WO2011015374A1 - Direction assistée avec bague de palier pré-tendue et divisée - Google Patents

Direction assistée avec bague de palier pré-tendue et divisée Download PDF

Info

Publication number
WO2011015374A1
WO2011015374A1 PCT/EP2010/004841 EP2010004841W WO2011015374A1 WO 2011015374 A1 WO2011015374 A1 WO 2011015374A1 EP 2010004841 W EP2010004841 W EP 2010004841W WO 2011015374 A1 WO2011015374 A1 WO 2011015374A1
Authority
WO
WIPO (PCT)
Prior art keywords
power steering
steering system
rolling bearing
ring
spring
Prior art date
Application number
PCT/EP2010/004841
Other languages
German (de)
English (en)
Inventor
Helmut Bareis
Rainer SCHÄNZEL
Gerd Speidel
Alexander VÄHNING
Andreas Lay
Original Assignee
Zf Lenksysteme 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
Priority claimed from DE102009036303A external-priority patent/DE102009036303A1/de
Priority claimed from DE102010002892A external-priority patent/DE102010002892A1/de
Application filed by Zf Lenksysteme Gmbh filed Critical Zf Lenksysteme Gmbh
Publication of WO2011015374A1 publication Critical patent/WO2011015374A1/fr

Links

Classifications

    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing

Definitions

  • the invention relates to a power steering, in particular an electrical
  • Power steering system for a vehicle with a, driven by a servomotor motor screw from a substantially axially immovably mounted in a frame nut, according to the preamble of claim 1.
  • the DE 103 10 492 A1 shows and describes an electric power steering wherein a servo motor drives an axially displaceable component that with his
  • Ball screw is in engagement with a nut thread of an axially fixed in a frame mounted nut.
  • the nut is connected to a pulley of a traction mechanism between the servomotor and the thus formed
  • Motion screw rotatably connected.
  • the nut is supported and mounted on the frame via a radial bearing.
  • the radial bearing is formed as a rolling bearing and in particular as a four-point bearing, since in particular axial forces are to be absorbed.
  • Tolerances may occasionally cause rattling noises at the beginning of a power steering operation, until a steady state blow is achieved
  • Heating the components of the bearing ultimately sets the design specified operating clearance.
  • the bearing clearance is unfavorably small in relation to the bearing friction.
  • the rolling bearing can not always sufficiently offset on a shaft mounted therewith bending moments by a misalignment so that a low pivoting moment results and jamming of the shaft is avoided.
  • the known rolling bearing types are not always able to prevent noise in the specific operating range in a power steering system.
  • the invention has for its object to provide a power steering, the operating noise is minimized, in particular their bearings a radial play and
  • BESTATIGUNGSKOPIE Axial play does not rise above the operating clearance under the influence of ambient temperatures of the rolling bearing.
  • a power steering is provided, which is able to adjust the bearing clearance in the rolling bearing to the current operating temperature, or to allow a constant bearing clearance over the operating temperature.
  • the inner ring or the outer ring or both bearing rings of the bearing are radially biased in a defined manner, preferably by dividing the inner ring and the ring halves of the inner ring are axially clamped against each other.
  • the ring halves or parts of the inner ring are pressed by the spring element against each other and the rolling elements pressed slightly radially to the outer ring, or with the desired operating clearance between the
  • Inner ring parts or inner ring halves held. A perfect compensation of thermal expansion of the bearing rings and a constant operating clearance of the bearing is effected. Disturbing operating noise does not occur.
  • the inner ring of the rolling bearing is divided into two ring halves and spring-loaded against each other by a plurality of axially acting on both ring halves spring elements.
  • the outer ring of the rolling bearing is divided into two ring halves and spring-loaded against each other by a plurality of spring elements axially acting on both ring halves
  • the spring elements or the spring element may be formed of an elastomeric material or of a metallic material such as spring steel.
  • Spring elements may be, for example helical compression springs, which are arranged at intervals to each other around the circumference of the ring halves, between the component, which acts as a frame for the shaft to be supported, and the end faces of the
  • the helical compression springs spring the ring halves of the
  • one or more spring elements may be provided which engage or pass through axially guided openings in the ring halves or are otherwise secured to the ring halves in a suitable manner so that they are spring-loaded against each other by the tensile force of the spring elements.
  • This embodiment of the rolling bearing has the advantage that the respective ring halves are fixed to the other components of the bearing and the rolling bearing is easy to handle and assemble.
  • the respective ring halves of the inner or outer ring are preferably constructed symmetrically with respect to the parting plane.
  • the rolling elements of the rolling bearing are formed as balls and form a deep groove ball bearing or a four-point bearing.
  • the ring halves are axially sprung in a particularly preferred embodiment with the aid of one or two disc springs.
  • the disc springs may be slotted radially over a portion of their width to define the spring rate.
  • radially guided slots may be guided from their inner peripheral edge over part of their width.
  • the disc springs can thus partially or completely take over the task of bearing washers.
  • the installation tolerances of the ring parts or halves together with disc springs and the axial gap between the ring parts or - halves can be chosen so that in a cold state in which the power steering is not in operation, the disc springs almost block on the ring halves or - share and axial stops come to rest.
  • the rims of the split inner or outer ring may be higher than the undivided ring.
  • the rolling bearing can receive a larger pressure angle.
  • Fig. 1 is a partial longitudinal section through a steering gear of a
  • FIG. 2 is an enlarged view of an embodiment of a
  • Fig. 4 is an illustration of only the storage area of an embodiment with
  • Fig. 1 a partial longitudinal section through a power steering system formed as an electric power steering system 1 for a passenger car is shown. basics
  • Components of the power steering 1 are formed as a closed steering gear housing 22 frame 4 made of die-cast aluminum.
  • the steering gear housing 22 has a radial flange on which an electric servomotor 2 is screwed by means of bolts.
  • the electric servomotor 2 serves to provide a
  • the rack 24 shows an axially displaceable component 6 in the steering gear housing 22.
  • articulated tie rods are set, which are used with wheel steering steered wheels of the passenger car for steering angle adjustment of the wheels at an axial displacement of the rack 24.
  • the threaded portion 23 of the rack 24 is with its thread 7 with a female thread 8 of a nut 5 in engagement.
  • the nut 5 is formed as a ball nut 25 or ball nut.
  • a driven by the electric servomotor 2 motion screw 3 is formed.
  • the ball nut 25 is around the
  • Threaded portion 23 rotatably mounted in the frame 4, but arranged axially largely immovable.
  • the ball nut 25 is axially and radially mounted on a bearing ring formed as an inner ring 10 and a bearing ring formed as an outer ring 26 of a rolling bearing 9 in the frame 4 or steering gear housing 22.
  • the rolling bearing 9 is formed as a deep groove ball bearing 21.
  • the outer ring 26 of the rolling bearing 9 is between two axial stops forming bearing plates 27, 28 in one
  • Servomotor 2 is operatively connected via a traction mechanism with the nut 5, wherein a belt formed as a toothed belt 30 runs on a pulley 31 on the nut 5.
  • the pulley 31 is formed in the manner of a stepped cylindrical sleeve. It is with its, the rolling bearing 9 facing end 32 to a peripheral bead
  • the peripheral bead 33 forms a stop for the inner ring 10 and the ring portion 13 of the inner ring 10.
  • a nut 34 which is turned on an outer peripheral surface of the ball nut 25, forms a stop 33 opposite the stop 34 for the inner ring, whose construction in Described in more detail below.
  • the belt 30 also runs on one
  • Pulley 36 which is rotatably connected to a motor shaft of the electric servomotor 2, from.
  • the servo motor 2 is driven by a control and / or regulating device, not shown, in accordance with sensor signals which represent a desired steering angle and a wheel steering angle. It can be operated with pulse width modulation. As a result, the ball nut 25 is rotated in one direction or the other and the rack 24 is displaced in one or the other direction. On the ball nut 25, on the other hand, axial forces derived from the wheel reaction forces are introduced. In addition, resulting in steering movements on a steering handle in one or the other direction changing axial forces on the ball nut 25, which act on the rolling bearing 9. At the beginning of operation, the outer ring 26 of the heated
  • Rolling bearing 9 first, since heat usually from an engine room in which the steering gear housing 22 is mounted, first from the outside to the
  • Steering gear housing 22 and the housing cover 29 is blasted.
  • the inner ring 10 is divided along a centrally extending in the radial direction of the rolling bearing 9 dividing plane 11 in two symmetrically to this parting plane 11 formed ring parts or ring halves 12,13.
  • Ring halves 12,13 parallel to each other and arranged at an axial distance a to each other so that the ring halves 12,13 axially on the parting plane 11 can be pushed to and away.
  • the ring halves 12,13 are spring-loaded against each other by spring elements 14 formed as disc springs 17.
  • the disc springs 17 in the embodiments in Figures 1 to 3 are in the cold state
  • Power steering 1 built almost block and have a spring force of about 100 N to 200 N, with each of which they each spring the ring halves 12,13 against each other.
  • the axial distance a of the ring halves 12, 13 remains, as shown in particular in FIG. 2, approximately at its maximum dimension.
  • the disc springs 17 have one
  • Inner ring 10 corresponds.
  • the outer radius r is larger than the largest
  • the plate spring 17 in the embodiment shown in FIG. 3 has from its inner peripheral edge 18 radially star-shaped around the entire circumference of the respective plate spring 17 slots 19, which protrude over half the width of the plate spring 17 and formed against notch effect, semicircular ends 40 have.
  • the ring halves 12,13 of the inner ring 10 each form a partial track for balls 41 of the rolling bearing 9 and are at the axial distance shown a to the balls.
  • the inner ring 10 is like described split and the ring parts or in the embodiment shown, the ring halves 12,13 are axially spring-loaded. This makes it possible that when the outer ring 26 heats up, the inner ring halves 12, 13 can axially move towards one another and the distance dimension a is slightly reduced. The balls 41 are thereby guided without play, at least by the inner ring 10, until both rings 10,26 of the rolling bearing 9 have approximately the same temperature and the constructive provided tolerance position of the two rings 10, 26 is taken. The distance a is again increased slightly.
  • disc springs 17 as spring elements for the ring halves
  • the disc springs 17 may come to rest in circumferential notches on the nut 5, so that a simple mounting option and a cohesion of the ring halves 12,13 may result during assembly on the nut 5.
  • Figure 4 shows a deep groove ball bearing 21, which is supported with an outer ring 26 on a frame 4, a housing wall of the steering gear housing.
  • the outer ring 26 is held in an inner circumferential groove 4 'with a rectangular, U-shaped cross-section.
  • Inner circumferential groove 4 ' has approximately a depth corresponding to the thickness of the outer ring 26.
  • the inner circumferential groove 4 ' is wider than the roller bearing 9 and its outer ring 26.
  • the outer ring 26 of the rolling bearing 9 is symmetrical to a parting plane 11 arranged at an angle of 90 ° to a longitudinal axis of the rolling bearing 9 in two ring parts 12, 13 shared.
  • the ring parts 12, 13 each form one
  • the ring parts 12, 13 are provided with spring elements 14 which are shown in FIG.
  • the inner ring 10 is axially immovable by suitable securing elements, such as snap rings 42 at its two end faces the shaft 6 or ball nut 25 is held.
  • the roller bearing 9 is supported on the respective component of the steering system, such as a ball nut 25 and can tilt relative to the ball nut 25 under the influence of bending moments about on a cross-ball nut 25 spindle without jamming in any way ,

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)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne une direction assistée (1), en particulier une direction assistée électrique pour un véhicule, comprenant une vis de déplacement (3) entraînée par un servomoteur (2) et constituée d'un écrou (5) monté dans un bâti (4) très largement non déplaçable axialement et d'un composant (6) déplaçable axialement, dont le filetage (7) est en prise avec un filetage (8) de l'écrou (5), et un palier de roulement (9) pour la fixation axiale et radiale de l'écrou (5) dans le bâti (4). Pour créer une direction assistée, dont le bruit de fonctionnement est réduit au minimum et dont le jeu de fonctionnement se situe toujours dans une plage prédéfinie, il est prévu qu'au moins la bague intérieure (10) ou la bague extérieure (26) du palier de roulement (9) est divisée en deux parties de bague (12, 13) le long d'un plan de séparation (11) disposé à peu près perpendiculairement au composant (6) déplaçable axialement, que les parties de bague (12, 13) sont montées dans le bâti (4) à une distance axiale (a) les unes des autres et maintenues par au moins un élément de ressort (14) les unes contre les autres.
PCT/EP2010/004841 2009-08-06 2010-08-06 Direction assistée avec bague de palier pré-tendue et divisée WO2011015374A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102009036303A DE102009036303A1 (de) 2009-08-06 2009-08-06 Wälzlager
DE102009036303.3 2009-08-06
DE102010002892A DE102010002892A1 (de) 2010-03-16 2010-03-16 Servolenkung
DE102010002892.4 2010-03-16

Publications (1)

Publication Number Publication Date
WO2011015374A1 true WO2011015374A1 (fr) 2011-02-10

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ID=43066757

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/004841 WO2011015374A1 (fr) 2009-08-06 2010-08-06 Direction assistée avec bague de palier pré-tendue et divisée

Country Status (1)

Country Link
WO (1) WO2011015374A1 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011147824A1 (fr) * 2010-05-25 2011-12-01 Zf Lenksysteme Gmbh Transmission à recirculation de billes
WO2013068104A1 (fr) * 2011-11-07 2013-05-16 Thyssenkrupp Presta Ag Vis d'entraînement à billes à compensation de palier
US20130228026A1 (en) * 2010-03-22 2013-09-05 Zf Lenksysteme Gmbh Power steering system
CN103889823A (zh) * 2011-10-18 2014-06-25 蒂森克虏伯普利斯坦有限公司 机电的机动车转向器
US20140319811A1 (en) * 2013-03-22 2014-10-30 Aktiebolaget Skf Pre-stressed rolling bearing, notably for a steering column
US20140345966A1 (en) * 2013-05-22 2014-11-27 Jtekt Corporation Electric power steering system
EP2810851A1 (fr) * 2013-06-04 2014-12-10 Jtekt Corporation Système de direction
DE102014109407A1 (de) * 2014-07-04 2016-01-07 Trw Automotive Gmbh Servolenkung für Kraftfahrzeuge
JP2016514815A (ja) * 2013-03-28 2016-05-23 スネクマ 内部予圧付係合離脱可能な軸方向のスラスト軸受
WO2018086782A1 (fr) * 2016-11-09 2018-05-17 Robert Bosch Gmbh Palier fixe et mécanisme de direction
WO2020108684A1 (fr) * 2018-11-26 2020-06-04 Schaeffler Technologies AG & Co. KG Système de direction avec palier de pivotement
CN114029886A (zh) * 2021-11-11 2022-02-11 徐州徐工液压件有限公司 一种双向螺杆副导轨式夹紧装置
DE102020213618A1 (de) 2020-10-29 2022-05-05 Robert Bosch Gesellschaft mit beschränkter Haftung Vierpunktlager mit einstellbaren Reibmoment

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4229199A1 (de) * 1992-09-02 1994-03-03 Schaeffler Waelzlager Kg Spielfreies Wälzlager
DE4231272A1 (de) * 1992-09-18 1994-03-24 Wagner Gmbh & Co Fahrzeugteile Kugellager
DE10310492A1 (de) 2003-03-11 2004-09-23 Zf Lenksysteme Gmbh Servolenkung
DE102005015756A1 (de) * 2005-04-06 2006-10-12 Zf Lenksysteme Gmbh Lenkung
DE102007039733A1 (de) * 2007-08-22 2009-02-26 Zf Lenksysteme Gmbh Lenkeinrichtung mit Anschlagbegrenzung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4229199A1 (de) * 1992-09-02 1994-03-03 Schaeffler Waelzlager Kg Spielfreies Wälzlager
DE4231272A1 (de) * 1992-09-18 1994-03-24 Wagner Gmbh & Co Fahrzeugteile Kugellager
DE10310492A1 (de) 2003-03-11 2004-09-23 Zf Lenksysteme Gmbh Servolenkung
DE102005015756A1 (de) * 2005-04-06 2006-10-12 Zf Lenksysteme Gmbh Lenkung
DE102007039733A1 (de) * 2007-08-22 2009-02-26 Zf Lenksysteme Gmbh Lenkeinrichtung mit Anschlagbegrenzung

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130228026A1 (en) * 2010-03-22 2013-09-05 Zf Lenksysteme Gmbh Power steering system
US8997597B2 (en) * 2010-03-22 2015-04-07 Zf Lenksysteme Gmbh Power steering system
WO2011147824A1 (fr) * 2010-05-25 2011-12-01 Zf Lenksysteme Gmbh Transmission à recirculation de billes
US8931362B2 (en) 2010-05-25 2015-01-13 Zf Lenksysteme Gmbh Recirculating ball gear
CN103889823A (zh) * 2011-10-18 2014-06-25 蒂森克虏伯普利斯坦有限公司 机电的机动车转向器
CN103889823B (zh) * 2011-10-18 2016-10-26 蒂森克虏伯普利斯坦有限公司 机电的机动车转向器
US9376139B2 (en) 2011-11-07 2016-06-28 Thyssenkrupp Presta Ag Ball screw having bearing compensation
WO2013068104A1 (fr) * 2011-11-07 2013-05-16 Thyssenkrupp Presta Ag Vis d'entraînement à billes à compensation de palier
US20140319811A1 (en) * 2013-03-22 2014-10-30 Aktiebolaget Skf Pre-stressed rolling bearing, notably for a steering column
US9422980B2 (en) * 2013-03-22 2016-08-23 Aktiebolaget Skf Pre-stressed rolling bearing, notably for a steering column
JP2016514815A (ja) * 2013-03-28 2016-05-23 スネクマ 内部予圧付係合離脱可能な軸方向のスラスト軸受
US20140345966A1 (en) * 2013-05-22 2014-11-27 Jtekt Corporation Electric power steering system
US10787195B2 (en) * 2013-05-22 2020-09-29 Jtekt Corporation Electric power steering system
EP2810851A1 (fr) * 2013-06-04 2014-12-10 Jtekt Corporation Système de direction
DE102014109407A1 (de) * 2014-07-04 2016-01-07 Trw Automotive Gmbh Servolenkung für Kraftfahrzeuge
WO2018086782A1 (fr) * 2016-11-09 2018-05-17 Robert Bosch Gmbh Palier fixe et mécanisme de direction
US11661098B2 (en) 2016-11-09 2023-05-30 Robert Bosch Gmbh Fixed bearing and steering gear
WO2020108684A1 (fr) * 2018-11-26 2020-06-04 Schaeffler Technologies AG & Co. KG Système de direction avec palier de pivotement
CN112789418A (zh) * 2018-11-26 2021-05-11 舍弗勒技术股份两合公司 具有枢轴承的转向***
DE102020213618A1 (de) 2020-10-29 2022-05-05 Robert Bosch Gesellschaft mit beschränkter Haftung Vierpunktlager mit einstellbaren Reibmoment
CN114029886A (zh) * 2021-11-11 2022-02-11 徐州徐工液压件有限公司 一种双向螺杆副导轨式夹紧装置
CN114029886B (zh) * 2021-11-11 2023-08-15 徐州徐工液压件有限公司 一种双向螺杆副导轨式夹紧装置

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