EP3265702A1 - Transmission à variation continue à commande améliorée - Google Patents

Transmission à variation continue à commande améliorée

Info

Publication number
EP3265702A1
EP3265702A1 EP16706192.8A EP16706192A EP3265702A1 EP 3265702 A1 EP3265702 A1 EP 3265702A1 EP 16706192 A EP16706192 A EP 16706192A EP 3265702 A1 EP3265702 A1 EP 3265702A1
Authority
EP
European Patent Office
Prior art keywords
conical disk
transmission according
axially movable
adjusting rod
crankshaft
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP16706192.8A
Other languages
German (de)
English (en)
Inventor
Falko Winter
Rudolf Eydam
Daniel Schwartz
Stefan Woerz
Carolin Breitinger
Mykhaylo Klymenko
Ianislav Krastev
Ingo Drewe
Rasmus Frei
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3265702A1 publication Critical patent/EP3265702A1/fr
Withdrawn legal-status Critical Current

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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/062—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions electric or electro-mechanical actuating means
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • F16H55/563—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable actuated by centrifugal masses
    • 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
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/14—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using only one pulley built-up out of adjustable conical parts

Definitions

  • the present invention relates to a CVT transmission (continuously variable transmission) with a significantly improved controllability and controllability.
  • CVT transmissions are different from the prior art
  • two-wheelers tricycles, so-called tuk-tuks, snowmobiles, quads or
  • centrifugal governors are often used to adjust a position of a belt on a cone pulley pair. Depending on the speed centrifugal weights of the shift
  • Centrifugal governors in the prior art usually not operated at an optimum point, so that fuel consumption and / or emissions of
  • centrifugally-controlled CVT transmissions Vehicle are deteriorated. It would therefore be desirable to exploit this potential in centrifugally-controlled CVT transmissions and to obtain a possibility of fuel reduction and emission reduction. Furthermore, centrifugally controlled CVT transmissions also have no optimal design with regard to vehicle dynamics. In particular, with an acceleration of
  • the CVT transmission according to the invention with the features of claim 1, on the other hand, has the advantage that an emission behavior and a
  • Fuel consumption of a vehicle can be significantly improved. Furthermore, also significantly better performance, especially in the
  • the CVT transmission can be operated in each case in an optimized position.
  • the CVT transmission in this case comprises a pair of conical disks with a stationary conical disk and an axially movable conical disk.
  • the invention is also a
  • Adjustment device for adjusting a position of the axially movable
  • the adjusting device comprises a spindle drive and an adjusting rod which is connected to the axially movable conical disk.
  • the spindle drive allows an axial adjustment of the adjusting rod.
  • a control unit is configured to operate the actuator to change a position of the axially movable cone pulley. As a result, a position of a belt of the cone pulley pair is changed, so that a ratio of the CVT transmission is changed.
  • an intervention by the control unit in a CVT transmission can be made possible in order to operate the CVT transmission at optimum operating points.
  • the adjusting device comprises an actuator which drives the spindle drive to exert tensile forces or compressive forces on the adjusting rod.
  • the adjusting rod is moved axially, so that a position of the axially movable conical disk, which is connected to the adjusting rod, is also changed.
  • the transmission according to the invention further comprises at least one centrifugal force element, which is arranged movably on the axially movable conical disk.
  • the support wall is preferably connected to a crankshaft.
  • the support wall comprises a tapered
  • the tapered contact surface of the support wall is preferably conical. As the speed increases, so do the increase on the or
  • Centrifugal force acting centrifugal force so that centrifugal elements are moved radially outward. Here they run on the rejuvenating
  • an output shaft of the actuator of the adjusting device is arranged parallel to a crankshaft. This allows a particularly compact design can be achieved.
  • the output shaft of the actuator is parallel to
  • a line arrangement of actuator and adjusting rod can be provided. Particularly preferred is on a line next to the adjusting rod and the output shaft of the actuator and the crankshaft, so that a particularly space-saving design is possible.
  • the adjusting rod is partially disposed in the crankshaft to allow a simple and compact structure, in particular in the axial direction.
  • the spindle drive comprises a sleeve nut, which with the
  • Adjusting rod is connected to allow rotation of a spindle of the spindle drive in an axial movement of the spindle sleeve and thereby also an axial movement of the adjusting rod.
  • the adjusting rod is preferably connected via a crossbar with the axially movable conical disk.
  • the control unit is preferably set up to control the setting device based on parameters of a drive motor. As parameters of the
  • Drive motor a speed of the drive motor and / or a torque of the drive motor and / or a temperature and / or air pressure are preferably used.
  • the parameters for controlling the adjusting device can be detected directly on the drive motor or on with the
  • the drive motor connected components.
  • the drive motor is preferably an internal combustion engine.
  • control unit is configured to control the setting device based on a choice of a driving mode of a driver.
  • a driving mode e.g. a sports mode or a fuel economy mode or the like.
  • predetermined transmission settings can be stored which, with appropriate selection of a driving mode, e.g. a sports mode or a fuel economy mode or the like., Are taken by the adjusting device.
  • crankshaft passes through the cone pulley pair.
  • the stationary conical disk is connected directly to the crankshaft, so that in the axial direction of the crankshaft only a minimal
  • control unit and the actuator are arranged in a housing of the CVT transmission. This allows a particularly compact design can be achieved.
  • the present invention relates to a vehicle comprising a
  • the vehicle is preferably a Small vehicle, especially a two-wheeler or a tricycle or a snowmobile or quad or a scooter or the like.
  • the actuator is arranged on a housing of the transmission.
  • an output shaft of the actuator protrudes into the housing interior and an intermediate gear for adjusting the support wall is preferably arranged in the housing interior.
  • Figure 1 is a schematic sectional view of a CVT transmission according to a preferred embodiment of the invention.
  • CVT transmission 1 that is, a continuously variable continuously variable transmission according to a first embodiment will be described in detail with reference to FIG.
  • the CVT transmission 1 comprises a
  • Conical disk pair 2 with a fixed conical disk 20 and an axially movable conical disk 21.
  • the fixed conical disk 20 is fixed on a crankshaft 1 1. More precisely, as can be seen from FIG. 1, the stationary conical disk 20 is arranged at the end of the crankshaft 11.
  • the crankshaft 1 as indicated in Figure 1, connected to a drive motor 10, in particular an internal combustion engine.
  • the CVT transmission 1 is a centrifugal force-controlled transmission and comprises a plurality of centrifugal force elements 3, which on the axially movable
  • Cone pulley 21 are arranged.
  • the centrifugal elements are balls.
  • the centrifugal elements are cylinders with a through hole.
  • the CVT transmission 1 comprises a non-axially movable support wall 4, which is arranged on the axially movable conical disk.
  • Supporting wall 4 rotates together with the crankshaft 1 1st
  • Radial position of the centrifugal elements 3 is an axial position in the axial direction X-
  • an adjusting device 5 is provided according to the invention, which is connected to a control unit 6.
  • the adjusting device 5 comprises an actuator 50, an output shaft 51 of the
  • the spindle drive 7 comprises a spindle 70 and a sleeve nut 71, which is arranged on the spindle 70 in the axial direction X-X movable.
  • the sleeve nut 71 is connected to an adjusting rod 8 via a bearing 81, so that during an axial movement of the sleeve nut 71, the adjusting rod 8 is moved axially in the axial direction X-X.
  • a cross bar 80 is connected to the adjusting rod 8, which is connected to the axially movable conical disk 21.
  • an axial movement of the adjusting rod 8 is transmitted via the cross bar 80 to the axially movable conical disk 21, so that this, as indicated in Figure 1 by the double arrow A, is movable in the axial direction.
  • the sleeve nut 71 is prevented from rotating together with the spindle 70 by means not shown.
  • the adjusting rod 8 is partially in the
  • crankshaft 1 1 arranged. This allows a particularly compact design can be achieved.
  • the crankshaft 1 1 in this case has a slot or a
  • the support disk 4 comprises a tapered contact surface 40, which is in contact with the centrifugal force elements 3.
  • the actuator 50 is preferably an electric motor.
  • the adjusting device 5 comprises a pneumatically operated adjustment drive or a hydraulically operated adjustment drive or an electromagnetic
  • a belt 1 for example a belt, is between the two
  • Cone disks 20, 21 arranged.
  • the belting means 1 2 is connected to an output element 13, preferably also a pair of conical disks.
  • the output element 1 3 can also be, for example, a directly driven wheel or the like.
  • a position of the movable conical disk 21 and thereby an axial distance between the two conical disks 20, 21 are set, which provides a desired ratio of the CVT transmission.
  • Actuator 50 is driven and the output shaft 51 of the actuator 50 drives the spindle 70 directly. It should be noted that the output shaft 51 may also be formed integrally with the spindle 7. By the rotation of the spindle 70 (arrow D in Figure 1), the sleeve nut 71 is moved in the axial direction X-X (double arrow C), depending on the direction of rotation of the spindle 70th Since the
  • Sleeve nut 71 is fixedly connected to the adjusting rod 8, the adjusting rod 8 also moves in the axial direction X-X (double arrow B). About the associated with the adjusting rod 8 crossbar 80, the axially movable conical disk 21 is then moved (double arrow A).
  • Umschlingungsmittels 1 2 between the two conical disks 20, 21 are changed, thus allowing a stepless transmission change.
  • a fine adjustment of a translation which is basically predetermined by the centrifugal force elements 3, can be realized.
  • an optimized gear ratio can be realized as a function of parameters, for example the rotational speed and / or the torque of the drive motor 10.
  • the transmission ratio can be selected in terms of consumption optimization or emission optimization or optimization of acceleration of the vehicle. It is also possible to select any desired combination of output variables to be optimized and, correspondingly, to set an optimum gear ratio of the CVT transmission for this purpose.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)

Abstract

Transmission à variation continue qui comprend une poulie en deux parties (2) comportant un flasque conique fixe (20) et un flasque conique axialement mobile (21), un dispositif de réglage (5) pour régler une position du flasque conique axialement mobile (21), le dispositif de réglage (5) comprenant un entraînement à broche (7) et une tige de réglage (8) qui est reliée au flasque conique axialement mobile (21), et une unité de commande (6) conçue pour actionner le dispositif de réglage (5) afin de modifier la position du flasque conique axialement mobile (21).
EP16706192.8A 2015-03-05 2016-02-25 Transmission à variation continue à commande améliorée Withdrawn EP3265702A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015203913.7A DE102015203913A1 (de) 2015-03-05 2015-03-05 CVT-Getriebe mit verbesserter Steuerbarkeit
PCT/EP2016/053906 WO2016139106A1 (fr) 2015-03-05 2016-02-25 Transmission à variation continue à commande améliorée

Publications (1)

Publication Number Publication Date
EP3265702A1 true EP3265702A1 (fr) 2018-01-10

Family

ID=55411392

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16706192.8A Withdrawn EP3265702A1 (fr) 2015-03-05 2016-02-25 Transmission à variation continue à commande améliorée

Country Status (6)

Country Link
EP (1) EP3265702A1 (fr)
JP (1) JP6472535B2 (fr)
KR (1) KR20170121197A (fr)
CN (1) CN107567555A (fr)
DE (1) DE102015203913A1 (fr)
WO (1) WO2016139106A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3906368B1 (fr) * 2018-12-31 2023-11-15 PIAGGIO & C. S.p.A. Transmission variable en continu, unité de propulsion et véhicule à moteur comprenant ladite transmission
DE202019004758U1 (de) * 2019-11-22 2019-12-04 Scc Fahrzeugtechnik Gmbh Stufenlos schaltbarer Riemenantrieb oder Antriebseinheit
CN112032266A (zh) * 2020-10-26 2020-12-04 山东交通职业学院 一种机械式增力传动装置

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1888853U (de) * 1963-09-26 1964-03-05 Heinkel Ag Ernst Vorschubvorrichtung, insbesondere fuer die steuerung von keilriemenwechselgetrieben.
NL1011732C2 (nl) * 1999-04-06 2000-10-09 Skf Engineering & Res Services Poelieset voor een continu variabele transmissie-eenheid.
ITPI20010041A1 (it) * 2001-05-30 2002-11-30 Doveri Marco Dispositivo meccanico per utilizzare come cambio sequenziale una trasmissione a variazione continua su un veicolo
US7771300B2 (en) * 2005-05-02 2010-08-10 Purdue Research Foundation Devices for electrically assisting and actuating continuously variable transmissions
JP4817228B2 (ja) * 2005-09-22 2011-11-16 本田技研工業株式会社 自動変速制御装置
DE102007043780A1 (de) * 2007-09-13 2009-03-19 Zf Friedrichshafen Ag Vorrichtung zur Variatorverstellung bei einem stufenlosen Umschlingungsgetriebe umfassend einen Variator
JP2014055649A (ja) * 2012-09-13 2014-03-27 Honda Motor Co Ltd Ｖベルト式無段変速機
EP2784357B1 (fr) * 2013-03-29 2016-02-17 Musashi Seimitsu Industry Co., Ltd. Transmission variable continue à courroie en V
JP6144517B2 (ja) * 2013-03-29 2017-06-07 武蔵精密工業株式会社 Ｖベルト式無段変速機
EP2853781B1 (fr) * 2013-09-30 2016-06-01 Honda Motor Co., Ltd. Transmission variable continue à courroie en V

Also Published As

Publication number Publication date
WO2016139106A1 (fr) 2016-09-09
JP6472535B2 (ja) 2019-02-20
JP2018507998A (ja) 2018-03-22
CN107567555A (zh) 2018-01-09
KR20170121197A (ko) 2017-11-01
DE102015203913A1 (de) 2016-09-08

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