WO2010043193A1 - Agencement d'arbre de commande pour une transmission d'un véhicule à moteur - Google Patents

Agencement d'arbre de commande pour une transmission d'un véhicule à moteur Download PDF

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Publication number
WO2010043193A1
WO2010043193A1 PCT/DE2009/001339 DE2009001339W WO2010043193A1 WO 2010043193 A1 WO2010043193 A1 WO 2010043193A1 DE 2009001339 W DE2009001339 W DE 2009001339W WO 2010043193 A1 WO2010043193 A1 WO 2010043193A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive shaft
bearing
exzenterbauteiles
eccentric component
shaft assembly
Prior art date
Application number
PCT/DE2009/001339
Other languages
German (de)
English (en)
Inventor
Oswald Friedmann
Original Assignee
Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Luk Lamellen Und Kupplungsbau Beteiligungs Kg filed Critical Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority to JP2011531343A priority Critical patent/JP5570512B2/ja
Priority to DE112009002339T priority patent/DE112009002339A5/de
Publication of WO2010043193A1 publication Critical patent/WO2010043193A1/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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
    • F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts

Definitions

  • the present invention relates to a drive shaft assembly for a transmission of a motor vehicle, in particular for a crank CVT
  • From DE 102 43 535 A1 discloses such a continuously variable transmission of a motor vehicle, which essentially comprises a drive shaft and an output shaft, which are aligned parallel to one another rotatably mounted in a transmission housing.
  • the drive shaft and the output shaft via an eccentric device provided on the drive shaft, a freewheel device arranged on the output shaft and a connecting rod device arranged between the eccentric device and the freewheel device are connected to one another.
  • the eccentric consists of a plurality of eccentric units, which are arranged axially next to one another on the drive shaft.
  • the freewheel device consists of several freewheel units, which are arranged axially adjacent to each other on the output shaft.
  • the connecting rod device comprises a plurality of connecting rod parts, which each connect an eccentric unit and a freewheel unit.
  • the mounted in the gear housing 10 drive shaft 1 according to Figure 1 integrally formed with her, with respect to its axis of rotation 3 eccentrically offset, crescent-shaped cam parts 4, on whose lateral surfaces 2 each an eccentric 5 is rotatably mounted.
  • On the Exzenterbauteil 5 one side of at least one Pleuelteiles 7 with a bearing 18 is rotatably mounted.
  • Each eccentric component 5 has a recess 15 (FIG. 3) for receiving the cam part 4, wherein an internal toothing 6 extends around the recess 15.
  • the internal toothing 6 is matched to the lateral surface 2 of the cam part 4 such that the eccentric component 5 is centered on the cam part 4 via the internal toothing 6.
  • the drive shaft 1, or the cam parts 4 thereof, have a recess 8 which extends in the direction of the axis of rotation 3 of the drive shaft 1 and in which an adjusting shaft 9 is rotatably arranged.
  • the adjusting shaft 9 has an external toothing 13 which engages in the internal toothing 6 of the eccentric components 5.
  • the adjusting shaft 9 is mounted in the recess 8 of the drive shaft 1 via the sections of the outer toothing 13 which form the tip circle of the external toothing 13.
  • the cam parts 4 are so crescent-shaped formed so that their recesses 8 are open over a certain angular range, so that in these open angle regions, the outer teeth 13 of the adjusting 9 protrudes radially relative to the outer surface 2 of the cam parts 4, wherein engagement in the internal teeth 6 of the Exzenterbaumaschines 5 is made possible.
  • the cam parts 4 have with respect to their cylindrical surface 2 a central axis 16 ( Figure 3), which is arranged eccentrically by a certain distance from the axis of rotation 3 of the drive shaft 1.
  • the eccentric 5 have with respect to their cylindrical surfaces 12 a central axis 4, which is offset relative to the said central axis 16 of the cam parts 4 eccentrically by a distance so that the eccentricity of the central axis 14 of the Exzenterbaumaschine 5 relative to the axis of rotation 3 of the drive shaft 1, for example twice is as large as the eccentricity of the central axis 16 of the cam parts 4 with respect to the axis of rotation.
  • the eccentric 5 Due to the rotation of the adjusting shaft 9 in the recess 8 of the drive shaft 1, the eccentric 5 is rotated about the central axis 16 of the corresponding cam member 4. In this case, the central axis 14 of the Exzenterbaumaschines 5 moves about the central axis 16 of the cam member 4, wherein the extent of the eccentricity of the Exzenterbaumaschines 5 with respect to the axis of rotation 3 of the drive shaft 1 is changed.
  • the adjusting shaft 9 is rotated by an adjusting drive in the form of an electric motor 17, wherein between the electric motor 17 and the adjusting shaft 9, a transmission gear 19 is connected.
  • a problem of such a drive shaft arrangement is that the result of the weight of the Exzenterbaumaschines 5 during rotation of the drive shaft 1 is an outwardly acting torque that must be supported by the electric motor 17 with the associated transmission gear 19. For a constant travel of the motor vehicle or for slow adjustments, therefore, the electric motor 17 must be energized. The torque resulting from the Pleuelzugkraft is too small in many operating points to compensate for the torque from the centrifugal force.
  • the object of the present invention is therefore to design a drive shaft arrangement for a transmission, in particular for a crank CVT, so that the torques resulting from the centrifugal force and from the connecting rod tensile force on the eccentric component are compensated for in the main drive regions of the motor vehicle.
  • This object is achieved by a drive shaft assembly for a transmission of a motor vehicle, in particular for a crank CVT, with a drive shaft mounted in a transmission housing, wherein on the drive shaft at least one offset relative to its axis of rotation cam member is rotatably disposed on the lateral surface of an eccentric rotatable is.
  • On the lateral surface of the Exzenterbaumaschineerss one end of a Pleuelteiles is rotatably mounted with a bearing.
  • the eccentricity of the Exzenterbaumaschines is adjustable by an adjustment.
  • the eccentric component has a balancing mass range which at least partially compensates for torques which are due to the centrifugal force produced during the rotation of the eccentric component and / or to the connecting rod tensile force caused on the connecting rod part.
  • the essential advantage of the drive shaft arrangement according to the invention is that the provision of an additional or compensating mass on the eccentric component of a crank CVT ensures that the torques attributable to the centrifugal force and the connecting rod tensile force are compensated in the main driving ranges of a motor vehicle.
  • the eccentric component as a particularly advantageous adjusting mechanism with respect to its central axis eccentrically offset recess in which the cam member is rotatably mounted, wherein the drive shaft has an axially extending recess in which an adjusting shaft rotatably arranged with an external toothing is.
  • an internal toothing is arranged on the inner circumference of the eccentric recess of the eccentric component.
  • the cam member is formed so crescent-shaped that the recess is open in its area over a certain angular range, so engages in this angular range, the outer toothing of the adjusting shaft in the internal toothing of the eccentric component.
  • the internal toothing of the recess of the eccentric component can be matched to the lateral surface of the cam member in such a way that the eccentric component is centered on the cam portion via the head circle of its internal toothing.
  • the outer toothing of the adjusting shaft can be dimensioned such that the adjusting shaft is rotatably supported via the head circle of its outer toothing in the recess of the drive shaft.
  • the balancing mass range in such a way on Exzenterbautei! is arranged so that it is opposite to the center of gravity of the Exzenterbauers with respect to the central axis thereof.
  • the balancing mass range is the center of gravity of the Exzenterbauers with respect to the center axis of the same diametrically opposite.
  • the balancing mass range is at least partially radially outside the inner diameter of the bearing for the connecting rod part, in particular axially seen on one side of the bearing.
  • the balancing mass region may have a radially extending on one side of the bearing mass range, to which an axially extending holding portion may be integrally formed, which is held between the outer surface of the Exzenterbaumaschines and the inner ring of the bearing.
  • the symmetrically arranged balancing mass range axially seen on both sides of the bearing, the balancing mass range having a first radially on one side of the bearing extending first mass range and at the first mass range axially opposite side of the bearing a radially extending second mass range can.
  • an axially extending first holding region and to the second mass region a second axially extending holding region may be integrally formed on the first mass region, the first holding region and the second holding region being held between the lateral surface of the eccentric component and the inner ring of the bearing.
  • the eccentric component may have at least one material recess on the side opposite the balancing mass region with respect to its central axis. Expediently, a material recess is provided axially on each side of the eccentric component.
  • Figure 1 in section a known drive shaft assembly of a crank CVT's;
  • Figure 2 is an illustration for explaining the principle of the invention;
  • FIG. 3 partly in section a side view of a drive shaft arrangement according to the invention.
  • FIG. 4 shows a longitudinal section through the drive shaft arrangement according to the invention of FIG. 3 along the line IV-IV.
  • an adjusting shaft 9 is arranged in a recess 8 of the cam part 4 and the drive shaft (not shown).
  • the adjusting shaft 9 has an axial external toothing 13 and is rotatably supported in the recess 8 via the head circle of this external toothing 13.
  • the eccentric component 5 has an eccentric recess 15, on whose inner circumference an internal toothing 6 is located.
  • This internal toothing 6 is matched to the lateral surface 2 of the cam part 4 such that the eccentric component 5 is centered on the cam part 4 via the internal toothing 6.
  • the cam areas 4 are designed in a crescent-shaped manner so that their recesses 8 are open over a certain angular range, so that in these open angle regions, the external teeth 13 of the adjusting shaft 9 project radially relative to the outer circumferential surface 2 of the cam parts 4, wherein a Intervention in the internal toothing 6 of the Exzenterbaumaschinemaschines 5 is made possible.
  • the eccentric component! 5 may have in a conventional manner for weight reduction two preferably axially opposite material recesses 20.
  • the balancing mass region 21 is the center of gravity of the Exzenterbaumaschines 5 with respect to the central axis 16 of the same preferably 180 ° opposite. It is also conceivable to place the mass on very slow motors on the same side as the center of gravity in order to increase the centrifugal force.
  • the size of the balancing mass range 21 is according to the invention laid so that in the main driving ranges of the motor vehicle caused by the centrifugal force and the Pleuelzugkraft torques D1, D2 just compensate. As a result, it is advantageously achieved that the holding torque on the adjusting shaft 9 drops to a minimum. In addition, a good emergency driving behavior of the transmission is achieved because automatically with increasing engine speed in the direction of overdrive and with decreasing engine speed or with increasing wheel torque in the direction of translation infinitely adjusted.
  • the balancing mass region 21 is advantageously divided on both sides of the bearing 18 of the connecting rod 7. Accordingly, a first mass region 22 extends radially outward on one side of the bearing 18 and a second mass region 23 on the opposite side of the bearing 18 extends radially outward.
  • an axially extending holding portion 24 is preferably integrally formed on the side facing the adjusting shaft 9, which extends up to half of the axial extent of the bearing 18.
  • an axially extending holding region 25 is integrally formed on the second mass region 23 on the side facing the adjusting shaft 9, which extends up to half of the axial extent of the bearing 18 in the direction of the holding region 24, preferably up to the same.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un agencement d'arbre de commande pour la transmission d'un véhicule à moteur, en particulier pour une transmission à variation continue à bielle, qui comprend un arbre de commande monté dans un carter de boîte de vitesses. Au moins une came (4), décalée par rapport à l'axe de rotation de l'arbre, est montée fixe en rotation sur l'arbre de commande, et un élément excentrique (5) est monté rotatif sur la surface périphérique de la came. L'extrémité d'une bielle est montée rotative, au moyen d'un roulement, sur la surface périphérique de l'élément excentrique. L'excentricité de l'élément excentrique est réglable au moyen d'un mécanisme de réglage. L'élément excentrique présente une région à masse d'équilibrage, qui équilibre au moins partiellement les couples résultant de la force centrifuge produite par la rotation de l'élément excentrique et/ou de la force de traction s'exerçant sur la bielle.
PCT/DE2009/001339 2008-10-16 2009-09-24 Agencement d'arbre de commande pour une transmission d'un véhicule à moteur WO2010043193A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2011531343A JP5570512B2 (ja) 2008-10-16 2009-09-24 自動車の伝動装置のための駆動軸アッセンブリ
DE112009002339T DE112009002339A5 (de) 2008-10-16 2009-09-24 Antriebswellenanordnung für ein Getriebe eines Kraftfahrzeuges

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008051966.9 2008-10-16
DE102008051966 2008-10-16

Publications (1)

Publication Number Publication Date
WO2010043193A1 true WO2010043193A1 (fr) 2010-04-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2009/001339 WO2010043193A1 (fr) 2008-10-16 2009-09-24 Agencement d'arbre de commande pour une transmission d'un véhicule à moteur

Country Status (3)

Country Link
JP (1) JP5570512B2 (fr)
DE (2) DE112009002339A5 (fr)
WO (1) WO2010043193A1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012251612A (ja) * 2011-06-03 2012-12-20 Honda Motor Co Ltd 無段変速機の潤滑油供給構造
JP2012251611A (ja) * 2011-06-03 2012-12-20 Honda Motor Co Ltd 無段変速機の潤滑油供給構造
WO2013001859A1 (fr) * 2011-06-30 2013-01-03 本田技研工業株式会社 Transmission à variation continue du type liaison à quatre joints
JP2013024382A (ja) * 2011-07-25 2013-02-04 Honda Motor Co Ltd 無段変速機構及び自動車用駆動システム
JP2013036536A (ja) * 2011-08-08 2013-02-21 Honda Motor Co Ltd 四節リンク機構型無段変速機
JP2013036535A (ja) * 2011-08-08 2013-02-21 Honda Motor Co Ltd 四節リンク機構型無段変速機
JP2013087932A (ja) * 2011-10-21 2013-05-13 Honda Motor Co Ltd 無段変速機
WO2014084067A1 (fr) * 2012-11-29 2014-06-05 本田技研工業株式会社 Dispositif de transmission de puissance de véhicule
JPWO2013008624A1 (ja) * 2011-07-13 2015-02-23 本田技研工業株式会社 無段変速機
US20160032881A1 (en) * 2013-04-01 2016-02-04 Honda Motor Co., Ltd. Vehicular power transmission device

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011087631B4 (de) 2010-12-23 2016-07-21 Schaeffler Technologies AG & Co. KG Geräuschreduzierter Drehschwingungsdämpfer
WO2014038296A1 (fr) * 2012-09-04 2014-03-13 本田技研工業株式会社 Transmission à variation continue
US9382985B2 (en) 2012-09-13 2016-07-05 Honda Motor Co., Ltd. Vehicle power transmission device
JP5844714B2 (ja) * 2012-10-30 2016-01-20 本田技研工業株式会社 四節リンク機構型無段変速機の制御装置
DE112013005806T5 (de) * 2012-12-04 2015-08-20 Honda Motor Co., Ltd. Fahrzeugleistungsübertragungsvorrichtung
BR112015012217A2 (pt) * 2012-12-05 2017-07-11 Honda Motor Co Ltd dispositivo de transmissão de energia de veículo
DE112013005797T5 (de) * 2012-12-05 2015-08-20 Honda Motor Co., Ltd. Fahrzeugleistungsübertragungsvorrichtung
WO2014103636A1 (fr) * 2012-12-27 2014-07-03 本田技研工業株式会社 Transmission à variation continue
WO2014162816A1 (fr) * 2013-04-01 2014-10-09 本田技研工業株式会社 Dispositif de transmission de puissance pour véhicules
JP6100609B2 (ja) * 2013-05-24 2017-03-22 本田技研工業株式会社 無段変速機
JP6120326B2 (ja) * 2013-08-19 2017-04-26 本田技研工業株式会社 無段変速機
JP6067593B2 (ja) * 2014-01-08 2017-01-25 本田技研工業株式会社 無段変速機
JP6847772B2 (ja) * 2017-06-15 2021-03-24 本田技研工業株式会社 車両用動力伝達装置
JP6817900B2 (ja) * 2017-06-15 2021-01-20 本田技研工業株式会社 車両用動力伝達装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4020310A1 (de) * 1989-07-07 1991-01-17 Kaiser Kg Otto Exzenterpresse mit hubverstellung und massenausgleich
US5189927A (en) * 1988-11-08 1993-03-02 Egan Michael J Variable ratio drive transmission
DE10243535A1 (de) * 2001-09-26 2003-04-24 Luk Lamellen & Kupplungsbau Getriebe
DE102005048611A1 (de) * 2004-10-22 2006-04-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Antriebsanordnung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5189927A (en) * 1988-11-08 1993-03-02 Egan Michael J Variable ratio drive transmission
DE4020310A1 (de) * 1989-07-07 1991-01-17 Kaiser Kg Otto Exzenterpresse mit hubverstellung und massenausgleich
DE10243535A1 (de) * 2001-09-26 2003-04-24 Luk Lamellen & Kupplungsbau Getriebe
DE102005048611A1 (de) * 2004-10-22 2006-04-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Antriebsanordnung

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012251612A (ja) * 2011-06-03 2012-12-20 Honda Motor Co Ltd 無段変速機の潤滑油供給構造
JP2012251611A (ja) * 2011-06-03 2012-12-20 Honda Motor Co Ltd 無段変速機の潤滑油供給構造
WO2013001859A1 (fr) * 2011-06-30 2013-01-03 本田技研工業株式会社 Transmission à variation continue du type liaison à quatre joints
JP5552572B2 (ja) * 2011-06-30 2014-07-16 本田技研工業株式会社 四節リンク型無段変速機
US9121483B2 (en) 2011-06-30 2015-09-01 Honda Motor Co., Ltd. Four-joint link type continuously variable transmission
JPWO2013008624A1 (ja) * 2011-07-13 2015-02-23 本田技研工業株式会社 無段変速機
JP2013024382A (ja) * 2011-07-25 2013-02-04 Honda Motor Co Ltd 無段変速機構及び自動車用駆動システム
JP2013036536A (ja) * 2011-08-08 2013-02-21 Honda Motor Co Ltd 四節リンク機構型無段変速機
JP2013036535A (ja) * 2011-08-08 2013-02-21 Honda Motor Co Ltd 四節リンク機構型無段変速機
JP2013087932A (ja) * 2011-10-21 2013-05-13 Honda Motor Co Ltd 無段変速機
WO2014084067A1 (fr) * 2012-11-29 2014-06-05 本田技研工業株式会社 Dispositif de transmission de puissance de véhicule
US20160032881A1 (en) * 2013-04-01 2016-02-04 Honda Motor Co., Ltd. Vehicular power transmission device

Also Published As

Publication number Publication date
JP2012506003A (ja) 2012-03-08
JP5570512B2 (ja) 2014-08-13
DE102009042834A1 (de) 2010-04-22
DE112009002339A5 (de) 2011-06-30

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