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WO2006018132A1 - Multi-row angular ball bearing - Google Patents

Multi-row angular ball bearing Download PDF

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Publication number
WO2006018132A1
WO2006018132A1 PCT/EP2005/008395 EP2005008395W WO2006018132A1 WO 2006018132 A1 WO2006018132 A1 WO 2006018132A1 EP 2005008395 W EP2005008395 W EP 2005008395W WO 2006018132 A1 WO2006018132 A1 WO 2006018132A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
ball
main
rings
preload
Prior art date
Application number
PCT/EP2005/008395
Other languages
German (de)
French (fr)
Inventor
Horst DÖPPLING
Ludwig Winkelmann
Wolfgang Steinberger
Original Assignee
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 Schaeffler Kg filed Critical Schaeffler Kg
Publication of WO2006018132A1 publication Critical patent/WO2006018132A1/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
    • 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
    • F16C33/588—Races of sheet metal
    • 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
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • 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
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/182—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact in tandem arrangement
    • 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
    • F16C19/50—Other types of ball or roller bearings
    • F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/56—Systems consisting of a plurality of bearings with rolling friction in which the rolling bodies of one bearing differ in diameter from those of another
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/067—Fixing them in a housing
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/80—Pitch circle diameters [PCD]
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Definitions

  • the invention relates to a double-sided loadable multi-row Schrägkugella ⁇ ger, which has a main bearing for supporting the main load with at least two Ku ⁇ gelkränzen, which is assigned to set an axial preload a preload bearing with at least one ball race with opposite pressure angle.
  • FIG. 18 of this document shows the mounting of a bevel pinion shaft for a transfer case of a motor vehicle.
  • the bearing is designed in three rows with a one-piece bearing outer ring and a two-part positional inner ring, the bearing inner rings having one or two shoulders. This makes it possible to easily mount the bearing by the bearing inner rings are pushed on both sides in the axial direction from outside to inside on the ball races.
  • the one-piece bearing outer ring has raceway grooves in which the ball races are arranged.
  • the Haupt ⁇ the forces of the bevel pinion shaft receiving main bearing is formed in two rows, while the associated preload bearing is single row.
  • the adjustment of the bias voltage is such that the inner ring of the preload bearing is moved in the axial direction by an actuator on the main bearing.
  • the two part bearings are arranged at an opposite pressure angle to one another, ie, the ball pressure lines of both bearings each extend obliquely from the inside to the outside.
  • the disadvantage here is, on the one hand, that during storage the storage arrangement can disintegrate into its individual components. Since, however, as a rule the individual bearing components are assigned to one another, this can lead to problems if a large number of ball bearings is accommodated in a packaging unit. On the other hand, it is disadvantageous that these angular contact ball bearings are made solid and require a larger radial space due to their expansion.
  • the expert is also known in this context that the machining of bearing rings is relatively complex and thus teu ⁇ er.
  • the invention is therefore based on the object to develop a generic Wälzla- ger so that its cohesion is improved and that it can be easier to manufacture.
  • this object is achieved by the characterizing part of claim 1 in conjunction with the preamble in that a bearing gerinnenring of two spaced apart by a gap partial rings is formed, the partial ring and a bearing outer ring of the main bearing depending on the ball races separating in the radial Direction opposite first shoulder and each have a at one outer and one inner end diametrically opposed second shoulder, wherein at least one of the bearing rings is made of a bearing steel by a non-cutting shaping process.
  • This arrangement of the shoulders on the bearing rings of the main bearing ensures that this can not disintegrate in the axial direction.
  • Another advantage lies in the non-cutting production of the bearing rings, since they can be manufactured substantially simpler in terms of their production. Taking into account the available installation space, the most varied variants of bearing rings can be produced without cutting, which can also be implemented in simple fashion. rather adaptable to the respective connection construction. Also, space is saved by their small radial expansion. It is also advantageous that weight can be saved due to the lower mass of the non-cutting bearing rings.
  • the ball raceways of the main bearing have the same or a different diameter.
  • the ball races of the preload bearing should have the same or a larger diameter than the ball raceways of the main bearing.
  • the bearing balls of the preload bearing have a same or a smaller diameter than the bearing balls of the main bearing.
  • the bearing outer ring should be integrally formed. A further variant of the invention is described in claim 6. Thereafter, the bearing outer ring should be formed in two pieces and be encompassed by a sleeve surrounding its circumferential surface.
  • the outer ring is reinforced by a radial doubling, which is extended in the axial direction and forms an outer raceway for the preload bearing.
  • the ball bearing is designed as a captive assembly, wherein at least one of the ball rings of the bearing inner ring and / or the bearing outer ring of Vorspan ⁇ mbislagers verlier ⁇ safely held by a running in the circumferential direction Schnier ⁇ is. From claim 9 it is apparent that the ball bearing is designed as a captive assembly, wherein at least one of the Kugel ⁇ wreaths of the bearing inner ring and / or the bearing outer ring of the main bearing is held captive by a running in the circumferential direction Schnapplace.
  • the bearing rings are subjected to a heat treatment process for increasing the hardness.
  • a through-hardening or a Case hardening of the bearing rings As an advantageous method, in particular the low-distortion laser hardening or induction hardening offer here.
  • this ball bearing should be used for supporting a shaft in a change-speed gearbox for a motor vehicle or for supporting a bevel pinion shaft in a Achsverteilergetriebe.
  • the ball raceways of the main bearing and / or the preload bearing are provided with a hard material coating.
  • a hard material coating cause a high surface hardness and thus increase the wear resistance.
  • the hard material layer also causes a reduction of the friction, whereby the friction conditions are almost constant over the entire service life of the layer.
  • Suitable hard coatings are, for example, modified carbon layers (diamond-like carbon) or nitrides of titanium and niobium, which are distinguished by high hardness, high wear resistance and low-friction properties, in particular improving the emergency running properties of the bearing in the event of insufficient lubrication.
  • Figures 1 to 10 show different embodiments of the invention Phyg in longitudinal section.
  • the illustrated in Figure 1 and provided with the reference numeral 1 three-row angular contact ball bearings consists of the main bearing 2 and the Vorwoodsla ⁇ ger 3 together.
  • Main bearing because it has to take the axial forces shown in the arrow direction, which are greater than in the reverse axial direction.
  • Preload bearings because with the help of the bias the total angular contact ball bearing 1 is set.
  • the bearing outer ring 4 is formed ein ⁇ part and is provided in the region of the main bearing 2 with the radially inwardly directed first shoulder 4.1, which separates the rows of balls 9, 10 voneinan ⁇ . To the left of this follows the second shoulder 4.2, which separates the rows of balls 10, 11 from each other.
  • the bearing inner ring 5 is formed in two parts and consists of the partial ring 5.3, which is assigned to the main bearing 2 and the partial ring 5.4, which belongs to the preload bearing 3. Both partial rings 5.3, 5.4 are spaced apart in the axial direction by the gap s. The targeted preselection of the gap s ensures that after installation and axial clamping of the partial rings 5.3, 5.4, a bearing tolerance lying in the narrow tolerance range can be set, wherein the gap s can drop to a value of zero.
  • the partial ring 5.3 has in its center the radially outwardly directed first shoulder 5.1, which faces the shoulder 4.1.
  • the second shoulder 5.2 which separates the rows of balls 9, 10 from each other and the second shoulder 4.2 of the Lager ⁇ outer ring is diametrically opposite.
  • the main bearing 2 and the preload bearing 3 have an opposite pressure angle, ie, they are set to each other in the O position, as indicated by the associated ball pressure lines.
  • the angular contact ball bearing 1 is arranged in the housing 12 for supporting the shaft 13. The bearing preload is now set such that the Detail ⁇ ring 5.4 of the inner ring 5 is moved in the axial direction to the right.
  • the figure further shows that such a bearing can be mounted in a simple manner. This takes place in such a way that the partial ring 5.3, which at the same time carries the row of balls 9, is inserted from right to left until its shoulder 5.1 comes into contact with the crown ring 10, which in turn is supported by the bearing outer ring 4.
  • the preload bearing 3 is completed by pushing the partial ring 5.4 in the direction of the partial ring 5.3.
  • the partial ring 5.3 is in the region of Kugel ⁇ wreath 10 with the Schnapplace 5.3.1 and in the ball ring 11 are the bearing outer ring 4 with the snap stage 4.3 and the partial ring 5.4 with the snap stage 5.4 .1 provided.
  • the bearing arrangement shown in FIG. 2 differs from that in FIG. 1 only in that the raceways of the bearing balls 11 of the preload bearing 3 have a larger diameter than the raceways of the bearing balls 9, 10 of the main bearing 2. This is achieved in that the La geraus touchring 4 is provided following its shoulder 4.2 with a radial extension 4.4, which merges into the shoulder 4.5.
  • the bearing arrangement shown in FIGS. 3 and 4 is distinguished by the fact that the bearing balls 11 of the preload bearing 3 have a smaller diameter than the bearing balls 9, 10 of the main bearing 2 and opposite ball raceways of larger diameter.
  • Both bearing rings 4, 5 are formed as thin-walled produced without cutting, wherein according to Figure 4, the axial distance between the main bearing 2 and preload bearing 3 is magnö ⁇ ßert. Between the partial rings 5.3, 5.4, in turn, the gap s is arranged to set the bearing preload.
  • the bearing assembly shown in Figures 5 and 6 is characterized in that the bearing outer ring 4 of the main bearing 2 is reinforced by a double 4.6, which extends over the entire raceway range of the bearing balls 9, 10. This doubling 4.6 is extended in the axial direction over the shoulder 4.5 and thus forms the raceway for the bearing balls 11 of the preload bearing 3.
  • the bearing preload is adjusted via the gap s between the two partial rings 5.3, 5.4.
  • bearing variants according to the invention are shown, in which the bearing outer ring 4 is formed in two pieces and is enclosed by a sleeve 14 comprising its circumferential surface.
  • the preload bearing 3 is of double-row configuration, wherein the partial ring 5.4 is provided with the shoulder 5.4.3 arranged centrally and the shoulder 5.4.2 arranged on the left side thereof.
  • the associated bearing outer ring 4.7 has the centrally arranged shoulder 4.7.1 and the right side arranged therefrom shoulder 4.7.2, which is the shoulder 5.4.2 diametrically opposite.
  • Main bearing 2 and preload bearings 3 are spaced apart in the axial direction, with either the plastically deformable sleeve 15 or the spacer ring 16 being arranged between them.
  • Both Hauptla ⁇ ger 2 and preload 3 are enclosed by the sleeve 14, which engages either at the right-hand outer end in the housing 12 or the bearing outer ring 4 engages behind on its end face.
  • the gap s required for setting the bearing preload is determined in the upper part of the figure by the distance between the partial rings 5.3, 5.4, wherein after the preload has been reached, the gap between the sleeve 15 arranged radially is deformed radially outward. In the lower part of the picture, the gap s required for adjusting the pretensioning is present between the spacer ring 16 and the partial ring 5.3.
  • both the main bearing 2 and the preload bearing 3 are provided with the same diameter and are surrounded by the sleeve 14, wherein the distance between the outer bearing rings 4 and 4.7 is set by an indentation 14.1 of the sleeve 14.
  • the sub-rings 5.3, 5.4 are, as shown in the upper part of the picture, either almost to each other or, as shown in the lower part of the image, separated by the spacer ring 16, wherein the required for adjusting the bias gap s zwi ⁇ tween the two sub-rings 5.3, 5.4 or between partial ring 5.4 and spacer ring 16 is arranged.
  • the bearing arrangement shown in FIG. 9 is distinguished from that shown in FIG. 8 in that the indentation 14. 1 is dispensed with in the case of the sleeve 14. As can be seen, the gap s between the partial rings 5.3, 5.4 and in the lower part of the picture between the partial ring 5.4 and the spacer ring 16 is formed in the upper part of the picture.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)

Abstract

The invention relates to a double-sided loadable multi-row angular ball bearing (1) comprising at least two ball rims (9, 10) with equal pressure angles in order to support the main load and at least one additional ball rim (11) having counter pressure angles in order to adjust axial pretensioning. The invention further relates to a bearing arrangement comprising a main bearing and a pretensioning bearing which are connected together by means of a sleeve. Said bearing and/or bearing arrangement is characterised in that an inner bearing ring (5) and an external bearing ring (4) of the main bearing (2) comprise a first collar (4.1, 5.1) which is arranged opposite therefrom in a radial direction and which separates the ball rims (9, 10) and a second collar (4.2, 5.2) which is arranged opposite therefrom in a diametrical manner on an external or an internal end. At least one of the bearing rings (4, 5) is produced from a bearing steel by means of a non-cutting shaping process.

Description

Mehrreihiges Schrägkugellager Multi-row angular contact ball bearings
Anwendungsgebiet der ErfindungField of application of the invention
Die Erfindung betrifft ein doppelseitig belastbares mehrreihiges Schrägkugella¬ ger, das zur Abstützung der Hauptlast ein Hauptlager mit wenigstens zwei Ku¬ gelkränzen aufweist, denen zur Einstellung einer axialen Vorspannung ein Vor- spannungslager mit wenigstens einem Kugelkranz mit entgegengesetztem Druckwinkel zugeordnet ist.The invention relates to a double-sided loadable multi-row Schrägkugella¬ ger, which has a main bearing for supporting the main load with at least two Ku¬ gelkränzen, which is assigned to set an axial preload a preload bearing with at least one ball race with opposite pressure angle.
Hintergrund der ErfindungBackground of the invention
Ein derartig gattungsgemäß ausgebildetes Lager ist aus der WO 03/089798 A1 vorbekannt. In Figur 18 dieses Dokumentes ist die Lagerung einer Kegelritzel¬ welle für ein Verteilergetriebe eines Kraftfahrzeuges dargestellt. Das Lager ist dreireihig mit einem einstückigen Lageraußenring und einem zweiteiligen Lage¬ rinnenring ausgebildet, wobei die Lagerinnenringe eine bzw. zwei Schultern aufweisen. Dadurch ist es möglich das Lager einfach zu montieren, indem die Lagerinnenringe beidseitig in axialer Richtung von außen nach innen auf die Kugelkränze aufgeschoben werden. Der einstückige Lageraußenring weist Laufbahnrillen auf, in denen die Kugelkränze angeordnet sind. Das die Haupt¬ kräfte der Kegelritzelwelle aufnehmende Hauptlager ist zweireihig ausgebildet, während das zugehörige Vorspannungslager einreihig ist. Die Einstellung der Vorspannung erfolgt derart, dass der Innenring des Vorspannungslagers in axialer Richtung durch ein Stellelement auf das Hauptlager zubewegt wird. Die beiden Teillager sind mit einem entgegengesetzten Druckwinkel zueinander angeordnet, d. h., die Kugeldrucklinien beider Lager verlaufen jeweils schräg von innen nach außen. Nachteilig dabei ist zum einen, dass während des Transportes die Lageranord¬ nung in ihre Einzelbestandteile zerfallen kann. Da aber in der Regel die einzel¬ nen Lagerbestandteile einander zugemessen sind, kann dies zu Problemen führen, wenn in einer Verpackungseinheit eine Vielzahl von Kugellagern unter- gebracht ist. Zum anderen ist nachteilig, dass diese Schrägkugellager massiv gefertigt sind und aufgrund ihrer Ausdehnung einen größeren radialen Bau¬ raum benötigen. Dem Fachmann ist in diesem Zusammenhang auch bekannt, dass die spanende Fertigung von Lagerringen relativ aufwändig und damit teu¬ er ist.A bearing of such a generic design is previously known from WO 03/089798 A1. FIG. 18 of this document shows the mounting of a bevel pinion shaft for a transfer case of a motor vehicle. The bearing is designed in three rows with a one-piece bearing outer ring and a two-part positional inner ring, the bearing inner rings having one or two shoulders. This makes it possible to easily mount the bearing by the bearing inner rings are pushed on both sides in the axial direction from outside to inside on the ball races. The one-piece bearing outer ring has raceway grooves in which the ball races are arranged. The Haupt¬ the forces of the bevel pinion shaft receiving main bearing is formed in two rows, while the associated preload bearing is single row. The adjustment of the bias voltage is such that the inner ring of the preload bearing is moved in the axial direction by an actuator on the main bearing. The two part bearings are arranged at an opposite pressure angle to one another, ie, the ball pressure lines of both bearings each extend obliquely from the inside to the outside. The disadvantage here is, on the one hand, that during storage the storage arrangement can disintegrate into its individual components. Since, however, as a rule the individual bearing components are assigned to one another, this can lead to problems if a large number of ball bearings is accommodated in a packaging unit. On the other hand, it is disadvantageous that these angular contact ball bearings are made solid and require a larger radial space due to their expansion. The expert is also known in this context that the machining of bearing rings is relatively complex and thus teu¬ er.
Zusammenfassung der ErfindungSummary of the invention
Der Erfindung liegt daher die Aufgabe zugrunde, ein gattungsgemäßes Wälzla- ger so weiterzuentwickeln, dass dessen Zusammenhalt verbessert ist und dass es sich einfacher fertigen lässt.The invention is therefore based on the object to develop a generic Wälzla- ger so that its cohesion is improved and that it can be easier to manufacture.
Erfindungsgemäß wird diese Aufgabe nach dem kennzeichnenden Teil von Anspruch 1 in Verbindung mit dessen Oberbegriff dadurch gelöst, dass ein La- gerinnenring aus zwei durch einen Spalt voneinander beabstandete Teilringe gebildet ist, der Teilring und ein Lageraußenring des Hauptlagers je eine die Kugelkränze trennende, in radialer Richtung sich gegenüberliegende erste Schulter und je eine an einem äußeren und einem inneren Ende sich diametral gegenüberliegende zweite Schulter aufweisen, wobei wenigstens einer der Lagerringe aus einem Wälzlagerstahl durch einen spanlosen Formgebungspro- zess hergestellt ist.According to the invention this object is achieved by the characterizing part of claim 1 in conjunction with the preamble in that a bearing gerinnenring of two spaced apart by a gap partial rings is formed, the partial ring and a bearing outer ring of the main bearing depending on the ball races separating in the radial Direction opposite first shoulder and each have a at one outer and one inner end diametrically opposed second shoulder, wherein at least one of the bearing rings is made of a bearing steel by a non-cutting shaping process.
Durch diese Anordnung der Schultern an den Lagerringen des Hauptlagers ist sichergestellt, dass dieses in axialer Richtung nicht zerfallen kann. Ein weiterer Vorteil liegt in der spanlosen Herstellung der Lagerringe, da diese in ihrer Ferti¬ gungsweise wesentlich vereinfacht hergestellt werden können. Unter Berück¬ sichtigung des zur Verfügung stehenden Bauraumes können spanlos die ver¬ schiedensten Varianten von Lagerringen hergestellt werden, die auch in einfa- eher Weise der jeweiligen Anschlusskonstruktion anpassbar sind. Auch wird durch deren geringe radiale Ausdehnung Bauraum eingespart. Es ist auch von Vorteil, dass durch die geringere Masse der spanlos gefertigten Lagerringe Gewicht einsparbar ist.This arrangement of the shoulders on the bearing rings of the main bearing ensures that this can not disintegrate in the axial direction. Another advantage lies in the non-cutting production of the bearing rings, since they can be manufactured substantially simpler in terms of their production. Taking into account the available installation space, the most varied variants of bearing rings can be produced without cutting, which can also be implemented in simple fashion. rather adaptable to the respective connection construction. Also, space is saved by their small radial expansion. It is also advantageous that weight can be saved due to the lower mass of the non-cutting bearing rings.
Weitere vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprü¬ chen beschrieben.Further advantageous embodiments of the invention are described in the subclaims.
So geht aus Anspruch 2 hervor, dass die Kugellaufbahnen des Hauptlagers einen gleichen oder einen unterschiedlichen Durchmesser aufweisen. Nach einem weiteren Merkmal gemäß der Erfindung Anspruch 3 sollen die Kugel¬ laufbahnen des Vorspannungslagers einen gleichen oder einen größeren Durchmesser als die Kugellaufbahnen des Hauptlagers aufweisen. Nach An¬ spruch 4 ist vorgesehen, dass die Lagerkugeln des Vorspannlagers einen glei- chen oder einen kleineren Durchmesser als die Lagerkugeln des Hauptlagers besitzen. Nach einem weiteren zusätzlichen Merkmal gemäß Anspruch 5 soll der Lageraußenring einstückig ausgebildet sein. Eine weitere Variante der Er¬ findung ist in Anspruch 6 beschrieben. Danach soll der Lageraußenring zweistückig ausgebildet sein und von einer seine Mantelfläche umfassenden Hülse umgriffen sein. Nach Anspruch 7 ist vorgesehen, dass der Außenring durch eine radiale Doppelung verstärkt ist, die in axialer Richtung verlängert ist und eine Außenlaufbahn für das Vorspannungslager bildet. Nach einem ande¬ ren Merkmal gemäß Anspruch 8 ist vorgesehen, dass das Kugellager als eine unverlierbare Baueinheit ausgebildet ist, wobei wenigstens einer der Kugel- kränze des Lagerinnenrings und/oder des Lageraußenringes des Vorspan¬ nungslagers durch eine in Umfangsrichtung verlaufende Schnappstufe verlier¬ sicher gehalten ist. Aus Anspruch 9 geht hervor, dass das Kugellager als eine unverlierbare Baueinheit ausgebildet ist, wobei wenigstens einer der Kugel¬ kränze des Lagerinnenrings und/oder des Lageraußenringes des Hauptlagers durch eine in Umfangsrichtung verlaufende Schnappstufe verliersicher gehalten ist. Nach Anspruch 10 ist vorgesehen, dass die Lagerringe einem Wärmebe¬ handlungsverfahren zur Steigerung der Härte unterworfen sind. Je nach dem verwendeten Material kann das beispielsweise ein Durchhärten oder auch ein Einsatzhärten der Lagerringe sein. Als vorteilhafte Verfahren bieten sich hier insbesondere das verzugsarme Laserhärten oder Induktionshärten an. Auch geht aus den Ansprüchen 11 und 12 die Verwendung des erfindungsgemäßen Kugellagers hervor. Danach soll dieses Kugellager zur Lagerung einer Welle in einem Zahnräderwechselgetriebe für ein Kraftfahrzeug oder zur Lagerung einer Kegelritzelwelle in einem Achsverteilergetriebe eingesetzt sein.It is apparent from claim 2, that the ball raceways of the main bearing have the same or a different diameter. According to a further feature of the invention claim 3, the ball races of the preload bearing should have the same or a larger diameter than the ball raceways of the main bearing. According to claim 4 it is provided that the bearing balls of the preload bearing have a same or a smaller diameter than the bearing balls of the main bearing. According to a further additional feature according to claim 5, the bearing outer ring should be integrally formed. A further variant of the invention is described in claim 6. Thereafter, the bearing outer ring should be formed in two pieces and be encompassed by a sleeve surrounding its circumferential surface. According to claim 7 it is provided that the outer ring is reinforced by a radial doubling, which is extended in the axial direction and forms an outer raceway for the preload bearing. According to another feature according to claim 8 is provided that the ball bearing is designed as a captive assembly, wherein at least one of the ball rings of the bearing inner ring and / or the bearing outer ring of Vorspan¬ nungslagers verlier¬ safely held by a running in the circumferential direction Schnier¬ is. From claim 9 it is apparent that the ball bearing is designed as a captive assembly, wherein at least one of the Kugel¬ wreaths of the bearing inner ring and / or the bearing outer ring of the main bearing is held captive by a running in the circumferential direction Schnappstufe. According to claim 10 it is provided that the bearing rings are subjected to a heat treatment process for increasing the hardness. Depending on the material used, for example, a through-hardening or a Case hardening of the bearing rings. As an advantageous method, in particular the low-distortion laser hardening or induction hardening offer here. Also, it is apparent from the claims 11 and 12, the use of the ball bearing according to the invention. Thereafter, this ball bearing should be used for supporting a shaft in a change-speed gearbox for a motor vehicle or for supporting a bevel pinion shaft in a Achsverteilergetriebe.
Schließlich ist nach Anspruch 13 vorgesehen, dass die Kugellaufbahnen des Hauptlagers und/oder des Vorspannungslagers mit einer Hartstoffbeschichtung versehen sind. Derartige Beschichtungen bewirken einerseits eine hohe Ober¬ flächenhärte und sorgen so für eine Erhöhung der Verschleißfectigkeit. Ande¬ rerseits bewirkt die Hartstoffschicht auch eine Verminderung der Reibung, wo¬ bei die Reibungsverhältnisse über die gesamte Lebensdauer der Lage nahezu konstant sind. Als Hartstoffschichten eignen sich beispielsweise modifizierte Kohlenstoffschichten (Diamond like Carbon) oder Nitride von Titan und Niob, die sich durch eine hohe Härte, hohe Verschleißbeständigkeit und reibungs- mindemde Eigenschaften auszeichnen, wobei insbesondere die Notlaufeigen¬ schaften des Lagers bei Mangelschmierung verbessert werden.Finally, it is provided according to claim 13, that the ball raceways of the main bearing and / or the preload bearing are provided with a hard material coating. On the one hand, such coatings cause a high surface hardness and thus increase the wear resistance. On the other hand, the hard material layer also causes a reduction of the friction, whereby the friction conditions are almost constant over the entire service life of the layer. Suitable hard coatings are, for example, modified carbon layers (diamond-like carbon) or nitrides of titanium and niobium, which are distinguished by high hardness, high wear resistance and low-friction properties, in particular improving the emergency running properties of the bearing in the event of insufficient lubrication.
Die Erfindung wird an nachstehenden Ausführungsbeispielen näher erläutert.The invention will be explained in more detail in the following embodiments.
Kurze Beschreibung der ZeichnungenBrief description of the drawings
Die Figuren 1 bis 10 zeigen unterschiedliche Ausführungsvarianten der Erfin- düng im Längsschnitt.Figures 1 to 10 show different embodiments of the invention düng in longitudinal section.
Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings
Das in Figur 1 dargestellte und mit dem Bezugszeichen 1 versehene dreireihige Schrägkugellager setzt sich aus dem Hauptlager 2 und dem Vorspannungsla¬ ger 3 zusammen. Hauptlager deshalb, weil es die in Pfeilrichtung dargestellten axialen Kräfte aufzunehmen hat, die größer sind, als in umgekehrter axialer Richtung. Vorspannungslager deshalb, weil mit dessen Hilfe die Vorspannung des Gesamtschrägkugellagers 1 eingestellt wird. Der Lageraußenring 4 ist ein¬ teilig ausgebildet und ist im Bereich des Hauptlagers 2 mit der radial einwärts gerichteten ersten Schulter 4.1 versehen, die die Kugelreihen 9, 10 voneinan¬ der trennt. Links davon folgt die zweite Schulter 4.2, die die Kugelreihen 10, 11 voneinander trennt. Der Lagerinnenring 5 ist zweiteilig ausgebildet und besteht aus dem Teilring 5.3, der dem Hauptlager 2 zugeordnet ist und dem Teilring 5.4, der zum Vorspannungslager 3 gehört. Beide Teilringe 5.3, 5.4 sind in axia¬ ler Richtung durch den Spalt s voneinander beabstandet. Durch die gezielte Vorwahl des Spaltes s ist sichergestellt, dass nach dem Einbau und axialem Verspannen der Teilringe 5.3, 5.4 eine im engen Toleranzbereich liegende La¬ gervorspannung eingestellt werden kann, wobei der Spalt s bis zu einem Wert Null abfallen kann. Der Teilring 5.3 weist in seiner Mitte die radial nach außen gerichtete erste Schulter 5.1 auf, die der Schulter 4.1 gegenübersteht. Am rechtsseitigen Ende weist der Teilring 5.3 die zweite Schulter 5.2 auf, die die Kugelreihen 9, 10 voneinander trennt und der zweiten Schulter 4.2 des Lager¬ außenringes diametral gegenüberliegt. Zwischen den Lagerringen 4, 5 wälzen in Käfigen 6, 7, 8 geführte Lagerkugeln 9, 10, 11 ab, die sich an den Schultern 4.1 , 5.2, 4.2, 5.1 , 4.2 und 5.4.2 abstützen. Hauptlager 2 und Vorspannlager 3 weisen eine demnach einen entgegengesetzten Druckwinkel auf, d. h., sie sind zueinander in O-Stellung angestellt, wie die zugehörigen Kugeldrucklinien zei¬ gen. Das Schrägkugellager 1 ist im Gehäuse 12 zur Lagerung der Welle 13 angeordnet. Die Lagervorspannung wird nun derart eingestellt, dass der Teil¬ ring 5.4 des Innenringes 5 in axialer Richtung nach rechts verschoben wird. Die Figur zeigt weiter, dass sich ein solches Lager in einfacher Weise montieren lässt. Dies erfolgt derart, dass der Teilring 5.3, der gleichzeitig die Kugelreihe 9 trägt, von rechts nach links eingeschoben wird, bis seine Schulter 5.1 am Ku¬ gelkranz 10 zur Anlage kommt, der wiederum vom Lageraußenring 4 getragen ist. Das Vorspannlager 3 wird durch Aufschieben des Teilringes 5.4 in Richtung des Teilringes 5.3 komplettiert. Um ein Zerfallen der Gesamtlageranordnung in ihre Einzelbestandteile zu verhindern, ist der Teilring 5.3 im Bereich des Kugel¬ kranzes 10 mit der Schnappstufe 5.3.1 und im Bereich des Kugelkranzes 11 sind der Lageraußenring 4 mit der Schnappstufe 4.3 und der Teilring 5.4 mit der Schnappstufe 5.4.1 versehen. Im Sinne der Erfindung ist unter Schnappstu- fe ein radial nach außen oder ein radial nach innen weisender Vorsprung zu verstehen, dessen Außen- bzw. Innendurchmesser von der Lagerkugel beim Aufschieben des Lagerringes überwunden werden muss. Dies erfolgt derart, dass die Lagerkugel den Lagerring elastisch zusammenpresst oder elastisch aufweitet bis sie ihre endgültige Lage eingenommen hat. Nach Einnehmen der Endlage der Lagerkugel sorgt der in seine Ausgangslage zurückkehrende La¬ gerring dafür, dass die Lagerkugeln durch die Schnappstufe gehindert ist, vom Lagerring in axialer Richtung abzugleiten.The illustrated in Figure 1 and provided with the reference numeral 1 three-row angular contact ball bearings consists of the main bearing 2 and the Vorspannungsla¬ ger 3 together. Main bearing, because it has to take the axial forces shown in the arrow direction, which are greater than in the reverse axial direction. Preload bearings, because with the help of the bias the total angular contact ball bearing 1 is set. The bearing outer ring 4 is formed ein¬ part and is provided in the region of the main bearing 2 with the radially inwardly directed first shoulder 4.1, which separates the rows of balls 9, 10 voneinan¬. To the left of this follows the second shoulder 4.2, which separates the rows of balls 10, 11 from each other. The bearing inner ring 5 is formed in two parts and consists of the partial ring 5.3, which is assigned to the main bearing 2 and the partial ring 5.4, which belongs to the preload bearing 3. Both partial rings 5.3, 5.4 are spaced apart in the axial direction by the gap s. The targeted preselection of the gap s ensures that after installation and axial clamping of the partial rings 5.3, 5.4, a bearing tolerance lying in the narrow tolerance range can be set, wherein the gap s can drop to a value of zero. The partial ring 5.3 has in its center the radially outwardly directed first shoulder 5.1, which faces the shoulder 4.1. At the right-hand end of the sub-ring 5.3, the second shoulder 5.2, which separates the rows of balls 9, 10 from each other and the second shoulder 4.2 of the Lager¬ outer ring is diametrically opposite. Between the bearing rings 4, 5 roll in cages 6, 7, 8 guided bearing balls 9, 10, 11, which are supported on the shoulders 4.1, 5.2, 4.2, 5.1, 4.2 and 5.4.2. Accordingly, the main bearing 2 and the preload bearing 3 have an opposite pressure angle, ie, they are set to each other in the O position, as indicated by the associated ball pressure lines. The angular contact ball bearing 1 is arranged in the housing 12 for supporting the shaft 13. The bearing preload is now set such that the Teil¬ ring 5.4 of the inner ring 5 is moved in the axial direction to the right. The figure further shows that such a bearing can be mounted in a simple manner. This takes place in such a way that the partial ring 5.3, which at the same time carries the row of balls 9, is inserted from right to left until its shoulder 5.1 comes into contact with the crown ring 10, which in turn is supported by the bearing outer ring 4. The preload bearing 3 is completed by pushing the partial ring 5.4 in the direction of the partial ring 5.3. In order to prevent disintegration of the overall bearing arrangement into its individual components, the partial ring 5.3 is in the region of Kugel¬ wreath 10 with the Schnappstufe 5.3.1 and in the ball ring 11 are the bearing outer ring 4 with the snap stage 4.3 and the partial ring 5.4 with the snap stage 5.4 .1 provided. For the purposes of the invention, under snapshot Fe to understand a radially outward or radially inwardly facing projection whose outer or inner diameter of the bearing ball when pushing the bearing ring must be overcome. This is done in such a way that the bearing ball elastically compresses the bearing ring or elastically expands it until it has assumed its final position. After taking the end position of the bearing ball of returning to its original position La¬ gerring ensures that the bearing balls is prevented by the Schnappstufe to slide off from the bearing ring in the axial direction.
Die in Figur 2 dargestellte Lageranordnung unterscheidet sich von der in Figur 1 lediglich dadurch, dass die Laufbahnen der Lagerkugeln 11 des Vorspan¬ nungslagers 3 einen größeren Durchmesser aufweisen als die Laufbahnen der Lagerkugeln 9, 10 des Hauptlagers 2. Erreicht wird dies dadurch, dass der La¬ geraußenring 4 im Anschluss an seine Schulter 4.2 mit einer radialen Verlänge- rung 4.4 versehen ist, die in die Schulter 4.5 übergeht.The bearing arrangement shown in FIG. 2 differs from that in FIG. 1 only in that the raceways of the bearing balls 11 of the preload bearing 3 have a larger diameter than the raceways of the bearing balls 9, 10 of the main bearing 2. This is achieved in that the La gerausßenring 4 is provided following its shoulder 4.2 with a radial extension 4.4, which merges into the shoulder 4.5.
Die in den Figuren 3 und 4 dargestellte Lageranordnung zeichnet sich dadurch aus, dass die Lagerkugeln 11 des Vorspannungslagers 3 einen kleineren Durchmesser als die Lagerkugeln 9, 10 des Hauptlagers 2 und gegenüber die- sen im Durchmesser größere Kugellaufbahnen besitzen. Beide Lagerringe 4, 5 sind als dünnwandige spanlos hergestellte Teile ausgebildet, wobei gemäß Figur 4 der axiale Abstand zwischen Hauptlager 2 und Vorspannlager 3 vergrö¬ ßert ist. Zwischen den Teilringen 5.3, 5.4 ist wiederum zur Einstellung der La¬ gervorspannung der Spalt s angeordnet.The bearing arrangement shown in FIGS. 3 and 4 is distinguished by the fact that the bearing balls 11 of the preload bearing 3 have a smaller diameter than the bearing balls 9, 10 of the main bearing 2 and opposite ball raceways of larger diameter. Both bearing rings 4, 5 are formed as thin-walled produced without cutting, wherein according to Figure 4, the axial distance between the main bearing 2 and preload bearing 3 is magnö¬ ßert. Between the partial rings 5.3, 5.4, in turn, the gap s is arranged to set the bearing preload.
Die in den Figuren 5 und 6 gezeigte Lageranordnung zeichnet sich dadurch aus, dass der Lageraußenring 4 des Hauptlagers 2 durch eine Doppelung 4.6 verstärkt ist, die sich über den gesamten Laufbahnbereich der Lagerkugeln 9, 10 erstreckt. Diese Doppelung 4.6 ist in axialer Richtung über die Schulter 4.5 verlängert und bildet so die Laufbahn für die Lagerkugeln 11 des Vorspan¬ nungslagers 3. Die Einstellung der Lagervorspannung erfolgt über den zwi¬ schen den beiden Teilringen 5.3, 5.4 angeordneten Spalt s. In den Figuren 7 bis 10 sind erfindungsgemäße Lagervarianten dargestellt, bei denen der Lageraußenring 4 zweistückig ausgebildet ist und von einer seine Mantelfläche umfassenden Hülse 14 umschlossen ist.The bearing assembly shown in Figures 5 and 6 is characterized in that the bearing outer ring 4 of the main bearing 2 is reinforced by a double 4.6, which extends over the entire raceway range of the bearing balls 9, 10. This doubling 4.6 is extended in the axial direction over the shoulder 4.5 and thus forms the raceway for the bearing balls 11 of the preload bearing 3. The bearing preload is adjusted via the gap s between the two partial rings 5.3, 5.4. In the figures 7 to 10 bearing variants according to the invention are shown, in which the bearing outer ring 4 is formed in two pieces and is enclosed by a sleeve 14 comprising its circumferential surface.
Wie aus Figur 7 erkennbar, ist das Vorspannungslager 3 doppelreihig ausge¬ bildet, wobei der Teilring 5.4 mit der mittig angeordneten Schulter 5.4.3 und der linksseitig davon angeordneten Schulter 5.4.2 versehen ist. Der zugehörige Lageraußenring 4.7 weist die mittig angeordnete Schulter 4.7.1 und die rechts¬ seitig davon angeordnete Schulter 4.7.2 auf, die der Schulter 5.4.2 diametral gegenüberliegt. Hauptlager 2 und Vorspannungslager 3 sind in axialer Richtung voneinander beabstandet, wobei zwischen ihnen entweder die plastisch ver¬ formbare Hülse 15 oder der Abstandsring 16 angeordnet ist. Sowohl Hauptla¬ ger 2 als auch Vorspannungslager 3 sind von der Hülse 14 umschlossen, die am rechtsseitigen äußeren Ende entweder in das Gehäuse 12 eingreift oder den Lageraußenring 4 an seiner Stirnfläche hintergreift. Der zur Einstellung der Lagervorspannung erforderliche Spalt s wird im oberen Teil der Figur durch den Abstand zwischen den Teilringen 5.3, 5.4 bestimmt, wobei nach erreichter Vor¬ spannung die zwischen bei der angeordnete Hülse 15 radial nach außen ver¬ formt ist. Im unteren Bildteil ist der zur Einstellung der Vorspannung erforderli- che Spalt s zwischen dem Abstandsring 16 und dem Teilring 5.3 vorhanden.As can be seen from FIG. 7, the preload bearing 3 is of double-row configuration, wherein the partial ring 5.4 is provided with the shoulder 5.4.3 arranged centrally and the shoulder 5.4.2 arranged on the left side thereof. The associated bearing outer ring 4.7 has the centrally arranged shoulder 4.7.1 and the right side arranged therefrom shoulder 4.7.2, which is the shoulder 5.4.2 diametrically opposite. Main bearing 2 and preload bearings 3 are spaced apart in the axial direction, with either the plastically deformable sleeve 15 or the spacer ring 16 being arranged between them. Both Hauptla¬ ger 2 and preload 3 are enclosed by the sleeve 14, which engages either at the right-hand outer end in the housing 12 or the bearing outer ring 4 engages behind on its end face. The gap s required for setting the bearing preload is determined in the upper part of the figure by the distance between the partial rings 5.3, 5.4, wherein after the preload has been reached, the gap between the sleeve 15 arranged radially is deformed radially outward. In the lower part of the picture, the gap s required for adjusting the pretensioning is present between the spacer ring 16 and the partial ring 5.3.
Gemäß Figur 8 sind sowohl das Hauptlager 2 als auch das Vorspannungslager 3 mit gleichem Durchmesser versehen und sind von der Hülse 14 umfasst, wo¬ bei der Abstand zwischen den äußeren Lagerringen 4 und 4.7 durch eine Ein- bauchung 14.1 der Hülse 14 eingestellt ist. Die Teilringe 5.3, 5.4 liegen, wie aus dem oberen Bildteil ersichtlich, entweder nahezu aneinander an oder sind, wie aus dem unteren Bildteil ersichtlich, durch den Abstandsring 16 voneinander getrennt, wobei der zur Einstellung der Vorspannung erforderliche Spalt s zwi¬ schen den beiden Teilringen 5.3, 5.4 oder zwischen Teilring 5.4 und Abstands- ring 16 angeordnet ist. In der unteren Bildhälfte ist ein weiterer Abstandsring 17 erkennbar, die äußeren Lagerringe 4 und 4.7 voneinander getrennt, wobei die Einbauchung 14.1 der Hülse 14 in eine nicht bezeichnete Ausnehmung dieses Abstandsringes 17 eingepresst ist oder durch einen Rolliervorgang eingeformt ist.According to FIG. 8, both the main bearing 2 and the preload bearing 3 are provided with the same diameter and are surrounded by the sleeve 14, wherein the distance between the outer bearing rings 4 and 4.7 is set by an indentation 14.1 of the sleeve 14. The sub-rings 5.3, 5.4 are, as shown in the upper part of the picture, either almost to each other or, as shown in the lower part of the image, separated by the spacer ring 16, wherein the required for adjusting the bias gap s zwi¬ tween the two sub-rings 5.3, 5.4 or between partial ring 5.4 and spacer ring 16 is arranged. In the lower half of a further spacer ring 17 can be seen, the outer bearing rings 4 and 4.7 separated from each other, wherein the indentation 14.1 of the sleeve 14 in an unspecified recess this Spacer ring 17 is pressed or is formed by a rolling process.
Die in Figur 9 dargestellte Lageranordnung zeichnet sich gegenüber der in Fi- gur 8 gezeigten dadurch aus, dass bei der Hülse 14 auf die Einbauchung 14.1 verzichtet ist. Wie erkennbar, wird im oberen Bildteil der Spalt s zwischen den Teilringen 5.3, 5.4 und im unteren Bildteil zwischen dem Teilring 5.4 und dem Abstandsring 16 gebildet.The bearing arrangement shown in FIG. 9 is distinguished from that shown in FIG. 8 in that the indentation 14. 1 is dispensed with in the case of the sleeve 14. As can be seen, the gap s between the partial rings 5.3, 5.4 and in the lower part of the picture between the partial ring 5.4 and the spacer ring 16 is formed in the upper part of the picture.
Schließlich ist in Figur 10 eine Lageranordnung gezeigt, bei der beide Lager 2, mit ihren Lageraußenringen 4, 4.7 unmittelbar aneinander anliegen und von der Hülse 14 an ihren Mantelflächen umfasst sind, während der Spalt s zur Einstel¬ lung der Vorspannung zwischen den Teilringen 5.3, 5.4 gebildet ist.Finally, a bearing arrangement is shown in FIG. 10, in which both bearings 2, with their bearing outer rings 4, 4, 7, bear directly against each other and are covered by the sleeve 14 on their lateral surfaces, while the gap s for adjusting the preload between the partial rings 5. 5.4 is formed.
Zur Einstellung der gewünschten Vorspannung ist es denkbar, den piezoelek¬ trischen Effekt zu nutzen. Durch Beschichten von Lagerringen und/oder An¬ schlussteilen mit bestimmten Kristallarten entsteht bei Ausübung von Druck auf diese Kristalle eine elektrische Spannung, die als Meßgröße für die richtige Einstellung der Lagervorspannung verwendbar ist. To set the desired bias, it is conceivable to use the piezoe tric effect. By coating bearing rings and / or An¬ concluding parts with certain types of crystals arises when pressure is applied to these crystals, an electrical voltage that can be used as a measure of the correct setting of the bearing preload.
Bezugszeichenreference numeral
1 Schrägkugellager1 angular contact ball bearing
2 Hauptlager2 main bearings
3 Vorspannungslager3 preload bearings
4 Lageraußenring4 bearing outer ring
4.1 erste Schulter4.1 first shoulder
4.2 zweite Schulter4.2 second shoulder
4.3 Schnappstufe4.3 Snap
4.4 Verlängerung4.4 Extension
4.5 Schulter4.5 shoulder
4.6 Doppelung4.6 duplication
4.7 Lageraußenring4.7 bearing outer ring
4.7.1 Schulter4.7.1 Shoulder
4.7.2 Schulter4.7.2 Shoulder
5 Lagerinnenring5 bearing inner ring
5.1 erste Schulter5.1 first shoulder
5.2 zweite Schulter5.2 second shoulder
5.3 Teilring5.3 partial ring
5.3.1 Schnappstufe5.3.1 Snap
5.4 Teilring5.4 partial ring
5.4.1 Schnappstufe5.4.1 Snap stage
5.4.2 Schulter5.4.2 Shoulder
5.4.3 Schulter5.4.3 Shoulder
6 Käfig6 cage
7 Käfig7 cage
8 Käfig8 cage
9 Lagerkugel9 bearing ball
10 Lagerkugel 11 Lagerkugel10 bearing ball 11 bearing ball
12 Gehäuse12 housing
13 Welle13 wave
14 Hülse 14.1 Einbauchung14 sleeve 14.1 indentation
15 Hülse15 sleeve
16 Abstandsring16 spacer ring
17 Abstandsring17 spacer ring
s Spalt s gap

Claims

Patentansprüche claims
1. Doppelseitig belastbares mehrreihiges Schrägkugellager (1 ), das zur Ab- Stützung der Hauptlast ein Hauptlager (2) mit wenigstens zwei Kugelkränzen1. Double-sided loadable multi-row angular contact ball bearing (1), which for supporting the main load a main bearing (2) with at least two ball races
(9, 10) aufweist, dem zur Einstellung einer axialen Vorspannung ein Vor¬ spannungslager (3) mit wenigstens einem Kugelkranz (11 ) mit entgegenge¬ setztem Druckwinkel zugeordnet ist, dadurch gekennzeichnet, dass ein Lagerinnenring (5) aus zwei durch einen Spalt (s) voneinander beabstande- te Teilringe (5.3, 5.4) gebildet ist, der Teilring (5.3) und ein Lageraußenring (4) des Hauptlagers (2) je eine die Kugelkränze (9, 10) trennende, in radia¬ ler Richtung sich gegenüberliegende erste Schulter (5.1 , 4.1) und je eine an einem äußeren oder einem inneren Ende sich diametral gegenüberliegen¬ de zweite Schulter (5.2, 4.2) aufweisen, wobei wenigstens einer der Lager- ringe (4, 5) aus einem Wälzlagerstahl durch einen spanlosen Formge- bungsprozess hergestellt ist.(9, 10), which is assigned to set an axial prestressing a Vor¬ voltage bearing (3) with at least one ball race (11) with entgegenge¬ set pressure angle, characterized in that a bearing inner ring (5) consists of two through a gap ( s) spaced apart partial rings (5.3, 5.4) is formed, the partial ring (5.3) and a bearing outer ring (4) of the main bearing (2) each one the ball races (9, 10) separating, in Radia¬ ler direction opposite first Shoulder (5.1, 4.1) and each have at one outer or one inner end diametrically gegenüberliegen¬ de second shoulder (5.2, 4.2), wherein at least one of the bearing rings (4, 5) made of a bearing steel by a non-cutting shaping process is made.
2. Kugellager (1) nach Anspruch 1 , dadurch gekennzeichnet, dass die Kugel¬ laufbahnen des Hauptlagers (2) einen gleichen oder einen unterschiedli- chen Durchmesser aufweisen.2. Ball bearing (1) according to claim 1, characterized in that the ball runways of the main bearing (2) have the same or a different diameter.
3. Kugellager nach Anspruch 1 , dadurch gekennzeichnet, dass die Kugel¬ laufbahnen des Vorspannungslagers (3) einen gleichen oder einen größe¬ ren Durchmesser als die Kugellaufbahnen des Hauptlagers (2) aufweisen.3. Ball bearing according to claim 1, characterized in that the ball runways of the preload bearing (3) have a same or a larger diameter than the ball raceways of the main bearing (2).
4. Kugellager (1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass die La¬ gerkugeln (11 ) des Vorspannungslagers (3) einen gleichen oder einen klei¬ neren Durchmesser als die Lagerkugeln (9, 10) des Hauptlagers (2) aufwei¬ sen.4. Ball bearing (1) according to claim 1, characterized in that the bearing balls (11) of the preload bearing (3) have a same or a smaller diameter than the bearing balls (9, 10) of the main bearing (2) ,
5. Kugellager (1) nach Anspruch 1 , dadurch gekennzeichnet, dass der La¬ geraußenring (4) einstückig ausgebildet ist. 5. Ball bearing (1) according to claim 1, characterized in that the La geraußenring (4) is integrally formed.
6. Kugellager nach Anspruch 1 , dadurch gekennzeichnet, dass der Lagerau¬ ßenring (4) zweistückig ausgebildet ist und von einer seine Mantelfläche umfassenden Hülse (14) umgriffen ist.6. Ball bearing according to claim 1, characterized in that the Lagerau¬ ßenring (4) is formed in two pieces and is encompassed by a circumferential surface of its sleeve (14).
7. Kugellager nach Anspruch 5, dadurch gekennzeichnet, dass der Außen¬ ring (4) durch eine Dopplung (4.6) verstärkt ist, die in axialer Richtung ver¬ längert ist und eine Außenlaufbahn für das Vorspannungslager (3) bildet.7. Ball bearing according to claim 5, characterized in that the outer ring (4) by a doubling (4.6) is reinforced, which is extended ver¬ in the axial direction and forms an outer raceway for the preload bearing (3).
8. Kugellager (1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass es als eine unverlierbare Baueinheit ausgebildet ist, wobei wenigstens einer der8. Ball bearing (1) according to claim 1, characterized in that it is designed as a captive assembly, wherein at least one of
Kugelkränze (11 ) des Lagerinnenringes (5) und/oder des LageraußenringesSpherical rings (11) of the bearing inner ring (5) and / or the bearing outer ring
(4) des Vorspannungslagers (3) durch eine in Umfangsrichtung verlaufende(4) of the preload bearing (3) by a circumferentially extending
Schnappstufe (5.4.1 , 4.3) verliersicher gehalten ist.Snap stage (5.4.1, 4.3) is held captive.
9. Kugellager (1) nach Anspruch 1 , dadurch gekennzeichnet, dass es als eine unverlierbare Baueinheit ausgebildet ist, wobei wenigstens einer der Kugelkränze (9, 10) des Lagerinnenringes (5) und/oder des Lageraußenrin¬ ges (4) des Hauptlagers (2) durch eine in Umfangsrichtung verlaufende Schnappstufe (5.3.1 ) verliersicher gehalten ist.9. ball bearing (1) according to claim 1, characterized in that it is designed as a captive assembly, wherein at least one of the ball rings (9, 10) of the bearing inner ring (5) and / or Lageraußenrin¬ ges (4) of the main bearing ( 2) is held captive by a running in the circumferential direction Schnappstufe (5.3.1).
10. Kugellager (1) nach Anspruch 1, dadurch gekennzeichnet, dass die La¬ gerringe (4, 5) einem Wärmebehandlungsverfahren zur Steigerung der Här¬ te unterworfen sind.10. Ball bearing (1) according to claim 1, characterized in that the bearing rings (4, 5) are subjected to a heat treatment process for increasing the hardness.
11. Kugellager (1) nach Anspruch 1 , dadurch gekennzeichnet, dass es zur Lagerug einer Welle (13) in einem Zahnräderwechselgetriebe für ein Kraft¬ fahrzeug eingesetzt ist.11. Ball bearing (1) according to claim 1, characterized in that it is used for Lagerug a shaft (13) in a change-speed gearbox for a Kraft¬ vehicle.
12. Kugellager (1) nach Anspruch 1 , dadurch gekennzeichnet, dass es zur Lagerung einer Kegelritzelwelle in einem Achsverteilergetriebe eingesetzt ist. 12. Ball bearing (1) according to claim 1, characterized in that it is used for supporting a bevel pinion shaft in a Achsverteilergetriebe.
13. Kugellager (1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass die Ku¬ gellaufbahnen des Hauptlagers (2) und/oder des Vorspannungslagers (3) mit einer Hartstoffbeschichtung versehen sind. 13. Ball bearing (1) according to claim 1, characterized in that the ball raceways of the main bearing (2) and / or the preload bearing (3) are provided with a hard material coating.
PCT/EP2005/008395 2004-08-10 2005-08-03 Multi-row angular ball bearing WO2006018132A1 (en)

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Application Number Priority Date Filing Date Title
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DE102004038709A DE102004038709A1 (en) 2004-08-10 2004-08-10 Multi-row angular contact ball bearings

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WO2007099110A1 (en) * 2006-03-04 2007-09-07 Schaeffler Kg Multi-row axially preloaded angular contact ball bearing, and method for its production
WO2007137929A1 (en) 2006-06-01 2007-12-06 Schaeffler Kg Multiple-row, axially biased angular ball bearing and method for production thereof
DE102007053789A1 (en) * 2007-11-12 2009-05-20 Minebea Co., Ltd. Electrical machine, has spacer sleeve inserted between roller bearings and defining preset distance between bearings, where spacer sleeve is made of metallic pipe and is brought to preset length by axial compression
DE102009053599A1 (en) 2009-11-17 2011-05-19 Schaeffler Technologies Gmbh & Co. Kg Angular bearing has two axially outer rolling body rows, axially central rolling body rows, outer ring and two inner rings, where rolling body rows are made of multiple rolling bodies
DE102010009483A1 (en) * 2010-02-26 2011-09-01 Bayerische Motoren Werke Aktiengesellschaft Method for adjusting bearing pre-stressing of bearing arrangement, involves providing bearing arrangement unstressed in axial direction

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DE102012222788A1 (en) * 2012-12-11 2014-06-12 Schaeffler Technologies Gmbh & Co. Kg Bearing device for use as pinion shaft bearing, has bearing points provided in row in circumferential direction about rotation axis of pinion shaft and comprise inner bearing ring and outer bearing ring with raceway for rolling element
DE102016209201A1 (en) * 2016-05-27 2017-11-30 Schaeffler Technologies AG & Co. KG Double row angular contact ball bearing, in particular for an intermediate shaft of a vehicle transmission
DE102017125910B4 (en) * 2017-11-07 2019-05-23 Schaeffler Technologies AG & Co. KG Three-row angular contact ball bearing
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WO2007099110A1 (en) * 2006-03-04 2007-09-07 Schaeffler Kg Multi-row axially preloaded angular contact ball bearing, and method for its production
WO2007137929A1 (en) 2006-06-01 2007-12-06 Schaeffler Kg Multiple-row, axially biased angular ball bearing and method for production thereof
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DE102007053789B4 (en) * 2007-11-12 2020-10-29 Minebea Mitsumi Inc. Electrical machine and method for producing a bearing arrangement of an electrical machine
DE102009053599A1 (en) 2009-11-17 2011-05-19 Schaeffler Technologies Gmbh & Co. Kg Angular bearing has two axially outer rolling body rows, axially central rolling body rows, outer ring and two inner rings, where rolling body rows are made of multiple rolling bodies
DE102010009483A1 (en) * 2010-02-26 2011-09-01 Bayerische Motoren Werke Aktiengesellschaft Method for adjusting bearing pre-stressing of bearing arrangement, involves providing bearing arrangement unstressed in axial direction

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