JP2003194087A - Elastic shaft coupling with slider shaft - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an elastic shaft coupling with a slider shaft capable of adjusting the sliding resistant force and capable of perfectly eliminating the generation of looseness in the rotating direction. <P>SOLUTION: This elastic shaft coupling with a slider shaft is provided with a cross shaft 10 pivotally supported by a first yoke and a second yoke, a buffer cylinder 2 fitted in a cylinder part 1a of the first yoke for fixation, an outer shaft 6 inserted into the buffer cylinder for fixation, and an inner shaft 7 inserted into the outer shaft freely to be slid in the axial direction. The inner shaft is provided with diameter expansion adjusting means 6a, 7a, 8 and 9 for freely adjusting the sliding resistant force between the outer shaft. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a stretchable elastic shaft joint with a slider shaft, which is incorporated in a steering device of an automobile and transmits movement of a steering wheel to a steering gear.

[0002]

2. Description of the Related Art Conventionally, there has been a telescopic steering device for an automobile, which is capable of adjusting the axial length of a steering shaft according to the posture and physique of a driver. In such a telescopic steering shaft, an inner shaft connected to a steering wheel via a universal joint or the like is generally fitted with an outer shaft connected to a steering wheel via a universal joint or the like by spline fitting. With this configuration, the length of the steering shaft can be arbitrarily adjusted by sliding the inner shaft in the axial direction with respect to the outer shaft.

In such a telescopic steering shaft, when the outer shaft is spline-fitted to the inner shaft and the shafts are assembled, the sliding resistance generated between the shafts varies depending on the product. Rattling may occur between both shafts. Therefore, in general, the pressing force of the inner shaft with respect to the outer shaft in the radial direction is adjusted to adjust the sliding resistance of both shafts and to prevent looseness of both shafts.

On the other hand, although a mechanism for adjusting the sliding resistance of the inner shaft and the outer shaft is not provided, the bending of the shaft, the sliding in the axial direction, and the absorption of rotational vibration can be achieved with the shortest possible structural length and the minimum number of parts. A steering shaft capable of As an example thereof, an elastic shaft coupling with a slider shaft disclosed in German Patent DE 1905350A1 is shown in FIGS. 17 and 18.

In FIG. 1, the elastic shaft joint (handle shaft cardan joint) 100 comprises handle shaft joint forks 13 and 14, which are hingedly connected to each other via a cross shaft 10. The multifunctional handle shaft section 15 forms part of the handle shaft joint forks 13, 14 of the elastic shaft joint 100. The handle shaft section 15 is a tubular section of the joint forks 13 and 14, and has an elastically rotatable coupling (buffer cylinder) 16 as a vibration absorbing member. The coupling 16 includes a tubular outer bush 3, an inner bush 4 having a smaller diameter, and a tubular elastomer body (elastic body) 5 interposed between the inner and outer bushes 3, 4.
A coupling (shaft portion) 17 that can expand and contract in the axial direction is fitted inside the inner bush 4. The coupling 17 is fitted in the inner bush 4 by lateral press fitting in the axial direction, has an outer shaft 18 having a female serration groove 18a on the inner peripheral surface, and an inner shaft 19 having a male serration groove 19a on the outer peripheral surface. Made of. The outer shaft 18 has a cam flange (projection) 18b at the right end in the figure.
b is engaged with a notch 15a provided on the end face of the handle shaft section 15 on the joint fork 14 side. This is an engagement such that the protrusion 18b does not come into contact with the cutout portion 15a in the circumferential direction and the axial direction during traveling as specified.

In this structure, the operation of the elastomer body (elastic body) 5 allows bending of the handle shaft within the elastic limit, and can absorb the vibration transmitted from the wheels during traveling to some extent.

[0007]

However, in the above-mentioned conventional elastic shaft joint with slider shaft,
Since the fitting of the inner shaft 19 and the outer shaft 18 depends on the manufacturing accuracy of the serration grooves 18a, 19a, and high accuracy is required, there is a problem that the manufacturing is not easy.

Moreover, the outer shaft 18 is internally press-fitted into the inner bush 4 by a lateral press fit. In fact, when the outer shaft 18 is fitted, a force is applied in the radial direction of the outer shaft 18 to form the female serration groove. Since the dimension of 18a changes in the radial direction, it is difficult to fit the inner shaft 19 into the outer shaft 18 with an optimum contact pressure and to obtain an appropriate sliding resistance force. there were.

In this case, each serration groove 18a, 19
It is possible to set a large gap from the beginning in anticipation of the decrease in the gap of a, but in reality it is difficult to set the estimated amount with high accuracy, and if the gap is made too large, there is rattling. If it is too small, the fitting becomes tight and the inner shaft 19 cannot move with respect to the outer shaft 18.

The present invention improves the disadvantages of the above-described conventional example, can easily adjust the sliding resistance force of the inner shaft with respect to the outer shaft, and completely eliminates the play in the rotational direction of the inner shaft. It is an object of the present invention to provide an elastic shaft coupling with a slider shaft that has a simple structure and that can be manufactured.

[0011]

In order to achieve the above object, according to the present invention, a tubular portion, a pair of first arms extending in the axial direction from diametrically opposite ends of one axial end of the tubular portion, each first arm. A first yoke having axial holes formed concentrically with each other at the tip of one arm, and a second yoke having a second arm having substantially the same shape as the first yoke and having the same shape as the first arm. And a cross shaft having four ends rotatably supported in respective shaft holes of the first arm and the second arm, and internally fitted and fixed to the other end of the tubular portion of the first yoke. Cushioning tube having elasticity, a tubular outer shaft fitted and fixed in the cushioning tube, and an inner shaft that is slidably fitted in the outer shaft with a predetermined sliding resistance force in the axial direction. Elastic shaft coupling with slider shaft Oite, the inner shaft, by changing the radial dimensions of the shaft, is characterized in that a freely adjustable diameter expansion adjustment means sliding resistance force between the outer shaft.

In the above construction, after the outer shaft is fitted in and fixed to the buffer cylinder, the inner shaft is inserted into the outer shaft and the radial expansion adjusting means changes the radial size of the inner shaft. Let me
Since the sliding resistance with the outer shaft is arbitrarily adjusted, as described above, even if the diameter of the outer shaft changes when the outer shaft is fitted in and fixed to the cushion cylinder,
The sliding resistance with the inner shaft can be adjusted to an optimum value.

[0013]

DETAILED DESCRIPTION OF THE INVENTION An embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a sectional configuration diagram of an elastic shaft joint with a slider shaft showing a first embodiment of the present invention, FIG.
1 is an exploded view showing a part of the component of the elastic shaft joint with the slider shaft of FIG. 1, FIG. 3 is a cross-sectional view showing the AA cross section of FIG. 1, and FIG. 4 is a cross-sectional view showing the BB cross section of FIG. FIG. 5 is FIG.
6 is a perspective view showing a modified example of the cylindrical yoke of FIG. 1, FIG. 6 is a sectional view showing a modified example of the BB cross section of FIG. 1, FIG. 7 is a perspective view showing another modified example of the cylindrical yoke of FIG. 1, and FIG. 9 is a sectional view showing a modified example of the AA section, FIG. 9 is a sectional view showing another modified example of the BB section of FIG. 1, and FIG. 10 shows a state in which the elastic shaft joint with slider shaft of FIG. 1 is shortened. Sectional view, FIG. 11 is a sectional view of an elastic shaft joint with a slider shaft showing a second embodiment of the present invention, and FIG. 12 is a sectional view of an elastic shaft joint with a slider shaft showing a third embodiment of the present invention. FIG. 13, FIG. 13 is a sectional configuration view of an elastic shaft joint with a slider shaft showing a fourth embodiment of the present invention, FIG. 14 is a sectional view showing a DD cross section of FIG. 13, and FIG. 15 is a fifth section of the present invention. Sectional drawing of an elastic shaft joint with a slider shaft showing an embodiment, 16 the sixth cross-sectional view of a slider shaft with elastic shaft joint showing an embodiment of the present invention,
FIG. 17 is a sectional configuration diagram of an elastic shaft joint with a slider shaft showing a seventh embodiment of the present invention.

In FIGS. 1 and 2, a cylindrical yoke 1 (first yoke) is a cylindrical tubular portion 1a, and a pair of arms 1b extending axially from both diametrically opposite ends of one axial end of the tubular portion 1a. The first arm includes a shaft hole 1c and the like formed concentrically with each other at the tip of each arm 1b. The cross shaft 10 is pivotally supported in the shaft holes 1c of the two arms 1b, and the other end of the cross shaft 10 has an opposing yoke 11 (second
It is rotatably supported by an arm 11a (second arm) of a yoke. The buffer cylinder 2 is fitted inside the other end of the cylinder portion 1a.
It is fixed. This buffer cylinder 2 has a metal outer bush 3 at the outermost peripheral portion, a metal inner bush 4 having a smaller diameter than the outer bush 3 at the innermost peripheral portion, and no gap between the inner and outer bushes 3, 4. The fixed cylindrical elastic member 5
And consists of. The outer shaft 6 is internally fitted and fixed to the inner bush 4 by lateral press fitting. The inner shaft 7 is fitted in the outer shaft 6 in an axially slidable state with an appropriate sliding resistance force. A connecting yoke 12 is fixed to one end of the inner shaft 7.

As shown in FIG. 3, an adjusting hole 6a is provided at a predetermined position of the non-press-fitted portion of the outer shaft 6, and an adjusting screw hole 7a is provided at a position of the inner shaft 7 facing the adjusting hole 6a. Each is provided. As shown in FIG. 1, a U-shaped expansion member 8 capable of expanding the inner diameter of the inner shaft 7 is arranged at a predetermined position of the inner shaft 7. This expansion member 8 has one arm (in the figure,
An adjusting screw 9 is screwed into a screw hole 8a provided in the upper arm portion). The expansion member 8 is arranged at a position where the adjusting screw 9 fits into the adjusting screw hole 7a of the inner shaft 7. However, the adjusting screw hole 7a is a normal hole having no thread. The adjustment hole 6a of the outer shaft 6,
The adjustment screw hole 7a of the inner shaft 7, the adjustment screw 9, and the expansion member 8 constitute a diameter expansion adjustment means.

The outer shaft 6 and the inner shaft 7
It is not easy to align the adjusting screw hole 7a of the inner shaft 7 with the position of the adjusting hole 6a of the outer shaft 6 when fitting the inside. Therefore, although not shown, at least a pair of serration grooves for positioning, for example, a female serration groove on the inner peripheral side of the outer shaft 6,
By forming a male serration groove on the outer peripheral side of the inner shaft 7 and fitting them together, the positions of the adjusting hole 6a and the adjusting screw hole 7a in the rotational direction inevitably coincide with each other, and there is no axial deviation. It is desirable to move the inner shaft 7 arbitrarily so that the holes 6a and 7a are aligned with each other.

On the other hand, the end portion of the outer shaft 6 on the arm 1b side has a T-shaped side surface as shown in FIG. 4, and the end edge thereof projects from both end positions in the diametrical direction toward both end sides thereof. A shaped stopper 6b (locking portion) is formed. As shown in FIG. 5, the stopper 6b is arranged circumferentially and axially with respect to a rectangular open window-shaped notch 1d provided at an end portion between the arms 1b of the tubular portion 1a of the cylindrical yoke 1. When they are not in contact with each other, they are fitted (see FIG. 4) with a gap s in the circumferential direction. In this way, when torque of a predetermined value or less is transmitted between both shafts, torque is transmitted through the buffer cylinder, but when torque of a predetermined value or more acts on one shaft, the stopper 6b is provided with the notch 6b. Direct contact with. The stopper 6b, as shown in FIG.
The protrusion may have a wide shape, and as shown in FIGS. 6 and 7, the notch 1d may have a window shape in which the outer peripheral portion of the cylindrical yoke 1 is closed.

Further, as shown in FIG. 8, the diameter expansion adjusting means may be the adjustment screw 9 alone without providing the expansion member 8. In this case, the adjusting screw hole 7a of the inner shaft 7
Is provided with a screw thread and needs to be screwed with the adjusting screw 9.

Further, as shown in FIG. 9, the outer shaft 26 may have a square outer peripheral portion in its cross-sectional shape, that is, as is well known (Japanese Patent Laid-Open No. 10-89373), that is, its outer peripheral portion is Almost four faces 26 like a cube
It may consist of a. In this case, the inner peripheral surface of the cylindrical portion 1a of the cylindrical yoke 1 has at least one pair of opposing surfaces 1.
The e is disposed so as to closely oppose the two parallel surfaces 26a of the outer shaft 26 at a distance d. With this configuration, the outer shaft 26 has the surfaces 26a forming the outer peripheral portion thereof serving as stoppers.

In the above structure, after the outer shaft 6 is fitted in and fixed to the inner bush 4 of the buffer cylinder 2, the inner shaft 7 is inserted into the outer shaft 6 and the inner shaft 7 is adjusted at the position of the adjusting hole 6a. The position of the inner shaft 7 is adjusted so that the screw holes 7a are aligned. After that, a tool such as a screwdriver is inserted through the adjustment hole 6a of the outer shaft 6, the tip thereof is applied to the head of the adjustment screw 9, and this is rotated.

As a result, the arm portion (upper side in the figure) of the expansion member 8 is pressed against the inner peripheral surface side of the inner shaft 7,
This pressing force expands the inner diameter of the inner shaft 7.
Since the radially expanded inner shaft 7 is pressed against the inner peripheral surface side of the outer shaft 6, the sliding resistance of the inner shaft 7 with respect to the outer shaft 6 increases.

On the other hand, if the adjusting screw 9 is rotated in the reverse direction,
The sliding resistance of the inner shaft 7 with respect to the outer shaft 6 decreases. In this way, the sliding resistance of the inner shaft 7 with respect to the outer shaft 6 is adjusted. If the desired sliding resistance force is obtained by this adjustment, as shown in FIG. 10, the inner shaft 7 is pushed into the outer shaft 6 to obtain the fitting length for actual use. In this case, when the outer shaft 6 is fitted into and fixed to the inner bush 4 and the diameter of the outer shaft 6 is reduced, the diameter of the inner shaft 7 is set to be small in consideration of the reduction amount. The adjustment screw 9 can be tightened to adjust the sliding resistance to a desired value.

Next, a second embodiment will be described with reference to FIG. This embodiment is substantially the same as the first embodiment, and the same members are given the same numbers,
Description of that part is omitted. The difference is that the diameter expansion adjusting means disclosed in Japanese Utility Model Laid-Open No. 2-87116 is adopted.

In the figure, a spline is formed on the outer circumference, a tapered portion 20a is formed at the tip end portion, and the taper portion 20a is formed with an axial threaded hole 20b at the axial center portion. A solid inner shaft 20 is fitted inside the outer shaft 6. An adjusting screw 24 is screwed into the screw hole 20b of the inner shaft 20 via a play preventing collar 23. The play preventing collar 23 has a tapered hole 23a into which the tip of the tapered portion 20a is fitted, and a slit (not shown) formed in the outer peripheral portion in the axial direction.

In this structure, the inner shaft 20 is inserted into the outer shaft 6 after the outer shaft 6 is fitted and fixed to the inner bush 4 of the buffer cylinder 2. Then, using a tightening tool (not shown), adjust screw 2
When 4 is rotated and tightened, the tip of the tapered portion 20a enters into the tapered hole 23a of the backlash preventing collar 23, so that the tapered hole 23a is gradually expanded by the tapered portion 20a. Along with this, the play preventing collar 23 is expanded in the radial direction, and the outer peripheral portion thereof presses the inner peripheral surface of the outer shaft 6, so that the sliding resistance force of the inner shaft 20 with respect to the outer shaft 6 increases. On the other hand, if the adjusting screw 24 is rotated in the reverse direction, the inner shaft 20 with respect to the outer shaft 6
Sliding resistance is reduced. Thereby, it is possible to adjust to a desired sliding resistance force.

Next, a third embodiment will be described with reference to FIG. This embodiment is substantially the same as the second embodiment, and the same members are designated by the same reference numerals,
Description of that part is omitted. The difference is that the diameter expansion adjusting means disclosed in JP-A-11-198824 is adopted.

In the figure, a spline is formed on the outer circumference, a slit 30a is formed at the tip portion, and a female taper screw portion 30b whose diameter increases toward the tip is formed at the end portion of this slit 30a. A solid inner shaft 30 is fitted inside the outer shaft 6.
A conical adjustment screw 34 is screwed into the female taper screw portion 30b of the inner shaft 30.

In this structure, the inner shaft 30 is inserted into the outer shaft 6 after the outer shaft 6 is fitted in and fixed to the inner bush 4 of the buffer cylinder 2. Then, using a tightening tool (not shown), adjust screw 3
When 4 is rotated and screwed in, the adjusting screw 34 expands the female taper screw portion 30b, so that the tip end portion of the inner shaft 30 expands in the radial direction. As a result, the outer peripheral portion of the inner shaft 30 presses the inner peripheral surface of the outer shaft 6, so that the sliding resistance force of the inner shaft 30 with respect to the outer shaft 6 increases.
On the other hand, if the adjusting screw 34 is rotated in the reverse direction, the sliding resistance of the inner shaft 30 with respect to the outer shaft 6 decreases. Thereby, it is possible to adjust to a desired sliding resistance force.

Next, a fourth embodiment will be described with reference to FIGS. 13 and 14. This embodiment is substantially the same as the third embodiment, the same members are designated by the same reference numerals, and the description thereof will be omitted. The difference is that the adjustment cam 41 is adopted.

13 and 14, a spline is formed on the outer circumference, an axial slit 40a is formed at the tip portion, and a tubular inner member in which an adjusting cam 41 is fitted at the end portion of this slit 40a. Shaft 40
Is fitted inside the outer shaft 6. The adjusting cam 41 has a substantially columnar shape, and a hexagonal hole 41a for adjustment is provided at the center of its axis, and its sectional shape is, as shown in FIG. 14, when the adjusting cam 41 is rotated, In the direction in which the slit 40a is expanded in the radial direction, the shape is formed such that there are a portion where the diameter of the cylinder is relatively large and a portion where the diameter is relatively small.

In this structure, the inner shaft 40 is inserted into the outer bush 6 after the outer shaft 6 is fitted in and fixed to the inner bush 4 of the buffer cylinder 2. Then, when the adjusting cam 41 is rotated using a tool (not shown) having a hexagonal prism portion, a portion where the diameter of the cam is relatively large may be located in the direction in which the slit 40a is expanded in the radial direction. is there. At this time, since the slit 40a is pressed in the radial direction by the adjustment cam 41,
The tip portion of the inner shaft 40 expands in the radial direction. As a result, the tip outer peripheral portion of the inner shaft 40 presses the inner peripheral surface of the outer shaft 6, so that the sliding resistance force of the inner shaft 40 with respect to the outer shaft 6 increases. On the other hand, in the direction in which the adjustment cam 41 is rotated and the slit 40a is expanded in the radial direction, the sliding resistance force of the inner shaft 40 with respect to the outer shaft 6 decreases in the portion where the diameter of the cam becomes relatively small. By adjusting the rotation of the adjusting cam 41, it is possible to adjust to a desired sliding resistance force.

Next, a fifth embodiment will be described with reference to FIG. This embodiment is substantially the same as the fourth embodiment, and the same members are designated by the same reference numerals,
Description of that part is omitted. The difference is that a tapered collar 50 is used as the diameter expansion adjusting means.

In the figure, a tubular inner shaft 7 having a spline formed on the outer periphery and a tapered collar 50 fitted at the tip is internally fitted to the outer shaft 6. The tapered collar 50 has a circular cross-section, or a shape having circular arcs only on both circumferential portions in the radial direction, and has a shape that tapers toward the tip.

In this structure, the inner shaft 7 is inserted into the outer shaft 6 after the outer shaft 6 is fitted into and fixed to the inner bush 4 of the buffer cylinder 2. The tip of the tapered collar 50 is attached to the inner shaft 7
When it is fitted in, the diameter of the collar 50 and the inner diameter of the shaft 7 stay in the same place on the way. Further, using a tool (not shown), the rear end portion 5 of the tapered collar 50 is
When the user presses 0a by pushing it lightly, the outer peripheral surface of the collar 50, which abuts the inner periphery of the inner shaft 7 end, presses the inner periphery of the inner shaft 7 end, so that the distal end of the inner shaft 7 moves radially. It is about to be expanded. As a result, the outer periphery of the tip of the inner shaft 7 presses the inner peripheral surface of the outer shaft 6, and the sliding resistance of the inner shaft 7 with respect to the outer shaft 6 increases.

The sixth embodiment will be described with reference to FIG. This embodiment is substantially the same as the fifth embodiment, the same members are designated by the same reference numerals, and the description of those parts will be omitted. The difference is that an elastic body 60 made of metal or the like having elasticity is adopted as the diameter expansion adjusting means.

In the figure, a tubular inner shaft 7 in which splines are formed on the outer periphery and an elastic body 60 is fitted at the tip is fitted inside the outer shaft 6. The elastic body 60 is U-shaped, and its arm portion 60a always has a predetermined biasing force that presses the inner peripheral surface of the inner shaft 7 in the radial direction.

In this structure, after the outer shaft 6 is fitted and fixed to the inner bush 4 of the buffer cylinder 2, the inner shaft 7 with the elastic body 60 fitted therein is press-fitted into the outer shaft 6. At this time, the inner shaft 7
Is elastically deformable, so the inner bushing 4 of the buffer cylinder 2
The diameter of the shaft 7 in the press-fitting part that is fitted inside is
The diameter is slightly smaller than the diameter of the non-press-fitted portion that is deviated from the position of the inner bush 4. If the pressing force of the elastic body 60 is not elastic, when the elastic body 60 is in the press-fitting portion of the inner bush 4 of the buffer cylinder 2, even if the elastic body 60 exerts an appropriate pressing force, When the elastic body 60 is moved from the position of the press-fitting portion to the position of the non-press-fitting portion by sliding 7 in the right direction in the figure, the diameter of the shaft 7 is increased, and therefore the pressing force of the elastic body 60 is sufficient. Instead, the sliding resistance of the inner shaft 7 with respect to the outer shaft 6 may be reduced.

However, since the elastic body 60 can always exert a constant biasing force (pressing force) within the elastic limit, even if the diameter of the inner shaft 7 increases, the elastic force in the radial direction is increased. Accordingly, the required pressing force can be exerted by following this, and the required sliding resistance force of the inner shaft 7 with respect to the outer shaft 6 can be maintained.

The seventh embodiment will be described with reference to FIG. This embodiment is substantially the same as the first and sixth embodiments, the same members are designated by the same reference numerals, and the description of those parts will be omitted. The difference is that the expansion member 8 used in the first embodiment as the diameter expansion adjusting means.
Is adopted, and the diameter r of the non-press-fitted portion of the outer shaft 65 is set to be slightly smaller than the diameter R of the press-fitted portion.

In the figure, a tubular inner shaft 7 having a spline formed on the outer circumference and an expansion member 8 fitted at the tip is internally fitted to the outer shaft 65.
The diameter R of the press-fitting portion of the outer shaft 65 that is internally fitted to the inner bush 4 of the shock absorber cylinder 2 allows for a reduction amount when this diameter R is reduced when it is fitted and fixed to the inner bush 4. The diameter is set to be larger than the diameter r of the non-press-fitted portion deviated from the position of the inner bush 4 by the reduction amount.

In this structure, after the outer shaft 65 is fitted and fixed to the inner bush 4 of the buffer cylinder 2, the inner shaft 7 fitted with the expansion member 8 is inserted into the outer shaft 65, and the first embodiment As described above, a tool is inserted from the adjustment hole 65a of the outer shaft 65 and the adjustment screw 9 is tightened, whereby the pressing pressure of the expansion member 8 in the non-press-fitted portion is appropriately adjusted. As described above, the diameter R of the outer shaft 65 at the press-fitting portion is set to be slightly larger than the diameter r of the non-press-fitting portion deviated from the position of the inner bush 4, so that the inner bushing 4 of the cushioning cylinder 2 is provided.
When the outer shaft 65 is press-fitted into the outer shaft 65, the diameter R at the press-fitting portion of the shaft 65 is compressed and becomes slightly smaller, so that the diameter is eventually equal to the diameter r at the non-press-fitting portion. Therefore, the expansion member 8 can exert an appropriate pressing force even in the press-fitting portion, and can maintain a necessary sliding resistance force of the inner shaft 7 with respect to the outer shaft 6.

[0042]

As described above, according to the present invention,
A buffer cylinder having a tubular elastic member that is axially fitted and fixed to the other end of the cylindrical portion of the first yoke, and a tubular outer shaft that is fitted and fixed to the buffer cylinder. In an elastic shaft joint with a slider shaft, the inner shaft slidably fitted in the outer shaft in the axial direction, and the outer shaft is configured to have a radial size that is different from that of the outer shaft. Since the diameter expansion adjusting means capable of arbitrarily adjusting the sliding resistance force with the shaft is provided, even if the diameter of the outer shaft changes due to fitting, the inner shaft is fitted inside the outer shaft and the outer shaft is adjusted by the diameter expansion adjusting means. Since the sliding resistance force with and can be adjusted arbitrarily, and the play in the rotational direction can be completely removed, the operability is improved. Further, since the outer shaft and the inner shaft can be adjusted after being combined, they can be assembled in a state where the sliding resistance is small, the working efficiency can be improved, and the cost can be reduced. Further, since the contact surface between the outer shaft and the inner shaft can be made into metal contact, heat resistance and durability are improved.

[Brief description of drawings]

FIG. 1 is a cross-sectional configuration diagram of an elastic shaft joint with a slider shaft showing a first embodiment of the present invention.

FIG. 2 is an exploded view showing a part of the component of the elastic shaft coupling with the slider shaft of FIG.

FIG. 3 is a sectional view showing an AA section in FIG.

FIG. 4 is a cross-sectional view showing a BB cross section of FIG.

5 is a perspective view showing the cylindrical yoke of FIG. 1. FIG.

6 is a cross-sectional view showing another embodiment of the BB cross section of FIG.

FIG. 7 is a perspective view showing another embodiment of the cylindrical yoke of FIG.

FIG. 8 is a cross-sectional view showing another embodiment of the AA cross section of FIG.

FIG. 9 is a cross-sectional view showing another embodiment of the BB cross section of FIG. 1;

10 is a cross-sectional configuration diagram showing a state in which the elastic shaft joint with the slider shaft of FIG. 1 is shortened.

FIG. 11 is a cross-sectional configuration diagram of an elastic shaft coupling with a slider shaft showing a second embodiment of the present invention.

FIG. 12 is a cross-sectional configuration diagram of an elastic shaft joint with a slider shaft showing a third embodiment of the present invention.

FIG. 13 is a cross-sectional configuration diagram of an elastic shaft joint with a slider shaft showing a fourth embodiment of the present invention.

FIG. 14 is a cross-sectional view showing a DD cross section of FIG. 13;

FIG. 15 is a cross-sectional configuration diagram of an elastic shaft coupling with a slider shaft showing a fifth embodiment of the present invention.

FIG. 16 is a cross-sectional configuration diagram of an elastic shaft joint with a slider shaft showing a sixth embodiment of the present invention.

FIG. 17 is a cross-sectional configuration diagram of an elastic shaft joint with a slider shaft showing a seventh embodiment of the present invention.

FIG. 18 is a perspective view showing a conventional elastic shaft coupling with a slider shaft.

FIG. 19 is an exploded perspective view showing a conventional elastic shaft coupling with a slider shaft.

[Explanation of symbols]

1 Cylindrical yoke 1 (1st yoke) 1a tube 1b Arm (1st arm) 1c shaft hole 1d notch 2 shock absorber 3 outer bush 4 Inner bush 5 Elastic member 6 Outer shaft 6a Adjustment hole 6b Locking part (stopper) 7 Inner shaft 7a Adjustment screw hole 8 Expansion member 9 Adjustment screw 10 cross axis 11 Opposing yoke (second yoke)

Claims (3)

[Claims] 1. A cylindrical portion, a pair of first arms extending in the axial direction from the diametrically opposite ends of one axial end of the cylindrical portion, and axial holes formed concentrically with each other at the tip of each first arm. A first yoke, a second yoke having a second arm having a shape substantially similar to that of the first yoke and having the same shape as the first arm, and shaft holes of the first arm and the second arm, A cross shaft whose four ends are rotatably supported, an elastic cushioning cylinder internally fitted and fixed to the other end of the cylinder portion of the first yoke, and an internal fitting to the cushioning cylinder. An elastic shaft joint with a slider shaft, comprising: a fixed tubular outer shaft; and an inner shaft that is slidably fitted in the outer shaft in a predetermined sliding resistance force in the axial direction. To the shaft By changing the direction of the size, the outer shaft and a slider shaft with elastic coupling, characterized in that a freely adjustable diameter expansion adjustment means the sliding resistance of the. 2. The buffer cylinder comprises an inner bush made of metal in contact with the outer peripheral surface of the outer shaft and an elastic member fixed to the outer peripheral surface of the inner bush. Elastic shaft coupling with slider shaft. 3. The outer shaft is such that when the inner shaft is fitted / fixed in the inner bush, the diameter of the press-fitting portion is reduced by the amount of the shrinkage of the non-press-fitting portion. The elastic shaft joint with a slider shaft according to claim 1, wherein the elastic shaft joint is set larger than the above.