WO2024040710A1 - 一种台阶式外径自密封双列圆锥滚子轴承 - Google Patents

一种台阶式外径自密封双列圆锥滚子轴承 Download PDF

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Publication number
WO2024040710A1
WO2024040710A1 PCT/CN2022/124605 CN2022124605W WO2024040710A1 WO 2024040710 A1 WO2024040710 A1 WO 2024040710A1 CN 2022124605 W CN2022124605 W CN 2022124605W WO 2024040710 A1 WO2024040710 A1 WO 2024040710A1
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WO
WIPO (PCT)
Prior art keywords
outer ring
sealing
groove
wall
tapered roller
Prior art date
Application number
PCT/CN2022/124605
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English (en)
French (fr)
Inventor
田佩来
宋世勇
于长鑫
谭剑光
马忠超
顿丽华
夏克博
宫赫成
石佳艺
宋涛
张策
Original Assignee
瓦房店轴承集团有限责任公司
瓦房店轴承集团国家轴承工程技术研究中心有限公司
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Publication of WO2024040710A1 publication Critical patent/WO2024040710A1/zh

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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
    • F16C19/38—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 two or more rows of rollers
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members

Definitions

  • the utility model belongs to the technical field of rail transit bearing manufacturing, and specifically relates to a stepped outer diameter self-sealing double row tapered roller bearing.
  • the outer ring of self-sealing double-row tapered roller bearings used in rail transit adopts a traditional design.
  • the size of the outer diameter of the outer ring is uniform.
  • the outer diameter boss of the seal assembly needs to be press-fitted. to the sealing groove of the outer ring.
  • this utility model is to provide a stepped outer diameter self-sealing double-row tapered roller bearing, which reserves a deformation space for the press-fitting of the bearing sealing component and ensures the bearing size after press-fitting.
  • a stepped outer diameter self-sealing double row tapered roller bearing including an inner ring, an outer ring, a cage and double row rollers, and the double row rollers are retained by The frame is held between the inner ring and the outer ring.
  • Seal grooves for assembling sealing components are respectively provided on both sides of the inner wall of the outer ring. Grooves that are concave along the radial direction are provided on both sides of the outer wall of the outer ring. Each side The grooves and sealing grooves are set correspondingly, and the axial length of the groove is greater than the axial length from the sealing groove to the corresponding outer ring end face.
  • the groove extends from the end of the outer wall of the outer ring to the middle of the outer wall of the outer ring, and the grooves on both sides of the outer wall of the outer ring are symmetrically arranged.
  • a chamfer is provided at the connection between the outer wall of the outer ring and the end surfaces on both sides of the outer ring, and the groove extends from the chamfered end to the middle of the outer wall of the outer ring.
  • the groove is arranged along an annular circle, and the annular shape formed by the groove is coaxial with the annular shape formed by the outer wall of the outer ring.
  • the axial length from the sealing groove to the corresponding outer ring end face is the axial length from the first side wall of the sealing groove to the corresponding outer ring end face; the corresponding outer ring end face is the outer ring end face on the side close to the sealing groove. ;
  • the first side wall of the sealing groove is the side wall of the sealing groove away from the end face of the corresponding outer ring.
  • the axial length of the groove is 13-16mm.
  • the radial concave height of the groove is 0.15-0.3mm.
  • a central part between the grooves on both sides is a central part, and the grooves on both sides are connected with the central part to form a complete outer wall of the outer ring.
  • the groove and the central part have a stepped structure.
  • groove and the central part are transitioned by a slope.
  • the utility model compensates for the deformation of the outer ring during the pressing process by arranging grooves on the outer wall of the outer ring, so that the deformation caused by the pressing will not affect the size between the outer diameter of the bearing and the bearing seat.
  • the fit avoids the change of the fit between the bearing outer diameter and the bearing seat into an interference fit, which facilitates the installation of the bearing and also reduces the risk of bearing temperature rise.
  • Figure 1 is a partial structural schematic diagram of a double-row tapered roller bearing with evenly arranged outer walls in the prior art.
  • Figure 2 is an enlarged view of part of the structure of the stepped outer diameter self-sealing double row tapered roller bearing of the present invention.
  • Figure 3 is a schematic structural diagram of the bearing after press-fitting according to the present invention.
  • Figure 4 is a schematic structural diagram of a stepped outer diameter self-sealing double row tapered roller bearing.
  • a stepped outer diameter self-sealing double-row tapered roller bearing includes an inner ring, an outer ring, a cage and double-row rollers.
  • the double-row rollers are retained in the inner ring and outer ring by the cage.
  • sealing grooves for assembling sealing components are respectively provided on both sides of the inner wall of the outer ring.
  • Grooves that are concave in the radial direction are provided on both sides of the outer wall of the outer ring.
  • the grooves and sealing grooves on each side are provided correspondingly.
  • the axial length of the groove is greater than the axial length from the seal groove to the corresponding outer ring end face, that is, D is greater than D1.
  • the groove extends from the end of the outer wall of the outer ring to the middle of the outer wall of the outer ring, and the grooves on both sides of the outer wall of the outer ring are symmetrically arranged.
  • a chamfer is provided at the connection between the outer wall of the outer ring and the end surfaces on both sides of the outer ring, and the groove extends from the chamfered end to the middle of the outer wall of the outer ring.
  • the groove is arranged along an annular shape, and the annular shape formed by the groove is coaxial with the annular shape formed by the outer wall of the outer ring.
  • the uniform size of the groove ensures that the deformation zone with thickening is uniform in size and can fit well with the bearing seat.
  • the axial length from the sealing groove to the corresponding outer ring end face is the axial length from the first side wall of the sealing groove to the corresponding outer ring end face; the corresponding outer ring end face is the one close to the sealing groove.
  • side outer ring end face; the first side wall of the sealing groove is the side wall of the sealing groove away from the corresponding outer ring end face.
  • the axial length D of the groove is 15.5 mm.
  • the radial concave height H of the groove is 0.2 mm. That is, the grooves on both sides are concave 0.2mm relative to the central part, and the radial concave height of the groove is greater than the increased outer diameter of the deformation zone.
  • a central portion is between the grooves on both sides, and the grooves on both sides are connected and continued with the central portion to form a complete outer wall of the outer ring.
  • the groove and the central portion have a stepped structure.
  • the central part is not in the press-fit edge area and will not increase in size. Therefore, the size of the central part is consistent with the product specifications and protrudes from the grooves on both sides.
  • the groove and the central portion are transitioned through a bevel to form a chamfer to avoid stress concentration.
  • This utility model adds grooves 15.5mm long and 0.2mm deep at both ends of the outer ring outer diameter, and the grooves and the outer diameter of the outer ring form a stepped structure. That is, 0.2mm deep and 15.5mm long grooves are reserved at both ends of the outer diameter as a deformation buffer area when the bearing is press-fitted, which overcomes the long length that often occurs at both ends of the outer diameter of traditional double-row tapered roller bearings due to press-fitting.
  • the outer diameter of the deformation zone usually increases by 0.1 to 0.15 mm.
  • the groove length of 15.5mm makes the groove length longer than the length of the deformation zone to avoid the overlap of the groove chamfer and the convex area of the deformation zone to form a stress concentration area and cause fracture; the depth of the 0.2mm groove is much larger than the outer diameter deformation, making the press fit The resulting deformation will not affect the dimensional fit between the bearing outer diameter and the bearing seat, avoiding the transformation of the bearing outer diameter and the bearing seat into an interference fit, which facilitates the installation of the bearing and reduces the risk of bearing temperature rise. Since the groove area completely covers the deformation area, the outer ring after pressing is first convex from the end and then concave at the groove (as shown in Figure 3). The convex part a is pressed by the groove. It is formed by deformation after installation, and the concave part b is formed by the original groove at the groove that has not been deformed by press installation.
  • first and second are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of indicated technical features. Therefore, features defined as “first” and “second” may explicitly or implicitly include at least one of these features.
  • “plurality” means at least two, such as two, three, etc., unless otherwise clearly and specifically limited.
  • connection In this utility model, unless otherwise expressly stipulated and limited, the terms “installation”, “connection”, “connection”, “fixing” and other terms should be understood in a broad sense. For example, it can be a fixed connection or a detachable connection. Connection, or integration; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be an internal connection between two elements or an interaction between two elements, unless otherwise Clear limits.
  • connection or integration
  • connection can be a mechanical connection or an electrical connection
  • it can be a direct connection or an indirect connection through an intermediate medium
  • it can be an internal connection between two elements or an interaction between two elements, unless otherwise Clear limits.
  • specific meanings of the above terms in the present invention can be understood according to specific circumstances.
  • the first feature "on” or “below” the second feature may be that the first and second features are in direct contact, or the first and second features are in direct contact through an intermediate medium. indirect contact.
  • the terms “above”, “above” and “above” the first feature is above the second feature may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is higher in level than the second feature.
  • "Below”, “below” and “beneath” the first feature to the second feature may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature has a smaller horizontal height than the second feature.

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

Abstract

一种台阶式外径自密封双列圆锥滚子轴承，包括内圈（1）、外圈（2）、保持架（3）和双列滚子（4），双列滚子通过保持架保持在内圈和外圈之间，外圈内壁的两侧分别设置有用于装配密封组件（5）的密封槽（6），外圈外壁的两侧分别设置有沿径向内凹的凹槽（7），每侧的凹槽和密封槽对应设置，凹槽的轴向长度大于密封槽到相应外圈端面的轴向长度，两侧凹槽之间为中心部（8），两侧凹槽与中心部连接延续形成完整的外圈外壁，凹槽与中心部为台阶式结构。通过在外圈设置凹槽，弥补外圈在压装过程产生的变形，使变形不会影响到轴承外径与轴承座之间的配合，避免轴承外径与轴承座配合转变为过盈配合，便于轴承安装，减少温升风险。

Description

一种台阶式外径自密封双列圆锥滚子轴承 技术领域
本实用新型属于轨道交通轴承制造技术领域，具体涉及一种台阶式外径自密封双列圆锥滚子轴承。
 背景技术
现有技术中应用于轨道交通的自密封双列圆锥滚子轴承外圈采用传统式设计，外圈外径的尺寸均匀一致，在轴承密封组成压装时需将密封组成外径凸台压装至外圈的密封牙口沟槽处。
 技术问题
因压装原因外径两端部位经常出现形变，形变区外径尺寸增大，致使轴承外径与轴承座配合由间隙配合变为过盈配合，为轴承安装带来困难，同时也为后续的轴承使用带来温升隐患。
 技术解决方案
根据上述现有技术存在的缺陷，本实用新型的目的是提供一种台阶式外径自密封双列圆锥滚子轴承，为轴承密封组成压装预留出变形空间，保证压装后的轴承尺寸。
为实现上述目的，本实用新型所采用的技术方案为：一种台阶式外径自密封双列圆锥滚子轴承，包括内圈、外圈、保持架和双列滚子，双列滚子通过保持架保持在内圈和外圈之间，所述外圈内壁的两侧分别设置有用于装配密封组件的密封槽，外圈外壁的两侧分别设置有沿径向内凹的凹槽，每侧的凹槽和密封槽对应设置，凹槽的轴向长度大于密封槽到相应外圈端面的轴向长度。
进一步地，所述凹槽由外圈外壁端部向外圈外壁中部延伸，外圈外壁的两侧凹槽对称设置。
进一步地，所述外圈外壁与外圈两侧端面的连接处设置倒角，凹槽由倒角的端部向外圈外壁中部延伸。
进一步地，所述凹槽沿环形设置一周，凹槽形成的环形与外圈外壁形成的环形同轴。
进一步地，密封槽到相应外圈端面的轴向长度为密封槽的第一侧壁到相应外圈端面的轴向长度；所述的相应外圈端面为该密封槽靠近的一侧外圈端面；所述密封槽的第一侧壁为密封槽远离相应外圈端面的侧壁。
进一步地，所述凹槽的轴向长度为13-16mm。
进一步地，所述凹槽的径向内凹高度为0.15-0.3mm。
进一步地，两侧凹槽之间为中心部，两侧凹槽与中心部连接延续形成完整的外圈外壁，所述的凹槽与中心部为台阶式结构。
进一步地，所述凹槽与中心部之间通过斜面过渡。
 有益效果
本实用新型的有益效果为：本实用新型通过在外圈外壁设置凹槽，弥补外圈在压装过程产生的变形，使压装产生的变形不会影响到轴承外径与轴承座之间的尺寸配合，避免了轴承外径与轴承座配合转变为过盈配合，便于轴承的安装，也减少了轴承温升风险。
 附图说明
图1为现有技术中外壁均匀设置的双列圆锥滚子轴承部分结构示意图。
图2为本实用新型台阶式外径自密封双列圆锥滚子轴承部分结构放大图。
图3为本实用新型压装后的轴承部分结构示意图。
图4为台阶式外径自密封双列圆锥滚子轴承结构示意图。
图中：1、内圈， 2、外圈， 3、保持架， 4、滚子， 5、密封组件， 6、密封槽， 7、凹槽， 8、中心部。
D、凹槽轴向长度，D1、密封槽到相应外圈端面的轴向长度 ，H、凹槽径向内凹高度。
a、压装后凹槽内凸起部分， b、压装后凹槽内内凹部分。
 本发明的最佳实施方式
为使本实用新型的上述目的、特征和优点能够更加明显易懂，下面结合附图对本实用新型的具体实施方式做详细的说明。在下面的描述中阐述了很多具体细节以便于充分理解本实用新型。但是本实用新型能够以很多不同于在此描述的其它方式来实施，本领域技术人员可以在不违背本实用新型内涵的情况下做类似改进，因此本实用新型不受下面公开的具体实施例的限制。
参见附图2-4，一种台阶式外径自密封双列圆锥滚子轴承，包括内圈、外圈、保持架和双列滚子，双列滚子通过保持架保持在内圈和外圈之间，所述外圈内壁的两侧分别设置有用于装配密封组件的密封槽，外圈外壁的两侧分别设置有沿径向内凹的凹槽，每侧的凹槽和密封槽对应设置，凹槽的轴向长度大于密封槽到相应外圈端面的轴向长度，即D大于D1。
 本发明的实施方式
在其中一个实施例中，所述凹槽由外圈外壁端部向外圈外壁中部延伸，外圈外壁的两侧凹槽对称设置。
在其中一个实施例中，所述外圈外壁与外圈两侧端面的连接处设置倒角，凹槽由倒角的端部向外圈外壁中部延伸。
在其中一个实施例中，所述凹槽沿环形设置一周，凹槽形成的环形与外圈外壁形成的环形同轴。凹槽的尺寸均匀确保性变厚的形变区尺寸均匀，能够与轴承座良好配合。
在其中一个实施例中，密封槽到相应外圈端面的轴向长度为密封槽的第一侧壁到相应外圈端面的轴向长度；所述的相应外圈端面为该密封槽靠近的一侧外圈端面；所述密封槽的第一侧壁为密封槽远离相应外圈端面的侧壁。
在其中一个实施例中，所述凹槽的轴向长度D为15.5mm。
在其中一个实施例中，所述凹槽的径向内凹高度H为0.2mm。即两侧凹槽相对于中心部内凹0.2mm，凹槽的径向内凹高度大于形变区增大的外径尺寸。
在其中一个实施例中，两侧凹槽之间为中心部，两侧凹槽与中心部连接延续形成完整的外圈外壁，所述的凹槽与中心部为台阶式结构。中心部不在压装的形边区，不会产生尺寸增大，因此中心部尺寸与产品规格保持一致并凸出于两侧凹槽。
在其中一个实施例中，所述凹槽与中心部之间通过斜面过渡，形成倒角，避免应力集中。
本实用新型在外圈外径两端增加了15.5mm长0.2mm深的凹槽，凹槽与外圈外径形成台阶式结构。即在外径两端预留了0.2mm深15.5mm长的凹槽作为轴承压装时的形变缓冲区域，克服了传统双列圆锥滚子轴承因压装原因外径两端部位经常出现的长为10～13mm的尺寸形变区，通常形变区外径尺寸增大0.1～0.15mm。15.5mm长度的凹槽使得凹槽长度长于形变区长度，避免凹槽倒角与形变区凸起区域重叠形成应力集中区，产生断裂；0.2mm凹槽深度远大于外径形变量，使压装产生的变形不会影响到轴承外径与轴承座之间的尺寸配合，避免了轴承外径与轴承座配合转变为过盈配合，便于轴承的安装，也减少了轴承温升风险。由于凹槽区域完全覆盖形变区域，压装后的外圈在凹槽处呈现由端部开始先凸起再内凹的结构（如图3所示），凸起部分a是由凹槽处压装后变形形成，内凹部分b是由凹槽处未经过压装变形的原始凹槽形成。
 工业实用性
在本实用新型的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本实用新型和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本实用新型的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本实用新型的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本实用新型中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系，除非另有明确的限定。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本实用新型中的具体含义。
在本实用新型中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
需要说明的是，当元件被称为“固定于”或“设置于”另一个元件，它可以直接在另一个元件上或者也可以存在居中的元件。当一个元件被认为是“连接”另一个元件，它可以是直接连接到另一个元件或者可能同时存在居中元件。本文所使用的术语“垂直的”、“水平的”、“上”、“下”、“左”、“右”以及类似的表述只是为了说明的目的，并不表示是唯一的实施方式。
以上列举的仅是本实用新型的最佳实施例。显然，本实用新型不限于以上实施例，还可以有许多变形。本领域的普通技术人员能从本实用新型公开的内容直接导出或联想到的所有变形，均应认为是本实用新型的保护范围。

Claims (8)

  1.  一种台阶式外径自密封双列圆锥滚子轴承，其特征在于：包括内圈、外圈、保持架和双列滚子，双列滚子通过保持架保持在内圈和外圈之间，所述外圈内壁的两侧分别设置有用于装配密封组件的密封槽，外圈外壁的两侧分别设置有沿径向内凹的凹槽，每侧的凹槽和密封槽对应设置，凹槽的轴向长度大于密封槽到相应外圈端面的轴向长度；两侧凹槽之间为中心部，两侧凹槽与中心部连接延续形成完整的外圈外壁，所述的凹槽与中心部为台阶式结构。
  2.  根据权利要求1所述的一种台阶式外径自密封双列圆锥滚子轴承，其特征在于：所述凹槽由外圈外壁端部向外圈外壁中部延伸，外圈外壁的两侧凹槽对称设置。
  3.  根据权利要求2所述的一种台阶式外径自密封双列圆锥滚子轴承，其特征在于：所述外圈外壁与外圈两侧端面的连接处设置倒角，凹槽由倒角的端部向外圈外壁中部延伸。
  4.  根据权利要求1所述的一种台阶式外径自密封双列圆锥滚子轴承，其特征在于：所述凹槽沿环形设置一周，凹槽形成的环形与外圈外壁形成的环形同轴。
  5.  根据权利要求1所述的一种台阶式外径自密封双列圆锥滚子轴承，其特征在于：密封槽到相应外圈端面的轴向长度为密封槽的第一侧壁到相应外圈端面的轴向长度；所述的相应外圈端面为该密封槽靠近的一侧外圈端面；所述密封槽的第一侧壁为密封槽远离相应外圈端面的侧壁。
  6.  根据权利要求1所述的一种台阶式外径自密封双列圆锥滚子轴承，其特征在于：所述凹槽的轴向长度为13-16mm。
  7.  根据权利要求1所述的一种台阶式外径自密封双列圆锥滚子轴承，其特征在于：所述凹槽的径向内凹高度为0.15-0.3mm。
  8.  根据权利要求1所述的一种台阶式外径自密封双列圆锥滚子轴承，其特征在于：所述凹槽与中心部之间通过斜面过渡。
PCT/CN2022/124605 2022-08-25 2022-10-11 一种台阶式外径自密封双列圆锥滚子轴承 WO2024040710A1 (zh)

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