CN111188832A - Energy efficiency type tapered roller bearing - Google Patents
Energy efficiency type tapered roller bearing Download PDFInfo
- Publication number
- CN111188832A CN111188832A CN202010170165.9A CN202010170165A CN111188832A CN 111188832 A CN111188832 A CN 111188832A CN 202010170165 A CN202010170165 A CN 202010170165A CN 111188832 A CN111188832 A CN 111188832A
- Authority
- CN
- China
- Prior art keywords
- bearing
- inner ring
- roughness
- flange
- tapered roller
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
- 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
-
- 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
- F16C33/34—Rollers; Needles
- F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
- F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones
-
- 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
- F16C33/583—Details of specific parts of races
- F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
-
- 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/50—Crowning, e.g. crowning height or crowning radius
-
- 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/54—Surface roughness
Abstract
The invention relates to an energy efficiency type tapered roller bearing, which is provided with an inner ring, an outer ring, a plurality of rollers and a retainer; the rotation precision of the whole bearing and the form and position tolerance of each part include but are not lower than P6 grade in GB/T307.1, and the roughness of other surfaces is common grade or more except the mutual contact surface of the parts in the bearing; the large flange of the inner ring is a conical surface, and the contact point of the large flange surface and the base surface of the roller ball is the effective length of the flange which is 0.3-0.4 times of the effective length of the flange close to the oil groove; the roughness of the large flange surface is less than or equal to 0.16 mu m; the distance from the small end of the rolling body to the small rib of the inner ring is not more than 0.5 mm. The invention effectively reduces the friction of the bearing and the temperature rise without reducing the rated load.
Description
Technical Field
The invention belongs to the technical field of bearings, and mainly relates to an energy-efficiency tapered roller bearing.
Background
The tapered roller bearing can bear axial force and has large bearing capacity, so that the tapered roller bearing is often applied to industries such as automobiles, rail transit, metallurgical machinery and the like. Along with the gradual maturity of materials and processing technologies, the bearing capacity of the bearing is difficult to be greatly improved at the current stage, so the bearing gradually develops towards other performances, wherein the reduction of friction and the improvement of energy efficiency are important development directions, and the purposes of energy source saving, pollution reduction and green manufacturing are all energy efficiency type bearings; the bearing has more detailed dimensions and data, can be considered as a bearing of a special model, lacks universality, and the data can not be applied to tapered roller bearings of different dimensions.
Disclosure of Invention
In order to solve the technical problems, the invention aims to provide an energy-efficiency type tapered roller bearing.
The purpose of the invention can be realized by adopting the following technical scheme:
an energy efficiency type tapered roller bearing comprises an inner ring, an outer ring, a plurality of rollers and a retainer; the rotation precision of the whole bearing and the form and position tolerance of each part include but are not lower than P6 grade in GB/T307.1, and the roughness of other surfaces is normal grade or more except the mutual contact surfaces of the parts in the bearing.
The roller form and position tolerance of the energy-efficiency type tapered roller bearing is not lower than the II-level regulation in GB/T25767; the roughness of the rolling surface and the roughness of the ball base surface are less than or equal to 0.16 mu m; the radius of the spherical base surface is 0.83-0.85 times of the radius of the arc flange, and the tolerance is-0.02 times of the radius of the spherical base surface to 0;
the large flange of the inner ring is a conical surface, and the roughness of the rolling surface is in accordance with the specification of not less than P5 level; the contact point of the large flange surface and the base surface of the roller ball is 0.3-0.4 times of the effective length of the flange close to the oil groove; the roughness of the large flange surface is less than or equal to 0.16 mu m; the distance from the small end of the rolling body to the small flange of the inner ring is not more than 0.5mm;
the inner ring, the outer ring and the rolling body are subjected to convexity modification, and the convexity uses logarithm shape in common arc shape, modified linear shape and logarithm shape, so that the contact fatigue life of the bearing can be ensured. The shape modification equation is a classic Lundberg logarithmic curve equation:
according to the energy-efficiency tapered roller bearing provided by the invention, through the implementation of the technical means, the main parameters of the tapered roller bearing are the same as the original structure, so that the rated load is not reduced, but the starting friction torque and the running torque are both reduced, the heat generation of the bearing is reduced due to the lower friction, the higher rotating speed is allowed, and the bearing performance is improved.
Drawings
Fig. 1 is a schematic view of an energy-efficient tapered roller bearing of the present invention.
Fig. 2 is a schematic view of the rolling elements of the present invention.
Fig. 3 is a schematic view of the inner ring of the present invention.
Figure 4 is a schematic view of the outer race of the present invention.
Fig. 5 and 6 show the variation trend of the friction torque and the service life of the bearing.
In the figure: 1. an outer ring 2, an inner ring 3, a retainer 4 and a rolling body,
half cone angle, SR-radius of spherical base surface, DwLarge end diameter of rolling elements, large L-inner ring stopThe effective length of the edge.
Detailed Description
The invention is described in connection with the drawings and the detailed description.
As shown in fig. 1, the energy-efficient tapered roller bearing includes an outer ring 1, an inner ring 2, a cage 3, and a plurality of rolling elements 4. The external dimension of the bearing is the same as that of the traditional bearing, so that the use interchangeability is ensured. The contact angle, the size and the number of the rolling elements of the bearing are the same as those of the traditional bearing, so that the rated dynamic load Cr of the bearing is ensured to be the same as that of the traditional bearing. Because the traditional bearing is optimally designed by taking the maximum rated load Cr as an objective function, the energy-efficiency bearing also ensures the maximum rated load Cr. However, unlike conventional bearings, the rotational accuracy of the bearing as a whole and the form and position tolerances of the individual parts include but are not less than class P6 in GB/T307.1, and the roughness of the other surfaces, except for the mutual contact surfaces of the parts inside the bearing, includes but is not less than class P6. The contact surface is a friction surface, and besides the integral precision of the bearing is improved, special measures are required to be taken to reduce the friction torque of the bearing so that the bearing has energy-efficiency performance.
As shown in fig. 2, since the rolling surface and the ball base surface of the roller are contact surfaces, the rolling element of the energy-efficient tapered roller bearing has the following characteristics: the processing technology of the existing bearing is greatly improved, so the form and position tolerance of the specified roller is not lower than the II-grade specification in GB/T25767; the roughness of the rolling surface and the roughness of the ball base surface are less than or equal to 0.16 mu m; in addition to the improvement of roughness, the ball base surface of the roller and the large flange of the inner ring are in ball-cone contact, according to the Hertz contact theory, the ball surface contact forms point contact, the smaller the contact area is, the smaller the friction is, therefore, the energy efficiency type ball base surface radius is 0.83-0.85 times of the arc flange radius, different from the traditional arc flange with the ball base surface radius SR of 0.95 times, so that the radius of the ball base surface of the roller is reduced, and the formed contact point area is reduced. Due to the limitation of processing and detecting capabilities, the value error of the radius of the spherical base surface is large, but the processing error of the radius of the spherical base surface is strictly controlled when the tolerance of the energy-efficient bearing is regulated to be-0.02 times of the radius of the spherical base surface to be 0. At this time, under the condition that the contact area is smaller and the roughness of the contact surface is better, a better lubricating oil film is formed according to the lubricating theory, and the friction coefficient of the contact surface is reduced in the bearing operation process.
As shown in fig. 3, the inner ring of the energy-efficient tapered roller bearing has the following characteristics: the rolling surface is a contact surface, so the specified roughness should meet the specification of not less than P5 level; the large rib of the inner ring is a conical surface and is contacted with the base surface of the ball of the roller, the traditional design is that a contact point is in the middle of the large rib, the distance between the contact point and the outer side edge and the inner side oil groove of the large rib is equal, but after the test, the contact point is considered to be inward, so that the friction can be reduced, and the contact ellipse formed by extrusion after being stressed is broken by the oil groove due to too inward direction. The method is characterized in that the contact point of the ball base surface of the roller is set to be the effective length L of the flange which is 0.3-0.4 times of the effective length L of the flange close to the oil groove, the effective length L is different from the effective length L of the flange which is 0.5 times of the effective length L of the flange of the conventional design, and the large flange cone value can be calculated after the radius SR of the ball base surface of the roller is. Meanwhile, in order to limit the skew angle of the rolling body, the distance from the small end of the rolling body to the small flange of the inner ring is not more than 0.5 mm. By the measures, the contact between the ball base surface of the roller and the spherical surface formed by the large rib of the inner ring is in a better state, the roughness of the contact surface is further improved at the moment, and better lubrication is formed, so that the roughness of the large rib surface is less than or equal to 0.16 mu m.
As shown in fig. 4, the outer ring of the energy-efficient tapered roller bearing has the following characteristics: the outer ring has only rolling surfaces in contact with the rollers, so that the rolling surface roughness complies with the specification of no less than class P5.
The integral rotation precision, the non-contact surface and the contact surface of the bearing are respectively regulated, the non-contact surface only needs to follow the common level, and the precision of the main machine used by the bearing is properly improved, so that the bearing is at the common level or above, the contact surface is the main innovation point of the invention, and the measures are mainly used for optimizing and improving the roughness of the contact surface, the base surface of the roller ball and the contact point of the large flange of the inner ring. In addition, the contact surface needing to be improved is the contact between the roller and the inner and outer ring raceways, and the tapered roller bearing is in line contact, which is different from point contact. In the field of traditional bearings, rollers are generally subjected to convexity modification to improve contact stress and prolong the service life of the bearings, and the inner ring and the outer ring are not modified. Common modifications include circular arcs, modified linear shapes, and logarithmic shapes, where logarithmic shapes are preferred but are limited in processing. From the perspective of reducing friction, the smaller the contact area, the lower the friction, so that the energy-efficient bearing provided by the invention comprehensively considers that the rolling surfaces of the roller, the inner ring and the outer ring are modified, the contact area is reduced, and meanwhile, the requirement on the service life is considered, and the ideal logarithmic form is adopted for modification. Therefore, the inner ring, the outer ring and the rolling body are subjected to convexity modification, and the modification equation is a classical Lundberg logarithmic curve equation:
since the amount of convexity affects not only the bearing friction but also the bearing life, the effect of a change in the amount of convexity on the bearing is illustrated below by way of example.
Taking a single-row tapered roller bearing of a certain type as an example, the bearing parameters are that the inner diameter is 88.9mm, the outer diameter is 152.4mm, the width is 39.688mm, and the rated dynamic load is Cr =248 KN. And (3) applying axial force Fa =1000N, radial force 50KN and digital simulation under the working condition of rotating speed of 100rpm to the bearing. Other parameters of the bearing are kept unchanged, when different convexity amounts (different design loads W are taken), the W taking value in the convexity equation is shown in table 1, the friction torque and service life values of the bearing are shown in tables 2 and 3, and the change trend is shown in fig. 5 and 6.
As can be seen from fig. 5 and 6, the increase in the amount of convexity (increase in the value of W) of each part reduces the friction torque at the rate of the largest roller, then the inner ring, and then the outer ring. And for the influence on the service life of the bearing, the influence of the outer ring is minimum, the influence of the change of the convexity on the service life is not large, the design load W of the convexity of the outer ring is recommended to be not less than 0.3Cr, the influence on the service life is small, and the friction is also properly reduced. The service life change trends of the inner ring and the roller are obvious, the service life of the bearing is longest near 0.1Cr, the service life of the bearing is rapidly reduced after the service life is larger than 0.1Cr, the reduction trends of the two lines are almost the same, the friction torque of the inner ring is considered to be reduced slowly, if a large convexity is taken, the service life influence is too obvious and the friction influence is small, so the value of the design load W of the convexity of the inner ring is not larger than 0.2Cr, the service life of the roller and the reduction of a friction curve are fast, and the value of the design load W is not larger than 0.3Cr in comprehensive consideration.
According to the rules, optimization and improvement are carried out on a certain type of bearing, samples are 5 sets of new and old bearings, and practical tests are carried out. The test equipment is self-developed equipment by my unit. The bearing improvement section includes:
| bearing parameters | Original bearing | Improved bearing |
| Bearing rotation accuracy | Stage P0 | Stage P5 |
| Radius of ball base surface of roller | 270mm (coefficient 0.95) | 240mm (coefficient 0.84) |
| Radius tolerance of sphere base | ±10mm | （-5~0）mm |
| Value of flange inclination angle | 89 degree 46'35 "(contact point 0.5 times effective length of flange) | 89 degree 46'35 "(contact point 0.4 times effective length of flange) |
| Roughness of spherical basal plane | Ra0.32 | Ra0.16 |
| Roughness of the edge surface | Ra0.5 | Ra0.16 |
| Convexity of rolling body | Circular arc shape, design load 0.2Cr | Logarithmic shape, design load 0.2Cr |
| Camber of outer ring raceway | Is free of | Logarithmic shape, design load 0.4Cr |
| Convexity of inner ring raceway | Is free of | Logarithmic shape, design load 0.2Cr |
The test results are shown in the following table
The starting torque is reduced by more than 16% and the friction torque is reduced by more than 18% from the test data. Because the test state is free of lubricant, the bearing is in dry friction, and the friction torque is further reduced when the machine is used.
The technology such as precision requirement, contact point position, logarithmic convexity design load and the like has universality, and is also suitable for single-row, double-row and four-row tapered roller bearings and tapered roller bearings with wide sizes. The bearing retainer part is not involved in the measure, so the method is also applicable to bearings of all retainer structures.
Through the special measures on the non-contact surface, the contact surface and the overall precision of the bearing, the starting friction torque and the running friction torque of the bearing can be effectively reduced, and the bearing has a wide application prospect in low-friction-requirement industries such as automobiles and motors and the heavy machinery industry needing temperature rise reduction.
The invention is not detailed in the prior art.
Claims (4)
1. An energy efficiency type tapered roller bearing comprises an inner ring, an outer ring, a plurality of rollers and a retainer; the method is characterized in that: the rotation precision of the whole bearing and the form and position tolerance of each part include but are not lower than P6 grade in GB/T307.1, and the roughness of other surfaces is common grade or more except the mutual contact surface of the parts in the bearing; the large flange of the inner ring is a conical surface, and the contact point of the large flange surface and the base surface of the roller ball is the effective length of the flange which is 0.3-0.4 times of the effective length of the flange close to the oil groove; the roughness of the large flange surface is less than or equal to 0.16 mu m; the distance from the small end of the rolling body to the small rib of the inner ring is not more than 0.5 mm.
2. An energy-efficient type tapered roller bearing according to claim 1, characterized in that: the roller form and position tolerance of the energy-efficiency type tapered roller bearing is not lower than the II-level regulation in GB/T25767; the roughness of the rolling surface and the roughness of the ball base surface are less than or equal to 0.16 mu m; the radius of the spherical base surface is 0.83-0.85 times of the radius of the arc flange, and the tolerance is-0.02 times of the radius of the spherical base surface to 0.
3. An energy-efficient type tapered roller bearing according to claim 1, characterized in that: the large flange of the inner ring is a conical surface, and the roughness of the rolling surface is in accordance with the specification of not less than P5 grade.
4. An energy-efficient type tapered roller bearing according to claim 1, characterized in that: the inner ring, the outer ring and the rolling body are subjected to convexity modification, and the convexity uses logarithm shape in common arc shape, modified linear shape and logarithm shape, so that the contact fatigue life of the bearing can be ensured. The shape modification equation is a classic Lundberg logarithmic curve equation:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010170165.9A CN111188832A (en) | 2020-03-12 | 2020-03-12 | Energy efficiency type tapered roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010170165.9A CN111188832A (en) | 2020-03-12 | 2020-03-12 | Energy efficiency type tapered roller bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111188832A true CN111188832A (en) | 2020-05-22 |
Family
ID=70704104
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010170165.9A Pending CN111188832A (en) | 2020-03-12 | 2020-03-12 | Energy efficiency type tapered roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111188832A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109296633A (en) * | 2018-11-27 | 2019-02-01 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | High-power, energy-saving compressor tapered roller bearing |
| CN112036055A (en) * | 2020-07-15 | 2020-12-04 | 成都飞机工业（集团）有限责任公司 | Cone fit part tolerance distribution method based on simulation technology |
| CN112643408A (en) * | 2020-12-23 | 2021-04-13 | 中国航发哈尔滨轴承有限公司 | Anti-deflection starter bearing and manufacturing method of roller thereof |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4016492A1 (en) * | 1989-05-22 | 1990-11-29 | Koyo Seiko Co | RADIAL ROLLER BEARING |
| JPH0575520U (en) * | 1992-03-19 | 1993-10-15 | 光洋精工株式会社 | Tapered roller bearing |
| CN203257879U (en) * | 2013-05-28 | 2013-10-30 | 哈尔滨新哈精密轴承股份有限公司 | Inner-ring rib-free unangular-outer-ring double-rib oil groove and oil hole free precise bearing |
| CN104105894A (en) * | 2013-01-25 | 2014-10-15 | 日本精工株式会社 | Tapered roller bearing |
| WO2018181174A1 (en) * | 2017-03-28 | 2018-10-04 | Ntn株式会社 | Tapered roller bearing |
| WO2018181317A1 (en) * | 2017-03-28 | 2018-10-04 | Ntn株式会社 | Tapered roller bearing |
| CN109661522A (en) * | 2016-09-06 | 2019-04-19 | Ntn株式会社 | Tapered roller bearing |
| CN110312875A (en) * | 2017-02-21 | 2019-10-08 | Ntn株式会社 | Tapered roller bearing |
| CN110325748A (en) * | 2017-02-20 | 2019-10-11 | Ntn株式会社 | Tapered roller bearing |
| CN110494664A (en) * | 2017-04-12 | 2019-11-22 | 日本精工株式会社 | Tapered roller bearing |
-
2020
- 2020-03-12 CN CN202010170165.9A patent/CN111188832A/en active Pending
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4016492A1 (en) * | 1989-05-22 | 1990-11-29 | Koyo Seiko Co | RADIAL ROLLER BEARING |
| JPH03113U (en) * | 1989-05-22 | 1991-01-07 | ||
| JPH0575520U (en) * | 1992-03-19 | 1993-10-15 | 光洋精工株式会社 | Tapered roller bearing |
| CN104105894A (en) * | 2013-01-25 | 2014-10-15 | 日本精工株式会社 | Tapered roller bearing |
| CN203257879U (en) * | 2013-05-28 | 2013-10-30 | 哈尔滨新哈精密轴承股份有限公司 | Inner-ring rib-free unangular-outer-ring double-rib oil groove and oil hole free precise bearing |
| CN109661522A (en) * | 2016-09-06 | 2019-04-19 | Ntn株式会社 | Tapered roller bearing |
| CN110325748A (en) * | 2017-02-20 | 2019-10-11 | Ntn株式会社 | Tapered roller bearing |
| CN110312875A (en) * | 2017-02-21 | 2019-10-08 | Ntn株式会社 | Tapered roller bearing |
| WO2018181174A1 (en) * | 2017-03-28 | 2018-10-04 | Ntn株式会社 | Tapered roller bearing |
| WO2018181317A1 (en) * | 2017-03-28 | 2018-10-04 | Ntn株式会社 | Tapered roller bearing |
| CN110494664A (en) * | 2017-04-12 | 2019-11-22 | 日本精工株式会社 | Tapered roller bearing |
Non-Patent Citations (2)
| Title |
|---|
| 李伟伟、陈晓阳、沈雪瑾: "修型量理论对数凸型方程的数值求解及滚子受力分析", 《中国机械工程》 * |
| 李国栋，张东亮，谢兴会，范强，贾松阳: "圆锥滚子轴承内圈大挡边接触和设计探讨", 《煤矿机械》 * |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109296633A (en) * | 2018-11-27 | 2019-02-01 | 瓦房店轴承集团国家轴承工程技术研究中心有限公司 | High-power, energy-saving compressor tapered roller bearing |
| CN112036055A (en) * | 2020-07-15 | 2020-12-04 | 成都飞机工业（集团）有限责任公司 | Cone fit part tolerance distribution method based on simulation technology |
| CN112643408A (en) * | 2020-12-23 | 2021-04-13 | 中国航发哈尔滨轴承有限公司 | Anti-deflection starter bearing and manufacturing method of roller thereof |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN111188832A (en) | Energy efficiency type tapered roller bearing | |
| US20090016664A1 (en) | Tapered roller bearing | |
| US9593718B2 (en) | Multipoint contact ball bearing | |
| CN101520071B (en) | Tapered roller bearing with high strength and low friction torque | |
| CN100366932C (en) | Cylindrical roller with logarithmic curve | |
| US9011018B2 (en) | Roller bearing | |
| CN201347963Y (en) | Bidirectional thrust conical roller bearing | |
| CN100472079C (en) | Roller thrust bearing | |
| US20100183256A1 (en) | Angular ball bearing | |
| CN201106625Y (en) | Locating bearing for high speed aluminium foil mill | |
| CN207961267U (en) | A kind of high-wearing feature self-aligning roller bearing | |
| WO2021109581A1 (en) | Ball retainer and angular contact ball bearing | |
| CN203404247U (en) | High-load full-capacity self-aligning roller bearing | |
| US10197094B2 (en) | Double-row spherical roller bearing | |
| CN101586610A (en) | Conical roller bearing with low friction moment | |
| CN111946736B (en) | Tapered roller bearing | |
| CN201487049U (en) | Tapered roller bearing with high strength and low frictional moment | |
| CN111140598A (en) | Shape-modifying roller of self-aligning bearing for wind power equipment | |
| CN203202015U (en) | Double-row cylindrical roller bearing for numerically-controlled machine tool main shaft | |
| CN207830362U (en) | A kind of double-row bearing | |
| CN216241834U (en) | Low-noise low-friction ball bearing | |
| CN113631821A (en) | Tapered roller bearing | |
| JPH109255A (en) | Angular ball bearing for supporting ball screw | |
| CN218152004U (en) | High-speed rail bearing | |
| CN216951281U (en) | Needle bearing |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20200522 |