U.S. patent application number 09/435530 was filed with the patent office on 2001-06-14 for transducer for converting linear energy to rotational energy.
Invention is credited to SIMONDS, EDWARD L..
Application Number | 20010003257 09/435530 |
Document ID | / |
Family ID | 26983558 |
Filed Date | 2001-06-14 |
United States Patent
Application |
20010003257 |
Kind Code |
A1 |
SIMONDS, EDWARD L. |
June 14, 2001 |
TRANSDUCER FOR CONVERTING LINEAR ENERGY TO ROTATIONAL ENERGY
Abstract
A transducer includes a linear input power source (12) connected
to a connecting rod (24) in turn connected to output drive shafts
(30 & 36) through one-way clutches (28 & 40), with the
output drive shafts being interconnected through gears (32 &
40) such that when one shaft is powered, the other is coasting. The
power source includes multiple stern powered cylinders (16 &
94). Inlet and outlet valves (44) for each cylinder chamber are
controlled by an actuator (56) which instantaneously snaps the
valves between open and closed positions. The power cylinders (16
& 94) may be operated individually, in parallel or in series
and as required, a valve passageway through the piston (18) may be
operated to equalize pressure. A pair of O-rings (121) on the
piston (18) engage the cylinder wall only when the adjacent chamber
is pressurized, thereby reducing drag in operation of the
piston.
Inventors: |
SIMONDS, EDWARD L.; (ADEL,
IA) |
Correspondence
Address: |
BRUCE W MCKEE
ZARLEY MCKEE THOMTE VOORHEES & SEASE
801 GRAND AVENUE
SUITE 3200
DES MOINES
IA
50309
|
Family ID: |
26983558 |
Appl. No.: |
09/435530 |
Filed: |
November 8, 1999 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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09435530 |
Nov 8, 1999 |
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08817131 |
Apr 7, 1997 |
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08817131 |
Apr 7, 1997 |
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PCT/US95/13486 |
Oct 10, 1995 |
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09435530 |
Nov 8, 1999 |
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08322695 |
Oct 13, 1994 |
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5461863 |
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Current U.S.
Class: |
91/218 |
Current CPC
Class: |
F01B 17/00 20130101;
F01B 9/08 20130101 |
Class at
Publication: |
91/218 |
International
Class: |
F04B 001/26 |
Claims
What is claimed is:
1. A transducer for converting linear energy to rotational energy
comprising, a linear input power source connected to a connecting
rod with gear teeth, the rod in turn being continuously connected
to a first output drive shaft having a first gear and a second
output drive shaft having a second gear, the first and second gears
being in operative engagement with one another, one-way clutches
operatively interconnecting said first and second output drive
shafts to said connecting rod, and said power source reciprocating
said connecting rod back and forth in opposite linear directions
causing said first and second output drive shafts to be
continuously rotated in a single direction respectively.
2. The transducer of claim 1 wherein said one-way clutches include
gear teeth with said connecting rod gear teeth continuously
engaging the gear teeth of said one-way clutches.
3. The transducer of claim 2 wherein said connecting rod has first
and second opposing sides and said connecting rod gear teeth are on
one of said sides in engagement with the gear teeth of said one-way
clutches which are positioned in side by side relationship on the
same side of said connecting rod.
4. The transducer of claim 3 and a guide roller is positioned on
the opposite side of said connecting rod from said one-way clutches
for maintaining said connecting rod teeth in engagement with the
teeth of said one-way clutches.
5. The transducer of claim 2 wherein said connecting rod has first
and second opposing sides and said connecting rod gear teeth are on
said first and second opposing sides in engagement with the gear
teeth of said one-way clutches which are positioned on opposite
sides of said connecting rod.
6. The transducer of claim 1 wherein said first and second gears
are in operative engagement through an idler gear which allows both
of said first and second gears to rotate in the same direction.
7. The transducer of claim 1 wherein said first and second output
drive shafts are continuously rotated in opposite directions.
8. The transducer of claim 1 wherein said linear input power source
includes a piston in a cylinder.
9. The transducer of claim 8 wherein said cylinder includes
pressure chambers on opposite sides of said piston.
10. The transducer of claim 9 wherein said power source includes a
flowable medium source and a control system for alternatively
directing medium to each of said pressure chambers to cause said
connecting rod to be reciprocated.
11. The transducer of claim 10 wherein said control system includes
valve means for directing flowable medium to said pressure chambers
and said piston is centered between said pressure chambers when
said connecting rod is centered in its range of movement during
each cycle of operation.
12. The structure of claim 11 wherein said valve means is connected
to an actuator means which is operatively connected to said piston,
said pressure chambers being adapted to be alternately pressurized,
said valve means including inlet and outlet ports in each of said
chambers, said one chamber is adapted to be pressurized when the
inlet port in said one chamber is open while the input port in the
other chamber is closed, and the outlet port in said one chamber is
closed and the outlet port in said other chamber is open, said
other chamber is adapted to be pressurized when the inlet port in
said first chamber is closed and the inlet port in said other
chamber is open, and the outlet port in said first chamber is open
and the outlet port in said other chamber is closed.
13. The transducer of claim 12 wherein said actuator means includes
a first link operatively connected to said connecting rod and a
second link connected to said valve means for opening and closing
said valve means as said connecting rod moves back and forth in
opposite directions.
14. The transducer of claim 13 wherein said actuator means includes
a spring means interconnecting said first and second links such
that energy is increased in said spring means as said first link
moves in said opposite directions and is released when resistance
to movement of said valve means is overcome thereby causing said
valve means to be snapped between open and closed positions.
15. The transducer of claim 14 wherein said actuator means includes
a rocker block adapted to pivot about a pivot axis, and said first
link is connected to said rocker block on one side of said pivot
axis and said second link is connected to said rocker block on the
opposite side of said pivot axis such that said rocker block is
pivotably snapped back and forth between opposite positions as said
valve means are snapped between open and closed positions.
16. The transducer of claim 11 wherein said flowable medium is
steam.
17. The transducer of claim 12 wherein said flowable medium is
steam and a condenser is connected to said outlet ports in each of
said chambers.
18. The transducer of claim 12 wherein said flowable medium is
connected through said valve means to said inlet ports of said
chambers.
19. The transducer of claim 18 further comprising multiple input
power sources having a piston in a cylinder with pressure chambers
on opposite sides equivalent to said first power source, and said
flowable medium is connected through said valve means to inlet
ports in said chambers where all power sources operate in unison to
power said output drive shafts.
20. The transducer of claim 8 wherein a second input power source
is provided having a piston in a cylinder with pressure chambers on
opposite sides, said second input power source being functionally
equivalent to said first power source and having its inlet ports
alternately connected to said outlet ports of said first power
source whereby feedback flowable medium is utilized to supplement
power for rotating the output drive shafts.
21. The transducer of claim 20 wherein said second power source is
smaller in its capacity to process said flowable medium.
22. The transducer of claim 12 wherein said piston has passageway
means through it for connecting said opposite chambers, and a
piston valve for opening and closing said passageway and to
equalize pressure in each chamber.
23. The transducer of claim 22 wherein a fixed sensor is provided
adjacent to a signaling means on said connecting rod such that the
position of said piston can be determined as it moves through each
half cycle of operation.
24. The transducer of claim 23 wherein said fixed sensor and
signaling means include interactive magnets which generate a signal
transmitted to a computer operatively connected to said piston
valve for opening and closing said piston valve.
25. The transducer of claim 12 wherein said piston includes
peripherally positioned circumferential seal elements movably
received in annular slots formed in the outer periphery adjacent
opposite ends of said piston, and said piston having opposite end
faces having openings connecting said annular slots to the adjacent
chamber whereby pressure in said chamber yieldably forces said seal
element outwardly into engagement with the cylinder and the absence
of pressure in said chamber allows the adjacent seal to retract
into its annular slot thereby reducing drag on said cylinder.
26. A transducer for converting linear energy to rotational energy
comprising, a linear input power source connected to a connecting
rod having gear teeth, the rod in turn being continuously connected
to a first crank connected to a first output drive shaft having a
first gear, a second crank continuously connected to said
connecting rod and to a second output drive shaft having a second
gear in operative engagement with said first gear on said first
output drive shaft, one-way clutches interconnecting said first and
second output drive shafts to said first and second cranks, and
said power source reciprocating said connecting rod back and forth
in linear opposite directions causing said first and second output
drive shafts to be continuously rotated in a single direction,
respectively.
27. A transducer for converting linear energy to rotational energy
comprising, a linear input power source connected to a connecting
rod in turn connected to a first output drive shaft having a first
gear, a second output drive shaft having a second gear in meshing
engagement with said first gear on said first output drive shaft,
one-way clutches operatively interconnecting said first and second
output drive shafts to said connecting rod, and said power source
reciprocating said connecting rod back and forth in opposite linear
directions causing said first and second output drive shafts to be
continuously rotated in opposite directions.
Description
BACKGROUND OF THE INVENTION
[0001] The internal combustion engine, while improved over years of
use, still falls short of being the ultimate power source for
vehicles and other related uses. The engine is both inefficient and
environmentally unfriendly due to its production of contaminants.
It is believed that an alternative type power source has been found
that has many advantages over the internal combustion engine
SUMMARY OF THE INVENTION
[0002] Any flowable medium may be used but steam is preferred for
powering the transducer of this invention when converting linear
energy into rotational power. A piston in a cylinder has chambers
on opposite sides alternately receiving steam pressure through
operation of a valve control system. A connecting rod connected to
the piston reciprocates a pair of arms through approximately a 70
degree arc. Each of the arms are connected through one-way clutches
such as a Sprag clutch, to shafts carrying intermeshing gears
whereby movement of the piston in one direction causes one gear to
be powered while turning both gears and movement in the opposite
direction causes the other gear to be powered while turning both
gears. The one-way clutches permit this alternate powering of one
output shaft while the other is rotated as a slave. With this
arrangement, there is no wasted motion on the part of the powered
piston as it produces rotational power moving in both linear
directions.
[0003] Multiple power cylinders may be connected to multiple pivot
arms, in turn connected to common output drive shafts.
[0004] Through the operation of linkages operatively connected
between the piston connecting rod and the control valves in inlet
and outlet ports in each of the oppositely disposed cylinder
chambers, the transducer will be operated to produce continuous and
instantaneous power as required. The linkages include spring means
which accumulate pressure to overcome valve switching resistance
which provides a snap type switching of pressure from one chamber
to another.
[0005] Pressure in the chambers is monitored and if it is desired
to equalize the pressure in both chambers, it can be done so
through operation of a solenoid valve in a passageway in the piston
connecting both chambers. Magnetic sensing is provided to determine
the position of the piston and this information coupled with the
pressure information are fed into a computer which allows for the
desired control and operation.
[0006] A pair of O-rings are provided in annular slots in the outer
piston wall for engagement with the cylinder wall. The slots
communicate with the adjacent pressure chambers through a series of
holes around the circumference of the piston end walls. Medium
pressure in a chamber extends through the end wall holes and causes
Teflon O-rings in the slots to expand outwardly into sealing
engagement with the cylinder wall. The absence of pressure in a
chamber allows the O-ring to contract into the annular slot
reducing drag. Multiple power cylinders may be operated
individually, in parallel or in series. When operating in series,
the outlet port of the chamber of one cylinder is fed to the inlet
port in the chamber of another cylinder in the sense of
regenerative feedback.
[0007] It is possible, of course, to use an entirely different
power source in combination with the one-way clutch driven output
rotational power shafts.
[0008] In an alternate embodiment, an input power source includes a
connecting rod having teeth engaging teeth on one-way clutches on
first and second output drive shafts, which in turn have output
first and second gears respectively engaging each other through an
idler gear. The one-way clutches and their respective output shafts
and gears may be on the same side of the connecting rod, or in an
alternate embodiment, on opposite sides of the connecting rod.
[0009] A Sprag one-way clutch is preferred but it is understood
that other one-way clutches can be used, such as air or hydraulic
clutches, magnetic clutches, band clutches, screw clutches, or
ratchet clutches.
DESCRIPTION OF THE DRAWINGS
[0010] FIG. 1 is a top plan view of a transducer having two steam
driven power cylinders connected through connecting rods to a pair
of shafts which in turn are connected to output drive shafts
through one-way clutches.
[0011] FIG. 2 is a side elevational view thereof taken along line
2-2 in FIG. 1.
[0012] FIG. 3 is a cross sectional view taken along line 3-3
showing the steam line circuitry for powering the power cylinders
arranged in parallel.
[0013] FIG. 4 is a view similar to FIG. 3, but showing the steam
lines for operating only the larger of the two cylinders.
[0014] FIG. 5 is a view similar to FIG. 3, but showing the
cylinders connected in series to provide feedback regenerative use
of the flowable steam medium.
[0015] FIG. 6 is an enlarged fragmentary view as indicated along
line 6-6 in FIG. 2, illustrating the control system including
actuator for operating the inlet and outlet valves for each chamber
of each cylinder.
[0016] FIG. 7 is a cross sectional view taken along line 7-7 in
FIG. 6.
[0017] FIG. 8 is a cross sectional view taken along line 8-8 in
FIG. 1 showing the one-way clutch in its driving condition.
[0018] FIG. 9 is a cross sectional view similar to FIG. 8 but
showing the one-way clutch in free wheeling condition.
[0019] FIG. 10 is a cross sectional view taken along line 10-10 in
FIG. 3 with an enlarged fragmentary side elevational view of the
connecting rod and piston illustrating the valve in the passage way
through the piston for selectively equalizing pressure in opposite
chambers.
[0020] FIG. 11 is an enlarged cross sectional view of the O-ring
taken along line 11-11 in FIG. 10 with the sealing elements on the
periphery of the piston engaging the cylinder sidewall on the
pressurized side of the piston and spaced therefrom on the non
pressurized side.
[0021] FIG. 12 is view similar to FIG. 11 but showing the O-rings
on the piston sidewall when pressure in both piston chambers is
reduced and equalized.
[0022] FIG. 13 is a cross sectional view of an alternate embodiment
wherein the connecting rod engages one-way clutches positioned on
the same side of the connecting rod.
[0023] FIG. 14 is a cross sectional view taken along line 14-14 in
FIG. 13.
[0024] FIG. 15 is a cross sectional view of a further alternative
embodiment wherein the connecting rod engages one-way clutches on
opposite sides of the connecting rod.
[0025] FIG. 16 is a cross sectional view taken along line 16-16 in
FIG. 15.
DESCRIPTION OF THE PREFERRED EMBODIMENT
[0026] The transducer of this invention is referred to in FIG. 1
generally by the reference numeral 10. It includes a linear power
input section 12 which drives a rotational power output section
14.
[0027] The input section 12 of the invention 10 includes a power
cylinder 16 having a piston 18 with oppositely disposed chambers 20
and 22. A connecting rod 24 extends from the cylinder 16 and is
connected to a first crank arm 26 which is connected through a
one-way clutch 28 to an output shaft 30 having a gear 32 engaging a
gear 34 on a second output drive shaft 36, also connected to a
second crank arm 38 through a one-way clutch 40. The first crank
arm 26 and second crank arm 38 are interconnected by a link 41.
[0028] Steam from a boiler 42 is provided to the chambers 20 and 22
alternately as seen in FIG. 3. A valve assembly 44 opens and closes
in each chamber an inlet port 46 and an outlet port 48. The valve
assembly 44 includes a shaft 50 connected to a horizontally
extending arm 52 connected to a link 54, in turn connected to a
pivotal actuator 56 which pivots about an axis 58 between the solid
and dash line positions of FIG. 6. An oppositely disposed link 60
extends to the opposite end of the cylinder 16 where it is
connected to an arm 62 pivotal about an axis 64 which is the
longitudinal axis of an upstanding shaft 66, which operates a valve
assembly like the valve assembly 44 in FIG. 3.
[0029] A link 68 extends through a block 70 pivotally connected to
the actuator 56 and includes springs 72 mounted on opposite sides
thereof held in place by washers 74 and nuts 76. The opposite end
of the link 68 is connected to the first crank arm 26. A variable
pressure resistance roller 78 rolls along a convex surface 80 on
the top end of the actuator 56 between upstanding stop shoulders 82
having notches 84 to yieldably retain the roller 78 against each of
the stops 82 as the actuator 56 pivots back and forth between the
dash and solid line positions of FIG. 6. The resistance roller is
carried on a shaft 86 pressed downwardly by a spring 88. Adjustable
tension is provided by an adjustment screw 90 mounted in a support
member 92.
[0030] A second input power cylinder 94 larger in size than the
cylinder 16, otherwise having the same components, is connected
through a connecting rod 95 to the output section 14 in the same
fashion that the connecting rod 24 connects cylinder 16 to the
output section. Like components are identified by like reference
numerals. Both cylinders 16 and 94 are anchored to a common support
shaft 96.
[0031] The operation of the transducer to this point involves steam
from the boiler 42 being introduced into the chamber 22 of the
cylinder 16 and presses on the right side of piston 18 to push the
connecting rod 24 to the left, in turn pivoting the first crank arm
26 to the left. The one-way clutch 28 is connected to the output
shaft 30, where movement of the crank arm 26 to the left does not
cause any rotation of the shaft 30 since the one-way clutch 28, as
seen in FIG. 9, is disengaged from the shaft 30. The link 40,
however, connected to the second crank arm 38, is pivoted to the
left. Its one-way clutch 40, as seen in FIG. 8, causes the shaft 36
to rotate in a clockwise direction as indicated by the arrow 98.
The gear 34 on the shaft 36 engages the gear 32 on the shaft 30
and, thus, causes it to rotate in the counter clockwise direction,
as indicated by the arrow 100. This, in turn, causes an auxiliary
output gear 103 to be rotated in a clockwise direction. When the
piston 18 moves then to the right, the one-way clutch 40 will allow
the second crank arm 38 to coast while the first crank arm 26
performs an output drive function by rotating the output shaft 30
in a counter clockwise direction and, thus, it is seen that as the
piston 18 moves in either direction, it is producing rotational
output power.
[0032] It is desirable to have an instantaneous switching of the
valves in the valve assembly 44 in a positive fashion such that
pressure is applied exclusively to one chamber or the other of the
chambers 20 and 22. This is accomplished by the use of the springs
72, which adsorb energy applied to them through the link 68. Once
that pressure overcomes the resistance of the roller 78, engaging
the convex surface 80 of the actuator 56, the actuator will be
snapped to the opposite position, in turn moving the links 54 and
60 which operate the valve assemblies 44 at opposite ends of the
cylinder 16.
[0033] At times, it may be desirable to equalize the pressure on
either side of the piston and this has been provided for as seen in
FIG. 10, wherein the piston 18A in cylinder 94 includes a solenoid
102 which operates a valve 104 in a passageway 106 that
communicates with the chambers on either side of the piston. A set
screw 108 presses against a spring 110 which resists the action of
the solenoid 102. Magnets 112 and 114 are mounted on the connecting
rod 24 and their presence is sensed by the sensor 116 which sends a
signal to a computer not shown, which in turns sends a signal to
the solenoid 102 through the wires 118. The computer will also
receive information from a pressure sensor 120 as seen in FIG. 3
and this information combined with the piston position location
information provided by the magnetic sensor 116 will determine if
the solenoid valve 102 need be operated to neutralize pressure on
either side of the piston 18A.
[0034] It is desirable to minimize the frictional drag between the
piston 18A and the cylinder sidewall 94 as seen in FIGS. 11 and 12.
A pair of neoprene O-rings 121 are mounted in peripheral annular
slots 122 which communicate with the adjacent chamber through a
series of spaced apart openings 124. As seen in FIG. 11, pressure
in a chamber on the right hand side will force the O-ring 121
outwardly into engagement with the interface of the cylinder wall
94. However, the left hand side not having any pressure allows the
O-ring seal to remain spaced from the cylinder wall 94, thus,
avoiding any unnecessary frictional drag. In FIG. 12, it is seen
that both chambers on opposite sides of the piston 18A are under
equal reduced pressure, thus, allowing the O-rings to remain spaced
from the cylinder sidewall 94.
[0035] Three different modes of operation are shown in FIGS. 3, 4
and 5, with FIG. 3 showing both input power cylinders 16 and 18
being under power and functioning in parallel with each other to
provide rotational output power to the shafts 30 and 36. In FIG. 4,
the large cylinder 94 only is being operated and in FIG. 5, the
outlet of the smaller cylinder 16 is fed to the inlet of the larger
cylinder 94 and then back to the condenser 126. This mode involves
feedback and regeneration of the steam otherwise returned to the
condenser as shown in FIGS. 3 and 4.
[0036] It is seen that there are numerous advantages in the use of
a transducer of this invention as a rotational power source for
vehicles or other equipment requiring rotational power. Consumption
of energy through energy consuming friction has been minimized. The
cranks 26 and 38 operate at maximum efficiency by pivoting only
through 70 degrees of a possible 360 degree arc of rotation. The
transducer of this invention can operate at a very low rpm and
still produce the desired output power. The output shafts 30 and 36
provide constant power due to the instant on and off of control
valves of valve assembly 44. The transducer is able to start in any
position due to the valving system employed. The size of the
transducer compared to a conventional engine can be reduced
dramatically due to the absence of a crank shaft. The transducer,
unlike the conventional internal combustion engine, produces no
contaminates such as oil and fuel exhaust and involves no noise
pollution. Thus, it is more environmentally sound. The transducer
will operate at a lower rpm and eliminates centrifugal forces; and
the system's life is greatly extended. A very important distinction
from the conventional engine is that when the transducer is not
producing energy, it does not need to be idled as in the case of an
automobile engine.
[0037] The linearly reciprocated connecting rod 24A as seen in the
embodiments of FIGS. 13-14 and FIGS. 15-16, is connected to the
one-way clutches through gear teeth on the connecting rod, engaging
gear teeth on the one-way clutches. Specifically, in the embodiment
of FIGS. 13 and 14, the first and second output drive shafts 30A
and 36A respectively are positioned on the same side of the
connecting rod 24A. Gears 130 and 132 are mounted on the output
drive shafts 30A and 36A respectively, and engage teeth 134 on the
bottom side of the connecting rod 24A. The gears 130 and 132 each
include one-way clutches as previously described regarding clutches
40 and 28 in FIGS. 8 and 9 respectively. The output drive shafts
30A and 36A include first and second output gears 32A and 34A
respectively. Guide rollers 138 and 140 engage the rail edge top
side of the connecting rod 24A to hold it in a stable position in
engagement with the gears 130 and 132.
[0038] A further alternative embodiment is shown in FIGS. 15 and
16, wherein the connecting rod 24B includes teeth 134 on the bottom
side and teeth 144 on the top side. The second output drive shaft
36B is positioned above the first output drive shaft 30B on
opposite sides of the connecting rod 24B. The gear 132 having a
one-way clutch engages the teeth 144 on the connecting rod 24B
while the other gear, 130, engages the teeth 134 on the bottom side
of the connecting rod 24B. The output gears, including first gear
32B and second gear 36B, engage each other through an idling gear
136, thereby allowing the first and second output shafts 30B and
36B to rotate in a common direction.
* * * * *