DE19803929A1 - Roller bearing arrangement for components moving in azimuth - Google Patents

Roller bearing arrangement for components moving in azimuth

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Publication number
DE19803929A1
DE19803929A1 DE19803929A DE19803929A DE19803929A1 DE 19803929 A1 DE19803929 A1 DE 19803929A1 DE 19803929 A DE19803929 A DE 19803929A DE 19803929 A DE19803929 A DE 19803929A DE 19803929 A1 DE19803929 A1 DE 19803929A1
Authority
DE
Germany
Prior art keywords
bearing
outer race
rotary connection
rolling bearing
axial
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.)
Ceased
Application number
DE19803929A
Other languages
German (de)
Inventor
Juergen Dipl Ing Oetjen
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 Waelzlager Schaeffler OHG
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 Waelzlager Schaeffler OHG filed Critical INA Waelzlager Schaeffler OHG
Priority to DE19861237A priority Critical patent/DE19861237B4/en
Priority to DE19803929A priority patent/DE19803929A1/en
Publication of DE19803929A1 publication Critical patent/DE19803929A1/en
Ceased legal-status Critical Current

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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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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
    • F16C19/30—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 axial load mainly
    • 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
    • F16C19/38—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 two or more rows 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/60—Positive connections with threaded parts, e.g. bolt and nut connections
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm

Abstract

Two components are joined by a bearing allowing each to rotate in azimuth by 360 degrees. The bearing incorporates roller bearings (6, 16) and two concentric bearing rings (9, 10) on which the rollers turn. The two roller bearings are inclined such that their axis of rotation (7) intersects at a point in the outer ring (10).

Description

Anwendungsgebiet der ErfindungField of application of the invention

Die Erfindung betrifft eine Wälzlager-Drehverbindung, die aus zwei konzen­ trisch ineinander angeordneten Laufringen besteht, zwischen denen Wälzkörper auf zugehörigen Laufbahnen abrollen.The invention relates to a rolling bearing slewing ring, which consist of two there are tria nested races, between which rolling elements roll on associated tracks.

Hintergrund der ErfindungBackground of the Invention

Derartige Wälzlager-Drehverbindungen sind bereits bekannt ("Die Wälzlager­ praxis", Vereinigte Fachverlage GmbH, Mainz 1995). Solche Wälzlager-Dreh­ verbindungen werden als Schwenklager für die Abstützung von Baggern, Kränen oder im Fahrzeugbau für Gelenkbusse bzw. Straßenbahnen eingesetzt, d. h. in Einsatzgebieten, bei denen bei begrenztem Einbauraum hohe Belastungen auftreten und die eine hohe Betriebssicherheit verlangen. Diese Drehverbindun­ gen können Axialkräfte, Radialkräfte und Kippmomente aufnehmen. Kleinere Drehverbindungen mit einem Laufkreisdurchmesser bis zu 200 mm werden darüber hinaus in der Medizintechnik, im Roboterbau oder in der Wehrtechnik benötigt.Such roller bearing slewing rings are already known ("The roller bearings practice ", Vereinigte Fachverlage GmbH, Mainz 1995). Such rolling bearing rotation Connections are used as swivel bearings for supporting excavators, cranes or used in vehicle construction for articulated buses or trams, d. H. in Areas of application in which high loads with limited installation space occur and which require high operational reliability. This pivot connection can absorb axial forces, radial forces and tilting moments. Smaller ones Turning connections with a running circle diameter up to 200 mm in addition in medical technology, in robot construction or in defense technology needed.

Diese Schwenklager werden als Vierpunktlager ausgebildet, das insbesondere zur Aufnahme von Kippkräften bei kleinem Querschnitt gut geeignet ist. Gelen­ ke von Industrierobotern und andere Lagerstellen, die die Tragfähigkeit und die Steifigkeit von Kugellagern überfordern, rüstet man gern mit Kreuzrollenlagern aus. Diese Lager haben einen Kranz von Rollen mit annähernd quadratischem Querschnitt, die abwechselnd mit versetzter Achse auf den Laufbahnen abrol­ len.These pivot bearings are designed as four-point bearings, which in particular is well suited to absorb tilting forces with a small cross-section. Gels ke of industrial robots and other storage locations that have the carrying capacity and the Overloading the stiffness of ball bearings is something you like to equip with crossed roller bearings out. These bearings have a ring of approximately square rollers  Cross-section that alternately roll on the raceways with an offset axis len.

Nachteilig dabei ist, daß die Laufbahnen direkt im inneren bzw. im äußeren Laufring untergebracht sind, so daß aufgrund der erforderlichen Güte der Laufbahnen deren Herstellung verteuert ist. So ist immer der gesamte Laufring einem Schleif- und Härteverfahren zu unterwerfen. Das kann beim Härten beispielsweise dazu führen, daß der Laufring einem Härteverzug unterliegt und für die Drehverbindung unbrauchbar ist.The disadvantage here is that the raceways directly inside or outside Race are housed so that due to the required quality of the Careers whose manufacture is more expensive. So is the entire race subject to a grinding and hardening process. This can happen when hardening cause, for example, that the race is subject to a delay in hardness and is unusable for the slewing ring.

Zusammenfassung der ErfindungSummary of the invention

Der Erfindung liegt daher die Aufgabe zugrunde, eine Wälzlager-Drehverbin­ dung zu entwickeln, die sich im Vergleich zum bisherigen Stand der Technik wesentlich einfacher fertigen läßt.The invention is therefore based on the object, a rolling bearing rotary joint to develop, which is compared to the previous state of the art much easier to manufacture.

Erfindungsgemäß wird diese Aufgabe nach dem kennzeichnenden Teil von Anspruch 1 dadurch gelöst, daß die Wälzkörper durch Lagernadeln zweier einander entgegengerichteter Axialschrägnadellager gebildet sind, die Lauf­ scheiben aufweisen und wobei der Schnittpunkt der verlängerten Drehachsen der Lagernadeln im äußeren Laufring liegt.According to the invention, this task is performed according to the characterizing part of Claim 1 solved in that the rolling elements by bearing needles two opposed axial angular contact needle bearings are formed, the barrel have discs and where the intersection of the elongated axes of rotation the bearing needles are in the outer race.

Diese Axialschrägnadellager werden als separate Bauteile gefertigt und erlauben eine von der eigentlichen Wälzlagerung der Drehverbindung unabhängige Fertigung der beiden Laufringe, so daß die Wälzlager-Drehverbindung in ihrer Gesamtheit einfacher gefertigt werden kann. Durch die Trennung von Laufrin­ gen und Wälzlagerung wird auch eine Gewichtsverminderung der Wälzlager- Drehverbindung in einfacher Weise möglich, indem die Laufringe aus einem Leichtmetall hergestellt werden. Gegenüber den bekannten Drehverbindungen, die in beschriebener Weise bevorzugt als Vierpunktlager oder Kreuzrollenlager ausgeführt sind, ist bei Verwendung von zwei Schrägnadellagern die Wälzkör­ peranzahl mindestens doppelt so hoch. Die statische Tragzahl bzw. axiale Kipp­ steifigkeit der erfindungsgemäßen Drehverbindung wird daher erheblich verbes­ sert.These axial angular contact needle roller bearings are manufactured and permitted as separate components an independent of the actual rolling bearing of the slewing ring Production of the two races, so that the rolling bearing slewing ring in their The whole can be manufactured more easily. By separating Laufrin and rolling bearings will also reduce the weight of the rolling bearing Slewing ring possible in a simple manner by the races from a Light metal can be produced. Compared to the known slewing rings, which in the manner described preferably as four-point bearings or crossed roller bearings are the rolling elements when using two angular needle bearings number of employees at least twice as high. The basic static load rating or axial tilt  rigidity of the slewing ring according to the invention is therefore considerably improved sert.

Weitere vorteilhafte Ausgestaltungen der Erfindung sind in den abhängigen Ansprüchen 2, 3, 4, 5 und 6 beschrieben.Further advantageous embodiments of the invention are in the dependent Claims 2, 3, 4, 5 and 6 described.

So ist nach Anspruch 2 vorgesehen, daß der innere Laufring an seiner Mantel­ fläche einen in Richtung äußeren Laufring weisenden Vorsprung besitzt, der Anlageflächen für die beiden Axialschrägnadellager bildet. Im Gegensatz zum bisherigen Stand der Technik erstrecken sich in diesem Fall die Anlageflächen hervorstehend nach außen, so daß diese problemlos in der erforderlichen Weise mechanisch bearbeitet werden können.It is provided according to claim 2 that the inner race on its jacket surface has a projection pointing towards the outer race, which Forms contact surfaces for the two axial angular contact needle bearings. In contrast to previous state of the art in this case the contact surfaces protruding outwards, so that they can easily in the required manner can be machined.

In Weiterbildung der Erfindung nach Anspruch 3 soll der äußere Laufring zweigeteilt sein und eine Trennebene aufweisen, die einen um 90° zur Dreh­ achse der Drehverbindung versetzt angeordneten Verlauf nimmt bzw. parallel zu dieser verläuft. Durch diese Trennebene wird die Montage der Wälzlager- Drehverbindung erleichtert bzw. überhaupt erst ermöglicht.In a development of the invention according to claim 3, the outer race be divided into two and have a parting plane that is 90 ° to the rotation axis of the rotary connection is offset or parallel runs to this. The assembly of the rolling bearing Slewing ring facilitated or made possible at all.

Nach einem zusätzlichen Merkmal der Erfindung gemäß Anspruch 4 soll in der Trennebene der Wälzlager-Drehverbindung eine Abstimmscheibe angeordnet sein. Mit Hilfe von unterschiedlichen Stärken dieser Abstimmscheiben kann nun in einfacher Weise auf die Vorspannung dieser Drehverbindung eingewirkt wer­ den.According to an additional feature of the invention according to claim 4 in Separating plane of the roller bearing slewing ring arranged a tuning disc be. With the help of different strengths of these tuning disks can now who acted in a simple manner on the preload of this slewing ring the.

Nach einem anderen Merkmal der Erfindung gemäß Anspruch 5 soll der äußere Laufring an seiner inneren Mantelfläche eine Ausnehmung zur Aufnahme der Schrägnadellager besitzen, in die ein Gewindering einschraubbar ist. Durch diese spezielle Ausbildung des äußeren Laufringes ist es möglich, daß dieser einstückig ausbildbar ist. Darüber hinaus kann ebenfalls in einfacher Weise durch die axiale Stellung des Gewinderinges auf die Vorspannung der Wälz­ lagerung eingewirkt werden. According to another feature of the invention according to claim 5, the outer Race on its inner lateral surface a recess for receiving the Have angular needle bearings into which a threaded ring can be screwed. By this special design of the outer race, it is possible that this can be formed in one piece. It can also be done in a simple manner by the axial position of the threaded ring on the preload of the roller storage.  

Schließlich geht aus Anspruch 6 hervor, daß die Axialschrägnadellager spanlos hergestellt, die Lagernadeln in einem Käfig geführt und die Laufscheiben gehär­ tet sein sollen.Finally, it is apparent from claim 6 that the axial angular contact needle bearings without cutting manufactured, the bearing needles guided in a cage and the running disks hardened should be.

Die Erfindung wird an nachstehenden Ausführungsbeispielen näher erläutert.The invention is explained in more detail using the following exemplary embodiments.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Es zeigen:Show it:

Fig. 1 einen teilweisen Längsschnitt durch ein Axialschrägnadel­ lager, Fig. 1 a partial longitudinal section through a bearing Axialschrägnadel,

Fig. 2 und 3 eine teilweisen Längsschnitt durch eine erfindungsgemäße Wälzlager-Drehverbindung. Figs. 2 and 3 is a partial longitudinal section through a rolling bearing slewing ring.

Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings

Das in Fig. 1 gezeigte und mit 1 bezeichnete Axialschrägnadellager besteht aus zwei Laufscheiben 2 und 3, zwischen denen auf nicht näher bezeichneten Laufbahnen in einem Käfig 4 geführte Lagernadeln 5 abwälzen. Dieses Axial­ schrägnadellager 1 ist so ausgebildet, daß die Laufscheiben 2 und 3 gegenüber der Drehachse 6 des Axialschrägnadellagers 1 unter einem Winkel verlaufen, der kleiner als 90° ist, d. h. schräggestellt sind. Die Drehachse der Lagerna­ deln 5 ist in Fig. 1 mit 7 bezeichnet.The axial inclined needle bearing shown in FIG. 1 and designated by 1 consists of two running disks 2 and 3 , between which roller bearing needles 5 which are guided in a cage 4 run on unspecified tracks. This axial angular contact needle bearing 1 is designed so that the running wheels 2 and 3 extend from the rotational axis 6 of the Axialschrägnadellagers 1 at an angle which is smaller than 90 °, that is, are inclined. The axis of rotation of the Lagerna needles 5 is designated by 7 in FIG. 1.

Die in Fig. 2 mit 8 bezeichnete Wälzlager-Drehverbindung besteht aus einem inneren Laufring 9 und einem äußeren Laufring 10, der entlang einer Trenn­ ebene 13 in die beiden Teilringe 11 und 12 zerfällt. Die Trennebene 13 verläuft dabei sowohl parallel zur Drehachse 6 als auch zu dieser um 90° versetzt. Der innere Laufring 9 weist an seiner Mantelfläche einen radial nach außen gerichte­ ten Vorsprung 14 auf, der trapezförmig ausgebildet ist. An den schrägverlaufen­ den Seitenflächen des Vorsprunges 14 liegen die beiden Axialschrägnadel­ lager 1 jeweils mit ihrer inneren Laufscheibe 2 an. Die anderen, ebenfalls schräg zur Drehachse 6 verlaufenden Anlageflächen für die Axialschrägnadel­ lager 1 werden durch die beiden Teilringe 11 und 12 gebildet. In der Trenn­ ebene 13 zwischen den beiden Teilringen 11 und 12 ist eine Abstimmscheibe 15 angeordnet über dessen Stärke auf die Vorspannung der Wälzlager-Drehver­ bindung 8 eingewirkt werden kann. Je geringer diese Abstimmscheibe 15 in ihrer Dicke ausgebildet ist, um so näher lassen sich die beiden Teilringe 11 und 12 in axialer Richtung aufeinander zubewegen, so daß auf diese Art und Weise die gewünschte Vorspannung der Wälzlager-Drehverbindung einstellbar ist. Der Fig. 2 ist weiter entnehmbar, daß die verlängerten Drehachsen 7 der Lagerna­ deln 5 ihren Schnittpunkt im äußeren Laufring 10 haben, etwa im Bereich der Trennebene 13, in dem diese von einem waagerechten Verlauf in einen senk­ rechten Verlauf übergeht.The designated in Fig. 2 roller bearing slewing ring 8 consists of an inner race 9 and an outer race 10 , the level along a parting 13 disintegrates into the two partial rings 11 and 12 . The parting plane 13 runs both parallel to the axis of rotation 6 and offset by 90 °. The inner race 9 has on its outer surface a radially outward th projection 14 which is trapezoidal. On the oblique side surfaces of the projection 14 , the two axial oblique needle bearings 1 each rest with their inner running disk 2 . The other, also inclined to the axis of rotation 6 contact surfaces for the axial oblique needle bearing 1 are formed by the two partial rings 11 and 12 . In the parting plane 13 between the two partial rings 11 and 12 , a tuning disc 15 is arranged via its strength on the bias of the roller bearing-Drehver connection 8 can be affected. The smaller the thickness of this tuning disc 15 , the closer the two partial rings 11 and 12 can be moved towards one another in the axial direction, so that the desired preload of the roller bearing rotary connection can be set in this way. Fig. 2 can also be seen that the elongated axes of rotation 7 of the Lagerna needles 5 have their intersection in the outer race 10 , approximately in the region of the parting plane 13 , in which it changes from a horizontal course to a vertical right course.

Die in Fig. 3 gezeigte Wälzlager-Drehverbindung 16 besteht ebenfalls aus einem inneren Laufring 9 und einem äußeren Laufring 10 und dazwischen angeordneten Axialschrägnadellagern 1. Der innere Laufring 9 ist wiederum mit einem radial nach außen zeigenden Vorsprung 14 versehen, der jedoch im Vergleich zu Fig. 2 dreieckförmig ausgebildet ist und wiederum die Anlageflä­ chen für beide Axialschrägnadellager 1 bildet. Der äußere Laufring 10 ist an seiner Innenseite mit einer nicht bezeichneten Ausnehmung versehen, die an ihrem oberen Ende schräg zur Drehachse 6 der Wälzlager-Drehverbindung 16 verläuft und die andere Anlagefläche für eines der beiden Axialschrägnadel­ lager 1 bildet. In diese Ausnehmung des äußeren Laufringes 10 wird nun ein Gewindering 17 eingeschraubt, der an seinem oberen Ende dachartig abfällt und die zweite Auflagefläche im äußeren Laufring 10 für das zweite Axialschrä­ gnadellager 1 bildet. Über die axiale Verschiebbarkeit des Gewinderinges 17 im äußeren Laufring 10 kann nun auf die Vorspannung der beiden Axialschrä­ gnadellager 1 und damit auf die Vorspannung der Wälzlager-Drehverbindung 16 eingewirkt werden. Der Vorteil dieser Lösung gegenüber der in Fig. 2 ist hauptsächlich darin zu sehen, daß der äußere Laufring 10 einstückig ausgebildet sein kann und in einfacher Weise durch Verdrehen des Gewinderinges 17 auf die Vorspannung eingewirkt werden kann. The roller bearing rotary connection 16 shown in FIG. 3 also consists of an inner race 9 and an outer race 10 and axial angular contact needle bearings 1 arranged between them. The inner race 9 is in turn provided with a radially outward projection 14 which, however, is triangular in comparison to FIG. 2 and in turn forms the contact surfaces for both axial angular contact needle bearings 1 . The outer race 10 is provided on its inside with a not designated recess, which extends obliquely to the axis of rotation 6 of the rolling bearing rotating connection 16 at its upper end and forms the other contact surface for one of the two axial helical needle bearings 1 . In this recess of the outer race 10 , a threaded ring 17 is now screwed, which slopes down at its upper end like a roof and forms the second bearing surface in the outer race 10 for the second axial bevel bearing 1 . About the axial displacement of the threaded ring 17 in the outer race 10 can now act on the preload of the two Axialschrä gnadellager 1 and thus on the preload of the rolling bearing slewing ring 16 . The advantage of this solution compared to that in Fig. 2 is mainly to be seen in the fact that the outer race 10 can be formed in one piece and can be acted on the bias in a simple manner by turning the threaded ring 17 .

BezugszeichenlisteReference list

11

Axialschrägnadellager
Axial angular contact needle bearings

22nd

Laufscheibe
Disc

33rd

Laufscheibe
Disc

44th

Käfig
Cage

55

Lagernadel
Bearing needle

66

Drehachse
Axis of rotation

77

Drehachse
Axis of rotation

88th

Wälzlager-Drehverbindung
Rolling bearing slewing ring

99

innerer Laufring
inner race

1010th

äußerer Laufring
outer race

1111

Teilring
Partial ring

1212th

Teilring
Partial ring

1313

Trennebene
Dividing plane

1414

Vorsprung
head Start

1515

Abstimmscheibe
Tuning disc

1616

Wälzlager-Drehverbindung
Rolling bearing slewing ring

1717th

Gewindering
Threaded ring

Claims (6)

1. Wälzlager-Drehverbindung (8, 16), die aus zwei konzentrisch ineinander angeordneten Laufringen (9, 10) besteht, zwischen denen Wälzkörper auf zugehörigen Laufbahnen abrollen, dadurch gekennzeichnet, daß die Wälzkör­ per durch Lagernadeln (5) zweier einander entgegengerichteter Axialschräg­ nadellager (1) gebildet sind, die Laufscheiben (2, 3) aufweisen und wobei der Schnittpunkt der verlängerten Drehachsen (7) der Lagernadeln (5) im äußeren Laufring (10) liegt.1. Rolling bearing slewing ring ( 8 , 16 ), which consists of two concentrically arranged races ( 9 , 10 ), between which rolling elements roll on associated raceways, characterized in that the rolling elements by means of bearing needles ( 5 ) of two opposing axial inclined needle bearings ( 1 ) are formed, which have running disks ( 2 , 3 ) and the intersection of the extended axes of rotation ( 7 ) of the bearing needles ( 5 ) lies in the outer race ( 10 ). 2. Wälzlager-Drehverbindung (8, 16) nach Anspruch 1, dadurch gekennzeich­ net, daß der innere Laufring (9) an seiner Mantelfläche einen in Richtung des äußeren Laufringes (10) weisenden Vorsprung (14) besitzt, der Anlageflächen für die beiden Axialschrägnadellager (1) bildet.2. Rolling bearing rotary connection ( 8 , 16 ) according to claim 1, characterized in that the inner race ( 9 ) has on its outer surface a in the direction of the outer race ( 10 ) facing projection ( 14 ), the contact surfaces for the two axial angular needle bearings ( 1 ) forms. 3. Wälzlager-Drehverbindung (8) nach Anspruch 1, dadurch gekennzeichnet, daß der äußere Laufring (10) zweigeteilt ist und eine Trennebene (13) aufweist, die einen um 90° zur Drehachse (6) der Drehverbindung versetzt angeordneten Verlauf nimmt bzw. parallel zu dieser verläuft.3. Rolling bearing rotary connection ( 8 ) according to claim 1, characterized in that the outer race ( 10 ) is divided into two and has a parting plane ( 13 ) which takes a course offset by 90 ° to the axis of rotation ( 6 ) of the rotary connection or runs parallel to this. 4. Wälzlager-Drehverbindung (8) nach Anspruch 3, dadurch gekennzeichnet, daß in der Trennebene (13) eine Abstimmscheibe (15) angeordnet ist.4. Rolling bearing rotary connection ( 8 ) according to claim 3, characterized in that a tuning disc ( 15 ) is arranged in the parting plane ( 13 ). 5. Wälzlager-Drehverbindung (16) nach Anspruch 1, dadurch gekennzeichnet, daß der äußere Laufring (10) an seiner inneren Mantelfläche eine Ausnehmung zur Aufnahme der Axialschrägnadellager (1) besitzt, in die ein Gewindering (17) einschraubbar ist.5. roller bearing rotary connection ( 16 ) according to claim 1, characterized in that the outer race ( 10 ) has on its inner circumferential surface a recess for receiving the axial angular contact needle bearing ( 1 ) into which a threaded ring ( 17 ) can be screwed. 6. Wälzlager-Drehverbindung (8, 16) nach Anspruch 1, dadurch gekennzeich­ net, daß die Axialschrägnadellager (1) spanlos hergestellt, die Lagernadeln (5) in einen Käfig (4) geführt und die Laufscheiben (2, 3) gehärtet sind.6. rolling bearing slewing ring ( 8 , 16 ) according to claim 1, characterized in that the axial angular contact needle bearings ( 1 ) manufactured without cutting, the bearing needles ( 5 ) in a cage ( 4 ) and the discs ( 2 , 3 ) are hardened.
DE19803929A 1998-02-02 1998-02-02 Roller bearing arrangement for components moving in azimuth Ceased DE19803929A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE19861237A DE19861237B4 (en) 1998-02-02 1998-02-02 Rolling bearing slewing connection
DE19803929A DE19803929A1 (en) 1998-02-02 1998-02-02 Roller bearing arrangement for components moving in azimuth

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19803929A DE19803929A1 (en) 1998-02-02 1998-02-02 Roller bearing arrangement for components moving in azimuth

Publications (1)

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Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10017401A1 (en) * 2000-04-07 2001-10-11 Schaeffler Waelzlager Ohg Roller bearing has additional axial inclined bearing needles in supplementary disks mounted between flanges on inner ring using adapter rings.
DE10039136A1 (en) * 2000-08-07 2002-02-21 Mercedes Benz Lenkungen Gmbh Steering device for vehicle has spindle in roller bearings, of which at least one can move axially and/or radially relative to housing
DE10112293C1 (en) * 2001-03-08 2002-07-25 Demag Mobile Cranes Gmbh & Co Pivot bearing between two annular rotary parts each with circular running and bearing surfaces, has roller bodies, through-holes parallel with bearing axis, and divided first bearing part.
DE10342132A1 (en) * 2003-09-12 2005-04-07 Ina-Schaeffler Kg Thin-race bearing is constituted as an inclined-roller bearing whose running surfaces are produced by a chipless forming process
DE102005027520A1 (en) * 2005-06-15 2006-12-21 Schaeffler Kg bottom bracket
WO2006133909A2 (en) * 2005-06-15 2006-12-21 Schaeffler Kg Axial angular-contact needle bearing
DE102005027516A1 (en) * 2005-06-15 2006-12-21 Schaeffler Kg Bicycle pedal has two sets of conical needle bearings both directed towards the pedal mid-point
DE102006004749A1 (en) * 2006-02-02 2007-08-09 Schaeffler Kg Axial-inclined needle bearing for use in e.g. bicycle, has rotation axes shifting under angle inclined to bearing axis on paths between two co-planar operating plates, where retainer with plates forms labyrinth-seal
DE202007002609U1 (en) * 2007-02-19 2008-04-03 Landwehr, Markus rotary joint
DE102006055581A1 (en) * 2006-11-24 2008-05-29 Schaeffler Kg roller bearing
DE102007003970A1 (en) * 2007-01-26 2008-07-31 Schaeffler Kg roller bearing
DE102007003859A1 (en) * 2007-01-26 2008-07-31 Schaeffler Kg Insert roller bearing for e.g. agricultural machinery, has adapter and outer rings made of light metal, and sealing rings arranged between outer ring and adapter rings, where one of adapter ring and clamping ring has holes to insert pins
DE102007013164A1 (en) * 2007-03-20 2008-09-25 Schaeffler Kg Rolling bearing with a braking device
DE102007018158A1 (en) * 2007-04-18 2008-10-23 Schaeffler Kg Rolling bearing with a braking device
DE102007034501A1 (en) 2007-07-25 2009-01-29 Schaeffler Kg Rolling bearing slewing connection
DE102007049087A1 (en) * 2007-10-12 2009-04-23 Rothe Erde Gmbh Radially and axially loadable rolling bearing
CN103322039B (en) * 2013-07-09 2015-09-09 青岛迪玛尔海洋工程有限公司 The rotary main shaft of single point mooring system holds
CN105545944A (en) * 2016-03-07 2016-05-04 洛阳轴研科技股份有限公司 Large double-direction thrust ball bearing with airtightness and assembling method of large double-direction thrust ball bearing
US9551458B2 (en) 2002-04-29 2017-01-24 Ondal Holding Gmbh Pivot bearing unit comprising a braking device

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DE102008004070B4 (en) * 2008-01-12 2011-04-28 Franke & Heydrich Kg Method for adjusting the bearing clearance and / or the bearing preload in a rolling bearing

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DE211548C (en) * 1906-12-30 1909-07-13 Ball bearings with a weakened race
US2652295A (en) * 1949-05-05 1953-09-15 Morey E Wollin Rotary bearing construction
DE1160648B (en) * 1959-12-12 1964-01-02 Rothe Erde Eisenwerk Process for the production of the light metal support rings of ball bearings with steel race rings resting on the support rings and then produced ball bearings
DE1525140A1 (en) * 1966-01-28 1969-06-19 Jaeger Gmbh G & J Swivel bearing or slewing ring
DE2724849A1 (en) * 1977-06-02 1978-12-07 Hoesch Werke Ag MULTI-ROW BEARING
FR2549174A1 (en) * 1983-07-13 1985-01-18 Nadella Roulements Prestressed rolling-contact bearing with two series of rolling elements
DE3643278A1 (en) * 1986-12-18 1988-06-23 Skf Gmbh ROLLER BEARING
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Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10017401B4 (en) * 2000-04-07 2009-10-08 Schaeffler Kg insert bearings
DE10017401A1 (en) * 2000-04-07 2001-10-11 Schaeffler Waelzlager Ohg Roller bearing has additional axial inclined bearing needles in supplementary disks mounted between flanges on inner ring using adapter rings.
DE10039136A1 (en) * 2000-08-07 2002-02-21 Mercedes Benz Lenkungen Gmbh Steering device for vehicle has spindle in roller bearings, of which at least one can move axially and/or radially relative to housing
DE10112293C1 (en) * 2001-03-08 2002-07-25 Demag Mobile Cranes Gmbh & Co Pivot bearing between two annular rotary parts each with circular running and bearing surfaces, has roller bodies, through-holes parallel with bearing axis, and divided first bearing part.
US9551458B2 (en) 2002-04-29 2017-01-24 Ondal Holding Gmbh Pivot bearing unit comprising a braking device
DE10342132A1 (en) * 2003-09-12 2005-04-07 Ina-Schaeffler Kg Thin-race bearing is constituted as an inclined-roller bearing whose running surfaces are produced by a chipless forming process
DE102005027516A1 (en) * 2005-06-15 2006-12-21 Schaeffler Kg Bicycle pedal has two sets of conical needle bearings both directed towards the pedal mid-point
DE102005027521A1 (en) * 2005-06-15 2007-01-25 Schaeffler Kg Axial angular contact needle roller bearings
WO2006133909A3 (en) * 2005-06-15 2007-03-15 Schaeffler Kg Axial angular-contact needle bearing
WO2006133909A2 (en) * 2005-06-15 2006-12-21 Schaeffler Kg Axial angular-contact needle bearing
DE102005027520A1 (en) * 2005-06-15 2006-12-21 Schaeffler Kg bottom bracket
DE102006004749A1 (en) * 2006-02-02 2007-08-09 Schaeffler Kg Axial-inclined needle bearing for use in e.g. bicycle, has rotation axes shifting under angle inclined to bearing axis on paths between two co-planar operating plates, where retainer with plates forms labyrinth-seal
DE102006004749B4 (en) * 2006-02-02 2015-08-27 Schaeffler Technologies AG & Co. KG Axial angular contact needle roller bearings
DE102006055581A1 (en) * 2006-11-24 2008-05-29 Schaeffler Kg roller bearing
DE102007003970A1 (en) * 2007-01-26 2008-07-31 Schaeffler Kg roller bearing
US8371760B2 (en) 2007-01-26 2013-02-12 Schaeffler Technologies AG & Co. KG Rolling bearing
DE102007003859A1 (en) * 2007-01-26 2008-07-31 Schaeffler Kg Insert roller bearing for e.g. agricultural machinery, has adapter and outer rings made of light metal, and sealing rings arranged between outer ring and adapter rings, where one of adapter ring and clamping ring has holes to insert pins
DE202007002609U1 (en) * 2007-02-19 2008-04-03 Landwehr, Markus rotary joint
DE102007013164A1 (en) * 2007-03-20 2008-09-25 Schaeffler Kg Rolling bearing with a braking device
DE102007018158A1 (en) * 2007-04-18 2008-10-23 Schaeffler Kg Rolling bearing with a braking device
DE102007034501A1 (en) 2007-07-25 2009-01-29 Schaeffler Kg Rolling bearing slewing connection
WO2009013048A2 (en) * 2007-07-25 2009-01-29 Schaeffler Kg Anti-friction bearing revolving joint
WO2009013048A3 (en) * 2007-07-25 2009-05-07 Schaeffler Kg Anti-friction bearing revolving joint
DE102007049087A1 (en) * 2007-10-12 2009-04-23 Rothe Erde Gmbh Radially and axially loadable rolling bearing
CN103322039B (en) * 2013-07-09 2015-09-09 青岛迪玛尔海洋工程有限公司 The rotary main shaft of single point mooring system holds
CN105545944A (en) * 2016-03-07 2016-05-04 洛阳轴研科技股份有限公司 Large double-direction thrust ball bearing with airtightness and assembling method of large double-direction thrust ball bearing
CN105545944B (en) * 2016-03-07 2018-01-26 洛阳轴研科技股份有限公司 A kind of large-scale thrust ball bearing and its assemble method with air-tightness

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