JP2014126097A - Torsional vibration reduction device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torsional vibration reduction device which can reduce torsional vibration even in a high-torque region.SOLUTION: In the torsional vibration reduction device 1, rotation torque is transmitted while absorbing the torsional vibration between a first rotating member 10 and a second rotating member 20 by a coil spring 30 interposed between the first rotating member 10 and the second rotating member 20. One end of a push rod 33 extending to a direction which is the same with that of the coil spring 30 is connected to the first rotating member 10, a disc spring 34 is attached to the second rotating member 20 so as to oppose the other end of the push rod 33, and the push rod 33 is formed so that the other end of the push rod 33 abuts on the disc spring 34 when the coil spring 30 is compressed by a prescribed amount.

Description

  The present invention relates to a torsional vibration reducing device.

  Conventionally, a side plate to which rotational torque is transmitted from an engine as a drive source and a flange for transmitting rotational torque to an input shaft of a transmission are arranged so as to relatively rotate in the circumferential direction. There is known a clutch disk assembly in which a small-diameter coil spring and a large-diameter coil spring are incorporated so as to be elastically deformed according to the relative rotation of the side plate and the flange (see, for example, Patent Document 1).

  The small-diameter coil spring is compressed from a state where the torsion angle between the side plate and the flange is 0 ° to a predetermined value, and the large-diameter coil spring is compressed when the torsion angle between the side plate and the flange exceeds a predetermined value. It is designed to be compressed.

Japanese Utility Model Publication No. 1-149024

  However, in the clutch disk assembly disclosed in Patent Document 1, the large-diameter coil spring resonates in a high torque region where the rotational speed of the drive source is, for example, 2000 to 3000 rpm, and torsional vibration increases. There has been a problem that noise and vibration generated in a transmission and the like increase.

  Accordingly, an object of the present invention is to provide a torsional vibration reduction device capable of reducing torsional vibration in a high torque region as compared with the conventional one.

  In order to achieve the above object, the torsional vibration reducing device according to the present invention includes (1) a first rotating member attached to an input shaft of a drive transmission system and a second rotation in which rotational torque is transmitted from a driving source. A coil spring interposed between the first rotating member and the second rotating member and elastically deformed when the first rotating member and the second rotating member rotate relative to each other. A torsional vibration reducing device configured to transmit rotational torque while absorbing torsional vibration between the first rotating member and the second rotating member. A push rod extending in the same direction as the spring; and a disc spring that is elastically deformed in a longitudinal direction of the push rod; one end of the push rod is connected to the first rotating member; and the second rotation The disc spring is attached to the member. Mounted for facing the other end of the Sshuroddo, the push rod, the other end of the push rod when the coil spring is compressed a predetermined amount is formed so as to contact with the disc spring.

  With this configuration, the torsional vibration reduction device of the present invention is a disc spring in which a push rod having one end connected to the first rotating member is attached to the second rotating member when the coil spring is compressed by a predetermined amount. In addition, since the other end of the push rod is formed to contact, the disc spring is compressed and elastically deformed when the twist angle between the first rotating member and the second rotating member exceeds a predetermined value. start. At this time, the spring constant of the disc spring becomes smaller according to the amount of deformation. As a result, torsional vibration in a high torque region due to resonance is reduced.

  In the torsional vibration reduction device described in (1) above, (2) the push rod may be arranged in a space in the coil spring.

  With this configuration, the torsional vibration reduction device of the present invention has the push rod disposed in the space in the coil spring, and thus the device can be miniaturized by effectively using the space in the coil spring.

  According to the present invention, it is possible to provide a torsional vibration reduction device capable of reducing torsional vibration in a high torque region as compared with the conventional one.

It is a front view of the torsional vibration reducing device according to the embodiment of the present invention. It is AA direction arrow sectional drawing of FIG. It is a fragmentary sectional view of the torsional vibration reduction device concerning an embodiment of the invention. FIG. 4 is a side view of the push rod in FIG. 3. It is a BB direction arrow sectional view of Drawing 5. It is a diagram which shows the relationship between the twist angle and torque of the torsional vibration reduction apparatus which concerns on embodiment of this invention.

  Embodiments of a torsional vibration reducing device according to the present invention will be described below with reference to the drawings.

  As shown in FIGS. 1 to 3, the torsional vibration reduction device 1 according to the present embodiment includes a first rotating member 10, a second rotating member 20, and a plurality of coil springs 30. .

  The first rotating member 10 and the second rotating member 20 are annular bodies, and the coil spring 30 extends in the tangential direction of the first rotating member 10 and the second rotating member 20.

  The first rotating member 10 includes a hub plate 11 and a boss 12 provided at the center of the hub plate 11. The hub plate 11 includes an annular portion 13 that surrounds the boss 12 in the circumferential direction, and a plurality of projecting portions 14 that project radially outward from the annular portion 13. A spring accommodating space 15 for accommodating the coil spring 30 is formed therebetween.

  The inner peripheral portion of the annular portion 13 and the outer peripheral portion of the boss 12 are engaged with each other by known spline grooves and spline teeth, and rotational torque is transmitted from the annular portion 13 to the boss 12.

  The boss 12 is fitted with an input shaft 16 of a transmission that constitutes a drive transmission system of the vehicle. The vehicle drive transmission system includes a known differential, a drive shaft, wheels, and the like.

  The inner peripheral portion of the boss 12 and the outer peripheral portion of the input shaft 16 are engaged with each other by known spline grooves and spline teeth so that rotational torque is transmitted from the boss 12 to the input shaft 16.

  The second rotating member 20 has disk plates 21 and 22 formed so as to surround the boss 12 in the circumferential direction, and a clutch disk 23 formed so as to surround the disk plates 21 and 22 in the circumferential direction. The disk plates 21 and 22 are arranged so as to be coaxial with the boss 12 with the hub plate 11 sandwiched in the member thickness direction.

  An annular bushing 24 is fitted between the inner periphery of one disk plate 21 and the outer periphery of the boss 12, and between the inner periphery of the other disk plate 22 and the outer periphery of the boss 12. An annular bush 25 is fitted. These bushes 24, 25 play a role of coaxially positioning the disk plates 21, 22 with respect to the boss 12.

  Further, the disk plates 21 and 22 are connected to each other by a rivet 26 extending parallel to the axis of the boss 12 so as to rotate integrally around the boss 12 around the boss 12.

  A window hole 27 penetrating in the member thickness direction is formed in one disk plate 21 so as to face the above-described spring accommodating space 15, and a window penetrating in the member thickness direction is formed in the other disk plate 22. A hole 28 is formed to face the spring storage space 15. The above-described coil springs 30 are accommodated in the window holes 27 and 28.

  The clutch disk 23 includes an annular cushioning plate 29 and annular clutch linings 41 and 42. The cushioning plate 29 is attached to the disk plate 21 by rivets 26. As described above, the rivet 26 connects the disk plates 21 and 22 to each other.

  The clutch linings 41 and 42 are disposed so as to be positioned coaxially with the boss 12 with the cushioning plate 29 sandwiched in the member thickness direction. The clutch linings 41 and 42 are respectively attached to the cushioning plate 29 by rivets 43 extending in parallel to the axis of the boss 12.

  The clutch disk 23 is configured such that rotational torque is transmitted from the crankshaft of the engine that is a drive source, and the second rotating member 20 rotates integrally with the clutch disk 23 in accordance with the rotation of the crankshaft. It is like that.

  The coil spring 30 is interposed between the first rotating member 10 and the second rotating member 20. The coil spring 30 is elastically deformed when the first rotating member 10 and the second rotating member 20 are relatively rotated, and torsional vibration is generated between the first rotating member 10 and the second rotating member 20. It plays the role of transmitting rotational torque while absorbing.

  The coil spring 30 is housed in the spring housing space 15 and the window holes 27 and 28 facing the spring housing space 15. A resin spring seat 31 is attached to one end of the coil spring 30, and a resin spring seat 32 is attached to the other end of the coil spring 30.

  One spring seat 31 is configured to contact one of the projecting portions 14 facing each other across the spring storage space 15, and the other spring seat 32 is configured of the projecting portion 14 facing each other across the spring storage space 15. It is comprised so that it may contact | abut on the other.

  Furthermore, one spring seat 31 is configured to abut one of the edge portions facing the circumferential direction of the second rotating member 20 in the window holes 27 and 28 formed in the disk plates 21 and 22. The spring seat 32 is configured to come into contact with the other of the edge portions facing the circumferential direction of the second rotating member 20 in the window holes 27 and 28.

  Therefore, the coil spring 30 is compressed between the hub plate 11 of the first rotating member 10 and the disk plates 21 and 22 of the second rotating member 20 in a state where the coil spring 30 is compressed in the longitudinal direction in advance via the spring seats 31 and 32. Is intervening.

  That is, the coil spring 30 is used when the disk plates 21 and 22 are twisted toward the acceleration side R1 with respect to the hub plate 11 due to an increase in the number of rotations of the crankshaft of the engine when the vehicle is accelerated, or when the vehicle is decelerated. Due to the decrease in the number of rotations of the crankshaft, the disk plates 21 and 22 are compressed in any case where the disk plates 21 and 22 are twisted to the deceleration side R2 with respect to the hub plate 11.

  The amount of compression of the coil spring 30 increases in proportion to the twist angle between the hub plate 11 of the first rotating member 10 and the disk plates 21 and 22 of the second rotating member 20.

  Thus, during acceleration of the vehicle, the rotational torque of the engine is transmitted from the clutch disk 23, the disk plates 21, 22, the coil spring 30, the hub plate 11, the boss 12, and the input shaft 16 to the transmission, the differential device, and the drive shaft. The torsional vibration is absorbed between the first rotating member 10 and the second rotating member 20 due to the elastic deformation of the coil spring 30.

  When the vehicle is decelerated, the rotational torque of the wheels is transmitted from the drive shaft, differential gear, transmission, etc. to the input shaft 16, boss 12, hub plate 11, coil spring 30, disk plates 21 and 22, and clutch disk 23. The torsional vibration is absorbed between the first rotating member 10 and the second rotating member 20 due to the elastic deformation of the coil spring 30.

  The torsional vibration reduction device 1 according to the present embodiment is characterized by a push rod 33 extending in the same direction as the coil spring 30 and the push rod 33 as shown in FIGS. This is in the point of using a disc spring 34 that is elastically deformed in the longitudinal direction.

  One end of the push rod 33 is connected to the first rotating member 10, and the disc spring 34 is attached to the second rotating member 20 so as to face the other end of the push rod 33. That is, the push rod 33 and the disc spring 34 are interposed between the first rotating member 10 and the second rotating member 20.

  The disc spring 34 has a characteristic that the spring constant decreases as the amount of deformation increases. The change in the spring constant of the disc spring 34 depends on the ratio between the effective height of the spring and the plate thickness of the spring, and the change in the spring constant increases as the effective height with respect to the plate thickness increases. The disc spring 34 in the present embodiment has a washer shape with an opening formed at the center, but may have no opening formed at the center.

  In order to connect the push rod 33 to the first rotating member 10, the other spring seat 32 is formed with a rod hole 32 a penetrating in the same direction as the axis of the coil spring 30. The push rod 33 is inserted into the rod hole 32 a and the other end is located in the space of the coil spring 30.

  Further, in order to connect the push rod 33 to the first rotating member 10, the projecting portion 14 of the hub plate 11, which is a constituent element of the first rotating member 10, is arranged at one end of the push rod 33 in the member thickness direction. A support portion 33a for sandwiching is formed so as to face each other across the notch portion 33b.

  A pin hole 14a penetrating in the thickness direction of the member is formed in the protruding portion 14 of the hub plate 11, and a pin hole 33c penetrating in the same direction as the pin hole 14a is formed in the support portion 33a of the push rod 33. Has been. A pin 35 is inserted into the pin hole 33 c formed in the support portion 33 a of the push rod 33 and the pin hole 14 a formed in the protruding portion 14 of the hub plate 11, and one end portion of the push rod 33 is It is connected to the first rotating member 10.

  The disc spring 34 is disposed between one spring seat 31 and one end of the coil spring 30. That is, the disc spring 34 is attached to the disk plates 21 and 22 that are components of the second rotating member 20 via the one spring seat 31.

  Further, the torsional vibration reducing device 1 according to the present embodiment is characterized by the length of the push rod 33, in other words, the distance X1 between the other end of the push rod 33 and the disc spring 34, and the coil spring 30 is located. The point is that the other end of the push rod 33 is set to abut against the disc spring 34 when fixed compression is performed.

  That is, the other end of the push rod 33 comes into contact with the disc spring 34 when the coil spring 30 is compressed by a predetermined amount. Then, after the other end of the push rod 33 contacts the disc spring 34, the torsion angle between the hub plate 11 of the first rotating member 10 and the disk plates 21 and 22 of the second rotating member 20 becomes larger. The other end of the push rod 33 compresses the disc spring 34.

  The disc spring 34 is elastically deformed when the other end of the push rod 33 comes into contact with the first rotating member 10 and the second rotating member 20 relative to each other, and the first rotating member 10 and the second rotating member 20 plays a role of transmitting rotational torque while absorbing torsional vibration.

  Next, the operation of the torsional vibration reducing device 1 according to the present embodiment will be described.

  If the disk plates 21 and 22 are twisted to the acceleration side R1 with respect to the hub plate 11 with the increase in the number of rotations of the crankshaft of the engine at the time of acceleration of the vehicle, the rotational torque of the engine becomes the clutch disk 23 and the disk plate. 21, 22, coil spring 30, hub plate 11, boss 12, and input shaft 16 are transmitted to the wheels via a transmission, a differential, a drive shaft, and the like. At this time, the coil spring 30 is elastically deformed and absorbs torsional vibration between the first rotating member 10 and the second rotating member 20.

  When the vehicle is decelerating and the disc plates 21 and 22 are twisted to the deceleration side R2 with respect to the hub plate 11 as the rotational speed of the crankshaft of the engine decreases, the rotational torque of the wheels becomes the drive shaft and differential unit. The transmission is transmitted to the crankshaft of the engine via the input shaft 16, the boss 12, the hub plate 11, the coil spring 30, the disk plates 21 and 22, and the clutch disk 23. At this time, the coil spring 30 is elastically deformed and absorbs torsional vibration between the first rotating member 10 and the second rotating member 20.

  As described above, the coil spring 30 is compressed according to the torsion angle of the first rotating member 10 and the second rotating member 20 when the vehicle is accelerating or the vehicle is decelerating. Is compressed by a predetermined amount, the other end of the push rod 33 comes into contact with the disc spring 34. Thereafter, when the twist angle between the first rotating member 10 and the second rotating member 20 becomes larger, the other end of the push rod 33 compresses the disc spring 34.

  Therefore, during the acceleration of the vehicle, the rotational torque of the engine is transmitted from the disk plates 21 and 22 to the hub plate 11 also by the push rod 33 and the disc spring 34. At this time, the disc spring 34 is elastically deformed and absorbs torsional vibration between the first rotating member 10 and the second rotating member 20.

  Further, when the vehicle is decelerated, the rotational torque of the wheels is also transmitted from the hub plate 11 to the disk plates 21 and 22 by the push rod 33 and the disc spring 34. At this time, the disc spring 34 is elastically deformed and absorbs torsional vibration between the first rotating member 10 and the second rotating member 20.

  As shown in FIG. 6, when the torsion angles between the first rotating member 10 and the second rotating member 20 when the coil spring 30 is compressed by a predetermined amount are θ1 and θ2, the torsion angle is from 0 ° to θ1. Until the torsion angle reaches from 0 ° to θ2, the disc spring 34 is not compressed by the other end of the push rod 33, so that only the coil spring 30 is elastically deformed and the disc spring 34 is compressed. Does not elastically deform.

  That is, when the rotational torque of the engine is low, the torsional vibration reducing device 1 according to the present embodiment has the first rotating member 10 and the second rotating member 20 due to the rigidity of the coil spring 30 alone. Absorb torsional vibrations between.

  When the twist angle between the first rotating member 10 and the second rotating member 20 exceeds θ1 or θ2, the disc spring 34 is compressed by the other end of the push rod 33. The spring 34 is elastically deformed.

  That is, in the torsional vibration reduction device 1 according to the present embodiment, when the rotational torque of the engine becomes high, the first rotary member 10 and the second rotation are caused by the rigidity of the coil spring 30 and the disc spring 34. Torsional vibration is absorbed between the members 20.

  Further, since the spring constant of the disc spring 34 decreases as the amount of deformation increases, the rate of increase in rigidity decreases as the torsion angle between the first rotating member 10 and the second rotating member 20 increases. Become.

  Therefore, in the torsional vibration reduction device 1 according to the present embodiment, the coil spring 30 or the like does not resonate in the high rotational torque region F1 or F2 in which the rotational speed of the crankshaft of the engine is, for example, 2000 to 3000 rpm, Torsional vibration does not increase.

  Note that the other end of the push rod 33 is separated from the disc spring 34 when the twist angle between the first rotating member 10 and the second rotating member 20 does not satisfy θ1 or θ2.

  Further, by changing the length of the push rod 33, specifically, by changing the distance X 1 between the other end of the push rod 33 and the disc spring 34, the disc spring 34 is compressed by the push rod 33. The twist angle between the first rotating member 10 and the second rotating member 20 when starting can be adjusted.

  As described above, the torsional vibration reduction device 1 according to the present embodiment is compared with the conventional one between the first rotating member 10 and the second rotating member 20 in the high rotational torque region F1 or F2. Torsional vibration can be reduced, and therefore noise and vibration generated in a transmission or the like do not increase.

  Furthermore, in the torsional vibration reduction device 1 according to the present embodiment, since the push rod 33 is arranged in the space in the coil spring 30, the device can be miniaturized by effectively using the space in the coil spring 30. Can do.

  Note that the torsional vibration reduction device according to the present invention is not limited to the one exemplified in the above-described embodiment, and includes changes corresponding to the matters described in the claims.

  As described above, the torsional vibration reduction device according to the present invention has an effect of reducing torsional vibration in a high torque region, and is useful for a rotational torque transmission mechanism of various vehicles.

  DESCRIPTION OF SYMBOLS 1 ... Torsional vibration reduction apparatus, 10 ... 1st rotation member, 16 ... Input shaft (input shaft of a drive transmission system), 20 ... 2nd rotation member, 30 ... Coil spring (coil spring), 33 ... Push rod, 34 ... Belleville spring

Claims (2)

A first rotating member attached to the input shaft of the drive transmission system;
A second rotating member to which rotational torque is transmitted from a driving source;
A coil spring interposed between the first rotating member and the second rotating member, and elastically deformed when the first rotating member and the second rotating member rotate relative to each other,
A torsional vibration reducing device configured to transmit rotational torque while the coil spring absorbs torsional vibration between the first rotating member and the second rotating member;
A push rod extending in the same direction as the coil spring;
A disc spring that elastically deforms in the longitudinal direction of the push rod;
Connecting one end of the push rod to the first rotating member;
Attaching the disc spring to the second rotating member so as to face the other end of the push rod,
2. The torsional vibration reducing device according to claim 1, wherein the push rod is formed such that the other end of the push rod contacts the disc spring when the coil spring is compressed by a predetermined amount.   The torsional vibration reduction device according to claim 1, wherein the push rod is disposed in a space in the coil spring.

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