Water induction system for internal combustion engines

A water induction system for internal combustion engines which consists of a metering device for metering controlled amounts of air and water, a control valve which is vacuum operated and connected to the metering device to allow a predetermined amount of air and water to be drawn into a heater wherein the air water mixture is vaporized and admixed with the fuel air mixture entering the intake manifold.

BACKGROUND OF THE INVENTION 
This invention relates to an air-water induction system for internal 
combustion engines. More particularly this invention relates to a system 
for admixing air and water and passing said air-water mixture in a 
vaporized condition into the air fuel mixture entering the intake 
manifold. 
It has long been known that the introduction of water, preferably in vapor 
form, into the air fuel mixture of an internal combustion engine possesses 
many advantages especially when the engine is accelerating. In other words 
when the throttle opening is increased the demand for water injection will 
be increased to meet maximum performance. 
Many of the advantages of using a water induction system have been set 
forth in patents such as U.S. Pat. No. 1,561,693; U.S. Pat. No. 1,686,470; 
U.S. Pat. No. 1,783,746; U.S. Pat. No. 2,112,972; U.S. Pat. No. 2,444,628; 
U.S. Pat. No. 3,141,447; U.S. Pat. No. 3,665,897 and especially U.S. Pat. 
No. 2,444,670. 
The advantages attributed to the introduction of water vapor into the air 
fuel mixture include more complete combustion of the fuel, less pollution, 
less carbon formation in the cylinder, the suppression of detonation, a 
reduction in internal temperatures of the cylinder heads, rings, valves 
and the like, the use of lower octane fuels and an increase in engine 
horsepower. 
However many disadvantages are also attendant to these prior art systems. 
Often the flow of water is not regulated resulting in too little or too 
much water in the fuel. In many cases the size of the water droplets fed 
into the engine are too large to be effectively intermixed with the fuel 
and evenly fed to the cylinders by the intake manifold. Of those patents 
which regulate the flow of water vapor by vacuum the rate of flow seems to 
be dicatated by the intake manifold vacuum. However this is not a true 
measure of the engine's need for water supply. When the engine is 
accelerating or the throttle is wide open the intake manifold vacuum may 
be low allowing more air and fuel to be fed to the engine but lessening 
the water vapor fed at the time of maximum need. 
OBJECTS AND SUMMARY OF THE INVENTION 
It is an object of the present invention to provide a system wherein 
required amounts of vaporized water or steam can be fed into an internal 
combustion engine in proper proportions. 
It is also an object of the present invention to provide a water injection 
system for internal combustion engines wherein water and air are first 
metered together in a metering assembly. 
Another object of the present invention is to provide a water injection 
system wherein a metered supply of air and water are fed into a vacuum 
actuated control valve which controls the amount of air and water fed to 
an exhaust heat exchange heater in response to the water requirements of 
the engine. 
A still further object of the present invention is to provide a vacuum 
controlled valve which feeds controlled amounts of air and water to an 
exhaust heater wherein the water is flashed into a vapor state and the air 
water mixture fed into the engine via the intake manifold along with the 
air fuel mixture from the carburetor. 
These and other objects may be accomplished by means of a system consisting 
of a water supply reservoir and an air tube coming from the air filter 
wherein the air and water are fed through small orifices into a metering 
device from which they are subsequently fed to a vacuum operated control 
valve. The vacuum actuated control valve exerts zero vacuum on the 
metering orifice assembly when the engine is idling but is designed to 
provide maximum flow of air and water at the time of greatest need such as 
start up, climbing up a hill or accelerating. The air-water mixture 
passing through the control valve pass to an exhaust heat exchange heater 
where the water is almost instantaneously vaporized and the combined air 
vapor mixture is fed into the engine along with air fuel mixture from the 
carburetor. The point at which the air-vapor mixture enters the fuel 
system is below the throttle and no later than the point the air fuel 
mixture enters the intake manifold. Various modifications may be made in 
the vacuum control source and metering device without departing from the 
scope of this invention. The various parts of the invention are all 
integrated into an operative system as will be hereinafter described in 
detail.

DETAILED DESCRIPTION OF THE INVENTION 
There is shown in FIG. 1 a complete schematic diagram of the present 
invention. As supplemented and detailed by FIGS. 2 to 10 incorporating the 
metering device of FIG. 3. For purposes of this description the vacuum 
source for operation of the control valve will be the vacuum spark advance 
tube leading to the distributor as found on late model cars. However, 
other vacuum sources such as exhaust gas recirculation (EGR) could also be 
used. Any vacuum line taken from the carburetor above the throttle that 
provides zero vacuum to the control valve at idle engine speeds can be 
adapted to the present invention on later model cars. However, on older 
cars the distributor vacuum line is not ahead of the throttle but after 
the throttle. Therefore this line will show a vacuum. This line can be 
used to actuate the control valve and will work perfectly well. However a 
modified valve needle is required as shown in FIG. 6. 
In operation this needle operates on both sides of a null point (idle 
condition zero flow), when the engine is idling the needle as shown in 
FIG. 6 is drawn forward against spring pressure (not shown, but 
illustrated as spring 21 in FIG. 4) until idle land 27a is under aperture 
26 and blocks flow. When accelerating, intake manifold vacuum decreases 
and the needle 15 is forced back by spring pressure 21 allowing maximum 
flow. 
As the engine approaches cruise the intake manifold vacuum increases and 
needle 15 moves forward. It will go through land 27a and operate in the 
cruise range. On deceleration (throttle closed) the intake manifold vacuum 
goes much higher and the needle is pulled by the vacuum diaphram 13 
further forward to a second null or valve tail position 28b after going 
through idle land 27a and shuts out any flow of water and air. However, 
this time span is very minimal having little effect on the over all 
operation. But in either event no water is supplied to the fuel system at 
idle engine conditions. 
The system and apparatus as subsequently described revolves around 
operation of the control valve which is the center of operation of the 
system. 
The control valve 10 as shown in FIG. 4 consists of a vacuum diaphragm 
assembly containing an attachment part 11 integral with a solid wall 12 to 
which is attached a movable diaphragm 13. Attached to diaphragm 13 is 
backwardly extending rod 14. The valve control needle 15 is mounted in 
housing 16. Housing 16 contains a nut 17 having an aperture therein and 
threaded into the end of housing 16 nearest the diaphragm. Nut 17 is 
adjustable and therefore serves to regulate the tension of spring 21 as 
hereinafter described. The needle valve 15 has an elongated neck 18. The 
neck 18 terminates at its outer end by protruding through the aperture in 
nut 17 and is connected to diaphragm rod 14 by means of a pin 19 or other 
appropriate means. At the inner neck a shoulder 20 flares outwardly at 
right angles to a diameter essentially the same as the inner diameter of 
the housing. Interposed between nut 17 and shoulder 20 is a spring 21, 
which operates to keep valve needle 15 closed in the absence of applied 
vacuum. Shoulder 20 actually forms a flange or rim which turns inwardly, 
then lengthwise and outwardly to the housing diameter thereby forming an 
indentation or groove 22 into which is seated an O ring 23 in fluid tight 
relationship with the inner housing wall. A second flange or rim 24 
terminates in a valve body 25 which is decreased in diameter from the 
flange 24. The valve housing in the area of the O ring and valve body is 
thickened and slants backwardly at the rear portion to form a relatively 
narrow aperture 26. The valve body is similarly slanted or angled at the 
end portion 27 to engage or seat with the angled valve housing in a fluid 
tight relationship. The valve body contains a valve tail 28 which as shown 
in FIG. 4 is assymetrically formed angling outwardly for a portion of its 
circumference and having a portion of its circumference in contact with 
the wall of aperture 26. Another configuration is shown in FIG. 5 wherein 
tail 28a is symmetrical and conical in shape and would be centered in 
aperture 26. The control valve is completed by an entry port 29 for the 
air water mixture and an exit port 30 into which valve tail 28 extends. 
In operation vacuum applied at attachment port 11 to diaphragm 13 causes 
diaphragm 13 to move forward with sufficient force to overcome the tension 
of spring 21. The tension placed on spring 21 may be regulated by 
loosening or tightening nut 17. It is to be noted that in a partially open 
position of valve control needle 15 allows maximum air water flow through 
aperture 26. In the closed position no flow is allowed and in a fully open 
position the flow is restricted by the expanded end of valve tail 28 or 
28a blocking aperture 26. 
For use on older cars where the distributor vacuum line is influenced by 
the intake manifold the needle configuration would be as in FIG. 6. In 
operation under these conditions vacuum applied at attachment port 11 to 
diaphragm 13 causes the diaphragm 13 to move forward with sufficient force 
to overcome the tension of spring 21 and coming to rest where the idle 
land 27a of the needle is within the aperture 26. This blocks the flow of 
air and water mixture at idle conditions. When the throttle is opened such 
as during acceleration on high power demand on the engine the intake 
manifold vacuum decrease allowing the needle 15 under spring force to move 
back thus permitting the flow of air and water mixture. As the engine 
speeds up and the intake manifold vacuum increases the needle under the 
force of the diaphragm assembly moves forward through the zero flow 
position to a cruise position where the flow is restricted by valve tail 
28b. Under deceleration (throttle closed) the intake manifold vacuum 
increases moving the needle to a full forward position and in which 
position the flow of air and water mixture is stopped. 
With the control valve thus described the operation of the system can now 
be detailed. The supply sources include a water container 31 which as 
shown in FIG. 2 is adapted to be bolted to the firewall of the engine on 
one side and fit over the top of the air filter 32 so as to be attached 
thereto by wing nut 33 at the top of the filter. The other side of the 
water container is attached to support means extending from the fender or 
some other part of the frame. The water container 31 contains a vented 
filler cap 34 on top and a water supply tube 35 on the bottom. The water 
container may be constructed of any durable material such as 
polypropylene, polyethylene, polyvinyl chloride or any similar material. 
An air bleed tube 36 extends from air filter 32 to the metering assembly 37 
as shown in detail in FIG. 3. Preferably the metering assembly 37 is a T 
shape having an air bleed orifice 38 of predetermined dimensions between 
aoubt 1/16 and 3/32 of an inch feeding into an air plenum leading into the 
main assembly 37. Likewise the assembly contains a water orifice 39 having 
a dimension of between about 0.014 and 0.022 of an inch. The air and water 
passing through the orifice are drawn in responsive to intake manifold 
vacuum allowed to pass through control valve 10. Because of the reduction 
of vacuum in the metering assembly 37 carried by the relatively large air 
bleed orifice a larger orifice 39 may be used for a given amount of water. 
This minimizes the clogging of the water orifice due to particles of 
solids and reduces any filtering demand on the water inlet filter. 
The air water mixture in metering assembly 37 is responsive to the intake 
manifold vacuum as exerted on line 40 through control valve 10, heater 
line 41, heater 42 and inlet line 43. 
The heater 42 is shown in FIGS. 7 and 8 as being in the shape of a half 
cylinder and as such is bolted to the exhaust manifold where, through heat 
exchange, the water vapor is instantly flashed into minute water mist like 
particles. A specific advantage of the air metered into the metering 
assembly 37 is that the water vapor is carried through the system 
uniformly preventing the pooling of water, especially in the heater, which 
could cause surges of steam and water to enter the intake manifold and 
engine cylinders. As a result of the air bleed the system becomes a dry 
system thus preventing freeze damage during cold weather. The air bleed 
also provides air to the heater 42 to act as a heat transfer agent between 
the heater walls and water particles improving efficiency of operation. 
Heater 42 consists of a hollow body portion 44 having an inlet part 45 and 
an outlet part 46. Because of the flashing of water vapor in heater body 
43 the outlet part 45 will necessarily be larger than the inlet part 44. 
The heater need not be fastened directly to the exhaust manifold to 
provide heat exchange. Various designs utilizing the exhaust pipe as the 
heat exchange means could also be utilized. Of course, the closer the 
heater is to the exhaust manifold the greater the heat exchange will be. 
The hot water vapor is injected into the fuel system at any position 
between the throttle and the beginning of the intake manifold. 
The actuating source for the control valve can be any carburetor vacuum 
line preferably above the throttle valve, but as shown in older cars, may 
actually be below the throttle valve. For purposes of illustration the 
vacuum spark advance tube will be used. An actuation line 48 leading to 
the control valve inlet port 11 supplies the necessary vacuum to operate 
the control valve 10. 
FIG. 9 graphically shows the vacuum exerted by a typical vacuum spark 
advance tube at various throttle openings. Whereas FIG. 10 shows the 
typical intake manifold vacuum as compared with engine RPM at various 
throttle openings. 
From FIG. 4 it is evident that maximum flow through control valve 10 occur 
when the valve needle is only partially open. In other words when the 
engine is accelerating or operating at full throttle the vacuum spark 
advance vacuum is not at a maximum and by choosing the correct tension on 
spring 21 and by adjustment of nut 17 the diaphragm 13 will only partially 
open the valve needle 15 allowing maximum air water flow. At idle engine 
speeds the vacuum zeros out and the throttle remains closed creating a 
relatively high intake manifold vacuum. As the throttle opens the intake 
manifold vacuum varies roughly according to the engine RPM but the vacuum 
remains sufficient to allow the air water flow through control valve 10. 
At cruising speed the vacuum spark advance vacuum reaches a maximum 
thereby causing diaphragm 13 to pull control needle 15 forward a maximum 
distance. The result is that the valve tail 28 enters aperture 26 
restricting air water flow to heater 42 because less water is required at 
cruising speeds and deceleration than during acceleration. 
Because of the interaction of the various portions of the system the 
moisturized air entering the intake manifold from inlet line 43 makes 
essentially a dry system. 
While not wishing to be confined to any particular theory as to why the 
system provides greater efficiency, including lower emissions and greater 
gas mileage the following explanation is offered. Most automobile engine 
carburetors are designed to provide an air fuel ratio dependent upon the 
operating conditions such as (1) engine idle conditions, (2) engine 
acceleration conditions providing high torque at low RPM and (3) engine 
cruise conditions designed for increased economy. 
Normal combustion requires about 15.1 pounds of dry air to completely burn 
1 pound of gasoline. Thus the air to fuel ratio is 15.1 to 1. 
Idle conditions are different. The air fuel mixture or ratio is relatively 
low, e.g. from about 10:1 to 12:1. When accelerating with high torque at 
low engine RPM, i.e. high start up and acceleration, the air to fuel ratio 
is usually in the range of 13:1 to 15:1. Under cruise conditions where 
maximum power is not required the air to fuel ratio is higher being in the 
realm of 15:1 to 18:1. 
While running under the above conditions the phenomenon can be noticed, 
that engines run better under high humidity conditions, e.g. better 
acceleration response, less knocking or pinging, less tendency for the 
engine to diesel or continue running after the ignition has been turned 
off, and cooler running of the engine. 
It is believed that there are two primary reasons for the increased 
advantages both of which require an air bleed as well as water injection 
into the metering device. Water and water vapor have relatively high 
specific heats. Water vapor exhibits a very high pressure increase with 
only a nominal increase in temperature. For example confined water vapor 
at 705.degree. F. will exhibit a pressure of 3192 psig. 
Combustion temperatures in the automobile engine reach temperatures in the 
order of 4000.degree. F. The partial pressure of a small amount of water 
vapor rises to very high pressure under this temperature. The high 
specific heat of water vapor in turn tends to keep the peak temperatures 
in the combustion chamber down. This accounts for more power, less 
knocking or pinging and less tendency to develop hot spots and diesel. A 
cleaner smoother running engine is the result wherein the burning of the 
fuel mixture is uniform providing a smooth power stroke to the piston 
rather than an explosion. 
According to Dalton's Law of partial pressure the total pressure of a 
mixture of gasses is the sum of the pressures exhibited by each gas 
separately were it to occupy the vessel alone. Water vapor at atmospheric 
or any other low pressure can be considered to be a gas. 
Under high humidity conditions the air drawn into the engine is a mixture 
of dry air and water vapor. The carburetor cannot distinguish the 
difference and therefore feeds a set amount of fuel into the stream of air 
and water vapor. The result is that the engine is burning a richer mixture 
of true dry air to fuel than is anticipated. As previously stated this 
lower ratio is approaching that required for acceleration, therefore 
ignoring the compensating positive factors of the water vapor, the air to 
fuel mixture becomes richer and therefore the engine has better 
acceleration response. 
Under humid conditions or even with the addition of just water to the 
carburetor the mixture fed to the intake manifold is a mixture of dry air, 
fuel and water vapor. With a system introducing more water vapor the 
manifold mixture drawn into the combustion chamber is further diluted with 
the added water vapor. The air to fuel ratio is thus lowered. To 
compensate for this condition more air must be introduced into the intake 
manifold. The bleed air mixed with the water in the metering device serves 
to accomplish this. 
There is a practical limit as to the amount of water vapor that can be 
introduced into the intake manifold and cylinders without quenching the 
flame in the combustion chamber causing loss of power, incomplete 
combustion and expelling partially burned hydrocarbons and carbon as black 
smoke from the exhaust. There is also a limit as to the amount of 
vaporized water and air that can be fed into the intake manifold as the 
pressure differential between the intake manifold and the outside 
atmosphere must be maintained to prevent loss of carburetor efficiency. 
Thus, the amount of bleed air that can be used is also limited. 
If operated properly however, these limiting factors prove to be 
advantageous because the same power can be generated using less fuel at a 
proper air to fuel ratio. Since less dry air is admitted into the fuel 
system because of the use of water vapor and bled in air and since the 
carburetor cannot sense the difference between dry and humid air the 
compensating factor is to introduce less fuel by reducing the size of the 
power jets in the carburetor fuel feed system. The size of the reduction 
will of course, depend upon the carburetor used. 
In general the weight ratio of water to fuel will vary from about 0.20:1 to 
0.30:1 with the control valve 10 being set to deliver water in the minimum 
ratio so that extra water brought in because of high humidity will not 
exceed the water requirement. 
Thus the control valve and the vacuum executed thereon, the manifold vacuum 
the size of the power jets in the carburetor and the air water metering 
assembly all interact to produce an efficient system having the above 
detailed advantages. 
Although the invention as has been described is deemed to be that which 
would form the preferred embodiment of the invention, it is recognized 
that departures may be made therefrom without departing from the scope of 
the invention which is not to be limited to the details disclosed, but is 
to be accorded the full scope of the claims so as to include any and all 
equivalent devices and apparatus.