JP2009030770A - Damper mechanism of torque transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a damper mechanism, employing a low-rigidity elastic member, preventing inappropriate force from acting thereon even when the low-rigidity elastic member is in initial setting and under high-torque external force. <P>SOLUTION: The damper mechanism is equipped with a disk-like first rotational member which is arranged rotatably to a given rotating shaft and is equipped with: a first window; a disk-like second rotational member which is arranged rotatably to the rotating shaft in such a fashion as to overlap with the first rotational member in the axial direction of the rotating shaft and is equipped with a second window at a position opposable the first window; and an elastic member which is stored within a space formed by the first and second windows arranged in such a fashion as to overlap with each other and, when the first and second rotational members rotate relatively to each other, is subjected to a compressive force in a rotative direction to be elastically deformable. Thus, there is provided the damper mechanism of a torque transmission device, which is formed with a plurality of abutting portions, against which an end of the elastic member abuts, in a rotative directional end of each of the first and second windows. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a damper mechanism applied to a torque transmission device such as a torque converter lockup device or a clutch device for a manual transmission.

  Conventionally, there has been a torque converter lockup device that employs a damper mechanism to suppress vibration generated when an input / output shaft is connected and noise based on the vibration. Such a damper mechanism incorporates an elastic member that absorbs or attenuates vibration, such as a coil spring. However, when the setting condition (installation environment) of the coil spring is poor, there is a case where an inappropriate force acts on the coil spring when the lockup device is operated, thereby reducing its life. With this, the expected damper effect cannot be obtained with certainty.

  Therefore, for example, Patent Document 1 proposes a preferable damper mechanism of the lockup device. The damper mechanism includes a first rotating member, a second rotating member, and a plurality of coil springs. Here, the first rotating member and the second rotating member are substantially disk-shaped, and are arranged so as to face each other and be relatively rotatable. The first rotating member has a plurality of first window portions arranged in the rotation direction. The second rotating member also has a plurality of second window portions provided so as to overlap the first window portion. A coil spring is accommodated in this overlapping portion, and is arranged so as to be compressed when the first rotating member and the second rotating member rotate relative to each other. Here, the outer peripheral side edges of the first window part and the second window part have a longer shape than the inner peripheral side edge, and are configured to be bent outward when the coil spring receives a compressive force. The end of the coil spring is generally formed at a substantially right angle with respect to the expansion / contraction direction (free length direction).

In the damper mechanism, the contact surface with which the end portion of the coil spring contacts the end portion in the rotation direction of the first window portion and the second window portion (hereinafter referred to as “rotation direction end portion”) is a predetermined condition. It is formed with. More specifically, the contact surface is set to be inclined by a predetermined angle with respect to a center line passing through the center portion and the rotation center in the rotation direction of the first window portion and the second window portion. Thus, the coil spring is designed to suppress the force that is pushed outward in the radial direction when bent by receiving a compressive force, and to suppress an increase in the compression amount of the outer peripheral portion of the coil spring. Therefore, it is said that the damper mechanism of Patent Document 1 can extend the life of the coil spring.
Japanese Patent Laying-Open No. 2005-54845

  By the way, in recent years, there has been an increasing demand for improvement in fuel consumption of engines mounted on vehicles. In order to meet this demand, it is known that it is effective to make the lock-up device function when the torque converter is rotating at a low speed (for example, about 1000 rpm) (hereinafter referred to as low-speed rotation). . However, if an attempt is made to reduce the rotation in this way, the noise described above becomes more noticeable when the lockup device is operated. In order to cope with this problem, low rigidity of the coil spring is required. Furthermore, the engine torque tends to increase year by year, so that the demand for damper performance is more severe.

  As described above, in the damper mechanism in the lockup device, it is necessary to reduce the rigidity of the elastic member such as a coil spring to be used and to ensure the damper performance at the time of high torque.

  By the way, the outer shape of the coil spring changes when the lockup device is in the initial set state (standby state) and when the lockup device is activated and the damper mechanism functions. That is, the coil spring in a free state that does not receive an external force has a linear shape, but when the lockup device is activated and a compression force is applied to the coil spring, the coil spring is curved outward in the window. As a result, the end of the coil spring is inclined. In consideration of this point, the damper mechanism of the lockup device disclosed in Patent Document 1 described above has a predetermined inclination of the contact surface at the end in the rotational direction so that an inappropriate force does not act on the coil spring. It was set to an angle. However, the contact surface is formed as a flat single surface. Therefore, in the initial setting state where no external force acts, the inner peripheral edge side of the contact surface comes into contact with the coil spring. Since the contact surfaces inclined at the left and right ends have a “reverse C shape”, a force is generated to push the coil spring toward the outer peripheral side, and the coil spring comes into contact with the inside of the window portion. Therefore, the wear of the contact portion is increased, and the life of the coil spring is shortened.

  It is also conceivable to set the coil spring to be shorter than the inner width of the window. However, in this case, the coil springs play around the window and become loose. Therefore, it is not realistic to adopt such a structure. Further, the damper mechanism of the clutch device for the manual transmission has the same problem as described here.

  Therefore, the present invention is not effective when a low-rigid elastic member is used, either when the elastic member is in the initial set state or when a high torque (torsion) external force is applied. It is an object of the present invention to propose a damper mechanism for a torque transmission device that can suppress the application of an appropriate force.

  To achieve the above object, a damper mechanism of a torque transmission device according to the present invention is disposed so as to be rotatable with respect to a predetermined rotation axis, and includes a disk-shaped first rotating member having a first window portion, and the first A disc-shaped first member that is disposed so as to overlap with the one rotation member in the direction of the rotation axis so as to be rotatable with respect to the rotation axis and includes a second window portion at a position that can face the first window portion. When the first rotating member and the second rotating member rotate relative to each other, the second rotating member is housed in a space formed by the first window portion and the second window portion arranged to overlap each other. And an elastic member that can be elastically deformed by receiving a compressive force in the rotational direction, and the end portions of the elastic member abut on the respective rotational direction end portions of the first window portion and the second window portion. It is characterized by having a configuration in which a plurality of contact surfaces are formed.

  According to the damper mechanism of the torque transmission device of the present invention, the first rotating member and the second rotating member are relatively rotated, the compressive force acting on the elastic member is changed, and the direction of the end of the elastic member is changed. Even if it changes, since a plurality of contact surfaces are formed, it is possible to suppress the occurrence of a situation in which the end portion slides or hits one side. Thereby, it is possible to suppress an inappropriate force from acting when the elastic member is in the initial set state or when the external force is applied. Therefore, this damper mechanism can suppress the generation of wear and noise by making the balance of stress acting on the elastic member uniform.

  Hereinafter, an example suitable as one embodiment of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a partially enlarged view of a main configuration of a torque converter of a vehicle drive system to which a lockup device as a torque transmission device including a damper mechanism according to a first embodiment is applied. Since the torque converter has a substantially point-symmetrical structure around the input / output shaft, FIG. 1 shows a configuration on one side of the input / output shaft (upper side in FIG. 1).

  First, a basic configuration provided in the torque converter TC will be described. The torque converter TC includes a pump impeller 5 fixed to a shell 8 coupled to the converter cover 7. In addition, a turbine runner 4 is provided which is coupled to the transmission input shaft 9 via the turbine hub 12 while being restricted in relative rotation. A stator 6 positioned between the turbine runner 4 and the pump impeller 5 and a stator shaft 10 that supports the stator 6 via a one-way clutch 11 are provided. Such a configuration is the same basic structure as a conventional torque converter.

  The torque converter TC incorporates a lockup device 20 for improving output efficiency. The lockup device 20 includes a lockup piston 1 that is supported by the transmission input shaft 9 via the turbine hub 12 so as to be relatively rotatable. The lock-up piston 1 is a substantially disk-shaped member, and a lock-up facing 2 is fixed to the outer peripheral surface. The lock-up piston 1 has a structure that slides on the turbine hub 12 and is designed to be movable in the left direction (engine side) along the transmission input shaft 9. When the lockup facing 2 is pressed against the inner wall of the converter cover 7, the torque input shaft 3 (crankshaft coupled to an engine (not shown)) and the output shaft 9 (transmission input shaft) are connected via a damper mechanism 30 described later. Connected mechanically.

  A release pressure oil passage 21 is formed inside the transmission input shaft 9, and the release pressure oil passage 21 communicates with a release chamber 23 formed between the lockup piston 1 and the converter cover 7. An apply pressure oil passage 22 for supplying an apply pressure to an apply chamber 24 formed between the pump impeller 5 and the turbine runner 4 is formed on the outer periphery of the stator shaft 10. The release chamber 23 and the apply chamber 24 communicate with each other at the outer peripheral portion of the lockup piston 1 when the lockup is released.

  When the torque converter TC to which the lockup device 20 is applied supplies the apply pressure from the apply pressure oil passage 22 to the apply chamber 24, the lockup facing 2 of the lockup piston 1 approaches and contacts the converter cover 7. The lock-up fastening state is established. Further, when the release pressure is supplied from the release pressure oil passage 21 to the release chamber 23, the lockup facing 2 of the lockup piston 1 moves away from the converter cover 7, and the lockup state can be released. Therefore, the transmission efficiency of torque can be improved by appropriately connecting the input / output shaft.

However, when the lockup device 20 is activated and the input / output shaft is connected, vibration may occur as described above. Therefore, a damper mechanism 30 is incorporated on the back side of the lockup piston 1 of the lockup device 20. The damper mechanism 30 includes a first rotating member 31 coupled to the lockup piston 1 and a second rotating member 32 coupled to the transmission input shaft 9 (rotating shaft) via the turbine hub 12 and the spline structure. I have.
The first rotating member 31 and the second rotating member 32 are both disk-shaped members and are arranged so as to overlap in the rotation axis direction AD. Here, the 1st rotation member 31 consists of two members, and the 1st rotation member 31 and the 2nd rotation member 32 are arrange | positioned so that the 2nd rotation member 32 may be pinched | interposed between these.

  A first window 33 is provided in each of the first rotating members 31 disposed on both sides, and a second window 34 is disposed in the circumferential direction of the second rotating member 32 disposed between the first rotating members 31. Are formed at predetermined positions. And these window parts 33 and 34 are arrange | positioned so that it may mutually overlap, and space SP is formed in the part. A coil spring (torsion spring) 35 is housed in the space SP as an elastic member that suppresses vibration generated when the lockup device is operated. A plurality of the first window part 33 and the second window part 34 are provided in the circumferential direction, and a coil spring 35 is similarly provided in each of them.

  FIG. 2 is a perspective view showing a part relating to the damper mechanism 30 extracted from the structure shown in FIG. 1 so that the configuration of the damper mechanism 30 described above can be easily confirmed. In FIG. 2, one member of the first rotating member 31 is illustrated on the front side, and the second rotating member 32 and the other of the first rotating member 31 are positioned so as to overlap each other on the back side. Four window portions 33 (window portions 34) are formed in the circumferential direction in the first rotating member 31 (and the second rotating member 32). Here, since the first rotating member 31 and the second rotating member 32 are disposed so as to be relatively rotatable, the second rotating member 32 is fixed when the lockup device 20 is operated, and the first rotating member 31 is fixed. When the coil spring 35 is rotated in the rotation direction MD of the arrow, it receives a compressive force corresponding to the amount of change (twisting angle) when the coil spring 35 is relatively rotated.

  When the coil spring 35 is in a state of being contracted by receiving a compressive force from the contact surface formed at the rotation direction end of the window portions 33 and 34 from the initial setting state where no pressure is received, the angle at which the end of the coil spring 35 is inclined Change. In particular, when a low-rigidity coil spring is used to reduce rotation as described above and a damper performance corresponding to a high torque (high torsion) is to be obtained, the coil spring 35 has a relatively low rigidity and a free length. Longer ones are used. This further increases the angle at which the end of the coil spring 35 is inclined. Therefore, if the contact surfaces provided at the rotation direction end portions of the first window portion 33 and the second window portion 34 are flat, as described above, the non-uniform force is applied to the coil spring, causing problems such as wear. Will occur. The damper mechanism of the present embodiment has a structure that can cope with this. This point will be further described with reference to FIG.

  FIG. 3 is an enlarged schematic view of the configuration of the circle CR portion in FIG. 2, wherein (a) is an initial set state of the coil spring 35 to which no compressive force is applied, and (b) is a coil spring. A curved state is shown in FIG. This FIG. 3 is shown so that the inclination state of the contact surface formed in the rotation direction end part of the 1st window part 33 of the 1st rotation member 31 can be confirmed. The contact surface is a surface with which the end portion 35ED of the coil spring 35 contacts, and a plurality of contact surfaces (two in this case) are formed at the end portion of the first window portion 33. As shown in FIG. 3 (a), even in the case of this coil spring 35, in a free state where it does not receive external force, its end 35ED is substantially perpendicular to the expansion / contraction direction PD as in the case of a conventional general coil spring. Is formed.

  In the initial set state in which the lockup device shown in FIG. 3A is not operating, no substantial compressive force is applied to the coil spring 35. However, it is necessary to support the coil spring 35 with a certain amount of restraining force in order to avoid a state of being played in the first window 33 (a state of rattling). From such a viewpoint, the first contact surface 41 is set. Since the inclination angle θ1 of the first contact surface 41 supports the coil spring 35 in the initial set, the inclination angle is set to zero (0) or a small angle close thereto. The inclination angle here is set under the same conditions as described in the prior art, and is a reference parallel to the center line of the first rotating member 31 and the second rotating member 32 and the center line passing through the rotation center. An angle formed with respect to the line SL.

  On the other hand, when the lockup device operates and the first rotating member and the second rotating member rotate relative to each other and twist occurs, a compression force acts on the coil spring 35 according to the twist angle. At this time, as shown in FIG. 3B, the coil spring 35 is curved outward. At this time, since the end 35ED of the coil spring 35 receives a force that rotates counterclockwise (counterclockwise), the angle changes. The second contact surface 42 is a surface prepared so as to contact the end ED that has been rotated by receiving the compression force in this way, and is set with an inclination angle θ2 that is larger than the inclination angle θ1. ing. That is, the first contact surface 41 is a surface formed on the inner peripheral side so that the end portion 35ED of the coil spring 35 before receiving the compression force contacts in parallel. On the other hand, the second contact surface 42 is a surface formed on the outer peripheral side so that the end portion 35ED of the coil spring 35 that has received the compressive force contacts in parallel.

  The specific angle of the inclination angle θ <b> 2 of the second contact surface 42 can be set based on the maximum twist angle of the lockup device 20. For example, when the maximum twist angle is 30 degrees, the inclination angle θ2 is about 15 degrees, which is half of 30 degrees. FIG. 3 shows the left end of the first window 33 of the first rotating member 31. In the case of the second window portion 34 provided in the second rotating member 32 located on the back surface of the first rotating member 31, the first contact surface and the first contact surface described above at the right rotational end on the opposite side to FIG. 2 contact surfaces are formed. By similarly setting the inclination angle of the inclination angle θ2 of the first contact surface to about 15 degrees, it is possible to correspond to the maximum twist angle of 30 degrees. Furthermore, it is more preferable to set the oblique angle θ1 of the first contact surface 41 to half (about 7.5 degrees) of the inclination angle of the second contact surface θ2. The inventor of the present application has confirmed that the stress acting on the coil spring 35 employing such a configuration can be reduced by about 10%.

  In the damper mechanism 30 of the lockup device 20 described above, the first rotating member and the second rotating member rotate relative to each other, and the compression force acts on the coil spring 35 to change the angle of the end portion 35ED. In addition, since a plurality of contact surfaces are formed at the rotation direction end portion, the end portion ED can contact the contact surface suitable at that time. As a result, since it is possible to suppress an inappropriate force from acting on the coil spring, it is possible to reliably suppress the occurrence of a situation in which the coil spring slides or hits one side. Therefore, the life of the coil spring can be extended, and noise when the lockup device 20 is operated can be suppressed.

  Further, a damper mechanism of the lockup device according to the second embodiment will be described with reference to FIG. The basic structure of the damper mechanism of the second embodiment is the same as that of the above-described damper mechanism of the first embodiment, and the contact surface formed at the rotational direction end of the window portion is different. In order to avoid overlapping description, the second embodiment will be described with a focus on differences from the first embodiment. In FIG. 4, the same parts as those in FIG.

  FIG. 4 is a diagram schematically illustrating the contact surface formed at the rotation direction end of the first window 33 of the first rotation member 31 so that the contact surface can be confirmed. FIG. 4 shows the same as FIG. That is, (a) shows the initial setting state of the coil spring 35 to which no compressive force is applied, and (b) shows the curved state in which the compressive force is applied to the coil spring 35.

  In the second embodiment, the first abutting surface 43 and the second abutting surface 44 are inclined in the same direction, and are arranged in a step shape via the connecting portion 45. In the case of the second embodiment, the first contact surface 43 and the second contact surface 44 have different circumferential positions in the rotational direction MD. Since the interval between the second contact surfaces 44 on the outer peripheral side is narrow, the end portion of the coil spring 35 can be reliably contacted when the aforementioned compressive force is applied. The inclination angle of the second contact surface 44 may be set similarly to the case of the second contact surface 42 of the first embodiment described above.

  In the case of the second embodiment, in the initial setting state where the lock-up device 20 is not operating, the end 35ED of the coil spring 35 is located below the first contact surface 43 and the first contact surface 43. And the second contact surface 44 are in contact with a plurality of portions of the stepped portion, and are supported with a certain restraining force in the first window portion 33 in accordance with the case of contacting in parallel with the contact surface. When the lock-up device is activated and the first rotating member and the second rotating member rotate relative to each other and twist occurs, and the compression force is applied to the coil spring 35, the end 35ED of the coil spring 35 is moved to the left. Since it rotates around, the end 35ED of the coil spring 35 abuts in parallel with the second abutment surface 44 and is stably supported.

  Also in the case of the damper mechanism 30 according to the second embodiment described above, the compression force acting on the coil spring 35 changes due to the relative rotation of the first rotating member and the second rotating member, and the inclination of the end portion 35ED is changed. Even if it changes, it can contact | abut on the contact surface suitable at that time. As can be understood from the second embodiment, the end portion 35ED of the coil spring 35 only needs to be stably supported by a plurality of abutting surfaces. Also good. In the case of this embodiment as well, it is possible to suppress an inappropriate force from acting on the coil spring, so that it is possible to prevent wear and extend the life.

Although the preferred embodiments of the present invention have been described in detail above, the present invention is not limited to the specific embodiments, and various modifications and changes can be made within the scope of the gist of the present invention described in the claims. It can be changed. For example, in the above-described embodiments, a damper mechanism having a so-called short travel structure in which one coil spring is installed in the window portion is exemplified. The present invention can be similarly applied even to a damper mechanism having a long travel structure to be installed.
Moreover, although the torque converter lockup device has been described as an example of the torque transmission device, the present invention is not limited thereto, and the present invention may be similarly applied to a normal clutch device.

  According to the damper mechanism of the torque transmission device of the present invention, the first rotating member and the second rotating member rotate relative to each other, the compressive force acting on the elastic member changes, and the direction of the end of the elastic member changes. However, since a plurality of contact surfaces are formed, it is possible to suppress the occurrence of a situation in which the end portion slides or hits one side. The plurality of contact surfaces may include a first contact surface and a second contact surface set with different inclination angles. Further, the first contact surface is formed on an inner peripheral side so that an end portion of the elastic member before receiving the compression force contacts, and the second contact surface receives the compression force. Alternatively, the elastic member may have a structure formed on the outer peripheral side so that the end of the elastic member comes into contact therewith. The inclination angle of the first contact surface and the inclination angle of the second contact surface can be set based on the maximum torsion angle of the torque transmission device. Further, the plurality of contact surfaces include a first contact surface and a second contact surface that are set by changing the positions in the circumferential direction of the first rotating member and the second rotating member forward and backward, The first contact surface and the second contact surface may be a damper mechanism of a torque transmission device arranged in a step shape.

It is the figure which expanded and showed partially the main structure of the torque converter to which the lockup apparatus provided with the damper mechanism which concerns on Example 1 is applied. It is the perspective view which took out and showed the part which concerns on the damper mechanism shown in FIG. It is the figure which expanded and showed the CR part in FIG. 2 typically, (a) is the initial setting state of the coil spring to which the compression force does not act, (b) is a curve by the compression force acting on the coil spring. FIG. It is the figure shown about the damper mechanism of the lockup apparatus which concerns on Example 2, (a) is the initial setting state of the coil spring in which the compression force is not acting, (b) is a curve by the compression force acting on the coil spring. FIG.

Explanation of symbols

20 Lock-up device (torque transmission device)
30 damper mechanism 31 first rotating member 32 second rotating member 33 first window portion 34 second window portion 35 coil spring (elastic member)
TC Torque converter SP space

Claims (5)

A damper mechanism applied to a torque transmission device,
A disc-shaped first rotating member that is rotatably arranged with respect to a predetermined rotation axis and includes a first window;
A disk-like shape that is arranged so as to overlap with the first rotation member in the direction of the rotation axis so as to be rotatable with respect to the rotation axis and has a second window portion at a position that can face the first window portion. A second rotating member of
When the first rotating member and the second rotating member rotate relative to each other, they are accommodated in a space formed by the first window portion and the second window portion arranged so as to overlap each other. An elastic member that is elastically deformable under a compressive force,
A damper mechanism for a torque transmission device, wherein a plurality of contact surfaces with which the end portions of the elastic members abut are formed at the respective rotation direction end portions of the first window portion and the second window portion. . The damper mechanism of the torque transmission device according to claim 1,
The damper mechanism for a lockup device, wherein the plurality of contact surfaces include a first contact surface and a second contact surface set with different inclination angles. In the damper mechanism of the torque transmission device according to claim 2,
The first contact surface is formed on the inner peripheral side so that an end of the elastic member before receiving the compressive force contacts,
The damper mechanism of the torque transmission device, wherein the second contact surface is formed on an outer peripheral side so that an end of the elastic member that has received the compressive force contacts. In the damper mechanism of the torque transmission device according to claim 3,
The damper mechanism for a torque transmission device, wherein the inclination angle of the first contact surface and the inclination angle of the second contact surface are set based on a maximum torsion angle of the torque transmission device. The damper mechanism of the torque transmission device according to claim 1,
The plurality of abutting surfaces include a first abutting surface and a second abutting surface that are set by differentiating front and rear positions of the first rotating member and the second rotating member in the circumferential direction. The damper mechanism of the torque transmission device, wherein the first contact surface and the second contact surface are arranged in a step shape.

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