WO2023276770A1 - Mécanisme de mouvement linéaire de type à vis à rouleaux planétaires, et dispositif de frein électrique - Google Patents

Mécanisme de mouvement linéaire de type à vis à rouleaux planétaires, et dispositif de frein électrique Download PDF

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Publication number
WO2023276770A1
WO2023276770A1 PCT/JP2022/024650 JP2022024650W WO2023276770A1 WO 2023276770 A1 WO2023276770 A1 WO 2023276770A1 JP 2022024650 W JP2022024650 W JP 2022024650W WO 2023276770 A1 WO2023276770 A1 WO 2023276770A1
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WIPO (PCT)
Prior art keywords
roller shaft
roller
rotation
linear motion
planetary
Prior art date
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PCT/JP2022/024650
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English (en)
Japanese (ja)
Inventor
雅章 江口
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Ntn株式会社
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Publication of WO2023276770A1 publication Critical patent/WO2023276770A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • 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
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/24—Electric or magnetic using motors
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/44—Mechanical mechanisms transmitting rotation
    • F16D2125/46—Rotating members in mutual engagement
    • F16D2125/50—Rotating members in mutual engagement with parallel non-stationary axes, e.g. planetary gearing

Definitions

  • the present invention relates to a planetary roller screw type linear motion mechanism used in an electric linear motion actuator, and an electric brake device using the planetary roller screw type linear motion mechanism.
  • the planetary roller screw type linear motion mechanism of Patent Document 1 includes a rotating shaft to which rotation is input from the outside, a hollow cylindrical outer ring member surrounding the rotating shaft, and an inner circumference of the outer ring member and an outer circumference of the rotating shaft.
  • a plurality of planetary rollers arranged at intervals in the circumferential direction therebetween, a plurality of roller shafts rotatably supporting the plurality of planetary rollers, and a carrier holding both ends of the plurality of roller shafts.
  • a helical ridge is provided on the inner circumference of the outer ring member, and a helical groove or a circumferential groove that engages with the helical ridge is provided on the outer circumference of each planetary roller.
  • the carrier has a first disk and a second disk that face each other in the axial direction with a plurality of planetary rollers interposed therebetween, and a connecting portion that passes between the plurality of planetary rollers and connects the first disk and the second disk.
  • the first disk has a plurality of first elongated holes for radially movably holding the first ends of the roller shafts
  • the second disk has a plurality of roller shafts.
  • a plurality of circumferentially spaced second slots are formed to movably retain the second end of the shaft in the radial direction.
  • a first C-shaped ring spring and a second C-shaped ring spring are stretched over the first end and the second end of the roller shaft, respectively, in a state in which the diameter is elastically expanded and deformed.
  • the elastic restoring forces of the C-shaped ring springs urge the first end and the second end of each roller shaft radially inward, and as a result, the planetary rollers are pressed against the outer circumference of the rotating shaft.
  • this planetary roller screw type linear motion mechanism when rotation is input to the rotating shaft from the outside, the rotation of the rotating shaft is transmitted to the planetary rollers that are in rolling contact with the outer circumference of the rotating shaft. It revolves around its axis of rotation. At this time, the engagement between the spiral groove or the circumferential groove on the outer circumference of the planetary roller and the spiral ridge on the inner circumference of the outer ring member causes the outer ring member, which is prevented from rotating from the outside, to move in the axial direction.
  • the planetary roller screw type linear motion mechanism converts rotation of the rotating shaft into linear motion of the outer ring member.
  • this planetary roller screw type linear motion mechanism is compact and can generate a large axial load. There is an advantage that it is suitable for an electric brake device that is used.
  • Patent Document 1 a pair of flat surfaces (hereinafter referred to as "width across flats") are provided on the outer circumference of the first end and the outer circumference of the second end of each roller shaft. ) so that the width across flats of the first end is engaged with the longitudinal surface of the first elongated hole of the first disc, and the width across flats of the second end is also the longitudinal direction of the second elongated hole of the second disc. By engaging the surfaces, the roller shaft is prevented from rotating by the first disk and the second disk.
  • a carrier composed of a first disc, a second disc, and a connecting portion connecting the two discs is assembled, and then the roller shaft is connected to the first long hole of the first disc and the second disc of the second disc. If the roller shaft can be inserted into the two elongated holes, it is possible to automate the assembling work of the roller shaft. can't This is because the width dimension of the first slot and the width dimension of the second slot correspond to the width across flats of the end portion of the roller shaft, and are narrower than the outer diameter dimension of the roller shaft.
  • the second end of the roller shaft does not form the width across flats.
  • the second long hole should not have a dimension corresponding to the width across flats formed at the first end of the roller shaft, but should have a wider width dimension corresponding to the outer diameter dimension of the roller shaft. to form.
  • the first end of the roller shaft Since the shape and size of the portion and the shape and size of the second end are different from each other, it becomes necessary to distinguish between the front and rear directions of the roller shaft when inserting the roller shaft into the first long hole and the second long hole. .
  • the shape of the end of the roller shaft is detected, and based on the detected shape of the end of the roller shaft, the correct orientation of the roller shaft (roller shaft
  • the first end of the roller shaft should be the front side of the insertion direction, and the second end of the roller shaft should be the rear side of the insertion direction), but it is costly to provide such facilities.
  • FIG. 25A A method of extension is conceivable. That is, as shown in FIG. 25A, the roller shaft is extended to a position where the width across flats 72 of the first end 71 of the roller shaft 70 engages the longitudinal surface 75 of the first elongated hole 74 of the first disc 73 .
  • a possible method is to extend the roller shaft 70 so that the width across flats 77 of the second end 76 of the roller shaft 70 does not reach the position of the second long hole 79 of the second disk 78 when the roller shaft 70 is inserted. .
  • FIG. 25A A possible method is to extend the roller shaft 70 so that the width across flats 77 of the second end 76 of the roller shaft 70 does not reach the position of the second long hole 79 of the second disk 78 when the roller shaft 70 is inserted.
  • a width across flats 72 is formed at the first end 71 of the roller shaft 70, and as shown in FIG. is formed. Further, as shown in FIG. 25C, the width dimension of the second elongated hole 79 is set not to the dimension corresponding to the width across flats 77 but to the dimension corresponding to the outer diameter dimension of the roller shaft 70 .
  • the shape and dimensions of the first end portion 71 of the roller shaft 70 and the shape and dimensions of the second end portion 76 of the roller shaft 70 are the same, so the roller shaft 70 can be positioned between the second long hole 79 and the first end portion 79 . There is no need to distinguish between the front and rear directions of the roller shafts 70 when they are sequentially inserted into the long holes 74 .
  • the problem to be solved by the present invention is to provide a planetary roller screw type linear motion mechanism that facilitates automation of the work of assembling the roller shaft of the planetary roller to the carrier.
  • the present invention provides a planetary roller screw type linear motion mechanism having the following configuration. a rotating shaft; a hollow cylindrical outer ring member surrounding the rotating shaft; a plurality of planetary rollers arranged at intervals in the circumferential direction between the inner periphery of the outer ring member and the outer periphery of the rotating shaft; a spiral ridge provided on the inner periphery of the outer ring member; a spiral groove or a circumferential groove provided on the outer circumference of each planetary roller so as to engage with the spiral ridge; a plurality of roller shafts that rotatably support the plurality of planetary rollers; a first disk and a second disk axially opposed to each other with the plurality of planetary rollers interposed therebetween; and a connecting portion passing between the plurality of planetary rollers and connecting the first disk and the second disk.
  • a plurality of first elongated holes are formed in the first disk at intervals in a circumferential direction to hold the first ends of the plurality of roller shafts so as to be movable in a radial direction, Planetary roller screw type linear motion, wherein a plurality of second elongated holes are formed in the second disk at intervals in the circumferential direction to hold the second ends of the plurality of roller shafts so as to be movable in the radial direction.
  • the width dimension of the second long hole is wider than the width dimension of the first long hole
  • a first anti-rotation shape portion and a first partial cylindrical surface adjacent to the first anti-rotation shape portion around the axis of the roller shaft are formed on the outer circumference of the first end portion of the roller shaft.
  • the first anti-rotation shaped portion is engaged with the longitudinal surface of the first elongated hole to prevent rotation of the roller shaft
  • a second anti-rotation shape portion and a second partial cylindrical surface adjacent to the second anti-rotation shape portion around the axis of the roller shaft are formed on the outer circumference of the second end portion of the roller shaft.
  • the shape and dimensions of the second end are the same as the shape and dimensions of the first end, but the angular position of the second detent shape about the axis of the roller shaft and the first detent Different from the angular position of the shaped portion about the axis of the roller shaft, only the second partial cylindrical surface out of the second anti-rotation shaped portion and the second partial cylindrical surface is aligned with the longitudinal surface of the second long hole.
  • a planetary roller screw type linear motion mechanism characterized by being supported in contact.
  • the second elongated hole is formed to have a wide width
  • first the carrier composed of the first disk, the second disk, and the connecting portion connecting the two disks is assembled, and then the roller shaft is assembled.
  • the roller shaft is assembled.
  • the roller shaft is assembled.
  • the shape and dimensions of the first end of the roller shaft and the shape and dimensions of the second end of the roller shaft are the same, when the roller shaft is inserted into the second elongated hole and the first elongated hole in this order, There is no need to distinguish between the front and rear orientations of the roller shafts. Therefore, it is easy to automate the work of assembling the roller shaft of the planetary roller to the carrier.
  • first anti-rotation shape portion and the second anti-rotation shape portion adopt a flat surface having a shape obtained by cutting the outer periphery of the roller shaft along a plane parallel to the axial center of the roller shaft.
  • the first detent shape is a flat surface, it comes into surface contact with the longitudinal surface of the first elongated hole, and it is possible to effectively detent the roller shaft so that it does not rotate. Further, the reduction in the cross-sectional area of the first end and the second end of the roller shaft due to the formation of the first anti-rotation shape portion and the second anti-rotation shape portion is minimized, and the first end of the roller shaft is The strength of the portion and the second end can be easily ensured, and the first anti-rotation shape portion and the second anti-rotation shape portion can be processed with high accuracy at a low processing cost.
  • the difference between the angular position of the first anti-rotation shape portion about the axis of the roller shaft and the angular position of the second anti-rotation shape portion about the axis of the roller shaft is in the range of 40° or more and 140° or less. preferably set to .
  • a first C-shaped ring spring for biasing the first end of the roller shaft radially inward; and a second C-shaped ring spring for biasing the second end of the roller shaft radially inward.
  • a ring spring A first ring groove with which the first C-shaped ring spring engages is formed on the outer periphery of the first end of the roller shaft, When a second ring groove with which the second C-shaped ring spring engages is formed on the outer circumference of the second end of the roller shaft,
  • the difference between the angular position of the first anti-rotation shape portion about the axis of the roller shaft and the angular position of the second anti-rotation shape portion about the axis of the roller shaft is 40° or more and 50° or less, or 130°. It is preferable to set the angle between 140° and 140°.
  • the first anti-rotation shaped portion is a pair of flat surfaces formed parallel to each other on the outer circumference of the first end of the roller shaft with the axis of the roller shaft interposed therebetween
  • the second anti-rotation shaped portion may be a pair of parallel flat surfaces formed on the outer periphery of the second end portion of the roller shaft with the axis of the roller shaft interposed therebetween.
  • the first anti-rotation shaped portion is formed only at one location on the outer periphery of the first end of the roller shaft, A configuration may be adopted in which the second anti-rotation shaped portion is formed only at one location on the outer periphery of the second end portion of the roller shaft.
  • the present invention also provides an electric brake device having the following configuration as an electric brake device using the planetary roller screw type linear motion mechanism.
  • the above-mentioned planetary roller screw type linear motion mechanism an electric motor that rotationally drives the rotary shaft of the planetary roller screw type linear motion mechanism; and a brake pad axially pressed by the outer ring member of the planetary roller screw type linear motion mechanism.
  • the carrier is first formed of the first disc, the second disc, and the connecting portion connecting the two discs. is assembled, and then the roller shafts can be sequentially inserted into the second slot and the first slot from the side of the second disk.
  • the shape and dimensions of the first end of the roller shaft and the shape and dimensions of the second end of the roller shaft are the same, when the roller shaft is inserted into the second elongated hole and the first elongated hole in this order, There is no need to distinguish between the front and rear orientations of the roller shafts. Therefore, it is easy to automate the work of assembling the roller shaft of the planetary roller to the carrier.
  • FIG. 1 is a sectional view showing an electric linear motion actuator incorporating a planetary roller screw type linear motion mechanism according to a first embodiment of the present invention
  • FIG. Enlarged cross-sectional view of the vicinity of the planetary roller screw type linear motion mechanism in FIG. Cross-sectional view along the III-III line in Fig. 2
  • Cross-sectional view along the IV-IV line in Fig. 2 Enlarged view of the vicinity of the roller shaft in FIG.
  • Cross-sectional view along the VI-VI line in Fig. 2 Enlarged view of the vicinity of the roller shaft in FIG. Cross-sectional view along line VIII-VIII in Fig. 2
  • FIG. 3 is an enlarged view of the roller shaft shown in FIG.
  • FIG. 5 is a cross-sectional view of the vicinity of the planetary rollers of the planetary roller screw type linear motion mechanism according to the second embodiment of the present invention;
  • Cross-sectional view along line BB in FIG. 15A Cross-sectional view along CC line of FIG. 15A
  • FIG. 15B is an enlarged view of the roller shaft shown in FIG. 15A;
  • FIG. 8 Sectional view along line XVIII-XVIII in FIG.
  • FIG. 8 is a cross-sectional view of the vicinity of the planetary rollers of the planetary roller screw type linear motion mechanism according to the third embodiment of the present invention;
  • Cross-sectional view along line BB in FIG. 19A Cross-sectional view along CC line of FIG. 19A
  • FIG. 19B is an enlarged view of the roller shaft shown in FIG. 19A;
  • FIG. 8 Sectional view along line XVIII-XVIII in FIG.
  • FIG. 8 is a cross-sectional view of the vicinity of the planetary rollers of the planetary roller screw type linear motion mechanism according to the third embodiment of the present invention.
  • Cross-sectional view along line BB in FIG. 19A Cross-sectional view along CC line of FIG. 19A
  • FIG. 19B is an enlarged view
  • FIG. 11 is a cross-sectional view of the vicinity of the planetary rollers of the planetary roller screw type linear motion mechanism according to the fourth embodiment of the present invention; Cross-sectional view along line BB of FIG. 23A Cross-sectional view along CC line of FIG. 23A
  • FIG. 11 is a cross-sectional view of the vicinity of the planetary rollers of the planetary roller screw type linear motion mechanism according to the fifth embodiment of the present invention; Cross-sectional view along line BB of FIG. 24A Cross-sectional view along CC line of FIG. 24A Cross-sectional view of the vicinity of the planetary roller of the planetary roller screw type linear motion mechanism of the reference example Cross-sectional view along line BB of FIG. 25A Cross-sectional view along CC line of FIG. 25A
  • FIG. 1 shows an electric linear motion actuator 2 using the planetary roller screw type linear motion mechanism 1 of the first embodiment of the present invention.
  • This electric linear motion actuator 2 includes an electric motor 3 , a reduction gear mechanism 4 that decelerates and transmits the rotation of the electric motor 3 , and an outer ring member 5 that transmits the rotation input from the electric motor 3 via the reduction gear mechanism 4 . and a planetary roller screw type linear motion mechanism 1 that converts and outputs the linear motion.
  • the reduction gear mechanism 4 includes an input gear 7 fixed to the motor shaft 6 of the electric motor 3, an output gear 9 fixed to the rotary shaft 10 of the planetary roller screw type linear motion mechanism 1, an input gear 7 and an output gear 9. and a gear case 11 for housing these gears 7, 8 and 9.
  • the gear case 11 consists of a base plate 12 and a cover 13 .
  • the reduction gear mechanism 4 reduces the speed of the rotation input from the motor shaft 6 of the electric motor 3 to the input gear 7 by sequentially transmitting the rotation through the input gear 7, the intermediate gear 8, and the output gear 9, which have different numbers of teeth. The reduced rotation is output from the output gear 9 to the rotary shaft 10 .
  • the planetary roller screw type linear motion mechanism 1 includes a rotary shaft 10 that is rotationally driven by an electric motor 3 (see FIG. 1) and a hollow cylindrical outer ring member 5 that surrounds the rotary shaft 10. , a plurality of planetary rollers 14 arranged at intervals in the circumferential direction between the inner circumference of the outer ring member 5 and the outer circumference of the rotating shaft 10, and a plurality of rollers supporting the plurality of planetary rollers 14 so as to be rotatable.
  • Shaft 15 , carrier 18 holding both ends (first end 16 and second end 17 ) of the plurality of roller shafts 15 in the axial direction, and outer ring member 5 are moved in parallel with the axial direction of rotating shaft 10 . and a housing 19 (see FIG. 2) that accommodates it. As shown in FIG. 1, the housing 19 is fixed to the axial front side surface of the base plate 12 .
  • the direction parallel to the rotating shaft 10 is the axial direction
  • the direction of movement of the outer ring member 5 when the outer ring member 5 moves toward the side where the projection length of the outer ring member 5 from the housing 19 is increased is the axial forward direction.
  • the moving direction of the outer ring member 5 when the outer ring member 5 moves to the side where the projection length of the member 5 from the housing 19 becomes smaller is the axial rearward direction
  • the direction of rotation around the rotating shaft 10 is the circumferential direction
  • the direction in which the distance changes is called the radial direction.
  • the plurality of planetary rollers 14 are in rolling contact with the outer circumference of the rotating shaft 10 .
  • a contact portion of the rotating shaft 10 with the planetary roller 14 is a cylindrical surface.
  • each planetary roller 14 revolves around the rotating shaft 10 while rotating about the roller shaft 15 due to friction between the outer periphery of the rotating shaft 10 and the outer periphery of the planetary rollers 14 .
  • a spiral ridge 20 is provided on the inner circumference of the outer ring member 5.
  • the spiral ridge 20 is a ridge obliquely extending with a predetermined lead angle with respect to the circumferential direction.
  • a plurality of circumferential grooves 21 that engage with the spiral ridges 20 are formed on the outer periphery of each planetary roller 14 at intervals in the axial direction. The interval between adjacent circumferential grooves 21 on the outer periphery of each planetary roller 14 in the axial direction is the same size as the pitch of the spiral ridges 20 .
  • the circumferential groove 21 having a lead angle of 0 degrees is provided on the outer periphery of the planetary roller 14, but instead of the circumferential groove 21, a spiral groove having a lead angle different from that of the spiral ridge 20 may be provided. .
  • the carrier 18 connects the first disk 22 and the second disk 23 by passing between the plurality of planetary rollers 14 and the first disk 22 and the second disk 23 that face each other in the axial direction with the plurality of planetary rollers 14 interposed therebetween. It has a plurality of connecting portions 24 that connect to each other.
  • the connecting portion 24 is a columnar member extending in the axial direction between the planetary rollers 14 adjacent in the circumferential direction.
  • the axial front end of the connecting portion 24 is press-fitted into a press-fitting hole 25 formed in the first disk 22 and fixed, and the axial rear end of the connecting portion 24 is press-fitted into a press-fitting hole 26 formed in the second disk 23 . has been fixed.
  • the connecting portion 24 fixes the first disk 22 and the second disk 23 to each other so that the first disk 22 and the second disk 23 do not move relative to each other in either the axial direction or the circumferential direction.
  • a first end portion 16 of the roller shaft 15 (an end portion on the front side in the axial direction in the figure) is held by a first elongated hole 31 formed in the first disc 22 so as to be movable in the radial direction.
  • the second end 17 of the roller shaft 15 (the end on the rear side in the axial direction in the figure) is also held by a second elongated hole 32 formed in the second disc 23 so as to be radially movable.
  • a second C-shaped ring spring 34 is stretched over the second end portion 17 of the roller shaft 15 in a state of being elastically expanded in diameter.
  • the second end 17 of each roller shaft 15 is urged radially inward by the elastic restoring force of .
  • a first C-shaped ring spring 33 is stretched over the first end portions 16 of the plurality of roller shafts 15 in a state of being elastically deformed to expand its diameter.
  • the elastic restoring force of the C-shaped ring spring 33 urges the first end 16 of each roller shaft 15 radially inward.
  • the outer circumference of each planetary roller 14 is pressed against the outer circumference of the rotating shaft 10 by the elastic restoring forces of the first C-shaped ring spring 33 and the second C-shaped ring spring 34 .
  • the first disk 22 and the second disk 23 are formed in an annular shape through which the rotating shaft 10 is passed.
  • Slide bearings 35 are mounted on the inner circumferences of the first disk 22 and the second disk 23 so as to be in sliding contact with the outer circumference of the rotating shaft 10 .
  • the slide bearing 35 supports the carrier 18 rotatably around the rotary shaft 10 .
  • a radial bearing 36 is provided between the inner circumference of each planetary roller 14 and the outer circumference of the roller shaft 15 to support the planetary roller 14 so that it can rotate.
  • the radial bearing 36 supports the outer circumference of the central portion of each roller shaft 15 (the portion between the first end portion 16 and the second end portion 17).
  • the outer circumference of the central portion of each roller shaft 15 is a constant cylindrical surface whose outer diameter does not change along the axial direction. Needle rollers with retainers can be used as the radial bearings 36 .
  • a thrust bearing 37 is incorporated between each planetary roller 14 and the second disk 23 to axially support the planetary roller 14 in a rotatable state.
  • the outer ring member 5 is axially slidably supported on the inner surface of a housing hole 38 formed in the housing 19 .
  • a shaft support member 39 is fixedly provided inside the housing 19 at a position spaced rearward in the axial direction from the outer ring member 5 .
  • the shaft support member 39 is formed in an annular shape through which the rotating shaft 10 passes.
  • a radial bearing 40 that rotatably supports the rotating shaft 10 is incorporated in the inner periphery of the shaft support member 39 .
  • a thrust bearing 41 is incorporated between the carrier 18 and the shaft support member 39 to axially support the carrier 18 so that it can revolve.
  • a spacer 42 that revolves integrally with the carrier 18 is incorporated between the carrier 18 and the thrust bearing 41 .
  • the axially rearward movement of the shaft support member 39 is restricted by a snap ring 43 mounted on the inner circumference of the housing hole 38, and the carrier 18 is also restricted from axially rearward movement. . Further, the carrier 18 is restricted from moving forward in the axial direction by a retaining ring 44 provided at the axial front end of the rotary shaft 10 . As a result, the carrier 18 is restricted from moving forward and backward in the axial direction, and the planetary rollers 14 held by the carrier 18 are also restricted from moving in the axial direction.
  • a plurality of first elongated holes 31 are provided at intervals in the circumferential direction.
  • Each first slot 31 axially penetrates the first disc 22 , and the first end 16 of the roller shaft 15 is inserted into each first slot 31 .
  • the first elongated hole 31 is elongated in the radial direction (vertical direction in the figure) and has a pair of longitudinal surfaces 45 that extend linearly in the radial direction.
  • the pair of longitudinal surfaces 45 are flat surfaces arranged to face each other in the circumferential direction.
  • a pair of first partial cylindrical surfaces 47 are formed.
  • the first anti-rotation shape portion 46 is a portion formed by cutting out a part of the outer circumference of the circular cross section by processing the outer circumference of the end portion of the roller shaft 15 .
  • 15 is a portion having a shape capable of restricting its rotation.
  • the first anti-rotation portion 46 is a flat surface obtained by cutting the outer periphery of the roller shaft 15 along a plane parallel to the axial center of the roller shaft 15 .
  • the pair of first anti-rotation shaped portions 46 are formed in parallel with the axis of the roller shaft 15 interposed therebetween (so-called width across flats).
  • the width dimension of the first long hole 31 corresponds to the width dimension of the pair of first detent shaped portions 46 on the outer periphery of the first end portion 16. Also, the width dimension of the first long hole 31 is smaller than the outer diameter dimension of the roller shaft 15 . The roller shaft 15 is prevented from rotating by engaging the first anti-rotation shape portion 46 with the longitudinal surface 45 of the first elongated hole 31 (surface contact in this embodiment).
  • a plurality of second elongated holes 32 are also provided at intervals in the circumferential direction.
  • Each second slot 32 axially penetrates the second disc 23 , and the second end 17 of the roller shaft 15 is inserted into each second slot 32 .
  • the second elongated hole 32 is elongated in the radial direction (vertical direction in the figure) and has a pair of longitudinal surfaces 48 that extend linearly in the radial direction.
  • the pair of longitudinal surfaces 48 are flat surfaces that face each other in the circumferential direction.
  • the outer circumference of the second end portion 17 of the roller shaft 15 is provided with a pair of second detent shaped portions 49 and adjacent to the pair of second detent shaped portions 49 around the axis of the roller shaft 15 .
  • a pair of second partial cylindrical surfaces 50 are formed.
  • the second anti-rotation shape portion 49 is a flat surface formed by cutting the outer periphery of the roller shaft 15 along a plane parallel to the axis of the roller shaft 15 .
  • the pair of second detent shaped portions 49 are formed in parallel with the axis of the roller shaft 15 interposed therebetween.
  • the shape and dimensions of the second end 17 of the roller shaft 15 shown in FIG. 9 are the same as the shape and dimensions of the first end 16 of the roller shaft 15 shown in FIG.
  • the angular position of the second detent shape portion 49 shown in FIG. 9 around the axis of the roller shaft 15 is different from the angular position of the first detent shape portion 46 shown in FIG. different. That is, as shown in FIGS. 10 to 12 , the first anti-rotation shape portion 46 and the second anti-rotation shape portion 49 are aligned in the normal direction of the first anti-rotation shape portion 46 and the normal direction of the second anti-rotation shape portion 49 . They are formed such that their line directions are different from each other.
  • the difference between the angular position of the first detent shape portion 46 about the axis of the roller shaft 15 and the angular position of the second detent shape portion 49 about the axis of the roller shaft 15 is 40° or more. It is set within a range of 50° or less (45° in the drawing).
  • the four flat surfaces of the roller shaft 15 (the two first anti-rotation shaped portions 46 and the two second anti-rotation shaped portions 49) all face different directions.
  • the width dimension of the second elongated hole 32 (the spacing dimension between the pair of longitudinal surfaces 48 ) is a dimension corresponding to the outer diameter dimension of the roller shaft 15 .
  • the width dimension of the second long hole 32 is wider than the width dimension of the first long hole 31 (see FIG. 7). ing.
  • the second detent shape portion 49 and the second partial cylindrical surface 50 are on the outer periphery of the second end portion 17 of the roller shaft 15 .
  • only the second partial cylindrical surface 50 is in contact with the longitudinal surface 48 of the second elongated hole 32 . It is supported, and the second anti-rotation shape portion 49 is out of contact with the longitudinal surface 48 .
  • a second ring groove 52 with which the second C-shaped ring spring 34 engages is formed on the outer circumference of the second end 17 of the roller shaft 15 .
  • the outer circumference of the first end 16 of the roller shaft 15 is formed with a first ring groove 51 with which the first C-shaped ring spring 33 (see FIG. 2) engages.
  • the first anti-rotation shaped portion 46 is formed so as to cross the forming region of the first ring groove 51 in the axial direction and reach the end surface of the roller shaft 15 on the first end portion 16 side.
  • the second anti-rotation shape portion 49 is also formed so as to extend axially across the forming region of the second ring groove 52 and reach the end surface of the roller shaft 15 on the second end portion 17 side.
  • the shape and dimensions of the second end 17 after the reversal are as follows. Symmetry such that the shape and dimensions of the first end 16 before inversion are identical to the shape and dimensions of the first end 16 after inversion, and the shape and dimensions of the first end 16 after inversion are the same as the shape and dimensions of the second end 17 before inversion have sex.
  • the planetary roller screw type linear motion mechanism 1 converts the rotation input from the electric motor 3 to the rotary shaft 10 into linear motion of the outer ring member 5 .
  • This electric brake device includes a brake disc 60 that rotates together with a wheel (not shown), a mounting bracket 61 that is fixed to the vehicle body so as not to move in the axial direction with respect to the brake disc 60, and a A caliper body 62 slidably supported in parallel with the axial direction of the brake disc 60, an inner side brake pad 63 and an outer side brake pad 64 axially opposed to each other with the brake disc 60 interposed therebetween, and an inner side brake pad. and an electric linear motion actuator 2 that moves 63 in the axial direction.
  • the inner side brake pad 63 and the outer side brake pad 64 are each held by a mounting bracket 61 so as to be axially movable and circumferentially immovable.
  • the caliper body 62 has a claw portion 65 that axially faces the rear surface of the outer brake pad 64 and an outer shell portion 66 that faces the outer diameter side of the brake disc 60 .
  • the outer shell portion 66 is formed integrally with the housing 19 of the electric linear motion actuator 2 .
  • the outer shell portion 66 of the caliper body 62 and the housing 19 of the electric linear motion actuator 2 may be formed separately and then integrated with bolts or the like.
  • the outer ring member 5 is arranged behind the inner side brake pad 63 so that the inner side brake pad 63 moves integrally with the outer ring member 5 when the outer ring member 5 moves.
  • An end portion of the outer ring member 5 on the brake disc 60 side is formed with a detent groove 68 that engages with a detent projection 67 formed on the back surface of the inner side brake pad 63 .
  • the engagement of the groove 68 prevents rotation of the outer ring member 5 .
  • the outer ring member 5 of the electric linear motion actuator 2 axially presses the back surface of the inner side brake pad 63 to press the inner side brake pad 63 against the side surface of the brake disc 60 .
  • the caliper body 62 slides relative to the mounting bracket 61 due to the axial reaction force that the outer ring member 5 receives from the inner side brake pad 63 , and the claw portion 65 of the caliper body 62 slides along the back surface of the outer side brake pad 64 .
  • the outer side brake pad 64 is pressed against the side surface of the brake disc 60 .
  • the inner side brake pad 63 and the outer side brake pad 64 are pressed against the brake disc 60 , and braking force is generated in the brake disc 60 by friction between the contact surfaces of the brake pads and the brake disc 60 .
  • the roller shaft 15 is rotated together with the planetary roller 14 (so-called ) can be prevented. Therefore, it is possible to prevent wear of the contact portions of the roller shaft 15 with the C-shaped ring springs 33 and 34, and to prevent idle rotation of the rotating shaft 10 caused by the wear.
  • the planetary roller screw type linear motion mechanism 1 is formed with a wide second elongated hole 32. Therefore, when the planetary roller screw type linear motion mechanism 1 is produced, First, the carrier 18 composed of the first disk 22, the second disk 23, and the connecting portion 24 shown in FIG. It can be inserted into the first long hole 31 in order. Moreover, as shown in FIGS. 10 to 12, since the shape and dimensions of the first end 16 of the roller shaft 15 and the shape and dimensions of the second end 17 of the roller shaft 15 are the same, the roller shaft 15 can be When the roller shaft 15 is inserted into the second long hole 32 and the first long hole 31 in order, it is not necessary to distinguish between the front and rear directions of the roller shaft 15 . Therefore, the work of assembling the roller shaft 15 of the planetary roller 14 to the carrier 18 can be easily automated.
  • the planetary roller screw type linear motion mechanism 1 has a plane parallel to the axis of the roller shaft 15 as a first anti-rotation shape portion 46 and a second anti-rotation shape portion 49. Since the flat surface of the shape obtained by cutting the outer periphery of the roller shaft 15 along the .theta. In addition, it is possible to prevent the roller shaft 15 from rotating. In addition, the reduction in the cross-sectional area of the first end 16 and the second end 17 of the roller shaft 15 due to the formation of the first anti-rotation shape portion 46 and the second anti-rotation shape portion 49 is minimized, The strength of the first end portion 16 and the second end portion 17 of the shaft 15 can be easily ensured. Further, the first anti-rotation shape portion 46 and the second anti-rotation shape portion 49 can be processed with high accuracy at low processing cost.
  • the planetary roller screw type linear motion mechanism 1 has a difference between the angular position of the first anti-rotation shaped portion 46 and the angular position of the second anti-rotation shaped portion 49 (in the figure, 45°) is set large, so when the first anti-rotation shape portion 46 is engaged with the longitudinal surface 45 of the first elongated hole 31 of the first disk 22 as shown in FIG. 2, it is possible to reliably arrange the second partial cylindrical surface 50 at the position of the longitudinal surface 48 of the second elongated hole 32 of the second disk 23. As shown in FIG.
  • the planetary roller screw type linear motion mechanism 1 has a difference between the angular position of the first anti-rotation shape portion 46 and the angular position of the second anti-rotation shape portion 49 of 40°. Since it is set to 50° or less (45° in the figure), as shown in FIG. It is possible to stabilize the engagement between the ring spring 34 and the second ring groove 52 .
  • the difference between the angular position of the first detent shape portion 46 and the angular position of the second detent shape portion 49 is 40° or more and 50° or less (45° in the drawings). ), as shown in FIG. can be stabilized.
  • 15A to 15C show a second embodiment of the invention.
  • the second embodiment differs from the first embodiment only in the partial configuration of the roller shaft 15, and the rest of the configuration is the same. Therefore, parts corresponding to those in the first embodiment are denoted by the same reference numerals, and descriptions thereof are omitted.
  • a first anti-rotation shape portion is formed by cutting the outer periphery of the roller shaft 15 along a plane parallel to the axial center of the roller shaft 15 .
  • 46 and a first partial cylindrical surface 47 adjacent to the first detent shape portion 46 around the axis of the roller shaft 15 are formed.
  • the first detent shape portion 46 is formed only at one location on the outer circumference of the first end portion 16 of the roller shaft 15 (so-called D-cut).
  • the width dimension of the first long hole 31 corresponds to the width dimension in the direction perpendicular to the first detent shape portion 46 (flat surface) of the first end portion 16. ing. Also, the width dimension of the first long hole 31 is smaller than the outer diameter dimension of the roller shaft 15 . The roller shaft 15 is prevented from rotating by engaging the first anti-rotation shape portion 46 with the longitudinal surface 45 of the first elongated hole 31 .
  • a second anti-rotation shaped portion is formed by cutting the outer circumference of the roller shaft 15 along a plane parallel to the axial center of the roller shaft 15 .
  • 49 and a second partial cylindrical surface 50 adjacent to the second detent shape portion 49 around the axis of the roller shaft 15 are formed.
  • the second detent shape portion 49 is formed only at one location on the outer circumference of the second end portion 17 of the roller shaft 15 .
  • the shape and dimensions of the second end 17 of the roller shaft 15 shown in FIG. 15C are the same as the shape and dimensions of the first end 16 of the roller shaft 15 shown in FIG. 15B.
  • the angular position around the axis of the roller shaft 15 of the second detent shape portion 49 shown in FIG. 15C is different from the angular position around the axis of the roller shaft 15 of the first detent shape portion 46 shown in FIG. 15B. different. That is, as shown in FIGS. 16 to 18 , the first anti-rotation shape portion 46 and the second anti-rotation shape portion 49 are aligned in the normal direction of the first anti-rotation shape portion 46 and the normal direction of the second anti-rotation shape portion 49 . They are formed such that their line directions are different from each other.
  • the difference between the angular position of the first detent shape portion 46 about the axis of the roller shaft 15 and the angular position of the second detent shape portion 49 about the axis of the roller shaft 15 is 40° or more. It is set within a range of 50° or less (45° in the figure).
  • the width dimension of the second elongated hole 32 (the spacing dimension between the pair of longitudinal surfaces 48 ) is a dimension corresponding to the outer diameter dimension of the roller shaft 15 .
  • the width dimension of the second long hole 32 is wider than the width dimension of the first long hole 31 shown in FIG. 15B.
  • the second detent shape portion 49 and the second partial cylindrical surface 50 on the outer periphery of the second end portion 17 of the roller shaft 15 only the second partial cylindrical surface 50 is located in the second elongated hole 32 . It is supported in contact with the longitudinal surface 48 , and the second detent shape portion 49 is out of contact with the longitudinal surface 48 .
  • This second embodiment has the same effects as the first embodiment.
  • 19A to 19C show a third embodiment of the invention.
  • the third embodiment differs from the second embodiment only in the difference between the angular position of the first anti-rotation shape portion 46 and the angular position of the second anti-rotation shape portion 49, and the rest of the configuration is the same. Therefore, portions corresponding to those in the second embodiment are denoted by the same reference numerals, and descriptions thereof are omitted.
  • the shape and dimensions of the second end 17 of the roller shaft 15 shown in FIG. 19C are the same as the shape and dimensions of the first end 16 of the roller shaft 15 shown in FIG. 19B.
  • the angular position around the axis of the roller shaft 15 of the second detent shape portion 49 shown in FIG. 19C is different from the angular position around the axis of the roller shaft 15 of the first detent shape portion 46 shown in FIG. 19B. different. That is, as shown in FIGS.
  • the angular position of the first anti-rotation shape portion 46 about the axis of the roller shaft 15 and the angular position of the second anti-rotation shape portion 49 about the axis of the roller shaft 15 is set in the range of 130° or more and 140° or less (135° in the drawing).
  • the third embodiment has the same effects as the first embodiment.
  • the fourth embodiment differs from the first embodiment only in the difference between the angular position of the first anti-rotation shape portion 46 and the angular position of the second anti-rotation shape portion 49, and the rest of the configuration is the same. Therefore, parts corresponding to those in the first embodiment are denoted by the same reference numerals, and descriptions thereof are omitted.
  • the shape and dimensions of the second end 17 of the roller shaft 15 shown in FIG. 23C are the same as the shape and dimensions of the first end 16 of the roller shaft 15 shown in FIG. 23B.
  • the angular position around the axis of the roller shaft 15 of the second detent shape portion 49 shown in FIG. 23C is different from the angular position around the axis of the roller shaft 15 of the first detent shape portion 46 shown in FIG. 23B. different. That is, the difference between the angular position of the first detent shape portion 46 about the axis of the roller shaft 15 and the angular position of the second detent shape portion 49 about the axis of the roller shaft 15 is set to 90°.
  • the carrier 18 shown in FIG. 23A is first assembled, and then the roller shaft 15 is inserted into the second elongated hole 32 and the first elongated hole from the second disc 23 side. 31 can be inserted in sequence. Moreover, since the shape and dimensions of the first end portion 16 of the roller shaft 15 and the shape and dimensions of the second end portion 17 of the roller shaft 15 are the same, the roller shaft 15 can be divided into the second elongated hole 32 and the first elongated hole 31 . There is no need to distinguish between the front and rear directions of the roller shafts 15 when inserting them in order. Therefore, the work of assembling the roller shaft 15 of the planetary roller 14 to the carrier 18 can be easily automated.
  • the difference between the angular position of the first detent shape portion 46 and the angular position of the second detent shape portion 49 is large.
  • Figures 24A to 24C show a fifth embodiment of the present invention.
  • the fifth embodiment differs from the first embodiment only in the shapes of the first anti-rotation shape portion 46 and the second anti-rotation shape portion 49, and the rest of the configuration is the same. Therefore, parts corresponding to those in the first embodiment are denoted by the same reference numerals, and descriptions thereof are omitted.
  • first anti-rotation shaped portions 46 As shown in FIG. 24B, on the outer periphery of the first end portion 16 of the roller shaft 15, there are a pair of first anti-rotation shaped portions 46, and the roller shaft 15 for each of the pair of first anti-rotation shaped portions 46.
  • a pair of first partial cylindrical surfaces 47 are formed adjacent to each other around the axis.
  • the first anti-rotation shape portion 46 is a portion formed by cutting out a part of the outer circumference of the circular cross section by processing the outer circumference of the end portion of the roller shaft 15.
  • FIG. 31 has a shape capable of restricting the rotation of the roller shaft 15 when pressed against the longitudinal surface 45 of the roller shaft 31 .
  • the first anti-rotation shape portion 46 is a groove that extends parallel to the axis of the roller shaft 15 on the outer periphery of the roller shaft 15 .
  • the second anti-rotation shape portion 49 has a shape obtained by partially cutting the outer circumference of the circular end section of the roller shaft 15 (the rotation of the roller shaft 15 when pressed against an imaginary plane). It is a shape that can regulate the
  • the shape and dimensions of the second end 17 of the roller shaft 15 shown in FIG. 24C are the same as the shape and dimensions of the first end 16 of the roller shaft 15 shown in FIG. 24B. However, the angular position around the axis of the roller shaft 15 of the second detent shape portion 49 shown in FIG. 24C is different from the angular position around the axis of the roller shaft 15 of the first detent shape portion 46 shown in FIG. 24B. different.
  • the first anti-rotation shape portion 46 and the second anti-rotation shape portion 49 are positioned at the angular positions (first ) and the angular position of the second detent shape portion 49 about the axis of the roller shaft 15 (the second detent shape).
  • the normal direction of the plane when the shape portion 49 is engaged with the virtual plane) is formed so as to be different from each other.
  • the difference between the angular position of the first detent shape portion 46 about the axis of the roller shaft 15 and the angular position of the second detent shape portion 49 about the axis of the roller shaft 15 is 40° or more. It is set within a range of 50° or less (45° in the drawing).
  • the fifth embodiment has the same effects as the first embodiment.
  • the axially front disc is the first disc 22 (the disc in which the first elongated hole 31 is formed), and the axially rear disc is the second disk 23 (the disk in which the second elongated hole 32 is formed), but the front and rear in the axial direction may be reversed. That is, of the pair of discs 22 and 23, the disc on the rear side in the axial direction is the first disc 22 (the disc in which the first long hole 31 is formed), and the disc on the front side in the axial direction is the second disc 23 (the second long hole). It is also possible to use a disk with holes 32 formed therein.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Transmission Devices (AREA)
  • Braking Systems And Boosters (AREA)
  • Braking Arrangements (AREA)

Abstract

La dimension de largeur d'un second trou long (32) est définie pour être supérieure à la dimension de largeur d'un premier trou long (31). Une partie en forme d'inhibition de rotation (46) et une première surface cylindrique partielle (47) sont formées sur une périphérie externe d'une première partie extrémité (16) d'un arbre de rouleau (15), et la première partie en forme d'inhibition de rotation (46) vient en prise avec une surface longitudinale (45) du premier trou long (31) de façon à empêcher la rotation de l'arbre de rouleau (15). Une seconde partie en forme d'inhibition de rotation (49) et une seconde surface cylindrique partielle (50) sont formées sur une périphérie externe d'une seconde partie extrémité (17) de l'arbre de rouleau (15), et seule la seconde surface cylindrique partielle (50) est mise en contact avec une surface longitudinale (48) du second trou long (32) et supportée par celle-ci.
PCT/JP2022/024650 2021-06-28 2022-06-21 Mécanisme de mouvement linéaire de type à vis à rouleaux planétaires, et dispositif de frein électrique WO2023276770A1 (fr)

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JP2021-106568 2021-06-28
JP2021106568A JP2023004701A (ja) 2021-06-28 2021-06-28 遊星ローラねじ式直動機構および電動ブレーキ装置

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016098873A (ja) * 2014-11-19 2016-05-30 Ntn株式会社 電動式直動アクチュエータおよび電動式ブレーキ装置
JP2016217420A (ja) * 2015-05-19 2016-12-22 Ntn株式会社 電動式直動アクチュエータおよび電動式ブレーキ装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016098873A (ja) * 2014-11-19 2016-05-30 Ntn株式会社 電動式直動アクチュエータおよび電動式ブレーキ装置
JP2016217420A (ja) * 2015-05-19 2016-12-22 Ntn株式会社 電動式直動アクチュエータおよび電動式ブレーキ装置

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