Abstract:
An internal combustion rotary power machine which functions in general accordance with the principles of the Carnot heat engine cycle without dependence upon reciprocating pistons, valves or other reciprocating mechanical components for working fluid manipulation. Through elimination reciprocating components the machine potentially offers a large measure of functional excellence in terms power density, efficiency, reliability, mechanical simplicity and production economy. Combustion occurs as a continuously sustained process thereby significantly facilitating the use of gaseous fuel. The machine presented in this disclosure is based on substantial analysis of the functional principles of internal combustion rotary vane machines as related to thermodynamic efficiency, mechanical efficiency, and thermal control considerations. The disclosure demonstrates the integration of primary geometric relationships and technical features necessary to effectively fulfill functional viability requirements.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
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     STATEMENT REGARDING FEDERALLY FUNDED RESEARCH OR DEVELOPMENT 
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     REFERENCE TO A MICROFICHE APPENDIX 
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     BACKGROUND OF THE INVENTION 
     At the present time, machines employed for the production of mechanical energy by internal combustion of organic fuel consist primarily of mechanical displacement machines, generally called “reciprocating” engines, and gas turbines. 
     Reciprocating internal combustion machines employ reciprocating mechanical motion of pistons and valves for working fluid manipulation and fuel combustion is a pulsed, non-continuous, process. The function of a reciprocating internal combustion engine is theoretically described in terms of a thermodynamic cycle such as first postulated by Sadi Carnot (1824) or one of the alternative thermodynamic cycles such as postulated by Nicholas Otto (1876), and Rudolph Diesel (1892). Gas turbines employ purely rotational components, aerofoil surfaces, and aerodynamic interaction for working fluid manipulation and fuel combustion is a self-sustaining continuous process. In general, gas turbines theoretically function in accordance with a thermodynamic cycle such as postulated by G. B. Breyton (1876). 
     Reciprocating machines offer an operationally flexible, relatively high torque power source and are economically satisfactory for many commercial applications, however their featured reciprocating components and pulsed combustion are inherent sources of undesirable noise and vibration. In comparison, gas turbine machines offer a relatively high rotational speed power source, and, relatively, reduced emissions of noise and vibration but offer economic superiority only in applications requiring relatively high measures of power density and delivered power. 
     Over a number of years significant inventive effort has been directed toward the derivation of a “rotary” internal combustion machine such as would feature mechanical displacement for working fluid manipulation but employ only rotationally dynamic components to accomplish fluid manipulation. By retention of the mechanical displacement means for working fluid manipulation the “rotary” machine is perceived to offer the performance characteristics given by reciprocating type machines, but, through elimination of reciprocating components, preclude their concomitant mechanical complexity and potential for emission of noise and vibration. The radial vane type rotary machine has been the subject of particular attention in this regard. 
     Conceptually the rotary vane machine primarily consists of a stationary containment structure and an internal assembly of rotationally dynamic components. The stationary containment structure consists of a containment cylinder with a precisely or approximately circular bore, installed with end closure structures. Ports are installed for induction of combustion air and for discharge of combustion products through the boundary of said containment structure. 
     The internal assembly of rotationally dynamic components primarily consists of a rotational armature, a plurality of radial vanes, and a means for extracting rotary power. Said rotational armature is precisely or approximately circular in cross section. The diameter of said rotational armature is less than the bore diameter of said containment cylinder such as to create an annular cavity between the peripheral surface of said rotational armature and the bore of said containment cylinder. Said rotational armature is fitted with a plurality of radial slots equally spaced around its periphery and parallel to its longitudinal axis. Each said slot accommodates and provides annular sliding support for one radial vane. Each said radial vane is a relatively thin structural panel axially extending through the armature length and radially extending from within said slot to contact or closely approach the bore of said containment cylinder. The plurality of said radial vanes subdivides the volume of aforesaid annular cavity into a plurality of annular segmental cells. Said rotational armature is supported such as to rotate on an axis parallel to, but radially displaced from the bore axis of said containment cylinder. Since the rotational axis of said rotational shaft is radially displaced from the bore axis of said containment cylinder, the relative volume of any given segmental cell is dependent upon its orbital location and, therefore, cyclically changes through rotation of said rotational armature. Said rotationally related cyclical change in relative volume functionally equates to the change in relative volume caused by the reciprocation of a piston within a cylinder such as employed in reciprocating type internal combustion and provides the basic features of working fluid manipulation necessary for the function of a heat engine cycle. For a given set of said containment cylinder proportions, the manipulated volume is inversely influenced by the diameter of said armature. Within certain limits, the compression ratio or expansion ratio of the volumetric cycle is directly influenced by both the number of segmental cells surrounding said rotational armature and the distance separating the rotational axis of said rotational armature from the bore axis of said containment cylinder. Said compression ratio is also influenced by the angular width and radial location of the sector allocated for the combustion air supply port. Similarly the expansion ratio is influenced by the angular width and radial location of the sector allocated for the combustion product discharge port. Means for extracting rotary power from the machine may consist of an axial extension of said rotational armature through one or both aforesaid end closure structures or by means of a rotational shaft functionally integrated with said rotational armature. 
     A number of patents have been awarded for rotary vane internal combustion machine concepts. However, despite the potentially excellent qualities offered by the rotary vane machine, as of this writing none of the concepts presented in prior art are known to have matured sufficiently to demonstrate practical utility. It may be reasonably hypothesized that the reason for such non-maturation is the result of singular or compounded inadequacies regarding functional viability considerations. 
     As known to persons skilled in the art, the fundamental functional viability of all machines is their capability to function within the constraints of common natural laws as defined in mechanics, physics, and mathematics. It is also known to persons skilled in the art that, beyond these fundamental considerations, the functional viability of an energy related machine is demonstrated by its capability to meet thresholds for efficiency, and power density within constraints of imposed by the physical properties of economically available constituent materials. The overall efficiency of thermal machines is the product of thermodynamic cycle efficiency and mechanical efficiency. The physical properties of constituent materials such as dimensional stability and lubricity may be significantly influenced by thermal environment. For these reasons the potential functional viability of a thermal machine may be theoretically assessed by analysis of its functional geometry and components features relative to thermodynamic cycle efficiency, mechanical efficiency, and thermal control considerations. 
     For internal combustion machines thermodynamic cycle efficiency is directly influenced by the compression ratio of the volumetric cycle. For machines based on Carnot principles, and with numerically equal compression and expansion ratios, the basic relationship between cycle efficiency (“Air Standard Efficiency”) and compression ratio is described as:          η   c     =     1   -     1     v     (     κ   -   1     )                             Where:                     η   c       =                Cycle                 Efficiency                 v   =                Compression                 Ratio                 k   =                Universal                 Gas                 Constant                                  
     As previously noted, the compression ratio of a rotary vane machine is directly related to the plurality of the annular segmental cells surrounding the armature and inversely influenced by the relative angular extent of the induction port sector. Finite numerical analysis demonstrates that the threshold for adequate cycle efficiency is attained only when the plurality of radial vanes exceeds a certain minimum value and the angular extent of the induction port sector is less than a certain maximum value. 
     Mechanical efficiency is essentially the measure of mechanical energy conservation exhibited by a mechanism in the process of doing work. Mechanical efficiency is inversely influenced by the quantity of energy dissipated by frictional interaction between dynamically related components and, in this context, may be expressed as:          η   m     =         P   i     -     P   f         P   i                         Where:                     η   m       =                Mechanical                 Efficiency                   P   i     =                Input                 Power                   P   f     =                Power                 Consumed                 by                 Friction                                  
     Power consumed by internal friction is the sum of the increments of power consumed by individual frictional components. In radial vane type rotary machines the radial vanes create the preponderance of the dynamically active mechanical interfaces and are, thereby, a particularly significant potential cause of power loss due to friction. Potential friction sources are; peripheral edge friction caused by sliding contact of said radial vanes with bore of said containment cylinder, axial end friction caused by sliding contact of axial ends of said radial vanes with non-rotating end closure components, and radial friction caused by sliding contact of the faces of said radial vanes with the supporting surfaces of said rotational armature. The magnitude of energy loss due to friction is also significantly influenced by the nature of the materials in sliding contact and the effectiveness of lubrication at the contact surface. Finite numerical modeling demonstrates that, in the plurality necessary to achieve thermodynamic cycle viability, the radial vanes alone could, potentially, incur friction losses of sufficient magnitude as to cause non-viability from a mechanical efficiency viewpoint. Minimization of the potential contributions of mechanical friction from all sources is therefore a vital consideration regarding the functional viability of rotary vane machines. 
     Machine component temperature is a source of concern from thermal expansion, component flexure, friction, and bearing life viewpoints. Dynamic components of internal combustion machines are exposed to heating from three sources, adiabatic heating due to gas compression, heat released by fuel combustion, and heat produced by the work done in overcoming friction. For this reason the functional viability of internal combustion machines is dependent upon adequate means for environmental control. Environmental control normally consists of the movement of liquid and/or gaseous heat extraction media across component surfaces. In general, the rate of heat extraction is directly influenced by the area of structural surface exposed to heat extraction media and flow rate of said heat extraction media across said structural surface. Extraction of waste heat from stationary components of reciprocating machines is accomplished by exposure of external surfaces to ambient air or liquid heat extraction media. Extraction of waste heat from the stationary enclosures of rotary vane machines may be readily accomplished by similar means. Environmental control for internal dynamic components is normally accomplished by circulation of air and liquid lubricant. In the case of reciprocating machines environmental control of dynamic internal components is facilitated by their functional assembly which precludes exposure of many components to high temperature working fluid and contains them within a stationary crankcase structure and thus readily accessible for internal circulation of environmental control media. In comparison the internal dynamic components of rotary vane machines are, relatively, more substantially exposed to contact with high temperature working fluid and their functional assembly makes them significantly less accessible for internal circulation of environmental control media. For these reasons the means for maintaining environmental control within the interior of the machine assembly is a vital consideration regarding the functional viability of rotary vane machines. 
     Several prior rotary vane machine disclosures present technical approaches toward minimization of friction particularly as related to sliding friction between radial vanes and containment cylinder bore but in general are substantially silent regarding the other functional viability issues discussed above. Principal features of several rotary vane type machines disclosed in prior patents are briefly reviewed below. 
     U.S. Pat. No. 2,590,132 issued to F. Scognamillo on Mar. 25, 1952 discloses a rotary cylinder rotary device. Said device features a stationary housing with an internal circular bore, end closure structures, and fluid transfer ports. Within said stationary housing a solid rotor is concentrically secured to a rotational shaft. Said rotational shaft is radially and axially constrained by two rotational bearings with one bearing installed in each said end closure structure. Said rotor is fitted with a plurality of axial slots uniformly distributed around its periphery. Each said rotor slot annularly constrains one radial vane such as to permit relative sliding motion. Each said radial vane is installed with a cylindrical extension at each end. Said cylindrical extensions engage a rotating ring at one end and a rotating disk at the other such as to radially constrain said radial vane. Said radial vane is constrained such that its outer peripheral edge remains a small distance from the said circular bore at all rotational positions. A spring loaded sliding seal is installed on the radial periphery of each said radial vane such as to maintain pressure contact with the circular said bore. Said rotating ring and said rotating disk are concentrically and mechanically connected by means of an annular cylinder. Said rotating ring, rotating disk, and annular cylinder assembly is and axially and radially constrained by a rotational bearing installed in one said end structure. Axial aligned sealing strips are installed on the outer periphery of said annular cylinder such as to maintain sliding contact with the circular said bore. Said annular cylinder is fitted with axial slots such as to permit radial passage of said radial vanes. Said radial vanes are axially constrained by contact with said rotating ring at one end and with said rotating disk at the other. Issues related to lubrication, and heat extraction are not discussed. 
     U.S. Pat. No. 5,568,796 issued to William R Palmer on Oct. 29, 1996 discloses a rotary compressor and engine machine system Said disclosure features a stationary housing with an internal non-circular bore, end closure structures and fluid transfer ports. Within the stationary housing a plurality of radial vanes is radially constrained by means of pivotal bearings installed on a rotating hub. Said radial vanes extend through a rotating circular annulus such as to closely approach the bore of said stationary housing. Said annulus are installed on rotational bearings such that said annulus rotates on an axis parallel to but separate from the rotational axis of the said hub. Said hub and said annulus synchronously rotate by means of gearing. The bore of said stationary housing is contoured such that the free ends of said radial vanes remain a constant distance from the bore of the said stationary housing. Seals are installed on the free edges of the said radial vanes to close the gap between the free edges of said radial vanes and the said stationary housing. The disclosure demonstrates that one said assembly can fulfill the expansion and discharge phases of a heat engine cycle, one said assembly can fulfill the induction and compression phases of the said heat engine cycle, and coupling of two said assemblies can fulfill all of the four required phases of a heat engine cycle. The disclosure is silent regarding means for sealing the axial ends of rotational components, centrifugal restraint of vane edge seals and issues related to lubrication, extraction of waste heat, and accommodation of functionally related geometric variations. 
     U.K. Pat. No. 468,390 issued to Drehkolben Kraftsmachinen G.m.b.H on Jul. 2, 1937 discloses improvements in and relating to rotary piston machines. Features presented in this disclosure consist of means by which uninterrupted combustion of fuel can take place at constant pressure, a means by which rotary machines can be made to function by combustion of different fuel types (e.g. pulverized coal), and a means by which throttle like devices may be installed on either the induction or the expansion side of a rotary machine for the purpose of performance control. The disclosure also presents methods by which two rotary vane devices may be non-mechanically coupled such as to collectively function such as to fulfill the four required phases of a heat engine cycle. The disclosure drawings illustrate a rotary device consisting of a stationary containment cylinder, a solid rotor installed on a rotational shaft, fitted with six radial slots and accommodating six radial vanes. The disclosure is silent regarding the mechanical features of the rotary vane device and issues related to extraction of waste heat and lubrication. 
     BRIEF SUMMARY OF THE INVENTION 
     This disclosure presents a rotary vane internal combustion machine for efficient conversion of chemical energy, as contained in liquid or gaseous fuels, to rotational energy suitable for accomplishing mechanical work. Functional characteristics such as rotational velocity and power density are, in general, comparable to the functional characteristics of modern reciprocating internal combustion machines, however functional efficiency is enhanced by elimination of major reciprocating components, minimization of mechanical friction, and utilization of a continuously sustained combustion process. The machine primarily consists of a stationary containment structure and an internal assembly of rotationally dynamic components. 
     The stationary containment and foundation structure consists of a containment cylinder with circular bore installed with a closure structure at each axial end. Ports are installed for induction of combustion air and for discharge of combustion products through the wall of said containment cylinder. Said induction and discharge ports are mutually interspersed throughout the axial length of the aforesaid stationary containment cylinder, peripherally dispersed such as to minimize their collective sector width, and radially oriented such that their respective flow streams maximize working fluid manipulation efficiency. Ports are for introduction of fuel, externally supplied energy, and ports for maintaining combustion as a sustained continuous process are incorporated in the structural wall of said containment cylinder. 
     The internal assembly of rotationally dynamic components primarily consists of a rotational armature, a rotational shaft and a plurality of radial vanes. Said rotational armature features a circular cross section and a hollow core. The outside diameter of said rotational armature is approximately ninety percent of the bore diameter of aforesaid containment cylinder thus creating an annular cavity between the peripheral surface of the said armature and the said bore of aforesaid containment cylinder. Said rotational armature is simply supported by low friction rotational bearings installed in aforesaid end closure structures and rotates on an axis parallel to but radially separated from the bore axis of aforesaid containment cylinder. The annulus of said rotational armature accommodates a plurality of axially aligned radial slots uniformly distributed around its periphery. Each said radial slot is installed with one radially sliding radial vane and a pair of radially extending compression springs. Said radially extending compression springs are installed such as to exert a radially outward force on the associated said radial vane. An articulated extension is secured to the innermost edge of each said radial vane and to the periphery of said rotational shaft by means of hinged connections. Said rotational shaft is simply supported by, and extends through, a low-friction rotational bearing installed in each aforesaid end closure structure. Axial ends of said rotational shaft are configured to facilitate transmission of rotational power to external power consuming systems. The axis of rotation of said rotational shaft is coincident with the bore axis of said containment cylinder. The radial widths of said radial vanes and said articulated extension are selected such as to preclude contact between the outer edges of said radial vanes and the bore of said containment cylinder. By this means the centripetal force induced by each radial vane upon high-speed rotation of said armature is reacted by said rotational shaft and not through sliding contact with the bore of said containment cylinder. A mechanical radial vane edge seal installed on the outermost edge of each said radial vane exerts a nominal spring force on the bore of aforesaid containment cylinder. Said radial vanes and said radial vane edge seals subdivide the said annular cavity into a number of annular segmental cells. Axial ends of said annular segmental cells are closed by means of rotational assemblies consisting of a sealing ring, axial spring, and retainer ring components installed at each end of said rotational armature. Said sealing ring, axial spring, and retainer ring assemblies resiliently respond to axial component geometry adjustments such as caused by thermal variations. Since the rotational axis of said rotational armature is radially displaced from the bore axis of aforesaid containment cylinder, the relative volume of any given segmental cell is dependent upon its orbital location and, therefore, will cyclically change upon rotation of said armature. The described mechanism therefore fulfills the fundamental requirements for physical manipulation of working fluid necessary to achieve a functional heat engine thermodynamic cycle and, with selection of appropriate geometric relationships, support systems, and design details, be evolved to function as an internal combustion machine. 
     The internal axial cavity in aforesaid rotational armature provides a means for delivering environmental control media to internal dynamic components. Contouring the internal peripheral surface of the said internal axial cavity such as to enlarge the surface area exposed to environmental control media facilitates extraction of heat from said rotational armature and interfacing components. Environmental control media are supplied to and discharged from said internal axial cavity by means of ports installed in the aforesaid end closure structures. 
     Necessary ancillaries consist of an air supply fan, fuel delivery system, an externally powered rotational device to initiate machine rotation, an electrically powered igniter to initiate combustion, and a liquid lubricant management system. 
     The internal combustion rotary machine presented in this disclosure illustrates the primary geometric relationships and other design features appropriate to obtaining the measures of thermodynamic efficiency, mechanical efficiency, and internal environmental control necessary for demonstration of functional viability. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a side elevation of the external general assembly. For the purposes of this disclosure the axis of rotation is horizontal. The machine is illustrated with diagrammatic representations of ancillary components as deemed appropriate for general service and for combustion of liquid fuel. Special service requirements or combustion of gaseous fuel may require changes in said ancillary components but remain within the scope of this disclosure. 
     FIG.  2  and FIG. 3 are, respectively, left hand and right hand end views of the external general assembly relative to the elevation given in FIG.  1 . 
     FIG. 4 illustrates the internal general assembly along the axis of rotation. Cross section indicators given in FIG. 4 define the axial locations of cross sections presented in FIG.  5  through FIG.  10 . 
     FIG. 4A is an enlarged detail of the rotational bearing arrangement shown in FIG.  4 . 
     FIG. 5 is a cross section at mid-length of the containment cylinder and illustrates the primary geometric features of the rotational mechanism and the radial arrangement of combustion air induction and combustion products discharge ports, and other functionally significant system components. Section indicators given in FIG. 5 define the locations of sectional elevations presented in FIG. 11, FIG. 12, and FIG.  13 . 
     FIG. 6 is a cross section close to the end of the rotational armature and illustrates arrangements for constraint of radial vane ends. 
     FIG. 7 is a cross section at the inside face of the rotational axial end sealing assembly and illustrates the ports for discharge of excess lubricant from within the armature cavity. 
     FIG. 8 is a cross section through the rotational axial end sealing assembly and primarily illustrates the interface between significant rotational components. 
     FIG. 9 is a cross section primarily through the mid-length of one end structure and illustrates the arrangement of rotational armature and rotational shaft support bearings. 
     FIG. 10 is a cross section at the external face of the containment structure and illustrates the arrangement of induction/discharge ports for conduit of heat extraction media through the containment structure. 
     FIG. 11 is a section through the stationary containment cylinder and end closure structures to illustrate the geometric arrangement of the combustion air supply port and combustion product discharge port relative to the combustion air supply manifold. 
     FIG. 12 is a section through the stationary containment cylinder and end closure structures to illustrate the geometric arrangement of the combustion air supply port and combustion product discharge port relative to the combustion product discharge manifold. 
     FIG. 13 is a section through the stationary containment cylinder and end closure structures to illustrate the geometric arrangement of the continuous combustion port. 
     FIG. 14 is an elevation of one radial vane to illustrate significant geometric and assembly features of the vane and its directly associated components. 
     FIG. 15 presents a section through one radial vane at mid-length and illustrates the articulated radial vane assembly. FIG. 15 also illustrates, by reference, other machine components directly interfacing with the articulated radial vane assembly. 
     FIG. 16 presents a section through one radial vane and illustrates the articulated radial vane assembly at the quarter-length. FIG. 16 also illustrates, by reference, other machine components directly interfacing with the articulated radial vane assembly. 
     FIG. 17 presents a section of one radial vane close to its axial end. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Referring to FIG. 1, FIG.  2  and FIG. 3, containment cylinder  1  and end closure structures  2  are the principal stationary containment and foundation components. Said containment cylinder features a set of closely spaced fins to promote dissipation of waste heat to ambient atmosphere, alternatively, waste heat may be removed by circulation of heat extraction liquid through integral structural passageways. Said end closure structures  2  are secured to said containment cylinder  1  by means of machine screws  3 . Flange coupling  4  provides the interface for the conduit of rotational mechanical energy to an external power transmission system. Integral gearbox  5  drives air supply fan  6  to provide air for combustion and internal environmental control. Externally energized device  7  delivers rotational mechanical energy to said gearbox  5  for initiation of rotation. Electrical alternator  8  driven by said gearbox  5  supplies electrical energy to power auxiliary support systems. Manifold  9  provides conduit for supply of combustion air and manifold  10  provides conduit for supply of air for internal environmental control. Valve  11  controls the movement of combustion air. Valve  12  controls the movement of air for internal environmental control. Manifold  13  provides conduit for discharge of internal environmental control air to lubricant coalescer and reservoir assembly  14 . Manifold  15  provides conduit for discharge of combustion product to atmosphere. Pump  16 , filter  17 , and valve  18  deliver a controlled supply of liquid fuel to injector  19 . Said fuel injector  19  provides conduit or finely dispersed (atomized) fuel through the wall of aforesaid containment cylinder  1 . Specific nature and plurality of fuel supply components are dependent upon machine size, operational requirements and characteristics of chosen fuel. Electrical igniter  20  provides thermal input as necessary to initiate combustion. Circulation pump  21 , heat exchanger  23 , and injector  22  deliver liquid internal environmental control lubricant to internal dynamically active components. Manifold  24  provides conduit for return of excess liquid lubricant to said coalescer and reservoir assembly  14 . Bearing carrier  25  accommodates rotational bearings for support of rotational shaft  26 . 
     With reference to FIG.  4  and FIG. 4A, rotational shaft  26  is radially constrained by low-friction roller bearings  27  installed in aforesaid bearing carrier  25  such as to rotate on an axis concentric with the bore axis of aforesaid containment cylinder  1 . Said low-friction rotational bearings  27  are protected from contamination by bearing seals  28  and secured within aforesaid bearing carriers  25  by bearing retainers  29 . Said rotational shaft  26  is axially constrained by annular collar  30  and spring clip  31 . Rotational armature  32  is a hollow annulus structure constructed from two coaxial components connected at the middle of the axial length and features a center section, which accommodates radial vane components  40 , and an extension of reduced diameter at each axial end. Said rotational armature  32  is radially and axially constrained one low-friction roller bearing  33  installed within each end closure structure  2 . Said rotational armature  32  rotates on an axis parallel to, but radially displaced from, the bore axis of aforesaid containment cylinder  1 . Low-friction roller bearings  33  are secured within end closure structures  2  by bearing retainers  34 . Axial retainer rings  35  are concentrically secured on said rotational armature  32  and axially constrained by annular spring clips  36 . Wear rings  37  constrain axial compression springs  38 . Said axial compression springs  38  exert a resilient axial force such as to maintain resilient, axial, contact of seal rings  39  with said rotational armature  32  and axial ends of radial vanes  40 . The outer periphery of each said seal ring  39  features an axially extended annular flange fitted with circumferential channels such as to create a cascade type fluid seal between said seal ring  39  and the bore of aforesaid containment cylinder  1 . Radial vane anchor sleeve  41  is concentrically secured on aforesaid rotational shaft  26  by means of a close tolerance mechanical spline connection such that said radial vane anchor sleeve  41  and aforesaid rotational shaft  26  function as a single rotational entity. Each radial vane articulated extension  42  is secured to one said radial vane  40  and to said radial vane anchor sleeve  41  by hinged connections. Radial compression springs  43  exert a resilient radial force such as to thrust each said radial vane  40  radially outward relative to said rotational armature  32 . Manifold  10  and supply port  44  in association with discharge port  45  and discharge manifold  13  provide conduit for movement of internal environmental control air and atomized liquid lubricant through the machine interior. Drain ports  46  extend though the wall of aforesaid containment cylinder  1  to provide conduit for discharge of excess liquid lubricant to aforesaid discharge manifold  24 . 
     With reference to FIG. 5, the rotational axis of rotational shaft  26  is coincident with the bore axis of aforesaid containment cylinder  1 . The rotational axis of aforesaid rotational armature  32  and the bore axis of aforesaid containment cylinder  1  are separated by radial distance “X.” A plurality of interference fitted dowel pins  47  mechanically secure aforesaid coaxial components of rotational armature  32 . The annulus of aforesaid rotational armature  32  features a number of radial slots  48  equidistantly spaced around its outer periphery and extending radially through the annulus thickness. Each said radial slot  48  accommodates one aforesaid radial vane  40  and two aforesaid radial compression springs  43 . Each said radial slot  48  is sized to closely constrain aforesaid radial vane  40  at the outer and inner peripheries of the annulus of aforesaid rotational armature  32  but allow relative sliding motion. The annulus of aforesaid rotational armature  32  also incorporates a plurality of surface area augmentation slots  49  interspaced between said radial vane slots  48 . Said surface area augmentation slots  49  extend partially through the said rotational armature  32  annulus from its inner periphery and facilitate transfer of waste heat from said rotational armature  32  to internal environmental control media. Port  50  provides conduit for supply of combustion air from aforesaid combustion air supply manifold  9  through the wall of aforesaid containment cylinder  1 . Port  51  provides conduit for discharge of expended combustion product through the wall of aforesaid containment cylinder  1  to aforesaid combustion products discharge manifold  15 . Port  52  within aforesaid containment cylinder  1  provides conduit for hot combustion product for controlled combustion propagation. Details of combustion port arrangements are discussed in a later paragraph. Aforesaid injector  19  provides conduit for delivery of finely dispersed fuel through the wall of aforesaid containment cylinder  1  and aforesaid igniter  20  provides conduit for electrical power through the wall of aforesaid containment cylinder  1  to initiate combustion. Each aforesaid radial vane articulated extension  42  is secured to one aforesaid radial vane  40  and aforesaid radial vane anchor sleeve  41  by hinged connections. Also each aforesaid radial vane  40  is fitted with radial vane edge seal  53  at its outer periphery. Details of aforesaid radial vane  40  and associated components are discussed in a later paragraph. 
     With reference to FIG. 6, at this section the thickness of the annulus of aforesaid rotational armature  32  is increased and aforesaid radial vane slots  48  extend from the outer periphery of aforesaid rotational armature  32  partially through the annulus thickness. Aforesaid radial vanes  40  are reduced in radial width to be accommodated within the radial depth of aforesaid radial vane slots  48 . Aforesaid area augmentation slots  49  penetrate the annulus structure in an axial direction and provide conduit for discharge of excess liquid lubricant from inside aforesaid rotational armature  32 . As previously noted aforesaid radial vane anchor sleeve  41  is concentrically secured on aforesaid rotational shaft  26  by a closely fitted spline connection. As previously noted, aforesaid port  50  from aforesaid combustion air supply manifold  9  and aforesaid port  51  to aforesaid combustion products discharge manifold  15  provide conduit for movement of working fluid through the wall of aforesaid containment cylinder  1 . 
     With reference to FIG. 7, at this section the inner and outer diameters of aforesaid rotational armature  32  are reduced. The outer periphery of aforesaid axial seal ring  39  maintains a close tolerance, rotationally sliding fit with the bore of aforesaid containment cylinder  1 . The inner periphery of aforesaid axial seal ring  39  is sized to permit radial clearance from the outer periphery of aforesaid rotational armature  32 . Ports  54  installed in the face of aforesaid seal ring  39  provide conduit for discharge excess liquid lubricant from within the rotational assembly. As previously noted aforesaid radial vane anchor sleeve  41  is concentrically secured on aforesaid rotational shaft  26  by a closely fitted spline connection. 
     With reference to FIG. 8, as previously noted the outer periphery of aforesaid axial seal ring  39  maintains a close tolerance, rotationally sliding fit with the bore of aforesaid containment cylinder  1 . The outer periphery of aforesaid wear ring  37  maintains a close tolerance, sliding fit with the inner periphery of the axially extended peripheral flange of aforesaid axial seal ring  39 . The inner periphery of aforesaid wear ring  39  is sized to permit radial clearance from the outer periphery of the flange of aforesaid axial retainer ring  35 . Aforesaid axial retainer ring  35  is concentrically installed on aforesaid rotating armature  32  with a close tolerance, sliding, fit. As noted in prior paragraphs, radial vane anchor sleeve  41  is concentrically secured on rotational shaft  26  by a closely fitted spline connection. Aforesaid port  46  and aforesaid drain manifold  24  provide conduit for the removal of excess liquid lubricant from the interior of aforesaid containment cylinder  1 . 
     With reference to FIG. 9, aforesaid containment cylinder end structure  2  accommodates aforesaid rotational bearing  33  for support of aforesaid rotational armature  32 . Aforesaid rotational bearing  27  for support of aforesaid rotational shaft  26  is accommodated in aforesaid bearing carrier  25 . 
     With reference to FIG. 10, rotational bearing seal retainer  29  secured to aforesaid bearing carrier  25  axially constrains aforesaid bearing seal  28  associated with aforesaid rotational shaft  26 . Aforesaid port  44  provides conduit for movement of internal environmental control air and finely dispersed liquid lubricant through aforesaid bearing carrier  25  to the internal mechanical assembly. 
     With reference to FIG. 11, aforesaid port  50  consists of a plurality of openings uniformly distributed throughout the axial length of containment cylinder  1  and provides conduit for combustion air from aforesaid combustion air supply manifold  9  through the wall of aforesaid containment cylinder  1 . The elongated openings of aforesaid combustion products discharge port  51  are interspersed between the openings of aforesaid combustion air supply port  50 . 
     With reference to FIG. 12, aforesaid port  51  consists of a plurality of openings uniformly dispersed throughout the axial length of containment cylinder  1  and provides conduit for combustion product through the wall of containment cylinder  1  to discharge manifold  15 . The elongated openings of aforesaid combustion air supply port  50  are interspersed between the openings of aforesaid combustion products discharge port  51 . 
     With reference to FIG. 13, aforesaid continuous combustion port  52  consists of a plurality of peripheral channels installed in the bore periphery and uniformly dispersed throughout the axial length of aforesaid containment cylinder  1 . 
     With reference to FIG. 14 each radial vane assembly consists of an aforesaid radial vane  40 , an aforesaid radial vane articulated extension  42 , and an aforesaid radial vane edge seal  53 . The aforesaid radial vane is connected to the aforesaid radial vane articulated extension  42  by a hinge type connection secured by a hinge pin  55 . 
     With reference to FIG.  15  and FIG. 16, aforesaid radial vane  40  features a material concentration on its radially outermost axial edge to accommodate an aforesaid vane-edge seal  53 . Aforesaid radial vane edge seal  53  engages the outer peripheral edge of each said radial vane  40  by means of a closely fitted, journal bearing type, interface sized to allow partial relative rotation. Aforesaid radial vane edge seal  53  is a relatively thin spring-grade steel structure axially bifurcated on its outer peripheral edge such as to maintain resilient contact with the bore of aforesaid containment cylinder  1 . Aforesaid radial vane  40  also features a material protrusion on each side to engage aforesaid radial compression springs  43 . Aforesaid radial vane articulated extension  42  is a quasi-rectangular panel structure connected to the aforesaid radial vane  40  and aforesaid radial vane anchor sleeve  41  by hinge type connections with each connection secured by one aforesaid hinge pin  55 . 
     With reference to FIG. 17, beyond the axial limits of hinged length, the radial breadth of aforesaid radial vane  40  is reduced. The aforesaid radial vane edge seal  53  is incorporated as previously discussed.