KR101826196B1 - Tandem ball bearing - Google Patents

Tandem ball bearing Download PDF

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Publication number
KR101826196B1
KR101826196B1 KR1020160014472A KR20160014472A KR101826196B1 KR 101826196 B1 KR101826196 B1 KR 101826196B1 KR 1020160014472 A KR1020160014472 A KR 1020160014472A KR 20160014472 A KR20160014472 A KR 20160014472A KR 101826196 B1 KR101826196 B1 KR 101826196B1
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KR
South Korea
Prior art keywords
outer ring
ball rolling
raceway surface
inner ring
ball
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KR1020160014472A
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Korean (ko)
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KR20170093030A (en
Inventor
현준수
이운주
배송식
허두학
Original Assignee
주식회사 베어링아트
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Priority to KR1020160014472A priority Critical patent/KR101826196B1/en
Publication of KR20170093030A publication Critical patent/KR20170093030A/en
Application granted granted Critical
Publication of KR101826196B1 publication Critical patent/KR101826196B1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/182—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact in tandem arrangement
    • 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
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • 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
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings

Abstract

The present invention relates to a tandem ball bearing, and more particularly, to a tandem ball bearing comprising: an inner ring; an outer ring disposed apart from a radius of the inner ring to form a bearing space with the inner ring; And a ball rolling member inserted into the ball rolling member. According to the present invention, the shock absorbing member is mounted on the inner circumferential surface of the outer ring, and the impact absorbing member reduces the impact generated when the ball rolling member is assembled to the outer ring.

Description

[0001] TANDEM BALL BEARING [0002]

The present invention relates to a tandem ball bearing for a vehicle, and more particularly, to a tandem ball bearing having improved durability by interposing an impact absorbing member between an outer ring and an inner ring.

In general, a bearing is a mechanical element mounted between a rotating element and a non-rotating element to facilitate rotation of the rotating element while supporting the axis of the rotating element.

These bearings are divided into sliding bearings and rolling bearings depending on the state of contact with the shaft, and can be classified into a radial bearing and a thrust bearing depending on the direction in which the load is applied.

Among them, the rolling bearing is capable of supporting a rotating shaft by a rolling member such as a ball or a roller. Rolling bearings having such a structure are widely used because they have a small frictional resistance as compared with sliding bearings that directly contact a part of a shaft.

Rolling bearings can be divided into various bearings such as ball bearings, tapered roller bearings, and needle bearings depending on the shape of rolling elements. Among these tapered roller bearings, the rolling elements are formed in a roller shape, and the rolling elements are in line contact between the inner and outer rings. Therefore, even if the load is applied from the axial direction and the radial direction, it can be sufficiently supported. However, since the frictional resistance torque also increases, there is a problem that the power transmission loss is increased.

Due to the above problems, tandem type angular contact ball bearings having relatively smaller bearing capacity but smaller power transmission loss than tapered roller bearings have recently been applied.

The tandem-type angular contact ball bearings are composed of a double row, and the ball bearings in the upper row include rolling elements. The contact angles of the rolling elements are set to be the same for all double row ball bearings. Therefore, the loads acting on the double row ball bearings are directed parallel to each other in the same direction.

When assembling the tandem ball bearing of such a double row, the outer ring is fixed and the inner ring and the rolling elements are inserted axially into the inner ring. However, when inserting the inner ring and the rolling elements, the jaw portion formed inside the outer ring frequently contacts with the rolling elements, resulting in damage to the rolling elements, the outer ring, or the inner ring. Even though the above damage is slight, the damage caused by the high heat generated in the bearing rotating at high speed is further enlarged, which has a serious effect on the life of the bearing. In addition, smooth rolling of the rolling elements is difficult, resulting in a reduction in bearing function.

If the degree of contact between the inner circumferential surface of the outer ring and the rolling element is made small in order to avoid the above damage, the assembling property is weakened and the rolling elements can not be arranged at the set proper position. Furthermore, in the assembly process of the ball bearing, more delicate machining is required in order to lower the defect rate, which leads to a decrease in productivity.

SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a tandem ball bearing capable of preventing shocks even when a rolling member is assembled inside an outer ring by providing an impact absorbing member between the outer ring and the rolling member. The purpose of that is to do.

According to an aspect of the present invention, there is provided a tandem ball bearing comprising: an inner ring; an outer ring spaced radially outwardly of the inner ring and forming an inner bearing and a bearing space; And a ball rolling body mounted on the inner ring and inserted in the axial direction in the outer ring.

The tandem ball bearing includes an impact absorbing member provided separately from the outer ring and mounted on an inner circumferential surface of the outer ring so as to reduce an impact between the ball rolling member and the outer ring, And is mounted on a portion where the ball rolling body contacts.

Wherein the ball rolling member includes a first ball rolling member and a second ball rolling member, wherein the first ball rolling member has a first outer ring raceway surface formed on one side of the inner circumferential surface of the outer ring and a first outer ring raceway surface formed on one side of the outer circumferential surface of the inner ring, Wherein the second ball rolling element is interposed between a second outer ring raceway surface formed on the other side of the inner circumferential surface of the outer ring and a second inner ring raceway surface formed on the other side of the outer circumferential surface of the outer ring, And is mounted on one end of the second raceway surface and is in contact with the second ball rolling member.

Wherein the first ball rolling member, the first inner ring raceway surface, and the first outer ring raceway surface have one contact angle with respect to the rotation axis, and the second ball rolling member has a contact angle equal to the one contact angle, The inner ring raceway surface and the second outer ring raceway surface.

A first row ball bearing including the inner ring, the outer ring, and the first ball rolling member; And a second row ball bearing including the inner ring and the outer ring, and the second ball rolling member, wherein the PCD of the first row ball bearing is smaller than the PCD of the second row ball bearing can do.

And the second row ball bearings are disposed on the side where the load is heavily loaded.

The first inner ring raceway surface is located radially inwardly and axially one side of the second inner ring raceway surface, and the first outer ring raceway surface is located radially inward and one axial side of the second outer ring raceway surface. have.

Wherein one end of each of the first and second inner ring raceways is located radially inward of the other end of each of the first and second inner ring raceways, And is located radially inward of each of the other ends of the raceway surfaces.

The inner peripheral surface of the flat outer ring extends in the axial direction between the other end of the first outer ring raceway surface and one end of the second outer ring raceway surface, and the other end of the inner peripheral surface of the flat outer ring has a fitting groove, can do.

The shock absorbing member may be formed in the shape of a ring.

Wherein the shock absorbing member comprises: a mounting portion to be inserted into the mounting groove; And a main body portion contacting the inner circumferential surface of the outer ring at a radially inner side of the mounting portion.

And a mounting space is formed between the other surface of the mounting portion and the outer ring to improve the coupling property of the shock absorbing member.

And a radially inner side surface of the main body portion extends so as to be parallel to the inner circumferential surface of the flat outer ring in the axial direction and one surface of the main body portion contacts the outer ring and the other surface smoothly connects with the second outer ring raceway surface.

And an inner circumferential surface of the outer ring is formed with a support portion contacting the radially outer side surface of the main body to support the main body in the radial direction.

And when the first ball rolling body mounted on the inner ring is inserted into the outer ring, the impact absorbing member hits the first ball rolling member to relieve the impact.

The shock absorbing member may be formed of rubber or plastic material resistant to heat.

As described above, according to the embodiment of the present invention, by attaching the shock absorbing member between the outer ring and the rolling member, the impact generated when the rolling member is assembled to the outer ring can be prevented in advance. Therefore, it is possible to prevent breakage of the tandem ball bearing and increase the life expectancy thereof. Further, the position of the rolling elements of the tandem ball bearing can be adjusted to a more precisely set position, the functional performance thereof can be improved, and the durability of the tandem ball bearing can be improved. Further, in the process of assembling the rolling elements to the outer ring, the productivity is increased.

1 is a cross-sectional view of a tandem ball bearing according to an embodiment of the present invention.
2 is an exploded cross-sectional view of a tandem ball bearing according to an embodiment of the present invention.
3 is a perspective view of an outer ring of a tandem ball bearing according to an embodiment of the present invention.
4 is an enlarged sectional view of a portion A in Fig.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

Throughout the specification, when an element is referred to as "comprising ", it means that it can include other elements as well, without excluding other elements unless specifically stated otherwise.

For convenience of explanation, the left side of the drawing in the axial direction is referred to as' one side ',' one end ',' one end 'and the like name, and the right side of the drawing in the axial direction is referred to as' other side, End " and similar names.

The parts denoted by the same reference numerals throughout the specification mean the same or similar components.

1 is a cross-sectional view of a tandem ball bearing according to an embodiment of the present invention.

A tandem ball bearing 1 according to an embodiment of the present invention includes an inner ring 10, an outer ring 20 which is spaced apart from the inner ring 10 by a predetermined distance and forms a bearing space, And a retainer or a cage 40 provided so as to maintain a constant spacing in the circumferential direction from the other ball bearings adjacent to the first and second ball rolling elements 31 and 33.

The first and second inner ring raceways 11 and 13 are formed on the outer circumferential surface of the inner ring 10 and the first and second inner ring raceways 11 and 13 are formed on the inner circumferential surface of the outer ring 20 to correspond to the first and second inner ring raceways 11 and 13, The outer ring raceways 21 and 23 are formed.

The first and second ball rolling members 31 and 33 are provided between the first inner ring raceway surface 11 and the first outer ring raceway surface 21 and between the second inner ring raceway surface 13 and the second outer ring raceway surface 23. [ So that relative rotation between the inner ring 10 and the outer ring 20 can be achieved.

The first inner ring raceway surface 11 is formed in an arc shape concaved radially inward from one side of the outer circumferential surface of the inner ring 10 to the other side in the axial direction and a second inner ring raceway surface 13 is formed at the other end of the first inner ring raceway surface 11. [ The outer peripheral surface 15 of the flat inner ring parallel to the axial direction is formed. The outer peripheral surface 15 of the flat inner ring is positioned radially outwardly of the outer peripheral surface of the inner ring 10 and the first inner ring step 16 is formed at one end of the outer peripheral surface 15 of the flat inner ring. Therefore, when the first ball rolling member 31 is seated on the first inner ring raceway surface 11, the movement of the first ball rolling member 31 toward the other axial side by the first inner ring step 16 Is limited.

The second inner ring raceway surface 13 is formed in an arc shape from the other axial end of the outer peripheral surface 15 of the flat inner ring toward the other axial end. Each of the arcs of the first and second inner ring raceways 11 and 13 is formed radially outwardly of the one end thereof so that the first and second inner ring raceways 11 and 13, The ball rolling bodies 31 and 33 also have a height difference. That is, the first inner ring raceway surface 11 is located radially inward and on one side in the axial direction of the second inner ring raceway surface 13, so that the first ball rolling member 31 is also in contact with the second ball rolling member 33 ) In the radial direction.

The second inner ring step 17 is formed at the other end of the second inner ring raceway surface 13 so that the movement of the second ball rolling member 33 toward the other axial direction is restricted.

The first outer ring raceway surface 21 is formed in an arc shape so as to be recessed radially outward from a position spaced a certain distance in the axial direction from one end of the inner ring surface of the outer ring 20, A planar outer ring inner peripheral surface 25 is formed which faces the outer ring raceway surface 23 and is parallel to the axial direction. An outer ring step 26 is formed at one end of the first outer ring raceway surface 21 to block the first ball rolling member 31 from moving to one side in the axial direction.

The second outer ring raceway surface 23 is formed at the other end of the flat outer ring inner circumferential surface 25 in the shape of an arc toward the other axial side. Is located radially outward. At this time, an impact absorbing member 100 is mounted between the flat outer ring inner circumferential surface 25 and the second outer ring raceway surface 23, and even when the second ball rolling member 33 is operated, .

Thus, the first ball rolling member 31 constitutes one row of ball bearings between the first inner ring raceway surface 11 and the first outer ring raceway surface 21, and the second ball rolling member 33 forms a ball bearing And the other two rows of ball bearings are formed between the inner ring raceway surface 13 and the second outer ring raceway surface 23.

As described in the Background of the Invention, the tandem-type angular contact ball bearing is constituted by a double row ball bearing, and the contact angles of the ball rolling members provided in the respective ball bearings are set to be equal to each other. Therefore, the load lines that extend the contact points of the respective rolling elements and the inner and outer rings face each other in the same direction.

The tandem ball bearing 1 according to the embodiment of the present invention is a tandem type angular contact ball bearing and has inner ring raceways (inner ring raceways) for supporting the inner radius of the first ball rolling member 31 and the second ball rolling member 33 All of the first and second ball rolling bodies 11 and 13 are formed radially outward than the one end thereof to prevent the first and second ball rolling bodies 31 and 33 from moving to the other side. Similarly, all of the outer ring raceways 21, 23 supporting the outer radius of the first and second rolling bodies 31, 33 are all located radially outward of the one end thereof, (31, 33) from moving to one side.

The radius or diameter from the center of the upper rotation shaft to the center of the first ball rolling member 31 is defined as a first pitch circle diameter (PCD) ) And the radius or diameter from the center of the rotation axis to the center of the second ball rolling member 33 is referred to as a second PCD (PCD2). According to the embodiment of the present invention, as described above, since the first ball rolling member 31 is located on one side in the axial direction and in the radial direction from the second ball rolling member 33, the first PCCD1, (PCD2).

Since one row of ball bearings having the first PDCD (PCD1) has a smaller bearing capacity than the other row of ball bearings having the second PCD (PCD2), one row of the ball bearings is disposed on the side receiving less load than the other row of the ball bearings .

FIG. 2 is an exploded sectional view of a tandem ball bearing according to an embodiment of the present invention, FIG. 3 is a perspective view of an outer ring of a tandem ball bearing according to an embodiment of the present invention, and FIG. 4 is an enlarged sectional view of a portion A of FIG.

According to the embodiment of the present invention, as shown in Figs. 1 to 4, the shock absorbing member 100 is provided at the step portion between the other end of the flat outer ring inner peripheral surface 25 and one end of the second outer ring raceway surface 23 Respectively.

The shock absorbing member 100 extends in the circumferential direction along the inner peripheral surface of the outer ring 20 and is formed in the shape of a ring. The shock absorbing member 100 is installed at one end of the second outer ring raceway surface 23 for fast and stable assembly of the tandem ball bearing 1. At this time, the upper shock absorber 100 is installed so as not to receive the load from the second ball rolling member 33, thereby ensuring durability and maintaining the performance of the tandem ball bearing 1 as it is.

The shock absorbing member 100 according to the embodiment of the present invention absorbs the impact between the first ball rolling member 31 and the outer ring 20 in the assembling process of the tandem ball bearing 1. [ A detailed description thereof will be described in detail below.

The tandem ball bearing 1 is constructed such that the ball rolling members 31 and 33 are seated on the outer circumferential surface of the inner ring 10 by a cage or a retainer 40 and thereafter the inner ring 10 and the ball rolling members 31 and 33 Is inserted in the axial direction toward the outer ring 20 fixed to one side of the assembly.

The first outer ring raceway surface 21 formed on the inner peripheral surface of the outer ring 20 is formed radially inward of the second outer ring raceway surface 23 and the first outer ring raceway surface 21 and the second outer ring raceway surface 23 A step should be formed to limit the movement of the second ball rolling member 33 to one side.

The ball rolling elements 31 and 33 mounted on the inner ring 10 are inserted in the axial direction and hit the upper step formed on the inner circumferential surface of the outer ring 20 according to the prior art. Therefore, the inner ring 10, the outer ring 20, or the first ball rolling member 31 may be damaged or broken.

However, according to the embodiment of the present invention, the shock absorbing member 100 is mounted on the upper step portion along the inner peripheral surface of the outer ring 20. Therefore, when the assembly of the inner ring 10 and the first ball rolling member 31 is assembled to the outer ring 20, even if the first ball rolling member 31 hits the impact absorbing member 100, Or the breakage of the first ball rolling member 31 can be minimized.

Referring to FIG. 4, the shock absorbing member 100 according to the embodiment of the present invention may be formed in the shape of a ring of rubber or plastic material resistant to heat, and is inserted and fixed in the mounting groove 150.

The shock absorbing member 100 includes a body portion 110 and a mounting portion 120.

The inner circumferential surface of the main body portion 110 can smoothly extend from the other end of the inner circumferential surface 25 of the flat outer ring to the second outer ring raceway surface 23 side. The inner circumferential surface of the body portion 110 may have the same radial height as the flat outer ring inner circumferential surface 25 or may be disposed outside the inner circumferential surface 25 of the flat outer ring 25 radially. The other surface 105 of the main body 110 may be formed of a curved surface drawing the same locus as the second outer ring raceway surface 23 or a surface having a tangent line in a direction not contacting the ball. Accordingly, the other surface 105 of the upper main body portion 110 is not subjected to the load from the second ball rolling member 33 disposed on the other side.

1, the main body 110 and the second ball rolling body 33 of the shock absorbing member 100 are shown as being in contact with each other. However, the present invention is not limited thereto, (33) can be formed. Accordingly, the upper body portion 110 does not receive the load even when the second ball rolling member 33 operates.

The mounting portion 120 protrudes radially outward from the main body 110, and the mounting groove 150 is inserted and mounted. At this time, one surface of the mounting portion 120 may be in contact with the outer ring 20, and the other surface may be configured to form the mounting space 125. The shock absorbing member 100 can be more easily coupled to the mounting groove 150 of the outer ring 20 by the upper mounting space 125. [

On the other hand, the step portion between the planar outer ring inner circumferential surface 25 of the outer ring 20 and the second outer ring raceway surface 23 is formed in a cut-away shape so as to be able to insert the upper shock absorbing member 100, And a support portion 160 for supporting the impact absorbing member 100 at the other side thereof is formed. The upper support portion 160 prevents the shock absorbing member 100 from being displaced in the axial direction while the mounting portion 120 is inserted into the mounting groove 150, Thereby fixing the shock absorbing member 100 in the radial direction.

While the present invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, And all changes to the scope that are deemed to be valid.

Claims (19)

An internal combustion engine comprising: an inner ring; an outer ring arranged to be spaced radially outward of the inner ring and forming a bearing space; and a ball rolling member mounted on the inner ring and inserted axially into the outer ring, In the ball bearing,
Wherein an inner peripheral surface of the outer ring is provided separately from the outer ring, and an impact absorbing member for absorbing impact is mounted,
Wherein the shock absorbing member reduces an impact generated when the ball rolling element is assembled to the outer ring.
The method according to claim 1,
Wherein the shock absorbing member is spaced apart from the ball rolling body so as not to receive a load from the ball rolling body.
The method according to claim 1,
And the inner circumferential surface of the shock absorbing member has a raceway surface having the same curvature as that of the inner circumferential surface of the outer ring so as to prevent a load from being transmitted from the ball rolling body Tandem ball bearings.
3. The method of claim 2,
Wherein the ball rolling member includes a first ball rolling member and a second ball rolling member,
The first ball rolling element is interposed between a first outer ring raceway surface formed on one side of the inner circumferential surface of the outer ring and a first inner ring raceway surface formed on one side of the outer circumferential surface of the inner ring,
The second ball rolling element is interposed between a second outer ring raceway surface formed on the other side of the inner circumferential surface of the outer ring and a second inner ring raceway surface formed on the other side of the outer circumferential surface of the inner ring,
Wherein the shock absorbing member is mounted on one end of the second outer ring raceway surface, and is spaced apart from the second ball rolling element so as not to receive a load from the second ball rolling surface.
5. The method of claim 4,
The first ball rolling member, the first inner ring raceway surface, and the first outer ring raceway surface have one contact angle with respect to the rotation axis,
And the second ball rolling element is in contact with the second inner ring raceway surface and the second outer ring raceway surface so as to have the same contact angle as the one contact angle.
6. The method of claim 5,
A first row ball bearing including the inner ring, the outer ring, and the first ball rolling member; And,
A second row ball bearing including the inner ring, the outer ring, and the second ball rolling member;
≪ / RTI >
Wherein the PCD of the first row ball bearing is smaller than the PCD of the second row ball bearing.
The method according to claim 6,
And the second row ball bearings are disposed on a side where a load is relatively large.
The method according to claim 6,
Wherein the first inner ring raceway surface is located radially inward and one axial side of the second inner ring raceway surface,
Wherein the first outer ring raceway surface is located radially inward and one axial side of the second outer ring raceway surface.
9. The method of claim 8,
One end of each of the first and second inner ring raceways is located radially inward of the other end of each of the first and second inner ring raceways,
Wherein one end of each of the first and second outer ring raceways is located radially inward of the other end of each of the first and second outer ring raceways.
10. The method of claim 9,
The inner peripheral surface of the flat outer ring extends in the axial direction between the other end of the first outer ring raceway surface and one end of the second outer ring raceway surface,
And the other end of the inner circumferential surface of the flat outer ring is formed with a fitting groove having a shape of a radius inward.
11. The method of claim 10,
Wherein the shock absorbing member is formed in the shape of a ring.
12. The method of claim 11,
The shock absorbing member
A mounting portion to be inserted into the mounting groove; And
A main body portion extending further in the axial direction than the mounting portion inside the radius of the mounting portion;
The tandem ball bearing comprising:
13. The method of claim 12,
And a mounting space is formed between the other surface of the mounting portion and the outer ring so as to improve the coupling property of the shock absorbing member.
13. The method of claim 12,
Wherein the inner circumferential surface of the main body portion has the same radial height as the inner circumferential surface of the flat outer ring or is disposed radially outward of the inner circumferential surface of the flat outer ring.
15. The method of claim 14,
Wherein one surface of the main body portion contacts the outer ring, and the other surface smoothly connects with the second outer ring raceway surface.
13. The method of claim 12,
And a support portion that is in contact with a radially outer side surface of the main body portion is formed on an inner circumferential surface of the outer ring to radially support the main body portion.
17. The method of claim 16,
Wherein when the first ball rolling body mounted on the inner ring is assembled to the outer ring in an axial direction, the shock absorbing member alleviates an impact transmitted from the first ball rolling body.
18. The method of claim 17,
Wherein the shock absorbing member is formed of a rubber material resistant to heat.
18. The method of claim 17,
Wherein the shock absorbing member is formed of a plastic material.
KR1020160014472A 2016-02-04 2016-02-04 Tandem ball bearing KR101826196B1 (en)

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KR20170093030A KR20170093030A (en) 2017-08-14
KR101826196B1 true KR101826196B1 (en) 2018-02-06

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009036348A (en) * 2007-08-03 2009-02-19 Ntn Corp Tandem type double-row angular contact ball bearing and bearing device for pinion shaft
JP2011106649A (en) * 2009-11-20 2011-06-02 Nsk Ltd Tandem angular contact ball bearing

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009036348A (en) * 2007-08-03 2009-02-19 Ntn Corp Tandem type double-row angular contact ball bearing and bearing device for pinion shaft
JP2011106649A (en) * 2009-11-20 2011-06-02 Nsk Ltd Tandem angular contact ball bearing

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