KR20170070735A - Ball bearing with flange - Google Patents

Ball bearing with flange Download PDF

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Publication number
KR20170070735A
KR20170070735A KR1020150178626A KR20150178626A KR20170070735A KR 20170070735 A KR20170070735 A KR 20170070735A KR 1020150178626 A KR1020150178626 A KR 1020150178626A KR 20150178626 A KR20150178626 A KR 20150178626A KR 20170070735 A KR20170070735 A KR 20170070735A
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KR
South Korea
Prior art keywords
flange
ball bearing
inner ring
gripping hole
outer ring
Prior art date
Application number
KR1020150178626A
Other languages
Korean (ko)
Inventor
현준수
이운주
배송식
김규복
염민철
Original Assignee
주식회사 베어링아트
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 주식회사 베어링아트 filed Critical 주식회사 베어링아트
Priority to KR1020150178626A priority Critical patent/KR20170070735A/en
Publication of KR20170070735A publication Critical patent/KR20170070735A/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • 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
    • 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
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/65—Gear shifting, change speed gear, gear box

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

Abstract

The present invention relates to an internal combustion engine comprising an inner ring, an outer ring spaced radially outward from the inner ring, a rolling member provided to be relatively rotatable between the inner ring and the outer ring, and a flange extending radially outward from the outer ring, And a flange-integrated ball bearing arranged between the friction element and rotatably supporting the output gear.
The flange is formed at one side thereof with an arc-shaped incision toward the bearing axis. The other end of the flange has a U-shaped chamfer interference Wherein the flange is formed with a circular oil groove penetrating in the axial direction so that the gear oil can flow from the friction element to the output gear, and the oil groove is formed in the flange at 90 degrees in the circumferential direction And the first gripping hole is formed between the one side of the unshaded chamfer interfering portion and the circumferential direction of the oil groove, and the first gripping hole, Wherein the second and third gripping holes are sequentially positioned on the other side in the circumferential direction of the united chamfer interfering portion, The third gripping hole generally faces the first gripping hole, so that the oil can smoothly flow, while the operator can easily perform the operation of manually assembling or disassembling the flanged monolithic ball bearing have.

Description

Flange integrated ball bearing {BALL BEARING WITH FLANGE}

The present invention relates to a flange-integrated ball bearing, and more particularly, to a flange-integrated ball bearing having an oil groove and a holding hole penetrating in the axial direction, thereby improving the lubricating and assembling work efficiency.

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.

Such a bearing is divided into a sliding bearing and a rolling bearing according to the state of contact with the shaft, wherein the sliding bearing has a structure in direct contact with the shaft, while the rolling bearing is a structure that supports a rotating shaft by a rolling element such as a ball or a ruler . Therefore, the rolling bearing has an advantage in that the frictional resistance is smaller than that of the sliding bearing which directly contacts a part of the shaft.

Ball bearings, tapered roller bearings, and needle bearings are used for rolling bearings depending on the shape of the rolling elements. Among them, the ball bearings effectively support the high-speed rotating shaft . The ball bearings are classified into deep groove ball bearings and angular ball bearings according to their structure.

Deep groove ball bearings are the most representative type of rolling bearings and have a rolling element in the grooves formed in the inner and outer rings. On the other hand, the angular ball bearing has a structure in which a raceway surface having a constant contact angle is formed on the inner ring and the outer ring, and a rolling body is provided therebetween, so that the driving shaft rotating at high speed can be smoothly supported.

In recent years, flange bearings have been developed in which a flange is coupled to an outer ring of a ball bearing, and other components are mounted on the flange. Particularly, the flange-integrated bearing which integrally forms the flange and the outer ring can be configured as a roller or a ball bearing type, and generally a ball bearing type in which friction or torque generation is relatively small is used.

However, in the flange-integrated ball bearing installed to support the drive shaft rotating at high speed, there is a problem that the temperature rises due to frictional heat generated between the rolling elements and the inner and / or outer rings, and the lubricating performance is deteriorated.

In addition, when mounting or moving the upper flange integrated type ball bearing for the purpose of assembling and moving, it is often necessary to proceed with the hand. However, the conventional flanged integral type ball bearing has a structure that is difficult for the operator to handle.

The matters described in the background section are intended to enhance the understanding of the background of the invention and may include matters not previously known to those skilled in the art.

SUMMARY OF THE INVENTION Accordingly, the present invention has been made keeping in mind the above problems occurring in the prior art, and an object of the present invention is to provide a flange-integrated ball bearing having an oil groove that does not affect flange rigidity, And the like.

In order to achieve the above object, a flanged ball bearing according to an embodiment of the present invention includes an inner ring, an outer ring spaced radially outward from the inner ring, a rolling member provided to be relatively rotatable between the inner ring and the outer ring, And a flange extending radially outwardly from the outer ring and disposed between the output gear and the friction element of the transmission to rotatably support the output gear.

The flange is formed at one side thereof with an arc-shaped incision toward the bearing axis. The other end of the flange has a U-shaped chamfer interference Wherein the flange is formed with a circular oil groove penetrating in the axial direction so that the gear oil can flow from the friction element to the output gear, and the oil groove is formed in the flange at 90 degrees in the circumferential direction And the first gripping hole is formed between the one side of the unshaded chamfer interfering portion and the circumferential direction of the oil groove, and the first gripping hole, Wherein the second and third gripping holes are sequentially positioned on the other side in the circumferential direction of the united chamfer interfering portion, And the third phage hole generally faces the first phage hole.

And the second gripping hole extends further in the circumferential direction than the first gripping hole and the third gripping hole.

A fulcrum angle is formed between a first extension line extending between the center of the first fulcrum hole and the center of the bearing shaft and a second extension line extending between the center of the third fulcrum hole and the center of the bearing axis, 180 degrees or less.

As described above, according to the ball bearing according to the embodiments of the present invention, the oil can smoothly flow and the operator can easily manually assemble or disassemble the flange-integrated ball bearing. Therefore, the working efficiency can be increased and the productivity can be improved.

1 is a sectional view of a flange-integrated ball bearing according to an embodiment of the present invention.
2 is a front view of a flange-integrated ball bearing according to an embodiment of the present invention.
3 is a perspective view of a flange-integrated ball bearing according to an embodiment of the present invention.
FIG. 4 is an analysis diagram showing the equivalent equivalent stresses acting on a ball bearing with a flange integrated ball bearing according to an embodiment of the present invention and a ball bearing removed therefrom.

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 in the drawing is referred to as 'one side', 'one end', 'one end', and the like name, and the right side in the drawing indicates 'other side', 'other end', 'other end' Quot;

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

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

The ball bearing shown in FIG. 1 illustrates one of various types of ball bearings for convenience of description, and the technical idea of the present invention is not limited to the ball bearings exemplified herein, It can be applied to bearings.

1, the flange-integrated ball bearing 1 according to the embodiment of the present invention includes a cylindrical inner ring 10, an outer ring 40 spaced radially outward from the inner ring 10, And a retainer or cage 60 provided to maintain a constant spacing in the circumferential direction from other adjacent ball bearings.

The upper inner ring 10 can be separated into the first inner ring 11 and the second inner ring 13. [ In this case, the first inner ring raceway surface 21 is formed on the outer circumferential surface of the first inner ring 11 disposed on one axial side and the second inner ring raceway surface 13 disposed on the other axial side is provided with the second inner ring raceway surface (23) is formed. A first outer ring raceway surface 41 is formed on one inner circumferential surface of the outer ring 40, and a second outer ring raceway surface 43 is formed on the other inner circumferential surface.

The upper rolling body 50 is also divided into the first rolling member 51 and the second rolling member 53 so that the first rolling member 51 is supported by the first inner ring raceway surface 21 and the first outer ring raceway 51, And the second rolling member 53 is accommodated between the second inner ring raceway surface 23 and the second outer ring raceway surface 43. [

Since the inner ring 10 and the rolling elements 50 are separated from each other, the flange-integrated ball bearing 1 according to the embodiment of the present invention can be assembled more easily.

The first inner ring 11, the outer ring 40 and the first rolling member 51 constitute one ball bearing and the second inner ring 13, the outer ring 40 and the second rolling member 53 constitute one ball bearing. And each of the ball bearings may be provided in the form of an angular contact ball bearing.

That is, the first inner ring raceway surface 21 and the first rolling member 51 can be contacted along the first tangential line A, and the first outer ring raceway surface 41 and the first rolling member 51 2 < / RTI > tangent line (B). The first and second tangential lines A and B are inclined downward from one axial side and from the radially outer side to the other axial side and the radially inward side.

On the other hand, the second inner ring raceway surface 23 and the second rolling member 53 can be contacted along the third tangential line C, and the second outer ring raceway surface 43 and the second rolling member 53 can be brought into contact with each other 4 tangent line (D). The third and fourth tangential lines (C, D) are inclined upward from one axial side and from the radially inner side to the other axial side and the radially outer side.

Therefore, since each ball bearing is coupled in different directions, there is an effect that it is not separated or disassembled by an external impact.

Although the double-row angular contact ball bearings have been described above as an example, the technical idea of the present invention is not limited to this, but can be applied to various ball bearings.

The flange integrated ball bearing 1 according to the embodiment of the present invention further includes a flange 100 extending radially outward from the outer peripheral surface of one end of the outer ring 40. The flange 100 may be integrally formed with the outer ring 40, but is not limited thereto and may be integrally formed with the inner ring 10. The flange-integrated ball bearing 1 may be disposed between the output gear 70 of the vehicle transmission and the friction element 80 and may rotatably support the output gear 70.

FIG. 2 is a front view of a flange-integrated ball bearing according to an embodiment of the present invention, and FIG. 3 is a perspective view of a flange-integrated ball bearing according to an embodiment of the present invention.

As shown in FIG. 2, the flange 100 according to the embodiment of the present invention is generally formed in a circular plate shape, but an arc-shaped cutout 110 is formed on one side thereof. The incision 110 is formed in a convex shape toward the axial center O of the bearing.

On the other side of the flange 100, a judder chamfer interfering portion 120 is formed at a position spaced from the cutout portion 110 by a predetermined angle in the circumferential direction. The judder chamfer interfering portion 120 is formed to eliminate interference with protrusions of the UD chamfer. That is, the judder chamfer interfering portion 120 may be formed to penetrate the flange 100 such that a judder chamfer is installed.

At least one circular oil groove 105 is formed in the flange 100 so that gear oil can flow from the friction element 80 to the output gear 70 in the axial direction. The oil groove 105 may be formed at a position spaced apart from the eddy chamfer interfering portion 120 by 90 degrees in the circumferential direction. The inner diameter of the oil groove 105 is preferably 7 mm to 10 mm.

As described above, the oil groove 105 is formed in a circular shape at an angle of 90 degrees in the circumferential direction with respect to the eddy chamfer interfering portion 120, so that the rigidity of the flange 100 is not affected. When the oil groove 54 having a circular shape with an inner diameter of 7 mm to 10 mm at the upper position is formed, the stiffness change of the flange 100 is less than 1% as a result of the finite element analysis.

Further, a plurality of bolt fasteners 107 are formed in the circumferential direction along the radially outer edge of the flange 100 so as to be spaced apart from each other.

Meanwhile, according to the embodiment of the present invention, the flange 100 may be formed with a plurality of grip holes 200. The plurality of grip holes 200 will be described in more detail with reference to FIG. Hereinafter, for convenience of explanation, one side in the circumferential direction means the clockwise direction and the other side in the circumferential direction means the counterclockwise direction.

The first holding hole 210, the second holding hole 220, and the third holding hole 230 may be formed on the flange 100.

The first gripping hole 210 is located between the outer circumferential direction of the oil chamfer 105 and the eddy chamfer interfering portion 120 with respect to the center axis O of the bearing. That is, the first gripping hole 210 is located between one side of the oil groove 105 and the other side of the unshaded chamfer interfering part 120, and is formed in the shape of an arc based on the bearing axis center O. Both side ends of the first grip hole 210 are formed to be convex on both sides.

In addition, the second and third finger holes 220 and 230 are sequentially formed on one side of the judder chamfer interfering portion 120. The second gripping hole 220 is formed in a shape of a circular arc extending in a circumferential direction from one end of the first camming interfering portion 120 to a circumferential direction of the first gripping hole 210, The third finger hole 230 is formed at one side of the second finger hole 220 and is more preferably located at an angle of 90 degrees or more with respect to the circumferential direction than the unified chamfer interfering portion 120.

By forming the gripping holes 210, 220 and 230 in addition to the eddy-chamfer interfering portion 120 and the oil groove 105, the weight of the flange 100 itself is reduced and the weight is reduced. By using the upper finger holes 210, 220, and 230 when assembling or disassembling the integrated ball bearing 1 to the drive shaft, it is possible to perform more precise and convenient operations. Further, both ends of the grip holes 210, 220, and 230 are formed in a curved shape, so that it is possible to prevent the occurrence of scratches such as scratches when a worker is working with the hand, thereby achieving safety. Accordingly, the work efficiency of the assembly and disassembly process of the flange 100 can be improved.

3, the operator's thumb 350, the index finger 340, the stop 330, the finger 320 and the finger 310 are positioned on the upper finger holes 210, 220, So that the flange-integrated ball bearing 1 can be stably gripped. Particularly, as described above, the second gripping holes 220 extend further in the circumferential direction than the first and third gripping holes 210 and 230. This is to enable insertion of the stop 330 and the phantom 320 into the second phage hole when the right hand is gripped.

Meanwhile. A first extension line A extending from the center of the first gripping hole 210 and the bearing axis O and a second extension line B extending from the center of the third gripping hole 230 and the bearing axis O A fake angle X is formed.

According to the embodiment of the present invention, the firing angle X is set to be not less than 170 degrees and not more than 180 degrees. If the upper crest angle X is 180 degrees or more, the angle between the thumb 310 and the base 350 must be 180 degrees or more. Therefore, it is inconvenient to insert the finger into the flanged ball bearing 1 do. On the other hand, when the crest angle X is less than 170 degrees, since the holes concentrate on a part of the flange 100, the rigidity of the flange 100 is lowered, and the durability can be weakened. Therefore, it is appropriate that the crest angle X is set to 170 degrees or more and 180 degrees or less as described above.

FIG. 4 is an analysis diagram showing the equivalent equivalent stresses acting on a ball bearing with a flange integrated ball bearing according to an embodiment of the present invention and a ball bearing removed therefrom.

The upper diagram in Fig. 4 means that the stress is concentrated from blue to red.

4 is a flange-integrated ball bearing before forming the grip holes, and the other upper side view of FIG. 4 is a flange-integrated ball bearing after forming the grip holes according to the embodiment of the present invention. 4 is a graph that numerically analyzes stress values for a portion where a maximum stress acts after forming a phihi hole according to an embodiment of the present invention.

As shown in the lower part of FIG. 4, when equivalent holes are formed, the equivalent stress is about 337 MPa before forming the holes, and the equivalent stress is about 362 MPa. Although the equivalent stress is slightly increased, considering that the yield stress of general steel is about 500 MPa, even if the upper holding holes are formed, the durability of the flange-integrated ball bearing 1 is not affected.

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 (5)

An internal combustion engine comprising: an inner ring; an outer ring spaced radially outwardly from the inner ring; a rolling member provided to be relatively rotatable between the inner ring and the outer ring; and a flange extending radially outward from the outer ring, And the output gear is rotatably supported by the flange-integrated ball bearing,
The flange is formed at one side thereof with an arc-shaped incision toward the bearing axis. The other end of the flange has a U-shaped chamfer interference Further,
The flange is formed with a circular oil groove penetrating in the axial direction so that the gear oil can flow out from the friction element to the output gear, and the oil groove is formed at a position 90 degrees in the circumferential direction from the oil chamfer interfering portion Lt; / RTI &
Wherein the flange is formed with a first gripping hole, a second gripping hole, and a third gripping hole, the first gripping hole being located between one side of the unshaded chamfer interfering portion and the circumferential direction of the oil groove,
Wherein the second gripping hole and the third gripping hole are sequentially positioned on the other side in the circumferential direction of the judder chamfer interfering portion and the third gripping hole generally faces the first gripping hole. .
The method according to claim 1,
And the second gripping hole extends further in the circumferential direction than the first gripping hole and the third gripping hole.
3. The method of claim 2,
A fulcrum angle is formed between a first extension line extending between the center of the first fulcrum hole and the center of the bearing shaft and a second extension line extending between the center of the third fulcrum hole and the center of the bearing axis, Wherein the flange-integrated ball bearing has a diameter of 180 degrees or less.
The method of claim 3,
Wherein both ends of the first, second and third grip holes are formed in a curved shape so as to be convex toward both sides of the flange-integrated ball bearing.
5. The method of claim 4,
Wherein the inner ring includes a first inner ring and a second inner ring, the rolling member includes a first rolling member and a second rolling member,
Wherein the first inner ring, the outer ring, and the first rolling member constitute one ball bearing,
The second inner ring, the outer ring, and the second rolling member constitute another ball bearing,
Wherein the one ball bearing and the other ball bearing are each formed of an angular contact ball bearing,
Wherein the first inner ring and the outer ring have a contact angle inclined downward with respect to the first rolling member and the second inner ring and the outer ring have a contact angle inclined upward with respect to the second rolling member. bearing.
KR1020150178626A 2015-12-14 2015-12-14 Ball bearing with flange KR20170070735A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020150178626A KR20170070735A (en) 2015-12-14 2015-12-14 Ball bearing with flange

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020150178626A KR20170070735A (en) 2015-12-14 2015-12-14 Ball bearing with flange

Publications (1)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190000324U (en) 2017-07-27 2019-02-11 주식회사 엠볼트 Bearing with joint fixing structure
CN113847405A (en) * 2021-08-31 2021-12-28 东风商用车有限公司 Gearbox gear spoke structure and gearbox
KR20220080887A (en) * 2020-12-08 2022-06-15 섀플러 테크놀로지스 아게 운트 코. 카게 Wave gear and bearing element for a wave gear

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190000324U (en) 2017-07-27 2019-02-11 주식회사 엠볼트 Bearing with joint fixing structure
KR20220080887A (en) * 2020-12-08 2022-06-15 섀플러 테크놀로지스 아게 운트 코. 카게 Wave gear and bearing element for a wave gear
CN113847405A (en) * 2021-08-31 2021-12-28 东风商用车有限公司 Gearbox gear spoke structure and gearbox

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