WO2024250167A1 - 分体式调心滚子轴承 - Google Patents

分体式调心滚子轴承 Download PDF

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Publication number
WO2024250167A1
WO2024250167A1 PCT/CN2023/098533 CN2023098533W WO2024250167A1 WO 2024250167 A1 WO2024250167 A1 WO 2024250167A1 CN 2023098533 W CN2023098533 W CN 2023098533W WO 2024250167 A1 WO2024250167 A1 WO 2024250167A1
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WIPO (PCT)
Prior art keywords
ring
inner ring
roller bearing
locking ring
spherical roller
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2023/098533
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English (en)
French (fr)
Inventor
程涛
刘际轩
贺思传
王为华
夏厚桥
霍华
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to CN202380096687.0A priority Critical patent/CN121039409A/zh
Priority to PCT/CN2023/098533 priority patent/WO2024250167A1/zh
Publication of WO2024250167A1 publication Critical patent/WO2024250167A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers

Definitions

  • the present disclosure relates to the technical field of bearings, and in particular to a split-type spherical roller bearing.
  • Spherical roller bearings mainly bear radial loads, and can also bear axial loads in any direction.
  • Spherical roller bearings have high radial load capacity and are suitable for working under heavy loads or vibration loads. They have good aligning performance and can compensate for coaxiality errors.
  • Spherical roller bearings include integral spherical roller bearings and split spherical roller bearings. Replacing integral spherical roller bearings usually requires additional high-cost work, including disassembling gears or couplings, disassembling drives, or disassembling shaft transmission systems. Therefore, split spherical roller bearings are usually used to replace integral spherical roller bearings, which reduces the downtime of machines and factories, and in many cases can save production costs and assembly costs.
  • the split spherical roller bearings need to be cut, and considering the space reserved for the bolt parts connecting the split structure during the installation process, the size, number and pitch circle of the rolling elements of the split spherical roller bearings will be affected, and their load-bearing capacity is often significantly lower than that of the integral spherical roller bearings.
  • the present disclosure provides a split-type spherical roller bearing.
  • the present disclosure provides a split spherical roller bearing, comprising: an outer ring; an inner ring, the inner ring having an axial width equal to that of the outer ring, the inner ring comprising a first inner ring and a second inner ring which are circumferentially split; a retainer, radially located between the inner ring and the outer ring, the retainer comprising a cross beam portion and a clamping portion, the cross beam portion forming a pocket, the clamping portion being located axially outside the cross beam portion and extending toward the inner ring; A rolling body, located in the pocket of the retaining frame; and a locking ring, located on the axial outside of the rolling body, for circumferentially locking the first inner ring and the second inner ring, wherein the locking ring is located on the radial inside of the clamping portion of the retaining frame and overlaps with the clamping portion in the axial direction.
  • the axial outer side of the rolling body includes a first abutment surface; the axial inner side of the locking ring includes a second abutment surface, wherein the second abutment surface matches the first abutment surface, and the first abutment surface and the second abutment surface are planes or arcuate surfaces.
  • the retaining frame further includes a connecting portion, which is located axially inward of the cross beam portion and is used to connect the cross beam portion, wherein a radial thickness of the connecting portion is greater than a thickness of the cross beam portion.
  • FIG2 is a cross-sectional view of a split spherical roller bearing according to an exemplary embodiment
  • FIG5 is a cross-sectional view of a split spherical roller bearing according to another exemplary embodiment
  • axial direction A, radial direction R and circumferential direction W refer to axial direction A, radial direction R and circumferential direction W of the split spherical roller bearing respectively;
  • the axial outer side refers to the side away from the symmetry axis H in Figure 2 in the axial direction A (for example, the right side in Figure 3), and the axial inner side refers to the side close to the symmetry axis H in Figure 2 in the axial direction A (for example, the left side in Figure 3);
  • the radial outer side refers to the side away from the central axis O in Figure 2 in the radial direction R (the upper side in Figure 2), and the radial inner side refers to the side close to the central axis O in the radial direction R (the lower side in Figure 2).
  • transmission connection means that the driving force/torque can be transmitted between two components, and the two components can be directly connected or through various transmission mechanisms or connection structures to achieve the above function.
  • torque-resistant connection means that torque can be transmitted between two components, and the methods for achieving the torque-resistant connection can include interference fit and bolt connection, etc.
  • the width of the inner ring 10 is much wider than that of the inner ring 10 of the standard integral spherical roller bearing, so that the replacement of the integral spherical roller bearing cannot be met or completed without changing the surrounding structure.
  • the split spherical roller bearing of this structure is difficult to meet customer expectations.
  • the present invention provides a split spherical roller bearing 100 , as shown in FIGS. 2 to 5 , the split spherical roller bearing 100 may include an outer ring 10 , an inner ring 20 , a retaining frame 30 , rolling elements 40 and a locking ring 50 .
  • the split outer ring 10, inner ring 20, retainer 30 and locking ring 50 make the split spherical roller bearing 100 divided into two identical parts. Without disassembling other structures around the integral spherical roller bearing, the split spherical roller bearing 100 has the same appearance as the original integral spherical roller bearing, that is, the axial width of the inner ring 20 is equal to that of the outer ring 10, which improves the problem of the split spherical roller bearing in the related art that the inner ring needs to be widened, resulting in a different appearance size from the integral spherical roller bearing and cannot be simply and directly replaced.
  • the width of the inner ring 20 along the axial direction A is equal to that of the outer ring 10.
  • the retainer 30 is located between the inner ring 20 and the outer ring 10 along the radial direction R.
  • the retainer 30 includes a through hole extending along the axial direction.
  • the beam portions 33 are used to guide and separate the plurality of rolling elements 40 in the circumferential direction W.
  • the beam portions 33 are spaced apart in the circumferential direction to form pockets 35 , and the rolling elements 40 are located in the pockets 35 between the beam portions 33 .
  • first locking ring 51 or the second locking ring 52 is located axially outside each row of rolling elements 40 and is used to circumferentially lock the first inner ring 21 and the second inner ring 22 .
  • the first locking ring 51 and the second locking ring 52 are located between the inner ring 20 and the outer ring 10 along the radial direction R, and the axial outer sides of the first locking ring 51 and the second locking ring 52 can be shorter than or flush with the axial outer sides of the first inner ring 21 and the second outer ring 12 respectively.
  • the first locking ring 51 and the second locking ring 52 are respectively located on the radial inner sides of the clamping parts 34 of the first retaining frame 31 and the second retaining frame 32, and overlap with the clamping parts 34 in the axial direction A, that is, the locking ring 50 and the clamping parts 34 of the retaining frame 30 are stacked in the radial direction R.
  • the second abutting surface 53 may be parallel to the first abutting surface 41.
  • the first abutting surface 41 and the second abutting surface 53 may be convex arcuate surfaces and concave arcuate surfaces that match each other.
  • the space in the axial direction A is fully utilized, so that the axial clearance between the locking ring 50 and the rolling element 40 is reduced, and the locking ring 50 and the rolling element 40 are arranged more compactly in the axial direction A. While ensuring the load-bearing capacity of the split spherical roller bearing 100, there is no need to increase the size of the split spherical roller bearing 100.
  • the cross beam portion 33 is located radially outside the pitch circle of the rolling body 40 , where the pitch circle of the rolling body 40 refers to a circle formed by the center of the rolling body.
  • the gap between the rolling elements can be reduced as much as possible, thereby increasing the number of rolling elements 40.
  • the number of rolling elements 40 can be increased in the circumferential direction W.
  • the split spherical roller bearing 100 of this structure increases the overall load-bearing capacity.
  • the engaging portion 34 can be elastically deformed in the axial direction
  • the hook 36 can be a hook-shaped structure bent toward the radial outside, or a wedge-shaped structure gradually enlarged toward the radial outside
  • the engaging groove 42 It can be a circular groove located on the first abutting surface 41 of the rolling body 40.
  • the hook 36 can slide relative to the inner wall of the circular groove 42 to prevent the hook 36 from detaching from the groove 42.
  • the clamping method of the hook 36 and the groove 42 makes the pre-installation of the rolling body 40 and the retaining frame 30 simpler and more convenient.
  • the split spherical roller bearing 100 is divided into two identical parts. As shown in FIG4 , the split spherical roller bearing 100 is axially divided into the same upper and lower parts, and both the upper and lower parts have two rows of rolling elements 40.
  • the retainer 30 of the upper part can be a split retainer, that is, each row of rolling elements 40 has an independent first retainer 31, and the axial inner sides of the two rows of first retainers 31 abut against each other.
  • the retainer 30 of the lower part can also be a split retainer, that is, each row of rolling elements 40 has an independent second retainer 32, and the axial inner sides of the two rows of second retainers 32 abut against each other.
  • a gap is set between the crossbeam portion 33 of the split retaining frame 30 and the raceway of the outer ring 10 , and the radial inner side of the clamping portion 34 of the retaining frame 30 is used to abut against the radial outer side of the locking ring 50 , so that the retaining frame 30 is guided by the locking ring 50 .
  • the connecting portion 38 can space the two rows of rolling elements 40 in the axial direction, and the connecting portion 38 located on the axial inner side of the rolling element 40 and the clamping portion 34 located on the axial outer side of the rolling element 40 jointly limit the axial movement of the rolling element 40. Furthermore, the thickness of the connecting portion 38 along the radial direction R can be greater than the thickness of the cross beam portion 33. The main purpose is to better control the yaw angle of the rolling element 40 when the split spherical roller bearing 100 is running.
  • the retaining frame 30 can be a structure in which the outer ring 10 raceway is guided, that is, the connecting portion 38 maintains a smaller radial clearance with the raceway of the outer ring 10, while the inner diameter of the retaining frame 30 (the clamping portion 34) needs to maintain a larger clearance with the locking ring 50.
  • the integrated retainer 30 is guided by the outer ring 10 through the connecting portion 38, and the split retainer 30 is guided by the locking ring 50 through the clamping portion 34.
  • the above embodiments are only exemplary and are not intended to limit the protection scope of the present disclosure.
  • the split retainer 30 may also be guided by the outer ring 10, and the integrated retainer 30 may also be guided by the locking ring 50 through the clamping portion 34.
  • the end of the first locking ring 51 may be provided with a radial R-recessed mounting notch 37, a first hole (not shown in the figure) is provided at the mounting notch 37, and a second hole (not shown in the figure) is provided at the end of the second locking ring 52.
  • the fastener 60 (such as a bolt or a screw) can be screwed into the second hole through the first hole of the mounting notch 37 to achieve a fixed connection between the first locking ring 51 and the second locking ring 52.
  • annular groove 23 may also be provided on the radial outer side of the inner ring 20, and the annular groove 23 prevents the locking ring 50 from moving axially, thereby preventing the locking ring 50 from axially falling off and causing the first inner ring 21 and the second inner ring 22 to scatter.
  • the locking ring 50 is inserted into the annular groove 23 by interference fit, and the locking ring 50 circumferentially covers the end face contact points of the first inner ring 21 and the second inner ring 22. In this way, a quick locking connection between the first inner ring 21 and the second inner ring 22 can be achieved without using fasteners such as bolts or screws, thereby saving installation steps and time.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

一种分体式调心滚子轴承（100），包括外圈（10）；内圈（20），内圈（20）沿轴向(A)的宽度与外圈(10)相等，内圈（20）包括沿周向（W）分体的第一内圈（21）和第二内圈（22）；保持架（30），沿径向(R)位于内圈（20）和外圈（10）之间，保持架（30）包括过梁部（33）和卡接部（34），卡接部（34）位于过梁部（33）的轴向(A)外侧，且朝内圈（20）的方向延伸；滚动体（40），位于保持架（30）的兜孔（35）内；以及锁紧环（50），位于滚动体（40）的轴向(A)外侧，用于周向（W）锁紧第一内圈（21）和第二内圈（22），其中，锁紧环（50）位于保持架（30）的卡接部（34）的径向(R)内侧，且与卡接部（34）在轴向(A)上重叠。通过锁紧环（50）与保持架（30）的径向(R)堆叠设置，在不改变其他周围结构的情况下，即可更换整体式调心滚子轴承（100），保证了滚动体（40）原有的轴向长度及承载能力。

Description

分体式调心滚子轴承 技术领域
本公开涉及轴承技术领域，尤其涉及一种分体式调心滚子轴承。
背景技术
常用标准设计的调心滚子轴承，主要承受径向载荷，同时也能承受任一方向的轴向载荷。调心滚子轴承有高的径向载荷能力，适用于重载或振动载荷下工作，其调心性能良好，能补偿同轴度误差。
调心滚子轴承包括整体式调心滚子轴承和分体式调心滚子轴承，更换整体式调心滚子轴承，通常需要额外的高成本工作，包括拆卸齿轮或联轴器，拆卸驱动器或拆卸轴传动系统。因此，通常使用分体式调心滚子轴承更换整体式调心滚子轴承，减少了机器和工厂的停机时间，且在许多情况下可以节省生产成本以及组装成本。
然而相关技术中，分体式调心滚子轴承由于分体结构的限制，即轴承各部件需要被切割，且考虑到给安装过程预留连接分体结构的螺栓部分的空间，分体后的调心滚子轴承的滚动体的大小、数量以及节圆均会受影响，其承载能力往往较整体式调心滚子轴承有较明显的下降。
发明内容
为克服相关技术中存在的问题，本公开提供一种分体式调心滚子轴承。
根据本公开实施例的第一方面，本公开提供一种分体式调心滚子轴承，包括：外圈；内圈，所述内圈沿轴向的宽度与所述外圈相等，所述内圈包括沿周向分体的第一内圈和第二内圈；保持架，沿径向位于所述内圈和所述外圈之间，所述保持架包括过梁部和卡接部，所述过梁部形成兜孔，所述卡接部位于所述过梁部的轴向外侧，且朝所述内圈的方向延伸； 滚动体，位于所述保持架的所述兜孔内；以及锁紧环，位于所述滚动体的轴向外侧，用于周向锁紧所述第一内圈和所述第二内圈，其中，所述锁紧环位于所述保持架的卡接部的径向内侧，且与所述卡接部在轴向上重叠。
在一些实施例中，所述滚动体的轴向外侧包括第一抵接面；所述锁紧环的轴向内侧包括第二抵接面，其中，所述第二抵接面与所述第一抵接面相匹配，且所述第一抵接面和所述第二抵接面为平面或弧形面。
在一些实施例中，所述过梁部位于所述滚动体的节圆的径向外侧。
在一些实施例中，所述卡接部的轴向内侧设置有卡勾；所述滚动体的轴向外侧设置有卡槽；其中，所述滚动体由径向内侧朝径向外侧挤入所述兜孔，使所述卡接部弹性变形并回弹后，所述卡勾卡入所述卡槽内，实现所述滚动体与所述保持架的预安装。
在一些实施例中，所述保持架还包括连接部，所述连接部位于所述过梁部的轴向内侧，用于连接所述过梁部，其中，所述连接部的沿径向的厚度大于所述过梁部的厚度。
在一些实施例中，所述过梁部与所述外圈滚道间隙设置，且所述卡接部的径向内侧与所述锁紧环的径向外侧抵接，使得所述保持架由所述锁紧环引导。
在一些实施例中，所述锁紧环包括沿周向分体的第一锁紧环和第二锁紧环，所述第一锁紧环和所述第二锁紧环之间通过紧固件连接，实现所述第一内圈和所述第二内圈的锁紧。
在一些实施例中，所述锁紧环与所述内圈分体设置；其中，所述内圈的径向外侧设置有环形槽，所述锁紧环通过过盈配合卡入所述环形槽内，实现所述第一内圈和所述第二内圈的锁紧连接。
在一些实施例中，所述锁紧环与所述内圈一体成型。
在一些实施例中，所述保持架包括沿周向分体设置的第一保持架和第二保持架；和所述外圈包括沿周向分体设置的第一外圈和第二外圈。
本公开的实施例提供的技术方案可以包括以下有益效果：通过锁紧环与保持架的径向堆叠设置，在不改变其他周围结构的情况下，即可更换整体式调心滚子轴承，不仅保证了滚动体原有的轴向长度，还使分体式调心 滚子轴承的承载能力大于或等于原有整体式调心滚子轴承的承载能力。
附图说明
此处的附图被并入说明书中并构成本说明书的一部分，示出了符合本公开的实施例，并与说明书一起用于解释本公开的原理。
图1是相关技术中分体式调心滚子轴承的剖视图；
图2是根据一示例性实施例示出的分体式调心滚子轴承的剖视图；
图3是图2中的Z部放大示意图；
图4是根据一示例性实施例示出的分体式调心滚子轴承的爆炸图；
图5是根据另一示例性实施例示出的分体式调心滚子轴承的剖视图；
图6是根据另一示例性实施例示出的保持架的立体示意图。
具体实施方式
这里将详细地对示例性实施例进行说明，其示例表示在附图中。下面的描述涉及附图时，除非另有表示，不同附图中的相同数字表示相同或相似的要素。以下示例性实施例中所描述的实施方式并不代表与本公开相一致的所有实施方式。相反，它们仅是与如所附权利要求书中所详述的、本公开的一些方面相一致的装置和方法的例子。
在本发明中，除非另有说明，否则轴向A、径向R和周向W分别是指分体式调心滚子轴承的轴向A、径向R和周向W；轴向外侧是指在轴向A上远离图2中的对称轴H的一侧(例如图3中的右侧)，轴向内侧是指在轴向A上靠近图2中的对称轴H的一侧(例如图3中的左侧)；径向外侧是指在径向R上远离图2中的中心轴线O的那侧(图2中的上侧)，径向内侧是指在径向R上接近该中心轴线O的那侧(图2中的下侧)。
另外，术语“传动连接”是指两个部件之间能够传递驱动力/扭矩，这两个部件可以直接连接也可以通过各种传动机构或连接结构以实现上述功能。术语“抗扭连接”，是指两个部件之间可以传递扭矩，并且实现抗扭矩连接的方式可以包括过盈配合以及螺栓连接等等。
图1为相关技术中的分体式调心滚子轴承的剖视图，如图1所示，分 体式的内圈常常采用螺栓紧定的方式将两部分连接在一起，为了尽可能提高分体式轴承的承载能力的同时达到锁紧内圈的目的，不得不提高整个内圈的整体宽度，即内圈10比外圈20宽，以使得在内圈两侧可以添加相应的锁紧环50。除此之外，为了进一步增加承载，有时还将保持架设计成穿销式结构用以增加轴承滚动体40的数量以提高承载能力。
虽然调心滚子轴承的承载能力得到较大程度保留，但由于内圈10的宽度比标准整体式调心滚子轴承的内圈10宽很多，以至于在不改变周边结构的情况下无法满足或完成对整体式调心滚子轴承的替换，这种结构的分体式调心滚子轴承难以达到客户的期望。
若要达到原整体式调心滚子轴承同等的宽度，则需要大幅度减小滚动体40的尺寸，但轴承性能和寿命有较大的负面影响，对于维修市场而言，不可能改变机械和零部件既有的尺寸，也同样不愿意接受轴承承载能力的降低。
为解决上述技术问题，本发明提供一种分体式调心滚子轴承100，如图2至图5所示，分体式调心滚子轴承100可以包括外圈10、内圈20、保持架30、滚动体40以及锁紧环50。
如图4所示，外圈10可以包括沿周向分体设置的第一外圈11和第二外圈12；内圈20可以包括沿周向分体设置的第一内圈21和第二内圈22；保持架30可以包括沿周向分体设置的第一保持架31和第二保持架32；锁紧环50可以包括沿周向分体设置的第一锁紧环51和第二锁紧环52。
分体式的外圈10、内圈20、保持架30以及锁紧环50，使得分体式调心滚子轴承100分为相同的两部分，在无需拆卸整体式调心滚子轴承周围其他结构的情况下，分体式调心滚子轴承100与原先的整体式调心滚子主城具有相同的外形，即内圈20与外圈10轴向宽度相等，改进了相关技术中的分体式调心滚子轴承的内圈需要加宽导致的与整体式调心滚子轴承外形尺寸不同，不能简单直接地更换的问题。
如图2和图3所示，内圈20沿轴向A的宽度与外圈10相等，保持架30沿径向R位于内圈20和外圈10之间，保持架30包括沿轴向延伸的过 梁部33，用于周向W引导和分隔多个滚动体40，过梁部33周向间隔以形成兜孔35，滚动体40则位于过梁部33之间的兜孔35内。
由于分体式调心滚子轴承100的分体设置，保持架30通常还包括卡接部34，卡接部34位于过梁部33的轴向外侧且朝内圈20的方向延伸，卡接部34可以抵挡于滚动体40的轴向外侧以防止滚动体40沿轴向A脱落。
进一步地，第一锁紧环51或第二锁紧环52均位于各列滚动体40的轴向外侧，用于周向锁紧第一内圈21和第二内圈22。
其中，第一锁紧环51和第二锁紧环52沿径向R位于内圈20和外圈10之间，第一锁紧环51和第二锁紧环52的轴向外侧可以分别短于或平齐于第一内圈21和第二外圈12的轴向外侧，同时，第一锁紧环51和第二锁紧环52分别位于第一保持架31和第二保持架32的卡接部34的径向内侧，并与卡接部34在轴向A上重叠，即锁紧环50与保持架30的卡接部34在径向R上堆叠设置。
通过锁紧环50与保持架30的径向堆叠设置，在不改变整体式调心滚子轴承周围其他结构的情况下，例如，分体式调心滚子轴承100的轴向A和径向R尺寸都不变的情况下，无需牺牲滚动体40的轴向A长度，保证了分体式调心滚子轴承100的承载能力。
在一些实施例中，如图3所示，滚动体40的轴向外侧包括第一抵接面41；锁紧环50的轴向内侧包括第二抵接面53，其中，第二抵接抵接面53与第一抵接抵接面41相匹配，且第一抵接面41和第二抵接面53为平面或弧形面。
当第一抵接面41和第二抵接面53均为平面时，第二抵接面53可以与第一抵接面41平行。当第一抵接面41和第二抵接面53均为弧形面时，第一抵接面41和第二抵接面53可以为相互匹配的凸形弧面和凹形弧面。
通过滚动体40的第一抵接面41和锁紧环50的第二抵接面53的形状相匹配设置，充分利用轴向A上的空间，使锁紧环50与滚动体40的轴向间隙减小，锁紧环50与滚动体40在轴向A上布置更加紧凑，在保证分体式调心滚子轴承100承载能力的同时，无需增加分体式调心滚子轴承100 的轴向长度。此外，在滚动体40滚动过程中，滚动体40与锁紧环50可以通过面接触，增大了接触面积，避免了滚动体40与锁紧环50之间通过角面或棱面接触产生的较大的摩擦力，延长了使用寿命，另外，锁紧环50与滚动体40的间隙减小，可限制滚动体40的轴向移动及轴向脱落。
在一些实施例中，如图2所示，过梁部33位于滚动体40的节圆的径向外侧，滚动体40的节圆是指滚动体的中心所构成的圆。
由此可知，过梁部33位于滚动体40节圆的径向外侧，使得保持架30整体沿径向R朝远离内圈20的方向外移，一方面，保持架30的卡接部34与锁紧环50径向堆叠，充分利用径向空间，减小轴向空间的堆叠；另一方面，兜孔35沿周向上的宽度可以减小，以及过梁部33会因为保持架30位于滚动体40的节圆的径向外侧置，其充分利用了滚动体与滚动体之间的间隙沿着径向外侧不断增加的特点，在不损失过梁部33厚度的情况下，滚动体与滚动体之间的间隙可以尽可能的减少，从而增加滚动体40的数量，如此可以在周向W上可以增加滚动体40的数量，与同尺寸的原有整体式调心滚子轴承相比，该结构的分体式调心滚子轴承100增加了整体的承载能力。
在一些实施例中，卡接部34的轴向内侧设置有卡勾36；滚动体40的轴向外侧设置有卡槽42；其中，滚动体40可以由径向内侧朝径向外侧挤入兜孔35，同时轴向挤压卡接部34，使卡接部34弹性变形，待卡勾36卡入卡槽42内后，卡接部34回弹，实现滚动体40与保持架30的预安装。
由于调心滚子轴承的分体式结构，在实际安装的过程中，滚动体40需要和保持架30组件预安装在一起后，形成保持架30和滚动体40组件，才能更方便的在现场进行分体式调心滚子轴承100的安装，因此，保持架30的卡接部34位于滚动体40的轴向外侧，通过卡接部34的卡勾36与滚动体40的卡槽42的卡接，在保持架30整体径向外移时，避免滚动体40与保持架30预组装时沿轴向和径向脱落。
进一步地，卡接部34可以沿轴向弹性形变，卡勾36可以是朝径向外侧弯曲的钩状结构，也可以是朝径向外侧逐渐增大的楔形结构，卡槽42 可以是位于滚动体40的第一抵接面41上的圆形槽，在滚动体40滚动时，卡勾36可以相对于圆形卡槽42的内壁滑动，以避免卡勾36脱离卡槽42，卡勾36和卡槽42的卡接方式使滚动体40和保持架30的预安装更简单方便。
由上述内容可知，分体式调心滚子轴承100分为相同的两部分，如图4所示，分体式调心滚子轴向100分为相同的上半部分和下半部分，且上半部分和下半部分均具有两列滚动体40。在一些实施例中，上半部分的保持架30可以是分体式保持架，即每列滚动体40具有独立的第一保持架31，两列第一保持架31的轴向内侧相互抵接。同理，下半部分的保持架30也可以是分体式保持架，即每列滚动体40具有独立的第二保持架32，两列第二保持架32的轴向内侧相互抵接。
在该实施例中，分体式的保持架30的过梁部33与外圈10滚道间隙设置，且保持架30的卡接部34的径向内侧用于与锁紧环50的径向外侧抵接，使得保持架30由锁紧环50引导。
在另一些实施例中，如图5和图6所示，保持架30还可以包括连接部38，连接部38用于连接两个第一保持架31(或两个第二保持架32)，使得两个第一保持架31(或两个第二保持架32)一体成型，两列滚动体40共用一个保持架30，如此可以减小保持架30的组件的数量，避免保持架30或滚动体40散落，且便于安装和组装。
同时，连接部38可以使两列滚动体40在轴向上间隔，位于滚动体40轴向内侧的连接部38与位于滚动体40轴向外侧的卡接部34共同限制滚动体40的轴向移动。进一步地，连接部38的沿径向R的厚度可以大于过梁部33的厚度。其主要目的是为了更好的在分体式调心滚子轴承100运转时控制滚动体40的偏摆角度。
此外，在具有连接部38的一体成型的保持架30的调心滚子轴承中，保持架30可以为外圈10滚道引导的结构形式，即连接部38与外圈10滚道保持较小的径向间隙，而保持架30的内径(卡接部34)需要和锁紧环50之间保持较大的间隙。
由此可知，通过选择保持架30的分体式或一体式结构，，以适应不 同的使用环境的需求，增加了分体式调心滚子轴承100的适配性，且使保持架30能够更好的对滚动体40进行修正。
需要说明的是，一体式保持架30通过连接部38由外圈10引导，分体式保持架30通过卡接部34由锁紧环50引导，上述实施例只是示例性的，并非用以限定本公开的保护范围。在其他一些实施例中，分体式保持架30也可以由外圈10引导，一体式保持架30也可以通过卡接部34由锁紧环50引导。
在一些实施例中，锁紧环50可以与内圈20是两个独立的个体，锁紧环50也可以与内圈20一体成型。在锁紧环50与内圈20一体或分体设置时，第一锁紧环51和第二锁紧环52之间均可以通过紧固件60连接，实现第一内圈21和第二内圈22的锁紧。
在一个实施例中，第一锁紧环51的端部可以设置有径向R凹陷的安装缺口37，安装缺口37处设置有第一孔(图中未显示)，第二锁紧环52的端部设置第二孔(图中未显示)，紧固件60(例如螺栓或螺钉)可以通过安装缺口37的第一孔拧入第二孔内，实现第一锁紧环51和第二锁紧环52的固定连接。
此外，可以在第一锁紧环51的两个端部均设置安装缺口37，在第二锁紧环52的两个端部设置两个对应的第二孔。也可以在第一锁紧环51的一端设置安装缺口37，另一端设置第二孔，第二锁紧环52的一端也设置安装缺口37，另一端设置第二孔，第一锁紧环51的安装缺口37与第二锁紧环52的第二孔对接，第一锁紧环51的第二孔与第二锁紧环52的安装缺口37对接，实现力的中心对称平衡。
在另一个实施例中，第一锁紧环51的端部和第二锁紧环52的端部也可以通过销孔的过盈配合实现第一锁紧环51和第二锁紧环52的固定连接。其中，销孔的位置与安装缺口37和第二孔的位置设置同理，在此不再追溯。
在一些实施例中，当锁紧环50与内圈20分体设置时；其中，内圈20的径向外侧还可以设置有环形槽23，环形槽23使锁紧环50无法轴向移动，避免锁紧环50的轴向脱落，导致第一内圈21和第二内圈22的散落。
此外，锁紧环50通过过盈配合卡入环形槽23内，且锁紧环50沿周向覆盖第一内圈21和第二内圈22的端面接触处，如此，无需使用螺栓或螺钉等紧固件，便可以实现第一内圈21和第二内圈22之间的快速锁紧连接，节省安装步骤和时间。

Claims (10)

  1. 一种分体式调心滚子轴承(100)，其特征在于，包括：
    外圈(10)；
    内圈(20)，所述内圈(20)沿轴向(A)的宽度与外圈(10)相等，所述内圈(20)包括沿周向(W)分体的第一内圈(21)和第二内圈(22)；
    保持架(30)，沿径向(R)位于所述内圈(20)和所述外圈(10)之间，所述保持架(30)包括过梁部(33)和卡接部(34)，所述卡接部(34)位于所述过梁部(33)的轴向外侧，且朝所述内圈(20)的方向延伸；
    滚动体(40)，位于所述保持架(30)的兜孔(35)内；以及
    锁紧环(50)，位于所述滚动体(40)的轴向外侧，用于周向(W)锁紧所述第一内圈(21)和所述第二内圈(22)，
    其中，所述锁紧环(50)位于所述保持架(30)的卡接部(34)的径向内侧，且与所述卡接部(34)在轴向上重叠。
  2. 根据权利要求1的分体式调心滚子轴承(100)，其特征在于，
    所述滚动体(40)的轴向外侧包括第一抵接面(41)；
    所述锁紧环(50)的轴向内侧包括第二抵接面(53)，
    其中，所述第二抵接面(53)与所述第一抵接面(41)相匹配，且所述第一抵接面(41)和所述第二抵接面(53)为平面或弧形面。
  3. 根据权利要求1的分体式调心滚子轴承(100)，其特征在于，
    所述过梁部(33)位于所述滚动体(40)的节圆的径向外侧。
  4. 根据权利要求1的分体式调心滚子轴承(100)，其特征在于，
    所述卡接部(34)的轴向内侧设置有卡勾(36)；
    所述滚动体(40)的轴向外侧设置有卡槽(42)；
    其中，所述滚动体(40)由径向内侧朝径向外侧挤入所述兜孔(35)，使所述卡接部(34)弹性变形并回弹后，所述卡勾(36)卡入所述卡槽(42)内，实现所述滚动体(40)与所述保持架(30)的预安装。
  5. 根据权利要求1的分体式调心滚子轴承(100)，其特征在于，
    所述保持架(30)还包括连接部(38)，所述连接部(38)位于所述过梁部(33)的轴向内侧，用于连接所述过梁部(33)，其中，所述连接部(38)的沿径向(R)的厚度大于所述过梁部(33)的厚度。
  6. 根据权利要求1的分体式调心滚子轴承(100)，其特征在于，
    所述过梁部(33)与所述外圈(10)滚道间隙设置，且所述卡接部(34)的径向内侧与所述锁紧环(50)的径向外侧抵接，使得所述保持架(30)由所述锁紧环(50)引导。
  7. 根据权利要求1的分体式调心滚子轴承(100)，其特征在于，
    所述锁紧环(50)包括沿周向分体的第一锁紧环(51)和第二锁紧环(52)，所述第一锁紧环(51)和所述第二锁紧环(52)之间通过紧固件(60)连接，实现所述第一内圈(21)和所述第二内圈(22)的锁紧。
  8. 根据权利要求1的分体式调心滚子轴承(100)，其特征在于，
    所述锁紧环(50)与所述内圈(20)分体设置；
    其中，所述内圈(20)的径向外侧设置有环形槽(23)，所述锁紧环(50)通过过盈配合卡入所述环形槽(23)内，且所述锁紧环(50)沿周向覆盖所述第一内圈(21)和所述第二内圈(22)的端面抵接处，实现所述第一内圈(21)和所述第二内圈(22)的锁紧连接。
  9. 根据权利要求1的分体式调心滚子轴承(100)，其特征在于，
    所述锁紧环(50)与所述内圈(20)一体成型。
  10. 根据权利要求1的分体式调心滚子轴承(100)，其特征在于，
    所述保持架(30)包括沿周向分体设置的第一保持架(31)和第二保持架(32)；和
    所述外圈(10)包括沿周向分体设置的第一外圈(11)和第二外圈(12)。
PCT/CN2023/098533 2023-06-06 2023-06-06 分体式调心滚子轴承 Ceased WO2024250167A1 (zh)

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