WO2012052234A1 - Élément de changement de vitesses fonctionnant par complémentarité de forme - Google Patents

Élément de changement de vitesses fonctionnant par complémentarité de forme Download PDF

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Publication number
WO2012052234A1
WO2012052234A1 PCT/EP2011/066182 EP2011066182W WO2012052234A1 WO 2012052234 A1 WO2012052234 A1 WO 2012052234A1 EP 2011066182 W EP2011066182 W EP 2011066182W WO 2012052234 A1 WO2012052234 A1 WO 2012052234A1
Authority
WO
WIPO (PCT)
Prior art keywords
profile
sliding sleeve
flanks
idler gear
switching element
Prior art date
Application number
PCT/EP2011/066182
Other languages
German (de)
English (en)
Inventor
Manuel Goetz
Christian Sibla
Detlef Baasch
Matthias Arzner
Johannes Winkler
Steffen Bertsch
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2012052234A1 publication Critical patent/WO2012052234A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D11/08—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially
    • F16D11/10—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially with clutching members movable only axially
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D2011/002—Clutches in which the members have interengaging parts using an external and axially slidable sleeve for coupling the teeth of both coupling components together
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D2011/008—Clutches in which the members have interengaging parts characterised by the form of the teeth forming the inter-engaging parts; Details of shape or structure of these teeth

Definitions

  • the present invention relates to a positive switching element for switching at least one gear ratio for a transmission of a vehicle according to the closer defined in the preamble of claim 1.
  • a tooth-on-tooth position can be resolved by applying a torque to the jaw switching element.
  • the applied torque serves to overcome the friction as a result of the frontal tooth-on-tooth contact in order to allow a relative movement and a subsequent sensing of the sliding sleeve.
  • This results in the problem that at too high torque unwanted high acceleration occurs and thus the meshing process can not be performed because of excessive differential speeds.
  • the present invention is based on the object to propose a form-fitting switching element, with the occurrence of a tooth-on-tooth position when meshing is reliably prevented.
  • a positive switching element for a transmission such as for a manual transmission and for a partially or fully automated transmission
  • the switching element comprises at least one axially displaceable on a shaft but rotatably connected sliding sleeve or the like, preferably from a non-switched neutral position or from another, for example switched position in at least one further switched position is axially displaceable, in which a loose wheel with the shaft rotatably connected to switch a translation stage via corresponding profile contours, teeth or the like.
  • the profile contours z. B. may be formed as a radial toothing, spur gear or the like.
  • the number of profile flanks of the sliding sleeve and the idler gear is different, and that at least one profile flank of the idler gear or the sliding sleeve, depending on which profile contour more teeth or profile flanks, in the axial direction is made resilient or resilient.
  • the smaller number of profile flanks can be completely achieved with a tooth-on-tooth position or with a profile on flank position due to the sprung profile flanks already be at least partially Schemespurt in the axial direction.
  • rotation takes place between the sliding sleeve and the idler gear in a tooth-on-gap position or profile flange-on-gap position, so that the tooth-on-tooth position is resolved without a unintentional upward rotation of one of the coupling halves of the switching element occurs.
  • the switching element designed, for example, as a claw switching element is then also converted into a form-fitting configuration.
  • a tooth-on-gap position can be ensured.
  • the proposed switching element regardless of whether a tooth-on-tooth position or a tooth-on-Lückegna is present positively connected. Immediately after the switching element has been moved to its switched position, load can be applied to and transferred from the switching element, so that the meshing operation can be completed quickly and completely avoided the disadvantages of a known jaw switching element in a tooth-on-tooth position become.
  • the respective non-sprung profile contour has a smaller number of profile flanks or teeth.
  • the smaller number of profile flanks or teeth and provided on the loose-wheel side coupling part the larger number of profile edges or teeth, wherein the loose-wheel-side profile edges spring-loaded or resilient in the axial direction or elastic are formed.
  • the tooth-on-tooth contact on the axial end side is released by the applied torque and the resultant relative movement if the applied torque is greater than the friction torque resulting from the end-side profile edge contact. Since the axially displaced or sprung profile flanks of the idler gear spring back to their original position, the relative movement between the idler gear and the sliding sleeve is limited until a tooth-on-gap position exists between the profile contour of the idler gear and the sliding sleeve. Thereafter, the switching element can be completely switched by the sliding sleeve is moved axially in its switched position for tracking the profile contours.
  • an elastic member made of metal, plastic or the like is used to allow axial compliance and guidance of the individual profile edges.
  • a spring plate with the profile flanks associated spring tabs or the like can be provided.
  • the resilient member is formed as a profile contour, for example, the idler gear, wherein the spring tabs are designed to be axially elastic and relatively stiff in the circumferential direction for torque transmission.
  • the suspension of the profile contour if on the one hand the required elasticity and on the other hand, the required rigidity are ensured with the selected design.
  • Figure 1 is a sectional view of a positive switching element
  • Figure 2 is a developed in the drawing plane schematic side view of a loose wheel and a sliding sleeve of the switching element in a neutral position
  • FIG. 2A shows a schematic side view of a loose wheel and a sliding sleeve of the switching element in an axial intermediate position, which is developed into the plane of the drawing;
  • FIG. 2B shows a schematic side view of a loose wheel and a sliding sleeve of the shifting element in the axial intermediate position with partly infeed profile contour unwound in the plane of the drawing;
  • Figure 3 is a plan view of a spring plate for alternative embodiment of a springing of the profile contour of the idler gear
  • FIG. 3A shows a side view of the spring plate according to FIG. 3.
  • a positive switching element for a transmission of a vehicle is shown by way of example, wherein the invention is not limited to a specific embodiment of the positive switching element.
  • the switching element can be used in a manual transmission or in a partially or fully automated transmission, in particular a dual-clutch transmission to realize the insertion of gears or the switching of Gangradpresen.
  • the switching element or the switching claw comprises at least one on a shaft 1 axially displaceable, but non-rotatably connected sliding sleeve 2, which is actuated by a Heidelbergaktorik not shown.
  • a shaft-fixed claw outer toothing 3 is provided, which is constantly engaged with a claw internal toothing of a sliding sleeve side coupling part formed profile contour 4 of the sliding sleeve 2, wherein the sliding sleeve 2 from a neutral position A or a non-switched position axially via an intermediate position C. in a switched position B can be moved to a To shift translation stage.
  • the sliding sleeve 2 in the neutral position A and in the switched position B side by side is schematically indicated, wherein the direction of movement from the neutral position A is displayed in the switched position B by an arrow.
  • a loose wheel 5 is shown, which is rotatably supported by a bearing 6 on the shaft 1.
  • the idler gear 5 is provided with an integrally formed coupling part, which extends axially in the direction of the sliding sleeve 2.
  • the coupling part has as a profile contour 7 of the idler gear 5 a freewheel-claw external teeth, which is selected such that in the switched position B, the profile contour 4 of the sliding sleeve 2 at least partially axially overlaps with the profile contour 7 of the idler gear 5, so that the sliding sleeve. 2 realized in the switched position B, a rotationally fixed connection between the idler gear 5 and the shaft 1.
  • profile contours 4 and 7 radial toothings are used by way of example, it also being possible to use spur gear toothings without further ado.
  • FIG. 1 also shows a section line l-1 to which the side views developed in the plane shown in FIGS. 2, 2A and 2B are related.
  • the switching element according to the invention is in the neutral position A and in Figures 2A and 2B, the axial intermediate position C is shown, in which the sliding sleeve 2 is axially between the neutral position A and the switched position B. From the intermediate position C, the sliding sleeve 2 can be moved by further axial displacement in the direction of the idler gear 5 in the switched position B.
  • the idler gear 5 of the switching element comprises a toothing or profile contour 7, the teeth or profile flanks 8 are each supported by an elastic member or spring element 9 in the axial direction sprung or sprung, so that upon contact with the teeth or profile flanks 10 of the toothing or the profile contour 4 of the sliding sleeve 2 an axial evasive movement is made possible by corresponding retraction of the profile flanks 8.
  • the Switching provided that for Einspur silk a different number of teeth or a different profile edge number in the profile contours 4 and 7 is present.
  • the profile contour 4 of the sliding sleeve-side coupling half has only half the number of profile flanks 10, so that each intermediate space 13 between profile flanks 10 of the sliding sleeve 2 is available for every two profile flanks 8 of the loose-wheel-side profile contour 7 stand.
  • a pre-alignment of the profile contours to be engaged with each other 4, 7 of the sliding sleeve 2 and the idler gear 5 are made possible.
  • FIGS. 2, 2A and 2B illustrate the sequence and mode of operation of the switching element according to the invention for dissolving a tooth-on-tooth position in three steps.
  • the switching element or the sliding sleeve 2 is in the neutral position A, which is shown in FIG.
  • the neutral position A with the shaft 1 rotatably connected profile contour 4 of the sliding sleeve 2 is not with the profile contour 7 of the idler gear 5 in contact.
  • the axial length of the profile flanks 10 of the sliding sleeve 2 is selected accordingly.
  • the sliding sleeve 2 from the neutral position A in the intermediate position C moves axially, as indicated in Figure 2A by an arrow 15, meet all the profile flanks 10 each in the illustrated tooth-on-tooth position associated profile edge 8 of the idler gear 5. It becomes due to the tooth-on-tooth position the sprung profile edge 8 of the idler gear 5 in the axial direction, ie pushed back in the direction of the idler gear 5, which is indicated by the arrows 16 in Figure 2A.
  • the axially resilient spring elements 9 of the profile flank 8 are dimensioned such that in the compressed state of the profile flanks 8, an axial overlap between the profile flanks 10 of the sliding sleeve 2 and the non-deflected profile flanks 8 of the idler gear 5 is given.
  • the Einspurvorgang can be terminated by the sliding sleeve 2 is moved axially from the intermediate position C in the switched position B.
  • the sliding sleeve 2 is moved axially from the intermediate position C in the switched position B.
  • FIG 3 an alternative embodiment for the springing of the profile edges 8 of the idler wheel 5 is shown, in which the springing is carried out by an approximately circular or annular formed spring plate 1 1.
  • the spring plate 1 1 has a plurality of distributed over the inner circumference arranged spring tabs 12.
  • the spring tabs 12 are at a predetermined angle to the ground plane of the spring plate 1 1 and therefore provide in the axial direction a predetermined suspension or elasticity, so that in the installed state, the associated profile edge 8 of the idler gear 5 a corresponding axial spring travel having.
  • the spring tabs 12 themselves serve as toothing or profile flanks 8, it is provided that the spring tabs 12 are designed to be yielding in the axial direction and stiff in the circumferential direction.
  • the transmission is first switched load-free and designed the previous gear and the synchronous speed produced on the switching element before the start of the opposition process.
  • Either the switching operation can be successfully completed by corresponding Einspuren or there is a tooth-on-tooth position.
  • the sprung profile flanks 8 now yield in the case of the switching element according to the invention, and a full axial overlap of the profile contours 4 and 7 is already produced, so that immediately thereafter the full load torque is achieved can be applied to the switching element according to the invention, whereby it comes to a defined rotation of the switching element in the tooth-on-Lückegna and the foundedrfitten profile edges 8 jump back to their original positions.
  • the full load of the proposed switching element can be transmitted even before the end of the switching process, whereby the switching operation is carried out in no time.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un élément de changement de vitesses fonctionnant par complémentarité de forme, servant à changer au moins un rapport de transmission pour une boîte de vitesses d'un véhicule, comportant au moins un manchon coulissant (2) pouvant coulisser axialement sur un arbre (1) mais solidaire en rotation de ce dernier, ledit manchon coulissant pouvant coulisser axialement à partir d'une position neutre (A), non engagée, dans au moins une position engagée (B), dans laquelle un pignon fou (5) est raccordé à l'arbre (1) de manière solidaire en rotation pour changer un rapport de transmission, par l'intermédiaire de contours profilés (4, 7) correspondants, le nombre de flancs profilés (10) du contour profilé (4) du manchon coulissant (2) et le nombre de flancs profilés (8) du contour profilé (7) du pignon fou (5) étant différents, le contour profilé (4, 7) du manchon coulissant (2) ou du pignon fou (5) présentant au moins un flanc profilé (8, 10) élastique dans le sens axial, de façon à permettre, en tant qu'aide à l'engrènement, un préalignement des contours profilés (4, 7), à engrener, du manchon coulissant (2) et du pignon fou (5).
PCT/EP2011/066182 2010-10-22 2011-09-19 Élément de changement de vitesses fonctionnant par complémentarité de forme WO2012052234A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010042798.5 2010-10-22
DE102010042798A DE102010042798A1 (de) 2010-10-22 2010-10-22 Formschlüssiges Schaltelement

Publications (1)

Publication Number Publication Date
WO2012052234A1 true WO2012052234A1 (fr) 2012-04-26

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PCT/EP2011/066182 WO2012052234A1 (fr) 2010-10-22 2011-09-19 Élément de changement de vitesses fonctionnant par complémentarité de forme

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DE (1) DE102010042798A1 (fr)
WO (1) WO2012052234A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016176529A (ja) * 2015-03-20 2016-10-06 ジヤトコ株式会社 ドグクラッチ

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH82113A (fr) * 1918-11-23 1920-01-16 Serge Kousminsky Dispositif d'embrayage
FR557499A (fr) * 1922-10-17 1923-08-09 Appareil d'embrayage à griffes
US1866270A (en) * 1930-10-30 1932-07-05 William H Schoonmaker Clutch mechanism
CH305510A (fr) * 1950-10-13 1955-02-28 English Electric Co Ltd Embrayage à cannelures.
AT220894B (de) * 1959-07-08 1962-04-25 Escher Wyss Ag Wellenkupplung
EP0090084A2 (fr) * 1982-03-25 1983-10-05 Nissan Motor Co., Ltd. Synchroniseur pour transmission à commande manuelle
JPH05106643A (ja) * 1991-08-21 1993-04-27 Toyota Motor Corp 同期噛合装置
DE4324815A1 (de) * 1993-07-23 1995-01-26 Zahnradfabrik Friedrichshafen Getriebeschaltung mit Synchronisiereinrichtung
DE10122450A1 (de) 2001-05-09 2002-11-14 Bayerische Motoren Werke Ag Schaltgetriebe für ein Motorrad
EP1998084A1 (fr) * 2007-05-22 2008-12-03 Peugeot Citroen Automobiles SA Boîte de vitesses à crabots auto-éjectants et procédé de changement de rapport associé

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE7910540L (sv) * 1979-12-20 1981-06-21 Volvo Ab Synkroniseringsanordning for fordonsvexellador
DE3322881C2 (de) * 1983-06-24 1985-05-15 Jahnel-Kestermann Getriebewerke Bochum GmbH, 4630 Bochum Zahnrad-Schaltvorrichtung
DE10113948A1 (de) * 2001-03-22 2002-09-26 Daimler Chrysler Ag Synchronisiereinrichtung

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH82113A (fr) * 1918-11-23 1920-01-16 Serge Kousminsky Dispositif d'embrayage
FR557499A (fr) * 1922-10-17 1923-08-09 Appareil d'embrayage à griffes
US1866270A (en) * 1930-10-30 1932-07-05 William H Schoonmaker Clutch mechanism
CH305510A (fr) * 1950-10-13 1955-02-28 English Electric Co Ltd Embrayage à cannelures.
AT220894B (de) * 1959-07-08 1962-04-25 Escher Wyss Ag Wellenkupplung
EP0090084A2 (fr) * 1982-03-25 1983-10-05 Nissan Motor Co., Ltd. Synchroniseur pour transmission à commande manuelle
JPH05106643A (ja) * 1991-08-21 1993-04-27 Toyota Motor Corp 同期噛合装置
DE4324815A1 (de) * 1993-07-23 1995-01-26 Zahnradfabrik Friedrichshafen Getriebeschaltung mit Synchronisiereinrichtung
DE10122450A1 (de) 2001-05-09 2002-11-14 Bayerische Motoren Werke Ag Schaltgetriebe für ein Motorrad
EP1998084A1 (fr) * 2007-05-22 2008-12-03 Peugeot Citroen Automobiles SA Boîte de vitesses à crabots auto-éjectants et procédé de changement de rapport associé

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016176529A (ja) * 2015-03-20 2016-10-06 ジヤトコ株式会社 ドグクラッチ

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