WO2010061805A1 - Unité de poulie - Google Patents

Unité de poulie Download PDF

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Publication number
WO2010061805A1
WO2010061805A1 PCT/JP2009/069763 JP2009069763W WO2010061805A1 WO 2010061805 A1 WO2010061805 A1 WO 2010061805A1 JP 2009069763 W JP2009069763 W JP 2009069763W WO 2010061805 A1 WO2010061805 A1 WO 2010061805A1
Authority
WO
WIPO (PCT)
Prior art keywords
pulley
screw member
friction plate
hub
female screw
Prior art date
Application number
PCT/JP2009/069763
Other languages
English (en)
Japanese (ja)
Inventor
智昭 牧野
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 JP2008302107A external-priority patent/JP2010127370A/ja
Priority claimed from JP2008302070A external-priority patent/JP2010127369A/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2010061805A1 publication Critical patent/WO2010061805A1/fr

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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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • 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
    • F16D13/00—Friction clutches
    • F16D13/76—Friction clutches specially adapted to incorporate with other transmission parts, i.e. at least one of the clutch parts also having another function, e.g. being the disc of a pulley
    • 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
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
    • F16D43/21—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members
    • F16D43/213—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members with axially applied torque-limiting friction surfaces
    • F16D43/215—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members with axially applied torque-limiting friction surfaces with flat friction surfaces, e.g. discs
    • 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
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • F16D7/024—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces
    • F16D7/025—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs
    • 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
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms

Definitions

  • the present invention relates to a pulley unit that is used by being attached to a rotating shaft of an engine auxiliary machine such as an alternator using an engine as a drive source.
  • the rotation of the crankshaft of the engine is transmitted to the rotation shaft of an engine accessory such as an alternator via a belt transmission.
  • crankshaft varies in angular speed during one rotation under the influence of intermittent combustion in the cylinder and inertial force of the reciprocating piston, and the crankshaft is caused by the fluctuation of the angular speed.
  • a slip occurs between the pulley and the belt, and the belt wears due to the slip and the durability is lowered.
  • this pulley With built-in clutch on the rotating shaft of the engine accessory, if the rotating speed of the pulley is lower than the rotating speed of the rotating shaft of the engine accessory, the one-way clutch is disengaged and the pulley is free. Since it rotates, an increase in belt tension is prevented, and a decrease in belt durability can be suppressed.
  • Patent Document 2 a power transmission device described in Patent Document 2 that can effectively absorb fluctuations in the rotational speed of the pulley has been proposed.
  • This power transmission device is prevented from rotating with respect to the pulley between the pulley and the rotor shaft, and can move in the axial direction, and can rotate with respect to the rotor shaft and move in the axial direction.
  • the second annular race is incorporated, and the first annular race is biased toward the second annular race by the pressing of the coil spring, and on the back side of the second annular race (opposite to the first annular race).
  • a friction clutch that clutches the second annular race and the rotor shaft by pressing the coil spring is provided.
  • the power transmission device described in Patent Document 1 has a configuration in which the second annular race and the friction clutch are positioned in the axial direction by a rolling bearing that supports a pulley and a rotor shaft so as to be relatively rotatable, and a coil spring is formed by the rolling bearing. And a reaction force of the axial force applied to the first annular race by the cam action of the arcuate inclined surface. As a result, there is a problem that the durability of the rolling bearing is lowered.
  • an object of the present invention is to suppress a decrease in durability of a bearing that supports these members so as to be relatively rotatable between a pulley and a pulley hub.
  • the present invention supports a pulley and a pulley hub incorporated inside the pulley so as to be relatively rotatable by a bearing incorporated between one end portions of both the members.
  • Two projecting portions are provided on the outer diameter surface or the inner diameter surface of the pulley at an interval in the axial direction, and a male screw member and a female screw member that are screw-engaged with each other are incorporated between the two projecting portions.
  • One of the screw members is prevented from rotating around one of the pulley or the pulley hub, and the one projecting portion prevents movement outward in the axial direction, and the other screw member is the other of the pulley or the pulley hub.
  • the pulley or the pulley hub is supported between the other screw member and the other protrusion so as to be rotatable with respect to the shaft and movable in the axial direction.
  • a friction plate that is prevented from rotating and that is movable in the axial direction to form a friction clutch with the other screw member, and an elastic member that urges the friction plate toward the one projecting portion are incorporated, and
  • the pulley rotates relative to the pulley hub in one direction
  • the other screw member rotates relative to the one screw member in one direction, and axially moves toward the other protrusion with the friction plate.
  • the friction plate is moved, the elastic member is pushed by the friction plate to be elastically deformed so that the friction clutch is engaged, and the rotation of the pulley is transmitted to the pulley hub.
  • the friction plate in a state where torque is not applied to the pulley and the pulley hub, that is, in a state where the pulley is stopped, the friction plate is pressed against the other screw member by the biasing force of the elastic member. A small pressing force is acting.
  • the friction plate Due to the elastic deformation of the elastic member, the friction plate is strongly pressed against the other screw member, and the friction clutch is engaged. Further, since the screw portion of the other screw member against which the friction plate is pressed presses the screw portion of the one screw member, the friction resistance between the screw portions of both screw members increases.
  • the pulley hub tries to continue to rotate due to the inertial force, and the rotation of the pulley hub causes the friction plate to rotate, and the other screw member and one screw member that are clutch-coupled with the friction plate move in the other direction. Relative rotation occurs, and the other screw member moves to one projecting portion side.
  • the friction plate is also moved, the elastic member is extended, and the pressing force to the other screw member by the friction plate is lowered.
  • the coupled state of the friction clutch is released, slip occurs at the contact portion between the friction plate and the other screw member, and the pulley hub continues to rotate due to the inertial force.
  • the elastic member elastically deforms to absorb the rotational fluctuation of the pulley, and when the pulley stops, slippage occurs at the contact portion between the other screw member and the friction plate.
  • the pulley hub continues to rotate due to the inertial force. For this reason, it is possible to prevent the belt tension from abruptly increasing or slipping between the pulley and the belt.
  • the pulley and the pulley hub are configured to receive the pressing force of the elastic member that presses the friction plate against the other screw member by the two protruding portions formed on the outer diameter surface of the pulley hub or the inner diameter surface of the pulley.
  • the bearing is supported so as to be relatively rotatable, and the pressing force is not applied to the bearing, so that a decrease in the durability of the bearing can be suppressed.
  • the configuration of the two protrusions with respect to the outer diameter surface of the pulley hub or the inner diameter surface of the pulley, and one screw member of the two screw members when the pulley rotates relative to the pulley hub in one direction can be adopted as a specific configuration that rotates relative to the other screw member in one direction. That is, the two protrusions are provided on the outer diameter surface of the pulley hub at an axial interval, and are prevented from rotating by the pulley between the two protrusions.
  • the female screw member that is prevented from moving to the pulley hub and the male screw member that is supported so as to be rotatable and axially movable with respect to the pulley hub are incorporated, and between the male screw member and the other protruding portion.
  • a configuration in which the friction plate that is prevented from rotating with respect to the pulley hub and the elastic member are incorporated can be employed.
  • a stopper is provided on the outer diameter surface of the pulley hub to restrict the axial movement amount of the male screw member within the range of the maximum axial movement amount of the male screw member that is moved by the screw portion of the female screw portion. Then, excessive bending of the elastic member due to the male screw member moving in the axial direction more than necessary can be prevented, and a decrease in durability of the elastic member can be suppressed.
  • a configuration in which a radial bearing is incorporated between the inner diameter surface of the male screw member and the outer diameter surface of the pulley hub, or the one projecting portion and the female screw member It is possible to adopt a configuration in which a bearing holding member is provided between the opposite surfaces of the bearing holding member, and a radial bearing is incorporated between the radial outer surface of the bearing holding member and the inner diameter surface of the pulley.
  • a configuration in which a radial bearing is incorporated between the outer diameter surface of the female screw member and the inner diameter surface of the pulley, or the one projecting portion and the male screw member A structure in which a bearing holding member is provided between the opposing surfaces and a radial bearing is incorporated between the radial inner surface of the bearing holding member and the outer diameter surface of the pulley hub can be employed.
  • the pulley unit according to the present invention a configuration in which the male screw member and the female screw member are ball screws in which screws are engaged via balls, or a configuration in which the screw portions of the male screw member and the female screw member are slide screws is adopted. be able to.
  • the screw engagement is a screw connection between a screw thread and a screw groove, which is a general screw connection
  • the driving torque is reduced due to the rolling of the ball. Therefore, the relative rotation of the female screw member with respect to the male screw member becomes smooth.
  • the starting torque is small, torque transmission from the pulley to the pulley hub or switching between cutoffs becomes faster.
  • the friction coefficient can be increased, and the capacity of the transmission torque can be increased. Further, when the friction coefficient at the contact portion is increased, the pressing force applied to the friction plate by the elastic member necessary for torque transmission is reduced, and a decrease in the durability of the friction plate can be suppressed.
  • the male screw member or the female screw member that is the one screw member and the first screw member A friction material may be provided on at least one of the opposing surfaces of the two friction plates. Also in this case, similarly to the configuration in which the friction material is provided on at least one of the opposing surfaces of the other screw member and the friction plate, the capacity of the transmission torque can be increased and the decrease in the durability of the second friction plate can be suppressed. it can.
  • the pulley unit of the present invention receives the pressing force of the elastic member that presses the friction plate against the other screw member of the male screw member or the female screw member by two protrusions formed on the outer diameter surface of the pulley hub or the inner diameter surface of the pulley.
  • the bearing that supports the pulley and the pulley hub so as to be relatively rotatable can be prevented from being subjected to the pressing force, so that a decrease in the durability of the bearing can be suppressed, and the life can be extended.
  • Sectional drawing which shows the pulley unit which concerns on 1st Embodiment.
  • Enlarged sectional view showing the state before the pulley unit is activated
  • Enlarged sectional view showing the operating state of the pulley unit
  • Sectional drawing which shows the external thread member and internal thread member in the operation state of a pulley unit
  • Sectional drawing which shows the other structure of the external thread member and internal thread member of a pulley unit
  • Sectional drawing which shows the pulley unit which concerns on 3rd Embodiment.
  • Sectional drawing which shows the pulley unit which concerns on 4th Embodiment Enlarged sectional view showing the state before the pulley unit is activated Enlarged sectional view showing the operating state of the pulley unit Sectional drawing which shows the external thread member and internal thread member in the operation state of a pulley unit Sectional drawing which shows the other structure of the external thread member and internal thread member of a pulley unit Sectional drawing which shows the pulley unit which concerns on 5th Embodiment Sectional drawing which shows the pulley unit which concerns on 6th Embodiment
  • a pulley unit according to a first embodiment of the present invention will be described below with reference to FIGS.
  • This pulley unit is applied to an engine accessory of an automobile, and as shown in FIG. 1, includes a cylindrical pulley 1 having a double row V-groove 2 on an outer peripheral surface, and a pulley hub 3 incorporated inside the pulley. Yes.
  • the pulley 1 and the pulley hub 3 are supported so as to be relatively rotatable by a bearing 4 incorporated between opposite one ends thereof, and the bearing 4 includes a seal on one end side in the axial direction.
  • the outer periphery of the seal member 5 is press-fitted to the inner periphery of the other end, and the lip 6 formed on the inner periphery of the seal member 5 is in sliding contact with the outer periphery of the other end of the pulley hub 3.
  • the other end opening between the pulley 1 and the pulley hub 3 is closed to prevent foreign matter from entering the inside.
  • the pulley hub 3 is provided with a flange 7 as a protruding portion for positioning the bearing 4 in the axial direction at one end portion of the outer diameter surface, and a retaining ring 8 as a protruding portion is attached to the inner periphery of the other end portion.
  • a male screw member 9 and a female screw member 10 that are screw-engaged with each other are incorporated between the flange 7 and the retaining ring 8, and one of the screw members 9 and 10 is one screw member.
  • a washer 11 is incorporated between the female screw member 10 and the retaining ring 8.
  • the male screw member 9, which is the other screw member of the both screw members 9, 10, has a cylindrical shape, has a flange-shaped large diameter portion at the flange 7 side end portion, and an outer peripheral portion of the male screw member 9 on the retaining ring 8 side.
  • a helical thread groove 13 is formed as a threaded portion.
  • the male screw member 9 is supported by a radial bearing 14 formed of a needle roller bearing built between the inner periphery thereof and the outer periphery of the pulley hub 3 so as to be rotatable and movable in the axial direction.
  • the radial bearing 14 By incorporating the radial bearing 14, it is possible to receive a larger radial load applied to the pulley 1. However, when the radial load applied to the pulley 1 is relatively small, the radial bearing 14 may be omitted. Good.
  • the female screw member 10 that engages with the outer side of the male screw member 9 in the radial direction has a cylindrical shape.
  • a spline 12 is formed on the outer periphery of the male screw member 9. And rotate together. Further, the female screw member 10 is prevented from moving outward in the axial direction via a washer 11 by a retaining ring 8 which is a protruding portion.
  • a spiral screw groove 15 as a screw portion is formed in the inner peripheral portion of the female screw member 10, and a plurality of balls 16 are interposed between the screw groove 15 and the screw groove 13 of the male screw member 9. Yes. Accordingly, the male screw member 9, the female screw member 10 and the ball 16 constitute a ball screw. The female screw member 10 and the male screw member 9 are screw-engaged via the ball 16, and the male screw member 9 is axially connected to the female screw member 10. It can be moved to.
  • a friction plate 17 is incorporated between the male screw member 9 and the flange 7 to form a friction clutch with the large diameter portion of the male screw member 9.
  • the friction plate 17 is prevented from rotating with respect to the pulley hub 3 by fitting of a spline 18 formed between the fitting surfaces with the pulley hub 3 and is rotated integrally with the pulley hub 3.
  • the friction plate 17 can fix a friction material 19 mainly composed of a non-metallic material to a surface facing the male screw member 9 by a known bonding means.
  • the friction material 19 is not limited to a structure that is fixed only to the friction plate 17 as long as the friction coefficient can be increased at the contact portion between the male screw member 9 and the friction plate 17 forming the friction clutch. And at least one of them.
  • An elastic member 20 is incorporated between the friction plate 17 and the flange 7.
  • a disc spring is employed as the elastic member 20, and the friction plate 17 is biased toward the male screw member 9 (retaining ring 8), and the male screw member 9 moves toward the flange 7 with respect to the female screw member 10. Then, it is pressed by the friction plate 17 and elastically deforms. The friction plate 17 is pressed against the male screw member 9 by this elastic deformation, and the friction clutch is brought into a coupled state.
  • a ring-shaped stopper 21 is fitted between the friction plate 17 on the outer diameter surface of the pulley hub 3 and the flange 7, and the amount of movement of the male screw member 9 in the axial direction is moved by the screw portion of the female screw member 10.
  • the male screw member 9 is restricted within the range of the maximum amount of movement in the axial direction.
  • the pulley unit according to the first embodiment has the above-described structure, and when driving an alternator as an engine accessory, the pulley hub 3 is fitted to the rotating shaft of the alternator to prevent rotation, and the pulley 1 of the pulley unit A belt is stretched between a pulley attached to a crankshaft of the engine and the rotation of the crankshaft is transmitted to the pulley 1.
  • the friction plate 17 biased by the elastic member 20 exerts a small pressing force on the female screw member 10 in a state where the rotation of the pulley 1 is stopped.
  • rotational torque is input to the pulley 1 in the forward rotation direction in a state where this pressing force is applied, the female screw member 10 that is prevented from rotating about the pulley 1 rotates relative to the male screw member 9 in one direction.
  • the elastic member 20 is also elastically deformed so as to move together with the male screw member 9 and compress the elastic member 20 (see FIG. 3).
  • the friction plate 17 is strongly pressed against the male screw member 9 by the elastic restoring force of the elastic member 20 that has been elastically deformed, and the friction clutch is engaged. Further, when the male screw member 9 is pressed against the other axial end side (retaining ring 8 side) by the friction plate 17 (see arrow a in FIG. 4), one end side of the groove wall of the screw groove 13 of the male screw member 9 ( The portion on the flange 7 side presses the portion on the other end side (the retaining ring 8 side) of the groove wall of the thread groove 15 of the female screw member 10 through the ball 16.
  • the rotation of the pulley 1 is transmitted from the female screw member 10 to the male screw member 9 and is also transmitted to the pulley hub 3 via the friction plate 17 that forms a friction clutch with the male screw member 9. It rotates in the same direction as the pulley 1.
  • the fluctuation of the rotational speed of the pulley 1 is absorbed by the fluctuation of the elastic deformation amount. As a result, transmission of fluctuations in the rotational speed of the pulley 1 to the pulley hub 3 is prevented, and the friction clutch is maintained in the coupled state.
  • the pulley hub 3 tries to continue to rotate because the rotating shaft of the alternator has a large inertial force. Due to the rotation of the pulley hub 3 by the inertial force, the male screw member 9 and the female screw member 10 are relatively rotated in the other direction, and the male screw member 9 is moved in the axial direction opposite to the friction plate 17 side. As the male screw member 9 moves, the friction plate 17 also moves, the elastic member 20 extends, and the pressing force of the friction plate 17 on the male screw member 9 decreases. As a result, the coupled state of the friction clutch is released, slip occurs at the contact portion between the friction plate 17 and the male screw member 9, and the pulley hub 3 continues to rotate due to inertial force.
  • the elastic member 20 is elastically deformed to absorb the fluctuation of the rotational speed of the pulley 1, and when the pulley 1 is suddenly decelerated or stopped, Sliding occurs at the contact portion with the friction plate 17, and the pulley hub 3 continues to rotate due to the inertial force. For this reason, it is possible to prevent an abrupt increase in the tension of the belt and to prevent the occurrence of slip between the pulley 1 and the belt.
  • the male screw member 9 that receives the pressing force of the elastic member 20 by the flange 7 and the retaining ring 8 and is not loaded on the bearing 4 and is movable in the axial direction by relative rotation with the female screw member 10 is
  • the radial bearing 14 is slid and moved so that a large axial load is not applied to the radial bearing 14. For this reason, the possibility of damage to the bearing 4 and the radial bearing 14 is extremely reduced, and a pulley unit having excellent durability can be obtained.
  • the male screw member 9 when the amount of movement of the male screw member 9 in the axial direction is larger than necessary due to the relative rotation of the male screw member 9 and the female screw member 10 in one direction, the male screw member 9 is pressed by the friction plate 17 that moves with the male screw member 9.
  • the elastic member 20 may be bent excessively and be damaged.
  • the pulley unit according to this embodiment includes a ring-shaped stopper 21 on the outer diameter surface of the pulley hub 3 as shown in FIG.
  • the stopper 21 limits the amount of axial movement of the friction plate 17 that moves together with the male screw member 9, and can prevent excessive deformation of the elastic member 20.
  • the threaded portions of the male screw member 9 and the female screw member 10 are formed of ball screws that are screw-engaged via the balls 16.
  • a configuration in which the thread portion of the female screw member 10 is formed of a sliding screw can be employed.
  • the sliding screw is obtained by screwing a helical thread 22 formed on the inner peripheral surface of the female screw member 10 into the screw groove 13 of the male screw member 9.
  • a pulley unit according to a second embodiment of the present invention will be described with reference to FIG.
  • a bearing holding member 23 and a second friction plate 24 are incorporated between the retaining ring 8 and the female screw member 10, and instead of the radial bearing 14 incorporated between the pulley hub 3 and the male screw member 9,
  • a radial bearing 25 is incorporated between the outer diameter surface of the bearing holding member 23 and the inner diameter surface of the pulley 1.
  • the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
  • the bearing holding member 23 is positioned in the axial direction by the retaining ring 8 and is prevented from rotating with respect to the pulley hub 3, and a radial bearing 25 is incorporated between the outer diameter portion of the pulley 1 and the inner diameter surface of the pulley 1.
  • the radial bearing 25 can receive a radial load applied to the pulley 1, and the outer diameter surface of the pulley hub 3 and the inner diameter surface of the male screw member 9 according to the magnitude of the radial load applied to the pulley 1. Further, a radial bearing may be incorporated between the two.
  • the second friction plate 24 is prevented from rotating on the pulley hub 3 by fitting a spline 28 formed between the fitting surfaces with the pulley hub 3. Further, for the purpose of increasing the friction coefficient at the facing surface between the female screw member 10 and the second friction plate 24, a friction material 26 mainly composed of a non-metallic material may be fixed to at least one of the facing surfaces. .
  • the transmission torque from the pulley 1 can be transmitted from each of the two friction plates 17 and 24 to the pulley hub 3.
  • the transmission power can be reduced, wear of the friction plates 17 and 24 is suppressed, and the occurrence of seizure is prevented.
  • a pulley unit according to a third embodiment of the present invention will be described with reference to FIG.
  • the bearing holding member 23 is incorporated between the retaining ring 8 and the female screw member 10, and the outer diameter of the bearing holding member 23 is used instead of the radial bearing 14 incorporated between the pulley hub 3 and the male screw member 9.
  • a radial bearing 25 is incorporated between the surface and the inner diameter surface of the pulley 1 and a thrust bearing 27 is incorporated between the opposed surfaces of the bearing holding member 23 and the female screw member 10.
  • the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
  • the rotational resistance of the female screw member 10 can be reduced by incorporating a thrust bearing 27 between the opposed surfaces of the female screw member 10 and the bearing holding member 23, and the male screw member 9, the female screw member 10, Torque transmission during the period becomes stable, and the absorption performance of fluctuations in rotational speed can be further enhanced.
  • the radial bearing 25 is incorporated between the outer diameter surface of the bearing holding member 23 and the inner diameter surface of the pulley 1, it is possible to receive a radial load applied to the pulley 1.
  • a radial bearing may be further incorporated between the outer diameter surface of the pulley hub 3 and the inner diameter surface of the male screw member 9 according to the magnitude of the radial load applied to the pulley 1.
  • the bearing with the resin pulley according to the fourth embodiment has a flange 7 and a retaining ring 8 that are two projecting portions provided on the inner diameter surface of the pulley 1 at an interval in the axial direction.
  • the male screw member 9 and the female screw member 10 are incorporated between the retaining ring 8 and the friction plate 17 and the elastic member 20 that are prevented from rotating with respect to the pulley 1 between the female screw member 10 and the flange 7. It is incorporated.
  • a male screw member 9 and a female screw member 10 are incorporated between the flange 7 and the retaining ring 8, and a washer 11 is incorporated between the male screw member 9 and the retaining ring 8.
  • the male screw member 9 has a cylindrical shape and is prevented from rotating with respect to the pulley hub 3 by fitting a spline 12 formed on the inner peripheral portion thereof, so that the pulley hub 3 rotates integrally. Further, a helical thread groove 13 as a threaded portion is formed on the outer peripheral portion of the male screw member 9.
  • the female screw member 10 has a cylindrical shape with a bottom closed at one end in the axial direction, and is rotatably and axially moved by a radial bearing 14 formed of a needle roller bearing built in between the inner periphery of the pulley 1. Supported as possible.
  • the female screw member 10 is formed with a helical thread groove 15 as a threaded portion on the inner peripheral portion of the cylindrical portion, and the thread groove 15 and the thread groove 13 of the male screw member 9 disposed inside the cylindrical portion. A plurality of balls 16 are interposed therebetween. Accordingly, the male screw member 9, the female screw member 10 and the ball 16 constitute a ball screw. The female screw member 10 and the male screw member 9 are screw-engaged via the ball 16, and the female screw member 10 is axial with respect to the male screw member 9. It can be moved to.
  • a friction plate 17 is incorporated between the closed end of the female screw member 10 and the flange 7 to form a friction clutch between the closed end of the female screw member 10.
  • the friction plate 17 is prevented from rotating around the pulley 1 by the fitting of a spline 18 formed between the fitting surfaces with the pulley 1, and rotates integrally with the pulley 1.
  • the friction plate 17 can fix a friction material 19 mainly composed of a non-metallic material to a surface facing the female screw member 10 by a known bonding means.
  • the friction material 19 can be fixed to at least one of the female screw member 10 and the friction plate 17.
  • a disc spring is employed as the elastic member 20 between the friction plate 17 and the flange 7, and the friction plate 17 is biased toward the female screw member 10, and the female screw member 10 moves toward the flange 7 with respect to the male screw member 9. When it moves, it is elastically deformed by being pressed by the friction plate 17. The friction plate 17 is pressed against the female screw member 10 by this elastic deformation, and the friction clutch is brought into a coupled state.
  • a ring-shaped stopper 21 is fitted between the friction plate 17 and the flange 7 on the inner peripheral surface of the pulley 1, and the axial movement amount of the male screw member 9 is moved by the screw portion of the male screw member 9 by the stopper 21.
  • the internal thread member 10 is restricted within the range of the maximum amount of movement in the axial direction.
  • the pulley unit according to the fourth embodiment has the above-described structure.
  • the friction plate 17 biased by the elastic member 20 is A small pressing force is applied.
  • a rotational torque is input to the pulley 1 in the forward rotation direction with this pressing force acting, the torque is transmitted from the friction plate 17 to the female screw member 10, and the female screw member 10 and the male screw member 9 are relatively relative to each other in one direction. Rotate.
  • the female screw member 10 By the relative rotation of the female screw member 10 and the male screw member 9, the female screw member 10 is screw-engaged with the male screw member 9, and therefore moves to the flange 7 side as the other protruding portion (see FIG. 10). As the internal thread member 10 moves, the friction plate 17 also moves and elastically deforms so that the elastic member 20 is compressed.
  • the friction plate 17 is strongly pressed against the female screw member 10 by the elastic restoring force of the elastic member 20 which has been elastically deformed, and the friction clutch is engaged.
  • the female screw member 10 is pressed against the other axial end by the friction plate 17 (see arrow a in FIG. 11)
  • the other end portion of the groove wall of the screw groove 15 of the female screw member 10 becomes the ball 16.
  • a portion on one end side of the groove wall of the screw groove 13 of the male screw member 9 is pressed through
  • the male screw member 9 and the female screw member 10 are relative to each other as in the first embodiment.
  • the female screw member 10 rotates and the female screw member 10 moves in the axial direction with respect to the male screw member 9, and the elastic deformation amount of the elastic member 20 in the axial direction due to the pressing from the friction plate 17 varies.
  • the fluctuation of the rotational speed of the pulley 1 is absorbed by the fluctuation of the elastic deformation amount. As a result, transmission of fluctuations in the rotational speed of the pulley 1 to the pulley hub 3 is prevented, and the friction clutch is maintained in the coupled state.
  • the pulley hub 3 tries to continue to rotate because the rotating shaft of the alternator has a large inertial force. Due to the rotation of the pulley hub 3 by the inertial force, the male screw member 9 and the female screw member 10 rotate relative to each other, and the female screw member 10 moves in the axial direction opposite to the friction plate 17 side. As the female screw member 10 moves, the friction plate 17 also moves, the elastic member 20 expands, and the pressing force applied to the female screw member by the friction plate 17 decreases. As a result, the coupled state of the friction clutch is released, slip occurs at the contact portion between the friction plate 17 and the female screw member 10, and the pulley hub 3 continues to rotate due to the inertial force.
  • the elastic member 20 is elastically deformed to absorb the rotational speed of the pulley 1, and when the pulley 1 is suddenly decelerated or stopped, Sliding occurs at the contact portion with the friction plate 17, and the pulley hub 3 continues to rotate due to the inertial force. For this reason, it is possible to prevent an abrupt increase in the tension of the belt and to prevent the occurrence of slip between the pulley 1 and the belt.
  • the female screw member 10 that receives the pressing force of the elastic member 20 by the flange 7 and the retaining ring 8 and is not loaded on the bearing 4 and can move in the axial direction by relative rotation with the male screw member 9 is
  • the radial bearing 14 is slid and moved so that a large axial load is not applied to the radial bearing 14. For this reason, the possibility of damage to the bearing 4 and the radial bearing 14 is extremely reduced, and a pulley unit having excellent durability can be obtained.
  • the friction plate 17 that moves together with the female screw member 10 is pressed.
  • the elastic member 20 may be bent due to excessive bending.
  • the pulley unit according to this embodiment includes a ring-shaped stopper 21 on the inner diameter surface of the pulley 1 as shown in FIG.
  • the stopper 21 limits the amount of axial movement of the friction plate 17 that moves together with the female screw member 10, and can prevent excessive deformation of the elastic member 20.
  • the male screw member 9 and the screw portion of the female screw member 10 are composed of ball screws that are screw-engaged via balls 16.
  • a configuration in which the thread portion of the female screw member 10 is formed of a sliding screw can be employed.
  • the sliding screw is obtained by screwing a helical thread 22 formed on the inner peripheral surface of the female screw member 10 into the screw groove 13 of the male screw member 9.
  • a pulley unit according to a fifth embodiment of the present invention will be described with reference to FIG.
  • a bearing holding member 23 and a second friction plate 24 are incorporated between the retaining ring 8 and the male screw member 9, and instead of the radial bearing 14 incorporated between the pulley 1 and the female screw member 10,
  • the same components as those in the fourth embodiment are denoted by the same reference numerals, and the description thereof is omitted.
  • the bearing holding member 23 is positioned in the axial direction by the retaining ring 8 and is prevented from rotating with respect to the pulley 1, and a radial bearing 25 is incorporated between the outer diameter surface of the pulley hub 3 at the inner diameter portion thereof.
  • the radial bearing 25 can receive a radial load applied to the pulley 1, and further, between the inner diameter surface of the pulley 1 and the outer diameter surface of the female screw member 10, depending on the magnitude of the radial load.
  • a radial bearing may be incorporated.
  • the second friction plate 24 is prevented from rotating around the pulley 1 by fitting a spline 28 formed between the fitting surfaces with the pulley 1. Further, for the purpose of increasing the friction coefficient at the facing surface between the male screw member 9 and the second friction plate 24, a friction material 26 mainly composed of a nonmetallic material may be fixed to at least one of the facing surfaces. .
  • the transmission torque from the pulley 1 can be transmitted from each of the two friction plates 17 and 24 to the pulley hub 3.
  • the transmission power can be reduced, wear of the friction plates 17 and 24 is suppressed, and the occurrence of seizure is prevented.
  • a pulley unit according to a sixth embodiment of the present invention will be described with reference to FIG.
  • a bearing holding member 23 is incorporated between the retaining ring 8 and the male screw member 9, and an inner diameter surface of the bearing holding member 23 is used instead of the radial bearing 14 incorporated between the pulley 1 and the female screw member 10.
  • a radial bearing 25 is incorporated between the outer peripheral surface of the pulley hub 3 and the thrust bearing 27 between the opposing surfaces of the bearing holding member 23 and the male screw member 9.
  • the same components as those in the fourth embodiment are denoted by the same reference numerals, and the description thereof is omitted.
  • the rotational resistance of the male screw member 9 can be reduced by incorporating the thrust bearing 27 between the opposing surfaces of the male screw member 9 and the bearing holding member 23, and the male screw member 9, the female screw member 10, Torque transmission during the period becomes stable, and the absorption performance of fluctuations in rotational speed can be further enhanced.
  • the radial bearing 25 is incorporated between the inner diameter surface of the bearing holding member 23 and the outer diameter surface of the pulley hub 3, it is possible to receive a radial load applied to the pulley 1.
  • a radial bearing may be further incorporated between the inner diameter surface of the pulley 1 and the outer diameter surface of the female screw member 10 according to the magnitude of the radial load.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pulleys (AREA)

Abstract

L'invention consiste à augmenter la durabilité d'un palier disposé entre une poulie et un moyeu de poulie et qui supporte ces composants de manière à leur permettre de tourner librement l'un par rapport à l'autre. Une poulie (1) et un moyeu de poulie (3), qui est assemblé à l'intérieur de celle-ci, sont supportés par un palier (4) de manière à pouvoir tourner librement l'un par rapport à l'autre. Une bride (7) et une bague d'arrêt (8) sont disposées sur la surface de diamètre extérieur du moyeu de poulie (3) ; un élément fileté femelle (10), dont la rotation est bloquée par rapport à la poulie (1), et dont le mouvement axial vers l'extérieur est empêché par la bague d'arrêt (8), et un élément fileté mâle (9), qui est supporté de manière à tourner et se déplacer axialement par rapport au moyeu de poulie (3), et qui forme conjointement avec l'élément fileté femelle (10) une vis à bille, sont assemblés entre la bride (7) et la bague d'arrêt (8). Un plateau de friction (17), dont la rotation est empêchée par rapport au moyeu de poulie (3), et qui forme un embrayage à friction entre celui-ci et l'élément fileté mâle (9), et un élément élastique (20), qui force le plateau de friction (17) vers l'élément fileté mâle (9), sont assemblés entre l'élément fileté mâle (9) et la bride (7) de telle sorte que la force de compression de l'élément élastique (20) soit reçue par la bride (7) et la bague d'arrêt (8), et que la force de compression ne s'exerce pas sur le palier (4).
PCT/JP2009/069763 2008-11-27 2009-11-24 Unité de poulie WO2010061805A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2008-302107 2008-11-27
JP2008302107A JP2010127370A (ja) 2008-11-27 2008-11-27 プーリユニット
JP2008302070A JP2010127369A (ja) 2008-11-27 2008-11-27 プーリユニット
JP2008-302070 2008-11-27

Publications (1)

Publication Number Publication Date
WO2010061805A1 true WO2010061805A1 (fr) 2010-06-03

Family

ID=42225680

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2009/069763 WO2010061805A1 (fr) 2008-11-27 2009-11-24 Unité de poulie

Country Status (1)

Country Link
WO (1) WO2010061805A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012101020A1 (fr) * 2011-01-26 2012-08-02 Rolls-Royce Plc Dispositif d'accouplement à limitation de couple
US9022193B2 (en) * 2013-03-08 2015-05-05 Dayco Ip Holdings, Llc Recirculating ball screw assembly
US9291217B2 (en) 2014-04-08 2016-03-22 Dayco Ip Holdings, Llc Pulley assembly with radially oriented decoupling mechanism
US9850997B2 (en) 2013-08-06 2017-12-26 Dayco Europe S.R.L Filtering pulley for a belt drive

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000227128A (ja) * 1999-02-05 2000-08-15 Koyo Seiko Co Ltd 一方向クラッチ
JP2003207033A (ja) * 2001-11-29 2003-07-25 Ntn Corp 軸方向長さを小さくしたオーバーランニングクラッチプーリー
JP2004257535A (ja) * 2003-02-27 2004-09-16 Koyo Seiko Co Ltd 動力伝達装置
JP2008223979A (ja) * 2007-03-15 2008-09-25 Jtekt Corp プーリユニット
WO2009142139A1 (fr) * 2008-05-20 2009-11-26 Ntn株式会社 Unité de poulie

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000227128A (ja) * 1999-02-05 2000-08-15 Koyo Seiko Co Ltd 一方向クラッチ
JP2003207033A (ja) * 2001-11-29 2003-07-25 Ntn Corp 軸方向長さを小さくしたオーバーランニングクラッチプーリー
JP2004257535A (ja) * 2003-02-27 2004-09-16 Koyo Seiko Co Ltd 動力伝達装置
JP2008223979A (ja) * 2007-03-15 2008-09-25 Jtekt Corp プーリユニット
WO2009142139A1 (fr) * 2008-05-20 2009-11-26 Ntn株式会社 Unité de poulie

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012101020A1 (fr) * 2011-01-26 2012-08-02 Rolls-Royce Plc Dispositif d'accouplement à limitation de couple
US9051972B2 (en) 2011-01-26 2015-06-09 Rolls-Royce Plc Torque-limiting coupling
US9022193B2 (en) * 2013-03-08 2015-05-05 Dayco Ip Holdings, Llc Recirculating ball screw assembly
US9850997B2 (en) 2013-08-06 2017-12-26 Dayco Europe S.R.L Filtering pulley for a belt drive
US9291217B2 (en) 2014-04-08 2016-03-22 Dayco Ip Holdings, Llc Pulley assembly with radially oriented decoupling mechanism

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