JP2011031670A - Vehicle bearing device - Google Patents

Vehicle bearing device Download PDF

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JP2011031670A
JP2011031670A JP2009177843A JP2009177843A JP2011031670A JP 2011031670 A JP2011031670 A JP 2011031670A JP 2009177843 A JP2009177843 A JP 2009177843A JP 2009177843 A JP2009177843 A JP 2009177843A JP 2011031670 A JP2011031670 A JP 2011031670A
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bearing device
vehicle
axial direction
wheel
rotating body
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Takaaki Onizuka
高晃 鬼塚
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JTEKT Corp
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JTEKT Corp
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction 

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vehicle bearing device suppressing large deformation of a rotor, while reducing weight of the rotor by forming space therein. <P>SOLUTION: A hollow section 25 extended from a flange surface 26 toward a vehicle body in the axial direction is installed in a cylindrical section 21 of the rotor 2 of the rolling bearing device. The flange surface 26 is disposed on the vehicle outside in the axial direction from the outer surface 22a of an attachment section 22 on the vehicle outside in the axial direction. A hole diameter R1 of a wheel side space 251, which is an inner diameter of an inner peripheral surface 21 of the cylindrical section 21 constituting the wheel side space 251 of the hollow section 25, is constant along the axial direction, or is gradually decreased toward the vehicle outside in the axial direction. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

本発明は、車輪が取り付けられる車輪取付部、及び軸体を有する回転体と、この回転体の軸体を外囲し、且つ転動体を介して軸体を支持する固定体とを備える車両用軸受装置に関する。   The present invention is for a vehicle including a wheel mounting portion to which a wheel is mounted, a rotating body having a shaft body, and a fixed body that surrounds the shaft body of the rotating body and supports the shaft body via a rolling element. The present invention relates to a bearing device.

近年、自動車等の車両の二酸化炭素の排出削減及び燃費向上のために、車両の軽量化が求められている。この車両の軽量化に伴い、車両の車体に取り付けられて、車輪と共に回転する車両用軸受装置である転がり軸受装置に関しても、軽量化が求められている。   In recent years, there has been a demand for lighter vehicles in order to reduce carbon dioxide emissions and improve fuel efficiency in vehicles such as automobiles. Along with the reduction in weight of the vehicle, a reduction in weight is also required for a rolling bearing device that is a vehicle bearing device that is attached to the vehicle body and rotates together with the wheels.

従来の車両用軸受装置である転がり軸受装置１００について、図１０を用いて説明する。
図１０に示すように、転がり軸受装置１００は、車輪に取り付けられる回転する回転体１０１と、車体に取り付けられるとともに、回転体１０１を外囲する固定体１０２と、回転体１０１と固定体１０２との間に配置された転動体１０３とにより構成されている。 A rolling bearing device 100, which is a conventional vehicle bearing device, will be described with reference to FIG.
As shown in FIG. 10, the rolling bearing device 100 includes a rotating rotating body 101 that is attached to a wheel, a fixed body 102 that is attached to the vehicle body and surrounds the rotating body 101, and the rotating body 101 and the fixed body 102. It is comprised with the rolling element 103 arrange | positioned between.

また、回転体１０１には、円筒部１０４と、車輪に固定されるとともに、転がり軸受装置１００の径方向（以下、単に「径方向」という。）において、円筒部１０４から外側に延設される取付部１０５と、転がり軸受装置１００の軸方向（以下、単に「軸方向」という。）において、円筒部１０４の車体側に固定された内輪１０８とが設けられている。また、内輪１０８には、転動体１０３と摺接する軌道溝１０７が設けられている。また、円筒部１０４の軸方向の車外側には、転動体１０３と摺接する軌道溝１０９が設けられている。   The rotating body 101 is fixed to the cylindrical portion 104 and the wheel, and extends outward from the cylindrical portion 104 in the radial direction of the rolling bearing device 100 (hereinafter simply referred to as “radial direction”). In the axial direction of the rolling bearing device 100 (hereinafter simply referred to as “axial direction”), an inner ring 108 fixed to the vehicle body side of the cylindrical portion 104 is provided. The inner ring 108 is provided with a raceway groove 107 that is in sliding contact with the rolling element 103. A raceway groove 109 that is in sliding contact with the rolling element 103 is provided on the outer side of the cylindrical portion 104 in the axial direction.

回転体１０１の円筒部１０４には、軽量化を目的として、取付部１０５から軸方向の車体側に向かい形成された凹形状の穴である中空部１０６が設けられている。ここで、中空部１０６の内径ＲＤ１は、中空部１０６の軸方向の車体側の先端である底面１０６ａから軸方向の車外側に向かい拡径している。即ち、中空部１０６を構成する円筒部１０４の内周面１０６ｂの軸方向の車外側の端部が内径ＲＤ１の最大径となる（例えば、特許文献１参照）。   The cylindrical portion 104 of the rotating body 101 is provided with a hollow portion 106 that is a concave hole formed from the mounting portion 105 toward the vehicle body side in the axial direction for the purpose of weight reduction. Here, the inner diameter RD1 of the hollow portion 106 increases from the bottom surface 106a, which is the front end of the hollow portion 106 on the vehicle body side in the axial direction, toward the vehicle outer side in the axial direction. That is, the axially outer end of the inner peripheral surface 106b of the cylindrical portion 104 constituting the hollow portion 106 becomes the maximum diameter of the inner diameter RD1 (see, for example, Patent Document 1).

特開平０８−９１１８７号公報Japanese Patent Laid-Open No. 08-91187

ところで、上記従来の転がり軸受装置１００によれば、回転体１０１において、円筒部１０４と取付部１０５との境界付近にて比較的大きな変形が生じることが本願発明者の実施した試験等を通じて確認されている。これは、軽量化のため、回転体１０１に中空部１０６が設けられていることにより、円筒部１０４と取付部１０５との接続部の剛性が十分に確保されていないことに起因すると考えられる。そこで、上記変形を抑制するため、中空部１０６を省略することも考えられるが、この場合には、軽量化が図られないため、好ましい対策とは言い難い。   By the way, according to the conventional rolling bearing device 100 described above, it is confirmed through tests and the like conducted by the inventors of the present application that a relatively large deformation occurs in the rotating body 101 near the boundary between the cylindrical portion 104 and the mounting portion 105. ing. It is considered that this is because the rigidity of the connecting portion between the cylindrical portion 104 and the mounting portion 105 is not sufficiently secured due to the hollow portion 106 provided in the rotating body 101 for weight reduction. Therefore, in order to suppress the above deformation, the hollow portion 106 may be omitted, but in this case, it is difficult to say that it is a preferable measure because the weight cannot be reduced.

本発明は、上記実情に鑑みてなされたものであり、その目的とするところは、回転体に空間を形成して軽量化を図りつつも回転体の大きな変形を抑制することのできる車両用軸受装置を提供することである。   The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a vehicle bearing capable of suppressing a large deformation of the rotating body while forming a space in the rotating body and reducing the weight. Is to provide a device.

請求項１に記載の発明は、車輪が取り付けられる車輪取付部、及び軸体を有する回転体と、前記軸体を外囲し、且つ転動体を介して前記軸体を支持する固定体とを備え、前記車輪取付部には、前記軸体より径方向の外側に突出する突出部が設けられ、前記車輪取付部及び前記軸体の内部には、前記車輪取付部の軸方向の車外側の端部から前記軸体の中間部までにわたり軸方向に延び、前記中間部にて閉塞する空間である内部空間が設けられ、前記回転体が前記車輪と共に前記固定体に対して回転する車両用軸受装置において、前記内部空間には、前記突出部の径方向の内側と対応するところにあり、且つ軸方向に沿って前記内部空間の内径が一定、または軸方向の車体側に向かうにしたがい前記内径が小さくなる車輪側空間が形成されることを要旨とする。   The invention according to claim 1 includes a wheel mounting portion to which a wheel is mounted and a rotating body having a shaft body, and a fixed body that surrounds the shaft body and supports the shaft body via a rolling element. The wheel mounting portion is provided with a protruding portion that protrudes radially outward from the shaft body, and the wheel mounting portion and the shaft body include an outside of the wheel mounting portion in the axial direction of the vehicle. A vehicle bearing that extends in an axial direction from an end portion to an intermediate portion of the shaft body and has an internal space that is a space closed at the intermediate portion, and the rotating body rotates relative to the fixed body together with the wheels. In the device, the inner space is located at a position corresponding to the radially inner side of the protruding portion, and the inner diameter of the inner space is constant along the axial direction, or the inner diameter increases toward the vehicle body side in the axial direction. A wheel-side space that reduces The gist.

上記発明によれば、内部空間を構成する車輪側空間の内径が軸方向に沿って一定であるため、回転体の軸体の外周面の形状を変更することなく、車輪取付部に対する軸体の剛性を向上させることができる。また、軸受装置の軽量化のため、内部空間を設けるので、軸受装置の軽量化を図ることができる。したがって、軸体の変形に伴う、軸体と転動体とが圧接される部位の形成を抑制するとともに、転動体の表面及び転動体と接触する軸体の表面が損傷することを抑制することができる。その結果、回転体に内部空間を形成して軽量化を図りつつも回転体の大きな変形を抑制することのできる車両用軸受装置を提供することができる。ここで、「車輪側空間の内径が軸方向に沿って一定である」とは、車輪側空間の内径が完全に一定であることのみではなく、車輪側空間を加工する際の加工誤差による内径のばらつきも含む。   According to the above invention, since the inner diameter of the wheel-side space constituting the internal space is constant along the axial direction, the shaft body relative to the wheel mounting portion is not changed without changing the shape of the outer peripheral surface of the shaft body of the rotating body. Stiffness can be improved. Moreover, since an internal space is provided for reducing the weight of the bearing device, the weight of the bearing device can be reduced. Therefore, it is possible to suppress the formation of a portion where the shaft body and the rolling element are pressed in contact with the deformation of the shaft body, and to prevent the surface of the rolling body and the surface of the shaft body that contacts the rolling body from being damaged. it can. As a result, it is possible to provide a vehicle bearing device that can suppress a large deformation of the rotating body while reducing the weight by forming an internal space in the rotating body. Here, “the inner diameter of the wheel-side space is constant along the axial direction” not only means that the inner diameter of the wheel-side space is completely constant, but also the inner diameter due to processing errors when processing the wheel-side space. Including variations in

請求項２に記載の発明は、請求項１に記載の軸受装置において、前記車輪取付部は、前記車輪側空間を形成する基部と、前記基部の径方向の外側に設けられ、略円盤状を形成する突出部とを有し、前記基部の軸方向の車外側には、フランジ面が設けられ、前記突出部の軸方向の車外側には、外側面が設けられ、前記フランジ面は、前記外側面より軸方向の車外側に設けられることを要旨とする。   According to a second aspect of the present invention, in the bearing device according to the first aspect, the wheel mounting portion is provided on a base portion that forms the wheel side space, and on a radially outer side of the base portion, and has a substantially disk shape. A flange surface is provided on the outer side of the base in the axial direction, and an outer surface is provided on the outer side of the projecting portion in the axial direction. The gist is to be provided on the outside of the vehicle in the axial direction from the outer surface.

上記発明によれば、フランジ面が突出部の外側面より軸方向の車外側に設けられることにより、車輪取付部に対する軸体の剛性を向上させることができる。したがって、軸体の変形に伴う、軸体と転動体とが圧接される部位の形成を抑制するとともに、転動体の表面及び転動体と接触する軸体の表面が損傷することを抑制することができる。   According to the said invention, the rigidity of the shaft body with respect to a wheel attaching part can be improved by providing a flange surface in the vehicle outer side of an axial direction rather than the outer side surface of a protrusion part. Therefore, it is possible to suppress the formation of a portion where the shaft body and the rolling element are pressed in contact with the deformation of the shaft body, and to prevent the surface of the rolling body and the surface of the shaft body that contacts the rolling body from being damaged. it can.

請求項３に記載の発明は、請求項２に記載の車両用軸受装置において、前記突出部には、前記車輪に締結されるボルトが挿入され、当該車両用軸受装置が前記車輪に固定される固定部が設けられ、前記突出部の厚さについて、周方向において隣り合う固定部間の厚さは、前記固定部の厚さより小さく設定されることを要旨とする。   According to a third aspect of the present invention, in the vehicle bearing device according to the second aspect, a bolt fastened to the wheel is inserted into the projecting portion, and the vehicle bearing device is fixed to the wheel. The gist is that a fixing portion is provided, and the thickness of the protruding portion is set such that the thickness between the fixing portions adjacent in the circumferential direction is smaller than the thickness of the fixing portion.

上記発明によれば、周方向において、隣り合う固定部の間の厚さが固定部の厚さより小さく設定されることにより、従来の車両用軸受装置の取付部と比較して、車両用軸受装置の突出部の軽量化を図ることができる。   According to the above invention, in the circumferential direction, the thickness between the adjacent fixed portions is set smaller than the thickness of the fixed portion, so that the vehicle bearing device is compared with the mounting portion of the conventional vehicle bearing device. It is possible to reduce the weight of the protruding portion.

請求項４に記載の発明は、請求項１〜請求項３のいずれか一項に記載の車両用軸受装置において、前記軸体には、外周溝が設けられ、前記外周溝には、前記転動体を保持する内輪が取り付けられ、前記車輪側空間の内径は、前記外周溝の外径より小さく設定されることを要旨とする。   According to a fourth aspect of the present invention, in the vehicle bearing device according to any one of the first to third aspects, the shaft body is provided with an outer peripheral groove, and the outer peripheral groove includes the rolling member. The gist is that an inner ring for holding a moving body is attached, and an inner diameter of the wheel side space is set smaller than an outer diameter of the outer circumferential groove.

上記発明によれば、内部空間の車輪側空間の内径が、内輪が取り付けられる外周溝の外径より小さく設定されるため、軸体の外周溝の軸方向の位置まで、内部空間を形成することができる。したがって、車両用軸受装置の回転体の軽量化を図ることができる。   According to the above invention, since the inner diameter of the wheel side space of the inner space is set smaller than the outer diameter of the outer circumferential groove to which the inner ring is attached, the inner space is formed up to the axial position of the outer circumferential groove of the shaft body. Can do. Therefore, the weight of the rotating body of the vehicle bearing device can be reduced.

本発明によれば、回転体に空間を形成して軽量化を図りつつも回転体の大きな変形を抑制することのできる車両用軸受装置を提供することができる。   ADVANTAGE OF THE INVENTION According to this invention, the vehicle bearing apparatus which can suppress the big deformation | transformation of a rotary body can be provided, forming a space in a rotary body and achieving weight reduction.

本発明の車両用軸受装置を具体化した第１の実施形態について、同車両用軸受装置の断面構造を示す断面図。Sectional drawing which shows the cross-section of the bearing apparatus for vehicles about 1st Embodiment which actualized the bearing apparatus for vehicles of this invention. 同実施形態の車両用軸受装置について、図１の断面構造から固定体、保持器及び転動体を省略した状態の断面構造を示す断面図。Sectional drawing which shows the cross-section of the state which abbreviate | omitted the fixed body, the holder | retainer, and the rolling element from the cross-section of FIG. 1 about the vehicle bearing device of the embodiment. 同実施形態の車両用軸受装置について、図２の矢視Ｘから同車両用軸受装置を見た平面構造を示す平面図。The top view which shows the planar structure which looked at the vehicle bearing apparatus from the arrow X of FIG. 2 about the vehicle bearing apparatus of the embodiment. 同実施形態の車両用軸受装置について、同車両用軸受装置の回転体の斜視構造を示す斜視図。The perspective view which shows the perspective structure of the rotary body of the bearing device for vehicles about the bearing device for vehicles of the embodiment. 同実施形態の車両用軸受装置に対する比較例である従来の車両用軸受装置について、同車両用軸受装置の回転体の断面構造を示す断面図。Sectional drawing which shows the cross-section of the rotary body of the bearing device for vehicles about the conventional vehicle bearing device which is a comparative example with respect to the bearing device for vehicles of the embodiment. 同従来の車両用軸受装置について、図５を矢視Ｙから同車両用軸受装置を見た平面構造を示す平面図。The top view which shows the planar structure which looked at the vehicle bearing apparatus from FIG. 同従来の車両用軸受装置について、同車両用軸受装置の回転体の斜視構造を示す斜視図。The perspective view which shows the perspective structure of the rotary body of the vehicle bearing device about the conventional vehicle bearing device. 本発明の車両用軸受装置を具体化した第２の実施形態について、同車両用軸受装置の正面構造を示す平面図。The top view which shows the front structure of the bearing apparatus for vehicles about 2nd Embodiment which actualized the bearing apparatus for vehicles of this invention. 本発明の車両用軸受装置を具体化した第３の実施形態について、同車両用軸受装置の回転体の断面構造を示す断面図。Sectional drawing which shows the cross-section of the rotary body of the vehicle bearing device about 3rd Embodiment which actualized the vehicle bearing device of this invention. 従来の車両用軸受装置について、同車両用軸受装置の断面構造を示す断面図。Sectional drawing which shows the cross-section of the conventional vehicle bearing apparatus about the vehicle bearing apparatus.

（第１の実施形態）
図１を参照して、本発明の車両用軸受装置として、自動車等の車両の車体に取り付けられて、車輪と共に回転可能に支持する転がり軸受装置を具体化した第１の実施形態について説明する。 (First embodiment)
With reference to FIG. 1, a first embodiment in which a rolling bearing device mounted on a vehicle body of a vehicle such as an automobile and rotatably supported with wheels is embodied as a vehicle bearing device of the present invention will be described.

図１に示すように、転がり軸受装置１は、車輪に固定される回転体２と、車体に固定されるとともに回転体２を外囲する固定体３と、回転体２及び固定体３の間の空間に配置される保持器５により保持された複数の転動体４とにより構成されている。この転がり軸受装置１は、回転体２が、転動体４を介して、固定体３に対して中心軸を中心に回転可能に支持されている。   As shown in FIG. 1, a rolling bearing device 1 includes a rotating body 2 that is fixed to a wheel, a fixed body 3 that is fixed to a vehicle body and that surrounds the rotating body 2, and between the rotating body 2 and the fixed body 3. It is comprised by the some rolling element 4 hold | maintained by the holder | retainer 5 arrange | positioned in this space. In this rolling bearing device 1, a rotating body 2 is supported via a rolling element 4 so as to be rotatable about a central axis with respect to a fixed body 3.

回転体２は、軸体である円筒部２１と、ボルトによって車輪が取り付けられる車輪取付部である取付部２２と、円筒部２１の軸方向の車体側に固定された内輪２４とにより構成されている。   The rotating body 2 includes a cylindrical portion 21 that is a shaft body, an attachment portion 22 that is a wheel attachment portion to which a wheel is attached by a bolt, and an inner ring 24 that is fixed to the vehicle body side in the axial direction of the cylindrical portion 21. Yes.

取付部２２には、円筒部２１と連続する基部２２１と、転がり軸受装置１の径方向（以下、単に「径方向」という。）において、円筒部２１より外側に突出する突出部２２２とが設けられている。また、取付部２２の径方向の内側には、転がり軸受装置１の軸方向（以下、単に「軸方向」という。）において、取付部２２から車外側に沿って延設されるとともに、車輪のホイールと嵌合する略円筒形状のインロー部２３が設けられている。これら取付部２２及びインロー部２３により、回転体２は、車輪のホイールと嵌合するとともに、ボルトによりホイールに固定されている。   The mounting portion 22 includes a base portion 221 that is continuous with the cylindrical portion 21, and a protruding portion 222 that protrudes outward from the cylindrical portion 21 in the radial direction of the rolling bearing device 1 (hereinafter simply referred to as “radial direction”). It has been. Further, on the inner side in the radial direction of the mounting portion 22, in the axial direction of the rolling bearing device 1 (hereinafter simply referred to as “axial direction”), the mounting portion 22 extends from the mounting portion 22 along the vehicle outer side, and the wheel A substantially cylindrical inlay portion 23 that is fitted to the wheel is provided. With the mounting portion 22 and the spigot portion 23, the rotating body 2 is fitted to the wheel of the wheel and is fixed to the wheel with a bolt.

また、内輪２４には、転動体４が潤滑油を介して摺接する車体側軌道溝２４ａが設けられている。また、円筒部２１の軸方向の車外側には、転動体４が潤滑油を介して摺接する車外側軌道溝２１ａが設けられている。内輪２４と円筒部２１の車体側の端部２１ｂとは、かしめにより互いに固定されている。   Further, the inner ring 24 is provided with a vehicle body side raceway groove 24a in which the rolling element 4 comes into sliding contact with the lubricating oil. Further, on the vehicle outer side in the axial direction of the cylindrical portion 21, a vehicle outer side track groove 21 a is provided in which the rolling element 4 is in sliding contact with the lubricating oil. The inner ring 24 and the end portion 21b on the vehicle body side of the cylindrical portion 21 are fixed to each other by caulking.

固定体３には、回転体２の円筒部２１を径方向において外囲する円筒部３１と、円筒部３１より径方向の外側に延設されるフランジ部３２とが設けられている。また、円筒部３１には、フランジ部３２より軸方向の車体側に延設されるとともに、車体と転がり軸受装置１とを接続するナックルと嵌合する略円筒形状の嵌合部３１ｃが設けられている。そして、フランジ部３２には、ボルトを固定する固定孔３２ａが設けられている。即ち、固定体３は、嵌合部３１ｃにより嵌合したナックルがフランジ部３２の固定孔３２ａにボルトにより固定されることにより、車体に対して固定されている。   The fixed body 3 is provided with a cylindrical portion 31 that radially surrounds the cylindrical portion 21 of the rotating body 2 and a flange portion 32 that extends outward from the cylindrical portion 31 in the radial direction. The cylindrical portion 31 is provided with a substantially cylindrical fitting portion 31c that extends from the flange portion 32 toward the vehicle body side in the axial direction and fits with a knuckle that connects the vehicle body and the rolling bearing device 1. ing. The flange portion 32 is provided with a fixing hole 32a for fixing the bolt. That is, the fixed body 3 is fixed to the vehicle body by the knuckle fitted by the fitting portion 31c being fixed to the fixing hole 32a of the flange portion 32 by the bolt.

また、円筒部３１の内周面（即ち、円筒部３１の径方向の内側の面）には、軸方向に一定の距離を介して、車外側軌道溝３１ａ及び車体側軌道溝３１ｂがそれぞれ設けられている。   Further, an outer raceway groove 31a and a vehicle body side raceway groove 31b are provided on the inner peripheral surface of the cylindrical portion 31 (that is, the inner surface in the radial direction of the cylindrical portion 31) via a certain distance in the axial direction. It has been.

内輪２４と回転体２の円筒部２１とがかしめられることによって、内輪２４の車体側軌道溝２４ａ及び固定体３の車体側軌道溝３１ｂと転動体４、及び、回転体２の車外側軌道溝２１ａ及び固定体３の車外側軌道溝３１ａと転動体４に、それぞれ予圧が加えられている。   By caulking the inner ring 24 and the cylindrical portion 21 of the rotating body 2, the vehicle body side track groove 24 a of the inner ring 24, the vehicle body side track groove 31 b and the rolling element 4 of the fixed body 3, and the vehicle outer side track groove of the rotating body 2. Preloads are applied to the outer raceway groove 31a of the fixed body 3 and the rolling element 4 respectively.

回転体２と固定体３との径方向の間には、シール装置である車外側シール６及び車体側シール７がそれぞれ設けられている。車外側シール６及び車体側シール７は、それぞれ転がり軸受装置１の外部の空間から転動体４への小石や泥水等の異物の侵入をシールする役割を果たしている。   Between the radial direction of the rotating body 2 and the fixed body 3, a vehicle outer side seal 6 and a vehicle body side seal 7 which are sealing devices are respectively provided. The vehicle outer side seal 6 and the vehicle body side seal 7 serve to seal entry of foreign matter such as pebbles and muddy water from the space outside the rolling bearing device 1 into the rolling element 4.

車外側シール６は、固定体３の軸方向の車外側の端部に固定された略Ｌ字形状の芯金６１と、芯金６１に固定されるとともに、回転体２と摺接する弾性シール体６２とにより構成されている。そして、車体側シール７は、固定体３の軸方向の車体側の端部に固定された略Ｌ字形状の固定側芯金７１と、内輪２４に固定された略Ｌ字形状の回転側芯金７２と、固定側芯金７１に固定されるとともに、回転側芯金７２と摺接する弾性シール体７３とにより構成されている。   The vehicle exterior seal 6 includes a substantially L-shaped cored bar 61 fixed to the end of the fixed body 3 in the axial direction of the vehicle, and an elastic seal body fixed to the cored bar 61 and in sliding contact with the rotating body 2. 62. The vehicle body-side seal 7 includes a substantially L-shaped fixed-side metal bar 71 fixed to the end of the fixed body 3 on the vehicle body side in the axial direction, and a substantially L-shaped rotation-side core fixed to the inner ring 24. A metal 72 and an elastic seal body 73 that is fixed to the fixed core 71 and is in sliding contact with the rotary core 72 are configured.

次に、図２〜図４を参照して、回転体２の構造の詳細について説明する。
図２に示すように、回転体２の円筒部２１及び取付部２２の基部２２１には、基部２２１から軸方向の車体側に向かう有底の穴の内部空間である中空部２５が設けられている。また、回転体２の軸方向の車体側の端部には、軸方向の車外側に向かう有底の穴である穴部２７が設けられている。そして、中空部２５の底部２１ｆと穴部２７の底部２７ａとによって、中間部である隔壁部２８が形成されている。即ち、中空部２５は、基部２２１の軸方向の車外側の端部から隔壁部２８まで軸方向に延び、隔壁部２８にて閉塞する空間である。ここで、隔壁部２８が形成されることにより、円筒部の軸方向に沿って貫通孔を設けた場合（即ち、隔壁部が形成されていない場合）と比較して、円筒部２１の剛性を向上させることができる。 Next, with reference to FIGS. 2-4, the detail of the structure of the rotary body 2 is demonstrated.
As shown in FIG. 2, the cylindrical portion 21 of the rotating body 2 and the base portion 221 of the mounting portion 22 are provided with a hollow portion 25 that is an internal space of a bottomed hole that extends from the base portion 221 toward the vehicle body side in the axial direction. Yes. Further, a hole portion 27 that is a bottomed hole that extends toward the vehicle outer side in the axial direction is provided at the end of the rotating body 2 on the vehicle body side in the axial direction. A partition wall 28 that is an intermediate portion is formed by the bottom 21 f of the hollow portion 25 and the bottom 27 a of the hole 27. That is, the hollow portion 25 is a space that extends in the axial direction from the end of the base portion 221 on the vehicle outer side in the axial direction to the partition wall portion 28 and is closed by the partition wall portion 28. Here, by forming the partition wall portion 28, the rigidity of the cylindrical portion 21 is improved as compared with the case where the through-hole is provided along the axial direction of the cylindrical portion (that is, when the partition wall portion is not formed). Can be improved.

また、中空部２５は、基部２２１、及び円筒部２１の軸方向の車外側によって形成される車輪側空間２５１と、車輪側空間２５１と連続するとともに、車輪側空間２５１より軸方向の車体側に形成される車体側空間２５２と、車輪側空間２５１と連続するとともに、車輪側空間２５１より軸方向の車外側に形成される開口部２５３とにより構成されている。   Further, the hollow portion 25 is continuous with the wheel side space 251 formed by the axially outer side of the base portion 221 and the cylindrical portion 21 and the wheel side space 251, and is closer to the vehicle body side in the axial direction than the wheel side space 251. The vehicle body side space 252 is formed, and the wheel side space 251 is connected to the vehicle body side space 251, and the opening 253 is formed on the vehicle outer side in the axial direction from the wheel side space 251.

中空部２５の車輪側空間２５１の穴径を規定する、車輪側空間２５１を構成する円筒部２１の内周面２１ｃの内径（以下、「車輪側空間２５１の穴径Ｒ１」という。）は、軸方向に沿って等しくなるように形成されている。   The inner diameter of the inner peripheral surface 21c of the cylindrical portion 21 constituting the wheel side space 251 (hereinafter referred to as “the hole diameter R1 of the wheel side space 251”) that defines the hole diameter of the wheel side space 251 of the hollow portion 25 is defined as follows. It is formed to be equal along the axial direction.

また、車輪側空間２５１を構成する内周面２１ｃの軸方向の車外側の端部には、開口部２５３を構成する面取り部２１ｄが設けられている。面取り部２１ｄは、フランジ面２６と内周面２１ｃとが連結するとともに、内周面２１ｃの軸方向の車外側の端部から軸方向の車外側に向かうにしたがい拡径するように設けられている。即ち、開口部２５３は、フランジ面２６上に設けられている。   Further, a chamfered portion 21d constituting the opening 253 is provided at an end portion on the outer side in the axial direction of the inner peripheral surface 21c constituting the wheel side space 251. The chamfered portion 21d is provided so that the flange surface 26 and the inner peripheral surface 21c are connected to each other, and the diameter of the chamfered portion 21d increases from the axially outer end of the inner peripheral surface 21c toward the outer side in the axial direction. Yes. That is, the opening 253 is provided on the flange surface 26.

また、内周面２１ｃより軸方向の車体側の端部には、車体側空間２５２を構成する縮径部２１ｅが設けられている。縮径部２１ｅは、内周面２１ｃから底部２１ｆに向かい内径が縮径するように設けられている。即ち、車体側空間２５２は、軸方向の車体側に向かい、車体側空間２５２を径方向に沿った平面にて切った断面積が小さくなる形状にて構成されている。   Further, a reduced diameter portion 21e constituting the vehicle body side space 252 is provided at the end of the vehicle body side in the axial direction from the inner peripheral surface 21c. The reduced diameter portion 21e is provided such that the inner diameter is reduced from the inner peripheral surface 21c toward the bottom portion 21f. That is, the vehicle body side space 252 is formed in a shape in which a cross-sectional area of the vehicle body side space 252 cut along a plane along the radial direction is reduced toward the vehicle body side in the axial direction.

また、中空部２５の底部２１ｆの軸方向の位置は、内輪２４の車体側軌道溝２４ａの軸方向の位置と略等しい。即ち、隔壁部２８の軸方向の位置は、内輪２４の車体側軌道溝２４ａの軸方向の位置と略等しい。したがって、隔壁部２８により、円筒部２１における内輪２４の車体側軌道溝２４ａの部位の剛性を向上させるとともに、車体側軌道溝２４ａの変形を抑制することができる。   Further, the axial position of the bottom 21 f of the hollow portion 25 is substantially equal to the axial position of the vehicle body side raceway groove 24 a of the inner ring 24. That is, the axial position of the partition wall 28 is substantially equal to the axial position of the vehicle body side raceway groove 24 a of the inner ring 24. Therefore, the partition wall portion 28 can improve the rigidity of the portion of the vehicle body side raceway groove 24a of the inner ring 24 in the cylindrical portion 21, and can suppress deformation of the vehicle body side raceway groove 24a.

また、車輪側空間２５１の穴径Ｒ１は、円筒部２１における内輪２４が取り付けられる外周溝２１ｇの外周面の外径（以下、「軸径Ｒ２」という。）より小さい。特に、中空部２５の穴径Ｒ１は、軸径Ｒ２の約１／２以下が望ましい。車輪側空間２５１の穴径Ｒ１が、軸径Ｒ２の約１／２以下であることにより、円筒部２１の剛性の低下をより効果的に抑制することが可能となることが本願発明者の実施した試験等により確認されている。なお、本実施形態の車輪側空間２５１の穴径Ｒ１は、軸径Ｒ２の１／２である。   Moreover, the hole diameter R1 of the wheel side space 251 is smaller than the outer diameter (hereinafter referred to as “shaft diameter R2”) of the outer peripheral surface of the outer peripheral groove 21g to which the inner ring 24 in the cylindrical portion 21 is attached. In particular, the hole diameter R1 of the hollow portion 25 is desirably about ½ or less of the shaft diameter R2. Implementation of the present inventor that the hole diameter R1 of the wheel-side space 251 is about ½ or less of the shaft diameter R2, thereby making it possible to more effectively suppress a decrease in rigidity of the cylindrical portion 21. It has been confirmed by tests conducted. In addition, the hole diameter R1 of the wheel side space 251 of this embodiment is 1/2 of the shaft diameter R2.

また、回転体２には、インロー部２３と中空部２５との径方向の間に、軸方向（即ち、中心軸）に対して垂直な平面となるフランジ面２６が設けられている。このフランジ面２６は、取付部２２の車外側の面である外側面２２ａより軸方向の車外側に設けられている。   The rotating body 2 is provided with a flange surface 26 that is a plane perpendicular to the axial direction (that is, the central axis) between the radial direction of the spigot part 23 and the hollow part 25. The flange surface 26 is provided on the vehicle outer side in the axial direction with respect to the outer surface 22a which is the surface of the mounting portion 22 on the vehicle outer side.

図３及び図４に示すように、取付部２２の突出部２２２には、取付部２２の周方向に離間した複数個の取付穴２２ｂを有する固定部２２ｃと、転がり軸受装置１の周方向（以下、単に「周方向」という。）において、隣り合う固定部２２ｃを互いに連結する薄肉部２２ｄとが設けられる。また、薄肉部２２ｄの軸方向の厚さＴ２は、固定部２２ｃの軸方向の厚さＴ１より薄い（図２参照）。   As shown in FIGS. 3 and 4, the projecting portion 222 of the mounting portion 22 includes a fixed portion 22 c having a plurality of mounting holes 22 b spaced in the circumferential direction of the mounting portion 22, and a circumferential direction of the rolling bearing device 1 ( Hereinafter, simply referred to as “circumferential direction”), a thin-walled portion 22d that connects adjacent fixing portions 22c to each other is provided. Further, the axial thickness T2 of the thin portion 22d is thinner than the axial thickness T1 of the fixed portion 22c (see FIG. 2).

薄肉部２２ｄには、取付部２２の軸方向の車外側に向かい径方向の外側に傾斜する傾斜面２２ｅと、傾斜面２２ｅと連続するとともに、径方向において、外側に向かい延設する略円弧形状の平面部２２ｆ（図３参照）とが設けられている。平面部２２ｆは、軸方向（即ち、中心軸）に対して垂直な方向に延設されている。   The thin wall portion 22d has an inclined surface 22e inclined outward in the radial direction toward the vehicle outer side in the axial direction of the mounting portion 22, and a substantially arc shape that is continuous with the inclined surface 22e and extends outward in the radial direction. The flat portion 22f (see FIG. 3) is provided. The planar portion 22f extends in a direction perpendicular to the axial direction (that is, the central axis).

また、図３に示す固定部２２ｃの幅Ｗ１は、固定部２２ｃの径方向の内側から径方向の外側に向かい小さくなるように形成されている。この構成により、突出部２２２において、薄肉部２２ｄが占める割合を大きくなる。そして、軸方向において、固定部２２ｃの取付穴２２ｂが設けられる第１固定部２２ｇの厚さＴ３（図２参照）は、固定部２２ｃにおける第１固定部２２ｇより径方向の内側の部位である第２固定部２２ｈの厚さＴ４（図２参照）と比較して、薄く形成されている。   Further, the width W1 of the fixing portion 22c shown in FIG. 3 is formed so as to decrease from the inner side in the radial direction of the fixing portion 22c toward the outer side in the radial direction. With this configuration, the proportion of the thin portion 22d in the protruding portion 222 is increased. In the axial direction, the thickness T3 (see FIG. 2) of the first fixing portion 22g in which the mounting hole 22b of the fixing portion 22c is provided is a portion on the inner side in the radial direction from the first fixing portion 22g in the fixing portion 22c. The second fixing portion 22h is formed thinner than the thickness T4 (see FIG. 2).

次に、図２〜図７を参照して、本実施形態の転がり軸受装置と従来の転がり軸受装置との重量及び剛性の相違について説明する。
図５に示すように、回転体１０１には、従来の転がり軸受装置１００において、回転体１０１の取付部１０５から軸方向の車外側に向けて延設されるとともに、車輪のホイールと嵌合するインロー部１１０が設けられている。そして、中空部１０６とインロー部１１０との径方向の間には、軸方向（即ち、中心軸）に対して垂直な平面であるフランジ面１１１が形成されている。このフランジ面１１１は、取付部１０５の軸方向の車外側の面１０５ａより軸方向の車体側に設けられている。 Next, with reference to FIGS. 2-7, the difference in the weight and rigidity of the rolling bearing apparatus of this embodiment and the conventional rolling bearing apparatus is demonstrated.
As shown in FIG. 5, in the conventional rolling bearing device 100, the rotating body 101 is extended from the mounting portion 105 of the rotating body 101 toward the outside of the vehicle in the axial direction and is fitted to the wheel of the wheel. An inlay portion 110 is provided. A flange surface 111 that is a plane perpendicular to the axial direction (ie, the central axis) is formed between the hollow portion 106 and the spigot portion 110 in the radial direction. The flange surface 111 is provided closer to the vehicle body side in the axial direction than the surface 105a on the vehicle outer side in the axial direction of the mounting portion 105.

また、図６及び図７に示すように、取付部１０５には、周方向に一定の距離を介して設けられている固定部１１２と、周方向において、隣り合う固定部１１２の間に形成されているとともに、隣り合う固定部１１２を連結する連結部１１３とが設けられている。そして、各固定部１１２には、取付穴１１４が設けられている。   Further, as shown in FIGS. 6 and 7, the attachment portion 105 is formed between the fixed portion 112 provided at a certain distance in the circumferential direction and the adjacent fixed portion 112 in the circumferential direction. In addition, a connecting portion 113 that connects adjacent fixing portions 112 is provided. Each fixing portion 112 is provided with a mounting hole 114.

ここで、本実施形態の回転体２と、従来構造の回転体１０１との重量及び剛性を比較すると、本実施形態の回転体２の重量と従来構造の回転体１０１の重量とは略等しくなるが、本実施形態の回転体２の剛性が、従来構造の回転体１０１の剛性より、約２０％向上する結果が得られた。なお、本実施形態の回転体２と従来構造の回転体１０１との比較には、有限要素法の解析（ＦＥＭ解析）を用いた。   Here, when the weight and rigidity of the rotating body 2 of the present embodiment and the rotating body 101 of the conventional structure are compared, the weight of the rotating body 2 of the present embodiment and the weight of the rotating body 101 of the conventional structure are substantially equal. However, the result that the rigidity of the rotating body 2 of this embodiment is improved by about 20% from the rigidity of the rotating body 101 of the conventional structure was obtained. In addition, the finite element method analysis (FEM analysis) was used for the comparison between the rotating body 2 of the present embodiment and the rotating body 101 of the conventional structure.

まず、本実施形態の回転体２の重量と従来構造の回転体１０１との重量が略等しくなる理由について説明する。
図５〜図７に示すように、従来構造の回転体１０１の取付部１０５の連結部１１３は、取付部１０５の軸方向の車外側に向かい径方向の外側に向かい厚さＴＤ１が薄くなるように設けられている。しかし、中空部１０６が設けられることにより、円筒部１０４の剛性が低くなるため、回転体１０１の剛性を必要分確保するためには、取付部１０５の剛性を向上させる必要がある。その結果、固定部１１２の軸方向の厚さＴＤ２に対して、連結部１１３の軸方向の厚さＴＤ１を大幅に薄くすることができない。 First, the reason why the weight of the rotating body 2 of the present embodiment and the weight of the rotating body 101 of the conventional structure are substantially equal will be described.
As shown in FIGS. 5 to 7, the connecting portion 113 of the mounting portion 105 of the rotating body 101 having the conventional structure is formed so that the thickness TD1 decreases toward the outer side in the radial direction toward the outer side of the mounting portion 105 in the axial direction. Is provided. However, since the hollow portion 106 is provided, the rigidity of the cylindrical portion 104 is lowered. Therefore, in order to secure the necessary rigidity of the rotating body 101, it is necessary to improve the rigidity of the mounting portion 105. As a result, the axial thickness TD1 of the connecting portion 113 cannot be significantly reduced with respect to the axial thickness TD2 of the fixed portion 112.

その上、取付部１０５の周方向において、取付部１０５の固定部１１２の幅ＷＤ１は、径方向に沿って一定となるように形成されている。したがって、取付部１０５に対して、固定部１１２及び連結部１１３が寄与する重量の低減の効果は小さい。   In addition, in the circumferential direction of the attachment portion 105, the width WD1 of the fixing portion 112 of the attachment portion 105 is formed to be constant along the radial direction. Therefore, the effect of reducing the weight contributed by the fixing portion 112 and the connecting portion 113 is small with respect to the attachment portion 105.

一方、図２〜図４に示すように、本実施形態の回転体２の取付部２２は、固定部２２ｃの厚さＴ１と比較して、大幅に薄い厚さＴ２を有する薄肉部２２ｄが形成されている。
その上、取付部２２の固定部２２ｃの幅Ｗ１は、取付部２２の径方向において、円筒部２１から外側に向かい小さくなる。即ち、従来構造の取付部１０５に対する連結部１１３の割合に対して、本実施形態の取付部２２に対する薄肉部２２ｄの割合が大きくなる。 On the other hand, as shown in FIGS. 2 to 4, the attachment portion 22 of the rotating body 2 of the present embodiment is formed with a thin portion 22d having a thickness T2 that is significantly thinner than the thickness T1 of the fixing portion 22c. Has been.
In addition, the width W1 of the fixing portion 22c of the attachment portion 22 decreases from the cylindrical portion 21 toward the outside in the radial direction of the attachment portion 22. That is, the ratio of the thin portion 22d to the mounting portion 22 of the present embodiment is larger than the ratio of the connecting portion 113 to the mounting portion 105 having the conventional structure.

したがって、薄肉部２２ｄの厚さＴ２は、連結部１１３の厚さＴＤ２よりも薄く形成されること、及び取付部２２に対する薄肉部２２ｄの割合が、取付部１０５に対する連結部１１３の割合よりも大きいことにより、従来構造の取付部１０５と比較して、本実施形態の取付部２２の重量を大幅に低減させることができる。   Therefore, the thickness T2 of the thin portion 22d is formed thinner than the thickness TD2 of the connecting portion 113, and the ratio of the thin portion 22d to the mounting portion 22 is larger than the ratio of the connecting portion 113 to the mounting portion 105. Thereby, compared with the attachment part 105 of the conventional structure, the weight of the attachment part 22 of this embodiment can be reduced significantly.

また、図５に示すように、従来構造の取付部１０５の固定部１１２の軸方向の厚さＴＤ１は、取付部１０５の径方向に沿って等しい。一方、図２に示すように、本実施形態の取付部２２の固定部２２ｃは、第２固定部２２ｈの厚さＴ４より薄い厚さＴ３を有する第１固定部２２ｇが形成されている。したがって、取付部２２に第１固定部２２ｇが形成されているため、従来構造の取付部１０５と比較して、本実施形態の取付部２２の重量をさらに低減させることができる。   Further, as shown in FIG. 5, the axial thickness TD <b> 1 of the fixing portion 112 of the mounting portion 105 having the conventional structure is equal along the radial direction of the mounting portion 105. On the other hand, as shown in FIG. 2, the fixing portion 22c of the attachment portion 22 of the present embodiment is formed with a first fixing portion 22g having a thickness T3 that is thinner than the thickness T4 of the second fixing portion 22h. Therefore, since the first fixing portion 22g is formed in the attachment portion 22, the weight of the attachment portion 22 of the present embodiment can be further reduced as compared with the attachment portion 105 having the conventional structure.

また、図２に示すように、本実施形態の回転体２の中空部２５の穴形状は、車輪側空間２５１の穴径Ｒ１が軸方向に沿って一定となる略円筒形状であるため、図５に示す従来構造の回転体１０１の軸方向の車外側に拡径する穴形状である中空部１０６と比較して、軽量化の効果は小さい。その上、フランジ面２６の軸方向の位置が取付部２２の突出部２２２の外側面２２ａの軸方向の位置より軸方向の車外側に配置されるため、従来の転がり軸受装置１００と比較して、重量が若干増加する。   Further, as shown in FIG. 2, the hole shape of the hollow portion 25 of the rotating body 2 of the present embodiment is a substantially cylindrical shape in which the hole diameter R1 of the wheel side space 251 is constant along the axial direction. Compared with the hollow portion 106 that has a hole shape that expands outward in the axial direction of the rotating body 101 of the conventional structure shown in FIG. In addition, since the axial position of the flange surface 26 is arranged on the outer side of the vehicle in the axial direction with respect to the axial position of the outer surface 22a of the protrusion 222 of the mounting portion 22, compared to the conventional rolling bearing device 100. The weight increases slightly.

本実施形態の回転体２は、従来構造の回転体１０１の取付部１０５と比較して、軽量化した取付部２２を有するとともに、従来構造の回転体１０１の中空部１０６と比較して、軽量化の効果の低い中空部２５及びフランジ面２６を有する。したがって、従来構造の取付部１０５に対する本実施形態の取付部２２の重量の低減量と、本実施形態の中空部２５及びフランジ面２６に対する従来の転がり軸受装置１００の中空部１０６及びフランジ面１１１の重量の低減量とが略等しいため、本実施形態の回転体２の重量と従来構造の回転体１０１の重量とは略等しくなる。   The rotating body 2 of the present embodiment has a lighter mounting portion 22 as compared to the mounting portion 105 of the rotating body 101 having the conventional structure, and is lighter than the hollow portion 106 of the rotating body 101 having the conventional structure. It has the hollow part 25 and the flange surface 26 with a low effect. Therefore, the amount of weight reduction of the mounting portion 22 of the present embodiment relative to the mounting portion 105 of the conventional structure, and the hollow portion 106 and the flange surface 111 of the conventional rolling bearing device 100 with respect to the hollow portion 25 and the flange surface 26 of the present embodiment. Since the weight reduction amount is substantially equal, the weight of the rotating body 2 of the present embodiment and the weight of the rotating body 101 of the conventional structure are substantially equal.

次に、本実施形態の回転体２の剛性が、従来構造の回転体１０１の剛性に対して向上する理由について説明する。
図２に示すように、本実施形態の回転体２のフランジ面２６は、回転体２の取付部２２の軸方向の車外側の面である外側面２２ａより軸方向の車外側に設けられるため、フランジ面１１１が取付部１０５の軸方向の車外側の面である外側面１０５ａより軸方向の車体側に設けられる従来の転がり軸受装置１００の回転体１０１の円筒部１０４と比較して、取付部２２に対する円筒部２１の剛性は高くなる。即ち、円筒部２１が、取付部２２に対して、傾くことを抑制することができる。したがって、円筒部２１の傾きによって生じる回転体２の車外側軌道溝２１ａ及び内輪２４の車体側軌道溝２４ａの変形に伴う転動体４と車外側軌道溝２１ａ及び車体側軌道溝２４ａとの間において、間隙が形成される部位及び圧接させる部位が形成されることを抑制することができる。 Next, the reason why the rigidity of the rotating body 2 of the present embodiment is improved with respect to the rigidity of the rotating body 101 having the conventional structure will be described.
As shown in FIG. 2, the flange surface 26 of the rotating body 2 of the present embodiment is provided on the outside of the vehicle in the axial direction from the outer surface 22 a that is the surface of the mounting portion 22 of the rotating body 2 on the outside of the vehicle in the axial direction. Compared with the cylindrical portion 104 of the rotating body 101 of the conventional rolling bearing device 100 in which the flange surface 111 is provided on the vehicle body side in the axial direction with respect to the outer surface 105a which is the outer surface of the mounting portion 105 in the axial direction. The rigidity of the cylindrical portion 21 with respect to the portion 22 is increased. That is, the cylindrical portion 21 can be prevented from tilting with respect to the mounting portion 22. Therefore, between the rolling element 4 and the vehicle outer side track groove 21a and the vehicle body side track groove 24a accompanying the deformation of the vehicle outer side track groove 21a of the rotating body 2 and the vehicle body side track groove 24a of the inner ring 24 caused by the inclination of the cylindrical portion 21. It is possible to suppress the formation of the part where the gap is formed and the part to be pressed.

また、本実施形態の回転体２は、中空部２５の車輪側空間２５１の穴径Ｒ１が軸方向に沿って一定に形成されている。即ち、取付部２２の突出部２２２の軸方向の位置と略同位置となる中空部２５の車輪側空間２５１を構成する内周面２１ｃと、円筒部２１及び突出部２２２の境界部Ｐ１とを径方向に結んだ距離Ｄ１によって規定される円筒部２１の肉厚は、円筒部２１の外周面の他の部位（即ち、円筒部２１において、境界部Ｐ１より軸方向の車体側となる外周面）と内周面２１ｃとを径方向に結んだ距離Ｄ２によって規定される円筒部２１の肉厚より大きく形成されている。したがって、円筒部２１の取付部２２に対する剛性をさらに向上させることができる。ここで、「境界部Ｐ１」は、車外側シール６の弾性シール体６２（図１参照）が摺接する円筒部２１の曲面２１ｈの径方向の外縁をいう。   Moreover, as for the rotary body 2 of this embodiment, the hole diameter R1 of the wheel side space 251 of the hollow part 25 is formed uniformly along the axial direction. That is, the inner peripheral surface 21c constituting the wheel-side space 251 of the hollow portion 25 and the boundary portion P1 between the cylindrical portion 21 and the protruding portion 222 that are substantially the same as the axial position of the protruding portion 222 of the mounting portion 22 The thickness of the cylindrical portion 21 defined by the distance D1 connected in the radial direction is the other portion of the outer peripheral surface of the cylindrical portion 21 (that is, the outer peripheral surface of the cylindrical portion 21 that is closer to the vehicle body in the axial direction than the boundary portion P1). ) And the inner peripheral surface 21c are formed to be larger than the thickness of the cylindrical portion 21 defined by a distance D2 that connects the inner peripheral surface 21c in the radial direction. Accordingly, the rigidity of the cylindrical portion 21 with respect to the attachment portion 22 can be further improved. Here, the “boundary portion P1” refers to an outer edge in the radial direction of the curved surface 21h of the cylindrical portion 21 with which the elastic seal body 62 (see FIG. 1) of the vehicle exterior seal 6 is in sliding contact.

一方、図５に示すように、従来構造の回転体１０１は、軸方向において、取付部１０５と同位置の中空部１０６の内径ＲＤ１が最大径となるため、中空部１０６の内周面１０６ｂと、円筒部１０４及び取付部１０５の境界部ＰＤ１とを径方向に結んだ距離ＴＲ１によって規定される円筒部１０４の肉厚は、本実施形態の距離Ｄ１と比較して、小さくなる。したがって、従来構造の回転体１０１の円筒部１０４の剛性は、本実施形態の回転体２の円筒部２１の剛性よりも低くなる。   On the other hand, as shown in FIG. 5, the rotating body 101 of the conventional structure has a maximum inner diameter RD1 of the hollow portion 106 at the same position as the mounting portion 105 in the axial direction. The thickness of the cylindrical portion 104 defined by the distance TR1 connecting the cylindrical portion 104 and the boundary portion PD1 of the mounting portion 105 in the radial direction is smaller than the distance D1 of the present embodiment. Therefore, the rigidity of the cylindrical portion 104 of the rotating body 101 having the conventional structure is lower than the rigidity of the cylindrical portion 21 of the rotating body 2 of the present embodiment.

したがって、取付部２２に対する円筒部２１の剛性に対して大きく寄与する距離Ｄ１によって規定される円筒部２１の肉厚を大きくし、取付部２２に対する円筒部２１の剛性に対して寄与が小さい取付部２２の突出部２２２に薄肉部２２ｄを設けることにより、転がり軸受装置１の回転体２は、図５に示す従来の転がり軸受装置１００の回転体１０１と比較して、回転体の重量を略等しくしつつも、剛性を向上させることができる。   Therefore, the thickness of the cylindrical portion 21 defined by the distance D1 that greatly contributes to the rigidity of the cylindrical portion 21 with respect to the mounting portion 22 is increased, and the mounting portion has a small contribution to the rigidity of the cylindrical portion 21 with respect to the mounting portion 22. By providing the thin portion 22d on the projecting portion 222, the rotating body 2 of the rolling bearing device 1 has substantially the same weight as the rotating body 101 of the conventional rolling bearing device 100 shown in FIG. However, the rigidity can be improved.

本実施形態の転がり軸受装置１では、以下の効果を奏することができる。
（１）本実施形態の転がり軸受装置１では、取付部２２の突出部２２２の軸方向の位置と略同位置の中空部２５の車輪側空間２５１を構成する内周面２１ｃの内径が、軸方向に沿って一定である構成とする。この構成により、回転体２の円筒部２１の外周面の形状を変更することなく、内周面２１ｃと取付部２２と円筒部２１の外周面との境界部Ｐ１を径方向に結んだ距離Ｄ１によって規定される円筒部２１の肉厚を、円筒部２１の他の部位の外周面と中空部２５を構成する内周面２１ｃとを径方向に結んだ距離Ｄ２によって規定される円筒部２１の肉厚より大きくすることができる。したがって、取付部２２に対する円筒部２１の剛性を向上させることができる。その結果、円筒部２１の変形に伴い、円筒部２１と転動体４とが圧接することを抑制することができる。即ち、転動体４の表面及び転動体４と接触する円筒部２１の車外側軌道溝２１ａの表面が損傷することを抑制するとともに、転がり軸受装置１の寿命の低下を抑制することができる。 In the rolling bearing device 1 of the present embodiment, the following effects can be obtained.
(1) In the rolling bearing device 1 of the present embodiment, the inner diameter of the inner peripheral surface 21c constituting the wheel side space 251 of the hollow portion 25 at substantially the same position as the axial position of the protruding portion 222 of the mounting portion 22 is the shaft. The configuration is constant along the direction. With this configuration, the distance D1 connecting the boundary portion P1 between the inner peripheral surface 21c, the mounting portion 22, and the outer peripheral surface of the cylindrical portion 21 in the radial direction without changing the shape of the outer peripheral surface of the cylindrical portion 21 of the rotating body 2. Of the cylindrical portion 21 defined by the distance D2 that connects the outer peripheral surface of the other part of the cylindrical portion 21 and the inner peripheral surface 21c constituting the hollow portion 25 in the radial direction. Can be larger than the wall thickness. Therefore, the rigidity of the cylindrical portion 21 with respect to the attachment portion 22 can be improved. As a result, it is possible to prevent the cylindrical portion 21 and the rolling element 4 from being in pressure contact with the deformation of the cylindrical portion 21. That is, the surface of the rolling element 4 and the surface of the outer raceway groove 21a of the cylindrical portion 21 in contact with the rolling element 4 can be prevented from being damaged, and the life of the rolling bearing device 1 can be prevented from being reduced.

また、本実施形態の転がり軸受装置１では、中空部２５が設けられることにより、中空部２５が設けられない転がり軸受装置の重量と比較して、図５に示す従来の転がり軸受装置１００に対する転がり軸受装置１の重量の増加を抑制することができる。   Further, in the rolling bearing device 1 of the present embodiment, by providing the hollow portion 25, the rolling bearing device 100 shown in FIG. 5 is compared with the weight of the rolling bearing device 100 in which the hollow portion 25 is not provided. An increase in the weight of the bearing device 1 can be suppressed.

したがって、本実施形態の転がり軸受装置１は、図５に示す従来の転がり軸受装置１００の回転体１０１と比較して、回転体２の重量の増加を抑制すること、及び回転体２の剛性を向上させることができる。その結果、回転体２の軽量化を図りつつも、回転体２の大きな変形を抑制することができる。   Therefore, the rolling bearing device 1 of this embodiment suppresses the increase in the weight of the rotating body 2 and the rigidity of the rotating body 2 as compared with the rotating body 101 of the conventional rolling bearing device 100 shown in FIG. Can be improved. As a result, large deformation of the rotating body 2 can be suppressed while reducing the weight of the rotating body 2.

（２）本実施形態の転がり軸受装置１では、フランジ面２６は、取付部２２の外側面２２ａより軸方向の車外側に設けられている構成とする。この構成によれば、図５に示す従来の転がり軸受装置１００の回転体１０１と比較して、取付部２２に対する円筒部２１の剛性を高くすることができる。   (2) In the rolling bearing device 1 of the present embodiment, the flange surface 26 is provided on the vehicle outer side in the axial direction from the outer surface 22 a of the mounting portion 22. According to this configuration, the rigidity of the cylindrical portion 21 relative to the mounting portion 22 can be increased as compared with the rotating body 101 of the conventional rolling bearing device 100 shown in FIG.

（３）本実施形態の転がり軸受装置１では、回転体２の取付部２２には、取付部２２の周方向に離間した取付穴２２ｂを有する固定部２２ｃと、取付部２２の周方向において、隣り合う固定部２２ｃの間には、固定部２２ｃの軸方向の厚さＴ１より薄い厚さＴ２を有する薄肉部２２ｄが設けられている構成とする。この構成によれば、薄肉部２２ｄが設けられるため、図５に示す従来構造の転がり軸受装置１００の回転体１０１と比較して、回転体２の重量の増加を抑制することができる。その結果、図１０に示す従来構造と比較して、転がり軸受装置１の重量の増加を抑制することができる。   (3) In the rolling bearing device 1 of the present embodiment, the mounting portion 22 of the rotating body 2 has a fixing portion 22c having mounting holes 22b spaced in the circumferential direction of the mounting portion 22 and a circumferential direction of the mounting portion 22. A thin portion 22d having a thickness T2 smaller than the axial thickness T1 of the fixed portion 22c is provided between the adjacent fixed portions 22c. According to this configuration, since the thin portion 22d is provided, an increase in the weight of the rotating body 2 can be suppressed as compared with the rotating body 101 of the rolling bearing device 100 having the conventional structure shown in FIG. As a result, an increase in the weight of the rolling bearing device 1 can be suppressed as compared with the conventional structure shown in FIG.

（４）本実施形態の転がり軸受装置１では、中空部２５を構成する円筒部２１の内周面２１ｃの内径である車輪側空間２５１の穴径Ｒ１は、回転体２の円筒部２１における内輪２４が取り付けられる部位である外周溝２１ｇの外周面の外径Ｒ２より小さい構成とする。この構成により、円筒部２１の軸方向において、外周溝２１ｇまで中空部２５を形成することができる。したがって、図５に示す従来構造の転がり軸受装置１００の回転体１０１に設けられた中空部１０６と比較して、円筒部２１の軸方向において、中空部２５を長く形成することができる。その結果、従来構造の回転体１０１に対して、回転体２の重量の増加を抑制することができる。   (4) In the rolling bearing device 1 of the present embodiment, the hole diameter R1 of the wheel-side space 251 that is the inner diameter of the inner peripheral surface 21c of the cylindrical portion 21 constituting the hollow portion 25 is the inner ring in the cylindrical portion 21 of the rotating body 2. It is set as the structure smaller than the outer diameter R2 of the outer peripheral surface of the outer peripheral groove | channel 21g which is a site | part 24 is attached. With this configuration, the hollow portion 25 can be formed up to the outer peripheral groove 21 g in the axial direction of the cylindrical portion 21. Accordingly, the hollow portion 25 can be formed longer in the axial direction of the cylindrical portion 21 than the hollow portion 106 provided in the rotating body 101 of the rolling bearing device 100 having the conventional structure shown in FIG. As a result, an increase in the weight of the rotating body 2 can be suppressed compared to the rotating body 101 having the conventional structure.

（第２の実施形態）
次に、図８を参照して、本発明の車両用軸受装置について、自動車等の車両の車体に取り付けられて、車輪と共に回転する転がり軸受装置として具体化した第２の実施形態を説明する。なお、本実施形態に係る転がり軸受装置は、第１の実施形態の転がり軸受装置と比較して、回転体の取付部が変更するのみであるために、取付部のみの説明を行い、他の部位の説明は省略する。また、図８において、第１の実施形態の回転体と同一部位には、同一の符号を付す。 (Second Embodiment)
Next, with reference to FIG. 8, a second embodiment in which the vehicle bearing device of the present invention is embodied as a rolling bearing device that is attached to the body of a vehicle such as an automobile and rotates with wheels will be described. In addition, since the rolling bearing device according to the present embodiment only changes the mounting portion of the rotating body as compared with the rolling bearing device of the first embodiment, only the mounting portion will be described, Description of the part is omitted. Moreover, in FIG. 8, the same code | symbol is attached | subjected to the same site | part as the rotary body of 1st Embodiment.

図８に示すように、回転体２の取付部２２は、取付部２２の周方向に離間した複数の固定部２２ｃが設けられている。そして、周方向において、隣り合う固定部２２ｃの間には、切欠部２２ｋが設けられている。即ち、本実施形態の回転体２は、図３に示す第１の実施形態の回転体２の薄肉部２２ｄがなくなった形状である。   As shown in FIG. 8, the attachment portion 22 of the rotating body 2 is provided with a plurality of fixing portions 22 c that are separated in the circumferential direction of the attachment portion 22. In the circumferential direction, a notch 22k is provided between the adjacent fixed portions 22c. That is, the rotating body 2 of the present embodiment has a shape in which the thin portion 22d of the rotating body 2 of the first embodiment shown in FIG. 3 is eliminated.

本実施形態の転がり軸受装置では、第１の実施形態の転がり軸受装置１の効果（１）、（２）、及び（４）と同様の効果に加え、以下の効果を奏することができる。
（５）本実施形態の転がり軸受装置１では、回転体２の取付部２２に切欠部２２ｋが設けられている構成とする。この構成によれば、第１の実施形態の転がり軸受装置１に設けられていた薄肉部２２ｄがなくなった形状であるため、第１の実施形態の回転体２より、回転体２の重量を低減することができる。したがって、図５に示す従来の転がり軸受装置１００の回転体１０１と比較して、回転体２の重量の増加をさらに抑制すること、もしくは、回転体２の重量の低減をすることができる。 In addition to the effects (1), (2), and (4) of the rolling bearing device 1 of the first embodiment, the rolling bearing device of the present embodiment can exhibit the following effects.
(5) In the rolling bearing device 1 of the present embodiment, the notched portion 22k is provided in the mounting portion 22 of the rotating body 2. According to this configuration, since the thin portion 22d provided in the rolling bearing device 1 of the first embodiment is eliminated, the weight of the rotating body 2 is reduced compared to the rotating body 2 of the first embodiment. can do. Therefore, as compared with the rotating body 101 of the conventional rolling bearing device 100 shown in FIG. 5, it is possible to further suppress an increase in the weight of the rotating body 2 or to reduce the weight of the rotating body 2.

（第３の実施形態）
次に、図９を参照して、本発明の車両用軸受装置について、自動車等の車両の車体に取り付けられて、車輪と共に回転する転がり軸受装置として具体化した第３の実施形態を説明する。なお、本実施形態に係る転がり軸受装置は、第１の実施形態の転がり軸受装置と比較して、回転体の中空部の形状が変更するのみであるために、中空部のみの説明を行い、他の部位の説明は省略する。また、図９において、第１の実施形態の回転体と同一部位には、同一の符号を付す。 (Third embodiment)
Next, with reference to FIG. 9, a third embodiment in which the vehicle bearing device of the present invention is embodied as a rolling bearing device that is attached to a vehicle body of a vehicle such as an automobile and rotates with wheels will be described. In addition, since the rolling bearing device according to the present embodiment only changes the shape of the hollow portion of the rotating body as compared with the rolling bearing device of the first embodiment, only the hollow portion is described. Description of other parts is omitted. Moreover, in FIG. 9, the same code | symbol is attached | subjected to the site | part same as the rotary body of 1st Embodiment.

図９に示すように、回転体２の円筒部２１に設けられた中空部２５は、車輪側空間２５１の穴径Ｒ１が、フランジ面２６から軸方向の車体側に向かい拡径するように設けられている。即ち、取付部２２に対する円筒部２１の剛性に必要な円筒部２１の軸方向の車外側の距離Ｄ１にて規定される肉厚を残すことができるとともに、取付部２２に対する円筒部２１の剛性に影響の少ない円筒部２１の軸方向の車体側の肉厚Ｄ３を薄くなる。したがって、円筒部２１の剛性を維持しつつも、中空部２５による回転体２の重量の低減の効果を向上させることができる。   As shown in FIG. 9, the hollow portion 25 provided in the cylindrical portion 21 of the rotating body 2 is provided so that the hole diameter R1 of the wheel side space 251 increases from the flange surface 26 toward the vehicle body side in the axial direction. It has been. In other words, the thickness defined by the distance D1 on the outside of the vehicle in the axial direction of the cylindrical portion 21 necessary for the rigidity of the cylindrical portion 21 with respect to the mounting portion 22 can be left, and the rigidity of the cylindrical portion 21 with respect to the mounting portion 22 can be increased. The wall thickness D3 on the vehicle body side in the axial direction of the cylindrical portion 21 having a small influence is reduced. Therefore, the effect of reducing the weight of the rotating body 2 by the hollow portion 25 can be improved while maintaining the rigidity of the cylindrical portion 21.

本実施形態の転がり軸受装置では、第１の実施形態の転がり軸受装置１の効果（２）〜（４）と同様の効果に加え、以下の効果を得ることができる。
（６）本実施形態の転がり軸受装置１では、取付部２２の突出部２２２の軸方向の位置と略同位置の中空部２５の車輪側空間２５１の穴径Ｒ１が、軸方向の車外側に向かうにしたがい小さくなる構成とする。この構成により、回転体２の円筒部２１の外周面の形状を変更することなく、内周面２１ｃと取付部２２と円筒部２１の外周面との境界部Ｐ１を径方向に結んだ距離Ｄ１によって規定される円筒部２１の肉厚を、円筒部２１の他の部位の外周面と中空部２５を構成する内周面２１ｃとを径方向に結んだ距離Ｄ２によって規定される円筒部２１の肉厚より大きくすることができる。したがって、取付部２２に対する円筒部２１の剛性を向上させることができる。その結果、円筒部２１の変形に伴い、円筒部２１と転動体４とが圧接することを抑制することができる。即ち、転動体４の表面及び転動体４と接触する円筒部２１の車外側軌道溝２１ａの表面が損傷することを抑制するとともに、転がり軸受装置１の寿命の低下を抑制することができる。 In the rolling bearing device of the present embodiment, the following effects can be obtained in addition to the same effects as the effects (2) to (4) of the rolling bearing apparatus 1 of the first embodiment.
(6) In the rolling bearing device 1 of the present embodiment, the hole diameter R1 of the wheel-side space 251 of the hollow portion 25 at substantially the same position as the axial position of the protruding portion 222 of the mounting portion 22 is on the outer side in the axial direction. The structure becomes smaller as it goes. With this configuration, the distance D1 connecting the boundary portion P1 between the inner peripheral surface 21c, the mounting portion 22, and the outer peripheral surface of the cylindrical portion 21 in the radial direction without changing the shape of the outer peripheral surface of the cylindrical portion 21 of the rotating body 2. Of the cylindrical portion 21 defined by the distance D2 that connects the outer peripheral surface of the other part of the cylindrical portion 21 and the inner peripheral surface 21c constituting the hollow portion 25 in the radial direction. Can be larger than the wall thickness. Therefore, the rigidity of the cylindrical portion 21 with respect to the attachment portion 22 can be improved. As a result, it is possible to prevent the cylindrical portion 21 and the rolling element 4 from being in pressure contact with the deformation of the cylindrical portion 21. That is, the surface of the rolling element 4 and the surface of the outer raceway groove 21a of the cylindrical portion 21 in contact with the rolling element 4 can be prevented from being damaged, and the life of the rolling bearing device 1 can be prevented from being reduced.

また、本実施形態の転がり軸受装置１では、中空部２５が設けられることにより、中空部２５が設けられない転がり軸受装置の重量と比較して、図５に示す従来の転がり軸受装置１００に対する転がり軸受装置１の重量の増加を抑制することができる。   Further, in the rolling bearing device 1 of the present embodiment, by providing the hollow portion 25, the rolling bearing device 100 shown in FIG. 5 is compared with the weight of the rolling bearing device 100 in which the hollow portion 25 is not provided. An increase in the weight of the bearing device 1 can be suppressed.

したがって、本実施形態の転がり軸受装置１は、図５に示す従来の転がり軸受装置１００の回転体１０１と比較して、回転体２の重量の増加を抑制すること、及び回転体２の剛性を向上させることができる。その結果、回転体２の軽量化を図りつつも、回転体２の大きな変形を抑制することができる。   Therefore, the rolling bearing device 1 of this embodiment suppresses the increase in the weight of the rotating body 2 and the rigidity of the rotating body 2 as compared with the rotating body 101 of the conventional rolling bearing device 100 shown in FIG. Can be improved. As a result, large deformation of the rotating body 2 can be suppressed while reducing the weight of the rotating body 2.

（その他の実施形態）
本発明の転がり軸受装置は、以下の変形も可能である。
・第１〜第３の実施形態の転がり軸受装置１では、転動体４に球状の鋼球を用いたが、本発明は、転動体４の形状に限定されることはない。例えば、転動体を鋼球に代えて、円筒形状、もしくは円錐形状のころを用いてもよい。 (Other embodiments)
The rolling bearing device of the present invention can be modified as follows.
In the rolling bearing device 1 of the first to third embodiments, a spherical steel ball is used for the rolling element 4, but the present invention is not limited to the shape of the rolling element 4. For example, instead of the steel ball as the rolling element, a cylindrical or conical roller may be used.

・第１〜第３の実施形態の転がり軸受装置１では、回転体２の取付部２２の固定部２２ｃが５個設けられたが、本発明は、取付部２２の固定部２２ｃの個数に限定されることはない。例えば、固定部２２ｃの数は、４個以下でも、６個以上であってもよい。   In the rolling bearing device 1 of the first to third embodiments, the five fixing portions 22c of the attachment portion 22 of the rotating body 2 are provided, but the present invention is limited to the number of the fixing portions 22c of the attachment portion 22. It will never be done. For example, the number of fixing portions 22c may be 4 or less, or 6 or more.

・第１〜第３の実施形態の転がり軸受装置１では、回転体２の薄肉部２２ｄが、軸方向の車外側に向かい径方向の外側に傾斜する傾斜面２２ｅを有していたが、本発明は、傾斜面２２ｅの形状に限定されることはない。例えば、傾斜面２２ｅの代わりに、軸方向に沿って伸びる平面であってもよい。また、傾斜面２２ｅの代わりに、軸方向の車外側に向かい径方向の内側に傾斜する傾斜面であってもよい。   In the rolling bearing device 1 of the first to third embodiments, the thin portion 22d of the rotating body 2 has the inclined surface 22e that is inclined outward in the radial direction toward the vehicle outer side in the axial direction. The invention is not limited to the shape of the inclined surface 22e. For example, a plane extending along the axial direction may be used instead of the inclined surface 22e. Further, instead of the inclined surface 22e, an inclined surface that is inclined inward in the radial direction toward the vehicle outer side in the axial direction may be used.

次に、以上の実施形態から把握できる技術的思想について、以下に記載する。
（イ）請求項１乃至請求項４のいずれか一項に記載の車両用軸受装置において、軸方向において、前記突起部と略同位置の、前記車輪側空間を構成する内径は、前記回転体における前記内輪が固定される部位の外周面の外径の略１／２以下であることを特徴とする車両用軸受装置。 Next, the technical idea that can be grasped from the above embodiment will be described below.
(A) In the vehicle bearing device according to any one of claims 1 to 4, the inner diameter of the wheel-side space, which is substantially the same position as the protrusion in the axial direction, is the rotating body. The bearing device for a vehicle according to claim 1, wherein the outer diameter of the outer peripheral surface of the portion to which the inner ring is fixed is approximately ½ or less.

この構成によれば、突出部の軸方向の位置と略同位置において、車輪側空間を構成する内径が、内輪が固定される部位の外周面の外径の略１／２以下であることにより、車輪取付部に対する軸体の剛性を向上させることができる。したがって、回転体の剛性が向上するために、回転体の大きな変形を抑制することができる。   According to this configuration, at substantially the same position as the axial position of the protrusion, the inner diameter constituting the wheel side space is approximately ½ or less of the outer diameter of the outer peripheral surface of the portion to which the inner ring is fixed. The rigidity of the shaft body with respect to the wheel mounting portion can be improved. Therefore, since the rigidity of the rotating body is improved, large deformation of the rotating body can be suppressed.

１…転がり軸受装置（車両用軸受装置）、２…回転体、２１…円筒部、２１ａ…車外側軌道溝（軌道溝）、２１ｂ…端部、２１ｃ…内周面、２１ｄ…面取り部、２１ｅ…縮径部、２１ｆ…底部、２１ｇ…第１外周面（外周面）、２１ｈ…曲面、２２…取付部、２２ａ…外側面、２２ｂ…取付穴、２２ｃ…固定部、２２ｄ…薄肉部、２２ｅ…傾斜面、２２ｆ…平面部、２２ｇ…第１固定部、２２ｈ…第２固定部、２２１…基部、２２２…突起部、２３…インロー部、２４…内輪（回転体）、２４ａ…車体側軌道溝（軌道溝）、２５…中空部、２５１…車輪側空間、２５２…車体側空間、２５３…開口部、２６…フランジ面、２７…穴部、２７ａ…底部、２８…隔壁部、３…固定体、３１…円筒部、３１ａ…車外側軌道溝（軌道溝）、３１ｂ…車体側軌道溝（軌道溝）、３１ｃ…嵌合部、３２…フランジ部、３２ａ…固定孔、４…転動体、５…保持器、６…車外側シール、６１…固定側芯金、６２…弾性シール体、７…車体側シール、７１…固定側芯金、７２…回転側芯金、７３…弾性シール体。   DESCRIPTION OF SYMBOLS 1 ... Rolling bearing apparatus (vehicle bearing apparatus), 2 ... Rotating body, 21 ... Cylindrical part, 21a ... Outer side raceway groove (tracking groove), 21b ... End part, 21c ... Inner peripheral surface, 21d ... Chamfering part, 21e ... reduced diameter portion, 21f ... bottom, 21g ... first outer peripheral surface (outer peripheral surface), 21h ... curved surface, 22 ... mounting portion, 22a ... outer surface, 22b ... mounting hole, 22c ... fixing portion, 22d ... thin wall portion, 22e ... Inclined surface, 22f ... Plane part, 22g ... First fixing part, 22h ... Second fixing part, 221 ... Base part, 222 ... Protrusion part, 23 ... Inlay part, 24 ... Inner ring (rotating body), 24a ... Vehicle side track Groove (track groove), 25 ... hollow portion, 251 ... wheel side space, 252 ... vehicle body side space, 253 ... opening, 26 ... flange surface, 27 ... hole, 27a ... bottom, 28 ... partition wall, 3 ... fixed Body, 31 ... cylindrical portion, 31a ... outer side track groove (track groove), 31b ... car Side raceway groove (track groove), 31c ... fitting portion, 32 ... flange portion, 32a ... fixed hole, 4 ... rolling element, 5 ... cage, 6 ... vehicle outer side seal, 61 ... fixed side core, 62 ... elastic Seal body 7... Car body side seal 71... Fixed side metal core 72.

Claims (4)

車輪が取り付けられる車輪取付部、及び軸体を有する回転体と、前記軸体を外囲し、且つ転動体を介して前記軸体を支持する固定体とを備え、前記車輪取付部には、前記軸体より径方向の外側に突出する突出部が設けられ、前記車輪取付部及び前記軸体の内部には、前記車輪取付部の軸方向の車外側の端部から前記軸体の中間部までにわたり軸方向に延び、前記中間部にて閉塞する空間である内部空間が設けられ、前記回転体が前記車輪と共に前記固定体に対して回転する車両用軸受装置において、
前記内部空間には、前記突出部の径方向の内側と対応するところにあり、且つ軸方向に沿って前記内部空間の内径が一定、または軸方向の車体側に向かうにしたがい前記内径が小さくなる車輪側空間が形成される
ことを特徴とする車両用軸受装置。 A wheel mounting portion to which a wheel is mounted, a rotating body having a shaft body, and a fixed body that surrounds the shaft body and supports the shaft body via a rolling element, the wheel mounting portion includes: Protrusions projecting radially outward from the shaft body are provided, and an intermediate portion of the shaft body is provided in the wheel mounting portion and the shaft body from an axially outer end portion of the wheel mounting portion. In the vehicular bearing device in which an internal space is provided that extends in the axial direction and is closed at the intermediate portion, and the rotating body rotates with respect to the fixed body together with the wheels,
The inner space corresponds to the radially inner side of the protruding portion, and the inner diameter of the inner space is constant along the axial direction, or the inner diameter becomes smaller toward the vehicle body side in the axial direction. A vehicle bearing device characterized in that a wheel side space is formed. 請求項１に記載の軸受装置において、
前記車輪取付部は、前記車輪側空間を形成する基部と、前記基部の径方向の外側に設けられ、略円盤状を形成する突出部とを有し、
前記基部の軸方向の車外側には、フランジ面が設けられ、
前記突出部の軸方向の車外側には、外側面が設けられ、
前記フランジ面は、前記外側面より軸方向の車外側に設けられる
ことを特徴とする車両用軸受装置。 The bearing device according to claim 1,
The wheel mounting part has a base part that forms the wheel side space, and a protruding part that is provided on the outer side in the radial direction of the base part and forms a substantially disk shape,
A flange surface is provided on the outer side of the base in the axial direction,
On the vehicle outer side in the axial direction of the protrusion, an outer surface is provided,
The said bearing surface is provided in the vehicle outer side of an axial direction from the said outer surface. The vehicle bearing apparatus characterized by the above-mentioned. 請求項２に記載の車両用軸受装置において、
前記突出部には、前記車輪に締結されるボルトが挿入され、当該車両用軸受装置が前記車輪に固定される固定部が設けられ、
前記突出部の厚さについて、周方向において隣り合う固定部間の厚さは、前記固定部の厚さより小さく設定される
ことを特徴とする車両用軸受装置。 The vehicle bearing device according to claim 2,
A bolt that is fastened to the wheel is inserted into the protruding portion, and a fixing portion that fixes the vehicle bearing device to the wheel is provided.
About the thickness of the said protrusion part, the thickness between the fixing parts adjacent in the circumferential direction is set smaller than the thickness of the said fixing part. The vehicle bearing device characterized by the above-mentioned. 請求項１〜請求項３のいずれか一項に記載の車両用軸受装置において、
前記軸体には、外周溝が設けられ、
前記外周溝には、前記転動体を保持する内輪が取り付けられ、
前記車輪側空間の内径は、前記外周溝の外径より小さく設定される
ことを特徴とする車両用軸受装置。 In the vehicle bearing device according to any one of claims 1 to 3,
The shaft body is provided with an outer peripheral groove,
An inner ring that holds the rolling element is attached to the outer circumferential groove,
An inner diameter of the wheel side space is set to be smaller than an outer diameter of the outer circumferential groove.
JP2009177843A 2009-07-30 2009-07-30 Vehicle bearing device Pending JP2011031670A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102133838A (en) * 2011-02-21 2011-07-27 安徽福马车桥有限公司 Vehicle front axle hub
JP2017083012A (en) * 2015-10-23 2017-05-18 日本精工株式会社 Wheel supporting double row rolling bearing unit

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102133838A (en) * 2011-02-21 2011-07-27 安徽福马车桥有限公司 Vehicle front axle hub
JP2017083012A (en) * 2015-10-23 2017-05-18 日本精工株式会社 Wheel supporting double row rolling bearing unit

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