JP2000161384A - Slippage absorbing clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make a clutch well function by absorbing possible slippage even if a male part and a female part, which constitutes a clutch, are relatively slipped off in position and attitude in a clutch intermitting the transmission of rotational driving force mechanically. SOLUTION: A female part 67 has a spherical recessed part 93 at the center, and includes plural fitting recessed parts around the recessed part. A male part 69 has a spherical projected part 101 at the center portion, and includes a plurality of fitting pawls 103 around the aforesaid projected part. The fitting recessed parts of the female part and the boundary portions 97c of the fitting recessed parts, are formed into a circular arc shape each at their tip ends. And the tip end 103A of each fitting pawl is also formed into a circular arc shape. The dimension in the circumferential direction of the plural fitting recessed parts, is larger than the dimension in the circumferential direction of the plural fitting pawls, and the back lash 105 is formed between both of them. The back lash formed at the base portions of the plural fitting pawls is made larger than that formed at their tip ends. In addition, a horn shaped guide is provided around the female part coming to a standstill when a clutch is intermitted, in a state that it is opened forward.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch for mechanically interrupting the transmission of a rotational driving force, and more particularly to a displacement absorbing mechanism capable of absorbing a relative displacement between a female portion and a male portion constituting a part of the clutch. It relates to the structure of the clutch.

[0002]

2. Description of the Related Art A clutch that mechanically interrupts the transmission of rotational driving force is used in various fields. The example shown in FIGS. 9 and 10 is a swivel table device 1 used for exchanging rolls of a rolling mill.

[0003] In this device 1, a traveling cart 5 is mounted on a turntable 3 which turns in a horizontal plane so as to be able to travel by wheels 7. The rails 9 and 11 on which the wheels 7 run are provided on the turntable 3 and outside the turntable 3. The other rail 11 is provided linearly toward the stand 13 of the rolling mill. On the swivel table 3, a traveling cart 5
A feed screw bar 15 for moving the shaft is disposed so as to be rotatable around an axis. Nut 1 screwed into this feed screw rod 15
7 is fixed to the bottom surface of the traveling vehicle 5.

[0004] On the traveling trolley 5, there is mounted a device called an iscale 21 for attaching the roll 19 to the stand 13 of the rolling mill. Jigs 23 are provided at the front end and the rear end of the scale 21, respectively, and hold the roll 19. A motor 25 for rotating the feed screw bar 15 is fixed to an apparatus base 27 outside the turning table 3 and on the side opposite to the stand 13 of the rolling mill.

That is, the output shaft of the motor 25 is connected to the clutch 31 via the speed reducer 29. This clutch 31 is provided with a key 33 provided on the output shaft of the transmission 29.
And a key groove 35 formed at the end of the feed screw bar 15. The output shaft provided with the key 33 is moved forward and backward by a link mechanism 39 provided with an operation lever 37 toward a key groove 35 formed at an end of the feed screw bar 15. The roll changing operation performed by using the roll changing turning table device 1 will be described with reference to FIG.

First, the scale 2 mounted on the traveling vehicle 3
Out of the two jigs 23 of the rolling mill 1
The jig 23 on the third side is kept empty without holding the roll 19, and the jig 23 on the opposite side to the stand 13 holds a new roll 19 (FIG. 10A).

The operation lever 37 is moved to the left in FIG.
Into the key groove 35 of the feed screw bar 15. Furthermore,
When the motor 25 is driven to rotate the feed screw bar 15, the traveling vehicle 5 moves forward and reaches the stand 13 of the rolling mill through the rail 11 outside the swivel table 3. In this state, the old roll 19 is held by the empty jig 23 (FIG. 2B).

After that, the motor 25 is rotated in the reverse direction, the traveling carriage 5 is moved backward, and returned to the turntable 3 (FIG. 2C). Next, the clutch 31 is disengaged, the turning table 3 is turned, and the positions of the old roll 19 and the new roll 19 are exchanged (FIG. 3D). In this state, the clutch 31 is connected, the motor 25 is rotated forward again to advance the traveling vehicle 5, and the roll 19 is moved to the stand 1 of the rolling mill by the jig 23 of the scale mounted on the traveling vehicle 5.
3 ((F) in the same figure).

The motor 25 is again rotated in the reverse direction,
Is retracted and returned on the swivel table 3 ((G) in the same figure).
In this state, the old roll 19 is removed from the jig 23, and the replacement operation is completed (FIG. 7H). From this state, the jig 23 again holds the new roll 19 and returns to the beginning (FIG. 7A).

[0010]

However, the clutch 31 including the key 33 and the key groove 35 has a condition that there is almost no displacement or displacement between the two 33, 35 on the precondition of use. is there. But clutch 3
When the key 33 is retracted in a state where 1 is cut off, the retreat distance becomes longer, or the installation error or operation error of the device causes
There is a possibility that the key 33 and the key groove 35 of the clutch 31, that is, the male part and the female part may have a relative positional deviation or a positional deviation.

When such a shift occurs, the clutch 31
Did not work well, and it was necessary to redo the installation work of the apparatus, or to use a precise drive mechanism, in this case, a turning mechanism for turning the turning table 33, etc. so as to prevent an operation error. SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and provides a displacement absorbing clutch that can function sufficiently even if a relative displacement occurs between a female portion and a male portion constituting a clutch. The purpose is to:

[0012]

Means for Solving the Problems To solve the above problems, the following invention is provided. According to a first aspect of the present invention, there is provided a clutch that mechanically interrupts transmission of rotational driving force,
A female part which constitutes a part of the clutch, and a male part which constitutes a part of the clutch and can be relatively disengaged and fitted from the female part, wherein the female part is provided at a central part. Having a spherical concave portion, having a plurality of fitting concave portions at equal intervals around the concave portion,
The male portion has a spherical convex portion at a central portion, and has a plurality of fitting claws around the convex portion to be fitted into the fitting concave portion of the female portion at equal intervals, and The displacement absorbing clutch is characterized in that a circumferential dimension is larger than a circumferential dimension of the fitting claw.

A second aspect of the present invention is further characterized in that a difference in circumferential dimension between the fitting concave portion and the fitting claw is larger at a base portion than at a tip end of the fitting claw. It is an absorption clutch.

In a third aspect of the present invention, it is preferable that the boundary between the fitting recess and the fitting recess has an arc-shaped tip, and the fitting claw has an arc-shaped tip. This is a feature of the slip absorbing clutch.

According to a fourth aspect of the present invention, there is further provided a displacement absorbing clutch, wherein the set of the fitting recess and the fitting claw is 3, 4, 5, 6, 7, or 8 sets. is there.

According to a fifth aspect of the present invention, a trumpet-shaped guide is provided around the female portion or the male portion which does not move at the time of detachment / fitting, in a state of opening forward. This is a shift absorption clutch characterized in that:

In a sixth aspect of the present invention, the rotating member provided with the female portion or the male portion, which moves at the time of detachment / fitting, has a relative position in a plane orthogonal to the moving direction. A displacement absorbing clutch including a displacement absorbing mechanism that absorbs displacement and absorbs displacement in the axial direction.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An apparatus using a slip absorbing clutch according to one embodiment of the present invention will be described with reference to FIGS. This device is provided in an opening adjustment mechanism that adjusts the opening of a nozzle that discharges molten steel at an ironworks. That is, for example, in a continuous casting machine of an ironworks, molten steel taken out of a converter is received in a ladle called a ladle 51 (FIG. 2), and the ladle 51 is transported to a funnel-like turn dish installed at a predetermined position. Dispense molten steel.

The nozzle 53 for performing this discharge is the ladle 51
The nozzle 53 is provided with an opening adjusting mechanism 55 for adjusting the opening of the nozzle 53.
By adjusting the opening degree, the upper surface (so-called molten metal level) of the molten steel in the turn dish is made constant, so that impurities such as slug are not sent from the turn dish to the continuous casting machine.

At the bottom of the ladle 51, two plates 5
7, 59, namely the upper plate 57 and the lower plate 59
Are arranged at right angles to the axial direction of the nozzle 53. The upper plate 57 and the lower plate 59 are formed with holes 61 and 63 having substantially the same diameter as the nozzle 53. By moving the lower plate 59, the area where both holes 61 and 63 overlap is adjusted, and thereby the opening of the nozzle 53 is adjusted.

The opening adjusting mechanism 55 shown is of a rotary sliding type in which a driving source transmits a rotational driving force. The opening adjustment mechanism 55 uses a worm wheel and a worm gear. The transmission of the rotational driving force to the worm gear is performed by a clutch 65 that performs mechanical intermittent operation.

The female part 6 constituting a part of the clutch 65
7 is provided on the opening adjustment mechanism 55 side. Further, the male part 69 constituting a part of the clutch 65 is formed in a shape capable of being detached from and fitted to the female part 67, and is provided at the tip of the rotating rod 71. The rotating rod 71 has a biaxial bearing 73
Are supported by the moving mechanism 75 via the. Further, the rotating rod 71 has an extensible structure partially supported by a coil spring. A hydraulic motor 77 as a drive source for rotating the rotating rod 71 can be moved forward and backward by a moving mechanism 75.

As shown in FIG. 2, the moving mechanism 75 is mounted on the apparatus base 79 with the slide base 81 horizontal toward the opening adjustment mechanism 55. On this slide base 81, a slider 83 is moved by a hydraulic cylinder 85.
Thereby, it can move in the forward and backward directions (in the left and right directions in the figure).

For this slider 83, a biaxial bearing 7
The rotating rod 71 is supported via 3. This 2
The axial bearing 73 allows the tip of the rotating rod 71, that is, the position of the male part 69, to be finely adjusted in a plane orthogonal to the direction toward the female part 67. A restriction stopper 87 for restricting the movement of the rotary rod 71 due to the fine adjustment, that is, the swinging movement within a predetermined range, is attached to the slider 83, and surrounds the vicinity of the front part of the rotary rod 71. Next, the clutch 65 will be described in detail.

As shown in FIGS. 1 to 5, the clutch 65
Consists of a female part 67 provided on the side of the opening adjustment mechanism 55 (see FIG. 2) and a male part 69 provided on the tip of the rotating rod 71. That is, the female portion 67 is provided at the other end of the universal joint 64 that transmits the rotational driving force to the worm gear of the opening adjustment mechanism 55. The columnar base 89 of the female part 67 is horizontally rotatably supported by a bearing 91 provided on the bottom surface of the ladle 51. The distal end of the female portion 67 has an enlarged diameter, and has a hemispherical concave portion 93 at the center of the distal end surface, as shown in FIGS.
Extends in the axial direction,

This short cylindrical portion 95 has four fitting recesses 97.
Are formed at equal intervals in the circumferential direction. The fitting concave portion 97 has a substantially mountain shape, and the shape of the mountain-shaped tip portion 97A and both shoulder portions 97B draws a smooth curve when viewed from the radially outer side of the short cylindrical portion 95. The male portion 69 has a cylindrical base 99 fitted into the rotating rod 71. Male part 69
Has a hemispherical convex portion 101 formed at the center of the distal end surface, and a fitting claw 10 is provided around the convex portion 101.
3 The fitting claw 103 fits into the fitting concave portion 97 of the female portion 67 and has a substantially similar mountain shape, but is formed to have a smaller circumferential dimension than the size of the fitting concave portion 97. I have.

Due to this dimensional difference, a backlash 105 is positively formed between the fitting claw 103 and the fitting recess 97, and a later-described displacement is absorbed. Mating claw 1 that forms an angle
The tip portion 103A of 03 is formed separately from a metal having excellent wear resistance, and is attached to the groove formed between the two shoulder portions 103B by the bolt 102. The backlash 105 includes a chevron-shaped tip 103A of the fitting claw 103 and a chevron-shaped tip 97 of the fitting recess 97.
Between A, it is smaller than other parts,
There is a characteristic that the rotational driving force is easily transmitted by these chevron tips 97A and 103A.

The backlash 105 is large at the two shoulder portions 97B and 103B of the chevron, and the male portion 69 absorbs the angular deviation 109 caused by the swing of the rotating rod 71 (see FIG. 3) provided at the tip. It is easier.

The shoulder 97B of the adjacent fitting recess 97
Tip portion 9 which forms a boundary between
7C has a round arc shape, and the distal end portion 103A of the fitting claw 103 also has a round arc shape. A trumpet-like guide 107 extends from a bearing 91 provided on the bottom surface of the ladle 51 so as to cover the female portion 67. Guide 107
Is open in the direction toward the male part 69, that is, forward.

(Operation and Effect of the Embodiment) In the above embodiment, when it is not necessary to adjust the opening of the nozzle 53 by the opening adjusting mechanism 55, the slider 83 of the moving mechanism 75 is used.
Is retracted by the hydraulic cylinder 85 along the slide base 81 and is in the retracted position (see FIG. 2B). Next, when the opening degree needs to be adjusted, the slider 83 moves forward by the hydraulic cylinder 85, and the rotating rod 71 supported by the slider 83 moves the opening degree adjusting mechanism 55 of the nozzle 53 provided on the bottom surface of the ladle 51. Move forward towards.

At this time, if there is an error in the installation position of the ladle 51 or the like, the position of the female portion 67 of the clutch 65 is also shifted. When the forward movement is performed as it is, the clutch 65 provided at the tip of the rotating rod 71 is provided.
The male part 69 contacts the inside of the trumpet-shaped guide 107, is guided to the female part 67 along the trumpet-like shape, and
Contact 7

In this contact, even if the rotating rod 71 is displaced in the rotation direction between the female part 67 and the male part 69, the tip 103A of the fitting claw 103 of the male part 69 is The fitting recess 97 of the portion 67 is guided by the shoulder 97B having a mountain shape, and the fitting between the fitting claw 103 and the fitting recess 97 is reliably performed.

At this time, the shoulders 97 of the adjacent fitting recesses 97
Since the tip portion 97C between B and the shoulder portion 97B has a round shape, and the tip portion 103A of the fitting claw 103 also has a round shape, even when both tips come into contact, the component force of the contact force is obtained. As a result, relative rotation between the male portion 69 and the female portion 67 occurs, and the fitting is performed.

Further, even if the position of the female portion 67 in the axial direction is displaced, the rotating rod 7 on which the male portion 69 is provided
Since a part of 1 has a structure that can be extended and contracted via a coil spring, fitting in the axial direction is performed.
Further, in the connection state of the clutch 65, the spherical concave portion 93 of the female portion 67 and the spherical convex portion 101 of the male portion 69 come into contact with each other, so that point contact is performed and even if there is a slight relative displacement, the contact occurs. No significant friction occurs. Moreover, the spherical recess 93
Thereby, the spherical convex portion 101 is held deeply and firmly.

The fitting recesses 97 and the fitting claws 103 to be fitted have circumferentially larger dimensions in the fitting recesses 97 than the fitting claws 103, and there is a difference. Since 105 is obtained, a certain degree of relative displacement can be positively absorbed. Further, the backlash 105 caused by the difference in the circumferential dimension between the fitting recess 97 and the fitting claw 103 is larger at the base portion than at the tip of the fitting claw 103, so that the female portion 6 is formed.
Even if the relative posture of the male part 7 and the male part 69 is shifted, it can be absorbed.

Further, even if the clutch 65 is connected with a relative displacement between the male portion 69 and the female portion 67, the rotating member is provided with the female portion 67 or the male portion 69. The rotational rod 71 can absorb the relative displacement by a displacement absorbing mechanism, that is, by a telescopic structure or a biaxial bearing 73 supported by a coil spring, and an excessive force is applied to the rotating member. Can be prevented.

(Other Embodiments) The shift absorbing clutch in the above embodiment is provided at a portion for transmitting a rotational driving force to the rotation adjusting mechanism 9 for adjusting the rotation of the nozzle 53 of the ladle 51. However, in other embodiments, the shift absorbing clutch of the present invention can be applied to other devices. In other words, it is necessary to separate the mechanism that operates by the rotational driving force and the driving source that transmits the rotational driving force and retract the driving source, and transmit the rotational driving force only when necessary, or Preferred devices are capable of implementing the present invention.

That is, as shown in FIG. 8, the present invention can also be implemented in the conventional rotary table for exchanging rolls of a rolling mill described with reference to FIGS. As shown in the figure, the female part 67 is provided at the end of the feed screw bar 15, and a trumpet-shaped guide 107 is provided around the female part 67 in a state of opening forward. The configuration on the male portion 69 side, that is, the male portion 69, the rotating rod 71, and the moving mechanism 75 are the same as those in FIG. With this configuration, the male part 6
It is also possible to sufficiently absorb the relative positional deviation and the positional deviation caused by the bending of the rotating rod 71 caused by increasing the retreat distance of the 9 side.

In the above embodiment, a plurality of fitting concave portions 97 are provided around the hemispherical concave portion 93 at equal intervals, and a plurality of fitting claws 103 are provided around the hemispherical convex portion 101 at equal intervals. However, in other embodiments, these relationships can be reversed. That is, the hemispherical recess 9
A plurality of fitting claws 103 can be provided at equal intervals around the periphery 3, and a plurality of fitting recesses 97 can be provided at equal intervals around the hemispherical convex portion 101.

[0040]

As described above, the first, second, third,
According to the invention of 4, 5, or 6, since the spherical concave portion of the female portion and the spherical convex portion of the male portion come into contact with each other in the connected state of the clutch, point contact is performed and slight relative displacement occurs. Even if it does, there is no significant friction due to contact. In addition, the fitting recesses and the fitting claws to be fitted have circumferential dimensions that are larger in the fitting recesses than the fitting claws, and a sufficient backlash is obtained, thereby absorbing a certain degree of relative displacement. it can.

According to the second, third, fourth, fifth or sixth aspect of the present invention, the difference in the circumferential dimension between the fitting concave portion and the fitting claw is larger at the base portion than at the tip of the fitting claw. Thereby, even if the relative displacement between the female part and the male part occurs, it can be absorbed. According to the third, fourth, fifth, or sixth aspect of the present invention, even if the rotational direction in which the rotational driving force is transmitted is shifted between the female part and the male part, the fitting recess and the fitting recess are formed. The arc-shaped tip at the boundary between the two contacts the arc-shaped tip of the fitting claw, and the relative rotation of the male part and the female part occurs due to the component force of the contact force, and the fitting is performed naturally. Therefore, the displacement in the rotation direction is absorbed.

According to the fifth or sixth aspect of the present invention, even if a large displacement occurs between the female part and the male part, the wrapper provided around the female part or the male part. Since the male part or the female part is guided by the shape guide, a large displacement can be absorbed. Further, according to the sixth aspect, even when the clutch is connected while the relative displacement between the male part and the female part is generated, the rotating member provided with the female part or the male part absorbs the deviation. The relative displacement can be absorbed by the mechanism, and an excessive force can be prevented from being applied to the rotating member.

[Brief description of the drawings]

FIG. 1 is an enlarged view of a part I of FIG. 3 showing a main part of a displacement absorbing clutch according to an embodiment of the present invention, and FIG. 1 (A) is an external view showing a state where a female part and a male part are fitted. (B) is a sectional view showing a state where the female part and the male part are separated.

FIGS. 2A and 2B show the entire rotary nozzle device having a displacement absorbing clutch according to this embodiment, in which FIG. 2A shows a state in which the clutch of the rotary nozzle device is connected, and FIG. It is a figure showing the state where the source was evacuated.

FIG. 3 is an enlarged view of a part III in FIG. 2;

4A is a perspective view of a female part in FIG. 1; FIG. 4B is a perspective view of a male part in FIG. 1;

5A is a perspective view showing a state in which the female part and the male part of FIG. 4 are fitted together, and FIG. 5A is a perspective view showing a state in which the male part is tilted due to an angle shift and the backlash is increased. (B) is a perspective view showing a state in which backlash is reduced, contrary to (A).

6 (A) is a front view showing a detailed shape of the female part, and FIG. (D) is a rear view of (A).

7A and 7B show the detailed shape of the male part. FIG. 7A is a side view showing a cross section of a cylindrical base. FIG. 7B is a side view showing a tip part of FIG. (A) is a side external view of (C) viewed obliquely from above by 45 degrees.

FIG. 8 shows another embodiment of the present invention, and is a schematic overall side view showing a state in which a slip absorbing clutch is used for a turning table device for exchanging rolls of a rolling mill.

FIG. 9 is an enlarged side view of a main part of a roll exchange turning table device using a conventional clutch.

10 (A) to 10 (H) show a procedure for exchanging rolls by the apparatus shown in FIG. 9;

[Explanation of symbols]

Reference Signs List 51 ladle 53 nozzle 55 opening adjustment mechanism 65 clutch 67 female part 69 male part 71 rotating rod 73 two-axis bearing 75 moving mechanism 77 hydraulic motor (drive source) 81 slide base 83 slider 85 hydraulic cylinder 93 hemispherical concave part 97 Fitting concave portion 101 Hemispherical convex portion 103 Fitting claw 105 Backlash 107 Bugle-shaped guide

Claims (6)

[Claims] 1. A clutch for mechanically intermittently transmitting a rotational driving force, comprising: a female part forming a part of the clutch; and a female part forming a part of the clutch and being relatively disengaged from the female part. A male portion capable of fitting, the female portion has a spherical concave portion in the center portion, and has a plurality of fitting concave portions or fitting claws at equal intervals around the concave portion, The male part has a spherical convex part in the center part, and is fitted around the convex part with a plurality of fitting claws fitted into the fitting concave part of the female part or with the fitting claw of the female part. A displacement absorbing clutch having a plurality of fitting recesses at equal intervals, wherein a circumferential dimension of the fitting recess is larger than a circumferential dimension of the fitting claw. 2. The displacement absorbing clutch according to claim 1, wherein a difference in a circumferential dimension between the fitting concave portion and the fitting claw is larger at a base portion than at a tip end of the fitting claw. . 3. A boundary between the fitting recess and the fitting recess,
3. The shift absorbing clutch according to claim 1, wherein the tip has an arc shape, and the fitting claw has an arc portion at the tip. 4. The combination of the fitting concave portion and the fitting claw is 3,
4. The clutch according to claim 1, wherein the clutch is a set of 4, 5, 6, 7, or 8 pairs. 5. A trumpet-like guide is provided around the female part or the male part which does not move at the time of disengagement / fitting, in a state of opening forward. Item 5. The displacement absorbing clutch according to Item 1, 2, 3, or 4. 6. The rotating member provided with the female portion or the male portion which moves at the time of detachment / fitting absorbs a relative displacement in a plane orthogonal to a moving direction, and is provided in an axial direction. 6. The displacement absorbing clutch according to claim 1, further comprising a displacement absorbing mechanism for absorbing the positional displacement of the clutch.