WO2000043694A1 - Transmission mecanique a variation continue du rapport de transmission - Google Patents
Transmission mecanique a variation continue du rapport de transmission Download PDFInfo
- Publication number
- WO2000043694A1 WO2000043694A1 PCT/FR2000/000121 FR0000121W WO0043694A1 WO 2000043694 A1 WO2000043694 A1 WO 2000043694A1 FR 0000121 W FR0000121 W FR 0000121W WO 0043694 A1 WO0043694 A1 WO 0043694A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- counterweight
- pivot
- pivots
- mechanical transmission
- axis
- Prior art date
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
- F16H33/00—Gearings based on repeated accumulation and delivery of energy
- F16H33/02—Rotary transmissions with mechanical accumulators, e.g. weights, springs, intermittently-connected flywheels
- F16H33/04—Gearings for conveying rotary motion with variable velocity ratio, in which self-regulation is sought
- F16H33/08—Gearings for conveying rotary motion with variable velocity ratio, in which self-regulation is sought based essentially on inertia
Definitions
- the present invention relates to an automatic mechanical transmission device with continuous variation of the transmission ratio from an infinite ratio to the 1/1 ratio comprising a driving shaft and a driven shaft of coincident axes, and a driving plate comprising, at equal distance of the leading tree, articulation axes on which weights are articulated.
- Such an apparatus falls into the category where any difference in rotational speed between the driven shaft and the driving shaft causes an angular movement of the weights around said articulation axes, these angular movements causing a radial displacement of the centers of gravity of said weights with respect to the driving shaft therefore a variation in the kinetic energy of said weights and, consequently, an increase in the torque transmitted to the driven shaft.
- a diameter AA ′ passing through the axis common to the driving and driven shafts and through the axis of the eccentric circular track determines on this track two half-circumferences.
- a half circumference AA ' the center of gravity of each flyweight moves closer to the central axis common to the driving and driven shafts and therefore undergoes deceleration, which causes a reduction in the kinetic energy of the flyweight while in the other half circumference A 'A, the center of gravity of each counterweight moves away from the common axis and undergoes an acceleration resulting in an increase in the kinetic energy of the counterweight.
- Accelerations and decelerations are accompanied by angular deflections of the counterweight and consequently modifications of the angular position of the counterweight relative to the radius joining its axis of articulation to the central axis common to the driving and driven shafts. Given these angular positions, the inertia of each counterweight produces a resultant force directed towards the interior of the device during acceleration, while during deceleration, the resulting force produced by the inertia of each counterweight is directed outwards.
- this automatic mechanical transmission device with continuous variation of the transmission ratio from an infinite ratio to the 1/1 ratio, comprising a driving shaft and a driven shaft of coincident axes, a driving plate integral with the driving shaft and carrying, uniformly distributed angularly on a circle centered on the driving shaft, first pivots on which the flyweights are articulated, so that any difference in rotational speed between the driven shaft and the driving shaft causes an angular movement of the weights around their pivots, causing a radial displacement of their centers of gravity with respect to the driving shaft, therefore a variation of the kinetic energy of the weights and consequently an increase in the torque transmitted to the driven shaft, control rods of the same length, respectively fixed on the one hand, at one of their ends, on second pivots secured to the angular deflections of the counterweights, and on the other hand, at their other end, on third pivots articulated around the crankpin of a central crankshaft constituting
- the third pivots are carried by a driven hub, mounted for rotation around the crankpin of the central crankshaft constituting the driven shaft, the third pivots being regularly distributed at equal distance from the axis of the crankpin being parallel to each other and parallel to this axis.
- the control rods are articulated on pivots carried by a hub surrounding the crankpin, and not directly articulated on the crankpin itself, constitutes a particular embodiment of the invention.
- the double articulation device connecting the front part of each counterweight to a first pivot, is located near the inner surface of the counterweight and the articulation of each control rod on the counterweight is located on the rear part near the outer surface of the counterweight.
- a second plate parallel to the driving plate, centered on the central shaft of the crankshaft, is intended to hold the other ends of the first pivots, and it thus constitutes, with the first driving plate and the first pivots, a very rigid and resistant assembly intended to undergo the centrifugal forces applied to the flyweights, which can take on significant values at high rotational speeds.
- the apparatus according to the invention has a number of advantages. Firstly, it provides a wide range of continuous variation providing automatic adaptation of the speed and torque ratios to the best operating conditions.
- the transmission ratio varies from zero output speed (or infinite ratio) to 1/1 ratio, avoiding any use of any clutch or coupling device.
- the torques produced are much greater at start-up than on the 1/1 ratio, and they decrease regularly between these two limits. It is understood that these torques increase as a function of the square of the engine speeds, of the masses used, of the radii of the circular trajectories of these masses, of the eccentricity of the crankpins relative to the central axis, and of the frequencies of the angular movements of the weights on their pivots.
- the double articulation device provided at the front of each counterweight makes it possible to absorb any vibrations and to regularize the torques transmitted to the driven shaft even at high rotational speeds.
- the device according to the invention offers great ease of manufacture, very small footprint, high mechanical efficiency reaching almost 100% on the 1/1 ratio, for a particularly reduced cost price.
- the device can be fixed directly at the end of the crankshaft of thermal engines, replacing the usual flywheel, and it thus allows a considerable weight saving compared to the conventional device comprising a clutch and a gearbox.
- FIG. 1 is a cross-sectional view of the device taken along the line I-I of Figure 2
- - Figure 2 is an axial sectional view of one device.
- FIG. 3 represents a variant of a double articulation device arranged on a counterweight
- FIG. 4 is a schematic view showing sixteen successive positions, in equal time fractions, of the different pivots, during a rotation.
- the apparatus shown in FIGS. 1 and 2 comprises several weights 1, generally four in number, of generally elongated and curved shape, having a convex outer surface la and a concave inner surface lb_, each connected by a double articulation device to a first pivot 2 disposed at the front and near the inner surface lb of the counterweight 1.
- the first pivot 2 is fixed perpendicularly, by its two ends, between a first driving plate 3 and a second parallel plate 4 and coaxial with the first driving plate 3, itself driven in rotation by a driving shaft 5 of central axis O
- the first pivots 2 are uniformly distributed angularly on a circle centered on the central axis O.
- crankshaft 8 constituting the driven shaft 6 , of central axis O, coaxial with the driving shaft 5.
- a crank pin 7, of axis 0_ ⁇ _, of the crankshaft 8 is rotatably mounted a hub 9 crossed by third pivots 10 regularly repa rtis on a circumference surrounding the axis 0_ ⁇ _ of the crank pin 7, parallel to each other and to the axis p_ ⁇ _ of the crank pin 7.
- the direction of rotation of the device is the clockwise direction, as indicated on the Figures 1 and 4.
- Each flyweight 1 is also associated with a control rod 14, which is articulated, at each of its ends, on the one hand on a second pivot 13 disposed at one rear end and near the outer surface 11a. of the counterweight 1, and on the other hand on a third pivot 10 mounted on the hub 9 surrounding the crankpin 7 of the crankshaft 8.
- Each connecting rod 14 consists of two bars, the end portions of which are fixed respectively on either side the ends of pivots 10 and 13.
- each counterweight 1 causes a resultant force transmitted to the control rod 14 which in return exerts a push towards the right, that is to say in the positive direction , on the third pivot 10 and therefore on the hub 9 and on the crankpin 7, the positive direction being that of the hands of a watch, as shown in FIGS. 1 and 4.
- the deceleration zone AA ' the resulting forces due to the kinetic energy of the weights 1 exert a tensile force on the control rods 14 which is transmitted on the hub 9 and on the crank pin 7 to the right, that is to say again in the positive sense.
- Schematic figure 4 represents sixteen positions successive, at equal fractions of time, of the different pivots, and allows the need to position the successive centers of gravity of the flyweights 1 during a rotation of the drive plate 3 around the crankpin 7 in the case of a simple rigid articulation between the counterweight 1 and the driving pivot 2.
- the measurements taken in this diagrammatic figure 4 show that in this case the greater circumferential speeds of the second pivots 13 actually occur when they pass in the vicinity of a position A "situated well before the position A, and that decelerations, starting from A ", produce counter-torques and very detrimental jolts between A" and A.
- the double articulation device forming the subject of the invention comprises a circular cam 11 with center 0 2 rotatably mounted in a bore provided in the front part of the counterweight 1, that cam 11 being itself same rotationally mounted around the first driving pivot 2 whose axis is eccentric relative to the center of the cam 0_ 2 and close to the inner surface lb of the counterweight 1.
- This device allows, thanks to the tilting of the cam 11 under the action of the driving torques, a limited circumferential movement of the counterweight 1 relative to the first pivot 2, of deferring the accelerations and the maximum speeds of the zone A "towards the position A, and of starting the decelerations after the passage of the said position A.
- FIG. 1 shows that, of the four connecting rods 14 represented, three produce positive effects, and only one produces negative effects.
- Schematic figure 4 also shows that out of the sixteen successive positions represented, ten connecting rods produce positive effects, and six others only negative effects.
- the invention provides, according to the embodiment shown in FIG. 2, to have a second set of weights articulated on the same first ones pivots 2 as the weights 1 of the first set, control rods 14 ', pivots 10' and 13 'cooperating with a second hub 9' rotatably mounted around a second crank pin 7 'diametrically opposite the first crank pin 7 with respect to to the central axis O of the crankshaft 8. All these elements of the second set are exactly similar to the homologous elements of the first set.
- the device can be enclosed either in a fixed and waterproof casing, or in a rotary and watertight casing, obtained by extending and connecting by their outer edges the two leading plates 3 and 4
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
- Friction Gearing (AREA)
- Flexible Shafts (AREA)
- Lock And Its Accessories (AREA)
- Golf Clubs (AREA)
- Transmissions By Endless Flexible Members (AREA)
- Endoscopes (AREA)
- Ultra Sonic Daignosis Equipment (AREA)
- Analysing Materials By The Use Of Radiation (AREA)
- Reduction Or Emphasis Of Bandwidth Of Signals (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT00900623T ATE225476T1 (de) | 1999-01-20 | 2000-01-20 | Kontinuierlich verstellbares, mechanisches getriebe |
DE60000534T DE60000534T2 (de) | 1999-01-20 | 2000-01-20 | Kontinuierlich verstellbares, mechanisches getriebe |
EP00900623A EP1147329B1 (fr) | 1999-01-20 | 2000-01-20 | Transmission mecanique a variation continue du rapport de transmission |
AU30566/00A AU3056600A (en) | 1999-01-20 | 2000-01-20 | Mechanical transmission with continuously varying transmission ratio |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9900569A FR2788574B1 (fr) | 1999-01-20 | 1999-01-20 | Transmission mecanique a variation continue du rapport de transmission |
FR99/00569 | 1999-01-20 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000043694A1 true WO2000043694A1 (fr) | 2000-07-27 |
Family
ID=9541030
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2000/000121 WO2000043694A1 (fr) | 1999-01-20 | 2000-01-20 | Transmission mecanique a variation continue du rapport de transmission |
Country Status (8)
Country | Link |
---|---|
EP (1) | EP1147329B1 (fr) |
AT (1) | ATE225476T1 (fr) |
AU (1) | AU3056600A (fr) |
DE (1) | DE60000534T2 (fr) |
ES (1) | ES2188500T3 (fr) |
FR (1) | FR2788574B1 (fr) |
PT (1) | PT1147329E (fr) |
WO (1) | WO2000043694A1 (fr) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2945601A1 (fr) * | 2009-05-14 | 2010-11-19 | Louis Guichard | Appareil de transmission mecanique a variation continue et automatique du rapport de transmission |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE343984C (de) * | 1919-10-22 | 1921-11-12 | Theodore Lafitte | Selbsttaetige Kupplung |
US1767311A (en) * | 1927-03-17 | 1930-06-24 | Earl W Rohrbacher | Variable transmission or torque converter |
US4179943A (en) * | 1976-09-30 | 1979-12-25 | Vittorio Gamba | Mechanical torque converter |
EP0399888A1 (fr) | 1989-05-24 | 1990-11-28 | Louis Guichard | Appareil de transmission mécanique automatique à variation continue du rapport de transmission depuis un rapport infini jusqu'à un rapport inférieur à 1/1 |
WO1997029304A1 (fr) * | 1996-02-07 | 1997-08-14 | Louis Guichard | Transmission automatique a variation continue depuis un rapport infini jusqu'au rapport 1/1 |
-
1999
- 1999-01-20 FR FR9900569A patent/FR2788574B1/fr not_active Expired - Fee Related
-
2000
- 2000-01-20 WO PCT/FR2000/000121 patent/WO2000043694A1/fr active IP Right Grant
- 2000-01-20 AT AT00900623T patent/ATE225476T1/de not_active IP Right Cessation
- 2000-01-20 DE DE60000534T patent/DE60000534T2/de not_active Expired - Fee Related
- 2000-01-20 PT PT00900623T patent/PT1147329E/pt unknown
- 2000-01-20 ES ES00900623T patent/ES2188500T3/es not_active Expired - Lifetime
- 2000-01-20 EP EP00900623A patent/EP1147329B1/fr not_active Expired - Lifetime
- 2000-01-20 AU AU30566/00A patent/AU3056600A/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE343984C (de) * | 1919-10-22 | 1921-11-12 | Theodore Lafitte | Selbsttaetige Kupplung |
US1767311A (en) * | 1927-03-17 | 1930-06-24 | Earl W Rohrbacher | Variable transmission or torque converter |
US4179943A (en) * | 1976-09-30 | 1979-12-25 | Vittorio Gamba | Mechanical torque converter |
EP0399888A1 (fr) | 1989-05-24 | 1990-11-28 | Louis Guichard | Appareil de transmission mécanique automatique à variation continue du rapport de transmission depuis un rapport infini jusqu'à un rapport inférieur à 1/1 |
WO1997029304A1 (fr) * | 1996-02-07 | 1997-08-14 | Louis Guichard | Transmission automatique a variation continue depuis un rapport infini jusqu'au rapport 1/1 |
Also Published As
Publication number | Publication date |
---|---|
FR2788574B1 (fr) | 2001-03-30 |
EP1147329B1 (fr) | 2002-10-02 |
PT1147329E (pt) | 2003-02-28 |
ATE225476T1 (de) | 2002-10-15 |
ES2188500T3 (es) | 2003-07-01 |
DE60000534D1 (de) | 2002-11-07 |
FR2788574A1 (fr) | 2000-07-21 |
AU3056600A (en) | 2000-08-07 |
DE60000534T2 (de) | 2003-06-18 |
EP1147329A1 (fr) | 2001-10-24 |
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