Abstract:
A rotary piston machine includes a first spheroidal element including pistons and/or cylinders and a second spheroidal element including pistons and/or cylinders, wherein the first element can move relative to the second element. The machine can be used as part of a pump, compressor, or engine.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS  
       [0001]    Priority of my U.S. Provisional Patent Application No. 60/375,889, filed 26 Apr. 2002, incorporated herein by reference, is hereby claimed. 
     
    
     
       STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT  
         [0002]    Not applicable  
         REFERENCE TO A “MICROFICHE APPENDIX” 
         [0003]    Not applicable  
         BACKGROUND OF THE INVENTION  
         [0004]    1. Field of the Invention  
           [0005]    The present invention relates to compressors, pumps, and engines. More particularly, the present invention relates to a pumping apparatus that includes two housing or rotor sections that engage a spherical bearing that enables each housing section to rotate together but about different axes of rotation. These axes intersect to form an obtuse angle. Valved pistons on the housing sections pump fluid as the housing sections are rotated.  
           [0006]    2. General Background of the Invention  
           [0007]    The three predominate forms of pumping, driving and compressing that are available on the market at the time of this document are reciprocating, mechanical screw and rotary and centrifugal.  
           [0008]    The following patent documents are incorporated herein by reference:  
           [0009]    U.S. Pat. Nos.: 3,945,766; 4,277,228; 4,858,480; 5,249,512; 5,647,729; 6,352,418; 6,368,072; JP 02305381A and U.S.2001/0014288.  
           [0010]    U.S. Published patent application Ser. No. U.S.2001/0014288 discloses a pump with a back and forth piston motion (see FIG. 12).  
         BRIEF SUMMARY OF THE INVENTION  
         [0011]    The present invention provides a unique pump apparatus. However, the mechanism of the present invention can also be configured to be a compressor or engine. As used herein, the term pump should be broadly construed to include any piston machine including but not limited to a pump, a compressor or engine.  
           [0012]    The apparatus includes a first housing or rotor section having a concave portion. A second housing section is provided that also has a concave portion.  
           [0013]    A spherically shaped bearing member forms an interface between the first and second housing sections so that the concave portion of each of the housing sections fits and conforms to the outer surface of the spherically shaped bearing member. The outer surface of the spherical bearing member and the inner surface of the concave portions are preferably identically curved.  
           [0014]    A first shaft is provided for rotating the first housing section about a first axis. A second shaft can be provided for rotating with the second housing section about a second axis that forms an obtuse angle with the first axis.  
           [0015]    A plurality of valved pistons are positioned circumferentially about the spherically bearing member, each piston having an upper portion on the first housing section and a second portion on the second housing section.  
           [0016]    A means is provided for rotating one of the shafts to initiate the pumping apparatus. The rotating means can be, for example, a motor, engine or the like.  
           [0017]    The pistons are interconnected so that they interconnect the first and second housing sections. When one housing section is rotated, the other housing section rotates with it. As a shaft (e.g., powered or driven) is rotated, its housing sections rotate about different axes that form an obtuse angle. Because of this obtuse angle seen in FIGS.  5 - 10 , the periphery of one housing section approaches and then spaces away from the periphery of the other housing section in continuous fashion along a circumferential path.  
           [0018]    A fluid flow path transmits fluid though the housing sections using the pistons. Each piston reciprocates to pump fluid under pressure as the housing sections rotate.  
           [0019]    The first and second housing sections can each have a generally rounded periphery. At least one of the concave sections of the housing sections, and preferably both of the concave sections of the housing sections, closely conform to and fit the outside surface of the spherically shaped bearing member. The pistons can be equally spaced apart, positioned radially of and circumferentially around the spherically shaped bearing member.  
           [0020]    The pistons preferably each include interlocking portions of the first and second housing sections.  
           [0021]    Each piston can include a projecting part of one of the housing sections and a socket part of the other of the housing sections. The projecting and socket parts interlock. Each piston is valved (e.g., two check valves) so that as each piston expands and contracts, fluid is pumped through the piston in a desired direction.  
           [0022]    The machine (e.g., pump, compressor, engine) of the present invention was invented to replace the three predominate forms of pumping, driving and compressing that are available on the market at the time of this document.  
           [0023]    The machine of the present invention combines the good attributes of each and discards the inadequacies. Inherently, a reciprocating device is very flexible in its variations of flow stream acceptability while having many moving parts subject to wear and damage.  
           [0024]    This machine of the present invention has the ability to fit a wide variety of flow situations by varying speed and loading and unloading individual piston/receiver pairs. This flexibility is accomplished with very few moving parts subject to wear and damage.  
           [0025]    Mechanical screw rotary devices have few moving parts yet they cannot accept high speeds due to the geometry and shear mass of the rotating compression screws. They also require extensive sealing be it mechanical or oil flood to entrap the compression fluids. Screw type compressors fit the function of compressing fluids from a set pressure to a higher pressure at a set flow rate and can do little with varying flow conditions.  
           [0026]    The machine of the present invention institutes the small number of wear parts inherent to the screw while surpassing its ability to be flexible. Centrifugal devices have the ability to compress large quantities of fluids from low pressure to high pressure yet they accept little variations in flow rate and pressure differential. So much is the effect of variations, in a driver configuration (turbine) intricate surge control systems must be designed to protect the units against damage. In addition, very little solid particular or larger matter introduced to the flow stream will produce catastrophic and costly damage. Centrifugal devices are not positive displacement and are greatly affected by stream contents and characteristics.  
           [0027]    The machine of the present invention has the ability to compress large quantities of fluids with increased speeds or staging of the unit while not being affected adversely by the content nor characteristics of the flow stream being positive displacement and not dependant on the holding of tight engaging dimensions.  
           [0028]    Using, for example, the stream requirements of typical offshore facilities and for a summary, three types of compression are used. For vapor (low-pressure) compression, rotary oil flood screws are used to compress fluid up to low-pressure well pressures. This stream is combined with low-pressure wells and introduced to a reciprocating compressor to bring the stream first to the pressure of intermediate fluid then to deliver the fluid to a turbine driven centrifugal compressor for boosting to pipeline pressure at large flow rates.  
           [0029]    This machine of the present invention replaces all three units at the facility in a multi-stage configuration. The multi-stage unit would be setup in stage series and parallel configurations per stage if required as follows: Stage  1  is vapor compression, stage  2  is low-pressure fluid, stage  3  is intermediate pressure fluid, stage four high-pressure boost.  
           [0030]    All compression is accommodated in one multi-stage unit with less vulnerability to wear and failure and with the flexibility required. To enhance the appeal of the machine of the present invention, an engine can be used to integrally drive a multi-stage unit for an extreme savings of labor, repair, deck space platform weight and operator interface. 
       
    
    
     BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS  
       [0031]    For a further understanding of the nature, objects, and advantages of the present invention, reference should be had to the following detailed description, read in conjunction with the following drawings, wherein like reference numerals denote like elements and wherein:  
         [0032]    FIGS.  1 A- 1 B are exploded perspective views the preferred embodiment of the apparatus of the present invention and wherein the figures meet at match lines A-A;  
         [0033]    [0033]FIG. 2 is a exploded side, sectional view of the preferred embodiment of the apparatus of the present invention;  
         [0034]    FIGS.  3 A- 3 B are fragmentary sectional views of the preferred embodiment of the apparatus of the present invention showing maximum opening in FIG. 2A and minimum opening if  3 B;  
         [0035]    [0035]FIGS. 4A and 4B are schematic plan views showing one of the housing sections, with a single circle of pistons in FIG. 3A and a double circle of pistons in  3 B;  
         [0036]    [0036]FIG. 5 is a side sectional view of the preferred embodiment of the apparatus of the present invention;  
         [0037]    [0037]FIG. 6 is a side sectional elevation view of the preferred embodiment of the apparatus of the present invention;  
         [0038]    [0038]FIG. 7 is a side sectional view of the preferred embodiment of the apparatus of the present invention showing a single stage unit;  
         [0039]    [0039]FIG. 8 is a side sectional view of the preferred embodiment of the apparatus of the present invention showing a multi-stage unit;  
         [0040]    [0040]FIG. 9 is a side sectional view of the preferred embodiment of the apparatus of the present invention illustrating a free rotor engine;  
         [0041]    [0041]FIG. 10 is a side sectional view of the preferred embodiment of the apparatus of the present invention showing a dual rotor engine;  
         [0042]    [0042]FIG. 11 is a side sectional exploded view of an alternate embodiment of the preferred embodiment of the apparatus of the present invention;  
         [0043]    [0043]FIG. 12 is a top view of an alternate valve construction for use with the present invention;  
         [0044]    [0044]FIG. 13 is a side view of an alternate valve construction for use with the present invention;  
         [0045]    [0045]FIG. 14 is a side exploded view thereof for a piston valve;  
         [0046]    [0046]FIG. 15 is a side exploded view thereof for a receiver valve;  20  FIG. 16 is a top view of another, alternate pressure booster design that shows a suction inlet scoop design (the scoop acts as a pressure booster); and  
         [0047]    [0047]FIG. 17 is a side view thereof. 
     
    
     DETAILED DESCRIPTION OF THE INVENTION  
       [0048]    In FIGS. 1A, 1B and  2 - 6 , the preferred embodiment of the apparatus of the present invention is designated generally by the numeral  5 . Pump apparatus  5  includes an upper housing or rotor section  10  and a lower housing or rotor section  16 . Each of the housing sections  10 ,  16  rotate together as a unit when one of the housing sections  10  or  16  is rotated such as with a powered or driven shaft (e.g., shaft  90 ). Rotation can be clockwise or counterclockwise.  
         [0049]    The apparatus  5  includes a plurality of pistons  11 . Each piston  11  carries a suction valve assembly  40  to seal the interface between projection  18  and socket  19  of each piston  11 . Valve  40  orientation determines which side (i.e. section  10  or  16 ) is suction and which is discharge. Either section  10  or  16  can be a driver or be driven. The apparatus  5  can be used with or without spherical ball bearing  20 , though use of bearing  20  is preferred.  
         [0050]    A seal  12  on the outer surface of projection  18  part of piston  11  is provided. Seal  12  can be on the piston  11  or on the socket  19  of receiver  31 . Socket  19  of piston  11  is provided on the second housing section  16  as shown in FIGS. 1A, 1B and  2 - 6 .  
         [0051]    Housing section  10  has inlet fluid chamber  61  that is receptive of fluid to be pumped or compressed. Housing section  16  has discharge passageway  64  through which fluid being pumped is discharged. The suction valve assembly  40  is positioned in inlet fluid chamber  61 . A discharge valve assembly  50  is positioned in discharge passageway  64 .  
         [0052]    Ball or spherical bearing  20  forms an interface bearing that contacts both of the housing sections  10 ,  16  at respective dished or concaved surfaces  21 ,  22 . In FIG. 6, a gearing system  13  (e.g., toothed racks) can be optionally used to mechanically interface and transfer load between the housing sections  10 ,  16 .  
         [0053]    In FIG. 7, a single stage unit is disclosed wherein the upper and lower housing section  10 ,  16  are mounted within a block  6  that is defined by block sections  101 ,  102 ,  103 , outer surfaces  30  engaged by sections  101 ,  102 ,  103 . Seals  14  can be provided in between each housing section  10 ,  16  and block  6 . In FIG. 11, a suction pressure booster  15  can be added to housing section  10 . Torque enhancer  34  can be added to section  16 .  
         [0054]    In FIG. 11, part  15  is a pressure booster that can be finned either centrifugally or axially to boost the stream delivered to the suction valves. This booster  15  takes advantage of the fact that the rotor  10  is revolving in water and mechanically increases delivery to the compression chamber.  
         [0055]    Part  34  has the opposite effect on the stream. It operates as a torque enhancer. As fluid leaves chamber  64 , it will impinge on part  34  slightly reducing the stream pressure while giving the apparatus  5  added torque boost though fluid impact on part  34 .  
         [0056]    [0056]FIG. 8 shows a multi-stage unit  17  that can be comprised of a plurality of blocks  6  each having an apparatus  5 . Each apparatus  5  has its own flow inlet and flow outlet as shown, designated generally by the numerals  111 - 116  in FIG. 8.  
         [0057]    The obtuse angle that is formed between an axis of rotation for the sections  10 ,  16  is shown in FIG. 8 as 180° plus angle  72 . The apparatus  17  of FIG. 8 thus shows a multi-stage apparatus that could have utility, for example, in the pumping of gas when the apparatus  17  is to be used as a compressor. Each socket  19  defines a receiver  31  into which projecting portion  18  extends.  
         [0058]    An optional gearing system  13 , 32  can help transfer load between the sections  10 ,  16  when they are rotated together using shafts  23 ,  24 .  
         [0059]    Two meshing gears  13 ,  32  can be mounted on the housing sections  10  and  16  respectively. The clearances between the gear teeth is less than the clearance between piston  11  and receiver  13 . Therefore, the transfer of torque from part  10  to part  16  (i.e. driver to driven) is carried by the gears  13 ,  32  and not the seal rings  12 . If there is no gear  13 ,  32  provided, part  10  transfers torque to part  16  and vice versa using seal  12  pushing on socket  19   
         [0060]    [0060]FIG. 4A is a schematic plan view showing one of the housing sections, with a single circle of pistons  11  in FIG. 4A and a double circle of pistons  11  in  4 B;  
         [0061]    Each rotor section or housing section  10 ,  16  can have angle cuts  70  along the face, a dished cut out or concave surface  21  mating face for the spherical ball bearing  20 . Conversely, depicted is the receiver rotor  16  including receivers  31 , outlet chamber ports  63 , discharge valve assemblies  50  depicted but not limited to ball/spring type and rotor outlet discharge passageway  64 .  
         [0062]    Fluid enters suction port  61  either boosted by part  15  or not, at a pressure assuming FIG. 3B minimum position as the piston  11  pulls away from the receiver  30  a lower pressure is experienced in chamber  60 . The pressure differential between the suction passage  61  and compression chamber  60  opens valve  40  to allow fluid flow into chamber  60 . During this operation, discharge valve  50  remains closed due to higher discharge line pressure in discharge chamber  64  compared to compression chamber  60 . At FIG. 4A, maximum position, both valves  40 ,  50  are closed. During the compression stroke going from position  3 A (maximum) to position  3 B (minimum) pressure builds up in chamber  60 . This higher pressure closes valve  40  as the pressure in the chamber  60  is higher than the suction line pressure  61 .  
         [0063]    When the pressure in chamber  60  becomes greater than the discharge pressure in port  64  plus the valve seating pressure, the discharge valve  50  opens and releases chamber  60  pressure into port  64  and into the discharge line. The drawings show a ball/spring combination which valve seating pressure is a function of ball area in contact with the stream and a spring constant.  
         [0064]    An alternative valve design is shown in FIGS.  12 - 17 , designated as valve  45 . Valve  45  replaces the spring  42  or  52  with a shim disk  47  for which the spring constant is replaced by the beam flex of the shim disk  47 . This shim disk  46  shows a smaller profile radially to the rotor  10  and  16  rotation reducing the centrifugal force effects on the mechanical operation of the valve allowing for higher speed operation. Valve  40  can be comprised of a ball  41 , spring  42  and sleeve  43  having valve seat  44 . Similarly, valve  50  can be comprised of ball  51 , spring  52  and sleeve  53  having seat  54 . For the alternate valve  45 , a housing (e.g. steel)  46  has multiple radially and peripherally placed flow openings  48  covered with shim  47  (e.g. rubber or polymeric or metal). A central fastener  49  holds shim  47  to body  46 . Flow through body  46  and its openings  48  causes shim  47  to bend and enable valve  45  to open.  
         [0065]    Another pressure booster  54  is seen in FIGS.  16 - 17  that uses housing  55  that is U-shaped. A shim  56  (e.g. metal) covers flow opening  57 . Fasteners  58  secure shim  56  to housing  55 . Flow through housing  55  and its opening  57  causes shim  56  to bend and enables pressure booster  54  to open.  
         [0066]    The face of the housing section  10  is cut at an angle  71  and includes dished cut out or concave surface  22  mating face for acceptance of orbiting ball or sphere  20 . The ball  20  is not limited to being a separate item but also may be an integral part of either the piston rotor  10  or the receiver rotor  16 ,  30 .  
         [0067]    [0067]FIG. 3A is a diagram of maximum opening of a piston  11 , and maximum volume, minimum pressure of the compression chambers  60  at the zero degree of rotation point between the piston rotor  10  and the receiver rotor  16  in relation to valve inlet  62  of piton  11  and outlet  64 . FIG. 3B is a diagram that shows minimum opening and minimum volume, maximum pressure of the compression chambers  60  at the 180 degree of rotation point between the piston rotor  10  and the receiver rotor  16  in relation to valve inlet  62  and outlet  64 .  
         [0068]    [0068]FIG. 4A illustrates an exemplary layout of piston/receiver pairs  11 / 31  on the piston rotor  10  and receiver rotor  30  mating circle  82  while centering on the orbiting rider ball  20 .  
         [0069]    [0069]FIG. 4B illustrates an exemplary layout of piston/receiver pairs  11 / 31  on the piston rotor  10  and receiver rotor  30  dual mating circles  82 / 83  while centering on the orbiting rider ball  20 .  
         [0070]    [0070]FIG. 5 illustrates the engagement geometry of the piston rotor  10 , the receiver rotor  30  on the orbiting rider ball  20  with integral porting and valving described in FIG. 2. Linear offsets from the center of rotation (center of orbiting rider ball  20 )  80 / 81  are depicted along with the piston rotor  10  rotation angular offset  72 . Also, circumferential piston/receiver circular path  84  is shown.  
         [0071]    [0071]FIG. 6 illustrates machine  5  including all aspects of subsequent figures combined with rotational shafts (clockwise or counter clockwise)  90 / 92  and a system of bearings to contain the rotation both in radial and axial directions. These bearings can be preferably installed to a fixed case or housing. Also depicted are a system of seals  14 / 33  to separate suction and discharge and provide an internal chamber that can be liquid filled for lubricating (if necessary) or cooling (predicted). In addition, a torque transmitting gearing system  13 / 32  is provided to allow driving through the machine  5  without relying on the piston/receiver  11 / 31  and seal  12  surfaces to provide that function. In certain designs the engaging piston/receiver/seal  11 / 31 / 12  surfaces may be able to transfer the torque. Therefore, the apparatus of the present invention does not exclude piston/receiver/seal  11 / 31 / 12  as an option for torque transmission.  
         [0072]    [0072]FIG. 7 is an illustrative example of a single stage unit  6  incorporating the machine  5  in a fixed split housing  101 / 102  providing a fluid inlet connection  107 , a suction collection chamber  105  open to all piston rotor inlet chambers  61 . A fluid outlet discharge chamber  104  is provided, open to all receiver discharge ports  64  along with a housing outlet connection  106 . Additionally, an end cap  103  is depicted to provide and additional bearing to confine the driven rotor that may or may not be necessary in all configurations.  
         [0073]    [0073]FIG. 8 is an illustrative example of a multi-stage unit  17  which in effect is an alignment of single stage units  6  provided with an end cap. Although the multi-stage unit is shown as a having an external transfer of fluid for cooling and side streaming, all stages may be incorporated in a single housing. Fluid would pass from stage to stage internally and connection inter-stage for cooling and side streaming would be provided as an integral part of the single case.  
         [0074]    [0074]FIG. 9 is an illustrative example of a free rotor engine  130  is depicted incorporating the machine  5  and allowing the receiver rotor to rotate on a case mounted bearing assembly  94  mounted as part of the split housing  132 . Fuel would be introduced to the inlet chamber  140  and open to each of the piston rotor  10  inlet suction passageways  61 . Around the 180-degree rotation position a sparking device  150 , connected to each combustion chamber  60 , would institute a spark in a combustion chamber. The release of combustion by-products would be via each piston/receiver pair  11 / 31  discharge valve assembly  50  through the outlet (exhaust) port  141 . The housing depicted is not the limit of this document for the housing of the machine  5 .  
         [0075]    [0075]FIG. 10 is an illustrative example of a dual shaft rotating engine  135  that incorporates the machine  5  modified to include a sparking device for each receiver chamber  60 . As rotating will not provide the ability for permanent connection of the sparking devices  150  a points type system  152  being wired through an access connection  151  is illustrated. The housing depicted is not the limit of this document for the housing of the machine  5 .  
         [0076]    [0076]FIG. 11 is an illustrative example of a suction pressure booster  15  and a discharge torque-enhancing device  34  added to the components described in FIG. 2. These two items  15 / 34  serve as examples for suction pressure increase and discharge torque accumulation but do not limit the machine  5  to just these two examples.  
         [0077]    The machine  5  of the present invention are positive displacement devices used to compress fluids (gas or liquid) or work as an engine by engaging piston  11  and receiver  31  chambers  60  that exist on two opposing rotors  10  and  30 . The compression occurs due to the inversion angle of the piston rotor  10  face in reference to the receiver rotor  30  face  20  created by the engagement angle  72  or angular offset of the opposing shafts  90 / 92  (see FIG. 6). It is irrelevant which shaft  90 / 92  receives the displacement angle  72 . Side to side tilting of the piston  11  and receiver  31  sealing surfaces in relation to each other is handled by coordinating two sets of dimensions. First the angle cuts  70 / 71  in the piston  10  and receiver  30  rotors, then by the offsets  80 / 81  (see FIG. 5) from the center of the  25  orbiting riding ball  20 . When the machine  5  is assembled, the two opposing rotors  10 / 30  are aligned on the riding ball  20  on opposing rotor cutouts  21 / 22  (FIGS. 2 and 5).  
         [0078]    Compression occurs on a circular path  84  (FIG. 5) radiated out from the center of rotation along the circumference of the circle  84 . Each chamber  60  is isolated from the environment via the use of sealing rings  12  that seal the surfaces between the pistons  11   30  and receivers  31 . The introduction of fluid (gas or liquid) is handled by a system of springs and balls that rotate with the rotor. For use as a pump or compressor  6 , each piston/receiver  11 / 31  combination has an adjoining suction spring/ball assembly  40  located in the piston rotor  10 . Conversely, for the release of fluid (gas or liquid) each piston/receiver pair  11 / 31  has an adjoining discharge spring/ball assembly  50  located in the receiver rotor  30 . The piston/receiver pairs  11 / 30  are located along a circular path radiated out  82  or  83  (see FIG. 4B) as viewed from the center of the rotating shafts looking down the shaft toward the rotors  10 / 30 . Each device may have either one  82  or multiple  83  compression circles on the same piston/receiver rotor pairs  10 / 30 . For multi-stage operations  17 , one device may be aligned to work in parallel or series service with adjoining devices of the same make-up.  
         [0079]    Fluids (gas or liquid) are introduced to the single stage unit  6  (FIG. 7) through suction inlet  107  into the suction passage  105 . The fluid then enters rotor suction chamber  61 . Differential pressure in the compression chamber  60  and the rotor suction chamber  61  causes suction spring/ball assembly  40  to open allowing fluid into compression chamber  60  via suction rotor chamber inlet  62 . As the rotors rotate they cause the volume in the compression chamber  60  to decrease, thereby increasing the pressure. When the pressure in the compression chamber reaches a point higher than that of the discharge passage  104 , this differential pressure opens the spring/ball assembly  50  in the receiver rotor  30 . Fluid will then flow through rotor the compression chamber outlet  63 , over the spring/ball assembly  50  out of the rotor discharge passage  64 . This compressed fluid collects in the case discharge chamber  104  and exits the machine  6  through the unit discharge outlet  106 .  
         [0080]    For multi-stage parallel or series service the flow path described above through the machine  5  from the suction rotor  10  inlet port  61  to the discharge rotor  30  outlet port  64  will remain consistent in each fluid compression path description to follow. For series stream compression, fluids (gas or liquid) are introduced to the multi-stage unit  17  through suction inlet  112  of the single stage unit  6  and through the machine  5  as described above. The fluid is collected in the case discharge chamber  111  and exits the single stage unit  6 . This fluid may be taken off for inter-stage cooling and the stream may be increased or decreased by side stream gas ready for entry into the next single stage unit  6  to the second stage inlet chamber  114 . The fluid is compressed though the second in-line machine  5  and passes through discharge outlet chamber  113  where again it may be cooled or effect a side stream as noted above. The fluid enters the next stage unit  6  through suction inlet chamber  116 . The fluid is again compressed to a higher pressure through the machine  5  located in this single stage unit  6  and delivered to discharge passage  115  ready for delivery to another single stage compression unit  6  or for final delivery for service. For purely parallel service connection, two or more single stage units  6  may be connected in parallel with common suction pressure delivered to the inlet suction chambers  112 / 114 / 116 . The fluid is compressed through each of the units and discharged through each single stage unit  6 , discharge outlet chamber  111 / 113 / 115 . For a mix of parallel and series service fluid may enter the first two single stage units  6  though the suction inlet chambers  112 / 114  and discharge through their discharge outlet chambers  111 / 113 . This stream may be cooled or a side stream may be effected readying the fluid for deliver to the suction inlet chamber of the next single stage unit  6  at suction inlet port  116 . The fluid is then compressed for final delivery exiting from the single stage unit  6  through discharge outlet chamber  115 . These are but a few examples of how the multi-stage unit  17  may be setup. These examples are not meant to restrict the machine  5  to any of the fore mentioned examples. Any combinations of connection either internal or external are acceptable. Any size rotor pairs  10 / 30  is acceptable and shall be sized for the flow characteristics of each compression stream. Any combination of compression rings  82 / 83 / 84  is acceptable and covered by this document. Any shape and geometry of rotor pairs  10 / 30  and piston/receivers  11 / 31  are acceptable as long as they maintain the sealing of the compression chamber  60 . Any configuration of inlet and outlet rotor passageways  61 / 62 / 63 / 64  and inlet and outlet valve assemblies  40 / 50  is acceptable.  
         [0081]    This machine  5 , being a positive displacement device, will inherently have the ability to institute flow control via speed control with low and high-speed applications included. In addition, setup flow control can be instituted via insertion or removal of suction spring/ball value assemblies  40 / 50  to activate or deactivate individual piston/receiver pairs  11 / 31 , and is included. Any geometry for mounting the machine  5  into a case  6  and sizes of inlet and outlet chambers, passageways and connections are included.  
         [0082]    For use as an engine  130  or  135 , each rotor may rotate as dual drive  135  or single shaft drive  130 . In the case dual drive  135 , each piston cylinder pair  11 / 31  may have an adjoining suction (intake)  40  and discharge (exhaust)  50  spring/ball combination for the introduction of fuel and the release of combustion gases. In addition, each piston/receiver  11 / 31  pair will also have an adjoining device to spark the combustion  150  be it spark plug, element, etc., and a system to deliver the spark  151  transferred external to the rotors  10 / 30 . In the case of single shaft drive  130  (case mounted bearing  94 ) this may be either the piston  10  or the receiver  30  rotor. The transfer of fuel to each chamber may be accomplished via a spring/ball combination  40  adjoined to each of the rotating piston/receiver  11 / 31  pairs. Each combustion chamber  60  will have an accompanying spring/ball assembly  50  in the case-rotating rotor to handle the release of combustion gases (exhaust)  141 . Sparking of each combustion chamber may be handled by the sparking device  150  attached to each combustion chamber  60  and fed through the spark generating case port  151 .  
         [0083]    Torque requirements for use as an engine  130 / 135  may be effected and varied by the sequencing of spark delivered to the sparking device  150 . For example, at low torque requirement periods a combustion-instituting spark may only be delivered to a set number of alternating piston/receiver  11 / 31  pairs. As the torque requirements increase more and more chambers  60  will be ignited. As stated above for the compression unit  6 , the engine is not limited to the few configurations noted for engines  130 / 135 , but includes all mounting, sizes and geometry required to use the machine  5  for engine, torque development applications. Variable aspects may include, but not be limited to, bearings  91 / 93 / 94 , shafts  90 / 92 , inlet and outlet valves  40 / 50 , piston receiver pairs  11 / 31 , rotor pairs  10 / 30 , torque transfer gears  13 / 32 , seals  12 , sparking devices  150 / 151 . They also include case designs  131 / 132 / 133  or any other factor that is required to place the machine  5  in service as an engine, pump or compressor.  
         [0084]    Additions to the device may include the attachment of a turbine type device  15  to the piston rotor  10  to institute an increase in pressure delivered to the suction spring/ball  40  inlet ports  61 . In a similar mounting arrangement, a torque converting or torque-enhancing device  34  may be mounted to the discharge or receiver rotor  30 . In driving, or force transmission through the rotors  10 / 30  from shaft  90  to shaft  92 , a gear system  13 / 32  may be incorporated as part of the rotors  10 / 30  to transfer the torque from shaft  90  to shaft  92  without transferring the force to the piston/receiver assemblies  11 / 30  nor to the seals  12  therein.  
         [0085]    One of ordinary skill in this art will be able to determine appropriate materials for the various parts of the present invention.  
         [0086]    All measurements disclosed herein are at standard temperature and pressure, at sea level on Earth, unless indicated otherwise. All materials used or intended to be used in a human being are biocompatible, unless indicated otherwise.  
                                                 PARTS LIST       PARTS NO.   DESCRIPTION                                5   pump apparatus       6   block       10   upper housing section       11   piston       12   seal       13   gearing system       14   seal       15   suction pressure booster       16   lower housing section       17   multi-stage unit       18   projection       19   socket       20   spherical bearing       21   concave surface       22   concave surface       23   shaft       24   shaft       25   surface       26   surface       27   surface       28   surface       30   outer surface       31   receivers       32   gearing system       33   seal       34   discharge torque device       40   suction valve assembly       41   ball       42   spring       43   sleeve       44   seat       45   valve       46   housing       47   shim       48   opening       49   fastener       50   discharge valve assembly       51   ball       52   spring       53   sleeve       54   pressure booster       55   housing       56   shim       57   opening       58   fastener       60   compression chamber       61   inlet port       62   inlet       63   outlet chamber port       64   discharge passageway       70   angle       71   angle       72   angle       80   offset       81   offset       82   mating circle       84   mating circle       84   piston receiver circular path       101   block section       102   block section       103   block section       104   outlet chamber       105   suction chamber       106   housing outlet connection       107   fluid inlet connection       130   free rotor engine       132   split housing       135   dual shaft rotating engine       140   inlet chamber       141   exhaust port       150   sparking device       151   access connection       152   points type system                  
 
         [0087]    The foregoing embodiments are presented by way of example only; the scope of the present invention is to be limited only by the following claims.