GB2251900A - Variable speed transmission using twin flywheels - Google Patents
Variable speed transmission using twin flywheels Download PDFInfo
- Publication number
- GB2251900A GB2251900A GB9101128A GB9101128A GB2251900A GB 2251900 A GB2251900 A GB 2251900A GB 9101128 A GB9101128 A GB 9101128A GB 9101128 A GB9101128 A GB 9101128A GB 2251900 A GB2251900 A GB 2251900A
- Authority
- GB
- United Kingdom
- Prior art keywords
- mounting
- variable speed
- input device
- transmission mechanism
- speed transmission
- 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.)
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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
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/08—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B is a disc with a flat or approximately flat friction surface
- F16H15/10—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B is a disc with a flat or approximately flat friction surface in which the axes of the two members cross or intersect
- F16H15/12—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B is a disc with a flat or approximately flat friction surface in which the axes of the two members cross or intersect in which one or each member is duplicated, e.g. for obtaining better transmission, for lessening the reaction forces on the bearings
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The transmission comprises two oppositely rotatably mounted flywheels (10, 10a) between which are mounted an input device (14) and an output device (14a) which are both movable radially relative to the flywheels along a support (20) to change the ratio. The input and output devices preferably comprise conical rollers (29, 29a) which can be disengaged from the flywheels by hydraulic pistons (32, 32a) acting through a linkage. Engagement between the rollers and the flywheel is preferably by friction but there could be toothed engagement in which case the gearing would change ratio step by step. <IMAGE>
Description
VARIABLE SPEED TRANSMISSION MECHANISM FIELDS OF THE INVENTION The present invention relates to a variable speed transmission mechanism and particularly to a variable speed mechanism being permissible for stage or no-stage variable speed so steadily without vibration and noise as to provide multi-axial output speed and horsepower effectively.
BACKGROUND OF THE INVENTION
Generally speaking, variable speed operation for a transmission system to meet different conditions or change due to the requirement of operation is one of important cycles of system technology. Today relatively common variable speed gear systems are V-belt or Vario system, hydraulic and automatic variable speed gear mechanism, frequency converter, voltage governor and planet wheel system, etc. Of which said V-belt System to achieve the effect of 3 times to 5 times variable speed by means of adjusting the spacing of pulleys, but the loss of transmission power at the belt is comparatively great. Besides, the range of adjusting the spacing of pulleys is limited so that said System is in failure of to extend the range of variable speed.In general said hydraulic and automatic variable speed transmission mechanism is often applied to the cars and the function of automatic variable speed shall be effective when the car runs at a certain speed. Howeve'r, there are various conditions that tend to affect car speed so that such mechanism should need a sensitive governor being operated together with throttle valves and accelerating pedal simultaneously not convenient for use.
Said frequency converter or voltage governor is provided to change the speed of AC or DC motor but it is not satisfactory for use because loss of output power will occur at the motor. Regarding the planet wheel system, sun wheel is provided as an input end and minor friction wheels are provided to drive internally-connected planet wheel: for variable speed. the position of friction wheels can be changed. In general, the range of variable speed relating to said system is limited within 5 times and max imum power rat-c at I because the disolacement cf friction wheels is limited. Besides, slipping and vibration occur very often at such system to affect the effect of variable speed.
In crder to solve the defects found in those traditional and aforesaid variable speed systems and mechanism, the inventor thus has achieved the present invention through careful thinking together with accumulated experiences in the field of variable speed mechanism and by means of persistent tests and improvements.
,SU,M ARY~OF THE INVENTION
One object of the present invention is to provide a stage or non-stage variable speed mechanism that is effec tive for industrial purpose.
Another object of the present invention is to provide a variable speed mechanism that is permissible for multiaxial output.
Still another object of the present invention is to provide a variable speed mechanism that is effective to extend the range of output speed due to the increase in the diameter of fly wheel and economize energy consumD ti on.
Still another object of the present invention is to provide a variable speed mechanism having the function of clutch device without vibration and noise.
Techniques. elements and its effects for the above and other objects, features and advantages of the present.
invention shall be better understood from the following descriptions wen taken con3unction with the accompany- ing drawings in which preferred embodiments of the present invention are shown by means of llustrative example.
Nevertheless, special terms of ecuioment and accessories are only for explanation, not for limiting its meanings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a cross sectional view, showing the arrangement of the variable soeed mechanism of the present invention, wherein the mechanism is in an initial or low sowed state.
FIG. 2 is a partial sectional view, showing the clutch function of the present invention.
FIG. 3 7s an enlarged partial sectional view taken cn the lines 3-3 of FIG. 1, showing the arrangement of the input device.
FIG. 4 is an enlarged top view, showing the structure of the mounting.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring to the drawings, a variable speed mechanism according to the present invention comprises a pair of gravity fly wheels 10, 10a being mounted in parallel, bearings 11. ila being respectively mounted at the center of each wheel and provided to pivot with each suooorting shaft that is provided mainly for supporting and position- ng fly wheels 10, 10a. For design, a single supporting shaft can be provided to connect oth fly wheels 10, 10a and both ends of shaft are positioned; or two suoporting shafts 12. 12a are provided to connect fly wheels 10, '.0a respectively.Besides, eccentric force of fly wheels 10, 10a would cause a significant influence upon output power cf variable speed mechanism (to be described later).
Therefore, for design the external rim of fly wheels shall be increased with inertia, i.e. the rim of fly wheels 10, 10a should be respectlvely welded or one-pieced together with heavy materials 13, 13a securely (as FIG. 1).
An input device 14 and an output device lox are movably mounted between said fly wheels 10 and 11Ja. Said input device and output device are composed of identical elements. For the convenience of description, only the structure cf the input device 14 except the outout device 14a will be described in details hereunder.
Said input device 14 comprises a mounting 15, a pair of friction wheel assemblies 16, a'hydraulic member 17 and an input shaft 18 (see FIGS. 1 and 4). Said mounting 15 is resembling a rectangular frame, and each major side is outward fixing a guide ring 19 provided for a support 20 going through to permit the mounting being displacable along the support 20 smoothly; a movable frame 21 is pivoted at the inner side in the leading end of mounting 15.
The plane at which said movable frame 21 is mounted is slightly vertical to the plane where said mounting 15 is located. Said movable frame 21 comprises two opposite V type arms 22 being pivoted together uD and down. The end of each V-type arm 22- is formed a bent joint (see FIGS. 2 and 8.). A cross arm 23 is vertically fixed within the mounting 15 and a cylindrical room 24 is located at the central portion of said cross arm 23 provided t accomme- date the hydraulic member 17. An oil pipeline 25 is mounted at side wall of cross arm 23; two opposite arm ends of cross arm 23 are fixed at te mayor sides of said mounting i5 and the other two opDosite arm ends are respectively set in a self-aligning ball bearing 26. The rear ends of the major sides of mounting 15 intersect obliquely and a drum 27 ts mounted at the intersection provided for accom modating a bearing 28.
Said friction wheel assembly 16 is pivoted at the leading end of mounting 15 and has a conical friction wheel 29. The end of axis of said friction wheel 29 is pivoted at bearing seat 36 of V-type arm 22 and the other end of axis is backward and inward pierced into the cross arm 23 provided to pivot bearing 26, and tail end of axis of the wheel 29 is pivoted to a driven bevel gear 30.
Said hydraulic member 17 is accommodated within the mounting 15, including a compression spring 31, a piston rod 32 and a lateral bar 33 (see FIGS. 3 and 4) wherein said spring 31 and piston rod 32 are mounted within the room 24 of said cross arm and the end of said piston rod 32 extends outside the room 24 and expands resembling a block, and a lateral hole is provided for said lateral bar 33 penetrating through and being led to displace back and forth. Each end of said lateral bar 33 extends across the end of each V-type arm 22 inside the leading end of mounting 15. To met the requirement of said lateral bar 33 displacing the mounting 15 has each rectangular slip 34 (see FIGS. 1 and 4) at nner edge on either side of leading end along respective major side.
Said input shaft ; is mounted at rear end of mounting 15 and is forward penetrating through the drum 27 of mounting and pivoted to the bearing 28. the front end of the shaft 19 is pivoted to a driving bevel gear 35 for driving the bevel gear 30 in rotation and further driving the friction wheel assembly 16 hereof.
Basic principle of the present invent' on is to drive the fly wheels 10. 10a by means of the input device 14, to drive the output device 14a in rotation and high-speed output by means of eccentric force and direct contact function of counter-rotation fly wheels 10, la. The input device 14 and the output device 14a are mounted toward the central line of fly wheels 10. 10a but it is not required to specify an angle formed between relative position of said two devices. Besides, within the range of permissible transmission force of fly wheels 10, 10a, we may arrange more than one unit of the input device 14 and the output device 14a so as to meet the purpose of multi-shaft output.But it should be noted that under the premise not to affect said fly wheels' yenuine levelling degree or parallelity, the friction wheels 29, 29a of the input device 14 and the output device 14a should maintain in expanding manner toward the inner faces of fly wheels 10, 10a so as to offer better positive pressure and compensation for friction loss and to facilitate friction wheels to drive fly wheels in rotation effectively. Meanwhile, due to interior shrinkage of friction wheels 16, 16a, it is convenient to remove the input device 14 and output device 14a for maintenance and repairment. The technique that enables friction wheel 29 to hold down or break away from the fly wheels 10, 10a is achieved through movable frame 21 expanding outward or contracting inward due to being driven by the hydraulic member 17.
The object for friction wheels holding down the fly wheels is certainly to promote driving accuracy of friction wheels and fly wheels. However, for practical use rotational speed tends to be limited due to space restriction and over- increased positive pressure is likely to damage the mechanism so that the means for increasing driving accuracy and transmission horsepower can be done through the design for increasing friction coefficient at contact surface between friction wheels and fly wheels.
-Referring to the embodiments of this invention, the internal surface of said fly wheels can be made into a rough surface or convex sublattices, and the surface of friction wheels 29, 29a of the input device 14 and output device 14a also can be made of plastic material.
It is foreseeable that inertia action and static friction must be overcome when we desire to start operating fly wheels 10, 10a, the input device 14 and output device 14a from a static state. To make easy for fly wheels 10, 10a in rotation as well as to reduce the load applied te the input device 14, before starting the variable speed mechanism of the present invention, the friction wheel 29 of said input device 14 is better to contact the rim cf fly wheels 10, 10a as close as possible, and the frlstlon wheel 9a of the output device 14a should contact the center of fly wheels 10, 10a as close as Dos sible (see FIG. 1).
When the input shaft 18 of the input device 14 is driven by external force in fi,xed-spsed rotation, friction wheel 16 is in rotation synclastically to overcome inertia gravity from fly wheels 10, 10a and enable them to rotate slowly and in opposite direction each otter w-herecy they can easily drive the friction wheel 16a of the output device 14a.At this moment, however friction wheel 29a comes near the center of fly wheel to suffer little eccentric force so that friction wheel 1Sa is engaged in slow rotation synclastically only, i.e. the output shaft 18a is in slower rotation but its torsion is increased than the input shaft 20.
When fly wheels 10, 10a begin in fixed-sneed rotation, the input device 14 would come closer to the center of fly wheel gradually until it arrives at a predetermined position and at this moment the input shaft 18, fly wheels 10, ina are engaged in fgxed-speed rotation. When fly wheels 10, 10a are in fixed-speed rotation friction wheel also rotates in fixed speed. When the input device 14 moves near the center of fly wheel, input power would be reduced to economize energy and cause no loss of inertia upon fly wheels. Then enable the output device 14a to move outward gradually as well as the contact position between friction wheel 29a and fly wheels 10, 10a to move outward gradually too.Owing to the distance from said contact position to the center of fly wheels increased eccentric force applied to friction wheel 29a from fly wheels 10, 10a would increase significantly whereby friction due to eccentric force is increased t enable friction wheel 16a to rotate faster, i.e. the output shaft 18a may receive a higher output speed. Especially the more the output device 14a is moving outward, the higher the speed of tha output shaft l.8a is in rotation, whereby the present invention may achieve no-stage variable speed effect by means of the output device 14a movement. During the operation of veri- able speed, the diameter of fly wheels has an extreme influence upon the output of the output device 14a. For practical application the diameter of fly wheels may be enlarged or reduced subject to the user's requirement for output power.
fly fly wheels 10, 10a and friction wheels 29, 29a contact each other and are in rotation, resistance therebetween would be decreased so ttat the input device 14 and output device 14a shall suffer no severe stoppage during displac 7 Il9, that 1S advan tageous for the output device 14 displacing and reaching smooth effect of variable speed to avoid the defects such as vibration, noise and bumping found in conventional gearing mechanisms. Besides, the input device 14 and output device 14a can be engaged in independent or synchronous displacement along the support 20, that is further advantageous for the present invention to develop the characteristics of smooth variable speed operation.For aforesaid devices displacing, the source of power may match the mountings 15, 15a, or shafts 18, 18a to select worm or hydraulic member which concern conventional arts and thus further description is omitted.
Certainly, to drive fly wheels, the input device and output device is not necessarily to apply friction only, the other means such as gearing transmission is also feasible. Since the rotational speed of gear transmission is easier to be controlled it is only required to change friction wheel into bevel gear and provide a toothed face at relatively inner side of fly wheel; however, for using friction wheel, the input device 14 and output device 14a are permissible to be engaged in free displacing so as to achieve no-stage variable speed effect, if using gear random displacement can not be permitted except to control the hydraulic member 17 for intermittently breaking-away, engaging displacement to change position stage by stage, i.e. the output device 14a may receive greater output speed and horsepower than conventional gear transmission mechanism but variable speed operation is stage by stage.
As mentioned above, without resulting in interference, the output device 14 of said variable speed mechanism may be arranged in multiple assemblies. For application according to the present invention characteristics of multi-axial output, output horsepower and rotational speed increasing can be simultaneously applied in a working field such as automobile, factory or power plant to provide power supply to various equipment and they can always achieve better power performance and economize input energy and power.As far as the application to a car is concerned, said variable speed mechanism may provide multishaft output function which is advantageous for being simultaneously applied to such mechanism as steer, gear and clutch system, etc. so as to enable automobile industry to make a breakthrough development. What should be noted another is though the present invention has obtained higher output speed by means cf fly wheel inertia energy ana eccentric force, however higher rotational speed does not cause any problem to the present invent1on in respect of brake because said force input device 2, 14 and output device 14 adept the way of friction transmission witr the characteristics of smooth displacement: when the friction wheel 16a of the outcut-. device '4a is driven by te h > - draulic member 17a to break away from fly wheels 10, lOa, i.e. friction wheel 29a breaks away from fly wheels 10, 10a, (see FIG. 2) rotational speed of the output shaft l'.a is being reduced gradually but fly wheels remain in lner- tia rotation (idle run) so that the output device 14a is not required to move away from the part between fly wheels 10, 10a, whereby it is advantageous for selecting the position to contact fly wheels again and to obtain necessary rotational speed immediately hereof. Besides, as far as fly wheels are concerned the loss of dynamic energy and mechanical energy can be reduced. It is visible from such motion during the braking operation the present invention also has performance like a clutch device. However, the present invention enables engaging/disengaging and variable speed operation to be better than conventional clutch device by means of advantage of displacement so that it can provide a significant contribution to industrial technology.
Obviously, many modlficaticns may be made without departing from the basic spirit of the present invention.
Accordingly, it will be appreciated by those skilled in the art that within the scope of the appended claims, the Invention may be practoed other than has been spec,fi- calls described hereiri.
Claims (13)
1. A variable speed transmission mechanism comprising: a pair of fly wheels arranged in parallel and respectively positioned at a support; an input device mounted at radial position between said pair of fly wheels, provided as power input part to drive fly wheels in opposite rotation each other; an output device mounted at radial position between said fly wheels, having a same structure as said force input device and provided as power output part to transfer rotational power from said fly wheels; when said force input device driving said fly wheels in opposite rotation each other at a fixed speed, said input device being able to reduce necessary input power by means of moving the position of said input device and/or said output device from the rim to the center of fly wheels, and said output device being able to reach smooth effect of variable speed and increasing the range of variable speed by means of transmission by unequal inertia eccentric force.
2. The variable speed transmission mechanism as claimed in claim 1, wherein the inner surface of each fly wheel being made into a rough surface or with convex sublattice and the external side of fly wheels near the rim of wheel being fixed with an appropriate heavy materials.
3. The variable speed transmission mechanism as claimed in claim 1, wherein at least one or more said input device and said output device may be adopted but not required for any opposite or symmetric arrangement.
4. The variable speed transmission mechanism as claimed in claim 1, wherein said input device including a mounting, a pair of friction wheels assemblies pivoted at leading end of said mounting, a hydraulic member mounted within the mounting and an input shaft mounted at rear end of the mounting.
5. The variable speed transmission mechanism as claimed in claim 4, wherein said mounting resembling a rectangular frame, and two major sides being outward vertically fixing with a guide ring respectively provided for a support going through, a movable frame mounted at leading end of said mounting, a cross arm vertically fixed within the mounting, rear ends of major sides of the mounting intersected obliquely, and intersection having a drum for accommodating a bearing.
6. The variable speed transmission mechanism as claimed in claim 5, wherein the plane at which said movable frame located being vertical to the plane where the mounting located, said movable frame composed of two opposite V-type arms pivoted together up and down, the end of each V-type arm formed a bent joint.
7. The variable speed transmission mechanism as claimed in claim 5, wherein said cross arm having a cylindrical room with an oil pipeline provided to accommodate said hydraulic member, opposite ends of the cross arm fixed at major sides of the mounting, and the other opposite ends of the cross arm set in a self-aligning bearing respectively.
8. The variable speed transmission mechanism as claimed in claim 4, wherein each said friction wheel assembly having a conical friction wheel, the end of the friction wheel axis- pivoted at a bearing seat at the top of said V-type arm,.- the other end of the wheel axis being through said cross arm and pivoted to said self-aligning bearing, and the end of the axis pivoted to a driven bevel gear.
9. The variable speed transmission mechanism as claimed in claim 4, wherein said hydraulic member having a compression spring and a piston rod accommodated within the room of said cross arm, the end of said piston rod extending outside the room and expanding to resemble a bloc and provided for a lateral bar to penetrate through.
10. The variable speed transmission mechanism as claimed in claim 9, wherein the ends of said lateral bar respectively penetrating through the end of each V-type arm and extending inside a rectangular slip at inner side on leading ends of the mounting.
11. The variable speed transmission mechanism as claimed in claim 10, wherein said input shaft peing for- ward to penetrate through the drum of said mounting and pivoted to the bearing therein. the leading end of the input shaft pivoted a driving bevel gear provided for engaging and driving the driven bevel gears of said friction wheel assemblies.
12. An input device for a variable speed transmisson mechanism including: a mounting resembling a rectangular frame, major 'sides being fixed with each guide ring externally and verticalls, the inner side on the leading end of the mounting pivoted with a movable frame, the interior of the mounting vertically fixed with a cross arm, and the central part at rear end of the mounting having a drum; a hydraulic member mounted within said mounting, having a compression spring and a piston rod accommodated within the center of said cross arm, the outer end of the piston rod pivoted with a lateral bar provided to drive said movable frame; and an input shaft mounted at rear end of the mounting, being forward to penetrate through said drum the end of the shaft connecting a bevel gear being proper to engage with the bevel gears of said friction wheel assemblies; when power being input the end of the friction whees cr of the force input shaft, the other end being able to output said power. the accuracy of variable speed transms.sion be; maintained by means e f the hydraulic member driving fric tic wheel assemblies to displace radially.
13. The input device as claimed in claim 12, wherein the plane t which said oable frame located being vert-.- cal to the plane ere said mounting located, movable frame composed of opposite V-type arms pivoted together up and down, the end of each V-type arm formed a bent joint.
4 The input device as claimed in claim 12. wherein the interior of said cross arm having a room including an
Oil pipeline provided to accommodate said hydraulic mei- ber, opposite ends of the cross arm fixed at major sides of the mounting, the other opposite ends of the cross arm set in a self-aligning bearing.
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US07/641,477 US5142926A (en) | 1991-01-15 | 1991-01-15 | Variable speed transmission mechanism |
GB9101128A GB2251900A (en) | 1991-01-15 | 1991-01-18 | Variable speed transmission using twin flywheels |
FR9105197A FR2675875A1 (en) | 1991-01-18 | 1991-04-26 | Variable-speed transmission mechanism |
DE9105263U DE9105263U1 (en) | 1991-01-15 | 1991-04-29 | Variable speed transmission device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US07/641,477 US5142926A (en) | 1991-01-15 | 1991-01-15 | Variable speed transmission mechanism |
GB9101128A GB2251900A (en) | 1991-01-15 | 1991-01-18 | Variable speed transmission using twin flywheels |
Publications (2)
Publication Number | Publication Date |
---|---|
GB9101128D0 GB9101128D0 (en) | 1991-02-27 |
GB2251900A true GB2251900A (en) | 1992-07-22 |
Family
ID=26298289
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
GB9101128A Withdrawn GB2251900A (en) | 1991-01-15 | 1991-01-18 | Variable speed transmission using twin flywheels |
Country Status (1)
Country | Link |
---|---|
GB (1) | GB2251900A (en) |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB225133A (en) * | 1924-05-23 | 1924-11-27 | Percy Benjamin Ashworth | Improvements in variable speed gearing |
GB241695A (en) * | 1924-10-04 | 1925-10-29 | Percy Benjamin Ashworth | Improvements in friction gearing |
GB911848A (en) * | 1960-04-08 | 1962-11-28 | William Robinson Andrews | Improvements in and relating to friction driven steplessly variable speed gearing |
GB946850A (en) * | 1961-11-29 | 1964-01-15 | William Robinson Andrews | Improvements in or relating to friction driven, steplessly variable speed gearing |
GB1148886A (en) * | 1965-09-10 | 1969-04-16 | Nat Res Dev | Variable ratio transmission unit |
GB1153572A (en) * | 1965-07-16 | 1969-05-29 | Nat Res Dev | Variable Ratio Transmission Unit |
GB1527959A (en) * | 1976-04-22 | 1978-10-11 | Carini E | Rotary motion producing apparatus |
-
1991
- 1991-01-18 GB GB9101128A patent/GB2251900A/en not_active Withdrawn
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB225133A (en) * | 1924-05-23 | 1924-11-27 | Percy Benjamin Ashworth | Improvements in variable speed gearing |
GB241695A (en) * | 1924-10-04 | 1925-10-29 | Percy Benjamin Ashworth | Improvements in friction gearing |
GB911848A (en) * | 1960-04-08 | 1962-11-28 | William Robinson Andrews | Improvements in and relating to friction driven steplessly variable speed gearing |
GB946850A (en) * | 1961-11-29 | 1964-01-15 | William Robinson Andrews | Improvements in or relating to friction driven, steplessly variable speed gearing |
GB1153572A (en) * | 1965-07-16 | 1969-05-29 | Nat Res Dev | Variable Ratio Transmission Unit |
GB1148886A (en) * | 1965-09-10 | 1969-04-16 | Nat Res Dev | Variable ratio transmission unit |
GB1527959A (en) * | 1976-04-22 | 1978-10-11 | Carini E | Rotary motion producing apparatus |
Also Published As
Publication number | Publication date |
---|---|
GB9101128D0 (en) | 1991-02-27 |
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Legal Events
Date | Code | Title | Description |
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WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |