JP2017096448A - Gear shaft supporting device and rolling bearing - Google Patents

Gear shaft supporting device and rolling bearing Download PDF

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JP2017096448A
JP2017096448A JP2015230803A JP2015230803A JP2017096448A JP 2017096448 A JP2017096448 A JP 2017096448A JP 2015230803 A JP2015230803 A JP 2015230803A JP 2015230803 A JP2015230803 A JP 2015230803A JP 2017096448 A JP2017096448 A JP 2017096448A
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inner ring
gear
gear shaft
shaft
raceway surface
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健 岩脇
Takeshi Iwawaki
健 岩脇
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JTEKT Corp
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  • Mounting Of Bearings Or Others (AREA)
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Abstract

PROBLEM TO BE SOLVED: To provide a gear shaft supporting device capable of preventing creep of an inner ring to a gear shaft and a rolling bearing.SOLUTION: A gear shaft supporting device 10 includes a gear shaft 6 having an axial shaft portion 61 and a gear portion 62 projecting to an outer part of the shaft portion 61, an inner ring 2 externally fitted to the shaft portion 61, an outer ring 3 fixed to a supporting body, and a plurality of rolling elements 41, 42 disposed between the inner ring 2 and the outer ring 3, and rolling on inner raceway surfaces 21a, 22a formed on the inner ring 2 and outer raceway surfaces 30a, 30b formed on the outer ring 3. The inner ring 2 is provided with a fitting portion 620 fitted to the gear portion 62, on a side face opposed to the gear portion 62, and restricted in relative rotation to the gear shaft 6 by fitting of the fitting potion 620.SELECTED DRAWING: Figure 2

Description

本発明は、ギヤ部を有するギヤ軸が支持体に回転可能に支持されたギヤ軸支持装置、及びギヤ軸を支持体に対して回転可能に支持するための転がり軸受に関する。   The present invention relates to a gear shaft support device in which a gear shaft having a gear portion is rotatably supported by a support, and a rolling bearing for rotatably supporting the gear shaft with respect to the support.

従来、例えば自動車のトランスミッションやトランスファあるいはディファレンシャル装置には、駆動力を伝達するためのギヤ軸が転がり軸受によって回転可能に支持されている。ギヤ軸は、軸状の軸部と、外周面に複数のギヤ歯が設けられたギヤ部とを有し、軸部が転がり軸受を介してケース部材に設けられた支持部に支持されている（例えば、特許文献１参照）。   Conventionally, for example, in a transmission, a transfer, or a differential device of an automobile, a gear shaft for transmitting a driving force is rotatably supported by a rolling bearing. The gear shaft has a shaft-shaped shaft portion and a gear portion provided with a plurality of gear teeth on the outer peripheral surface, and the shaft portion is supported by a support portion provided on the case member via a rolling bearing. (For example, refer to Patent Document 1).

特許文献１には、ディファレンシャルケース内に配置されたギヤ軸（ピニオンギヤシャフト）を一対の転がり軸受によって支持する支持構造が記載されている。転がり軸受は、内輪及び外輪と、内輪と外輪との間に配置された複数の転動体とを有し、内輪がギヤ軸の軸部に外嵌され、外輪がディファレンシャルケースに固定されている。ギヤ軸の一端部には雄ねじが形成され、この雄ねじに螺合するナット部材の締付力によって一対の転がり軸受に予圧が付与されている。そして、この予圧によってギヤ軸の支持剛性が増し、ギヤ軸の位置が安定化されている。   Patent Document 1 describes a support structure in which a gear shaft (pinion gear shaft) disposed in a differential case is supported by a pair of rolling bearings. The rolling bearing has an inner ring and an outer ring, and a plurality of rolling elements arranged between the inner ring and the outer ring, the inner ring is fitted on the shaft portion of the gear shaft, and the outer ring is fixed to the differential case. A male screw is formed at one end of the gear shaft, and a preload is applied to the pair of rolling bearings by a tightening force of a nut member screwed into the male screw. The preload increases the support rigidity of the gear shaft and stabilizes the position of the gear shaft.

特開２０１３−９２２４５号公報JP 2013-92245 A

上記のように構成されたギヤ軸の支持構造において、予圧抜けを防止するために初期予圧を高く設定すると、転がり軸受に余分な荷重を常時負荷することとなり、軸受寿命が短くなる。また、内輪は、その側面がギヤ部に押し付けられてギヤ軸との相対回転が抑制され、クリープの発生が抑えられるが、初期予圧が低いとクリープが発生しやすくなる。なお、クリープを防止するために内輪におけるギヤ軸の軸部に対する締め代を大きく設定すれば、内輪を軸部に外嵌する際に予め内輪を加熱した状態で圧入する必要があり、組立工数及び製造コストの上昇を招来してしまう。ここで、クリープとは、内輪がギヤ軸に対して周方向に微動することをいう。このクリープは、ギヤ軸の外周面又は内輪の内周面における摩耗や焼き付きの発生原因となり得る。   In the gear shaft support structure configured as described above, if the initial preload is set high in order to prevent preload loss, an extra load is always applied to the rolling bearing, and the bearing life is shortened. In addition, the side surface of the inner ring is pressed against the gear portion to suppress the relative rotation with the gear shaft and the occurrence of creep is suppressed. However, if the initial preload is low, the creep tends to occur. In order to prevent creep, if the allowance for the shaft part of the gear shaft in the inner ring is set large, it is necessary to press-fit the inner ring in a heated state when the inner ring is fitted onto the shaft part. The manufacturing cost will increase. Here, creep means that the inner ring slightly moves in the circumferential direction with respect to the gear shaft. This creep can cause wear and seizure on the outer peripheral surface of the gear shaft or the inner peripheral surface of the inner ring.

そこで、本発明は、ギヤ軸に対する内輪のクリープを防ぐことが可能なギヤ軸支持装置及び転がり軸受を提供することを目的とする。   Accordingly, an object of the present invention is to provide a gear shaft support device and a rolling bearing capable of preventing creep of the inner ring with respect to the gear shaft.

本発明は、上記の目的を達成するため、軸状の軸部及び前記軸部の外方に突出したギヤ部を有するギヤ軸と、前記軸部に外嵌された内輪と、支持体に固定された外輪と、前記内輪と前記外輪との間に配置され、前記内輪に形成された内側軌道面及び前記外輪に形成された外側軌道面を転動する複数の転動体とを備え、前記内輪は、前記ギヤ部に対向する側面に前記ギヤ部と嵌合する嵌合部が形成され、前記嵌合部の嵌合によって前記ギヤ軸との相対回転が規制される、ギヤ軸支持装置を提供する。   In order to achieve the above object, the present invention provides a gear shaft having a shaft-shaped shaft portion and a gear portion protruding outward from the shaft portion, an inner ring externally fitted to the shaft portion, and fixed to a support body. The inner ring, and a plurality of rolling elements that are disposed between the inner ring and the outer ring and roll on an inner raceway surface formed on the inner ring and an outer raceway surface formed on the outer ring. Provides a gear shaft support device in which a fitting portion that fits with the gear portion is formed on a side surface facing the gear portion, and relative rotation with the gear shaft is restricted by the fitting of the fitting portion. To do.

また、本発明は、上記の目的を達成するため、軸状の軸部及び前記軸部の外方に突出したギヤ部を有するギヤ軸を支持体に対して回転可能に支持する転がり軸受であって、前記軸部に外嵌される内輪と、前記支持体に固定される外輪と、前記内輪と前記外輪との間に配置され、前記内輪に形成された内側軌道面及び前記外輪に形成された外側軌道面を転動する複数の転動体とを備え、前記内輪は、前記ギヤ部に対向する側面に前記ギヤ部と嵌合する嵌合部が形成され、前記嵌合部の嵌合によって前記ギヤ軸との相対回転が規制される、転がり軸受を提供する。   In order to achieve the above object, the present invention is a rolling bearing that rotatably supports a gear shaft having a shaft-shaped shaft portion and a gear portion protruding outward from the shaft portion with respect to a support. An inner ring that is externally fitted to the shaft portion, an outer ring that is fixed to the support, and an inner raceway surface formed on the inner ring and the outer ring that is disposed between the inner ring and the outer ring. A plurality of rolling elements that roll on the outer raceway surface, and the inner ring has a fitting portion that is fitted to the gear portion on a side surface facing the gear portion, and the fitting portion engages with the fitting portion. Provided is a rolling bearing in which relative rotation with the gear shaft is restricted.

本発明によれば、ギヤ軸に対する内輪のクリープを防ぐことが可能となる。   According to the present invention, it is possible to prevent creep of the inner ring with respect to the gear shaft.

本発明の第１の実施の形態に係る転がり軸受を示す斜視図である。It is a perspective view which shows the rolling bearing which concerns on the 1st Embodiment of this invention. 図１に示す転がり軸受によってトランスミッションケース９にギヤ軸が回転可能に支持されたギヤ軸支持装置の構成例を示す断面図である。It is sectional drawing which shows the structural example of the gear shaft support apparatus by which the gear shaft was rotatably supported by the transmission case 9 by the rolling bearing shown in FIG. 図２の一部を拡大して示す拡大図である。It is an enlarged view which expands and shows a part of FIG. （ａ）は、第１内輪部材の嵌合部を周方向に沿う断面で示す断面図であり、（ｂ）は、嵌合部の別例を示す断面図である。(A) is sectional drawing which shows the fitting part of a 1st inner ring member in the cross section along a circumferential direction, (b) is sectional drawing which shows another example of a fitting part. ギヤ軸及び補助ギヤ部材の側面を、内輪の内側におけるギヤ軸の軸部の断面と共に軸方向から見た状態を示す側面図である。It is a side view which shows the state which looked at the side surface of the gear shaft and the auxiliary gear member from the axial direction together with the cross section of the shaft portion of the gear shaft inside the inner ring. （ａ）は、第２の実施の形態に係る内輪及びその周辺部を示す拡大図である。（ｂ）は、内輪を製造する際の加締め工程を示す概略の説明図である。(A) is an enlarged view which shows the inner ring | wheel which concerns on 2nd Embodiment, and its peripheral part. (B) is a schematic explanatory drawing which shows the caulking process at the time of manufacturing an inner ring. 第３の実施の形態に係る内輪及びその周辺部を示す拡大図である。It is an enlarged view which shows the inner ring | wheel which concerns on 3rd Embodiment, and its peripheral part. 第４の実施の形態に係る第１内輪部材の嵌合部の周辺部を示す拡大図である。It is an enlarged view which shows the peripheral part of the fitting part of the 1st inner ring member which concerns on 4th Embodiment. 第５実施の形態に係る第１内輪部材の嵌合部の周辺部を示す拡大図である。It is an enlarged view which shows the peripheral part of the fitting part of the 1st inner ring member which concerns on 5th Embodiment. 第６の実施の形態に係る転がり軸受を示す斜視図である。It is a perspective view which shows the rolling bearing which concerns on 6th Embodiment.

［第１の実施の形態］
本発明の第１の実施の形態について、図１乃至図４を参照して説明する。なお、本実施の形態では、自動車のトランスミッションに本発明を適用した場合について説明するが、本発明はこれに限らず、トランスファやディファレンシャル装置等の自動車における駆動力伝達系を構成する各装置や、各種の工作機械等に適用することが可能である。 [First Embodiment]
A first embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the case where the present invention is applied to a transmission of an automobile will be described.However, the present invention is not limited to this, and each device constituting a driving force transmission system in an automobile such as a transfer or a differential device, It can be applied to various machine tools.

図１は、本発明の第１の実施の形態に係る転がり軸受１を示す斜視図である。図２は、図１に示す転がり軸受１によって、支持体としてのトランスミッションケース９にギヤ軸６が回転可能に支持されたギヤ軸支持装置１０の構成例を示す断面図である。図３は、図２の一部を拡大して示す拡大図である。   FIG. 1 is a perspective view showing a rolling bearing 1 according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view showing a configuration example of a gear shaft support device 10 in which a gear shaft 6 is rotatably supported by a transmission case 9 as a support by the rolling bearing 1 shown in FIG. FIG. 3 is an enlarged view showing a part of FIG.

転がり軸受１は、内輪２及び外輪３と、内輪２と外輪３との間に配置された複数の転動体４１，４２と、複数の転動体４１，４２を転動可能に保持する保持器５１，５２とを備えている。ギヤ軸支持装置１０は、転がり軸受１と、転がり軸受１によって回転可能に支持されるギヤ軸６とを備えて構成されている。   The rolling bearing 1 includes an inner ring 2 and an outer ring 3, a plurality of rolling elements 41 and 42 disposed between the inner ring 2 and the outer ring 3, and a cage 51 that holds the plurality of rolling elements 41 and 42 in a rollable manner. , 52. The gear shaft support device 10 includes a rolling bearing 1 and a gear shaft 6 that is rotatably supported by the rolling bearing 1.

本実施の形態では、転がり装置１が複列円錐ころ軸受であり、複数の転動体４１を内輪２及び外輪３の周方向に沿って等間隔に配置してなる第１の転動体列４ａと、複数の転動体４２を内輪２及び外輪３の周方向に沿って等間隔に配置してなる第２の転動体列４ｂとを有している。第１の転動体列４ａの複数の転動体４１は、保持器５１に保持されている。第２の転動体列４ｂの複数の転動体４２は、保持器５２に保持されている。   In the present embodiment, the rolling device 1 is a double-row tapered roller bearing, and a plurality of rolling elements 41 are arranged at equal intervals along the circumferential direction of the inner ring 2 and the outer ring 3; The second rolling element row 4 b is formed by arranging a plurality of rolling elements 42 at equal intervals along the circumferential direction of the inner ring 2 and the outer ring 3. The plurality of rolling elements 41 in the first rolling element row 4 a are held by a cage 51. The plurality of rolling elements 42 in the second rolling element row 4 b are held by a cage 52.

外輪３は、円筒状の本体部３０と、本体部３０の軸方向一端部から外方に突出して形成されたフランジ部３１とを一体に有している。本体部３０の内周面には、第１の転動体列４ａの複数の転動体４１を転動させる第１外側軌道面３０ａ、及び第２の転動体列４ｂの複数の転動体４２を転動させる第２外側軌道面３０ｂが軸方向に並んで形成されている。第１外側軌道面３０ａ及び第２外側軌道面３０ｂは、外輪３の軸方向両端部に近づくほど内径が大きくなるテーパ状である。   The outer ring 3 integrally includes a cylindrical main body portion 30 and a flange portion 31 formed to protrude outward from one axial end portion of the main body portion 30. The first outer raceway surface 30a for rolling the plurality of rolling elements 41 of the first rolling element row 4a and the plurality of rolling elements 42 of the second rolling element row 4b are rolled on the inner peripheral surface of the main body 30. The second outer raceway surface 30b to be moved is formed side by side in the axial direction. The first outer raceway surface 30 a and the second outer raceway surface 30 b are tapered so that the inner diameter increases as they approach the axial both ends of the outer ring 3.

外輪３のフランジ部３１は、支持体としてのトランスミッションケース９に固定されている。より具体的には、フランジ部３１に形成された複数のボルト挿通孔３１０を挿通するボルト９１によって、フランジ部３１がトランスミッションケース９の支持部９０に固定されている。支持部９０には、外輪３の本体部３０が内部に挿通される挿通孔９００、及びボルト９１が螺合する複数のねじ孔９０１が形成されている。   The flange portion 31 of the outer ring 3 is fixed to a transmission case 9 as a support. More specifically, the flange portion 31 is fixed to the support portion 90 of the transmission case 9 by bolts 91 that pass through a plurality of bolt insertion holes 310 formed in the flange portion 31. The support portion 90 is formed with an insertion hole 900 through which the main body portion 30 of the outer ring 3 is inserted, and a plurality of screw holes 901 into which the bolts 91 are screwed.

内輪２、外輪３、及び複数の転動体４１，４２は、例えば炭素鋼や浸炭鋼等の鋼材からなり、トランスミッションケース９は例えばアルミニウム合金等の軽合金からなる。挿通孔９００の内周面と外輪３の本体部３０の外周面との間には、径方向の隙間Ｓが形成されている。この隙間Ｓは、外輪３とトランスミッションケース９との線膨張係数の違いにより、特に低温時において転がり軸受１に作用する予圧が高くなり過ぎることを防ぐために設けられたものである。   The inner ring 2, the outer ring 3, and the plurality of rolling elements 41, 42 are made of a steel material such as carbon steel or carburized steel, and the transmission case 9 is made of a light alloy such as an aluminum alloy. A radial gap S is formed between the inner peripheral surface of the insertion hole 900 and the outer peripheral surface of the main body 30 of the outer ring 3. This gap S is provided to prevent the preload acting on the rolling bearing 1 from becoming too high due to the difference in the linear expansion coefficient between the outer ring 3 and the transmission case 9, particularly at low temperatures.

つまり、軽合金からなるトランスミッションケース９は、鋼材からなる外輪３よりも温度変化によって膨張及び収縮しやすいため、高温時に予圧抜けが発生しないようにするためには、常温時における予圧を高くする必要がある。しかし、この場合、低温時にトランスミッションケース９が収縮すると、外輪３の本体部３０が外周側から締め付けられ、予圧が高くなり過ぎるおそれがある。そこで、本実施の形態では、隙間Ｓによって線膨張係数の違いによる影響を緩和している。すなわち、低温時にトランスミッションケース９が収縮した際には、隙間Ｓが設けられていることにより、外輪３の本体部３０がトランスミッションケース９によって外周側から締め付けられることが抑止される。隙間Ｓの寸法ｄは、常温において例えば３０〜４０μｍであることが望ましい。   In other words, the transmission case 9 made of a light alloy is more easily expanded and contracted by a temperature change than the outer ring 3 made of a steel material. Therefore, in order to prevent preload loss at high temperatures, it is necessary to increase the preload at room temperature. There is. However, in this case, when the transmission case 9 contracts at a low temperature, the main body 30 of the outer ring 3 is tightened from the outer peripheral side, and the preload may become too high. Therefore, in the present embodiment, the influence due to the difference in the linear expansion coefficient is mitigated by the gap S. That is, when the transmission case 9 contracts at a low temperature, the clearance S is provided, so that the main body 30 of the outer ring 3 is prevented from being tightened from the outer peripheral side by the transmission case 9. The dimension d of the gap S is desirably, for example, 30 to 40 μm at room temperature.

内輪２は、第１外側軌道面３０ａに対向する第１内側軌道面２１ａを外周面に有する第１内輪部材２１と、第２外側軌道面３０ｂに対向する第２内側軌道面２２ａを外周面に有する第２内輪部材２２とを有している。本実施の形態では、第１内輪部材２１と第２内輪部材２２とがギヤ軸６の回転軸線Ｏと平行な軸方向に並び、互いの側面が当接するように配置されている。   The inner ring 2 has a first inner ring member 21 having a first inner raceway surface 21a facing the first outer raceway surface 30a on the outer peripheral surface, and a second inner raceway surface 22a facing the second outer raceway surface 30b on the outer peripheral surface. And a second inner ring member 22. In the present embodiment, the first inner ring member 21 and the second inner ring member 22 are arranged in an axial direction parallel to the rotation axis O of the gear shaft 6 so that the side surfaces thereof are in contact with each other.

ギヤ軸６は、軸状の軸部６１、及び軸部６１の外方に突出したギヤ部６２を有し、転がり軸受１によってトランスミッションケース９に対して回転可能に支持されている。ギヤ部６２の外周部には、複数のギヤ歯６２１が設けられている。軸部６１には、内輪２が外嵌されている。また、ギヤ部６２は、内輪２の内側における軸部６１の外径Ｄ１よりも大きな外径Ｄ２を有する円筒部６２２を有している。この円筒部６２２には、補助ギヤ部材７が外嵌されている。補助ギヤ部材７の外周部には、複数のギヤ歯７１が設けられている。補助ギヤ部材７の内周端部７２は、ギヤ軸６におけるギヤ部６２の円筒部６２２の外周面に対向する内周面を有し、かつ第１内輪部材２１の側面と軸方向に対向している。 The gear shaft 6 includes a shaft-shaped shaft portion 61 and a gear portion 62 protruding outward from the shaft portion 61, and is supported by the rolling bearing 1 so as to be rotatable with respect to the transmission case 9. A plurality of gear teeth 621 are provided on the outer peripheral portion of the gear portion 62. The inner ring 2 is fitted on the shaft portion 61. The gear portion 62 has a cylindrical portion 622 having an outer diameter D 2 that is larger than the outer diameter D 1 of the shaft portion 61 inside the inner ring 2. The auxiliary gear member 7 is fitted on the cylindrical portion 622. A plurality of gear teeth 71 are provided on the outer peripheral portion of the auxiliary gear member 7. The inner peripheral end portion 72 of the auxiliary gear member 7 has an inner peripheral surface that opposes the outer peripheral surface of the cylindrical portion 622 of the gear portion 62 of the gear shaft 6, and is opposed to the side surface of the first inner ring member 21 in the axial direction. ing.

ギヤ部６２のギヤ歯６２１には、トランスミッションケース９内で回転可能に支持された入力回転部材８１のギヤ歯８１１が噛み合っている。ギヤ歯６２１，８１１は、歯筋が軸方向に対して傾斜した斜歯である。ギヤ軸６は、入力回転部材８１から入力される回転力によって回転軸線Ｏを中心として回転する。   The gear teeth 621 of the gear portion 62 are engaged with the gear teeth 811 of the input rotation member 81 that is rotatably supported in the transmission case 9. The gear teeth 621 and 811 are oblique teeth whose tooth traces are inclined with respect to the axial direction. The gear shaft 6 rotates about the rotation axis O by the rotational force input from the input rotation member 81.

補助ギヤ部材７のギヤ歯７１には、トランスミッションケース９内で回転可能に支持された出力回転部材８２のギヤ歯８２１が噛み合っている。補助ギヤ部材７は、ギヤ軸６と共に回転し、ギヤ軸６に入力された回転力の一部を出力回転部材８２に出力する。なお、補助ギヤ部材７には、出力回転部材８２に替えて、ギヤ軸６の回転を停止させるためのロックギヤを噛み合わせてもよい。   The gear teeth 71 of the auxiliary gear member 7 mesh with the gear teeth 821 of the output rotating member 82 that is rotatably supported in the transmission case 9. The auxiliary gear member 7 rotates together with the gear shaft 6, and outputs a part of the rotational force input to the gear shaft 6 to the output rotating member 82. The auxiliary gear member 7 may be engaged with a lock gear for stopping the rotation of the gear shaft 6 instead of the output rotating member 82.

ギヤ軸６には、軸部６１の端部に雄ねじ６１０が形成されている。この雄ねじ６１０には、ナット６０が螺合している。転がり軸受１には、ナット６０の締付力による予圧が付与されている。また、内輪２は、ナット６０の締付力によって、後述する嵌合部２１０がギヤ軸６のギヤ部６２に押し付けられている。   The gear shaft 6 is formed with a male screw 610 at the end of the shaft portion 61. A nut 60 is screwed into the male screw 610. The rolling bearing 1 is preloaded with a tightening force of the nut 60. Further, in the inner ring 2, a fitting portion 210 described later is pressed against the gear portion 62 of the gear shaft 6 by the tightening force of the nut 60.

内輪２は、ギヤ軸６のギヤ部６２及び補助ギヤ部材７側に第１内輪部材２１が配置され、ナット６０側に第２内輪部材２２が配置されている。第１内輪部材２１の第１内側軌道面２１ａは、ギヤ軸６のギヤ部６２及び補助ギヤ部材７側ほど外径が大きくなるテーパ状である。第２内輪部材２２の第２内側軌道面２２ａは、ナット６０側ほど外径が大きくなるテーパ状である。   In the inner ring 2, the first inner ring member 21 is disposed on the gear portion 62 and auxiliary gear member 7 side of the gear shaft 6, and the second inner ring member 22 is disposed on the nut 60 side. The first inner raceway surface 21a of the first inner ring member 21 is tapered so that the outer diameter increases toward the gear portion 62 and the auxiliary gear member 7 side of the gear shaft 6. The second inner raceway surface 22a of the second inner ring member 22 has a tapered shape whose outer diameter increases toward the nut 60 side.

第１内輪部材２１は、ギヤ軸６のギヤ部６２に対向する側面２１ｂに、ギヤ部６２と嵌合する嵌合部２１０が形成されている。本実施の形態では、この嵌合部２１０が、軸方向に突出した複数の突起２１１からなる歯車状である。複数の突起２１１は、図１に示すように径方向に延びる突条として形成され、第１内輪部材２１の側面２１ｂの周方向全体にわたって等間隔に設けられている。   In the first inner ring member 21, a fitting portion 210 that fits with the gear portion 62 is formed on the side surface 21 b facing the gear portion 62 of the gear shaft 6. In the present embodiment, the fitting portion 210 has a gear shape composed of a plurality of protrusions 211 protruding in the axial direction. As shown in FIG. 1, the plurality of protrusions 211 are formed as ridges extending in the radial direction, and are provided at equal intervals over the entire circumferential direction of the side surface 21 b of the first inner ring member 21.

図４（ａ）は、第１内輪部材２１の嵌合部２１０を周方向に沿う断面で示す断面図である。複数の突起２１１は、軸方向の先端部ほど歯厚が薄くなる台形状であり、歯先面２１１ａは平坦面である。歯先面２１１ａを挟む両歯面２１１ｂ，２１１ｃがなす角度θは、例えば６０±１５°（４５°以上７５°以下）である。なお、別例として、図４（ｂ）に示すように、突起２１１が平坦な歯先面２１１ａを有しない、周方向に沿う断面が三角形状の突条であってもよい。この場合でも、突起２１１の稜線を挟む両歯面２１１ｂ，２１１ｃがなす角度θは６０±１５°であるとよい。   FIG. 4A is a cross-sectional view showing the fitting portion 210 of the first inner ring member 21 in a cross section along the circumferential direction. The plurality of protrusions 211 have a trapezoidal shape in which the tooth thickness becomes thinner toward the tip in the axial direction, and the tooth tip surface 211a is a flat surface. An angle θ formed by both tooth surfaces 211b and 211c sandwiching the tooth tip surface 211a is, for example, 60 ± 15 ° (45 ° or more and 75 ° or less). As another example, as shown in FIG. 4B, the protrusion 211 may not have a flat tooth tip surface 211a, and the protrusion along the circumferential direction may be a triangular protrusion. Even in this case, the angle θ formed by the two tooth surfaces 211b and 211c sandwiching the ridge line of the protrusion 211 is preferably 60 ± 15 °.

図５は、ギヤ軸６及び補助ギヤ部材７の側面を、内輪２の内側におけるギヤ軸６の軸部６１の断面と共に軸方向から見た状態を示す側面図である。ギヤ軸６のギヤ部６２における円筒部６２２の軸方向端面には、第１内輪部材２１の嵌合部２１０における複数の突起２１１に噛み合う複数の突起６２３が形成されている。ギヤ軸６の複数の突起６２３は、第１内輪部材２１の複数の突起２１１に対応する形状を有している。この複数の突起６２３により、ギヤ軸６のギヤ部６２における円筒部６２２の軸方向端面には、第１内輪部材２１の嵌合部２１０が嵌合する被嵌合部６２０が形成されている。   FIG. 5 is a side view showing a state in which the side surfaces of the gear shaft 6 and the auxiliary gear member 7 are viewed from the axial direction along with the cross section of the shaft portion 61 of the gear shaft 6 inside the inner ring 2. A plurality of protrusions 623 that mesh with the plurality of protrusions 211 in the fitting portion 210 of the first inner ring member 21 are formed on the axial end surface of the cylindrical portion 622 of the gear portion 62 of the gear shaft 6. The plurality of protrusions 623 of the gear shaft 6 have a shape corresponding to the plurality of protrusions 211 of the first inner ring member 21. By the plurality of protrusions 623, a fitted portion 620 to which the fitting portion 210 of the first inner ring member 21 is fitted is formed on the axial end surface of the cylindrical portion 622 of the gear portion 62 of the gear shaft 6.

また、補助ギヤ部材７において第１内輪部材２１の側面２１ｂと軸方向に対向する内周端部７２の軸方向端面には、第１内輪部材２１の嵌合部２１０における複数の突起２１１に噛み合う複数の突起７３が形成されている。補助ギヤ部材７の複数の突起７３は、第１内輪部材２１の複数の突起２１１に対応する形状を有している。この複数の突起７３により、補助ギヤ部材７における内周端部７２の軸方向端面には、第１内輪部材２１の嵌合部２１０が嵌合する被嵌合部７３０が形成されている。   Further, in the auxiliary gear member 7, the axial end surface of the inner peripheral end portion 72 facing the side surface 21 b of the first inner ring member 21 in the axial direction meshes with the plurality of protrusions 211 in the fitting portion 210 of the first inner ring member 21. A plurality of protrusions 73 are formed. The plurality of protrusions 73 of the auxiliary gear member 7 have a shape corresponding to the plurality of protrusions 211 of the first inner ring member 21. By the plurality of protrusions 73, a fitted portion 730 into which the fitting portion 210 of the first inner ring member 21 is fitted is formed on the axial end surface of the inner peripheral end portion 72 of the auxiliary gear member 7.

このように、第１内輪部材２１の複数の突起２１１には、ギヤ軸６のギヤ部６２における複数の突起６２３、及び補助ギヤ部材７の内周端部７２における複数の突起７３が噛み合う。換言すれば、第１内輪部材２１の嵌合部２１０は、ギヤ軸６のギヤ部６２及び補助ギヤ部材７の内周端部７２に嵌合する。これにより、第１内輪部材２１は、嵌合部２１０の嵌合によって、ギヤ軸６との相対回転、及び補助ギヤ部材７との相対回転が規制される。また、補助ギヤ部材７は、内輪２（第１内輪部材２１）を介してギヤ軸６と一体回転するように連結される。   As described above, the plurality of projections 623 in the gear portion 62 of the gear shaft 6 and the plurality of projections 73 in the inner peripheral end portion 72 of the auxiliary gear member 7 mesh with the plurality of projections 211 of the first inner ring member 21. In other words, the fitting portion 210 of the first inner ring member 21 is fitted to the gear portion 62 of the gear shaft 6 and the inner peripheral end portion 72 of the auxiliary gear member 7. Thus, the first inner ring member 21 is restricted from relative rotation with the gear shaft 6 and relative rotation with the auxiliary gear member 7 by the fitting of the fitting portion 210. Further, the auxiliary gear member 7 is connected so as to rotate integrally with the gear shaft 6 via the inner ring 2 (first inner ring member 21).

（第１の実施の形態の効果）
以上説明した第１の実施の形態によれば、第１内輪部材２１の嵌合部２１０がギヤ軸６のギヤ部６２に形成された被嵌合部６２０に嵌合し、第１内輪部材２１のギヤ軸６との相対回転が規制される。これにより、ギヤ軸６に対する第１内輪部材２１のクリープを防ぐことができる。また、第２内輪部材２２についても、第１内輪部材２１との連れ回りによってギヤ軸６に対して回転することがなく、ギヤ軸６に対するクリープを防ぐことができる。 (Effects of the first embodiment)
According to the first embodiment described above, the fitting portion 210 of the first inner ring member 21 is fitted to the fitted portion 620 formed on the gear portion 62 of the gear shaft 6, and the first inner ring member 21 is engaged. Relative rotation with the gear shaft 6 is restricted. Thereby, the creep of the 1st inner ring member 21 with respect to the gear shaft 6 can be prevented. Further, the second inner ring member 22 does not rotate with respect to the gear shaft 6 due to the rotation with the first inner ring member 21, and creeping with respect to the gear shaft 6 can be prevented.

また、補助ギヤ部材７における内周端部７２の軸方向端面には、第１内輪部材２１の嵌合部２１０が嵌合する被嵌合部７３０が形成されているので、補助ギヤ部材７とギヤ軸６とが一体に回転する。これにより、補助ギヤ部材７とギヤ軸６とを例えばスプライン嵌合やボルト締結によって相対回転不能に連結することが不要となり、補助ギヤ部材７及びギヤ軸６の加工工数を削減することが可能となる。   Further, since the fitted portion 730 into which the fitting portion 210 of the first inner ring member 21 is fitted is formed on the axial end surface of the inner peripheral end portion 72 of the auxiliary gear member 7, The gear shaft 6 rotates integrally. As a result, it is not necessary to connect the auxiliary gear member 7 and the gear shaft 6 so that they cannot be rotated relative to each other by, for example, spline fitting or bolt fastening, and the processing man-hours of the auxiliary gear member 7 and the gear shaft 6 can be reduced. Become.

また、内輪２の第１内輪部材２１は、軸部６１の雄ねじ６１０に螺合するナット６０の締付力によって嵌合部２１０がギヤ軸６のギヤ部６２側に押し付けられているので、ギヤ軸６の被嵌合部６２０との嵌合、及び補助ギヤ部材７の被嵌合部７３０との嵌合が確実となる。   Further, the first inner ring member 21 of the inner ring 2 has the fitting portion 210 pressed against the gear portion 62 side of the gear shaft 6 by the tightening force of the nut 60 screwed into the male screw 610 of the shaft portion 61. The fitting of the shaft 6 with the fitted portion 620 and the fitting of the auxiliary gear member 7 with the fitted portion 730 are ensured.

［第２の実施の形態］
次に、本発明の第２の実施の形態について、図６を参照して説明する。 [Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.

図６（ａ）は、本実施の形態に係る内輪２Ａ及びその周辺部を示す拡大図である。図６（ｂ）は、内輪２Ａを製造する際の加締め工程を示す概略の説明図である。図６（ａ）ならびに後述する図７乃至１０において、第１の実施の形態について説明したものと共通する部材等については、同一の符号を付して重複した説明を省略する。   Fig.6 (a) is an enlarged view which shows 2 A of inner rings which concern on this Embodiment, and its peripheral part. FIG. 6B is a schematic explanatory view showing a caulking process when the inner ring 2A is manufactured. In FIG. 6A and FIGS. 7 to 10 described later, members and the like that are the same as those described in the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

本実施の形態に係る内輪２Ａは、第１の実施の形態と同様に、第１内輪部材２１Ａ及び第２内輪部材２２Ａによって構成されているが、本実施の形態では、第１内輪部材２１Ａが第２内輪部材２２Ａの内側を挿通する筒部２１２を有し、筒部２１２の端部が加締めされた加締め部２１３によって第２内輪部材２２Ａが第１内輪部材２１Ａに固定されると共に、複数の転動体４１，４２に予圧が付与されている。   The inner ring 2A according to the present embodiment is configured by the first inner ring member 21A and the second inner ring member 22A as in the first embodiment. However, in the present embodiment, the first inner ring member 21A is The second inner ring member 22 </ b> A is fixed to the first inner ring member 21 </ b> A by the crimping part 213 having the cylinder part 212 inserted through the inner side of the second inner ring member 22 </ b> A and the end of the cylinder part 212 being crimped. Preload is applied to the plurality of rolling elements 41, 42.

内輪２Ａは、加締め部２１３とは反対側の端部がギヤ軸６のギヤ部６２に対向するように配置され、第１内輪部材２１Ａの嵌合部２１０は、第１内輪部材２１Ａの加締め部２１３とは反対側に形成されている。第１内輪部材２１Ａの嵌合部２１０は、第１の実施の形態と同様に、ギヤ軸６の被嵌合部６２０、及び補助ギヤ部材７の被嵌合部７３０に嵌合している。   The inner ring 2A is arranged so that the end opposite to the crimping portion 213 faces the gear portion 62 of the gear shaft 6, and the fitting portion 210 of the first inner ring member 21A is connected to the first inner ring member 21A. The fastening part 213 is formed on the opposite side. The fitting portion 210 of the first inner ring member 21A is fitted to the fitted portion 620 of the gear shaft 6 and the fitted portion 730 of the auxiliary gear member 7 as in the first embodiment.

図６（ｂ）に示すように、第１内輪部材２１Ａの加締め部２１３は、加締め治具Ｊを用いた加締め加工によって形成される。加締め治具Ｊは、その中心軸Ｃ２を内輪２Ａの中心軸Ｃ１に対して所定角度で傾斜させ、中心軸Ｃ１回りに回転する。加締め治具Ｊには、中心軸Ｃ２に沿う方向の荷重が付与され、この荷重によって筒部２１２の端部が加締め治具Ｊにおける凹曲面状の当接面Ｊ０に沿って変形し、加締め部２１３となる。図６（ｂ）では、加締め前における筒部２１２の端部の形状を二点鎖線で示している。 As shown in FIG. 6B, the caulking portion 213 of the first inner ring member 21A is formed by caulking using a caulking jig J. Crimping jig J is tilted at a predetermined angle and the central axis C 2 with respect to the center axis C 1 of the inner ring 2A, it rotates about axis C 1 around. The caulking jig J, a load in the direction grant along the central axis C 2, the end portion of the cylindrical portion 212 by the load along the contact surface J 0 of the concavely curved in caulking jig J deformation And it becomes the caulking part 213. In FIG.6 (b), the shape of the edge part of the cylinder part 212 before crimping is shown with the dashed-two dotted line.

本実施の形態によっても、第１の実施の形態と同様の作用及び効果を得ることができる。また、ギヤ軸６の線膨張係数と内輪２Ａの線膨張係数とが異なる場合でも、ギヤ軸６の軸部６１と内輪２Ａとの温度変化による膨張又は収縮量の違いが予圧に与える影響を小さくすることができ、予圧変動を抑制することが可能となる。   Also according to the present embodiment, the same operation and effect as the first embodiment can be obtained. Further, even when the linear expansion coefficient of the gear shaft 6 and the linear expansion coefficient of the inner ring 2A are different, the influence of the difference in expansion or contraction due to the temperature change between the shaft portion 61 of the gear shaft 6 and the inner ring 2A on the preload is reduced. This makes it possible to suppress fluctuations in the preload.

［第３の実施の形態］
次に、本発明の第３の実施の形態について、図７を参照して説明する。 [Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIG.

図７は、本実施の形態に係る内輪２Ｂ及びその周辺部を示す拡大図である。図７に示すように、本実施の形態では、第２の実施の形態と同様に、内輪２Ｂが第１内輪部材２１Ｂ及び第２内輪部材２２Ｂを有し、第１内輪部材２１Ｂにおける筒部２１２の端部が加締められた加締め部２１３によって第２内輪部材２２Ｂが第１内輪部材２１Ｂに固定されると共に複数の転動体４１，４２に予圧が付与されているが、内輪２Ｂにおける第１内輪部材２１Ｂ及び第２内輪部材２２Ｂの並びが第２の実施の形態に係る内輪２Ａとは逆になっている。また、本実施の形態では、第１内輪部材２１Ｂの加締め部２１３がギヤ軸６のギヤ部６２に対向するように配置され、第１内輪部材２１Ｂの嵌合部２１０は、加締め部２１３に形成されている。   FIG. 7 is an enlarged view showing the inner ring 2B and its peripheral part according to the present embodiment. As shown in FIG. 7, in the present embodiment, as in the second embodiment, the inner ring 2B has a first inner ring member 21B and a second inner ring member 22B, and the cylindrical portion 212 in the first inner ring member 21B. The second inner ring member 22B is fixed to the first inner ring member 21B and the preload is applied to the plurality of rolling elements 41, 42 by the crimped portion 213 with the end of the first end thereof being crimped. The arrangement of the inner ring member 21B and the second inner ring member 22B is opposite to that of the inner ring 2A according to the second embodiment. In the present embodiment, the caulking portion 213 of the first inner ring member 21B is disposed so as to face the gear portion 62 of the gear shaft 6, and the fitting portion 210 of the first inner ring member 21B is the caulking portion 213. Is formed.

本実施の形態によっても、第２の実施の形態と同様の作用及び効果を得ることができる。また、嵌合部２１０における複数の突起２１１を加締め部２１３と同時に成形することが可能となる。つまり、加締め治具Ｊの当接面Ｊ０に、複数の突起２１１に対応する形状の凹凸を設けることにより、この凹凸形状の転写によって複数の突起２１１を成形することができる。これにより、加工工数を削減することが可能となる。 Also according to this embodiment, the same operations and effects as those of the second embodiment can be obtained. In addition, the plurality of protrusions 211 in the fitting part 210 can be formed simultaneously with the caulking part 213. In other words, the contact surface J 0 of the caulking jig J, by providing an uneven shape corresponding to a plurality of protrusions 211, it is possible to form the plurality of protrusions 211 by a transfer of the concavo-convex shape. As a result, the number of processing steps can be reduced.

［第４の実施の形態］
次に、本発明の第４の実施の形態について、図８を参照して説明する。本実施の形態は、第１の実施の形態を変形したものであり、第１内輪部材２１Ｃの形状、ならびに第１内輪部材２１Ｃ、ギヤ軸６、及び補助ギヤ部材７の嵌合構造が、第１の実施の形態とは異なっている。なお、図示は省略しているが、第１内輪部材２１Ｃにおけるギヤ軸６のギヤ部６２とは反対側にあたるギヤ部６１の外周には、第２内輪部材２２（図２，図３参照）が第１内輪部材２１Ｃと軸方向に並んで配置されている。 [Fourth Embodiment]
Next, a fourth embodiment of the present invention will be described with reference to FIG. This embodiment is a modification of the first embodiment. The shape of the first inner ring member 21C and the fitting structure of the first inner ring member 21C, the gear shaft 6, and the auxiliary gear member 7 are This is different from the first embodiment. In addition, although illustration is abbreviate | omitted, the 2nd inner ring member 22 (refer FIG. 2, FIG. 3) is provided in the outer periphery of the gear part 61 on the opposite side to the gear part 62 of the gear shaft 6 in the 1st inner ring member 21C. The first inner ring member 21C is arranged side by side in the axial direction.

図８は、本実施の形態に係る第１内輪部材２１Ｃの嵌合部２１０の周辺部を示す拡大図である。本実施の形態では、第１内輪部材２１Ｃの嵌合部２１０が補助ギヤ部材７の被嵌合部７３０に嵌合しているが、ギヤ軸６には被嵌合部６２０が形成されていない。補助ギヤ部材７とギヤ軸６とは、補助ギヤ部材７の内周端部７２における内周面に形成された複数のスプライン突起７４が、ギヤ軸６の円筒部６２２の外周面に形成された複数のスプライン突起６２４にスプライン係合することにより、相対回転不能に連結されている。   FIG. 8 is an enlarged view showing a peripheral portion of the fitting portion 210 of the first inner ring member 21C according to the present embodiment. In the present embodiment, the fitting portion 210 of the first inner ring member 21C is fitted to the fitted portion 730 of the auxiliary gear member 7, but the fitted portion 620 is not formed on the gear shaft 6. . In the auxiliary gear member 7 and the gear shaft 6, a plurality of spline protrusions 74 formed on the inner peripheral surface of the inner peripheral end portion 72 of the auxiliary gear member 7 are formed on the outer peripheral surface of the cylindrical portion 622 of the gear shaft 6. A plurality of spline protrusions 624 are connected to each other so as not to rotate relative to each other by spline engagement.

本実施の形態によれば、第１内輪部材２１Ｃの嵌合部２１０が補助ギヤ部材７の被嵌合部７３０に嵌合することにより、第１内輪部材２１Ｃと補助ギヤ部材７との相対回転が規制される。また、補助ギヤ部材７とギヤ軸６とは、複数のスプライン突起７４，６２４のスプライン係合によって相対回転不能であるので、第１内輪部材２１Ｃとギヤ軸６との相対回転も規制される。これにより、内輪２におけるクリープ現象の発生を防ぐことができる。   According to the present embodiment, when the fitting portion 210 of the first inner ring member 21C is fitted to the fitted portion 730 of the auxiliary gear member 7, the relative rotation between the first inner ring member 21C and the auxiliary gear member 7 is achieved. Is regulated. Further, since the auxiliary gear member 7 and the gear shaft 6 cannot be rotated relative to each other by the spline engagement of the plurality of spline protrusions 74 and 624, the relative rotation between the first inner ring member 21C and the gear shaft 6 is also restricted. Thereby, generation | occurrence | production of the creep phenomenon in the inner ring | wheel 2 can be prevented.

［第５の実施の形態］
次に、本発明の第５の実施の形態について、図９を参照して説明する。本実施の形態は、第４の実施の形態と同様、第１の実施の形態を変形したものであり、第１内輪部材２１Ｄの形状、ならびに第１内輪部材２１Ｄ、ギヤ軸６、及び補助ギヤ部材７の嵌合構造が、第１の実施の形態とは異なっている。第１内輪部材２１Ｄにおけるギヤ軸６のギヤ部６２とは反対側にあたるギヤ部６１の外周には、第２内輪部材２２（図２，図３参照）が第１内輪部材２１Ｄと軸方向に並んで配置されている。 [Fifth Embodiment]
Next, a fifth embodiment of the present invention will be described with reference to FIG. As in the fourth embodiment, the present embodiment is a modification of the first embodiment, and the shape of the first inner ring member 21D, the first inner ring member 21D, the gear shaft 6, and the auxiliary gear. The fitting structure of the member 7 is different from that of the first embodiment. A second inner ring member 22 (see FIGS. 2 and 3) is aligned with the first inner ring member 21D in the axial direction on the outer periphery of the gear portion 61 on the opposite side to the gear portion 62 of the gear shaft 6 in the first inner ring member 21D. Is arranged in.

図９は、本実施の形態に係る第１内輪部材２１Ｄの嵌合部２１０の周辺部を示す拡大図である。本実施の形態では、第１内輪部材２１Ｄの嵌合部２１０がギヤ軸６の被嵌合部６２０に嵌合しているが、補助ギヤ部材７には被嵌合部７３０が形成されていない。補助ギヤ部材７とギヤ軸６とは、補助ギヤ部材７の内周端部７２における内周面に形成された複数のスプライン突起７４が、ギヤ軸６の円筒部６２２の外周面に形成された複数のスプライン突起６２４にスプライン係合することにより、相対回転不能に連結されている。   FIG. 9 is an enlarged view showing a peripheral portion of the fitting portion 210 of the first inner ring member 21D according to the present embodiment. In the present embodiment, the fitting portion 210 of the first inner ring member 21D is fitted to the fitted portion 620 of the gear shaft 6, but the fitted portion 730 is not formed on the auxiliary gear member 7. . In the auxiliary gear member 7 and the gear shaft 6, a plurality of spline protrusions 74 formed on the inner peripheral surface of the inner peripheral end portion 72 of the auxiliary gear member 7 are formed on the outer peripheral surface of the cylindrical portion 622 of the gear shaft 6. A plurality of spline protrusions 624 are connected to each other so as not to rotate relative to each other by spline engagement.

本実施の形態によれば、第１内輪部材２１Ｄの嵌合部２１０がギヤ軸６の被嵌合部６２０に嵌合することにより、第１内輪部材２１Ｄとギヤ軸６との相対回転が規制される。これにより、内輪２におけるクリープ現象の発生を防ぐことができる。   According to the present embodiment, when the fitting portion 210 of the first inner ring member 21D is fitted to the fitted portion 620 of the gear shaft 6, the relative rotation between the first inner ring member 21D and the gear shaft 6 is restricted. Is done. Thereby, generation | occurrence | production of the creep phenomenon in the inner ring | wheel 2 can be prevented.

［第６の実施の形態］
次に、本発明の第６の実施の形態について、図１０を参照して説明する。 [Sixth Embodiment]
Next, a sixth embodiment of the present invention will be described with reference to FIG.

図１０は、本発明の第６の実施の形態に係る転がり軸受１Ｅを示す斜視図である。第１の実施の形態では、第１内輪部材２１の嵌合部２１０に、多数の突起２１１が側面２１ｂの周方向全体にわたって等間隔に設けられた場合について説明したが、本実施の形態に係る転がり軸受１Ｅは、第１内輪部材２１Ｅの嵌合部２１０の４つの突起２１１が十字状をなすように設けられている。この第１内輪部材２１Ｅの嵌合部２１０が嵌合する被嵌合部６２０，７３０には、第１内輪部材２１Ｅの４つの突起２１１に対応する４つの凹部が形成される。第１内輪部材２１Ｅは、第２内輪部材２２Ｅと共に内輪２Ｅを構成する。第２内輪部材２２Ｅは、第１の実施の形態に係る第２内輪部材２２と同様に形成されている。   FIG. 10 is a perspective view showing a rolling bearing 1E according to the sixth embodiment of the present invention. In 1st Embodiment, although the case where many protrusions 211 were provided in the fitting part 210 of the 1st inner ring member 21 at equal intervals over the whole circumferential direction of the side surface 21b, it concerns on this Embodiment. The rolling bearing 1E is provided such that the four protrusions 211 of the fitting portion 210 of the first inner ring member 21E have a cross shape. Four recessed portions corresponding to the four protrusions 211 of the first inner ring member 21E are formed in the fitted portions 620 and 730 into which the fitting portion 210 of the first inner ring member 21E is fitted. The first inner ring member 21E constitutes the inner ring 2E together with the second inner ring member 22E. The second inner ring member 22E is formed in the same manner as the second inner ring member 22 according to the first embodiment.

本実施の形態によっても、第１の実施の形態と同様の作用及び効果を得ることができる。   Also according to the present embodiment, the same operation and effect as the first embodiment can be obtained.

（付記）
以上、本発明の駆動力伝達装置及び駆動力伝達制御装置を第１乃至第６の実施の形態に基づいて説明したが、本発明はこれら実施の形態に限定されるものではなく、その要旨を逸脱しない範囲で適宜変形して実施することが可能である。例えば、上記各実施の形態では、転がり装置１が複列円錐ころ軸受であり、転動体４１，４２が円錐ころである場合について説明したが、これに限らず、転動体が球体であってもよい。また、内輪２及び外輪３にそれぞれ２つの軌道面（第１内側軌道面２１ａ、第２内側軌道面２２ａ、第１外側軌道面３０ａ、第２外側軌道面３０ｂ）が形成された場合について説明したが、内輪及び外輪にそれぞれ１つの軌道面を形成してもよい。 (Appendix)
The driving force transmission device and the driving force transmission control device of the present invention have been described based on the first to sixth embodiments. However, the present invention is not limited to these embodiments, and the gist thereof is as follows. Modifications can be made as appropriate without departing from the scope. For example, in each of the above embodiments, the case where the rolling device 1 is a double-row tapered roller bearing and the rolling elements 41 and 42 are tapered rollers has been described. However, the present invention is not limited thereto, and the rolling element may be a spherical body. Good. In addition, a case where two raceways (first inner raceway surface 21a, second inner raceway surface 22a, first outer raceway surface 30a, and second outer raceway surface 30b) are formed on the inner ring 2 and the outer ring 3 respectively has been described. However, one track surface may be formed on each of the inner ring and the outer ring.

１，１Ｅ…転がり軸受、１０…ギヤ軸支持装置、２，２Ａ，２Ｂ，２Ｅ…内輪、２１，２１Ａ，２１Ｂ，２１Ｃ，２１Ｄ，２１Ｅ…第１内輪部材、２１ａ…第１内側軌道面、２１０…嵌合部、２１１…突起、２１２…筒部、２１３…加締め部、２２，２２Ａ，２２Ｂ，２２Ｅ…第２内輪部材、２２ａ…第２内側軌道面、３…外輪、３０ａ…第１外側軌道面、３０ｂ…第２外側軌道面、４１，４２…転動体、６…ギヤ軸、６０…ナット、６１…軸部、６１０…雄ねじ、６２…ギヤ部、６２０…被嵌合部、６２２…円筒部、６２３…突起、７…補助ギヤ部材、７１…ギヤ歯、７３０…被嵌合部、９…トランスミッションケース（支持体）、９０…支持部、９１…ボルト DESCRIPTION OF SYMBOLS 1,1E ... Rolling bearing, 10 ... Gear shaft support device, 2, 2A, 2B, 2E ... Inner ring, 21, 21A, 21B, 21C, 21D, 21E ... First inner ring member, 21a ... First inner raceway surface, 210 ... fitting part, 211 ... projection, 212 ... cylindrical part, 213 ... caulking part, 22, 22A, 22B, 22E ... second inner ring member, 22a ... second inner raceway surface, 3 ... outer ring, 30a ... first outer side Raceway surface, 30b ... 2nd outer raceway surface, 41, 42 ... rolling element, 6 ... gear shaft, 60 ... nut, 61 ... shaft portion, 610 ... male screw, 62 ... gear portion, 620 ... mated portion, 622 ... Cylindrical part, 623 ... projection, 7 ... auxiliary gear member, 71 ... gear teeth, 730 ... fitted part, 9 ... transmission case (support), 90 ... support part, 91 ... bolt

Claims (9)

軸状の軸部及び前記軸部の外方に突出したギヤ部を有するギヤ軸と、
前記軸部に外嵌された内輪と、
支持体に固定された外輪と、
前記内輪と前記外輪との間に配置され、前記内輪に形成された内側軌道面及び前記外輪に形成された外側軌道面を転動する複数の転動体とを備え、
前記内輪は、前記ギヤ部に対向する側面に前記ギヤ部と嵌合する嵌合部が形成され、前記嵌合部の嵌合によって前記ギヤ軸との相対回転が規制される、
ギヤ軸支持装置。 A gear shaft having a shaft-shaped shaft portion and a gear portion protruding outward from the shaft portion;
An inner ring externally fitted to the shaft portion;
An outer ring fixed to the support;
A plurality of rolling elements that are disposed between the inner ring and the outer ring and roll on an inner raceway surface formed on the inner ring and an outer raceway surface formed on the outer ring;
The inner ring has a fitting portion that is fitted to the gear portion on a side surface facing the gear portion, and relative rotation with the gear shaft is restricted by the fitting of the fitting portion.
Gear shaft support device. 前記外輪には、内周面に第１外側軌道面及び第２外側軌道面が軸方向に並んで形成され、
前記内輪は、前記第１外側軌道面に対向する第１内側軌道面を外周面に有すると共に前記ギヤ部に対向する側面を有する第１内輪部材と、前記第１内輪部材と軸方向に並んで配置され、前記第２外側軌道面に対向する第２内側軌道面を外周面に有する第２内輪部材とを有し、
前記第１内輪部材の前記側面に前記嵌合部が形成された、
請求項１に記載のギヤ軸支持装置。 In the outer ring, a first outer raceway surface and a second outer raceway surface are formed side by side in the axial direction on the inner peripheral surface,
The inner ring has a first inner ring member having a first inner raceway surface facing the first outer raceway surface on the outer peripheral surface and a side surface facing the gear portion, and is aligned with the first inner ring member in the axial direction. A second inner ring member disposed on the outer peripheral surface and having a second inner raceway surface facing the second outer raceway surface,
The fitting portion is formed on the side surface of the first inner ring member.
The gear shaft support device according to claim 1. 前記外輪には、内周面に第１外側軌道面及び第２外側軌道面が軸方向に並んで形成され、
前記内輪は、前記第１外側軌道面に対向する第１内側軌道面を外周面に有する第１内輪部材と、前記第２外側軌道面に対向する第２内側軌道面を外周面に有する第２内輪部材とを有し、
前記第１内輪部材は、前記第２内輪部材の内側を挿通する筒部を有し、前記筒部の端部が加締めされた加締め部によって前記複数の転動体に予圧が付与されている、
請求項１に記載のギヤ軸支持装置。 In the outer ring, a first outer raceway surface and a second outer raceway surface are formed side by side in the axial direction on the inner peripheral surface,
The inner ring has a first inner ring member having a first inner raceway surface facing the first outer raceway surface on the outer peripheral surface, and a second inner race member having a second inner raceway surface facing the second outer raceway surface on the outer peripheral surface. An inner ring member,
The first inner ring member has a cylindrical portion inserted through the inner side of the second inner ring member, and a preload is applied to the plurality of rolling elements by a crimped portion in which an end of the cylindrical portion is crimped. ,
The gear shaft support device according to claim 1. 前記内輪は、前記加締め部とは反対側の端部が前記ギヤ部に対向するように配置され、
前記嵌合部は、前記第１内輪部材の前記加締め部とは反対側に形成されている、
請求項３に記載のギヤ軸支持装置。 The inner ring is arranged such that an end opposite to the caulking part is opposed to the gear part,
The fitting portion is formed on the opposite side of the caulking portion of the first inner ring member.
The gear shaft support device according to claim 3. 前記内輪は、前記加締め部が前記ギヤ部に対向するように配置され、
前記嵌合部は、前記第１内輪部材の前記加締め部に形成されている、
請求項３に記載のギヤ軸支持装置。 The inner ring is arranged so that the caulking part faces the gear part,
The fitting portion is formed in the caulking portion of the first inner ring member.
The gear shaft support device according to claim 3. 前記ギヤ軸には、前記軸部の端部に雄ねじが形成され、
前記内輪は、前記雄ねじに螺合するナットの締付力によって前記嵌合部が前記ギヤ部に押し付けられている、
請求項１乃至５の何れか１項に記載のギヤ軸支持装置。 The gear shaft is formed with a male screw at the end of the shaft portion,
In the inner ring, the fitting portion is pressed against the gear portion by a tightening force of a nut screwed into the male screw.
The gear shaft support device according to any one of claims 1 to 5. 前記ギヤ軸と一体に回転する補助ギヤ部材をさらに備え、
前記ギヤ部は、前記内輪の内側における前記軸部の外径よりも大きな外径を有する円筒部を有し、前記円筒部に前記補助ギヤ部材が外嵌され、
前記円筒部の軸方向端面及び前記補助ギヤ部材の軸方向端面に、前記内輪の前記嵌合部が嵌合する被嵌合部が形成された、
請求項１乃至６の何れか１項に記載のギヤ軸支持装置。 An auxiliary gear member that rotates integrally with the gear shaft;
The gear portion has a cylindrical portion having an outer diameter larger than the outer diameter of the shaft portion inside the inner ring, and the auxiliary gear member is externally fitted to the cylindrical portion,
A fitted portion into which the fitting portion of the inner ring is fitted is formed on the axial end surface of the cylindrical portion and the axial end surface of the auxiliary gear member.
The gear shaft support device according to any one of claims 1 to 6. 前記内輪の前記嵌合部は、前記ギヤ軸の回転軸と平行な軸方向に突出した複数の突起からなる、
請求項１乃至７の何れか１項に記載のギヤ軸支持装置。 The fitting portion of the inner ring includes a plurality of protrusions protruding in an axial direction parallel to the rotation axis of the gear shaft.
The gear shaft support device according to any one of claims 1 to 7. 軸状の軸部及び前記軸部の外方に突出したギヤ部を有するギヤ軸を支持体に対して回転可能に支持する転がり軸受であって、
前記軸部に外嵌される内輪と、
前記支持体に固定される外輪と、
前記内輪と前記外輪との間に配置され、前記内輪に形成された内側軌道面及び前記外輪に形成された外側軌道面を転動する複数の転動体とを備え、
前記内輪は、前記ギヤ部に対向する側面に前記ギヤ部と嵌合する嵌合部が形成され、前記嵌合部の嵌合によって前記ギヤ軸との相対回転が規制される、
転がり軸受。 A rolling bearing that rotatably supports a gear shaft having a shaft-shaped shaft portion and a gear portion protruding outward from the shaft portion with respect to a support,
An inner ring fitted on the shaft portion;
An outer ring fixed to the support;
A plurality of rolling elements that are disposed between the inner ring and the outer ring and roll on an inner raceway surface formed on the inner ring and an outer raceway surface formed on the outer ring;
The inner ring has a fitting portion that is fitted to the gear portion on a side surface facing the gear portion, and relative rotation with the gear shaft is restricted by the fitting of the fitting portion.
Rolling bearing.
JP2015230803A 2015-11-26 2015-11-26 Gear shaft supporting device and rolling bearing Pending JP2017096448A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021502296A (en) * 2017-11-08 2021-01-28 ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフトＺｆ Ｆｒｉｅｄｒｉｃｈｓｈａｆｅｎ Ａｇ System that supports rotor shafts

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021502296A (en) * 2017-11-08 2021-01-28 ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフトＺｆ Ｆｒｉｅｄｒｉｃｈｓｈａｆｅｎ Ａｇ System that supports rotor shafts
JP7074850B2 (en) 2017-11-08 2022-05-24 ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフト System that supports rotor shafts

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