WO2016107680A1 - Transmission à variation continue à gradation accrue et procédé de commande de rapport pour une telle transmission - Google Patents

Transmission à variation continue à gradation accrue et procédé de commande de rapport pour une telle transmission Download PDF

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Publication number
WO2016107680A1
WO2016107680A1 PCT/EP2015/025115 EP2015025115W WO2016107680A1 WO 2016107680 A1 WO2016107680 A1 WO 2016107680A1 EP 2015025115 W EP2015025115 W EP 2015025115W WO 2016107680 A1 WO2016107680 A1 WO 2016107680A1
Authority
WO
WIPO (PCT)
Prior art keywords
pulley
drive belt
transmission
discs
radial
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/EP2015/025115
Other languages
English (en)
Inventor
Paulus Adrianus Josephus Maria Faes
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
Priority to CN201580071999.1A priority Critical patent/CN107208759B/zh
Priority to JP2017535356A priority patent/JP2018505358A/ja
Publication of WO2016107680A1 publication Critical patent/WO2016107680A1/fr
Anticipated expiration legal-status Critical
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
    • 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
    • F16H9/125—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 characterised by means for controlling the geometrical interrelationship of pulleys and the endless flexible member, e.g. belt alignment or position of the resulting axial pulley force in the plane perpendicular to the pulley axis
    • 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
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G5/00—V-belts, i.e. belts of tapered cross-section
    • F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several 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
    • 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
    • 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
    • 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
    • F16H9/24—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using chains or toothed belts, belts in the form of links; Chains or belts specially adapted to such gearing

Definitions

  • the present invention relates to a continuously variable transmission incorporating a push-type drive belt with increased ratio coverage and, more in particular to a control method for such a transmission.
  • the continuously variable transmission is generally known, for example from European patent application EP1529985-A.
  • EP1529985-A European patent application
  • Various manners of accomplishing this aim exist, often requiring extensive research and significant redesign of the pulley and/or the drive belt components of the transmission.
  • it is therefore an object to realise the same in a cost effective and preferably simple manner, in particular without substantial changes to the existing transmission designs being required.
  • the above object is realised in the transmission according to claim 1 and, more in particular, with the ratio control method according to claim 5 hereinafter.
  • a radial position of the drive belt between the pulley discs of at least one of the transmission pulleys is determined such that the ring set of the drive belt extends, at least partly, beyond the outer circumference, i.e. to the radial outside of the respective pulley, however, only over a segment of the curved trajectory of the drive belt at the respective pulley.
  • the present disclosure makes use of the circumstance that during operation of the transmission the curved pulley trajectory of the drive belt spirals radially inwards as seen in the direction of movement of the drive belt, due to the elastic deformation of the pulleys and of the drive belt itself.
  • the radius of curvature of the drive belt's curved pulley trajectory between the pulley discs is larger at the point of entry of the drive belt there between than at the point of exit from in-between such pulley discs.
  • the ring set of the drive belt can be located inside the outer circumference of the pulley discs where the drive belt exits (from in-between the discs of) the pulley, thus being constrained thereby in the axial direction, even though it is located to the radial outside of pulley discs of that pulley at the said point of entry.
  • the above-mentioned elastic deformation and, hence, also the amount of radially inward spiralling of the drive belt is proportional to not only to the force with which the drive belt is clamped between the pulley discs, but also to the radial position of the drive belt between such discs. Therefore, in accordance with the present disclosure, the most extreme radial position of the drive belt (at entry) between the pulley discs is advantageously set in proportion to such clamping force.
  • the radially inward spiralling of the drive belt typically amounts up to 1 to 2 millimetres or more, such that according to the present disclosure the ring set can extend beyond the circumference of the pulley, at the point of entry of the drive belt between the pulley discs thereof, by at most the same amount.
  • the largest controlled radial position of the drive belt can be increased by the same amount relative to the conventional control method, whereby the ratio coverage of the transmission is favourably increased without any modification being required to the transmission other than incorporating therein a somewhat longer drive belt to make possible the said increased radial position thereof.
  • the diameter of the pulleys -and thus an envelop of the transmission as a whole- can be reduced, while favourably maintaining the ratio coverage of the transmission.
  • figure 1 provides a schematic perspective view of the continuously variable transmission with a drive belt running over two pulleys
  • figure 2 shows a cross section of the known drive belt oriented in the circumference direction thereof
  • figure 3 provides a width-wise oriented view of a transverse member of the known drive belt
  • figure 4 provides a cross-section of the prior art transmission part including the pulley and the belt, the latter being represented in an ultimate radial position relative to the pulley;
  • figure 5 in a schematic side elevation of the prior art transmission illustrates an aspect of the operation thereof;
  • figure 6 illustrates the same aspect of the prior art transmission in a cross-section of the pulley and the belt thereof;
  • figure 7 illustrates the novel transmission during operation in a schematic side elevation thereof.
  • figure 8 illustrates the novel transmission of figure 5 in a cross-section of the pulley and the belt thereof.
  • the schematic illustration of a continuously variable transmission in figure 1 shows a drive belt 3 that runs over two pulleys 1 , 2 and that includes two sets of a number of flexible rings 31 and a number of transverse members 32 that are consecutively arranged along the circumference of the ring sets 31 in an essentially contiguous row, while being contained and guided thereby.
  • the transmission pulleys 1 , 2 each include a pair of conical discs 4, 5 that define a tapered circumferential groove that opens towards the radial outside whilst enclosing an acute angle; the so- called pulley angle ⁇ .
  • Circumference sections of the drive belt 3 are located in the pulley grooves, while being clamped by and between the pulley discs 4, 5 of the respective pulley 1 , 2.
  • the axial separation between these pulley discs 4, 5 can be controlled, typically by way of only one pulley disc 4 of the pulleys 1 , 2 being arranged axially movable relative to a respective pulley shaft 6, 7, in order to control a speed ratio between the pulleys 1 , 2.
  • the upper pulley 1 will rotate more quickly than the lower pulley 2.
  • the radial positions or running radii R1 , R2 of the drive belt 3 at the pulleys 1 , 2 are changed in mutually opposite radial directions and, as a result, the ratio between rotational speeds of the two pulleys 1 , 2 is varied.
  • the speed ratio is defined as a rotational speed of an output pulley 2 of the transmission, which output pulley 2 is associated with a load, divided by a rotational speed of an input pulley 1 of the transmission, which input pulley is associated 1 with an engine or motor driving the load.
  • the transmission is thus depicted in its smallest speed ratio.
  • an exemplary embodiment of the drive belt 3 is shown in cross section oriented in circumference or length direction L thereof, i.e. facing in a direction perpendicular to the axial or width direction W and the radial or height direction H of the drive belt 3.
  • the ring sets 31 are shown in cross- section and one transverse member 32 of the drive belt 3 is shown in a front elevation.
  • the ring sets 31 are in this case constituted by five individual flat, thin and flexible endless rings each, which endless rings are mutually concentrically nested to form the respective ring set. In practice, however, these ring sets 31 often comprise more than five endless rings, e.g. nine or twelve or possibly even more.
  • the transverse members 32 take- up a clamping force exerted between the discs 4, 5 of each pulley 1 , 2 via contact faces 37 thereof, one such contact face 37 being provided at each axial side of the transverse member 32.
  • These contact faces 37 are mutually diverging in radial outward direction such that an acute angle is defined there between that is denoted the belt angle ⁇ J>b of the drive belt 3 and that closely corresponds to the pulley angle ⁇ .
  • the transverse members 32 are able to move, i.e.
  • a first or base portion 34 of the transverse member 32 thus extends radially inwards from the ring sets 31
  • a second or middle portion 35 of the transverse member 32 is situated in between the ring sets 31
  • a third or top portion 36 of the transverse member 32 extends radially outwards from the ring sets 31 .
  • each cut-out 33 is delimited by a so-called bearing surface 42 of the base portion 34 of the transverse member 32, which bearing surface 42 faces radially outwards, generally in the direction of the top portion 36 of the transverse member 32, and contacts the inside of one of the ring sets 31.
  • a first or rear surface 38 of the two main body surfaces 38, 39 of transverse member 32 that face in mutually opposite circumference directions L, is essentially flat.
  • the other or front main body surface 39 of the transverse member 32 is provided with a so-called rocking edge 18 that forms, in the radial direction H, the transition between an upper part of the front surface 39, extending essentially in parallel with its rear surface 38, and a lower part thereof that is slanted such that it extends towards the rear surface 38.
  • the said upper part of the transverse member 32 is thus provided with an essentially constant dimension between the main body surfaces 38, 39, i.e. as seen in the circumference direction L, which dimension is typically referred to as the thickness of the transverse member 32.
  • the transverse segment 10 is shown to be provided with a projection 40 that protrudes from its front main face 38 thereof and with a corresponding hole 41 that is provided in its rear main face 39.
  • the projection 40 of the trailing transverse segment 32 is at least partially located in the hole 41 of the leading transverse segment 32, such that mutual displacement of these adjacent transverse segments 32 in a plane perpendicular to the circumferential direction of the drive belt 3 is prevented or, at least, limited.
  • the transverse members 32 and the (endless rings of the) ring sets 31 of the drive belt 3 are typically made of steel.
  • maximum running radius R- max at both pulleys 1 , 2 also determines the maximum and minimum speed ratio provided by the transmission, i.e. determine the total ratio coverage of the transmission, at least in combination with a minimum radial position of the drive belt 3 as determined by the diameters of the respective pulley shafts 6; 7.
  • the running radius of the drive belt 3 is defined by the radially outer extent of the ring sets 31 relative to the rotational centre thereof, whereas this parameter is often associated with the rocking edge 18 in the art instead.
  • the trajectory of the drive belt 3 is schematically indicated by the dash-dotted line T3 that tracks the radial outer extent of the ring sets 31 .
  • a clear difference can be observed between the running radius R-in of the drive belt 3 when entering (between the discs 4, 5 of) the output pulley 2 and such running radius R-out when exiting from that output pulley 2. This radially inward spiralling of the drive belt
  • a bending of the shaft 7 is the primary cause of the deformation of the output pulley 2 and has been exaggerated to more clearly illustrate the running radii of the drive belt 3 at entering (R-in) between and at exiting (R-out) from in- between the pulley discs 4, 5.
  • the pulley discs 4, 5 will also bend or flex in the axial direction to a certain extent.
  • the curved pulley trajectory of the drive belt 3 satisfies the above-explained requirement that the radially outer extent of the ring sets 31 remains within the outer circumference or radial dimension RD of the pulley discs 4, 5 of the pulleys 1 , 2.
  • the ring sets 31 is already sufficiently constrained in the axial direction if it is located within the radial dimension RD of the pulley discs 4, 5 for only a part of the said curved pulley trajectory of the drive belt 3. This insight opens up the possibility to increase the said maximum running radius R-max.
  • such maximum running radius R-max is determined not by the running radius of the drive belt 3 at entering R-in between the pulley discs 4, 5, but rather by the running radius thereof at exiting R-out from in-between the pulley discs 4, 5, which latter running radius at exiting R- out should be smaller than the radial dimension RD of the pulleys 1 , 2, in particular of the pulley discs 4, 5 thereof.
  • the ring set 31 extends at least partly beyond a radial dimension of the pulley discs 4, 5 at a point of entry of the drive belt 3 between the pulley discs 4, 5 of such respective pulley 1 , 2 and, simultaneously, is fully contained between, i.e. constrained in the axial direction by the pulley discs 4, 5 at a point of exit of the drive belt 3 from between the pulley discs 4, 5 of such respective pulley 1 , 2.
  • the trajectory of the drive belt 3 is schematically indicated by the dash-dotted line T3 that tracks the radial outer extent of the ring sets 31.
  • the running radius of the drive belt 3 (as defined by the radially outer extent of the ring sets 31 thereof) at entering R-in (between the discs 4, 5 of) the output pulley 2 exceeds the radial dimension RD of the output pulley 2, whereas such running radius at exiting R- out when from that output pulley 2, due to the radially inward spiralling of the drive belt 3 in the said curved pulley trajectory thereof at the output pulley 2 and in accordance with the present disclosure.
  • the output pulley 2 of figure 7 is shown in a cross-section corresponding to that of figure 6 with the elastic deformation thereof being exaggerated to more clearly illustrate the running radii of the drive belt 3 at entering R-in between the pulley discs 4, 5, as well as at exiting R-out from in-between these pulley discs 4, 5 in relation to the radial dimension RD thereof.
  • the radially inward spiralling of the drive belt typically amounts up to 2 millimetres or so, such that according to the present disclosure the ring set 31 can extend beyond the radial dimension RD of the pulley, at the point of entry of the drive belt between the pulley discs thereof, by at most the same amount.
  • the novel transmission that is controlled in accordance with the present disclosure for the maximum running radius R-in at pulley entry of both the input pulley 1 and the output pulley 2 provides a highly significant increase in ratio coverage of almost 6%, namely the ratio coverage of the said typical, conventional transmission amounts to (70 mm/30 mm) 2 , i.e. 5.44, whereas the novel transmission provides a ratio coverage of (70+2 mm/30 mm) 2 , i.e. 5.76.

Landscapes

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

Abstract

La présente invention concerne une transmission à variation continue à gradation accrue, pourvue d'une courroie d'entraînement (3) comprenant un ensemble d'anneaux (31), et de deux poulies (1, 2) comprenant chacune deux joues (4, 5) de poulie à déplacement axial relatif entre lesquelles est maintenu un segment circonférentiel de la courroie d'entraînement (3), et un procédé permettant de commander une telle transmission à variation continue. Lors du fonctionnement de la transmission et au moins au niveau de l'une de ses poulies (1, 2), l'ensemble d'anneaux (31) s'étend au moins partiellement au-delà d'une dimension radiale des joues (4, 5) de poulie au niveau d'un point d'entrée de la courroie d'entraînement (3) entre les joues (4, 5) de chaque poulie (1, 2) respective, est simultanément situé entre les joues (4, 5) de poulie et est contraint dans la direction axiale par celles-ci au niveau d'un point de sortie de la courroie d'entraînement (3) à partir d'une position entre les joues (4, 5) de la poulie respective (1, 2).
PCT/EP2015/025115 2014-12-30 2015-12-29 Transmission à variation continue à gradation accrue et procédé de commande de rapport pour une telle transmission Ceased WO2016107680A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201580071999.1A CN107208759B (zh) 2014-12-30 2015-12-29 具有增加的速度比覆盖范围的无级变速器和用于这种变速器的速度比控制方法
JP2017535356A JP2018505358A (ja) 2014-12-30 2015-12-29 レシオカバレッジが増大した無段変速機およびこのような変速機のためのレシオ制御方法

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL1041130A NL1041130B1 (en) 2014-12-30 2014-12-30 Continuously variable transmission with increased ratio coverage and ratio control method for such transmission.
NL1041130 2014-12-30

Publications (1)

Publication Number Publication Date
WO2016107680A1 true WO2016107680A1 (fr) 2016-07-07

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Family Applications (1)

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PCT/EP2015/025115 Ceased WO2016107680A1 (fr) 2014-12-30 2015-12-29 Transmission à variation continue à gradation accrue et procédé de commande de rapport pour une telle transmission

Country Status (4)

Country Link
JP (1) JP2018505358A (fr)
CN (1) CN107208759B (fr)
NL (1) NL1041130B1 (fr)
WO (1) WO2016107680A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11512763B2 (en) 2019-11-05 2022-11-29 Toyota Jidosha Kabushiki Kaisha Belt-type continuously variable transmission

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1288530A1 (fr) * 2001-09-04 2003-03-05 Van Doorne's Transmissie B.V. Transmission à variation continue efficace à couple élevé
EP1529985A1 (fr) * 2003-11-06 2005-05-11 Robert Bosch Gmbh Transmission à variation continue
WO2006049493A1 (fr) * 2004-11-03 2006-05-11 Robert Bosch Gmbh Transmission avec gaines de poulie convexes et courroie d’entraînement
DE112011105685T5 (de) * 2011-09-28 2014-07-31 Honda Motor Co., Ltd. Stufenloses Getriebe vom Typ mit endlosem Kraftübertragungsriemen

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06272737A (ja) * 1993-03-18 1994-09-27 Nissan Motor Co Ltd 無段変速機用ｖベルト
JP2009074671A (ja) * 2007-09-25 2009-04-09 Jtekt Corp 動力伝達装置および動力伝達チェーン
JP2011069410A (ja) * 2009-09-24 2011-04-07 Jtekt Corp 動力伝達装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1288530A1 (fr) * 2001-09-04 2003-03-05 Van Doorne's Transmissie B.V. Transmission à variation continue efficace à couple élevé
EP1529985A1 (fr) * 2003-11-06 2005-05-11 Robert Bosch Gmbh Transmission à variation continue
WO2006049493A1 (fr) * 2004-11-03 2006-05-11 Robert Bosch Gmbh Transmission avec gaines de poulie convexes et courroie d’entraînement
DE112011105685T5 (de) * 2011-09-28 2014-07-31 Honda Motor Co., Ltd. Stufenloses Getriebe vom Typ mit endlosem Kraftübertragungsriemen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11512763B2 (en) 2019-11-05 2022-11-29 Toyota Jidosha Kabushiki Kaisha Belt-type continuously variable transmission

Also Published As

Publication number Publication date
NL1041130B1 (en) 2016-10-11
CN107208759A (zh) 2017-09-26
CN107208759B (zh) 2020-03-17
JP2018505358A (ja) 2018-02-22

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