WO2008083649A1 - Roller bearing device for shafts in particular motor shafts - Google Patents

Roller bearing device for shafts in particular motor shafts Download PDF

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Publication number
WO2008083649A1
WO2008083649A1 PCT/DE2007/002231 DE2007002231W WO2008083649A1 WO 2008083649 A1 WO2008083649 A1 WO 2008083649A1 DE 2007002231 W DE2007002231 W DE 2007002231W WO 2008083649 A1 WO2008083649 A1 WO 2008083649A1
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WO
WIPO (PCT)
Prior art keywords
bearing
rolling
roller bearing
bearing device
ring
Prior art date
Application number
PCT/DE2007/002231
Other languages
German (de)
French (fr)
Inventor
Gordana Michos
Gabriele Laugisch
Oswald Bayer
Chris Mitchell
Oliver Schellberg
Horst Masuch
Wolfgang May
Lothar Rödemer
Original Assignee
Schaeffler Kg
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Publication date
Application filed by Schaeffler Kg filed Critical Schaeffler Kg
Publication of WO2008083649A1 publication Critical patent/WO2008083649A1/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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
    • 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
    • F16C35/08—Rigid support of bearing units; Housings, e.g. caps, covers for spindles
    • F16C35/12—Rigid support of bearing units; Housings, e.g. caps, covers for spindles with ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/525—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to temperature and heat, e.g. insulation
    • 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
    • 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
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/02—Arrangements for equalising the load on a plurality of bearings or their elements

Definitions

  • Rolling bearing device for spindles, in particular motor spindles
  • the invention relates to a rolling bearing device for spindles, in particular motor spindles, comprising a tandem bearing with a saw in Spindelachslegi inner and an outer bearings in the form of angular contact ball bearings, which are operated under radial bias.
  • a temperature gradient in the axial direction from the shaft center to the shaft ends is formed during operation, for example due to the heat input of the motor. Since such spindles are usually mounted on a housing or other component via a tandem bearing, that is to say two rolling bearings connected in series, the rolling bearings also experience the temperature gradient, whereby the latter adjusts both axially and radially there. Of the Temperaturgradient can sometimes be increased in the axial and radial directions in that the housing or the component on which the rolling bearings are arranged, is additionally cooled.
  • Another effect is due to the different temperatures different thermal elongation of shaft and housing, which naturally extends the warmer wave stronger than the cooled housing. As a result, the inner rings of the tandem pair migrate farther apart than the outer rings fixed on the housing side.
  • DE 10 2004 048 720 A1 discloses a ball bearing, which is particularly suitable for supporting the main spindle of a machine tool, in which, in order to compensate for the temperature-induced increase in radial tension, which increases the friction between the bearing rings and the bearings
  • Bearing rings is formed, both of which are accommodated in a sliding sleeve.
  • the one bearing ring is rigidly received in the sliding sleeve, while rend the other is arranged axially displaceable against the restoring force of a spring.
  • the bearing is thus formed within this sliding sleeve both as the temperature-related difference in length of the main spindle relative to the fixed bearing seat compensating floating bearing and as the temperature-induced radial stresses between the inner bearing ring and the outer bearing rings compensating, self-biased three-point bearing.
  • This embodiment is very complex, since it requires separate outer bearing rings, as ultimately results in a disassembly movement of these two bearing rings only a three-point support.
  • the invention is thus based on the problem of specifying a rolling bearing device which is simple and suitable for tandem bearings.
  • both rolling bearings are accommodated in a common sleeve or the like, and that means for compensating for thermally induced changes in the radial bias on a in an axial sliding seat in the sleeve or the like salaried outer ring of the inner bearing axially acting clamping element is provided.
  • a voltage compensation device is provided only on the inner rolling bearing, that is to say the thermally more heavily loaded roller bearing on which a stronger temperature gradient is to be expected. It has proved to be sufficient only to make the compensation there.
  • the higher-loaded inner bearing now has a sliding fit on the outer ring, ie, with its outer ring, it is accommodated axially displaceably in the sleeve or the like holding element. In addition, it is released via an axially acting tensioning tense.
  • the rolling device according to the invention is therefore very simple, special components such as special matched double bearing rings, etc. are not required, but the voltage compensation takes place directly on the one-piece outer bearing ring alone of the inner rolling bearing, after an increase in the bias in the outer bearing ring and thus is exceeded when the spring force of the outer ring is axially displaced, resulting in a more uniform stress on the entire tandem pair as a result of the bearing ring movement.
  • the clamping element itself is preferably a spring element, which may be designed as a plate spring, a spiral spring or a leaf spring.
  • the clamping element may also be a piezoelectric actuator, that is to say an electrically driven clamping element. Hydraulically or pneumatically actuated actuators are also conceivable, in which case a corresponding control line always has to be provided to the actuator.
  • a shape memory alloy consisting of a, then preferably also annular clamping element.
  • the shape memory alloy for example, a NiTi or CuZnAI alloy material can be used. Such alloys are characterized by a shape change from reaching a certain transformation temperature, resulting from a change in structure taking place at this temperature, from.
  • the outer ring is suitably secured by a rotation, so that it does not rotate with the fixedly connected to the spindle inner ring and there is an unnecessary friction loading of the sliding seat.
  • the inner roller bearing has an outer bearing ring.
  • the outer roller bearing may have such a separate outer bearing ring.
  • the outer ring of the outer bearing of the sleeve or the like is formed directly, that is, that there is no separate bearing ring provided. This is readily possible, as a possible bias overshoot on the more heavily loaded inner roller bearing can be reduced according to the invention and therefore always a consistently good, slip-free WälzSystemterrorism is given to the sleeve-side career.
  • FIG. 1 is a schematic representation, partially in section, of a rolling bearing device according to the invention of a first embodiment
  • Fig. 2 is a schematic diagram, partially in section, of a rolling bearing device according to the invention a second embodiment
  • Fig. 3 is a schematic representation, partially in section, of a rolling bearing device according to the invention a third embodiment. Detailed description of the drawings
  • Fig. 1 shows a rolling bearing device 1 according to the invention, comprising a tandem bearing 2 consisting of two rolling bearings 3a, 3b, wherein the rolling bearing 3a, the inner roller bearing and the rolling bearing 3b, the outer bearing, based on the arrangement of a spindle 4, for example, a motor spindle.
  • the inner roller bearing 3a is more thermally stressed during operation, since it is closer to the engine than the outer roller bearing 3b.
  • Each rolling bearing 3a, 3b comprises an inner ring 5a, 5b, which is respectively arranged on the spindle 4, and in the example shown, an outer ring 6a, 6b.
  • the tandem bearing 2 is arranged inside a sleeve 7, which engages over the two outer rings 6a, 6b.
  • the two bearings are on the spindle side via a spacer ring 8, against which the two inner rings 5a, 5b, spaced from each other.
  • a radial web 9 is provided on the sleeve, which spacing the two outer rings 6a, 6b from one another.
  • the outer ring 6b is received in a fixed position in the sleeve 7, while the outer ring 6a is arranged in a sliding fit on the sleeve 7.
  • This axially displaceable bearing ring 6a is further biased axially via a clamping element 10, here a spring, wherein the clamping element 10 is mounted counter to a stop flange 11.
  • the two rolling bearings 3a, 3b are both designed as angular contact ball bearings, see the corresponding embodiments of the running surfaces on the two bearing outer rings 6a, 6b.
  • This angular contact ball bearing design now makes it possible to compensate for thermally induced changes in preload in the region of the more heavily loaded inner roller bearing and thus overall to ensure a more uniform bearing load on the entire tandem bearing 2.
  • the inner roller bearing 3a is the more thermally loaded bearings during operation. It forms a radial temperature gradient after the spindle 4 heats up during operation, with it also the inner ring 5a.
  • the outer ring 6a is colder, in particular when the sleeve 7 is arranged on a motor housing or the like which is actively cooled.
  • the bias on the inner bearing can be kept substantially constant, so that can be maintained at the outer roller bearing 3a, a substantially constant bias voltage.
  • a temperature gradient can occur at this bearing as well, since this rolling bearing is somewhat remote from the motor, it is smaller than the temperature gradient occurring at the inner rolling bearing 3a, so that the stress ratios do not change there to such an extent as in the area of the inner rolling bearing. Also, bearing slippage can be avoided.
  • Fig. 2 shows another variant of a rolling bearing according to the invention. This also includes a tandem bearing 2 with the inner roller bearing 3a and the outer bearing 3b.
  • the inner bearing rings 5a, 5b are in turn arranged on the shaft 4, and here again both rolling bearings 3a, 3b with their balls 12a, 12b are designed as angular contact ball bearings.
  • the inner roller bearing 3a here also has an outer bearing ring 6a, which is prestressed via a tensioning element 10 and is arranged axially displaceably in the sleeve 7.
  • the clamping element 10 is clamped against an arranged in the sleeve bearing ring 13.
  • the outer rolling bearing 3b does not have a separate bearing ring. Rather, here the sleeve 7 itself is provided with a tread 14, the sleeve 7 thus forms even the outer ring of the rolling bearing 3b.
  • the shape of the tread 14 corresponds to the required shape for the formation of an angular contact ball bearing.
  • the compensation device according to the invention 15 is provided to compensate for the thermally induced change in the radial preload on the inner roller bearing 3a, a corresponding Vorspan- ubensüberhöhung resulting from a thermally induced strain, be compensated easily and ensure a uniform bearing load.
  • the rolling bearing device 1 also has a tandem bearing comprising the two rolling bearings 3a and 3b.
  • the embodiment corresponds essentially to the embodiment according to FIG. 1, but there is no annular collar provided on the sleeve 7 that separates the two outer bearing rings 6a, 6b. Rather, the bearing ring 6b is provided with a radially extending shoulder 16, which laterally surrounds the sleeve 7. It is also fixed in position here, while the bearing ring 6a is received in the sliding seat in the sleeve and biased here via a compensating device 15 comprising the clamping element 10.

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

Abstract

Roller bearing device for shafts, in particular, motor shafts, comprising a tandem bearing with an inner and an outer roller bearing when viewed in the axial direction of the shaft in the form of angular contact ball bearings, operated under radial preload. At least the inner roller bearing has an outer ring, both roller bearings (3a, 3b) being housed in a common bush (7) or similar and a device (15) is provided for compensating for the thermal changes to radial preload, comprising a tensioning element (10) acting axially on the outer ring (6a) of the inner roller bearing (3a) which is mounted in an axial sliding seat in the bush (7), or similar.

Description

Wälzlagereinrichtung für Spindeln, insbesondere Motorspindeln Rolling bearing device for spindles, in particular motor spindles
Beschreibungdescription
Gebiet der ErfindungField of the invention
Die Erfindung betrifft eine Wälzlagereinrichtung für Spindeln, insbesondere Motorspindeln, umfassend ein Tandemlager mit einem in Spindelachsrichtung gesehen inneren und einem äußeren Wälzlager in Form von Schrägkugellagern, die unter radialer Vorspannung betrieben werden.The invention relates to a rolling bearing device for spindles, in particular motor spindles, comprising a tandem bearing with a saw in Spindelachsrichtung inner and an outer bearings in the form of angular contact ball bearings, which are operated under radial bias.
Hintergrund der ErfindungBackground of the invention
Bei vielen Spindeln, insbesondere bei Motorspindeln, bildet sich im Betrieb beispielsweise durch den Wärmeeintrag des Motors ein Temperaturgradient in axialer Richtung von der Wellenmitte zu den Wellenenden hin aus. Nachdem derartige Spindeln üblicherweise über ein Tandemlager, also zwei axial hintereinander geschaltete Wälzlager an einem Gehäuse oder sonstigen Bauteil gelagert sind, erfahren folglich auch die Wälzlager den Temperaturgradienten, wobei sich dieser dort sowohl axial als auch radial einstellt. Der Temperaturgradient kann in axialer wie radialer Richtung mitunter noch dadurch vergrößert werden, dass das Gehäuse oder das Bauteil, an dem die Wälzlager angeordnet sind, zusätzlich gekühlt wird. Mithin stellt sich folglich ein beachtlicher axialer Temperaturgradient ein, wobei das innere, motornä- here Wälzlager wärmer ist als das äußere, wie sich auch ein radialer Temperaturgradient in jedem Wälzlager einstellt, wobei der innere Lagerring wärmer ist als der äußere. Bei den üblicherweise in Motorspindeln verwendeten Hochgenauigkeits-Schrägkugellagem führt dies letztlich zu unterschiedlichen Änderungen des axialen Überstandes innerhalb eines Tandempaares.In many spindles, especially in motor spindles, a temperature gradient in the axial direction from the shaft center to the shaft ends is formed during operation, for example due to the heat input of the motor. Since such spindles are usually mounted on a housing or other component via a tandem bearing, that is to say two rolling bearings connected in series, the rolling bearings also experience the temperature gradient, whereby the latter adjusts both axially and radially there. Of the Temperaturgradient can sometimes be increased in the axial and radial directions in that the housing or the component on which the rolling bearings are arranged, is additionally cooled. Consequently, a considerable axial temperature gradient therefore sets in, with the inner, outer-part rolling bearing being warmer than the outer one, just as a radial temperature gradient also occurs in each rolling bearing, with the inner bearing ring being warmer than the outer one. In the case of the high-precision angular contact ball bearings usually used in motor spindles, this ultimately leads to different changes in the axial projection within a tandem pair.
Ein weiterer Effekt ist die durch die unterschiedlichen Temperaturen bedingte unterschiedliche thermische Längendehnung von Welle und Gehäuse, wobei sich naturgemäß die wärmere Welle stärker dehnt als das gekühlte Gehäuse. Dadurch wandern die Innenringe des Tandempaares weiter aus- einander als die gehäuseseitig fixierten Außenringe.Another effect is due to the different temperatures different thermal elongation of shaft and housing, which naturally extends the warmer wave stronger than the cooled housing. As a result, the inner rings of the tandem pair migrate farther apart than the outer rings fixed on the housing side.
Letztendlich führen die unterschiedlichen Temperaturgradienten zu unterschiedlichen Belastungen der einzelnen Wälzlager eines Tandempaares, wobei das innere, also motornäher bzw. stärker erwärmte Lager stärker be- lastet wird, mithin also eine Vorspannung dort deutlich stärker erhöht wird als im äußeren Lager, an dem es gegebenenfalls auch zu einem Vorspannungsverlust mit entsprechenden Schlupfschäden kommen kann.Ultimately, the different temperature gradients lead to different loads on the individual rolling bearings of a tandem pair, whereby the inner, that is closer to the engine or more heated bearing is loaded more heavily, therefore a bias is there significantly more increased than in the outer camp, where it possibly to a Vorspannungsverlust can come with corresponding slippage damage.
Aus DE 10 2004 048 720 A1 ist ein Kugellager, das insbesondere zur Lage- rung der Hauptspindel einer Werkzeugmaschine geeignet ist, bekannt, bei dem zum Ausgleichen der temperaturbedingten Radialverspannungserhö- hung, die zur zunehmenden Reibung zwischen den Lagerringen und denDE 10 2004 048 720 A1 discloses a ball bearing, which is particularly suitable for supporting the main spindle of a machine tool, in which, in order to compensate for the temperature-induced increase in radial tension, which increases the friction between the bearing rings and the bearings
Rollkörpern führt, wodurch eine zu hohe Reibungswärme entsteht, die die zulässige Betriebstemperatur des Lagers überschreitet und gegebenenfalls den Schmierfilm verbrennt, der äußere Lagerring in Form zweier separaterRolling leads, whereby a too high frictional heat arises, which exceeds the permissible operating temperature of the bearing and possibly burns the lubricating film, the outer bearing ring in the form of two separate
Lagerringe ausgebildet ist, die beide in einer Schiebehülse aufgenommen sind. Der eine Lagerring ist in der Schiebehülse starr aufgenommen, wäh- rend der andere gegen die Rückstellkraft einer Feder axial verschieblich angeordnet ist. Das Lager ist damit innerhalb dieser Schiebehülse sowohl als die temperaturbedingte Längendifferenz der Hauptspindel gegenüber deren Festlagersitz ausgleichendes Loslager als auch als die temperaturbedingte Radialverspannungen zwischen dem inneren Lagerring und den äußeren Lagerringen ausgleichendes, in sich vorgespanntes Dreipunktlager ausgebildet. Diese Ausgestaltung ist sehr aufwändig, da sie separate äußere Lagerringe erfordert, wie sich auch letztlich bei einer Auseinanderbewegung dieser beiden Lagerringen nur eine Dreipunktauflage ergibt.Bearing rings is formed, both of which are accommodated in a sliding sleeve. The one bearing ring is rigidly received in the sliding sleeve, while rend the other is arranged axially displaceable against the restoring force of a spring. The bearing is thus formed within this sliding sleeve both as the temperature-related difference in length of the main spindle relative to the fixed bearing seat compensating floating bearing and as the temperature-induced radial stresses between the inner bearing ring and the outer bearing rings compensating, self-biased three-point bearing. This embodiment is very complex, since it requires separate outer bearing rings, as ultimately results in a disassembly movement of these two bearing rings only a three-point support.
Zusammenfassung der ErfindungSummary of the invention
Der Erfindung liegt damit das Problem zugrunde, eine Wälzlagereinrichtung anzugeben, die einfach ausgeführt und für Tandemlager geeignet ist.The invention is thus based on the problem of specifying a rolling bearing device which is simple and suitable for tandem bearings.
Zur Lösung dieses Problems ist bei einer Wälzlagereinrichtung der eingangs genannten Art erfindungsgemäß vorgesehen, dass beide Wälzlager in einer gemeinsamen Hülse oder dergleichen aufgenommen sind, und dass eine Einrichtung zum Ausgleich thermisch bedingter Änderungen der radialen Vorspannung umfassend ein auf den in einem axialen Schiebesitz in der Hülse oder dergleichen gehalterten Außenring des inneren Wälzlagers axial wirkendes Spannelement vorgesehen ist.To solve this problem is provided according to the invention in a rolling bearing device of the type mentioned that both rolling bearings are accommodated in a common sleeve or the like, and that means for compensating for thermally induced changes in the radial bias on a in an axial sliding seat in the sleeve or the like salaried outer ring of the inner bearing axially acting clamping element is provided.
Bei der erfindungsgemäßen Wälzlagereinrichtung ist lediglich am inneren Wälzlager, also dem thermisch stärker belasteten Wälzlager, an dem ein stärkerer Temperaturgradient zu erwarten ist, eine Spannungsausgleichsvorrichtung vorgesehen. Es hat sich nämlich als ausreichend erwiesen, lediglich dort den Ausgleich vorzunehmen. Erfindungsgemäß hat nun das höher be- anspruchte innere Lager am Außenring einen Schiebesitz, ist also mit seinem Außenring axial verschiebbar in der Hülse oder dergleichen Halteelement aufgenommen. Zusätzlich wird es über ein axial wirkendes Spannele- ment verspannt. Nachdem es sich bei beiden Wälzlagern um Schrägkugellager handelt, stellt sich im Falle eines gegebenen Temperaturgradienten ausdehnungsbedingt ein auf den äußeren Lagerring axial wirkender Kraftvektor ein, der den im Schiebesitz aufgenommenen äußeren Lagerring im Falle einer temperaturbedingten Aufweitung axial gegen das Federelement bewegt. Bei dieser Erfindungsausgestaltung ist also lediglich ein äußerer Lagerring, der unmittelbar axial vorgespannt ist, vorgesehen, wobei die Axialbewegung infolge der Verwendung eines Schrägkugellagers ermöglicht wird.In the rolling bearing device according to the invention, a voltage compensation device is provided only on the inner rolling bearing, that is to say the thermally more heavily loaded roller bearing on which a stronger temperature gradient is to be expected. It has proved to be sufficient only to make the compensation there. According to the invention, the higher-loaded inner bearing now has a sliding fit on the outer ring, ie, with its outer ring, it is accommodated axially displaceably in the sleeve or the like holding element. In addition, it is released via an axially acting tensioning tense. After it is angular contact ball bearings in both bearings, arises in the case of a given temperature gradient due to expansion on the outer bearing ring axially acting force vector, which moves the received in the sliding seat outer bearing ring in the event of temperature-induced expansion axially against the spring element. In this embodiment of the invention, therefore, only an outer bearing ring, which is directly axially biased, is provided, wherein the axial movement is made possible due to the use of an angular contact ball bearing.
Die erfindungsgemäße Wälzeinrichtung ist damit sehr einfach aufgebaut, besondere Bauelemente wie spezielle aufeinander abgestimmte Doppellagerringe etc. sind nicht erforderlich, vielmehr erfolgt der Spannungsausgleich unmittelbar über den einteiligen äußeren Lagerring allein des inneren Wälz- lagers, nachdem bei einem Anstieg der Vorspannung im äußeren Lagerring und damit bei Überschreiten der Federkraft der Außenring axial verschoben wird, wodurch sich eine gleichmäßigere Beanspruchung des gesamten Tandempaares infolge der Lagerringbewegung ergibt.The rolling device according to the invention is therefore very simple, special components such as special matched double bearing rings, etc. are not required, but the voltage compensation takes place directly on the one-piece outer bearing ring alone of the inner rolling bearing, after an increase in the bias in the outer bearing ring and thus is exceeded when the spring force of the outer ring is axially displaced, resulting in a more uniform stress on the entire tandem pair as a result of the bearing ring movement.
Das Spannelement selbst ist bevorzugt ein Federelement, das als Tellerfeder, als Spiralfeder oder als Blattfeder ausgeführt sein kann. Alternativ hierzu kann das Spannelement auch ein piezoelektrischer Aktor, also ein elektrisch angesteuertes Spannelement, sein, denkbar sind auch hydraulisch oder pneumatisch angesteuerte Aktoren, wobei in diesen genannten Fällen stets eine entsprechende Steuerleitung zu dem Aktor vorgesehen sein muss. Denkbar ist auch die Verwendung eines aus einer Formgedächtnislegierung bestehenden, dann bevorzugt ebenfalls ringförmigen Spannelements. Als Formgedächtnislegierung kann beispielsweise ein NiTi- oder CuZnAI- Legierungsmaterial verwendet werden. Solche Legierungen zeichnen sich durch eine Formwandlung ab Erreichen einer bestimmten Umwandlungstemperatur, resultierend aus einer bei dieser Temperatur stattfindenden Gefügeänderung, aus. Der Außenring ist zweckmäßigerweise über eine Verdrehsicherung gesichert, so dass er nicht mit dem fest mit der Spindel verbundenen Innenring mitdreht und es zu einer unnötigen Reibebelastung des Schiebesitzes kommt.The clamping element itself is preferably a spring element, which may be designed as a plate spring, a spiral spring or a leaf spring. Alternatively, the clamping element may also be a piezoelectric actuator, that is to say an electrically driven clamping element. Hydraulically or pneumatically actuated actuators are also conceivable, in which case a corresponding control line always has to be provided to the actuator. It is also conceivable to use a shape memory alloy consisting of a, then preferably also annular clamping element. As the shape memory alloy, for example, a NiTi or CuZnAI alloy material can be used. Such alloys are characterized by a shape change from reaching a certain transformation temperature, resulting from a change in structure taking place at this temperature, from. The outer ring is suitably secured by a rotation, so that it does not rotate with the fixedly connected to the spindle inner ring and there is an unnecessary friction loading of the sliding seat.
Bei der erfindungsgemäßen Wälzlagereinrichtung ist es zwingend erforderlich, dass das innere Wälzlager einen äußeren Lagerring aufweist. Auch das äußere Wälzlager kann einen solchen separaten äußeren Lagerring aufweisen. Denkbar ist es aber auch, dass der Außenring des äußeren Wälzlagers von der Hülse oder dergleichen unmittelbar gebildet ist, das heißt, dass dort überhaupt kein separater Lagerring vorgesehen ist. Dies ist ohne weiteres möglich, als eine etwaige Vorspannungsüberhöhung am stärker belasteten inneren Wälzlager erfindungsgemäß abgebaut werden kann und mithin stets ein gleich bleibend guter, schlupffreier Wälzkörperlauf an der hülsenseitigen Laufbahn gegeben ist.In the rolling bearing device according to the invention, it is imperative that the inner roller bearing has an outer bearing ring. Also, the outer roller bearing may have such a separate outer bearing ring. But it is also conceivable that the outer ring of the outer bearing of the sleeve or the like is formed directly, that is, that there is no separate bearing ring provided. This is readily possible, as a possible bias overshoot on the more heavily loaded inner roller bearing can be reduced according to the invention and therefore always a consistently good, slip-free Wälzkörperlauf is given to the sleeve-side career.
Kurze Beschreibung der ZeichnungenBrief description of the drawings
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung werden nachfolgend anhand von Ausführungsbeispielen unter Bezugnahme auf die Figuren beschrieben. Die Figuren sind schematische Darstellungen und zeigen:Further advantages, features and details of the invention are described below with reference to embodiments with reference to the figures. The figures are schematic representations and show:
Fig. 1 eine Prinzipdarstellung, teilweise im Schnitt, einer erfindungs- gemäßen Wälzlagereinrichtung einer ersten Ausführungsform,1 is a schematic representation, partially in section, of a rolling bearing device according to the invention of a first embodiment,
Fig. 2 eine Prinzipdarstellung, teilweise im Schnitt, einer erfindungsgemäßen Wälzlagereinrichtung einer zweiten Ausführungsform, undFig. 2 is a schematic diagram, partially in section, of a rolling bearing device according to the invention a second embodiment, and
Fig. 3 eine Prinzipdarstellung, teilweise im Schnitt, einer erfindungsgemäßen Wälzlagereinrichtung einer dritten Ausführungsform. Detaillierte Beschreibung der ZeichnungenFig. 3 is a schematic representation, partially in section, of a rolling bearing device according to the invention a third embodiment. Detailed description of the drawings
Fig. 1 zeigt eine erfindungsgemäße Wälzlagereinrichtung 1 , umfassend ein Tandemlager 2 bestehend aus zwei Wälzlagern 3a, 3b, wobei das Wälzlager 3a das innere Wälzlager und das Wälzlager 3b das äußere Wälzlager, bezogen auf die Anordnung einer Spindel 4, beispielsweise eine Motorspindel ist. Das innere Wälzlager 3a wird im Betrieb stärker thermisch belastet, da es motornäher ist als das äußere Wälzlager 3b.Fig. 1 shows a rolling bearing device 1 according to the invention, comprising a tandem bearing 2 consisting of two rolling bearings 3a, 3b, wherein the rolling bearing 3a, the inner roller bearing and the rolling bearing 3b, the outer bearing, based on the arrangement of a spindle 4, for example, a motor spindle. The inner roller bearing 3a is more thermally stressed during operation, since it is closer to the engine than the outer roller bearing 3b.
Jedes Wälzlager 3a, 3b umfasst einen Innenring 5a, 5b, der jeweils an der Spindel 4 angeordnet ist, sowie im gezeigten Beispiel einen Außenring 6a, 6b. Das Tandemlager 2 ist im Inneren einer Hülse 7 angeordnet, die die beiden Außenringe 6a, 6b übergreift. Die beiden Wälzlager sind spindelseitig über einen Distanzring 8, an dem die beiden Innenringe 5a, 5b anliegen, voneinander beabstandet. Im Bereich der Lageraußenringe ist an der Hülse ein Radialsteg 9 vorgesehen, der die beiden Außenringe 6a, 6b voneinander beabstandet. Dabei ist der Außenring 6b in der Hülse 7 lagefest aufgenommen, während der Außenring 6a in einem Schiebesitz an der Hülse 7 angeordnet ist. Dieser axial verschiebbare Lagerring 6a ist des Weiteren über ein Spannelement 10, hier eine Feder, axial vorgespannt, wobei das Spannelement 10 an einem Anschlagflansch 11 gegengelagert ist.Each rolling bearing 3a, 3b comprises an inner ring 5a, 5b, which is respectively arranged on the spindle 4, and in the example shown, an outer ring 6a, 6b. The tandem bearing 2 is arranged inside a sleeve 7, which engages over the two outer rings 6a, 6b. The two bearings are on the spindle side via a spacer ring 8, against which the two inner rings 5a, 5b, spaced from each other. In the area of the bearing outer rings, a radial web 9 is provided on the sleeve, which spacing the two outer rings 6a, 6b from one another. In this case, the outer ring 6b is received in a fixed position in the sleeve 7, while the outer ring 6a is arranged in a sliding fit on the sleeve 7. This axially displaceable bearing ring 6a is further biased axially via a clamping element 10, here a spring, wherein the clamping element 10 is mounted counter to a stop flange 11.
Die beiden Wälzlager 3a, 3b sind beide als Schrägkugellager ausgeführt, siehe die entsprechenden Ausbildungen der Laufflächen an den beiden La- geraußenringen 6a, 6b. Diese Schrägkugellagerausführung ermöglicht es nun, im Bereich des stärker beanspruchten inneren Wälzlagers thermisch bedingt auftretende Vorspannungsänderungen zu kompensieren und so insgesamt für eine gleichmäßigere Lagerbelastung des gesamten Tandemlagers 2 zu sorgen. Das innere Wälzlager 3a ist das im Betrieb stärker thermisch belastete Lager. Es bildet sich ein radialer Temperaturgradient aus, nachdem die Spindel 4 sich im Betrieb erwärmt, mit ihr auch der Innenring 5a. Der Außenring 6a ist demgegenüber kälter, insbesondere, wenn die Hülse 7 an einem Moto- rengehäuse oder dergleichen, das aktiv gekühlt wird, angeordnet. Es stellt sich also ein beachtlicher Temperaturgradient vom Innenring 5a zum Außenring 6a ein. Bedingt durch die Erwärmung dehnt sich der Innenring 5a etwas, woraus eine erhöhte, über die Kugeln 12a auf den Lagerring 6a übertragene Erhöhung der von Haus aus gegebenen Vorspannung resultiert. Die über die Kugeln 12a übertragene, dehnungsbedingte Kraftkomponente hat jedoch infolge der Schrägkugellagerausgestaltung einen axialen Kraftvektor. Dieser bewirkt, dass der im Schiebesitz aufgenommene äußere Lagerring 6a gegen das Spannelement 10 bewegt wird, wodurch dieses wiederum etwas komprimiert wird. Hierüber kann die überhöhte Lagervorspannung abgebaut und in das Spannelement geleitet werden. Es ergibt sich somit am inneren Wälzlager 3a keine Überlastung, aus der ein entsprechender Vorspannungsverlust am äußeren Wälzlager 3b resultieren würde. Vielmehr kann die Vorspannung am inneren Lager weitgehend konstant gehalten werden, so dass sich auch am äußeren Wälzlager 3a eine im Wesentlichen konstante Vor- Spannung beibehalten lässt. Zwar kann auch an diesem Lager ein Temperaturgradient auftreten, jedoch ist dieser, da dieses Wälzlager etwas motorferner ist, kleiner als der am inneren Wälzlager 3a auftretende Temperaturgradient, so dass dort die Spannungsverhältnisse sich nicht in einem solchen Maß ändern wie im Bereich des inneren Wälzlagers. Auch kann ein Lager- schlupf vermieden werden.The two rolling bearings 3a, 3b are both designed as angular contact ball bearings, see the corresponding embodiments of the running surfaces on the two bearing outer rings 6a, 6b. This angular contact ball bearing design now makes it possible to compensate for thermally induced changes in preload in the region of the more heavily loaded inner roller bearing and thus overall to ensure a more uniform bearing load on the entire tandem bearing 2. The inner roller bearing 3a is the more thermally loaded bearings during operation. It forms a radial temperature gradient after the spindle 4 heats up during operation, with it also the inner ring 5a. In contrast, the outer ring 6a is colder, in particular when the sleeve 7 is arranged on a motor housing or the like which is actively cooled. Thus, a considerable temperature gradient arises from the inner ring 5a to the outer ring 6a. Due to the heating, the inner ring 5a expands somewhat, resulting in an increased, transmitted via the balls 12a on the bearing ring 6a increase in the given home bias. However, the tensile force component transmitted through the balls 12a has an axial force vector due to the angular ball bearing design. This causes the received in the sliding seat outer bearing ring 6a is moved against the clamping element 10, whereby this in turn is slightly compressed. Over this, the excessive bearing preload can be reduced and passed into the clamping element. Thus, there is no overload on the inner roller bearing 3a, from which a corresponding loss of preload would result on the outer roller bearing 3b. Rather, the bias on the inner bearing can be kept substantially constant, so that can be maintained at the outer roller bearing 3a, a substantially constant bias voltage. Although a temperature gradient can occur at this bearing as well, since this rolling bearing is somewhat remote from the motor, it is smaller than the temperature gradient occurring at the inner rolling bearing 3a, so that the stress ratios do not change there to such an extent as in the area of the inner rolling bearing. Also, bearing slippage can be avoided.
Der Außenring 6a ist des Weiteren über eine Verdrehsicherung 17 gesichert, so dass er sich bei einer Rotation der Spindel 4, bei der die beiden Innenringe 5a, 5b und mit ihnen die Wälzkörper 12a, 12b bewegt werden, sich nicht mitbewegt. Fig. 2 zeigt eine weitere Variante eines erfindungsgemäßen Wälzlagers. Auch dieses umfasst ein Tandemlager 2 mit dem inneren Wälzlager 3a und dem äußeren Wälzlager 3b. Die inneren Lagerringe 5a, 5b sind wiederum an der Welle 4 angeordnet, auch hier sind beide Wälzlager 3a, 3b mit ihren Kugeln 12a, 12b als Schrägkugellager ausgeführt. Das innere Wälzlager 3a weist auch hier einen äußeren Lagerring 6a auf, der über ein Spannelement 10 vorgespannt ist und axial verschieblich in der Hülse 7 angeordnet ist. Bei dieser Ausgestaltung ist das Spannelement 10 gegen einen in der Hülse angeordneten Gegenlagerring 13 verspannt.The outer ring 6a is further secured by an anti-rotation 17, so that it does not move with a rotation of the spindle 4, in which the two inner rings 5a, 5b and with them the rolling elements 12a, 12b are moved. Fig. 2 shows another variant of a rolling bearing according to the invention. This also includes a tandem bearing 2 with the inner roller bearing 3a and the outer bearing 3b. The inner bearing rings 5a, 5b are in turn arranged on the shaft 4, and here again both rolling bearings 3a, 3b with their balls 12a, 12b are designed as angular contact ball bearings. The inner roller bearing 3a here also has an outer bearing ring 6a, which is prestressed via a tensioning element 10 and is arranged axially displaceably in the sleeve 7. In this embodiment, the clamping element 10 is clamped against an arranged in the sleeve bearing ring 13.
Anders als bei der Ausgestaltung nach Fig. 1 weist das äußere Wälzlager 3b keinen separaten Lagerring auf. Vielmehr ist hier die Hülse 7 selbst mit einer Lauffläche 14 versehen, die Hülse 7 bildet also selbst den Außenring des Wälzlagers 3b. Die Form der Lauffläche 14 entspricht der geforderten Form für die Ausbildung eines Schrägkugellagers.Unlike the embodiment according to FIG. 1, the outer rolling bearing 3b does not have a separate bearing ring. Rather, here the sleeve 7 itself is provided with a tread 14, the sleeve 7 thus forms even the outer ring of the rolling bearing 3b. The shape of the tread 14 corresponds to the required shape for the formation of an angular contact ball bearing.
Auch hier kann, nachdem die erfindungsgemäße Ausgleichseinrichtung 15 zum Ausgleich der thermisch bedingten Änderung der radialen Vorspannung am inneren Wälzlager 3a vorgesehen ist, eine entsprechende Vorspan- nungsüberhöhung, resultierend aus einer thermisch bedingten Dehnung, ohne weiteres kompensiert werden und für eine gleichmäßige Lagerbelastung gesorgt werden.Again, after the compensation device according to the invention 15 is provided to compensate for the thermally induced change in the radial preload on the inner roller bearing 3a, a corresponding Vorspan- nungsüberhöhung resulting from a thermally induced strain, be compensated easily and ensure a uniform bearing load.
Eine dritte Erfindungsausgestaltung ist in Fig. 3 dargestellt. Die Wälzlager- einrichtung 1 weist ebenfalls ein Tandemlager umfassend die beiden Wälzlager 3a und 3b auf. Die Ausgestaltung entspricht im Wesentlichen der Ausgestaltung gemäß Fig. 1 , jedoch ist dort kein die beiden äußeren Lagerringe 6a, 6b beabstandender Ringbund an der Hülse 7 vorgesehen. Vielmehr ist der Lagerring 6b mit einem radial verlaufenden Ansatz 16 versehen, der seit- lieh die Hülse 7 umgreift. Er ist auch hier lagefest, während der Lagerring 6a im Schiebesitz in der Hülse aufgenommen ist und auch hier über eine Ausgleichseinrichtung 15 umfassend das Spannelement 10 vorgespannt. BezugszeichenlisteA third embodiment of the invention is shown in FIG. The rolling bearing device 1 also has a tandem bearing comprising the two rolling bearings 3a and 3b. The embodiment corresponds essentially to the embodiment according to FIG. 1, but there is no annular collar provided on the sleeve 7 that separates the two outer bearing rings 6a, 6b. Rather, the bearing ring 6b is provided with a radially extending shoulder 16, which laterally surrounds the sleeve 7. It is also fixed in position here, while the bearing ring 6a is received in the sliding seat in the sleeve and biased here via a compensating device 15 comprising the clamping element 10. LIST OF REFERENCE NUMBERS
1 Wälzlagereinrichtung1 rolling bearing device
2 Tandemlager2 tandem camps
3a Wälzlager3a rolling bearings
3b Wälzlager3b rolling bearings
4 Spindel4 spindle
5a Innenring5a inner ring
5b Innenring5b inner ring
6a Außenring6a outer ring
6b Außenring6b outer ring
7 Hülse7 sleeve
8 Distanzring8 spacer ring
9 Radialsteg9 radial bridge
10 Spannelement (Feder10 clamping element (spring
11 Spannelement (Anschlagflansch)11 clamping element (stop flange)
12a Kugeln12a balls
12b Kugeln12b balls
13 Gegenlagerring13 counter bearing ring
14 Lauffläche14 tread
15 Ausgleichseinrichtung15 equalizing device
17 Verdrehsicherung 17 anti-twist device

Claims

Patentansprüche claims
1. Wälzlagereinrichtung für Spindeln, insbesondere Motorspindeln, umfassend ein Tandemlager mit einem in Spindelachsrichtung gesehen inneren und einem äußeren Wälzlager in Form von Schrägkugellagern, die unter radialer Vorspannung betrieben werden, wobei zumin- dest das innere Wälzlager einen Außenring aufweist, dadurch gekennzeichnet, dass beide Wälzlager (3a, 3b) in einer gemeinsamen Hülse (7) o.dgl. aufgenommen sind, und dass eine Einrichtung (15) zum Ausgleich thermisch bedingter Änderungen der radialen Vorspannung umfassend ein auf den in einem axialen Schiebesitz in der Hülse (7) o.dgl. gehalterten Außenring (6a) des inneren Wälzlagers1. Rolling bearing device for spindles, in particular motor spindles, comprising a tandem bearing with a seen in Spindelachsrichtung inner and an outer bearings in the form of angular contact ball bearings, which are operated under radial bias, wherein at least the inner roller bearing has an outer ring, characterized in that both Rolling (3a, 3b) in a common sleeve (7) or the like. are received, and that means (15) for compensating for thermally induced changes in the radial bias comprising a in the axial sliding fit in the sleeve (7) or the like. supported outer ring (6a) of the inner bearing
(3a) axial wirkendes Spannelement (10) vorgesehen ist.(3 a) axially acting clamping element (10) is provided.
2. Wälzlagereinrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass das Spannelement (10) ein Federelement ist.2. Rolling bearing device according to claim 1, characterized in that the clamping element (10) is a spring element.
3. Wälzlagereinrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass das Spannelement (10) ein piezoelektrischer Aktor oder ein aus einer Formgedächtnislegierungen bestehendes Spannelement oder ein hydraulischer oder pneumatischer Aktor ist. 3. Rolling bearing device according to claim 1, characterized in that the clamping element (10) is a piezoelectric actuator or a shape memory alloy existing clamping element or a hydraulic or pneumatic actuator.
4. Wälzlagereinrichtung nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass der Außenring (3a) über eine Verdrehsicherung (17) gesichert ist.4. Rolling bearing device according to one of the preceding claims, characterized in that the outer ring (3a) via an anti-rotation (17) is secured.
5. Wälzlagereinrichtung nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass der Außenring (6a) des äußeren Wälzlagers (3b) von der Hülse (7) o.dgl. gebildet ist. 5. Rolling bearing device according to one of the preceding claims, characterized in that the outer ring (6 a) of the outer roller bearing (3 b) of the sleeve (7) or the like. is formed.
PCT/DE2007/002231 2007-01-12 2007-12-11 Roller bearing device for shafts in particular motor shafts WO2008083649A1 (en)

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