JPH0245055B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a torque fluctuation absorbing device, and more particularly, compresses a columnar elastic member disposed between two members that are relatively rotationally displaced to each other, thereby causing both members to have a predetermined relative rotational displacement. This invention relates to a torque fluctuation absorbing device that absorbs torque fluctuations in this manner.

As this type of device, especially an engine torque fluctuation absorbing device, a so-called torsional damper or a ship damper, which is incorporated in a clutch disk, flywheel, etc., is known. In these devices, when compressing a columnar elastic member disposed between two members that are rotationally displaced relative to each other, the columnar elastic member undergoes elastic contraction in the direction of the center of rotation and in the direction of the outer circumference. There was a problem that the initial performance (particularly the load characteristics of the elastic member) could not be satisfied because the amounts were different. In this regard, the applicant has proposed a method in which a seat member that holds both ends of a columnar resilient member is tilted according to the degree of relative rotational displacement between the first and second members. Proposed a device that equalized the amount of elasticity [Patent Application No. 93024 (filed in 1978)]
Proposed in Patent Application Publication No. 43176 (published on October 9, 1982)], it was put into practical use and underwent repeated durability tests to ensure stable performance over a long period of time. We have conducted various tests to maintain this level.

Among them, the results of tests carried out on vehicles (so-called actual vehicle tests) show that the rotational force (usually expressed as torsional torque) in response to the relative rotational displacement (usually expressed as a torsion angle) of two members that are relatively rotationally displaced relative to each other. It has been frequently observed that the hysteresis in the torsion-torque characteristic (generally referred to as the torsion-torque characteristic) fluctuates significantly or that abnormal noise occurs. Therefore, when we disassembled the device in which this phenomenon occurs and inspected the parts that make up the device in detail, we found that the sixth
In the device configured as shown in the figure, traces of interference between the radially outer edge of the window portion 231b formed in the flat plate member serving as the first member and the radially outer portion of the columnar resilient member 227 are observed. Ta.

Regarding this point, we conducted a bench test using a continuous light emitting device and visually observed the relationship between the radially outer edge of the window portion 231b and the radially outer portion of the columnar elastic member 227 in synchronization with the rotation speed. Upon observation, the aforementioned interference was confirmed when the rotational speed rapidly increased to near the initially set rotational speed limit. Then, when the rotational speed is maintained near the limit after that, the radially outer edge of the window portion 231b and the radially outer portion of the columnar resilient member 227 remain in contact with each other, and the columnar resilient member 227 It was also confirmed that it was curved outward in the radial direction.

The radially outward curvature of the columnar resilient member 227 becomes more pronounced as the mounting position (radius from the rotation center) of the columnar resilient member 227 is farther from the rotation center and the amount of elastic contraction is larger. It was noticeable.

From the above, the centrifugal force acting on the columnar resilient member causes the columnar resilient member to curve, and in particular, the tilting center of the seat member and the column center of the columnar resilient member are aligned. I learned that there is a great deal of connection between what we do and what we do.

The present invention has been made in view of the above points,
To provide a device that suppresses the influence of centrifugal force acting on a columnar elastic member, minimizes radially outward curving of the columnar elastic member, and has stable characteristics.

The present invention provides a first motor which is connected to a drive side member and rotates.
The first member is compressed by compressing a columnar elastic member disposed between the member and a second member that stands concentrically in parallel with the first member and rotates while being connected to the driven member.
and torque fluctuation such that when the second members undergo a predetermined relative rotational displacement, the seat member holding both ends of the resilient member tilts in accordance with the degree of relative rotational displacement of the first and second members. The torque fluctuation absorbing device is characterized in that the column center of the columnar elastic member is displaced toward the rotation center with respect to the tilt rotation center of the seat member.

According to the present invention, with the above-described configuration, it is possible to minimize the radially outward curving of the columnar resilient member, and for example, the first member that is connected to the drive side member and rotates. Friction between the radially outer edge of the window housing the resilient member and the radially outer portion of the columnar resilient member is suppressed, thereby preventing abnormal wear.

When carrying out the present invention, it is preferable to carry out the following procedure.

A seat member that abuts and engages the edges of both ends in the circumferential direction of the window or notch that accommodates the columnar elastic member, and holds both ends of the elastic member so as to be tiltable relative to the edges. The center of the columnar resilient member is displaced toward the center of rotation with respect to the center of rotation of the seat member.

Further, a pivot mechanism for tilting the seat member with respect to the edges of both circumferential ends of the window or notch that accommodates the columnar elastic member is formed in the abutting and engaging portion, and the pivot mechanism is In order to displace the column center of the columnar resilient member toward the rotation center with respect to the tilting center, the center of the support part that supports the longitudinal end of the columnar resilient member is moved toward the rotation center with respect to the tilting center. The configuration is such that it is displaced.

Furthermore, an extension with a substantially semicircular cross section forming a pivot mechanism is formed on the back surface of the seat member, and a substantially semicircular groove is formed on the opposing edge, and a side surface portion of the seat member is guided. do.

Embodiments of the present invention will be described below based on the drawings.

In Figures 1 to 4, a drive plate 1 that is concentrically connected to a drive shaft (not shown) and rotates integrally with it.
0, a sub-plate 20b is positioned with a pin 18 and screwed with a bolt 19,
A ring gear 20a is held, and the ring gear member 20 rotates concentrically with the drive plate 10. The sliding surface 21 of the sub-plate 20b and the sliding surface 11 of the drive plate 10
The annular friction members 25b and 25a are connected to the flat plate member 3.
They are pressed together by a disc spring 26 stretched between 0b and 30a. Flat plate parts 30a and 30b
The central portion of the driven member 40 is concentrically screwed to the driven member 40 by a pin 48 and a bolt 49, and is connected to the flat plate member 30a.
and 30b, and is supported by the cylindrical surface portion 66 of the driven plate 60 so as to be rotationally movable relative to the driven plates 50 and 60, which are arranged to sandwich the driven plates 50 and 30b. Further, a thrust bearing 16 and a radial bearing 15 are interposed between the inner cylindrical surface portions 55 and 65 of the driven plates 50 and 60 and the sliding surface 12 and the cylindrical outer surface portion 13 of the driven plate 10. Driven side member 4 integrated with screws
0. The driven plates 50 and 60 are supported concentrically with respect to the driven plate so as to be rotatably displaceable relative to the driven plate. The driven side member 40 and the driven plates 50 and 60, which are screwed together, are supported by the cylindrical surface portion 66 of the driven plate 60, and are connected to the flat plate portion of the driven plate 60 and the flat plate member 30.
b and is pressed in the direction of the driven plate 10 by a thrust plate 45 and a ring spring plate 46 (not shown), which are disposed between the drive plate 10 and the drive plate 10. The flat plate member 30b has a predetermined number of windows 31b radially and equally spaced in the circumferential direction, and substantially radial grooves 32b and 33b are formed at both ends of the window in the circumferential direction. It is provided. Similarly, the flat plate member 30a has a window 31a that is exactly the same as the window 31b of the flat plate member 30b, and the window 31a is similarly provided with the window 31b of the flat plate member 30b.
A groove portion that is exactly the same as that of b and 33b is provided.
In these groove portions, an extending portion 71 having a substantially semicircular cross-section extending in the radial direction is abutted and engaged with the back surface of the flat plate portion 73 as shown in the fourth figure. The mechanism is configured.

The protruding portion 72 has an end surface abuttingly engaged with the receiving surface 74 of the flat plate portion 73 of the spring seat 70 serving as the tiltable seat member, and serves as a support portion for the resilient member protruding from the receiving surface 74. A spring member 27, which is a pillar-shaped resilient member, is supported by the outer circumferential portion and stretched between both spring seats 70, 70, and an elastic member which also acts as a stopper is provided in the inner cavity of the spring 27. A member 28 is inserted. On the other hand, the driven plate 50 is provided with a predetermined number of notches 51 at positions corresponding to the windows of the flat plate member, and the both sides of the notches 51 in the circumferential direction are approximately half-sized like the windows. Circular grooves 52 and 53 are provided and constitute a pivot mechanism. Similarly, the driven plate 60 is also provided with a notch 61.
Grooves are similarly provided on both sides of the notch 61 in the circumferential direction, and similarly constitute a pivot mechanism.

The center of rotation is the center of the protrusion 72, which serves as a support part that supports the longitudinal end of the columnar elastic member, with respect to the center of rotation of the extending part 71 formed on the back surface of the spring seat 70 with respect to the mating member. As shown in the first diagram, the center of the columnar resilient member is displaced by δ toward the center of rotation with respect to the center of rotation. In this installation condition, the spring 27
The window portion 31 is approximately at the center in the left-right direction in the first drawing.
a, 31b and the circular arc strip portion 35 formed approximately in the center of the rotation center side edges of the notches 51 and 61 in the left-right direction.
a, 35b and the tops of 51a, 61a slightly. Moreover, the spring seat 70 is the fourth
As shown in the figure, it has a roughly octagonal shape, and its side surface 7
5, 75 are drive side members; drive plate 1;
0 and the inner guide surfaces 17, 47 of the driven member 40 to prevent abnormal inclination.

In such a configuration, when power is transmitted between the driven plate 10 and the driven member 40, the flat plate members 30a and 30b move clockwise relative to the driven plates 50 and 60, for example, in FIG. When the spring seat 70 tries to rotate relative to the spring seat 70 (in the right direction in FIG. 3), the extending portion 71 of the spring seat 70 (on the right side in FIG. 3) comes into contact with the groove 53 of the driven plate 50 and the groove of the driven plate 60. ,
The extending portion 71 of the other (left side in FIG. 3) spring seat 70 comes into contact with the groove 32b of the flat plate member 30b and the groove of the flat plate member 30a, and the spring seat 27 is clamped by these two. As a result, the spring 27 is bent in accordance with the magnitude of the transmitted torque, and the flat plate members 30a, 30 are bent relative to the driven plates 50, 60.
b undergoes a relative rotational displacement.

At the time of this relative rotational displacement, in the conventional device, as shown in FIG.
31 and grooves 232, 23 forming a pivot mechanism formed on both sides of the circumferential direction of the notches 251, 261.
3 and 252, 253, 262, 263, the extending portions 71, 71 of the seat members 270, 270 rotate, and the seat members 270, 270 tilt. For this purpose, the flat plate member 230 and the driven plate 25
The spring seats 270, 270 are tilted in accordance with the degree of relative rotational displacement of 0.260 degrees, and the spring 227 is elastically compressed substantially uniformly. However, if the rotational speed becomes abnormally high (for example, near the initially planned maximum rotational speed), the centrifugal force acting on the spring 227 causes the spring 227 to bend in the centrifugal direction opposite to the direction of the center of rotation. The curvature is promoted by tilting and rotating the seat members 270, 270 by the pivot mechanism, and the spring 227 abuts and engages with the edge of the window portion 231, causing various problems.

According to the device according to the present invention, as described above, the coil center, which is the column center of the spring 27, which is a columnar elastic member, is moved closer to the rotation center with respect to the tilting center of the spring seat 70, which is a seat member. By displacing the flat plate members 30a, 30 to the driven plates 50, 60, a force is applied to cause curvature in the direction of the center of rotation, and by countering the centrifugal force acting on the spring 27, the flat plate members 30a, 30
When b undergoes relative rotational displacement, the spring seat 70,
When the spring 70 is tilted relative to the driven plates 50, 60 and the flat plate members 30a, 30b, respectively, around the extending portions 71, 71, even if centrifugal force is applied as described above, the spring 27 will not abnormally move outward. It is compressed almost uniformly without being curved. Further, the flat plate members 30a, 30b for the driven plates 50, 60
If attempts to rotate relative counterclockwise, then
Contrary to what was described above, the extending portion 71 of one spring seat 70 contacts the groove portion 33b of the flat plate member 30b and the groove portion of the flat plate member 30a, and the extending portion 71 of the other spring seat 70 contacts the driven plate 50.
The spring 27 comes into contact with the groove 52 of the driven plate 60 and the groove of the driven plate 60, and the spring 27 is clamped by these two. As a result, the spring 27 is elastically compressed according to the magnitude of the transmitted torque, and the driven plates 50, 60
On the other hand, the flat plate members 30a and 30b undergo relative rotational displacement in the opposite direction to that up to now, and the spring 27 is compressed substantially uniformly as described above.

FIG. 5 shows another embodiment of the present invention, in which a spring seat 170 is provided with a substantially semicircular shape 171, and a window portion 131b and a notch portion 151 of a flat plate member 130 and a driven plate 150 are provided on both sides in the circumferential direction. Approximately semicircular convex portions 132b, 133b and 152, 153 are provided, and a spring 127 is tensioned as shown in the figure.
Since it is easily understood from the explanation of FIGS.

As explained in detail above, according to the present invention, the first member (flat plate members 30a, 30b) that is connected to the driving side member and rotates, and the first member (flat plate members 30a, 30b) that stands concentrically in parallel with the first member and is connected to the driven side member. The columnar resilient member (spring 27), which is disposed between the rotating second member (driven plates 50, 60), is elastically compressed, and both the first and second members (flat plate member 30a,
30b and driven plates 50, 60) undergo a predetermined relative rotational displacement, the elastic member (spring 2
7) The seat member (spring seat 70) that holds both ends of the first and second members (flat plate member 30a,
In the torque fluctuation absorbing device that tilts according to the degree of relative rotational displacement between the seat member (spring seat 70) and the driven plates 50, 60), a columnar elastic member (spring 27) ) by displacing the column center (coil center) closer to the rotation center, it is possible to minimize the outward radial curvature of the columnar elastic member (spring 27). The first member (flat plate members 30a, 30
The radially outer edge of the window housing the resilient member formed in b) and the columnar resilient member (spring 27)
Abnormal wear can be prevented by suppressing friction on the radially outer portion of the shaft.

Although the present invention has been described above as an embodiment in which the present invention is incorporated into a flyhole, the present invention is not limited to the embodiment and is not limited to the embodiment, and within the scope of the spirit of the present invention (for example, a clutch disc or a vehicle). (as a damper for ships, etc.) can be modified and modified as appropriate.

[Brief explanation of the drawing]

Figure 1 is a front view showing one embodiment of the present invention, Figure 2 is a front view showing one embodiment of the present invention;
The figure is a sectional view taken along the line of FIG. 1, FIG. 3 is a sectional view taken along the line of FIG. FIG. 6 is a partial view showing a modified example of the pivot mechanism forming the main part, and FIG. 6 is a partial view showing the main part of the conventional device. Explanation of symbols: In the figure, 10 is a drive side member, 30
a, 30b are first members, 40 is a driven member, 5
0 and 60 are second members, 27 are columnar elastic members, and 7
0 is a seat member 32a that holds both ends of the elastic member;
32b, 33a, 33b, 52, 53, 62, 6
3 and 71 are tilting mechanisms, and δ is the amount of displacement of the column center of the columnar resilient member with respect to the tilt center of the seat member.

Claims (1)

[Claims] 1 Column-shaped columns arranged mutually between a first member that rotates while being connected to the driving side member and a second member that is concentrically parallel to the first member and rotates while being connected to the driven side member. Compressing the elastic member to remove the first and second
In the torque fluctuation absorbing device, when the two members undergo a predetermined relative rotational displacement, a seat member that holds both ends of the elastic member tilts according to the degree of relative rotational displacement of the first and second members. . A torque fluctuation absorbing device, characterized in that the longitudinal center of the columnar resilient member is displaced toward the center of rotation with respect to a line connecting the centers of tilting of the seat members.