WO2019122975A1

WO2019122975A1 - A three-speed differential transmission for increasing rpm in geometric progression with common ratio 3, wherein torque is preserved

Info

Publication number: WO2019122975A1
Application number: PCT/IB2017/058244
Authority: WO
Inventors: Shukhrat MUKHAMEDJANOV
Original assignee: Mukhamedjanov Shukhrat
Priority date: 2017-12-21
Filing date: 2017-12-21
Publication date: 2019-06-27

Abstract

A three-speed differential transmission for increasing RPM in geometric progression with common ratio 3, wherein torque is preserved. The inventive device includes a frame, an input and output shafts, an output shaft housing attached to the output wall of the frame, a carrier, a first large bevel gear rotatably attached to the back end of the input shaft. The first large bevel gear engages at 90 degrees a third large bevel gear rotatably attached on a half shaft to the side wall of the frame. The third large bevel gear engages at 90 degrees a second large bevel gear rotatably mounted onto the output shaft housing. A first medium bevel gear coupled with the second large bevel gear and rotatably mounted onto the output shaft housing. A carrier having a pair of arms attached with one end to the side plane of the first large bevel gear, with the other end rotatably mounted on the output shaft housing. A perpendicular shaft is rotatably attached to the carrier. A second medium bevel gear is attached to one end of the perpendicular shaft and engages at 90 degrees a first medium bevel gear. A first small bevel gear is attached to the other end of the perpendicular shaft and engages a second small bevel gear at 90 degrees attached to the front end of the output shaft. The output shaft is rotatably housed inside the output shaft housing. A load is attached to the other end of the perpendicular shaft next to the first small bevel gear for proper balancing of the perpendicular shaft.

Description

A THREE-SPEED DIFFERENTIAL TRANSMISSION FOR INCREASING RPM IN GEOMETRIC PROGRESSION WITH COMMON RATIO 3, WHEREIN TORQUE IS PRESERVED

The present invention relates to speed/RPM increasing devices and more specifically it relates to a three-speed differential transmission used between input source and generator for increasing RPM of the generator shaft in geometric progression and when set in series a few input rotations of the input source create several thousand output RPM of the generator shaft wherein torque is preserved.

A differential gear train in automobiles is typically designed to drive a pair of wheels allowing them to rotate at different speeds. This is necessary when the vehicle turns, making the wheel that is traveling around the outside of the turning curve roll farther and faster than the other. The average of the rotational speed of the two driving wheels equals the input rotational speed of the drive shaft. An increase in the speed of one wheel is balanced by a decrease in the speed of the other.

An epicyclical differential gear set, also called planetary gear set is used in some automatic transmission systems to increase, reduce or reverse the direction of rotation of the drive shaft. However, as the speed is increased in such gear trains a torque loss occurs due to different gear ratio.

Accordingly, emergency charging generators such as pedal powered or hand crank driven charging devices have very low output generators. Such devices cannot have powerful enough generators due to a tradeoff in conventional transmissions that simply do not allow such emergency devices to have powerful generators. Hence, the maximum output range of such generators doesn’t go beyond 500 Watts. Since large several Kilowatt generators require high speed RPM, conventional transmission gear sets do not provide a viable solution to the problem of driving several Kilowatt generators by pedal force, hand crank or small water/wind power stations at high speed and torque. It is therefore necessary to have a transmission device allowing human power or other low speed input source to rotate emergency charging devices equipped with several kilowatt generators and amplify speed in geometric progression without loss of torque. Other areas of usage include, but not limited to, power stations of any type, pedal powered devices, civil and military vehicles, marine vessels, boats, yachts, cargo ships, helicopters and etc.

There are numerous gear train devices. For example, U.S. Pat. No. 2,783,657 to Kohlhagen Walter; U.S. Pat. No. 106,360 to B. Hamlin; U.S. Pat. No. 1,067,144 to Charles R. Schilling; U.S. Pat. No. 4,550,629 to Mutsumi Kawamoto; U.S. Pat. No. 2,513,217 to Thomas F.I. Tomlines; U.S. Pat. No. 3,812,739 to Yoichi Mori; U.S. Pat. No. 4,395,925 to Hermann Gaus; FR Pat. No. 985.976 to Louis Breguet; FR Pat. No. 977648 to Paul-Robert Clement; FR Pat. No. 55636E to M. Paul-Robert Clement; U.S. Pat. No. 9121481 B2 to Blake Sessions; U.S. Pat. No. 7654934 B2 to Jonas Lars Alfredson; U.S. Pat. No. 3283611 A to Albert A. Weismann, Peter H. Weismann; U.S. Pat. No. 2065661 A to Charles C. Davis; U.S. Pat. No. 2859641 A to Vernon E. Gleasman.

Kohlhagen Walter (U.S. Pat. No. 2,783,657) discloses constant torque drive that is constant in magnitude despite intermittent power input in the drive.

Mutsumi Kawamoto (U.S. Pat. No. 4,550,629) discloses a continuously variable speed transmission for motor vehicles.

M. Paul-Robert Clement (FR Pat. No. 977648) discloses a speed reducer applicable to shaft control, for example, including cardan shafts, simple or coaxial. Further, L. Breguet (FR Pat. No. 985.976) discloses gears which, by means of a fixed control without passing through large gear crowns, rotate rapidly to allow angular displacement of several elements rotating at the same speed or not in the same direction or in the opposite direction.

Jonas Lars Alfredson (US7654934 B2) discloses a differential gear equipped with a selectively controllable locking device which is self energizing, i.e. it utilizes the differentiation energy to self-lock on its own accord.

Blake Sessions (US9121481 B2) discloses differential drive assemblies and methods of making and operating differential drive assemblies.

Albert A. Weismann, Peter H. Weismann (US3283611 A) discloses a differential of a type usable in an automotive vehicle drive train, but differing from the gear types used in most mass-produced automobiles in that one wheel is not permitted under any circumstances to spin relative to the other in the manner of gear type differentials.

Charles C. Davis (US2065661 A) discloses improvements in differential bevel gearing of the type in which a periodic varioation in leverage or torque ratio occurs between mating.

Vernon E. Gleasman (US2859641 A) discloses improvement in differential gearings of the type sometimes referred as Fpositive drive.

While conventional transmission systems and gear trains may be suitable for the particular purpose to which they address, they are not suitable to drive emergency charging devices equipped with several kilowatt generators at high speed and torque. None of the prior art discloses an invention which can efficiently increase RPM of the generator driven by human or low speed input source in geometric progression with common ratio 3 to several thousand rotations wherein torque remains preserved.

In these respects, the present invention substantially departs from the conventional concepts and devices of prior art and in so doing, provide a device primarily developed to increase RPM in geometric progression with common ratio 3 wherein torque is preserved.

A primary object of the invention is to provide a three-speed differential transmission that will overcome the shortcomings of the prior art devices.

Another object is to provide a differential transmission that increases input RPM in geometric progression.

An additional object is to provide a differential transmission that preserves input torque in the output shaft.

A further object is to provide a differential transmission that when set in series allows human power or other low speed input source to rotate several kilowatt generator shafts at high speed and torque.

Another object is to provide a three-speed differential transmission that is not prone to a tradeoff between speed and torque.

Further objects of the invention will appear as the description proceeds.

To the accomplishment of the above and related objects, this invention may be embodied in the form illustrated in the accompanying drawings, attention being called to the fact, however, that the drawings are illustrative only, and that changes may be made in the specific construction illustrated and described within the scope of the appended claims.

Various other objects, features and attendant advantages of the present invention will become fully appreciated as the same becomes better understood when considered in conjunction with the accompanying drawings, in which like reference characters designate the same or similar parts throughout the several views, and wherein:

Fig.1

is an upper perspective view of the present invention.

Fig.2

is a cross-sectional view of the present invention.

Fig.3

is a view from above showing directions of rotation and spinning without a frame.

Fig.4

is a top view of the present invention set in series.

Turning now descriptively to the drawings, in which similar reference characters denote similar elements throughout the several views, FIGS. 1 through 4 illustrate a three-speed differential transmission 10, which comprises a frame 40 having input and output end, an input shaft 14, rotatably attached to the input wall of frame 40, an output shaft 16 rotatably attached to the output wall of frame 40 and a hand crank 12 or other mechanical means attached to the front end of the input shaft 14.

As shown in FIG. 1 of the drawings, a first large bevel gear 20 is mounted to the back end of the input shaft 14 and vertically oriented. A carrier 18 having a pair of arms is attached with one end to the side plane of the first large bevel gear 20. The carrier 18, the first large bevel gear 20, the input shaft 14 and the hand crank 12 rotate as a single unit. A perpendicular shaft is rotatably attached through bearings into the pair of arms of the carrier 18 as best illustrated in FIG. 2 of the drawings and also rotate as a single unit together with the hand crank 12, the input shaft 14, the first large bevel gear 20 and the carrier 18.

As shown in FIG. 1 and 2 of the drawings, an output shaft housing 38 is secured to the output wall of the frame 40. The back end of the carrier 30 rotatably mounted through bearings onto the output shaft housing 38. A second large bevel gear 22 rotatably mounted through bearings onto the output shaft housing and vertically oriented. The second large bevel gear 22 engages at 90 degrees a third large bevel gear 24 rotatably attached on a half shaft 44 to the side wall of the frame 40 and vertically oriented. As best illustrated in FIGS. 1 and 2 of the drawings, the third large bevel gear 24 acts as a neutral gear allowing the first large bevel gear 20 and the second large bevel gear 22 to rotate at a differential to one another.

As shown in FIG. 2 of the drawings, a first medium bevel gear 26 is rotatably mounted and vertically oriented onto the output shaft housing 38 and coupled with the second large bevel gear 22. The second large bevel gear 22 and the first medium bevel gear 26 rotate as a single unit. A pair of rings 42 is attached onto the output shaft 38 next to the second large bevel gear 22 and the first medium bevel gear 26 for preventing shifting of the gears. A second medium planetary bevel gear 28 is attached to one end of the perpendicular shaft 30 and engages at 90 degrees the first medium bevel gear 26. A first small planetary bevel gear 32 is attached to the other end of the perpendicular shaft 30. A load of an appropriate weight 36 is attached to the other end of the perpendicular shaft 30 next to the first small planetary gear 32 for balancing the perpendicular shaft 30. A second small sun bevel gear 34 is attached to the front end of the output shaft 16 and is vertically oriented. The second small sun gear 34 engages the first small planetary gear 32 at 90 degrees. The output shaft 16 rotatably mounted through bearings inside the output shaft housing 38.

The input hand crank 12 or other means of input power source, as shown in FIG. 3 of the drawings, rotates the input shaft 14 in the clockwise direction. Hence, the first large bevel gear 20, the carrier 18 and the perpendicular shaft 30 rotate as well in the same direction simultaneously. The first large bevel gear 20 makes the second large bevel gear 22 and coupled with it the first medium bevel gear 26 rotate in the opposite direction through the third large neutral bevel gear 24.

As the first medium bevel gear 26 engages the second medium planetary bevel gear 28, the rotation of the perpendicular shaft 30 and the first medium bevel gear 26 in the opposite direction create a two-speed spinning velocity of the second medium planetary bevel gear 28. Since the first small planetary bevel gear 32 is attached to the other end of the perpendicular shaft 30, it has the same two-speed spinning velocity. As a result, a single speed rotational velocity of the perpendicular shaft 30 and a two-speed spinning velocity of the second medium planetary bevel gear 28 attached to one end of the perpendicular shaft produce a three-speed unidirectional velocity in the perpendicular shaft and thus in the first small planetary bevel gear 32 attached to the other end of the perpendicular shaft 30 which then transmits a three-speed unidirectional velocity to the engaging second small sun bevel gear 34 attached to the front end of the output shaft 16.

As shown in FIG. 4 of the drawings, when the present invention 10 is placed in series consisting of 5 stages, where the output shaft of the first stage becomes the input shaft of the next stage, the output RPM is increased to over three thousand for mere 15 RPM of the input hand crank. Since the present invention 10 is a three-speed differential transmission, when set in series the speed increase takes place in geometric progression with common ratio 3. Accordingly, a single rotation of the input produces the following speed increase in a five-stage setting:

3, 9, 27, 81, 243

Hence, 15 RPM in the input produce 3645 RPM in the output:

45, 135, 405, 1215, 3645

As best shown in FIG. 1 of the drawings, the rotation of the input hand crank 12 creates a two-speed spinning and one-speed rotational velocities that are combined and transmitted to the output shaft 16. Hence, speed is increased through combination of spinning and rotational velocities. The transmission of torque goes through compound gears where a large gear 22 being the driver and the medium gear 26 being the driven and fixed together transmit input torque further to the second medium gear 28 and from the second medium gear 28 to smaller gear 32 that are attached to the same shaft. Thus, the input torque is preserved in every step of speed increase, both spinning and rotation. This is an important feature of the present invention 10, in that typically any conventional type of transmission devices undergoes torque loss when increasing speed, as speed, according to the conventional method, is derived in the opposite way, when a small gear is the driver and a large gear is the driven gear.

As to a further discussion of the manner of usage and operation of the present invention, the same should be apparent from the above description. Accordingly, no further discussion relating to the manner of usage and operation will be provided.

With respect to the above description then, it is to be realized that the optimum dimensional relationships for the parts of the invention, to include variations in size, materials, shape, form, function and manner of operation, assembly and use, are deemed readily apparent and obvious to one skilled in the art, and all equivalent relationships to those illustrated in the drawings and described in the specification are intended to be encompassed by the present invention.

Therefore, the foregoing is considered as illustrative only of the principles of the invention. Further, since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the invention to the exact construction and operation shown and described, and accordingly, all suitable modifications and equivalents may be resorted to, falling within the scope of the invention.

Claims

A three-speed differential transmission for increasing RPM in geometric progression with common ratio 3 wherein torque is preserved, comprising:
a frame having an input end and an output end;
an input shaft rotatably attached to said input wall of said frame;
an output shaft rotatably attached to the output wall of said frame;
a carrier;
a perpendicular shaft rotatably attached to said carrier;
an output shaft housing fixed to the output wall of said frame;
a half shaft;
a set of gears; and
wherein said set of gears comprises:
a first large bevel gear attached to said input shaft and vertically oriented, wherein a plane of said first large bevel gear is parallel to said perpendicular shaft; and
a second large bevel gear rotatably mounted on said output shaft housing and vertically oriented, wherein a plane of said second large bevel gear is parallel to said perpendicular shaft; and
a third large bevel gear rotatably attached to the side wall of said frame and vertically oriented, wherein a plane of said third large bevel gear is parallel to said carrier; and
a first medium bevel gear rotatably mounted onto said output shaft housing and vertically oriented next to said second large bevel gear, wherein a plane of said first medium bevel gear is parallel to said perpendicular shaft; and
a second medium bevel gear attached to one end of said perpendicular shaft; and
a first small bevel gear attached to the other end of said perpendicular shaft; and
a second small bevel gear attached to the front end of said output shaft and vertically oriented; and
an input hand crank or other input means for rotating said set of gears.
The three-speed differential transmission of claim 1, wherein said first large bevel gear engages said third large bevel gear at 90 degrees, wherein said third large bevel gear engages said second large bevel gear at 90 degrees for allowing said first and said second large bevel gears to rotate at differential to each other.
The three-speed differential of claim 2, wherein said first, said second and said third large bevel gears are of the same radius.
The three-speed differential of claim 3, wherein said second large bevel gear fixed to said second medium bevel gear and rotatably mounted on said output shaft housing.
The three-speed differential transmission of claim 4, wherein said second medium bevel gear and said first medium bevel gear are of the same radius.
A three-speed differential, comprising:
a frame having an input end and an output end;
an input shaft rotatably attached to said input wall of said frame;
an output shaft rotatably attached to the output wall of said frame;
a perpendicular shaft rotatably attached to said carrier;
an output shaft housing fixed to the output wall of said frame;
a load for balancing said perpendicular shaft;
a half shaft;
a set of gears; and
wherein said set of gears comprises:
a first large bevel gear attached to said input shaft and vertically oriented, wherein a plane of said first large bevel gear is parallel to said perpendicular shaft; and
a second large bevel gear rotatably mounted on said output shaft housing and vertically oriented, wherein a plane of said second large bevel gear is parallel to said perpendicular shaft; and
a third large bevel gear rotatably attached to the side wall of said frame and vertically oriented, wherein a plane of said third large bevel gear is parallel to said carrier; and
a first medium bevel gear rotatably mounted onto said output shaft housing and vertically oriented next to said second large bevel gear, wherein a plane of said first medium bevel gear is parallel to said perpendicular shaft; and
a second medium bevel gear attached to one end of said perpendicular shaft; and
a first small bevel gear attached to the other end of said perpendicular shaft; and
a second small bevel gear attached to the front end of said output shaft and vertically oriented;
an input hand crank or other input means for rotating said set of gears; and
a carrier attached with one end of its arms to said first large bevel gear and the other end rotatably mounted on said output shaft housing
The three-speed differential transmission of claim 6, wherein said first large bevel gear engages said third large bevel gear at 90 degrees, wherein said third large bevel gear engages said second large bevel gear at 90 degrees for allowing said first and said second large bevel gears to rotate at differential to each other.
The three-speed differential of claim 6, wherein said first, said second and said third large bevel gears are of the same radius.
The three-speed differential of claim 8, wherein said second large bevel gear fixed to said second medium bevel gear and rotatably mounted on said output shaft housing.
The three-speed differential transmission of claim 9, wherein said second medium bevel gear and said first medium bevel gear are of the same radius.
A three-speed differential transmission for increasing RPM in geometric progression with common ratio 3 wherein torque is preserved, comprising:
a frame having an input end and an output end;
an input shaft rotatably attached to said input wall of said frame;
an output shaft rotatably attached to the output wall of said frame;
a carrier;
a perpendicular shaft rotatably attached to said carrier;
an output shaft housing fixed to the output wall of said frame;
a half shaft;
a set of gears; and
wherein said set of gears comprises:
a first large bevel gear attached to said input shaft and vertically oriented; and
a second large bevel gear rotatably mounted on said output shaft housing and vertically oriented; and
a third large bevel gear rotatably attached to the side wall of said frame and vertically oriented, wherein a plane of said third large bevel gear is parallel to said carrier; and
a first medium bevel gear rotatably mounted onto said output shaft housing and vertically
oriented next to said second large bevel gear, wherein a plane of said first medium bevel gear is parallel to said perpendicular shaft; and
a second medium bevel gear attached to one end of said perpendicular shaft; and
a first small bevel gear attached to the other end of said perpendicular shaft; and
a second small bevel gear attached to the front end of said output shaft and vertically oriented; and
an input hand crank or other input means for rotating said set of gears.
The three-speed differential transmission of claim 11, wherein said first small bevel gear and said second small bevel gear are of the same radius.
The three-speed differential transmission of claim 12, wherein said first large bevel gear engages said third large bevel gear at 90 degrees, wherein said third large bevel gear engages said second large bevel gear at 90 degrees for allowing said first and said second large bevel gears to rotate at differential to each other.
The three-speed differential of claim 11, wherein said first, said second and said third large bevel gears are of the same radius.
The three-speed differential of claim 11, wherein said second large bevel gear fixed to said second medium bevel gear and rotatably mounted on said output shaft housing.
The three-speed differential transmission of claim 11, wherein said second medium bevel gear and said first medium bevel gear are of the same radius.
The three-speed differential transmission of claim 11, wherein one or more stages set in series where the output shaft of the first stage becomes the input shaft of the next stage, the output RPM increases in geometric progression with common ratio 3.