JP2014206238A - Torsional vibration attenuation device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torsional vibration attenuation device which suppresses the resonance of a rotating body in the case that a rotation number is small and a damper, prevents or suppresses the generation of noise and vibration.SOLUTION: In a torsional vibration attenuation device, drive-side members 8, 9 and a driven-side member 11 are relatively rotatably connected to each other via an elastic body 12, and a rolling body 17 which reciprocates by a variation of torque is arranged at a rolling part 16 which is formed at an external peripheral part of the driven-side member 11. When the torque is transmitted to the driven-side member 11 from the drive-side members 8, 9, and a direction in which the driven-side member 11 relatively rotates with respect to the drive-side members 8, 9 is set as a forward rotation direction pr, the rolling body 17 is fixed to one end of the rolling part 16 in a state that the driven-side member 11 is not relatively rotated in the forward rotation direction pr due to the non-transmission of the torque to the driven-side member 11 from the drive-side members 8, 9, and when the driven-side member is relatively rotated in the forward rotation direction pr, fixing pieces 13 for releasing the fixation are arranged at the drive-side members 8, 9.

Description

  The present invention relates to an apparatus for attenuating torsional vibration of a rotating body that receives torque and, more particularly, to a torsional vibration damping apparatus configured to attenuate torsional vibration by reciprocating motion or pendulum motion of an inertial mass body. Is.

  An example of this type of device is described in Patent Document 1. The vibration reducing device described in Patent Document 1 includes an elastic damper configured to attenuate torsional vibration generated in a first rotating body to which engine torque is transmitted by expansion and contraction of a coil spring. The torsional vibration generated in the second rotating body connected to the first rotating body so as to be able to transmit power to the downstream side of the elastic damper in the transmission direction of the engine torque is attenuated by the swing of the pendulum. A pendulum damper is provided. That is, the device described in Patent Document 1 is configured to attenuate torsional vibration that cannot be damped by the elastic damper by the pendulum damper.

  Patent Document 2 discloses a disk-shaped main body, side plates disposed on both sides of the main body, and rolling holes that are formed through the main body and both side plates and accommodate rollers that are rolling elements. A device comprising: is described. Further, when the rotation speed of the main body and both side plates is high, the movable weight moves outward by centrifugal force to rotate the main body and both side plates integrally, and when the rotation speed is low, that is, the movable weight. In the case where the centrifugal force generated in the case is small, a spring that causes twisting of the main body and both side plates is provided. In the apparatus described in Patent Document 2, when the rotational speed is high, the rolling holes in the main body and the rolling holes in the both side plates coincide with each other, and the rollers reciprocate on the inner wall surface according to torsional vibration. . On the other hand, when the number of rotations is low, the rolling holes in the main body and the rolling holes in the side plates are displaced by the elastic force of the spring, so that the rollers are sandwiched and fixed by these rolling holes.

  Further, Patent Document 3 describes a device in which a pendulum is attached to a flywheel integrated with a crankshaft via a pin so as to be reciprocally movable. A mass body is disposed outside the pendulum in the radial direction of the flywheel, and the mass body is pressed inward in the radial direction by the elastic force of the leaf spring disposed outside the mass body in the radial direction. ing. That is, the elastic force of the leaf spring acts on the mass body so as to resist the centrifugal force generated in the mass body. A friction material is attached to the surface of the mass body that faces the pendulum. Therefore, in the device described in Patent Document 3, when the elastic force of the leaf spring overcomes the centrifugal force of the mass body due to, for example, the engine speed being low, the pendulum and the mass body are caused to friction by the elastic force. Because of contact through the material, the reciprocating motion of the pendulum is stopped. On the other hand, when the centrifugal force of the mass body overcomes the elastic force of the leaf spring due to the high engine speed, the mass body is separated from the pendulum by the centrifugal force. Become.

JP 2011-208774 A JP 2012-62962 A Japanese Patent No. 3135670

  In the apparatus described in Patent Document 1, for example, when the engine speed is low, if the vibration of the engine torque and the natural vibration of the pendulum damper resonate, abnormal noise or vibration may occur. Further, when the engine speed is low, the centrifugal force generated in the pendulum is small, and therefore the pendulum may move freely due to fluctuations in the engine torque. When the pendulum freely moves, abnormal noise or vibration may be generated even when the pendulum collides with its peripheral members. Thus, for example, by using a coil spring having low rigidity as the coil spring of the elastic damper described in Patent Document 1, it is conceivable that the elastic damper generates vibration damping capability even when the engine speed is low. However, in order to attenuate a large engine torque fluctuation by such a low rigidity coil spring, the torsion angle of the coil spring, that is, the torsion angle between the members connected via the coil spring, must be increased. Absent. Further, since the maximum settable torsion angle is limited mechanically or structurally, even if the rigidity of the coil spring is reduced by this, there is a limit to reducing the rigidity.

  By the way, if the configuration described in Patent Document 2 or Patent Document 3 is applied to the device described in Patent Document 1, the rolling element is fixed by the elastic force of the spring or leaf spring when the engine speed is low. Thus, it is possible to prevent or suppress the generation of abnormal noise and vibration caused by the resonance and rolling elements colliding with the peripheral members. Moreover, said fixation can be cancelled | released with the movable weight and the centrifugal force of a mass body which increase with a raise of engine speed. However, the devices described in Patent Document 2 and Patent Document 3 are provided with movable weights and mass bodies that generate centrifugal force, so that these movable weights and mass bodies not only increase the number of parts. , There is a possibility of increasing the material cost and processing cost.

  The present invention has been made paying attention to the above technical problem, and suppresses the resonance between the rotating body and the damper when the rotational speed of the rotating body is low, and prevents or suppresses the generation of abnormal noise and vibration. An object of the present invention is to provide a torsional vibration damping device that can perform the above-described operation.

  In order to achieve the above object, according to the first aspect of the present invention, the driving side member to which the torque output from the internal combustion engine is transmitted and the driven side member to transmit the torque to the output side member are interposed via the elastic body. And a rolling portion having a predetermined length in the circumferential direction is formed in a portion on the outer peripheral side of the driven side member, and the rolling portion is subjected to the torque variation of the driven side member. In the torsional vibration damping device in which the rolling elements reciprocating in the circumferential direction of the driven member are movably engaged, the elastic body is compressed from the drive side member to the driven side member to generate torque. When the direction in which the driven member is transmitted and rotated relative to the driving member is a positive rotating direction, torque is not transmitted from the driving member to the driven member. Is in phase with the drive side member A fixed piece that presses and fixes the rolling element against one end of the rolling part while not rotating in the normal rotation direction, and releases the fixation when the roller rotates relative to the positive rotation direction. It is provided in the member.

  The invention according to claim 2 is the torsional vibration damping device according to claim 1, wherein the driven member includes a ring gear that meshes with a gear of a starter motor that starts the internal combustion engine. .

  According to this invention, the drive side member and the driven side member are connected via the elastic body. Further, when torque is not transmitted from the drive side member to the driven side member and the driven side member does not rotate in the positive rotation direction relative to the drive side member, the fixing provided on the drive side member The rolling element is fixed to one end portion of the rolling portion by the piece, and torque is transmitted from the driving side member to the driven side member, so that the driven side member is relatively forwardly rotated with respect to the driving side member. When rotating, the above fixing is released. That is, when the driving side member and the driven side member are displaced from each other in the circumferential direction, that is, when twisting occurs, the rolling element is fixed, and the above fixing is released by eliminating the twisting. It is configured as follows. Therefore, for example, when a change in torque is input to the driven side member and the driven side member rotates in the reverse rotation direction with respect to the drive side member, the rolling element is fixed to one end portion of the rolling portion by the fixing piece. Therefore, generation | occurrence | production of the noise and vibration by a rolling element colliding with the peripheral member can be prevented or suppressed. Further, for example, even when the driven member is rotated by the starter motor and the driven member rotates in the reverse rotation direction relative to the driving member, the rolling element is fixed by the fixing piece. Can do. Therefore, it is possible to prevent or suppress the generation of abnormal noise and vibration when starting the internal combustion engine. Furthermore, since the driving side member and the driven side member are connected via the elastic body as described above, if the rigidity of the elastic body is reduced, the fluctuation in torque when the rotational speed of the internal combustion engine is low Can be attenuated by the expansion and contraction of the elastic body. That is, when the rotational speed of the internal combustion engine is low, it is possible to prevent or suppress the resonance between the vibration of the torque output from the internal combustion engine and the natural vibration of the rolling element and the resonance due to the pulling phenomenon. In addition to the above, the configuration is such that the rolling element is fixed by twisting the driving side member and the driven side member, and the above fixing is released by eliminating the twist, so the number of parts as an entire device increases. In addition, it is possible to reduce component costs and manufacturing costs.

It is a figure showing typically an example of a torsional vibration damping device concerning this invention. It is a figure which shows typically the operation area | region of a torsional damper and an idle damper. It is a figure which shows an example of the shape of a center plate. It is a figure which shows an example of the shape of a cover member. It is a figure which shows an example of the damper for idles typically. It is a figure which shows the state of the damper for idles when a center plate is rotated by a starter motor. It is a figure which shows the state of the idle damper in idling rotation speed. It is a figure which shows the state of the idle damper when an engine speed is higher than an idling speed. It is a figure which shows the state of the idle damper when an engine has stopped.

  Next, the present invention will be described more specifically. FIG. 1 is a diagram schematically showing an example of a torsional vibration damping device according to the present invention. A flywheel 2 is attached to a crankshaft 1 of an engine (not shown). The drive plate 4 in the torsional damper 3 is connected. The principle configuration of the torsional damper 3 is the same as that conventionally known. To briefly describe the configuration, the drive plate 4 that is the input-side rotator and the output-side rotator are shown. The driven plate 5 is arranged on the same axis so as to face each other so as to be relatively rotatable, and these members 4 and 5 are connected to each other via a spring 6 that is an elastic body in the rotational direction. Therefore, when relative rotation occurs between the drive plate 4 and the driven plate 5, that is, when twisting occurs, the members 4 and 5 are displaced from each other in the circumferential direction as described above. The spring 6 is expanded and contracted so that the torsion is attenuated.

  The radially inner portion of the driven plate 5 described above is connected to the radially inner portion of the cover member 8 by bolts 7. A cover member 9 is disposed so as to face the cover member 8, and the cover member 9 and the cover member 8 are integrated with each other on the inner peripheral side thereof. On the other hand, a hollow damper housing 10 is formed on the outer peripheral portion of these members 8 and 9. A center plate 11 is disposed between the cover member 8 and the lid member 9 and is rotatable relative to the members 8 and 9. The center plate 11 and the cover member 8 or the center plate 11 and the lid member 9 are arranged on the same axis. The members 8 and 11 are connected to each other at an inner portion in the radial direction via a spring 12 that is an elastic body with respect to the rotation direction. Therefore, when relative rotation occurs between the cover member 8 and the lid member 9 and the center plate 11, that is, when twisting occurs, these members 8 and 11 are connected to each other in the circumferential direction. When the spring 12 is displaced, the spring 12 expands and contracts, and the above-described twist is attenuated.

  Fixing pieces 13 that protrude toward the inside of the damper housing 10 are respectively provided on both side surfaces of the damper housing 10 in the rotation center axis direction. These fixing pieces 13 are configured so as to contact the side surfaces of the rolling elements and restrain the reciprocation when, for example, a twist occurs between the cover member 8 and the lid member 9 and the center plate 11 described above. Has been. The fixing piece 13 is provided only on one of the surface of the cover member 8 constituting the damper housing 10 that faces the lid member 9 and the surface of the lid member 9 that faces the cover member 8. It may be. The configuration of the fixed piece 13 will be described later.

  The rigidity, that is, the spring constant of the spring 12 is set smaller than the spring constant of the spring 6 in the torsional damper 3. More specifically, for example, the spring constant of the spring 12 is set so that the engine 12 can expand and contract when the engine speed is a low speed of about the idling speed and the engine torque fluctuates. The idling rotational speed is a rotational speed at which the engine is not working and can rotate independently. That is, the damper 14 constituted by the cover member 8, the lid member 9, and the center plate 11 described above is configured to attenuate torsional vibration smaller than the torsional vibration that can be attenuated by the torsional damper 3. The damper 14 will be referred to as an idle damper 14 in the following description. The cover member 8 and the lid member 9 described above correspond to the driving side member in the present invention, and the center plate 11 corresponds to the driven side member in the present invention.

  As shown in FIG. 1, the inner peripheral side of the center plate 11 is connected to a shaft portion 15, and the shaft portion 15 is connected to an input shaft of a transmission (not shown) so that power can be transmitted. In addition, a plurality of rolling chambers 16 are formed at regular intervals in the circumferential direction inside the damper housing 10 and on the outer peripheral portion of the center plate 11. The rolling chamber 16 is, for example, a hollow part formed through or penetrating the center plate 11, and a rolling element 17 is accommodated in the hollow part so as to be able to roll. . The rolling chamber 16 is formed, for example, in a fan shape, and a rolling surface 18 is formed on the inner wall surface on the outer peripheral side in the radial direction of the center plate 11 among the inner wall surfaces. The rolling surface 18 does not need to be a complete circular arc surface, and may be a curved surface whose curvature center or instantaneous center changes continuously. In other words, a pendulum damper is formed in the inside of the damper housing 10 and on the outer peripheral side portion of the center plate 11. In a state where centrifugal force is applied to the rolling element 17 and no force in the circumferential direction of the center plate 11 is applied, the rolling element 17 is pressed against the rolling surface 18, and the crank of the rolling surface 18 is The shaft 1 is moved to a position farthest from the rotation center axis of the shaft 1. This position is a neutral position on the rolling surface 18. Said rolling chamber 16 is equivalent to the rolling part in this invention.

  In the example shown in FIG. 1, the rolling element 17 is provided with disc portions 17 b having outer diameters larger than the outer diameter of the support shaft 17 a at both ends of the support shaft 17 a slightly longer than the thickness of the center plate 11. The cross-sectional shape is “H” shape. Therefore, the outer peripheral surface of the support shaft 17a is pressed against the rolling surface 18 by centrifugal force.

  A ring gear 19 is provided on the outer periphery of the center plate 11 exposed from the damper housing 10, and the ring gear 19 starts the cranking of the stopped engine before supplying fuel to the engine. The gears (not shown) are connected so as to be able to transmit power. When the starter motor is driven, the center plate 11 rotates in the forward rotation direction via the gear and the ring gear, so that the spring 12 is compressed and the center plate 11 and the cover member 8 rotate integrally. The crankshaft 1 is rotated in the forward rotation direction as the cover member 8 rotates in the forward rotation direction. That is, the engine is cranked.

  FIG. 2 is a diagram schematically showing the operation region of the torsional damper 3 and the idle damper 14. The idle damper 14 has a smaller input torque than the torsional damper 3, and It is configured to operate when the torque fluctuation is small. The operating region is indicated by symbol A. That is, the spring 12 of the idle damper 14 is configured to expand and contract due to the fluctuation of the engine torque when the output torque of the engine is small, so as to attenuate the fluctuation of the engine torque. For example, when the engine speed becomes higher than the idling speed, that is, the engine works, the torque input to the idle damper 14 also increases. The spring 12 is compressed by the large torque, and the cover member 8 and the center plate 11 rotate integrally. Therefore, the idle damper 14 does not operate when the engine speed is high.

  On the other hand, the spring constant of the spring 6 in the torsional damper 3 is set to a value larger than the spring constant of the spring 12, so that the spring 6 does not expand or contract due to the small engine torque fluctuation as described above. The engine is configured to expand and contract due to fluctuations in engine torque when the engine speed is higher than the idling speed. The operating region is indicated by symbol B. That is, the torsional damper 3 is configured not to operate when the engine speed is low, but to operate when the engine speed is high, so as to attenuate a large torsional vibration compared to the idle damper 14. It has become.

  FIG. 3 is a diagram showing an example of the shape of the center plate 11. In the example shown in FIG. 3, the forward rotation direction of the center plate 11 is indicated by reference sign pr and the reverse rotation direction is indicated by reference sign ir. In addition, a rolling element 17 is disposed at the end of the rolling chamber 16 in the reverse rotation direction ir in the circumferential direction of the center plate 11. A rolling chamber 16 is formed in a fan-like shape on the outer peripheral side of the center plate 11, and a window 11 a is formed on the inner side in the radial direction of the center plate 11 than the rolling chamber 16. FIG. 4 is a diagram illustrating an example of the shape of the cover member 8, and the fixing piece 13 described above is provided on the side surface of the cover member 8 that faces the rolling chamber 16. More specifically, as shown in FIG. 5, the fixed piece 13 has a cover member 8 so that the contact angle with the rolling element 17 disposed at the end of the rolling chamber 16 on the reverse rotation side becomes large. It is provided on the side. Further, in the example shown in FIG. 5, the fixed piece 13 is configured to come into contact with the outer peripheral surfaces of both the disk portions 17 b of the rolling element 17. In addition, in the edge part of the rolling chamber 16 mentioned above, by making the side surface of the disc part 17b of the rolling element 17 and the side surface of the set of fixed pieces 13 contact, that is, the rolling elements by the set of fixed pieces 13. You may comprise so that 17 may be pinched and fixed. A window 8a is formed at a portion on the inner side in the radial direction of the cover member 8 with respect to the fixed piece 13 and facing the window 11a described above. Although not shown in detail, a fixing piece 13 is also provided on the lid member 9, and the fixing piece 13 on the lid member 9 and the fixing piece 13 provided on the cover member 8 are symmetric with respect to the center plate 11. Is arranged. Moreover, the window 9a is formed in the part corresponding to the window 8a and the window 11a which were mentioned above in the cover member 9, and the spring 12 mentioned above is inserted over those windows 8a, 9a, 11a.

  Next, the operation of the torsional vibration damping device having the above-described configuration will be described. First, a case where the engine is started will be described. FIG. 6 is a diagram illustrating a state of the idle damper 14 when the center plate 11 is rotated by the starter motor. When the center plate 11 is rotated in the forward rotation direction pr by the starter motor, the rolling element 17 moves to the end of the rolling chamber 16 on the reverse rotation side by its own inertial force. Further, immediately after the center plate 11 is rotated by the starter motor, the cover member 8 is stopped by the inertial force, and apparently rotates in the reverse rotation direction ir with respect to the center plate 11. When the cover member 8 rotates in the reverse rotation direction ir, the fixed piece 13 moves to the reverse rotation side in the rolling chamber 16 and contacts the rolling element 17. That is, the fixed piece 13 presses and fixes the rolling element 17 to the end of the rolling chamber 16 in the reverse rotation direction ir of the center plate 11. In this state, since the cover member 8 and the center plate 11 are integrated with the rolling element 17 interposed therebetween, the members 8, 11, and 17 integrally rotate in the normal rotation direction pr. Then, the crankshaft 1 is rotated by the rotation of the cover member 8, and the engine is cranked.

  When the engine explodes and starts outputting torque, the cover member 8 rotates in the normal rotation direction pr so as to follow the rotation of the center plate 11 by the torque. That is, engine torque is transmitted from the cover member 8 to the center plate 11. FIG. 7 is a diagram illustrating a state of the idle damper 14 at the idling rotational speed. The engine state in which the engine speed is the idling speed is referred to as an idle state in the following description. In this idle state, as shown in FIG. 7, the spring 12 is in an expandable / contractable state, and when the engine torque varies in this state, the cover member 8 and the center plate 11 are displaced from each other in the circumferential direction. The spring 12 expands and contracts to attenuate the engine torque fluctuation described above. On the other hand, the rolling element 17 is pressed against the rolling surface 18 by centrifugal force and is in contact with the fixed piece 13. That is, the position of the rolling element 17 is positioned by the centrifugal force and the fixed piece 13, that is, fixed between the rolling surface 18 and the fixed piece 13. Therefore, even if the engine torque fluctuation described above is input to the center plate 11, the engine torque fluctuation cannot be attenuated by the reciprocating motion of the rolling elements 17.

  If the engine rotational speed becomes higher than the idling rotational speed due to an increase in the drive request amount for the engine, the engine torque input to the cover member 8 also increases. When the cover member 8 is rotated in the forward rotation direction pr with respect to the center plate 11 by the engine torque, the fixed piece 13 is moved in the forward rotation direction pr. Therefore, the fixed piece 13 is separated from the rolling element 17. Further, the spring 12 is compressed. As a result, the cover member 8 and the center plate 11 rotate integrally, the fixing of the rolling element 17 described above is released, and the rolling element 17 can reciprocate on the rolling surface 18. FIG. 8 shows this state. In this state and in the state where the force in the circumferential direction of the center plate 11 is not applied, the rolling element 17 is pressed against the rolling surface 18, and the rolling surface 18 is at a position farthest from the rotation center axis. Moved. That is, it exists in the neutral position in the rolling surface 18 mentioned above.

  On the other hand, when the engine torque fluctuates in the above-described state, acceleration in the circumferential direction is generated with respect to the center plate 11, and on the other hand, an inertial force acts on the rolling element 17 in the direction opposite to the acceleration. The moving body 17 rolls along the rolling surface 18. If the acceleration is due to torsional vibration, the rolling element 17 vibrates by reciprocating along the rolling surface 18, that is, pendulum movement, and the torsional vibration is attenuated. In the torsional damper 3, the spring 6 is expanded and contracted when the drive plate 4 and the driven plate 5 are displaced from each other in the circumferential direction, and the torsion is attenuated by the elastic force of the spring 6.

  Next, a case where the engine is stopped will be described. FIG. 9 is a diagram showing a state of the idle damper 14 when the engine is stopped. In this state, since the engine does not generate torque, the engine is rotated in the normal rotation direction pr by inertia torque, for example. As a result, there is a difference between the rotational speed of the cover member 8 and the rotational speed of the center plate 11, and the members 8 and 11 are displaced from each other in the circumferential direction. That is, the state is the same as the state shown in FIG. 6, and the reciprocation of the rolling element 17 is restricted.

  Therefore, according to the torsional vibration damping device having the above-described configuration, the cover member 8 and the center plate 11 are connected via the spring 12 having a small spring constant, so that the rolling element 17 reciprocates, that is, the vibration of the rolling element 17. And the resonance point of vibration of the engine torque are lowered. That is, since the fluctuation of the engine torque in the idle state is attenuated by the spring 12, it is possible to prevent or suppress the resonance between the vibration of the engine torque in the idle state and the reciprocation of the rolling element 17 and the resonance due to the reduction of the pull-in. it can. Further, when the engine is stopped or in an idle state, when the center plate 11 rotates in the reverse rotation direction ir with respect to the cover member 8, that is, when twisting occurs between these members 8 and 11, The rolling element 17 is pressed against and fixed to the end of the rolling chamber 16 by the fixed piece 13. Therefore, the rolling element 17 moves irregularly due to the small centrifugal force of the rolling element 17, and as a result, the rolling element 17 is prevented from colliding with the inner wall surface of the rolling chamber 16 to generate abnormal noise or vibration. Can be suppressed. Since the above-described twist also occurs when the engine is cranked by a starter motor, it is possible to prevent or suppress the above-described abnormal noise and vibration when the engine is started. When the engine speed becomes higher than the idling speed, the above-described restraint by the fixed piece 13 is released, so that the torsional vibration can be attenuated by the reciprocating motion of the rolling element 17.

  DESCRIPTION OF SYMBOLS 8 ... Cover member, 9 ... Cover member, 11 ... Center plate, 12 ... Spring, 13 ... Fixed piece, 16 ... Rolling chamber, 17 ... Rolling body.

Claims (2)

A drive-side member that transmits torque output from the internal combustion engine and a driven-side member that transmits torque to the output-side member are connected to each other via an elastic body so as to be relatively rotatable. A rolling portion having a predetermined length in the circumferential direction is formed in the portion, and a rolling element that reciprocates in the circumferential direction of the driven side member due to a variation in torque of the driven side member at the rolling portion. In the torsional vibration damping device provided movably,
When the torque is transmitted from the driving side member to the driven side member via the elastic body and the direction in which the driven side member rotates relative to the driving side member is defined as the positive rotation direction, the driving side Since the torque is not transmitted from the member to the driven side member, the driven body is not rotated relative to the driving side member in the positive rotation direction, and the rolling element is connected to one end of the rolling portion. A torsional vibration damping device characterized in that a fixing piece is provided on the drive side member to be fixed by pressing against a portion and releasing the fixing when rotating relative to the forward rotation direction.   The torsional vibration damping device according to claim 1, wherein the driven member includes a ring gear that meshes with a gear of a starter motor that starts the internal combustion engine.

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