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WO2004044444A1 - Dispositif de guidage de mouvement, vis a billes et realisation d'un chemin de roulement pour billes - Google Patents

Dispositif de guidage de mouvement, vis a billes et realisation d'un chemin de roulement pour billes Download PDF

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Publication number
WO2004044444A1
WO2004044444A1 PCT/JP2003/014253 JP0314253W WO2004044444A1 WO 2004044444 A1 WO2004044444 A1 WO 2004044444A1 JP 0314253 W JP0314253 W JP 0314253W WO 2004044444 A1 WO2004044444 A1 WO 2004044444A1
Authority
WO
WIPO (PCT)
Prior art keywords
ball
rolling groove
ball rolling
pole
guide device
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/JP2003/014253
Other languages
English (en)
Japanese (ja)
Inventor
Takeki Shirai
Yuuji Tachikake
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
Original Assignee
THK Co Ltd
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 filed Critical THK Co Ltd
Priority to DE10393641T priority Critical patent/DE10393641T5/de
Publication of WO2004044444A1 publication Critical patent/WO2004044444A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/005—Guide rails or tracks for a linear bearing, i.e. adapted for movement of a carriage or bearing body there along
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B19/00—Single-purpose machines or devices for particular grinding operations not covered by any other main group
    • B24B19/02—Single-purpose machines or devices for particular grinding operations not covered by any other main group for grinding grooves, e.g. on shafts, in casings, in tubes, homokinetic joint elements
    • B24B19/06—Single-purpose machines or devices for particular grinding operations not covered by any other main group for grinding grooves, e.g. on shafts, in casings, in tubes, homokinetic joint elements for grinding races, e.g. roller races
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/04—Ball or roller bearings
    • F16C29/06—Ball or roller bearings in which the rolling bodies circulate partly without carrying load
    • F16C29/0633—Ball or roller bearings in which the rolling bodies circulate partly without carrying load with a bearing body defining a U-shaped carriage, i.e. surrounding a guide rail or track on three sides
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/76—Osculation, i.e. relation between radii of balls and raceway groove

Definitions

  • the present invention relates to a method for manufacturing a motion guide device, a pole screw and a ball rolling groove.
  • the present invention relates to a motion guide device that guides a linear motion or a rotary motion of a guided object, in which a plurality of poles that perform rolling motion are interposed between a track member and a moving member, or between a screw shaft and a nut.
  • the present invention relates to a ball screw in which a plurality of rolling balls are interposed.
  • a pole rolling groove is formed on a track member and a moving member of the motion guide device so as to be a track of a rolling ball.
  • Various forms are applied to the ball rolling grooves depending on the intended load receiving method.
  • FIG. 12 shows a cross section of the ball rolling groove.
  • the two main types of ball rolling grooves are circular arc grooves and gothic arch grooves.
  • the cross section of one circular groove is made of one circular arc.
  • the contact point of the ball It is called two-point contact because there are two points.
  • the cross-sectional shape of the Gothic arch groove is composed of two arcs, so that the ball contacts usually have four four-point contact structures (for example, see Non-Patent Document 1). .
  • each contact is a point contact where the ball and the smooth curved surface come into contact.
  • the load capacity of each ball is uniquely determined by the geometrical shape and material of the ball and the ball rolling groove. Therefore, in order to increase the load capacity by using balls of the same material and dimensions, a method has been adopted in which the radius of curvature of the ball rolling groove approaches the radius of the ball.
  • reducing the radius of curvature between the ball and the pole rolling groove increased the precision required for machining, and also caused industrial disadvantages such as increased costs.
  • an object of the present invention is to provide a motion guide device, a ball screw, and a method of manufacturing the same, which can increase the load capacity without making the radius of curvature of the pole rolling groove close to the radius of the ball. I do.
  • the present inventor has formed a plurality of convex portions which can be deformed in the direction in which the ball rolling grooves extend in the vicinity of the contact points of the pole rolling grooves, thereby forming a plurality of poles receiving the load.
  • the projections of the strip were in contact with each other. That is, the invention according to claim 1 is a movement in which a ball rolling groove is formed on at least one of the track member and the moving member, the ball rolling groove being a track when a ball interposed between the track member and the moving member rolls.
  • the ball rolling groove is formed with a plurality of elastically deformable protrusions extending uniformly in a direction in which the pole rolling groove extends, and a load is applied between the track member and the moving member.
  • the contact point between the ball and the ball rolling groove comes into contact at a plurality of points instead of at one point, the load on the ball is distributed at each point, and the ball is loaded at a specific point. High stress concentration can be suppressed.
  • the plurality of convex portions extend uniformly in the direction in which the pole rolling groove extends, when the pole rolls, the direction of the rotation axis of the ball is changed and the rotation of the ball is changed. Does not work. Therefore, whether the ball touches at one point or many points has little effect on the ball's rolling resistance.
  • the ⁇ portion is elastically deformed by the load so that the ball comes into contact with the depression.
  • the convex portion is elastically deformed, and a wide contact area between the pole and the ball rolling groove is ensured, so that the ball rolling groove has a wide rail load area.
  • the motion guide device of the present invention is a linear or curved motion guide device in which a moving member is slidably attached to a track member that extends linearly or in a curved line, or an annular track member in which an annular moving member is rotatable. It can be suitably used for the found rolling bearing.
  • the present invention also provides a ball screw in which a helical ball rolling groove is formed on a screw shaft and a nut, the helical ball rolling groove serving as a trajectory when the ball interposed between the screw shaft and the nut is rolled.
  • the rolling groove is formed with a plurality of elastically deformable convex portions that extend uniformly in the direction in which the spiral pole rolling groove extends, and receives a load between the track member and the moving member.
  • the pole may be configured as a ball screw that comes into contact with the plurality of protrusions before contacting the depression between the plurality of protrusions.
  • the present invention provides a method of manufacturing a ball rolling groove, wherein at least one of a track member and a moving member forms a ball rolling groove which becomes a track when a ball interposed between the track member and the moving member rolls.
  • a disk-shaped blade or grindstone having a smaller radius than the ball is moved in a direction in which the ball rolling groove extends, and the outer peripheral shape of the blade or grinding wheel is transferred to the pole rolling groove.
  • the depression between the plurality of protrusions has a radius of curvature smaller than the radius of the ball, so that the contact point between the ball and the ball rolling groove is not at one point but at a plurality of points.
  • FIG. 1 A perspective view of the motion guide device (linear guide) according to the first embodiment of the present invention. Figure (including partial cross section).
  • Fig. 2 is a cross-sectional view of the endless circuit along the direction in which the endless circuit of the motion guide device extends.
  • FIG. 3 Cross-sectional view of the ball rolling groove in a plane perpendicular to the direction in which the ball rolling groove extends.
  • Fig. 4 Diagram showing the distribution of generated stress (Von Mses stress) (when the pole and the smooth surface are in contact at one point).
  • Fig. 5 Diagram showing the distribution of generated stress (Von Mses stress) (when the ball and the smooth surface come in contact at two points).
  • Fig. 6 Diagram showing the distribution of the generated shearing force (XY shear) (when the ball and the smooth surface make contact at one point).
  • Fig. 7 Diagram showing the distribution of the generated shear force (XY shear) (when the ball and the smooth surface come in contact at two points).
  • Figure 8 Diagram showing the manufacturing method of the pole rolling groove (cross-sectional view in a direction perpendicular to the pole rolling groove).
  • FIG. 9 is a perspective view of a motion guide device (ball spline) according to a second embodiment of the present invention.
  • FIG. 10 is a perspective view of a ball screw according to a third embodiment of the present invention.
  • FIG. 11 is a cross-sectional view of a radial rolling bearing according to a fourth embodiment of the present invention.
  • Fig. 12 Cross-sectional view of a conventional general ball rolling groove ((A) in the figure shows the circuit groove, and (B) shows the Gothic arch groove).
  • FIG. 1 is a perspective view of a motion guide device according to a first embodiment of the present invention.
  • the lower guide includes a track rail 1 as a track member, and a moving block 3 as a moving member slidably mounted on the track rail 1 via a number of poles 2.
  • the track rail 1 is a long member whose cross section orthogonal to the longitudinal direction is formed in a substantially rectangular shape, and has a ball rolling groove 1a on its upper surface and both side surfaces which is a track for rolling the ball. Are formed over the entire length of the orbital rail 1.
  • the track rail 1 may be formed to extend linearly or may be formed to extend in a curved line.
  • the number of pole rolling grooves 1a is four in total, two on each side, but the number can be variously changed depending on the application of the linear guide.
  • the moving block 3 is also provided with pole rolling grooves 3a, which oppose the ball rolling grooves 1a, respectively.
  • Load rolling paths 1 2 are formed between the pole rolling grooves 1 a of the track rail 1 and the pole rolling grooves 3 a of the moving block 3, and a plurality of balls 2 are sandwiched therebetween.
  • the moving block 3 is provided with four return paths 13 extending in parallel with each ball rolling groove 1a, and a direction change path connecting each return path 13 and each load rolling path 1 2 ... ing.
  • One infinite circulation path is composed of a combination of one turning path 5 and return path 13 and a pair of turning paths 5 connecting them (see Fig. 2).
  • FIG. 2 shows a cross-sectional view of the infinite circuit along the extending direction of the infinite circuit.
  • Each of the infinite circulation paths is loaded with a large number of balls 2.
  • the connecting body 8 has a large number of spacers 4 provided at predetermined intervals, and a pair of belt portions 10, 10 connecting the spacers 4 on both sides thereof.
  • the pole 2 is housed and held between the parts 4,4.
  • the surface of the spacer 4 facing the ball 2 is spherically concave in accordance with the pole 2. This prevents contact between the poles 2 and 2 and enables smooth circulation of the poles 2 in the infinite circulation path.
  • the ponole 2 rolls on the load rolling path 12 from one end to the other while receiving a load, and then moves to one of the direction changing paths 5. It is scooped up, guided to the return path 13, and further returned to one end of the load rolling path 12 via the direction change path 5 on the opposite side.
  • FIG. 3 shows a sectional view of the pole rolling groove 1a in a plane perpendicular to the direction in which the pole rolling groove 1a extends.
  • the ball rolling groove 1a which is a track on which the ball 2 normally rolls, has a smooth surface and has a shape as close as possible to a geometric arc.
  • a plurality of protrusions 7 extending in the direction in which the pole rolling groove 1a extends are formed near the contact point between the ball 2 and the ball rolling groove 1a.
  • the projections 7 are not random irregularities such as roughness, but the direction in which the ball 2 travels (the direction perpendicular to the paper surface).
  • the outline of the ball rolling groove 1a on which the convex portions 7 are formed may be formed in a circular arc groove, may be formed in a Gothic arch groove, or may be formed in a smooth plane. .
  • a load acts on the pole 2 interposed between the track rail 1 and the moving block 3.
  • the pole receiving the load contacts a plurality of protrusions 7 before contacting the depression 39 between the protrusions 7.
  • the ball 2 contacts only the pair of projections 7, 7 and the depression between the projections 7, 3.
  • the plurality of protrusions 7, 7 are elastically deformed, and the ball 2 also comes into contact with the depression 39 between the protrusions 7, 7.
  • the pole 2 contacts the depression 13 between the projections 7, 7, the projections 7 are elastically deformed but not plastically deformed. Therefore, when the load is removed from the ball 2, the convex portions 7 are restored as shown in FIG.
  • the pitch of the convex portions 7 is determined, for example, as follows. There is a contact area between the ball 2 and the ball rolling groove 1a which is expected in the assumed load, for example, the basic static load rating. The pitch of the projections 7 is set such that the three or four projections 7 contact the ball 2 in this contact area.
  • the basic static load rating is the sum of the permanent deformation amount of the pole 2 and the permanent deformation amount of the ball rolling groove 1a at the contact part where the maximum stress is applied. A static load with a fixed direction and magnitude that increases by a factor of 0.00.
  • the plurality of convex portions 7 play a role like a rail, and the ball 2 rolls on the rail.
  • the ball 2 rolls in the ball rolling groove 1a
  • the ball 2 has a rotation axis 14 in a direction orthogonal to the moving direction.
  • friction acts on the contact point between the ball 2 and the ball rolling groove 1a.
  • the ball 2 comes into contact with the pair of projections 7 at two points, Does the force that binds 14 work? Therefore, even if the projections 7 are provided, the influence on the resistance in the rolling direction of the pole 2 is small.
  • the load applied to the ball 2 is received at multiple points rather than at one point, the contact area expands faster for the load, and the load capacity is proportional to the increase in the contact area. Can be larger.
  • Figures 4 to 7 show the results of FEM (finite element method) analysis of the stress and shear force generated when the pole and the smooth surface make contact at one point and when they make contact at two points.
  • FEM finite element method
  • Figures 4 and 5 show the distribution of the generated stress (Von Mses stress).
  • Fig. 4 shows a normal case where the pole and the smooth surface make contact at one point
  • Fig. 5 shows a case where the ball and the projection make contact at two points. The same hatching is applied to portions where the magnitude of the stress is equal.
  • Figures 6 and 7 show the distribution of the generated shear force (XY shear).
  • Fig. 6 shows the case where the ball and the smooth surface make contact at one point, as usual, and
  • Fig. 7 shows the case where the ball and the projection make contact at two points. The same hatching is applied to the parts with the same shear force.
  • FIG. 8 shows a method of manufacturing the ball rolling groove 1a.
  • a disk-shaped grindstone 15 having a smaller radius than the radius of the ball 2 is prepared.
  • roll the ball while rotating whetstone 15 Move in the direction in which the groove la extends (in the direction perpendicular to the paper surface), and make the ball rolling groove 1a on the outer peripheral surface of the grindstone 15; Grind from the ffiil opening surface to the rolling surface, and form the outer peripheral shape of the grindstone 15 Is transferred to the ball rolling groove 1a.
  • a certain interval is set in a plane orthogonal to the direction in which the ball rolling groove 1a extends so that the position of the grinding wheel 15 is aligned with the grinding wheel position of No. 10 from the grinding wheel position of No.
  • FIG. 9 is a perspective view of a motion guide device according to a second embodiment of the present invention. This figure shows a pole spline as a linear motion guide device.
  • the ball spline has a spline shaft 21 as a track member, and an outer cylinder 23 as a moving member movably attached to the spline shaft 21 via a number of balls 22.
  • ball rolling grooves 21 a Extending in the axial direction of the spline shaft 21.
  • a pole rolling groove corresponding to the pole rolling groove 21 a is formed in the outer cylinder 23 attached to the spline shaft 21.
  • a plurality of convex portions extending in the direction in which the ball rolling grooves 21a ... extend.
  • FIG. 10 is a perspective view of a pole screw according to the third embodiment of the present invention.
  • the screw shaft 31 is formed with a ball rolling groove 31a having a substantially semicircular cross section and a constant spiral lead around the screw shaft 31.
  • a pole rolling groove 32a having a substantially semicircular cross section is formed to face the ball rolling groove 31a of the screw shaft 31.
  • a plurality of spiral convex portions extending in the direction in which the ball rolling grooves 31 a and 32 a extend are formed.
  • a plurality of balls 34 are accommodated in the pole rolling path between the ball rolling groove 31 a of the screw shaft 31 and the ball rolling groove 32 a of the nut 32.
  • Circulation parts 33, 33 are attached to the nut 32.
  • the circulating parts 3 3, 3 3 form a no-load return passage connecting one end of the ball rolling path to the other end, and allow a plurality of balls 3 4... to move relative to the nut 3 2 with respect to the screw shaft 3 1. Circulate together.
  • FIG. 11 is a sectional view of a radial type rolling bearing according to a fourth embodiment of the present invention.
  • An inner race 42 as an annular moving member is rotatably mounted on the outer race 41 as an annular race member.
  • Ball rolling grooves 41a and 42a are formed on the outer ring 41 and the inner ring 42, respectively.
  • the ball 43 is sandwiched between the ball rolling grooves 41a and 42a.
  • a plurality of annular convex portions extending in the direction in which the ball rolling grooves extend are formed in these pole rolling grooves 41a and 42a.
  • the radial type rolling bearing has been described.
  • the ball rolling groove in which a plurality of convex portions are formed may be used for a thrust type rolling bearing.
  • the present invention is not limited to the above-described embodiment, and can be variously changed without changing the gist of the present invention.
  • the ball rolling groove in which a plurality of convex portions are formed may not be formed in both the track member and the moving member, or may be formed in either one.
  • a plurality of protrusions extending in the direction in which the ball rolling groove extends are formed near the contact point of the pole rolling groove, and the ball and the plurality of protrusions are formed by the load acting on the ball. Since the protruding portions are in contact with each other, the load on the ball is distributed and applied to each point, and high stress concentration at a specific point can be suppressed. Therefore, the load capacity can be increased without making the radius of curvature of the ball rolling groove close to the radius of the pole.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Bearings For Parts Moving Linearly (AREA)
  • Transmission Devices (AREA)
  • Grinding And Polishing Of Tertiary Curved Surfaces And Surfaces With Complex Shapes (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

Cette invention concerne un dispositif de guidage de mouvement dont la capacité de charge est accru que le rayon de courbure des gorges de roulement des billes ne se rapproche du rayon des billes. Les gorges de roulement des billes sont réalisées dans un chemin de roulement et un bloc mobile de guidage linéaire, lesdites gorges de roulement servant de chemins de roulement dans lesquels les billes sont interposées entre un élément de chemin de roulement et un rouleau d'élément mobile. Des lignes à déformation élastique d'arêtes orientées dans le sens des gorges de roulement sont formées à proximité des points de contact avec les billes. Ainsi, la charge agissant sur les billes met ces dernières en contact avec les lignes d'arêtes. La charge s'exerçant sur les billes est répartie sur chaque point des arêtes, ce qui empêche la concentration d'efforts élevés sur un point précis. Par voie de conséquence, la capacité de charge du dispositif peut être accrue sans que le rayon de courbure des gorges de roulement des billes ne se rapproche du rayon des billes
PCT/JP2003/014253 2002-11-11 2003-11-10 Dispositif de guidage de mouvement, vis a billes et realisation d'un chemin de roulement pour billes Ceased WO2004044444A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE10393641T DE10393641T5 (de) 2002-11-11 2003-11-10 Bewegungsführungsvorrichtung, Kugelumlaufspindel und Verfahren zum Formen einer Kugellaufrille

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002326800A JP2004162748A (ja) 2002-11-11 2002-11-11 運動案内装置、ボールねじ及びボール転走溝の製造方法
JP2002-326800 2002-11-11

Publications (1)

Publication Number Publication Date
WO2004044444A1 true WO2004044444A1 (fr) 2004-05-27

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ID=32310504

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2003/014253 Ceased WO2004044444A1 (fr) 2002-11-11 2003-11-10 Dispositif de guidage de mouvement, vis a billes et realisation d'un chemin de roulement pour billes

Country Status (3)

Country Link
JP (1) JP2004162748A (fr)
DE (1) DE10393641T5 (fr)
WO (1) WO2004044444A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020211329A1 (de) * 2020-09-09 2022-03-10 Aktiebolaget Skf Lageranordnung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0388653U (fr) * 1989-12-28 1991-09-10
JPH03107518U (fr) * 1990-02-22 1991-11-06
JPH0647729U (ja) * 1992-10-14 1994-06-28 日本トムソン株式会社 転がり案内ユニット
JP2002039190A (ja) * 2000-07-28 2002-02-06 Koyo Seiko Co Ltd ４点接触玉軸受
JP2002276765A (ja) * 2001-03-21 2002-09-25 Ntn Corp ダブルナット予圧式ボールねじ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0388653U (fr) * 1989-12-28 1991-09-10
JPH03107518U (fr) * 1990-02-22 1991-11-06
JPH0647729U (ja) * 1992-10-14 1994-06-28 日本トムソン株式会社 転がり案内ユニット
JP2002039190A (ja) * 2000-07-28 2002-02-06 Koyo Seiko Co Ltd ４点接触玉軸受
JP2002276765A (ja) * 2001-03-21 2002-09-25 Ntn Corp ダブルナット予圧式ボールねじ

Also Published As

Publication number Publication date
JP2004162748A (ja) 2004-06-10
DE10393641T5 (de) 2005-10-06

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