WO2023212859A1 - 行星齿轮箱和风电设备 - Google Patents

行星齿轮箱和风电设备 Download PDF

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Publication number
WO2023212859A1
WO2023212859A1 PCT/CN2022/090953 CN2022090953W WO2023212859A1 WO 2023212859 A1 WO2023212859 A1 WO 2023212859A1 CN 2022090953 W CN2022090953 W CN 2022090953W WO 2023212859 A1 WO2023212859 A1 WO 2023212859A1
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Prior art keywords
planetary
axial
bearing member
planetary gearbox
planet
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PCT/CN2022/090953
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English (en)
French (fr)
Inventor
韩慧敏
刘际轩
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舍弗勒技术股份两合公司
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Priority to PCT/CN2022/090953 priority Critical patent/WO2023212859A1/zh
Publication of WO2023212859A1 publication Critical patent/WO2023212859A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H57/022—Adjustment of gear shafts or bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion

Definitions

  • the invention relates to a planetary gearbox used in the field of wind power. Specifically, it concerns planetary shafts used in planetary gearboxes.
  • 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.
  • 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.
  • 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.
  • 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
  • an excessive fit or a fit that needs to be tightened has a negative impact on the function of the journal or on the teeth of the planetary gearbox.
  • the planetary gears will move during operation. , thus producing a large axial load on the planet carrier or axial bearings at both ends of the axis, easily causing damage to the parts.
  • 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 gear and the planetary carrier are assembled on the planetary shaft, wherein first axial bearing members are respectively provided on the planetary shaft and at both axial ends of the planetary gear. and a second axial bearing member, a modification area is provided on the end surface of the first axial bearing member and/or the second axial bearing member that contacts the planetary gear.
  • 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 axial bearing member and the planetary gear, and uses oil pressure to better carry the axial load of the planetary gear to reduce edge stress. Centralize and increase system life.
  • the trimming area may preferably be 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.
  • 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 modification areas on the end surfaces of the first axial bearing member and the second axial bearing member that are in contact with the planet gear; if the planet gear is on the axis If the machine will only move in one direction, it is only necessary to set a trimming area on the axial bearing member in the direction of movement.
  • the first axial bearing member is a shoulder of the planet shaft
  • the second axial bearing member is a bearing or a ring.
  • the axial force carrying function used in wind power gearboxes is transferred to the planetary shaft.
  • the function of the axial dynamic pressure plane bearing is transferred to the shaft shoulder on one side and relies on a replaceable bearing or annular part on the other side. Realized, so that the planet shaft can bear both radial load and unidirectional axial load, no additional thrust plane bearing is required on one side, the number of parts is reduced, and the cost can be reduced.
  • both the first axial bearing member and the second axial bearing member are rings. The use of rings with simple and low-cost structures reduces costs and is easy to replace.
  • the planetary shaft has a modified area on its circumferential surface that is in contact with the planetary gear, so that the planetary shaft can bear both radial loads and unidirectional axial loads. It is also preferred that the thermal expansion coefficients of the planetary shafts and the planetary gears are equal. The thermal expansion coefficients of the planetary shaft and planetary gear are close to or equal, and changes in the oil film gap caused by temperature rise have little impact on the functions of the radial and axial dynamic pressure sliding bearings, making the system more stable.
  • the connection between the bearing as the axial load-bearing member, the ring and the planet carrier can be an interference connection or a threaded connection.
  • the ring has external threads and the planet carrier There are internal threads, or there are internal threads on the ring and external threads on the planetary shaft.
  • the HMZ locking method can be used, that is, the axial load-bearing member also has an axial fastening screw, and the axial fastening screw is used to lock the ring or sliding bearing and the planet carrier.
  • 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.
  • Figure 1 shows a cross-sectional view of a first embodiment of a planetary gearbox
  • Figure 2 shows a perspective view of the planetary axis
  • Figure 3 shows a cross-sectional view of a second embodiment of the planetary gearbox
  • Figure 4 shows a cross-sectional view of the first fixing method of the axial thrust dynamic pressure sliding bearing
  • Figure 5 shows a cross-sectional view of the second fixing method of the axial thrust dynamic pressure sliding bearing
  • Figure 6 shows a cross-sectional view of the third fixing method of the axial thrust dynamic pressure sliding bearing.
  • Figure 1 shows a cross-sectional view of a first embodiment of a planetary gearbox designed according to the present invention, which has a planet shaft 10 on which an axial thrust dynamic pressure sliding bearing 20, a planet gear 40 and a planet carrier 50 are assembled. .
  • the axial thrust dynamic pressure sliding bearing 20 is fixed on the planet carrier 50 through pins 30 .
  • the planet shaft 10 has a shoulder 60 for axially stopping the planet gear 40 , whereby the planet gear 40 is in contact with the shaft member 60 and the axial thrust dynamic pressure sliding bearing 20 at both axial ends of the planet gear 40 .
  • the shoulder 60 and the axial thrust dynamic pressure sliding bearing 20 have axial end surfaces that are in axial contact with the planet gear 40, and modified areas 101 and 201 are provided on the axial end surfaces.
  • 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.
  • FIG. 2 shows a perspective view of the planet shaft 10 , in which only the shoulder 60 of the planet shaft 10 is shown, and the axial thrust dynamic pressure sliding bearing 20 is not shown.
  • the modified area 101 can function as an axial dynamic pressure sliding bearing, for example, is designed in a convex arc shape, or can be processed into an oil storage tank to store enough oil to form an oil film.
  • a trimming area can also be provided in the radial direction, that is, the trimming areas 102 and 103 can be provided on the cylindrical surface of the planet shaft 10.
  • the shape of the trimming area is a commonly used logarithmic curve. Of course, it can also be set in other shapes.
  • the design of the trimming area needs to facilitate the formation of the dynamic pressure oil film, and you can also consider setting up a hardened coating or cladding bronze coating, which helps reduce friction and wear.
  • Figure 3 shows a second preferred embodiment of a planetary gearbox designed according to the invention.
  • the difference from the first embodiment is that the rings 70 with modified areas are used as axial thrust sliding bearings on both left and right sides.
  • the ring 70 may be made of pure bronze material, or may be a steel ring or nut that is surface hardened or clad with bronze.
  • pins 30 are used to fix the axial thrust dynamic pressure sliding bearing 20 to the planet carrier 50 .
  • Figures 4-6 show three ways of fixing the axial thrust dynamic pressure sliding bearing 20.
  • the connection method between the axial thrust dynamic pressure sliding bearing 20 and the planet carrier 50 can be an interference connection or a thread. Connection, there are two connection methods for threaded connection, the ring has external threads and the planet carrier 50 has internal threads, or the ring has internal threads and the planet shaft 10 has external threads.
  • the HMZ locking method can be used, that is, the axial load-bearing member also has an axial fastening screw, and the ring or sliding bearing is locked with the planet carrier by relying on the axial fastening screw, as shown in Figure 5.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Details Of Gearings (AREA)

Abstract

一种用于风电设备的行星齿轮箱和风电设备，包括行星轴（10）、行星齿轮（40）以及行星架（50），行星齿轮（40）和行星架（50）装配在行星轴（10）上，在行星轴（10）上、在行星齿轮（40）的轴向两端分别设置第一轴向承载件（60、70）和第二轴向承载件（20、70），在第一轴向承载件（60、70）和/或第二轴向承载件（20、70）的与行星齿轮（40）接触的端面上设置修型区（101、201）；该行星齿轮箱结构通过设置修型区，能够在接触面上形成压力变化，由此在接触位置形成油膜，从而形成油压以抵抗轴向荷载。

Description

行星齿轮箱和风电设备 技术领域
本发明涉及到一种应用在风电领域的行星齿轮箱。具体地讲，涉及的是应用在行星齿轮箱里的行星轴。
背景技术
随着海上风电的发展，大兆瓦级风机是未来发展的趋势，同时度电成本的降低，对齿轮箱的成本以及运行可靠性有更苛刻的要求，而轴承是齿轮箱中的关键部件，这对轴承的尺寸以及承载能力有更高的要求。由于滚动轴承的失效导致了风力发电齿轮箱失效，致使大量的维修时间和成本的浪费。
WO 03/014 567 A1公开了一种风力发电设备，包括：可旋转地安装在机塔上的、具有用于发电的发电机的机房；承载至少两个转子叶片的转子轮毂的、风力驱动的转子；以及承载转子的大型滚动轴承。此外，大型滚动轴承与和机房中的发电机连接的、并以已知的方式由带有环绕的内齿部的环形齿轮、多个支承在行星齿轮架上的行星齿轮以及中间的恒星齿轮组成的行星齿轮变速器相连接，方法是该大型滚动轴承的两个轴承环的内轴承环通过压力配合连接固定在行星齿轮变速器的环形齿轮的外罩面上。另外，EP 811 764 A1也公开了如此实现大型滚动轴承与行星齿轮变速器的连接，使得大型滚动轴承的两个轴承环的内轴承环压到与转子轮毂连接的并承载行星齿轮架的环上。
现有技术中的风力发电设备具有这样的缺点，大型滚动轴承和连接在后面的行星齿轮变速器由较多的单个部件组成，并且由此一方面在其制造中非常耗成本并且另一方面具有较高的总重量，该总重量在其装配在120m高度以下的机房中时会引起很多缺点。此外，行星齿轮变速器的环形齿轮和大型滚动轴承的内轴承环必须具有至少一个2m以上的外直径或者说内直径，尽管其尺寸制造得非常精确，使得可以可靠地排除由在内轴承环和环形齿轮之间进行压力配合连接时正的配合过度形成的或者说由有 待夯实的配合形成的对轴颈的功能或者对行星齿轮变速器的齿部的负面影响，但是由于存在间隙在工作时行星齿轮会移动，从而对轴向两端的行星架或轴向轴承产生较大的轴向荷载，容易造成零件的损坏。
发明内容
因此，本发明要解决的技术问题是提供一种行星齿轮箱，其能够解决上述现有技术中的缺点。
所述技术问题被根据本发明设计的一种用于风电设备的行星齿轮箱所解决。该行星齿轮箱具有行星轴、行星齿轮以及行星架，其中，行星齿轮和行星架装配在行星轴上，其中，在行星轴上、在行星齿轮的轴向两端分别设置第一轴向承载件和第二轴向承载件，在第一轴向承载件和/或第二轴向承载件的与行星齿轮接触的端面上设置修型区。修型区是指具有特殊结构的区域，例如楔形结构，从而在轴向承载件与行星齿轮的接触区域内形成油膜，利用油压更好地承载行星齿轮的轴向荷载，以减小边缘应力集中，增加系统寿命。修型区优选地可以是储油槽，该结构能够存储润滑油，以便更好地形成油膜。更一步优选地，修型区具有硬化涂层或者熔覆的青铜镀层，可以增加其耐磨损能力，降低维修成本。本发明并不限制修型区的具体结构，只要可以形成油膜即可。修型区具体设置在行星齿轮的轴向一端还是两端，取决于风电设备的设置以及齿轮箱的装配结构。如果行星齿轮在轴向的两个方向上都会移动，则优选在在第一轴向承载件和第二轴向承载件的与行星齿轮接触的端面上都设置修型区；如果行星齿轮在轴向只会朝一个方向移动，则只需要在移动方向上的轴向承载件上设置修型区。
根据本发明的优选实施方式，第一轴向承载件是行星轴的轴肩，第二轴向承载件是轴承或者环件。将应用在风电齿轮箱中的轴向力承载功能转移到行星轴上实现，轴向动压平面轴承的功能一侧转移到轴肩上实现，另外一侧依靠一个可更换的轴承或环形零件来实现，从而行星轴既可以承受径向载荷又可以承受单向轴向载荷，一侧不需要额外的推力平面轴承，零件的数量减少，可以降低成本。另外优选的是，第一轴向承载件和第二轴向承载件都是环件。使用结构简单且造价低廉的环件可以降低成本，且易 于更换。
根据本发明的优选实施方式，行星轴的与行星齿轮接触的圆周面上具有修型区，从而使得行星轴既可以承受径向载荷又可以承受单向的轴向载荷。另外优选的是，行星轴与行星齿轮的热膨胀系数相等。行星轴和行星齿轮的热膨胀系数接近或相等，由于温升引起的油膜间隙的变化对径向和轴向动压滑动轴承的功能几乎没有影响，从而使得系统的运行更加稳定。
根据本发明的优选实施方式，作为轴向承载件的轴承与环件和行星架的连接方式可以是过盈连接或者螺纹连接，螺纹连接时有两种连接方式，环上具有外螺纹，行星架具有内螺纹，或者是环上具有内螺纹，行星轴上具有外螺纹。在采用螺纹连接时可以采用HMZ的锁紧方式，即轴向承载件还具有轴向紧固螺钉，依靠轴向紧固螺钉将环或滑动轴承与行星架进行锁紧。此外，还可以考虑用螺栓在轴向/径向上讲轴向承载件固定在行星架上。
此外，本发明要解决的技术问题还能够被一种风电设备所解决，该风电设备具有包括前面所述的技术特征的行星齿轮箱。
附图说明
以下结合附图进一步描述本发明。图中以相同的附图标记来表示相同或功能相同的部件。附图为：
图1示出行星齿轮箱第一实施例的剖面图；
图2示出行星轴的立体图；
图3示出行星齿轮箱第二实施例的剖面图；
图4示出轴向推力动压滑动轴承第一固定方式的剖面图；
图5示出轴向推力动压滑动轴承第二固定方式的剖面图；
图6示出轴向推力动压滑动轴承第三固定方式的剖面图。
具体实施方式
以下将结合附图阐述根据本发明的行星齿轮箱的具体实施方式。下面的详细描述和附图用于示例性地说明本发明的原理，本发明不限于所描述 的优选实施例，本发明的保护范围由权利要求书限定。
图1示出根据本发明设计的行星齿轮箱第一实施例的剖面图，其具有行星轴10，在该行星轴10上装配有轴向推力动压滑动轴承20、行星齿轮40以及行星架50。轴向推力动压滑动轴承20通过销钉30被固定在行星架50上。行星轴10具有用于轴向止挡行星齿轮40的轴肩60，由此在行星齿轮40的轴向两端分别与轴件60和轴向推力动压滑动轴承20接触。轴肩60和轴向推力动压滑动轴承20具有与行星齿轮40轴向接触的轴向端面，在轴向端面上设置修型区101和201。修型区主要原理是在接触面上形成压力变化，由此在接触位置形成油膜，从而形成油压以抵抗轴向荷载。
图2示出行星轴10的立体图，其中，只示出了行星轴10的轴肩60，并没有示出轴向推力动压滑动轴承20。修型区101可以起到轴向动压滑动轴承的功能，例如设计为凸起的圆弧形，也可以加工为储油槽，从而存储足够的油以形成油膜。此外，径向上也可以设置修型区，即可以在行星轴10的圆柱面上设置修型区102和103，例如该修型区的形状是常用对数曲线，当然也可以设置为其它形状。修型区的设计需要便于动压油膜的形成，同时也可以考虑设置硬化涂层或者熔覆的青铜镀层，其有助于降低摩擦，减少磨损。
图3示出根据本发明设计的行星齿轮箱的第二优选实施例。与第一实施例的区别在于，左右两侧都用具有修型区的环件70作为轴向推力滑动轴承。环件70可以是纯青铜材料，也可以是钢的环或者螺母进行表面硬化或者青铜熔覆。
在图1示出的第一优选实施例中，销钉30被用于将轴向推力动压滑动轴承20固定到行星架50上。图4-6示出了轴向推力动压滑动轴承20的三种固定方式，其中，如图4所示轴向推力动压滑动轴承20和行星架50的连接方式可以是过盈连接或者螺纹连接，螺纹连接时有两种连接方式，环上具有外螺纹，行星架50处具有内螺纹，或者是环上具有内螺纹，行星轴上10具有外螺纹。在采用螺纹连接时可以采用HMZ的锁紧方式，即轴向承载件还具有轴向紧固螺钉，依靠轴向紧固螺钉将环或滑动轴承与行星架进行锁紧，如图5所示。此外，还可以考虑用螺栓在轴向/径向上将轴 向承载件固定在行星架上，如图6所示。
虽然在上述说明中示例性地描述了可能的实施例，但是应当理解到，仍然通过所有已知的和此外技术人员容易想到的技术特征和实施方式的组合存在大量实施例的变化。此外还应该理解到，示例性的实施方式仅仅作为一个例子，这种实施例绝不以任何形式限制本发明的保护范围、应用和构造。通过前述说明更多地是向技术人员提供一种用于转化至少一个示例性实施方式的技术指导，其中，只要不脱离权利要求书的保护范围，便可以进行各种改变，尤其是关于所述部件的功能和结构方面的改变。
附图标记列表
10    行星轴
20    轴向推力动压滑动轴承
30    销钉
40    行星齿轮
50    行星架
60    轴肩
70    环件
101   修型区
102   修型区
103   修型区
201   修型区

Claims (10)

  1. 一种用于风电设备的行星齿轮箱，具有行星轴(10)、行星齿轮(40)以及行星架(50)，其中，所述行星齿轮(40)和所述行星架(50)装配在所述行星轴(10)上，其中，在所述行星轴(10)上、在所述行星齿轮(40)的轴向两端分别设置第一轴向承载件(60、70)和第二轴向承载件(20、70)，在所述第一轴向承载件(60、70)和/或所述第二轴向承载件(20、70)的与所述行星齿轮(40)接触的端面上设置修型区(101、201)。
  2. 根据权利要求1所述的行星齿轮箱，其特征在于，所述第一轴向承载件是所述行星轴(10)的轴肩(60)，所述第二轴向承载件是轴承(20)或者环件(70)。
  3. 根据权利要求1所述的行星齿轮箱，其特征在于，所述第一轴向承载件和所述第二轴向承载件都是环件(70)。
  4. 根据权利要求1至3中任一项所述的行星齿轮箱，其特征在于，所述修型区(101、201)是储油槽。
  5. 根据权利要求1至3中任一项所述的行星齿轮箱，其特征在于，所述修型区(101、201)具有硬化涂层或者熔覆的青铜镀层。
  6. 根据权利要求1所述的行星齿轮箱，其特征在于，所述行星轴(10)的与所述行星齿轮(40)接触的圆周面上具有修型区(102、103)。
  7. 根据权利要求1所述的行星齿轮箱，其特征在于，所述行星轴(10)与所述行星齿轮(40)的热膨胀系数相等。
  8. 根据权利要求2所述的行星齿轮箱，其特征在于，所述第二轴向承载件(20、70)通过过盈连接、螺纹连接或者销钉(30)固定。
  9. 根据权利要求8所述的行星齿轮箱，其特征在于，如果所述第二轴向承载件(20、70)通过螺纹连接固定，则所述第二轴向承载件还具有轴向紧固螺钉。
  10. 一种风电设备，其特征在于，所述风电设备具有根据权利要求1至9中任一项所述的行星齿轮箱。
PCT/CN2022/090953 2022-05-05 2022-05-05 行星齿轮箱和风电设备 WO2023212859A1 (zh)

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WO2010105914A1 (de) * 2009-03-14 2010-09-23 Schaeffler Technologies Gmbh & Co. Kg Planetenträger aus blech und planetenradeinheit mit mindestens einem planetenträger aus blech
DE102011083090A1 (de) * 2011-09-21 2013-01-03 Schaeffler Technologies AG & Co. KG Planetenlagerung und Windenergieanlagengetriebe
US20130217535A1 (en) * 2010-08-31 2013-08-22 Ishibashi Manufacturing, Co., Ltd. Planetary gear train with thrust collar used as thrust bearing of planetary gear and wind turbine generator incorporating the same
CN105422745A (zh) * 2015-12-28 2016-03-23 南京高速齿轮制造有限公司 风力发电机齿轮箱中的行星轮减速级
CN108253128A (zh) * 2018-03-06 2018-07-06 杭州前进齿轮箱集团股份有限公司 一种风电齿轮箱行星结构
DE102018220531A1 (de) * 2018-11-29 2020-06-04 Zf Friedrichshafen Ag Planetengleitlager mit verminderter Breite
CN113187877A (zh) * 2021-05-11 2021-07-30 中国船舶重工集团公司第七0三研究所 一种用于高速重载斜齿轮传动系统的轴向力锥面止推结构

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010105914A1 (de) * 2009-03-14 2010-09-23 Schaeffler Technologies Gmbh & Co. Kg Planetenträger aus blech und planetenradeinheit mit mindestens einem planetenträger aus blech
US20130217535A1 (en) * 2010-08-31 2013-08-22 Ishibashi Manufacturing, Co., Ltd. Planetary gear train with thrust collar used as thrust bearing of planetary gear and wind turbine generator incorporating the same
DE102011083090A1 (de) * 2011-09-21 2013-01-03 Schaeffler Technologies AG & Co. KG Planetenlagerung und Windenergieanlagengetriebe
CN105422745A (zh) * 2015-12-28 2016-03-23 南京高速齿轮制造有限公司 风力发电机齿轮箱中的行星轮减速级
CN108253128A (zh) * 2018-03-06 2018-07-06 杭州前进齿轮箱集团股份有限公司 一种风电齿轮箱行星结构
DE102018220531A1 (de) * 2018-11-29 2020-06-04 Zf Friedrichshafen Ag Planetengleitlager mit verminderter Breite
CN113187877A (zh) * 2021-05-11 2021-07-30 中国船舶重工集团公司第七0三研究所 一种用于高速重载斜齿轮传动系统的轴向力锥面止推结构

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