A hydraulic tensioner for an electric vehicle drive system

Abstract

This invention discloses a hydraulic tensioner for an electric vehicle transmission system, relating to the field of automotive tensioner technology. It includes a bracket, a tensioning arm, a hydraulic adjustment unit, a pivot, a rotating part, blades, and a tensioning wheel. The tensioning wheel is coaxial with the rotating part, and an annular cavity is coaxially formed on one end face of the tensioning wheel. Multiple air holes communicating with the annular cavity are formed around the periphery of the tensioning wheel. A flow guiding unit, located on the pivot, guides the airflow generated by the rotation of the blades into the annular cavity. In this invention, the hydraulic adjustment unit imparts rotational potential energy to the tensioning arm, enabling the tensioning wheel to tension the surface of the multi-ribbed belt. Furthermore, when the tensioning wheel rotates, the blades rotate accordingly, generating airflow. This airflow enters the flow guiding unit and is guided to the annular cavity, then blown onto the surface of the multi-ribbed belt through the air holes, thereby dissipating heat from the multi-ribbed belt surface and at least partially reducing the impact on the service life of the multi-ribbed belt.

Description

Technical Field

[0001] This invention relates to the field of automotive tensioner technology, specifically a hydraulic tensioner for electric vehicle transmission systems. Background Technology

[0002] Electric vehicles are complex products involving multiple systems such as cooling, steering, braking, and pneumatics. These systems all require a power source to drive them. The cooling system needs a coolant pump as its power source; the steering system needs a steering pump; and the pneumatic system needs an air compressor. Integrating these power sources and controlling them uniformly can save chassis space and reduce costs. Current electric vehicles typically use a drive motor to power these systems, which is connected to them via belt drive.

[0003] Currently, multi-ribbed belts are mainly used to drive the transmission mechanism of electric vehicles. These belts typically require tensioners. Existing tensioners primarily use spring force to tighten the belt via a tensioning wheel. When the tensioning wheel is tightening the belt, friction occurs between its surface and the belt surface. Over prolonged tensioning, this can generate significant heat on the belt surface. Multi-ribbed belts are rubber-based composite materials with viscoelastic properties. As the belt bends and straightens around the pulley, its internal rubber molecular chains are continuously stretched, compressed, twisted, and recover. During this cyclic deformation, the internal friction between the molecular chains consumes energy, most of which is converted into heat. Current tensioners can only tighten the belt; they cannot effectively dissipate the heat generated. This leads to an increase in heat generation as the tension increases, potentially causing a faster decline in the belt's lifespan. Summary of the Invention

[0004] The purpose of this invention is to provide a hydraulic tensioner for electric vehicle transmission systems to solve the problems mentioned in the background art.

[0005] To achieve the above objectives, the present invention provides the following technical solution: a hydraulic tensioner for an electric vehicle transmission system, comprising: A support frame is rotatably connected to a tensioning arm. The support frame is equipped with a hydraulic adjustment unit, which imparts rotational potential energy to the tensioning arm. The support frame is fixedly mounted with a pivot. A rotating part is rotatably mounted on the pivot. Multiple blades are fixedly connected in an array along the axial direction of the rotating part. A tension wheel is fixedly connected to the end of the blades away from the rotating part. The tension wheel is coaxial with the rotating part. An annular cavity is coaxially opened on one end face of the tension wheel. Multiple air holes communicating with the annular cavity are opened around the periphery of the tension wheel. A flow guiding unit is located on the pivot and is used to guide the airflow generated by the rotation of the blades into the annular cavity.

[0006] Through the above technical solution, the hydraulic adjustment unit imparts the potential energy of the tensioning arm to the rotation, enabling the tensioning wheel to tension the surface of the multi-ribbed belt. In addition, when the tensioning wheel rotates, the blades rotate with it and generate airflow. The airflow enters the guide unit and is guided by the guide unit to the annular cavity, and then blown onto the surface of the multi-ribbed belt through the air blowing hole, thereby dissipating heat from the surface of the multi-ribbed belt and reducing the impact on the service life of the multi-ribbed belt to a certain extent.

[0007] Furthermore, the hydraulic adjustment unit includes a rotating part rotatably connected to the bracket. A hollow cylinder is fixedly connected to the periphery of the rotating part. The end of the hollow cylinder away from the rotating part is open and fitted with a sealing end cap. A drive rod is slidably coaxially inserted through the sealing end cap. A piston is fixedly connected to one end of the drive rod that penetrates into the hollow cylinder. The piston divides the inner cavity of the hollow cylinder into two hydraulic chambers. The hollow cylinder is provided with a damping structure. A rotating arm is fixedly connected to the tensioning arm. A hinge block is fixedly connected to one end of the drive rod that extends out of the hollow cylinder. The hinge block is hinged to the rotating arm. An elastic element is installed in the inner cavity of the hollow cylinder. The elastic element elastically abuts against the piston and imparts potential energy to the piston to move away from the sealing end cap.

[0008] Through the above technical solution, the elastic element generates an elastic resisting force on the piston, which in turn causes the drive rod to exert a pulling force on the rotating arm, which in turn causes the rotating arm to drive the tensioning arm to swing, so that the tensioning wheel can generate tension on the multi-wedge belt. In addition, by setting a damping structure, the piston has a damping force when sliding in the hollow cylinder, preventing the piston from moving too frequently, which would cause the tensioning wheel to frequently change the tension on the surface of the multi-wedge belt, and thus may cause the multi-wedge belt to vibrate.

[0009] Furthermore, the damping structure includes fixed tubes respectively fixed to both ends of the hollow cylinder, and the two fixed tubes are jointly fixed to a damping cylinder, which communicates with the inner cavity of the hollow cylinder.

[0010] With the above technical solution, hydraulic oil is stored in both the hydraulic chamber and the damping cylinder. When the piston moves in the hollow cylinder, it will squeeze the hydraulic oil in one of the hydraulic chambers, causing the hydraulic oil to flow through the fixed pipe in the damping cylinder. Since the hydraulic oil has viscous force, the piston has a certain damping force when it moves in the hollow cylinder. This prevents the acceleration of the piston in the hollow cylinder from being too large, which would cause the tensioning wheel to cause the multi-ribbed belt to vibrate.

[0011] Furthermore, the elastic element is a damping spring wrapped around the drive rod, and the two ends of the damping spring elastically abut against the piston and the sealing end cap respectively in the direction of the spring force.

[0012] Through the above technical solution, the damping spring generates an elastic resisting force on the piston, which in turn causes the drive rod to exert a pulling force on the rotating arm, and enables the tensioning wheel to generate a tensioning force on the surface of the multi-wedge belt.

[0013] Furthermore, the flow guiding unit includes a hollow sleeve rotatably fitted onto a pivot, a flow guiding shroud fixedly fitted around the periphery of the hollow sleeve, and the maximum outer diameter of the flow guiding shroud is consistent with the outer diameter of the tensioning wheel. One end face of the flow guiding shroud slides in contact with one end face of the tensioning wheel that has an annular cavity, and an adjustment component is provided in the annular cavity.

[0014] With the above technical solution, when the blades rotate, the airflow generated will enter the guide shroud, and through the guiding effect of the guide shroud, the airflow will enter the annular cavity, and then enter the blowing hole through the directional component, so that the blowing hole blows air onto the surface of the multi-wedge belt to cool the surface of the multi-wedge belt.

[0015] Furthermore, the outer diameter of the flow guide decreases sequentially in the direction away from the tensioning wheel.

[0016] The above technical solution enables the airflow generated by the blades to be blown along the inner wall of the guide shield into the annular cavity, thereby allowing the airflow to be smoothly guided into the annular cavity.

[0017] Furthermore, the steering assembly includes an annular baffle fixed to the hollow sleeve by multiple stiffeners. The annular baffle engages within the annular cavity and slides in contact with the inner wall of the annular cavity. A steering port in the form of a notch is provided around the periphery of the annular baffle.

[0018] With the above technical solution, the airflow entering the annular cavity is blocked by the annular baffle and cannot be blown out from the air hole. Instead, it can only enter the air hole through the directional port. That is, it can prevent the airflow from blowing out in multiple directions, which would prevent it from being concentrated on the contact surface between the tension wheel and the multi-wedge belt, thus reducing the heat dissipation effect of the airflow on the multi-wedge belt.

[0019] Furthermore, the tensioning wheel is coaxially fixed with multiple annular flanges around its periphery, and the air blowing holes are correspondingly distributed between two adjacent annular flanges.

[0020] Through the above technical solution, the annular flange corresponds to the ribs on the multi-ribbed belt. This reduces the tension on the core wire of the multi-ribbed belt by the tensioning wheel surface, preventing excessive tension on the core wire due to the large contact area between the tensioning wheel surface and the multi-ribbed belt surface when tensioning the multi-ribbed belt. This would affect the strength of the core wire and potentially reduce the tear resistance of the multi-ribbed belt, thus affecting its service life. In addition, because the position of the annular flange corresponds to the ribs of the multi-ribbed belt, the tensioning effect of the tensioning wheel when tensioning the multi-ribbed belt is not significantly affected, ensuring that the multi-ribbed belt maintains tension. Furthermore, an airflow channel is formed between two adjacent annular flanges, allowing airflow from the air holes to the surface of the multi-ribbed belt to flow through this channel, thereby enabling large-scale airflow heat dissipation at the contact area between the annular flange and the multi-ribbed belt surface.

[0021] Furthermore, the height of the annular flange protruding to the outer edge of the tensioning wheel is no more than 3mm.

[0022] The above technical solution prevents the edge of the annular flange from cutting the surface of the multi-wedge belt, thereby reducing wear on the surface of the multi-wedge belt.

[0023] Furthermore, a gear is coaxially and fixedly sleeved at the end of the hollow sleeve, and a connecting column is connected to the bracket. The connecting column is provided with an arc-shaped rack, and the arc-shaped rack meshes with the gear for transmission.

[0024] Through the above technical solution, when the tensioning arm swings, it will cause the arc-shaped rack and gear to move relative to each other, thereby causing the gear and the arc-shaped rack to mesh and transmit power, which in turn causes the gear to rotate. When the gear rotates, it will drive the hollow sleeve to rotate, which in turn drives the annular baffle to rotate. When the annular baffle rotates, it will simultaneously change the orientation of the adjusting port, so that when the tensioning arm rotates, the position of the adjusting port will change accordingly, so that the opening of the adjusting port can always face the contact area between the multi-wedge belt surface and the tensioning wheel.

[0025] Compared with the prior art, the beneficial effects of the present invention are: 1. In this invention, the hydraulic adjustment unit imparts potential energy to the tensioning arm, enabling the tensioning wheel to tension the surface of the multi-ribbed belt. In addition, when the tensioning wheel rotates, the blades rotate along with it and generate airflow. The airflow enters the guide unit and is guided by the guide unit to the annular cavity, and then blown onto the surface of the multi-ribbed belt through the air blowing hole, thereby dissipating heat from the surface of the multi-ribbed belt and reducing the impact on the service life of the multi-ribbed belt to a certain extent. 2. In this invention, the elastic element generates an elastic resisting force on the piston, which in turn causes the drive rod to exert a pulling force on the rotating arm, which in turn causes the rotating arm to drive the tensioning arm to swing, so that the tensioning wheel can generate a tensioning force on the multi-wedge belt. In addition, by setting a damping structure, the piston has a damping force when sliding in the hollow cylinder, preventing the piston from moving too frequently, which would cause the tensioning force on the surface of the multi-wedge belt to change frequently, and thus may cause the multi-wedge belt to vibrate. 3. In this invention, the annular flange corresponds to the ribs on the multi-wedge belt. This reduces the tension on the core wire of the multi-wedge belt caused by the tensioning wheel surface, preventing excessive tension on the core wire due to the large contact area between the tensioning wheel surface and the multi-wedge belt surface when tensioning the multi-wedge belt. This would affect the strength of the core wire and potentially reduce the tear resistance of the multi-wedge belt, thus affecting its service life. In addition, because the position of the annular flange corresponds to the ribs of the multi-wedge belt, the tensioning effect of the tensioning wheel when tensioning the multi-wedge belt is not significantly affected, thus maintaining the tension of the multi-wedge belt. Furthermore, an airflow channel is formed between two adjacent annular flanges, allowing the airflow from the air holes to the surface of the multi-wedge belt to flow through this channel, thereby enabling large-scale airflow heat dissipation at the contact area between the annular flange and the surface of the multi-wedge belt. Attached Figure Description

[0026] Figure 1 This is a schematic diagram of the overall structure of a hydraulic tensioner for an electric vehicle transmission system according to the present invention; Figure 2 for Figure 1 A diagram illustrating the positional relationships from a first-person perspective. Figure 3 for Figure 1 A diagram illustrating the positional relationships from a second-person perspective; Figure 4 for Figure 1 A diagram illustrating the positional relationships from a third-person perspective; Figure 5 for Figure 1 Schematic diagram of the explosive decomposition of the medium structure; Figure 6 for Figure 5 Enlarged schematic diagram of the local structure at point A; Figure 7 This is a schematic diagram showing the positional relationship of the tensioning wheel, hollow sleeve, and arc-shaped rack after assembly in this invention; Figure 8 for Figure 7 A schematic diagram showing the positional relationship of the middle section after it has been cut open; Figure 9 for Figure 7 Schematic diagram of the explosive decomposition of the medium structure; Figure 10This is a schematic diagram showing the positional relationship of the tensioning wheel, rotating part, and blades after assembly in this invention; Figure 11 for Figure 10 A diagram illustrating the positional relationships from a first-person perspective. Figure 12 for Figure 10 A diagram illustrating the positional relationships from a second-person perspective; Figure 13 This is a schematic diagram showing the positional relationship of the rotating part, hollow cylinder and damping cylinder after assembly in this invention. Figure 14 for Figure 13 A schematic diagram showing the positional relationship of the middle section after it has been cut open.

[0027] The following are explanations of the reference numerals in the figures: 1. Rotating part; 2. Damping cylinder; 3. Hollow cylinder; 4. Support; 5. Tensioning wheel; 6. Air inlet; 7. Annular flange; 8. Flow guide; 9. Gear; 10. Arc rack; 11. Connecting column; 12. Hinge block; 13. Drive rod; 14. Pivot; 15. Tensioning arm; 16. Rotating part; 17. Blade; 18. Rotating arm; 19. Hollow sleeve; 20. Annular cavity; 21. Piston; 22. Orientation port; 23. Annular baffle; 24. Sealing end cap; 25. Damping spring. Detailed Implementation

[0028] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0029] Please see Figures 1-14 This invention provides a technical solution: a hydraulic tensioner for an electric vehicle transmission system, comprising a bracket 4 mounted in the electric vehicle by screws, a tensioning arm 15 rotatably connected to the bracket 4, a rotating part 1 rotatably connected to the bracket 4, a hollow cylinder 3 fixed to the periphery of the rotating part 1, the hollow cylinder 3 being open at one end away from the rotating part 1 and fitted with a sealing end cap 24, a drive rod 13 slidably passing through the sealing end cap 24, a piston 21 fixed to one end of the drive rod 13 that passes into the hollow cylinder 3, the piston 21 dividing the inner cavity of the hollow cylinder 3 into two hydraulic chambers, and a fixing tube fixed to each end of the outer wall of the hollow cylinder 3, the two fixing tubes being fixed together to a damping cylinder 2, the damping cylinder 2 being in communication with the inner cavity of the hollow cylinder 3, and the inner cavity of the damping cylinder 2 and the two hydraulic chambers being filled with hydraulic oil, a damping spring 25 being wound around the periphery of the drive rod 13, the two ends of the damping spring 25 elastically abutting against the piston 21 and the sealing end cap 24 respectively in the direction of the spring force; A hinge block 12 is fixedly connected to one end of the drive rod 13 that protrudes from the hollow cylinder 3. A rotating arm 18 is fixedly connected to the downward-facing end of the tensioning arm 15. The rotating arm 18 is hinged to the hinge block 12. A pivot 14 is horizontally fixed to the support 4. A rotating part 16 is rotatably mounted on the periphery of the pivot 14. Multiple blades 17 are arrayed and fixedly connected along the axial direction of the rotating part 16. A tensioning wheel 5 is fixedly connected to the end of each blade 17 away from the rotating part 16. The tensioning wheel 5 is coaxial with the rotating part 16. An annular cavity 20 is coaxially formed on one end face of the tensioning wheel 5. Multiple air holes 6 communicating with the annular cavity 20 are formed around the periphery of the tensioning wheel 5. In addition, a hollow sleeve 19 is rotatably fitted around the periphery of the pivot 14. A guide shroud 8 is fixedly fitted around the periphery of the hollow sleeve 19. The maximum outer diameter of the guide shroud 8 is the same as the outer diameter of the tensioning wheel 5. One end face of the guide shroud 8 slides in contact with the end face of the tensioning wheel 5 with the annular cavity 20. The outer diameter of the guide shroud 8 decreases sequentially in the direction away from the tensioning wheel 5. A hollow sleeve 19 is fixedly connected to an annular baffle 23 by multiple ribs. The annular baffle 23 engages within the annular cavity 20 and slides in contact with the inner wall of the annular cavity 20. The annular baffle 23 has a notch-shaped adjustment port 22 around its periphery. Multiple annular flanges 7 are coaxially fixedly connected to the periphery of the tension wheel 5. Air holes 6 are correspondingly distributed between two adjacent annular flanges 7. The height of the annular flanges 7 protruding to the outer periphery of the tension wheel 5 is no more than 3mm. A gear 9 is coaxially fixedly sleeved at the end of the hollow sleeve 19. A connecting post 11 is connected to the bracket 4. The connecting post 11 has arc-shaped teeth. The arc-shaped rack 10 meshes with the gear 9 for transmission. When the tensioning arm 15 swings, it causes relative movement between the arc-shaped rack 10 and the gear 9, which in turn causes the gear 9 to mesh with the arc-shaped rack 10 for transmission, thus causing the gear 9 to rotate. When the gear 9 rotates, it drives the hollow sleeve 19 to rotate, which in turn drives the annular baffle 23 to rotate. When the annular baffle 23 rotates, it synchronously changes the orientation of the adjusting port 22, so that when the tensioning arm 15 rotates, the position of the adjusting port 22 changes accordingly, ensuring that the opening of the adjusting port 22 always faces the same direction. The annular flange 7 corresponds to the ribs on the multi-ribbed belt, which is located in the contact area between the surface of the multi-ribbed belt and the tensioning wheel 5. This design reduces the tension on the core wire of the multi-ribbed belt caused by the tensioning wheel 5. It prevents the core wire from experiencing excessive tension due to the large contact area between the tensioning wheel 5 and the multi-ribbed belt surface, which could lead to a decrease in core wire strength over time. The contact between the annular flange 7 and the multi-ribbed belt surface effectively prevents excessive tension on the core wire. This affects the strength of the core wire, which may lead to a decrease in the tear resistance of the multi-ribbed tape and affect its service life. In addition, since the position of the annular flange 7 corresponds to the rib of the multi-ribbed tape, the tensioning wheel 5 will not have a significant impact on the tensioning effect when tensioning the multi-ribbed tape, so that the multi-ribbed tape can maintain tension. Furthermore, an airflow channel is formed between two adjacent annular flanges 7, allowing the airflow blown from the air hole 6 to the surface of the multi-ribbed tape to flow in this channel, thereby enabling a large-scale airflow heat dissipation at the contact point between the annular flange 7 and the surface of the multi-ribbed tape.

[0030] Working principle of the invention: The damping spring 25 generates an elastic resisting force on the piston 21, which in turn enables the drive rod 13 to drive the rotating arm 18 to rotate. The rotating arm 18 then drives the tensioning arm 15 to rotate, causing the annular flange 7 on the tensioning wheel 5 to press against the surface of the multi-ribbed belt. The position of the annular flange 7 corresponds to the position of the ribs on the multi-ribbed belt, thus giving the annular flange 7 a tensioning force on the multi-ribbed belt. As the piston 21 moves within the hydraulic chamber, it compresses the hydraulic oil in one hydraulic chamber. The hydraulic oil in this hydraulic chamber flows into the damping cylinder 2 through the fixed pipe and enters another hydraulic chamber. Because the hydraulic oil has a viscous flow, the piston 21 has a damping force when flowing within the hollow cylinder 3. This prevents the acceleration of the piston 21 moving within the hollow cylinder 3 from being too large, which would cause the tensioning arm 15 to swing too frequently and thus cause the multi-ribbed belt to vibrate. When the tension wheel 5 rotates along with the multi-ribbed belt, the blades 17 will also rotate synchronously. When the blades 17 rotate, they will agitate the air and allow the air to enter the space between the tension wheel 5 and the rotating part 16 from the side of the tension wheel 5 away from the guide shroud 8, and then enter the guide shroud 8. The airflow flows along the inner surface of the guide shroud 8 to the annular cavity 20. The airflow entering the annular cavity 20 is blocked by the annular baffle 23 and cannot be blown out from the air hole 6. It can only enter the air hole 6 through the directional port 22. That is, it can prevent the airflow from blowing out in multiple directions, which would prevent it from being concentrated on the contact surface between the tension wheel 5 and the multi-ribbed belt, thus reducing the heat dissipation effect of the airflow on the multi-ribbed belt. Furthermore, when the tensioning arm 15 rotates, it causes relative movement between the arc-shaped rack 10 and the gear 9, which in turn causes the gear 9 to mesh with the arc-shaped rack 10, thus causing the gear 9 to rotate. When the gear 9 rotates, it drives the hollow sleeve 19 to rotate, which in turn drives the annular baffle 23 to rotate. When the annular baffle 23 rotates, it simultaneously changes the orientation of the opening of the adjusting port 22, so that when the tensioning arm 15 rotates, the position of the adjusting port 22 changes accordingly, so that the opening of the adjusting port 22 can always face the contact area between the multi-wedge belt surface and the tensioning wheel 5.

[0031] It should be noted that, in this document, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A hydraulic tensioner for an electric vehicle drive train, characterized in that include: A support frame is rotatably connected to a tensioning arm. The support frame is equipped with a hydraulic adjustment unit, which imparts rotational potential energy to the tensioning arm. The support frame is fixedly mounted with a pivot. A rotating part is rotatably mounted on the pivot. Multiple blades are fixedly connected in an array along the axial direction of the rotating part. A tension wheel is fixedly connected to the end of the blades away from the rotating part. The tension wheel is coaxial with the rotating part. An annular cavity is coaxially opened on one end face of the tension wheel. Multiple air holes communicating with the annular cavity are opened around the periphery of the tension wheel. A flow guiding unit is provided on the pivot and is used to guide the airflow generated by the rotation of the blades into the annular cavity; The hydraulic adjustment unit includes a rotating part rotatably connected to a bracket. A hollow cylinder is fixedly connected to the periphery of the rotating part. The end of the hollow cylinder away from the rotating part is open and fitted with a sealing end cap. A drive rod is slidably coaxially inserted through the sealing end cap. A piston is fixedly connected to one end of the drive rod that penetrates into the hollow cylinder. The piston divides the inner cavity of the hollow cylinder into two hydraulic chambers. The hollow cylinder is provided with a damping structure. A rotating arm is fixedly connected to the tensioning arm. A hinge block is fixedly connected to one end of the drive rod that extends out of the hollow cylinder. The hinge block is hinged to the rotating arm. An elastic element is installed in the inner cavity of the hollow cylinder. The elastic element elastically abuts against the piston and imparts potential energy to the piston to move away from the sealing end cap. The damping structure includes fixed tubes respectively fixed to both ends of the hollow cylinder. The two fixed tubes are jointly fixed to a damping cylinder, which communicates with the inner cavity of the hollow cylinder. The flow guiding unit includes a hollow sleeve rotatably fitted onto a pivot. A flow guiding shroud is fixedly fitted around the periphery of the hollow sleeve, and the maximum outer diameter of the flow guiding shroud is consistent with the outer diameter of the tensioning wheel. One end face of the flow guiding shroud slides in contact with one end face of the tensioning wheel that has an annular cavity. An adjustment component is provided inside the annular cavity. The steering assembly includes an annular baffle fixed to a hollow sleeve by multiple stiffeners. The annular baffle engages within the annular cavity and slides in contact with the inner wall of the annular cavity. A notch-shaped steering port is provided around the periphery of the annular baffle. A gear is coaxially and fixedly sleeved at the end of the hollow sleeve. A connecting column is connected to the bracket. The connecting column is provided with an arc-shaped rack, which meshes with the gear for transmission.

2. The hydraulic tensioner for an electric vehicle drive system of claim 1, wherein, The elastic element is a damping spring wrapped around the drive rod, and the two ends of the damping spring elastically abut against the piston and the sealing end cap, respectively, in the direction of the spring force.

3. The hydraulic tensioner for an electric vehicle drive system of claim 1, wherein, The outer diameter of the flow guide decreases sequentially in the direction away from the tensioning wheel.

4. The hydraulic tensioner for an electric vehicle transmission system according to claim 1, characterized in that, The tensioning wheel has multiple annular flanges coaxially fixed around its periphery, and the air holes are correspondingly distributed between two adjacent annular flanges.

5. The hydraulic tensioner for an electric vehicle transmission system according to claim 4, characterized in that, The height of the annular flange protruding to the outer edge of the tensioning wheel is no more than 3mm.

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