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WO1996001960A1 - Mecanisme d'entrainement - Google Patents

Mecanisme d'entrainement Download PDF

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Publication number
WO1996001960A1
WO1996001960A1 PCT/AU1995/000414 AU9500414W WO9601960A1 WO 1996001960 A1 WO1996001960 A1 WO 1996001960A1 AU 9500414 W AU9500414 W AU 9500414W WO 9601960 A1 WO9601960 A1 WO 9601960A1
Authority
WO
WIPO (PCT)
Prior art keywords
axis
drive
radial
follower
stroke
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/AU1995/000414
Other languages
English (en)
Inventor
Glenn Alexander Thompson
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.)
PROSSER-FENN JAMES EDWARD
Original Assignee
PROSSER-FENN JAMES EDWARD
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
Priority claimed from AUPM6698A external-priority patent/AUPM669894A0/en
Priority claimed from AUPM6924A external-priority patent/AUPM692494A0/en
Application filed by PROSSER-FENN JAMES EDWARD filed Critical PROSSER-FENN JAMES EDWARD
Priority to AU28757/95A priority Critical patent/AU2875795A/en
Publication of WO1996001960A1 publication Critical patent/WO1996001960A1/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
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
    • 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
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/12—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for conveying rotary motion
    • F16H21/14—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for conveying rotary motion by means of cranks, eccentrics, or like members fixed to one rotary member and guided along tracks on the other

Definitions

  • This invention relates to a drive mechanism.
  • Drive mechanisms for transmission of torque from a drive shaft to a driven shaft are known.
  • One such mechanism employs a number of sets of gears, the gears of each set being sized to intermesh directly at peripheral edges or via an interconnecting chain.
  • the gears are sized to provide predetermined speed ratios and constant torque to the driven shaft on application of a predetermined torque to the drive shaft. Different speed ratio and torque requirements are accommodated by changing gears.
  • the method of changing gears is relatively complicated and requires synchronisation of gears or use of a complex clutch system.
  • the present invention seeks to provide a simpler mechanism which allows for varying torque transmission and speed ratios between a drive member, such as a drive shaft, and a driven member, such as a cog.
  • a drive mechanism comprising: a drive member rotatable about a first axis; a driven member rotatable about a second axis; and a linkage interconnecting the members such that rotation of the drive member results in rotation of the driven member, wherein the linkage is fixed to the drive member for rotation about the first axis and is coupled to the driven member via a guide means which allows for movement of the linkage along a predetermined path relative to the second axis, and wherein the members are adapted to be positioned such that the first and second axis are substantially parallel and spaced apart whereby the linkage rotates eccentrically about the second axis upon rotation of the drive member.
  • the drive member is moveable relative to the driven member so that the orientation of the first and second axis can be varied, whilst maintaining a substantially parallel relationship.
  • the guide means includes a substantially radially extending slot and the linkage includes a follower which is received in the slot.
  • the slot may be formed with curved or sinusoidal portions, as required.
  • the follower is adapted to be located at different radial positions relative to the first axis.
  • the drive member is mounted to revolve about the second axis.
  • the drive member is mounted in a journal, offset from a rotational axis of the journal and the journal is mounted coaxially with respect to the driven member.
  • journal is mounted in a sleeve assembly which is keyed to the driven member.
  • the eccentric motion of the linkage results in the follower being spaced from the second axis by varying distances during revolution of the driven member and this accordingly varies the torque transmitted to the driven member for a given input drive force.
  • the spacing between the first and second axis can also be varied according to torque requirements so that, for example, torque can be maximised for a particular range of revolution of the drive member which corresponds with a power stroke of a drive means coupled to the drive member.
  • the mechanism can be arranged such that the power stroke occurs when the follower is closest to the second axis, thereby providing for a maximum speed ratio between the two members.
  • the variation in the speed ratio can be enhanced further by altering the radius of rotation of the follower relative to the first axis.
  • a free wheel assembly may perhaps also be included in the mechanism so that the lower speed ratio for the remainder of the revolution does not adversely affect the output speed of the driven member.
  • Figure 1 is an exploded partial perspective view of the mechanism in accordance with the present invention
  • Figure 2 is an exploded side view of a mechanism in accordance with another aspect of the present invention.
  • Figure 3 is a diagrammatic end view of the mechanism of Figure 1 viewed along the line 3-3, shown in Figure 2;
  • Figure 4 is an end view representing the mechanism in a first condition
  • Figure 5 is an end view similar to that shown in Figure 4, representing the mechanism in a second condition
  • Figure 6 is an end view of the mechanism, similar to that shown in Figure 3 representing the mechanism in a third condition;
  • Figure 7 is an end view of the mechanism, similar to that shown in figure 3 representing the mechanism in a fourth condition;
  • Figure 8 is an end view of the mechanism, similar to that shown in figure 3 representing the mechanism in a fifth condition;
  • Figure 9 is an end view of the mechanism, similar to that shown in figure 3 representing the mechanism in a sixth condition;
  • Figure 10 is an end view of the mechanism of Figure 1 , including a curved guide channel;
  • Figure 1 1 is a view similar to that shown in Figure 9, showing the mechanism in a further condition; and Figure 12 is an exploded side view of a modified mechanism, in accordance with the present invention;
  • a drive mechanism 1 is shown in Figure 1 as comprising a drive member 2, a driven member 3 and linkage 4 in the form of a follower 5 which is received in a guide slot 6 of the member 3 to thereby interconnect the drive and driven members 2, 3.
  • the drive member 2 has an axis of rotation 7 which is arranged in a substantially parallel spaced apart manner with respect to an axis of rotation 8 of the driven member 3.
  • a driving force is applied to the drive member 2 so that the follower 5 executes circular motion about the axis 7 and simultaneously causes the member 3 to rotate as a result of the interconnection via linkage 4.
  • the path of rotation travelled by the follower 5 is shown by phantom lines 5a.
  • the path of rotation of the follower is eccentric with respect to the axis 8.
  • the follower 5 will be forced to travel along the slot 6 during rotation and, accordingly, the distance between the follower and the axis will vary during revolution of the member 3. The variation in the distance will result in corresponding variation in the torque applied to the driven member 3 and the speed ratio between the members, for a constant predetermined torque applied to the drive member 2.
  • particular torque conditions can be provided by suitable orientation of member 2 relative to member 3, as required.
  • the members may be arranged such that the greatest distance between the follower and the axis 8 is provided simultaneously with a power stroke of a drive means (not shown) which provides the drive force to member 2. whereby to maximise torque transfer.
  • the mechanism can be arranged such that the power stroke occurs when the follower is closest to the second axis, thereby providing for a maximum speed ratio between the two members.
  • the variation in the speed ratio can be enhanced further by altering the radius of rotation of the follower relative to the first axis.
  • a free wheel assembly may perhaps also be included in the mechanism so that the lower speed ratio for the remainder of the revolution does not adversely affect the output speed of the driven member.
  • FIG. 1 illustrates an arrangement whereby the drive member is in the form of a shaft 9 and the driven member is in the form of a wheel 10 which transfers its turning motion via a belt 1 1 arranged around the periphery thereof.
  • both members 2 and 3 can be in the form of gears or the driven member 3 may be connected directly to a driven shaft (not shown).
  • Other embodiments of the invention are shown in Figures 2 and 12 and more detailed description of additional features and advantages of the invention are described below with reference to these embodiments.
  • the embodiment of the mechanism 20 shown in Figure 2 includes parts providing a similar function to parts described with reference to Figure 1 and, where appropriate, these are indicated by the same reference number.
  • the mechanism 20 includes a drive member 2 in the form of shaft 21 and a driven member 3 in the form of disc 22.
  • the shaft 21 has a linkage 4 secured to one end 23 thereof.
  • the linkage includes a radially extending arm 24 and a follower 5 coupled to the end 25 thereof.
  • the follower 5 is received in slot 6 to interconnect the members 2 and 3 for rotation in sympathy.
  • the mechanism also includes a journal 26 housed in a sleeve 27 which extends concentrically from the disc 22.
  • the shaft 21 is located in a correspondingly shaped lengthwise recess 28 formed in the journal.
  • the journal 26, when mounted in the sleeve 27, is arranged coaxially with respect to axis 8 and is adapted to rotate within the sleeve 27 so that the shaft 21 can be revolved about the axis 8 whilst the axes 7 and 8 remain in substantially parallel spaced relation.
  • the journal 26 also includes attachment means, such as lug 29, for coupling to a suitable device for effecting rotational movement of the journal 26 within the sleeve 27, although the journal is also adapted to be fixed in position, when required.
  • Figure 3 represents, for the purpose of illustration, only the outer perimeter of the disc 22 when viewed in a direction indicated in Figure 2 by the line 3-3.
  • moving radial arm 24 through the arc zero degrees to 180 degrees will cause the disc 22 to rotate through greater than 180 degrees of arc. If radial arm 24 is then moved through the arc 180 degrees to 360 degrees the disc 22 will be caused to rotate through the remaining portion of 360 degrees which is less than 180 degrees. If then the journal 26 is caused to rotate such that the axis 7 of shaft 21 is on the 90 degree radial then it can be seen that moving radial arm 24 through the arc zero degrees to 180 degrees will cause disc 22 to rotate through less than 180 degrees of arc and the subsequent movement of radial arm 24 through the remaining 180 degrees of arc will cause the disc 22 to move through its remaining portion of 360 degrees of arc which is greater that 180 degrees.
  • One non limiting practical application of the invention is to provide between design or configuration extremes a continuous range of drive ratios on, for example a bicycle.
  • one assembly as described above would be mounted on the bicycle in such a manner that one radial arm 24 would occupy the same position as a normal pedal crank and a second assembly would be mounted so that the radial arm 24 of a second assembly would occupy the same position as a second pedal crank.
  • Pedals would be attached to the radial arms 24 and the two discs 22 and sleeves 27 connected so as to rotate in unison. Teeth would be cut into the circumference of disc so as to provide for chain drive.
  • a lever or connecting rod or cable could be provided so as to provide for rotation of each of the journals 26 in such a manner that they both maintain similar relationship to each other such that each shaft 21 is coaxial.
  • shaft 21 could be an extension of or driven by the crankshaft of a single cylinder internal combustion engine (not shown).
  • a preferred configuration would provide that the disc 22 provide the mass of a flywheel.
  • both shaft 21 and disc 22 are effectively joined together by linkage 4 mating with radial slot 6 and therefore must complete a single revolution at the same time as each other and, there does not, therefore appear to be any overall drive ratio present in the present invention.
  • drive ratio does exist for some portion of revolution of the shaft 21.
  • these examples were firstly a bicycle and secondly a single cylinder internal combustion engine. For purpose of simplicity first consider the example of a bicycle.
  • Such alteration may also provide a mechanical advantage or disadvantage during that half of a revolution that the power is applied to such a system.
  • the degree of mechanical advantage present or absent on the redundant, return or coasting half of a revolution is for the sake of this discussion omitted. (More on this point later).
  • journal 26 is positioned so that the axis 7 of shaft 21 and hence radial arm 24, or in the case of a bicycle the axis of a pedal crank, is positioned on the 90 degree radial of disc 22.
  • the invention has equal application where the power input is from a smooth source but the output is applied to a pulsed load or any load analogous to a stroke for example the invention could be interposed between an electric motor and a compressor or pump or any application where there is a load for a proportion of a cycle but not the remainder.
  • a smooth power source is driving a pulsed load the preferred configuration would provide for the flywheel (if any) as is effectively the case with the armature of an electric motor to be on the drive side of the invention.
  • Firstly one method of inducing a constantly changing arc is to provide a radial slot in radial arm 24 so that follower is free to slide within that slot, and then possibly also having a sinusoidal guiding means interposed between radial arm 24 and the plane of the face of disc 22 so that follower 5 is caused to slide within the radial slot in radial arm 24 during revolution.
  • An understanding of a change in radius of the arc described by follower 5 is best understood by again considering Figure 3 and Figure 4. Consider first the effect of a lesser radius of arc of the follower 5 than that depicted in Figure 3 and Figure 4.
  • a power stroke corresponds to a portion of a revolution of shaft 21 it is also true that one need only correlate the most efficient or desirable portion of stroke of an input device to the most efficient or desirable portion of a revolution of shaft 21 hence in a multi cylinder engine where there are portions of multiple power strokes concurrently present one can correlate the most advantageous proportion of rotation of shaft 21 to correspond to the concurrent power stroke or proportion of concurrent power stroke from which the most benefit can be derived.
  • a separate assembly of the invention was provided for each pedal a separate assembly could be provided for each cylinder or group of cylinders.
  • the engine could be divided into essentially three parts each of two cylinders without connection between three separate crankshafts except through the interposing of three assemblies of the invention driving a common or single drive shaft, while it is pointless to describe in detail such a configuration it is readily obvious that there are a great variety of possible constructions however for the sake of simple explanation consider three separate two cylinder engines placed in line each driving a shaft 21 of the invention which has been mounted on the side of the crankcase of each and in turn the perimeter of each of the discs 22 could be meshed to or driving a single shaft to which the power of the engines is ultimately transmitted. In addition to the above modifications, any one of three further improvements described below may also be employed.
  • the mechanism 30 of Figure 12 includes many components similar to those of mechanism 20, described with reference to Figure 2, and like parts are denoted with the same reference numeral, the difference in construction resides in the disc 22 being arranged in spaced relation with respect to the sleeve 27 and journal 26.
  • the disc 22 is, instead mounted to a flange 31, which extends radially of the sleeve 27, via a cylindrical collar 32.
  • the linkage 4 is also modified in that the follower 5 is located on an opposite side of the arm 24 so as to engage in slot 33 from a reverse direction to that shown in Figure 2.
  • the length of the slot 33 is not limited by the diameter of the journal 26, thereby allowing a minimum radius of arc of the follower 5 about the axis 8 to be achieved.
  • the second improvement relates to the changing of ratio manifest by the mechanism when there is a requirement to maintain the spacing of, for example, the axes 7 in relation to the axis of drive or driven shafts (not shown) forming other parts of a power train.
  • the arrangement of the mechanism can be such as to maximise speed ratios to correspond to a power stroke or portion of power stroke.
  • the first in relation to the bicycle example involved rotating journal 26 about it axis
  • the second as discussed in relation to internal combustion engines may involve rotating the journal 26 about the axis 7 of shaft 21.
  • journal 26 The rotation of journal 26 about the axis 7 shaft would alter the position of the axis 8 of disc 22 in relation to a power train and, in order to compensate for such a change in axis position there may be provided, attached to outer face 34 of disc 22, a ring gear coaxial with disc 22 and having its teeth oriented inward and the meshing point on the extended axis of shaft 21.
  • the whole assembly may be arranged to maintain a fixed axis 8 and a coupled pair of epicyclic gears may instead be provided, one on the end of shaft 21 and one on a shaft driving shaft 21 or driven by shaft 21 such that with movement of the outer ring of one or both of the sets of epicyclic gears is rotated one way or the other in relation to its coupled shaft and so the orientation of the various points of ratio or moment of the system is moved in relation to the stroke.
  • the third improvement is the addition of a gear train to the system, as with any system of gearing or torque conversion there are limits to the ranges available, this is true of the present invention however the mere addition of a conventional gearbox to the power train would be a somewhat self defeating process.
  • the present invention while not altering output shaft speed in relation to overall or average crank speed it does continuously alter between design or configuration limits the torque transmitted to the output shaft.
  • the present invention therefore does have an effect analogous to the effect of conventional gears.
  • This improvement or addition provides for the addition of a gearbox of conventional design except in having steps between ratios that are proportionate to the range of effective gearing provided by the present invention in any particular configuration.
  • a gearbox which has its ratios set in sympathy with or take into account the effective range provided by the present invention, for example it may be that with the lowest gear of the gearbox selected and the present invention set at equivalent to low, then the combination of the two effects is equivalent to standard first gear for the subject vehicle type, then with operation the invention setting is moved up through its range to the top a ratio change would then be made in the gearbox while at the same time setting the invention back to its low setting after which the invention would be again moved through its range.
  • it is possible to exceed design or configuration settings or limits of the present invention while maintaining a stepless range of transmission ratios while concurrently reducing the complexity and cost of a standard gearbox whether manual or automatic.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un mécanisme d'entraînement (20) comprenant un élément d'entraînement (2) rotatif autour d'un premier axe (7), un élément entraîné (3) rotatif autour d'un second axe (8), et une liaison (4) reliant réciproquement ces éléments, de sorte que la rotation de l'élément d'entraînement (2) provoque la rotation de l'élément entraîné (3), la liaison étant fixée à l'élément d'entraînement pour tourner autour du premier axe (7) et accouplée à l'élément entraîné (3) au moyen d'éléments de guidage (6) permettant à la liaison (4) de se déplacer le long d'un trajet prédéterminé par rapport au second axe (8). Les éléments (2, 3) sont conçus pour être positionnés de façon que le premier et le second axe (7, 8) soient pratiquement parallèles et écartés, la liaison (4) tournant de façon excentrique autour du second axe (8) lors de la rotation de l'élément d'entraînement.
PCT/AU1995/000414 1994-07-08 1995-07-07 Mecanisme d'entrainement Ceased WO1996001960A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU28757/95A AU2875795A (en) 1994-07-08 1995-07-07 Drive mechanism

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
AUPM6698A AUPM669894A0 (en) 1994-07-08 1994-07-08 A mechanism
AUPM6698 1994-07-08
AUPM681594 1994-07-14
AUPM6815 1994-07-14
AUPM6924A AUPM692494A0 (en) 1994-07-20 1994-07-20 Improvement to "a mechanism"
AUPM6924 1994-07-20

Publications (1)

Publication Number Publication Date
WO1996001960A1 true WO1996001960A1 (fr) 1996-01-25

Family

ID=27157794

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU1995/000414 Ceased WO1996001960A1 (fr) 1994-07-08 1995-07-07 Mecanisme d'entrainement

Country Status (1)

Country Link
WO (1) WO1996001960A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0985095A4 (fr) * 1998-03-27 2002-01-09 Thermo Fibertek Inc Systeme de pompe haute pression

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR574624A (fr) * 1923-03-02 1924-07-16 Dispositif de commande automatique
US3491604A (en) * 1968-02-12 1970-01-27 Cass B Levi Device for modifying rotary motion
DE3211437A1 (de) * 1981-04-02 1982-10-21 Karl 5206 Neunkirchen Beuke Mechanisches getriebe
GB2138094A (en) * 1983-04-12 1984-10-17 Cefin Spa Device for converting uniform rotary motion into variable speed rotary motion
CA1230760A (fr) * 1982-04-29 1987-12-29 Adron (Proprietary) Limited Variateur de vitesse

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR574624A (fr) * 1923-03-02 1924-07-16 Dispositif de commande automatique
US3491604A (en) * 1968-02-12 1970-01-27 Cass B Levi Device for modifying rotary motion
DE3211437A1 (de) * 1981-04-02 1982-10-21 Karl 5206 Neunkirchen Beuke Mechanisches getriebe
CA1230760A (fr) * 1982-04-29 1987-12-29 Adron (Proprietary) Limited Variateur de vitesse
GB2138094A (en) * 1983-04-12 1984-10-17 Cefin Spa Device for converting uniform rotary motion into variable speed rotary motion

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0985095A4 (fr) * 1998-03-27 2002-01-09 Thermo Fibertek Inc Systeme de pompe haute pression

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