JP7218205B2 - Dynamic damper device - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dynamic damper device, and more particularly to a dynamic damper device that is attached to a rotating member of a power transmission path and dampens vibrations.

2. Description of the Related Art A power transmission device such as a torque converter is provided with a dynamic damper device for damping vibrations at the time of lockup or the like, as disclosed in Japanese Unexamined Patent Application Publication No. 2002-200012. This dynamic damper device includes a base plate connected to an output-side member, an inertial body, and an elastic unit. The inertial body is rotatable relative to the base plate. Also, the elastic unit elastically connects the base plate and the inertial body in the rotational direction.

The dynamic damper device of Patent Literature 1 is intended to stably obtain high damping performance over the entire normal rotation speed range. In order to achieve this purpose, the dynamic damper device has 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).

JP 2015-212568 A

In the torque converter provided with the dynamic damper device of Patent Document 1, the peak of torque fluctuation that appears in the high rotation speed range can be moved to the high rotation speed side from 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 torque fluctuation peak that appears in the low rotational speed region continues for a long time because the equivalent rigidity is high.

SUMMARY OF THE INVENTION An object of the present invention is to improve the damping performance of torque fluctuations that appear particularly in the low rotational speed range in a dynamic damper device.

(1) A dynamic damper device according to the present invention is attached to a rotating member of a power transmission path and dampens vibrations. This dynamic damper device includes a first rotor, a second rotor, an inertia body, and a damper section. The first rotating body is attached to the rotating member and has a plurality of accommodating portions. The second rotating body has first and second plates axially opposed to each other 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 support portions arranged corresponding to the plurality of storage portions. The inertia body is provided on the second rotating body. The damper section elastically connects the first rotating body and the second rotating body in the rotational direction, and has a plurality of elastic members arranged in the plurality of housing sections and the support section. The damper section has a first torsional rigidity in the first torsional angle region and a second torsional rigidity lower than the first torsional rigidity in a second torsional angle region larger than the first torsional angle region.

Here, the torque fluctuation input from the rotating member is attenuated by the action of the inertia body and the damper section. The damper section has a relatively high first torsional rigidity in a first torsional angle region of a low rotational speed region, and has a relatively low second torsional rigidity in a second torsional angle region of a high rotational speed region. Here, since the slope connecting the amplitude point of the torque fluctuation on the torsional characteristic and the origin becomes the equivalent stiffness, when the amplitude point is the second torsional stiffness with low stiffness, the larger the amplitude, the lower the equivalent stiffness. When the equivalent stiffness is low, the resonance frequency is low, so the resonance frequency is lower as the amplitude is larger. Therefore, when resonance occurs at a certain frequency, the amplitude increases, but when the resonance frequency becomes lower and the resonance frequency shifts, the amplitude of the torque fluctuation decreases. As a result, it is possible to effectively suppress torque fluctuations appearing in the low rotation speed range, thereby improving the vibration damping performance in the low rotation speed range.

(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 of the plurality of elastic members stops operating in the second torsion angle region. Therefore, the stiffness in the second torsion angle region is lower than that in the first torsion angle region.

(5) Preferably, the plurality of housing portions have a first housing portion and a second housing portion arranged side by side in the circumferential direction. Also, the plurality of support portions has a first support portion and a second support portion. The first supporting portion is arranged so as to partially overlap the first accommodating portion when viewed 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 accommodation portion.

Here, the offset direction of the first accommodation portion and the first support portion is opposite to the offset direction of the second accommodation portion and the second support portion. Therefore, one of the elastic members accommodated therein is compressed and the other is expanded as the first and second rotating bodies rotate relative to each other. Therefore, when the elastic member that stretches becomes, for example, free length, this elastic member is released from the compressed state and stops working. Therefore, the rigidity becomes lower than when the elastic member having a free length 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 receiving portions. Preferably, the first and second plates are axially opposed to each other 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 torque fluctuations that appear particularly in the low rotational speed range.

1 is a cross-sectional view of a dynamic damper device according to an embodiment of the present invention; FIG. The front view of a dynamic damper apparatus. FIG. 4 is a schematic diagram showing the positional relationship between a hub flange and a support plate; The figure which shows the assembly|attachment procedure of a hub flange, a support plate, and a torsion spring. The figure which shows the state where the twist angle of a hub flange and a support plate is 0 degrees (neutral position). The figure which shows the state where the twist angle of a hub flange and a support plate is 1.5 degrees. The figure which shows the state where the twist angle of a hub flange and a support plate is 2.0 degrees. FIG. 4 is a diagram showing torsional characteristics of the dynamic damper device; The figure which shows the relationship between an input rotational speed and a rotational speed fluctuation.

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

[overall structure]
This dynamic damper device 1 is attached to 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 rotor), a pair of support plates 20 (an example of a second rotor), an inertia member 30, and a damper portion 40.

[Hub flange 10]
Hub flange 10 has a boss 11 and a flange 12 . The boss 11 is formed in a cylindrical shape and has a spline hole 11a formed in the center. The dynamic damper device 1 is connected to the rotating shaft 2 by meshing the spline teeth formed on the outer peripheral surface of the rotating shaft 2 with the spline holes 11a. The flange 12 is formed in a disc shape and extends radially outward from the outer peripheral surface of the boss 11 . The flange 12 is formed with four first to fourth housing portions 12a to 12d arranged in the circumferential direction. The first accommodating portion 12a and the third accommodating portion 12c are formed symmetrically with respect to the center of rotation. Similarly, the second housing portion 12b and the fourth housing portion 12d are formed symmetrically with respect to the center of rotation. In addition, a plurality of stopper cutouts 12e are formed between adjacent accommodating portions in the circumferential direction.

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

[Support plate 20]
A pair of support plates 20 are formed in a disc shape. A pair of support plates 20 are axially spaced across the flange 12 and fixed to each other by a plurality of stop pins 21 . As a result, the pair of support plates 20 cannot move axially relative to 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 housing portions 12a to 12d of the flange 12, respectively. The first support portion 20a and the third support portion 20c are formed symmetrically with respect to the center of rotation. Similarly, the second support portion 20b and the fourth support portion 20d are formed symmetrically across the center of rotation.

Each of the support portions 20a to 20d has an axially penetrating hole and edge portions cut and raised 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 hole (the distance between the R1 support surface 201 and the R2 support surface 202) in each support portion 20a-20d is L2 (eg, 37.5 mm), and width L1>width L2 in this embodiment. End surfaces of torsion springs, which will be described later, can come into contact with the support surfaces 201 and 202 .

The stop pin 21 passes through the stopper notch 12 e 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 (eg, ±2.0°).

[Inertia member 30]
The inertia member 30 is constructed by stacking four disk-shaped plates 31 to 34 . The four plates 31-34 are fixed by a plurality of rivets 35 axially penetrating them. An 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 a stop pin 21 . Thereby, the inertia member 30 rotates together with the pair of support plates 20 .

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

[Stored state of the torsion spring]
Here, the arrangement of the housing portions 12a to 12d and the support portions 20a to 20d and the housing of the torsion springs 41 to 44 are shown when the hub flange 10 and the pair of support plates 20 are not twisted (neutral position). The states are 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 second supporting portion 20b are referred to as "second window set w2". , the third accommodating portion 12c and the third supporting portion 20c may be referred to as the “third window set w3”, and the fourth accommodating portion 12d and the fourth supporting portion 20d may be referred to as the “fourth window set w4”. be.

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

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

The torsion springs 41 to 44 are attached in a compressed state to openings (holes penetrating in the axial direction) of portions of the supporting portions 20a to 20d corresponding to the accommodating portions 12a to 12d and corresponding to the supporting portions 20a to 20d. there is

Specifically, as shown in FIG. 3, in the first and third window sets w1 and w3, the end surfaces of the first and third torsion springs 41 and 43 on the R1 side in the circumferential direction abut against the R1 accommodation surface 121. The end surface 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, w4, the end faces of the second and fourth torsion springs 42, 44 on the R1 side in the circumferential direction abut against the R1 support surface 201, and the end faces on the R2 side in the circumferential direction It abuts on the R2 accommodation surface 122 .

[Assembly procedure]
A 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 support portion 20a, and the second accommodating portion 12b and the second support portion 20b. FIG. 4 shows the case where the first and second torsion springs 41 and 42 are assembled to the first and second window sets w1 and w2. The third and fourth torsion springs 43, 44 are assembled.

First, as shown in FIGS. 4(a) and 4(b), the first accommodation portion 12a of the hub flange 10 and the first and third support portions 20a of one support plate 20 are aligned (FIG. 4b). , the first torsion spring 41 is assembled to the first window set w1 (Fig. 1c).

Next, as shown in FIG. 4(d), the hub flange 10 is twisted at a predetermined angle in the circumferential direction (to the right in the figure) with respect to the support plate 20. Then, as shown in FIG. In this state, the positions of the second housing portion 12b and the second support portion 20b are substantially aligned. In this state, the second torsion spring 42 is assembled to the second window set w2 (e).

Next, the hub flange 10 is twisted back with respect to the support plate 20 in the opposite circumferential direction (left side in the figure) (f in the figure), and in this state, the other support plate 20 is assembled ( 4g), a pair of support plates 20 are fixed by stop pins 21. As shown in FIG. As a result, the torsion springs 41 to 44 are attached to the respective window sets w1 to w4 in a compressed state.

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

[motion]
In a state where no vibration is 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. The first torsion spring 41 is arranged under compression between the R1 accommodation surface 121 and the R2 support surface 202 . Similarly, in the third window set w3, the third torsion spring 43 is placed in compression between the R1 receiving surface 121 and the R2 bearing surface 202. As shown in FIG. In the state shown in FIG. 5, the distance between the R1 accommodation surface 121 and the R2 support surface 202 is G0, and this distance G0 corresponds to the width L2 of the first support portion 20a (=the free length Lf of the torsion spring 40). ).

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

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

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

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

In this region of the twist angle of 1.5° to 2.0°, the interval between the first and third window sets w1 and w3 becomes even narrower, so that the first and third window sets w1 and w3 Torsion springs 41 and 43 are further compressed. On the other hand, the interval between the second and fourth window sets w2, w4 is further increased. However, the second and fourth torsion springs 42, 44 of the second and fourth window sets w2, w4 are already at free length and do not operate.

As described above, the first to fourth torsion springs 41 to 44 all operate in a compressed state when the torsion angle is 0 to 1.5 degrees. However, at a torsion angle of 1.5° to 2.0°, the second and fourth torsion springs 42, 44 are in free length, so these torsion springs 42, 44 do not operate. Therefore, in the torsion region with a torsion angle of 1.5° to 2.0°, the rigidity is reduced to 1/2 of the rigidity up to that point. The above operation is the same when the hub flange 10 is twisted in the opposite direction.

Due to the above operation, the dynamic damper device 1 has torsional characteristics as shown in FIG. That is, when the torsion angle is in the range of 0 to 1.5°, the rigidity is 2K, and when the torsion angle is 1.5° or more, the rigidity is low. The equivalent stiffness in this case is low, as indicated by the dashed line in the figure.

FIG. 9 shows the relationship between the input rotation speed of the power transmission device and the rotation speed fluctuation. In the figure, the dashed line is the characteristic when no dynamic damper device is provided, and the one-dot chain line is the characteristic of the conventional dynamic damper device with low rigidity at the first stage and high rigidity at the second stage. The solid line indicates the characteristics when the dynamic damper device of this embodiment is installed. As is clear from this figure, the dynamic damper device of this embodiment can effectively suppress rotation speed fluctuations (that is, vibration) in the low rotation speed range.

[Other embodiments]
The present invention is not limited to the embodiments as described above, and various modifications or modifications are possible without departing from the scope of the present invention.

(a) In the above embodiment, the width L1 of each accommodating portion 12a to 12d and the width L2 of each supporting portion 20a to 20d are defined as width L1>width L2. good too.

(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-20d, but the free length Lf of the torsion spring is shorter than the width L2 of each support portion 20a-20d. You may

(c) In the above embodiment, the dimensions of each part are set so that the relative angle between the hub flange 10 and the support plate 20 is a predetermined angle or more 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 a predetermined angle or more, 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 was 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 embodiment.

1 dynamic damper device 2 rotating shaft 10 hub flange (first rotating body)
11 Boss 12 Flanges 12a to 12d Accommodating portion 121, 122 Accommodating surface 20 Support plate (first and second plates, second rotor)
20a to 20d support portions 201, 202 support surface 30 inertia member (inertia body)
40 torsion spring (damper part)

Claims (5)

A dynamic damper device mounted on a rotating member of a power transmission path and damping vibration,
a first rotating body mounted on the rotating member and having a plurality of housing portions;
It has first and second plates that face each other in the axial direction with the first rotating body interposed therebetween, and the first and second plates are rotatable relative to the first rotating body and correspond to the plurality of housing portions. a second body of rotation having a plurality of supports arranged as
an inertial body provided on the second rotating body;
The first rotating body and the second rotating body are elastically connected in a rotational direction, and has a plurality of elastic members arranged in the plurality of accommodating portions and the supporting portion, and has a first torsion angle. a damper portion having a first torsional rigidity in a region and a second torsional rigidity lower than the first torsional rigidity in a second torsional angle region larger than the first torsional angle region;
with
the first twist angle region is wider than the second twist angle region;
dynamic damper device.
A dynamic damper device mounted on a rotating member of a power transmission path and damping vibration,
a first rotating body mounted on the rotating member and having a plurality of housing portions;
It has first and second plates that face each other in the axial direction with the first rotating body interposed therebetween, and the first and second plates are rotatable relative to the first rotating body and correspond to the plurality of housing portions. a second body of rotation having a plurality of supports arranged as
an inertial body provided on the second rotating body;
The first rotating body and the second rotating body are elastically connected in a rotational direction, and has a plurality of elastic members arranged in the plurality of accommodating portions and the supporting portion, and has a first torsion angle. a damper portion having a first torsional rigidity in a region and a second torsional rigidity lower than the first torsional rigidity in a second torsional angle region larger than the first torsional angle region;
with
at least one elastic member of the plurality of elastic members stops operating in the second torsion angle region ;
dynamic damper device.
A dynamic damper device mounted on a rotating member of a power transmission path and damping vibration,
a first rotating body mounted on the rotating member and having a plurality of housing portions;
It has first and second plates that face each other in the axial direction with the first rotating body interposed therebetween, and the first and second plates are rotatable relative to the first rotating body and correspond to the plurality of housing portions. a second body of rotation having a plurality of supports arranged as
an inertial body provided on the second rotating body;
The first rotating body and the second rotating body are elastically connected in a rotational direction, and has a plurality of elastic members arranged in the plurality of accommodating portions and the supporting portion, and has a first torsion angle. a damper portion having a first torsional rigidity in a region and a second torsional rigidity lower than the first torsional rigidity in a second torsional angle region larger than the first torsional angle region;
with
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 the accommodating portions,
The first and second plates are arranged 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 ,
dynamic damper device.
4. The dynamic damper device according to claim 1, wherein said first torsion angle region and said second torsion angle region are continuous.
The plurality of storage portions have a first storage portion and a second storage portion arranged side by side in a circumferential direction,
The plurality of support portions include a first support portion arranged so as to partially overlap the first accommodation portion when viewed in the axial direction and offset to a first side in the circumferential direction, and the second accommodation portion. a second support arranged circumferentially offset from the second side with respect to
A dynamic damper device according to any one of claims 1 to 4.

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