WO2017061417A1 - Roulement à billes à contact oblique, et dispositif de vis sphérique mettant en œuvre celui-ci - Google Patents

Roulement à billes à contact oblique, et dispositif de vis sphérique mettant en œuvre celui-ci Download PDF

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Publication number
WO2017061417A1
WO2017061417A1 PCT/JP2016/079464 JP2016079464W WO2017061417A1 WO 2017061417 A1 WO2017061417 A1 WO 2017061417A1 JP 2016079464 W JP2016079464 W JP 2016079464W WO 2017061417 A1 WO2017061417 A1 WO 2017061417A1
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WIPO (PCT)
Prior art keywords
ball
diameter
ball bearing
separator
balls
Prior art date
Application number
PCT/JP2016/079464
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English (en)
Japanese (ja)
Inventor
浩樹 谷村
Original Assignee
Ntn株式会社
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
Priority claimed from JP2016189478A external-priority patent/JP6765920B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to CN201680058046.6A priority Critical patent/CN108138839B/zh
Priority to DE112016004538.7T priority patent/DE112016004538T5/de
Publication of WO2017061417A1 publication Critical patent/WO2017061417A1/fr
Priority to US15/941,897 priority patent/US20180223899A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of 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
    • 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
    • F16C19/20—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows with loose spacing bodies, e.g. balls, between the bearing 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
    • F16C31/00—Bearings for parts which both rotate and move linearly
    • F16C31/04—Ball or roller bearings
    • 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
    • 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

Definitions

  • the present invention relates to an angular ball bearing used for supporting a ball screw or the like of an injection molding machine, and a ball screw device using the angular ball bearing.
  • the injection molding machine is provided with a feed mechanism for advancing and retracting a resin material extrusion screw and a feed mechanism for clamping a mold.
  • these feed mechanisms have been electrified in place of the conventional hydraulic type.
  • a rotary motor and a ball screw are used for the electric feed mechanism.
  • the ball screw has a function of positioning two objects relative to each other and a function of converting rotational force into direct power, but the ball screw used in the injection molding machine has only the latter function. Is required. Since such a bearing for supporting a ball screw used mainly for direct power application receives a large thrust load, generally a roller bearing is often used. However, since the roller bearing has a large torque cross, a ball screw is sometimes supported by an angular ball bearing with a small torque cross in order to improve the conversion efficiency of the direct power with respect to the rotational force (for example, Patent Document 1).
  • a large force is applied to the column portion 5b due to the delayed advancement of the ball 3 during rapid acceleration / deceleration rotation, so that the thin column portion 5b may be damaged. That is, it is difficult to employ the ladder-type or comb-type cage 5 that is generally used at present from the viewpoint of the arrangement space and the strength of the column portion 5b.
  • the diameter Da of the ball 3 and the depth of the raceway grooves 1a and 2a can be set to appropriate values. However, in that case, it becomes necessary to review the structure around the ball screw, and the versatility is lost.
  • An angular contact ball bearing according to the present invention is an angular contact ball bearing in which a plurality of balls are rotatably interposed between an inner ring raceway groove formed on an outer peripheral surface of an inner ring and an outer ring raceway groove formed on an inner peripheral surface of an outer ring.
  • the balls are held by a plurality of separator holders interposed between adjacent balls and separated from each other, and the contact angle of the balls is in the range of 45 ° to 65 °.
  • each ball is held by a plurality of separator cages separated from each other, rather than a cage having a ladder shape, a comb shape, or the like, the column portion due to the delayed advancement of the balls during rapid acceleration / deceleration rotation No damage will occur. Moreover, since there is no column part, the space between the inner ring and the outer ring is widened by that much, so that a lot of grease can be put in the bearing, and the lubricity is improved. If the separator cage is made of resin, the grease retention capability is increased and the lubricity is further improved.
  • the diameter of the ball may be 68% or more of 1/2 of the difference between the outer diameter of the outer ring and the inner diameter of the inner ring.
  • the ball diameter is 68% or more of 1/2 of the difference, the ratio of balls in the space between the inner ring and the outer ring becomes too large. This makes it difficult to install. Since it is not a pillar part if it is a separator holder
  • the deepest groove depth may be 47% or more of the diameter of the ball.
  • Chamfering is provided at the boundary between the outer peripheral surface of the inner ring raceway groove and the inner ring raceway groove in the inner ring, and the boundary between the inner peripheral surface of the outer ring raceway groove and the outer ring raceway groove in the outer ring. Is given.
  • the above configuration is such that the outer diameter of the portion on the back side of the inner ring raceway groove in the inner ring and the inner diameter of the portion on the back side of the outer ring raceway groove in the outer ring are the pitch diameter of the ball. It can be said that they are almost the same.
  • the outer diameter of the rear side of the inner ring raceway groove in the inner ring cannot be made larger than the pitch circle diameter of the ball, and the inner diameter of the rear side of the outer ring raceway groove in the outer ring The dimensions cannot be smaller than the pitch circle diameter of the balls. Therefore, it can be said that the said structure is a form which can load the largest thrust load substantially.
  • the outer diameter of the inner ring at the back side of the inner ring raceway groove and the inner diameter of the outer ring at the back side of the outer ring raceway groove are the same as the pitch circle diameter of the balls. There may be.
  • the outer diameter of the back side of the inner ring raceway groove in the inner ring cannot be made larger than the pitch circle diameter of the ball, and the rear side part of the outer ring of the outer ring raceway groove in the outer ring is not allowed. Since the inner diameter cannot be made smaller than the pitch circle diameter of the ball, this configuration is a form capable of applying the largest thrust load.
  • the outer diameter and width of the separator cage are such that when the separator cage is inclined at a maximum angle in the circumferential direction from the radial direction of the bearing between two adjacent balls,
  • the size may be set such that the outer end portion in the radial direction contacts one ball and the inner surface of the outer ring, and the inner end portion contacts a portion on the inner diameter side of the pitch circle in the other ball.
  • the separator cage used in the angular ball bearing may preferably have an outer diameter of 75 to 85% of the ball diameter and a width of 20 to 50% of the ball diameter.
  • the outer diameter and width of the separator cage are set within the predetermined range, the locked state and the falling state can be more reliably avoided.
  • the separator cage revolves while being in contact with and guided by the balls and the raceway surface.
  • the clearance between the separator retainer and the ball is important in order to suppress the collision noise between the separator retainer and the ball and to rotate smoothly.
  • the separator retainer moves radially outward due to centrifugal force and comes into contact with the raceway surface of the outer ring.
  • the rotational torque increases and problems such as heat generation occur.
  • the collision noise between the separator cage and the ball becomes large, which causes noise.
  • the clearance between both ends of the aggregate is 15 to 25% of the diameter of the ball. It may be good.
  • an appropriate clearance is held between the separator cage and the ball during rotation of the bearing, and the bearing can be smoothly rotated.
  • the clearance between the separator cage and the ball is larger than 25% of the ball diameter, the rotational torque and heat generated by the separator cage coming into contact with the raceway surface, and the ball and separator holding The noise generated when the collision sound with the vessel becomes loud can be avoided.
  • the clearance between the separator cage and the ball is less than 15% of the ball diameter, the temperature rise during rotation of the bearing will eliminate the clearance between the ball and the separator cage due to thermal expansion of the separator cage and ball. Friction and heat generated due to the above can be avoided.
  • the angular ball bearing of the present invention has a large load capacity and can be loaded with a particularly large thrust load. Therefore, the angular ball bearing is mainly used for supporting a ball screw used in an application of direct power. Suitable for.
  • a screw shaft or a nut of a ball screw is supported on the angular ball bearing.
  • the angular ball bearing has a large load capacity and can be loaded with a particularly large thrust load. For this reason, by supporting the screw shaft or nut of the ball screw with the angular ball bearing, a ball screw device suitable for use mainly in the application of direct power is provided.
  • FIG. 3B is a cross-sectional view taken along the line IIIB-O-IIIB of FIG. 3A. It is the elements on larger scale of FIG. 3B.
  • FIG. 4 is a partial cutaway front view of an angular ball bearing, showing the maximum tilt angle of the separator cage between two adjacent balls.
  • surface which shows the preferable range of the outer diameter dimension H and the width dimension W of a separator holder
  • It is a fracture front view of an angular ball bearing and shows the state where all the balls of the angular ball bearing and the separator cage are gathered together in the circumferential direction of the bearing.
  • It is a fracture front view of a separator holder showing an appropriate dimensional relationship between a ball and a separator holder.
  • It is a fracture front view of the separator holder which is a modification of Drawing 5A.
  • retainer which is a modification of FIG.
  • or 4 It is the side view which is a modification of FIG. It is a figure which shows the whole structure of the injection molding machine in which the angular ball bearing shown in FIG. 1 thru
  • FIG. 1 is a front view of an angular ball bearing according to an embodiment of the present invention
  • FIG. 2 is a rear view
  • FIG. 3A is a cutaway front view
  • FIG. 3B is a sectional view taken along line IIIB-O-IIIB in FIG.
  • FIG. 1 is a front view of an angular ball bearing according to an embodiment of the present invention
  • FIG. 2 is a rear view
  • FIG. 3A is a cutaway front view
  • FIG. 3B is a sectional view taken along line IIIB-O-IIIB in FIG.
  • FIG. 1 is a front view of an angular ball bearing according to an embodiment of the present invention
  • FIG. 2 is a rear view
  • FIG. 3A is a cutaway front view
  • FIG. 3B is a sectional view taken along line IIIB-O-IIIB in FIG.
  • FIG. 1 is a front view of an angular ball bearing according to an embodiment of the present invention
  • FIG. 2 is a rear view
  • this angular ball bearing J includes an inner ring raceway groove 1 a (FIG. 3B) formed on the outer peripheral surface of the inner ring 1 and an outer ring raceway groove 2 a ( A plurality of balls 3 are interposed between the balls 3 in FIG. 3B). The plurality of balls 3 are held by a plurality of separator holders 4 interposed between adjacent balls 3 and separated from each other.
  • the “inner ring raceway groove” and the “outer ring raceway groove” may be simply referred to as “track groove”.
  • the angular ball bearing J has an inner diameter d1, an outer diameter D1, and a width B according to the ISO standard. Except for these dimensions, the following conditions (1) to (4) are determined regardless of the bearing size.
  • the contact angle ⁇ of the ball 3 is in the range of 45 ° to 65 °. In the illustrated example, the contact angle ⁇ is 55 °. When the contact angle ⁇ is 45 ° or more, the load capacity of the thrust load is larger than the radial load. By setting the contact angle ⁇ of the ball 3 to 65 ° or less, it is possible to prevent the ball 3 from riding on the back side portions of the inner race 1 and the outer race 2 relative to the raceway grooves 1a, 2a, so-called shoulder portions 1b, 2b.
  • the diameter Da of the ball 3 is 68% or more of the radial cross-sectional thickness T.
  • the radial cross-sectional thickness T is 1 ⁇ 2 of the difference between the outer diameter D1 of the outer ring 2 and the inner diameter d1 of the inner ring 1.
  • the diameter Da of the ball 3 is 68% or less of the radial cross-sectional thickness T. Therefore, the angular ball bearing J has a radial cross-sectional thickness T greater than that of the general angular ball bearing.
  • the ratio of the diameter Da of the ball 3 to the is large. The larger this ratio, the greater the load capacity as a bearing.
  • the outer diameter d2 of the shoulder 1b of the inner ring 1 and the inner diameter D2 of the shoulder 2b of the outer ring 2 are the same as the pitch circle diameter PCD of the ball 3. That is, the height of the shoulder portion 1b of the inner ring 1 and the height of the shoulder portion 2b of the outer ring 2 are set as high as possible within processing constraints. As described above, by increasing the height of the shoulder portions 1b and 2b, the load capacity with respect to the thrust load is increased. Further, the contact angle ⁇ of the ball 3 can be increased to 45 ° or more. If the shoulder portions 1b and 2b have a height exceeding the pitch circle diameter PCD of the balls 3, it becomes difficult to polish the raceway grooves 1a and 2a.
  • the deepest groove depth h of the inner ring raceway groove 1a with respect to the shoulder 1b of the inner ring 1 and the deepest groove depth H of the outer ring raceway groove 2a with respect to the shoulder 2b of the outer ring 2 are It is 47% or more of the diameter Da.
  • the groove depth h of the inner ring raceway 1a is a depth excluding the chamfer 1c applied to the boundary between the outer peripheral surface of the shoulder 1b and the inner ring raceway groove 1a.
  • the depth H of the outer ring raceway groove 2a is a depth excluding the chamfer 2c applied to the boundary between the inner peripheral surface of the shoulder 2b and the outer ring raceway groove 2a.
  • condition (4) is almost synonymous with (3).
  • the ball 3 between the inner ring 1 and the outer ring 2 is increased.
  • the space that does not exist is narrowed and it is difficult to incorporate ladder-type and comb-type cages. Therefore, the balls 3 are held by a plurality of separator holders 4.
  • the separator retainer 4 can be applied to ceramics, aluminum alloys, copper alloys, stainless steel, etc., in addition to resins such as PA (polyamide), PPS (polyphenylene sulfide), and PEEK (polyether ether ketone). If it is made of resin, the holding ability of the grease is increased, and the lubricity is further improved.
  • resins such as PA (polyamide), PPS (polyphenylene sulfide), and PEEK (polyether ether ketone). If it is made of resin, the holding ability of the grease is increased, and the lubricity is further improved.
  • the separator retainer 4 has a contact portion 4a that contacts the balls 3 on both sides, and a surface that is perpendicular to the pitch circle of the arrangement of the balls 3 from the contact portions 4a (FIG. 5B). And a shift prevention portion 4b that spreads along the plane parallel to the paper surface.
  • the abutting portion 4a has both side surfaces recessed spherically on the center side, and this recessed portion is a pocket 4c into which a part of the balls 3 on both sides are fitted.
  • the pocket 4c has a concave spherical shape with a slightly larger curvature than the ball 3, but may have a conical surface shape or a Gothic arch shape in cross section. Further, the pocket 4c may have a ring shape opened on both sides at the center.
  • the shift prevention portion 4b has a shape in which the shift prevention portions 4b are evenly spread in all directions along a plane perpendicular to the pitch circle of each ball 3 as shown in FIGS. 6A and 6B.
  • the shift preventing portion 4b may have a shape in which convex portions 4ba having a large extent from the contact portion 4a and concave portions 4bb having a small extent are arranged alternately. 6A and 6B, the lubricant such as grease can be held in the recess 4bb.
  • the separator retainer during revolution is set. 4, the separator retainer 4 is sandwiched between adjacent balls 3 and 3 to prevent a locked state that impedes the rotation of the bearing, and at the same time, the separator retainer 4 is removed from the clearance of the raceway ring. The situation of falling off and falling off can be avoided. Thereby, the angular ball bearing J provided with the separator holder
  • the preferable range of the outer diameter dimension H and the width dimension W of the separator cage 4 is as shown in FIG.
  • the range marked with ⁇ where smooth rotation of the bearing is obtained is that the outer diameter dimension H of the separator retainer 4 is 75 to 85% of the ball diameter Da, and the width dimension W of the separator retainer 4 is It is 20 to 50% of the diameter Da. Outside this range, there is a problem that the contact between the retainer and the bearing lock or the raceway surface is too strong.
  • the width dimension W exceeds 50% of the ball diameter Da, it becomes impossible to incorporate the separator cage 4 into a bearing having a normal number of balls.
  • the separator cage 4 revolves while being in contact with and guided by the balls 3 and the raceway surfaces 1a and 2a.
  • the clearance between the separator retainer 4 and the ball 3 is important in order to suppress the collision noise between the separator retainer 4 and the ball 3 and to rotate smoothly.
  • the clearance between the separator holder 4 and the balls 3 is large, the separator holder 4 comes into contact with the raceway surfaces 1a and 2a. As a result, the rotational torque increases and problems such as heat generation occur. In addition, the collision sound between the separator holder 4 and the balls 3 is increased, causing noise.
  • the separator cage 4 moves radially outward due to centrifugal force and comes into contact with the raceway surface 2a of the outer ring 2. It is possible to avoid the noise generated due to the increase in rotational torque and heat generation, and the collision sound between the ball 3 and the separator holder 4 becoming louder.
  • the separator cage 4 and the ball 3 are thermally expanded due to a temperature rise during the rotation of the bearing, so that the gap G between the ball 3 and the separator cage 4 is increased. It is possible to avoid friction and heat generated due to the disappearance of.
  • FIG. 12 shows an appropriate dimensional relationship between the ball and the separator cage in the angular ball bearing.
  • the spherical diameter Dc of the pocket 4c of the separator holder 4 is 105 to 125% of the ball diameter Da
  • the groove depth E of the separator holder 4 is as follows.
  • the ball diameter Da is 10 to 30% and the bottom wall thickness F of the pocket 4c of the separator retainer 4 is 5 to 20% of the ball diameter Da, the rotation of the bearing becomes smoother.
  • the separator holder 4 shown in FIGS. 5A and 5B, FIG. 6A and FIG. 6B has concave shapes on both sides of the contact portion 4a.
  • both side surfaces of the contact portion 4a are recessed in a spherical shape on the center side, the ball 3 and the contact portion 4a come into contact with each other, and the contact portion 4a is not easily worn, but the friction torque increases.
  • the separator holders 4 may be used for different purposes.
  • the angular ball bearing J having the above-described configuration holds each ball 3 by a plurality of separator cages 4 separated from each other, not a cage having a pillar shape such as a ladder shape or a comb shape. For this reason, the pillar part is not damaged by the delayed advancement of the balls 3 during the rapid acceleration / deceleration rotation. Further, since there is no column portion, the space between the inner ring 1 and the outer ring 2 is widened by that much, so that a lot of grease can be put in the bearing, and the lubricity is improved. Since the separator holder 4 is made of resin, the ability to hold grease is increased, and the lubricity is further improved.
  • This angular ball bearing J has a large load capacity due to the large diameter Da of the ball 3, and a large load capacity with respect to the thrust load due to the high height of the shoulder portions 1b and 2b. For this reason, it is suitable for supporting a ball screw used mainly for applications in which direct power is applied. For example, it is suitable for supporting a ball screw used in a mechanism for advancing and retracting a screw for extruding a resin material in an injection molding machine or a mechanism for clamping a mold.
  • FIG. 15 is a diagram showing an overall configuration of an injection molding machine in which the angular ball bearing J shown in FIGS. 1 to 4 is used.
  • the injection molding machine 10 is an in-line screw type, and heats and melts the resin supplied into the heating cylinder 12 from the hopper 11 with a heater (not shown) while kneading it with the extrusion screw 13, and extrudes the heat-melted resin. It is extruded from the nozzle 14 by the screw 13 and filled between the pair of molds 15 and 16.
  • the heating cylinder 12 is mounted on a movable table 17 that can move in the left-right direction in the figure, which is the central axis direction of the extrusion screw 13.
  • the moving table 17 is advanced and retracted by the injection table moving unit 18.
  • the extrusion screw 13 is rotated by a screw part 19 in order to knead the resin. Further, the extrusion screw 13 can be moved back and forth in the left-right direction in the figure by the injection unit 20, and is advanced to the left side when the molten resin is injected into the molds 15 and 16.
  • the molds 15 and 16 are mounted on the fixed platen 21 and the movable platen 22, respectively.
  • the movable platen 22 can move back and forth in the left-right direction in the drawing along a guide bar 23 provided on the fixed platen 21, and approaches and separates from the fixed platen 21.
  • the movable platen 22 is advanced and retracted by a mold clamping unit 24 composed of a toggle mechanism. Further, the movable platen 22 is provided with an ejecting portion 25 for removing the mold 16 from the mold 15 and taking out a molded product.
  • Ball screw devices 26, 27, 28, and 29 are used as feed mechanisms for the injection table moving unit 18, the injection unit 20, the mold clamping unit 24, and the eject unit 25, respectively. Since the screw part 19 is a mechanism that only rotates the extrusion screw 13, no ball screw device is provided. Since the structure of each of the ball screw devices 26, 27, 28, and 29 is basically the same, description will be given by taking the ball screw device 27 of the injection unit 20 as an example.
  • the ball screw device 27 includes a screw shaft 31 extending in the left-right direction that is rotatably supported by the bearing device 30, and a nut 32 that is screwed to the screw shaft 31.
  • the motor 33 rotates the screw shaft 31.
  • the nut 32 moves forward and backward in the left-right direction.
  • the bearing device 30 is configured by arranging a plurality of (for example, five) angular ball bearings J shown in FIGS.
  • the ball screw device 27 of the injection unit 20 generates a large direct power for injection / holding pressure of the molten resin. Further, the ball screw device 28 of the mold clamping unit 24 also generates a large linear power to receive the internal pressure generated in the molds 15 and 16 when the molten resin is injected.
  • the bearing device 30 of the injection unit 20 and the bearing device 34 of the mold clamping unit 24 that receive such a large thrust load are more angular balls than the bearing device 35 of the injection table moving unit 18 and the bearing device 36 of the eject unit 25. Bearings J are arranged. Note that the angular ball bearing J shown in FIGS. 1 to 4 is also used for the bearing device 37 of the screw portion 19 that supports the extrusion screw 13.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention fournit un roulement à billes à contact oblique qui permet d'élever une capacité de charge par augmentation du diamètre de billes, et qui est adapté à une mise en œuvre dans une application telle qu'une charge axiale est principalement appliquée. Ce roulement à billes à contact oblique (J) est tel que des billes (3) sont intercalées de manière à rouler librement entre une gorge de roue interne (1a) formée sur une face périphérique externe d'une roue interne (1), et une gorge de roue externe (2a) formée sur une face périphérique interne d'une roue externe (2). La pluralité de billes (3) est maintenue par une pluralité de cages de séparateur (4) intercalées entre les billes (3) adjacentes et séparées les unes des autres. L'angle de contact (θ) des billes (3) se trouve dans une plage de 45° à 65°.
PCT/JP2016/079464 2015-10-05 2016-10-04 Roulement à billes à contact oblique, et dispositif de vis sphérique mettant en œuvre celui-ci WO2017061417A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201680058046.6A CN108138839B (zh) 2015-10-05 2016-10-04 角接触滚珠轴承和采用它的滚珠丝杠装置
DE112016004538.7T DE112016004538T5 (de) 2015-10-05 2016-10-04 Schrägkugellager und Kugellagervorrichtung mit Schrägkugellager
US15/941,897 US20180223899A1 (en) 2015-10-05 2018-03-30 Angular contact ball bearing, and ball screw device using same

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2015-197525 2015-10-05
JP2015197525 2015-10-05
JP2016189478A JP6765920B2 (ja) 2015-10-05 2016-09-28 アンギュラ玉軸受およびこれを用いたボールねじ装置
JP2016-189478 2016-09-28

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US15/941,897 Continuation US20180223899A1 (en) 2015-10-05 2018-03-30 Angular contact ball bearing, and ball screw device using same

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WO2017061417A1 true WO2017061417A1 (fr) 2017-04-13

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD822082S1 (en) * 2015-11-20 2018-07-03 Ntn Corporation Separator for a ball bearing
USD829787S1 (en) * 2015-11-20 2018-10-02 Ntn Corporation Separator for a ball bearing
USD836144S1 (en) * 2016-02-25 2018-12-18 Ntn Corporation Separator for a ball bearing

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007247901A (ja) * 2006-03-13 2007-09-27 Roller Bearing Co Of America Inc 回転翼航空機に向けた、タンデムスタック型アンギュラコンタクトベアリング
JP2011094719A (ja) * 2009-10-30 2011-05-12 Nsk Ltd 玉軸受
JP2012177412A (ja) * 2011-02-25 2012-09-13 Nsk Ltd 多列組合せ玉軸受
WO2015129064A1 (fr) * 2014-02-27 2015-09-03 日本精工株式会社 Roulement à billes à contact oblique

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007247901A (ja) * 2006-03-13 2007-09-27 Roller Bearing Co Of America Inc 回転翼航空機に向けた、タンデムスタック型アンギュラコンタクトベアリング
JP2011094719A (ja) * 2009-10-30 2011-05-12 Nsk Ltd 玉軸受
JP2012177412A (ja) * 2011-02-25 2012-09-13 Nsk Ltd 多列組合せ玉軸受
WO2015129064A1 (fr) * 2014-02-27 2015-09-03 日本精工株式会社 Roulement à billes à contact oblique

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD822082S1 (en) * 2015-11-20 2018-07-03 Ntn Corporation Separator for a ball bearing
USD829787S1 (en) * 2015-11-20 2018-10-02 Ntn Corporation Separator for a ball bearing
USD836144S1 (en) * 2016-02-25 2018-12-18 Ntn Corporation Separator for a ball bearing

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