WO2010094166A1 - 高速纯滚动轴承 - Google Patents

高速纯滚动轴承 Download PDF

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Publication number
WO2010094166A1
WO2010094166A1 PCT/CN2009/001277 CN2009001277W WO2010094166A1 WO 2010094166 A1 WO2010094166 A1 WO 2010094166A1 CN 2009001277 W CN2009001277 W CN 2009001277W WO 2010094166 A1 WO2010094166 A1 WO 2010094166A1
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WO
WIPO (PCT)
Prior art keywords
rolling
ring
bearing
rolling element
positioning
Prior art date
Application number
PCT/CN2009/001277
Other languages
English (en)
French (fr)
Inventor
林融
Original Assignee
Lin Rong
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Lin Rong filed Critical Lin Rong
Publication of WO2010094166A1 publication Critical patent/WO2010094166A1/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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/37—Loose spacing bodies
    • F16C33/3713—Loose spacing bodies with other rolling elements serving as spacing bodies, e.g. the spacing bodies are in rolling contact with the load carrying rolling elements
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/20—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows with loose spacing bodies, e.g. balls, between the bearing balls
    • 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
    • F16C19/40—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 with loose spacing bodies between the 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly with a single row 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
    • 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
    • F16C19/364—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone

Definitions

  • the present invention relates to a bearing, and more particularly to an idle speed pure rolling bearing without a cage, without sliding friction between the inner ring, the outer ring and the main rolling element.
  • the traditional bearing is mainly composed of the outer ring, the inner ring, the rolling element and the cage.
  • the cage design of different types of bearings has different technical reference values, but no matter which kind of cage, the clearance between the bearing and the rolling elements is relatively large, the bearing is in the idle speed and the shifting motion, the rolling elements are Strolling "dancing" in the cage. When the clearance is small, the rolling element will have a physical elastic deformation when the bearing load is large, which will cause a "catch” phenomenon between the rolling element and the cage.
  • bearings have been produced by using a rolling element (or a positioning rolling element) instead of a cage.
  • a rolling element or a positioning rolling element
  • the pure rolling bearing of the Chinese invention patent of the public number CN1301926A the number is CN101101021A.
  • the pure rolling bearing involved in the Chinese invention patent and the low-wear super-rolling bearing involved in the Chinese utility model patent No. ZL022607935 form a rolling friction between the rolling element and the main rolling body.
  • the above patents have played a positive role in solving this technical problem, but they also have the following shortcomings:
  • the relative position between the rolling element and the inner and outer rings is not easy to determine. This makes it necessary to design a special positioning ring and positioning groove for the inner ring and the outer ring. When the bearing is working, the rolling element and the positioning ring and the positioning groove are required. There is a sliding friction between them.
  • the distance between the main and the rolling elements is not equal to the central axis of the bearing, which causes the force distribution of the external bearing to be uneven, which is easy to damage the components and reduce the service life of the bearing.
  • the centrifugal force of the main rolling element during idle rotation Inconsistent, it will also cause damage to the outer ring of the bearing.
  • the wear-resistant layer is formed, so that it is resistant to temperature, corrosion, and corrosion.
  • the present invention provides an idle speed pure rolling bearing.
  • the "group coordinate theory”, “gyro theory”, “automatic control theory” and “Newton's” are adopted and borrowed.
  • Three Laws, etc. form three independent rotating bodies of "bearing sleeve bearings", and rolling friction is formed between the components during movement.
  • the bearing is composed of an outer ring, an inner ring and a main rolling element as main power transmission components, and a flower-shaped rotating body formed by a rolling element and a positioning ring at both ends replaces the original designed cage. All parts are sprayed and sintered by nano- and rare earth materials to form a wear-resistant layer.
  • an idle speed pure rolling bearing comprising: an outer ring, an inner ring, a plurality of main rolling bodies, a plurality of rolling elements and a positioning ring; the main rolling body is arranged on the outer ring and In the groove between the inner rings, a rolling element is disposed between two main rolling bodies; a positioning ring is respectively disposed at two ends of the rolling element; and the positioning ring has a section a ring-shaped body of a rectangular tube, a slit groove is formed at an inner end of the rectangular tube; a small stepped column is respectively formed at both ends of the rolling element, and the small stepped column is smoothly fitted and inserted in the open groove;
  • the rolling element and the positioning ring at both ends constitute an independent flower-shaped rotating body, and the rotating body is concentric with the inner and outer rings; the middle portion of the rolling element is always in line contact with the adjacent two main rolling bodies. There is no contact with the outer ring and the inner ring at all; the positioning ring is only connected
  • the rotating body composed of the rolling element and the positioning ring, wherein the rolling element rotates, and revolves around the bearing center together with the positioning ring; when the rotating body revolves, the center line of the rolling element is The radius of gyration is equal to the radius of gyration of the center line when the main rolling element revolves.
  • the length of the rotating body composed of the rolling element and the positioning ring that is, the distance between the outer end faces of the two positioning rings is slightly smaller than the thickness of the outer ring and the inner ring.
  • the outer ring, the inner ring, the main rolling element, the rolling element and the surface of the positioning ring are all sprayed and sintered by a nanometer, a rare earth ceramic material or the like to form a wear layer.
  • the shape of the main rolling body can be made into a cylinder, a sphere, a cone, and respectively constitute a roller bearing, a ball bearing, a tapered roller bearing; an inner groove and an inner ring of the outer ring matched with the same
  • the outer groove also has corresponding rectangular, semi-circular, trapezoidal grooves, etc.; wherein the shape of the rolling element in the roller bearing and the ball bearing is a cylinder, and the shape of the tapered roller bearing rolling element is a cone body.
  • the number of the main rolling elements and the rolling elements are all even values.
  • the main and the rolling elements are even numbers, so that the direction of revolution and rotation is the same, avoiding the sliding friction between the rolling elements, and at the same time making the rotation speed of the bearing faster.
  • the inner and outer rings have high concentricity, small radial runout, higher bearing speed, better concentricity, and the effect of automatically adjusting the concentricity. At the same time, the vibration of the bearing is smaller and the noise is smaller.
  • All parts of the bearing are sprayed and sintered by nano- and rare earth materials to form a wear-resistant layer, which makes the friction resistance small, the temperature rise is low, and the wear resistance is better.
  • Figure 1 is a schematic structural view of the present invention
  • Figure 2 is a cross-sectional view taken along line A-A of Figure 1;
  • FIG. 3 is a schematic structural view of a ball bearing in an embodiment of the present invention.
  • FIG. 4 is a schematic structural view of a tapered roller bearing according to an embodiment of the present invention.
  • outer ring 1, outer ring, 2, inner ring, 3, main rolling body, 4, rolling element, 4-1, small step column, 5, positioning ring, 5-1, open slot.
  • the idle rolling bearing of the present invention mainly comprises: outer ring 1, inner ring 2, multiple main rolls The moving body 3, the plurality of rolling elements 4 and the positioning ring 5; the main rolling body 3 is disposed in the groove between the outer ring 1 and the inner ring 2, and the rolling is arranged between the two main rolling bodies 3 a positioning ring 5 is disposed at each end of the rolling element 4; the positioning ring 5 is preferably a circular body of a rectangular tube, and an open groove 5-1 is formed at an inner end of the rectangular tube;
  • the small stepped column 4-1 is respectively formed on both ends of the rolling element 3, and the small stepped column 4-1 is slip-fitted and inserted in the opening groove 5-1;
  • the positioning ring 5 constitutes an independent flower-shaped rotating body, and the rotating body is concentric with the inner and outer rings 2, 1; the middle portion of the rolling element 4 is always in line contact with the adjacent two main rolling bodies 3, However, there is no contact between the outer ring 1 and the inner ring 2; the positioning ring 5 is only
  • the two adjacent main rolling bodies 3 and the rolling elements 4 are in point contact or line contact state, the relative movement speed difference of the contact points is zero, and the relative movement speed difference of the indirect contacts of the rolling element 4 positioning ring 5 is also Zero, thereby ensuring the axial positioning and radial positioning of the rolling elements in the bearing, and at the same time, the rolling elements in the actual use process are not easy to fall off when the bearing moves, and the high-speed pure rolling bearing of the invention can be realized completely. It requires grease to lubricate it. Its biggest features are: high speed, heavy load, safety and energy saving.
  • the rotating body composed of the rolling element 4 and the positioning ring 5, wherein the rolling element 4 rotates at the same time, and revolves around the center of the bearing ring 5; when the rotating body revolves, the rolling element 4
  • the radius of gyration of the center line is equal to the radius of gyration of the center line when the main rolling element 3 revolves.
  • load energy transfer, feedback return and load can be achieved when the moving object is under pressure. The effect of the burden. Therefore, the new structural design greatly increases the load capacity of the original bearing.
  • the length of the rotating body composed of the rolling element 4 and the positioning ring 5, that is, the distance between the outer end faces of the two positioning rings 5 is slightly smaller than the thickness of the outer ring 1 and the inner ring 2.
  • the outer ring 1, the inner ring 2, the main rolling element 3, the rolling element 4 and the positioning ring 5 are all sprayed and sintered by a nano-, rare earth ceramic material to form a wear-resistant layer.
  • the shape of the main rolling body 1 can be made into a cylinder, a sphere, a cone, and respectively constitute a roller bearing, a ball bearing, a tapered roller bearing, and an inner groove and an inner ring 2 of the outer ring 1 matched with the same
  • the outer groove also has corresponding rectangular, semi-circular, trapezoidal grooves, etc.; wherein the shape of the rolling element 4 in the roller bearing and the ball bearing is a cylinder, and the shape of the tapered roller bearing is the rolling element 4. It is a cone.
  • the number of the main rolling elements 3 and the rolling elements 4 is an even value.
  • Main rolling element 3, outer ring 1 or the inner ring 2 has the same rolling direction, and under the action of the same rolling frictional force of the main rolling body 3 and the inner ring 2 or the outer ring 1, the rotational speed of the bearing is greatly accelerated and lifted, thereby The speed of the original bearing has been greatly improved. Therefore, the rotational speed of the idle pure rolling bearing is greatly reduced by the limit speed of the same type of modern ordinary bearing with a cage.

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

Description

高速纯滚动轴承
技术领域
本发明涉及一种轴承， 具体涉及一种不设保持架， 内圈、外圈与主滚动体之 间没有滑动摩擦的髙速纯滚动轴承。
背景技术
传统轴承主要是由外圈、 内圏、滚动体和保持架所组成。不同类型的轴承的 保持架的设计，有着不同的技术参考值， 但不论哪一种保持架，其和滚动体之间 的游隙都比较大， 轴承在髙速、 变速运动时， 滚动体在保持架中逛荡 "跳舞"。 当其游隙小时，滚动体在轴承负载大时，会产生物理性的弹性形变， 使滚动体和 保持架之间会发生 "卡死"现象。
轴承在高速运转工作时，其摩擦力主要来自于滚动体和保持架之间运动时的 滑动摩擦。在轴承高速运动时， 保持架和滚动体所产生的离心力， 使得其滑动摩 擦力急剧增大， 从而引起轴承的温度升高、 震动加大、 噪声增大， 润滑"失油", 磨损严重， 最终导致轴承严重损坏， 以至无法使用。
为了解决上述技术问题， 近几年出现了用付滚动体（或称定位滚动体）代替 保持架制作的轴承， 例如公幵号为 CN1301926A的中国发明专利涉及的纯滚动 轴承、么^幵号为 CN101101021A的中国发明专利涉及的纯滚动轴承以及专利号为 ZL022607935的中国实用新型专利涉及的低磨损超级滚动轴承等，付滚动体与主 滚动体之间形成滚动摩擦。 上述专利在解决该技术问题时起到了一定的积极效 果， 但也存在如下不足之处：
1、 付滚动体与内、 外圈之间的相对位置不易确定， 这使得需要对内圈和外 圈设计专门的定位环和定位槽， 轴承在工作时，付滚动体与定位环、定位槽之间 产生滑动摩檫。
2、 主、 付滚动体距轴承的中心轴线的距离不相等， 这造成承载外部作用的 力分布不均匀，从而容易损伤部件并降低轴承的使用寿命；此外主付滚动体在髙 速转动时离心力不一致， 也会造成损伤轴承外圈。
3、 由于没有用納米、稀土陶瓷材料等对上述专利中的轴承外圈、 内圈、主、 付滚动体的表面进行喷射、烧结处理以形成耐磨层， 所以其耐髙温、耐腐蚀、抗
确 认 本 氧化等性能不好， 在恶劣的环境下工作的综合性能不强。 发明内容
为了解决上述技术问题，本发明提供一种髙速纯滚动轴承，在轴承设计原理 和设计理论上， 采用和借鉴了 《群坐标理论》、 《陀螺仪理论》、 《自动控制理论》 和《牛顿第三定律》等， 形成了 "轴承套轴承"的三个独立的转动体， 各部件之 间在运动时均形成滚动摩擦。该轴承由外圈、 内圈、主滚动体作为主要动力传动 部件， 由付滚动体和两端的定位环形成的花栏形回转体， 取代原设计的保持架。 全部零部件经过纳米、 稀土等材料喷射、 烧结制作成耐磨层。
本发明是通过如下技术方案实现的；一种髙速纯滚动轴承， 包括； 外圈、 内 圈、多只主滚动体、多只付滚动体及定位环； 所述的主滚动体设置在外圈与内圈 之间的凹槽中，相临两只主滚动体之间设置付滚动体；所述的付滚动体两端分别 设置一只定位环； 其特征在于： 所述的定位环， 其断面为矩形管的环行体， 矩形 管的内端制作幵口槽；所述的付滚动体两端分别制作小台阶柱，所述的小台阶柱 滑配合插装在所述的开口槽中；多只付滚动体与两端的定位环组成独立的花栏形 回转体， 该回转体与内、外圈同圆心；所述的付滚动体的中部始终与相临的两只 主滚动体保持线接触， 而与外圈、 内圈之间完全不接触； 所述的定位环仅仅与付 滚动体两端连接， 而与外圈、 内圈之间完全不接触。
优选地,所述的付滚动体与定位环组成的回转体，其中付滚动体自转的同时， 还与定位环一同绕轴承中心公转；所述的回转体公转时，其付滚动体中心线的回 转半径与主滚动体公转时中心线的回转半径相等。
优选地，所述的付滚动体与定位环组成的回转体， 其长度， 即两只定位环外 端面之间的距离略小于外圈和内圈的厚度。
优选地， 所述的外圈、 内圈、 主滚动体、 付滚动体及定位环表面均用纳米、 稀土陶瓷材料等经过喷射、 烧结处理形成耐磨层。
优选地， 所述的主滚动体的形状可以制作成圆柱体、球体、 圆锥体形， 分别 组成滚柱轴承、滚珠轴承、 圆锥滚柱轴承； 与之相配合的外圈的内沟槽、 内圈的 外沟槽也随之制作相对应的矩形、 半圆形、梯形沟槽等； 其中滚柱轴承、滚珠轴 承中付滚动体的形状为圆柱体， 圆锥滚柱轴承付滚动体的形状为圆锥体。 优选地， 所述的主滚动体、 付滚动体的数量均为偶数值。
本发明的积极效果是：
1、 不设保持架， 避免各部件之间的滑动摩擦， 部件之间均形成滚动摩擦， 表面进行耐磨处理， 使轴承使用寿命更高、 耐磨性、 安全性能更好。
2、 轴承在负荷不均匀时， 各主、付滚动体将受力均匀分摊， 使之受力均匀， 从而大大地提髙轴承整体的负荷力， 轴承的负荷增大。
3、 主、 付滚动体均为偶数， 使之公转与自转的方向相同， 避免滚动体之间 的滑动摩擦， 同时使得轴承的转速更快。
4、 内、 外圈的同心度高， 径向跳动量小， 轴承转速越高， 同心度越好， 并 实现了自动调整同心度的作用。 同时使轴承的震动更小、 噪音更小。
5、 轴承 DN值低的问题得到了解决， 同时轴承髙速、 重载运动时能耗低、 故其对于油脂润滑的过度依赖性问题大大地降低。
6、 轴承的全部零部件经过纳米、 稀土等材料喷射、 烧结制作成耐磨层， 从 而使得其摩擦阻力小、 温升低、 耐磨性能更好适用范围更广。
附图说明
下面结合附图， 对本发明的优选实施方式进行描述， 其中，
图 1为本发明的结构示意图；
图 2为图 1的 A— A旋转剖面图；
图 3为本发明一种实施例中的滚珠轴承的结构示意图；
图 4为本发明一种实施例中的圆锥滚柱轴承的结构示意图；
其中附图中的附图标记含义如下：
1、 外圈， 2、 内圈， 3、 主滚动体， 4、 付滚动体， 4-1、 小台阶柱， 5、 定位 环， 5-1、 开口槽。
具体实施方式
容易理解， 根据本发明的技术方案， 在不变更本发明的实质精神下， 本领 域熟悉此项技术的一般技术人员可以提出本发明的多个结构方式。因此以下具体 实施方式以及附图仅是对本发明技术方案的具体说明，而不应当视为本发明的全 部或者视为对本发明技术方案的限定或限制。
参考附图， 本发明的髙速纯滚动轴承主要包括： 外圈 1、 内圈 2、 多只主滚 动体 3、 多只付滚动体 4及定位环 5 ; 所述的主滚动体 3设置在外圈 1与内圈 2 之间的凹槽中， 相临两只主滚动体 3之间设置付滚动体 4; 所述的付滚动体 4两 端分别设置一只定位环 5 ; 所述的定位环 5， 其断面优选为矩形管的环行体， 矩 形管的内端制作开口槽 5-1 ; 所述的付滚动体 3两端分别制作小台阶柱 4-1， 所 述的小台阶柱 4-1滑配合插装在所述的开口槽 5-1中； 多只付滚动体 4与两端的 定位环 5组成独立的花栏形回转体， 该回转体与内、 外圈 2、 1同圆心； 所述的 付滚动体 4的中部始终与相临的两只主滚动体 3保持线接触， 而与外圈 1、 内圈 2之间完全不接触； 所述的定位环 5仅仅与付滚动体 4两端连接， 而与外圈 1、 内圈 2之间完全不接触。两个相邻的主滚动体 3与付滚动体 4间呈点接触或线触 状态，接触点的相对运动速度差为零，付滚动体 4定位环 5间接触点的相对运动 速度差也为零，从而保证了滚动体在轴承内的轴向定位和径向定位， 同时在实际 使用过程中的滚动体当轴承运动时不易发生掉珠现象，并且本发明的高速纯滚动 轴承完全可以实现在不需要油脂对其进行润滑的情况下工作， 其最大的特点是： 高速、 重载、 安全、 节能。
所述的付滚动体 4与定位环 5组成的回转体， 其中付滚动体 4自转的同时， 还与定位环 5—同绕轴承中心公转；所述的回转体公转时，其付滚动体 4中心线 的回转半径与主滚动体 3公转时中心线的回转半径相等。在轴承内由于多个付滚 动体 4和主滚动体 3之间所组成的圆周形结构，根据牛顿第三定律， 当运动物体 在受到压力时可以做到负荷能量传递、反馈回输和负载均担的效果。因此新型的 结构设计使得原有轴承的负荷容量大大地增加和提髙。
所述的付滚动体 4与定位环 5组成的回转体，其长度， 即两只定位环 5外端 面之间的距离略小于外圈 1和内圈 2的厚度。
所述的外圈 1、 内圈 2、 主滚动体 3、 付滚动体 4及定位环 5表面均用纳米、 稀土陶瓷材料等经过喷射、 烧结处理形成耐磨层。
所述的主滚动体 1的形状可以制作成圆柱体、球体、圆锥体形， 分别组成滚 柱轴承、滚珠轴承、 圆锥滚柱轴承； 与之相配合的外圈 1的内沟槽、 内圈 2的外 沟槽也随之制作相对应的矩形、半圆形、梯形沟槽等； 其中滚柱轴承、滚珠轴承 中付滚动体 4的形状为圆柱体， 圆锥滚柱轴承付滚动体 4的形状为圆锥体。
所述的主滚动体 3、 付滚动体 4的数量均为偶数值。 使主滚动体 3 、 外圈 1或内圈 2之间滚动方向相同， 在主滚动体 3与内圈 2或外圈 1接触的同向滚动 摩擦力的作用下，使得轴承的旋转运动速度大大地加快和提髙，从而使得原有轴 承的转速得到了极大地提髙。因此髙速纯滚动轴承的转速大大地髙于带保持架的 同类型现代普通轴承的极限转速。

Claims

权利要求书
1、 一种高速纯滚动轴承， 包括： 外圈 （1 )、 内圈 （2)、 多只主滚动体（3 )、 多只付滚动体 （4) 及定位环 （5); 所述的主滚动体 （3 )设置在外圈 （1 ) 与内 圈 （2)之间的凹槽中， 相临两只主滚动体（3 )之间设置付滚动体（4); 所述的 付滚动体 （4)两端分别设置一只定位环 （5);
其特征在于： 所述的定位环 （5) 的断面为矩形管的环行体， 矩形管的内端 制作开口槽 ( 5-1 )； 所述的付滚动体 (3 ) 两端分别制作小台阶柱 （4-1 )， 所述 的小台阶柱（4-1 )滑动配合插装在所述的开口槽 （5-1) 中； 多只付滚动体 （4) 与两端的定位环 （5) 组成独立的花栏形回转体， 该回转体与内、 外圈 （2、 1 ) 同圆心； 所述的付滚动体（4)的中部始终与相临的两只主滚动体（3 )保持线接 触， 而与外圈 （1 )、 内圈 （2)之间完全不接触； 所述的定位环（5)仅仅与付滚 动体（4)两端连接， 而与外圈 （1 )、 内圈 （2)之间完全不接触。
2、 根据权利要求 1所述的高速纯滚动轴承， 其特征在于： 所述的付滚动体 (4) 与定位环 （5) 组成的回转体， 其中付滚动体（4) 自转的同时， 还与定位 环（5)—同绕轴承中心公转； 所述的回转体公转时， 其付滚动体（4) 中心线的 回转半径与主滚动体 （3) 公转时中心线的回转半径相等。
3、 根据权利要求 2所述的高速纯滚动轴承， 其特征在于： 所述的付滚动体 (4) 与定位环 （5) 组成的回转体的长度， 即两只定位环 （5)外端面之间的距 离， 略小于外圈 （1 ) 和内圈 （2) 的厚度。
4、根据权利要求 1所述的高速纯滚动轴承， 其特征在于： 所述的外圈（1 )、 内圈 （2)、 主滚动体 （3〉、 付滚动体（4)及定位环（5) 的表面均用纳米、 稀土 陶瓷材料进行喷射、 烧结处理， 用以形成耐磨层。
5、 根据权利要求 1所述的髙速纯滚动轴承， 其特征在于 .· 所述的主滚动体 ( 1 ) 的形状可以制作成圆柱体、 球体、 圆锥体形， 分别组成滚柱轴承、 滚珠轴 承、 圆锥滚柱轴承； 与之相配合的外圈（1 ) 的内沟槽、 内圈 （2) 的外沟槽也随 之制作相对应的矩形、半圆形、梯形沟槽； 其中滚柱轴承、滚珠轴承中付滚动体
(4) 的形状为圆柱体， 圆锥滚柱轴承付滚动体 （4) 的形状为圆锥体。
6、根据权利要求 1所述的高速纯滚动轴承， 其特征在于： 所述的主滚动体（3)、 付滚动体 （4) 的数量均为偶数值。
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CN101493115A (zh) * 2009-02-17 2009-07-29 林融 高速纯滚动轴承
CN102102708A (zh) * 2011-03-14 2011-06-22 纽尚(宁波)汽车轴承制造有限公司 防跑偏滚子及应用有该滚子的滚动轴承
CN105485173B (zh) * 2014-09-15 2019-10-25 舍弗勒技术股份两合公司 轴承保持架和包括它的轴承
CN105987074A (zh) * 2015-11-09 2016-10-05 王钢 减速轴承

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