Infinitely and continuously variable transmission system

• US 6,119,539 A
• Filed: 08/10/1998
• Issued: 09/19/2000
• Est. Priority Date: 02/06/1998
• Status: Expired due to Fees

• Current Assignee: Galaxy Shipping Enterprises, Inc.
• Original Assignee: Galaxy Shipping Enterprises, Inc.
• Inventors: Papanicolaou, John Paul
• Primary Examiner(s): Herrmann, Allan D.
• Application Number:
  US09/131,644
• Time in Patent Office: 771 Days
• Field of Search: 74/63, 74/112, 74/123
• US Class Current: 74/112
• CPC Class Codes: F16H 29/04 in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts
• CPC Class Codes: Y10T 74/1503 Rotary to intermittent unidirectional motion
• CPC Class Codes: Y10T 74/1519 Adjustable throw

Abstract

An infinitely and continuously variable transmission system capable of gradually multiplying TORQUE while decreasing RPM and vice-versa. For a given input shaft TORQUE and RPM, the system delivers to the output shaft such increases or reductions in TORQUE with inversely corresponding increases or reductions in RPM as may be desired across a predetermined and very wide range of transmission ratios. The range can include zero RPM for the output shaft while the input shaft continues to rotate at any RPM, thus eliminating the need for an input shaft disengaging clutch. The invention includes a main assembly consisting of one or more pairs of co-axial diametrically opposed one-way clutches and corresponding pairs of diametrically opposed carrying shafts which are interconnected through a central hub assembly. The axes of the carrying shafts share the same plane with each other and with the central hub'"'"'s multi-directional center around which they are radially and symmetrically mounted. The freewheels are engaged in one rotational direction and disengaged in the opposite rotational direction of their carrying shafts and are in turn continuously and interactionally meshed to a common rotatable output gear. The infinitely and continuously variable TORQUE and RPM ratios are produced by causing the freewheel carrying shafts to rotatably oscillate at gradually variable oscillation arcs thereby causing their respective freewheels to smoothly rotate the common output gear at correspondingly variable rotation speeds through a simultaneous combination of the oscillation arc magnitude of their carrying shaft rotatable oscillations and their corresponding engagement/disengagement action.

Claims

1. An infinitely and continuously variable transmission system comprising:

a main frame;

a rotatable input shaft having a retaining member on a first end thereof;

a main output gear having at least one toothed surface; and

at least one drive assembly comprising

an outer ring member pivotally mounted to the main frame about two opposing first shaft members;

first and second one-way clutch assemblies mounted on each of the two outer ring first shaft members, each said clutch assembly being freely rotatable in one direction of rotation of its carrying shaft and non-rotatable in the opposite direction of rotation of its carrying shaft and having a toothed gear on its outer perimeter for positively engaging the toothed surface of the output gear, said clutch assemblies being mounted such that they each move the main output gear in the same circular direction as their freely rotatable direction of rotation;

a swash plate assembly comprising an outer non-rotating portion pivotally coupled to the outer ring member by two second shaft members mounted on an outer perimeter of the non-rotating portion;

an inner circular rotating portion mounted concentrically to the outer non-rotating portion;

said inner circular rotating portion having a slot formed through its center and a centrally positioned retaining member housing for pivotally mounting the retaining member of the input shaft to thereby force the inner portion to co-rotate with the input shaft while at the same time allowing it to pivot with respect to the input shaft thereby causing the outer portion to oscillate about its shaft axes;

wherein the common plane shared by the longitudinal axis of each shaft passes through the point where the longitudinal axis of the retaining member intersects the longitudinal axis of the input shaft and wherein one clutch assembly positively engages the main output gear through the first one-hundred eighty degrees of rotation of the input shaft and the other clutch assembly positively engages the main output gear through the other one-hundred eighty degrees of rotation of the input shaft; and

pivoting means connected to the inner circular rotating portion of the swash plate assembly and a shifting member for causing the inner circular rotating portion of the swash plate assembly to pivot in response to movement of the shifting member, to thereby vary the torque and revolutions per minute of the transmission system.

2. The transmission system of claim 1 further comprising a pair of opposing third shaft members mounted on an outer perimeter of the non-rotating portion ninety degrees apart from the second shafts and a spider having an inner yoke and an outer yoke, said yokes formed by two sets of double legs set ninety degrees apart and connected to each other through a common hub, the inner yoke of the spider pivotally mounted to the first shafts of the swash plate assembly, the outer yoke of the spider having two protruding opposed main shafts vertically fixed at the end of each leg such that the longitudinal axis of said outer yoke main shafts share the same plane;

said two spider main shafts being pivotally mounted to the main frame to allow the spider to pivot with respect to the main frame about the axle of the spider main shafts and third and fourth one-way clutch assemblies concentrically mounted on each of the two spider main shafts and being engaged with the main output gear such that the four clutch assemblies positively engage the main output gear sequentially one at a time through corresponding sequential ninety degree rotations of the input shaft.

3. The transmission system of claim 1 wherein the clutch assemblies are mounted between the main frame and the outer ring member.

4. The transmission system of claim 2 wherein the first and second clutch assemblies are mounted between the main frame and the outer ring member and the third and fourth clutch assemblies are mounted between the spider and the main frame.

5. The transmission system of claim 1 wherein the output gear comprises a double faced gear having a first toothed surface on a first face of the gear a second toothed surface on a second face of the gear and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly for engaging the second toothed surface of the output gear, said clutch assemblies of said second drive assembly being ninety degrees out of phase with said clutch assemblies of said first drive assembly.

6. The transmission system of claim 2 wherein the output gear comprises a double faced gear having a first toothed surface on a first face of the gear a second toothed surface on a second face of the gear and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly for engaging the second toothed surface of the output gear, said clutch assemblies of said second drive assembly being forty-five degrees out of phase with said clutch assemblies of said first drive assembly.

9. The transmission system of any of claims 1-8 wherein the inner rotating portion of the swash plate assembly is mounted to the outer portion by an intervening main thrusts bearing and further comprising a thrust bearing retention ring concentrically fixedly attached to the non-rotating portion of said swash plate assembly, said retention ring holding the inner rotating portion, the intervening main thrust bearing and the outer non-rotating portion together as an assembly through an auxiliary thrust bearing intervening between the retention ring and the inner rotating portion.

7. An infinitely and continuously variable transmission system comprising:

a main frame;

a rotatable input shaft having a retaining member on a first end thereof;

a main output gear having at least one toothed surface; and

at least one drive assembly comprising

an outer ring member pivotally mounted to the main frame about two opposed outer ring shaft members;

first and second spiders each having an inner yoke and an outer yoke, said yokes formed by two sets of double legs set ninety degrees apart and connected to each other through a common hub, the outer yoke of each of the spiders having a pair of protruding opposed main shafts vertically fixed at the end of each leg such that the longitudinal axis of said outer yoke main shafts share the same plane and such that the pair of outer yoke main shafts of said first spider, the pair of outer yoke main shafts of said second spider and the pair of outer ring shaft members are set sixty degrees apart;

said spider main shafts being pivotally mounted to the main frame to allow the spider to pivot with respect to the main frame;

first and second one-way clutch assemblies concentrically mounted on each of the two outer ring shaft members and third, fourth, fifth and sixth one-way clutch assemblies concentrically mounted on each outer yoke main shaft of the first and second spiders, each said clutch assembly being freely rotatable in one direction of rotation of its carrying shaft and non-rotatable in the opposite direction of rotation of its carrying shaft and having a toothed gear on its outer perimeter for positively engaging the toothed surface of the output gear, said clutch assemblies being mounted such that they each move the main output gear in the same circular direction as their freely rotatable direction of rotation;

an inner ring member concentric with said outer ring member and having first and second pairs of inner ring shafts on an outer perimeter of the inner ring member, said first pair of inner ring shafts being pivotally coupled to the outer ring sixty degrees apart from said first pair of outer ring shaft members and said second pair of inner ring shafts being pivotally coupled to the inner yoke of said second spider ninety degrees apart from said first pair of inner ring shafts;

a swash plate assembly comprising an outer non-rotating portion pivotally coupled to the inner ring member by a first pair of short shafts mounted on an outer perimeter of the non-rotating portion coaxially with the outer yoke main shafts of the first spider and pivotally coupled to the inner yoke of said first spider by a second pair of short shafts on said outer perimeter of the non-rotating portion ninety degrees apart from said outer yoke main shafts of the first spider;

an inner circular rotating portion mounted concentrically to the outer non-rotating portion;

said inner circular rotating portion having a slot formed through its center and a centrally positioned retaining member housing for pivotally mounting the retaining member of the input shaft to thereby force the inner portion to co-rotate with the input shaft while at the same time allowing it to pivot with respect to the input shaft thereby causing the outer portion to oscillate about its axes;

wherein the common plane shared by the longitudinal axis of each shaft passes through the point where the longitudinal axis of the retaining member intersects the longitudinal axis of the input shaft and wherein the six clutch assemblies positively engage the main output gear sequentially one at a time through corresponding sequential sixty degree rotations of the input shaft; and

pivoting means connected to the inner circular rotating portion of the swash plate assembly and a shifting member for causing the inner circular rotating portion of the swash plate assembly to pivot in response to movement of the shifting member, to thereby vary the torque and revolutions per minute of the transmission system.

8. The transmission system of claim 7 wherein the output gear comprises a double faced gear having a first toothed surface on a first face of the gear a second toothed surface on a second face of the gear and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly for engaging the second toothed surface of the output gear, said clutch assemblies of said second drive assembly being thirty degrees out of phase with said clutch assemblies of said first drive assembly.

10. An infinitely and continuously variable transmission system comprising:

a main frame;

a rotatable input shaft driving a rotating grooved member; and

at least one drive assembly comprising

a main output gear having at least one toothed surface;

a double yoke assembly having a fixed first yoke, a pivotable second yoke opposed to and out of phase with respect to said first yoke and a central cross assembly pivotably connected to the two opposed yokes at their respective fork ends;

said fixed yoke having a central shaft rigidly mounted to the main frame at a rear portion thereof to thereby prevent said first yoke from either rotating or being rotatably displaced;

said pivotable second yoke having an attached pivotable yoke shaft that cannot rotate but whose free end can be rotatably displaced thereby causing it to oscillate about infinite axes with respect to the fixed yoke to which it is pivotally mounted;

said central cross assembly having a central hollow hub having a first pair of opposed co-axial main shafts radially and rigidly mounted on its outer perimeter in a first axis and rotatably connected to correspondingly axially oriented orifices of the fixed yoke fork ends, said shaft ends being rotatably housed in the main frame and a second pair of opposed co-axial main shafts radially and rigidly mounted on its outer perimeter in a second axis out of phase with the first axis and rotatably connected to the corresponding axially oriented orifices of the pivotable yoke fork ends, all said first and second pair shafts axis being co-planar to each other such that their theoretical extensions intersect each other vertically at the same point as the hub'"'"'s multidirectional center;

first and second one-way clutch assemblies concentrically mounted on each of the two first main shafts, each said clutch assembly being freely rotatable in one direction of rotation of its carrying shaft and non-rotatable in the opposite direction of rotation of its carrying shaft and having a toothed gear on its outer perimeter for positively engaging the toothed surface of the output gear, said clutch assemblies being mounted such that they each move the main output gear in the same circular direction as their freely rotatable direction of rotation, wherein one clutch assembly positively engages the main output gear through the first one-hundred eighty degrees of rotation of the rotating grooved member and the other clutch assembly positively engages the main output gear through the other one-hundred eighty degrees of rotation of the rotating grooved member;

the rotating grooved member being rotatably mounted on the main frame and connected to a free end of the pivotable second yoke shaft through a first groove which passes diametrically through the grooved member surface facing said pivotable second yoke shaft, the free end of the pivotable second yoke shaft being slidably and rotatably mounted in said first groove; and

displacement means connected to a shifting member and the pivotable second yoke shaft for displacing the pivotable second yoke shaft smoothly throughout the length of the groove while the grooved member is rotating in response to movement of the shifting member, to thereby vary the torque and revolutions per minute of the transmission system.

11. The transmission system of claim 10 further comprising an oscillation conversion assembly including a central section having a pair of diametrically opposed, protruding, co-axial third main shafts co-aligned with the second axis and radially fitted on its outer perimeter whose ends are rotatably housed in the main frame wherein the two first main shafts of the central cross assembly and the two third main shafts of the oscillation conversion assembly are co-planar such that their theoretical extensions vertically intersect each other at a point co-incidental to the point of intersection of the first and second pair of main shafts of the central cross assembly;

and third and fourth one-way clutch assemblies concentrically mounted on each of the main shafts of the oscillation conversion assembly and being engaged with the main output gear such that the four one-way clutch assemblies positively engage the main output gear sequentially one at a time through corresponding sequential ninety degree rotations of the rotating grooved member.

12. The transmission system of claim 11 having a second oscillation conversion assembly mounted such that the main shafts of the first and second oscillation conversion assemblies are co-planar with each other and with the central cross assembly'"'"'s first main shafts and are radially and symmetrically positioned at 60 degree intervals with respect to the central cross assembly'"'"'s first main shafts and each other, wherein the second oscillation conversion assembly is dimensioned such that it clears the first oscillation conversion assembly when they both begin oscillating as a result of the oscillating motion of the pivotable second yoke shaft;

and fifth and sixth one-way clutch assemblies concentrically mounted on each of the main shafts of the second oscillation conversion assembly and being engaged with the main output gear such that the six one-way clutch assemblies positively engage the main output gear sequentially one at a time through corresponding sequential sixty degree rotations of the rotating grooved member.

13. The transmission system of claim 12 wherein more than two oscillation conversion assemblies are radially and symmetrically positioned around the central cross assembly'"'"'s first main shafts such that their main shafts are co-planar and positioned at equal angular intervals with respect to the central cross assembly'"'"'s first main shafts and are dimensioned to clear each other when they all begin oscillating as a result of the oscillating motion of the pivotable second yoke shaft;

and further one-way clutch assemblies concentrically mounted on each of the main shafts of such additional oscillation conversion assemblies and being engaged with the main output gear such that they all positively engage the main output gear sequentially one at a time through corresponding sequential equal rotational arcs of the rotating grooved member.

14. The transmission system of claims 11, 12 or 13 wherein the central section of each oscillation conversion assembly comprises a hollow cylindrical ring having a perimetrical arch shaped radial slot cut-out symmetrically positioned between and sharing the same plane with the two diametrically opposed, protruding, co-axial main shafts radially fitted on its outer perimeter, through which slot the pivotable second yoke shaft, is slidably and rotatably mounted such that it can oscillate within such slot through an arc aligned with and co-planar to the said main shafts.

15. The transmission system of claims 11, 12 or 13 wherein the central section of each oscillation conversion assembly comprises a hollow semi-cylindrically shaped horse shoe having a perimetrical arc shaped radial slot cut-out symmetrically positioned between and sharing the same plane with the two diametrically opposed, protruding, co-axial main shafts radially fitted to the horse shoe ends of its outer perimeter, through which slot the pivotable second yoke shaft is slidably and rotatably mounted such that it can oscillate within such slot through an arc aligned with and co-planar to the said main shafts.

16. The transmission system of claims 11, 12 or 13 wherein the central section of the oscillation conversion assembly comprises an outer hollow cylindrical ring having a perimetrical arc shaped radial slot cut-out symmetrically positioned between and sharing the same plane with the two diametrically opposed, protruding, co-axial main shafts radially fitted on its outer perimeter, through which slot the pivotable second yoke shaft is freely fitted such that it can oscillate within such slot through an arc aligned with and co-planar to the said main shafts, and an inner hollow cylindrical ring having a centrally positioned orifice on its cylindrical shell through which the pivotable second yoke shaft is rotatably mounted such that said orifice is rotatably aligned with the slot cut-out of the outer ring;

the inner and outer rings being coaxially and rotatably fitted to each other such that the inner ring freely and centrally rotates with respect to the outer ring.

17. The transmission system of claims 10, 11, 12 or 13 wherein said displacement means comprises an extension arm that can be either screwed-in or screwed-out through a hollow central section of the pivotable second yoke shaft, thereby forcing a pivotably and rotatably fitted sliding bogie attached to the extension arm end to slide radially within a straight second grooved-track of the grooved rotating member which is aligned with and positioned behind the first groove, thereby displacing the pivotable second yoke shaft within the first groove.

18. The transmission system of claims 10, 11, 12 or 13 wherein said displacement means comprises an extension arm that can be either screwed-in or screwed-out through a hollow central section of the pivotable second yoke shaft, thereby forcing a twin flange assembly, whose first flange is rotatably mounted to the extension arm end and slidably fitted within the first groove of the rotating grooved member and whose second flange is rotatably mounted to the pivotable second yoke shaft and pivotally connected to two pivoting bracket arms, said bracket arms being rotatably connected to two co-axial anchoring points lying within the grooved member and running parallel with and on either side of the first groove, to follow an arc-shaped track around the co-axial anchoring points thereby displacing the pivotable second yoke shaft within the first groove.

19. The transmission system of claims 10, 11, 12 or 13 wherein said displacement means comprises an extension arm that can be either screwed-in or screwed-out through a hollow central section of the pivotable second yoke shaft, thereby forcing a geared side of a rack rotatably mounted to the extension arm and to engage gear cage gears rotatably mounted within a slidable gear cage on independent shafts, said gear cage being rotatably mounted around a free end of the pivotable second yoke shaft and slidably mounted within said first groove, and further comprising means for preventing rotation of the rack within the gear cage by sliding in a longitudinal groove of the rack, at least one of said gear cage gears being coaxially and rigidly fixed to twin gears that mesh with twin corresponding gear surfaces that are rigidly fixed upon an inner concave face of the grooved member in coaxial alignment with and running parallel on either side of and outside the first groove, wherein the screwing out of the extension arm causes the rack to rotate the gear cage gears and the twin gears to thereby force the free end of the pivotable yoke shaft to be gradually displaced out of alignment with respect to a central shaft of the grooved member.

20. The transmission system of claims 10, 11, 12 or 13 wherein said displacement means comprises an extension arm that can be either screwed-in or screwed-out through a hollow central section of the pivotable second yoke shaft, thereby forcing a geared side of a rack rotatably mounted to the extension arm end to engage gear cage gears rotatably mounted within a slidable gear cage on independent shafts, said gear cage being rotatably mounted around a free end of the pivotable second yoke shaft and slidably mounted within said first groove, and further comprising means for preventing rotation of the rack within the gear cage by sliding in a longitudinal groove of the rack, at least one of said gear cage gears being coaxially and rigidly fixed to twin gears that mesh with twin corresponding gear surfaces that are rigidly fixed within the first groove in coaxial alignment with and running parallel to the first groove, wherein the screwing out of the extension arm causes the rack to rotate the gear cage gears and the twin gears to thereby force the free end of the pivotable yoke shaft to be gradually displaced out of alignment with respect to a central shaft of the grooved member.

21. The transmission system of claim 10 wherein the first and second clutch assemblies are mounted between the fixed yoke'"'"'s fork ends and the main frame.

22. The transmission system of claim 11 wherein the first and second clutch assemblies are mounted between the fixed yoke'"'"'s fork ends and the main frame and each of the third and forth clutch assemblies are mounted between the conversion assembly and the main frame.

23. The transmission system of claim 12 wherein the first and second clutch assemblies are mounted between the fixed yoke'"'"'s fork ends and the main frame and each of the third and fourth clutch assemblies are mounted between the first conversion assembly and the main frame and each of the fifth and sixth clutch assemblies are mounted between the second conversion assembly and the main frame.

24. The transmission system of claims 10, 11, 12 or 13 wherein the axis of rotation of the rotating grooved member is concentric to the axis of the fixed yoke'"'"'s central shaft.

25. The transmission system of claim 24 wherein the groove is an arc-shaped groove.

26. The transmission system of claim 25 wherein the center of the arc is the multidirectional center of the central hollow bub.

27. The transmission system of claim 10 wherein the output gear comprises a double faced gear having a first toothed surface on a first face of the gear and a second toothed surface on a second face of the gear and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly for engaging the second toothed surface of the output gear, said clutch assemblies of said second drive assembly being ninety degrees out of phase with said clutch assemblies of said first drive assembly.

28. The transmission system of claim 11 wherein the output gear comprises a double faced gear having a first toothed surface on a first face of the gear and a second toothed surface on a second face of the gear and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly for engaging the second toothed surface of the output gear, said clutch assemblies of said second drive assembly being forty-five degrees out of phase with said clutch assemblies of said first drive assembly.

29. The transmission system of claim 12 wherein the output gear comprises a double faced gear having a first toothed surface on a first face of the gear and a second toothed surface on a second face of the gear and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly for engaging the second toothed surface of the output gear, said clutch assemblies of said second drive assembly being thirty degrees out of the phase with said clutch assemblies of said first drive assembly.

30. The transmission system of claim 10 wherein the rotating grooved member comprises a double faced grooved member and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly, the main output gear of said first drive assembly and the main output gear of said second drive assembly being co-rotatable, wherein a first face of the double faced grooved member cooperates with said first drive assembly and a second face of the double faced grooved member cooperates with said second drive assembly, said clutch assemblies of said second drive assembly being ninety degrees out of phase with said clutch assemblies of said first drive assembly.

31. The transmission system of claim 11 wherein the rotating grooved member comprises a double faced grooved member and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly, the main output gear of said first drive assembly and the main output gear of said second drive assembly being co-rotatable, wherein a first face of the double faced grooved member cooperates with said first drive assembly and a second face of the double faced grooved member cooperates with said second drive assembly, said clutch assemblies of said second drive assembly being forty-five degrees out of phase with said clutch assemblies of said first drive assembly.

32. The transmission system of claim 12 wherein the rotating grooved member comprises a double faced grooved member and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly, the main output gear of said first drive assembly and the main output gear of said second drive assembly being co-rotatable, wherein a first face of the double faced grooved member cooperates with said first drive assembly and a second face of the double faced grooved member cooperates with said second drive assembly, said clutch assemblies of said second drive assembly being thirty degrees out of phase with said clutch assemblies of said first drive assembly.

55. The transmission system of any of claims 10, 11, 12, 13, 21, 22, 23, 27, 28, 29, 30, 31, 32, 33, 34, 35, 36, 49, 50, 51, 52, 53 or 54 wherein the grooved member comprises a grooved disc.

56. The transmission system of any of claims 11, 12, 13, 34, 35 or 36 wherein the co-axial main shafts of any of the oscillation conversion assemblies are not evenly or symmetrically fitted with respect to the first axis of the central cross assembly or with respect to the first main shaft.

57. The transmission system of any of claims 10, 11, 12, 13, wherein the pivotable second yoke is ninety degrees out of phase with respect to said first yoke.

33. An infinitely and continuously variable transmission system comprising:

a main frame;

a rotatable input shaft driving a rotating grooved member; and

at least one drive assembly comprising

a main output gear having at least one toothed surface;

a T-joint pivotable shaft assembly having a first main shaft rotatably mounted to the main frame in a first axial orientation, said first main shaft being allowed to pivot with respect to the main frame but not being otherwise displaceable;

a second pivotable and rotatably displaceable shaft having a first end pivotably mounted at a mid section of the first main shaft through a central cross assembly, and a second free end that can be rotatably displaced to cause the second pivotable shaft to oscillate about infinite axes with respect to the main frame;

first and second one-way clutch assemblies concentrically mounted on each of the first axially-oriented sections of the first shaft, each said clutch assembly being freely rotatable in one direction of rotation of its carrying section of the first shaft and non-rotatable in the opposite direction of rotation of its carrying section of the first shaft and having a toothed gear on its outer perimeter for positively engaging the toothed surface of the output gear, said clutch assemblies being mounted such that they each move the main output gear in the same circular direction as their freely rotatable direction of rotation, wherein one clutch assembly positively engages the main output gear through the first one-hundred eighty degrees of rotation of the rotating grooved member and the other clutch assembly positively engages the main output gear through the other one-hundred eighty degrees of rotation of the rotating grooved member; and

the grooved member being rotatably mounted on the main frame and connected to the free end of the second pivotable shaft through a first groove which passes diametrically through the grooved member surface facing said second pivotable shaft, such free end of the second pivotable shaft being slidably and rotatably mounted in said first groove through a rotatable sliding shoe; and

displacement means connected to a shifting member and the shoe of the second shaft for displacing the second shaft smoothly throughout the length of the first groove while the grooved member is rotating in response to movement of the shifting member, to thereby vary the torque and revolutions per minute of the transmission system.

34. The transmission system of claim 33 further comprising an oscillation conversion assembly including a central section having a pair of diametrically opposed, protruding, co-axial second main shafts aligned in a second axial orientation and radially fitted on its outer perimeter whose ends are rotatably housed in the main frame in said second axial orientation, wherein the two ends of the first main shaft and the two second main shafts of the oscillation conversion assembly are co-planar such that their theoretical extensions vertically intersect each other at the central mid-point of the first main shaft;

and third and fourth one-way clutch assemblies concentrically mounted on each of the second main shafts of the oscillation conversion assembly and being engaged with the main output gear such that the four one-way clutch assemblies positively engage the main output gear sequentially one at a time through corresponding sequential ninety degree rotations of the rotating grooved member.

35. The transmission system of claim 34 having a second oscillation conversion assembly mounted such that the second main shafts of the first oscillation conversion assembly and the third main shafts of the second oscillation conversion assembly are co-planar with each other and with the shaft ends of the first main shaft and are radially and symmetrically positioned at 60 degree intervals with respect to the first main shaft and each other, wherein the second oscillation conversion assembly is dimensioned such that it clears the first oscillation conversion assembly when they both begin oscillating as a result of the oscillating motion of the second pivotable shaft;

and fifth and sixth one-way clutch assemblies concentrically mounted on each of the third main shafts of the second oscillation conversion assembly and being engaged with the main output gear such that the six one-way clutch assemblies positively engage the main output gear sequentially one at a time through corresponding sequential sixty degree rotations of the rotating grooved member.

36. The transmission system of claim 35 wherein more than two oscillation conversion assemblies are radially and symmetrically positioned around the shaft ends of the first main shaft such that their main shafts are co-planar and positioned at equal angular intervals with respect to the shaft ends of the first main shaft and are dimensioned to clear each other when they all begin oscillating as a result of the oscillating motion of the second pivotable shaft;

and further one-way clutch assemblies concentrically mounted on each of the main shafts of such additional oscillation conversion assemblies and being engaged with the main output gear such that they all positively engage the main output gear sequentially one at a time through corresponding sequential equal rotational arcs of the rotating grooved member.

37. The transmission system of claims 34, 35 or 36 wherein the central section of each oscillation conversion assembly comprises a hollow cylindrical ring having a perimetrical arc shaped radial slot cut-out symmetrically positioned between and sharing the same plane with the two diametrically opposed, protruding, co-axial main shafts radially fitted on its outer perimeter, through which slot the second pivotable shaft is slidably and rotatably mounted such that it can oscillate within such slot through an arc aligned with and co-planar to the said main shafts.

38. The transmission system of claims 34, 35 or 36 wherein the central section of each oscillation conversion assembly comprises a hollow semi-cylindrically shaped horse shoe having a perimetrical arc shaped radial slot cut-out symmetrically positioned between and sharing the same plane with the two diametrically opposed, protruding, co-axial main shafts radially fitted to the horse shoe ends of its outer perimeter, through which slot the second pivotable shaft is slidably and rotatably mounted such that it can oscillate within such slot through an arc aligned with and co-planar to the said main shafts.

39. The transmission system of claims 34, 35 or 36 wherein the central section of each oscillation conversion assembly comprises an outer hollow cylindrical ring having a perimetrical arc shaped radial slot cut-out symmetrically positioned between and sharing the same plane with the two diametrically opposed, protruding, co-axial main shafts radially fitted on its outer perimeter through which slot the second pivotable shaft is freely fitted such that it can oscillate within such slot through an arc aligned with and co-planar to the said main shafts, and an inner hollow cylindrical ring having a centrally positioned orifice on its cylindrical shell through which the second pivotable shaft is rotatably mounted such that said orifice is rotatably aligned with the slot cut-out of the outer ring;

the inner and outer rings being coaxially and rotatably fitted to each other such that the inner ring freely and centrally rotates with respect to the outer ring.

40. The transmission system of claims 35 or 36 wherein the clutch assemblies are mounted between their corresponding conversion assemblies and the main frame.

41. The transmission system of claims 33, 34, 35 or 36 wherein the central cross assembly is a rigid cross assembly comprising a yoke rigidly mounted to the first end of the second pivotable shaft and having its opposed orifices rotatably mounted to the ends of a pair of diametrically opposed coaxial stub shafts rigidly and vertically fixed to the mid point of the first main shaft.

42. The transmission system of claims 33, 34, 35 or 36 wherein the central cross assembly is a rigid cross assembly comprising a flattened first end of the second pivotable shaft which is pivotably mounted to the first main shaft through a horizontal slot centrally located in the mid section of the first main shaft, and wherein the two shafts are held in place through a centrally located pin shaft that passes through two opposed vertical orifices centrally located on either side of the first main shaft'"'"'s horizontal slot and an intervening vertical orifice centrally located on the flattened first end of the second pivotable shaft.

43. The transmission system of claims 33, 34, 35 or 36 wherein the central cross assembly is a pivotable cross assembly comprising a short pivotable central shaft having a flattened central section which is rotatably fitted through a vertical slot centrally located in the mid section of the first main shaft by way of a pin shaft that passes through two opposed horizontal orifices centrally located on either side of the first main shaft'"'"'s vertical slot and an intervening horizontal orifice centrally located on the flattened section of the short central shaft;

and a hollow cylindrical section rigidly mounted to the first end of the second pivotable shaft such that the second pivotable shaft extends radially and vertically outward from a point of the cylindrical section'"'"'s outer perimeter lying at the mid point of the cylindrical section'"'"'s length, the cylindrical section being rotatably mounted to the ends of the short pivotable central shaft by two diametrically opposed orifices lying on the cylindrical section'"'"'s outer perimeter and whose theoretical central axis intersects the cylindrical section'"'"'s longitudinal axis vertically and is co-planar with the second pivotable shaft'"'"'s axis.

44. The transmission system of claims 33, 34, 35 or 36 wherein the central cross assembly is a pivotable cross assembly comprising two parallel circular plates having central horizontal orifices perimetrically connected to each other by two vertically intervening parallel and diametrically opposed plates each fitted with a radially and outwardly protruding co-axial stub shaft, said cross assembly being rotatably fitted over the mid point of the first main shaft which is flange shaped and has a central horizontal orifice, wherein the central pivotable cross assembly and first main shaft are held in place by a pin shaft fitted through the orifices of the two parallel circular plates and the intervening central orifice of the first main shaft;

and a hollow cylindrical section rigidly mounted to the first end of the second pivotable shaft such that the second pivotable shaft extends radially and vertically outward from a point of the cylindrical section'"'"'s outer perimeter lying at the mid point of the cylindrical section'"'"'s length, the cylindrical section being rotatably mounted to the ends of the central pivotable cross assembly by way of two diametrically opposed orifices lying on the cylindrical section'"'"'s outer perimeter and whose theoretical central axis intersects the cylindrical section'"'"'s longitudinal axis vertically and is co-planar with the second pivotable shaft'"'"'s axis.

45. The transmission system of claims 33, 34, 35 or 36 wherein the displacement means comprises a threaded shaft which is vertical to the grooved member'"'"'s axis of rotation and runs through the entire diameter of the rotating grooved member within a second straight squared cross-section groove lying directly behind and radially aligned with the first arc shaped groove, said threaded shaft being rotatable in either direction, said rotation forcing a carriage threadably mounted to the threaded shaft and having an outer body slidably mounted in the second squared cross-section groove to slide up or down the squared cross-section groove;

wherein the rotatable sliding shoe mounted to the second free end of the second pivotable shaft is connected to the threadably mounted carriage through at least one pivotable bracket arm and the rotation of the threaded shaft causes the threadably mounted carriage to shift thereby forcing the second pivotable shaft to be gradually displaced out of alignment with respect to the grooved member'"'"'s central shaft.

46. The transmission system of claim 45 further comprising a counterweight carriage and wherein a first section of the threaded shaft is threaded in one direction and a second section is threaded in the other direction and the threadably mounted carriage occupies said first section and said counter-weight carriage occupies the second section, and the threadably mounted carriage and the threadably mounted counter-weight carriage move apart as the threaded shaft is rotated in one direction and move together as the threaded shaft is rotated in the opposite direction, thereby balancing any vibrations.

47. The transmission system of claim 46 wherein the first and second sections of the threaded shaft each occupy one half of the length of the threaded shaft.

48. The transmission system of claim 47 wherein the thread pitch of the first section is different than the thread pitch of the second section.

49. The transmission system of claim 33 wherein the output gear comprises a double faced gear having a first toothed surface on a first face of the gear and a second toothed surface on a second face of the gear and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly for engaging the second toothed surface of the output gear, said clutch assemblies of said second drive assembly being ninety degrees out of phase with said clutch assemblies of said first drive assembly.

50. The transmission system of claim 34 wherein the output gear comprises a double faced gear having a first toothed surface on a first face of the gear and second toothed surface on a second face of the gear and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly for engaging the second toothed surface of the output gear, said clutch assemblies of said second drive assembly being forty-five degrees out of phase with said clutch assemblies of said first drive assembly.

51. The transmission system of claim 35 wherein the output gear comprises a double faced gear having a first toothed surface on a first face of the gear and a second toothed surface on a second face of the gear and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly for engaging the second toothed surface of the output gear, said clutch assemblies of said second drive assembly being thirty degrees out of phase with said clutch assemblies of said first drive assembly.

52. The transmission system of claim 33 wherein the rotating grooved member comprises a double faced grooved member and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly, the main output gear of said first drive assembly and the main output gear of said second drive assembly being co-rotatable, wherein a first face of the double faced grooved member cooperates with said first drive assembly and a second face of the double faced grooved member cooperates with said second drive assembly, said clutch assemblies of said second drive assembly being ninety degrees out of phase with said clutch assemblies of said first drive assembly.

53. The transmission system of claim 34 wherein the rotating grooved member comprises a double faced grooved member and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly, the main output gear of said first drive assembly and the main output gear of said second drive assembly being co-rotatable, wherein a first face of the double faced grooved member cooperates with said first drive assembly and a second face of the double faced grooved member cooperates with said second drive assembly, said clutch assemblies of said second drive assembly being forty-five degrees out of phase with said clutch assemblies of said first drive assembly.

54. The transmission system of claim 35 wherein the rotating grooved member comprises a double faced grooved member and further comprising a second drive assembly co-axially and co-rotatably mounted with said first drive assembly, the main output gear of said first drive assembly and the main output gear of said second drive assembly being co-rotatable, wherein a first face of the double faced grooved member cooperates with said first drive assembly and a second face of the double faced grooved member cooperates with said second drive assembly, said clutch assemblies of said second drive assembly being thirty degrees out of phase with said clutch assemblies of said first drive assembly.

58. The transmission system of any of claims 33, 34, 35 or 36 wherein the second pivotable shaft is mounted at the midsection of the first main shaft such that the second pivotable shaft can pivot ninety degrees out of phase with respect to the first shaft.

59. Apparatus for providing an infinitely and continuously variable transmission system comprising:

a main assembly having at least one pair of co-axial diametrically opposed one-way clutch assemblies carried by corresponding pairs of diametrically opposed assembly carrying shafts interconnected through a central hub assembly,

the carrying shafts being mounted symmetrically and radially around a multi-directional center of the central hub assembly, the axes of said carrying shafts sharing the same plane with each other and with the central hub'"'"'s multi-directional center, the one-way clutch assemblies being engaged in one rotational direction and disengaged in the opposite rotational direction of their carrying shafts and being uni-directionally meshed to a common rotatable output gear, and means for rotatably oscillating the carrying shafts at gradually variable oscillation arcs, thereby causing the respective clutch assemblies to smoothly rotate the common output gear at correspondingly variable rotation speeds.