JP2019178755A - Vibration attenuation device - Google Patents

Abstract

To further improve a vibration attenuation performance of a vibration attenuation device including a restoring force generation member which oscillates with the rotation of a support member, and an inertial mass body which oscillates in conjunction with the restoring force generation member.SOLUTION: The vibration attenuation device includes: a support member which rotates integrally with a rotating element around a rotation center of the rotating element to which torque from an engine is transmitted; a restoring force generation member which is connected to the support member so as to receive the torque between the support member and the restoring force generation member, and can oscillate with the rotation of the support member; and an inertia mass body which is connected to the support member via the restoring force generation member, and oscillates around the rotation center in conjunction with the restoring force generation member with the rotation of the support member. A sliding resistance reduction member is arranged between the two axially adjoining components, out of the support member, the restoring force generation member and the inertia mass body.SELECTED DRAWING: Figure 2

Description

  The invention of the present disclosure includes a restoring force generating member that can swing as the supporting member rotates, and is connected to the supporting member via the restoring force generating member and is also connected to the restoring force generating member as the supporting member rotates. The present invention relates to a vibration damping device including an inertial mass body that swings in conjunction with it.

  2. Description of the Related Art Conventionally, as a torque fluctuation suppressing device that suppresses torque fluctuation of a rotating body to which torque from an engine is input, the mass body is arranged side by side with the rotating body and is relatively rotatable with respect to the rotating body. A centrifuge arranged to be movable in the radial direction in a recess formed in the rotating body so as to receive a centrifugal force due to the rotation of the rotating body and the mass body, and either the centrifuge or the rotating body and the mass body And a cam mechanism having a cam follower provided in any one of a rotating body and a mass body or a centrifuge (see, for example, Patent Document 1). In this torque fluctuation suppressing device, the mass body has a first inertia ring and a second inertia ring arranged so as to face each other with the rotating body interposed therebetween, and the first and second inertia rings are configured so that the rotating body is axially disposed. Are connected to each other by a pin that penetrates through or a connecting portion that connects the outer peripheral ends of both. In addition, a plurality of centrifuges are arranged at intervals in the circumferential direction between the first and second inertia rings. The cam mechanism receives a centrifugal force acting on the centrifuge, and when the relative displacement in the rotational direction occurs between the rotating body and the mass body, the circumferential direction in which the relative displacement decreases Convert to force. Thereby, the centrifugal force acting on the centrifuge is used as a force for suppressing torque fluctuation, and the characteristic for suppressing torque fluctuation changes according to the rotational speed of the rotating body.

JP 2017-53467 A

  In the torque fluctuation suppressing device described in Patent Document 1, a plurality of centrifuges are arranged between the first and second inertia rings in the axial direction of the mass body, and each centrifuge is used to rotate the rotating body. Accordingly, when moving in the radial direction, the first and second inertia rings come into sliding contact. For this reason, the vibration damping performance of the torque fluctuation suppression device is the sliding resistance generated between the centrifuge moving in the radial direction of the rotating body and the first and second inertia rings swinging coaxially with the rotating body. It will be affected by (frictional force). Such sliding resistance between the centrifuge and the first and second inertia rings greatly affects the vibration damping performance and becomes a factor of deteriorating the vibration damping performance. Therefore, in the conventional torque fluctuation suppressing device, it is difficult to obtain a desired vibration damping effect.

  Accordingly, the invention of the present disclosure further improves the vibration damping performance of a vibration damping device including a restoring force generating member that swings as the support member rotates and an inertial mass that swings in conjunction with the restoring force generating member. The main purpose is to improve.

  The vibration damping device of the present disclosure includes a support member that rotates integrally with the rotation element around the rotation center of the rotation element to which torque from the engine is transmitted, and the torque is exchanged between the support member and the support member. A restoring force generating member coupled to the supporting member and swingable with the rotation of the supporting member; and coupled to the supporting member via the restoring force generating member and with the rotation of the supporting member; In a vibration damping device including an inertial mass body that swings around the rotation center in conjunction with a restoring force generating member, the supporting member, the restoring force generating member, and the inertial mass body are adjacent to each other in the axial direction. A sliding resistance reducing member is disposed between the two.

  In the vibration damping device of the present disclosure, the sliding resistance reducing member is disposed between two of the supporting member, the restoring force generating member, and the inertial mass body that are adjacent in the axial direction. Thereby, the sliding resistance between two adjacent to the axial direction among a support member, a restoring force generation member, and an inertial mass body can be reduced. As a result, it is possible to further improve the vibration damping performance of the vibration damping device including the restoring force generating member that swings as the support member rotates and the inertia mass body that swings in conjunction with the restoring force generating member. It becomes.

It is a schematic block diagram which shows the power transmission device containing the vibration damping device of this indication. It is sectional drawing which shows the vibration damping device of this indication, and a damper device combined with it. It is an enlarged view which shows the vibration damping device of this indication. It is sectional drawing which shows the other damping device of this indication, and a damper device combined with it. It is an enlarged view showing other vibration damping devices of this indication.

  Next, embodiments for carrying out the invention of the present disclosure will be described with reference to the drawings.

  FIG. 1 is a schematic configuration diagram illustrating a power transmission device 1 including a vibration damping device 20 of the present disclosure. A power transmission device 1 shown in FIG. 1 is mounted on a vehicle equipped with an engine (internal combustion engine) EG as a drive device, for example, and transmits power from the engine EG to a drive shaft DS of the vehicle. In addition to the vibration damping device 20, the power transmission device 1 includes a damper device 10 combined with the vibration damping device 20, a transmission TM, and a clutch C disposed between the damper device 10 and the transmission TM. including. The transmission TM includes an electric motor (not shown) connected to the input shaft IS, a transmission mechanism (not shown) connected to the input member Im, and an output member Om connected to the drive shaft DS. The transmission mechanism may include a planetary gear or a friction engagement element, or may be a dual clutch transmission or a continuously variable transmission. The clutch C connects the output shaft OS of the damper device 10 and the input member Im of the transmission and releases the connection between them. The clutch C may be a single-plate or multi-plate hydraulic clutch or dry clutch, a dog clutch, an electromagnetic clutch, or the like.

  The damper device 10 is configured as a dry damper, and includes a drive member (input element) 11 and a driven member (output element) 15 as rotating elements, as shown in FIGS. 1 and 2. Furthermore, the damper device 10 includes a plurality of springs (elastic bodies) SP disposed on the same circumference as torque transmitting elements. As the spring SP, an arc coil spring made of a metal material wound so as to have an arc extending in an arc shape when no load is applied, or an axis extending straight when no load is applied. A straight coil spring made of a metal material wound in a spiral shape is employed. As the spring SP, a so-called double spring may be employed.

  The drive member 11 of the damper device 10 is a metal annular member formed so as to define a space 12 in which the plurality of springs SP, the driven member 15 and the vibration damping device 20 are arranged. To the crankshaft (not shown) of the engine EG. Further, in the outer peripheral side region in the space 12 of the drive member 11, a plurality of spring contact portions (not shown) are formed at intervals in the circumferential direction so as to form a pair. As shown in FIG. 2, the driven member 15 includes a damper hub 16 as an output member fixed (connected) so as to rotate integrally with the output shaft OS, and an annular first member whose inner peripheral portion is fixed to the damper hub 16. 1 driven plate (support plate) 17 and an annular second driven plate (support plate) 18 whose inner periphery is fixed to the damper hub 16. The damper hub 16 and the first and second driven plates 17 and 18 are all made of metal.

  A plurality of spring contact portions 17c are formed on the outer peripheral portion of the first driven plate 17 so as to protrude outward in the radial direction at intervals in the circumferential direction and to form a pair of two. A plurality of spring abutting portions 18c are formed on the outer peripheral portion of the plate 18 so as to protrude radially outward at intervals in the circumferential direction and to form two pairs. The first and second driven plates 17 and 18 are fixed to the damper hub 16 so as to face each other with an interval in the axial direction, and each spring contact portion 17c of the first driven plate 17 is formed by the second driven plate. It opposes 18 corresponding spring contact parts 18c at intervals in the axial direction. Further, the first driven plate 17 is closer to the engine EG than the second driven plate 18, and the second driven plate 18 is closer to the transmission TM than the first driven plate 17. Furthermore, in this embodiment, the thickness of the 1st and 2nd driven plates 17 and 18 is mutually determined equally.

  In the mounted state of the damper device 10, both ends of each spring SP are in contact with corresponding ones of the two spring contact portions of the drive member 11 that are paired with each other. Further, both ends of each spring SP are in contact with corresponding ones of the two spring contact portions 17c of the first driven plate 17 and the two springs of the second driven plate 18 are paired with each other. It abuts on a corresponding one of the abutment portions 18c. Thereby, the drive member 11 and the driven member 15 are connected in the rotation direction via the plurality of springs SP. Further, the plurality of springs SP are arranged in the circumferential direction in the outer peripheral side region of the space 12 defined by the drive member 11.

  As shown in FIGS. 2 and 3, the vibration damping device 20 is provided between the first and second driven plates 17 and 18 as support members (support plates) and the first and second driven plates 17 and 18. A plurality (for example, three in this embodiment) of weight restoring members 22 connected to the first and second driven plates 17 and 18 so as to transmit and receive torque, and connected to the weights 22. One annular inertial mass body 23 and a plurality (for example, six in this embodiment) of connecting members 25 (see FIG. 3) are included.

  As shown in FIG. 3, the first driven plate 17 projects radially outward from the small-diameter portion between the adjacent spring contact portions 17 c in the circumferential direction at regular intervals (equally spaced). A plurality of (for example, three in this embodiment) protruding portions 172 are formed so as to be closer to the rotation center RC than the spring contact portion 17c. Each protrusion 172 is formed with one slit (opening) 173 extending in the radial direction of the first driven plate 17. Each slit 173 has a pair of flat inner surfaces 174 that extend in the radial direction of the first driven plate 17 and face each other at an interval in the circumferential direction of the first driven plate 17. Each functions as a torque transmission surface for transmitting and receiving torque to and from the weight body 22. In the present embodiment, as shown in FIG. 3, the slit 173 is formed so that the radially outer end is opened, but the slit 173 is formed so that the radially outer end is not opened. May be.

  In addition, the second driven plate 18 is formed so as to protrude radially outwardly (at equal intervals) from the small diameter portion between the adjacent spring contact portions 17c in the circumferential direction (at equal intervals). In the present embodiment, for example, three protrusions (not shown) are provided. One slit (opening) (not shown) extending in the radial direction is also formed in the protruding portion of each second driven plate 18. Each slit has a pair of flat inner surfaces that extend in the radial direction of the second driven plate 18 and are opposed to each other in the circumferential direction of the second driven plate 18. It functions as a torque transmission surface that transmits and receives torque to and from the body 22. The slit of the second driven plate 18 is also formed so that the radially outer end is opened, but the slit may also be formed so that the radially outer end is not opened.

  As can be seen from FIGS. 2 and 3, each weight body 22 is rotatable by two plate members (mass bodies) 220 having the same shape, one metal connecting shaft 221, and the connecting shaft 221. The outer ring 222 is supported by the outer ring 222. As shown in FIG. 3, each plate member 220 is formed of a metal plate so as to have a bilaterally symmetric and arcuate planar shape, and the two plate members 220 are connected to each other via one connecting shaft 221. The second driven plates 17 and 18 are connected to each other at their inner peripheral portions so as to face each other with an interval in the axial direction. As shown in FIG. 3, each plate member 220 has an outer peripheral surface and an inner peripheral surface formed by cylindrical surfaces.

  Further, each plate member 220 has two first guide portions 225 arranged so as to be arranged at intervals in the width direction (circumferential direction). The two first guide portions 225 are formed symmetrically with respect to the center line CL in the width direction of the plate member 220 passing through the center of gravity of the weight body 22 with respect to the plate member 220. Each first guide portion 225 is an opening extending like a bow, and as shown in FIG. 3, the rotation center RC of the first and second driven plates 17, 18 (driven member 15) on the inner peripheral side of the plate member 220. A first guide surface 226 that is a concave spherical surface that is recessed toward the side, and a first support surface 227 that is continuous with the first guide surface 226 and faces the first guide surface 226 on the outer peripheral side of the plate member 220.

  The connection shaft 221 is formed in a solid (or hollow) round bar shape, and as shown in FIGS. 3 and 4, the shaft center thereof is in the width direction (circumferential direction) of the weight body 22 (plate member 220). Fixed (coupled) to the two plate members 220 so as to pass through the center of gravity G of the weight body 22 on the center line CL (a straight line passing through the rotation center RC of the first and second driven plates 17 and 18 in the attached state of the weight body 22). ) The outer ring 222 has an outer diameter shorter than the distance between the pair of inner surfaces 174 of the first and second driven plates 17, 18 (width of the slit 173) and the radial direction length of the inner surface 174. The outer ring 222 is disposed so as to roll any one of the pair of inner surfaces 174 in the slits 173 of the protrusions 172 of the first driven plate 17, and in the slits of the protrusions of the second driven plate 18. It arrange | positions so that any one of a pair of inner surface may roll.

  Thereby, each weight body 22 is connected to the first and second driven plates 17 and 18 as support members so as to be movable in the radial direction, and slides with the first and second driven plates 17 and 18. Make an even number. Furthermore, the connecting shaft 221 and the outer ring 222 that rolls on any one of the inner surface 174 such as the corresponding slit 173 and the like, a torque transmission unit that transmits and receives torque between the first and second driven plates 17 and 18. Function as. The connecting shaft 221 may support the cylindrical outer ring 222 rotatably via a plurality of rollers or balls (rolling elements). The connecting shaft 221 supports the outer ring 222 rotatably without using the rolling elements. You may do. Further, the outer ring 222 may be omitted and the connecting shaft 221 may be slid on the inner surface 174 or the like.

  The inertia mass body 23 is an annular member formed of a metal plate. The thickness of the inertial mass body 23 is smaller than the distance between the first and second driven plates 17 and 18 in the axial direction, and the weight of the inertial mass body 23 is set to be sufficiently heavier than the weight of one weight body 22. It has been. In addition, as shown in FIG. 3, a plurality of (for example, six in this embodiment) second inertia mass bodies 23 are arranged so as to be arranged in pairs in pairs in the circumferential direction. A guide portion 235 is included. In the present embodiment, the two second guide portions 235 that form a pair are straight lines extending in the radial direction that divide the inertial mass 23 into three equal parts around the center (the number of weights 22). Are formed symmetrically with respect to a straight line that equally divides the inertial mass 23 by the same amount. Each second guide portion 235 is an opening extending like a bow, and as shown in FIG. 3, a concave spherical surface that is recessed on the outer peripheral side of the inertial mass body 23 on the side opposite to the rotation center RC, that is, radially outward. And a second support surface 237 that is continuous with the second guide surface 236 and faces the second guide surface 236 on the inner peripheral side of the inertial mass body 23. The inertia mass body 23 may be a stack of a plurality of plate members.

  The connecting member 25 is made of metal, and as shown in FIG. 3, the two first rolling portions (rollers) 251 and the second rolling members that are integrated with each other and extend coaxially. Part (roller) 252. In the present embodiment, the outer diameter of the first rolling portion 251 is determined to be smaller than the outer diameter of the second rolling portion 252, and the two first rolling portions 251 are at both ends of the second rolling portion 252. Projecting outward in the axial direction. The connecting member 25 may be formed solid or hollow. Further, the connecting member 25 may be a member in which a rod or tube forming the first rolling part 251 is fitted into a pipe forming the second rolling part 252.

  The first and second driven plates 17 and 18 as support members are arranged side by side in the axial direction between two plate members 220 constituting the weight body 22. The inertial mass body 23 is supported by the driven member 15 so as to be rotatable around the rotation center RC between the first and second driven plates 17 and 18 in the axial direction, and the first and second driven plates 23 and 18 are supported. It makes a pair even with the plates 17 and 18. Further, the two plate members 220 of the weight body 22 are connected to each other by the connecting shaft 221 so as to sandwich the first and second driven plates 17 and 18 (the projecting portion 172 and the like) and the inertia mass body 23 from both sides in the axial direction. They are connected to each other at the inner periphery. Further, as shown in FIG. 3, a notch 239 for eliminating interference with the outer ring 222 is formed in the inner peripheral portion of the inertia mass body 23. In addition, the inertia mass body 23 is formed with an opening (not shown) for eliminating interference with the connecting shaft 221 and the outer ring 222 of each cone 22.

  Further, as can be seen from FIG. 3, the first guide portion 225 of each plate member 220 of each weight body 22 and the second guide portion 235 of the inertial mass body 23 are located on the radially outer side than the connecting shaft 221. Each connecting member 25 is disposed in the corresponding first guide portion 225 of each plate member 220 and the corresponding second guide portion 235 of the inertial mass body 23. That is, each connecting member 25 corresponds so that each first rolling part 251 rolls on the corresponding first guide surface 226 and the second rolling part 252 rolls on the corresponding second guide surface 236. It arrange | positions between the 1st guide part 225 of the weight body 22, and the 2nd guide part 235 of the inertial mass body 23, and, thereby, each weight body 22 and the inertial mass body 23 are connected.

  Here, the first guide surface 226 of the first guide portion 225 of the weight body 22 and the second guide surface 236 of the second guide portion 235 of the inertial mass body 23 correspond to the first and second driven plates 17, 18. The first rolling portion 251 of the connecting member 25 rolls on the first guide surface 226 and the second rolling portion 252 rolls on the second guide surface 236 as the rotation rotates, whereby the center of gravity G of the weight body 22 is obtained. Oscillates (approaches and separates) along the radial direction with respect to the rotation center RC of the first and second driven plates 17 and 18, and is determined so that the relative position with respect to the inertial mass body 23 is not changed. It is formed so as to swing around the virtual axis while maintaining a constant distance L1 between the virtual axis and the virtual axis. The virtual axis is a point on a straight line (a straight line that equally divides the inertial mass 23 by the number of the weights 22) that divides the inertial mass 23 into three equal parts around the center. Is a straight line orthogonal to the inertial mass body 23 through a point separated from the center (rotation center RC) by a predetermined inter-axis distance L2.

  As described above, in the vibration damping device 20, each weight body 22 and the first and second driven plates 17, 18 form a sliding pair, and the first and second driven plates 17, 18 and the inertia mass body 23 include Make a turning pair. Furthermore, the first rolling portion 251 of the connecting member 25 can roll on the first guide surface 226, and the second rolling portion 252 can roll on the second guide surface 236. And the inertial mass body 23 form a slip pair. Thus, the first and second driven plates 17 and 18, the plurality of weight bodies 22, the inertia mass body 23, and the connecting member 25 constitute a slider crank mechanism (both slider crank chains). The equilibrium state of the vibration attenuating device 20 is such that the center of gravity G of each weight body 22 is located on a straight line passing through the corresponding virtual axis and the rotation center RC (see FIG. 3).

  Further, in the present embodiment, the plate member 220 and the inertia mass body 23 of each weight body 22 are arranged offset in the axial direction of the first and second driven plates 17 and 18 as support members, and the first and second The second driven plates 17 and 18 are arranged between the plate member 220 of each weight body 22 and the inertia mass body 23 in the axial direction. That is, the first driven plate 17 is disposed between one plate member 220 of each weight body 22 and the inertial mass body 23 in the axial direction, and the second driven plate 18 is the other plate member of each weight body 22. It arrange | positions between 220 and the inertial mass body 23 in the axial direction. As shown in FIG. 2, each weight body 22 and the inertia mass body 23 are disposed on the radially inner side of the plurality of springs SP of the damper device 10, and are at least partially axially connected to the plurality of springs SP as viewed from the radial direction. Overlapping directions.

  Further, as shown in FIGS. 2 and 3, each of the first and second driven plates 17 and 18 has a low static friction coefficient and a dynamic friction coefficient, such as polyamide resin such as nylon, fluorine resin, or the like (low μ material). A plurality of sliding resistance reducing members 90 formed by the above are attached. As shown in FIG. 2, each sliding resistance reducing member 90 is in sliding contact with the inner surface of the plate member 220 of the corresponding weight body 22, and the axial direction of the plate member 220 with respect to the first or second driven plate 17, 18. A first sliding contact portion 91 that restricts movement of the inertial mass body 23, and a first sliding contact portion 91 that slides on one surface of the inertial mass body 23 to regulate movement of the inertial mass body 23 in the axial direction relative to the first or second driven plate 17, 18. 2 sliding contact portions 92. That is, in each of the first and second driven plates 17, 18, the first sliding contact portion 91 is always opposed to the corresponding one of the two plate members 220 of each weight body 22 so as to be slidable and inertial. A plurality of sliding resistance reducing members 90 are attached so that the second sliding contact portion 92 always faces the mass body 23 and can slide. In addition, a movement restricting member 95 that restricts the movement of the drive member 11 in the axial direction toward the transmission TM (left side in FIG. 2) of the drive member 11 is attached to the first driven plate 17. A movement restricting member 96 that restricts the movement of the drive member 11 in the axial direction toward the engine EG (the right side in FIG. 2) is attached. In this embodiment, the sliding contact portions of the movement restricting members 95 and 96 with the drive member 11 are also formed of a polyamide resin such as nylon or a fluorine resin (low μ material) having a low static friction coefficient and a dynamic friction coefficient.

  Next, operations of the damper device 10 and the vibration damping device 20 of the power transmission device 1 will be described. In the power transmission device 1, when the engine EG as a prime mover is started, torque (power) from the engine EG is transmitted to the drive member 11, and the torque from the engine EC is shown in FIG. 11 and the plurality of springs SP and the driven member 15 are transmitted to the output shaft OS via a path. As a result, torque fluctuation from the engine EG is attenuated (absorbed) by the spring SP of the damper device 10.

  Further, when torque (power) from the engine EG is transmitted to the drive member 11, the first and second driven plates 17 and 18 (driven member 15) of the damper device 10 also rotate around the rotation center RC, The outer ring 222 supported by the connecting shaft 221 of the weight body 22 contacts either one of a pair of inner surfaces 174 such as a slit 173 corresponding to the rotation direction of the first and second driven plates 17 and 18. Further, each first rolling portion 251 of each connecting member 25 is pressed against the first guide surface 226 of the corresponding first guide portion 225 of the weight body 22 by the action of centrifugal force on the corresponding weight body 22. Further, the second rolling part 252 is pressed by the corresponding weight body 22 via the first rolling part 251 and pressed against the second guide surface 236 of the corresponding second guide part 235 of the inertial mass body 23. And the 2nd rolling part 252 of each connection member 25 receives the force by the inertia moment (rotation difficulty) of the inertial mass body 23, and on the corresponding 2nd guide surface 236 in the circumferential direction of the 2nd guide part 235. Roll toward one end. Accordingly, each first rolling part 251 of each connecting member 25 rolls on the corresponding first guide surface 226 toward the other end in the circumferential direction of the first guide part 225.

  As a result, when the first and second driven plates 17 and 18 rotate in one direction around the rotation center RC, each weight body 22 (center of gravity G) has two sets of first and second guide surfaces 226 and 236, and While being guided by the connecting member 25 and being restricted from rotating, the rotational center RC approaches the rotational center RC along the radial direction of the first and second driven plates 17 and 18. Further, the first rolling part 251 of each connecting member 25 rolls on the first guide surface 226 and the second rolling part 252 rolls on the second guide surface 236, whereby the center of gravity G of each weight body 22. Rotates around the imaginary axis while keeping the inter-axis distance L1 constant, and accordingly, the inertial mass body 23 rotates in the opposite direction with respect to the first and second driven plates 17 and 18 around the rotation center RC. Rotate relative to

  Further, the centrifugal force acting on the center of gravity G of each weight body 22 is inertial via the first guide surface 226, the first and second rolling portions 251 and 252 of the connecting member 25, and the second guide surface 236. It is transmitted to the mass body 23 and becomes a restoring force for returning the inertial mass body 23 to the position in the equilibrium state. Such a restoring force is at the end of the swing range of the weight body 22 determined according to the amplitude (vibration level) of vibration transmitted from the engine EG to the first and second driven plates 17 and 18 (driven member 15). The force (moment of inertia) that attempts to rotate the inertial mass 23 in the rotation direction so far is overcome. Thereby, each weight body 22 is guided by the two sets of first and second guide surfaces 226 and 236 and the connecting member 25, and the rotation of the weight body 22 is regulated along the radial direction of the first and second driven plates 17 and 18. Then, it moves in the opposite direction so as to be separated from the rotation center RC. Further, the inertial mass body 23 is moved toward the position in the equilibrium state around the rotation center RC while interlocking with each weight body 22 by the action of the restoring force from each weight body 22, that is, the component force of the centrifugal force. Rotates in the opposite direction.

  When the inertial mass body 23 reaches a position in an equilibrium state with the first and second driven plates 17 and 18 rotating in the one direction, the inertial mass body 23 is the same due to the moment of inertia (hardness to stop). Try to rotate further in the direction. Further, the second rolling portion 252 of each connecting member 25 receives a force due to the moment of inertia (hardness of stopping) of the inertial mass body 23 and corresponds on the second guide surface 236 in the circumferential direction of the second guide portion 235. Roll toward the other end. Accordingly, the first rolling part 251 of each connecting member 25 rolls on the corresponding first guide surface 226 toward one end in the circumferential direction of the first guide part 225. As a result, each weight 22 (center of gravity G) is guided by the two sets of first and second guide surfaces 226 and 236 and the connecting member 25 to restrict the rotation of the first and second driven plates 17 and 18. It approaches the rotation center RC again along the radial direction. Further, the first rolling part 251 of each connecting member 25 rolls on the first guide surface 226 and the second rolling part 252 rolls on the second guide surface 236, whereby the center of gravity G of each weight body 22. Rotates around the imaginary axis while keeping the inter-axis distance L1 constant, and accordingly, the inertial mass body 23 is rotated around the rotation center RC in the same direction with respect to the first and second driven plates 17, 18. Relative rotation.

  Also in this case, the centrifugal force acting on the center of gravity G of each weight body 22 is transmitted via the first guide surface 226, the first and second rolling portions 251 and 252 of the connecting member 25, and the second guide surface 236. Thus, the force is transmitted to the inertial mass 23 as the restoring force, and overcomes the force (inertia moment) for rotating the inertial mass 23 in the rotation direction up to that point at the end of the swing range. Thereby, each weight body 22 is guided by the two sets of first and second guide surfaces 226 and 236 and the connecting member 25, and the rotation of the weight body 22 is regulated along the radial direction of the first and second driven plates 17 and 18. To move away from the center of rotation RC. Further, the inertial mass body 23 rotates toward the position in the equilibrium state around the rotation center RC while interlocking with each weight body 22 by the action of the restoring force from each weight body 22, that is, the component force of the centrifugal force. .

  Thus, when the first and second driven plates 17 and 18 (driven member 15) rotate in one direction, each weight body 22 serving as a restoring force generating member of the vibration damping device 20 is driven from the engine EG to the driven member 15. With respect to the center of rotation RC along the radial direction of the first and second driven plates 17 and 18 within a swing range centered on the position in an equilibrium state determined according to the amplitude (vibration level) of vibration transmitted to Oscillate (reciprocate). Further, the inertia mass body 23 has a component of centrifugal force acting on each weight body 22 via the first guide surface 226, the first and second rolling portions 251 and 252 of the connecting member 25, and the second guide surface 236. The force is transmitted as a restoring force, and the inertia mass body 23 has a first and a second rotation center around the rotation center RC within a swing range centered on a position in an equilibrium state determined according to the swing range of each weight body 22. The second driven plates 17 and 18 swing (reciprocate and rotate) in the opposite direction to the vibrations.

  As a result, torque (inertia torque) having a phase opposite to the fluctuation torque (vibration) transmitted from the swinging inertial mass body 23 to the drive member 11 from the engine EG is applied to the second guide surface 236, the connecting member 25, and the first member. It can be applied to the first and second driven plates 17 and 18 via the guide surface 226. As a result, the order of vibration transmitted from the engine EG to the first and second driven plates 17 and 18 (excitation order: when the engine EG is a three-cylinder engine, when it is a 1.5-order and four-cylinder engine, 2 By determining the specifications of the vibration damping device 20 so as to have an order according to (next), the engine EG is driven by the vibration damping device 20 regardless of the rotational speed of the engine EG (first and second driven plates 17, 18). It is possible to attenuate the vibration transmitted from the first to the driven member 15 (first and second driven plates 17, 18). Therefore, when the clutch C is engaged, the vibration from the engine EG can be satisfactorily suppressed from being transmitted to the input member Im of the transmission TM by the damper device 10 and the vibration damping device 20.

  Further, each weight body 22 and the inertial mass body 23 are connected by the connecting member 25 that rolls on the first and second guide surfaces 226 and 236, so that the first guide surface 226 of the weight body 22 and the connecting member 25 can be connected to each other. The friction generated between the first rolling part 251 and between the second guide surface 236 of the inertial mass body 23 and the second rolling part 252 of the connecting member 25 is reduced, and the vibration damping performance of the friction is reduced. It becomes possible to make the influence smaller. In addition, the degree of freedom of shape change in the connecting member 25 having the first and second rolling portions 251 and 252 is high, and the connecting member 25 and the peripheral members can be easily contacted by optimizing the shape of the connecting member 25. Can be suppressed. As a result, the vibration damping performance of the vibration damping device 20 can be further improved. In addition, in the vibration damping device 20, the movement of the weight body 22 is defined (constrained) by the two sets of first and second guide surfaces 226 and 236 and the connecting member 25 that are arranged symmetrically with respect to the center line CL. Friction generated between the outer ring 222 on the center line CL and the first and second driven plates 17 and 18 when torque is transferred between the weight 22 and the first and second driven plates 17 and 18. The force can be reduced. As a result, the vibration damping performance of the vibration damping device 20 can be further improved.

  Further, in the vibration damping device 20, the first and second driven plates 17, 18, the plate member 220 of each weight body, and the two adjacent in the axial direction among the inertial mass bodies 23, that is, the first driven plate 17. Between the first driven plate 17 and the inertia mass body 23, between the second driven plate 18 and the other plate member 220 of each weight body 22, The first or second sliding contact portions 91 and 92 of each sliding resistance reducing member 90 are disposed between the two driven plates 18 and the inertia mass body 23. Thereby, the sliding resistance between two adjacent to the axial direction among the 1st and 2nd driven plates 17 and 18, the plate member 220 of each weight body, and the inertial mass body 23 can be reduced. As a result, it is possible to further improve the vibration damping performance of the dry vibration damping device 20 in which the first and second driven plates 17 and 18, the respective weight bodies 22, and the inertia mass body 23 are not disposed in the oil.

  Further, according to the research and analysis by the present inventors, the sliding resistance between each weight body 22 and the first and second driven plates 17 and 18, and the inertia mass body 23 and the first and second driven plates 17. , 18 does not significantly affect the vibration damping performance of the vibration damping device 20 as compared with the sliding resistance between each weight body 22 and the inertia mass body 23. Accordingly, the first or second driven plates 17 and 18 are disposed between the one plate member 220 of each cone 22 and the inertia mass body 23 in the axial direction, and the first and second driven plates 17 and 18 are disposed on the first and second driven plates 17 and 18. On the other hand, by attaching the sliding resistance reducing member 90 as described above, the vibration damping performance of the vibration damping device 20 can be further improved. Further, by attaching the sliding resistance reducing member 90 including the first and second sliding contact portions 91 and 92 to the first and second driven plates 17 and 18, each weight body 22 and the inertia mass body 23 are slid to each other. Without making contact, it is possible to sufficiently secure the weight of both to improve the vibration damping performance and to reduce the number of sliding resistance reducing members 90. In addition, by arranging the plurality of springs SP of the damper device 10 on the radially outer side of each weight body 22 and the inertia mass body 23, the rigidity of each spring SP is further reduced and the vibration damping performance of the damper device 10 is further improved. It becomes possible to improve.

  In the vibration damping device 20, the portion of each weight 22 of the first driven plate 17 that always faces the plate member 220, the portion of the first driven plate 17 that always faces the inertial mass 23, and the second driven plate 18. The portions of the weights 22 that always face the plate member 220 and the portions of the second driven plate 18 that always face the inertial mass body 23 may be coated with a low μ material such as polyamide resin or fluororesin. In the vibration damping device 20, a sliding resistance reducing member having a sliding contact portion that can slide on the first or second driven plate 17, 18 may be attached to the plate member of each weight body 22. A sliding resistance reducing member having a sliding contact portion capable of sliding contact with the first or second driven plate 17 or 18 may be attached to the mass body 23.

  Further, the first guide surface 226 may be a concave curved surface that is recessed on the side opposite to the rotation center RC, that is, radially outward, and the second guide surface 236 is on the side opposite to the first guide surface 226, that is, the rotation center. A concave curved surface recessed toward the RC side may be used. When each weight 22 is connected to the first and second driven plates 17 and 18 so as to transmit and receive torque via the connecting shaft 221, the outer ring 222, and a pair of inner surfaces 174 such as the slit 173, the outer ring 222 The rotation of each weight body 22 can be restricted by the inner surface 174 and the like, the pair of first and second guide surfaces 226 and 236, and the connecting member 25. Accordingly, the first and second guide surfaces 226 and 236 and the connecting member 25 may be provided one for each weight body 22.

  Further, the support member (two support plates) of the vibration damping device 20 may rotate integrally with the drive member 11 of the damper device 10. Further, the damper device 10 combined with the vibration damping device 20 transmits the torque between the intermediate element, the elastic member that transmits the torque between the drive member 11 and the intermediate element, and the intermediate element and the driven member 15. It may include an elastic body, or may include a plurality of intermediate elements. In these cases, the support member (two support plates) of the vibration damping device 20 may be configured to rotate integrally with any one of the drive member 11, the driven member 15, and the intermediate element. The damper device 10 may be configured as a wet damper device in which the drive member 11, the driven member 15, the spring SP, and the like are disposed in the oil, and the vibration damping device 20 includes the first and second driven plates 17. , 18, each weight body 22, inertia mass body 23, and the like may be configured as a wet vibration damping device arranged in oil.

  FIG. 4 is a cross-sectional view showing another vibration damping device 20B of the present disclosure and a damper device 10B combined therewith, and FIG. 5 is an enlarged view showing the vibration damping device 20B. Each weight body 22B of the vibration damping device 20B shown in these drawings is a metal plate member having a bilaterally symmetric and circular arc shape, and each weight body 22B has a connecting shaft 221B so as to protrude on both sides. Is fixed. Both end portions of the connecting shaft 221B rotatably support the outer ring 222, and the axis of the connecting shaft 221 has the center of gravity of the weight body 22B located on the center line in the width direction (circumferential direction) of the weight body 22B. Pass through. Furthermore, each weight body 22B has two first guide portions 225 (first guide surfaces 226) arranged so as to be arranged at intervals in the width direction (circumferential direction). The two first guide portions 225 are formed symmetrically with respect to the center line in the width direction of the plate member 220 passing through the center of gravity of the weight body 22B. Inertial mass body 23B of vibration damping device 20B includes two plate members 230 that are connected to each other via a connecting member (not shown) so as to face each other with an interval in the axial direction. Each plate member 230 has a plurality of second guide portions 235 arranged in pairs so as to be arranged in pairs in the circumferential direction.

  Further, as shown in FIG. 5, each coupling member 25B of the vibration damping device 20B is integrated with each other and has one round bar-like first rolling part 251 and two second rolling parts 252 that extend coaxially. Have In the example of FIG. 5, the outer diameter of the second rolling part 252 is determined to be smaller than the outer diameter of the first rolling part 251, and the two second rolling parts 252 are the same as the first rolling part 251. Projects axially outward from both ends. The connecting member 25 </ b> B may be formed solid or hollow, and a rod or tube forming the second rolling part 252 is fitted into the pipe forming the first rolling part 251. It may be a thing.

  As shown in FIG. 4, each weight body 22 </ b> B is disposed between the first and second driven plates 17 and 18 in the axial direction. In addition, one outer ring 222 supported by the connecting shaft 221 </ b> B of each weight body 22 </ b> B is disposed in the slit 173 of the first driven plate 17 so as to roll any one of the pair of inner surfaces 174. Further, the other outer ring 222 supported by the connecting shaft 221 </ b> B is arranged to roll one of a pair of inner surfaces (not shown) in a slit (not shown) of the second driven plate 18. The first and second driven plates 17 and 18 are arranged in the axial direction between the two plate members 230 of the inertial mass body 23B. Further, each connecting member 25B is disposed in the corresponding first guide portion 225 of the weight body 22B and the corresponding second guide portion 235 of the plate member 230. That is, each connecting member 25B rolls on the first guide surface 226 corresponding to the first rolling part 251 and the corresponding weight so that the second rolling part 252 rolls on the corresponding second guide surface 236. It arrange | positions between the 1st guide part 225 of the body 22B, and the 2nd guide part 235 of the inertial mass body 23B, and, thereby, each weight body 22B and the inertial mass body 23B are connected. In each of the first and second driven plates 17 and 18, the first sliding contact portion 91 is always opposed to the corresponding weight body 22 so as to be slidable, and the two plate members of the inertia mass body 23B. A plurality of sliding resistance reducing members 90 are attached so that the second sliding contact portion 92 always faces the corresponding one of 230 and can slide. Also in this vibration damping device 20B, the same effect as that of the above-described vibration damping device 20 can be obtained.

  As described above, the vibration damping device according to the present disclosure is the same as the vibration damping device according to the present disclosure, in which the rotational element (15) around which the torque from the engine (EG) is transmitted is rotated around the rotational center (RC). The support member (17, 18) that rotates integrally with the support member (15) and the support member (17, 18) are connected to the support member (17, 18) so as to transfer torque between the support member (17, 18) and the support member. A restoring force generating member (22, 22B) that can swing as the member (17, 18) rotates, and is connected to the support member (17, 18) via the restoring force generating member (22, 22B). And an inertia mass body (23, 23B) that swings around the rotation center (RC) in conjunction with the restoring force generating member (22, 22B) as the support member (17, 18) rotates. In the vibration damping device (20, 20B) including: A sliding resistance reducing member (90) between two axially adjacent ones of the supporting member (17, 18), the restoring force generating member (22, 22B) and the inertia mass body (23, 23B). Are arranged.

  In the vibration damping device of the present disclosure, the sliding resistance reducing member is disposed between two of the supporting member, the restoring force generating member, and the inertial mass body that are adjacent in the axial direction. Thereby, the sliding resistance between two adjacent to the axial direction among a support member, a restoring force generation member, and an inertial mass body can be reduced. As a result, it is possible to further improve the vibration damping performance of the vibration damping device including the restoring force generating member that swings as the support member rotates and the inertia mass body that swings in conjunction with the restoring force generating member. It becomes.

  The support member (17, 18) is disposed between at least a part of the restoring force generating member (22, 22B) and at least a part of the inertial mass body (23, 23B) in the axial direction. The axial direction between the support member (17, 18) and the restoring force generating member (22, 22B) and between the support member (17, 18) and the inertia mass body (23, 23B) may be sufficient. The sliding resistance reducing member (90) may be arranged between the axial directions. That is, according to the research and analysis of the present inventors, the sliding resistance between the restoring force generating member and the supporting member and the sliding resistance between the inertial mass body and the supporting member are It has been found that the vibration damping performance of the vibration damping device is not greatly affected compared to the sliding resistance between the two. Accordingly, the support member is disposed between at least a part of the restoring force generating member and at least a part of the inertial mass body in the axial direction, and between the supporting member and the restoring force generating member in the axial direction and between the supporting member and the inertial member. By disposing the sliding resistance reducing member in the axial direction with respect to the mass body, the vibration damping performance of the vibration damping device can be further improved.

  Further, one of the restoring force generating member (22, 22B) and the inertial mass body (23, 23B) is connected to two plate members (220, 230) so as to face each other with an interval in the axial direction. And the support member may include two support plates (17, 18) arranged side by side in the axial direction between the two plate members (220, 230). The other of the member (22, 22B) and the inertial mass (23, 23B) may be disposed between the two support plates (17, 18) in the axial direction, and the two support plates (17 , 18) includes a sliding resistance reducing member (90) corresponding to one of the two plates (17, 18), the restoring force generating member (22, 22B), and the inertia. Mer may be mounted so as to sliding contact with said other (23,23B). As a result, the restoring force generating member and the inertial mass body are not in sliding contact with each other, and the weight of both is sufficiently secured to further improve the vibration damping performance and to reduce the number of sliding resistance reducing members. It becomes possible.

  The restoring force generating member (22) may include the two plate members (220), and the inertia mass body (23) may be disposed between the two support plates (17, 18) in the axial direction. May be arranged.

  Further, the inertial mass body (23B) may include the two plate members (230), and the restoring force generating member (22B) is located between the two support plates (17, 18) in the axial direction. May be arranged.

  The vibration damping device (20, 20B) includes a first guide surface (226) provided on the restoring force generating member (22, 22B) and a first guide provided on the inertia mass body (23, 23B). Two guide surfaces (236), and a first rolling portion (251) and a second rolling portion (252) integrated with each other, the first rolling portion (251) being the first guide surface. (226) and a connecting member (25, 25B) disposed so that the second rolling portion (252) rolls on the second guide surface (236). The first and second guide surfaces (226, 236) roll on the first guide surface (226) by the first rolling part (251) as the support member (17, 18) rotates. The second rolling part (252) rolls on the second guide surface (236). The restoring force generating member (22, 22B) swings along the radial direction of the support member (17, 18) with respect to the rotation center (RC), and the inertia mass body (23, 23B) A centrifugal force acting on the restoring force generating member (22, 22B) when the supporting member (17, 18) rotates may be formed to swing around the rotation center (RC). A component force may be transmitted from the first guide surface (226) to the second guide surface (236) via the connecting member (25, 25B). Thus, the first and second guide surfaces are By connecting the restoring force generating member and the inertial mass body by the connecting member that rolls, between the restoring force generating member (first guide surface) and the connecting member (first rolling part) and the inertial mass body (first 2 guide surface) and the friction generated between the connecting member (second rolling part) And Fight, it is possible to further reduce the influence on the vibration damping performance of the friction. In addition, the degree of freedom of shape change in the connecting member having the first and second rolling portions is high, and the contact between the connecting member and peripheral members can be easily suppressed by optimizing the shape of the connecting member. .

  Further, the vibration damping device (20, 20B) is a dry-type device in which the support member (17, 18), the restoring force generating member (22, 22B) and the inertia mass body (23, 23B) are not disposed in oil. It may be. That is, the vibration damping performance of the dry vibration damping device is further improved by arranging the sliding resistance reducing member between two of the supporting member, the restoring force generating member, and the inertial mass body that are adjacent in the axial direction. Is possible. However, the vibration damping device (20, 20B) may be a wet device.

  The support member (17, 18) includes a plurality of rotating elements including at least an input element (11) and an output element (15), and torque between the input element (11) and the output element (15). May be rotated coaxially and integrally with any one of the rotating elements of the damper device (10, 10B) including the elastic body (SP) for transmitting the power.

  Furthermore, the elastic body (SP) may be arranged on the radially outer side of the restoring force generating member (22, 22B) and the inertia mass body (23, 23B). Thereby, it is possible to further improve the vibration damping performance of the damper device by further reducing the rigidity of the elastic body.

  The output element (15) may be operatively connected to an input member (Im) of the transmission (TM).

  And the invention of this indication is not limited to the above-mentioned embodiment at all, and it cannot be overemphasized that various changes can be made within the range of the extension of this indication. Furthermore, the mode for carrying out the invention described above is merely a specific form of the invention described in the Summary of Invention column, and does not limit the elements of the invention described in the Summary of Invention column. Absent.

  The invention of the present disclosure can be used in the field of manufacturing a vibration damping device that attenuates the vibration of a rotating element.

  DESCRIPTION OF SYMBOLS 1 Power transmission device, 10, 10B damper apparatus, 11 drive member, 12 space, 15 driven member, 16 damper hub, 17 1st driven plate, 17c spring contact part, 172 protrusion part, 173 slit, 174 inner surface, 18 2nd Driven plate, 18c Spring contact portion, 20, 20B vibration damping device, 22, 22B weight body, 220, 230 plate member, 221, 221B connecting shaft, 222 outer ring, 225 first guide portion, 226 first guide surface, 227 First support surface, 23, 23B inertial mass body, 235 second guide portion, 236 second guide surface, 237 second support surface, 239 notch, 25, 25B connecting member, 251 first rolling portion, 252 second Rolling part, 90 sliding resistance reducing member, 91 first sliding contact part, 92 second sliding contact part, 95, 96 Movement restriction member, C clutch, CL center line, DS drive shaft, EG engine, G center of gravity, Im input member, L1, L2 center distance, Om output member, OS output shaft, RC rotation center, SP spring, TM speed change Machine.

Claims (10)

A support member that rotates integrally with the rotation element around the rotation center of the rotation element to which torque from the engine is transmitted, and is connected to the support member so as to transfer torque between the support member and the support member A restoring force generating member that can swing with the rotation of the supporting member, and connected to the supporting member through the restoring force generating member and interlocked with the restoring force generating member with the rotation of the supporting member A vibration damping device including an inertial mass body that swings around the rotation center;
A vibration damping device in which a sliding resistance reducing member is disposed between two axially adjacent ones of the support member, the restoring force generating member, and the inertia mass body. The vibration damping device according to claim 1,
The support member is disposed between at least a part of the restoring force generating member and at least a part of the inertial mass body in the axial direction,
The vibration damping device in which the sliding resistance reducing member is disposed between the support member and the restoring force generating member in the axial direction and between the support member and the inertial mass body in the axial direction. The vibration damping device according to claim 1 or 2,
One of the restoring force generating member and the inertial mass body includes two plate members that are coupled to each other so as to face each other with an interval in the axial direction,
The support member includes two support plates arranged in the axial direction between the two plate members,
The other of the restoring force generating member and the inertial mass body is disposed between the two support plates in the axial direction,
The sliding resistance reducing member is attached to each of the two support plates so as to be in sliding contact with a corresponding one of the two plates, the restoring force generating member, and the other of the inertial mass bodies. Vibration damping device. The vibration damping device according to claim 3,
The restoring force generating member includes the two plate members,
The inertial mass body is a vibration damping device disposed between the two support plates in the axial direction. The vibration damping device according to claim 3,
The inertial mass includes the two plate members,
The restoring force generating member is a vibration damping device disposed between the two support plates in the axial direction. The vibration damping device according to any one of claims 1 to 5,
A first guide surface provided on the restoring force generating member;
A second guide surface provided on the inertia mass body;
The first rolling part and the second rolling part are integrated with each other, the first rolling part rolls on the first guide surface, and the second rolling part is on the second guide surface. And a connecting member arranged so as to roll,
As for the first and second guide surfaces, the first rolling part rolls on the first guide surface as the support member rotates, and the second rolling part rolls on the second guide surface. Thus, the restoring force generating member swings along the radial direction of the support member with respect to the rotation center, and the inertial mass body swings around the rotation center,
A vibration damping device in which a component of centrifugal force acting on the restoring force generating member is transmitted from the first guide surface to the second guide surface via the connecting member when the support member rotates. The vibration damping device according to any one of claims 1 to 6,
A vibration damping device, which is a dry device in which the support member, the restoring force generating member, and the inertia mass body are not disposed in oil. The vibration damping device according to any one of claims 1 to 7,
The support member is coaxial with a rotating element of any one of the damper devices including a plurality of rotating elements including at least an input element and an output element, and an elastic body that transmits torque between the input element and the output element. Vibration damping device that rotates together. The vibration damping device according to claim 8,
The elastic body is a vibration damping device that is disposed radially outside the restoring force generating member and the inertia mass body.   The vibration damping device according to claim 8 or 9, wherein the output element is operatively connected to an input shaft of a transmission.

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