JP2014228009A - Vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration damping device which has an improved damping performance with respect to torsional vibration and also is configured to prevent abnormal noise.SOLUTION: The vibration damping device includes: a damper mechanism 4 having an input element 41 to which engine torque is input, an output element 42 connected to a rotary shaft on an output side so as to be rotated integrally therewith and a coil spring 43 provided between the input element 41 and the output element 42; and a pendulum type vibration absorber 6 which has a pendulum 62 held in a rotor 61 and oscillates with the rotation of the rotor 61. The rotor 61 of the pendulum type vibration absorber 6 is supported on a shaft part 11c being the rotary shaft on the output side so as to be relatively rotatable. The vibration damping device further includes a selecting mechanism 7 for selecting such a first fastening state that the rotor 61 and the shaft part 11c are fastened to each other to be integrally rotated or such a releasing state that the rotor 61 and the shaft part 11c are released from each other to be relatively rotatable.

Description

  The present invention relates to a vibration damping device including a vibration damping device having an elastic body and a pendulum type vibration damping device.

  Rotating bodies such as drive shafts and gears for transmitting the torque generated by the power source to the target location or member are caused by fluctuations in the input torque itself, fluctuations in the load, friction, etc. Inevitably vibrates. The frequency of the vibration changes according to the number of rotations, and a higher-order vibration higher than the secondary vibration is also generated. Therefore, the amplitude becomes large due to resonance, which may cause noise and durability deterioration. is there. For this reason, devices or mechanisms for preventing vibration as described above are widely used in various devices that transmit power by rotation.

  For example, in Patent Document 1, an elastic damper having a spring and a pendulum damper having a pendulum are arranged in series in a power transmission path between an engine and a torque converter, and transmission of power from the engine to the torque converter is performed. In the direction, it is described that a pendulum damper is provided on the downstream side of the elastic damper.

  In Patent Document 2, a torsional damper is provided between the engine crankshaft and the torque converter. When the engine is started or when the engine speed is in the resonance rotation range, the input element of the torsional damper is It is described that the output gear of the starter motor is meshed with both the gear rotating integrally and the gear rotating integrally with the output element of the torsional damper.

JP 2011-208774 A JP 05-306733 A

  However, in the configuration described in Patent Document 1, when the engine speed is low, such as when the engine is started or when the engine is stopped, the pendulum of the pendulum damper swings in a state where the centrifugal force is weak. There was a possibility of causing abnormal noise.

  Further, in the configuration described in Patent Document 2, since the torsional damper rotates integrally in a resonance rotation range where the engine speed is low, it can be prevented from resonating due to vibration transmitted from the engine to the power transmission path. It was limited to the vibration damping characteristics of the body, and did not exhibit various vibration damping characteristics. When a configuration that exhibits different vibration damping characteristics is added, there remains room for various studies such as the structure, type, and assembly.

  The present invention has been made paying attention to the above technical problem, and is configured to exhibit various vibration damping characteristics to improve the damping effect of torsional vibration and to prevent abnormal noise. An object of the present invention is to provide a vibration damping device.

  In order to solve the above problems, an invention according to claim 1 is directed to an input element to which engine output torque is input, an output element coupled to rotate integrally with an output-side rotating shaft, and the input element And the output element, a damper mechanism having an elastic body that expands and contracts in the rotation direction, and a pendulum type vibration absorber having a pendulum that is held by the rotating body and swings when the rotating body rotates The rotating body in the pendulum type vibration absorber is supported so as to be relatively rotatable on the output side rotating shaft, and the rotating body in the pendulum type vibration absorber and the rotating shaft on the output side Between a fastening state that is fastened so as to rotate integrally and an open state in which the rotating body and the rotary shaft on the output side of the pendulum type damper are opened to be relatively rotatable. And it is characterized in that it comprises a replacement mechanism.

  According to a second aspect of the present invention, in the first aspect of the invention, the switching mechanism is configured to switch to a fastening state in which the input element and the output element in the damper mechanism are fastened so as to rotate together. It is the vibration damping device characterized by having.

  According to a third aspect of the present invention, in the first or second aspect of the invention, the switching mechanism fastens the rotating body and the output-side rotating shaft of the pendulum type vibration absorber, and the rotating shaft and the damper. A first fastening state in which the input element in the mechanism is opened, the input element in the damper mechanism and the rotating shaft on the output side are fastened, and the rotating body and the rotating body in the pendulum damper The second fastening state in which the opening is opened, and the neutral state in which the rotating element in the pendulum type vibration absorber and the input element in the damper mechanism are opened from the rotating shaft on the output side are configured to be switched. Is a vibration damping device characterized by

  According to the first aspect of the present invention, the state where the pendulum type vibration absorber is operated and the state where the pendulum type vibration absorber is not operated can be switched by the switching mechanism. Thereby, since the switching mechanism can isolate | separate a pendulum type vibration absorber from a power transmission system, the abnormal noise produced by a pendulum can be prevented. For example, when the engine speed is in the low rotation range, the pendulum type vibration absorber is not operated in a state where the centrifugal force is weak by operating the switching mechanism and disconnecting the pendulum type vibration absorber from the power transmission system. An abnormal noise caused by the vibration absorber can be prevented. Further, in this case, the inertia due to the pendulum type absorber does not need to act on the power transmission system, and the acceleration performance can be improved. In addition, when the engine speed is in the high speed range, the pendulum type vibration absorber can be connected to the power transmission system by the switching mechanism, so that the vibration control effect by the pendulum type vibration absorber can be achieved while the operation of the pendulum is stable. Can be demonstrated. Therefore, the vibration damping characteristic by the damper mechanism and the vibration damping characteristic by the pendulum absorber can be effectively acted to attenuate the vibration and prevent abnormal noise.

  According to the invention of claim 2, the state where the damper mechanism is operated and the state where the damper mechanism is not operated can be switched by the switching mechanism. Thereby, the abnormal noise which arises with the elastic body of a damper mechanism can be prevented. For example, when the engine speed is in the low rotation region, the switching mechanism is operated to directly connect the input element and the output element of the damper mechanism, so that the damper mechanism is not operated in the low rotation region. Abnormal noise that occurs can be prevented.

  According to the invention of claim 3, for example, when the engine speed is in a high rotation range, the pendulum type vibration absorber can be connected to the power transmission system by the switching mechanism and the damper mechanism can be operated. The vibration control effect by the pendulum absorber can be exhibited in a state where the operation of the pendulum is stable, and the vibration control effect by the damper mechanism can also be exhibited. Therefore, according to the engine speed, the vibration damping characteristic by the damper mechanism and the vibration damping characteristic by the pendulum absorber can be effectively acted to attenuate the vibration and prevent abnormal noise.

It is sectional drawing which shows the power transmission device provided with the vibration damping device in an example of this invention. It is the schematic which showed typically the power transmission path | route and inertial system in the power transmission device.

  Hereinafter, a vibration damping device according to the present invention will be described in detail with reference to the drawings. FIG. 1 shows a vibration damping device according to an example of the present invention, and schematically shows a power transmission device including the vibration damping device. The power transmission device 1 is mounted on an internal combustion engine as a power source, particularly a vehicle equipped with an engine, and the output torque of the engine is a torsion having an elastic body from a drive plate 3 integrally attached to the crankshaft 2 of the engine. It is configured to transmit to the fluid transmission device 10 via the damper mechanism 4 which is a vibration damping device. That is, the damper mechanism 4 is provided between the drive plate 3 and the fluid transmission device 10 and is called a so-called torsional damper.

  As shown in FIG. 1, the damper mechanism 4 includes an input element 41 that is an input-side rotating member, an output element 42 that is an output-side rotating member, and an elastic body that is elastically deformed in the rotational direction by torsional vibration caused by engine torque. The coil spring 43 is provided. The input element 41 is connected to rotate integrally with the drive plate 3. The output element 42 is coupled to rotate integrally with the front cover 11 of the fluid transmission device 10. Moreover, the input element 41 and the output element 42 are comprised so that it can rotate relatively. The coil spring 43 is provided between the input element 41 and the output element 42. Therefore, when the input element 41 and the output element 42 rotate relative to each other, the coil spring 43 expands and contracts in the rotation direction.

  The input element 41 includes an outer peripheral plate 41a that is formed in an annular shape and is disposed so as to face the drive plate 3 in the axial direction. An interposition plate 41f is integrated as much as possible on the outer peripheral side of the outer peripheral plate 41a on the surface facing the drive plate 3. The bolt 52 that penetrates the drive plate 3 is screwed into the set block 51 joined to the surface of the interposition plate 41f that faces the drive plate 3, so that the outer peripheral plate 41a rotates integrally with the drive plate 3. Is configured to do.

  The input element 41 includes a first side plate 41c and a second side plate 41d that are formed in a substantially annular shape and fastened so as to rotate integrally with the outer peripheral side plate 41a. Specifically, the first side plate 41c is provided on the drive plate 3 side with respect to the outer peripheral plate 41a, and the second side plate 41d is provided on the pendulum type vibration absorber 6 side described later with respect to the outer peripheral plate 41a. ing. Moreover, the outer peripheral side of the 1st side plate 41c and the 2nd side plate 41d is integrally fastened with the outer peripheral side plate 41a by the rivet 41b. That is, the first side plate 41c, the second side plate 41d, and the outer peripheral plate 41a are configured to rotate integrally.

  The first side plate 41 c and the second side plate 41 d are provided with a window portion 41 e that opens in the axial direction on the inner peripheral side of the portion fastened by the rivet 41 b and accommodates the coil spring 43. A storage chamber is formed. Further, a second clutch gear 75b of the switching mechanism 7 described later is connected to the second side plate 41d on the inner peripheral side of the window portion 41e so as to rotate integrally.

  The output element 42 includes an inner peripheral plate 42 a that is formed in an annular shape and is disposed so as to face the drive plate 3 in the axial direction. The inner peripheral plate 42a is disposed closer to the rotation center than the outer peripheral plate 41a. The inner peripheral portion of the inner peripheral plate 42 a is spline-fitted with the outer peripheral surface of the shaft portion 11 c of the front cover 11. That is, the output element 42 and the front cover 11 rotate integrally. The front cover 11 is formed in a bottomed cylindrical shape, and includes a front wall 11a forming a bottom portion, and a substantially cylindrical outer peripheral wall 11b formed so as to extend in the axial direction from the outer peripheral portion of the front wall 11a. ing. The shaft portion 11c is formed so as to protrude from the front wall 11a to the engine side in the axial direction. Therefore, the shaft portion 11 c includes the rotation center axis of the front cover 11 and is formed in parallel with the rotation center axis. In this specific example, the shaft portion 11c constitutes an output-side rotation shaft in the vibration damping device.

  The inner peripheral plate 42 a is provided with a holding portion 42 b that holds the coil spring 43 in contact with the coil spring 43 in the circumferential direction. The holding portion 42b is configured by a portion in which the inner peripheral side plate 42a is opened in a predetermined range in the circumferential direction, and a plurality of holding portions 42b are arranged at equal intervals. That is, the inner peripheral side plate 42a is formed so that the inner peripheral side plates 42a and the space portions are alternately arranged in the circumferential direction. In short, the holding portion 42b may be a through portion that penetrates the inner peripheral plate 42a in the axial direction so as to have a predetermined width in the radial direction and the circumferential direction, and the outer peripheral surface of the inner peripheral plate 42a has a radius. It may be a portion that is formed in a concavo-convex shape in the direction and is sandwiched between convex portions in the circumferential direction. The holding portion 42b forms a storage chamber for storing the coil spring 43, and is provided in the window portion 41e of the side plates 41c and 41d. Further, the outer peripheral edge portion of the holding portion 42b is constituted by an outer peripheral frame portion 42c integrated with the inner peripheral plate 42a. A resin sheet member 42 d is provided between the outer peripheral frame portion 42 c and the coil spring 43 in the radial direction. A load of the coil spring 43 acts on the outer peripheral frame portion 42 a by centrifugal force, and the sheet member 42 d is configured to slide with the coil spring 43.

  A storage chamber is formed by the input element 41 and the output element 42, and a coil spring 43 is stored in the storage chamber. The coil spring 43 is held in contact with the input element 41 and the output element 42 at the end in the rotational direction (circumferential direction) of the damper mechanism 4. When the damper mechanism 4 operates, both ends of the coil spring 43 in the circumferential direction are in contact with the input element 41 at one end and in contact with the output element 42 at the other end. That is, when the input element 41 and the output element 42 rotate relative to each other, the coil spring 43 is sandwiched between the input element 41 and the output element 42 in the rotation direction and expands and contracts in the rotation direction.

  A pendulum type vibration absorber 6 that is a vibration damping device having a pendulum is provided on a shaft portion 11c of the front cover 11 on which the damper mechanism 4 is provided. The pendulum damper 6 is a so-called dynamic damper or pendulum type, and is disposed on the shaft portion 11c between the damper mechanism 4 and the front wall 11a of the front cover 11 in the axial direction. . Specifically, the pendulum type vibration absorber 6 includes a rotating body 61 that is formed in an annular shape and is fitted to the shaft portion 11c so as to be relatively rotatable. A hub shaft 61a that is formed in a hollow shape and is fitted to the shaft portion 11c so as to be relatively rotatable is provided on the inner peripheral portion of the rotating body 61. In this specific example, the inner peripheral surface of the hub shaft 61a is in contact with the bearing 9 fitted to the shaft portion 11c. That is, the rotating body 61 is supported by the shaft portion 11 c via the bearing 9. The rotating body 61 includes a flange portion 61b that protrudes radially outward from the hub shaft 61a. Further, a first clutch gear 75a of a switching mechanism 7 described later is connected to the rotating body 61 so as to rotate integrally.

  A pendulum 62 corresponding to a weight that is held by the rotating body 61 and can freely move relative to the rotating body 61 is provided on the outer peripheral side of the flange portion 61 b. A plurality of pendulums 62 are arranged at equal intervals in the circumferential direction. Further, a cover member 63 formed so as to cover the pendulum 62 is integrally provided on the outer peripheral side of the flange portion 61b. That is, the pendulum 62 is accommodated in the cover member 63. In short, the pendulum 62 may be configured to swing in the same direction as the rotating body 61 or the direction of relative rotation with the rotating body 61 as the rotating body 61 rotates. It is configured to include moving objects.

  For example, in the pendulum type vibration absorber 6, a penetrating portion penetrating in the thickness direction is formed in the outer peripheral portion of the flange portion 61 b with a predetermined width in the radial direction and long in the circumferential direction. . The penetrating portion accommodates the pendulum 62 so as to be movable with respect to the rotating body 61, and constitutes a rolling chamber in which the pendulum 62 rolls as a rolling element on the outer peripheral surface of the penetrating portion. That is, a plurality of rolling chambers are provided at equal intervals in the circumferential direction, and a plurality of pendulums 62 are accommodated for each rolling chamber. The surface on the outer peripheral side of each rolling chamber constitutes a surface on which the pendulum 62 that receives centrifugal force comes into contact and moves along the pendulum 62, that is, a rolling surface. That is, the rolling surface is configured such that the left and right surfaces in the rotation direction starting from the center are, for example, toroidal surfaces. In this description, the penetrating part may be described as a rolling chamber and the pendulum may be described as a rolling element.

  Further, the pendulum 62 includes weights having disc portions having outer diameters larger than the outer diameter of the support pins at both ends of the support pins slightly longer than the plate thickness of the flange portion 61b. The outer diameter of the disk portion is set to be smaller than the maximum distance between the outer peripheral surface and the inner peripheral surface forming the rolling chamber and larger than the minimum interval on both sides of the rolling chamber. Yes. The outer diameter of the support pin is set smaller than the radial opening width in the rolling chamber. That is, the pendulum 62 can move in a direction parallel to the rotation center axis of the rotating body 61 while being accommodated in each rolling chamber. Therefore, the pendulum 62 is configured such that the inner wall surface of the disc portion is caught by the side surface of the flange portion 61b and does not come out of the rolling chamber. In this specific example, since the cover member 63 is provided so as to cover the rolling chamber, the pendulum 62 is accommodated in the cover member 63.

  Furthermore, in addition to the damper mechanism 4 and the pendulum damper 6 described above, the shaft 11 c of the front cover 11 is connected to the shaft 11 c and the damper mechanism 4, and the shaft 11 c and the pendulum damper 6. A switching mechanism 7 configured to switch between the fastening states is provided. The switching mechanism 7 is a clutch mechanism, and is provided between the damper mechanism 4 and the pendulum type vibration absorber 6 in the axial direction on the shaft portion 11c. Specifically, the switching mechanism 7 switches between a fastening state and an open state between the input element 41 of the damper mechanism 4 and the front cover 11 of the fluid transmission device 10, and the rotating body 61 and the front cover of the pendulum type vibration absorber 6. 11 is configured to be able to switch between a fastening state and an open state.

  As an example, FIG. 1 shows a switching mechanism 7 constituted by a key-type synchromesh mechanism. The switching mechanism 7 shown in FIG. 1 is provided with a hub 71 provided with splines and kerfs (key grooves) on the outer peripheral portion and with splines on the inner peripheral portion. The inner peripheral portion of the hub 71 is spline-fitted with the outer peripheral surface of the shaft portion 11c. Further, the spline provided on the outer peripheral portion of the hub 71 is engaged with the spline provided on the inner peripheral portion of the sleeve 72 formed in an annular shape. A key 73 is accommodated in the key groove of the hub 71, and the key 73 is pressed toward the sleeve 72 in the radial direction by a spring (not shown). The outer periphery of the key 73 and the inner periphery of the sleeve 72 are engaged with each other. When the sleeve 72 moves in the axial direction, the sleeve 72 and the key 73 are integrally formed in the engaged state. Is configured to move.

  Further, the switching mechanism 7 includes a synchronizer ring 74 that has a protrusion on the outer peripheral portion for meshing with an inner peripheral spline in the sleeve 72 and has a conical cone surface on the inner peripheral surface. In this specific example, a first synchronizer ring 74a provided on the pendulum type absorber 6 side and a second synchronizer ring 74b provided on the damper mechanism 4 side are provided with respect to the hub 71 in the axial direction. ing. In addition, the switching mechanism 7 has a conical cone surface facing the cone surface of the synchronizer ring 74 on the outer peripheral surface, and the inner portion of the sleeve 72 protrudes to the outer peripheral side in the radial direction from the cone surface. A clutch gear 75 having a spline for meshing with the peripheral spline is provided. The cone surface forms a friction engagement surface.

  In this specific example, a first clutch gear 75a that rotates integrally with the rotating body 61 of the pendulum damper 6 and a second clutch gear 75b that rotates integrally with the input element 41 of the damper mechanism 4 are provided. Yes. Specifically, the inner peripheral surface of the first clutch gear 75a and the outer peripheral surface of the hub 61a of the rotating body 61 are spline-fitted. The second clutch gear 75b is configured to rotate integrally with the second side plate 41d provided on the input element 41 on the pendulum vibration absorber 6 side. For example, the support member 8 that is fitted to the shaft portion 11c of the front cover 11 so as to be relatively rotatable is provided, the outer peripheral surface of the support member 8 and the inner peripheral surface of the second clutch gear 75b are spline-fitted, and the support member 8 The outer peripheral surface of the second side plate 41d and the inner peripheral surface of the second side plate 41d are spline fitted.

  Furthermore, the switching device 7 includes an appropriate actuator (not shown) that moves the sleeve 72 in the axial direction, and the actuator is electrically controlled by an electronic control device such as an ECU. This actuator includes a mechanically operated actuator and a hydraulically operated actuator. For example, when the sleeve 72 is operated to the pendulum type vibration absorber 6 side, the key 73 moves together with the sleeve 72 to the left and presses the first synchronizer ring 74a, so that the cone surface of the first synchronizer ring 74a is Frictional contact with the cone surface of the first clutch gear 75a occurs. As a result, an action (synchronization action) of matching the rotational speed of the front cover 11 with the rotational speed of the rotating body 61 in the pendulum absorber 6 starts to occur. When the synchronization of the rotational speed is completed, the frictional force between the cone surfaces disappears, the sleeve 72 moves further leftward, the spline of the sleeve 72 meshes with the spline of the first clutch gear 75a, and the shaft portion 11c. And the rotating body 61 of the pendulum type vibration absorber 6 are fastened so as to rotate integrally. On the other hand, when the sleeve 72 and the first clutch gear 75a are spline-fitted, the sleeve 72 is moved to the right by the actuator when the sleeve 72 is shifted to the second clutch gear 75b and the spline-fitted state. In order to move, the sleeve 72 and the first clutch gear 75a are released. That is, the switching mechanism 7 in this specific example is a rotation synchronization device, and is configured to equalize the rotation speed of the rotation member on the synchronization side and the rotation speed of the rotation unit on the synchronized side by the frictional force. Yes.

  Here, the fastening state and the release state set by the switching mechanism 7 will be described. In the switching mechanism 7, the sleeve 72 is spline-fitted to both the first clutch gear 75 a and the hub 71 on the side of the pendulum damper 6, so that the shaft 11 c of the front cover 11 and the rotating body of the pendulum damper 6 are rotated. 61 can be set to a fastened state (first fastened state). Therefore, by controlling the switching mechanism 7 to be in the first fastening state, the rotating body 61 of the pendulum type vibration absorber 6 is rotated by the torque of the front cover 11. That is, in the first engagement state, the input element 41 of the damper mechanism 4 and the front cover 11 are in an open state in which the relative rotation is possible. Therefore, the vibration suppression effect by the pendulum damper 6 and the vibration suppression effect by the damper mechanism 4 Both are demonstrated. FIG. 2 schematically shows a power transmission path and an inertial system in the power transmission device 1 of this specific example. As described above, when the switching mechanism 7 is set to the first fastening state, the pendulum type vibration absorber 6 is added to the inertial system (power transmission system) including the output element 42 of the damper mechanism 4 as shown by a one-dot chain line in FIG. An inertial system including can be added.

  Further, the switching mechanism 7 separates the input element 41 and the shaft portion 11c of the damper mechanism 4 from the fact that the sleeve 72 is not engaged with the first clutch gear 75a and the second clutch gear 75b, and The rotating body 61 and the shaft portion 11c can be set in a separated state (neutral state). Therefore, by controlling the switching mechanism 7 to be in the neutral state, torque is not transmitted between the shaft portion 11c of the front cover 11 and the rotating body 61 of the pendulum absorber 6 and the damper mechanism 4 The input element 41 and the output element 42 are not directly connected. That is, in the neutral state, the damping effect by the pendulum absorber 6 is not exhibited, but only the damping effect by the damper mechanism 4 is exhibited. As described above, when the neutral state is set by the switching mechanism 7, the inertial system including the output element 42 of the damper mechanism 4 and the inertial system including the pendulum vibration absorber 6 are separated as shown by a dotted line in FIG. 2. ing.

  Further, the switching mechanism 7 is in a state where the input element 41 and the shaft portion 11c of the damper mechanism 4 are fastened by the spline fitting of the sleeve 72 to both the second clutch gear 75b and the hub 71 on the damper mechanism 4 side. (Second fastening state) can be set. Therefore, by controlling the switching mechanism 7 so as to be in the second fastening state, the input element 41 and the output element 42 are directly connected in the damper mechanism 4. That is, in the 2nd fastening state, since the input element 41 and the output element 42 of the damper mechanism 4 rotate integrally, the damping effect by the damper mechanism 4 is not exhibited. Furthermore, in the 2nd fastening state, since the shaft part 11c of the front cover 11 and the rotating body 61 of the pendulum type vibration absorber 6 are separated, the vibration damping effect by the pendulum type vibration absorber 6 is not exhibited. In this way, when the switching mechanism 7 is set to the second fastening state, the inertial system including the input element 41 of the damper mechanism 4 and the inertial system including the output element 42 of the damper mechanism 4 as shown by a solid line in FIG. And are connected. In other words, the switching mechanism 7 can selectively switch the power transmission path between the input element 41 of the damper mechanism 4 and the shaft portion 11 c of the front cover 11.

  As described above, the switching mechanism 7 is configured to fasten either the input element 41 of the damper mechanism 4 or the rotating body 61 of the pendulum absorber 6 and the shaft portion 11c of the front cover 11, and the input element 41. And it is comprised so that it can switch to the state which isolate | separated the rotary body 61 from the axial part 11c. In short, the switching mechanism 7 provides a state in which the damping effect by the damper mechanism 4 is exerted, a state in which the damping effect by the pendulum damper 6 is exhibited, and a damping effect by the damper mechanism 4 and the pendulum damper 6. It is comprised so that it can switch to the state which is not exhibited.

  As shown in FIG. 1, the fluid transmission device 10 is disposed on the downstream side of the damper mechanism 4 in the power transmission device 1 and is configured to store oil as fluid in the front cover 11. The fluid transmission device 10 in this specific example is a torque converter, and the internal structure that contains oil is well known. For example, the fluid transmission device 10 includes a pump impeller 12 that generates an oil flow, and a turbine runner 13 that is rotated by the oil flow. The pump impeller 12 and the turbine runner 13 are axially aligned on the same axis. It is arranged to face. The cylindrical portion 11b of the front cover 11 is joined to the outer peripheral end portion or the engine end portion of the pump shell. The pump shell is connected to an oil pump (not shown). Further, a stator 14 is disposed between the inner peripheral portion of the pump impeller 12 and the inner peripheral portion of the turbine runner 13. The stator 14 is supported by a fixed portion (not shown) via a one-way clutch 15.

  Further, a lock-up clutch 20 is provided inside the fluid transmission device 10 for transmitting torque between the pump impeller 12 and the turbine runner 13 without using oil. That is, the lockup clutch 20 is a so-called direct coupling clutch, and is mainly composed of a lockup piston 21 formed in an annular shape. A friction member 21a that is pressed against the inner surface (front wall surface) 11d of the front wall 11a of the front cover 11 to generate a frictional force is attached to the outer peripheral side of the side surface on the engine side of the lockup piston 21 as much as possible. . An outer peripheral portion 21 b extending in the axial direction along the inner peripheral surface of the outer peripheral wall 11 b of the front cover 11 is formed at the outer peripheral end portion of the lockup piston 21. The outer peripheral portion 21b is formed in a cylindrical shape or a fork shape provided at equal intervals in the circumferential direction. That is, the outer diameter of the lock-up piston 21 is slightly smaller than the inner diameter of the cylindrical portion 11 b of the front cover 11. Further, a connecting member configured integrally with the turbine runner 13 is connected to the outer peripheral portion 21 b of the lockup piston 21. That is, the lockup piston 21 is configured to rotate integrally with the turbine runner 13 via the connecting member.

  The inner peripheral portion of the turbine runner 13 is integrated with a hub shaft 16 that is formed hollow. The hub shaft 16 has a cylindrical portion 16a formed in a hollow cylindrical shape, and a hub 16b formed in a flange shape protruding from the cylindrical portion 16a to the outer peripheral side in the radial direction. A lockup piston 21 is fitted on the outer peripheral surface of the cylindrical portion 16a so as to be movable in the axial direction and relatively rotatable in the rotational direction. The inner peripheral portion of the cylindrical portion 16 a is spline-fitted with the outer peripheral surface of the output shaft 17 that is an output member in the fluid transmission device 10.

  Furthermore, the side surface on the engine side of the lock-up piston 21, that is, the side surface on which the friction material 21 a is provided faces the front wall surface 11 d of the front cover 11. That is, the front wall surface 11d constitutes a lockup engagement surface. Therefore, when the lock-up clutch 20 is in the released state, a slight gap is left between the engine-side side surface of the lock-up piston 21 and the front wall surface 11d, and the gap constitutes an oil passage through which oil flows. To do.

  For example, in the lockup engagement state, when the hydraulic pressure of the engagement oil passage is made lower than the hydraulic pressure of the release oil passage, the hydraulic pressure between the lockup piston 21 and the front wall 11a is increased in the storage chamber in which the turbine runner 13 is stored. Higher than hydraulic pressure. As a result, the lock-up piston 21 is pushed away from the front wall 11a, and the friction material 21a is separated from the front wall surface 11d. Therefore, when the lockup clutch 20 is in the released state, the transmission of torque between the front wall 11a and the lockup piston 21 is interrupted. On the other hand, in the lockup released state, the hydraulic pressure in the accommodating chamber for accommodating the turbine runner 13 is increased between the lockup piston 21 and the front wall surface 11d by making the hydraulic pressure in the engaging oil passage higher than the hydraulic pressure in the opening oil passage. Higher than the hydraulic pressure. As a result, the lock-up piston 21 is pushed toward the front wall 11a, and the friction material 21a is brought into contact with and pressed against the front wall surface 11d to be frictionally engaged. In the engaged state of the lock-up clutch 20, torque is transmitted between the lock-up piston 21 and the front cover 11 by a frictional force generated between the friction material 21a and the front wall surface 11d.

  As described above, according to the vibration damping device of this specific example, the switching device exhibits the vibration suppression effect by the pendulum absorber, and the vibration suppression effect by the damper mechanism having the elastic body. Will be able to select.

  For example, when the switching mechanism is set to the first engagement state and the pendulum type vibration absorber is connected to the torque transmission system, the damping effect of the pendulum type vibration absorber can be exhibited. In other words, since the pendulum type absorber can be connected by the switching mechanism in the high rotation region where the engine speed has increased to some extent, the damping effect of the pendulum type absorber is exhibited in the rotation region where the operation of the pendulum is stable. be able to. In other words, in the rotation speed region where the rotational speed is slow and the centrifugal force is insufficient, the pendulum type vibration absorber can be disconnected from the power transmission system, so that the noise generated by the operation of the pendulum type vibration absorber with insufficient centrifugal force is reduced. While being able to prevent, the abrasion resistance of a pendulum type vibration absorber can be improved.

  In addition, when the switching mechanism is set to the neutral state, the damping effect by the damper mechanism in which the input element and the output element can be rotated relative to each other is exerted. For example, in the low speed region below the idling speed, Vibrations due to engine torque can be attenuated and the pendulum can be prevented from operating. Further, in the neutral state, the pendulum absorber is disconnected from the torque transmission system, so that the inertial force of the pendulum absorber is not added to the torque transmission system. Therefore, in the engine rotation region where the vibration control effect by the pendulum is not necessary, the moment of inertia can be reduced by separating the pendulum type absorber from the power transmission system, and the acceleration performance can be improved.

  Furthermore, when the switching mechanism is set to the second fastening state and the input element and the output element of the damper mechanism are fastened, an elastic body such as a coil spring included in the damper mechanism does not expand and contract in the rotation direction. That is, in the second fastening state, although the vibration damping effect by the damper mechanism is not exhibited, the elastic body does not expand and contract in the rotation direction, so that resonance by the damper mechanism does not occur when the engine is started or stopped. For this reason, it is possible to prevent abnormal vibration and abnormal noise caused by resonance of the damper mechanism. Further, since the input element and the output element are directly connected in the damper mechanism, the torque transmission efficiency is improved and the responsiveness when starting the engine can be improved. Furthermore, in the second fastening state, the pendulum type vibration absorber is disconnected from the power transmission system. Therefore, in the region where the engine speed is low, for example, the engine speed equal to or lower than the idle speed, It is possible to prevent the hitting sound generated by colliding with the constituent members.

  The vibration damping device according to the present invention is not limited to the specific examples described above, and can be appropriately changed without departing from the object of the present invention.

  For example, in the specific example described above, an example in which the switching mechanism is configured by a key-type synchromesh mechanism has been described, but the switching mechanism in the present invention is not limited to this. That is, the vibration damping device according to the present invention is not limited to the structure of the switching mechanism. In short, the vibration damping effect by the pendulum absorber and the vibration damping effect by the damper mechanism are exhibited. Any mechanism that can be switched to a state may be used. Another specific example of the switching mechanism is a device that has a friction material and synchronizes the rotational speed by frictional contact, and a clutch mechanism that equalizes the difference in rotational speed between the synchronization side member and the synchronized side member by friction force. It may be configured. Further, the switching mechanism may be constituted by a dog clutch.

  Furthermore, the vibration damping device according to the present invention is not limited to the configuration in which the damper mechanism having the elastic body, the pendulum type absorber, and the switching mechanism are provided between the drive plate and the fluid transmission device. That is, the input side rotating member in the vibration damping device is not limited to the drive plate, and the output side rotating member is not limited to the front cover of the fluid transmission device.

  Further, the structure of the damper mechanism having the elastic body and the structure of the pendulum type vibration absorber having the pendulum are not limited to the structure in the specific example described above, and can be changed as appropriate. For example, the shape of the rotating body in the pendulum absorber, the shape of the pendulum that holds the rotating body, the shape of the rolling chamber that rolls the pendulum, and the like can be changed from the shape of the specific example described above. is there.

  DESCRIPTION OF SYMBOLS 1 ... Power transmission device, 2 ... Crankshaft, 3 ... Drive plate, 4 ... Damper mechanism, 6 ... Pendulum type vibration absorber, 7 ... Switching mechanism, 8 ... Support member, 9 ... Bearing, 10 ... Fluid transmission device, 11 ... 11a ... front wall, 11b ... outer peripheral wall, 11c ... shaft, 41 ... input element, 41a ... outer peripheral side plate, 41b ... rivet, 41c ... first side cover, 41d ... second side cover, 41e ... window Part 41f ... intervening plate 42 ... output element 42a ... inner peripheral side plate 42b ... holding part 42c ... outer frame part 42d ... sheet member 43 ... coil spring (elastic body) 61 ... rotating body 61a ... Hub shaft, 61b ... Flange part, 62 ... Pendulum, 71 ... Hub, 72 ... Sleeve, 74a ... First synchronizer , 74b, second synchronizer ring, 75a, first clutch gear, 75b, second clutch gear.

Claims (3)

An input element to which engine output torque is input, an output element connected to rotate integrally with an output-side rotating shaft, and an elasticity that is provided between the input element and the output element and expands and contracts in the rotation direction. In a vibration damping device comprising a damper mechanism having a body, and a pendulum type damper having a pendulum that is held by the rotating body and swings when the rotating body rotates,
The rotating body in the pendulum type vibration absorber is supported so as to be relatively rotatable on the rotating shaft on the output side,
The fastening state in which the rotating body and the output-side rotating shaft in the pendulum type damper are fastened so as to rotate together, and the rotating body and the output-side rotating shaft in the pendulum absorber are relatively rotated. A vibration damping device comprising a switching mechanism for switching between an open state and an open state so as to be enabled.   2. The vibration damping device according to claim 1, wherein the switching mechanism is configured to switch to a fastening state in which the input element and the output element in the damper mechanism are fastened so as to rotate together. . The switching mechanism is
A first fastening state in which the rotating body and the output-side rotating shaft in the pendulum absorber are fastened, and the rotating shaft and the input element in the damper mechanism are opened;
A second fastening state in which the input element in the damper mechanism and the output-side rotating shaft are fastened, and the rotating shaft and the rotating body in the pendulum absorber are opened;
3. The structure according to claim 1, wherein the rotating body in the pendulum type vibration absorber and the input element in the damper mechanism are switched to a neutral state in which the rotating element is opened from the rotating shaft on the output side. The vibration damping device described.

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