JPS59166723A - Torque variation absorber - Google Patents

Abstract

PURPOSE:To prevent abnormal wear by displacing the axis of the stem of a columnar resilient member toward the center of turn thereof with respect to the center of inclined revolution of a seat member. CONSTITUTION:The axis of the stem of a columnar resilient member 27 is displaced by delta to the center of rotation thereof with respect to the center of inclined revolution of a seat member. Since the force is applied to the resilient member 27 so that it may be bent toward the center thereof and said force counteracts the centrifugal force which acts on the resilient member 27 so that the member 27 will not be bent externally to an unallowable extent and be compressed uniformly, thereby preventing the member from abnormal wear.

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, particularly an engine torque fluctuation absorbing device, a so-called torsional damper built into a clutch disc or a flywheel, a damper for ships, etc. are 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 in that the amounts were different and the initial performance (especially the load characteristics of the elastic member) could not be satisfied. In view of this, the applicant has developed a system in which a seat member that holds both ends of a columnar resilient member is tilted in accordance with the degree of relative rotational displacement between the first and second members. Proposed a device that equalized the amount of elasticity and contraction of members [Patent Application No. 93024 of 1978 (filed on July 28, 1978), Patent Application Publication No. 43176 of 1981 (published in October 1980) We have put it into practical use and have conducted various tests to maintain its performance stably over a long period of time, while conducting repeated durability tests.

Among them, the results of tests carried out on vehicles (so-called actual vehicle tests) show that the rotational force (usually expressed as a 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 characteristics (generally referred to as torsion-torque characteristics) fluctuates significantly or that abnormal noise occurs. Therefore, when we disassembled the device in which such a phenomenon occurs and inspected the parts that make up the device in detail, we found that in the device configured as shown in Figure 6, the window portion 231b formed in the flat plate member serving as the first member. Traces of interference between the radially outer edge and the radially outer portion of the columnar resilient member 227 were observed.

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. When the rotation speed is maintained near the limit, 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 remains in contact with the radially outer edge of the window 231b. It was also confirmed that the curved shape 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 was made in view of the above points, and it suppresses the influence of centrifugal force acting on the columnar elastic member, minimizes the outward radial curvature of the columnar elastic member, and provides stable characteristics. The purpose is to provide a device with

The present invention provides a structure that extends between a first member that rotates while being connected to a driving side member, and a second member that stands concentrically in parallel with the first member and rotates while being connected to a driven side member. When the columnar elastic member is compressed and the first and second members undergo a predetermined relative rotational displacement, the seat member holding both ends of the elastic member moves the first and second members relative rotationally. The torque fluctuation absorbing device is configured to tilt according to the degree of displacement, and is characterized in that the column center of the columnar elastic member is displaced toward the center of rotation with respect to the center of rotation of the seat member. This is a torque fluctuation absorber.

According to the present invention, with the above-described configuration, it is possible to minimize the radially outward curvature of the columnar resilient member, and for example, the first
Friction between the radially outer edge of the window formed on the member and accommodating the resilient member and the radially outer portion of the columnar resilient member is suppressed, thereby preventing abnormal wear.

In 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 a window or notch that accommodates a columnar elastic member, and holds both ends of the elastic member so as to be tiltable relative to the edges. established,
The structure is such that the column center of the columnar resilient member is displaced toward the rotation center with respect to the cartwheel center of the seat member.

Further, a pivot mechanism for tilting the seat member with respect to both edges in the circumferential direction of the window section or cutout section that accommodates the columnar elastic member is formed in the abutting and engaging section, 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. It has a displaced configuration.

Furthermore, 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.

1 to 4, a sub-plate 20b is positioned by a pin 18 and screwed by a port 19 on a drive plate 10 which is concentrically connected to a drive shaft (not shown) and rotates integrally with the drive shaft (not shown). A ring gear 20a is held therein, 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
Annular friction members 25b and 25a are pressed against flat plate members 30b and 30a by a disc spring 26 stretched between them. The center direction portions of the flat plate members 30a and 30b are
It is screwed concentrically to the driven member 40 by a pin 48 and a bolt 49 in the central direction of the driven member 40, and is capable of relative rotational displacement with respect to driven plates 50 and 60 arranged with the flat plate members 30a and 30b in between. It is supported by a cylindrical surface portion 66 of the driven plate 60. 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. The driven side member 40 and the driven plates 50 and 60, which are screwed into one body, are supported concentrically with respect to the driven plate so as to be rotatably displaceable relative to the driven plate. This screw-integrated driven side member 4
0, the driven plates 50 and 60 are supported by the cylindrical surface portion 66 of the driven plate 60, and are provided with a thrust plate 45 and an axial spring plate 46 (not shown) disposed between the flat plate portion of the driven plate 60 and the flat plate member 30b. is pressed in the direction of the driven plate 10 by. 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. Flat plate member 3. Similarly, a window 31a that is exactly the same as the window 31b of the flat plate member 30b is bored in Oa, and the window is also provided with a groove that is exactly the same as the members 32b and 33b. In these grooves, a construction part 71 having a substantially semicircular cross-section extending in the radial direction is abutted and engaged with the back surface of the flat plate part 73 as shown in FIG. The mechanism is configured.

The end surface of the spring seat 70 is abuttingly engaged with the receiving surface 74 of the flat plate portion 73 of the spring seat 70, which serves as the tiltable seat member, and the protruding portion 72 serves as a support portion for the elastic member protruding from the receiving surface 74. A spring member 27, which is a columnar resilient member, is supported by the outer circumferential portion and stretched between both spring seats 70 and 70, and an elastic member which also acts as a stopper is provided in the inner cavity of this 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 on both sides of the notches 51 in the circumferential direction are approximately half-sized like the windows. Circular grooves 52, 53 are provided and constitute a pivot mechanism. Also, the driven plate 60 is similarly provided with a notch 61, and grooves are similarly provided on both sides of the notch 61 in the circumferential direction, thereby forming a pivot mechanism.

The center of the protrusion 72, which serves as a support part that supports the longitudinal end of the columnar elastic member, is the center of rotation relative to the center of tilt of the proof 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 such a state, the approximately center portion of the spring 27 in the left-right direction in the first drawing is the window portion 31a.

31b and the circular arcuate portions 35a, 35b and 5 formed approximately in the left-right direction at the rotation center side edges of the notches 51 and 61.
It slightly contacts the tops of 1a and 61a. Further, the spring seat 70 has a substantially rectangular shape as shown in FIG. , abnormal tilt is prevented.

In such a configuration, when power is transmitted between the driven plate 1o and the driven member 40, the flat plate members 30a, 30b move clockwise in FIG. 1 relative to the driven plate 50, 60. When the spring seat 70 tries to rotate relative to the other side (in the right direction in FIG. 3), one of the spring seats 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 confession part 71 of the other spring seat 70 (left side in Figure 3)
comes into contact with the groove 32b of the flat plate member 30b and the groove of the flat plate member 30a, and the suffling 27 is compressed by both. As a result, the spring 27 is bent in accordance with the magnitude of the transmitted torque, and the flat plate members aoa and 30b are rotationally displaced relative to the driven plates 50 and 60.

At the time of this relative rotational displacement, in the conventional device, as shown in FIG. Grooves 2 forming a pivot mechanism formed on both sides of the notches 251 and 261 in the circumferential direction
32, 233 and 252, 253, 262, 263, the blank parts 71', 71 of the seat members 270, 276 rotate relative to each other, and the seat members 270, 270 tilt. For this reason,
The spring seat 270. '
270 is tilted, and the spring 227 is elastically compressed almost uniformly. Free of charge, if the rotation speed becomes abnormally high (for example, close to the initially planned maximum rotation speed), the spring 227
The centrifugal force acting on the spring 227 causes the spring 227 to curve in the centrifugal direction opposite to the direction of the center of rotation. This caused 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 plate 50, 60, a force is applied that causes curvature in the direction of the center of rotation, and the centrifugal force acting on the spring 27 is counteracted.
When b undergoes a relative rotational displacement, the spring seat 70°70 moves the driven plate 50.60 around the construction part 7L71
When the flat plate members 30a and 30b are tilted, even if centrifugal force acts as described above, the spring 2
7 is compressed approximately evenly without being abnormally curved outward. Also driven play) 50. When the 60 pair flat plate members 30a and 30b try to rotate relative to each other in the counterclockwise direction, contrary to what has been described above, the offset portion 71 of one of the spring seats 70 engages with the groove portion 3 of the flat plate member 30b.
3b and the grooves of the flat plate member 30a, and the blank portion 71 of the other spring seat 70 comes into contact with the groove 52 of the driven plate 5° and the groove of the driven plate 6o, and the spring 27 is compressed by both. As a result, the spring 27 is elastically contracted in accordance with the magnitude of the transmitted torque, and the flat plate members 30a, 30 are moved against the driven plates 50, 60.
b undergoes a relative rotational displacement opposite to that up until now, and the spring 27
is compressed approximately 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 131b and a notch 1 of a flat plate member 130 and a driven play 150 are provided.
Approximately semicircular convex portions 1 are provided on both sides in the circumferential direction of 51.
32b, 133b and 152, 153 are provided by tensioning a spring 127 as shown in the drawings, and their functions will be omitted since they can be easily understood from the explanation of FIGS. 1 to 4.

As described in detail above, according to the present invention, the first member (flat plate member 30 a,
30 b) and a second member (driven play) that stands concentrically parallel to the first member and rotates while being connected to the driven member.
50, 60), the columnar resilient member (spring 27) is elastically contracted, and both the first and second members (flat plate member 30a) are compressed.

30b and the driven plates 50, 60) undergo a predetermined relative rotational displacement, the seat member (spring seat 70) that holds both ends of the resilient member (spring 27)
Both members (flat plate members 30a, 30b and driven play)
50.60) In the torque fluctuation absorbing device that tilts according to the degree of relative rotational displacement, the column center of the columnar elastic member (spring 27) is relative to the tilt center of the seat member (spring seat 70). By displacing the coil center (coil center) toward the rotation center, it is possible to minimize the radially outward bending of the columnar elastic member (spring 27). The first member (
Flat plate member 30a, 3. Since the radially outer edge of the window housing the resilient member formed in Ob) and the radially outer portion of the columnar resilient member (spring 27) are prevented from coming into contact with each other, abnormal wear can be prevented.

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

[Brief explanation of drawings]

FIG. 1 is a front view showing one embodiment of the present invention, and FIG. 2 is a front view showing one embodiment of the present invention.
3 is a sectional view taken along line mm in 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. In the explanatory diagram of the symbols, 10 is a driving side member, 30a and 30b are first members, 40 is a driven side member, 50 and -60 are second members, 27 is a columnar elastic member, and 70 is both ends of the elastic member Seat members 32a, 32 that hold
b, 3'3a, 33b, 52, 53.62.63 and 7
1 indicates the 11J rotation mechanism, and δ indicates the amount of displacement of the center of the column of the columnar elastic member with respect to the center of tilting of the seat member. Patent applicant: 1 Ireshi w4 Narai Co., Ltd. Representative: Reio Nakai

Claims (1)

[Claims] A column-shaped member arranged between a first member that rotates while being connected to the driving side member and a second member that stands concentrically in parallel with the first member and rotates while being connected to the driven side member. When the elastic member is compressed and the first and second members undergo a predetermined relative rotational displacement, the seat member that holds both ends of the elastic member adjusts to the extent of the relative rotational displacement between the first and second members. A torque fluctuation absorbing device configured to tilt according to the rotational direction, wherein the column center of the columnar resilient member is displaced toward the rotation center with respect to the tilting center of the seat member.