WO2020063467A1 - 用于保持高负载平行度的负载保持架及轴承 - Google Patents

用于保持高负载平行度的负载保持架及轴承 Download PDF

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Publication number
WO2020063467A1
WO2020063467A1 PCT/CN2019/106908 CN2019106908W WO2020063467A1 WO 2020063467 A1 WO2020063467 A1 WO 2020063467A1 CN 2019106908 W CN2019106908 W CN 2019106908W WO 2020063467 A1 WO2020063467 A1 WO 2020063467A1
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Prior art keywords
load
holder
main body
wall
gap
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PCT/CN2019/106908
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English (en)
French (fr)
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林明
范俊
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林明
范俊
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Application filed by 林明, 范俊 filed Critical 林明
Priority to KR1020207022574A priority Critical patent/KR102474527B1/ko
Priority to JP2020543037A priority patent/JP7175318B2/ja
Publication of WO2020063467A1 publication Critical patent/WO2020063467A1/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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/467—Details of individual pockets, e.g. shape or roller retaining means
    • 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

Definitions

  • the invention relates to the technical field of mechanical transmission and transmission, in particular to a load holder and a bearing for maintaining high load parallelism.
  • the so-called “parallel load on the axis line” means that in a conventional mechanical transmission structure such as an overrunning clutch, a bearing, or the like, torque is transmitted to the driven wheel through the driving wheel, or the driving wheel rotates relative to the driven wheel.
  • the axis line of the load located between the driving wheel and the driven wheel used to transmit torque or maintain the gap between the driving wheel and the driven wheel, needs to be parallel to the transmission shaft without deflection.
  • This type of load is usually a roller And wedges appear.
  • the length direction (axial line direction) of these loads should be consistent with the axial direction of the driving wheel / driven wheel, so that each load can be guaranteed in the driving wheel / slave.
  • the load provided in each axial direction is in a high-precision axial parallel state with respect to the axis line, and the load is freely rolling and rolling in the gap between the driving wheel and the driven wheel; however, when each If the axially set load cannot be paralleled with high precision, it causes the squeeze roll transfer of the working state in the gap between the driving wheel and the driven wheel to be forced when it is working.
  • FIG. 1 it is a schematic diagram of the bearing force of the existing truck.
  • the bearing includes an inner ring A, an outer ring B, a roller C, and a roller cage D.
  • the inner ring A of the bearing is installed on a fixed central axis. Instead of turning, the outer ring B rotates clockwise and is affected by the gravity of the car.
  • the inner ring A applies a certain pressure to the outer ring B through the roller C below, while the upper roller C is idling without pressure. Because the position of the roller cage D is not restricted, and the size of the limiting hole for receiving the roller C on the roller cage D is larger than that of the roller C, the roller C does not have a circumferential direction in the limiting hole.
  • the actual binding force of the roller causes the two ends to oscillate freely.
  • the rollers undergo long-term squeezing and rolling transmission, which causes the rollers to deform, severely wear, and collapse.
  • the inner and outer rings of the bearings are subject to Abnormal pressing will inevitably lead to irregular indentations, grooves, etc., and the running clearance of the roller will further increase and become irregular, which will further reduce the accuracy of the axial alignment of the roller and further accelerate the damage process of the bearing.
  • the existing bearing life is generally shortened, and the roller cage has not actually played a significant role.
  • the present invention provides a load cage and bearing for maintaining high load parallelism, which can ensure that the load still maintains high-precision axial parallelism during operation, which greatly improves structural operation. Stability and reliability reduce noise and greatly extend bearing life.
  • a load holder for maintaining high load parallelism includes a ring-shaped holder body, and elastic pretensioners and gap holders installed on the holder body.
  • the cage main body is arranged in a circumferential direction on the inner ring surface or the outer ring surface of the cage main body; the outer peripheral surface of the cage main body is provided with a plurality of limits arranged at intervals in the circumferential direction of the cage main body.
  • Positioning holes extending along the axial direction of the holder main body for passing and receiving by a roller-like load, at least one of the inner walls of each of the positioning holes is fixed for elastic pushing in the circumferential direction. The pre-tensioning member of the load is pressed.
  • an inner ring surface or an outer ring surface of the holder main body is provided with a groove for the gap holder to be embedded, and the gap holder is rotatably provided in the groove and The diameter is greater than the groove depth.
  • the groove is annular, and the gap holders are closely arranged in the circumferential direction of the groove.
  • the holder main body includes two spaced positioning rings that are arranged opposite to each other and a plurality of connecting beams connected between the two positioning portions, and the grooves are opened in the The inner ring surface or the outer ring surface of the positioning ring; the limiting hole is formed between two adjacent connecting beams, and each of the connecting beams is fixed with one of the pretensioning members.
  • two of the pre-tensioning members are fixed to an inner wall of each of the limiting holes, and the two pre-tensioning members in each of the limiting holes are respectively used for holding the retaining frame.
  • the load is pushed by two different parts in the axial direction of the main body.
  • the gap holder is a ball or a roller.
  • each of the limit holes includes a first inner wall and a second inner wall opposite to each other in the rotation direction of the holder body, and the pre-tensioning member is provided on each of the limit holes.
  • a free end of the first inner wall extends toward the second inner wall.
  • the first inner wall and the second inner wall of each of the limiting holes are parallel to each other.
  • Another object of the present invention is to provide a bearing, which includes an inner ring, an outer ring, a load, and the load holder for maintaining a high load parallelism.
  • the load is plural and is provided in a rollable manner in the inner ring.
  • the load holder for maintaining high load parallelism is provided between the inner ring and the outer ring, and the gap holder is rotatably provided on the holder body
  • the load is accommodated in the limit hole, and under the action of the pretensioning member Elastically abutting the holder main body.
  • the load holder of the present invention can ensure that the load always maintains a high degree of parallelism in the axial direction during the transmission process, and avoids the occurrence of noise, vibration, damage and the like during the operation of the equipment to the greatest extent.
  • the axis line is in a high-precision axial parallel state, and the load can be freely rolled and rolled in the gap between the driving wheel and the driven wheel, achieving the ideal state of force and greatly extending the use of the bearing life.
  • FIG. 1 is a schematic diagram of a force during the use of a heavy-duty bearing in the prior art
  • FIG. 2 is an exploded schematic view of a bearing structure according to an embodiment of the present invention.
  • FIG. 3 is a schematic structural diagram of a bearing according to an embodiment of the present invention.
  • FIG. 4 is a cross-sectional view taken along the line K-K in FIG. 3;
  • FIG. 5 is a cross-sectional view taken along the line M-M in FIG. 4;
  • FIG. 6 is an exploded schematic diagram of a structure of a load holder according to an embodiment of the present invention.
  • FIG. 7 is an exploded schematic view of another bearing structure according to an embodiment of the present invention.
  • FIG. 8 is a schematic structural diagram of another bearing according to an embodiment of the present invention.
  • FIG. 9 is a cross-sectional view taken along the direction K1-K1 of FIG. 8;
  • FIG. 10 is a cross-sectional view taken along the M1-M1 direction in FIG. 9.
  • the terms “provided”, “provided”, and “connected” should be understood in a broad sense.
  • it can be a fixed connection, a detachable connection, or a monolithic structure; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, or it can be two devices, components, or components. Internal connectivity.
  • the specific meanings of the above terms in the present invention can be understood according to specific situations.
  • the load holder of the present invention has a ring-shaped holder body and elastic pretensioners and gap holders mounted on the holder body. There are multiple gap holders and pretensioners, and the gap holders are along the holder body.
  • the circumferential direction is arranged on the inner ring surface or the outer ring surface of the holder main body, and a plurality of limiting holes spaced in the circumferential direction of the holder main body are provided on the outer peripheral surface of the holder main body.
  • the axial extension of the for the roller-shaped load to pass through and accommodate, at least one pre-tensioning member is fixed to the inner wall of each limiting hole, and the free end of the pre-tensioning member extends toward the opposite inner wall for assembling under load.
  • the pre-tensioning members are uniformly extended from the inner wall on the same side of each limit hole in the rotation direction of the holder body toward the opposite inner wall (for example, in a clockwise direction, extending from upstream to downstream).
  • upstream and downstream refer to two relative positions on the rotation path in the rotation direction. In the rotation direction, the circumferential movement direction from “upstream” to “downstream” is consistent with the rotation direction.
  • the load cage After the load cage is assembled into the bearing, the load cage is located between the inner and outer rings that can rotate relatively on the bearing, and the load cage rolls with the inner or outer ring through the gap retaining member to roll on the back of the inner or outer ring
  • the ring guarantees reliable limit accuracy, and the load cage no longer randomly moves.
  • the roller load assembled in the load holder is subject to the elastic pre-tensioning force of the pre-tensioning member.
  • the roller load above the bearing is not subject to the pressure of the outer ring and is subject to the elastic pre-tensioning force of the upstream pre-tensioning member. They are abutted on the downstream inner wall of the limit hole without rolling or slight rolling.
  • rollers are loaded tightly against the downstream inner wall of the limit hole and are constrained in the circumferential direction. They are in an absolute axial parallel state.
  • the roller load is subject to the compression force of the inner ring and the outer ring at the same time, and it rolls under the same rotation direction as the outer ring; when the upper roller load moves with the load cage under the bearing, the roller load is simultaneously received by the inner ring
  • the preload is compressed by the pressing force of the outer ring and the outer ring, and the roller load is separated from the downstream inner wall of the limit hole, and can no longer be subject to circumferential restraint, so rolling can occur.
  • the front of the downstream inner wall is in a precise axial pre-tensioning state, so it can still maintain high axial accuracy in the subsequent rolling process.
  • the load holder 30 for maintaining high load parallelism mainly includes a ring-shaped holder main body 31, and an elastic pretensioner 32 and a gap holder installed on the holder main body 31.
  • the holder main body 31 is mounted to the inner ring 10 and the outer ring in the bearing. After the rings 20, a high-precision gap can be maintained between the inner and outer rings of the bearing through the gap holders 33 arranged in the circumferential direction, without affecting the circumferential rotation of the cage body 31.
  • it can be a ball or a roller.
  • the outer peripheral surface of the holder main body 31 is provided with a plurality of limiting holes 312 spaced apart in the circumferential direction of the holder main body 31.
  • the limiting holes 312 are along the axial direction of the holder main body 31. It is extended for the roller-shaped load 40 to pass through and be accommodated.
  • At least one pre-tensioning member 32 for fixing the load 40 in the circumferential direction is fixed on the inner wall of each position-limiting hole 312.
  • the width of the limiting hole 312 (that is, the size along the circumferential direction of the holder main body 31) is slightly larger than the radial dimension of the load 40.
  • the length direction of the limiting hole 312 is the same as the axial direction of the holder main body 31.
  • the depth direction of the bit holes 312 is the radial direction of the holder main body 31.
  • Each of the limit holes 312 includes a first inner wall and a second inner wall opposite to each other in the rotation direction of the holder main body 31.
  • a pretensioning member 32 is provided on each The first inner wall and the free end of the restriction hole 312 extend toward the second inner wall.
  • the first inner wall and the second inner wall of the restriction hole 312 are parallel to each other, and are parallel to the depth direction of the restriction hole 312, that is, perpendicular to the restriction hole 312. In the width direction, the load 40 can be subjected to a completely vertical circumferential warning force in the limit hole 312 to achieve a reliable limit.
  • the first inner wall of each limit hole 312 is located upstream / downstream of the second inner wall.
  • the limiting holes 312 are evenly distributed in the circumferential direction of the holder main body 31, and a load 40 is installed in each limiting hole 312, and the number of the limiting holes 312 in the load 40 and the load holder 30 are the same.
  • the load 40 in each limiting hole 312 is simultaneously subjected to at least two elastic pushing forces in the same direction from the pretensioning member 32.
  • one pre-tensioning member 32 can simultaneously push at least two different locations in the length direction of the load 40, or two inner pre-tensioning members 32 can be fixed to the inner wall of each limiting hole 312, each limiting hole
  • the two pretensioning members 32 in 312 are respectively used to push the load 40 at two different locations in the length direction of the load 40.
  • the inner ring surface or the outer ring surface of the holder main body 31 is provided with a groove 311 for the gap holder 33 to be embedded.
  • the gap holder 33 is rotatably provided in the groove 311 and has a diameter larger than the depth of the groove 311, so that the gap is maintained.
  • the piece 33 partially protrudes out of the groove 311.
  • the grooves 311 have a ring shape, and the gap holders 33 are closely arranged in the circumferential direction of the grooves 311. There are at least two grooves 311.
  • the two grooves 311 are spaced apart from each other in the axial direction of the holder main body 31 to ensure that the cage main body 31 can maintain axial balance during the rotation process, it is preferable that two grooves 311 are opened at both ends in the axial direction of the cage main body 31 to facilitate the opening of the limiting hole 312 and the clearance of the retaining member 33. assembly.
  • the holder main body 31 includes two spaced positioning rings 3a facing each other and a plurality of connecting beams 3b connected between the two positioning portions 3a.
  • a groove 311 is opened in the positioning ring 3a.
  • a limiting hole 312 is formed between two adjacent connecting beams 3b, and a pretensioning member 32 is fixed on each connecting beam 3b.
  • the pretensioning member 32 of this embodiment is an elastic piece, and the outer surface of the connection beam 3b of the holder main body 31 is provided with two intervals of positioning grooves P.
  • One end of the pretensioning member 32 is wound on the surface of the connection beam 3b and Embedded in the positioning slot P, the free end of the pre-tensioning member 32 projects toward the opposite inner wall of the limiting hole 312.
  • the limiting hole 312 can also be made narrower, and the limiting hole 312 can also be designed more. More loads 40 can also share more pressing force, and the limiting hole 312 is closer to the radial size of the load 40, which can also be beneficial to improve the axial parallelism.
  • the pretensioning member 32 may be replaced by a compression spring, a torsion spring, or the like.
  • the present invention also provides a bearing having the above-mentioned load retainer 30, which includes an inner ring 10, an outer ring 20, a load retainer 30, and a load 40.
  • the distance between the inner ring surface and the outer ring surface of the retainer body 31 is the wall thickness of the retainer body 31 less than the load 40, which is located in the limiting hole 312, and the outer surface of the inner ring 10 and the inner surface of the outer ring 20. Scrollable.
  • the grooves 311 are opened on the inner ring surface of the holder body 31, and the gap holders 33 are arranged at intervals.
  • chamfered surfaces 10S are respectively provided at both ends of the inner ring 10.
  • each load 40 is installed in each limit hole 312, so that each load 40 is elastically abutted against the second inner wall of the limit hole 312 by the pretensioning member 32, and then the outer
  • the ring 20 is sleeved outside the load holder 30, and the axial direction of the bearing is limited to complete the assembly.
  • the bearing may further include a retaining ring 50 and a retaining ring 60.
  • An inner surface of one end of the outer ring 20 is provided with a retaining groove 200 for retaining the retaining ring 50.
  • the inner ring 10 of the bearing does not rotate and the outer ring 20 rotates clockwise as an example.
  • the “inner ring 10 does not rotate” here refers to the movement of the outer ring 20 relative to the outer ring 20. In actual operation, the outer ring 20 may not rotate and the inner ring 10 may rotate.
  • the high-precision axial line cage of the present invention is particularly suitable for heavy-duty bearings with linear contact loads.
  • the inner ring 10 is subjected to a downward load pressure, and the outer ring 20 of the bearing faces a pressure-bearing surface (such as the ground). ) While applying vertical pressure, the outer ring 20 rotates clockwise. In this process, the inner ring 10 can be considered to be slightly eccentric toward the pressure surface.
  • the load 40 located above the bearing axis X is not subject to the longitudinal pressure of the inner ring 10, and the bearing pressure is mainly concentrated on the bearing shaft
  • the load 40 located below the bearing axis X is rolled clockwise synchronously under the squeeze of the inner ring 10 and the outer ring 20.
  • the roller load 40 located above the bearing axis X is not pressed by the outer ring 20 and is abutted against the downstream inner wall (second inner wall) of the limiting hole 312 under the clockwise elastic preload force.
  • roller loads 40 are closely constrained in the circumferential direction against the downstream inner wall of the limiting hole 32 and are in an absolute axial parallel state; when the upper roller load 40 moves to the bearing axis with the load cage 30 After the line X, the load 40 is compressed by the compression force of the inner ring 10 and the outer ring 20 at the same time, so that the pre-tensioning member 32 is compressed, and the downstream inner wall of the limit hole 32 is separated, and is no longer constrained in the circumferential direction, and can roll.
  • the load 40 receives a gradual increase in the pressing force and starts to roll synchronously with the outer ring 20 on the inner surface of the outer ring 20.
  • the load 40 is gradually increased during the clockwise movement of the load 40 from the bearing axis X to the bottom. Load 40 moves from below to bearing axis X During the process on one side (as shown on the left side of FIG. 5), the pressing force gradually decreases. When the load 40 moves above the bearing axis line X, the pressing force becomes 0, and the pretensioning member 32 recovers from deformation. The load 40 is pushed again to the downstream inner wall of the limiting hole 32 and rotates with the holder body 31.
  • the grooves 311 ' are opened on the outer ring surface of the holder main body 31, and the gap holders 33 are arranged at intervals.
  • the outer ring 20 is sleeved outside the holder main body 31 and the gap holder 33, and then the loads 40 are installed in the respective limiting holes 312, so that each load 40 is elastically resisted by the pretensioning member 32.
  • the gap holder 33 is located between the outer ring 20 and the groove 311 '. After the load holder 30 is mounted on the outer ring 20, the inner ring 10 is inserted into the load holder 30 to limit the axial direction of the bearing to complete the assembly.
  • the present embodiment may be provided with a retaining groove 100 for retaining the retaining ring 50 on the outer surface of one end of the inner ring 10.
  • the retaining ring 60 is first set on the inner ring 10, and then the retaining ring 50 is inserted into the retaining groove 100.
  • the retainer body 31 is received by the retaining ring in the axial direction. 60 blocks to achieve axial limit.
  • the load holder of the present invention can ensure that the load always maintains a high degree of parallelism in the axial direction during the transmission process, and avoids the occurrence of noise, vibration, damage and the like during the operation of the equipment to the greatest extent.
  • the axis line is in a high-precision axial parallel state, and the load can be freely rolled and rolled in the gap between the driving wheel and the driven wheel, achieving the ideal state of force and greatly extending the use of the bearing life.

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

Abstract

一种用于保持高负载平行度的负载保持架（30），包括环形的保持架主体（31）以及安装在保持架主体（31）上的预紧件（32）和间隙保持件（33），多个间隙保持件（33）沿保持架主体（31）的周向排列地布置在保持架主体（31）的内环面或外环面；保持架主体（31）的外周面开设有在保持架主体（31）周向上间隔设置的多个限位孔（312），每个限位孔（312）的内壁固定有至少一个用于沿周向上弹性推压负载（40）的预紧件（32）。所述负载保持架可以保证负载在传动过程中始终保持轴向的高精确的平行度，最大限度地避免设备运行过程中了噪音、震动、损伤等的出现，各轴向设置的负载相对于轴心线处于高精度的轴向平行状态，负载在主动轮与从动轮之间的间隙内可以处于自由状的滚动、滚转传递，极大地延长了轴承的使用寿命。

Description

用于保持高负载平行度的负载保持架及轴承 技术领域
本发明涉及机械传动和传递技术领域，尤其涉及一种用于保持高负载平行度的负载保持架及轴承。
背景技术
在全球机械传动行业中，“低精度轴心线平行负载”应用的结构性现象，是制约行业技术发展的根本性障碍。
这里，所谓的“轴心线平行负载”是指，在传统的机械传动结构如超越离合器、轴承等类似的结构中，在通过主动轮向从动轮传递扭矩，或者主动轮相对于从动轮进行转动的过程中，位于主动轮与从动轮之间、用于传递扭矩或保持主动轮与从动轮之间间隙的负载的轴心线需要与传动轴平行而不出现偏转，这类负载通常以滚轴、楔块等形式出现，理想状态下，在同一个产品中，这些负载的长度方向(轴心线方向)应与主动轮/从动轮的轴向一致，这样才能保证各个负载在主动轮/从动轮传动过程中均参与到力矩传递或传动的作用。
然而，即使主动轮与从动轮的制作精度非常高，二者的径向和轴向尺寸均与负载精确匹配，在实际的机械传动过程中，此类负载会毫无征兆地出现轴向倾斜而不再与传动轴向平行，导致单个负载仅局部受力而出现应力集中，各负载之间的受力也无法一致，导致整个传动结构出现受力不均，表现为局部磨损、变形、压溃等，出现噪音、震动、损伤等，严重缩短了传动结构的使用寿命。
目前市面上也出现了一些用来改善这些负载的轴向平行度的设计，最具代表性的就是在传动结构中设计出负载保持架，目的在于使得各负载的轴向保持一致，然而，由于该保持架并不固定，而是悬于主动轮与从动轮之间，导致保持架本身的位置就不能精确固定，更不谈如何实现负载的精确轴向平行度。此种缺陷尤其是在超越离合器及高速、重载荷轴承等传动基础件中表现尤为明显。
理想状态下，各轴向设置的负载相对于轴心线处于高精度的轴向平行状态，负载在主动轮与从动轮之间的间隙内处于自由状的滚动、滚转传递；然而，当 各轴向设置的负载如果无法做到高精度平行，导致其工作时在主动轮和从动轮之间的间隙内的工作状态为强制状态的挤压滚转传递。
如图1所示，为现有的载重汽车的轴承受力示意图，轴承包括内圈A、外圈B、滚柱C和滚柱保持架D，轴承的内圈A安装在固定的中心轴上而不会转动，外圈B顺时针转动，受汽车重力作用，内圈A通过处于下方的滚柱C对外圈B施加一定的压力，而处于上方的滚柱C则不受压力而处于空转状态，由于滚柱保持架D本身的位置并无约束，而滚柱保持架D上用于容纳滚柱C的限位孔尺寸也大于滚柱C，滚柱C在限位孔内并无周向上的实际约束力而导致其两端处于随意摆动的状态，上方处于空转状态的滚柱C在不受压力的情况下随意摆动，当其随外圈B转动过程中进入下方时，由于其并不是与轴承的轴向完全平行，在其转动过程中同时受到内圈A、外圈B挤压力时，则会发生强制状态的挤压滚转传递，当滚柱C进入最下方时受到的挤压力最大。在理想状态下滚柱C与内圈A、外圈B处于线性接触状态，当滚柱C处于偏摆状态时，滚柱C与内圈A的外弧面处于单点(滚柱上靠近中部的接触点)接触状态而受力，滚柱C与外圈B的内弧面处于两点(滚柱上靠近两端的接触点)接触状态而受力，即形成所谓的“强制状态的挤压滚转传递”，一般来说，滚柱C两端的偏摆幅度越大，其两端在有限的径向间隙内所受到的挤压力越大，所产生的噪音、震动、损伤越大，对于轴承的内圈A、外圈B的磨损、损伤也越大。
此种轴承在经过一段时间的使用后，一方面，滚柱长期发生挤压滚转传递导致滚柱变形、严重磨损、压溃等现象发生，另一方面，轴承的内圈和外圈长期受到非正常挤压，必然出现非规则的压痕、压槽等，滚柱的运行间隙进一步增大且呈不规则的间隙，进一步降低滚柱的轴向对准精度，轴承的损坏进程进一步加速，导致现有的轴承寿命普遍缩短，滚柱保持架实际上并未起到明显作用。
发明内容
鉴于现有技术存在的不足，本发明提供了一种用于保持高负载平行度的负载保持架及轴承，可以保证负载在运行过程中仍然保持高精度的轴向平行度，大幅提升了结构运行稳定性和可靠性，降低了噪音，也极大地延长了轴承的使用寿命。
为了实现上述的目的，本发明采用了如下的技术方案：
一种用于保持高负载平行度的负载保持架，包括环形的保持架主体以及安 装在所述保持架主体上的弹性的预紧件和间隙保持件，所述间隙保持件为多个，沿所述保持架主体的周向排列地布置在所述保持架主体的内环面或外环面；所述保持架主体的外周面开设有在所述保持架主体周向上间隔设置的多个限位孔，所述限位孔沿所述保持架主体的轴向延伸，以供滚柱状的负载穿过并容纳，每个所述限位孔的内壁固定有至少一个用于沿周向上弹性推压所述负载的所述预紧件。
作为其中一种实施方式，所述保持架主体的内环面或外环面开设有供所述间隙保持件嵌设的沟槽，所述间隙保持件可滚动地设于所述沟槽内且直径大于所述沟槽深度。
作为其中一种实施方式，所述沟槽呈环形，所述间隙保持件在所述沟槽的周向上紧密排列。
作为其中一种实施方式，所述沟槽至少为两个，两个所述沟槽在所述保持架主体的轴向上间隔设置。
作为其中一种实施方式，所述保持架主体包括两个间隔且正对设置环状的定位环和连接在两个所述定位部之间的多根连接梁，所述沟槽开设在所述定位环的内环面或外环面；相邻的两根所述连接梁之间形成所述限位孔，每根所述连接梁上固定有一个所述预紧件。
作为其中一种实施方式，每个所述限位孔的内壁固定有两个所述预紧件，每个所述限位孔内的两个所述预紧件分别用于在所述保持架主体的轴向上的两个不同部位推压所述负载。
作为其中一种实施方式，所述间隙保持件为滚珠或滚柱。
作为其中一种实施方式，每个所述限位孔包括在所述保持架主体的转动方向上相对的第一内壁和第二内壁，所述预紧件设于每个所述限位孔的所述第一内壁且自由端朝向所述第二内壁延伸。
作为其中一种实施方式，每个所述限位孔的所述第一内壁与所述第二内壁相互平行。
本发明的另一目的在于提供一种轴承，包括内圈、外圈、负载和所述用于保持高负载平行度的负载保持架，所述负载为多个，可滚动地设于所述内圈和所述外圈之间；所述用于保持高负载平行度的负载保持架设于所述内圈和所述外圈之间，所述间隙保持件可滚动地设置在所述保持架主体与所述内圈外环面 之间，或所述保持架主体与所述外圈内环面之间；所述负载容纳于所述限位孔内，且在所述预紧件的作用下弹性抵接所述保持架主体。
本发明的负载保持架可以保证负载在传动过程中始终保持轴向的高精确的平行度，最大限度地避免设备运行过程中了噪音、震动、损伤等的出现，各轴向设置的负载相对于轴心线处于高精度的轴向平行状态，负载在主动轮与从动轮之间的间隙内可以处于自由状的滚动、滚转传递，实现了理想状态的受力，极大地延长了轴承的使用寿命。
附图说明
图1为现有技术的重载轴承的使用过程中的受力示意图；
图2为本发明实施例的一种轴承的结构分解示意图；
图3为本发明实施例的一种轴承的结构示意图；
图4为图3的K-K向的剖视图；
图5为图4的M-M向的剖视图；
图6为本发明实施例的一种负载保持架的结构分解示意图；
图7为本发明实施例的另一种轴承的结构分解示意图；
图8为本发明实施例的另一种轴承的结构示意图；
图9为图8的K1-K1向的剖视图；
图10为图9的M1-M1向的剖视图。
具体实施方式
在本发明中，术语“设置”、“设有”、“连接”应做广义理解。例如，可以是固定连接，可拆卸连接，或整体式构造；可以是机械连接，或电连接；可以是直接相连，或者是通过中间媒介间接相连，又或者是两个装置、元件或组成部分之间内部的连通。对于本领域普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
另外，术语“上”、“下”、“左”、“右”、“顶”、“底”、“顺时针”、“逆时针”、“内”、“外”、“中”、“竖直”、“水平”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。这些术语主要是为了更好地描述本发明及其实施例，并 非用于限定所指示的装置、元件或组成部分必须具有特定方位，或以特定方位进行构造和操作。
并且，上述部分术语除了可以用于表示方位或位置关系以外，还可能用于表示其他含义，例如术语“上”在某些情况下也可能用于表示某种依附关系或连接关系。对于本领域普通技术人员而言，可以根据具体情况理解这些术语在本发明中的具体含义。
为了使本发明的目的、技术方案及优点更加清楚明白，以下结合附图及实施例，对本发明进一步详细说明。应当理解，此处所描述的具体实施例仅仅用以解释本发明，并不用于限定本发明。
本发明的负载保持架具有环形的保持架主体以及安装在该保持架主体上的弹性的预紧件和间隙保持件，间隙保持件、预紧件均为多个，间隙保持件沿保持架主体的周向排列地布置在保持架主体的内环面或外环面，在保持架主体的外周面开设有在保持架主体周向上间隔设置的多个限位孔，限位孔沿保持架主体的轴向延伸，以供滚柱状的负载穿过并容纳，每个限位孔的内壁固定有至少一个预紧件，该预紧件的自由端朝对侧的内壁延伸，用于在负载装配到限位孔内后，沿周向上弹性推压位于限位孔内的负载。预紧件统一自每个限位孔在保持架主体的转动方向上的同一侧内壁朝对侧内壁延伸(如在顺时针方向，自上游朝下游延伸出)。这里，“上游”“下游”是指在转动方向上位于转动路径上的两个相对方位，在转动方向上，从“上游”到“下游”的周向移动方向与转动方向一致。
当负载保持架装配到轴承内后，负载保持架位于轴承上可相对转动的内圈和外圈之间，且负载保持架通过间隙保持件在内圈或外圈背面滚动而与内圈或外圈保证可靠的限位精度，负载保持架不再发生随意窜动的现象。同时，装配于负载保持架内的滚柱负载受到预紧件的弹性预紧力，具体是，位于轴承上方的滚柱负载不受外圈压力且在上游预紧件的弹性预紧力作用下被抵接在限位孔的下游内壁上而不发生滚动或轻微滚动，这些滚柱负载紧贴限位孔的下游内壁而受到周向约束，处于绝对的轴向平行状态；而位于轴承下方的滚柱负载同时受到内圈和外圈的挤压力下发生滚动而与外圈的转动方向一致；当上方的滚柱负载随负载保持架运动至轴承下方时，该滚柱负载同时受到内圈和外圈的挤压力而使预紧件被压缩，该滚柱负载则脱离限位孔的下游内壁、不再受到周向约束而可以发生滚动，由于在该滚柱负载脱离限位孔的下游内壁前处于精确的轴 向预紧状态，因此在后续的滚动过程中可以仍保持较高的轴向精度。
参阅图2～5，本实施例中，用于保持高负载平行度的负载保持架30主要包括呈环形的保持架主体31以及安装在保持架主体31上的弹性的预紧件32和间隙保持件33，间隙保持件33为多个，沿保持架主体31的周向排列地布置在保持架主体31的内环面或外环面，保持架主体31安装到轴承内的内圈10和外圈20之间后，可以通过周向排列的间隙保持件33与轴承的内圈或外圈保持高精度的间隙，且不影响保持架主体31的周向转动。这里，可以是滚珠或滚柱。
结合图5和图6所示，具体地，保持架主体31的外周面开设有在保持架主体31周向上间隔设置的多个限位孔312，限位孔312沿保持架主体31的轴向延伸，以供滚柱状的负载40穿过并容纳，每个限位孔312的内壁固定有至少一个用于沿周向上弹性推压负载40的预紧件32。
需要说明的是，限位孔312的宽度(即沿保持架主体31周向的尺寸)略大于负载40的径向尺寸，限位孔312的长度方向与保持架主体31的轴向相同，限位孔312的深度方向即为保持架主体31的径向，每个限位孔312包括在保持架主体31的转动方向上相对的第一内壁和第二内壁，预紧件32设于每个限位孔312的第一内壁且自由端朝向第二内壁延伸，限位孔312的第一内壁与第二内壁相互平行，均与限位孔312的深度方向平行，即垂直于限位孔312的宽度方向，可以使得负载40在限位孔312内受到完全垂直的周向预警力，实现可靠限位，每个限位孔312的第一内壁均位于第二内壁的上游/下游。
最好是，限位孔312均布在保持架主体31周向上，每个限位孔312内安装有一个负载40，负载40和负载保持架30内的限位孔312的数量一致。每个限位孔312内的负载40同时受到来自预紧件32的至少两个同向的弹性推压力。例如，可以是一个预紧件32同时推压负载40的长度方向上的至少两个不同部位，也可以是每个限位孔312的内壁固定有两个预紧件32，每个限位孔312内的两个预紧件32分别用于在负载40的长度方向上的两个不同部位推压负载40。
保持架主体31的内环面或外环面开设有供间隙保持件33嵌设的沟槽311，间隙保持件33可滚动地设于沟槽311内且直径大于沟槽311深度，使得间隙保持件33部分伸出沟槽311外。这里，沟槽311呈环形，间隙保持件33在沟槽311的周向上紧密排列，该沟槽311至少为两个，两个沟槽311在保持架主体31的轴向上间隔设置，用以保证保持架主体31在转动过程中可以保持轴向平衡，最好是两个沟槽311开设在保持架主体31的轴向上的两端，便于限位孔312的 开设和间隙保持件33的装配。
作为其中一种实施方式，保持架主体31包括两个间隔且正对设置环状的定位环3a和连接在两个定位部3a之间的多根连接梁3b，沟槽311开设在定位环3a的内环面或外环面；相邻的两根连接梁3b之间形成限位孔312，每根连接梁3b上固定有一个预紧件32。
进一步地，本实施例的预紧件32为弹片，保持架主体31的连接梁3b的外表面上开设有两圈间隔的定位槽P，预紧件32的一端卷绕在连接梁3b表面并嵌设在定位槽P内，预紧件32的自由端朝向限位孔312对侧内壁伸出，如此，限位孔312也可以做得更窄，限位孔312也可以设计得更多，更多的负载40也可以分担更多的挤压力，限位孔312更接近负载40的径向尺寸，也可以更利于提高轴向平行度。在其他实施方式中，预紧件32也可以采用压簧、扭簧等代替。
同时，本发明也提供了一种具有上述负载保持架30的轴承，包括内圈10、外圈20、负载保持架30和负载40，负载40为多个，可滚动地设于内圈10和外圈20之间，负载保持架30设于内圈10和外圈20之间，间隙保持件33可滚动地设置在保持架主体31与内圈10外环面之间，或保持架主体31与外圈20内环面之间；负载40容纳于限位孔312内，且在预紧件32的作用下弹性抵接保持架主体31。
保持架主体31的内环面与外环面之间的距离即保持架主体31的壁厚小于负载40，负载40位于限位孔312内，且在内圈10外表面和外圈20内表面可滚动。
如图2-6所示，为间隙保持件33可滚动地设置在保持架主体31内环面的情形，沟槽311开设在保持架主体31的内环面，间隙保持件33间隔地排列在沟槽311内，内圈10的两端分别设有倒角面10S，当负载保持架30组装到轴承的内圈10上后，间隙保持件33位于倒角面10S与沟槽311之间。当负载保持架30安装到内圈10上后，将负载40安装到各个限位孔312内，使得各个负载40被预紧件32弹性抵接在限位孔312的第二内壁，再将外圈20套设在负载保持架30外，对轴承的轴向进行限位即可完成组装。
作为轴承端面的一种限位方式，轴承还可包括卡圈50、挡圈60，外圈20的一端的内表面开设有供卡圈50卡持的卡持槽200。当外圈20套设在负载保持架30外后，先将挡圈60放入外圈20，再将卡圈50卡入卡持槽200，保持架主体31在轴向上受挡圈60阻挡而实现轴向限位。
下面对轴承受压过程中，负载40的运行状况进行分析，这里，以轴承的内圈10不转，外圈20顺时针转动为例进行说明。需要说明的是，这里的“内圈10不转”指的是相对于外圈20的运动情况，在实际运行过程中，也可以是外圈20不转，内圈10进行转动。
本发明的高精度轴心线保持架特别适用于线状接触负载的重载荷轴承，如图5所示，内圈10受到向下的承载压力，轴承的外圈20对受压面(如地面)施加垂直压力，同时，外圈20顺时针转动。在此过程中，内圈10可以认为是呈现朝向受压面的微偏心状态，位于轴承轴心线X上方的负载40不受内圈10的纵向压力，承载压力主要集中施加在位于轴承轴心线X下方的负载40上，位于轴承轴心线X下方的负载40在内圈10、外圈20的挤压下顺时针同步滚动。位于轴承轴心线X上方的滚柱负载40不受外圈20压力且在顺时针方向的弹性预紧力作用下被抵接在限位孔312的下游内壁(第二内壁)上而不发生滚动或轻微滚动，这些滚柱负载40紧贴限位孔32的下游内壁而受到周向约束，处于绝对的轴向平行状态；当上方的滚柱负载40随负载保持架30运动至轴承轴心线X下方后，该负载40同时受到内圈10和外圈20的挤压力而使预紧件32被压缩，则脱离限位孔32的下游内壁、不再受到周向约束而可以发生滚动，该负载40受到的挤压力逐渐增大而开始在外圈20内表面随外圈20同步滚动，由于在该负载40脱离限位孔32的下游内壁前处于精确的轴向预紧状态，因此在后续的滚动过程中可以仍保持较高的轴向精度，不会发生周向摆动，负载40从轴承轴心线X顺时针运动至最下方的过程中，受到的挤压力逐渐增大，负载40从下方运动至轴承轴心线X另一侧(如图5的左侧)的过程中，受到的挤压力逐渐减小，当负载40运动至轴承轴心线X上方后，挤压力变为0，预紧件32恢复形变而再次将负载40推压至限位孔32的下游内壁而随保持架主体31转动。
如图7-10所示，为间隙保持件33可滚动地设置在保持架主体31外环面的情形，沟槽311’开设在保持架主体31的外环面，间隙保持件33间隔地排列在沟槽311’内，先将外圈20套设在保持架主体31与间隙保持件33外面，再将负载40安装到各个限位孔312内，使得各个负载40被预紧件32弹性抵接在限位孔312的第二内壁，当负载保持架30组装到轴承的外圈20上后，间隙保持件33位于外圈20与沟槽311’之间。当负载保持架30安装到外圈20上后，再将内圈10插设在负载保持架30内，对轴承的轴向进行限位即可完成组装。
与前一种轴承的实施方式不同的是，本实施方式可以在内圈10的一端的外表面开设有供卡圈50卡持的卡持槽100。当内圈10插设在负载保持架30内后， 先将挡圈60套设在内圈10上，再将卡圈50卡入卡持槽100，保持架主体31在轴向上受挡圈60阻挡而实现轴向限位。
本发明的负载保持架可以保证负载在传动过程中始终保持轴向的高精确的平行度，最大限度地避免设备运行过程中了噪音、震动、损伤等的出现，各轴向设置的负载相对于轴心线处于高精度的轴向平行状态，负载在主动轮与从动轮之间的间隙内可以处于自由状的滚动、滚转传递，实现了理想状态的受力，极大地延长了轴承的使用寿命。
以上所述仅是本申请的具体实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本申请原理的前提下，还可以做出若干改进和润饰，这些改进和润饰也应视为本申请的保护范围。

Claims (20)

  1. 一种用于保持高负载平行度的负载保持架，其中，包括环形的保持架主体以及安装在所述保持架主体上的弹性的预紧件和间隙保持件，所述间隙保持件为多个，沿所述保持架主体的周向排列地布置在所述保持架主体的内环面或外环面；所述保持架主体的外周面开设有在所述保持架主体周向上间隔设置的多个限位孔，所述限位孔沿所述保持架主体的轴向延伸，以供滚柱状的负载穿过并容纳，每个所述限位孔的内壁固定有至少一个用于沿所述保持架主体的周向上弹性推压所述负载的所述预紧件，所有的所述预紧件沿所述保持架主体的周向上的同一方向推压对应的预紧件。
  2. 根据权利要求1所述的用于保持高负载平行度的负载保持架，其中，每个所述限位孔包括在所述保持架主体的转动方向上相对的第一内壁和第二内壁，所述预紧件设于每个所述限位孔的所述第一内壁且自由端朝向所述第二内壁延伸。
  3. 根据权利要求2所述的用于保持高负载平行度的负载保持架，其中，所述保持架主体的内环面或外环面开设有供所述间隙保持件嵌设的沟槽，所述间隙保持件可滚动地设于所述沟槽内且直径大于所述沟槽深度。
  4. 根据权利要求3所述的用于保持高负载平行度的负载保持架，其中，所述沟槽呈环形，所述间隙保持件在所述沟槽的周向上紧密排列。
  5. 根据权利要求4所述的用于保持高负载平行度的负载保持架，其中，所述沟槽至少为两个，两个所述沟槽在所述保持架主体的轴向上间隔设置。
  6. 根据权利要求5所述的用于保持高负载平行度的负载保持架，其中，所述保持架主体包括两个间隔且正对设置环状的定位环和连接在两个所述定位部之间的多根连接梁，所述沟槽开设在所述定位环的内环面或外环面；相邻的两根所述连接梁之间形成所述限位孔，每根所述连接梁上固定有至少一个所述预紧件。
  7. 根据权利要求6所述的用于保持高负载平行度的负载保持架，其中，所述预紧件为弹片，所述保持架主体的所述连接梁的外表面上开设有两圈间隔的定位槽，所述预紧件的一端卷绕在所述连接梁表面并嵌设在定位槽内，所述预紧件的自由端朝向所述限位孔对侧内壁伸出。
  8. 根据权利要求1所述的用于保持高负载平行度的负载保持架，其中，每个所述限位孔的内壁固定有两个所述预紧件，每个所述限位孔内的两个所述预紧件分别用于在所述保持架主体的轴向上的两个不同部位推压所述负载。
  9. 根据权利要求2所述的用于保持高负载平行度的负载保持架，其中，所述间隙保持件为滚珠或滚柱。
  10. 根据权利要求2所述的用于保持高负载平行度的负载保持架，其中，每个所述限位孔的所述第一内壁与所述第二内壁相互平行。
  11. 一种轴承，其中，包括内圈、外圈、负载和用于保持高负载平行度的负载保持架，所述负载为多个，可滚动地设于所述内圈和所述外圈之间；所述用于保持高负载平行度的负载保持架设于所述内圈和所述外圈之间，包括环形的保持架主体以及安装在所述保持架主体上的弹性的预紧件和间隙保持件，所述间隙保持件为多个，沿所述保持架主体的周向排列地布置在所述保持架主体的内环面或外环面；所述保持架主体的外周面开设有在所述保持架主体周向上间隔设置的多个限位孔，所述限位孔沿所述保持架主体的轴向延伸，以供滚柱状的负载穿过并容纳，每个所述限位孔的内壁固定有至少一个用于沿所述保持架主体的周向上弹性推压所述负载的所述预紧件，所有的所述预紧件沿所述保持架主体的周向上的同一方向推压对应的预紧件；所述间隙保持件可滚动地设置在所述保持架主体与所述内圈外环面之间，或所述保持架主体与所述外圈内环面之间；所述负载容纳于所述限位孔内，且在所述预紧件的作用下弹性抵接所述保持架主体。
  12. 根据权利要求11所述的轴承，其中，每个所述限位孔包括在所述保持架主体的转动方向上相对的第一内壁和第二内壁，所述预紧件设于每个所述限位孔的所述第一内壁且自由端朝向所述第二内壁延伸。
  13. 根据权利要求12所述的轴承，其中，所述保持架主体的内环面或外环面开设有供所述间隙保持件嵌设的沟槽，所述间隙保持件可滚动地设于所述沟槽内且直径大于所述沟槽深度。
  14. 根据权利要求13所述的轴承，其中，所述沟槽呈环形，所述间隙保持件在所述沟槽的周向上紧密排列。
  15. 根据权利要求14所述的轴承，其中，所述沟槽至少为两个，两个所述沟槽在所述保持架主体的轴向上间隔设置。
  16. 根据权利要求15所述的轴承，其中，所述保持架主体包括两个间隔且正对设置环状的定位环和连接在两个所述定位部之间的多根连接梁，所述沟槽开设在所述定位环的内环面或外环面；相邻的两根所述连接梁之间形成所述限位孔，每根所述连接梁上固定有至少一个所述预紧件。
  17. 根据权利要求16所述的轴承，其中，所述预紧件为弹片，所述保持架主体的所述连接梁的外表面上开设有两圈间隔的定位槽，所述预紧件的一端卷绕在所述连接梁表面并嵌设在定位槽内，所述预紧件的自由端朝向所述限位孔对侧内壁伸出。
  18. 根据权利要求11所述的轴承，其中，每个所述限位孔的内壁固定有两个所述预紧件，每个所述限位孔内的两个所述预紧件分别用于在所述保持架主体的轴向上的两个不同部位推压所述负载。
  19. 根据权利要求12所述的轴承，其中，所述间隙保持件为滚珠或滚柱。
  20. 根据权利要求12所述的轴承，其中，每个所述限位孔的所述第一内壁与所述第二内壁相互平行。
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