Blaine Staver: Transmission, USP #6800045 & article

![](0logo.gif)  
**[rexresearch.com](../index.htm)**

---

**Blaine STAVER** **Transmission**

---

***Williamsport Sun-Gazette* ( August 11,
2007 )**


**An Area Inventor Gets a Patent,**
  
**but not every invention needs one**

**By ALISSA EATON**   
aeaton@sungazette.com

COGAN STATION  American Inventor, a popular ABC
television show, aired its second season finale this week, but
area residents may not know that there are inventors right here
in Williamsport and the surrounding areas.

Blaine Staver, of Cogan Station may be on to something with his
invention, the automatic gear ratio reduction system, a new type
of highly efficient transmission.

Staver is working with the Williamsport-Lycoming Keystone
Innovation Zone to get his invention into the hands of people
who can help him.

Staver worked on his own to secure a patent for the invention,
which acts as a highly efficient transmission by supplying the
perfect amount of power needed in any situation.

It can go as fast or as slow as you as want it to, and it does
it with the least amount of energy that is needed, Staver
explained.

Staver said gear systems in cars today work with hydraulics and
his new invention does not need them.

Currently, he only has one demonstration model, and he showed
the Sun-Gazette the gear system had enough strength to pull the
weight of a car, only using a cordless drill as a power source.

Staver said he is marketing to the lawn tractor and mower
industry, hopefully providing them with a more efficient
transmission for those machines.

Staver said he hopes it changes the way people see
transmissions and wants to see his invention in cars and trucks
someday.

If this invention acted as a transmission in cars, it would
greatly increase fuel economy and decrease the nations
dependency on foreign oil, Staver said.

But Staver, isnt the only inventor to hail from the area.

Katie Bell of the Keystone Innovation Zone, who works with both
Staver and many other clients, said she is currently working
with over 60 inventors and start-up companies and said she
encourages them to all evaluate whether a patent is worthwhile
or feasible regarding their specific concepts.

Depending on the concept it may or may not benefit an
individual to pursue a patent, Bell said.

For example, Coca-Colas recipe is a trade secret  something
they keep secret within their company. They did not patent the
recipe because in 20 years the patent would have expired and
anyone could have reproduced Coke exactly, Bell added.

Bell said it can take up to two years or even longer to get a
patent. This depends on if claims are rejected and need to be
re-written or adjusted, she said.

Patents are received through the United States Patent and
Trademark Office.

---

![](staver.jpg)  
Photo by Craig McKibben Jr./Sun-Gazette

**Blaine Staver of Cogan Station tows a car Wednesday using
the transmission he designed and fit into a small chassis
during a demonstration**

---

**US Patent # 6,800,045**   
**Automatic Gear Ratio Reduction System**   
**( October 5, 2004 )**   
**Blaine STAVER**

**Abstract**

A system for automatically lowering an effective gear ratio
between an input gear, driven by a rotary power source, and an
output gear that drives a driven load. A variance gear is
interposed coaxially between the input gear and output gear. The
input gear normally drives the output gear through an upper
motion transfer gear, an upper variance gear, a lower variance
gear, and a lower motion transfer gear. When resistance to
rotation is presented to the output gear the upper and lower
variance gear begin planetary motion around the lower motion
transfer gear, rotate the lower motion transfer gear and output
gear more slowly, and thereby lower the effective gear ratio
between the input and output gears.

Current U.S. Class:  475/104   
Current International Class:  F16H 3/72 (20060101); F16H
3/44 (20060101); F16H 047/08 ()   
Field of Search:  475/104,102   
References Cited:   
U.S. Patent Documents: 1859347 - May 1932 - Michael // 
2330375 - September 1943 - Orner //  4627312 - December
1986 - Fujieda, et al. //  4868753 - September 1989 - Mori
//  5150297 - September 1992 - Daubenmier, et al. // 
5645506 - July 1997 - Mleczko

**Description**

**BACKGROUND OF THE INVENTION**

The invention relates to an automatic gear ratio reduction
system. In particular, the invention relates to a system that
automatically adjusts a gear ratio between a drive source and a
driven load sufficiently to maintain rotation of the driven
load, in accordance with the resistance to rotation presented by
the load.

A rotary power source, such as a motor, is generally not
coupled directly with a load. Typically the motor has an
operating rotational speed and torque. It is rare that this
rotational speed is directly matched with the requirements of
the load. For a given power, rotational speed and torque are
inversely proportional. Thus, Accordingly, various transmission
systems are employed to either reduce or increase the ratio
between speed and torque to achieve a compromise, which best
suits the load.

Many applications, however, will vary the torque/rotational
speed requirements under different operating conditions. For
example, an automobile initially begins motion with low
rotational speed of the tires, but supplies high torque to the
tires that allows the automobile to accelerate to a higher speed
of travel. When the automobile reaches its cruising speed, the
tires must be rotated at a higher speed, while less torque is
necessary to accelerate the automobile. Accordingly, automobile
transmissions have several gear ratios. The lowest gears are
suitable for lower travel speeds and for a greater ability to
accelerate, while the highest gears are suitable for cruising at
higher speeds while keeping the engine within its designed range
of rotational speed. Naturally, less torque and thereby less
ability to accelerate is available when using the highest gears.
Generally, automobiles have three to six fixed gear ratios
between the engine and the `final drive`. Picking one of the
gear ratios requires `shifting gears`, either manually, or
through an automatic mechanism.

In addition, common power tools undergo a similar battle for
torque and rotational speed. A drill, for example, will commonly
rotate at a high speed while it travels with little resistance
through a workpiece. At times, however, the drill bit will
encounter considerable resistance, which has a tendency to stall
the drill. A stalled electric drill motor will draw considerable
current, may overheat, and will shorten the useful life of the
motor. Ordinarily, a drill stall causes the worker to halt
working to prevent damaging the drill.

Various transmissions have been proposed which seek to allow
the gear ratio to be altered continuously. So-called
`continuously variable transmissions` supposedly allow infinite
gear ratios to be achieved within a range. Such systems however,
generally rely on belts, selective friction, and slippage, which
thereby greatly decrease their efficiency and useful life.

While these units may be suitable for the particular purpose
employed, or for general use, they would not be as suitable for
the purposes of the present invention as disclosed hereafter.

**SUMMARY OF THE INVENTION**

It is an object of the invention to provide a gear ratio
adjustment system that automatically adjusts the gearing ratio
to achieve the necessary torque to maintain rotational motion at
the load. Accordingly, the system reacts in response to
increased resistance at the load to lower the gear ratio,
increase the torque at the load, and thereby maintain motion.

It is another object of the invention to provide a gear ratio
adjustment system which substantially operates using gears in
mesh, and does not require `shifting of gears` or otherwise
altering the arrangement of gears in mesh to achieve different
gear ratios. Accordingly, the system effectively lowers the gear
ratio while all gears remain in mesh.

It is a further object of the invention to provide a gear ratio
adjustment system, which quickly adapts to changes in resistance
upon the output gear, without stopping motion. Accordingly, the
configuration of gears according to the present invention
according to a primary embodiment employs an input/output gear
set that allows the gear ratio to be lowered by the automatic
commencement of planetary motion of the lower variance
determining gear around the lower motion transfer gear mounted
radially off center on a variance gear coaxial with the input
and output gears, to compensate for the increased resistance at
the output gear, wherein the lower variance gear is in part
rotating the output gear through the lower motion transfer gear
and in part orbiting around the lower motion transfer gear.

It is yet a further object of the invention to provide a gear
ratio adjustment system, which allows continuous gear ratios to
be achieved. Accordingly, the amount of resistance presented to
the output gear will vary the degree to which the lower variance
determining gear directly turns the lower motion transfer gear
and the degree to which the lower variance determining gear
revolves around the lower motion transfer gear. The partial
direct rotation of the lower variance determining gear and
revolution around the lower motion transfer gear by the lower
variance determining gear will depend on the amount of
resistance and will thereby achieve a `comfortable` gear ratio
by which rotation may continue.

It is a still further object of the invention to help ensure
that the lower gear ratio associated with planetary motion only
occurs when the resistance to rotation renders it necessary to
lower the gear ratio. Accordingly, pressure can be applied to
the variance gear of the input/output gear set to help ensure to
increase the resistance necessary to begin lowering the
effective gear ratio between the input and output gear set.

It is yet another object of the invention to provide a feedback
loop which automatically increases the range of gear ratios
achievable by the system. Accordingly, a variance control gear
set is provided which is a substantial clone of the input/output
gear set, except wherein the input gear is known as a speed gear
which is driven by the output gear of the input/output gear set;
and the output gear is a control gear which drives the variance
gear of the input/output gear set.

To the accomplishment of the above and related objects the
invention may be embodied in the form illustrated in the
accompanying drawings. Attention is called to the fact, however,
that the drawings are illustrative only. Variations are
contemplated as being part of the invention, limited only by the
scope of the claims.

**BRIEF DESCRIPTION OF THE DRAWINGS**

In the drawings, like elements are depicted by like reference
numerals. The drawings are briefly described as follows.

**FIG. 1** is a diagrammatic perspective view, illustrating
a first embodiment of the invention, namely having an
input/output gear set, a drive source and a driven load, and an
auxiliary variance control gear.

![](6800-1.jpg)

**FIG. 2** is an exploded perspective view of the
input/output gear set, having an input gear set, an output gear
set, and a middle motion transfer assembly therebetween.

![](6800-2.jpg)

**FIG. 3** is an exploded view of the input/output gear set,
illustrating the interconnection of the middle motion transfer
assembly with the upper motion transfer gear and lower motion
transfer gear.

![](6800-3.jpg)

**FIG. 4** is a diagrammatic perspective view, illustrating
thee invention in use, during typical operation such that the
lower motion transfer gear is rotated by the lower variance
determining gear, and wherein the variance gear is substantially
stationary.

![](6800-4.jpg)

**FIG. 5** is a diagrammatic perspective view, similar to
FIG. 4, except wherein the driven load has encountered
significant resistance to rotation and wherein the middle motion
transfer assembly has begun planetary motion such that the lower
variance determining gear is revolving around the lower motion
transfer gear to maintain motion of the output gear while the
middle motion transfer assembly--including the variance
gear--begins rotating in the same direction as the input and
output gears.

![](6800-5.jpg)

**FIG. 6** is a diagrammatic perspective view of a further
embodiment of the invention, wherein a variance control gear set
is provided, which is substantially identical to the
input/output gear set and provides a feedback loop to adjust the
sensitivity of the output gear to initiating planetary motion
when resistance is encountered at the output gear.

![](6800-6.jpg)

**DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS**

FIGS. 1-5 illustrate a first embodiment of the automatic gear
reduction system according to the present invention 10. In
particular, an input/output gear set 20 is illustrated. The
input/output gear set 20 can function as a stand-alone
embodiment of the invention, or can be used as a building block
in a further embodiment of the invention, described below,
wherein further feedback is implemented to more efficiently
control the automatic gear reduction of the input/output gear
set 20--which will be described in further detail below.

For the purpose of the following discussion, "shaft drives" or
"shaft driven" means that two components are mounted on the same
axis and linked by a shaft therebetween so that both components
rotate together. Further "mesh drives" or "mesh driven" means
that two components are tangentially engaged at their respective
circumferences either frictionally or with gear teeth so that
they rotate together.

Referring to FIG. 1, the input/output gear set 20 has a central
axis 20C, and has an input gear 22 and output gear 24 coaxially
mounted on the central axis 20C but not connected thereon. The
central axis 20C contains a series of shafts and bearings, such
that various gears and spacers coaxially mounted on the central
axis do not rotate together. With the interconnection and lack
of connection of the gears described in detail hereinbelow,
specific details regarding the shafts, bearings, and spacers for
mounting of such gears is well within the knowledge of those
skilled in the art--yet is to a large extent illustrated in the
drawing figures. Accordingly, full details regarding the same
are beyond the scope of this discussion.

The input gear 22 is driven by a rotary drive power source 12,
which includes a motor 13, and the output gear 24 drives a load
14, which by example herein includes a drill bit 15. In typical
fixed gearing arrangements, the torque supplied to the output
gear 24, and thus the load 14 is fixed. As will be illustrated
herein, however, additional torque will be supplied, by lowering
the effective gear ratio between the input gear 22 and output
gear 24 when resistance to the output gear 24 from the load 14
would otherwise stall the output gear 24, and thus the input
gear 22 and rotary drive power source 12. A variance gear 26
forms a part of the input/output gear set 20, and allows control
over conditions under which the input/output gear set 20 lower
the gear ratio between the input 22 and output gear 24. The
variance gear 26 can be controlled by a variance gear control
16, which is diagrammatically illustrated in FIG. 1, and will be
the subject of further discussion and further examples
subsequent to the complete discussion of the input/output gear
set 20.

FIG. 2 illustrates ganging of various gears of the input/output
gear set 20. In particular, an input gear assembly 23 includes
the input gear 22 and upper motion transfer gear 28, which are
both coaxial with the central axis 20C and mechanically ganged
such that the upper motion transfer gear 28 is shaft driven by
the input gear 22. An output gear assembly 25 includes the
output gear 24 and a lower motion transfer gear 30, which are
both coaxial with the central axis 20C and mechanically ganged
such that the output gear 24 is shaft driven by the lower motion
transfer gear. Accordingly, the input gear assembly 23 and
output gear assembly 25 are coaxial on the central axis 20C, but
are not mechanically ganged, and thus do not rotate together.

A middle motion transfer assembly 27 includes the variance gear
26, a upper variance determining gear 32, a lower determining
variance gear 34, and a xx plate 35. The variance gear 26 and
the xx plate 35 are coaxially mounted on the central axis 20C
with the input gear assembly 23 and output gear assembly 25. The
upper variance determining gear 32 and lower variance
determining gear 34 are located on a variance determining gear
axis 36 that is not coaxial with the input gear assembly 23 and
output gear assembly 25 but is located radially outward on the
variance gear 26 on a variance determining gear shaft 33. In
particular, the variance determining gear shaft 33 extends
between the variance gear 26 and the xx plate, parallel to the
central axis 20C. The upper variance gear 32 and lower variance
gear 34 are coaxial with each other and are ganged for rotation
together on the variance determining gear axis 36 with the
variance determining gear shaft 33. The variance gear 26 and the
xx plate 35 are further connected by a post 39 extending
parallel to the central axis 20C to stabilize the middle motion
transfer assembly 27 into a single `piece` that can selectively
rotate together around the central axis 20C although during
typical operation the variance gear 26 remains stationary.

Now, referring to FIG. 3, the upper motion transfer gear 28 is
in mesh with the upper variance determining gear 32, and the
lower variance determining gear 34 is in mesh with the lower
motion transfer gear 30. However, the upper motion transfer gear
28 and lower motion transfer gear 30 are not mechanically linked
such that they do directly drive each other or rotate together.
Accordingly, during typical operation, the input gear 22 shaft
drives the upper motion transfer gear 28, the upper motion
transfer gear 28 mesh drives the upper variance determining gear
32; the upper variance determining gear 32 shaft drives the
lower variance determining gear 34; the lower variance gear 34
mesh drives the lower motion transfer gear; and the lower motion
transfer gear 30 shaft drives the output gear 24.

FIG. 4 illustrates the assembled device 10 during typical
operation. Note that an additional transfer plate 35A, omitted
for clarity in FIG. 2 and FIG. 3, is mounted substantially
parallel with transfer plate 35, immediately beneath the
variance gear 26 to stabilize the middle motion transport
assembly 27, and similarly rotates therewith.

During such typical operation, the input gear 22 and output
gear 24 rotate in the same direction, the drive source 12
rotates the input gear 22, the lower variance determining gear
34 rotates the lower motion transfer gear 30 to rotate the
output gear 24 and thereby rotate driven load 14. Accordingly,
the output gear 24 is rotated at a relatively high rate of speed
and there is a relatively high gear ratio between the input gear
22 and output gear 24. During such typical operation, the
variance gear 26 and plate 35 is substantially stationary as
motion of the lower variance determining gear 34 is
substantially transferred to the lower motion transfer gear 30
through direct meshed rotation.

Referring to FIG. 5, however, when resistance is placed on the
output gear 24 by the driven load 14, tension occurs at the
interface of the lower motion transfer gear 30 and lower
variance determining gear 34, which causes the lower variance
determining gear 34 to revolve or orbit around the lower motion
transfer gear 39, causing the variance gear 26 to rotate, such
that the variance gear axis 36 rotates around the central axis
20C (in the same direction as the input gear 22 and output gear
24). At this point, motion of the lower variance determining
gear will be partially translated to direct rotation of the
lower motion transfer gear, albeit with greater leverage due to
rotation around the central axis 20C; and partially translated
to orbital motion around the lower motion transfer gear 30.
Accordingly, the input gear will continue rotating, and the
drive source 13 will not be unduly taxed. In addition, to the
extent possible, the lower motion transfer gear 30 and thus the
output gear 24 will still rotate--although at a lower speed but
with greater torque being delivered to the driven load 14. An
equilibrium point (speed) will be reached by which the lower
variance determining gear 34 rotates the output gear 24 to the
extent possible, and revolves around the lower motion transfer
gear 30 as well. Accordingly, a input gear 22 to output gear 24
overall gear ratio will be achieved at which motion of the
output gear 24 will continue.

Accordingly, as the resistance is increased, the motion of the
variance gear axis 36 around the central axis 20C will increase.
This is because the upper and lower variance gears 32, 34 are on
a common axis and must rotate together, yet the upper motion
transfer gear 28 (see FIG. 3) are also in mesh but are at
different but complementary gear ratios so that the lower
variance gear 34 will begin revolving around the lower motion
transfer gear 30 to maintain rotation.

To facilitate the actual reduction in gear ratio, rather than a
simple planetary cavitation of the lower variance determining
gear 34 around the output gear, the ratio between the upper
motion transfer gear 28 and upper variance determining gear 32
is preferably equal to the ratio between the lower variance
determining gear 34 and the lower motion transfer gear 30. See
FIG. 3, where the motion transfer gears 28, 30 and the variance
determining gears 32 and 34 are clearly "reversed"--i.e. large
upper motion transfer gear 28 and lower variance determining
gear 34, and small lower motion transfer gear 30 and upper
variance determining gear 32. This relationship helps the
input/output gear set 20 "find" an equilibrium overall gear
ratio to help maximize the maintenance of speed at the output
gear 24 when encountering resistance thereat.

Naturally when the middle motion transfer assembly 27 is in
planetary motion, the lower motion transfer gear 30 will rotate
more slowly--subtracting the planetary motion of the lower
variance gear therearound. The input gear 22 will continue to
rotate at the same speed--however by virtue of the planetary
motion, lower speed and greater torque will be imparted to the
lower motion transfer gear 30, and thus the output gear 24.
Accordingly, a lower gear ratio between the input gear 22 and
output gear 24 will be automatically achieved upon the output
gear 24 encountering sufficient resistance.

The magnitude of the "sufficient resistance" necessary to begin
such planetary motion can be further controlled with the
variance gear, by giving it a tendency against planetary motion.
This can be accomplished by restraining the variance gear 26
with the auxiliary variance gear control assembly 16 shown in
FIGS. 1-5, or by actually rotating the variance gear 26 in the
opposite direction as the input gear 22 and output gear 24.
Restraint of the variance gear 26 can be accomplished with
magnetism, friction, or any other means well known to those
skilled in the art. In addition, a feedback loop can be
established to help maximize the efficiency of the device 10 by
maximizing the speed achievable at a given resistance. Such can
be achieved by externally rotating the variance gear can be
accomplished with a variance control gear set 50, illustrated in
FIG. 6.

In particular, the variance control gear set 50 which is
analogous in structure to the input/output gear set 20, such
that the variance control gear set 50 has a substantially
identical structure as the input/output gear set 20 except that
its components are spaced along its central axis 50C in a
slightly different manner, and the variance control gear set 50
herein is illustrated upside down for convenience of appropriate
interconnection with the input/output gear set 20. Regarding
nomenclature, the variance control gear set 50 has a speed gear
62 which is analogous to the input gear 22 of the input/output
gear set 20, and it has a variance control gear 64 which is
analogous to the output gear 24 of the input/output gear set 20.

The variance control gear set 50 effectively provides a
feedback loop between the output gear 24 and variance gear 26 of
the input/output gear set 20. Accordingly, the speed gear 62 of
the variance control gear set 50 is connected to be rotate with
the output gear 24 of the input/output gear set 20; and the
variance control gear 64 connected to rotate the variance gear
26 of the input/output gear set. The result is that the output
gear 24 rotates the speed gear 62. The speed gear 62 causes the
variance control gear 64 to following the same principles by
which both the input gear 22 and output gear 24 of the
input/output gear set rotate together. The variance control gear
64 attempts to rotate the variance gear 26 of the input/output
gear set 20 in the opposite direction as its input gear 22 and
output gear 24. Accordingly, the middle motion transfer assembly
27 is given a `reverse incentive` to rotate and lower the gear
ratio. Thus, rotational speed is actually increased at the
output gear 24, the gear ratio between the input gear 22 and
output gear 24 is increased, and the sensitivity of the middle
motion transfer assembly toward beginning planetary motion in
the face of "some resistance" at the output gear is lowered.
Accordingly, the effective range of gear ratios achievable
between the input and output gear 24 increased, such that more
than just "a little resistance" at the output gear is required
before planetary motion is initiated to lower the effective gear
ratio between the input and output gears 22, 24.

Note that the system may grow modularly by the additional of
further variance control gear sets 50. In addition, auxiliary
variance control gears 70 may be employed to engage the
analogous variance gear 26A of the variance control gear set 50
to further tune the "sensitivity" toward changing gear ratios
between the input gear 22 and output gear 24 of the input/output
gear set 20.

In conclusion, herein is provided a system for automatically
achieving an idealized gear ratio, by lowering the overall gear
ratio between a rotary drive source and an output load to
maintain motion at the output load when resistance is
encountered thereat. The invention is illustrated by example in
the foregoing description and in the accompanying drawings.
Numerous variations, however, are possible while adhering to the
invention concept. Such variations are contemplated as being a
part of the present invention.

---