WO2006104015A1 - ボールねじ - Google Patents
ボールねじ Download PDFInfo
- Publication number
- WO2006104015A1 WO2006104015A1 PCT/JP2006/305850 JP2006305850W WO2006104015A1 WO 2006104015 A1 WO2006104015 A1 WO 2006104015A1 JP 2006305850 W JP2006305850 W JP 2006305850W WO 2006104015 A1 WO2006104015 A1 WO 2006104015A1
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- WO
- WIPO (PCT)
- Prior art keywords
- ball
- groove
- ball screw
- screw
- nut
- Prior art date
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Classifications
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- 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
- F16C33/37—Loose spacing bodies
- F16C33/3706—Loose spacing bodies with concave surfaces conforming to the shape of the rolling elements, e.g. the spacing bodies are in sliding contact with the rolling elements
-
- 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
-
- 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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- 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
- F16H2025/2242—Thread profile of the screw or nut showing a pointed "gothic" arch in cross-section
-
- 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
- F16H2025/249—Special materials or coatings for screws or nuts
-
- 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
-
- 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
- Y10T74/19777—Interconnected or cooperating rollers or roller structure
Definitions
- the present invention relates to a ball screw, and particularly for an actuator, for example, a ball screw and a linear guide that are used in industrial machines such as an electric injection molding machine and a press machine and are used at high loads. It relates to a linear motion device such as.
- Ball screws used in electric injection molding apparatuses, electric press apparatuses, and the like are used under severe conditions under extremely short loads and reciprocating movements with a relatively short stroke. Therefore, the peeling life due to repeated stress on the raceway surface becomes a problem.
- the ball diameter is made as large as possible, the radius of curvature of the raceway surface is made as close as possible to the ball diameter, and the contact surface pressure is lowered to suppress repeated stress values, thereby reducing the required life. It will be fulfilled.
- the slip component is large due to a geometric problem that the ball rolls on a spiral track. Due to the size of the sliding component, in a general ball screw with a lead angle of 15 degrees or less, the ratio of the radius (R) of the arc that forms the cross section of the groove to the ball diameter (D) (RZD) 52% In the following, as represented by white peeling, there was a problem that the life would be shortened, so R / D was usually set to 52% or more and 54% or less.
- the first background art is a relatively large ball screw used in a conventional electric injection molding machine, a press machine, etc., and a high load. It is used in the harsh condition where it is used in a rooke, and after stopping once with the maximum load applied, it moves backwards and backwards.
- the ball surface hardness of the ball screw that secures positioning accuracy by applying a preload between the ball and the ball screw groove of the screw shaft and the ball screw groove of the nut is increased.
- the wear resistance of the ball is improved by making it higher than the surface hardness of the ball screw groove of the screw shaft and the ball screw groove of the nut (see Patent Document 1).
- MoS molybdenum disulfide
- a film is also formed to improve wear resistance!
- Patent Document 2 fine particles of molybdenum disulfide molybdenum are sprayed and fixed to at least one sliding contact portion of a screw shaft screw groove, a nut screw groove, and a ball.
- Ball screws with a lubricant coating with a dimension of 0.5 ⁇ m or less have been proposed.
- FIGS. 14 and 15 an example of a conventional ball screw is shown in FIGS. 14 (perspective view) and 15 (sectional view).
- This ball screw is a tube-type ball screw using a tube as a return path of the ball, and includes a screw shaft 101, a nut 102, a ball 103, and a tube 104.
- Reference numeral 106 in FIG. 14 is a tube presser for fixing the tube 104 to the nut 102. In FIG. 15, the tube retainer 106 is not shown.
- Helical grooves 111, 121 are formed on the outer peripheral surface of the screw shaft 101 and the inner peripheral surface of the nut 102, and the track K of the ball 103 is formed by these grooves 111, 121. And Bo When the nut 103 rolls on the track K in a loaded state, the nut 102 moves linearly relative to the screw shaft 101.
- the tube 104 is formed in a substantially portal shape, and both ends thereof are inserted into through holes 122 provided in the cylinder forming the nut 102, and the screw shaft 101 is connected so as to connect the start point and the end point of the track rod. It is arranged diagonally across. Therefore, the ball 103 that has reached the end point of the track ⁇ ⁇ is returned to the start point of the track ⁇ ⁇ through the tube 104.
- two tubes 104 are provided.
- Ball screws for electric injection molding machines and press machines are relatively large and receive high loads.
- a ball screw for the above-mentioned use has been conventionally used with a single nut and a very small assembly clearance (about 1Z400 as a ratio to the ball diameter).
- the ratio of the radius (R) of the cross-section arc of the grooves 111 and 121 (of the screw shaft 101 and nut 102) to the diameter (D) of the ball 103 ( RZD) may be made smaller than the conventional 52.0 to 54.0%.
- the longer axis of the contact ellipse between the ball and the groove forming the track becomes longer than that of the conventional ball screw, and the slip component becomes larger.
- the tangential force in the contact ellipse increases, it is impossible to deny the possibility of surface-origin separation or internal origin delamination due to white texture.
- the ball screw has a slower rolling speed than a general rolling bearing such as a ball bearing, it is difficult to form an oil film. Therefore, when the ratio (RZD) is made smaller than 52.0 to 54.0% with a ball screw, it is necessary to take measures to prevent premature damage.
- Patent Document 3 describes that a specific grease is used to prevent early peeling of the ball screw used in the drive system of the electric injection molding machine.
- Patent Document 4 At least a part of the rolling friction surface and sliding friction surface of a machine part using a ball is softened with gold, silver, lead, zinc, tin (Sn), indium or the like. It is disclosed that fine particles made of carbonaceous metal, polytetrafluoroethylene (PTFE), perfluoroalkoxy fluorine resin (PTA), etc. are sprayed together with air from a nozzle cover to form a solid lubricating film. Yes.
- PTFE polytetrafluoroethylene
- PTA perfluoroalkoxy fluorine resin
- FIG. 1 is a top view showing an example of a ball screw which is one of linear motion devices
- FIG. 2 is a cross-sectional view taken along AA in FIG.
- the ball screw 1 includes a screw shaft 3 having a male screw groove 3a formed on the outer peripheral portion, a cylindrical nut 7 which is a linear motion body having a female screw groove 5 formed on the inner peripheral surface, and a male screw. It is composed of a plurality of balls 9 interposed between the groove 3a and the female thread groove 5.
- the nut 7 moves linearly along the axial direction of the screw shaft 3, and has a cylindrical shape.
- a flange 11 for fixing to a table (not shown) of the apparatus is formed at one end.
- a part of the outer peripheral surface is cut away to form a flat portion 13.
- a female screw groove 5 having the same shape and pitch as the male screw groove 3a is formed on the inner peripheral surface of the nut 7, and a tube 15 serving as a circulation path by connecting one end side and the other end side of the female screw groove 5 is provided. It is fixed to the flat surface portion 13 by a tube presser 17. Then, the ball 9 is transferred through the tube 15, and the ball 9 is circulated to the other end side by the force on one end side of the female screw groove 5.
- plastic dust seals 19 are disposed at both ends of the nut 7 to prevent foreign matter from entering the nut 7 from the outside.
- a holding piece 21 is generally inserted between the balls 9 and 9.
- the holding piece 21 in which the contact surface 11 with the ball 9 is formed in a concave spherical shape between the balls 9 and 21. Is inserted.
- a polyamide such as 66 nylon and a synthetic resin such as fluorine resin are generally used (see Patent Document 5).
- a ball screw used in an electric injection molding machine or a press machine is relatively large and is loaded with a high load. The It is used under harsh conditions, such as when it is stopped with the maximum load applied, and then reverse rotation (reciprocating motion).
- such a ball screw is designed such that the diameter of the ball is larger than the diameter of the screw shaft in order to increase the load capacity. Therefore, as the ball diameter increases, the kinetic energy of the ball also increases, and the influence of the ball on the ball return path increases.
- the inner surface of the ball return path may be worn or peeled off, resulting in poor circulation of the ball.
- the wear powder and peeling powder act as foreign matters, early peeling occurs in the thread groove and the ball, and the ball screw may have a short life.
- a ball screw in which a circulating member corresponding to the above-described ball return path is formed of a solid lubricant.
- a ball screw can be suitably used in an environment where normal lubrication with a lubricating oil or grease is difficult. (See Patent Document 7)
- Patent Document 1 JP 2000-346162
- Patent Document 2 JP 2004-60742
- Patent Document 3 Japanese Patent Laid-Open No. 2001-49274
- Patent Document 4 Japanese Patent Laid-Open No. 6-109022
- Patent Document 5 Japanese Patent Laid-Open No. 11 315835
- Patent Document 6 Japanese Unexamined Patent Application Publication No. 2004-92787
- Patent Document 7 Japanese Patent Laid-Open No. 62-283252
- RZD is set to 52% or more and 54% or less, but it is extremely large required for a ball screw in an electric injection molding device or an electric press device. As a result, it becomes impossible to sufficiently suppress the surface pressure against the load, and as a result, peeling damage (peeling due to fatigue life) due to repeated stress on the raceway surface occurs early, and the required life is not satisfied. there were.
- the ball surface with RZD of 52% or less is used.
- the problem is that the life of the ball is shortened due to the effect of sliding between the ball and the ball.
- the screw shaft and the ball screw groove of the nut are usually moved in the axial direction while rotating the general-purpose mortar formed in a predetermined cross-sectional shape, so that the mortar shape is changed.
- Complete grinding is performed by transferring and grinding. Therefore, the surface roughness in the perpendicular direction where the turret shape is transferred as it is compared to the roughness in the axial direction is considerably rough, and the surface roughness is generally about 0.3 m.
- balls are finished to a surface roughness of about 0.006 ⁇ m. Therefore, as in Patent Document 1, damage and wear of the ball cannot be avoided simply by making the surface hardness of the ball higher than the surface hardness of the ball screw groove of the screw shaft or the ball screw groove of the nut.
- Patent Document 2 a lubricant film having a disulfide-molybdenum force is formed on the ball, the ball screw groove of the screw shaft, and the ball screw groove of the nut.
- Perspective power of the film The film thickness is defined as 0.5 m or less.
- the present invention has been made paying attention to such a conventional problem, and suppresses damage and wear of the ball as compared with the conventional one, and has a long life and high reliability.
- the electric injection molding apparatus and the electric motor An object of the present invention is to provide a ball screw suitable for a high load application used in a press device or the like.
- the present invention has been made in view of such a situation, and an object thereof is to improve the operability in a linear motion apparatus including a holding piece.
- the present invention solves the problems of the conventional ball screw as described above, and even when used under conditions in which a high load is applied and a torsional moment load acts, wear, separation, etc. It is an object of the present invention to provide a ball screw having a long life due to damage.
- the present invention has the following constitutional power as the first constitution.
- a screw shaft having a spiral groove formed on the outer peripheral surface and a spiral groove formed on the inner peripheral surface A nut, a raceway in which the screw shaft groove and the nut groove are formed to face each other, a return path connecting the end point and the start point of the raceway, a plurality of paths arranged in the return path and in the track
- a ball screw having a ball
- the ratio (R / D) of the radius (R) of the arc forming the cross section of the groove to the diameter (D) of the ball is 51.0% or more and less than 52.0%
- a ball screw wherein a solid lubricant film is formed on at least a surface of at least one of the ball itself or a part in contact with the ball.
- the present invention has the following constitutional power as the second constitution.
- connection path a ball circulation path constituted by the connection path and the ball rolling path, and a plurality of balls accommodated so as to be endlessly arranged in the ball circulation path;
- the surface hardness of the ball is higher than the surface hardness of each of the ball screw groove of the screw shaft and the ball screw groove of the nut, and 1 ⁇ m or more on the surface of the ball.
- a solid lubricant film is formed with a film thickness of ⁇ m or less.
- the present invention has the following constitutional power as the third constitution.
- At least one of the screw shaft and the nut has a Gothic arc cross section of the groove (a shape in which two arcs having the same radius and different centers are connected), and the diameter of the ball (D
- the ratio (RZ D) of the radius (R) of the circular arc is 51.0% or more and less than 52.0%, and the screw shaft groove or nut groove
- at least one of the balls has a solid lubricant film formed on a surface thereof.
- the groove has a Gothic arc cross section, and the ratio (RZD) is 51.0% or more and 52.0% or less. , Can increase the load capacity.
- RZD ratio
- the long axis of the contact ellipse between the ball and the groove forming the track becomes longer, and the slip component increases, but at least one of the screw shaft groove, nut groove, and ball is increased. Since a solid lubricant film is formed on the surface, good lubricating characteristics are ensured and early damage is prevented.
- the thickness of the solid lubricant film is 0.5 m or more. 3. Good lubrication characteristics can be obtained by using ⁇ ⁇ m or less.
- Examples of the solid lubricant film include a film made of molybdenum disulfide or tin.
- the present invention has the following constitutional power as the fourth constitution.
- the present invention has the following constitutional power as the fifth constitution.
- the groove R ratio was 51 to 52%, and a solid lubricant film was formed on the surface of the ball or in contact with the ball by surface coating treatment of molybdenum disulfide, soft metal, etc.
- the surface pressure acting on the groove can be suppressed, and the problem of short life due to the increase in the slip component that occurs due to the fact that it is a spiral groove, which is a characteristic of the ball screw, and the reduced groove R ratio is tangential. By suppressing the force, it can be solved at the same time, resulting in high load and long life
- the surface hardness of the ball is higher than the surface hardness of each of the ball screw groove of the screw shaft and the ball screw groove of the nut, and further, 1 ⁇ m or more to 5 ⁇ m on the ball surface. Since the following thick solid lubricant film is deposited, damage and wear of the ball can be prevented more reliably, resulting in a long life and high reliability.
- the linear motion device of the present invention operates stably over a long period of time with no malfunction due to the holding piece having a lubricating film formed on the surface in contact with the ball. .
- the ball screw of the present invention has a long service life due to damage such as wear and peeling even when used under conditions where a high load is applied and a moment load is applied.
- FIG. 1 is a top view showing an example of a ball screw which is a kind of linear motion device.
- FIG. 2 is a cross-sectional view taken along the line AA in FIG.
- FIG. 3 is an enlarged view taken along the thread groove of the ball screw shown in FIG. 1.
- FIG. 4 is a cross-sectional view showing an example of a holding piece.
- FIG. 5 is a cross-sectional view showing another example of a holding piece.
- FIG. 6 is a view showing still another example of the holding piece.
- FIG. 7 is a perspective view showing an example of a linear guide which is another example of the linear motion device.
- FIG. 8 is a torque measurement data of Example 7.
- FIG. 9 shows a torque measurement data of Example 8.
- FIG. 10 shows a torque measurement data according to the ninth embodiment.
- FIG. 11 is a torque measurement data of Comparative Example 6.
- FIG. 12 is a torque measurement data of Comparative Example 7.
- FIG. 13 is a view showing a groove cross section of a screw shaft and a nut of the ball screw of this embodiment.
- FIG. 14 is a perspective view showing an example of a ball screw.
- FIG. 15 is a cross-sectional view showing an example of a ball screw.
- FIG. 16 is a partial cross-sectional view showing an example of a ball screw having a holding piece.
- FIG. 17 is a cross-sectional view showing an example of a holding piece.
- FIG. 18 is a cross-sectional view showing an example of a holding piece.
- FIG. 19 is a cross-sectional view of a principal part showing a peripheral portion of an end portion of a tube.
- the type and configuration of the ball screw itself are not limited.
- the ball screw itself is used in a relatively large and high load, such as used in an electric injection molding machine or a press machine.
- the ball screw is the main target.
- An example of a ball screw is shown in FIG. 1 (top view) and FIG. 2 (cross-sectional view of FIG. 1).
- the ball screw 1 has a male screw groove 3a formed in a spiral shape on the outer periphery thereof.
- the nut 7 is formed with a flange 11 for fixing to a table or the like (not shown) at one end, and a flat surface (notch surface) 13 is cut on a part of the outer peripheral surface (upper side in FIG. 2).
- a pair of front and rear steel tube tubes 15 serving as a circulation path for the balls 9 are fixed to the nut 7. It has a structure that circulates through.
- reference numeral 17 denotes a tube presser for fixing the tube 15 on the flat surface 13 of the nut 7
- reference numeral 19 denotes a dust-proof plastic sheath attached to both ends of the nut 7. Speak.
- the surface hardness of the ball 9 is set to be higher than the surface hardness of each of the male screw groove 3a and the female screw groove 5a. If the surface hardness of the ball 9 is a relatively set force HRC63 or more, damage and wear can be further suppressed. In order to satisfy this relationship of surface hardness, each material of ball 9, screw shaft 3 and nut 7 can be selected or surface treatment such as heat treatment can be performed. Just give it.
- a lubricant film having a molybdenum disulfide or soft metal force is formed.
- the film thickness of the lubricant film should be 1 ⁇ m or more and 5 ⁇ m considering high load applications. If the film thickness is less than 1 m, it may be inferior in durability when used for high load applications.
- ball screws for high-load applications do not require the dimensional accuracy of the ball 9 as much as the ball screw (see Patent Document 2) that increases the feed accuracy by applying a preload.
- ⁇ Force Lubricant coating exceeds 5 / zm It will come in trouble. Note that molybdenum disulfide and soft metal that form a lubricant film are solid lubricants, and therefore, even if they are peeled off, they are mixed into the grease and exert a lubricating action.
- the shot-peening method is suitable for forming a relatively thick film as described above while controlling the film thickness.
- a small sphere called a shot material with a particle size of several tens / zm is accelerated and injected from the projection device toward the surface to be processed, and the small sphere collides with the surface to be processed at high speed.
- molybdenum disulfide molybdenum or a soft metal is used for the shot material and is sprayed toward the surface of the ball 9.
- the shot-peening method tends to roughen the coating surface. Therefore, the surface of the lubricating coating may be smoothed as necessary.
- Lube Co., Ltd. YS2 grease is automatically supplied by an automatic lubricator.
- Example 1 is a specification in which a 1.2 ⁇ ⁇ ( ⁇ 8 film is formed on a ball having a surface hardness of HRC64
- Example 2 The service life was 1.68 times longer, and peeling occurred on the rolling surface of the screw shaft.
- a 4.8 m MoS film was formed on a ball with a surface hardness of HRC63.
- Example 3 is a specification in which a 2.0 m Sn film is formed on a ball having a surface hardness of HRC64, and the life is 1.5.
- Example 4 is a specification in which a Sn / 3.6 m Sn coating is formed on a ball having a surface hardness of HRC63, the life is 1.65 times longer, and peeling occurs on the screw shaft rolling surface.
- Example 5 is applied to a ball having a surface hardness of HRC65. 4.
- the life of the Sn coating was 1.48 times longer, and the screw shaft rolling surface was peeled off.
- the surface hardness of the ball is made higher than the surface hardness of the rolling contact surface, and a solid lubricant film of 1 ⁇ m or more and 5 ⁇ m or less is formed on Bonore.
- a solid lubricant film of 1 ⁇ m or more and 5 ⁇ m or less is formed on Bonore.
- Comparative Example 1 is a conventional general high-load use actuator ball screw specification.
- the surface hardness (HRC62) is the same as the surface hardness of the rolling surface, and it is a specification that uses a ball that does not have a solid lubricating film formed on it.
- the surface hardness of the ball is higher than the surface hardness of the screw shaft and the ball screw groove of the nut.
- the solid lubricant film is not formed, the balls cause metal contact with each other.
- the surface roughness of the ball is poor and peeling occurs on the rolling surface.
- the force effect that should increase the surface hardness of the ball and improve the wear resistance does not appear, and the life is the same as in Comparative Example 1.
- Comparative Example 3 is a specification in which a solid lubricating film is formed in the configuration of Comparative Example 1, but the metal contact between the balls is eliminated, but the surface hardness of the ball is equal to the surface hardness of the rolling surface. There is little increase in the life of the ball with less improvement in wear resistance of the ball.
- Comparative Example 4 is a specification using a ball having a surface hardness lower than the surface hardness of the rolling contact surface and no solid lubricant film, but the balls are in metal contact with each other and the surface roughness of the ball is low. The rolling surface is lowered and the rolling surface is damaged. Further, since the surface hardness of the ball is lower than the surface hardness of the rolling surface, the ball is peeled off. for that reason, Compared with Comparative Example 1, the lifetime is considerably short.
- FIG. 13 is a view showing a screw shaft of the ball screw and a groove cross section of the nut of this embodiment.
- the cross section of the groove 111 of the screw shaft 101 is Gothic arc, i.e. the radius is the same (R)
- the ratio (RZD) of the radius (R) of the cross-section arc of the grooves 111 and 121 to the diameter (D) of the ball 102 is 51.0% or more and 52.0% or less.
- a film made of molybdenum disulfide is formed on the surface of the ball 103 with a thickness of 0.5 ⁇ m or more and 3.0 m or less.
- the gap between the track formed by the grooves 111 and 121 of the screw shaft 101 and the nut 102 and the ball 103 is not less than 5 ⁇ m and not more than 70 ⁇ m.
- the ball screw of this embodiment has a larger load capacity and a longer life than the conventional ball screw.
- a solid lubricant film is formed on the ball 103.
- the groove 111 of the screw shaft 101 and the groove 121 of the nut 102 are formed without forming the solid lubricant film on the ball 103.
- the material of the solid lubricant film may be other than disulfurium molybdenum (for example, the one described in Patent Document 2)! /.
- the ball screw having a total ball structure in which the balls are in contact with each other has been described.
- the ball screw of the present invention has a holding piece 107 between the balls 103 as shown in FIG.
- the holding piece 107 may be arranged and held by the holding piece 107.
- the holding piece 107 can be obtained by molding a synthetic resin into a predetermined shape.
- Synthetic resins that can be used include polyamide 6, polyamide 66, polyamide 64, aromatic polyamide, etc., polyacetal resin, polyacetal resin, polybutylene terephthalate, polybutylene terephthalate elastomer, polybutylene naphthalate elastomer.
- the first class is mentioned. Also this These synthetic resins may be blended with glass fiber, carbon fiber, titanium fiber, strong re-wiss force, aluminum borate whisker or the like as a reinforcing material.
- Examples of the shape of the holding piece include those shown in Figs. 17 and 18.
- the holding piece 107 in FIG. 17 has a substantially cylindrical shape, and a concave surface 171 for receiving the ball 103 is formed on the two bottom surfaces of the column.
- the concave surface 171 has a spherical surface with a radius of curvature R larger than the radius r of the ball 103, the thickness t of the central portion with respect to the thickness L of the peripheral portion of the holding piece 107 Is getting smaller.
- a large number of balls 103 can be arranged in the track K, and the contact area between the balls 103 and the holding piece 107 can be reduced to reduce the sliding resistance.
- the shape of the concave surface 171 of the holding piece 107 can be a Gothic arc shape in which two circular arcs are connected, or a conical shape.
- a through hole may be provided in the concave surface 171 and a lubricant may be held in the through hole to reduce the contact resistance with the ball 103.
- the outer diameter of the holding piece 10 7 can be smoothly circulated without interfering with the track K, the tube 104, and the connection portion. It is set smaller than the diameter.
- the outer diameter of the holding piece 107 is preferably 0.5 to 0.9 times the diameter of the ball 103.
- the holding piece 170 in FIG. 18 has a shape in which two opposite sides of the sphere are removed by a concave spherical surface 172, and the outer periphery is a convex surface. Further, the ball may be held by a member in which a plurality of holding pieces are connected by a connecting member.
- ball screw of the present invention is suitable for uses such as for automobile brakes and automobile continuously variable transmissions (belt type CVT), in addition to electric injection molding machines and press machines.
- the life test was conducted by changing the ratio (RZD) to the 1 2 diameter (D) and the material and film thickness of the solid lubricant film as shown in Table 1 below.
- the ball was formed by adjusting the treatment time so that a film having a predetermined thickness was obtained on the ball.
- the thickness of these films was calculated by measuring the ball diameter before and after film formation with an electric dial gauge and dividing the difference between them by two.
- Each ball screw is subjected to a ball screw durability life tester manufactured by Nippon Seie Co., Ltd., test load (axial load): 300kN, stroke: 80mm, rotation speed: 500rpm, temperature: nut outer periphery temperature of 80 ° Durability life test was performed by reciprocating the ball screw under the condition of automatically supplying the lubricant “YS2 Grease” manufactured by Lube Co., Ltd. with an automatic lubricator. In this test, the distance traveled until peeling occurred in either the screw shaft, nut groove, or ball was measured as the life. Next, a relative value was calculated from the lifetime obtained for each sample, assuming that the lifetime of sample No. 10 was “1”.
- the ball screws No. 1 to No. 9 corresponding to Example 6 of the present invention have a longer life than No. 10 to No. 13 corresponding to Comparative Example 5.
- No. 1-9 the thickness of the solid lubricant film is 1. or more 2. The following is the life of No. 2-4, 7-9: 1.28 to 1.67 times that of No. 10 In contrast, the life of No. 1 with a film thickness of SO. 4 m, No. 5 with 3.6 m, and No. 6 with 5. is 1. 11 to 1.20 times.
- the thickness of the solid lubricant film is preferably 0.5 / ⁇ ⁇ to 3.
- the force R / D forming the solid lubricant film with a thickness of 2.2 to 2.8 m is out of the range force of the present invention, so the life is about the same as No. 10. It was. In No. 11, the RZD was 51.6%, but the life was shorter than No. 10 because no solid lubricant film was formed.
- the type of the linear motion device is not particularly limited, and it is intended for a ball screw, a linear guide device, a linear bearing device, etc. having a holding piece. be able to.
- the holding piece 21 is provided with a film having lubricity on at least the surface in contact with the ball 9, preferably the entire surface, specifically, a film made of molybdenum disulfide, a soft metal, or a polymer material.
- a film made of molybdenum disulfide, a soft metal, or a polymer material form a film.
- soft metal tin, gold, silver, lead, zinc, indium and their respective alloys, white metal, and the like are suitable.
- PTGE, PTA and the like are suitable. Even if these coatings are peeled off, they are mixed with grease and develop a lubricating action.
- the film thickness of the coating is preferably L m to 5 m in order to ensure the effect and develop over a long period of time.
- a thin film of less than 1 ⁇ m may be inferior in durability, and even if a film having a thickness exceeding 5 ⁇ m is formed, the effect is saturated and uneconomical.
- the method for forming a film is not limited, but the shot-peening method is suitable for forming a relatively thick film as described above while controlling the film thickness.
- This shot-peung method is a method in which small spheres with a particle size of several tens / zm, called a shot material, are accelerated and jetted toward the surface to be processed by the projection device, and the spheres collide with the surface to be processed at high speed.
- molybdenum disulfide, a soft metal, or a polymer material is used for the shot material and sprayed toward the holding piece 21 mm.
- the shot peening method tends to make the surface of the coating rough, and therefore the coating surface may be smoothed as necessary.
- the holding piece 21 can be made of a synthetic resin, such as polyamide 6, polyamide 66, polyamide 46, polyamide polyamide such as aromatic polyamide, polyacetal resin, polybutylene terephthalate, polybutylene terephthalate. It is obtained by molding an elastomer, polybutylene naphthalate-based elastomer or the like into a predetermined shape. These synthetic resins are also used for reinforcement.
- a synthetic resin such as polyamide 6, polyamide 66, polyamide 46, polyamide polyamide such as aromatic polyamide, polyacetal resin, polybutylene terephthalate, polybutylene terephthalate. It is obtained by molding an elastomer, polybutylene naphthalate-based elastomer or the like into a predetermined shape. These synthetic resins are also used for reinforcement.
- Glass fiber, carbon fiber, titanium fiber, potassium whisker, aluminum borate whisker, etc. may be blended.
- the shape of the holding piece 21 is not particularly limited. However, as shown in the sectional view of Fig. 4, the concave spherical surface 23 having a radius of curvature R larger than the radius r of the ball 9 on both sides 23 It can be in the shape of a disk formed with. By adopting such a shape, the thickness t of the central portion becomes smaller than the total thickness L, and more balls 9 can be disposed, and the contact area between the balls 9 and the holding piece 21 Can be reduced to minimize sliding resistance.
- the shape of the concave spherical surface 23 may be a Gothic arch-shaped concave surface formed by intersecting two arcs at an intermediate portion, or a conical concave surface. Also, provide a through hole in the concave surface or hold a lubricant in the through hole to reduce the contact resistance with the ball 9.
- the holding piece 21 may have a cross-sectional shape as shown in FIG. 5, or a plurality of holding pieces 21 connected by connecting members 22 as shown in FIG. It is. Similarly, any of the holding pieces 21 is formed with the above film.
- the ball screw has been exemplified and described with respect to the embodiment of the present invention. However, for a linear guide or the like which is another linear motion device, the operability is improved by inserting a similar holding piece. Can be planned.
- the force shown in FIG. 7 is an example of a linear guide.
- This linear guide includes a guide rail 31 having a rolling groove 32 on its outer surface, and a slider 35 assembled across the guide rail 31. .
- a ball circulation path is formed inside the slider 35 with the rolling groove 32 of the guide rail 31, and the ball and the coating film are formed inside the ball circulation path as described above. The pieces are housed so that they can roll!
- Example 7 disulfurized molybdenum fine particles having an average particle diameter of 1 ⁇ m, and in Example 8, the average particle diameter of 2.5 ⁇ m.
- a film was formed using m fine tin particles, and in Example 9, PTFE fine particles having an average particle diameter of 3 m.
- Comparative Example 6 the total ball specification does not include a holding piece, and in Comparative Example 7, the film is not formed and the holding piece is used as it is.
- Test load 8800N axial load is applied to the double nut panel.
- Lube Co., Ltd. YS2 grease is automatically supplied by an automatic lubricator.
- FIG. 19 is a cross-sectional view of the main part showing the peripheral portion of the end of the tube.
- the ball screw 1 includes a screw shaft 3 having a helical screw groove 3a on the outer peripheral surface and a helical screw groove 5a facing the screw groove 3a of the screw shaft 3.
- a nut 7 provided on the inner peripheral surface, and a plurality of balls 9 movably loaded in a spiral ball rolling path 77 formed by both screw grooves 3a and 5a. Then, when the nut 7 and the screw shaft 3 are rotated relative to each other by being screwed onto the screw shaft 3 via the ball 9, the screw shaft 3 and the nut 5 are axially moved via the rolling of the ball 9. It is designed to move relative.
- the cross-sectional shape of the thread grooves 3a, 5a may be an arc shape or a gothic arc shape! /.
- a part of the outer peripheral surface of the nut 7 is cut out to form a flat surface portion 13.
- a tube 15 that forms an endless ball circulation path by communicating the starting point and the end point of the ball rolling path 77 is fixed to the flat portion 13 by a tube presser 17.
- the ball 9 moves in the ball rolling path 77 and turns around the screw shaft 3 a plurality of times and reaches the end point of the ball rolling path 77, the ball 9 is scooped up from one end of the tube 15 and moved to the tube 15 Through the inside, the other end force of the tube 15 is also returned to the starting point of the ball rolling path 77. In this way, the ball 9 rolling in the ball rolling path 77 is circulated indefinitely by the tube 15. Therefore, the screw shaft 3 and the nut 7 can continuously move relative to each other.
- the tube 15 corresponds to a ball return path which is a constituent of the present invention.
- the material of the tube 15 is not particularly limited, but a resin is preferably a resin.
- the ball return path may be manufactured by Xia-Ji, or may be formed by molding if the material is grease, or by pressing if the material is metal.
- the inner surface of the tube 15 is covered with a solid lubricating film (not shown) consisting of at least one of molybdenum disulfide and an organic molybdenum compound.
- This solid lubricating coating may be further coated on the groove surfaces of both screw grooves 3a and 5a. Since it has such a solid lubricating film, the ball screw 1 is used under conditions where a high load is applied and a moment load is applied, and the ball 9 is rubbed against the inner surface of the tube 15 with an excessive force. Even if this occurs, the inner surface of the tube 15 is less likely to be damaged, such as abrasion or peeling. Therefore, poor circulation of ball 9 is unlikely to occur!
- the ball screw 1 has a long life. Even if the solid lubricant film is peeled off by rubbing the balls 9, the release powder of the solid lubricant film diffuses into the grease and acts as a solid lubricant, so that the lubricating action of the grease is improved.
- Such a ball screw 1 can be suitably used in a mold clamping mechanism of a mold clamping apparatus incorporated in an electric injection molding machine or a press machine. That is, it is suitable as a ball screw in a mold clamping mechanism that performs mold clamping of the mold clamping device by driving the ball screw with an electric motor.
- the use of the ball screw of the present invention is not limited to the above.
- Specific examples of the organomolybdenum compound include molybdenum dialkyldithiodicarbamate molybdenum and molybdenum dialkyldithiodiphosphate.
- the solid lubricant film may be composed of soft metal, polymer material, metal oxide, metal nitride, metal carbide, clay mineral, lead zirconate titanate (PZT), and solid lubricant.
- N, ZrN, CrN, TiAIN are examples.
- Specific examples of metal carbides include SiC, TiC,
- WC is given.
- clay minerals include bentonite, smectite, and mica.
- solid lubricants include graphite, BN, and WS.
- the method for forming the solid lubricant film is not particularly limited, but a method in which fine particles of disulfurium-molybdenum or organic molybdenum-molybdenum compound collide with the surface to be treated is preferable.
- a method of spraying fine particles together with a gas such as a shot peening method or a sandblast method, or a centrifugal projection method can be used.
- grease for lubricating the groove surfaces of both screw grooves 3a and 5a and the surface of the ball 9 is disposed.
- the type of grease is not particularly limited, but examples include greases using mineral oil, ester-based synthetic oil, ether-based synthetic oil, hydrocarbon-based synthetic oil, or the like as a base oil.
- the grease may contain additives such as a thio-based extreme pressure agent, a sulfur-phosphorus-based extreme pressure agent, and an organometallic compound-based extreme pressure agent containing io, phosphorus and zinc.
- Plastic dust seals 19 may be disposed at both ends of the nut 7. This prevents foreign matter from entering the nut 7 from the outside.
- a holding piece 21 for preventing contact between the balls 9 may be interposed between the adjacent balls 9. Then, since the competition between the balls 9 is eliminated, the movement of the balls 9 is performed more smoothly. Therefore, the circulation performance of the ball 9 and the feeding accuracy of the ball screw 1 are excellent, and the generation of noise and vibration is further suppressed.
- the material of the holding piece 21 is not particularly limited.
- a polyamide having a lubricating action on its own is a fluorine resin, or polyethylene impregnated with a lubricating oil.
- the ball screw BS6316—10.5 (Nominal: 63 X 16 X 300—Ct7) manufactured by NIPPON SEI CO., LTD. Having the same configuration as the ball screw 1 described above, A durability test was conducted.
- the ball screws of Examples 10 to 13 and Comparative Examples 8 and 9 subjected to the durability test differed in the tube material and the type of solid lubricant film (see Table 4).
- the ball screw was lubricated by automatically supplying YS2 grease from Lube Co., Ltd. with an automatic lubricator.
- the ball screw is mounted on a ball screw endurance tester manufactured by Nippon Seige Co., Ltd. and rotated to rotate the screw shaft thread groove, nut thread groove or ball, or ball circulation failure. The distance traveled until the ball screw malfunctions due to was taken as the life of the ball screw.
- Table 4 shows the test results.
- the life values in Table 4 are relative values when the life of the ball screw of Comparative Example 1, which is a general ball screw, is 1.
- the ball screws of Examples 10 to 13 had a longer life than the ball screws of Comparative Examples 8 and 9 in which the inner surface of the tube was not coated with a solid lubricant film.
- the ball screws of Examples 10, 12, and 13 were peeled off in the thread groove of the screw shaft, and the ball screw of Example 11 As for the screw screw, peeling occurred in the thread groove of the nut.
- the RZD ratio is not set to different values for the male screw groove and female screw groove. Because of this curved surface, the contact stress approximated to the male thread groove is RZD54%. (This difference varies depending on the ball diameter, etc.) Thus, there is no problem even if the RZD of the female thread groove is larger than that of the male thread groove.
- the ball screw of the present invention is suitable for an actuator, for example, and is particularly suitable for applications that are relatively large and subject to a high load such as an actuator such as an electric injection molding machine or a press machine.
- the lower limit of the groove R ratio was about 52% from the viewpoint of adverse effects of slipping, but by applying MoS coating to the ball, the tangential force can be suppressed, and 51.5%
- the degree of groove R can prevent early damage due to the adverse effects of slipping.
- the surface pressure can be reduced, the load capacity can be increased, and the life of the high-load ball screw can be extended.
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- Engineering & Computer Science (AREA)
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Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/909,271 US20090007710A1 (en) | 2005-03-25 | 2006-03-23 | Ball screw |
EP06729798A EP1862707A4 (en) | 2005-03-25 | 2006-03-23 | BALL STEM |
JP2007510436A JPWO2006104015A1 (ja) | 2005-03-25 | 2006-03-23 | ボールねじ |
Applications Claiming Priority (8)
Application Number | Priority Date | Filing Date | Title |
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JP2005088323 | 2005-03-25 | ||
JP2005-088324 | 2005-03-25 | ||
JP2005-088323 | 2005-03-25 | ||
JP2005088324 | 2005-03-25 | ||
JP2005092375 | 2005-03-28 | ||
JP2005-092375 | 2005-03-28 | ||
JP2006011765 | 2006-01-19 | ||
JP2006-011765 | 2006-01-19 |
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WO2006104015A1 true WO2006104015A1 (ja) | 2006-10-05 |
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PCT/JP2006/305850 WO2006104015A1 (ja) | 2005-03-25 | 2006-03-23 | ボールねじ |
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US (1) | US20090007710A1 (ja) |
EP (1) | EP1862707A4 (ja) |
JP (1) | JPWO2006104015A1 (ja) |
WO (1) | WO2006104015A1 (ja) |
Families Citing this family (5)
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US9336177B2 (en) | 2007-10-15 | 2016-05-10 | 23Andme, Inc. | Genome sharing |
DE102010042180A1 (de) * | 2010-10-08 | 2012-04-12 | Schock Metallwerk Gmbh | Auszugführung |
CN103228953B (zh) * | 2010-11-15 | 2016-04-27 | 日本精工株式会社 | 滚珠丝杠 |
FR2983546B1 (fr) * | 2011-12-06 | 2014-04-11 | Sagem Defense Securite | Organe mecanique |
US20230279941A1 (en) * | 2020-08-24 | 2023-09-07 | Nsk Ltd. | Method and device for sealing grease into ball screw device, ball screw device, method for producing ball screw device, method for producing linear actuator, method for producing vehicle brake, and method for producing vehicle |
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JPS62283252A (ja) | 1986-05-30 | 1987-12-09 | Toshiba Corp | 固体潤滑ボ−ルねじ |
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JP2002276765A (ja) * | 2001-03-21 | 2002-09-25 | Ntn Corp | ダブルナット予圧式ボールねじ |
JP2003301920A (ja) * | 2002-04-10 | 2003-10-24 | Nsk Ltd | 転動装置 |
JP2003314659A (ja) * | 2002-04-24 | 2003-11-06 | Nsk Ltd | ボールねじ装置 |
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JP2005076650A (ja) * | 2003-08-29 | 2005-03-24 | Nsk Ltd | ボールねじ |
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2006
- 2006-03-23 WO PCT/JP2006/305850 patent/WO2006104015A1/ja active Application Filing
- 2006-03-23 JP JP2007510436A patent/JPWO2006104015A1/ja active Pending
- 2006-03-23 EP EP06729798A patent/EP1862707A4/en not_active Withdrawn
- 2006-03-23 US US11/909,271 patent/US20090007710A1/en not_active Abandoned
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JPS62283252A (ja) | 1986-05-30 | 1987-12-09 | Toshiba Corp | 固体潤滑ボ−ルねじ |
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Also Published As
Publication number | Publication date |
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JPWO2006104015A1 (ja) | 2008-09-04 |
EP1862707A4 (en) | 2012-11-07 |
EP1862707A1 (en) | 2007-12-05 |
US20090007710A1 (en) | 2009-01-08 |
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