Abstract:
A rotary vane device for hydraulic transmission of mechanical energy with industrial scale measures of power and rotational velocity. The device offers high measures of both volumetric efficiency and rotational velocity and hence substantial measures of functional excellence in terms of power density and functional efficiency. Additionally the device functions without the use of reciprocating primary components and for this reason potentially offers substantial measures of excellence in terms of enhanced operational reliability and relatively low measures of radiated mechanical noise and vibration.

Description:
BACKGROUND OF THE INVENTION 
     For certain power distribution applications transmission of mechanical energy by hydraulic manipulation is preferable to other options for reasons of power density, arrangement flexibility, and controllability. At the present time, machines employed for the hydraulic transmission of mechanical energy primarily consist of hydraulic pumps and hydraulic motors employing reciprocating mechanical motion of pistons and valves to accomplish movement of pressurized working fluid. Due to reciprocation of primary function components the working fluid flow inherently involves the presence of pressure fluctuations and hence inherently feature the potential for propagation of undesirable noise and mechanical vibration. Hydraulic power systems featuring relatively high measures of working fluid pressure and relatively low measures of working fluid flow velocity are often identified as “hydrostatic” power systems. 
     Over a number of years significant inventive effort has been directed toward the derivation of a “rotary” fluid displacement machine employing only rotationally dynamic mechanical components for working fluid manipulation. In comparison with reciprocating machines the rotary machine is perceived to offer advantages in terms of mechanical simplification and elimination of fluid flow pressure fluctuations. The radial vane type rotary machine has been the subject of particular attention in this regard. 
     Conceptually the rotary vane machine features a stationary hollow containment structure consisting of a containment cylinder with a precisely or approximately circular bore and with an end closure structure installed at each axial end. Said containment structure is fitted with ports for induction and discharge of working fluid through the structural boundary. A rotational armature approximately circular in cross-section and concentrically secured on a rotational shaft is installed within the bore of said containment cylinder. The diameter of said rotational armature is proportioned to create an annular cavity between the peripheral surface of said rotational armature and the bore of said containment cylinder. Said rotational shaft axially extends through the axial length of said containment structure and is radially constrained by rotational bearings. Axial ends of said rotational shaft are configured as necessary to interface with external rotational power systems. Said rotational shaft is aligned with its rotational axis parallel to but radially separated from the bore axis of said containment cylinder. Said rotational armature accommodates an axially aligned radial vane slot at each of several centers equally spaced around its periphery and said radial vane slot is proportioned to accommodate and provide sliding support for one radial vane. Said radial vane is axially proportioned to extend through the axial length of said rotational armature and radially proportioned to extend from within said radial vane slot to interface with the bore of said containment cylinder. Collectively the radial vanes subdivide said annular cavity into a number of annular segmental chambers. Since the rotational axis of said rotational shaft is radially separated from the bore axis of said containment cylinder the volume of each annular segmental chamber is dependent upon its rotational position and is cyclically manipulated upon rotation of said rotational armature. The cyclical relationship between annular segmental chamber volume and rotation of said rotational armature equates to the cyclical relationship between contained volume and piston movement featured in reciprocating type fluid displacement machines. 
     A number of patents have been awarded for rotary vane hydraulic power machine concepts however as of this writing none of the concepts presented in prior art are known to have matured sufficiently to demonstrate adequacy regarding one or more practical functional viability parameters. Functional viability of energy transmission machines is measured by their capability to meet thresholds for efficiency and power density within constraints imposed by natural physical phenomena. 
     The efficiency and power density of hydraulic rotational power machines are directly influenced by machine capabilities defined in terms of volume cycle efficiency, pressure cycle efficiency, mechanical efficiency, working fluid pressure amplification, and rotational velocity. 
     For rotary vane type machines volume cycle efficiency is directly related to the proportional relationship between the internal bore diameter of the containment structure and the diameter of the internal rotational armature. Pressure cycle efficiency is directly influenced by both the number of segmental chambers surrounding said rotational armature and the distance separating the rotational axis of said rotational armature from the bore axis of said containment structure. Pressure cycle efficiency is inversely influenced the relative thickness of the radial vanes and by hydrodynamic impedance imposed on the movement of working fluid as required to accomplish the cyclical manipulation. 
     Analysis demonstrates that the threshold for adequate pressure cycle efficiency is attained only when the number of segmental chambers surrounding said rotational armature exceeds a certain minimum value. However the radial vanes are, collectively, a potentially significant cause of degradation in mechanical efficiency due to frictional resistance at sliding interfaces. Additionally the radial vanes are, collectively, a potentially significant cause of degradation in mechanical efficiency if ancillary pumping of working fluid is incurred by reciprocating motion of the radial vane within the radial vane slot. For these reasons functional viability is dependent upon derivation the optimum balance between several efficiency considerations. 
     In addition to the efficiency considerations discussed above, power density is directly influenced the magnitude of working fluid pressure amplification, and the magnitude of rotational velocity. However hydraulic machines function by manipulation of an essentially non-compressible working fluid and so entail the possible occurrence of noise, vibration, and efficiency degradation due to high-pressure hydrodynamic impacting and low-pressure hydrodynamic cavitation. For these reasons acceptable limits for working fluid pressure amplification and rotational velocity and technical approaches for avoidance of hydrodynamic impacting and hydrodynamic cavitation phenomena are also functional viability considerations. 
     The principal features of several rotary vane type hydraulic machines presented in prior patent disclosures are reviewed below. 
     U.K. Pat. No. 114,584, U.K. Pat. No. 577,569, and Japan Pat. No. 63-9685 each discloses a rotary vane pump device featuring a stationary housing with an end closure structure installed at each axial end and with fluid transfer ports. Within said stationary housing a rotor is concentrically secured to a rotational shaft. Said rotational shaft is radially and axially constrained by rotational bearings installed in said end closure structure. Said rotor is fitted with an axially aligned radial vane slot at each of several centers uniformly distributed around its periphery. Each said rotor slot annularly constrains one radial vane but permits relative sliding motion in a radial direction. Said radial vane is radially constrained at each axial end by a rotating ring configured as an axially extended peripheral flange on a rotating disk. Said rotating ring is proportioned to maintain a constant distance between the outer peripheral edge of said radial vane and the bore of said stationary housing. Centripetal load induced by said radial vane due to rotor rotation is imposed on the said rotating ring by direct edge contact of said radial vane. Said rotating disk is radially and axially constrained by a low friction rotational bearing. The rotational axis of said rotating disk is aligned to be concentric with the longitudinal axis of the bore of said stationary housing. Said rotating disk maintains contact with the axial end of each said radial vane and with the axial end of said rotating armature. 
     All disclosures identified above present the primary mechanical features required for manipulation of hydraulic fluids and substantially focus on technical approaches toward minimization of friction particularly as related to radial vanes. However all disclosures identified above are essentially silent regarding other mechanical considerations inherently related to the functional viability of rotary vane hydraulic power devices. 
     BRIEF SUMMARY OF THE INVENTION 
     This disclosure presents a rotary vane device for hydraulic transmission of rotational mechanical energy on a scale commonly associated with modern hydraulic power systems in industrial and marine service. Primary manipulation of the working fluid is accomplished without the use of reciprocating pistons, valves, or similar mechanical components and the device may function as either a hydraulic pump or hydraulic motor depending only upon the relative direction of flow of the working fluid. 
     The device primarily consists of a stationary structure for system containment, an internal rotational assembly for energy conversion, and volume compensating valves for protection from excessive pressure fluctuations. Said stationary structure primarily features a containment cylinder with a circular bore installed with diametrically opposed working fluid induction ports and working fluid discharge ports distributed along its axial length and with an end closure structure mechanically secured at each axial end. Said rotational assembly primarily features a rotational shaft, a rotational armature, a set of radial vanes, and one freely rotating radial vane constraint ring installed at each axial end of said armature. Said rotational shaft extends through the axial length of said stationary structure and is simply supported and radially constrained by a low-friction rotational bearing installed in each end closure structure. Said rotational shaft is aligned to rotate on an axis parallel to but radially separate from the bore axis of said containment cylinder. Said rotational shaft is configured to interface with an external rotational power generator or rotational power transmission device. Said rotational armature is concentrically installed on said rotational shaft within said containment cylinder. Said rotational armature features a circular cross-section and is configured as a hollow structural annulus fitted with a structurally integral disk at each axial end. Said rotational armature is diametrically proportioned with an outer diameter of approximately ninety percent of the effective bore of said containment cylinder. A radial vane slot axially proportioned to extend through the axial length of said rotational armature is installed at each of twelve centers uniformly distributed around the periphery of said rotational armature. Said radial vane slot is radially proportioned to extend through the thickness of said structural annulus to preclude efficiency degradation due to radial vane pumping. Said radial vane slot accommodates and annularly constrains one radial vane between linear bearing inserts. Said radial vane is proportioned to extend through the axial length of said rotational armature, radially extend through said structural annulus to approach the bore of said containment cylinder, and permit relative sliding motion within said radial vane slot. A radial vane edge-seal proportioned to make resilient sealing contact with the bore of said containment cylinder is installed on the radially outermost axial edge of said radial vane. A sliding block is installed at each axial end of said radial vane. Said radial vane constraint ring is diametrically proportioned to make a close but sliding fit with the bore of said containment cylinder and is axially and radially constrained by low-friction rotational bearings. Said radial vane constraint ring features an axially extended flange on its outer periphery with said axially extended flange diametrically and axially proportioned to radially constrain said sliding block installed on said radial vane. Said radial vane constraint ring accommodates a concentrically installed axial wear ring and a concentrically installed axial compression spring. Said axial compression spring is proportioned to constrain said axial wear ring to maintain resilient pressure contact with the axial end of said rotating armature. Axially aligned ports with non-return valves installed in the axial face of said wear ring permit high-pressure working fluid to augment the actuation force of said axial compression spring. A high-pressure volume compensation valve and a low-pressure volume compensation valve are installed in said containment cylinder and aligned to preclude the occurrence of hydraulic impacting hydraulic cavitation respectively. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a side elevation illustrating the axial disposition of external components. FIG. 1 also presents section indicators defining the axial locations and projection directions for FIG.  2  and FIG.  3 . 
     FIG.  2  and FIG. 3 are, respectively, left hand and right hand end elevations from the viewpoints of the section indicators given in FIG.  1  and illustrate the radial disposition of external components. 
     FIG. 4 is a sectional elevation illustrating the internal general assembly along the axis of rotation. FIG. 4 is supported by enlarged scale illustrations of details given in FIG. 4A, FIG. 4B, and FIG.  4 C. Section indicators given in FIG. 4 define the axial locations and projection directions for FIG.  5  through FIG.  10 . 
     FIG. 5 is a cross section at mid-length of the containment cylinder and illustrates the radial arrangement of working fluid induction ports, working fluid discharge ports, and other functionally significant components. 
     FIG. 6 is a cross section close to the axial end of the rotational armature and illustrates arrangements for radial vane end constraint. 
     FIG. 7 is a cross section at the axially innermost face of one wear ring and primarily illustrates the radial arrangement at the axial interface of the radial vane end constraint assembly. 
     FIG. 8 is a cross section at the axially outermost face of one wear ring and primarily illustrates the non-return reed-valve installation. 
     FIG. 9 is a cross section at the axially innermost face of one radial constraint ring and illustrates the arrangement and geometry of the axial compression spring. 
     FIG. 10 is a cross section through the mid-length of one rotational bearing assembly and illustrates arrangements for radial constraint of primary rotational components. 
     FIG. 11 is a horizontal elevation and illustrates the axial arrangement of working fluid induction ports and working fluid discharge ports at the external interface of the containment cylinder. 
     FIG. 12 is a cross section through the stationary containment cylinder and illustrates the radial arrangement and geometry of working fluid induction ports and working fluid discharge ports. 
     FIG. 13 is a cross section through the stationary containment cylinder and illustrates the continuity of containment structure between working fluid induction ports and working fluid discharge ports. 
     FIG. 14 is a sectional elevation through the stationary containment cylinder and illustrates the axial distribution of working fluid induction ports and working fluid discharge ports. 
     FIG. 15 is a sectional elevation of one radial vane and illustrates the significant geometric and assembly details of said radial vane and directly associated components. Section indicators given in FIG. 15 define the axial locations and projection directions for FIG.  16  and FIG.  17 . 
     FIG. 16 is an elevation at the axial end of one radial vane and illustrates radial vane end geometry and interface details. 
     FIG. 17 is a section through one radial vane and its associated radial vane-edge seal and illustrates the installation interfaces and construction details of one radial vane-edge seal. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Please note that the device assembly is geometrically symmetrical around the middle of the axial length of the containment structure. 
     With reference to FIG. 1, FIG. 2, and FIG. 3, containment cylinder  1  and end closure structure  2  are mechanically secured by machine screw  3  installed at each of twenty-four centers. Similarly containment cylinder  1  and end closure structure  4  are mechanically secured by machine screw  5  installed at each of twenty-four centers. Bearing carrier  6  is mechanically secured by machine screw  8  installed at each of twelve centers and bearing carrier  7  is mechanically secured by machine screw  9  installed at each of twelve centers. Machine screw  12  and machine screw  13  each installed at each of twelve centers mechanically secure rotational shaft bearing retainer  10  and rotational shaft bearing retainer  11  respectively. Rotational shaft  14  axially protrudes through rotational shaft seal retainer  10  and rotational shaft seal retainer  11  and the axial ends of rotational shaft  14  are each configured to interface with an external rotational power system appropriate for the intended function. Fluid induction manifold  15  interfaces with fluid supply conduit  16  and working fluid discharge manifold  17  interfaces with working fluid discharge conduit  18 . Volume compensation valve  19  and volume compensation valve  20  are mechanically secured to containment cylinder  1  at diametrically opposed locations later discussed.  21  and  22  are conduits for disposal of fractional quantities of working fluid discharged from volume compensation valve  19  and volume compensation valve  20  respectively. Drain sump  23 , drain sump  24 , and drain manifold  25  are conduits for disposal of fractional quantities of waste working fluid from containment cylinder  1 . 
     With reference to FIG. 4, FIG. 4A, FIG. 4B, and FIG. 4C, rotational shaft  14  extends throughout the length of stationary containment cylinder  1  and passes through end closure structure  2  and end closure structure  4 . Low-friction rotational shaft bearing  26  and low-friction rotational shaft bearing  27  radially and axially constrain rotational shaft  14 . Bearing seal  28  and bearing seal  29  preclude working fluid contamination of rotational shaft bearing  26  and rotational shaft bearing  27  respectively. Bearing seal  30  and bearing seal  31  preclude lubrication leakage from rotational shaft bearing  26  and rotational shaft bearing  27  respectively. Seal retainer  10  and seal retainer  11  axially secure bearing seal  30  and bearing seal  31  respectively.  32  and  33  are conduits for supply of lubrication media to rotational shaft bearing  26  and rotational shaft bearing  27  respectively.  34  and  35  are conduits for discharge of excess lubrication media from rotational shaft bearing  26  and rotational shaft bearing  27  respectively. Rotational armature  36  is concentrically secured on rotational shaft  14  by spline  37  and spline  38 . Low-friction thrust bearing  39  and low friction radial bearing  40  axially and radially constrain axially extended flange  41  integrally installed on the inner periphery of radial vane axial constraint ring  42 . Low-friction thrust bearing  43  and low friction radial bearing  44  axially and radially constrain axially extended flange  45  integrally installed on the inner periphery of radial vane axial constraint ring  46 . Bearing  39 , bearing  40 , bearing  43 , and bearing  44  are aligned with their rotational axes coincident with the axis of containment cylinder bore  47 . Bearing seal  48  and bearing seal  49  preclude working fluid contamination of thrust bearing  39  and thrust bearing  43  respectively. Bearing seal  50  and bearing seal  51  preclude lubrication leakage from radial bearing  40  and radial bearing  44  respectively.  52  is a conduit for supply of lubrication media to bearing  39  and bearing  40  and  53  is a conduit for supply of lubrication media to bearing  43  and bearing  44 .  54  is a conduit for discharge of lubrication media from bearing  39  and bearing  40  and  55  is a conduit for discharge of lubrication media from bearing  43  and bearing  44 . Radial vane radial constraint ring  56  and radial vane radial constraint ring  57  each consist of an axially extended flange integrally installed on the outer periphery of radial vane axial constraint ring  42  and the outer periphery of radial vane axial constraint ring  46  respectively. Radial vane radial constraint ring  56  and radial vane radial constraint ring  57  are each diametrically proportioned to maintain a sliding fit with the containment cylinder bore  47 . Four axially spaced circumferential channels  58  and four axially spaced circumferential channels  59  are installed in the outer periphery of radial vane radial constraint ring  56  and radial vane radial constraint ring  57  respectively. Radial vane  60  is radially constrained by radial vane radial constraint ring  56  at one axial end and radial vane radial constraint ring  57  at the other. Radial vane edge seal  61  is installed on the outermost peripheral edge of radial vane  60 . Wear ring  62  is diametrically proportioned to maintain a constrained sliding fit between the radially outermost surface of axially extended flange  41  and the radially innermost surface of radial vane radial constraint ring  56 . Wear ring  65  is diametrically proportioned to maintain a constrained sliding fit between the radially outermost surface of axially extended flange  45  and the radially innermost surface of radial vane radial constraint ring  57 . Wear ring  62  is installed with structurally integral, axially extended flange  63  on its outer periphery and structurally integral, axially extended flange  64  on its inner periphery. Wear ring  65  is installed with structurally integral, axially extended flange  66  on its outer periphery and structurally integral, axially extended flange  67  on its inner periphery. Axial compression spring  68  and axial compression spring  69  are proportioned to induce, respectively, wear ring  62  and wear ring  65  to maintain resilient axial contact with rotational armature  36 . Working fluid transfer port  70  and working fluid transfer port  71  allow movement of pressurized working fluid to axial compression spring chamber  72  and axial compression spring chamber  73  respectively. Non-return reed valve  74  and non-return reed valve  75  preclude movement of pressurized working fluid from axial compression spring chamber  72  and axial compression spring chamber  73  respectively.  76  and  77  are conduits for discharge of leaked working fluid from containment cylinder  1  to waste working fluid drain sump  23  and working fluid drain sump  24  respectively. Sliding block  78  and sliding block  79  are proportioned to distribute the centripetal force induced by rotation of radial vane  60  over appropriate areas of radial vane radial constraint ring  56  and radial vane radial constraint ring  57  respectively. Volume compensation valve  19  and volume compensation valve  20  extend partially through and are mechanically secured to containment cylinder  1 .  80  and  81  are conduits for movement of working fluid to volume compensation valve  19  and volume compensation valve  20  respectively. Within volume compensation valve  19  sliding piston  82  is resiliently constrained between outer axial compression spring  83  and inner axial compression spring  84 . Outer axial compression spring  83  is proportioned to permit radially outward movement of sliding piston  82  in reaction to working fluid pressure pulses with a high-pressure threshold in excess of prescribed maximum system pressure and frequency equal to radial vane passage frequency. Inner axial compression spring  84  is proportioned to decelerate sliding piston  82  when returning to its rest location. Threaded core  85  is proportioned to axially secure outer axial compression spring  83  and compresses outer axial compression spring  83  and inner axial compression spring  84  to obtain appropriate valve activation parameters.  21  is a conduit for return of leakage working fluid to the working fluid discharge manifold. Within volume compensation valve  20  sliding piston  86  is resiliently constrained between inner axial compression spring  87  and outer axial compression spring  88 . Inner axial compression spring  87  is proportioned to permit radially inward movement of sliding piston  86  in reaction to working fluid pressure pulses with a low-pressure threshold less than prescribed minimum system pressure and a frequency equal to radial vane passage frequency. Outer axial compression spring  88  is proportioned to decelerate sliding piston  86  when returning to its rest location. Threaded core  89  axially secures outer axial compression spring  88  and compresses outer axial compression spring  88  and inner axial compression spring  87  to obtain appropriate valve activation parameters.  22  is a conduit for return of leakage working fluid to the working fluid supply manifold. 
     With reference to FIG. 5, the vertical plane of the rotational axis of rotational shaft  14  is horizontally coincident with the vertical plane of the longitudinal axis of containment cylinder bore  47 . The horizontal plane  90  of the rotational axis of rotational shaft  14  is separated from the horizontal plane  91  of the axis of the containment cylinder bore  47  by radial distance “X”. Rotational armature  36  is circular in cross-section and is installed with one axially aligned radial vane slot  92  at each of twelve equidistantly spaced centers around its periphery. Radial vane slot  92  is configured and proportioned to closely constrain one linear bearing segment  93  in the side of said slot oriented in the direction of rotation and closely constrain one linear bearing segment  94  in the side of said slot opposite to the direction of rotation. Linear bearing segment  93  and linear bearing segment  94  are preferably constructed from hard graphite, ceramic or other wear resistant, low friction, bearing material. Radial vane  60  is proportioned to make a closely constrained sliding fit between the opposing faces of linear bearing segment  93  and linear bearing segment  94  and is radially constrained to maintain a relatively small distance between its radially outermost edge and the bore  47  of stationary containment cylinder  1  at all rotational positions. One vane edge seal  61  is installed on the outer axial edge of radial vane  60  to resiliently close the gap between radial vane  60  and stationary containment bore  47 . Working fluid induction port  95  and working fluid discharge port  96  are interfaced with working fluid supply manifold  15  and with working fluid discharge manifold  17  respectively.  16  and  18  are terminations of the external working fluid distribution system. Volume compensation valve  19  is installed in containment cylinder  1  on the radian at which the peripheral surface of rotational armature  36  is least distant from containment cylinder bore  47 . Volume compensation valve  20  is installed in containment cylinder  1  on the radian at which the peripheral surface of rotational armature  36  is most distant from containment cylinder bore  47 . Internal details of volume compensation valve  19  and volume compensation valve  20  were previously discussed. 
     With reference to FIG. 6, rotational armature  36  is integrally secured to rotating shaft  14  by closely fitted mechanical spline  37 . One sliding block  78  attached to radial vane  60  maintains uniform sliding contact with the radially innermost surface of radial vane radial constraint ring  56 . Radial vane  60  is constrained between the opposing faces of linear bearing segment  93  and linear bearing segment  94 . 
     With reference to FIG. 7, the outer diameter of radial vane radial constraint ring  56  is proportioned to maintain a sliding fit with containment cylinder bore  47 . Wear ring  62  is proportioned to maintain a closely constrained but sliding fit with the inner periphery of radial vane radial constraint ring  56  and the outer surface of axially extended flange  41 . The axial face of wear ring  62  accommodates a working fluid transfer port  70  installed on each of twelve equally spaced radian centers. 
     With reference to FIG. 8, wear ring flange  66  is diametrically proportioned to maintain a constrained sliding fit with the inner peripheral surface of radial vane radial constraint ring  57  and wear ring flange  67  is diametrically proportioned to maintain a constrained sliding fit with the outer peripheral surface of radial vane constraint ring flange  45 . Non-return reed valve  75  is a thin flat-spring radial projection installed at each of twenty-four equidistantly spaced radial centers around the inner periphery of reed valve ring  97 . Non-return reed valve  75  is radially proportioned and aligned to cover one working fluid transfer port  71  discussed in the previous paragraph. Reed valve ring  97  is diametrically proportioned to maintain a constrained fit with the inner axial surface of wear ring peripheral flange  66 . 
     With reference to FIG. 9, axial compression spring  69  is a quasi-flat ring with an inner diameter proportioned to maintain a constrained sliding fit with wear ring peripheral flange  67 . The outer diameter of annular axial compression spring  69  is proportioned to maintain a small distance of separation from the inside surface of wear ring outer peripheral flange  66 . Axial compression spring  69  features an integral but semi-independent radial spring segment  98  installed at each of twenty-four equidistantly spaced radial centers around a common root ring  99 . Material thickness and axial shaping of annular axial compression spring  69  are proportioned to fulfill spring rate and axial extension requirements as specifically appropriate for intended service. For the purpose of this disclosure annular axial compression spring  69  is illustrated as a single entity however an assembly consisting of a multiplicity of annular axial compression spring entities may be selected as necessary to fulfill particular service requirements. Arrangements of other illustrated components were discussed in prior paragraphs. 
     With reference to FIG. 10, rotational shaft bearing  26  installed in bearing carrier  6  radially supports rotational shaft  14 . Rotational bearing  40  installed in end closure structure  2  radially supports rim flange  41 .  32  and  34  are conduits for supply of lubricant to bearing  26  and discharge of excess lubricant from bearing  26  respectively. 
     With reference to FIG. 11, FIG. 12, FIG. 13, and FIG. 14, working fluid induction port  95  and working fluid discharge port  96  are opposite handed but geometrically similar and each consists of an elongated opening penetrating the wall of containment cylinder  1 . For the purpose of this disclosure one working fluid induction port  95  and one working fluid discharge port  96  are installed at each of six centers distributed along the axial length of containment cylinder  1 . 
     With reference to FIG. 15, radial vane  60  primarily consists of a flat panel structure. Sliding block  78  is secured on one radially outermost axial end of radial vane  60  and sliding block  79  secured at the other radially outermost axial end of radial vane  60 . Radial vane edge seal  61  is secured along the radially outermost axial edge of radial vane  60 . 
     With reference to FIG. 16, sliding block  78  and sliding block  79  are secured to radial vane  60  by closely fitted rotational bearing interface  100  and closely fitted rotational bearing interface  101  respectively. Rotational bearing interface  100  and rotational bearing interface  101  are proportioned to allow only partial rotation of the attached sliding block relative to radial vane  60 . 
     With reference to FIG. 17, radial vane edge seal  61  is, essentially, a relatively thin cylindrical spring structure. One radial vane edge seal  61  is installed on the radially outermost edge of radial vane  60  by a closely fitted rotational bearing interface  102 . Rotational bearing interface  102  is proportioned to allow only partial rotation of radial vane edge seal  61  relative to radial vane  60 . The radially outermost side of radial vane edge seal  61  is axially bifurcated and proportioned to allow both edges of said axial bifurcation to maintain resilient sliding contact with containment cylinder bore  47 .