WO2024016324A1

WO2024016324A1 - Planetary gearbox and wind power apparatus

Info

Publication number: WO2024016324A1
Application number: PCT/CN2022/107375
Authority: WO
Inventors: 韩慧敏; 马索雷克帕特里克; 陈向科
Original assignee: 舍弗勒技术股份两合公司
Priority date: 2022-07-22
Filing date: 2022-07-22
Publication date: 2024-01-25

Abstract

A planetary gearbox for a wind power apparatus has a planetary shaft (10), a planetary gear (50), and a planetary carrier (60). The planetary shaft (10) is mounted on the planetary carrier (60), and the planetary gear (50) is mounted on the planetary shaft (10), wherein modification areas (101, 102, 501, 502) are provided in the axial contact area between the planetary gear (50) and the planetary shaft (10) and on the inner circumferential surface of the planetary gear (50) and/or on the outer circumferential surface of the planetary shaft (10). The structure of the planetary gearbox can reduce edge stress concentration and extend the service life of the system.

Description

Planetary gearboxes and wind power equipment

Technical field

The invention relates to a planetary gearbox used in the field of wind power. Specifically, it concerns planetary shafts used in planetary gearboxes.

Background technique

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 forward more stringent requirements on the cost and operational reliability of gearboxes. Bearings are key components in gearboxes. This places higher requirements on the size and load-carrying capacity of the bearings. The failure of the rolling bearing leads to the failure of the wind power gearbox, resulting in a lot of waste of repair time and cost.

WO 03/014 567 A1 discloses a wind power generation equipment, including: a machine room with a generator for generating electricity rotatably installed on a machine tower; a wind-driven rotor hub carrying at least two rotor blades The rotor; and the large rolling bearings that carry the rotor. In addition, a large rolling bearing is connected to the generator in the engine room and consists in a known manner of a ring gear with surrounding internal toothing, a plurality of planetary gears supported on a planetary gear carrier, and an intermediate sun gear. The planetary gear transmission is connected by means that the inner bearing ring of the two bearing rings of the large rolling bearing is fixed to the outer cover surface of the ring gear of the planetary gear transmission through a pressure-fit connection. In addition, EP 811 764 A1 also discloses the connection between a large rolling bearing and a planetary gear transmission in such a way that the inner bearing rings of the two bearing rings of the large rolling bearing are pressed against the ring connected to the rotor hub and carrying the planetary gear carrier.

Wind turbines of the prior art have the disadvantage that the large rolling bearings and the downstream planetary gearboxes consist of a large number of individual components and are therefore very cost-intensive to manufacture on the one hand and have a high cost on the other hand. The total weight will cause many disadvantages when it is installed in a computer room with a height below 120m. In addition, the ring gear of the planetary gearbox and the inner bearing ring of the large rolling bearing must have at least an outer diameter or inner diameter of more than 2m, although its dimensions are manufactured very accurately, so that the inner bearing ring and ring gear can be reliably excluded When the pressure fit connection is made between the positive and excessive fits, or the fit that needs to be tightened, it has a negative impact on the function of the journal or on the teeth of the planetary gear transmission. However, due to the presence of clearance, the planetary gears will still remain in operation during operation. Movement, resulting in a large radial load on the planetary shaft, which can easily cause damage to parts. There is also a gap between the planet gear and the planet shaft, and the same technical problem exists.

Contents of the invention

Therefore, the technical problem to be solved by the present invention is to provide a planetary gearbox that can solve the above-mentioned shortcomings in the prior art.

The technical problem is solved by a planetary gearbox for wind power equipment designed according to the present invention. The planetary gearbox has a planetary shaft, a planetary gear and a planetary carrier, wherein the planetary shaft is installed on the planetary carrier, and the planetary gear is installed on the planetary shaft. In the axial contact area of the planetary gear and the planetary shaft, the inside of the planetary gear is A trimming area is provided on the circumferential surface and/or on the outer circumferential surface of the planetary shaft. The modified area refers to an area with a special structure, such as a wedge-shaped structure, which forms an oil film in the contact area between the planetary gear and the planetary shaft. The oil pressure is used to better carry the load from the planetary gear to reduce edge stress concentration and increase System life.

The trimming area may preferably be provided with an oil storage tank, which structure can store lubricating oil to better form an oil film. It is further preferred that the trimming area has a hardened coating or a clad bronze coating, which can increase its wear resistance and reduce maintenance costs. The present invention does not limit the specific structure of the trimming area, as long as an oil film can be formed.

According to a preferred embodiment of the present invention, a circumferential oil groove located in the middle is provided in the axial contact area of the planet gear and the planet shaft, and a first contact area and a second contact area are respectively provided on both axial sides of the circumferential oil groove. , wherein a shaping area is provided in the first contact area and/or the second contact area. The central oil groove provides lubricant evenly to all contact areas. The middle oil groove cuts the functional area into two areas in the axial direction: a first contact area and a second contact area, and a first trimming area and a second trimming area are respectively provided in the contact area. The shaping area can be localized within the contact area or arranged over the entire functional area. It is also preferred that the positions and areas of the first trimming area and the second trimming area are set according to the actual working conditions of the planetary gearbox. In order to adapt to various application conditions, reduce edge stress concentration, and improve the load-bearing capacity of dynamic pressure sliding bearings, the modification area can be symmetrical or asymmetrical, and can be set according to the stress of the planetary shaft in actual working conditions. . For example, when the axial force of the planetary shaft is uniform, the first trimming area and the second trimming area are axially symmetrical about the circumferential oil groove, thereby reducing edge stress concentration and increasing system life.

According to a preferred embodiment of the present invention, an axial bearing member is provided on the planet shaft and at one or both axial ends of the planet gear, and an axial modification area is provided on the end surface of the axial bearing member that contacts the planet gear. Whether the trimming area is specifically located at one or both axial ends of the planetary gear depends on the settings of the wind power equipment and the assembly structure of the gearbox. If the planet gear can move in both axial directions, it is preferable to provide a modification area on the end surface of the axial bearing member that contacts the planet gear; if the planet gear can only move in one direction in the axial direction, then It is only necessary to provide a trimming area on the axial bearing member in the direction of movement. It is further preferred that the axial support is a shoulder of the planetary shaft, or a bearing or a ring. The axial force carrying function used in wind power gearboxes is transferred to the planetary shaft, and the function of the axial dynamic pressure plane bearing is transferred to the shaft shoulder. In addition, it can also be realized through replaceable bearings or annular parts. If a shaft shoulder is used, the planetary shaft can bear both radial load and unidirectional axial load. There is no need for an additional thrust plane bearing on one side, and the number of parts is reduced, which can reduce costs. If bearings or rings are used, the structure is simple and low-cost, which can reduce costs and is easy to replace.

In addition, the technical problem to be solved by the present invention can also be solved by a wind power equipment having a planetary gearbox including the aforementioned technical features.

Description of drawings

The present invention is further described below in conjunction with the accompanying drawings. The same reference numerals are used in the figures to identify identical or functionally identical components. The attached picture is:

Figure 1 shows a cross-sectional view of a planetary gearbox designed according to the invention;

Figure 2a shows a perspective view of a planetary shaft designed according to the first embodiment of the present invention;

Figure 2b shows a perspective view of a planetary shaft designed according to a second embodiment of the present invention;

Figure 2c shows a perspective view of a planetary shaft designed according to a third embodiment of the present invention;

Figure 3 shows a perspective view and a cross-sectional view of a planetary gear designed according to the invention.

Detailed ways

Specific implementations of the planetary gearbox according to the present invention will be described below with reference to the accompanying drawings. The following detailed description and drawings are used to illustrate the principles of the present invention by way of example. The present invention is not limited to the described preferred embodiments, and the protection scope of the present invention is defined by the claims.

Figure 1 shows a cross-sectional view of a planetary gearbox designed according to the present invention, which has a planet shaft 10, an axial thrust dynamic pressure sliding bearing 20, a planet gear 50 and a planet carrier 60. The axial thrust dynamic pressure sliding bearing 20 is fixed on the planet carrier 60 through pins 30 . According to another embodiment, the planet shaft 10 has a shoulder for axially stopping the planet gear 50 , whereby the planet gear 50 is in contact with the shoulder and the axial thrust dynamic pressure sliding bearing 20 at both axial ends of the planet gear 50 . The shoulder and axial thrust dynamic pressure sliding bearing 20 has an axial end surface that is in axial contact with the planet gear 50, and a modification is provided on the axial end surface. The main principle of the trimming zone is to form pressure changes on the contact surface, thereby forming an oil film at the contact position, thereby forming oil pressure to resist axial load.

Figure 2a shows a perspective view of a planetary shaft designed according to a first embodiment of the present invention. A circumferential oil groove 103 is provided in the middle of the functional surface of the planet shaft 10 (that is, the area in axial contact with the planet gear 50), and a first contact area and a second contact area are provided on the left and right sides of the circumferential oil groove 103 in the axial direction. Among them, a first trimming area 101 is provided in the first contact area, and a second trimming area 102 is provided in the second contact area. The trimming

areas

101 and 102 are symmetrical about the circumferential oil groove 103 . This design is suitable for working conditions where the load offset is not very large or there is no load offset.

Figure 2b shows a perspective view of a planetary shaft designed according to a second embodiment of the present invention. The design of this embodiment is roughly the same as that of the first embodiment. The difference is that the first trimming area 101 and the second trimming area 102 are asymmetric, that is, the lengths of the trimming areas in the axial direction of the functional surface are different. This design is suitable for For working conditions with large load offset, the areas and positions of the trimming area 101 and the trimming area 102 are designed according to the specific application conditions. It is also preferred that the first trimming area 101 and the second trimming area 102 are asymmetric in radial size (relative to the middle position of the functional area), that is, the amount of trimming is different in radial size.

Figure 2c shows a perspective view of a planetary shaft designed according to a third embodiment of the present invention. The entire functional surface 104 of the planetary shaft 10 has a profile, and the design of the profile is defined according to the specific application conditions.

Figure 3 shows a perspective view and a cross-sectional view of a planetary gear designed according to the invention. Modifications can also be designed on the planetary gear, as shown in Figure 3. The design principle of modification on planetary gears is similar to that on planetary shafts. A circumferential oil groove 503 in the middle is provided on the inner circumferential surface of the planetary gear. A first contact area and a second contact area are provided on the left and right sides of the circumferential oil groove 503 in the axial direction, wherein there are The first shaping area 501 is provided with a second shaping area 502 in the second contact area. The shaping

areas

501 and 502 can be either symmetrical or asymmetrical with respect to the middle position of the functional area. The trimming area can be set on part of the functional area, or the trimming area can be set on the entire functional surface of the functional area. The trimming design is defined according to the specific application conditions.

Although possible embodiments are exemplarily described in the above description, it should be understood that there are still numerous variations of the embodiments through combinations of all known technical features and embodiments that are otherwise readily apparent to the skilled person. Furthermore, it should be understood that the exemplary embodiment is merely an example, and such embodiment in no way limits the scope, application, and construction of the present invention. The foregoing description is intended to provide skilled persons with technical guidance for transforming at least one exemplary embodiment, in which various changes may be made without departing from the scope of the claims, especially regarding the Changes in the functionality and structure of components.

List of reference signs

10 planetary shaft

20 Axial thrust dynamic pressure sliding bearing

30 pins

40 closing screws

50 planetary gear

60 planetary carrier

101 The first repair area

102 Second trimming area

103 Circumferential oil groove

104 Functional surface

501 First repair area

502 Second repair area

503 Circumferential oil groove

Claims

A planetary gearbox for wind power equipment, having a planet shaft (10), a planet gear (50) and a planet carrier (60), wherein the planet shaft (10) is installed on the planet carrier (60), The planet gear (50) is mounted on the planet shaft (10), wherein in the axial contact area of the planet gear (50) and the planet shaft (10), the planet gear (50) ) and/or the outer circumferential surface of the planet shaft (10) are provided with shaping areas (101, 102, 501, 502).
The planetary gearbox according to claim 1, characterized in that a circumferential oil groove (103, 503) located in the middle is provided in the axial contact area of the planetary gear (50) and the planetary shaft (10). , a first contact area and a second contact area are respectively provided on both axial sides of the circumferential oil groove (103, 503), wherein a first contact area and/or a second contact area are provided in the The shaping area (101, 102, 501, 502).
The planetary gearbox according to claim 2, characterized in that a first shaping area (101, 501) is provided in part or all of the first contact area, and in part of the second contact area Or a second trimming area (102, 502) is set in the entire area.
The planetary gearbox according to claim 3, characterized in that the first modification area (101, 501) and the second modification area (102, 502) are set according to the actual working conditions of the planetary gearbox. ) location and area.
The planetary gearbox according to claim 4, characterized in that the first shaping area (101, 501) and the second shaping area (102, 502) are arranged relative to the circumferential oil groove (103, 503). ) is axially symmetrical.
The planetary gearbox according to any one of claims 1 to 5, characterized in that the modification area (101, 102, 501, 502) is provided with an oil storage tank.
The planetary gearbox according to any one of claims 1 to 5, characterized in that the shaping area (101, 102, 501, 502) has a hardened coating or a clad bronze coating.
The planetary gearbox according to claim 1, characterized in that an axial bearing member (20) is provided on the planetary shaft (10) and at one or both axial ends of the planetary gear (50). An axial modification area is provided on the end surface of the axial bearing member (20) that contacts the planet gear (50).
The planetary gearbox according to claim 8, characterized in that the axial bearing member is a shoulder, a bearing or a ring member of the planetary shaft (10).
A wind power equipment, characterized in that the wind power equipment has a planetary gearbox according to any one of claims 1 to 9.