WO1998019080A1 - Engrenage a friction - Google Patents

Engrenage a friction Download PDF

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Publication number
WO1998019080A1
WO1998019080A1 PCT/EP1997/005938 EP9705938W WO9819080A1 WO 1998019080 A1 WO1998019080 A1 WO 1998019080A1 EP 9705938 W EP9705938 W EP 9705938W WO 9819080 A1 WO9819080 A1 WO 9819080A1
Authority
WO
WIPO (PCT)
Prior art keywords
rolling elements
drive
driven
cage
friction gear
Prior art date
Application number
PCT/EP1997/005938
Other languages
German (de)
English (en)
Inventor
Herbert Bolter
Original Assignee
Herbert Bolter
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 Herbert Bolter filed Critical Herbert Bolter
Priority to AU69097/98A priority Critical patent/AU6909798A/en
Priority to EP97948819A priority patent/EP1025374A1/fr
Priority to CA002311789A priority patent/CA2311789A1/fr
Publication of WO1998019080A1 publication Critical patent/WO1998019080A1/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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/40—Gearings providing a continuous range of gear ratios in which two members co-operative by means of balls, or rollers of uniform effective diameter, not mounted on shafts

Definitions

  • the invention relates to a friction wheel transmission according to the preamble of claim 1 and claim 5.
  • Such friction gear are known for example from EP-A1-021 126, DE-PS 23 61 993 or from "Dubbel, Taschenbuch für den Maschinenbau", 16th edition 1987, G 104-108.
  • a stepless adjustment of the transmission ratio is made possible in these gears by shifting the radial position of the rolling element.
  • WO 92/08912 and WO 83/02986 describe friction wheel transmissions with toroidal or curved friction surfaces.
  • the gear unit disclosed in WO 92/08912 provides disc-shaped rolling elements, the adjustability of which depends on the particular operating state. Unrestricted adjustability is not possible without appropriate wear.
  • the gear unit disclosed in WO 83/02986 shows a double ring of spherical rolling elements, one ring of rolling elements each transmitting torque, the double ring as such being essentially intended to absorb supporting forces.
  • the invention has set itself the task of providing friction wheel transmissions which remedy the disadvantage which has become known from the prior art, can furthermore be switched without restrictions, for example by generating a torque-dependent preload, and in which occurring
  • Axial tensions are dissipated within the shafts, the slidability under load runs with a corresponding number of balls or geometry of the running surfaces as a pure rolling motion, with a corresponding number of balls also independent of the respective operating state and, if necessary - depending on the position of the rolling elements - also for setting the preload automatically.
  • Another advantageous property of the friction wheel transmission according to the invention is the possible duplication of the torques.
  • 2a shows the schematic representation of the arrangement of several intermediate members, each with three rolling elements in a friction gear with toroidal running surfaces;
  • 3a, 3b, 3c show schematic representations of the adjustability of three drive elements with different cages arranged in series in the drive between two friction surfaces;
  • 4 shows a schematic top view of a further exemplary embodiment with mutually parallel friction surfaces;
  • 5 shows a side view of a friction gear according to FIG. 4;
  • FIG. 6 shows a schematic side view of a further exemplary embodiment with a plurality of drive disks and driven disks arranged between them;
  • FIG. 8c shows a detail B from FIG. 8a.
  • a driven disk 2a is rotatably mounted on a shaft 5 between two drive disks 1a and 1b.
  • the curved, here toroidal, drive surfaces 70a and 70b of the disks 1a and 1b and the likewise curved, also toroidal, driven surfaces 71a and 71b of the disk 2a there is a non-positive connection between which the first and second rolling elements 7, 8 in the form of balls are arranged in series with one another in terms of drive, which convey the rotational movement of the disks 1a and 1b to the disk 2a via three friction points 9, 10, 11 in a frictional manner.
  • the rolling elements 7, 8 are arranged in a common cage 15 (indicated by dashed lines), which can also be designed as a ball-bearing plate.
  • the direction of rotation of the disks 1a and 1b and 2a is in each case the same direction; when the radial position of the rolling elements 7, 8 is pivoted, the gear ratio is changed.
  • the preload can be generated from the inside via the two rolling elements, in contrast to the situation as in WO
  • the arrangement multiplies the torque transmission via the multiple intermediate links and the parallel arrangement of the friction surface situation.
  • 2a and 2b show friction wheel transmissions in which a plurality of intermediate elements, each with three rolling elements 17, 18, 19 arranged in series in the drive, are provided between the toroidal running surfaces.
  • the rolling elements can either be in a common cage 15c (FIG. 3a) or also in several cages, for example in a cage 15d (FIG. 3a) comprising two rolling elements, or also be arranged in a cage 15e (FIG.
  • FIGS. 3a to 3c show - for the sake of clarity - the treads, the drive surface and the driven surface 70c, 71c, on shafts 1c 1 , 2c '; the situation is basically analogous to that with a concavely curved tread. The situation is also comparable for flat treads (stiched).
  • the - always rolling - movement of the rolling elements depending on the arrangement in the cages according to FIGS. 3a to 3c opens up the possibility of generating the preload by pivoting two rolling elements 18d, 19d with their cage 15d (FIG. 3a), the different Exercise or pivoting a rolling element 18e (Fig.3b) and the joint pivoting of all three rolling elements 17c, 18c, 19c in the common cage 15c (Fig.3c).
  • the pivoting and / or The displacement of the cage to generate the preload depends on the friction cones and the force relationships, as well as the type of cage holder. In principle, the pivoting or displacement is possible with any number of rolling elements.
  • FIG.2b analogous to Fig. 1 - a duplication of an arrangement according to Fig.2a is shown.
  • a driven pulley 2d is rotatably mounted on a shaft 5 between two drive pulleys 1c, 1d.
  • Drive disks 1c, 1d and driven disk 2d have curved running surfaces 70c, 70d, 71d, 71d ', each forming a toroid in this way.
  • the rolling elements are rotated radially, for example into the position 17 ', 18', 19 'indicated by the broken line, and they roll on the torus surface, so that the adjustment is possible even when the load is present without increased, friction-related wear.
  • the linear arrangement of the rolling elements shown in FIGS. 2a and 2b is purely exemplary, the rolling elements can also be offset from one another or arranged in an "arc" shape.
  • the necessary pretension can - in a known manner - also be generated by applying pressure to the two outer disks, here 1c and 1d, for example via spring force, hydraulically or else in the manner of the device described in CH-A-157736.
  • the pressure to be applied is dependent on the radial position of the rolling elements, since only in a position parallel to the shaft axis - corresponding to a transmission ratio of 1: 1 - does the contact pressure correspond to this pressure applied from the outside.
  • the preload can also be preset when installing the washers.
  • a drive pulley 1f and an attached driven disc 2f parallel to each other, but with offset axes 3, 4 arranged on rotatably mounted shafts 5f, 6f.
  • two spherical rolling elements 7f, 8f are arranged in series.
  • the rotational movement of the drive pulley 1f is transmitted to the driven pulley 2f via the three friction points 9, 10, 11.
  • the rolling elements 7f, 8f are arranged in a common cage 15f, which can also be designed as a ball-bearing plate.
  • the connecting lines 60, 61, 62, 63 which connect the friction points 9, 10, 11, of the respective rolling element 7f, 8f with the center 13, 14 of the rolling element 7f, 8f, each include angles 12, 17 which differ from 180 °.
  • an imaginary connecting line between the friction points 9, 10, 11 of a rolling element 7f, 8f does not lead through the center point 13, 14 of this rolling element 7f, 8f.
  • the sum of the diameters of the two rolling elements 7f, 8f is therefore greater than the distance between the disks 1f, 2f.
  • the cage 15f is pivotally mounted about an axis 19 which is perpendicular to the connecting lines 60, 61, 62, 63 between the friction points 9, 10, 11 of the rolling elements 7f, 8f and the center points 13, 14 of the rolling elements 7f, 8f.
  • the transmission ratio is changed by adjusting the radial position of the rolling elements, for which purpose the cage 15f is displaced along the axis 19.
  • the rolling elements 7f, 8f can roll on each other and on the running surfaces of the disks 1f, 2f, so that an adjustment of the transmission ratio without having to overcome high friction is possible even when the load is applied and the disks are at a standstill.
  • the cage is mounted so as to be pivotable about a swivel axis, which is perpendicular to the connecting lines between the friction points of the rolling elements and the center points of the rolling elements.
  • the necessary contact pressures are generated by pivoting the cage about its pivot axis, which takes place automatically when the gear is driven.
  • first driven disks 25 and 25 ′ protrude into the space 23 enclosed by the first and second drive disks 20, 21 and m the space 24 between the drive disks 21, 22 further driven disks 26, 26 ′.
  • Two of these driven disks each 25, 25 'and 26, 26' are arranged on a common shaft 6, 6 '.
  • First and second rolling elements 7g, 8g are provided between the drive disks 20, 21, 22 and the driven disks 25, 25 ', 26 and 26', which, analogously to the exemplary embodiment shown in FIGS. 4 and 5, are each not shown here Cages are arranged.
  • an angular gear is created by transmitting the movement from a drive pulley 1 ⁇ to a driven shaft 42, which is rotatably supported about its axis 44, via the rolling elements 7 ⁇ , 8 ⁇ .
  • Translation and direction of rotation of the shaft 42 can be changed by the displacement of the cage 7 ⁇ , 8 ⁇ holding cage (not shown) m arrow direction 45.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

La présente invention concerne un engrenage à friction comprenant au moins une surface d'entraînement, (70c, 70d) au moins une surface entraînée (71d, 71d') et, installée entre les deux, au moins un membre intermédiaire se présentant sous la forme d'un ensemble de corps de roulement (17, 18, 19) sphériques. La surface d'entraînement (70c, 70d) et la surface entraînée (71d, 71d') présentent un bombement toroïdal. Au moins deux, de préférence trois, corps de roulement (17, 18, 19) sont disposés en série aux fins de l'entraînement. Dans une variante, les corps de roulement sont montés coulissants ou pivotants, d'où la possibilité de régler les rapports et la tension initiale.
PCT/EP1997/005938 1996-10-28 1997-10-28 Engrenage a friction WO1998019080A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU69097/98A AU6909798A (en) 1996-10-28 1997-10-28 Friction gear engrenage a friction
EP97948819A EP1025374A1 (fr) 1996-10-28 1997-10-28 Engrenage a friction
CA002311789A CA2311789A1 (fr) 1997-10-28 1997-10-28 Engrenage a friction

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA1878/96-1 1996-10-28
AT187896 1996-10-28

Publications (1)

Publication Number Publication Date
WO1998019080A1 true WO1998019080A1 (fr) 1998-05-07

Family

ID=3522975

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1997/005938 WO1998019080A1 (fr) 1996-10-28 1997-10-28 Engrenage a friction

Country Status (3)

Country Link
EP (1) EP1025374A1 (fr)
AU (1) AU6909798A (fr)
WO (1) WO1998019080A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19907637C1 (de) * 1999-02-23 2001-01-11 Clark Equipment Belgium Nv Planetengetriebe
EP1132650A1 (fr) 2000-03-08 2001-09-12 Herbert Bolter Transmission à roues de friction
WO2002016803A1 (fr) * 2000-08-19 2002-02-28 Bernard Maitland Hartley Systeme de transmission variable

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB115345A (en) * 1917-07-30 1918-05-09 Hannibal Choate Ford An Improved Variable Speed Gear.
FR30467E (fr) * 1925-01-17 1926-07-17 Système de transmission de mouvement pouvant constituer réducteur ou multiplicateur de vitesse
CH157736A (de) 1931-06-05 1932-10-15 Arter Jakob Vorrichtung zum selbsttätigen Aneinanderpressen der im Reibungseingriff stehenden Teile von Reibrädergetrieben.
FR1116854A (fr) * 1953-12-04 1956-05-14 Hollandse Signaalapparaten Bv Perfectionnement apporté à un mécanisme d'entraînement par frottement
GB788563A (en) * 1955-07-12 1958-01-02 Harrison Reproduction Equipmen Improvements in or relating to variable speed driving mechanisms
DE2361993B1 (de) * 1973-12-13 1975-04-10 P.I.V. Antrieb Werner Reimers Kg, 6380 Bad Homburg Stufenlos einstellbares Reibscheibengetriebe
EP0021126A1 (fr) 1979-06-07 1981-01-07 Bernd Grewe Dispositif de production continue de la pression de contact nécessaire pour un variateur continu de la vitesse à friction
WO1983002986A1 (fr) 1982-02-18 1983-09-01 Kugle, Jens Mecanisme de transmission
WO1992008912A1 (fr) 1990-11-16 1992-05-29 Torotark (Development) Limited Transmission du type a roulement-traction et a voie toroidale

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB115345A (en) * 1917-07-30 1918-05-09 Hannibal Choate Ford An Improved Variable Speed Gear.
FR30467E (fr) * 1925-01-17 1926-07-17 Système de transmission de mouvement pouvant constituer réducteur ou multiplicateur de vitesse
CH157736A (de) 1931-06-05 1932-10-15 Arter Jakob Vorrichtung zum selbsttätigen Aneinanderpressen der im Reibungseingriff stehenden Teile von Reibrädergetrieben.
FR1116854A (fr) * 1953-12-04 1956-05-14 Hollandse Signaalapparaten Bv Perfectionnement apporté à un mécanisme d'entraînement par frottement
GB788563A (en) * 1955-07-12 1958-01-02 Harrison Reproduction Equipmen Improvements in or relating to variable speed driving mechanisms
DE2361993B1 (de) * 1973-12-13 1975-04-10 P.I.V. Antrieb Werner Reimers Kg, 6380 Bad Homburg Stufenlos einstellbares Reibscheibengetriebe
EP0021126A1 (fr) 1979-06-07 1981-01-07 Bernd Grewe Dispositif de production continue de la pression de contact nécessaire pour un variateur continu de la vitesse à friction
WO1983002986A1 (fr) 1982-02-18 1983-09-01 Kugle, Jens Mecanisme de transmission
WO1992008912A1 (fr) 1990-11-16 1992-05-29 Torotark (Development) Limited Transmission du type a roulement-traction et a voie toroidale

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
DUBBEL: "TASCHENBUCH FUR DEN MASCHINENBAU", vol. 16, 1987, pages: 104-108

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19907637C1 (de) * 1999-02-23 2001-01-11 Clark Equipment Belgium Nv Planetengetriebe
EP1132650A1 (fr) 2000-03-08 2001-09-12 Herbert Bolter Transmission à roues de friction
WO2002016803A1 (fr) * 2000-08-19 2002-02-28 Bernard Maitland Hartley Systeme de transmission variable

Also Published As

Publication number Publication date
EP1025374A1 (fr) 2000-08-09
AU6909798A (en) 1998-05-22

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