WO2014108951A1 - Dispositif d'amortissement de vibration de torsion - Google Patents

Dispositif d'amortissement de vibration de torsion Download PDF

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Publication number
WO2014108951A1
WO2014108951A1 PCT/JP2013/006862 JP2013006862W WO2014108951A1 WO 2014108951 A1 WO2014108951 A1 WO 2014108951A1 JP 2013006862 W JP2013006862 W JP 2013006862W WO 2014108951 A1 WO2014108951 A1 WO 2014108951A1
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WO
WIPO (PCT)
Prior art keywords
rotating member
elastic body
flywheel
torsional vibration
auxiliary elastic
Prior art date
Application number
PCT/JP2013/006862
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English (en)
Japanese (ja)
Inventor
徹宏 竹中
一成 稲田
Original Assignee
トヨタ自動車株式会社
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Filing date
Publication date
Application filed by トヨタ自動車株式会社 filed Critical トヨタ自動車株式会社
Publication of WO2014108951A1 publication Critical patent/WO2014108951A1/fr

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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
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs

Definitions

  • the present invention relates to a torsional vibration reducing device.
  • a main plate to which rotational torque is transmitted from an engine as a drive source, a control plate, and a flange for transmitting rotational torque to an input shaft of a transmission are relatively rotated in the circumferential direction.
  • a strong elastic body is incorporated to elastically deform between the main plate and control plate and the flange, and a weak elastic body is incorporated to elastically deform between the control plate and the flange.
  • the weak elastic body is compressed from a state where the twist angle between the control plate and the flange is 0 ° to a predetermined value, and the strong elastic body is compressed when the twist angle between the control plate and the flange exceeds the predetermined value. It has come to be.
  • the torsional rigidity is high because the reaction force of the strong elastic body is large in a specific high torque region where the rotational speed of the drive source is exclusively 2000 to 3000 rpm. Torsional vibration is likely to increase, and noise and vibration of a vehicle equipped with this device may increase. Therefore, for example, when it is required to employ an engine whose rotational fluctuation increases due to downsizing, the number of cylinders, etc., or to suppress vibrations and noise such as booming noise, etc. I could't respond enough.
  • the present invention adjusts the torsional rigidity in the high torque region, increases the torsional rigidity in the high torque region, and suppresses the increase in the torsional rigidity in the specific high torque region, thereby torsional vibration in the high torque region.
  • An object of the present invention is to provide a torsional vibration reducing device capable of reducing the above.
  • the torsional vibration reduction device includes a first rotating member to which rotational torque is transmitted from a driving source, and a second rotation that is disposed relatively rotatably on the first rotating member.
  • a main elastic body that is interposed between the first rotating member and the second rotating member and elastically deforms in accordance with relative rotation between the first rotating member and the second rotating member.
  • a torsional vibration reducing device configured to transmit rotational torque from the second rotating member to the drive transmission system, and interposed between the first rotating member and the second rotating member.
  • an auxiliary elastic body having one end connected to the second rotating member, wherein the auxiliary elastic body and the first rotating member are connected to the first rotating member and the second rotating member.
  • the first rotating member When the twist angle exceeds a predetermined value, the first rotating member is The other end portion of the auxiliary elastic body is pushed in the first rotation as the twisting angle between the first rotating member and the second rotating member is increased. It is comprised so that it may move toward the radial direction outer side of a member.
  • the other end of the auxiliary elastic body is moved to the first rotation. It moves toward the outside in the radial direction of the member.
  • the reaction force acting on the first rotating member from the auxiliary elastic body can be made different from the reaction force when the other end of the auxiliary elastic body is simply pressed in the circumferential direction. It can be reduced according to the amount of movement of the other end.
  • the reaction force of the main elastic body and the reaction force of the auxiliary elastic body corresponding to the torsion angle are generated in the high torque region, and the torsional rigidity is increased as compared with the case of only the reaction force of the main elastic body.
  • an increase in torsional rigidity can be suppressed by reducing the reaction force of the auxiliary elastic body below the reaction force according to the torsion angle.
  • the torsional vibration reduction device includes a first rotating member to which rotational torque is transmitted from a driving source, and a second rotation that is disposed relatively rotatably on the first rotating member.
  • a main elastic body that is interposed between the first rotating member and the second rotating member and elastically deforms in accordance with relative rotation between the first rotating member and the second rotating member.
  • a torsional vibration reducing device configured to transmit rotational torque from the second rotating member to the drive transmission system, and interposed between the first rotating member and the second rotating member.
  • an auxiliary elastic body having one end connected to one of the first rotating member and the second rotating member, and the first rotating member and the second rotating member.
  • the first The other rotating member and the second rotating member press the other end of the auxiliary elastic body, and the other end of the auxiliary elastic body increases as the twist angle increases.
  • You may comprise so that a part may move toward the radial direction outer side of a said 1st rotation member.
  • the other end portion of the auxiliary elastic body is the first rotating member.
  • the reaction force acting on the other rotating member from the auxiliary elastic body changes according to the amount of movement of the other end of the auxiliary elastic body.
  • the reaction force of the auxiliary elastic body corresponding to the torsion angle is generated in the high torque region to increase the torsional rigidity compared to the case of using only the reaction force of the main elastic body, while the auxiliary elastic body is assisted in a specific high torque region.
  • An increase in torsional rigidity can be suppressed by reducing the reaction force of the elastic body below the reaction force according to the torsion angle, and it becomes possible to reduce torsional vibration and avoid resonance in a specific high torque region.
  • the auxiliary elastic body is supported by the one rotating member so as to be rotatable in the radial direction on the one end side, and the auxiliary elastic body is provided on the one rotating member. And an inclined guide portion extending in the rotational direction and the radial direction of the one rotating member is provided, and the other end portion of the auxiliary elastic body is provided by the other rotating member. When pressed in the increasing direction of the twist angle, the other end portion of the auxiliary elastic body may move outward in the pressing direction and the radial direction.
  • the torsional rigidity between the first rotating member and the second rotating member increases in accordance with the reaction force of the auxiliary elastic body within the torsional angle range in which the torsional angle exceeds a predetermined value.
  • the other end of the elastic body moves outward in the radial direction, an increase in torsional rigidity can be suppressed.
  • the auxiliary elastic body is, for example, a cylindrical compression coil spring
  • the torsional rigidity is increased by the reaction force generated by the compression of the auxiliary elastic body in addition to the reaction force of the main elastic body, while the auxiliary elastic body
  • the one end portion moves radially outward from the other end portion of the auxiliary elastic body, an increase in the reaction force of the auxiliary elastic body is suppressed, and the torsional rigidity is appropriately reduced.
  • the auxiliary elastic body has a supporting sheet at the one end and a pressing sheet at the other end, and the one rotating member includes the one rotating member.
  • Guide grooves extending in the rotation direction and the radial direction are formed, and the support sheet has support pins parallel to the rotation center axes of the first rotation member and the second rotation member, and is centered on the support pins.
  • the pressing sheet is connected to the one rotating member so as to rotate in the direction, and has a guide member that fits into the guide groove, and may be configured to move along the guide groove by the guide member.
  • the torsional vibration reduction device of the present invention connects the support sheet to one rotating member so as to rotate around the support pin, and moves the guide member along the guide groove.
  • the pressing sheet at the other end of the auxiliary elastic body moves reliably in the radial direction of the other rotating member.
  • the other rotating member has a protruding portion protruding outward in the radial direction, and the torsion angle has the predetermined value at the other end of the auxiliary elastic body.
  • a contact member that is in contact with the protruding portion of the other rotating member is mounted, and the other end portion of the auxiliary elastic body when the twist angle exceeds a specific twist angle greater than the predetermined value.
  • the contact member may change a contact posture with respect to the other rotation member so that the contact member is moved outward in the radial direction.
  • the abutting member abuts against a base end portion supported by the other end portion of the auxiliary elastic body and the projecting portion of the other rotating member when the twist angle exceeds the predetermined value.
  • a parallel guide portion extending from the corresponding contact portion toward the protruding portion side of the other rotating member and slidably engaging with the protruding portion on both sides in the rotation center axis direction of the other rotating member; It may have.
  • the other end portion of the auxiliary elastic body is stably held by the other rotating member via the contact member while being movable in the radial direction, which is advantageous in terms of vibration and noise. .
  • the reaction force of the auxiliary elastic body is generated in the high torque region to increase the torsional rigidity, and in the specific high torque region, the torsional rigidity is increased by moving the auxiliary elastic body to the outer side in the radial direction. It is possible to provide a torsional vibration reduction device that can suppress an increase and can reduce torsional vibration in a high torque region.
  • FIG. 2 is a cross-sectional view taken along the line AA of the torsional vibration reducing device according to the first embodiment shown in FIG. It is a diagram which shows the relationship between the twist angle and torque of the torsional vibration reduction apparatus which concerns on the 1st Embodiment of this invention. It is operation
  • FIG. 6 is a cross-sectional view of the torsional vibration reducing device according to the second embodiment shown in FIG.
  • FIG. 9A It is a perspective view of the support component which supports the base end part of the auxiliary
  • the torsional vibration reducing device As shown in FIGS. 1 and 2, the torsional vibration reducing device according to the present embodiment is a flywheel 1 and is interposed between an engine crankshaft 2 and a clutch mechanism 3.
  • the flywheel 1 includes a primary flywheel 10 that is a first rotating member, a secondary flywheel 20 that is a second rotating member, a main spring 30 that is a main elastic body, and an auxiliary spring 40 that is an auxiliary elastic body. It is configured.
  • the primary flywheel 10 has an annular boss 11 and a plurality of projecting portions 12 projecting radially outward from the boss 11.
  • the boss 11 is connected to a crankshaft 2 of an engine that is a drive source, and the primary flywheel 10 rotates together with the crankshaft 2.
  • the protrusions 12 are positioned at equal intervals in the circumferential direction of the boss 11, and the member thickness dimension T of the protrusion 12 is formed to be smaller than the dimension L of the boss 11 in the axial direction.
  • the secondary flywheel 20 includes a first disk 21 disposed on the engine side of the primary flywheel 10 and a second disk 22 disposed on the clutch side of the primary flywheel 10. It is located on the same axis.
  • the first disk 21 is formed in an annular shape so as to cover the engine side surface of the protrusion 12 with respect to the primary flywheel 10 and surround the end of the boss 11 on the engine side in the circumferential direction so as to store the protrusion 12. Has been.
  • the second disc 22 covers the clutch-side surface of the protrusion 12 with respect to the primary flywheel 10 and surrounds the end of the boss 11 on the clutch side in the circumferential direction so as to store the protrusion 12 in an annular shape. Has been.
  • a first bearing 23 is fitted between the inner periphery of the first disk 21 and the outer periphery of the boss 11, and between the inner periphery of the second disk 22 and the outer periphery of the boss 11.
  • the second bearing 24 is fitted. Further, the first disk 21 and the second disk 22 are fastened together by bolts 25.
  • the first bearing 23 and the second bearing 24 play a role of coaxially positioning the primary flywheel 10 and the secondary flywheel 20, and the primary flywheel 10 and the secondary flywheel 20 are the first bearings. 23 and the second bearing 24 can be rotated relative to each other.
  • a known clutch mechanism 3 is attached to the second disk 22.
  • the clutch mechanism 3 includes a clutch disk 301, a clutch cover 302, a pressure plate 303, a diaphragm spring 304, a release bearing 305, a release fork 306, and the like.
  • the clutch mechanism 3 plays a role of transmitting the rotation of the secondary flywheel 20 to the input shaft 4 of a known transmission or blocking the transmission, and a known differential device, a drive shaft, wheels, and the like.
  • a drive transmission system of the vehicle is configured.
  • the main spring 30 is a compression coil spring that extends in the circumferential direction of the secondary flywheel 20, and is disposed inside the secondary flywheel 20, that is, in a space 26 surrounded by the first disk 21 and the second disk 22. ing.
  • the main spring 30 has a non-linear corresponding to the torsion characteristic of the solid line until reaching the predetermined torsion angle ⁇ 1 and the torsion characteristic indicated by the two-dot chain line of the torsion angle ⁇ 1 or more. It has a spring characteristic and is constituted by a combination spring in which a plurality of types of coil springs are combined so that the torsion angles at which reaction forces start to be generated are different from each other. That is, in this embodiment, the torsional rigidity when the torsional angle becomes equal to or larger than ⁇ 1 is increased with respect to the torsional rigidity until the predetermined torsional angle ⁇ 1 is reached only by the reaction force of the main spring 30. The required torsional vibration reducing action and torque response can be obtained.
  • the main spring 30 as the main elastic body referred to in the present invention may be one type of coil spring having non-linear spring characteristics, or may be constituted by one type of linear coil spring.
  • One end portion of the main spring 30 is in contact with the protruding portion 12.
  • the other end of the main spring 30 is engaged with an engagement portion (not shown) formed on the secondary flywheel 20 so as to be positioned in the space 26. That is, the main spring 30 is interposed between the protruding portion 12 of the primary flywheel 10 and the engaging portion of the secondary flywheel 20 in a pre-compressed state.
  • the engaging portions referred to here protrude into the space 26 with the protruding portion 12 sandwiched between the circumferential portions of the secondary flywheel 20.
  • other engaging portions such as projecting engaging portions 21 a and 22 a are also provided on one end portion side of the main spring 30.
  • the main spring 30 is compressed in advance between the two engaging portions so that the end portion position of the main spring 30 is maintained on the side where the protruding portion 12 is separated. In this state, one end of the main spring 30 is engaged with the protrusion 12.
  • the main spring 30 is, for example, when the primary flywheel 10 is twisted to the acceleration side R1 with respect to the secondary flywheel 20 due to an increase in the rotational speed of the crankshaft 2 of the engine during acceleration of the vehicle or when the vehicle is decelerated. Due to the decrease in the rotational speed of the crankshaft 2 of the engine, the primary flywheel 10 is compressed in any case where the secondary flywheel 20 is twisted to the deceleration side R2.
  • the rotational torque of the wheels is transferred from the drive shaft, the differential, the transmission, etc. to the crankshaft 2 via the input shaft 4, the clutch mechanism 3, the secondary flywheel 20, the main spring 30, and the primary flywheel 10.
  • the torsional vibration is absorbed between the primary flywheel 10 and the secondary flywheel 20 by the elastic deformation of the main spring 30.
  • the flywheel 1 is characterized in that, in addition to the main spring 30, an auxiliary spring 40 is provided in parallel to the main spring 30 between the primary flywheel 10 and the secondary flywheel 20, and the auxiliary spring One end of 40 is supported by the secondary flywheel 20 (one rotating member) so as to be rotatable in the radial direction.
  • the characteristic part of the flywheel 1 according to the present embodiment is that when the twist angle between the primary flywheel 10 and the secondary flywheel 20 exceeds a predetermined value, the primary flywheel 10 (the other rotating member) The protrusion 12 is configured to press the other end of the auxiliary spring 40.
  • the characteristic part of the flywheel 1 according to the present embodiment is that after the twist angle between the primary flywheel 10 and the secondary flywheel 20 exceeds a predetermined value, the auxiliary spring 40 is increased or decreased according to the increase or decrease of the twist angle.
  • the other end is configured to move in the radial direction of the primary flywheel 10.
  • the auxiliary spring 40 is a compression coil spring that extends in the circumferential direction of the secondary flywheel 20, and is located in the space 26 inside the secondary flywheel 20 on the radially inner side of the secondary flywheel 20 relative to the main spring 30. Is arranged.
  • a support sheet 41 is attached to one end of the auxiliary spring 40, and a pressing sheet 42 is attached to the other end of the auxiliary spring 40. And the front-end
  • a support pin 43 parallel to the rotation center axis of the flywheel 1 is attached to the support sheet 41, and a guide member 44 parallel to the rotation center axis of the flywheel 1 is attached to the pressing sheet 42.
  • the support sheet 41 is connected to the first disk 21 and the second disk 22 by a support pin 43 and is configured to rotate around the support pin 43.
  • the mounting position of the support pin 43 with respect to the first disk 21 and the second disk 22 is set so that the pressing sheet 42 is interposed between the support pin 43 and the protruding portion 12.
  • the mounting positions of the support pins 43 and the guide members 44 with respect to the first disk 21 and the second disk 22 are such that when the twist angle between the primary flywheel 10 and the secondary flywheel 20 is 0 °, the pressing sheet 42. Is set to be spaced from the protrusion 12.
  • the mounting position of the support pin 43 and the guide member 44 with respect to the first disk 21 and the second disk 22 has a predetermined twist angle between the primary flywheel 10 and the secondary flywheel 20 (hereinafter also simply referred to as a twist angle).
  • a twist angle between the primary flywheel 10 and the secondary flywheel 20
  • the first disk 21 and the second disk 22 are formed with concave grooves facing each other so that the other end of the auxiliary spring 40 can move toward the radially outer side of the primary flywheel 10. Has been.
  • the guide groove 45 is located between the support pin 43 and the protrusion 12 and extends in the radial direction of the secondary flywheel 20.
  • a guide member 44 is fitted in the guide groove 45 so as to move along the guide groove 45.
  • the guide member 44 and the guide groove 45 constitute an inclined guide portion that is inclined with respect to the radial direction so as to extend in the rotational direction and the radial direction of the secondary flywheel 20.
  • the shape and position of the guide groove 45 are set so that the pressing sheet 42 is spaced from the protrusion 12 when the twist angle between the primary flywheel 10 and the secondary flywheel 20 is 0 °.
  • the shape and the position of the guide groove 45 are such that when the twist angle between the primary flywheel 10 and the secondary flywheel 20 exceeds a predetermined value, the protrusion 12 contacts the pressing sheet 42 and the protrusion 12 The auxiliary spring 40 is set to be pressed through the pressing sheet 42.
  • the shape of the guide groove 45 is such that after the twist angle between the primary flywheel 10 and the secondary flywheel 20 exceeds a predetermined value, the pressing sheet 42 is guided by the guide member 44 as the twist angle increases. It is set to move radially outward of the primary flywheel 10.
  • the rotational torque of the engine is increased to the crankshaft 2 and the primary flywheel. It is transmitted from the wheel 10, the main spring 30, the secondary flywheel 20, the clutch mechanism 3, and the input shaft 4 to the wheels via a transmission, a differential device, a drive shaft, and the like. At this time, the main spring 30 is elastically deformed, and rotational fluctuation is absorbed between the primary flywheel 10 and the secondary flywheel 20 or the impact torque is relieved, and torsional vibration is reduced.
  • the main spring 30 is torsionally vibrated while being compressed according to the torsion angle between the primary flywheel 10 and the secondary flywheel 20 as described above, both when the vehicle is accelerated and when the vehicle is decelerated.
  • the reduction effect is exerted and the main spring 30 is compressed by a predetermined amount, the protruding portion 12 of the primary flywheel 10 contacts the pressing sheet 42 at the other end of the auxiliary spring 40.
  • the protrusion 12 compresses the auxiliary spring 40 via the pressing sheet 42.
  • the torsional rigidity between the primary flywheel 10 and the secondary flywheel 20 is increased by the amount by which the auxiliary spring 40 is compressed, and required torque response (so-called drivability characteristics) is ensured.
  • the torsional rigidity referred to here is the magnitude (N ⁇ m / rad) of torque (N ⁇ m) required to cause a torsion of a unit torsion angle (rad) between the primary flywheel 10 and the secondary flywheel 20. ).
  • the rotational torque of the engine is transmitted from the primary flywheel 10 to the secondary flywheel 20 selectively by the auxiliary spring 40 in addition to the main spring 30.
  • the necessary torsional vibration reduction action and torque response between the primary flywheel 10 and the secondary flywheel 20 are obtained according to the elastic deformation of the main spring 30 and the auxiliary spring 40.
  • the rotational torque of the wheels is transmitted from the secondary flywheel 20 to the primary flywheel 10 selectively by the auxiliary spring 40 in addition to the main spring 30. Also at this time, the necessary torsional vibration reduction action and torque response between the primary flywheel 10 and the secondary flywheel 20 are obtained according to the elastic deformation of the main spring 30 and the auxiliary spring 40.
  • the pressing sheet 42 at the other end of the auxiliary spring 40 has the guide member 44 as the torsion angle increases after the torsion angle of the primary flywheel 10 and the secondary flywheel 20 exceeds a predetermined value. Since the guide groove 45 guides, the primary flywheel 10 moves outward in the radial direction.
  • the increasing rate of the reaction force acting on the primary flywheel 10 from the auxiliary spring 40 becomes smaller in accordance with the movement amount of the pressing sheet 42, that is, the rotation amount of the auxiliary spring 40 around the support pin 43.
  • the reaction force F ⁇ b> 1 acting on the protruding portion 12 from the auxiliary spring 40 at the contact position of the protruding portion 12 and the pressing sheet 42 compresses the auxiliary spring 40 as the torsion angle increases.
  • the reaction force component that contributes to the torsional rigidity due to the reaction force of the auxiliary spring 40 by changing the direction of the reaction force applied from the auxiliary spring 40 to the protruding portion 12 Changes from F1 ⁇ cos ⁇ a to F2 ⁇ cos ⁇ b.
  • the torsional rigidity and torsional characteristics in the high torque region can be adjusted by appropriately setting the position and mode of engagement between the pressing sheet 42 and the protruding portion 12.
  • the rigidity ⁇ (Nm / rad) and the low torsional rigidity ⁇ (Nm / rad) after reaching the specific torque region Z1 can be realized.
  • the reaction force of the auxiliary spring 40 is compressed in advance when the auxiliary spring 40 is incorporated. Get up to the reaction force of the minute.
  • the main spring 30 has a non-linear spring characteristic having a torsion characteristic indicated by a two-dot chain line in FIG. 3 when the torsion angle ⁇ 1 or more. Therefore, when the torsion angle becomes equal to or larger than ⁇ 1 and the auxiliary spring 40 starts to be compressed in the substantially circumferential direction, a high torsional rigidity ⁇ is generated before reaching the specific torque region Z1 in FIG.
  • the pressing sheet 42 at the other end of the auxiliary spring 40 has a twist angle in a state where the twist angle between the primary flywheel 10 and the secondary flywheel 20 exceeds a predetermined value. When it decreases, it moves toward the radially inner side of the primary flywheel 10 together with the pressing sheet 42 as the twist angle becomes smaller.
  • the flywheel 1 when the rotational torque of the engine is low, the flywheel 1 according to the present embodiment causes rotational fluctuations between the primary flywheel 10 and the secondary flywheel 20 due to the rigidity of the main spring 30 alone. Reduce torsional vibrations by absorbing or mitigating impact torque.
  • the auxiliary spring 40 When the torsion angle between the primary flywheel 10 and the secondary flywheel 20 exceeds ⁇ 1 or ⁇ 2, the auxiliary spring 40 is compressed by the protruding portion 12, so that the auxiliary spring 40 is elastically deformed together with the main spring 30.
  • the flywheel 1 when the rotational torque of the engine becomes high, the flywheel 1 according to the present embodiment is in a highly rigid state that compresses both the main spring 30 and the auxiliary spring 40, and the rigidity makes the primary flywheel 1 The required torque responsiveness with respect to the input rotational torque is ensured while the torsional vibration can be reduced between the secondary flywheel 20 and the secondary flywheel 20.
  • the increasing rate of the reaction force that acts on the primary flywheel 10 from the auxiliary spring 40 depends on the amount of movement of the pressing sheet 42, that is, the amount of rotation of the auxiliary spring 40 around the support pin 43. Get smaller. Therefore, as shown in FIG. 3, in the high torque region exceeding the torsion angles ⁇ 1 and ⁇ 2, the specific torque region Z1 in which the torsional rigidity ⁇ is increased until reaching the specific torque regions Z1 and Z2, and the torque becomes higher than that. , Z2 can be suppressed to a low torsional rigidity ( ⁇ ⁇ ) smaller than the torsional rigidity ⁇ .
  • the auxiliary spring 40 becomes the projecting portion 12.
  • the torsion angles ⁇ 1 and ⁇ 2 between the primary flywheel 10 and the secondary flywheel 20 when starting to be compressed can be adjusted.
  • the flywheel 1 has a torsional rigidity between the primary flywheel 10 and the secondary flywheel 20 in the specific high rotational torque regions Z1 and Z2 as compared with the conventional one. Reduction can be achieved, so that noise and vibration do not need to be increased.
  • the flywheel 1 connects the support sheet 41 to the secondary flywheel 20 so as to rotate around the support pin 43, and moves the guide member 44 along the guide groove 45. Therefore, the pressing sheet 42 at the other end of the auxiliary spring 40 can be reliably moved in the radial direction of the primary flywheel 10.
  • the primary flywheel 10 has a plurality of protrusions 12, and the secondary flywheel 20 accommodates the plurality of protrusions 12 in the boss 11 of the primary flywheel 10.
  • the first bearing 23 and the second bearing 24 are rotatably coupled to each other.
  • the one end part of the auxiliary spring 40 was supported by the secondary flywheel 20 via the support sheet 41 and the support pin 43 so that rotation in the radial direction was possible.
  • the rotating member on the driving side and the rotating member on the driven side when the torsional vibration is reduced by an elastic body such as a coil spring are not limited to the forms such as the primary flywheel 10 and the secondary flywheel 20.
  • assistant spring be rotatably supported by the rotary body of a drive side in the radial direction.
  • FIGS. 5 and 6 show a second embodiment in which one end of the auxiliary spring is supported by the driving-side rotating member so as to be rotatable in the radial direction.
  • the same or similar components as those in the first embodiment are denoted by the reference numerals of corresponding components shown in FIGS. 6 and FIG. 6, the following description will be made on differences of the present embodiment from the first embodiment.
  • the torsional vibration reducing device includes different types of springs having different compression start timings interposed in parallel between a first rotating member and a second rotating member. As shown in FIG. 6, the flywheel 51 is mounted between the crankshaft 2 and the clutch mechanism 3.
  • the clutch mechanism 3 in the present embodiment is a so-called CSC provided with an annular slave cylinder 308 that is coaxially arranged with respect to the input shaft 4 of the transmission, instead of the release fork 306 in the first embodiment. (Concentric slave cylinder) system, and the release cylinder 305 is directly moved by the slave cylinder 308.
  • the clutch mechanism 3 includes a spring 307, a hydraulic pipe 309, and the like.
  • the flywheel 51 of the present embodiment is a so-called dual mass flywheel, which is a primary flywheel 60 that is a first rotating member, a secondary flywheel 70 that is a second rotating member, and a main elastic body.
  • One and the other arc springs 80L and 80R, at least one auxiliary spring 90 which is an auxiliary elastic body, and the like are included.
  • the primary flywheel 60 includes a primary wheel main body 61, a disc-shaped cover 62 and a pressing plate 63.
  • the primary wheel main body 61 includes a concave body portion 61a having a concave shape capable of accommodating the arc springs 80L and 80R, a substantially annular plate-like cover portion 61b supported by the outer peripheral portion on the opening side of the concave body portion 61a, and the illustrated figure.
  • the ring gear portion 61c used at the time of starting by the starter motor that is not connected is integrally coupled.
  • the primary wheel main body 61 has a substantially annular annular guide surface 61e that holds the arc springs 80L and 80R together with the concave body portion 61a in an arcuate state and that can be extended and contracted in the rotation direction, and an inner side from the guide surface 61e.
  • the disc-shaped cover 62 has a substantially disc shape that closes the plurality of work holes 61h on the back side of the primary wheel main body 61, and the end of the crankshaft 2 is inserted in the center thereof.
  • the pressing plate 63 includes a short cylindrical fitting portion 63a fitted between the inner periphery of the primary wheel main body 61 and the outer periphery of the end portion of the crankshaft 2, and an annular holding member formed integrally with the fitting portion 63a. And a plate portion 63b.
  • the primary wheel main body 61, the cover 62, and the pressing plate 63 are positioned and coupled to the flange portion 2 f of the crankshaft 2 by a plurality of bolts 64 and positioning pins 65 so that the center of rotation coincides with the crankshaft 2. Yes.
  • the secondary flywheel 70 includes a secondary flywheel main body 71 arranged coaxially with respect to the primary wheel main body 61, and a flange 72 positioned on the inner side of the primary wheel main body 61 while being supported by the secondary flywheel main body 71. .
  • the secondary flywheel main body 71 is rotatably supported by a pressing plate 63 of the primary wheel main body 61 via a bearing 66 on the inner peripheral side.
  • the secondary flywheel main body 71 has a clutch mechanism 3 on one side of the outer peripheral portion of the secondary flywheel main body 71.
  • the clutch cover 302 is bolted.
  • the flange 72 includes an annular plate portion 72a that is integrally fastened to the secondary flywheel main body 71 by a plurality of bolts 74 and press-fit pins 75, and an equal angular interval radially outward (outside in the radial direction) from the annular plate portion 72a.
  • a plurality of protruding portions for example, a pair of protruding portions 72b are provided.
  • the protrusions 72b of the flanges 72 are disposed in the vicinity of the center surfaces of the arc springs 80L and 80R in the direction of the rotation center axis of the flywheel 51.
  • the arc springs 80L and 80R are compression coil springs held in an arc shape between a plurality of pairs of spring receiving projecting engaging portions 61f and 61g of the primary wheel main body 61, respectively.
  • the primary flywheel 60 and the secondary flywheel When the 70 rotates relative to each other, the projection 72b of the flange 72 is pressurized and compressed from one end side.
  • the arc springs 80L and 80R are assembled with a predetermined spring length and an assembling load while being held in an arc shape between the plurality of pairs of spring receiving projecting engaging portions 61f and 61g in the primary wheel main body 61. ing.
  • the arc springs 80L and 80R have different torsion angles at which reaction forces start to be generated so as to have the same torsional characteristics as the torsional characteristics of the first embodiment shown in FIG.
  • the arc springs 80L and 80R as the main elastic body according to the present invention may be one type of coil spring having non-linear spring characteristics, or may be constituted by one type of linear coil spring. May be.
  • the arc springs 80L and 80R can be applied to the crankshaft during vehicle deceleration even when the primary flywheel 60 is twisted to the acceleration side R1 with respect to the secondary flywheel 70 due to an increase in the rotational speed of the crankshaft 2 during vehicle acceleration. Even when the primary flywheel 60 is twisted to the deceleration side R2 with respect to the secondary flywheel 70 due to the decrease in the rotational speed of 2, the compression is performed. Further, the compression amount of the arc springs 80L and 80R increases in proportion to the twist angle between the primary flywheel 60 and the secondary flywheel 70.
  • the auxiliary spring 90 is formed of a cylindrical compression coil spring, and one end 91 of the auxiliary spring 90 is a primary flywheel that is a rotating member of either the primary flywheel 60 or the secondary flywheel 70. 60 is supported so as to be rotatable in the radial direction.
  • the other end 92 of the auxiliary spring 90 is either the primary flywheel 60 or the secondary flywheel 70 when the twist angle between the primary flywheel 60 and the secondary flywheel 70 exceeds a predetermined value ⁇ 1. Is engaged with a secondary flywheel 70 which is a rotating member of the first rotary member so as to be movable in the radial direction.
  • a support sheet 93 is attached to one end 91 of the auxiliary spring 90, and the support sheet 93 is parallel to the rotation center axis of the flywheel 51 as shown in FIGS. 9A and 9B.
  • a support pin 93a is rotatably mounted.
  • the support sheet 93 is connected to the primary wheel main body 61 so as to be rotatable in the radial direction by a support pin 93a, and the one end 91 of the auxiliary spring 90 is rotated in the radial direction of the primary wheel main body 61 around the support pin 93a. It can be moved.
  • the mounting position of the support pin 93a of the support sheet 93 with respect to the primary wheel main body 61 is set so that the auxiliary spring 90 is positioned between the support pin 93a of the support sheet 93 and the protrusion 72b of the flange 72.
  • the mounting position of the support pin 93a is such that when the twist angle between the primary flywheel 10 and the secondary flywheel 20 is between 0 ° and ⁇ 1 (less than ⁇ 1), the other end 92 of the auxiliary spring 90 is a flange.
  • 72 is set to be in a non-engaged state where it is not pressed from the protruding portion 72b side.
  • the attachment position of the support pin 93a of the support sheet 93 with respect to the primary wheel body 61 is such that the other end of the auxiliary spring 90 when the twist angle between the primary flywheel 10 and the secondary flywheel 20 exceeds a predetermined value ⁇ 1.
  • 92 is set to be in an engaged state in which the flange 92 is pressed from the protruding portion 72 b side of the flange 72.
  • the other end 92 of the auxiliary spring 90 has a contact member 95 that contacts the protrusion 72b of the flange 72 when the twist angle between the primary flywheel 60 and the secondary flywheel 70 exceeds a predetermined value ⁇ 1.
  • it is mounted as a pressing sheet.
  • the abutting member 95 abuts against the protrusion 72b of the flange 72 so as to move the other end of the auxiliary spring 90 radially outward when the torsion angle exceeds a specific torsion angle ⁇ 3 greater than a predetermined value ⁇ 1.
  • the posture is changed.
  • the abutment member 95 abuts against the base end portion 95a supported by the other end portion 92 of the auxiliary spring 90 and the protrusion 72b of the flange 72 when the twist angle exceeds a predetermined value ⁇ 1.
  • the base end portion 95 a of the contact member 95 has an uneven shape that engages with the other end portion 92 of the auxiliary spring 90 in the radial direction, and the other end of the auxiliary spring 90. It is fitted into the part 92 and is securely supported.
  • the contact portion 95b of the contact member 95 has, for example, a cross-sectional shape in which a surface that can contact the protrusion 72b of the flange 72 is curved in an arc shape, and the contact member with respect to the protrusion 72b of the flange 72 Even if the contact posture of 95 changes, the contact portion 95 b can stably contact the protruding portion 72 b of the flange 72.
  • the contact member 95 further extends from the contact portion 95b toward the protruding portion 72b side of the flange 72, and is slidably engaged with the protruding portion 72b of the flange 72 on both sides in the rotation center axis direction of the secondary flywheel 70.
  • the projecting portion 72b of the flange 72 has a constricted portion 72c that has a smaller thickness than the other portions and is slidably sandwiched between the parallel guide portions 95c, and the constricted portion.
  • An inclined stepped portion 72d adjacent to the radially outer side of 72c is provided.
  • the reaction force from the auxiliary spring 90 gradually changes its direction outward in the radial direction. While getting bigger.
  • the contact member 95 contacts the protrusion 72 b of the flange 72.
  • the contact posture is changed from the radially inner contact posture shown in FIG. 10A to the radially outer contact posture shown in FIG. 10B.
  • the contact member 95 When the contact member 95 changes from the radially inner contact posture to the radially outer contact posture, the contact member 95 moves the other end portion 92 of the auxiliary spring 90 outward in the radial direction, and assists.
  • the spring 90 is bent.
  • the contact member 95 contacts the jaw-shaped stepped portion 72d and is positioned in the radial direction, and presses the contact portion 95b against the protruding portion 72b of the flange 72.
  • the projecting portion 72b of the flange 72 is sandwiched between the base portions of the pair of plate-like parallel guide portions 95c, and the state is substantially fixed to the projecting portion 72b of the flange 72.
  • the contact portion 95b of the contact member 95 contacts the protruding portion 72b of the flange 72, and the other of the auxiliary spring 90 is within a torsion angle range in which the torsion angle exceeds a predetermined value ⁇ 1.
  • the end 92 moves in the radial direction with respect to the flange 72 of the secondary flywheel 20.
  • the reaction force F1 acting on the protrusion 72b of the flange 72 from the auxiliary spring 90 at the contact position of the protrusion 72b of the flange 72 and the contact part 95b of the contact member 95 is as follows. It is assumed that the reaction force F2 increases due to an increase in the compression amount of the auxiliary spring 90 with an increase in the twist angle.
  • the amount of compression and reaction force of the auxiliary spring 90 corresponding to F2 / F1 is different due to the difference ( ⁇ a ⁇ b) between the rotation angles ⁇ a and ⁇ b of the auxiliary spring 90 around the support pin 93a of the support sheet 93.
  • the increase rate of the reaction force component corresponding to (F2 ⁇ cos ⁇ b) / (F1 ⁇ cos ⁇ a) is reduced with respect to the increase rate.
  • the specific twist larger than the twist angle ⁇ 1.
  • the high torsional rigidity ⁇ (Nm / rad) before reaching the specific torque region Z1 exceeding the angle ⁇ 3 and the low torsional rigidity ⁇ (Nm / rad) after reaching the specific torque region Z1 can be realized.
  • the torsional rigidity between the primary flywheel 10 and the secondary flywheel 20 is reduced in the specific torque regions Z1 and Z2 in the torsion angle range where the torsion angle exceeds the predetermined value ⁇ 1. Can be made.
  • the other end 92 of the auxiliary spring 90 moves radially outward in the high torque region and is stably held by the protrusion 72b of the flange 72 via the contact member 95. This is also advantageous in terms of vibration and noise.
  • a predetermined twist angle ⁇ ⁇ b> 2 is set on the negative twist angle side in FIG. 3.
  • a constricted portion 72c and a jaw-shaped stepped portion 72d are arranged symmetrically in the vertical direction in FIG.
  • the constricted portion 72 c and the jaw-shaped stepped portion 72 d are arranged in the same direction in the rotational direction of the flange 72 with respect to the pair of projecting portions 72 b of the flange 72.
  • the auxiliary spring 90, the support sheet 93, and the contact member 95 are arranged at positions where the rotation phases are different from each other by 180 ° in one direction of rotation with respect to the primary wheel main body 61. 95 can be pressed against the pair of protrusions 72b of the lunge 72 simultaneously in the same rotational direction.
  • the rigidity ⁇ and the low torsional rigidity ⁇ after reaching the specific torque region Z1 are realized.
  • the inclination angle of the guide groove 45 for each torsion angle, the guide surface shape (straight or curved), etc. are appropriately set, and the radial position of the other end of the auxiliary spring 40 and the contact point between the pressing sheet 42 and the protruding portion 12 are set. It is also possible to set the radial position to an optimum position for each twist angle.
  • the inclined guide portion that engages the guide member 44 with the guide groove 45 is configured.
  • the track that guides the movement of the other end of the auxiliary spring 40 is not a guide groove.
  • An arbitrary guide mechanism for forming can be employed.
  • the torsion angle ⁇ exceeds a specific torsion angle ⁇ 3 greater than a predetermined value ⁇ 1
  • the other end of the auxiliary spring 40 is moved outward in the radial direction by the guide groove 45 or the trajectory of the inclined guide part instead.
  • a section having a small radial inclination and a section having a large radial inclination can be provided.
  • centrifugal force and the rotational balance are not mentioned. It is preferable to set the shape and position of the groove 45, and it is preferable to adjust the balance of peripheral components so as to optimize the rotational balance of the flywheels 1 and 51 in accordance with their arrangement.
  • the number of protrusions 72b of the flange 72, auxiliary springs 40, 90, etc. need not be a pair, but any number, preferably a plurality in consideration of the rotation balance, should be taken into account. .
  • auxiliary spring 40 when there are a large number of protrusions 12 (or protrusions 72b of the flange 72), a part of the auxiliary spring 40 (or 90) is partly corresponding to a part of the protrusions 12 from one side in the rotational direction. The remaining portions of the auxiliary springs 40 may be engaged with the corresponding remaining protruding portions 12 from the other side in the rotational direction. Of course, all of the many auxiliary springs 40 can be engaged with all the protrusions 12 from any one side in the rotational direction.
  • torsional vibration reduction device is not limited to those exemplified in the above-described embodiment, and includes modifications according to the matters described in the claims.
  • the torsional vibration reduction device has an effect of being able to reduce torsional vibration in a specific high torque region, and is useful for a rotational torque transmission mechanism of various vehicles. .
  • flywheel torsional vibration reduction device
  • 2 ... crankshaft drive source
  • 3 ... clutch mechanism drive transmission system
  • 4 ... input shaft drive transmission system
  • 10 ..Primary flywheel first rotating member, other rotating member
  • 20 ... secondary flywheel second rotating member, one rotating member
  • 21 ... first disk, 22 ... second disk 21a, 22a ... protruding engagement part, 23 ... first bearing, 24 ... second bearing, 30. ..Main spring (main elastic body, compression coil spring), 40 ... auxiliary spring (auxiliary elastic body), 41 ... support sheet, 42 ... pressing sheet, 43 ... support pin, 44 .. Guide member (inclined guide part), 45 ...
  • Auxiliary spring ( Auxiliary elastic body), 91 ... one end, 92 ... other end, 93 ... support sheet, 93a ... support pin, 95 ... contact member, 95a ... base end, 95b ... contact portion, 95c ... parallel guide portion, Z1, Z2 ... specific torque region (specific torsion angle region, specific height Rotation torque range), ⁇ a, ⁇ b ... rotational angle of auxiliary spring, ⁇ 1, ⁇ 2 ... predetermined value (predetermined torsion angle), ⁇ 3 ... specific torsion angle, ⁇ ... low torsional rigidity ⁇ ... High torsional rigidity

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

La présente invention concerne un dispositif d'amortissement de vibration par torsion, capable de réduire les vibrations par torsion dans une plage spécifiée de couples élevés, par l'ajustement de la rigidité de torsion dans la plage de couples élevés. La rigidité de torsion est augmentée par la génération d'une contre-force dans un ressort auxiliaire (40) dans une plage de couples élevés, dans laquelle l'angle de torsion entre un volant principal (10) et un volant secondaire (20) dépasse une valeur spécifiée (θ1). Entre-temps, en amenant l'autre extrémité du ressort auxiliaire (40), située sur un côté siège pressé (42), à se déplacer vers l'extérieur dans la direction radiale du volant principal (10), la contre-force agissant à partir du ressort auxiliaire (40) sur le volant principal (10) est réduite en fonction de l'ampleur de mouvement de l'autre extrémité du ressort auxiliaire, ce qui permet de réduire la rigidité de torsion entre le volant principal (10) et le volant secondaire (20) dans la plage spécifiée de couples élevés.
PCT/JP2013/006862 2013-01-11 2013-11-22 Dispositif d'amortissement de vibration de torsion WO2014108951A1 (fr)

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JP2013-003506 2013-01-11
JP2013003506 2013-01-11

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3060689A1 (fr) * 2016-12-20 2018-06-22 Valeo Embrayages Amortisseur de torsion et vehicule automobile

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58162324U (ja) * 1982-04-23 1983-10-28 株式会社大金製作所 ダンパ−デイスク
WO2012104926A1 (fr) * 2011-02-04 2012-08-09 トヨタ自動車株式会社 Dispositif d'amortissement de vibrations de torsion
WO2012137234A1 (fr) * 2011-04-01 2012-10-11 トヨタ自動車株式会社 Dispositif d'amortissement des vibrations en torsion

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58162324U (ja) * 1982-04-23 1983-10-28 株式会社大金製作所 ダンパ−デイスク
WO2012104926A1 (fr) * 2011-02-04 2012-08-09 トヨタ自動車株式会社 Dispositif d'amortissement de vibrations de torsion
WO2012137234A1 (fr) * 2011-04-01 2012-10-11 トヨタ自動車株式会社 Dispositif d'amortissement des vibrations en torsion

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3060689A1 (fr) * 2016-12-20 2018-06-22 Valeo Embrayages Amortisseur de torsion et vehicule automobile

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