KR20100078276A - Spacer of pinion bearing for differential device - Google Patents

Spacer of pinion bearing for differential device Download PDF

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Publication number
KR20100078276A
KR20100078276A KR1020080136490A KR20080136490A KR20100078276A KR 20100078276 A KR20100078276 A KR 20100078276A KR 1020080136490 A KR1020080136490 A KR 1020080136490A KR 20080136490 A KR20080136490 A KR 20080136490A KR 20100078276 A KR20100078276 A KR 20100078276A
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KR
South Korea
Prior art keywords
pinion
bearing
spacer
shaft
race
Prior art date
Application number
KR1020080136490A
Other languages
Korean (ko)
Inventor
최석
Original Assignee
다이모스(주)
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Filing date
Publication date
Application filed by 다이모스(주) filed Critical 다이모스(주)
Priority to KR1020080136490A priority Critical patent/KR20100078276A/en
Publication of KR20100078276A publication Critical patent/KR20100078276A/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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • 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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H2048/382—Methods for manufacturing differential gearings
    • 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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • F16H2048/405—Constructional details characterised by features of the rotating cases characterised by features of the bearing of the rotating case

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)

Abstract

The present invention relates to a spacer of a pinion bearing for a differential device, the outer spacer (23) installed so that both ends are supported on the outer race (9b) of the pinion inner bearing (9) and the outer race (10b) of the pinion outer bearing (10). When the lock nut 14 is fastened to the upper end of the shaft of the pinion shaft 6, the pinion inner bearing 9 and the pinion outer bearing 10 may not only maintain a constant preload at all times, but also outer races 9b and 10b. The gap between the roller and the rollers 9c and 10c does not occur, and thus the pinion inner bearing 9 and the pinion outer bearing 10 can reduce noise, improve durability and extend life. .

Description

Spacer of pinion bearing for differential device

The present invention relates to a spacer installed between a pinion inner bearing and a pinion outer bearing, and more particularly, to a pinion bearing for a differential device for maintaining the distance and preload between the pinion inner bearing and the pinion outer bearing at an appropriate level. Is a technique relating to a spacer.

In general, as shown in FIG. 1, the differential gear device is installed in a state in which a differential case 2 (hereinafter, abbreviated as 'deep case') is rotatable inside the carrier 1, and the deep case 2 is installed. 3) is formed of a spider (4) having a pinion (3) inside and a side gear (5) engaged with both sides of the pinion (3), the both side gear (5) and the hub of the wheel drive Connection to the shaft allows transmission of engine power.

The deep case 2 is rotated by receiving engine power from the final gear 7 of the pinion shaft 6 connected to the transmission output shaft or the propulsion shaft. For this purpose, the deep case 2 is connected to the final gear 7. A disk-shaped drive gear (8, also known as a ring gear) that is engaged at right angles to the center is mounted.

The shaft of the pinion shaft 6 is installed in the pinion bearing, the pinion bearing is composed of a pinion inner bearing (9) and a pinion outer bearing (10), the pinion inner bearing (9) and the pinion outer bearing (10) ) Are installed apart from each other.

The bearing retainer 11 surrounding the pinion inner bearing 9 and the pinion outer bearing 10 is fastened to the carrier 1 via a plurality of bolts 12, and the upper end of the shaft of the pinion shaft 6. The companion flange 13 is installed in the penetrated state.

The lower end of the companion flange 13 is installed to be in close contact with the upper end of the pinion outer bearing 10, the companion flange 13 to the lock nut 14 screwed to the upper end of the shaft portion of the pinion shaft (6). Disassembly is prevented.

The upper end of the pinion outer bearing 10 is a structure that is wrapped by the dust cover 15, the dust cover 15 is assembled together when the companion flange 13 is assembled by the lock nut (14). .

Meanwhile, a spacer 16 is provided between the pinion inner bearing 9 and the pinion outer bearing 10 to maintain the preload of the bearing as shown in FIGS. 1 and 2, wherein the spacer 16 is in the middle. The portion has a shape having a circular protrusion 16a which protrudes convexly in the outward direction toward the bearing retainer 11.

Therefore, when the lock nut 14 is fastened to the upper end of the shaft portion of the pinion shaft 6, the fastening force of the lock nut 14 presses the pinion outer bearing 10 through the companion flange 13, and the spacer ( 16 has a force to be compressed by receiving the pressing force of the pinion outer bearing (10).

However, the spacer 16 is not compressively deformed, and instead, the pinion inner bearing 9 exerts a force for pushing the pinion inner bearing 9 and the pinion outer bearing 10 in opposite directions by the circular protrusion 16a. And the pinion outer bearing 10, so that the pinion inner bearing 9 and the pinion outer bearing 10 can maintain an appropriate level of preload.

However, the conventional structure as described above has a structure in which both ends of the spacer 16 support the inner race 9a of the pinion inner bearing 9 and the inner race 10a of the pinion outer bearing 10. The inner races 9a and 10a and the rollers 9c and 10c are forced in directions (arrows R1 and R2) which are separated from the outer races 9b and 10b, respectively.

That is, the inner races 9a and 10a are integrally formed with the rollers 9c and 10c, and the outer races 9b and 10b are coupled to the rollers 9c and 10c so as to be separated from each other. The inner race 9a of the pinion inner bearing 9, which is provided with elastic force from the spacer 16, has a force to move downward in the state of FIG. 2 together with the roller 9c, and the pinion outer bearing ( The inner race 10a of 10 has a force to move upward in the state of FIG. 2 together with the roller 10c.

At this time, when the inner races 9a and 10a are provided with elastic force from the spacer 16 by the inclined surface shape between the outer races 9b and 10b and the rollers 9c and 10c, the inner races 9a and 10a ) Are applied to the rollers 9c and 10c in the directions (arrows R1 and R2) separated from the outer races 9b and 10b, respectively.

Accordingly, the conventional structure has a disadvantage in that a gap is generated between the outer races 9b and 10b and the rollers 9c and 10c, and the pinion inner bearing 9 and the pinion outer bearing 10 are caused by such a gap. There is a problem that increases the noise and decreases durability and decreases the lifespan.

Accordingly, the present invention has been made to solve the above problems, and between the outer race and the roller constituting the pinion inner bearing and the pinion outer bearing through the change of the spacer installed between the pinion inner bearing and the pinion outer bearing. The purpose of the present invention is to provide a spacer of a pinion bearing for a differential device, which can eliminate gaps and thereby reduce noise, improve durability, and extend the life of the pinion inner bearing and the pinion outer bearing. have.

In order to achieve the above object, the spacer of the pinion bearing for a differential device of the present invention has an inner race between the pinion inner bearing and the pinion outer bearing between the pinion inner bearing and the pinion outer bearing installed at the shaft portion of the pinion shaft. An inner spacer which is installed to contact each of the inner races and maintains a distance between the pinion inner bearing and the pinion outer bearing when the lock nut is fastened to the pinion shaft; Both ends of the pinion inner bearing and the outer race of the pinion outer bearing are supported so as to be respectively supported on the outer side of the inner spacer so as to provide elastic force to the outer races when the lock nut is fastened to the pinion shaft. And an outer spacer for maintaining a preload of the pinion outer bearing.

According to the present invention, the pinion inner bearing 9 and the pinion outer bearing when the lock nut is fastened to the upper end of the shaft portion of the pinion shaft through an outer spacer installed at both ends of the outer race of the pinion inner bearing and the outer race of the pinion outer bearing. Not only maintains a constant preload, but also a gap does not occur between the outer race and the roller, thereby reducing the noise, improving durability and extending the life of the pinion inner bearing and the pinion outer bearing. There is.

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

3 is a cross-sectional view of the differential gear device for explaining the spacer according to the present invention, Figure 4 is an enlarged view of the installation portion of the spacer according to the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention will be described with reference to the drawings. In the differential gear device, as shown in FIG. 3, a differential case 2 (hereinafter, referred to as a 'deep case') is rotated inside the carrier 1. It is installed in a possible state, and is made of a structure in which the spider 4 having the pinion 3 and the side gears 5 engaged with both sides of the pinion 3 are installed inside the deep case 2, the both sides The side gear 5 and the hub of the wheel are connected to the drive shaft so that engine power can be transmitted.

The deep case 2 is rotated by receiving engine power from the final gear 7 of the pinion shaft 6 connected to the transmission output shaft or the propulsion shaft. For this purpose, the deep case 2 is connected to the final gear 7. The disk-shaped drive gear 8 meshed with respect to the orthogonal direction is assembled.

The shaft of the pinion shaft 6 is installed in the pinion bearing, the pinion bearing is composed of a pinion inner bearing (9) and a pinion outer bearing (10), the pinion inner bearing (9) and the pinion outer bearing (10) ) Are installed apart from each other.

The bearing retainer 11 surrounding the pinion inner bearing 9 and the pinion outer bearing 10 is fastened to the carrier 1 via a plurality of bolts 12, and the upper end of the shaft of the pinion shaft 6. The companion flange 13 is installed in the penetrated state.

The lower end of the companion flange 13 is installed to be in close contact with the upper end of the pinion outer bearing 10, the companion flange 13 to the lock nut 14 screwed to the upper end of the shaft portion of the pinion shaft (6). Disassembly is prevented.

The upper end of the pinion outer bearing 10 is a structure that is wrapped by the dust cover 15, the dust cover 15 is assembled together when the companion flange 13 is assembled by the lock nut (14). .

Meanwhile, between the pinion inner bearing 9 and the pinion outer bearing 10, the distance between the pinion inner bearing 9 and the pinion outer bearing 10 is constant as shown in FIGS. 3 and 4. At the same time, a spacer is provided for maintaining the preload of the bearing at the same time.

The pinion inner bearing 9 and the pinion outer bearing 10 are composed of inner races 9a and 10a, outer races 9b and 10b and rollers 9c and 10c, respectively, as shown in FIG. The inner races 9a and 10a and the rollers 9c and 10c are integrally coupled, and the outer races 9b and 10b are coupled to the rollers 9c and 10c.

On the other hand, the spacer according to the present invention is largely composed of the inner spacer 21 and the outer spacer 23.

The inner spacer 21 is formed in a cylindrical shape having a cross section, and is installed such that both ends contact the inner race 9a of the pinion inner bearing 9 and the inner race 10a of the pinion outer bearing 10, respectively. do.

Accordingly, when the lock nut 14 is fastened to the upper end of the shaft portion of the pinion shaft 6, the inner spacer 21 uniformly spaces the gap between the pinion inner bearing 9 and the pinion outer bearing 10. It serves to maintain.

The outer spacer 23 is located outside the inner spacer 21, and is both ends of the outer race 9b of the pinion inner bearing 9 and the outer race 10b of the pinion outer bearing 10. It is installed so that each is tungsten.

The outer spacer 23 has a cylindrical shape having a circular protrusion 23a in which an intermediate portion between the pinion inner bearing 9 and the pinion outer bearing 10 protrudes convexly toward the inner spacer 21. Formed structure.

Accordingly, when the lock nut 14 is fastened to the upper end of the shaft portion of the pinion shaft 6, the outer spacer 23 provides the elastic force to the outer races 9b and 10b so that the pinion inner bearing 9 is provided. And the pinion outer bearing 10 serves to maintain a constant preload.

That is, when the lock nut 14 is fastened to the upper end of the shaft portion of the pinion shaft 6, the fastening force of the lock nut 14 presses the pinion outer bearing 10 through the companion flange 13.

In this case, since the inner spacer 21 is not a spacer providing elastic force to the inner race 9a of the pinion inner bearing 9 and the inner race 10a of the pinion outer bearing 10, the inner spacer 21 ) Serves to keep the gap between the pinion inner bearing 9 and the pinion outer bearing 10 constant.

However, the outer spacer 23 is subjected to pressing force through the pinion outer bearing 10 when the lock nut 14 is fastened to the upper end of the shaft of the pinion shaft 6, thereby compressing the outer spacer 23. You have the power to be.

However, the outer spacer 23 is not compressively deformed, and instead, the outer race 9b of the pinion inner bearing 9 and the outer race 10b of the pinion outer bearing 10 are each other by the circular protrusion 23a. A force pushing in the opposite direction is provided to the pinion inner bearing 9 and the pinion outer bearing 10, so that the pinion inner bearing 9 and the pinion outer bearing 10 are the outer spacer 23 ), It is possible to maintain an appropriate level of preload.

On the other hand, in the structure of the present invention, since both ends of the outer spacer 23 support the outer race 9b of the pinion inner bearing 9 and the outer race 10b of the pinion outer bearing 10, the outer The races 9b and 10b are subjected to a force in the direction of engaging with the rollers 9c and 10c as shown by arrows R31 and R4 shown in FIG.

That is, the outer race 9b of the pinion inner bearing 9 provided with the elastic force from the outer spacer 23 has a force to move downward in the state of FIG. 4, and the outer of the pinion outer bearing 10 The race 10b has a force to move upward in the state of FIG. 4.

At this time, when the outer races 9b and 10b are provided with the elastic force from the outer spacer 23 by the inclined surfaces of the rollers 9c and 10c, the outer races 9b and 10b are connected to the rollers 9c and 10c. You will receive strength in the direction of unity.

Accordingly, the structure of the present invention has the advantage that a gap does not occur between the outer race (9b, 10b) and the roller (9c, 10c), by this advantage the pinion inner bearing 9 and the pinion outer bearing ( 10) has the advantage of reducing noise, improving durability and extending the life.

1 and 2 are a cross-sectional view of a differential gear device for explaining a conventional spacer and an enlarged partial extract of FIG.

3 and 4 are views corresponding to FIGS. 1 and 2, respectively, and are cross-sectional views of the differential gear device for explaining the spacer according to the present invention and partially enlarged views of FIG. 3.

<Description of Symbols for Main Parts of Drawings>

6-Pinion Shaft 9-Pinion Inner Bearing

9a, 10a-Inner Race 9b, 10b-Outer Race

10-Pinion Outer Bearing 14-Locknut

21-Inner Spacer 23-Outer Spacer

23-circular projection

Claims (3)

Inner race 9a of the pinion inner bearing 9 and inner race of the pinion outer bearing 10 are connected at both ends between the pinion inner bearing 9 and the pinion outer bearing 10 provided on the shaft portion of the pinion shaft 6. Inner spacers 21 which are installed to be in contact with the respective pins 10a and maintain the gap between the pinion inner bearing 9 and the pinion outer bearing 10 when the lock nut 14 is fastened to the pinion shaft 6. ; Both ends of the outer race 9b of the pinion inner bearing 9 and the outer race 10b of the pinion outer bearing 10 are mounted so as to be respectively supported on the outer side of the inner spacer 21 so that the pinion shaft 6 An outer spacer 23 which provides an elastic force to the outer races 9b and 10b when the lock nut 14 is fastened to maintain a preload of the pinion inner bearing 9 and the pinion outer bearing 10; Spacer of the pinion bearing for the differential comprising a. The method according to claim 1, wherein the inner spacer 21 is formed in a cylindrical shape having a straight cross section; A spacer of a pinion bearing for a differential device. The method according to claim 1, wherein the outer spacer 23, An intermediate portion between the pinion inner bearing (9) and the pinion outer bearing (10) is formed in a cylindrical shape with a circular protrusion (23a) projecting convexly toward the inner spacer (21); A spacer of a pinion bearing for a differential device.
KR1020080136490A 2008-12-30 2008-12-30 Spacer of pinion bearing for differential device KR20100078276A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020080136490A KR20100078276A (en) 2008-12-30 2008-12-30 Spacer of pinion bearing for differential device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020080136490A KR20100078276A (en) 2008-12-30 2008-12-30 Spacer of pinion bearing for differential device

Publications (1)

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KR20100078276A true KR20100078276A (en) 2010-07-08

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3042562A1 (en) * 2015-10-20 2017-04-21 Moteurs Leroy-Somer SPEED REDUCER AND METHOD OF MOUNTING SUCH A REDUCER
KR20210103252A (en) * 2020-02-13 2021-08-23 현대위아 주식회사 Power transmission device

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3042562A1 (en) * 2015-10-20 2017-04-21 Moteurs Leroy-Somer SPEED REDUCER AND METHOD OF MOUNTING SUCH A REDUCER
WO2017067905A1 (en) * 2015-10-20 2017-04-27 Moteurs Leroy-Somer Speed reducer and method of assembling such a reducer
US10371201B2 (en) 2015-10-20 2019-08-06 Moteurs Leroy-Somer Speed reducer and method of assembling such a reducer
KR20210103252A (en) * 2020-02-13 2021-08-23 현대위아 주식회사 Power transmission device

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