WO2020113514A1 - 滚动轴承 - Google Patents

滚动轴承 Download PDF

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Publication number
WO2020113514A1
WO2020113514A1 PCT/CN2018/119534 CN2018119534W WO2020113514A1 WO 2020113514 A1 WO2020113514 A1 WO 2020113514A1 CN 2018119534 W CN2018119534 W CN 2018119534W WO 2020113514 A1 WO2020113514 A1 WO 2020113514A1
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WO
WIPO (PCT)
Prior art keywords
rolling
rolling bearing
rolling element
bearing
diameter
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Application number
PCT/CN2018/119534
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English (en)
French (fr)
Inventor
柴仲冬
莱纳施罗德
程涛
Original Assignee
舍弗勒技术股份两合公司
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Priority to PCT/CN2018/119534 priority Critical patent/WO2020113514A1/zh
Publication of WO2020113514A1 publication Critical patent/WO2020113514A1/zh

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    • 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
    • F16C19/49—Bearings with both balls and 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • 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
    • F16C33/38—Ball cages
    • F16C33/40—Ball cages for multiple rows of balls

Definitions

  • the invention relates to a rolling bearing.
  • the invention particularly relates to a rolling bearing capable of preventing slippage.
  • railway gauges When the load on the rolling bearing becomes smaller, there is a risk of slippage between the rolling element and the bearing ring of the rolling bearing.
  • railway gauges due to current differences in railway technical equipment in various countries, railway gauges generally have different gauges such as meter gauge, narrow gauge, standard gauge, and wide gauge. In this case, China uses standard rails, Russia uses wide rails, and Vietnam uses narrow rails. Therefore, for example, on the Eurasian train freight line or on the Southeast Asia train freight line, the train wheel pair needs to adapt to the changing track conditions. , The wheelset bearings on it also need to adapt to the changing conditions.
  • the existing wheelset bearings are generally double-row tapered roller bearings.
  • the load on the double-row tapered roller bearings deviates from the original center position, and the two rows of rolling elements are unevenly loaded, so the load is too small.
  • the rolling elements and the bearing rings of the rolling bearing are at risk of slipping, so the wheelset bearings may fail early.
  • the technical problem to be solved by the present invention is to provide a rolling bearing, especially an improved rolling bearing based on a tapered roller bearing, which can reduce the load it carries due to changes in operating conditions, or the load carried by, for example, Due to the deviation from the center position, there is no risk of slipping when the local load is too small, so the rolling bearing can also be used as a wheelset bearing to adapt to the railway track changing conditions.
  • a rolling bearing including an outer ring, an inner ring and a first rolling body located between the outer ring and the inner ring.
  • the first rolling body is designed as a tapered roller, wherein the rolling bearing further has at least one A second rolling element between the outer ring and the inner ring, wherein the first rolling element has a first axis of rotation and the second rolling element has a second axis of rotation, wherein at least one of the same axial position of the rolling bearing
  • the diameter of the second rolling element in the section perpendicular to the second axis of rotation is larger than the diameter of the first rolling element in the section perpendicular to the axis of first rotation.
  • the rolling bearing can be a single-row bearing, a double-row bearing or a multi-row bearing.
  • the first self-rotation axis of the first rolling body is the ideal self-rotation rotation axis of the tapered roller, and is also its middle axis. That is to say, in the plane where the rotation axis of the rolling bearing and the center axis of the first rolling body are located, the angle between the first self-rotation axis and the outer ring of the bearing is equal to the angle between the first self-rotation axis and the inner ring of the bearing.
  • the second self-rotation axis of the second rolling body is an ideal self-rotation self-rotation axis of the second rolling body.
  • the angle between the second self-rotation axis and the outer ring of the bearing is equal to the angle between the second self-rotation axis and the inner ring of the bearing.
  • the center of the second rolling element refers to the center of the ball sphere; when the second rolling element is a drum roller or a tapered roller, the center of the second rolling element refers to The central axis of the second rolling element.
  • the first spin axis of the first rolling element and the second spin axis of the second rolling element in the same row can intersect at one point.
  • At least one second rolling element replaces part of the rolling elements in the roller bearing including only the first rolling element.
  • the second rolling element in the same row as the first rolling element
  • the self-rotation axis is compared with the self-rotation axis of the first rolling element by a point.
  • the geometry of the second rolling element is designed in this way.
  • the gap between the second rolling element and the outer and inner rings of the bearing is smaller than that of the first rolling element with the original bearing clearance maintained.
  • the gap between the outer ring and the inner ring, that is, at the same axial position of the rolling bearing, the diameter of the second rolling body in the section perpendicular to the second axis of rotation is larger than that of the first rolling body perpendicular to the first axis of rotation
  • the diameter of the second rolling element in a section perpendicular to the second axis of rotation is larger than the diameter of the first rolling element in a section perpendicular to the first axis of rotation Large 3 to 50 ⁇ m.
  • the difference between the diameters in the above two sections is between 5 and 30 ⁇ m.
  • the second rolling element is designed as a ball.
  • the balls are, for example, steel balls.
  • the balls When the bearing load is small, the balls fully contact the inner ring and the outer ring of the rolling bearing, and drive a row of rolling elements with lighter load. Since the balls roll purely and the friction is small, this embodiment can be adapted to higher-speed rolling bearings.
  • the diameter of the ball in the section perpendicular to the rotation axis of its self-rotation, that is, the second self-rotation axis refers to the connection line between the two contact points when the inner ring and the outer ring of the ball and rolling bearing come into contact The distance in the direction.
  • the distance of the above-mentioned contact point in the direction of its connecting line is larger than the diameter of the first rolling body in a section perpendicular to the first axis of rotation.
  • the numerical value for increasing the size is preferably between 3 and 50 ⁇ m, especially between 5 and 30 ⁇ m.
  • the inner ring has a rib for axially stopping the first rolling body and the second rolling body, wherein the rib has a first contact surface for stopping the first rolling body and a second for stopping the second rolling body
  • the second contact surface of the rolling element are respectively two circumferential sections adjacent to each other along the radial direction of the bearing on the inner peripheral surface of the rib.
  • the second contact surface can be designed as a circumferential section extending along a straight line, or a circumferential section extending along an arc, wherein the arc of the arc matches the diameter of the ball.
  • the size of the rib is increased along the radial direction of the bearing, so that the balls are guided by the inner ring rib, and the rotation center of the ball rotation is in contact with the large rib.
  • this design does not change the contact characteristics of the existing first rolling body, that is, the tapered roller and the rib.
  • the second rolling body is a drum roller.
  • the original design can be used for the inner ring, and there is no need to separately process the rib part.
  • the diameters of the two axial end surfaces of the drum roller are different, that is, the second rolling body is substantially frusto-conical, but its generatrix is an arc protruding radially outward.
  • the maximum diameter of the second rolling element is 3-50 ⁇ m larger than the diameter dimension of the first rolling element in the adjacent position at the same axial position of the bearing.
  • the position with the largest diameter difference at the same axial position can be designed according to the actual load distribution, and is normally designed to be close to the large-diameter end of the second rolling element. For example, the distance between the position of the largest diameter difference and the large end face of the second largest diameter end is 1/3 of the length of the entire second rolling element.
  • the second rolling element is a frusto-conical roller.
  • the inner ring can also adopt the original design without having to process the rib part separately.
  • the diameter of the second rolling element in each section perpendicular to the second axis of rotation is larger than the diameter of the first rolling element in the corresponding section perpendicular to the first axis of rotation, the difference The value is between 3 and 50 ⁇ m.
  • the second rolling body is partially provided with a protrusion protruding in the radial direction of the rolling body.
  • the axial ends of the second rolling element are respectively provided with protrusions protruding in the radial direction.
  • the size of the protrusion can be set according to the operating conditions so that the two sections of the second rolling element with the protrusion also form two truncated cones, and any two new truncated cones
  • the diameter of a radial section is 3-50um larger than the diameter of the radial section of the corresponding axial position of the original truncated cone.
  • the rolling bearing is a double-row rolling bearing or a multi-row rolling bearing, and each row of the rolling bearing has a second rolling body.
  • the rolling bearing is a double-row rolling bearing or a multi-row rolling bearing, and the number of second rolling bodies in each row of the rolling bearing is not equal.
  • the number of the second rolling elements and the circumferential distribution position in each row of rolling elements are determined according to the specific working conditions of the rolling bearing, especially according to the load conditions under various working conditions.
  • FIG. 1 is a half cross-sectional view of a rolling bearing according to a first preferred embodiment of the present invention
  • FIG. 2 is a partially enlarged view of the rolling bearing according to FIG. 1,
  • FIG. 3 is a half cross-sectional view of the rolling bearing according to FIG. 1 taken along another cross-section,
  • FIG. 5 is a schematic view of a second rolling element of a rolling bearing according to a third preferred embodiment of the present invention.
  • FIG. 6 is a half cross-sectional view of a double-row tapered roller bearing according to the related art.
  • This double row tapered roller bearing can be used as a wheelset bearing and includes an outer ring 10, two adjacently arranged inner rings 50, two plastic cages 30, an intermediate ring 40, and two rows of tapered rollers 20 .
  • FIG. 1 shows a half cross-sectional view of a rolling bearing according to a first preferred embodiment of the present invention.
  • the rolling bearing includes an outer ring 1, two adjacent inner rings 5, two plastic cages 3, an intermediate ring 4, and two rows of rolling elements.
  • Each row of rolling bodies includes a first rolling body and a second rolling body.
  • the first rolling element is designed as a tapered roller (marked as 2 in FIG. 3), and the second rolling element is designed as a steel ball 6 in this embodiment.
  • three steel balls 6 are evenly arranged in the circumferential direction, and the remaining rolling elements are tapered rollers 2.
  • the diameter of the steel ball 6 is designed such that the distance between the contact point of the steel ball 6 and the inner ring 5 and the outer ring 1 is 3 to 50 ⁇ m larger than the diameter of the tapered roller 2 at the same axial position.
  • the difference The value is between 5 and 30 ⁇ m.
  • the steel ball 6 is stopped by the outer peripheral surface of the inner ring 5 and the inner peripheral surface of the outer ring 1 at one end, and at the other end by the rib of the inner ring 5 at the large end surface of the tapered roller 2 Therefore, it is necessary to design the diameter of the steel ball 6 so that the steel ball 6 can contact the rib of the inner ring 5.
  • FIG. 2 shows a partially enlarged view of area A in FIG. 1. It can be seen that on the large ribs of the inner ring 5, that is, on the ribs at both axial ends of the rolling bearing in FIG. 3, there is a tapered roller contact surface 51 for the axial stop of the tapered roller 2, that is, the first contact surface.
  • the outer diameter of the large rib is increased compared to the prior art in FIG. 6 to provide a steel ball contact surface 53 for axially stopping the steel ball 6 on the radially outer side of the tapered roller contact surface 51, ie The second contact surface. Thereby, the large rib can guide the movement of the steel ball 6.
  • the steel ball contact surface 53 is designed as a concave surface to match the shape of the steel ball 6.
  • the tapered roller contact surface 51 and the steel ball contact surface 53 form an oil reservoir 52.
  • FIG. 3 shows a half-section view of the rolling bearing according to FIG. 1 taken along a further section. It can be clearly seen that the tapered roller 2 is in dynamic contact with the large rib of the inner ring 5 as in the existing design according to FIG. 6. At this time, the oil storage tank 52 can store a certain amount of lubricating grease to achieve a lubricating effect.
  • Fig. 4 shows a schematic view of a second rolling element of a rolling bearing according to a second preferred embodiment of the invention.
  • the second rolling element 6' is substantially frusto-conical, and the left side is the large-diameter end and the right side is the small-diameter end in the illustration.
  • the truncated cone generatrix of the second rolling element 6' is designed as a convex arc line extending radially outward as shown.
  • the diameter of the second rolling element 6' is larger than the diameter of the tapered roller 2 in the same axial position by 3 to 50 [mu]m.
  • the position with the largest diameter difference that is, the position as shown in Figure ⁇ Dmax can be designed according to the actual load distribution, and is generally designed to be close to the large diameter end.
  • the position of ⁇ Dmax is about 1/3 of the length of the second rolling element 6'from the end face of the large-diameter end.
  • Fig. 5 shows a schematic view of a second rolling element of a rolling bearing according to a third preferred embodiment of the invention.
  • the second rolling element 6' is substantially frusto-conical, and its axial ends have protrusions protruding in the radial direction, namely a first flange 61" and a second flange 62".
  • the first flange 61" and the second flange 62" are both frusto-conical, and at the same axial position of the rolling bearing, the outer diameters of the first flange 61" and the second flange 62" are compared to the same axial position
  • the diameter of the tapered roller increases by 3-50 ⁇ m, depending on the needs of the working conditions.

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

Abstract

一种滚动轴承，包括外圈（1）、内圈（5）和位于外圈（1）和内圈（5）之间的第一滚动体（2），第一滚动体（2）被设计为圆锥滚子，其中，滚动轴承还具有至少一个位于外圈（1）和内圈（5）之间的第二滚动体（6；6'；6"），其中，第一滚动体（2）具有第一自旋转轴线，第二滚动体（6；6'；6"）具有第二自旋转轴线，其中，在滚动轴承的至少一个相同的轴向位置上，第二滚动体（6；6'；6"）在垂直于第二自旋转轴线的截面内的直径大于第一滚动体（2）在垂直于第一自旋转轴线的截面内的直径。该滚动轴承能够防止在其所承载的载荷变小时发生打滑。

Description

滚动轴承 技术领域
本发明涉及一种滚动轴承。本发明特别涉及一种能够防打滑的滚动轴承。
背景技术
当滚动轴承所受载荷变小，滚动体和滚动轴承的轴承圈之间有打滑的风险。例如，由于目前各国铁路技术装备的差异，铁路轨距一般有米轨、窄轨、标轨、宽轨等不同轨距。在这种情况下，中国使用标准轨道，俄罗斯使用宽轨，越南使用窄轨，因此例如载欧亚火车货运线上或者在东南亚火车货运线上，火车轮对需要适应变轨工况，相应的，其上的轮对轴承也需要适应该变轨工况。现有的轮对轴承一般为双列圆锥滚子轴承，然而在变轨之后，双列圆锥滚子轴承上载荷偏离原有中心位置，两列滚动体受力不均，因此在载荷过小一侧，滚动体和滚动轴承的轴承圈有打滑的风险，由此轮对轴承可能会早期失效。
发明内容
因此，本发明所要解决的技术问题是提供一种滚动轴承，特别是基于圆锥滚子轴承的改进的滚动轴承，该滚动轴承能够在其所承载的载荷因工况改变而变小，或所承载的载荷例如因偏离中心位置，局部载荷过小的时候也不会有打滑的风险，因此该滚动轴承还能够用作适应铁路变轨工况的轮对轴承。
该技术问题通过一种滚动轴承，该滚动轴承包括外圈、内圈和位于外圈和内圈之间的第一滚动体，第一滚动体被设计为圆锥滚子，其中，滚动轴承还具有至少一个位于外圈和内圈之间的第二滚动体，其中，第一滚动体具有第一自旋转轴线，第二滚动体具有第二自旋转轴线，其中，在滚动 轴承的至少一个相同的轴向位置上，第二滚动体在垂直于第二自旋转轴线的截面内的直径大于第一滚动体在垂直于第一自旋转轴线的截面内的直径。
在本发明的范围中，滚动轴承能够是单列轴承、双列轴承或多列轴承。第一滚动体的第一自旋转轴线是圆锥滚子的理想的自旋转的转旋轴线，也是其中轴线。也就是说，在滚动轴承的旋转轴线和第一滚动体的中轴线所在的平面内，第一自旋转轴线与轴承的外圈的夹角等于第一自旋转轴线与轴承的内圈的夹角。第二滚动体的第二自旋转轴线是第二滚动体的理想的自旋转的自旋转轴线。也就是说，在滚动轴承的旋转轴线和第二滚动体的中心所在的平面内，第二自旋转轴线与轴承的外圈的夹角等于第二自旋转轴线与轴承的内圈的夹角。在此，当第二滚动体是滚珠时，第二滚动体的中心是指滚珠球体的球心；当第二滚动体是鼓形滚子或圆锥滚子时，第二滚动体的中心是指第二滚动体的中轴线。在这种情况下，第一滚动体的第一自旋转轴线与同一列中的第二滚动体的第二自旋转轴线能够相交于一点。能够理解为用至少一个第二滚动体替代只包括第一滚动体的滚子轴承中的部分滚动体，为了保持原滚动轴承的滚动体的滚动特性，与第一滚动体同列的第二滚动体的自旋转轴线与第一滚动体的自旋转轴线相较于一点。为了解决“打滑”的技术问题，如此设计第二滚动体的几何尺寸，优选在保持原轴承游隙的情况下，第二滚动体与轴承的外圈和内圈的间隙小于第一滚动体与外圈和内圈的间隙，即在滚动轴承的相同的轴向位置上，第二滚动体在垂直于第二自旋转轴线的截面内的直径大于第一滚动体在垂直于第一自旋转轴线的截面内的直径。因此，当滚动轴承的至少一列滚动体上所受的载荷变小，被设计为圆锥滚子的第一滚动体承载变小，而第二滚动体由于具有更大的尺寸能够与外圈和内圈有更充分接触，从而能够带动保持架及整列滚动体运动，从而避免打滑；而当在正常运转过程中，滚动轴承的第一滚动体和第二滚动体均承载，保证轴承正常的运转状态。
有利地，在滚动轴承的至少一个相同的轴向位置上，第二滚动体在垂直于第二自旋转轴线的截面内的直径比第一滚动体在垂直于第一自旋转轴 线的截面内的直径大3至50μm。特别地，上述两个截面内的直径的差值在5至30μm之间。
在一种优选的实施方式中，第二滚动体被设计为滚珠。滚珠例如是钢球。当轴承载荷较小时，滚珠充分接触滚动轴承的内圈和外圈，带动受载较轻一列滚动体运动。由于滚珠纯滚动，摩擦小，因此这种实施方式可适应较高转速的滚动轴承。在这种情况下，滚珠在垂直于其自旋转的旋转轴线，即第二自旋转轴线的截面内的直径是指在滚珠和滚动轴承的内圈与外圈接触时的两个接触点的连线方向上的距离。在滚动轴承的相同的轴向位置上，上述接触点在其连线方向上的距离大于第一滚动体在垂直于第一自旋转轴线的截面内的直径。增大尺寸的数值优选在3-50um之间，特别在5～30μm之间。
有利地，内圈具有用于轴向止挡第一滚动体和第二滚动体的挡边，其中，挡边具有用于止挡第一滚动体的第一接触面和用于止挡第二滚动体的第二接触面。在这种情况下，第一接触面和第二接触面分别是挡边的内周面上沿轴承径向相邻的两个圆周部段。能够将第二接触面设计为沿直线延伸的圆周部段，或者沿弧线延伸的圆周部段，其中弧线的弧度匹配滚珠的直径。由此，相比现有的内圈的挡边设计，沿轴承径向增加了挡边的尺寸，使得滚珠由内圈的挡边引导，滚珠自转的旋转中心与大挡边接触，理论上为纯滚动运动。同时，这种设计不改变现有第一滚动体，即圆锥滚子与挡边的接触特性。
在这种情况下，特别有利地，在第一接触面和第二接触面之间设有储油槽。从而可保证轴承较好的润滑特性。
在另一种优选的实施方式中，第二滚动体是鼓形滚子。在这种情况下，内圈能够采用原有设计，不必另外加工挡边部分。有利地，鼓形滚子的两个轴向端面的直径不同，即第二滚动体基本呈截圆锥形，然而其母线是沿径向向外凸出的弧线。特别地，能够设计第二滚动体的最大直径比在相邻位置的第一滚动体在轴承相同轴向位置上的直径尺寸大3-50μm。相同轴向位置的直径差最大的位置可根据实际载荷的分布情况进行设计，正常设计为靠近第二滚动体的大直径端处。比如，最大直径差位置距离第二 大直径端大端面的距离为整个第二滚动体的长度的1/3。
在另一种优选的实施方式中，第二滚动体是截圆锥形的滚子。在这种情况下，内圈也能够采用原有设计，不必另外加工挡边部分。有利地，第二滚动体在每一个垂直于第二自旋转轴线的截面内的直径均比第一滚动体在相应的垂直于第一自旋转轴线的截面内的直径大相同的尺寸，其差值在3至50μm。备选地，第二滚动体局部地设有沿滚动体的径向凸出的凸出部。例如，第二滚动体的轴向两端分别设有沿径向凸出的凸出部。在这种情况下，能够根据工况这样设置凸出部的尺寸，使得第二滚动体的带有凸出部的两个部段也形成两段截圆锥形，两段新的截圆锥的任一径向截面的直径较原来截圆锥的相应轴向位置的径向截面的直径大3-50um。
在一种有利的实施方式中，滚动轴承为双列滚动轴承或多列滚动轴承，在滚动轴承的每一列均具有第二滚动体。
备选地或附加地，滚动轴承为双列滚动轴承或多列滚动轴承，第二滚动体在滚动轴承的各列中个数不相等。第二滚动体的个数和在每列滚动体中的周向分布位置根据滚动轴承的具体工况，特别是根据在各种工况的受载荷情况确定。
附图说明
下面结合附图来示意性地阐述本发明的优选实施方式。附图为：
图1是根据本发明的第一优选实施方式的滚动轴承的半剖视图，
图2是根据图1的滚动轴承的局部放大图，
图3是根据图1的滚动轴承的沿另外的剖面剖切的半剖视图，
图4是根据本发明的第二优选实施方式的滚动轴承的第二滚动体的示意图，
图5是根据本发明的第三优选实施方式的滚动轴承的第二滚动体的示意图，以及
图6是根据现有技术的双列圆锥滚子轴承的半剖视图。
具体实施方式
图6示出了根据现有技术的一种双列圆锥滚子轴承的半剖视图。这种双列圆锥滚子轴承能够用作轮对轴承，并且包括外圈10，两个相邻布置的内圈50，两个塑料的保持架30，中隔圈40，两列圆锥滚子20。
图1示出根据本发明的第一优选实施方式的滚动轴承的半剖视图。该滚动轴承包括外圈1，两个相邻布置的内圈5，两个塑料的保持架3，中隔圈4，两列滚动体。每列滚动体均包括第一滚动体和第二滚动体。第一滚动体被设计为圆锥滚子(图3中被标记为2)，第二滚动体在本实施方式中被设计为钢球6。在每一列滚动体中，沿圆周方向均匀设置三个钢球6，其余滚动体为圆锥滚子2。这样设计钢球6的直径，使得钢球6和内圈5以及和外圈1接触点的距离相比在相同轴向位置上的圆锥滚子2的直径大3至50μm，特别地，其差值在5至30μm之间。当载荷较小时，圆锥滚子2承载较小，但钢球6与内圈5及外圈1有充分接触，因此能够钢球6能够带动保持架3及整列滚动体运动，从而避免打滑风险；而当在正常运转过程中，圆锥滚子2和钢球6均承载，保证滚动轴承正常的运转状态。如图所示，钢球6在一端通过由内圈5的外周面和外圈1的内周面共同止挡，在另一端由内圈5的在圆锥滚子2的大端面的挡边止挡，因此，还需设计钢球6的直径，使得钢球6能够接触到内圈5的挡边。
图2示出图1中A区域的局部放大图。能够看到内圈5的大挡边上，即在图3中滚动轴承的轴向两端的挡边上，具有用于轴向止挡圆锥滚子2的圆锥滚子接触面51，即第一接触面。该大挡边的外周直径相比图6中的现有技术被增大，以在圆锥滚子接触面51的径向外侧设置用于轴向止挡钢球6的钢球接触面53，即第二接触面。由此，大挡边可以引导钢球6运动。钢球6在运转过程中，其自转中心与内圈大挡边接触，从而引导滚动体在圆周方向上进行纯滚动。钢球接触面53被设计为凹面，以配合钢球6的形状。圆锥滚子接触面51和钢球接触面53形成储油槽52。
图3示出根据图1的滚动轴承的沿另外的剖面剖切的半剖视图。能够清楚地看到，圆锥滚子2与内圈5的大挡边动接触和根据图6的现有设计一样。此时，储油槽52能够存储一定润滑油脂，起到润滑的效果。
图4示出根据本发明的第二优选实施方式的滚动轴承的第二滚动体的 示意图。如图所示，第二滚动体6’基本呈截圆锥形，在图示中左侧为大直径端，右侧为小直径端。第二滚动体6’的截圆锥母线被设计为如图所示的沿径向向外的凸出的弧线。在滚动轴承的至少一个轴向位置上，第二滚动体6’的直径比在相同轴向位置的圆锥滚子2的直径大3～50μm。直径差最大的位置，即如图Δ Dmax的位置可根据实际载荷的分布情况进行设计，一般设计为靠近大直径端。例如，Δ Dmax的位置距离大直径端的端面为第二滚动体6’长度的约1/3。
图5示出根据本发明的第三优选实施方式的滚动轴承的第二滚动体的示意图。如图所示，第二滚动体6’基本呈截圆锥形，其轴向两端分别具有沿径向凸出的凸出部，即第一凸缘61”和第二凸缘62”。第一凸缘61”和第二凸缘62”均为截圆锥形，在滚动轴承的相同轴向位置上，第一凸缘61”和第二凸缘62”的外周直径相比相同轴向位置的圆锥滚子的直径增加3～50μm，具体根据工况需要而定。
虽然在上述说明中示例性地描述了可能的实施例，但是应该理解到，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
1     外圈
2     第一滚动体，圆锥滚子
3     保持架
4     中隔圈
5     内圈
51    第一接触面
52    储油槽
53    第二接触面
6     第二滚动体
6’   第二滚动体
6”   第二滚动体
61”  第一凸缘
62”  第二凸缘
10    外圈
20    圆锥滚子
30    保持架
40    中隔圈
50    内圈

Claims (10)

  1. 一种滚动轴承，所述滚动轴承包括外圈(1)、内圈(5)和位于所述外圈(1)和所述内圈(5)之间的第一滚动体(2)，所述第一滚动体(2)被设计为圆锥滚子，
    其特征在于，所述滚动轴承还具有至少一个位于所述外圈(1)和所述内圈(5)之间的第二滚动体(6；6’；6”)，
    其中，所述第一滚动体(2)具有第一自旋转轴线，所述第二滚动体(6；6’；6”)具有第二自旋转轴线，其中，在所述滚动轴承的至少一个相同的轴向位置上，所述第二滚动体(6；6’；6”)在垂直于所述第二自旋转轴线的截面内的直径大于所述第一滚动体(2)在垂直于所述第一自旋转轴线的截面内的直径。
  2. 根据权利要求1所述的滚动轴承，其特征在于，在所述滚动轴承的至少一个相同的轴向位置上，所述第二滚动体(6；6’；6”)在垂直于所述第二自旋转轴线的截面内的直径比所述第一滚动体(2)在垂直于所述第一自旋转轴线的截面内的直径大3至50μm。
  3. 根据权利要求1所述的滚动轴承，其特征在于，所述第二滚动体(6)被设计为滚珠。
  4. 根据权利要求3所述的滚动轴承，其特征在于，所述内圈(5)具有用于轴向止挡所述第一滚动体(2)和所述第二滚动体(6)的挡边，其中，所述挡边具有用于止挡所述第一滚动体(2)的第一接触面(51)和用于止挡所述第二滚动体(6)的第二接触面(53)。
  5. 根据权利要求4所述的滚动轴承，其特征在于，在所述第一接触面(51)和所述第二接触面(53)之间设有储油槽(52)。
  6. 根据权利要求1所述的滚动轴承，其特征在于，所述第二滚动体(6’)是鼓形滚子。
  7. 根据权利要求1所述的滚动轴承，其特征在于，所述第二滚动体(6”)是截圆锥形的滚子。
  8. 根据权利要求7所述的滚动轴承，其特征在于，所述第二滚动体 (6”)的轴向两端分别设有沿径向凸出的凸出部。
  9. 根据权利要求1所述的滚动轴承，其特征在于，所述滚动轴承为双列滚动轴承或多列滚动轴承，在所述滚动轴承的每一列均具有所述第二滚动体。
  10. 根据权利要求1所述的滚动轴承，其特征在于，所述滚动轴承为双列滚动轴承或多列滚动轴承，所述第二滚动体在所述滚动轴承的各列中个数不相等。
PCT/CN2018/119534 2018-12-06 2018-12-06 滚动轴承 WO2020113514A1 (zh)

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DE4142433C1 (en) * 1991-12-20 1993-05-27 Ibo Gesellschaft Fuer Beschaffung Und Absatz Von Industrieguetern Mbh, 8011 Kirchheim, De Combined roller and ball bearing with inner and outer races - is of thin race type with rollers and balls of same dia. and on same race tracks
US20040096132A1 (en) * 2002-06-10 2004-05-20 Fag Kugelfischer Ag & Co. Kg Radial self-aligning rolling bearing
CN1860306A (zh) * 2003-08-20 2006-11-08 谢夫勒两合公司 自动调心滚动轴承和用于自动调心滚动轴承的保持架
CN203856891U (zh) * 2011-05-04 2014-10-01 谢夫勒科技股份两合公司 滚动轴承
CN204387102U (zh) * 2015-01-05 2015-06-10 常州市武进永达机械轴承有限公司 紧凑型长圆柱滚子和滚珠组合轴承
CN105134775A (zh) * 2015-10-12 2015-12-09 山东凯美瑞轴承科技有限公司 一种具有调心功能的混合轴承

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4142433C1 (en) * 1991-12-20 1993-05-27 Ibo Gesellschaft Fuer Beschaffung Und Absatz Von Industrieguetern Mbh, 8011 Kirchheim, De Combined roller and ball bearing with inner and outer races - is of thin race type with rollers and balls of same dia. and on same race tracks
US20040096132A1 (en) * 2002-06-10 2004-05-20 Fag Kugelfischer Ag & Co. Kg Radial self-aligning rolling bearing
CN1860306A (zh) * 2003-08-20 2006-11-08 谢夫勒两合公司 自动调心滚动轴承和用于自动调心滚动轴承的保持架
CN203856891U (zh) * 2011-05-04 2014-10-01 谢夫勒科技股份两合公司 滚动轴承
CN204387102U (zh) * 2015-01-05 2015-06-10 常州市武进永达机械轴承有限公司 紧凑型长圆柱滚子和滚珠组合轴承
CN105134775A (zh) * 2015-10-12 2015-12-09 山东凯美瑞轴承科技有限公司 一种具有调心功能的混合轴承

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