WO2010050408A1 - Pulley unit - Google Patents

Pulley unit Download PDF

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Publication number
WO2010050408A1
WO2010050408A1 PCT/JP2009/068245 JP2009068245W WO2010050408A1 WO 2010050408 A1 WO2010050408 A1 WO 2010050408A1 JP 2009068245 W JP2009068245 W JP 2009068245W WO 2010050408 A1 WO2010050408 A1 WO 2010050408A1
Authority
WO
WIPO (PCT)
Prior art keywords
pulley
cam disk
cam
friction clutch
movable
Prior art date
Application number
PCT/JP2009/068245
Other languages
French (fr)
Japanese (ja)
Inventor
真昭 福田
聡 宇都宮
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 JP2008277631A external-priority patent/JP2010106903A/en
Priority claimed from JP2008299096A external-priority patent/JP2010127294A/en
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2010050408A1 publication Critical patent/WO2010050408A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16D43/216—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 with multiple lamellae
    • 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
    • F16D43/24—Automatic clutches actuated entirely mechanically controlled by acceleration or deceleration of angular speed
    • 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 mainly relates to a pulley unit that is used by being mounted on a rotating shaft of an engine auxiliary machine such as an alternator using an engine as a drive source.
  • a pulley attached to the rotation shaft of the engine accessory is also included. Try to decelerate suddenly.
  • the rotating shaft of the alternator has a large inertial force, so the pulley attached to the rotating shaft keeps rotating at a constant speed.
  • a large rotational speed difference is generated between the pulley on the crankshaft and the pulley on the rotating shaft of the alternator, and the belt tension increases and is easily damaged.
  • crankshaft fluctuates in angular speed during one rotation due to intermittent in-cylinder combustion in the engine and the inertial force of a reciprocating piston. Slip occurs between the pulley and the belt, and the slip causes wear of the belt, resulting in a decrease in durability.
  • a first annular race that is prevented from rotating with respect to the pulley between the opposed surfaces of the pulley and the rotor shaft and is movable in the axial direction is provided.
  • a friction clutch is provided for clutch-connecting the second annular race and the rotor shaft by pressing the coil spring, and is formed on the opposing surfaces of the first annular race and the second annular race when the rotational speed fluctuation occurs in the pulley.
  • the first annular race is moved away from the second annular race by the cam action of the arcuate slope, and the rotational speed is changed by the axial movement of the first annular race and the compression of the coil spring. So as to absorb the.
  • the second annular race and the friction clutch are positioned in the axial direction by a rolling bearing that relatively rotatably supports the pulley and the rotor shaft. Since the rolling bearing receives the pressing force of the coil spring and receives the reaction force of the axial force applied to the first annular race by the cam action of the arcuate slope, the durability of the rolling bearing is reduced. There is an inconvenience.
  • An object of the present invention is to suppress a decrease in durability of a bearing that rotatably supports a pulley and a pulley hub.
  • the pulley and the pulley hub incorporated inside the pulley are relatively rotatably supported by a bearing incorporated between one end portions of both members.
  • Two protrusions are provided on the outer diameter surface of the pulley hub at an interval in the axial direction, and the pulley is prevented from rotating between the two protrusions.
  • a fixed cam disk to be blocked and a movable cam disk supported so as to be rotatable with respect to the pulley hub and movable in the axial direction are incorporated, and both cams are disposed between the opposed surfaces of the fixed cam disk and the movable cam disk.
  • a torque cam that moves the movable cam disk in a direction away from the fixed cam disk by relative rotation in one direction of the disk and engages both cam disks in the rotation direction at the time of relative rotation in the other direction.
  • a multi-plate friction clutch that couples the movable cam disc and a pulley hub between the movable cam disc and the other protrusion, and the multi-plate friction clutch when the movable cam disc moves away from the fixed cam disc. This is a structure that incorporates an elastic member that is elastically deformed by the pressing and that restores the multi-plate friction clutch.
  • the multi-plate friction clutch is in a disengaged state where slipping occurs when the pulley is stopped.
  • the fixed cam disk and the movable cam disk rotate relative to each other in one direction.
  • the torque cam acts by the relative rotation, and the movable cam disk moves away from the fixed cam disk.
  • the multi-plate friction clutch also moves together with the movable cam disk to elastically deform the elastic member. Due to the elastic deformation of the elastic member, the multi-plate friction clutch enters a coupled state in which the movable cam disk and the pulley hub are coupled.
  • the rotation of the pulley is transmitted from the fixed cam disk to the movable cam disk via the torque cam, and from the movable cam disk to the pulley hub via the friction plate, and the pulley hub rotates in the same direction as the pulley. .
  • the torque cam returns to the state where the movable cam disk is released due to the rotation of the pulley hub due to the inertial force, the elastic member expands and the pressing force becomes weaker, and the multi-plate friction clutch enters the disengaged state.
  • slip occurs in the multi-plate friction clutch, and the pulley hub continues to rotate due to the inertial force.
  • the elastic member elastically deforms to absorb the rotation fluctuation of the pulley, and when the pulley stops, the multi-plate friction clutch slips and the pulley hub rotates due to inertial force. Since the belt tension continues, the belt tension does not increase rapidly, and there is no inconvenience that slip occurs between the pulley and the belt.
  • a stopper is provided on the outer diameter surface of the pulley hub to limit the amount of movement of the movable cam disk in the axial direction within the range of the maximum movement amount of the movable cam disk moved by the torque cam. Can be prevented, and deterioration of durability due to excessive bending of the elastic member can be suppressed.
  • the friction plate at one end in the axial direction contacting the elastic member and the elastic member are prevented from rotating on the pulley hub, the friction plate at one end in the axial direction and the elastic member Can be prevented from rotating relative to each other, so that contact wear of the elastic member can be suppressed. For this reason, there is no inconvenience that the load characteristic of the elastic member changes, and the slip of the multi-plate friction clutch can be prevented.
  • the pulley and the pulley hub incorporated inside the pulley are relatively rotatably supported by a bearing incorporated between one end portions of both members.
  • Two protrusions are provided on the inner diameter surface of the pulley at an interval in the axial direction, and the pulley hub is prevented from rotating between the two protrusions, and one protrusion prevents movement outward in the axial direction.
  • the fixed cam disk and a movable cam disk supported so as to be rotatable with respect to the pulley and movable in the axial direction are incorporated, and both cam disks are disposed between the opposed surfaces of the fixed cam disk and the movable cam disk.
  • a torque cam that moves the movable cam disc in a direction away from the fixed cam disc by relative rotation in one direction and engages both cam discs in the rotation direction at the time of relative rotation in the other direction.
  • a multi-plate friction clutch that couples the movable cam disk and a pulley hub between the movable cam disk and the other protrusion, and the multi-plate friction clutch when the movable cam disk moves away from the fixed cam disk.
  • the multi-plate friction clutch is in a disengaged state where slipping occurs when the pulley is stopped.
  • the fixed cam disk and the movable cam disk rotate relative to each other in one direction.
  • the torque cam acts by the relative rotation, and the movable cam disk moves away from the fixed cam disk.
  • the multi-plate friction clutch also moves together with the movable cam disk to elastically deform the elastic member. Due to the elastic deformation of the elastic member, the multi-plate friction clutch enters a coupled state in which the movable cam disk and the pulley hub are coupled.
  • the rotation of the pulley is transmitted from the multi-plate friction clutch to the movable cam disk, and is also transmitted to the pulley hub via the torque cam and the fixed cam disk, so that the pulley hub rotates in the same direction as the pulley.
  • the torque cam returns to the state where the movable cam disk is released due to the rotation of the pulley hub due to the inertial force, the elastic member expands and the pressing force becomes weaker, and the multi-plate friction clutch enters the disengaged state.
  • slip occurs in the multi-plate friction clutch, and the pulley hub continues to rotate due to the inertial force.
  • the elastic member elastically deforms to absorb the rotation fluctuation of the pulley, and when the pulley stops, the multi-plate friction clutch slips and the pulley hub rotates due to inertial force. Since the belt tension continues, the belt tension does not increase rapidly, and there is no inconvenience that slip occurs between the pulley and the belt.
  • the torque cam includes an inclined cam surface that is inclined with a downward gradient in the circumferential direction, and an engagement surface that is formed continuously at a lower end of the inclined cam surface. And a pair of opposed cam grooves formed on the opposed surfaces of the fixed cam disk and the movable cam disk so that the gradient of the inclined cam surface is reversed, and is incorporated between the opposed pair of cam grooves. Or an inclined cam surface inclined with a downward slope in the circumferential direction and an engaging surface formed continuously at the lower end of the inclined cam surface at the groove bottom. It may be composed of a cam groove having a cam projection and a cam projection adapted to the cam groove.
  • the friction coefficient at each contact portion can be increased, so that the capacity of the transmission torque can be increased. it can. On the contrary, it is possible to reduce the pressing force applied to the friction plate and suppress the decrease in the durability of the friction plate.
  • each of the plurality of friction plates forming the multi-plate friction clutch is subjected to a hardening treatment consisting of one of nitriding treatment, carburizing treatment, and high-frequency heat treatment, or titanium nitride (TiN), chromium nitride (CrN).
  • a hardening treatment consisting of one of nitriding treatment, carburizing treatment, and high-frequency heat treatment, or titanium nitride (TiN), chromium nitride (CrN).
  • TiN titanium nitride
  • CrN chromium nitride
  • each of the plurality of friction plates forming the multi-plate friction clutch is made of an aluminum alloy or a magnesium alloy, the moment of inertia can be reduced and the pulley unit can be reduced in weight.
  • the axial force applied to the movable cam disk by the pressing force of the elastic member pressing the multi-plate friction clutch against the movable cam disk or the action of the torque cam by the two protrusions formed on the inner diameter surface of the pulley is not subjected to the pressing force or the axial force, and the durability of the bearing is reduced. Deterioration can be suppressed.
  • both the first and second inventions by adopting a multi-plate friction clutch as the friction clutch, the rotation of the pulley can be transmitted to the pulley hub from each contact portion of the plurality of friction plates. Therefore, the pressing force required for the friction clutch can be reduced. For this reason, the surface pressure in the torque cam portion can be reduced, and the durability of the torque cam portion can be improved.
  • Sectional view along the line II-II in FIG. is sectional drawing of the torque cam shown in FIG. 1
  • (b) is sectional drawing which shows the operating state of a torque cam.
  • Sectional drawing which shows the operating state of the torque cam shown in FIG. Sectional view showing another example of a friction clutch (A), (b), (c), (d) is a front view showing another example of the friction plate of the friction clutch.
  • (A) is sectional drawing which shows the other example of a torque cam
  • (b) is sectional drawing which shows an operation state.
  • FIG. 1 shows a first embodiment of a pulley unit according to the present invention.
  • the pulley 1 has double rows of V-grooves 2 on its outer peripheral surface, and a pulley hub 3 is incorporated inside the pulley 1.
  • the pulley 1 and the pulley hub 3 are relatively rotatably supported by a bearing 4 with a single seal that is incorporated between opposite ends thereof.
  • the outer periphery of the seal member 5 is press-fitted into the inner periphery of the other end of the pulley 1, and the lip 6 formed on the inner periphery of the seal member 5 is in elastic contact with the outer periphery of the other end of the pulley hub 3. As a result, the opening of the other end of the pulley 1 is closed, and foreign matter is prevented from entering the inside.
  • a flange 7 as a protruding portion for positioning the bearing 4 in the axial direction is provided at one end portion of the outer diameter surface of the pulley hub 3.
  • a retaining ring 8 as a protruding portion is attached to the outer periphery of the other end of the pulley hub 3.
  • a fixed cam disk 9 and a movable cam disk 10 are assembled between the flange 7 and the retaining ring 8, and a washer 11 is assembled between the fixed cam disk 9 and the retaining ring 8.
  • the fixed cam disk 9 is prevented from rotating around the pulley 1 by the fitting of the spline 12, and rotates together with the pulley 1.
  • a radial bearing 13 composed of a needle roller bearing is incorporated between the fixed cam disk 9 and the movable cam disk 10 and the pulley hub 3 and the radial bearing 13 is loaded on the pulley 1 with the bearing 4. It is designed to support the load.
  • the movable cam disk 10 is supported by the radial bearing 13 so as to be rotatable and movable in the axial direction, and a torque cam 14 is provided between the opposed surfaces of the movable cam disk 10 and the fixed cam disk 9.
  • the torque cam 14 is assembled between a pair of opposed cam grooves 15 and 16 formed on the opposed surfaces of the fixed cam disk 9 and the movable cam disk 10, and the cam grooves 15 and 16, respectively. And a ball 17 as a rolling element.
  • the pair of opposed cam grooves 15 and 16 include inclined cam surfaces 15a and 16a that are inclined with a downward gradient in the circumferential direction, and arcuate engagement surfaces 15b and 16b that are continuous to the lower ends of the inclined cam surfaces 15a and 16a.
  • the inclined cam surfaces 15a and 16a are formed on the opposing surfaces of the fixed cam disk 9 and the movable cam disk 10 so that the slopes of the inclined cam surfaces 15a and 16a are opposite to each other.
  • the torque cam 14 separates the movable cam disk 10 from the fixed cam disk 9 by the rolling movement of the ball 17 along the inclined cam surfaces 15 a and 16 a during relative rotation of the fixed cam disk 9 and the movable cam disk 10 in one direction. It is designed to move in the direction. Further, during relative rotation of the fixed cam disk 9 and the movable cam disk 10 in the other direction, the ball 17 is engaged with the engagement surfaces 15b and 16b, and the fixed cam disk 9 and the movable cam disk 10 are engaged in the rotation direction. It is supposed to let you.
  • a multi-plate friction clutch 20 and an elastic member 30 that biases the multi-plate friction clutch 20 toward the movable cam disk 10 are incorporated between the movable cam disk 10 and the flange 7. .
  • the multi-plate friction clutch 20 has a plurality of friction plates. Here, two inner friction plates 21 and one outer friction plate 22 are shown, but the number of friction plates is not limited to this.
  • the inner side friction plate 21 and the outer side friction plate 22 are arranged alternately in the axial direction in a cylindrical portion 23 formed on the outer peripheral portion of one side of the movable cam disk 10, and the inner side friction plate 21 is interposed via a spline 24.
  • the pulley hub 3 is prevented from rotating, and rotates together with the pulley hub 3.
  • the outer friction plate 22 is prevented from rotating by the cylindrical portion 23 via a spline 25 and rotates integrally with the movable cam disk 10.
  • the elastic member 30 is made of a disc spring.
  • the elastic member 30 is elastically deformed by being pressed by the multi-plate friction clutch 20 when the movable cam disk 10 moves in the axial direction away from the fixed cam disk 9, and the elastic plate 30 of the multi-plate friction clutch 20 is elastically deformed. , 22 are pressed against the movable cam disk 10, and the multi-plate friction clutch 20 is switched to the coupled state.
  • a ring-shaped stopper 31 is fitted between the multi-plate friction clutch 20 and the flange 7 on the outer diameter surface of the pulley hub 3, and the axial movement amount of the movable cam disk 10 is moved by the torque cam 14 by the stopper 31.
  • the movable cam disk 10 is regulated within the range of the maximum movement amount.
  • the pulley unit shown in 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 it from rotating, and the pulley of the pulley unit A belt is stretched between 1 and a pulley attached to the crankshaft of the engine so that the rotation of the crankshaft is transmitted to the pulley 1.
  • FIG. 4 shows the moving state of the movable cam disk 10, and the elastic member 30 is elastically deformed by the movement of the movable cam disk 10, and the contact pressure and the movable pressure of the plurality of friction plates 21 and 22 of the multi-plate friction clutch 20 are movable.
  • the contact pressure between the cam disk 10 and the inner friction plate 21 facing the cam disk 10 is increased, and the multi-plate friction clutch 20 is brought into a coupled state.
  • the rotation of the pulley 1 is transmitted from the fixed cam disk 9 to the movable cam disk 10 via the torque cam 14, and from the movable cam disk 10 to the pulley hub 3 via the multi-plate friction clutch 20, and the pulley hub. 3 rotates in the same direction as the pulley 1.
  • the elastic member 30 is elastically deformed to absorb the rotation fluctuation of the pulley 1, and when the pulley 1 decelerates suddenly or stops, the multi-plate friction clutch 20 Since the pulley hub 3 continues to rotate due to the inertial force due to slippage at the contact portions of the friction plates 21 and 22, the belt tension does not increase suddenly, and between the pulley 1 and the belt. There is no inconvenience of slipping.
  • the axial force generated by the pressing force of the elastic member 30 and the operation of the torque cam 14 is received by the flange 7 and the retaining ring 8 and is not loaded on the bearing 4, and the axial direction by the operation of the torque cam 14. Since the movable cam disk 10 that moves in a sliding manner slides on the radial bearing 13, a large axial force is not applied to the radial bearing 13. For this reason, the bearing 4 and the radial bearing 13 are hardly damaged, and a pulley unit having excellent durability can be obtained.
  • a ring-shaped stopper 31 is provided on the outer diameter surface of the pulley hub 3, and the amount of movement of the movable cam disk 10 in the axial direction is limited by the stopper 31. The rotation of the pulley 1 can be reliably transmitted to the pulley hub 3.
  • a multi-plate friction clutch 20 as a friction clutch for connecting and releasing the pulley 1 and the pulley hub 3, the pulley from each contact portion of the plurality of friction plates 21 and 22. 1 rotation can be transmitted to the pulley hub 3.
  • the pressing force applied to the multi-plate friction clutch 20 from the elastic member 30 can be lowered, and the surface pressure at the torque cam 14 portion is reduced by the reduction of the pressing force. Therefore, the durability of the torque cam 14 can be improved.
  • a notch 32 is formed on the inner surface of the elastic member 30 that applies an elastic force to the inner friction plate 21 at one end in the axial direction of the multi-plate friction clutch 20, for example, as shown by a chain line in FIG.
  • the protrusion 33 that fits the notch 32 is provided on the flange 7 of the third flange and the elastic member 30 is prevented from rotating around the pulley hub, the inner friction plate 21 and the elastic member 30 can be prevented from rotating relative to each other. Therefore, contact wear of the elastic member 30 can be suppressed. For this reason, there is no inconvenience that the load characteristic of the elastic member 30 changes, and the slip of the multi-plate friction clutch 20 can be prevented.
  • the friction material 26 when the friction material 26 is provided on at least one of the contact surfaces of the plurality of friction plates 21 and 22 forming the multi-plate friction clutch 20, the friction coefficient at each contact surface can be increased. Therefore, the capacity of transmission torque can be increased. Conversely, since the pressing force applied to the friction plates 21 and 22 can be reduced, it is possible to suppress a decrease in the durability of the friction plates 21 and 22.
  • the respective contact surfaces of the plurality of friction plates 21 and 22 forming the multi-plate friction clutch 20 are subjected to hardening treatment such as nitriding treatment, carburizing treatment, and high-frequency heat treatment, the hardness of the friction plates 21 and 22 can be increased. It is possible to improve wear resistance and durability.
  • a nitride film such as titanium nitride, chromium nitride, titanium nitride aluminum, titanium carbonitride, titanium carbide, etc. may be used instead of the above-described curing treatment.
  • a hard coating made of a carbide coating may be provided.
  • a plurality of lubricant discharge grooves 27 are provided radially on the friction surfaces of the inner side friction plate 21 and the outer side friction plate 22.
  • the lubricant discharge groove 27 is formed in the friction plates 21 and 22 in this way, when the inner friction plate 21 and the outer friction plate 22 are pressed against each other by the pressing of the elastic member 30, the friction plates 21 and 22 are Since the intervening lubricating oil is pushed into the lubricant discharge groove 27, it is possible to prevent the lubricant from excessively adhering to the friction surface and to prevent the multi-plate friction clutch 20 from slipping.
  • each of the plurality of friction plates 21 and 22 forming the multi-plate friction clutch 20 is made of aluminum alloy or magnesium alloy, the moment of inertia can be reduced and the weight of the pulley unit can be reduced.
  • the torque cam 14 is composed of the cam grooves 15, 16 and the ball 17, but may be composed of a roller instead of the ball 17.
  • the fixed cam disk 9 is formed continuously with the inclined cam surface 18a inclined with a downward gradient in the circumferential direction and the lower end of the inclined cam surface 18a in the axial direction.
  • the cam groove 18 having the engaging surface 18b facing the groove may be formed, and the movable cam disk 10 may be provided with a cam protrusion 19 adapted to the cam groove 18.
  • a cam protrusion may be provided on the fixed cam disk 9 and a cam groove may be formed on the movable cam disk 10.
  • FIG. 7B shows the operating state of the torque cam 14.
  • a flange 40 and a retaining ring 41 as protruding portions are provided on the inner diameter surface of the pulley 1 with an interval in the axial direction, and between the flange 40 and the retaining ring 41 in order from the retaining ring 41 side,
  • a washer 42, a fixed cam disk 9, a movable cam disk 10, an outer side friction plate 22 and an inner side friction plate 21 constituting a multi-plate friction clutch 20, and an elastic member 43 made up of a disc spring are incorporated, and is movable with the fixed cam disk 9.
  • a torque cam 14 is provided between a portion facing the cam disk 10.
  • the fixed cam disk 9 is prevented from rotating with respect to the pulley hub 3 by the spline 44
  • the outer side friction plate 22 is prevented from rotating with respect to the pulley 1 by the spline 45, and is movable in the axial direction.
  • the side friction plate 21 is supported by a cylindrical portion 46 formed on the inner peripheral portion of the side surface of the movable cam disk 10 through a spline 47 and supported so as to be movable in the axial direction.
  • a ring-shaped stopper 48 is incorporated between the outer diameter surface of the elastic member 43 and the inner diameter surface of the pulley 1 so that the moving amount of the movable cam disk 10 in the axial direction is the maximum of the movable cam disk 10 moved by the torque cam 14.
  • a radial bearing 49 is incorporated between the outer diameter surface of the fixed cam disk 9 and the movable cam disk 10 and the inner diameter surface of the pulley 1 so that the fixed cam disk 9 and the movable cam disk 10 are rotated. It differs from the pulley unit shown in FIG. 1 in that it is supported freely.
  • FIG. 9 shows the moving state of the movable cam disk 10, and the elastic member 43 is elastically deformed by the movement of the movable cam disk 10, and the mutual contact pressure and the movement of the plurality of friction plates 21 and 22 of the multi-plate friction clutch 20 are shown.
  • the contact pressure between the cam disk 10 and the outer side friction plate 22 opposed to the cam disk 10 is increased, and the multi-plate friction clutch 20 is engaged.
  • the rotation of the pulley 1 is transmitted from the multi-plate friction clutch 20 to the movable cam disk 10 and from the movable cam disk 10 to the fixed cam disk 9 via the balls 17 of the torque cam 14. Further, the rotation of the fixed cam disk 9 is transmitted to the pulley hub 3, and the pulley hub 3 rotates in the same direction as the pulley 1.
  • the elastic member 43 elastically deforms and absorbs the rotation variation of the pulley 1, and when the pulley 1 decelerates suddenly or stops, the multi-plate friction clutch 20 Since the pulley hub 3 continues to rotate due to the inertial force due to slippage at the contact portions of the friction plates 21 and 22, the belt tension does not increase suddenly, and between the pulley 1 and the belt. There is no inconvenience of slipping.
  • the axial force generated by the pressing force of the elastic member 43 and the operation of the torque cam 14 is received by the flange 7 and the retaining ring 8 and is not loaded on the bearing 4, and the axial direction by the operation of the torque cam 14. Since the movable cam disk 10 that moves to slides on the radial bearing 49, a large axial force is not applied to the radial bearing 49 either. For this reason, the bearing 4 and the radial bearing 49 are hardly damaged, and a pulley unit having excellent durability can be obtained.
  • a ring-shaped stopper 48 is provided on the inner diameter surface of the pulley 1 and the amount of movement of the movable cam disk 10 in the axial direction is limited by the stopper 48, the ball 17 can be prevented from climbing, and the pulley 1 rotation can be reliably transmitted to the pulley hub 3.
  • a multi-plate friction clutch 20 as a multi-plate friction clutch for connecting and releasing the pulley 1 and the pulley hub 3, the same as the pulley unit shown in the first embodiment.
  • the rotation of the pulley 1 can be transmitted to the pulley hub 3 from the contact portions of the plurality of friction plates 21 and 22.
  • the pressing force applied from the elastic member 30 to the multi-plate friction clutch 20 can be reduced, and the surface pressure at the torque cam 14 portion is reduced by the reduction of the pressing force. Therefore, the durability of the torque cam 14 can be improved.
  • the friction material 26 shown in FIG. 5 may be provided on at least one of the contact surfaces of the plurality of friction plates 21 and 22 forming the multi-plate friction clutch 20.
  • a plurality of lubricant discharge grooves 27 as shown in FIGS. 6A to 6D may be provided on the friction surfaces of the inner friction plate 21 and the outer friction plate 22.
  • a protrusion 50 is provided on the flange 40, and the protrusion 50 is inserted into a notch 51 formed on the outer diameter portion of the elastic member 43 to prevent the pulley 1 from rotating. Also good.
  • torque cam 14 shown in FIGS. 7A and 7B may be adopted as the torque cam 14.

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

Abstract

Disclosed is a pulley unit constituted to control decreased durability in bearings that rotatably and relatively support a pulley and pulley hub. A pulley hub (3) is rotatably supported by a bearing (4), which is assembled on the inside of a pulley (1), a flange (7) and stop ring (8) are disposed on the outer circumferential surface of this pulley hub (3), and a stationary cam disc (9), which is fitted around the pulley hub (3) between the flange (7) and stop ring (8), and a moving cam disc (10) are assembled. A torque cam (14) is disposed between the facing surfaces of the stationary cam disc (9) and moving cam disc (10). A multiple disc friction clutch (20), which bonds the moving cam disc (10) and pulley hub (3) together, and an elastic member (30), which forces that multiple disc friction clutch (20) toward the moving cam disc (10), are assembled between the moving cam disc (10) and flange (7), so that counterforce to the axial force loaded on the moving cam disc (10) by the compression of the elastic member (30) and the action of the torque cam (14) is born by the flange (7) and a washer (11).

Description

プーリユニットPulley unit
　この発明は、主として、エンジンを駆動源とするオルタネータ等のエンジン補機の回転軸上に取付けて使用するプーリユニットに関する。 The present invention mainly relates to a pulley unit that is used by being mounted on a rotating shaft of an engine auxiliary machine such as an alternator using an engine as a drive source.
　一般に、エンジンのクランクシャフトの回転をベルト伝動装置によってエンジン補機の回転軸に伝えるようにした補機駆動装置においては、エンジンを急減速した場合、エンジン補機の回転軸に取付けられたプーリも急減速しようとする。 In general, in an accessory drive device that transmits the rotation of the crankshaft of the engine to the rotation shaft of the engine accessory by a belt transmission device, when the engine is suddenly decelerated, a pulley attached to the rotation shaft of the engine accessory is also included. Try to decelerate suddenly.
　このとき、エンジン補機がオルタネータの場合、そのオルタネータの回転軸は慣性力が大きいため、その回転軸に取付けられたプーリは一定の速度で回り続けようとする。その結果、クランクシャフト上のプーリとオルタネータの回転軸上のプーリとの間で大きな回転速度差が生じ、ベルトの張力が増大して破損し易くなる。 At this time, if the engine accessory is an alternator, the rotating shaft of the alternator has a large inertial force, so the pulley attached to the rotating shaft keeps rotating at a constant speed. As a result, a large rotational speed difference is generated between the pulley on the crankshaft and the pulley on the rotating shaft of the alternator, and the belt tension increases and is easily damaged.
　また、クランクシャフトは、エンジンの間歇的な気筒内燃焼や往復動するピストンの慣性力の影響を受けて１回転中に角速度が変動しており、その角速度の変動に起因してクランクシャフト上のプーリとベルトとの間で滑りが生じ、その滑りによってベルトが摩耗し、耐久性が低下することになる。 In addition, the crankshaft fluctuates in angular speed during one rotation due to intermittent in-cylinder combustion in the engine and the inertial force of a reciprocating piston. Slip occurs between the pulley and the belt, and the slip causes wear of the belt, resulting in a decrease in durability.
　そのような不都合を解消するため、特許文献１に記載された動力伝達装置においては、プーリとロータ軸の対向面間にプーリに対して回り止めされ、軸方向に移動可能な第１環状レースと、ロータ軸に対して回転自在に支持された第２環状レースとを組込み、その第１環状レースをコイルばねの押圧により第２環状レースに向けて付勢し、第２環状レースの背面側に上記コイルばねの押圧により第２環状レースとロータ軸とをクラッチ接続する摩擦クラッチを設け、上記プーリに回転速度変動が生じた際に、第１環状レースと第２環状レースの対向面に形成した円弧状斜面のカム作用により第１環状レースを第２環状レースから離反する方向に移動させ、その第１環状レースの軸方向への移動とコイルばねの圧縮とによって上記回転速度変動を吸収するようにしている。 In order to eliminate such inconvenience, in the power transmission device described in Patent Document 1, a first annular race that is prevented from rotating with respect to the pulley between the opposed surfaces of the pulley and the rotor shaft and is movable in the axial direction is provided. And a second annular race supported rotatably with respect to the rotor shaft, and the first annular race is urged toward the second annular race by pressing the coil spring, and is placed on the back side of the second annular race. A friction clutch is provided for clutch-connecting the second annular race and the rotor shaft by pressing the coil spring, and is formed on the opposing surfaces of the first annular race and the second annular race when the rotational speed fluctuation occurs in the pulley. The first annular race is moved away from the second annular race by the cam action of the arcuate slope, and the rotational speed is changed by the axial movement of the first annular race and the compression of the coil spring. So as to absorb the.
特開２００６－３８１８３号公報JP 2006-38183 A
　ところで、特許文献１に記載された動力伝達装置においては、プーリとロータ軸とを相対的に回転自在に支持する転がり軸受により第２環状レースと摩擦クラッチとを軸方向に位置決めする構成であり、その転がり軸受によってコイルばねの押圧力を受けると共に、円弧状斜面のカム作用によって第１環状レースに負荷される軸方向力の反力を受けるようにしているため、転がり軸受の耐久性を低下させるという不都合がある。 By the way, in the power transmission device described in Patent Document 1, the second annular race and the friction clutch are positioned in the axial direction by a rolling bearing that relatively rotatably supports the pulley and the rotor shaft. Since the rolling bearing receives the pressing force of the coil spring and receives the reaction force of the axial force applied to the first annular race by the cam action of the arcuate slope, the durability of the rolling bearing is reduced. There is an inconvenience.
　この発明の課題は、プーリとプーリハブを相対的に回転自在に支持する軸受の耐久性の低下を抑制することである。 An object of the present invention is to suppress a decrease in durability of a bearing that rotatably supports a pulley and a pulley hub.
　上記の課題を解決するために、第１の発明においては、プーリとその内側に組込まれたプーリハブを、その両部材の一方の端部間に組込まれた軸受によって相対的に回転自在に支持し、前記プーリハブの外径面に２つの突出部を軸方向に間隔をおいて設け、その２つの突出部間に、前記プーリに回り止めされ、一方の突出部によって軸方向外方への移動が阻止される固定カムディスクと、プーリハブに対して回転可能に、かつ、軸方向に移動可能に支持された可動カムディスクとを組込み、その固定カムディスクと可動カムディスクの対向面間に、両カムディスクの一方向への相対回転により可動カムディスクを固定カムディスクから離反する方向に移動させ、他方向への相対回転時に前記両カムディスクを回転方向に係合させるトルクカムを設け、前記可動カムディスクと他方の突出部間に、前記可動カムディスクとプーリハブとを結合する多板摩擦クラッチと、前記可動カムディスクが固定カムディスクから離反する移動時にその多板摩擦クラッチからの押圧により弾性変形し、その復元弾性により多板摩擦クラッチを結合状態とする弾性部材を組込んだ構成を採用したのである。 In order to solve the above-described problems, in the first invention, the pulley and the pulley hub incorporated inside the pulley are relatively rotatably supported by a bearing incorporated between one end portions of both members. Two protrusions are provided on the outer diameter surface of the pulley hub at an interval in the axial direction, and the pulley is prevented from rotating between the two protrusions. A fixed cam disk to be blocked and a movable cam disk supported so as to be rotatable with respect to the pulley hub and movable in the axial direction are incorporated, and both cams are disposed between the opposed surfaces of the fixed cam disk and the movable cam disk. A torque cam that moves the movable cam disk in a direction away from the fixed cam disk by relative rotation in one direction of the disk and engages both cam disks in the rotation direction at the time of relative rotation in the other direction. A multi-plate friction clutch that couples the movable cam disc and a pulley hub between the movable cam disc and the other protrusion, and the multi-plate friction clutch when the movable cam disc moves away from the fixed cam disc. This is a structure that incorporates an elastic member that is elastically deformed by the pressing and that restores the multi-plate friction clutch.
　上記の構成からなるプーリユニットにおいて、プーリの回転停止状態では、多板摩擦クラッチは滑りが生じる結合解除状態にある。 In the pulley unit configured as described above, the multi-plate friction clutch is in a disengaged state where slipping occurs when the pulley is stopped.
　上記の状態からプーリに正回転方向の回転トルクが入力されると、固定カムディスクと可動カムディスクが一方向に相対回転する。その相対回転によりトルクカムが作用し、可動カムディスクが固定カムディスクから離反する方向に移動する。また、多板摩擦クラッチも可動カムディスクと共に移動して弾性部材を弾性変形させる。その弾性部材の弾性変形によって多板摩擦クラッチは可動カムディスクとプーリハブを結合する結合状態となる。 When the rotational torque in the forward rotation direction is input to the pulley from the above state, the fixed cam disk and the movable cam disk rotate relative to each other in one direction. The torque cam acts by the relative rotation, and the movable cam disk moves away from the fixed cam disk. The multi-plate friction clutch also moves together with the movable cam disk to elastically deform the elastic member. Due to the elastic deformation of the elastic member, the multi-plate friction clutch enters a coupled state in which the movable cam disk and the pulley hub are coupled.
　このため、プーリの回転は、固定カムディスクからトルクカムを介して可動カムディスクに伝達されると共に、その可動カムディスクから摩擦プレートを介してプーリハブに伝達されて、プーリハブがプーリと同方向に回転する。 Therefore, the rotation of the pulley is transmitted from the fixed cam disk to the movable cam disk via the torque cam, and from the movable cam disk to the pulley hub via the friction plate, and the pulley hub rotates in the same direction as the pulley. .
　プーリからプーリハブへの回転伝達状態において、プーリに回転変動が生じると、固定カムディスクと可動カムディスクが相対回転し、トルクカムが作用して可動カムディスクが軸方向に移動し、多板摩擦クラッチからの押圧により弾性部材が弾性変形する。その弾性部材の弾性変形によってプーリの回転変動が吸収され、プーリハブにその回転変動が伝達されるのが防止されると共に、多板摩擦クラッチは結合状態に維持される。 In the state of transmission of rotation from the pulley to the pulley hub, if rotation fluctuation occurs in the pulley, the fixed cam disk and the movable cam disk rotate relative to each other, the torque cam acts and the movable cam disk moves in the axial direction, and the multi-plate friction clutch The elastic member is elastically deformed by the pressing. The elastic deformation of the elastic member absorbs the rotational fluctuation of the pulley and prevents the rotational fluctuation from being transmitted to the pulley hub, and the multi-plate friction clutch is maintained in the coupled state.
　また、プーリが停止すると、慣性力によるプーリハブの回転によりトルクカムは可動カムディスクの押圧を解除する状態に戻り、弾性部材は伸張して押圧力が弱くなり、多板摩擦クラッチは結合解除状態となって、多板摩擦クラッチに滑りが生じ、プーリハブは慣性力によって回転を継続する。 When the pulley stops, the torque cam returns to the state where the movable cam disk is released due to the rotation of the pulley hub due to the inertial force, the elastic member expands and the pressing force becomes weaker, and the multi-plate friction clutch enters the disengaged state. Thus, slip occurs in the multi-plate friction clutch, and the pulley hub continues to rotate due to the inertial force.
　このように、プーリに回転変動が生じると、弾性部材が弾性変形してプーリの回転変動を吸収し、また、プーリが停止すると、多板摩擦クラッチに滑りが生じてプーリハブは慣性力によって回転を継続するため、ベルトの張力が急激に増大するというようなことはなく、また、プーリとベルトの相互間でスリップが生じるという不都合の発生はない。 As described above, when the rotation fluctuation occurs in the pulley, the elastic member elastically deforms to absorb the rotation fluctuation of the pulley, and when the pulley stops, the multi-plate friction clutch slips and the pulley hub rotates due to inertial force. Since the belt tension continues, the belt tension does not increase rapidly, and there is no inconvenience that slip occurs between the pulley and the belt.
　第１の発明に係るプーリユニットにおいて、プーリハブの外径面に可動カムディスクの軸方向の移動量をトルクカムによって移動される可動カムディスクの最大移動量の範囲内に規制するストッパを設けると、トルクカムの乗り上げを防止し、弾性部材の過大な撓みによる耐久性の低下を抑制することができる。 In the pulley unit according to the first aspect of the present invention, if a stopper is provided on the outer diameter surface of the pulley hub to limit the amount of movement of the movable cam disk in the axial direction within the range of the maximum movement amount of the movable cam disk moved by the torque cam. Can be prevented, and deterioration of durability due to excessive bending of the elastic member can be suppressed.
　また、多板摩擦クラッチを形成する複数の摩擦プレートのうち、弾性部材と当接する軸方向一端の摩擦プレートと前記弾性部材とをプーリハブに回り止めすると、軸方向一端の摩擦プレートと前記弾性部材とが相対回転するのを防止することができるため、上記弾性部材の接触摩耗を抑制することができる。このため、弾性部材の荷重特性が変化するという不都合の発生はなく、多板摩擦クラッチの滑りを防止することができる。 Further, among the plurality of friction plates forming the multi-plate friction clutch, when the friction plate at one end in the axial direction contacting the elastic member and the elastic member are prevented from rotating on the pulley hub, the friction plate at one end in the axial direction and the elastic member Can be prevented from rotating relative to each other, so that contact wear of the elastic member can be suppressed. For this reason, there is no inconvenience that the load characteristic of the elastic member changes, and the slip of the multi-plate friction clutch can be prevented.
　上記の課題を解決するために、第２の発明においては、プーリとその内側に組込まれたプーリハブを、その両部材の一方の端部間に組込まれた軸受によって相対的に回転自在に支持し、前記プーリの内径面に２つの突出部を軸方向に間隔をおいて設け、その２つの突出部間に、前記プーリハブに回り止めされ、一方の突出部によって軸方向外方への移動が阻止される固定カムディスクと、プーリに対して回転可能に、かつ、軸方向に移動可能に支持された可動カムディスクとを組込み、その固定カムディスクと可動カムディスクの対向面間に、両カムディスクの一方向への相対回転により可動カムディスクを固定カムディスクから離反する方向に移動させ、他方向への相対回転時に前記両カムディスクを回転方向に係合させるトルクカムを設け、前記可動カムディスクと他方の突出部間に、前記可動カムディスクとプーリハブとを結合する多板摩擦クラッチと、前記可動カムディスクが固定カムディスクから離反する移動時にその多板摩擦クラッチからの押圧により弾性変形し、その復元弾性により多板摩擦クラッチを結合状態とする弾性部材を組込んだ構成を採用したのである。 In order to solve the above-described problems, in the second invention, the pulley and the pulley hub incorporated inside the pulley are relatively rotatably supported by a bearing incorporated between one end portions of both members. Two protrusions are provided on the inner diameter surface of the pulley at an interval in the axial direction, and the pulley hub is prevented from rotating between the two protrusions, and one protrusion prevents movement outward in the axial direction. The fixed cam disk and a movable cam disk supported so as to be rotatable with respect to the pulley and movable in the axial direction are incorporated, and both cam disks are disposed between the opposed surfaces of the fixed cam disk and the movable cam disk. A torque cam that moves the movable cam disc in a direction away from the fixed cam disc by relative rotation in one direction and engages both cam discs in the rotation direction at the time of relative rotation in the other direction. And a multi-plate friction clutch that couples the movable cam disk and a pulley hub between the movable cam disk and the other protrusion, and the multi-plate friction clutch when the movable cam disk moves away from the fixed cam disk. A configuration incorporating an elastic member that is elastically deformed by pressing and that brings the multi-plate friction clutch into a coupled state by its restoring elasticity is adopted.
　上記の構成からなるプーリユニットにおいて、プーリの回転停止状態では、多板摩擦クラッチは滑りが生じる結合解除状態にある。 In the pulley unit configured as described above, the multi-plate friction clutch is in a disengaged state where slipping occurs when the pulley is stopped.
　上記の状態からプーリに正回転方向の回転トルクが入力されると、固定カムディスクと可動カムディスクが一方向に相対回転する。その相対回転によりトルクカムが作用し、可動カムディスクが固定カムディスクから離反する方向に移動する。また、多板摩擦クラッチも可動カムディスクと共に移動して弾性部材を弾性変形させる。その弾性部材の弾性変形によって多板摩擦クラッチは可動カムディスクとプーリハブを結合する結合状態となる。 When the rotational torque in the forward rotation direction is input to the pulley from the above state, the fixed cam disk and the movable cam disk rotate relative to each other in one direction. The torque cam acts by the relative rotation, and the movable cam disk moves away from the fixed cam disk. The multi-plate friction clutch also moves together with the movable cam disk to elastically deform the elastic member. Due to the elastic deformation of the elastic member, the multi-plate friction clutch enters a coupled state in which the movable cam disk and the pulley hub are coupled.
　このため、プーリの回転は、多板摩擦クラッチから可動カムディスクに伝達されると共に、トルクカムおよび固定カムディスクを介してプーリハブに伝達されて、プーリハブがプーリと同方向に回転する。 Therefore, the rotation of the pulley is transmitted from the multi-plate friction clutch to the movable cam disk, and is also transmitted to the pulley hub via the torque cam and the fixed cam disk, so that the pulley hub rotates in the same direction as the pulley.
　プーリからプーリハブへの回転伝達状態において、プーリに回転変動が生じると、固定カムディスクと可動カムディスクが相対回転し、トルクカムが作用して可動カムディスクが軸方向に移動し、多板摩擦クラッチからの押圧により弾性部材が弾性変形する。その弾性部材の弾性変形によってプーリの回転変動が吸収され、プーリハブにその回転変動が伝達されるのが防止されると共に、多板摩擦クラッチは結合状態に維持される。 In the state of transmission of rotation from the pulley to the pulley hub, if rotation fluctuation occurs in the pulley, the fixed cam disk and the movable cam disk rotate relative to each other, the torque cam acts and the movable cam disk moves in the axial direction, and the multi-plate friction clutch The elastic member is elastically deformed by the pressing. The elastic deformation of the elastic member absorbs the rotational fluctuation of the pulley and prevents the rotational fluctuation from being transmitted to the pulley hub, and the multi-plate friction clutch is maintained in the coupled state.
　また、プーリが停止すると、慣性力によるプーリハブの回転によりトルクカムは可動カムディスクの押圧を解除する状態に戻り、弾性部材は伸張して押圧力が弱くなり、多板摩擦クラッチは結合解除状態となって、多板摩擦クラッチに滑りが生じ、プーリハブは慣性力によって回転を継続する。 When the pulley stops, the torque cam returns to the state where the movable cam disk is released due to the rotation of the pulley hub due to the inertial force, the elastic member expands and the pressing force becomes weaker, and the multi-plate friction clutch enters the disengaged state. Thus, slip occurs in the multi-plate friction clutch, and the pulley hub continues to rotate due to the inertial force.
　このように、プーリに回転変動が生じると、弾性部材が弾性変形してプーリの回転変動を吸収し、また、プーリが停止すると、多板摩擦クラッチに滑りが生じてプーリハブは慣性力によって回転を継続するため、ベルトの張力が急激に増大するというようなことはなく、また、プーリとベルトの相互間でスリップが生じるという不都合の発生はない。 As described above, when the rotation fluctuation occurs in the pulley, the elastic member elastically deforms to absorb the rotation fluctuation of the pulley, and when the pulley stops, the multi-plate friction clutch slips and the pulley hub rotates due to inertial force. Since the belt tension continues, the belt tension does not increase rapidly, and there is no inconvenience that slip occurs between the pulley and the belt.
　第１の発明および第２の発明に係るプーリユニットにおいて、トルクカムは、周方向に下り勾配を持って傾斜する傾斜カム面およびその傾斜カム面の低所端に連続して形成された係合面を溝底に有し、前記傾斜カム面の勾配が逆向きとなるよう固定カムディスクと可動カムディスクの対向面それぞれに形成された対向一対のカム溝と、その対向一対のカム溝間に組込まれた転動体とからなるものであってもよく、あるいは、周方向に下り勾配をもって傾斜する傾斜カム面およびその傾斜カム面の低所端に連続して形成された係合面を溝底に有するカム溝と、そのカム溝に適合するカム突起とからなるものであってもよい。 In the pulley unit according to the first and second inventions, the torque cam includes an inclined cam surface that is inclined with a downward gradient in the circumferential direction, and an engagement surface that is formed continuously at a lower end of the inclined cam surface. And a pair of opposed cam grooves formed on the opposed surfaces of the fixed cam disk and the movable cam disk so that the gradient of the inclined cam surface is reversed, and is incorporated between the opposed pair of cam grooves. Or an inclined cam surface inclined with a downward slope in the circumferential direction and an engaging surface formed continuously at the lower end of the inclined cam surface at the groove bottom. It may be composed of a cam groove having a cam projection and a cam projection adapted to the cam groove.
　また、多板摩擦クラッチを形成する複数の摩擦プレートのそれぞれの接触面における少なくとも一方に摩擦材を設けると、各接触部での摩擦係数を高めることができるため、伝達トルクの容量を高めることができる。逆に、摩擦プレートに負荷する押圧力の低減を図り、摩擦プレートの耐久性の低下を抑制することができる。 In addition, if a friction material is provided on at least one of the contact surfaces of each of the plurality of friction plates forming the multi-plate friction clutch, the friction coefficient at each contact portion can be increased, so that the capacity of the transmission torque can be increased. it can. On the contrary, it is possible to reduce the pressing force applied to the friction plate and suppress the decrease in the durability of the friction plate.
　さらに、多板摩擦クラッチを形成する複数の摩擦プレートのそれぞれの接触面に、窒化処理、浸炭処理、高周波熱処理の一種からなる硬化処理を施し、あるいは，窒化チタン（ＴｉＮ）、窒化クロム（ＣｒＮ）、窒化チタンアルミ（ＴｉＡｌＮ）、炭窒化チタン（ＴｉＣＮ）等の窒化物被膜や炭化チタン（ＴｉＣ）等の炭化物被膜からなる硬質被膜を設けると、摩擦プレートの耐摩耗性と耐久性の向上を図ることができる。 Further, the contact surface of each of the plurality of friction plates forming the multi-plate friction clutch is subjected to a hardening treatment consisting of one of nitriding treatment, carburizing treatment, and high-frequency heat treatment, or titanium nitride (TiN), chromium nitride (CrN). When a hard coating made of a nitride coating such as titanium aluminum nitride (TiAlN) or titanium carbonitride (TiCN) or a carbide coating such as titanium carbide (TiC) is provided, the wear resistance and durability of the friction plate are improved. be able to.
　第１の発明および第２の発明に係るプーリユニットにおいて、多板摩擦クラッチを形成する複数の摩擦プレートのそれぞれの接触面における少なくとも一方に半径方向に延びる潤滑剤排出溝を形成すると、複数の摩擦プレートが弾性部材の押圧により互いに押し付けられる押圧時に、摩擦プレート間に介在する潤滑剤は潤滑剤排出溝に押し出されるため、摩擦面に潤滑剤が過剰に付着するのを防止することができ、摩擦クラッチの滑りを防止することができる。 In the pulley unit according to the first invention and the second invention, when a lubricant discharge groove extending in the radial direction is formed on at least one of the contact surfaces of the plurality of friction plates forming the multi-plate friction clutch, the plurality of friction When the plates are pressed against each other by the pressing of the elastic member, the lubricant intervening between the friction plates is pushed out to the lubricant discharge groove, so that it is possible to prevent excessive adhesion of the lubricant to the friction surface, and friction The slip of the clutch can be prevented.
　また、多板摩擦クラッチを形成する複数の摩擦プレートのそれぞれを、アルミニウム合金またはマグネシウム合金製とすると、慣性モーメントを低減し、プーリユニットの軽量化を図ることができる。 Also, if each of the plurality of friction plates forming the multi-plate friction clutch is made of an aluminum alloy or a magnesium alloy, the moment of inertia can be reduced and the pulley unit can be reduced in weight.
　第１の発明においては、プーリハブの外径面に形成された２つの突出部によって可動カムディスクに摩擦クラッチを押し付ける弾性部材の押圧力やトルクカムの作用によって可動カムディスクに負荷される軸方向力を受けるようにしたので、プーリとプーリハブとを相対的に回転自在に支持する軸受に上記押圧力や軸方向力が負荷されるようなことがなく、軸受の耐久性の低下を抑制することができる。 In the first invention, the axial force applied to the movable cam disk by the pressing force of the elastic member that presses the friction clutch against the movable cam disk by the two protrusions formed on the outer diameter surface of the pulley hub and the action of the torque cam. As a result, the bearing that supports the pulley and the pulley hub so as to be relatively rotatable is not subjected to the pressing force or the axial force, and a decrease in the durability of the bearing can be suppressed. .
　第２の発明においては、プーリの内径面に形成された２つの突出部によって可動カムディスクに多板摩擦クラッチを押し付ける弾性部材の押圧力やトルクカムの作用によって可動カムディスクに負荷される軸方向力を受けるようにしたので、上記代の発明と同様に、プーリとプーリハブとを相対的に回転自在に支持する軸受に上記押圧力や軸方向力が負荷されるようなことがなく、軸受の耐久性の低下を抑制することができる。 In the second invention, the axial force applied to the movable cam disk by the pressing force of the elastic member pressing the multi-plate friction clutch against the movable cam disk or the action of the torque cam by the two protrusions formed on the inner diameter surface of the pulley. As in the above-described invention, the bearing that supports the pulley and the pulley hub so as to be relatively rotatable is not subjected to the pressing force or the axial force, and the durability of the bearing is reduced. Deterioration can be suppressed.
　また、第１の発明および第２の発明のいずれの発明も、摩擦クラッチとして多板摩擦クラッチを採用したことにより、複数の摩擦プレートのそれぞれの接触部からプーリの回転をプーリハブに伝達することができるため、摩擦クラッチに必要とされる押圧力を低くすることができる。このため、トルクカム部における面圧を低下させることができ、上記トルクカム部の耐久性の向上を図ることができる。 Also, in both the first and second inventions, by adopting a multi-plate friction clutch as the friction clutch, the rotation of the pulley can be transmitted to the pulley hub from each contact portion of the plurality of friction plates. Therefore, the pressing force required for the friction clutch can be reduced. For this reason, the surface pressure in the torque cam portion can be reduced, and the durability of the torque cam portion can be improved.
この発明に係るプーリユニットの第１の実施の形態を示す縦断正面図Longitudinal front view showing a first embodiment of a pulley unit according to the present invention 図１のII－II線に沿った断面図Sectional view along the line II-II in FIG. （ａ）は、図１に示すトルクカムの断面図、（ｂ）は、トルクカムの作動状態を示す断面図(A) is sectional drawing of the torque cam shown in FIG. 1, (b) is sectional drawing which shows the operating state of a torque cam. 図１に示すトルクカムの作動状態を示す断面図Sectional drawing which shows the operating state of the torque cam shown in FIG. 摩擦クラッチの他の例を示す断面図Sectional view showing another example of a friction clutch （ａ），（ｂ），（ｃ），（ｄ）は、摩擦クラッチの摩擦プレートの他の例を示す正面図(A), (b), (c), (d) is a front view showing another example of the friction plate of the friction clutch. （ａ）は、トルクカムの他の例を示す断面図、（ｂ）は、作動状態を示す断面図(A) is sectional drawing which shows the other example of a torque cam, (b) is sectional drawing which shows an operation state. この発明に係るプーリユニットの第２の実施の形態を示す縦断正面図A longitudinal front view showing a second embodiment of a pulley unit according to the present invention 図８のトルクカム部を拡大して示す断面図Sectional drawing which expands and shows the torque cam part of FIG.
　以下、この発明の実施の形態を図面に基いて説明する。図１は、この発明に係るプーリユニットの第１の実施の形態を示す。図示のように、プーリ１は複列のＶ溝２を外周面に有し、その内側にはプーリハブ３が組込まれている。プーリ１とプーリハブ３は、その対向する一端部間に組込まれた片シール付きの軸受４によって相対的に回転自在に支持されている。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows a first embodiment of a pulley unit according to the present invention. As shown in the figure, the pulley 1 has double rows of V-grooves 2 on its outer peripheral surface, and a pulley hub 3 is incorporated inside the pulley 1. The pulley 1 and the pulley hub 3 are relatively rotatably supported by a bearing 4 with a single seal that is incorporated between opposite ends thereof.
　プーリ１の他端部内周にはシール部材５の外周部が圧入され、そのシール部材５の内周部に形成されたリップ６がプーリハブ３の他端部外周に弾性接触し、そのシール部材５によってプーリ１の他端部開口が閉塞され、内部に異物が侵入するのが防止されている。 The outer periphery of the seal member 5 is press-fitted into the inner periphery of the other end of the pulley 1, and the lip 6 formed on the inner periphery of the seal member 5 is in elastic contact with the outer periphery of the other end of the pulley hub 3. As a result, the opening of the other end of the pulley 1 is closed, and foreign matter is prevented from entering the inside.
　プーリハブ３の外径面の一端部には軸受４を軸方向に位置決めする突出部としてのフランジ７が設けられている。また、プーリハブ３の他端部外周には突出部としての止め輪８が取り付けられている。 A flange 7 as a protruding portion for positioning the bearing 4 in the axial direction is provided at one end portion of the outer diameter surface of the pulley hub 3. A retaining ring 8 as a protruding portion is attached to the outer periphery of the other end of the pulley hub 3.
　フランジ７と止め輪８間には、固定カムディスク９と可動カムディスク１０が組込まれ、その固定カムディスク９と止め輪８間にワッシャ１１が組込まれている。 A fixed cam disk 9 and a movable cam disk 10 are assembled between the flange 7 and the retaining ring 8, and a washer 11 is assembled between the fixed cam disk 9 and the retaining ring 8.
　固定カムディスク９は、スプライン１２の嵌合によってプーリ１に回り止めされて、そのプーリ１と一体に回転するようになっている。固定カムディスク９および可動カムディスク１０とプーリハブ３の嵌合面間には針状ころ軸受からなるラジアル軸受１３が組込まれ、そのラジアル軸受１３は、前記軸受４とでプーリ１に負荷されるラジアル荷重を支持するようになっている。 The fixed cam disk 9 is prevented from rotating around the pulley 1 by the fitting of the spline 12, and rotates together with the pulley 1. A radial bearing 13 composed of a needle roller bearing is incorporated between the fixed cam disk 9 and the movable cam disk 10 and the pulley hub 3 and the radial bearing 13 is loaded on the pulley 1 with the bearing 4. It is designed to support the load.
　可動カムディスク１０は、上記ラジアル軸受１３によって回転自在に、かつ、軸方向に移動自在に支持され、その可動カムディスク１０と固定カムディスク９の対向面間にトルクカム１４が設けられている。 The movable cam disk 10 is supported by the radial bearing 13 so as to be rotatable and movable in the axial direction, and a torque cam 14 is provided between the opposed surfaces of the movable cam disk 10 and the fixed cam disk 9.
　図２および図３に示すように、トルクカム１４は、固定カムディスク９と可動カムディスク１０の対向面それぞれに形成された対向一対のカム溝１５、１６と、そのカム溝１５、１６間に組込まれた転動体としてのボール１７とからなる。 As shown in FIGS. 2 and 3, the torque cam 14 is assembled between a pair of opposed cam grooves 15 and 16 formed on the opposed surfaces of the fixed cam disk 9 and the movable cam disk 10, and the cam grooves 15 and 16, respectively. And a ball 17 as a rolling element.
　対向一対のカム溝１５，１６は、周方向に下り勾配をもって傾斜する傾斜カム面１５ａ、１６ａと、その傾斜カム面１５ａ、１６ａの低所端に連続する円弧状の係合面１５ｂ、１６ｂを溝底に有し、上記傾斜カム面１５ａ、１６ａの勾配が逆向きとなるようにして固定カムディスク９と可動カムディスク１０の対向面それぞれに形成されている。 The pair of opposed cam grooves 15 and 16 include inclined cam surfaces 15a and 16a that are inclined with a downward gradient in the circumferential direction, and arcuate engagement surfaces 15b and 16b that are continuous to the lower ends of the inclined cam surfaces 15a and 16a. The inclined cam surfaces 15a and 16a are formed on the opposing surfaces of the fixed cam disk 9 and the movable cam disk 10 so that the slopes of the inclined cam surfaces 15a and 16a are opposite to each other.
　トルクカム１４は、固定カムディスク９と可動カムディスク１０の一方向への相対回転時に、傾斜カム面１５ａ、１６ａに沿ってのボール１７の転がり移動により可動カムディスク１０を固定カムディスク９から離反する方向に移動させるようになっている。また、固定カムディスク９と可動カムディスク１０の他方向への相対回転時に、ボール１７を係合面１５ｂ、１６ｂに係合させて、固定カムディスク９と可動カムディスク１０を回転方向に係合させるようになっている。 The torque cam 14 separates the movable cam disk 10 from the fixed cam disk 9 by the rolling movement of the ball 17 along the inclined cam surfaces 15 a and 16 a during relative rotation of the fixed cam disk 9 and the movable cam disk 10 in one direction. It is designed to move in the direction. Further, during relative rotation of the fixed cam disk 9 and the movable cam disk 10 in the other direction, the ball 17 is engaged with the engagement surfaces 15b and 16b, and the fixed cam disk 9 and the movable cam disk 10 are engaged in the rotation direction. It is supposed to let you.
　図１に示すように、可動カムディスク１０とフランジ７間には、多板摩擦クラッチ２０と、その多板摩擦クラッチ２０を可動カムディスク１０に向けて付勢する弾性部材３０が組込まれている。 As shown in FIG. 1, a multi-plate friction clutch 20 and an elastic member 30 that biases the multi-plate friction clutch 20 toward the movable cam disk 10 are incorporated between the movable cam disk 10 and the flange 7. .
　多板摩擦クラッチ２０は、複数の摩擦プレートを有している。ここでは、２枚のインナ側摩擦プレート２１と、１枚のアウタ側摩擦プレート２２が示されているが、摩擦プレートの数はこれに限定されるものではない。 The multi-plate friction clutch 20 has a plurality of friction plates. Here, two inner friction plates 21 and one outer friction plate 22 are shown, but the number of friction plates is not limited to this.
　インナ側摩擦プレート２１とアウタ側摩擦プレート２２は可動カムディスク１０の片面外周部に形成された円筒部２３内において軸方向に交互に並ぶ配置とされ、上記インナ側摩擦プレート２１はスプライン２４を介してプーリハブ３に回り止めされ、プーリハブ３と一体に回転するようになっている。 The inner side friction plate 21 and the outer side friction plate 22 are arranged alternately in the axial direction in a cylindrical portion 23 formed on the outer peripheral portion of one side of the movable cam disk 10, and the inner side friction plate 21 is interposed via a spline 24. The pulley hub 3 is prevented from rotating, and rotates together with the pulley hub 3.
　一方、アウタ側摩擦プレート２２は上記円筒部２３にスプライン２５を介して回り止めされ、可動カムディスク１０と一体に回転するようになっている。 On the other hand, the outer friction plate 22 is prevented from rotating by the cylindrical portion 23 via a spline 25 and rotates integrally with the movable cam disk 10.
　弾性部材３０は、皿ばねからなる。この弾性部材３０は、可動カムディスク１０が固定カムディスク９から離反する軸方向への移動時に多板摩擦クラッチ２０により押圧されて弾性変形し、その弾性変形により多板摩擦クラッチ２０の摩擦プレート２１、２２が可動カムディスク１０に押し付けられ、多板摩擦クラッチ２０が結合状態に切り換えられる。 The elastic member 30 is made of a disc spring. The elastic member 30 is elastically deformed by being pressed by the multi-plate friction clutch 20 when the movable cam disk 10 moves in the axial direction away from the fixed cam disk 9, and the elastic plate 30 of the multi-plate friction clutch 20 is elastically deformed. , 22 are pressed against the movable cam disk 10, and the multi-plate friction clutch 20 is switched to the coupled state.
　プーリハブ３の外径面には、多板摩擦クラッチ２０とフランジ７間にリング状のストッパ３１が嵌合され、そのストッパ３１によって可動カムディスク１０の軸方向の移動量はトルクカム１４によって移動される可動カムディスク１０の最大移動量の範囲内に規制されるようになっている。 A ring-shaped stopper 31 is fitted between the multi-plate friction clutch 20 and the flange 7 on the outer diameter surface of the pulley hub 3, and the axial movement amount of the movable cam disk 10 is moved by the torque cam 14 by the stopper 31. The movable cam disk 10 is regulated within the range of the maximum movement amount.
　第１の実施の形態で示すプーリユニットは上記の構造からなり、エンジン補機としてのオルタネータの駆動に際しては、そのオルタネータの回転軸にプーリハブ３を嵌合して回り止めし、そのプーリユニットのプーリ１とエンジンのクランクシャフトに取付けられたプーリ間にベルトを掛け渡して、クランクシャフトの回転がプーリ１に伝達されるようにする。 The pulley unit shown in 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 it from rotating, and the pulley of the pulley unit A belt is stretched between 1 and a pulley attached to the crankshaft of the engine so that the rotation of the crankshaft is transmitted to the pulley 1.
　上記のような使用状態において、プーリ１の回転停止状態では、図３（ａ）に示すように、ボール１７はカム溝１５、１６の係合面１５ｂ、１６ｂに係合しており、多板摩擦クラッチ２０は滑りが生じる結合解除状態にある。 In the use state as described above, when the pulley 1 is in the rotation stopped state, the ball 17 is engaged with the engagement surfaces 15b and 16b of the cam grooves 15 and 16 as shown in FIG. The friction clutch 20 is in a disengaged state where slipping occurs.
　上記の状態からプーリ１に正回転方向の回転トルクが入力されると、固定カムディスク９と可動カムディスク１０が、図３（ａ）の矢印で示す方向に相対回転する。その両カムディスク９、１０の一方向への相対回転により、図３（ｂ）に示すように、ボール１７はカム溝１５、１６の傾斜カム面１５ａ、１６ａに沿って転がり移動し、可動カムディスク１０に軸方向の押圧力が負荷されて、可動カムディスク１０が固定カムディスク９から離反する方向に移動する。 When a rotational torque in the forward rotation direction is input to the pulley 1 from the above state, the fixed cam disk 9 and the movable cam disk 10 are relatively rotated in the direction indicated by the arrow in FIG. Due to the relative rotation of the cam disks 9, 10 in one direction, the ball 17 rolls along the inclined cam surfaces 15a, 16a of the cam grooves 15, 16 as shown in FIG. An axial pressing force is applied to the disc 10, and the movable cam disc 10 moves away from the fixed cam disc 9.
　図４は、可動カムディスク１０の移動状態を示し、上記可動カムディスク１０の移動によって弾性部材３０が弾性変形し、多板摩擦クラッチ２０の複数の摩擦プレート２１、２２の相互の接触圧および可動カムディスク１０とこれに対向するインナ側摩擦プレート２１の接触圧が高くなって多板摩擦クラッチ２０が結合状態となる。 FIG. 4 shows the moving state of the movable cam disk 10, and the elastic member 30 is elastically deformed by the movement of the movable cam disk 10, and the contact pressure and the movable pressure of the plurality of friction plates 21 and 22 of the multi-plate friction clutch 20 are movable. The contact pressure between the cam disk 10 and the inner friction plate 21 facing the cam disk 10 is increased, and the multi-plate friction clutch 20 is brought into a coupled state.
　このため、プーリ１の回転は、固定カムディスク９からトルクカム１４を介して可動カムディスク１０に伝達されると共に、その可動カムディスク１０から多板摩擦クラッチ２０を介してプーリハブ３に伝達され、プーリハブ３がプーリ１と同方向に回転する。 For this reason, the rotation of the pulley 1 is transmitted from the fixed cam disk 9 to the movable cam disk 10 via the torque cam 14, and from the movable cam disk 10 to the pulley hub 3 via the multi-plate friction clutch 20, and the pulley hub. 3 rotates in the same direction as the pulley 1.
　プーリハブ３への回転トルクの伝達状態において、クランクシャフトの角速度の変化によりプーリ１に回転変動が生じると、固定カムディスク９と可動カムディスク１０が相対回転する。このとき、クランクシャフトの角速度の変化によるプーリ１の回転変動は比較的小さいため、ボール１７は傾斜カム面１５ａ、１６ａに沿って転がり移動する。その転がり移動によって可動カムディスク１０が軸方向に移動し、その可動カムディスク１０と共に移動する多板摩擦クラッチ２０からの押圧により弾性部材３０が弾性変形する。その弾性部材３０の弾性変形によってプーリの回転変動が吸収され、プーリハブ３にその回転変動が伝達されるのが防止される。また、多板摩擦クラッチ２０は結合状態に維持される。 When the rotational fluctuation occurs in the pulley 1 due to the change in the angular speed of the crankshaft in the state of transmission of the rotational torque to the pulley hub 3, the fixed cam disk 9 and the movable cam disk 10 rotate relative to each other. At this time, since the rotation fluctuation of the pulley 1 due to the change in the angular velocity of the crankshaft is relatively small, the ball 17 rolls along the inclined cam surfaces 15a and 16a. Due to the rolling movement, the movable cam disk 10 moves in the axial direction, and the elastic member 30 is elastically deformed by the pressure from the multi-plate friction clutch 20 that moves together with the movable cam disk 10. Due to the elastic deformation of the elastic member 30, the rotational fluctuation of the pulley is absorbed, and the rotational fluctuation is prevented from being transmitted to the pulley hub 3. Further, the multi-plate friction clutch 20 is maintained in the coupled state.
　エンジンを急減速し、あるいは、停止すると、オルタネータの回転軸は慣性力が大きいため、プーリハブ３は回転を続けようとする。慣性力によるプーリハブ３の回転により、可動カムディスク１０は固定カムディスク９に対して図３（ｂ）の矢印で示す方向に相対回転し、ボール１７は、図３（ａ）に示すように係合面１５ｂ、１６ｂに係合する。また、可動カムディスク１０は固定カムディスク９に向けて移動し、その可動カムディスク１０の移動によって弾性部材３０は伸張して押圧力が弱くなり、多板摩擦クラッチ２０は結合解除状態となって、多板摩擦クラッチ２０の摩擦プレート２１、２２の接触部で滑りが生じ、プーリハブ３は慣性力によって回転を継続する。 When the engine is decelerated suddenly or stopped, the rotating shaft of the alternator has a large inertial force, so the pulley hub 3 tries to continue rotating. Due to the rotation of the pulley hub 3 due to the inertial force, the movable cam disk 10 rotates relative to the fixed cam disk 9 in the direction indicated by the arrow in FIG. 3B, and the ball 17 engages as shown in FIG. Engages with the mating surfaces 15b, 16b. Further, the movable cam disk 10 moves toward the fixed cam disk 9, and the elastic member 30 is extended by the movement of the movable cam disk 10 to weaken the pressing force, and the multi-plate friction clutch 20 is in the disengaged state. Slip occurs at the contact portions of the friction plates 21 and 22 of the multi-plate friction clutch 20, and the pulley hub 3 continues to rotate due to inertial force.
　このように、プーリ１に回転変動が生じると、弾性部材３０が弾性変形してプーリ１の回転変動を吸収し、また、プーリ１が急減速し、あるいは、停止すると、多板摩擦クラッチ２０の摩擦プレート２１、２２の接触部で滑りが生じてプーリハブ３は慣性力によって回転を継続するため、ベルトの張力が急激に増大するというようなことはなく、また、プーリ１とベルトの相互間でスリップが生じるという不都合の発生はない。 As described above, when the rotation fluctuation occurs in the pulley 1, the elastic member 30 is elastically deformed to absorb the rotation fluctuation of the pulley 1, and when the pulley 1 decelerates suddenly or stops, the multi-plate friction clutch 20 Since the pulley hub 3 continues to rotate due to the inertial force due to slippage at the contact portions of the friction plates 21 and 22, the belt tension does not increase suddenly, and between the pulley 1 and the belt. There is no inconvenience of slipping.
　また、弾性部材３０の押圧力やトルクカム１４の作動によって発生する軸方向力はフランジ７と止め輪８で受けられて、軸受４に負荷されることがなく、また、トルクカム１４の作動によって軸方向に移動する可動カムディスク１０はラジアル軸受１３上を滑り移動するため、そのラジアル軸受１３にも大きな軸方向力が負荷されることもない。このため、軸受４やラジアル軸受１３が破損するようなことは極めて少なく、耐久性に優れたプーリユニットを得ることができる。 Further, the axial force generated by the pressing force of the elastic member 30 and the operation of the torque cam 14 is received by the flange 7 and the retaining ring 8 and is not loaded on the bearing 4, and the axial direction by the operation of the torque cam 14. Since the movable cam disk 10 that moves in a sliding manner slides on the radial bearing 13, a large axial force is not applied to the radial bearing 13. For this reason, the bearing 4 and the radial bearing 13 are hardly damaged, and a pulley unit having excellent durability can be obtained.
　ここで、トルクカム１４の作動によって可動カムディスク１０の軸方向への移動量が必要以上に大きい場合は、ボール１７が固定カムディスク９と可動カムディスク１０の対向面に乗り上げてプーリ１の回転をプーリハブ３に伝達することができなくなるという問題が発生する。 Here, when the movement amount of the movable cam disk 10 in the axial direction is larger than necessary due to the operation of the torque cam 14, the ball 17 rides on the opposing surface of the fixed cam disk 9 and the movable cam disk 10 to rotate the pulley 1. There arises a problem that transmission to the pulley hub 3 becomes impossible.
　しかし、図１に示すプーリユニットにおいては、プーリハブ３の外径面上にリング状のストッパ３１を設け、そのストッパ３１によって可動カムディスク１０の軸方向の移動量を制限しているため、ボール１７の乗り上げを防止することができ、プーリ１の回転をプーリハブ３に確実に伝達することができる。 However, in the pulley unit shown in FIG. 1, a ring-shaped stopper 31 is provided on the outer diameter surface of the pulley hub 3, and the amount of movement of the movable cam disk 10 in the axial direction is limited by the stopper 31. The rotation of the pulley 1 can be reliably transmitted to the pulley hub 3.
　第１の実施の形態で示すように、プーリ１とプーリハブ３を結合および結合解除する摩擦クラッチとして多板摩擦クラッチ２０を採用することにより、複数の摩擦プレート２１、２２のそれぞれの接触部からプーリ１の回転をプーリハブ３に伝達することができる。 As shown in the first embodiment, by adopting a multi-plate friction clutch 20 as a friction clutch for connecting and releasing the pulley 1 and the pulley hub 3, the pulley from each contact portion of the plurality of friction plates 21 and 22. 1 rotation can be transmitted to the pulley hub 3.
　このため、単板摩擦クラッチに比較して、弾性部材３０から多板摩擦クラッチ２０に負荷される押圧力を低くすることができ、その押圧力の低下によってトルクカム１４部における面圧を低下させることができるので、上記トルクカム１４部の耐久性の向上を図ることができる。 For this reason, compared with a single-plate friction clutch, the pressing force applied to the multi-plate friction clutch 20 from the elastic member 30 can be lowered, and the surface pressure at the torque cam 14 portion is reduced by the reduction of the pressing force. Therefore, the durability of the torque cam 14 can be improved.
　ここで、多板摩擦クラッチ２０の軸方向一端のインナ側摩擦プレート２１に弾性力を負荷する弾性部材３０の内径面に、例えば、図４の鎖線で示すように切欠部３２を形成し、プーリハブ３のフランジ７にその切欠部３２に嵌合する突起部３３を設けて弾性部材３０をプーリハブに回り止めすると、インナ側摩擦プレート２１と弾性部材３０とが相対回転するのを防止することができるため、上記弾性部材３０の接触摩耗を抑制することができる。このため、弾性部材３０の荷重特性が変化するという不都合の発生はなく、多板摩擦クラッチ２０の滑りを防止することができる。 Here, a notch 32 is formed on the inner surface of the elastic member 30 that applies an elastic force to the inner friction plate 21 at one end in the axial direction of the multi-plate friction clutch 20, for example, as shown by a chain line in FIG. When the protrusion 33 that fits the notch 32 is provided on the flange 7 of the third flange and the elastic member 30 is prevented from rotating around the pulley hub, the inner friction plate 21 and the elastic member 30 can be prevented from rotating relative to each other. Therefore, contact wear of the elastic member 30 can be suppressed. For this reason, there is no inconvenience that the load characteristic of the elastic member 30 changes, and the slip of the multi-plate friction clutch 20 can be prevented.
　図５に示すように、多板摩擦クラッチ２０を形成する複数の摩擦プレート２１、２２のそれぞれの接触面における少なくとも一方に摩擦材２６を設けると、各接触面での摩擦係数を高めることができるため、伝達トルクの容量を高めることができる。逆に、摩擦プレート２１、２２に負荷する押圧力の低減を図ることができるため、摩擦プレート２１、２２の耐久性の低下を抑制することができる。 As shown in FIG. 5, when the friction material 26 is provided on at least one of the contact surfaces of the plurality of friction plates 21 and 22 forming the multi-plate friction clutch 20, the friction coefficient at each contact surface can be increased. Therefore, the capacity of transmission torque can be increased. Conversely, since the pressing force applied to the friction plates 21 and 22 can be reduced, it is possible to suppress a decrease in the durability of the friction plates 21 and 22.
　多板摩擦クラッチ２０を形成する複数の摩擦プレート２１、２２のそれぞれの接触面に窒化処理、浸炭処理、高周波熱処理等の硬化処理を施すと、摩擦プレート２１、２２の硬度を高めることができるため、耐摩耗性と耐久性の向上を図ることができる。 If the respective contact surfaces of the plurality of friction plates 21 and 22 forming the multi-plate friction clutch 20 are subjected to hardening treatment such as nitriding treatment, carburizing treatment, and high-frequency heat treatment, the hardness of the friction plates 21 and 22 can be increased. It is possible to improve wear resistance and durability.
　また、摩擦プレート２１、２２の耐摩耗性と耐久性の向上を図るため、上記硬化処理に代えて、窒化チタン、窒化クロム、窒化チタンアルミ、炭窒化チタン等の窒化物被膜や炭化チタン等の炭化物被膜からなる硬質被膜を設けるようにしてもよい。 Further, in order to improve the wear resistance and durability of the friction plates 21 and 22, a nitride film such as titanium nitride, chromium nitride, titanium nitride aluminum, titanium carbonitride, titanium carbide, etc. may be used instead of the above-described curing treatment. A hard coating made of a carbide coating may be provided.
　図６（ａ）、（ｂ）は、インナ側摩擦プレート２１およびアウタ側摩擦プレート２２の摩擦面に複数の潤滑剤排出溝２７を放射状に設けている。このように、摩擦プレート２１、２２に潤滑剤排出溝２７を形成すると、インナ側摩擦プレート２１とアウタ側摩擦プレート２２とが弾性部材３０の押圧により互いに圧接するとき、摩擦プレート２１、２２間に介在する潤滑油は潤滑剤排出溝２７内に押し出されるため、摩擦面に潤滑剤が過剰に付着するのを防止することができ、多板摩擦クラッチ２０の滑りを防止することができる。 6 (a) and 6 (b), a plurality of lubricant discharge grooves 27 are provided radially on the friction surfaces of the inner side friction plate 21 and the outer side friction plate 22. When the lubricant discharge groove 27 is formed in the friction plates 21 and 22 in this way, when the inner friction plate 21 and the outer friction plate 22 are pressed against each other by the pressing of the elastic member 30, the friction plates 21 and 22 are Since the intervening lubricating oil is pushed into the lubricant discharge groove 27, it is possible to prevent the lubricant from excessively adhering to the friction surface and to prevent the multi-plate friction clutch 20 from slipping.
　ここで、図６（ｃ）、（ｄ）に示すように、潤滑剤排出溝２７をスパイラル状とすると、各摩擦プレート２１、２２の回転時に、潤滑剤排出溝２７の内端と外端間に圧力差を生じさせることができるため、潤滑剤は潤滑剤排出溝２７内にスムーズに流れ込み、摩擦面に潤滑剤が過剰に付着するのをより効果的に防止することができる。 Here, as shown in FIGS. 6C and 6D, when the lubricant discharge groove 27 is spiral, when the friction plates 21 and 22 rotate, the distance between the inner end and the outer end of the lubricant discharge groove 27 is increased. Therefore, the lubricant can smoothly flow into the lubricant discharge groove 27 and more effectively prevent the lubricant from adhering to the friction surface.
　なお、多板摩擦クラッチ２０を形成する複数の摩擦プレート２１、２２のそれぞれを、アルミニウム合金またはマグネシウム合金製とすると、慣性モーメントを低減し、プーリユニットの軽量化を図ることができる。 If each of the plurality of friction plates 21 and 22 forming the multi-plate friction clutch 20 is made of aluminum alloy or magnesium alloy, the moment of inertia can be reduced and the weight of the pulley unit can be reduced.
　図３（ａ）、（ｂ）では、トルクカム１４として、カム溝１５、１６とボール１７から成るものを示したが、ボール１７の代わりにローラからなるものであってもよい。また、図７（ａ）に示すように、固定カムディスク９に、周方向に下り勾配をもって傾斜する傾斜カム面１８ａと、その傾斜カム面１８ａの低所端に連続して形成されて軸方向に向く係合面１８ｂを溝底に有するカム溝１８を形成し、可動カムディスク１０に、そのカム溝１８に適合するカム突起１９を設けた構成からなるものであってもよい。この場合、固定カムディスク９にカム突起を設け、可動カムディスク１０にカム溝を形成するようにしてもよい。図７（ｂ）はトルクカム１４の作動状態を示している。 3 (a) and 3 (b), the torque cam 14 is composed of the cam grooves 15, 16 and the ball 17, but may be composed of a roller instead of the ball 17. Further, as shown in FIG. 7A, the fixed cam disk 9 is formed continuously with the inclined cam surface 18a inclined with a downward gradient in the circumferential direction and the lower end of the inclined cam surface 18a in the axial direction. The cam groove 18 having the engaging surface 18b facing the groove may be formed, and the movable cam disk 10 may be provided with a cam protrusion 19 adapted to the cam groove 18. In this case, a cam protrusion may be provided on the fixed cam disk 9 and a cam groove may be formed on the movable cam disk 10. FIG. 7B shows the operating state of the torque cam 14.
　図８および図９は、この発明に係るプーリユニットの第２の実施の形態を示す。この実施の形態においては、プーリ１の内径面に突出部としてのフランジ４０と止め輪４１を軸方向に間隔をおいて設け、そのフランジ４０と止め輪４１間に、止め輪４１側から順に、ワッシャ４２、固定カムディスク９、可動カムディスク１０、多板摩擦クラッチ２０を構成するアウタ側摩擦プレート２２およびインナ側摩擦プレート２１、皿ばねからなる弾性部材４３を組込み、上記固定カムディスク９と可動カムディスク１０との対向部間にトルクカム１４を設けている。 8 and 9 show a second embodiment of the pulley unit according to the present invention. In this embodiment, a flange 40 and a retaining ring 41 as protruding portions are provided on the inner diameter surface of the pulley 1 with an interval in the axial direction, and between the flange 40 and the retaining ring 41 in order from the retaining ring 41 side, A washer 42, a fixed cam disk 9, a movable cam disk 10, an outer side friction plate 22 and an inner side friction plate 21 constituting a multi-plate friction clutch 20, and an elastic member 43 made up of a disc spring are incorporated, and is movable with the fixed cam disk 9. A torque cam 14 is provided between a portion facing the cam disk 10.
　また、固定カムディスク９をスプライン４４によりプーリハブ３に対して回り止めし、上記アウタ側摩擦プレート２２をスプライン４５によりプーリ１に対して回り止めし、かつ、軸方向に移動自在とし、一方、インナ側摩擦プレート２１を可動カムディスク１０の側面内周部に形成された円筒部４６にスプライン４７を介して回り止めし、かつ、軸方向に移動自在に支持している。 Further, the fixed cam disk 9 is prevented from rotating with respect to the pulley hub 3 by the spline 44, the outer side friction plate 22 is prevented from rotating with respect to the pulley 1 by the spline 45, and is movable in the axial direction. The side friction plate 21 is supported by a cylindrical portion 46 formed on the inner peripheral portion of the side surface of the movable cam disk 10 through a spline 47 and supported so as to be movable in the axial direction.
　さらに、弾性部材４３の外径面とプーリ１の内径面間にリング状のストッパ４８を組み込んで、可動カムディスク１０の軸方向の移動量を、トルクカム１４によって移動される可動カムディスク１０の最大移動量の範囲内に規制し、さらに、固定カムディスク９および可動カムディスク１０の外径面とプーリ１の内径面間にラジアル軸受４９を組み込んで、固定カムディスク９および可動カムディスク１０を回転自在に支持している点で図１に示すプーリユニットと相違している。 Further, a ring-shaped stopper 48 is incorporated between the outer diameter surface of the elastic member 43 and the inner diameter surface of the pulley 1 so that the moving amount of the movable cam disk 10 in the axial direction is the maximum of the movable cam disk 10 moved by the torque cam 14. In addition, a radial bearing 49 is incorporated between the outer diameter surface of the fixed cam disk 9 and the movable cam disk 10 and the inner diameter surface of the pulley 1 so that the fixed cam disk 9 and the movable cam disk 10 are rotated. It differs from the pulley unit shown in FIG. 1 in that it is supported freely.
　このため、図１に示すプーリユニットと同一の部品には同一の符合を付して説明を省略する。 For this reason, the same parts as those of the pulley unit shown in FIG.
　上記の第２の実施の形態で示すプーリユニットにおいて、プーリ１に正回転方向の回転トルクが入力されると、アウタ側摩擦プレート２２が回転し、そのアウタ側摩擦プレート２２と可動カムディスク１０の接触部に作用する摩擦抵抗により、可動カムディスク１０もアウタ側摩擦プレート２２と共に回転する。 In the pulley unit shown in the second embodiment, when a rotational torque in the forward rotation direction is input to the pulley 1, the outer side friction plate 22 rotates, and the outer side friction plate 22 and the movable cam disk 10 Due to the frictional resistance acting on the contact portion, the movable cam disk 10 also rotates with the outer side friction plate 22.
　このとき、可動カムディスク１０は固定カムディスク９に対して相対回転するため、トルクカム１４の作動により、可動カムディスク１０に軸方向の押圧力が負荷されて、可動カムディスク１０が固定カムディスク９から離反する方向に移動する。 At this time, since the movable cam disk 10 rotates relative to the fixed cam disk 9, an axial pressing force is applied to the movable cam disk 10 by the operation of the torque cam 14, so that the movable cam disk 10 is fixed to the fixed cam disk 9. Move away from the direction.
　図９は、可動カムディスク１０の移動状態を示し、上記可動カムディスク１０の移動によって弾性部材４３が弾性変形し、多板摩擦クラッチ２０の複数の摩擦プレート２１、２２の相互の接触圧および可動カムディスク１０とこれに対向するアウタ側摩擦プレート２２の接触圧が高くなって多板摩擦クラッチ２０が結合状態となる。 FIG. 9 shows the moving state of the movable cam disk 10, and the elastic member 43 is elastically deformed by the movement of the movable cam disk 10, and the mutual contact pressure and the movement of the plurality of friction plates 21 and 22 of the multi-plate friction clutch 20 are shown. The contact pressure between the cam disk 10 and the outer side friction plate 22 opposed to the cam disk 10 is increased, and the multi-plate friction clutch 20 is engaged.
　このため、プーリ１の回転は、多板摩擦クラッチ２０から可動カムディスク１０に伝達されると共に、その可動カムディスク１０からトルクカム１４のボール１７を介して固定カムディスク９に伝達される。また、固定カムディスク９の回転はプーリハブ３に伝達され、プーリハブ３がプーリ１と同方向に回転する。 For this reason, the rotation of the pulley 1 is transmitted from the multi-plate friction clutch 20 to the movable cam disk 10 and from the movable cam disk 10 to the fixed cam disk 9 via the balls 17 of the torque cam 14. Further, the rotation of the fixed cam disk 9 is transmitted to the pulley hub 3, and the pulley hub 3 rotates in the same direction as the pulley 1.
　プーリハブ３への回転トルクの伝達状態において、クランクシャフトの角速度の変化によりプーリ１に回転変動が生じると、固定カムディスク９と可動カムディスク１０が相対回転する。このとき、クランクシャフトの角速度の変化によるプーリ１の回転変動は比較的小さいため、図３に示すボール１７は傾斜カム面１５ａ、１６ａに沿って転がり移動する。その転がり移動によって可動カムディスク１０が軸方向に移動し、その可動カムディスク１０と共に移動する多板摩擦クラッチ２０からの押圧により弾性部材４３が弾性変形する。その弾性部材４３の弾性変形によってプーリ１の回転変動が吸収され、プーリハブ３にその回転変動が伝達されるのが防止される。また、多板摩擦クラッチ２０は結合状態に維持される。 When the rotational fluctuation occurs in the pulley 1 due to the change in the angular speed of the crankshaft in the state of transmission of the rotational torque to the pulley hub 3, the fixed cam disk 9 and the movable cam disk 10 rotate relative to each other. At this time, since the rotational fluctuation of the pulley 1 due to the change in the angular velocity of the crankshaft is relatively small, the ball 17 shown in FIG. 3 rolls along the inclined cam surfaces 15a and 16a. Due to the rolling movement, the movable cam disk 10 moves in the axial direction, and the elastic member 43 is elastically deformed by the pressure from the multi-plate friction clutch 20 that moves together with the movable cam disk 10. The elastic deformation of the elastic member 43 absorbs the rotational fluctuation of the pulley 1 and prevents the rotational fluctuation from being transmitted to the pulley hub 3. Further, the multi-plate friction clutch 20 is maintained in the coupled state.
　エンジンを急減速し、あるいは、停止すると、オルタネータの回転軸は慣性力が大きいため、プーリハブ３は回転を続けようとする。慣性力によるプーリハブ３の回転により、可動カムディスク１０は固定カムディスク９に対して図３（ｂ）の矢印で示す方向に相対回転し、ボール１７は、図３（ａ）に示すように係合面１５ｂ、１６ｂに係合する。また、可動カムディスク１０は固定カムディスク９に向けて移動し、その可動カムディスク１０の移動によって弾性部材４３は伸張して押圧力が弱くなり、多板摩擦クラッチ２０は結合解除状態となって、多板摩擦クラッチ２０の摩擦プレート２１、２２の接触部で滑りが生じ、プーリハブ３は慣性力によって回転を継続する。 When the engine is decelerated suddenly or stopped, the rotating shaft of the alternator has a large inertial force, so the pulley hub 3 tries to continue rotating. Due to the rotation of the pulley hub 3 due to the inertial force, the movable cam disk 10 rotates relative to the fixed cam disk 9 in the direction indicated by the arrow in FIG. 3B, and the ball 17 engages as shown in FIG. Engages with the mating surfaces 15b, 16b. Further, the movable cam disk 10 moves toward the fixed cam disk 9, and the elastic member 43 is extended by the movement of the movable cam disk 10 and the pressing force is weakened, and the multi-plate friction clutch 20 is in the disengaged state. Slip occurs at the contact portions of the friction plates 21 and 22 of the multi-plate friction clutch 20, and the pulley hub 3 continues to rotate due to inertial force.
　このように、プーリ１に回転変動が生じると、弾性部材４３が弾性変形してプーリ１の回転変動を吸収し、また、プーリ１が急減速し、あるいは、停止すると、多板摩擦クラッチ２０の摩擦プレート２１、２２の接触部で滑りが生じてプーリハブ３は慣性力によって回転を継続するため、ベルトの張力が急激に増大するというようなことはなく、また、プーリ１とベルトの相互間でスリップが生じるという不都合の発生はない。 As described above, when the rotation variation occurs in the pulley 1, the elastic member 43 elastically deforms and absorbs the rotation variation of the pulley 1, and when the pulley 1 decelerates suddenly or stops, the multi-plate friction clutch 20 Since the pulley hub 3 continues to rotate due to the inertial force due to slippage at the contact portions of the friction plates 21 and 22, the belt tension does not increase suddenly, and between the pulley 1 and the belt. There is no inconvenience of slipping.
　また、弾性部材４３の押圧力やトルクカム１４の作動によって発生する軸方向力はフランジ７と止め輪８で受けられて、軸受４に負荷されることがなく、また、トルクカム１４の作動によって軸方向に移動する可動カムディスク１０はラジアル軸受４９上を滑り移動するため、そのラジアル軸受４９にも大きな軸方向力が負荷されることもない。このため、軸受４やラジアル軸受４９が破損するようなことは極めて少なく、耐久性に優れたプーリユニットを得ることができる。 Further, the axial force generated by the pressing force of the elastic member 43 and the operation of the torque cam 14 is received by the flange 7 and the retaining ring 8 and is not loaded on the bearing 4, and the axial direction by the operation of the torque cam 14. Since the movable cam disk 10 that moves to slides on the radial bearing 49, a large axial force is not applied to the radial bearing 49 either. For this reason, the bearing 4 and the radial bearing 49 are hardly damaged, and a pulley unit having excellent durability can be obtained.
　さらに、プーリ１の内径面上にリング状のストッパ４８を設け、そのストッパ４８によって可動カムディスク１０の軸方向の移動量を制限しているため、ボール１７の乗り上げを防止することができ、プーリ１の回転をプーリハブ３に確実に伝達することができる。 Furthermore, since a ring-shaped stopper 48 is provided on the inner diameter surface of the pulley 1 and the amount of movement of the movable cam disk 10 in the axial direction is limited by the stopper 48, the ball 17 can be prevented from climbing, and the pulley 1 rotation can be reliably transmitted to the pulley hub 3.
　第２の実施の形態で示すように、プーリ１とプーリハブ３を結合および結合解除する多板摩擦クラッチとして多板摩擦クラッチ２０を採用することにより、第１の実施の形態で示すプーリユニットと同様に、複数の摩擦プレート２１、２２のそれぞれの接触部からプーリ１の回転をプーリハブ３に伝達することができる。 As shown in the second embodiment, by adopting a multi-plate friction clutch 20 as a multi-plate friction clutch for connecting and releasing the pulley 1 and the pulley hub 3, the same as the pulley unit shown in the first embodiment. In addition, the rotation of the pulley 1 can be transmitted to the pulley hub 3 from the contact portions of the plurality of friction plates 21 and 22.
　このため、単板摩擦クラッチと比較して、弾性部材３０から多板摩擦クラッチ２０に負荷される押圧力を小さくすることができ、その押圧力の低下によってトルクカム１４部における面圧を低下させることができるので、上記トルクカム１４部の耐久性の向上を図ることができる。 For this reason, compared with a single plate friction clutch, the pressing force applied from the elastic member 30 to the multi-plate friction clutch 20 can be reduced, and the surface pressure at the torque cam 14 portion is reduced by the reduction of the pressing force. Therefore, the durability of the torque cam 14 can be improved.
　上記第２の実施の形態におけるプーリユニットにおいても、多板摩擦クラッチ２０を形成する複数の摩擦プレート２１、２２のそれぞれの接触面における少なくとも一方に図５に示す摩擦材２６を設けるようにしてもよく、また、インナ側摩擦プレート２１およびアウタ側摩擦プレート２２の摩擦面に、図６（ａ）乃至（ｄ）に示すような複数の潤滑剤排出溝２７を設けるようにしてもよい。さらに、図９の鎖線で示すように、フランジ４０に突起部５０を設け、その突起部５０を弾性部材４３の外径部に形成された切欠部５１に挿入してプーリ１に回り止めしてもよい。 Also in the pulley unit in the second embodiment, the friction material 26 shown in FIG. 5 may be provided on at least one of the contact surfaces of the plurality of friction plates 21 and 22 forming the multi-plate friction clutch 20. Alternatively, a plurality of lubricant discharge grooves 27 as shown in FIGS. 6A to 6D may be provided on the friction surfaces of the inner friction plate 21 and the outer friction plate 22. Further, as shown by a chain line in FIG. 9, a protrusion 50 is provided on the flange 40, and the protrusion 50 is inserted into a notch 51 formed on the outer diameter portion of the elastic member 43 to prevent the pulley 1 from rotating. Also good.
　また、トルクカム１４として、図７（ａ）、（ｂ）に示すトルクカム１４を採用してもよい。 Further, the torque cam 14 shown in FIGS. 7A and 7B may be adopted as the torque cam 14.
１　　　プーリ
３　　　プーリハブ
４　　　軸受
７　　　フランジ（突出部）
８　　　止め輪（突出部）
９　　　固定カムディスク
１０　　可動カムディスク
１３　　ラジアル軸受
１４　　トルクカム
１５　　カム溝
１５ａ　傾斜カム面
１５ｂ　係合面
１６　　カム溝
１６ａ　傾斜カム面
１６ｂ　係合面
１７　　ボール（転動体）
１８　　カム溝
１８ａ　傾斜カム面
１８ｂ　係合面
１９　　カム突起
２０　　多板摩擦クラッチ
２１　　インナ側摩擦プレート
２２　　アウタ側摩擦プレート
２６　　摩擦材
２７　　潤滑剤排出溝
３０　　弾性部材
３１　　ストッパ
４０　　フランジ（突出部）
４１　　止め輪（突出部）
４３　　弾性部材
４８　　ストッパ
４９　　ラジアル軸受 1 Pulley 3 Pulley hub 4 Bearing 7 Flange (protrusion)
8 Retaining ring (protruding part)
9 fixed cam disk 10 movable cam disk 13 radial bearing 14 torque cam 15 cam groove 15a inclined cam surface 15b engaging surface 16 cam groove 16a inclined cam surface 16b engaging surface 17 ball (rolling element)
18 Cam groove 18a Inclined cam surface 18b Engagement surface 19 Cam projection 20 Multi-plate friction clutch 21 Inner side friction plate 22 Outer side friction plate 26 Friction material 27 Lubricant discharge groove 30 Elastic member 31 Stopper 40 Flange (protrusion)
41 Retaining ring (protrusion)
43 Elastic member 48 Stopper 49 Radial bearing

Claims (15)

  1. 　プーリとその内側に組込まれたプーリハブを、その両部材の一方の端部間に組込まれた軸受によって相対的に回転自在に支持し、前記プーリハブの外径面に２つの突出部を軸方向に間隔をおいて設け、その２つの突出部間に、前記プーリに回り止めされ、一方の突出部によって軸方向外方への移動が阻止される固定カムディスクと、プーリハブに対して回転可能に、かつ、軸方向に移動可能に支持された可動カムディスクとを組込み、その固定カムディスクと可動カムディスクの対向面間に、両カムディスクの一方向への相対回転により可動カムディスクを固定カムディスクから離反する方向に移動させ、他方向への相対回転時に前記両カムディスクを回転方向に係合させるトルクカムを設け、前記可動カムディスクと他方の突出部間に、前記可動カムディスクとプーリハブとを結合する多板摩擦クラッチと、前記可動カムディスクが固定カムディスクから離反する移動時にその多板摩擦クラッチからの押圧により弾性変形し、その復元弾性により多板摩擦クラッチを結合状態とする弾性部材を組込んだプーリユニット。 A pulley and a pulley hub incorporated inside the pulley are supported relatively rotatably by a bearing incorporated between one end of both members, and two protrusions are axially provided on the outer diameter surface of the pulley hub. A fixed cam disk, which is provided at an interval and is prevented from rotating by the pulley between the two protrusions and is prevented from moving outward in the axial direction by one protrusion, and is rotatable with respect to the pulley hub. In addition, a movable cam disk supported so as to be movable in the axial direction is incorporated, and the movable cam disk is fixed to the fixed cam disk by relative rotation in one direction between the fixed cam disk and the movable cam disk. A torque cam that is moved in a direction away from the other and engaged with the two cam disks in the rotation direction at the time of relative rotation in the other direction, between the movable cam disk and the other protrusion, The multi-plate friction clutch that couples the movable cam disk and the pulley hub, and the multi-plate friction clutch that is elastically deformed by the pressure from the multi-plate friction clutch when the movable cam disk moves away from the fixed cam disk, and that is restored. Pulley unit that incorporates an elastic member that connects the two.
  2. 　前記プーリハブの外径面に可動カムディスクの軸方向の移動量を、前記トルクカムによって移動される可動カムディスクの最大移動量の範囲内に規制するストッパを設けた請求項１に記載のプーリユニット。 The pulley unit according to claim 1, wherein a stopper is provided on the outer diameter surface of the pulley hub to restrict a movement amount of the movable cam disk in an axial direction within a range of a maximum movement amount of the movable cam disk moved by the torque cam.
  3. 　前記多板摩擦クラッチを形成する複数の摩擦プレートのうち、弾性部材と当接する軸方向一端の摩擦プレートと前記弾性部材とをプーリハブに回り止めした請求項１又は２に記載のプーリユニット。 The pulley unit according to claim 1 or 2, wherein, among a plurality of friction plates forming the multi-plate friction clutch, a friction plate at one end in an axial direction contacting an elastic member and the elastic member are prevented from rotating on a pulley hub.
  4. 　プーリとその内側に組込まれたプーリハブを、その両部材の一方の端部間に組込まれた軸受によって相対的に回転自在に支持し、前記プーリの内径面に２つの突出部を軸方向に間隔をおいて設け、その２つの突出部間に、前記プーリハブに回り止めされ、一方の突出部によって軸方向外方への移動が阻止される固定カムディスクと、プーリに対して回転可能に、かつ、軸方向に移動可能に支持された可動カムディスクとを組込み、その固定カムディスクと可動カムディスクの対向面間に、両カムディスクの一方向への相対回転により可動カムディスクを固定カムディスクから離反する方向に移動させ、他方向への相対回転時に前記両カムディスクを回転方向に係合させるトルクカムを設け、前記可動カムディスクと他方の突出部間に、前記可動カムディスクとプーリハブとを結合する多板摩擦クラッチと、前記可動カムディスクが固定カムディスクから離反する移動時にその多板摩擦クラッチからの押圧により弾性変形し、その復元弾性により多板摩擦クラッチを結合状態とする弾性部材を組込んだプーリユニット。 A pulley and a pulley hub incorporated inside the pulley are supported relatively rotatably by a bearing incorporated between one end of both members, and two protrusions are axially spaced on the inner diameter surface of the pulley. A fixed cam disk that is prevented from rotating by the pulley hub between the two protrusions and is prevented from moving outward in the axial direction by one protrusion, and is rotatable with respect to the pulley, and , A movable cam disk supported so as to be movable in the axial direction is incorporated, and the movable cam disk is separated from the fixed cam disk by relative rotation in one direction between the fixed cam disk and the movable cam disk. A torque cam is provided that moves in a direction away from each other and engages both cam discs in the rotational direction at the time of relative rotation in the other direction, and between the movable cam disc and the other protrusion, A multi-plate friction clutch that couples the moving cam disk and the pulley hub; and when the movable cam disk moves away from the fixed cam disk, the multi-plate friction clutch is elastically deformed by the pressure from the multi-plate friction clutch, and the restoring elasticity causes the multi-plate friction clutch to Pulley unit that incorporates an elastic member to be connected.
  5. 　前記プーリの内径面に可動カムディスクの軸方向の移動量を、前記トルクカムによって移動される可動カムディスクの最大移動量の範囲内に規制するストッパを設けた請求項４に記載のプーリユニット。 The pulley unit according to claim 4, wherein a stopper is provided on the inner diameter surface of the pulley to restrict the amount of movement of the movable cam disk in the axial direction within the range of the maximum movement amount of the movable cam disk moved by the torque cam.
  6. 　前記多板摩擦クラッチを形成する複数の摩擦プレートのうち、弾性部材と当接する軸方向一端の摩擦プレートと前記弾性部材とをプーリに回り止めした請求項４に記載のプーリユニット。 The pulley unit according to claim 4, wherein, among the plurality of friction plates forming the multi-plate friction clutch, the friction plate at one end in the axial direction contacting the elastic member and the elastic member are prevented from rotating by the pulley.
  7. 　前記トルクカムが、周方向に下り勾配をもって傾斜する傾斜カム面およびその傾斜カム面の低所端に連続して形成された係合面を溝底に有するカム溝と、そのカム溝に適合するカム突起とからなる請求項１乃至６のいずれかの項に記載のプーリユニット。 The torque cam includes a cam groove having an inclined cam surface that is inclined with a downward slope in the circumferential direction and an engagement surface formed continuously at a lower end of the inclined cam surface at the groove bottom, and a cam that fits the cam groove The pulley unit according to any one of claims 1 to 6, comprising a protrusion.
  8. 　前記トルクカムが、周方向に下り勾配を持って傾斜する傾斜カム面およびその傾斜カム面の低所端に連続して形成された係合面を溝底に有し、前記傾斜カム面の勾配が逆向きとなるよう固定カムディスクと可動カムディスクの対向面それぞれに形成された対向一対のカム溝と、その対向一対のカム溝間に組込まれた転動体とからなる請求項１乃至６のいずれかの項に記載のプーリユニット。 The torque cam has an inclined cam surface inclined with a downward gradient in the circumferential direction and an engagement surface formed continuously at a lower end of the inclined cam surface at the groove bottom, and the gradient of the inclined cam surface is 7. The method according to claim 1, further comprising: a pair of opposed cam grooves formed on opposite surfaces of the fixed cam disk and the movable cam disk so as to be opposite to each other, and a rolling element assembled between the pair of opposed cam grooves. The pulley unit described in the above section.
  9. 　前記多板摩擦クラッチを形成する複数の摩擦プレートのそれぞれの接触面における少なくとも一方に摩擦材を設けた請求項１乃至８のいずれかの項に記載のプーリユニット。 The pulley unit according to any one of claims 1 to 8, wherein a friction material is provided on at least one of contact surfaces of the plurality of friction plates forming the multi-plate friction clutch.
  10. 　前記多板摩擦クラッチを形成する複数の摩擦プレートのそれぞれの接触面に硬化処理を施した請求項１乃至８のいずれかの項に記載のプーリユニット。 The pulley unit according to any one of claims 1 to 8, wherein the contact surfaces of the plurality of friction plates forming the multi-plate friction clutch are subjected to a curing process.
  11. 　前記硬化処理が、窒化処理、浸炭処理、高周波熱処理の一種からなる請求項１０に記載のプーリユニット。 The pulley unit according to claim 10, wherein the hardening treatment is a kind of nitriding treatment, carburizing treatment, or high-frequency heat treatment.
  12. 　前記多板摩擦クラッチを形成する複数の摩擦プレートのそれぞれの接触面に硬質被膜を設けた請求項１乃至８のいずれかの項に記載のプーリユニット。 The pulley unit according to any one of claims 1 to 8, wherein a hard coating is provided on each contact surface of the plurality of friction plates forming the multi-plate friction clutch.
  13. 　前記硬質被膜が窒化物被膜または炭化物被膜からなる請求項１２に記載のプーリユニット。 The pulley unit according to claim 12, wherein the hard coating is made of a nitride coating or a carbide coating.
  14. 　前記多板摩擦クラッチを形成する複数の摩擦プレートのそれぞれの接触面における少なくとも一方に半径方向に延びる潤滑剤排出溝を形成した請求項１乃至１３のいずれかの項に記載のプーリユニット。 The pulley unit according to any one of claims 1 to 13, wherein a lubricant discharge groove extending in a radial direction is formed in at least one of contact surfaces of the plurality of friction plates forming the multi-plate friction clutch.
  15. 　前記多板摩擦クラッチを形成する複数の摩擦プレートのそれぞれが、アルミニウム合金またはマグネシウム合金からなる請求項１乃至１４のいずれかの項に記載のプーリユニット。 The pulley unit according to any one of claims 1 to 14, wherein each of the plurality of friction plates forming the multi-plate friction clutch is made of an aluminum alloy or a magnesium alloy.
PCT/JP2009/068245 2008-10-29 2009-10-23 Pulley unit WO2010050408A1 (en)

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JP2008277631A JP2010106903A (en) 2008-10-29 2008-10-29 Pulley unit
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JP2008299096A JP2010127294A (en) 2008-11-25 2008-11-25 Pulley unit

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2474121A (en) * 2009-09-30 2011-04-06 Honda Motor Co Ltd Multi-plate clutch system, having paired cam plates
JP2011236991A (en) * 2010-05-12 2011-11-24 Valeo Unisia Transmission Kk Stator of torque converter
JP2012211666A (en) * 2011-03-31 2012-11-01 Aisin Aw Co Ltd Hydraulic clutch
US20130161150A1 (en) * 2011-12-16 2013-06-27 Paul T. McCrary Pulley assembly with a decoupling mechanism
US9291217B2 (en) 2014-04-08 2016-03-22 Dayco Ip Holdings, Llc Pulley assembly with radially oriented decoupling mechanism
CN105782267A (en) * 2016-05-09 2016-07-20 黄山奔马集团有限公司 Separate multi-piece type clutch assembly
US9850997B2 (en) 2013-08-06 2017-12-26 Dayco Europe S.R.L Filtering pulley for a belt drive
TWI632306B (en) * 2016-09-10 2018-08-11 本土股份有限公司 Clutch structure

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6196222A (en) * 1984-10-17 1986-05-14 Kawasaki Heavy Ind Ltd Multiple disc friction clutch
JPH03140629A (en) * 1989-10-26 1991-06-14 Yamaha Motor Co Ltd Wet multiple disk clutch
JPH0617841A (en) * 1992-07-06 1994-01-25 Suzuki Motor Corp Plate for multiple-plate friction clutch
JPH0650353A (en) * 1992-07-28 1994-02-22 Toyota Motor Corp Frictional engagement device
JP2006009899A (en) * 2004-06-24 2006-01-12 Koyo Seiko Co Ltd Power transmission
JP2006349108A (en) * 2005-06-17 2006-12-28 Ntn Corp Rotation transmission device
JP2007040526A (en) * 2005-06-28 2007-02-15 Nsk Warner Kk Wet clutch friction plate and multiple disc friction clutch apparatus
JP2007270883A (en) * 2006-03-30 2007-10-18 Jtekt Corp Pulley unit

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6196222A (en) * 1984-10-17 1986-05-14 Kawasaki Heavy Ind Ltd Multiple disc friction clutch
JPH03140629A (en) * 1989-10-26 1991-06-14 Yamaha Motor Co Ltd Wet multiple disk clutch
JPH0617841A (en) * 1992-07-06 1994-01-25 Suzuki Motor Corp Plate for multiple-plate friction clutch
JPH0650353A (en) * 1992-07-28 1994-02-22 Toyota Motor Corp Frictional engagement device
JP2006009899A (en) * 2004-06-24 2006-01-12 Koyo Seiko Co Ltd Power transmission
JP2006349108A (en) * 2005-06-17 2006-12-28 Ntn Corp Rotation transmission device
JP2007040526A (en) * 2005-06-28 2007-02-15 Nsk Warner Kk Wet clutch friction plate and multiple disc friction clutch apparatus
JP2007270883A (en) * 2006-03-30 2007-10-18 Jtekt Corp Pulley unit

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2474121A (en) * 2009-09-30 2011-04-06 Honda Motor Co Ltd Multi-plate clutch system, having paired cam plates
GB2474121B (en) * 2009-09-30 2016-08-17 Honda Motor Co Ltd Multi-plate clutch system
JP2011236991A (en) * 2010-05-12 2011-11-24 Valeo Unisia Transmission Kk Stator of torque converter
JP2012211666A (en) * 2011-03-31 2012-11-01 Aisin Aw Co Ltd Hydraulic clutch
US20130161150A1 (en) * 2011-12-16 2013-06-27 Paul T. McCrary Pulley assembly with a decoupling mechanism
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
CN105782267A (en) * 2016-05-09 2016-07-20 黄山奔马集团有限公司 Separate multi-piece type clutch assembly
TWI632306B (en) * 2016-09-10 2018-08-11 本土股份有限公司 Clutch structure

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