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WO2018016212A1 - Dispositif de suppression de fluctuation de couple, convertisseur de couple et dispositif de transmission de force motrice - Google Patents

Dispositif de suppression de fluctuation de couple, convertisseur de couple et dispositif de transmission de force motrice Download PDF

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Publication number
WO2018016212A1
WO2018016212A1 PCT/JP2017/020880 JP2017020880W WO2018016212A1 WO 2018016212 A1 WO2018016212 A1 WO 2018016212A1 JP 2017020880 W JP2017020880 W JP 2017020880W WO 2018016212 A1 WO2018016212 A1 WO 2018016212A1
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WO
WIPO (PCT)
Prior art keywords
centrifuge
rotating body
torque fluctuation
torque
cam
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2017/020880
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English (en)
Japanese (ja)
Inventor
富山　直樹
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Exedy Corp
Original Assignee
Exedy Corp
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Filing date
Publication date
Application filed by Exedy Corp filed Critical Exedy Corp
Publication of WO2018016212A1 publication Critical patent/WO2018016212A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/167—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material having an inertia member, e.g. ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type

Definitions

  • the present invention relates to a torque fluctuation suppressing device, and more particularly to a torque fluctuation suppressing device for suppressing torque fluctuation of a rotating body to which torque is input.
  • the present invention also relates to a torque converter and a power transmission device including a torque fluctuation suppressing device.
  • a clutch device including a damper device and a torque converter are provided between an automobile engine and a transmission. Further, the torque converter is provided with a lockup device for mechanically transmitting torque at a predetermined rotational speed or more in order to reduce fuel consumption.
  • the lockup device generally has a clutch part and a damper having a plurality of torsion springs.
  • the clutch portion has a piston with a friction member that is pressed against the front cover by the action of hydraulic pressure. In the lock-up-on state, torque is transmitted from the front cover to the piston via the friction member, and further transmitted to the output side member via the plurality of torsion springs.
  • torque fluctuations can be suppressed by a damper having a plurality of torsion springs.
  • a dynamic damper device including an inertia member.
  • the dynamic damper device of Patent Document 1 is mounted on a plate that supports a torsion spring, a pair of inertia rings that are rotatable relative to the plate, and a plurality of coil springs provided between the plate and the inertia ring. And have.
  • An object of the present invention is to be able to suppress a peak of torque fluctuation in a relatively wide rotational speed range in an apparatus for suppressing torque fluctuation of a rotating member.
  • a torque fluctuation suppressing device is a device for suppressing torque fluctuation of a rotating body to which torque is input, and includes a mass body, a centrifuge, a cam mechanism, a movement restricting portion, It has.
  • the mass body is arranged side by side with the rotating body in the axial direction, is rotatable with the rotating body, and is disposed so as to be relatively rotatable with respect to the rotating body.
  • the centrifuge is supported by the rotating body and is arranged to be movable in the radial direction under centrifugal force.
  • the cam mechanism has a cam and a cam follower, and receives a centrifugal force acting on the centrifuge, and when a relative displacement in the rotational direction occurs between the rotating body and the mass body, the centrifugal force is reduced to a small relative displacement. Convert to a circumferential force in the direction
  • the cam is provided on one of the centrifuge and the mass body.
  • the cam follower is provided on the other of the centrifuge and the mass body and moves along the cam.
  • the movement restricting unit has an oil passage through which the viscous fluid can flow along with the movement of the centrifuge in the radial direction, and regulates the moving speed of the centrifuge inward in the radial direction.
  • the centrifuge receives a centrifugal force.
  • the cam mechanism converts the centrifugal force acting on the centrifuge into a circumferential force, which is applied between the rotating body and the mass body. It acts to reduce the relative displacement of. Torque fluctuation is suppressed by the operation of the cam mechanism.
  • the centrifugal force acting on the centrifuge is used as a force for suppressing the torque fluctuation
  • the characteristic for suppressing the torque fluctuation changes according to the rotational speed of the rotating body. Further, for example, the characteristics for suppressing torque fluctuation can be appropriately set depending on the shape of the cam and the like, and the peak of torque fluctuation in a wider rotational speed range can be suppressed.
  • the centrifuge moves in the radial direction, the viscous fluid passes through the oil passage of the movement restricting portion. Due to the resistance caused by the viscous fluid passing through the oil passage (especially the oil passage having a reduced cross-sectional area), the moving speed of the centrifuge decreases. Therefore, it is possible to suppress the hitting sound when the centrifuge falls to the inner peripheral side and collides with another member when the rotation is stopped.
  • the centrifuge is moved inward in the radial direction by the action of the cam mechanism. In this case as well, the movement of the centrifuge is restricted. The For this reason, the relative displacement between the rotating body and the mass body is restricted. That is, the movement restricting portion also functions as a stopper mechanism that restricts the relative rotation angle between the rotating body and the mass body.
  • the rotating body has a protrusion protruding outward in the radial direction on the outer periphery.
  • the protruding portion opens in the outer peripheral direction and has an opening having a predetermined depth on the inner peripheral side.
  • a centrifuge has a hole part in which a projection part is inserted, and a piston part inserted in an opening part.
  • the centrifuge can move in the radial direction along the protrusion.
  • an opening part functions as a cylinder by inserting a piston part in an opening part. Accordingly, the viscous fluid in the cylinder is moved by the movement of the piston portion of the centrifuge, and the moving speed of the centrifuge is regulated by the moving viscous fluid passing through the oil passage.
  • the oil passage is a gap around the piston portion inserted into the opening.
  • a fluid accommodating portion capable of accommodating a viscous fluid is formed by the opening of the rotating body and the hole of the centrifuge into which the protrusion of the rotating body is inserted.
  • the centrifuge is formed so as to extend in the rotational direction and has guide portions formed at both ends in the rotational direction.
  • the guide part is supported by the end surface of the circumferential direction of the projection part of a rotary body.
  • the cam is provided in the centrifuge and the cam follower is provided in the mass body.
  • the centrifuge guide portion is located on the opposite side of the contact point between the cam and the cam follower with the center of gravity of the centrifuge interposed therebetween. Abuts against the circumferential end face.
  • the guide portion of the centrifuge has at least a contact point between the cam and the cam follower with the center of gravity of the centrifuge interposed therebetween. It abuts against the end face of the protrusion at the opposite position. For this reason, in a centrifuge, it can suppress that a big rotational moment arises by using the end of a rotation direction as a fulcrum. Therefore, the centrifuge moves smoothly, and the configuration of the guide portion can be simplified.
  • the guide portion is a pair of rollers that are rotatably supported at both ends in the rotation direction of the centrifuge and roll on the circumferential end surface of the protrusion.
  • the movement of the centrifuge in the radial direction becomes smooth.
  • the guide portions are respectively arranged on the inner peripheral side and the outer peripheral side. It is necessary to provide a pair of rollers (two pairs in total).
  • the centrifuge since the rotational moment with one end in the rotational direction as a fulcrum is suppressed, even if the guide portion is configured by only a pair of rollers, The centrifuge can be moved smoothly.
  • the rotating body has a concave portion recessed on the inner peripheral side on the outer peripheral surface, and the centrifuge is accommodated in the concave portion.
  • the centrifuge has a hole that is recessed from the inner peripheral surface to the outer peripheral side, and the rotating body has a protrusion that is inserted into the hole of the centrifuge on the bottom surface of the recess.
  • a viscous fluid can be accommodated in the hole of the centrifuge, and the oil passage is a gap around the protrusion of the rotating body inserted into the hole.
  • the mass body includes a first inertia ring and a second inertia ring arranged to face each other with the rotating body interposed therebetween, and a pin that connects the first inertia ring and the second inertia ring so as not to be relatively rotatable.
  • the centrifuge is arranged between the first inertia ring and the second inertia ring in the axial direction on the outer peripheral portion of the rotating body and on the inner peripheral side of the pin.
  • the cam follower is a cylindrical roller having a hole through which a pin penetrates in the axial direction.
  • the cam is formed in the centrifuge and contacts the cam follower, and has a shape such that the circumferential force changes according to the relative displacement amount in the rotational direction between the rotating body and the mass body.
  • the cam follower is mounted using a pin that connects the first inertia ring and the second inertia ring. This simplifies the configuration of the cam mechanism.
  • the torque converter according to the present invention is disposed between the engine and the transmission.
  • the torque converter includes an input-side rotating body that receives torque from the engine, an output-side rotating body that outputs torque to the transmission, and a damper that is disposed between the input-side rotating body and the turbine. Any of the torque fluctuation suppression devices.
  • a power transmission device includes a flywheel, a clutch device, and any of the torque fluctuation suppression devices described above.
  • the flywheel includes a first inertial body that rotates about a rotation axis, a second inertial body that rotates about the rotation axis and is rotatable relative to the first inertial body, and a first inertial body and a second inertial body. And a damper disposed therebetween.
  • the clutch device is provided on the second inertial body of the flywheel.
  • the peak of torque fluctuation can be suppressed in a relatively wide rotational speed range in the apparatus for suppressing torque fluctuation of the rotating member. Further, according to the present invention, it is possible to suppress the hitting sound that the centrifuge collides with other members, and it is possible to realize the stopper mechanism with a simple configuration.
  • FIG. 2 is a partial front view of the output side rotating body and the torque fluctuation suppressing device of FIG. 1.
  • FIG. 3 is an arrow A view of FIG. 2.
  • the external appearance perspective view of the part shown by FIG. The figure for demonstrating the internal structure of a centrifuge.
  • the arrow B figure of FIG. The schematic diagram which shows the application example 1 of this invention.
  • the schematic diagram which shows the application example 3 of this invention The schematic diagram which shows the application example 4 of this invention.
  • the schematic diagram which shows the application example 5 of this invention The schematic diagram which shows the application example 6 of this invention.
  • the schematic diagram which shows the application example 7 of this invention The schematic diagram which shows the application example 8 of this invention.
  • FIG. 1 is a schematic diagram when the torque fluctuation suppressing device according to the first embodiment of the present invention is mounted on a lock-up device of a torque converter.
  • OO is the rotational axis of the torque converter.
  • the torque converter 1 includes a front cover 2, a torque converter main body 3, a lockup device 4, and an output hub 5. Torque is input to the front cover 2 from the engine.
  • the torque converter main body 3 includes an impeller 7 connected to the front cover 2, a turbine 8, and a stator (not shown).
  • the turbine 8 is connected to the output hub 5, and an input shaft (not shown) of the transmission can be engaged with the inner peripheral portion of the output hub 5 by a spline.
  • the lock-up device 4 has a clutch part, a piston that is operated by hydraulic pressure, and the like, and can take a lock-up on state and a lock-up off state.
  • the lock-up on state the torque input to the front cover 2 is transmitted to the output hub 5 via the lock-up device 4 without passing through the torque converter body 3.
  • the lock-up off state torque input to the front cover 2 is transmitted to the output hub 5 via the torque converter body 3.
  • the lockup device 4 includes an input side rotating body 11, an output side rotating body 12, a damper 13, and a torque fluctuation suppressing device 14.
  • the input side rotating body 11 includes a piston that is movable in the axial direction, and has a friction member 16 on the side surface on the front cover 2 side. When the friction member 16 is pressed against the front cover 2, torque is transmitted from the front cover 2 to the input side rotating body 11.
  • the output side rotator 12 is disposed so as to face the input side rotator 11 in the axial direction, and is rotatable relative to the input side rotator 11.
  • the output side rotating body 12 is connected to the output hub 5.
  • the damper 13 is disposed between the input side rotating body 11 and the output side rotating body 12.
  • the damper 13 has a plurality of torsion springs, and elastically connects the input side rotating body 11 and the output side rotating body 12 in the rotation direction.
  • the damper 13 transmits torque from the input-side rotator 11 to the output-side rotator 12, and absorbs and attenuates torque fluctuations.
  • FIG. 2 is a front view of the output side rotating body 12 and the torque fluctuation suppressing device 14. 2 shows a part of the output-side rotator 12 and the torque fluctuation suppressing device 14, but as a whole, the portions shown in FIG. 2 are provided at equiangular intervals at four locations in the circumferential direction.
  • ing. 3 is a view seen from the direction A in FIG. 2, and
  • FIG. 4 is an external perspective view of FIG. In FIG. 4, the inertia ring on one side (front side in FIG. 4) is removed and shown.
  • the torque fluctuation suppressing device 14 includes a first inertia ring 201 and a second inertia ring 202 that constitute the mass body 20, four centrifuges 21, and four cam mechanisms 22.
  • the first and second inertia rings 201 and 202 are plates each having a predetermined thickness formed in a continuous annular shape. As shown in FIG. 3, the output-side rotator 12 sandwiches the output-side rotator 12. Are arranged with a predetermined gap on both sides in the axial direction. That is, the output-side rotating body 12 and the first and second inertia rings 201 and 202 are arranged side by side in the axial direction.
  • the first and second inertia rings 201 and 202 have the same rotation axis as that of the output-side rotator 12, can rotate together with the output-side rotator 12, and can rotate relative to the output-side rotator 12. It is.
  • first and second inertia rings 201, 202 holes 201a, 202a penetrating in the axial direction are formed. And the 1st inertia ring 201 and the 2nd inertia ring 202 are being fixed by the rivet 24 which penetrates those holes 201a and 202a. Therefore, the first inertia ring 201 cannot move in the axial direction, the radial direction, and the rotation direction with respect to the second inertia ring 202.
  • the output-side rotator 12 is formed in a disc shape, and the inner peripheral portion is connected to the output hub 5 as described above.
  • the protrusion 121 has guide support portions 121a and 121b on both end faces in the circumferential direction, and further has an opening 121c with a predetermined width at the center in the circumferential direction.
  • the opening 121c is formed so as to open to the outer peripheral side and has a predetermined depth.
  • the centrifuge 21 has a first member 211 and a second member 212 whose longitudinal ends are connected by four screw members.
  • the first and second members 211 and 212 have the same shape.
  • the first and second members 211 and 212 sandwich the protrusion 121 of the output-side rotator 12 on the inner peripheral side of the rivet 24 between the axial directions of the first inertia ring 201 and the second inertia ring 202. Is arranged.
  • the centrifuge 21 rotates with the output-side rotator 12 and is movable in the radial direction by the centrifugal force generated by the rotation of the output-side rotator 12.
  • the centrifuge 21 is formed to extend in the rotation direction.
  • the first member 211 and the second member 212 constituting the centrifuge 21 are, as shown by the hatched lines in FIG. 5, connected portions C1 to C4 formed by four screw members formed at both ends in the longitudinal direction. Except for the central portion C5 in the longitudinal direction, a gap is provided in the axial direction. This gap constitutes a hole into which the protruding portion 121 of the output side rotating body 12 is inserted.
  • the first member 211 and the second member 212 constituting the centrifuge 21 are composed of connecting portions C1 to C4 formed by four screw members formed at both ends in the longitudinal direction, and a central portion C5 in the longitudinal direction. , Are in close contact.
  • first guide roller 26a and second guide roller 26b In the gap between both ends of the first member 211 and the second member 212 (the gap in the axial direction of both members 211 and 212), one first guide roller 26a and second guide roller 26b (guide portion), Both ends of the protrusion 121 of the output side rotating body 12 are arranged.
  • the first and second guide rollers 26a and 26b are rotatably mounted via bushes 28 around pins 27 supported at both ends of the first and second members 211 and 212.
  • the outer peripheral surface of the first guide roller 26 a is in contact with one guide support portion (side surface) 121 a of the protrusion 121 and can roll
  • the outer peripheral surface of the second roller 26 b is the other guide support of the protrusion 121. It is possible to roll in contact with the portion (side surface) 121b.
  • the central portion of the centrifuge 21 is formed with a piston portion 21a (a region C5 where the first member 211 and the second member 212 shown in FIG. 5 are in close contact with each other) having a predetermined length from the upper end surface to the inner peripheral side. .
  • the piston portion 21a is formed such that the first member 211 and the second member 212 are in close contact with each other without a gap.
  • the piston portion 21a is inserted into the opening 121c of the projection 121 so as to be movable in the radial direction through a predetermined gap.
  • the hydraulic oil can be accumulated by the opening 121c of the protrusion 121 and the hole portion (the gap between the first member 211 and the second member 212) in which the protrusion 121 is inserted.
  • a fluid containing portion is formed.
  • the gap between the piston portion 21a and the fluid storage portion functions as an oil passage through which the working oil flows, that is, an orifice Or in which a cross-sectional area through which the working oil passes is narrowed.
  • the first and second members 211 and 212 of the centrifuge 21 are formed in an arc shape in which the outer peripheral surfaces 211a and 212a are recessed toward the inner peripheral side, and as will be described later, these outer peripheral surfaces 211a and 212a, 212 a functions as the cam 31.
  • the cam mechanism 22 includes a cylindrical roller 30 as a cam follower and cams 31 that are outer peripheral surfaces 211 a and 212 a of the first and second members 211 and 212.
  • the roller 30 is fitted on the outer periphery of the trunk portion of the rivet 24. That is, the roller 30 is supported by the rivet 24.
  • the roller 30 is preferably mounted so as to be rotatable with respect to the rivet 24, but may not be rotatable.
  • the cam 31 is an arc-shaped surface with which the roller 30 abuts.
  • rotational phase difference the relative displacement amount in the rotation direction between the output-side rotator 12 and the inertia ring 20 is referred to as “rotational phase difference”.
  • FIG. 2, FIG. 6, and FIG. The deviation between the center position of the centrifuge 21 and the cam 31 in the circumferential direction and the center position of the roller 30 is shown.
  • FIG. 6 shows a case where a rotational phase difference + ⁇ occurs on the + R side
  • FIG. 7 shows a case where a rotational phase difference ⁇ occurs on the ⁇ R side.
  • the first component force P1 is a force that moves the output side rotating body 12 to the left in FIG. 6 via the cam mechanism 22 and the centrifuge 21. That is, a force in the direction of reducing the rotational phase difference between the output side rotating body 12 and the inertia ring 20 acts on the output side rotating body 12. Moreover, the centrifuge 21 is moved to the inner peripheral side against the centrifugal force by the second component force P2.
  • FIG. 7 shows a case where a rotational phase difference ⁇ is generated between the output-side rotator 12 and the inertia ring 20, and the moving direction of the roller 30 of the cam mechanism 22, the reaction force P0, and the first component force P1.
  • the operation of the cam mechanism 22 is the same except that the direction of the second component force P2 is different from that in FIG.
  • the force that suppresses the above torque fluctuations changes depending on the centrifugal force, that is, the rotational speed of the output side rotating body 12, and also changes depending on the rotational phase difference and the shape of the cam 31. Therefore, by setting the shape of the cam 31 as appropriate, the characteristics of the torque fluctuation suppressing device 14 can be optimized according to engine specifications and the like.
  • the shape of the cam 31 can be made such that the first component force P1 changes linearly according to the rotational phase difference in the state where the same centrifugal force is acting.
  • the shape of the cam 31 can be a shape in which the first component force P1 changes nonlinearly according to the rotational phase difference.
  • FIG. 8 is a diagram illustrating an example of torque fluctuation suppression characteristics.
  • the horizontal axis represents the rotational speed, and the vertical axis represents the torque fluctuation (rotational speed fluctuation).
  • the characteristic Q1 is a case where a device for suppressing torque fluctuation is not provided
  • the characteristic Q2 is a case where a conventional dynamic damper device is provided
  • the characteristic Q3 is a case where the torque fluctuation suppressing device 14 of the present embodiment is provided. Show.
  • centrifuge 21 For example, as shown in FIG. 6, when a rotational phase difference is generated between the output-side rotator 12 and the inertia ring 20, the centrifuge 21 has a force P 0 from the inertia ring 20 at the contact C 1 with the roller 30. Works. With this force P0, the first guide roller 26a attached to the centrifuge 21 and one side surface 121a of the projection 121 come into contact with each other at the contact C2, and the second guide roller 26b and the other side surface 121b of the projection 121 are in contact with each other. Abuts at the contact C3. That is, as shown in FIG.
  • the centrifuge 21 located above the plurality of centrifuges 21 falls downward.
  • the moving speed of the centrifuge 21 is suppressed by the hydraulic oil passing through the orifice Or as described above, the striking when the inner peripheral surface of the piston portion 21a of the centrifuge 21 collides with the bottom surface of the opening 121c. The sound can be suppressed.
  • the rotational phase difference between the inertia ring 20 and the output-side rotator 12 is set to a predetermined value.
  • the angle can be regulated. That is, a stopper mechanism can be realized. Furthermore, even if a stopper mechanism due to the collision of the members is provided separately, the hitting sound at the time of the collision of the members can be suppressed.
  • FIG. 9 shows a part of the torque fluctuation suppressing device according to the second embodiment of the present invention, and corresponds to FIG. 2 of the first embodiment.
  • FIG. 10 is a view seen from the direction B in FIG.
  • FIG. 9 shows the inertia ring removed from one side (front side in FIG. 9).
  • the torque fluctuation suppressing device 140 of the second embodiment is basically the same as that of the first embodiment, but mainly the shape of the output-side rotator, the configuration for supporting the centrifuge, and the movement restricting portion. The configuration is different.
  • inertia rings 201 and 202 constituting the mass body 20 are the same as those in the first embodiment. That is, the first and second inertia rings 201 and 202 are plates each having a predetermined thickness formed in a continuous annular shape, and are disposed so as to sandwich the output-side rotating body 120 and the centrifuge 210.
  • first and second inertia rings 201, 202 are fixed by the rivet 24, and the first inertia ring 201 is axially and radially oriented with respect to the second inertia ring 202. And immovable in the rotational direction.
  • a recess 120a that opens to the outer peripheral side is formed on the outer peripheral surface of the output-side rotator 120.
  • a protrusion 120b that protrudes from the bottom surface of the recess 120a by a predetermined height on the outer peripheral side is formed at the center in the circumferential direction of the recess 120a.
  • the centrifuge 210 is disposed in the recess 120a of the output-side rotator 120, and can be moved in the radial direction by the centrifugal force generated by the rotation of the output-side rotator 120.
  • the centrifuge 210 has grooves 210a and 210b at both ends in the circumferential direction.
  • the width of the grooves 210a and 210b is larger than the thickness of the output-side rotator 120, and the output-side rotator 120 is inserted into a part of the grooves 210a and 210b.
  • a hole 210c that is recessed toward the outer peripheral side is formed on the inner peripheral surface of the central portion in the circumferential direction (longitudinal direction) of the centrifuge 210.
  • the protrusion 120b of the output side rotating body 120 is inserted through a predetermined gap. That is, the hole 210c functions as a fluid storage unit capable of storing hydraulic oil, and the gap between the hole 210c and the protrusion 120b is an oil passage through which hydraulic oil flows, as in the first embodiment, that is, It functions as an orifice Or in which the cross-sectional area of the flow path through which the hydraulic oil passes is reduced.
  • the outer peripheral surface 210d of the centrifuge 210 is formed in an arc shape that is recessed toward the inner peripheral side, and functions as the cam 31 as in the first embodiment.
  • rollers 26a and 26b are disposed in the grooves 210a and 210b at both ends of the centrifuge 210, respectively.
  • the configuration of each roller 26a, 26b is the same as in the first embodiment.
  • Each of the rollers 26a and 26b can be brought into contact with the side surface of the recess 120a to roll.
  • the cam mechanism 220 is the same as that of the first embodiment, and includes a cylindrical roller 30 as a cam follower and a cam 31 formed on the outer peripheral surface 210d of the centrifuge 210. Further, the operation of the cam mechanism 220 is the same as that in the first embodiment.
  • torque fluctuation occurs, the rotational position between the output side rotating body 120 and the first and second inertia rings 201 and 202 is increased. A phase difference is generated, and torque fluctuation is suppressed by the action of the cam mechanism 220.
  • the configuration of the movement restricting unit that restricts the moving speed of the centrifuge 210 is basically the same as that of the first embodiment. Specifically, when a rotational phase difference occurs between the output-side rotating body 120 and the inertia rings 201 and 202, the centrifuge 210 moves radially inward by the operation of the cam mechanism 220. Due to the movement of the centrifuge 210, the hydraulic oil stored in the hole 210c is discharged through the orifice Or. At this time, the moving speed of the centrifuge 210 is suppressed by the resistance of the hydraulic oil passing through the orifice Or.
  • the inertia ring is constituted by a continuous annular member, but a plurality of divided inertia bodies may be arranged in the circumferential direction.
  • a holding member such as an annular holding ring on the outer peripheral side of the inertia body.
  • the guide roller is disposed as the guide portion, but another member that reduces friction such as a resin race or a sheet may be disposed.
  • the gap is used as the oil passage constituting the movement restricting portion, but other configurations may be adopted.
  • a hole penetrating in the radial direction may be formed in the piston portion 21a of the centrifuge 21.
  • FIG. 11 is a diagram schematically showing a torque converter, which includes an input-side rotating body 41, an output-side rotating body 42, and a damper provided between the rotating bodies 41 and 42. 43.
  • the input side rotating body 41 includes members such as a front cover, a drive plate, and a piston.
  • the output side rotating body 42 includes a driven plate and a turbine hub.
  • the damper 43 includes a plurality of torsion springs.
  • a centrifuge is provided in any of the rotating members that constitute the input-side rotator 41, and a cam mechanism 44 that operates using centrifugal force acting on the centrifuge is provided. It has been. About the cam mechanism 44, the structure similar to the structure shown by the said each embodiment is applicable.
  • the torque converter shown in FIG. 12 is provided with a centrifuge in any of the rotating members constituting the output-side rotator 42, and is a cam mechanism that operates by utilizing the centrifugal force acting on the centrifuge. 44 is provided. About the cam mechanism 44, the structure similar to the structure shown by the said each embodiment is applicable.
  • the torque converter shown in FIG. 13 has another damper 45 and an intermediate member 46 provided between the two dampers 43, 45 in addition to the configurations shown in FIGS. is doing.
  • the intermediate member 46 is relatively rotatable with the input side rotating body 41 and the output side rotating body 42, and causes the two dampers 43 and 45 to act in series.
  • the intermediate member 46 is provided with a centrifuge, and a cam mechanism 44 that operates using a centrifugal force acting on the centrifuge is provided.
  • a cam mechanism 44 that operates using a centrifugal force acting on the centrifuge is provided.
  • the structure similar to the structure shown by the said each embodiment is applicable.
  • the torque converter shown in FIG. 14 has a float member 47.
  • the float member 47 is a member for supporting the torsion spring constituting the damper 43, and is formed, for example, in an annular shape so as to cover the outer periphery and at least one side surface of the plurality of torsion springs.
  • the float member 47 is relatively rotatable with the input-side rotator 41 and the output-side rotator 42, and rotates around the damper 43 by friction with the plurality of torsion springs of the damper 43. That is, the float member 47 also rotates.
  • the float member 47 is provided with a centrifuge 48, and a cam mechanism 44 that operates using a centrifugal force acting on the centrifuge 48 is provided.
  • a cam mechanism 44 that operates using a centrifugal force acting on the centrifuge 48 is provided.
  • the structure similar to the structure shown by the said each embodiment is applicable.
  • FIG. 15 is a schematic diagram of a power transmission device having a flywheel 50 having two inertia bodies 51 and 52 and a clutch device 54.
  • the flywheel 50 disposed between the engine and the clutch device 54 includes a first inertial body 51, a second inertial body 52 disposed so as to be rotatable relative to the first inertial body 51, and two inertial bodies. And a damper 53 disposed between 51 and 52.
  • the second inertia body 52 also includes a clutch cover that constitutes the clutch device 54.
  • a centrifuge is provided in any of the rotating members that constitute the second inertial body 52, and a cam mechanism 55 that operates using a centrifugal force acting on the centrifuge is provided. ing.
  • the cam mechanism 55 the same configuration as that shown in each of the above embodiments can be applied.
  • FIG. 16 is an example in which a centrifuge is provided in the first inertial body 51 in the same power transmission device as in FIG.
  • a cam mechanism 55 that operates using centrifugal force acting on the centrifuge is provided.
  • the cam mechanism 55 the same configuration as that shown in each of the above embodiments can be applied.
  • the power transmission device shown in FIG. 17 includes another damper 56 and an intermediate member 57 provided between the two dampers 53, 56. Have.
  • the intermediate member 57 is rotatable relative to the first inertial body 51 and the second inertial body 52.
  • the intermediate member 57 is provided with a centrifuge 58, and a cam mechanism 55 that operates using a centrifugal force acting on the centrifuge 58 is provided.
  • the cam mechanism 55 the same configuration as that shown in each of the above embodiments can be applied.
  • FIG. 18 is a schematic diagram of a power transmission device in which a clutch device is provided on one flywheel.
  • the first inertia body 61 in FIG. 18 includes one flywheel and a clutch cover of the clutch device 62.
  • a centrifuge is provided in any of the rotating members constituting the first inertial body 61, and a cam mechanism 64 that operates by utilizing a centrifugal force acting on the centrifuge is provided.
  • the cam mechanism 64 the structure similar to the structure shown by the said each embodiment is applicable.
  • FIG. 19 is an example in which a centrifuge 65 is provided on the output side of the clutch device 62 in the same power transmission device as FIG.
  • a cam mechanism 64 that operates by utilizing the centrifugal force acting on the centrifuge 65 is provided.
  • the structure similar to the structure shown by the said each embodiment is applicable.
  • the torque fluctuation suppressing device of the present invention may be disposed on any of the rotating members constituting the transmission, and further, the shaft (propeller shaft or drive) on the output side of the transmission (Shaft).
  • the torque fluctuation suppressing device of the present invention may be further applied to a conventionally known dynamic damper device or a power transmission device provided with a pendulum type damper device.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Transmission Devices (AREA)

Abstract

La présente invention a pour but de supprimer un pic de fluctuation de couple sur une plage de vitesse de rotation relativement large dans un dispositif qui permet de supprimer les fluctuations de couple d'un élément rotatif. Pour atteindre ce but, l'invention concerne un dispositif qui est équipé d'un corps de masse (20), d'un élément centrifuge (21), d'un mécanisme (22) à came et d'une pièce de limitation de mouvement. Le corps de masse (20) peut tourner par rapport à un corps rotatif (12) côté sortie. L'élément centrifuge (21) est porté par le corps rotatif (12) côté sortie et peut se déplacer dans la direction radiale. Le mécanisme (22) à came possède une came (31) et un rouleau (30), reçoit une force centrifuge agissant sur l'élément centrifuge (21), et, lorsqu'une différence de phase de rotation est produite entre le corps rotatif (12) côté sortie et le corps de masse (20), convertit la force centrifuge en une force de direction circonférentielle dans la direction qui diminue le déplacement relatif. La pièce de restriction de mouvement possède un orifice (Or) pouvant faire circuler un fluide de travail en fonction du mouvement de l'élément centrifuge (21) dans la direction radiale, et limite la vitesse du mouvement de l'élément centrifuge (21) vers l'intérieur dans la direction radiale.
PCT/JP2017/020880 2016-07-20 2017-06-05 Dispositif de suppression de fluctuation de couple, convertisseur de couple et dispositif de transmission de force motrice Ceased WO2018016212A1 (fr)

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JP2016142113A JP2018013153A (ja) 2016-07-20 2016-07-20 トルク変動抑制装置、トルクコンバータ、及び動力伝達装置

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CN111692284A (zh) * 2019-03-13 2020-09-22 株式会社艾科赛迪 扭矩波动抑制装置及扭矩转换器

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JP2019138421A (ja) * 2018-02-14 2019-08-22 株式会社エクセディ トルク変動抑制装置、トルクコンバータ、及び動力伝達装置
JP6764430B2 (ja) 2018-02-21 2020-09-30 株式会社エクセディ トルク変動抑制装置、トルクコンバータ、及び動力伝達装置
JP7144165B2 (ja) * 2018-03-20 2022-09-29 株式会社エクセディ 動力伝達装置
JP7144166B2 (ja) * 2018-03-20 2022-09-29 株式会社エクセディ 動力伝達装置
JP6682572B2 (ja) * 2018-05-23 2020-04-15 株式会社エクセディ トルク変動抑制装置
JP2019218957A (ja) 2018-06-15 2019-12-26 株式会社エクセディ トルク変動抑制装置

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JP2011099490A (ja) * 2009-11-05 2011-05-19 Toyota Motor Corp 捩り振動低減装置
JP2014516142A (ja) * 2011-05-31 2014-07-07 ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフト 車両用の駆動システム
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JPH1182628A (ja) * 1997-09-12 1999-03-26 Exedy Corp ダイナミックダンパー及びフライホイール組立体
JP2011099490A (ja) * 2009-11-05 2011-05-19 Toyota Motor Corp 捩り振動低減装置
JP2014516142A (ja) * 2011-05-31 2014-07-07 ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフト 車両用の駆動システム
JP2014145413A (ja) * 2013-01-29 2014-08-14 Toyota Motor Corp 捩り振動減衰装置

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CN111692284B (zh) * 2019-03-13 2023-06-30 株式会社艾科赛迪 扭矩波动抑制装置及扭矩转换器

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