WO2012086338A1 - Steering device for vehicle - Google Patents

Steering device for vehicle Download PDF

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Publication number
WO2012086338A1
WO2012086338A1 PCT/JP2011/076189 JP2011076189W WO2012086338A1 WO 2012086338 A1 WO2012086338 A1 WO 2012086338A1 JP 2011076189 W JP2011076189 W JP 2011076189W WO 2012086338 A1 WO2012086338 A1 WO 2012086338A1
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WO
WIPO (PCT)
Prior art keywords
shaft
bearing
inter
steering
bush
Prior art date
Application number
PCT/JP2011/076189
Other languages
French (fr)
Japanese (ja)
Inventor
九郎丸　善和
Original Assignee
株式会社ジェイテクト
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 株式会社ジェイテクト filed Critical 株式会社ジェイテクト
Priority to CN201180061167.3A priority Critical patent/CN103269939B/en
Publication of WO2012086338A1 publication Critical patent/WO2012086338A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
    • B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
    • B62D1/16—Steering columns
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D6/00—Arrangements for automatically controlling steering depending on driving conditions sensed and responded to, e.g. control circuits
    • B62D6/08—Arrangements for automatically controlling steering depending on driving conditions sensed and responded to, e.g. control circuits responsive only to driver input torque
    • B62D6/10—Arrangements for automatically controlling steering depending on driving conditions sensed and responded to, e.g. control circuits responsive only to driver input torque characterised by means for sensing or determining torque

Definitions

  • the present invention relates to a vehicle steering system.
  • a steering shaft is supported using a number of ball bearings.
  • the steering shaft includes an upper shaft, an intermediate shaft rotatably coupled to the lower end of the upper shaft, and a lower shaft rotatably coupled to the intermediate shaft via a torsion bar. It is done.
  • the upper end of the upper shaft is supported by the first ball bearing.
  • An intermediate shaft is supported by the second ball bearing.
  • the lower shaft is supported by the third and fourth ball bearings on both sides of the lower shaft and the worm wheel rotating together with the lower shaft. Further, a bush is disposed at a fitting portion between the intermediate shaft and the lower shaft.
  • the present invention is made in view of the above-mentioned subject, and it aims at providing a steering device for vehicles which can control collapse of an element of a steering shaft inexpensively.
  • the invention according to claim 1 comprises a hollow support member, a steering shaft including an upper shaft and a lower shaft coaxially connected to each other through the support member through a torsion bar;
  • the first shaft-to-shaft bearing includes a portion disposed radially inward of the bearing center of the second ball bearing; Intercluster between the bearing and the second shaft bearing provides a steering apparatus for a vehicle which is remote in the axial direction of the steering shaft.
  • a stopper mechanism for restricting the relative rotation amount of the upper shaft and the lower shaft.
  • the stopper mechanism has the first inter-shaft bearing and the second shaft in the axial direction. It may be disposed between the shaft-to-shaft bearings. Further, as in the invention of claim 3, at least one of the first inter-shaft bearing and the second inter-shaft bearing may include a bush.
  • At least one of the first inter-shaft bearing and the second inter-shaft bearing may include a needle roller bearing.
  • the upper end of the upper shaft is supported by the first ball bearing. Since a portion of the first inter-shaft bearing supporting the lower end of the upper shuttle is disposed at a radially inward position of the second ball bearing supporting the lower shaft, the lower end of the upper shaft is substantially It can be supported by two ball bearings.
  • the second inter-shaft bearing is disposed at a position axially separated from the first inter-shaft bearing, the following advantages can be obtained. That is, when a moment load for tending to lower the lower shaft is generated by a couple of forces with the bearing center of the second ball bearing as a fulcrum, the second upper shaft suppresses the falling as described above. The tilt of the lower shaft can be suppressed via the inter-shaft bearing. Therefore, it becomes possible to support stably both shafts in the state which suppressed fall by the cheap structure which used few ball bearings.
  • a bush which is a slide bearing as at least one inter-shaft bearing.
  • a needle roller bearing may be used as at least one inter-shaft bearing.
  • the manufacturing cost can be reduced.
  • the manufacturing cost can be reduced.
  • at least one of the first and second inter-shaft bearings includes a needle roller bearing as in claim 4, the rotational resistance between the two shafts can be suppressed.
  • FIG. 1 is a schematic cross-sectional view of a vehicle steering system according to an embodiment of the present invention. It is a schematic sectional drawing of a stopper mechanism.
  • FIG. 6 is a schematic cross-sectional view of a vehicle steering system according to another embodiment of the present invention.
  • FIG. 1 is a schematic cross-sectional view of an electric power steering apparatus 100 as a vehicle steering apparatus according to an embodiment of the present invention.
  • the electric power steering apparatus 100 includes a steering shaft 2 for transmitting the rotation of a steering wheel 1 as a steering member.
  • the steering shaft 2 includes a column shaft 4 rotatably supported by a steering column 3 as a supporting member fixed to a vehicle body B, an intermediate shaft 6 connected to the column shaft 4 via a universal joint 5, and an intermediate member It has a pinion shaft 8 connected with an it-shaft 6 and a universal joint 7.
  • the electric power steering apparatus 100 further includes a steering mechanism A including a rack and pinion mechanism including the pinion shaft 8 and a rack bar 9 having a rack 9a that meshes with a pinion 8a provided on the pinion shaft 8. .
  • the rack bar 9 is axially movably supported by the housing 10. Both ends of the rack bar 9 protruding from the housing 10 are connected to the steered wheels 13 via the corresponding tie rods 11 and knuckle arms 12 respectively.
  • the column shaft 4 includes a cylindrical upper shaft 14, a cylindrical lower shaft 15, and a torsion bar 16 coaxially rotatably connecting the upper shaft 14 and the lower shaft 15.
  • the upper end 161 of the torsion bar 16 is integrally rotatably coupled with the upper shaft 14 by press-fitting with serrations.
  • the lower end 162 of the torsion bar 16 and the lower shaft 15 are integrally rotatably connected by a pin 17 passing through both.
  • a steering wheel 1 as a steering member is attached to an upper end 141 of the upper shaft 14.
  • the lower end of the lower shaft 15 is connected to the steering mechanism A via the universal joint 5, the intermediate shaft 6 and the universal joint 7.
  • the steering column 3 as a hollow support member includes a cylindrical jacket 19, a housing 20 coupled to the lower end 191 of the jacket 19, and an end cover 21 closing the lower portion of the housing 20.
  • the steering column 3 is fixed to the vehicle body via a mounting member 50 fitted and fixed to the end cover 21.
  • a speed reduction mechanism 23 for decelerating the output rotation of the electric motor 22 that generates a steering assist force is accommodated.
  • the speed reduction mechanism 23 is, for example, a worm gear mechanism, and includes a worm shaft 24 as a drive gear driven by the electric motor 22 and a worm wheel 25 as a driven gear meshing with the worm shaft 24.
  • the worm wheel 25 includes an annular core metal 25a fitted integrally with the outer periphery 15a of the lower shaft 15 and a synthetic resin member 25b surrounding the core metal 25a and forming teeth on the outer periphery. .
  • the cored bar 25a is inserted into a mold, for example, at the time of resin molding of the synthetic resin member 25b.
  • the core metal 25a and the molded synthetic resin member 25b are integrally rotatably coupled.
  • the housing 20 has a first cylindrical portion 26 and a second cylindrical portion 27 provided so as to cross the first cylindrical portion 26.
  • the housing 20 is integrally formed of, for example, an aluminum alloy.
  • the worm shaft 24 is accommodated in the first cylindrical portion 26.
  • the worm wheel 25 of the speed reduction mechanism 23 and the torque sensor 28 are accommodated in the first cylindrical portion 26.
  • the upper end 27 a of the second tubular portion 27 is fitted to the jacket 19.
  • An annular end cover 21 is coupled to the lower end 27 b of the second cylindrical portion 27.
  • the end cover 21 includes an annular plate 21a opposed to the end face of the synthetic resin member 25b of the worm wheel 25, a large cylindrical portion 21b extending axially downward from the outer edge of the annular plate 21a, and axially upward from the inner edge of the annular plate 21a. And a small tube portion 21c.
  • the small cylindrical portion 21 c intrudes radially inward of the synthetic resin member 25 b of the worm wheel 25.
  • the control chamber 30 is divided by the outside portion of the housing 20 and the controller case 29.
  • an ECU 32 Electric Control Unit
  • a control board 31 for controlling the operation of the electric motor 22 and a power board (not shown) is accommodated.
  • the feature of the present embodiment is the structure for supporting the column shaft 4 of the steering shaft 2.
  • the upper end 141 of the upper shaft 14 of the column shaft 4 is rotatably supported by the first ball bearing 33 held by the jacket 19 of the steering column 3.
  • the first ball bearing 33 is provided between the outer ring 33a fitted and fixed to the inner periphery 19a of the jacket 19, the inner ring 33b fitted rotatably to the outer periphery 14a of the upper shaft 14, and the outer ring 33a and the inner ring 33b.
  • a plurality of balls 33c interposed therebetween.
  • the lower shaft 15 of the column shaft 4 is rotatably supported by a second ball bearing 34 held by the small cylindrical portion 21 c of the end cover 21 of the housing 20 of the steering column 3.
  • the second ball bearing 34 includes an outer ring 34a fitted and fixed to the inner periphery of the small cylindrical portion 21c, an inner ring 34b fitted rotatably to the outer periphery 15a of the lower shaft 15, and the outer ring 34a and the inner ring 34b. And a plurality of balls 34c interposed therebetween.
  • the fitting cylinder 51 of the mounting member 50 is fitted and fixed to the inner periphery of the small cylindrical portion 21 c of the end cover 21.
  • the outer ring 34 a of the second ball bearing 34 is between the annular flange 52 provided at one end of the fitting cylinder 51 of the mounting member 50 and the annular flange 21 d provided at one end of the small cylindrical portion 21 c of the end cover 21. It is held by Thus, the movement of the outer ring 34a in the axial direction X1 of the steering shaft 2 is restricted.
  • the inner ring 34 b of the second ball bearing 34 is provided between the step 15 b provided on the outer periphery 15 a of the lower shaft 15 and the nut 35 screwed on the screw provided on the outer periphery 15 a of the lower shaft 15. It is pinched. Thus, the relative movement of the inner ring 34b and the lower shaft 15 in the axial direction X1 is restricted.
  • the lower portion of the upper shaft 14 is inserted into the lower shaft 15 and can be rotated via the first bush 36 as a first inter-shaft bearing and the second bush 37 as a second inter-shaft bearing It is supported by Each of the bushes 36 and 37 is a slide bearing.
  • each bush may be a porous sintered alloy bush in which a lubricant is impregnated in pores, or may be a synthetic resin bush.
  • a synthetic resin bushing a self-lubricating fluorocarbon resin may be used.
  • a sliding surface of the synthetic resin bush may be coated with a solid lubricant (for example, molybdenum disulfide).
  • the first bush 36 and the second bush 37 are arranged at predetermined intervals in the axial direction X1.
  • the first bush 36 is fitted and held by the first bearing holding portion 38 provided on the inner periphery 15 c of the lower shaft 15, and rotatably supports the lower end 142 of the upper shaft 14.
  • the first bush 36 includes a portion disposed radially inward of the bearing center C 1 of the second ball bearing 34.
  • the second bush 37 is fitted and held by a second bearing holding portion 39 provided on the inner periphery of the upper end 151 of the lower shaft 15, and rotatably supports the upper shaft 14.
  • the first bush 36 and the second bush 37 are separated in the axial direction X1, and regulate the relative rotation amount of the upper shaft 14 and the lower shaft 15 between the first bush 36 and the second bush 37.
  • the stopper mechanism 40 is disposed. As shown in FIG. 2, the stopper mechanism 40 is provided on a recess 41 provided on the inner periphery 15 c of the lower shaft 15 and on the outer periphery 14 a of the upper shaft 14 to allow play in the rotational direction in the recess 41. It is comprised by the convex part 42 arrange
  • the upper end 141 of the upper shaft 14 is supported by the first ball bearing 33.
  • a portion of the first inter-shaft bearing (first bush 36) supporting the lower end 142 of the upper chassis 14 is disposed at the radially inward position of the second ball bearing 34 supporting the lower shaft 15.
  • the lower end 142 of the upper shaft 14 can be supported by the second ball bearing 34 substantially.
  • the second inter-shaft bearing (the second bush 37) is disposed at a position separated in the axial direction X1 from the first inter-shaft bearing (the first bush 36), the following advantages can be obtained. . That is, under the influence of the secondary couple generated in the universal joint 5 by the rotational torque of the intermediate shaft 6, the moment load for tilting the lower shaft 15 with the bearing center C1 of the second ball bearing 34 as a fulcrum When it occurs, it is possible to suppress the falling of the lower shaft 15 via the second inter-shaft bearing (the second bush 37) by the upper shaft 14 in which the falling is suppressed as described above.
  • the ball bearings for supporting the column shaft 4 the first ball bearing 33 for supporting the upper shaft 14 and the second ball bearing 34 for supporting the lower shaft 15, while achieving cost reduction, It becomes possible to support stably both shafts 14 and 15 in the state where fall was controlled. In addition, it is possible to prevent in advance the adverse effect such as the deterioration of the detection accuracy of the torque sensor 28 that may occur due to the tilting of the both shafts 14 and 15.
  • first bush 36 and the second bush 37 are used as inter-shaft bearings interposed between the upper shaft 14 and the lower shaft 15, the manufacturing cost can be further reduced.
  • the method of detecting the steering torque based on the relative rotation of the upper shaft 14 and the lower shaft 15 is employed, so the relative amount of rotation of both shafts 14 and 15 is regulated. It is necessary to provide a stopper mechanism 40.
  • the stopper mechanism 40 is disposed in the empty space between the shaft-to-shaft bearings (the first bush 36 and the second bush 37), so that wasted space can be eliminated and the lower shaft 15 can be eliminated. Can be made as small as possible.
  • the present invention is not limited to the above embodiment.
  • an inter-shaft bearing as shown in FIG. 3 in place of the first and second bushes 36 and 37 of FIG. , 37A may be used. In this case, the rotational resistance between the upper shaft 14 and the lower shaft 15 can be reduced.
  • a needle roller bearing may be used instead of only one of the first and second bushes 36 and 37.
  • a so-called column assist type electric power steering apparatus applies steering assist by applying the power of the electric motor 22 to the lower shaft 15 of the column shaft 4 of the steering shaft 2 supported by the steering column 3
  • the present invention is not limited to this, and is applied to a so-called pinion assist type electric power steering apparatus that applies the power of the electric motor 22 to the pinion shaft 8 of the steering shaft 2 to assist steering. You may do it.
  • First bush (first inter-shaft bearing), 36A: first needle roller bearing (first inter-shaft bearing), 37: second Bush (second inter-shaft bearing), 37A: second needle roller bearing (second inter-shaft bearing), 40: stopper mechanism, 41: recess, 42: protrusion, 100: electric power steering device (vehicle Steering device), B: vehicle body, C1: bearing center, X1: axial direction

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Power Steering Mechanism (AREA)
  • Steering Controls (AREA)

Abstract

A steering shaft (2) penetrating through a hollow support member (3) includes an upper shaft (14) and a lower shaft (15) which are coaxially connected through a torsion bar (16). A first ball bearing (33) retained by the support member (3) rotatably supports the upper end (141) of the upper shaft. A second ball bearing (34) retained by the support member (3) rotatably supports the lower shaft (15). A first inter-shaft bearing (36; 36A) retained by the lower shaft (15) rotatably supports the lower end (142) of the upper shaft (14). A second inter-shaft bearing (37; 37A) retained by the upper shaft (14) rotatably supports the upper end (151) of the lower shaft (15). The first inter-shaft bearing (36; 36A) includes a portion disposed inward radially of the bearing center (C1) of the second ball bearing (34). The first and second inter-shaft bearings (36, 37; 36A, 37A) are separated from each other in the direction (X1) of the axis of the steering shaft (2).

Description

車両用操舵装置Vehicle steering system
　本発明は車両用操舵装置に関する。 The present invention relates to a vehicle steering system.
　一般に、電動パワーステアリング装置では、ステアリングシャフトを多くの玉軸受を用いて支持している。例えば特許文献１では、ステアリングシャフトが、アッパーシャフトと、アッパーシャフトの下端に同伴回転可能に連結された中間シャフトと、中間シャフトにトーションバーを介して相対回転可能に連結されたロアーシャフトとにより構成されている。 In general, in an electric power steering apparatus, a steering shaft is supported using a number of ball bearings. For example, in Patent Document 1, the steering shaft includes an upper shaft, an intermediate shaft rotatably coupled to the lower end of the upper shaft, and a lower shaft rotatably coupled to the intermediate shaft via a torsion bar. It is done.
　アッパーシャフトの上端が、第１の玉軸受によって支持されている。中間シャフトが、第２の玉軸受によって支持されている。ロアーシャフトが、当該ロアーシャフトと同伴回転するウォームホイールを挟んだ両側において、第３および第４の玉軸受によって支持されている。また、中間シャフトとロアーシャフトとの嵌合部分に、ブッシュが配置されている。 The upper end of the upper shaft is supported by the first ball bearing. An intermediate shaft is supported by the second ball bearing. The lower shaft is supported by the third and fourth ball bearings on both sides of the lower shaft and the worm wheel rotating together with the lower shaft. Further, a bush is disposed at a fitting portion between the intermediate shaft and the lower shaft.
特開２００３－３４１５２８号公報JP 2003-341528 A
　特許文献１では、使用している玉軸受の数が４個と多いため、製造コストが高いという問題があった。しかし、玉軸受の数を減じた場合、下記のおそれがある。すなわち、ラック軸のストローク端で生ずる衝撃荷重で、インターミディエイトシャフトに大きな回転トルクが作用すると、インターミディエイトシャフトとステアリングシャフトの要素であるロアーシャフトとを連結する自在継手に生じる二次偶力によって、ロアーシャフトに大きなモーメント荷重が作用する。このため、ロアーシャフトに、倒れが発生するおそれがある。倒れの発生は、軸受寿命に影響を与える。また、トルクセンサの検出精度が悪くなる。 In patent document 1, since the number of ball bearings used is as many as four pieces, there existed a problem that manufacturing cost was high. However, if the number of ball bearings is reduced, the following may occur. That is, when a large rotational torque is applied to the intermediate shaft by the impact load generated at the stroke end of the rack shaft, the secondary couple generated at the universal joint connecting the intermediate shaft and the lower shaft which is an element of the steering shaft A large moment load acts on the lower shaft. For this reason, there is a possibility that the lower shaft may fall. The occurrence of falling affects bearing life. In addition, the detection accuracy of the torque sensor is degraded.
　本発明は、上記課題に鑑みてなされたものであり、安価にステアリングシャフトの要素の倒れを抑制することができる車両用操舵装置を提供することを目的とする。 The present invention is made in view of the above-mentioned subject, and it aims at providing a steering device for vehicles which can control collapse of an element of a steering shaft inexpensively.
　上記目的を達成するため、請求項１の発明は、中空の支持部材と、上記支持部材を貫通し、トーションバーを介して同軸上に連結されたアッパーシャフトおよびロアーシャフトを含むステアリングシャフトと、上記支持部材に保持され、上記アッパーシャフトの上端を回転可能に支持する第１の玉軸受と、上記支持部材に保持され、上記ロアーシャフトを回転可能に支持する第２の玉軸受と、上記ロアーシャフトに保持され、上記アッパーシャフトの下端を回転可能に支持する第１のシャフト間軸受と、上記アッパーシャフトに保持され、上記ロアーシャフトの上端を回転可能に支持する第２のシャフト間軸受と、を備え、上記第１のシャフト間軸受は、上記第２の玉軸受の軸受中心の径方向内方に配置された部分を含み、上記第１のシャフト間軸受および上記第２のシャフト間軸受は、上記ステアリングシャフトの軸方向に離隔している車両用操舵装置を提供する。 In order to achieve the above object, the invention according to claim 1 comprises a hollow support member, a steering shaft including an upper shaft and a lower shaft coaxially connected to each other through the support member through a torsion bar; A first ball bearing held by a support member and rotatably supporting the upper end of the upper shaft, a second ball bearing held by the support member and rotatably supporting the lower shaft, and the lower shaft A first inter-shaft bearing rotatably supported by the lower end of the upper shaft, and a second inter-shaft bearing rotatably supported by the upper shaft and rotatably supporting the upper end of the lower shaft; The first shaft-to-shaft bearing includes a portion disposed radially inward of the bearing center of the second ball bearing; Intercluster between the bearing and the second shaft bearing provides a steering apparatus for a vehicle which is remote in the axial direction of the steering shaft.
　また、請求項２の発明のように、上記アッパーシャフトおよび上記ロアーシャフトの相対回転量を規制するストッパ機構を備え、上記ストッパ機構は、軸方向に関して、上記第１のシャフト間軸受および上記第２のシャフト間軸受の間に配置されていてもよい。
　また、請求項３の発明のように、上記第１のシャフト間軸受および上記第２のシャフト間軸受の少なくとも一方は、ブッシュを含んでいてもよい。 According to a second aspect of the present invention, a stopper mechanism for restricting the relative rotation amount of the upper shaft and the lower shaft is provided. The stopper mechanism has the first inter-shaft bearing and the second shaft in the axial direction. It may be disposed between the shaft-to-shaft bearings.
Further, as in the invention of claim 3, at least one of the first inter-shaft bearing and the second inter-shaft bearing may include a bush.
　また、請求項４の発明のように、上記第１のシャフト間軸受および上記第２のシャフト間軸受の少なくとも一方は、針状ころ軸受を含んでいてもよい。 Further, as in the invention of claim 4, at least one of the first inter-shaft bearing and the second inter-shaft bearing may include a needle roller bearing.
　請求項１の発明によれば、アッパーシャフトの上端が第１の玉軸受によって支持されている。アッパーシャトの下端を支持する第１のシャフト間軸受の一部を、ロアーシャフトを支持する第２の玉軸受の径方向内方の位置に配置したので、アッパーシャフトの下端を、実質的に第２の玉軸受によって支持することができる。
　また、第１のシャフト間軸受から軸方向に離隔した位置に、第２のシャフト間軸受が配置されているので、下記の利点がある。すなわち、偶力によって第２の玉軸受の軸受中心を支点として、ロアーシャフトを傾かせようとするモーメント荷重が生じたときに、上記のように倒れが抑制されているアッパーシャフトによって、第２のシャフト間軸受を介して、ロアーシャフトの倒れを抑制することができる。したがって、数少ない玉軸受を用いた安価な構成で、両シャフトを、倒れを抑制した状態で安定して支持することが可能となる。 According to the invention of claim 1, the upper end of the upper shaft is supported by the first ball bearing. Since a portion of the first inter-shaft bearing supporting the lower end of the upper shuttle is disposed at a radially inward position of the second ball bearing supporting the lower shaft, the lower end of the upper shaft is substantially It can be supported by two ball bearings.
In addition, since the second inter-shaft bearing is disposed at a position axially separated from the first inter-shaft bearing, the following advantages can be obtained. That is, when a moment load for tending to lower the lower shaft is generated by a couple of forces with the bearing center of the second ball bearing as a fulcrum, the second upper shaft suppresses the falling as described above. The tilt of the lower shaft can be suppressed via the inter-shaft bearing. Therefore, it becomes possible to support stably both shafts in the state which suppressed fall by the cheap structure which used few ball bearings.
　製造コストをより安くするためには、少なくとも一方のシャフト間軸受として、すべり軸受であるブッシュを用いることが好ましい。ただし、両シャフト間の回転抵抗を低減するために、少なくとも一方のシャフト間軸受として、針状ころ軸受を用いるようにしてもよい。
　請求項２の発明によれば、下記の利点がある。すなわち、ロアーシャフトの倒れを抑制するために、第１のシャフト間軸受と第２のシャフト間軸受との間隔を広くすることが好ましい。一方、通例、アッパーシャフトとロアーシャフトの相対回転に基づいて操舵トルクを検出する方式が採用されているため、両シャフトの相対回転量を規制するストッパを設けることが必要である。本発明では、上記ストッパを第１および第２のシャフト間軸受間の空きスペースに配置するので、無駄なスペースを省くことができ、且つロアーシャフトの倒れを極力小さくすることができる。 In order to make the manufacturing cost lower, it is preferable to use a bush which is a slide bearing as at least one inter-shaft bearing. However, in order to reduce the rotational resistance between both shafts, a needle roller bearing may be used as at least one inter-shaft bearing.
According to the invention of claim 2, there are the following advantages. That is, it is preferable to widen the distance between the first inter-shaft bearing and the second inter-shaft bearing in order to suppress the tilt of the lower shaft. On the other hand, since the method of detecting the steering torque based on the relative rotation of the upper shaft and the lower shaft is generally employed, it is necessary to provide a stopper that regulates the relative amount of rotation of both shafts. In the present invention, since the stopper is disposed in the empty space between the first and second shaft-to-shaft bearings, unnecessary space can be eliminated, and the lower shaft can be made as small as possible.
　また、請求項３のように、第１および第２のシャフト間軸受の少なくとも一方がブッシュを含む場合には、製造コストを安くすることができる。
　また、請求項４のように、第１および第２のシャフト間軸受の少なくとも一方が針状ころ軸受を含む場合には、両シャフト間の回転抵抗を抑制することかできる。 In addition, as in claim 3, when at least one of the first and second inter-shaft bearings includes a bush, the manufacturing cost can be reduced.
When at least one of the first and second inter-shaft bearings includes a needle roller bearing as in claim 4, the rotational resistance between the two shafts can be suppressed.
本発明の一実施の形態の車両用操舵装置の模式的断面図である。FIG. 1 is a schematic cross-sectional view of a vehicle steering system according to an embodiment of the present invention. ストッパ機構の概略断面図である。It is a schematic sectional drawing of a stopper mechanism. 本発明の別の実施の形態の車両用操舵装置の模式的断面図である。FIG. 6 is a schematic cross-sectional view of a vehicle steering system according to another embodiment of the present invention.
　本発明の好ましい実施の形態を添付図面を参照しつつ説明する。
　図１は本発明の一実施の形態の車両用操舵装置としての電動パワーステアリング装置１００の概略断面図である。図１を参照して、電動パワーステアリング装置１００は、操舵部材としてのステアリングホイール１の回転を伝達するためのステアリングシャフト２を備えている。ステアリングシャフト２は、車体Ｂに固定された支持部材としてのステアリングコラム３によって回転可能に支持されたコラムシャフト４と、コラムシャフト４と自在継手５を介して連結されたインターミディエイトシャフト６と、インターミディエイトシャフト６と自在継手７を介して連結されたピニオンシャフト８とを備えている。 Preferred embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 is a schematic cross-sectional view of an electric power steering apparatus 100 as a vehicle steering apparatus according to an embodiment of the present invention. Referring to FIG. 1, the electric power steering apparatus 100 includes a steering shaft 2 for transmitting the rotation of a steering wheel 1 as a steering member. The steering shaft 2 includes a column shaft 4 rotatably supported by a steering column 3 as a supporting member fixed to a vehicle body B, an intermediate shaft 6 connected to the column shaft 4 via a universal joint 5, and an intermediate member It has a pinion shaft 8 connected with an it-shaft 6 and a universal joint 7.
　また、電動パワーステアリング装置１００は、上記ピニオンシャフト８と、ピニオンシャフト８に設けられたピニオン８ａと噛み合うラック９ａを有するラックバー９とを備えるラックアンドピニオン機構からなる転舵機構Ａを備えている。
　ラックバー９は、ハウジング１０によって軸方向に移動可能に支持されている。ハウジング１０から突出するラックバー９の両端は、それぞれ対応するタイロッド１１およびナックルアーム１２を介して転舵輪１３と連結されている。 The electric power steering apparatus 100 further includes a steering mechanism A including a rack and pinion mechanism including the pinion shaft 8 and a rack bar 9 having a rack 9a that meshes with a pinion 8a provided on the pinion shaft 8. .
The rack bar 9 is axially movably supported by the housing 10. Both ends of the rack bar 9 protruding from the housing 10 are connected to the steered wheels 13 via the corresponding tie rods 11 and knuckle arms 12 respectively.
　コラムシャフト４は、筒状のアッパーシャフト１４と、筒状のロアーシャフト１５と、アッパーシャフト１４およびロアーシャフト１５を同軸的に相対回転可能に連結したトーションバー１６とを備えている。トーションバー１６の上端１６１は、セレーションを用いた圧入により、アッパーシャフト１４と一体回転可能に連結されている。トーションバー１６の下端１６２およびロアーシャフト１５は、両者を貫通するピン１７によって、一体回転可能に連結されている。 The column shaft 4 includes a cylindrical upper shaft 14, a cylindrical lower shaft 15, and a torsion bar 16 coaxially rotatably connecting the upper shaft 14 and the lower shaft 15. The upper end 161 of the torsion bar 16 is integrally rotatably coupled with the upper shaft 14 by press-fitting with serrations. The lower end 162 of the torsion bar 16 and the lower shaft 15 are integrally rotatably connected by a pin 17 passing through both.
　アッパーシャフト１４の上端１４１には、操舵部材としてのステアリングホイール１が取り付けられている。ロアーシャフト１５の下端は、自在継手５、インターミディエイトシャフト６および自在継手７を介して、転舵機構Ａに連結されている。
　中空の支持部材としてのステアリングコラム３は、筒状のジャケット１９と、ジャケット１９の下端１９１に結合されたハウジング２０、ハウジング２０の下部を閉塞するエンドカバー２１とを備えている。ステアリングコラム３は、エンドカバー２１に嵌合固定された取付部材５０を介して車体に固定されている。 A steering wheel 1 as a steering member is attached to an upper end 141 of the upper shaft 14. The lower end of the lower shaft 15 is connected to the steering mechanism A via the universal joint 5, the intermediate shaft 6 and the universal joint 7.
The steering column 3 as a hollow support member includes a cylindrical jacket 19, a housing 20 coupled to the lower end 191 of the jacket 19, and an end cover 21 closing the lower portion of the housing 20. The steering column 3 is fixed to the vehicle body via a mounting member 50 fitted and fixed to the end cover 21.
　ハウジング２０内には、操舵補助力を発生する電動モータ２２の出力回転を減速する減速機構２３が収容されている。減速機構２３は、例えばウォームギヤ機構からなり、電動モータ２２により駆動される駆動ギヤとしてのウォーム軸２４と、ウォーム軸２４と噛み合う被動ギヤとしてのウォームホイール２５とを備えている。
　ウォームホイール２５は、ロアーシャフト１５の外周１５ａに一体回転可能に嵌合された環状の芯金２５ａと、芯金２５ａの周囲を取り囲み、外周に歯を形成する合成樹脂部材２５ｂとを備えている。芯金２５ａは、例えば合成樹脂部材２５ｂの樹脂成形時に金型内にインサートされる。芯金２５ａと成形された合成樹脂部材２５ｂとは、一体回転可能に結合されている。 In the housing 20, a speed reduction mechanism 23 for decelerating the output rotation of the electric motor 22 that generates a steering assist force is accommodated. The speed reduction mechanism 23 is, for example, a worm gear mechanism, and includes a worm shaft 24 as a drive gear driven by the electric motor 22 and a worm wheel 25 as a driven gear meshing with the worm shaft 24.
The worm wheel 25 includes an annular core metal 25a fitted integrally with the outer periphery 15a of the lower shaft 15 and a synthetic resin member 25b surrounding the core metal 25a and forming teeth on the outer periphery. . The cored bar 25a is inserted into a mold, for example, at the time of resin molding of the synthetic resin member 25b. The core metal 25a and the molded synthetic resin member 25b are integrally rotatably coupled.
　ハウジング２０は、第１の筒状部２６と、第１の筒状部２６と交差状に設けられた第２の筒状部２７とを有し、例えばアルミニウム合金により一体に形成されている。第１の筒状部２６には、ウォーム軸２４が収容されている。ハウジング２０の第２の筒状部２７には、減速機構２３のウォームホイール２５とトルクセンサ２８とが収容されている。第２の筒状部２７の上端２７ａが、ジャケット１９に嵌合されている。第２の筒状部２７の下端２７ｂには、環状のエンドカバー２１が結合されている。 The housing 20 has a first cylindrical portion 26 and a second cylindrical portion 27 provided so as to cross the first cylindrical portion 26. The housing 20 is integrally formed of, for example, an aluminum alloy. The worm shaft 24 is accommodated in the first cylindrical portion 26. In the second cylindrical portion 27 of the housing 20, the worm wheel 25 of the speed reduction mechanism 23 and the torque sensor 28 are accommodated. The upper end 27 a of the second tubular portion 27 is fitted to the jacket 19. An annular end cover 21 is coupled to the lower end 27 b of the second cylindrical portion 27.
　エンドカバー２１は、ウォームホイール２５の合成樹脂部材２５ｂの端面に対向する環状板２１ａと、環状板２１ａの外縁から軸方向下方に延びる大筒部２１ｂと、環状板２１ａの内縁から軸方向上方へ延びる小筒部２１ｃとを有している。小筒部２１ｃは、ウォームホイール２５の合成樹脂部材２５ｂの径方向内方に侵入している。
　また、ハウジング２０の外側部とコントローラケース２９とによって、制御室３０が区画されている。制御室３０内には、電動モータ２２の動作を制御する制御基板３１やパワー基板（図示せず）等を含むＥＣＵ３２（Electronic Control Unit:電子制御ユニット）が収容されている。 The end cover 21 includes an annular plate 21a opposed to the end face of the synthetic resin member 25b of the worm wheel 25, a large cylindrical portion 21b extending axially downward from the outer edge of the annular plate 21a, and axially upward from the inner edge of the annular plate 21a. And a small tube portion 21c. The small cylindrical portion 21 c intrudes radially inward of the synthetic resin member 25 b of the worm wheel 25.
Further, the control chamber 30 is divided by the outside portion of the housing 20 and the controller case 29. In the control room 30, an ECU 32 (Electronic Control Unit) including a control board 31 for controlling the operation of the electric motor 22 and a power board (not shown) is accommodated.
　本実施の形態の特徴とするところは、ステアリングシャフト２のコラムシャフト４を支持する構造にある。具体的には、コラムシャフト４のアッパーシャフト１４の上端１４１が、ステアリングコラム３のジャケット１９に保持された第１の玉軸受３３によって、回転可能に支持されている。第１の玉軸受３３は、ジャケット１９の内周１９ａに嵌合固定された外輪３３ａと、アッパーシャフト１４の外周１４ａに同伴回転可能に嵌合された内輪３３ｂと、外輪３３ａおよび内輪３３ｂの間に介在する複数の玉３３ｃとを有している。 The feature of the present embodiment is the structure for supporting the column shaft 4 of the steering shaft 2. Specifically, the upper end 141 of the upper shaft 14 of the column shaft 4 is rotatably supported by the first ball bearing 33 held by the jacket 19 of the steering column 3. The first ball bearing 33 is provided between the outer ring 33a fitted and fixed to the inner periphery 19a of the jacket 19, the inner ring 33b fitted rotatably to the outer periphery 14a of the upper shaft 14, and the outer ring 33a and the inner ring 33b. And a plurality of balls 33c interposed therebetween.
　また、コラムシャフト４のロアーシャフト１５は、ステアリングコラム３のハウジング２０のエンドカバー２１の小筒部２１ｃに保持された第２の玉軸受３４によって、回転可能に支持されている。第２の玉軸受３４は、小筒部２１ｃの内周に嵌合固定された外輪３４ａと、ロアーシャフト１５の外周１５ａに同伴回転可能に嵌合された内輪３４ｂと、外輪３４ａおよび内輪３４ｂの間に介在する複数の玉３４ｃとを有している。 The lower shaft 15 of the column shaft 4 is rotatably supported by a second ball bearing 34 held by the small cylindrical portion 21 c of the end cover 21 of the housing 20 of the steering column 3. The second ball bearing 34 includes an outer ring 34a fitted and fixed to the inner periphery of the small cylindrical portion 21c, an inner ring 34b fitted rotatably to the outer periphery 15a of the lower shaft 15, and the outer ring 34a and the inner ring 34b. And a plurality of balls 34c interposed therebetween.
　エンドカバー２１の小筒部２１ｃの内周に、取付部材５０の嵌合筒５１が嵌合固定されている。第２の玉軸受３４の外輪３４ａは、取付部材５０の嵌合筒５１の一端に設けられた環状フランジ５２と、エンドカバー２１の小筒部２１ｃの一端に設けられた環状フランジ２１ｄとの間に挟持されている。これにより、ステアリングシャフト２の軸方向Ｘ１への外輪３４ａの移動が規制されている。 The fitting cylinder 51 of the mounting member 50 is fitted and fixed to the inner periphery of the small cylindrical portion 21 c of the end cover 21. The outer ring 34 a of the second ball bearing 34 is between the annular flange 52 provided at one end of the fitting cylinder 51 of the mounting member 50 and the annular flange 21 d provided at one end of the small cylindrical portion 21 c of the end cover 21. It is held by Thus, the movement of the outer ring 34a in the axial direction X1 of the steering shaft 2 is restricted.
　また、第２の玉軸受３４の内輪３４ｂは、ロアーシャフト１５の外周１５ａに設けられた段部１５ｂと、ロアーシャフト１５の外周１５ａに設けられたねじ部に螺合するナット３５との間に挟持されている。これにより、内輪３４ｂおよびロアーシャフト１５の軸方向Ｘ１の相対移動が規制されている。
　一方、アッパーシャフト１４の下部は、ロアーシャフト１５内に挿入され、第１のシャフト間軸受としての第１のブッシュ３６および第２のシャフト間軸受としての第２のブッシュ３７を介して、回転可能に支持されている。各ブッシュ３６，３７は、すべり軸受であり、例えば、各ブッシュは、潤滑剤を気孔に含浸させた多孔質焼結合金ブッシュであってもよいし、合成樹脂ブッシュであってもよい。合成樹脂ブッシュの場合、自己潤滑性のあるフッ素樹脂を用いてもよい。また、合成樹脂ブッシュのすべり面に固体潤滑剤（例えば二硫化モリブデン）が被覆されていてもよい。 Further, the inner ring 34 b of the second ball bearing 34 is provided between the step 15 b provided on the outer periphery 15 a of the lower shaft 15 and the nut 35 screwed on the screw provided on the outer periphery 15 a of the lower shaft 15. It is pinched. Thus, the relative movement of the inner ring 34b and the lower shaft 15 in the axial direction X1 is restricted.
On the other hand, the lower portion of the upper shaft 14 is inserted into the lower shaft 15 and can be rotated via the first bush 36 as a first inter-shaft bearing and the second bush 37 as a second inter-shaft bearing It is supported by Each of the bushes 36 and 37 is a slide bearing. For example, each bush may be a porous sintered alloy bush in which a lubricant is impregnated in pores, or may be a synthetic resin bush. In the case of a synthetic resin bushing, a self-lubricating fluorocarbon resin may be used. In addition, a sliding surface of the synthetic resin bush may be coated with a solid lubricant (for example, molybdenum disulfide).
　第１のブッシュ３６および第２のブッシュ３７は、軸方向Ｘ１に所定間隔離して配置されている。第１のブッシュ３６は、ロアーシャフト１５の内周１５ｃに設けられた第１の軸受保持部３８に嵌合保持され、アッパーシャフト１４の下端１４２を回転可能に支持している。
　第１のブッシュ３６は、第２の玉軸受３４の軸受中心Ｃ１の径方向内方に配置される部分を含んでいる。一方、第２のブッシュ３７は、ロアーシャフト１５の上端１５１の内周に設けられた第２の軸受保持部３９に嵌合保持され、アッパーシャフト１４を回転可能に支持している。 The first bush 36 and the second bush 37 are arranged at predetermined intervals in the axial direction X1. The first bush 36 is fitted and held by the first bearing holding portion 38 provided on the inner periphery 15 c of the lower shaft 15, and rotatably supports the lower end 142 of the upper shaft 14.
The first bush 36 includes a portion disposed radially inward of the bearing center C 1 of the second ball bearing 34. On the other hand, the second bush 37 is fitted and held by a second bearing holding portion 39 provided on the inner periphery of the upper end 151 of the lower shaft 15, and rotatably supports the upper shaft 14.
　第１のブッシュ３６および第２のブッシュ３７は、軸方向Ｘ１に離隔しており、第１のブッシュ３６および第２のブッシュ３７間に、アッパーシャフト１４およびロアーシャフト１５の相対回転量を規制するストッパ機構４０が配置されている。
　図２に示すように、ストッパ機構４０は、ロアーシャフト１５の内周１５ｃに設けられた凹部４１と、アッパーシャフト１４の外周１４ａに設けられ、上記凹部４１内に回転方向に遊びを持たせて配置された凸部４２とにより構成されている。 The first bush 36 and the second bush 37 are separated in the axial direction X1, and regulate the relative rotation amount of the upper shaft 14 and the lower shaft 15 between the first bush 36 and the second bush 37. The stopper mechanism 40 is disposed.
As shown in FIG. 2, the stopper mechanism 40 is provided on a recess 41 provided on the inner periphery 15 c of the lower shaft 15 and on the outer periphery 14 a of the upper shaft 14 to allow play in the rotational direction in the recess 41. It is comprised by the convex part 42 arrange | positioned.
　本実施の形態によれば、アッパーシャフト１４の上端１４１が第１の玉軸受３３によって支持されている。一方、アッパーシャト１４の下端１４２を支持する第１のシャフト間軸受（第１のブッシュ３６）の一部を、ロアーシャフト１５を支持する第２の玉軸受３４の径方向内方の位置に配置したので、アッパーシャフト１４の下端１４２を、実質的に第２の玉軸受３４によって支持することができる。 According to the present embodiment, the upper end 141 of the upper shaft 14 is supported by the first ball bearing 33. On the other hand, a portion of the first inter-shaft bearing (first bush 36) supporting the lower end 142 of the upper chassis 14 is disposed at the radially inward position of the second ball bearing 34 supporting the lower shaft 15. Thus, the lower end 142 of the upper shaft 14 can be supported by the second ball bearing 34 substantially.
　また、第１のシャフト間軸受（第１のブッシュ３６）から軸方向Ｘ１に離隔した位置に、第２のシャフト間軸受（第２のブッシュ３７）が配置されているので、下記の利点がある。すなわち、インターミディエイトシャフト６の回転トルクによって自在継手５に発生した二次偶力の影響で、第２の玉軸受３４の軸受中心Ｃ１を支点として、ロアーシャフト１５を傾かせようとするモーメント荷重が発生したときに、上記のようにして倒れが抑制されているアッパーシャフト１４によって、第２のシャフト間軸受（第２のブッシュ３７）を介して、ロアーシャフト１５の倒れを抑制することができる。 In addition, since the second inter-shaft bearing (the second bush 37) is disposed at a position separated in the axial direction X1 from the first inter-shaft bearing (the first bush 36), the following advantages can be obtained. . That is, under the influence of the secondary couple generated in the universal joint 5 by the rotational torque of the intermediate shaft 6, the moment load for tilting the lower shaft 15 with the bearing center C1 of the second ball bearing 34 as a fulcrum When it occurs, it is possible to suppress the falling of the lower shaft 15 via the second inter-shaft bearing (the second bush 37) by the upper shaft 14 in which the falling is suppressed as described above.
　コラムシャフト４を支持する玉軸受としては、アッパーシャフト１４を支持する第１の玉軸受３３とロアーシャフト１５を支持する第２の玉軸受３４との２つであるので、低廉化を果たしつつ、両シャフト１４，１５を、倒れを抑制した状態で安定して支持することが可能となる。また、両シャフト１４，１５の倒れによって発生するおそれのあるトルクセンサ２８の検出精度の悪化等の悪影響を未然に防止することができる。 As the ball bearings for supporting the column shaft 4, the first ball bearing 33 for supporting the upper shaft 14 and the second ball bearing 34 for supporting the lower shaft 15, while achieving cost reduction, It becomes possible to support stably both shafts 14 and 15 in the state where fall was controlled. In addition, it is possible to prevent in advance the adverse effect such as the deterioration of the detection accuracy of the torque sensor 28 that may occur due to the tilting of the both shafts 14 and 15.
　また、アッパーシャフト１４とロアーシャフト１５の間に介在するシャフト間軸受として、第１のブッシュ３６および第２のブッシュ３７を用いたので、製造コストをより安くすることができる。
　ロアーシャフト１５の倒れを抑制するために、両シャフト間軸受（第１のブッシュ３６および第２のブッシュ３７）間の間隔を広くすることが好ましい。一方、通例、電動パワーステアリング装置１００においては、アッパーシャフト１４とロアーシャフト１５の相対回転に基づいて操舵トルクを検出する方式が採用されているため、両シャフト１４，１５の相対回転量を規制するストッパ機構４０を設けることが必要である。 Further, since the first bush 36 and the second bush 37 are used as inter-shaft bearings interposed between the upper shaft 14 and the lower shaft 15, the manufacturing cost can be further reduced.
In order to prevent the lower shaft 15 from falling, it is preferable to widen the distance between the shaft-to-shaft bearings (the first bush 36 and the second bush 37). On the other hand, usually, in the electric power steering apparatus 100, the method of detecting the steering torque based on the relative rotation of the upper shaft 14 and the lower shaft 15 is employed, so the relative amount of rotation of both shafts 14 and 15 is regulated. It is necessary to provide a stopper mechanism 40.
　本実施の形態では、そのストッパ機構４０を両シャフト間軸受（第１のブッシュ３６および第２のブッシュ３７）間の空きスペースに配置するので、無駄なスペースを省くことができ、且つロアーシャフト１５の倒れを極力小さくすることができる。
　本発明は上記実施の形態に限定されるものではなく、例えばシャフト間軸受として、図１の第１および第２のブッシュ３６，３７に代えて、図３に示すように、針状ころ軸受３６Ａ，３７Ａを用いるようにしてもよい。この場合、アッパーシャフト１４とロアーシャフト１５の間の回転抵抗を低減することができる。なお、第１および第２のブッシュ３６，３７の何れか一方のみに代えて針状ころ軸受を用いるようにしてもよい。 In the present embodiment, the stopper mechanism 40 is disposed in the empty space between the shaft-to-shaft bearings (the first bush 36 and the second bush 37), so that wasted space can be eliminated and the lower shaft 15 can be eliminated. Can be made as small as possible.
The present invention is not limited to the above embodiment. For example, as an inter-shaft bearing, as shown in FIG. 3 in place of the first and second bushes 36 and 37 of FIG. , 37A may be used. In this case, the rotational resistance between the upper shaft 14 and the lower shaft 15 can be reduced. A needle roller bearing may be used instead of only one of the first and second bushes 36 and 37.
　また、上記実施の形態は、電動モータ２２の動力をステアリングコラム３に支持されたステアリングシャフト２のコラムシャフト４のロアーシャフト１５に付与して操舵補助する、いわゆるコラム・アシスト型の電動パワーステアリング装置に則して説明したが、これに限らず、本発明を、電動モータ２２の動力をステアリングシャフト２のピニオンシャフト８に付与して操舵補助する、いわゆるピニオン・アシスト型の電動パワーステアリング装置に適用するようにしてもよい。 In the above embodiment, a so-called column assist type electric power steering apparatus applies steering assist by applying the power of the electric motor 22 to the lower shaft 15 of the column shaft 4 of the steering shaft 2 supported by the steering column 3 However, the present invention is not limited to this, and is applied to a so-called pinion assist type electric power steering apparatus that applies the power of the electric motor 22 to the pinion shaft 8 of the steering shaft 2 to assist steering. You may do it.
　以上、本発明を具体的な態様により詳細に説明したが、上記の内容を理解した当業者は、その変更、改変及び均等物を容易に考えられるであろう。したがって、本発明は請求の範囲とその均等の範囲とするべきである。 Although the present invention has been described in detail by way of specific embodiments, those skilled in the art who have the above-mentioned content will be able to easily think of variations, modifications and equivalents. Therefore, the scope of the present invention should be within the scope of the claims and the equivalents thereof.
　１…ステアリングホイール、２…ステアリングシャフト、３…ステアリングコラム（支持部材）、４…コラムシャフト、６…インターミディエイトシャフト、８…ピニオンシャフト、９…ラックバー、Ａ…転舵機構、１４…アッパーシャフト、１４１…上端、１４２…下端、１４ａ…外周、１５…ロアーシャフト、１５１…上端、１５ａ…外周、１５ｂ…段部、１５ｃ…内周、１６…トーションバー、１９…ジャケット、２０…ハウジング、２１…エンドカバー、２２…電動モータ、２３…減速機構、２４…ウォーム軸（駆動ギヤ）、２５…ウォームホイール（被動ギヤ）、３３…第１の玉軸受、３４…第２の玉軸受、３６…第１のブッシュ（第１のシャフト間軸受）、３６Ａ…第１の針状ころ軸受（第１のシャフト間軸受）、３７…第２のブッシュ（第２のシャフト間軸受）、３７Ａ…第２の針状ころ軸受（第２のシャフト間軸受）、４０…ストッパ機構、４１…凹部、４２…凸部、１００…電動パワーステアリング装置（車両用操舵装置）、Ｂ…車体、Ｃ１…軸受中心、Ｘ１…軸方向 Reference Signs List 1 steering wheel 2 steering shaft 3 steering column (support member) 4 column shaft 6 intermediate shaft 8 pinion shaft 9 rack bar A steering mechanism 14 upper shaft , 141: upper end, 142: lower end, 14a: outer periphery, 15: lower shaft, 151: upper end, 15a: outer periphery, 15b: step portion, 15c: inner periphery, 16: torsion bar, 19: jacket, 20: housing, 21 ... end cover, 22 ... electric motor, 23 ... reduction mechanism, 24 ... worm shaft (drive gear), 25 ... worm wheel (driven gear), 33 ... first ball bearing, 34 ... second ball bearing, 36 ... First bush (first inter-shaft bearing), 36A: first needle roller bearing (first inter-shaft bearing), 37: second Bush (second inter-shaft bearing), 37A: second needle roller bearing (second inter-shaft bearing), 40: stopper mechanism, 41: recess, 42: protrusion, 100: electric power steering device (vehicle Steering device), B: vehicle body, C1: bearing center, X1: axial direction

Claims (4)

  1. 　中空の支持部材と、
    　上記支持部材を貫通し、トーションバーを介して同軸上に連結されたアッパーシャフトおよびロアーシャフトを含むステアリングシャフトと、
    　上記支持部材に保持され、上記アッパーシャフトの上端を回転可能に支持する第１の玉軸受と、
    　上記支持部材に保持され、上記ロアーシャフトを回転可能に支持する第２の玉軸受と、
    　上記ロアーシャフトに保持され、上記アッパーシャフトの下端を回転可能に支持する第１のシャフト間軸受と、
    　上記アッパーシャフトに保持され、上記ロアーシャフトの上端を回転可能に支持する第２のシャフト間軸受と、を備え、
    　上記第１のシャフト間軸受は、上記第２の玉軸受の軸受中心の径方向内方に配置された部分を含み、
    　上記第１のシャフト間軸受および上記第２のシャフト間軸受は、上記ステアリングシャフトの軸方向に離隔している車両用操舵装置。     A hollow support member,
    A steering shaft including an upper shaft and a lower shaft coaxially connected to each other through the support member and connected via a torsion bar;
    A first ball bearing held by the support member and rotatably supporting the upper end of the upper shaft;
    A second ball bearing held by the support member and rotatably supporting the lower shaft;
    A first inter-shaft bearing held by the lower shaft and rotatably supporting a lower end of the upper shaft;
    And a second inter-shaft bearing rotatably supported by the upper shaft and rotatably supporting the upper end of the lower shaft,
    The first inter-shaft bearing includes a portion disposed radially inward of the bearing center of the second ball bearing,
    A steering apparatus for a vehicle, wherein the first inter-shaft bearing and the second inter-shaft bearing are separated in the axial direction of the steering shaft.
  2. 　上記アッパーシャフトおよび上記ロアーシャフトの相対回転量を規制するストッパ機構を備え、
    　上記ストッパ機構は、軸方向に関して、上記第１のシャフト間軸受および上記第２のシャフト間軸受の間に配置されている請求項１に記載の車両用操舵装置。     A stopper mechanism that regulates the relative rotation amount of the upper shaft and the lower shaft;
    The vehicle steering system according to claim 1, wherein the stopper mechanism is disposed between the first inter-shaft bearing and the second inter-shaft bearing in an axial direction.
  3. 　上記第１のシャフト間軸受および上記第２のシャフト間軸受の少なくとも一方は、ブッシュを含む請求項１または２に記載の車両用操舵装置。 The vehicle steering apparatus according to claim 1, wherein at least one of the first inter-shaft bearing and the second inter-shaft bearing includes a bush.
  4. 　上記第１のシャフト間軸受および上記第２のシャフト間軸受の少なくとも一方は、針状ころ軸受を含む請求項１または２に記載の車両用操舵装置。                                                   The vehicle steering apparatus according to claim 1, wherein at least one of the first inter-shaft bearing and the second inter-shaft bearing includes a needle roller bearing.
PCT/JP2011/076189 2010-12-22 2011-11-14 Steering device for vehicle WO2012086338A1 (en)

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FR3013301B1 (en) * 2013-11-21 2017-02-17 Peugeot Citroen Automobiles Sa ELECTRIC SWITCH PLATE AND STEERING COLUMN OF A VEHICLE
KR101869160B1 (en) * 2016-10-10 2018-06-19 주식회사 만도 Electronic Power Steering System of Dual Torsion Bar

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JP2000002603A (en) * 1998-06-17 2000-01-07 Koyo Seiko Co Ltd Torque sensor
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JP2003048549A (en) * 2001-08-08 2003-02-18 Koyo Seiko Co Ltd Electric power steering device
JP2003182603A (en) * 2001-12-13 2003-07-03 Toyoda Mach Works Ltd Midpoint setting method for torque sensor

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EP1541299B1 (en) * 2002-07-03 2008-05-14 Nsk Ltd., Motor power steering system
CN1766359A (en) * 2004-10-25 2006-05-03 日本精工株式会社 Steering device

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JP2000002603A (en) * 1998-06-17 2000-01-07 Koyo Seiko Co Ltd Torque sensor
JP2002104213A (en) * 2000-09-29 2002-04-10 Koyo Seiko Co Ltd Power steering device
JP2003048549A (en) * 2001-08-08 2003-02-18 Koyo Seiko Co Ltd Electric power steering device
JP2003182603A (en) * 2001-12-13 2003-07-03 Toyoda Mach Works Ltd Midpoint setting method for torque sensor

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