JP2005106112A - Torque vibration suppressing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To easily obtain a large angle of torsion while obtaining a vibration suppressing effect of booming noise sound and the like, without increasing size. <P>SOLUTION: The torque vibration suppressing device 17 is interposed between a driving side rotating member 19 and a driven side rotating member 16 which are coaxially disposed, and suppresses vibrations of rotation torque. The torque vibration suppressing device 17 comprises a plurality of platy spiral springs 21 to 23 having different stiffness; and regulating means 21c, 22a, 23a fixing inner peripheral ends of all spiral screws to be engaging portion with either one of the driving side rotating member or the driven side rotating member, making outer peripheral ends of low stiffness spiral screws 21, 23 become engaging portions with the other one of the driving side rotating member or the driven side rotating member, and regulating relative positional change in a shaft peripheral direction between the outer peripheral ends of the low stiffness spiral spring and a high stiffness spiral screw 22 at a specified amount. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a torque vibration suppressing device, for example, a torque vibration suppressing device used for a torque converter of a vehicle such as an automobile (hereinafter referred to as “vehicle”).

  In general, in an internal combustion engine such as a reciprocating engine with large fluctuations in rotational torque, when the frequency of the torque fluctuation is close to the natural vibration frequency of the power train system, a large vibration is induced by a resonance phenomenon, and the vibration is generated in the vehicle. There are cases where uncomfortable air column resonance (so-called “buzzing noise”) is generated.

  For this reason, the natural vibration frequency of the powertrain system is set to be equal to or lower than the torque fluctuation frequency at the idle speed of the engine, and measures are taken to move away from the resonance point. However, since the number of vehicles with a mechanism for locking up is increasing, the above measures are not sufficient, and there is a problem that an unpleasant booming noise may be experienced especially when locking up in a low rotation range.

  Therefore, in order to suppress such a loud noise, a “torque vibration suppressing device” called a lock-up damper is provided in the torque converter of the vehicle. Since this torque vibration suppression device is incorporated together with the lock-up device in a narrow space in the torque converter, a thin torque vibration suppression device that can reduce the assembly space is required in accordance with the demand for further downsizing of the torque converter. ing.

  As a technique that contributes to a reduction in the thickness of the torque vibration suppression device, for example, “a torsional shock absorber for automobiles” is known (see Patent Document 1). The main part of this torsional shock absorber for an automobile is constituted by stacking four elastic plates having the same shape and formed from a flat steel material having spring properties. Each plate has an arm that spirally continues between the outer peripheral side support ring and the inner peripheral side support ring, and is laminated so that the spiral direction of the arms is alternately reversed. Hereinafter, each of the four plates is referred to as plate A, plate B, plate C, and plate D. For example, if the spiral direction of plate A is clockwise, the spiral direction of plate B is counterclockwise, the spiral direction of plate C is clockwise, and the spiral direction of plate D is counterclockwise.

  After the four plates are stacked in the order as described above, the outer peripheral support rings are fixed to each other, and the inner peripheral support rings are fixed to each other.

  In such a configuration, when a rotation angle difference in the direction around the axis is given between the inner and outer peripheries (inner peripheral side support ring and outer peripheral side support ring) of the assembly of plates A to D, the plates A to D are changed according to the angular difference. Each arm of D is elastically deformed. That is, the width of the spiral is widened or narrowed, and at this time, each arm generates a drag force in a direction that reduces the rotational angle difference.

Therefore, if engine torque is applied to one of the inner and outer peripheries of the plate assembly and the engine torque is extracted from the other side, the above-mentioned rotational angle difference caused by the fluctuation component of the engine torque is suppressed, and unpleasant noise is reduced. Can be achieved. In addition, in this prior art, the main part is composed of a laminate of four plates, so that it is possible to reduce the axial thickness and achieve a reduction in thickness. By reducing the number, it is possible to contribute to downsizing of the torque converter and the like.
Japanese Patent No. 2899975 (page 5-6, FIG. 4)

  However, the above prior art is advantageous in that the axial thickness can be reduced and the assembly space can be further reduced, but only four plates of the same shape are simply laminated. For this reason, the spring constant obtained from the laminated body becomes single. For example, when trying to increase the “twist angle” in a limited assembly space, the arm (spiral spring) of each plate is lengthened. Therefore, there is a problem that the plate area becomes large and the above-mentioned requirement (miniaturization of the torque converter or the like) cannot be met.

  The present invention has been made in view of the above points, and an object thereof is to easily obtain a large twist angle without incurring an increase in size while obtaining a vibration suppressing effect such as a sufficient booming sound. Therefore, it is possible to meet the demand for downsizing of a torque converter or the like.

The torque vibration suppressing device according to the present invention is a rotational torque transmitted from the driving side rotating member to the driven side rotating member interposed between the driving side rotating member and the driven side rotating member arranged coaxially. It is applied to a torque vibration suppression device that suppresses vibrations of the plate. The feature of this device is that it has a plurality of flat spiral springs with different stiffnesses, and the inner peripheral ends of all the spiral springs are fixed to each other. The fixed portion is used as an engaging portion with either the driving side rotating member or the driven side rotating member, and the outer peripheral end of the low rigidity spiral spring is set as either the driving side rotating member or the driven side rotating member. And a restricting means for restricting a relative position change between the outer peripheral ends of the low-rigid spiral spring and the high-rigid spiral spring in the axial direction to a predetermined amount. .
In the present invention, a torque vibration suppressing device composed of a plurality of flat spiral springs having different stiffnesses is inserted between the driving side rotating member and the driven side rotating member arranged on the same axis. Since this torque vibration suppressing device has the above-described characteristic configuration, (a) the spring of the low rigidity spiral spring is exclusively used in the region where the rotational torque transmitted from the driving side rotating member to the driven side rotating member is small. The constants dominate the “torque-torsion angle characteristics” of the torque vibration suppression device. (B) In the region where the rotational torque is large, the parallel composite value of the spring constant of the low-rigid spiral spring and the spring constant of the high-rigid spiral spring is Dominates the “torque-torsion angle characteristics” of the torque vibration suppression device. Therefore, (b) and (b) achieve a two-stage “torque-torsion angle characteristic”. By adjusting the torque range in (b), vibration suppression effects such as full sound can be sufficiently achieved. A large twist angle can be easily obtained without increasing the size. Therefore, the above-described object of being able to meet the demand for downsizing the torque converter or the like is achieved.

  According to the present invention, a two-stage “torque-torsion angle characteristic” can be achieved. For this reason, it is possible to easily obtain a large torsion angle without causing an increase in size while satisfying a vibration suppressing effect such as a sufficient booming noise, and to meet a demand for downsizing a torque converter or the like.

  Embodiments of the present invention will be described below with reference to the drawings, taking application to a torque converter as an example. It should be noted that the specific details or examples in the following description and the illustrations of numerical values, character strings, and other symbols are only for reference in order to clarify the idea of the present invention, and the present invention may be used in whole or in part. Obviously, the idea of the invention is not limited. In addition, a well-known technique, a well-known procedure, a well-known architecture, a well-known circuit configuration, and the like (hereinafter, “well-known matter”) are not described in detail, but this is also to simplify the description. Not all or part of the matter is intentionally excluded. Such well-known matters are known to those skilled in the art at the time of filing of the present invention, and are naturally included in the following description.

(Embodiment 1)
<Structure of torque converter>
FIG. 1 is a cross-sectional view of a torque converter. In this figure, the torque converter 1 is provided between the engine 2 and the transmission 3. A front cover 4 is attached to the output shaft 2 a of the engine 2, and a torque converter cover 5 is disposed opposite to the front cover 4. The outer peripheral edge portions of the front cover 4 and the torque converter cover 5 are fixed to each other by bolts 6 and nuts 7, whereby the front cover 4 and the torque converter cover 5 are transmitted through the output shaft 2a. It receives the rotational torque from and rotates integrally.

  The outer edge portion 5a of the torque converter cover 5 is bent toward the transmission 3, the one end side of the impeller cover 8 is fixed to the tip of the outer edge portion 5a, and the other end side of the impeller cover 8 is connected to the input of the transmission 3. It is fixed to a rotating body 9 that is rotatably engaged on the outer peripheral surface of the shaft 3a. The torque converter cover 5 and the impeller cover 8 define a liquid-tight converter chamber 10, and a fluid (automatic fluid) is sealed in the converter chamber 10.

  Three types of impellers, that is, an impeller 11 fixed to the impeller cover 8, a turbine 13 fixed to the turbine shell 12, and a stator 15 fixed to the carrier 14 are arranged in the converter chamber 10. The rotation of the impeller cover 8 is transmitted to the turbine 13 and the stator 15 via the impeller 11 and the fluid, and the rotational torque increased by the turbine 13 is transmitted to the turbine shell 12.

  The inner peripheral end of the turbine shell 12 is fixed to a turbine hub 16 that rotates integrally with the input shaft 3a of the transmission 3, and thus increases by the action of the three impellers (the impeller 11, the turbine 12, and the stator 15). The rotational torque of the engine 2 thus transmitted is finally transmitted to the input shaft 3 a of the transmission 3.

  The converter chamber 10 further includes a damper device 17 for absorbing fluctuations in rotational torque from the engine 2 and a lock-up device for transmitting rotational torque from the engine 2 directly (without fluid). 18 is incorporated. That is, a damper device 17 and a lockup device 18 are incorporated in a slight gap between the turbine shell 12 and the torque converter cover 5 in order from the left side as viewed in the drawing.

  The lock-up device 18 includes a lock-up piston 19 and a facing (friction material) 20 provided at the peripheral edge of the lock-up piston 19, and controls the fluid pressure between the lock-up piston 19 and the torque converter cover 5. By lowering (lock-up operation), the facing 20 is strongly pressed against the inner surface of the torque converter cover 5, whereby the rotational torque from the engine 2 is torque converter cover 5 → lock-up piston 19 → damper device 17 → turbine hub 16 → transmission. 3 is directly transmitted through the path of the input shaft 3a.

<Detailed structure of damper device>
The damper device 17 is located between the lockup device 18 and the input shaft 3a of the transmission 3 (and the turbine hub 16 that rotates integrally with the transmission 3), and the rotational torque transmitted from the engine 2 to the transmission 3 during the lockup operation described above. Absorbs fluctuating components. The principle of this damper device 17 is that an elastic body is interposed in the transmission path of the rotational torque, thereby obtaining a desired fluctuation distribution suppression effect by the “torque-torsion angle characteristics” of the elastic body. The embodiment is characterized in that two-stage characteristics are obtained by combining two types of spiral springs having different radial rigidity, as will be described in detail below.

  A spiral spring is a spring that uses the winding force or rewinding force of a spring material. Also called spring spring. A timepiece spring is a representative example, but many timepiece springs are formed by winding a belt-like spring plate around an axis and have an axial thickness corresponding to the width of the spring plate. The presence of this thickness is undesirable for the present invention. This is because the thickness of the damper device 17 is increased and eventually the torque converter 1 is increased in size. In this regard, a plate-like spiral spring formed by punching a flat spring material or the like is convenient for application to the present invention. This is because the thickness of the plate-like spiral spring is only equivalent to the plate thickness of the flat spring material, and thus the torque converter 1 is not enlarged.

  The damper device 17 shown in the figure is composed of three flat, substantially circular plates 21, 22, and 23. In the following description, the left plate 21 is referred to as a “first plate”, the central plate 22 is referred to as a “second plate”, and the left plate 23 is referred to as a “third plate”. As will be described later, the inner peripheral ends of the first to third plates 21 to 23 are fixed to each other by welding or the like, and only the first plate 21 and the third plate 23 are welded or the like to the outer peripheral ends. It is fixed. That is, the outer peripheral end of the second plate 22 is free in the direction around the axis.

  FIG. 2 is a plan view of the first plate 21 (a view of the first plate 21 as viewed from the transmission 3 toward the engine 2; hereinafter, the other plan views are also the same). The first plate 21 has a substantially circular shape formed of a flat steel material having spring properties, and a support ring 21a is integrally attached to an inner peripheral end thereof. The four holes 21b drilled in the support ring 21a are for fixing to the turbine hub 16 by the locking parts 24 in FIG.

  Three outer peripheral convex portions 21c arranged at equal intervals along the circumferential direction are formed at the outer peripheral end of the first plate 21, and the outer peripheral convex portions 21c are formed as shown in FIG. A predetermined amount d projects from the back side of the first plate 21. This protrusion amount d is slightly larger than the thickness of the second plate 22 in order to finally fix the back side of the outer peripheral convex portion 21c and the outer peripheral convex portion 23a of the third plate 23 by welding or the like. ing. The inner peripheral end and the outer peripheral end of the first plate 21 are connected by a spiral arm 21d that is clockwise when viewed from the direction shown in the drawing. In addition, "... direction" here means that a radius becomes large as it advances in the direction. In the illustrated example, the number of the outer peripheral convex portions 21c is three, but the number is not limited thereto. It is sufficient that there are at least three and are arranged at equal intervals on the outer periphery.

  FIG. 3 is a plan view of the second plate 22. The second plate 22 also has a substantially circular shape formed from a flat steel material having spring properties. Similarly, the outer peripheral end 22e is formed with three outer peripheral convex portions 22a arranged at equal intervals along the circumferential direction, and the space between the outer peripheral end and the inner peripheral end extends from the inner peripheral end to the outer peripheral end. It is connected by a large number of arms 22b extending radially toward the ends.

  Here, the arm 22b is a remaining portion of a large number of elongated holes 22c drilled along the radial direction of the second plate 22, and the elongated holes 22c are elongated holes 22c ′ of FIG. As shown in FIG. 4, the holes may be formed so as to be slightly inclined with respect to the radial line 22d. When skewed in this manner, the arm 22b 'between the elongated holes 22c' is also skewed with respect to the radial line 22d, and the radius of the skewed arm 22b 'increases in the clockwise direction. Therefore, it corresponds to the “spiral spring” similar to the arm 21d of the first plate 21. Therefore, the arm 21b of FIG. It can be said that the spiral spring has zero skew in the radial direction.

  FIG. 4 is a plan view of the third plate 23. The third plate 23 is a plate having the same spring constant as that of the first plate 21, and is formed of a flat steel material having spring properties like the first and second plates 21 and 22. It has a substantially circular shape. And the outer peripheral end is formed with three outer peripheral convex portions 23a arranged at equal intervals along the circumferential direction, and the space between the outer peripheral end and the inner peripheral end extends from the inner peripheral end to the outer peripheral end. The force generated by the first plate 21 by being connected by an arm 23b that is continuous in a predetermined direction (a direction reverse to the arm 21d of the first plate 21 in the assembled state; in the illustrated example, a counterclockwise direction). (The radial force on the shaft) is canceled.

  When the rigidity in the direction around the axis of these three plates (first to third plates 21 to 23) is compared, the arms 21d and 23b of the first plate 21 and the third plate 23 are The arms 22b of the second plate 22 are not skewed at all, or even if skewed, a slight skew amount (FIG. 3 ( Therefore, the rigidity in the direction around the axis of the arm 22b of the second plate 22 is considerably higher than the rigidity in the direction around the axis of the first plate 21 and the third plate 23. That is, the first plate 21 and the third plate 23 are “low-rigidity plates”, and the second plate 22 is a “high-rigidity plate”.

  5 and 6 are assembled state diagrams of three plates (first plate 21, second plate 22, and third plate 23). In these drawings, the first plate 21 and the third plate 23 are arranged on both surfaces of the second plate 22, and the inner peripheral ends of the three plates 21, 22, 23 are fixed by welding or the like. The outer peripheral convex portion 21c of the first plate 21 and the outer peripheral convex portion 23a of the third plate 23 are assembled by being fixed by welding or the like. 5B, the inner peripheral surface 21e of the outer peripheral convex portion 21c of the first plate 21 and the outer peripheral surface 22e of the second plate 22 are assembled by inlay fitting.

  The assembled state shown in the figure is a state before being assembled to the torque converter 1. That is, this is when no external force is applied to the three plates 21 to 23. Hereinafter, this state is referred to as an “initial state”.

  In the initial state, the outer peripheral convex portion 22a of the second plate 22 is separated by a predetermined angle along the circumferential direction between the outer peripheral convex portions 21c and 23a integrated with the first and third plates 21 and 23. In the position. This angle will be represented by “α” and “β” for convenience. “Α” is an angle to the outer peripheral convex portions 21 c and 23 a closer to the outer peripheral convex portion 22 a of the second plate 22, and “β” is an angle to the far outer peripheral convex portions 21 c and 23 a. .

  FIG. 7 is an assembly diagram of the damper device 17 assembled as described above to the torque converter 1. In this figure, three engagement portions 19 a are formed at equal intervals on the peripheral edge portion of the lock-up piston 19. The outer peripheral convex portions 21c and 23a of the first and third plates 21 and 23 of the damper device 17 are fitted and assembled to these engaging portions 19c. In addition, the outer peripheral convex part 22a of the 2nd plate 22 does not engage with the lockup piston 19, and is free in the circumference direction. Further, the inner peripheral ends of the three plates 21 to 23 are fixed to each other and are fixedly assembled to the turbine hub 16 of the torque converter 1.

  FIG. 8 is a characteristic diagram of the damper device 17. The vertical axis represents the magnitude and direction of the rotational torque of the power train system, and the horizontal axis represents the magnitude and direction of the twist angle of the damper device 17. Here, “drive” on the vertical axis indicates the torque direction when the tire is driven by the rotational torque from the engine 2, and “coast” indicates when the engine 2 is driven by the rotational torque from the tire (so-called This is the torque direction when the engine brake is applied. Further, “broadening” on the horizontal axis refers to the twist angle direction when the spiral spacing of the arms 21d and 23b of the damper device 17 is widened, and “winding” is the twist angle direction when the spiral spacing is conversely narrowed. Say.

  In this characteristic diagram, the twist angle is gradually increased from the point P1 to the point P2, and the two characteristic lines L1 and L2 that gradually increase after P2 and the points P1 to P3 are gradually increased. Two characteristic lines L3 and L4 are drawn which decrease the twist angle and increase the degree of decrease sharply after P3. P1 is that in the above-described initial state (when no external force is applied to the three plates 21 to 23).

  P2 indicates that the outer peripheral convex portions 21c and 23a of the first and third plates 21 and 23 move relatively counterclockwise (see the white arrow a) in FIG. 5 or FIG. This is when it comes into contact with the outer peripheral convex portion 22a of the plate 22 (that is, when the angle β becomes zero). Similarly, P3 indicates that the outer peripheral projections 21c and 23a of the first and third plates 21 and 23 are moved in the clockwise direction (see the white arrow b) in FIG. This is the case when the second plate 22 is in contact with the outer peripheral convex portion 22a (that is, when the angle α is zero).

  Now, when a torque in the “drive” direction is applied from the initial state, the twist angle of the damper device 17 increases along the characteristic line L1. The torsion angle given by this characteristic line L1 corresponds to the magnitude of elastic deformation of the arms 21d, 23b of the first and third plates 21, 23. Therefore, if the spring constants of the arms 21d and 23b of the first and third plates 21 and 23 are optimized and particularly adapted to the fluctuation frequency of the rotational torque of the engine 2, the damper device 17 exhibits low rigidity. The booming noise can be suppressed.

  On the other hand, when the twist angle of the damper device 17 increases beyond the point P2, the outer peripheral convex portions 21c and 23a of the first and third plates 21 and 23 come into contact with the outer peripheral convex portion 22a of the second plate 22. The arm 22b of the second plate 22 that has been free until now also undergoes elastic deformation. Therefore, after the point P2, a transition is made to a characteristic line L2 in which the spring constants of the arms 21d and 23b of the first and third plates 21 and 23 and the spring constant of the arm 22b of the second plate 22 are combined in parallel. Since the degree of change of the characteristic line L2 is more rapid than the degree of change of the characteristic line L1 so far, the damper device 17 can exhibit high rigidity, for example, stepwise accompanying sudden depression of the accelerator. Even when a torque change occurs, the torque change can be received without any trouble.

  The same applies to torque input in the “coast” direction. That is, when a torque in the “coast” direction is applied from the initial state, the twist angle of the damper device 17 decreases along the characteristic line L3. The torsion angle given by this characteristic line L3 corresponds to the magnitude of elastic deformation of the arms 21d, 23b of the first and third plates 21, 23.

  On the other hand, when the twist angle of the damper device 17 increases beyond the point P3, the outer peripheral convex portions 21c and 23a of the first and third plates 21 and 23 come into contact with the outer peripheral convex portion 22a of the second plate 22. The arm 22b of the second plate 22 that has been free until now also undergoes elastic deformation. Therefore, after the point P3, a transition is made to a characteristic line L4 in which the spring constants of the arms 21d and 23b of the first and third plates 21 and 23 and the spring constant of the arm 22b of the second plate 22 are combined in parallel. Since the degree of change of the characteristic line L4 is more rapid than the degree of change of the characteristic line L1 so far, the damper device 17 can exhibit high rigidity.

  (1) Thus, according to the damper device 17 of the present embodiment, since the three plates (first to third plates 21 to 23) are laminated, the axial thickness thereof is determined by the plate lamination. As many as the number of sheets, it can be made extremely thin. Therefore, the torque converter 1 can be reduced in size.

  (2) In addition, as shown in FIG. 8, the “torque-torsion angle characteristic” is a two-stage characteristic, that is, with respect to torque input in the “drive” direction, a point P2 having a predetermined twist angle from the point P1 in the initial state. And a characteristic line L3 from a point P1 in the initial state to a point P3 having a predetermined twist angle with respect to torque input in the “coast” direction. Since the two-stage characteristics with the characteristic line L4 thereafter are set, the maximum torsion angles (P2, P3) can be freely set, and the angles α, β are simply adjusted when setting. Therefore, it is possible to obtain a particularly beneficial effect that the tuning (fine adjustment) of the damper device 17 is easy.

  (3) Incidentally, since the rigidity of the first plate 21 and the third plate 23 is low, the outer end portions of these plates are easy to move, so that the center of gravity of the first plate 21 and the third plate 23 is reduced. Although it is conceivable that vibration is generated due to movement and rotation, the first and second plates 21 and 23 having low rigidity and the second plate 22 having high rigidity are stacked together. Since the damper device 17 is configured so that the inner peripheral surface 21e of the outer peripheral convex portion 21c and the outer peripheral surface 22e of the second plate 22 are fitted together, there is no fear of the occurrence of the vibration, but rather the damper device 17 This centering function can be mainly handled by the high-rigidity second plate 22, and there is an advantage that it is not necessary to separately provide a centering means.

  (4) And this merit (there is no need to provide a separate centering means) brings about the following ripple effect. That is, when the drive-side member is the lock-up piston 19, the second plate 22 has a function of centering the first plate 21 and the third plate 23, thereby preventing the lock-up piston 19 from operating. The effect that it can prevent that it is prevented is also acquired. That is, when the movement of the outer ends of the first plate 21 and the third plate 23 is centered on the inner peripheral surface 19b (see FIG. 7) of the lockup piston 19, The contact between the peripheral surface 19b and the first plate 21 or the third plate 23 prevents the movement of the piston in the axial direction (that is, the operation of the lockup piston 19 is prevented). By providing the centering function of the first plate 21 and the third plate 23 and engaging only with the lock-up piston 19 in the rotation direction (axial direction), the inner peripheral surface 19b of the lock-up piston 19 And the outer peripheral surface 21f (see FIG. 7) of the first plate 21 and the outer peripheral surface 23f (see FIG. 7) of the third plate 23 are not in contact with each other. It can reliably prevent the operation of the click-up piston 19 is prevented.

  (5) In addition, the high-rigidity second plate 22 is not easily deformed out of plane, and therefore it is not necessary to provide the damper device 17 with a mechanism for preventing out-of-plane deformation. Furthermore, for example, if the first and third plates 21 and 23 having low rigidity are made as thick as possible, deformation in the thickness direction (that is, out-of-plane deformation) is less likely to occur. Combined with rigidity, a further effect of preventing out-of-plane deformation can be obtained.

  (6) Further, the third plate 23 is a plate having the same spring constant as that of the first plate 21, and, like the first and second plates 21 and 22, a plate-like steel material having spring properties. The outer peripheral end is formed with three outer peripheral convex portions 23a arranged at equal intervals along the peripheral direction, and the outer peripheral end, the inner peripheral end, Is connected by an arm 23b continuous in a predetermined direction from the inner peripheral end to the outer peripheral end (direction opposite to the arm 21d of the first plate 21 in the assembled state; counterclockwise direction in the illustrated example). Thus, the radial force generated by the first plate 21 on the axis can be canceled.

The outer extension of the present invention is not limited to the above embodiment. It goes without saying that various modifications and developments are included within the scope of the idea.
For example, in the above embodiment, two low-rigidity plates (the first plate 21 and the second plate 23) are laminated on both surfaces of the high-rigidity second plate 22, It is not limited to this. You may deform | transform as follows.

(Embodiment 2)
FIG. 9 is a diagram showing a modification thereof. In this figure, the configuration of each part of the torque converter 1 is the same as that of the above-described embodiment except for the damper device 25, and thus the description thereof is omitted. The damper device 25 of this modification is common to the above embodiment in terms of the number of stacked plates, but differs in that one low-rigidity plate is sandwiched between two high-rigidity plates. That is, the damper device 25 is configured by stacking a high-rigidity first plate 26, a low-rigidity second plate 27, and a high-rigidity third plate 28.

  FIG. 10 is a plan view of the high-rigidity plate (first and third plates 26 and 28). The first and third plates 26 and 28 have the same shape. That is, the first plate 26 has a substantially circular shape formed from a flat steel material having spring properties, and three outer peripheral convex portions 26a arranged at equal intervals along the circumferential direction are formed on the outer peripheral end thereof. The outer peripheral end and the inner peripheral end are connected by a number of arms 26b extending radially from the inner peripheral end to the outer peripheral end.

  The arm 26b is a remaining portion of a number of long holes 26c drilled along the radial direction of the first plate 26. The long hole 26c may be formed so as to be slightly inclined with respect to the radial line 26d, as indicated by a long hole 26c 'in FIG. When skewed in this manner, the arm 26b 'between the elongated holes 26c' is also skewed with respect to the radial line 26d, and the radius of the skewed arm 26b 'increases in the clockwise direction. Therefore, the arm 26b shown in FIG. 6A is also a spiral spring (exactly, a spiral having a skew angle of zero with respect to the radial direction of the first plate 26). Spring).

  Similarly, the 3rd plate 28 has the substantially circular shape formed from the flat steel material which has spring property, and the outer peripheral edge has three outer peripheral convex parts 28a arranged at equal intervals along the circumferential direction. The outer peripheral end and the inner peripheral end are connected by a number of arms 28b extending radially from the inner peripheral end to the outer peripheral end. The arm 28b is a remaining portion of a number of long holes 28c drilled along the radial direction of the third plate 28 in the same manner as described above.

  As shown in FIG. 5C, the outer peripheral convex portions 26a and 28a of the first and third plates 26 and 28 are bent by a predetermined amount in the axial direction, and the bent end portions of both are fixed portions by welding or the like. 29. Here, after the fixing portion 29 is formed, a gap A is generated between the first and third plates 26 and 28. The second plate 27 is sandwiched in the gap A and assembled.

  FIG. 11 is a plan view of the second plate 27. This 2nd plate 27 also has the substantially circular shape formed from the flat steel material which has spring property. A support ring 27a is integrally attached to the inner peripheral end, and the four holes 27b drilled in the support ring 27a are locking parts as in the damper device 17 of the above embodiment. 24 for fixing to the turbine hub 16.

  At the outer peripheral end of the second plate 27, three outer peripheral concave portions 27c are formed that are arranged at equal intervals along the circumferential direction. The outer peripheral recess 27 c serves as an engagement portion of the lockup piston 19 when the damper device 25 is assembled to the torque converter 1. The inner peripheral end and the outer peripheral end of the second plate 27 are connected by a spiral arm 27d that is counterclockwise when viewed from the illustrated direction.

  When the rigidity in the direction around the axis of these three plates (first to third plates 26 to 28) is compared, the arm 27d of the second plate 27 is greatly skewed with respect to the radial direction of the plate. On the other hand, the arms 26b and 28b of the first plate 26 and the third plate 28 are not skewed at all, or even if skewed, a slight skew amount (FIG. 10 (b Therefore, the rigidity of the arms 26b, 28b of the first and third plates 26, 28 is considerably higher than the rigidity of the second plate 27 around the axis. That is, the second plate 27 is a “low-rigidity plate”, and the first and third plates 26 and 28 are “high-rigidity plates”.

  FIG. 12 is a state diagram when the damper device 25 assembled by the above three plates (first to third plates 26 to 28) is assembled to the torque converter 1. In this figure, the inner peripheral end (the inner peripheral ends of the first to third plates 26 to 28) of the damper device 25 is fixed to the turbine hub 16. Of the outer peripheral ends of the damper device 25, the outer peripheral ends (outer peripheral convex portions 26a and 28a) of the first and third plates 26 and 28 are free in the direction around the axis. The outer peripheral end (outer peripheral recess 27 c) is engaged with the lockup piston 19. Further, as shown in FIG. 10C, the inner peripheral surfaces 26 e and 28 e of the outer peripheral protrusions 26 a and 28 a of the first and third plates 26 and 28 and the outer periphery of the outer peripheral end of the second plate 27. The surface 27e is inlay-fitted.

  When a torque in the “drive” direction or a torque in the “coast” direction is applied to the damper device 25, first, elastic deformation occurs in the low-rigidity second plate 27 according to the direction and magnitude of the torque, If the deformation exceeds a predetermined value, the first and third plates 26 and 28 having high rigidity are also elastically deformed.

  FIG. 13 is a conceptual diagram for explaining the “predetermined value”. In this figure, the amount of elastic deformation of the low-rigidity second plate 27 increases, and for example, the outer peripheral recess 27c of the second plate 27 moves in the counterclockwise direction (see the white arrow c) in the figure. When the side surface of the outer peripheral concave portion 27c and the side surfaces of the outer peripheral convex portions 26a and 28a of the first and third plates 26 and 28 come into contact with each other, the elastic deformation of the first and third plates 26 and 28 is also performed thereafter. Prompted.

  Accordingly, the “torque-torsion angle characteristic” of the damper device 25 is given only by the spring constant of the low-rigidity second plate 27 until the contact state, and after the contact state, Since it is given by a parallel composite value of the spring constant of the second plate 27 having low rigidity and the spring constant of the first and third plates 26 and 28 having high rigidity, such a configuration also provides “torque-torsion”. A two-stage characteristic of “angular characteristics” can be realized.

  Incidentally, also in this embodiment, since the rigidity of the second plate 27 is low, the outer end portion of the second plate 27 is easy to move. As a result, the center of gravity of the second plate 27 moves, and vibration accompanying rotation occurs. It is conceivable to stack the low-rigidity second plate 27 and the high-rigidity first and third plates 26, 28, and the outer peripheral convex portions of the first and third plates 26, 28. Since the damper device 25 is configured so as to fit the inner peripheral surfaces 26e, 28e of 26a, 28a with the outer peripheral surface 27e of the second plate 27, there is no fear of the occurrence of the above-mentioned vibration. Rather, the damper device The centering function of 25 can be mainly assigned to the first and second plates 26 and 28 having high rigidity, and there is an advantage that it is not necessary to separately provide centering means.

  And this merit (it is not necessary to provide a separate centering means) brings about the following ripple effects like the above-mentioned embodiment. That is, when the drive-side member is the lock-up piston 19, the first and third plates 26 and 28 have the centering function of the second plate 27, thereby preventing the operation of the lock-up piston 19. The effect that it can prevent is also acquired. That is, when the movement of the outer end portion of the second plate 27 is centered on the inner peripheral surface 19b of the lockup piston 19, the inner peripheral surface 19b of the lockup piston 19 and the second plate 27 The contact prevents the piston from moving in the axial direction (that is, prevents the lock-up piston 19 from being actuated), but the first and third plates 26 and 28 have the function of centering the second plate 27, In addition, since the lock-up piston 19 is fitted only in the rotational direction (axial direction), the inner peripheral surface 19b of the lock-up piston 19 and the outer peripheral surface of the second plate 27 do not come into contact with each other. It is possible to reliably prevent the operation of the up piston 19 from being hindered.

  Further, as in this embodiment, when one low-rigidity plate (second plate 27) is sandwiched between two high-rigidity plates (first and third plates 26, 28), high It is preferable because a more reliable out-of-plane deformation prevention function can be realized by the two rigid plates (first and third plates 26 and 28). Furthermore, for example, if the low-rigidity second plate 27 is made as thick as possible, deformation in the thickness direction (that is, out-of-plane deformation) is less likely to occur, so the height of the first and third plates 26 and 28 is high. Combined with rigidity, a further effect of preventing out-of-plane deformation can be obtained.

(Embodiment 3)
FIG. 14 is a diagram showing another modification. The difference from the second embodiment is that the spiral spring is changed to a plurality of spiral springs having a single elastic arm. Compared to the second embodiment, the spiral spring has a half plate thickness and is easily deformed out of the plane, but is excellent in that a large twist angle can be taken.

  In the figure, 31 and 32 are two low-rigid spiral springs having the same spiral shape. The shape of the spiral portion is constituted by one elastic arm (see reference numeral 21d) as in FIG. The two low-rigid spiral springs 31 and 32 are welded at the inner peripheral portion and the outer peripheral portion so as to be rotated 180 degrees so that the spiral shape is point-symmetric. On the outer periphery of each of the two low-rigid spiral springs 31 and 32, a protrusion similar to the outer peripheral recess 27c in FIG. 11 is formed.

  Similarly to the outer peripheral recess 27 c of FIG. 11, this protrusion is fitted to the notch of the lock-up piston 19, and is integrally rotatable with the lock-up piston 19 so as to be capable of relative rotational movement in the axial direction. Reference numeral 33 denotes two high-rigid springs, the shape of which is the same as that of the first and third plates 26 and 28 in FIG. These two high rigidity springs 33 are arranged in the axial direction so as to sandwich the low rigidity springs 31 and 32 therebetween. The inner periphery of the two high-rigidity springs 33 is welded to the low-rigidity springs 31 and 32, but the outer periphery is free (not welded to the low-rigidity springs 31 and 32). The outer peripheries of the two high stiffness springs 33 are welded and integrated. The assembled state is the same as in FIG.

  In this embodiment configured as described above, the shape of the arms of the low-rigidity springs 31 and 32 is changed from two to one as compared with the second embodiment, and the plate thickness per arm is further changed. Is different in that is approximately halved. The other points, that is, the shape and assembly method of the high-rigidity spring 33 are not significantly different. However, since the shape of the arm is changed from two to one, a larger twist angle is obtained compared to the previous embodiment. There is a peculiar effect that it is obtained.

It is sectional drawing of a torque converter. 3 is a plan view of a first plate 21. FIG. 4 is a plan view of a second plate 22. FIG. 4 is a plan view of a third plate 23. FIG. It is an assembly state figure of three plates. It is an assembly state figure of three plates. FIG. 3 is an assembly diagram of the damper device 17 to the torque converter 1. FIG. 6 is a characteristic diagram of the damper device 17. It is a figure which shows a modification. It is a top view of the 1st and 3rd plates 26 and 28. FIG. 3 is a plan view of a second plate 27. FIG. It is a state figure when the damper apparatus 25 is assembled | attached to the torque converter 1. FIG. It is a conceptual diagram for demonstrating "predetermined value". It is a figure which shows another modification.

Explanation of symbols

16 Turbine hub (driven side rotating member)
17 Damper device (torque vibration suppression device)
19 Lock-up piston (drive side rotating member)
21 First plate (low rigidity spiral spring)
21a Support ring (engagement part)
21c Periphery convex part (engagement part, regulating means)
22 Second plate (high rigidity spiral spring)
22a Periphery convex part (engagement part, regulating means)
23 Third plate (low rigidity spiral spring)
23a Periphery convex part (engagement part, regulating means)
25 Damper device (torque vibration suppression device)
26 First plate (high rigidity spiral spring)
26a Periphery convex part (engagement part, regulating means)
27 Second plate (low rigidity spiral spring)
27c Peripheral recess (engagement part, restricting means)
28 3rd plate (high rigidity spiral spring)
28a Periphery convex part (engagement part, regulating means)

Claims (6)

In a torque vibration suppressing device that suppresses vibration of rotational torque transmitted from the driving side rotating member to the driven side rotating member interposed between the driving side rotating member and the driven side rotating member arranged on the same axis ,
Equipped with a plurality of flat spiral springs with different stiffness
The inner peripheral ends of all the spiral springs are fixed to each other, and the fixed portion is set as an engaging portion with either the driving side rotating member or the driven side rotating member.
The outer peripheral end of the low-rigid spiral spring is an engagement portion with the other of the driving side rotating member or the driven side rotating member,
In addition, the torque vibration suppressing device further includes a restricting unit that restricts a relative position change between the outer peripheral ends of the low-rigid spiral spring and the high-rigid spiral spring in a direction around the axis to a predetermined amount. An outer peripheral convex portion extending in the axial direction is provided at one outer peripheral end of the low-rigid spiral spring and the high-rigid spiral spring, and an outer peripheral surface of the outer peripheral end of the outer peripheral convex portion and the outer peripheral end of the other spiral spring The torque vibration suppressing device according to claim 1, wherein the two are fitted so as to be rotatable in a direction around the axis. 3. The torque vibration suppressing device according to claim 1, wherein low-rigid spiral springs are arranged on both surfaces of the high-rigid spiral spring, respectively. 3. The torque vibration suppressing device according to claim 1, wherein high rigidity spiral springs are disposed on both surfaces of the low rigidity spiral spring, respectively. 5. The torque vibration suppressing device according to claim 3, wherein the spiral direction of the spiral spring disposed on one surface and the spiral spring disposed on the other surface are reversed. 6. The torque vibration suppressing device according to claim 1, wherein the plate thickness of the low-rigid spiral spring is increased with respect to the plate thickness of the high-rigid spiral spring.

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