JP6796583B2 - Damper device - Google Patents

Description

The present invention relates to a damper device for a torque transmission device such as a lockup clutch used in a vehicle or the like.

An automatic vehicle (hereinafter referred to as "AT vehicle") that transmits engine output to an automatic transmission via a fluid transmission device such as a torque converter or a fluid coupling is widely known.

Some of such fluid transmission devices are provided with a lockup clutch in parallel so that the engine and the automatic transmission can be directly connected to each other. This lock-up clutch is provided for the purpose of improving fuel efficiency, and is generally equipped with a damper device to absorb torque vibration accompanying engine rotation.

Such a damper device is assembled to, for example, the torque transmission device of Patent Document 1, and has a structure having a drive side rotating member, a driven side rotating member, a coil spring guide, and a coil spring.

The drive-side rotating member and the driven-side rotating member are assembled so as to have the same axial center, and the driving-side rotating member is configured to receive the engine output. The coil spring guide is formed in an arc having the center of curvature as the center of curvature, and is arranged on either the driving side rotating member or the driven side rotating member. The coil spring is housed on the inner peripheral side of the coil spring guide in an arc-shaped curved state, and both ends are separately engaged with the driving side rotating member and the driven side rotating member.

Therefore, the coil spring expands and contracts with the relative rotation of the driving side rotating member and the driven side rotating member, and the torque vibration accompanying the engine rotation can be damped.

Here, from the viewpoint of vehicle fuel efficiency, it is desirable to engage the lockup clutch from the low speed range of the engine. For this purpose, it is required to lower the resonance frequency of the coil spring. In order to lower the resonance frequency, it is necessary to lower the spring constant of the coil spring, so it is better to use a coil spring that is as long as possible.

However, a long coil spring tends to bend so that the intermediate portion of the coil strengthens the curvature, and there is a problem that a hysteresis torque is generated in the transmission torque due to a large frictional force when the coil spring expands and contracts with respect to the coil spring guide.

The hysteresis of this transmission torque is as shown in FIG. 13 when illustrated. FIG. 13 is a graph showing the relationship between the twist angle and the transmitted torque at the time of torque transmission between the driving side rotating member and the driven side rotating member. The horizontal axis of FIG. 13 shows the twist angle, and the vertical axis shows the transmission torque.

As shown in FIG. 13, the torque of the outward path on the compression side of the coil spring between the drive side rotating member and the driven side rotating member is shown by a solid line, and the torque of the return path on the extension side is shown by a broken line.

The difference between the solid line and the broken line is hysteresis, and when the coil spring is twisted from the twist angles D1 to D2 in FIG. 13, the static spring constant becomes the slope A of the median value of the outward path and the return path due to this hysteresis, and the dynamic spring constant. Is the slope B between the maximum and minimum values of the outward route and the return route. When the inclination B becomes the actual spring constant and the amplitude from D1 to D2 is low, the spring constant becomes relatively high and the vibration is difficult to be damped.

The occurrence of such hysteresis is simply caused by assembling a coil spring having a linear coil center to a coil spring guide having a curved coil center. The spring restoring force due to such assembly is shown in FIG.

FIG. 14 is an explanatory view showing the spring restoring force, and shows a state in which the coil spring 101 whose coil center line was linear before assembly was assembled to the curved coil spring guide 103.

As shown in FIG. 14, after assembly, a spring restoring force P1 is generated, the central portion of the coil spring 101 abuts on the guide surface on the inner diameter side of the coil spring guide 103 in the radial direction of curvature, and both ends thereof are coil springs. It abuts on the guide surface on the outer diameter side of the guide 103 in the radius of curvature direction.

The coil spring 101 is pressed against the coil spring guide 103 by such a spring restoring force P1, and a hysteresis torque is generated by the frictional force. Further, during high-speed rotation, in addition to this, a centrifugal force is applied to the spring, so that the spring is pressed against the guide surface, the frictional force is increased, and a larger hysteresis torque is generated.

On the other hand, in order to prevent the generation of hysteresis torque due to the assembly of the coil spring 101, the radius of curvature on the outer peripheral side of the coil spring 101 in the free state substantially matches the radius of curvature of the coil spring guide 103. ), And the coil spring 101 can be accommodated in the coil spring guide 103 without applying an external force, as Patent Document 1.

However, even in such a damper device, the coil spring 101 is bent by an external force input to the end of the coil spring 101 for damping during rotation, and the friction between the coil spring 101 and the coil spring guide 103 can be sufficiently reduced. However, hysteresis torque was also generated, and the substantial spring constant could not always be sufficiently reduced.

FIG. 15 illustrates such a situation, and is an explanatory diagram showing a state of a resultant force when an external force is applied along the coil spring guide.

As shown in FIG. 15, when an external force P2 is applied along the coil spring guide 103, the coil spring 101 is compressed and a resultant force P3 facing outward in the radial direction is generated. If the coil spring 101 is not restrained, it is deformed so as to bulge outward in the radial direction due to the resultant force P3. However, since the coil spring 101 is housed in the coil spring guide 103, the coil spring 101 is pressed against the coil spring guide 103 by the resultant force P3, and a hysteresis torque is generated by the frictional force F = μP3.

On the other hand, there is a damper device disclosed in Patent Document 2. FIG. 16 is an explanatory view showing the damper device with a part cutout, and FIG. 17 is an explanatory view showing the curvature of the coil spring with respect to the coil spring guide.

As shown in FIG. 16, in this damper device, an arc-shaped (arc-shaped) coil spring 101 is arranged between the claw portion 105a of the driving side rotating member 105 and the claw portion 107a of the driven side rotating member 107, and the coil spring It is housed in the guide 103. The coil spring guide 103 is fitted inside the cylindrical portion 109, which is a drive-side rotating member.

Then, as shown in FIG. 17, in this conventional example, the arc curvature of the coil spring 101 is made larger than the curvature of the coil spring guide 103, and the contact area of the coil spring 101 with respect to the coil spring guide 103 is reduced.

It is disclosed in Patent Document 2 that the generation of hysteresis torque can be suppressed and the substantial spring constant can be reduced by reducing the contact area.

However, this damper device has a problem that local wear occurs due to a decrease in the contact area, which hinders stable torque transmission for a long period of time.

Moreover, the central portion of the curvature of the coil spring 101 is located on the outer diameter side of the set position of the seat surface 101a of the coil spring 101, which tends to cause an increase in centrifugal force, and is locally located at the central portion of the curvature of the coil spring 101. It promoted wear.

Japanese Unexamined Patent Publication No. 5-172184 Japanese Unexamined Patent Publication No. 8-105508

The problem to be solved is that the generation of hysteresis torque and the generation of local wear could not be suppressed at the same time.

In order to make it possible to simultaneously suppress the generation of hysteresis torque and the occurrence of local wear, the present invention includes a drive-side rotating member and a driven-side rotating member that can rotate relative to a common axial center, and the shaft. A coil spring guide that is curved with a center of curvature on the central side and is arranged on either the driving side rotating member or the driven side rotating member, and one end of the coil spring guide that is accommodated in an arc shape to drive the driving side. The coil spring is provided with a coil spring that engages with the side rotating member and the other end engages with the driven side rotating member, and the coil spring expands and contracts with relative rotation between the driving side rotating member and the driven side rotating member. A damper device for a torque transmission device that damps the input rotation from the drive-side rotating member and outputs it from the driven-side rotating member. The coil spring has an arc-shaped coil in a free state and has an arc-shaped curvature. The center is located on the opposite side of the coil spring with the axial center in between, and the drive-side rotating member includes a claw portion in which a contact edge portion oriented in the circumferential direction engages with the seat surface of the coil spring. The seat surface and the contact edge portion are characterized in that they are along a radial direction line passing through the center of curvature of the coil spring .

Since the present invention has the above configuration, it is easy to arrange the central portion side of the arc shape of the coil spring closer to the axial center side with respect to the end portion, suppress the generation of hysteresis torque, and lower the substantial spring constant. It is possible to suppress the occurrence of local wear and to perform stable torque transmission.

It is a front view of the damper device of a lockup clutch. (Example 1) It is a perspective view seen from the back side of the damper device of a lockup clutch. (Example 1) It is a side view of the damper device of a lockup clutch. (Example 1) It is a perspective view which shows the damper device with the disc on the back side seen from the back side. (Example 1) It is a front view which shows the relationship of the radius of curvature of a damper device. (Example 1) It is a front view which shows the contact angle between a coil spring of a damper device and a claw part. (Example 1) It is explanatory drawing which shows the decrease of the resultant force acting in the radial direction of a claw part and a coil spring guide. (Example 1) It is a graph which shows the relationship between the angle of a claw part with respect to a seat surface, and hysteresis torque. It is explanatory drawing which shows the contact of the claw part with respect to the outer diameter side of a seat surface. (Example 1) The attachment of the coil spring to the coil spring guide with a gap is shown, where (A) is an explanatory view before rotation and (B) is an explanatory diagram during rotation. (Comparison example) It is a graph of the relationship between R3 / R1 of FIG. 5 and the reduction rate of the hysteresis torque. (Example 1) It is a graph which concerns on the comparison of the relationship between a transmission torque and a hysteresis torque. (Example 1) It is a graph which shows the relationship between the twist angle and transmission torque at the time of torque transmission between a drive side rotating member and a driven side rotating member. It is explanatory drawing which shows the spring restoration force. (Conventional example) It is explanatory drawing which shows the state of the resultant force when the external force is applied along the coil spring guide. (Conventional example) It is explanatory drawing which shows the damper device with a part cutout. (Conventional example) It is explanatory drawing which shows the curvature of the coil spring with respect to the coil spring guide. (Conventional example)

For the purpose of making it possible to simultaneously suppress the generation of hysteresis torque and the occurrence of local wear, a coil spring having an arc-shaped coil center line in a free state is used, and the arc-shaped center of curvature forms the axis. It was realized by sandwiching it and locating it on the opposite side of the coil spring.

The coil center line of the coil spring may have an arc shape near the center, and may be a straight line near the seat surface.

The drive-side rotating member includes a claw portion in which a contact edge portion facing in the circumferential direction engages with the seat surface of the coil spring, and the seat surface and the contact edge portion pass through the center of curvature of the coil spring. It may be along the radial direction line.

The drive-side rotating member includes a claw portion in which a contact edge portion facing in the circumferential direction engages with the seat surface of the coil spring, and the contact edge portion is on the outer diameter side in the radial direction of curvature of the coil spring. It may come into contact with the seating surface at a position biased toward.

The coil spring guide may include a guide surface having a curvature that guides the outer diameter side of the coil spring in the radial direction of curvature as a whole.

[Damper device]
1 to 7 relate to the first embodiment of the present invention, FIG. 1 is a front view of the lockup clutch damper device, and FIG. 2 is a perspective view and a view of the lockup clutch damper device as viewed from the back surface side. 3 is a side view of the damper device of the lockup clutch, FIG. 4 is a perspective view showing the damper device from the back side with the disc on the back side removed, and FIG. 5 is a front view showing the relationship of the radius of curvature of the damper device. FIG. 6 is a front view showing the contact angle between the coil spring of the damper device and the claw portion, and FIG. 7 is an explanatory view showing a decrease in the radial component of the resultant force between the claw portion and the coil spring guide. The rotation direction means the rotation direction of the damper device, and the radial direction means the radial direction of the damper device.

As shown in FIGS. 1 to 4, the damper device 1 of the lockup clutch is rotationally elastic, and is during damping between the claw plate 3 as the driving side rotating member and the discs 5 and 7 as the driven side rotating member. Coil springs 9 for storing power are provided at three locations in a 120 ° arrangement. The number of coil springs 9 that can be set is arbitrary, and for example, the coil springs 9 may be arranged at 90 ° or the like so that they are provided at four locations or the like.

Therefore, the damper device 1 of the lockup clutch expands and contracts the coil spring 9 with the relative rotation of the claw plate 3 and the discs 5 and 7, and damps and outputs the torque fluctuation of the input rotation from the claw plate 3. .. The claw plate 3 may be used as a driven side rotating member, and the discs 5 and 7 may be used as a driving side rotating member. The lockup clutch is an example of a torque transmission device. The damper device of the present invention can also be applied to a torque transmission device other than the lockup clutch. For example, the damper device of the present invention can also be applied to a torque transmission device such as a clutch disc, a dual mass flywheel, and a belt for driving an auxiliary machine of an automobile used in a manual car or the like. That is, the drive-side rotating member may be a member that receives a drive input, and the driven-side rotating member may be a member that performs a drive output. The damper device absorbs torque vibration between the drive-side rotating member and the driven-side rotating member, and the driving-side rotating member and the driven-side rotating member are members corresponding to the target torque transmission device.

The claw plate 3 and the discs 5 and 7 are arranged so as to be relatively rotatable around a common axial center.

The claw plate 3 on the drive side has a structure in which a hole 3a is coupled to, for example, the crankshaft side of an engine to receive an input from the engine. Holes 5a and 7a of the driven discs 5 and 7 are coupled to the output side of the torque converter via a friction plate (not shown).

The claw plate 3 and the discs 5 and 7 are connected to each other by, for example, three rivets 11 in the circumferential direction. Due to this coupling, the claw plate 3 and the discs 5 and 7 can rotate relative to each other and cannot move relative to each other in the axial direction.

Therefore, when the engine speed rises to the set speed, the lockup clutch is locked up. Due to this lockup, the connection between the engine and the transmission changes from the torque transmission state by the torque converter to the direct connection state via the damper device 1. The impact of torque transmission between the engine and the transmission at the time of direct connection and the engine torque vibration after direct connection can be damped by the damper device 1.

The claw plate 3 is formed with arc-shaped regulating recesses 13 at three locations at 120 ° with respect to the rivet 11. The regulation recess 13 is formed to be concave in the radial direction and has a length in the circumferential direction, and has an arcuate length equal to both sides in the rotational direction with respect to the rivet 11 in a stationary state.

Due to the relative guide between the rivet 11 and the regulation recess 13, the claw plate 3 and the discs 5 and 7 are allowed to rotate relative to each other within the length range in the circumferential direction of the regulation recess 13.

It should be noted that various configurations of the claw plate 3 on the driving side and the discs 5 and 7 on the driven side can be considered, and the driving side and the driven side can each be formed by one plate.

The claw plate 3 is formed of a plate that is relatively thicker than the discs 5 and 7, and integrally has a claw portion 15 that protrudes in the radial direction between the circumferential directions of each regulation recess 13. The claw portions 15 are provided at three locations in the circumferential direction in a 120 ° arrangement. The claw portion 15 corresponds to the coil spring 9, and if the coil spring 9 is arranged at 90 ° or the like, the claw portion 15 is also arranged at 90 ° or the like. The outer peripheral edge 15a of the claw portion 15 is formed in an arc shape, and the outer peripheral edge 15a is formed along the outer peripheral edge of the discs 5 and 7. The outer peripheral edge 15a of the claw portion 15 can be arranged on the inner diameter side or the outer diameter side of the outer peripheral edges of the discs 5 and 7, and when arranged on the inner diameter side, the claw portion 15 is arranged on the outer peripheral portion of the discs 5 and 7. It is also possible to form a cylindrical portion that covers the outer peripheral edge 15a of the.

Each claw portion 15 is formed in a concave shape on both sides in the circumferential direction between the outer peripheral edge 15a and the regulation recess 13 in the radial direction, and the contact edge portions 15b and 15c are linearly formed. The contact edge portions 15b and 15c are set on the seat surface 9a of the coil spring 9 so as to face the circumferential direction. The set angles of the contact edge portions 15b and 15c will be described later.

Coil spring guides 18 and 19 are formed on the discs 5 and 7. The coil spring guides 18 and 19 are curved so as to have a center of curvature on the common axial side of the claw plate 3 and the discs 5 and 7, and either of the driving side rotating member and the driven side rotating member, in this embodiment. Is arranged on the discs 5 and 7 of the driven side rotating member. The coil spring guides 18 and 19 of this embodiment are formed in an arc shape with a constant curvature on the outer peripheral side of the rivet 11. The arcuate length of the coil spring guides 18 and 19 is formed to be substantially the same as the length on the coil center line between the seat surfaces 9a and 9b of the coil spring 9 in the free state.

The coil spring 9 is housed in the coil spring guides 18 and 19 in an arc shape, and one end of the coil spring 9 engages with the claw plate 3 and the other end engages with the discs 5 and 7. The coil spring guides 18 and 19 are composed of guide holes 20 and 21 and guide tongue portions 23a, 23b, 25a and 25b. The radial widths of the guide holes 20 and 21 are formed to be substantially constant over the circumferential direction. Locking edges 20a and 20b and locking edges 21a and 21b are linearly formed at both ends of the guide holes 20 and 21 in the circumferential direction.

The locking edge portions 20a and 20b and the locking edge portions 21a and 21b are formed so as to face the both seat surfaces 9a and 9b of the coil spring 9 and lock the both seat surfaces 9a and 9b in the circumferential direction. .. Therefore, the locking edge portions 21a and 21b are the circumferential ends of the guide holes 20 and 21 in the direction in which both seat surfaces 9a and 9b are orthogonal to the coil center line, or in the direction orthogonal to the inclined direction, and in the inclined direction. It is formed in the part.

The set angles of the locking edge portions 21a and 21b will be described later together with the contact edge portions 15b and 15c of the claw portion 15.

The guide tongue portions 23a and 23b and the guide tongue portions 25a and 25b have a center of curvature on the axial center side of the damper device 1 and are curved in the circumferential direction, and are either a drive side rotating member or a driven side rotating member. In the example, it is arranged on the disks 5 and 7 of the driven side rotating member.

The guide tongue portions 23a and 25a are formed along the outer peripheral side edges of the guide holes 20 and 21, and are integrally cut and raised from the discs 5 and 7. The guide tongue portions 23b and 25b are formed along the radial side edges of the guide holes 20 and 21, and are integrally cut and raised from the discs 5 and 7. The guide tongue portions 23b and 25b are cut and raised in the cross-sectional direction of the discs 5 and 7. The guide tongue portions 23b and 25b are curved in the cross-sectional direction of the discs 5 and 7. The curvature of the curves of the guide tongue portions 23b and 25b in the cross-sectional direction substantially coincides with the coil diameter of the coil spring 9. However, the guide tongue portions 23b and 25b can be formed as an inclined wall without being curved in the cross-sectional direction of the discs 5 and 7, or as a locking wall oriented in the axial direction without being inclined. The curvature of the guide tongues 23b and 25b in the cross-sectional direction of the discs 5 and 7 may be a part of the circumferential direction of the guide tongues 23b and 25b, and the remainder may be an inclined surface or the like. The guide tongues 23b and 25b are curved along the outer circumference of the coil spring 9 in the coil circumferential direction with substantially the same curvature, and face the guide holes 20 and 21. In this embodiment, the guide tongue portions 23b and 25b are formed over the entire circumferential direction of the guide holes 20 and 21. However, the guide tongue portions 23b and 25b can be formed by selecting a part of the guide holes 20 and 21 in the circumferential direction. This partial selection in the circumferential direction is performed so as not to interfere with the operation of the coil spring 9 during the damping operation. For example, the guide tongue portions 23b and 25b may be set on both end sides or one end side in the circumferential direction of the guide holes 20 and 21.

Therefore, the outer peripheral side edges of the guide holes 20 and 21 and the guide tongue portions 23a and 25a are guided by the outer diameter side of the coil spring 9 in the radial radius of curvature as a whole. Is provided for the entire length facing the coil spring 9. The guide surfaces 20c and 21c have a curvature corresponding to the curvature of the guide tongue portions 23b and 25b in the cross-sectional direction of the discs 5 and 7. However, depending on the settings of the guide tongue portions 23b and 25b, it may be formed of a slope, a locking surface, or the like having no curvature.

The guide tongue portions 23a and 23b and the guide tongue portions 25a and 25b of both the discs 5 and 7 form a pair and surround the coil spring 9 from the coil radial direction. With this enclosure, the coil spring guides 18 and 19 guide the expansion and contraction operation of the coil spring 9 along the guide holes 20 and 21 while preventing the coil spring 9 from falling off.

The guide tongue portions 23a and 23b and the guide tongue portions 25a and 25b can be formed separately from the discs 5 and 7, and can be assembled to the discs 5 and 7 by welding, adhesion, screwing, or the like. A part of the guide tongue portions 23a and 23b and the guide tongue portions 25a and 25b can be cut up and the other parts can be assembled to the discs 5 and 7 by welding, adhesion, screwing or the like.

The guide tongue portion can be replaced with a guide portion provided on the claw plate 3 which is a drive-side rotating member. When the guide portion is provided on the drive side rotating member, the guide portion is set within a range in which the operation of compressing the coil spring 9 can be secured, and the guide portion is configured to rotate together with the claw plate 3. At this time, the guide portion can similarly perform the functions described later in the relative relationship with the coil spring 9.

The guide tongue portions 23a and 23b are not limited to the form cut up from the disc 5, and may be formed as an integral guide portion in which the guide tongue portions 23a and 23b are continuous with each other in a circular arc shape. In this case, an integral guide portion having an arcuate cross section may be formed of a plate material separate from the disc 5, and may be retrofitted to the edge portion of the guide hole 20 by welding, adhesion, screwing, or the like.

The same applies to the guide tongue portions 25a and 25b, which can be formed as an integral guide portion in which the guide tongue portions 25a and 25b are continuous with each other in an arcuate cross-section. It can be retrofitted to the edge of the guide hole 21 by welding, adhesion, screwing, or the like.

The coil spring guides 18 and 19 are not limited to those composed of the guide holes 20 and 21 and the guide tongue portions 23a and 23b and the guide tongue portions 25a and 25b, but are composed of two members including a concave guide portion and a cover serving as a lid thereof. It can also be formed by such as.

That is, instead of the form in which the claw plate 3 is sandwiched between the discs 5 and 7, the claw plate 3 is arranged side by side between the discs 5 and 7, for example, a guide portion curved in the circumferential direction is hooked to the disc 7. A cover that is attached by hooking or the like and has a circular hole-shaped cross section facing the guide portion and is curved in the circumferential direction is attached to the disc 5, and a spring holding space for guiding the coil spring 9 is formed between the guide portion and the cover. To do. The claw portion of the claw plate 3 is bent in the thickness direction of the discs 5 and 7, for example, and is arranged so as to face the end portion of the coil spring 9 in the circumferential direction. The end portion of the coil spring 9 is exposed to an open portion for the circumferential operation range of the claw portion formed by cutting out the cover, and the claw portion faces the end portion of the coil spring 9 from this open portion.

Further, if an open portion for the circumferential operation range of the claw portion of the claw plate 3 can be provided, the discs 5 and 7 are made into one disc, and the claw plate 3 is arranged side by side on one disc. You can also do it. In this configuration, a guide portion that is substantially tubular and covers the coil spring is attached to a single disc, and the claw portion of the claw plate 3 is bent in the disc thickness direction, for example, and is arranged so as to face the end portion of the coil spring 9 in the circumferential direction. Will be done. The end portion of the coil spring 9 is exposed to an open portion for the circumferential operation range of the claw portion formed by cutting out the guide portion, and the claw portion faces the end portion of the coil spring 9 from this open portion.

Coil springs 9 are arranged in the guide holes 20 and 21 on the inner circumferences of the guide tongue portions 23a and 23b and the guide tongue portions 25a and 25b.

The coil spring 9 is housed in the coil spring guides 18 and 19 in an arc shape, and the seat surfaces 9a and 9b at both ends engage with the claw plate 3 which is a driving side rotating member and the discs 5 and 7 which are driven side rotating members. To do.

That is, the coil spring 9 is formed in an arc shape (arc shape) having a constant curvature as a whole in the direction in which the coil is in the free state along the coil center line. The radius of curvature of the arc-shaped outer peripheral side of the coil spring 9 is formed so as to substantially coincide with the radius of curvature of the guide tongues 23a and 25a in the circumferential direction. The arcuate shape of the coil spring 9 is intended to prevent the surface pressure from being locally concentrated when the coil spring guides 18 and 19 are housed and arranged. Therefore, in the coil spring 9, at least a part of the coil in the free state is arcuate, and the arcuate curvature may substantially match the arcuate curvature of the coil spring guides 18 and 19. Also in this form, it is possible to suppress the concentration of local surface pressure generated when the linear coil spring is housed in the arc-shaped coil spring guides 18 and 19 in the free state. The seat surfaces 9a and 9b of the coil spring 9 are oriented in the radial direction of the damper device 1 orthogonal to the coil center line in this embodiment. The directivity of the seat surfaces 9a and 9b toward the radial side can be appropriately inclined. As described above, the seat surfaces 9a and 9b are coil springs in the guide holes 20 and 21 so as to engage with the locking edges 20a and 20b and the locking edges 21a and 21b of the guide holes 20 and 21 in a free state. 9 is housed. In this state, the contact edge portions 15b and 15c of the claw portion 15 also face the seat surfaces 9a and 9b of the coil spring 9.

[Curvature of coil spring, etc.]
FIG. 5 is a front view showing the relationship between the radius of curvature of the damper device.

Here, with R1: rotation center (axis center) O1 as the origin, a circle (rotation on the claw portion 15) passing through a point where the coil center lines of the coil spring 9 intersect at the positions of both seat surfaces 9a and 9b of the coil spring 9. The radius of curvature of the locus). However, when one of the seat surfaces 9a and 9b of the coil spring 9 is positioned so as to be relatively offset to the inner diameter side according to the arrangement form of the coil spring 9 and the coil spring guides 18 and 19, both seat surfaces of the coil spring 9 The radius of curvature of the circle passing through the point where the coil center lines of the coil spring 9 intersect at the position of the seat surface located on the outer diameter side of both seat surfaces 9a or 9b of the coil spring 9 instead of the positions of 9a and 9b. In some cases. R2: The shortest distance from the rotation center O1 to the coil center line of the coil spring 9. R3: The radius of curvature of the arcuate coil center line of the coil spring 9.

The relationship of each R is set so that R3> R1> R2. Therefore, the center of curvature O3 of the coil center line of the coil spring 9 is located on the opposite side of the coil spring 9 and the coil spring guides 18 and 19 with the axis O1 of the damper device 1 interposed therebetween. Further, a circle whose origin is the axis O1 and whose radius is R1 and a circle whose origin is the center of curvature O3 and whose radius is R3 intersect with each other. In this embodiment, since the arc-shaped curvatures of the coil spring guides 18 and 19 and the arc-shaped curvatures of the coil springs 9 are set to be substantially the same as a whole, the arc-shaped curvature centers of the coil spring guides 18 and 19 are set. Also substantially coincides with the center of curvature O3 of the coil spring 9. To set the position of the center of curvature O3 of the coil center line of the coil spring 9, the shortest distance R2 from the center of rotation O1 to the coil center line of the coil spring 9 is made shorter than the radius of curvature R1 to reduce the radius of action of centrifugal force. It is intended to be reduced. Therefore, the position of the center of curvature O3 may be located on the opposite side of the coil spring 9 and the coil spring guides 18 and 19 with the axis O1 of the damper device 1 interposed therebetween, and is not particularly limited.

In a general arc-shaped coil spring, the coil center line comes on the rotation locus of the claw portion 15. Therefore, the coil spring is arranged on a circle having a radius R1 with the rotation center (axis center) O1 as the origin.

In FIG. 5, both seat surfaces 9a and 9b of the coil spring 9 are located on the same circumference with respect to the rotation center (axis center) O1 and symmetrically with respect to the coil center. However, the seat surfaces 9a and 9b of the coil spring 9 are not limited to those located on the same circumference, and one of the seat surfaces 9a and 9b may be located slightly on the inner diameter side with respect to the other. In this case, R1 has the rotation center (axis center) O1 as the origin, and of the coil center lines of the coil spring 9 and the seat surfaces 9a and 9b of the coil spring 9, the seat surfaces 9a and 9b located relatively on the inner diameter side. The radius of curvature of the circles that match at one position is set, and the relationship of each R is set in the same way. Further, the coil spring guides 18 and 19 and the coil spring 9 may be formed in an arc shape having the same curvature, and the arc shape may be slightly changed such that the curvature on the center side is relatively small along the center of the coil. Good.

The center of curvature O3 of this embodiment is a coil in which the coil spring 9 is housed with the center of rotation (axis) O1 sandwiched on a plane passing through the center of the coil spring guides 18 and 19 and the coil spring 9 in the arcuate circumferential direction. It is located on the opposite side of the spring guides 18 and 19.

[Relationship between claws and seat]
FIG. 6 is a front view showing the contact angle between the coil spring of the damper device and the claw portion.

As shown in FIGS. 4 and 6, the contact edge portions 15b and 15c of the claw portion 15 are in a so-called surface pressing state in which the entire contact edge portions 15b and 15c push the entire seat surfaces 9a and 9b at the time of damping. There is.

In FIG. 6, the radial direction line passing through the position of the seat surface on the L1: rotation center (axis center) O1 and the coil center line (the line pointing in the radial direction and the line pointing in the radial direction and not necessarily in the radial direction but on the radial side). Includes both directional lines). L2: Radial direction line passing through the position of the seat surface on the coil center line O3 of the coil center line of the coil spring 9 and the coil center line (the line pointing in the radial direction and the line pointing in the radial direction and not necessarily in the radial direction but on the radial side) Includes both directional lines). L3: The contact edge portion 15b (15c) (see FIG. 4) of the claw portion 15 (see FIG. 4), the locking edge portion 20a (20b) of the guide hole 20 (21), the locking edge portion (21a), ( 21b) (see FIGS. 1 and 2). θ1: The angle of the contact edge portion 15b (15c) of the claw portion 15, the locking edge portion 20a (20b), and the locking edge portion 21a (21b). θ2: The angle of the seat surface 9a (9b). Although these relationships are shown only on the seat surface 9a side of the coil spring 9 in FIG. 6, since they are also set symmetrically on the seat surface 9b side, the seat surface 9b side is shown in parentheses.

The relationship of θ is θ1> 0 and θ2 = 0.

The bearing surfaces 9a and 9b of the coil spring 9, the contact edges 15b and 15c of the claw portion 15, the locking edges 20a and 20b of the guide holes 20 and 21, and the locking edges 21a and 21b are the radial direction lines L2. It becomes a form along with. This form is a so-called face-pressing state.

However, θ1> 0 and θ2> 0 can also be set. In this embodiment, the contact edge portions 15b and 15c abut on the seat surfaces 9a and 9b at positions biased toward the outer diameter side in the radial direction of curvature of the coil spring 9, which is a so-called outer peripheral pushing state. In this outer peripheral pushing state, the unbalanced position where the contact edge portions 15b and 15c abut on the seat surfaces 9a and 9b is set by the relative relationship between the contact edge portions 15b and 15c and the seat surfaces 9a and 9b. Can be changed.

It should be noted that the selection of surface pressing or outer peripheral pressing can also be performed by setting the seat surfaces 9a and 9b with respect to the coil spring 9.

That is, the contact edge portions 15b and 15c of the claw portion 15, the locking edge portions 20a and 20b of the guide holes 20 and 21, and the locking edge portions 21a and 21b are formed along the radial direction line L2, and the seat surface. It is also possible to incline the 9a and 9b with respect to the radial direction line L2 by inclining and polishing the coil spring 9 with respect to the coil center line to form an outer peripheral push.

[Action of damper device]
When the oil pressure of the pressure chamber formed on the side surface of the discs 5 and 7 is increased by a hydraulic control circuit (not shown), the discs 5 and 7 come into contact with the torque converter output side via a friction member (not shown).

Therefore, the torque converter input side and output side are engaged with each other via the coil spring 9.

Further, by controlling the hydraulic pressure, the contact state with the friction member can be controlled, and the input / output side of the torque converter can be engaged in a slip state in which the torque converter rotates relative to each other at a predetermined relative rotation speed.

When the flood control is released, the friction member is separated from the torque converter output side by the urging force of the return spring. As a result, the claw plate 3 and the discs 5 and 7 move integrally.

When the claw plate 3 receives the input torque from the engine side while the input / output side of the torque converter is directly connected, the seat of the coil spring 9 in which either the contact edge portions 15b or 15c of the claw portion 15 abuts in front of the rotation direction. One of the surfaces 9a and 9b, for example, the seat surface 9b is pressed. By this pressing, one of the locking edges 20a, 20b, 21a and 21b of the guide holes 20 and 21 of the coil spring guides 18 and 19 is used, for example, from the coil spring 9 to the discs 5 and 7 side via the locking edges 20a and 21a. Torque is transmitted to. The torque transmitted to the discs 5 and 7 side is transmitted to the output side of the torque converter.

If there is a torque fluctuation during such torque transmission, the coil spring 9 is engaged in torque transmission with any of the contact edge portions 15b and 15c, for example, the contact edge portion 15c and the locking edge portions 20a and 21a. The torque fluctuation is absorbed by expanding and contracting between one of the edge portions 20b and 21b, for example, the locking edge portions 20a and 21a, and the torque transmitted to the output side of the torque converter is stabilized.

The radial outward force acting on the coil spring 9 at the time of torque transmission is reduced as compared with the conventional general arc-shaped coil spring.

FIG. 7 is an explanatory view showing a decrease in the resultant force acting in the radial direction between the claw portion and the coil spring guide.

In FIG. 7, in the coil spring 9 of the embodiment, the coil center line is on the circle C2 having a radius R3 with O3 as the origin. Explaining both general arc-shaped coil springs, in a general arc-shaped coil spring, the coil center line is on a circle C1 having a radius R1 with O1 as the origin.

Since the coil spring 9 bends along the coil center line, the pressing force acting on the claw portion and the locking edge of the guide hole on the seat surface 9b of the coil spring 9 acts in the tangential direction of the coil center line of the coil spring 9. ..

For this reason, in a general arc-shaped coil spring, a pressing force acts on the seat surface 9b of the coil spring 9 from the claw portion and the locking edge portion of the guide hole in the direction of arrow A1 in FIG. 7, and the resultant force is in the radial direction. It works strongly on the spring and becomes the size of arrow B1.

On the other hand, in the coil spring 9 of the embodiment, a pressing force acts on one of the seat surfaces 9a and 9b of the coil spring, for example, the seat surface 9b from the claw portion 15 and the guide holes 20 and 21 in the direction of arrow A2 in FIG. , The resultant force acting in the radial direction decreases to the size of arrow B2.

Since the resultant force acting in the radial direction is received by the outer edge side of the guide holes 20 and 21 and the guide surface inside the guide tongue portions 23a and 25a, a frictional force is generated when the coil spring 9 bends along the coil center line. It causes hysteresis torque.

However, the hysteresis torque decreases due to the decrease of the resultant force acting in the radial direction from B1 to B2.

Further, the shortest distance R2 (see FIG. 5) from the rotation center O1 to the coil spring 9 can be made smaller than the radius R1 of the arc-shaped coil spring having a general arrangement. By setting the shortest distance R2, the centrifugal force acting on the coil spring 9 at high rotation is reduced as compared with the arc-shaped coil spring having a general arrangement.

Therefore, at high rotation or the like, the outer diameter side of the coil spring 9 in the radial radius of curvature is pressed against the outer edge side of the guide holes 20 and 21 and the inner guide surface of the guide tongues 23a and 25a by centrifugal force. Hysteresis torque is reduced compared to an arcuate coil spring in a typical arrangement.

Further, when the coil spring 9 receives a force outward in the radial direction in the arrow A2 direction of FIG. 7 due to a pressing force or a centrifugal force, the outer diameter side of the coil spring 9 in the arcuate radial direction of curvature is outside the guide holes 20 and 21. The guide surface is generally pressed in the circumferential direction against the guide surface on the edge side and inside the guide tongues 23a and 25a to guide the guide. This overall guide suppresses the generation of local wear and stress on the coil spring 9.

[Examination of outer circumference pushing and surface pushing]
FIG. 8 is a graph showing the relationship between the angle of the claw portion with respect to the seat surface and the hysteresis torque, and FIG. 9 is an explanatory view showing the contact of the claw portion with respect to the outer diameter side of the seat surface.

In FIG. 6, the surface pressing state and the outer peripheral pressing state have been described in the contact of the contact edge portions 15b and 15c of the claw portion 15 with respect to the seat surfaces 9a and 9b of the coil spring 9.

As shown in FIG. 8, the hysteresis torque changed with respect to the angle of the claw portion with respect to the seat surface. The measurement was carried out by applying a general torque measuring device and attaching a coil spring and a claw portion corresponding to this embodiment.

In FIG. 8, the angle (claw angle) between the seat surfaces 9a and 9b and the contact edge portions 15b and 15c in the surface-pushed state was set to 0 deg, and the angles were gradually increased to 2 deg, 4 deg, and 6 deg in the outer peripheral pressed state. The inner peripheral push in FIG. 8 is a form in which the contact edge portions 15b and 15c of the claw portion 15 are brought into contact with the seat surfaces 9a and 9b at positions biased toward the inner diameter side in the radial direction of curvature of the coil spring 9. This contact form is the opposite of the outer peripheral pushing state.

As shown in FIG. 8, in the inner peripheral pushing state, the hysteresis torque increased as the angle in the negative direction increased, and in the outer peripheral pushing state, there was almost no change in the hysteresis torque.

The state in which the hysteresis torque does not change regardless of the increase in the claw angle in the outer peripheral pushing state is the contact state on the left side of FIG. As shown on the left side of FIG. 9, the claw portion 15 abuts on the seat surface 9b of the coil spring 9, but the angle of the seat surface 9b does not follow the angle of the claw portion 15 and the direction of the force does not change, so that the hysteresis torque changes. There is no.

Therefore, in the contact of the contact edge portions 15b and 15c of the claw portion 15 with respect to the seat surfaces 9a and 9b of the coil spring 9, the hysteresis torque can be suppressed by selecting the outer peripheral pushing state or the surface pushing state.

[Initial contact state]
10A and 10B show the attachment of the coil spring to the coil spring guide with a gap, where FIG. 10A is an explanatory view before rotation and FIG. 10B is an explanatory view during rotation.

As shown in FIG. 10A, in the initial setting state of the coil spring 9, a clearance is provided between the outer diameter side 27a of the coil spring guide 27 and the arc-shaped outer diameter side of the coil spring 9 of the coil spring 9 in the radial direction of curvature. Has. The coil spring 9 is brought into a non-contact state with respect to the outer diameter side 27a of the coil spring guide 27.

Even in the non-contact state shown in FIG. 10A, the hysteresis torque can be suppressed by using the configuration of this embodiment.

However, as shown in FIG. 10B, the coil spring 9 is deformed in a bow shape so as to be bent in the coil radial direction (spring lateral bending), and high stress is generated in the portion 9c having a high curvature. In the form in which such a high stress state occurs, the durability is low and stable operation cannot be performed for a long period of time.

Considering the problem of non-contact spring lateral bending in FIG. 10B, the problem of spring restoring force described in FIG. 15, and the problem of local wear in partial contact of FIG. 16, the outer circumferences of the guide holes 20 and 21 are taken into consideration. The side edges and the guide tongues 23a and 25a are configured to totally contact and guide the outer diameter side of the coil spring 9 in the radial radius of curvature, and the spring laterally bends, the spring restoring force is suppressed, and local wear occurs. Was suppressed.

[Effect of Examples]
In the embodiment of the present invention, the claw plate 3 and the discs 5 and 7 that can rotate relative to the common axial center and the discs 5 and 7 that are curved with a center of curvature on the axial center side are arranged. The coil spring guides 18 and 19 and the coil springs 9 which are housed in an arc-shaped curved state on the inner peripheral side of the coil spring guides 18 and 19 and whose both ends engage with the claw plate 3 and the discs 5 and 7. The coil spring 9 expands and contracts with the relative rotation of the claw plate 3 and the discs 5 and 7, and the input rotation from the claw plate 3 is damped and the torque is transmitted from the discs 5 and 7 such as the lockup clutch. The damper device 1 of the device was used.

The coil spring 9 has an arc-shaped coil center line in a free state, and the arc-shaped curvature center O3 is located on the opposite side of the coil spring guides 18 and 19 with the axis O1 in between.

Therefore, the radial outward force acting on the coil spring 9 can be reduced as compared with the conventional arc-shaped coil spring having a general arrangement, and the generation of hysteresis torque can be suppressed.
By suppressing the generation of this hysteresis torque, the substantial spring constant can be lowered.

FIG. 11 is a graph of the relationship between R3 / R1 of FIG. 5 and the reduction rate of the hysteresis torque.

As shown in FIG. 11, the reduction rate of the hysteresis torque increases significantly until R3 / R1 reaches 1.3, and gradually increases after that. That is, in FIG. 5, the hysteresis torque was measured with the coil spring guide and the coil spring in an arc shape having a general arrangement, and this case was compared as R1.

From this result, it can be seen that it is desirable that R3 / R1 exceeds 1.3.

As R3 increases, the radius on which the torque acts decreases, so the transmission torque decreases. Further, since the length of the coil spring 9 becomes shorter, the spring constant increases.

Therefore, the larger the R3 / R1, the better, and about 1.3 is the most desirable.

FIG. 12 shows the relationship between the twist angle and the transmission torque at the time of torque transmission by aligning the transmission torques with respect to the coil spring of a general arc and the coil spring 9 of the embodiment of the present invention.

As shown in FIG. 12, the torque change due to the coil spring of a general arc is T1, while the torque change due to the coil spring 9 of the embodiment of the present invention is T2, and the generation of hysteresis torque is suppressed.

Moreover, the coil spring 9 can bring the arc-shaped intermediate portion closer to the center of rotation with respect to the support positions of the seat surfaces 9a and 9b in the radial direction, and the mounting state of the arc-shaped coil spring in the conventional general arrangement. Centrifugal force can be reduced as compared with.

Also in this respect, the generation of hysteresis torque can be suppressed.

Moreover, since the arc-shaped outer peripheral side is totally abutted and supported on the inner surfaces of the outer peripheral sides of the coil spring guides 18 and 19 in the circumferential direction during torque transmission, local wear is suppressed at the arc-shaped intermediate portion of the coil spring 9. Therefore, stable torque transmission can be performed for a long period of time.

The claw plate 3 includes a claw portion 15 in which the contact edge portions 15b, 15c facing in the circumferential direction engage with the seat surfaces 9a, 9b of the coil spring 9, and the seat surfaces 9a, 9b and the contact edge portions 15b, 15c. Is along the radiation direction line passing through the center of curvature O3 of the coil spring 9.

Therefore, the claw portion 15 can be brought into a surface-pressed state on the coil spring 9 as described above, and the hysteresis torque can be reliably suppressed as shown in FIG.

The claw plate 3 includes a claw portion 15 in which the contact edge portions 15b and 15c facing in the circumferential direction engage with the seat surfaces 9a and 9b of the coil spring 9, and the contact edge portions 15b and 15c are the coil spring 9. It abuts on the seat surfaces 9a and 9b at a position biased toward the outer diameter side in the radius of curvature direction.

Therefore, the claw portion 15 can be pushed to the outer circumference by the coil spring 9, and the hysteresis torque can be reliably suppressed as shown in FIG.

The coil spring guides 18 and 19 are provided with guide surfaces having a curvature that guides the outer diameter side of the coil spring 9 in the radial direction of curvature as a whole at the outer peripheral side edges of the guide holes 20 and 21 and the guide tongues 23a and 25a.

Therefore, it is possible to suppress partial high stress due to the occurrence of local wear of the coil spring 9 and the occurrence of lateral bending of the spring, and stable torque transmission for a long period of time becomes possible.

1 Lock-up clutch damper device 3 Claw plate (driving side rotating member)
5 and 7 discs (driven side rotating member)
9 Coil springs 9a, 9b Seat surface 15 Claws 15b, 15c Abutment edge 18,19 Coil spring guides 20, 21 Guide holes 23a, 25a Guide tongue O1 Center of rotation (axis center)
O3 Center of curvature R1 Center of curvature (axis) O1 is the origin, and the radius of curvature of the circle (rotation locus on the claw) passing through the point where the coil center lines of the coil spring intersect at the positions of both seating surfaces of the coil spring R2 rotation The shortest distance from the center O1 to the coil centerline of the coil spring 9 R3 Radius of curvature of the arcuate coil centerline of the coil spring

Claims (6)

A drive-side rotating member and a driven-side rotating member that can rotate relative to a common axis,
A coil spring guide that has a center of curvature on the axial side and is curved and is arranged on either the driving side rotating member or the driven side rotating member.
It is provided with a coil spring which is accommodated in the coil spring guide in an arc shape and one end thereof engages with the driving side rotating member and the other end portion engages with the driven side rotating member.
A damper of a torque transmission device that expands and contracts the coil spring with relative rotation between the driving side rotating member and the driven side rotating member to dampen the input rotation from the driving side rotating member and output it from the driven side rotating member. It ’s a device,
In the free state of the coil spring, at least a part of the coil is arcuate.
The arc-shaped center of curvature is located on the opposite side of the coil spring guide with the axial center in between.
The drive-side rotating member includes a claw portion in which a contact edge portion facing in the circumferential direction engages with the seat surface of the coil spring.
The bearing surface and the contact edge are along a radial direction line passing through the center of curvature of the coil spring.
A damper device for a torque transmission device. The damper device of the torque transmission device according to claim 1.
The coil spring guide is provided with a guide surface having a curvature that guides the outer diameter side of the coil spring in the radial direction of curvature as a whole.
A damper device for a torque transmission device. The damper device of the torque transmission device according to claim 1 or 2 .
R1: The radius of curvature of a circle that passes through the point where the coil center lines of the coil spring intersect at the position of the seating surface of the coil spring with the axis as the origin.
R3: Arc-shaped radius of curvature of the coil spring
age,
A damper device for a torque transmission device characterized in that R3 / R1 exceeds 1.3 . A drive-side rotating member and a driven-side rotating member that can rotate relative to a common axis,
A coil spring guide that has a center of curvature on the axial side and is curved and is arranged on either the driving side rotating member or the driven side rotating member.
It is provided with a coil spring which is accommodated in the coil spring guide in an arc shape and one end thereof engages with the driving side rotating member and the other end portion engages with the driven side rotating member.
A damper of a torque transmission device that expands and contracts the coil spring with relative rotation between the driving side rotating member and the driven side rotating member to dampen the input rotation from the driving side rotating member and output it from the driven side rotating member. It ’s a device,
In the free state of the coil spring, at least a part of the coil is arcuate.
The arc-shaped center of curvature is located on the opposite side of the coil spring guide with the axial center in between .
The coil spring guide is provided with a guide surface having a curvature that guides the outer diameter side of the coil spring in the radial direction of curvature as a whole.
A damper device for a torque transmission device. The damper device of the torque transmission device according to claim 4 .
The drive-side rotating member includes a claw portion in which a contact edge portion facing in the circumferential direction engages with the seat surface of the coil spring.
The contact edge abuts on the seat surface at a position biased toward the outer diameter side in the radial radius of curvature of the coil spring.
A damper device for a torque transmission device. The damper device of the torque transmission device according to claim 4 or 5.
R1: The radius of curvature of a circle that passes through the point where the coil center lines of the coil spring intersect at the position of the seating surface of the coil spring with the axis as the origin.
R3: Arc-shaped radius of curvature of the coil spring
age,
R3 / R1 exceeds 1.3
A damper device for a torque transmission device.

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