Planetary transmission mechanism and gearbox
By designing large radial cross-section rolling elements and limiting parts in the planetary transmission mechanism, the problem of uneven bearing life in the wind turbine main gearbox was solved, achieving higher load-bearing capacity and lower maintenance costs.
Patent Information
- Application Number
- CN202520381435.9
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-03-06
- Publication Date
- 2025-11-25
- Estimated Expiration
- 2035-03-06
AI Technical Summary
In the main gearbox of a wind turbine, the bearing located at the end of the first-stage planetary pin shaft experiences greater contact stress when subjected to eccentric loads, resulting in a shorter lifespan than the bearing in the middle section and increased maintenance costs.
Design a planetary transmission mechanism including a rotating shaft, an inner ring, and rolling elements. The radial cross-sectional dimension of the rolling element near the end face of the rotating shaft is larger than that of the other rolling elements. The rolling elements transmit and distribute the load. The rotating element is connected to the inner ring through the rolling elements. The inner ring is interference-fitted with the rotating shaft. The planetary carrier restricts the position of the inner ring, and the limiting part ensures stability.
This improves the load-bearing capacity and service life of the planetary transmission mechanism, while reducing maintenance costs.
Smart Images
Figure CN223594870U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The utility model relates to gear box technical field especially relates to a kind of planetary transmission mechanism and gear box. BACKGROUND
[0002] In wind power main gear box, the bearing of large load-bearing first planetary gear is three or four column cylindrical roller bearings, and the size specification of each column bearing is same.When first planetary pin shaft is under some working conditions eccentric load, the bearing at the end of pin shaft is contacted stress after load, which leads to the life of bearing at the end of pin shaft is lower than the bearing at the middle of pin shaft, and operating personnel need to replace or disassemble and repair damaged bearing in time, thereby improving the maintenance cost of gear box. SUMMARY
[0003] The utility model discloses a kind of planetary transmission mechanism, which can improve service life and reduce use cost.
[0004] To achieve this purpose, the utility model adopts the following technical solutions:
[0005] A kind of planetary transmission mechanism, comprising:
[0006] Shaft;
[0007] Multiple inner rings, sequentially fitted on the shaft along the axial direction of the shaft;
[0008] Multiple rolling elements, each outer periphery of the inner ring is circumferentially spaced apart from a group of rolling elements, along the radial direction of the shaft, the radial cross-sectional dimension of the rolling elements close to one end surface of the shaft is greater than the radial cross-sectional dimension of the rolling elements of the remaining groups;
[0009] Rotating member, rotatingly connected to the inner ring through the rolling elements, and multiple groups of rolling elements are clamped between the inner ring and the rotating member.
[0010] Optionally, the planetary transmission mechanism further comprises a planet carrier, the shaft is arranged on the planet carrier, and the inner ring is limited in the planet carrier.
[0011] Optionally, the planet carrier is in clearance fit with the inner ring close to the end of the shaft.
[0012] Optionally, along the axial direction of the shaft, the clearance between the planet carrier and the inner ring close to the end of the shaft is 0.5-1.5mm.
[0013] Optionally, a limiting portion is provided on the rotating member, and the limiting portion is clamped between two adjacent groups of rolling elements along the axial direction of the shaft.
[0014] Optionally, the rotating member is provided with a step portion, and the rolling member close to the end of the rotating shaft abuts against the step portion.
[0015] Optionally, the inner ring and the rotating shaft are in interference fit.
[0016] Optionally, the end faces of the adjacent inner rings abut against each other.
[0017] Optionally, the rolling member is a cylindrical roller.
[0018] Another object of the present application is to provide a gear box, which can improve the service life of the gear box and reduce the use cost.
[0019] To achieve the above object, the present application adopts the following technical scheme.
[0020] The gear box comprises a box body and the planetary transmission mechanism as described above, and the planetary transmission mechanism is arranged in the box body.
[0021] The present application has the following advantages:
[0022] The present application provides a planetary transmission mechanism and a gear box. The planetary transmission mechanism comprises a rotating shaft, inner rings, rolling members and a rotating member. The inner rings and the rolling members are provided in plurality, respectively. The plurality of inner rings are sequentially sleeved on the rotating shaft along the axial direction of the rotating shaft. A group of rolling members are arranged on the outer periphery of each inner ring in circumferential direction. The arrangement can more effectively transfer and disperse the load, so that the whole planetary transmission mechanism is more stable. The radial cross-sectional dimension of the rolling members close to one end face of the rotating shaft is greater than that of the rolling members of the other groups. When the rotating shaft bears eccentric load, the rolling members with greater radial cross-sectional dimension can better disperse stress and reduce the contact stress per unit area, thereby improving the load capacity of the planetary transmission mechanism and prolonging the service life thereof. The rotating member is rotatably connected to the inner ring through the rolling members. The plurality of groups of rolling members are clamped between the inner ring and the rotating member, thereby ensuring that the rotating member can freely rotate relative to the rotating shaft and the inner ring and improving the compactness of the overall structure of the planetary transmission mechanism. The gear box comprises a box body and the planetary transmission mechanism, and the planetary transmission mechanism is arranged in the box body. Through the above arrangement, the planetary transmission mechanism of the present application can improve the service life and reduce the use cost. BRIEF DESCRIPTION OF DRAWINGS
[0023] Figure 1 is the first schematic view of the planetary transmission mechanism provided by the present application;
[0024] Figure 2 is the second schematic view of the planetary transmission mechanism provided by the present application;
[0025] Figure 3 is the third schematic view of the planetary transmission mechanism provided by the present application;
[0026] Figure 4 is a fourth schematic view of the planetary transmission mechanism provided by the embodiment of the present application;
[0027] Figure 5 is a fifth schematic view of the planetary transmission mechanism provided by the embodiment of the present application;
[0028] Figure 6 is a sixth schematic view of the planetary transmission mechanism provided by the embodiment of the present application.
[0029] In the drawings:
[0030] 1, rotating shaft; 11, stepped portion; 2, inner ring; 3, rolling element; 4, rotating element; 41, limiting portion; 5, planetary carrier. DETAILED DESCRIPTION
[0031] The present application will be further described below in conjunction with the drawings and embodiments. It can be understood that the specific embodiments described herein are only used to explain the present application, and not to limit the present application. In addition, it should be noted that, in order to facilitate the description, only the parts related to the present application are shown in the drawings, rather than all the structures.
[0032] In the description of the present application, unless otherwise explicitly specified and limited, the terms "connected", "connected", "fixed" should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or it can be integrated; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the internal communication of two elements or the interaction relationship between two elements. For ordinary skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.
[0033] In the present application, unless otherwise explicitly specified and limited, the first feature "on" or "below" the second feature can include the direct contact between the first and second features, or it can include the contact between the first and second features through another feature between them. Moreover, the first feature "on", "above" and "above" the second feature includes the first feature above and obliquely above the second feature, or only indicates that the horizontal height of the first feature is higher than that of the second feature. The first feature "below", "below" and "below" the second feature includes the first feature below and obliquely below the second feature, or only indicates that the horizontal height of the first feature is less than that of the second feature.
[0034] In the description of this embodiment, the terms "upper," "lower," "right," etc., refer to the orientation or positional relationship shown in the accompanying drawings. They are used only for ease of description and simplification of operation, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. In addition, the terms "first" and "second" are only used for distinction in description and have no special meaning.
[0035] In wind turbine main gearboxes, the primary planetary gear bearings, which bear the heaviest loads, are typically three- or four-row cylindrical roller bearings, with each row having identical dimensions. When the primary planetary pins are subjected to eccentric loads under certain operating conditions, the bearings at the pin ends experience higher contact stress under load. This results in a shorter lifespan for the bearings at the pin ends compared to those in the middle of the pin, requiring timely replacement or disassembly and repair by maintenance personnel, thus increasing the gearbox's maintenance costs.
[0036] Therefore, there is an urgent need for a planetary transmission mechanism and gearbox to solve the above-mentioned technical problems.
[0037] like Figures 1-6 As shown, this embodiment provides a planetary transmission mechanism, which includes a rotating shaft 1, an inner ring 2, rolling elements 3, and a rotating element 4. Multiple inner rings 2 and multiple rolling elements 3 are provided. Multiple inner rings 2 are sequentially sleeved on the rotating shaft 1 along its axial direction. Each inner ring 2 has a set of rolling elements 3 spaced circumferentially around its outer periphery. The radial cross-sectional dimension of the rolling element 3 closest to one end face of the rotating shaft 1 is larger than the radial cross-sectional dimension of the other sets of rolling elements 3. The rotating element 4 is rotatably connected to the inner ring 2 through the rolling elements 3. Multiple sets of rolling elements 3 are sandwiched between the inner ring 2 and the rotating element 4.
[0038] In this embodiment, multiple inner rings 2 and rolling elements 3 are provided. Multiple inner rings 2 are sequentially sleeved on the rotating shaft 1 along its axial direction. A set of rolling elements 3 is spaced circumferentially around the outer periphery of each inner ring 2. This arrangement can more effectively transmit and distribute loads, making the entire planetary transmission mechanism more stable. The radial cross-sectional dimension of the rolling element 3 closest to one end face of the rotating shaft 1 is larger than that of the other sets of rolling elements 3. When the rotating shaft 1 is subjected to eccentric loads, the rolling element 3 with a larger radial cross-sectional dimension can better distribute stress, reduce contact stress per unit area, thereby improving the load-bearing capacity of the planetary transmission mechanism and extending its service life. A rotating element 4 is rotatably connected to the inner ring 2 via the rolling elements 3. Multiple sets of rolling elements 3 are sandwiched between the inner ring 2 and the rotating element 4, ensuring that the rotating element 4 can rotate freely relative to the rotating shaft 1 and the inner ring 2, improving the overall compactness of the planetary transmission mechanism. Through the above arrangement, the planetary transmission mechanism of this embodiment can improve its service life and reduce operating costs.
[0039] It should be noted that one set of rolling elements 3 includes a plurality of rolling elements 3, which can be two, three, or four, etc., and the specific number of rolling elements 3 in each set is not limited here.
[0040] The specific structure of the planetary transmission mechanism will be described below:
[0041] Specifically, the planetary transmission mechanism further includes a planet carrier 5, the rotating shaft 1 is arranged on the planet carrier 5, and the inner ring 2 is limited in the planet carrier 5. By arranging the planet carrier 5 to limit the position of the inner ring 2, it is ensured that the inner ring 2 and the rolling elements 3 work in the correct position, and the use safety of the planetary transmission mechanism is improved. The planet carrier 5 is a double-wall split type planet carrier or a double-wall integral type planet carrier, and the specific structure of the planet carrier 5 is not limited here as long as the above functions can be achieved.
[0042] More specifically, the planet carrier 5 is in clearance fit with the inner ring 2 near the end of the rotating shaft 1. Such an arrangement not only facilitates installation, but also allows the planet carrier 5 and the inner ring 2 to have certain thermal expansion and slight displacement to ensure the stability of the overall structure.
[0043] More specifically, the size of the clearance between the planet carrier 5 and the inner ring 2 near the end of the rotating shaft 1 is 0.5-1.5 mm in the axial direction of the rotating shaft 1, which not only ensures the compactness of the planetary transmission mechanism, but also ensures the stability of the overall structure. For example, the size of the clearance between the planet carrier 5 and the inner ring 2 near the end of the rotating shaft 1 is 0.5 mm, 1.0 mm, or 1.5 mm.
[0044] Specifically, the rotating element 4 is provided with a limiting portion 41, which is clamped between two adjacent rolling elements 3 in the axial direction of the rotating shaft 1, thereby ensuring the stability and safety of the planetary transmission mechanism and preventing the rotating element 4 from moving in the axial direction of the rotating shaft 1.
[0045] More specifically, in this embodiment, the rotating element 4 is a bevel gear, which abuts against the plurality of rolling elements 3. Since the rolling elements 3 have a small friction coefficient, it is ensured that the bevel gear can freely rotate around its own axis. The limiting portion 41 is a protruding block, which is arranged in the shaft hole of the bevel gear along the circumferential direction of the bevel gear. This not only facilitates the assembly of the bevel gear, but also ensures the axial positioning of the bevel gear by clamping the protruding block between two adjacent rolling elements 3, thereby preventing the bevel gear from moving. In other embodiments, the rotating element 4 is a cylindrical gear, and the limiting portion 41 is a convex ridge. The specific structure of the rotating element 4 and the limiting portion 41 is not limited here as long as the above functions can be achieved.
[0046] More specifically, in the embodiment, the rolling members 3 are cylindrical rollers, and the contact between the rolling members 3 and the inner ring 2 is linear contact, so that the planetary transmission mechanism can bear larger radial load, and the friction coefficient of the cylindrical rollers is relatively small, which helps to reduce the energy loss and heat generation of the planetary transmission mechanism during operation. In other embodiments, the rolling members 3 are spherical rollers, and the specific structure of the rolling members 3 is not limited here as long as the above functions can be achieved.
[0047] Specifically, in the embodiment, the rotating member 4 is provided with a stepped portion 11, and the rolling members 3 near the end of the rotating shaft 1 abut against the stepped portion 11, thereby providing support and positioning for the rolling members 3 near the end of the rotating shaft 1, ensuring the stability and accuracy of the structure.
[0048] More specifically, in other embodiments, the rotating shaft 1 is provided with a stepped portion 11, and the inner ring 2 near the end of the rotating shaft 1 abuts against the stepped portion 11, thereby providing support and positioning for the inner ring 2 near the end of the rotating shaft 1, ensuring the stability and accuracy of the structure.
[0049] Specifically, the inner ring 2 is in interference fit with the rotating shaft 1, thereby enhancing the overall rigidity and stability of the planetary transmission mechanism.
[0050] More specifically, the end faces of adjacent inner rings 2 abut against each other, thereby improving the operation safety of the planetary transmission mechanism, and reducing the risk of failure of adjacent inner rings 2 due to looseness or excessive clearance.
[0051] The embodiment also provides a gear box, which comprises a box body and the above planetary transmission mechanism, and the planetary transmission mechanism is arranged in the box body, thereby improving the service life of the gear box and reducing the use cost.
[0052] Obviously, the above embodiments of the utility model are only examples for clearly illustrating the utility model, and are not a limitation on the embodiments of the utility model. For ordinary skilled in the art, various obvious changes, re-adjustments and replacements can be made without departing from the protection scope of the utility model. Here, it is unnecessary and impossible to enumerate all the embodiments. Any modification, equivalent replacement and improvement made within the spirit and principle of the utility model should be included in the protection scope of the utility model claim.
Claims
1. A planetary transmission mechanism, characterized in that, include: Shaft (1); Multiple inner rings (2) are sequentially sleeved on the rotating shaft (1) along the axial direction of the rotating shaft (1); Multiple rolling elements (3), each inner ring (2) has a set of rolling elements (3) spaced around its outer periphery in the circumferential direction, and the radial cross-sectional dimension of the set of rolling elements (3) near one end face of the rotating shaft (1) is larger than the radial cross-sectional dimension of the other sets of rolling elements (3); The rotating component (4) is rotatably connected to the inner ring (2) via the rolling component (3), and multiple sets of the rolling components (3) are sandwiched between the inner ring (2) and the rotating component (4).
2. The planetary transmission mechanism according to claim 1, characterized in that, The planetary transmission mechanism also includes a planet carrier (5), the rotating shaft (1) is disposed on the planet carrier (5), and the inner ring (2) is limited to the planet carrier (5).
3. The planetary transmission mechanism according to claim 2, characterized in that, The planetary carrier (5) is clearance-fitted with the inner ring (2) near the end of the pivot (1).
4. The planetary transmission mechanism according to claim 2, characterized in that, Along the axial direction of the rotating shaft (1), the gap between the planetary carrier (5) and the inner ring (2) near the end of the rotating shaft (1) is 0.5 to 1.5 mm.
5. The planetary transmission mechanism according to claim 1, characterized in that, The rotating member (4) is provided with a limiting part (41), which is engaged between two adjacent sets of rolling members (3) along the axial direction of the rotating shaft (1).
6. The planetary transmission mechanism according to claim 1, characterized in that, The rotating member (4) is provided with a stepped portion (11), and the rolling member (3) near the end of the rotating shaft (1) abuts against the stepped portion (11).
7. The planetary transmission mechanism according to claim 1, characterized in that, The inner ring (2) and the rotating shaft (1) are interference-fitted.
8. The planetary transmission mechanism according to claim 1, characterized in that, The end faces of adjacent inner rings (2) abut against each other.
9. The planetary transmission mechanism according to any one of claims 1-8, characterized in that, The rolling element (3) is a cylindrical roller.
10. A gearbox, characterized in that, It includes a housing and a planetary transmission mechanism as described in any one of claims 1-9, wherein the planetary transmission mechanism is disposed in the housing.