Gearbox

Abstract

The invention relates to a gear box which comprises a planet carrier, a gear shaft and a gear shaft, the planet carrier comprises an axial end face and a shoulder part, and the shoulder part protrudes out of the axial end face of the planet carrier in the axial direction and is located on the radial outer side of the axial end face; the dynamic pressure sliding thrust bearing is installed on the radial inner side of the shoulder of the planet carrier, and the dynamic pressure sliding thrust bearing is connected with the shoulder of the planet carrier in an anti-torque mode and used for being connected with the planet carrier in an anti-torque mode. The dynamic pressure sliding thrust bearing and the planet carrier can be mounted and dismounted in the radial direction through the shoulder portion of the planet carrier, the machining cost is reduced, meanwhile, axial movement and circumferential rotation of the dynamic pressure sliding thrust bearing can be limited, the axial bearing capacity of the dynamic pressure sliding thrust bearing can be improved, and the service life of the dynamic pressure sliding thrust bearing is prolonged. And the pin or the bolt is prevented from jumping out from the dynamic pressure sliding thrust bearing force to the side far away from the planet carrier under the action of the axial load, so that the risk that the positioning pin or the bolt axially falls off under the condition of long-time operation under different working conditions is reduced, and the maintenance cost is reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of wind power generation, and in particular to a gear box used in a wind power generator. Background Art

[0002] With the development of offshore wind power, large megawatt wind turbines are the future development trend. At the same time, the reduction of electricity cost has put more stringent requirements on the cost and operation reliability of wind turbine gearboxes. Bearings are key components in gearboxes. If the bearings fail, the gearbox of the wind turbine will fail, which will lead to a lot of maintenance time and cost waste.

[0003] In order to prevent the bearing failure in the gearbox, it is necessary to prevent the thrust bearing from moving axially and radially relative to the gearbox. The solution in the related art is to design a number of countersunk holes on the functional surface of the thrust bearing along the axial direction, and connect the thrust bearing to the gearbox with bolts or pins. However, if the thrust bearing is axially connected to the gearbox with bolts, there is a risk that the bolts or pins will fall off when running for a long time under different working conditions, which will cause the thrust bearing's load-bearing capacity to decrease or even fail. Summary of the invention

[0004] In order to overcome the problems existing in the related art, the present disclosure provides a gearbox for a wind turbine.

[0005] According to a first aspect of an embodiment of the present disclosure, the present disclosure provides a gearbox, comprising: a planetary carrier, comprising an axial end face and a shoulder, the shoulder protruding axially from the axial end face of the planetary carrier and located radially outside the axial end face; a dynamic pressure sliding thrust bearing, located radially inside the shoulder of the planetary carrier, wherein the dynamic pressure sliding thrust bearing is torsionally connected to the shoulder of the planetary carrier for torsionally connecting to the planetary carrier.

[0006] In some embodiments, the hydrodynamic sliding thrust bearing includes, in the axial direction: a first axial end face, the first axial end face being opposite to the axial end face of the planet carrier; and a second axial end face, the second axial end face protruding axially from the axial end face of the shoulder.

[0007] In some embodiments, the shoulder of the planet carrier is provided with a plurality of radial through holes correspondingly in the radial direction, and the outer peripheral surface of the hydrodynamic sliding thrust bearing is provided with a plurality of radial blind holes, wherein fasteners pass through the radial through holes from the outer peripheral surface of the shoulder of the planet carrier and are inserted into the radial blind holes, so that the hydrodynamic sliding thrust bearing is torsionally connected to the shoulder of the planet carrier.

[0008] In some embodiments, the inner circumferential surface of the shoulder of the planet carrier and the outer circumferential surface of the hydrodynamic sliding thrust bearing are both cylindrical surfaces and are clearance-fitted.

[0009] In some embodiments, the inner circumferential surface of the shoulder of the planet carrier and the outer circumferential surface of the dynamic pressure sliding thrust bearing are both conical surfaces and are interference fit.

[0010] In some embodiments, the first axial end surface of the hydrodynamic sliding thrust bearing is axially spaced from the axial end surface of the planet carrier to form a gap.

[0011] In some embodiments, the hydrodynamic sliding thrust bearing is provided with an axial through hole along the axial direction; the hydrodynamic sliding thrust bearing also includes a disassembly pin, wherein the disassembly pin is inserted into the axial through hole from the second axial end face of the hydrodynamic sliding thrust bearing, so as to separate the hydrodynamic sliding thrust bearing from the planetary carrier.

[0012] In some embodiments, a step is formed on the radial outer side of the second axial end face of the hydrodynamic sliding thrust bearing, a plurality of axially extending protrusions are provided on the outer circumferential surface of the step, a plurality of axial grooves corresponding to the protrusions are provided on the inner circumferential surface of the shoulder of the planetary carrier, and the protrusions are installed in the axial grooves.

[0013] In some embodiments, the inner circumferential surface of the shoulder of the planet carrier is further provided with a circumferential groove, and the dynamic pressure sliding thrust bearing further includes a retaining spring, which is inserted into the circumferential groove and abuts against the step surface of the step.

[0014] In some embodiments, the outer circumferential surface of the step and the inner circumferential surface of the shoulder are cylindrical surfaces or conical surfaces.

[0015] The technical solution provided by the embodiments of the present disclosure may include the following beneficial effects: the hydrodynamic sliding thrust bearing can be installed and disassembled with the planetary carrier in the radial direction through the shoulder of the planetary carrier, which can not only limit the axial movement and circumferential rotation of the hydrodynamic sliding thrust bearing while reducing the processing cost, but also increase the axial load-bearing capacity of the hydrodynamic sliding thrust bearing, and prevent pins or bolts from escaping from the hydrodynamic sliding thrust bearing to the side away from the planetary carrier under the action of the axial load, thereby reducing the risk of axial separation of the positioning pins or bolts when running for a long time under different working conditions, and reducing maintenance costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and, together with the description, serve to explain the principles of the present disclosure.

[0017] Figure 1 is a cross-sectional view showing an assembly of a dynamic pressure sliding thrust bearing and a planet carrier according to a first exemplary embodiment;

[0018] Figure 2 is a cross-sectional view showing an assembly of a dynamic pressure sliding thrust bearing and a planet carrier according to a second exemplary embodiment;

[0019] Figure 3 is a cylindrical cross-sectional view of a hydrodynamic sliding thrust bearing and a planet carrier assembled according to a third exemplary embodiment;

[0020] Figure 4 is a conical cross-sectional view of a dynamic pressure sliding thrust bearing and a planet carrier assembled according to a third exemplary embodiment;

[0021] Figure 5 yes Figure 4 A three-dimensional diagram of a hydrodynamic sliding thrust bearing. DETAILED DESCRIPTION

[0022] Exemplary embodiments will be described in detail herein, examples of which are shown in the accompanying drawings. When the following description refers to the drawings, the same numbers in different drawings represent the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present disclosure. Instead, they are merely examples of devices and methods consistent with some aspects of the present disclosure as detailed in the appended claims.

[0023] In the present invention, unless otherwise specified, the axial direction, radial direction and circumferential direction refer to the axial direction, radial direction and circumferential direction of the hydrodynamic sliding thrust bearing, respectively; the radial outer side refers to the direction away from the outer side in the radial direction. Figure 1 The side of the central axis O in ( Figures 1 to 4 The radial inner side refers to the side closer to the central axis O in the radial direction ( Figures 1 to 4 The term "torsionally resistant connection" refers to a connection between two components that does not rotate relative to each other, which can be achieved by press fit (i.e., interference fit) or by forming the two components as one piece. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood according to the specific circumstances.

[0024] To solve the above technical problems, the present disclosure provides a gearbox 100 , which can be applied to a wind turbine in the field of wind power generation. The gearbox 100 may include a planet carrier 10 , a planetary gear shaft, a planetary gear, a hydrodynamic sliding radial bearing, and a hydrodynamic sliding thrust bearing 20 .

[0025] The planet carrier 10 includes an axial end surface, wherein the planet carrier 10 includes two fixing parts, which are respectively sleeved on the axial ends of the planet gear shaft to ensure a torsion-proof connection between the planet gear shaft and the planet carrier 10. The planet carrier 10 can be integral or split.

[0026] The fixed portion radially protrudes from the planetary gear shaft to form two axially opposite axial end faces 11 . The planetary gear, the dynamic pressure sliding radial bearing and the dynamic pressure sliding thrust bearing 20 are all sleeved on the planetary gear shaft and are located between the two axial end faces 11 along the axial direction A.

[0027] The hydrodynamic sliding radial bearing is arranged between the planetary gear shaft and the planetary gear in the radial direction R to support the planetary gear on the planetary gear shaft so that the planetary gear can rotate relatively. The hydrodynamic sliding thrust bearing 20 is arranged between the axial end face 11 of the planetary gear and the axial end face 11 of the fixed part of the planetary carrier 10 in the axial direction. A hydrodynamic sliding thrust bearing 20 is respectively arranged at both axial ends of the planetary gear, and the two hydrodynamic sliding thrust bearings 20 have the same structure. The hydrodynamic sliding thrust bearing 20 can be made of copper or copper alloy.

[0028] The dynamic pressure sliding radial bearing and the dynamic pressure sliding thrust bearing 20 respectively form a dynamic pressure oil film with the inner peripheral surface and the axial end surface 11 of the planetary gear, and the dynamic pressure oil film can withstand the radial and axial loads acting on the planetary gear.

[0029] Furthermore, the axial end surface 11 of the planet carrier 10 includes a shoulder 12. Figures 1 to 4 As shown, the shoulder 12 protrudes from the axial end face 11 of the planet carrier 10 along the axial direction A and is located radially outside the axial end face 11 of the planet carrier 10; the hydrodynamic sliding thrust bearing 20 is located radially inside R of the shoulder 12 of the planet carrier 10. Specifically, the shoulder 12 and the axial end face 11 of the planet carrier 10 form an annular receiving groove, and the hydrodynamic sliding thrust bearing 20 is installed in the receiving groove.

[0030] The hydrodynamic sliding thrust bearing 20 is torsionally connected to the shoulder 12 of the planetary carrier 10, and is used for torsionally connecting to the planetary carrier 10. Specifically, in the axial direction A, the hydrodynamic sliding thrust bearing 20 is not connected to the axial end face 11 of the planetary carrier 10, and in the radial direction R, the outer peripheral surface of the hydrodynamic sliding thrust bearing 20 is torsionally connected to the inner peripheral surface of the shoulder 12, thereby limiting the axial movement and circumferential rotation of the hydrodynamic sliding thrust bearing 20 relative to the planetary carrier 10, and realizing the torsionally connecting between the hydrodynamic sliding thrust bearing 20 and the planetary carrier 10.

[0031] The hydrodynamic sliding thrust bearing 20 can be installed and disassembled with the planetary carrier 10 in the radial direction R through the shoulder 12 of the planetary carrier 10. Compared with the prior art in which the hydrodynamic sliding thrust bearing 20 is fixedly connected with the planetary carrier 10 in the axial direction A, the radial connection disclosed in the present invention simplifies the processing method of the planetary carrier 10 and the hydrodynamic sliding thrust bearing 20, can reduce the processing cost, and is also convenient for installation and disassembly.

[0032] In addition, the radial torsion-resistant connection can not only limit the axial movement and circumferential rotation of the hydrodynamic sliding thrust bearing 20, but also the hydrodynamic sliding thrust bearing 20 does not need to open and install a number of blind holes on the axial end face 11 to install locating pins or bolts. Therefore, the strength and axial load-bearing capacity of the hydrodynamic sliding thrust bearing 20 can be increased, and the pins or bolts can be prevented from escaping from the hydrodynamic sliding thrust bearing 20 to the side away from the planetary carrier 10 under the action of the axial load. When running for a long time under different working conditions, the risk of the locating pins or bolts falling off in the axial direction A is reduced, thereby reducing maintenance costs.

[0033] In some embodiments, Figures 1 to 4 As shown, the hydrodynamic sliding thrust bearing 20 includes a first axial end face 21 and a second axial end face 22 along the axial direction A. The first axial end face 21 is opposite to the axial end face 11 of the planetary carrier 10; the second axial end face 22 protrudes from the axial end face 121 of the shoulder 12 along the axial direction A.

[0034] The second axial end face 22 protrudes from the axial end face 121 of the shoulder 12, and the lubricating medium between the second axial end face 22 and the axial end face 11 of the planetary gear forms a dynamic pressure oil film, thereby avoiding wear on the axial end face 11 of the planetary gear due to the unevenness of the second axial end face 22 and the axial end face 121 of the shoulder 12, and affecting the formation of the dynamic pressure oil film.

[0035] In addition, the second axial end face 22 protrudes from the axial end face 121 of the shoulder 12, which can also reduce the tolerance requirements when designing the hydrodynamic sliding thrust bearing 20 and the shoulder 12, simplifying the design, production and installation.

[0036] The first embodiment, the second embodiment and the third embodiment of the present disclosure will be specifically listed below, wherein the first embodiment, the second embodiment and the third embodiment can be implemented individually, and the first embodiment can also be used in combination with the second embodiment or the third embodiment to achieve a torsion-resistant connection between the hydrodynamic sliding thrust bearing 20 and the planetary carrier 10 in the radial direction R.

[0037] First embodiment

[0038] like Figure 1 As shown, the shoulder 12 of the planetary carrier 10 is correspondingly provided with a plurality of radial through holes 122 along the radial direction R, and the outer peripheral surface of the hydrodynamic sliding thrust bearing 20 is provided with a plurality of radial blind holes 23 (also called countersunk holes), wherein the fastener 30 passes through the radial through holes 122 from the outer peripheral surface of the shoulder 12 of the planetary carrier 10 and is inserted into the radial blind holes 23, so that the hydrodynamic sliding thrust bearing 20 is torsionally connected to the shoulder 12 of the planetary carrier 10.

[0039] Machining the radial through hole 122 on the shoulder 12 and machining the radial blind hole 23 on the outer peripheral surface of the hydrodynamic sliding thrust bearing 20 is more convenient and simpler than machining the blind hole on the axial end face 11 of the planetary carrier 10 and on the first axial end face 21 of the hydrodynamic sliding thrust bearing 20, thereby reducing the machining cost.

[0040] One end of the fastener 30 is located in the blind hole of the hydrodynamic sliding thrust bearing 20, and the other end is located in the radial through hole 122 of the shoulder 12, so that the circumferential rotation of the hydrodynamic sliding thrust bearing 20 relative to the planet carrier 10 can be limited in the circumferential direction W. At the same time, the fastener 30 and the axial end surface 11 of the planet carrier 10 can simultaneously limit the axial movement of the hydrodynamic sliding bearing.

[0041] In addition, the fastener 30 is arranged radially, which can avoid the risk of the fastener 30 falling off in the axial direction A under the action of the axial load when running for a long time under different working conditions, thereby reducing maintenance costs.

[0042] The number and position of the radial through holes 122 on the shoulder 12 correspond to the number and position of the radial blind holes 23 of the hydrodynamic sliding thrust bearing 20, and the radial through holes 122 and the radial blind holes 23 may be arranged at equal intervals along the circumferential direction W. The fasteners 30 may be pins or bolts, and the number of the fasteners 30 may be selected according to the corresponding working conditions, which is not specifically limited herein.

[0043] Furthermore, the inner circumference of the shoulder 12 of the planet carrier 10 and the outer circumference of the dynamic pressure sliding thrust bearing 20 are both cylindrical surfaces and have clearance fit. The planet carrier 10 and the dynamic pressure sliding thrust bearing 20 have clearance fit, which facilitates the installation, removal and replacement of the dynamic pressure sliding thrust bearing 20, thereby reducing maintenance costs.

[0044] Second embodiment

[0045] like Figure 2 As shown, the inner circumference of the shoulder 12 of the planet carrier 10 and the outer circumference of the dynamic pressure sliding thrust bearing 20 are both tapered and interference fit. The dynamic pressure sliding thrust bearing 20 and the planet carrier 10 are matched through the tapered surface, which makes it easier to make the dynamic pressure sliding thrust bearing 20 interference press into the planet carrier 10, making the installation and disassembly between the two more convenient.

[0046] The interference fit between the hydrodynamic sliding thrust bearing 20 and the planetary carrier 10 needs to be large enough so that the hydrodynamic sliding thrust bearing 20 can be torsionally connected to the planetary carrier 10 to prevent the hydrodynamic sliding thrust bearing 20 from axial movement A and circumferential rotation W.

[0047] The hydrodynamic sliding thrust bearing 20 can be connected to the shoulder 12 of the planetary carrier 10 through a mechanical structure design. There is no need to design a plurality of blind holes on the first axial end face 21 of the hydrodynamic sliding thrust bearing 20 to install the fasteners 30. This reduces the processing cost while also increasing the axial A load-bearing capacity of the hydrodynamic sliding thrust bearing 20 and reducing the risk of axial load on the hydrodynamic sliding thrust bearing 20.

[0048] In some embodiments, the first axial end face 21 of the hydrodynamic sliding thrust bearing 20 is axially spaced from the axial end face 11 of the planet carrier 10 to form a gap. When the hydrodynamic sliding thrust bearing 20 is installed in the shoulder 12 of the planet carrier 10, the gap can ensure that an interference fit is generated between the hydrodynamic sliding thrust bearing 20 and the shoulder 12 of the planet carrier 10, so that the hydrodynamic sliding thrust bearing 20 can be torsionally connected to the planet carrier 10, so as to prevent the axial A movement and circumferential rotation of the hydrodynamic sliding thrust bearing 20.

[0049] In addition, the gap can also make the second axial end face 22 protrude from the axial end face 121 of the shoulder 12, so that the second axial end face 22 and the axial end face 11 of the planetary gear can better form a dynamic pressure oil film. In addition, the gap can also prevent the first axial end face 21 of the dynamic pressure sliding thrust bearing 20 from completely fitting with the axial end face 11 of the planetary carrier 10, which is more conducive to the disassembly of the dynamic pressure sliding thrust bearing 20.

[0050] Furthermore, the hydrodynamic sliding thrust bearing 20 is provided with an axial through hole along the axial direction A; the hydrodynamic sliding thrust bearing 20 also includes a disassembly pin (not shown in the figure), wherein the disassembly pin is inserted into the axial through hole from the second axial end face 22 of the hydrodynamic sliding thrust bearing 20, and is used to more advantageously separate the hydrodynamic sliding thrust bearing 20 from the planetary carrier 10, thereby facilitating rapid replacement of the hydrodynamic sliding thrust bearing 20 and reducing replacement and maintenance costs.

[0051] Third embodiment

[0052] like Figures 3 to 5 As shown, a step 24 is formed radially outwardly of the second axial end face 22 of the hydrodynamic sliding thrust bearing 20 , and the step 24 includes a step surface 242 , which is annular and located radially outwardly of the second axial end face 22 , and the outer peripheral surface of the step 24 is torsionally connected to the shoulder 12 of the planetary carrier 10 .

[0053] Furthermore, a plurality of protrusions 241 extending in the axial direction A are provided on the outer circumferential surface of the step 24, and a plurality of axial grooves corresponding to the protrusions 241 are provided on the inner circumferential surface of the shoulder 12 of the planetary carrier 10. When the hydrodynamic sliding thrust bearing 20 is assembled with the planetary carrier 10, the protrusions 241 of the step 24 are aligned with the axial direction of the planetary carrier 10 and installed in the axial grooves. The axial grooves limit the circumferential movement of the protrusions 241, thereby enabling the shoulder 12 of the planetary carrier 10 to limit the circumferential rotation of the hydrodynamic sliding thrust bearing 20.

[0054] Among them, the number and position of the protrusions 241 on the outer peripheral surface of the step 24 of the hydrodynamic sliding thrust bearing 20 correspond to the number and position of the axial grooves of the planetary carrier 10, and the protrusions 241 and the axial grooves are arranged at equal intervals along the circumferential direction, so that the hydrodynamic sliding thrust bearing 20 is balanced in the circumferential force.

[0055] Furthermore, a circumferential groove is further provided on the inner circumferential surface of the shoulder 12 of the planet carrier 10 , and the dynamic pressure sliding thrust bearing 20 further includes a retaining spring 25 , which is inserted into the circumferential groove and abuts against the step surface 242 of the step 24 .

[0056] Among them, the axial distance between the circumferential groove and the axial end face 11 of the planetary carrier 10 is greater than the axial thickness of the step 24 of the dynamic pressure sliding thrust bearing 20. Therefore, when the step 24 of the dynamic pressure sliding thrust bearing 20 is installed into the position of the shoulder 12 of the planetary carrier 10, and after the retaining spring 25 is inserted into the circumferential groove, the retaining spring 25 abuts against the step surface 242 of the step 24. The retaining spring 25 and the axial end face 11 of the planetary carrier 10 jointly define the axial position of the dynamic pressure sliding thrust bearing 20, thereby preventing the axial movement of the dynamic pressure sliding thrust bearing 20.

[0057] In the third embodiment, the outer circumferential surface of the step 24 and the inner circumferential surface of the shoulder 12 are cylindrical surfaces or conical surfaces.

[0058] The protrusion 241 of the hydrodynamic sliding thrust bearing 20 cooperates with the axial groove of the shoulder 12 to limit the circumferential rotation of the hydrodynamic sliding thrust bearing 20, and the circumferential groove of the shoulder 12 of the planetary carrier 10 is used to limit the axial movement of the hydrodynamic sliding thrust bearing 20. Therefore, in the third embodiment, the connection can also be made through mechanical structure design, and there is no need to design a plurality of blind holes on the first axial end face 21 of the hydrodynamic sliding thrust bearing 20 to install the fasteners 30. This reduces the processing cost while also increasing the axial load-bearing capacity of the hydrodynamic sliding thrust bearing 20 and reducing the risk of axial load on the hydrodynamic sliding thrust bearing 20.

[0059] It is understood that in the present disclosure, "plurality" refers to two or more than two, and other quantifiers are similar thereto. It is further understood that the terms "first", "second", etc. are used to describe various structures, but these structures should not be limited to these terms. These terms are only used to distinguish structures of the same type from each other and do not indicate a specific order or degree of importance. In fact, expressions such as "first", "second", etc. can be used interchangeably. For example, without departing from the scope of the present disclosure, the first structure may also be referred to as the second structure, and similarly, the second structure may also be referred to as the first structure.

[0060] It should be further understood that the orientation or positional relationship indicated by the terms "center", "inside", "outside", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present embodiment and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation.

[0061] It is further understood that, although the operations are described in a specific order in the drawings in the embodiments of the present disclosure, it should not be understood as requiring the operations to be performed in the specific order shown or in a serial order, or requiring the execution of all the operations shown to obtain the desired results. In certain environments, multitasking and parallel processing may be advantageous.

[0062] Those skilled in the art will readily appreciate other embodiments of the present disclosure after considering the specification and practicing the invention disclosed herein. This application is intended to cover any modification, use or adaptation of the present disclosure, which follows the general principles of the present disclosure and includes common knowledge or customary techniques in the art that are not disclosed in the present disclosure. The specification and examples are intended to be exemplary only, and the true scope and spirit of the present disclosure are indicated by the following scope of rights.

[0063] It should be understood that the present disclosure is not limited to the precise structures that have been described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the scope of the appended claims.

Claims

1. A gearbox (100), characterized in that: include: A planet carrier (10) comprising an axial end face (11) and a shoulder (12), wherein the shoulder (12) protrudes from the axial end face (11) of the planet carrier (10) along the axial direction (A) and is located radially outside the axial end face (11); A dynamic pressure sliding thrust bearing (20) is mounted on the radial inner side of the shoulder (12) of the planet carrier (10). The dynamic pressure sliding thrust bearing (20) is connected to the shoulder (12) of the planet carrier (10) in a torsion-resistant manner, and is used for being connected to the planet carrier (10) in a torsion-resistant manner.

2. The gearbox (100) according to claim 1, characterized in that: The dynamic pressure sliding thrust bearing (20) comprises, along the axial direction: a first axial end surface (21), the first axial end surface (21) being opposite to the axial end surface (11) of the planet carrier (10); and A second axial end surface (22), wherein the second axial end surface (22) protrudes axially from the axial end surface (121) of the shoulder (12).

3. The gearbox (100) according to claim 2, characterized in that: The shoulder (12) of the planet carrier (10) is provided with a plurality of radial through holes (122) correspondingly along the radial direction (R). The outer peripheral surface of the dynamic pressure sliding thrust bearing (20) is provided with a plurality of radial blind holes (23). The fastener (30) passes through the radial through hole (122) from the outer peripheral surface of the shoulder (12) of the planet carrier (10) and is inserted into the radial blind hole (23), so that the dynamic pressure sliding thrust bearing (20) is torsionally connected to the shoulder (12) of the planet carrier (10).

4. The gearbox (100) according to claim 3, characterized in that: The inner circumferential surface of the shoulder (12) of the planet carrier (10) and the outer circumferential surface of the dynamic pressure sliding thrust bearing (20) are both cylindrical surfaces and are clearance-matched.

5. The gearbox (100) according to claim 2, characterized in that: The inner circumferential surface of the shoulder (12) of the planet carrier (10) and the outer circumferential surface of the dynamic pressure sliding thrust bearing (20) are both conical surfaces and are interference fit.

6. The gearbox (100) according to claim 5, characterized in that: The first axial end surface (21) of the dynamic pressure sliding thrust bearing (20) is spaced apart from the axial end surface (11) of the planet carrier (10) in the axial direction to form a gap.

7. The gearbox (100) according to claim 5, characterized in that: The dynamic pressure sliding thrust bearing (20) is provided with an axial through hole along the axial direction; The dynamic pressure sliding thrust bearing (20) further comprises a disassembly pin, The disassembly pin is inserted into the axial through hole from the second axial end face (22) of the dynamic pressure sliding thrust bearing (20) to separate the dynamic pressure sliding thrust bearing (20) from the planetary carrier (10).

8. The gearbox (100) according to claim 2, characterized in that: A step (24) is formed on the radial outer side of the second axial end face (22) of the dynamic pressure sliding thrust bearing (20), and a plurality of axially extending protrusions (241) are arranged on the outer peripheral surface of the step (24), and a plurality of axial grooves corresponding to the protrusions (241) are arranged on the inner peripheral surface of the shoulder (12) of the planetary carrier (10), and the protrusions (241) are installed in the axial grooves.

9. The gearbox (100) according to claim 8, characterized in that: The inner circumferential surface of the shoulder (12) of the planetary carrier (10) is also provided with a circumferential groove, and the dynamic pressure sliding thrust bearing (20) also includes a retaining spring (25), the retaining spring (25) is inserted into the circumferential groove and abuts against the step surface (242) of the step (24).

10. The gearbox (100) according to claim 8, characterized in that: The outer circumferential surface of the step (24) and the inner circumferential surface of the shoulder (12) are cylindrical surfaces or conical surfaces.

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