Infinitely variable pumps and compressors

Infinitely variable motion control (IVMC) provides motion control without any requirement for changing gears or use of a clutch. A spur gear transgear, defined as a system having an input, an output and a control, a variable pitch cam having an eccentric inner and outer cam assembly and a driver may be used to form a speed converter. The speed converter is used in various forms to provide an infinitely variable transmission, a differential, embodiments of wind and river turbines and pumps/compressors. In one embodiment, the speed converter drives first and second directional control assemblies to provide a vehicle with zero turn radius. Various embodiments of an infinitely variable pump or compressor are described.

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'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 '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 ofFIG. 1, a spur gear transgear is utilized to form clutches perFIG. 2, differential steering perFIG. 3and 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 inFIG. 7U.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 cam702that comprise a portion of a shaft701, for example, an input shaft or an output Shaft. The inner eccentric cam may be positioned and free to move within an eccentric outer cam703. 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 inFIG. 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. 8of 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 housing800of such a ratchet or one-way clutch bearing (or Sprag) has at least one notch805,806for receiving, for example, a needle roller803,804and 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 race801may move) because the needle roller803,804is loose or free-wheeling and located at one end of its associated notch. On the other hand, when the internal race801rotates in the other rotational direction with respect to the outer housing802or vice versa, the needle roller rolls into an engaged position between the race and the notch such that the housing802is controlled to rotate in this other rotational direction with the inner race801.

A further control technology is accomplished when the cam controlled assembly technology described above is used as a driver (FIG. 9of 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 Sprag912,913is embedded inside an output gear910,911and 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. 17or18of 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. 22of 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.

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 toFIGS. 1(A),1(B) and1(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.

A spur gear assembly100, for example, shown inFIG. 1(A), left view,FIG. 1(B), front view, andFIG. 1(C), right view, is an example of a transgear assembly having an input (input shaft101is driven from the left), an output (sleeve106provides 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 viewFIG. 1(A)and front viewFIG. 1(B), an input gear comprising a left sun gear102is attached to and may be integral with input shaft101(seen in the center of corresponding front viewFIG. 1(B)). Planetary gears103and103B are meshed to left sun gear102, and planetary gears104and104B are meshed to right sun gear105. The planetary gears103and104, and103B and104B are meshed respectively. Right sun gear105may be attached to or integral with right sun gear sleeve106which surrounds shaft101and provides the output. Other components of transgear assembly100include left carrier108and right carrier109, each of which may be a disc or gear. Components110,110B,111and111B comprise pins. The assembly100thus comprises a spur gear transgear with input, output and control. Assembly100is very similar in mechanical diagram to the spur gear assembly ofFIG. 3of 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 numerals103B,104B,110B and111B), refer to an extra set of components, such as carrier portions and gears for enhanced, more balanced performance. For example, gear103B may, however, provide greater torque capacity and dynamically balance the spur gear transgear system100.

Spur gear transgears may basically comprise two sun gears102,105, meshed with each other through planetary gears103,104. Spur gears may he either regular spur gears or helical gears.

Referring toFIG. 1(B), front view, left sun gear102is attached to or integral with input shaft101. Carrier brackets108and109are attached together with pins110and111. Planetary gears103and104may rotate freely around the pins110,111and mesh with sun gear102(input) and sun gear105(output) respectively. Thus, the output105having sleeve106is controlled by the planetary and sun gears forming a basic spur gear transgear assembly100.

Assume that input rotational energy is connected to input shaft101and so shaft101rotates clock-wise and the carriers108,109and pins110,111are fixed. Left sun gear102is the input gear and right sun gear105is the output gear connected to an output sleeve106. The input sun gear102may rotate clock-wise (CW) with the input shaft101. Planetary gear103then rotates counter clock-wise (CCW), and planetary gear104rotates clock-wise (CW), and right sun gear105of the output rotates CCW along with output sleeve106. Since the sun gears102and105are the same size in diameter as seen inFIG. 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 transgear100with the same size sun gears may be called a “basic transgear.”

Spur Gear Transgear Clutches

Embodiments of Spur Gear Transgear Clutches are shown inFIGS. 2(A),2(B) and2(C). Similar reference numerals are used inFIGS. 2(A),2(B) and2(C) to denote similar elements where the first digit indicates the figure number where the element first appears. For example, shaft101, left sun gear102and so on having the same names appear as similar components with similar function in theFIGS. 2(A),2(B) and2(C) as in theFIGS. 1(A),1(B) and1(C). Elements beginning with the numeral2denote elements first introduced inFIGS. 2(A),2(B) and2(C) such as center block201and brake disc202(attached to left sun gear102through 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 shaft101may be CW and the output sleeve106CCW 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 shaft101may be CW and the output sleeve245CW, and the output rotational velocity or speed being the same at input and output.

Referring toFIG. 2(A), embodiment clutch200. Center block201may be either attached to or is integral with shaft101. Brake Disc202is attached to left sun gear102through an associated sleeve proximate to input shaft101. Band brake203of brake disc202(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 block201and the output is right sun gear105. The control is left sun gear102. Since the planetary gears are rotating around the stationary left sun gear102, and the sun gears are the same in size, the right sun gear105rotates two times faster than the input shaft101. 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 gear103rotates CW, planetary gear104CCW and right sun gear105CW. So the output direction is the same as the input direction in this embodiment.

As shown in eitherFIG. 2(B), clutch embodiment220, orFIG. 2(C), clutch embodiment240are shown with no brake disc202provided. On the other hand, braking is similar. Brake Disc221is attached to a sleeve which in turn couples with pins and carriers, carrier108, in particular. Pressure applied via band brake222brakes the speed of carriers108and109. The input is left sun gear102, the carrier is the control and the right sun gear105is the output. So left sun gear102may turn CW,103CCW,104CW and105CCW. 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 toFIG. 1.

FIG. 2(C), clutch embodiment240, starts with the basic embodiment ofFIG. 2(B), embodiment220, and adds additional components for providing the same direction at output as input. Gear241is attached to or may be integral with right sun gear sleeve106. Two direction change gears are provided, direction change gear #1242and direction change gear #2243. Direction change gear #1 is meshed to gear241and direction change gear #2 is meshed to an output gear244of output gear sleeve245and to direction change gear #1242.

Spur Gear Transgear Differential Steering Assembly

Referring now toFIG. 3, there is shown a mechanical diagram for providing spur gear transgear differential steering. Shaft101is shown not attached to or integral with any members; (shaft101is a support member). Left sun gear102is attached to sleeve303. As before, planetary gear103is shown with left sun gear102. Carriers108and109are similarly shown. Right sun gear105may be attached to or integral with an output sleeve307.

New toFIG. 3are input shaft301displaced from shaft101. Shaft101may just be a support shaft but can be attached to or be integral with one of the sleeves303or307and so reduce the number of parts in an alternative embodiment. Input shaft301is coupled to input gear302associated with left carrier108and right carrier109. Sleeve303is attached to or integral with left sun gear102. For braking, brake disc304is attached to sleeve303. Pressure applied to band brake305is felt at sleeve303which is attached to left driving wheel306and so slows a left wheel. Similarly, on the right. sleeve307is attached to or integral with right sun gear105. For braking, brake disc308is attached to sleeve307. Pressure applied to band brake309is felt at sleeve307which is attached to right driving wheel310and 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 toFIGS. 4(A) and 4(B), an Infinitely Variable Motion Control (IVMC) speed converter comprises an input shaft403and an output shaft424with a shaft101serving as a cam shaft. The IVMC speed converter further comprises a variable pitch cam (inner cam420, outer cam422) surrounding cam shaft101and is shown in Section A-A ofFIG. 4(B)embedded in front viewFIG. 4(A). A variable pitch cam is extensively shown and described in connection with the description ofFIGS. 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 cam419and outer cam421form a similar variable pitch cam surrounding cam shaft101. At the bottom of Section A-A.FIG. 4(B), is a Sprag gear assembly surrounding output shaft424having race section423. Race section423of output shaft424couples with Sprags429,430,431and432and having output gears425,426,427,428designated together but seen separately. Together section A-A forms a driver416which is duplicated inFIG. 4(A)as driver415. Pins413,414are designated together and associated with slots409,410,411and412discussed further below.

To the left ofFIG. 4(A)is seen a spur gear transgear assembly100comprising cam shaft101, left sun gear102integral or attached to a sleeve surrounding cam shaft101, planetary gear103integral with or attached to cam shaft101, carriers108,109(see FIGS.1(A) through1(C)), pins110,111(not marked) and so on. With respect to newly shown components, inFIG. 4, worm402turns worm gear401which is attached to or is integral with the sleeve and left sun gear102and meshed to carrier gears108and109of spur gear assembly100(FIG. 1). A drive gear405is attached to input shaft403and meshed to slotted gears406,407and408, where slotted gear406has one slot at the top, slotted gear407has two slots, one at the top and one at the bottom, and slotted gear407has one slot at the bottom. Slots409,410,411and412are designated together where slot410and slot411are at the middle of slotted gear407. The operation of slotted gears is described by reference toFIGS. 11) and 11U.S. application Ser. No. 13/435,501 filed Mar. 21, 2012, incorporated by reference in its entirety.

IVMC with Two Speed Ranges

Referring toFIG. 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 graphFIG. 5(B). The IVMC speed converter400ofFIGS. 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. IVMC500operable at city and highway speeds is modified fromFIGS. 4(A)and (B) by further including brake disc501and band brake502for input shaft403. Moreover, additional gears are provided including gear503surrounding cam shaft101, and output gear504surrounding output shaft424where output gear504further has an associated Sprag505. Note that in an alternative embodiment, gear503may not be needed if carrier gears108and109are meshed to output gear504directly. Operationally, when the band brake502is engaged, output gear504may rotate in the same direction but faster than output gears425,426,427and428.

Infinitely Variable Transmission or IVT (Speed Converter and Direction Control)

Referring toFIG. 6, there is shown a combination of the IVMC speed converter400ofFIG. 4(A)with the addition of a direction control. A discussion ofFIGS. 4(A) and 4(B)will not be repeated and the emphasis will be placed on direction control600wherein input shaft403and worm402are shown. Output shaft424extends from speed converter400to direction control600and comprises right sun gear601(similar to a right sun gear of spur gear transgear100ofFIG. 1(B)). Left sun gear602is likewise similar to a left sun gear of spur gear transgear100. Brake disc603is operated by band brake604. Carrier gears605and606are likewise similar to the carrier gears of transgear100, left side. Right sun gear607is similar to the right side of spur gear transgear100(FIGS. 1(A), (B) and (C)). Left sun gear608is attached to or integral with carrier gear606which is similar to the right side of spur gear transgear100. Further braking is provided by right carrier and brake disc609operated by band brake610. Output shaft612is now able to operate in forward, neutral and reverse where output gear611is meshed to carrier gears605and606. Assume that the shaft424is rotating one revolution CW. If band brake604is applied (braked), carrier brackets605and606will rotate one half rotation CW. If band brake610is applied (braked) the carrier will rotate one revolution CCW. When the band brakes604and610are not applied (not braked), the carrier will be free or neutral.

Infinitely Variable Transmission (IVT) with Differential

Referring toFIG. 7, there is shown a combination of the IVMC speed convener400ofFIGS. 4(A) and 4(B)with the addition of direction control and a differential. Neither speed converter elements designated in the400series nor direction control elements designated in the600series will be described again in detail. Attention will be focused on new differential elements designated in the700series. Direction control and differential700are driven by shaft424from speed convener400. The right differential shaft713is coupled to shaft424by directional control comprising a band brake604and611. Carrier gears605,606are shown as is left sun gear608which may be attached to or integral with output gear706.

The differential portion of direction control and differential700comprises elements701-713. Referring to the spur gear transgear ofFIGS. 1(A), (B) and (C), carrier gear701(Left side of spur gear transgear100) and carrier gear702are similar as are right sun gear703and left sun gear704. Left differential output sleeve705surrounds right differential output shaft713. Brake disc711is operated by band brake712on differential output shaft713. Left sun gear output gear706is similar to the right side of spur gear transgear100. Left carrier gear707is likewise similar to the right side of spur gear transgear100. Right carrier708is similar to the right of transgear100and left sun gear709is also similar to the right of spur gear transgear100. Right sun gear710is similar to the right sun gear of spur gear transgear100. The differential can be open or locked. This embodiment comprises a compact transaxle. There are two outputs from the direction control: carrier gears605and606, and gear706that is attached to left sun gear608and carrier gear606. Carrier gears605and606are meshed to carrier gears701and702. The gear ratios are, for example, one to one. Gear706is attached to left sun gear608and is meshed to carrier gear707, and the ratio is, for example, one to two. If the direction control output is one revolution CW, carriers701and702will be rotating one revolution CCW, and carrier707will be rotating one half revolutions CCW. When band brake712is not engaged, the differential outputs are sleeve705to the left and shaft713to the right. The input to carrier707is not in effect. This state is now an open differential. When band brake712is engaged or right sun gear710is fixed, and not rotating, left sun gear709will be rotating one revolution CCW. Since left sun gear709and right sun gear703are attached to shaft713, left sleeve705does 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 toFIG. 8, there is shown an IVMC speed converter ofFIGS. 4(A) and 4(B)having an output shaft424which drives two direction control assemblies according toFIG. 6, one assembly600on the left of speed converter400and one on the right of speed converter400. With first and second direction control assemblies, one can achieve a zero turn radius (ZTR). In the embodiment ofFIG. 8, shaft803may be turned clock-wise (or CCW) at the same time as shaft806may 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 brakes801,802,804,805where brake bands801and804comprise left band brakes and802and805comprise right band brakes. Band brakes801and802operate oppositely on left output shaft803in concert with band brakes804and805operating oppositely on right output shaft806. In a ZTR left turn, shaft803turns oppositely from shaft806so that803moves a vehicle downward on the drawing sheet and shaft806moves 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 shafts803,806. Note that in an alternative embodiment, instead of one IVMC and two sets of direction controls, two sets of IVMC400and direction control600, 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 inFIG. 8) may turn the shaft403of one or both speed converters. In a further alternative embodiment, a ZTR800may 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 toFIG. 9, there is shown a reciprocating pump900driven by an IVMC speed converter400perFIG. 4having worm control402, shaft403(seeFIG. 4for similar elements not labeled inFIG. 9) and piston components labeled in the900series of reference numerals. Note that the cam portion (right side) comprising cam shaft101and associated elements drives the reciprocating pump portion901-906under control of worm402of a transgear assembly. In the reciprocating pump900, the IVMC speed converter400operates two pistons comprising reciprocating piston drivers901and904(or more pistons/cams in alterative embodiments) with piston arms902,905and pistons903,906shown. For example, first piston driver901operates piston arm902for actuating piston903. The reciprocating pump driven by the cam controlled speed converter400is shown contained in a surrounding housing (not labeled).

Pitch Controlled Speed Converter

Referring toFIGS. 10(A) and 10(B), there is shown a variation of spur gear transgear clutch240with clutch components ofFIG. 2(C)driven by a blade assembly of variable pitch shown in front view orFIG. 10(A)and side view orFIG. 10(B). A feedback control box1010is 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 clutch240comprises shaft101, left sun gear102, left carrier108fromFIGS. 1(A),1(B) and1(C), output gear244and output gear sleeve245fromFIG. 2(C)and a number of components labeled1001-1012. Platform1012may 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. Gearbox1011sits on platform1012and houses components and may be rotated to face the direction of renewable energy flow. Worm1009operates worm gear1008as 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 gear1002may be a top bevel gear and bevel gear1004may be a bottom bevel gear with left and right bevel gears not identified but shown. In side view,FIG. 10(B), bevel gear1001couples to bevel gears of the rotor blade assembly shown in front viewFIG. 10(A)and is attached to or integral with the shaft101. Right bevel gear1006is shown on the right side of the blade assembly and is attached to or integral with output gear sleeve245and output gear244shown in black. Rotor blade1005is 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 gears1001and1007may be housed in housing1007.

Control box1010senses the revolutions per minute of shaft101turned by the rotor blade assembly and controls worm1009. Worm1009in 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 blade1005to 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 toFIGS. 11(A), (B) and (C) and12(A), (B) and (C), there are shown alternative designs of, for example, a river turbine that may be mounted on a platform plate1112. Platform plate1112may 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 embodiment1100ofFIGS. 11(A), (B) and (C) is shown inFIG. 11(A)as sectional view A-A, top view inFIG. 11(B)and alternate input control hatch embodimentFIG. 11(C). The water (river) turbine ofFIG. 12is shown similarly.

Referring toFIG. 11(A), there is seen platform1112on which is provided turbine1100for receiving renewable energy water flow from flow direction1101. Ribs1111also help protect the turbine from debris. Turbine1100comprises waterwheel brackets1105,1106and flow control bracket1110. On flow control bracket1110is shown hatch1109comprising 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 hatch1109is wholly enclosed in the circular slot of flow control bracket1110and 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 (perFIG. 11(A)). Hatch brackets1107,1108preferably comprise round discs. Waterwheel rotor blade assembly1104is attached to or integral with rotor drum1103and rotates on waterwheel shaft1102when 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 drum1103couples the multiple blades1104(for example, eight blades are shown) to the shaft1102.

Referring now toFIG. 11(B), there is seen in top view a number of protector ribs1111. 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 flow1101such as branches or trunks of trees toward the unit and so cause the debris to flow past the turbine1100. Also, the ribs1100may be contoured inward so as to accelerate water flow toward a narrower passage through the turbine. Sealed gearbox1113encases all gears, control box and servo motor required of the turbine1100. Waterwheel brackets1105,1106are shown inFIG. 11(B)with hatch brackets1107and1108inside. The hatch brackets also serve as protectors from debris. Control box1121may sense generator output, voltage and rotational velocity in revolutions per minute and send a signal to servo motor1116to open or close the hatch1109so as to achieve, for example, constant output speed. In this manner, the speed of output shaft1102may be controlled with variable input to achieve a desired rotational velocity output. Servo motor1116gear (not numbered) meshes worm1115and a further worm1114and is controlled by control box1121and control cable1122connects these. Worm gear1114is attached to hatch bracket1108and worm1115is meshed to worm gear1116. Constant speed generator1119is connected to control box1121to increase or decrease ratio increase gear1118. The output of the water (river) turbine is generator output cable1120shown as a three phase power alternating power cable. In an alternative embodiment and referring toFIG. 11(C), a spring-loaded hatch with lips or ribs1123on the flow-in direction1101side is shown. Water flowing toward lip or rib1123tends to cause the hatch to rise and cover the waterwheel assembly depending on the flow rate. Spring1124impedes 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 ribs1123of the spring-loaded hatch.

Referring now toFIGS. 12(A), (B) and (C), an alternative embodiment of a river turbine1200is shown whereFIGS. 12(A), (B), (C) are substantially identical toFIGS. 11(A), (B) and (C). The differences lie in the gear box1113and relate to the further addition of input compensation. PerFIG. 12(B), center block1201is similarly shown with waterwheel shaft1102at its center. The block1201is attached to or integral with waterwheel shaft1102. Control gear1203is meshed to worm gear1204. Bottom output gear1207is attached to a bottom sun gear (not numbered). Increase gear1208is in the gear train from gear1207to ratio increase gear1118. Increase gear1209is attached to gear1208. This system may have two speed controls: a flow control and an input compensation control. Servo motor1206is provided for input compensation with worm1205in addition to servo motor1116and worm1115. The control box may then send two signals through cables1122and1211to 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 inFIGS. 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 inFIGS. 13(A), (B) or (C), a constant speed, variable torque generator1300, comprises rotor shaft1301on which may be displaced a moveable rotor1303to positions of minimum overlap with stator1302(FIG. 13(A)) to medium overlap1304(FIG. 13(B)) and maximum overlap1305(FIG. 13(C)). Moveable rotor1303,1304,1305may 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 thatFIGS. 4(A)and (B) is reversed inFIG. 14), for example, speed converter400, it becomes an infinitely variable, cam controlled rotary pump or compressor1400as seen inFIG. 14. Shown inFIG. 14is a cam controlled speed converter assembly400with its output1403connected to a rotary pump (or compressor). This is one exemplary application of a cam controlled speed converter400to form a cam controlled pump/compressor1400that is not unlike the reciprocating pump/compressor shown inFIG. 9in efficiency, both using IVMC.

Cam Controlled Reciprocating Pump/Compressor

To achieve a smaller pump or compressor than that depicted inFIG. 14, the drivers and output tears can be replaced by pistons to make a reciprocating pump or compressor1500as shown inFIG. 15, The reciprocating pump1503is similar in many respects to reciprocating pump900ofFIG. 9but in reverse configuration and no worm control. (The external rotary pump of cam controlled compressor1400is eliminated inFIG. 15as is the worm control402ofFIG. 9). The input shaft1501and control sleeve1502arc connected to an internal reciprocating pump1503via 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.

FIG. 16is a pitch controlled compressor1600has no hydraulic motor and direction control. Pitch control assembly1613comprises gear1610meshed to gear1612integral with or attached to shaft1601. Gear1610is meshed to gear2010of a sleeve having a gear1609. As shown inFIG. 16, a constant speed motor input1601can produce variable flow output by controlling the pitch of the blade of pitch control assembly1613in a pitch controlled compressor1600. The pitch controlled pump/compressor1600comprises the basic building block of pitch controlled IVMC1700ofFIG. 17of U.S. patent application Ser. No. 13/425,501 of the same inventor filed Mar. 21, 2012. The input of pitch controlled compressor1600is denoted1601and the compressor output1614. Similar reference numerals denote similar elements, for example, per1711of the previously mentionedFIG. 17is equivalent to gear1611where the first two digits represent the figure number.

FIG. 17provides an overview of an input compensated infinitely variable motion control for a pump or compressor utilizing the basic spur gear assembly ofFIG. 1(in reverse) for driving a compressor or a rotary pump1710, the assembly shown in cross-sectional front view. Compensating motor1709compensates for the input1701via worm gear1708. Operationally, the inoput torque may be kl=larger than the compensating force. The compensating motor1709may be a variable speed motor and so relieve the input instead of driving against the input. When the input1701torque on input sleeve1701of the spur gear transgear is fairly big and the output load does not vary much, this input compensated system1700can be applied to advantage. As shown inFIG. 17, a rotary pump1710(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 motor1709compensates for input1701as 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 gear1705, planetary gears1703,1704and 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.