Wind power planetary gear assembly and wind power gear box

Abstract

The present disclosure relates to a wind power planetary gear assembly and a wind power gear box. The wind power planetary gear assembly comprises a planetary shaft, a planetary gear sleeved outside the planetary shaft, and a cylindrical roller radially rollably arranged between the planetary shaft and the planetary gear, so that the planetary gear can rotate relative to the planetary shaft, wherein an outer circumferential surface of the planetary shaft is provided with at least one row of raceways, the cylindrical roller is located in the raceways, and a rolling surface of the cylindrical roller is in direct contact with the outer circumferential surface of the planetary shaft. The wind power planetary gear assembly of the present disclosure can significantly improve the bearing capacity of the planetary gear assembly and the torque density of the gear box without increasing the volume of the gear box, thereby meeting the increasing demand for high power density of the gear box.

Description

Technical Field

[0001] This utility model relates to the field of bearing technology, and in particular to a wind power planetary gear assembly for a wind power generation gearbox. Background Technology

[0002] In wind power generation technologies, gearboxes typically employ conventional rolling bearings, with a retaining flange 21 within the inner bore of the planetary gear 20 to withstand the axial force and torque acting on it. The rolling bearings are responsible for bearing the radial force Fr and axial force Fa of the planetary gear 20, and transmitting these forces to the planet shaft and planet carrier, respectively. Figure 1 As shown.

[0003] As the megawatt count of wind power systems increases, the power density requirements for gearboxes are constantly rising, while also demanding reductions in gearbox size and weight. These new requirements mean that while increasing the load-carrying capacity of the cylindrical roller bearings in planetary gear assemblies, their overall dimensions must also be reduced, posing an unprecedented challenge to traditional bearing design concepts.

[0004] The traditional design concept of cylindrical roller bearings is to increase load-bearing capacity and life by increasing the size of the cylindrical rollers. However, while keeping the overall gearbox dimensions constant, increasing the size of the cylindrical rollers will lead to a reduction in the inner diameter of the bearing's inner ring 22. Because of the reduced bearing inner diameter, the outer diameter of the planetary shaft 10 must also be reduced, resulting in a significant decrease in the rigidity and strength of the planetary shaft 10. Therefore, bearings with traditional structures are no longer sufficient to meet the radial and axial load requirements of high-power-density gearboxes. Utility Model Content

[0005] To overcome the problems existing in related technologies, this disclosure provides a wind power generation planetary gear assembly and a wind power generation gearbox, which improves the bearing capacity and power density without sacrificing the rigidity and strength of the planetary shaft.

[0006] According to a first aspect of the present disclosure, a wind power generation planetary gear assembly is provided, comprising: a planetary shaft; a planetary gear sleeved on the outside of the planetary shaft; and cylindrical rollers radially and rotatably disposed between the planetary shaft and the planetary gear, such that the planetary gear can rotate relative to the planetary shaft. The outer circumferential surface of the planetary shaft is provided with at least one row of raceways, the cylindrical rollers are located within the raceways, and the rolling surfaces of the cylindrical rollers are in direct contact with the outer circumferential surface of the planetary shaft.

[0007] In some embodiments, the wind power planetary gear assembly includes two axially spaced planet carriers, the planet carriers being torsionally connected to the planetary shaft, and the planetary gears being located axially between the two planet carriers; wherein, an axial force-bearing ring is provided on the inner axial end face of the planet carriers and the planetary gears, and the axial end face of the axial force-bearing ring abuts against the axial end face of the planetary gears.

[0008] In some embodiments, the axial force-bearing ring is an integral annular structure.

[0009] In some embodiments, the axially stressed ring is composed of a plurality of segmented annular blocks.

[0010] In some embodiments, the raceway of the planetary shaft is formed by a shoulder integrally formed with the outer peripheral surface of the planetary shaft.

[0011] In some embodiments, the raceway of the planetary shaft is formed by a positioning ring that is anti-torsionally connected to the outer circumferential surface of the planetary shaft.

[0012] In some embodiments, at least two rows of cylindrical rollers are arranged side by side along the axial direction within each row of the raceways.

[0013] In some embodiments, the planetary gear assembly further includes a cage.

[0014] In some embodiments, the wind power planetary gear assembly is a planetary gear assembly fully loaded with cylindrical rollers.

[0015] According to a second aspect of the present disclosure, the present disclosure provides a wind power generation gearbox, including a wind power generation planetary gear assembly as described in the first aspect.

[0016] The technical solutions provided by the embodiments of this disclosure can include the following beneficial effects: by using the planetary shaft as the inner ring of the bearing and directly forming raceways on its outer circumferential surface, a larger radial space can be provided for the cylindrical rollers without changing the gearbox size. This allows for the use of larger or more numerous cylindrical rollers. Simultaneously, the axial force of the planetary gears can be directly transmitted to the planetary carriers at both axial ends of the planetary shaft through the axial force-bearing ring, eliminating the need for the intermediate flange in the prior art. This increases the axial length of the cylindrical rollers, improving the radial and axial load-bearing capacity of the bearing, thereby enhancing the overall load-bearing capacity and torque density of the planetary gear assembly and meeting the requirements of modern high-power-density gearboxes. Attached Figure Description

[0017] The accompanying drawings, which are incorporated in and form a part of this specification, illustrate embodiments consistent with this disclosure and, together with the description, serve to explain the principles of this disclosure.

[0018] Figure 1This is a cross-sectional view of a planetary gear assembly in related technologies;

[0019] Figure 2 This is a cross-sectional view of a planetary gear assembly according to an exemplary embodiment;

[0020] Figure 3 This is a cross-sectional view of a planetary gear assembly according to another exemplary embodiment;

[0021] Figure 4 This is a cross-sectional view of a planetary gear assembly according to yet another exemplary embodiment;

[0022] Figure 5 This is a three-dimensional structural schematic diagram of an axially stressed ring according to an exemplary embodiment;

[0023] Figure 6 This is a three-dimensional structural schematic diagram of an axially stressed ring according to another exemplary embodiment. Detailed Implementation

[0024] Exemplary embodiments will now be described in detail, examples of which are illustrated in the accompanying drawings. When the following description relates to the drawings, unless otherwise indicated, the same numerals in different drawings denote the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this disclosure. Rather, they are merely examples of apparatuses and methods consistent with some aspects of this disclosure as detailed in the appended claims.

[0025] In this invention, unless otherwise stated, axial A, radial R, and circumferential W refer to the axial A, radial R, and circumferential W of the planetary gear assembly 100, respectively; the term "torsional connection" refers to a connection between two elements in a manner that does not rotate relative to each other, which can be achieved via a press fit (i.e., an interference fit) or by integrally forming the two mentioned components. Those skilled in the art will understand the specific meaning of the above terms in this invention as appropriate.

[0026] To solve the above-mentioned technical problems, this disclosure provides a planetary gear assembly 100, such as... Figures 2 to 4 As shown, the planetary gear assembly 100 includes at least a planetary shaft 10, a planetary gear 20, a cylindrical roller 30, and a planet carrier 40.

[0027] The planetary carrier 40 comprises two planetary carriers spaced axially by A. The two planetary carriers 40 are torsionally connected to the axial ends of the outer circumferential surface of the planetary shaft 10. The planetary gear 20 is located between the two planetary carriers 40 along the axial direction A and is sleeved on the outside of the outer circumferential surface of the planetary shaft 10. Cylindrical rollers 30 are rollably disposed between the planetary shaft 10 and the planetary gear 20 along the radial direction R, allowing the planetary gear 20 to rotate circumferentially relative to the planetary shaft 10. The outer circumferential surface of the planetary shaft 10 is provided with at least one row of raceways 11, and the cylindrical rollers 30 are located within the raceways 11, with the rolling surfaces of the cylindrical rollers 30 in direct contact with the outer circumferential surface of the planetary shaft 10.

[0028] The planetary gear assembly 100 disclosed herein eliminates the inner ring structure of the conventional cylindrical roller bearing 30, using the planet shaft 10 as the inner ring and directly forming the raceway 11 on the outer circumferential surface of the planet shaft 10. This allows for greater radial space for the cylindrical rollers 30 without changing the gearbox size. It enables the use of larger or more numerous cylindrical rollers 30, increasing the load capacity and radial force Fr of the planetary gear assembly 100, and enhancing the overall load-bearing capacity and torque density of the planetary gear assembly 100.

[0029] Furthermore, the omission of the bearing inner ring allows for a reduction in gearbox size while increasing the size of the cylindrical roller 30, thus meeting the requirements for high power density and lightweight gearbox.

[0030] In addition, omitting the bearing inner ring not only simplifies the number of parts and the overall structure, reduces manufacturing costs, and improves assembly efficiency, but also maintains the rigidity and strength of the planetary shaft 10 since the increase in the size of the cylindrical roller 30 does not require a reduction in the diameter of the planetary shaft 10. Furthermore, the omission of the bearing inner ring allows for an increase in the diameter of the planetary shaft 10, further enhancing its rigidity and strength.

[0031] Furthermore, the planetary carrier 40 is provided with an axial force-bearing ring 50 on its axial inner end face close to the planetary gear 20, and the axial end face of the axial force-bearing ring 50 abuts against the axial end face of the planetary gear 20. The axial force Fa of the planetary gear 20 on the cylindrical roller 30 can be directly borne by the axial force-bearing ring 50 and transmitted to the planetary carrier 40 at both ends of the planetary shaft 10, without passing through the cylindrical roller 30 and the shoulders 12 or locating rings 13 described below.

[0032] The inner bore of the existing planetary gear 20 is provided with a retaining 21 (such as...). Figure 1 As shown in the figure, the planetary gear 20 of this disclosure no longer has a middle stop 21 in the middle of the inner hole, which increases the axial length of the cylindrical roller 30, improves the radial R and axial A load-bearing capacity of the bearing, meets the requirements of high power density of the gearbox, and thus improves the overall stability and load-bearing capacity of the planetary gear assembly 100.

[0033] Furthermore, by eliminating the intermediate flange 21 of the prior art, the internal structure of the planetary gear 20 is simplified, while the assembly difficulty and assembly accuracy with the cylindrical roller 30 are reduced, thus reducing manufacturing costs and improving assembly efficiency.

[0034] The axial load-bearing ring 50 can be fixed to the axial inner end face of the planetary carrier 40 by fasteners. The axial load-bearing ring 50 can also be fixed to the axial inner end face of the planetary carrier 40 by welding, bonding, or other methods.

[0035] like Figure 5 As shown, in some embodiments, the axial force-bearing ring 50 is a one-piece annular structure. The one-piece annular structure has no seams or connection points in the circumferential direction W, thus resulting in higher overall strength and the ability to withstand the larger axial force Fa of the planetary gear 20. Furthermore, the one-piece annular structure can distribute the axial force Fa more evenly in the circumferential direction, reducing local stress concentration and extending service life. In addition, the one-piece annular structure simplifies the assembly process by requiring only the placement of the entire annular structure during installation, eliminating the need for alignment and fixing of multiple components.

[0036] In some other embodiments, such as Figure 6 As shown, the axial force-bearing ring 50 is composed of multiple segmented annular blocks 51. The segmented design of the axial force-bearing ring 50 allows for the individual manufacture of each annular block, reducing manufacturing difficulty and cost. If an annular block 51 is damaged, only the damaged annular block 51 needs to be replaced, reducing maintenance costs.

[0037] In certain complex working conditions, the segmented axial force-bearing ring 50 can adapt to situations such as large temperature changes and inconsistent coefficients of thermal expansion by using appropriate gaps, reducing unevenness at the end face of the axial force-bearing ring 50 caused by thermal and mechanical stress. Furthermore, the material, thickness, or shape of each annular block 51 can be flexibly adjusted. For example, different materials or reinforcing structures can be used at specific locations to cope with different axial forces Fa.

[0038] In some embodiments, the raceway 11 of the planetary shaft 10 is formed by a shoulder 12 integrally formed with the outer peripheral surface of the planetary shaft 10. The shoulder 12 abuts against the axial end face of the cylindrical roller 30, thereby isolating the cylindrical roller 30 along the axial direction A and limiting the axial position of the cylindrical roller 30.

[0039] Because the shoulder 12 and the planetary shaft 10 are integrally formed without welding or connection points, the overall structural strength of the planetary shaft 10 is higher, enabling it to withstand greater radial force Fr and axial force Fa. At the same time, the integrally formed shoulder 12 reduces the possibility of loosening or mutual wear between the shoulder 12 and the outer circumferential surface of the planetary shaft 10, improving the reliability and durability of the planetary gear assembly 100.

[0040] For example, in such Figure 2 In the illustrated embodiment, the outer surface of the planetary shaft 10 is provided with three shoulders 12, which form two rows of raceways 11. By providing three shoulders 12 to form two rows of raceways 11, not only can the number and contact area of ​​the cylindrical rollers 30 be significantly increased, thereby improving the radial and axial load-bearing capacity of the planetary gear assembly 100, but also the radial load can be distributed more evenly, reducing local stress concentration and extending service life.

[0041] In another embodiment, such as Figure 3 As shown, the raceway 11 of the planetary shaft 10 is formed by a positioning ring 13. The positioning ring 13 is disposed on the outer circumferential surface of the planetary shaft 10. The positioning ring 13 can be locked or sleeved in the annular groove formed on the outer circumferential surface of the planetary shaft 10, and fixed on the outer circumferential surface of the planetary shaft 10 in a manner that keeps the axial position unchanged. Alternatively, it can be sleeved on the outer circumferential surface of the planetary shaft 10 in a torsion-resistant manner by means of interference fit, thereby ensuring that the axial position of the positioning ring 13 is fixed.

[0042] The positioning ring 13 is fixed in the axial position of the planetary shaft 10 and abuts against the axial end face of the cylindrical roller 30, thereby limiting the axial position of the cylindrical roller 30 and preventing the cylindrical roller 30 from moving axially.

[0043] By using the locating ring 13, the position of the locating ring 13 can be flexibly adjusted according to the different radial force Fr or axial force Fa requirements of different planetary gear assemblies 100, so as to obtain raceways 11 with different positions, axial widths, depths, and numbers. For example, in... Figure 3 In the illustrated embodiment, three positioning rings 13 are also provided on the outer surface of the planetary shaft 10, forming two rows of raceways 11. In such... Figure 4 In the embodiment shown, the planetary gear assembly 100 is provided with five positioning rings 13, which form four rows of raceways 11, and each row of raceways 11 has only one row of cylindrical rollers 30 along the axial direction A.

[0044] This makes the structure of the planetary gear assembly 100 more flexible, thus adapting to different working conditions and load requirements, and expanding its application range. In addition, if a locating ring 13 is damaged or needs adjustment, only that locating ring 13 needs to be replaced, without replacing or remanufacturing the entire planetary shaft 10, saving time and costs, and reducing maintenance costs and time.

[0045] It should be noted that, Figure 2 and Figure 3In the illustrated embodiment, the two rows of raceways 11 on the outer circumferential surface of the planetary shaft 10 are merely exemplary, and each row of raceways 11 contains two rows of cylindrical rollers 30 arranged side-by-side along the axial direction. In other embodiments, depending on the load-bearing requirements, only one row of raceways 11 may be provided, or three or four rows may be provided (e.g., ...). Figure 4 (As shown) and other multiple raceways 11, which are not specifically limited here.

[0046] In some other embodiments, such as Figures 1 to 3 As shown, the planetary gear assembly 100 may also include a cage 60. The cage 60 ensures that the cylindrical rollers 30 are evenly distributed circumferentially W within the raceway 11, preventing mutual collisions and friction between the cylindrical rollers 30, thereby reducing wear and extending service life. In addition, under high-speed conditions, the cage 60 can effectively control the position of the cylindrical rollers 30, preventing the cylindrical rollers 30 from shifting due to centrifugal force, thus ensuring the high-speed performance of the planetary gear assembly 100.

[0047] Depending on the position of the cage 60, the cage 60 can also be guided by the positioning ring 13 (e.g., Figure 3 (as shown) or cylindrical roller 30 guide (as shown) Figure 2 (As shown), no specific limitations are made here.

[0048] In other embodiments, such as under low-speed, heavy-load conditions, the wind power planetary gear assembly 100 may be a planetary gear assembly with fully loaded cylindrical rollers 30, such as... Figure 4 As shown, the cylindrical rollers 30 in the raceway 11 have no cage 60. The cylindrical rollers 30 are in direct contact with each other, closely arranged, and fill the entire circumferential space of the raceway 11. Due to the absence of a cage, the circumferential space within the raceway 11 can be utilized more fully, allowing for more or larger cylindrical rollers 30, thereby improving load-bearing capacity and torque density.

[0049] Based on the same inventive concept, this disclosure provides a gearbox including the planetary gear assembly 100 described above. In some embodiments, the gearbox is a wind turbine gearbox. The specific manner in which the functions of the gearbox in the above embodiments are implemented has been described in detail in the embodiments relating to the planetary gear assembly 100, and will not be elaborated upon here.

[0050] Other embodiments of this disclosure will readily occur to those skilled in the art upon consideration of the specification and practice of the invention disclosed herein. This application is intended to cover any variations, uses, or adaptations of this disclosure that follow the general principles of this disclosure and include common knowledge or customary techniques in the art not disclosed herein. The specification and examples are to be considered exemplary only, and the true scope and spirit of this disclosure are indicated by the following scope of claims.

[0051] It should be understood that this disclosure is not limited to the precise structures described above and shown in the accompanying drawings, and various modifications and changes can be made without departing from its scope. The scope of this disclosure is limited only by the appended claims.

Claims

1. A wind power generation planetary gear assembly (100), characterized in that, include: Planetary axis (10); Planetary gears (20) are fitted onto the outside of the planetary shaft (10); as well as Cylindrical rollers (30) are rotatably disposed between the planetary shaft (10) and the planetary gear (20) in a radial direction (R), allowing the planetary gear (20) to rotate relative to the planetary shaft (10). The planetary shaft (10) has at least one row of raceways (11) on its outer peripheral surface. The cylindrical rollers (30) are located in the raceways (11), and the rolling surfaces of the cylindrical rollers (30) are in direct contact with the outer peripheral surface of the planetary shaft (10).

2. The wind power planetary gear assembly (100) according to claim 1, characterized in that, The wind power planetary gear assembly (100) includes two axially spaced planet carriers (40), the planet carriers (40) being torsionally connected to the planet shaft (10), and the planet gears (20) being located axially between the two planet carriers (40). An axial force-bearing ring (50) is provided on the inner axial end face of the planet carrier (40) and the planet gear (20), and the axial end face of the axial force-bearing ring (50) abuts against the axial end face of the planet gear (20).

3. The wind power planetary gear assembly (100) according to claim 2, characterized in that, The axial force-bearing ring (50) is an integral circular ring structure.

4. The wind power planetary gear assembly (100) according to claim 2, characterized in that, The axial force-bearing ring (50) is composed of multiple segmented annular blocks (51).

5. The wind power planetary gear assembly (100) according to claim 1, characterized in that, The raceway (11) of the planetary shaft (10) is formed by a shoulder (12) integrally formed with the outer peripheral surface of the planetary shaft (10).

6. The wind power planetary gear assembly (100) according to claim 1, characterized in that, The raceway (11) of the planetary shaft (10) is formed by a positioning ring (13) that is anti-torsional connected to the outer circumferential surface of the planetary shaft (10).

7. The wind power planetary gear assembly (100) according to claim 1, characterized in that, At least two rows of cylindrical rollers (30) are arranged side by side along the axial direction (A) within each row of the raceway (11).

8. The wind power planetary gear assembly (100) according to claim 1, characterized in that, The planetary gear assembly (100) also includes a cage (60).

9. The wind power planetary gear assembly (100) according to any one of claims 1-6, characterized in that, The wind power planetary gear assembly (100) is a planetary gear assembly fully loaded with cylindrical rollers (30).

10. A wind power generation gearbox, characterized in that, Includes the wind power planetary gear assembly (100) as described in any one of claims 1-9.

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