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WO1998032992A1 - Convertisseur de couple mecanique - Google Patents

Convertisseur de couple mecanique Download PDF

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Publication number
WO1998032992A1
WO1998032992A1 PCT/GB1998/000178 GB9800178W WO9832992A1 WO 1998032992 A1 WO1998032992 A1 WO 1998032992A1 GB 9800178 W GB9800178 W GB 9800178W WO 9832992 A1 WO9832992 A1 WO 9832992A1
Authority
WO
WIPO (PCT)
Prior art keywords
gearwheel
rotatable housing
shaft
torque
axis
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/GB1998/000178
Other languages
English (en)
Inventor
Arnold Derek Child
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
Application filed by Individual filed Critical Individual
Priority to EP98900932A priority Critical patent/EP0961888A1/fr
Publication of WO1998032992A1 publication Critical patent/WO1998032992A1/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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/74—Complexes, not using actuatable speed-changing or regulating members, e.g. with gear ratio determined by free play of frictional or other forces

Definitions

  • This invention relates to mechanical torque converters and more especially to a stepless variable ratio mechanical torque converter in which the input to output speed ratio and therefore torque multiplication is infinitely variable within predetermined limits.
  • Conventionally continuously variable ratio mechanical transmission systems rely on the pressure acting between untoothed rotating components to transmit torque and on variation of the radial distance at which the pressure acts on rotating components to vary the input to output speed ratio.
  • a control system is required to adjust the relative position of the rotating components.
  • Torque converters in accordance with this invention are load sensitive and the input to output speed ratio adjusts automatically in response to variation of the relative values of input torque and output load. No control system is necessary and torque is transmitted only via toothed gearing.
  • the proposed torque converter consists of a torque multiplying gear assembly and a torque splitting gear assembly which transmits part of the multiplied torque to the output shaft and returns the remainder of the multiplied torque to the rotatable housing of the torque multiplying gear assembly.
  • Contained within the rotatable housing are components arranged to modify the effect of reactive force which occurs during torque multiplication and thereby prevent reverse rotation of the rotatable housing which would normally occur in this arrangement.
  • a torque converter comprising a fixed structure which supports within coaxial bearings an output shaft and the carrier shafts of a rotatable housing in turn supporting within coaxial bearings carrier shafts of an input gearwheel and an annular gearwheel the axes of rotation being coincident with the axis of rotation of the rotatable housing.
  • One carrier shaft of the rotatable housing forms the carrier shaft of a first bevel gearwheel and the output shaft forms the carrier shaft of a second bevel gearwheel.
  • Intermediate bevel gearwheels are adapted to mesh with the first and second bevel gearwheels to form a differential unit and the carrier shafts of the intermediate bevel gearwheels form a cross member integral with the carrier shaft of the annular gearwheel with axis of rotation coincident with the axis of rotation of the rotatable housing.
  • An intermediate shaft with axis of rotation not coincident with the axis rotation of the rotatable housing is the carrier shaft of an annular gearwheel adapted to mesh with the input gearwheel.
  • the said intermediate shaft is also the carrier shaft of a gearwheel adapted to mesh with the annular gearwheel with axis of rotation coincident with the axis of rotation of the rotatable housing.
  • a projection within the rotatable housing is arranged to contact a roller bearing in turn contacting the longer arm of a lever with pivot not coincident with the axes of rotation of the rotatable housing or intermediate shaft.
  • the pivot of the lever is preferably the axis of rotation of a system consisting of a convex face or faces which are an integral part of the lever and are supported on roller bearings held within a concave track or tracks of a pivot support positioned on roller bearings within the rotatable housing and with an axis of rotation coincident with the axis of rotation of the rotatable housing.
  • the intermediate shaft is located within the bearing surface of a shaft support which contacts the shorter arm of the said lever along two or more individual lines or continuously between two individual lines preferably parallel to the rotational axis of the intermediate shaft.
  • a ball bearing or bearings are located between the shaft support and the rotatable housing and a roller bearing or bearings are located between the shaft support and the pivot support.
  • the shaft support and the shorter arm of the lever incorporate guides to maintain the relative positions of these components longitudinally and transversely.
  • the pivot support and the rotatable housing incorporate guides to maintain the relative positions of these components longitudinally.
  • FIGURE 1 is a side view depicting the disposition of the gearwheels and carrier shafts of the torque multiplying and torque splitting gear assemblies of the proposed torque converter.
  • FIGURE 2 is a cross view of figure 1 depicting the supporting components within the rotatable housing of the torque multiplying gear assembly.
  • FIGURE 3 is a cross view of two sections of figure 1 each section depicting the relative positions of a gearwheel meshed with the complimentary teeth of an annular gearwheel.
  • FIGURE 4 is an isometric view in simplified form of the assemblies depicted in figure 1 and includes linear representation of torque values.
  • FIGURE 5 is an analysis of the forces acting throughout the torque converter during the two extreme operating conditions.
  • FIGURE 6 is an isometric view in simplified form of two coupled torque multiplying gear assemblies similar to that depicted in figure 1 forming a single unit connected to a torque splitting gear assembly similar to that depicted in figure 1.
  • FIGURE 7 is an analysis of the performance throughout the operating range of a dual unit as depicted in figure 6 and including two sets of components similar to that depicted in figure 2.
  • the carrier shafts 6 and 7 of rotatable housing 5 are supported within coaxial bearings 2 and 3 of fixed structure 1.
  • the rotatable housing 5 supports within bearing 11 which is coaxial with bearing 2 input shaft 14 which is the carrier shaft of gearwheel 15.
  • the rotatable housing 5 also supports within bearing 12 which is coaxial with bearing 3 shaft 20 which is the carrier shaft of annular gearwheel 19.
  • Carrier shaft 7 of rotatable housing 5 forms the carrier shaft of bevel gearwheel 8 and fixed structure 1 supports within bearing 4 which is coaxial with bearing 3 output shaft 10 which is the carrier shaft of bevel gearwheel 9 which has the same number of teeth as bevel gearwheel 8.
  • Shaft 20 is supported by a second bearing 13 within output shaft 10.
  • the teeth of bevel gearwheels 8 and 9 mesh with complimentary teeth of bevel gearwheels 25 and 26 which are supported by bearings 23 and 24 of carrier shafts 21 and 22 which form an integral cross member of shaft 20.
  • Shaft 17 which is not coaxial with the other shafts is the carrier shaft of annular gearwheel 16 and gearwheel 18.
  • a projection on the inside of rotatable housing 5 contacts a roller bearing 34 which in turn contacts the longer arm of a lever 33 which is supported by convex projections 32 formed each side of lever 33.
  • the projections 32 are supported via roller bearings resting on the concave tracks.31 of pivot support 29 which is supported via roller bearings on an inner surface of rotatable housing 5.
  • Shaft support 28 which supports shaft 17 within bearing 27 includes lobes which contact the shorter arm of lever 33 at two points.
  • a ball bearing 35 preferably located by uncompressed springs is positioned between shaft support 28 and rotatable housing 5 and a roller bearing 30 located by uncompressed springs is positioned between shaft support 28 and pivot support 29.
  • a pilot pin 36 is positioned between the shaft support 28 and the shorter arm of lever 33 and a guide 37 is positioned between the pivot support 29 and rotatable housing 5.
  • a spring 38 under compression is positioned between shaft support 28 and rotatable housing 5.
  • the roller bearings supporting pivot support 29 and lever projections 32 would include means (not shown) to maintain the relative position of the roller bearings.
  • the force F acting on annular gearwheel 16 about axis c will generate a torque F32 (force F acting at 32mm from axis c) in shaft 17 which will be transmitted to gearwheel 18.
  • the force F acting between the teeth of gearwheel 18 and annular gearwheel 19 at 32mm from the rotational axis c of gearwheel 18 will generate a reactive force F in a parallel but opposite direction via axis c at 16mm from axis a and a torque F48 (force F acting at 48mm from axis a) in annular gearwheel 19.
  • Torque transmitted from annular gearwheel 19 via carrier shaft 21 to bevel gearwheel 25 will be split equally by the differential unit, F24 units torque via bevel gearwheel 9 to output shaft 10 and F24 units torque via bevel gearwheel 8 to rotatable housing 5.
  • the torque F32 force 2F acting on shaft 17 via axis c at 16mm from axis a
  • that torque F24 returned to rotatable housing 5 which if released would rotate in a reverse direction to input shaft 14 which would commence to rotate simultaneously.
  • figure 5 (A) of the drawings In accordance with the previous analysis a load is applied to the output shaft and a torque F16 applied to the input shaft but in this analysis the rotatable housing 5 is free to rotate.
  • Reverse rotation of the unrestrained rotatable housing 5 can be prevented if shaft support 28 of shaft 17 is arranged to contact the shorter arm of lever 33 via two lobes at 24mm and 12mm from axis b.
  • the reactive force 2F acting on shaft support 28 via axis c is constrained by roller bearing 30 to act on the shorter arm of lever 33 in the direction of a chord of the circle described by axis a as centre.
  • the force 0.5F (the force element of F24 units torque) acting on rotatable housing 5 at 48mm from axis a and transmitted via roller bearing 34 to act on the longer arm of lever 33 at 72mm from axis b will generate a torque F36 which will act on the lever 33 about axis b.
  • the reactive force 2F acting via axis c will initially act via the first lobe of shaft support 28 which is 24mm from axis b but movement of the shorter arm of lever 33 about axis b cannot occur because parallel movement of the second lobe would separate the first lobe from its contact point.
  • This constraint will cause the reactive force 2F acting via axis c to be divided equally between the two lobes of shaft support 28 to act on the shorter arm of lever 33 about axis b and the two component torques generated, F12 (force F acting at 12mm from axis b) and F 24 (force F acting at 24mm from axis b) produce a total torque F36 about axis b which is equal to the opposing torque generated via the longer arm of lever 33.
  • Axis c is located 24mm from the contact point of the first lobe of shaft support 28 and the force F which via lever 33 opposes the force F acting via the second lobe of shaft support 28 which is 12mm from the first lobe will generate a torque F12 about the first lobe and a resultant force 0.5F which will act on shaft support 28 via axis c in the direction of a radius of the circle described by axis a as centre.
  • the load acting on the transmission will resist relative rotation of the gearwheels and cause the force F acting between gearwheel 15 and annular gearwheel 16 to attempt to rotate the whole mechanism as a unit and if the load acting on output shaft 10 is reduced the F16 units torque (force F acting 16mm from axis a) plus the torque F24 acting on rotatable housing 5 about axis a will produce a total of F40 units of torque which is sufficient to overcome the reactive force 2F acting 16mm from axis a and rotation of rotatable housing 5 will commence, reducing relative rotation of the gearwheels and thereby reducing the input to output speed ratio and torque multiplication through the system.
  • the preferred embodiment of the invention as described would utilise a bevel gearwheel differential to give an equal torque split but an alternative embodiment could utilise a bevel gearwheel differential to give an unequal torque split.
  • the bevel gearwheel differential could be replaced by an alternative differential gearwheel arrangement.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
  • Gear Transmission (AREA)

Abstract

L'invention concerne un convertisseur de couple ne nécessitant pas une composante réactive fixe, le couple de rappel étant limité par une force exercée sur le bras court d'un levier (33) qui pivote autour d'un axe adjacent à l'axe d'entrée-sortie sur un support pivot séparé (29) à l'intérieur d'un boîtier tournant (5). La force est transmise du boîtier tournant (5) au bras long du levier (33) et la vitesse de rotation du boîtier tournant (5) est tributaire des valeurs relatives du couple d'entrée et de la charge de sortie. La variation de la vitesse de rotation du boîtier tournant (5) par rapport à la vitesse de rotation de l'arbre d'entrée (14) modifie le rapport de transmission entrée-sortie. Il est ainsi possible d'obtenir une variation infinie du rapport de transmission entrée-sortie dans des limites prédéterminées.
PCT/GB1998/000178 1997-01-27 1998-01-21 Convertisseur de couple mecanique Ceased WO1998032992A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP98900932A EP0961888A1 (fr) 1997-01-27 1998-01-21 Convertisseur de couple mecanique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9701613.3 1997-01-27
GB9701613A GB2321505B (en) 1997-01-27 1997-01-27 Mechanical torque converter

Publications (1)

Publication Number Publication Date
WO1998032992A1 true WO1998032992A1 (fr) 1998-07-30

Family

ID=10806627

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1998/000178 Ceased WO1998032992A1 (fr) 1997-01-27 1998-01-21 Convertisseur de couple mecanique

Country Status (3)

Country Link
EP (1) EP0961888A1 (fr)
GB (1) GB2321505B (fr)
WO (1) WO1998032992A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB453013A (en) * 1934-07-16 1936-09-03 Cesare Fontana Automatically variable gear device
GB478705A (en) * 1936-07-21 1938-01-21 John Herbert Cole Improvements in variable speed gears
US2595628A (en) * 1945-02-17 1952-05-06 Gerhard H J Baule Transmission mechanism
US2667089A (en) * 1950-07-08 1954-01-26 Charles E Gregory Direct drive transmission with automatically load responsive range of low gear ratios
US3439561A (en) * 1968-04-12 1969-04-22 Martin Preston Mechanical torque converter
JPS5969556A (ja) * 1982-10-14 1984-04-19 Satoru Inoue 自動変速装置

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1286279A (en) * 1969-11-21 1972-08-23 Edward Hartley Clay Improvements in and relating to gear boxes
GB8604461D0 (en) * 1986-02-22 1986-03-26 Stidworthy F M Self-adjusting transmissions
US5059163A (en) * 1990-10-15 1991-10-22 Von Greyerz John W Trans-planetary mechanical torque impeller

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB453013A (en) * 1934-07-16 1936-09-03 Cesare Fontana Automatically variable gear device
GB478705A (en) * 1936-07-21 1938-01-21 John Herbert Cole Improvements in variable speed gears
US2595628A (en) * 1945-02-17 1952-05-06 Gerhard H J Baule Transmission mechanism
US2667089A (en) * 1950-07-08 1954-01-26 Charles E Gregory Direct drive transmission with automatically load responsive range of low gear ratios
US3439561A (en) * 1968-04-12 1969-04-22 Martin Preston Mechanical torque converter
JPS5969556A (ja) * 1982-10-14 1984-04-19 Satoru Inoue 自動変速装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 008, no. 177 (M - 317) 15 August 1984 (1984-08-15) *

Also Published As

Publication number Publication date
GB2321505B (en) 2001-04-25
GB9701613D0 (en) 1997-03-19
EP0961888A1 (fr) 1999-12-08
GB2321505A (en) 1998-07-29

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