U.S. patent number 3,736,745 [Application Number 05/151,331] was granted by the patent office on 1973-06-05 for supercritical thermal power system using combustion gases for working fluid.
This patent grant is currently assigned to The United States of America as represented by the Secretary of the Navy. Invention is credited to Horace E. Karig.
United States Patent |
3,736,745 |
Karig |
June 5, 1973 |
SUPERCRITICAL THERMAL POWER SYSTEM USING COMBUSTION GASES FOR
WORKING FLUID
Abstract
A supercritical thermal power system including components
conventionally luded in a Rankine cycle, uses a portion its own
combustion gases as its only working fluid. The system recirculates
all the combustion gases, cools them, and purges the excess amounts
from the system. The cooled remainder portion is reheated to
conserve energy and mixed with oxygen and fuel in the combustion
chamber to lower the temperature of the burning gases to pass
cooler combustion gases to a turbine for minimizing failure
otherwise due to excessive heat in the system. By using a portion
of the system's own combustion gases as the only working fluid, the
system's overall efficiency is significantly increased over
contempory systems.
Inventors: |
Karig; Horace E. (La Jolla,
CA) |
Assignee: |
The United States of America as
represented by the Secretary of the Navy (Washington,
DC)
|
Family
ID: |
22538275 |
Appl.
No.: |
05/151,331 |
Filed: |
June 9, 1971 |
Current U.S.
Class: |
60/772; 60/39.52;
60/597; 60/279 |
Current CPC
Class: |
F02C
3/34 (20130101); F01K 25/005 (20130101); Y02E
20/32 (20130101); Y02E 20/34 (20130101); Y02E
20/344 (20130101); Y02E 20/326 (20130101) |
Current International
Class: |
F02C
3/00 (20060101); F01K 25/00 (20060101); F02C
3/34 (20060101); F02n 025/06 () |
Field of
Search: |
;60/36,279,278,39.52,39.02 ;123/119A |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Smith; Al Lawrence
Assistant Examiner: Olsen; Warren
Claims
What is claimed is:
1. A supercritical thermal power system producing and using a
portion of its composite combustion gas as its only working fluid
comprising:
a regenerator having a first duct and a second duct receiving said
combustion gas in said first duct at a first pressure and a first
temperature for venting said combustion gas at a reduced second
pressure and second temperature while providing an energy
conversion said first pressure and said second pressure being in
excess of 1100 PSIA;
a condenser coupled to said first duct for lowering the temperature
of said combustion gas below a critical temperature for effecting
an immediate change of state of the carbon dioxide in said
combustion gas to a liquid form;
means connected to the said condenser for purging an excess
quantity of said liquid form of said carbon dioxide from said
system while retaining a remainder of said liquid form in said
system;
means joining said condenser to said second duct for increasing the
pressure and temperature of the remainder of said liquid form of
said carbon dioxide to a value substantially corresponding to said
first pressure and to a temperature level above the critical
temperature of said liquid form of said carbon dioxide to change
the state of said remainder to a gaseous fluid at the output of
said second duct;
a source of oxygen;
a source of distillate fuel; and
a combustion chamber connected to the oxygen source, the distillate
fuel source, and the output of said second duct, upon feeding said
gaseous fluid to said combustion chamber during combustion of said
oxygen and said distillate fuel, resultant combustion gases are
cooled to a magnitude which prevents heat damage to said system and
which ensures higher system efficiency.
2. A system according to claim 1 in which said regenerater passes
said combustion gas at said second pressure and said second
temperature to effect a partial reduction of temperature of said
combustion gas and said condenser is serially connected and water
cooled to further reduce the temperature of said combustion gas
below the critical temperature of carbon dioxide ensuring its
change of state to said liquid form.
3. A system according to claim 2 in which said increasing means
includes a pump joined to said second duct, said remainder quantity
is changed in state to said gaseous fluid by the heat of said
combustion gas at said second pressure and said second temperature,
thereby ensuring the raising of the temperature of said gaseous
fluid to a level above its critical temperature.
4. A system according to claim 3 in which the purging means
includes a water separator having a water feeder line connected to
said distillate fuel source for replacing burned fuel with
condensed water vapor and said water cooled condenser is provided
with a CO.sub.2 feeder line connected to said oxygen source for
replacing burned oxygen with condensed CO.sub.2 rendering said
system completely closed with in-system storage of combustion
by-products.
5. A method of raising the overall system efficiency of a
supercritical thermal power system by using its composite
combustion gas as its working fluid comprising:
extracting work from said combustion gas in an energy
converter;
lowering the temperature of said combustion gas below the critical
temperature of carbon dioxide;
condensing said carbon dioxide to a liquid form;
purging excess said liquid form of said carbon dioxide from said
system;
raising the temperature of said liquid form of said carbon dioxide
to a gaseous form;
mixing said gaseous form of said carbon dioxide in a combustion
chamber with a hot combustion gas created as oxygen and distillate
fuel burns in said combustion chamber said gaseous form being
cooler than said hot combustion gas to cool the mixed combustion
gas;
feeding the mixed combustion gas to said energy converter for
preventing heat damage to said energy converter and to raise said
overall system efficiency; and
maintaining said combustion gas at supercritical pressure levels
throughout said system to further raise said overall system
efficiency.
6. A method according to claim 5 further including:
storing said excess said liquid form of said carbon dioxide making
said system closed and self contained.
7. A system according to claim 1 in which a heat transfer occurring
as said combustion gas has its temperature reduced from said first
temperature to said second temperature raises the temperature of
the remainder of said liquid form of said combustion gas above the
critical temperature of said liquid form of said combustion gas to
ensure a change of state to said gaseous form.
8. A system according to claim 7 in which said first temperature is
in excess of 1400.degree. F, said first pressure is in excess of
1475 PSIA, said second temperature is in excess of 100.degree. F,
said second pressure is in excess of 1425 PSIA and said critical
temperature is substantially 87.degree. F.
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
A wide variety of thermal power systems operating generally within
a Carnot cycle have been developed throughout the years. One
notable example is the Walter engine which called for the direct
combustion of hydrogen peroxide and diesel oil in a combustion
chamber and feeding the combustion gases through a prime mover to
effect an energy conversion. A disadvantage of the Walter engine
resided in its having to tolerate the hot combustion gases being
directly fed into the prime mover. Since the gases by being so hot
tended to damage the prime mover, water was sprayed into the
combustion chamber to bring the combustion temperature within a
workable range; however, the heat required to evaporate the cooling
water seriously degraded the system's efficiency. In addition, the
Walter engine, an "open-cycle" system required that the exhaust
gases be pumped out of the system. This creates considerable design
difficulties, especially where the ambient pressure is high, as is
the case at great depths in the ocean. An alternate system approach
is to design a "closed-cycle" power system using a secondary
recirculating fluid for effecting a power transfer when it is
heated by combustion gases in a boiler-like chamber. An immediate
disadvantage of this approach is apparent since a relatively
inefficient heat transfer occurs as the gases heat the secondary
recirculating fluid to seriously lower this system's overall
efficiency. An attempt to raise the efficiency in a "closed-cycle"
system has been proposed by Ernest G. Feher in U.S. Pat. No.
3,237,403 issued Mar. 1, 1966 in his "Supercritical Cycle Heat
Engine." This heat engine used CO.sub.2 at supercritical
temperatures and pressures as the secondary recirculating fluid to
function as the working fluid in a modified Rankine cycle. The
advantages of employing carbon dioxide as the working fluid at its
supercritical temperature and pressure levels are disclosed and
thoroughly explained in the Feher Patent and this publication
provides a nearly complete background for a thorough understanding
of the present invention. However, with the Feher approach, a
serious loss of efficiency burdens the engine which is created at
the heat transfer interface between the heater element and the
recirculating CO.sub.2. The Feher engine does not directly use the
combustion gases to drive the turbine but rather relies on a
conventional heat exchange in a heater for system power. Here
again, direct employment of uncooled combustion gases as the
working fluid in a turbine has been avoided due to the combustion
gases high temperature which causes heat damage to the turbine.
SUMMARY OF THE INVENTION
The present invention is directed to providing a supercritical
thermal power system using its combustion gas as its only working
fluid and includes a turbine receiving the combustion gas to
provide an energy conversion. A regenerator and condenser receive
the combustion gas expelled from the turbine and condense the
excess amounts of water vapor and CO.sub.2 to either expel or to
store them. While passing through the regenerator in the opposite
direction, the residue of the carbon dioxide is raised above its
critical temperature and assumes the gaseous state. The gaseous
residue is fed to a combustion chamber where oxygen and a
distillate fuel are being burned to form more combustion gas. In
the chamber the gaseous residue is mixed with the burning oxygen
and fuel to cool the resultant combustion gas which is vented to
drive the turbine. Directly employing the combustion gases as the
working fluid results in a higher overall system efficiency and by
mixing the gaseous residue with the burning oxygen and fuel, the
temperature of the combustion gases is lowered to prevent heat
damage to the turbine.
A prime object of the invention is to provide a thermal power
system having a higher overall system efficiency.
Another object is to provide a thermal power system using its
combustion gases as its only working fluid.
Still another object is to provide a system using recirculating
combustion gases comprised mostly of CO.sub.2 at supercritical
temperatures as its working fluid.
Yet another object is to provide a closed thermal power system
designed to store its combustion by-products.
Still another object is to provide a closed thermal power system
having a high discharge pressure to overcome ambient pressures
found at extreme ocean depths.
A further object is to provide a thermal power system burning
low-cost hydrocarbon fuel and oxygen at low temperatures not
requiring elaborate heat exchangers or feed water injectors.
Still another object is to provide a thermal power system of small
size yet having a high overall efficiency.
These and other objects of the invention will become more readily
apparent from the ensuing description when taken with the
drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a schematic representation of one embodiment of the
invention.
FIG. 2 is a schematic representation of another embodiment of the
invention .
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring to the drawings, two representative thermal power systems
are depicted each embracing the heart of the present invention,
that being, using the combustion gas as its only working fluid to
effect an energy conversion. In both of these systems the specific
temperatures and pressures discussed in the specification and
appearing on the drawings are for purposes of demonstrating
specific embodiments. If different efficiencies are tolerable, then
variation from the identified temperatures and pressures is
permissible within the teachings of the invention.
A turbine 10, preferably a single stage turbine, is assembled to
allow a low gas expansion ratio and is capable of operating at high
efficiency over a wide operating range to convert heat energy to
rotary motion. The turbine receives combustion gases at 3000 PSIA
and 1600.degree. F., exacts an energy conversion, and vents or
exhausts them at 1500 PSIA and at 1445.degree. F. A mechanically
interconnected load 11 converts the turbine's rotary motion to
electrical power, or whatever other energy conversion desired, and
a mechanical linkage 11a extends to another system component, the
purpose of which will be elaborated on below.
Exhausted combustion gases are received by a regenerator 12 which
cools the exhausted gases to approximately 125.degree. F and vents
them to its "downstream" side. Within a cross duct 12a in the
regenerator the exhausted combustion gases are maintained above the
critical 87.degree. F. temperature of CO.sub.2 to retain the
CO.sub.2 portion of the combustion gases in its gaseous state.
However, within the cross duct, water vapor, formed as a by-product
of burning and diffused throughout the combustion gases, is
condensed and flows along with the other combustion gases at the
duct outlet.
The physical construction of the regenerator optionally assumes one
of many of a variety of different configurations. A typical
regenerator is no more than an elongate cylinder having a pair of
concentrically, coaxially disposed ducts the inner one 12a passing
the exhaust gases in one direction and the outer one 12b having a
cooler fluid traversing in the other direction, as will be
explained later, to cause the desired temperature drop in the
exhaust gases.
Following the regenerator, a coil 13a in a condenser 13 receives
the cooled combustion gases, now lowered to the 125.degree. F.
temperature at approximately 1450 PSIA pressure. A sufficient
quantity of sea water is pumped through another coil 13b in the
condenser to perform a direct conductional cooling of the
combustion gases bringing the carbon dioxide below its critical
temperature of 87.degree. F. Because CO.sub.2 pressurized to 1100
PSIA, or greater, undergoes a direct change of state from gaseous
form to liquid form, or vice versa, when brought to its critical
temperature of 87.degree. F., the carbon dioxide in the present
system, being under a pressure of approximately 1450 PSIA,
undergoes a direct transition to change from the gaseous state to
the liquid state. Such an immediate change in state takes place in
the condenser by the heat transfer occurring between the carbon
dioxide in condenser coil 13a and the sea water in condenser coil
13b.
Having liquid CO.sub.2 and liquid water in the system "downstream"
from coil 13a permits the purging of carbon monoxide or other
noncondenseable gases also created as by-products of the burning
process. A simple valve arrangement 14 allows purging and disposal
of these by-products to increase the system's overall efficiencies.
In addition, when the amounts of water vapor and carbon dioxide
created during burning are beyond the quantity needed for
maintaining a suitable level of working fluid this excess amount of
the liquid form of the combustion gas is vented at this point. For
more efficient operation, most of the water is purged to retain
carbon dioxide as the system's major working fluid.
With the remainder of the combustion gases, that portion not being
vented off at valve 14, still in the system, a pump 15 draws it in
at 1450 PSIA pressure at 68.degree. F. The pump increases the
remainder's pressure to 3050 PSIA and slightly raises its
temperature to 85.degree. F. Although the temperature of the
remaining gases, optionally, is raised above the critical
87.degree. F. temperature in the pump to convert it to the gaseous
state, system efficiency was enhanced by feeding it back through
regenerator 12 via the above mentioned longitudinal duct 12b.
The heat transfer between the combustion gases vented from the
turbine through longitudinal duct 12a and the remainder of
combustion gas passing through longitudinal duct 12b is mutually
beneficial to both fluids. The hot gases in duct 12a are cooled by
the liquid remainder in duct 12b to condense water vapor and to
lower their temperature. Simultaneously, the liquid remainder in
duct 12b is heated above and beyond its critical temperature to
change to the gaseous state and to raise the remainder's
temperature to approximately 1315.degree. F. at 3020 PSIA. Thusly,
the heated remainder has been appropriately preprocessed to be
recirculated and recycled back to a combustion chamber 16.
The combustion chamber is connected to receive oxygen and a
distillate fuel from a source of oxygen 17 and a source of fuel 18.
Suitable valving is provided to ensure that the proper volumes of
each are fed to the combustion chamber for complete burning.
Since the stoichiometric burning of diesel oil, for example, in
oxygen produces a burning temperature of approximately 6000.degree.
F., most combustion chambers are unable to contain such a high
temperature, with the exception of heavy, massive chambers made of
substantial volumes of high refractory materials. In the present
invention, to lower the internal temperature of the combustion
chamber, the remainder of the combustion gases of the previous
cycle are recycled back into the combustion chamber to mix with the
burning oxygen and fuel. Further protection of the chamber from
overheating is ensured by directing the flow of recycled gas to
line the chamber inner walls insulating them from the flames. The
temperature of combustion is significantly reduced by the recycled
remainder and the temperature of the burning combustion gases is
brought considerably below that temperature which causes damage to
the chamber and the following turbine. Since temperatures in excess
of 3000.degree. F. may cause heat damage to a stainless steel
coaxial boiler or a conventional turbine, bringing the gases ducted
to the turbine to a temperature of 1600.degree. F. at 3000 PSIA,
leaves an adequate margin of safety. Thus, by the mixing action of
the remainder of the combustion gases of the preceding cycle with
the burning oxygen and fuel, the overall thermal efficiency of this
system is measured to approach 42 percent, far above the
efficiencies reached by contemporary systems calling for the
injection of water coolants in the combustion chamber.
By prepressurizing the system with carbon dioxide at approximately
1450 PSIA and including a mechanical linkage 11a, shown in phantom
between load 11 and pump 15, the system is readied for immediate
operation.
A modification of the aforedescribed system is shown in FIG. 2
which, in addition to having the components already identified,
includes a water separator 19 connected on the "downstream" side of
longitudinal duct 12a. The water separator passes condensed water
at 1475 PSIA and 125.degree. F. to a water storage compartment
separated from the fuel oil in source 18 by a flexible wall 18a.
The pressurized condensed water acting on the flexible wall tends
to force the remaining volume of fuel oil into the combustion
chamber at a high flow rate. A metering pump 18b is desirably
included to precisely regulate the fuel flow to the combustion
chamber.
In a similar manner, a feeder line on the "downstream" side of pump
15 feeds excess liquified CO.sub.2 to a CO.sub.2 storage tank 20
and also to a bank of bottles representing oxygen source 17. As
oxygen is used and the bottles become empty, excess CO.sub.2 is
stored by merely opening an ingress valve 17a and shutting an
egress valve 17b. Here again, a metering pump 17c allowing the
selective change from one oxygen bottle to the other and for
regulating the bottle's flow rate is highly desirable to ensure
reliable system operation.
An advantage of storing the recovered products of combustion in,
for example, a submersible where precise bouyancy and trim control
are important, becomes apparent when it is noted that the
energy-transfer process imparts no gain or loss of weight making
weight or trim compensation unnecessary.
Obviously, many modifications and variations of the present
invention are possible in the light of the above teachings, and, it
is therefore understood that within the scope of the disclosed
inventive concept, the invention may be practiced otherwise than
specifically described.
* * * * *