CN208804122U - Double row tapered roller bearing - Google Patents
Double row tapered roller bearing Download PDFInfo
- Publication number
- CN208804122U CN208804122U CN201821490261.6U CN201821490261U CN208804122U CN 208804122 U CN208804122 U CN 208804122U CN 201821490261 U CN201821490261 U CN 201821490261U CN 208804122 U CN208804122 U CN 208804122U
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- Prior art keywords
- ring raceway
- roller
- inner ring
- row
- double
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Abstract
The utility model proposes a kind of double row tapered roller bearings, including double-row outer-ring and two single-row inner rings, middle spacer ring is provided between two single-row inner rings, retainer is provided between the double-row outer-ring and two single-row inner rings, several rollers are provided on the retainer, the double-row outer-ring is provided with the outer ring raceway for roller rolls, described two single-row inner rings are provided with the inner ring raceway for the roller rolls, the inner ring raceway bus and the outer ring raceway bus are arc-shaped shape, and the roller bus is in logarithmic curve shape.The utility model is uniformly distributed contact stress between roller and outer ring raceway and inner ring raceway, reduces edge stress effect, improves the service life of double row tapered roller bearing, can satisfy passenger train speed per hour 160km/h~350km/h operating condition.
Description
Technical field
The utility model belongs to technical field of bearings, is related to tapered roller bearing more particularly to a kind of double-row conical
Bearing.
Background technique
Currently, with the continuous development of society, Railway Transport Industry is also more and more flourishing, thus mentions to railway transport of passengers speed
Higher requirement is gone out.Since domestic bearing is influenced by modes such as structure, manufacturing process, tooling devices, domestic bearing due to
Bearing life is short and the problems such as bearing bearing capacity is low caused by stress distribution is uneven between roller and raceway, only
It is confined to speed per hour 160km/h passenger train below to use, the Rolling Stock Bearing of speed per hour 160km/h or more depends on import.
And with the progress of China's technology, the introduction of the innovation of manufacturing process and tooling device, the limitation of foreign technology has been breached, has been had
The designed capacity and manufacturing condition of standby speed per hour 160km/h~350km/h.
In consideration of it, it is necessary to provide a kind of new double row tapered roller bearing, which be can satisfy
Under passenger train speed per hour 160km/h~350km/h operating condition, stress distribution is more uniform and horizontal between bearing roller and raceway
To the higher requirement of bearing capacity.
Summary of the invention
The utility model in view of the above technical problems, provides a kind of new double row tapered roller bearing, the double row tapered roller
Sub- bearing can make the more uniform service life to improve bearing of stress distribution between bearing roller and raceway, have simultaneously
Higher bearing capacity.
In order to achieve the above object, the technical solution adopted in the utility model are as follows:
A kind of double row tapered roller bearing, including double-row outer-ring and two single-row inner rings, between two single-row inner rings
It is provided with middle spacer ring, retainer is provided between the double-row outer-ring and two single-row inner rings, is arranged on the retainer
There are several rollers, the double-row outer-ring is provided with the outer ring raceway for roller rolls, and described two single-row inner ring settings are useful
In the inner ring raceway of the roller rolls, the inner ring raceway bus and the outer ring raceway bus are arc-shaped shape, the rolling
Primary and secondary line is in logarithmic curve shape, and the inner ring raceway bus convexity is 0 μm~10 μm, and the outer ring raceway bus convexity is 0 μ
M~10 μm, the roller bus convexity is 5 μm~15 μm, so as to the roller and the outer ring raceway and the inner ring raceway
Stress is uniformly distributed between contact surface.
Preferably, the inner ring further includes the big flange of inner ring, the roller further includes roller ball basal plane, and the inner ring is big
Flange at the big flange angle of inner ring be 7 °~8.5 ° along the longitudinal institute of the double row tapered roller bearing, the roller ball basal plane half
Diameter is 57cm~60cm, to reduce the roller axially loaded.
Preferably, the inner ring raceway is with the inner ring raceway angle formed by the double row tapered roller bearing transverse direction
7 °~8.5 °, the outer ring raceway is 9 °~11 ° with the outer ring raceway angle formed by the double row tapered roller bearing transverse direction,
The roller angle is 2 °~3 °, to prevent the roller stress deflection.
Preferably, the inner ring raceway bus convexity is 2.5 μm, the outer ring raceway bus convexity is 1.5 μm, described
Roller bus convexity is 10.5 μm.
Preferably, the big flange angle of inner ring is 7 ° 54 ', the roller ball basal plane radius is 58.5cm.
Preferably, the inner ring raceway angle is 7 ° 34 ', the outer ring raceway angle is 10 °, and the roller angle is
2°26’。
Preferably, the retainer is provided with annular trapped fuel slot close to the middle spacer ring side.
Compared with prior art, it the advantages of the utility model and has the active effect that
1, double row tapered roller bearing described in the utility model, by adjusting the outer ring raceway bus convex value, institute
Inner ring raceway bus convex value and the roller bus convex value are stated, the roller and the outer ring raceway and the inner ring are rolled
Contact stress is uniformly distributed between road, to reduce edge stress effect, to improve making for the double row tapered roller bearing
Use the service life.
2, double row tapered roller bearing described in the utility model, by adjusting the big flange angular dimension of the inner ring and institute
Roller ball basal plane radius size is stated, so that the big flange of the inner ring and the roller ball basal plane is realized good contact relation, to subtract
The low roller axially loaded, to improve the bearing capacity of the double row tapered roller bearing.
Detailed description of the invention
Fig. 1 is a kind of double row tapered roller bearing of the utility model along its longitudinal cross-sectional view；
Fig. 2 is outer ring in double row tapered roller bearing described in the utility model along its longitudinal cross-sectional view；
Fig. 3 is inner ring in double row tapered roller bearing described in the utility model along its longitudinal cross-sectional view；
Fig. 4 is retainer structural schematic diagram in double row tapered roller bearing described in the utility model；
Fig. 5 is the side view of roller in double row tapered roller bearing described in the utility model；
In above each figure: 1, outer ring；11, outer ring raceway；2, inner ring；21, inner ring raceway；22, the big flange of inner ring；3, interval
Circle；4, retainer；41, trapped fuel slot；5, roller；51, roller ball basal plane；α, outer ring raceway angle；β, inner ring raceway angle；It is δ, interior
Enclose big flange angle；γ, roller angle；.
Specific embodiment
In the following, the present invention is specifically described by illustrative embodiment.It should be appreciated, however, that not into one
In the case where step narration, element, structure and features in an embodiment can also be advantageously incorporated into other embodiments
In.
In the description of the present invention, it should be noted that being laterally the horizontal direction in attached drawing 1, longitudinal is attached drawing 1
In vertical direction, the orientation or positional relationships of the instructions such as term "inner", "outside", "upper", "lower", "front", "rear" is based on attached
Positional relationship shown in figure, is merely for convenience of describing the present invention and simplifying the description, rather than indication or suggestion meaning
Device or element must have a particular orientation, be constructed and operated in a specific orientation, therefore should not be understood as practical new to this
The limitation of type.
As shown in Figure 1, the utility model provides a kind of double row tapered roller bearing, including double-row outer-ring 1 and two it is single-row
Inner ring 2 is provided with middle spacer ring 3 between two single-row inner rings, between the double-row outer-ring 1 and two single-row inner rings 2
It is provided with retainer 4, several rollers 5 are provided on the retainer 4, the double-row outer-ring 1 is provided with for the rolling of roller 5
Outer ring raceway 11, described two single-row inner rings 2 are provided with the inner ring raceway 21 rolled for the roller 5, the inner ring raceway
21 buses and 11 bus of outer ring raceway are arc-shaped shape, and 5 bus of roller is in logarithmic curve shape, the inner ring raceway
21 bus convexitys are 0 μm~10 μm, and the 11 bus convexity of outer ring raceway is 0 μm~10 μm, and the 5 bus convexity of roller is 5 μ
M~15 μm, so that stress is uniformly distributed between the roller 5 and the outer ring raceway 11 and 21 contact surface of the inner ring raceway,
Edge stress effect is reduced, to improve the service life of the double row tapered roller bearing.Wherein, when the inner ring raceway 21
Bus convexity is 2.5 μm, and the 11 bus convexity of outer ring raceway is 1.5 μm, when the 5 bus convexity of roller is 10.5 μm, institute
It is most uniform to state stress distribution between roller 5 and the outer ring raceway 11 and 21 contact surface of the inner ring raceway.
It is rolled as shown in Fig. 2, the outer ring raceway 11 is formed by outer ring with the transverse direction along the double row tapered roller bearing
Road angle [alpha] is 7 °~8.5 °.
As shown in figure 3, the inner ring raceway 21 is 9 °~11 ° with inner ring raceway angle beta is laterally formed by, the inner ring
2 further include the big flange 22 of inner ring, the big flange 22 of the inner ring be formed by along the longitudinal direction of the double row tapered roller bearing in
Enclosing big flange angle δ is 7 °~8.5 °.
As shown in figure 5, the roller angle γ is 2 °~3 °, the roller 5 further includes roller ball basal plane 51, the roller
Ball basal plane radius SR is 57cm~60cm.
Wherein, the outer ring raceway angle [alpha], the inner ring raceway angle beta and the roller angle γ three cooperate
5 edge of roller and 21 contact position of the outer ring raceway 11 and the inner ring raceway generated to prevent 5 deflection of roller
Stress concentration phenomenon, further increase the service life of the double row tapered roller bearing；When the inner ring raceway angle [alpha] is
7 ° 34 ', the outer ring raceway angle beta be 10 ° and when the roller angle γ is 2 ° 26 ', can most prevent 5 deflection of roller and
5 edge of roller of generation and the stress concentration phenomenon of 21 contact position of the outer ring raceway 11 and the inner ring raceway.
Both the big flange angle δ of inner ring and the roller ball basal plane radius SR cooperate to the big shelves of the inner ring
Side 22 and roller ball basal plane 51 are better contacted with to reduce by 5 axially loaded of roller, improve the double row tapered roller bearing
Bearing capacity, wherein when the big flange angle δ of the inner ring is 7 ° 54 ', the roller ball basal plane radius SR is 58.5cm
When, the bearing capacity of the double row tapered roller bearing is most strong.
As shown in figure 4, the retainer 4 is provided with annular trapped fuel slot 41 close to middle 3 side of spacer ring, to improve
The lubricating oil replenishing ability of double row tapered roller bearing in the running is stated, when double row tapered roller bearing operating is effectively reduced
Temperature.
With continued reference to Fig. 1, the double row tapered roller bearing arranges outer ring 1 for described two using multistage labyrinth sealing mode
It is sealed with single-row inner ring 2 described in two, so that the double row tapered roller bearing is sealed, it is close by labyrinth type
The throttle effect that envelope generates makes the double row tapered roller bearing play better seal effect.
The double row tapered roller bearing of the utility model is by adjusting 11 bus convex value of outer ring raceway, inner ring raceway
5 bus convex value of 21 bus convex values and roller, keeps contact stress between roller 5 and outer ring raceway 11 and inner ring raceway 21 uniform
Distribution reduces edge stress effect, to improve the service life of double row tapered roller bearing；By adjusting the big flange of inner ring
Angle δ and roller ball basal plane radius SR make the big flange 22 of inner ring realize good contact relation with roller ball basal plane 51, reduce institute
The axially loaded of roller 5 is stated, so that the bearing capacity of the double row tapered roller bearing is improved, the double row tapered roller
Sub- bearing can satisfy passenger train speed per hour 160km/h~350km/h operating condition.
Claims (7)
1. a kind of double row tapered roller bearing, including double-row outer-ring and two single-row inner rings, set between two single-row inner rings
It is equipped with middle spacer ring, retainer is provided between the double-row outer-ring and two single-row inner rings, is provided on the retainer
Several rollers, the double-row outer-ring are provided with the outer ring raceway for roller rolls, and described two single-row inner rings, which are provided with, to be used for
The inner ring raceway of the roller rolls, it is characterised in that: the inner ring raceway bus is arc-shaped with the outer ring raceway bus
Shape, the roller bus are in logarithmic curve shape, and the inner ring raceway bus convexity is 0 μm~10 μm, and the outer ring raceway is female
Line convexity is 0 μm~10 μm, and the roller bus convexity is 5 μm~15 μm, so as to the roller and the outer ring raceway and institute
Stress between inner ring raceway contact surface is stated to be uniformly distributed.
2. double row tapered roller bearing according to claim 1, it is characterised in that: the inner ring further includes the big shelves of inner ring
Side, the roller further include roller ball basal plane, the big flange of inner ring with along the longitudinal institute of the double row tapered roller bearing at interior
Enclosing big flange angle is 7 °~8.5 °, and the roller ball basal plane radius is 57cm~60cm, to reduce the roller axially loaded.
3. double row tapered roller bearing according to claim 1, it is characterised in that: the inner ring raceway with along the biserial
Inner ring raceway angle formed by tapered roller bearing transverse direction be 7 °~8.5 °, the outer ring raceway with along the double-row conical
Outer ring raceway angle formed by bearing transverse direction is 9 °~11 °, and the roller angle is 2 °~3 °, inclined to prevent the roller stress
Tiltedly.
4. double row tapered roller bearing according to claim 1, it is characterised in that: the inner ring raceway bus convexity is
2.5 μm, the outer ring raceway bus convexity is 1.5 μm, and the roller bus convexity is 10.5 μm.
5. double row tapered roller bearing according to claim 2, it is characterised in that: the big flange angle of inner ring is 7 °
54 ', the roller ball basal plane radius is 58.5cm.
6. double row tapered roller bearing according to claim 3, it is characterised in that: the inner ring raceway angle is 7 ° 34 ',
The outer ring raceway angle is 10 °, and the roller angle is 2 ° 26 '.
7. double row tapered roller bearing according to claim 1, it is characterised in that: the retainer is close to the middle spacer ring
Side is provided with annular trapped fuel slot.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821490261.6U CN208804122U (en) | 2018-09-12 | 2018-09-12 | Double row tapered roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821490261.6U CN208804122U (en) | 2018-09-12 | 2018-09-12 | Double row tapered roller bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN208804122U true CN208804122U (en) | 2019-04-30 |
Family
ID=66237284
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821490261.6U Active CN208804122U (en) | 2018-09-12 | 2018-09-12 | Double row tapered roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN208804122U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113530981A (en) * | 2021-08-06 | 2021-10-22 | 中车大连机车研究所有限公司 | Double-row tapered roller bearing for urban rail transit axle box |
-
2018
- 2018-09-12 CN CN201821490261.6U patent/CN208804122U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113530981A (en) * | 2021-08-06 | 2021-10-22 | 中车大连机车研究所有限公司 | Double-row tapered roller bearing for urban rail transit axle box |
| CN113530981B (en) * | 2021-08-06 | 2023-09-12 | 中车大连机车研究所有限公司 | Double-row tapered roller bearing for urban rail transit axle box |
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| GR01 | Patent grant |