JP2020133746A - Dynamic damper device - Google Patents

Abstract

To improve damping performance for torque fluctuation occurring in a low rotational frequency area, in a dynamic damper device.SOLUTION: The dynamic damper device comprises: a hub flange 10 having a plurality of housing parts 12a to 12d; a pair of support plates 20 having a plurality of support parts 20a to 20d and rotatable relatively to the hub flange 10; an inertia member 30 provided on the support plate 20; and a damper part 40. The damper part 40 has a plurality of torsion springs 41 to 44 arranged in the plurality of housing parts 12a to 12d and the plurality of support parts 20a to 20d, and elastically connects the hub flange 10 and the support plate 20 in a rotational direction. The damper part 40 has a first torsional rigidity in a first torsional angle area, and a second torsional rigidity lower than the first torsional rigidity in the second torsional angle area larger than the first torsional angle area.SELECTED DRAWING: Figure 8

Description

The present invention relates to a dynamic damper device, particularly a dynamic damper device that is attached to a rotating member of a power transmission path to attenuate vibration.

In a power transmission device such as a torque converter, as shown in Patent Document 1, a dynamic damper device is provided to attenuate vibration at the time of lockup or the like. This dynamic damper device includes a base plate connected to a member on the output side, an inertial body, and an elastic unit. The inertial body can rotate relative to the base plate. Further, the elastic unit elastically connects the base plate and the inertial body in the rotational direction.

The dynamic damper device of Patent Document 1 aims to stably obtain high damping performance over the entire range of normal rotation speed. In order to achieve this purpose, the dynamic damper device has a torsional characteristic of low rigidity in the first stage and high rigidity in the second stage. The equivalent rigidity of the dynamic damper device in this case is higher than the torsional rigidity of the first stage (see FIG. 8 of Patent Document 1).

Japanese Unexamined Patent Publication No. 2015-21268

In the torque converter provided with the dynamic damper device of Patent Document 1, the peak of the torque fluctuation appearing in the high rotation speed range can be moved to the higher rotation speed side than the normal rotation speed range. That is, it is possible to suppress torque fluctuations in the normal rotation speed range (see FIG. 9 of Patent Document 1).

However, the dynamic damper of Patent Document 1 has a problem that the peak of the torque fluctuation appearing in the low rotation speed range continues for a long time because the equivalent rigidity becomes high.

An object of the present invention is to improve the damping performance of torque fluctuations appearing in a low rotation speed region in a dynamic damper device.

(1) The dynamic damper device according to the present invention is attached to a rotating member of a power transmission path to attenuate vibration. This dynamic damper device includes a first rotating body, a second rotating body, an inertial body, and a damper portion. The first rotating body is attached to a rotating member and has a plurality of accommodating portions. The second rotating body has first and second plates that face each other in the axial direction with the first rotating body interposed therebetween. The first and second plates are rotatable relative to the first rotating body and have a plurality of supports arranged so as to correspond to the plurality of accommodating portions. The inertial body is provided on the second rotating body. The damper portion elastically connects the first rotating body and the second rotating body in the rotational direction, and has a plurality of elastic members arranged in a plurality of accommodating portions and supporting portions. The damper portion has a first torsional rigidity in the first torsional angle region and a second torsional rigidity lower than the first torsional rigidity in the second torsional angle region larger than the first torsional angle region.

Here, the torque fluctuation input from the rotating member is damped by the operation of the inertial body and the damper portion. The damper portion has a relatively high first torsional rigidity in the first torsional angle region in the low rotation speed region, and has a relatively low second torsional rigidity in the second torsional angle region in the high rotation speed region. Here, since the slope connecting the amplitude point and the origin of the torque fluctuation on the torsional characteristics has the equivalent rigidity, when the amplitude point is the second torsional rigidity with low rigidity, the larger the amplitude, the lower the equivalent rigidity. When the equivalent rigidity is low, the resonance frequency is low, so that the larger the amplitude, the lower the resonance frequency. Therefore, when the resonance occurs at a certain frequency, the amplitude becomes large, but when the resonance frequency becomes low and the resonance frequency deviates, the amplitude of the torque fluctuation becomes small. As a result, torque fluctuations appearing in the low rotation speed range can be effectively suppressed, and vibration damping performance in the low rotation speed range is improved.

(2) Preferably, the first twist angle region and the second twist angle region are continuous.

(3) Preferably, the first twist angle region is wider than the second twist angle region.

(4) Preferably, at least one elastic member among the plurality of elastic members stops operating in the second twist angle region. Therefore, the rigidity of the second twist angle region is lower than that of the first twist angle region.

(5) Preferably, the plurality of accommodating portions have a first accommodating portion and a second accommodating portion arranged side by side in the circumferential direction. Further, the plurality of support portions have a first support portion and a second support portion. The first support portion is arranged so as to partially overlap the first accommodating portion in the axial direction and offset to the first side in the circumferential direction. The second support portion is arranged offset to the second side in the circumferential direction with respect to the second accommodating portion.

Here, the offset direction of the first accommodating portion and the first supporting portion and the offset direction of the second accommodating portion and the second supporting portion are opposite to each other. Therefore, one of the elastic members housed therein is compressed and the other is expanded as the first and second rotating bodies rotate relative to each other. Therefore, when the stretchable elastic member has, for example, a free length, the elastic member is released from the compressed state and becomes inoperable. Therefore, the rigidity of the elastic member having a free length is lower than that when the elastic member is compressed.

(6) Preferably, the first rotating body has a boss connected to the rotating member and a flange extending radially outward from the boss and having a plurality of accommodating portions. Preferably, the first and second plates are arranged so as to face each other in the axial direction with the flange interposed therebetween. The inertial body is fixed to the outer peripheral portion of the first plate.

According to the present invention as described above, in the dynamic damper device, it is possible to improve the damping performance of the torque fluctuation appearing especially in the low rotation speed range.

Sectional drawing of the dynamic damper apparatus by one Embodiment of this invention. Front view of the dynamic damper device. The schematic diagram which shows the positional relationship between a hub flange and a support plate. The figure which shows the assembly procedure of a hub flange, a support plate, and a torsion spring. The figure which shows the state which the twist angle of a hub flange and a support plate is 0 ° (neutral position). The figure which shows the state which the twist angle of a hub flange and a support plate is 1.5 °. The figure which shows the state which the twist angle of a hub flange and a support plate is 2.0 °. The figure which shows the torsional characteristic of a dynamic damper device. The figure which shows the relationship between the input rotation speed and the rotation speed fluctuation.

FIG. 1 is a cross-sectional view of a dynamic damper device 1 according to an embodiment of the present invention, and FIG. 2 is a front view thereof. In addition, a part of FIG. 2 is shown by omitting the members. The OO line in FIG. 1 is the center of rotation of the dynamic damper device 1.

[overall structure]
The dynamic damper device 1 is mounted on a rotating shaft 2 provided in a power transmission path. The dynamic damper device 1 includes a hub flange 10 (an example of a first rotating body), a pair of support plates 20 (an example of a second rotating body), an inertia member 30, and a damper portion 40.

[Hub Flange 10]
The hub flange 10 has a boss 11 and a flange 12. The boss 11 is formed in a tubular shape, and a spline hole 11a is formed in the central portion thereof. The dynamic damper device 1 is connected to the rotating shaft 2 by engaging the spline holes 11a with the spline teeth formed on the outer peripheral surface of the rotating shaft 2. The flange 12 is formed in a disk shape and extends radially outward from the outer peripheral surface of the boss 11. The flange 12 is formed with four first to fourth accommodating portions 12a to 12d arranged side by side in the circumferential direction. The first accommodating portion 12a and the third accommodating portion 12c are formed symmetrically with the rotation center interposed therebetween. Similarly, the second accommodating portion 12b and the fourth accommodating portion 12d are formed symmetrically with the rotation center in between. Further, a plurality of stopper notches 12e are formed between the circumferential directions of the adjacent accommodating portions.

Each of the accommodating portions 12a to 12d is a substantially rectangular hole having an arcuate outer peripheral portion. As shown in FIG. 3, each of the accommodating portions 12a to 12d has an R1 accommodating surface 121 at the end on the first side in the circumferential direction and an R2 accommodating surface 122 at the end on the second side in the circumferential direction. ing. The width of the holes (distance between the R1 accommodating surface 121 and the R2 accommodating surface 122) of each accommodating portion 12a to 12d is set to L1 (for example, 38.0 mm). Then, the end faces of the torsion springs, which will be described later, can come into contact with the accommodating surfaces 121 and 122. Note that FIG. 3 shows the entire hub flange 10 and only a part of the support plate 20 (end face in the circumferential direction). Further, FIG. 3 is a view of the hub flange 10 and the like of FIG. 1 viewed from the opposite side of FIG.

[Support plate 20]
The pair of support plates 20 are formed in a disk shape. The pair of support plates 20 are arranged at intervals in the axial direction with the flange 12 interposed therebetween, and are fixed to each other by a plurality of stop pins 21. As a result, the pair of support plates 20 cannot move in the axial direction with each other and cannot rotate relative to each other. Each support plate 20 has first to fourth support portions 20a to 20d at positions corresponding to the first to fourth accommodating portions 12a to 12d of the flange 12. The first support portion 20a and the third support portion 20c are formed symmetrically with the rotation center interposed therebetween. Similarly, the second support portion 20b and the fourth support portion 20d are formed symmetrically with the rotation center interposed therebetween.

Each of the support portions 20a to 20d has a hole penetrating in the axial direction and an edge portion cut up on the inner and outer peripheral edges of the hole. As shown in FIG. 3, each of the support portions 20a to 20d has an R1 support surface 201 at the end on the first side in the circumferential direction and an R2 support surface 202 at the end on the second side in the circumferential direction. ing. The width of the holes (distance between the R1 support surface 201 and the R2 support surface 202) in each of the support portions 20a to 20d is L2 (for example, 37.5 mm), and in this embodiment, the width L1> the width L2. Then, the end faces of the torsion springs, which will be described later, can come into contact with the support surfaces 201 and 202.

The stop pin 21 penetrates the stopper notch 12e of the flange 12. A gap is provided between the stop pin 21 and the stopper notch 12e in the circumferential direction. Therefore, the hub flange 10 and the pair of support plates 20 can rotate relative to each other by an angle corresponding to this gap (for example, ± 2.0 °).

[Inertia member 30]
The inertia member 30 is formed by laminating four disc-shaped plates 31 to 34. The four plates 31 to 34 are fixed by a plurality of rivets 35 penetrating them in the axial direction. Then, the inner peripheral portion of the plate 31 on one end side (left side in FIG. 1) is fixed to one of the pair of support plates 20 by the stop pin 21. As a result, the inertia member 30 rotates together with the pair of support plates 20.

[Damper section 40]
The damper portion 40 has first to fourth torsion springs 41 to 44. The torsion springs 41 to 44 are housed in the housing portions 12a to 12d of the flange 12, and are supported in the radial and axial directions by the support portions 20a to 20d of the pair of support plates 20. All four torsion springs 41 to 44 have the same free length Lf (for example, 37.5 mm), and this free length Lf is the same as the width L2 (37.5 mm) of each support portion 20a to 20d.

[Accommodation state of torsion spring]
Here, the arrangement of the accommodating portions 12a to 12d and the supporting portions 20a to 20d and the accommodating the torsion springs 41 to 44 in a state where the hub flange 10 and the pair of support plates 20 are not twisted (neutral position). The state will be described in detail below. In the following description, the first accommodating portion 12a and the first supporting portion 20a are referred to as "first window set w1", and the second accommodating portion 12b and the second supporting portion 20b are referred to as "second window set w2". In some cases, the third accommodating portion 12c and the third supporting portion 20c are described as "third window set w3", and the fourth accommodating portion 12d and the fourth supporting portion 20d are described as "fourth window set w4". is there.

Torsion springs 41 to 44 are attached to each of the window sets w1 to w4 in a compressed state. Then, in the neutral position, as shown in FIG. 3, the first support portion 20a is offset toward the circumferential direction R1 with respect to the first accommodating portion 12a. Similarly, the third support portion 20c is also offset toward the circumferential direction R1 with respect to the third accommodating portion 12c.

On the other hand, the second support portion 20b is offset toward the circumferential direction R2 with respect to the second accommodating portion 12b. Similarly, the fourth support portion 20d is also offset toward the circumferential direction R2 with respect to the fourth accommodating portion 12d.

Then, the torsion springs 41 to 44 are mounted in a compressed state in the openings (holes penetrating in the axial direction) of the portions of the supporting portions 20a to 20d corresponding to the accommodating portions 12a to 12d overlapping in the axial direction. There is.

Specifically, as shown in FIG. 3, in the first and third window sets w1 and w3, the end faces of the first and third torsion springs 41 and 43 on the circumferential direction R1 side correspond to the R1 accommodating surface 121. The end face on the R2 side in the circumferential direction is in contact with the R2 support surface 202.

On the other hand, in the second and fourth window sets w2 and w4, the end faces of the second and fourth torsion springs 42 and 44 on the circumferential direction R1 side come into contact with the R1 support surface 201, and the end faces on the circumferential direction R2 side It is in contact with the R2 accommodating surface 122.

[Assembly procedure]
The procedure for assembling the torsion springs 41 to 44 to the hub flange 10 and the pair of support plates 20 will be described with reference to FIG. Note that FIG. 4 schematically shows the relationship between the first accommodating portion 12a and the first supporting portion 20a and the second accommodating portion 12b and the second supporting portion 20b. FIG. 4 shows a case where the first and second torsion springs 41 and 42 are assembled to the first and second window sets w1 and w2, but at the same time, the same applies to the third and fourth window sets w3 and w4. Assemble the 3rd and 4th torsion springs 43 and 44.

First, as shown in FIGS. 4A and 4B, the first accommodating portion 12a of the hub flange 10 and the first and third supporting portions 20a of one of the support plates 20 are aligned (FIG. 4b). , The first torsion spring 41 is assembled to the first window set w1 (Fig. C).

Next, as shown in FIG. 2D, the hub flange 10 is twisted at a predetermined angle with respect to the support plate 20 in the circumferential direction (right side in the figure). In this state, the positions of the second accommodating portion 12b and the second supporting portion 20b are substantially the same. In this state, the second torsion spring 42 is assembled to the second window set w2 (Fig. E).

Next, the hub flange 10 is twisted back with respect to the support plate 20 in the circumferential direction (left side in the same figure) opposite to the above (figure f), and in this state, the other support plate 20 is assembled ( FIG. G) A pair of support plates 20 are fixed to each other by a stop pin 21. As a result, the torsion springs 41 to 44 are attached to the window sets w1 to w4 in a compressed state.

At this time, the hub flange 10 receives a rotational force on the R1 side with respect to the support plate 20 by the first and third torsion springs 41 and 43 mounted on the first and third window sets w1 and w3. On the other hand, the hub flange 10 receives a rotational force on the R2 side with respect to the support plate 20 due to the second and fourth torsion springs 42 and 44 mounted on the second and fourth window sets w2 and w4. Then, in a state where these rotational forces are balanced, the positional relationship between the hub flange 10 and the support plate 20 is maintained. Therefore, the misalignment of the hub flange 10 can be prevented, and the vibration of the rotating shaft 2 can be suppressed.

[motion]
In a state where vibration is not transmitted to the dynamic damper device 1, that is, in a state where the hub flange 10 and the support plate 20 are not relatively rotating (neutral position), as shown in FIG. 5, in the first window set w1, The first torsion spring 41 is compressed and arranged between the R1 accommodating surface 121 and the R2 support surface 202. Similarly, in the third window set w3, the third torsion spring 43 is compressed and arranged between the R1 accommodating surface 121 and the R2 support surface 202. In the state shown in FIG. 5, the distance between the R1 accommodating surface 121 and the R2 support surface 202 is G0, and this distance G0 is the width L2 of the first support portion 20a (= free length Lf of the torsion spring 40). ) Is shorter.

On the other hand, in the second window set w2, the second torsion spring 42 is compressed and arranged between the R1 support surface 201 and the R2 accommodating surface 122. Similarly, in the fourth window set w4, the fourth torsion spring 44 is compressed and arranged between the R1 support surface 201 and the R2 accommodating surface 122. In the state shown in FIG. 5, the distance between the R1 support surface 201 and the R2 accommodating surface 122 is G0.

FIG. 6 shows a state in which the vibration is transmitted and the hub flange 10 is twisted from the neutral position to the circumferential direction R2 side with respect to the support plate 20, for example, by 1.5 °. Here, in the first and third window sets w1 and w3, the distance G1 between the R1 accommodating surface 121 and the R2 support surface 202 is narrower than the distance G0. On the other hand, in the second and fourth window sets w2 and w4, the distance G2 between the R1 support surface 201 and the R2 accommodating surface 122 is wider than the distance G0. Therefore, the first and third torsion springs 41 and 43 of the first and third window sets w1 and w3 are compressed, but the second and fourth torsion springs 42 and 44 of the second and fourth window sets w2 and w4 are compressed. Stretches.

In the state shown in FIG. 6, the interval G2 in the second and fourth window sets w2 and w4 is the same as the free length Lf of the second and fourth torsion springs 42 and 44. That is, in the state shown in FIG. 6, the second and fourth torsion springs 42 and 44 of the second and fourth window sets w2 and w4 have free lengths, and in the subsequent twist angle region, unless they are further compressed. , Does not work. That is, it does not contribute to the torsional characteristics.

Then, as shown in FIG. 7, when the hub flange 10 is further twisted toward the R2 side with respect to the support plate 20, for example, when the twist angle is 2.0 °, the stopper notch 12e and the stop pin 21 come into contact with each other. Therefore, the relative rotation between the hub flange 10 and the support plate 20 is prohibited. In this state, in the second and fourth window sets w2 and w4, the offsets between the second and fourth accommodating portions 12b and 12d and the second and fourth support portions 20b and 20d are "0".

In this region of the twist angle of 1.5 ° to 2.0 °, the distance between the first and third window sets w1 and w3 is further narrowed, so that the first and third window sets w1 and w3 are the first and third. The torsion springs 41 and 43 are further compressed. On the other hand, the intervals between the second and fourth window sets w2 and w4 become wider. However, the second and fourth torsion springs 42 and 44 of the second and fourth window sets w2 and w4 have already become free lengths and do not operate.

As described above, at a twist angle of 0 to 1.5 °, all the first to fourth torsion springs 41 to 44 operate in a compressed state. However, at a twist angle of 1.5 ° to 2.0 °, the second and fourth torsion springs 42 and 44 have free lengths, so that these torsion springs 42 and 44 do not operate. Therefore, in the twisting region with a twisting angle of 1.5 ° to 2.0 °, the rigidity is halved as compared with the conventional rigidity. The above operation is the same when the hub flange 10 is twisted to the opposite side.

By the above operation, the dynamic damper device 1 has a twisting characteristic as shown in FIG. That is, it has the characteristics of high rigidity 2K when the twist angle is in the range of 0 to 1.5 ° and low rigidity K when the twist angle is 1.5 ° or more. The equivalent rigidity in this case is low as shown by the broken line in the figure.

FIG. 9 shows the relationship between the input rotation speed of the power transmission device and the fluctuation of the rotation speed. In the figure, the broken line is the characteristic when the dynamic damper device is not provided, and the alternate long and short dash line is the characteristic of the conventional dynamic damper device with low rigidity in the first stage and high rigidity in the second stage. The solid line is the characteristic when the dynamic damper device of the present embodiment is mounted. As is clear from this figure, in the dynamic damper device of the present embodiment, the rotation speed fluctuation (that is, vibration) in the low rotation speed range can be effectively suppressed.

[Other Embodiments]
The present invention is not limited to the above embodiments, and various modifications or modifications can be made without departing from the scope of the present invention.

(A) In the above embodiment, the width L1 of the accommodating portions 12a to 12d and the width L2 of the supporting portions 20a to 20d are defined as width L1> width L2, but conversely, width L1 <width L2. May be good.

(B) In the above embodiment, the free length Lf of the torsion spring is the same as the width L2 of each support portion 20a to 20d, but the free length Lf of the torsion spring is shorter than the width L2 of each support portion 20a to 20d. You may.

(C) In the above embodiment, the dimensions of each part are set so that the relative angles between the hub flange 10 and the support plate 20 are equal to or greater than a predetermined angle and the second and fourth torsion springs 42 and 44 have free lengths. However, the relative angle between the hub flange 10 and the support plate 20 may be equal to or greater than a predetermined angle, and the second and fourth torsion springs 42 and 44 may be compressed only by the second and fourth support portions 20b and 20d.

(D) In the above embodiment, the inertia member is fixed to the support plate, but the support plate and the inertia member may be integrated.

(E) The number of accommodating portions, supporting portions, and torsion springs is an example, and is not limited to the above embodiment. Similarly, the amount of offset between the accommodating portion and the supporting portion is not limited to the above-described embodiment.

1 Dynamic damper device 2 Rotating shaft 10 Hub flange (1st rotating body)
11 Boss 12 Flange 12a-12d Accommodating parts 121,122 Accommodating surface 20 Support plate (first and second plates, second rotating body)
20a to 20d Support parts 201,202 Support surface 30 Inertia member (inertial body)
40 Torsion spring (damper part)

Claims (6)

A dynamic damper device that is attached to the rotating member (2) of the power transmission path and attenuates vibration.
A first rotating body (10) mounted on the rotating member (2) and having a plurality of accommodating portions (12a to 12d), and
It has first and second plates (20) that face each other in the axial direction with the first rotating body (10) in between, and the first and second plates (20) are relative to the first rotating body (10). A second rotating body (20) that is rotatable and has a plurality of support portions (20a to 20d) arranged corresponding to the plurality of accommodating portions (12a to 12d).
An inertial body (30) provided on the second rotating body (20) and
The first rotating body (10) and the second rotating body (20) are elastically connected in the rotational direction, and the plurality of accommodating portions (12a to 12d) and supporting portions (20a to 20d) are connected. It has a plurality of elastic members (41 to 44) arranged in, has a first torsional rigidity in a first torsional angle region, and has a first torsional rigidity in a second torsional angle region larger than the first torsional angle region. The damper part (40) having a low second torsional rigidity and
Dynamic damper device equipped with.
The dynamic damper device according to claim 1, wherein the first twist angle region and the second twist angle region are continuous.
The dynamic damper device according to claim 1 or 2, wherein the first twist angle region is wider than the second twist angle region.
At least one elastic member (42,44) of the plurality of elastic members (41 to 44) stops operating in the second twist angle region.
The dynamic damper device according to any one of claims 1 to 3.
The plurality of accommodating portions (12a to 12d) have a first accommodating portion (12a) and a second accommodating portion (12b) arranged side by side in the circumferential direction.
The plurality of support portions (20a to 20d) are arranged so as to partially overlap the first accommodating portion (12a) in the axial direction and offset to the first side (R1) in the circumferential direction. It has a first support portion (20a) and a second support portion (20b) arranged offset to the second side (R2) in the circumferential direction with respect to the second accommodating portion (12b).
The dynamic damper device according to any one of claims 1 to 4.
The first rotating body (10) has a boss (11) connected to the rotating member (2), and a plurality of accommodating portions (12a to 12d) extending radially outward from the boss (11). With a flange (12),
The first and second plates (20) are arranged so as to face each other in the axial direction with the flange (12) interposed therebetween.
The inertial body (30) is fixed to the outer peripheral portion of the first plate (20).
The dynamic damper device according to any one of claims 1 to 5.

Images