US2259013A - Apparatus for producing power - Google Patents

Description

Oct. 14, 1941. E. TAYLOR APPARATUS FOR PRODUCING POWER Filed May 24, 1939 6 Sheets-Sheet 1 INVENTOR EDI VIN 7 4VZ 0 ATTORNEYS Oct. 14, 1941. E, TAYLOR 2,259,013

APPARATUS FOR PRODUCING POWER Filed May 24, 1959 6 Sheets-Sheet 2 ATTORNEY E. TAYLOR APPARATUS FOR PRODUCING POWER 6 Sheets-Sheet 3 Filed May 24, 1959 EOW/A/ 74%01? 9 W ATTORNEYS 6 Sheets-Sheet 4 NS W I INVENTOR &

EDW/IV 754% 0/? BY MMMQ ATTORNEYS Oct. 14, 1941. E. TAYLOR I APPARATUS FOR PRODUCING POWER Filed May 24, 1939 Oct. 14, 1941. A L 2,259,013

' APPARATUS FOR PRODUCING POWER 1 INVENTOR EDWIN Til 10R ATTORNEYS Oct. 14, 1941.

E. TAYLOR APPARATUS FOR.PRODUCING POWER Filed May 24, 1939 6 Sheets-Sheet 6 a g i ,0 4 6 muvmagaam Z .6 3 W50 U 7 0 4 %m "0!, 0 9 7 fiwm Qfi 2 g: 5 1 9% a 4 m 6 Maw s .9 flu 7 r a Mr} f V y INVENTOR EQWl/V 747101? ATTORNEYS Patented Oct. 14, 1941 pairs s .ATENT osrics APPARATUS FOR PRODUCING POWER Edwin Taylor, Brooklyn, N. Y., assignor of twofifths to William F. Doyle, Summit, N. J.

Application May 24, 1939, Serial No. 275,465

(Cl. 1 2l-144) 4 Claims.

It is an object of the present invention to provide an apparatus consisting of arcombination of cooperative elements whereby a substantially theoretical amount of heat is liberated during the oxidation of a fluid fuel and whereby the thus liberated heat is transformed into useful work with increased efficiencies. The invention in a particularly advantageous embodiment comprehends an improved means for controlling the admission cf the motive power fluid to the engine cylinders, thus controlling the operation of the engine. The motive power fluid produced and used in my improved engine assembly comprises a mixture containing products of complete combustion of a liquid or gaseous fuel, inert gases,

and a volatilized condensable liquid, at a pressure substantially in excess of atmospheric pressure and at a temperature substantially-less than the combustion temperature. The entire amount of heat generated in the complete combustion of the fuel is carried in the form of sensible heat and of latent heat of vaporization, the large quantities present in the latter form serving to maintain at a higher level the pressure curve of the motive power fluid during its expansion in the prime mover portion of the apparatus.

It has previously been proposed to operates ternal combustion engines by subjecting hot products of combustion to contact with water to produce steam, and to expand the thus produced gas-steam mixture in the working cylinders of the engine. In spite of the fact that such methods are in several respects more advantageous than those commonly used in current steam engine and internal combustion engine practice, they have not been widely employed, due primarily to the incomplete nature of the fuel combustion. Such incomplete combustion introduces carbon monoxide into the gas-steam mixture, making its use hazardous, and further produces sooty, carbonaceous materials which deposit in loss in efliciency and frequently completely clogging the apparatus.

Th present invention provides a means ior producing power which, as more completely described below, eliminate completely or greatly minimize the above described difiiculties and inefficiencies attending the use of steam engines or the hitherto proposed methods of using a gas.- st m m xtu e di to m nv n ion a fluid fuel is continuously and completely burned between catalytic plates of novel arrangement; the hot products of combustion substantially free of products of incomplete combustion are subjected to contact with a volatile liquid medium, for example water, whereby a motive power fluid medium is produced having any desired temperature below the combustion temperature and wherein the sensible heat lost in th cooling is retained in the form of latent heat of vaporization; and the thus produced pressurefluid me dium is supplied to a prime mover mechanism through suitable controlva lves to produce power by expansion to substantially atmospheric pressure without substantial loss of heat. The invention further comprehends a particularly effective means associated with the prime mover for supplying the fluid fuel and the combustion-supporting medium to the combustion area defined by v the said catalytic plates under a pressure in excess of that obtaining in the remainder of the system.

The control mechanism for regulating the admission of pressure fluid medium to each of the cylinders which is included in the present inven- Piston valves which operate to cut off the ad- ,rnission of the pressure fluid to a cylinder by mechanical action resulting from their attachment to or synchronization with the movement of the main piston are known. Various methods for regulating the time of cut-off have been suggested but have all involved a complicated movable regulating means, most if not all of which have failed to produce the desired instantaneous cut-oil". Mechanical acting pistons in general result in decreased efficiencies due to the lag in effecting a complete closure of the connection to the cylinder, which causes a throttled down steam admission. The present invention provides a simple adjustable means, stationary with rethe engine and connection means causing marked 9 sheet to the pist n valve, va yin the point tion will be had by reference to the drawings which illustrate typical horizontal and vertical types of engine made in accordance with the invention. Like reference numerals have been employed throughout the drawings to designate corresponding parts.

In the drawings:

Figure 1 illustrates a generator for producing the pressure fluid medium supplied to the engine in accordance with the invention, and is a vertical section taken along the line I-I of Fig. 2.

Figure 2 is a transverse section of a horizontal type engine, the generator being shown in elevation and the prime mover portion being broken away, and is taken along the line 2-2 of Fig. 3.

Figure 3 is a horizontal plan view partially in section along the line 3-3 of Figure 2, which illustrates the prime mover portion of the engine.

Figure 4 is an enlarged vertical section along the line 44 of Figure 3, and shows in detail the cut-off valve mechanism and control means in an advanced position.

Figures 5, 6 and 7 are diagrammatical representations showing the relative positions of the principal cut-01f valve parts at the time of admission, cut-off and release respectively.

Figure 8 is a side elevation of a vertical type engine, parts being broken away and parts shown in vertical section.

Figure 9 is a vertical axial section of a vertical prime mover cylinder and attached cut-off valve taken on the line 99 of Figure 8.

Figure 10 is a plan view of the cylinder of Fig ure 9 along the line Ill-II] showing the relation I3 and extends through an opening in plate I4,

into the flat combustion zone I5 defined by plates I4 and I5. An atomizer such as that illustrated injects a substantially flat disc-like sheet of atomized fuel and air between two layers of additional air radially outwardly between the closely,.

spaced contact surfaces I4 and I5. Such an atomizer is described and claimed in a co-pending application, Serial No. 275,463, filed of even date herewith. In an atomizer of this type oil may be introduced through pipe H into chamber from which it feeds downwardly through the grooves in the fluted cylinder I8 which is movable vertically within the cylindrical wall I9, and from which depends a conical block 22. A regulated quantity of oil is thus permitted to flow through the annular opening between the bottom beveled edge of wall I9 and the surface of the conical block, and outwardly over the surface of said conical block. Air introduced through pipe I2 into the annular chamber 2I passes with the oil through the annular beveled exit 22 and atomizes the fuel as it passes therethrough and particularly as it reaches the sharp peripheral edge of the cone. A portion of the air from chamber 2I passes through the tubular ports 23 situated in the conical block and thence radially outwardly across the surface of the base of the cone, being diverted in this direction by the opposing plate I5. When this additional air reaches the periphery of the base of the cone, an increased atomization isproduced. The passage of air through these ports results in the further important advantage that the first point of contact between the fuel and the contact surface is extended radially outwardly, thus preventing the possibility of the deposition of carbon on the coolest portion of the contact surface. A portion of the air passing through the beveled exit 22 remains above the oil spray, thus delivering the fuel to the contact surfaces between two layers of combustion-supporting gas. The conical block in the atomizer here illustrated has an angle of which, with the arrangement as shown, is appropriate to produce a fiat disc-like sheet of atomized fuel and air. In generators in which the two closely spaced contact surfaces assume a slightly dome-shaped or conical structure, the combustible mixture being injected at the apex, conical angles somewhat less than 120 are advantageously employed. The atomized fuel-air mixture is ignited by an ignition device 24 which may be of the jump-spark type or, as here'shown, a hot wire. This wire may advantageously be extended to form a ring surrounding the atomizing head, thus insuring complete instantaneous ignition throughout the combustion area. The fuel-air mixture in expanding radially outwardly between surfaces I4 and I5, which may be spaced at a distance of about A; to inch, is completely oxidized. The contact surfaces which define a flattened circular zone are with particular advantage composed of a refractory material in which is incorporated a combustion-catalyzing substance such as an oxide of chromium. Extensions of plates I4 and I5 form a connecting annularvertical zone 25 and a lower horizontal zone 26 which extends inwardly to connect with a second vertical annular chamber 21 extending to the bottom of a cupshaped member 28 which is releasably secured to the outer generator cover 29, and forms with said outer cover a container for the generator elements. Supported on the bottom of this cupshaped member are annular plates 30 and 3I which are concentrically arranged extensions of contact plates I4 and I5 and serve to support them. These supporting plates may be made of any suitable heat and pressure resistant material such as an alloy steel or other appropriate alloy.

A water supply pipe 32 leading from a water pump is connected to a thermostatic valve 33 which serves to regulate the inlet of water to the generator responsively to the temperature of the water in the bottom thereof. This valve may be of any suitable type, but is here shown as comprising a fixed partition 34 provided with Openings 35, a sliding partition 36 provided with openings 31 which is under the yieldable pressure of a compression spring 38. This spring serves to move the openings 31 in the slidable partition out of registry with the ports 35 to an extent dependent on the opposing pressure of a sylphonic bellows 39. The pressure of the thermostatic fluid in the bellows is dependent on the temperature of the water adjacent the bulb 40 which extends through the bottom of the cupshaped member 28. When the temperature of the water rises, ports 35 and 31 are brought more nearly in alignment, and an increased proportion of water passes from delivery pipe 32 into connecting pipe 4| which connects with outwardly and upwardly extending branch pipes 42 which pass through the stay bolts43 serving to reenforce the outer generator walls 29. Branch pipes 42 enter an annular chamber 44 adjacent to and surrounding the lower portion of the atomizer. Incoming water passes from chamber 44 through perforations in the bottom thereof into a horizontal basin 45 situated between the outer wall 29 and the top portion of supporting plate 39. overflowing from this basin through peripheral notches 46 and passing over a mesh screen 4? which surrounds the cylindrical portion of plate 39, the water enters the vertical annular chamber 48, passing from and to cham ber 21 and in turn to chamber 49 through radially spaced openings 59 and situated at or near the bottom of supporting plates 30 and 3|. These openings permit the maintenance of a common liquid level in the three adjacent annular vere tical chambers. The incoming water in its passage through basin 45 and over screen 11 serves to cool the supporting plate 30 and is in turn preheated. The dead gas space between plate 39 and the outer wall of the generator serves to insulate the generator and prevent the radiation of any substantial proportion of heat to the atmosphere. The hot products of combustion pass through chambers and 25 and into and through the continuously renewed body of water contained in the cup-shaped container 28. Passing through the openings 5! the hot gases volatilize a portion of the Water to form steam, thus transferring a portion of their sensible heat to latent heat of vaporization. The resulting gassteam mixture comprising the motive power fluid passes upwardly through chamber 49, outwardly in chamber 52 around the edge of a dished circular baiile 53 and thence inwardly to the openings 55 situated at the top of a down-comer pipe 55 which opens into the top wall of and midway of the length of a large tubular manifold 55. Bafiie 53 prevents the entrainment of any substantial amount of water with the pressure fluid medium. Stand pipes 51 return any water which may collect on the baffle to the main body of water in container 28.

In an engine of the type here illustrated, the outer ends of the manifold pipe 56 are connected to connection pipes 58. These connection pipes, as shown in Figures 3 and 4, are bifurcated be.- low to form flattened branches 59 providing a connection through annular chambers .69 to a cylindrical cut-off valve 6|.

The flow of the pressure fluid medium from the generator to the main cylinders of the engine; and the exhaust from the main cylinders on the return stroke of the main pistons is automatically regulated and controlled by the special type of cut-off valve mechanism best shown 'in Figure 4 and illustrated diagrammatically in Fig.- ures 5 to '7. As illustrated in Figure 4, the automatic cut-off valve is contained within a housing 52. The gas-steam mixture from the generator is introduced into fiat annular space 60 situated approximately midway of the housing 62, and from there into the main valve chamber as described below. The effective area of the exit 63 from chamber 69 into the valve chamber which surrounds the housing 62 is approximately equal :to the area. of delivery pipe .58, as a result of This adjustable" sleeve comprises axially spaced v rings 64 and 65' integrally connected by the cylindrical web 66 provided with circumferential ports 61. Said sleeve may be regulated and set at any desired axial position by means of rod 68. The peripheral surfaces of rings M and 65 slidably engage the inner surface of valve housing 62. The inner surfaces of the said rings slidably engage the outer surface of a piston valve mechanism presently to be described. The valve housing 62 is providedwith oppositely disposed extensions 69 and. 10, which may be integrally connected therewith. The said extensions 59 and Hi slidably support and engage the axially spaced piston heads H and 12, which are rigidlyjoined to form a unitary structure by a cylindrical wall 73; Ihemain housing 62 is provided near its outer end with peripherally spaced angled port openings 14 which connect with the adjacent main cylinder 15 through extension 16 which surrounds the valve chamber and forms an annularspace connecting therewith. Piston head 1 l, slidable in extension 69, reciprocates past the ports M and the annular chamber 15, and is of a dimension greater than the width of openings into chamber 16. The cylinder wall '53 adjacent the piston head H isprovided with peripheral openings 11, which are in turn adjacent an inwardly extending portion 78 forming a valve seat for valve 19 carried by a valve stem 89. Supporting the valve head and stem and permitting the same to be brought into and out of seating engagement with valve'seat 18 is a spider guide member 8| and a piston slide 82 which reciprocally engages the inner surface of' cylindrical wall 13 and which has an axial boss 83 which prevents the entire surface of valve piston 82 from coming in contact with piston head I2, thus insuring at all times the existence of a flat circular space 84 between the two piston heads. Such an arrangement serves to maintain opencommunication with a series of port openings 85 formed in the cylindrical wall 73 adjacent the head of piston 12. The sliding cylindrical wall 13 is provided approximately midway of its length with port openings 89 through which motive power fluid from opening .61 passes into the central valve space for operating the valve and controlling the admission of the said fiuid to the main cylinder '15 via openings Ti and 14. :Situated near the rear of valve housing 62 is an annular space 99 between said housing and the slidable piston 12 or connecting cylinder 7.3. As the piston assembly moves to the right, port openings 85 move past control sleeve 64 and are exposed to connection with said annular chamber 99,. thusproviding an exhaust connection through pipe I09 for the gas-steam mixture which entered chamber 84 at the time when ports 85 were in connection with gas-steam inlet 63. A connection Iiil is provided from the space ahead of the. forward sleeve portion 65 to the exhaust pipe I09 to remove any steam which may have escaped into the space ahead of the sleeve. Valve piston head 72 carries a wrist pin 8-! pivotally connected with connecting rod 83 foractuating-the cut-off valve structure as described below.

main c l nders and dr v n m hanism .of

the horizontal type prime mover being described are best shown in Figures 2 and 3; As shownin the horizontal plan view of Figure 3, the main prime mover cylinders I5 arey'connected in coaxially aligned pairs in such a way that a double acting double faced piston comprising two piston heads 89 rigidly connected by rods 90 may reciprocate in unison in the interconnected main cylinders shown on each side of the central longitudinal plane of this figure. Coaxially aligned with each of pistons 89 and an integral part thereof, are air-compressing pistons 9| each reciprocating in a cylinder 92 of smaller diameter connecting with each of main cylinders 15, and each having an area so proportioned with respect to the main piston as to supply combustion-supporting medium to the generator at a pressure slightly in excess of the pressure, in the generator. The end of each air-compressing cylinder is provided with a discharge valve 93 for delivering compressed air to connection pipe 94. Said connection pipe is connected with connection pipe I2 for delivering compressed air to the atomizer shown in Figure 1. Each of the air-compressing piston heads is provided with an air inlet valve 95 for admitting air to the compression chamber on the return stroke of the compression piston 9|. A connecting rod96 is pivotally connected at one end to a wrist pin carried by one of each pair of air-compressor pistons and at the other end to a crank-pin attached to spaced sections 91 of the corresponding crank-arm on the main drive-shaft 98. journalled in the exterior walls of the main cylinders. The main driveshaft may be hollow to decrease'weight and to provide an air inlet for supplying the air-compressor cylinders through valve 95. Such intakes should be within the limits of travel of the inner faces of the main pistons, and may advantageously assume the form of a series of peripherally spaced openings in alignment with the axis of the main drive-shaft 98. v

The operation of the improved cut-off valve mechanism of my invention will best be understood by reference to Figures 5 to '7, which illustrate diagrammatically the principle of operation of such a valve. The diagrammatic illustrations in these figures do not include certain of the details to be found in the cut-ofivalve of Figure 4, which operates on the same principle. As shown in Figure 5, the prime mover crankarm 9'! has reached its forward dead center position. and the port opening I1; which leads to the main cylinder through connection I6, is about to be uncovered by the forward movement of piston head II. Pressure valve I9 having been opened by an excess of gas-steam pressure within the 'valve center over that present in space 84, i. e. by a positive pressure on the forward face of piston 82, admission of gas and steam to the main cylinder for the working stroke begins and continues until the several parts of the cut-off valve have reached the relative positions shown in Figure 6. As there shown, the valve piston I9 has just come into engagement with valve seat I8, due to admission of live gassteam mixture behind the piston 82 through port openings 85, and the connection 16 has again been closed by the slidable valve cylinder, as has likewise the connection between the valve center and inlet pipe 63. The position shown in Figure 6 represents the forward limit of motion of the cut-off piston assembly. As the clearance space I6 connecting with the main cylinder is opened to the exhaust on the return stroke of the valve piston,

the pressure valve I9; as shown in Figure 7, leaves itsseat due to the entrance of the gassteam mixture into the valve center through opening 86, and to the release to exhaust through chamber 99 and pipe I00 of the gas-steam mixture which had been acting on the rear face of piston 82. By connection with chamber 99 the pressure in the space 84 is reduced to substantially atmospheric pressure. During this period the main cylinder I5 remains open to the exhaust through pipe 69, until on the return stroke piston 'II again covers port 16. Relatively stationary control means 64 adjustable axially in the valve mechanism by means of rod 68, which is here shown as a small block and in Figure 4 as a sleeve or ring, makes possible the instantaneous cut-off of the gas-steam mixture at any desired point in the stroke of the main piston 89. Such an arrangement as more fully explained below is an important feature of the sliding outoff valve here described. This control member is effective in determining the point of cut-off and thus the amount of motive power fluid supplied to the main prime mover cylinder for each stroke which in turn governs the speed of the engine. On the forward motion of the valve assembly the pressure fluid will pass valve I9 and thus be admitted to the prime mover cylinder until the point at which ports 05 clear the front edge of control member 64. At this point gas-steam mixture will enter space 84 behind piston 82 and equalize the pressure therein and immediately thereafter the force of the entering gas-steam mixture will instantaneously close valve 19. On the returnstroke the valve will open at the point at which the ports 85 clear the rear edge of control member 94 and establish connection to the exhaust, thus permitting the excess pressure on the forward face of piston 72, which is larger than valve piston 79, to open the valve mechanism. From this description it will be understood that the time of introduction of live gassteam mixture to space 84, and its escape therefrom will be regulated by the position of control means 64, which remains fixed with respect to the reciprocating valve mechanism.

The relationship between the operation of the main pistons and drive shaft and the cut-off valve is illustrated in Figures 2 and 4. As there shown, connecting rod 88 for actuating the sliding valve is pivotally connected to crank-pin I02 which projects from crank-arm I03 provided with a counterbalancing arm. The crank-arm is keyed to one end of valve-operating shaft I04 journalled in spaced standards I055 As shown in Figure 3, there are four valve housings 6| for controlling the admission and exhaust of motive power fluid in a horizontal engine of this type which must be properly coordinated. Valve pistons I2 on each side of the central longitudinal plane of Figure 3 are rigidly joined by rods I06 so that they will move in unison. Keyed to the valve shaft I 04 between the standards I05 is a chain gear I01 driven by an endless chain I08. As best shown in Figure 4, the endless chain I08 is driven by main drive shaft 98 through a chain pinion I09. Incorporated with this actuating means for operating the valve mechanisms may be a means for adjusting the positions of the valves with respect to the main pistons of the engine, for example to reverse the direction of the main drive shaft. A radial arm IIO serving as a reverse lever is attached to a sleeve III oscillatably mounted upon and movable relatively to the crank-shaft 98. A radial post H2 carried ful as an automobile or marine engine.

by the sleeve; III, s-erves'to journal a gear H3, over which the endless chain I08 is passed. Also mounted on the sleeve III is a hollow post H4 within which a rod I I5 is yielclable longitudinally under the resistance of spring I I6. Journalled in the outer end rod H5 is a gear II'I over which endless chain I08 also runs. From this description it will be understood that an angular displacement of the lever III] and a corresponding movement of sleeve III will impart a displacement to the chain gear IIl'I around its axis without a corresponding movement of crank-shaft 98. Asa result the positions of the valve pistons are altered with respect to the main pistons and the engine may be' reversed.

Referring now to Figures 8 to 10, my invention is illustrated in application to an engine of the vertical type. Such an engine is particularly use- According to the embodiment illustrated in Figure 8, a three-cylinder engine is supplied with a motive power fluid produced in generator I3. This generat'or is similar to the type illustrated in Figure l and operates on the same principle to produce a pressure fluid medium substantially free of products of incomplete combustion. The pressure fluid medium is discharged through pipe 56, 58 at any desired temperature and pressure, into cylinders I5,through cut-off valves BI. Each main cylinderis provided with a coaxially aligned extension 92 serving as a compressor for supplying compressed air to the atomizer Ill through valve 93 and manifold delivery pipe I2. Aircompressor inlet and outlet valves 93 and 95 may be similar in structure to those illustrated in Figure 3. The fuel enters the atomizer and the water enters the generator head through pipes II and 42 respectively, which are connected to individual pumps (not shown) operated from the main drive-shaft 98. A prime mover piston 89 of larger diameter than the air-compressor piston, and integral therewith, reciprocates in each of cylinders I5.

For adjusting the point of cut-off and regulating the expansion of the motive power fluid as well as providing a connection between the cylinclers and the inlet and exhaust pipes, a valve 6| is provided for each cylinder. The details of an improved valve for this purpose, which may be similar in structure to that shown in Figure 5, are shown in Figure 9. As there illustrated, a stationary control sleeve 64, 65 is adjustable by rack 68, which is activated by pinion I I9 attached to shaft IN. The valve-operating connecting rods 88 may be driven by means of crank-arms I2I in turn activated by a common drive-shaft I64 supported in bearings I22. This shaft may in turn be driven from the main crank-shaft 98 by an endless chain I68 through a hollow gear I23, which is connected with shaft I94 and prevented from moving axially thereon. A mechanism suitable for reversing the engine is illustrated as comprising a pivoted arm I24, which engages a spool member I rigidly joined to an exteriorly threaded sleeve member I26. This sleeve as shown is splined to the shaft I64 but is adapted to move endwise thereon into and out of the threaded hollow hub of gear I23. From this description it will be understood that a movement of the arm I2 imparts a rotary movement to shaft I04, not related to the movement resulting from the action of the main drive-shaft. Such an arrangement permits the adjustment of the central piston cut-ofi valves to any desired Position relative to the position of the main. drivnecessary' in actual practice.

ing pistons 89, and makes possible the reversing of the engine. Connection between the variable cut-off valves and the working cylinders is advantageously effectedthrough a hollow lug I21 projecting from the closure head of main cylinder I5, and forming passage I6. 'As illustrated in Figure 9 lug I2Iis extended to a greater relative distance from the cylinder head than would be A connection means and valve of this ty'pe'make it. possible to decrease the clearance space at .the end of the main piston stroke'and thus to further increase the efficiency of the engine.

Iclaimb 1. In a positive pressure engine assembly a valve mechanism for controlling the inlet and exhaust of the prime mover cylinders comprising an outer relatively fixed valve housing having an inletopening for thepressure fluid medium and an outlet opening connected to a prime mover cylinder, an inner relatively-movable cylindrical valve housing reciprocable in the outer housing and operatively connected with said prime mover, said inner housing being provided with a central pressure fluid. chamber adapted to provide an intermittent passage for the pressure fluid between said inlet and outlet connections, an inner piston valve assembly within the inner housing operative 'b-ylmeans'of the 'pressure fluid to close and open the passage between the inlet and outlet connections, and an adjustable relatively stationary'means for regulating the operation of said inner valve vassembly by controlling the point of admission'of pressure fluid medium whereby the time of connection between said. inlet and outlet connections may be controlled.

2 In'a positive pressure engine assembly a valve mechanism for controlling the inlet and exhaust of a prime mover cylindercomprising an outer relatively fixed valve housing provided'with at least one port opening leading to the prime mover cylinder and at least one port opening axially spaced therefrom for introducing a pressure fluid medium into the valve mechanism, an inner relatively movable cylindrical valve housing operatively connected with the prime mover, reciprocable in said outer housing and provided with front and rear closure piston heads, the front piston head being reciprocable past the port opening in the outer housing leading to the prime mover cylinder, said inner housing having a central pressure fluid chamber and a forward port opening into said chamber and adapted to be brought into and out of registry with the port opening in the outer housing leading to said cylinder to provide alternate inlet and outlet connections to the cylinder, and a midlength port opening adapted to be brought into and. out of registry with the port in the outer cylinder for introducing pressure fluid medium into the valve mechanism, an inner valve assembly operative within said inner movable housing by means of pressure fluid medium to close and open the connection between said forward and midlength openings, and an adjustable relatively stationary means for regulating the operation of said 'inner valve assembly by controlling the point of admission of pressure fluid medium whereby the time of connection between said forward and midlength openings in the inner valve housing may be controlled.

3. In a positive pressure engine assembly, a valve mechanism for controlling the inlet and exhaust of a prime mover cylinder comprising an outer relatively fixed cylindrical housing having front and rear piston guide portions connected by an enlarged cylindrical wall forming an annular pressure fluid chamber, the front piston guide being provided with a port opening leading to a prime mover cylinder and said annular chamber being provided with an inlet port opening for introducing pressure fluid medium into the valve mechanism and rearwardly thereof an exhaust opening, an outer valve assembly having front and rear piston heads connected by an intermediate cylindrical housing, said valve assembly being reciprocable in the piston guide portions of the outer housing and operatively connected with the prime mover, an annular valve seat presented inwardly from said intermediate housing and spaced axially from the front piston head, said intermediate housing being pro vided with forward port openings between the piston head and valve seat, an intermediate series of inlet port openings in its midlength portion and a series of rear port openings adjacent said rear piston head, an inner valve assembly operative by means of pressure fluid medium having a valve movable to and from said valve seat, a piston slide reciprocable in said intermediate housing between'thes aid intermediate and rear port openings and a slidably supported stem for rigidly connecting. said valve and piston slide, and a relatively stationary cylindrical slide adjustable exteriorly on said intermediate cylindrical housing within the annular pressure fluid chamber forregulating the operation of said inner valve assembly by controlling the point of admission of pressure fluid medium.

4. In a positive pressure engine assembly, a valve mechanism for controlling the inlet and exhaust of a prime mover cylinder comprising an outer relatively fixed cylindrical housing having front and rear piston guide portions connected by an enlarged cylindrical wall forming an annular pressure fluid chamber, the front piston guide being provided with a port opening leading to a prime mover cylinder and said annular chamber being provided with an inlet port opening for introducing pressure fluid medium into the valve mechanism and rearwardly thereof an exhaust opening, an outer valve assembly having front and rear piston heads connected by an intermediate cylindrical housing, said valve assembly being reciprocable in the piston guide portions of the outer housing and operatively connected with the prime mover, an annular valve seat presented inwardly from said intermediate housing and spaced axially from the front piston head, said intermediate housing being provided with forward port openings between the piston head and valve seat, an intermediate series of inlet port openings in its midlength portion and a series of rear port openings adjacent said rear piston head, an inner valve assembly operative by means of pressure fluid medium having a valve movable to and from said valve seat, a piston slide reciprocable in said intermediate housing between the said intermediate and rear port openings and a slidably supported stem for rigidly connecting said valve and piston slide, and a relatively stationary cylindrical slide assembly adjustable exteriorly on said intermediate cylindrical housing within the annular pressure fluid chamber for regulating the operation of said inner valve assembly by controlling the point of admission of pressure fluid medium, said cylindrical slide assembly having front and rear ring piston slides and a cylindrical connecting wall provided with inlet port openings in substantial registry with the port opening in said enlarged cylindrical wall, the rear slide portion being adjustable within the outer limits of travel of said rear port openings in said intermediate housing.

EDWIN TAYLOR.

CERTIFICATE OF CORRECTION.

Patent No. 2,259,015. October 1h, 19in.

EDWIN TAYLOR.

It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows: Page 2, secmd column, Iines 52 to 56, strike out the sentence "This wire may advanageously be extended to formaring surrounding the atomizing head, thus nsuring complete instantaneous ignition throughout the combustion area.";'

nd that the said Letters Patent shouldbe read with this correction therein hat the same may conform to the record of the case in the Patent Office.

Signed and sealed this 2nd day of December, A. D. 19111.

Henry Van Arsdale,

(Seal) Acting Commissioner of Patents.

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