JP5227204B2 - Electric power steering device - Google Patents

Description

  The present invention relates to an electric power steering apparatus.

  In an electric power steering device, a pinion shaft connected to a steering shaft via a torsion bar is pivotally supported by a gear housing, and a rack shaft that meshes with the pinion shaft is supported by the gear housing so as to be linearly movable. A worm gear coupled to the gear housing is pivotally supported by the gear housing, and a worm wheel fixed to the intermediate portion of the pinion shaft and meshing with the worm gear is pivotally supported by the gear housing. The electric motor applies a steering assist torque corresponding to the steering torque applied by the driver to the steering shaft to the rack shaft through the engagement of the worm gear and the worm wheel and the engagement of the pinion shaft and the rack shaft.

  In such an electric power steering device, the distance between the worm gear and the worm wheel can be easily set without being affected by dimensional errors of parts such as the worm gear at the time of assembly, and the mesh between the worm gear and the worm wheel after assembly. It is required that no abnormal noise occurs.

  In the electric power steering device described in Patent Document 1, a ring body and a bearing case are interposed between the outer periphery of the bearing that supports the tip shaft of the worm gear and the gear housing, and the inner periphery of the bearing case and the outer periphery of the ring body are Are in contact via an inclined surface. A disc spring and an adjustment screw are provided outside the worm gear in the axial direction, and the disc spring pressed by the adjustment screw is brought into contact with one end surface of the outer ring of the bearing integrated with the ring body. During or after assembly of the electric power steering device, the bearing and the ring body are pressed in the axial direction by the spring force of the disc spring, and the bearing is moved along the inclined surface of the bearing case, so that the worm gear is directed toward the worm wheel. They are biased to adjust their inter-axis distances and thus remove their backlash.

JP2001-10512

The electric power steering device described in Patent Document 1 has the following problems.
(1) As a backlash adjusting means, a ring body and a bearing case are provided on the outer peripheral side of the worm gear bearing, and a disc spring and an adjusting screw are provided on the outer side in the axial direction of the worm gear bearing. Therefore, even if it is possible to eliminate the noise at the time of meshing by eliminating backlash between the worm gear and the worm wheel, the meshing friction (friction resistance accompanying meshing) of both is increased.

  (2) The outward size increases in both the radial direction and the axial direction around the bearing of the worm gear, and the electric power steering device becomes large.

  (3) Since the disc spring is provided outside the worm gear bearing in the axial direction, the installation space for the disc spring is reduced when trying to suppress the increase in the size of the electric power steering device, and the design flexibility of the disc spring is reduced. Becomes lower.

  (4) Since the adjusting screw for pressurizing the disc spring is screwed into the gear housing and is accompanied by a screw portion, the assembly of the electric power steering device is poor.

  An object of the present invention is to prevent an abnormal noise while preventing an increase in friction due to meshing of a worm gear and a worm wheel in an electric power steering device, and to improve the downsizing, the degree of freedom of design, and the assembling property of the electric power steering device. It is in.

  According to the first aspect of the present invention, the worm gear connected to the drive shaft of the electric motor is pivotally supported on the gear housing, and the worm wheel fixed to the intermediate portion of the steering shaft and meshed with the worm gear is pivotally supported on the gear housing. In the power steering device, the base end shaft on the electric motor side in the worm gear is supported by a reference bearing fixed to the gear housing, and the tip shaft on the opposite side to the electric motor in the worm gear is a tip bearing fixed to the gear housing. The collar is supported via a collar, the collar is slidably inserted in the axial direction with respect to the tip bearing, and urges the collar toward the opposite side of the worm gear between the support surface provided at the intermediate portion of the worm gear. The elastic body is pre-compressed and the collar is provided with an enlarged inner periphery that expands toward the opposite side of the worm gear. The tip end of the shaft of the worm gear is configured to be supported by the enlarged inner diameter portion of the collar, and when the motor is not rotating, the entire circumference of the tip of the worm gear tip shaft is set to the entire circumference of the enlarged diameter inner diameter portion of the collar. The central axis of the worm gear is set to a neutral position coaxial with the central axis of the collar, and is separated from the central axis of the worm wheel by the rotational contact pressure between the tooth surface of the worm gear and the tooth surface of the worm wheel when the motor rotates. The tip of the tip shaft of the worm gear to be supported is supported by a part in the circumferential direction of the enlarged diameter inner diameter portion of the collar urged by the elastic body.

  According to a second aspect of the present invention, in the first aspect of the present invention, the reference bearing further supports the central shaft of the worm gear so as to be swingable.

(Claim 1)
(a) The tip of the tip shaft of the worm gear is supported by the radially inner diameter portion of the collar. At this time, the collar is urged toward the opposite side to the worm gear by the elastic body.

  When the motor (worm gear) is not rotating, the entire circumference of the tip of the tip shaft of the worm gear is seated on the entire circumference of the enlarged diameter inner diameter portion of the collar so that the center axis of the worm gear is in a neutral position coaxial with the center axis of the collar Set. At this time, the central axes of the worm gear and the collar are coaxial, and the worm gear and the worm wheel are set to have moderate backlash (the backlash is zero or constant backlash) (FIG. 7A). The collar is urged toward the opposite side of the worm gear by the elastic body, and the distance between the worm gear and the worm wheel is A1 (FIGS. 3 and 4).

  On the other hand, when the motor (worm gear) rotates, the tip of the tip shaft of the worm gear that is separated from the central shaft of the worm wheel by the rotational contact pressure between the tooth surface of the worm gear and the tooth surface of the worm wheel is urged by an elastic body. Is supported by a part in the circumferential direction of the expanded inner diameter portion. At this time, the tip of the tip shaft of the worm gear operates to push the collar out of the bearing against the urging force of the elastic body, and the worm gear is biased to the side opposite to the worm wheel (FIG. 7B). Thereby, when the worm gear and the worm wheel mesh with each other due to the rotation of the motor, the collision between the tooth surfaces increases the distance A2 between the shafts (the worm gear is released from the worm wheel) (backlash increases). ) To reduce noise caused by collision between the two. Further, by increasing the distance between the shafts of the worm gear and the worm wheel, it is possible to prevent an increase in the friction when they are engaged (FIGS. 5 and 6).

  (b) The collar and elastic body constituting the friction and noise prevention means are provided inside the tip bearing in both the radial direction and the axial direction of the tip bearing for the tip shaft of the worm gear. Therefore, the outer size of the electric power steering device does not increase in both the radial direction and the axial direction around the tip bearing for the worm gear, and the electric power steering device can be downsized.

  (c) An elastic body that urges the collar toward the opposite side of the worm gear is interposed between the collar and a support surface provided at an intermediate portion of the worm gear. Accordingly, the elastic body is provided on the inner side in the axial direction of the tip bearing for the worm gear, and the elastic body is provided between the collar and the support surface provided at the intermediate portion of the worm gear while reducing the size of the electric power steering device. It can be installed in a wide range of empty space between them, and the degree of freedom in designing the elastic body is increased.

  (d) Since the components of the friction and noise prevention means are the collar and the elastic body and are not accompanied by the threaded portion, the assemblability of the electric power steering apparatus can be improved.

  (e) The collar and elastic body, which are components of the friction and noise prevention means, are assembled between the bulging tip on the tip side of the worm gear and the support surface in the middle portion of the worm gear at the stage of assembly into the electric power steering device. It is pre-arranged to be sandwiched between them. Therefore, the friction and noise prevention means can be completed by inserting the collar into the inner ring of the tip bearing in a state where the collar and the elastic body are stably pre-assembled to the worm gear as described above. Can be improved.

(Claim 2)
(f) A reference bearing that supports the base end shaft of the worm gear supports the central shaft of the worm gear so as to be swingable. Therefore, the worm gear can be swung around the reference bearing and biased toward the worm wheel by the pressurizing force by which the radially inner diameter portion of the collar presses the worm gear toward the worm wheel.

FIG. 1 is a front view of the electric power steering apparatus with a part broken away. FIG. 2 is a sectional view taken along line II-II in FIG. FIG. 3 is a cross-sectional view showing a neutral state of the worm gear along the line III-III in FIG. FIG. 4 is an enlarged cross-sectional view of the main part of FIG. FIG. 5 is a sectional view showing a biased state of the worm gear. FIG. 6 is an enlarged cross-sectional view of the main part of FIG. 7A and 7B show the state of supporting the worm gear by the collar, FIG. 7A is a sectional view showing a neutral state, and FIG. 7B is a sectional view showing a biased state.

  As shown in FIGS. 1 and 2, the electric power steering apparatus 10 includes a gear housing 11 fixed to a vehicle body frame or the like by a bracket (not shown). Then, a pinion shaft 14 is coaxially connected to a steering shaft 12 to which a steering wheel is coupled via a torsion bar 13, a pinion 15 is provided on the pinion shaft 14, and a rack provided with a rack 16 A that meshes with the pinion 15. The shaft 16 is supported on the gear housing 11 so as to be movable in the left-right direction. A steering torque detecting device 17 is provided between the steering shaft 12 and the pinion shaft 14. The steering shaft 12 and the pinion shaft 14 are supported by the gear housing 11 via bearings 12A, 14A, and 14B.

  As shown in FIG. 2, the steering torque detection device 17 is provided with two detection coils 17 </ b> A and 17 </ b> B surrounding the cylindrical core 17 </ b> C engaged with the steering shaft 12 and the pinion shaft 14 in the gear housing 11. The core 17C includes a vertical groove 17E that engages with the guide pin 17D of the pinion shaft 14 so as to be movable only in the axial direction, and includes a spiral groove 17G that engages with the slider pin 17F of the steering shaft 12. As a result, the steering torque applied by the driver to the steering wheel is applied to the steering shaft 12, and when a relative displacement in the rotational direction occurs between the steering shaft 12 and the pinion shaft 14 due to the elastic torsional deformation of the torsion bar 13, the steering The displacement in the rotational direction of the shaft 12 and the pinion shaft 14 causes the core 17C to be displaced in the axial direction, and the inductance of the detection coils 17A and 17B due to the magnetic change around the detection coils 17A and 17B due to the displacement of the core 17C. Changes. That is, when the core 17C moves to the steering shaft 12 side, the inductance of the detection coil 17A closer to the core 17C increases, and the inductance of the detection coil 17B farther away from the core 17C decreases. Can be detected.

  As shown in FIG. 2, a rack guide 19 is built in the cylinder portion 18 provided at a portion facing the pinion 15 across one end of the rack shaft 16 in the gear housing 11, and the rack guide 19 (bush 19A) is provided. Is springed to the rack shaft 16 side by a spring 21 supported on the back by a cap 20 attached to the cylinder portion 18, pressing the rack 16 </ b> A of the rack shaft 16 against the pinion 15, and sliding one end of the rack shaft 16. Support freely. The other end side of the rack shaft 16 is supported by the bearing 22. In addition, the left and right tie rods 23A and 23B are connected to the intermediate portion of the rack shaft 16 by connecting bolts 22A and 22B.

  As shown in FIG. 3, a motor case 31 of the electric motor 30 is attached to the gear housing 11. A worm gear 40 is splined to the drive shaft 32 of the electric motor 30, and the worm gear 40 is supported on both ends of the gear housing 11 by bearings 61 and 62 described later. The worm gear 40 meshes with the worm wheel 50, and the worm wheel 50 is fixed to an intermediate portion of the pinion shaft 14 (steering shaft). The electric motor 30 is driven based on the steering torque detected by the steering torque detection device 17, and the torque generated by the electric motor 30 is generated through the engagement between the worm gear 40 and the worm wheel 50 and the engagement between the pinion 15 and the rack 16 </ b> A. A steering assist torque is applied to the rack shaft 16 and assists the steering torque applied to the steering shaft 12 by the driver.

  However, the electric power steering apparatus 10 supports the worm gear 40 with respect to the gear housing 11 as shown in FIGS. 4 and 5, and includes the friction and noise preventing means 60 for the worm gear 40 and the worm hole 50 as follows. .

  A base end shaft 41 protruding from the electric motor 30 side of the worm gear 40 is supported by a reference bearing 61 fixed to the gear housing 11. The reference bearing 61 is composed of, for example, a ball bearing, and the outer ring is fitted into a hole provided in the gear housing 11, and one end surface of the outer ring is supported against and supported by a stepped surface provided on one side of the hole, and screwed to the other side of the hole. The other end surface of the outer ring is pressed and supported by the attached nut 61A. The base end shaft 41 of the worm gear 40 is inserted into the inner ring of the reference bearing 61, the flange portion 41 </ b> F provided near the worm gear 40 of the base end shaft 41 is abutted against and supported by one end surface of the inner ring, and the electric motor of the base end shaft 41 is supported. The other end surface of the inner ring is pressed and supported by a nut 61B screwed toward 30. The base end shaft 41 of the worm gear 40 may be fastened to the inner ring of the reference bearing 61 by press fitting or caulking. In this way, the base end shaft 41 of the worm gear 40 is fixed to the inner ring of the reference bearing 61, and the front end 41 </ b> A of the base end shaft 41 is spline connected to the drive shaft 32 of the electric motor 30. The axial load acting on the worm gear 40 is supported by the reference bearing 61.

  The reference bearing 61 is composed of, for example, an angular ball bearing, and supports the central axis (base end shaft 41 and a distal end shaft 42 described later) of the worm gear 40 so as to be swingable with respect to the gear housing 11.

  A distal end shaft 42 (coaxial with the proximal end shaft 41) protruding from the worm gear 40 on the opposite side to the electric motor 30 is supported via a collar 70 by a distal end bearing 62 fixed to the gear housing 11. The support center 62C of the tip bearing 62 (same as the center axis 70C of the collar 70) is coaxially arranged with the support center 61C of the reference bearing 61. The tip bearing 62 is made of a ball bearing, for example, and is press-fitted and fixed in a hole provided in the gear housing 11 with an outer ring.

  The collar 70 is inserted so as to be slidable in the axial direction with respect to the inner circumference of the inner ring of the tip bearing 62 (the collar 70 does not rotate relative to the inner ring of the tip bearing 60), and from the inner ring of the tip bearing 62 to the worm gear 40 side. The collar 70 is urged toward the opposite side of the worm gear 40 between a flange portion 71 provided on the side projecting from the flange portion and a flange-like support surface 43 provided at an intermediate portion near the tip shaft 42 of the worm gear 40. The elastic body 80 is inserted in a pre-compressed state. As shown in FIG. 7, the elastic body 80 is formed by adhering and sandwiching an annular rubber 83 (a disc spring or the like) between two annular steel plates 81 and 82. The elastic body 80 is installed around the tip shaft 42 of the worm gear 40 between the flange portion 71 of the collar 70 and the support surface 43 of the worm gear 40. The steel plate 81 and the steel plate 82 of the elastic body 80 are slightly slid in the rotation direction with respect to the flange portion 71 of the collar 70 and the support surface 43 of the worm gear 40.

  The collar 70 is inserted into the tip bearing 62 and is tapered (R-shaped) whose diameter is increased toward the opposite side to the worm gear 40 in an assembled state in which the elastic body 80 can be biased toward the opposite side to the worm gear 40. However, the bulging tip 42A of the tip shaft 42 of the worm gear 40 incorporated in the gear housing 11 is pressed against and supported by the diameter increasing inner diameter portion 72A of the collar 70. The tip 42A of the tip shaft 42 of the worm gear 40 is supported so as to be slidable in the axial direction with respect to the enlarged diameter inner diameter portion 72A of the collar 70, and is generally rolled (with slight sliding) in the rotational direction. Supported.

  Note that the tip 42A of the tip shaft 42 of the worm gear 40 includes an R-shaped or tapered chamfered portion 42B supported by the diameter-enlarged inner diameter portion 72A of the collar 70. Further, the tip 42A of the tip shaft 42 of the worm gear 40 is supported by the enlarged diameter inner diameter portion 72A of the collar 70 through the grease G.

  The collar 70 includes a straight inner diameter portion 72B connected to the small diameter end of the enlarged inner diameter portion 72A on the flange portion 71 side.

  The backlash adjustment operation of the worm gear 40 and the worm wheel 50 by the friction and noise prevention means 60 is as follows.

  The distal end 42A of the distal end shaft 42 of the worm gear 40 is supported by the expanded inner diameter portion 72A of the collar 70. At this time, the collar 70 is urged toward the opposite side to the worm gear 40 by the elastic body 80.

  When the motor 30 (worm gear 40) is not rotating, the entire circumference of the tip 42A of the tip shaft 42 of the worm gear 40 is seated on the entire circumference of the enlarged inner diameter portion 72A of the collar 70, and the central axis of the worm gear 40 is the collar 70. Set to a neutral position that is coaxial with the center axis. At this time, the central axes of the worm gear 40 and the collar 70 are coaxial, and the worm gear 40 and the worm wheel 50 are set to have moderate backlash (the backlash is zero or constant backlash) (FIG. 7A). ). The collar 70 is urged toward the opposite side of the worm gear 40 by the elastic body 80, and the distance between the worm gear 40 and the worm wheel 50 is A1 (FIGS. 3 and 4).

  On the other hand, when the motor 30 (worm gear 40) rotates, the tip 42A of the tip shaft 42 of the worm gear 40 that is separated from the central axis of the worm wheel 50 by the rotational contact pressure between the tooth surface of the worm gear 40 and the tooth surface of the worm wheel 50 is elastic. The collar 70 urged by the body 80 is supported by a part in the circumferential direction of the enlarged diameter inner diameter portion 72A. At this time, the tip 42A of the tip shaft 42 of the worm gear 40 operates to push the collar 70 out of the bearing 62 against the urging force of the elastic body 80, and the worm gear 40 is biased to the opposite side of the worm wheel 50 ( FIG. 7 (B)). Thereby, when the worm gear 40 and the worm wheel 50 are engaged with each other by the rotation of the motor 30, the collision between the tooth surfaces is increased by the distance A2 between the axes (the worm gear 40 is released from the worm wheel 50) ( Backlash increases), and noise due to collision between the two can be reduced. Further, by increasing the distance between the shafts of the worm gear 40 and the worm wheel 50, it is possible to prevent an increase in the friction when they are engaged (FIGS. 5 and 6).

According to the present embodiment, the following operational effects can be obtained.
(i) The collar 70 and the elastic body 80 constituting the friction and noise prevention means 60 are disposed inside the tip bearing 62 in both the radial direction and the axial direction of the tip bearing 62 for the tip shaft 42 of the worm gear 40. Provided. Therefore, the outer size of the electric power steering device 10 does not increase in both the radial direction and the axial direction around the tip bearing 62 for the worm gear 40, and the electric power steering device 10 can be downsized. .

  (ii) An elastic body 80 that urges the collar 70 toward the opposite side of the worm gear 40 is interposed between the collar 70 and a support surface 43 provided at an intermediate portion of the worm gear 40. Accordingly, the elastic body 80 is provided inside the tip bearing 62 for the worm gear 40 in the axial direction, and the elastic body 80 is arranged between the collar 70 and the intermediate portion of the worm gear 40 while reducing the size of the electric power steering apparatus 10. It can install in the wide range of the empty space between the support surfaces 43 provided in, and the freedom degree of design of the elastic body 80 becomes high.

  (iii) Since the components of the friction and noise prevention means 60 are the collar 70 and the elastic body 80 and are not accompanied by a thread portion, the assemblability of the electric power steering apparatus 10 can be improved.

  (iv) The collar 70 and the elastic body 80 which are components of the friction and noise preventing means 60 are assembled to the electric power steering apparatus 10 at the stage of assembly of the worm gear 40 and the bulged tip 42A of the worm gear 40. It is pre-assembled so that it may be pinched | interposed between the support surfaces 43 of an intermediate part. Accordingly, the friction and noise prevention means 60 can be assembled by inserting the collar 70 into the inner ring of the tip bearing 62 in a state where the collar 70 and the elastic body 80 are stably pre-assembled to the worm gear 40 as described above. The assemblability of the electric power steering device 10 can be improved.

  (v) A reference bearing 61 that supports the base end shaft 41 of the worm gear 40 supports the central shaft of the worm gear 40 so as to be swingable. Therefore, the worm gear 40 can be swung around the reference bearing 61 and biased toward the worm wheel by the pressure applied by the enlarged inner diameter portion 72A of the collar 70 to press the worm gear 40 toward the worm wheel. .

  (vi) The tip of the tip shaft 42 of the worm gear 40 is provided with an R-shaped or tapered chamfered portion that is supported by the enlarged diameter inner diameter portion 72A of the collar 70. Therefore, the tip end of the tip shaft 42 of the worm gear 40 can be stably supported by the enlarged diameter inner diameter portion 72 </ b> A of the collar 70.

  (vii) The tip of the tip shaft 42 of the worm gear 40 is supported by the enlarged diameter inner diameter portion 72A of the collar 70 through the grease G. Therefore, sliding friction in which the tip of the tip shaft 42 of the worm gear 40 is supported by the enlarged diameter inner diameter portion 72A of the collar 70 can be reduced and stably supported.

  The embodiment of the present invention has been described in detail with reference to the drawings. However, the specific configuration of the present invention is not limited to this embodiment, and even if there is a design change or the like without departing from the gist of the present invention. It is included in the present invention.

  According to the present invention, in the electric power steering device, noise can be prevented while preventing an increase in friction due to the engagement between the worm gear and the worm wheel, and the electric power steering device can be reduced in size, freedom of design, and assembling. .

10 Electric power steering device 11 Gear housing 14 Pinion shaft (steering shaft)
30 Electric motor 32 Drive shaft 40 Worm gear 41 Base end shaft 42 Front end shaft 42A Front end 42B Chamfered portion 43 Support surface 50 Worm wheel 61 Reference bearing 62 Front end bearing 70 Collar 71 Flange portion 72A Expanded inner diameter portion 80 Elastic body

Claims (2)

In an electric power steering device in which a worm gear connected to a drive shaft of an electric motor is pivotally supported on a gear housing, and a worm wheel fixed to an intermediate portion of the steering shaft and meshed with the worm gear is pivotally supported on the gear housing.
The base shaft on the electric motor side of the worm gear is supported by a reference bearing fixed to the gear housing,
The tip shaft on the opposite side to the electric motor in the worm gear is supported via a collar on the tip bearing fixed to the gear housing,
The collar is inserted so as to be slidable in the axial direction with respect to the tip bearing, and an elastic body that urges the collar toward the opposite side of the worm gear is pre-compressed between the collar and the support surface provided at the intermediate portion of the worm gear. Intervening,
The collar has an enlarged inner periphery that expands toward the opposite side of the worm gear, and is configured to support the tip of the tip shaft of the worm gear on the enlarged inner diameter portion of the collar,
When the motor is not rotating, the entire circumference of the tip end of the tip shaft of the worm gear is seated on the entire circumference of the enlarged inner diameter portion of the collar, and the center axis of the worm gear is set to a neutral position coaxial with the center axis of the collar,
When the motor rotates, the diameter of the collar's expanded diameter is urged by the elastic body at the tip of the tip of the worm gear that is separated from the center axis of the worm wheel by the rotational contact pressure between the tooth surface of the worm gear and the tooth surface of the worm wheel. An electric power steering device characterized in that the electric power steering device is supported by a part of the circumferential direction of the portion.   The electric power steering apparatus according to claim 1, wherein the reference bearing supports the central shaft of the worm gear so as to be swingable.

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