JP2005155675A - Torque fluctuation absorbing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a torque fluctuation absorbing device capable of suppressing shift of the center of gravity due to generation of radial force when connecting one spiral spring in series and suppressing rotational vibration. <P>SOLUTION: This torque fluctuation absorbing device is arranged between an output shaft of a driving source and an input shaft of a transmission. It has a plurality of spiral springs composed of an inner end part provided on an inside diameter side, an outer end part provided on an outside diameter side, and an elastic arm connecting the inner end part with the outer end part. The inner end parts and the outer end parts of the plurality of spiral springs are mutually connected to form a connection part. The plurality of spiral springs are arranged in series to form a set of spiral springs. An end part on one side of the set of spiral springs is connected with a first rotary member on an output shaft side of the driving source to form the input part, and the other end part is connected with a second rotary member which is coaxial with the first rotary member on the input shaft side of the transmission to form the output part. This torque fluctuation absorbing device is provided with a centering means for restraining the input part, the output part, and the connection part so that they are on the same axis as the center of rotation of the first and second rotary members. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a torque fluctuation absorber for an internal combustion engine.

Generally, in order to reduce body vibrations due to engine vibrations, vehicle interior vibrations, and low-pitched noises, torque fluctuation absorption that absorbs torque fluctuations of the engine that connects the engine output shaft and transmission input shaft via a spring member The device is widely known.
In a conventional torque fluctuation absorber, in order to reduce the natural frequency of a vibration system composed of a spring member, two strips of spiral springs are joined together by outer end members, and one inner end member is placed on the drive side, and the other The inner end member is connected to the driven side. By connecting the spiral springs in series, the spring constant is lowered while preventing an increase in size and weight (for example, see Patent Document 1).
No. 2-5141

However, in the conventional torque fluctuation absorbing device for the spiral springs coupled in series, the coupling portion of the two plate spiral springs is not constrained in the radial direction. There is a problem that vibration occurs.
That is, since a single spiral spring is not an axial object shape, when a torque is received, a radial force is generated, the unconstrained coupling part is biased with respect to the center of rotation, and the spiral spring moves its center of gravity, An imbalance between the center of rotation and the center of gravity occurs.

  The present invention has been made in view of such points, and suppresses the movement of the center of gravity of the spiral spring when the radial force is generated with respect to the generation of the radial force generated by connecting the single spiral spring in series. The purpose is to suppress rotational vibration.

  In order to achieve the above object, a torque fluctuation absorber disposed between the output shaft of the drive source and the input shaft of the transmission, the inner end portion provided on the inner diameter side, and the outer diameter side A plurality of spiral springs comprising an outer end portion provided and an elastic arm connecting the inner end portion and the outer end portion; and the inner end portion or the outer end portion of the plurality of spiral springs. Are connected to each other to form a connection portion, and the plurality of spiral springs are arranged in series to form a spiral spring set, and one end of the spiral spring set is connected to the first output shaft side of the drive source. Torque fluctuation connected to the rotating member as an input unit and the other end as an output unit connected to a second rotating member coaxial with the first rotating member on the input shaft side of the transmission In the absorber, the input unit, the output unit, and the connecting unit are coaxial with the rotation centers of the first and second rotating members. Centering means for constraining to the provided.

  According to the torque fluctuation absorbing device of the first aspect, the centering means performs the first and second rotations of the input portion, the output portion, and the connecting portion of the spiral spring group in which a plurality of spiral springs are arranged in series. Centering is performed with respect to the center of rotation of the member.

  Therefore, in the spiral spring set, the input portion, the output portion, and the connecting portion are constrained to be coaxial, so that the center of gravity of the spiral spring is reduced against the radial force generated when the input torque enters. The movement can be suppressed, and the rotation vibration due to the imbalance between the rotation center and the center of gravity can be suppressed.

  Embodiments of the present invention will be described below with reference to the drawings. It should be noted that the specification or examples of various details and the illustration of numerical values, character strings, and other symbols in the following description are only for reference in order to clarify the idea of the present invention, and all or part of them may Obviously, the idea of the invention is not limited. In addition, a well-known method, 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.

  Embodiments for realizing a torque fluctuation absorbing device according to the present invention will be described below as embodiments corresponding to claims 1, 2, 3, 4, 5, 6, and 7. Based on

FIG. 1 is a cross-sectional view of the torque converter 40.
First, the configuration of the torque converter 40 will be described.
In this figure, the torque converter 40 is provided between an engine (drive source / not shown) and a transmission (transmission / not shown). A drive plate (not shown) is attached to an output shaft (not shown) of the engine, and a torque converter cover 22 is disposed opposite to the drive plate. The outer peripheral portions of the drive plate and the torque converter cover 22 are fixed to each other with bolts 21 and nuts (not shown), whereby the drive plate and the torque converter cover 22 are transmitted from the engine transmitted via the output shaft. It receives the torque of and rotates integrally.

  The torque converter cover 22 is coupled to the outer peripheral end of the impeller cover 23a, and the inner peripheral end of the impeller cover 23a rotates on the outer peripheral surface of the transmission input shaft 30 that rotates about the rotation center L (rotation center of the rotating member). Further, it is coupled to a rotating body 34 that is rotatably arranged. The torque converter cover 22 and the impeller cover 23 a define a liquid-tight converter chamber 35, and fluid (automatic fluid) is sealed inside the converter chamber 35.

  In the converter chamber 35, there are three types of impellers, that is, an impeller 24 fixed to the impeller cover 23a, a turbine 26 fixed to the turbine shell 23c and rotating around the rotation center L, and a stator fixed to the carrier 23b. The rotation of the impeller cover 23a is transmitted to the turbine 26 and the stator 25 via the impeller 24 and fluid, and the torque increased by the turbine 26 is transmitted to the turbine shell 23c. .

  The turbine shell 23c is coupled to the damper support member 28 (first centering member) and the transmission input shaft 30 at the inner periphery by a turbine hub 27 and a rivet 29, and at the outer periphery, the damper retainer 31 (second rotation). Member). That is, the damper retainer 31 and the damper support member 28 rotate around the rotation center L.

  The engine torque increased by the action of the three impellers (impeller 24, turbine 26, stator 25) is finally transmitted to the input shaft 30 of the transmission.

  The converter chamber 35 further includes a damper device 41 (torque fluctuation absorber / described later) for absorbing torque fluctuations from the engine and a torque directly from the engine (without fluid). The lock-up clutch 42 is incorporated. That is, the damper device 41 and the lock-up clutch 42 are incorporated in the slight gap between the turbine shell 23c and the torque converter cover 22 in order from the left side as viewed in the drawing.

  The lock-up clutch 42 is provided on the boss portion of the turbine hub 27, and is provided on the lock-up piston 32 (first rotating member) that rotates about the rotation center L and the peripheral portion of the lock-up piston 32. The lockup clutch facing is formed on the content surface of the torque converter cover 22 by lowering the fluid pressure between the lockup piston 32 and the torque converter cover 22. The torque from the engine is directly transmitted through the path of the torque converter cover 22 → the lockup piston 32 → the damper device 41 → the turbine hub 27 → the transmission input shaft 30.

Next, the configuration of the damper device 41 will be described with reference to FIGS. 1, 2, and 3.
The damper device 41 includes a spiral spring set 43 including the spiral spring 1 and the spiral spring 2, a second centering member 4 (second centering member), a third centering member 3 (third centering member), and a damper support. It is comprised with the member 28. FIG.

  As shown in FIG. 2, the spiral spring 1 has an elastic arm 9, an inner ring 8 (inner end portion / connecting portion), and an outer ring 7 (outer end portion / output portion) formed from the same member by press punching, for example. Yes. The inner ring 8 of the spiral spring 1 is welded to the inner ring 15 (inner end / connecting portion) of the spiral spring 2 (described later) and the connection portion 5 over the entire circumference to constitute a spiral spring set 43. The inner peripheral surface 11 a of the inner ring 8 of the spiral spring 1 is fitted to the outer peripheral surface of the cylindrical portion 3 b formed on the inner peripheral portion of the third centering member 3 so as to be slidable in the rotational direction. Further, the side surface on the turbine shell 23 c side of the outer ring 7 of the spiral spring 1 is welded over the entire periphery with the side surface of the flange portion 3 a of the third centering member 3 and the connection portion 13. Three protrusions 10 are formed at equal intervals on the outer peripheral surface 11b of the outer ring 7 of the spiral spring 1, and a notch (not shown) formed in a damper retainer 31 that is a second rotating member. The torque is transmitted to the damper retainer 31 by fitting and rotating integrally.

  Similarly, as shown in FIG. 3, in the spiral spring 2, the elastic arm 16, the inner ring 15, and the outer ring 14 (outer end / input part) are formed from the same member by, for example, press punching. The inner peripheral surface 18 a of the inner ring 15 of the spiral spring 2 is fitted to the outer peripheral surface of the cylindrical portion 4 b formed on the inner peripheral portion of the second centering member 4 so as to be slidable in the rotational direction. Further, the side surface of the outer ring 14 of the spiral spring 2 on the lock-up piston 32 side is welded to the side surface of the cylindrical portion 4 a of the second centering member 4 and the connection portion 6 over the entire circumference. Three protrusions 17 are formed at equal intervals on the outer peripheral surface 18b of the outer ring 14 of the spiral spring 2, and notches (not shown) formed in the lockup piston 32 that is the first rotating member. , And rotate together to transmit torque to the spiral spring set 43.

The inner peripheral surfaces of the cylindrical portion 3b of the third centering member 3 and the cylindrical portion 4b of the second centering member 4 are fitted to the outer peripheral surface of the cylindrical portion 28b of the damper support member 28 so as to be slidable in the rotational direction.
About the 3rd centering member 3 and the 2nd centering member 4, the inner peripheral parts are not contacting and there is no mechanical relationship.

  A gap s is formed between the outer peripheral surface 11 b of the outer ring 7 and the outer peripheral surface 18 b of the outer ring 14 and the inner peripheral surfaces of the damper retainer 31 and the lockup piston 32.

Next, the operation of the first embodiment will be described.
When the lockup clutch 42 does not act, the engine torque is transmitted via the fluid. Further, when the lockup clutch 42 is operated, the engine torque is transmitted through the lockup path.

  In this case, the engine torque is transmitted to the torque converter cover 22, and is transmitted by pushing the protruding side surface 19 of the outer ring 14 of the spiral spring 2 in the rotational direction via the lock-up facing 33 and the lock-up piston 32.

  This torque is transmitted to the outer ring 14, the elastic arm 16, the inner ring 15, the inner ring connecting portion 5, the inner ring 8, the elastic arm 9, the outer ring 7, the outer ring protruding portion 10, and the outer ring protruding portion side surface 12, and finally to the damper retainer 31. Is transmitted from the turbine shell 23c to the input shaft 30 of the transmission.

  In this transmission, the elastic arm of the spiral spring is greatly deformed, and a large angle change occurs between the outer ring 14 and the outer ring 7 to form a torsion spring, which absorbs engine torque fluctuations.

  First, considering a single spiral spring, a large torsional deformation occurs when the load on the elastic arm increases, and the torque between the inner ring and the outer ring balances as an action and reaction, and force acts on the inner and outer peripheral parts of the elastic arm. Since there is only one elastic arm and geometrically it is not an axial object, the radial forces are not balanced.

  Next, if the radial force is balanced by two spiral springs, in the case of series, it is possible to balance at a certain torque, but not at other torques.

  In the case of series connection, the relative angular displacement of the outer ring 14 and the outer ring 7 changes according to the torque, so the relative position of the outer peripheral portions of the two elastic arms changes according to the torque. Even if the relative position of the part can be set to the axial target position, it cannot be set to the axially symmetric position with other torque.

  For this reason, unless the center of gravity of the spiral spring is displaced before and after the torque load, the radial force is not balanced as a whole of the vibration absorbing device, and the inner ring and the outer ring of the spiral spring move in the radial direction to a position where the radial force is balanced. It will be. As a result, rotational vibration occurs due to imbalance between the rotation center L and the center of gravity of the spiral spring. In order to prevent this, in this embodiment, the spiral spring set 43 is centered as follows to suppress the occurrence of rotational vibration.

  In the spiral spring 1, the outer ring 7 is welded to the flange part 3a of the third centering member 3, and the inner ring 8 is fitted to the cylindrical part 3b of the third centering member 3 so as to be slidable in the rotational direction. The outer ring 7 and the inner ring 8 are constrained on the same axis so as to be relatively rotatable. Similarly, in the spiral spring 2, the outer ring 14 is welded to the flange portion 4a of the second centering member 4, and the inner ring 15 is fitted to the cylindrical portion 4b of the second centering member so as to be slidable in the rotational direction. Therefore, the outer ring 14 and the inner ring 15 are relatively rotatable and constrained on the same axis.

  That is, the outer ring 14 that is the input part of the spiral spring set 43 in which the spiral spring 1 and the spiral spring 2 are connected in series, the outer ring 7 that is the output part, and the inner ring 8 and the inner ring 15 that are the connection parts are coaxial. It will be restrained by.

  In this way, the inner ring and the outer ring of the spiral spring are prevented from relatively moving in the radial direction due to the unbalance of the radial force described above, and the movement of the center of gravity in the spiral spring is suppressed.

  Further, the third centering member 3 and the second centering member 4 are fitted so as to be slidable in the rotation direction on the outer peripheral surface of the cylindrical portion 28b of the damper support member 28 that rotates about the rotation center L. For this reason, the spiral spring set 43 rotates around the rotation center L.

  As described above, the input portion, the output portion, and the connecting portion of the spiral spring set 43 are centered so as to be coaxial with the rotation center L. Therefore, the rotation center L and the spiral spring set 43 are constrained coaxially, and the center of gravity is moved. Therefore, the occurrence of rotational vibration is suppressed.

The first embodiment described above has the following effects.
(1) In the spiral spring set 43, the input portion, the output portion, and the connecting portion are constrained on the same axis as the rotation center L by the first to third centering members 3, 4, and 28. The movement of the center of gravity of the spiral spring can be suppressed with respect to the radial force generated when the air enters, and the rotational vibration due to the unbalance between the center of rotation and the center of gravity can be suppressed (effect resulting from claim 1). .

  (2) Since the inner ends of the spiral springs 1 and 2 that are the connecting portions of the spiral spring set 43 are ring-shaped inner rings, the portions connected in series with each other are welded over the entire circumference as described above, for example. By doing so, the power transmission positions can be distributed and arranged with respect to the circumferential direction of the rotation center L. Therefore, it is possible to avoid stress concentration at the connecting portion of the inner end portion, and it is possible to improve the durability of the spiral springs 1 and 2.

  Further, the inner ends of the spiral springs 1 and 2 have an annular structure, and are fitted with the damper support member 28 so as to be slidable in the rotation direction, so that the centering can be performed so as to be coaxial with the rotation center L. (Effects resulting from claim 2).

  (3) Since the outer end portion of the spiral spring 2 that is the input portion of the spiral spring set 43 is an outer ring having an annular structure, the portion where the outer ring 14 that is the input portion and the lockup piston 32 are connected is, for example, described above. As described above, by forming the projections 17 at three equal intervals, the power transmission positions can be distributed and arranged in the circumferential direction of the rotation center L. Therefore, stress concentration at the connecting portion can be avoided, and the durability of the portion where the outer ring 14 serving as the input portion and the lockup piston 32 are connected can be improved (effect resulting from claim 3).

  (4) Since the outer end portion of the spiral spring 1 that is the output portion of the spiral spring set 43 is an outer ring having an annular structure, the portion where the outer ring 7 that is the output portion and the damper retainer 31 are connected is, for example, described above. Thus, by forming the projections 10 at three equal intervals, the power transmission positions can be distributed and arranged in the circumferential direction of the rotation center L. Therefore, stress concentration at the connecting portion can be avoided, and the durability of the portion where the outer ring 7 that is the output portion and the damper retainer 31 are connected can be improved (effect resulting from claim 4).

  (5) The damper support member 28 centers the inner rings 8 and 15, which are connecting portions of the spiral spring set 43, so as to be coaxial with the rotation center L, and the second centering member 4 is an input portion of the spiral spring set 43. A certain outer ring 14 and an inner ring 15 that is a connecting portion are concentrically constrained so as to be relatively rotatable, and the third centering member 3 includes an outer ring 7 that is an output portion of the spiral spring set 43, and an inner ring 8 that is a connecting portion. Are constrained on the same axis so as to be relatively rotatable. That is, the outer ring and the inner ring centered so as to be coaxial with the rotation center L are coaxial. That is, the input unit, the output unit, and the connecting unit are centered so as to be coaxial with the rotation center L.

  Therefore, the inner ring and the outer ring are concentrically constrained by the second centering member 4 and the third centering member 3, so that the inner ring and the outer ring are compared with the case where the inner ring and the outer ring are constrained coaxially with the rotation center L, respectively. And the accuracy of being coaxial is improved. In other words, the accuracy with which the input portion, the output portion, and the connecting portion are coaxial with the rotation center L is improved, and rotational vibration due to imbalance between the rotation center and the center of gravity can be further suppressed (effect resulting from claim 5).

  (6) The second centering member 4 is in contact with the spiral spring 2 from the side surface on the output shaft side of the engine, and the third centering member 3 is in contact with the spiral spring 1 from the side surface on the input shaft side of the transmission.

  Therefore, the elastic arms 9 and 16 of the spiral spring 1 and the spiral spring 2, the inner end portion 8 and the inner end portion 15, and the outer end portion 7 and the outer end portion 14 are respectively moved or deformed in the axial direction. This can be suppressed, and interference with peripheral members can be suppressed (effect resulting from claim 6).

  (7) The outer ring 7 of the spiral spring 1 that is the output part of the spiral spring set 43 is rotationally coupled to the damper retainer 31, and the outer ring 14 of the spiral spring 2 that is the input part of the spiral spring set 43 is the lock-up piston 32. For example, as described above, the damper support member 28 is rotationally coupled to the lock-up piston 32 by engaging the notch so as to be movable in the axial direction, and the damper support member 28 is an inner ring 8 that is a connecting portion of the spiral spring set 43. And the inner ring 15 is centered.

Therefore, when the lockup piston 32 is operated, the lockup piston 32 can move in the axial direction with respect to the outer ring 14, and therefore, the elastic force of the spiral springs 1 and 2 prevents the lockup piston 32 from moving in the axial direction. Can be suppressed.
Further, since the outer ring 14 of the spiral spring 2 that is the input part of the spiral spring set 43 is not centered on the lockup piston 32, the lockup piston 32 and the spiral spring are moved when the lockup piston 32 moves in the axial direction. Friction with the outer ring 14 of the spiral spring 2 that is the input portion of the set 43 can be reduced (effect caused by claim 7).

  Hereinafter, an embodiment for realizing a torque fluctuation absorber according to the present invention will be described based on a second embodiment corresponding to claim 1, claim 2, claim 3, and claim 4.

4, FIG. 5 and FIG. 6 show a torque fluctuation absorber which is an embodiment of the present invention.
That is, in the second embodiment, the configuration of the centering means is changed from the configurations of FIGS. 1, 2, and 3 of the first embodiment to the configurations of FIGS. 4, 5, and 6, respectively. Since the main configuration other than the centering means in the second embodiment is the same as that of the first embodiment, only different points will be described.

  The outer peripheral surface 11b of the outer ring 7 of the spiral spring 1 is fitted in an axially slidable manner with the inner peripheral surface of the damper retainer 31 (centering means), and the inner peripheral surface 11a of the inner ring 8 of the spiral spring 1 is a damper support member. 28 (centering means) is fitted to the outer peripheral surface of the cylindrical portion 28b so as to be slidable in the rotational direction. Similarly, the outer peripheral surface 18b of the outer ring 14 of the spiral spring 2 is slidably fitted in the axial direction with the inner peripheral surface of the lockup piston 32 (centering means), and the inner peripheral surface 18a of the inner ring 15 of the spiral spring 2 is The damper support member 28 is slidably fitted to the outer peripheral surface of the cylindrical portion 28b in the rotational direction.

  Next, the operation of the second embodiment will be described. In the second embodiment, the spiral spring set 43 is centered as follows to suppress the occurrence of rotational vibration.

  The turbine hub 27 is spline-coupled with the input shaft 30 and rotates about the rotation center L. Further, the turbine shell 23c is coupled to the turbine hub 27 by the coupling portion 28a of the damper support member 28 and the rivet 29 in the inner peripheral portion, and is coupled to the damper retainer 31 in the outer peripheral portion. That is, the turbine hub 27, the turbine shell 23c, the damper support member 28, and the damper retainer 31 rotate about the rotation center L. Here, the outer ring 7 of the spiral spring 1 is fitted to the damper retainer 31 so as to be slidable in the axial direction, and the inner ring 8 is fitted to the damper support member 28 so as to be slidable in the rotational direction. For this reason, the outer ring 7 and the inner ring 8 of the spiral spring 1 rotate around the rotation center L.

  On the other hand, the lock-up piston 32 is provided on the boss portion of the turbine hub 27 and rotates around the rotation center L.

  Here, the outer ring 14 of the spiral spring 2 is fitted to the lockup piston 32 so as to be slidable in the axial direction, and the inner ring 15 is fitted to the damper support member 28 so as to be slidable in the rotational direction. The outer ring 14 and the inner ring 15 rotate about the rotation center L.

  Accordingly, the input part, the output part, and the connecting part of the spiral spring set 43 are centered so as to be coaxial with the rotation center L, so that the rotation center L and the spiral spring set 43 are concentric and prevent the movement of the center of gravity. Therefore, the occurrence of rotational vibration is suppressed.

  The second embodiment described above has the following effects in addition to the effects (1) to (4) of the first embodiment.

(8) The inner ring 15 and the outer ring 14 of the spiral spring 2 are rotated by the damper support member 28 coupled to the turbine hub 27 and the lockup piston 32 that is slidably fitted in the axial direction with the turbine hub 27. The inner ring 8 and the outer ring 7 of the spiral spring 2 are centered so as to be coaxial with the center L, and the damper support member 28 and the damper retainer 31 coupled to the turbine shell 23c are centered so as to be coaxial with the rotation center L. Is done.
Therefore, the input portion, the output portion, and the connecting portion can be centered so as to be coaxial with the rotation center L without adding parts such as the second centering member and the third centering member in the first embodiment. it can.

  Embodiments corresponding to claims 1, 2, 3, 4, 5, 6, and 7 will be described below as embodiments for realizing the torque fluctuation absorber according to the present invention. Based on

  7, 8, and 9 show a torque fluctuation absorber according to an embodiment of the present invention. That is, in the third embodiment, the configuration of the centering means is changed from the configurations of FIGS. 1, 2, and 3 of the first embodiment to the configurations of FIGS. 7, 8, and 9, respectively. Since the main configuration other than the centering means in the third embodiment is the same as that of the first embodiment, only different points will be described.

  The inner ring 8 of the spiral spring 1 is welded to the inner ring 15 of the spiral spring 2 and the connection portion 5 over the entire circumference to constitute a spiral spring set 43. The inner peripheral surface 11 a of the inner ring 8 of the spiral spring 1 is fitted to the outer peripheral surface of the cylindrical portion 3 b formed on the inner peripheral portion of the third centering member 3 so as to be slidable in the rotational direction. Further, the side surface of the outer ring 7 of the spiral spring 1 on the turbine shell 23 c side is welded over the entire periphery by the flange portion 3 a and the connection portion 13 of the third centering member 3. The outer peripheral surface 11b of the outer ring of the spiral spring 1 is fitted to the inner peripheral surface of the damper retainer 31 (first centering member) so as to be slidable in the axial direction.

  Similarly, the inner peripheral surface 18a of the inner ring 15 of the spiral spring 2 is fitted to the outer peripheral surface of the cylindrical portion 4b formed on the inner peripheral portion of the second centering member 4 so as to be slidable in the rotational direction. Further, the side surface on the lockup piston side of the outer ring 14 of the spiral spring 2 is welded over the entire circumference by the flange portion 4 a of the second centering member 4 and the connection portion 13. The outer peripheral surface 18b of the outer ring of the spiral spring 2 is fitted so as to be slidable in the axial direction with a clearance s that does not contact the inner peripheral surface of the lockup piston 32.

  Next, the operation of the third embodiment will be described. In the third embodiment, the spiral spring set 43 is centered as follows to suppress the occurrence of rotational vibration.

  In the spiral spring 1, the outer ring 7 is welded to the flange part 3a of the third centering member 3, and the inner ring 8 is fitted to the cylindrical part 3b of the third centering member 3 so as to be slidable in the rotational direction. The outer ring 7 and the inner ring 8 are constrained on the same axis so as to be relatively rotatable. Similarly, in the spiral spring 2, the outer ring 14 is welded to the flange portion 4a of the second centering member 4, and the inner ring 15 is fitted to the cylindrical portion 4b of the second centering member so as to be slidable in the rotational direction. Therefore, the outer ring 14 and the inner ring 15 are relatively rotatable and constrained on the same axis.

  That is, the outer ring 14 that is the input part of the spiral spring set 43 in which the spiral spring 1 and the spiral spring 2 are connected in series, the outer ring 7 that is the output part, and the inner ring 8 and the inner ring 15 that are the connection parts are coaxial. It will be restrained as in.

  In this way, the inner ring and the outer ring of the spiral spring are prevented from relatively moving in the radial direction due to the unbalance of the radial force described above, and the movement of the center of gravity in the spiral spring is suppressed. Further, the outer ring 7 is fitted to a damper retainer 31 that rotates about the rotation center L so as to be slidable in the axial direction, and movement in the radial direction is restricted.

  Therefore, as described above, the outer ring 14, outer ring 7, inner ring 8, and inner ring 15 of the spiral spring set 43 are constrained to be coaxial, so that the outer ring and inner ring of the spiral spring set 43 are centered on the rotation center L. It will rotate.

  As described above, the input portion, the output portion, and the connecting portion of the spiral spring set 43 are centered so as to be coaxial with the rotation center L. Therefore, the rotation center L and the spiral spring set 43 are constrained coaxially, and the center of gravity is moved. Therefore, the occurrence of rotational vibration is suppressed.

The third embodiment described above has the following effects in addition to the effects (1) to (7) of the first embodiment.
(9) The damper retainer 31 performs centering so that the outer ring 7 that is the output portion of the spiral spring set 43 is coaxial with the rotation center L, and the second centering member 4 is the outer ring that is the input portion of the spiral spring set 43. 14 and the inner ring 15 that is the connecting portion are concentrically constrained so as to be relatively rotatable, and the third centering member 3 causes the outer ring 7 that is the output portion of the spiral spring set 43 and the inner ring 8 that is the connecting portion to move relative to each other. Restrained on the same axis to be rotatable.

  Since the inner ring 8 and the inner ring 15 are connected to each other, and the inner ring 8 and the inner ring 15 are coaxial, the second centering member 4 and the third ring 3 are arranged with respect to the outer ring 7 centered so as to be coaxial with the rotation center L. The inner ring 8, the inner ring 15 and the outer ring 14 are centered by the centering member 3.

  That is, the input unit, the output unit, and the connecting unit are centered so as to be coaxial with the rotation center L. Therefore, the inner ring and the outer ring are concentrically constrained by the second centering member 4 and the third centering member 3, so that the inner ring and the outer ring are compared with the case where the inner ring and the outer ring are constrained coaxially with the rotation center L, respectively. And the accuracy of being coaxial is improved.

  That is, the accuracy of the input portion, the output portion, and the connecting portion being coaxial with the rotation center L is improved without adding the parts such as the damper support member 28 in the first embodiment. Rotational vibration due to unbalance can be further suppressed.

  The outer extension of the present invention is not limited to each of the above embodiments. It goes without saying that various modifications and developments are included within the scope of the idea.

For example, in each of the above-described embodiments, the damper device is used for the lock-up clutch of the torque converter, but is not limited to this, and may be used for the flywheel of the engine. In each of the above-described embodiments, the damper support member 28 is coupled to the turbine shell 23c. However, the present invention is not limited to this and may be coupled to the lock-up clutch.
In each of the above embodiments, the outer end of the spiral spring is the input part and the output part, and the inner end is the connection part, but it is not necessary to be limited to this, and the outer end is the connection part. The inner end may be an input part and an output part. Further, three or more spiral springs may be arranged in series, and a plurality of connecting parts may be provided. In addition, the centering, that is, the accuracy of being coaxial may be within a range in which, for example, rotational vibration can be allowed.

1 is an axial cross-sectional view illustrating an example of a torque fluctuation absorber in Embodiment 1. FIG. It is radial direction sectional drawing which looked at the spiral spring 1 in Example 1 from the engine side. It is radial direction sectional drawing which looked at the spiral spring 2 in Example 1 from the engine side. It is an axial sectional view showing an example of a torque fluctuation absorber in Example 2. It is radial direction sectional drawing which looked at the spiral spring 1 in Example 2 from the engine side. It is radial direction sectional drawing which looked at the spiral spring 2 in Example 2 from the engine side. It is an axial sectional view showing an example of a torque fluctuation absorber in Embodiment 3. It is radial direction sectional drawing which looked at the spiral spring 1 in Example 3 from the engine side. It is radial direction sectional drawing which looked at the spiral spring 2 in Example 3 from the engine side.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Spiral spring 2 Spiral spring 3 3rd centering member (3rd centering member)
3a Flange portion of the third centering member 3 3b Cylindrical portion of the third centering member 3 4 Second centering member (second centering member)
4a Flange portion of the second centering member 4 4b Cylindrical portion of the second centering member 4 5 Connection portion 6 Connection portion 7 Outer ring (output portion)
8 Inner ring (connecting part)
DESCRIPTION OF SYMBOLS 9 Elastic arm 10 Protrusion part 11a Inner peripheral surface of inner ring 8 11b Outer ring surface of outer ring 7 12 Protrusion side surface 13 Connection part 14 Outer ring (input part)
15 Inner ring (connecting part)
16 Elastic arm 17 Protruding portion 18a Inner peripheral surface 18b of inner ring 15 Outer peripheral surface of outer ring 14 19 Protruding portion side surface 21 Bolt 22 Torque converter cover 23a Impeller cover 23b Carrier 23c Turbine shell 24 Impeller 25 Stator 26 Turbine 27 Turbine hub 28 Damper support member (First centering member / Example 1, Centering means / Example 2)
28a Joint part of damper support member 28 28b Cylindrical part of damper support member 28 29 Rivet 30 Input shaft 31 Damper pallet (second rotating member, centering means / example 2, first centering member / example 3)
32 Lock-up piston (first rotating member, centering means / Example 2)
33 Lock-up clutch facing 34 Rotating body 35 Converter chamber 40 Torque converter 41 Damper device 42 Lock-up clutch 43 Spiral spring assembly

Claims (7)

A torque fluctuation absorber disposed between the output shaft of the drive source and the input shaft of the transmission,
A plurality of spiral springs composed of an inner end portion provided on the inner diameter side, an outer end portion provided on the outer diameter side, and an elastic arm connecting the inner end portion and the outer end portion;
The inner end portion or the outer end portion of the plurality of spiral springs are connected to each other to form a connecting portion, and the plurality of spiral springs are arranged in series to form a spiral spring set.
One end portion of the spiral spring set is connected to a first rotating member on the output shaft side of the drive source as an input portion, and the other end portion is the first shaft on the input shaft side of the transmission. In the torque fluctuation absorbing device that is connected to the second rotating member that is coaxial with the rotating member, and is used as the output unit,
A torque fluctuation absorbing device comprising a centering means for restraining the input portion, the output portion, and the connecting portion so as to be coaxial with the rotation centers of the first and second rotating members. In the torque fluctuation absorber according to claim 1,
The torque fluctuation absorber according to claim 1, wherein the connecting portion of the spiral spring set is an inner ring or an outer ring having an annular structure. The torque fluctuation absorber according to claim 2,
The torque fluctuation absorber according to claim 1, wherein the input portion of the spiral spring set is an inner ring or an outer ring having an annular structure. The torque fluctuation absorber according to claim 3,
The torque fluctuation absorber according to claim 1, wherein the output portion of the spiral spring set is an inner ring or an outer ring having an annular structure. In the torque fluctuation absorber according to any one of claims 1 to 4,
The centering means includes
A first centering member that centers either the inner end or the outer end of the spiral spring with respect to the rotation center;
A second centering member that constrains the input portion and the connecting portion of the spiral spring set coaxially so as to be relatively rotatable, and performs centering;
A torque fluctuation absorbing device comprising a third centering member that performs centering by constraining the output portion and the connecting portion of the spiral spring set coaxially so as to be relatively rotatable. In the torque fluctuation absorber according to claim 5,
The second centering member is in contact with the spiral spring including the input portion of the spiral spring set from a side surface on the output shaft side of the drive source,
The third centering member is in contact with the spiral spring provided with the output portion of the spiral spring set from the side surface on the input shaft side of the transmission. In the torque fluctuation absorber according to any one of claims 5 and 6,
The transmission includes an impeller to which torque is transmitted from the drive source, a turbine for transmitting torque transmitted from the impeller via a fluid to the transmission, and movement of a lockup piston between the impeller and the turbine. A torque converter having a lock-up clutch that is in a directly connected state and capable of rotating integrally;
The input portion of the spiral spring set is rotationally coupled to the lockup piston so that the lockup piston is movable in the axial direction;
The output of the spiral spring set is rotationally coupled to the turbine;
The torque fluctuation absorber according to claim 1, wherein the first centering member centers the connecting portion or the output portion of the spiral spring set.

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