JP2005249036A - Ball screw device - Google Patents

Ball screw device Download PDF

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Publication number
JP2005249036A
JP2005249036A JP2004058955A JP2004058955A JP2005249036A JP 2005249036 A JP2005249036 A JP 2005249036A JP 2004058955 A JP2004058955 A JP 2004058955A JP 2004058955 A JP2004058955 A JP 2004058955A JP 2005249036 A JP2005249036 A JP 2005249036A
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Japan
Prior art keywords
nut member
ball screw
axial direction
outer ring
eccentric
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JP2004058955A
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Japanese (ja)
Inventor
Masahiro Inoue
昌弘 井上
Norio Usuki
功雄 臼杵
Takanori Kurokawa
貴則 黒川
Hisayasu Murakami
久康 村上
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Koyo Seiko Co Ltd
Daihatsu Motor Co Ltd
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Koyo Seiko Co Ltd
Daihatsu Motor Co Ltd
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Priority to JP2004058955A priority Critical patent/JP2005249036A/en
Publication of JP2005249036A publication Critical patent/JP2005249036A/en
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  • Transmission Devices (AREA)
  • Injection Moulding Of Plastics Or The Like (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To manufacture a ball screw device 1 at lower cost in comparison with a current one by omitting a bracket used in the current one. <P>SOLUTION: A part 9c of a radial base part 9b of a gear 9 is fitted in a first eccentric recessed part 7 formed in the outer diameter surface of an outer ring member 33 of a rolling bearing 31, and a stepped part 12b of a nut member 13 is fitted in a second eccentric recessed part 8 formed in the outer diameter surface of the outer ring member 33 of the rolling member 31. With this simple structure, the three parts can be integrally rotated. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、ボールねじ装置に関する。   The present invention relates to a ball screw device.

従来のボールねじ装置には、ナット部材とねじ軸との間でトルクを推力に変換したり、推力をトルクに変換したりする構成を有するものがある（例えば特許文献１参照）。   Some conventional ball screw devices have a configuration in which torque is converted into thrust between a nut member and a screw shaft, or thrust is converted into torque (see, for example, Patent Document 1).

図５に示すように、このボールねじ装置５０は、筒状のナット部材５１と動力伝達用の樹脂歯車５２とがブラケット５３を介して一体に取付けられている。そして、樹脂歯車５２を軸心回りに回転させるとブラケット５３が軸心回りに回転し、ねじ軸５４に複数個のボール５５を介して組込まれている前記ナット部材５１が、ブラケット５３とともに軸心回りに回転する。また、ナット部材５１は、自らが軸心回りに回転する動作に伴なって軸方向に移動（伸縮動作）し、ナット部材５１の軸方向移動に伴なってブラケット５３および樹脂歯車５２も軸方向に移動する。
特開２００２−３２３１０８号（第３頁，第４頁，第２図） As shown in FIG. 5, the ball screw device 50 includes a cylindrical nut member 51 and a power transmission resin gear 52 that are integrally attached via a bracket 53. Then, when the resin gear 52 is rotated around the axis, the bracket 53 rotates around the axis, and the nut member 51 incorporated in the screw shaft 54 via the plurality of balls 55 becomes the axis along with the bracket 53. Rotate around. Further, the nut member 51 moves in the axial direction (extension / contraction operation) along with the rotation of the nut member 51 around the axis, and the bracket 53 and the resin gear 52 move in the axial direction as the nut member 51 moves in the axial direction. Move to.
JP 2002-323108 (Page 3, Page 4, Figure 2)

上記従来のボールねじ装置５０では、筒状のナット部材５１と動力伝達用の樹脂歯車５２とがブラケット５３を介して一体に取付けられている。このため、部品点数が多くなり、製造コストが高くなる傾向にある。   In the conventional ball screw device 50, a cylindrical nut member 51 and a power transmission resin gear 52 are integrally attached via a bracket 53. For this reason, the number of parts increases and the manufacturing cost tends to increase.

本発明のボールねじ装置は、径方向内外位置に配置されて軸方向に相対移動可能に設けられた筒状のナット部材およびねじ軸と、前記ナット部材の内周面およびねじ軸の外径面に形成されたねじ溝に転動自在に配置された複数個のボールとを備え、前記ナット部材の軸方向一方端部と、該ナット部材に駆動力を伝達するための駆動力伝達部材の径方向基端部とが、転がり軸受の外輪部材に軸方向に並べて外嵌して配置されている。   The ball screw device of the present invention includes a cylindrical nut member and a screw shaft that are disposed at radially inner and outer positions and are relatively movable in the axial direction, an inner peripheral surface of the nut member, and an outer diameter surface of the screw shaft. A plurality of balls disposed in a freely rotatable manner in a thread groove formed in the shaft, and one end portion in the axial direction of the nut member, and a diameter of the driving force transmitting member for transmitting the driving force to the nut member The direction base end portion is arranged so as to be externally fitted in the axial direction on the outer ring member of the rolling bearing.

上記構成のように、ナット部材の軸方向一方端部と、ナット部材に駆動力を伝達するための駆動力伝達部材の径方向基端部とを、転がり軸受の外輪部材に軸方向に並べて外嵌配置したことにより、従来用いていたブラケットが不要となるので、ボールねじ装置の製造コストを低減することができる。   As in the above configuration, one end of the nut member in the axial direction and the radial base end of the driving force transmitting member for transmitting the driving force to the nut member are arranged on the outer ring member of the rolling bearing in the axial direction. By fitting and arranging, a bracket that has been conventionally used is not necessary, and the manufacturing cost of the ball screw device can be reduced.

また、前記転がり軸受の外輪部材の外径面に、該転がり軸受の軸中心から偏心した環状の第一偏心凹部が形成され、前記駆動力伝達部材として樹脂製歯車が用いられ、該樹脂製歯車の形成用樹脂を前記第一偏心凹部に充填するよう該樹脂歯車が射出成形され、前記外輪部材の外径面の、前記第一偏心凹部に軸方向に離隔した位置に環状の第二偏心凹部が形成され、該第二偏心凹部に前記ナット部材の軸方向一方端部が嵌合されている。   Also, an annular first eccentric recess that is eccentric from the axial center of the rolling bearing is formed on the outer diameter surface of the outer ring member of the rolling bearing, and a resin gear is used as the driving force transmission member. The resin gear is injection-molded so as to fill the first eccentric recess with the forming resin, and an annular second eccentric recess is formed on the outer diameter surface of the outer ring member at a position axially spaced from the first eccentric recess. And one end of the nut member in the axial direction is fitted into the second eccentric recess.

上記構成のように転がり軸受の外輪部材の外周面に第一偏心凹部および第二偏心凹部を形成して、第一偏心凹部および第二偏心凹部のそれぞれに樹脂製歯車およびナット部材を嵌合した簡単な構成で、樹脂歯車、外輪部材およびナット部材が回転一体となる。   As described above, the first eccentric recess and the second eccentric recess are formed on the outer peripheral surface of the outer ring member of the rolling bearing, and the resin gear and the nut member are fitted to the first eccentric recess and the second eccentric recess, respectively. With a simple configuration, the resin gear, the outer ring member, and the nut member are integrally rotated.

本発明によれば、転がり軸受の外輪部材に駆動力伝達部材とナット部材とを直接組込んだことにより、ブラケットを省略して製造コストを低減することができる。   According to the present invention, since the driving force transmission member and the nut member are directly incorporated in the outer ring member of the rolling bearing, the manufacturing cost can be reduced by omitting the bracket.

以下、本発明の実施形態に係るボールねじ装置を図面に基づいて説明する。図１および図２は、本発明の実施形態を示すボールねじ装置の使用状態を示す全体断面図、図３は分解斜視図、図４は転がり軸受の単体正面図である。   Hereinafter, a ball screw device according to an embodiment of the present invention will be described with reference to the drawings. 1 and 2 are overall sectional views showing a use state of a ball screw device showing an embodiment of the present invention, FIG. 3 is an exploded perspective view, and FIG. 4 is a single front view of a rolling bearing.

図１に示すように、本発明の実施の形態におけるボールねじ装置１は、軸方向に対で設けた第一，第二フランジ５，６を有するプーリ２における前記第一，第二フランジ５，６間の軸方向離隔距離を変更することで、プーリ２に巻掛られるベルト３の巻掛径を変更するために用いられる。   As shown in FIG. 1, the ball screw device 1 according to the embodiment of the present invention includes the first and second flanges 5 and 5 in a pulley 2 having first and second flanges 5 and 6 provided in pairs in the axial direction. It is used to change the winding diameter of the belt 3 wound around the pulley 2 by changing the axial separation distance between the pulleys 6.

プーリ２は、回転軸４に軸心回りに回転一体に設けられる前記第一フランジ５と、回転軸４に軸心回りに回転一体かつ軸方向に沿って摺動自在に配置される前記第二フランジ６とを備える。   The pulley 2 is provided on the rotary shaft 4 so as to rotate integrally around the axis thereof, and the second flange is arranged on the rotary shaft 4 so as to rotate integrally around the axis and slidable along the axial direction. And a flange 6.

本発明の実施の形態におけるボールねじ装置１は、駆動力伝達部材としての樹脂製歯車（以下単に「歯車」という）９、転がり軸受３０，３１およびボールねじ１２を有する。ボールねじ１２と両転がり軸受３０，３１とは同心に配置されており、特にボールねじ１２と転がり軸受３１とは、軸方向一方側および軸方向他方側に並べて配置されている。歯車９の外周歯部９ａには、不図示の回転動力源から駆動力が伝達されて回転する減速歯車１０の歯部１０ａが噛合されている。   The ball screw device 1 according to the embodiment of the present invention includes a resin gear (hereinafter simply referred to as “gear”) 9, rolling bearings 30 and 31, and a ball screw 12 as driving force transmission members. The ball screw 12 and the two rolling bearings 30 and 31 are arranged concentrically. In particular, the ball screw 12 and the rolling bearing 31 are arranged side by side on the one axial side and the other axial side. The outer peripheral tooth portion 9a of the gear 9 is meshed with the tooth portion 10a of the reduction gear 10 that is rotated by a driving force transmitted from a rotational power source (not shown).

ボールねじ１２は、円筒状のナット部材１３を有し、このナット部材１３の内周面に、両端部間で連続した所定のリード角を有する一条のねじ溝１５が形成されている。   The ball screw 12 includes a cylindrical nut member 13, and a single thread groove 15 having a predetermined lead angle continuous between both ends is formed on the inner peripheral surface of the nut member 13.

ボールねじ１２は、ナット部材１３の内径側に配置されて中心穴１６を有する円筒状のねじ軸１７を有する。このねじ軸１７は、図示しない所定の支持装置でもって軸心回りに非回転に支持されるとともに、軸方向に不動に支持されている。このねじ軸１７は、外周面に、互いに平行でそれぞれ独立の閉ループとした所定のリード角を有する３条のねじ溝１８を有する。この構成により、ねじ溝１８に嵌合するボール群２０（ボール２０ａ）をそれぞれ独立して転動循環させる構成となっている。   The ball screw 12 has a cylindrical screw shaft 17 disposed on the inner diameter side of the nut member 13 and having a center hole 16. The screw shaft 17 is non-rotatably supported around a shaft center by a predetermined support device (not shown) and is supported immovably in the axial direction. The threaded shaft 17 has three threaded grooves 18 on the outer peripheral surface having a predetermined lead angle that are mutually parallel and independent closed loops. With this configuration, the ball group 20 (ball 20a) fitted in the screw groove 18 is configured to circulate and circulate independently.

さらに具体的には、図３に示すように、各ねじ溝１８は、所定のリード角を有するねじ溝１８の端部どうしをリード角と異なる角度をもって連続させるボール循環溝２２を有し、このボール循環溝２２によって各ねじ溝１８は別個に閉ループとされる。   More specifically, as shown in FIG. 3, each screw groove 18 has a ball circulation groove 22 that makes the end portions of the screw groove 18 having a predetermined lead angle continuous with each other at an angle different from the lead angle. Each thread groove 18 is individually closed loop by the ball circulation groove 22.

これらボール循環溝２２は、それぞれのねじ溝１８の上流側と下流側とを連通する部分である。すなわち、これらボール循環溝２２は、各ねじ溝１８の下流側に位置するボール２０ａをねじ軸１８の内径側に沈みこませて上流へ戻すよう、ねじ溝１８の他の部分に比べて深く形成されるとともに蛇行した形状に形成されている。   These ball circulation grooves 22 are portions that communicate the upstream side and the downstream side of each screw groove 18. That is, these ball circulation grooves 22 are formed deeper than the other portions of the screw grooves 18 so that the balls 20a located on the downstream side of the screw grooves 18 are submerged on the inner diameter side of the screw shaft 18 and returned upstream. And is formed in a meandering shape.

ここでボールねじ１２の構成を詳細に説明する。このボールねじ１２は、ねじ溝１５，１８の間に転動自在に配置される３列の前記ボール群２０と、これら３列の各ボール群２０をそれぞれ円周方向等配位置に保持する保持器リング２３とを備える。この保持器リング２３は、軸方向に沿うポケット２３ａが円周方向等配位置に形成されている。これら各ポケット２３ａに各ボール群２０のボール２０ａが１個ずつ計３個配置されている。保持器リング２３は、ねじ軸１７に遊嵌されている。   Here, the configuration of the ball screw 12 will be described in detail. The ball screw 12 includes three rows of the ball groups 20 that are rotatably arranged between the screw grooves 15 and 18, and holding the ball groups 20 in the three rows at equal circumferential positions. Instrument ring 23. In this cage ring 23, pockets 23a along the axial direction are formed at equidistant positions in the circumferential direction. A total of three balls 20a of each ball group 20 are arranged in each of these pockets 23a. The cage ring 23 is loosely fitted on the screw shaft 17.

ねじ軸１７の軸方向一方側の縮径部２４に形成された周溝２５に止め輪２６が嵌合され、保持器リング２３の一端に、ねじ軸１７の外周部一側に形成された縮径部２４における段付壁２７に係合するフランジ２８が形成され、このフランジ２８が、止め輪２６と段付壁２７との間で軸方向にわずかな遊びを有する状態とされている。   A retaining ring 26 is fitted in a circumferential groove 25 formed in the reduced diameter portion 24 on one axial side of the screw shaft 17, and a reduction formed in one end of the retainer ring 23 on one side of the outer peripheral portion of the screw shaft 17. A flange 28 that engages a stepped wall 27 in the diameter portion 24 is formed, and this flange 28 has a slight play between the retaining ring 26 and the stepped wall 27 in the axial direction.

ねじ軸１７の内周面途中に環状の補強部２９が形成され、この補強部２９の内周面一方側で、かつねじ軸１７の縮径部２４に対向する内方部位に、前記転がり軸受３０が嵌着されている。   An annular reinforcing portion 29 is formed in the middle of the inner peripheral surface of the screw shaft 17, and the rolling bearing is provided on one side of the inner peripheral surface of the reinforcing portion 29 and on an inner portion facing the reduced diameter portion 24 of the screw shaft 17. 30 is fitted.

この転がり軸受３０としてアンギュラ玉軸受が用いられる。この転がり軸受３０は、ねじ軸１７に嵌着された外輪部材３２と、前記回転軸４の途中が挿通する内輪部材３４と、外輪部材３２と内輪部材３４との間に内外軌道面を転動自在に配置された複数個の玉３６とを備える。   An angular ball bearing is used as the rolling bearing 30. This rolling bearing 30 rolls on the inner and outer raceway surfaces between an outer ring member 32 fitted to the screw shaft 17, an inner ring member 34 through which the rotary shaft 4 is inserted, and between the outer ring member 32 and the inner ring member 34. A plurality of balls 36 arranged freely.

次に、転がり軸受３１の構成を詳細に説明する。転がり軸受３１として、アンギュラ玉軸受が用いられている。転がり軸受３１は、外輪部材３３と、内輪部材３５と、外輪部材３３および内輪部材３５の間に内外軌道面を転動自在に配置された複数個の玉３７とを備える。内輪部材３５は、前記第二フランジ６に一体形成された筒軸３８の外周面に嵌着される。   Next, the configuration of the rolling bearing 31 will be described in detail. An angular ball bearing is used as the rolling bearing 31. The rolling bearing 31 includes an outer ring member 33, an inner ring member 35, and a plurality of balls 37 that are arranged between the outer ring member 33 and the inner ring member 35 so that the inner and outer raceway surfaces can roll freely. The inner ring member 35 is fitted on the outer peripheral surface of a cylindrical shaft 38 that is integrally formed with the second flange 6.

図４に示すように、転がり軸受３１の外輪部材３３の外径面軸方向途中に、転がり軸受３１の軸中心Ｐ１から偏心して中心Ｐ２を有する環状の第一偏心凹部７が形成されている。   As shown in FIG. 4, in the middle of the outer ring member 33 of the rolling bearing 31 in the axial direction of the outer diameter surface, an annular first eccentric recess 7 having a center P2 that is eccentric from the axial center P1 of the rolling bearing 31 is formed.

外輪部材３３の外径面の、第一偏心凹部７に軸方向他方側に離隔した端部位置に、環状の第二偏心凹部８が第一偏心凹部７に並べて形成されている。第一偏心凹部７と第二偏心凹部８とは、共通の中心Ｐ２を有する。   An annular second eccentric concave portion 8 is formed side by side on the first eccentric concave portion 7 at an end position on the outer diameter surface of the outer ring member 33 that is spaced apart from the first eccentric concave portion 7 in the other axial direction. The first eccentric recess 7 and the second eccentric recess 8 have a common center P2.

歯車９の径方向基部９ｂの一部９ｃが、歯車９の形成用樹脂が第一偏心凹部７に充填されるように歯車９が射出成形され、これにより外輪部材３３と歯車９とが一体化されている。従って、歯車９の径方向基部９ｂの一部９ｃは、第一偏心凹部７と相対形状となっている。   The gear 9 is injection-molded so that a part 9c of the radial base 9b of the gear 9 is filled with the resin for forming the gear 9 into the first eccentric recess 7, whereby the outer ring member 33 and the gear 9 are integrated. Has been. Accordingly, a part 9 c of the radial base portion 9 b of the gear 9 has a shape relative to the first eccentric recess 7.

前記ナット部材１２の軸方向一方側端部は、他の部分に比べて薄肉に形成されて外輪部材３３の一部を覆う被覆部１２ａとされる。この被覆部１２ａの軸方向他方側に連続する段付部１２ｂが第二偏心凹部８と相対形状に形成され、ナット部材１２の段付部１２ｂが第二偏心凹部８に嵌合している。   One end portion in the axial direction of the nut member 12 is formed as a covering portion 12 a that is thinner than the other portion and covers a part of the outer ring member 33. A stepped portion 12 b continuous to the other axial side of the covering portion 12 a is formed in a shape that is relative to the second eccentric recessed portion 8, and the stepped portion 12 b of the nut member 12 is fitted into the second eccentric recessed portion 8.

被覆部１２ａの軸方向一方側端面は、歯車９の径方向基部９ｂの軸方向他方側面に当接している。この構成により、ナット部材１２の軸方向一方端部と、歯車９の径方向基端部９ｂとが、転がり軸受３１の外輪部材３３に軸方向に並べて配置されている。   One end surface in the axial direction of the covering portion 12 a is in contact with the other side surface in the axial direction of the radial base portion 9 b of the gear 9. With this configuration, the one axial end of the nut member 12 and the radial base end 9 b of the gear 9 are arranged side by side in the axial direction on the outer ring member 33 of the rolling bearing 31.

上記構成のボールねじ装置１において、図１に示す状態はボールねじ１２が最も縮んだ状態で、図２に示す状態はボールねじ１２が最も伸びた状態である。すなわち、図１に示す状態では、ベルト３の巻掛径が小さくなっており、図２に示す状態は、ベルト３の巻掛径が大きくなった状態である。   In the ball screw device 1 configured as described above, the state shown in FIG. 1 is the state in which the ball screw 12 is most contracted, and the state shown in FIG. 2 is the state in which the ball screw 12 is most extended. That is, in the state shown in FIG. 1, the winding diameter of the belt 3 is small, and in the state shown in FIG. 2, the winding diameter of the belt 3 is large.

図１で示したボールねじ１２が最も縮んだ状態から、減速歯車１０が軸心回りに回転して歯部１０ａが回転すると、減速歯車１０の回転とともに歯車９が軸心回りに回転する。   When the reduction gear 10 rotates around the axis from the state where the ball screw 12 shown in FIG. 1 is most contracted and the tooth portion 10a rotates, the gear 9 rotates around the axis as the reduction gear 10 rotates.

そうすると、この歯車９の回転に伴なって、第一偏心凹部７に径方向基部９ｂの一部９ｃが嵌合するようにして歯車９に一体化されている転がり軸受３１の外輪部材３３が軸心回りに回転する。   Then, along with the rotation of the gear 9, the outer ring member 33 of the rolling bearing 31 integrated with the gear 9 so that the portion 9c of the radial base 9b is fitted into the first eccentric recess 7 is pivoted. Rotate around the heart.

また、外輪部材３３が軸心回りに回転すると、この外輪部材３３の第二偏心凹部８に段付部１２ｂが嵌合しているナット部材１３がねじ軸１７の回りを軸心回りに回転する。ところで、ナット部材１３が軸心回りに回転すると、ナット部材１３およびねじ軸１７のねじ溝１５，１８の間に配置された３列のボール群２０が、ねじ溝１５，１８に沿って転動し、ナット部材１３は回転しながら軸方向（図１の左方）に移動する。   Further, when the outer ring member 33 rotates around the axis, the nut member 13 in which the stepped portion 12b is fitted in the second eccentric recess 8 of the outer ring member 33 rotates around the screw shaft 17 around the axis. . By the way, when the nut member 13 rotates about the axis, the three rows of ball groups 20 arranged between the nut member 13 and the screw grooves 15 and 18 of the screw shaft 17 roll along the screw grooves 15 and 18. The nut member 13 moves in the axial direction (left side in FIG. 1) while rotating.

なお、３列のボール群２０を構成するボール２０ａは、それぞれボール循環溝２２に至り、ねじ溝１８を循環する。ナット部材１３が軸方向に移動すると、これに伴なって転がり軸受３１、外輪部材３３に一体の歯車９も軸方向に移動し、第二フランジ６が軸方向に移動する。   The balls 20 a constituting the three rows of ball groups 20 reach the ball circulation grooves 22 and circulate through the screw grooves 18. When the nut member 13 moves in the axial direction, the gear 9 integrated with the rolling bearing 31 and the outer ring member 33 also moves in the axial direction, and the second flange 6 moves in the axial direction.

第二フランジ６が軸方向に移動すると、回転しているベルト３が第一フランジ５、第二フランジ６どうしの対向斜面からの押圧力によって、フランジ５，６間を拡径するようにせり上がり、ベルト３の巻掛径が大きくなる。そして、図２に示すように、第一フランジ５および第二フランジ６の径方向内方部位どうしが軸方向で当接した時点で、ナット部材１３は軸方向の移動を停止する。   When the second flange 6 moves in the axial direction, the rotating belt 3 rises so as to increase the diameter between the flanges 5 and 6 by the pressing force from the opposed inclined surfaces of the first flange 5 and the second flange 6. The winding diameter of the belt 3 is increased. As shown in FIG. 2, the nut member 13 stops moving in the axial direction when the radially inner portions of the first flange 5 and the second flange 6 contact each other in the axial direction.

再びベルト３の巻掛径を小さくする場合は、上記と反対方向の回転力を減速歯車１０から歯車９に対して付与することで、ボールねじ１２のナット部材１３は軸方向（図２の右方）に移動し、図１のように保持器リング２３の端面が転がり軸受３１の外輪部材３３の端面に当接した時点で、ナット部材１３は軸方向の移動を停止する。   When the winding diameter of the belt 3 is reduced again, the nut member 13 of the ball screw 12 is axially moved (rightward in FIG. 2) by applying a rotational force in the opposite direction to the gear 9 from the reduction gear 10. When the end surface of the cage ring 23 comes into contact with the end surface of the outer ring member 33 of the rolling bearing 31 as shown in FIG. 1, the nut member 13 stops moving in the axial direction.

ところで、本発明の実施の形態では、従来設けていたブラケットを用いていない。すなわち、転がり軸受３１の外輪部材３３の外径面に形成した第一偏心凹部７に、径方向基部９ｂの一部９ｃが嵌合するようにして歯車９が一体化され、転がり軸受３１の外輪部材３３の外径面に形成した第二偏心凹部８に段付部１２ｂが嵌合するようにしてナット部材１３が一体的に回転するようにしている。   By the way, in the embodiment of the present invention, the bracket provided conventionally is not used. That is, the gear 9 is integrated with the first eccentric recess 7 formed on the outer diameter surface of the outer ring member 33 of the rolling bearing 31 so that a part 9c of the radial base 9b is fitted, and the outer ring of the rolling bearing 31 is integrated. The nut member 13 is rotated integrally so that the stepped portion 12b is fitted into the second eccentric recess 8 formed on the outer diameter surface of the member 33.

このように、従来用いていたブラケットを省略し、転がり軸受３１の外輪部材３３に第一偏心凹部７および第二偏心凹部８を形成し、各偏心凹部７，８に歯車９およびナット部材１３の一部を嵌合するといった簡単な構成で、外輪部材３３、歯車９およびナット部材１３を軸心回りに回転一体としたので、ボールねじ装置１を従来に比べて低コストで製造することが可能となる。   Thus, the bracket used conventionally is abbreviate | omitted, the 1st eccentric recessed part 7 and the 2nd eccentric recessed part 8 are formed in the outer ring member 33 of the rolling bearing 31, and the gearwheel 9 and the nut member 13 of each eccentric recessed part 7 and 8 are formed. Since the outer ring member 33, the gear 9 and the nut member 13 are integrally rotated around the shaft center with a simple configuration such that a part of them is fitted, the ball screw device 1 can be manufactured at a lower cost than the conventional one. It becomes.

また、転がり軸受３１の外輪部材３３を、第一偏心凹部７および第二偏心凹部８を形成するだけで、外輪部材３３にブラケットの機能を有せしめたので、ブラケットを用いた場合に比べて剛性が高く、このため、ねじ軸１７に対するナット部材１３の軸方向の移動を、正確かつ確実に行い得る。   Further, since the outer ring member 33 of the rolling bearing 31 is provided with the function of a bracket only by forming the first eccentric recess 7 and the second eccentric recess 8, the outer ring member 33 is more rigid than the case where the bracket is used. Therefore, the axial movement of the nut member 13 relative to the screw shaft 17 can be performed accurately and reliably.

さらに、本発明の実施の形態のボールねじ装置１において、ボールねじ１２と転がり軸受３１とは、軸方向一方側および軸方向他方側に並べて配置した構成を有する。このため、従来プーリ側の転がり軸受をボールねじの内径側に配置したボールねじ装置に比べて、その分だけボールねじ（ボールねじ装置）の径を小さくすることができる。   Furthermore, in the ball screw device 1 according to the embodiment of the present invention, the ball screw 12 and the rolling bearing 31 are arranged side by side on the one axial side and the other axial side. For this reason, the diameter of the ball screw (ball screw device) can be reduced by that amount as compared with the conventional ball screw device in which the pulley-side rolling bearing is arranged on the inner diameter side of the ball screw.

そして本発明の実施の形態のように、ボールねじ１２の径を小さくすることによりリード角を従来品に比べて大きくすることができる。そしてリード角を大きくすることができたことによって、ボールねじ１２の効率を向上させることができ、ナット部材１３の回転角度に対応するナット部材１３の軸方向への移動量を、従来に比べて大きくすることができる。   Then, as in the embodiment of the present invention, the lead angle can be increased compared to the conventional product by reducing the diameter of the ball screw 12. Since the lead angle can be increased, the efficiency of the ball screw 12 can be improved, and the amount of movement of the nut member 13 in the axial direction corresponding to the rotation angle of the nut member 13 can be increased as compared with the related art. Can be bigger.

なお、転がり軸受３１の外輪部材３３、歯車９およびナット部材１３を回転一体とするために、外輪部材３３に第一偏心凹部７および第二偏心凹部８を形成し、各偏心凹部７，８に歯車９およびナット部材１３の一部を嵌合するといった技術を用いたがこれに限定されるものではない。   In order to integrally rotate the outer ring member 33, the gear 9 and the nut member 13 of the rolling bearing 31, the first eccentric recess 7 and the second eccentric recess 8 are formed in the outer ring member 33. Although the technique of fitting part of the gear 9 and the nut member 13 is used, the present invention is not limited to this.

例えば歯車９では、外輪部材３３の外周面に凹凸を形成して、この凹凸部分に樹脂を射出成形することで、歯車９を回転一体に組付けることも可能であるし、ナット部材１３は、外輪部材３３にボルトなどの固定手段を用いて回転一体に組付けるようにしてもよい。この場合も、ブラケットを用いる場合に比べて製造コストを低減することができる。   For example, in the gear 9, it is possible to assemble the gear 9 integrally by rotating the outer ring member 33 by forming irregularities on the outer peripheral surface and injection-molding resin on the irregular portions. You may make it assemble | attach to the outer ring member 33 integrally with rotation using fixing means, such as a volt | bolt. Also in this case, the manufacturing cost can be reduced as compared with the case where the bracket is used.

本発明の実施形態を示すボールねじ装置の使用状態を示す全体断面図である。It is a whole sectional view showing the use state of the ball screw device showing the embodiment of the present invention. 同じくボールねじ装置の使用状態を示す全体断面図である。It is a whole sectional view showing the use condition of a ball screw device similarly. 同じく分解斜視図である。It is an exploded perspective view similarly. 同じく転がり軸受の単体正面図である。It is the single-piece | unit front view of a rolling bearing similarly. 従来のボールねじ装置の全体断面図である。It is a whole sectional view of the conventional ball screw device.

符号の説明Explanation of symbols

１ ボールねじ装置
７ 第一偏心凹部
８ 第二偏心凹部
９ 歯車
９ｂ 径方向基部
１２ ボールねじ
１２ａ 被覆部
１３ ナット部材
１５ ねじ溝
１７ ねじ軸
１８ ねじ溝
２０ ボール群
２２ ボール循環溝
２３ 保持器リング
３０ 転がり軸受
３１ 転がり軸受
３３ 外輪部材 DESCRIPTION OF SYMBOLS 1 Ball screw apparatus 7 1st eccentric recessed part 8 2nd eccentric recessed part 9 Gear 9b Radial direction base 12 Ball screw 12a Covering part 13 Nut member 15 Screw groove 17 Screw shaft 18 Screw groove 20 Ball group 22 Ball circulation groove 23 Cage ring 30 Rolling bearing 31 Rolling bearing 33 Outer ring member

Claims (2)

径方向内外位置に配置されて軸方向に相対移動可能に設けられた筒状のナット部材およびねじ軸と、前記ナット部材の内周面およびねじ軸の外径面に形成されたねじ溝に転動自在に配置された複数個のボールとを備え、
前記ナット部材の軸方向一方端部と、該ナット部材に駆動力を伝達するための駆動力伝達部材の径方向基端部とが、転がり軸受の外輪部材に軸方向に並べて外嵌して配置された、ことを特徴とするボールねじ装置。 A cylindrical nut member and a screw shaft which are disposed at radially inner and outer positions and are relatively movable in the axial direction, and are transferred to screw grooves formed on the inner peripheral surface of the nut member and the outer diameter surface of the screw shaft. With a plurality of freely arranged balls,
One end of the nut member in the axial direction and the radial base end of the driving force transmitting member for transmitting the driving force to the nut member are arranged so as to be fitted in the axial direction on the outer ring member of the rolling bearing. A ball screw device characterized by that. 請求項１記載のボールねじ装置において、
前記転がり軸受の外輪部材の外径面に、該転がり軸受の軸中心から偏心した環状の第一偏心凹部が形成され、
前記駆動力伝達部材として樹脂製歯車が用いられ、該樹脂製歯車の形成用樹脂を前記第一偏心凹部に充填するよう該樹脂歯車が射出成形され、
前記外輪部材の外径面の、前記第一偏心凹部に軸方向に離隔した位置に環状の第二偏心凹部が形成され、該第二偏心凹部に前記ナット部材の軸方向一方端部が嵌合された、ことを特徴とするボールねじ装置。 The ball screw device according to claim 1, wherein
An annular first eccentric concave portion that is eccentric from the axial center of the rolling bearing is formed on the outer diameter surface of the outer ring member of the rolling bearing,
A resin gear is used as the driving force transmission member, and the resin gear is injection-molded so as to fill the first eccentric recess with resin for forming the resin gear,
An annular second eccentric recess is formed at an axially spaced position in the first eccentric recess on the outer diameter surface of the outer ring member, and one end of the nut member in the axial direction is fitted into the second eccentric recess. A ball screw device characterized by that.
JP2004058955A 2004-03-03 2004-03-03 Ball screw device Withdrawn JP2005249036A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2004058955A JP2005249036A (en) 2004-03-03 2004-03-03 Ball screw device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004058955A JP2005249036A (en) 2004-03-03 2004-03-03 Ball screw device

Publications (1)

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Family Applications (1)

Application Number Title Priority Date Filing Date
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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008050862A1 (en) * 2006-10-27 2008-05-02 Jtekt Corporation Electric power steering device
JP2012132555A (en) * 2010-11-30 2012-07-12 Nsk Ltd Ball screw
KR101739197B1 (en) 2015-10-07 2017-05-23 주식회사 만도 Hybrid alternator pulley assembly
US9737926B2 (en) 2010-03-17 2017-08-22 Nsk Ltd. Ball screw and manufacturing method of nut for ball screw

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008050862A1 (en) * 2006-10-27 2008-05-02 Jtekt Corporation Electric power steering device
JP2008105649A (en) * 2006-10-27 2008-05-08 Jtekt Corp Electric power steering device
US8042645B2 (en) 2006-10-27 2011-10-25 Jtekt Corporation Electric power steering device
US9737926B2 (en) 2010-03-17 2017-08-22 Nsk Ltd. Ball screw and manufacturing method of nut for ball screw
JP2012132555A (en) * 2010-11-30 2012-07-12 Nsk Ltd Ball screw
KR101739197B1 (en) 2015-10-07 2017-05-23 주식회사 만도 Hybrid alternator pulley assembly

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