JP4687019B2 - Pinion shaft support bearing device - Google Patents
Pinion shaft support bearing device Download PDFInfo
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- JP4687019B2 JP4687019B2 JP2004187294A JP2004187294A JP4687019B2 JP 4687019 B2 JP4687019 B2 JP 4687019B2 JP 2004187294 A JP2004187294 A JP 2004187294A JP 2004187294 A JP2004187294 A JP 2004187294A JP 4687019 B2 JP4687019 B2 JP 4687019B2
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- gear
- pinion shaft
- ring
- pinion
- ball
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- 239000010687 lubricating oil Substances 0.000 claims description 22
- 238000005096 rolling process Methods 0.000 claims description 21
- 238000005461 lubrication Methods 0.000 claims description 5
- 239000000446 fuel Substances 0.000 description 3
- 238000005498 polishing Methods 0.000 description 2
- 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
- 238000007789 sealing Methods 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
- 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
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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
- 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)
- 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、自動車の燃費向上の観点から軸受の低トルク化が課題となっており、円すいころ軸受より回転トルクが小さい玉軸受への切換えが望まれている。 Tapered roller bearings are preferable in terms of obtaining high rigidity, but lowering the torque of the bearings is an issue from the viewpoint of improving the fuel efficiency of automobiles, and switching to ball bearings with lower rotational torque than tapered roller bearings is desired. ing.
この発明の目的は、円すいころ軸受に代えて玉軸受の使用を可能とし、これにより、燃費向上およびコンパクト化を可能としたピニオン軸支持用軸受装置を提供することにある。 An object of the present invention is to provide a bearing device for supporting a pinion shaft that enables the use of a ball bearing instead of a tapered roller bearing, thereby improving fuel efficiency and reducing the size.
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、軌道溝の形状が互いに同じとされた１対の内輪、１対の内輪の境界線に対して対称な軌道溝が形成された１つの外輪および各内輪と外輪との間に配された２列の同径の玉を有し、２列の玉の接触角が互いに同じとなる複列アンギュラー玉軸受が使用されており、玉軸受の潤滑は、ケーシング内を循環する潤滑油によって行われており、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、両内輪の外側端面間の中心線からギア側作用点までの距離が両内輪の外側端面間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 in which the shape of the raceway grooves is the same as each other , one outer ring in which a raceway groove symmetrical with respect to the boundary line of the pair of inner rings is formed, and between each inner ring and the outer ring have a second column the diameter of the balls disposed, the contact angle of the two rows ball has the double row angular ball bearing comprising a mutually same is used, lubrication of the ball bearing, the lubricating oil circulating in the casing The width of the shoulder of the inner ring closer to the pinion gear is narrower than the width of the shoulder of the inner ring farther from the pinion gear, so that the row closer to the pinion gear Contact angle direction and axis The center line between the outer end faces of both inner rings is defined as the point where the crossing point is the gear side action point and the point where the contact angle direction of the ball farthest from the pinion gear and the axis intersect is the counter gear side action point The distance from the gear side action point to the gear side action point is larger than the distance from the center line between the outer end faces of both inner rings to the counter gear side action point.
複列アンギュラー玉軸受は、内輪、外輪および玉のほかに、通常、各列の玉を保持する１対の保持器と、ピニオン・ギアから遠い方の両輪端部間に配されたシール部材をさらに有しているものとされる。各保持器は、２列の玉の中央を通る線に対して対称に配置される。 In addition to the inner ring, outer ring, and balls, the double-row angular contact ball bearing usually includes a pair of cages for holding the balls in each row and a seal member disposed between the end portions of the two wheels far from the pinion gear. Furthermore, it is assumed to have. Each cage is arranged symmetrically with respect to a line passing through the center of the two rows of balls.
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.
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（両内輪の外側端面間の中心線）からギア側作用点までの距離が転がり軸受の中心線（両内輪の外側端面間の中心線）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が好ましい。 The point at which 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 point where the contact angle direction of the ball in the row farther from the pinion gear intersects the axis The distance from the center line of the rolling bearing (the center line between the outer end faces of both inner rings ) to the gear side action point as the counter gear side action point is opposite from the center line of the rolling bearing ( center line between the outer end faces of both inner rings). It is preferable that the distance is larger than the distance to the gear side action point.
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。転がり軸受の中心線（両内輪の外側端面間の中心線）からギア側作用点までの距離が転がり軸受の中心線（両内輪の外側端面間の中心線）から反ギア側作用点までの距離よりも大きくすると、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。 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. A load will be applied. The distance from the center line of the rolling bearing ( center line between the outer end faces of both inner rings) to the gear side action point is the distance from the center line of the rolling bearing ( center line between the outer end faces of both inner rings) to the counter gear side action point If it is larger than this, the gear side action point position can be moved away from the gear meshing point, thereby reducing the load on the bearing portion closer to the pinion gear that is subjected to a large load and extending the service life. .
転がり軸受の中心線（両内輪の外側端面間の中心線）からギア側作用点までの距離＞転がり軸受の中心線（両内輪の外側端面間の中心線）から反ギア側作用点までの距離とするには、接触角、内輪形状、外輪形状などをギアに近い側と遠い側とで非対称にすることで可能であるが、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より好ましい。このようにすると、２列の玉が全体としてピニオン・ギアに近づき、これにより、潤滑性が向上し、より一層長寿命化が図られる。 Distance from the center line of the rolling bearing ( center line between the outer end faces of both inner rings) to the gear side action point> Distance from the center line of the rolling bearing ( center line between the outer end faces of both inner rings) to the counter gear side action point To achieve this, it is possible to make the contact angle, inner ring shape, outer ring shape, etc. asymmetric between the side closer to the gear and the side farther away, but the width of the shoulder of the inner ring closer to the pinion gear is More preferably, it is narrower than the width of the shoulder of the inner ring farther from the gear. In this way, the two rows of balls approach the pinion gear as a whole, thereby improving lubricity and further extending the life.
外輪にフランジが設けられており、このフランジの根元部にＯリングが配置されていることが好ましい。この場合に、ケーシングの角部には、断面が略三角形のＯリング収納溝が形成されるように、面取りが施される。このようにすると、面取りの大きさをＯリング径に応じて調整することが必要となるものの、Ｏリング収納溝を外輪外径に切削加工する必要がなくなるため、全体的な工数が削減される。 It is preferable that a flange is provided on the outer ring, and an O-ring is disposed at the base of the flange. In this case, chamfering is performed at the corner of the casing so that an O-ring storage groove having a substantially triangular cross section is formed. In this way, although it is necessary to adjust the size of the chamfering according to the O-ring diameter, it is not necessary to cut the O-ring storage groove to the outer diameter of the outer ring, so that the overall man-hour is reduced. .
さらにまた、外輪の２列の玉の中央に相当する部分に潤滑油入口用の貫通孔が設けられ、外輪のピニオン・ギアに遠い方の端部に潤滑油出口用の貫通孔が設けられていることが好ましい。この場合に、ケーシングの内周には、軸方向にのびる潤滑油溝が形成され、両貫通孔は、潤滑油溝に連通するように設けられる。このようにすると、焼付きが起こりやすい反ギ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。 Furthermore, a through hole for the lubricating oil inlet is provided in the portion corresponding to the center of the two rows of balls of the outer ring, and a through hole for the lubricating oil outlet is provided at the end of the outer ring far from the pinion gear. Preferably it is. In this case, a lubricating oil groove extending in the axial direction is formed on the inner periphery of the casing, and both through holes are provided so as to communicate with the lubricating oil groove. If it does in this way, circulation of lubricating oil in a bearing part by the side of the counter gear which tends to occur seizure is promoted, and seizure resistance performance improves.
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、１対の内輪、１つの外輪および両輪間に配された２列の玉からなる複列アンギュラー玉軸受が使用されるとともに、玉軸受の潤滑は、ケーシング内を循環する潤滑油によって行われているので、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、耐焼付き性能が向上し、しかも、回転トルクが小さくなり、燃費を向上することができる。 According to the pinion shaft supporting bearing device of the present invention, as the rolling bearing, a double row angular contact ball bearing composed of a pair of inner rings, one outer ring and two rows of balls arranged between the two rings is used. Since the lubrication is performed with lubricating oil circulating in the casing, the seizure resistance performance is improved and the rotational torque is reduced compared to the conventional pinion shaft support bearing device using tapered roller bearings. , Fuel economy can be improved.
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 shows an embodiment in which the pinion shaft support 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.
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。 The pinion shaft support bearing device (1) includes a pinion shaft (2) having a pinion gear (3) disposed at the left end, and a rolling bearing that rotatably supports the pinion shaft (2) on the casing (4). (5). 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)の中心線（左右の内輪(11)(12)の外側端面間の中心線）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 ) To the left by half the difference in width of the shoulders (11b) and (12b) of the inner rings (11) and (12) from the center line of the inner rings (11 and 12). Is different in that.
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（左右の内輪(11)(12)の外側端面間の中心線）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（左右の内輪(11)(12)の外側端面間の中心線）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 at which the contact angle direction of the ball (14) in the row closer to the pinion gear (3) and the axis L intersect is the gear side action point P1, and the row farther from the pinion gear (3) The point where the contact angle direction of the ball (15) intersects the axis L is the counter gear side action point P2, and the center line of the rolling bearing (5) ( center line between the outer end faces of the left and right inner rings (11), (12)) ) The distance W1 from O to the gear side action point P1 is the center line of the rolling bearing (5) (center line between the outer end faces of the left and right inner rings (11), 12) The distance from O to the counter gear side action point P2 It is larger than W2 (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（左右の内輪(11)(12)の外側端面間の中心線）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（左右の内輪(11)(12)の外側端面間の中心線）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). The center line of the rolling bearing (5) (center line between the outer end faces of the left and right inner rings (11) and (12)) The distance W1 from O to the gear side action point P1 is the center line of the rolling bearing (5) (the left and right inner rings (11) The center line between the outer end faces of (12)) When the distance W2 from O to the counter gear side action point P2 is made larger, the position of the gear side action point P1 can be separated from the gear meshing point G. As a result, the load on the bearing portion closer to the pinion gear (3) to which a large load is applied is reduced, and the life is longer than when the left and right inner rings have the same width. Incidentally, W1> To and W2 is a different width inner ring of the left right, it may be also changed further contact angle.
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.
(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
(11)(12) 左右内輪
(13) 外輪
(14)(15) 玉
(19) Ｏリング
(20) Ｏリング収納溝
(21) 潤滑油入口用貫通孔
(22) 潤滑油出口用貫通孔
(23) 潤滑油溝
Ｐ１ ギア側作用点
Ｐ２ 反ギア側作用点
Ｏ 転がり軸受中心線
(1) Pinion shaft support bearing device
(2) Pinion shaft
(3) Pinion gear
(4) Casing
(5) Rolling bearing
(11) (12) Left and right inner ring
(13) Outer ring
(14) (15) Ball
(19) O-ring
(20) O-ring storage groove
(21) Lubricant inlet through hole
(22) Lubricating oil outlet through hole
(23) Lubricating oil groove P1 Gear side action point P2 Anti-gear side action point O Rolling bearing center line
Claims (4)
転がり軸受として、軌道溝の形状が互いに同じとされた１対の内輪、１対の内輪の境界線に対して対称な軌道溝が形成された１つの外輪および各内輪と外輪との間に配された２列の同径の玉を有し、２列の玉の接触角が互いに同じとなる複列アンギュラー玉軸受が使用されており、玉軸受の潤滑は、ケーシング内を循環する潤滑油によって行われており、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、両内輪の外側端面間の中心線からギア側作用点までの距離が両内輪の外側端面間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, a pair of inner rings with the same shape of the raceway grooves, one outer ring with a symmetrical raceway groove formed with respect to the boundary line of the pair of inner rings, and an inner ring and an outer ring are arranged. have been two rows have a ball of the same diameter, double row angular contact ball bearing contact angle of the two rows balls is the same as each other are used, lubrication of the ball bearings, the lubricating oil circulating within the casing The width of the shoulder of the inner ring closer to the pinion gear is narrower than the width of the shoulder of the inner ring farther from the pinion gear, so that the row closer to the pinion gear Both inner rings have the point where the contact angle direction of the ball intersects the axis as the gear side action point, and the point where the contact angle direction of the ball farthest from the pinion gear and the axis intersects as the counter gear side action point. The distance from the center line between the outer end faces of the two to the gear side action point is the outer end face of both inner rings. A pinion shaft supporting bearing device characterized in that it is made larger than the distance from the center line between them to the non-gear-side action point.
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| JP2004187294A JP4687019B2 (en) | 2004-06-25 | 2004-06-25 | Pinion shaft support bearing device |
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| JP2004187294A JP4687019B2 (en) | 2004-06-25 | 2004-06-25 | Pinion shaft support bearing device |
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| JP4687019B2 true JP4687019B2 (en) | 2011-05-25 |
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| JP2010091013A (en) | 2008-10-08 | 2010-04-22 | Sumitomo Heavy Ind Ltd | Supporting structure of shaft of reduction gear |
| FR3018860B1 (en) * | 2014-03-21 | 2021-10-15 | Hispano Suiza Sa | ACCESSORY RELAYS FOR GAS TURBINE ENGINES |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5374653A (en) * | 1976-12-01 | 1978-07-03 | Skf Nova Ab | Bearing device |
| JPS63207725A (en) * | 1987-02-21 | 1988-08-29 | ドクトル・インゲニ−ウル・ハ−・ツエ−・エフ・ポルシエ・アクチエンゲゼルシヤフト | Bearing device for bevel pinion of axle drive |
| JPH09303537A (en) * | 1996-05-10 | 1997-11-25 | Kubota Corp | Oil tank structure for tractor |
| JPH11182655A (en) * | 1997-12-17 | 1999-07-06 | Mitsubishi Motors Corp | Lubrication structure of final reduction gear unit |
| JP2000002239A (en) * | 1998-06-16 | 2000-01-07 | Tochigi Fuji Ind Co Ltd | Thrust bearing mechanism |
| JP2001280501A (en) * | 2000-03-31 | 2001-10-10 | Sanyo Denki Co Ltd | Sealing structure and dynamo-electric machine |
| JP2004028141A (en) * | 2002-06-21 | 2004-01-29 | Nsk Ltd | Shaft supporting device |
| JP2004169889A (en) * | 2002-11-22 | 2004-06-17 | Koyo Seiko Co Ltd | Pinion shaft supporting bearing device, and pinion shaft supporting device |
-
2004
- 2004-06-25 JP JP2004187294A patent/JP4687019B2/en not_active Expired - Lifetime
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5374653A (en) * | 1976-12-01 | 1978-07-03 | Skf Nova Ab | Bearing device |
| JPS63207725A (en) * | 1987-02-21 | 1988-08-29 | ドクトル・インゲニ−ウル・ハ−・ツエ−・エフ・ポルシエ・アクチエンゲゼルシヤフト | Bearing device for bevel pinion of axle drive |
| JPH09303537A (en) * | 1996-05-10 | 1997-11-25 | Kubota Corp | Oil tank structure for tractor |
| JPH11182655A (en) * | 1997-12-17 | 1999-07-06 | Mitsubishi Motors Corp | Lubrication structure of final reduction gear unit |
| JP2000002239A (en) * | 1998-06-16 | 2000-01-07 | Tochigi Fuji Ind Co Ltd | Thrust bearing mechanism |
| JP2001280501A (en) * | 2000-03-31 | 2001-10-10 | Sanyo Denki Co Ltd | Sealing structure and dynamo-electric machine |
| JP2004028141A (en) * | 2002-06-21 | 2004-01-29 | Nsk Ltd | Shaft supporting device |
| JP2004169889A (en) * | 2002-11-22 | 2004-06-17 | Koyo Seiko Co Ltd | Pinion shaft supporting bearing device, and pinion shaft supporting device |
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