U.S. patent number 3,839,863 [Application Number 05/325,271] was granted by the patent office on 1974-10-08 for fluid pressure power plant.
Invention is credited to Larry Vane W. Frazier.
United States Patent |
3,839,863 |
Frazier |
October 8, 1974 |
FLUID PRESSURE POWER PLANT
Abstract
An external combustion hydraulic power plant employing an
expanding gaseous medium and a non-expanding fluid medium in order
to create a body of fluid under pressure which may be used to
perform work. In one embodiment, steam is the expanding gaseous
medium and in another embodiment, hot gas is the medium. In both
embodiments, efficiency is enhanced because maximum heat
conservation is effected and the power plant operates only on
occasions of demand.
Inventors: |
Frazier; Larry Vane W.
(Ventura, CA) |
Family
ID: |
23267174 |
Appl.
No.: |
05/325,271 |
Filed: |
January 23, 1973 |
Current U.S.
Class: |
60/327; 60/325;
417/401 |
Current CPC
Class: |
F04B
9/1253 (20130101) |
Current International
Class: |
F04B
9/00 (20060101); F04B 9/125 (20060101); F15b
003/00 (); F04b 035/00 () |
Field of
Search: |
;60/325,327,419
;417/383,41X |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Cohen; Irwin C.
Assistant Examiner: Ostrager; Allen M.
Attorney, Agent or Firm: Sciascia; Richard S. St. Amand; J.
M. O'Reilly; David
Claims
I claim:
1. A fluid pressure power plant comprising:
means for generating heat energy;
at least one piston for converting the heat energy to high
hydraulic pressure;
said energy converting piston having an upper chamber for receiving
the heat energy and a lower chamber for receiving a hydraulic fluid
at low pressure;
means supplying low pressure hydraulic fluid to the lower chamber
of the energy converting piston;
means releasing the low pressure hydraulic fluid into the lower
chamber when the piston reaches the bottom of its stroke to force
the piston upward;
means for accumulating the high pressure hydraulic fluid output of
the energy converting piston;
means for utilizing the power from the high pressure hydraulic
fluid output of the energy converting piston;
means for controlling the flow of high pressure hydraulic fluid
from the accumulating means to the power utilizing means; and
means for returning the hydraulic fluid from the power utilizing
means to the low pressure hydraulic fluid supplying means.
2. The fluid pressure power plant of claim 1 wherein the means for
generating heat energy comprises:
a steam generator;
means supplying hydraulic fluid to said steam generator;
means for preheating the hydraulic fluid supplied to the steam
generator;
means for accumulating the steam generator under low pressure;
and
means for turning off the steam generator when the steam
accumulator reaches a predetermined limit.
3. The fluid pressure power plant of claim 2 wherein the energy
converting piston includes:
an intake valve for releasing steam into the upper chamber when the
piston is at the top of its stroke and on its downward stroke;
an exhaust valve for expending the steam from the upper chamber
when the piston is on its upward stroke;
hydraulic means for opening the intake valve and closing the
exhaust valve when the piston is at the top of its stroke and
closing the intake valve and opening the exhaust valve when the
piston is at the bottom of its stroke; and
means for controlling the flow of hydraulic fluid at high pressure
to the accumulating means when the piston is on its downward
stroke.
4. The fluid pressure power plant of claim 3 wherein the hydraulic
means for opening and closing the intake and exhaust valve
comprises a port connected to the lower chamber, said port
receiving the low pressure hydraulic fluid when the piston reaches
a predetermined position in its upward stroke so that the intake
valve is opened and the exhaust valve is closed;
the hydraulic fluid port to the intake and exhaust valves being
situated at a point in the lower chamber so that as the lower end
of the piston passes the port on its downward stroke, the hydraulic
pressure can gradually bleed off the valves until the intake valve
is closed and the exhaust valve is opened at the bottom of the
piston stroke.
5. The fluid pressure power plant of claim 4 wherein the means for
supplying hydraulic fluid at low pressure comprises:
a reservoir;
means for cooling the reservoir;
means for pumping the hydraulic fluid in the reservoir to a low
pressure accumulator; and
control means connecting the low pressure hydraulic fluid to the
steam generator and the lower chamber of the power conversion
piston.
6. The fluid pressure power plant of claim 5 wherein the means for
returning the hydraulic fluid to the low pressure supply
comprises:
means for feeding the hydraulic fluid back to the reservoir after
the high pressure has been dissipated in the power utilizing
means.
7. The fluid pressure power plant of claim 6 wherein the hydraulic
fluid is comprised of:
a lubricating fluid mixed with the hydraulic fluid capable of
passing through a vapor cycle; and
a centrifugal separator receiving the hydraulic fluid and lubricant
mixture from the low pressure accumulator and separating the
lubricant from the mixture prior to passing the hydraulic fluid to
the steam generator.
8. The fluid pressure power plant of claim 1 wherein the means for
converting heat energy to high hydraulic pressure comprises:
a group of at least four cylinders with each piston therein being
90.degree. out of phase with the preceding piston, said cylinders
comprising:
a heat input chamber;
an expansion chamber adjacent to the top of the piston containing a
heat expandable gas and separated from the heat chamber by a thin
metal membrane acting as a heat exchanger;
a cool gas chamber below the head of the piston including means for
cycling and recycling the heat expandable gas from the chamber
above the piston to the cool gas chamber below the piston of the
next adjacent piston; and
a low pressure hydraulic fluid chamber at the lower end of the
piston.
9. The fluid pressure power plant of claim 8 wherein the means for
cycling and recycling the heat expandable gas includes heat
regenerators for preheating the gas when it is flowing from the
cool gas chamber to the hot gas chamber above the piston.
10. The fluid pressure power plant of claim 9 including means for
cyclically providing low pressure hydraulic fluid to the power
conversion pistons, said means including a series of valves for
switching the flow of low pressure hydraulic fluid from one piston
to another as each successively reaches the bottom of its downward
stroke.
11. The fluid pressure power plant of claim 10 wherein the cool gas
chamber below the piston head is surrounded by a water cooling
jacket.
12. The fluid pressure power plant of claim 11 wherein the heat
energy is supplied to the heat chambers through heat pipes.
13. The fluid pressure power plant of claim 11 wherein the heat for
the hot gas chamber is supplied by direct heat transfer from a
built-in heat source.
14. A method of producing power from heat energy comprising:
supplying hydraulic fluid at low pressure to at least one power
converting piston;
generating heat energy;
feeding the heat energy to the power converting piston;
converting the heat energy to high hydraulic pressure;
storing the high pressure hydraulic fluid for use on demand;
recycling the piston with the low pressure hydraulic fluid;
driving a power unit with the power created by the high hydraulic
pressure.
15. The method of claim 14 further including the steps of:
controlling the flow of high hydraulic pressure to the power units;
and
directing the hydraulic fluid after use by the power unit back to a
main reservoir for recycling through the system.
16. The method of claim 15 wherein the step of generating heat
energy comprises:
generating steam;
storing the steam in an accumulator at low pressure; and
controlling the flow of steam to power converting piston.
17. The method of claim 15 wherein the heat energy generation step
comprises:
generating heat;
directing the heat to the power converting piston; and
transferring the heat to a heat expandable gas to drive the
piston.
18. The method of claim 17 wherein the power conversion system
includes the steps of:
cyclically operating a group of four pistons with the pistons
operating at a phase angle of 90 mechanical degrees with respect to
the preceding piston.
19. The fluid pressure power plant of claim 11 wherein the high
pressure accumulator is an air bladder type accumulator.
20. The fluid pressure power plant of claim 7 wherein the high
pressure accumulator is an air bladder type accumulator.
21. The method of claim 16 including the steps of:
condensing the steam to a fluid after use by the power conversion
piston;
preheating the hydraulic fluid flowing to the steam generator with
the heat of condensation; and
feeding the condensed steam back to the main reservoir for
recycling.
22. The method of claim 21 including the steps of:
reclaiming heat from the exhaust of the steam generator with a heat
exchanger; and
preheating the hydraulic fluid flowing to the steam generator with
the heat reclaimed in the heat exchanger.
Description
STATEMENT OF GOVERNMENT INTEREST
The invention described herein may be manufactured and used by or
for the Government of the United States of America for governmental
purposes without the payment of any royalties thereon or
therefor.
BACKGROUND OF THE INVENTION
This invention relates generally to power plants and more
particularly to a power plant which converts heat energy to
hydraulic power.
Presently, in the operation of almost all power systems, energy in
the form of heat is thrown away in huge quantities. Heat is thrown
away in the form of unused power developed because of the necessity
to maintain engine speed and angular momentum of mechanical drive
lines, etc. In conventional systems there is only one chance to use
the heat energy and that is the time when it resides in the kinetic
energy of expanding a gas or a vapor. After that it is unwanted
heat which is detrimental to engine components and must be
dissipated. The development of unused power also results in a gross
waste of fuel. Atmospheric contamination and combustion noise are
additional problems of conventional systems.
SUMMARY OF THE INVENTION
The purpose of the present invention is to provide a high
efficiency, demand cycle power plant which eliminates some of the
disadvantages of conventional systems. The system uses either steam
or hot gas for the energy input. In the steam system, a steam
generator supplies energy to a power converting piston which
transforms the input energy into output energy in the form of high
hydraulic pressure. The output power hydraulic pressure is stored
in a high pressure accumulator which in turn drives energy
utilization devices such as one or more hydraulic motors or
turbines through hydraulic output control valves. Since the system
uses external combustion in the form of a steam generator to
produce the energy input, it has the advantage over conventional
systems of being low in noise and air pollution. Another advantage
is that the system is highly efficient because it operates on a
demand cycle. That is, the system is arranged so that no energy
input from the steam generator is necessary until there is some
demand for power output from the hydraulic accumulator.
The hydraulic fluid used to produce the power output is
continuously circulated around a closed cycle. The hydraulic fluid
is pumped from a main reservoir to a low pressure hydraulic
accumulator and then to the power converting pistons. The power
converting pistons then force the hydraulic fluid under high
pressure into the high pressure hydraulic accumulator. The high
pressure hydraulic fluid is then used to drive one or more
hydraulic motors or turbines. The hydraulic fluid is then
recirculated back to the main reservoir. The main reservoir also
provides the fluid for the steam generator.
The system is highly efficient because of the use of a demand
cycle, but a further increase in efficiency can be made by using
thermal jacketing to reduce heat losses. Another important feature
of the invention is that it is simple in construction and highly
adaptable to be changed to meet future power requirements. The
components of the system need not be centrally located as is the
case in the conventional engine. Also, the system requires no gear
train, driven axle or crankshaft, except at the power output. This
further increases the system reliability.
OBJECTS OF THE INVENTION
It is an object of the present invention to provide a power plant
which employs an expanding gaseous medium to create a body of fluid
under pressure which may be used to perform work.
Another object of the present invention is to provide a power plant
which employs steam as the expanding gaseous medium.
Yet another object of the present invention is to provide a power
plant which employs a hot gas as the expanding gaseous medium.
Still another object of the present invention is to provide a power
plant which enhances efficiency by operating only on occasions of
demand.
Another object of the present invention is to provide a power plant
which is low in noise and air pollution.
Yet another object of the present invention is to provide a power
plant which is readily adaptable to increased power
requirements.
Still another object of the present invention is to provide a power
plant with improved maintenance characteristics by eliminating the
need for gears, axles or shafts.
Other objects, advantages and novel features of the invention will
become apparent from the following detailed description of the
invention when considered in conjunction with the accompanying
drawings in which like reference numbers indicate identical
components throughout the figures.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a fluid flow schematic diagram of an embodiment of the
present invention where the expanding gaseous medium is steam.
FIG. 2 is a longitudinal cross-sectional view of a power conversion
piston illustrating the operation of the intake and exhaust
valves.
FIG. 3 illustrates an alternate arrangement of the intake and
exhaust valves of FIG. 2.
FIG. 4 is a fluid flow schematic diagram of an embodiment where the
expanding gaseous medium is heated gas.
FIG. 5 is a cross-sectional view of a power conversion cylinder
group used in conjunction with the hot gas system of FIG. 4.
FIG. 6 is a cross-section through one of the power conversion
cylinders of FIG. 5.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Since both the steam and hot gas systems comprise a closed cycle
process, which only serves as a medium for transportation,
distribution, and transformation of the energy between the power
input and output, one must establish an arbitrary point in the
cycle as the beginning. The energy input, which in the system shown
in FIG. 1 is the steam generator, is an obvious starting point. For
purposes of analysis, the system can be subdivided into a number of
subsystems according to function as shown by the dashed lines in
FIG. 1. In that figure the subsystem designated A is the energy
input generating subsystem. That designated B is the power
conversion subsystem. That designated C is the hydraulic pressure
storage subsystem. That designated D is the power output subsystem
and that designated E is the fluid supply and low pressure
hydraulic subsystem.
Beginning with the energy input subsystem A, steam is generated in
boiler 10 and fed through check valve 12 to steam accumulator 14.
In order to improve the efficiency of the system, the exhaust from
the steam generator 10 may be fed through a heat exchanger 16 to
preheat the fluid coming into the steam generator, and may then be
exhausted to the atmosphere at 18. Pressure in steam accumulator 14
is sensed and a control signal is fed back through feedback control
20 to the steam generator 10 to turn off the latter when the
pressure reaches a certain limit.
The power conversion system includes intake and exhaust valves 22
and 22' power conversion piston units 24 and 24' and a number of
check valves 28, 28', 30 and 30' for controlling input and output
of hydraulic fluid. In addition, the hydraulic fluid may be fed
through an orifice restriction 26 and 26' to cushion the operation
of the intake and exhaust valves. Orifice restriction 26 is an
adjustable valve such as a needle valve, throttling valve, etc. It
should be adjustable such that the reaction of the intake and
exhaust valves 22 and 22' to the pressure changes in line 60 (FIG.
2) may be varied in order to optimize performance. Check valves 28
and 28' control the input of fluid to the power output side of
power conversion piston units 24 and 24'. Check valves 30 and 30'
control the output of the high pressure hydraulic fluid to high
pressure hydraulic accumulator 32. The high pressure accumulator 32
may be of the air chamber type illustrated in which a bladder is
preloaded with air to a particular pressure. However, other types
of pressure accumulators would also be suitable.
The high pressure hydraulic accumulator subsystem C stores the
hydraulic fluid under high pressure for use on demand by the power
output subsystem D. The air head provided by a suitable source such
as the preload air compressor 34 is the compressible medium which
allows the hydraulic fluid to build up and to diminish on a demand
basis. This high pressure hydraulic accumulator action also
functions to smooth out the pulsations of the individual piston
movements.
The hydraulic output control valves 36 and 36' control the flow of
power to hydraulic power output units 37 and 37'. These units may
be in the form of hydraulic motors, turbines or whatever is
dictated by the use for which the system is employed.
Fluid for the entire fluid cycle is furnished by the main fluid
reservoir 38, maintained at atmospheric pressure or less for
maximum pressure gradient across the power conversion units 24 and
24', and especially to maintain a low pressure in condenser 46. A
low pressure in condenser 46 aids in reducing the residual steam
pressure in the power conversion pistons on the upstroke, thus
adding to overall system efficiency. Low pressure hydraulic recycle
pump 40 pressurizes low pressure hydraulic accumulator 44 through
check valve 42 and supplies the fluid to steam generator 10 through
another check valve 43. Centrifugal separator 47 may or may not be
used as will be more fully explained hereinafter. Low pressure
hydraulic accumulator 44 also provides the recycle pressure for
power conversion piston units 24 and 24' as will be more fully
explained in conjunction with FIGS. 2 and 3 hereinafter. Input
check valve 42 prevents low pressure hydraulic accumulator 44 from
supplying back pressure to the low pressure hydraulic recycle pump
40.
The system is purely a demand system. When the power output units
37 and 37' are drawing no power, the pressure in the high pressure
hydraulic accumulator 32 builds to the maximum obtainable by the
power conversion piston units 24 and 24', which may be anywhere
from 1800 psia to 3000 psia. Whenever this occurs, the power
conversion piston units cease to operate and the pressure in the
steam accumulator 14 builds to a preset value at which point the
energy input subsystem A shuts down. The static head in the low
pressure hydraulic accumulator 44, supplied from preload air
compressor 34 through line 45 to 45' or some other source, reaches
the maximum deliverable pressure (approximately 150 psia) of low
pressure hydraulic recycle pump 40, which then ceases to pump. A
pressure regulator (not shown) may be required in line 45 to 45'
because of the pressure difference between accumulators 32 and 44.
As the demand by the power conversion units 37 and 37' increases,
the power conversion piston units 24 and 24' start to work, but
only to meet the demand since no zero-power cyclic phenomena are
present. There is absolutely no power developed by the system
except when there is power consumed by the power conversion units.
The system is flexible and can be adapted to meet any power demands
by employing parallel components in any or all of the subsystems A
through E, as required.
A detailed section view of power conversion piston 24 of the steam
system shown in FIG. 1 is illustrated in FIG. 2. The intake and
exhaust valves 48 and 50 are shown in the intake position with
piston 52 near the bottom of its stroke. When piston 52 reaches the
bottom of its stroke just short of low pressure fluid input line
54, the intake and exhaust spool valves 48 and 50 will reverse
position and the exhaust port 56 will be open and the intake port
58 closed. As low pressure fluid comes in the low pressure fluid
input line 54, the piston 52 will start to rise, forcing the
exhaust materials out the exhaust port 56. When the piston 52
reaches the position shown in dotted lines 52, the low pressure
fluid will begin to flow through line 60 to the spool valves. The
low pressure fluid will force the spool valve 50 closed, stopping
flow through exhaust line 56 and the intake valve 48 will then
open, allowing ingress of steam through line 58. At this time,
steam begins to come into upper piston chamber 62, starting
downward movement of piston 52. When lower piston ring(s) 64 get
beyond the line 60 from the low pressure fluid chamber 66 to the
spool valves 48 and 50, the low pressure fluid, which forced the
spool valves 48 and 50 into the intake position, begins to drain
off into the chamber 68 and out exhaust port 70 at the bottom of
the chamber 68. It should be noted that as piston 52 starts its
downward stroke, line 60 will momentarily be under high pressure.
The position of line 60 can be varied to control at what point in
the cycle of the piston 52 the valves 48 and 50 open and close.
Again when the piston 52 reaches the bottom of its downward stroke,
the spool valves 48 and 50 will reverse, opening the exhaust port
56 and closing the intake port 58. With each downward stroke, the
hydraulic fluid forced into the chamber 66 at low pressure will be
forced at high pressure through the check valve 30 in the line 29
from the bottom of the power output side of the piston chamber 66.
A suitable pressure gradient across the piston 52 was determined to
be about twelve to one, however, other values may be used, if
desired. That is, the ratio of the area of the top 51 of the piston
to the bottom 53 of the piston is about twelve to one.
The steam coming from exhaust port 56, along with the low pressure
hydraulic fluid flowing in line 70 are both fed to the condenser
46. Some of the heat from the steam is reclaimed in this condensing
process and also used to preheat the hydraulic fluid being fed to
the boiler 10. The use of reclaimed heat in heat exchanger 16 and
condenser 46 to preheat the hydraulic fluid conserves energy and is
an additional method of improving the overall efficiency of the
system.
FIG. 3 is another detailed section of the power conversion piston
24 with a different arrangement for the intake and exhaust valves
48 and 50. In this embodiment, the spool valves of FIG. 2 are
replaced with poppet valves. They operate in substantially the same
manner as the spool valves 48 and 50 of FIG. 2, except that they
are more like the conventional poppet valves with the up and down
motion. Again, as the low pressure fluid forces the piston 52
upward, fluid flows through the line 60 to the valves, forcing the
intake valve 48 open and the exhaust valve 50 closed. When the
piston 52 reaches the bottom of its stroke, the pressure is
relieved from the poppet valves and the intake valve 48 closes
while the exhaust valve 50 opens. The valve arrangements shown in
FIGS. 2 and 3 are merely illustrative and other valve arrangements
may be entirely suitable.
The steam system shown in FIG. 1 has two power conversion pistons
24 and 24', merely to illustrate that more than one power
conversion piston may be used. However, only one power conversion
piston may be used or any number may be used, as desired.
Additional power conversion pistons may be added as needed and the
only limit on the number of power conversion pistons is the size of
the main reservoir and the amount of energy output of the holder.
Additional pistons would be added in parallel with the existing
pistons as piston 24'. It is important to note that each power
conversion piston operates completely independent of any others. In
other words, a power conversion piston may be added or removed from
the system without affecting the performance of the other pistons.
Likewise, the power output may be used by one or more hydraulic
motors or turbines and as many as needed may be added within the
limits of the system.
One distinct advantage over conventional systems is that the entire
system may be in modular form. That is, each part may be located in
a different area from another part and operates independently. For
example, the main reservoir may be mounted on one part of the
vehicle with the pump at another position and the accumulators at
even different positions. Also, the power conversion pistons may be
located in the frame, on the body, or, if desired, can be centrally
located. The advantage of this is that if one portion of the system
is damaged, it may be easily replaced. Or for example, if a power
conversion piston is damaged, it may be removed or merely valved
off and the system will still operate without it.
With this system mounted in a vehicle and spread out throughout the
body and frame of the vehicle, it would be difficult to disable the
system completely. Further, by valving on or off additional power
conversion pistons, the power may be used as needed rather than
using full power all the time.
One of the difficulties with some of the present systems is the
problem of providing lubrication throughout the system. This is a
problem because many of the materials for lubrication cannot go
through the energy input cycle. However, there are many materials
now which can be included in with the fluid used to supply the
steam generator system and which can be separated out before the
water or other fluid passes to the steam generator system. For this
purpose, centrifugal separator 47 is inserted in the system after
the low pressure hydraulic accumulator 44. There are a number of
types of centrifugal separators which would be suitable for this
system.
Fluids suitable for the vapor cycle have quite poor, generally,
lubrication qualities and, therefore, a lubricant which has all the
proper qualities for use in a hydraulic medium will most likely be
required as an additive of some type. Thus, a fluid chosen which
has a density significantly different from the hydraulic fluid can
easily be separated in the centrifugal separator 47 and fed back
through a line 49 to the low pressure hydraulic accmumulator 44.
Then, only the hydraulic fluid capable of being used in the vapor
cycle will pass to the boiler 10. The vapor to hydraulic fluid
volumetric flow ratio is approximately 12 to 1 in this case
(although it could be any ratio desirable). Also, the vapor mass
flow rate is low compared to the hydraulic fluid mass flow rate.
This fact is due to the several hundred to one volumetric expansion
from liquid to vapor in the boiler. With these comparatively low
flow rates, separation of the lubricant from the hydraulic fluid in
the centrifugal separator does not present any problem. With the
continuing discovery of new materials, a simpler solution to the
lubrication/lubricant vapor cycling problem may be available. For
example, a lubricant which can pass through the vapor cycle would
eliminate the need for a centrifugal separator.
The most readily available hydraulic fluid, of course, would be
water. However, the Mollier diagrams (Enthalpy versus Entropy) for
some of the organic substances such as Dowtherm A, Dowtherm E, and
Toluene show promise for increasing thermal efficiency. Selection
of a suitable hydraulic fluid for the vapor cycle depends upon such
factors as the properties desired and the cost.
Preferably the power conversion pistons 24 and 24' would operate on
a full or partial expansion principle. This is because although the
non-expansion pressure multiplication or intensifier piston
described is the simplest, mechanically, it is less efficient than
full or partial expansion pistons. The boiler steam delivered to
the piston contains energy in the form of pressure and temperature.
The non-expansion piston cannot take advantage of the internal
energy represented by the temperature. An expansion piston converts
both pressure and internal energy into work. For example, using a
proposed boiler pressure of 150 psia, a partial-expansion piston
cycle, expanding to 40 psia, provides a cycle efficiency of more
than twice that of the non-expansion piston cycle. Efficiency
enhancement by application of such techniques is described in
detail in "Principles of Engineering Thermodynamics" by Kiefer and
Stuart, published in 1949 by John Wiley and Sons, and in "Steam
Power Plant Engineering" by Gebhardt, 6th Edition 1928, published
by John Wiley and Sons.
The system shown in FIG. 4 is an alternative embodiment which
operates on hot gas (such as air, nitrogen or helium) as the energy
input rather than the vapor cycle and requires power conversion
pistons in groups of four. As in the steam system, an arbitrary
point was selected as the starting point, and in this case it was
the energy input which is the heat source. Beginning with the heat
source, the theory of operation shall be explained in the sequence
in which the operational functions occur. Again, for clarification,
the system is broken down into five subsystems. These are the heat
generation subsystem A, the power conversion subsystem B, the
energy storage and distribution subsystem C, the hydraulic output
power utilization subsystem D, and the fluid supply and low
pressure hydraulic subsystem E.
As in the steam system, the system of FIG. 4 is an external
combustion engine employing hydraulic power transfer. A heat source
is used to produce heat which is applied to the hot end of the
power conversion cylinders 74, 76, 78 and 80. Direct heat transfer
will suffice in the case where the heat source is built into the
cylinders or, the heat source may be separate with heat transfer to
the cylinders by the use of heat pipes as at 82. When this heat is
applied to the cylinder heads, it causes the gas in the cylinder to
expand, thus driving the respective pistons downward. The pistons
are pressure multiplication pistons as in the steam system, the top
end being several times as large in area as the lower end (e.g. a
ratio of 4 to 1 might be suitable). Many such pistons can be
employed in parallel to meet whatever power requirements are
desired by the user, however, pistons function together in groups
of four and multiples of four are required. Other than the grouping
of four, no fixed number of pistons is required beyond the initial
four. Obviously, the sizing of the entire system must be considered
for the ultimate application of large numbers of pistons, etc. The
requirement that the pistons be employed in groups of four derives
from the fact that the pistons are phased 90.degree. apart and are
hydraulically interlocked to maintain this phase separation. Th use
of porting without valves, heat regenerators, and the hot-to-cold
gas cycling requires the 90.degree. phase relationship between
pistons. A half stroke is 90.degree..
As the gas in the chamber expands, forcing the piston down, it
drives a hydraulic fluid under high pressure through a check valve
75, 77, 79 or 81 into a high pressure accumulator 32, as in the
steam system. The hydraulic pressure stored in the accumulator 32
is fed to power output units such as hydraulic motors or turbines
37 and 37' through output control valves 36 and 36'. The hydraulic
fluid, after dissipating its energy, is then recycled to the main
fluid reservoir 38. The fluid is then cooled and pumped to a low
pressure hydraulic accumulator 44 from where it is fed to the power
conversion cylinders and is recycled through the system.
Referring now to FIG. 5, there is shown a sectional view
illustrating the function of the group of four power conversion
cylinders 74, 76, 78 and 80. Heat is generated either directly in
the top of the cylinders by a burner (not shown) or is fed to the
cylinders through heat pipes 82 as shown.
Direct heating by a burner is described in an article in the June
1971 issue of Popular Science, pages 54-56. In FIG. 4, the arrow
associated with the heat pipe 82 shows direction of heat flow. The
vapor flow and return capillary flow of fluid internal to the pipe
is bi-directional. There are many treatises on the subject of heat
pipes in "The Proceedings of the 4th Intersociety Energy Conversion
Engineering Conference, Washington, D.C., September 22-26, 1969,
such as Paper No. 27291, page XIV.
The heat is conducted to the chamber 98 at the top of the cylinder
by a thin metal membrane formed into fins 84, acting as a heat
exchanger and causes the gas in the cylinder to expand, forcing the
piston 86 downward. As the piston 86 moves downward, it drives
fluid under high pressure through a check valve 88 into high
pressure accumulator 32. As the piston reaches the bottom of its
stroke, the high pressure in the lower chamber 90 of the cylinder
falls and the high pressure hydraulic check valve 88 shuts off. The
low pressure hydraulic check valve 92 then opens under pressure
from the low pressure accumulator 44 and low pressure hydraulic
fluid forces the piston upwards.
As the piston 86 went through the cycle just described, its
movement caused several things to happen. As the piston 86 of
cylinder 80 starts its downward stroke, the gas in the water-cooled
lower end 94 of the large cylinder is forced through a line to a
regenerator 96 into the hot end 98 of the last cylinder 74. Cooling
water is supplied to the cylinder from pump 40, as shown, to cool
the gas in lower chamber 94 and then returned to reservoir 38 (FIG.
4). The gas is super-heated in chamber 98 of cylinder 74 and the
piston 86 moves downward on its power stroke, forcing hydraulic
fluid at the bottom end through the high pressure hydraulic fluid
check valve 88 and at the same time forcing cool gas in the lower
end 94 of cylinder 74 through the next regenerator 96 and into the
hot end of cylinder 76. Each successive piston and regenerator
works in the same way. The regenerators 96 preheat cool gas coming
from the watercooled end 94 of the cylinders and cools the gas as
it comes from the hot end 98 of the cylinders when the piston is in
its upward stroke. Only one heat regenerator per piston is shown,
however, more may be needed, depending upon the heat capacity
required. The interaction between the pistons 86, gas and heat
regenerators 96 is a type of Stirling cycle and is very
straightforward.
FIG. 6 shows one of the cylinders of FIG. 5 in greater detail. A
thin metal membrane formed into fins 84 act as a heat exchanger to
supply heat from heat pipe 82 to chamber 98. In FIG. 6, a
bi-directional flow of gas is shown through line 95 into chamber 94
from a source of expandable gas. Details are not shown in FIGS. 4
and 5 to avoid further complicating the drawings. Additional gas is
introduced during acceleration and bled off during deceleration.
This procedure is standard in Stirling cycle engines and the method
of application is somewhat arbitrary. No fixed method is prescribed
herein, rather the anticipated use of the technique is cited for
reference.
The hydraulic interaction at the lower end 90 of the pistons is a
little more complicated. As piston 86 of cylinder 80 begins to move
downward, the lower piston ring 100 passes a port 102 leading to a
cushioning valve 104 and a spool valve 106. The hydraulic pressure
in the line to cushioning valve 104 then drops to zero or near
zero. The cushioning valve 104 prevents the spool valve from
operating instantaneously and its reaction time should be
adjustable. When the spool valve 106 opens, low pressure hydraulic
fluid flows through check valve 92 to the cylinder 76, which is at
the bottom of its stroke. The piston 86 of cylinder 76 therefore
may not operate until the first piston 86 of cylinder 80 operates.
The position of the fluid port controlling the spool valve 106 in
cylinder 80 assures 180.degree. separation between these two
pistons.
As the piston 86 of cylinder 80 continues to move downward, the
piston ring 100 (or rings) pass the fluid port 108 leading to
another cushioning valve 110 and spool valve 112. This port is
located at the mid-point of the piston stroke or 90 mechanical
degrees of the piston cycle. As the ring 100 passes the port 108,
the pressure in the line to the cushioning valve 110 drops and the
adjacent spool valve 112 operates, allowing low pressure hydraulic
fluid to flow through a check valve 92 to the adjacent cylinder 78,
which will be at the bottom or 180.degree. of its stroke. Of
course, the first piston cylinder 80 and the adjacent piston
cylinder 78 are 90.degree. apart in phase so that when the first
piston cylinder 80 has reached the midpoint of its downard
movement, the adjacent piston cylinder 78 is at the bottom when the
spool valve 112 opens to allow the low pressure hydraulic fluid to
flow into the chamber 90.
At the same time that the first piston cylinder 80 is at its
mid-point on the way down, the third piston cylinder 76 is at its
mid-point on the way up. As the lower ring 100 on the third piston
86 of cylinder 76 passes the fluid port 114 leading to a cushioning
valve 116 and a spool valve 118, the presure on the spool valve 118
is restored and it shuts off the fluid flow to the last piston 86
of cylinder 74 through a check valve 92. The mid-point location of
the fluid port 114 leading to the cushioning valve 116 assures
90.degree. phase separation between the third and fourth piston
cylinders 76 and 74.
When the output power demand goes to zero, the pressure in the high
pressure accumulator 32 fills to the maximum deliverable by the
pistons and a flow rate indicator will "tell" the heat generating
source 72 through a feedback line indicated at 31 to retard its
output. Besides storing high pressure fluid for use on demand by
hydraulic motors or turbines, the accumulator 32 acts to smooth the
pulsations of the individual piston strokes. Hydraulic output
control valves 36 and 36', which may be throttle valves, if
desired, control the power flow to the hydraulic power units which
may be hydraulic motors or turbines, or whatever device is dictated
by the use for which the system is employed.
Fluid for the entire cycle is stored in a main reservoir 38 which
should be maintained at a pressure which will not allow the low
pressure hydraulic recycle pump 40 to flash and yet low enough that
for maximum efficiency the pressure gradient across the hydraulic
power units 37 and 37' is maximum. Cooling of the fluid in the main
reservoir 38 will probably be required. A fan 39, radiator, or
other cooling device may be employed.
A low pressure recycle pump 40 supplies the hydraulic pressure to
operate all the valves and recycle the pistons, as described at
length above, through a hydraulic check valve 42 and a low pressure
hydraulic accumulator 44. The hydraulic check valve 42 acts to
isolate the pressure of the low pressure hydraulic accumulator 44
from the recycle pump. Also, the low pressure hydraulic accumulator
44 stores hydraulic fluid under pressure and acts to smooth pumping
action of the low pressure recycle pump 40.
Most of the components for both the steam and the hot air systems
are readily available and it is merely a matter of selecting the
proper units for the particular use required. They must, however,
be properly connected and employed to operate in conjunction with
the proper conversion pistons, as described. An inherent advantage
of the system is the capability of efficiency enhancement through a
unique arrangement of system components. What is proposed here is
that the power output units 37 and 37' be hydraulic motors of the
variable displacement motor/pump design. The variability in
displacement may be achieved by varying the pitch of a camplate
(not shown). By varying the pitch until the plate passes through
the perpendicular and the pitch is reversed, the motor can be made
to act as a pump. By the simple expedience of using the motor as a
motor during acceleration, and as a pump during deceleration, a
large portion of the energy normally given up to breaking can be
reclaimed and used during future acceleration.
Whether one wants to maintain a single high pressure accumulator 32
or more than one to accommodate pumping and motor operation modes
would depend on the application for which the system is used. In
the case where an automotive application is considered, there will
be energy differences and speed differences based on the vehicle,
be it anything from a truck to a sports car, which will encompass a
power range far too comprehensive to cover with a flat statement
about "automotive applications." An overall increase in energy
conversion efficiency can be realized by utilizing the concept of
regenerative breaking.
Thus, there has been disclosed two types of fluid pressure power
plants which operate on a demand cycle and are adaptable to
variable power output requirements. The ability to build the system
in modular form is certain to increase reliability and enhance
maintenance requirements.
Obviously, many modifications and variations of the present
invention are possible in the light of the above teachings. It is
therefore to be understood that within the scope of the appended
claims the invention may be practiced otherwise than as
specifically described.
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