WO2015132066A1 - Change-speed gearbox - Google Patents

Change-speed gearbox Download PDF

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Publication number
WO2015132066A1
WO2015132066A1 PCT/EP2015/053170 EP2015053170W WO2015132066A1 WO 2015132066 A1 WO2015132066 A1 WO 2015132066A1 EP 2015053170 W EP2015053170 W EP 2015053170W WO 2015132066 A1 WO2015132066 A1 WO 2015132066A1
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WO
WIPO (PCT)
Prior art keywords
transmission
gear change
countershaft
shaft
roller bearing
Prior art date
Application number
PCT/EP2015/053170
Other languages
German (de)
French (fr)
Inventor
Andreas Heile
Jürgen THEUERER
Thomas Wolf
Original Assignee
Aktiebolaget Skf
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Filing date
Publication date
Application filed by Aktiebolaget Skf filed Critical Aktiebolaget Skf
Publication of WO2015132066A1 publication Critical patent/WO2015132066A1/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
    • 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
    • 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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • 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 change-speed gearbox, comprising at least one drive shaft, at least one output shaft and at least one countershaft, which is engageable with the drive shaft and the output shaft via teeth in engagement, wherein at least one of the transmission shafts is mounted in its axial end regions, each with a rolling bearing , Gear change gears of this type are well known.
  • the countershaft - where appropriate, there are two of these - is usually stored by means of two tapered roller bearings, which are employed axially. This axial and radial loads can be transmitted safely. Only the input shaft is usually stored in a fixed-LosLagerung. In the case of a gearbox with two countershafts, it is also intended to be stored in two engaged tapered roller bearings.
  • the invention is therefore based on the object, a gear change transmission of the type mentioned in such a way that the friction in the bearing of the transmission is minimized without reducing the life of the transmission. This is to reduce the power required in the transmission and thus the fuel consumption of the vehicle. Furthermore, in the operation of the vehicle, the C0 2 - emissions can be reduced.
  • the solution to this problem by the invention provides that the one rolling bearing for supporting the at least one transmission shaft is a tapered roller bearing and the other rolling bearing for supporting the same transmission shaft is a deep groove ball bearing.
  • the invention thus turns away from the previously known concept according to which the transmission shafts, in particular the countershaft, is always mounted in two salaried tapered roller bearings.
  • the teeth are preferably helical serrations. They may be arranged so that in the train operation, the at least one transmission shaft, in particular the countershaft, always only in an axial direction of the transmission shaft is loaded. In this case, practically only the tapered roller bearing is subjected to an axial load, while the deep groove ball bearing transmits substantially only radial loads.
  • the change-speed gearbox can also have a first and a second countershaft. Then it is preferably provided that a countershaft is mounted by means of the tapered roller bearing and the deep groove ball bearing, wherein the other countershaft is mounted by means of a tapered roller bearing and an angular contact ball bearing.
  • the change-speed gearbox is preferably a motor vehicle change-speed gearbox. It is especially thought of a car transmission. It can be designed as a manual transmission or as an automated manual transmission.
  • a dual-clutch transmission it is used in the embodiment as a dual-clutch transmission; this preferably has two countershafts.
  • the invention thus proposes that at least one of the countershafts of the change-speed gearbox is mounted with a roller bearing combination, which consists of a deep groove ball bearing and a tapered roller bearing.
  • a roller bearing combination which consists of a deep groove ball bearing and a tapered roller bearing.
  • This is preferably the storage of a second countershaft, as used for example in a dual-clutch transmission.
  • a combination of tapered roller bearings and deep groove ball bearings is used for storage in particular a second countershaft instead of two tapered roller bearings. Due to the direction of the forces acting in the teeth, advantageously almost all resulting axial forces are absorbed by the tapered roller bearing.
  • the existing deep groove ball bearing is thus largely loaded only radially.
  • the proposed solution makes it possible to store the countershaft - in particular the second countershaft in a change-speed gearbox - with less friction than before. Accordingly, power in the area of the transmission can be saved, which also reduces fuel consumption as a result. This effect is particularly noticeable in the case of a passenger car manual transmission.
  • FIG. 1 shows schematically a change-speed gearbox of a passenger car and the side view of a countershaft of the change-speed gearbox according to FIG. 1.
  • a change-speed gearbox 1 is shown schematically. It has a drive shaft 2 and an output shaft 3. The torque is transmitted via a countershaft 4. To this end, gears 5 and 6 are provided which can transmit the torque.
  • the change-speed gearbox 1 may also have two countershafts 4; this case is not shown.
  • each countershaft 4 is mounted in its two axial end portions 7 and 8, each with a rolling bearing 9 and 10. Details on this are shown in FIG. 2.
  • the one roller bearing 9 is formed as a tapered roller bearing, which is known per se.
  • the other rolling bearing 10 is a deep groove ball bearing. Since the two gears 5, 6 are formed as helical gears, axial forces are generated or transmitted via the teeth in operation. The gears are arranged so that in the train operation, the countershaft is pushed in the embodiment to the right. Accordingly, the tapered roller bearing 9 is axially loaded in this standard load, while the deep groove ball bearing 10 remains largely free of axial forces and only radial loads must be transmitted.
  • the other, not shown countershaft can be supported by means of a tapered roller bearing and an angular contact ball bearing, which corresponds to a preferred embodiment of the invention.
  • the friction in the gear can be minimized.
  • the arrangement is - as described - designed so that in the train operation, the countershaft 4 runs against the tapered roller bearing 9, d. H. the axial forces are absorbed exclusively by the tapered roller bearing 9.
  • the deep groove ball bearing 10 then transmits no axial forces; it runs only with radial load.
  • the deep groove ball bearing 10 is axially fixed on one side only, ie, it can be applied to the axial forces occurring. dents in train operation and so only radial forces, but no axial forces transmitted.
  • the bearing according to the invention for the countershaft 4 is described. It can be used analogously for the drive or output shaft 2, 3.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)

Abstract

The invention relates to a change-speed gearbox (1), comprising at least one input shaft (2), at least one output shaft (3) and at least one countershaft (4) which can be engaged with the input shaft (2) and the output shaft (3) via toothings (5, 6), the axial end sections (7, 8) of at least one of the gearbox shafts (2, 3, 4) being mounted by one rolling element bearing (9, 10) each. In order to minimize the friction in the gearbox, the one rolling element bearing (9) for mounting the at least one gearbox shaft (2, 3, 4) is a tapered roller bearing and the other rolling element bearing (10) for mounting the gearbox shaft (2, 3, 4) is a deep groove ball bearing.

Description

B e s c h r e i b u n g  Description
Zahnräderwechselgetriebe Gear shift transmission
Die Erfindung betrifft ein Zahnräderwechselgetriebe, umfassend mindestens eine An- triebswelle, mindestens eine Abtriebswelle und mindestens eine Vorgelegewelle, die mit der Antriebswelle und der Abtriebswelle über Verzahnungen in Eingriff bringbar ist, wobei mindestens eine der Getriebewellen in ihren axialen Endbereichen mit je einem Wälzlager gelagert ist. Zahnräderwechselgetriebe dieser Bauart sind hinlänglich bekannt. Die Vorgelegewelle - gegebenenfalls sind von diesen auch zwei vorhanden - ist dabei in der Regel mittels zweier Kegelrollenlager gelagert, die axial angestellt sind. Damit können axiale und radiale Lasten sicher übertragen werden. Lediglich die Eingangswelle ist zumeist in einer Fest-LosLagerung gelagert. Auch im Falle eines Getriebes mit zwei Vorgelegewellen ist vorgese- hen, diese in zwei angestellten Kegelrollenlagern zu lagern. The invention relates to a change-speed gearbox, comprising at least one drive shaft, at least one output shaft and at least one countershaft, which is engageable with the drive shaft and the output shaft via teeth in engagement, wherein at least one of the transmission shafts is mounted in its axial end regions, each with a rolling bearing , Gear change gears of this type are well known. The countershaft - where appropriate, there are two of these - is usually stored by means of two tapered roller bearings, which are employed axially. This axial and radial loads can be transmitted safely. Only the input shaft is usually stored in a fixed-LosLagerung. In the case of a gearbox with two countershafts, it is also intended to be stored in two engaged tapered roller bearings.
Nachteilig ist, dass die Lagerung der verschiedenen Wellen des Getriebes Reibungsverluste verursachen, die sich negativ hinsichtlich der Lebensdauer des Getriebes und vor allem im Kraftstoffverbrauch bemerkbar machen. Auch der C02-Ausstoß ist nachteilig entspre- chend groß. The disadvantage is that the storage of the various shafts of the transmission cause friction losses, which have a negative effect on the life of the transmission and especially in fuel consumption. C0 2 emissions are also disadvantageously large.
Der Erfindung liegt daher die A u f g a b e zugrunde, ein Zahnräderwechselgetriebe der eingangs genannten Art so auszubilden, dass die Reibung in der Lagerung des Getriebes minimiert wird, ohne dass sich die Lebensdauer des Getriebes reduziert. Damit soll die im Getriebe benötigte Leistung und somit der Kraftstoffverbrauch des Fahrzeugs vermindert werden. Ferner soll im Betrieb des Fahrzeugs der C02- Ausstoß reduziert werden können. Die L ö s u n g dieser Aufgabe durch die Erfindung sieht vor, dass das eine Wälzlager zur Lagerung der mindestens einen Getriebewelle ein Kegelrollenlager ist und das andere Wälzlager zur Lagerung derselben Getriebewelle ein Rillenkugellager ist. The invention is therefore based on the object, a gear change transmission of the type mentioned in such a way that the friction in the bearing of the transmission is minimized without reducing the life of the transmission. This is to reduce the power required in the transmission and thus the fuel consumption of the vehicle. Furthermore, in the operation of the vehicle, the C0 2 - emissions can be reduced. The solution to this problem by the invention provides that the one rolling bearing for supporting the at least one transmission shaft is a tapered roller bearing and the other rolling bearing for supporting the same transmission shaft is a deep groove ball bearing.
Die Erfindung kehrt sich also vom vorbekannten Konzept ab, nach dem die Getriebewellen, insbesondere die Vorgelegewelle, stets in zwei angestellten Kegelrollenlagern gelagert ist. The invention thus turns away from the previously known concept according to which the transmission shafts, in particular the countershaft, is always mounted in two salaried tapered roller bearings.
Die Verzahnungen sind bevorzugt schrägverzahnte Stirnverzahnungen. Sie können so angeordnet sein, dass im Zugbetrieb die mindestens eine Getriebewelle, insbesondere die Vorgelegewelle, stets nur in eine axiale Richtung der Getriebewelle belastet wird. In diesem Falle wird praktisch nur das Kegelrollenlager mit einer axialen Last beaufschlagt, während das Rillenkugellager im wesentlichen nur radiale Lasten überträgt. The teeth are preferably helical serrations. They may be arranged so that in the train operation, the at least one transmission shaft, in particular the countershaft, always only in an axial direction of the transmission shaft is loaded. In this case, practically only the tapered roller bearing is subjected to an axial load, while the deep groove ball bearing transmits substantially only radial loads.
Das Zahnräderwechselgetriebe kann auch eine erste und eine zweite Vorgelegewelle aufweisen. Dann ist bevorzugt vorgesehen, dass die eine Vorgelegewelle mittels des Kegelrollenlagers und des Rillenkugellagers gelagert ist, wobei die andere Vorgelegewelle mittels eines Kegelrollenlagers und eines Schrägkugellagers gelagert ist. The change-speed gearbox can also have a first and a second countershaft. Then it is preferably provided that a countershaft is mounted by means of the tapered roller bearing and the deep groove ball bearing, wherein the other countershaft is mounted by means of a tapered roller bearing and an angular contact ball bearing.
Das Zahnräderwechselgetriebe ist bevorzugt ein Kraftfahrzeug-Zahnräderwechselgetriebe. Dabei ist insbesondere an ein PKW-Getriebe gedacht. Es kann als Handschaltgetriebe oder als automatisiertes Schaltgetriebe ausgebildet sein. The change-speed gearbox is preferably a motor vehicle change-speed gearbox. It is especially thought of a car transmission. It can be designed as a manual transmission or as an automated manual transmission.
Gemäß einer bevorzugten Anwendung kommt es in der Ausgestaltung als Doppelkupplungsgetriebe zum Einsatz; dieses hat bevorzugt zwei Vorgelegewellen. According to a preferred application, it is used in the embodiment as a dual-clutch transmission; this preferably has two countershafts.
Die Erfindung schlägt also vor, dass zumindest eine der Vorgelegewellen des Zahnräderwechselgetriebes mit einer Wälzlagerkombination gelagert wird, die aus einem Rillenkugellager und einem Kegelrollenlager besteht. Bevorzugt handelt es sich hierbei um die Lagerung einer zweiten Vorgelegewelle, wie sie beispielsweise in einem Doppelkupplungsgetriebe zum Einsatz kommt. Somit wird zur Lagerung insbesondere einer zweiten Vorgelegewelle statt zweier Kegelrollenlager eine Kombination aus Kegelrollenlager und Rillenkugellager eingesetzt. Aufgrund der Richtung der Kräfte, die in den Verzahnungen wirken, werden vorteilhaft nahezu alle resultierenden Axialkräfte vom Kegelrollenlager aufgenommen. Das weiter vorhandene Rillenkugellager wird somit weitgehend nur radial belastet. The invention thus proposes that at least one of the countershafts of the change-speed gearbox is mounted with a roller bearing combination, which consists of a deep groove ball bearing and a tapered roller bearing. This is preferably the storage of a second countershaft, as used for example in a dual-clutch transmission. Thus, a combination of tapered roller bearings and deep groove ball bearings is used for storage in particular a second countershaft instead of two tapered roller bearings. Due to the direction of the forces acting in the teeth, advantageously almost all resulting axial forces are absorbed by the tapered roller bearing. The existing deep groove ball bearing is thus largely loaded only radially.
Insbesondere in der Kombination der Lagerung einer ersten Vorgelegewelle mittels eines Kegelrollenlagers und eines Schrägkugellagers sowie für die entsprechende Lagerung der Differentialwelle kann somit eine deutliche Reibmomentreduzierung erzielt werden, so dass Energie im Betrieb des Getriebes eingespart werden kann. In particular, in the combination of the storage of a first countershaft by means of a tapered roller bearing and an angular contact ball bearing and for the corresponding storage of the differential shaft thus a significant Reibmomentreduzierung can be achieved, so that energy can be saved in the operation of the transmission.
Mit der vorgeschlagenen Lösung wird es möglich, die Vorgelegewelle - insbesondere die zweite Vorgelegewelle in einem Zahnräderwechselgetriebe - reibungsärmer als bislang zu lagern. Demgemäß kann Leistung im Bereich des Getriebes eingespart werden, was in der Folge auch den Kraftstoffverbrauch senkt. Dieser Effekt macht sich insbesondere im Falle eines PKW-Schaltgetriebes bemerkbar. The proposed solution makes it possible to store the countershaft - in particular the second countershaft in a change-speed gearbox - with less friction than before. Accordingly, power in the area of the transmission can be saved, which also reduces fuel consumption as a result. This effect is particularly noticeable in the case of a passenger car manual transmission.
Die erzielbaren Vorteile sind also ein deutlich reibungsärmerer Lauf des Getriebes, ohne dessen Gebrauchsdauer zu reduzieren. Somit ist eine Einsparung von Energie möglich, was sich sowohl beim Kraftstoffverbrauch als auch beim C02-Ausstoß positiv bemerkbar macht. The achievable advantages are thus a significantly lower friction running of the transmission, without reducing its service life. Thus, a saving of energy is possible, which makes positive both in terms of fuel consumption and C0 2 emissions.
In der Zeichnung ist ein Ausführungsbeispiel der Erfindung dargestellt. Es zeigen: In the drawing, an embodiment of the invention is shown. Show it:
Fig. 1 schematisch ein Zahnräderwechselgetriebe eines Personenkraftwagens und die Seitenansicht einer Vorgelegewelle des Zahnräderwechselgetriebes nach Fig. 1. 1 shows schematically a change-speed gearbox of a passenger car and the side view of a countershaft of the change-speed gearbox according to FIG. 1.
In Fig. 1 ist ein Zahnräderwechselgetriebe 1 schematisch dargestellt. Es weist eine An- triebswelle 2 und eine Abtriebswelle 3 auf. Das Drehmoment wird über eine Vorgelegewelle 4 übertragen. Hierzu sind Verzahnungen 5 und 6 vorgesehen, die das Drehmoment übertragen können. Das Zahnräderwechselgetriebe 1 kann auch zwei Vorgelegewellen 4 aufweisen; dieser Fall ist allerdings nicht dargestellt. In Fig. 1, a change-speed gearbox 1 is shown schematically. It has a drive shaft 2 and an output shaft 3. The torque is transmitted via a countershaft 4. To this end, gears 5 and 6 are provided which can transmit the torque. The change-speed gearbox 1 may also have two countershafts 4; this case is not shown.
Die oder jede Vorgelegewelle 4 ist in ihren beiden axialen Endbereichen 7 und 8 mit je einem Wälzlager 9 und 10 gelagert. Details hierzu zeigt Fig. 2. The or each countershaft 4 is mounted in its two axial end portions 7 and 8, each with a rolling bearing 9 and 10. Details on this are shown in FIG. 2.
Jedenfalls für eine der Vorgelegewellen 4 des Zahnräderwechselgetriebes 1 ist vorgesehen, dass das eine Wälzlager 9 als Kegelrollenlager ausgebildet ist, was an sich bekannt ist. Neu ist indes, dass das andere Wälzlager 10 ein Rillenkugellager ist. Da die beiden Verzahnungen 5, 6 als Schrägverzahnungen ausgebildet sind, werden im Betrieb auch axiale Kräfte über die Verzahnungen erzeugt bzw. übertragen. Die Verzahnungen sind dabei so angeordnet, dass im Zugbetrieb die Vorgelegewelle im Ausführungsbeispiel nach rechts geschoben wird. Demgemäß wird bei dieser Standardbelastung das Kegelrollenlager 9 axial belastet, während das Rillenkugellager 10 weitgehend frei von axialen Kräften bleibt und nur radiale Lasten übertragen muss. In any case, for one of the countershafts 4 of the change-speed gearbox 1 is provided that the one roller bearing 9 is formed as a tapered roller bearing, which is known per se. What is new, however, is that the other rolling bearing 10 is a deep groove ball bearing. Since the two gears 5, 6 are formed as helical gears, axial forces are generated or transmitted via the teeth in operation. The gears are arranged so that in the train operation, the countershaft is pushed in the embodiment to the right. Accordingly, the tapered roller bearing 9 is axially loaded in this standard load, while the deep groove ball bearing 10 remains largely free of axial forces and only radial loads must be transmitted.
Die andere, nicht dargestellte Vorgelegewelle kann mittels eines Kegelrollenlagers und eines Schrägkugellagers gelagert sein, was einer bevorzugten Ausführungsform der Erfindung entspricht. Die Reibung im Getriebe kann so minimiert werden. The other, not shown countershaft can be supported by means of a tapered roller bearing and an angular contact ball bearing, which corresponds to a preferred embodiment of the invention. The friction in the gear can be minimized.
Die Anordnung ist - wie beschrieben - so ausgestaltet, dass im Zugbetrieb die Vorgelegewelle 4 gegen das Kegelrollenlager 9 läuft, d. h. die axialen Kräfte werden ausschließlich vom Kegelrollenlager 9 aufgenommen. Das Rillenkugellager 10 überträgt dann keine axia- len Kräfte; es läuft lediglich radial belastet mit. The arrangement is - as described - designed so that in the train operation, the countershaft 4 runs against the tapered roller bearing 9, d. H. the axial forces are absorbed exclusively by the tapered roller bearing 9. The deep groove ball bearing 10 then transmits no axial forces; it runs only with radial load.
Im Schubbetrieb kehrt sich die axiale Kraftrichtung betreffend die Vorgelegewelle 4 um, d. h. jetzt müssen axiale Kräfte ausschließlich vom Rillenkugellager 10 aufgenommen werden. Zu diesem Zweck muss das Rillenkugellager einseitig axial festgelegt sein. In overrun mode, the axial force direction is reversed regarding the countershaft 4, d. H. Now axial forces must be absorbed exclusively by the deep groove ball bearing 10. For this purpose, the deep groove ball bearing must be axially fixed on one side.
Damit im Zugbetrieb die axialen Kräfte der Vorgelegewelle 4 allerdings ausschließlich vom Kegelrollenlager 9 aufgenommen werden, ist bevorzugt vorgesehen, dass das Rillenkugellager 10 nur einseitig axial fixiert ist, d. h. es kann bei den auftretenden axialen Kräf- ten im Zugbetrieb ausweichen und so nur radiale Kräfte, jedoch keine axialen Kräfte übertragen. However, in order for the axial forces of the countershaft 4 to be absorbed exclusively by the tapered roller bearing 9 during traction, it is preferably provided that the deep groove ball bearing 10 is axially fixed on one side only, ie, it can be applied to the axial forces occurring. dents in train operation and so only radial forces, but no axial forces transmitted.
Im Ausführungsbeispiel ist die erfindungsgemäße Lagerung für die Vorgelegewelle 4 beschrieben. Sie kann analog auch für die Antriebs- bzw. Abtriebswelle 2, 3 eingesetzt werden. In the exemplary embodiment, the bearing according to the invention for the countershaft 4 is described. It can be used analogously for the drive or output shaft 2, 3.
Bezugszeichenliste LIST OF REFERENCE NUMBERS
1 Zahnräderwechselgetriebe1 change-speed gearbox
2 Antriebswelle (Getriebewelle)2 drive shaft (gear shaft)
3 Abtriebswelle (Getriebewelle)3 output shaft (transmission shaft)
4 Vorgelegewelle (Getriebewelle) 5 Verzahnung 4 Countershaft (Transmission shaft) 5 Gearing
6 Verzahnung  6 toothing
7 axialer Endbereich  7 axial end region
8 axialer Endbereich  8 axial end region
9 Wälzlager (Kegelrollenlager) 10 Wälzlager (Rillenkugellager)  9 Rolling Bearings (Tapered Roller Bearings) 10 Rolling Bearings (Deep Groove Ball Bearings)

Claims

P a t e n t a n s p r ü c h e P a t e n t a n s r ü c h e
Zahnräderwechselgetriebe Gear changing transmission
Zahnräderwechselgetriebe (1), umfassend mindestens eine Antriebswelle (2), mindestens eine Abtriebswelle (3) und mindestens eine Vorgelegewelle (4), die mit der Antriebswelle Gear change transmission (1), comprising at least one drive shaft (2), at least one output shaft (3) and at least one countershaft (4), which is connected to the drive shaft
(2) und der Abtriebswelle (3) über Verzahnungen (5, 6) in Eingriff bringbar ist, wobei mindestens eine der Getriebewellen (2, 3, 4) in ihren axialen Endbereichen (7, 8) mit je einem Wälzlager (9, 10) gelagert ist, dadurch gekennzeichnet, dass das eine Wälzlager (9) zur Lagerung der mindestens einen Getriebewelle (2, 3, 4) ein Kegelrollenlager ist und das andere Wälzlager (10) zur Lagerung der Getriebewelle (2, 3, 4) ein Rillenkugellager ist. (2) and the output shaft (3) can be brought into engagement via toothing (5, 6), with at least one of the transmission shafts (2, 3, 4) having a roller bearing (9, 10) in its axial end regions (7, 8). ) is stored, characterized in that one roller bearing (9) for supporting the at least one transmission shaft (2, 3, 4) is a tapered roller bearing and the other roller bearing (10) for supporting the transmission shaft (2, 3, 4) is a deep groove ball bearing is.
Zahnräderwechselgetriebe nach Anspruch 1, dadurch gekennzeichnet, dass die Verzahnungen (5, 6) schrägverzahnte Stirn Verzahnungen sind. Gear changing transmission according to claim 1, characterized in that the toothings (5, 6) are helical front toothings.
Zahnräderwechselgetriebe nach Anspruch 2, dadurch gekennzeichnet, dass die Verzahnungen (5, 6) so angeordnet sind, dass im Zugbetrieb die mindestens eine Getriebewelle (2, 3, 4) stets nur in eine axiale Richtung der Getriebewelle (2, Gear change transmission according to claim 2, characterized in that the toothings (5, 6) are arranged such that during pulling operation the at least one transmission shaft (2, 3, 4) always only moves in one axial direction of the transmission shaft (2,
3, 4) belastet wird. 3, 4) is charged.
4. Zahnräderwechselgetriebe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass es eine erste und eine zweite Vorgelegewelle (4) aufweist. 4. Gear change transmission according to one of claims 1 to 3, characterized in that it has a first and a second countershaft (4).
5. Zahnräderwechselgetriebe nach Anspruch 4, dadurch gekennzeichnet, dass die eine Vorgelegewelle (4) mittels des Kegelrollenlagers (9) und des Rillenkugellagers (10) gelagert ist, wobei die andere Vorgelegewelle mittels eines Kegelrollenlagers und eines Schrägkugellagers gelagert ist. 5. Gear change transmission according to claim 4, characterized in that one countershaft (4) is mounted by means of the tapered roller bearing (9) and the deep groove ball bearing (10), the other countershaft being mounted by means of a tapered roller bearing and an angular contact ball bearing.
6. Zahnräderwechselgetriebe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass es ein Kraftfahrzeug-Zahnräderwechselgetriebe ist. 6. gear change transmission according to one of claims 1 to 5, characterized in that it is a motor vehicle gear change transmission.
7. Zahnräderwechselgetriebe nach Anspruch 6, dadurch gekennzeichnet, dass es ein PKW-Getriebe ist. 7. Gear change transmission according to claim 6, characterized in that it is a car transmission.
8. Zahnräderwechselgetriebe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass es als Handschaltgetriebe ausgebildet ist. 8. Gear change transmission according to one of claims 1 to 7, characterized in that it is designed as a manual transmission.
9. Zahnräderwechselgetriebe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass es als automatisiertes Schaltgetriebe ausgebildet ist. 9. Gear change transmission according to one of claims 1 to 7, characterized in that it is designed as an automated manual transmission.
10. Zahnräderwechselgetriebe nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass es als Doppelkupplungsgetriebe ausgebildet ist. 10. Gear change transmission according to one of claims 1 to 9, characterized in that it is designed as a dual clutch transmission.
PCT/EP2015/053170 2014-03-06 2015-02-16 Change-speed gearbox WO2015132066A1 (en)

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DE102014204061.2A DE102014204061B4 (en) 2014-03-06 2014-03-06 Gear change transmission

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