JPS5861331A - Flexible shaft coupling - Google Patents

Abstract

PURPOSE:To aim at preventing an elastic member from wear and vibration, by setting up a pair of elastic members in a ring groove provided on the end face of one side coupling twin out of the pair at regular intervals in a linkage projection jug form, while making engagement claws provided at the other coupling twin to link up with circumferential elastic members in between. CONSTITUTION:A linkage projection 16 is formed in a ring groove 15 provided on the end face of one side coupling twin out of the pair at regular intervals and elastic members 17 and 18 are set up inside a groove 15 from the radial inside and outside in relation to the linkage projection 16. And, engagement claws 20 being projected to the other side coupling twin 13 are engaged with circumferential voids 19 of these elastic members 17 and 18 and then the coupling twins 12 and 13 are coupled together. With this constitution, even if an eccentric value alpha exists in the pair of rotary shaft, elastic members 17 and 18 are being divided into two parts so that the internal stress is theoretically decreased to about one fourth; wear and vibration of these elastic members 17 and 18 can be lessened.

Description

DETAILED DESCRIPTION OF THE INVENTION Technical Field The present invention relates to a flexible shaft coupling that connects a pair of rotating shafts to transmit power.

Prior Art Conventionally, when connecting a pair of opposing rotating shafts using a shaft coupling, it was extremely difficult to align the center lines of both shafts on the same line during assembly, so the center lines of both shafts were aligned from the beginning. What has been proposed is a flexible shaft joint, and various types of flexible shaft joints have been proposed.

For example, as shown in FIGS. 1 and 2, a plurality of H-shaped elastic members 1 are fitted into an annular retaining groove 3 recessed in the end face of one joint half 2. Locking protrusions 4 are provided which are fitted to each other at equal intervals and which are fitted to the four parts of the elastic member 1 from the inward side surface of the engagement groove 3.

An engaging pawl 6 is formed protruding from the other joint half 5 to lock into the locking space formed by the adjacent elastic members 1j in the one joint half 2, thereby forming an inner joint. Half holiday 2.
5 were to be concatenated with each other. In addition, 7
is a mounting hole for mounting a rotating shaft, which is provided in the axial direction of each of the joint halves 2, 5.

However, if the pair of rotating shafts to which the joint halves 2 and 5 are attached are eccentrically arranged, vibrations occur during operation, which causes wear on the elastic member 1 and the structure described above. It was not possible to completely prevent the vibrations.

The cause of the above-mentioned vibrations can be considered to be internal stress generated by eccentricity of both shafts in the elastic member 1 interposed between the inner joints, and the greater the internal stress, the greater the amount of movement. Therefore, respond internally.

By the way, it is known that the relationship between the amount of deflection τ and the load q in a cantilever beam based on material mechanics is as follows if the beam is integral.

Note that k is a constant, E is an elastic constant, l is the length of the beam, W is the width of the beam, and ■■ is the height of the beam.

It is also known that if the beam is divided into two equal parts n in the length direction, the load q will be .

Therefore, if the ratio of the load between the case where the elastic member 1 is integral and the case where it is divided into two equal parts is found, it will be θ'' 2-4 .

The internal stress generated in response to the load q applied to this beam can be considered to correspond to the internal stress generated in the elastic member 1 due to the eccentricity X, and if the elastic member 1 is divided into two in the radial direction of the joint half 2, Internal stress can be reduced. Since the wear of the elastic member 1 can be considered to be proportional to the internal stress, reducing the internal stress can reduce the wear and at the same time can suppress the occurrence of vibration. Furthermore, if the elastic member 1 is divided into three or more parts in the radial direction, wear of the elastic member 1 can be significantly reduced.

As described above, this invention has been made based on the above-mentioned theory, and the purpose of this defense is to connect a pair of l! Even if the F1 rotating shafts are installed eccentrically to each other, they will still be interposed between the joint halves! By reducing the internal stress generated in the elastic member, it is possible to reduce the wear of the elastic member by VC and extend the long life of the elastic member, and also to prevent the following movement during transportation. We aim to provide a flexible shaft joint that can achieve

EXAMPLE An example embodying the present invention will be described below with reference to FIGS. 5 to 8.

Reference numerals 10 and 11 shown in FIG. 7 denote a pair of rotating shafts having the same axis direction and facing 77 V'C, and the opposing ends of both shafts are provided with fludges 12a having the same diameter.

A joint half 12.13 having a diameter of 13υr is fitted and fixed through a mounting hole 14 provided through the shaft in the axial direction. 15
1 is an annular retaining groove formed concentrically with the rotating shaft 10 on the end surface of the flange 12a of one joint half 12;
Reference numeral 6 denotes a plurality of locking protrusions protruding from the bottom of the retaining groove 15 at equal intervals along the axial direction of the joint half body 12. It is formed at equal intervals from the inner wall, and its end surface is connected to the joint half body 1.
It is flush with the tip surface of 2.

Reference numeral 17 denotes an elastic member made of synthetic rubber, natural rubber, etc., which is secured between each locking protrusion 16 and the outer inner wall of the retaining groove 15, and has a width of four widths of the retaining groove g15. The four parts 17a which are engaged with the locking protrusions 16 are recessed in the center of the inner side, forming a U-shape.

18 is a U-shaped part 18a made of synthetic rubber, natural rubber, etc., which is held between each locking protrusion 16 and the inner wall of the engagement groove 15. It faces the inner surface of member 17. Therefore, unlike the conventional elastic member 1, both elastic members 17 and 18 are divided into two parts in the radial direction so as to wrap around the engagement projection 16 from both inside and outside directions.

Both elastic members 17 and 18 form a locking space 19 between them and another adjacent elastic member 17 and 18, and a locking space 19 is formed in the locking space 19 through which an engagement portion protrudes from the distal end surface of the joint half body 13. By engaging the claws 20, the two joint halves 12 and 13 are connected.

Now, the operation of the flexible shaft joint configured as described above will be explained.

When the rotating shaft 11 is rotated, the rotation torque is applied to the joint half 13, the engaging claw 20, the elastic members 17 and 18, and the retaining projection 1.
6. The rotating shaft 10V is transmitted through the joint half 12.

At this time, if the rotating shaft 10 and the rotating shaft 11 are eccentric by the eccentricity amount α, the elastic members 17 and 18 are moved inward and outward in the radial direction.
Since the elastic members are divided, the internal stress becomes the same as in the conventional case where the elastic members have an integral structure, which reduces the internal stress and therefore reduces the wear of the elastic members 17 and 18. At the same time, vibration can also be reduced. In addition, in this embodiment, if both elastic members 17 and 18 are made of the same thick groove, the manufacturing process of the elastic members can be reduced.

Next 1. A second example of this investigation is shown in Figures 9 and 101.
I'll explain once I made it to page 1. This embodiment has the structure of the first embodiment, in which the bottom of it+ between the locking protrusion 16 and both inner walls of the engagement groove 15 is maintained in the engagement groove 15 of the joint half body 12.
f: Raised lower than the height of the protrusion 16 to form a pair of locking body parts 21, and the base ends of the plurality of elastic members 17 and 18 are integrally connected to each other by a connecting part 22 with a VC to form an annular shape. The difference is that a notch 24 is formed at the center of each proximal end of the elastic member 17, 18 to engage with the mff rest body portion 21.

In this way, by forming the elastic members 17 and 18 into a one-ring shape, they can be easily attached to the retaining groove 15 without any effort, and the notch 24 is retained in the locking circumferential portion 21 for better retention. Can be held securely.

Next, a third embodiment will be explained with reference to FIG.

In this embodiment, the only difference in the configuration from the first embodiment is that the depth of the engagement groove 15 is made shallower so that each resting protrusion 16 protrudes outside the retaining groove 15. The retaining protrusion 16 of the opposing joint half 12 is inserted into the retaining space 19 between the elastic member 17.18 of each joint half 12 and another circumferentially adjacent resilient member 17.18. The structure is different from that of the embodiment described in (2) in that it is lowered through the angle of 18 degrees.

By doing this, compared to the case of the first embodiment, it is possible to construct the entire seven-stiffness shaft joint by simply using a pair of joint halves 12 having the same configuration.

It should be noted that the present invention is not limited to the above-mentioned embodiments. For example, as shown in FIG. 12, the surfaces of the radially opposing elastic members 17 and 18 may be formed to have a triangular wave cross section and be secured to each other. Alternatively, as shown in FIG. 13, the opposing ends of one elastic member 17 may be made into a triangular wave shape, and the opposing ends of the other elastic member 18 may be made into a planar shape and abut against each other. Both like 17.1
8 may be made into a rectangular wave shape so that the concave portions and protrusions of the two portions correspond to each other and come into contact with each other. ((If one is viewed as a single elastic body, excessive selection of the material of the elastic member 17 and 18 will result in J
It is possible to obtain 'fJJ combination 5 #1 with excellent elastic properties.

Effects As described in detail, the present invention provides an annular retaining groove with the axis center in the center and b on the end face of one of the pair of opposing joint half-holes, A number of retaining protrusions are provided extending in the axial direction at regular intervals from each other, and a pair of bullets are inserted into each retaining protrusion from both the inner and outer sides in the radial direction.
A retaining space formed between a hollow member and a pond elastic member adjacent to the elastic member in the circumferential direction by engaging each other at four parts recessed in the center of all the green members and facing each other. On the other hand, a retaining protrusion is formed protruding in the axial direction from the distal end of the other joint, which is secured to the elastic member with an engaging claw or the same structure as described above, and the pair is lowered together. Even if the m1 rotating shaft is installed eccentrically, it is possible to reduce the internal stress generated within the elastic member, thereby reducing the wear of the elastic member and improving the long life of the elastic member. This has the effect of preventing follow-up movement during shafting.

[Brief explanation of drawings]

Figures 1 and 2 are an exploded view and longitudinal sectional view of the main parts of a conventional example, Figures 3 and 4 are diagrams showing the eccentric state of the flexible shaft joint, and Figure 5 is an exploded view showing the conventional example. - 8th [f'l is an exploded perspective view of the first embodiment of the present invention, a side view of the main part, a sectional view taken along the line X-X shown in FIG. 9 and 10 are a perspective view and a cutaway perspective view of the elastic member of the second embodiment, FIG. 11 is a perspective view of the third embodiment, and 12 to 4 are other views, respectively. It is a l+1111 plane view of the example. Joint half-off 12, 13. Engagement groove 15. Retaining protrusion 16, elastic members 17, 18. Engagement gap 19. Holding nail 20° patent applicant Nabeya Kogyo Co., Ltd. Agent
Patent Attorney On 1) Hiroshi Nobu 1st Figure 3 Figure 4 Figure 5 Reason 7 Figure 9 Figure 1O Figure 11 Figure 13 Toj Figure 12

Claims (1)

[Scope of Claims] l An annular retaining direction centered on the axis is provided in the end face of one of a pair of opposing joint half-rests, and the buttocks are spaced at a constant distance from each other in the retaining groove. A plurality of resting protrusions extending in the axial direction are installed, and a pair of elastic members are engaged with each of the 1F-protrusions from both the inner and outer sides in the radial direction by recesses formed in the medium heating part. the elastic member and another elastic member that is in contact with the elastic member in the circumferential direction. 1. A flexible shaft joint, characterized in that a rest protrusion that is engaged with a member is formed to protrude in the axial direction from the distal end surface of the other joint half-rear, and is fitted therein. 2. The deflection shaft according to claim 1, wherein the pair of elastic members are integrally connected to another circumferentially adjacent elastic member via a connecting portion to form an annular shape. Fittings. 8. Claim 1, characterized in that a locking shoulder is provided between the rest projection and the inner wall of the locking groove, and a notch is provided at the base end of the elastic member to lock with the locking shoulder. Or the flexible shaft coupling described in Section 2. 4. The flexible shaft joint according to any one of claims 1 to 8, characterized in that at least one of the opposing surfaces of the pair of elastic members is provided with irregularities such as a triangular wave shape or a rectangular wave shape in cross section.