WO2004087485A1 - Rack and pinion steering - Google Patents

Rack and pinion steering Download PDF

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Publication number
WO2004087485A1
WO2004087485A1 PCT/EP2004/002105 EP2004002105W WO2004087485A1 WO 2004087485 A1 WO2004087485 A1 WO 2004087485A1 EP 2004002105 W EP2004002105 W EP 2004002105W WO 2004087485 A1 WO2004087485 A1 WO 2004087485A1
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WO
WIPO (PCT)
Prior art keywords
rack
guide roller
pressure piece
bearing
pinion
Prior art date
Application number
PCT/EP2004/002105
Other languages
German (de)
French (fr)
Inventor
Uwe Abraham
Peter Jennes
Original Assignee
Ina-Schaeffler Kg
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 Ina-Schaeffler Kg filed Critical Ina-Schaeffler Kg
Publication of WO2004087485A1 publication Critical patent/WO2004087485A1/en

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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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/26—Racks
    • F16H55/28—Special devices for taking up backlash
    • F16H55/283—Special devices for taking up backlash using pressure yokes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D3/00—Steering gears
    • B62D3/02—Steering gears mechanical
    • B62D3/12—Steering gears mechanical of rack-and-pinion type
    • B62D3/123—Steering gears mechanical of rack-and-pinion type characterised by pressure yokes
    • 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
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/006—Guiding rollers, wheels or the like, formed by or on the outer element of a single bearing or bearing unit, e.g. two adjacent bearings, whose ratio of length to diameter is generally less than one
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/44—Needle bearings
    • F16C19/46—Needle bearings with one row or needles
    • 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
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling 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
    • 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
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/084—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface sliding on a complementary spherical surface
    • 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
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/002—Elastic or yielding linear bearings or bearing supports
    • 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
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/04—Ball or roller bearings
    • F16C29/045—Ball or roller bearings having rolling elements journaled in one of the moving parts
    • 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
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/12—Arrangements for adjusting play
    • F16C29/123—Arrangements for adjusting play using elastic means
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/20—Land vehicles
    • F16C2326/24—Steering systems, e.g. steering rods or columns
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/26—Racks
    • F16H55/28—Special devices for taking up backlash
    • F16H55/283—Special devices for taking up backlash using pressure yokes
    • F16H55/285—Special devices for taking up backlash using pressure yokes with rollers or balls to reduce friction

Definitions

  • the invention relates to a rack and pinion steering for a motor vehicle with a steering housing in which a rack is mounted longitudinally displaceable, and a meshing with the rack pinion and a pressure piece, which is arranged on the side facing the engagement with the pinion side of the rack and by means of a spring is biased in the axial direction against the rack, wherein the pressure piece in its interior has a contour of the rack adapted, rotatable guide roller on which rests the rack.
  • Such rack and pinion steering systems are already known from the prior art for a long time.
  • the rack In these steering the rack is guided in the longitudinal direction displaceable in a steering housing.
  • a rotatably mounted in the steering housing pinion engages the toothing of the rack and causes upon rotation of the rotatably connected to the pinion steering column, the lateral displacement of the rack, which in turn leads via tie rods and stub axles to a pivoting of the steered wheels of the motor vehicle.
  • the engagement of the pinion in the rack is held backlash by a pressure applied to the toothed rack against the pinion presses under spring tension the rack against the pinion.
  • the pressure piece must be able to transmit the required pressing force and, on the other hand, provide a bearing surface which does not cause appreciable frictional forces and significant wear when the rack is displaced on the pressure piece.
  • Such a gattu ⁇ gswash trained pressure piece is from the DE 82 03 943 U1 previously known.
  • the rolling friction between the rack and pressure piece is realized in such a way that a contour of the rack adapted leadership role is taken in the pressure piece via a rolling bearing.
  • This guide roller is arranged on a support shaft, which is received with its two outer ends in the pressure piece.
  • this object is achieved by the characterizing part of claim 1 in conjunction with the preamble thereof, that the guide roller is held on both sides on its outer sides in the radial direction above and below its axis of rotation by a respective radial and axial forces receiving rolling bearing whose outer rings a spherical Having outer contour, which are taken up again in each case in a reversed spherical receiving bore tion of the pressure piece.
  • the advantage of the solution according to the invention is that through the side arranged storage of the guide roller in the pressure piece can be saved considerably radial space. Another advantage is due to the fact that radial and axial forces are much better absorbable by the inventive type of storage of the guide roller and the role can be employed radially and axially backlash. This is important because during transmission of the movement of the pinion forces act on the teeth of the rack having a first component in the direction of the axis of the rack and a second force component in the direction of pressure piece. Ideally, this second force component is oriented at right angles to the first force component.
  • this second component decomposes into a third axially directed subcomponent, which can be easily picked up by the rolling bearing arranged according to the invention.
  • Another significant advantage of the invention is that a malposition of the support shaft of the guide roller, due to non-aligned holes in the pressure piece, can be compensated. This is done in such a way that when assembling the pressure piece this malposition is correctable by moving one of the bearing outer rings with its spherical outer contour in the pressure piece.
  • the rolling bearings are designed as a single-row bearing inclined to the axis of rotation main load direction such as angular needle bearings, angular contact ball bearings, tapered roller bearings or the like.
  • the inner and / or the outer bearing ring are formed as thin-walled produced without cutting. This production makes a particularly cost-effective production in a variety of variants in a simple manner possible.
  • the inner raceway may be formed by a triangular ring whose inclined surface constitutes the raceway for the rolling elements.
  • Another advantage of a bearing according to the invention according to claim 5 is when the inner raceway is formed by an inclined surface of the guide roller. In this case can be dispensed cost-saving on this bearing ring.
  • the guide roller should be formed in two parts, it being provided according to claim 7, that the guide roller is arranged on a support shaft and a slotted spacer ring is arranged in a parting plane.
  • these spacers are to be formed with different thickness and assigned according to a measurement corresponding guide rollers. In this way it is possible to easily compensate occurring manufacturing tolerances between pressure piece, guide roller and roller bearing.
  • a receiving bore of the support shaft in the guide roller has a stepped diameter.
  • Fig. 1, 2 and 3 a longitudinal section and a partial longitudinal section through an inventively mounted guide roller and
  • Fig. 4 is a longitudinal section through a guide roller according to the prior art.
  • FIG. 1 shows a housing 1, in which a pinion 2, which merges into a steering shaft 3, is mounted.
  • a pinion 2 In the toothing of the pinion 2 engages the toothing of a rack 4, which extends transversely to the pinion 2.
  • a pressure piece 5 On the engagement side of the pinion 2 with the rack 4 opposite side of the rack 4, a pressure piece 5 is arranged, which essentially supports the force transmitted from the pinion 2 to the rack 4 force.
  • the pressure piece 5 is housed in a non-designated receiving bore of the housing 1. It is biased by a between the pressure piece 5 and a rigidly connected to the housing 1 cover 6 arranged spring 7 in the direction of the rack 4.
  • a guide roller 8 is housed, which is held on two axle formed as a deep groove ball bearing 9 on a support shaft 10.
  • the support shaft 10 in turn is secured with its two opposite ends in the pressure piece 5 in receiving holes 11. If these two opposite receiving bores 11 lie in one plane, that is to say they are in alignment with one another, then it can be seen that there is a linear contact between the rack 4 and the guide roller 8 because their respective faces are in contact with each other. pressure surfaces 4.1 and 8.1. However, if the two opposing receiving bores 11 are not in alignment, it is easy to see that no linear contact is possible between the rack 4 and the guide roller 8, but only pointy one-sided contact can take place or if there is an increased permanent tilting moment load when the rack 4 is displaced. This is where the invention begins.
  • the guide roller 13 is formed of two spaced-apart part rollers 13.1, 13.2. These sub-rollers 13.1 and 13.2 are each provided with a continuous receiving bore 14 into which a connecting axle 15 is inserted. Between the two sub-rollers 13.1, 13.2 a slotted spacer ring 16 is snapped onto the support shaft 15.
  • the guide roller 13 according to the invention is held in the pressure member 12 on both sides with its outer sides via a radial and axial al phenomenon receiving angular needle bearing 17. This consists of an outer and an inner bearing ring 17.1, 17.2, between which run on unspecified raceways in a cage 17.3 guided bearing needles 17.4.
  • the helical needle bearing 17 is formed so that the bearing rings 17.1, 17.2 opposite to its axis of rotation 18, which is also the axis of rotation of the guide roller 13, at an angle which is smaller than 90 °, that are inclined.
  • the main load direction of the two angular needle bearings 17 is therefore inclined relative to the axis of rotation 18, wherein the normal of the raceways meet in the axis of rotation 18, as the figure shows.
  • the outer side of the outer bearing ring 17.1 is provided with a spherical, ie convex outer contour to which an opposing matching ie, concave contour of the receiving bore 12.1 must be given in the pressure piece 12.
  • the outer bearing ring has the spherical ge outer contour, so that the axes of rotation of angular contact ball bearing 17 and guide roller 13 can match. If these match and the outer bearing ring 17.1 has adapted to the given positions, no movement takes place during the operation of the steering. The set friction thus remains constant during all operating conditions over the entire service life within narrow limits at a low level.
  • the figure 1 is further removed that over the axial thickness of the spacer ring 16 manufacturing tolerances can be compensated. Also can be acted upon the bias of the angular needle bearings 17. This is increased when a spacer ring 16 is used with greater axial strength, so that the two sub-rollers 13.1, 13.2 of the guide roller 13 are further moved away from each other.
  • FIGS. 2 and 3 slightly different variants of a helical needle bearing 17 are shown.
  • the inner bearing ring 17.5 is triangular in shape, with its inclined surface forms the track for the guided in the cage 17.3 bearing needles 17.4.
  • the raceway for the bearing needles 17.4 guided in the cage 17.3 is formed by an inclined running surface 13.1.1, 13.2.1 of the two part rollers 13.1, 13.2.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Transmission Devices (AREA)

Abstract

A pressure piece (12) for a rack and pinion steering device in motor vehicle, comprising a guide roller (13) arranged in the inside thereof, said guide roller being maintained on both sides on the outer sides thereof in a radial direction above and below the axis of rotation (18) by a respective rolling bearing (17) receiving radial and axial forces, whereby the outer rings (17.1) thereof have a spherical-shaped outer contour and are received in a respective inverted receiving opening (12.1) of the pressure piece (12).

Description

Zahnstangenlenkung Rack and pinion steering
Anwendungsgebiet der ErfindungField of application of the invention
Die Erfindung betrifft eine Zahnstangenlenkung für ein Kraftfahrzeug mit einem Lenkgehäuse, in dem eine Zahnstange längsverschieblich gelagert ist, sowie einem mit der Zahnstange kämmenden Ritzel und einem Druckstück, das auf der der Eingriffsseite mit dem Ritzel gegenüberliegenden Seite der Zahnstange angeordnet ist und mit Hilfe einer Feder in axialer Richtung gegen die Zahnstange vorgespannt ist, wobei das Druckstück in seinem Inneren eine der Kontur der Zahnstange angepaßte, drehbare Führungsrolle aufweist, an der die Zahnstange anliegt.The invention relates to a rack and pinion steering for a motor vehicle with a steering housing in which a rack is mounted longitudinally displaceable, and a meshing with the rack pinion and a pressure piece, which is arranged on the side facing the engagement with the pinion side of the rack and by means of a spring is biased in the axial direction against the rack, wherein the pressure piece in its interior has a contour of the rack adapted, rotatable guide roller on which rests the rack.
Hintergrund der ErfindungBackground of the invention
Derartige Zahnstangenlenkungen sind aus dem Stand der Technik seit langem vorbekannt. Bei diesen Lenkungen wird die Zahnstange in Längsrichtung verschiebbar in einem Lenkgehäuse geführt. Ein in dem Lenkgehäuse drehbar gelagertes Ritzel greift in die Verzahnung der Zahnstange ein und bewirkt bei Drehung der mit dem Ritzel drehfest verbundenen Lenksäule die seitliche Verlagerung der Zahnstange, die wiederum über Spurstangen und Achsschenkel zu einer Verschwenkung der gelenkten Räder des Kraftfahrzeuges führt. Der Eingriff des Ritzels in die Zahnstange wird spielfrei gehalten, indem ein gegen- über dem Ritzel an der Zahnstange anliegendes Druckstück unter Federvorspannung die Zahnstange gegen das Ritzel drückt. Das Druckstück muß dabei zum einen die erforderliche Anpreßkraft übertragen können und zum anderen eine Lagerfläche bieten, die bei der Verschiebung der Zahnstange auf dem Druckstück keine nennenswerten Reibkräfte und keinen wesentlichen Ver- schleiß hervorruft.Such rack and pinion steering systems are already known from the prior art for a long time. In these steering the rack is guided in the longitudinal direction displaceable in a steering housing. A rotatably mounted in the steering housing pinion engages the toothing of the rack and causes upon rotation of the rotatably connected to the pinion steering column, the lateral displacement of the rack, which in turn leads via tie rods and stub axles to a pivoting of the steered wheels of the motor vehicle. The engagement of the pinion in the rack is held backlash by a pressure applied to the toothed rack against the pinion presses under spring tension the rack against the pinion. On the one hand, the pressure piece must be able to transmit the required pressing force and, on the other hand, provide a bearing surface which does not cause appreciable frictional forces and significant wear when the rack is displaced on the pressure piece.
Ein derart gattuπgsgemäß ausgebildetes Druckstück ist aus der DE 82 03 943 U1 vorbekannt. Gemäß Figur 4 dieser Vorveröffentlichung wird die rollende Reibung zwischen Zahnstange und Druckstück derart realisiert, indem im Druckstück über ein Wälzlager eine der Kontur der Zahnstange angepaßte Führungsrolle aufgenommen ist. Diese Führungsrolle ist auf einer Tragachse angeordnet, die mit ihren beiden äußeren Enden im Druckstück aufgenommen ist.Such a gattuπgsgemäß trained pressure piece is from the DE 82 03 943 U1 previously known. According to Figure 4 of this prior publication, the rolling friction between the rack and pressure piece is realized in such a way that a contour of the rack adapted leadership role is taken in the pressure piece via a rolling bearing. This guide roller is arranged on a support shaft, which is received with its two outer ends in the pressure piece.
Nachteilig dabei ist zum einen, daß aufgrund der wälzgelagerten Führungsrolle ein erhöhter radialer Bauraum beansprucht werden muß. Zum anderen müssen die Aufnahmebohrungen in der Mantelfläche des Druckstückes zur Aufnahme der Tragachse fluchten, da anderenfalls durch eine Schrägstellung der Führungsrolle eine ungleiche Belastung zwischen Druckstück und Zahnstange realisiert ist, die sich negativ auf das Lenkverhalten und die Lebensdauer der Wälzlager auswirken kann.The disadvantage here is, on the one hand, that due to the roller bearing guide roller, an increased radial space must be claimed. On the other hand, the receiving holes must be aligned in the lateral surface of the pressure member for receiving the support shaft, otherwise an unequal load between the pressure piece and rack is realized by an inclination of the guide roller, which can adversely affect the steering behavior and life of the bearings.
Zusammenfassung der ErfindungSummary of the invention
Ausgehend von den Nachteilen des bekannten Standes der Technik ist es daher Aufgabe de Erfindung, ein gattungsgemäßes Druckstück für ein Zahnstan- genlenkgetriebe bereitzustellen, das sich einerseits relativ einfach fertigen läßt und das andererseits gleiche Belastungsverhältnisse zwischen Druckstück und Zahnstange gewährleistet.Based on the disadvantages of the known prior art, it is therefore an object of the invention to provide a generic pressure piece for a rack and pinion steering gear, which on the one hand relatively easy to manufacture and on the other hand equal load conditions between the pressure piece and rack guaranteed.
Erfindungsgemäß wird diese Aufgabe nach dem kennzeichnenden Teil von Anspruch 1 in Verbindung mit dessen Oberbegriff dadurch gelöst, daß die Führungsrolle beidseitig an ihren Außenseiten in radialer Richtung oberhalb und unterhalb ihrer Drehachse durch je ein Radial- und Axialkräfte aufnehmendes Wälzlager gehalten ist, dessen Außenringe eine kugelige Außenkontur aufweisen, die wieder um in je einer umgekehrt kugelig ausgebildeten Aufnahmeboh- rung des Druckstückes aufgenommen sind.According to the invention, this object is achieved by the characterizing part of claim 1 in conjunction with the preamble thereof, that the guide roller is held on both sides on its outer sides in the radial direction above and below its axis of rotation by a respective radial and axial forces receiving rolling bearing whose outer rings a spherical Having outer contour, which are taken up again in each case in a reversed spherical receiving bore tion of the pressure piece.
Der Vorteil der erfindungsgemäßen Lösung liegt darin, daß durch die seitlich angeordnete Lagerung der Führungsrolle im Druckstück erheblich radialer Bauraum eingespart werden kann. Ein anderer Vorteil ist dadurch begründet, daß durch die erfindungsgemäße Art der Lagerung der Führungsrolle Radial- und Axialkräfte wesentlich besser aufnehmbar sind und die Rolle radial und axial spielfrei angestellt werden kann. Dies ist von Bedeutung, da während der Übertragung der Bewegung des Ritzels Kräfte auf die Zähne der Zahnstange wirken, die eine erste Komponente in Richtung der Achse der Zahnstange ynd eine zweite Kraftkomponente in Richtung Druckstück haben. Im Idealfall ist diese zweite Kraftkomponente rechtwinklig zu ersten Kraftkomponente ausge- richtet. Ist dies aber nicht der Fall, zerlegt sich diese zweite Komponente in eine dritte axial gerichtete Teilkomponente, die vom erfindungsgemäß angeordneten Wälzlager problemlos aufgenommen werden kann. Ein weiterer wesentlicher Vorteil der Erfindung liegt darin, daß eine Fehlstellung der Tragachse der Führungsrolle, bedingt durch nicht fluchtende Bohrungen im Druckstück, ausgeglichen werden kann. Dies erfolgt derart, daß bei Montage des Druckstückes diese Fehlstellung durch ein Verschieben eines der Lageraußenringe mit seiner kugeligen Außenkontur im Druckstück korrigierbar ist.The advantage of the solution according to the invention is that through the side arranged storage of the guide roller in the pressure piece can be saved considerably radial space. Another advantage is due to the fact that radial and axial forces are much better absorbable by the inventive type of storage of the guide roller and the role can be employed radially and axially backlash. This is important because during transmission of the movement of the pinion forces act on the teeth of the rack having a first component in the direction of the axis of the rack and a second force component in the direction of pressure piece. Ideally, this second force component is oriented at right angles to the first force component. But if this is not the case, this second component decomposes into a third axially directed subcomponent, which can be easily picked up by the rolling bearing arranged according to the invention. Another significant advantage of the invention is that a malposition of the support shaft of the guide roller, due to non-aligned holes in the pressure piece, can be compensated. This is done in such a way that when assembling the pressure piece this malposition is correctable by moving one of the bearing outer rings with its spherical outer contour in the pressure piece.
Weitere vorteilhafte Ausführungsvarianten der Erfindung sind in den Unteran- Sprüchen 2 bis 9 beschrieben.Further advantageous embodiments of the invention are described in the subclaims 2 to 9.
So ist nach Anspruch 2 vorgesehen, daß die Wälzlager als einreihige Lager mit zur Drehachse geneigter Hauptbelastungsrichtung wie Schrägnadellager, Schrägkugellager, Kegelrollenlager oder dergleichen ausgebildet sind.Thus, it is provided according to claim 2 that the rolling bearings are designed as a single-row bearing inclined to the axis of rotation main load direction such as angular needle bearings, angular contact ball bearings, tapered roller bearings or the like.
Nach einem weiteren Merkmal der Erfindung nach Anspruch 3 ist vorgesehen, daß der innere und/oder der äußere Lagerring als dünnwandige spanlos hergestellte Teile ausgebildet sind. Diese Herstellungsart macht eine besonders kostengünstige Fertigung in mannigfaltigen Ausführungsvarianten in einfacher Weise möglich.According to a further feature of the invention according to claim 3, it is provided that the inner and / or the outer bearing ring are formed as thin-walled produced without cutting. This production makes a particularly cost-effective production in a variety of variants in a simple manner possible.
Nach einem zusätzlichen weiteren Merkmal der Erfindung nach Anspruch 4 soll die innere Laufbahn durch einen dreieckförmigen Ring gebildet sein, dessen geneigte Fläche die Laufbahn für die Wälzkörper stellt.According to an additional further feature of the invention according to claim 4 is intended the inner raceway may be formed by a triangular ring whose inclined surface constitutes the raceway for the rolling elements.
Ein weiterer Vorteil eines erfindungsgemäßen Lagers nach Anspruch 5 liegt darin, wenn die innere Laufbahn durch eine geneigte Fläche der Führungsrolle gebildet ist. in diesem Fall kann kostensparend auf diesen Lagerring verzichtet werden.Another advantage of a bearing according to the invention according to claim 5 is when the inner raceway is formed by an inclined surface of the guide roller. In this case can be dispensed cost-saving on this bearing ring.
Nach einem anderen zusätzlichen Merkmal der Erfindung nach Anspruch 6 soll die Führungsrolle zweiteilig ausgebildet sein, wobei nach Anspruch 7 vorgesehen ist, daß die Führungsrolle auf einer Tragachse angeordnet ist und in einer Teilungsebene ein geschlitzter Distanzring angeordnet ist. Durch diese Gestaltung wird es möglich, daß durch Verändern des axialen Abstandes der beiden Hälften der Führungsrollen zueinander eine gewünschte Vorspannung auf die Lagerung der Führungsrolle einstellbar ist.According to another additional feature of the invention according to claim 6, the guide roller should be formed in two parts, it being provided according to claim 7, that the guide roller is arranged on a support shaft and a slotted spacer ring is arranged in a parting plane. By this design, it is possible that by changing the axial distance of the two halves of the guide rollers to each other a desired bias on the bearing of the guide roller is adjustable.
Nach Anspruch 8 sollen diese Distanzringe mit unterschiedlicher Stärke ausgebildet sein und nach einer Messung entsprechenden Führungsrollen zugeordnet werden. Auf diese Weise ist es möglich, auftretende Fertigungstoleran- zen zwischen Druckstück, Führungsrolle und Wälzlagerung in einfacher Weise auszugleichen.According to claim 8, these spacers are to be formed with different thickness and assigned according to a measurement corresponding guide rollers. In this way it is possible to easily compensate occurring manufacturing tolerances between pressure piece, guide roller and roller bearing.
Schließlich ist nach Anspruch 9 vorgestehen, daß eine Aufnahmebohrung der Tragachse in der Führungsrolle einen abgestuften Durchmesser aufweist. Durch diese einfache Maßnahme läßt sich ein axiales Wandern der Tragachse innerhalb der Führungsrolle verhindern.Finally, according to claim 9 claim that a receiving bore of the support shaft in the guide roller has a stepped diameter. By this simple measure, an axial migration of the support shaft can be prevented within the leadership role.
Die Erfindung wird an nachstehenden Ausführungsbeispielen näher beschrieben. Kurze Beschreibung der ZeichnungenThe invention will be described in more detail in the following embodiments. Brief description of the drawings
Es zeigen:Show it:
Fig. 1 , 2 und 3 einen Längsschnitt bzw. einen Teillängsschnitt durch eine erfindungsgemäß gelagerte Führungsrolle undFig. 1, 2 and 3 a longitudinal section and a partial longitudinal section through an inventively mounted guide roller and
Fig. 4 einen Längsschnitt durch eine Führungsrolle nach dem bisherigen Stand der Technik.Fig. 4 is a longitudinal section through a guide roller according to the prior art.
Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings
Zur Darstellung des Gesamtzusammenhanges ist zunächst auf dem Stand der Technik gemäß Figur 4 verwiesen. Diese zeigt eine Gehäuse 1 , in dem ein Ritzel 2, das in eine Lenkspindel 3 übergeht, gelagert ist. In die Verzahnung des Ritzels 2 greift die Verzahnung einer Zahnstange 4 ein, die quer zum Ritzel 2 verläuft. Auf der der Eingriffsseite des Ritzels 2 mit der Zahnstange 4 gegenüberliegenden Seite der Zahnstange 4 ist ein Druckstück 5 angeordnet, das die vom Ritzel 2 auf die Zahnstange 4 übertragene Kraft im wesentlichen abstützt. Das Druckstück 5 ist in einer nicht bezeichneten Aufnahmebohrung des Gehäuses 1 untergebracht. Es wird von einer zwischen dem Druckstück 5 und einem starr mit dem Gehäuse 1 verbundenen Deckel 6 angeordneten Feder 7 in Richtung auf die Zahnstange 4 vorgespannt.To illustrate the overall context, reference is first made to the prior art according to FIG. This shows a housing 1, in which a pinion 2, which merges into a steering shaft 3, is mounted. In the toothing of the pinion 2 engages the toothing of a rack 4, which extends transversely to the pinion 2. On the engagement side of the pinion 2 with the rack 4 opposite side of the rack 4, a pressure piece 5 is arranged, which essentially supports the force transmitted from the pinion 2 to the rack 4 force. The pressure piece 5 is housed in a non-designated receiving bore of the housing 1. It is biased by a between the pressure piece 5 and a rigidly connected to the housing 1 cover 6 arranged spring 7 in the direction of the rack 4.
Im Druckstück 5 ist eine Führungsrolle 8 untergebracht, die über zwei als Rillenkugellager ausgebildete Wälzlager 9 auf einer Tragachse 10 gehalten ist. Die Tragachse 10 wiederum ist mit ihren beiden gegenüberliegenden Enden im Druckstück 5 in Aufnahmebohrungen 11 gesichert. Liegen diese beiden gegenüberliegenden Aufnahmebohrungen 11 in einer Ebene, also fluchten sie mit- einander, so ist erkennbar, daß eine linienförmige Berührung zwischen Zahnstange 4 und Führungsrolle 8 gegeben ist, weil deren jeweilige Ge- gendruckflächen 4.1 und 8.1 übereinstimmen. Fluchten die beiden gegenüberliegenden Aufnahmebohrungen 11 jedoch nicht, so ist unschwer zu erkennen, daß zwischen Zahnstange 4 und Führungsrolle 8 keine linienförmige Berührung mehr möglich ist, sondern nur eine punktförmige einseitige Berührung erfolgen kann bzw. bei Verlagerung der Zahnstange 4 eine erhöhte permanente Kippmomentbelastung vorliegt. Hier setzt nun die Erfindung an.In the pressure piece 5, a guide roller 8 is housed, which is held on two axle formed as a deep groove ball bearing 9 on a support shaft 10. The support shaft 10 in turn is secured with its two opposite ends in the pressure piece 5 in receiving holes 11. If these two opposite receiving bores 11 lie in one plane, that is to say they are in alignment with one another, then it can be seen that there is a linear contact between the rack 4 and the guide roller 8 because their respective faces are in contact with each other. pressure surfaces 4.1 and 8.1. However, if the two opposing receiving bores 11 are not in alignment, it is easy to see that no linear contact is possible between the rack 4 and the guide roller 8, but only pointy one-sided contact can take place or if there is an increased permanent tilting moment load when the rack 4 is displaced. This is where the invention begins.
In Figur 1 ist ein erfindungsgemäßes Druckstück 12 gezeigt, dessen Führungsrolle 13 aus zwei von einander beabstandeten Teilrollen 13.1 , 13.2 gebildet ist. Diese Teilrollen 13.1 und 13.2 sind mit je einer durchgehenden Aufnahmebohrung 14 versehen, in die eine beide verbindende Tragachse 15 eingeführt ist. Zwischen den beiden Teilrollen 13.1 , 13.2 ist ein geschlitzter Distanzring 16 auf die Tragachse 15 aufgeschnappt. Die erfindungsgemäße Führungsrolle 13 ist im Druckstück 12 beidseitig mit ihren Außenseiten über ein Radial- und Axi- alkräfte aufnehmendes Schrägnadellager 17 gehalten. Dieses besteht aus einem äußeren und einem inneren Lagerring 17.1 , 17.2, zwischen denen auf nicht näher bezeichneten Laufbahnen in einem Käfig 17.3 geführte Lagernadeln 17.4 abrollen. Das Schrägnadellager 17 ist so ausgebildet, daß die Lagerringe 17.1 , 17.2 gegenüber ihrer Drehachse 18, die gleichzeitig die Drehachse der Führungsrolle 13 ist, unter einem Winkel verlaufen, der kleiner als 90° ist, also schräg gestellt sind. Die Hauptbelastungsrichtung der beiden Schrägnadellager 17 ist demnach gegenüber der Drehachse 18 schräggestellt, wobei sich die Normalen der Laufbahnen in der Drehachse 18 treffen, wie die Figur zeigt.In Figure 1, an inventive pressure piece 12 is shown, the guide roller 13 is formed of two spaced-apart part rollers 13.1, 13.2. These sub-rollers 13.1 and 13.2 are each provided with a continuous receiving bore 14 into which a connecting axle 15 is inserted. Between the two sub-rollers 13.1, 13.2 a slotted spacer ring 16 is snapped onto the support shaft 15. The guide roller 13 according to the invention is held in the pressure member 12 on both sides with its outer sides via a radial and axial alkräfte receiving angular needle bearing 17. This consists of an outer and an inner bearing ring 17.1, 17.2, between which run on unspecified raceways in a cage 17.3 guided bearing needles 17.4. The helical needle bearing 17 is formed so that the bearing rings 17.1, 17.2 opposite to its axis of rotation 18, which is also the axis of rotation of the guide roller 13, at an angle which is smaller than 90 °, that are inclined. The main load direction of the two angular needle bearings 17 is therefore inclined relative to the axis of rotation 18, wherein the normal of the raceways meet in the axis of rotation 18, as the figure shows.
Wie Figur 1 weiter zeigt, ist die Außenseite des äußeren Lagerrings 17.1 mit einer kugeligen, d.h. konvexen Außenkontur versehen, zu der eine entgegengesetzt passende d.h., konkave Kontur der Aufnahmebohrung 12.1 im Druckstück 12 gegeben sein muß. Dadurch wird es möglich, daß bei nicht genau fluchtenden Aufnahmebohrungen 12.1 im Druckstück 12 einer der beiden äußeren Lagerringe 17.1 verschiebbar ist. Der äußere Lagerring weist die kugeli- ge Außenkontur auf, damit sich die Drehachsen von Schrägkugellager 17 und Führungsrolle 13 angleichen können. Stimmen diese überein und hat sich der äußere Lagerring 17.1 den gegebenen Positionen angepaßt, findet während des Betriebs der Lenkung keine Bewegung statt. Die eingestellte Reibung bleibt somit während aller Betriebszustände über die gesamte Lebensdauer in engen Grenzen auf niedrigem Niveau konstant.As Figure 1 further shows, the outer side of the outer bearing ring 17.1 is provided with a spherical, ie convex outer contour to which an opposing matching ie, concave contour of the receiving bore 12.1 must be given in the pressure piece 12. This makes it possible that in not exactly aligned receiving bores 12.1 in the pressure piece 12 of one of the two outer bearing rings 17.1 is displaceable. The outer bearing ring has the spherical ge outer contour, so that the axes of rotation of angular contact ball bearing 17 and guide roller 13 can match. If these match and the outer bearing ring 17.1 has adapted to the given positions, no movement takes place during the operation of the steering. The set friction thus remains constant during all operating conditions over the entire service life within narrow limits at a low level.
Der Figur 1 ist weiter entnehmbar, daß über die axiale Dicke des Distanzringes 16 Fertigungstoleranzen ausgeglichen werden können. Auch kann auf die Vor- Spannung der Schrägnadellager 17 eingewirkt werden. Diese wird erhöht, wenn ein Distanzring 16 mit größerer axialer Stärke eingesetzt wird, so daß die beiden Teilrollen 13.1 , 13.2 der Führungsrolle 13 weiter voneinander weggerückt sind.The figure 1 is further removed that over the axial thickness of the spacer ring 16 manufacturing tolerances can be compensated. Also can be acted upon the bias of the angular needle bearings 17. This is increased when a spacer ring 16 is used with greater axial strength, so that the two sub-rollers 13.1, 13.2 of the guide roller 13 are further moved away from each other.
In den Figuren 2 und 3 sind geringfügig veränderte Varianten eines Schrägnadellagers 17 dargestellt. In Figur 2 ist der innere Lagerring 17.5 dreieckförmig ausgebildet, wobei dessen geneigte Fläche die Laufbahn für die im Käfig 17.3 geführten Lagernadeln 17.4 bildet. Beim Schrägnadellager 17 gemäß Figur 3 ist auf den Innenring gänzlich verzichtet, da die Laufbahn für die im Käfig 17.3 geführten Lagernadeln 17.4 durch eine schräg gestellte Lauffläche 13.1.1 , 13.2.1 der beiden Teilrollen 13.1 , 13.2 gebildet ist. In FIGS. 2 and 3, slightly different variants of a helical needle bearing 17 are shown. In Figure 2, the inner bearing ring 17.5 is triangular in shape, with its inclined surface forms the track for the guided in the cage 17.3 bearing needles 17.4. 3, the raceway for the bearing needles 17.4 guided in the cage 17.3 is formed by an inclined running surface 13.1.1, 13.2.1 of the two part rollers 13.1, 13.2.
BezugszahlenlisteLIST OF REFERENCE NUMBERS
1 Gehäuse1 housing
2 Ritzel2 pinions
3 Lenkspindel3 steering spindle
4 Zahnstange4 rack
4.1 Gegendruckfläche4.1 counterpressure surface
5 Druckstück5 pressure piece
6 Deckel6 lids
7 Feder7 spring
8 Führungsrolle8 leadership role
8.1 Gegendruckfläche8.1 counter pressure surface
9 Wälzlager9 rolling bearings
10 Tragachse10 support axle
11 Aufnahmebohrung11 locating hole
12 Druckstück12 pressure piece
12.1 Aufnahmebohrung12.1 locating hole
13 Führungsrolle13 leadership role
13.1 Teilrolle13.1 Partial role
13.1.1 Lauffläche13.1.1 Tread
13.2 Teilrolle13.2 Partial role
13.2.1 Lauffläche13.2.1 Tread
14 Aufnahmebohrung14 receiving bore
15 Tragachse15 suspension axle
16 Distanzring16 spacer ring
17 Schrägnadellager17 angular needle bearings
17.1 äußerer Lagerring17.1 outer bearing ring
17.2 innerer Lagerring17.2 inner bearing ring
17.3 Käfig17.3 cage
17.4 Lagernadel17.4 Storage needle
17.5 innerer Lagerring17.5 inner bearing ring
18 Drehachse 18 axis of rotation

Claims

Patentansprüche Claims
1. Zahnstangenlenkung für ein Kraftfahrzeug mit einem Lenkgehäuse (1 ), in dem eine Zahnstange (4) längsverschieblich gelagert ist, sowie einem mit der Zahnstange (4) kämmenden Ritzel (2) und einem Druckstück, das auf der der Eingriffsseite mit dem Ritzel (2) gegenüberliegenden Seite der Zahnstange (4) angeordnet ist und mit Hilfe einer Feder (7) in axialer Richtung gegen die Zahnstange (4) vorgespannt ist, wobei das Druckstück in ' seinem Inneren eine der Kontur der Zahnstange (4) angepaßte, drehbare Führungsrolle aufweist, an der die Zahnstange (4) anliegt, dadurch gekennzeichnet, daß die Führungsrolle (13) beidseitig an ihren Außenseiten in radialer Richtung oberhalb und unterhalb ihrer Drehachse (18) durch je ein Radial- und Axialkräfte aufnehmendes Wälzager (17) gehalten ist, des- sen Außenringe (17.1 ) eine kugelige Außenkontur aufweisen, die wiederum in je einer umgekehrt kugelig ausgebildeten Aufnahmebohrung (12.1 ) des Druckstücks (12) aufgenommen sind.1. Rack and pinion steering for a motor vehicle with a steering housing (1), in which a rack (4) is mounted for longitudinal displacement, as well as a pinion (2) meshing with the rack (4) and a pressure piece, which on the engagement side with the pinion ( 2) opposite side of the rack (4) is arranged and is biased by means of a spring (7) in the axial direction against the rack (4), the pressure piece 'in its interior a rotating guide roller adapted to the contour of the rack (4) on which the toothed rack (4) rests, characterized in that the guide roller (13) is held on both sides on its outer sides in the radial direction above and below its axis of rotation (18) by a roller bearing (17) each absorbing radial and axial forces, whose outer rings (17.1) have a spherical outer contour, which in turn are received in a reversely spherical receiving bore (12.1) of the pressure piece (12).
2. Zahnstangenlenkung nach Anspruch 1 , dadurch gekennzeichnet, daß die Wälzlager als einreihige Lager mit zur Drehachse (18) geneigter Hauptbelastungsrichtung wie Schrägnadellager (17), Schrägkugellager, Kegelrollenlager oder dergleichen ausgebildet sind.2. Rack and pinion steering according to claim 1, characterized in that the rolling bearings are designed as a single-row bearing with the main axis of inclination to the axis of rotation (18) inclined needle bearings (17), angular contact ball bearings, tapered roller bearings or the like.
3. Schrägnadellager (17) nach Anspruch 1 , dadurch gekennzeichnet, daß der innere und/oder der äußere Lagerring (17.2,17.1 ) als dünnwandige spanlos hergestellte Teile ausgebildet sind.3. angular needle bearing (17) according to claim 1, characterized in that the inner and / or the outer bearing ring (17.2,17.1) are formed as thin-walled parts produced without cutting.
4. Schrägnadellager (17) nach Anspruch 2, dadurch gekennzeichnet, daß die innere Laufbahn durch einen dreieckförmigen Ring (17.3) gebildet ist, dessen geneigte Fläche die Laufbahn stellt. 4. angular needle bearing (17) according to claim 2, characterized in that the inner raceway is formed by a triangular ring (17.3), the inclined surface of which represents the raceway.
5. Schrägnadellager (17) nach Anspruch 1 , dadurch gekennzeichnet, daß die innere Laufbahn durch eine geneigte Fläche (13.1.1 , 13.2.1 ) der Führungsrolle (13) gebildet ist.5. angular needle bearing (17) according to claim 1, characterized in that the inner raceway is formed by an inclined surface (13.1.1, 13.2.1) of the guide roller (13).
6. Zahnstangenlenkung nach Anspruch 1 , dadurch gekennzeichnet, daß die Führungsrolle (13) zweiteilig ausgebildet ist.6. Rack and pinion steering according to claim 1, characterized in that the guide roller (13) is formed in two parts.
7. Zahnstangenlenkung nach Anspruch 6, dadurch gekennzeichnet, daß die Führungsrolle (13) auf einer Tragachse (15) angeordnet ist und in einer Tei- lungsebene ein geschlitzter Distanzring (16) angeordnet ist.7. Rack and pinion steering according to claim 6, characterized in that the guide roller (13) is arranged on a support axis (15) and a slotted spacer ring (16) is arranged in a division plane.
8. Führungsrolle (13) nach Anspruch 7, dadurch gekennzeichnet, daß die8. guide roller (13) according to claim 7, characterized in that the
Distanzringe (16) mit unterschiedlicher axialer Stärke ausgebildet sind und nach einer Messung entsprechenden Führungsrollen (13) zugeordnet sind.Spacer rings (16) are formed with different axial thickness and are assigned corresponding guide rollers (13) after a measurement.
9. Führungsrolle (13) nach Anspruch 7, dadurch gekennzeichnet, daß eine Aufnahmebohrung (14) der Führungsrolle (13) zur Aufnahme der Tragachse (15) einen abgestuften Durchmesser aufweist. 9. guide roller (13) according to claim 7, characterized in that a receiving bore (14) of the guide roller (13) for receiving the support shaft (15) has a stepped diameter.
PCT/EP2004/002105 2003-03-31 2004-03-03 Rack and pinion steering WO2004087485A1 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006024183A1 (en) * 2004-09-02 2006-03-09 Belimo Holding Ag Linear drive
US20140326913A1 (en) * 2013-05-06 2014-11-06 Michael Führer Arrangement for operating a shut-off valve having a tapered plug

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006043578A1 (en) * 2006-09-16 2008-03-27 Zf Lenksysteme Gmbh Rack pressing device for motor vehicle, has pressure piece movably guided into housing hole, loaded in direction of rack provided with pivoted shaft, and guiding unit e.g. guiding roll, rolling on shaft
DE102008041068A1 (en) 2008-08-07 2010-02-11 Zf Lenksysteme Gmbh Device for pressing toothed rack into pinion in toothed rack steering mechanism of motor vehicle, has thrust piece guided in direction of toothed rack by thrust piece spring, where spring is supported at end that is turned away from rack
DE102011012203A1 (en) * 2011-02-23 2012-08-23 Pierburg Gmbh Adjusting device for adjusting actuators in an internal combustion engine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1537507A (en) * 1967-09-21 1968-08-23 Skf Svenska Kullagerfab Ab Angular roller or needle bearing
US4189167A (en) * 1976-12-20 1980-02-19 Nadella Steering head set assembly
DE2913641A1 (en) * 1979-04-05 1980-10-16 Schaeffler Ohg Industriewerk Bearing for steering rack - has ball bearing races with bearing shells used as rolling supports
DE8203943U1 (en) * 1981-02-24 1982-07-01 RIV-SKF Officine di Villar Perosa S.p.A., 10123 Torino STEERING GEARBOX FOR MOTOR VEHICLES WITH A BACK PRESSURE ELEMENT FOR THE RACK
US4651585A (en) * 1984-10-02 1987-03-24 Riv-Skf Officine Di Villar Perosa S.P.A. Steering box for a motor vehicle
JPH1134886A (en) * 1997-07-16 1999-02-09 Toyoda Mach Works Ltd Steering gear
DE10124663A1 (en) * 2001-05-18 2002-11-21 Ina Schaeffler Kg Self-adjusting bearing for a separation coupling in motor vehicles, consists of an angled shoulder roller bearing with a rigid ring, a surrounding ring, and intermediate rollers

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3762783A (en) * 1972-06-15 1973-10-02 Gen Motors Corp Self adjusting take up bearing
US3826546A (en) * 1973-05-21 1974-07-30 Gen Motors Corp Self-adjusting thrust bearing assembly
SE8903688L (en) * 1989-07-24 1991-01-25 Torrington Co SELF-PROPERTY STOCK
US5983742A (en) * 1998-02-05 1999-11-16 Oiles America Corporation Rack and pinion steering device with split roller rack bar support
DE19928246B4 (en) * 1998-06-19 2004-08-12 Nsk Ltd. Tapered roller bearings

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1537507A (en) * 1967-09-21 1968-08-23 Skf Svenska Kullagerfab Ab Angular roller or needle bearing
US4189167A (en) * 1976-12-20 1980-02-19 Nadella Steering head set assembly
DE2913641A1 (en) * 1979-04-05 1980-10-16 Schaeffler Ohg Industriewerk Bearing for steering rack - has ball bearing races with bearing shells used as rolling supports
DE8203943U1 (en) * 1981-02-24 1982-07-01 RIV-SKF Officine di Villar Perosa S.p.A., 10123 Torino STEERING GEARBOX FOR MOTOR VEHICLES WITH A BACK PRESSURE ELEMENT FOR THE RACK
US4651585A (en) * 1984-10-02 1987-03-24 Riv-Skf Officine Di Villar Perosa S.P.A. Steering box for a motor vehicle
JPH1134886A (en) * 1997-07-16 1999-02-09 Toyoda Mach Works Ltd Steering gear
DE10124663A1 (en) * 2001-05-18 2002-11-21 Ina Schaeffler Kg Self-adjusting bearing for a separation coupling in motor vehicles, consists of an angled shoulder roller bearing with a rigid ring, a surrounding ring, and intermediate rollers

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1999, no. 05 31 May 1999 (1999-05-31) *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006024183A1 (en) * 2004-09-02 2006-03-09 Belimo Holding Ag Linear drive
US20140326913A1 (en) * 2013-05-06 2014-11-06 Michael Führer Arrangement for operating a shut-off valve having a tapered plug
US10385979B2 (en) 2013-05-06 2019-08-20 Magdeburger Industriearmatur-Manufaktur GmbH Arrangement for operating a shut-off valve having a tapered plug

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