US2861422A - Power gas generator - Google Patents

Description

Nov. 25, 1958 H. L. MAGILL 2,861,422

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POWER GAS GENERATOR I Filed June- 18. 1951 4 Sheets-Sheet 4 FIG.6

220 3'0 2 L40 CHECK VALVL 2|O 200A I ICAL GLOTQ INVENTOR 250 4 I t i F I G 7 80 HERBERT LMAGILL TTORNEYS United States Patent PUWER GAS GENERATOR Herbert L. Magill, Chicago, Ill.

Application June 18, 1951, Serial No. 232,219

33 Claims. (Cl. 60-3928) This invention relates to a gas pressure generator of the type wherein fuel energy is converted into heat energy by combustion, or wherein heat energy transmitted to a pressurized fluid, acts to produce a high pressure and temperature fluid flow which can, by proper means, be translated into power and/or propulsion or provide a source of heat for use. The present application is related to my copending application, Serial No. 575,158,

filed January 29, 1945, now U. S. Patent No. 2,557,128, issued June 19, 1951, and the entire disclosure of that application, in so far as it is not inconsistent with the present disclosure, is incorporated herein by reference.

It is the principal object of the present invention to provide such a gas pressure generator that exhibits a maximum of efiiciency in the heat pressurization of a fluid charge supplied to the pressure chamber.

Another object is to provide such a device that produces a uniform flow of the pressurized product from every point in the pressure chamber to a discharge port and thus achieves a maximum of efiiciency in the discharge of the product from the pressure chamber.

A further object is to provide a gas pressure generator arrangement wherein the fresh incoming fluid charges secure a maximum of efliciency in the internal cooling of the pressure chamber.

According to the present invention a specific construction and arrangement of the pressure chamber and associated devices is employed in accomplishing the above. A circular pressure chamber casing of uniform crosssectional shape and having intake and discharge ports located at its axial center is employed. The pressure chamber itself is substantially annular and cooperates with its intake port to direct the fresh incoming fluid charge radially outwardly. The sidewalls of the chamber diverge radially outwardly to merge with a generally rounded outer perimetric section of greater depth. Thus the radially directed incoming fluid charge is guided by the contoured sidewalls of the pressure chamber to form a vortex movement in a radial plane therein.

In addition it is proposed to provide a swirling means associated with the intake valve so that the fresh incoming fluid charge, instead of being directed radially from the intake port, is directed angularly therefrom whereby the fluid flow tends to swirl circumferentially in the pressure chamber. This swirling means cooperates with the sectional contour of the pressure chamber such that the fresh incoming fluid charge exhibits a combined swirling movement about the circumference of the pressure chamber and a simultaneous vortex movement. This arrangement creates a maximum of turbulence of the fluid charge in the pressure chamber which not only facilitates combustion in the case of a combustible charge but also materially improves the cooling effect exerted on the inside surface of the pressure chamber walls by the fresh incoming fluid charge.

Still another object is to provide fuel injection means responsive to the rise in pressure within the pressure chamber due to the formation of the fluid charge therein 2,861,422 Patented Nov. 25, 1958 for injecting fuel into the pressure chamber to form a combustion mixture therewith.

An additional object is to provide a continuously operable arrangement for automatically rotating the intake and discharge valves through a selected angular degree of movement during each operating cycle of the pressure generator. Further and other objects and advantages will become apparent as the disclosure proceeds and .the description is read in conjunction with the accompanying drawings, in which Figure l is a cro:s-sectional view showing a preferred form of the pressure generator;

Figure 2 is a fragmentary sectional view taken on the line 2-2 of Figure 1;

Figure 3 is a view. similar to Figure l but shows a slightly modified form of the invention;

Figure 4 is a diagrammatic view which shows the control apparatus for the pressure generator;

Figure 5 is a fragmentary cross-sectional view showing a slightly modified embodiment of the intake and exhaust valve arrangement in which autorotation of the valves is provided during operation;

Figure 5a is a sectional view taken along the line 5a5a of Figure 5 showing the spiral spline for accomplishing the autorotation;

Figure 6 is a sectional view showing the fuel injector; and

Figure 7 shows a modified form of the fuel injector.

7 It should be understood that the following description of specific forms of the invention is for the purpose of complying with section 4888 of the Revised Statutes, and should not be construed as imposing limitations on the appended claims, except as may be required by the prior art.

GENERAL ORGANIZATION The generator is designed to provide a substantially continuous flow of heated expanding gases for use in jet propulsion or indriving some type of a heat engine, as for example, a gas turbine.

The power generator 1 is characterized by having an annular chamber 2 with a centrally disposed combination intake and discharge valve for charging the pressure chamber and for discharging it after the fuel charge is ignited therein. The action is entirely automatic with the frequency of combustion being dependent upon the rate of flow of the compressed air being delivered to the chamber 2 through an intake valve 33.

Referring to Figure 4, a source of compressed air is delivered through a pipe 72, through a shut-ofi valve 60, a throttle valve 29 and a conduit 73 to a fitting 43A that communicates with an air intake passage or intake valve chamber 43 (Fig. l), and the air pressure in the intake passage 43 is sufficient to lift the intake valve 33 against the pressure of spring 40 to fill the chamber 2 with a prescribed charge of compressed air. While this takes place, a discharge valve 11 is urged by the pressure of spring 40 into its seat. When the generator is first started, it may be necessary to relieve pressure in the chamber before the charge of compressed air is delivered thereto, and for this purpose a manually controlled pressure relief valve 58 is provided which is solenoid operated and preferably operates during'initial movement of A fuel charge is introduced into the pressure chamber in any suitable way, one such way being disclosed in Figures 6 and 7, in which itwill be seen that the pressure within the chamber 2 operates through the passageway 290 to force a piston 200 to the right, thereby delivering a metered quantity of fuel to the pressure chamber.

Ignition of the air and fuel mixture is preferably accomplished by one or more spark plugs 46 which are fired in response to the closing of the intake valve, the ignition switch points being indicated at 53 and 56 (Figure l). p

The device is arranged to inject only a minor fraction of the total fuel charge prior to closing of the intake valve and this is accomplished by selecting an appropriate point in the pressure rise in the chamber at which the fuel pump initiates injection of the fuel. Since the fuel metering piston is subjected to the pressures exist- .ing within .the pressure chamber, the increasing pressures in the pressure chamber due tocombustion are automatically compensated and hence do not impair the fuel injection operation.

After the charge is ignited, the pressure within the chamber rises until it is sufficient to force open the discharge valve 11, which it does, due to the frustro-conical shape of such valve. The rapidly expanding gases are then injected through the nozzle 9 for delivery to the gas turbine, or such other point of use as is desired.

At the same time that compressed air is being delivered to the intake valve chamber 43 for charging the pressure chamber, compressed air is also being delivered through a throttle 29 and a conduit 28 to a fitting 27 which communicates with a cooling chamber 3 surrounding the pressure chamber 2, and after sweeping the pressure chamber and absorbing heat therefrom, this air combines with the gases delivered from the pressure chamber through a Venturi action for increasing the volume of gas being delivered to the turbine or other device, if any, connected with the discharge of the power generator.

The outer chamber 3, forming in effect a jacket chamber surrounding the inner automatic pressure chamber 2, constitutes a continuous flow pressure chamber in which the compressed air or other fluid introduced under pressure is accelerated in velocity by the absorption of heat energy transmitted thereto by radiation and convect'ion from the inner automatic pressure chamber 2,

and is thereafter discharged through a nozzle 70, concentric with the nozzle 9 and forming therewith a Venturi injection nozzle 23, whereby the discharge flow from each nozzle, one being continuous and the other intermittent, acts to create a Venturi injection effect as each flow predominates over the other.

A simple lubrication system is provided in which the enclosed space between the intake and discharge valves 33 and 11, respectively, contracts and expands in accordance with the relative movement between the two valves. The space between these two valves is connected with an oil reservoir 86 through parallel pressure relief valve 90 and check valve 88, so that any desired pressure may be maintained within the pumping chamber to pro- --vide adequate lubrication of the sole major moving parts of the generator, namely, the intake and discharge valves.

Description of pressure generator Coming now to the detailed construction of the pressure chamber, .and referring particularly to Fig. I, it

: will be seen that the .automatic pressure chamber 2 is composed of two case members (forgings or castings) 4 and 5 bolted together by the flange bolts 6 suitably disposed about the circumference of the case members,

axial-center of the'said chamber.

The sidewalls of the pressure. chamber 2 diverge radially outwardly to merge with a generally rounded outer perimetric section of greater depth, whereby when the said intake valve opens, the fluid flow therefrom is directed radially outward in every direction into the said chamber, the contour of the walls of the said chamber acting to direct the fluid flow therein to form a vortex as shown diagrammatically in Fig. 1.

To further increase this turbulence action, the intake valve 33 is provided (Fig. 1) with a series of helical shaped vanes 33A extending around the circumference of the said valve and suitably rigidly attached thereto close to the under side of the valve head and within the intake valve passage 43, whereby when the said valve opens the fluid flow instead of being directed radially outward from the valve is directed angularly therefrom thereby tending to swirl the fluid in the pressure chamber 2.

By means of the chamber form described and the said last-mentioned means the flow of the fluid charge within the chamber combines the swirling movement with the said vortex movement described, thus producing the maximum possible turbulence of the fluid charge in the chamber.

This action tends to facilitate the internal cooling of the said pressure chamber 2 by the fresh induced charges and the combustion of the fuel thereafter. 7

This particular form for the pressure chamber described has the further advantage that when the discharge valve 11 automatically opens to discharge the combustion products, the gas flow occurs uniformly from every direction within the pressure chamber to the unobstructed discharge port.

The fluid charges for the pressure generator auto matic pressure chamber 2 may be formed of any combustible fluid mixture supplied to or formed therein, such as air-fuel combinations employing gasoline, kerosene, fuel oil, etc.; rocket fuel combinations requiring no atmospheric air; an air-solid fuel combination, such as air with a finely powdered coal, etc.; or may be formed of an inert non-combustible fluid dependent upon the transmission of heat energy from a heat energy source to secure a rise in the pressure and temperature of the fluid charge in the pressure chamber of the pressure generator. Such a non-combustible fluid could be air, water, helium, etc., and the heat energy source could be an atomic pile.

A combustible fuel mixture induced to form a charge in the pressure chamber could be a pre-formed combustible mixture or could be formed by injection of the fuel into the chamber charged with compressed air or other combustion supporting medium to produce therein combustible charges substantially constant in volume, pressure, temperature, and composition.

In the case of the premixed charge, ignition in the pressure chamber 2 can be effected by an electrical ignition means, since the temperature of the charge mixture necessarily must be less than the spontaneous ignition temperature of the fuel content. In the case of separate fuel injection, the fuel-injection charge can be ignited in the same manner as above mentioned if the temperature of the compressed air charge in the pressure chamber is less than the spontaneous ignition tempera ture of thefuel, or self ignition of the fuel can be ob- .tained if the temperature of the compressed air charge within the pressure chamber is controlled to a temperature in excess of the spontaneous ignition temperature of the fuel.

Apart from the fact that the pressure generator will operateon any kind of combustible mixture charge which can be supplied, it is the only device of its character capable of operation on various air-fuel combustible mixture charges within the atmosphere strata which can continue to operate beyond the atmosphere strata by the simple expedient of changing to a rocket-fuel combination .requiring no atmosphere air.

The case 4 includes :an axial .nozzle' extension .Sxin

which is inserted a removable discharge nozzle 9 having a valve seat 10 for the discharge valve 11.

The case 5 includes an axial extension 12 having a screw thread 13 into which a removable valve unit 14 is screwed for rigid retainment therein.

Attached integrally to the outer surfaces of the cases 4 and 5 are a multiplicity of radiator fins 15 suitably disposed radially around the circumference of the cases.

The case enclosure 16 includes the generally dishshaped members 17 and 18 joined together by a telescoping joint 19 and a member 17a, the said parts being held in place by the flange bolts 6 suitably disposed about the circumference of the pressure chamber 2.

The enclosure member 17 has rigidly attached thereto a mounting flange 21 for mounting the pressure generator. The mounting flange 21 has a reinforcement extension to reinforce the nozzle extension 22 of the enclosure member 17 which is disposed concentric with the nozzle 9 to form therewith the Venturi injection nozzle 23.

In Fig. 1, the nozzle extension 22 has a tubular end 22a which, in the particular arrangement shown adaptable to a jet driven propeller, telescopes within a rotating tubular member with a close but free-running fit.

The enclosure member 18 is formed to provide an annular air passage or conduit 26 having a port 26a and a detachable pipe coupling 27 associated therewith for attachment to an air duct 28 (Fig. 4) leading from the throttle control valve 29.

A conical disc formed with suitable flanges to fit the perimeter of the said conduit 26 is provided with a central aperture closely surrounding the valve extension 12 and cooperating therewith to form the annular port 24, whereby air from the conduit 26 is directed to flow therefrom uniformly into the jacket chamber 3.

The space between the case members 4 and 5 and the enclosure 16 defines a continuous flow pressure chamber 3 that not only provides a cooling means for the inner automatic pressure chamber 2, but also has other important functions. The continuous flow of relatively high velocity fluid from the continuous flow chamber 3 passes through an annular nozzle 70, and the intermittent discharge flow from the automatic pressure chamber 2 passes through the nozzle 9. These flows alternately predominate to cause each to alternately exert a Venturi injection effect upon the other.

During the time that the continuous flow discharge predominates it acts to scavenge the automatic pressure chamber 2 of residual fluid thereby removing residual heat and reducing contamination of the incoming charges and also enabling the induction of a larger volume of fresh fluid charge. Another advantage of this arrangement is that the continuous flow fluid stream combines with the intermittent flow fluid stream to dampen the pulsations created thereby and provide a more uniform flow.

A further and important advantage of the arrangement is that the heat transferred to the continuous flow stream as it cools the chamber walls 71 acts to accelerate the continuous fluid flow thereby improving the scavenging effect and more nearly equalizing the velocities of the combining fluid streams so that they join with a minimum of frictional drag. The continuous flow stream is further accelerated by the Venturi injection action exerted by the high pressure discharge flow from the' automatic pressure chamber 2 during the intervals when it predominates over the continuous discharge flow.

It will be noted that the arrangement also conserves radiated heat energy which normally would be dissipated to a cooling system, and by utilizing the flow of this heat energy, in conjunction with a fluid supplied under pressure, creates a heat engine capable of a substantial augmentation of the mass of the fluid discharged from the pressure generator. The effective cooling provided for the pressure chamber 2 externally by the jacked chamber 3 and internally by the incoming freshcharges permits the development of high pressures and temperatures within the automatic pressure chamber 2 to secure high thermal efliciency and fuel economy.

The fluid flow from the continuous flow pressure chamber 3 is discharged through the concentric nozzle 70 of the Venturi injection nozzle 23 as a fluid tubular extrusion containing within it the higher temperature fluid discharged through the nozzle 9. Thus, the walls of the discharge duct 59, etc., are protected fromdirect contact with the high temperature fluid stream. As the two streams join and merge into a single stream of a greater mass, weight, and volume, they reach an equalized pressure and temperature lower than that of the discharge from the nozzle 9.

From the foregoing, it becomes apparent that the primary objective of the outer continuous flow pressure chamber 3 is cooling and scavenging of the automatic pressure chamber 2, power augmentation, heat conservation, and temperature control of the fluid discharge from the pressure chamber.

One or more ignition spark plugs 46 are screwed into suitable bosses provided in the case 5 as an ignition means for the pressure generator.

If a multiplicity of the spark plugs 46 are employed to supply simultaneous ignition of the combustion charge in the pressure chamber 2, they preferably would be arranged equidistant around the circumference of the case 5, as shown in Figures 1 and 3.

The valve unit 14 comprises a valve case 30 having the screw threads 31 for engagement with the screw thread 13 formed on the case extension 12 and a valve seat 32 for the intake valve 33.

The intake valve 33 forms a cylinder 34 adapted to slidably receive the discharge valve 11, and has a smaller diameter 35 adapted to slidably fit an extension cylinder 36 of the valve case 30. An axially attached extension shaft 37 of the intake valve 33 extends through a hole 38 in the valve case 30 into the ignition timer 50 for actuating the ignition mechanism.

The intake valve 33 and the discharge valve 11 being telescoped one Within the other form an internal chamber 39 in which a compression valve spring 40 is interposed between the two valves to thereby urge both valves to a normal position on their respective valve seats 10 and 32.

The discharge valve 11 is provided with suitable piston rings 41 to pressure seal the valve against leakage from the pressure chamber 2, and the intake valve 33 is likewise provided with the piston rings 42 to seal the valve against leakage from the intake valve passage 43.

The discharge valve 11 is preferably hollow with a closed end 44, and is loaded with sodium in the conventional manner to facilitate cooling.

In the pressure chamber, the time period, during which ignition, combustion and discharge of the combustible charge takes place, represents a fixed time period which remains constant regardless of the frequency rate of operation of the pressure generator 1.

Therefor, the maximum frequency rate or explosions per minute (E. P. M.) at which the pressure generator can operate will depend entirely on the intake valve area, the pressure and rate of flow of the fluid charge into the pressure chamber 2, and the rapidity with which the intake valve 33 can be closed from full open position as the pressures within the pressure chamber 2 and the intake valve passage 43 approach equalization as the pressure chamber becomes charged.

In the pressure generator operating cycle, it is desirable that the pressure in the pressure chamber 2 be as low as possible at the time the discharge valve 11 starts to close from full open position and the intake valve 33 starts to open from a closed position.

The time of opening of the intake valve 33 is deter- 7 mined-by the pressure within the pressure chamber 2, during the discharge part of the operating cycle, being applied to the projected diametral area of the head of the intake valve 33 as required to balance the opposing force exerted on the under side of the said intake valve by the fluid pressure existing in the intake valve passage 43.

It 'is therefore preferable that large diameter valves such as illustrated in Fig. 3 be employed since the larger projected diametral area of the valve enables a lower pressure value in the pressure chamber 2 to balance a given force value exerted under the valve head by the existing fluid pressure within the intake valve passage 43.

The large diameter valve, requiring less valve lift for a given intake port area, further enables a quicker opening and closing of the valves'and includes the pertinent advantage in that it permits forming the discharge port 57 with a more efficient nozzle-form opening.

As the intake valve 33 in opening acts to move the discharge valve 11 to close the discharge port 57 in conjunction with such force that the spring 44 may exert tending to separate the two valves, the spring 40 therefore exerts no resisting force to the said intake valve 33 until, during its opening movement the discharge valve 11 becomes seated on its valve seat 16 thereby closing the discharge port 57.

When the intake valve 33 obtains its full opening movement with the discharge valve 11 seated, the valve spring 4-0 then exerts its full pressure to close the intake valve when the pressures within the pressure chamber 2 and the intake valve passage 43 approach equalization resulting from the charging of the said pressure chamber.

The pressure or weight of the valve spring 49 then becomes important as the means to close the intake valve 33 as fast as the pressure differential between the pressure chamber 2 and the intake valve passage 43 changes due to the charging of the pressure chamber as the pressure in the two chambers approaches equalization.

When the objective is to obtain an extremely high frequency rate of operation of the pressure generator, an auxiliary valve spring 40a (see Fig. 3) may be employed to increase the closing force on the intake valve 33 so that the mass of the valve can be moved in the manner described in the much shorter time available for the charging of the pressure chamber 2.

The "alve spring 4361 can, of course, be calibrated by control of its flexibility rate to give any desired seating pressure for the intake valve taking into consideration the valve spring 41).

In some pressure generators where a slow frequency rate of operation may be employed, such as with a heating plant, a slow closing intake valve 33 may be desirable since it permits a closer approach to the equalization of the pressure within the pressure chamber to that within the intake valve passage 43 during the charging of the pressure chamber.

By reducing the diameter of the valve extension 35 of the intake valve 33, a part of the force exerted by the valve spring 40 to close the intake valve can be pressurebalanced whereby the valve spring is less effective against the intake valve 33 than against the discharge valve 11.

The opening movement of either the intake valve 33 or the discharge valve 11 with the other closed is restricted by contact between the surfaces 47 and 48 of the valves.

The discharge valve 11 is of frusto-conical shape and has a tapered end 49 exposed within the pressure chamber 2 when the valve is closed on its valve seat it By proper control of the taper of the valve end 49 to provide the correct cross-section area diiferential between the diameters of the discharge valve at its valve seat region and at its intake valve region, the area of the valve thus exposed to pressure reaction within the pressure chamber 2 can be correlated with the counter pressure o'rweight'of' the valve 'spring'40so'as to preselec't the combustion pressure value at which the discharge valve 11 will be moved off its valve seat 10 to open the discharge port 57.

Thus, by selecting a pressure value for the opening of the discharge valve 11 at or near to the maximum pressure risewhich can be obtained by combustion of the fuel, all of the available heat energy released by combustion of the charge can be exploited to increase" the pressure and temperature of the combustion gases before they are discharged from the pressure chamber 2.

Once lifted oir" its valve seat, the full cross-sectional area of the discharge valve 11 is exposed to the combustion pressure within the pressure chamber 2 and the valve opens fast against the pressure of the valve spring 40 to its full open position with its surface 47 contacting the surface 43 of, the intake valve 33. Thus, in opening the discharge valve 11 withdraws from the discharge port 57 leaving its area entirely unrestricted.

As a result of the construction described, both valves are exposed to combustion temperatures only on their surfaces facing within the pressure chamber 2, where, in contrast, the exhaust valve of a piston engine is subjected to high temperature over its entire surface including the exposed part of the valve stem.

The discharge valve 11 will remain in its full open position until the pressure within the pressure chamber 2 decreases, by discharge of the combustion gases through the discharge port 57, to a force valve acting on the full cross-section of the valve less than the pressure force exerted by the valve spring 4i), whereupon the valve spring acts to close the valve by moving it away from the intake valve 33 and toward the valve seat 10.

However, the closing of the discharge valve 11 on its seat 16 is not entirely dependent upon the valve spring 4b as above described, for at frequency rates of operation of the pressure generator at which the flow pressure rate through the intake valve passage 43 has enough kinetic energy or pressure force to open the intake valve 33' to its full open position, the discharge valve 11 is positively closed by the full opening movement of the intake valve 33 in conjunction with the action of the valve spring 4%}.

The valve chamber 39, by reason of the opening and closing of the valves, expands and contracts, thereby forming an oil pump for lubrication of the friction surfaces of the valves.

'When the chamber 39 is expanded by the closing of the intake valve 33, oil supplied from an oil supply tank or lubrication tank 86 through the pipe 87, the check valve 88 and the pipe 89 to the port 83 is drawn through the port 84 in the extension diameter 35 of the intake valve 33 into the chamber 39.

When the latter is contracted by the opening of the discharge valve 11, pressure is exerted on the oil in the chamber 39 against the pressure relief valve 90 in the oil supply line. 7

Thus the'oil in the chamber 39 is pulsated in and out and acts to supply lubrication to the friction surfaces of the intake-and discharge valves at a proper pressure controlled by the pressure relief valve above mentioned.

As the pressure applied to the oil in the chamber 39 occurs when a high combustion pressure exists in the pressure chamber 2 and a high fluid charge pressure occurs in the intake valve passage 43, the pressure at which the oil is controlled in the chamber 33 can be reasonably high without danger of being forced past the piston rings 41 and 4-2 into'the pressure chamber 2 or the intake passage 43.

Thus the pressure of the combustion and mixture gas being opposed by the oil pressure tends to effectively seal the valves against leakage in either direction.

The chamber 39, by reason of pressurizing the oil con tained therein by the opening of the discharge valve 11, which can occur with considerable force, also acts as a hydraulic shock absorber to cushion and control them:-

- 9 tion of the discharge valve as it opens and makes contact of its surface 47 with the surface 48 of the intake valve 33 which is in closed position on its valve seat 32.

As the intake and discharge valve is the only mechanism of the pressure generator requiring lubrication, it is obvious that little lubricant is required because of the small areas involved, short travel of the valves, effective cooling of the valves, and little or no loss of lubricant from the valve surfaces into the pressure chamber 2 or the intake valve passage 43 because of the pressure-balanced condition which exists as above described.

Referring to Figs. 1 and 3, it may be seen that the ignition timer 50 is relatively simple, comprising a dielectric case 51 removably attached to the extension 36 of the valve case 30 by means of spring snap locks (not shown) in common use with automobile ignition dis tributors.

The case 51 supports the pivot contact member 52 which, when the intake valve 33 closes on its seat 32, is simultaneously forced to contact the contact terminal 53 by the extension shaft 37 of the intake valve 33 against the resistance of a spring 54, thereby completing a low-tension ignition circuit across the ignition contact terminals 55 and 53 causing the energizing of the ignition coil or coils 69 and ignition sparks across the electrodes of the spark plugs 46 to ignite the charge in the pressure chamber 2. 7

When the combustible charges induced into the pressure chamber 2 are composed of compressed air or other combustion supporting medium and a suitable fuel and are formed of either a pre-formed mixture or by injection of the fuel into the chamber charged with the combustion supporting medium, the pressure of the latter may be any pressure in excess of that necessary to produce a temperature by the heat of compression suffi cient to vaporize the fuel, and ignition of the combustible charges thus formed can be accomplished in the above manner if the temperature of the combustion supporting medium is controlled to a value less than the spontaneous ignition temperature of the fuel content of the combustible charge.

By controlling the temperature of the compressed air charge inducted into the pressure chamber to a temperature high enough to spontaneously ignite the fuel when injected into it, ignition is thus effected by injection of the fuel as in a diesel engine.

As combustion gas is discharged from the pressure chamber 2, the resultant drop in pressure in the chamber automatically opens the intake valve 33 to permit induction of a new charge into the pressure chamber 2, the contact between the pivot contact member 52 and the contact terminal 53 is broken by the compression spring 54 as the shaft 37 'moves away from the pivot contact member 52.

The travel of the pivot contact member 52 is limited by a third contact terminal 56 which serves to both regulate the travel of the pivot contact member 52 and as an ignition circuit control switch required for use with a multiple pressure generator unit as described in the previously referred to U. S. patent application, Ser. No. 575,158.

The shut-off valve 60 is provided as a precautionary means whereby the compressed air from the compressed air supply source can be positively shut off to prevent leakage during extended periods of inactivity of the pressure generator 1.

The shut-cit valve 60 operates a master ignition switch 61 which, when the valve is full open, completes the ignition circuit to the terminal 64 of the switch 62 operated by the throttle control valve 29.

When the shut-off valve 60 is closed, the switch 61 breaks the ignition circuit so that accidental operation of the throttle valve 29 does not drain electric current should the key-lock ignition master switch be turned on.

- 10 When the throttle control valve 29 is moved through an initial distance prior to opening the valve to permit compressed air to flow to the pressure generator, the

switch 62 operated by the throttle control valve 29 completes the ignition circuit between its terminals 64 and 65, thereby completing the ignition circuit to the terminal 55 of the ignition timer 50 so that the ignition is turned on and the pressure generator starts operating upon completion of the charge initiated into the pressure chamber 2.

During the same initial movement of the throttle control valve 29 above mentioned, the switch 62 also makes and breaks the circuit between the terminals 64 and 66, thereby momentarily energizing the solenoid operated pressure relief valve 58 and causing the latter to open and drain the pressure chamber 2 of any existing residual pressure.

As this same operation occurs with the closing of the throttle control valve 29 to stop the pressure generator from operation, the pressure chamber 2 is double drained to insure removal of any residual pressure.

The solenoid operated pressure relief valve 53 may be any suitable type of such valves but preferably incorporating a manual release means such as shown at 68.

As a result of the foregoing means and procedure, whenever the pressure generator is initially started into operation, it starts with a complete fresh charge at the proper pressure and temperature. This is of particular advantage when heavy fuels are being employed for the pressure generator requiring heat to insure vaporization to a satisfactory combustible mixture.

Fuel injection system A fuel injector for a pressure generator of the character described necessarily must operate automatically in response to a change in pressure in the pressure chamber 2 during the charging phase of its operating cycle and be initiated preferably simultaneously with or near to the point of closing of the intake valve 33, and since the pressure generator operates with constant volume, pressure, and composition combustible charges, the same volume of fuel is required to be injected into the pressure chamber 2 per cycle to form the combustion charge therein irrespective of the operating frequency rate of the cycles per minute.

It will be apparent to those familiar with the art that while one form of fuel injection nozzle is shown as an example to illustrate the principle of operation of the devices hereinafter described that any suitable type of pressure actuated fuel injection nozzle can be incorporated therewith.

In Fig. 6, a piston 2% operating in a cylinder 300 against a compressionspring 4th] actuates an injector piston 5th) within a pump cylinder 600 to which fuel under pressure is supplied by fuel pump means through the fuel line 700 and a check valve 8% and the passage 900 to the injector chamber 100.

A passage communicating with the chamber 100 leads to and through an orifice 12% in the plate 130,

a check valve 14th, and a passage of the check valve retainer into the chamber in which a valve is normally held in closed position against a valve seat by a spring 2tltl-A reacting against a guide cylinder 210 retained on the stem of the valve 180 by a removable snap ring lock 220. The head of the valve 180 is enclosed in a fuel cup 240 provided with the suitable orifices 250 from which when the fuel is injected through the valve 180 into the said fuel cup it is subsequently discharged into the pressure chamber 2.

The cylinder 21%) is provided with a series of helical slots 230 around its circumference to provide communication between the upper and lower portions of the chamber 170. The fiow of fuel under high pressure through the said helical slots 230 during the injection period as the valve 180 is opened ofi its seat tends to a 11 rotate the said valve slightly thereby tending to maintain' perfect seating of the latter on its seat.

'The check valve 14% opens only if the pressure in chamber 100 exceeds a predetermined amount, and serves to maintain a pressure value in the nozzle chamber 170 after injection into the pressure chamber 2 when, as a result of discharge of the combustion gas therefrom, the decrease in pressure in the said pressure chamber 260 against the piston 2% enables the spring 4%!) to act to move the said piston to the opposite end of its stroke facilitated by the expansion of the pressure of the fuel existent in the chamber 100 and thereafter when relieved by the pressure of the fuel supplied by the same fuel pump means through the check valve 800 to the chamber-100.

Thus the piston 209 is actuated by pressure in the pressure chamber 2 to pressurize the fuel charge for injection therein, and its return movement through its operating stroke is actuated in part by the spring 490, the pressure in the chamber 1% until relieved by movement of the said piston 2th and thereafter by fuel pressure supplied by the fuel pump means provided.

vAn adjustment screw 2'70 adapted to limit the travel of the piston 200 is provided whereby the volume displacement of the fuel pump per stroke can be adjusted to provide injection of the correct amount of fuel per cycle into the pressure chamber 2 to thereby secure proper, efficient combustion of the fuel with the air volume contained therein.

The fuel injector 99 thus need not be critical as to its designed capacity as long as it is capable of supplying the fuel in some excess of the required amount since it can be easily adjusted in the foregoing manner to deliver the proper fuel volume per cycle.

By proper calibration of the Weight of the springs 460 and 200A in conjunction with a proper selection of the diametral area of the piston Ziltl and the piston 500 taking into consideration the pressure value available in the chamber 269 acting against the said piston 26%, the pressure of the fuel acting against the said piston 200, the pressure of the fuel for injection can be preselected and the time injection is initiated into the pressure chamber 2 can be determined to occur at any point in the pressure rise in the latter during the charging phase of the operating cycle.

It will be apparent that when the fuel is initially injected into the pressure chamber 2 that as a result of combustion, a pressure rise in the said chamber will then occur. As this increase of pressure is also effective on the piston 260 an increasing pressure force on the fuel is simultaneously exerted to inject it and compensates for any increasing pressure in the pressure chamber 2 resulting from combustion until all the fuel is injected.

Since the combustion chamber pressure is the motivating source of power compounded to exert pressure on the fuel to inject it into the combustion or pressure chamber, the fuel injector system can be designed to meter the injection of the fuel to the rate at which combustion of the fuel can efficiently occur, in other words, to supply the fuel only as fast as it can be properly burned.

Fig. 7 represents a modification of Fig. 6 in which the fuel pump means of the fuel injector system is a separate unit from the fuel injector nozzles. The functional operation of Fig. 7 is identical with that of Fig. 6 differing only in that one fuel injector pump is employed to actuate a multiple number of injector nozzles, and the fuel is delivered by the fuel pump means to a jacket surrounding the piston cylinder 304) from which it is delivered through a check valve to the pump chamber. The fuel thus serves as a cooling means for the piston cylinder 300, the absorbed heat acting as a means of preeating the fuel prior to entering the injection pump chamber 100.

The advantage of the arrangement of Fig. 7 will be apparent since it enables uniform fuel injection at various zeolites Autorotatz'on of pressure generator discharge and intake valves In valve design, it has been found that by rotating the valve relative to its valve seat during operation and progressively in the same direction, whereby the contacting surfaces of the valve and valve seat are continuously being changed in relation to each other, the operating life of the valve can be materially increased before regrinding is necessary.

In Fig. 5, a stud shaft rigidly attached to the intake valve 33 and extending within the valve chamber 39 concentric with the axis of the valve, is provided with the spiral spline teeth 91 adapted to engage the corresponding spiral spline grooves 93 of a tubular shaft 92 rigidly attached to the discharge valve 11 and concentric with the latter and the stud shaft 90.

When the discharge valve 11 is automatically opened at thepreselected pressure rise within the combustion chamber 2 of the pressure generator, the relative movement of the tubular shaft 92 to the stud shaft 90, which is being held stationary by the frictional contact of the intake valve 33 on its seat due to the pressure of the combustion gas within the combustion chamber and the pressure exerted by the valve spring 40, acts to rotate the discharge valve 11 through an angular movement determined by the spiral angle of the spiral teeth 91 and the linear travel of the valve itself.

As the combustion gas is discharged from the combustion chamber and the pressure therein drops, the intake valve 33 is opened due to the pressure of the incoming compressed air charge in intake passage 43 and acts to move the discharge valve 11 with it to its closed position on the valve seat 10. During this process the two valves move practically in unison-very little relative movement existing between the two by reason of the compressed valve spring 40.

Thereafter as the combustion chamber becomes charged, the valve spring 40 acts to close the intake valve 33 on its valve seat 32. Since the discharge valve remains stationary because of frictional contact with its seat due to the pressure exerted by the valve spring 40, the closing movement of the intake valve 33 to its seat 32 acts to rotate the intake valve 33 in the same direction of rotation as that of the discharge valve.

As a result of the foregoing cycle of operation of the valves, both valves are alternately rotated in the same direction of rotation with an angular movement per cycle determined by the spiral angle of the spiral teeth 91 of the stud shaft 90 and the linear travel of the valves.

With each succeeding operating cycle, the valves are both progressively rotated but with very little relative movement of one to the other, the discharge valve moving through its angular movement while the intake valve remains stationary, and the intake valve thereafter doing the same thing with the discharge valve remaining stationary.

The valves therefor are intermittently, progressively rotated in the same direction, of rotation, completing one revolution each successive number of operating cycles as determined by the angular movement of the valves per cycle.

I claim:

1. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber; intake and discharge valves mounted in said A 13 hub section for operative movement along the central axis of said chamber, and pressure operated means for opening and closing said valves.

2. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, intake and discharge valves mounted in said hub section for operative movement along the central axis of said chamber, and pressure operated means for opening and closing said valves, said pressure chamber having a smoothly curved cross-sectional shape whereby .gas entering the chamber through said intake valve is directed toward the sidewall of said chamber opposite to said intake valve and is then redirected radially outwardly by said sidewall to form vortices in radial planes within the outer regions of the chamber.

3. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, intake and discharge valves mounted in said hub section for operative movement along the central axis of said chamber, and pressure operated means for opening and closing said valves, said pressure chamber having a smoothly curved cross-sectional shape whereby gas entering the chamber through said intake valve is directed toward the sidewall of said chamber opposite to said intake valve and is then redirected radially outwardly by said sidewall to form vortices in radial planes within the outer regions of the chamber and said intake valve having a circular head and seat for the passage of gas therebetween into said chamber in all radial directions.

4. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, intake and discharge valves mounted in said hub section for operative movement along the central axis of said chamber, pressure operated means for opening and closing said valves and means disposed within the intake valve passage adjacent to the under side of the head of said valve for directing gas entering the chamber through said valve in a spiral direction about the axis of said chamber thereby to swirl the gases in said chamber about said longitudinal axis, said pressure chamber having a smoothly curved cross-sectional shape whereby gas entering the chamber through said intake valve is directed toward the sidewall of said chamber opposite to said intake valve and is then redirected radially outwardly by said sidewall to form vortices in radial planes within the outer regions of the chamber and said intake valve having a circular head and seat for the passage of gas therebetween into said chamber in all radial directions.

5. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, intake and discharge valves mounted in said hub section for operative movement along the central axis I of said chamber, pressure operated means for opening and closing said valves, electrical ignition means in said 14 chamber, and means for exciting said electrical ignition means in response to closing of intake valve.

6. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, a fluid supply passage entering one side of the chamber substantially along the axis thereof, and a fluid exhaust passage communicating with the other side of the chamber in alignment with said fluid supply passage, an intake valve responsive to the differential between the pressure in said chamber and the pressure in said fluid supply passage to open automatically when the chamber pressure is relatively low and to close automatically when the chamber pressure approaches the fluid supply passage pressure, an exhaust valve for said chamber responsive to pressure therein for automatic action, one of the valves telescoping within the other, spring means urging both of the valves toward their closed positions, and means to increase the pressure of said fluid in the chamber by the release of heat energy therein derived from a heat energy source.

7. In a device of the character described, a pressure chamber, a fluid supply passage to said chamber, an intake valve responsive to the difierential between the pressure in said chamber and the pressure in said passage to open automatically when the chamber pressure is relatively low and to close automatically when the chamber pressure approaches the passage pressure, an exhaust valve for said chamber responsive to pressure therein for automatic action, one of said valves telescoping inside the other to form a chamber that expands and contracts in response to valve operation, spring means in said chamber to urge both of the valves toward their closed positions, means to increase the pressure of said fluid in the chamber by the release of heat energy therein derived from a heat energy source, and an autorotation means for said intake and discharge valves.

8. In a device of the character described, a pressure chamber, a fluid supply passage to said chamber, an intake valve responsive to the differential between the pressure in said chamber and the pressure in said passage to open automatically when the chamber pressure is relatively low and to close automatically when the chamber pressure approaches the passage pressure, an exhaust valve for said chamber responsive to pressure therein for automatic action, one of said valves telescoping inside the other toform a chamber that expands and contracts in response to valve operation, spring means in said chamber to urge both of the valves toward their closed positions, means to increase the pressure of said fluid in the chamber by the release of heat energy therein derived from a heat energy source, and an autorotation means for said intake and discharge valves, said autorotation means including a spiral spline connection between the intake and discharge valves.

9. In a pressure generator, a casing having a pressure chamber therein, fluid supply and discharge passages communicating with said chamber, an intake valve for the supply passage and an exhaust valve for the discharge passage, spring means urging the intake and exhaust valves toward their closed positions, and a spirally splined connection between the intake and exhaust valves whereby relative longitudinal movement between said valves results in autorotation thereof for effective seating of said valves.

10. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having across-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded 7 section of greater depth forming the perimeter of said chamber, intake and discharge valves mounted in said hub section for operative movement along the central axis supply passage and a coolant exhaust passage substantially co-axial with the longitudinal axis of the pressure chamber.

11. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a; generally rounded section of greater depth forming the perimeter of said chamber, intake and discharge valves mounted in said hub section for operative movement along the central axis of said chamber, pressure operated means for opening and closing said valves, a cooling chamber completely enclosing the pressure chamber, and means for circulating a coolant through said cooling chamber including a coolant supply passage and a coolant exhaust passage substantially co-axial with the longitudinal axis of the pressure chamber, the coolant discharge passage communicating with the discharge passage for the pressure chamber through a venturi whereby the coolant forms a protective layer about the heated gases discharged from the pressure chamber.

12. In a pressure generator, a'casing having a pressure chamber, intake and discharge valves for admitting gas to and discharging gas from said chamber, means responsive at least in part to the pressure in said chamber for actuating said valves, a fuel injecting device for supplying fuel to said chamber, said device being responsive to pressure in said chamber, said fuel injection device comprising a fuel metering cylinder, a piston in said cylinder biased toward a metering stroke by pressure in said chamber and spring biased in the other direction, and an injection nozzle of the pressure actuated type in said chamber communicating with said metering cylinder.

13. In a pressure generator, a casing having a pressure chamber, intake and discharge valves for admitting gas to and discharging gas from said chamber, means responsive at least in part to the pressure in said chamber for actuating said valves, a fuel injecting device for supplying fuel to said chamber, said device being responsive to pressure in said chamber, said fuel injection device comprising a fuel metering cylinder, a piston in said cylinder biased toward a metering stroke by pressure in said chamber and spring biased in the other direction, an injection nozzle of the pressure actuated type in said chamber communicating with said metering cylinder and means for adjusting the length of the piston stroke to thereby vary the amount of fuel injected through said nozzle by movement of said piston in response to pressure in said pressure chamber.

14. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, intake and discharge valves mounted in said hub section for operative movement along the central axis of said chamber, pressure operated means for opening and closing said valves, a fuel injection device for introducing,

fuel into said chamber, said fuel injection device comprising a fluid metering cylinder, a piston in said cylinder movable toward a metering stroke in response to a predetermined pressure in the pressure chamber and resilient- 1y biased in the other direction and a plurality of injection nozzles of the pressure actuated type suitably distributed "16 about said chamber, said nozzles being in communication with said fuel metering cylinder.

15. A pressure chamber of generally circular shape having an inlet positioned on the central axis of said chamber, an intake valve for the inlet to said chamber to admit gas therethrough to said chamber, means to supply gas to said inlet including a passage leading thereto, said chamber having a side wall opposite said inlet extending generally radially from said axis to direct the gas entering the chamber through said inlet outwardly in every radial direction about said axis, and means disposed within said passage 7 generally adjacent to the inlet for directing gas entering the chamber in a spiral direction about said axis to thereby increase the turbulence of the gas within said chamber.

16. A pressure chamber of generally circular shape having an inlet positioned on the central axis of said chamber, an intake valve for the inlet to said chamber to admit fgas therethrough to said chamber, means to supply gas to said inlet including a passage leading thereto, said chamber having a cross-sectional shape such that the side walls of the chamber terminate in a generally rounded section forming the perimeter of the chamber with the side wall opposite to the inlet extending generally radially from said axis to direct the gas entering the chamber through said inlet outwardly in every radial direction about said axis to form vortices at the perimeter of said chamber, and means disposed within said passage generally adjacent to the inlet for directing gas entering the chamber in a spiral direction about said axis to thereby increase the turbulence of vthe gas within said chamber.

17. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, intake and discharge valves mounted in said hub section for operative movement along the central axis of said chamber, pressure operated means for opening and closing said valves, and an ignition means for said chamber.

18. In a pressure generator, a casing having a pressure chamber, intake and discharge valves for admitting gas to and discharging gas from said chamber, means responsive at least in part to the pressure in said chamber for actuating said valves, a fuel injecting device for supplying fuel to said chamber, said device being responsive to pressure in said chamber and means to supply fuel under pressure to said fuel injection device, said fuel injection device comprising a fuel metering cylinder, a piston in said cylinder biased toward a metering stroke by pressure in said chamber and spring biased in the other direction, an injection nozzle of the pressure actuated type in said chamber communi-cating with said metering cylinder, and means for adjusting the length of the piston stroke to thereby vary the amount of fuel injected through said nozzle by move- 'ment of said piston in response to pressure in said pressure chamber. 7

19. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said cham ber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, intake and discharge valves mounted in said hub section for operative movement along the central axis of said chamber, pressure operated means for opening and closing said valves, a fuel injection device for introducing fuel into said chamber, said fuel injection device comprising a fluid metering cylinder, a piston in said cylinder I movable toward a metering stroke in response to, a predetermined pressure in the pressure chamber and resilientl y biased in the other direction and an injection nozzle 17 of the pressure actuated type, said nozzle being in communication with said fuel metering cylinder.

20. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross-sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, intake and discharge valves mounted in said hub section for operative movement along the central axis of said chamber, pressure operated means for opening and closing said valves, a fuel injection device for introducing fuel into said chamber, said fuel injection device comprising a fluid metering cylinder, a piston in said cylinder movable toward a metering stroke in response to a pre-determined pressure in the pressure chamber and resiliently biased in, the other direction, a plurality ofinjection nozzles 'of the pressure actuated type suitably distributed about said chamber, said nozzles being in communication with said fuel metering cylinder and means to supply said fuel injection device with fuel under pressure for injection thereby into said chamber. 7

21. In a pressure chamber, means to form a charge of combustion supporting pressurized gas in said chamber, a fuel injection device responsive to rise in pressure in said chamber due directly to the induction of the pressurized gas that forms the charge therein to inject fuel into said chamber to form with said charge a combustible mixture, means to ignite or explode said combustible mixture, and means to discharge the resultant combustion product from said chamber.

22. In a pressure chamber, means to form a charge of combustion supporting pressurized gas in said chamber, a fuel injection device responsive to the rise in pressure in said chamber due directly to the induction of the pressurized gas that forms the charge therein to inject fuel into said chamber to form with said charge a combustible mixture, means to ignite or explode said combustible mixture, means to discharge the resultant combustion product from said chamber and means to supply fuel under pressure to said fuel injection device. v.

23. In a pressure chamber, means to form a charge of combustion supporting pressurized gas in said chamber, a fuel injection device responsive to the rise in pressure in said chamber due directly to the induction of the pressurized gas that forms the charge therein to inject fuel into said chamber to form with said charge a combustible mixture, said injection device including one or more injection nozzles in communication with said fuel injection device and suitably disposed in said chamber, means to ignite or explode said combustible mixture, means to discharge the resultant combustion product from said chamber, and means to supply fuel under pressure to said fuel injection device.

24. In a pressure chamber, means to form a charge of combustion supporting gas in said chamber, said gas being controlled to a temperature suflicient to vaporize a fuel to form therewith a combustible mixture, a fuel injection device responsive to the rise in pressure in said chamber due to the formation of the said gas charge therein to inject a portion of a. total fuel charge thereinto to form with said gas charge a combustible mixture, means to ignite or explode said combustible mixture, said fuel injection device being thereafter responsive to the rise in pressure due to combustion of said combustible mixture to inject the remainder of said fuel charge into said chamber for spontaneous ignition thereof to thereby secure a further rise in pressure and temperature of the contents of said chamber, and means to discharge the resultant combustion product from said chamber.

25. In a pressure chamber, means to form a charge of combustion supporting gas in said chamber, said gas being controlled to a temperature suflicientto vaporize a fuel to form therewith a combustible mixture, a fuel injection 18 device responsive to the rise in pressure in said chamber due to the formation of the said gas charge therein to inject a portion of a total fuel charge thereinto to form with said gas charge a combustible mixture, means to ignite or explode said combustible mixture, said fuel injection device being thereafter responsive to the rise in pressure due to combustion of said combustible mixture to inject the remainder of said fuel charge into said chamber for spontaneous ignition thereof to thereby secure a further rise in pressure and temperature of the contents of said chamber, means to discharge the resultant combustion product from said chamber, and means to supply fuel under pressure to said fuel injection device.

26. In a pressure chamber, means to form a charge of combustion supporting gas in said chamber, said gas being controlled to a temperature sufiicient to vaporize a fuel to form therewith a combustible mixture, a fuel injection device responsive to the rise in pressure in saidchamber due to the formation of the said gas charge therein to inject a portion of a total fuel charge thereinto to form with said gas a combustible mixture, said injection device including one or more injection nozzles in communica tion with said fuel injection device and suitably disposed in said chamber, means to ignite or explode said combustible mixture, said fuel injection device being thereafter responsive to the rise in pressure due to combustion of said combustible mixture to inject the remainder of said fuel charge into said chamber for spontaneous ignition thereof to thereby secure a further rise in pressure and temperature of the contents of said chamber, means to discharge the resultant combustion product from said chamber, and means to supply fuel under pressure to said fuel injection device.

27. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, a fluid supply passage entering one side of .the chamber substantially along the axis thereof, afluid exhaust passage communicating with the other side of the chamber in alignment with saidfluidsupply passage, intakeand discharge valves for said passages mounted in said hub section for operative movement along the central axis of said chamber, and pressure operated means for opening and closing said valves. 7

28. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being pro-.

vided with a hub section at the central axis of said chamber, said chamber having a cross sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generallyrounded section of greater depth forming the perimeter of said chamber, a fluid supply passage entering one side of the chamber substantially along the axis thereof, a fluid exhaust passage communicating with the other side of the chamber in alignment with said fluid supply passage, intake and discharge valves for said passages mounted in said hub section for operative movement along the central axis of said chamber, a cooling chamber completely enclosing the pressure chamber, and means for circulating a coolant through said cooling chamber including a coolant supply passage and coolant exhaust passage substantially coaxial with the central axis of the pressure chamber.

29. In a pressure generator, a casing having a substantially circular pressure chamber, said casing being provided with a hub section at the central axis of said chamber, said chamber having a cross sectional shape such that the sidewalls of the chamber diverge outwardly in a radial direction from said hub section to a generally rounded section of greater depth forming the perimeter of said chamber, a fluid supply passage entering one side of the chamber substantially along the axis thereof, a fluid exhailst passa ge communicating with'the dthens ide of the chamber in alignment with; saidfluid supply passage, intakan'd discharge valves for said passages mounted in s'aid'hub section for operative movement along the central axis of said chamber, a cooling chamber completely enclosing the pressure chamber, and means for-circulating a coolant through said cooling chamber including a coolant supply-passage and coolant exhaust passage substantially concentric with the fluid supply passage and fluid exhaust passage respectively.

30. In a pressure generator, a casing having a substantially circular pressure chamber, said" casing being provided with a hub sectionat thecent ral axis of said chainber; a fluid'supply passage entering one side of the chamber substantially along the axis therebf, a fluid exhaust passage-communicating with the other side of the chamber in alignment with said fluid supply passage, intake and dicliargevalves forsaid passages mounted in said hub seetio nifo r operative movement along 'the central axis of satd charnbe'r; pressure operated meahs for opening and closing saidvalves, a cooling chambercotnpletely enclostag thep'ressurechamber, and means for circulating a coblan't throughsaid cooling chamber including a coolant supply passage andcoola nt exhaust passage substantially concentric with the fluid supply passage and fluid exhaust passagerespectively.

31'. In a-pres'sure generatona casing having a substantially circular pressure chamber, said casing being provided with a hub sction at the central axis of said chain benafluid s upply passage'enteringone side of the chamher substantially 'along the axis thereof, a fluid exhaust passagecommunicatin g with the other side of1the cham her in alignment with said fluid supply passage, intake and discharge van/ester said'pa'ssages' mount ed in said hub sectionfor operative movement along the central axis of said chamber, pressure operated means for opening'and closing said valves, a cooling chamber completely enclosing the pressure chamber, and means for circulating a coolant through 'said cooling chamber including a coolant supply passage'ahd coolant exhaust passage substantially concentric with the fluid supply passage andfluid exhaust passage respectively, th'ecoolant discharge passage communicating with the discharge passage for the pressure chamber through a Venturi whereby the coolant forms a protective layer about the heated gases discharged from the pressure chamber.

32; In a pressure generatoiga casing having a pressure chamber of constant volume,-means including a sourceof gasu'nderpre'ssurc and a gas-supply passage communicating' with-said chamber through an intake port for foi'ming a gaschai'g'e-in said chamber, gas-intake means including an; intake valve for said port responsive to the differential between the pressure condition in said chamber and the pressure "condition insaid gas su ply passage "to open the .valve; said gas-discharge means being responsive to pressure in saidchambeito open said discharge valve surematically when the pressure insaid chamber substantially exceeds the chamber pressureat which said intake valve closes, and a fuel-injection device for supplying fuel to said chamber, said device including operating-means there for responsive to the rise in pressure in said chamber dun ing and as a result er the in'troductio-nof the gas charge therein, said operating means being initiated at apfefssure infsaid chamber that'is equalto or less than the'chambei pressure at which'said intake valve closes 33'. The arrangementbf claim 32 wherein the first named-meansthereinincludes means for variably controlling the rate of flow of gas into said chamber to there by determine the cycle rate of operation'of the 'gerierator.

References Citedin the file of this patent UNITED STATES PATENTS 7043.374 Raymond July 8, 1902 1,201,533 Wackenhuth Oct. 17, 1916 1,387,166 Paws-Martinez Aug. 9, 1921 1,586,006 Rochefort May 25,1926 2,090,431 Aumack May 7, 1935 2,139,284 Rieseler- ;a ;ee Dec. 6, 1938 2,230,920 Wirtsen Feb. 4, 1 941 72,272,094, Murphy Feb. 3, 194-2 2,393,589 Compton et a1. Jan; -29, 1 946 2,417,835 Moore 1;. Mar/25,, 1947 2,427,845 Forsyth Sept; 23,1947 2,429,005 Watson et a1. Oct. 14; 194 2,434,298 Truax- -2 Jan 13, 1948 2,522,945 Gongwer :Sept. 19, 1950 2,543,758 Bodine Man 6, 1951 2,546,966 Bodine Apr; 3,195] 2,557,128 Magill {one 19, 1951 2,578,596 Rieck Dec. 11, 1951 2,631,426 Jewett Mar. -17, 1953 2,635,421 Blum Apr. 21, 1953 FQREIG PA ENTS Bf t'tf f-i'fi'i 19.14 Great Britain Mar. 6, 1922 Great Britain Sept, 3, 1 934

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