JP4525208B2 - Bearing device for pinion shaft support - Google Patents
Bearing device for pinion shaft support Download PDFInfo
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- JP4525208B2 JP4525208B2 JP2004187297A JP2004187297A JP4525208B2 JP 4525208 B2 JP4525208 B2 JP 4525208B2 JP 2004187297 A JP2004187297 A JP 2004187297A JP 2004187297 A JP2004187297 A JP 2004187297A JP 4525208 B2 JP4525208 B2 JP 4525208B2
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- Prior art keywords
- gear
- pinion
- pinion shaft
- rolling bearing
- point
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- 238000005096 rolling process Methods 0.000 claims description 25
- 239000002184 metal Substances 0.000 claims description 4
- 239000010687 lubricating oil Substances 0.000 description 11
- 230000004323 axial length Effects 0.000 description 4
- 238000007789 sealing Methods 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 2
- 238000005498 polishing Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 235000018936 Vitellaria paradoxa Nutrition 0.000 description 1
- 230000004308 accommodation Effects 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 239000010802 sludge Substances 0.000 description 1
Images
Classifications
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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
- F16C19/183—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 with two rows at opposite angles
- F16C19/184—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 with two rows at opposite angles in O-arrangement
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
- F16C33/6666—Details of supply of the liquid to the bearing, e.g. passages or nozzles from an oil bath in the bearing housing, e.g. by an oil ring or centrifugal disc
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
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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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
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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
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
- F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Sealing Of Bearings (AREA)
- Rolling Contact Bearings (AREA)
Description
この発明は、エンジン等回転駆動源からの駆動トルクを伝達するピニオン軸を支持するのに好適なピニオン軸支持用軸受装置に関する。 The present invention relates to a pinion shaft support bearing device suitable for supporting a pinion shaft that transmits drive torque from a rotational drive source such as an engine.
エンジン等回転駆動源からの駆動トルクを伝達する装置としては、デファレンシャル装置やトランスファー装置が知られており、これらの装置は、基本構成として、一端部にピニオン・ギアが配設されたピニオン軸およびピニオン軸をケーシングに回転自在に支持する１対の円すいころ軸受を備えているピニオン軸支持用軸受装置と、軸受とは離れた位置でケーシングに取り付けられているシール部材とを有している（特許文献１、特許文献２など）。
円すいころ軸受は、高い剛性を得るという点では好ましいが、これを２個使用し、しかも、シール部材を軸受とは離れた位置でケーシングに取り付けていることで、シール部材を含めたピニオン軸支持用軸受装置が大型となるという問題があった。 Tapered roller bearings are preferable in terms of obtaining high rigidity, but two of them are used, and the seal member is attached to the casing at a position away from the bearing, thereby supporting the pinion shaft including the seal member. There is a problem that the bearing device for a vehicle becomes large.
この発明の目的は、潤滑油密封性と耐泥水性とが確保され、しかも、軸方向の長さを短くすることができるピニオン軸支持用軸受装置を提供することにある。 SUMMARY OF THE INVENTION An object of the present invention is to provide a pinion shaft support bearing device that can ensure lubricating oil sealing performance and muddy water resistance and can reduce the axial length.
この発明によるピニオン軸支持用軸受装置は、一端部にピニオン・ギアが配設されたピニオン軸と、ピニオン軸をケーシングに回転自在に支持する転がり軸受とを備えているピニオン軸支持用軸受装置において、転がり軸受として、１対の内輪、１つの外輪および各内輪と外輪との間に配された２列の玉を有する複列アンギュラー玉軸受が使用されており、ピニオン・ギアに近い方の両輪端部間にシール部材が配置されずに、ピニオン・ギアから遠い方の両輪端部間にのみシール部材が配置されており、ピニオン・ギアに近い方の内輪の肩部の幅がピニオン・ギアに遠い方の内輪の肩部の幅よりも狭くされていることにより、ピニオン・ギアに近い方の列の玉の接触角方向と軸線とが交差する点をギア側作用点とし、ピニオン・ギアに遠い方の列の玉の接触角方向と軸線とが交差する点を反ギア側作用点として、転がり軸受の中心線からギア側作用点までの距離が転がり軸受の中心線から反ギア側作用点までの距離よりも大きくなされていることを特徴とするものである。 A pinion shaft support bearing device according to the present invention is a pinion shaft support bearing device including a pinion shaft having a pinion gear disposed at one end thereof and a rolling bearing that rotatably supports the pinion shaft on a casing. As a rolling bearing, a pair of inner rings, a single outer ring, and a double-row angular ball bearing having two rows of balls arranged between the inner ring and the outer ring , both wheels closer to the pinion gear are used. the seal member is not arranged between the ends, shea seal member only between two wheels end remote from the pinion gear and is arranged, the inner ring of the width of the shoulders pinion closer to the pinion gear・ The point where the contact angle direction of the ball in the row closer to the pinion gear intersects with the axis due to being narrower than the width of the shoulder of the inner ring farther from the gear is the gear side action point, and the pinion・ Those far from the gear The distance from the center line of the rolling bearing to the gear side action point is the distance from the center line of the rolling bearing to the counter gear side action point, where the point where the contact angle direction of the ball in the row intersects with the axis is the anti-gear side action point. It is characterized by being made larger .
このピニオン軸支持用軸受装置は、トランスファー装置に使用するのに好適であり、デファレンシャル装置に適用することもできる。 This pinion shaft support bearing device is suitable for use in a transfer device, and can also be applied to a differential device.
シール部材は、芯金およびゴムシールを有しており、ゴムシールは、ピニオン・ギアから遠い方の内輪の肩部に接触している主シールリップ部と、外輪との間にラビリンスシールを形成するスリンガに接触しているラジアルリップ部とを有していることが好ましい。スリンガーは、例えば、ピニオン軸に転がり軸受の内輪を固定するための段付き状の抜け止め部材に嵌め合わされる。スリンガには、外輪に若干の隙間をおいて対向し外輪との間にラビリンスシールを形成する折り曲げ部が設けられることがより好ましい。 The seal member has a metal core and a rubber seal, and the rubber seal is a slinger that forms a labyrinth seal between the main seal lip portion that is in contact with the shoulder portion of the inner ring far from the pinion gear and the outer ring. It is preferable to have a radial lip part in contact with. The slinger is fitted to a stepped retaining member for fixing the inner ring of the rolling bearing to the pinion shaft, for example. More preferably, the slinger is provided with a bent portion that faces the outer ring with a slight gap and forms a labyrinth seal with the outer ring.
また、ピニオン・ギアに近い方の内輪の肩部の幅がピニオン・ギアに遠い方の内輪の肩部の幅よりも狭くされていることが好ましい。このようにすると、ピニオン・ギアから遠い方の両輪端部間にシール部材を配置する場所を確保することが容易となり、しかも、ピニオン・ギアに近い方の列の玉の接触角方向と軸線とが交差する点をギア側作用点とし、ピニオン・ギアに遠い方の列の玉の接触角方向と軸線とが交差する点を反ギア側作用点として、転がり軸受の中心線からギア側作用点までの距離が転がり軸受の中心線から反ギア側作用点までの距離よりも大きくなる。ギア側作用点は、ピニオン・ギアの略軸方向中央部にあるギア噛み合い点の軸方向外側でかつギア噛み合い点の近傍に位置することから、ピニオン・ギアに近い方の軸受部分には、大きな負荷がかかることになるが、転がり軸受の中心線からギア側作用点までの距離が転がり軸受の中心線から反ギア側作用点までの距離よりも大きくすることで、ギア側作用点位置をギア噛み合い点から離すことができ、これにより、大きな負荷がかかるピニオン・ギアに近い方の軸受部分の負荷が低減され、長寿命化を図ることができる。 Further, it is preferable that the width of the shoulder portion of the inner ring closer to the pinion gear is narrower than the width of the shoulder portion of the inner ring farther from the pinion gear. In this way, it becomes easy to secure a place for disposing the seal member between both wheel ends far from the pinion gear, and the contact angle direction and axis of the balls in the row closer to the pinion gear Is the gear side action point, and the point where the contact angle direction of the ball in the row far from the pinion gear intersects with the axis is the counter gear side action point, and the gear side action point from the center line of the rolling bearing. Is larger than the distance from the center line of the rolling bearing to the non-gear-side action point. The gear side action point is located on the outer side of the gear engagement point in the approximate axial center of the pinion gear and in the vicinity of the gear engagement point. Although the load is applied, the distance from the center line of the rolling bearing to the gear side action point is made larger than the distance from the center line of the rolling bearing to the anti-gear side action point. It is possible to move away from the meshing point, thereby reducing the load on the bearing portion closer to the pinion gear to which a large load is applied, and extending the life.
この発明のピニオン軸支持用軸受装置によると、転がり軸受として、接触角が大きく取れる複列アンギュラー玉軸受が使用されているので、従来の円すいころ軸受を使用したピニオン軸支持用軸受装置に比べて、軸方向の長さを短くすることができる。また、両輪のピニオン・ギアから遠い方の端部間にシール部材が配置されているので、潤滑油密封性と耐泥水性とが確保されるとともに、軸受とは離れた位置にシール部材が配置されているピニオン軸支持用軸受装置に比べて、軸方向の長さをより一層短くすることができる。 According to the pinion shaft support bearing device of the present invention, as the rolling bearing, a double-row angular contact ball bearing having a large contact angle is used. Therefore, compared to a conventional pinion shaft support bearing device using a tapered roller bearing. The axial length can be shortened. In addition, since a seal member is arranged between the ends of the two wheels that are far from the pinion gears, the sealing performance of the lubricant is ensured and the seal member is arranged at a position away from the bearing. Compared to the pinion shaft support bearing device, the axial length can be further shortened.
この発明の実施の形態を、以下図面を参照して説明する。 Embodiments of the present invention will be described below with reference to the drawings.
図１および図２は、この発明によるピニオン軸支持用軸受装置を４輪駆動車用のトランスファー装置として適用する場合の１実施形態を示している。以下の説明において、左右・上下は、図の左右・上下をいうものとする。なお、左が車両のフロント側、右が車両のリア側となっている。 FIG. 1 and FIG. 2 show an embodiment in which the pinion shaft supporting bearing device according to the present invention is applied as a transfer device for a four-wheel drive vehicle. In the following description, left / right / up / down refers to left / right / up / down in the figure. The left is the front side of the vehicle, and the right is the rear side of the vehicle.
図１に示すように、ピニオン軸支持用軸受装置(1)は、左端部にピニオン・ギア(3)が配設されたピニオン軸(2)と、ピニオン軸(2)をケーシング(4)に回転自在に支持する転がり軸受(5)とを備えている。そして、ピニオン・ギア(3)が後輪駆動用リング・ギアに噛み合わされるとともに、ピニオン軸(2)がプロペラシャフトに接続されることで、車両前側に配置されたエンジンから後輪に動力が伝達される。 As shown in FIG. 1, the pinion shaft support bearing device (1) includes a pinion shaft (2) having a pinion gear (3) disposed at the left end, and a pinion shaft (2) in a casing (4). And a rolling bearing (5) that is rotatably supported. The pinion gear (3) meshes with the rear wheel drive ring gear, and the pinion shaft (2) is connected to the propeller shaft, so that power is transmitted from the engine arranged on the front side of the vehicle to the rear wheels. Communicated.
転がり軸受(5)は、複列アンギュラー玉軸受であり、左右１対の内輪(11)(12)と、これらに共通の１つの外輪(13)と、左の内輪(11)と外輪(13)の左半部との間に配された左列の玉(14)と、右の内輪(12)と外輪(13)の右半部との間に配された右列の玉(15)と、各列の玉(14)(15)を保持する左右１対の保持器(16)(17)と、右の内輪(12)と外輪(13)の右半部との間すなわちピニオン・ギア(3)から遠い方の端部間に配されたシール部材(18)とからなる。 The rolling bearing (5) is a double-row angular ball bearing, a pair of left and right inner rings (11) and (12), a common outer ring (13), a left inner ring (11) and an outer ring (13 ) Ball in the left row (14) placed between the left half of) and the ball in the right row (15) placed between the right inner ring (12) and the right half of the outer ring (13) And a pair of left and right cages (16) (17) that hold the balls (14) (15) in each row, and the right half of the right inner ring (12) and the outer ring (13), that is, a pinion And a seal member (18) disposed between end portions far from the gear (3).
転がり軸受(5)の潤滑は、軸受内にグリースを封入するのではなく、ケーシング(4)内を循環する潤滑油によって行われている。 Lubrication of the rolling bearing (5) is performed by lubricating oil circulating in the casing (4) rather than enclosing grease in the bearing.
ピニオン軸(2)の右端部には、転がり軸受(5)の内輪(11)(12)を固定するための段付き状の抜け止め部材(6)がねじ止められており、抜け止め部材(6)の小径部の外径には、スリンガ(7)が嵌め合わされている。スリンガ(7)は、外輪(13)の右端部に若干の隙間をおいて対向する折り曲げ部(7a)を有しており、これにより、外輪(13)とスリンガ(7)によるラビリンスシールが形成されている。 At the right end of the pinion shaft (2), a stepped retaining member (6) for fixing the inner rings (11), (12) of the rolling bearing (5) is screwed, and the retaining member ( A slinger (7) is fitted to the outer diameter of the small diameter portion of 6). The slinger (7) has a bent portion (7a) facing the right end of the outer ring (13) with a slight gap, thereby forming a labyrinth seal by the outer ring (13) and the slinger (7). Has been.
左右の内輪(11)(12)は、軌道溝(11a)(12a)の形状が左右で同じとされるとともに、肩部(11b)(12b)の幅が左の方が狭くされた非対称に形成されている。これに対応して、外輪(13)には、左右の内輪(11)(12)の境界線に対して対称な軌道溝(13a)(13b)が形成されている。左右の保持器(16)(17)は、その柱部を軸方向内側にして対称に配置されている。 The left and right inner rings (11) and (12) are asymmetrical in that the shape of the raceway grooves (11a) and (12a) are the same on the left and right, and the width of the shoulders (11b) and (12b) is narrowed on the left side. Is formed. Correspondingly, the outer ring (13) is formed with raceway grooves (13a) (13b) symmetrical with respect to the boundary line between the left and right inner rings (11), (12). The left and right cages (16), (17) are arranged symmetrically with their column portions inside in the axial direction.
したがって、左右の玉(14)(15)の接触角は同じとなっており、左右の内輪が同じ幅の場合に比べると、左右の玉(14)(15)の中心線が転がり軸受(5)の中心よりも内輪(11)(12)の肩部(11b)(12b)の幅の差の半分だけ左に寄っている点で異なっている。 Therefore, the contact angles of the left and right balls (14) and (15) are the same, and the center line of the left and right balls (14) and (15) is the rolling bearing (5 ) Is different from the center of the inner ring (11) and (12) in that it is shifted to the left by half the width difference of the shoulders (11b) and (12b).
すなわち、ピニオン・ギア(3)に近い方の列の玉(14)の接触角方向と軸線Ｌとが交差する点をギア側作用点Ｐ１とし、ピニオン・ギア(3)に遠い方の列の玉(15)の接触角方向と軸線Ｌとが交差する点を反ギア側作用点Ｐ２として、転がり軸受(5)の中心線Ｏからギア側作用点Ｐ１までの距離Ｗ１が転がり軸受(5)の中心線Ｏから反ギア側作用点Ｐ２までの距離Ｗ２よりも大きく（Ｗ１＞Ｗ２）なされている。 That is, the point where the contact angle direction of the ball (14) in the row closer to the pinion gear (3) and the axis L intersects with the gear side action point P1, and the row farther from the pinion gear (3). The point at which the contact angle direction of the ball (15) intersects the axis L is defined as the anti-gear side action point P2, and the distance W1 from the center line O of the rolling bearing (5) to the gear side action point P1 is the rolling bearing (5). Is larger than the distance W2 from the center line O to the non-gear-side action point P2 (W1> W2).
ギア側作用点Ｐ１は、ピニオン・ギア(3)の略軸方向中央部にあるギア噛み合い点Ｇの軸方向外側でかつギア噛み合い点Ｇの近傍に位置することから、ピニオン・ギア(3)に近い方の軸受部分（左部）には、大きな負荷がかかることになる。転がり軸受(5)の中心線Ｏからギア側作用点Ｐ１までの距離Ｗ１が転がり軸受(5)の中心線Ｏから反ギア側作用点Ｐ２までの距離Ｗ２よりも大きくすると、ギア側作用点Ｐ１の位置をギア噛み合い点Ｇから離すことができ、これにより、大きな負荷がかかるピニオン・ギア(3)に近い方の軸受部分の負荷が低減され、左右の内輪が同じ幅の場合に比べて、長寿命となる。なお、Ｗ１＞Ｗ２とするには、左右の内輪を同じ幅として、接触角を変更することでも可能であり、左右の内輪を異なる幅とし、さらに接触角も変更するようにしてもよい。 The gear-side action point P1 is located on the outer side in the axial direction of the pinion gear (3) in the approximate axial center of the pinion gear (3) and in the vicinity of the gear engagement point G, so that the pinion gear (3) A large load is applied to the near bearing part (left part). When the distance W1 from the center line O of the rolling bearing (5) to the gear side action point P1 is larger than the distance W2 from the center line O of the rolling bearing (5) to the counter gear side action point P2, the gear side action point P1. Can be moved away from the gear meshing point G, which reduces the load on the bearing portion closer to the pinion gear (3) where a large load is applied, compared to the case where the left and right inner rings have the same width, Long service life. In order to satisfy W1> W2, the left and right inner rings may have the same width and the contact angle may be changed. Alternatively, the left and right inner rings may have different widths, and the contact angle may also be changed.
外輪(13)は、右端部にフランジ(13a)を有しており、このフランジ(13a)の左側根元部には、外輪(13)とケーシング(4)との間からの潤滑油の漏れを防止するためのＯリング(19)が配置されている。ケーシング(4)のＯリング(19)に接触する角部(4a)は、フランジ(13a)の左側根元部とによって断面略三角形状のＯリング収納溝(20)を形成するように面取りされており、Ｏリング(19)はこのＯリング収納溝(20)内に配置されている。Ｏリング収納溝(20)を形成するための外輪(13)の外径およびフランジ(13a)根元部に対する加工は、従来から行われている研磨により行うことができる。また、面取りは、従来から行われている面取りの大きさをＯリング(19)の径に応じて調整するだけでよい。これにより、Ｏリング収納溝を切削加工により外輪(13)外径に設ける場合に比べて、工数を削減することができる。また、Ｏリング収納溝(20)を研磨によって形成することで、切削に比べて溝精度が向上し、潤滑油密封性も向上する。 The outer ring (13) has a flange (13a) at the right end, and the left base of the flange (13a) leaks lubricating oil from between the outer ring (13) and the casing (4). An O-ring (19) is arranged for prevention. The corner (4a) that contacts the O-ring (19) of the casing (4) is chamfered so as to form an O-ring storage groove (20) having a substantially triangular cross section with the left base of the flange (13a). The O-ring (19) is disposed in the O-ring storage groove (20). The outer diameter of the outer ring (13) and the base of the flange (13a) for forming the O-ring housing groove (20) can be processed by conventional polishing. Further, the chamfering only needs to be adjusted in accordance with the diameter of the O-ring (19). Thereby, a man-hour can be reduced compared with the case where an O-ring accommodation groove | channel is provided in an outer ring | wheel (13) outer diameter by cutting. Further, by forming the O-ring storage groove (20) by polishing, the groove accuracy is improved as compared with cutting, and the lubricating oil sealing property is also improved.
外輪(13)には、２列の玉(14)(15)の軸方向中央に相当する部分すなわち外輪(13)の軸方向中央よりも内輪(11)(12)の幅が左右で非対称とされている分若干左に寄った部分に、潤滑油入口用の径方向貫通孔(21)が設けられ、外輪(13)の右端部すなわちピニオン・ギア(3)に遠い方の端部に潤滑油出口用の斜め方向貫通孔(22)が設けられている。ケーシング(4)の内周には、軸方向にのびる潤滑油溝(23)が形成され、両貫通孔(21)(22)は、この潤滑油溝(23)に連通するように設けられている。これにより、焼付きが起こりやすい右側（リア側）の軸受部分における潤滑油の循環が促進させられ、耐焼付き性能が向上するとともに、シール部材(18)へのスラッジの付着も防止される。潤滑油溝(23)およびこれに連通する両貫通孔(21)(22)は、周方向の同じ位相位置とすることで、１カ所だけに設ければよく、これにより、コスト増を抑えることができる。 In the outer ring (13), the width of the inner ring (11) (12) is asymmetrical in the left and right sides compared to the axial center of the two rows of balls (14) (15), that is, the axial center of the outer ring (13). A radial through hole (21) for lubricating oil inlet is provided in the part slightly to the left, and lubrication is provided at the right end of the outer ring (13), that is, the end far from the pinion gear (3). An oblique through hole (22) for the oil outlet is provided. A lubricating oil groove (23) extending in the axial direction is formed on the inner periphery of the casing (4), and both through holes (21) and (22) are provided so as to communicate with the lubricating oil groove (23). Yes. As a result, circulation of the lubricating oil in the right side (rear side) bearing portion where seizure is likely to occur is promoted, seizure resistance is improved, and sludge is prevented from adhering to the seal member (18). The lubricating oil groove (23) and both through holes (21) (22) communicating with the lubricating oil groove (23) need only be provided in one place by setting the same phase position in the circumferential direction, thereby suppressing an increase in cost. Can do.
図２に示すように、シール部材(18)は、環状芯金(24)およびゴムシール(25)を有している。芯金(24)は、外輪(13)の右端部内径に圧入されている大径部(31a)およびこれの軸方向外側（右側）に連なる小径部(31b)からなる円筒部(31)と、小径部(31b)の右端部に設けられた内向きフランジ部(32)とからなる。ゴムシール(25)は、芯金(24)の小径部(31b)および内向きフランジ部(32)に接着されており、環状のばね(26)によって径方向内向きに付勢されて右側の内輪(12)の肩部(12b)に接触している主シールリップ部(33)と、右側の内輪(12)の肩部(12b)右端部に接触している副シールリップ部(34)と、外輪(13)との間にラビリンスシールを形成しているスリンガ(7)に接触しているラジアルリップ部(35)とを有している。 As shown in FIG. 2, the seal member (18) has an annular cored bar (24) and a rubber seal (25). The metal core (24) includes a cylindrical portion (31) composed of a large diameter portion (31a) press-fitted into the inner diameter of the right end portion of the outer ring (13) and a small diameter portion (31b) connected to the outer side (right side) in the axial direction thereof. And an inward flange portion (32) provided at the right end of the small diameter portion (31b). The rubber seal (25) is bonded to the small diameter portion (31b) and the inward flange portion (32) of the core metal (24), and is urged radially inward by the annular spring (26) to A main seal lip portion (33) in contact with the shoulder portion (12b) of (12), and a secondary seal lip portion (34) in contact with the right end portion of the shoulder portion (12b) of the right inner ring (12). And a radial lip portion (35) in contact with the slinger (7) forming a labyrinth seal with the outer ring (13).
このようにして、シール部材(18)が転がり軸受(5)に組み込まれており、これにより、シール部材(18)の偏心が抑えられ、低トルク性を維持したままで、潤滑油密封性と耐泥水性とが確保されるとともに、装置の軸方向長さも短いものとされている。 In this way, the seal member (18) is incorporated in the rolling bearing (5), thereby suppressing the eccentricity of the seal member (18) and maintaining the low torque characteristic, while maintaining the lubricating oil sealability. The mud water resistance is ensured and the axial length of the apparatus is also short.
(1) ピニオン軸支持用軸受装置
(2) ピニオン軸
(3) ピニオン・ギア
(4) ケーシング
(5) 転がり軸受
(7) スリンガ
(11)(12) 左右内輪
(11b)(12b)肩部
(13) 外輪
(14)(15) 玉
(18) シール部材
(24) 芯金
(25) ゴムシール
(33) 主シールリップ部
(35) ラジアルリップ部
(1) Pinion shaft support bearing device
(2) Pinion shaft
(3) Pinion gear
(4) Casing
(5) Rolling bearing
(7) Slinger
(11) (12) Left and right inner ring
(11b) (12b) Shoulder
(13) Outer ring
(14) (15) Ball
(18) Seal member
(24) Core
(25) Rubber seal
(33) Main seal lip
(35) Radial lip
Claims (2)
転がり軸受として、１対の内輪、１つの外輪および各内輪と外輪との間に配された２列の玉を有する複列アンギュラー玉軸受が使用されており、ピニオン・ギアに近い方の両輪端部間にシール部材が配置されずに、ピニオン・ギアから遠い方の両輪端部間にのみシール部材が配置されており、ピニオン・ギアに近い方の内輪の肩部の幅がピニオン・ギアに遠い方の内輪の肩部の幅よりも狭くされていることにより、ピニオン・ギアに近い方の列の玉の接触角方向と軸線とが交差する点をギア側作用点とし、ピニオン・ギアに遠い方の列の玉の接触角方向と軸線とが交差する点を反ギア側作用点として、転がり軸受の中心線からギア側作用点までの距離が転がり軸受の中心線から反ギア側作用点までの距離よりも大きくなされていることを特徴とするピニオン軸支持用軸受装置。 In a pinion shaft support bearing device comprising a pinion shaft having a pinion gear disposed at one end thereof, and a rolling bearing that rotatably supports the pinion shaft on a casing.
As a rolling bearing, the inner race of the one-to-one of the outer race and the double row angular contact ball bearing is used, both wheels end closer to the pinion gear having two rows of balls disposed between the respective inner and outer rings the seal member is not arranged between the parts, only between two wheels end remote from the pinion gear is arranged a sheet seal member, it widths pinion inner shoulder portion of the near pinion gear By making it narrower than the width of the shoulder of the inner ring farther from the gear, the point where the contact angle direction of the ball in the row closer to the pinion gear intersects the axis is the gear side action point, and the pinion The point where the contact angle direction of the ball in the row far from the gear intersects the axis is the anti-gear-side action point, and the distance from the center line of the rolling bearing to the gear-side action point is the anti-gear side from the center line of the rolling bearing. characterized in that it is made larger than the distance to the point Bearing apparatus for supporting the pinion shaft to.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004187297A JP4525208B2 (en) | 2004-06-25 | 2004-06-25 | Bearing device for pinion shaft support |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004187297A JP4525208B2 (en) | 2004-06-25 | 2004-06-25 | Bearing device for pinion shaft support |
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| JP2006009930A JP2006009930A (en) | 2006-01-12 |
| JP4525208B2 true JP4525208B2 (en) | 2010-08-18 |
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| JP2004187297A Expired - Fee Related JP4525208B2 (en) | 2004-06-25 | 2004-06-25 | Bearing device for pinion shaft support |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JP4535018B2 (en) | 2006-03-29 | 2010-09-01 | 株式会社ジェイテクト | Roller bearing device for pinion shaft support |
| JP5218735B2 (en) | 2007-12-12 | 2013-06-26 | Ｎｏｋ株式会社 | Sealing device |
| JP5092166B2 (en) * | 2008-10-31 | 2012-12-05 | イーグル工業株式会社 | Shaft seal device |
| JP5867477B2 (en) | 2013-10-11 | 2016-02-24 | トヨタ自動車株式会社 | Automatic transmission |
| JP7401990B2 (en) * | 2019-08-07 | 2023-12-20 | Ntn株式会社 | ball bearing |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH058046U (en) * | 1991-07-15 | 1993-02-02 | 光洋精工株式会社 | Drive axle unit |
| JPH109258A (en) * | 1996-06-26 | 1998-01-13 | Nippon Seiko Kk | Bearing unit for supporting pinion shaft of differential gear |
| JP2003254362A (en) * | 2002-03-06 | 2003-09-10 | Nsk Ltd | Bearing unit for supporting wheel |
| JP2004169889A (en) * | 2002-11-22 | 2004-06-17 | Koyo Seiko Co Ltd | Pinion shaft supporting bearing device, and pinion shaft supporting device |
| JP2004176730A (en) * | 2002-11-22 | 2004-06-24 | Nsk Ltd | Roller bearing unit for wheel with encoder |
-
2004
- 2004-06-25 JP JP2004187297A patent/JP4525208B2/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH058046U (en) * | 1991-07-15 | 1993-02-02 | 光洋精工株式会社 | Drive axle unit |
| JPH109258A (en) * | 1996-06-26 | 1998-01-13 | Nippon Seiko Kk | Bearing unit for supporting pinion shaft of differential gear |
| JP2003254362A (en) * | 2002-03-06 | 2003-09-10 | Nsk Ltd | Bearing unit for supporting wheel |
| JP2004169889A (en) * | 2002-11-22 | 2004-06-17 | Koyo Seiko Co Ltd | Pinion shaft supporting bearing device, and pinion shaft supporting device |
| JP2004176730A (en) * | 2002-11-22 | 2004-06-24 | Nsk Ltd | Roller bearing unit for wheel with encoder |
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