WO1989003487A1 - Axial deep-groove ball bearing - Google Patents

Axial deep-groove ball bearing Download PDF

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Publication number
WO1989003487A1
WO1989003487A1 PCT/EP1988/000906 EP8800906W WO8903487A1 WO 1989003487 A1 WO1989003487 A1 WO 1989003487A1 EP 8800906 W EP8800906 W EP 8800906W WO 8903487 A1 WO8903487 A1 WO 8903487A1
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WO
WIPO (PCT)
Prior art keywords
shaft
bearing
ball
balls
seatings
Prior art date
Application number
PCT/EP1988/000906
Other languages
German (de)
French (fr)
Inventor
Dieter Bollmann
Original Assignee
Bollmann Hydraulik Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bollmann Hydraulik Gmbh filed Critical Bollmann Hydraulik Gmbh
Publication of WO1989003487A1 publication Critical patent/WO1989003487A1/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
    • 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
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows 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
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls

Definitions

  • the invention relates to an axial deep groove ball bearing according to the preamble of patent claim 1.
  • Axial deep groove ball bearings of this type are sold on the market in the most varied of embodiments, for example as single-sided or double-sided bearings or as single-disc or multi-disc bearings. They have proven themselves essentially well, but they have the disadvantage that, according to their designation, they are only suitable for receiving axial loads and when used in arrangements in which radial forces must also be absorbed in addition to axial forces (each ) a further radial bearing which is particularly suitable for this purpose must be used. Such a requirement occurs, for example, in spindle drives, swivel motors and the like.
  • the present invention is accordingly an object of creating an axial deep groove ball bearing of the type described with zero tolerance underlying. This object is achieved with an axial deep groove ball bearing with the features set out in claim 1.
  • the invention provides a thrust ball bearing is provided in which case, by one hand, choice of half of the respectively engaged in the two wave washers and the rotating shaft particular balls and walls ⁇ hand, the force applied to the housing discs bias, the manufacturing tolerances inevitably occur in the production during the Assembly can be individually compensated in each individual case, so that the power transmission can be set up with zero tolerance.
  • the space required hitherto has been substantially reduced, as has the constructional and thus financial outlay for the storage of rotating machine parts which are loaded both axially and radially. Because of this property of being able to absorb and transmit both axially acting and radially acting forces, there is the further significant advantage of the invention that the bearing, after the slightest structural changes, in kinematic reversal of its functions as an - unusually powerful - spindle drive. Linear motor can be used.
  • FIG. 1 shows a longitudinal section through a single-row axial deep groove ball bearing according to the invention.
  • FIG. 2 shows a section according to AA through FIG. 1
  • FIG. 3 shows a section through a two-row axial deep groove ball bearing.
  • FIG. 4 shows a section through a three-row axial deep groove ball bearing
  • the axial roller ball bearing shown in FIG. 1 of the drawing serves to support a rotating shaft 1. It consists of two outer housing washers 2, 3 and an inner shaft washer 4, the load-bearing connection between the shaft washer 4 and the two housings s disks are each caused by a row of balls 5.
  • the bearing to form a double wave washer is provided with a further shaft pulley 6, wherein the two wave washers 4, 6, shaped at their mutually facing inner edges each having an approximately quarter-circle ⁇ fullers 8 are designated 9, which together form a Halbkugelnut form for a row of balls 10, which engages with its other half in a hemispherical groove 11 machined into the rotating shaft 1, which is formed by an all-round groove in the case of simple mounting of a rotating shaft.
  • the balls serve not only as in the case of simple shaft bearing the receiving bearing forces son ⁇ countries the power transmission between the threaded spindle and the threaded sleeve ⁇ .
  • the flow of force during storage runs.
  • the invention is illustrated on the basis of a simple bearing of a rotating shaft.
  • the bearing of the invention may also be due to its ability both axial and radial forces take to, after only minor constructive AMENDING ⁇ gen in kinematic reversal BEZW as a linear drive.
  • Swivel motor for transferring forces between the in this case as a threaded spindle trained shaft 1 and the housing discs 2, 3 acting as "pistons" are used. All that is required is the attachment of the ball cage ring, which guides the balls 10 and in this case is designed to be stronger in accordance with the forces to be transmitted, to the housing disks to be provided with an axial guide in the housing, the ball cage taking over the function of the drive nut of the linear motor. It has been shown that linear drives designed in this way with thread pitches up to ten times the spindle diameter work without problems, whereas conventional linear drives with path ratios of at most that work
  • the housing and shaft washers 2, 3, 4, 6 and the ball cage rings 5, 10 and optionally 12 are inserted in the required order, the ball thickness of the ball cage rings 10
  • the bearing can - in the sense of the embodiment shown in FIG. 1 - be designed as a single-row bearing, but it can also be designed as any multi-row bearing, in which case each of the shaft washers 4 is supplemented by adding a further shaft washer 6 to form a double washer and the shaft washers are coupled to one another and to the shaft 1 by means of a ball cage 10.
  • a two-row bearing designed in this sense is shown in FIG. 2 and a three-row bearing in FIG. 4. It can be seen that the number of herons. can be can be enlarged in this manner, so that the bearing blank ⁇ borders for in principle any load-bearing capacity adapted.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

An axial deep-groove ball bearing for shafts (1), threaded spindles or similar rotating force-transmitting elements consists of two outer ball bearing seatings (2, 3) and an inner shaft seating (4). The bearing has an additional shaft seating (6) parallel to the first disc (4) and both shaft seatings (4, 6) have a quarter-circle flute (8, 9) on their inner facing edges, said flutes together forming a semicircular guide groove for balls (10) the other half of which engages in a semicircular groove (11) in the rotating shaft (1). To ensure transmission of force between the shaft, which is designed as a threaded spindle, and the ball bearing seatings, linearly guided in this case (linear drive), the balls (10) are lodged in a ball cage attached to the ball bearing seatings. In order to support bearing forces acting in any direction, the shaft seatings (4, 6) are provided with a circular ball seating (12). In order to form a multiple-row bearing, each shaft seating (4) has an additional shaft seating (6). The shaft seatings (4, 6) are coupled with each other in pairs and with the shaft (1) by means of a row of balls (10) and, if necessary, with a ball seating (12).

Description

A x i a l - R i 1 l en k u ge l l a g e r A x i a l - R i 1 l en k u ge l l a g e r
Die Erfindung geht aus von einem Axial-Rillenkugellager gemäß dem Oberbegriff des Patentanspruches 1.The invention relates to an axial deep groove ball bearing according to the preamble of patent claim 1.
Axial-Rillenkugellager dieser Art werden am Markt in den verschieden¬ sten Ausführungsformen, beispielsweise als einseitig oder zweiseitig wir¬ kende Lager oder als Einscheiben- oder Mehrscheibenlager vertrieben. Sie haben sich im wesentlichen gut bewährt, sie haben jedoch den Nachteil, daß sie entsprechend ihrer Bezeichnung zur Aufnahme lediglich von axialen La¬ sten ' geeignet sind und bei Einsatz in Anordnungen, in denen außer axialen Kräften auch radiale Kräfte aufgenommen werden müssen, (jeweils) ein wei¬ teres, für diesen Zweck speziell geeignetes Radiallager eingesetzt werden muß. Eine solche Anforderung tritt etwa in Spindeltrieben, Schwenkmotoren und dergl. Einrichtungen auf, in denen die doppelte Lagerung nicht nur einen erheblichen Konstruktionsaufwand und Platzbedarf erfordert sondern darüberhinaus der weitere Nachteil auftritt, daß eine Montage der Lager mit Nullspiel nicht möglich ist mit der weiteren Folge, daß eine toleranz¬ freie Betätigung eines Regelteils bei Einsatz einer derart doppelt gela¬ gerten Kraftübertragung nicht möglich ist.Axial deep groove ball bearings of this type are sold on the market in the most varied of embodiments, for example as single-sided or double-sided bearings or as single-disc or multi-disc bearings. They have proven themselves essentially well, but they have the disadvantage that, according to their designation, they are only suitable for receiving axial loads and when used in arrangements in which radial forces must also be absorbed in addition to axial forces (each ) a further radial bearing which is particularly suitable for this purpose must be used. Such a requirement occurs, for example, in spindle drives, swivel motors and the like. Devices in which the double bearing not only requires considerable construction effort and space but also has the further disadvantage that an assembly of the bearings with zero clearance is not possible with the further consequence, that a tolerance-free actuation of a control part is not possible when using such a double-bearing power transmission.
Der vorliegenden Erfindung liegt demgemäß als Aufgabe die Schaffung eines Axial-Rillenkugellagers der beschriebenen Art mit Null-Toleranz zugrunde. Diese Aufgabe wird mit einem Axial-Rillenkugellager mit den im Patentanspruch 1 wiedergegebenen Merkmalen gelöst.The present invention is accordingly an object of creating an axial deep groove ball bearing of the type described with zero tolerance underlying. This object is achieved with an axial deep groove ball bearing with the features set out in claim 1.
Durch die Erfindung ist ein Axial-Rillenkugellager geschaffen, bei dem durch einerseits fallweise Wahl der zum jeweils hälftigen Eingriff in die beiden Wellenscheiben und die drehende Welle bestimmten Kugeln und ande¬ rerseits die auf die Gehäusescheiben aufgebrachte Vorspannung die bei der Fertigung unvermeidbar auftretenden Fertigungstoleranzen während der Montage in jedem Einzelfall individuell ausgeglichen werden können, so daß die Kraftübertragung mit Nulltoleranz eingerichtet werden kann. In ent¬ sprechender Weise können im Betrieb unvermeidlich auftretende Ausarbei¬ tungen der Kugelführungsbahnen und ein sich hierdurch ergebendes Wegespiel bei der Kraftübertragung durch einfachen Austausch der ursprünglich mon¬ tierten Kugeln durch Kugeln mit einem entsprechend der eingetretenen Aus¬ arbeitung größeren Durchmesser ausgeglichen werden, wobei die Ausarbei¬ tungen nicht nur der in der drehenden Welle und den Außenkanten der Wel¬ lenscheiben sondern auch die Ausarbeitungen der in den Axiallager-flächen angeordneten Kugelbahnen ausgeglichen werden. Ein weiterer wesentlicher Vorteil des Lagers gemäß Erfindung besteht auch darin, daß es außer zur Aufnahme von axialen Kräften auch zur Aufnahme von radialen Kräften ge¬ eignet ist und gleichzeitig auch der Führung der gelagerten Welle dient. Es wird damit mit Hilfe des erfindungsgemäßen Lagers der bisher erforder¬ liche Platzbedarf wesentlich verringert, ebenso der konstruktive und damit finanzielle Aufwand bei der Lagerung drehender und sowohl axial als auch radial belasteter Maschinenteile. Aufgrund dieser Eigenschaft, sowohl axial wirkende als auch radial wirkende Kräfte aufnehmen und weiterleiten zu können, besteht der weitere wesentliche Vorteil der Erfindung, daß das Lager nach geringfügigsten konstruktiven Änderungen in kinematischer Umkehrung seiner Funktionen als - ungewöhnlich leistungsfähiger - Spindeltrieb bezw. Linearmotor eingesetzt werden kann.The invention provides a thrust ball bearing is provided in which case, by one hand, choice of half of the respectively engaged in the two wave washers and the rotating shaft particular balls and walls ¬ hand, the force applied to the housing discs bias, the manufacturing tolerances inevitably occur in the production during the Assembly can be individually compensated in each individual case, so that the power transmission can be set up with zero tolerance. In ent speaking manner during operation inevitably occurring Ausarbei ¬ being possible obligations of the ball tracks and a resultant thus directional game in power transmission by simply replacing the originally mon ¬ oriented balls by balls with one corresponding to the occurred Aus¬ processing larger diameter balanced, the Ausarbei ¬ obligations not only be in the rotating shaft and the outer edges of lenscheiben Wel¬ but also the elaboration of the thrust bearing surfaces in the arranged ball races balanced. Another important advantage of the bearing according to the invention is that it is suitable not only for absorbing axial forces but also for absorbing radial forces and at the same time also serves to guide the supported shaft. With the help of the bearing according to the invention, the space required hitherto has been substantially reduced, as has the constructional and thus financial outlay for the storage of rotating machine parts which are loaded both axially and radially. Because of this property of being able to absorb and transmit both axially acting and radially acting forces, there is the further significant advantage of the invention that the bearing, after the slightest structural changes, in kinematic reversal of its functions as an - unusually powerful - spindle drive. Linear motor can be used.
Weitere Ausführungsformen und Vorteile ergeben sich aus der nachfol¬ genden Beschreibung, in der die Erfindung anhand der beiliegenden Zeich¬ nung beispielsweise erläutert ist. Es zeigenFurther embodiments and advantages emerge from the nachfol ¬ constricting description in which the invention with reference to the accompanying Zeich¬ voltage for example, is explained. Show it
Fig. 1 einen Längsschnitt durch ein einreihiges Axial-Rillenkugel¬ lager gemäß Erfindung Fig. 2 einen Schnitt nach A - A durch Fig. 11 shows a longitudinal section through a single-row axial deep groove ball bearing according to the invention. FIG. 2 shows a section according to AA through FIG. 1
Fig. 3 einen Schnitt durch ein zweireihiges Axial-Rillenkugellager Fig. 4 einen Schnitt durch ein dreireihiges Axial-Rillenkugellager3 shows a section through a two-row axial deep groove ball bearing. FIG. 4 shows a section through a three-row axial deep groove ball bearing
Das in Fig. 1 der Zeichnung beispielsweise wiedergegebene Axial-Ril¬ lenkugellager dient der Lagerung einer drehenden Welle 1. Es besteht aus zwei äußeren Gehäusescheiben 2, 3 und einer inneren Wellenscheibe 4, wobei die tragende Verbindung zwischen der Wellenscheibe 4 und den beiden Gehäu¬ sescheiben jeweils von einer Kugelreihe 5 bewirkt wird. Erfindungsgemäß ist das Lager zur Bildung einer Doppelwellenscheibe mit einer weiteren Wellenscheibe 6 versehen, wobei die beiden Wellenscheiben 4, 6 an ihren gegeneinanderweisenden inneren Kanten mit jeweils einer etwa viertelkreis¬ förmigen Hohlkehlung 8, 9 versehen sind, die gemeinsam eine Halbkugelnut für eine Kugelreihe 10 bilden, die mit ihrer anderen Hälfte in einer in die drehende Welle 1 eingearbeitete Halbkugelnut 11 eingreift, die im Falle der einfachen Lagerung einer drehenden Welle von einer rundumlau¬ fenden Nut gebildet ist. In diesem Falle dienen die Kugeln nicht nur wie im Falle der einfachen Wellenlagerung der Aufnahme von Lagerkräften son¬ dern der Kraftübertragung zwischen der Gewindespindel und der Gewinde¬ muffe. Hierbei verläuft der Kraftfluß bei der Lagerung bezv. Kraftübertra¬ gung etwa wellenförmig von der Gehäusescheibe 2 über d__.e dieser Scheibe benachbarte Kugelreihe 5 zur Wellenscheibe 4, von dort über die Kugelreihe 10 zur Wellenscheibe 6 und schließlich über die dieser Wellenscheibe benachbarte Kugelreihe 5 zur Gehäusescheibe 3, wobei die "Wellenscheiben" 4 und 6 nicht mehr wie bei den bekannten Axial-Kugellagern direkt auf der Welle aufgekeilt sondern indirekt über die Kugelreihe 10 mit der Welle 1 gekoppelt sind. Zur Übertragung geringerer Kräfte genügt die Lagerung der Teile auf den Kugelreihen 5 und 10, zur Übertragung größerer Kräfte wird im Hinblick auf den wellenförmigen Kraftverlauf durch das Lager und das hierdurch bedingte Auftreten richtungsunbestimmter Kraftkomponenten zwi¬ schen den Wellenscheiben 4, 6 eine weitere stützende Kugelführung 12 vor¬ gesehen,The axial roller ball bearing shown in FIG. 1 of the drawing, for example, serves to support a rotating shaft 1. It consists of two outer housing washers 2, 3 and an inner shaft washer 4, the load-bearing connection between the shaft washer 4 and the two housings s disks are each caused by a row of balls 5. According to the invention the bearing to form a double wave washer is provided with a further shaft pulley 6, wherein the two wave washers 4, 6, shaped at their mutually facing inner edges each having an approximately quarter-circle ¬ fullers 8 are designated 9, which together form a Halbkugelnut form for a row of balls 10, which engages with its other half in a hemispherical groove 11 machined into the rotating shaft 1, which is formed by an all-round groove in the case of simple mounting of a rotating shaft. In this case, the balls serve not only as in the case of simple shaft bearing the receiving bearing forces son ¬ countries the power transmission between the threaded spindle and the threaded sleeve ¬. Here, the flow of force during storage runs. Power transmission approximately wave-shaped from the housing disc 2 via d__. E of this disc adjacent ball row 5 to the wave washer 4, from there via the ball row 10 to the wave washer 6 and finally via the ball row 5 adjacent to this wave washer to the housing washer 3, the "wave washers" 4 and 6 no longer wedged directly onto the shaft as in the known axial ball bearings, but are coupled indirectly to the shaft 1 via the row of balls 10. For the transfer of lower forces, the bearing of the parts on the rows of balls 5 and 10 is sufficient; for the transfer of larger forces, a further supporting ball guide 12 is provided with regard to the wave-shaped force profile through the bearing and the resultant occurrence of direction-independent force components between the shaft washers 4, 6 provided,
Im vorliegenden Beispiel ist die Erfindung anhand einer einfachen La¬ gerung einer drehenden Welle dargestellt. Das erfindungsgemäße Lager kann jedoch auch aufgrund seiner Eigenschaft, sowohl axiale als auch radiale Kräfte aufnehmen zu können, nach nur geringfügiger konstruktiver Änderun¬ gen in kinematischer Umkehrung als Linearantrieb bezw. Schwenkmotor zur Übertragung von Kräften zwischen der in diesem Falle als Gewindespindel ausgebildeten Welle 1 und den als "Kolben" wirkenden Gehäusescheiben 2, 3 eingesetzt werden. Es bedarf hierzu lediglich der Befestigung des die Kugeln 10 führenden und in diesem Falle entsprechend den zu Übertragenden Kräften stärker ausgelegten Kugelkäfigringes an den mit einer Axialführung im Gehäuse zu versehenden Gehäusescheiben, wobei der Kugelkäfig die Funk¬ tion der Antriebsmutter des Linearmotors übernimmt. Es hat sich gezeigt, daß in dieser Weise ausgebildete Linearantriebe mit Gewindesteigungen bis zu dem zehnfachen des Spindeldurchmessers störungsfrei arbeiten, wohin¬ gegen herkömmliche Linearantriebe mit Wegeübersetzungen von maximal demIn the present example, the invention is illustrated on the basis of a simple bearing of a rotating shaft. However, the bearing of the invention may also be due to its ability both axial and radial forces take to, after only minor constructive AMENDING ¬ gen in kinematic reversal BEZW as a linear drive. Swivel motor for transferring forces between the in this case as a threaded spindle trained shaft 1 and the housing discs 2, 3 acting as "pistons" are used. All that is required is the attachment of the ball cage ring, which guides the balls 10 and in this case is designed to be stronger in accordance with the forces to be transmitted, to the housing disks to be provided with an axial guide in the housing, the ball cage taking over the function of the drive nut of the linear motor. It has been shown that linear drives designed in this way with thread pitches up to ten times the spindle diameter work without problems, whereas conventional linear drives with path ratios of at most that work
10 zweifachen des Spindeldurchmessers eingesetzt werden können.10 times the spindle diameter can be used.
Zur Montage des Lagers werden in der erforderlichen Reihenfolge die Gehäuse- und Wellenscheiben 2, 3, 4, 6 sowie die Kugelkäfigringe 5, 10 und gegebenenfalls 12 eingelegt, wobei die Kugelstärke der Kugelkäfigringe 10To assemble the bearing, the housing and shaft washers 2, 3, 4, 6 and the ball cage rings 5, 10 and optionally 12 are inserted in the required order, the ball thickness of the ball cage rings 10
-•-■ und 12 in Abhängigkeit von dem sich aus der fertigungstechnischen Toleranz ergebenden Spiel zwischen wellenseitiger Nut 11 und wellenscheibenseitiger Nut 8, 9 ausgewählt werden. Es werden danach die Gehäusescheiben 2 und 3 gegeneinander verspannt mit der Wirkung, daß die Kugeln des Käfigringes 10 infolge der Ausbildung der Kehlungen 8 und 9 als Viertelkreisnut in die- • - ■ and 12 depending on the play resulting from the manufacturing tolerance between shaft-side groove 11 and shaft-disk-side groove 8, 9 are selected. There are then the housing washers 2 and 3 braced against each other with the effect that the balls of the cage ring 10 due to the formation of the grooves 8 and 9 as a quarter-circle groove in the
20 Wellennut 11 eingedrückt werden. Es wird hierdurch eine feste und absolut spielfreie Montage der Welle in dem Lager und damit in dem Gehäuse ermög¬ licht. Entsprechend kann später auftretendes (geringes) Spiel durch nach¬ trägliches weiteres Spannen der Gehäusescheiben 2, 3 gegeneinander ausge¬ glichen werden, während größeres Spiel durch einfachen Austausch des Ku- 5 gelkäfigringes 10 gegen einen Kugeln mit größerem Durchmesser enthaltenden Kugelkäfigring ausgeglichen werden kann. - -20 shaft groove 11 are pressed. This enables a fixed and absolutely play-free assembly of the shaft in the bearing and thus in the housing. Correspondingly, later (slight) play can be compensated for by later tensioning the housing disks 2, 3 against each other, while greater play can be compensated for by simply replacing the ball cage ring 10 with a ball cage ring containing balls with a larger diameter. - -
Das Lager kann - im Sinne der in Fig. 1 wiedergegebenen Ausführungs¬ form - als einreihiges Lager ausgebildet sein, es kann jedoch auch als beliebig mehrreihiges Lager ausgebildet sein, in welchem Falle jede der Wellenscheiben 4 durch Hinzufügen einer weiteren Wellenscheibe 6 zu einer Doppelscheibe ergänzt und die Wellenscheiben mittels eines Kugelkäfigrin¬ ges 10 miteinander und mit der Welle 1 gekoppelt werden. Ein in diesem Sinne ausgebildetes zweireihiges Lager ist in Fig. 2 und ein dreireihiges Lager in Fig. 4 wiedergegeben. Es ist erkennbar, daß die Zahl der Reiher. in dieser Weise beliebig vergrößert werden kann, so daß das Lager unbe¬ grenzt für grundsätzlich jede beliebige Tragfähigkeit ausgelegt werden kann. The bearing can - in the sense of the embodiment shown in FIG. 1 - be designed as a single-row bearing, but it can also be designed as any multi-row bearing, in which case each of the shaft washers 4 is supplemented by adding a further shaft washer 6 to form a double washer and the shaft washers are coupled to one another and to the shaft 1 by means of a ball cage 10. A two-row bearing designed in this sense is shown in FIG. 2 and a three-row bearing in FIG. 4. It can be seen that the number of herons. can be can be enlarged in this manner, so that the bearing blank ¬ borders for in principle any load-bearing capacity adapted.

Claims

0 -Patentansprüche 0 patent claims
1. Axial-Rillenkugellager für Wellen, Gewindespindeln oder dergl. dre¬ hende Kraftübertragungselemente, bestehend aus zwei äußeren Gehäuseschei¬ ben und einer inneren Wellenscheibe, dadurch gekennzeichnet, daß das Lager mit einer sich parallel zur Wellenscheibe (4) erstreckenden weiteren Wel¬ lenscheibe (6) versehen ist und die beiden Wellenscheiben (4, 6) an ihrer« gegeneinanderweisenden inneren Kanten mit jeweils einer viertelkreisförmi¬ gen Hohlkehlung (8, 9) oder einer Anphasung versehen sind, die gemeinsam. eine Halbkugel- bezw. Keilnut als Laufbahn für eine Kugelreihe bilden, de¬ ren Kugeln (10) mit ihrer anderen Hälfte in eine in die drehende Welle (1) eingearbeitete Halbkugelnut (11) bezw. entsprechende Keilnut eingreifen.1. Thrust ball bearings for shafts, spindles or the like. Dre ¬ rising force transmission elements consisting ben of two outer casing ticket ¬ and an inner shaft washer, characterized in that the bearing is lenscheibe with a parallel to the shaft washer (4) extending further Wel¬ ( 6) is provided and the two wave washers (4, 6) are provided on their mutually facing inner edges with a quarter-circle fillet (8, 9) or a chamfer, which together. a hemisphere or Form a keyway as a raceway for a row of balls, the other half of which balls (10) are machined into a hemispherical groove (11) machined into the rotating shaft (1). engage the corresponding keyway.
2. Axial-Rillenkugellager nach Anspruch 1, dadurch gekennzeichnet, daß zur Kraftübertragung zwischen der in diesem Falle als gesondert im Gehäuse gelagerte Gewindespindel ausgebildeten Welle (1) und den in diesem Falle axial im Gehäuse geführten Gehäusescheiben (Linearantrieb) die Kugeln (10) in einem an den Gehäusescheiben befestigten Kugelkafig gehalten sind.2. Axial deep groove ball bearing according to claim 1, characterized in that for power transmission between the in this case as a separately mounted in the housing threaded spindle shaft (1) and in this case axially guided in the housing housing discs (linear drive) the balls (10) in a ball cage attached to the housing washers.
3. Axial-Rillenkugellager nach Anspruch 1 oder 2, dadurch gekennzeich¬ net, daß die Wellenscheiben (4, 6) zur Abstützung richtungsunbestimmter - -3. Axial deep groove ball bearing according to claim 1 or 2, characterized gekennzeich¬ net that the shaft washers (4, 6) for supporting indefinite direction - -
Lagerkräfte mit einer umlaufenden Kugelabstützung (12) versehen sind.Bearing forces are provided with a circumferential ball support (12).
4. Axial-Rillenkugellager nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß zur Bildung mehrreihiger Lager jede der Wellenscheiben (4) durch eine weitere Wellenscheibe (6) ergänzt ist und die Wellenschei¬ ben (4, 6) jeweils paarweise mittels einer Kugelreihe (10) sowie gegebe¬ nenfalls einer Kugelabstützung (12) miteinander sowie mit der Welle (1) gekoppelt sind. 4. Axial deep groove ball bearing according to one of claims 1 to 3, characterized in that each of the wave washers (4) is supplemented by a further wave washer (6) and the wave washers ben (4, 6) each in pairs by means of a to form multi-row bearings row of balls (10) and are coupled gegebe ¬ appropriate, a ball support (12) and the shaft (1) together.
PCT/EP1988/000906 1987-10-12 1988-10-10 Axial deep-groove ball bearing WO1989003487A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP3734450.1 1987-10-12
DE19873734450 DE3734450A1 (en) 1987-10-12 1987-10-12 AXIAL GROOVE BALL BEARING

Publications (1)

Publication Number Publication Date
WO1989003487A1 true WO1989003487A1 (en) 1989-04-20

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Application Number Title Priority Date Filing Date
PCT/EP1988/000906 WO1989003487A1 (en) 1987-10-12 1988-10-10 Axial deep-groove ball bearing

Country Status (4)

Country Link
EP (1) EP0335935A1 (en)
AU (1) AU2538688A (en)
DE (1) DE3734450A1 (en)
WO (1) WO1989003487A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992020940A1 (en) * 1991-05-15 1992-11-26 Ina Wälzlager Schaeffler Kg Roller screw drive
WO1995010717A1 (en) * 1993-10-12 1995-04-20 Alliedsignal Inc. Thrust bearing for an actuator driving a sensor device

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1242582A (en) * 1911-01-14 1917-10-09 William H Needham Ball-bearing.
US1342756A (en) * 1919-06-24 1920-06-08 S K F Administrative Company I Double-acting thrust ball-bearing
DE3436242A1 (en) * 1984-10-03 1986-04-03 Heyligenstaedt & Co, Werkzeugmaschinenfabrik Gmbh, 6300 Giessen Rolling bearing and a double facing lathe fitted with such a bearing
DE3700430A1 (en) * 1986-01-09 1987-07-16 Hiroshi Teramachi BALL SPEED NUT

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT65482B (en) * 1909-03-29 1914-07-10 Fichtel & Sachs Ag United support and support ball bearings.
DE1053880B (en) * 1954-03-09 1959-03-26 Daimler Benz Ag Axial thrust bearings, especially for hydrostatic gears

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1242582A (en) * 1911-01-14 1917-10-09 William H Needham Ball-bearing.
US1342756A (en) * 1919-06-24 1920-06-08 S K F Administrative Company I Double-acting thrust ball-bearing
DE3436242A1 (en) * 1984-10-03 1986-04-03 Heyligenstaedt & Co, Werkzeugmaschinenfabrik Gmbh, 6300 Giessen Rolling bearing and a double facing lathe fitted with such a bearing
DE3700430A1 (en) * 1986-01-09 1987-07-16 Hiroshi Teramachi BALL SPEED NUT

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992020940A1 (en) * 1991-05-15 1992-11-26 Ina Wälzlager Schaeffler Kg Roller screw drive
WO1995010717A1 (en) * 1993-10-12 1995-04-20 Alliedsignal Inc. Thrust bearing for an actuator driving a sensor device

Also Published As

Publication number Publication date
EP0335935A1 (en) 1989-10-11
AU2538688A (en) 1989-05-02
DE3734450A1 (en) 1989-04-20

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