EP2337971A1 - Transmission épicycloïdale - Google Patents

Transmission épicycloïdale

Info

Publication number
EP2337971A1
EP2337971A1 EP09813875A EP09813875A EP2337971A1 EP 2337971 A1 EP2337971 A1 EP 2337971A1 EP 09813875 A EP09813875 A EP 09813875A EP 09813875 A EP09813875 A EP 09813875A EP 2337971 A1 EP2337971 A1 EP 2337971A1
Authority
EP
European Patent Office
Prior art keywords
elements
assembly
planet
assemblies
constrained
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.)
Withdrawn
Application number
EP09813875A
Other languages
German (de)
English (en)
Other versions
EP2337971A4 (fr
Inventor
Malcolm Leonard Stephen Dean
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
Priority claimed from AU2008904685A external-priority patent/AU2008904685A0/en
Application filed by Individual filed Critical Individual
Publication of EP2337971A1 publication Critical patent/EP2337971A1/fr
Publication of EP2337971A4 publication Critical patent/EP2337971A4/fr
Withdrawn legal-status Critical Current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
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously

Definitions

  • This invention relates to devices for the transmission of mechanical power in the form of rotational motion.
  • it is directed to transmission of power between a first rotationally movable element and a second rotationally movable element to provide a device which can provide, in a preferred form, continuously variable ratios, of angular velocity at an input to angular velocity at an output / within the range of ratios -1:1 to O to +l:l.
  • the present invention finds use in electronic, hydraulic or mechanical applications and, in a preferred form, provides variable input and output speeds; an output angular velocity that varies from 0 to + the gear ratio as the Input varies from zero to the input angular velocity; torque multiplication; the ability to vary speed and torque. Furthermore, the present invention provides multiple Inputs and/or outputs and reduction, step up or 1:1 gear ratios.
  • This invention includes the use of a planetary drive, that is a drive which includes a set of rollers, bearings or similar moveable parts, arranged in a circle around an axis and configured so that, through their movement in concert, apply torque to a body whose resultant rotation is used as the output of the drive.
  • planetary drives are manufactured by Sumitomo Heavy Industries Ltd, Japan, under the name "Cyclodrive”. Although planetary gears are known, the prior art gears have failed to take advantage of certain of their features, in particular, the contra-rotational nature of the input and output shafts being on the same axis.
  • Eccentric sun gear is chosen OR NOW WITH Bush only can be used. 4 Alternatively cams can be of anv profile shape used now.
  • this 23 allows them to return progressively back to a high tor ⁇ ue 4 to 1 reduction ratio.
  • Previous patent wording "Haying at least one input and one output and being of the epicyclic type involving interaction of three mechanically distinct rotating elements with any suitable form that allows the transfer of torque between input and output, namely a sun element, a ring element and a planet element in each of at least first and second unequal co-axial epicyclic assemblies, a first element of the first assembly and a first element of the second assembly able to rotate independently, the first element of the second assembly able to enclose the control means and able to be totally within the first rotating element of the first assembly, a second rotating element of the first assembly and a second rotating element of the second assembly being constrained to rotate at a common angular velocity, a third element of the first assembly being connected to a motive source, and control means for progressively changing the gear ratio applied to a load ( End previous original PAGE 1 - 1 Page 21 connected to the first element of the first assembly of the Transmission", (referred to as an "eM Dean” or "Variable Ratio Multi-gear” sometimes) characterised
  • the "roller” gear can be integrated with other planetary gear designs optionally,. - is described as follows wherein the first elements are the ring elements of the respective assemblies, the ring elements being outer bodies having spaced endless scallop guides being adapted to receive sets of planet elements being in the form of rollers, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet carrier elements locating and controlling the motion of integral spaced sets of rollers corresponding to the planet elements of each assembly, the rollers bridging .
  • Fig 1 shows the variable options with internal - either single electric or double contra- rotation and further, optionally three rotor electrical control variations.
  • the electrical coils were then shown as with multiple hypothetical abilities, with Fig 2 explaining the practical necessities as to how the ring-gears would be physically constructed for the optional external one or more or combined power sources including for Hybrid applications.
  • the ground reference WAS/ is shown with the shaded area of the housing, in order to more easily see how energy storage is actuated we can refer to the first Patent Windmill experiment.
  • Several alternative methods have been described with some trailed, within the previous pages.
  • divisional Patent 2003204953 (from AU 93246/98) There was is described how by placing a small wind turbine blade on the Input cam (sun gear), being the first input, say at 6 to l ratio.
  • ENCLOSING EVERYTHING would not be able to be turned because of the high torque necessary. Instead the large heavy turbine/blade would be forced to rotate in the opposite direction to its designed pitch, because of the gearing. Optionally - one wav restrictions to around reference only allows it to 90 in tbe same direction as the other blade having the same pitch. Providing geared toroue at any chosen ratio to start the Load. FURTHER THE Ring gear can enclose the Planetary components.
  • the large blade r provides added torque from both the first small wind turbine/blade together with the large blade returning adding stored reactive energy as well as from the wind.
  • the load will eventually turn faster than either of them and the load will also turn faster than both - the two input rotation speeds add together on the load.
  • contra-rotating blades/turbines are known to increase wind pressure bv Fans by 270% In wind Tunnel tests.
  • numps have initial starting friction to overcome - so "Solar eperov" systems. are now made Viable - revolutionised -.
  • VASSTCO Variable Automatic Self Supporting Transmission Co.
  • Opposite rotation direction of internal Governing is able to be used with anv "Self governing - with either Body or Carrier as output (12) More Sunoears or Cams can be added for anv chose ⁇ "Steps'* and more rinooears for Heavy Duty uses, overdrives, Reversi ⁇ o or Motor braking OR for storing
  • Governor action can further be controlled by the intrinsic dynamic nature of the transmission having fixed ratios, which may centrif ⁇ gally equalise the inputs and outputs for optimum operation. (Electronic control for optimum performance together with maximum efficiency is extremely complementary to this transmission and relatively low cost, with manual over-riding being available).
  • FIg 5 lower drawing can be integrated with Fig 12 for camber and caster.
  • the combined advance of low cost electronic sensors can be input into low cost Miro-processors thereby providing pre programmed reactive correction for any scenario and every obstacle or road irregularity encountered. This is the ultimate result which can be incorporated together with linear high torque acceleration and smooth braking. Silicone Polymers as used in shock absorbers are very complimentary and optionally able to be used for many of the present advances. These can be actuated again by low cost high voltage, low current electronics. (Or low Voltage offcourse )
  • the scallops can be machined inside the wheel hub, inside complete with motor, (or contra- rotating motor).
  • other epi-cyclic designs could be used where the bodies may be, for example within each other.
  • pump combinations may be used without differentiating from trie present invention.
  • the tetest obsolete Patent PCT/AUO2/003O5 d ⁇ djd. have a split body, but between the first epicyclic movement's double carrier as an alternative design).
  • Figure 1 shows a transmission (referred to as an "eM Dean” Gear or “Variable Ratio Multi-Gear” sometimes) input shaft 13 with
  • the previous alternative rotors can now still be duplicated internally concentrically, being shown as options here and also with dotted lines which were In the Fig 1 "
  • a Converter Patent AU 742781 ,or 35198/01 according to This invention as well can apply an input which is a rotor (14) an output (21) and electrical coil and permanent magnet arrangements (23 - 25) that did apply torques respectively to rotors (14, 15) and a planet element in the form of a cage (22).
  • Items 23, 24 and 25 are arrangements of permanent magnets and electrical coils so that with electricity flowing through the coils. Interacting magnetic fields • are produced which cause a torque on the rotors (14, 15) and cage (22) respectively.
  • the electricity supply can be adjusted individually for each of items 23 to 25.
  • the rotor (14) and input shaft (13) are combined as an Integrated part in this module.
  • the rotor (14) could be removed and the input could be solely from an external motive source driving the input shaft (13).
  • the point is the module comprising the groupings 11 and 12 remains the same.
  • Assembly 11 is the first unequal coaxial assembly and comprises of a cam ⁇ sun- element ⁇ (17), bearing (18) and rollers ⁇ planet-element ⁇ (20).
  • the cam (17) is fixed to. the input shaft (13), which is therefore fixed to the input.
  • the bearing (18) has an inner sleeve fitted to the outer diameter of the cam (17).
  • the bearing has an outer sleeve, the outer sleeve of the bearing (18) makes contact with the rollers (20). As the input rotates, the cam (17) causes the bearing (18) to move in an eccentric fashion.
  • rollers (20) This causes the rollers (20) to be cyclically displaced away and towards the central axis of the eM Dean Gear the total displacement relative to this central axis, being twice the cam axis offset from this axis.
  • the rollers (20) are located in equally spaced guides in the cage ⁇ planet element ⁇ (22).
  • the rollers (20) make contact with scallops In the output ⁇ ring element ⁇ (2l).
  • the number of scallops relative to the number rollers in contact with the scallops determines the direction of rotation it would rotate the output (21) if the cage (22) was held still.
  • One more scallop than the number of rollers gives an output rotation direction the same as the cam rotation.
  • One less scallop than the number of rollers would give an output rotation the opposite to the cam rotation.
  • the scallops are so shaped that as the rollers are acted on by the cam, the scallops rotate relative to the cage at a constant angular velocity ratio to that of the cam.
  • the cage (22) is constrained by a rotation blocking means in such a way as to allow the cage (22) to only rotate in a direction the same as the output (21). Therefore because of the reactive forces, the cage (22) will be held against the rotation blocking means and will therefore be stationary relative to the frame (26) with Just the actions of assembly 11 alone.
  • a “Solid Body” now encloses the second body able to be totally within and there is a very compact “Torque Multiplier” design provided as a result.
  • the carrier 22 can now be actuating energy storage internally by being forced into a reversing direction to the load direction, this can provide pumping (or even a coiled torsion spring can absorb energy)
  • the pumping can be integrated with internal accumulation or external accumulation for regeneration.
  • two one way clutches to reference the carrier 22 to ground accessed sequentially through the internal Ring Gear 45.
  • one wav control/restriction such as concentric extension of Carrier/Caoe 22 from either end. or frr>m 13B Shaft.
  • the one way clutches can be similar to as described in Arthur Woodbrid ⁇ e's Patent AU 6078?
  • the output (21) is constrained to rotate about the central axis of the input shaft (13).
  • the cyclical movement of the rollers (20) acting on the scallops alone, causes the output (21) to rotate at a. reduced rotational speed depending on the number of rollers and scallops.
  • the ratio would be one output (21) revolution for every FOUR five revolutions of the cam (17) with the output (21) rotating in the same direction as the cam (17).
  • Assembly 12 is the second unequal coaxial assembly and comprises of a rotor (15), cam (16), and rollers (19).
  • the scallops in the second ring gear 45 make contact with the rollers (19) which make contact with the cam (16).
  • the cam (16) Is fixed to the rotor (15) (shown as an internal clutch drum, now for lower value applications)
  • a slmp(e option which uses Centrifugally actuated Ball bearings throwing out on a sprung loaded "taper” locking up to the , 1 tP 1 ratio. As the load increases returning to 4 to 1 ratio torque on the "Taper"..
  • a bearing or Bush
  • the number of scallops and rollers for assembly 12 are different to the numbers for assembly 11.
  • the rollers are located in equally spaced guides in the cage (22).
  • the cage therefore bridges axially between assemblies 11 and 12 and the rollers (19) are constrained to rotate at the same angular velocity about the central axis of the input shaft (13) as the rollers (20) of assembly 11.
  • the numbers of scallops and rollers are such that if the cage (22) is held relative to the frame (26), the internal ring gear 45 tends to cause the cam (16) to rotate with an angular velocity in the SAME_.o_r-Qpposlte_dlrection to cam (17).
  • Assembly 12 is now chan g ed so that cam (161 rotates in the same direction as cam (17), the output js_thereby reversed as in cam (IS).
  • the cam (16) will have « ⁇ effect on the output angular velocity when ttfrtt ⁇ the electrical coils of items 24 are activated.
  • the electrical coils could be activated so that the torque acts in the same or opposite direction as the rotation of the cam (16). If the torque acts In the same direction as the rotation of the cam (16), the output would rotate at the angular velocity determined by the fixed ratio but with an Increased torque dependant on the amount of torque contributed by items 24.
  • the torque from items 24 act in the opposite direction of rotation of the cam (16) (ie. the same direction as the input shaft (13)).
  • assembly 12 will act so as to try and cause the output (21), to rotate in the opposite direction and the cage (22) in the same direction as the input.
  • the opposite actions on the output and cage caused by cam (16) tend to 'lock' the cage (22) to the input rotation.
  • the cage (22) is free to rotate in the direction of the input (cam (17)).
  • the cage (22) therefore tends to cause the output (21) tD rotate as one with the input.
  • the amount of rotation of the cage (22) and therefore the amount of superimposed rotation is determined by the relative differences in the output resistive torque (hereafter called the loadO and the input torque from cam (17) and items * 24.
  • the output gear ratio therefore can be progressively decreased from the fixed ratio of the first assembly to a 1: 1 ratio by progressively increasing the torque acting on the cam (16) from zero to a value that causes the caqe (22) to be Mocked' fully to the input.
  • Figure 2 shows another embodiment of a "eM Dean” Gear, in this case there is a combination of a module 10 with extensions (on the right-hand half) that enable further multiple fixed ratios to be obtained from the one eM Dean Gear
  • the module 10 shows the central concept of the present invention.
  • the Input is via a separate motive source (not shown) acting through the input shaft (13).
  • the output is the ring element or bod y (21).
  • Fig 2 For example there Is now the option of a second internal body ring -gear with added cam on the right hand side which can be actuated by optionally removing the two bolts and allowing the new second internally shown with arrows.
  • the ring-gear with output 51 can then itself drive another cage with a cam coupled to It so as to provide such as overdrive features.
  • Another cage/cam is shown able to be driven which can provide reversing features by breaking it from being operating in a forward direction of the chosen output.
  • the first unequal coaxial assembly comprises of a cam ⁇ sun-gear ⁇ (17), and rollers ⁇ planet-gears ⁇ (20) and the ring element or body (21).
  • the cam (17) is fixed to the input shaft (l3).
  • the outer diameter of the cam (17) makes contact with the rollers (20).
  • the cam (17) outer diameter moves in an eccentric fashion. This causes the rollers (20) to be cyclically displaced away and towards the central axis of the "eM Dean" Gear as also described in the "A Converter" prior Patent AU 742781 and A 35198/01, explaining the advance here as follows - "the total displacement relative to this central axis, being twice the cam axis offset from this axis.
  • the rollers (20) are located in equally spaced guides in the cage ⁇ planet carrier ⁇ (22).
  • the rollers (20) make contact with scallops in the output (21).
  • the number of scallops relative to the number rollers in contact with the scallops determines the direction of rotation it would rotate the output (21) if the cage (22) was held still.
  • One more scallop than the number of rollers gives an output rotation direction the same as the cam rotation.
  • One less scallop than the number of rollers would give an output rotation the opposite to the cam rotation.
  • the scallops are so shaped that as the rollers are acted on by the cam, the scallops rotate relative to the cage at a constant angular velocity ratio to that of the cam.
  • the cage (22) is constrained by a rotation blocking means in such a way as to allow the cage (22) to only rotate in a direction the same as the output (21). Therefore because of the reactive forces, the cage (22) will be held against the rotation blocking means and will therefore be stationary relative to the frame (the structure holding mounting the motor etc.) with just the actions of assembly il alone.
  • the rollers will rotate about there own axis as they move in relation to the scallops.
  • a bearing could be fitted to the outside diameter of the cams (16 & 17) to eliminate the sliding action of roller (19 & 20) against cam (16 & 17), which would occur (if they were in direct contact) because of the difference In their circumferential speeds.
  • the output (21) is constrained to rotate about the central axis of the input shaft (13). The cyclical movement of the rollers (20) acting on the scallops alone, causes the output (21) to rotate at a reduced rotational speed depending on the number of rollers and scallops.
  • the ratio would be one output (21) revolution for every five revolutions of the cam (17) with the output (21) rotating In the same direction as the cam (17).
  • the second unequal coaxial assembly comprises of a cam (16), and rollers (19) and inner body (45)
  • the scallops in the body (45) make contact with the rollers (19) which make contact with the cam (16).
  • the number of scallops and rollers for the assembly are different to the first assembly 11.
  • the rollers are located in equally spaced guides in the cage (22).
  • the cage therefore bridges axially between assemblies 11 and 12 and the rollers (19) are constrained to rotate at the same angular velocity about the central axis of the Input shaft (13) as the rollers (20) of assembly 11.
  • the numbers of scallops and rollers are such that if the cage (22) is held relative to the frame, the body (45) tends to cause the cam (16) to rotate with an angular velocity in the gAMEopposite direction to cam (17).
  • the ratio would be one body (45) revolution for every FQUR_tfwee-revolutions of the cam (16), with the body (45) rotating in the SAME opposite direction to the cam (16).
  • assembly 12 will act so as to try and cause the Inner body (45), to rotate in the SAME ⁇ ppe ⁇ rte direction and the cage (22) in the same direction as the input.
  • the SAME-eppesKe actions on the output and cage caused by cam (16) tend to l lock' the cage (22) to the input rotation.
  • the cage (22) is free to rotate in the direction of the input (cam (17)).
  • the cage (22) therefore tends to cause the output (21) to rotate as one with the input.
  • the rollers (20) rotation about the central axis of the input shaft (13) due to the action of the cam (17), has superimposed on it a rotation about this central axis due to the rotation of the cage (22) in the direction of the Input. It is this superimposed
  • the amount of rotation of the cage (22) and therefore the amount of superimposed rotation Is determined by the relative differences in the output resistive torque (hereafter called the 'load') and the input torque from the cams (17 & 16).
  • the 'load' lowers relatively and the torque acting on cam (16) is increased, the less is the torque required from cam (17).
  • the proportion of torque from cam (16) relative to cam (17) increases, the more the output (21) tends to be 'locked' to the input and the more the ratio of input to output angular velocity tends to approach 1:1.
  • the output gear ratio therefore can be progressively decreased from the fixed ratio of the first assembly to a 1:1 ratio by progressively increasing the torque acting on the cam (16) from zero to a value that causes the cage (22) to be Mocked' fully to the input.
  • the output torque is inversely proportional to the output angular velocity.
  • the input torque to cam (16) can be through another motive source or a clutch mechanism connecting the input shaft (13) to the extension of cam (16). If a clutch mechanism was used, the control mechanism could be automatic and linked to the output speed through the use of a centrifugal dutch. With a centrifugal clutch arrangement, as the speed of the output increases the clutch engages and tends to turn cam (16) in the same direction as the Input, cam (17). So as the output is accelerated at the lower fixed ratio, there will come a stage when the input shaft is spinning at such a speed that the centrifugal clutch starts to engage. As the centrifugal clutch engages, the output gear ratio would progressively decrease to 1: 1.

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

Abstract

L'invention porte sur un module qui comporte au moins les groupes 11 et 12 qui demeurent identiques pour tous les modes de réalisation. Les ensembles 11 et 12 sont effectivement des ensembles coaxiaux inégaux côte à côte. L'ensemble 11 est le premier ensemble coaxial inégal et comporte une came (élément central) (17), un palier (18) et des rouleaux (éléments planétaires) (20). L'ensemble 12 est le second ensemble coaxial inégal et comporte un rotor ou un composant réversible (15), une came (élément central) (16) et des rouleaux (éléments planétaires) (19) qui sont contraints avec les éléments planétaires des ensembles, et un corps (45) qui est le premier élément du second ensemble et qui peut renfermer le moyen de commande pour être totalement à l'intérieur du premier élément rotatif du premier ensemble, pouvant être totalement à l'intérieur de l'élément de corps (21) de l'ensemble 11.
EP09813875A 2008-09-16 2009-09-10 Transmission épicycloïdale Withdrawn EP2337971A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU2008904685A AU2008904685A0 (en) 2008-09-16 All planetary gears and pumps
PCT/AU2009/001187 WO2010031108A1 (fr) 2008-09-16 2009-09-10 Transmission épicycloïdale

Publications (2)

Publication Number Publication Date
EP2337971A1 true EP2337971A1 (fr) 2011-06-29
EP2337971A4 EP2337971A4 (fr) 2011-09-28

Family

ID=42038998

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09813875A Withdrawn EP2337971A4 (fr) 2008-09-16 2009-09-10 Transmission épicycloïdale

Country Status (3)

Country Link
EP (1) EP2337971A4 (fr)
AU (1) AU2009295250A1 (fr)
WO (1) WO2010031108A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2012236141B2 (en) 2011-04-01 2016-11-17 Terravia Holdings, Inc. Biomass-based oil field chemicals

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AUPP604398A0 (en) * 1998-09-18 1998-10-15 Dean, Malcolm Leonard Stephen Variable ratio multi-gear
AUPR377601A0 (en) * 2001-03-16 2001-04-12 Dean, Malcolm Leonard Stephen Variable ratio multi-gear
AU2002952792A0 (en) * 2002-11-15 2002-12-05 Malcolm Leonard Stephen Dean Variable ratio multi-gear

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO2010031108A1 *

Also Published As

Publication number Publication date
EP2337971A4 (fr) 2011-09-28
WO2010031108A9 (fr) 2012-04-12
WO2010031108A1 (fr) 2010-03-25
AU2009295250A1 (en) 2010-03-25

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