JP2016133123A - Damper device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damper deice capable of suppressing vibration or noise caused by resonance of the damper device during starting.SOLUTION: A damper device according to an embodiment is disposed between a first rotating shaft rotated by driving force of a motor and a second rotating shaft, and includes: a first rotating body which can be connected to the first rotating shaft, and is rotatable around a rotation center; a second rotating body which can be connected to the second rotating shaft, and is rotatable around the rotation center; and a first elastic part which is interposed between the first rotating body and the second rotating body in a compressed state, and is elastically compressed by set torque larger than a larger one of maximum toque at starting time up to an idle state of the motor and maximum torque at a period of time from the idling state of the motor to the stop, between the first rotating member and the second rotating member.SELECTED DRAWING: Figure 1

Description

  Embodiments described herein relate generally to a damper device.

  For example, a damper device provided between an output shaft of an engine and an input shaft of a transmission is known. The damper device includes, for example, two rotating bodies connected to an output shaft and an input shaft, and an elastic body and a friction material interposed between these rotating bodies. Such a damper device attenuates fluctuations in rotation input from the engine by an elastic body or a friction material.

  If the rotational speed of the damper device reaches the resonant rotational speed when the engine is started, resonance may occur and torque acting on the damper device may increase. In order to suppress vibration and noise due to resonance of such a damper device, for example, a technique for reducing the resonance rotational speed by reducing the torsional rigidity of the damper device or increasing the inertia moment of the damper device is known. .

Japanese Patent No. 4106153 Japanese Examined Patent Publication No. 4-57906

  The structure for suppressing vibration and noise due to resonance of the damper device as described above may make the damper device heavy or complicated, for example. For this reason, it is meaningful to have a simpler means for suppressing vibration and noise due to resonance of the damper device.

  An example of the problem to be solved by the present invention is to provide a damper device that can suppress vibration and noise due to resonance of the damper device at the time of starting.

  The damper device of the embodiment is a damper device provided between a first rotating shaft that rotates by a driving force of a prime mover and a second rotating shaft, and is connectable to the first rotating shaft. And a first rotating body rotatable around the rotation center and a second rotating body connectable to the second rotating shaft and rotatable around the rotation center, and in a compressed state Maximum torque at start-up until the prime mover is in an idle state between the first rotating member and the second rotating member, which is interposed between the first rotating member and the second rotating member. And a first elastic portion that is elastically compressed by a set torque that is larger than a larger value of the maximum torque until the prime mover stops from the idle state. This restricts the rotation of the first rotating body relative to the second rotating body during the start-up period until the prime mover enters the idle state and until the prime mover stops from the idle state. Is done. Therefore, vibration and noise due to resonance of the damper device are suppressed at the time of starting and until the prime mover stops from the idle state.

  The damper device is supported in a compressed state by either the first rotating body or the second rotating body, and the other of the first rotating body and the second rotating body. Between the first rotating body and the second rotating body when the first rotating body rotates relative to the second rotating body up to a predetermined angle. It further includes a second elastic portion that contacts either one of the rotating bodies and that elastically compresses when the first rotating body further rotates relative to the second rotating body. Therefore, when torque is input to the damper device, the transition from the relatively stationary state to the relatively rotating state of the first and second rotating bodies becomes smooth, and the vibration and noise during the transition are smoothed. Is suppressed.

  Further, in the damper device, the first elastic portion is supported in a compressed state by either the first rotating body or the second rotating body, and the first rotating body and the first rotating body are supported. It arrange | positions so that a clearance gap may be provided between either one of 2 rotary bodies. By providing the clearance, the first rotating body can be rotated by a certain amount relative to the second rotating body, so that, for example, when the engine is idling, the rotational fluctuation of the prime mover is directly transmitted to the second rotating shaft. Is suppressed, and noise and vibration are suppressed.

  The damper device further includes a limiting unit that restricts the first rotating body from rotating relative to the second rotating body in one direction around the rotation center. For example, when the prime mover is started, there is a case where the first rotational shaft of the prime mover is rotated via the damper device by rotating the second shaft by the motor. In this case, the restriction unit restricts the relative rotation of the first and second rotating bodies in the direction in which the torque difference is generated, so that vibration and noise due to resonance of the damper device can be more reliably suppressed at the time of starting.

  The damper device is connected to the second rotating body and is connectable to the third rotating body rotatable around the rotation center and the second rotating shaft, and rotates around the rotation center. A possible fourth rotating body, and the third rotating body is interposed between the third rotating body and the fourth rotating body, and the third rotating body rotates relative to the fourth rotating body. And a third elastic portion that compresses elastically. Therefore, the torsional rigidity of the entire damper device is reduced, and the generation of vibration and noise is suppressed.

FIG. 1 is a diagram schematically showing the structure of a vehicle according to the first embodiment. FIG. 2 is a front view of the damper device according to the first embodiment, partially cut away. FIG. 3 is a graph showing the number of rotations of the crankshaft and the torque input to the first spring of the first damper portion when the engine of the first embodiment is started. FIG. 4 is a graph showing the relationship between the torque input to the first damper portion of the first embodiment and the torsion angle of the first damper portion. FIG. 5 is a front view of the damper device according to the second embodiment, partially cut away. FIG. 6 is a front view schematically showing the first damper portion of the second embodiment. FIG. 7 is a graph showing the relationship between the torque input to the first damper portion of the second embodiment and the torsion angle of the first damper portion. FIG. 8 is a front view schematically showing a first damper portion in which the first plate is rotated to a predetermined angle relative to the second plate in the second embodiment. FIG. 9 is a front view schematically showing a first damper portion in which the first plate is further rotated with respect to the second plate in the second embodiment. FIG. 10 is a front view of the damper device according to the third embodiment, partially cut away. FIG. 11 is a graph showing the relationship between the torque input to the first damper portion of the third embodiment and the torsion angle of the first damper portion. FIG. 12 is a front view schematically showing a first damper portion of the third embodiment in which the first plate is rotated to a predetermined angle relative to the second plate. FIG. 13 is a front view schematically showing a first damper portion in which a torque difference larger than the rotatable torque is generated in the third embodiment. FIG. 14 is a front view of the damper device according to the fourth embodiment, partially cut away. FIG. 15 is a graph showing the relationship between the torque input to the first damper portion of the fourth embodiment and the torsion angle of the first damper portion.

  The first embodiment will be described below with reference to FIGS. 1 to 4. Note that a plurality of expressions may be written together for the constituent elements according to the embodiment and the description of the elements. It is not precluded that other expressions not described in the component and description are made. Furthermore, it is not prevented that other expressions are given for the components and descriptions in which a plurality of expressions are not described.

  FIG. 1 is a diagram schematically showing a structure of a vehicle 1 according to the first embodiment. FIG. 2 is a front view of the damper device 2 according to the first embodiment, partially cut away. 1 shows a cross section of the damper device 2 along the line F1-F1 in FIG.

  The damper device 2 is mounted on a vehicle 1 such as a four-wheeled vehicle. The damper device 2 is not limited to this, and may be mounted on another device. As shown in FIG. 1, the vehicle 1 includes a damper device 2, an engine 3, a transmission 4, a flywheel 5, and a starter motor 6. The engine 3 is an example of a prime mover.

  The engine 3 is, for example, a gasoline engine. The engine 3 has a crankshaft 31 that can rotate around the rotation center Ax. The crankshaft 31 is an example of a first rotating shaft. The engine 3 generates a driving force by burning fuel such as gasoline, and rotates the crankshaft 31 around the rotation center Ax by the driving force.

  In this specification, the direction perpendicular to the rotation center Ax is the radial direction of the rotation center Ax, the direction along the rotation center Ax is the axial direction of the rotation center Ax, and the direction rotating around the rotation center Ax is the circumferential direction of the rotation center Ax. Each is called.

  The transmission 4 can transmit the rotation of the engine 3 to, for example, an axle or a wheel. The transmission 4 has an input shaft 41 that can rotate about the rotation center Ax. The input shaft 41 is an example of a second rotating shaft. By rotating the input shaft 41 around the rotation center Ax, the transmission 4 can transmit the rotation to the axle and the wheels.

  The flywheel 5 is attached to the end of the crankshaft 31 of the engine 3 by, for example, bolts 51. The flywheel 5 is formed in a disk shape extending in the radial direction of the rotation center Ax. The flywheel 5 has a gear part 52. The gear portion 52 has a plurality of teeth provided at the outer peripheral end of the flywheel 5.

  The starter motor 6 has a motor shaft 61 and a pinion 62. The starter motor 6 can rotate the motor shaft 61 by driving. The pinion 62 is attached to the motor shaft 61 so as to be movable in the axial direction of the motor shaft 61.

  When the engine 3 starts driving, the pinion 62 is moved in the axial direction of the motor shaft 61 and meshes with the gear portion 52 of the flywheel 5. When the starter motor 6 is driven in this state, the starter motor 6 rotates the crankshaft 31 of the engine 3 via the flywheel 5. When the engine 3 is driven by fuel combustion, the pinion 62 is moved in the axial direction of the motor shaft 61 and is disengaged from the gear portion 52 of the flywheel 5.

  The damper device 2 is attached to the crankshaft 31 of the engine 3 via the flywheel 5 and is attached to the input shaft 41 of the transmission 4. That is, the damper device 2 is provided between the crankshaft 31 of the engine 3 and the input shaft 41 of the transmission 4.

  The engine 3 can rotate the input shaft 41 of the transmission 4 via the damper device 2. Similarly, the transmission 4 can rotate the crankshaft 31 of the engine 3 via the damper device 2. The damper device 2 attenuates rotational fluctuations of the engine 3 and the transmission 4.

  Hereinafter, the damper device 2 will be described in detail. The damper device 2 includes a first damper portion 21 on the engine 3 side, a second damper portion 22 on the transmission 4 side, and a clutch portion 23. The damper device 2 is not limited to this. FIG. 2 shows the first damper portion 21 of the damper device 2.

  The first damper portion 21 includes a first plate 211 on the engine 3 side, a second plate 212 on the transmission 4 side, eight seats 213 (shown in FIG. 2), and four first springs 214. And receive plate 215, a plurality of bolts 216, and a first friction portion 217. The first plate 211 is an example of a first rotating body. The second plate 212 is an example of a second rotating body. The first spring 214 is an example of a first elastic part. The number of seats 213 and first springs 214 is not limited to this.

  The first plate 211 is formed in a substantially annular shape extending in the circumferential direction of the rotation center Ax. Note that the shape of the first plate 211 is not limited to this. The first plate 211 includes an outer plate 211a, a first inner plate 211b, a second inner plate 211c, and a plurality of rivets 211d.

  The outer side plate 211a is formed in a substantially annular shape extending in the circumferential direction of the rotation center Ax. The outer peripheral portion of the outer plate 211 a is bent so as to approach the flywheel 5. The said outer peripheral part of the outer side board 211a is attached to the flywheel 5 with a some volt | bolt, for example. That is, the first plate 211 is connected to the crankshaft 31 of the engine 3 via the flywheel 5.

  An inner peripheral portion of the outer plate 211 a is separated from the flywheel 5. A first inner plate 211b is attached to a surface of the inner peripheral portion of the outer plate 211a facing the flywheel 5. Furthermore, the second inner side plate 211c is attached to the surface of the inner peripheral portion of the outer side plate 211a facing the opposite side of the flywheel 5 (right side in FIG. 1).

  The first and second inner plates 211b and 211c are formed in a substantially annular shape extending in the circumferential direction of the rotation center Ax. The outer diameters of the first and second inner plates 211b and 211c are smaller than the outer diameter of the outer plate 211a. The inner diameters of the first and second inner plates 211b and 211c are smaller than the inner diameter of the outer plate 211a.

  The first inner plate 211b and the second inner plate 211c are connected to each other via the outer plate 211a by a rivet 211d. In the axial direction of the rotation center Ax, the first inner plate 211b is separated from the second inner plate 211c.

  The outer side plate 211a, the first inner side plate 211b, and the second inner side plate 211c connected to each other by the rivet 211d can rotate integrally around the rotation center Ax. That is, the first plate 211 can rotate about the rotation center Ax.

  Four first openings 211e are provided in the first inner plate 211b. Similarly, four first openings 211e are provided in the second inner plate 211c. The first openings 211e extend in the circumferential direction of the rotation center Ax and are arranged at substantially equal intervals in the circumferential direction of the rotation center Ax. Note that the first opening 211e is not limited to this.

  The size and shape of the first opening 211e of the first inner plate 211b are substantially the same as the size and shape of the first opening 211e of the second inner plate 211c. The first opening 211e of the first inner plate 211b is disposed so as to overlap the corresponding first opening 211e of the second inner plate 211c.

  The second plate 212 is formed in a substantially annular shape extending in the circumferential direction of the rotation center Ax. Note that the shape of the second plate 212 is not limited to this. The inner peripheral portion of the second plate 212 is disposed between the first inner plate 211b and the second inner plate 211c of the first plate 211. The outer peripheral portion of the second plate 212 extends in the radial direction of the rotation center Ax from the outer peripheral ends of the first and second inner plates 211b and 211c. The outer peripheral portion of the second plate 212 is farther from the flywheel 5 than the outer plate 211 a of the first plate 211.

  The second plate 212 is provided with four second openings 212a. The second openings 212a extend in the circumferential direction of the rotation center Ax and are arranged at substantially equal intervals in the circumferential direction of the rotation center Ax. Note that the second opening 212a is not limited to this.

  In the circumferential direction of the rotation center Ax, the length of the second opening 212a is substantially the same as the length of the first opening 211e. In a state in which no torque acts on the damper device 2, the second opening 212a is disposed so as to overlap with the corresponding first opening 211e of the first and second inner plates 211b and 211c.

  As shown in FIG. 2, two sheets 213 are respectively disposed in the first and second openings 211 e and 212 a that are overlapped. The sheet 213 is disposed at both ends of the first and second openings 211e and 212a, which are disposed to overlap each other, in the circumferential direction of the rotation center Ax.

  The sheet 213 has a support wall 213a and a convex portion 213b. The support wall 213a can be swingably supported by the first and second inner plates 211b and 211c forming the first opening 211a. Furthermore, the support wall 213a can also be swingably supported by the second plate 212 that forms the second opening 212a. For this reason, the sheet 213 is supported by at least one of the first and second inner plates 211 b and 211 c and the second plate 212. The convex portion 213b projects from the support wall 213a in the circumferential direction of the rotation center Ax.

  The four first springs 214 are respectively disposed in the first and second openings 211e and 212a that are arranged to overlap each other, and extend in the circumferential direction of the rotation center Ax. Both ends of the first spring 214 are supported by the seat 213, respectively. The convex portion 213 b of the sheet 213 is inserted into the first spring 214.

  The first spring 214 is supported by at least one of the first and second inner plates 211 b and 211 c and the second plate 212 via the seat 213. Accordingly, the first spring 214 is interposed between the first plate 211 and the second plate 212 in the circumferential direction of the rotation center Ax.

  The lengths of the first and second openings 211e and 212a in the circumferential direction of the rotation center Ax are shorter than the natural length of the first spring 214. For this reason, the first spring 214 is interposed between the first plate 211 and the second plate 212 in a pre-compressed state. That is, the first spring 214 is compressed by at least one of the first plate 211 and the second plate 212 even when no torque acts on the damper device 2.

  The receive plate 215 is formed in an annular shape extending in the circumferential direction of the rotation center Ax. As shown in FIG. 1, the outer peripheral portion of the receive plate 215 is attached to the outer peripheral portion of the second plate 212 with a plurality of bolts 216.

  The receive plate 215 is further away from the flywheel 5 than the second plate 212. The receive plate 215 has a contact surface 215a facing the opposite side of the flywheel 5 (right side in FIG. 1). The contact surface 215a is formed to be substantially flat, but may have unevenness or inclination, for example.

  The first friction part 217 is interposed between the first plate 211 and the second plate 212. For example, the first friction portion 217 is attached to one of the first and second plates 211 and 212 and is pressed against the other of the first and second plates 211 and 212. As a result, the first friction portion 217 generates a frictional resistance torque (hysteresis torque) and suppresses the relative rotation of the first plate 211 with respect to the second plate 212.

  In such a first damper portion 21, the first plate 211 and the second plate 212 can transmit torque (rotation) to each other via the first spring 214. For example, when the crankshaft 31 of the engine 3 rotates, torque is transmitted from the first plate 211 to the second plate 212 via the first spring 214. Thereby, both the first plate 211 and the second plate 212 rotate around the rotation center Ax.

  Further, when the first plate 211 rotates relative to the second plate 212, the first spring 214 interposed between the first plate 211 and the second plate 212 becomes elastic. Compress. Thereby, the first damper portion 21 can attenuate fluctuations in the rotation of the crankshaft 31 of the engine 3. The detailed operation of the first damper portion 21 will be described later.

  The second damper portion 22 is used as a clutch disk. The second damper portion 22 includes a third plate 221 on the engine 3 side, a fourth plate 222 on the transmission 4 side, a second spring 223, a second friction portion 224, and two friction plates 225. And have. The third plate 221 is an example of a third rotating body. The fourth plate 222 is an example of a fourth rotating body. The second spring 223 is an example of a third elastic part.

  The third plate 221 is formed in a substantially annular shape extending in the circumferential direction of the rotation center Ax. Note that the shape of the third plate 221 is not limited thereto. The third plate 221 includes an outer plate 221a, a first inner plate 221b, a second inner plate 221c, and a plurality of rivets 221d.

  The outer plate 221a is formed in a substantially annular shape extending in the circumferential direction of the rotation center Ax. Friction plates 225 are attached to both surfaces of the outer peripheral portion of the outer plate 221a. The friction plate 225 is used as a clutch facing.

  A first inner plate 221b is attached to a surface of the inner peripheral portion of the outer plate 221a facing the flywheel 5. Further, in the axial direction of the rotation center Ax, the second inner plate 221c is disposed so as to overlap the first inner plate 221b with a gap.

  The first and second inner plates 221b and 221c are formed in a substantially annular shape extending in the circumferential direction of the rotation center Ax. The outer diameters of the first and second inner plates 221b and 221c are smaller than the outer diameter of the outer plate 221a. The inner diameters of the first and second inner plates 221b and 221c are smaller than the inner diameter of the outer plate 221a.

  The first inner plate 221b and the second inner plate 221c are connected to each other via the outer plate 221a by a rivet 221d. In the axial direction of the rotation center Ax, the outer plate 221a is disposed between the first inner plate 221b and the second inner plate 221c.

  The outer plate 221a, the first inner plate 221b, and the second inner plate 221c connected to each other by the rivet 221d can be integrally rotated about the rotation center Ax. That is, the third plate 221 can rotate around the rotation center Ax.

  Four third openings 221e are provided in the first inner plate 221b. Similarly, four third openings 221e are provided in the second inner plate 221c. The third openings 221e extend in the circumferential direction of the rotation center Ax and are arranged at substantially equal intervals in the circumferential direction of the rotation center Ax. Note that the third opening 221e is not limited to this.

  The size and shape of the third opening 221e of the first inner plate 221b are substantially the same as the size and shape of the third opening 221e of the second inner plate 221c. The third opening 221e of the first inner plate 221b is arranged to overlap the corresponding third opening 221e of the second inner plate 221c.

  The fourth plate 222 is formed in a substantially annular shape extending in the circumferential direction of the rotation center Ax. Note that the shape of the fourth plate 222 is not limited to this. The fourth plate 222 is disposed between the first inner plate 221b and the second inner plate 221c of the third plate 221.

  The fourth plate 222 is provided with four fourth openings 222a. The fourth openings 222a extend in the circumferential direction of the rotation center Ax and are arranged at substantially equal intervals in the circumferential direction of the rotation center Ax. Note that the fourth opening 222a is not limited to this.

  In the circumferential direction of the rotation center Ax, the length of the fourth opening 222a is substantially the same as the length of the third opening 221e. In a state in which no torque acts on the damper device 2, the fourth opening 222a is disposed so as to overlap the corresponding third opening 221e of the first and second inner plates 221b and 221c.

  The four second springs 223 are respectively disposed in the third and fourth openings 221e and 222a that are disposed to overlap each other, and extend in the circumferential direction of the rotation center Ax. Both ends of the second spring 223 are supported by, for example, sheets disposed in the third and fourth openings 221e and 222a, respectively.

  The second spring 223 is supported by at least one of the first and second inner plates 221b and 221c and the fourth plate 222 via a sheet, for example. Accordingly, the second spring 223 is interposed between the third plate 221 and the fourth plate 222 in the circumferential direction of the rotation center Ax. The second spring 223 may be supported on at least one of the third and fourth plates 221 and 222 in a pre-compressed state or may be supported in an uncompressed state.

  The fourth plate 222 is further provided with an insertion hole 222b. The insertion hole 222b is provided along the rotation center Ax. In other words, the insertion hole 222 b is provided at the center of the fourth plate 222.

  The input shaft 41 of the transmission 4 is inserted into the insertion hole 222b. For example, a spline is formed in the insertion hole 222 b and the input shaft 41. As a result, torque can be transmitted between the fourth plate 222 and the input shaft 41. That is, the fourth plate 222 is connected to the input shaft 41 and can rotate about the rotation center Ax together with the input shaft 41.

  The second friction part 224 is interposed between the third plate 221 and the fourth plate 222. The second friction part 224 is attached to one of the third and fourth plates 221 and 222 and is pressed against the other of the third and fourth plates 221 and 222. As a result, the second friction portion 224 generates a frictional resistance torque and suppresses the relative rotation of the third plate 221 with respect to the fourth plate 222.

  In such a second damper portion 22, the third plate 221 and the fourth plate 222 can transmit torque to each other via the second spring 223. When torque is input to at least one of the third plate 221 and the fourth plate 222, both the third plate 221 and the fourth plate 222 rotate around the rotation center Ax.

  Further, when the third plate 221 rotates relative to the fourth plate 222, the second spring 223 interposed between the third plate 221 and the fourth plate 222 is elastically elastic. Compress. Thereby, the second damper portion 22 can attenuate the rotational fluctuation of the rotation input to the third plate 221 and the fourth plate 222.

  In the present embodiment, the spring constant of the second spring 223 of the second damper portion 22 is different from the spring constant of the first spring 214 of the first damper portion 21. Further, the resonance rotational speed of the second damper portion 22 is different from the resonance rotational speed of the first damper portion 21. In addition, the 1st and 2nd damper parts 21 and 22 are not restricted to this.

  The clutch portion 23 is used as a clutch cover assembly and is used as a dry single plate clutch together with the second damper portion 22. The clutch unit 23 is not limited to this. The clutch unit 23 includes a cover 231, a diaphragm spring 232, two ring members 233, and a pressure plate 234.

  The cover 231 covers a part of the diaphragm spring 232, the ring member 233, and the pressure plate 234. The cover 231 is attached to the receive plate 215 of the first damper portion 21 with bolts 216. In this way, the second plate 212, the receive plate 215, and the cover 231 are connected to each other.

  The diaphragm spring 232 is made of metal, for example, and is formed in a substantially annular shape. The diaphragm spring 232 is not limited to this. The diaphragm spring 232 is sandwiched and supported by two ring members 233 and is displaceable (movable, swingable, and rotatable). The diaphragm spring 232 can be swung with a portion supported by the ring member 233 as a fulcrum by being pressed by, for example, a release bearing.

  The pressure plate 234 faces the outer plate 221 a of the third plate 221 of the second damper portion 22. The outer plate 221 a to which the friction plate 225 is attached is disposed between the receive plate 215 of the first damper portion 21 and the pressure plate 234. The two friction plates 225 face the contact surface 215 a of the receive plate 215 and the pressure plate 234.

  The diaphragm spring 232 pushes the pressure plate 234 toward the outer plate 221a of the third plate 221 to which the friction plate 225 is attached. As a result, the outer plate 221a to which the friction plate 225 is attached is sandwiched between the pressure plate 234 and the contact surface 215a of the receive plate 215.

  The pressure plate 234 and the receive plate 215 sandwich the outer plate 221a to which the friction plate 225 is attached, so that the second plate 212 of the first damper portion 21 and the second plate of the second damper portion 22 are caused by friction. Torque can be transmitted to and from the three plates 221. In other words, the second plate 212 is connected to the third plate 221. The second plate 212 is connected to the input shaft 41 via the third plate 221, the second spring 223, and the fourth plate 222.

  As described above, in the present specification, two connected members (for example, the second plate 212 and the third plate 221) do not need to be fixed to each other by means such as bolts, for example. (Rotation) can be transmitted. Further, another member may be interposed between the two connected members.

  When the diaphragm spring 232 is pushed by the release bearing, the diaphragm spring 232 swings and moves away from the pressure plate 234. As a result, the pressure plate 234 is separated from the outer plate 221a to which the friction plate 225 is attached. In other words, the connection between the second plate 212 and the third plate 221 is released. Thus, the second plate 212 is detachably connected to the third plate 221.

  As described above, the first damper portion 21 is attached to the crankshaft 31 of the engine 3 via the flywheel 5, and the second damper portion 22 is attached to the input shaft 41 of the transmission 4. In other words, the second damper portion 22 is attached to the transmission 4 side (output side) of the first damper portion 21. For this reason, the damper device 2 is interposed between the crankshaft 31 and the input shaft 41.

  For example, when the engine 3 rotates the crankshaft 31, torque is transmitted from the first plate 211 to the second plate 212, the third plate 221, and the fourth plate 222, and the fourth plate 222 is input. The shaft 41 is rotated. Thus, the crankshaft 31 of the engine 3 and the input shaft 41 of the transmission 4 can transmit torque (rotation) to each other via the damper device 2. The first damper portion 21 and the second damper portion 22 can each attenuate the rotational fluctuation of the rotation input to the damper device 2.

  Below, the effect | action of the 1st damper part 21 is demonstrated in detail. FIG. 3 is a graph showing the rotational speed of the crankshaft 31 and the torque input to the first spring 214 of the first damper portion 21 over time when the engine 3 of the first embodiment is started. is there. In this specification, when the engine 3 is started, the crankshaft 31 of the engine 3 is rotated by the starter motor 6 and then the engine 3 rotates the crankshaft 31 by combustion of the fuel by its own power. ) Is the period until.

  FIG. 3 shows the rotational speed of the crankshaft 31 by a two-dot chain line, and shows the torque input to the first spring 214 by a solid line. As shown in FIG. 3, when the starter motor 6 rotates the crankshaft 31 via the flywheel 5, the rotation speed of the crankshaft 31 increases with time. Furthermore, when the engine 3 rotates the crankshaft 31 by the combustion of fuel by itself, the rotation speed of the crankshaft 31 further increases.

  As the crankshaft 31 rotates, torque is input from the crankshaft 31 to the first plate 211 of the first damper portion 21 via the flywheel 5, and from the first plate 211 to the first spring 214. Torque is input. When the start of the engine 3 is completed and the engine 3 is in an idle state, the torque input to the first spring 214 is approximately 0 Nm.

As shown in FIG. 3, the torque input to the first spring 214 increases and decreases in the positive direction and the negative direction, forming a wavy graph. The torque in the positive direction in FIG. 3 indicates torque in one direction (positive rotation direction) around the rotation center Ax. The torque in the negative direction indicates the torque in the other direction (reverse rotation direction) around the rotation center Ax. Hereinafter, as indicated by a one-dot chain line in FIG. 3, the positive maximum value of the torque at the start of the engine 3 is referred to as T _{P +} and the negative maximum value of the torque is referred to as T _P− . The maximum torque values T _{P +} and T _P− are examples of the maximum torque at the start.

  FIG. 4 is a graph showing the relationship between the torque input to the first damper portion 21 and the torsion angle of the first damper portion 21 of the first embodiment. In the present specification, the torsion angle indicates a relative rotation angle of the second plate 212 with respect to the first plate 211.

  As shown in FIG. 4, the torque in the positive direction or the negative direction is input to the first plate 211 of the first damper portion 21, and the torque difference between the first plate 211 and the second plate 212. When the absolute value of (torque input to the first spring 214) reaches a predetermined rotatable torque Tm, the first plate 211 starts to rotate relative to the second plate 212 (torsion angle). Increase). The rotatable torque Tm is an example of a set torque. In other words, the first spring 214 is elastically compressed by the torque difference between the first plate 211 and the second plate 212 that is greater than or equal to the rotatable torque Tm, and the second plate 212 is compressed with respect to the second plate 212. One plate 211 rotates relatively.

The rotatable torque Tm is larger than the absolute values of the maximum torque values T _{P +} and T _P− . Such a rotatable torque Tm is set by a load (precompression load) acting on the first spring 214 compressed in advance. The pre-compressed first spring 214 is compressed by applying a load larger than the pre-compression load. In a state where the rotatable torque Tm is compressed so as to be larger than the absolute values of the maximum torque values T _{P +} and T _P− , the first spring 214 is moved between the first plate 211 and the second plate 212. Intervened between.

  The rotatable torque Tm is set, for example, in a range of 10 to 80% of the maximum torque shown in the specification table of the engine 3. It is more preferable that the rotatable torque Tm is set in a range of 20 to 70% of the maximum torque shown in the specification table of the engine 3. The rotatable torque Tm is not limited to this.

As described above, since the rotatable torque Tm is larger than the absolute values of the maximum torque values T _{P +} and T _P− when the engine 3 is started, the second plate 212 is compared with the second plate 212 when the engine 3 is started. The relative rotation of the one plate 211 is suppressed. In other words, the first damper portion 21 transmits the input torque to the input shaft 41 almost directly via the second damper portion 22 like a rigid body. The rotatable torque Tm is not only larger than the absolute values of the torque maximum values T _{p +} and T _p− when the engine 3 is started, but also the maximum torque value during the period until the engine 3 stops from the idle state. Greater than absolute value. That is, the rotatable torque Tm is larger than the larger one of the maximum torques T _{p +} and T _p− when the engine 3 is started and the maximum torque until the engine 3 stops from the idle state. For this reason, the rotation of the first plate 211 relative to the second plate 212 is also suppressed until the engine 3 stops from the idle state.

  When the start of the engine 3 is completed and the transmission 4 is in a state of transmitting the rotation of the engine 3 to the axle and wheels, the torque difference between the first plate 211 and the second plate 212 is larger than the rotatable torque Tm. May be. In this case, the first spring 214 is elastically compressed by the relative rotation of the first plate 211 with respect to the second plate 212. Thereby, the 1st damper part 21 attenuates rotation fluctuation.

In the damper device 2 according to the first embodiment, the first spring 214 is the maximum torque at the time of starting between the first plate 211 and the second plate 212 until the engine 3 enters an idle state. It is elastically compressed by a torque difference (rotatable torque Tm) larger than the larger one of T _{P +} and T _P− and the maximum torque until the engine 3 stops from the idle state. As a result, the first plate 211 rotates relative to the second plate 212 at the time of starting until the engine 3 becomes idle and between when the engine 3 stops from the idle state. Is limited. Therefore, vibration and noise due to resonance of the damper device 2 are suppressed during the start of the engine 3 and until the engine 3 stops from the idle state. With such a damper device 2, there is no need to increase the inertia (mass) of the damper device 2. Therefore, the damper device 2 and the vehicle 1 are reduced in weight, and the fuel efficiency of the vehicle 1 on which the damper device 2 is mounted is improved. Is possible. Furthermore, since it is not necessary to increase the number of parts of the damper device 2, the cost of the damper device 2 can be reduced.

  A second damper portion 22 having third and fourth plates 221 and 222 and a second spring 223 is provided on the transmission 4 side (output side) of the first damper portion 21. That is, the second damper portion 22 is connected in series to the output side of the first damper portion 21. Thereby, the torsional rigidity of the damper device 2 as a whole is reduced, and the occurrence of rattling noises and muffled noises is suppressed.

  The clutch part 23 can release the connection between the third plate 221 of the second damper part 22 and the second plate 212 of the first damper part 21. For this reason, the clutch part 23 cancels | releases the connection between the 3rd plate 221 and the 2nd plate 212 at the time of engine 3 start-up, and the vibration and noise by the resonance of the damper apparatus 2 at the time of start-up are suppressed. .

  Hereinafter, a second embodiment will be described with reference to FIGS. In the following description of the plurality of embodiments, components having the same functions as the components already described are denoted by the same reference numerals as those described above, and further description may be omitted. . In addition, a plurality of components to which the same reference numerals are attached do not necessarily have the same functions and properties, and may have different functions and properties according to each embodiment.

  FIG. 5 is a front view showing the damper device 2 according to the second embodiment with a part cut away. As shown in FIG. 5, the four first springs 214 of the second embodiment include two first springs 214A and two first springs 214B. The first spring 214A is an example of a first elastic part. The first spring 214B is an example of a second elastic part.

  Furthermore, the four first openings 211e of the first inner plate 211b include two first openings 211eA and two first openings 211eB. Similarly, the four first openings 211e of the second inner plate 211c include two first openings 211eA and two first openings 211eB. The four second openings 212a of the second plate 212 include two second openings 212aA and two second openings 212aB.

  The first spring 214A, the first opening 211eA, and the second opening 212aA are the same as the first spring 214, the first opening 211e, and the second opening 212a of the first embodiment, respectively. Are the same. On the other hand, as will be described below, the first spring 214B, the first opening 211eB, and the second opening 212aB are the same as the first spring 214, the first opening 211e, And the second opening 212a.

  The length of the second opening 212aB in the circumferential direction of the rotation center Ax is shorter than the natural length of the first spring 214B. The first spring 214B is disposed in the second opening 212aB of the second plate 212 in a pre-compressed state, and is supported by the second plate 212 via the sheet 213.

  FIG. 6 is a front view schematically showing the first damper portion 21 of the second embodiment. As shown in FIG. 6, in the circumferential direction of the rotation center Ax, the length of the first opening 211eB is longer than the length of the second opening 212aB. Therefore, in a state where no torque is applied to the damper device 2, the damper device 2 is supported by the first plate 211 (first and second inner plates 211b and 211c) and the seat 213 in the circumferential direction of the rotation center Ax. A gap G is provided between the first spring 214B.

  Below, the effect | action of the 1st damper part 21 of 2nd Embodiment is demonstrated. FIG. 7 is a graph showing the relationship between the torque input to the first damper portion 21 and the torsion angle of the first damper portion 21 of the second embodiment.

As in the first embodiment, the rotatable torque Tm of the first damper portion 21 is the absolute value of the maximum torque values T _{P +} and T _P− when the engine 3 is started, and the engine 3 stops from the idle state. Since the absolute value of the maximum torque until the engine 3 is larger than the larger one, the first plate 212 has a first torque with respect to the second plate 212 during the start of the engine 3 and until the engine 3 stops from the idle state. The relative rotation of the plate 211 is suppressed. For this reason, the first damper portion 21 applies the input torque almost directly to the second damper portion 22 like the rigid body during the start of the engine 3 and until the engine 3 stops from the idle state. Is transmitted to the input shaft 41 via.

  FIG. 8 is a front view schematically showing the first damper portion 21 in which the first plate 211 is rotated to a predetermined angle θ relative to the second plate 212 in the second embodiment. . When the start of the engine 3 is completed and the transmission 4 is in a state of transmitting the rotation of the engine 3 to the axle and the wheels, a torque difference larger than the rotatable torque Tm between the first plate 211 and the second plate 212. May occur. In this case, the first spring 214 </ b> A is elastically compressed by the relative rotation of the first plate 211 with respect to the second plate 212. On the other hand, the first spring 214B is separated from the first plate 211 and is not compressed.

  When a larger torque difference occurs between the first plate 211 and the second plate 212, the first plate 211 rotates relative to the second plate 212 to a predetermined angle θ. At this time, as shown in FIG. 8, the first spring 214 </ b> B supported by the seat 213 comes into contact with the first plate 211.

  FIG. 9 is a front view schematically showing the first damper portion 21 in which the first plate 211 is further rotated with respect to the second plate 212 in the second embodiment. As shown in FIG. 9, when a larger torque difference is generated between the first plate 211 and the second plate 212, the first spring 214 </ b> B also has the first plate 211 with respect to the second plate 212. Is compressed elastically by relatively rotating. As described above, the first damper portion 21 increases the torque difference generated between the first plate 211 and the second plate 212, so that the first spring 214A is compressed from the first state. The spring 214A and the first spring 214B are both compressed. In other words, the first spring 214A and the first spring 214B are sequentially compressed.

  In the damper device 2 of the second embodiment, the first spring 214B is configured so that the first plate 211 of the first plate 211 rotates when the first plate 211 rotates with respect to the second plate 212 to a predetermined angle θ. The second inner plates 211b and 211c are contacted and compressed. Thus, since the first spring 214B is compressed after the first spring 214A is compressed, the first damper portion 21 has two-stage torsional rigidity. For this reason, when the torque is input to the damper device 2, the first and second plates 211 and 212 are relatively stationary (precompression region) to relatively rotated (damper operating region). The transition becomes smoother. Therefore, it is possible to suppress vibrations from being generated in the vehicle 1 on which the damper device 2 is mounted, and the damper device 2 from generating noise.

  A third embodiment will be described below with reference to FIGS. 10 to 13. FIG. 10 is a front view of the damper device 2 according to the third embodiment with a part cut away. As shown in FIG. 10, the first spring 214, the first opening 211e, and the second opening 212a of the third embodiment are the same as the first spring 214B, the first opening 212a of the second embodiment. The opening 211eB is the same as the second opening 212aB.

  The first spring 214 is supported by the second plate 212 via the seat 213 in a pre-compressed state. In a state where no torque is applied to the damper device 2, the first and second inner plates 211 b and 211 c of the first plate 211 and the first spring supported by the seat 213 in the circumferential direction of the rotation center Ax. A gap G is provided between the first electrode 214 and the second electrode 214.

  Below, the effect | action of the 1st damper part 21 of 3rd Embodiment is demonstrated. FIG. 11 is a graph showing the relationship between the torque input to the first damper portion 21 and the torsion angle of the first damper portion 21 of the third embodiment. FIG. 12 is a front view schematically showing the first damper portion 21 in which the first plate 211 is rotated to a predetermined angle θ relative to the second plate 212 in the third embodiment. .

  Since a gap G is provided between the first and second inner plates 211b and 211c of the first plate 211 and the first spring 214, when torque is input to the first damper portion 21, The first plate 211 rotates relative to the second plate 212. When the first plate 211 rotates relative to the second plate 212 to a predetermined angle θ, the first spring 214 supported by the seat 213 contacts the first plate 211.

As in the first embodiment, the rotatable torque Tm of the first damper portion 21 is the absolute value of the maximum torque values T _{P +} and T _P− when the engine 3 is started, and the engine 3 stops from the idle state. Since the absolute value of the maximum torque up to is larger than the larger one, the first spring 214 is not elastically compressed during the start of the engine 3 and until the engine 3 stops from the idle state. . For this reason, the first plate 211 is restricted from rotating relative to the second plate 212 to be larger than the predetermined angle θ. Therefore, the first damper portion 21 applies the input torque almost directly to the second damper portion 22 like a rigid body during the start of the engine 3 and until the engine 3 stops from the idle state. To the input shaft 41.

  FIG. 13 is a front view schematically showing the first damper portion 21 in which a torque difference larger than the rotatable torque Tm is generated in the third embodiment. When the start of the engine 3 is completed and the transmission 4 is in a state of transmitting the rotation of the engine 3 to the axle and wheels, a torque difference larger than the rotatable torque Tm is present between the first plate 211 and the second plate 212. May occur. In this case, as shown in FIG. 13, the first spring 214 is elastically compressed, and the first plate 211 can rotate relative to the second plate 212 to be larger than a predetermined angle θ.

  In the damper device 2 of the third embodiment, the first spring 214 is supported in a compressed state by the second plate 212, and the first and second inner plates 211 b and 211 c of the first plate 211 are supported. It arrange | positions so that the clearance gap G may be provided between. For this reason, when a torque difference smaller than the rotatable torque Tm occurs between the first plate 211 and the second plate 212, the first plate 211 is relative to the second plate 212 by a certain amount. Can be rotated.

  For example, in a state where the torque difference generated between the first plate 211 and the second plate 212 is small, such as in an idle state, the first spring 214 is difficult to compress. For this reason, if there is no gap G, the first and second plates 211 and 212 are relatively difficult to rotate, and the damper device 2 is difficult to attenuate the rotational fluctuation of the engine 3. Thereby, the rotational fluctuation of the engine 3 is directly transmitted to the transmission 4, and there is a possibility that a rattling noise is generated in the transmission 4.

  However, since the gap G as in the present embodiment is provided, the first plate 211 can rotate relative to the second plate 212 by a certain amount. It is suppressed that it is transmitted directly to. Therefore, the occurrence of rattling noise in the transmission 4 is suppressed.

  In the second and third embodiments, the gap G is provided between the first spring 214 (214B) and the first and second inner plates 211b and 211c of the first plate 211. However, the gap G may be provided between the first spring 214 (214B) and the second plate 212.

  The fourth embodiment will be described below with reference to FIGS. 14 and 15. FIG. 14 is a front view showing the damper device 2 according to the fourth embodiment with a part cut away. As shown in FIG. 14, the first plate 211 of the fourth embodiment has a first stopper portion 211f. Further, the second plate 212 has a second stopper portion 212b. The first and second stopper portions 211f and 212b are an example of a limiting portion.

  The first stopper portion 211 f of the first plate 211 is disposed in the second opening 212 a of the second plate 212. The second stopper portion 212b of the second plate 212 is an end portion of the second opening 212a in the circumferential direction of the rotation center Ax. The first and second stopper portions 211f and 212b are not limited to this.

  In a state where no torque acts on the damper device 2, the first stopper portion 211f contacts the second stopper portion 212b. As a result, the first and second stopper portions 211f and 212b rotate relative to the second plate 212 in the reverse rotation direction, which is one direction around the rotation center Ax. Limit. On the other hand, the first and second stopper portions 211f and 212b allow the first plate 211 to rotate relative to the second plate 212 in the forward rotation direction.

  FIG. 15 is a graph showing the relationship between the torque input to the first damper portion 21 and the torsion angle of the first damper portion 21 according to the fourth embodiment. As shown in FIG. 15, even if a torque in the negative direction (reverse rotation direction) is input to the first damper portion 21, the torsion angle of the first damper portion 21 remains 0 rad. Note that the twist angle may slightly increase in the negative direction.

  In the damper device 2 of the fourth embodiment, the first and second stopper portions 211f and 212b restrict the first plate 211 from rotating relative to the second plate 212 in the reverse rotation direction. To do. For example, in the hybrid system, when the engine 3 is started, a motor provided on the transmission 4 side rotates the input shaft 41 instead of the starter motor 6 to rotate the crankshaft 31 of the engine 3 via the damper device 2. There are things to do. In this case, the direction in which the torque difference is generated between the first plate 211 and the second plate 212 is the reverse rotation direction. The first and second stopper portions 211f and 212b limit the relative rotation of the first and second plates 211 and 212 in the reverse rotation direction, so that vibration and noise due to resonance of the damper device 2 can be prevented at the time of starting. It is more reliably suppressed.

  In the state where the start of the engine 3 is completed and the transmission 4 transmits the rotation of the engine 3 to the axle and wheels (for example, when the vehicle 1 is traveling), the reverse rotation direction is between the first plate 211 and the second plate 212. This torque difference is unlikely to occur. For this reason, even if the first and second stopper portions 211f and 212b restrict the relative rotation of the first and second plates 211 and 212 in the reverse rotation direction, the first damper portion 21 rotates sufficiently. Variation can be attenuated.

  The above-described embodiments of the present invention do not limit the scope of the invention, but are merely examples included in the scope of the invention. An embodiment of the present invention is different from the above-described embodiment in that, for example, at least a part of a specific application, structure, shape, action, and effect is changed, omitted, and within the scope of the invention. It may be added.

  2 ... damper device, 3 ... engine, 211 ... first plate, 211f ... first stopper portion, 212 ... second plate, 212b ... second stopper portion, 214, 214A, 214B ... first spring, 221 ... 3rd plate, 222 ... 4th plate, 223 ... 2nd spring, 31 ... Crankshaft, 41 ... Input shaft, Ax ... Rotation center, G ... Gap.

Claims (5)

A damper device provided between a first rotating shaft and a second rotating shaft that are rotated by a driving force of a prime mover;
A first rotating body connectable to the first rotating shaft and rotatable about a rotation center;
A second rotating body connectable to the second rotating shaft and rotatable about the rotation center;
Until the prime mover is in an idling state between the first rotating member and the second rotating member interposed between the first rotating member and the second rotating member in a compressed state A first elastic portion that is elastically compressed by a set torque that is larger than the larger value of the maximum torque at the time of starting and the maximum torque until the prime mover stops from the idle state;
A damper device comprising:   The first rotary body and the second rotary body are supported in a compressed state, and a gap is provided between the first rotary body and the second rotary body. When the first rotating body rotates relative to the second rotating body up to a predetermined angle, either the first rotating body or the second rotating body is placed on the other 2. The damper device according to claim 1, further comprising a second elastic portion that contacts and elastically compresses when the first rotating body further rotates relative to the second rotating body.   The first elastic part is supported in a compressed state by one of the first rotating body and the second rotating body, and is either the first rotating body or the second rotating body. The damper device according to claim 1, wherein the damper device is disposed so as to provide a gap between the other.   The limiting part which restrict | limits that the said 1st rotary body rotates relatively to one direction around a rotation center with respect to a said 2nd rotary body is further provided in any one of Claim 1 thru | or 3. One damper device. A third rotating body connected to the second rotating body and rotatable about a rotation center;
A fourth rotating body connectable to the second rotating shaft and rotatable about the rotation center;
The third rotating body is interposed between the third rotating body and the fourth rotating body, and is compressed elastically by rotating the third rotating body relative to the fourth rotating body. An elastic part;
The damper device according to claim 1, further comprising:

Images