WO2018068933A1 - Système de direction - Google Patents

Système de direction Download PDF

Info

Publication number
WO2018068933A1
WO2018068933A1 PCT/EP2017/070938 EP2017070938W WO2018068933A1 WO 2018068933 A1 WO2018068933 A1 WO 2018068933A1 EP 2017070938 W EP2017070938 W EP 2017070938W WO 2018068933 A1 WO2018068933 A1 WO 2018068933A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
steering system
gear nut
steering
bearing
Prior art date
Application number
PCT/EP2017/070938
Other languages
German (de)
English (en)
Inventor
Oliver Hetzel
Original Assignee
Robert Bosch Gmbh
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.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2018068933A1 publication Critical patent/WO2018068933A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • B62D5/0421—Electric motor acting on or near steering gear
    • B62D5/0424—Electric motor acting on or near steering gear the axes of motor and final driven element of steering gear, e.g. rack, being parallel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • B62D5/0442—Conversion of rotational into longitudinal movement
    • B62D5/0445—Screw drives
    • B62D5/0448—Ball nuts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact bearings
    • F16C23/04—Sliding-contact bearings self-adjusting
    • F16C23/043—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts
    • F16H2025/2445—Supports or other means for compensating misalignment or offset between screw and nut

Definitions

  • the invention relates to a steering system with a longitudinal axis axially displaceably mounted in a housing handlebar and with a steering motor, via a
  • Ball screw on the handlebar acts, including the handlebar forms in at least a portion of a ball screw, which cooperates with a drivable by the steering motor gear nut, wherein the gear nut is mounted by means of a bearing assembly in the housing.
  • Such a steering system can be designed in particular in the form of a power steering system, by which during steering a supporting torque is generated in order to reduce the applied by an operator on a steering column steering torque.
  • a power steering system is known for example from EP 2 049 383 B1.
  • the screw drive is designed in the form of a ball screw.
  • operation of such a power steering system may be due to lateral forces, with which the handlebar is charged due to their connection with the wheel steering levers steered wheels of an auxiliary power steering system integrating motor vehicle, a bending and / or inclination of the handlebar within the housing.
  • Ball screw must be compensated by a radial bearing over which the gear nut of the ball screw rotatably mounted within the housing, to always a low-friction drive of the handlebar by means of the
  • the radial roller bearing is supported with its outer ring on both sides of each elastic bearing ring.
  • the radial roller bearing is supported with respect to its longitudinal axial directions within the housing.
  • a power steering system is in each case known in which the pulley of a toothed belt drive with a sleeve-shaped bearing portion in a bearing assembly, which consist in particular of two shoulder ball bearings in a so-called O-arrangement can, is stored.
  • the gear nut of a ball screw is mounted within the bearing portion of the pulley, which is allowed by a spherical formation of the inner surface of the bearing portion of the pulley that the gear nut can tilt within limits within the bearing section.
  • a torque transmission between the pulley and the gear nut is realized by means of drivers, which u.a. may be formed of an elastomer.
  • DE 10 2005 015 756 A1 discloses a steering system in which a pivotability of a threaded nut of a ball screw by a curved configuration of the inner surface of an inner ring or the outer surface of an outer ring of a
  • Rolling by means of which the threaded nut is mounted in a housing of the steering system, is realized.
  • the curved inner surface or outer surface acts together with a correspondingly curved counter surface of the threaded nut or the housing.
  • a ball screw for a steering system of a motor vehicle in which a gear nut is pivotally mounted with the interposition of a sliding ring and a plurality of driving elements in an inner ring of a rolling bearing.
  • a pulley of a belt transmission is connected to the inner ring of the rolling bearing.
  • the driving elements cause a Transmission of torque from the pulley via the inner ring of the
  • the invention was based on the object in a generic steering system according to DE 10 201 1 1 17 723 A1 to improve the tiltability of the gear nut.
  • preferably also axially and radially as possible backlash-free storage of the gear nut can be realized within the housing.
  • a steering system is provided with a longitudinal axis axially displaceably mounted in a steering rod and a steering motor, wherein the steering motor acts via a ball screw on the handlebar, to which
  • Handlebar forms a recirculating ball screw in at least one section, the spherical driving elements with one of the steering motor drivable
  • Gear nut cooperates, the gear nut by means of a
  • An inventive steering system further comprises a traction mechanism, which serves to transmit a drive power which is generated by the preferably electric, possibly also hydraulic steering motor, to the gear nut and optionally to achieve a translation for the input speed and the drive torque.
  • the traction mechanism can be designed in particular in the form of a belt drive, with the belt drive being able to be designed both in a force-fitting manner (for example as a flat belt or V-belt drive) and in a primarily form-fitting manner (for example as a toothed belt drive).
  • Gear nut is transmissible, with the inner ring of a pivot bearing of
  • Gear is transmitted to the traction mechanism.
  • the connection of the gear to the inner ring of the pivot bearing should be at least so that a tilting of the axis of rotation of the gear relative to the longitudinal axis of the inner ring
  • a torque transmitting connection may be provided but is not functionally required. Particularly preferred, among other things, because such a constructive is particularly easy to implement, a rigid, i. completely immobile connection between the gear and the inner ring of the
  • the invention provides that the gear is connected by means of a (preferably permanently connecting or not functionally openable) torque-transmitting coupling with the gear nut, wherein the clutch is further preferably designed such that a tilting of the
  • Gear nut is possible relative to the gear.
  • Bearing arrangement is therefore not limited by the fact that a transfer of torque between the inner ring of the pivot bearing and the gear nut ensuring carrier elements must be integrated into the pivot bearing.
  • the coupling is designed such that a tilting of the gear nut relative to the gear due to an elastic deformation of a deformation element is possible.
  • a deformation element advantageously allows both the intended possibility of tilting the
  • Torque of the gear on the gear nut which may also be free of play, causing unwanted noise, especially in a
  • the clutch can also be made for the clutch to be designed as a dog clutch with intermeshing claws of the gear wheel and the gear nut.
  • an elastic is provided between claws of the gear wheel and the gear nut
  • the claws of the gear nut can also be formed by a (preferably annular) jaw element, which is connected to at least torque-transmitting and preferably rigidly connected to a base body of the gear nut.
  • a (preferably annular) jaw element which is connected to at least torque-transmitting and preferably rigidly connected to a base body of the gear nut.
  • Gear nut can preferably be achieved in that the jaw member is annular and is mounted on a shaft portion of the body.
  • a torque transmitting connection between the jaw member and the body can then by means of one or more, in wells of a Inner surface of the jaw member and an outer surface of the shaft portion arranged driving elements, which may be formed for example in the form of dowel pins and in particular in the form of heavy tension pins, be realized.
  • the preferably annular claw element is attached to an end face at a longitudinal axial end of the base body.
  • an embodiment of the clutch can also be provided such that it exerts a tilting moment on the gear nut. This can serve to suppress by a "tilting" of the handlebar inside the gear nut with the interposition of the balls of the ball screw relative movement between the handlebar and the gear nut, which may be justified in particular by a movement excitation of the handlebar in the operation of a motor vehicle comprising the steering system This can prevent the spherical
  • a particularly advantageous in terms of design possibility for generating such a tilting moment may be that a coupling element of the clutch is arranged eccentrically with respect to the main body of the gear nut. Particular preference may be provided that at a
  • the coupling designed as a dog clutch comprises a (preferably annular) jaw member
  • the center of the (annular) jaw member is radially spaced relative to the longitudinal axis of the body, resulting in an eccentricity of the jaw member with respect to the base body. This eccentricity causes in conjunction with an axial distance to at least a portion of the gear nut
  • the bearing assembly is supported axially with the interposition of at least one spring element on the housing and two axially spaced pivot bearing comprises, the inner rings on an outer surface of the
  • Gear nut are movably guided, wherein the (inner surfaces of) the inner rings of the pivot bearing and / or the (outer surface of the) gear nut (at least partially) curved (in particular part spherical) is / are formed to form a pivot bearing.
  • the curvatures are in particular designed such that they extend with respect to a along the longitudinal axis of the handlebar
  • Such a steering system allows a structurally relatively simple manner a rotatable mounting of the tiltable within limits gear nut inside the housing, the bearing is substantially free of play with respect to both the direction along the longitudinal axis of the gear nut and radially thereto.
  • Spring element for example in the form of an annular wave spring or
  • Disk spring may be formed, (directly or indirectly) are supported on the housing.
  • pivot bearing preferably single row
  • Angular contact ball bearings and in particular shoulder ball bearings are. These can further preferably be arranged in an X-arrangement, whereby a secure transmission of the axial load by the spring or the elements of the outer rings can be ensured on the inner rings, which then leads to the desired loading of the inner rings to each other, through which the backlash the storage of the
  • Gear nut is ensured in the bearing assembly. At the same time thereby also advantageously a far backlash of the elements that make up the pivot bearing, realized.
  • a steering system in a further preferred embodiment of such a steering system according to the invention can also be provided that formed in the region of the pivot bearing between the inner surfaces of the inner rings and the outer surface of the gear nut (in the region of the curvature (s)) at least one sliding element, for example in the form of a sliding film can be arranged.
  • the sliding element or the sliding film may preferably be (at least partially) made of plastic and in particular comprise PTFE.
  • Ball screw can also be kept low.
  • the steering system according to the invention can preferably be designed as a power steering system and thus allow a via a steering handle (eg steering wheel) and preferably with the interposition of a steering column transmitted to a steering gear, manually generated steering torque to be superimposed by a steering torque generated by the steering motor to the height of the to limit the steering torque required to be steered manually.
  • the steering gear can in particular one with one of the handlebar in a section trained toothing cooperating steering pinion.
  • the steering pinion may be formed, for example, as a straight, helical or helical spur gear, with a trained as a rack section of the
  • Handlebar cooperates.
  • the steering system may also be designed such that the steering motor provides all the drive power required for steering.
  • the invention also relates to a motor vehicle, in particular a wheel-based vehicle
  • Motor vehicle preferably a car or truck, with a steering system according to the invention.
  • FIG. 1 shows a first embodiment of a steering system according to the invention in a partial longitudinal section
  • FIG. 2 shows a cross section through the steering system along the sectional plane II-II in FIG. 1;
  • Ball screw bearing for the ball screw and pulley of the steering system in a perspective view
  • 6 is an exploded view of a combination of ball screw
  • FIG. 8 is a side view of a partial longitudinal section through a combination of handlebar, ball screw, bearing for the ball screw and pulley of the steering system for a second embodiment of a steering system according to the invention.
  • 10 is a front view of the combination of handlebar, ball screw,
  • Fig. 1 1 in a perspective view an exploded view of a
  • Fig. 1 shows a first embodiment of an inventive
  • Steering system which is designed as a power steering system.
  • the steering system for this purpose comprises a multi-part, substantially tubular housing 1, within which a handlebar 2 longitudinal axial, i. along her
  • the steering rod 2 is connected to a ball joint (not shown), wherein the ball joints in turn the connection with a respective wheel steering lever (not shown) are used.
  • the wheel steering levers translate a longitudinal axial movement of the handlebar 2 in a pivoting of steered wheels (not shown) of a motor vehicle.
  • a longitudinal axial movement of the handlebar 2 is caused on the one hand by the generation of a rotational movement of a steering handle (not shown), in particular a steering wheel of the motor vehicle, said rotational movement of the steering handle via a steering column (not shown) on a steering pinion (not visible), the Part of a steering gear 3 of the steering system is transmitted.
  • the steering pinion can interact with a section of the steering rod 2 designed as a toothed rack, in order to translate the rotational movement of the steering pinion into a translational movement of the steering pinion
  • Handlebar 2 to translate along its longitudinal axis 4.
  • a longitudinal axial movement of the handlebar 2 can further by the generation of an auxiliary steering torque by means of a steering motor 5, in the present
  • Embodiment is electrically formed, be effected.
  • the drive power of the steering motor 5 is u.a. by means of a screw drive in the form of a
  • Thread groove cross-section forms.
  • Section of the ball screw 7 are a variety of spherical
  • transmission elements 8 Also arranged within transmission elements 8 transmission elements
  • Partial circular cross-sections having grooves of a ball screw thread are received, which are formed on the inside of a base body 14 of a gear nut 9 of the ball screw 6.
  • Ball screw 6 is due to a corresponding storage in a
  • Bearing arrangement rotatably, but at the same time substantially integrated with respect to their longitudinal axial directions in the housing 1.
  • Gear nut 9 is carried out with the interposition of a further gear stage, which is formed in the embodiment shown in the form of a belt drive, including the gear nut 9 with a first gear (pulley) 10 rotatably or torque-transmitting connected.
  • the first pulley 10 is partially surrounded by a belt 1 1, for example, a toothed or flat belt, wherein the belt 1 1 via a second gear 12, which is non-rotatably connected to an output shaft 13 of the steering motor 5, out.
  • Kugelgewindetriebs 6 a relatively large potential for a bending deflection of the ends of the handlebar 2.
  • Such bending deflection can optionally be kept as small as possible that the handlebar 2 is additionally mounted in the vicinity of the longitudinal axial ends of the housing 1 and thereby radially supported. Nevertheless, a relevant inclination or tilting of the handlebar 2 in the region of the gear nut 9 of the ball screw 9 can not always be avoided.
  • gear nut 9 In order to ensure a possible low-friction operation of the ball screw 9 even with such an inclined position of the handlebar 2 in the field of gear nut 9, the gear nut 9 should also be in a corresponding
  • Tilt can be tilted. At the same time by means of storage of
  • both the bearing assembly as free of play as possible in longitudinal axial and radial direction within the housing 1 and the gear nut 9 should be added according to backlash within the bearing assembly.
  • the bearing arrangement comprises two pivot bearings 15 in the form of single-row shoulder ball bearings, which have an X arrangement (position of the pressure centers of the pivot bearings 15 between the pivot bearings 15), a defined distance being provided between the pivot bearings 15.
  • Inner rings 16 of the pivot bearing 15 are further each such curved (with matching radii of curvature) formed that form both pivot bearings 15 in combination with their gear nut 9 facing inner surfaces a part-spherical pivot bearing receptacle in which a likewise part-spherical pivot bearing portion of the correspondingly curved (with to the curvatures of the inner rings 16 of the pivot bearing 15th
  • a pivot bearing 17 is formed by the pivot bearings 15 and the gear nut 9, which in principle both a rotation about the longitudinal axis 4 of the gear nut 9 as also within limits tilting about all axes, which are aligned radially with respect to this longitudinal axis 4 allows.
  • the two pivot bearings 15 in the unloaded state at a defined distance from each other by means of a
  • Retaining element 20 is connected, however, which hinder the intended for the achievement of backlash load or movement of the pivot bearing 15 to each other by means of the spring elements 19 to a relevant extent.
  • Gear nut trained swivel bearing 17 to ensure a low-friction as possible tilting of the gear nut 9 within the bearing assembly is disposed in the region of the pivot bearing 17 between the inner surfaces of the inner rings 16 of the pivot bearing 15 and the outer surface of the gear nut 9 each have a sliding member 21 in the form of a sliding film.
  • the sliding elements 21 form on each other facing a radially oriented portion 33 which is intended to engage in the space between the inner rings 16 of the pivot bearing 15. This prevents the sliding elements 21 when tilting the
  • Inner surfaces of the sliding elements 21 are provided.
  • the design of the formed between the bearing assembly and the nut 9 pivot bearing 17 allows despite the backlash, which is particularly advantageous for quiet operation of the steering system, a pivoting or tilting of the gear nut 9, which, because it is not based on an elastic deformation of a deformation element, is largely free of restoring moments, whereby a relatively low-friction function of the ball screw 6 can be ensured even when the handlebar 2 in the of the gear nut 9th
  • Such an inclination or such a tilting of the handlebar 2 and the gear nut 9 should not be transferred to the first gear 10 of the belt drive, because this can adversely affect the ability to transmit relatively high drive power and / or the load on the belt drive and in particular can increase the belt 1 1.
  • For the first gear 10 is therefore always a possible parallel arrangement of its axis of rotation 22 to the
  • Screws 23 are provided, which are guided through through holes in claws 24 which are arranged on the inside of the hollow first gear 10, and screwed into corresponding internal thread of the inner ring 16 of the adjacent rotary bearing 15 (see, in particular Fig. 3 and 6).
  • the tiltable mounting of the gear nut 9 within the bearing arrangement formed by the two pivot bearings 15 is such that a transmission of a torque in relevant height between the
  • This clutch is designed as a dog clutch and, in addition to the already mentioned claws 24, which are arranged on the inside of the hollow first gear 10, still claws 25 of the gear nut 9, of an annular claw member 26 (see, in particular Fig. 6 and 7). are trained, that
  • the connection between the annular claw element 26 and the main body 14 of the gear nut 9 is realized in that the annular claw member 26 is mounted with its inside on a axially spaced from the curved pivot bearing portion arranged shaft portion of the base body 14. Furthermore, both in the inside of the jaw member 26 and in the outside of the
  • Recesses 28 of the body 14 can be brought.
  • the thus formed cavities serve to receive a respective entrainment element 29 in the form of a (slotted in the longitudinal direction) tension pin, wherein the dowel pins are slightly radially deformed when inserted into the cavities, so that by the elastic and widening acting restoring action of the dowel pins a substantially backlash-free connection between the claw member 26 and the shaft portion of the
  • Basic body 14 of the gear nut 9 is realized (see, in particular Fig. 4 to 6).
  • the gear nut 9 should be tiltable, while such tilting of the gear nut 9 is not on the first
  • Gear 10 is to be transmitted.
  • the coupling element 35 of the gear nut 9 further comprises an annular
  • Deformation member 30 comprising a plurality of deformation elements 31, of which each for arrangement between adjacent contact surfaces of the jaws 24, 25 of the first gear 10 and the jaw member 26 is provided under elastic bias.
  • the deformation elements 31 allow due to their elastic deformability a defined relative movement between the jaws 24, 25 and in particular also such a relative movement resulting from a tilting of the gear nut 9 relative to the pivot bearings 15 and thus also relative to the first gear 10. As a result of their elastic bias prevent the
  • Deformation elements 31 connected to each other via a respective connecting portion 32, which is made possible to handle the deformation member 30 and thus all the deformation elements 31 as a coherent (possibly also one-piece) component.
  • the claw member 26 is formed such that the inner surface thereof is slightly eccentric with respect to an outer surface of the claw member 26. This eccentricity causes in conjunction with an axial distance to the portion of the formed by the gear nut 9 recirculating ball screw in which the
  • Spherical transmission elements 8 are arranged, the generation of a force acting on the gear nut 9 tilting moment- This serves, by a "tilting" of the handlebar 2 within the gear nut 9 with the interposition of
  • Transmission elements 8 a relative movement between the handlebar 2 and the gear nut 9, which may be due in particular by a movement excitation of the handlebar 2 in the operation of a motor vehicle comprising the steering system to suppress, thereby preventing the spherical
  • Ball screw thread of the handlebar 2 and the gear nut 9 are moved back and forth, which otherwise could lead to unwanted noise.
  • the second embodiment according to FIGS. 8 to 12 is basically characterized by a higher functional integration, which is reflected in a significantly reduced number of parts.
  • a co-operating with a handlebar 2 ball screw 6 is provided, wherein the ball screw 6 includes a gear nut 9 with a main body 14.
  • the main body 14 forms in a pivot bearing portion a partially spherical curved outer surface which cooperate with correspondingly part-spherically curved inner surfaces of inner rings 16 of two pivot bearings 15 (single row ball bearings having an X arrangement) to form a pivot bearing 17, the limited tilting of the Gear nut 9 due to a corresponding
  • Gear nut 9 facing inner sides each have a centrally disposed (with respect to the longitudinal axial ends), circumferentially and radially aligned portion or projection 33 (see Fig. 1 1), which is provided in a complementary circumferential recess 34 in the pivot bearing portion of
  • Inner surfaces of the inner rings 16 of the pivot bearing 15 takes place, while this in the first embodiment according to FIGS. 1 to 7 between the inner surfaces of the local sliding elements 21 and the outer surface of the local base body 14 of
  • Gear nut 9 takes place.
  • Main body 14 of the gear nut 9 can be omitted (this thus
  • Manufacturing costs for a steering system according to the invention are kept low.
  • the coupling element 35 comprises the substantially annular jaw member 26 which circumferentially in uniform pitch forms a plurality of jaws 25, which for cooperation with jaws 24, which are arranged on the inner surface of the (first) gear 10, are provided by the claws 24, 25 of the jaw member 26 and the first gear 10 engage with each other.
  • deformation elements 31 which are each arranged on both sides (in the circumferential direction) to each of the claws 25 of the jaw member 26 thereafter.
  • a production of the coupling element 35 can be carried out in an advantageous manner by 2-component injection molding, wherein in an injection molding process, the jaw member 26 may be formed of, for example, a thermoplastic material and the deformation elements 31 connected to the jaw member 26 made of an elastomer.
  • the coupling element 35 is additionally provided by means of
  • Fixing fasteners 37 (such as screws or dowel pins) to a longitudinal axial end face of the main body 14 of the gear nut 9, wherein
  • a defined eccentricity between the coupling element 35 and the base body 14 of the gear nut 9 is provided (see Fig. 10) to realize the already described for the first embodiment of FIGS. 1 to 7 generating a force acting on the gear nut 9 tilting moment ,
  • the coupling element 35 further has the function of a cover for the
  • the coupling element 35 also forms a guide portion 39 which engages in a corresponding recess of the base body 14 and part of a return for the
  • the main body 14 is closed by a separate cover 38, even in the second embodiment, but in this case as well
  • Coupling element 35 by means of several (specifically three) fasteners 37 (eg screws or dowel pins) is attached to the base body 14, whereas in the first embodiment, a snap ring 36 is provided for this purpose.
  • fasteners 37 eg screws or dowel pins

Landscapes

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

Abstract

Système de direction comprenant une barre de direction (2) montée de manière à pouvoir coulisser axialement dans le sens longitudinal dans un carter (1) et un moteur de direction (5) qui agit sur la barre de direction (2) par l'intermédiaire d'une vis à billes (6), la barre de direction (2) formant à cet effet dans au moins une partie un filetage à circulation de billes (7) qui coopère, par l'intermédiaire d'éléments de transmission sphériques (8), avec un écrou de transmission (9) pouvant être entraîné par le moteur de direction (5), l'écrou de transmission (9) étant monté dans le carter (1) au moyen d'un ensemble palier, une roue de transmission (10) d'une transmission à lien souple, au moyen de laquelle une puissance d'entraînement du moteur de direction (5) peut être transmise à l'écrou de transmission, étant reliée à une bague intérieure (16) d'un palier rotatif (15) de l'ensemble palier. Un tel système de direction est caractérisé en ce que la roue de transmission (10) coopère avec l'écrou de transmission (9) de manière à transmettre le couple au moyen d'un accouplement.
PCT/EP2017/070938 2016-10-12 2017-08-18 Système de direction WO2018068933A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016119367.4 2016-10-12
DE102016119367.4A DE102016119367A1 (de) 2016-10-12 2016-10-12 Lenksystem

Publications (1)

Publication Number Publication Date
WO2018068933A1 true WO2018068933A1 (fr) 2018-04-19

Family

ID=59649725

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/070938 WO2018068933A1 (fr) 2016-10-12 2017-08-18 Système de direction

Country Status (2)

Country Link
DE (1) DE102016119367A1 (fr)
WO (1) WO2018068933A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110901753A (zh) * 2019-12-16 2020-03-24 北京理工大学 一种带中位自锁功能的后轮线控转向器及其控制方法
US20210362772A1 (en) * 2020-05-25 2021-11-25 Robert Bosch Gmbh Steering System
US20210362773A1 (en) * 2020-05-25 2021-11-25 Robert Bosch Gmbh Steering System

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019201933A1 (de) * 2019-02-14 2020-08-20 Robert Bosch Gmbh Lenksystem

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2188890A (en) * 1986-04-11 1987-10-14 Honda Motor Co Ltd Motor-driven power steering system for vehicles
WO2002076808A1 (fr) * 2001-03-28 2002-10-03 Continental Teves Ag & Co.Ohg Dispositif d'entrainement d'un module de direction d'essieu de vehicule et systeme electromecanique de direction de vehicule
DE102005015756A1 (de) 2005-04-06 2006-10-12 Zf Lenksysteme Gmbh Lenkung
DE102006037479A1 (de) * 2006-08-10 2008-02-14 Zf Lenksysteme Gmbh Servolenkung
DE102007057391A1 (de) * 2006-12-01 2008-06-05 Zf Lenksysteme Gmbh Zahnstangen-Hilfskraftlenkung
DE102009020554A1 (de) * 2009-05-08 2010-11-11 Thyssenkrupp Presta Ag Kugelgewindetrieb mit sphärischer Lagerung
DE102011117723A1 (de) 2011-11-07 2013-05-08 Thyssenkrupp Presta Ag Kugelgewindetrieb mit Lagerausgleich
DE102011056025A1 (de) 2011-12-05 2013-06-06 Zf Lenksysteme Gmbh Kugelgewindetrieb
DE102011056031A1 (de) 2011-12-05 2013-06-06 Zf Lenksysteme Gmbh Kugelgewindetrieb
DE102014006469B3 (de) * 2014-05-06 2015-07-02 Thyssenkrupp Presta Ag Lager für einen Kugelgewindetrieb

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2188890A (en) * 1986-04-11 1987-10-14 Honda Motor Co Ltd Motor-driven power steering system for vehicles
WO2002076808A1 (fr) * 2001-03-28 2002-10-03 Continental Teves Ag & Co.Ohg Dispositif d'entrainement d'un module de direction d'essieu de vehicule et systeme electromecanique de direction de vehicule
DE102005015756A1 (de) 2005-04-06 2006-10-12 Zf Lenksysteme Gmbh Lenkung
DE102006037479A1 (de) * 2006-08-10 2008-02-14 Zf Lenksysteme Gmbh Servolenkung
EP2049383A1 (fr) * 2006-08-10 2009-04-22 ZF-Lenksysteme GmbH Direction assistée
EP2049383B1 (fr) 2006-08-10 2009-12-16 ZF-Lenksysteme GmbH Direction assistée
DE102007057391A1 (de) * 2006-12-01 2008-06-05 Zf Lenksysteme Gmbh Zahnstangen-Hilfskraftlenkung
DE102009020554A1 (de) * 2009-05-08 2010-11-11 Thyssenkrupp Presta Ag Kugelgewindetrieb mit sphärischer Lagerung
DE102011117723A1 (de) 2011-11-07 2013-05-08 Thyssenkrupp Presta Ag Kugelgewindetrieb mit Lagerausgleich
DE102011056025A1 (de) 2011-12-05 2013-06-06 Zf Lenksysteme Gmbh Kugelgewindetrieb
DE102011056031A1 (de) 2011-12-05 2013-06-06 Zf Lenksysteme Gmbh Kugelgewindetrieb
DE102014006469B3 (de) * 2014-05-06 2015-07-02 Thyssenkrupp Presta Ag Lager für einen Kugelgewindetrieb

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110901753A (zh) * 2019-12-16 2020-03-24 北京理工大学 一种带中位自锁功能的后轮线控转向器及其控制方法
US20210362772A1 (en) * 2020-05-25 2021-11-25 Robert Bosch Gmbh Steering System
US20210362773A1 (en) * 2020-05-25 2021-11-25 Robert Bosch Gmbh Steering System
US11866105B2 (en) * 2020-05-25 2024-01-09 Robert Bosch Gmbh Steering system
US11945520B2 (en) * 2020-05-25 2024-04-02 Robert Bosch Gmbh Steering system

Also Published As

Publication number Publication date
DE102016119367A1 (de) 2018-04-12

Similar Documents

Publication Publication Date Title
WO2018068932A1 (fr) Système de direction
EP1733155B1 (fr) Servomoteur
DE102011003485B4 (de) Kugelgewindetrieb und damit ausgestattete Lenkeinrichtung
EP2694355B1 (fr) Servodirection électromécanique comportant un compensateur de jeu pour l'engrenage à vis sans fin
EP3475146B1 (fr) Mécanisme de vis-écrou à billes d'une direction assistée électromécanique comportant des corps de déviation pour un retour des billes
WO2018068933A1 (fr) Système de direction
EP2283979A2 (fr) Outil manuel doté d'un entraînement par oscillations
WO2013152996A1 (fr) Palier libre pour mécanisme de direction
DE19508708C2 (de) Lenksystem mit variablem Lenkwinkelverhältnis
EP2345569B1 (fr) Engrenage hypoïde pour une direction d'un véhicule automobile
WO2004035996A1 (fr) Dispositif de deplacement
WO2020164774A1 (fr) Système de direction
WO2018095639A1 (fr) Mécanisme de direction et système de direction
DE19933875B4 (de) Linearwälzlager zum Übertragen von Drehmomenten
EP2669155B1 (fr) Entraînement de rangement pour remorque avec engrenage doté d'un agencement d'axes non parallèles
WO2013083538A1 (fr) Vis à billes
EP1032522B1 (fr) Mecanisme de commande a moteur electrique pour systeme de direction de vehicule
WO2018091200A1 (fr) Système de direction
DE10327090A1 (de) Gelenkbeschlag für eine Verstellvorrichtung eines Kraftfahrzeugsitzes
EP2255104A1 (fr) Boîte de vitesses
DE102012103857A1 (de) Vorrichtung zum Andrücken einer Schnecke oder eines Schraubritzels an ein Schneckenrad oder an ein Schraubrad
EP2530260B1 (fr) Arbre d'embrayage, actionneur, boîte de vitesses à dispositif de réglage d'arbre à came et régulateur de l'arbre à came
WO2021089212A1 (fr) Dispositif d'actionnement de piston
WO2006058743A1 (fr) Transmission
DE69216242T2 (de) Antrieb mit variabler drehzahl, insbesondere für fahrzeuge

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17754171

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17754171

Country of ref document: EP

Kind code of ref document: A1