JPH07224852A - Slipper metal type universal coupling device - Google Patents

Abstract

PURPOSE:To prevent the generation of a thrust force exerted on a work roll in linkage with rotation of a spindle. CONSTITUTION:Recessed parts 65a and 65b positioned in the slide surfaces of the nipping pieces 50a and 50b of a slipper metal 51 and closer to the base end part of a fork end part 48 are formed in the fork end part 48 of a coupling 49 on the roll side fixed to the other end part 43 of a work roll 45. Since the nipping pieces 50a and 50b are not moved over the recessed parts 65a and 65b to the base end side of the form end part 48, a stepped surface is not in danger of being generated even when the two surfaces of the fork end part 48 are worn. Thus, the stepped surface is not pressed by the stepped pieces 50a and 50b, and a thrust force is prevented from being generated.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a slipper metal type universal joint device which can be suitably implemented for connecting a rotating body such as a work roll of a rolling mill to a spindle.

[0002]

2. Description of the Related Art FIG. 10 is a simplified front view showing a typical prior art. As an example of a power transmission mechanism in which a conventional slipper metal type universal joint device is used, a rolling mill 1
Will be described. The rolling mill 1 includes a pair of upper and lower work rolls 3 supported by backup rolls (not shown).
a, 3b, and the axis 4 of each work roll 3a, 3b
Both ends 5a, 6a in the a, 4b direction; 5b, 6b are pivotally supported by the housing 7. Each one end 5a, 5b of each work roll 3a, 3b has a plate-shaped end plate 9 called a clamp fixed to the housing 7 by a clamp bolt 8.
The other end 6 in the direction of each axis 4a, 4b indicated by arrow A
It is configured so as to prevent displacement from a, 6b to the one end 5a, 5b side.

The other ends 6a and 6b are connected to two spindles 11a and 11b via slipper metal type universal joint devices 10a and 10b, respectively. The axes 13a and 13b of the spindles 11a and 11b are inclined at angles α and β in the direction intersecting the axes 4a and 4b of the work rolls 3a and 3b. These spindles 11a and 11b are rotationally driven in opposite directions to each other by electric motors around the respective axial lines 13a and 13b, and the rotational forces of these spindles 11a and 11b are the slipper metal type universal joint devices 10a and 1b.
It is configured so that the metal strip transmitted to each work roll 3a, 3b through 0b and passed between each work roll 3a, 3b can be rolled at a stripping speed of, for example, 30 to 100 m / min. There is.

FIG. 11 is an exploded perspective view of the slipper metal type universal joint device 10a shown in FIG. The slipper metal type universal joint device 10a described above basically includes a roll-side coupling 14 coaxially fixed to the other end 6a of the work roll 3a and one end 15 of the spindle 11a arranged on the work roll 3a side. And a roll side coupling 14 and a slipper metal 17 that are fitted and engaged with the spindle side coupling 16, respectively.

The roll-side coupling 14 has a fork end portion 28, and a notch 18 is formed in the fork end portion 28 to form two fork end portions 19, 2.
0 is formed. The slipper metal 17 includes a pair of sandwiching pieces 23 connected by an intermediate pin 21 having a right cylindrical shape.
a and 23b, and sliding protrusions 24a and 24b integrally formed with the sandwiching pieces 23a and 23b.

The spindle side coupling 16 includes
A fitting groove 25 into which the slipper metal 17 is relatively slidably fitted is formed, and with the slipper metal 17 fitted into the fitting groove 25, the slipper metal 17
And the spindle side coupling 16 are the work roll 3
a and an arrow B around a substantially vertical axis 26 in a plane including the axes 4a and 13a of the spindle 11a.
The shaft lines 4a, 1 are rotatable in the directions B1, B2.
An axis 27 that is substantially perpendicular to a plane including 3a and 17a.
It is rotatably connected around arrow C1 and C2 directions.

By such a slipper metal type universal joint device 10a, the rotational force from the spindle 11a forming an angle α with the axis 4a of the work roll 3a can be transmitted.

A spindle 11 is attached to the work roll 3b below.
The other slipper metal type universal joint device 10b that transmits the rotational force from b has the same configuration as the above slipper metal type universal joint device 10a.

[0009]

SUMMARY OF THE INVENTION In the above-mentioned prior art,
The slipper metal type universal joint devices 10a and 10b are shown in FIG.
Roll side coupling 1 as shown enlarged in 2
Since the holding pieces 23a and 23b of the slipper metal 17 slide on the fork end portion 28 of FIG.
Each sliding surface 29 on both sides in the thickness direction of 8 (vertical direction in FIG. 12)
As a and 29b are worn, the thickness of the fork end portion 28 decreases from T1 to T2. Further, as shown in FIG. 13, every time the axis 4a, 4b of each work roll 3a, 3b and each axis 13a, 13b of each spindle 11a, 11b form an angle α or β and rotate 180 degrees. , The sandwiching pieces 23a, 23b are angularly displaced about the axis 26, and the respective sliding surfaces 29a, 29b near the wear end 34 near the base end portion 30 have a non-wearing surface of thickness T1. Three
Stepped surfaces 33a and 33b are formed so as to be curved and continuous with 1a and 31b.

As a result of the actual measurement of the wear state of the fork end portion 28 by the inventor of the present invention, as shown in FIG. 14, the fork end portion 28 is located outward in the radial direction as indicated by arrows D1 and D2. As the amount of wear increases,
It was confirmed that each sliding surface 29a, 29b was unevenly worn thinly toward the outer side, as shown by the phantom line in FIG.

Such uneven wear occurs because, as shown in FIG. 13, the sliding distance between the sandwiching pieces 23a and 23b with the axis 26 as the center of angular displacement is such that the sandwiching pieces 23a and 23b.
As shown by the arrows D1 and D2 in the drawing, the gripping pieces 23a become longer as they are closer to both ends in the longitudinal direction, and the rotational torque from the spindle-side coupling 16 is closer to both ends in the radial direction of the fork end portion 28 as a surface pressure. , 23b
This is because it works from. It has been confirmed that such uneven wear of the fork end portion 28 also causes uneven wear of the other slipper metal type universal joint device 10b with a similar tendency although the amount of wear is different.

Further, the inventor of the present invention has found that each sandwiching piece 23 is rotated according to the rotation of each slipper metal type universal joint device 10a, 10b.
It was discovered that a and 23b press the step surfaces 33a and 33b in the directions of the axes 4a and 4b. Due to such pressing force, a thrust force acts on the work rolls 3a, 3b in the direction of the axes 4a, 4b, and as a result, the work rolls 3a, 3b
The end plate 9 fixed to the housing 7 of the rolling mill 1 by the crank bolt 8 is pressed so that the 3b is not pulled out, and the end plate 9 is cracked and the crank bolt 8 is broken. When such a crack in the end plate 9 and a breakage in the crank bolt 8 occur, the work rolls 3a and 3b may be pulled out, which causes a problem that stable operation of the equipment cannot be performed. Even if the work rolls 3a and 3b are not pulled out of the housing, the work rolls 3a and 3b are largely displaced in the directions of the axes 4a and 4b, so that the stability of the product shape accuracy is deteriorated. There is a problem that it ends up.

Therefore, an object of the present invention is to eliminate the action of thrust force on a rotating body such as a work roll and improve the stability of equipment operation and the stability of product shape accuracy. Is to provide.

[0014]

DISCLOSURE OF THE INVENTION According to the present invention, a rotating body which is prevented from being displaced from the other end portion in the axial direction to the one end portion side and which is rotatably supported around the axis line, intersects the axis line of the rotating body. A rotary body side cup having a spindle driven to rotate about an axis line and a flat convex fork end portion which is coaxially fixed to the other end portion in the axial direction of the rotary body and extends along a plane including the axis line of the rotary body. A ring, a pair of holding pieces for holding the fork end portion of the rotating body side coupling from both sides in the thickness direction thereof, and a slipper metal engaged with the fork end portion in a state in which the rotation is restrained; and a rotating body of the spindle. Is coaxially fixed to one end in the axial direction of the side connected to the, and the slipper metal is angularly displaceable around the axis perpendicular to the axis of the rotating body and the rotating body side coupling while the rotation is restricted. A spindle-side coupling having a yoke end portion that engages closely with the fork-end portion of the rotating-body-side coupling, closer to the base end portion than the wear end on the sliding surface on which each holding piece slides. The slipper metal type universal joint device is characterized in that a recess is formed.

Further, the present invention is characterized in that the recess is formed deeper within a wear control value of the sliding surface as it goes radially outward in a fork end portion of the rotor side coupling.

[0016]

According to the present invention, the rotating body is prevented from being displaced from the other end portion in the axial direction toward the one end portion side, and is supported rotatably around the axis line in this state. Also, the spindle
It is driven to rotate about an axis intersecting the axis of the rotating body. In order to connect such a rotating body and the spindle, a rotating body side coupling, a slipper metal, and a spindle side coupling are provided.

The rotating body side coupling is coaxially fixed to the other end portion in the axial direction of the rotating body, and has a flat convex fork end portion extending along a plane including the axis line of the rotating body. The slipper metal has a pair of holding pieces for holding the fork end portion of the rotating body side coupling from both sides in the thickness direction thereof, and engages with the fork end portion in a state where rotation is restricted. The spindle-side coupling is coaxially fixed to one end of the spindle in the axial direction on the side connected to the rotating body, and the slipper metal is embedded and engaged. In this state, with respect to the slipper metal engaged with the fork end portion of the rotating body side coupling in a state where the rotation is restrained, the rotation is restrained and an angle is generated around the axis perpendicular to the axis of the rotating body and the rotor side coupling. It is displaceable, so that the rotational force can be transmitted by forming an inclined axis line that intersects the axis lines of the rotating body and the rotating body side coupling.

A recess is formed in the fork end portion of the rotary body side coupling, and the recess is formed closer to the base end portion than the wear end on the sliding surface on which the holding pieces slide.
By forming the recess in such a range, it is possible to prevent the stepped surface from being formed in the fork end portion so as to be continuous with the sliding surface on which the holding pieces slide. As a result, the step surface is pressed by each sandwiching piece that slides on the sliding surface, and there is no risk that thrust force along the axial direction acts on the rotating body. Therefore, the displacement of the rotating body in the pressing direction and the rotating body are prevented. It is possible to prevent breakage of a member that receives a force in the axial direction.

Further, according to the present invention, the recess is formed deeper within the wear control value of the sliding surface as it goes outward in the radial direction of the fork end portion. Therefore, the place where the wear amount is large is deep, and the place where the wear amount is small is shallow to form a recess, and it is possible to prevent the thickness of the fork end portion from being unnecessarily thinned by forming the recess, It is possible to reduce the decrease in strength of the fork end portion.

[0020]

1 is a side view showing a slipper metal type universal joint device 40 according to an embodiment of the present invention. The slipper metal type universal joint device 40 of the present embodiment basically has the axis 4
A work roll 45, which is a rotating body that is prevented from displacing in the arrow E direction from the other end 43 in one direction to the one end 44 side, and is rotatably supported around the axis 41, and an axis 41 of the work roll 45. A spindle 47 that is driven to rotate about an axis 46 that intersects with the axis 46 of the work roll 45.
1. A roll-side coupling 49 coaxially fixed to the other end portion 43 in the direction, having a flat convex fork end portion 48 extending along a plane perpendicular to FIG. 1 including the axis 41 of the work roll 45; The fork end portion 48 of the coupling 49 has a pair of holding pieces 50a and 50b for holding the fork end portion 48 from both sides in the thickness direction (vertical direction in FIG. 1), and the slipper metal 51 that engages with the fork end portion 48 and the spindle 47. Axis 4 on the side connected to the work roll 45 of
Coaxially fixed to one end 53 in 6 directions, slipper metal 5
1 includes a spindle side coupling 55 having a yoke end portion 54 which is fitted and engaged.

The work roll 45, the spindle 47,
The roll side coupling 49, the slipper metal 51 and the spindle side coupling 55 are made of cast steel or forged steel. The axis 41 of the work roll 45 and the axis 46 of the spindle 47 intersect at an angle α1 within one plane including the axes 41 and 46, and the angle θ1 is, for example, 3 ° 25′6 ″. is there.

FIG. 2 is a plan view of the roll side coupling 49 shown in FIG. Roll side coupling 49
Is a base 56 having a right cylindrical outer peripheral surface, and the base 5
6 and the fork end portion 48 described above. The fork end portion 48 is formed over the entire length of the base portion 56 in the diametrical line direction (vertical direction in FIG. 2) along a plane including the axis 41, and forms a part of a semicircle that is continuous with the fork end portion 48 of the base portion 56. The two end faces 57, 58 are shown in FIG.
1 is a curved surface that is concave toward the work roll 45 side in the plane shape shown in FIG. 1 and is inclined toward the work roll 45 side by the angle α1 as it goes outward in the radial direction in the side surface shape shown in FIG. Has been done. By forming such end faces 57 and 58, it is possible to prevent the outer peripheral portion 59 of the spindle side coupling 55 from coming into contact with the roll side coupling 49.

The fork end portion 48 has a notch 60.
Two fork portions 61 and 63 are formed by the axial line 41 on both sides in the thickness direction of each fork portion 61 and 63.
A semi-conical recess 64a extending along an axis perpendicular to the
64b; 65a and 65b are formed respectively. These recesses 64a, 64b; 65a, 65b are formed so as to widen as they move away from the axis 41, and each of the sandwiching pieces 50a, 50b corresponding to the angle α1 of the slipper metal 51.
When the rocker swings, the sandwiching pieces 50a and 50b move into the recesses 6 respectively.
4a, 64b; 65a, 65b beyond each end face 57, 5
It is formed over a predetermined range so as not to be displaced toward 8.

FIG. 3 shows a slipper metal type universal joint device 4
It is an exploded perspective view of 0. The recesses 64a, 64b; 65
The a and 65b will be described in more detail. The fork end portion 48 of the roll-side coupling 49 has the holding piece 5 of the slipper metal 51 as shown by the phantom line in FIG.
By sliding 0a, 50b, each fork part 61, 63
Wears so that the thickness T4 on the side of the inner side of the sheet is smaller than the thickness T3 on the inner side. The reason is that as the spindle 47 rotates, the slipper metal 51 moves around the axis 66 with an arrow F.
This is because, as the holding pieces 50a, 50b are swung in the F1 and F2 directions and are closer to both ends in the longitudinal direction of the sandwiching pieces 50a, 50b, the pressing force due to the movement amount and the rotating torque increases. Therefore, FIG.
Surfaces 67a, 67b after wear indicated by phantom lines of
Reference characters a and 68b are sliding surfaces of the holding pieces 50a and 50b.

The wear ends 70a, 70b; 71a, 71b of the sliding surfaces 67a, 67b; 68a, 68b, which are closest to the base end 69 of the fork end portion 48, are displaced by the sandwiching pieces 50a, 50b of the slipper metal 51. It can be assumed from the position. These wear ends 70a, 70b; 71a, 71
The recesses 64a, 64b; 65 closer to the base end 69 than b
a and 65b are formed. As a result, there is no possibility that a step surface is formed between the sliding surfaces 67a, 67b; 68a, 68b after wear and the remaining surface 73 of the base end portion 69, so that each of the sandwiching pieces 50a, 50b becomes a step surface. It will not abut and be pressed.

In the slipper metal 51, the pair of sandwiching pieces 50a, 50b are connected in parallel by an intermediate pin 74, and a sliding protrusion is formed at a portion of each sandwiching piece 50a, 50b to which the intermediate pin 74 is connected. 75a and 75b are integrally formed. The respective first sliding surfaces 76a, 76b of the respective sliding protrusions 75a, 75b have the first sliding surfaces 76a, 76b forming part of a right cylindrical surface. In addition, each sandwiching piece 50a, 50b
Is a second sliding surface 77a, 77 forming a part of a straight cylindrical surface having a diameter smaller than that of the first sliding surface 76a, 76b of the sliding protrusion.
b; 78a and 78b are formed. The intermediate pin 74 has a right cylindrical shape, and has a notch 60 in the fork end portion 48.
Inside, it is fitted rotatably around the axis 66 in the directions of arrow F1 and F2.

The spindle side coupling 55 has a connecting portion 79 to which one end portion 53 of the spindle 47 is connected,
The yoke end portion 54 has a larger diameter than the connecting portion 79. The yoke end portion 54 has sliding protrusions 75a, 75
The first guide surface 8 on which the first sliding surfaces 76a and 76b of b slide.
1a, 81b and second guide surfaces 83a, 83b; 84a, 84b on which the second sliding surfaces 77a, 77b; 78a, 78b of the sandwiching pieces 50a, 50b slide are formed.

One guide surface 81a, 83a, 84a and the other guide surface 81b, 83b, 84b opposite thereto.
A fitting hole 86 into which the slipper metal 51 is fitted and engaged is formed between and. When the slipper metal 51 is fitted in the fitting hole 86, the slipper metal 51 is rotatable around its axis 87 in the arrow G1 and G2 directions. Therefore, the fork portion 61, between the pair of holding pieces 50a, 50b,
The slipper metal 51 and the fork end portion 48 are inserted into the fitting hole 86 with the intermediate pin 63 fitted in the notch 60, and the axis line 46 is the axis line of the work roll 45. The rotation torque from the spindle 47 inclined with respect to 41 can be reliably transmitted. Moreover, even if the fork end portion 48 wears due to long-term use, it is possible to reliably prevent the thrust force from acting on the work roll 45 via the roll-side coupling 49.

FIG. 4 shows a slipper metal type universal joint device 4
It is a front view which shows the quadruple rolling mill 91 provided with 0. The rolling mill 91 has a pair of work rolls 45a and 45b and a pair of backup rolls 93a and 93b that respectively support the work rolls 45a and 45b. These rolls 45a and 45b; 93a and 93b are the housing 94.
Is axially supported at both ends in the axial direction. Each work roll 4
Spindle 47 for transmitting rotational driving force to 5a and 45b
a and 47b are slipper metal type universal joint devices 40a,
They are connected by 40b.

The axis 46a of the upper spindle 47a is
As described above, the work roll 45a is inclined upward at an angle α1 with respect to the axis 41a. Further, the axis line 46b of the lower spindle 47b is connected to the work roll 45b.
Is inclined downward at an angle β1 with respect to the axis 41b. This angle β1 is selected to be 1 ° 42'10 ", for example.

These spindles 47a and 47b are provided with
Rotational driving force from a motor (not shown) is transmitted, and they are rotationally driven in mutually opposite directions. The subscripts a and b added to the reference numerals may be omitted when they are collectively referred to.

FIG. 5 is a simplified sectional view taken along the section line VV of FIG. The shaft end of the work roll 45 is held by the chocks 95a and 95b.
The chock 95a on the fourth side is supported by a support member 96, the peripheral edge of the support member 96 is pressed by two end plates 97, and each end plate 97 is tightened by a clamp bolt 98 to be fixed to the housing 94. . With such a configuration, the work roll 45 is prevented from being displaced in the arrow E direction.

The inventor of the present invention confirms how much the thrust force of the work roll 45 in the arrow E direction is reduced by forming the recesses 64a, 64b; 65a, 65b in the fork end portion 54. The experiment was conducted as follows. That is, as shown in FIG. 6, a pair of washers 9 are attached to the portions of the clamp bolts 98 inserted into the housing 94 in a state where they are retained, and projecting from the end plates 97.
A pressure detecting element 100 called a right-cylindrical load cell sandwiched by 9 is mounted, a nut 101 is tightened, and the end plate 97 is attached to the housing 94 under the situation as shown in FIG.
Fixed to. A strain gauge was electrically connected to the pressure detecting element 100, and a steel strip having a thickness of 2.3 mm and a width of 1040 mm was passed between the work rolls 45a and 45b five times. The indicated value of the strain gauge at the time of the fifth strip passing is shown in FIG. In the figure, the line L10 indicates the above-described recesses 64a, 64b; 65 in the fork end portion 48.
shows changes in thrust force when a and 65b are formed,
Line L20 shows the change in thrust force when the recesses are not formed. As is clear from such a graph, the recesses 64a and 64b are formed in the fork end portion 48;
It was confirmed that the thrust force acting on the clamp bolt 98 was reduced to about half by forming 65a and 65b.

The depth of each of the recesses 64a, 64b; 65a, 65b from the surface of the fork end portion 48 before wear is up to the wear control value.

A method of determining the wear control value will be described below.
When the rolling torque is measured, as shown in FIG. 8, the peak torque Tp immediately after the start of rolling shows a larger value than the steady torque Ts during rolling. The ratio TAF = Tp / Ts between the peak torque Tp and the steady torque Ts increases as the wear (hereinafter referred to as the spindle gap) of the rotary twisting portion of the entire spindle that transmits the rotary torque increases, as shown in FIG. . It is a well-known fact that this tendency exists.

Therefore, even if there is no change in the steady torque Ts, if the spindle gap becomes large, the peak torque Tp immediately after the start of rolling becomes large and exceeds the permissible transmission torque, leading to the destruction of drive system components. From the above relationship, it was confirmed that the wear control value should be 10 mm or less based on the strength calculation based on the rolling torque of the rolling mill and the material strength fore end part dimension and shape measured by the inventor.

Therefore, it is necessary to select the allowable wear amount of the fork end portion 48 to be 10 mm or less on both sides, and therefore the maximum depth of each recess 64a, 64b; 65a, 65b is 5 mm. Therefore, the fork end portion 48
Until the maximum wear amount of each sliding surface 67a, 67b; 68a, 68b reaches the maximum depth (= 5 mm).
The rotating torque from the spindle 47 can be smoothly transmitted to the work roll without generating a stepped surface which the 0a and 50b press.

In the above-mentioned embodiment, the work roll provided in the rolling mill is described as the rotating body.
As another embodiment of the present invention, the present invention can be suitably implemented to transmit power to a rotating body such as a tension reel, payoff reel, guide roll, or the like.

In another embodiment of the present invention, the recess 6
4a, 64b; 65a, 65b are not limited to the shape of a semi-conical trapezoid, and may be formed in any shape as long as they have a maximum depth or less. In this case, a shape that causes a corner portion must be avoided because the strength of the fork end portion is extremely reduced due to stress concentration. Therefore, the shape of the inner surface of each recess is preferably curved with a gentle curve in its cross section.

[0040]

As described above, according to the present invention, the formation of the stepped surface at the fork end portion can be eliminated by forming the recess in the fork end portion. As a result, the step surfaces are pressed by the sandwiching pieces that slide on the sliding surface, and there is no risk that thrust force along the axial direction will act on the rotating body. Therefore, the displacement of the rotating body in the pressing direction and the rotating body are prevented. It is possible to prevent the damage of the member receiving the force from the axial direction.

Further, according to the present invention, the recess is formed deeper toward the outer side in the radial direction of the fork end portion and further deeper within the wear control value of the sliding surface.
Therefore, it is possible to prevent the thickness of the fork end portion from being made thinner than necessary due to the formation of the recess, and it is possible to minimize the reduction in strength due to the formation of the recess in the fork end portion.

[Brief description of drawings]

FIG. 1 is a side view showing a slipper metal type universal joint device 40 of one embodiment of the present invention.

FIG. 2 is a plan view of a roll side coupling 49. FIG.

3 is an exploded perspective view of a slipper metal type universal joint device 40. FIG.

4 includes a slipper metal type universal joint device 40, FIG.
It is a front view of the heavy rolling mill 91.

5 is a simplified cross-sectional view taken along the section line VV of FIG.

FIG. 6 shows a clamp bolt 98 in an experiment conducted by the present inventor.
It is an expanded sectional view showing the state where load cell 100 was attached to.

FIG. 7 is a graph showing a change in thrust force, which is an experimental result of the present inventor.

FIG. 8 is a graph showing changes in rolling torque.

FIG. 9 is a graph showing the relationship between TEF value and spindle gap.

FIG. 10 is a simplified front view showing a typical prior art.

FIG. 11 Prior art slipper metal type universal joint device 1
It is an exploded perspective view showing 0a.

FIG. 12 is a diagram for explaining the principle of wear of the fork end portion 28.

FIG. 13 is a diagram for explaining the operation of the slipper metal 17 due to the rotation of the spindle 11.

FIG. 14 is a perspective view showing a worn state due to displacement of the slipper metal 17.

[Explanation of symbols]

 40, 40a, 40b Slipper metal type universal joint device 41, 41a, 41b Work roll axis 43 Work roll other end 44 Work roll one end 45, 45a, 45b Work roll 46, 46a, 46b Spindle axis 47, 47a, 47b Spindle 48 Fork end part 49 Roll side coupling 50a, 50b Clamping piece 51 Slipper metal 54 Yoke end part 55 Spindle side coupling 64a, 64b; 65a, 65b Recess 67a, 67b; 68a, 68b Sliding surface 69 Base parts 70a, 70b; 71a, 71b Wear ends

Claims (2)

[Claims] 1. A rotating body that is prevented from being displaced from the other end in the axial direction toward one end side and is rotatably supported around the axis, and is driven to rotate about an axis intersecting the axis of the rotating body. The spindle, the rotor-side coupling that is coaxially fixed to the other end of the rotor in the axial direction, and has a flat convex fork end that extends along a plane that includes the axis of the rotor, and the rotor-side coupling. It has a pair of clamping pieces that clamp the fork end part from both sides in the thickness direction, and slipper metal that engages with the fork end part in a state in which the rotation is restricted, and the axial direction of the side connected to the rotating body of the spindle. A yoke that is coaxially fixed to one end, and in which slipper metal is engaged and engaged so as to be angularly displaceable around an axis perpendicular to the axis of the rotating body and the rotating body-side coupling while the rotation is restricted. A spindle-side coupling having a winding portion, and a fork end portion of the rotor-side coupling is formed with a recess nearer to a base end portion than a wear end on a sliding surface on which each holding piece slides. Slipper metal type universal joint device characterized by the following. 2. The recess is formed deeper within a wear control value of the sliding surface as it goes radially outward at a fork end portion of the rotor-side coupling. The slipper metal type universal joint device described.