JPH04203649A - Roller screw - Google Patents
Roller screwInfo
- Publication number
- JPH04203649A JPH04203649A JP33080190A JP33080190A JPH04203649A JP H04203649 A JPH04203649 A JP H04203649A JP 33080190 A JP33080190 A JP 33080190A JP 33080190 A JP33080190 A JP 33080190A JP H04203649 A JPH04203649 A JP H04203649A
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- roller
- circumferential surface
- outer circumferential
- cylindrical member
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000005096 rolling process Methods 0.000 claims abstract description 24
- 230000036316 preload Effects 0.000 claims description 14
- 230000002093 peripheral effect Effects 0.000 claims description 12
- 230000001141 propulsive effect Effects 0.000 abstract description 2
- 230000005489 elastic deformation Effects 0.000 description 3
- 239000004519 grease Substances 0.000 description 3
- 238000007789 sealing Methods 0.000 description 2
- 230000004323 axial length Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
Landscapes
- Transmission Devices (AREA)
Abstract
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明は、ローラーを用いて回転運動と直線運動とを相
互に変換することが可能なローラースクリューに関する
。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a roller screw capable of mutually converting rotational motion and linear motion using rollers.
［従来の技術１
従来、産業用機械等の分野においては、回転運動と直線
運動とを相互に変換する装置としてボールスクリューが
一般に多用されている。[Prior Art 1] Conventionally, in the field of industrial machinery and the like, ball screws have generally been widely used as devices for mutually converting rotational motion and linear motion.
このボールスクリューは、所定のリード角を有する螺旋
状の転走溝が刻設されたスクリューシャフトと、上記転
走溝と相俟ってポールを挟み込む螺旋状の負荷転走溝及
びこの負荷転走溝の一端から他端へボールが循環するボ
ールリターン通路を備えたナンドとから構成されており
、例えば、シャフトあるいはナンドのいずれか一方に回
転運動を与えることにより、他方がら直線運動を導き出
すことができる。This ball screw consists of a screw shaft in which a spiral rolling groove with a predetermined lead angle is carved, a spiral load rolling groove that, together with the rolling groove, holds the pole, and It consists of a NAND with a ball return passage through which the balls circulate from one end of the groove to the other. For example, by applying rotational motion to either the shaft or the NAND, linear motion can be derived from the other. can.
しかし、このような構成の基に多用されているボールス
クリューは以下に示すような幾つかの問題点を有してい
る。However, the ball screw which is frequently used based on such a structure has several problems as shown below.
■ポールは断面略半円形状の転走溝及び負荷転走溝の内
部を面接触しながら転走するため、回転軸心を中心とす
るボールの外側接触直径と内側接触直径との間には差が
生じ、ボールの自転には上記多溝との間の滑りが必ず伴
なうので、動作時の発熱量が大きい。■Since the pole rolls in surface contact inside the rolling groove and the load rolling groove, which have a roughly semicircular cross section, there is a gap between the outer contact diameter and the inner contact diameter of the ball around the rotation axis. A difference occurs, and since the rotation of the ball is always accompanied by slippage between the balls and the multi-grooves, the amount of heat generated during operation is large.
■リターン通路によってボールを無限循環させているの
で、シャフトの転走溝からリターン通路へボールを掬い
上げる際に衝突音が発生し、又、リターン通路内でボー
ル同志が接触することから高い騒音を発生する。■Since the balls are endlessly circulated through the return passage, collision noise is generated when the balls are scooped up from the rolling groove of the shaft to the return passage, and high noise is generated as the balls come into contact with each other in the return passage. Occur.
この様なボールスクリューの問題点に鑑み、近年におい
ては上記欠点を補填する直線運動・回転運動の変換装置
として、実開平１−１１３６５６号に示される送り装置
が提案されている。In view of these problems with ball screws, in recent years, a feeding device shown in Japanese Utility Model Application Publication No. 1-113656 has been proposed as a linear motion/rotary motion conversion device that compensates for the above-mentioned drawbacks.
具体的には、所定のリード角に合致して傾いた姿勢のロ
ーラー複数個を円筒状シャフトの外周面に配すると共に
、これらローラーをシャフト外周面とナツト内周面との
間に挟み込んだものであり、ローラーがシャフト外周面
を公転する際に生じる軸方向の力を利用してナツトある
いはシャフトを軸方向に駆動する仕組みとなっている。Specifically, a plurality of rollers tilted in accordance with a predetermined lead angle are arranged on the outer circumferential surface of a cylindrical shaft, and these rollers are sandwiched between the outer circumferential surface of the shaft and the inner circumferential surface of the nut. The mechanism is such that the nut or shaft is driven in the axial direction by using the axial force generated when the rollers revolve around the shaft's outer peripheral surface.
この装置（以下、ローラースクリュー）によれば、ロー
ラーはナツト内周面を円周方向に沿って転走するので、
ボールスクリューのように転動体を無限循環させるため
のリターン通路をナンドに設ける必要がなく、非常に静
粛な動作をなし得る他、ローラーの自転はシャフト外周
面とナツト内周面に対する滑りを伴なわないので、動作
時の発熱を最小限に押さえられる。According to this device (hereinafter referred to as a roller screw), the rollers roll along the inner peripheral surface of the nut in the circumferential direction, so
Unlike a ball screw, there is no need to provide a return path in the NAND to circulate the rolling elements endlessly, and the rollers can operate very quietly, and the rotation of the rollers is accompanied by sliding on the shaft outer circumferential surface and the nut inner circumferential surface. Since there is no heat generated during operation, heat generation can be kept to a minimum.
［発明が解決しようとする課題］
ところで、このローラースクリューにおいては、ローラ
ーとシャフト外周面との間に生じる摩擦力がナツトある
いはシャフトの軸方向推力に利用されているため、当該
摩擦力をより大きく設定することができれば、ローラー
数を減じて装置の小型化が図れるといった面で好ましい
。[Problems to be Solved by the Invention] By the way, in this roller screw, the frictional force generated between the roller and the outer peripheral surface of the shaft is used for the axial thrust of the nut or the shaft, so it is difficult to increase the frictional force. If it can be set, it is preferable because the number of rollers can be reduced and the device can be made more compact.
しかしながら、従来のローラースクリューにあっては、
カムフォロア等のローラーベアリングに用いられている
円筒状ローラーを流用しているに過ぎないので、上述の
ように所定の角度をもってローラーをシャフト周囲に配
した場合、ローラーは軸方向の中央部のみがシャフト外
周面に接触する構造となってしまう。従って、両者の間
に十分な接触面積を生み出すことができず、十分な軸方
向推力を生み出すためにはローラー数を必要以上に多く
しなければならなかった。However, with conventional roller screws,
Since the cylindrical rollers used in roller bearings such as cam followers are simply used, if the rollers are arranged around the shaft at a predetermined angle as described above, only the axial center of the rollers will touch the shaft. The structure ends up being in contact with the outer peripheral surface. Therefore, it was not possible to create a sufficient contact area between the two, and the number of rollers had to be increased more than necessary in order to create a sufficient axial thrust.
軸方向推力を向上させる手段としては、ローラーとシャ
フト外周面との圧接力を高める方法、すなわち、ローラ
ーにより大きな予圧を付与する方法も考えられるが、そ
の場合には、シャフトあるいはナツトの回転に一層大き
なトルクが必要になるといった弊害が生じる。One possible way to increase the axial thrust is to increase the contact force between the roller and the outer circumferential surface of the shaft, that is, to apply a larger preload to the roller, but in that case, the rotation of the shaft or nut is This has the disadvantage that a large torque is required.
又、上述したようにローラーとシャフト外周面との接触
が一様でなく、同様にしてローラーとナツト内周面との
接触も一様でないことから、ローラーに付与する予圧を
大きくした場合にはローラーに無理な弾性変形が生じて
破損を招く可能性や、ローラーのスキューによって運動
不能に陥る可能性もある。In addition, as mentioned above, the contact between the roller and the outer peripheral surface of the shaft is not uniform, and the contact between the roller and the inner peripheral surface of the nut is also not uniform, so if the preload applied to the roller is increased, There is also the possibility that the rollers will undergo unreasonable elastic deformation, leading to damage, or the rollers may become skewed, resulting in an inability to move.
本発明はこの様な問題点に鑑みなされたものであり、そ
の目的とするところは、コンパクトな構成で軸方向の推
力が大きく、且つ、安定した運動を達成することか可能
なローラースクリューを提供することにある。The present invention was made in view of these problems, and its purpose is to provide a roller screw that has a compact configuration, has a large axial thrust, and is capable of achieving stable motion. It's about doing.
［課題を解決するための手段１
上記目的を達成するために、本発明のローラースクリュ
ーは、円筒状シャフトと、このシャフトの軸心に対して
所定角度に傾斜させた状態でシャフトの円周方向に沿っ
て配列されると共に、外形略鼓状に形成されて上記シャ
フト外周面と線接触し、当該外周面を螺旋状に転走する
複数のローラーと、これらローラーが線接触しながら転
走する凸曲面状の負荷転走面を内周面の円周方向に沿っ
て有し、上記シャフトと相俟ってローラーを挟み込む外
筒部材とからなることを特徴とするものである。[Means for Solving the Problems 1] In order to achieve the above object, the roller screw of the present invention includes a cylindrical shaft and a shaft that is tilted at a predetermined angle with respect to the axis of the shaft in the circumferential direction of the shaft. A plurality of rollers are arranged along the outer circumferential surface of the shaft and are arranged in a substantially drum shape and are in line contact with the outer circumferential surface of the shaft, and these rollers roll in line contact with the outer circumferential surface of the shaft. It is characterized by comprising an outer cylindrical member having a convexly curved load rolling surface along the circumferential direction of the inner circumferential surface and sandwiching the roller together with the shaft.
この様な技術的手段において、上記ローラーはシャフト
外周面と線接触することが要求され、その形状は、中央
部直径か両端部直径に比して小さい略鼓状に形成され、
外周面は軸方向に沿った凹曲面となる。この凹曲面の面
形状は、ローラーがシャフト軸心に対して傾斜している
角度、すなわちリード角に応じて適宜設計変更して差支
えない。In such technical means, the roller is required to be in line contact with the outer circumferential surface of the shaft, and its shape is approximately drum-shaped, which is smaller than the diameter of the center part or the diameter of both ends.
The outer peripheral surface becomes a concave curved surface along the axial direction. The surface shape of this concave curved surface may be appropriately designed depending on the angle at which the roller is inclined with respect to the shaft axis, that is, the lead angle.
又、上記外筒部材としては、その内周面の円周方向に沿
って上記ローラーの転走する負荷転走面を有すると共に
、この負荷転走面が軸方向に沿った凸曲面状に形成され
てローラーと線接触するものであれば、固定用のフラン
ジ部やグリース封入のためのシール部材を設ける等、そ
の構造を適宜設計変更して差支えない。Further, the outer cylindrical member has a load rolling surface on which the roller rolls along the circumferential direction of the inner peripheral surface thereof, and the load rolling surface is formed in a convex curved shape along the axial direction. As long as the roller is in line contact with the roller, the structure may be modified as appropriate, such as by providing a flange for fixing or a sealing member for sealing in grease.
更に、本発明のローラースクリューにおいては、ローラ
ーに付与する予圧を調整することで外筒部材のシャフト
に対する剛性を高め、更に、軸方向の推進力を調整可能
である。この際、上記予圧を調整するための手段として
は、外筒部材の外周面をテーパー状に形成し、その外周
面をテーパースリーブのテーパー状内周面に圧入してロ
ーラーに予圧を付与する構成が好ましい。この構成によ
れば、外筒部材のテーパースリーブへの圧入量に応じて
容易に予圧量を調整できる他、外筒部材の周囲に突呂物
がないので、外筒部材を容易にテーブル等に組み込むこ
とが可能となる。Further, in the roller screw of the present invention, by adjusting the preload applied to the roller, the rigidity of the outer cylinder member relative to the shaft can be increased, and furthermore, the axial driving force can be adjusted. At this time, as a means for adjusting the preload, the outer circumferential surface of the outer cylinder member is formed into a tapered shape, and the outer circumferential surface is press-fitted into the tapered inner circumferential surface of the tapered sleeve to apply preload to the roller. is preferred. According to this configuration, the amount of preload can be easily adjusted according to the amount of press-fitting of the outer cylinder member into the tapered sleeve, and since there are no objects around the outer cylinder member, the outer cylinder member can be easily placed on a table, etc. It becomes possible to incorporate it.
［作 用１
この様な技術的手段によれば、ローラーはその軸方向の
全長がシャフト及び外筒部材と接触した状態で両者の間
を転勤するので、ローラーとシャフトとの間の摩擦力が
増加して外筒部材あるいはシャフトの軸方向推力が向上
する。[Function 1] According to such a technical means, the roller moves between the shaft and the outer cylinder member with its entire axial length in contact with the shaft and the outer cylindrical member, so that the frictional force between the roller and the shaft is reduced. This increases the axial thrust of the outer cylinder member or shaft.
又、ローラーとシャフトとの間の摩擦力が大きいことか
ら予圧量が小さい場合でも十分な軸方向推進力を得られ
、その分シャフトあるし）は外筒部材の回転に必要なト
ルクが軽減される。In addition, since the frictional force between the roller and the shaft is large, sufficient axial propulsion force can be obtained even when the amount of preload is small, and the torque required to rotate the outer cylinder member is reduced accordingly. Ru.
更に、ローラーの外周面は略均−にシャフト及び外筒部
材に当接し、ローラーに無理な弾性変形の発生したり、
荷重が偏って作用することがない。Furthermore, the outer circumferential surface of the roller contacts the shaft and the outer cylindrical member approximately evenly, causing undue elastic deformation of the roller,
The load does not act unevenly.
［実施例］
以下、添付図面に基づいて本発明のローラースクリュー
を詳細に説明する。[Example] Hereinafter, the roller screw of the present invention will be explained in detail based on the accompanying drawings.
第１図は本発明の第一実施例を示すものでり、円筒状に
形成されてその外周面１１がローラー転走面となるシャ
フト１と、このシャフト１の円周方向に沿って配列され
た複数のローラー２と、内周面に上記ローラー２の転走
する負荷転走面３１を有し、上記シャフト１と相俟って
ローラー２を挟み込むリング状外筒部材３と、この外筒
部材３の外周面３２に嵌合して上記ローラー２に予圧を
付与するテーパースリーブ４とから構成されている。FIG. 1 shows a first embodiment of the present invention, which includes a shaft 1 formed in a cylindrical shape and whose outer circumferential surface 11 serves as a roller rolling surface, and a shaft 1 arranged along the circumferential direction of this shaft 1. a plurality of rollers 2, a ring-shaped outer cylinder member 3 having a load rolling surface 31 on the inner peripheral surface on which the rollers 2 roll, and sandwiching the rollers 2 together with the shaft 1; It is comprised of a tapered sleeve 4 that fits onto the outer circumferential surface 32 of the member 3 and applies preload to the roller 2.
上記ローラー２は、シャフト１の軸心に対して所定の角
度θだけ傾斜した姿勢で外筒部材３の負荷転走面３１と
シャフト外周面１１とに接触しており、シャフト１ある
いは外筒部材３が回転すると、シャフト外周面１１に関
しては螺旋状の軌跡を描きながら当該面１１を転走する
一方、上記負荷転走面３１に関しては円周方向に沿って
転走するようになっている。The roller 2 is in contact with the load rolling surface 31 of the outer cylindrical member 3 and the shaft outer circumferential surface 11 in an attitude inclined at a predetermined angle θ with respect to the axis of the shaft 1, and is in contact with the shaft 1 or the outer cylindrical member. 3 rotates, the shaft outer circumferential surface 11 rolls on the surface 11 while drawing a spiral trajectory, while the load rolling surface 31 rolls along the circumferential direction.
このローラー２の姿勢は第６図及び第７図に示すところ
の保持器５によって維持されている。この保持器５には
ローラー２を組み付けるポケット５１が円周方向を１２
等分するよう開設される一方、各ボケ・ノド５１にはロ
ーラー２を挾持する保持片５２が突出しており、ローラ
ー２の姿勢を維持する他、外筒部材３をシャフト１から
抜いた際のローラー２の脱落を防止している。This attitude of the roller 2 is maintained by a retainer 5 shown in FIGS. 6 and 7. This retainer 5 has a pocket 51 in which the roller 2 is assembled, extending 12 times in the circumferential direction.
Each bokeh throat 51 has a protruding holding piece 52 that holds the roller 2, which not only maintains the posture of the roller 2 but also maintains the position when the outer cylindrical member 3 is removed from the shaft 1. This prevents the roller 2 from falling off.
又、第２図に示すように、ローラー２はシャフト１外周
面との接触長を大きく採るために、軸方向中央部２１の
直径が両端部２２の直径よりも小さい略鼓状に形成され
て、その外周面は軸方向に沿った凹状曲面となっている
。この凹状曲面は、第３図に示すように、ローラー２の
軸方向に合致してシャフト１を切断した際に生じる楕円
の短軸と直交する円弧１２より若干大きい曲率あるいは
同一の曲率を有している。Further, as shown in FIG. 2, the roller 2 is formed into a substantially drum-like shape in which the diameter of the central portion 21 in the axial direction is smaller than the diameter of both end portions 22 in order to ensure a large contact length with the outer circumferential surface of the shaft 1. , its outer peripheral surface is a concave curved surface along the axial direction. As shown in FIG. 3, this concave curved surface has a curvature that is slightly larger than or the same as the arc 12 that is perpendicular to the short axis of the ellipse that occurs when the shaft 1 is cut along the axial direction of the roller 2. ing.
一方、上記外筒部材３は、その負荷転走面３１がローラ
ー２の凹状曲面に対応した凸状曲面に形成されており、
ローラー２と外筒部材３との間においてもローラー２の
接触長の増加が図られている（第３図参照）。On the other hand, the load rolling surface 31 of the outer cylinder member 3 is formed into a convex curved surface corresponding to the concave curved surface of the roller 2,
The contact length of the roller 2 is also increased between the roller 2 and the outer cylinder member 3 (see FIG. 3).
又、外筒部材３の外周には当該部材３をテーブル等に固
定するためのフランジ部３３が突設されており、このフ
ランジ部３３には固定ボルト（図示せず）が貫通する取
付孔３４が穿設されている。又、上記フランジ部３３に
は、第５図に示すように、ローラー２の転走する負荷域
にグリースを供給するための供給通路３５が半径方向に
穿設されると共に、当該通路３５に連通する供給口３６
が軸方向に開設され、Ｌ字型の油送路が形成されている
。尚、符号３７は、上記供給通路３５の一端を塞ぐため
の盲栓、符号６は、負荷域からのグリース洩れを防止す
るオイルシールである。Further, a flange portion 33 for fixing the member 3 to a table or the like is protruded from the outer periphery of the outer cylindrical member 3, and this flange portion 33 has a mounting hole 34 through which a fixing bolt (not shown) passes. is drilled. Further, as shown in FIG. 5, a supply passage 35 for supplying grease to the load area where the roller 2 rolls is bored in the radial direction in the flange portion 33, and a supply passage 35 is communicated with the passage 35. supply port 36
is opened in the axial direction, forming an L-shaped oil feed path. The reference numeral 37 is a blind plug for closing one end of the supply passage 35, and the reference numeral 6 is an oil seal for preventing grease from leaking from the load area.
又、外筒部材３の外周面３２は、フランジ部３３側で直
径が大きく他端側で直径の小さいテーパー状に形成され
ており、この外周面３２には内周面４１が逆テーパー状
に形成された上記テーパースリーブ４が嵌合している。Further, the outer circumferential surface 32 of the outer cylinder member 3 is formed in a tapered shape, with a diameter larger on the flange portion 33 side and smaller on the other end side, and an inner circumferential surface 41 on this outer circumferential surface 32 is formed in a reverse tapered shape. The formed tapered sleeve 4 is fitted therein.
このテーパースリーブ４には、外筒部材３のフランジ部
３３を貫通する予圧調整ボルト４２が螺合しており、当
該ボルト４２を締結するとテーパースリーブ４がスライ
ドして外筒部材３が締め付けられ、負荷転走面３１を転
走するローラー２に予圧が付与される。更に、この実施
例では、上記フランジ部３３にスリット３８が形成され
ており、フランジ部３３の剛性によって外筒部材３の締
め付けが阻害されない構造となっている。従って、予圧
調整ボルト４２の締結量を任意に調整する二とでローラ
ー２の予圧量を自由に変化させることが可能となってい
る。尚、フランジ部３３に開設された捩子孔３９は、テ
ーパースリーブ４を外筒部材３から外す際に当該スリー
ブ４を押圧するボルト（図示せず）を螺合させるもので
ある。A preload adjustment bolt 42 passing through the flange portion 33 of the outer cylinder member 3 is screwed into the tapered sleeve 4, and when the bolt 42 is tightened, the taper sleeve 4 slides and the outer cylinder member 3 is tightened. A preload is applied to the roller 2 rolling on the loaded rolling surface 31. Furthermore, in this embodiment, a slit 38 is formed in the flange portion 33, so that the rigidity of the flange portion 33 does not hinder the tightening of the outer cylinder member 3. Therefore, it is possible to freely change the amount of preload on the roller 2 by arbitrarily adjusting the amount of tightening of the preload adjustment bolt 42. The threaded hole 39 formed in the flange portion 33 is used to screw a bolt (not shown) that presses the tapered sleeve 4 when removing the sleeve 4 from the outer cylinder member 3.
このように構成された本実施例のローラースクリューは
、例えばシャフト１を回転自在に支持する一方、外筒部
材３はテーブル等の可動体へ回転不能に固定し、ステッ
ピングモータ等でシャフト１に所定の回転角を与えて外
筒部材３に生じる軸方向の推進力でテーブルを直線移動
させて使用される。The roller screw of this embodiment configured as described above rotatably supports the shaft 1, for example, while the outer cylindrical member 3 is unrotatably fixed to a movable body such as a table, and is attached to the shaft 1 in a predetermined position using a stepping motor or the like. The table is used by moving the table linearly by the axial thrust generated in the outer cylinder member 3 by giving a rotation angle of .
このとき、本実施例によれば、ローラー２を略鼓形状に
成形したことにより、ローラー２とシャフト１との接触
長が充分に発生するので、両者１，２の間に大きな摩擦
力が作用することとなり、当該摩擦力を利用した外筒部
材３の軸方向の推進力が向上したものとなる。At this time, according to this embodiment, since the roller 2 is formed into a substantially drum shape, a sufficient contact length between the roller 2 and the shaft 1 is generated, so that a large frictional force acts between the two. As a result, the axial propulsive force of the outer cylinder member 3 using the frictional force is improved.
又、ローラー２の外周面は略均−にシャフト外周面１１
及び外筒部材３の負荷転走面３１に接触するので、ロー
ラー２に無理な弾性変形が生じることもなく、且つ、荷
重の偏りによってローラー２の転勤が不安定となること
もない。Further, the outer circumferential surface of the roller 2 is approximately evenly aligned with the shaft outer circumferential surface 11.
Since the roller 2 contacts the load rolling surface 31 of the outer cylindrical member 3, the roller 2 will not undergo unreasonable elastic deformation, and the transfer of the roller 2 will not become unstable due to uneven load.
［発明の効果］
以上説明してきたように、本発明のローラースクリュー
によれば、ローラーとシャフトとの間の摩擦力が増加し
て外筒部材あるいはシャフトの軸方向推力が向上するの
で、従来に比してコンパクトな構成で同程度の軸方向推
進力を得ることが可能である。[Effects of the Invention] As explained above, according to the roller screw of the present invention, the frictional force between the roller and the shaft is increased and the axial thrust of the outer cylinder member or the shaft is improved. It is possible to obtain the same level of axial propulsion force with a relatively compact configuration.
又、小さな予圧量でも十分な軸方向推進力が生じるので
、シャフトあるいは外筒部材の回転に必要なトルクが軽
減され、起動力の小さなモータを動力源とすることがで
きる。Further, since a sufficient axial propulsion force is generated even with a small amount of preload, the torque required to rotate the shaft or the outer cylinder member is reduced, and a motor with a small starting force can be used as the power source.
更に、ローラーの外周面がシャフト及び外筒部材に均一
に接触するので、ローラーの破損やスキューが防止され
、長期にわたって安定した運動性能を維持することがで
きる。Further, since the outer circumferential surface of the roller uniformly contacts the shaft and the outer cylinder member, breakage and skew of the roller are prevented, and stable motion performance can be maintained over a long period of time.
第１図は本発明のローラースクリューの第一実施例を示
す正面断面図、第２図はローラーを示す斜視図、第３図
は第１図の■−■断面図、第４図は第一実施例に係るロ
ーラースクリューの側面図、第５図は第４図のＶ−Ｖ断
面図、第６図は第一実施例に係る保持器を示す側面類、
第７図は第６図のＡ矢視図（一部切欠き断面図）である
。
［符号説明］
１：シャフト ２：ローラー
３：外筒部材 ４：テーパースリーブ３１：負荷
転走面
特許出願人 ティエチケー株式会社代 理
人 弁理士 成 瀬 勝 夫（外１名）第１図
１ ンヤフト
２ ローラー
３ 外筒部材
第２図
第３図
第４図
第５図
第６図
第７図Fig. 1 is a front sectional view showing the first embodiment of the roller screw of the present invention, Fig. 2 is a perspective view showing the roller, Fig. 3 is a sectional view taken along the line ■-■ of Fig. 1, and Fig. 4 is a A side view of the roller screw according to the embodiment, FIG. 5 is a sectional view taken along the line V-V in FIG. 4, and FIG. 6 is a side view of the cage according to the first embodiment.
FIG. 7 is a view (partially cut away sectional view) taken along arrow A in FIG. 6. [Description of symbols] 1: Shaft 2: Roller 3: Outer cylindrical member 4: Tapered sleeve 31: Load rolling surface Patent applicant: TIETIK Co., Ltd.
Person Patent attorney Katsuo Naruse (1 other person) Fig. 1 1 Yaft 2 Roller 3 Outer cylinder member Fig. 2 Fig. 3 Fig. 4 Fig. 5 Fig. 6 Fig. 7
Claims (2)
所定角度に傾斜させた状態でシャフトの円周方向に沿っ
て配列されると共に、外形略鼓状に形成されて上記シャ
フト外周面と線接触し、当該外周面を螺旋状に転走する
複数のローラーと、これらローラーが線接触しながら転
走する凸曲面状の負荷転走面を内周面の円周方向に沿っ
て有し、上記シャフトと相俟ってローラーを挟み込む外
筒部材とからなることを特徴とするローラースク リュー。(1) A cylindrical shaft, which is arranged along the circumferential direction of the shaft in a state of being inclined at a predetermined angle with respect to the axis of the shaft, and is formed into a substantially drum-shaped outer shape and is connected to the outer circumferential surface of the shaft. It has a plurality of rollers that are in line contact and roll spirally on the outer peripheral surface, and a convex curved load rolling surface on which these rollers roll in line contact along the circumferential direction of the inner peripheral surface. , a roller screw comprising an outer cylindrical member that, together with the shaft, sandwiches a roller.
周面をテーパースリーブのテーパー状内周面に圧入して
ローラーに予圧を付与することを特徴とする請求項１記
載のローラースクリュー。(2) The roller screw according to claim 1, wherein the outer circumferential surface of the outer cylinder member is formed into a tapered shape, and the outer circumferential surface is press-fitted into the tapered inner circumferential surface of the tapered sleeve to apply preload to the roller. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33080190A JP2810228B2 (en) | 1990-11-30 | 1990-11-30 | Roller screw |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33080190A JP2810228B2 (en) | 1990-11-30 | 1990-11-30 | Roller screw |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04203649A true JPH04203649A (en) | 1992-07-24 |
| JP2810228B2 JP2810228B2 (en) | 1998-10-15 |
Family
ID=18236707
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP33080190A Expired - Lifetime JP2810228B2 (en) | 1990-11-30 | 1990-11-30 | Roller screw |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2810228B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2017040345A (en) * | 2015-08-21 | 2017-02-23 | 日本精工株式会社 | Rotation-linear motion converting device, and electric power steering device, vehicle and machine device equipped therewith |
| JP2017040344A (en) * | 2015-08-21 | 2017-02-23 | 日本精工株式会社 | Rotation-linear motion converting device, and electric power steering device, vehicle and machine device equipped therewith |
| WO2021065354A1 (en) * | 2019-10-01 | 2021-04-08 | 三井金属アクト株式会社 | Extension and contraction mechanism and method for manufacturing extension and contraction mechanism |
-
1990
- 1990-11-30 JP JP33080190A patent/JP2810228B2/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2017040345A (en) * | 2015-08-21 | 2017-02-23 | 日本精工株式会社 | Rotation-linear motion converting device, and electric power steering device, vehicle and machine device equipped therewith |
| JP2017040344A (en) * | 2015-08-21 | 2017-02-23 | 日本精工株式会社 | Rotation-linear motion converting device, and electric power steering device, vehicle and machine device equipped therewith |
| WO2021065354A1 (en) * | 2019-10-01 | 2021-04-08 | 三井金属アクト株式会社 | Extension and contraction mechanism and method for manufacturing extension and contraction mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2810228B2 (en) | 1998-10-15 |
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