WO2015132066A1 - Boîte manuelle à engrenages - Google Patents

Boîte manuelle à engrenages 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
Authority
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)
English (en)
Inventor
Andreas Heile
Jürgen THEUERER
Thomas Wolf
Original Assignee
Aktiebolaget Skf
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 Aktiebolaget Skf filed Critical Aktiebolaget Skf
Publication of WO2015132066A1 publication Critical patent/WO2015132066A1/fr

Links

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.

Landscapes

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

Abstract

L'invention concerne une boîte manuelle à engrenage (1), comprenant au moins un arbre d'entraînement (2), au moins un arbre de sortie (3) et au moins un arbre intermédiaire (4), qui peut être amené en prise avec l'arbre d'entraînement (2) et l'arbre de sortie (3) par l'intermédiaire de dentures (5, 6). Au moins un des arbres (2, 3, 4) est monté, dans leurs zones d'extrémité (7, 8) axiales, par respectivement un palier de roulement (9, 10). L'invention vise à réduire au minium la friction dans la boîte. A cet effet, l'un des paliers de roulement (9) servant au montage du ou des arbres (2, 3, 4) est un roulement conique à rouleaux, et l'autre palier de roulement (10) servant au montage de l'arbre (2, 3, 4) est un roulement rainuré à billes.
PCT/EP2015/053170 2014-03-06 2015-02-16 Boîte manuelle à engrenages WO2015132066A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014204061.2A DE102014204061B4 (de) 2014-03-06 2014-03-06 Zahnräderwechselgetriebe
DE102014204061.2 2014-03-06

Publications (1)

Publication Number Publication Date
WO2015132066A1 true WO2015132066A1 (fr) 2015-09-11

Family

ID=53883957

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/053170 WO2015132066A1 (fr) 2014-03-06 2015-02-16 Boîte manuelle à engrenages

Country Status (2)

Country Link
DE (1) DE102014204061B4 (fr)
WO (1) WO2015132066A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015223064A1 (de) * 2015-11-23 2017-05-24 Zf Friedrichshafen Ag Wälzlager, Getriebe sowie Kraftfahrzeug
WO2021099035A1 (fr) * 2019-11-20 2021-05-27 Robert Bosch Gmbh Accouplement d'arbres entre un arbre de rotor d'une machine électrique et un arbre d'entrée d'une boîte de vitesses

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3072748B1 (fr) * 2017-10-24 2021-02-19 Renault Sas Empilage de ligne d'arbres de transmission avec rondelle de calage indexee, procede de montage et transmission

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0177286A2 (fr) * 1984-09-27 1986-04-09 Toyota Jidosha Kabushiki Kaisha Transmission de puissance pour véhicules à quatre roues motrices
US5598747A (en) * 1995-05-04 1997-02-04 Dana Corporation Thermal compensating bearing support structure for transmission case
DE10253416A1 (de) * 2002-11-08 2004-05-27 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Stufengetriebe für ein Kraftfahrzeug
WO2005008098A1 (fr) * 2003-07-16 2005-01-27 Daimlerchrysler Ag Embrayage double
DE102007003675A1 (de) * 2007-01-25 2008-07-31 Schaeffler Kg Stirnraddifferenzial mit einem Planetentrieb
US20100099526A1 (en) * 2008-10-20 2010-04-22 Aisin Aw Co., Ltd. Belt type continuously variable transmission
DE102011010204A1 (de) * 2011-02-03 2012-08-09 Daimler Ag Antriebsstrang für ein Kraftfahrzeug

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006054281A1 (de) * 2006-11-17 2008-06-12 Zf Friedrichshafen Ag Doppelkupplungs-Windungsgetriebe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0177286A2 (fr) * 1984-09-27 1986-04-09 Toyota Jidosha Kabushiki Kaisha Transmission de puissance pour véhicules à quatre roues motrices
US5598747A (en) * 1995-05-04 1997-02-04 Dana Corporation Thermal compensating bearing support structure for transmission case
DE10253416A1 (de) * 2002-11-08 2004-05-27 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Stufengetriebe für ein Kraftfahrzeug
WO2005008098A1 (fr) * 2003-07-16 2005-01-27 Daimlerchrysler Ag Embrayage double
DE102007003675A1 (de) * 2007-01-25 2008-07-31 Schaeffler Kg Stirnraddifferenzial mit einem Planetentrieb
US20100099526A1 (en) * 2008-10-20 2010-04-22 Aisin Aw Co., Ltd. Belt type continuously variable transmission
DE102011010204A1 (de) * 2011-02-03 2012-08-09 Daimler Ag Antriebsstrang für ein Kraftfahrzeug

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015223064A1 (de) * 2015-11-23 2017-05-24 Zf Friedrichshafen Ag Wälzlager, Getriebe sowie Kraftfahrzeug
WO2021099035A1 (fr) * 2019-11-20 2021-05-27 Robert Bosch Gmbh Accouplement d'arbres entre un arbre de rotor d'une machine électrique et un arbre d'entrée d'une boîte de vitesses

Also Published As

Publication number Publication date
DE102014204061B4 (de) 2020-07-09
DE102014204061A1 (de) 2015-09-10

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