JP2011214614A - Damper mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damper mechanism increasing absorbable energy while suppressing rigidity of an elastic member.SOLUTION: The damper mechanism includes a drive plate 128; a hub 150 disposed opposing the drive plate 128, having a rotation center axis the same as the drive plate 128, and carrying out relative displacement a predetermined angle in a circumferential direction of the rotation center axis; and a spring damper 121 engaging with the drive plate 128 and the hub 150. In a region wherein the relative displacement of the hub 150 with respect to the drive plate 128 is relatively small, torsion energy is absorbed by the spring damper 121, and in a region wherein the relative displacement is relatively large, the torsion energy is absorbed by frictional resistance between the drive plate 128 and the hub 150 in addition to the spring damper 121.

Description

  The present invention relates to a damper mechanism, and more particularly to a damper mechanism capable of increasing energy that can be absorbed while suppressing rigidity of an elastic member.

  Japanese Patent Laying-Open No. 2002-13547 (Patent Document 1) discloses a damper for a hybrid drive device including a mechanism that interrupts transmission of power when a fluctuation torque by a power source reaches a predetermined value.

  Japanese Patent Laid-Open No. 5-240303 (Patent Document 2) includes a weak elastic body that is elastic in a low torque region, and first and second elastic members that are elastic in a medium torque region and a high torque region. A swing vibration damper is shown.

  In Japanese Patent Laid-Open No. 2002-174259 (Patent Document 3), in a pipe joint having a fitting portion composed of inner and outer shafts that allow relative rotation to be fitted to each other, a relative force due to a torque fluctuation is generated by a frictional force generated on a screw surface. It has been shown to inhibit rotation.

JP 2002-13547 A JP-A-5-240303 JP 2002-174259 A

  In the damper described in the cited document 1, when a transiently large torque is input, a torque larger than the limiter torque may be input. If the spring rigidity is increased in order to prevent this, the characteristics (noise characteristics, etc.) in the low torque region deteriorate.

  Even in the apparatus described in the cited document 2, the above problem is not sufficiently solved. The apparatus described in the cited document 3 relates to a “pipe joint”, and is completely different from the present invention related to a damper mechanism including an elastic member.

  This invention is made | formed in view of the above problems, and the objective of this invention is providing the damper mechanism which can increase the energy which can be absorbed, suppressing the rigidity of an elastic member. .

  The damper mechanism according to the present invention has a first rotation member and a rotation center axis that is disposed opposite to the first rotation member and has the same rotation center axis as that of the first rotation member. In the region where the relative displacement of the second rotating member relative to the first rotating member is relatively small, the second rotating member capable of rotating, and the first rotating member and the elastic member engaged with the second rotating member. In the region where the relative displacement of the second rotating member relative to the first rotating member is relatively large, the torsional energy is generated by the frictional resistance between the first rotating member and the second rotating member in addition to the elastic member. To absorb.

  In one embodiment, in the damper mechanism, the first rotating member has a first cylindrical portion, and the second rotating member has a second cylindrical portion that fits on the inner peripheral side of the first cylindrical portion. In the region where the taper screw mechanism is provided between the inner peripheral surface of the first cylindrical portion and the outer peripheral surface of the second cylindrical portion, and the relative displacement of the second rotating member with respect to the first rotating member is relatively large. The torsional energy is absorbed by the frictional resistance of the taper screw mechanism in addition to the elastic member.

  In one embodiment, in the damper mechanism, the first rotating member includes a first plate-shaped portion, the second rotating member includes a second plate-shaped portion, and the first plate-shaped portion and the second plate-shaped portion are: A predetermined gap is provided between the first rotating member and the second rotating member, and the predetermined gap is provided so as to change along the circumferential direction of the first rotating member and the second rotating member. In a relatively large region, the torsional energy is absorbed by the frictional resistance between the first plate-like portion and the second plate-like portion in addition to the elastic member.

  In one embodiment, in the damper mechanism, the first rotating member is connected to the output shaft of the internal combustion engine, and the second rotating member is connected to the input shaft of the power transmission device.

  In one embodiment, in the damper mechanism, the first rotating member is coupled to the output shaft of the internal combustion engine via a torque limiter.

  ADVANTAGE OF THE INVENTION According to this invention, the damper mechanism which can increase the energy which can be absorbed, suppressing the rigidity of an elastic member can be provided.

It is a top view of the damper mechanism concerning one embodiment of the present invention. It is II-II sectional drawing in FIG. It is a top view of the radial plate contained in the damper mechanism shown in FIG. It is a figure which shows the relationship between a twist angle and a torque absorption amount. It is a figure for demonstrating the damper mechanism which concerns on the modification of one embodiment of this invention.

  Embodiments of the present invention will be described below. Note that the same or corresponding portions are denoted by the same reference numerals, and the description thereof may not be repeated.

  Note that in the embodiments described below, when referring to the number, amount, and the like, the scope of the present invention is not necessarily limited to the number, amount, and the like unless otherwise specified. In the following embodiments, each component is not necessarily essential for the present invention unless otherwise specified.

  FIG. 1 is a plan view of a damper mechanism according to the present embodiment. 2 is a cross-sectional view taken along the line II-II in FIG.

  1 and 2, a damper mechanism 100 according to the present embodiment includes a damper mechanism provided between an output shaft of an engine and an input shaft such as a transmission, or an engine (internal combustion engine) in a hybrid vehicle. This is a damper mechanism provided between the output shaft of the engine and the rotary shaft of the rotating electrical machine (motor / generator), and can be used for absorbing torque fluctuations in other power transmissions.

  In the damper mechanism 100, the input shaft 160 is spline-fitted, and a hub 150 (second rotating member) provided to be rotatable around the rotation center axis a <b> 1 and the hub 150 in the rotation direction of the hub 150. A drive plate (first rotating member) 128 that is relatively rotatable with respect to the drive plate 128 and a spring damper 121 (elastic member) that engages with the drive plate 128 and the hub 150 are provided. Four spring dampers 121 are provided in the circumferential direction.

  The damper mechanism 100 includes a flywheel 200 that is fixed to a crankshaft 300 that can be rotationally driven coaxially with the rotation center axis a1 of the input shaft 160 by power from the engine. The outer peripheral part of the flywheel 200 and the outer peripheral part of the drive plate 128 are connected by a torque limiter 140. The torque limiter 140 can control the torque applied from the flywheel 200 to the drive plate 128.

  FIG. 3 is a plan view of the radial plate 153. As shown in FIG. 3, the hub 150 (second rotating member) includes a cylindrical portion 151 that can receive the input shaft 160, and a disk portion that is continuously provided outward from the outer peripheral surface of the cylindrical portion 151. 152 and a radial plate 153 extending radially from the disk portion 152. The radial plates 153 are arranged at four positions with a 90-degree pitch in the circumferential direction. At the tip of each radial plate 153, an engaging portion 154 with the spring damper 121 is provided.

  On the other hand, the drive plate 128 (first rotating member) includes an inner plate 128 a disposed on the side facing the flywheel 200 and an outer plate 128 b positioned on the opposite side of the radial plate 153 from the inner plate 161. . The inner plate 128a and the outer plate 128b are integrated by a rivet 148. An annular plate 126 that is in pressure contact with the radial plate 153 is attached to the surface of the inner plate 128 a that faces the radial plate 153. The annular plate 126 is pressed against the radial plate 153 by the inner plate 128a.

  The torque limiter 140 is provided on the outer peripheral side of the drive plate 128 and has a ring-shaped presser plate 146 and an annular brake plate that is sandwiched between the drive plates 128 and extends in the radial direction from the outer peripheral edge of the drive plate 128. 147, a disc spring 149, and a support plate 143.

  The brake plate 147 is sandwiched between the drive plates 128 using rivets 148. Lining portions 144 and 145 are mounted on both surfaces of the outer peripheral edge of the brake plate 147. The lining portion 144 is in contact with the disc spring 149, and the lining portion 145 is in contact with the presser plate 146.

  The support plate 143 and the presser plate 146 are integrally connected to the flywheel 200 by bolts 142. When the disc spring 149 presses the lining portion 144, the lining portion 145 is pressed by the presser plate 146, and a surface pressure between the lining portion 145 and the presser plate 146 is ensured. Further, the support plate 143 and the presser plate 146 rotate together with the flywheel 200.

  When the presser plate 146 rotates, the lining portions 144 and 145 and the brake plate 147 rotate together with the presser plate 146 due to friction between the lining portion 145 and the presser plate 146.

  When the crankshaft 300 is rotated by the driving force from the engine, the flywheel 200 is rotated. As the flywheel 200 rotates, the brake plate 147 rotates via the torque limiter 140. As the brake plate 147 rotates, the drive plate 128 rotates. Further, when the spring damper 121 rotates together with the drive plate 128, the radial plate 153 engaged with the spring damper 121 rotates. As a result, the driving force of the crankshaft 300 is transmitted to the input shaft 160 to which the hub 150 is coupled.

  By providing the spring damper 121 between the drive plate 128 and the hub 150, torque fluctuations can be absorbed.

  The damper mechanism according to the present embodiment has an important feature in that, in addition to the spring damper 121, another torque absorbing mechanism that operates only in the high torque region is provided. That is, the taper screw mechanism 170 shown in FIG. 2 is an example of this torque absorbing mechanism.

  The taper screw mechanism 170 is provided between the drive plate 128 and the hub 150. More specifically, a taper screw mechanism 170 is provided between the inner peripheral surface of the cylindrical portion 128 c formed on the drive plate 128 and the outer peripheral surface of the cylindrical portion 151 provided on the hub 150. When the relative displacement of the hub 150 with respect to the drive plate 128 increases, torque fluctuation is absorbed by the frictional resistance of the taper screw mechanism 170.

  On the other hand, the spring damper 121 absorbs torque fluctuations regardless of the relative displacement of the hub 150 with respect to the drive plate 128. Therefore, in the damper mechanism according to the present embodiment, in the low torque region where the relative displacement of the hub 150 with respect to the drive plate 128 is small, torsional energy is absorbed by the spring damper 121, and the relative displacement of the hub 150 with respect to the drive plate 128 is large. In the torque region, the torsional energy is absorbed by the frictional resistance between the drive plate 128 and the hub 150 in addition to the spring damper 121.

  Next, the operation and effect of the damper mechanism according to the present embodiment will be described with reference to FIG. 4 showing the relationship between the twist angle and the torque absorption amount. The horizontal axis in FIG. 4 indicates the relative displacement of the hub 150 with respect to the drive plate 128, and the vertical axis in FIG. 4 indicates the absorption torque. Further, “α” in FIG. 4 represents a “relative displacement-absorption torque” curve of the damper mechanism according to the reference example, and “β” in FIG. 4 represents “relative displacement of the damper mechanism according to the present embodiment. -Shows the "absorption torque" curve.

As shown in FIG. 4, in the damper mechanism (curve β) according to the present embodiment, the taper screw mechanism 170 of the taper screw mechanism 170 is in a state where the relative displacement of the hub 150 with respect to the drive plate 128 is relatively large (that is, in the high torque region). As a result, it is possible to absorb a large torque compared to the damper mechanism (curve α) according to the reference example. As a result, in the damper mechanism (curve α) according to the reference example, the torque limiter is reached after reaching a position where the relative rotation of the hub 150 with respect to the drive plate 128 is mechanically stopped by the stopper (“stopper position” in FIG. 4). In contrast, the damper mechanism (curve β) according to the present embodiment reaches the operating torque (T ₀ ) of the torque limiter 140 before reaching the “stopper position”. Therefore, a torque larger than the limiter torque is prevented from acting transiently.

  In addition, even with the damper mechanism according to the reference example, if the rigidity of the spring damper is increased, it is possible to suppress a torque that is larger than the limiter torque from acting transiently. Collision noise (common name, rattling noise, humming noise) due to the collision of gears is likely to occur, and the vehicle cabin environment deteriorates.

  On the other hand, according to the damper mechanism according to the present embodiment, it is possible to increase the energy that can be absorbed while suppressing the rigidity of the spring damper 121. Therefore, it is possible to suppress a torque larger than the limiter torque from acting transiently while preventing deterioration of the vehicle cabin environment.

  Next, a damper mechanism according to a modification of the present embodiment will be described with reference to FIG. Referring to FIG. 5, the damper mechanism according to this modification basically has the same structure as that described above, but has the following structure instead of taper screw mechanism 170. is there.

  That is, the outer plate 128b of the drive plate 128 and the radial plate 153 of the hub 150 are provided with a gap (L) therebetween. In this modification, the gap (L) is provided with the drive plate 128. The hub 150 is formed so as to decrease as the relative displacement of the hub 150 increases. When the relative displacement exceeds a predetermined value, the hub 150 contacts with each other. Thereby, in the low torque region where the relative displacement of the hub 150 with respect to the drive plate 128 is small, the torsional energy is absorbed by the spring damper 121, and in the high torque region where the relative displacement of the hub 150 with respect to the drive plate 128 is large, the outer plate 128b and the radial shape. Torsional energy can be absorbed by the frictional resistance with the plate 153. Therefore, as in the above example, in the low torque region where the relative displacement of the hub 150 with respect to the drive plate 128 is small, the torsional energy is absorbed by the spring damper 121, and in the high torque region where the relative displacement of the hub 150 with respect to the drive plate 128 is large, Torsional energy is absorbed by the frictional resistance between the drive plate 128 and the hub 150 in addition to the spring damper 121.

  In the above example, the example in which the torsional energy is absorbed by the frictional resistance between the outer plate 128b and the radial plate 153 has been described, but the inner plate 128a may be used instead of the outer plate 128b.

  The above contents are summarized as follows. That is, the damper mechanism according to the present embodiment has a drive plate 128 as a “first rotating member” and a rotational center axis that is disposed opposite to the drive plate 128 and has the same rotational center axis as the drive plate 128. A hub 150 as a “second rotating member” capable of relative displacement at a predetermined angle in the circumferential direction, and a spring damper 121 as an “elastic member” that engages with the drive plate 128 and the hub 150. In a region where the relative displacement of the hub 150 with respect to the drive plate 128 is relatively small, the torsional energy is absorbed by the spring damper 121. In the region where the relative displacement of the hub 150 with respect to the drive plate 128 is relatively large, the torsional energy is absorbed by the frictional resistance between the drive plate 128 and the hub 150 in addition to the spring damper 121.

  In the example shown in FIG. 2, the drive plate 128 has a cylindrical portion 128 c as a “first cylindrical portion”, and the hub 150 serves as a “second cylindrical portion” that fits on the inner peripheral side of the cylindrical portion 128 c. A cylindrical portion 151 is provided. A taper screw mechanism 170 is provided between the inner peripheral surface of the cylindrical portion 128 c and the outer peripheral surface of the cylindrical portion 151. In the region where the relative displacement of the hub 150 with respect to the drive plate 128 is relatively large, the torsional energy is absorbed by the frictional resistance of the taper screw mechanism 170 in addition to the spring damper 121.

  In the example shown in FIG. 5, the drive plate 128 includes an outer plate 128b as a “first plate-like portion”, and the hub 150 includes a radial plate 153 as a “second plate-like portion”. 153 are provided with a predetermined gap (L) therebetween, and the predetermined gap (L) is provided so as to change along the circumferential direction of the drive plate 128 and the hub 150. In the region where the relative displacement is relatively large, the torsional energy is absorbed by the frictional resistance between the outer plate 128 b and the radial plate 153 in addition to the spring damper 121.

  In a typical example, the drive plate 128 is connected to a crankshaft 300 as an “output shaft of an internal combustion engine”, and the hub 150 is connected to an input shaft 160 of a transmission or a transaxle as a “power transmission device”. However, the application destination of the damper mechanism of the present invention is not limited to these.

  In the example shown in FIG. 2, the drive plate 128 is connected to the crankshaft 300 via the torque limiter 140, but the torque limiter 140 is not an essential configuration for the present invention.

  Although the embodiments of the present invention have been described above, the embodiments disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  100 damper mechanism, 121 spring damper, 126 annular plate, 128 drive plate, 128a inner plate, 128b outer plate, 128c cylinder, 140 torque limiter, 142 bolt, 143 support plate, 144,145 lining, 146 presser plate, 147 Brake plate, 148 rivets, 149 disc spring, 150 hub, 151 cylinder part, 152 disc part, 153 radial plate, 154 engagement part, 160 input shaft, 170 taper screw mechanism, 200 flywheel, 300 crankshaft.

Claims (5)

A first rotating member;
A second rotating member disposed opposite to the first rotating member, having the same rotation center axis as the first rotation member, and capable of relative displacement at a predetermined angle in a circumferential direction of the rotation center axis;
An elastic member engaged with the first rotating member and the second rotating member,
In a region where the relative displacement of the second rotating member relative to the first rotating member is relatively small, the elastic member absorbs torsional energy, and the relative displacement of the second rotating member relative to the first rotating member is relatively A damper mechanism that absorbs torsional energy by a frictional resistance between the first rotating member and the second rotating member in addition to the elastic member in a large region. The first rotating member has a first tubular portion;
The second rotating member has a second cylindrical portion fitted on the inner peripheral side of the first cylindrical portion,
A taper screw mechanism is provided between the inner peripheral surface of the first cylindrical portion and the outer peripheral surface of the second cylindrical portion,
2. The damper mechanism according to claim 1, wherein in a region where the relative displacement of the second rotating member with respect to the first rotating member is relatively large, torsional energy is absorbed by frictional resistance of the tapered screw mechanism in addition to the elastic member. . The first rotating member includes a first plate-like portion;
The second rotating member includes a second plate-like portion;
The first plate-like portion and the second plate-like portion are provided with a predetermined gap therebetween,
The predetermined gap is provided to change along a circumferential direction of the first rotating member and the second rotating member,
In an area where the relative displacement of the second rotating member with respect to the first rotating member is relatively large, in addition to the elastic member, the torsional energy is generated by the frictional resistance between the first plate-like portion and the second plate-like portion. The damper mechanism according to claim 1, which absorbs The first rotating member is coupled to an output shaft of an internal combustion engine;
The damper mechanism according to any one of claims 1 to 3, wherein the second rotating member is coupled to an input shaft of a power transmission device.   The damper mechanism according to any one of claims 1 to 4, wherein the first rotating member is connected to an output shaft of the internal combustion engine via a torque limiter.

Images