JP5157506B2 - Telescopic shaft - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a telescopic shaft for improving the durability of am elastically deformable sleeve inserted into a gap between a male shaft and a female shaft while suppressing an increase in sliding resistance between the male shaft and the female shaft when rotating torque operates, and to provide a steering device having the same. <P>SOLUTION: When rotating torque operates between the female shaft 12A and the male shaft 12B, greater compressive force operates on the radial outside of an inclined sleeve part 712 than on the radial inside. However, the inclined sleeve part 712 has a recessed portion 7123 formed on the radial outside of a groove side contact face 7122 at a gap &delta; between a side face 411 of an axial groove 41 and itself, and so the recessed portion 7123 has no contact with the side face 411 of the axial groove 41 to avoid the operation of bearing pressure on the radial outside of the inclined sleeve part 712. <P>COPYRIGHT: (C)2009,JPO&amp;INPIT

Description

  The present invention relates to a telescopic shaft, in particular, a telescopic shaft capable of transmitting rotational torque and relatively moving in the axial direction, for example, a telescopic shaft such as an intermediate shaft or a steering shaft, and a steering device having a telescopic shaft.

  In the steering device, a telescopic shaft connected to be able to transmit rotational torque and to be relatively movable in the axial direction is incorporated in an intermediate shaft, a steering shaft, or the like. That is, when the universal joint is fastened to the pinion shaft that meshes with the rack shaft of the steering gear, the intermediate shaft needs to have a telescopic function in order to be contracted and then fitted to the pinion shaft and fastened.

  In addition, the steering shaft transmits the steering force of the steering wheel to the wheel, and the position of the steering wheel needs to be adjusted in the axial direction according to the physique and driving posture of the driver. .

  In order to achieve good operability of the steering wheel with such a telescopic shaft, the backlash in the rotational direction between the relatively slidable male shaft and female shaft is small, and the male shaft and female shaft The axial sliding resistance with the shaft needs to be maintained at a predetermined sliding resistance over a long period of time. Such telescopic shafts are disclosed in Patent Document 1 and Patent Document 2.

  The telescopic shaft of Patent Document 1 is a male shaft having a non-circular outer periphery, a female shaft having a non-circular inner periphery, and between the outer periphery of the male shaft and the inner periphery of the female shaft, and integrally formed with the male shaft. It is composed of two wedge pieces that are inserted into a gap between the two sliding bushes and are urged in a direction away from each other by a spring.

  The telescopic shaft of Patent Document 2 is inserted into a male shaft having a non-circular outer periphery, a female shaft having a non-circular inner periphery, and an inclined gap between the outer periphery of the male shaft and the inner periphery of the female shaft. It is composed of a wedge-shaped member that is elastically deformable. The plurality of wedge-shaped members are connected and integrated with each other through a leaf spring and a hinge for applying a preload so as not to be separated from each other. This coupling body is bent into an annular shape and is inserted into a gap between the outer periphery of the male shaft and the inner periphery of the female shaft.

  When the rotational torque is transmitted between the male shaft and the female shaft, the relative displacement in the circumferential direction between the male shaft and the female shaft is the radially outer side. Is larger than the radially inner side.

  Therefore, when the rotational torque is increased, the sliding bush of Patent Document 1 and the wedge-shaped member of Patent Document 2 are compressed by applying a large surface pressure to the outside in the radial direction, and the durability of the sliding bush and the wedge-shaped member is reduced. However, there is a problem that the axial sliding resistance between the male shaft and the female shaft increases.

Japanese Patent Laid-Open No. 5-116633 US Pat. No. 5,460,574

  According to the present invention, an increase in sliding resistance between a male shaft and a female shaft when a rotational torque is applied is small, and an elastically deformable sleeve inserted in a gap between the male shaft and the female shaft is provided. It is an object of the present invention to provide a telescopic shaft with improved durability and a steering device having the telescopic shaft.

The above problem is solved by the following means. That is, the first invention is a male shaft in which a plurality of axial ridges are formed substantially radially from the axial center, and is externally fitted so as to be able to move relative to the axial ridges of the male shaft and transmit rotational torque. And a female shaft in which a plurality of axial grooves having gaps between the axial ridges are formed at the same phase position as the axial ridges, and the axial direction of the male shafts and the axial direction of the female shafts. An elastically deformable sleeve inserted in a gap between the groove, and the sleeve is in contact with the ridge side contact surface that constantly contacts the axial ridge to transmit rotational torque, and the axial groove. A groove-side contact surface that is always in contact and transmits rotational torque, and is formed on the radially outer side of one of the protrusion-side contact surface and the groove-side contact surface, and rotates between the male shaft and the female shaft. When not transmitting and when transmitting rotational torque, Or between the axial grooves to a telescopic shaft which possess a recess gap is formed, the sleeve is formed in the gap between the axial ridges and axial grooves, the spacing It has an inclined sleeve portion inserted in an inclined gap that changes at a predetermined inclination, and the protruding sleeve side contact surface and the groove side contact surface are formed on the inclined sleeve portion. A plurality of partial sleeves having the inclined sleeve portion and arranged in a gap between the axial ridge and the axial groove, formed on the male shaft, and relatively moved in a direction perpendicular to the axial direction of the male shaft. The locking portion for locking the partial sleeve to the male shaft and the inclined sleeve portion from the maximum gap portion side to the minimum gap portion side of the inclined gap is possible and cannot be relatively moved in the axial direction of the male shaft. Energizing to apply preload to the partial sleeve A telescopic shaft, characterized in that with a timber.

A second invention is characterized in that, in the telescopic shaft of the first invention, the concave portion forms a substantially uniform parallel gap between the axial ridge or the axial groove. The telescopic shaft that

Third invention, in the telescopic shaft of the second invention, the recess is to form an inclined gap clearance between the axial projections or axial grooves expands radially outwards It is a telescopic shaft characterized by being.

Fourth invention is a steering device having a telescopic shaft of any one of the from the first to third.

  The telescopic shaft and the steering device of the present invention include an elastically deformable sleeve inserted in a gap between the axial ridge of the male shaft and the axial groove of the female shaft. Either the convex contact surface that always contacts the convex strip and transmits rotational torque, the groove contact surface that always contacts the axial groove and transmits rotational torque, and either the convex strip contact surface or the groove contact surface A recess formed on the outer side in the radial direction and having a gap between the axial ridge or the axial groove when the rotational torque is not transmitted between the male shaft and the female shaft and when the rotational torque is transmitted. have.

Therefore, a rotational torque acts between the female shaft and the male shaft, and even if a larger compressive force acts on the radially outer side of the sleeve than on the radially inner side, the concave portion is not aligned with the axial ridge or the axial groove. Since a gap is formed between them, a large surface pressure does not act on the outer side in the radial direction of the sleeve.
Therefore, the durability of the sleeve is improved, and there is no problem that the sliding resistance in the axial direction between the male shaft and the female shaft increases.

  Hereinafter, Example 1 to Example 2 of the present invention will be described with reference to the drawings.

  FIG. 1 shows the entire steering apparatus according to the first embodiment of the present invention, and is a side view with a part cut, showing an embodiment applied to an electric power steering apparatus having a steering assisting portion. FIG. 2 is a longitudinal sectional view of the main part of FIG.

  FIG. 3 shows a telescopic shaft according to the first embodiment of the present invention, and is a perspective view showing a state before the partial sleeve of the first embodiment is attached to the male shaft and the female shaft is externally fitted. 4 is an AA enlarged cross-sectional view of FIG. 2, showing a state in which the partial sleeve of Example 1 is attached to the male shaft, and the female shaft is externally fitted to the outer periphery of the partial sleeve.

  FIG. 5 is an enlarged cross-sectional view of a portion P in FIG. FIG. 6 shows a single plate spring for applying a preload to the partial sleeve, (1) is a plan view of the single plate spring, and (2) is a view taken in the direction of arrow R in (1).

  As shown in FIGS. 1 to 2, the steering device having the telescopic shaft according to the first embodiment of the present invention includes a steering shaft 12 on which a steering wheel 11 can be mounted on the rear side of the vehicle body (the right side in FIGS. 1 and 2), A steering column 13 inserted through the steering shaft 12, an assist device (steering assisting portion) 20 for applying auxiliary torque to the steering shaft 12, and a vehicle body front side of the steering shaft 12 (left side in FIGS. 1 and 2). And a steering gear 30 connected through a rack / pinion mechanism (not shown).

  The steering shaft 12 is formed by combining an outer shaft (hereinafter referred to as a female shaft) 12A and an inner shaft (hereinafter referred to as a male shaft) 12B so that rotational torque can be transmitted and relative displacement in the axial direction can be achieved.

  That is, as shown in FIGS. 2 to 4, a plurality of axial ridges are formed on the outer periphery of the male shaft 12B on the vehicle body rear side, and a plurality of axial grooves are formed on the inner periphery of the female shaft 12A on the vehicle body front side. Is formed at the same phase position as the axial ridge, and is fitted with a predetermined gap from the axial ridge of the male shaft 12B, so that rotational torque can be transmitted and relative displacement in the axial direction can be achieved. Is engaged. Therefore, the engaging portion of the female shaft 12A and the male shaft 12B can slide relative to each other at the time of collision, so that the overall length can be shortened.

  Further, the cylindrical steering column 13 inserted through the steering shaft 12 combines the outer column 13A and the inner column 13B so that they can be telescopically moved. It has a so-called collapsible structure in which the entire length is shortened while absorbing water.

  The vehicle body front side end portion of the inner column 13B is press-fitted and fixed to the vehicle body rear side end portion of the gear housing 21. Further, the vehicle body front side end portion of the male shaft 12B is passed through the inside of the gear housing 21, and is coupled to the vehicle body rear side end portion of the input shaft 22 of the assist device 20.

  That is, a large diameter shaft portion 121B is formed on the vehicle body front side (left side in FIG. 2) of the male shaft 12B, and a small diameter shaft portion 122B is formed on the vehicle body front side of the large diameter shaft portion 121B. The small-diameter shaft portion 122B is press-fitted and coupled to an inner diameter hole 221 formed on the rear side of the vehicle body (right side in FIG. 2) of the input shaft 22 of the assist device 20, and the axial position of the input shaft 22 and the male shaft 12B. Is fixed.

  The steering column 13 is supported by a support bracket 14 at a middle portion thereof on a part of the vehicle body 18 such as a lower surface of the dashboard. Further, a locking portion (not shown) is provided between the support bracket 14 and the vehicle body 18, and when an impact in a direction toward the front side of the vehicle body is applied to the support bracket 14, the support bracket 14 is locked to the locking bracket 14. It moves away from the vehicle and moves to the front side of the vehicle.

  The upper end portion of the gear housing 21 is also supported on a part of the vehicle body 18. In the case of this embodiment, by providing a tilt mechanism and a telescopic mechanism, the position of the steering wheel 11 in the longitudinal direction of the vehicle body and the height position can be freely adjusted. Such a tilt mechanism and a telescopic mechanism are well known in the art and are not characteristic features of the present invention, and thus detailed description thereof is omitted.

  The output shaft 23 protruding from the end face on the vehicle body front side of the gear housing 21 is connected to the rear end portion of the male intermediate shaft 16 </ b> A of the intermediate shaft 16 via the universal joint 15. Further, the input shaft 31 of the steering gear 30 is connected to the front end portion of the female intermediate shaft 16B of the intermediate shaft 16 via another universal joint 17.

  The male intermediate shaft 16A is coupled to the female intermediate shaft 16B so as to be relatively movable in the axial direction and to transmit rotational torque. A pinion (not shown) is formed at the front end of the input shaft 31. A rack (not shown) meshes with the pinion, and the rotation of the steering wheel 11 moves the tie rod 32 to steer a wheel (not shown).

  As shown in FIG. 2, an input shaft 22 and an output shaft 23 are rotatably supported by bearings 29A, 29B, and 29C on the same axis in the gear housing 21 of the assist device 20, and the input shaft 22 and the output shaft 23 are connected by a torsion bar 24. A worm wheel 25 is attached to the output shaft 23, and a worm 27 is engaged with the worm wheel 25. A case 261 of the electric motor 26 is fixed to the gear housing 21, and a worm 27 is coupled to a rotating shaft (not shown) of the electric motor 26.

  In addition, a torque sensor 28 that detects torsion of the torsion bar 24 is provided around an intermediate portion of the input shaft 22. The torque sensor 28 detects the direction and magnitude of torque applied from the steering wheel 11 to the steering shaft 12. In response to the detection signal, the electric motor 26 is driven, and an auxiliary torque is generated in a predetermined direction in a predetermined direction on the output shaft 23 via a speed reduction mechanism including a worm 27 and a worm wheel 25.

  As shown in FIGS. 2 to 6, the telescopic shaft according to the first embodiment of the present invention is applied to a connecting portion between the female shaft 12 </ b> A and the male shaft 12 </ b> B of the steering shaft 12. The front side (left side in FIG. 2) of the female shaft 12A is externally fitted and connected to the rear side (right side in FIG. 2) of the male shaft 12B.

  As shown in FIG. 4, the female shaft 12A is formed in a hollow cylindrical shape, and axial grooves 41, 41, 41, 41 extend and contract radially from the axis 19 of the female shaft 12A on the inner periphery thereof. Four are formed at regular intervals (90 degree intervals) over the entire length of the stroke. Each axial groove 41 is formed at an angle θ with respect to a center line 191 that passes through the axis 19 and is horizontal to the left and right in FIG. 4 or a center line 192 that passes through the axis 19 and is vertical in FIG. Side surfaces 411 and 411.

  Therefore, the interval between the side surfaces 411 and 411 constituting one axial groove 41 becomes narrower toward the radially outer side. Further, the outer ends in the radial direction of the side surfaces 411 and 411 are smoothly connected to an arc-shaped bottom surface 412 that protrudes outward, and each of the axial grooves 41 has a cross section perpendicular to the axis by the side surfaces 411 and 411 and the bottom surface 412. Is formed in a substantially U-shape.

  Further, the inner ends in the radial direction of the side surfaces 411 and 411 are smoothly connected to the inner ends in the radial direction of the adjacent side surfaces 411 and 411 by an arc-shaped connection surface 414 that protrudes inward.

  Further, on the outer periphery of the large-diameter portion of the male shaft 12B on the vehicle body rear side, axial ridges 51, 51, 51, 51 extend radially from the axis 19 over the entire axial length of the outer periphery of the large-diameter portion. Four are formed at equal intervals (90 degree intervals) at the same phase position as the grooves 41.

  The axial ridge 51 has side surfaces 511 and 511 parallel to the center line 191 horizontal to the left and right or the center line 192 vertical to the top and bottom. Accordingly, the distance between the side surface 511 and the side surface 511 constituting one axial ridge 51 is constant, and is formed in parallel toward the radially outer side.

  The outer ends in the radial direction of the side surfaces 511 and 511 are connected to a center line 192 that is vertically vertical or a linear top surface 512 that is orthogonal to the center line 191 that is horizontal to the left and right. With the top surface 512, each axial ridge 51 is formed in a substantially U-shaped cross section perpendicular to the axis. The radially inner ends of the side surfaces 511 and 511 are connected to the radially inner ends of the adjacent side surfaces 511 and 511 by an arc-shaped connection surface 514 that protrudes outward.

  Therefore, between the side surfaces 511 and 511 of the axial ridge 51 of the male shaft 12B and the side surfaces 411 and 411 of the axial groove 41 of the female shaft 12A, the inclined gap 62 whose distance decreases radially outward. Is formed.

  As shown in FIGS. 4 and 5, four partial sleeves 71 formed of an elastic member are inserted in the gap between the outer periphery of the male shaft 12 </ b> B and the inner periphery of the female shaft 12 </ b> A. In the first embodiment, four partial sleeves 71 of the same component are used by being externally fitted to the outer periphery of the male shaft 12B. The partial sleeve 71 includes two elements, an inclined sleeve portion 712 and a connecting sleeve portion 714. The partial sleeve 71 is arranged symmetrically with respect to the center lines 191 and 192.

  That is, the inclined sleeve portions 712 and 712 are inserted into the inclined gaps 62 and 62, respectively, and arc-shaped connecting sleeve portions 714 are formed on the radially outer ends of the inclined sleeve portions 712 and 712, and the connecting sleeve portion 714 is inserted into the outer arc-shaped gap 64 between the arc-shaped bottom surface 412 and the linear top surface 512 and is connected to the radially outer ends of the adjacent inclined sleeve portions 712 and 712.

  As shown in FIGS. 4 and 5, the inclined sleeve portion 712 has a ridge side contact surface (inner contact surface) 7121 that always contacts the side surface 511 of the axial ridge 51 and a side surface 411 of the axial groove 41. A groove-side contact surface (outer contact surface) 7122 that is always in contact is formed.

  In addition, the inclined sleeve portion 712 is formed with a concave portion 7123 having a gap δ between the side surface 411 of the axial groove 41 and on the radially outer side of the groove side contact surface 7122. The recess 7123 has a parallel gap with a constant gap δ between the side face 411 of the axial groove 41. The recess 7123 is sized so that a clearance is always ensured between the side surface 411 of the axial groove 41 and the inclined sleeve portion 712 when rotational torque is transmitted between the male shaft 12B and the female shaft 12A. Is formed.

  The connecting sleeve portion 714 is formed thinner than the inclined sleeve portion 712. Therefore, as shown in FIG. 3, when the four partial sleeves 71 are fitted on the outer circumference of the male shaft 12B, the connecting sleeve portion 714 is easily elastically deformed, and the sleeve 71 is easily fitted on the outer circumference of the male shaft 12B. can do.

  Further, when the female shaft 12A is fitted on the male shaft 12B on which the partial sleeve 71 is fitted, the connecting sleeve portion 714 is easily elastically deformed, and the inclined sleeve portion 712 is smoothly inserted along the inclined gap 62. It is. Since the partial sleeves 71 are not engaged with the adjacent partial sleeves 71, the adjacent partial sleeves 71 can move relative to each other in a direction (radial direction) perpendicular to the axial direction of the male shaft 12B.

  When the partial sleeve 71 is externally fitted to the outer periphery of the male shaft 12B, a leaf spring 84 as an urging member shown in FIG. 6 is attached to the top surface 512 of the outer periphery of the male shaft 12B and the connecting sleeve portion 714 of the partial sleeve 71. Insert between the inner circumference.

  The leaf spring 84 is formed by corrugating thin spring steel, and the width W2 of the leaf spring 84 is formed narrower than the interval W1 between the side surface 511 and the side surface 511 of the axial ridge 51. Further, the length L2 of the leaf spring 84 is formed slightly shorter than the overall length L1 (see FIG. 3) of the partial sleeve 71 in the axial direction.

  Next, as shown in FIG. 3, it protrudes radially outward at the four top surfaces 512 of the outer periphery of the male shaft 12B and at both end portions in the axial direction of the partial sleeve 71, and has convex portions (locking portions). ) 515 is formed by caulking.

  The convex portions 515 are in contact with both end portions of the four partial sleeves 71 in the axial direction, and the four partial sleeves 71 are fixed so as not to move relative to the male shaft 12B in the axial direction. As another example, the partial sleeve 71 may be fixed to the female shaft 12A so as not to move in the axial direction.

  Subsequently, as shown in FIG. 4, the female shaft 12A is externally fitted to the male shaft 12B on which the four partial sleeves 71 are externally fitted. Then, the groove side contact surface 7122 of the inclined sleeve portion 712 has a predetermined allowance with respect to the side surface 411 of the female shaft 12A, so that the female shaft 12A is externally fitted to the male shaft 12B against the allowance. Then, the inclined sleeve portion 712 (partial sleeve 71) moves inward in the radial direction (radial direction).

  When the inclined sleeve portion 712 moves inward in the radial direction (radial direction), the leaf spring 84 is compressed and inserted between the top surface 512 of the male shaft 12B and the inner periphery of the connecting sleeve portion 714. As a result, each partial sleeve 71 is urged outward in the radial direction (radial direction) by the urging force of the leaf spring 84, and the inclined sleeve portion 712 moves from the maximum gap portion side of the inclined gap 62 to the minimum gap portion side. Is pressed toward. Therefore, there is no backlash between the male shaft 12B and the female shaft 12A, and a predetermined preload is applied between the male shaft 12B and the female shaft 12A.

  When the vehicle body longitudinal direction position of the steering wheel 11 is adjusted in this state, the outer column 13A moves telescopically with respect to the inner column 13B, and the female shaft 12A slides in the axial direction with respect to the male shaft 12B.

  By sliding in the axial direction of the female shaft 12A, the groove-side contact surface 7122 of the inclined sleeve portion 712 slides while always contacting the side surface 411 of the female shaft 12A. Accordingly, the groove-side contact surface 7122 of the inclined sleeve portion 712 is gradually worn by the frictional force at the time of sliding, but the inclined sleeve portion 712 has the inclined sleeve portion 712 in the inclined gap 62 due to the elastic force of the leaf spring 84. Since the urging force in the direction of pressing is constantly acting, rattling does not occur.

  That is, in the first embodiment, the adjacent partial sleeves 71 are relatively movable in a direction (radial direction) orthogonal to the axial direction of the male shaft 12B, and therefore, the elastic force of the leaf spring 84 is all transmitted to the partial sleeve 71. Acts effectively as a preload.

  As a result, even if the groove-side contact surface 7122 of the inclined sleeve portion 712 is worn, the groove-side contact surface 7122 of the inclined sleeve portion 712 is worn away from the maximum gap portion of the inclined gap 62 toward the minimum gap portion. The inclined sleeve portion 712 (partial sleeve 71) is further pressed by the elastic force of the leaf spring 84. Therefore, a predetermined urging force always acts on the inclined sleeve portion 712.

  When there is a temperature change or a humidity change, the partial sleeve 71 formed of synthetic resin causes expansion or contraction. However, in the first embodiment, the adjacent partial sleeves 71 can move relative to each other in the direction (radial direction) orthogonal to the axial direction of the male shaft 12B. It can move, there is no fluctuation of the preload, and the axial sliding resistance between the male shaft 12B and the female shaft 12A is kept constant.

  When the steering wheel 11 is rotated and a wheel (not shown) is steered, rotational torque acts between the female shaft 12A and the male shaft 12B. As shown in FIG. 5, when a rotational torque is applied, the relative displacement amount in the circumferential direction between the male shaft 12B and the female shaft 12A is such that the relative displacement amount β2 on the radially outer side is the relative displacement on the radially inner side. It becomes larger than the amount β1.

  Therefore, a larger compressive force acts on the outer side in the radial direction of the inclined sleeve portion 712 than on the inner side in the radial direction. However, since the inclined sleeve portion 712 is formed with a recess 7123 having a gap δ between the side surface 411 of the axial groove 41 on the radially outer side of the groove-side contact surface 7122, the recess 7123 has an axial groove. 41 does not come into contact with the side surface 411 and a large surface pressure does not act on the radially outer side of the inclined sleeve portion 712.

  Therefore, there is no problem that the durability of the inclined sleeve portion 712 is lowered and the sliding resistance in the axial direction between the male shaft 12B and the female shaft 12A is increased.

  The material of the partial sleeve 71 is preferably molded from natural rubber, synthetic rubber, or a mixture of natural rubber and synthetic rubber. The material of the partial sleeve 71 is a material in which at least one solid lubricant of molybdenum disulfide, graphite, or fluorine compound is contained in natural rubber, synthetic rubber, or a mixture of natural rubber and synthetic rubber. It is preferable to mold by injection molding, and it can be molded by injection molding.

  The material of the partial sleeve 71 is based on at least one polymer material selected from polytetrafluoroethylene, phenol resin, acetal resin, polyimide resin, polyamideimide resin, polyethersulfone resin, and polyphenylene sulfide resin. It is preferable to mold with a material containing at least one solid lubricant of molybdenum sulfide, graphite and fluorine compound, and it can be molded by injection molding.

  The material of the partial sleeve 71 is based on at least one polymer material of polytetrafluoroethylene, phenol resin, acetal resin, polyimide resin, polyamide imide resin, polyether sulfone resin, polyphenylene sulfide resin, and carbon. It is preferable to mold with a material containing at least one of fiber and carbon beads, and it can be molded by injection molding.

  In Example 1, since the adjacent partial sleeves 71 are independent from each other, high dimensional accuracy is not required. Further, since the shape is simple, the partial sleeves 71 are not entangled with each other when being transported, so that handling becomes easy. Furthermore, even if there is a thermal deformation due to a temperature change, the sliding performance is not easily adversely affected.

  Next, a second embodiment of the present invention will be described. FIG. 7 shows a telescopic shaft according to a second embodiment of the present invention, and is a perspective view illustrating a state before the sleeve of the second embodiment is attached to the male shaft and the female shaft is externally fitted. FIG. 8 is an AA enlarged sectional view of FIG. 2, showing a state in which the sleeve of Example 2 is attached to the male shaft, and the female shaft is externally fitted to the outer periphery of the sleeve. FIG. 9 is an enlarged cross-sectional view of a portion Q in FIG. In the following description, only structural portions and operations different from the above embodiment will be described, and redundant description will be omitted. Further, the same parts as those in the above embodiment will be described with the same numbers.

  The second embodiment is a modification of the first embodiment, in which a concave portion having a shape different from that of the first embodiment is formed, and the four partial sleeves 71 are configured by one annular sleeve.

  As shown in FIG. 8, the female shaft 12A and the male shaft 12B of the second embodiment are formed in the same shape as the first embodiment, and the gap between the outer periphery of the male shaft 12B and the female shaft 12A is formed by an elastic member. An annular sleeve 72 is inserted. The sleeve 72 is composed of three elements: an inclined sleeve portion 712, an urging sleeve portion 713, and a connecting sleeve portion 714.

  The inclined sleeve portion 712 is inserted into the inclined gap 62, and the urging sleeve portion 713 is inserted into the inner arcuate gap 63 between the arcuate connection surface 514 and the arcuate connection surface 414. A corrugated connecting sleeve portion 714 is formed at the radially outer end of the inclined sleeve portion 712, and the connecting sleeve portion 714 is an outer circle between the arcuate bottom surface 412 and the arcuate top surface 512. It is inserted in the arc-shaped gap 64 and connected to the radially outer ends of the adjacent inclined sleeve portions 712 and 712.

  As shown in FIGS. 8 and 9, the inclined sleeve portion 712 has a protruding contact side (inner contact surface) 7121 that always contacts the side surface 511 of the axial protruding line 51, and a side surface 411 of the axial groove 41. A groove-side contact surface (outer contact surface) 7122 that is always in contact is formed.

  In addition, the inclined sleeve portion 712 is formed with a concave portion 7124 having a gap δ between the side surface 411 of the axial groove 41 and on the radially outer side of the groove side contact surface 7122. The recess 7124 has an inclined gap between the side face 411 of the axial groove 41 and the gap δ expands radially outward. The concave portion 7124 is sized so that a clearance is always ensured between the side surface 411 of the axial groove 41 and the inclined sleeve portion 712 when rotational torque is transmitted between the male shaft 12B and the female shaft 12A. Is formed.

  The biasing sleeve portion 713 and the connecting sleeve portion 714 are formed thinner than the inclined sleeve portion 712. Therefore, when the sleeve 72 is fitted on the outer periphery of the male shaft 12B, the biasing sleeve portion 713 and the connecting sleeve portion 714 are elastically expanded radially outward, and the sleeve 72 can be easily removed from the outer periphery of the male shaft 12B. Can be fitted.

  The wall thickness of the urging sleeve portion 713 is formed thinner than the distance between the inner arcuate gaps 63 between the arcuate connection surface 514 and the arcuate connection surface 414, and protrudes toward the axis 19 side. It is bent into a shape, elastically deformed, and bent into a wave shape. And the peak of this waveform peak is always in contact with the connection surface 514 of the male shaft 12B. Therefore, the urging sleeve portion 713 is elastically deformed freely within the inner arc-shaped gap 63 and can always apply an urging force to the inclined sleeve portion 712.

  Further, the connecting sleeve portion 714 is thinner than the first embodiment, and is bent to have a wave shape. And the peak of this waveform peak always contacts the top surface 512 of the male shaft 12B, and there is always a gap between the bottom surface 412 of the female shaft 12A. Accordingly, the connecting sleeve portion 714 freely elastically deforms in the outer arcuate gap 64, and the connecting sleeve portion 714 can smoothly elastically deform following the movement of the inclined sleeve portion 712.

  Since the urging sleeve portion 713 is elastically deformed, the urging force in the direction in which the inclined sleeve portion 712 is pressed against the inclined gap 62 is applied to the inclined sleeve portion 712 by the elastic force of the urging sleeve portion 713. Accordingly, there is no backlash between the male shaft 12B and the female shaft 12A, and a predetermined preload is applied between the male shaft 12B and the female shaft 12A.

  Next, as shown in FIGS. 7 and 8, on the outer periphery of the male shaft 12 </ b> B, two top surfaces 512 and 512 (two locations in the vertical direction in FIGS. 7 and 8) having a 180-degree phase difference, and Projecting portions 515 and 515 are formed by caulking at both end portions in the axial direction of the sleeve 72 so as to protrude outward in the radial direction.

  The convex portions 515 and 515 are in contact with both end portions in the axial direction of the sleeve 72, and the sleeve 72 is fixed so as not to move relative to the male shaft 12B in the axial direction. As another example, the sleeve 72 may be fixed to the female shaft 12A so as not to be axially movable.

  Subsequently, as shown in FIG. 8, the female shaft 12A is externally fitted to the male shaft 12B to which the sleeve 72 is externally fitted. Then, the groove side contact surface 7122 of the inclined sleeve portion 712 has a predetermined allowance with respect to the side surface 411 of the female shaft 12A, so that the female shaft 12A is externally fitted to the male shaft 12B against the allowance. Then, the inclined sleeve portion 712 moves to the inner arcuate gap 63 side.

  When the inclined sleeve portion 712 moves to the inner arcuate gap 63 side, the thinly formed biasing sleeve portion 713 is pushed by the inclined sleeve portion 712 and freely elastically deforms within the inner arcuate gap 63.

  Further, the connecting sleeve portion 714 is formed to be bent into a single corrugated shape, and the apex of the corrugated mountain is always in contact with the top surface 512 of the male shaft 12B and is always between the bottom surface 412 of the female shaft 12A. There is a gap. Accordingly, the connecting sleeve portion 714 is elastically deformed freely within the outer arcuate gap 64 so that the inclined sleeve portion 712 moves smoothly toward the inner arcuate gap 63 side.

  Since the urging sleeve portion 713 is elastically deformed, the urging force in the direction in which the inclined sleeve portion 712 is pressed against the inclined gap 62 is applied to the inclined sleeve portion 712 by the elastic force of the urging sleeve portion 713. Accordingly, there is no backlash between the male shaft 12B and the female shaft 12A, and a predetermined preload is applied between the male shaft 12B and the female shaft 12A.

  When the vehicle body longitudinal direction position of the steering wheel 11 is adjusted in this state, the outer column 13A moves telescopically with respect to the inner column 13B, and the female shaft 12A slides in the axial direction with respect to the male shaft 12B.

  By sliding in the axial direction of the female shaft 12A, the groove-side contact surface 7122 of the inclined sleeve portion 712 slides while always contacting the side surface 411 of the female shaft 12A. Therefore, the groove-side contact surface 7122 of the inclined sleeve portion 712 is gradually worn by the frictional force at the time of sliding, but the inclined sleeve portion 712 has the inclined sleeve 62 in the inclined gap 62 due to the elastic force of the biasing sleeve portion 713. Since the urging force in the direction of pressing the portion 712 is always acting, the preload is sustained.

  That is, even if the groove-side contact surface 7122 of the inclined sleeve portion 712 is worn, the groove-side contact surface 7122 of the inclined sleeve portion 712 is worn away from the maximum gap portion below the inclined gap 62 to the minimum gap portion above. Then, the inclined sleeve portion 712 is further pressed by the elastic force of the biasing sleeve portion 713. Therefore, a predetermined urging force always acts on the inclined sleeve portion 712.

  When the steering wheel 11 is rotated and a wheel (not shown) is steered, rotational torque acts between the female shaft 12A and the male shaft 12B. As shown in FIG. 9, when a rotational torque acts, the relative displacement amount in the circumferential direction between the male shaft 12B and the female shaft 12A is relatively larger in the radial direction relative displacement amount β2 than in the radial direction relative displacement amount β2. It becomes larger than the amount β1.

  Therefore, a larger compressive force acts on the outer side in the radial direction of the inclined sleeve portion 712 than on the inner side in the radial direction. However, since the inclined sleeve portion 712 is formed with a recess 7124 having a gap δ between the side surface 411 of the axial groove 41 on the radially outer side of the groove side contact surface 7122, the recess 7124 is formed in the axial groove. 41 does not come into contact with the side surface 411 and a large surface pressure does not act on the radially outer side of the inclined sleeve portion 712.

  Therefore, there is no problem that the durability of the inclined sleeve portion 712 is lowered and the sliding resistance in the axial direction between the male shaft 12B and the female shaft 12A is increased.

  In the above embodiment, the recesses 7123 and 7124 are formed on the outer side in the radial direction of the groove side contact surface 7122. However, the recess may be formed on the outer side in the radial direction of the ridge side contact surface 7121.

  In the above embodiment, the axial groove 41 is formed on the female shaft 12A side and the axial ridge 51 is formed on the male shaft 12B side. However, the axial ridge is formed on the female shaft 12A side, and the male shaft An axial groove may be formed on the 12B side.

  Moreover, in the said Example, although the axial direction groove | channel 41 and the axial direction protruding item | line 51 are formed in four equal intervals, what is necessary is just more than one. Furthermore, in the above-described embodiment, the example in which the present invention is applied to the steering shaft 12 has been described. However, the present invention can be applied to an arbitrary telescopic shaft constituting the steering device such as the intermediate shaft 16.

  Further, in the above embodiment, the shape of the outer peripheral surface of the female shaft 12A having the axial groove may be circular, rectangular, or polygonal, and does not need to be similar to the axial groove of the female shaft 12A.

  Further, in the above embodiment, the convex portion 515 is formed on the inner peripheral surface of the female shaft 12A and on both end portions in the axial direction of the sleeve so as to protrude radially inward, and the sleeve is axially formed with respect to the female shaft 12A. You may fix so that it may not move relatively.

BRIEF DESCRIPTION OF THE DRAWINGS It is the side view which cut off one part and showed the whole steering apparatus of Example 1 of this invention, Comprising: The Example applied to the electric power steering apparatus which has a steering assistance part is shown. It is a longitudinal cross-sectional view of the principal part of FIG. It is a perspective view which shows the expansion-contraction axis | shaft of Example 1 of this invention, attaches the partial sleeve of Example 1 to a male shaft, and shows the state before fitting a female shaft externally. FIG. 3 is an AA enlarged cross-sectional view of FIG. 2, showing a state in which the partial sleeve of Example 1 is attached to the male shaft, and the female shaft is fitted on the outer periphery of the partial sleeve. It is the P section expanded sectional view of FIG. The leaf | plate spring single-piece | unit which provides preload to a partial sleeve is shown, (1) is a top view of a leaf | plate spring single-piece | unit, (2) is R arrow directional view of (1). It is a perspective view which shows the expansion-contraction axis | shaft of Example 2 of this invention, attaches the sleeve of Example 2 to a male shaft, and shows the state before fitting a female shaft. FIG. 3 is an AA enlarged sectional view of FIG. 2, showing a state in which the sleeve of Example 2 is attached to the male shaft, and the female shaft is externally fitted to the outer periphery of the sleeve. It is the Q section expanded sectional view of Drawing 8.

Explanation of symbols

11 Steering wheel 12 Steering shaft 12A Outer shaft (female shaft)
12B Inner shaft (male shaft)
121B Large-diameter shaft portion 122B Small-diameter shaft portion 13 Steering column 13A Outer column 13B Inner column 14 Support bracket 15 Universal joint 16 Intermediate shaft 16A Male intermediate shaft 16B Female intermediate shaft 17 Universal joint 18 Car body 19 Axis 191 and 192 Center line 20 Assist Device 21 Gear housing 22 Input shaft 221 Inner diameter hole 23 Output shaft 24 Torsion bar 25 Worm wheel 26 Electric motor 261 Case 27 Worm 28 Torque sensor 29A, 29B, 29C Bearing 30 Steering gear 31 Input shaft 32 Tie rod 41 Axial groove 411 Side surface 412 Bottom surface 414 Connection surface 51 Axial ridge 511 Side surface 512 Top surface 514 Connection surface 515 Convex portion 62 Inclination gap 63 Inner arcuate gap 64 Outer arcuate gap 71 Sleeve 712 inclined sleeve portion 7121 protruding strip side contact surface (inner contact surface)
7122 Groove side contact surface (outer contact surface)
7123, 7124 Recessed portion 713 Biasing sleeve portion 714 Connection sleeve portion 72 Sleeve 84 Leaf spring

Claims (4)

A male shaft having a plurality of axial ridges formed substantially radially from the axial center;
A plurality of axial directions that are externally fitted so as to be able to move relative to the axial ridges of the male shaft and transmit rotational torque, and have gaps between the axial ridges at the same phase position as the axial ridges. Female shaft with grooves,
An elastically deformable sleeve inserted in the gap between the axial projection of the male shaft and the axial groove of the female shaft;
The sleeve is
A ridge-side contact surface that constantly contacts the axial ridge and transmits rotational torque;
A groove-side contact surface that constantly contacts the axial groove and transmits rotational torque;
The axial ridge is formed on the radially outer side of either the ridge side contact surface or the groove side contact surface, and when the rotational torque is not transmitted between the male shaft and the female shaft and when the rotational torque is transmitted. or between the axial grooves to a telescopic shaft which possess a recess gap is formed,
The sleeve has an inclined sleeve portion that is formed in a gap between the axial ridge and the axial groove and is inserted in an inclined gap whose interval changes with a predetermined inclination. The ridge side contact surface and the groove side contact surface are formed,
Furthermore, this telescopic shaft
A partial sleeve having the inclined sleeve portion and disposed in a plurality of gaps between the axial ridge and the axial groove;
A locking portion that is formed on the male shaft, is relatively movable in a direction perpendicular to the axial direction of the male shaft, and is non-movable relative to the axial direction of the male shaft;
A telescopic shaft, comprising: an urging member that urges the inclined sleeve portion from the maximum gap portion side to the minimum gap portion side of the inclined gap to apply a preload to the partial sleeve . The telescopic shaft according to claim 1 ,
The recess is
A telescopic shaft, wherein the gap between the axial ridge or the axial groove forms a substantially constant parallel gap. In the telescopic shaft according to claim 2 ,
The recess is
A telescopic shaft, wherein the gap between the axial ridge or the axial groove forms an inclined gap that expands radially outward. A steering apparatus having the telescopic shaft according to any one of claims 1 to 3 .

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