System for heating and utilizing fluids

Disclosed are methods and apparatus for the controlled heating and utilization of fluids by the use of vapor generators of the kind in which a flowing fuel/air mixture is combusted for heating a stream of feedwater to produce a stream of steam and non-condensibles, preferably at low pressure. The hot stream is then heat exchanged with a stream of the fluid desired to be heated and utilized, to heat it to the level desired for use, including partly or completely vaporizing it, if the use so requires. The fluid may be divided into two or more streams during the heat exchange, with different amounts of heat delivered into each stream. Preferably, the heat exchange is so conducted as to condense the steam from the stream of steam and non-condensibles, and the condensate so formed is selectively recycled to the vapor generator as feedwater. Also, disclosed are means for incorporating a feedback control network including remotely actuatable valves, temperature sensors and related feedback devices for utilizing the steam of heated fluid for commercial heating of petroleum reservoirs and pipelines as well as comfort heating of living spaces.

BACKGROUND OF THE INVENTION 
The present invention relates to hot water supply systems and, more 
particularly, to a versatile hot water supply system incorporating a vapor 
generator and feedback control means. 
The prior art generally recognizes boilers as the traditional means for 
supplying heat energy in many applications despite the fact that they may 
not be easily matchable to the temperature, pressure, and flow 
requirements of a particular application. One difficulty in this regard 
flows from the fact that in a boiler these parameters are not independent, 
and changes in heat throughput at constant flow, for example, are 
accompanied by changes in temperature, pressure, or both. In addition, 
conventional boilers are expensive and complex, and require extensive 
maintenance. In most instances the boiler feedwater requires chemical 
treatment to retard corrosive wear of the boiler. 
Hot water systems of conventional design generally incorporate a feedwater 
boiler where large amounts of cold water are stored and heated to a 
selected temperature which depends upon demand requirements. Applications 
include industrial hot water feed lines, schools and office buildings and 
commercial hot water markets such as car washes and airports. Water demand 
generally fluctuates in those instances and much energy can be lost from 
heating large boilers during time of inactivity. Commercial hot water 
markets may also include construction sites in locations often not 
accessible to utility lines. This presents the obvious problem of how to 
heat the water. 
Various prior art embodiments have addressed the need for versatile hot 
water supply systems which meet the needs of intermediate flow demands and 
remote utilization. Certain prior art systems have incorporated "in-line", 
electrical heating elements which directly engage the high pressure water 
flow along a select flow path for heating the water to a select 
temperature as it passes through the heater. Problems of cost, fuel energy 
conservation and limited demand capacity have been found to be prevalent 
in such systems. 
Commercial hot water systems must overcome numerous obstacles, yet the 
potential applications are plentiful. High pressure flooding of hot water 
in petroleum reservoirs is a proven technique. Equally feasible, both 
economically and logistically, is vaporization of LPG or propane for 
combustion. Similarly, line heating of natural gas and/or heavy oil 
pipelines to promote flow or to avoid condensation therein is a present 
need. Such commercial/industrial applications which are remotely disposed 
from power utility systems present a myriad of technological problems for 
maximally efficient hot water systems. Concrete batching plants, for 
example, are generally used in areas not having hot water; much less 
energy supply lines. Such applications include concrete paving of remote 
areas and/or the building of concrete structures. Hot water boilers and/or 
other prior art hot water heating elements are of extremely limited use in 
such markets. While combustion fuel is, or may be plentiful, means for 
safely and efficiently utilizing combustible fuel to meet varying hot 
water supply demands is severely limited by prior art designs. 
One difficulty encountered in combustion fuel hot water supply units of the 
prior art is the high carbon monoxide content in the end product. This 
difficulty is particularly prevalent in prior art fuel vaporizers. Such 
noxious vapor content is objectionable around human occupation; a 
generally occurring condition where hot water is needed. High carbon 
monoxide production is traceable to incomplete combustion, in the main, 
which is in turn traceable, in part, to difficulties in maintaining stable 
flames in most prior art vaporizing units. Excessive quenching of flames 
through direct radiative and convective contact between the flame and the 
feedwater is often the cause. The advantages that vapor generators might 
have in hot water supply systems have been overlooked in light of these 
problems and in view of the low pressure steam produced. To be effective, 
low pressure steam must be automatically convertible to high pressure hot 
water upon demand. Prior art boiler systems have not shown such 
capabilities and these hot water supply problems still exist. For this 
reason vapor generators have been developed for meeting such commercial 
and technological needs. 
Vapor generators of the kind shown in U.S. Pat. No. 4,211,071 and in my 
copending U.S. patent application Ser. Nos. 37,029 filed May 8, 1979; 
261,702 filed May 8, 1981; and 261,703 filed May 8, 1981, represent 
alternate means for supplying energy. The generators therein set forth 
material advantages over conventional boilers in the way of equipment 
simplification and reduced maintenance requirements. However, the product 
stream from a vapor generator contains a relatively high proportion of 
non-condensibles, which is undesirable in many applications. In the case 
of older forms of vapor generators, the non-condensibles include 
pollutants such as carbon monoxide and unburned hydrocarbons. In addition, 
when a high pressure stream is required, capital and operating costs for 
the air compressor stage of a vapor generator are high. It has also been 
observed that some energy consuming applications require a liquid product 
stream which is at a fairly high temperature and a very high pressure. Hot 
water flooding systems for recovering oil from reservoirs are one example. 
Other examples include the aforementioned heating of natural gas and 
petroleum pipelines. 
The method and apparatus of the present invention address such hot water 
supply needs and overcome the problems of the prior art by providing a low 
pressure, vapor generator in which a demand sensitive product stream 
substantially free of carbon monoxide and other deleterious end use gases 
is produced. The vapor generator of the present invention may also be used 
in remote areas to produce a watersteam product at a sufficiently high 
heat energy state to convert large cold water supplies relatively quickly 
into a hot water at either low or high pressure. 
SUMMARY OF THE INVENTION 
The present invention relates to a hot water supply system incorporating a 
low pressure vapor generator for providing either low pressure or high 
pressure hot water in a demand-sensitive configuration. More particularly, 
one aspect of the present invention relates to a hot water supply system 
utilizing a combustion of fuel and air and the mixture of water, steam and 
non-combustibles to provide resultant hot water at a select temperature. 
The system of the present invention comprises a vapor generator of the type 
having a chamber for the receipt and combustion of a fuel-air mixture. 
Means are provided for supplying feedwater to the chamber for the 
conversion of feedwater, fuel and air to steam and non-condensibles 
therein. A low pressure stream of steam and non-condensibles is generated 
by combusting a stream of mixed fuel and air and mixing the products of 
combustionn therefrom with a stream of feedwater, and the exchange of heat 
between that product stream and one or more streams of the fluid of 
interest to bring it (or them) to the particular temperature, pressure, 
and flow conditions required by, or desirable for, the use to which the 
fluid is put. To maximize efficiency, it is preferred that the heat 
exchange be so conducted that the steam is condensed from the product 
stream. It is also preferred that the condensate be separated from the 
non-condensibles and selectively recycled as a feedwater to the generator 
stage. Means may also be provided for sensing the temperature of the 
resultant hot and heated waters and producing output signals in response 
thereto. Control means are provided for detecting the output of the 
sensing means and controlling the supply water delivery means for 
regulating the flow of the supply water and, correspondingly, the 
temperature of the resultant hot water. 
When the fluid of interest is to be brought to a high pressure for use, 
whether vaporized in the heat exchange step or not, it may be pressurized 
by being pumped upon as a cool liquid upstream of the heat exchange step. 
Such pressurization of fluid of interest need not be accompanied by a 
parallel increase in the pressure of the stream of steam and 
non-condensibles. As a consequence of these features of the invention, a 
highly pressurized fluid of interest may be produced with relatively low 
costs (both capital and operating) for pumps and blowers. The pressurizing 
pump, since it is working on a cool liquid, is relatively small and 
trouble-free, as compared to a pump working on a hot liquid, or a vapor. 
The air blower for the combustion system is also relatively small and low 
in operating cost since the steam and non-condensibles side of the system 
is operated at low pressure, notwithstanding the high pressure of the 
fluid of interest output. 
As was mentioned above, it is preferred that the exchange of heat result in 
condensation of the steam in the product stream of the vaporizer. Such an 
operating condition tends to maximize efficiency by utilizing the heat of 
vaporization stored in the product stream as well as its sensible heat in 
both the vapor and liquid stages. The condensate is a very pure warm water 
which is quite suitable as a partial or total source of feedwater for the 
vapor generator, thus further enhancing efficiency. Condensate which is 
not so used may be employed as an auxiliary source of warm water for 
general utility purposes. 
In accordance with another aspect of the invention, an improved vapor 
generator is provided in conjunction with a water storage unit having 
temperature and high and low water level sensing units. Data from the 
sensing units is inputted into the control unit to activate the cold water 
feed into the heat exchanger. The storage tank water may also be used at 
high or low pressure by the incorporation of an additional pumping unit. 
In addition, the temperature of the holding tank water may be controlled 
by the addition of high heat, steam-water flow from the generator. This 
aspect of the invention facilitates high heat storage with no high 
pressure considerations. Moreover, chemical additives may be incorporated 
in the storage tank pumping unit at various stages and/or temperatures for 
select applications in industry, commercial hot water markets and/or 
petroleum pipeline systems.

DESCRIPTION OF THE PREFERRED EMBODIMENTS 
Attention is directed first to FIG. 1, where a system of the invention is 
designated generally as 10, and where it is shown set up to supply hot 
high pressure water for injection into an oil well 11. The system of FIG. 
1 includes a vapor generator 12, a heat exchanger 13, a separator 14, and 
an injection water supply tank 15, together with lines connecting these 
elements in accordance with the invention, and with pumps and valves at 
selected locations in side lines. 
As is explained in more detail in my above-mentioned U.S. Pat. No. 
4,211,071, generator 12 produces a product stream containing steam and hot 
non-condensibles primarily nitrogen and carbon dioxide by the combustion 
within the generator of fuel with air in the presence of feedwater. Fuel 
is introduced through line 16, combustion air through blower 17 and lines 
18, 19, and feedwater through line 20. The product stream leaves the 
generator 12 through generator output line 21, which delivers it to the 
shell side of heat exchanger 13. Typically, the product stream is at 
relatively low pressure, such as 5 psig (351.5 grams per sq. centimeter 
gauge), and is fairly warm, such as 149.degree. C. 
In heat exchanger 13, the product stream gives up heat to the fluid flowing 
through the tube side of the exchanger. It is preferred that the pressure 
and flow conditions be such that the steam in the product stream be 
condensed in the course of its traverse of the shell side of the 
exchanger. Under preferred conditions, then, the stream leaving exchanger 
13 through exchanger output line 22 is a mixture of warm liquid water and 
non-condensibles. 
Exchanger output line 22 delivers this mixture to separator 14 where the 
non-condensibles and the warm water separate, with the non-condensibles 
leaving the separator at the top through exhaust line 23. The separated 
water is pumped from the separator through separator output line 24, by 
pump 25 to leave the system through valves 26 and 27, or to be recycled 
for use as generator feedwater through recycle line 28, which is connected 
between lines 25 and 20. 
Injection water is introduced into tank 15 through line 29. In many cases 
it will be preferred that the injection water be "connate water", that is, 
water originally derived from the formation being treated and thus having 
the same ionic content as formation water. Connate water is thus in 
equilibrium with the minerals of the formation and when returned to 
contact with them does not cause swelling or other untoward effects. The 
injection water may also be artificially compounded connate water, or, in 
the case of formations which are not sensitive to the ionic content of the 
injected water, from surface water. In the latter two instances, some of 
the water may comprise condensate from line 25, which has the advantage 
that its heat is delivered to the formation being treated. 
Injection water is pumped from tank 15 to the tube side of exchanger 13 
through line 30 by pump 31, which develops the pressure desired for 
delivery into the formation. In its passage through exchanger 13, the 
injection water picks up heat and temperature from the vapor generator 
product stream. Various additives may be added through line 33. It should 
be noted that pump 31 works on the injection water while it is cool, which 
simplifies the pump requirements as compared to a pump working on hot 
water. Also, the product stream of the vapor generator is at a low 
pressure, while the injection water is injected into the well at high 
pressure. Furthermore, pump 31 for pressurizing liquid is a smaller item 
of capital expense than would be a compressor 17 capable of bringing an 
equivalent quantity of combustion air to the same pressure. 
FIG. 1 can be taken to illustrate another embodiment of the invention if 
one regards tank 15 as charged with liquid carbon dioxide rather than 
water. In such an embodiment the operation is substantially the same as 
described above, except that a change of state takes place in the carbon 
dioxide stream flowing through the tube side of the heat exchanger, as it 
extracts heat from the vapor generator product stream flowing on the shell 
side. Carbon dioxide, under pressure, and vaporized, is delivered to well 
11 through line 31. 
FIG. 2A shows another embodiment of the invention. Parts which are 
essentially the same as those shown in FIG. 1 are given the same reference 
character; those which are modified are given the same number with the 
addition of the letter "A". In the embodiment of FIG. 2A, tank 15 is 
charged with liquid propane or another liquified natural gas product, 
which is to be vaporized prior to delivery to burner 35 in kiln 37. The 
energy required for vaporization is generated in vapor generator 12 and 
heat exchanged with the propane in heat exchanger 13A. The vaporized 
propane leaves the exchanger through line 31A and is delivered to burner 
35. 
Heat exchanger 13A differs from heat exchanger 13 of FIG. 1 in that its 
tube side is divided, with some of the tubes issuing into line 31A and the 
remainder issuing into line 36. While such an arrangement would have 
limited application when the tube-side working fluid is propane, it is an 
attractive feature of the invention, because it makes it possible to 
divide the tube-side working fluid into two or more streams to which 
differing amounts of heat are added from the shell side product stream 
from the vapor generator, thus improving flexibility and efficiency. 
In FIGS. 2B and 3 there is shown an alternate embployment of the high 
temperature stream produced in line 31A, which in this case is presumed to 
be steam. By being bound in an insulation package 40 closely adjacent 
heavy oil line, the steam line 31A delivers heat to the flowing oil in 
line 41 to reduce its viscosity so it will be pumpable, and at lower cost. 
In FIG. 2C, still another alternate employment of the high temperature 
stream produced in line 31A, in this case again assumed to be steam. Steam 
line 31A traces a gas pipeline 42 to prevent natural gasoline fractions 
contained in the gas from condensing out of the flowing gas stream. 
Referring next to FIG. 4, there is shown a diagrammatic view of an 
alternative embodiment of a method and apparatus for hot water production 
constructed in accordance with the principles of the present invention. A 
hot water supply system 10, diagrammatically shown, includes a low 
pressure vapor generator 12, a heat exchanger 13, a separator 14, and an 
injection water supply tank 15, together with lines connecting these 
elements in accordance with the invention, and with pumps and valves at 
selected locations in said lines. 
The system of FIG. 4 also includes a programmable temperature-flow control 
unit 120, feedwater supply means, associated flow conduit, and sensor and 
flow control means. The control unit 120 is coupled to upstream and 
downstream temperature sensors 116 and 117, respectively, which delay data 
to unit 120 for temperature-sensing and responsive actuation within system 
10. Control unit 120 is programmed to responsively actuate generator 12 
and the flow valves governing the inflow and downstream heat exchanger 
operation to produce a heated fluid body 99 and 199 at a selected 
temperature and flow. In this manner, specific hot water demands of time, 
temperature, volume and pressure, can be efficiently met on an immediate 
use or long-term storage basis. Moreover, the demands for the desired hot 
water can be met at high or low pressures, with or without chemical 
additives, and with apparatus lending itself to set-up and use in remote 
areas where utility services may not be available. 
Addressing now the vapor generator 12 of FIG. 4, there is shown an 
alternative method of heating the feedwater without exposing it directly 
to the combustion occurring therein. Main combustion chamber 113 is 
preferably an upright closed-ended elongated cylinder adapted to enclose 
the bulk of the flame generated in accordance with the invention. To the 
bottom of chamber 113 is connected a product exit line or conduit 115. 
Chamber 113 has a cylindrical outer wall 117, and closed ends 119, 121. 
Provision is made for the delivery of feedwater to the area around the 
main combustion chamber. These provisions include an upper inlet water 
line 123, and internal cylindrical wall or tube 125. Tube 125 is attached 
to top end 119 and terminates a selected relatively small distance short 
of bottom end 121. An annular space 127 is thus established between walls 
117 and 125 extending over substantially the full height of chamber 113 
and the combustion occurring therein. 
In operation of the generator 12 of this particular embodiment, feedwater 
is delivered into annular space 127 through inlet line 123. The water is 
heated as it flows downwardly through the annular space or jacket 127 and 
under tube 125. During the first part of the downward travel, the water 
absorbs heat conductively from the shielded portion of the flame. During 
the final part of its downward flow in jacket 127, the feedwater is 
substantially vaporized therein to form steam that becomes part of the 
product stream leaving jacket 127 and chamber 113 via conduit 115. 
The fuel and air delivery system of the invention is designated generally 
as 40. It includes an air compressor 41, having an air filter (not shown). 
Various types of compressors having suitable output pressures and delivery 
rates may be employed. The compressed air issuing from compressor 41 
enters conduit 43. 
The compressed air stream in conduit 43 is divided into two streams bearing 
a selected ratio (volumetric or mass) to each other. The division is 
accomplished by providing mixing conduit 44, which is an extension of air 
conduit 43, and branch or auxiliary air conduit 45. Conduits 44 and 45 are 
each connected to the precombustion chamber 50. Preferably, the volume of 
flow through auxiliary air conduit 45 amounts to about 8 to 10 percent of 
the air flow through mixing conduit 44. 
Immediately downstream in mixing conduit 44 there is provided a fuel inlet 
48. Flow in conduit 44 is quite turbulent and it is desirable to introduce 
the fuel at this point to initiate thorough and intimate mixing of the 
fuel and air. Furthermore, it is preferred that mixing conduit 44 be 
fairly long in order to provide a full opportunity for thorough mixing of 
the air and fuel stream before it reaches the precombustion chamber. 
Mixing is also enhanced by the directional change in conduit 44 at bend or 
elbow 49. The diameter of mixing conduit 44 is selected in view of the 
desired flow rate so that the lineal velocity of the mixture flowing 
therethrough is substantially equal to or slightly greater than the flame 
propagation speed, so that the flame established and maintained in the 
precombustion chamber cannot migrate back up into conduit 44 or its bend 
49. For example, with a designed fuel flow of 0.48 cubic meters per 
minute, mixed with a stoichiometric quantity of air, a nominal conduit 
diameter of about 5.08 centimeters is satisfactory. 
The precombustion chamber of the vapor generator of the present invention 
is designated generally as 50. It includes a cylindrical housing 51, 
somewhat larger in diameter than opening 52 in the upper end 119 of 
chamber 13. The upper end of housing 51 is closed by plate 54. A frame 
enclosing skirt or shield 59 depends downwardly from plate 54, terminating 
short of opening 52 so that a circular slot 55 is defined between the 
outer edge of the skirt and the inner edge of the flange. A cylindrical 
annular space 56 is defined between skirt 59 and housing 51. Conduit 44 is 
attached to the top of the precombustion chamber to deliver a fuel-air 
mixture into the space within shield 59. Conduit 45 is attached to the 
side of the precombustion chamber to deliver auxiliary air into the 
annular space 56. 
A pilot burner assembly (not shown) is mounted on precombustion chamber 50 
so that its mouth opens preferably into the chamber near the junction of 
conduit 44 and plate 54, and within skirt 59. In the vaporizer 113, a 
second flame enclosing shield or skirt 58 is mounted to top end 119 to 
depend downwardly. The pilot flame thus formed in the pilot burner issues 
into the precombustion chamber to initiate combustion. 
As can be seen from the foregoing, three primary input streams are involved 
in the generator 12: fuel gas; combustion supporting gas (preferably air 
from an electrically-driven blower or compressor); and water. There are 
thus three primary points of control which are coordinated by control unit 
120: fuel, air and water. Such control means are setforth in my copending 
application Ser. No. 261,703 described above. Fuel metering valve 61 and 
feedwater flow valve 62 are provided, each remotely actuatable by control 
unit 120. During start-up, fuel gas and sparking current are supplied to 
the pilot burner. During operation, a series of monitoring devices monitor 
various operating conditions and turn the generator 12 off, or prevent its 
start-up if it is already off, when a condition departs from a desired 
value or range of values. These monitors include thermostats, water level 
sensors and fuel pressure switches which provide generator operations with 
low level carbon monoxide production. 
Still referring to FIG. 4, the particular embodiment of the present 
invention shown and described herein produces a product stream containing 
steam and hot non-condensibles, primarily nitrogen and carbon dioxide, by 
the combustion within the generator 12 of fuel with air. Fuel is 
introduced as above described and combusted with air. Feedwater is 
introduced through line 123 and mixes with the products of combustion. The 
resulting product stream leaves the generator 12 through generator output 
line 115, which delivers it to the shell side of heat exchanger 13 as 
described above. The product stream is, again, at relatively low pressure, 
such as 5 psig (351.5 grams per sq. centimeter gauge), and is fairly warm, 
such as 149.degree. C. 
Once sufficient fuel and supply water is made available, the system of FIG. 
4 can produce hot water of selectable temperature and programmable volume 
and do so within a wide range of elective times frames. The control of 
these production parameters is made possible by coordination of generator 
12 operation, fluid temperatures and regulated flow rates from the control 
unit 120. Referring again to FIG. 4, the volume of water from line 123 may 
be controlled by valve 62 actuatable by control unit 120. The valves 62 
and 61 may be of the conventional solenoid actuated variety. To coordinate 
such efforts, the control unit 120 preferably includes a conventional 
programmable computer capable of being programmed with the desired 
temperature, volume and time frame in which the final product is needed. 
The system 10 startup is thus the first phase of operation. The unit 120 
also coordinates a second phase of continued operation and therein must 
sense variable input data, analyze the data relative to the production 
parameters and make responsive changes to the various control areas of the 
system 10. 
In Phase I operation, the desired temperature, volume and demand time for 
hot water are programmed into the control unit 120 as production 
parameters. Ambient temperature sensors 16a and 118 communicate to the 
control unit 120 the initial working temperatures of the raw feedwater and 
the reservoir supply water to be heated, respectively. This data forms a 
basis for a determination of a projected initial mixture ratio of 
feedwater and supply water. The data of desired discharge volume to the 
heat exchanger 13 is then determinative of the projected flow rates of the 
respective constituents. The control unit 120, having received the above 
data and determinative operational parameters, then activates one of a 
series of preprogrammed start-up sequences of the generator 12 to cause it 
to operate at the most optimal fuel-air-water ratio for the particular 
parameters involved. 
It may thus be seen that the control unit 120 preferably includes a 
plurality of preprogrammed, Phase I start-up sequences for the various 
categories of production parameters through heat exchanger 13. These 
sequences are designed for maximizing operational efficiency through the 
Phase I start-up at particular demand levels. For example, if 3785.3 
liters (V1) of water at 38.degree. C. (T1) were needed over a 3-hour time 
frame, (A.sub.1) the generator 12 could be run at a much lower combustion 
level (L.sub.1) than the same remaining production parameters needed over 
a 1-hour time period conserving fuel and maximizing the efficiency of 
operation. The controlled combustion level (L.sub.2) could likewise be 
maintained at the (L.sub.1) level even if the temperature (T.sub.2) were 
raised to 82.degree. C., if the demand time frame (A.sub.2) was expanded 
sufficiently; a combustion level (L.sub.3), if a substantially higher 
volume (V.sub.3) of heated water was needed. The algorithm for solving 
such operational requirements is determined by conventional mathematical, 
programming methods and fed into control unit 14. 
Once the system 10 passes through the Phase I start-up and becomes operable 
at the flow rates and settings which were projected by control unit 120 to 
be optimal for a particular demand, the actual fluid temperatures become 
controlling which constitutes the second phase of operation. The vapor 
generator 12 and heat exchanger 13 need a predefined period to reach a 
stabilized output. Following this stabilization period, a Phase II program 
in control unit 120 takes over. This program is likewise determinable by 
conventional mathematical programming techniques and includes receiving 
temperature data from sensors 16a, 116, 118, 119A, and 178 for analyzing 
it. 
Sensor 116 detects the temperature of the upstream fluid product of 
generator 12, described above. The heat content of this high temperature 
fluid, referred to as fluid product 75 comprising evaporated feedwater and 
non-condensibles, is readily calculable and the control unit 120 performs 
a comparison with the heat exchanger output and associated sensors. The 
heat content of the fluid product 75 engaging the heat sensor 16 is 
readily calculable from the volume of input feedwater and the volume of 
fuel and air. Once these factors are fed into the control unit 120, the 
heat content (Q.sub.1) of the fluid product 75 detected by temperature 
sensor 116 is determinable. An optional heat content (Q) is programmed for 
desired output from the exchanger 13. The actual output temperature from 
sensor 119 and heat content (Q.sub.2) is then compared to the programmed 
value of (Q) and sensor 119A and adjustments in the three primary points 
of control of the generator 12 are effected by unit 120. 
The heat content of the fluid 75 may also be used to vary the volume of 
flow, of "cold", unheated supply water from cold water valve 62 and warm 
supply water from valve 64. The temperature of the raw feedwater does not 
have to be known although sensor 16a is so shown as a source of usable 
input data. Temperature sensors 118 and 119A can be used to measure 
downstream temperatures, and heat exchanger operation, and relay 
information to control unit 120. If the temperature at 119A is too low, 
either higher heat content from the generator 12 is needed or less "cold" 
water through valve 62. This decision is implemented through control unit 
120 which is programmed to adjust the respective flow rates toward the 
optimal efficiency levels discussed for Phase II operation. In this 
manner, the system 10 is not limited in operational scope by any one 
factor. Both "cold" feedwater supply volume, heat exchanger operation, and 
vapor generator heat output (Q) may be adjusted according to changes in 
operation conditions. Each can be automatically programmed in the present 
invention to balance parameter variation deficiencies in other areas of 
the system to produce a heated fluid body 199 from exchanger 13, 
discharging at the most optimal rate for a desired temperature, volume and 
pressure. 
The output rate of the discharging fluid body 199 produced in system 10 may 
be seen to be directly regulated by pump 31 in conjunction with the 
aforesaid operational parameters. An input data terminal 80 is 
illustratively shown in FIG. 1 and allows above described programming of 
control unit 120. The optimal temperature, volume, pressure and rate of 
flow for the resultant fluid body 199 discharged from heat exchanger 13 is 
is thus regulated by the control unit 120 in conjunction with the 
scheduled programming and actual parameters encountered. The fluid body 99 
within the line 22 generally comprises low pressure, evaporated and 
condensed feedwater and the non-condensibles produced by the generator 12. 
In certain applications, this active fluid mixture may be directly 
usuable. Such use depends upon the "upstream capacity" which refers to the 
operation level of the generator 12 and volume of water available. The 
present invention also provides the capacity of a high volume, high 
pressure, hot water discharge through the incorporation of a downstream 
storage tank 100. This particular embodiment permits the relatively low 
pressure, fluid discharge from heat exchanger 13 to be collected for use 
in a myriad of high or low pressure applications. The storage tank 100 
includes an ouput pumping network 102 and input settling system 104. The 
pumping network 102 comprises a discharge pipe 106 in combination with a 
regulating valve 108. A pump 112 then creates the requisite discharge 
pressure and channels the discharge water through conduit 114 to its end 
use or back through return line 115A through valve 64 to generator 12. 
Referring particularly now to the right hand portion of FIG. 4 comprising 
the tank 100, hot water 150 may be maintained at a level 152 beneath an 
output port 154 in the side wall 156 of the tank. The port 154 is in 
direct flow communication with heat exchanger 13 and may serve as a 
discharge port for said exchanger. The configuration of tank 100 is 
preferably such that the port 154 discharges the active fluid body 99 in a 
tangential fashion. A tangential entry creates a vortexual swirl of the 
heated supply water-evaporated feedwater mixture. In the vortexual swirl, 
the non-condensibles are allowed to separate out from the mixture to leave 
usable hot water 150. The non-condensibles and unmixed steam of the 
discharging fluid body 99 rise upwardly within the tank 100. A demisting 
screen 160 is provided to collect and condense rising steam and return it 
to the settled, hot water 150 therebelow. A vent 162 then permits escape 
of the non-condensibles. 
In operation, the tank 100 is coupled to a water level sensor package 176 
comprising an upper and lower level detector 172 and 174, respectively. 
Water level signals from detectors 172 and 174 are received by control 
unit 120 for coordination of the production of fluid body 99 and heat 
exchanger output simultaneously. Temperature sensor 178 may be provided in 
tank 100 to monitor the temperature of the stored water 150. This 
temperature may be received and relayed by sensor package 176 to control 
unit 120. In this manner, discharge fluid 99 with an increased heat 
content can be provided to heat the stored water 150 as necessary to 
maintain its usefulness over prolonged storage periods. 
It is thus believed that the operation and construction of the present 
invention will be apparent from the foregoing description. While the 
method and apparatus shown and described has been characterized as being 
preferred it will be obvious that various changes and modifications may be 
made therein without departing from the spirit and scope of the invention 
as defined in the following claims.