US3528242A

US3528242A - Rotary positive displacement machines

Info

Publication number: US3528242A
Application number: US715002A
Authority: US
Inventors: Michael D Hartmann
Original assignee: MICHAEL D HARTMANN
Current assignee: MICHAEL D HARTMANN
Priority date: 1968-03-21
Filing date: 1968-03-21
Publication date: 1970-09-15
Anticipated expiration: 1987-09-15

Description

Sept. 15,1910 M. D- HARTMANN," 3,528,242

ROTARY POSITIVE DISPLACEMENT MACHINES Filed March 21, 1968 e Sheets-Sheet 1 i I INVENTOR Alzcfiael Q Hanmem.

Sept. 15, 1970 M. D... HARTMAN-N 3,528,242

ROTARY PbSITIVE DISPLACEMENT MACHINES Filed March 21, 1968 6 Sheets-Sheet 2 fly. 2.

[/VVZWTOH flg 'chael D. Hand/2262120 M. D; HARTMANN 3,528,242

Sept. 15, 1970 ROTARY POSITIVE-DISPLACEMENT MACHINES Filed March 21, 1968 6 Sheets-Sheet 5 1*- 15, 1970 M.-D. HARTMANN ROTARY POSITIVE DISPLACEMENT MACHINES 6 SheetS-Shet 4 Filed March 21, 1968 Sept. 15, 1970 M. HARTMANN 3,528,242

ROTARY POSITIVE DISPLACEMENT MACHINES Filed March 21, 1968 e Sheets-Shee t 5 [IVE/V0705 Afi/zb/zael D. Ala/ 622mm.

P 15, 1970 D. HARTMANN' 3,528,242

ROTARY POSITIVE DISPLACEMENT MACHINES Filed March 21, 1968 6 Sheets-Sheet 6 [N VE'IVTOH Michael D. Hanozazza.

U.S. Cl. 6039.61 20 Claims ABSTRACT OF THE DISCLOSURE A positive displacement rotary engine is disclosed which is capable of use as a pump, internal combustion engine, external combustion engine, fluid motor and the like. The machine includes an annular stator cavity in which a pair of rotary discs are rotated in phase and inclined relative to one another. In one arrangement the discs are generally frusto-conical in shape and contact or nearly contact along a line extending radially across their conic surfaces. The rotor discs are provided with axially aligned slots whereby they slidably engage a number of vanes, each of which conforms substantially to the entire crosssectional area of the annular cavity. Relative movement between the discs and the vanes therefor is directed substantially axially of the rotor rather than radially. Thus, the usual biasing springs necessitated by radially sliding vanes are eliminated. Moreover, a much larger positive displacement is obtained through the use of the inclined rotor discs than is possible with the eccentric rotors or irregularly shaped cavities of conventional rotary machines.

The present invention relates to positive displacement rotary machines and more particularly to a machine of the character described wherein the rotor of the machine does not have to be eccentrically located relative to the stator chamber and the rotor vanes are not spring loaded for radilly sliding movement in the rotor in order to ob tain the necessary expansions and contractions of the chambers of the machine.

The term positive displacement rotary machines, as used herein, is inclusive of internal combustion engines, external combustion engines, pumps, fluid motors, or the like having a rotary positive displacement characteristic, to which my present invention is advantageously adaptable as set forth below in the detailed description thereof.

Previous positive displacement rotary machines for the most part are typified by eccentric rotors having springloaded vanes slidably radially of the rotors into engagement with the adjacent surfaces of the stator cavity. Such rotary machines are typified by the patents to Auensen, No. 1,069,516; Doane, No. 1,255,865 and Lockhart, No. 3,176,446. A disadvantage of this form of construction lies in the limited expansion and contraction of a given combustion chamber of the engine as defined by an adjacent pair of the vanes, the intervening surface of the rotor, and the adjacent relatively moving surfaces of the stator. Thus, the expansion and contraction is limited by the degree of eccentricity of the rotor which in turn is determined by the extent of radially sliding movement of the vanes relative to the rotor on which they are mounted and usually spring loaded.

Another disadvantage of prior rotary machines lies in the probabilities of breakage in the vane loading springs and of the incorporation of sufficient foreign matter between the sliding vanes and the rotor to cause the vanes to hang up and fail to contact the adjacent surfaces of the stator cavity.

On the other hand, a somewhat diiferent type of rotary combustion engine, as typified by Wiegert, 3,117,563, employs a regularly contoured rotor mounted centrally withd S ates Patent Olfice 3,528,242 Patented Sept. 15, 1970 in an irregularly shaped stator chamber. Here again, the van s or plungers are spring loaded for sliding movement in the rotor and suffer from the same disadvantages mentioned previously. Further, the amount of expansion and contraction of the combustion chambers formed by the vanes or plungers is similarly limited by limitations imposed both by the construction of the stator cavity and of the spring-loaded rotor plungers.

However, insofar as is known, none of the previously proposed rotary combustion engines or similar rotary machines, is capable of achieving the displacement made possible by my unique rotary, positive displacement machine disclosed herein. While my rotary machine em ploys vanes to separate the expandible chambers thereof, the movement of the vanes relative to the rotor structure is effected by positive engagement with relatively rigid machine components such that the vanes must always contact the stator cavity as the rotor structure is revolved. It is therefore impossible for the vanes of my novel rotor structure to hand up because of occlusion of foreign matter or to fail to be urged into engagement with the stator cavity because of broken or defective springs or other biasing means.

An important mechanical consideration is the fact that the vanes, as they are being revolved by the rotor structure, sealingly engage non-displaceable elements of the rotary machine, which define the stator cavity, throughout their revolution within the stator cavity. The vanes thus co-extend with the entire cross-sectional area of an annular stator cavity as defined by these components. On the other hand, the displacement in my novel rotary machine, instead of being determined by radially sliding vanes, is established by a pair of generally discoidal members rotatably mounted within the stator cavity but disposed at angles to one another. Desirably, the discoidal members are geared together to ensure that they are rotated in phase. Each of the aforementioned vanes is slidably mounted in a pair of slots therfor formed respectively in said discoidal members. However, the discoidal members slide axially relative to the vanes and these are no interconnecting springs.

In one example of my invention, the discoidal members are frusto-conical in contour and are disposed for engagement or near-engagement along a line contact extending radially along their respective conical surfaces. When a pair of adjacent vanes are juxtaposed to such line contact, a minimum displacement in the chamber defined by such vanes is realized. However, when the discs have been displaced to dispose the same pair of vanes diametrically opposite to such line contact, a maximum chamber displacement is realized.

I accomplish these desirable results by providing a rotary positive displacement machine comprising a casing defining a stator chamber therein, rotor means mounted for rotation within said cavity, a plurality of vanes fitted within said cavity and slidably engaged by said rotor means, said vanes and said rotor means and said cavity defining a plurality of chambers of variable size depending upon the rotational position of adjacent pairs of said vanes about said rotor means.

I also accomplish these desirable results by providing a rotary positive displacement machine comprising a casing defining a stator chamber therein, a pair of rotor discs mounted for rotation within said stator cavity at inclined positions relative to one another, a plurality of vanes closely fitted in said cavity and slidably engaged by said rotor discs, said vanes being substantially equally spaced about said discs, said vanes and said discs defining chambers of variable size depending upon the rotational position of adjacent pairs of said vanes about said discs.

I also desirably provide a similar machine wherein said rotor discs are of frusto-conical configuration and are inclined for engagement or near engagement with one another along a contact line extending radially across their conical surfaces.

I also desirably provide a similar machine wherein said rotor discs are of frusto-conical configuration and are seal member is mounted within said casing and between said discs, said mid-seal member at least partially defining the inner periphery of said stator cavity.

I also desirably provide a similar machine wherein said mid-seal member is supported on fixed shaft means about which said rotor discs are rotatably mounted.

I also desirably provide a similar machine wherein said machine is an internal combustion engine, and said casing is provided with an ignition spark plug disposed therein for successive communication with said chambers at a position adjacent the closest approach of said inclined discs, and said casing is provided with exhaust and fuel inlet ports generally opposite from said spark plug location.

I also desirably provide a similar engine wherein said engine is provided with an external combustor, an outlet duct of said combustor being coupled to an aperture in said casing for successive communication with said combustor chambers at a position adjacent the closest approach of said inclined rotor discs, and means are provided for supplying air and combustible fuel to said combustor.

I also desirably provide a similar engine wherein a pair of suction ports are formed in said casing and disposed for communication with expanding ones of said chambers, a pair of discharge ports are formed in said casing and located for communication with contracting ones of said chambers, and means are provided for supplying torque to one of said rotor discs so that said engine operates as a positive displacement pump.

During the foregoing discussion, various objects, features and advantages of the invention have been set forth. These and other objects, features and advantages of the invention together with structural details thereof will be elaborated upon during the forthcoming description of certain presently preferred embodiments of the invention and presently preferred methods of practicing the same.

In the accompanynig drawings I have shown certain presently preferred embodiments of the invention and have illustrated certain presently preferred methods of practicing the same, wherein:

FIG. 1 is a front elevational view of one form of rotary combustion machine arranged in accordance with my invention;

FIG. 2 is'across-sectional view of the apparatus as shown in FIG. 1, with certain of the component parts thereof in elevation and other parts omitted for clarity;

FIG. 3 is another cross-sectional view of the apparatus as shown in FIG. 1 and taken along reference line III- III thereof;

FIG. 4 is a plan view of one of the rotary discs shown in FIG. 2 and taken generally along reference line IV- IV thereof;

FIG. 4A is an elevational view of the disc shown in FIG. 4;

FIG. 5 is a side elevational view of the stationary spherical wedge member forming part of the mid-seal of the stator cavity and taken generally from the right hand side of FIG. 2 with the major proportion of the intervening components having been removed for clarity;

FIG. 6 is a cross-sectional view of the wedge member of FIG. 5 and taken along reference line VIVI thereof;

FIG. 7 is a bottom plan view of the apparatus as shown in FIG. 5;

FIG. 8 is an exploded view of one of the vanes utilized in my rotary combustion engine;

FIG. 9 is a right side elevational view of the vane shown in FIG. 8;

FIG. 10 is a bottom plan view of the vane shown in FIG. 8;

FIG. 11 is an elevational view, with parts removed, of one of the casing sections of an external combustion rotary engine arranged according to the invention;

FIG. 12 is a side elevational view of the apparatus shown in FIG. 11;

FIG. 13 is a front elevational view, with parts removed of a casing section of a novel positive displacement pump arranged in accordance with my invention; and

FIG. 14 is a side elevational view of the apparatus shown in FIG. 13.

Referring now more particularly to FIGS. 1-3 of the drawings, the exemplary arrangement of my novel positive displacement rotary machine shown therein is arranged as an internal combustion engine 20 and comprises a substantially identical pair of substantially

hemispherical casings

22 and 24 which in this example are bolted together by a plurality of mounting bolts 26. When thus bolted together the

casings

22, 24 enclose a stator cavity 28 therein, which is further defined by frusto-

conical casing protrusions

30, 32 formed within the hollow portions of the

casings

22, 24.

A substantially spherical mid seal 34 is mounted centrally of the stator cavity 28 and includes in this example a stationary spherical wedge 36 and spherical hub member 38 and 40 of the

inclined rotor discs

42, 44 described below. The wedge member 36 is stationarily mounted on fixed

tubular shaft extensions

46 and 48 as better shown in FIGS. 57 of the drawings. The fixed supporting shafts 46 48 of the spherical wedge 36 are provided with

central lubricating passages

47 and 49 respectively.

As shown in FIGS. 2 and 4, a pair of substantially identical

discoidal rotor elements

42, 44 are rotatably mounted within the stator chamber 28 and are each inclined to the vertical axis 50, as viewed in FIG. 2, and to one another. Each of the

discoidal members

42, 44 is rotatably mounted by rotational engagement of its aforementioned spherical hub 38 or 40 with a complementary recess formed in the frusto-

conical projections

30 or 32 of the engine casing.

The junction between each of the spherical hubs 38 or 40 and the associated frusto-

conical casing protrusions

30 or 32 is sealed by a sealing ring slidably mounted in annular recess 57 therefor. Each of the sealing rings 55 can be conventionally spring-loaded by a corrugated spring or by a conical spring such as that denoted by 59.

The idler disc 42 is further secured to an idler supporting shaft 52 for rotation therewith which in turn is rotatably mounted in bore 54 extending through the associated casing section 22 and frusto-conical protrusion 30. The bore 54 is substantially closed in this example by access cover 56 through which the splined end 58 of the Wedge member shaft 46 is extended and held in non-rotatable relation.

On the other hand, output rotor disc 44 is additionally mounted on output shaft 60 for rotation therewith, which shaft extends through bore 62 in the associated casing section 24 and frusto-conical protrusion 32. The idler disc shaft 52 and the output shaft 60 of the associated spherical hubs 38, 40 are each provided with

cylindrical bores

64 or 66 to receive the stationary supporting

shafts

46 or 48 of the spherical wedge 36.

From the description encountered thus far, it will be apparent that the

rotor disc

42, 44 are rotatably supported in the positions shown against any significant axial displacement for line contact or near contact of their conical surfaces as described below. In furtherance of this purpose, the central disc 36 is rigidly and closely supported between the central truncated surfaces 67 of the

discs

42, 44 and is generally coextensive therewith. The

discs

42, 44 are maintained exactly in phase throughout their rotational positions by enmeshed beveled gears 68,

70 mounted on the aforesaid truncated surfaces 67, of the

discs

42, 44. In some applications the gearing 68-70 can be located elsewhere on the

discs

42, 44, for example, on their beveled or conical surfaces 110.

As better shown in FIGS. 5-7 the stationary midseal or spherical wedge 36 is provided with complementary gear recesses 72, 74 which communicate in the lower area of the wedge, as designated by the reference character 76 (FIG. 5), in order respectively to receive the beveled gears 68, 70 and to permit their enmeshment in the area 76 of the recess communication.

In an exemplary arrangement of the invention the rotary combustion engine 20 is provided with six vanes 78 which are slidably engaged by the

rotor discs

42, 44 at slots 80 provided therein, as better shown in FIGS. 2 and 4. It will be understood, of course, that a different number of vanes 78 can be employed depending upon the application of the invention. The shape of each vane 78 is shown in FIG. 8 of the drawings and its relationship to the stator cavity 28 of the rotary engine 20 is denoted by chain outline 78a. thereof in FIG. 2. Thus, it will be seen that each vane 78 closely engages at its outer edge the inner spherical surfaces 81 of the

casing sections

22, 24 at its ends the conical surfaces 82 of the frusto-

conical casing protrusions

30, 32, and at its inward edge the spherical surfaces of the mid seal 34 of the stator cavity 28, i.e., the spherical hubs 38, 40 and the spherical surfaces of the stationary wedge 36.

As better shown in FIGS. 8 to the engagement of the aforementioned edges with these components is sealed by means of spring loaded sealing strips 84, 86 and 88 which are spring loaded in

complementary grooves

90, 92 and 94 therefor formed respectively in the outward, end, and inward edges of each of the vanes 78. In this example suitable biasing means such as corrugated spring means 96 are seated in the grooves 90-94 to urge the sealing members 84-88 into engagement with the aforementioned surfaces which define the boundaries of the stator chamber 28. The upper sealing strip 84 includes an integral spark plug hole cover 89 to prevent blow-by into an adjacent chamber as the vane 78 sweeps past the plug.

As indicated previously each sealing vane 78 is slidably engaged for relative axial movement by the

rotor discs

42, 44. For example, as seen in FIG. 2 the uppermost vane 78a is slidably mounted in slot 80a of the output disc 44 and also in slot 80b of the idler disc 42, with the

slots

80a, 80b (and the remaining pairs of slots) being maintained in angular alignment relative to the stator cavity 28, as the

rotor discs

42, 44 are revolved, by the bevel gears 68, 70.

As better shown in FIGS. 2, 4, and 4A the sliding engagement of the

rotor disc

42, 44 with each of the vanes 78 as the rotor assemblies are revolved, is desirably sealed by a pair of sealing strips 98 mounted in a pair of grooves 100 opening into each slot 80. Desirably, each slot 80 is accompanied by adjacent edge means such as

beveled edges

102, 104 to accommodate angular displacement of the vanes 78 relative to the adjacent conic surfaces the

rotor discs

42 and 44, as the latter revolve and as occasioned, for example, by slight phasal displacements between the

discs

42, 44 resulting form gearing clearances and tolerances.

The peripheral edges of each

rotor disc

42 or 44 is provided with a plurality of arcuate sealing segments 106 seated in appropriate grooves therefor, with each of the segments 106 extending between an adjacent pair of the slots 80 and their sealing means 98-100. If desired, the slot sealing segments 98 and the peripheral disc sealing segments 106 can be spring loaded in a conventional manner (not shown) such as illustrated with the vane sealing strips 84-88.

Desirably, each of the

rotor discs

42 or 44 are of frustoconical contour to provide a line contact or near contact therebetween as denoted by reference character 108 adjacent the lowest portion of the stator cavity 28 as viewed in FIG. 2. The line contact 108 thus defined extends radially across the opposed conical surfaces 110 of the

rotor discs

42, 44 and is equal to the height or radial dimension of each of the vanes 78, as evident from the chain outline 78a thereof in FIG. 2. Thus, an adjacent pair of vanes disposed on either side of the line contact 108 define a combustion chamber having maximum compression or minimum displacement. Conversely, an adjacent pair of vanes and the areas of the conical surfaces 110 at the top of FIG. 2 define a combustion chamber of maximum displacement.

Referring again to FIGS. 1-3 of the drawings, the fluid flow systems of my novel engine are described in detail. In an exemplary arrangement a bifurcated inlet manifold 111 is coupled to the

hemispheric casing sections

22, 24 at the elongated inlet slots 112 thereof as better shown in FIG. 1. As shown in FIG. 2 the slots 112 communicate with the stator chamber 28 at areas adjacent the frustoconical case protrusions 30, 32 and intake chambers 117 defined by the end portions of the vanes which project behind the

rotor discs

42, 44 respectively. The slots 112 are elongated to provide communication with intake chambers 117 throughout their displacement increasing or intake positions. Thus, the incoming fuel mixture entering slots 112 cannot pass directly into any of the rotating combustion or discharge chambers 29 defined by the front or opposing surfaces of

rotor discs

42, 44 and confined respectively between pairs of adjacent vanes 78. Instead, the fuel mixture flows from slots 112 as denoted by

flow arrows

115 and 116 into suction chambers 117 defined by the stator protuberances 82, the back surfaces of the

disc

42, 44 and the end portions of the vanes 78 (FIG. 2). As evident from FIG. 2, there are two suction chambers 117 for each combustion chamber 29. The suction chambers 117 have a minimum displacement at the top of the stator, as viewed in FIG. 2, and a maximum displacement at the bottom. As the suction chambers 117 move along the intake slots 112 their displacements are increasing to create a suction for fuel intake through slots 112. After the suction chambers 117 pass the lower ends of the intake slots 112, their decreasing displacement causes the fuel-air mixture to be compressed. Adjacent the minimum displacement of the chambers 117 the compressed fuel-air mixtures of the chambers 117 are successively discharged into casing passages 114 (FIGS. 1 and 2) which open at their inner ends 119 onto the conical surfaces 82 respectively of the frusto-

conical portions

30, 32. The openings 119 communicate with grooves 121 on the

conical surfaces

30, 32 to provide fuel-air transfer at reasonable pressures. Thence, the fuel mixture is forced into the combustion chambers 29 adjacent their positions of maximum displacement inlet ports 118 and inlet port covers as indicated by flow arrows 122.

As better shown in FIG. 3, the fuel mixture then is forced into the upper combustion chamber enclosed by the vanes 78b and 78c as these vanes are rotated past the two inlet ports 118. Previously, however, the expanding combustion gases have exited through exhaust ports 124 assuming engine rotation is in the direction denoted by arrow 126. The exhaust ports 124 communicate with a bifurcate exhaust duct 127 (FIG. 1).

In operation of the engine according to FIGS. 110, rotation of the

rotor discs

42, 44 causes a combustible fuel mixture to be forced into each combustion engine chamber 29 (defined by an adjacent pair of vanes 78) as the vanes revolve past the inlet ports 118. The mixture then is compressed as the vanes, for example the vanes 78b 78c (FIG. 3), are revolved by rotation of the

discs

42, 44 to the lowermost positions denoted by vanes 78d and 78e. At this position the fuel mixture contained in the combustion chamber between the vanes 78d, 78e is at its condition of maximum compression adjacent the line of contact or near contact 108 between the frustoconical discs 42, 44 (FIG. 2). This is equivalent to the top-dead-center position of the piston in a piston combustion engine. Desirably, the spark plug 91 is located on the stator in proximity to the contact line 108 as determined by considerations of ignition timing.

The exploding gases in the lowermost combustion chamber between

vanes

78d, 78c add impetus to the rotation of the

rotor discs

42, 44 as the burning gases expand. This applies force to the

rotating stator discs

42, 44 to urge them in the direction of increasing displacement as denoted by arrow 126a. Torque is thus transferred to the output shaft 60 (FIG. 2). When the expanding gases are carried to the combustion chamber position denoted by vanes 781 and 78g (FIG. 3) the expanded gases exit through exhaust ports 124.

In the arrangement as shown in FIG 2 the

rotor discs

44, 42 may be slightly separated along the line 108 of contact or near contact. The indicated spacing, disc inclination, and disc contour afford, in this example, a compression ratio suitable for commercial grades of gasoline and the like.

Referring now to FIGS. 11 and 12 of the drawing a similar arrangement of my rotary machine is employed as an external combustion engine 130 wherein hot combustion gases are supplied through duct 132 which communicates with the lowermost combustion chamber (FIG. 3) through an opening 134 in place of the spark plug 91. The expanding combustion gases supplied to each engine chamber 29 add impetus to the revolution of the

rotor discs

42, 44 and torque to output shaft 60' until the spent combustion gases are exhausted through ports 136. At the same time the suction chambers 117' supply compressed air through duct 138 to the combustor denoted by reference character 140. The duct 138 communicates with transfer ports 142 (through stator protuberances 30, 32) which in turn communicate with air inlet passage 144.

The operation of the external combustion rotary engine 130 of FIG. 11 is similar to that described above with the exceptions that fuel supplied through nozzle 146 is ignited in combustor 140 by spark plug 148 or the like and that only combustion air instead of fuel-air mixture is compressed in the suction chambers 117 of the engine 130 prior to ignition. Alternatively, a glow-plug can be substituted for the spark-plug 148 to eliminate the need for timed ignition, as is known.

With reference now to FIGS. 13 and 14, a similarly constructed rotary machine can be employed either as a positive displacement rotary pump or as a fluid motor, and denoted generally by the reference numeral 150. The internal structure of the pump 150 is essentially similar to that shown in FIG. 2 with the exception that inlet or

suction ports

152, 154 are provided in the spherical casings 22', 24, respectively, together with outlet or discharge

ports

156, 158. In each casing 22' or 24, the

suction port

152 or 154 communicates with suction chamber 117' while the

discharge ports

156 or 158 communicates with discharge chambers 29, which are similar in construction to the combustion chambers 29 of the preceding figures. The aforementioned inlet and outlet ports are coupled to suitable supply and delivery ducts (not shown).

In operation, counterclockwise torque (arrow 160) is supplied to drive shaft 60 causing each of the twelve suction chambers 117 as defined by the vanes 78 to take in air or other fluid through the

suction ports

152, 154; to transfer the fluid; to discharge chambers 29 which compress the fluid; and to deliver compressed fluid through

outlet ports

156, 158. It will be clear that the rotational direction of the pump 150 can be reversed with equal facility whereupon the functions of the

intake ports

152, 154 and of the

discharge ports

156, 158 will be interchanged respectively.

It is also intended that the machine 150 be employed as a fluid motor, as the function of the machine 150 is reversible in this respect also. Thus, an application of pressurized fluid such as steam or compressed air, to the

suction ports

152, 154 produces a counterclockwise torque at the output shaft 60. A similar application of i fluid pressure at the

intake ports

156, 158 results in clockwise torque. When the engine is used as a motor, the ports 152-158 can be relocated to allow the most efficient expansion of the particular pressurized fluid used.

From the foregoing it will be apparent that novel and efficient forms of positive displacement rotary machines have been disclosed herein. While I have shown and described certain presently preferred embodiments of the invention and have illustrated presently preferred methods of practicing the same, it is to be distinctly understood that the invention is not limited thereto but may be otherwise variously embodied and practiced.

I claim:

1. A rotary positive displacement machine comprising a casing defining a stator cavity therein, a pair of rotor discs mounted for rotation within said stator cavity at inclined positions relative to one another, a plurality of substantially planar and rigid vanes closely fitted in said cavity and slidably engaged by each of said rotor discs, through which said vanes extend, said vanes being substantially equally spaced about said discs and slidably and peripherally engaging juxtaposed surfaces of said stator cavity on the adjacent surfaces of said machine, said vanes and said discs defining chambers of variable size depending upon the rotational position of adjacent pairs of said vanes about said discs.

2. The combination according to claim 1 wherein a number of suction ports are formed in said casing and disposed for communication with expanding ones of said chambers, a number of discharge ports are formed in said casing and located for communication with contracting ones of said chambers, and means are provided supplying torque to one of said rotor discs so that said machine operates as a positive displacement pump.

3. The combination according to claim 1 wherein each of said vanes extends through closely fitting slot means in each of said rotor discs, said slot means having edge means in substantial engagement with said vanes to permit angulation thereof relative to said discs as said discs are rotated.

4. The combination according to claim 1 wherein said machine is provided with an external source of pressurized fluid, said source being coupled to aperture means in said casing at a position for successive communication with said chambers adjacent the area of minimum volume thereof and additional aperture means are provided for exhausting said fluid adjacent the area of maximum volume of said chambers.

5. The combination according to claim 4 wherein said source is an external combustor provided with means for supplying air and fuel thereto, said air supplying means includes air intake and discharge port means coupled to said casing and located so that air is drawn into some of said chambers through said intake port means, compressed, and supplied through said discharge port means to said combustor.

6. A rotary positive displacement machine comprising a casing defining a stator cavity therein, a pair of rotor discs mounted for rotation within said stator cavity at inclined positions relative to one another, a plurality of substantially planar and rigid vanes closely fitted in said cavity and slidably engaged by each of said rotor discs, said vanes being substantially equally spaced about said discs and slidably mounted on the adjacent surfaces of said machine, said vanes and said discs defining chambers of variable size depending upon the rotational position of adjacent pairs of said vanes about said discs, said stator cavity being of annular configuration, and a fixed mid seal member mounted within said casing and between said discs, said mid seal member at least partially defining the inner periphery of said stator cavity, said vanes slidably engaging said mid seal member and the remaining surfaces of said stator cavity.

7. The combination according to claim 6 wherein said mid seal member is a spherical wedge closely fitted between said discs, said mid seal member being supported centrally of said stator cavity, the remainder of said stator cavity being defined by a pair of spherical hub members secured to said discs respectively and slidably mounted on said casing.

8. The combination according to claim 6 wherein a pair of enmeshed beveled gears are secured respectively to said rotor discs to maintain said discs in phase during rotation thereof, said gears being at least partially enclosed within said fixed mid seal member.

9. The combination according to claim 8 wherein said gears are enclosed within a pair of communicating recesses formed in said spherical wedge.

10. The combination according to claim 6 wherein said mid seal member is supported on fixed shaft means about which said rotor discs are rotatably mounted, whereby relative alignment of said discs is maintained.

11. The combination according to claim 10 wherein one of said rotor discs is secured for rotation therewith to a rotatably mounted operating shaft for said engine, said shaft extending through said casing, and the other of said rotor discs is secured to a rotatably mounted idler shaft supported within said casing, each of said operating and idler shafts being rotatably mounted on said mid seal shaft means.

12. A rotary positive displacement machine comprising a casing defining a stator cavity therein, a pair of rotor discs mounted for rotation within said stator cavity at inclined positions relative to one another, a plurality of substantially planar and rigid vanes closely fitted in said cavity and slidably engaged by each of said rotor discs, said vanes being substantially equally spaced about said discs and slidably mounted on the adjacent surfaces of said machine, said vanes and said discs defining chambers of variable size depending upon the rotational position of adjacent pairs of said vanes about said discs, said casing is spherical, said stator cavity is partially defined by a pair of opposed frusto-conical portions fixedly secured to said casing, and said rotor discs are rotatably mounted on said frusto-conical portions respectively.

13. A rotary positive displacement machine comprising a casing defining a stator cavity therein, a pair of rotor members mounted for rotation within said cavity and inclined to one another, a plurality of substantially planar and rigid vanes fitted within said cavity, each of said vanes being slidably engaged by each of said rotor members and slidably mounted on the adjacent surfaces of said machine, at least one of said rotor members having a surface opposite from the other of said rotor members and inclined to a juxtaposed surface of said stator cavity, said vanes bridging the variable gaps on either side of said one rotor member so that said vanes and said rotor members and said juxtaposed cavity surface define a plurality of chambers of variable size on each side of said one rotor member depending upon the rotational position of adjacent pairs of said vanes about said rotor members.

14. The combination according to claim 13 wherein said rotor members and said juxtaposed cavity surface are so inclined one to the other that said chambers on one side of said one rotor member exhibit increasing and decreasing displacements while said chambers on the other side of said one rotor member exhibit decreasing and increasing displacements respectively as said rotor members are revolved.

15. The combination according to claim 13 wherein intake port means are coupled to said casing for communication with some of said chambers adjacent the minimum displacement positions, and exhaust port means are coupled to said casing in communication with others of said chambers adjacent their maximum displacement positions.

16. A rotary positive displacement machine comprising a casing defining an annular stator cavity therein, a rotor member mounted for rotation within said cavity, said rotor member being spaced generally opposite surface portions of said cavity on either side of said rotor member and being inclined thereto, a plurality of substantially planar and rigid vanes fitted Within said cavity and slidably engaged by said rotor means, each of said vanes extending across said cavity and slidably and peripherally engaging the juxtaposed surfaces thereof including said opposite surface portions, so that said vanes bridge the variable gaps between said surface portion and the adjacent surfaces respectively of said rotor member so that said vanes and said rotor member and said surface portions define a plurality of chambers of variable size on each side of said rotor member depending upon the rotational position of adjacent pairs of said vanes about said rotor member.

17. The combination according to claim 16 wherein said rotor member is so inclined to said surface portions that said chambers on one side of said rotor member exhibit increasing and decreasing displacements while said chambers on the other side of said rotor member exhibit decreasing and increasing displacements respectively as said rotor member is revolved.

18. The combination according to claim 17 wherein transfer port means are formed in said casing in communication with said some chambers adjacent their minimum displacement positions and in communication with said other chambers adjacent their maximum displacement positions.

19. A rotary positive displace-ment machine comprising a casing defining a stator cavity therein, a pair of rotor members mounted for rotation within said cavity, a plurality of substantially planar and rigid vanes fitted within said cavity, each of said vanes being slidably engaged by each of said rotor members and slidably mounted on the adjacent surfaces of said machine, said vanes and said rotor members defining a plurality of chambers of variable size depending upon the rotational position of ad jacent pairs of said vanes about said rotor members, said stator cavity being of annular configuration, each of said vanes being shaped to extend across said cavity and slidably to engage the juxtaposed wall surfaces thereof, and means for sealing the slidable engagements between said vanes and juxtaposed components of said machine.

20. The combination according to claim 19 wherein said sealing means including sealing members located on said vanes for sealing between said vanes and said cavity surfaces and additional sealing members on said rotor members for sealing between said rotor members and said vanes respectively.

References Cited UNITED STATES PATENTS 764,465 7/1904 Hendricks 91-82 1,773,635 8/1930 Simmons 91-85 1,912,634 6/1933 Gray. 2,482,325 9/1949 Davis 230-142 2,828,695 4/1958 Marshall 103-127 3,101,700 8/1963 Bowdish. 3,277,792 10/ 1966 Stenerson 91-85 CARLTON R. CROYLE, Primary Examiner A. D. HERRMANN, Assistant Examiner U.S. Cl. X.R.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3,528,242 September 15, 1970 Michael D. Hartmann It is certified that error appears in the above identified patent and that said Letters Patent are hereby corrected as shown below:

Column 1, line 39, "radilly" should read radially Column 2, line 40, "these" should read there Column 3, line 6, "rotor discs are of frusto-conical configuration and are" should read stator cavity is of annular configuration and a fixed mid Signed and sealed this 16th day of March 1971.

(SEAL) Attest:

WILLIAM E. SCHUYLER, JR.

Commissioner of Patents Edward M. Fletcher, Jr.

Attesting Officer