CN103967930A - Cylindrical roller bearing with high axial bearing capacity - Google Patents
Cylindrical roller bearing with high axial bearing capacity Download PDFInfo
- Publication number
- CN103967930A CN103967930A CN201410168840.9A CN201410168840A CN103967930A CN 103967930 A CN103967930 A CN 103967930A CN 201410168840 A CN201410168840 A CN 201410168840A CN 103967930 A CN103967930 A CN 103967930A
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- roller
- inner ring
- rib
- bearing
- cylindrical roller
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Abstract
The invention relates to the technical field of rolling bearings, in particular to a cylindrical roller bearing with high axial bearing capacity, which is used for a main cone guiding support of a main reducer of a drive axle of a truck. The cylindrical roller bearing comprises an outer ring, an inner ring, a full complement cylindrical roller clamped between the outer ring and the inner ring, and a flat check ring arranged on one side of the inner ring and one side of the cylindrical roller. Through the improvement of the strength of the retaining sides and the change of the shape of the retaining side at the contact part of the inner ring of the bearing and the end surface of the roller, the shape of the retaining side at the contact part of the outer ring of the bearing and the end surface of the roller, and the shape of the contacted end surface of the roller, the lubricating condition of the contact area of the retaining side of the inner ring of the bearing and the end surface of the roller and the lubricating condition of the contact area of the retaining side of the outer ring of the bearing and the end surface of the roller are improved to form better elastic dynaflow lubricating, so that the axial bearing capacity can be improved greatly, the breakage of the retaining side of the inner ring can be effectively prevented, and the use failure rate of the product can be reduced.
Description
Technical field
The present invention relates to technical field of rolling bearings, particularly a kind of roller bearing that can be used for the high axial carrying capacity of truck main reducing gear of drive axle main cone guided bearing.
Background technique
At present, in, heavy-load automobile main reducing gear of drive axle main cone guided bearing bearing generally all adopts roller bearing, shown in Fig. 1-Fig. 5.This roller bearing mainly bears radial load in design theory, does not bear thrust load.But in actual use, processing, the assembly precision that is subject to related components is difficult to the impact of the factors such as assurance and automobile overload, road conditions are poor, roller bearing often will bear larger thrust load, cause bearing inner race rib to break, bearing damage, and cause related components to be damaged, have a strong impact on vehicle driving safety.
Summary of the invention
The roller bearing that the object of this invention is to provide a kind of high axial carrying capacity for truck main reducing gear of drive axle main cone guided bearing, it contacts end surface shape with the rib shape of roller end face contact position with roller by changing the inside and outside circle of bearing, improve the lubrication state of the inside and outside circle rib of bearing and roller end face contact area, form good elastohydrodynamic lubrication, thereby can greatly improve axial carrying capacity, effectively prevent that inner ring rib from breaking, reduce the rate of fault that product is used.
Technical solution of the present invention is as described below:
A roller bearing for high axial carrying capacity, it comprises outer ring, inner ring, is located in the full-complement cylinder roller between outer ring and inner ring and is located at inner ring and the loose rib of cylindrical roller one side, it is characterized in that:
On the cross section dissecing along axis at described roller bearing, the rib of outer ring and inner ring is all the rib camber line of dimpling, between the longitudinal section of dissecing along vertical axis at the string of a musical instrument between this rib camber line two-end-point and described roller bearing, there is the rib inclined angle alpha of 0 ° 15 '～0 ° 30 ', and this rib camber line and this mid-chord has the maximum normal distance (also claiming convexity amount) of 2～3 μ m;
On the cross section dissecing along axis at described roller bearing, described cylindrical roller end face is sphere line with the contact position that the rib of outer ring and inner ring contacts, and the actual curvature radius of the sphere line of this cylindrical roller end face is (because the convexity amount of rib camber line is very small with rib tangential, during calculating, be approximately straight line, be equal to the string of a musical instrument) the 90%-95% of roller end face sphere lineation opinion Calculation of curvature radius;
The formula of described roller end face sphere lineation opinion Calculation of curvature radius R is as follows:
R＝(D
we/2-H
1)/sinα，
R: roller end face sphere lineation opinion Calculation of curvature radius;
D
we: the effective diameter of cylindrical roller;
H
1: the point of contact of cylindrical roller end face and rib is to raceway face radial distance;
α: rib tilt angle.
The actual curvature radius of the sphere line of described cylindrical roller end face is preferably and 95% of the roller end face sphere lineation opinion Calculation of curvature radius R of rib tangential.
In addition, in order further to increase rib intensity, improve axial carrying capacity, technique scheme of the present invention is also further improved as follows: between the rib camber line of described inner ring and the raceway bus of inner ring, cancel grinding undercut, change direct linking (being without grinding undercut between the rib camber line of inner ring and the raceway bus of inner ring) into.
Described inner ring raceway bus, outer ring raceway bus and cylindrical roller bus are the logarithmic curve protuberance shape of mutual coupling;
1. the convexity amount of the logarithmic curve protuberance shape of described outer ring raceway bus is 4～7 μ m, and logarithmic curve equation is:
Y
the upper limit=-2.41ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
Y
lower limit=-1.38ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
2. the convexity amount of the logarithmic curve protuberance shape of described inner ring raceway bus is 4～7 μ m, and logarithmic curve equation is:
Y
the upper limit=-2.41ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
Y
lower limit=-1.38ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
3. the convexity amount of the logarithmic curve protuberance shape of described cylindrical roller bus is 5～8 μ m, and logarithmic curve equation is:
Y
the upper limit=-2.31ln (1-0.1125 * 10
-3x-17.22 * 10
-3x
2+ 2 * 10
-6x
3);
Y
lower limit=-1.445ln (1-0.1125 * 10
-3x-17.22 * 10
-3x
2+ 2 * 10
-6x
3).
Compared to prior art, the present invention has the following advantages:
1, roller bearing of the present invention is not in the situation that its boundary dimension changes prior art bearing, in roller bearing, outer ring flange changes the dimpling arc flange with certain angle of inclination into by original straight rib, and change the roller end face of contact with it into sphere, on the cross section dissecing along axis at described roller bearing, described cylindrical roller end face is sphere line with the contact position that the rib of outer ring and inner ring contacts, and the actual curvature radius of the sphere line of this cylindrical roller end face is the 90%-95% with the roller end face sphere lineation opinion Calculation of curvature radius of rib tangential, thereby improved in bearing, the lubrication state of outer ring flange and roller end face contact area, form good elastohydrodynamic lubrication, can improve axial carrying capacity, effectively prevent that inner ring rib from breaking.Compare with prior art bearing, the present invention is meeting under the prerequisite of automobile installation requirement, and axial carrying capacity improves 3 times.
2, roller bearing of the present invention is cancelled original inner ring grinding undercut structure and is changed into without grinding undercut structure, thereby make rib Effective face width increase by 21% (as Fig. 4 and Figure 10 contrast, rib Effective face width is increased to the 4.0mm of Figure 10 by the 3.3mm of Fig. 4), increase rib intensity, improved axial carrying capacity; Can eliminate the larger stress that grinding undercut place exists, while preventing that bearing is subject to external impacts, collision, inner ring rib is broken simultaneously.
3, roller bearing inner ring raceway bus of the present invention, outer ring raceway bus and roller bus are changed into the logarithmic curve protuberance shape that is mutual coupling by original straight line, thereby can eliminate " edge stress ", improve bearing fatigue life.
4, experiment showed, and use roller bearing of the present invention to reduce rate of fault 92.6%, can effectively meet user's usage requirement.
Accompanying drawing explanation
Fig. 1 is the sectional view of the roller bearing of prior art;
Fig. 2 is the outer ring parts drawing of the roller bearing of prior art;
Fig. 3 is the inner ring parts drawing of the roller bearing of prior art;
Fig. 4 is the inner ring rib partial view of the roller bearing of prior art;
Fig. 5 is the cylindrical roller parts drawing of the roller bearing of prior art;
Fig. 6 is the sectional view of roller bearing of the present invention;
Fig. 7 is inner ring rib and the cylindrical roller end contact schematic diagram of roller bearing of the present invention;
Fig. 8 is the outer ring parts drawing of roller bearing of the present invention;
Fig. 9 is the inner ring parts drawing of roller bearing of the present invention;
Figure 10 is the inner ring rib partial view of roller bearing of the present invention;
Figure 11 is the cylindrical roller parts drawing of roller bearing of the present invention;
Figure 12 is that the present invention is for calculating the schematic diagram of roller end face sphere lineation opinion Calculation of curvature radius R.
Number in the figure explanation:
1-outer ring, 2-inner ring, 3-cylindrical roller, 4-loose rib;
2-1: the rib camber line of outer ring and inner ring;
2-2: the string of a musical instrument between the rib camber line two-end-point of outer ring and inner ring;
3-1: the contact position sphere line that cylindrical roller end face contacts with the rib of outer ring and inner ring.
Embodiment
Below in conjunction with Figure of description and specific embodiment, content of the present invention is elaborated:
Embodiment 1
As shown in Fig. 6-Figure 11:
For the roller bearing of a kind of high axial carrying capacity provided by the invention, it comprises outer ring 1, inner ring 2, is located in the full-complement cylinder roller 3 between outer ring 1 and inner ring 2 and is located at inner ring 2 and the loose rib 4 of cylindrical roller 3 one sides, it is characterized in that:
On the cross section dissecing along axis at described roller bearing, the rib of outer ring 1 and inner ring 2 is all the rib camber line 2-1 of dimpling, between the longitudinal section of dissecing along vertical axis at the string of a musical instrument 2-2 between this rib camber line 2-1 two-end-point and described roller bearing, there is the rib inclined angle alpha of 0 ° 15 '～0 ° 30 ', and this rib camber line 2-1 and this string of a musical instrument 2-2 mid point has the maximum normal distance (also claiming convexity amount) of 2～3 μ m;
On the cross section dissecing along axis at described roller bearing, described cylindrical roller 3 end faces are sphere line with the contact position that the rib of outer ring 1 and inner ring 2 contacts, and the actual curvature radius of the sphere line of these cylindrical roller 3 end faces is the 90%-95% of the roller end face sphere lineation opinion Calculation of curvature radius tangent with rib camber line 2-1; Be preferably 95%.According to the 928mm that is designed to of routine, now can be with reference to adopting 881mm, but the present invention is not limited to this size.
Shown in Figure 12, the formula of described roller end face sphere lineation opinion Calculation of curvature radius R is as follows:
R＝(D
we/2-H
1)/sinα，
R: roller end face sphere lineation opinion Calculation of curvature radius;
D
we: the effective diameter of cylindrical roller 3;
H
1: the point of contact of cylindrical roller 3 end faces and rib is to raceway face radial distance;
α: rib tilt angle.
The rib camber line 2-1 of described inner ring 2 is directly connected with the raceway bus of inner ring 2, between the two without grinding undercut structure.
Described inner ring 2 raceway buses, outer ring 1 raceway bus and cylindrical roller 3 buses are the logarithmic curve protuberance shape of mutual coupling;
1. the convexity amount of the logarithmic curve protuberance shape of described outer ring 1 raceway bus is 4～7 μ m, and logarithmic curve equation is:
Y
the upper limit=-2.41ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
Y
lower limit=-1.38ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
2. the convexity amount of the logarithmic curve protuberance shape of described inner ring 2 raceway buses is 4～7 μ m, and logarithmic curve equation is:
Y
the upper limit=-2.41ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
Y
lower limit=-1.38ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
3. the convexity amount of the logarithmic curve protuberance shape of described cylindrical roller 3 buses is 5～8 μ m, and logarithmic curve equation is:
Y
the upper limit=-2.31ln (1-0.1125 * 10
-3x-17.22 * 10
-3x
2+ 2 * 10
-6x
3);
Y
lower limit=-1.445ln (1-0.1125 * 10
-3x-17.22 * 10
-3x
2+ 2 * 10
-6x
3).
Above-mentioned embodiment is just explained in detail technological scheme of the present invention; the present invention has more than and is only confined to above-described embodiment; those skilled in the art should be understood that; the above-mentioned principle of every foundation and the improvement of spirit on basis of the present invention, substitute, all should be within protection scope of the present invention.
Claims (4)
1. the roller bearing of a high axial carrying capacity, it comprises outer ring (1), inner ring (2), is located in the full-complement cylinder roller (3) between outer ring (1) and inner ring (2) and is located at inner ring (2) and the loose rib (4) of cylindrical roller (3) one sides, it is characterized in that:
On the cross section dissecing along axis at described roller bearing, the rib of outer ring (1) and inner ring (2) is all the rib camber line (2-1) of dimpling, be positioned between the longitudinal section that the string of a musical instrument (2-2) between this rib camber line (2-1) two-end-point and described roller bearing dissect along vertical axis and there is the rib inclined angle alpha of 0 ° 15 '～0 ° 30 ', and this rib camber line (2-1) and this string of a musical instrument (2-2) mid point have the maximum normal distance of 2～3 μ m;
On the cross section dissecing along axis at described roller bearing, described cylindrical roller (3) end face is sphere line with the contact position that the rib of outer ring (1) and inner ring (2) contacts, and the actual curvature radius of the sphere line of this cylindrical roller (3) end face is the 90%-95% of the roller end face sphere lineation opinion Calculation of curvature radius tangent with rib camber line (2-1);
The formula of described roller end face sphere lineation opinion Calculation of curvature radius R is as follows:
R＝(D
we/2-H
1)/sinα，
R: roller end face sphere lineation opinion Calculation of curvature radius;
D
we: the effective diameter of cylindrical roller (3);
H
1: the point of contact of cylindrical roller (3) end face and rib is to raceway face radial distance;
α: rib tilt angle.
2. the roller bearing of high axial carrying capacity according to claim 1, is characterized in that: the actual curvature radius of the sphere line of described cylindrical roller (3) end face for 95% of the tangent roller end face sphere lineation opinion Calculation of curvature radius R of rib camber line (2-1).
3. the roller bearing of high axial carrying capacity according to claim 1 and 2, is characterized in that: the rib camber line (2-1) of described inner ring (2) is directly connected with the raceway bus of inner ring (2).
4. the roller bearing of high axial carrying capacity according to claim 1 and 2, is characterized in that:
Described inner ring (2) raceway bus, outer ring (1) raceway bus and cylindrical roller (3) bus are the logarithmic curve protuberance shape of mutual coupling;
1. the convexity amount of the logarithmic curve protuberance shape of described outer ring (1) raceway bus is 4～7 μ m, and logarithmic curve equation is:
Y
the upper limit=-2.41ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
Y
lower limit=-1.38ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
2. the convexity amount of the logarithmic curve protuberance shape of described inner ring (2) raceway bus is 4～7 μ m, and logarithmic curve equation is:
Y
the upper limit=-2.41ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
Y
lower limit=-1.38ln (1-0.1125 * 10
-3x-16.8 * 10
-3x
2+ 2 * 10
-6x
3);
3. the convexity amount of the logarithmic curve protuberance shape of described cylindrical roller (3) bus is 5～8 μ m, and logarithmic curve equation is:
Y
the upper limit=-2.31ln (1-0.1125 * 10
-3x-17.22 * 10
-3x
2+ 2 * 10
-6x
3);
Y
lower limit=-1.445ln (1-0.1125 * 10
-3x-17.22 * 10
-3x
2+ 2 * 10
-6x
3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410168840.9A CN103967930B (en) | 2014-04-24 | 2014-04-24 | The cylinder roller bearing of high axial carrying capacity |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410168840.9A CN103967930B (en) | 2014-04-24 | 2014-04-24 | The cylinder roller bearing of high axial carrying capacity |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103967930A true CN103967930A (en) | 2014-08-06 |
| CN103967930B CN103967930B (en) | 2016-06-22 |
Family
ID=51237817
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410168840.9A Active CN103967930B (en) | 2014-04-24 | 2014-04-24 | The cylinder roller bearing of high axial carrying capacity |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103967930B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104930053A (en) * | 2015-05-29 | 2015-09-23 | 浙江天马轴承有限公司 | Cylindrical roller bearing |
| CN112524150A (en) * | 2020-12-18 | 2021-03-19 | 杭州新坐标科技股份有限公司 | Rocker bearing capable of reducing friction loss |
| CN113464550A (en) * | 2021-08-06 | 2021-10-01 | 中车大连机车研究所有限公司 | Double-row cylindrical roller bearing for urban rail transit axle box |
| CN113503321A (en) * | 2021-08-06 | 2021-10-15 | 中车大连机车研究所有限公司 | Cylindrical roller bearing for urban rail transit gear box |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0814265A (en) * | 1994-06-30 | 1996-01-16 | Koyo Seiko Co Ltd | Expansion correcting conical roller bearing |
| EP1757824A2 (en) * | 2005-08-18 | 2007-02-28 | Jtekt Corporation | Tapered roller bearing and automotive pinion shaft supporting apparatus with such bearing |
| CN101520071A (en) * | 2009-04-09 | 2009-09-02 | 福建省永安轴承有限责任公司 | Tapered roller bearing with high strength and low friction torque |
| CN102287450A (en) * | 2011-08-05 | 2011-12-21 | 福建省永安轴承有限责任公司 | Structure-optimized long-life tapered roller bearing |
| CN202209352U (en) * | 2011-08-05 | 2012-05-02 | 福建省永安轴承有限责任公司 | Long-life tapered roller bearing with optimized structure |
| CN204025327U (en) * | 2014-04-24 | 2014-12-17 | 福建省永安轴承有限责任公司 | The roller bearing of high axial carrying capacity |
-
2014
- 2014-04-24 CN CN201410168840.9A patent/CN103967930B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0814265A (en) * | 1994-06-30 | 1996-01-16 | Koyo Seiko Co Ltd | Expansion correcting conical roller bearing |
| EP1757824A2 (en) * | 2005-08-18 | 2007-02-28 | Jtekt Corporation | Tapered roller bearing and automotive pinion shaft supporting apparatus with such bearing |
| CN101520071A (en) * | 2009-04-09 | 2009-09-02 | 福建省永安轴承有限责任公司 | Tapered roller bearing with high strength and low friction torque |
| CN102287450A (en) * | 2011-08-05 | 2011-12-21 | 福建省永安轴承有限责任公司 | Structure-optimized long-life tapered roller bearing |
| CN202209352U (en) * | 2011-08-05 | 2012-05-02 | 福建省永安轴承有限责任公司 | Long-life tapered roller bearing with optimized structure |
| CN204025327U (en) * | 2014-04-24 | 2014-12-17 | 福建省永安轴承有限责任公司 | The roller bearing of high axial carrying capacity |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104930053A (en) * | 2015-05-29 | 2015-09-23 | 浙江天马轴承有限公司 | Cylindrical roller bearing |
| CN112524150A (en) * | 2020-12-18 | 2021-03-19 | 杭州新坐标科技股份有限公司 | Rocker bearing capable of reducing friction loss |
| CN113464550A (en) * | 2021-08-06 | 2021-10-01 | 中车大连机车研究所有限公司 | Double-row cylindrical roller bearing for urban rail transit axle box |
| CN113503321A (en) * | 2021-08-06 | 2021-10-15 | 中车大连机车研究所有限公司 | Cylindrical roller bearing for urban rail transit gear box |
| CN113464550B (en) * | 2021-08-06 | 2023-02-28 | 中车大连机车研究所有限公司 | Double-row cylindrical roller bearing for urban rail transit axle box |
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|---|---|
| CN103967930B (en) | 2016-06-22 |
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