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WO2021020263A1 - Unité de vis à rouleaux - Google Patents

Unité de vis à rouleaux Download PDF

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Publication number
WO2021020263A1
WO2021020263A1 PCT/JP2020/028380 JP2020028380W WO2021020263A1 WO 2021020263 A1 WO2021020263 A1 WO 2021020263A1 JP 2020028380 W JP2020028380 W JP 2020028380W WO 2021020263 A1 WO2021020263 A1 WO 2021020263A1
Authority
WO
WIPO (PCT)
Prior art keywords
nut
screw shaft
thread
screw
raceway surface
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.)
Ceased
Application number
PCT/JP2020/028380
Other languages
English (en)
Japanese (ja)
Other versions
WO2021020263A9 (fr
Inventor
英二 社本
中村　隆
高橋　徹
喜大 濱田
弘幸 岸
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
THK Co Ltd
Tokai National Higher Education and Research System NUC
Original Assignee
THK Co Ltd
Tokai National Higher Education and Research System NUC
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by THK Co Ltd, Tokai National Higher Education and Research System NUC filed Critical THK Co Ltd
Priority to JP2021536991A priority Critical patent/JP7525905B2/ja
Publication of WO2021020263A1 publication Critical patent/WO2021020263A1/fr
Publication of WO2021020263A9 publication Critical patent/WO2021020263A9/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts

Definitions

  • the present invention relates to a rolling element screwing device such as a ball screw in which a rolling element is interposed between a screw shaft and a nut so that a rolling element can be rolled.
  • the ball screw is a rolling screw mechanism. That is, the ball screw includes a screw shaft, a nut, and a plurality of balls interposed between the screw shaft and the nut so as to be rollable. A spiral raceway surface is formed on the outer surface of the screw shaft. A spiral raceway surface facing the raceway surface of the screw shaft is formed on the inner surface of the nut. A ball is interposed between the raceway surface of the screw shaft and the raceway surface of the nut.
  • the shape of the raceway surface of the screw shaft and the raceway surface of the nut are both Gothic arch grooves.
  • the contact angle is set to 40 to 50 degrees (see Patent Document 1). This is so that the load can be received on both the outward and return paths of the nut.
  • the ball screw basically receives an axial load.
  • the contact angle is set to 40 to 50 degrees, so when an axial load acts on the ball screw, a load in the axial direction and the axial perpendicular direction (radial direction) is applied inside the ball screw. Occurs. Since the latter radial load does not help to receive the axial load, the conventional ball screw has a problem that the rated load in the axial direction is small. Further, since the radial position where the screw contacts the ball is smaller than the radial position where the nut contacts the ball, it has a convex curvature when viewed in the direction in which the raceway surface extends. Due to the curvature of the convex side, the area of elastic contact is reduced, and a large contact load cannot be received. That is, the conventional ball screw has a problem that the rated load is further reduced.
  • the ball comes into contact with the screw shaft and the Gothic arch groove of the nut at one point each, for a total of two points, and receives the load.
  • a third contact point is accompanied depending on whether the rotation is positive or reverse (see Non-Patent Document 1). Since slipping occurs instead of rolling at this third contact point, there is also a problem that friction loss increases and heat generation is large.
  • the ball screw generates heat, the screw shaft and nut cause metal expansion, which causes a change or deterioration in feed accuracy.
  • the present invention has been made in view of the above problems, and provides a rolling element screwing device which has a large rated load in the axial direction, generates little heat, and can suppress fluctuations in friction torque due to a free zone when the rolling direction is reversed.
  • the purpose is.
  • one aspect of the present invention includes a screw shaft having a spiral thread on the outer surface and a screw shaft raceway surface formed on the side surface of the screw thread, and a spiral nut on the inner surface.
  • a nut having a screw thread and having a nut raceway surface facing the screw shaft raceway surface formed on the side surface of the nut screw thread, and a rollable interposition between the screw shaft raceway surface and the nut raceway surface.
  • a rolling element screwing device including a plurality of rolling elements, wherein the outer diameter of the thread of the screw shaft is larger than the inner diameter of the nut thread of the nut.
  • a rolling element screw device that has a large rated load in the axial direction, generates less heat, and can suppress fluctuations in friction torque due to the free zone when the rolling direction is reversed.
  • FIG. 3A is a plan view of the rolling element screwing apparatus
  • FIG. 3B is a rolling element screwing apparatus which shows only the upper half of a nut
  • 3 (c) is a side view of FIG. 3 (b).
  • FIG. 1 is a cross-sectional view taken along the axis of the ball screw 1 as the rolling element screw device according to the first embodiment of the present invention.
  • FIG. 2 is an enlarged view of part II of FIG. 2 is a screw shaft, 2a is a screw shaft axis, 3 is a nut, and 5a and 5b are balls as rolling elements.
  • a spiral thread 10 is provided on the outer surface of the screw shaft 2.
  • the thread 10 of the screw shaft 2 has a pair of left and right side surfaces 10b and 10c and a peak 10a (see FIG. 2).
  • a first screw shaft raceway surface 11 is formed on one side surface 10c of the thread 10 (the side surface on the right side of the thread 10 in FIG. 1).
  • a second screw shaft raceway surface 12 is formed on the other side surface 10b of the screw thread 10 (the left side surface of the screw thread 10 in FIG. 1).
  • the outer diameter of the thread 10 of the screw shaft 2, that is, the diameter of the virtual cylinder in contact with the peak 10a of the thread 10 is D1.
  • the nut 3 includes a first nut portion 3a and a second nut portion 3b that are connected in the axial direction.
  • the first nut portion 3a is provided with a hole 8a into which the screw shaft 2 is inserted.
  • a spiral nut thread 6a is formed on the inner surface of the hole 8a.
  • the nut thread 6a has a pair of left and right side surfaces 7b and 7c and a peak 7a (see FIG. 2).
  • a first nut raceway surface 21 facing the first screw shaft raceway surface 11 of the screw shaft 2 is formed on one (left side of FIG. 1) side surface 7b of the pair of side surfaces 7b and 7c of the nut thread 6a.
  • the first nut raceway surface 21 is formed only on one side surface 7b of the nut thread 6a (see FIG. 2).
  • a 1-nut raceway surface 21 may be formed on each of the pair of left and right side surfaces 7b and 7c of the nut thread 6a.
  • the second nut portion 3b is provided with a hole 8b into which the screw shaft 2 is inserted. Similar to the first nut portion 3a, a spiral nut thread 6b is formed on the inner surface of the hole 8b of the second nut portion 3b.
  • the nut thread 6b has a pair of left and right side surfaces and a ridge.
  • a second nut raceway surface 22 facing the second screw shaft raceway surface 12 of the screw shaft 2 is formed on the other side surface (on the right side in FIG. 1) of the pair of side surfaces of the nut screw thread 6b.
  • the second nut raceway surface 22 is formed only on the other side surface (on the right side of FIG. 1) of the nut thread 6b.
  • a second nut raceway surface 22 may be formed on each of the pair of side surfaces of the nut thread 6b.
  • the inner diameters of the nut threads 6a and 6b that is, the diameters of the virtual cylinders in contact with the peaks 7a of the nut threads 6a and 6b are all D2.
  • the outer diameter D1 of the thread 10 of the screw shaft 2 is larger than the inner diameter D2 of the nut threads 6a and 6b of the nut 3.
  • the nut threads 6a and 6b enter the thread 10 adjacent to the screw shaft 2.
  • the first ball 5a is interposed between the first screw shaft raceway surface 11 of the screw shaft 2 and the first nut raceway surface 21 of the first nut portion 3a.
  • the first ball 5a exists only on the first screw shaft raceway surface 11 side of the thread 10 of the screw shaft 2, and does not exist on the second screw shaft raceway surface 12 side.
  • a load is applied to the first ball 5a in only one direction (direction of arrow (1) in FIG. 1) acting on the first nut portion 3a.
  • a second ball 5b is interposed between the second screw shaft raceway surface 12 of the screw shaft 2 and the second nut raceway surface 22 of the nut 3.
  • the second ball 5b exists only on the second screw shaft raceway surface 12 side of the screw thread 10 of the screw shaft 2, and does not exist on the first screw shaft raceway surface 11 side.
  • a load is applied to the second ball 5b only in the other direction (direction of arrow (2) in FIG. 1) acting on the second nut portion 3b.
  • the shape of the first screw shaft raceway surface 11 formed on the thread 10 of the screw shaft 2 is formed in a circular arc groove having a single arc.
  • the radius of this circular arc groove is slightly larger than the radius of the first ball 5a.
  • the first screw shaft raceway surface 11 and the first ball 5a come into contact with each other at a point P1 at the bottom of the groove. Since the screw thread 10 has a lead angle, to be precise, the shape of the first screw shaft raceway surface 11 is formed in the circular arc groove in the right-angled cross-sectional view of the screw thread 10.
  • the shape of the first screw shaft raceway surface 11 may be a Gothic arch groove that contacts the first ball 5a at two points.
  • the side surface 10c of the screw thread 10 of the screw shaft 2 (the line connecting the side surface of the root portion 10-1 of the screw thread 10 in FIG. 2 and the side surface of the top portion 10-2) is the axis line 2a of the screw shaft 2 (in FIG. 2). It is inclined with respect to the line 2b orthogonal to the axis 2a parallel to the axis 2a of the screw shaft 2 in FIG. 1).
  • the width of the root portion 10-1 of the thread 10 of the screw shaft 2 is wider than the width of the top portion 10-2. Even if the side surface 10c is inclined, the first screw shaft raceway surface 11 makes point contact with the first ball 5a at the point P1 at the bottom of the groove. That is, the contact angle ⁇ described later is maintained in the vicinity of 90 °.
  • the arc length of the first screw shaft raceway surface 11 from the point P1 to the groove end N1 on the root portion 10-1 side is the arc length from the point P1 to the top of the first screw shaft raceway surface 11. It is longer than the arc length up to the groove end N2 on the 10-2 side (upper side of FIG. 2).
  • the groove width of the first screw shaft raceway surface 11 of the screw shaft 2 (the region represented by the central angle ⁇ 1 in FIG. 2) is an allowable surface pressure of 4200 MPa at the contact point P1 between the first ball 5a and the first screw shaft raceway surface 11. It is desirable that the contact long axis radius (the region represented by the central angle ⁇ 2 in FIG. 2) does not deviate from the groove width when
  • the side surface 10b of the thread 10 of the screw shaft 2 is inclined in the direction opposite to the side surface 10c.
  • a second screw shaft raceway surface 12 is formed on the side surface 10b of the screw thread 10.
  • the shape of the second screw shaft raceway surface 12 is formed in a circular arc groove having a single arc, similarly to the first screw shaft raceway surface 11.
  • the screw thread 10 is formed symmetrically.
  • the shape of the first nut raceway surface 21 formed on the nut thread 6a of the first nut portion 3a is also formed in a circular arc groove having a single arc.
  • the radius of the circular arc groove is slightly larger than the radius of the first ball 5a, like the first screw shaft raceway surface 11.
  • the first nut raceway surface 21 and the first ball 5a come into contact with each other at a point P2 at the bottom of the groove. Since the nut thread 6a has a lead angle, to be precise, the shape of the first nut raceway surface 21 is formed in the circular arc groove in the right-angled cross-sectional view of the nut thread 6a.
  • the shape of the first nut raceway surface 21 may be a Gothic arch groove that contacts the first ball 5a at two points.
  • an allowable surface pressure of 4200 MPa acts on the contact point P2 between the first ball 5a and the first nut raceway surface 21 as in the case of the first screw shaft raceway surface 11. At that time, it is desirable to set so that the contact semimajor axis does not deviate from the groove width.
  • the side surface 7b of the nut thread 6a of the first nut portion 3a is also inclined with respect to the line 2b orthogonal to the axis 2a of the screw shaft 2.
  • the width of the root portion 6-1 of the nut thread 6a is wider than the width of the top portion 6-2.
  • the first nut raceway surface 21 makes point contact with the first ball 5a at the point P2 at the bottom of the groove. That is, the contact angle ⁇ described later is maintained in the vicinity of 90 °. Therefore, the arc length of the first nut raceway surface 21 from the point P2 to the groove end M1 on the root portion 6-1 side (upper side in FIG. 2) is the arc length from the point P2 to the top portion 6-2 of the first nut raceway surface 21. It is longer than the arc length up to the groove end M2 on the side (lower side of FIG. 2).
  • the side surface 7c of the nut thread 6a of the first nut portion 3a is inclined in the direction opposite to the side surface 7b.
  • the first nut raceway surface 21 is not formed on the side surface 7c of the nut thread 6a.
  • the angle ⁇ formed by the line connecting the contact P1 and the contact P2 and the line 2b orthogonal to the axis 2a of the screw shaft 2, that is, the contact angle ⁇ is in the range of 90 ° ⁇ 30 °, preferably in the range of 90 ° ⁇ 20 °. , And more preferably set in the range of 90 ° ⁇ 10 °.
  • the contact angle ⁇ is a line connecting the bottoms of the Gothic arch groove for convenience.
  • the nut thread 6b of the second nut portion 3b is formed symmetrically with the nut thread 6a of the first nut portion 3a.
  • a spacer 4 as a preload applying means for applying the preload to the first ball 5a and the second ball 5b.
  • the spacer 4 pushes the first nut portion 3a in one direction (direction of the arrow (1) in FIG. 1), and compresses the first rolling element between the first nut portion 3a and the screw shaft 2. Further, the spacer 4 pushes the second nut portion 3b in the other direction (direction of the arrow (2) in FIG. 1), and compresses the second rolling element between the second nut portion 3b and the screw shaft 2.
  • a spring may be used instead of the spacer 4.
  • the nut 3 may be a single nut in which the first nut portion 3a and the second nut portion 3b are integrated. By shifting the nut thread 6a of the first nut portion 3a and the nut thread 6b of the second nut portion 3b at the central portion of the single nut, preload can be applied to the first ball 5a and the second ball 5b. ..
  • first nut portion 3a and the second nut portion 3b are arranged in opposite directions from the state shown in FIG. 1, that is, the first nut portion 3a is arranged on the right side and the second nut portion 3b is arranged on the left side. Preload may be applied to the first ball 5a and the second ball 5b so that the nut portion 3a and the second nut portion 3b pull each other.
  • FIG. 3 shows the circulation structure of the ball screw 1 of the present embodiment.
  • 3 (a) is a plan view of the ball screw 1
  • FIG. 3 (b) is a side view of the ball screw 1 showing only the upper half of the nut 3
  • FIG. 3 (c) is a view taken along the line c of FIG. 3 (b). Is.
  • the first nut portion 3a is provided with two return pipes 23 connected to one end and the other end of the circulation path.
  • the return pipe 23 scoops up the first ball 5a that rolls to one end of the circulation path and returns it to the other end of the circulation path.
  • the second nut portion 3b is provided with, for example, two rows of 2.5 winding circulation paths.
  • the second nut portion 3b is also provided with two return pipes 25 connected to one end and the other end of the circulation path.
  • Reference numeral 24 denotes a key for stopping the rotation of the first nut portion 3a and the second nut portion 3b.
  • the number of turns and the number of rows of the circulation path are examples, and are set appropriately according to the rated load.
  • a circulation method instead of the return pipe method, a circulation method such as a spinning top type, an end cap type, an end deflector type, or a return plate type may be adopted.
  • the contact angle ⁇ can be set to an angle advantageous for receiving the load in the axial direction, and since the contact area between the balls 5a and 5b and the screw shaft 2 is large, the rated load in the axial direction can be increased.
  • the contact area between the screw shaft and the ball is small, but the contact area between the nut and the ball is large. Therefore, the rated load is determined on the smaller screw shaft side.
  • the difference in contact area between the two is reduced or eliminated, so that the rated load becomes large.
  • the balls 5a and 5b roll.
  • the angle formed by the two lines connecting the two contact points P1 and P2 and the ball center O is approximately 180. It becomes a degree. Therefore, slippage (friction) can be reduced, and heat generation of the ball screw due to friction can be suppressed.
  • a first screw shaft raceway surface 11 and a second screw shaft raceway surface 12 are formed on each of the pair of side surfaces 10b and 10c of the screw thread 10 of the screw shaft 2, and the first ball 5a of the first nut portion 3a is attached to the screw shaft 2 Since the second ball 5b of the second nut portion 3b is provided only on the second screw shaft raceway surface 12 side of the screw shaft 2, the lead angle of the screw shaft 2 is reduced. be able to. Further, a preload can be applied to the first ball 5a and the second ball 5b.
  • the screw shaft raceway surfaces 11 and 12 are on the side surfaces 10b and 10c of the screw thread 10. Is easy to process.
  • the grindstone T for grinding the first screw shaft raceway surface 11 is broken down from the solid line by inclining the side surfaces 10b and 10c of the thread 10 of the screw shaft 2 from the solid line in the figure as shown by the broken line.
  • the first screw shaft raceway surface 11 can be ground on the peripheral surface T1 of the grindstone T.
  • FIG. 5 is a cross-sectional view of a ball screw 31 as a rolling element screw device according to a second embodiment of the present invention.
  • 2 is a screw shaft
  • 2a is a screw shaft axis
  • 3 is a nut
  • 3a is a first nut portion
  • 3b is a second nut portion
  • 5a is a first ball
  • 5b is a second ball
  • 4 is a spacer. Since the basic configuration of the ball screw 31 of the second embodiment is the same as that of the ball screw 1 of the first embodiment, the same reference numerals are given and the description thereof will be omitted.
  • the side surfaces 10b and 10c of the screw thread 10 of the screw shaft 2 are inclined with respect to the line 2b orthogonal to the axis 2a of the screw shaft 2, whereas the second embodiment
  • the side surfaces 10b and 10c of the thread 10 of the screw shaft 2 are parallel to the line 2b orthogonal to the axis 2a of the screw shaft 2.
  • the side surfaces 7b and 7c of the nut threads 6a and 6b of the nut 3 are inclined with respect to the line 2b orthogonal to the axis 2a of the screw shaft 2.
  • the side surfaces 7b and 7c of the nut threads 6a and 6b of the nut 3 are parallel to the line 2b orthogonal to the axis 2a of the screw shaft 2.
  • FIG. 6 is a cross-sectional view of a ball screw 40 as a rolling element screw device according to a third embodiment of the present invention.
  • 41 is a screw shaft
  • 41a is a screw shaft axis
  • 42 is a nut
  • 43 is a ball.
  • the ball screw 1 of the first embodiment and the ball screw 31 of the second embodiment are configured so that the ball screws 1 and 31 can receive loads in two directions of the outward path and the return path, but the third embodiment.
  • the ball screw 40 of the form is configured so that the ball screw 40 can receive a load in one direction (downward on the Z axis indicated by the arrow (3) in FIG. 6).
  • the screw shaft 41 is arranged in the Z-axis direction. Then, rattling is prevented from occurring due to the gravity of a movable body (not shown) attached to the nut 42.
  • the screw shaft raceway surface 45 is formed on the side surface of the spiral thread 44 of the screw shaft 41.
  • a nut raceway surface 47 facing the screw shaft raceway surface 45 is formed on the side surface of the spiral nut thread 46 of the nut 42.
  • a plurality of balls 43 are interposed between the screw shaft raceway surface 45 and the nut raceway surface 47 so as to be rollable.
  • the outer diameter of the thread 44 of the screw shaft 41 is larger than the inner diameter of the nut thread 46 of the nut 42, and the contact angle is set in the range of 90 ° ⁇ 30 °.
  • the rated load in the axial direction is large, the heat generation is small, and the rolling direction. Fluctuations in friction torque due to the free zone during reversal can also be suppressed.
  • the ball is used as the rolling element, but a roller may be used as the rolling element.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne une unité de vis à rouleaux qui a une grande charge nominale dans une direction axiale, qui génère peu de chaleur et qui peut supprimer les fluctuations du couple de frottement provoquées par une zone libre obtenue lorsqu'une direction de laminage est inversée. Un filetage (10) en spirale est disposé sur une surface externe d'un arbre à vis (2). Des filetages d'écrou (6a, 6b) en spirale sont disposés sur une surface interne d'un écrou (3). Un diamètre externe (D1) du filetage (10) de l'arbre à vis (2) est réglé pour être supérieur à un diamètre interne (D2) des filetages d'écrou (6a, 6b) de l'écrou (3). Des surfaces de chemin de roulement (11, 12) d'arbre à vis sont formées sur des surfaces latérales respectives du filetage (10) de l'arbre à vis (2). Des surfaces de chemin de roulement (21, 22) d'écrou opposées aux surfaces de chemin de roulement (11, 12) d'arbre à vis sont formées sur des surfaces latérales respectives des filetages d'écrou (6a, 6b) de l'écrou (3). Plusieurs rouleaux (5a, 5b) sont interposés de manière enroulable entre les surfaces de chemin de roulement (11, 12) d'arbre à vis et les surfaces de chemin de roulement (21, 22) d'écrou.
PCT/JP2020/028380 2019-08-01 2020-07-22 Unité de vis à rouleaux Ceased WO2021020263A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2021536991A JP7525905B2 (ja) 2019-08-01 2020-07-22 転動体ねじ装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019-141986 2019-08-01
JP2019141986 2019-08-01

Publications (2)

Publication Number Publication Date
WO2021020263A1 true WO2021020263A1 (fr) 2021-02-04
WO2021020263A9 WO2021020263A9 (fr) 2021-03-25

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Application Number Title Priority Date Filing Date
PCT/JP2020/028380 Ceased WO2021020263A1 (fr) 2019-08-01 2020-07-22 Unité de vis à rouleaux

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JP (1) JP7525905B2 (fr)
TW (1) TW202113253A (fr)
WO (1) WO2021020263A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6154541U (fr) * 1984-09-14 1986-04-12
US5535638A (en) * 1994-11-10 1996-07-16 Cincinnati Milacron Inc. Antifriction screw drive
JP2003194177A (ja) * 2001-12-26 2003-07-09 Nsk Ltd ボールねじ
JP2004138214A (ja) * 2002-10-21 2004-05-13 Nsk Ltd ボールねじ装置および該装置の製造方法
WO2017010553A1 (fr) * 2015-07-15 2017-01-19 Ntn株式会社 Vis sphérique et actionneur à commande électrique doté de celle-ci

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6154541U (fr) * 1984-09-14 1986-04-12
US5535638A (en) * 1994-11-10 1996-07-16 Cincinnati Milacron Inc. Antifriction screw drive
JP2003194177A (ja) * 2001-12-26 2003-07-09 Nsk Ltd ボールねじ
JP2004138214A (ja) * 2002-10-21 2004-05-13 Nsk Ltd ボールねじ装置および該装置の製造方法
WO2017010553A1 (fr) * 2015-07-15 2017-01-19 Ntn株式会社 Vis sphérique et actionneur à commande électrique doté de celle-ci

Also Published As

Publication number Publication date
WO2021020263A9 (fr) 2021-03-25
TW202113253A (zh) 2021-04-01
JP7525905B2 (ja) 2024-07-31
JPWO2021020263A1 (fr) 2021-02-04

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