U.S. patent application number 11/509202 was filed with the patent office on 2007-03-15 for splitter valve in a heat regenerative engine.
This patent application is currently assigned to Cyclone Technologies LLLP. Invention is credited to Harry Schoell.
Application Number | 20070056287 11/509202 |
Document ID | / |
Family ID | 38957308 |
Filed Date | 2007-03-15 |
United States Patent
Application |
20070056287 |
Kind Code |
A1 |
Schoell; Harry |
March 15, 2007 |
Splitter valve in a heat regenerative engine
Abstract
In a heat regenerative engine that uses water as both the
working fluid and the lubricant, water is pumped through a single
line of a coil that wraps around a cylinder exhaust port, causing
the water to be preheated by steam exhausted from the cylinder. The
preheated water is then directed through multiple branch lines in a
steam generator to produce high pressure super heated steam. A
splitter valve at the juncture of the single line and multiple
branch lines equalizes the flow among the multiple branch lines. A
"Y" junction within the splitter valve minimizes turbulence as the
flow of water and steam is directed into the multiple branch lines.
Flow control restrictors in the splitter valve allow unimpeded flow
of fluid and steam towards the steam generator through each of the
branch lines, while allowing any incremental over-pressure in any
one branch line to "bleed" back to a branch line(s) bearing a
lesser amount of pressure, thereby equalizing flow through the
multiple branch lines.
Inventors: |
Schoell; Harry; (Pompano
Beach, FL) |
Correspondence
Address: |
ROBERT M. DOWNEY, P.A.
6751 N. FEDERAL HWY., SUITE 300
BOCA RATON
FL
33487
US
|
Assignee: |
Cyclone Technologies LLLP
|
Family ID: |
38957308 |
Appl. No.: |
11/509202 |
Filed: |
August 24, 2006 |
Related U.S. Patent Documents
|
|
|
|
|
|
Application
Number |
Filing Date |
Patent Number |
|
|
11489335 |
Jul 19, 2006 |
|
|
|
11509202 |
Aug 24, 2006 |
|
|
|
11225422 |
Sep 13, 2005 |
7080512 |
|
|
11489335 |
Jul 19, 2006 |
|
|
|
Current U.S.
Class: |
60/670 |
Current CPC
Class: |
F01K 11/00 20130101 |
Class at
Publication: |
060/670 |
International
Class: |
F01K 23/06 20060101
F01K023/06 |
Claims
1. A valve device for use at the juncture of a single steam line
and multiple branch steam lines through which liquid and steam
flow, said valve device comprising: a main body; an inlet on said
main body for connection to the single steam line; a plurality of
outlets on said main body, each of said plurality of outlets being
structured and disposed for connection to a respective one of the
multiple branch steam lines; a junction within said main body and
between said inlet and said plurality of outlets for directing the
flow of liquid and steam entering said inlet to each of said
plurality of outlets; and flow control restrictors for allowing
unimpeded flow of fluid and steam into each of the multiple branch
steam lines and said flow control restrictors being structured and
disposed for equalizing pressure and flow of steam through the
multiple branch steam lines.
2. The valve device as recited in claim 1 wherein said junction is
structured and disposed to minimize turbulence as the flow of
liquid and steam is directed to said plurality of outlets.
3. The valve device as recited in claim 2 wherein said flow control
restrictors include ball check valves between said junction and
said plurality of outlets for preventing back-flow of steam from
over-pressure into the single steam line.
4. The valve device as recited in claim 3 wherein said flow control
restrictors include over-pressure valves for releasing the
over-pressure in any of said multiple branch steam lines.
5. A valve device for use at the juncture of a single steam line
and multiple branch steam lines through which liquid and steam
flow, said valve device comprising: a main body; an inlet on said
main body for connection to the single steam line; a plurality of
outlets on said main body, each of said plurality of outlets being
structured and disposed for connection to a respective one of the
multiple branch steam lines; a junction within said main body and
between said inlet and said plurality of outlets for directing the
flow of liquid and steam entering said inlet to each of said
plurality of outlets; flow control restrictors for allowing
unimpeded flow of fluid and steam into each of the multiple branch
steam lines and said flow control restrictors being structured and
disposed for preventing back-flow of steam into the single steam
line; and over-pressure valves for releasing over-pressure in any
of the multiple branch steam lines.
6. The valve device as recited in claim 5 wherein said junction is
structured and disposed to minimize turbulence as the flow of
liquid and steam is directed to said plurality of outlets.
7. The valve device as recited in claim 6 wherein said flow control
restrictors include ball check valves.
Description
[0001] This application is a divisional patent application of
co-pending patent application Ser. No. 11/489,335 filed on Jul. 19,
2006, which is a continuation patent application of patent
application Ser. No. 11/225,422 filed on Sep. 13, 2005, now
patented under U.S. Pat. No. 7,080,512 B2 the disclosure of which
is incorporated herein by reference.
BACKGROUND OF THE INVENTION
[0002] 1. Field of the Invention
[0003] This invention relates to directing flow of fluid and steam
from a single line into multiple lines and, more particularly, to a
splitter valve at the juncture of a feeder line and multiple branch
lines for equalizing flow and pressure of fluid and steam among the
multiple branch lines.
[0004] 2. Discussion of the Related Art
[0005] In the art of steam generation it is known to direct water
through a metal tube (e.g., copper, aluminum, stainless steel)
while exposing the exterior surface of the tube to extremely high
temperatures. Eventually, after prolonged exposure to sufficient
temperatures of heat, the water traveling through the metal tube
boils and turns into steam. Continuing to expose the steam carrying
metal tube to temperatures in excess of 1,200 degrees Fahrenheit
will eventually cause the steam to become super heated steam.
However, reaching super heated steam levels requires a substantial
length of metal tube in order to provide sufficient surface area
for heat transfer. Accordingly, it has not been practical to
generate steam within a compact area by directing water through a
metal tube that is exposed to heat.
[0006] Splitting a feeder tube (i.e. feeder line) into multiple
branch tubes (i.e. branch lines) having a combined cross-sectional
area equal to the feeder tube would effectively and significantly
increase the tube surface area within the same volume of space. By
increasing the tube surface area and decreasing the tube size, the
efficiency of heat transfer is greatly improved. Additionally, the
smaller tube diameter allows the tube to withstand higher
pressures.
[0007] While such equalization of volumes and capacities between a
single feeder line and multiple branch lines of reduced size would
be balanced under static conditions, under the dynamic conditions
of super critical high temperatures and high pressures, comparative
flow among the smaller branch lines can become unbalanced. This can
lead to potential overheating and possible wall failure in the pipe
that has lower flow volume (i.e. a lower amount of water and steam
flowing therethrough). The present invention solves this problem by
equalizing flow and pressure in the multiple branch lines, even at
high temperatures and pressure levels.
OBJECTS AND ADVANTAGES OF THE INVENTION
[0008] With the foregoing in mind, it is a primary object of the
present invention to provide a valve device at the juncture of a
single feeder line and multiple branch lines in a steam engine for
equalizing flow and pressure of fluid and steam among the multiple
branch lines.
[0009] It is a further object of the present invention to provide a
splitter valve at the juncture of a single feeder line and multiple
branch lines in a steam engine that equalizes flow and pressure of
fluid and steam in the branch lines under dynamic conditions of
super critical high temperatures and high pressures.
[0010] It is still a further object of the present invention to
provide a splitter valve device at the juncture of a single steam
feeder line and multiple steam branch lines, and wherein the
splitter valve device is structured and disposed for equalizing
flow volume and pressure levels among the multiple steam branch
lines.
[0011] It is still a further object of the present invention to
provide a splitter valve for use at the juncture of a single steam
feeder line and multiple steam branch lines, and wherein the
splitter valve is structured and disposed for bleeding
"over-pressure" in any one steam branch line back to a steam branch
line(s) that has a lesser amount of pressure, thereby equalizing
flow through the multiple steam branch lines.
[0012] These and other objects and advantages of the present
invention are more readily apparent with reference to the detailed
description and accompanying drawings.
SUMMARY OF THE INVENTION
[0013] The present invention is directed to splitter valve for use
in a heat regenerative engine that uses water as both the working
fluid and the lubricant. In the heat regenerative engine, water is
pumped through a single line of a coil that wraps around a cylinder
exhaust port, causing the water to be preheated by steam exhausted
from the cylinder. The preheated water is then directed through
multiple branch lines in a steam generator to produce high pressure
super heated steam. The splitter valve is located at the juncture
of the single line and multiple branch lines to equalize the flow
among the multiple branch lines. A "Y" junction within the splitter
valve minimizes turbulence as the flow of water and steam is
directed into the multiple branch lines. Flow control restrictors
in the splitter valve allow unimpeded flow of fluid towards the
steam generator through each of the branch lines, while allowing
any incremental over-pressure in any one branch line to "bleed"
back to a branch line(s) bearing a lesser amount of pressure,
thereby equalizing flow through the multiple branch lines.
BRIEF DESCRIPTION OF THE DRAWINGS
[0014] For a fuller understanding of the nature of the present
invention, reference should be made to the following detailed
description taken in conjunction with the accompanying drawings in
which:
[0015] FIG. 1 is a general diagram illustrating air flow through
the engine;
[0016] FIG. 2 is a general diagram illustrating water and steam
flow through the engine;
[0017] FIG. 3 is a side elevational view, shown in cross-section,
illustrating the principal components of the engine;
[0018] FIG. 4 is a top plan view, in partial cross-section, taken
along the plane of the line 4-4 in FIG. 3;
[0019] FIG. 5 is a top plan view of the splitter valve of the
present invention; and
[0020] FIG. 6 is a cross-sectional view of the splitter valve taken
along line 6-6 in FIG. 5 and illustrating a flow control valve
within the splitter valve.
[0021] Like reference numerals refer to like parts throughout the
several views of the drawings.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0022] The present invention is directed to a splitter valve 26 for
use in a steam engine 10. Referring initially to FIGS. 1-4, the
engine 10 includes a steam generator 20, a condenser 30 and a main
engine section 50 comprising cylinders 52, valves 53, pistons 54,
push-rods 74, crank cam 61 and a crankshaft 60 extending axially
through a center of the engine section.
[0023] In operation, ambient air is introduced into the condenser
30 by intake blowers 38. The air temperature is increased in two
phases before entering a cyclone furnace 22 (referred to hereafter
as "combustion chamber"). The condenser 30 is a flat plate dynamic
condenser with a stacked arrangement of flat plates 31 surrounding
an inner core. This structural design of the dynamic condenser 30
allows for multiple passes of steam to enhance the condensing
function. In a first phase, air enters the condenser 30 from the
blowers 38 and is circulated over the condenser plates 31 to cool
the outer surfaces of the plates and condense the exhaust steam
circulating within the plates. More particularly, vapor exiting the
exhaust ports of the cylinders 52 passes over the pre-heating coils
surrounding the cylinders. The vapor drops into the core of the
condenser where centrifugal force from rotation of the crankshaft
drives the vapor into the inner cavities of the condenser plates
31. As the vapor changes phase into a liquid, it enters sealed
ports on the periphery of the condenser plates. The condensed
liquid drops through collection shafts and into the sump 34 at the
base of the condenser. A high pressure pump 90 returns the liquid
from the condenser sump 34 to the coils in the combustion chamber,
completing the fluid cycle of the engine. The stacked arrangement
of the condenser plates 31 presents a large surface area for
maximizing heat transfer within a relatively compact volume. The
centrifugal force of the crankshaft impeller that repeatedly drives
the condensing vapor into the cooling plates 31, combined with the
stacked plate design, provides a multi-pass system that is far more
effective than conventional condensers of single-pass design.
[0024] The engine shrouding 12 is an insulated cover that encloses
the combustion chamber and piston assembly. The shroud 12
incorporates air transfer ducts 32 that channel air from the
condenser 30, where it has been preheated, to the intake portion of
air-to-air heat exchangers 42, where the air is further heated.
Exiting the heat exchangers 42, this heated intake air enters the
atomizer/igniter assemblies in the burner 40 where it is combusted
in the combustion chamber. The shroud also includes return ducts
that capture the combustion exhaust gases at the top center of the
combustion chamber, and leads these gases back through the exhaust
portion of the air-to-air heat exchangers 42. The engine shrouding
adds to the efficiency and compactness of the engine by conserving
heat with its insulation, providing necessary ductwork for the
airflow of the engine, and incorporating heat exchangers that
harvest exhaust has heat.
[0025] Water in its delivery path from the condenser sump pump 90
to the combustion chamber 22 is pumped through one or more main
steam supply lines 21 for each cylinder. The main steam line 21
passes through a pre-heating coil 23 that is wound around each
cylinder skirt adjacent to that cylinder's exhaust ports (see FIG.
2). The vapor exiting the exhaust ports of cylinders 52 gives up
heat to this coil, which raises the temperature of the water being
directed through the coil 23 toward the combustion chamber 22.
Reciprocally, in giving up heat to the preheating coils 23, the
exhaust vapor begins the process of cooling on its path through
these coils preparatory to entering the condenser. The positioning
of these coils 23 adjacent to the cylinder exhaust ports scavenges
heat that would otherwise be lost to the system, thereby
contributing to the overall efficiency of the engine.
[0026] In the next phase, the air is directed through heat
exchangers 42 where the air is heated prior to entering the steam
generator 20 (see FIGS. 2 and 3). In the steam generator 20, the
preheated air is mixed with fuel from a fuel atomizer 41 (See FIG.
4). An igniter 43 burns the atomized fuel in a centrifuge, causing
the heavy fuel elements to move towards the outer sides of the
combustion chamber 22 where they are consumed. The combustion
chamber 22 is arranged in the form of a cylinder which encloses a
circularly wound coil of densely bundled tubes 24 (see FIG. 3)
forming a portion of the steam supply lines leading to the
respective cylinders. The bundled tubes 24 are heated by the
burning fuel of the combustion nozzle burner assembly 40 comprising
the air blowers 38, fuel atomizer 41, and the igniter 43 (see FIG.
4). The burners 40 are mounted on opposed sides of the circular
combustion chamber wall and are aligned to direct their flames in a
spiral direction. By spinning the flame front around the combustion
chamber, the coil of tubes 24 is repetitively `washed` by the heat
of this combustion gas which circulates in a motion to the center
of the tube bundle 24. Temperatures in the tube bundle 24 are
maintained at approximately 1,200 degrees Fahrenheit. The tube
bundle 24 carries the steam and is exposed to the high temperatures
of combustion, where the steam is superheated and maintained at a
pressure of approximately 3,200 psi. The hot gas exits through an
aperture located at the top center of the round roof of the
cylindrical combustion chamber. The centrifugal motion of the
combustion gases causes the heavier, unburned particles suspended
in the gases to accumulate on the outer wall of the combustion
chamber where they are incinerated, contributing to a cleaner
exhaust. This cyclonic circulation of combustion gases within the
combustion chamber creates higher efficiency in the engine.
Specifically, multiple passes of the coil of tubes 24 allows for
promoting greater heat saturation relative to the amount of fuel
expended. Moreover, the shape of the circularly wound bundle of
tubes permits greater lengths of tube to be enclosed within a
combustion chamber of limited dimensions than within that of a
conventional boiler. Furthermore, by dividing each cylinder's steam
supply line into two or more lines at entry to the combustion
chamber (i.e. in the tube bundle), a greater tube surface area is
exposed to the combustion gases, promoting greater heat transfer so
that the fluid can be heated to higher temperatures and pressures
which further improves the efficiency of the engine.
[0027] As the water exits the single line 21 of each individual
cylinder's pre-heating coil on its way to the combustion chamber,
it branches into the two or more lines 28 per cylinder forming part
of the tube bundle which consists of a coiled bundle 24 of all
these branched lines 28 for all cylinders, as described above.
These multiple lines 28 are identical in cross sectional area and
length. The splitter valve 26, located at the juncture of the
single line 21 to the multiple lines 28 (see FIG. 3), equalizes the
flow between the branch lines (see FIGS. 3, 15 and 6). The splitter
valve includes a main body 100 with an inlet 102 for connection to
the single feeder line 21 and a plurality of outlets 104 for
connection to each of the branch lines 28. A juncture 29 within the
splitter valve 26 minimizes turbulence by forming not a right angle
`T` intersection, but a `Y` intersection with a narrow apex 106.
Flow control valves or restrictors include ball check valves 27
between the juncture 29 and outlets 104 that allow unimpeded flow
of fluid towards the steam generator 20 through each of the branch
lines 28. The ball check valves 27 prevent back-flow into the
feeder line 21. Instead, any incremental over-pressure in one line
is caused to `bleed` back to an over pressure valve (pressure
regulator) 46 to prevent over-pressuring the system.
[0028] While the present invention has been shown and described in
accordance with a preferred and practical embodiment thereof, it is
recognized that departures from the instant disclosure are
contemplated within the spirit and scope of the present
invention.
* * * * *