168] In one embodiment, the amount of oil in one heat dissipation channel 1041 and the amount of oil in another heat dissipation channel 1042 output to the motor bearing 260 is adjusted, thereby adjusting the oil temperature to reduce the resistance of the oil to the motor bearing 260 and lowering the temperature of the motor bearing 260 to ensure the reliability of the motor bearing 260.

[0169] In one embodiment, a valve 1045 is provided on a heat dissipation channel 1041 to control the amount of oil in the heat dissipation channel 1041 output to the motor bearing 260. Specifically, when the temperature of the motor bearing 260 is low, the motor bearing 260 does not need to be cooled by oil, and the valve 1045 is controlled to open. The oil with increased temperature flows into the third heat dissipation channel 1043 and is transmitted to the motor bearing 260 through the third heat dissipation channel 1043, thereby increasing the temperature of the oil in the motor bearing 260, reducing the viscosity of the oil, and improving the lubrication effect. Moreover, the temperature of the oil flowing through the circumferential channel 101 is higher than the oil after heat exchange in the heat exchanger 500. The higher temperature oil is used to lubricate the motor bearing 260, and the viscosity of the oil is lower, thereby reducing the resistance of the oil to the motor bearing 260 during operation, thereby improving the operating efficiency of the drive motor 200.

[0170] In one embodiment, another valve 1046 is provided on the other heat dissipation channel 1042 to control the amount of oil in the other heat dissipation channel 1042 that is delivered to the motor bearing 260. Specifically, when the temperature of the motor bearing 260 is high and the motor bearing 260 requires low-temperature oil for heat dissipation, the other valve 1046 is controlled to open. This allows the oil cooled by the heat exchanger 500 to flow directly into the motor bearing 260, dissipating heat from the motor bearing 260 and improving its reliability.

[0171] In one embodiment, one valve 1045 and another valve 1046 are opened simultaneously, and the flow rates of one valve 1045 and another valve 1046 can be controlled according to the actual operating conditions of the motor bearing 260 to control the ratio of the amount of oil entering the motor bearing 260 from the heat exchanger 500 and the circumferential flow channel 101, thereby achieving a balance between the heat dissipation effect on the motor bearing 260 and the resistance of the motor bearing 260 during operation. In one embodiment, the inner diameters of one heat dissipation channel 1041 and another heat dissipation channel 1042 are set according to different operating conditions, thereby regulating the ratio of oil of different temperatures in one heat dissipation channel 1041 and another heat dissipation channel 1042 entering the third heat dissipation channel 1043 to ensure the lubrication and heat dissipation effects of the oil on the motor bearing 260, thereby improving the operating efficiency of the powertrain 10.

[0172] See also Figure 18 In one embodiment, the powertrain 10 includes a resolver sensor 800, the motor shaft 270 of the drive motor 200 is used to fixedly connect the resolver sensor 800, and the motor bearing 260 is used to be located on the same side of the stator 210 of the drive motor as the resolver sensor 800.

[0173] In one embodiment, the powertrain 10 further includes a resolver sensor 800, which is located on the motor shaft 270 and is used to detect the position and speed of the drive motor to ensure stable operation and efficiency of the drive motor. In one embodiment, when the resolver sensor 800 detects that the drive motor speed is too high, which can easily cause the temperature of the motor bearing 260 on the resolver side to rise, the bearing cooling channel 104 connects the heat exchanger 500 and the motor bearing 260 on the resolver side, so that oil can be accurately transferred from the heat exchanger 500 to the motor bearing 260 on the resolver side, dissipating heat from the motor bearing 260 on the resolver side, thereby improving the heat dissipation efficiency of the motor bearing 260 on the resolver side. In one embodiment, the bearing cooling channel 104 can determine the actual temperature of the resolver-side motor bearing 260 based on the motor speed detected by the resolver sensor 800. Based on the actual temperature, the amount of oil flowing from the heat exchanger 500 to the resolver-side motor bearing 260 is controlled. This ensures lubrication and heat dissipation of the resolver-side motor bearing 260 while reducing the resistance of the oil to the resolver-side motor bearing 260, thereby improving the operating efficiency of the powertrain 10. In one embodiment, the bearing cooling channel 104 is used to connect the circumferential channel 101 and the resolver-side motor bearing 260, allowing oil to be precisely transferred from the circumferential channel 101 to the resolver-side motor bearing 260, dissipating heat from the resolver-side motor bearing 260 and improving the heat dissipation efficiency of the resolver-side motor bearing 260.

[0174] The above embodiments are only used to illustrate the technical solutions of the present application, rather than to limit them. Although the present application has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. These modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the various embodiments of the present application, and should all be included in the scope of protection of the present application.

Claims

1. A three-phase copper busbar heat dissipation powertrain, characterized in that: The powertrain includes a drive motor and a three-phase copper busbar. The drive motor is used to receive alternating current output by a motor controller through the three-phase copper busbar. The oil cooling circuit of the powertrain includes a circumferential flow channel, a copper busbar cooling flow channel, and a stator cooling flow channel. The circumferential flow channel is used to receive oil after heat exchange in a heat exchanger. The copper busbar cooling flow channel is used to transmit oil to cool the three-phase copper busbar. The stator cooling flow channel is used to transmit oil to cool the stator of the drive motor, wherein: The circumferential flow channel is distributed along the circumference of the drive motor. The position where the circumferential flow channel is connected to the copper bar cooling flow channel and the position where the circumferential flow channel is connected to the stator cooling flow channel are spaced apart. The copper bar cooling flow channel and the stator cooling flow channel are used to divert the oil in the circumferential flow channel.

2. The powertrain according to claim 1, characterized in that: The position where the circumferential flow channel is connected to the copper bar cooling flow channel and the position where the circumferential flow channel is used to receive the oil after heat exchange in the heat exchanger are spaced apart along the circumference of the drive motor.

3. The powertrain according to claim 1 or 2, characterized in that: The position where the circumferential flow channel is connected to the copper bar cooling flow channel and the position where the circumferential flow channel is connected to the stator cooling flow channel are spaced apart along the circumference of the drive motor.

4. The powertrain according to any one of claims 1 to 3, characterized in that: The circumferential flow channel is used to receive the oil after heat exchange in the heat exchanger through multiple liquid inlet flow channels, and the positions where the multiple liquid inlet flow channels are connected to the circumferential flow channel are used to be spaced along the circumference of the drive motor.

5. The powertrain according to any one of claims 1 to 4, characterized in that: The housing of the power assembly encloses a motor cavity and the copper busbar cooling channel. The motor cavity is used to accommodate the stator of the drive motor. The copper busbar cooling channel is used to penetrate the inner wall of the motor cavity and connect to the circumferential channel.

6. The powertrain according to claim 5, characterized in that: The inner wall of the motor cavity and the stator of the drive motor enclose the circumferential flow channel, and the circumferential flow channel along the circumference of the drive motor is used to surround the stator.

7. The powertrain according to claim 5, characterized in that: The circumferential flow channel along the circumference of the drive motor is used to surround the end winding, and the circumferential flow channel is used to spray oil to the end winding through a plurality of penetrating oil spray holes, and the stator cooling flow channel is used to receive the oil sprayed from the oil spray holes.

8. The powertrain according to any one of claims 1 to 7, characterized in that: A portion of the copper bar cooling channel is used to connect to the circumferential channel in the radial direction of the stator, and another portion of the copper bar cooling channel is used to transmit oil in the axial direction of the stator to cool the three-phase copper bar.

9. The power assembly according to any one of claims 1 to 8, characterized in that: Along the axial direction of the power assembly, the copper bar cooling channel is used to be located on both sides of the axial direction of the power assembly together with the heat exchanger.

10. The powertrain according to any one of claims 1 to 9, characterized in that: The power assembly includes a bearing cooling channel, which is used to receive oil from the circumferential channel and to transmit oil to cool the bearings of the drive motor.

11. The powertrain according to claim 10, characterized in that: The position where the bearing cooling channel is connected to the circumferential channel and the position where the circumferential channel is used to receive the oil after heat exchange in the heat exchanger are spaced apart along the circumference of the drive motor.

12. The powertrain according to claim 11, characterized in that: The bearing cooling channel is used to respectively receive the oil after heat exchange in the heat exchanger and the oil in the circumferential channel and merge the two oils to cool the bearing.

13. The power assembly according to any one of claims 10 to 12, characterized in that: The power assembly includes a resolver sensor, the motor shaft of the drive motor is used to be fixedly connected to the resolver sensor, and the bearing is used to be located on the same side of the stator of the drive motor as the resolver sensor.

14. The power assembly according to any one of claims 1 to 13, characterized in that: The circumferential flow channel is used to receive the oil after heat exchange in the heat exchanger through the liquid inlet flow channel, and the inner diameter of the copper bar cooling flow channel is smaller than the inner diameter of the liquid inlet flow channel.

15. An electric vehicle, characterized in that: It comprises a wheel and a power assembly as claimed in any one of claims 1 to 14, wherein the power assembly is used to drive the wheel to rotate.

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