Planetary gear train, gearbox and vehicle

Abstract

The present application discloses a planetary gear train, a gearbox and a vehicle. The planetary gear train comprises several pin shafts, planet gears mounted on the pin shafts, and a sun gear meshing with the planet gears, wherein each pin shaft has an oil cavity, and an oil inlet hole and oil outlet holes, which are in communication with the oil cavity, and the oil outlet holes are located in the outer peripheral surface of the pin shaft; and a needle roller bearing is provided between each pin shaft and a planet gear, and an included angle is formed between the axial direction of each oil outlet hole and the direction of a resultant force borne by a needle roller bearing. By means of the structural characteristics and arrangement manner of the pin shafts of the planetary gear train of the present application, the service life of the pin shafts and the needle roller bearings can be prolonged.

Description

Planetary gear mechanism, gearbox and vehicle Technical Field

[0001] The present application belongs to the field of planetary gear technology, and specifically relates to a planetary gear mechanism, a gearbox, and a vehicle. Background Art

[0002] In the planetary gear mechanism, a needle bearing is provided between the pin shaft and the planetary gear to ensure that the pin shaft and the planetary gear can rotate relative to each other better.

[0003] In the related technology, the pin and the needle bearing interact with each other, and the needle roller of the needle bearing can easily cause the oil outlet hole of the pin to be damaged and deformed. As the pin and the needle roller continue to interact, the pin and the needle roller as a whole will be damaged and deformed, thereby affecting the service life of the pin and the needle bearing.

[0004] Summary of the Invention

[0005] In order to solve the technical problem that the current planetary gear mechanism causes damage to the pins and needle rollers, thereby affecting the service life, the present application provides a planetary gear mechanism, a gearbox and a vehicle.

[0006] In a first aspect of the present application, a planetary gear mechanism is provided, comprising a plurality of pins, planetary gears mounted on the pins, and a sun gear meshing with the planetary gears, wherein the pins have an oil cavity and an oil inlet and an oil outlet communicating with the oil cavity, the oil outlet being located on an outer circumferential surface of the pin and facing the sun gear;

[0007] A needle roller bearing is provided between the pin shaft and the planetary gear, and an angle is formed between the axial direction of the oil outlet hole and the direction of the resultant force acting on the needle roller bearing.

[0008] In some embodiments, the angle between the axial direction of the oil outlet hole and the direction of the resultant force acting on the needle bearing is 180°±60°.

[0009] In some embodiments, the angle between the axis connecting the pin and the sun gear and the axial direction of the oil outlet hole is 25° to 155°.

[0010] In some embodiments, the needle roller bearing is a double-row needle roller bearing; the oil outlet hole includes a first oil outlet hole and a second oil outlet hole, and the first oil outlet hole and the second oil outlet hole are respectively arranged corresponding to the two rows of needle rollers of the double-row needle roller bearing.

[0011] In some embodiments, an axial direction of the first oil outlet hole and an axial direction of the second oil outlet hole form an included angle.

[0012] In some embodiments, an included angle between an axial direction of the first oil outlet hole and an axial direction of the second oil outlet hole is 0° to 10°.

[0013] In some embodiments, the oil chamber is L-shaped, comprising a radial section and an axial section that are connected, and an opening of the radial section is located on the outer circumferential surface of the pin shaft to form the oil inlet hole;

[0014] The oil outlet hole is communicated with one end of the axial section that is connected to the radial section, and a plug is provided at the other end of the axial section.

[0015] In some embodiments, the pin has a threaded hole;

[0016] The planetary gear mechanism further includes a planet carrier, which is connected to the threaded hole via a threaded pin.

[0017] In some embodiments, the pin shaft has a positioning structure at one end close to the planet carrier;

[0018] The positioning structure includes a positioning groove provided in the middle of the end surface of the pin shaft and / or a positioning hole provided on one side of the end surface of the pin shaft.

[0019] In some embodiments, the threaded hole and the oil inlet hole are both provided on the circumferential surface of one end of the pin shaft close to the planetary carrier, and the threaded hole and the oil inlet hole are arranged opposite to each other.

[0020] In a second aspect of the present application, a gearbox is provided, comprising the planetary gear mechanism as claimed above.

[0021] In a second aspect of the present application, a vehicle is provided, comprising the gearbox as claimed above.

[0022] According to the planetary gear mechanism provided by one or more embodiments of the present application, in the planetary gear mechanism, the pin and the planetary gear revolve synchronously around the sun gear, the pin is stationary relative to the planetary gear, the planetary gear rotates about the pin as the axis, and the pin does not rotate. In order to enable the pin and the planetary gear to rotate better relative to each other, a needle bearing is provided between the pin and the planetary gear. The needle bearing is fixedly provided in the planetary gear, and the pin is provided in the needle bearing, and the pin and the needle bearing are rotatably connected. During the operation of the planetary gear mechanism, the outer circumferential surface of the pin interacts with the outer circumferential surface of the needle of the needle bearing. In order to improve the rotation effect between the pin and the needle bearing and reduce the wear between the pin and the needle bearing, it is necessary to add lubricating oil between the pin and the needle bearing.

[0023] The pin has a connected oil inlet, oil cavity, and oil outlet. External lubricating oil is injected through the pin's oil inlet, then enters the pin's oil cavity, and then discharged from the pin's oil outlet to lubricate the pin and the needle bearing. Since the main interaction is between the outer circumference of the pin and the outer circumference of the needle bearing's needle roller, it is necessary for the lubricating oil to act directly on the outer circumference between the pin and the needle roller. Therefore, the oil outlet is set on the outer circumference of the pin so that the lubricating oil is discharged from the oil outlet and acts directly on the outer circumference between the pin and the needle roller, thereby ensuring the lubrication effect.

[0024] Due to the interaction between the outer circumference of the pin and the outer circumference of the needle roller of the needle bearing, the oil outlet hole is set on the outer circumference of the pin, and the needle roller will act on the oil outlet hole of the pin. Especially when the oil outlet hole of the pin is facing the direction of the resultant force acting on the needle roller bearing, the needle roller may cause damage and deformation to the oil outlet hole of the pin. As the oil outlet hole of the pin is deformed, the deformed oil outlet hole of the pin will cause damage and deformation to the outer circumference of the needle roller. As the interaction between the pin and the needle roller continues, the pin and the needle roller will be damaged and deformed as a whole, thereby shortening the service life of the pin and the needle roller bearing.

[0025] It should be noted that the so-called resultant force acting on the needle bearing is the resultant force of the acting forces between the needle bearing and the pin during the operation of the planetary gear mechanism. This resultant force is the maximum acting force between the needle bearing and the pin. The direction of this resultant force is along the radial direction of the needle bearing and the pin, and the resultant force is close to the tangent of the motion trajectory of the pin. This resultant force is mainly composed of two components.

[0026] When the planetary gear mechanism is running stably, the pin mainly acts on the two needle rollers on both sides of the resultant force acting on the needle bearing. The forces acting on the two needle rollers on both sides of the resultant force acting on the needle bearing constitute the two components of the resultant force acting on the needle bearing. The directions of the two components are also along the radial direction of the needle bearing and the pin, and the directions of the two components are also close to the tangent of the motion trajectory of the pin.

[0027] Based on this, the axial direction of the oil outlet hole of the pin is set at an angle to the direction of the resultant force acting on the needle bearing. Moreover, since the oil outlet hole of the pin contacts the outer peripheral surface of the needle roller of the needle bearing, in order to ensure the stability of the force acting on the oil outlet hole of the pin, the axial direction of the oil outlet hole of the pin is set along the radial direction of the pin. In this way, the oil outlet hole of the pin avoids the direction of the resultant force acting on the needle bearing, thereby preventing the maximum force between the needle bearing and the pin from acting on the oil outlet hole of the pin, thereby reducing the possibility of the needle bearing damaging the oil outlet hole of the pin, and further reducing the possibility of damage to the pin and needle roller as a whole, thereby extending the service life of the pin and needle bearing. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] FIG1 shows a schematic structural diagram of a planetary gear mechanism in one or more embodiments of the present application.

[0029] FIG. 2 shows a cross-sectional view taken along line AA in FIG. 1 .

[0030] FIG. 3 is an overall cross-sectional view of the planetary gear mechanism in FIG. 1 taken along line BB in FIG. 2 .

[0031] FIG. 4 shows an overall cross-sectional view of the planetary gear mechanism in FIG. 1 taken along line CC in FIG. 2 .

[0032] FIG5 shows a schematic structural diagram of the pin shaft in FIG1 .

[0033] Description of reference numerals:

[0034] 10. Planetary gear mechanism; 100. Pin; 101. Oil chamber; 101a. Radial section; 101b. Axial section; 102. Oil inlet hole; 103. Oil outlet hole; 103a. First oil outlet hole; 103b. Second oil outlet hole; 104. Threaded hole; 110. Plug; 120. Positioning structure; 121. Positioning groove; 122. Positioning hole; 200. Planetary gear; 300. Sun gear; 400. Ring gear; 500. Planet carrier; 501. Through hole; 502. Oil circuit; 600. Needle roller bearing; 610. Needle roller; 700. Threaded pin. DETAILED DESCRIPTION

[0035] In order to enable those skilled in the art to understand the present application more clearly, the technical solutions in the embodiments of the present application will be clearly and completely 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, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without making creative efforts shall fall within the scope of protection of this application.

[0036] The present application is described below with reference to specific embodiments in conjunction with the accompanying drawings.

[0037] Referring to Figures 1 to 5 , a first embodiment of the present application provides a planetary gear mechanism 10. In conjunction with Figures 1 and 2 , the planetary gear mechanism 10 includes a pin 100, planetary gears 200, and a sun gear 300. A plurality of pins 100 and planetary gears 200 are provided. The planetary gears 200 are mounted on the pins 100. Needle roller bearings 600 are provided between the pins 100 and the planetary gears 200. The planetary gears 200 mesh with the sun gear 300. In practical applications, the planetary gear mechanism 10 also includes a ring gear 400. Both the planetary gears 200 and the sun gear 300 are disposed within the ring gear 400. Furthermore, the planetary gears 200 are disposed between the inner teeth of the sun gear 300 and the ring gear 400. The planetary gears 200 mesh with both the sun gear 300 and the ring gear 400. The pin 100 has an oil chamber 101 and an oil inlet hole 102 and an oil outlet hole 103 connected to the oil chamber 101. The oil outlet hole 103 is located on the outer peripheral surface of the pin 100. Combined with Figures 3 and 4, the axial direction of the oil outlet hole 103 has an angle with the direction of the resultant force acting on the needle bearing 600.

[0038] Specifically, in the planetary gear mechanism 10, the pin 100 and the planetary gear 200 revolve synchronously around the sun gear 300. The pin 100 is stationary relative to the planetary gear 200, and the planetary gear 200 rotates about the pin 100, while the pin 100 does not rotate. To facilitate relative rotation between the pin 100 and the planetary gear 200, a needle roller bearing 600 is disposed between the pin 100 and the planetary gear 200. The needle roller bearing 600 is fixedly mounted within the planetary gear 200, and the pin 100 is disposed within the needle roller bearing 600, with the pin 100 being rotationally connected to the needle roller bearing 600. During operation of the planetary gear mechanism 10, the outer circumferential surface of the pin 100 interacts with the outer circumferential surface of the needle roller 610 of the needle roller bearing 600. In order to improve the rotation effect between the pin 100 and the needle bearing 600 and reduce the wear between the pin 100 and the needle bearing 600, lubricating oil needs to be added between the pin 100 and the needle bearing 600.

[0039] The pin 100 has an oil inlet 102, an oil cavity 101, and an oil outlet 103 that are interconnected. External lubricating oil is injected through the oil inlet 102 of the pin 100, then enters the oil cavity 101 of the pin 100, and is then discharged through the oil outlet 103 of the pin 100 to lubricate the space between the pin 100 and the needle bearing 600. Since the main interaction is between the outer circumference of the pin 100 and the outer circumference of the needle roller 610 of the needle bearing 600, it is necessary for the lubricating oil to act directly on the outer circumference between the pin 100 and the needle roller 610. Therefore, the oil outlet 103 is provided on the outer circumference of the pin 100 so that the lubricating oil is discharged from the oil outlet 103 of the pin 100 and acts directly on the outer circumference between the pin 100 and the needle roller 610, thereby ensuring the lubrication effect.

[0040] Due to the interaction between the outer circumferential surface of the pin 100 and the outer circumferential surface of the needle roller 610 of the needle bearing 600, the oil outlet hole 103 is provided on the outer circumferential surface of the pin 100, and the needle roller 610 acts on the oil outlet hole 103 of the pin 100. In particular, when the oil outlet hole 103 of the pin 100 is oriented in the direction of the resultant force acting on the needle bearing 600 (F1 in Figures 3 and 4), the needle roller 610 may cause damage and deformation to the oil outlet hole 103 of the pin 100. As the oil outlet hole 103 of the pin 100 is deformed, the deformed oil outlet hole 103 of the pin 100 will cause damage and deformation to the outer circumferential surface of the needle roller 610. As the interaction between the pin 100 and the needle roller 610 continues, the pin 100 and the needle roller 610 will be damaged and deformed as a whole, thereby affecting the service life of the pin 100 and the needle bearing 600.

[0041] It should be noted that the so-called resultant force acting on the needle bearing 600 is the resultant force of the acting forces between the needle bearing 600 and the pin 100 during the operation of the planetary gear mechanism 10. This resultant force is the maximum acting force between the needle bearing 600 and the pin 100. The direction of this resultant force is along the radial direction of the needle bearing 600 and the pin 100, and the resultant force is close to the tangent of the motion trajectory of the pin 100. This resultant force is mainly composed of two component forces (F2 in Figures 3 and 4).

[0042] When the planetary gear mechanism 10 is running stably, the pin 100 mainly acts on the two needle rollers 610 on both sides of the resultant force applied to the needle bearing 600. The forces applied to the two needle rollers 610 on both sides of the resultant force applied to the needle bearing 600 constitute the two components of the resultant force applied to the needle bearing 600. The directions of the two components are also along the radial direction of the needle bearing 600 and the pin 100, and the directions of the two components are also close to the tangent of the motion trajectory of the pin 100.

[0043] Based on this, the axial direction of the oil outlet hole 103 of the pin 100 is set at an angle to the direction of the resultant force acting on the needle bearing 600. Moreover, since the oil outlet hole 103 of the pin 100 contacts the outer peripheral surface of the needle roller 610 of the needle bearing 600, in order to ensure the force stability of the oil outlet hole 103 of the pin 100, the axial direction of the oil outlet hole 103 of the pin 100 is set along the radial direction of the pin 100. In this way, the oil outlet hole 103 of the pin 100 avoids the direction of the resultant force acting on the needle bearing 600, thereby preventing the maximum force between the needle bearing 600 and the pin 100 from acting on the oil outlet hole 103 of the pin 100. This reduces the possibility of the needle bearing 600 damaging the oil outlet hole 103 of the pin 100, and further reduces the possibility of damage to the pin 100 and the needle roller 610 as a whole, thereby extending the service life of the pin 100 and the needle bearing 600.

[0044] In some embodiments, the angle between the axial direction of the oil outlet hole 103 and the direction of the resultant force acting on the needle bearing 600 is 180°±60°.

[0045] The resultant force acting on needle roller bearing 600 is primarily composed of two components, one on either side of the tangent to the pin 100's trajectory. The angle between the directions of the components and the tangent to the pin 100's trajectory is typically 10° to 20°. The resultant force lies between the two components. Typically, when the two components are equal in magnitude and the angles between them and the tangent to the pin 100's trajectory are the same, the direction of the resultant force coincides with the tangent to the pin 100's trajectory. However, in practice, the two components can vary in magnitude, so the resultant force is typically closer to the tangent to the pin 100's trajectory.

[0046] Based on this, the specific axial orientation of the oil outlet hole 103 of the pin 100 is configured so that the angle between the axial direction of the oil outlet hole 103 and the direction of the resultant force acting on the needle roller bearing 600 is 180°±60°. To minimize the impact of the force acting between the pin 100 and the needle roller bearing 600 on the oil outlet hole 103 of the pin 100, the orientation of the oil outlet hole 103 of the pin 100 is set opposite to the resultant force acting on the needle roller bearing 600. Theoretically, when the angle between the axial direction of the oil outlet hole 103 and the direction of the resultant force acting on the needle roller bearing 600 is 180°, the impact of the force acting between the pin 100 and the needle roller bearing 600 on the oil outlet hole 103 of the pin 100 is minimized, and this is the theoretically optimal location for the oil outlet hole 103. However, in practice, the force acting between the pin 100 and the needle roller bearing 600 is also affected by structures such as the planetary gear 200, the sun gear 300, and the ring gear 400. This results in the direction of the resultant force acting on the needle roller bearing 600 being unstable and varying within a certain range. Therefore, the angle between the axial direction of the oil outlet hole 103 and the direction of the resultant force acting on the needle roller bearing 600 is set to 180°±60°, so that the orientation of the oil outlet hole 103 is adaptively set according to the direction of the resultant force acting on the needle roller bearing 600. Furthermore, by setting the angle between the axial direction of the oil outlet hole 103 and the direction of the resultant force acting on the needle roller bearing 600 to 180°±60°, the orientation of the oil outlet hole 103 not only avoids the direction of the resultant force acting on the needle roller bearing 600, but also avoids the directions of the two components of the resultant force acting on the needle roller bearing 600.

[0047] It should be noted that, to ensure the stability of the force applied to the oil outlet hole 103 of the pin 100, the axial direction of the oil outlet hole 103 of the pin 100 is arranged along the radial direction of the pin 100, and the orientation of the oil outlet hole 103 of the pin 100 is located on the axis of the oil outlet hole 103. Therefore, the angle between the axial direction of the oil outlet hole 103 and the resultant force applied to the needle roller bearing 600 specifically refers to the angle between the orientation of the oil outlet hole 103 and the resultant force applied to the needle roller bearing 600.

[0048] In some embodiments, the angle between the axis connecting the pin 100 and the sun gear 300 and the axial direction of the oil outlet hole 103 is 25° to 155°.

[0049] The angle between the axial direction of the oil outlet hole 103 and the direction of the resultant force acting on the needle roller bearing 600 is 180°±60°. This effectively means that the oil outlet hole 103 of the pin 100 is oriented opposite to the resultant force acting on the needle roller bearing 600. Since the two components of the resultant force acting on the needle roller bearing 600 differ in magnitude and angle, the resultant force acting on the needle roller bearing 600 is typically close to the tangent of the pin 100's motion trajectory and does not overlap with the resultant force acting on the needle roller bearing 600. The angle between the resultant force acting on the needle roller bearing 600 and the tangent of the pin 100's motion trajectory is typically within 5°.

[0050] Therefore, based on the fact that the angle between the axial direction of oil outlet hole 103 and the direction of the resultant force acting on needle roller bearing 600 is 180°±60°, and considering that the direction of the resultant force acting on needle roller bearing 600 and the tangent to the motion trajectory of pin 100 are generally within 5°, the angle between the axis connecting the pin 100 and sun gear 300 and the axial direction of oil outlet hole 103 is limited to 25° to 155°. The axis connecting the axis of pin 100 and sun gear 300 serves as a reference for a fixed direction, while the resultant force acting on needle roller bearing 600 serves as a reference for an uncertain direction. By using the axis connecting the axis of pin 100 and sun gear 300 as a reference, the orientation of oil outlet hole 103 can be more accurately set.

[0051] In some embodiments, as shown in FIG2 , the needle roller bearing 600 is a double-row needle roller bearing; the oil outlet hole 103 includes a first oil outlet hole 103 a and a second oil outlet hole 103 b , and the first oil outlet hole 103 a and the second oil outlet hole 103 b are respectively arranged corresponding to the two rows of needle rollers 610 of the double-row needle roller bearing.

[0052] Due to the combined effects of the pin 100, planetary gears 200, and sun gear 300 in the planetary gear mechanism 10, there is a difference in the forces acting on the two ends of the pin 100. To ensure better force distribution between the pin 100 and the needle roller bearing 600, the needle roller bearing 600 is configured as a double-row needle roller bearing. The two rows of needle rollers 610 of the double-row needle roller bearing connect to the two ends of the pin 100, ensuring a stable force distribution between the pin 100 and the needle roller bearing 600.

[0053] To address this issue, it's necessary to lubricate both rows of needle rollers 610 in the double-row needle roller bearing simultaneously. Therefore, the oil outlet holes 103 of the pin 100 are configured to include a first oil outlet hole 103a and a second oil outlet hole 103b, corresponding to the two rows of needle rollers 610 in the double-row needle roller bearing. Lubricating oil within the oil chamber 101 of the pin 100 is discharged from the first oil outlet hole 103a and the second oil outlet hole 103b, respectively, to lubricate both rows of needle rollers 610 in the double-row needle roller bearing.

[0054] In some embodiments, an axial direction of the first oil outlet hole 103 a and an axial direction of the second oil outlet hole 103 b form an included angle.

[0055] Due to the difference in forces at both ends of the pin 100, which is mainly manifested in that the directions of the resultant forces acting on the two rows of needle rollers 610 of the double-row needle roller bearing from both ends of the pin 100 have an angle, the axial direction of the first oil outlet hole 103a and the axial direction of the second oil outlet hole 103b are respectively set to correspond to the directions of the resultant forces acting on the two rows of needle rollers 610 of the double-row needle roller bearing.

[0056] Specifically, in the two rows of needle rollers 610 in a double-row needle roller bearing, under the condition that the two components of the resultant force acting on the two rows of needle rollers 610 have the same angle with the tangent of the pin 100's trajectory, the two components of the resultant force acting on one row of needle rollers 610 are such that the component located outside the tangent of the pin 100's trajectory is greater than the component located inside the tangent of the pin 100's trajectory, resulting in the direction of the resultant force being outside the tangent of the pin 100's trajectory. The two components of the resultant force acting on the other row of needle rollers 610 are such that the component located inside the tangent of the pin 100's trajectory is greater than the component located outside the tangent of the pin 100's trajectory, resulting in the direction of the resultant force being inside the tangent of the pin 100's trajectory. This means that the resultant force acting on the two rows of needle rollers 610 in the double-row needle roller bearing is located on either side of the tangent of the pin 100's trajectory. This ensures that the first oil outlet hole 103a and the second oil outlet hole 103b are reasonably arranged, reduces the possibility of the first oil outlet hole 103a and the second oil outlet hole 103b being damaged, and extends the service life of the pin 100 and the needle bearing 600.

[0057] In some embodiments, the angle between the axial direction of the first oil outlet hole 103 a and the axial direction of the second oil outlet hole 103 b is 0° to 10°.

[0058] The difference in magnitude between the two components of the resultant force acting on needle roller bearing 600 is typically small, resulting in the direction of the resultant force being close to the tangent to the motion trajectory of pin 100. Correspondingly, when needle roller bearing 600 is a double-row needle roller bearing, the resultant force acting on the two rows of needle rollers 610 of the double-row needle roller bearing is located on either side of the tangent to the motion trajectory of pin 100. The angle between the resultant forces acting on the two rows of needle rollers 610 of the double-row needle roller bearing is typically small, and can range from 0° to 10°. That is, the angle between the axial direction of first oil outlet hole 103a and the axial direction of second oil outlet hole 103b is 0° to 10°.

[0059] In some embodiments, as shown in FIG2 , the oil chamber 101 is L-shaped and includes a connected radial section 101a and an axial section 101b. The opening of the radial section 101a is located on the outer peripheral surface of the pin shaft 100 to form an oil inlet hole 102. The oil outlet hole 103 is connected to the axial section 101b at one end of the radial section 101a, and a plug 110 is provided at the other end of the axial section 101b.

[0060] When designing the oil inlet hole 102, oil chamber 101, and oil outlet hole 103 of the pin 100, the oil chamber 101 of the pin 100 is configured in an L-shape. This L-shaped oil chamber 101 comprises a radial section 101a and an axial section 101b that communicate with each other. The axial section 101b is coaxial with the pin 100 to ensure the structural stability of the pin 100 and the machining accuracy of the oil chamber 101. The radial section 101a is arranged radially along the pin 100 and communicates with the axial section 101b. The opening of the radial section 101a is located on the outer circumference of the pin 100, serving as the oil inlet hole 102. Lubricating oil, through the oil inlet hole 102, then enters the radial section 101a and the axial section 101b in sequence.

[0061] To facilitate machining of the axial section 101b of the oil chamber 101, a slot is axially cut at one end of the pin 100. After the slotting is completed, the slot is sealed with a plug 110 to form the axial section 101b of the oil chamber 101. An oil inlet hole 102 (radial section 101a) and an oil outlet hole 103 communicating with the axial section 101b are then formed on the pin 100, completing the specific arrangement of the oil inlet hole 102, the oil chamber 101, and the oil outlet hole 103 of the pin 100.

[0062] In some embodiments, as shown in FIG. 2 , the pin shaft 100 has a threaded hole 104 ; the planetary gear mechanism 10 further includes a planet carrier 500 , which is connected to the threaded hole 104 via a threaded pin 700 .

[0063] The main structure of the planetary gear mechanism 10 includes a pin 100, a planetary gear 200, a sun gear 300, a ring gear 400 and a planet carrier 500. The planet carrier 500 is used to install the pin 100. The pin 100 is positioned on the planet carrier 500 so that when the pin 100 and the planetary gear 200 revolve synchronously around the sun gear 300, the pin 100 drives the planet carrier 500 to rotate, or the planet carrier 500 rotates to drive the pin 100 and the planetary gear 200 to revolve synchronously around the sun gear 300.

[0064] It should be noted that the acting force between the pin 100 and the needle bearing 600, as well as the force difference at both ends of the pin 100, are mainly formed by the interaction between the pin 100, the planetary gear 200, the sun gear 300, the ring gear 400 and the planetary carrier 500.

[0065] Since the axial direction of the oil outlet hole 103 of the pin 100 and the direction of the resultant force acting on the needle roller bearing 600 need to be arranged to avoid each other, the pin 100 needs to be fixed to the planetary carrier 500 to prevent the pin 100 from rotating relative to the planetary carrier 500. Therefore, a threaded hole 104 is provided on the pin 100, and a through hole 501 corresponding to the threaded hole 104 of the pin 100 is provided on the planetary carrier 500. By inserting a threaded pin 700 into the through hole 501 of the planetary carrier 500, the threaded pin 700 is threadedly connected to the threaded hole 104 of the pin 100, thereby positioning the pin 100 on the planetary carrier 500, preventing the pin 100 from rotating relative to the planetary carrier 500, and ensuring that the axial direction of the oil outlet hole 103 of the pin 100 and the direction of the resultant force acting on the needle roller bearing 600 are arranged to avoid each other.

[0066] In some embodiments, as shown in Figures 2 and 5, the pin 100 has a positioning structure 120 at one end close to the planetary carrier 500; the positioning structure 120 includes a positioning groove 121 provided in the middle of the end face of the pin 100 and / or a positioning hole 122 provided on one side of the end face of the pin 100.

[0067] Since the pin 100 is inserted into the interior of the planet carrier 500, when the pin 100 is installed on the planet carrier 500, the threaded hole 104 on the pin 100 for positioning and installation is located inside the planet carrier 500. If the pin 100 does not have a positioning structure 120, it will take multiple rotation attempts to align the threaded hole 104 of the pin 100 with the through hole 501 of the planet carrier 500 for inserting the threaded pin 700, which reduces installation efficiency. Therefore, a positioning structure 120 is provided at the end of the pin 100 close to the planet carrier 500. The positioning structure 120 can quickly align the threaded hole 104 of the pin 100 with the through hole 501 of the planet carrier 500, thereby improving installation efficiency.

[0068] The positioning structure 120 is typically configured as a positioning groove 121 provided in the middle of the end surface of the pin 100, a positioning hole 122 provided on one side of the end surface of the pin 100, or a combination of the positioning groove 121 in the middle of the end surface of the pin 100 and the positioning hole 122 provided on one side of the end surface of the pin 100. The threaded hole 104 of the pin 100 is positioned by the positioning groove 121 and / or the positioning hole 122, so that the threaded hole 104 of the pin 100 is quickly aligned with the through hole 501 of the planet carrier 500, thereby improving installation efficiency.

[0069] Furthermore, since the pin 100 is disposed inside the planet carrier 500, if the end surface of the pin 100 near the planet carrier 500 does not have the positioning structure 120, it is difficult to rotate the pin 100 so that the threaded hole 104 of the pin 100 is aligned with the through hole 501 of the planet carrier 500. Therefore, if the positioning groove 121 and / or the positioning hole 122 are provided, the pin 100 can be rotated by operating the positioning groove 121 or the positioning hole 122 to align the threaded hole 104 of the pin 100 with the through hole 501 of the planet carrier 500.

[0070] In some embodiments, as shown in FIG. 2 , the threaded hole 104 and the oil inlet hole 102 are both provided on the circumferential surface of one end of the pin 100 close to the planet carrier 500 , and the threaded hole 104 and the oil inlet hole 102 are provided opposite to each other.

[0071] In order to facilitate the fixing of the pin shaft 100 and the injection of lubricating oil into the pin shaft 100, on the planetary carrier 500, the through hole 501 of the planetary carrier 500 for passing the threaded pin 700 is set on the outside of the planetary carrier 500, and the oil passage 502 of the planetary carrier 500 for injecting lubricating oil into the pin shaft 100 is set inside the planetary carrier 500, and multiple pin shafts 100 are arranged in the circumferential direction of the planetary carrier 500, so that each through hole 501 and oil passage 502 of the planetary carrier 500 corresponding to the pin shaft 100 are arranged along the radial direction of the planetary carrier 500. Based on this, the threaded hole 104 and the oil inlet hole 102 of the pin shaft 100 are both arranged on the circumferential surface of one end of the pin shaft 100 close to the planetary carrier 500, and the threaded hole 104 and the oil inlet hole 102 are arranged opposite to each other, so that the threaded hole 104 of the pin shaft 100 and the through hole 501 of the planetary carrier 500 and the oil inlet hole 102 of the pin shaft 100 and the oil path 502 of the planetary carrier 500 are respectively arranged correspondingly.

[0072] A second embodiment of the present application provides a transmission including the aforementioned planetary gear mechanism 10. The structural features and arrangement of the pin 100 of the planetary gear mechanism 10 enhance the transmission's performance. Because the transmission is equipped with the aforementioned planetary gear mechanism 10, it exhibits at least all the beneficial effects of the aforementioned planetary gear mechanism 10. Other undescribed features of the planetary gear mechanism 10 can be referenced to relevant prior art disclosures and are not further described here.

[0073] A third embodiment of the present application provides a vehicle including the aforementioned transmission. Because the vehicle is equipped with the aforementioned transmission, it possesses at least all the beneficial effects provided by the aforementioned transmission's technical solution. Other undescribed structures of the vehicle can be referenced to relevant disclosures in the prior art and are not further described here.

[0074] In this application, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Moreover, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly below or obliquely below the second feature, or may simply mean that the first feature is lower in level than the second feature.

[0075] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise" and "counterclockwise" indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0076] In this application, unless otherwise specified or limited, the terms "connect," "fix," etc. should be understood broadly. For example, "fix" can mean fixed connection, detachable connection, or integration; it can mean mechanical connection or electrical connection; it can mean direct connection or indirect connection through an intermediate medium; it can mean internal communication between two elements or interaction between two elements. Those skilled in the art will understand the specific meanings of the above terms in this application based on specific circumstances.

[0077] In addition, the terms "first," "second," and so on, used in this application are for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, features specified as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "plurality" means two or more, unless otherwise specifically defined.

[0078] Although the embodiments of the present application have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and intent of the present application, and that the scope of the present application is defined by the claims and their equivalents.

Claims

1. A planetary gear mechanism, comprising a plurality of pins, planetary gears mounted on the pins, and a sun gear meshing with the planetary gears, characterized in that: The pin shaft has an oil cavity and an oil inlet hole and an oil outlet hole communicated with the oil cavity, and the oil outlet hole is located on the outer peripheral surface of the pin shaft; A needle bearing is arranged between the pin shaft and the planetary gear, and an angle is formed between the axial direction of the oil outlet hole and the direction of the resultant force acting on the needle bearing.

2. The planetary gear mechanism according to claim 1, characterized in that: The angle between the axial direction of the oil outlet hole and the direction of the resultant force on the needle bearing is 180°±60°.

3. The planetary gear mechanism according to claim 2, characterized in that: The angle between the axis connecting the pin shaft and the sun gear and the axial direction of the oil outlet hole is 25° to 155°.

4. The planetary gear mechanism according to any one of claims 1 to 3, characterized in that: The needle roller bearing is a double-row needle roller bearing; the oil outlet hole comprises a first oil outlet hole and a second oil outlet hole, and the first oil outlet hole and the second oil outlet hole are respectively arranged corresponding to the two rows of needle rollers of the double-row needle roller bearing.

5. The planetary gear mechanism according to claim 4, characterized in that: An axial direction of the first oil outlet hole and an axial direction of the second oil outlet hole form an included angle.

6. The planetary gear mechanism according to claim 5, characterized in that: The included angle between the axial direction of the first oil outlet hole and the axial direction of the second oil outlet hole is 0° to 10°.

7. The planetary gear mechanism according to any one of claims 1 to 3, characterized in that: The oil chamber is L-shaped, and includes a radial section and an axial section that are connected, and the opening of the radial section is located on the outer peripheral surface of the pin shaft to form the oil inlet hole; The oil outlet hole is communicated with one end of the axial section that is connected to the radial section, and a plug is provided at the other end of the axial section.

8. The planetary gear mechanism according to any one of claims 1 to 3, characterized in that: The pin shaft has a threaded hole; The planetary gear mechanism further comprises a planet carrier, and the planet carrier is connected to the threaded hole via a threaded pin.

9. The planetary gear mechanism according to claim 8, characterized in that: One end of the pin shaft close to the planet carrier has a positioning structure; The positioning structure includes a positioning groove arranged in the middle of the end surface of the pin shaft and / or a positioning hole arranged on one side of the end surface of the pin shaft.

10. The planetary gear mechanism according to claim 8, characterized in that: The threaded hole and the oil inlet hole are both arranged on the circumferential surface of one end of the pin shaft close to the planetary carrier, and the threaded hole and the oil inlet hole are arranged opposite to each other.

11. A gearbox, characterized in that: The invention comprises the planetary gear mechanism according to any one of claims 1 to 10.

12. A vehicle, characterized in that: Including the gearbox as claimed in claim 11.

Images