Differential mechanism

Abstract

The differential mechanism comprises a shaft pin, a main gear and a retainer, the main gear comprises a containing cavity, the inner wall of the containing cavity is provided with a matching part extending in the radial direction of the main gear, the matching part is provided with an installation groove, the installation groove is used for installing the shaft pin, and the retainer is installed on the main gear. Wherein the retainers are arranged on the two opposite sides of the main gear in the axial direction of the main gear respectively, each retainer comprises a main body part and an extending part, the extending parts are arranged in the circumferential direction of the main body parts and extend in the radial direction of the main gear, and each retainer is provided with an extending part extending in the radial direction of the main gear. And the extension part is welded with the main gear. According to the differential mechanism, the use of main gear materials can be reduced, the weight of the main gear is effectively reduced, the cost is reduced, and the manufacturing feasibility of the main gear is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicle transmissions, and particularly to a differential. Background Art

[0002] A differential is a device used to adjust the rotational speeds of the two wheels on a vehicle when turning. The differential includes a main gear and a cage. Generally, the main gear has a relatively small blank inner diameter, which results in a relatively large weight of the main gear, increasing the production cost. Summary of the Invention

[0003] This application provides a differential for solving the problems of a relatively small blank inner diameter of the main gear, large material consumption, and relatively large weight of the main gear.

[0004] An embodiment of this application provides a differential. The differential includes a pin, a main gear, and a cage. The main gear includes a receiving cavity. The inner wall of the receiving cavity is provided with a fitting portion extending in the radial direction of the main gear. The fitting portion is provided with a mounting groove for mounting the pin. The cage is mounted on the main gear. Wherein, along the axial direction of the main gear, the opposite sides of the main gear are respectively provided with the cage. The cage includes a main body portion and an extension portion. The extension portion is provided along the circumferential direction of the main body portion and extends in the radial direction of the main gear. The cages both have an extension portion extending in the radial direction of the main gear, and the extension portion is welded to the main gear.

[0005] Therefore, setting a main gear with a larger inner diameter can reduce the use of materials for the main gear, effectively reduce the weight of the main gear, reduce costs, and improve the feasibility of manufacturing the main gear. At the same time, during the operation of the differential, an overturning moment will be generated when the main gear and the cage rotate, increasing the risk of deformation of the cage. By setting the extension portion to be welded to the receiving cavity, the distance from the axis of the main gear to the side wall of the extension portion can be increased, that is, the distance from the outer wall of the main gear to the welding position of the receiving cavity and the cage can be reduced, thereby reducing the force arm of the main gear acting on the cage and reducing the overturning moment, which is beneficial to improving the stiffness of the cage and the service life of the differential.

[0006] In the embodiment of this application, the main gear has a convex portion. The convex portion is provided along the circumferential direction of the receiving cavity and protrudes along the axial direction of the main gear. The convex portion is sleeved outside the extension portion, and the extension portion is welded to the convex portion.

[0007] Specifically, the inner wall of the convex portion abuts against and is welded to the side wall of the extension portion. The convex portion is used to limit the position of the cage, improve the relative position accuracy between the cage and the main gear, and enhance the reliability of installing the cage on the main gear. Along the axial direction of the main gear, the end face of the extension portion close to the main gear can abut against the side wall of the mating portion, enabling the mating portion to also be used to limit the axial movement of the cage along the main gear, further improving the reliability of installing the cage on the main gear.

[0008] In the embodiment of the present application, along the radial direction of the main gear, the size of the extension portion is 5 mm to 25 mm.

[0009] The size of this extension portion can effectively reduce the distance from the outer wall of the main gear to the welding position of the cage in the accommodating cavity, further reduce the tilting moment, and lower the risk of cage damage. At the same time, this size can make the inner diameter of the accommodating cavity be at an appropriate length, which is beneficial to improving the stability of the main gear transmission.

[0010] In the embodiment of the present application, along the radial direction of the main gear, the size of the accommodating cavity is 115 mm to 130 mm. Compared with the conventional main gear design, the size of the accommodating cavity is increased, which is beneficial to reducing the weight of the main gear, reducing costs, and meeting the actual usage requirements.

[0011] In the embodiment of the present application, along the axial direction of the main gear, the installation groove penetrates through the mating portion.

[0012] The shaft pin can be directly placed into the installation groove along the axis of the main gear, which is more convenient for the assembly of the shaft pin. At the same time, the installation groove penetrating through the mating portion along the radial direction of the main gear can be machined in one step, which is convenient for processing and better meets the actual production requirements.

[0013] In the embodiment of the present application, two installation grooves are provided in the mating portion, and the installation grooves are located on the opposite sides of the mating portion along the radial direction.

[0014] Both ends of the shaft pin along the axis can be installed in the two installation grooves. The inner walls on both sides of the installation groove along the radial direction of the main gear can abut against the shaft pin to limit the radial movement of the shaft pin along the main gear, which is beneficial to improving the reliability of the connection between the shaft pin and the main gear. At the same time, the shaft pin is located in the radial direction of the main gear, which is beneficial to improving the stability of the torque transmission of the shaft pin.

[0015] In the embodiment of the present application, the installation groove is a square groove, and the cross-section of the shaft pin along the direction perpendicular to its own axis is a rectangle.

[0016] Therefore, the inner wall of the square groove abuts against the outer wall of the square shaft pin. The square groove can limit the side walls at both ends of the square shaft pin along the axial direction, that is, limit the circumferential movement of the shaft pin along the main gear, and improve the reliability of installing the shaft pin on the main gear. The square shaft pin can be directly placed into the square groove along the axis of the main gear, which is more convenient for the assembly of the square shaft pin.

[0017] In an embodiment of the present application, the differential further includes side gears, planetary gears, and gaskets. Two cages disposed opposite to each other along the radial direction of the main gear enclose an installation cavity, and the side gears, the planetary gears, and the gaskets are installed in the installation cavity.

[0018] Specifically, the differential includes two planetary gears disposed opposite to each other along the radial direction of the main gear and two side gears disposed opposite to each other along the axial direction of the main gear. The planetary gears are sleeved on both ends of the axle pin along the radial direction of the main gear, and the side gears are located on both sides of the axle pin along the axial direction of the main gear, that is, the side gears are located inside the cage, and each planetary gear can mesh with each side gear. The planetary gear can rotate on its own axis, that is, the planetary gear can rotate around the axle pin. At the same time, the planetary gear can revolve, that is, the planetary gear can rotate around the axis of the side gear. When the differential works, during the meshing process of the planetary gear and the side gear, the planetary gear rotates on its own axis based on the revolution, so that the two sides along the radial direction of the main gear have different rotational speeds.

[0019] Among them, the differential further includes a first gasket and a second gasket. A part of the structure of the planetary gear connected to the axle pin is located inside the cage. The first gasket is used to sleeve one side of the planetary gear close to the inner wall of the main body part, so that the planetary gear does not directly contact the inner wall of the main body part during rotation. The second gasket is used to sleeve one side of the side gear close to the cage, so that the side gear does not directly contact the inside of the cage during rotation, thereby reducing the risk of cage wear and being beneficial to improving the service life of the differential.

[0020] In an embodiment of the present application, the cage further includes a bearing seat extending along the axial direction of the main gear.

[0021] In a specific embodiment, the bearing seat communicates with the installation cavity. The differential further includes a half shaft, the half shaft is installed in the cage, the side gear is sleeved on the half shaft, and the half shaft is used to drive the side gear to rotate. Therefore, the half shaft can be installed in the differential through the bearing seat, which is beneficial to improving the assembly reliability of the differential.

[0022] It should be understood that the above general description and the following detailed description are only exemplary and do not limit the present application. Description of the Drawings

[0023] Figure 1 is a schematic structural diagram of the differential provided by the present application in a specific embodiment;

[0024] Figure 2 is Figure 1 an exploded view of the differential in ;

[0025] Figure 3 is Figure 1 a schematic structural diagram of the cooperation between the main gear and the axle pin in ;

[0026] Figure 4 is Figure 1 Another perspective structural schematic diagram of the main gear and the axle pin in

[0027] Figure 5 is Figure 1 Structural schematic diagram of the cage and the axle pin in

[0028] Explanation of the reference numerals in the drawings:

[0029] 1 - Differential

[0030] 11 - Axle pin

[0031] 12 - Main gear

[0032] 121 - Accommodating cavity

[0033] 122 - Fitting part

[0034] 123 - Installation groove

[0035] 124 - Protruding part

[0036] 13 - Cage

[0037] 131 - Main body part

[0038] 132 - Extension part

[0039] 133 - Bearing seat

[0040] 14 - Side gear

[0041] 15 - Planet gear

[0042] 16 - Spacer

[0043] The drawings here are incorporated into the specification and form a part of this specification, showing embodiments consistent with this application, and are used together with the specification to explain the principles of this application. Detailed implementation manners

[0044] To better understand the technical solutions of this application, the embodiments of this application will be described in detail below with reference to the drawings.

[0045] The differential 1 is used to adjust the rotational speed difference between the left and right wheels of an automobile. By the rotation of components such as the main gear 12 inside it, the rotational speeds of the left and right wheels are adjusted. Among them, the traditional main gear 12 has a relatively small inner diameter, resulting in a relatively large weight of the main gear 12, which is not conducive to actual production and manufacturing. At the same time, the main gear 12 of the differential 1 generally uses a helical gear. The helical gear can better eliminate the influence of pitch error on precision. This type of gear will generate an axial force during rotation. The axial force has a relatively small preset distance from the rotation axis of the main gear 12. Even if the distance from the outer wall of the main gear 12 to the connection position with the cage 13 is large, it further makes the rotational tipping moment of the main gear 12 acting on the cage 13 relatively large, easily leading to the problem of damage to the cage 13.

[0046] To solve the above technical problems, an embodiment of the present application provides a differential 1, as Figure 1 and Figure 2 shown. The differential 1 includes a shaft pin 11, a main gear 12, and a cage 13. As Figure 3 shown, the main gear 12 includes a receiving cavity 121. The inner wall of the receiving cavity 121 is provided with a mating portion 122 extending along the radial direction of the main gear 12. The mating portion 122 is provided with a mounting groove 123 for mounting the shaft pin 11. The cage 13 is mounted on the main gear 12. Among them, along the axial direction of the main gear 12, cage 13s are respectively arranged on the opposite sides of the main gear 12. The cage 13 includes a main body portion 131 and an extension portion 132. The extension portion 132 is arranged along the circumferential direction of the main body portion 131 and extends along the radial direction of the main gear 12. The cage 13s all have extension portions 132 extending along the radial direction of the main gear 12, and the extension portions 132 are welded to the main gear 12.

[0047] Specifically, the shaft pin 11 is used to transmit the torque on both sides of the main gear 12. The mounting groove 123 of the main gear 12 is used to fix the shaft pin 11. The cage 13 is welded inside the receiving cavity 121. In the embodiment of the present application, the inner diameter of the main gear 12 is increased, so that there is a certain required space for mounting the shaft pin 11 on the main gear 12. At the same time, since the inner diameter of the main gear 12 is increased, the cage 13 needs to extend the length of the component that cooperates with the main gear 12, that is, extend the length of the extension portion along the radial direction of the main gear 12, and the side wall of this extension portion is welded to the inner wall of the receiving cavity 121.

[0048] Therefore, setting a main gear 12 with a larger inner diameter can reduce the use of materials for the main gear 12, effectively reduce the weight of the main gear 12, reduce costs, and improve the feasibility of manufacturing the main gear 12. At the same time, during the operation of the differential 1, the main gear 12 and the retaining frame 13 will generate an overturning moment when rotating, increasing the risk of deformation of the retaining frame 13. By setting the extension portion and welding it to the accommodating cavity 121, the distance from the axis of the main gear 12 to the side wall of the extension portion can be increased, that is, the distance from the outer wall of the main gear 12 to the welding position of the accommodating cavity 121 and the retaining frame 13 can be reduced, thereby reducing the force arm of the main gear 12 acting on the retaining frame 13 and reducing the overturning moment, which is beneficial to improving the rigidity of the retaining frame 13 and increasing the service life of the differential 1.

[0049] Among them, the retaining frames 13 located on both axial sides of the main gear 12 are formed by forging technology. Compared with the traditional casting or stamping retaining frames 13, it can effectively avoid hard processing technology, make the forming steps simple and easy, and meet the actual production requirements of the retaining frames 13.

[0050] In a possible implementation manner, the radial edge of the matching portion 122 along the main gear 12 is arc-shaped.

[0051] In a specific embodiment, Figure 2 and Figure 3 As shown, the main gear 12 has a protrusion 124 , which is arranged along the axial direction of the accommodating cavity 121 and protrudes along the circumference of the main gear 12 , and the protrusion 124 is sleeved on the outside of the extension 132 , and the extension 132 and the protrusion 124 are welded.

[0052] Specifically, the inner wall of the protrusion 124 abuts and welds with the side wall of the extension 132, and the protrusion 124 is used to limit the position of the retainer 13, improve the relative position accuracy of the retainer 13 and the main gear 12, and improve the reliability of the retainer 13 being installed on the main gear 12. Along the axial direction of the main gear 12, the end surface of the extension close to the main gear 12 can abut against the side wall of the matching portion 122, so that the matching portion 122 can also be used to limit the axial movement of the retainer 13 along the main gear 12, further improving the reliability of the retainer 13 being installed on the main gear 12.

[0053] Among them, in a possible implementation manner, as Figure 1 As shown, the outer wall of the extension portion facing away from the main gear 12 is flush with the end surface of the protrusion 124 along the side close to the retaining frame 13, which can effectively reduce the space required by the retaining frame 13.

[0054] In a possible implementation, Figure 2As shown, the size of the extension portion 132 is 5 mm to 25 mm. The size of the extension portion 132 can be 5 mm, 6 mm, 7 mm, 8 mm, 9 mm, 10 mm, 11 mm, 12 mm, 13 mm, 14 mm, 15 mm, 16 mm, 17 mm, 18 mm, 19 mm, 20 mm, 21 mm, 22 mm, 23 mm, 24 mm, 25 mm, etc.

[0055] The size of the extension portion can effectively reduce the distance from the outer wall of the main gear 12 to the welding position of the receiving cavity 121 and the cage 13, further reduce the tilting moment, and reduce the risk of damage to the cage 13. At the same time, this size can make the inner diameter of the receiving cavity 121 at an appropriate length, which is beneficial to improving the transmission stability of the main gear 12.

[0056] In a possible implementation manner, as Figure 3 shown, along the radial direction of the main gear 12, the size of the receiving cavity 121 is 115 mm to 130 mm. Compared with the conventional design of the main gear 12, the size of the receiving cavity 121 is increased, which is beneficial to reducing the weight of the main gear 12, reducing costs, and meeting the actual usage requirements.

[0057] The size of the receiving cavity 121 can be 115 mm, 1116 mm, 117 mm, 118 mm, 119 mm, 120 mm, 121 mm, 122 mm, 123 mm, 124 mm, 125 mm, 126 mm, 127 mm, 128 mm, 129 mm, 130 mm, etc.

[0058] Among them, the size of the receiving cavity 121 is related to the outer diameter D of the main gear 12, and the size of the receiving cavity 121 can be 5% D to 80% D.

[0059] In a specific embodiment, as Figure 3 shown, along the axial direction of the main gear 12, the installation groove 123 penetrates the mating portion 122.

[0060] The shaft pin 11 can be directly placed into the installation groove 123 along the axis of the main gear 12, which is more convenient for the assembly of the shaft pin 11. At the same time, the installation groove 123 that penetrates the mating portion 122 along the radial direction of the main gear 12 can be machined in one step, which is convenient for machining and better meets the actual production requirements.

[0061] In a specific embodiment, as Figure 3 shown, two installation grooves 123 are provided in the mating portion 122, and the installation grooves 123 are located on the opposite sides of the mating portion 122 along the radial direction.

[0062] Both ends of the shaft pin 11 along the axis can be installed in the two installation grooves 123. The inner walls on both sides of the installation groove 123 along the radial direction of the main gear 12 can abut against the shaft pin 11, which is used to limit the radial movement of the shaft pin 11 along the main gear 12, facilitating to improve the connection reliability between the shaft pin 11 and the main gear 12. At the same time, the shaft pin 11 is located in the radial direction of the main gear 12, which is conducive to improving the stability of the transmission torque of the shaft pin 11.

[0063] In a specific embodiment, as Figure 3 shown, the installation groove 123 is a square groove, and the cross-section of the shaft pin 11 perpendicular to its own axis is a rectangle. That is, the shaft pin 11 is a square shaft pin.

[0064] Therefore, the inner wall of the square groove abuts against the outer wall of the square shaft pin, and the square groove can limit the side walls at both ends of the square shaft pin along the axis, that is, limit the circumferential movement of the shaft pin 11 along the main gear 12, improving the reliability of the installation of the shaft pin 11 on the main gear 12. The square shaft pin can be directly placed into the square groove along the axis of the main gear 12, which is more convenient for the assembly of the square shaft pin.

[0065] In a specific embodiment, as Figure 2 and Figure 5 shown, the differential 1 further includes side gears 14, planetary gears 15 and gaskets 16. The two cage 13s arranged oppositely along the radial direction of the main gear 12 enclose an installation cavity, and the side gears 14, planetary gears 15 and gaskets 16 are installed in the installation cavity.

[0066] Specifically, the differential 1 includes two planetary gears 15 arranged oppositely along the radial direction of the main gear 12 and two side gears 14 arranged oppositely along the axial direction of the main gear 12. The planetary gears 15 are sleeved on both ends of the shaft pin 11 along the radial direction of the main gear 12, and the side gears 14 are located on both sides of the shaft pin 11 along the axial direction of the main gear 12, that is, the side gears 14 are located in the cage 13, and the planetary gears 15 can be meshed with each side gear 14. The planetary gears 15 can rotate self, that is, the planetary gears 15 can rotate around the shaft pin 11. At the same time, the planetary gears 15 can revolve, that is, the planetary gears 15 can rotate around the axis of the side gear 14. When the differential 1 works, during the meshing process of the planetary gears 15 and the side gears 14, the planetary gears 15 rotate self on the basis of revolving, so that the two sides along the radial direction of the main gear 12 have different rotational speeds.

[0067] Among them, the differential 1 further includes a first gasket and a second gasket, as Figure 5As shown, a part of the structure of the planetary gear 15 connected by the axle pin 11 is located inside the cage 13. The first gasket is used to sleeve one side of the planetary gear 15 close to the inner wall of the main body part 131, so that the planetary gear 15 does not directly contact the inner wall of the main body part 131 during rotation. The second gasket is used to sleeve one side of the side gear 14 close to the cage 13, so that the side gear 14 does not directly contact the inside of the cage 13 during rotation, thereby reducing the risk of wear of the cage 13 and being beneficial to improving the service life of the differential 1.

[0068] In a possible implementation manner, the first gasket and the second gasket are arc-shaped structures. Along the radial direction of the cage 13, the inner contour of the cage 13 in contact with the gasket 16 is arc-shaped, and the outer contours of the planetary gear 15 and the side gear 14 in contact with the gasket 16 are arc-shaped, that is, the outer contour of the gasket 16 is substantially similar to the inner contour of the cage 13, and the gasket 16 is similar to the outer contours of the planetary gear 15 and the side gear 14, so that the gasket has a good fit with the cage 13, and at the same time is beneficial to reducing the occupation of the space in the installation cavity.

[0069] In another possible implementation manner, the cross-sectional shapes of the first gasket and the second gasket are planes. Along the radial direction of the cage 13, the inner end surface of the cage 13 in contact with the gasket 16 is a plane, and the outer end surfaces of the planetary gear 15 and the side gear 14 in contact with the gasket 16 are planes.

[0070] Wherein, the gasket 16 is formed by a heat treatment process to reduce the hardness and reduce the risk of tool damage.

[0071] In a specific embodiment, as Figure 5 shown, the cage 13 further includes a bearing seat 133 extending along the axial direction of the main gear 12. The bearing seat 133 communicates with the installation cavity. The differential 1 further includes a half shaft (not shown in the figure). The half shaft is installed in the cage 13, the side gear 14 is sleeved on the half shaft, and the half shaft is used to drive the side gear 14 to rotate.

[0072] Therefore, the half shaft can be installed in the differential 1 through the bearing seat 133, which is beneficial to improving the assembly reliability of the differential 1.

[0073] The above is only the specific implementation manner of the embodiments of the present application, but the protection scope of the embodiments of the present application is not limited thereto. Any changes or substitutions within the technical scope disclosed in the embodiments of the present application should be covered within the protection scope of the embodiments of the present application. Therefore, the protection scope of the embodiments of the present application should be subject to the protection scope of the claims.

Claims

1. A differential, characterized in that, The differential (1) includes: A spindle pin (11); A main gear (12), the main gear (12) includes a receiving cavity (121), the inner wall of the receiving cavity (121) is provided with a fitting portion (122) extending in the radial direction of the main gear (12), the fitting portion (122) is provided with a mounting groove (123), and the mounting groove (123) is used for mounting the spindle pin (11); A cage (13), the cage (13) is mounted on the main gear (12); Wherein, along the axial direction of the main gear (12), the cage (13) is respectively arranged on the opposite sides of the main gear (12), the cage (13) includes a main body portion (131) and an extension portion (132), the extension portion (132) is arranged along the circumferential direction of the main body portion (131) and extends in the radial direction of the main gear (12), the cage (13) has an extension portion (132) extending in the radial direction of the main gear (12), and the extension portion (132) is welded to the main gear (12).

2. The differential according to claim 1, characterized in that, The main gear (12) has a protrusion (124), the protrusion (124) is arranged along the circumferential direction of the receiving cavity (121) and protrudes along the axial direction of the main gear (12), the protrusion (124) is sleeved outside the extension portion (132), and the extension portion (132) is welded to the protrusion (124).

3. The differential according to claim 1, characterized in that, Along the radial direction of the main gear (12), the size of the extension portion (132) is 5 mm to 25 mm.

4. The differential according to claim 1, characterized in that, Along the radial direction of the main gear (12), the size of the receiving cavity (121) is 115 mm to 130 mm.

5. The differential according to claim 1, characterized in that, Along the axial direction of the main gear (12), the mounting groove (123) penetrates through the fitting portion (122).

6. The differential according to claim 1, wherein, Two mounting grooves (123) are provided in the fitting portion (122), and the mounting grooves (123) are located on the opposite sides of the fitting portion (122) in the radial direction.

7. The differential according to claim 1, characterized in that, The mounting groove (123) is a square groove, and the cross-section of the spindle pin (11) perpendicular to its own axial direction is a rectangle.

8. The differential according to any one of claims 1-7, characterized in that, The differential (1) further includes side gears (14), planet gears (15) and gaskets (16), and the two cages (13) arranged opposite to each other in the radial direction of the main gear (12) enclose a mounting cavity, and the side gears (14), the planet gears (15) and the gaskets (16) are mounted in the mounting cavity.

9. The differential according to any one of claims 1-7, characterized in that, The cage (13) further includes a bearing seat (133) extending along the axial direction of the main gear (12).

Images