EP2074338A1 - Transmission à cônes et bague de friction - Google Patents

Transmission à cônes et bague de friction

Info

Publication number
EP2074338A1
EP2074338A1 EP07817567A EP07817567A EP2074338A1 EP 2074338 A1 EP2074338 A1 EP 2074338A1 EP 07817567 A EP07817567 A EP 07817567A EP 07817567 A EP07817567 A EP 07817567A EP 2074338 A1 EP2074338 A1 EP 2074338A1
Authority
EP
European Patent Office
Prior art keywords
friction
conical
transmission according
friction ring
ring transmission
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.)
Ceased
Application number
EP07817567A
Other languages
German (de)
English (en)
Inventor
Werner Brandwitte
Christoph DRÄGER
Ulrich Rohs
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=39134565&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2074338(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Individual filed Critical Individual
Priority to EP11008645A priority Critical patent/EP2434182A1/fr
Publication of EP2074338A1 publication Critical patent/EP2074338A1/fr
Ceased 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
    • 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
    • F16H15/42—Gearings providing a continuous range of gear ratios in which two members co-operate by means of rings or by means of parts of endless flexible members pressed between the first mentioned 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/34—Non-adjustable friction discs

Definitions

  • the invention relates to conical friction ring gear with at least two mutually spaced friction cones and arranged at this distance along friction surfaces on the Reibkegeln displaceable, a torque of one of the two friction cone on the other of the two friction cones transmitting friction ring, wherein at least one friction surface axially varied.
  • Such conical friction ring transmissions are well known, for example, from WO 2004/031615 A2, wherein the variation of the friction surface serves to equalize the surface pressure, which otherwise due to the strongly differing tread diameter, in particular with respect to conical friction ring, in which Friction ring encompasses at least one of the cones, also subject to very strong deviations.
  • the grooves disclosed in this document have proven particularly useful, which can be introduced in a targeted manner into a surface.
  • the object of the invention is arranged by a conical friction ring gear with at least two spaced apart friction cones and arranged at this distance along friction surfaces on the Reibkegeln, transferring a torque from one of the two friction cone on the other of the two friction cones
  • Friction ring solved in which at least one friction surface varies axially and which is characterized in that the axial variation of the friction surface in at least two convex portions has a radius over 0.1 mm.
  • convex areas describes surface areas of the friction surface that are convexly shaped in a section. Accordingly, according to the invention, an axial variation is directed to an axial section in which convex areas are to be formed according to the invention Accordingly, in the context of the present invention, "convex areas” particularly describes those areas of the friction surface which form groove inlets, in particular also rounded groove inlets in the sense of the invention. Not to be covered by these variations of the envelope of the respective cone, such as for the friction ring in terms of its transmission ratio relevant variations of the friction surface, such as deviations from a strictly conical surface by a change in slope of the generatrix.
  • German Patent DE 825 933 B describes a continuously variable transmission in which a hard rubber ring circulates in a gap between two roughened or grooved cones.
  • a positive connection for the transmission of forces or torques between two bevel gears also makes use of the continuously variable transmission disclosed in DE 195 07 525 A1, in which a corresponding operative contact between the two bevel gears is achieved by means of a self-contained helical spring loop ,
  • a force transmission with respect to bevel gears caused by friction elements should now be achieved here by means of bevel gears and by means of helical spring loops engaging in the bevel gears.
  • the conical friction ring according to the invention provides a friction connection between the friction ring and the friction cones, also the disclosed in the published patent DE 195 07 525 Al object does not affect the present conical friction ring gear.
  • all illustrated continuously variable transmissions are not conical friction ring transmissions in the sense of the present invention, in which a transmission of forces or torques is achieved only by means of frictionally engaged connections.
  • a frictional connection can form between a friction ring and friction cones.
  • a fluidic friction connection can be formed between the friction ring and the friction cones.
  • a traction and / or a cooling fluid can be arranged in particular between the friction ring and the friction cones in a proper operating state, so that the respective surfaces are in direct contact only in special operating states, for example in start-up or standstill situations.
  • the convex regions according to the invention are advantageous, since the fluid is partially displaced by the convex regions, as a result of which the surface pressure can be suitably adapted.
  • the friction surface has radial circumferential grooves for forming an axial variation.
  • radially encircling grooves succeeds structurally simple to vary a friction surface in your axial longitudinal extent almost arbitrarily.
  • the axial variation of the friction surface in the convex areas may have a radius of more than 0.5 mm, preferably more than 1 mm.
  • the area of the friction surface which serves to realize a first speed range can have substantially smaller radii in its convex portions than is the case in regions of the friction surface which form a middle speed range or the highest speed range.
  • the object of the invention is also arranged by a conical friction ring gear with at least two spaced cones and arranged at this distance along friction surfaces on the Reibkegeln displaceable, a torque of one of the two cones on the other of the two cones transmitting friction ring in which at least one friction surface varies axially and which is characterized in that the axial variation of the friction surface in at least two convex regions has a radius over one hundredth of the width B of the friction ring.
  • a related embodiment provides that the axial variation of the friction surface in the convex areas has a radius over five hundredths, preferably over one-tenth, of the width of the friction ring.
  • the axial variation of the friction surface in concave regions has a radius over one thousandths of a width, preferably over five hundredths, of the width of the friction ring Accordingly, independently of the other features of the present invention is inventive.
  • the axial areas between two grooves are chosen to be sufficiently solid, since these form the actually viable area of the friction surface.
  • the grooves can be spaced apart from one another less than one third of the width of the friction ring. By limiting the groove spacing follows a smoother running under load changes. It is understood that the groove distances explained above are also advantageous independently of the other features of the present invention for generic conical friction ring gears.
  • the friction surface has radially extending elevations for forming an axial variation. Even by means of such radial circumferential elevations a friction surface can be easily varied axially in design terms.
  • a structurally particularly preferred embodiment provides that radially encircling elevations of the friction surface are formed by convex regions of the friction surface.
  • the convex areas correspondingly rotate radially on a friction surface.
  • a particularly advantageous interplay between such circumferential convex areas and the circumferential grooves may result if a respective elevation of the friction surface forming a convex area is arranged between two grooves of the friction surface.
  • a friction surface can be made particularly rich in variation.
  • grooves and elevations on the friction surface form a groove profile of the friction surface, which varies axially.
  • a friction ring can rub off in a particularly wear-resistant manner and with suitably selected changes in the surface pressure.
  • the elevations of the groove profile form peaks of the friction surface, wherein these wave peaks can advantageously be designed as convex regions with a radius of over 0.1 millimeter.
  • a further particularly advantageous embodiment of the present invention provides that the friction ring in interaction with a friction cone always covers at least two or more elevations of one of the friction surfaces. Covered the Friction ring at least two or more surveys, the risk is almost excluded that the friction ring can tip into an existing groove or runs restless. Advantageously, this can also prevent that a convex region of the friction surface is subjected to extremely unfavorable, which would result in increased wear of the friction surface.
  • FIG. 1 schematically shows an arrangement of a first cone, a second cone and a friction ring
  • FIG. 3 schematically shows the design of a friction surface in a region for realizing a middle gear range of a transmission
  • Figure 5 schematically shows an input cone with three axial surface variations for a conical friction ring gear.
  • the arrangement 1 shown in Figure 1 shows the main components of a conical-friction ring transmission comprising a first cone 2, a second cone 3 and a The first cone 2 encompassing friction ring 4.
  • the conical friction ring 4 in the present case has a width B. Both cones 2 and 3 are spaced apart by a distance 5, wherein the cone 2 rotates about a rotation axis 6 and the cone 3 about a rotation axis 7.
  • the friction ring 4 is displaced axially relative to the cones 2 and 3 according to the double arrow 8 along the axes of rotation 6, 7 and thus also axially to the cones 2, 3.
  • the portion 9 of the friction ring 4 which is in direct contact with the cones 2, 3 moves accordingly within the gap 5 according to the direction of movement 8.
  • the surface region 13 illustrated in FIG. 2 shows a friction surface 10, 11 of the conical-friction ring transmission from FIG. 1 in a first or very low gear range.
  • the surface region 14 from FIG. 3 is a friction surface 10, 11 in a central passage region, whereas the surface region 15 according to FIG. 4 represents a highest transition region of a friction surface 10, 11.
  • the surface area 13 essentially has grooves (not visible here for reasons of drawing) with a very small depth.
  • the resulting wave crests have a radius of R34.08 (the radius R is in mm) or R33 and have a distance of 2.2 mm from each other. The distance is in this embodiment between a first vertex (not explicitly here plotted) of a first wave crest and a second crest of a second wave crest.
  • Wave crests 17 are already more pronounced in the surface region 14. Wave crests 17 (numbered here only as an example) are also 2.2 mm apart. In the surface region 14, the grooves 16 have a depth 18 of 0.17 mm and their rounded groove bottom 19 have a radius R0.39. The wave crests 17 have a width 20 of about 1.4 mm, wherein they have rounded Nuteintrust 21, which have a radius R13,2.
  • the surface area 15 comprises grooves 25 with rounded groove bottoms 26 with values R0.6 and a groove depth 27 of 0.28 mm. Between the individual grooves 25 extend wave peaks 28, which are also spaced 2.2 mm apart. The wave crests here have a radius R5,8 and a width 29 of 1 mm, which extend from a rounded groove inlet to an adjacent rounded groove inlet.
  • the ring on the one hand runs much quieter and can transmit a relatively high torque with justifiable contact forces. Also, the life of the friction surface is significantly extended over known friction surfaces.
  • the friction cone 110 shown in FIG. 5 is an input friction cone 130 of a conical-friction ring transmission not shown here in detail, which can rotate about an axis of rotation 106 of a drive shaft of the conical-friction-ring transmission not shown here.
  • the input friction cone 130 is designed as a truncated cone 131 with a first edge region 132 and a second edge region 133.
  • the input friction cone 130 is further provided with a friction surface 110 that varies along the axial longitudinal extent 112 of the input friction cone 130.
  • the friction surface 110 is roughly divided into three friction surface variations 135, 136 and 137.
  • the first friction surface variation 135 forms a first gear range 138, in which a friction ring (not shown explicitly here, but see FIG. 1, reference numeral 4) is located when the conical friction ring transmission is switched, for example, into a starting situation of a vehicle.
  • the second friction surface variation 136 is followed by a middle gear region 139 at the first gear region 138, and then, with the third friction surface Variation 137, a highest gear region 140.
  • the wave peaks 128 are formed by elevations 142, which also form convex areas 143 at the input cone 130 with a radius C3. In the area of the third friction surface variation 137, the wave peaks 128 have a width (b) 129 which can be selected as a function of the desired surface pressure between the friction ring and the friction surface 110.
  • the friction ring mentioned here has a width (a) 144 which is chosen so that the friction ring is always in contact with two wave crests 128 and the friction ring is not in danger of tipping into one of the grooves 125 and thereby the convex portions 143, in particular groove slots 121, damage.
  • the groove volume can be structurally simply varied, which in turn allows the amount of traction fluid which is present between the friction ring and the input friction cone 130 to be varied.
  • a radius in the region of groove bottoms 126 is selected in this exemplary embodiment as a function of the ring width (a) 144, the radius in the region of the groove bottoms 126 corresponding to approximately one third of the friction ring width (a) 144.
  • the grooves 116 running around the friction surface 110 have, first, a smaller groove depth 118 and, secondly, a smaller radius as the radii of the groove bases 126 have on the third Reib lakevariation 137.
  • the radius in the region of the groove bottoms 119 is one fifth of the friction ring width (a) 144.
  • the grooves 116 also alternate in the region of the second friction surface variation 136 with corresponding circumferential wave crests 117, which are formed by further elevations 151 rotating on the input friction surface 110.
  • the wave crests 117 have a slightly greater width (b) 120 than the crests 128 of the third friction surface variation 137 in the region of the second friction surface variation 136.
  • Further convex regions 153 on the friction surface 110 of the input friction cone 130 are formed by means of the elevations 151 and the wave crests 117 formed thereby provided. These further convex portions 153 have a radius C2, which can be chosen as explained below.
  • the friction surface 110 has graphically no circumferential grooves that can be represented meaningfully, which is why these grooves are not numbered either (see third detail view 161).
  • These circumferential grooves in the region of the first friction surface variation 135 have only a very small depth, which is substantially smaller than the groove depths 118 and 127.
  • alternating wave peaks are in the area of the first friction surface variation 135 a radius Cl on.
  • the radii C 1, C 2, C 3 of all wave crests 117, 128 of the friction surface 110 are presently dependent on the forces or torques to be transmitted, the friction cones / friction ring geometries used and the permissible surface pressures which exist between the friction ring and the friction surface 110 exist, selected.
  • the widths (b) of the wave crests can also be selected from the surface pressure or from the contact surface to be provided between the friction ring and the friction surface 110.
  • the ring width (a) 144 of the friction ring can be chosen according to the desired application, however, the ring width (a) 144 should cover at least two of the wave crests, thus avoiding the risk of the friction ring creeping in, especially in one of the larger ones circumferential grooves 116, 125 to prevent.

Landscapes

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

Abstract

Selon l'invention, afin de mieux supporter les sollicitations sur les surfaces de friction de transmissions à cônes et bague de friction, une transmission à cônes et bague de friction comprend au moins deux cônes de friction disposés à distance l'un de l'autre, et une bague de friction disposée à déplacement dans cet espacement et transmettant un couple de rotation de l'un des deux cônes de friction à l'autre. Au moins une surface de friction varie axialement, et la variation axiale de la surface de friction présente un rayon supérieur à 0,1 mm dans au moins deux régions convexes.
EP07817567A 2006-09-22 2007-09-24 Transmission à cônes et bague de friction Ceased EP2074338A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11008645A EP2434182A1 (fr) 2006-09-22 2007-09-24 Engrenage à roues coniques à friction

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102006045343 2006-09-22
DE102007002581A DE102007002581A1 (de) 2006-09-22 2007-01-11 Kegelreibringgetriebe
PCT/DE2007/001725 WO2008034438A1 (fr) 2006-09-22 2007-09-24 Transmission à cônes et bague de friction

Publications (1)

Publication Number Publication Date
EP2074338A1 true EP2074338A1 (fr) 2009-07-01

Family

ID=39134565

Family Applications (2)

Application Number Title Priority Date Filing Date
EP07817567A Ceased EP2074338A1 (fr) 2006-09-22 2007-09-24 Transmission à cônes et bague de friction
EP11008645A Withdrawn EP2434182A1 (fr) 2006-09-22 2007-09-24 Engrenage à roues coniques à friction

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP11008645A Withdrawn EP2434182A1 (fr) 2006-09-22 2007-09-24 Engrenage à roues coniques à friction

Country Status (8)

Country Link
US (1) US8187142B2 (fr)
EP (2) EP2074338A1 (fr)
JP (1) JP5303789B2 (fr)
KR (1) KR20090059137A (fr)
CN (1) CN101542165B (fr)
BR (1) BRPI0715241B1 (fr)
DE (2) DE102007002581A1 (fr)
WO (1) WO2008034438A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011013070A1 (de) * 2011-03-04 2012-09-06 Ulrich Rohs Kegelreibringgetriebe
DE112019002839T5 (de) 2018-06-06 2021-02-25 Vectis Drive Inc. Traktions- oder reibradantrieb mit fester übersetzung
CN109555826A (zh) * 2018-12-08 2019-04-02 陈世昆 离心摆摩擦套环变速器
US11772743B2 (en) * 2022-02-18 2023-10-03 Joseph Francis Keenan System and method for bicycle transmission

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DE825933C (de) * 1950-05-05 1951-12-27 Braun Dieter Stufenloses Getriebe
FR1375048A (fr) * 1963-06-18 1964-10-16 Changement de vitesse continu par rouleaux coniques à axes parallèles
FR1386314A (fr) * 1963-11-14 1965-01-22 Changements de vitesse continus par laminoirs coniques ou cylindro-coniques avec cordon élastique ou pneumatique
US3481213A (en) * 1967-09-11 1969-12-02 Salvatore La Macchia Quick traverse machine tool accessory apparatus
US3747424A (en) * 1972-02-28 1973-07-24 Gourevitch J Variable speed reducer
US3873128A (en) * 1973-05-29 1975-03-25 Trans World Products Inc Drive transmission for a bicycle or the like
DE19507525A1 (de) * 1995-03-03 1996-09-05 Andrzej Dipl Ing Walczak Stufenloses Getriebe
JP3908370B2 (ja) * 1998-01-13 2007-04-25 日本精工株式会社 トロイダル型無段変速装置の入出力ディスクの製造方法
US6139465A (en) * 1999-06-16 2000-10-31 Holliday; Sander Infinite speed transmission
JP3736619B2 (ja) * 2000-06-29 2006-01-18 日産自動車株式会社 トロイダル型無段変速機
EP1348775B1 (fr) * 2000-12-27 2006-03-08 Nsk Ltd., Transmission variable en continu toroidale
JP3748067B2 (ja) * 2001-02-21 2006-02-22 日産自動車株式会社 トラクションドライブ用転動体
DE60238881D1 (de) 2001-02-21 2011-02-24 Nissan Motor Rotationseinheit eines Reibungsgetriebes
JP4563933B2 (ja) * 2002-09-30 2010-10-20 ロース，ウルリヒ 変速装置
WO2004031615A2 (fr) * 2002-09-30 2004-04-15 Ulrich Rohs Engrenage planetaire
CN1623053B (zh) * 2002-10-07 2011-07-20 乌尔里克·罗斯 传动机构
US6752740B2 (en) * 2002-11-12 2004-06-22 Jeffery T. Semmes Continuously variable transmission
US7025705B2 (en) * 2002-11-15 2006-04-11 Kuehnle Manfred R Toroidal transmission
US6955624B2 (en) * 2002-12-12 2005-10-18 Dwight Stanford Brass Motor vehicle drivetrain having at least two CNT's and flywheels
US6908406B2 (en) * 2003-03-05 2005-06-21 Mark Albert Overbay Continuously variable transmission with elastomeric meshing interface
DE10312555A1 (de) 2003-03-21 2004-10-21 Audi Ag Stufenloses Getriebe
DE102004003721A1 (de) * 2004-01-24 2005-08-11 Zf Friedrichshafen Ag Kegelringgetriebe

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See references of WO2008034438A1 *

Also Published As

Publication number Publication date
WO2008034438A1 (fr) 2008-03-27
DE112007002840A5 (de) 2009-09-10
CN101542165A (zh) 2009-09-23
US20090305841A1 (en) 2009-12-10
JP2010504477A (ja) 2010-02-12
KR20090059137A (ko) 2009-06-10
JP5303789B2 (ja) 2013-10-02
EP2434182A1 (fr) 2012-03-28
DE102007002581A1 (de) 2008-04-03
BRPI0715241A2 (pt) 2013-06-25
CN101542165B (zh) 2012-07-18
BRPI0715241B1 (pt) 2019-01-29
US8187142B2 (en) 2012-05-29

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