Patent Publication Number: US-8992370-B2

Title: Infinitely variable pumps and compressors

Description:
This application is a divisional of U.S. patent application Ser. No. 13/915,785 filed Jun. 12, 2013 (now U.S. Pat. No. 8,702,552 issued Apr. 22, 2014), which is a divisional of U.S. patent application Ser. No. 13/568,288 filed Aug. 7, 2012 (now U.S. Pat. No. 8,485,933 issued Jul. 16, 2013) Which claims the benefit of priority to U.S. Patent Application Ser. No, 61/521,408 filed Aug. 9, 2011, and to U.S. patent application Ser. No. 61/523,846 filed Aug. 16, 2011 and is a divisional of U.S. patent application Ser. No. 13/425501 filed Mar. 21, 2012 (now U.S. Pat. No. 8,641,570 issued Feb, 4, 2014) entitled “Infinitely Variable Motion Control (IVMC) for Generators, Transmissions and Pumps/Compressors” and U.S. application Ser. No. 13/568,288 tiled Aug. 7, 2012 (now U.S. Pat. No. 8,485,933 issued Jul. 16, 2013) and is a continuation-in-part of U.S. patent application Ser. No. 13/384,621 (now U.S. Pat. No. 8,388,481 issued Mar. 5, 2013), entitled “Apparatus. and Method for Providing a Constant Output from a Variable Flow Input” filed Jan. 18, 2012, being a national stage entry application of PCT US 10/42519 having an international tiling date of Jul. 20, 2010, all applications of Kyung Soo Han and being incorporated herein by herein by reference as to their entire contents. 
    
    
     TECHNICAL FIELD 
     The technical field of the invention relates to providing infinitely variable motion control in transmissions, wind and river turbines, and pumps and compressors and, in one embodiment, a vehicle with infinitely variable direction control and, in another, zero turn radius (ZTR). 
     BACKGROUND 
     It is generally known in the art to provide devices such as transmissions for vehicles, wind and river turbines (particularly at dams) for the generation of clean electric energy and pumps or compressors with variable speeds. In particular, transmissions are known with many speeds and gears whereby a shifting of gears and speeds typically involves the use of a clutch device so that a range of speed may be changed, for example, through a plurality of gears to reach a maximum number of revolutions per minute of an output shaft in each of the plurality of gears while an input shaft operates within the angular velocity range of, for example, a driving motor. 
     Applicant has been developing a concept referred to herein as infinitely variable motion control (IVMC) whereby an input, a control, and an output provide infinitely variable control without the need for any clutch. 
     Wind and water are examples of renewable energy sources. Wind is variable in velocity, but is “green” and abundant. Recently the demand for wind energy has increased sharply. A more effective and efficient system for reducing the cost of energy (COE) is needed. The rotor assembly of an Old Style Wind Generator (OSWG) rotates at a constant speed and a constant speed generator generates grid compatible constant power. The generator capacity is limited to the lowest torque produced at the cut-in speed which is low. A Current Wind Turbine (CWT) is designed to generate more energy by making the rotor assembly to rotate variably from the cut-in speed to a rated speed. The generator capacity is increased from the lowest torque produced at the cut-in speed to a higher torque produced at the rated speed. The increased capacity is significant; however, the improvement comes with a power converter called a Variable Frequency Converter (VFC). VFC is an assembly of power electronics and converts variable power to grid compatible constant power. VFC is known for having a high failure rate (˜26% of the total), short life (MTBF ˜2 years), expensive (˜$50 k to $120 K for 1.5 mW capacity), and tends to cause other parts to fail prematurely (for example, main bearing and gearbox). 
     River turbines are normally found at locations of dams on rivers for generation of electric energy. During the great depression in the United States, the Tennessee (River) Valley Authority (TVA) was instrumental in building great dams and providing electricity for the state of Tennessee. River turbines are considered in accordance with aspects of the present invention for use within river and stream beds without the need for building large dams and suffer the loss of land to lakes which result from the building of dams. It is suggested that river turbines may be utilized in streams and rivers for generation of electricity to power communities along the rivers and streams. 
     In connection with other embodiments, transmissions, pumps and compressors may comprise mechanical components to introduce infinitely variable motion control and zero radius steering. In this manner, for example, more practical, economical and more efficient vehicles may be built having less costly maintenance. Moreover, it is generally recognized that there is a need in the art for more efficient transmissions, wind and river turbines, and pumps and compressors which are not susceptible to costly breakdown. 
     Introduction to Infinitely Variable Motion Control (IVMC) 
     Differential Dynamics Corporation (DDMotion) has developed several different types of motion control technology to convert a given input to a controlled output. Each technology will be explained briefly first as part of the BACKGROUND. In the SUMMARY, the latest developments in infinitely variable motion controls will be described and, then, in the DETAILED DESCRIPTION of the drawings, the latest developments will be further described along with applications of the technology to some major products such as transmissions, differentials and steering for vehicles, wind and river turbines, and pumps and compressors, and at least one embodiment will be discussed directed to a zero turn radius (ZTR) vehicle. Most of the concepts disclosed herein are based on the Kyung Soo Han&#39;s previous developmental work as exemplified by the patents and publications discussed briefly below. 
     U.S. Pat. No. 6,068,570 discusses speed control with planetary gears, speed control with spur gears, worm and worm gear control and compensated variable speed control. U.S. Pat. No. 6,537,168 discusses direction control with bevel gears and direction control with spur gears. U.S. Pat. No. 7,731,616 discusses a variable pitch cam. U.S. Pat. No. 7.462,124 discusses three variable control where the variable control comprises an input, an output, and a control. U.S. Pat. No. 7,731,619 discusses three variable control with bevel gears and three variable control with spur gears. W02011011358A2 is a published international application of PCI U.S. 10/42519 filed Jul. 20, 2010 andclaiming priority to provisional patent application 61/226,943 filed Jul. 20, 2009, which describes a speed converter with cam driven control and a variable torque generator producing a constant frequency and voltage output from a variable input. This PCT application has been filed in the United States as U.S. patent application Ser. No. 131384,621, filed Jan. 18, 2012 (now U.S. Pat. No. 8,388.481 issued Mar. 5, 2013), Since priority is claimed to this &#39;621 national stage entry patent application, its teachings are not to be considered prior art to the present IVMC apparatus. Applications of this speed converter/variable torque generator technology include and are not limited to applications in the field of clean energy generation such as wind and water driven electrical energy generators, All of the above-identified patents and published applications are incorporated by reference herein as to their entire contents. 
     SUMMARY OF THE SEVERAL EMBODIMENTS OF IVMC 
     This summary is provided to introduce a selection of concepts. These concepts are further described below in the Detailed Description. This summary is not intended to identify key features or essential features of the claimed subject matter, nor is this summary intended as an aid in determining the scope of the claimed subject matter. 
     Three variable mechanical controls may be used to convert variable input to constant output or constant input to variable output. Mechanical controls are efficient and scalable. All gear assemblies having three variables, input, output, and control, will be called “transgears” in this context. As will be described in the context of  FIG. 1 , a spur gear transgear is utilized to form clutches per  FIG. 2 , differential steering per  FIG. 3  and build speed converters that operate pumps, compressors and the like therefrom. 
     A first control technology described herein may be referred to as cam driven infinitely variable motion control. Cam control iS thoroughly described in  FIG. 7  U.S. patent application Ser. No. 13/425,501filed Mar. 21, 2012 (now U.S. Pat. No. 8,641.570 issued Feb. 4, 2014). A variable pitch cam assembly may comprise an eccentric inner cam  702  that comprise a portion of a shaft  701 , for example, an input shaft or an output Shaft. The inner eccentric cam may be positioned and free to move within an eccentric outer cam  703 . The control assembly thus comprises a shaft, the inner cam and an outer cam. The control assembly may be continuously controlled from a minimum eccentricity when the shaft is located central to the cam assembly,  FIG. 7(D) , to .a period of maximum eccentricity,  FIG. 7(E) , when the shaft is located most proximate to the edge of the cam assembly; In this eccentric position, When the shaft rotates, the cam assembly forms an effective cam profile as depicted in  FIG. 7(E)  such that the profile is in the form of a circle having a much larger diameter than when the inner and outer cams are in a least eccentric position. 
     A further control technology as described herein may be referred to a ratchet bearing or a one-way clutch bearing ( FIG. 8  of U.S. patent application Ser. No. 13,425,501 filed Mar. 21, 2012 (now U.S. Pat. No. 8,641,570 issued Feb, 4, 2014). A Sprag is a trade name for such a bearing and is commercially available, for example, from Renold plc, of the United Kingdom and from NMTG of India. Sprag may be used herein as a short-hand for such a bearing and assembly which is free-wheeling in one direction of rotation and engaged in the other rotation direction and may be referred to herein generally as output gears, or example, when discussing a driver and its application in a cam controlled speed converter. 
     An external housing  800  of such a ratchet or one-way clutch bearing (or Sprag) has at least one notch  805 ,  806  for receiving, for example, a needle roller  803 ,  804  and the needle roller rolls prevents roiling such that when an internal race is moving in one rotational direction, the outer housing may move in either direction and be free-wheeling (or vice versa, if the outer housing rotates, the inner race  801  may move) because the needle roller  803 ,  804  is loose or free-wheeling and located at one end of its associated notch. On the other hand, when the internal race  801  rotates in the other rotational direction with respect to the outer housing  802  or vice versa, the needle roller rolls into an engaged position between the race and the notch such that the housing  802  is controlled to rotate in this other rotational direction with the inner race  801 . 
     A further control technology is accomplished when the cam controlled assembly technology described above is used as a driver ( FIG. 9  of U.S. patent application Ser. No. 13/425,501 filed Mar. 21, 2012 (now U.S. Pat. No. 8,641.570 issued Feb. 4, 2014)). A Sprag  912 ,  913  is embedded inside an output gear  910 ,  911  and the race of the ratchet bearing or one-way clutch is attached to the output shaft for rotation it E one direction. 
     A rotor blade has a pitch used, for example. to capture renewable energy such as wind energy or water energy which causes a rotor to rotate and so turn an input shaft ( FIG. 17  or  18  of U.S. patent application Ser. No. 13/425.501 filed Mar. 21, 2012 (U.S. Pat. No. 8,641,570 issued Feb. 4, 2014)). Rotor blade pitch may be controlled to further control the control technologies introduced above to achieve a pitch-controlled infinitely variable motion control to provide for example, a relatively constant velocity output from a variable velocity input. 
     Finally, input compensated infinitely variable motion control ( FIG. 22  of U.S. patent application Ser. No. 13/425,501 filed Mar. 21, 2012 (now U.S. Pat. No. 8,641,570 issued Feb. 4, 2014)) may comprise two independent inputs, a drive input and a control input, and an output for a three variable control motion control, A system or variable output may be achieved by releasing the drive input so that the output may be varied. 
     These several technologies will be further described with reference to particular applications in generators, transmissions and compressors or pumps and are depicted in the drawings, a brief description of which follows. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The features and advantages of the present invention will become more apparent from the detailed description set forth below when taken in conjunction with the drawings in which like reference numbers may indicate identical or functionally similar elements. 
         FIGS. 1(A) ,  1 (B) and  1 (C) provide mechanical diagrams of a spur gear transgear assembly wherein  FIG. 1(A)  is a left view,  FIG. 1(B)  is a front view and  Figure 1(C)  is a right view and wherein a spur gear transgear assembly is a building block of embodiments described below wherein the present spur gear transgear assembly may be preferred for embodiments described herein, but other types may be used as appropriate as described in U.S. patent application Ser. No. 13/384,621 (now U.S. Pat. No. 8,388,481issued Mar. 5, 2013),  FIGS. 1-6 , incorporated herein by reference as to its entire contents. 
         FIGS. 2(A) ,  2 (B) and  2 (C) provide mechanical diagrams of spur gear transgear clutch embodiments wherein  FIG. 2(A)  depicts a first embodiment;  FIG. 2(B)  depicts a second embodiment and  FIG. 2(C)  depicts a third embodiment, the spur gear transgear clutch most practically being actuated by a brake wherein a transgear clutch embodiment as depicted and described herein is compact, non-grinding and economical to manufacture and maintain. 
         FIG. 3  provides an overview mechanical diagram of a spur gear transgear differential steering assembly that comprises a speed controlled steering system such that by braking one side of a differential, the other side will be speeding up faster. The concept may be considered opposite in concept to differential reaction to the steering. 
         FIGS. 4(A) and 4(B)  provide an overview mechanical diagram of an Infinitely Variable Motion Control (IVMC) speed converter wherein  FIG. 4(A)  is a front view and  FIG. 4(B)  is a sectional view. This is a variable pitch earn controlled IVMC with the cam control shown in  FIG. 4(B) . The output is infinitely variable from zero to a designed or predetermined maximum speed. 
         FIGS. 5(A) and 5(B)  provide an overview mechanical diagram in  FIG. 5(A)  and speed range graph in  FIG. 5(B)  for a Two Speed Range IVMC. City driving of a typical vehicle is stop-and-go while highway driving is an over-drive (typically at a constant high speed with few stops except for emergencies). By adding a by-pass circuit, the highway driving can be done by the engine and the IVMC system can be by-passed in, this embodiment. 
         FIG. 6  provides an overview mechanical diagram of an Infinitely Variable Transmission (IVT). This IVMC transmission is a speed converter with a direction control and so provides a forward, neutral and reverse direction. 
         FIG. 7  provides an infinitely variable transmission (IVT) with a built-in Differential where IVT is an IVMC with a direction control. The differential can be open or locked. This embodiment comprises a compact transaxle. 
         FIG. 8  provides an overview mechanical diagram for a Zero Turn Radius (ZTR) speed converter with direction controls. An IVMC with two direction controls can make two driving wheels turn independently (one forward and one reverse) and so provide a ZTR. 
         FIG. 9  provides an overview mechanical diagram of a Reciprocating Pump which may be used to advantage in many applications. By replacing the drivers with pistons, the mechanical drive system can be changed to hydraulics. The output of the depicted reciprocating pump is infinitely variable from zero to the designed maximum. 
         FIGS. 10(A) and 10(B)  provide an overview mechanical diagram of a Pitch Controlled Speed Converter (useful, for example, in wind or river electricity generation) wherein  FIG. 10(A)  provides a front view and  FIG. 10(B)  provides a side view. When the variable input (such as wind speed or water flow rate) rotates a rotor, the variable input can be converted to a constant output by controlling the rotor blade pitch with a feedback and/or a feed-forward control system. 
         FIGS. 11(A) ,  11 (B) and  11 (C) provide an overview mechanical diagram of an Input Controlled Speed Converter wherein  FIG. 11(A)  is sectional view;  FIG. 11(B)  is a top view; and  FIG. 11(C)  depicts an alternative embodiment of a hatch assembly input control. The embodiment may lie at the bottom (or under the water surface) of a river, a stream or near an ocean shore for capturing wave or tidal motion and energy. The kinetic energy of flowing water is high and the harnessing members must be durable. An embodiment of this system is a fixed pitch waterwheel with a hatch which is opening or closing depending on water flow to control the input flow. 
         FIGS. 12(A) ,  12 (B) and  12 (C) provide overview mechanical diagrams of an Input Controlled and Input Compensated Speed Converter wherein  FIG. 12(A)  is a sectional view;  FIG. 12(B)  is a top view; and  FIG. 12(C)  depicts an alternative embodiment of a hatch assembly input control. In this embodiment, if the flow speed is erratic and the hatch control is not adequate, another control system can be added. The input compensating system is releasing overshoot to make the output constant. The releasing is different from the driving and the required force is much less than the driving. 
         FIGS. 13(A) ,  13 (B) and  13 (C) provide an overview mechanical diagram of a Variable Torque Generator (VTG) which may be continuously adjusted from minimum to maximum torque wherein  FIG. 13(A)  shows minimum overlap of a rotor and a stator;  FIG. 13(B)  shows medium overlap between a rotor and a stator and  FIG. 13(C)  shows maximum overlap between a rotor and a stator. To minimize the cut-in speed and maximize the energy harnessing, the generator rotor and stator overlap is continuously controlled. 
         FIG. 14  provides an overview of a cam controlled infinitely variable compressor as first presented as  FIG. 14  of US patent application Ser. No. 13/1425,501 of the same inventor filed Mar. 21, 2012 (now U.S. Pat. No. 8,641.570 issued Feb. 4, 2014) and described therein as showing a rotary pump or compressor at an output which may be driven by a constant motor input with speed control ( FIG. 4(A)  and  FIG. 4(B) , IVMC Speed Converter), the cam-controlled infinitely variable motion control (IVMC) controlling the pump/compressor rotational speed in rpm while the motor input is constant wherein  FIG. 14  provides a cross-sectional front view. . 
         FIG. 15  provides an overview of a further cam controlled infinitely variable compressor (reciprocating pump) as first presented as  FIG. 15  of U.S. patent application Ser. No. 13/425,501 of the same inventor filed Mar. 21, 2012 and described therein as having a driving motor at an input  1501  to a speed converter for operating a reciprocating pump  1503  under cam control  1502  in cross-sectional front view. 
         FIG. 16  provides an overview of a pitch controlled infinitely variable compressor/pump as first presented as  FIG. 20  of U.S. patent application Ser. No. 13/425,501 of the same inventor filed Mar. 21, 2012 and described therein as used to control the pitch controlled pump or compressor, shown in cross-sectional front view. 
         FIG. 17  provides an overview of an input compensated infinitely variable pump or compressor with an input compensating motor as first presented as  FIG. 24  of U.S. patent application Ser. No. 13/425,501 of the same inventor filed Mar. 21, 2012 and described therein as utilizing the input compensated infinitely variable motion control of  FIG. 22  of U.S. patent application Ser. No. 13/425,501 of the same inventor tiled Mar. 21, 2012, for driving a compressor or a rotary pump  1710  in cross-sectional front view. 
     
    
    
     These applications of variations and technologies of infinitely variable motion control (IVMC) with respect to embodiments of transmissions, wind and river turbines and pumps/compressors will be further described in the detailed description of the drawings which follows. 
     DETAILED DESCRIPTION 
     The present invention is directed to applications of infinitely variable motion control (IVMC) in transmissions, wind and river turbines, and pumps/compressors wherein transgears are used for control, for example, spur gear transgears. A spur gear transgear will be described with reference to  FIGS. 1(A) ,  1 (B) and  1 (C); however, a plurality of embodiments of a transgear assemblies may be utilized to advantage as alternatives in accordance with U.S. application Ser. No. 13/425,501,  FIGS. 1-6 , incorporated herein by reference as to its entire contents. 
     Transgear: Spur Gear Transgear 
     A spur gear assembly  100 , for example, shown in  FIG. 1(A) , left view,  FIG. 1(B) , front view, and  FIG. 1(C) , right view, is an example of a transgear assembly having an input (input shaft  101  is driven from the left), an output (sleeve  106  provides the output), and a control (a mechanical concept similar in concept to an electronic transistor) such as a carrier assembly provided by a series of planetary gears, carrier brackets and pins. Spur gear transgears may be used as differentials, but their applications as controls may be virtually unlimited. 
     Referring to left view  FIG. 1(A)  and front view  FIG. 1(B) , an input gear comprising a left sun gear  102  is attached to and may be integral with input shaft  101  (seen in the center of corresponding front view  FIG. 1(B) ). Planetary gears  103  and  103 B are meshed to left sun gear  102 , and planetary gears  104  and  104 B are meshed to right sun gear  105 . The planetary gears  103  and  104 , and  103 B and  104 B are meshed respectively. Right sun gear  105  may be attached to or integral with right sun gear sleeve  106  which surrounds shaft  101  and provides the output. Other components of transgear assembly  100  include left carrier  108  and right carrier  109 , each of which may be a disc or gear. Components  110 ,  110 B,  111  and  111 B comprise pins. The assembly  100  thus comprises a spur gear transgear with input, output and control. Assembly  100  is very similar in mechanical diagram to the spur gear assembly of  FIG. 3  of U.S. application Ser. No. 13/384,621 filed Mar. 21, 2012 by Mr. Han. 
     The elements of the drawings denoted with “B” at the end of each reference numeral, (sec, for example.  FIG. 1(B) , reference numerals  103 B,  104 B,  110 B and  111 B), refer to an extra set of components, such as carrier portions and gears for enhanced, more balanced performance. For example, gear  103 B may, however, provide greater torque capacity and dynamically balance the spur gear transgear system  100 . 
     Spur gear transgears may basically comprise two sun gears  102 ,  105 , meshed with each other through planetary gears  103 ,  104 . Spur gears may he either regular spur gears or helical gears. 
     Referring to  FIG. 1(B) , front view, left sun gear  102  is attached to or integral with input shaft  101 . Carrier brackets  108  and  109  are attached together with pins  110  and  111 . Planetary gears  103  and  104  may rotate freely around the pins  110 ,  111  and mesh with sun gear  102  (input) and sun gear  105  (output) respectively. Thus, the output  105  having sleeve  106  is controlled by the planetary and sun gears forming a basic spur gear transgear assembly  100 . 
     Assume that input rotational energy is connected to input shaft  101  and so shaft  101  rotates clock-wise and the carriers  108 ,  109  and pins  110 ,  111  are fixed. Left sun gear  102  is the input gear and right sun gear  105  is the output gear connected to an output sleeve  106 . The input sun gear  102  may rotate clock-wise (CW) with the input shaft  101 . Planetary gear  103  then rotates counter clock-wise (CCW), and planetary gear  104  rotates clock-wise (CW), and right sun gear  105  of the output rotates CCW along with output sleeve  106 . Since the sun gears  102  and  105  are the same size in diameter as seen in  FIG. 1(B) , the angular rotation will be same at input and output, but the input and output rotate in opposite directions from one another. This spur gear transgear  100  with the same size sun gears may be called a “basic transgear.” 
     Spur Gear Transgear Clutches 
     Embodiments of Spur Gear Transgear Clutches are shown in  FIGS. 2(A) ,  2 (B) and  2 (C). Similar reference numerals are used in  FIGS. 2(A) ,  2 (B) and  2 (C) to denote similar elements where the first digit indicates the figure number where the element first appears. For example, shaft  101 , left sun gear  102  and so on having the same names appear as similar components with similar function in the  FIGS. 2(A) ,  2 (B) and  2 (C) as in the  FIGS. 1(A) ,  1 (B) and  1 (C). Elements beginning with the numeral  2  denote elements first introduced in  FIGS. 2(A) ,  2 (B) and  2 (C) such as center block  201  and brake disc  202  (attached to left sun gear  102  through a sleeve).  FIG. 2(A)  shows an output direction being the same direction (for example, both input and output arc CW) but with the output speed (rotational velocity) being two times faster.  FIG. 2(B)  shows an output direction being opposite, i.e., the input shaft  101  may be CW and the output sleeve  106  CCW and the output rotational velocity or speed being the same at input and output.  FIG. 2(C)  shows an output direction being the same, i.e., the input shaft  101  may be CW and the output sleeve  245  CW, and the output rotational velocity or speed being the same at input and output. 
     Referring to  FIG. 2(A) , embodiment clutch  200 . Center block  201  may be either attached to or is integral with shaft  101 . Brake Disc  202  is attached to left sun gear  102  through an associated sleeve proximate to input shaft  101 . Band brake  203  of brake disc  202  (or alternative brake mechanism known in the art) is shown in black and may denote a braking mechanism inside a vehicle operated by a vehicle operator. The input is the carrier through a center block  201  and the output is right sun gear  105 . The control is left sun gear  102 . Since the planetary gears are rotating around the stationary left sun gear  102 , and the sun gears are the same in size, the right sun gear  105  rotates two times faster than the input shaft  101 . This is the same as in a bevel gear transgear. With respect to the direction, the input may be CW. As the carrier rotates CW, planetary gear  103  rotates CW, planetary gear  104  CCW and right sun gear  105  CW. So the output direction is the same as the input direction in this embodiment. 
     As shown in either  FIG. 2(B) , clutch embodiment  220 , or  FIG. 2(C) , clutch embodiment  240  are shown with no brake disc  202  provided. On the other hand, braking is similar. Brake Disc  221  is attached to a sleeve which in turn couples with pins and carriers, carrier  108 , in particular. Pressure applied via band brake  222  brakes the speed of carriers  108  and  109 . The input is left sun gear  102 , the carrier is the control and the right sun gear  105  is the output. So left sun gear  102  may turn CW,  103  CCW,  104  CW and  105  CCW. So the output direction CCW may be opposite the input CW. The speed is the same since the sun gears are the same size as explained above with reference to  FIG. 1 . 
       FIG. 2(C) , clutch embodiment  240 , starts with the basic embodiment of  FIG. 2(B) , embodiment  220 , and adds additional components for providing the same direction at output as input. Gear  241  is attached to or may be integral with right sun gear sleeve  106 . Two direction change gears are provided, direction change gear #1  242  and direction change gear #2  243 . Direction change gear #1 is meshed to gear  241  and direction change gear #2 is meshed to an output gear  244  of output gear sleeve  245  and to direction change gear #1  242 . 
     Spur Gear Transgear Differential Steering Assembly 
     Referring now to  FIG. 3 , there is shown a mechanical diagram for providing spur gear transgear differential steering. Shaft  101  is shown not attached to or integral with any members; (shaft  101  is a support member). Left sun gear  102  is attached to sleeve  303 . As before, planetary gear  103  is shown with left sun gear  102 . Carriers  108  and  109  are similarly shown. Right sun gear  105  may be attached to or integral with an output sleeve  307 . 
     New to  FIG. 3  are input shaft  301  displaced from shaft  101 . Shaft  101  may just be a support shaft but can be attached to or be integral with one of the sleeves  303  or  307  and so reduce the number of parts in an alternative embodiment. Input shaft  301  is coupled to input gear  302  associated with left carrier  108  and right carrier  109 . Sleeve  303  is attached to or integral with left sun gear  102 . For braking, brake disc  304  is attached to sleeve  303 . Pressure applied to band brake  305  is felt at sleeve  303  which is attached to left driving wheel  306  and so slows a left wheel. Similarly, on the right. sleeve  307  is attached to or integral with right sun gear  105 . For braking, brake disc  308  is attached to sleeve  307 . Pressure applied to band brake  309  is felt at sleeve  307  which is attached to right driving wheel  310  and so slows a right wheel. When one wheel slows down, the other wheel may speed up for steering in the direction of the slower wheel. 
     IVMC Speed Converter 
     Referring now to  FIGS. 4(A) and 4(B) , an Infinitely Variable Motion Control (IVMC) speed converter comprises an input shaft  403  and an output shaft  424  with a shaft  101  serving as a cam shaft. The IVMC speed converter further comprises a variable pitch cam (inner cam  420 , outer cam  422 ) surrounding cam shaft  101  and is shown in Section A-A of  FIG. 4(B)  embedded in front view  FIG. 4(A) . A variable pitch cam is extensively shown and described in connection with the description of  FIGS. 7(A) through 7(E)  of U.S. application Ser. No. 13,425,501, filed Mar. 21, 2012, incorporated by reference as to its entire contents. Inner cam  419  and outer cam  421  form a similar variable pitch cam surrounding cam shaft  101 . At the bottom of Section A-A.  FIG. 4(B) , is a Sprag gear assembly surrounding output shaft  424  having race section  423 . Race section  423  of output shaft  424  couples with Sprags  429 ,  430 ,  431  and  432  and having output gears  425 ,  426 ,  427 ,  428  designated together but seen separately. Together section A-A forms a driver  416  which is duplicated in  FIG. 4(A)  as driver  415 . Pins  413 ,  414  are designated together and associated with slots  409 ,  410 ,  411  and  412  discussed further below. 
     To the left of  FIG. 4(A)  is seen a spur gear transgear assembly  100  comprising cam shaft  101 , left sun gear  102  integral or attached to a sleeve surrounding cam shaft  101 , planetary gear  103  integral with or attached to cam shaft  101 , carriers  108 ,  109  (see FIGS.  1 (A) through  1 (C)), pins  110 ,  111  (not marked) and so on. With respect to newly shown components, in  FIG. 4 , worm  402  turns worm gear  401  which is attached to or is integral with the sleeve and left sun gear  102  and meshed to carrier gears  108  and  109  of spur gear assembly  100  ( FIG. 1 ). A drive gear  405  is attached to input shaft  403  and meshed to slotted gears  406 ,  407  and  408 , where slotted gear  406  has one slot at the top, slotted gear  407  has two slots, one at the top and one at the bottom, and slotted gear  407  has one slot at the bottom. Slots  409 ,  410 ,  411  and  412  are designated together where slot  410  and slot  411  are at the middle of slotted gear  407 . The operation of slotted gears is described by reference to  FIGS. 11) and 11  U.S. application Ser. No. 13/435,501 filed Mar. 21, 2012, incorporated by reference in its entirety. 
     IVMC with Two Speed Ranges 
     Referring to  FIG. 5(A) , there is shown an IVMC with two speed ranges, city I and highway III, and a transition speed range II as seen from graph  FIG. 5(B) . The IVMC speed converter  400  of  FIGS. 4(A) and 4(B)  has been so modified and may be enclosed in an outer housing including a brake system and be, for example, in the form of a vehicle. IVMC  500  operable at city and highway speeds is modified from  FIGS. 4(A)  and (B) by further including brake disc  501  and band brake  502  for input shaft  403 . Moreover, additional gears are provided including gear  503  surrounding cam shaft  101 , and output gear  504  surrounding output shaft  424  where output gear  504  further has an associated Sprag  505 . Note that in an alternative embodiment, gear  503  may not be needed if carrier gears  108  and  109  are meshed to output gear  504  directly. Operationally, when the band brake  502  is engaged, output gear  504  may rotate in the same direction but faster than output gears  425 ,  426 ,  427  and  428 . 
     Infinitely Variable Transmission or IVT (Speed Converter and Direction Control) 
     Referring to  FIG. 6 , there is shown a combination of the IVMC speed converter  400  of  FIG. 4(A)  with the addition of a direction control. A discussion of  FIGS. 4(A) and 4(B)  will not be repeated and the emphasis will be placed on direction control  600  wherein input shaft  403  and worm  402  are shown. Output shaft  424  extends from speed converter  400  to direction control  600  and comprises right sun gear  601  (similar to a right sun gear of spur gear transgear  100  of  FIG. 1(B) ). Left sun gear  602  is likewise similar to a left sun gear of spur gear transgear  100 . Brake disc  603  is operated by band brake  604 . Carrier gears  605  and  606  are likewise similar to the carrier gears of transgear  100 , left side. Right sun gear  607  is similar to the right side of spur gear transgear  100  ( FIGS. 1(A) , (B) and (C)). Left sun gear  608  is attached to or integral with carrier gear  606  which is similar to the right side of spur gear transgear  100 . Further braking is provided by right carrier and brake disc  609  operated by band brake  610 . Output shaft  612  is now able to operate in forward, neutral and reverse where output gear  611  is meshed to carrier gears  605  and  606 . Assume that the shaft  424  is rotating one revolution CW. If band brake  604  is applied (braked), carrier brackets  605  and  606  will rotate one half rotation CW. If band brake  610  is applied (braked) the carrier will rotate one revolution CCW. When the band brakes  604  and  610  are not applied (not braked), the carrier will be free or neutral. 
     Infinitely Variable Transmission (IVT) with Differential 
     Referring to  FIG. 7 , there is shown a combination of the IVMC speed convener  400  of  FIGS. 4(A) and 4(B)  with the addition of direction control and a differential. Neither speed converter elements designated in the  400  series nor direction control elements designated in the  600  series will be described again in detail. Attention will be focused on new differential elements designated in the  700  series. Direction control and differential  700  are driven by shaft  424  from speed convener  400 . The right differential shaft  713  is coupled to shaft  424  by directional control comprising a band brake  604  and  611 . Carrier gears  605 ,  606  are shown as is left sun gear  608  which may be attached to or integral with output gear  706 . 
     The differential portion of direction control and differential  700  comprises elements  701 - 713 . Referring to the spur gear transgear of  FIGS. 1(A) , (B) and (C), carrier gear  701  (Left side of spur gear transgear  100 ) and carrier gear  702  are similar as are right sun gear  703  and left sun gear  704 . Left differential output sleeve  705  surrounds right differential output shaft  713 . Brake disc  711  is operated by band brake  712  on differential output shaft  713 . Left sun gear output gear  706  is similar to the right side of spur gear transgear  100 . Left carrier gear  707  is likewise similar to the right side of spur gear transgear  100 . Right carrier  708  is similar to the right of transgear  100  and left sun gear  709  is also similar to the right of spur gear transgear  100 . Right sun gear  710  is similar to the right sun gear of spur gear transgear  100 . The differential can be open or locked. This embodiment comprises a compact transaxle. There are two outputs from the direction control: carrier gears  605  and  606 , and gear  706  that is attached to left sun gear  608  and carrier gear  606 . Carrier gears  605  and  606  are meshed to carrier gears  701  and  702 . The gear ratios are, for example, one to one. Gear  706  is attached to left sun gear  608  and is meshed to carrier gear  707 , and the ratio is, for example, one to two. If the direction control output is one revolution CW, carriers  701  and  702  will be rotating one revolution CCW, and carrier  707  will be rotating one half revolutions CCW. When band brake  712  is not engaged, the differential outputs are sleeve  705  to the left and shaft  713  to the right. The input to carrier  707  is not in effect. This state is now an open differential. When band brake  712  is engaged or right sun gear  710  is fixed, and not rotating, left sun gear  709  will be rotating one revolution CCW. Since left sun gear  709  and right sun gear  703  are attached to shaft  713 , left sleeve  705  does not have freedom to rotate. This means that the differential is rotating one revolution CCW without freedom, or is locked. 
     An IVMC Speed Converter with Zero Turn Radius (ZTR) 
     Referring to  FIG. 8 , there is shown an IVMC speed converter of  FIGS. 4(A) and 4(B)  having an output shaft  424  which drives two direction control assemblies according to  FIG. 6 , one assembly  600  on the left of speed converter  400  and one on the right of speed converter  400 . With first and second direction control assemblies, one can achieve a zero turn radius (ZTR). In the embodiment of  FIG. 8 , shaft  803  may be turned clock-wise (or CCW) at the same time as shaft  806  may be turned counter clock-wise (or CW). In this manner, a vehicle may be turned “on a dime” with zero turn radius. The zero turn radius is achieved by appropriate actuation of band brakes  801 ,  802 ,  804 ,  805  where brake bands  801  and  804  comprise left band brakes and  802  and  805  comprise right band brakes. Band brakes  801  and  802  operate oppositely on left output shaft  803  in concert with band brakes  804  and  805  operating oppositely on right output shaft  806 . In a ZTR left turn, shaft  803  turns oppositely from shaft  806  so that  803  moves a vehicle downward on the drawing sheet and shaft  806  moves the vehicle upwards on the drawing sheet so that the turning radius is defined by the width of the vehicle or between wheels (not shown) which would be attached to the shafts  803 ,  806 . Note that in an alternative embodiment, instead of one IVMC and two sets of direction controls, two sets of IVMC  400  and direction control  600 , one set for a left wheel and one set for a right wheel may also be employed to construct a ZTR steering. A vehicle engine (not shown in  FIG. 8 ) may turn the shaft  403  of one or both speed converters. In a further alternative embodiment, a ZTR  800  may be replaced with a hydraulic system consisting of two sets of hydraulic pumps consistent with hydraulic principles well known in the art to form a hydraulic ZTR. 
     A Reciprocating Pump Driven by a Speed Converter 
     Referring now to  FIG. 9 , there is shown a reciprocating pump  900  driven by an IVMC speed converter  400  per  FIG. 4  having worm control  402 , shaft  403  (see  FIG. 4  for similar elements not labeled in  FIG. 9 ) and piston components labeled in the  900  series of reference numerals. Note that the cam portion (right side) comprising cam shaft  101  and associated elements drives the reciprocating pump portion  901 - 906  under control of worm  402  of a transgear assembly. In the reciprocating pump  900 , the IVMC speed converter  400  operates two pistons comprising reciprocating piston drivers  901  and  904  (or more pistons/cams in alterative embodiments) with piston arms  902 ,  905  and pistons  903 ,  906  shown. For example, first piston driver  901  operates piston arm  902  for actuating piston  903 . The reciprocating pump driven by the cam controlled speed converter  400  is shown contained in a surrounding housing (not labeled). 
     Pitch Controlled Speed Converter 
     Referring to  FIGS. 10(A) and 10(B) , there is shown a variation of spur gear transgear clutch  240  with clutch components of  FIG. 2(C)  driven by a blade assembly of variable pitch shown in front view or  FIG. 10(A)  and side view or  FIG. 10(B) . A feedback control box  1010  is introduced to control pitch of the rotor blades in, for example, an application where the pitch controlled speed converter is utilized, for example, with a variable wind source of variable wind speed and a constant output speed or output angular velocity when the generation of electricity is desired. In particular, same output direction, same speed spur gear transgear clutch  240  comprises shaft  101 , left sun gear  102 , left carrier  108  from  FIGS. 1(A) ,  1 (B) and  1 (C), output gear  244  and output gear sleeve  245  from  FIG. 2(C)  and a number of components labeled  1001 - 1012 . Platform  1012  may be located, for example, on a river bed for capturing river flow or on a land mass or on an ocean platform to capture renewable energy flow or current velocity. Preferably, the rotor is pointed and controlled to point into a direction of renewable energy, wind or water, flow. Gearbox  1011  sits on platform  1012  and houses components and may be rotated to face the direction of renewable energy flow. Worm  1009  operates worm gear  1008  as discussed above. In front view,  FIG. 10(A) , a rotor assembly comprises rotor blades of variable pitch mounted to a plurality, for example, four of bevel gear shafts attached to associated bevel gears. For example, in a four blade assembly, bevel gear  1002  may be a top bevel gear and bevel gear  1004  may be a bottom bevel gear with left and right bevel gears not identified but shown. In side view,  FIG. 10(B) , bevel gear  1001  couples to bevel gears of the rotor blade assembly shown in front view  FIG. 10(A)  and is attached to or integral with the shaft  101 . Right bevel gear  1006  is shown on the right side of the blade assembly and is attached to or integral with output gear sleeve  245  and output gear  244  shown in black. Rotor blade  1005  is an example of one of a plurality of for example, four rotor blades whose pitch may be varied from facing into the wind or water flow so as to not turn at all in the face of renewable energy flow or to a maximum pitch where the rotor may turn at a maximum angular velocity in one direction, for example, clock-wise, Bevel gears  1001  and  1007  may be housed in housing  1007 . 
     Control box  1010  senses the revolutions per minute of shaft  101  turned by the rotor blade assembly and controls worm  1009 . Worm  1009  in turn may operate to control the pitch of the blade in high/low renewable energy flow velocity situations to turn the blade assembly so as to force blade  1005  to allow wind or water to flow to attempt to minimize turning the blade (for example, in extremely high wind situations) or to turn at maximum velocity thus controlling output rotational velocity to a relatively constant speed with varying renewable energy flow conditions. 
     Water (River) Turbines 
     Referring now to  FIGS. 11(A) , (B) and (C) and  12 (A), (B) and (C), there are shown alternative designs of, for example, a river turbine that may be mounted on a platform plate  1112 . Platform plate  1112  may be elevated above river bottom by a platform (not shown) and towards the center of the river, depending on the circumstances and the river or stream or ocean environment, to receive maximum water flow. Water (river) turbines as envisioned are desirably placed at a maximum flow location of a river or stream or in a position proximate to an ocean shore where the placement is between high and low tides and for maximum water renewable energy flow. River traffic and recreational use as well as recreational use of an ocean shore line may be considered when placing the present embodiments. Water (river) turbine embodiment  1100  of  FIGS. 11(A) , (B) and (C) is shown in  FIG. 11(A)  as sectional view A-A, top view in  FIG. 11(B)  and alternate input control hatch embodiment  FIG. 11(C) . The water (river) turbine of  FIG. 12  is shown similarly. 
     Referring to  FIG. 11(A) , there is seen platform  1112  on which is provided turbine  1100  for receiving renewable energy water flow from flow direction  1101 . Ribs  1111  also help protect the turbine from debris. Turbine  1100  comprises waterwheel brackets  1105 ,  1106  and flow control bracket  1110 . On flow control bracket  1110  is shown hatch  1109  comprising a portion of a circle which may be permitted to revolve in an associated circular slot from a wholly closed or raised position to receive less water flow to a position where hatch  1109  is wholly enclosed in the circular slot of flow control bracket  1110  and so wholly open to receive maximum water flow. The hatch assembly may mostly resemble a can with part of the hatch (circular pipe section) cut out or removed (per  FIG. 11(A) ). Hatch brackets  1107 ,  1108  preferably comprise round discs. Waterwheel rotor blade assembly  1104  is attached to or integral with rotor drum  1103  and rotates on waterwheel shaft  1102  when water flows to push the blades at a rotational velocity depending on water flow rates and operation of the hatch. The hatch opening and closing may be controlled by water flow sensors to provide constant speed output. A waterwheel drum  1103  couples the multiple blades  1104  (for example, eight blades are shown) to the shaft  1102 . 
     Referring now to  FIG. 11(B) , there is seen in top view a number of protector ribs  1111 . These may serve at least two functions. They may protect the inner assembly from floating/travelling large and heavy debris moved by the river or water flow  1101  such as branches or trunks of trees toward the unit and so cause the debris to flow past the turbine  1100 . Also, the ribs  1100  may be contoured inward so as to accelerate water flow toward a narrower passage through the turbine. Sealed gearbox  1113  encases all gears, control box and servo motor required of the turbine  1100 . Waterwheel brackets  1105 ,  1106  are shown in  FIG. 11(B)  with hatch brackets  1107  and  1108  inside. The hatch brackets also serve as protectors from debris. Control box  1121  may sense generator output, voltage and rotational velocity in revolutions per minute and send a signal to servo motor  1116  to open or close the hatch  1109  so as to achieve, for example, constant output speed. In this manner, the speed of output shaft  1102  may be controlled with variable input to achieve a desired rotational velocity output. Servo motor  1116  gear (not numbered) meshes worm  1115  and a further worm  1114  and is controlled by control box  1121  and control cable  1122  connects these. Worm gear  1114  is attached to hatch bracket  1108  and worm  1115  is meshed to worm gear  1116 . Constant speed generator  1119  is connected to control box  1121  to increase or decrease ratio increase gear  1118 . The output of the water (river) turbine is generator output cable  1120  shown as a three phase power alternating power cable. In an alternative embodiment and referring to  FIG. 11(C) , a spring-loaded hatch with lips or ribs  1123  on the flow-in direction  1101  side is shown. Water flowing toward lip or rib  1123  tends to cause the hatch to rise and cover the waterwheel assembly depending on the flow rate. Spring  1124  impedes the covering of the waterwheel assembly. Such a spring-loaded hatch assembly may render unnecessary a flow sensor and actuator motor, the spring loading automatically compensating for water flow rate as increased water flow pushes the lips or ribs  1123  of the spring-loaded hatch. 
     Referring now to  FIGS. 12(A) , (B) and (C), an alternative embodiment of a river turbine  1200  is shown where  FIGS. 12(A) , (B), (C) are substantially identical to  FIGS. 11(A) , (B) and (C). The differences lie in the gear box  1113  and relate to the further addition of input compensation. Per  FIG. 12(B) , center block  1201  is similarly shown with waterwheel shaft  1102  at its center. The block  1201  is attached to or integral with waterwheel shaft  1102 . Control gear  1203  is meshed to worm gear  1204 . Bottom output gear  1207  is attached to a bottom sun gear (not numbered). Increase gear  1208  is in the gear train from gear  1207  to ratio increase gear  1118 . Increase gear  1209  is attached to gear  1208 . This system may have two speed controls: a flow control and an input compensation control. Servo motor  1206  is provided for input compensation with worm  1205  in addition to servo motor  1116  and worm  1115 . The control box may then send two signals through cables  1122  and  1211  to provide the flow and input compensation controls, for example, for the hatch movement. 
     Variable Torque Generator 
     A variable torque generator useful in all embodiments for controlling torque from a maximum to a minimum is shown in  FIGS. 13(A) , (B) and (C). For steady flowing streams, without much flow rate variation, a constant speed output can be easily produced by compensating the input. As shown in  FIGS. 13(A) , (B) or (C), a constant speed, variable torque generator  1300 , comprises rotor shaft  1301  on which may be displaced a moveable rotor  1303  to positions of minimum overlap with stator  1302  ( FIG. 13(A) ) to medium overlap  1304  ( FIG. 13(B) ) and maximum overlap  1305  ( FIG. 13(C) ). Moveable rotor  1303 ,  1304 ,  1305  may be connected to a variable transformer or other device or turbine discussed above. Note that in an alternative embodiment a stator may be moveable with respect to the rotor if needed to achieve minimum, medium and maximum torque. These variable torque generators may be added to an input compensating IVMC with a speed converter, for example, to output electric power to a grid. 
     Cam Controlled Pump/Compressor 
     When a rotary pump or compressor (rotary pump shown) is attached to a cam controlled speed converter (note that  FIGS. 4(A)  and (B) is reversed in  FIG. 14 ), for example, speed converter  400 , it becomes an infinitely variable, cam controlled rotary pump or compressor  1400  as seen in  FIG. 14 . Shown in  FIG. 14  is a cam controlled speed converter assembly  400  with its output  1403  connected to a rotary pump (or compressor). This is one exemplary application of a cam controlled speed converter  400  to form a cam controlled pump/compressor  1400  that is not unlike the reciprocating pump/compressor shown in  FIG. 9  in efficiency, both using IVMC. 
     Cam Controlled Reciprocating Pump/Compressor 
     To achieve a smaller pump or compressor than that depicted in  FIG. 14 , the drivers and output tears can be replaced by pistons to make a reciprocating pump or compressor  1500  as shown in  FIG. 15 , The reciprocating pump  1503  is similar in many respects to reciprocating pump  900  of  FIG. 9  but in reverse configuration and no worm control. (The external rotary pump of cam controlled compressor  1400  is eliminated in  FIG. 15  as is the worm control  402  of  FIG. 9 ). The input shaft  1501  and control sleeve  1502  arc connected to an internal reciprocating pump  1503  via unlabeled cam shaft. This concept does not require one-way clutch bearings, ratchets or Sprags or other one way rotational means known in the art and may save cam controlled compressor unit costs to manufacture and operate. 
     Pitch Controlled Pump/Compressor 
       FIG. 16  is a pitch controlled compressor  1600  has no hydraulic motor and direction control. Pitch control assembly  1613  comprises gear  1610  meshed to gear  1612  integral with or attached to shaft  1601 . Gear  1610  is meshed to gear  2010  of a sleeve having a gear  1609 . As shown in  FIG. 16 , a constant speed motor input  1601  can produce variable flow output by controlling the pitch of the blade of pitch control assembly  1613  in a pitch controlled compressor  1600 . The pitch controlled pump/compressor  1600  comprises the basic building block of pitch controlled IVMC  1700  of  FIG. 17  of U.S. patent application Ser. No. 13/425,501 of the same inventor filed Mar. 21, 2012. The input of pitch controlled compressor  1600  is denoted  1601  and the compressor output  1614 . Similar reference numerals denote similar elements, for example, per  1711  of the previously mentioned  FIG. 17  is equivalent to gear  1611  where the first two digits represent the figure number. 
       FIG. 17  provides an overview of an input compensated infinitely variable motion control for a pump or compressor utilizing the basic spur gear assembly of  FIG. 1  (in reverse) for driving a compressor or a rotary pump  1710 , the assembly shown in cross-sectional front view. Compensating motor  1709  compensates for the input  1701  via worm gear  1708 . Operationally, the inoput torque may be kl=larger than the compensating force. The compensating motor  1709  may be a variable speed motor and so relieve the input instead of driving against the input. When the input  1701  torque on input sleeve  1701  of the spur gear transgear is fairly big and the output load does not vary much, this input compensated system  1700  can be applied to advantage. As shown in  FIG. 17 , a rotary pump  1710  (or compressor) may be added to an input compensating IVMC 2200 ( FIG. 22 ) of U.S. patent application Ser. No. 13/425,501 of the same inventor filed Mar. 21, 2012. Compensating motor  1709  compensates for input  1701  as described above. in this drawing, the elements are numbered similarly as above where the first two digits indicate the drawing number and the last two are the element, e.g. right sun gear  1705 , planetary gears  1703 ,  1704  and so on. 
     While various aspects of the present invention have been described above, it should be understood that they have been presented by way of example and not limitation. It will be apparent to persons skilled in the relevant art(s) that various changes in form and detail can be made therein without departing from the spirit and scope of the present invention. Thus, the present invention should not be limited by any of the above described exemplary aspects, but should be defined only in accordance with the following claims and their equivalents. 
     In addition, it should be understood that the figures in the attachments, which highlight the structure, methodology, functionality and advantages of the present invention, are presented for example purposes only. The present invention is sufficiently flexible and configurable, such that it may be implemented in ways other than that shown in the accompanying figures. 
     Further, the purpose of the foregoing Abstract is to enable the U.S. Patent and Trademark Office and the public generally and especially the scientists, engineers and practitioners in the relevant art(s) who are not familiar with patent or legal terms or phraseology, to determine quickly from a cursory inspection the nature and essence of this technical disclosure. The Abstract is not intended to be limiting as to the scope of the present invention in any way.