WO2005038301A1 - ローラねじ - Google Patents
ローラねじ Download PDFInfo
- Publication number
- WO2005038301A1 WO2005038301A1 PCT/JP2004/012945 JP2004012945W WO2005038301A1 WO 2005038301 A1 WO2005038301 A1 WO 2005038301A1 JP 2004012945 W JP2004012945 W JP 2004012945W WO 2005038301 A1 WO2005038301 A1 WO 2005038301A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- roller
- load
- rolling groove
- roller rolling
- nut member
- Prior art date
Links
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
- F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
- F16H25/2247—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rollers
-
- 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
- F16H25/2247—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rollers
- F16H2025/2271—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rollers with means for guiding circulating rollers
-
- 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
- F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
- F16H25/2233—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls with cages or means to hold the balls in position
- F16H25/2238—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls with cages or means to hold the balls in position using ball spacers, i.e. spacers separating the balls, e.g. by forming a chain supporting the balls
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
- Y10T74/19698—Spiral
- Y10T74/19702—Screw and nut
- Y10T74/19744—Rolling element engaging thread
- Y10T74/19749—Recirculating rolling elements
- Y10T74/19767—Return path geometry
Definitions
- the present invention relates to a roller screw having a roller interposed between a screw shaft and a nut member so as to be able to roll.
- a ball screw in which a ball is interposed between a screw shaft and a nut member so as to be capable of rolling motion is known.
- the ball is interposed between a spiral ball rolling groove formed on the outer peripheral surface of the screw shaft and a spiral load ball rolling groove formed on the inner peripheral surface of the nut member.
- Patent Document 1 JP-A-11 210858
- Patent Document 2 Japanese Utility Model Application Laid-Open No. 6-87764
- roller screws are often used in a state where a large load is applied.
- rigidity is one of those that cannot be lacking. If there is a gap between the rollers and the roller rolling grooves, so-called looseness, or if the rigidity is insufficient even if the looseness is eliminated, the point at which the machine incorporating the roller screw performs work will be displaced. No, it lacks accuracy. Also, if the machine vibrates when it stops after moving fast, It is hard to settle down.
- roller screws that use rollers as rolling elements have been devised, for example, as in Patent Documents 1 and 2, but those that have not yet been commercialized have developed technology to apply a preload to roller screws. ⁇ .
- an object of the present invention is to provide a roller screw that can optimally apply a preload in accordance with the structure of a roller screw that improves the rigidity of the roller screw.
- the invention of claim 1 is directed to a screw shaft (1) in which a spiral roller rolling groove (la) having a V-shaped cross section is formed on an outer peripheral surface and an inner peripheral surface.
- a plurality of rollers (6) housed between the roller rolling grooves (2a), and the plurality of rollers (6) are arranged in one direction ((1) in the axial direction of the screw shaft (1)).
- rollers in the traveling direction of the rollers are cross-arranged so that the axes of the rollers ⁇ and the axes thereof are orthogonal to each other, and the load in the direction opposite to the one direction ((2))
- a plurality of rollers (6) having a diameter (D), a wall (la) of the roller rolling groove on which the roller rolls, and a roller (6) facing the wall (la).
- Said b A roller having an oversize larger than a distance between the load roller rolling groove and a wall surface (2a) on which the roller rolls is used.
- the invention of claim 2 provides a screw shaft (1) in which a spiral roller rolling groove (la) having a V-shaped cross section is formed on the outer peripheral surface, and the roller rolling groove (la) on the inner peripheral surface.
- the central groove (22) which has a large pitch, is formed on both sides of the central groove (22). It has a pitch (PI) and a pair of end grooves (23, 24) having the same pitch.
- the invention of claim 3 provides a screw shaft (1) in which a spiral roller rolling groove (la) having a V-shaped cross section is formed on the outer peripheral surface and the roller rolling groove (la) on the inner peripheral surface.
- a plurality of rollers (6) housed between the first nut member (12) and the second nut member (12) in the axial direction.
- a plurality of first nut rollers (6) separated and accommodated in the first nut member (12); and a plurality of second nut rollers (6) accommodated in the second nut.
- a shim (13) is interposed between the first nut member (12) and the second nut member (12) so that a compressive load can be applied to each.
- both the roller ⁇ group and the roller group receive the load as described above, so that the number of rollers receiving the load is doubled.
- the rollers existing in the nut member can be effectively used against the external force that acts, and the load can be distributed so that the rollers can receive the load without originally receiving the load, thereby improving the rigidity.
- the roller diameter is smaller than the distance (specified size) between the wall of the roller rolling groove and the wall of the load roller rolling groove, the roller receiving the axial load becomes ⁇ Group or j8 group only. Therefore, the number of rollers receiving the load is halved.
- FIG. 1 is a cross-sectional view showing a roller screw according to an embodiment of the present invention.
- FIG. 2 is a side view showing a screw shaft.
- FIG. 3 is a detailed sectional view of a roller rolling groove and a load roller rolling groove.
- FIG. 4 is a graph showing a relationship between a load and a displacement caused by a preload.
- FIG. 5 is a diagram showing a return pipe.
- FIG. 6 is a diagram showing spacers interposed between rollers.
- FIG. 7 is a sectional view showing a roller screw according to a second embodiment of the present invention.
- FIG. 8 is a plan view of a nut member according to a third embodiment of the present invention.
- FIG. 9 is an enlarged sectional view of a roller screw according to a third embodiment of the present invention. Explanation of symbols
- FIG. 1 shows a roller screw according to an embodiment of the present invention.
- the roller screw has a screw shaft 1 having a spiral roller rolling groove la formed on the outer peripheral surface, and a spiral load roller rolling groove 2a corresponding to the roller rolling groove la formed on the inner peripheral surface.
- a nut member 2 rotatably mounted on the screw shaft 1.
- the nut member 2 has a return pipe 4 as a return member that connects one end and the other end of the load roller rolling path 3 between the roller rolling groove la of the screw shaft 1 and the load roller rolling groove 2a of the nut member 2. It is attached.
- a roller return path 5 having a quadrangular cross section along the axial direction, in this embodiment, a square, is formed.
- the load roller rolling path 3 between the roller rolling groove la of the screw shaft 1 and the load roller rolling groove 2a of the nut member 2 and the roller return path 5 in the return pipe 4 have a plurality of rollers 6 Is contained in the array '.
- the screw shaft 1 rotates relative to the nut member 2
- the nut member 2 linearly moves relative to the screw shaft 1 in the axial direction of the screw shaft 1.
- the roller 6 rolls between the roller rolling groove la and the load roller rolling groove 2a.
- the roller 6 that has rolled to one end of the load roller rolling groove 2a is guided to the roller return path 5 in the return pipe 4, and is returned to the other end of the load roller rolling groove 2a several turns before.
- the roller 6 circulates in the roller circulation path constituted by the load roller rolling path 3 and the roller return path 5.
- FIG. 2 shows the screw shaft 1.
- a spiral roller On the outer periphery of the screw shaft 1 is a spiral roller A running groove la is formed.
- the cross section of the roller rolling groove la is V-shaped and its opening angle is set to 90 degrees.
- Various types of screws such as a single screw, a double screw, and a triple screw, can be used. In this embodiment, a double screw is used.
- FIG. 3 is a detailed view of the roller rolling groove la of the screw shaft 1 and the load roller rolling groove 2a of the nut member 2.
- the nut member 2 is formed with a spiral load roller rolling groove 2a facing the roller rolling groove la.
- the cross section of the load roller rolling groove 2a of the nut member 2 is also V-shaped, and its opening angle is set to 90 degrees.
- the pitch of the roller rolling groove la of the screw shaft 1 and the pitch of the load roller rolling groove 2a of the nut member 2 are both constant over the entire length of the groove.
- the roller rolling groove la and the load roller rolling groove 2a form a load roller rolling path 3 having a square cross section, in this embodiment, a square.
- a plurality of rollers 6 are crossed on the load roller rolling path 3 such that the rotation axes 7 and 8 of the adjacent rollers 6 are orthogonal to each other when viewed along the load roller rolling path.
- the ball applies a load in one direction in the axial direction of the screw shaft and in the other direction opposite to the negative direction.
- the roller 6 applies a load by its peripheral surface being compressed between one wall surface of the roller rolling groove la and one wall surface of the load roller rolling groove 2a facing the wall. Therefore, the load can be applied in only one direction in the axial direction of the screw shaft 1.
- a load in one direction (1) and another direction (2) in the axial direction of the screw shaft 1 can be applied.
- a roller that applies a load in one direction (1) in the axial direction of the screw shaft 1 is an ex group
- a roller that applies a load in the other direction (2) is a ⁇ group.
- the number of rollers in the group and the number of rollers in the group are preferably the same.
- the rollers ⁇ and the rollers j8 are alternately arranged as ⁇ , ⁇ , ⁇ , ⁇ , ⁇ , a, j8,. If there is, besides this, you can be a rooster yourself in the form of, ⁇ ⁇ ⁇ ⁇ , ⁇ , ⁇ , j8 ..., a, ⁇ , ⁇ , ⁇ , a, a, a,, j8 ... May be arranged.
- the diameter D of the roller 6 is larger than the length L in the axial direction.
- the diameter D of the roller 6 is larger than the distance between the wall surface 9 of the roller rolling groove la and the wall surface 10 of the load roller rolling groove 2a opposed to the wall surface 9, that is, a so-called oversized one. Therefore, the load roller rolling path 3
- the roller is elastically deformed in the inside, and a load commensurate therewith exists inside the nut member 2 as a preload. Since the rollers 6 are arranged crosswise in the loaded roller rolling path 3, the load applied to the nut member 2 from the roller 6 acts in a direction in which the adjacent rollers 6 and 6 repel each other.
- FIG. 4 shows this relationship in detail. Since the preload is applied by inserting the oversized roller 6, the rollers of the group of rollers ⁇ are elastically deformed by ⁇ 1 and the rollers of the group of rollers j8 are elastically deformed by ⁇ 2 in the initial state. The load generated at that time is ⁇ in the preload load.
- the axial load P acts on it and generates an axial displacement ⁇
- the displacement increases along the elastic displacement diagram for the roller group ⁇ , and decreases along the elastic displacement diagram for the roller group ⁇ . Will be.
- the load acting on the roller group ⁇ becomes ⁇ + ⁇
- the load acting on the roller j8 group becomes AC. Therefore, the applied load P is divided into B and C, and the direction of the load is applied to the roller ⁇ group and the roller ⁇ group. Even if it changes to this state, the internal load must be balanced.
- the reason that the rigidity is increased by applying the preload is that the number of rollers that receive the load increases and the roller load per roller decreases.
- the roller is used without a preload smaller than the specified size for the diameter of the roller 6, only the roller a or the group ⁇ receives the axial load.
- both the roller ⁇ group and the roller j8 group receive the load as described above, so that the number of rollers receiving the load is doubled.
- the roller 6 existing in the nut member 2 can be effectively utilized for the external force acting thereon, and the load can be distributed so that the roller 6 can receive the load without receiving the load.
- the roller rolling groove la of the screw shaft 1 and the load roller rolling of the nut member 2 Escape grooves lb, 2b are further formed along the grooves at the bottom of each of the running grooves 2a.
- the intersection between the upper surface and the peripheral surface of the roller 6 and the intersection between the bottom surface and the peripheral surface are rounded 6a. Since the dimension L in the axial direction of the roller 6 is smaller than the diameter D of the roller 6, the roller 6 is biased during the rolling motion S and the roundness 6a of the roller 6 contacts the relief grooves lb, 2b. There is. When a preload is applied to the roller 6, this bias phenomenon tends to occur.
- the round radius of the clearance grooves lb, 2b is set to be larger than the round radius of the roller 6 so that resistance is not generated when the roller 6 is biased and does not hinder the rotation of the roller 6. Also, by forming the relief grooves lb and 2b, it is not necessary to cut the pointed end of the V-groove, so that the cutting workability is of course improved.
- FIG. 5 shows the return pipe 4 attached to the nut member 2.
- a plurality of return pipes 4 are attached to the nut member 2 corresponding to the roller rows to be circulated.
- the return pipe 4 connects one end and the other end of the load roller rolling path 3, and returns the roller 6 that has rolled to one end of the load roller rolling path 3 to the other end of the load roller rolling path 3 several turns before.
- Inside the return pipe 4 a roller return path 5 having a square cross section is formed along the axial direction.
- the return pipe 4 has a central portion 14 extending linearly, and a pair of ends 15 bent at about 90 ° on both sides of the central portion, and the entire shape thereof is formed in a gate shape.
- the end portion 15 includes an arc portion 15a having a constant curvature and a linear tip portion 15b extending from the arc portion 15a.
- the tip 15b is inclined in the lead angle direction and in the opposite direction to each other when viewed from the side of the screw shaft 1.
- the tip portion 15b faces the tangential direction of the load roller rolling path.
- the tip 28 of the end of the return pipe 4 extends to a horizontal plane 17 including the axis of the screw shaft 1.
- the axis of the roller 6 is inclined by the lead angle.
- the posture of the rollers 6 when the rollers 6 are guided from the load roller rolling path 3 into the return pipe 4 and when the rollers 6 are returned from the return pipe 4 to the load roller rolling path 3 are extremely low. It is important.
- the attitude of the roller 6 changes when entering the load roller rolling path 3 from the return pipe 4.
- the roller 6 can be smoothly returned to the load roller rolling path 3 without any occurrence (no so-called skew in which the axis of the roller 6 is inclined). Further, the roller 6 can be smoothly guided from the load roller rolling path 3 into the return pipe 4.
- an arch-shaped cut 18 is formed at the tip 15b along the center line of the track of the roller 6.
- the shape of the cut 18 as viewed from the axial direction of the screw shaft 1 is formed in an arc shape.
- a roller guide portion 19 that enters the inside of the thread is formed inside the cut 18 when the axial force of the screw shaft 1 is viewed.
- the cross-sectional shape of the roller return path 5 at the position of the roller guide 19 is formed in a quadrangle, in this embodiment, a square.
- the section in which the cross-sectional shape of the roller return path 5 in a plane orthogonal to the axis of the return pipe 4 is formed in a square becomes longer. For this reason, the gap h in which the roller return path 5 having a square cross section is not formed can be reduced, and the continuity of the cross-sectional shapes of the load roller rolling path 3 and the roller return path 5 can be improved.
- FIG. 6 shows a spacer 31 interposed between the rollers 6.
- curved concave portions 31 a, 31 a are formed so as to conform to the outer peripheral surface of the adjacent roller 6 and slidably contact the outer peripheral surface of the roller 6.
- the curved concave portions 31a, 31a are formed so that the rollers can be arranged crosswise, and the radius of curvature thereof is set slightly larger than the radius of the roller 6.
- FIG. 7 shows a roller screw according to a second embodiment of the present invention.
- the basic configurations of the screw shaft 1, the nut member 2, and the roller 6 are the same as those in the first embodiment, and thus the same reference numerals are given and the description thereof will be omitted.
- one pitch P2 of the central groove 22 in the central portion of the loaded ball rolling groove 2a of the nut member 2 is set slightly larger than the pitch P1 of the screw shaft.
- the pitch P3 of the end grooves 23, 24 on both sides of the center groove 22 is set equal to the pitch P1 of the screw shaft.
- a preload load (compressive load) indicated by (1) in the figure is applied to the roller 6 on the end groove 23 side.
- a preload (compression load) indicated by (2) in the figure is applied to the roller 6 on the side of the end groove 24.
- rollers 6 are arranged in a cross so that the axes of the adjacent rollers are orthogonal to each other. Also not shown However, the roller 6 rolling between the roller rolling groove la of the screw shaft 1 and the load roller rolling groove 2a of the nut member 2 is circulated by a return pipe.
- FIG. 8 and FIG. 9 show a roller screw according to the third embodiment of the present invention.
- FIG. 8 is a plan view of the nut member
- FIG. 9 is an enlarged sectional view of the roller screw to which a preload is applied.
- the nut member 2 is axially separated by two separating nuts 12, 12, and a shim 13 is interposed between the two separating nuts 12, 12.
- the configurations of the screw shaft 1, the separation nut 12 (corresponding to the nut member 2 of the first embodiment), the roller 6, and the return pipe 4 are substantially the same as those of the roller screw of the first embodiment, and therefore are the same. The description is omitted by attaching reference numerals.
- the pitch of the loaded roller rolling grooves 2a of the separation nuts 12, 12 is equal to the pitch of the roller rolling grooves la of the screw shaft 1.
- P2 n X Pl + al (al: thickness of the shim, P1: Pitch of the load roller rolling groove la, n: any integer). Since the pitch P1 of the load roller rolling grooves la of the screw shaft 1 is always constant, the distance P2 between the load roller rolling grooves 2a, 2a on both sides of the shim 13 is determined by the presence of the shim 13. It will be S wide by the thickness.
- a preload (compression load) shown in (1) in the drawing is applied to the roller 6 in one separation nut 12, and a roller (2) in the drawing is applied to the roller 6 in the other separation nut 12.
- Preload compression load
- a highly rigid roller screw can be obtained.
- the plurality of rollers 6 are arranged in a so-called parallel manner so that the axis of the rollers 6 faces in the same direction when viewed from the traveling direction of the rollers.
- the roller 6 in one separation nut 12 is moved from the traveling direction of the roller 6 with respect to the roller 6 in the other separation nut 12 so that preloads (1) and (2) in opposite directions can be applied. They are arranged so that their axes are orthogonal.
- the rollers 6 rolling between the roller rolling groove la of the screw shaft 1 and the load roller rolling groove 2a of the nut member 2 are circulated by a return pipe.
- the rollers 6 may be arranged in a cross arrangement, and the rollers arranged in a cross arrangement may be circulated through a return pipe.
- the embodiment of the present invention can be variously modified without changing the gist of the present invention.
- the present invention can be applied to a roller screw of a type that does not include a force that circulates a roller through a return pipe and does not circulate the roller.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA002541770A CA2541770A1 (en) | 2003-10-20 | 2004-09-06 | Roller screw |
JP2005514717A JPWO2005038301A1 (ja) | 2003-10-20 | 2004-09-06 | ローラねじ |
US10/576,019 US20070137347A1 (en) | 2003-10-20 | 2004-09-06 | Roller screw |
EP04787649A EP1679454A4 (en) | 2003-10-20 | 2004-09-06 | ROLLER SCREW |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003-360042 | 2003-10-20 | ||
JP2003360042 | 2003-10-20 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005038301A1 true WO2005038301A1 (ja) | 2005-04-28 |
Family
ID=34463399
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/012945 WO2005038301A1 (ja) | 2003-10-20 | 2004-09-06 | ローラねじ |
Country Status (8)
Country | Link |
---|---|
US (1) | US20070137347A1 (ja) |
EP (1) | EP1679454A4 (ja) |
JP (1) | JPWO2005038301A1 (ja) |
KR (1) | KR20060103256A (ja) |
CN (1) | CN1871460A (ja) |
CA (1) | CA2541770A1 (ja) |
TW (1) | TW200519306A (ja) |
WO (1) | WO2005038301A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2020508424A (ja) * | 2017-02-27 | 2020-03-19 | コンセプト アンド デザイン リミテッド | ガタ防止装置および方法 |
WO2020217346A1 (ja) * | 2019-04-24 | 2020-10-29 | 三菱電機株式会社 | 送りネジ機構、及びアクチュエータ |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8272289B2 (en) * | 2004-09-08 | 2012-09-25 | Thk Co., Ltd. | Roller screw |
CN102124251A (zh) * | 2009-08-31 | 2011-07-13 | 日本精工株式会社 | 滚珠丝杠装置 |
JP5951873B2 (ja) | 2014-12-26 | 2016-07-13 | Thk株式会社 | ボールねじ |
CN106609819A (zh) * | 2015-10-21 | 2017-05-03 | 王心成 | 一种外循环交叉滚子丝杆副及使用方法 |
JP6704827B2 (ja) * | 2016-09-30 | 2020-06-03 | 日本電産サンキョー株式会社 | 直線駆動装置 |
WO2019078105A1 (ja) * | 2017-10-19 | 2019-04-25 | Thk株式会社 | 予圧検知可能なねじ装置 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0687764U (ja) | 1993-06-02 | 1994-12-22 | 株式会社エノモト | 送りねじ軸系 |
JPH11210858A (ja) | 1998-01-19 | 1999-08-03 | Koyo Mach Ind Co Ltd | 循環式ねじ装置 |
JP2002161961A (ja) * | 2000-11-27 | 2002-06-07 | Koyo Seiko Co Ltd | ボールねじ装置および無段変速機 |
JP2002276765A (ja) * | 2001-03-21 | 2002-09-25 | Ntn Corp | ダブルナット予圧式ボールねじ |
JP2003194177A (ja) * | 2001-12-26 | 2003-07-09 | Nsk Ltd | ボールねじ |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1290245A (fr) * | 1961-02-28 | 1962-04-13 | Perfectionnements aux assemblages vis-écrou | |
US3192791A (en) * | 1962-06-07 | 1965-07-06 | Textron Inc | Antifriction screw and nut assembly |
US4896552A (en) * | 1988-01-19 | 1990-01-30 | Ballscrews & Actuators Co., Inc. | Ballscrew follower and method of making and operating the same |
JP4475442B2 (ja) * | 2000-02-28 | 2010-06-09 | Thk株式会社 | ローラねじおよびローラねじのローラ配列方法 |
DE602004031348D1 (de) * | 2003-09-10 | 2011-03-24 | Thk Co Ltd | Rollspindel |
JPWO2005038300A1 (ja) * | 2003-10-20 | 2007-11-22 | Thk株式会社 | ローラねじ |
US8272289B2 (en) * | 2004-09-08 | 2012-09-25 | Thk Co., Ltd. | Roller screw |
-
2004
- 2004-09-06 US US10/576,019 patent/US20070137347A1/en not_active Abandoned
- 2004-09-06 JP JP2005514717A patent/JPWO2005038301A1/ja active Pending
- 2004-09-06 WO PCT/JP2004/012945 patent/WO2005038301A1/ja active Application Filing
- 2004-09-06 KR KR1020067007479A patent/KR20060103256A/ko not_active Application Discontinuation
- 2004-09-06 CA CA002541770A patent/CA2541770A1/en not_active Abandoned
- 2004-09-06 EP EP04787649A patent/EP1679454A4/en not_active Withdrawn
- 2004-09-06 CN CNA200480030796XA patent/CN1871460A/zh active Pending
- 2004-10-15 TW TW093131343A patent/TW200519306A/zh unknown
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0687764U (ja) | 1993-06-02 | 1994-12-22 | 株式会社エノモト | 送りねじ軸系 |
JPH11210858A (ja) | 1998-01-19 | 1999-08-03 | Koyo Mach Ind Co Ltd | 循環式ねじ装置 |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2020508424A (ja) * | 2017-02-27 | 2020-03-19 | コンセプト アンド デザイン リミテッド | ガタ防止装置および方法 |
JP7162608B2 (ja) | 2017-02-27 | 2022-10-28 | コンセプト アンド デザイン リミテッド | ガタ防止装置および方法 |
WO2020217346A1 (ja) * | 2019-04-24 | 2020-10-29 | 三菱電機株式会社 | 送りネジ機構、及びアクチュエータ |
JPWO2020217346A1 (ja) * | 2019-04-24 | 2021-09-13 | 三菱電機株式会社 | 送りネジ機構、及びアクチュエータ |
Also Published As
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CA2541770A1 (en) | 2005-04-28 |
CN1871460A (zh) | 2006-11-29 |
JPWO2005038301A1 (ja) | 2007-11-22 |
EP1679454A4 (en) | 2010-03-24 |
EP1679454A1 (en) | 2006-07-12 |
TW200519306A (en) | 2005-06-16 |
US20070137347A1 (en) | 2007-06-21 |
KR20060103256A (ko) | 2006-09-28 |
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