JP2021122891A - Spindle device - Google Patents

Spindle device Download PDF

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JP2021122891A
JP2021122891A JP2020017618A JP2020017618A JP2021122891A JP 2021122891 A JP2021122891 A JP 2021122891A JP 2020017618 A JP2020017618 A JP 2020017618A JP 2020017618 A JP2020017618 A JP 2020017618A JP 2021122891 A JP2021122891 A JP 2021122891A
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bearing
shaft
spindle device
load
sleeve
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JP7456792B2 (en
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真一 田中
Shinichi Tanaka
真一 田中
雄三 稲口
Yuzo Inaguchi
雄三 稲口
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Fanuc Corp
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Fanuc Corp
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  • Rolling Contact Bearings (AREA)
  • Turning (AREA)
  • Machine Tool Units (AREA)
  • Support Of The Bearing (AREA)

Abstract

To provide a spindle device configured so that an increase of precompression can be suppressed when a shaft rotates.SOLUTION: A spindle device 10 comprises a load application part 22, mounted on a shaft 12, which applies a load in an axial direction to a bearing 16, and a sleeve 20 arranged between an inner ring 30 of the bearing 16 and the load application part 22. A first surface 20F as an end face at the load application part 22 side in the sleeve 20 and a second surface 22F as an end face at the sleeve 20 side in the load application part 22 are inclined with respect to the shaft 12.SELECTED DRAWING: Figure 1

Description

本発明は、主軸装置に関する。 The present invention relates to a spindle device.

主軸装置は、シャフトと、シャフトが挿通されるハウジングと、シャフトをハウジングに対して回転可能に支持する軸受とを有している。軸受は、あらかじめ予圧が加わっている状態で用いられる場合がある。軸受に対して予圧を加える場合、ロックナットを用いて予圧を付与する定位置予圧が知られている。 The spindle device includes a shaft, a housing through which the shaft is inserted, and a bearing that rotatably supports the shaft with respect to the housing. Bearings may be used with preload applied in advance. When a preload is applied to a bearing, a fixed position preload is known in which a locknut is used to apply the preload.

下記の特許文献１には、シャフト（ねじ軸）がハウジングに挿通され、軸方向に間隔をあけて一対の軸受がハウジング内に収納された軸受ユニットが開示される。一対の軸受の一方は、ハウジングの内周面に嵌合された間座とシャフトの係止部との当接により、軸方向への軸移動が規制され、一対の軸受の他方は、シャフトに嵌合されたロックナットとハウジングの係止部との当接により、軸方向への移動が規制されている。 Patent Document 1 below discloses a bearing unit in which a shaft (screw shaft) is inserted into a housing and a pair of bearings are housed in the housing at intervals in the axial direction. One of the pair of bearings is restricted from axial movement in the axial direction by the contact between the spacer fitted to the inner peripheral surface of the housing and the locking portion of the shaft, and the other of the pair of bearings is attached to the shaft. Axial movement is restricted by contact between the fitted locknut and the locking portion of the housing.

特開２００８−１６７６０８号公報JP-A-2008-167608

しかし、上記の特許文献１のように、定位置予圧で予圧が付与される場合、シャフトが回転していないときの予圧に比べて、シャフトが回転しているときの予圧が上昇する傾向にあり、当該予圧の上昇量は、シャフトの回転が高速になるほど大きくなり易い。 However, as in Patent Document 1 above, when a preload is applied by a fixed position preload, the preload when the shaft is rotating tends to increase as compared with the preload when the shaft is not rotating. The amount of increase in the preload tends to increase as the rotation speed of the shaft increases.

そこで、本発明は、シャフトが回転するときの予圧の上昇を抑制し得る主軸装置を提供することを目的とする。 Therefore, an object of the present invention is to provide a spindle device capable of suppressing an increase in preload when the shaft rotates.

本発明の態様は、シャフトと、前記シャフトが挿通されるハウジングと、前記シャフトを前記ハウジングに対して回転可能に支持する軸受とを有する主軸装置であって、前記シャフトに取り付けられ、前記軸受にアキシアル方向の荷重を付与する荷重付与部と、前記軸受の内輪と、前記荷重付与部との間に配置されるスリーブと、を備え、前記スリーブにおける前記荷重付与部側の端面である第１面と、前記荷重付与部における前記スリーブ側の端面である第２面とは、前記シャフトに対して傾斜している。 Aspect of the present invention is a spindle device having a shaft, a housing through which the shaft is inserted, and a bearing that rotatably supports the shaft with respect to the housing, and is attached to the shaft and attached to the bearing. A first surface of the sleeve, which includes a load-applying portion for applying a load in the axial direction, an inner ring of the bearing, and a sleeve arranged between the load-applying portion, and is an end surface of the sleeve on the load-applying portion side. And the second surface, which is the end surface on the sleeve side of the load-applying portion, is inclined with respect to the shaft.

本発明の態様によれば、シャフトの回転時に生じる遠心力が大きくなるほど、第１面および第２面の接触位置（相対位置）が変位し、荷重付与部が軸受に付与する荷重の荷重量を下げることができる。この結果、シャフトが回転するときの予圧の上昇を抑制することができる。 According to the aspect of the present invention, as the centrifugal force generated when the shaft rotates increases, the contact positions (relative positions) of the first surface and the second surface are displaced, and the load amount of the load applied to the bearing by the load applying portion is increased. Can be lowered. As a result, it is possible to suppress an increase in the preload when the shaft rotates.

第１実施形態の主軸装置を示す断面図である。It is sectional drawing which shows the spindle apparatus of 1st Embodiment. シャフトの回転により荷重付与部が変形した様子を示す断面図である。It is sectional drawing which shows the appearance that the load-applied part was deformed by the rotation of a shaft. 第２実施形態の主軸装置を示す断面図である。It is sectional drawing which shows the spindle apparatus of 2nd Embodiment. 第３実施形態の主軸装置を示す断面図である。It is sectional drawing which shows the spindle apparatus of 3rd Embodiment.

本発明について、好適な実施形態を掲げ、添付の図面を参照しながら以下、詳細に説明する。 A preferred embodiment of the present invention will be described below in detail with reference to the accompanying drawings.

〔実施形態〕
（第１実施形態）
図１を用いて、第１実施形態の主軸装置１０を説明する。主軸装置１０は、工作機械に用いられる。工作機械が旋盤機である場合、主軸装置１０は主軸台に相当する。工作機械がマシニングセンタである場合、主軸装置１０は主軸頭に相当する。主軸装置１０は、シャフト１２、ハウジング１４、軸受１６、第２の軸受１８、スリーブ２０および荷重付与部２２を有する。 [Embodiment]
(First Embodiment)
The spindle device 10 of the first embodiment will be described with reference to FIG. The spindle device 10 is used in a machine tool. When the machine tool is a lathe, the spindle device 10 corresponds to a spindle base. When the machine tool is a machining center, the spindle device 10 corresponds to the spindle head. The spindle device 10 includes a shaft 12, a housing 14, a bearing 16, a second bearing 18, a sleeve 20, and a load applying portion 22.

シャフト１２は、シャフト１２を駆動するモータ（図示せず）から伝達される動力により回転する軸である。なお、シャフト１２は、シャフト１２が延びる方向（軸方向）に沿って貫通する貫通孔を有してもよい。シャフト１２の外周面には、第２の軸受１８の内輪３０を係止する内輪係止部１２Ａが形成されている。 The shaft 12 is a shaft that is rotated by power transmitted from a motor (not shown) that drives the shaft 12. The shaft 12 may have a through hole penetrating along the direction (axial direction) in which the shaft 12 extends. An inner ring locking portion 12A for locking the inner ring 30 of the second bearing 18 is formed on the outer peripheral surface of the shaft 12.

ハウジング１４は、シャフト１２が挿通される孔を有する箱体である。ハウジング１４は、複数のハウジング分体に分割され、ハウジング分体の各々を組み立てることで形成されてもよい。ハウジング１４の内周面には、軸受１６の外輪３２を係止する第１外輪係止部１４Ａと、第２の軸受１８の外輪３２を係止する第２外輪係止部１４Ｂとが、シャフト１２が延びる軸方向に間隔をあけて形成されている。 The housing 14 is a box body having a hole through which the shaft 12 is inserted. The housing 14 may be divided into a plurality of housing divisions and formed by assembling each of the housing divisions. On the inner peripheral surface of the housing 14, a first outer ring locking portion 14A for locking the outer ring 32 of the bearing 16 and a second outer ring locking portion 14B for locking the outer ring 32 of the second bearing 18 are shafts. 12 is formed at intervals in the extending axial direction.

軸受１６および第２の軸受１８は、シャフト１２をハウジング１４に対して回転可能に支持するものであり、内輪３０と外輪３２と転動体３４とを有する。軸受１６および第２の軸受１８は、本実施形態では、アンギュラ玉軸受とし、背面合わせでハウジング１４の内部に配置されるものとする。軸受１６の内輪３０と第２の軸受１８の内輪３０との間には内輪間座３６が配置され、軸受１６の外輪３２と第２の軸受１８の外輪３２との間には外輪間座３８が配置される。なお、内輪間座３６は省かれていてもよい。外輪間座３８が軸受１６の外輪３２と第２の軸受１８の外輪３２との間に配置されることで、軸受１６の外輪３２は第１外輪係止部１４Ａに押さえ付けられるとともに、第２の軸受１８の外輪３２は第２外輪係止部１４Ｂに押さえ付けられる。これにより、軸受１６および第２の軸受１８の外輪３２がハウジング１４に固定される。 The bearing 16 and the second bearing 18 rotatably support the shaft 12 with respect to the housing 14, and have an inner ring 30, an outer ring 32, and a rolling element 34. In the present embodiment, the bearing 16 and the second bearing 18 are angular contact ball bearings, and are arranged inside the housing 14 so as to be back-to-back. An inner ring spacer 36 is arranged between the inner ring 30 of the bearing 16 and the inner ring 30 of the second bearing 18, and an outer ring spacer 38 is arranged between the outer ring 32 of the bearing 16 and the outer ring 32 of the second bearing 18. Is placed. The inner ring spacer 36 may be omitted. By arranging the outer ring spacer 38 between the outer ring 32 of the bearing 16 and the outer ring 32 of the second bearing 18, the outer ring 32 of the bearing 16 is pressed against the first outer ring locking portion 14A and the second. The outer ring 32 of the bearing 18 of the above is pressed against the second outer ring locking portion 14B. As a result, the outer ring 32 of the bearing 16 and the second bearing 18 is fixed to the housing 14.

スリーブ２０は、ハウジング１４の内部に配置される軸受１６の内輪３０と、当該ハウジング１４の外部に配置される荷重付与部２２との間に配置されるものであり、筒状に形成される。スリーブ２０は、軸受１６の内輪３０と別体のものであっても、軸受１６の内輪３０と一体であってもよい。なお、図１では、スリーブ２０は、軸受１６の内輪３０と別体のものとして示している。 The sleeve 20 is arranged between the inner ring 30 of the bearing 16 arranged inside the housing 14 and the load applying portion 22 arranged outside the housing 14, and is formed in a tubular shape. The sleeve 20 may be separate from the inner ring 30 of the bearing 16 or may be integrated with the inner ring 30 of the bearing 16. In FIG. 1, the sleeve 20 is shown as a separate body from the inner ring 30 of the bearing 16.

荷重付与部２２は、軸受１６にアキシアル方向の荷重を付与するものであり、ハウジング１４の外部のシャフト１２に取り付けられる。本実施形態では、荷重付与部２２は、ロックナットとする。荷重付与部２２（ロックナット）は、ハウジング１４から露出するシャフト１２の外周面に形成されたねじ部位に螺合する。 The load applying portion 22 applies a load in the axial direction to the bearing 16 and is attached to a shaft 12 outside the housing 14. In the present embodiment, the load applying portion 22 is a locknut. The load applying portion 22 (locknut) is screwed into a screw portion formed on the outer peripheral surface of the shaft 12 exposed from the housing 14.

荷重付与部２２（ロックナット）は、工具を用いて締め付けられると、スリーブ２０を介して軸受１６にアキシアル方向の荷重を付与する。この荷重が付与されることで、軸受１６はスリーブ２０と外輪間座３８とに押さえつけられるとともに、第２の軸受１８は外輪間座３８と内輪係止部１２Ａとに押さえつけられる。これにより、軸受１６および第２の軸受１８に常に予圧が加わった状態で、軸受１６および第２の軸受１８の内輪３０がシャフト１２に固定される。 When the load applying portion 22 (locknut) is tightened with a tool, a load in the axial direction is applied to the bearing 16 via the sleeve 20. By applying this load, the bearing 16 is pressed against the sleeve 20 and the outer ring spacer 38, and the second bearing 18 is pressed against the outer ring spacer 38 and the inner ring locking portion 12A. As a result, the inner ring 30 of the bearing 16 and the second bearing 18 is fixed to the shaft 12 in a state where the bearing 16 and the second bearing 18 are constantly preloaded.

本実施形態の主軸装置１０では、スリーブ２０における荷重付与部２２側の端面である第１面２０Ｆと、荷重付与部２２におけるスリーブ２０側の端面である第２面２２Ｆとは、シャフト１２に対して傾斜している。第１面２０Ｆおよび第２面２２Ｆは、具体的には、互いにシャフト１２から離れるほど軸受１６に近づくように傾斜し、接触している。 In the spindle device 10 of the present embodiment, the first surface 20F, which is the end surface of the sleeve 20 on the side of the load applying portion 22, and the second surface 22F, which is the end surface of the load applying portion 22 on the sleeve 20 side, are opposed to the shaft 12. Is tilted. Specifically, the first surface 20F and the second surface 22F are inclined and in contact with each other so as to be closer to the bearing 16 as the distance from the shaft 12 increases.

これにより、図２に示すように、シャフト１２の回転時に働く遠心力に応じて、荷重付与部２２が外側に広がるように変形する。荷重付与部２２が外側に広がるように変形する変形量は、シャフト１２の回転が高速になるほど大きくなる。荷重付与部２２が外側に広がるように変形すると、その変形量に応じて、互いに接触する第１面２０Ｆおよび第２面２２Ｆの接触位置（相対位置）が変化し、スリーブ２０に付与する荷重が解放される。これにより、軸受１６に付与する荷重の荷重量が下がる。 As a result, as shown in FIG. 2, the load applying portion 22 is deformed so as to spread outward according to the centrifugal force acting during the rotation of the shaft 12. The amount of deformation that the load-applying portion 22 deforms so as to spread outward increases as the rotation speed of the shaft 12 increases. When the load applying portion 22 is deformed so as to spread outward, the contact positions (relative positions) of the first surface 20F and the second surface 22F that are in contact with each other change according to the amount of deformation, and the load applied to the sleeve 20 is applied. To be released. As a result, the amount of load applied to the bearing 16 is reduced.

このように本実施形態の主軸装置１０は、シャフト１２の回転時に生じる遠心力が大きくなるほど、第１面２０Ｆと第２面２２Ｆとの接触面を小さくして荷重付与部２２が軸受１６に付与する荷重の荷重量を下げることができる。この結果、シャフト１２が回転するときの予圧の上昇を抑制することができる。 As described above, in the spindle device 10 of the present embodiment, as the centrifugal force generated when the shaft 12 rotates increases, the contact surface between the first surface 20F and the second surface 22F becomes smaller, and the load applying portion 22 applies to the bearing 16. It is possible to reduce the amount of load to be applied. As a result, it is possible to suppress an increase in the preload when the shaft 12 rotates.

なお、荷重付与部２２の縦弾性係数がスリーブ２０の縦弾性係数よりも小さい場合、あるいは、荷重付与部２２の密度がスリーブ２０の密度よりも小さい場合、荷重付与部２２が外側に広がるように変形し易くなる。したがって、荷重付与部２２の縦弾性係数および密度の少なくとも一方がスリーブ２０よりも小さい場合には、シャフト１２の回転速度（遠心力）に応じた第１面２０Ｆおよび第２面２２Ｆの接触位置の変位量を大きくすることができる。 When the Young's modulus of the load applying portion 22 is smaller than the Young's modulus of the sleeve 20, or when the density of the load applying portion 22 is smaller than the density of the sleeve 20, the load applying portion 22 is spread outward. It becomes easy to be deformed. Therefore, when at least one of the longitudinal elasticity coefficient and the density of the load applying portion 22 is smaller than the sleeve 20, the contact positions of the first surface 20F and the second surface 22F according to the rotational speed (centrifugal force) of the shaft 12 The amount of displacement can be increased.

（第２実施形態）
次に、図３を用いて、第２実施形態の主軸装置１０を説明する。図３では、第１実施形態において説明した構成と同等の構成に対して同一の符号が付されている。なお、本実施形態では、第１実施形態と重複する説明は省略する。 (Second Embodiment)
Next, the spindle device 10 of the second embodiment will be described with reference to FIG. In FIG. 3, the same reference numerals are given to the configurations equivalent to the configurations described in the first embodiment. In this embodiment, the description overlapping with the first embodiment will be omitted.

本実施形態では、第１面２０Ｆおよび第２面２２Ｆは、互いにシャフト１２から離れるほど軸受１６から遠ざかるように傾斜し、接触している。 In the present embodiment, the first surface 20F and the second surface 22F are inclined and in contact with each other so as to be farther from the bearing 16 as the distance from the shaft 12 increases.

これにより、図示はしないが、シャフト１２の回転時に働く遠心力に応じて、スリーブ２０が外側に広がるように変形する。スリーブ２０が外側に広がるように変形する変形量は、第１実施形態と同様に、シャフト１２の回転が高速になるほど大きくなる。スリーブ２０が外側に広がるように変形すると、その変形量に応じて、互いに接触する第１面２０Ｆおよび第２面２２Ｆの接触位置（相対位置）が変化することで、荷重付与部２２が軸受１６に付与する荷重の荷重量が下がる。 As a result, although not shown, the sleeve 20 is deformed so as to spread outward in response to the centrifugal force acting during the rotation of the shaft 12. The amount of deformation that the sleeve 20 deforms so as to spread outward increases as the rotation speed of the shaft 12 increases, as in the first embodiment. When the sleeve 20 is deformed so as to spread outward, the contact positions (relative positions) of the first surface 20F and the second surface 22F that are in contact with each other change according to the amount of deformation, so that the load applying portion 22 becomes the bearing 16. The amount of load applied to is reduced.

このように本実施形態の主軸装置１０は、第１実施形態と同様に、シャフト１２の回転時に生じる遠心力が大きくなるほど、第１面２０Ｆおよび第２面２２Ｆの接触位置（相対位置）を変位させて荷重付与部２２が軸受１６に付与する荷重の荷重量を下げることができる。この結果、シャフト１２が回転するときの予圧の上昇を抑制することができる。 As described above, the spindle device 10 of the present embodiment displaces the contact positions (relative positions) of the first surface 20F and the second surface 22F as the centrifugal force generated when the shaft 12 rotates increases, as in the first embodiment. The load amount of the load applied to the bearing 16 by the load applying portion 22 can be reduced. As a result, it is possible to suppress an increase in the preload when the shaft 12 rotates.

なお、本実施形態では、荷重付与部２２の縦弾性係数がスリーブ２０の縦弾性係数よりも大きい場合、あるいは、荷重付与部２２の密度がスリーブ２０の密度よりも大きい場合、スリーブ２０が外側に広がるように変形し易くなる。したがって、荷重付与部２２の縦弾性係数および密度の少なくとも一方がスリーブ２０よりも大きい場合には、シャフト１２の回転速度（遠心力）に応じた第１面２０Ｆおよび第２面２２Ｆの接触位置の変位量を大きくすることができる。 In the present embodiment, when the Young's modulus of the load applying portion 22 is larger than the Young's modulus of the sleeve 20, or when the density of the load applying portion 22 is larger than the density of the sleeve 20, the sleeve 20 is moved to the outside. It becomes easy to deform so as to spread. Therefore, when at least one of the longitudinal elasticity coefficient and the density of the load applying portion 22 is larger than that of the sleeve 20, the contact positions of the first surface 20F and the second surface 22F according to the rotational speed (centrifugal force) of the shaft 12 The amount of displacement can be increased.

（第３実施形態）
次に、図４を用いて、第３実施形態の主軸装置１０を説明する。図４では、第１実施形態において説明した構成と同等の構成に対して同一の符号が付されている。なお、本実施形態では、第１実施形態と重複する説明は省略する。 (Third Embodiment)
Next, the spindle device 10 of the third embodiment will be described with reference to FIG. In FIG. 4, the same reference numerals are given to the configurations equivalent to the configurations described in the first embodiment. In this embodiment, the description overlapping with the first embodiment will be omitted.

本実施形態では、第１面２０Ｆは、シャフト１２から離れるほど軸受１６に近づくように傾斜し、第２面２２Ｆは、シャフト１２から離れるほど軸受１６から遠ざかるように傾斜している。 In the present embodiment, the first surface 20F is inclined so as to be closer to the bearing 16 as the distance from the shaft 12 is increased, and the second surface 22F is inclined so as to be closer to the bearing 16 as the distance from the shaft 12 is increased.

また、本実施形態では、第１面２０Ｆと第２面２２Ｆとの間にスペーサ４０が設けられる。スペーサ４０は、筒状に形成され、第１面２０Ｆおよび第２面２２Ｆに接触する接触面を有している。 Further, in the present embodiment, the spacer 40 is provided between the first surface 20F and the second surface 22F. The spacer 40 is formed in a tubular shape and has a contact surface that contacts the first surface 20F and the second surface 22F.

本実施形態では、図示はしないが、シャフト１２の回転時に働く遠心力に応じて、スペーサ４０が外側に広がるように変形する。スペーサ４０が外側に広がるように変形する変形量は、第１実施形態と同様に、シャフト１２の回転が高速になるほど大きくなる。スペーサ４０が外側に広がるように変形すると、その変形量に応じて、スペーサ４０が接触する第１面２０Ｆおよび第２面２２Ｆの少なくとも一方の接触位置（相対位置）が変化することで、荷重付与部２２が軸受１６に付与する荷重の荷重量が下がる。 In the present embodiment, although not shown, the spacer 40 is deformed so as to spread outward according to the centrifugal force acting when the shaft 12 rotates. The amount of deformation that the spacer 40 deforms so as to spread outward increases as the rotation speed of the shaft 12 increases, as in the first embodiment. When the spacer 40 is deformed so as to spread outward, at least one contact position (relative position) of the first surface 20F and the second surface 22F with which the spacer 40 contacts changes according to the amount of deformation, thereby applying a load. The amount of the load applied to the bearing 16 by the portion 22 is reduced.

このように本実施形態の主軸装置１０は、第１実施形態と同様に、シャフト１２の回転時に生じる遠心力が大きくなるほど、第１面２０Ｆおよび第２面２２Ｆの接触位置（相対位置）を変位させることで荷重付与部２２が軸受１６に付与する荷重の荷重量を下げることができる。この結果、シャフト１２が回転するときの予圧の上昇を抑制することができる。 As described above, the spindle device 10 of the present embodiment displaces the contact positions (relative positions) of the first surface 20F and the second surface 22F as the centrifugal force generated when the shaft 12 rotates increases, as in the first embodiment. By doing so, the load amount of the load applied to the bearing 16 by the load applying portion 22 can be reduced. As a result, it is possible to suppress an increase in the preload when the shaft 12 rotates.

なお、本実施形態では、スペーサ４０の縦弾性係数が荷重付与部２２およびスリーブ２０の縦弾性係数よりも小さい場合、あるいは、スペーサ４０の密度が荷重付与部２２およびスリーブ２０の密度よりも小さい場合、スペーサ４０が広がるように変形し易くなる。したがって、スペーサ４０の縦弾性係数および密度の少なくとも一方が荷重付与部２２およびスリーブ２０よりも小さい場合には、シャフト１２の回転速度（遠心力）に応じた第１面２０Ｆおよび第２面２２Ｆの接触位置の変位量を大きくすることができる。 In the present embodiment, the longitudinal elastic modulus of the spacer 40 is smaller than the longitudinal elastic modulus of the load applying portion 22 and the sleeve 20, or the density of the spacer 40 is smaller than the density of the load applying portion 22 and the sleeve 20. , The spacer 40 is easily deformed so as to expand. Therefore, when at least one of the Young's modulus and the density of the spacer 40 is smaller than the load applying portion 22 and the sleeve 20, the first surface 20F and the second surface 22F according to the rotational speed (centrifugal force) of the shaft 12. The amount of displacement of the contact position can be increased.

〔本発明〕
上記の実施形態から把握し得る発明について、以下に記載する。 [Invention]
The inventions that can be grasped from the above embodiments are described below.

本発明は、シャフト（１２）と、シャフト（１２）が挿通されるハウジング（１４）と、シャフト（１２）をハウジング（１４）に対して回転可能に支持する軸受（１６）とを有する主軸装置（１０）である。主軸装置（１０）は、シャフト（１２）に取り付けられ、軸受（１６）にアキシアル方向の荷重を付与する荷重付与部（２２）と、軸受（１６）の内輪（３０）と、荷重付与部（２２）との間に配置されるスリーブ（２０）と、を備える。スリーブ（２０）における荷重付与部（２２）側の端面である第１面（２０Ｆ）と、荷重付与部（２２）におけるスリーブ（２０）側の端面である第２面（２２Ｆ）とは、シャフト（１２）に対して傾斜している。 The present invention is a spindle device having a shaft (12), a housing (14) through which the shaft (12) is inserted, and a bearing (16) that rotatably supports the shaft (12) with respect to the housing (14). (10). The spindle device (10) is attached to the shaft (12) and applies a load in the axial direction to the bearing (16), a load applying portion (22), an inner ring (30) of the bearing (16), and a load applying portion (16). A sleeve (20) arranged between the sleeve (22) and the sleeve (20) is provided. The first surface (20F), which is the end surface of the sleeve (20) on the side of the load applying portion (22), and the second surface (22F), which is the end surface of the load applying portion (22) on the sleeve (20) side, are shafts. It is inclined with respect to (12).

これにより、シャフト（１２）の回転時に生じる遠心力が大きくなるほど、第１面（２０Ｆ）および第２面（２２Ｆ）の接触位置（相対位置）が変位し、荷重付与部（２２）が軸受（１６）に付与する荷重の荷重量を下げることができる。この結果、シャフト（１２）が回転するときの予圧の上昇を抑制することができる。 As a result, as the centrifugal force generated when the shaft (12) rotates increases, the contact positions (relative positions) of the first surface (20F) and the second surface (22F) are displaced, and the load applying portion (22) becomes a bearing (22). The load amount of the load applied to 16) can be reduced. As a result, it is possible to suppress an increase in the preload when the shaft (12) rotates.

第１面（２０Ｆ）と第２面（２２Ｆ）とは、互いにシャフト（１２）から離れるほど軸受（１６）に近づくように傾斜し、接触してもよい。これにより、シャフト（１２）の回転時に働く遠心力に応じて、荷重付与部（２２）が外側に広がるように変形し、第１面（２０Ｆ）および第２面（２２Ｆ）の接触位置（相対位置）を変位させることができる。 The first surface (20F) and the second surface (22F) may be inclined and brought into contact with each other so as to be closer to the bearing (16) as the distance from the shaft (12) increases. As a result, the load-applying portion (22) is deformed so as to spread outward according to the centrifugal force acting during the rotation of the shaft (12), and the contact positions (relative) of the first surface (20F) and the second surface (22F). Position) can be displaced.

第１面（２０Ｆ）と第２面（２２Ｆ）とが互いにシャフト（１２）から離れるほど軸受（１６）に近づくように傾斜し、接触する場合、荷重付与部（２２）の縦弾性係数は、スリーブ（２０）の縦弾性係数よりも小さくてもよい。これにより、荷重付与部（２２）が変形し易くなり、シャフト（１２）の回転速度に応じた第１面（２０Ｆ）および第２面（２２Ｆ）の接触位置の変位量を大きくすることができる。 When the first surface (20F) and the second surface (22F) are inclined so as to be closer to the bearing (16) as they are farther from the shaft (12) and come into contact with each other, the Young's modulus of the load-applying portion (22) is determined. It may be smaller than the Young's modulus of the sleeve (20). As a result, the load applying portion (22) is easily deformed, and the displacement amount of the contact positions of the first surface (20F) and the second surface (22F) can be increased according to the rotation speed of the shaft (12). ..

第１面（２０Ｆ）と第２面（２２Ｆ）とが互いにシャフト（１２）から離れるほど軸受（１６）に近づくように傾斜し、接触する場合、荷重付与部（２２）の密度は、スリーブ（２０）の密度よりも小さくてもよい。これにより、荷重付与部（２２）が変形し易くなり、シャフト（１２）の回転速度に応じた第１面（２０Ｆ）および第２面（２２Ｆ）の接触位置の変位量を大きくすることができる。 When the first surface (20F) and the second surface (22F) are inclined so as to be closer to the bearing (16) as they are farther from the shaft (12) and come into contact with each other, the density of the load applying portion (22) is the sleeve (22F). It may be smaller than the density of 20). As a result, the load applying portion (22) is easily deformed, and the displacement amount of the contact positions of the first surface (20F) and the second surface (22F) can be increased according to the rotation speed of the shaft (12). ..

第１面（２０Ｆ）と第２面（２２Ｆ）とは、互いにシャフト（１２）から離れるほど軸受（１６）から遠ざかるように傾斜し、接触してもよい。シャフト（１２）の回転時に働く遠心力に応じて、スリーブ（２０）が外側に広がるように変形し、第１面（２０Ｆ）および第２面（２２Ｆ）の接触位置（相対位置）を変位させることができる。 The first surface (20F) and the second surface (22F) may be inclined and come into contact with each other so as to move away from the bearing (16) as the distance from the shaft (12) increases. The sleeve (20) is deformed so as to spread outward according to the centrifugal force acting during the rotation of the shaft (12), and the contact positions (relative positions) of the first surface (20F) and the second surface (22F) are displaced. be able to.

第１面（２０Ｆ）と第２面（２２Ｆ）とは、互いにシャフト（１２）から離れるほど軸受（１６）から遠ざかるように傾斜し、接触する場合、荷重付与部（２２）の縦弾性係数は、スリーブ（２０）の縦弾性係数よりも大きくてもよい。これにより、スリーブ（２０）が変形し易くなり、シャフト（１２）の回転速度に応じた第１面（２０Ｆ）および第２面（２２Ｆ）の接触位置の変位量を大きくすることができる。 When the first surface (20F) and the second surface (22F) are inclined so as to be farther from the bearing (16) as they are farther from the shaft (12) and come into contact with each other, the Young's modulus of the load-applying portion (22) is , May be larger than the Young's modulus of the sleeve (20). As a result, the sleeve (20) is easily deformed, and the displacement amount of the contact positions of the first surface (20F) and the second surface (22F) can be increased according to the rotation speed of the shaft (12).

第１面（２０Ｆ）と第２面（２２Ｆ）とは、互いにシャフト（１２）から離れるほど軸受（１６）から遠ざかるように傾斜し、接触する場合、荷重付与部（２２）の密度は、スリーブ（２０）の密度よりも大きくてもよい。これにより、スリーブ（２０）が変形し易くなり、シャフト（１２）の回転速度に応じた第１面（２０Ｆ）および第２面（２２Ｆ）の接触位置の変位量を大きくすることができる。 When the first surface (20F) and the second surface (22F) are inclined so as to be farther from the bearing (16) as they are farther from the shaft (12) and come into contact with each other, the density of the load applying portion (22) is the sleeve. It may be higher than the density of (20). As a result, the sleeve (20) is easily deformed, and the displacement amount of the contact positions of the first surface (20F) and the second surface (22F) can be increased according to the rotation speed of the shaft (12).

第１面（２０Ｆ）は、シャフト（１２）から離れるほど軸受（１６）に近づくように傾斜し、第２面（２２Ｆ）は、シャフト（１２）から離れるほど軸受（１６）から遠ざかるように傾斜し、主軸装置（１０）は、第１面（２０Ｆ）および第２面（２２Ｆ）に接触する接触面を有し、第１面（２０Ｆ）と第２面（２２Ｆ）との間に設けられるスペーサ（４０）を備えてもよい。これにより、シャフト（１２）の回転時に働く遠心力に応じて、スペーサ（４０）が外側に広がるように変形し、第１面（２０Ｆ）および第２面（２２Ｆ）の接触位置（相対位置）を変位させることができる。 The first surface (20F) is inclined so as to approach the bearing (16) as the distance from the shaft (12), and the second surface (22F) is inclined so as to move away from the bearing (16) as the distance from the shaft (12) increases. The spindle device (10) has contact surfaces that come into contact with the first surface (20F) and the second surface (22F), and is provided between the first surface (20F) and the second surface (22F). A spacer (40) may be provided. As a result, the spacer (40) is deformed so as to spread outward according to the centrifugal force acting during the rotation of the shaft (12), and the contact positions (relative positions) of the first surface (20F) and the second surface (22F). Can be displaced.

スペーサ（４０）の縦弾性係数は、荷重付与部（２２）およびスリーブ（２０）の縦弾性係数よりも小さくてもよい。これにより、スペーサ（４０）が変形し易くなり、シャフト（１２）の回転速度に応じた第１面（２０Ｆ）および第２面（２２Ｆ）の接触位置の変位量を大きくすることができる。 The Young's modulus of the spacer (40) may be smaller than the Young's modulus of the load-bearing portion (22) and the sleeve (20). As a result, the spacer (40) is easily deformed, and the amount of displacement of the contact positions of the first surface (20F) and the second surface (22F) can be increased according to the rotation speed of the shaft (12).

スペーサ（４０）の密度は、荷重付与部（２２）およびスリーブ（２０）の密度よりも小さくてもよい。これにより、スペーサ（４０）が変形し易くなり、シャフト（１２）の回転速度に応じた第１面（２０Ｆ）および第２面（２２Ｆ）の接触位置の変位量を大きくすることができる。 The density of the spacer (40) may be lower than the density of the load-bearing portion (22) and the sleeve (20). As a result, the spacer (40) is easily deformed, and the amount of displacement of the contact positions of the first surface (20F) and the second surface (22F) can be increased according to the rotation speed of the shaft (12).

軸受（１６）は、アンギュラ玉軸受であってもよい。また、主軸装置（１０）は、軸受（１６）を基準として荷重付与部（２２）側とは逆側に配置され、シャフト（１２）をハウジング（１４）に対して回転可能に支持する第２の軸受（１８）と、軸受（１６）の外輪（３２）と第２の軸受（１８）の外輪（３２）との間に配置される外輪間座（３８）と、を備えてもよい。 The bearing (16) may be an angular contact ball bearing. Further, the spindle device (10) is arranged on the side opposite to the load applying portion (22) side with reference to the bearing (16), and the shaft (12) is rotatably supported with respect to the housing (14). The bearing (18) and the outer ring spacer (38) arranged between the outer ring (32) of the bearing (16) and the outer ring (32) of the second bearing (18) may be provided.

１０…主軸装置 １２…シャフト
１４…ハウジング １６…軸受
１８…第２の軸受 ２０…スリーブ
２０Ｆ…第１面 ２２…荷重付与部
２２Ｆ…第２面 ３０…内輪
３２…外輪 ３４…転動体
３６…内輪間座 ３８…外輪間座
４０…スペーサ 10 ... Spindle device 12 ... Shaft 14 ... Housing 16 ... Bearing 18 ... Second bearing 20 ... Sleeve 20F ... First surface 22 ... Load applying part 22F ... Second surface 30 ... Inner ring 32 ... Outer ring 34 ... Rolling element 36 ... Inner ring Bearing 38 ... Outer ring bearing 40 ... Spacer

Claims (12)

シャフトと、前記シャフトが挿通されるハウジングと、前記シャフトを前記ハウジングに対して回転可能に支持する軸受とを有する主軸装置であって、
前記シャフトに取り付けられ、前記軸受にアキシアル方向の荷重を付与する荷重付与部と、
前記軸受の内輪と、前記荷重付与部との間に配置されるスリーブと、
を備え、
前記スリーブにおける前記荷重付与部側の端面である第１面と、前記荷重付与部における前記スリーブ側の端面である第２面とは、前記シャフトに対して傾斜している、主軸装置。 A spindle device having a shaft, a housing through which the shaft is inserted, and a bearing that rotatably supports the shaft with respect to the housing.
A load-applying portion that is attached to the shaft and applies a load in the axial direction to the bearing,
A sleeve arranged between the inner ring of the bearing and the load-bearing portion,
With
A spindle device in which a first surface of the sleeve, which is an end surface on the load-applying portion side, and a second surface, which is an end surface of the load-applying portion on the sleeve side, are inclined with respect to the shaft. 請求項１に記載の主軸装置であって、
前記第１面と前記第２面とは、互いに前記シャフトから離れるほど前記軸受に近づくように傾斜し、接触する、主軸装置。 The spindle device according to claim 1.
A spindle device in which the first surface and the second surface are inclined and come into contact with each other so as to approach the bearing as the distance from the shaft increases. 請求項２に記載の主軸装置であって、
前記荷重付与部の縦弾性係数は、前記スリーブの縦弾性係数よりも小さい、主軸装置。 The spindle device according to claim 2.
A spindle device in which the Young's modulus of the load-applying portion is smaller than the Young's modulus of the sleeve. 請求項２または３に記載の主軸装置であって、
前記荷重付与部の密度は、前記スリーブの密度よりも小さい、主軸装置。 The spindle device according to claim 2 or 3.
A spindle device in which the density of the load-applying portion is smaller than the density of the sleeve. 請求項１に記載の主軸装置であって、
前記第１面と前記第２面とは、互いに前記シャフトから離れるほど前記軸受から遠ざかるように傾斜し、接触する、主軸装置。 The spindle device according to claim 1.
A spindle device in which the first surface and the second surface are inclined and come into contact with each other so as to move away from the bearing as the distance from the shaft increases. 請求項５に記載の主軸装置であって、
前記荷重付与部の縦弾性係数は、前記スリーブの縦弾性係数よりも大きい、主軸装置。 The spindle device according to claim 5.
A spindle device in which the Young's modulus of the load-applying portion is larger than the Young's modulus of the sleeve. 請求項５または６に記載の主軸装置であって、
前記荷重付与部の密度は、前記スリーブの密度よりも大きい、主軸装置。 The spindle device according to claim 5 or 6.
A spindle device in which the density of the load-applying portion is higher than the density of the sleeve. 請求項１に記載の主軸装置であって、
前記第１面は、前記シャフトから離れるほど前記軸受に近づくように傾斜し、
前記第２面は、前記シャフトから離れるほど前記軸受から遠ざかるように傾斜し、
前記第１面および前記第２面に接触する接触面を有し、前記第１面と前記第２面との間に設けられるスペーサを備える、主軸装置。 The spindle device according to claim 1.
The first surface is inclined so as to be closer to the bearing as the distance from the shaft increases.
The second surface is inclined so as to move away from the bearing as the distance from the shaft increases.
A spindle device having a contact surface in contact with the first surface and the second surface, and provided with a spacer provided between the first surface and the second surface. 請求項８に記載の主軸装置であって、
前記スペーサの縦弾性係数は、前記荷重付与部および前記スリーブの縦弾性係数よりも小さい、主軸装置。 The spindle device according to claim 8.
A spindle device in which the Young's modulus of the spacer is smaller than the Young's modulus of the load-bearing portion and the sleeve. 請求項８または９に記載の主軸装置であって、
前記スペーサの密度は、前記荷重付与部および前記スリーブの密度よりも小さい、主軸装置。 The spindle device according to claim 8 or 9.
A spindle device in which the density of the spacer is smaller than the density of the load-applying portion and the sleeve. 請求項１〜１０のいずれか１項に記載の主軸装置であって、
前記軸受は、アンギュラ玉軸受である、主軸装置。 The spindle device according to any one of claims 1 to 10.
The bearing is a spindle device which is an angular contact ball bearing. 請求項１〜１１のいずれか１項に記載の主軸装置であって、
前記軸受を基準として前記荷重付与部側とは逆側に配置され、前記シャフトを前記ハウジングに対して回転可能に支持する第２の軸受と、
前記軸受の外輪と前記第２の軸受の外輪との間に配置される外輪間座と、
を備える、主軸装置。 The spindle device according to any one of claims 1 to 11.
A second bearing, which is arranged on the side opposite to the load applying portion side with the bearing as a reference and rotatably supports the shaft with respect to the housing.
An outer ring spacer arranged between the outer ring of the bearing and the outer ring of the second bearing,
A spindle device.
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115370658A (en) * 2022-10-24 2022-11-22 江苏比傲汽车科技有限公司 Stable firm automobile wheel hub bearing

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3317258A (en) * 1964-10-06 1967-05-02 Leblond Mach Tool Co R K Compensation for spindle creep due to bearing temperature
US3454313A (en) * 1967-06-02 1969-07-08 Kearney & Trecker Corp Force transmitting and compensating device
JPH0192005A (en) * 1987-10-02 1989-04-11 Nippon Seiko Kk Preload regulation spindle unit
JPH01135916A (en) * 1987-11-18 1989-05-29 Nippon Seiko Kk Preload adjustable type spindle unit
JP2002235740A (en) * 2001-02-13 2002-08-23 Koyo Seiko Co Ltd Bearing structure
WO2009049980A1 (en) * 2007-10-20 2009-04-23 Schaeffler Kg Compensation device for compensating thermally-related relative axial position changes between two components
JP2013170656A (en) * 2012-02-22 2013-09-02 Ntn Corp Preload adjustment structure and preload adjustment method of bearing device

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3317258A (en) * 1964-10-06 1967-05-02 Leblond Mach Tool Co R K Compensation for spindle creep due to bearing temperature
US3454313A (en) * 1967-06-02 1969-07-08 Kearney & Trecker Corp Force transmitting and compensating device
JPH0192005A (en) * 1987-10-02 1989-04-11 Nippon Seiko Kk Preload regulation spindle unit
JPH01135916A (en) * 1987-11-18 1989-05-29 Nippon Seiko Kk Preload adjustable type spindle unit
JP2002235740A (en) * 2001-02-13 2002-08-23 Koyo Seiko Co Ltd Bearing structure
WO2009049980A1 (en) * 2007-10-20 2009-04-23 Schaeffler Kg Compensation device for compensating thermally-related relative axial position changes between two components
JP2013170656A (en) * 2012-02-22 2013-09-02 Ntn Corp Preload adjustment structure and preload adjustment method of bearing device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115370658A (en) * 2022-10-24 2022-11-22 江苏比傲汽车科技有限公司 Stable firm automobile wheel hub bearing
CN115370658B (en) * 2022-10-24 2023-02-03 江苏比傲汽车科技有限公司 Stable firm automobile wheel hub bearing

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