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EP1238212A2 - Differentiel - Google Patents

Differentiel

Info

Publication number
EP1238212A2
EP1238212A2 EP00987388A EP00987388A EP1238212A2 EP 1238212 A2 EP1238212 A2 EP 1238212A2 EP 00987388 A EP00987388 A EP 00987388A EP 00987388 A EP00987388 A EP 00987388A EP 1238212 A2 EP1238212 A2 EP 1238212A2
Authority
EP
European Patent Office
Prior art keywords
output shaft
torque
continuously variable
automatic transmission
pulley
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Withdrawn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
EP00987388A
Other languages
German (de)
English (en)
Inventor
Michael Prof. Dr. -Ing. Butsch
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.)
Individual
Original Assignee
Individual
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
Priority claimed from DE1999160656 external-priority patent/DE19960656A1/de
Priority claimed from DE2000101963 external-priority patent/DE10001963A1/de
Application filed by Individual filed Critical Individual
Publication of EP1238212A2 publication Critical patent/EP1238212A2/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Withdrawn legal-status Critical Current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
    • 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
    • F16H9/16—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 two pulleys, both built-up out of adjustable conical parts
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/0846—CVT using endless flexible members
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power-split transmissions with summing differentials, with the input of the CVT connected or connectable to the input shaft

Definitions

  • the present invention relates to a CVT belt transmission with power split on two belts, chains or belts with differential for merging the two power flows with the torques M ⁇ and M 2 , the differential consisting of a sun and two planetary gears meshing with it, which are in engagement with ring gears.
  • the differential can be switched via a switching device, so that the ratio of the torques Mi and M 2 can be the same or different in accordance with the translations provided by the differential.
  • a metal band is also required for small vehicles in order to be able to transmit sufficient torque. Since the coefficients of friction between the metal band and the adjusting discs are low, the discs have to be applied with high forces and therefore with high energy expenditure. Such CVT transmissions have poor efficiency.
  • a continuously variable automatic transmission is also described, for example, in EP 0 309 427 AI.
  • the disadvantage here is that a plurality of actuating cylinders have to be provided in a complex manner in order to continuously adjust the two belts.
  • a differential function for merging the two torques is not described.
  • the present invention has for its object to provide a differential of the type mentioned, which eliminates the disadvantages mentioned and with which very high torques can be achieved with a large spread in the belt area of the CVT continuously variable transmission.
  • the differential should also be one Have switching device that ensures different switching positions with short switching times.
  • the simple planetary gears have a common sun gear shaft.
  • At least one belt can be moved continuously with respect to the pulley by means of only one actuating element in order to produce a stepless torque transmission without interrupting the tractive force.
  • this solution offers adjustment options for adjacent belts on the individual pulleys, which can also be adjusted separately by means of a locking device. It should also be within the scope of the present invention that a plurality of pulleys and belts are provided in parallel on the input and / or output shaft, so that a further division of the line flow is still possible.
  • Another advantage is the use of dry-running belts, which results in very low losses when hydraulic actuators are not used.
  • hydraulics e.g. B. electromechanical linear actuators can be used.
  • a first input torque can be introduced into the differential via a drive sleeve.
  • This drive sleeve is with the
  • Planet carrier of the planets of the first planetary stage connected.
  • the second input moment is initiated via the common sun.
  • the two input torques are finally brought together in the ring gear of the first planetary stage, which is connected to the planetary gear carrier of the planets of the second planetary stage in a particularly space-saving manner.
  • the second stage planet carrier is also the output shaft.
  • the planets and the non-switched ring gear of the second planetary stage rotate freely.
  • the switching sleeve is switched and a first torque is introduced via the ring gear of the second planetary stage.
  • the second input torque introduced via the sun and the input torque via the shift sleeve are brought together in the planet gear carrier of the second planetary stage and passed on to the output.
  • the drive sleeve does not remain switched in this second switching position and the ring gear and the planets of the first planetary stage rotate freely.
  • the overall transmission ratio can be changed when the vehicle or the output shaft are stationary. This is an important function after braking hard.
  • Figure 1 is a plan view of a continuously variable automatic transmission according to the invention in a starting and reverse gear position with subsequent differential;
  • Figure 2 is a plan view of the continuously variable automatic transmission in a first driving range
  • Figure 3 is a plan view of a continuously variable automatic transmission according to Figures 1 and 2 in another driving range, in particular overdrive;
  • Figure 4 is a plan view of a further embodiment of a continuously variable automatic transmission with subsequent differential in a geared-neutral position when moving forward or backward;
  • FIG. 5 shows a top view of the continuously variable automatic transmission according to FIG. 4 in a main driving area
  • FIG. 6 is a top view of the continuously variable automatic transmission according to FIG. 4 in an overdrive.
  • a continuously variable automatic transmission Ri has at least one drive shaft 1 and one output shaft 2.
  • input shaft 1 and output shaft 2 are arranged parallel to one another.
  • two pulleys 3.1 and 3.2 each, the first two pulleys 3.1 arranged on the drive shaft 1 and the output shaft 2 being connected to each other via a belt 4 and the second two pulleys 3.2 being connected to one another by a belt 5.
  • the individual pulleys 3.1, 3.2 are preferably divided into individual pulley elements 6.1 to 6.4, the pulley 3.1 being formed from the pulley element 6.1 which is fixedly connected with respect to the drive shaft 1 and a further pulley element 6.2 which can be moved axially on the drive shaft 1.
  • the pulley 3.2 on the drive shaft 1 consists of the two disk elements 6.3, 6.4, both of which are axially movable on the drive shaft 1.
  • the disk elements 6.2 to 6.4 are arranged on the drive shaft 1 in a rotationally fixed but axially movable manner.
  • the pulley elements 6.2, 6.3 of the two adjacent pulleys 3.1, 3.2 are preferably firmly connected to one another, but can be moved axially relative to the drive shaft 1.
  • the outermost pulley element 6.4 is assigned an actuating device 7.1 which, by appropriate pressurization, pressurizes the individual pulley elements 6.2 to 6.4 against the pulley element 6.1 fixed on the drive shaft 1 in order to achieve different transmission ratios of the belts 4, 5 by correspondingly moving the different pulley elements 6.2 to 6.4 to generate according to the CVT principle or to the required
  • the pulleys 3.1, 3.2 of the output shaft 2 are also in disk elements in the manner described above
  • Axial bearing 8 is arranged, which different rotational speeds of the adjacent pulleys 3.1,
  • a further special feature of the present invention is that the individual pulley elements 6.3, 6.4, in particular the pulley 3.1 of the output shaft 2, are axially movable thereon and rotatable relative to the output shaft 2 and are connected in a rotationally rigid manner to a second drive shaft 9.
  • a torque Mi which is transmitted via the belt 4, is derived separately via an output sleeve 9 independently of a torque M 2 of the output shaft 2 and transmitted to the shift sleeve 12 of a shifting device 13.
  • the pulley 3.2 is non-rotatably on the output shaft 2, the pulley element 6.2 being axially movable but non-rotatably connected to the drive shaft 2.
  • An actuating device 7.2 is assigned to the disk element 6.4 of the output shaft 2 and applies pressure to the individual disk elements 6.4, 6.3 and 6.2 to generate the required belt pretension in order, if necessary, to carry out a basic setting, adjustment or fine adjustment of a translation, in particular of the belts 4, 5 or to generate the different transmission ratios of the belts 4, 5.
  • Another advantage of the present invention is that only one actuating device 7.1 or 7.2 has to be assigned to the drive shaft 1 and / or the output shaft 2, in particular to the disk element 6.1, in order to move the remaining disk elements 6.2 to 6.4 axially.
  • a torque M is introduced via the drive shaft 1 and distributed to the two pulleys 3.1, 3.2, with a distribution or power split of the individual torques M x , M 2 on the drive shaft 2, in particular on its pulleys 3.2, 3.1.
  • a switching device 13 is switched via the shift sleeve 12, the torque M i # being transferable to the differential 10 via a drive sleeve 14.
  • the torque M x is transmitted to a planet carrier 14.1 of corresponding planets 15 which are in engagement with a sun 16.
  • the torque M 2 of the output shaft 2 is transmitted directly to the sun 16 via a sun gear shaft 2.1 and is introduced into the sun 16.
  • the planet 15 sit in a ring gear 17, which transmits the torque M 2 to the planet carrier 14.1 of the output planet 18.
  • the output planets 18 are preferably also spaced apart from the sun 16 the planet 15.
  • the ring gear 17 is connected to the planet carrier 14.2 of the output planet 18.
  • the output planet 18 are in engagement with an output ring gear 19.
  • the output torque M ab is generated in the switching position shown by combining the moments Mi, M 2 in the ring gear 17.
  • the output ring gear 19 is connected to a switching sleeve 20 which leads into the area of the switching device 13.
  • a switching sleeve 20 which leads into the area of the switching device 13.
  • Output shaft 2 is transmitted directly to the drive sleeve 14, from there it is introduced into the planet 15 via the planetary gear carrier 14.1 and transmitted to the planet carrier 14.2 via their common ring gear 17.
  • the torque M 2 which is applied to the sun 16, is also introduced into the planet 15. In this switching position, the ratio of the torques Mi and M 2 is preferably approximately 3: 1.
  • both belts 4, 5 are approximately the same
  • the disk elements 6.2 to 6.4 can be moved, as shown in FIGS. 1, 2 and 3, so that different, infinitely variable gear ratios and gear ratios can be set.
  • FIG. 2 a further shift position is shown, in which the torque M x is transmitted directly to the shift sleeve 20 via the shift sleeve 12 and passed to the drive ring gear 19.
  • the torque M 2 of the output shaft 2 is also transmitted directly to the sun 16, as in FIG. 1.
  • the output planets 18 are also directly connected to the sun 16, so that, in corresponding size ratios, a torque M x approximately equal to the torque M 2 , which is transmitted directly to the sun 16, for a common output torque M ⁇ can be merged with the torque M 2 in the planet carrier 14.2.
  • a continuously variable automatic transmission R 2 is shown, in which, in particular, a locking device 11 is assigned to the drive shaft 1, which in particular ensures that the disk elements 6.2, 6.3 can be fixed in a releasable manner.
  • a selectable gear ratio of the pulley 3.1 and / or 3.2 can be set and defined.
  • the disk elements 6.1, 6.2 After, for example, the disk elements 6.1, 6.2 have been fixed against axial movement with respect to the drive shaft 1 in a desired ratio, the disk element 6.4 can be moved relative to the fixed disk element 6.3 by means of the actuating element 7.1. In this way, a second translation stage can be regulated and controlled continuously compared to the first defined translation stage.
  • the disk elements 6.2 and 6.3 are axially locked in a first position by the locking device 11.
  • the belt 4 remains in the position shown and the belt 5 is adjusted in the direction of the arrow with increasing driving speed from the illustrated starting position (geared-neutral).
  • the belts 4 and 5 have the same position and the locking device 11 gives the pulleys 6.2 and 6.3 axially free.
  • the belts are adjusted in parallel in the direction of the arrow with increasing speed.
  • FIG. 6 In order to further increase the spread of the transmission, there is the possibility shown in FIG. 6 of locking the disk elements 6.2 and 6.3 in a further position of the locking device 11.
  • the belt 4 remains in the position shown and the belt 5 is adjusted in the direction of the arrow with increasing driving speed ,

Landscapes

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

Abstract

L'invention concerne un différentiel destiné à combiner deux couples (M>1<, M>2<), composé de deux trains planétaires simples (P>1<, P>2<) comportant les éléments suivants ; planétaire (16), satellites (15, 18), et couronnes (17, 19). Selon l'invention, les trains planétaires simples (P>1<, P>2<) comportent un arbre de planétaire commun (2.1).
EP00987388A 1999-12-15 2000-12-12 Differentiel Withdrawn EP1238212A2 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19960656 1999-12-15
DE1999160656 DE19960656A1 (de) 1999-12-15 1999-12-15 Stufenloses Automatgetriebe
DE2000101963 DE10001963A1 (de) 2000-01-18 2000-01-18 Differential
DE10001963 2000-01-18
PCT/EP2000/012557 WO2001044685A2 (fr) 1999-12-15 2000-12-12 Differentiel

Publications (1)

Publication Number Publication Date
EP1238212A2 true EP1238212A2 (fr) 2002-09-11

Family

ID=26003910

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00987388A Withdrawn EP1238212A2 (fr) 1999-12-15 2000-12-12 Differentiel

Country Status (3)

Country Link
EP (1) EP1238212A2 (fr)
AU (1) AU2364901A (fr)
WO (1) WO2001044685A2 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3670594A (en) * 1970-01-26 1972-06-20 North American Rockwell Infinitely variable planetary transmission
CH658890A5 (de) * 1983-03-04 1986-12-15 Schweizerische Lokomotiv Antriebseinrichtung mit variabler gesamtuebersetzung.
IT1211317B (it) 1987-09-23 1989-10-12 Autec Ricerche E Applic Ind S Variatore continuo di velocita a pulegge espansibili
US5827146A (en) * 1996-01-18 1998-10-27 Kwang Yang Motor Co., Ltd. Dual transmission for motorcycles
DE59701263D1 (de) * 1996-04-30 2000-04-20 Steyr Daimler Puch Ag Verfahren zum steuern der kupplungen eines hydrostatisch-mechanischen leistungsverzweigungsgetriebes

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0144685A2 *

Also Published As

Publication number Publication date
WO2001044685A2 (fr) 2001-06-21
AU2364901A (en) 2001-06-25
WO2001044685A3 (fr) 2002-02-14

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