EP1360423A1 - Linear guide - Google Patents

Linear guide

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Publication number
EP1360423A1
EP1360423A1 EP02712841A EP02712841A EP1360423A1 EP 1360423 A1 EP1360423 A1 EP 1360423A1 EP 02712841 A EP02712841 A EP 02712841A EP 02712841 A EP02712841 A EP 02712841A EP 1360423 A1 EP1360423 A1 EP 1360423A1
Authority
EP
European Patent Office
Prior art keywords
shaft
bearing
linear guide
needle
housing
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP02712841A
Other languages
German (de)
French (fr)
Inventor
Alexander Zernickel
Horst DÖPPLING
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IHO Holding GmbH and Co KG
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 EP1360423A1 publication Critical patent/EP1360423A1/en
Withdrawn legal-status Critical Current

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/06—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
    • B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
    • B62D1/16—Steering columns
    • B62D1/18—Steering columns yieldable or adjustable, e.g. tiltable
    • B62D1/185—Steering columns yieldable or adjustable, e.g. tiltable adjustable by axial displacement, e.g. telescopically
    • 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
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/06—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement
    • F16D3/065—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement by means of rolling elements
    • 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

Definitions

  • the invention relates to a linear guide for transmitting torques between a tubular housing rotatable about its longitudinal axis and a shaft mounted therein axially displaceably via rolling elements.
  • Linear guides for transmitting torques are used in the motor vehicle sector, for example, for guiding racks or for guiding the steering spindle in a steering column. They are also used for guiding shift shafts or shift rails in the transmission.
  • a linear guide is known from US 3427 656, in which in the area of a radial plane of a shaft, axial roller bearing sets, which surround the shaft and are held in a tubular housing, are supported on the shaft surface with spherically shaped running disks. Since the shaft is circular in cross section, torques of the shaft cannot be transmitted to the housing. In addition, this linear guide requires a tension screw to generate a preload on the installed bearing sets, which acts on the housing in the area of a radial slot in the housing.
  • the document DE 196 19 449 A1 shows and describes a linear guide with a rod or shaft on the running surfaces of which rollers are supported, which are rotatably mounted in a carriage surrounding the shaft.
  • the slide is a rectangular hollow profile with externally accessible T-slots, via which desired parts can be attached.
  • holes must be drilled in the side walls of the hollow profile, in which rotary bearings, in particular ball bearings, are arranged.
  • at least one roller or the rotary bearing holding it requires an adjusting device, preferably an adjusting screw, with which the roller can be adjusted against the shaft without play.
  • the invention has for its object to provide an inexpensive to produce, working with an unlimited stroke linear guide, in which the influences of dimensional tolerances both of the tubular housing and the shaft axially displaceable therein are switched off and which is suitable as a steering shaft or steering column for a motor vehicle, wherein the tubular housing is designed as a steering tube and the shaft axially displaceable therein as a steering spindle.
  • a plurality of axial roller bearings surrounding the shaft are arranged in two radial planes at an axial distance from one another, the axial roller bearings each having two races or running disks and one in between in the area of a radial bearing plane Rolling element set are executed, of which a running disk is completed to form a bushing and is held in the housing, the central axis of the bushing also being arranged offset parallel to a normal to the longitudinal axis of the shaft, and of which the other running disk of the axial rolling bearing is dome-shaped and is supported with its convex spherical cap surface in a surface region of the shaft.
  • the object according to the invention is achieved in that a plurality of radial needle bearings surrounding the shaft are arranged in two radial planes at an axial distance from one another in the tubular housing, the radial needle bearings in each case in the area of a radial bearing plane are each designed with two races or disks and a roller body set located between them, of which a disk is completed to form a needle bushing and held in the housing, the central axis of the The needle bushing is offset or inclined parallel to a normal to the longitudinal axis of the shaft, and of which the other running disk of the needle bearing is dome-shaped and is supported with its convex dome surface in a surface area of the shaft and is provided with a bearing pin which is from is surrounded by the needle bushing and the roller bodies arranged therein as needles.
  • An advantage of the designs according to the invention is that the linear guide not only enables the transmission of torques but also tilting moments. If one considers the shaft longitudinal axis as the X axis and the two axes perpendicular to the X axis and to each other as the Y axis and the Z axis, moments about the X axis are torques which are transmitted from the shaft to the housing. Because the bearings that surround the shaft are arranged in two radial planes at an axial distance from one another, moments about the Y axis and moments about the Z axis, which are tilting moments here, can also pass from the shaft to the housing be transmitted.
  • the housing as a steering tube is a thin-walled housing, it can be used as a pretensioning element due to its elasticity.
  • the respective support bearings are first assembled in the housing with an oversize towards the center.
  • the housing is then expanded, that is to say an elastic deformation of the steering tube, with the corresponding desired prestressing effect.
  • a special clamping screw such as is used in the known prior art, is therefore not necessary in the embodiments according to the invention.
  • the shaft of the linear guide can be a steering column spindle, which is designed as a polygonal shaft with a triangular, square, square or polygonal basic shape in cross-section, with a surface area with a concave surface being worked in between two longitudinal edges that follow one another in the circumferential direction. Due to the concave surface before the bearing capacity is increased. As a result of the use of complete bearing assemblies with rolling elements and raceways according to the invention, it is no longer necessary to incorporate raceways into the housing.
  • FIG. 1 shows a linear guide according to the invention in a perspective view with a cross section in the region of a bearing plane, which shows axial rolling bearings installed in parallel displacement;
  • Figure 2 shows the cross section of Figure 1 in an enlarged view
  • FIG. 3 shows a partial cross section corresponding to FIG. 2 with a modified axial roller bearing
  • FIG. 4 shows a partial cross section corresponding to FIG. 2 with a combined roller bearing containing needles and balls;
  • FIG. 5 shows a partial cross section corresponding to FIG. 2 with a needle bearing modified and pivoted in relation to FIG. 4.
  • a linear guide according to the invention shown in FIGS. 1 and 2 consists of a shaft 1, a housing 2 and a plurality of axial rolling bearings 3 designed as ball bearings.
  • the shaft 1 is the result of a basic shape with a square cross section, into which concave on the four long sides ve surface areas 4 are incorporated. These extend with constant cross-sectional dimensions in the longitudinal direction of the shaft 1.
  • the housing 2 is designed in the form of a square tube with internal cross-sectional dimensions that are larger than the shaft dimensions.
  • the shaft 1 is inserted axially in the housing 2 and is supported there with the axial roller bearings 3 in a radially supported manner.
  • two radial bearing planes are provided on the linear guide, which maintain a longitudinal distance from one another.
  • four axial roller bearings 3 are arranged one behind the other in the circumferential direction of the tubular housing 2.
  • the housing 2 has continuous radial bores 5, each bore 5 being adjacent to a concave surface area 4 of the shaft 1.
  • An axial roller bearing 3 consists in each case of a running disk 6, a bushing 7 and a roller element set 8 arranged between them, balls being used as roller elements.
  • the running disk 6 is dome-shaped and has a dome surface 9 which is convex to the shaft 1 and with which it is supported on the shaft in the adjacent concave surface region 4 of the shaft 1. Due to suitable osculation conditions, there is point contact in a contact point 10.
  • the dome-shaped running disk 6 is supported by the rotating roller set 8 on the bushing 7, which is a non-cutting component and has a raceway for the roller body 8.
  • the bushing 7 is pressed into the respective bore 5 of the housing 2.
  • the bore 5 is arranged in the housing 2 so that the central axis 11 of the bushing 7 is displaced in parallel with an offset a with respect to a normal 12 of the longitudinal axis of the shaft 1 running in the bearing plane.
  • the point of contact 10 is displaced by the dimension b from the normal 12, which can be referred to as a rotary lever.
  • this rotary lever b causes the rotating disk 6 to rotate about the point of contact or the contact line 10 that is created.
  • a tolerance-independent positioning of the axial roller bearings 3 with respect to the shaft 1 is achieved during assembly in the tubular housing 2 as follows: The axial roller bearings 3 are pressed into the bores 5 as deep or until the desired contact on the shaft 1 is reached, which you can tell by the amount of force increase.
  • Figure 1 shows the section in the area of the front bearing level.
  • At least one further bearing level of this type is required in order to enable a play-free torque transmission in both circumferential directions of the linear guide.
  • Two bushings of axial roller bearings 3 can be seen in the area of a rear bearing level.
  • at least two axial roller bearings 3 must be provided for each bearing level.
  • the shaft can have a profile that deviates from the illustration, for example a triangular, polygonal, hollow or solid profile.
  • a round shaft can also be guided according to this principle, but without torque absorption.
  • FIG. 3 shows an axial roller bearing 13 of a linear guide according to the invention, in whose bush 14 an elastic rubber ring 15 is additionally inserted, on which an additional bearing disk 16, which is provided with a raceway for the rolling element set 8, is supported.
  • the rubber ring 15 acts as a compensating element for dimensional tolerances and as a noise-insulating component.
  • FIG. 4 shows that in the linear guide according to the invention, instead of a pure axial roller bearing, a needle bush can also be used.
  • a needle bush can also be used.
  • an additional set of rolling elements 19 for the axial support of a bearing journal 20 is arranged in a needle bushing 17 of a radial needle bearing 18 and is attached to the running disk 6 or in one piece therewith is executed. With the rolling element set 19, the friction of the rotating bearing pin 20 is reduced.
  • FIG. 5 the bottom of a needle bushing 21, which surrounds the bearing journal 20 and the roller body set of a needle bearing 22 consisting of needles, has an inwardly convex bulge 23, on which the bearing journal 20 is axially supported. In this way, the friction is reduced when the journal 20 rotates.
  • the central axis 11 of the needle bush 21 shown in FIG. 5 is inclined at an angle ⁇ to the normal 12 of the shaft longitudinal axis. This results in the same way as in the embodiments according to FIGS. 1 to 4, a rotation lever b for the running disk 6 and the resulting rotation effect.
  • the respective bearing can be fastened in the bore 5 of the housing 2 by caulking 24 (FIGS. 4 and 5) of the housing material or by means of a snap ring.
  • the housing acts as a preloading element

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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)
  • Bearings For Parts Moving Linearly (AREA)

Abstract

The invention relates to a linear guide for transmitting torque between a tubular housing (2) that can be rotated about its longitudinal axis and a shaft (1) that is mounted in said housing so that it can be displaced axially by means of rolling bodies. Several axial anti-friction bearings (3) that surround the shaft (1), each having two bearing races or discs, with a set of rolling bodies therebetween, are arranged in the tubular housing (2) in the vicinity of a radial bearing plane. One bearing disc of the anti-friction bearings forms a bushing and is retained in the housing (2), the central axis of said bushing being offset in parallel by a certain distance (a) from the perpendicular of the longitudinal axis of the shaft and the other bearing disc of the anti-friction bearings (3) is dome-shaped, its convex dome surface being supported by a surface region of the shaft (1).

Description

LINEARFÜHRUNG ZUM ÜBERTRAGEN VON DREHMOMENTEN LINEAR GUIDE FOR TRANSMITTING TORQUE
Beschreibungdescription
Gebiet der ErfindungField of the Invention
Die Erfindung betrifft eine Linearführung zum Übertragen von Drehmomenten zwischen einem rohrformigen, um seine Längsachse drehbaren Gehäuse und einer darin über Wälzkörper axial verschiebbar gelagerten Welle.The invention relates to a linear guide for transmitting torques between a tubular housing rotatable about its longitudinal axis and a shaft mounted therein axially displaceably via rolling elements.
Linearführungen zum Übertragen von Drehmomenten werden im Kraftfahrzeugbereich beispielsweise für die Führung von Zahnstangen oder für die Füh- rung der Lenkspindel in einer Lenksäule verwendet. Auch für die Führung von Schaltwellen oder Schaltschienen im Getriebe werden sie eingesetzt.Linear guides for transmitting torques are used in the motor vehicle sector, for example, for guiding racks or for guiding the steering spindle in a steering column. They are also used for guiding shift shafts or shift rails in the transmission.
Aus der Druckschrift US 3427 656 ist eine Linearführung bekannt, bei der sich im Bereich einer radialen Ebene einer Welle Axialwälzlagersätze, welche die Welle umgeben und in einem rohrformigen Gehäuse gehalten sind, mit kalot- tenförmig ausgebildeten Laufscheiben an der Wellenoberfläche abstützen. Da die Welle im Querschnitt kreisförmig ist, können Drehmomente der Welle auf das Gehäuse nicht übertragen werden. Außerdem benötigt diese Linearführung zur Erzeugung einer Vorspannung der eingebauten Lagersätze eine Spann- schraube, die im Bereich eines Radialschlitzes des Gehäuses auf das Gehäuse einwirkt. Die Druckschrift DE 196 19 449 A1 zeigt und beschreibt eine Linearführung mit einer Stange oder Welle an deren Laufflächen Rollen abgestützt sind, die in einem die Welle umgebenden Schlitten drehbar gelagert sind. Der Schlitten ist ein rechteckiges Hohlprofil mit von außen zugänglichen T-Nuten, über welche gewünschte Teile befestigt werden können. Zur Lagerung der Rollen müssen hier in den Seitenwänden des Hohlprofils Bohrungen angebracht werden, in welchen Drehlager, insbesondere Kugellager, angeordnet sind. Darüberhinaus benötigt mindestens eine Rolle bzw. das sie haltende Drehlager eine Stellvorrichtung, vorzugsweise eine Stellschraube, mit welcher die Rolle spielfrei ge- gen die Welle eingestellt werden kann.A linear guide is known from US 3427 656, in which in the area of a radial plane of a shaft, axial roller bearing sets, which surround the shaft and are held in a tubular housing, are supported on the shaft surface with spherically shaped running disks. Since the shaft is circular in cross section, torques of the shaft cannot be transmitted to the housing. In addition, this linear guide requires a tension screw to generate a preload on the installed bearing sets, which acts on the housing in the area of a radial slot in the housing. The document DE 196 19 449 A1 shows and describes a linear guide with a rod or shaft on the running surfaces of which rollers are supported, which are rotatably mounted in a carriage surrounding the shaft. The slide is a rectangular hollow profile with externally accessible T-slots, via which desired parts can be attached. To support the rollers, holes must be drilled in the side walls of the hollow profile, in which rotary bearings, in particular ball bearings, are arranged. In addition, at least one roller or the rotary bearing holding it requires an adjusting device, preferably an adjusting screw, with which the roller can be adjusted against the shaft without play.
Aus der Druckschrift DE 37 30 393 A1 ist eine Drehmomente übertragende Verbindung für axial ineinander verschiebliche Wellenteile bekannt, die für die Lenkwelle von Kraftfahrzeugen bestimmt ist. Bei dieser Linearführung der ein- gangs genannten Art sind als Wälzkörper Kugeln einerseits in inneren Längsnuten des äußeren Wellenteils und andererseits in äußeren Längsnuten des inneren Wellenteils spielfrei eingespannt. Um bei der Axialverschiebung der Wellenteile relativ zueinander einen Ausgleich von Fertigungstoleranzen und eine Leichtgängigkeit ohne zusätzliche Bearbeitung zu erreichen, müssen hier die Kugeln in Laufbahnen aus Blech angeordnet werden, welche in die Längsnuten eingesetzt und, bezogen auf die Mittellängsachse der Welle, radial unter Vorspannung gesetzt sind. Außerdem können die beiden Wellenteile nur mit einem begrenzten Hub relativ zueinander axial bewegt werden.From the document DE 37 30 393 A1 a torque-transmitting connection for axially displaceable shaft parts is known, which is intended for the steering shaft of motor vehicles. In this linear guide of the type mentioned at the beginning, balls are clamped without play as rolling elements on the one hand in inner longitudinal grooves of the outer shaft part and on the other hand in outer longitudinal grooves of the inner shaft part. In order to compensate for manufacturing tolerances and ease of movement without additional machining when axially displacing the shaft parts relative to each other, the balls must be arranged in sheet metal raceways, which are inserted into the longitudinal grooves and radially preloaded with respect to the central longitudinal axis of the shaft are. In addition, the two shaft parts can only be moved axially relative to one another with a limited stroke.
Zusammenfassung der ErfindungSummary of the invention
Der Erfindung liegt die Aufgabe zugrunde, eine preisgünstig herstellbare, mit unbegrenztem Hub arbeitende Linearführung anzugeben, bei welcher die Einflüsse von Maßtoleranzen sowohl des rohrformigen Gehäuses als auch der darin axial verschiebbaren Welle ausgeschaltet sind und die sich als Lenkwelle oder Lenksäule für ein Kraftfahrzeug eignet, wobei das rohrförmige Gehäuse als Lenkrohr und die darin axial verschiebbare Welle als Lenkspindel ausgebildet ist. Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß in dem rohrformigen Gehäuse mehrere die Welle umgebende Axialwälzlager in zwei radialen, in einem axialen Abstand voneinander befindlichen Ebenen angeordnet sind, wobei jeweils im Bereich einer radialen Lagerebene die Axialwälzlager mit jeweils zwei Laufringen oder Laufscheiben und einem dazwischen befindlichen Wälzkörpersatz ausgeführt sind, von denen eine Laufscheibe zu einer Büchse vervollständigt und in dem Gehäuse gehalten ist, wobei außerdem die Mittelachse der Büchse mit einem Versatz zu einer Normalen der Wellen- Längsachse parallel verschoben angeordnet ist, und von denen die andere Laufscheibe des Axialwälzlagers kalottenförmig ausgebildet und mit ihrer konvexen Kalottenfläche in einem Oberflächenbereich der Welle an dieser abgestützt ist.The invention has for its object to provide an inexpensive to produce, working with an unlimited stroke linear guide, in which the influences of dimensional tolerances both of the tubular housing and the shaft axially displaceable therein are switched off and which is suitable as a steering shaft or steering column for a motor vehicle, wherein the tubular housing is designed as a steering tube and the shaft axially displaceable therein as a steering spindle. This object is achieved in that in the tubular housing a plurality of axial roller bearings surrounding the shaft are arranged in two radial planes at an axial distance from one another, the axial roller bearings each having two races or running disks and one in between in the area of a radial bearing plane Rolling element set are executed, of which a running disk is completed to form a bushing and is held in the housing, the central axis of the bushing also being arranged offset parallel to a normal to the longitudinal axis of the shaft, and of which the other running disk of the axial rolling bearing is dome-shaped and is supported with its convex spherical cap surface in a surface region of the shaft.
Infolge der Parallelverschiebung der Büchsenachse gegenüber der Wellenmitte einerseits und infolge der konvexen Kalottenfläche der Laufscheibe andererseits, die sich in dem Oberflächenbereich der Welle abstützt, ergibt sich eine Verschiebung von deren Berührungspunkt und damit ein Rotationshebel, der während der Linearbewegung der Welle eine Rotation der Laufscheibe bewirkt. Das Ausschalten des Einflusses von Maßtoleranzen wird durch eine toleranzunabhängige Positionierung des Axialwälzlagers in Bezug auf die Welle erreicht.As a result of the parallel displacement of the sleeve axis with respect to the shaft center on the one hand and due to the convex spherical surface of the running disk, which is supported in the surface area of the shaft, there is a shift from its contact point and thus a rotation lever which causes the running disk to rotate during the linear movement of the shaft , Switching off the influence of dimensional tolerances is achieved by positioning the axial roller bearing with respect to the shaft regardless of tolerance.
Anstatt die Büchse mit ihrer Achse parallel verschoben anzuordnen, kann die gleiche Wirkung auch durch eine Anordnung der Büchse mit geneigter Achse erzielt werden. Nach einem weiteren Vorschlag wird die erfindungsgemäße Aufgabe dadurch gelöst, dass in dem rohrformigen Gehäuse mehrere die Welle umgebende Radial-Nadellager in zwei radialen, in einem axialen Abstand voneinander befindlichen Ebenen angeordnet sind, wobei jeweils im Be- reich einer radialen Lagerebene die Radial-Nadellager mit jeweils zwei Laufringen oder Laufscheiben und einem dazwischen befindlichen Wälzkörpersatz ausgeführt sind, von denen eine Laufscheibe zu einer Nadelbüchse vervollständigt und in dem Gehäuse gehalten ist, wobei die Mittelachse der Nadelbüchse mit einem Versatz zu einer Normalen der Wellen-Längsachse parallel verschoben oder geneigt angeordnet ist, und von denen die andere Laufscheibe des Nadellagers kalottenförmig ausgebildet und mit ihrer konvexen Kalottenfläche in einem Oberflächenbereich der Welle an dieser abgestützt und mit einem Lagerzapfen versehen ist, der von der Nadelbüchse und darin angeordneten, als Nadeln ausgebildeten Wälzkörpern umgeben ist.Instead of arranging the sleeve with its axis displaced in parallel, the same effect can also be achieved by arranging the sleeve with an inclined axis. According to a further proposal, the object according to the invention is achieved in that a plurality of radial needle bearings surrounding the shaft are arranged in two radial planes at an axial distance from one another in the tubular housing, the radial needle bearings in each case in the area of a radial bearing plane are each designed with two races or disks and a roller body set located between them, of which a disk is completed to form a needle bushing and held in the housing, the central axis of the The needle bushing is offset or inclined parallel to a normal to the longitudinal axis of the shaft, and of which the other running disk of the needle bearing is dome-shaped and is supported with its convex dome surface in a surface area of the shaft and is provided with a bearing pin which is from is surrounded by the needle bushing and the roller bodies arranged therein as needles.
Ein Vorteil der erfindungsgemäßen Ausführungen besteht darin, dass mit der Linearführung nicht nur die Übertragung von Drehmomenten, sondern auch von Kippmomenten möglich ist. Betrachtet man die Wellenlängsachse als X- Achse und die beiden zu der X-Achse und zueinander rechtwinklig stehenden Achsen als Y-Achse und Z-Achse, so sind Momente um die X-Achse Drehmomente, welche von der Welle auf das Gehäuse übertragen werden. Weil die Lager, welche die Welle umgeben, in zwei radialen, in einem axialen Abstand voneinander befindlichen Ebenen angeordnet sind, können auch Momente um die Y-Achse und Momente um die Z-Achse, welche hier Kippmomente sind, von der Welle auf das Gehäuse übertragen werden.An advantage of the designs according to the invention is that the linear guide not only enables the transmission of torques but also tilting moments. If one considers the shaft longitudinal axis as the X axis and the two axes perpendicular to the X axis and to each other as the Y axis and the Z axis, moments about the X axis are torques which are transmitted from the shaft to the housing. Because the bearings that surround the shaft are arranged in two radial planes at an axial distance from one another, moments about the Y axis and moments about the Z axis, which are tilting moments here, can also pass from the shaft to the housing be transmitted.
Da das Gehäuse als Lenkrohr ein dünnwandiges Gehäuse ist, kann es infolge seiner Elastizität als Vorspannelement genutzt werden. In diesem Fall werden die jeweiligen Stützlager zunächst in dem Gehäuse mit einem Übermaß zur Mitte hin montiert. Beim anschließenden Einführen der Welle in das Gehäuse erfolgt dann ein Aufweiten des Gehäuses, also eine elastische Verformung des Lenkrohres, mit dem entsprechenden gewünschten Vorspannungseffekt. Eine besondere Spannschraube, wie sie im vorbekannten Stand der Technik verwendet wird', ist bei den erfindungsgemäßen Ausführungen also nicht erforderlich.Since the housing as a steering tube is a thin-walled housing, it can be used as a pretensioning element due to its elasticity. In this case, the respective support bearings are first assembled in the housing with an oversize towards the center. When the shaft is subsequently introduced into the housing, the housing is then expanded, that is to say an elastic deformation of the steering tube, with the corresponding desired prestressing effect. A special clamping screw, such as is used in the known prior art, is therefore not necessary in the embodiments according to the invention.
Die Welle der Linearführung kann eine Lenksäulenspindel sein, welche als Mehrkantwelle mit im Querschnitt dreieckiger, viereckiger, quadratischer oder vieleckiger Grundform ausgebildet ist, wobei zwischen zwei in Umfangsrichtung aufeinanderfolgenden Längskanten jeweils ein Oberflächenbereich mit einer konkaven Oberfläche eingearbeitet ist. Durch die konkaven Oberflächenberei- ehe wird die Tragfähigkeit der Lager erhöht. Infolge der erfindungsgemäßen Verwendung vollständiger Lagerbausätze mit Wälzkörpern und Laufbahnen ist es nicht mehr erforderlich, Laufbahnen in das Gehäuse einzuarbeiten.The shaft of the linear guide can be a steering column spindle, which is designed as a polygonal shaft with a triangular, square, square or polygonal basic shape in cross-section, with a surface area with a concave surface being worked in between two longitudinal edges that follow one another in the circumferential direction. Due to the concave surface before the bearing capacity is increased. As a result of the use of complete bearing assemblies with rolling elements and raceways according to the invention, it is no longer necessary to incorporate raceways into the housing.
Kurze Beschreibung der ZeichnungBrief description of the drawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden im folgenden näher beschrieben. Es zeigenEmbodiments of the invention are shown in the drawing and are described in more detail below. Show it
Figur 1 eine erfindungsgemäße Linearführung in einer perspektivischen Ansicht mit einem Querschnitt im Bereich einer Lagerebene, welcher parallel verschoben eingebaute Axialwälzlager zeigt;FIG. 1 shows a linear guide according to the invention in a perspective view with a cross section in the region of a bearing plane, which shows axial rolling bearings installed in parallel displacement;
Figur 2 den Querschnitt nach Figur 1 in vergrößerter Darstellung;Figure 2 shows the cross section of Figure 1 in an enlarged view;
Figur 3 einen Figur 2 entsprechenden Teilquerschnitt mit einem abgewandelten Axialwälzlager;3 shows a partial cross section corresponding to FIG. 2 with a modified axial roller bearing;
Figur 4 einen Figur 2 entsprechenden Teilquerschnitt mit einem kombinierten, Nadeln und Kugeln enthaltenden Wälzlager;FIG. 4 shows a partial cross section corresponding to FIG. 2 with a combined roller bearing containing needles and balls;
Figur 5 einen Figur 2 entsprechenden Teilquerschnitt mit einem gegenüber Figur 4 abgewandelten und verschwenkt ein- gebauten Nadellager.5 shows a partial cross section corresponding to FIG. 2 with a needle bearing modified and pivoted in relation to FIG. 4.
Ausführliche Beschreibung der ZeichnungDetailed description of the drawing
Eine in den Figuren 1 und 2 dargestellte erfindungsgemäße Linearführung be- steht aus einer Welle 1 , einem Gehäuse 2 und mehreren als Kugellager ausgebildeten Axialwälzlagern 3. Die Welle 1 ist aus einer im Querschnitt quadratischen Grundform hervorgegangen, in welche an den vier Längsseiten konka- ve Oberflächenbereiche 4 eingearbeitet sind. Diese erstrecken sich mit konstanten Querschnittsabmessungen in Längsrichtung der Welle 1.A linear guide according to the invention shown in FIGS. 1 and 2 consists of a shaft 1, a housing 2 and a plurality of axial rolling bearings 3 designed as ball bearings. The shaft 1 is the result of a basic shape with a square cross section, into which concave on the four long sides ve surface areas 4 are incorporated. These extend with constant cross-sectional dimensions in the longitudinal direction of the shaft 1.
Das Gehäuse 2 ist in der Form eines Vierkantrohres mit gegenüber den Wel- lenabmessungen größeren Querschnittsinnenmaßen ausgebildet. Die Welle 1 ist in dem Gehäuse 2 axial eingesteckt und dort mit den Axialwälzlagern 3 radial abgestützt gelagert. Hierfür sind an der Linearführung zwei radiale Lagerebenen vorgesehen, die einen Längsabstand voneinander einhalten. In dem Bereich jeder Lagerebene sind vier Axialwälzlager 3 in Umfangsrichtung des rohrformigen Gehäuses 2 hintereinander angeordnet. Zu diesem Zweck weist das Gehäuse 2 durchgehende radiale Bohrungen 5 auf, wobei jede Bohrung 5 einem konkaven Oberflächenbereich 4 der Welle 1 benachbart ist.The housing 2 is designed in the form of a square tube with internal cross-sectional dimensions that are larger than the shaft dimensions. The shaft 1 is inserted axially in the housing 2 and is supported there with the axial roller bearings 3 in a radially supported manner. For this purpose, two radial bearing planes are provided on the linear guide, which maintain a longitudinal distance from one another. In the area of each bearing level, four axial roller bearings 3 are arranged one behind the other in the circumferential direction of the tubular housing 2. For this purpose, the housing 2 has continuous radial bores 5, each bore 5 being adjacent to a concave surface area 4 of the shaft 1.
Ein Axialwälzlager 3 besteht jeweils aus einer Laufscheibe 6, einer Büchse 7 und einem dazwischen angeordneten Wälzkörpersatz 8, wobei als Wälzkörper Kugeln verwendet sind. Die Laufscheibe 6 ist kalottenförmig geformt und weist eine zu der Welle 1 konvexe Kalottenfläche 9 auf, mit der sie in dem benachbarten konkaven Oberflächenbereich 4 der Welle 1 an der Welle abgestützt ist. Aufgrund geeigneter Schmiegungsverhältnisse ergibt sich dabei eine Punktbe- rührung in einem Berührungspunkt 10.An axial roller bearing 3 consists in each case of a running disk 6, a bushing 7 and a roller element set 8 arranged between them, balls being used as roller elements. The running disk 6 is dome-shaped and has a dome surface 9 which is convex to the shaft 1 and with which it is supported on the shaft in the adjacent concave surface region 4 of the shaft 1. Due to suitable osculation conditions, there is point contact in a contact point 10.
Die kalottenförmige Laufscheibe 6 stützt sich über den umlaufenden Wälzkörpersatz 8 an der Büchse 7 ab, die ein spanlos geformtes Bauteil ist und eine Laufbahn für den Wälzkörpersatz 8 aufweist. Die Büchse 7 ist in die jeweilige Bohrung 5 des Gehäuses 2 eingepreßt. Dabei ist die Bohrung 5 in dem Gehäuse 2 so angeordnet, daß die Mittelachse 11 der Büchse 7 gegenüber einer in der Lagerebene verlaufenden Normalen 12 der Längsachse der Welle 1 mit einem Versatz a parallel verschoben ist. Infolge dieser Verschiebung ergibt sich eine Verlagerung des Berührungspunktes 10 um das Maß b aus der Nor- malen 12, welches als Rotationshebel bezeichnet werden kann. Während einer Linearbewegung der Welle 1 innerhalb des Gehäuses 2 bewirkt dieser Rotationshebel b eine Rotation der Laufscheibe 6 um den Berührungspunkt bzw. die entstehende Berührungslinie 10. Eine toleranzunabhängige Positionierung der Axialwälzlager 3 zu der Welle 1 wird während der Montage im rohrformigen Gehäuse 2 wie folgt erreicht: Die Axialwälzlager 3 werden in die Bohrungen 5 so tief bzw. so lange eingepreßt, bis der gewünschte Kontakt an der Welle 1 erreicht ist, was man an dem Maß des Kraftanstiegs erkennen kann.The dome-shaped running disk 6 is supported by the rotating roller set 8 on the bushing 7, which is a non-cutting component and has a raceway for the roller body 8. The bushing 7 is pressed into the respective bore 5 of the housing 2. The bore 5 is arranged in the housing 2 so that the central axis 11 of the bushing 7 is displaced in parallel with an offset a with respect to a normal 12 of the longitudinal axis of the shaft 1 running in the bearing plane. As a result of this displacement, the point of contact 10 is displaced by the dimension b from the normal 12, which can be referred to as a rotary lever. During a linear movement of the shaft 1 within the housing 2, this rotary lever b causes the rotating disk 6 to rotate about the point of contact or the contact line 10 that is created. A tolerance-independent positioning of the axial roller bearings 3 with respect to the shaft 1 is achieved during assembly in the tubular housing 2 as follows: The axial roller bearings 3 are pressed into the bores 5 as deep or until the desired contact on the shaft 1 is reached, which you can tell by the amount of force increase.
Figur 1 zeigt den Schnitt im Bereich der vorderen Lagerebene. Zur Positionierung der Welle 1 in dem Gehäuse 2 wird mindestens noch eine weitere solche Lagerebene benötigt, um eine spielfreie Drehmomentübertragung in beiden Umfangsrichtungen der Linearführung zu ermöglichen. Hiervon sind im Bereich einer hinteren Lagerebene zwei Büchsen von Axialwälzlagern 3 erkennbar. Um bei diesem Vierkantprofil die Wellenpositionierung in allen Achsrichtungen durchführen zu können, müssen pro Lagerebene mindestens zwei Axialwälzla- ger 3 vorgesehen werden.Figure 1 shows the section in the area of the front bearing level. To position the shaft 1 in the housing 2, at least one further bearing level of this type is required in order to enable a play-free torque transmission in both circumferential directions of the linear guide. Two bushings of axial roller bearings 3 can be seen in the area of a rear bearing level. In order to be able to position the shaft in all axial directions with this square profile, at least two axial roller bearings 3 must be provided for each bearing level.
Die Welle kann ein von der Darstellung abweichendes Profil, beispielsweise ein Dreikant-, Mehrkant-, Hohl- oder Vollprofil aufweisen. Auch eine runde Welle kann nach diesem Prinzip geführt werden, jedoch ohne Drehmomentauf- nähme.The shaft can have a profile that deviates from the illustration, for example a triangular, polygonal, hollow or solid profile. A round shaft can also be guided according to this principle, but without torque absorption.
Figur 3 zeigt ein Axialwälzlager 13 einer erfindungsgemäßen Linearführung, in dessen Büchse 14 zusätzlich ein federnder Gummiring 15 eingesetzt ist, an dem sich eine zusätzliche, mit einer Laufbahn für den Wälzkörpersatz 8 verse- hene Lagerscheibe 16 abstützt. Hier wirkt der Gummiring 15 als Ausgleichselement für Maßtoleranzen und als geräuschdämmendes Bauteil.FIG. 3 shows an axial roller bearing 13 of a linear guide according to the invention, in whose bush 14 an elastic rubber ring 15 is additionally inserted, on which an additional bearing disk 16, which is provided with a raceway for the rolling element set 8, is supported. Here the rubber ring 15 acts as a compensating element for dimensional tolerances and as a noise-insulating component.
Die Figuren 4 und 5 zeigen, daß bei der erfindungsgemäßen Linearführung statt eines reinen Axialwälzlagers auch eine Nadelbüchse verwendet werden kann. In Figur 4 ist in einer Nadelbüchse 17 eines Radial-Nadellagers 18 ein zusätzlicher Wälzkörpersatz 19 für die axiale Abstützung eines Lagerzapfens 20 angeordnet, der an der Laufscheibe 6 befestigt bzw. mit dieser einstückig ausgeführt ist. Mit dem Wälzkörpersatz 19 wird die Reibung des sich drehenden Lagerzapfens 20 verringert.Figures 4 and 5 show that in the linear guide according to the invention, instead of a pure axial roller bearing, a needle bush can also be used. In FIG. 4, an additional set of rolling elements 19 for the axial support of a bearing journal 20 is arranged in a needle bushing 17 of a radial needle bearing 18 and is attached to the running disk 6 or in one piece therewith is executed. With the rolling element set 19, the friction of the rotating bearing pin 20 is reduced.
In Figur 5 weist der Boden einer Nadelbüchse 21, die den Lagerzapfen 20 und den aus Nadeln bestehenden Wälzkörpersatz eines Nadellagers 22 umgibt, eine nach innen konvexe Auswölbung 23 auf, an welcher der Lagerzapfen 20 axial abgestützt ist. Auf diese Weise wird hier bei der Drehung des Lagerzapfens 20 die Reibung reduziert. Die Mittelachse 11 der in Figur 5 dargestellten Nadelbüchse 21 ist zu der Normalen 12 der Wellen-Längsachse um einen Winkel α geneigt angeordnet. Dadurch entsteht ebenso, wie bei den Ausführungen nach den Figuren 1 bis 4 ein Rotationshebel b für die Laufscheibe 6 und der dadurch bedingte Rotationseffekt.In FIG. 5, the bottom of a needle bushing 21, which surrounds the bearing journal 20 and the roller body set of a needle bearing 22 consisting of needles, has an inwardly convex bulge 23, on which the bearing journal 20 is axially supported. In this way, the friction is reduced when the journal 20 rotates. The central axis 11 of the needle bush 21 shown in FIG. 5 is inclined at an angle α to the normal 12 of the shaft longitudinal axis. This results in the same way as in the embodiments according to FIGS. 1 to 4, a rotation lever b for the running disk 6 and the resulting rotation effect.
Bei allen Ausführungsbeispielen kann das jeweilige Lager durch eine Ver- stemmung 24 (Figuren 4 und 5) des Gehäusewerkstoffs oder mittels eines Sprengringes in der Bohrung 5 des Gehäuses 2 befestigt werden.In all of the exemplary embodiments, the respective bearing can be fastened in the bore 5 of the housing 2 by caulking 24 (FIGS. 4 and 5) of the housing material or by means of a snap ring.
Zur Erzeugung der Vorspannung der Linearführung ist es möglich, eines oder mehrere Lager tiefer einzupressen, als es das Wellenmaß erfordert, beispiels- weise nach Einführen eines Werkzeugs mit gegenüber der Welle geringeren Abmessungen, und nach dem Entfernen dieses Werkzeugs die Welle in das Gehäuse einzuführen. In diesem Fall wirkt das Gehäuse als vorspannendes Element To generate the preload of the linear guide, it is possible to press one or more bearings deeper than the shaft dimension requires, for example after inserting a tool with smaller dimensions than the shaft, and after removing this tool, inserting the shaft into the housing. In this case, the housing acts as a preloading element
BezugszahlenlisteLIST OF REFERENCE NUMBERS
1 Welle1 wave
Gehäusecasing
3 Axialwälzlager konkaver Oberflächenbereich3 axial roller bearings with concave surface area
5 Bohrung5 holes
Laufscheibesheave
7 Büchse7 rifle
8 Wälzkörpersatz8 rolling element set
9 Kalottenfläche9 calotte surface
10 Berührungspunkt10 point of contact
11 Mittelachse11 central axis
12 Normale12 normal
13 Axialwälzlager13 axial roller bearings
14 Büchse14 rifle
15 Gummiring15 rubber ring
16 Lagerscheibe16 bearing washer
17 Nadelbüchse17 needle bush
18 Nadellager18 needle bearings
19 Wälzkörpersatz19 Rolling element set
20 Lagerzapfen20 journals
21 Nadelbüchse21 needle bush
22 Nadellager22 needle bearings
23 Auswölbung23 bulge
24 Verstemmung24 caulking
a Versatz b Maß, Rotationshebel α Winkel a offset b dimension, rotary lever α angle

Claims

Patentansprüche claims
1. Linearführung zum Übertragen von Drehmomenten zwischen einem rohrformigen, um seine Längsachse drehbaren Gehäuse (2) und einer darin über Wälzkörper axial verschiebbar gelagerten Welle (1), dadurch gekennzeichnet, daß in dem rohrformigen Gehäuse (2) mehrere die Welle (1) umgebende Axialwälzlager (3, 13) in zwei radialen, in einem axialen Abstand voneinander befindlichen Ebenen angeordnet sind, wo- bei jeweils im Bereich einer radialen Lagerebene die Axialwälzlager (3,1. Linear guide for transmitting torques between a tubular housing (2) rotatable about its longitudinal axis and a shaft (1) axially displaceably mounted in it via rolling elements, characterized in that in the tubular housing (2) several surrounding the shaft (1) Axial roller bearings (3, 13) are arranged in two radial planes at an axial distance from one another, the axial roller bearings (3, 13,
13) mit jeweils zwei Laufringen oder Laufscheiben und einem dazwischen befindlichen Wälzkörpersatz ausgeführt sind, von denen eine Laufscheibe zu einer Büchse (7, 14) vervollständigt und in dem Gehäuse (2) gehalten ist, wobei außerdem die Mittelachse (11) der Büchse (7, 14) mit einem Versatz (a) zu einer Normalen (12) der Wellen-13) are each designed with two races or running disks and a set of rolling elements in between, of which a running disk is completed to form a bush (7, 14) and is held in the housing (2), the central axis (11) of the bush (7 , 14) with an offset (a) to a normal (12) of the wave
Längsachse parallel verschoben angeordnet ist, und von denen die andere Laufscheibe (6) des Axialwälzlagers (3, 13) kalottenförmig ausgebildet und mit ihrer konvexen Kalottenfläche (9) in einem Oberflächenbereich (4) der Welle (1) an dieser abgestützt ist.Longitudinal axis is arranged in parallel, and of which the other disc (6) of the axial roller bearing (3, 13) is dome-shaped and is supported with its convex dome surface (9) in a surface region (4) of the shaft (1).
2. Linearführung zum Übertragen von Drehmomenten zwischen einem rohrformigen, um seine Längsachse drehbaren Gehäuse (2) und einer darin über Wälzkörper axial verschiebbar gelagerten Welle (1), dadurch gekennzeichnet, daß in dem rohrformigen Gehäuse (2) mehrere die Welle (1) umgebende Radial-Nadellager (18, 22) in zwei radialen, in einem axialen Abstand voneinander befindlichen Ebenen angeordnet sind, wobei jeweils im Bereich einer radialen Lagerebene die Radial- Nadellager (18, 22) mit jeweils zwei Laufringen oder Laufscheiben und einem dazwischen befindlichen Wälzkörpersatz ausgeführt sind, von denen eine Laufscheibe zu einer Nadelbüchse (17, 21) vervollständigt und in dem Gehäuse (2) gehalten ist, wobei die Mittelachse (11) der Nadelbüchse (17, 21) mit einem Versatz zu einer Normalen (12) der Wellen-Längsachse parallel verschoben oder geneigt angeordnet ist, und von denen die andere Laufscheibe (6) des Nadellagers (18, 22) kalot- tenförmig ausgebildet und mit ihrer konvexen Kalottenfläche (9) in einem Oberflächenbereich (4) der Welle (1) an dieser abgestützt und mit einem Lagerzapfen (20) versehen ist, der von der Nadelbüchse (17, 21) und darin angeordneten, als Nadeln ausgebildeten Wälzkörpern umgeben ist.2. Linear guide for transmitting torques between a tubular housing (2) rotatable about its longitudinal axis and a shaft (1) axially displaceably mounted therein via rolling elements, characterized in that in the tubular housing (2) several surrounding the shaft (1) Radial needle roller bearings (18, 22) are arranged in two radial planes at an axial distance from one another, the radial needle roller bearings (18, 22) each having two races or running disks and a rolling element set in between in the area of a radial bearing plane of which a running disk is completed to form a needle bushing (17, 21) and held in the housing (2), the central axis (11) of the needle bushing (17, 21) being offset with respect to a normal (12) of the shaft Longitudinal axis is displaced parallel or inclined, and of which the other running disk (6) of the needle bearing (18, 22) is dome-shaped and with its convex dome surface (9) is supported on the shaft (1) in a surface region (4) thereof and is provided with a bearing journal (20) , which is surrounded by the needle bushing (17, 21) and rolling elements arranged therein and designed as needles.
3. Linearführung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Büchse (7, 14) des Axialwälzlagers (3, 13) bzw. die Nadelbüchse (17, 21) des Nadellagers (18, 22) jeweils in eine durchgehende radiale3. Linear guide according to claim 1 or 2, characterized in that the bush (7, 14) of the axial roller bearing (3, 13) or the needle bush (17, 21) of the needle bearing (18, 22) each in a continuous radial
Bohrung (5) des Gehäuses (2) eingepreßt ist.Bore (5) of the housing (2) is pressed.
4. Linearführung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Welle (1) eine Lenksäulenspindel ist, welche als Mehrkantwelle mit im Querschnitt dreieckiger, viereckiger, quadratischer oder vieleckiger4. Linear guide according to claim 1 or 2, characterized in that the shaft (1) is a steering column spindle, which as a polygonal shaft with a triangular, quadrangular, square or polygonal cross section
Grundform ausgebildet ist, wobei zwischen zwei in Umfangsrichtung aufeinanderfolgenden Längskanten jeweils ein Oberflächenbereich (4) mit einer konkaven Oberfläche eingearbeitet ist.Basic shape is formed, a surface area (4) with a concave surface being worked in between each of two longitudinal edges that follow one another in the circumferential direction.
5. Linearführung nach Anspruch 1, dadurch gekennzeichnet, daß das Axialwälzlager (3) als Kugellager ausgeführt ist.5. Linear guide according to claim 1, characterized in that the axial rolling bearing (3) is designed as a ball bearing.
6. Linearführung nach Anspruch 2, dadurch gekennzeichnet, daß am Boden der Nadelbüchse (21) eine nach innen konvexe warzenförmige Auswölbung (23) angeordnet ist, an welcher der Lagerzapfen (20) mit seiner äußeren Stirnseite abgestützt ist.6. Linear guide according to claim 2, characterized in that an inwardly convex wart-shaped bulge (23) is arranged on the bottom of the needle sleeve (21), on which the bearing journal (20) is supported with its outer end face.
7. Linearführung nach Anspruch 2, dadurch gekennzeichnet, daß zwischen dem Boden der Nadelbüchse (17) und der äußeren Stirnseite des Lagerzapfens (20) ein Wälzkörpersatz (19) eines Axialwälzlagers angeordnet ist. 7. Linear guide according to claim 2, characterized in that a roller body set (19) of an axial roller bearing is arranged between the bottom of the needle bush (17) and the outer end face of the bearing pin (20).
8. Linearführung nach Anspruch 1 , dadurch gekennzeichnet, daß in dem Axialwälzlager (13) eine mit einer Laufbahn für Wälzkörper versehene Lagerscheibe (16) mittels eines Federelementes, beispielsweise eines Gummiringes (15) abgestützt ist.8. Linear guide according to claim 1, characterized in that in the axial rolling bearing (13) is provided with a raceway for rolling elements bearing disc (16) by means of a spring element, for example a rubber ring (15) is supported.
9. Linearführung nach Anspruch 2, dadurch gekennzeichnet, daß bezüglich der Mittelachse (11) der Nadelbüchse (21) anstelle einer um den Versatz parallel verschobenen Anordnung eine um einen Winkel α zu der Normalen (12) der Wellen-Längsachse geneigte Anordnung vorge- sehen ist. 9. Linear guide according to claim 2, characterized in that with respect to the central axis (11) of the needle bush (21) instead of an arrangement displaced parallel by the offset, an arrangement inclined by an angle α to the normal (12) of the shaft longitudinal axis is provided is.
EP02712841A 2001-02-15 2002-01-24 Linear guide Withdrawn EP1360423A1 (en)

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DE10106982A DE10106982A1 (en) 2001-02-15 2001-02-15 linear guide
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JP2004518099A (en) 2004-06-17
US20040109620A1 (en) 2004-06-10
KR20030077008A (en) 2003-09-29
US7147375B2 (en) 2006-12-12
WO2002064989A1 (en) 2002-08-22
US20060005659A1 (en) 2006-01-12
US6948401B2 (en) 2005-09-27
DE10106982A1 (en) 2002-08-29

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