Range-extended power assembly with double liquid storage cavities and electric vehicle

Abstract

The utility model provides an extended-range power assembly with double liquid storage cavities and an electric vehicle, a shell of the extended-range power assembly comprises an oil pump groove, two motor cavities arranged in parallel and a speed reducer cavity, the speed reducer cavity is used for containing two parallel shaft gear sets and a liquid baffle, the speed reducer cavity comprises the two liquid storage cavities which are adjacently arranged and communicate with each other, and the two liquid storage cavities are communicated with the oil pump groove. One liquid storage cavity is used for containing cooling liquid to immerse and lubricate one part of one output wheel, one liquid storage cavity comprises two axial cavity walls and a radial cavity wall, the two axial cavity walls are arranged on the two sides of the output wheel in the axial direction of the range-extended power assembly, and the radial cavity wall is stacked on the peripheral side of the output wheel in the radial direction of the range-extended power assembly; and the liquid baffle is used for separating the two liquid storage cavities. The cooling liquid in the cavity of the speed reducer is divided into two parts through the liquid baffle, in the rotating oil stirring process of the output wheel, only a small amount of cooling liquid in one liquid storage cavity needs to be stirred, the oil stirring loss of the speed reducer can be reduced, and the efficiency of the speed reducer is improved.

Description

Technical Field

[0001] The present application relates to the technical field of electric vehicles, and in particular to an extended-range powertrain and an electric vehicle with dual liquid storage chambers. Background Art

[0002] The existing extended-range powertrain has two motors and two parallel shaft gear sets, which require a large amount of coolant to cool and lubricate the two motors and the two parallel shaft gear sets. The internal space of the reducer is an integral cavity with a large amount of coolant, which causes large oil stirring losses during the rotation of the gears inside the reducer cavity, affecting the efficiency of the reducer. Utility Model Content

[0003] The present application provides an extended-range powertrain and an electric vehicle with dual liquid storage chambers.

[0004] In a first aspect, the present application provides an extended-range powertrain with dual fluid reservoirs. The extended-range powertrain includes a drive motor, a generator, and two parallel-shaft gear sets. One parallel-shaft gear set includes an input wheel, an intermediate wheel, and an output wheel. One input wheel is used to drive a drive motor, an intermediate wheel is used to drive an input wheel and an output wheel, and an output wheel is used to drive a wheel through a differential. The other parallel-shaft gear set includes another input wheel and another output wheel that are sequentially connected. The other input wheel is used to receive drive from an engine and is connected to a generator through the other output wheel. The housing of the extended-range powertrain includes an oil pump groove, two motor cavities arranged in parallel, and a reducer cavity. An oil pump groove is used to accommodate an oil pump, and an oil pump is used to deliver coolant to dissipate heat from a drive motor and a generator and to lubricate the two parallel-shaft gear sets. The two motor cavities are arranged in parallel, and the two motor cavities are used to fix the stators of a drive motor and a generator, respectively. A reducer cavity, a reducer cavity is used to accommodate two parallel shaft gear sets and a liquid baffle, a reducer cavity includes two adjacently arranged and connected liquid storage cavities, a liquid storage cavity is used to accommodate coolant for immersing and lubricating a part of an output wheel, a liquid storage cavity includes two axial cavity walls and a radial cavity wall, the two axial cavity walls are arranged on both sides of an output wheel along the axial direction of the extended-range powertrain, and a radial cavity wall is stacked on the outer peripheral side of an output wheel along the radial direction of the extended-range powertrain, another liquid storage cavity is used to accommodate coolant and to connect an oil pump groove to deliver coolant to an oil pump, and a liquid baffle is used to separate the two liquid storage cavities.

[0005] In an embodiment of the present application, a liquid storage chamber is used to contain coolant for immersing and lubricating a portion of an output wheel, so that an output wheel can rotate, stir the oil, and lubricate the coolant in a liquid storage chamber to ensure the normal operation of a parallel shaft gear set.

[0006] In an embodiment of the present application, two axial cavity walls are arranged on both sides of an output wheel along the axial direction of the extended-range powertrain, and the radial cavity wall of a liquid storage cavity is stacked on the outer peripheral side of an output wheel along the radial direction of the extended-range powertrain, so that one liquid storage cavity can wrap one output wheel along the axial direction and radial direction of the extended-range powertrain, so that one output wheel only stirs the coolant contained in one liquid storage cavity, but does not stir the coolant in another liquid storage cavity. The extended-range powertrain requires more coolant for cooling and lubrication, so more coolant is stored in the reducer cavity, resulting in a larger stirring loss of one output wheel. If one output wheel can only stir the coolant in one liquid storage cavity, the drag loss of one output wheel can be effectively reduced, and the efficiency of the reducer can be improved.

[0007] In an embodiment of the present application, another liquid storage chamber is used to contain coolant and to connect to the oil pump groove to deliver coolant to the oil pump, so that the coolant in the other liquid storage chamber can be pumped into the internal flow channel of the housing of the extended-range powertrain through the oil pump to cool and lubricate the drive motor, generator, and reducer, thereby reducing the risk of overheating and failure of the drive motor and generator, and ensuring the normal operation of the reducer.

[0008] In an embodiment of the present application, a liquid baffle separates two liquid storage chambers, and an output wheel rotates during operation to throw out the coolant in one liquid storage chamber, so that the amount of coolant in one liquid storage chamber is less than the amount of coolant in the other liquid storage chamber, so that one liquid storage chamber can only store part of the coolant in the reducer chamber. Compared with one output wheel stirring the coolant in the entire reducer chamber, one output wheel only stirs part of the coolant in one liquid storage chamber, which can reduce the oil stirring loss of one output wheel and improve the efficiency of the reducer.

[0009] In one embodiment, the distance between the two axial cavity walls and an intermediate wheel is less than the radius of an output wheel. The distance between a radial cavity wall and an intermediate wheel is greater than or equal to half the radius of an output wheel, and the distance between a radial cavity wall and an intermediate wheel is less than the radius of an output wheel.

[0010] In an embodiment of the present application, the distance between the two axial cavity walls and the intermediate wheel is smaller than the radius of an output wheel, so that a liquid storage cavity can accommodate a portion of an output wheel, so that a portion of an output wheel can be immersed in lubrication, thereby ensuring the normal operation of a parallel shaft gear set.

[0011] In an embodiment of the present application, the distance between the radial cavity wall and the intermediate wheel is greater than or equal to half the radius of an output wheel, and the distance between the radial cavity wall and the intermediate wheel is less than the radius of an output wheel, so that a liquid storage cavity can accommodate a part of an output wheel along the radial direction of the extended-range powertrain, so that a part of an output wheel can be immersed in coolant and lubricated, ensuring the normal operation of a parallel shaft gear set, and also ensuring that the amount of coolant stored in a liquid storage cavity can be stirred and lubricated by an output wheel.

[0012] In one embodiment, the maximum length of each axial cavity wall along the circumference of the range-extended powertrain is greater than or equal to half the outer circumference of an output wheel. The maximum length of a radial cavity wall along the circumference of the range-extended powertrain is greater than or equal to half the outer circumference of an output wheel.

[0013] In an embodiment of the present application, the maximum length of each axial cavity wall along the circumference of the extended-range powertrain is greater than or equal to half of the outer circumference of an output wheel. Since the extended-range powertrain uses a large amount of coolant, the length of each axial cavity wall is set to be larger, which is beneficial to isolating one output wheel from the coolant in another liquid storage cavity along the axial direction of the extended-range powertrain, thereby reducing the oil stirring loss of one output wheel.

[0014] In an embodiment of the present application, the maximum length of the radial cavity wall along the circumference of the extended-range powertrain is greater than or equal to half of the outer circumference of one output wheel. Since the extended-range powertrain uses a large amount of coolant, the length of the radial cavity wall is set to be larger, which is beneficial to isolating one output wheel from the coolant in another liquid storage cavity along the radial direction of the extended-range powertrain, thereby reducing the oil stirring loss of one output wheel.

[0015] In one embodiment, the inner wall of each axial cavity wall includes an arcuate rib, which protrudes along the axial direction of the range-extended powertrain toward the inner cavity of a liquid storage cavity. In the radial direction of the range-extended powertrain, the distance between the arcuate rib and the axis of an output wheel is less than half the outer diameter of the output wheel.

[0016] In the embodiment of the present application, the inner wall of each axial cavity wall includes a curved rib that protrudes along the axial direction of the range-extended powertrain toward the inner cavity of a liquid reservoir. This reduces the space within a liquid reservoir, thereby reducing the amount of coolant contained within the liquid reservoir, and further reducing oil churning losses at a single output wheel. The curved rib protrudes along the axial direction of the range-extended powertrain toward the inner cavity of a liquid reservoir, thereby reducing the oil churning amplitude at a single output wheel, thereby reducing oil churning losses.

[0017] In an embodiment of the present application, the distance between the radial arc rib of the extended-range powertrain and the axis of an output wheel is less than half the outer diameter of an output wheel, so that the coolant falling from the partial tooth portion above the direction of gravity of an output wheel can first drip onto the arc rib instead of directly hitting the partial tooth portion below the direction of gravity, thereby reducing the oil throwing amplitude of an output wheel, reducing oil stirring loss, and improving the efficiency of the reducer.

[0018] In one embodiment, the distance between two arcuate ribs on the axial cavity walls of the range-extended powertrain is less than the length of a tooth of an output gear. The central angle of each arcuate rib along the circumference of the range-extended powertrain is greater than or equal to half the central angle of the axial cavity wall in which it is located.

[0019] In this embodiment of the present application, the spacing between the two axially extending arcuate ribs of the extended-range powertrain's cavity wall is less than the length of one output gear's teeth. This allows coolant falling from one output gear's teeth to land directly on the arcuate ribs rather than striking other parts of the output gear's teeth, thereby reducing the oil slinging amplitude of the output gear. Furthermore, the arcuate ribs extend into both end faces of one output gear along the axial direction of the extended-range powertrain, further reducing the oil churning space of the output gear and further blocking coolant slinging from the output gear, thereby reducing oil churning losses and wear on the output gear's teeth.

[0020] In an embodiment of the present application, the central angle of each arc-shaped rib along the circumference of the extended-range powertrain is greater than or equal to half of the central angle of an axial cavity wall in which it is located, so that the arc-shaped rib has a longer length along the circumference of the extended-range powertrain, which is beneficial for the arc-shaped rib to occupy more space in a liquid storage cavity, so that the cooling amount in a liquid storage cavity is less, reducing the oil stirring loss of an output wheel, and also beneficial for the arc-shaped rib to better receive the coolant dripping from the teeth above an output wheel along the direction of gravity, reducing the loss of coolant to an output wheel, and extending the service life of an output wheel.

[0021] In one embodiment, the range-extended powertrain further includes a differential, wherein an axial cavity wall, an output wheel, a differential, and another axial cavity wall are arranged in sequence. The other axial cavity wall, along the radial direction of the range-extended powertrain, includes a first segment and a second segment connected to each other, wherein the spacing between the second segment and the axis of one output wheel is smaller than the spacing between the first segment and the axis of one output wheel. The second segment is bent away from the output wheel relative to the first segment along the axial direction of the range-extended powertrain and partially overlaps with a differential housing.

[0022] In an embodiment of the present application, an axial cavity wall, an output wheel, a differential and another axial cavity wall are arranged in sequence, so that one axial cavity wall and another axial cavity wall can block the coolant of one output wheel and the differential from another liquid storage cavity along the axial direction of the extended-range powertrain, thereby reducing the oil stirring loss of one output wheel and the differential.

[0023] In an embodiment of the present application, another axial cavity wall along the radial direction of the extended-range powertrain includes a first section and a second section that are connected. The distance between the second section and the axis of one output wheel is smaller than the distance between the first section and the axis of one output wheel, so that the second section can partially wrap the differential. Since the amount of coolant in the extended-range powertrain is large, the oil stirring loss of the coolant by the differential can be reduced.

[0024] In the embodiment of the present application, the second section along the axial direction of the extended-range powertrain is bent away from an output wheel compared to the first section, and the second section is partially stacked with the differential housing. Since the amount of coolant in the extended-range powertrain is large, the second section is stacked and covered on the differential housing to prevent the coolant from entering the differential housing through the window of the differential housing and increasing the oil stirring loss of the gears in the differential, such as the planetary gears or the half-shaft gears, thereby further reducing the oil stirring loss of the reducer.

[0025] In one embodiment, a liquid storage chamber includes a through hole extending radially through the chamber wall along the radial direction of the range-extended powertrain. The distance between the through hole and the axis of the other input wheel is smaller than the distance between the axis of the output wheel and the axis of the other input wheel. The distance between the through hole and the axis of the intermediate wheel is greater than the outer diameter of the output wheel.

[0026] In an embodiment of the present application, a liquid storage cavity includes a through hole, which penetrates the radial cavity wall of a liquid storage cavity along the radial direction of the extended-range powertrain, so that the coolant outside a liquid storage cavity can enter the liquid storage cavity through the through hole, so that there can be a coolant amount in the liquid storage cavity to meet the lubrication of an output wheel and a differential, thereby ensuring the normal operation of an output wheel and a differential.

[0027] In the embodiment of the present application, the distance between the through hole and the axis of the other input wheel is smaller than the distance between the axis of one output wheel and the axis of the other input wheel, so that the through hole is close to the position of the other input wheel, and further the through hole is adjacent to another liquid storage cavity below the other input wheel, so that the coolant in the other liquid storage cavity can enter the interior of the one liquid storage cavity through the through hole, ensuring that at least part of the coolant in the one liquid storage cavity is supplied to the one output wheel and the differential for lubrication.

[0028] In the embodiment of the present application, the distance between the through hole and the axis of the intermediate wheel is greater than the outer diameter of an output wheel, and the through hole is further away from the position of the intermediate wheel, so that the through hole is closer to the bottom of the liquid storage chamber, thereby allowing the coolant to enter the liquid storage chamber from a lower position, thereby ensuring that there is a small amount of coolant in the liquid storage chamber to lubricate the output wheel.

[0029] In one embodiment, the distance between one through hole and the axis of the other input wheel in the direction of gravity is greater than the distance between the liquid level of the other liquid storage chamber and the axis of the other input wheel.

[0030] In the embodiment of the present application, the distance between a through hole and the axis of another input wheel along the direction of gravity is greater than the distance between the liquid level of another liquid storage chamber and the axis of the other input wheel, so that the through hole can input the coolant in the other liquid storage chamber into the one liquid storage chamber to meet the minimum amount of lubricating oil for one output wheel and ensure the normal rotation of one output wheel.

[0031] In one embodiment, the wall of the other liquid storage chamber includes an oil return hole, which is used to connect the other liquid storage chamber and an oil pump tank. The diameter of one through hole is smaller than the diameter of one oil return hole. The distance between one through hole and one oil return hole is smaller than the distance between the axis of one output wheel and one oil return hole.

[0032] In the embodiment of the present application, the aperture of the through hole is smaller than the aperture of the oil return hole. The smaller aperture of the through hole makes the flow of coolant flowing from another liquid storage chamber into one liquid storage chamber smaller, so that the amount of coolant in one liquid storage chamber is maintained within a smaller range, which is beneficial to reducing the oil stirring loss of an output wheel and a differential, and improving the efficiency of the reducer.

[0033] In an embodiment of the present application, the distance between the through hole and the oil return hole is smaller than the distance between the axis of an output wheel and the oil return hole, so that the oil return hole is arranged at a lower position along the direction of gravity. The distance between the through hole and the oil return hole is smaller than the distance between the axis of the output wheel and the oil return hole, so that the through hole is arranged at a lower position of the output wheel, so that there is a small amount of coolant in the liquid storage chamber to lubricate the output wheel.

[0034] In one embodiment, along the radial direction of the extended-range powertrain, a distance between a radial cavity wall and an output wheel is smaller than a distance between a radial cavity wall and another input wheel.

[0035] In an embodiment of the present application, the distance between a radial cavity wall and an output wheel along the radial direction of the extended-range powertrain is smaller than the distance between the radial cavity wall and another input wheel. The distance between the radial cavity wall and an output wheel is smaller, so that when an output wheel rotates to stir the oil, it can stir the coolant in a liquid storage chamber and throw it out of the liquid storage chamber and into another liquid storage chamber, so that the amount of coolant in one liquid storage chamber is maintained at a relatively small state, thereby reducing the drag loss caused by the large amount of coolant in the reducer cavity of an output wheel in the extended-range powertrain causing it to stir a large amount of coolant when it rotates, thereby improving the efficiency of the reducer.

[0036] In one embodiment, a liquid baffle plate includes two oil baffle sub-plates, each of which includes a radial segment. The two radial segments of the two oil baffle sub-plates are aligned along the axial direction of the range-extended powertrain. Each radial segment includes two radial surfaces, which are radially opposed along an output gear. One radial surface of the two radial segments of the two oil baffle sub-plates forms a portion of the radial wall of one liquid storage cavity, and the other radial surface of the two radial segments forms a portion of the radial wall of the other liquid storage cavity. The sum of the lengths of the two radial segments along the axial direction of the range-extended powertrain is greater than the length of a tooth of an output gear.

[0037] In an embodiment of the present application, the radial sections of the two oil baffle plates are aligned along the axial direction of the extended-range powertrain to form at least a portion of the radial cavity wall of a liquid storage cavity, so that the liquid baffle plate can block the coolant flowing into the other liquid storage cavity along the radial direction of the extended-range powertrain, thereby reducing the amount of coolant in one liquid storage cavity and reducing the oil stirring loss of one output wheel.

[0038] In an embodiment of the present application, each radial segment includes two radial surfaces, and the two radial surfaces are radially opposite to each other along an output wheel. One radial surface of the two radial segments of the two oil baffle plates is part of the radial cavity wall of a liquid storage cavity, and the other radial surface of the two radial segments is part of the radial cavity wall of another liquid storage cavity. The radial sections of the two oil baffle plates of the liquid baffle plate separate the space for storing coolant in the reducer cavity into two liquid storage cavities, so that an output wheel accommodated in a liquid storage cavity can only stir and lubricate the less coolant in the liquid storage cavity, which is beneficial to reduce drag loss and improve the efficiency of the reducer.

[0039] In an embodiment of the present application, the sum of the lengths of the two radial segments along the axial direction of the extended-range powertrain is greater than the length of the teeth of one output wheel, so that one output wheel is wrapped in a liquid storage cavity along the axial direction of the extended-range powertrain, so that one output wheel is isolated from the coolant in another liquid storage cavity, so that one output wheel can stir the oil in a smaller amount of coolant in a liquid storage cavity, thereby reducing the oil stirring loss of one output wheel.

[0040] In one embodiment, the wall of a reducer cavity includes a radial inner wall, a portion of which is arcuate, and the portion of which is another portion of the radial wall of a liquid reservoir cavity. The portion of the radial inner wall is adjacent to two radial segments along the circumference of the range-extending powertrain. The spacing between the portion of the radial inner wall and another input pulley is greater than the spacing between each radial segment and another input pulley. The spacing between the portion of the radial inner wall and an output pulley along the radial direction of the range-extending powertrain is less than or equal to the spacing between each radial segment and the output pulley.

[0041] In an embodiment of the present application, part of the radial inner wall of the reducer cavity is arc-shaped, and part of the radial inner wall is used to form a radial cavity wall of a liquid storage cavity with two radial segments. By using part of the cavity wall of the reducer cavity as part of the radial cavity wall of a liquid storage cavity, materials can be saved and the integration of the extended-range powertrain can be improved.

[0042] In the embodiment of the present application, the radial inner wall of the circumferential portion of the extended-range powertrain is arranged adjacent to the two radial segments, so that a liquid storage cavity constitutes a relatively closed space, so that the coolant in a liquid storage cavity will not leak from the liquid storage cavity, and at least part of the coolant in a liquid storage cavity can be used for stirring and lubricating an output wheel.

[0043] In an embodiment of the present application, the distance between part of the radial inner wall and the other input wheel is greater than the distance between each radial segment and the other input wheel, so that a liquid storage cavity can use part of the radial inner wall of the reducer cavity away from the other input wheel to form another part of the radial cavity wall, and will not occupy too much space outside a liquid storage cavity of the reducer cavity, so that there is enough space to accommodate the coolant outside a liquid storage cavity in the reducer cavity, thereby meeting the large amount of coolant consumption of the extended-range powertrain.

[0044] In an embodiment of the present application, the distance between the radial inner wall of the radial portion of the extended-range powertrain and an output wheel is less than or equal to the distance between each radial segment and an output wheel, which is conducive to the cooperation between the radial inner wall and each radial segment to form a relatively closed space so that the coolant in a liquid storage cavity will not leak out of the liquid storage cavity excessively from the radial cavity wall, thereby ensuring that the amount of coolant is sufficient to lubricate an output wheel, or the coolant outside a liquid storage cavity leaks into a liquid storage cavity from the radial cavity wall, so that the coolant in a liquid storage cavity is maintained at a relatively small amount, thereby reducing the oil churning loss of an output wheel.

[0045] In one embodiment, each oil deflector plate includes an axial segment, and an axial segment of each of the two oil deflector plates corresponds to two axial walls of a liquid storage cavity. The maximum length of each axial segment along the circumference of the range-extended powertrain is greater than half the outer circumference of an output pulley. The length of each axial segment along the radial direction of the range-extended powertrain is less than half the outer diameter of an output pulley.

[0046] In an embodiment of the present application, the maximum length of each axial segment along the circumference of the extended-range powertrain is greater than half the outer circumference of an output wheel. Since the extended-range powertrain uses a large amount of coolant, the length of each axial cavity wall is set to be larger, which is beneficial for isolating the output wheel from the coolant outside a liquid storage cavity and reducing the oil stirring loss of an output wheel.

[0047] In the embodiment of the present application, the length of each axial segment along the radial direction of the extended-range powertrain is less than half the outer diameter of an output wheel, so that each axial segment does not affect the arrangement of the output shaft through which the output wheel passes, and also provides space for the arrangement of a differential connected to the output wheel for transmission, and is also conducive to throwing out the coolant in a liquid storage chamber during the rotation of an output wheel.

[0048] In one embodiment, the cavity wall of a reducer cavity includes two side walls, which are opposite to each other along the axial direction of the extended-range powertrain, a portion of one side wall is an axial cavity wall of at least one of the two liquid storage cavities, and a portion of the other side wall is another axial cavity wall of at least one of the two liquid storage cavities.

[0049] In an embodiment of the present application, the two side walls of the cavity wall of the reused reducer cavity form two axial cavity walls of the two liquid storage cavities. Compared with using additional components to form the two axial cavity walls, the layout space of the reducer in the axial direction of the extended-range powertrain can be reduced, which is conducive to the miniaturization of the reducer. It can also improve the integration of the reducer, save materials and reduce costs.

[0050] In a second aspect, the present application provides an electric vehicle, which includes a frame, a power battery and an extended-range powertrain as in the first aspect, wherein the frame is used to fix the power battery and the extended-range powertrain, a generator is used to receive drive from an engine through another parallel shaft gear set to charge the power battery, and a drive motor is used to receive power from the power battery and drive the wheels through a parallel shaft gear set.

[0051] In the powertrain in the embodiment of the present application, the reducer cavity is divided into two liquid storage cavities by a liquid baffle, and part of an output wheel is accommodated in one liquid storage cavity, so that one output wheel stirs a small amount of coolant in one liquid storage cavity, reducing the oil stirring loss of one output wheel, improving the working efficiency of the reducer, and then improving the efficiency of the powertrain and optimizing the performance of the entire vehicle. BRIEF DESCRIPTION OF THE DRAWINGS

[0052] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings required for use in the embodiments of the present application will be described below.

[0053] Figure 1 is a structural diagram of an electric vehicle provided in an embodiment of the present application;

[0054] Figure 2 is a schematic diagram of an extended-range powertrain provided in an embodiment of the present application;

[0055] Figure 3 Schematic diagram of the structure of the extended-range powertrain provided in an embodiment of the present application;

[0056] Figure 4 is a partial structural diagram of the extended-range powertrain provided in an embodiment of the present application;

[0057] Figure 5 yes Figure 4 Exploded diagram of the mid-range extended-range powertrain;

[0058] Figure 6 is a schematic diagram of a parallel shaft gear set provided in an embodiment of the present application;

[0059] Figure 7 is another schematic diagram of a parallel shaft gear set provided in an embodiment of the present application;

[0060] Figure 8 is another structural schematic diagram of the extended-range powertrain provided in an embodiment of the present application;

[0061] Figure 9 is another structural schematic diagram of the extended-range powertrain provided in an embodiment of the present application;

[0062] Figure 10 is a cross-sectional view of an extended-range powertrain provided in an embodiment of the present application;

[0063] Figure 11 This is another structural schematic diagram of an axial cavity wall provided in an embodiment of the present application;

[0064] Figure 12 is a schematic structural diagram of another axial cavity wall provided in an embodiment of the present application;

[0065] Figure 13 This is a schematic structural diagram of an axial cavity wall provided in an embodiment of the present application;

[0066] Figure 14 yes Figure 8 A partially enlarged view of the M1 part of the mid-range extended-range powertrain. DETAILED DESCRIPTION

[0067] The technical solutions in the embodiments of the present application will be described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments.

[0068] The present application provides an extended-range powertrain with dual fluid reservoirs. The extended-range powertrain includes a drive motor, a generator, and two parallel-shaft gear sets. One parallel-shaft gear set includes an input wheel, an intermediate wheel, and an output wheel. One input wheel is used to drive a drive motor, an intermediate wheel is used to drive an input wheel and an output wheel, and an output wheel is used to drive a wheel through a differential. The other parallel-shaft gear set includes another input wheel and another output wheel that are sequentially connected. The other input wheel is used to receive drive from an engine and is connected to a generator through the other output wheel. The housing of the extended-range powertrain includes an oil pump groove, two motor cavities arranged in parallel, and a reducer cavity. An oil pump groove is used to accommodate an oil pump, which is used to transport coolant to dissipate heat from the drive motor and generator and to lubricate the two parallel-shaft gear sets. The two motor cavities are arranged in parallel, and the two motor cavities are used to fix the stator of the drive motor and the stator of the generator, respectively. The reducer cavity is used to accommodate two parallel shaft gear sets and a liquid baffle. The reducer cavity includes two adjacent and interconnected liquid reservoirs. One liquid reservoir is used to accommodate coolant for immersion lubrication of a portion of an output wheel. One liquid reservoir includes two axial cavity walls and one radial cavity wall. The two axial cavity walls are arranged on either side of an output wheel along the axial direction of the extended-range powertrain, and the radial cavity walls are stacked on the outer peripheral side of an output wheel along the radial direction of the extended-range powertrain. The other liquid reservoir is used to accommodate coolant and is connected to the oil pump groove to deliver coolant to the oil pump. The liquid baffle is used to separate the two liquid reservoirs. In the embodiment of the present application, the amount of coolant required by the extended-range powertrain is relatively large. By accommodating a portion of the output wheel in one liquid reservoir, the output wheel and the differential only stir a small amount of coolant in one liquid reservoir, reducing oil stirring losses at the output wheel and improving the operating efficiency of the reducer.

[0069] The extended-range powertrain 10 provided in the embodiment of the present application can be applied to the electric vehicle 1 .

[0070] Figure 1 This is a schematic structural diagram of the electric vehicle 1 provided in an embodiment of the present application.

[0071] In one embodiment, the electric vehicle 1 includes an extended-range powertrain 10, a frame 20, a power battery 30, and wheels 40. Figure 1 As shown, the vehicle frame 20 is used to secure the extended-range powertrain 10, wheels 40, and power battery 30. The extended-range powertrain 10 is in driving connection with the wheels 40. The power battery 30 provides electrical energy to the extended-range powertrain 10 and can also charge the power battery 30. In this embodiment, the electric vehicle 1 is a car. The extended-range powertrain 10 can drive the wheels 40 to rotate, meaning that the electric vehicle 1 is an extended-range electric vehicle.

[0072] Figure 2A schematic diagram of the extended-range powertrain 10 provided in an embodiment of the present application.

[0073] In one embodiment, the range-extended powertrain 10 includes an engine 11, a drive motor 12, a generator 13, a reducer 14, and a power supply 15. Figure 1 and Figure 2 As shown, the engine 11 is used to output power. For example, the engine 11 can be a fuel engine, which includes a gasoline engine and a diesel engine. The generator 13 is connected to the engine 11 in a transmission manner, and the engine 11 provides power to the generator 13, and the generator 13 converts the kinetic energy output by the engine 11 into electrical energy. The generator 13 is electrically connected to the power battery 30, and the generator 13 can charge the power battery 30 through the power supply device 15. The drive motor 12 is electrically connected to the power battery 30, and the power battery 30 can supply power to the drive motor 12 through the power supply device 15. The drive motor 12 is used to convert the electrical energy output by the power battery 30 into kinetic energy. The drive motor 12 is connected to the wheel 40 in a transmission manner through the reducer 14 to provide power to the wheel 40 and drive the wheel 40 to move. In one embodiment, the generator 13 can be used as a drive motor.

[0074] In this embodiment of the present application, power supply device 15 includes at least one of a motor controller, an onboard charger, a DC converter, a DC power supply, and a vehicle controller. Power supply device 15 is electrically connected to engine 11, drive motor 12, and generator 13 to control the power mode switching of extended-range powertrain 10.

[0075] In one embodiment, the extended-range powertrain 10 further includes a differential 16, such as Figure 1 and Figure 2 As shown, the differential 16 is connected to the wheels 40 via the half-shafts 50. The power generated by the extended-range powertrain 10 is sequentially transmitted to the half-shafts 50 and the wheels 40 to enable the electric vehicle 1 to travel. When the electric vehicle 1 turns or travels on uneven roads, the differential 16 can cause the left and right half-shafts 50 to rotate at different speeds, thereby causing the left and right wheels 40 to rotate at different speeds, ensuring the wheels 40 can roll.

[0076] In the extended-range powertrain, a large amount of coolant is used due to the dual motors and two parallel shaft gear sets in the reducer. The internal space of the reducer is an integral reducer cavity. During the rotation of the reducer gear assembly, all the coolant at the bottom of the reducer cavity is rotated and stirred, resulting in large oil stirring losses, which affects the efficiency of the reducer.

[0077] The embodiment of the present application arranges a liquid baffle in the reducer cavity to separate the coolant in the reducer cavity into two liquid storage chambers, and the output wheel is accommodated in one liquid storage chamber. Compared with stirring all the coolant in the reducer cavity, the output wheel in the embodiment of the present application can only rotate and stir a small amount of coolant in one liquid storage chamber, thereby reducing the oil stirring loss of the reducer and improving the efficiency of the reducer.

[0078] The extended-range powertrain 10 with dual liquid storage chambers of the present application is described in detail below.

[0079] Figure 3 This is a schematic structural diagram of the extended-range powertrain 10 provided in an embodiment of the present application. Figure 4 This is a partial structural diagram of the extended-range powertrain 10 provided in an embodiment of the present application. Figure 5 for Figure 4 Exploded diagram of the mid-range extended-range powertrain 10.

[0080] In one embodiment, a range-extended powertrain 10 with dual fluid reservoirs includes a drive motor 12, a generator 13, and two parallel shaft gear sets 201, as shown in FIG. Figure 2 and Figure 3 As shown, two parallel shaft gear sets 201 are respectively designated as parallel shaft gear set 210 and parallel shaft gear set 220. Parallel shaft gear set 210 includes an input wheel 214, an intermediate wheel 215, and an output wheel 216. Input wheel 214 is used for driving connection to drive motor 12. Intermediate wheel 215 is used for driving connection between input wheel 214 and output wheel 216. Output wheel 216 is used to drive wheels via a differential 16. Parallel shaft gear set 220 includes another input wheel 223 and another output wheel 224, which are sequentially connected. Input wheel 223 is used to receive drive from a generator 13 and is driven to generator 13 via output wheel 224. The housing 101 of the range-extended powertrain 10 includes an oil pump tank 400, two parallel motor cavities 300a and 300b, and a reducer cavity 200. The oil pump groove 400 is used to accommodate an oil pump 17, which is used to deliver coolant to dissipate heat from the drive motor 12 and the generator 13 and to lubricate the two parallel shaft gear sets 201. The two motor cavities 300a and 300b are used to fix the stators of the drive motor 12 and the generator 13 respectively.

[0081] In one embodiment, the reducer cavity 200 is used to accommodate two parallel shaft gear sets 201 and a liquid baffle 100, such as Figures 3 to 5As shown, the reducer cavity 200 includes two adjacently arranged and connected liquid storage chambers 200a and 200b. One liquid storage chamber 200a is used to contain coolant for immersing and lubricating a portion of the output wheel 216. The liquid storage chamber 200a includes two axial cavity walls 110 and one radial cavity wall 120. The two axial cavity walls 110 are arranged on both sides of the output wheel 216 along the axial direction O of the extended-range powertrain, and the radial cavity wall 120 is stacked on the outer peripheral side of the output wheel 216 along the radial direction R of the extended-range powertrain. The other liquid storage chamber 200b is used to contain coolant and to connect the oil pump groove 400 to deliver coolant to the oil pump 17. The liquid baffle 100 is used to separate the two liquid storage chambers 200a and 200b.

[0082] In the embodiment of the present application, the liquid storage chamber 200a is used to contain coolant to immerse and lubricate a portion of the output wheel 216, so that the output wheel 216 can rotate, stir and lubricate the coolant in the liquid storage chamber 200a, thereby ensuring the normal operation of the parallel shaft gear set 210.

[0083] In the embodiment of the present application, two axial cavity walls 110 are arranged on either side of the output wheel 216 along the axial direction O of the extended-range powertrain, and radial cavity walls 120 are stacked on the outer periphery of the output wheel 216 along the radial direction R of the extended-range powertrain. This allows the liquid reservoir 200a to wrap around the output wheel 216 along the axial direction O of the extended-range powertrain and along the radial direction R of the extended-range powertrain. This allows the output wheel 216 to only stir the coolant contained in the liquid reservoir 200a, and not stir the coolant in the liquid reservoir 200b. The extended-range powertrain 10 requires a large amount of coolant for cooling and lubrication. Therefore, a large amount of coolant is stored in the reducer cavity 200, resulting in a large amount of churning loss at the output wheel 216. If the output wheel 216 can only stir the coolant in the liquid reservoir 200a, the drag loss of the output wheel 216 can be effectively reduced, thereby improving the efficiency of the reducer 14.

[0084] In an embodiment of the present application, the liquid storage chamber 200b is used to contain coolant and to connect the oil pump groove 400 to deliver coolant to the oil pump 17, so that the coolant in the liquid storage chamber 200b can be pumped into the two motor chambers 300a, 300b and other internal flow channels of the housing 101 of the extended-range powertrain 10 through the oil pump 17, to cool and lubricate the drive motor 1, the generator 13, and the reducer 14, thereby reducing the risk of overheating and failure of the drive motor 12 and the generator 13, and ensuring the normal operation of the reducer 14.

[0085] In the embodiment of the present application, the liquid baffle 100 separates the two liquid storage chambers 200a and 200b, and the output wheel 216 rotates during operation to throw out the coolant in the liquid storage chamber 200a, so that the amount of coolant in the liquid storage chamber 200a is less than the amount of coolant in the liquid storage chamber 200b, so that the liquid storage chamber 200a can only store part of the coolant in the reducer chamber 200. Compared with the output wheel 216 stirring the coolant in the entire reducer chamber 200, the output wheel 216 only stirs part of the coolant in the liquid storage chamber 200a, which can reduce the stirring loss of the output wheel 216 and improve the efficiency of the reducer 14.

[0086] It should be noted that the axial cavity wall 110 of the liquid storage cavity 200a refers to the cavity wall of the liquid storage cavity 200a arranged along the axial direction O of the extended-range powertrain, and the radial cavity wall 120 refers to the cavity wall of the liquid storage cavity 200a arranged along the radial direction R of the extended-range powertrain.

[0087] The types of coolant include glycol cooling oil, synthetic oil, mineral oil, etc. Exemplarily, the coolant is glycol cooling oil.

[0088] In one embodiment, if Figure 3 and Figure 4 As shown, the amount of coolant in the liquid storage chamber 200a is less than the amount of coolant in the liquid storage chamber 200b.

[0089] The extended-range powertrain 10 requires a large amount of oil for cooling and lubrication. Consequently, a large amount of oil is stored within the reducer chamber 200, resulting in significant oil churning losses at the output pulley 216. In this embodiment of the present application, the reservoir chamber 200a is used to contain coolant to partially immerse and lubricate the output pulley 216. The output pulley 216 rotates and churns the oil within the reservoir chamber 200a. The reservoir chamber 200a is designed to hold less coolant than the reservoir chamber 200b, thereby reducing the amount of oil churning at the output pulley 216, thereby reducing drag losses at the output pulley 216 and improving the efficiency of the reducer 14.

[0090] In one embodiment, the parallel shaft gear set 210 further includes an input shaft 211, an intermediate shaft 212, and an output shaft 213, and the parallel shaft gear set 220 further includes an input shaft 222 and an output shaft 221. Figure 2 and Figure 3 As shown, the output wheel 216 fixed by the output shaft 213 is connected to the motor shaft 302 of the drive motor 12 through an intermediate wheel 215 fixed by an intermediate shaft 212 and an input wheel 214 fixed by the input shaft 211, and the input wheel 223 fixed by the input shaft 222 is connected to the motor shaft 301 of the generator 13 through the output wheel 224 fixed by the output shaft 221.

[0091] The input shaft 211 is drivingly connected to the motor shaft 302 of the drive motor 12. The input wheel 214 is fixed to the input shaft 211. The input shaft 211 is drivingly connected to the intermediate shaft 212 via the intermediate wheel 215 fixed to the intermediate shaft 212. The intermediate shaft 212 is drivingly connected to the output shaft 213. The output wheel 216 is fixed to the output shaft 213. The output wheel 216 transmits power to the differential 16, thereby driving the wheels 40. Bearings are fixed to the motor shaft 302, input shaft 211, intermediate shaft 212, and output shaft 213 of the drive motor 12, respectively, for rotatably connecting the motor shaft 302, input shaft 211, intermediate shaft 212, and output shaft 213 of the drive motor 12 to the housing 101 of the extended-range powertrain 10.

[0092] The input wheel 223 is fixed to the input shaft 222, and the output wheel 224 is fixed to the output shaft 221. The input shaft 222 is drivingly connected to the engine 11, so that the input wheel 223 receives kinetic energy from the engine 11. The input wheel 223 and the input shaft 222 are used to transmit the kinetic energy of the engine 11 to the output shaft 221 and the output wheel 224. The output shaft 221 is drivingly connected to the motor shaft 301 of the generator 13, thereby transmitting the kinetic energy of the engine 11 to the generator 13, driving the motor shaft 301 of the generator 13 to rotate, generate current, and charge the power battery 30. Bearings are fixed to the motor shaft 301 of the generator 13, the input shaft 222, and the output shaft 221, which are used to rotatably connect the motor shaft 301 of the generator 13, the input shaft 222, and the output shaft 221 to the housing 101 of the extended-range powertrain 10.

[0093] In one embodiment, the outer diameter of the input wheel 214 is smaller than the outer diameter of the intermediate wheel 215 , and the outer diameter of the intermediate wheel 215 is smaller than the outer diameter of the output wheel 216 .

[0094] In one embodiment, the outer diameter of the input wheel 223 is greater than the outer diameter of the output wheel 224 .

[0095] In one embodiment, if Figure 2 As shown, the parallel shaft gear set 210 is used to decelerate the kinetic energy of the drive motor 12 and transmit it to the wheels 40, thereby driving the wheels 40. The parallel shaft gear set 220 is used to accelerate the kinetic energy of the engine 11 and transmit it to the generator 13, driving the generator 13 to rotate and generate induced current for power generation. The parallel shaft gear set 210 can also be called a reduction gear set, and the parallel shaft gear set 220 can also be called a speed-increasing gear set.

[0096] Figure 6 Schematic diagram of the parallel shaft gear set 201 provided in an embodiment of the present application.

[0097] In one embodiment, if Figure 3 and Figure 6As shown, along the radial direction R of the extended-range powertrain, the intermediate wheel 215, the input wheel 223 and the output wheel 216 are arranged on the same side of the input wheel 214 and the output wheel 224. The distance between the axis of the intermediate wheel 215 and the axis of the output wheel 224 is greater than the distance between the axis of the input wheel 214 and the axis of the output wheel 224. The distance between the axis of the input wheel 223 and the axis of the input wheel 214 is smaller than the distance between the axis of the input wheel 214 and the axis of the output wheel 224. The distance between the axis of the output wheel 216 and the axis of the input wheel 223 is smaller than the distance between the axis of the intermediate wheel 215 and the axis of the input wheel 223.

[0098] In the embodiments of this application, Figure 6 As shown, the distance between the axis of intermediate wheel 215 and the axis of output wheel 224 is L1, the distance between the axis of input wheel 214 and the axis of output wheel 224 is L2, the distance between the axis of input wheel 223 and the axis of input wheel 214 is L3, the distance between the axis of output wheel 216 and the axis of input wheel 223 is L4, and the distance between the axis of intermediate wheel 215 and the axis of input wheel 223 is L5. L1>L2, so that in the extended-range powertrain radial direction R, intermediate wheel 215 is farther away from output wheel 224 than input wheel 214. L3<L2, so that in the extended-range powertrain radial direction R, input wheel 223 is closer to input wheel 214 than output wheel 224. L4<L5, so that in the extended-range powertrain radial direction R, output wheel 216 is closer to input wheel 223 than intermediate wheel 215. L1>L2, L3<L2, L4<L5 make the arrangement of the parallel shaft gear set 201 of the reducer 14 more centralized.

[0099] Figure 7 Another schematic diagram of the parallel shaft gear set 201 provided in an embodiment of the present application.

[0100] In one embodiment, if Figure 3 and Figure 7 As shown, the distance between the axis of the output wheel 216 and the axis of the output wheel 224 is greater than the distance between the axis of the output wheel 216 and the axis of the input wheel 223, and the distance between the axis of the output wheel 216 and the axis of the input wheel 223 is greater than the sum of the radius of the output wheel 216 and the radius of the input wheel 223.

[0101] In the embodiment of the present application, the distance between the axis of the output wheel 216 and the axis of the output wheel 224 is denoted as L6, the distance between the axis of the output wheel 216 and the axis of the input wheel 223 is denoted as L7, the distance between the axis of the output wheel 216 and the axis of the intermediate wheel 215 is denoted as L8, the radius of the output wheel 216 is denoted as L9, and the radius of the input wheel 223 is denoted as L10. L6>L7, which makes the parallel shaft gear set 210 on the left side of the parallel shaft gear set 201 of the reducer 14 closer to the parallel shaft gear set 220 on the right side, making the arrangement of the parallel shaft gear set 201 more centralized, and also makes the output wheel 216 closer to the input wheel 223, so that there is space between the input wheel 223, the output wheel 216, and the wall of the reducer cavity 200, forming a larger liquid storage chamber 200b, thereby allowing the liquid storage chamber 200b to accommodate more coolant. Since the extended-range powertrain 10 uses a large amount of coolant, L7>L9+L10, L8<L9+L10, so that the liquid storage chamber 200b can accommodate more coolant, and the amount of coolant in the liquid storage chamber 200a is less, which is beneficial to reducing the drag loss of the output wheel 216 and the differential 16 in the extended-range powertrain 10 and improving the efficiency of the reducer 14.

[0102] Figure 8 This is another structural schematic diagram of the extended-range powertrain 10 provided in an embodiment of the present application.

[0103] In one embodiment, if Figure 8 As shown, the distance between the axis of the input wheel 223 and the liquid level in the liquid storage chamber 200b along the gravity direction G is greater than the minimum distance between the axis of the input wheel 223 and the radial cavity wall 120 of the liquid storage chamber 200a.

[0104] In the embodiment of the present application, the distance between the axis of the input wheel 223 and the liquid level in the liquid storage chamber 200b along the gravity direction G is recorded as L11, and the minimum distance between the axis of the input wheel 223 and the radial cavity wall 120 of the liquid storage chamber 200a is recorded as L12. L11>L12, so that along the gravity direction G, the liquid level in the liquid storage chamber 200b is lower than the radial cavity wall 120 of the liquid storage chamber 200a, so that the liquid baffle 100 can prevent the coolant in the liquid storage chamber 200b from entering the liquid storage chamber 200a, so that a smaller amount of coolant is maintained in the liquid storage chamber 200a. The extended-range powertrain 10 requires more coolant for cooling and lubrication, so a large amount of coolant is stored in the reducer cavity 200, which can easily cause large oil stirring losses in the output wheel 216 and the differential 16. At this time, the output wheel 216 and the differential 16 only need to stir less coolant in the liquid storage cavity 200a, effectively reducing the drag loss of the output wheel 216 and the differential 16, which is beneficial to improving the efficiency of the reducer 14.

[0105] In one embodiment, if Figure 3 and Figure 4As shown, the distance between the two axial cavity walls 110 and the intermediate wheel 215 is less than or equal to the radius of the output wheel 216. The distance between the radial cavity wall 120 and the intermediate wheel 215 is greater than or equal to half the radius of the output wheel 216, and the distance between the radial cavity wall 120 and the intermediate wheel 215 is less than the radius of the output wheel 216.

[0106] In this embodiment of the present application, the distance between the two axial cavity walls 110 and the intermediate wheel 215 is smaller than the radius of the output wheel 216. This allows the liquid reservoir 200a to accommodate a portion of the output wheel 216, allowing the portion of the output wheel 216 to be immersed in lubrication, thereby ensuring normal operation of the parallel-axis gear set 210. The distance between the two axial cavity walls 110 and the intermediate wheel 215 refers to the minimum distance between either of the two axial cavity walls 110 and the intermediate wheel 215.

[0107] In the embodiment of the present application, the distance between the radial cavity wall 120 and the intermediate wheel 215 is greater than or equal to half the radius of the output wheel 216, and the distance between the radial cavity wall 120 and the intermediate wheel 215 is less than the radius of the output wheel 216. The liquid reservoir 200a can accommodate the output wheel 216 along the radial direction R of the extended-range powertrain, allowing a portion of the output wheel 216 to be immersed in lubrication, ensuring normal operation of the parallel-axis gear set 210, and ensuring that the amount of coolant stored in the liquid reservoir 200a can be stirred and lubricated by the output wheel 216. The distance between the radial cavity wall 120 and the intermediate wheel 215 refers to the minimum distance between the radial cavity wall 120 and the intermediate wheel 215.

[0108] In one embodiment, if Figure 3 and Figure 4 As shown, the radial cavity wall 120 is stacked on the tooth portion 216 a of the output wheel 216 along the radial direction R of the extended-range powertrain.

[0109] In the embodiment of the present application, the radial cavity wall 120 is stacked on the tooth portion 216a of the output wheel 216 along the radial direction R of the extended-range powertrain, so that the output wheel 216 can be isolated from the coolant in the liquid storage cavity 200b along the radial direction R of the extended-range powertrain through the radial cavity wall 120, so that a smaller amount of coolant is maintained in the liquid storage cavity 200a, thereby reducing the oil stirring loss of the output wheel 216.

[0110] Figure 9 This is another structural schematic diagram of the extended-range powertrain 10 provided in an embodiment of the present application.

[0111] In one embodiment, if Figure 4 and Figure 9 As shown, the maximum length of each axial cavity wall 110 along the circumferential direction C of the extended-range powertrain is greater than or equal to half the outer circumference of the output wheel 216. The maximum length of the radial cavity wall 120 along the circumferential direction C of the extended-range powertrain is greater than or equal to half the outer circumference of the output wheel 216.

[0112] In the embodiment of the present application, the maximum length of each axial cavity wall 110 along the circumferential direction C of the extended-range powertrain is greater than or equal to half of the outer circumference of the output wheel 216. Since the extended-range powertrain 10 uses a large amount of coolant, the length of each axial cavity wall 110 is set to be larger, which is beneficial to isolating the output wheel 216 from the coolant in the liquid storage cavity 200b along the axial direction O of the extended-range powertrain, thereby reducing the oil stirring loss of the output wheel 216.

[0113] In the embodiment of the present application, the maximum length of the radial cavity wall 120 along the circumferential direction C of the extended-range powertrain is greater than or equal to half of the outer circumference of the output wheel 216. Since the extended-range powertrain 10 uses a large amount of coolant, the length of the radial cavity wall 120 is set to be larger, which is beneficial to isolating the output wheel 216 from the coolant in the liquid storage cavity 200b along the radial direction R of the extended-range powertrain, thereby reducing the oil stirring loss of the output wheel 216.

[0114] Figure 10 A cross-sectional view of the extended-range powertrain 10 provided in an embodiment of the present application.

[0115] In one embodiment, the inner wall of each axial cavity wall 110 includes an arc-shaped rib 130, such as Figure 4 and Figure 5 As shown, the arc-shaped rib 130 protrudes toward the inner cavity of the liquid storage cavity 200a along the axial direction O of the extended-range powertrain. Figure 10 As shown, the distance between the R-shaped arc-shaped rib 130 and the axis of the output wheel 216 along the radial direction of the extended-range powertrain is less than half of the outer diameter of the output wheel 216 .

[0116] In the embodiment of the present application, the inner wall of each axial cavity wall 110 includes an arcuate rib 130. The arcuate rib 130 protrudes along the axial direction O of the extended-range powertrain toward the inner cavity of the liquid reservoir chamber 200a. This reduces the space within the liquid reservoir chamber 200a, thereby reducing the amount of coolant contained within the liquid reservoir chamber 200a and further reducing oil churning losses caused by the output wheel 216. The arcuate rib 130 protrudes along the axial direction O of the extended-range powertrain toward the inner cavity of the liquid reservoir chamber 200a, thereby reducing the oil churning amplitude caused by the output wheel 216 and, therefore, reducing oil churning losses.

[0117] In the embodiments of this application, Figure 10As shown, the distance between the arc-shaped rib 130 and the axis of the output wheel 216 along the radial direction R of the extended-range powertrain is recorded as L13, and half of the outer diameter of the output wheel 216 is recorded as L14. L13<L14, so that the coolant falling from the tooth portion 216a of the output wheel 216 facing upward along the gravity direction G can first drip onto the arc-shaped rib 130 instead of directly hitting the tooth portion 216a facing downward along the gravity direction G, thereby reducing the loss caused by the coolant hitting the output wheel 216, reducing the oil throwing amplitude of the output wheel 216, reducing the oil stirring loss, and improving the efficiency of the reducer 14.

[0118] Figure 11 This is a schematic structural diagram of an axial cavity wall 110a provided in an embodiment of the present application. Figure 12 This is a schematic structural diagram of another axial cavity wall 110b provided in an embodiment of the present application.

[0119] In one embodiment, the distance between the arc-shaped ribs 130 of the two axial cavity walls 110 along the axial direction O of the extended-range powertrain is less than the length of the tooth portion 216a of the output wheel 216. Figure 11 and Figure 12 As shown, the central angle of each arc-shaped rib 130 along the circumferential direction C of the extended-range powertrain is greater than or equal to half of the central angle of the axial cavity wall 110 where it is located.

[0120] In the embodiments of this application, Figure 10 As shown, the distance between the two axial walls 110 of the range-extended powertrain along the axial direction O is designated as L15, and the length of the tooth portion 216a of the output wheel 216 is designated as L16. L15 < L16 allows coolant falling from the teeth of the output wheel 216 to fall directly onto the ribs 130 rather than striking other portions of the tooth portion 216a of the output wheel 216. This reduces the oil slinging amplitude of the output wheel 216, thereby reducing coolant damage to the output wheel 216 caused by the impact, and thus extending the service life of the output wheel 216. Furthermore, the ribs 130 extend into the two end surfaces 216b of the output wheel 216 along the axial direction O of the range-extended powertrain, further reducing the oil churning space of the output wheel 216 and further blocking coolant slinging from the output wheel 216, thereby reducing oil slinging losses and damage to the tooth portion 216a of the output wheel 216.

[0121] In the embodiments of this application, Figure 11 and Figure 12As shown, the central angle of each arcuate rib 130 along the circumferential direction C of the extended-range powertrain is recorded as α, and the central angle of the axial cavity wall 110 where each arcuate rib 130 is located is recorded as β, α≥0.5β, so that the arcuate rib 130 has a longer length along the circumferential direction C of the extended-range powertrain, which is beneficial for the arcuate rib 130 to occupy more space in the liquid storage cavity 200a, so that the cooling amount in the liquid storage cavity 200a is less, reducing the oil stirring loss of the output wheel 216, and also beneficial for the arcuate rib 130 to better receive the coolant dripping from the tooth portion 216a above the output wheel 216 along the gravity direction G, reducing the loss of the coolant to the output wheel 216, and extending the service life of the output wheel 216.

[0122] In one embodiment, if Figure 5 As shown, the extended-range powertrain 10 further includes a differential 16, an axial cavity wall 110a, an output wheel 216, the differential 16 and another axial cavity wall 110b are arranged in sequence. Figure 9 As shown, along the extended-range powertrain radial direction R, the axial cavity wall 110b includes a first section 111 and a second section 112 connected to each other. The distance between the second section 112 and the axis of the output wheel 216 is smaller than the distance between the first section 111 and the axis of the output wheel 216. Along the extended-range powertrain axial direction O, the second section 112 is bent away from the output wheel 216 compared to the first section 111. The second section 112 partially overlaps with the housing 161 of the differential 16.

[0123] In the embodiment of the present application, the axial cavity wall 110a, the output wheel 216, the differential 16 and the axial cavity wall 110b are arranged in sequence, so that the axial cavity wall 110a and the axial cavity wall 110b can block the coolant of the output wheel 216 and the differential 16 from the liquid storage cavity 200b along the axial direction O of the extended-range powertrain, thereby reducing the oil stirring loss of the output wheel 216 and the differential 16.

[0124] In the embodiment of the present application, the axial cavity wall 110b along the radial direction R of the extended-range powertrain includes a first section 111 and a second section 112 connected to each other. The distance between the second section 112 and the axis of the output wheel 216 is recorded as L17, and the distance between the first section 111 and the axis of the output wheel 216 is recorded as L18. L17<L18, so that the second section 112 can partially wrap the differential 16. Since the amount of coolant in the extended-range powertrain 10 is large, the oil stirring loss of the coolant by the differential 16 can be reduced.

[0125] In the embodiment of the present application, the second section 112 is bent away from the output wheel 216 compared to the first section 111 along the axial direction O of the extended-range powertrain, and the second section 112 is partially overlapped with the housing 161 of the differential 16. Since the amount of coolant in the extended-range powertrain 10 is large, the second section 112 is overlapped and covered on the housing 161 of the differential 16 to prevent the coolant from entering the differential 16 housing 161 through the window 162 of the differential 16 housing and increasing the oil stirring loss of the gears in the differential 16, such as the oil stirring loss of the planetary gears or the half-shaft gears, thereby further reducing the oil stirring loss of the reducer 14.

[0126] In one embodiment, the arc-shaped rib 130 of the axial cavity wall 110b is divided into two sections, such as Figure 12 As shown, the first section 130a and the second section 130b are spaced apart along the circumferential direction C of the extended-range powertrain, as shown in FIG. Figure 9 and Figure 12 As shown, the output wheel 216 and the differential 16 are fixedly connected along the axial direction O of the extended-range powertrain. The interval between the first section 111 and the second section 112 reserves space for screws to fix the differential 16 and the output wheel 216 through holes, which is beneficial to the structural stability of the extended-range powertrain 10.

[0127] Figure 13 This is a schematic structural diagram of an axial cavity wall 110a provided in an embodiment of the present application.

[0128] In one embodiment, a liquid storage chamber 200a includes a through hole 121, such as Figure 5 and Figure 13 As shown, the through hole 121 penetrates the radial cavity wall 120 along the radial direction R of the extended-range powertrain. Figure 8 and Figure 13 As shown, the distance between the through hole 121 and the axis of the input wheel 223 is smaller than the distance between the axis of the output wheel 216 and the axis of the input wheel 223. The distance between the through hole 121 and the axis of the intermediate wheel 215 is larger than the outer diameter of the output wheel 216.

[0129] In the embodiment of the present application, the liquid storage chamber 200a includes a through hole 121, which penetrates the radial cavity wall 120 of the liquid storage chamber 200a along the radial direction R of the extended-range powertrain, so that the coolant outside the liquid storage chamber 200a can enter the liquid storage chamber 200a through the through hole 121, so that the liquid storage chamber 200a can have an amount of coolant sufficient to lubricate the output wheel 216 and the differential 16, thereby ensuring the normal operation of the output wheel 216 and the differential 16.

[0130] In the embodiments of this application, Figure 8As shown, the distance between the through hole 121 and the axis of the input wheel 223 is L19, and the distance between the axis of the output wheel 216 and the axis of the input wheel 223 is L7, L19<L7, so that the through hole 121 is close to the input wheel 223, and further the through hole 121 is adjacent to the liquid storage chamber 200b below the input wheel 223, so that the coolant in the liquid storage chamber 200b can enter the interior of the liquid storage chamber 200a through the through hole 121, ensuring that at least part of the coolant in the liquid storage chamber 200a is supplied to the output wheel 216 and the differential 16 for lubrication.

[0131] In the embodiment of the present application, the distance between the through hole 121 and the axis of the intermediate wheel 215 is greater than the outer diameter of the output wheel 216. The through hole 121 is further away from the position of the intermediate wheel 215, so that the through hole 121 is closer to the bottom of the liquid storage chamber 200a, thereby allowing the coolant to enter the liquid storage chamber 200a from a lower position, thereby ensuring that there is a small amount of coolant in the liquid storage chamber 200a to lubricate the output wheel 216.

[0132] In one embodiment, if Figure 8 As shown, the distance between the through hole 121 and the axis of the input wheel 223 along the gravity direction G is greater than the distance between the liquid level of the liquid storage chamber 200 b and the axis of the input wheel 223 .

[0133] In the embodiments of this application, Figure 8 As shown, the distance between the through hole 121 and the axis of the input wheel 223 along the gravity direction G is recorded as L20, and the distance between the liquid level of the liquid storage chamber 200b and the axis of the input wheel 223 is L11. L20>L11, so that the through hole 121 can input the coolant in the liquid storage chamber 200b into the liquid storage chamber 200a to meet the minimum amount of lubricating oil for the output wheel 216 and ensure the normal rotation of the output wheel 216.

[0134] In one embodiment, the wall of the liquid storage chamber 200b includes an oil return hole 203, such as Figure 3 As shown, the oil return hole 203 is used to connect the liquid storage chamber 200b and the oil pump groove 400. Figure 3 and Figure 8 As shown, the diameter of the through hole 121 is smaller than the diameter of the oil return hole 203. The distance between the through hole 121 and the oil return hole 203 is smaller than the distance between the axis of the output wheel 216 and the oil return hole 203.

[0135] In an embodiment of the present application, the cavity wall of the liquid storage cavity 200b includes an oil return hole 203, which is used to connect the liquid storage cavity 200b and the oil pump groove 400. The oil pump groove 400 is used to accommodate the oil pump 17. The oil pump 17 is used to transport the coolant in the liquid storage cavity 200b to the internal flow channel of the extended-range powertrain 10 shell through the oil return hole 203, for cooling and lubricating the parallel shaft gear set 201 of the drive motor 12, the generator 13 and the reducer 14.

[0136] In the embodiment of the present application, the diameter of through-hole 121 is smaller than that of oil return hole 203. The smaller diameter of through-hole 121 reduces the flow of coolant from reservoir chamber 200b into reservoir chamber 200a, keeping the amount of coolant in reservoir chamber 200a within a relatively small range. This helps reduce oil churning losses in output wheel 216 and differential 16, and improves the efficiency of reducer 14. The larger diameter of oil return hole 203 facilitates oil pump 17 to draw coolant from reservoir chamber 20b through oil return hole 203 and deliver it to housing 101 of range-extended powertrain 10 for cooling and lubricating reducer 14, drive motor 12, and generator 13.

[0137] In an embodiment of the present application, the oil return hole 203 is arranged at a lower position along the gravity direction G, and the distance between the through hole 121 and the oil return hole 203 is smaller than the distance between the axis of the output wheel 216 and the oil return hole 203, so that the through hole 121 is arranged at a lower position of the output wheel 216, so that there is a small amount of coolant in the liquid storage chamber 200a to lubricate the output wheel 216.

[0138] Figure 14 for Figure 8 A partially enlarged view of the M1 portion of the mid-range extended-range powertrain 10.

[0139] In one embodiment, if Figure 4 、 Figure 8 and Figure 14 As shown, along the radial direction R of the extended-range powertrain, the distance between the radial cavity wall 120 and the output wheel 216 is smaller than the distance between the radial cavity wall 120 and the input wheel 223 .

[0140] In the embodiments of this application, Figure 8 As shown, the distance between the radial cavity wall 120 and the output wheel 216 along the radial direction R of the extended-range powertrain is smaller than the distance between the radial cavity wall 120 and the input wheel 223. The distance between the radial cavity wall 120 and the output wheel 216 is smaller, so that when the output wheel 216 rotates to stir the oil, it can stir the coolant in the liquid storage chamber 200a and throw it out of the liquid storage chamber 200a and into the liquid storage chamber 200b, so that the amount of coolant in the liquid storage chamber 200a is maintained at a relatively small state, thereby reducing the drag loss caused by the large amount of coolant in the reducer chamber 200 that the output wheel 216 in the extended-range powertrain 10 needs to stir a large amount of coolant when it rotates, thereby improving the efficiency of the reducer 14.

[0141] In one embodiment, a liquid baffle plate 100 includes two oil baffle sub-plates 140, such as Figure 11 and Figure 12 As shown, each oil deflector plate 140 includes a radial section 142. Figure 9 As shown, the two radial sections 142 of the two oil baffle plates 140 are aligned along the axial direction O of the extended-range powertrain. Figure 3 、 Figure 5 and Figure 9 As shown, each radial segment 142 includes two radial surfaces 142a and 142b. The two radial surfaces 142a are radially opposed to each other along the output wheel 216. One radial surface 142a of the two radial segments 142 of the two oil deflector plates 140 forms a portion of the radial cavity wall 120 of the liquid storage chamber 200a, while the other radial surface 142b of the two radial segments 142 forms a portion of the radial cavity wall 200b. The sum of the lengths of the two radial segments 142 along the axial direction O of the extended-range powertrain is greater than the length of the tooth portion 216a of the output wheel 216.

[0142] In the embodiment of the present application, the radial sections 142 of the two oil baffle plates 140 are aligned along the axial direction O of the extended-range powertrain to form at least a portion of the radial cavity wall 120 of the liquid storage chamber 200a, so that the liquid baffle plate 100 can block the coolant in the liquid storage chamber 200b along the radial direction R of the extended-range powertrain, reduce the amount of coolant in the liquid storage chamber 200a, and reduce the oil stirring loss of the output wheel 216.

[0143] In the embodiment of the present application, each radial segment 142 includes two radial surfaces 142a and 142b, and the two radial surfaces 142a are radially opposite to each other along the output wheel 216. One radial surface 142a of the two radial segments 142 of the two oil baffle plates 140 is part of the radial cavity wall 120 of the liquid storage chamber 200a, and the other radial surface 142b of the two radial segments 142 is part of the radial cavity wall of the liquid storage chamber 200b. Through the two oil baffle plates 140 of the liquid baffle plate 100, the space for storing coolant in the reducer cavity 200 is divided into two liquid storage chambers 200a and 200b, so that the output wheel 216 accommodated in the liquid storage chamber 200a can only stir and lubricate the less coolant in the liquid storage chamber 200a, which is beneficial to reduce drag loss and improve the efficiency of the reducer 14.

[0144] In the embodiments of this application, Figure 9 As shown, the sum of the lengths of the radial sections 142 of the two oil baffles 140 along the axial direction O of the extended-range powertrain is recorded as L21, and the length of the tooth portion 216a of the output wheel 216 is L16. L21>L16, so that the output wheel 216 is wrapped in the liquid storage chamber 200a along the axial direction O of the extended-range powertrain, so that the output wheel 216 is isolated from the coolant in the liquid storage chamber 200b, so that the output wheel 216 can stir the oil in the smaller amount of coolant in the liquid storage chamber 200a, thereby reducing the oil stirring loss of the output wheel 216.

[0145] In one embodiment, the cavity wall of the reducer cavity 200 includes a radial inner wall 202, such as Figure 8As shown, the partial radial inner wall 202 is arcuate and forms another portion of the radial wall 120 of the liquid storage chamber 200a. Along the circumferential direction C of the extended-range powertrain, the partial radial inner wall 202 is adjacent to two radial segments 142. The distance between the partial radial inner wall 202 and the input pulley 223 is greater than the distance between each radial segment 142 and the input pulley 223. Along the radial direction R of the extended-range powertrain, the distance between the partial radial inner wall 202 and the output pulley 216 is less than or equal to the distance between each radial segment 142 and the output pulley 216.

[0146] In the embodiment of the present application, a portion of the radial inner wall 202 of the reducer cavity 200 is arcuate. This portion of the radial inner wall 202 is used to form the radial cavity wall 120 of the liquid storage cavity 200a together with the two radial segments 142. Utilizing a portion of the cavity wall of the reducer cavity 200 as part of the radial cavity wall 120 of the liquid storage cavity 200a can save material and improve the integration of the extended-range powertrain 10. In one embodiment, the circumferential length of this portion of the radial inner wall 202 is greater than or equal to the circumferential length of each radial segment 142.

[0147] In the embodiment of the present application, the radial inner wall 202 of the circumferential portion C of the extended-range powertrain is arranged adjacent to the two radial segments 142, so that the liquid storage chamber 200a constitutes a relatively closed space, so that the coolant in the liquid storage chamber 200a will not leak from the liquid storage chamber 200a, and at least part of the coolant in the liquid storage chamber 200a can be stirred and lubricated by the output wheel 216.

[0148] In the embodiments of this application, Figure 8 As shown, the distance between the partial radial inner wall 202 and the input wheel 223 is recorded as L22, and the distance between each radial segment 142 and the input wheel 223 is recorded as L23, L22>L23, so that the liquid storage cavity 200a can use the partial radial inner wall 202 on the left side of the reducer cavity 200 to form another part of the radial cavity wall 120, and will not occupy too much space outside the liquid storage cavity 200a of the reducer cavity 200, so that the coolant outside the liquid storage cavity 200a in the reducer cavity 200 has enough space to be accommodated, meeting the large amount of coolant required by the extended-range powertrain 10.

[0149] In the embodiments of this application, Figure 8As shown, the distance between the radial inner wall 202 and the output wheel 216 along the radial direction R of the extended-range powertrain is less than or equal to the distance between each radial segment 142 and the output wheel 216, which is conducive to the cooperation between the radial inner wall 202 and each radial segment 142 to form a relatively closed space so that the coolant in the liquid storage chamber 200a will not leak out of the liquid storage chamber 200a from the radial cavity wall 120 too much, ensuring that the amount of coolant meets the lubrication of the output wheel 216, or the coolant outside the liquid storage chamber 200a leaks into the liquid storage chamber 200a from the radial cavity wall 120, so that the coolant in the liquid storage chamber 200a is maintained at a relatively small amount, reducing the oil stirring loss of the output wheel 216.

[0150] It should be noted that the radial inner wall 202 of the reducer cavity 200 refers to the inner wall of the reducer cavity 200 arranged along the radial direction R of the extended-range powertrain.

[0151] In one embodiment, if Figure 8 、 Figure 11 and Figure 12 As shown, each oil deflector plate 140 includes an axial segment 141. The axial segments 141 of the two oil deflector plates 140 correspond to the two axial cavity walls 110 of the liquid storage cavity 200a. Along the circumferential direction C of the extended-range powertrain, the maximum length of each axial segment 141 is greater than half the outer circumference of the output pulley 216. Along the radial direction R of the extended-range powertrain, the length of each axial segment 141 is less than half the outer diameter of the output pulley 216.

[0152] In the embodiment of the present application, the maximum length of each axial segment 141 along the circumferential direction C of the extended-range powertrain is greater than half of the outer circumference of the output wheel 216. Since the extended-range powertrain 10 uses a large amount of coolant, the length of each axial cavity wall 110 is set to be larger, which is beneficial for isolating the output wheel from the coolant outside the liquid storage cavity 200a and reducing the oil stirring loss of the output wheel 216.

[0153] In the embodiment of the present application, the length of each axial segment 141 along the radial direction R of the extended-range powertrain is less than half of the outer diameter of the output wheel 216, so that each axial segment 141 will not affect the arrangement of the output shaft 213 through which the output wheel 216 passes, and also provides space for the arrangement of the differential 16 that is transmission-connected to the output wheel 216, and is also beneficial for throwing out the coolant in the liquid storage chamber 200a during the rotation of the output wheel 216.

[0154] In one embodiment, the housing of the extended-range powertrain 10 includes a central integrated housing (not shown), two motor covers (not shown), and a reducer cover. The central integrated housing includes three grooves, two of which, together with the two motor covers, form two motor cavities 300a and 300b, and another groove, together with the reducer cover, forms a reducer cavity 200. One oil baffle plate 140 is pre-fixed to the reducer cover, and another oil baffle plate 140 is pre-fixed in another groove. When the reducer cover is engaged with the other groove of the central integrated housing, the two oil baffle plates 140 enclose a fluid reservoir 200a that accommodates the differential 16 and the output wheel 216.

[0155] In one embodiment, if Figure 3 and Figure 4 As shown, the cavity wall of the reducer cavity 200 includes two side walls (not shown), and the two side walls are opposite to each other along the axial direction O of the extended-range powertrain. A portion of one side wall is an axial cavity wall 110a of at least one of the two liquid storage cavities 200a and 200b, and a portion of the other side wall is another axial cavity wall 110b of at least one of the two liquid storage cavities 200a and 200b.

[0156] In the embodiment of the present application, the two side walls of the cavity wall of the reused reducer cavity 200 form two axial cavity walls 110 of the two liquid storage cavities 200a and 200b. Compared with using additional components to form the two axial cavity walls 110, the layout space of the reducer 14 in the axial direction O of the extended-range powertrain can be reduced, which is conducive to the miniaturization of the reducer 14. It can also improve the integration of the reducer 14, save materials, and reduce costs.

[0157] In one embodiment, the two oil baffle plates 140 of the liquid baffle plate 100 include a radial section 142, and the two radial sections 142 separate the two liquid storage chambers 200a and 200b. Part of the two side walls of the cavity wall of the reused reducer cavity 200 are used to form the two axial cavity walls 110a and 110b of the liquid storage chamber 200a. Part of the two side walls of the cavity wall of the reused reducer cavity 200 are used to form the two axial cavity walls 110a and 110b of the liquid storage chamber 200b, which is conducive to the miniaturization of the reducer 14, and can also improve the integration of the reducer 14, save materials, and reduce costs.

[0158] The above is a detailed introduction to the extended-range powertrain and electric vehicle with dual liquid storage chambers provided in the embodiments of the present application. Specific examples are used herein to illustrate the principles and embodiments of the present application. The description of the above embodiments is only used to help understand the method of the present application and its core idea. At the same time, for those skilled in the art, according to the ideas of the present application, there will be changes in the specific embodiments and application scope. In summary, the content of this specification should not be understood as a limitation on the present application.

Claims

1. An extended-range powertrain with dual liquid storage chambers, characterized in that: The range-extending powertrain includes a drive motor, a generator, and two parallel shaft gear sets. One of the parallel shaft gear sets includes an input wheel, an intermediate wheel, and an output wheel. The input wheel is used to drive the drive motor, the intermediate wheel is used to drive the input wheel and the output wheel, and the output wheel is used to drive the wheels through a differential. The other parallel shaft gear set includes another input wheel and another output wheel that are sequentially connected in a driving manner. The other input wheel is used to receive drive from an engine and is driven to connect to the generator through the other output wheel. The housing of the range-extending powertrain includes: an oil pump tank, the oil pump tank being used to accommodate an oil pump, the oil pump being used to deliver coolant to dissipate heat for the drive motor and the generator and to lubricate the two parallel shaft gear sets; Two motor cavities arranged in parallel, the two motor cavities being used to fix the stator of the one drive motor and the stator of the one generator respectively; A reducer cavity, wherein the reducer cavity is used to accommodate the two parallel shaft gear sets and a liquid baffle, the reducer cavity includes two adjacently arranged and connected liquid storage cavities, one of the liquid storage cavities is used to accommodate coolant for immersing and lubricating a portion of the output wheel, the liquid storage cavity includes two axial cavity walls and one radial cavity wall, the two axial cavity walls are arranged on both sides of the output wheel along the axial direction of the extended-range powertrain, and the radial cavity wall is stacked on the outer peripheral side of the output wheel along the radial direction of the extended-range powertrain, the other liquid storage cavity is used to accommodate coolant and to communicate with the oil pump groove to deliver coolant to the oil pump, and the liquid baffle is used to separate the two liquid storage cavities.

2. The extended-range powertrain according to claim 1, characterized in that: The distance between the two axial cavity walls and the intermediate wheel is less than or equal to the radius of the output wheel; The distance between the radial cavity wall and the intermediate wheel is greater than or equal to half of the radius of the output wheel, and the distance between the radial cavity wall and the intermediate wheel is less than the radius of the output wheel.

3. The extended-range powertrain according to claim 1, characterized in that: The maximum length of each axial cavity wall along the circumference of the extended-range powertrain is greater than or equal to half the outer circumference of the output wheel; The maximum length of the radial cavity wall along the circumference of the extended-range powertrain is greater than or equal to half of the outer circumference of the output wheel.

4. The extended-range powertrain according to claim 2, characterized in that: The maximum length of each axial cavity wall along the circumference of the extended-range powertrain is greater than or equal to half the outer circumference of the output wheel; The maximum length of the radial cavity wall along the circumference of the extended-range powertrain is greater than or equal to half of the outer circumference of the output wheel.

5. The extended-range powertrain according to claim 1, characterized in that: The inner wall of each axial cavity wall includes an arc-shaped convex rib, and the arc-shaped convex rib protrudes along the axial direction of the extended-range powertrain toward the inner cavity of the liquid storage cavity, wherein: A distance between the arc-shaped rib and the axis of the output wheel in a radial direction of the range-extended powertrain is less than half of an outer diameter of the output wheel.

6. The extended-range powertrain according to claim 5, characterized in that: The distance between the arc-shaped ribs of the two axial cavity walls along the axial direction of the extended-range powertrain is smaller than the length of the teeth of the output wheel; The central angle of each of the arc-shaped ribs along the circumference of the extended-range powertrain is greater than or equal to half of the central angle of the axial cavity wall where the rib is located.

7. The extended-range powertrain according to any one of claims 1 to 6, characterized in that: The range-extended powertrain further includes a differential, wherein one of the axial cavity walls, one of the output wheels, one of the differentials, and another of the axial cavity walls are arranged in sequence, wherein: The other axial cavity wall includes a first section and a second section connected in the radial direction of the extended-range powertrain, wherein the distance between the second section and the axis of the one output wheel is smaller than the distance between the first section and the axis of the one output wheel; The second section is bent away from the output wheel compared to the first section along the axial direction of the extended-range powertrain, and the second section is partially overlapped with the housing of the differential.

8. The extended-range powertrain according to any one of claims 1 to 6, characterized in that: The one liquid storage cavity includes a through hole, and the through hole penetrates the radial cavity wall along the radial direction of the extended-range powertrain, wherein: The distance between the one through hole and the axis of the other input wheel is smaller than the distance between the axis of the one output wheel and the axis of the other input wheel; The distance between the through hole and the axis of the intermediate wheel is greater than the outer diameter of the output wheel.

9. The extended-range powertrain according to claim 8, characterized in that: Along the gravity direction, the distance between the one through hole and the axis of the other input wheel is greater than the distance between the liquid level of the other liquid storage chamber and the axis of the other input wheel.

10. The extended-range powertrain according to claim 8, characterized in that: The wall of the other liquid storage cavity includes an oil return hole, and the oil return hole is used to connect the other liquid storage cavity and the oil pump groove, wherein: The aperture of the through hole is smaller than the aperture of the oil return hole; The distance between the one through hole and the one oil return hole is smaller than the distance between the axis of the one output wheel and the one oil return hole.

11. The extended-range powertrain according to any one of claims 1-6, 9, and 10, characterized in that: Along the radial direction of the extended-range powertrain, a distance between the one radial cavity wall and the one output wheel is smaller than a distance between the one radial cavity wall and the other input wheel.

12. The extended-range powertrain according to any one of claims 1-6, 9, and 10, characterized in that: The one liquid baffle plate includes two oil baffle sub-plates, each of the oil baffle sub-plates includes a radial segment, and the two radial segments of the two oil baffle sub-plates are aligned along the axial direction of the extended-range powertrain, wherein: Each of the radial segments includes two radial surfaces, the two radial surfaces being radially opposite to each other along the one output wheel, one radial surface of the two radial segments of the two oil deflector plates being a part of the radial cavity wall of the one liquid storage cavity, and the other radial surface of the two radial segments being a part of the radial cavity wall of the other liquid storage cavity; The sum of the lengths of the two radial segments along the axial direction of the range-extended powertrain is greater than the length of the teeth of the one output wheel.

13. The extended-range powertrain according to claim 12, characterized in that: The cavity wall of the one reducer cavity includes a radial inner wall, a portion of the radial inner wall is arc-shaped, and the portion of the radial inner wall is another portion of the radial cavity wall of the one liquid storage cavity, wherein: The portion of the radial inner wall is arranged adjacent to the two radial segments along the circumference of the extended-range powertrain; The distance between the portion of the radial inner wall and the other input wheel is greater than the distance between each of the radial segments and the other input wheel; Along the radial direction of the extended-range powertrain, the distance between the portion of the radial inner wall and the one output wheel is less than or equal to the distance between each of the radial segments and the one output wheel.

14. The extended-range powertrain according to claim 12, characterized in that: Each of the oil baffle plates comprises an axial section, and the one axial section of the two oil baffle plates respectively corresponds to the two axial cavity walls of the one liquid storage cavity; The maximum length of each of the axial segments along the circumference of the extended-range powertrain is greater than half of the outer circumference of the one output wheel; A length of each of the axial segments along the radial direction of the range-extended powertrain is less than half of an outer diameter of the one output wheel.

15. The extended-range powertrain according to any one of claims 1-6, 9, 10, 13, and 14, characterized in that: The cavity wall of the reducer cavity includes two side walls, which are opposite to each other along the axis of the extended-range powertrain. A portion of one side wall is an axial cavity wall of at least one of the two liquid storage cavities, and a portion of the other side wall is another axial cavity wall of at least one of the two liquid storage cavities.

16. An electric vehicle, characterized in that: The electric vehicle includes a frame, a power battery and an extended-range powertrain as described in any one of claims 1 to 15, wherein the frame is used to fix the power battery and the extended-range powertrain, the generator is used to receive the drive of an engine to charge the power battery through the other parallel shaft gear set, and the drive motor is used to receive power from the power battery and drive the wheels through the parallel shaft gear set.

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