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WO2010022701A1 - Ensemble de poulies coniques pour transmission à variation continue à poulies coniques et transmission à variation continue à poulies coniques - Google Patents

Ensemble de poulies coniques pour transmission à variation continue à poulies coniques et transmission à variation continue à poulies coniques Download PDF

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Publication number
WO2010022701A1
WO2010022701A1 PCT/DE2009/001127 DE2009001127W WO2010022701A1 WO 2010022701 A1 WO2010022701 A1 WO 2010022701A1 DE 2009001127 W DE2009001127 W DE 2009001127W WO 2010022701 A1 WO2010022701 A1 WO 2010022701A1
Authority
WO
WIPO (PCT)
Prior art keywords
conical disk
shaft
conical
cone
cone 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.)
Ceased
Application number
PCT/DE2009/001127
Other languages
German (de)
English (en)
Other versions
WO2010022701A8 (fr
Inventor
Bernhard Walter
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.)
Schaeffler Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau 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 LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Priority to DE112009001809T priority Critical patent/DE112009001809A5/de
Publication of WO2010022701A1 publication Critical patent/WO2010022701A1/fr
Anticipated expiration legal-status Critical
Publication of WO2010022701A8 publication Critical patent/WO2010022701A8/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
    • 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
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
    • F16D1/092—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces the pair of conical mating surfaces being provided on the coupled hub and shaft
    • 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
    • F16H63/065—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 hydraulic actuating means

Definitions

  • the invention relates to a conical disk arrangement for a conical-disc CVT transmission and a conical-disc CVT transmission as a continuously variable transmission, in particular for a motor vehicle.
  • a cone-pulley CVT transmission has a cone pulley pair each on an input shaft and an output shaft of the transmission.
  • One of the conical disks of the pair is rotationally fixed and held fixed in position on the shaft in the axial direction of the shaft, while the other conical disk is adjustable in the axial direction relative to the first conical disk.
  • the conical disks thus define a ring which can be changed with respect to its width in the axial direction between them, which, owing to the conical shape of the conical disks, in particular their mutually facing surfaces, widens outwards in the radial direction. In this ring, i.
  • a belt is introduced, which produces a power transmission connection between the conical disk pair of the drive side and the cone pulley pair of the output side.
  • the wrapping means at one of the shafts radially inward or further out in the plant.
  • the radial position of the belt on the drive side and the output side is adjusted by changing the distances of the conical disks of the cone pulley pairs on the drive side and output side opposite to each other. This alters and adjusts the ratio of the bevel CVT transmission.
  • a contact pressure which is applied to the adjustable conical disk and is transmitted to the belt, the belt is held so that it does not move substantially unintentionally in the radial direction and thus can transmit a force between the drive shaft and the output shaft.
  • a hydraulic adjusting mechanism is contemplated in which the adjustable conical disk on the side facing away from the fixed conical disk is encompassed by a supporting cylinder wall and thus so sealingly but relatively displaceably connected, that in a space between the supporting cylinder wall and the adjustable conical disk hydraulic fluid can be supplied and removed and thus on the one hand, the adjustment of the conical disk can be effected and on the other hand, the necessary contact force on the belt in the axial Direction can be provided.
  • the supporting cylinder wall is fixedly provided in the axial direction on the associated shaft.
  • the components fixed in the axial direction namely the first conical disk fixed in the axial direction and a supporting cylinder wall, are conventionally held in a positionally stable manner against the pressing force using shaft shoulders in the axial direction.
  • corresponding shoulders are provided on the shaft, against which a radially inner region of the fixed conical disk or the cylinder support wall abuts and rests, wherein the contact force acts such that it presses the conical disk or the Zylinderabstützwand further against the shaft shoulder.
  • Such an arrangement is shown, for example, in the documents US Pat. No. 6,506,136 B2 and EP 0 777 069 B1.
  • the shaft must be made very solid in the area of the shaft shoulder, so that it has sufficient strength, since the shaft shoulder, especially its corner, is loaded very high by the acting contact forces.
  • the formation of wave heels often involves notching with them in order to produce them, which in turn adversely affect the strength of the shaft.
  • the proposed arrangement is equally suitable for the arrangement of the cone pulley pair on the drive shaft and the output shaft.
  • the invention is based on the idea of supporting the fixed conical disk and, as required, a cylinder supporting wall by means of an interference fit on the shaft.
  • a conical interference fit is recommended in order to be able to support the high required contact forces.
  • the supporting cylinder wall can either by a press fit or a Transition seat between cylindrical surfaces in production with appropriate tolerance or be achieved by another suitable attachment.
  • a conical disk arrangement for a continuously variable bevel gear includes a shaft and a pair of conical disks mounted on the shaft with a first conical disk and a second conical disk facing the first conical disk in the axial direction of the shaft.
  • the first conical disk is rotatably mounted on the shaft and fixed in the axial direction, while the second conical disk is slidably mounted to the first conical disk in the axial direction on the shaft.
  • the first cone pulley is held on the shaft by a tapered press fit.
  • the facing surfaces i. the inner peripheral surface of the conical disk and the outer peripheral surface of the shaft directed thereon are at least partially shaped so as to enclose a cone angle with each other which allows an interference fit of the conical disk on the shaft.
  • the cone angle is preferably chosen so that a self-locking arises in the press-fit area. This ensures a secure fit of the conical disk on the shaft.
  • the cone angle between the inner circumferential surface and the outer peripheral surface preferably includes an angle of 3 to 5 degrees. Both surfaces may be conical, each with different cone angles, so that preferably results in a cone angle in the preferred range of 3 to 5 degrees between the two surfaces. In the installed, compressed state, equal angles set. - A -
  • the pressing force between the conical disk and the shaft during assembly is at least as large as the maximum operating force occurring in operation on the belt, whereby a secure position of the conical disk in the axial direction relative to the shaft can be ensured regardless of the operating condition.
  • the conical disk can not be moved during operation.
  • the inner peripheral surface of the first conical disk which is directed onto the outer peripheral surface of the shaft, is provided with a cylindrical centering region adjacent to the conical disk press-fit region, wherein the outer peripheral surface region of the shaft likewise has a cylindrical centering seat.
  • the centering area on the conical disk preferably has a smaller diameter than the conical cone-type press fit.
  • the conical disk is further on its end face, in particular the end face, on which the pressing force of the belt means acts and thus also the pressing force is applied to the shaft, i. preferably that of the other, second conical disk facing end face, provided with a flat surface region which forms a preferably substantially perpendicular to the axial direction of the shaft surface. With this flat surface, the cone pulley can be pressed well and reliably onto the shaft.
  • the conical disk arrangement is preferably provided in the second conical disk, which is adjustable in the axial direction, a Zylinderabstützwand which supports the force applied to the second conical disk adjusting force.
  • the cylinder support wall is thus also held firmly in the axial direction on the shaft.
  • the Zylinderabstützwand is held on the shaft by a press fit, wherein preferably a pressure between two custom-made cylindrical surfaces is achieved with a circular cylindrical cross section.
  • the cylinder support wall can be further secured additionally by welding or for example a split retaining ring or other fastening means on the shaft.
  • the cylinder support wall serves to adjust the distance between the two conical disks. In the ground state of the bevel belt transmission, a defined distance must exist between the conical disks. Due to the press connection with a conical seat of the axially fixed conical disk whose axial position on the shaft is not well defined. The Zylinderabstützwand and thus the axially movable conical disk is pushed onto the shaft so that the defined distance is set in the basic position between the two conical disks. Subsequently, the Zylinderabstützwand is at least fixed axially, if a possibly provided press fit is not sufficient.
  • Figure 1 shows a cross section along the axial direction through a conical disk arrangement according to the invention.
  • Figure 2 is an enlargement of Figure 1 in the area X, wherein the press-fit area between the conical disk and the shaft is shown.
  • FIG. 1 shows a conical disk arrangement 10 according to the invention.
  • Two embodiments with respect to the attachment of a Zylinderabstützwand 20 on a shaft 12 are shown in Figure 1, which are explained below, wherein the one variant is shown above the shaft axis A and the other variant is shown below the shaft axis A.
  • the arrangement includes, in addition to the shaft 12, a conical disk pair 30 with a first conical disk 32 and a second conical disk 34.
  • the conical disks 32, 34 are rotatably mounted on the shaft 12.
  • the second conical disk 34 is movable in the axial direction of the shaft 12, the conical disk 32 is fixed in the axial direction of the shaft 12.
  • Each of the conical disks 32, 34 has an end face 33, 35 which is directed to the respective other conical disk 34, 32 of the cone pulley pair 30, wherein the end faces 33, 35 define a conical ring 36 between them, into which a (not shown). Belting can be introduced.
  • the conical ring 36 which is formed as a space between the conical disks 34, 32, widens in the radial direction to the outside.
  • the conical disks 32, 34 are conical overall with an (imaginary) cone point on the shaft axis A and a base surface, which is one of the end faces of the conical disk, namely the front side facing away from the respective other conical disk.
  • the width b of this ring 36 between the conical disks 32, 34 in the axial direction of the shaft 12 can be changed by adjusting the adjustable, second conical disk 34 in the axial direction, so that the distance to the first conical disk 32 changes.
  • the wrapping means (not shown) having a fixed length in the axial direction of the shaft 12 can be forced to different diameters and thus the gear ratio of a bevel gear can be changed.
  • the inner circumferential surface of the conical disk 34 and the outer peripheral surface of the shaft 12 opposite this are provided with, for example, a spline 14.
  • the spline 14 allows a displacement of the conical disk 34 in the axial direction, but holds it against rotation.
  • the adjusting mechanism for the displaceable cone pulley 34 is formed in the embodiment shown in Figure 1 by a hydraulic mechanism.
  • a hydraulic mechanism To adjust the second conical disk 34 in the axial direction hydraulic fluid via a supply line 16 which is formed by corresponding holes in the shaft 12 and to which a hydraulic supply can be connected, as needed in a chamber 50 supplied or removed, which between the adjustable cone pulley 34 and a Zylinderabstützwand 20, which surrounds the adjustable cone pulley 34 on the side facing away from the first conical disk 32 side is formed.
  • the chamber 50 is sealed between the second cone pulley 34 and the cylinder support wall 20, for example by an O-ring seal 51 or any other type of seal.
  • Corresponding sealing means may also be provided (not shown) between the second conical disk 34 and the shaft 12 and between the cylinder support wall 20 and the shaft 12 as required. Just between the Zylinderabstützwand 20 and the shaft 12, the requirement of a seal depends on the attachment of the cylinder support wall 20 on the shaft 12, which will be described later.
  • the second conical disk 34 shifts in the direction to the right in FIG. 1, ie toward the first conical disk 32.
  • the pressure in the chamber 50 is a larger or smaller adjustment of the cone pulley 34 caused and the contact pressure of the conical disk 34 on the (not shown) wrapping means and the Umschlingungsmit- means on the first conical disk 32 set accordingly.
  • the Zylinderabstweilwand 20 is rotatably mounted on the shaft 12 and fixed in the axial direction.
  • two embodiments are shown in FIG.
  • the Zylinderabstützwand 20 is pressed onto the shaft 12 to measure by with appropriate tolerance and dimensional stability, the Zylinderabstützwand 20 with a circular cylindrical inner surface 22 and the shaft 12 with an associated dimensionally stable, also circular cylindrical outer surface 18 are provided.
  • the two surfaces are fitted with each other, so that the cylinder support wall 20 is securely held by the interference fit by means of press fit.
  • a weld 24 can secure the location between the cylinder support wall 20 and the shaft 12.
  • the use of a weld 24 is further advantageous in that then no additional sealing of the hydraulic chamber 50 must be provided.
  • the Zylinderabstützwand 20 is also provided with a cylindrical inner surface 22 as a fitting surface, which comes into interference fit with a corresponding outer surface 18 of the shaft 12.
  • the cylinder support wall 20 is held in the axial direction by a split ring 26.
  • the cylinder support wall 20 has been pushed during assembly as far as the shaft 12 in the direction of the assembled cone pulley 32 that the predetermined distance between the two conical disk end faces 33, 35 is set in the basic position of the transmission. Subsequently, if necessary, an axial fixation of the cylinder support wall.
  • the attachment between the first conical disk 32 and the shaft 12 is best seen in Figure 2 with the detailed view of the detail X in Figure 1.
  • a conical interference fit 40 is provided between the first conical disk 32 and the shaft 12.
  • the tapered press fit 40 is formed by a portion of the inner peripheral surface of the cone pulley 32 (conical-press-seat portion 42) and an opposite portion of the outer peripheral surface of the shaft 12 (wave press-fit portion 43).
  • the conical disk press seat region 42 or the wave press seat region 43 are provided with mating surfaces, which are matched to one another in such a way that they form a cone angle ⁇ of, for example, 3 to 5 degrees.
  • the cone angle ⁇ is preferably selected such that self-locking arises in the press-fit area.
  • the shaft 12 is provided with a conically widening peripheral surface 44, the associated conical disk press-fit surface 42 of the first conical disk 32 is also conical.
  • the surfaces 42, 43 are further selected so that the pressing force acting in the direction of the force F (see Figure 1), greater than the maximum operating force or contact force of the belt can be selected in operation, so that the operating forces arising from the first cone pulley 32 can be recorded.
  • the angles of the press-fit surfaces 42, 43 are the same in any case.
  • a centering region 70 is further formed between the first conical disk 32 and the shaft 12 by a cylindrical (circular cylindrical) portion of the outer peripheral surface of the shaft 12 as a centering seat 73 and a nikzylin- derförmigen portion of the inner peripheral surface of the first conical disk 32 is formed as centering 72.
  • a centering seat 73 By the respective cylindrical centering of the centering 72 and the centering 73, the first cone pulley 32 can be kept centered on the shaft 12.
  • an exemption 74 is formed on the inner peripheral surface of the first conical disk 32 in the region of the centering region 72, adjacent to the end face 33 of the first conical disk 32 facing the second conical disk 34.
  • a plane surface area 60 adjacent to the inside of the conical disk 34 is also provided. nenprofit of the conical disk 32 is formed. This flat surface area 60 serves to provide a surface for pressing the conical disk 32 onto the shaft 12.

Landscapes

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

Abstract

L'invention concerne un ensemble de poulies coniques (10) pour une transmission à variation continue à poulies coniques, comprenant un arbre (12) et une paire de poulies coniques (30) comportant une première poulie conique (32) et une seconde poulie conique (34) positionnée en vis-à-vis de la première dans le sens axial de l'arbre. L'invention se caractérise en ce que la première poulie conique est fixée solidaire en rotation sur l'arbre et de manière fixe dans le sens axial et en ce qu'elle est maintenue sur l'arbre par l'intermédiaire d'un ajustement serré (40) en forme de cône.
PCT/DE2009/001127 2008-08-28 2009-08-10 Ensemble de poulies coniques pour transmission à variation continue à poulies coniques et transmission à variation continue à poulies coniques Ceased WO2010022701A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112009001809T DE112009001809A5 (de) 2008-08-28 2009-08-10 Kegelscheibenanordnung für ein Kegelscheiben-CVT-Getriebe und Kegelscheiben-CVT-Getriebe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008044821 2008-08-28
DE102008044821.4 2008-08-28

Publications (2)

Publication Number Publication Date
WO2010022701A1 true WO2010022701A1 (fr) 2010-03-04
WO2010022701A8 WO2010022701A8 (fr) 2011-04-21

Family

ID=41388825

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2009/001127 Ceased WO2010022701A1 (fr) 2008-08-28 2009-08-10 Ensemble de poulies coniques pour transmission à variation continue à poulies coniques et transmission à variation continue à poulies coniques

Country Status (2)

Country Link
DE (2) DE102009036882A1 (fr)
WO (1) WO2010022701A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014216239A1 (de) 2014-08-15 2016-02-18 Schaeffler Technologies AG & Co. KG Kegelscheibenanordnung
DE102014216652B4 (de) 2014-08-21 2016-10-13 Schaeffler Technologies AG & Co. KG Kegelscheibenanordnung und Verfahren zum Betreiben einer Kegelscheibenanordnung
DE102015223016A1 (de) 2014-12-16 2016-06-16 Schaeffler Technologies AG & Co. KG Kegelscheibenanordnung
DE102015215054A1 (de) 2015-08-06 2017-02-09 Schaeffler Technologies AG & Co. KG Kegelscheibenanordnung

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB110522A (en) * 1917-07-05 1917-10-25 Jose Maria Armangue Improvements relating to Pulleys for the Transmission of Movement at Variable Speed.
FR1061668A (fr) * 1950-09-18 1954-04-14 Changement de vitesse constitué par une série de couronnes de poulies, de roues dentées ou analogue
US4061047A (en) * 1976-09-20 1977-12-06 Deere & Company Pulley half mounting of variable speed pulley
DE3726115A1 (de) * 1987-08-06 1989-02-16 Gerwah Praezision Gmbh Verfahren zur starren befestigung eines maschinenelementes auf einer welle sowie befestigungsanordnung
DE8911061U1 (de) * 1989-09-15 1989-10-26 Gebrüder Sulzer AG, Winterthur Spannvorrichtung zur drehfesten Verbindung einer Welle mit einem Maschinenelement
WO2003106866A2 (fr) * 2002-06-17 2003-12-24 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Transmission a variation continue a disques coniques
NL1026210C2 (nl) * 2004-05-17 2005-11-21 Gear Chain Ind Bv Kegelschijfstel voor een continu variabele transmissie en continu variabele transmissie voorzien van een dergelijk kegelschijfstel.

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1001755C2 (nl) 1995-11-28 1997-05-30 Doornes Transmissie Bv Poelie.
DE19909347B4 (de) 1998-03-10 2012-03-29 Schaeffler Technologies Gmbh & Co. Kg Getriebe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB110522A (en) * 1917-07-05 1917-10-25 Jose Maria Armangue Improvements relating to Pulleys for the Transmission of Movement at Variable Speed.
FR1061668A (fr) * 1950-09-18 1954-04-14 Changement de vitesse constitué par une série de couronnes de poulies, de roues dentées ou analogue
US4061047A (en) * 1976-09-20 1977-12-06 Deere & Company Pulley half mounting of variable speed pulley
DE3726115A1 (de) * 1987-08-06 1989-02-16 Gerwah Praezision Gmbh Verfahren zur starren befestigung eines maschinenelementes auf einer welle sowie befestigungsanordnung
DE8911061U1 (de) * 1989-09-15 1989-10-26 Gebrüder Sulzer AG, Winterthur Spannvorrichtung zur drehfesten Verbindung einer Welle mit einem Maschinenelement
WO2003106866A2 (fr) * 2002-06-17 2003-12-24 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Transmission a variation continue a disques coniques
NL1026210C2 (nl) * 2004-05-17 2005-11-21 Gear Chain Ind Bv Kegelschijfstel voor een continu variabele transmissie en continu variabele transmissie voorzien van een dergelijk kegelschijfstel.

Also Published As

Publication number Publication date
DE112009001809A5 (de) 2011-04-28
WO2010022701A8 (fr) 2011-04-21
DE102009036882A1 (de) 2010-03-04

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