Patent Publication Number: US-7214045-B2

Title: Spherical fluid machine with flow control mechanism

Description:
“CROSS-REFERENCE TO RELATED APPLICATION” 
   This application is a continuation of U.S. Ser. No. 09/376,032, filed Aug. 17, 1999, U.S. Pat. No. 6,241,493, SPHERICAL FLUID MACHINE WITH CONTROL MECHANISM by William Frank Turner. 

   TECHNICAL FIELD 
   The invention relates generally to fluid flow machines or devices such as motors, pumps or compressors and, more particularly, to the construction and control of such machines utilizing rotary mounted vanes. 
   BACKGROUND 
   Rotary motors, pumps and compressors have been known for many years. Generally these devices consist of a housing or casing within which one or more vanes rotate. This is in contrast to those devices which utilize a reciprocating, linearly moving piston. In the case of rotary pumps or compressors, the vanes are rotated by a shaft to pressurize or cause the fluid to flow through the device. In the case of a rotary motor, the opposite occurs. Fluid is introduced into the device under pressure to displace the vanes, which in turn rotates and powers a drive shaft to which the vanes are coupled. 
   For rotary fluid pumps, the flow of fluid is typically controlled by the rate at which the rotary vanes are rotated. By increasing the speed, more fluid is pumped through the device, while decreasing the speed decreases the amount of fluid pumped. Further, reversing the flow through the device, if possible at all, requires the vanes to be rotated in the opposite direction or requires that the inlet and outlet ports be reconfigured or reversed. 
   U.S. Pat. No. 5,199,864 discloses a rotary fluid pump that employs vanes rotating within a spherical housing. These devices are highly efficient, and are capable of displacing large quantities of fluid. The flow capacity of these devices, however, is also usually controlled by varying the speed at which the vanes are rotated within the housing. Because this typically requires varying the speed of the motor that rotates the rotary shaft, the flow rate is often difficult to control with any degree of precision. Further, the direction of flow cannot be reversed without modifying the device or reversing the direction of rotation of the drive shaft that drives the vanes. 
   Other mechanical limitations apply to these prior art devices, such as inadequate removal of heat from the devices, the construction of the vanes to provide improved performance, and methods of securing together the components of the spherical race assembly about which the vanes rotate. 
   What is therefore needed is a fluid machine or device, such as a rotary motor, pump or compressor, in which the fluid flow through the device can be controlled in an effective, simple and precise manner, and which allows the rotary or drive shaft of the device to be rotated at a generally constant rate or direction of rotation while the direction or rate of fluid flow is varied, and which also addresses the mechanical limitations of the prior art devices. 
   SUMMARY 
   These and other needs are addressed by the present invention, which provides a method and apparatus for controlling the flow of fluid through a rotary pump, compressor, motor, and similar devices. In the present invention, at least one primary vane rotates within a housing, causing at least one secondary vane to pivotally oscillate between alternating open and closed positions, respectively further from and closer to the primary vane. Fluid is displaced through a port in the housing as the secondary vane approaches the closed position, while fluid enters the housing as the secondary vane approaches the open position. The quantity or direction of flow of fluid through the port is adjusted by varying the point during rotation of the primary vane or timing at which the closed and open positions are reached, relative to the port. 
   In another aspect of the invention a method and apparatus for controlling or regulating fluid flow through a fluid machine, such as a motor, fluid pump or compressor, is provided. The device is provided with a housing having at least two fluid ports in communication with the interior of the housing. At least one of the ports is in communication with a fluid source. A primary vane is disposed within the interior of the housing. A rotary shaft having a primary axis of rotation is coupled to and rotates the primary vane about the primary axis. A secondary vane is mounted for pivotal movement between open and closed positions with respect to the primary vane, about a pivotal axis passing through the primary vane, as the primary vane rotates. The primary and secondary vanes divide the interior of the housing into chambers, with the volume of the chambers varying as the secondary vane is moved between the open and closed positions. Pivoting of the secondary vane between open and closed positions is accomplished by a guide that directs diametrically opposed points on the secondary vane to rotate about a secondary vane rotational axis intersecting, but angularly offset from, the primary pivotal axis of the secondary vane. The secondary vane pivotal and rotational axes define a control plane. 
   By adjusting the secondary vane guide and therefore also adjusting the control plane, both the rate of flow and direction of flow of fluid through the ports of the housing can be altered to thereby regulate fluid flow through the machine. 
   In another aspect of the invention, the housing includes cooling fins for enhancing heat transfer with the surrounding environment. 
   In yet another aspect of the invention, at least a substantial portion of one or more of the vanes is hollow to reduce material cost, weight and enhance performance of the device. 
   In still another aspect of the invention, the actuator includes a timing plate or lever that is adjusted relative to the position of one or more ports to control the flow rate or direction of fluid. 
   Other aspects and features of the present invention will become apparent to those ordinarily skilled in the art upon review of the following description of specific embodiments of the invention in conjunction with the accompanying figures. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     For a more complete understanding of the present invention, and the advantages thereof, reference is now made to the following descriptions taken in conjunction with the accompanying drawings, in which: 
       FIG. 1  is front perspective view of a fluid pump, shown with the upper half of a housing of the pump exploded away to reveal internal components of the device, and constructed in accordance with the invention; 
       FIG. 2  is a perspective view of the lower half of the housing of the pump of  FIG. 1  with the internal components removed; 
       FIG. 3  is a perspective view of a rotary shaft and primary vane assembly of the pump of  FIG. 1 , shown with the primary vane assembly exploded into two halves; 
       FIG. 4  is a perspective view of a secondary vane assembly of the pump of  FIG. 1 , shown with the secondary vane assembly exploded into two halves; 
       FIG. 5  is an exploded perspective view of a fixed shaft assembly of the pump of  FIG. 1 , constructed in accordance with the invention; 
       FIG. 6  is a perspective view of a flow capacity control lever for rotating the fixed shaft of  FIG. 5 , and constructed in accordance with the invention; 
       FIG. 7  is a cross-sectional view of the lever of  FIG. 6  taken along the lines  7 — 7 ; 
       FIG. 8A  is a detailed cross-sectional view of the pump of  FIG. 1 ; 
       FIG. 8B  is a cross-sectional view of the pump of  FIG. 1 , showing various rotational axes of the device; 
       FIG. 8C  is a schematical diagram of the pump housing showing the rotation of a control plane with respect to the pump housing; 
       FIG. 9A  is a perspective view of the pump of  FIG. 1  shown with the upper half of the housing removed and the control lever in a 0° position; 
       FIG. 9B  is a front elevational view of the pump of  FIG. 9A ; 
       FIG. 9C  is a top plan view of the pump of  FIG. 9A ; 
       FIG. 9D  is a side elevational view of the pump of  FIG. 9A ; 
       FIGS. 10A–10E  are sequenced perspective views of the pump of  FIGS. 9A–9D  with the control lever in the 0° position, as the rotary shaft of the pump is rotated 180° during the pump&#39;s operation; 
       FIG. 11A  is a perspective view of the pump of  FIG. 1  shown with the upper half of the housing removed and the control lever in a 180° position; 
       FIG. 11B  is a front elevational view of the pump of  FIG. 11A ; 
       FIG. 11C  is a top plan view of the pump of  FIG. 11A ; 
       FIG. 11D  is a side elevational view of the pump of  FIG. 11A ; 
       FIGS. 12A–12E  are sequenced perspective views of the pump of  FIGS. 11A–11D , with the control lever in a 180° position, as the rotary shaft of the pump is rotated 180° during the pump&#39;s operation; 
       FIG. 13A  is a perspective view of the pump of  FIG. 1  shown with the upper half of the housing removed and the control lever in a 90° or neutral position; 
       FIG. 13B  is a front elevational view of the pump of  FIG. 13A ; 
       FIG. 13C  is a top plan view of the pump of  FIG. 13A ; 
       FIG. 13D  is a side elevational view of the pump of  FIG. 13A ; 
       FIGS. 14A–14E  are sequenced perspective views of the pump of  FIGS. 13A–13D , with the control lever in the 90° or neutral position, as the rotary shaft of the pump is rotated 180° during the pump&#39;s operation; 
       FIG. 15  is a schematic representation of a fluid system utilizing the pump of the invention with fluid flow in a given direction; 
       FIG. 16  is a schematic representation of a fluid system utilizing the pump of the invention with fluid flow in a reverse direction from that of  FIG. 15  by rotation of the control lever; 
       FIG. 17  is an elevational view of a flow capacity control plate for use with the pump of  FIG. 1  for mounting the fixed shaft assembly in different fixed positions, and constructed in accordance with the invention; 
       FIG. 18  is a cross-sectional side view of the control plate of  FIG. 17  and the fixed shaft assembly of the pump of  FIG. 1 , with the control plate exploded away from the fixed shaft assembly to illustrate how the control plate is mounted; 
       FIG. 19  is a top plan view of another flow capacity control plate for use with the pump of  FIG. 1 , shown with dowel holes of the control plate in a different orientation, and constructed in accordance with the invention; 
       FIG. 20  is an elevational view of the control plate of  FIG. 17 , shown mounted to the housing of the pump of  FIG. 1 ; 
       FIG. 21  is an elevational view of the control plate of  FIG. 19 , shown mounted to the housing of the pump of  FIG. 1 ; 
       FIG. 22  is a perspective view of another embodiment of a secondary vane half for a secondary vane assembly, constructed in accordance with the invention; and 
       FIG. 23  is a perspective view of a primary vane half of a primary vane assembly for use in cooperation with the secondary vane half of  FIG. 22 , and constructed in accordance with the invention. 
       FIG. 23A  is an elevational view of the primary vane half along line  23 A— 23 A of  FIG. 23 . 
   

   DETAILED DESCRIPTION 
   Referring to  FIG. 1  of the drawings, the reference numeral  10  generally designates a fluid pump or compressor embodying features of the present invention. The pump  10  is generally similar in construction to the device described in U.S. Pat. No. 5,199,864, which is herein incorporated by reference. It should be noted that although the device  10  has been more specifically described with respect to its function and use as a fluid pump or compressor, it could also function as motor, as would be readily appreciated by those skilled in the art. 
   The pump  10  includes a metal housing  12 , such as steel or aluminum, which is formed into two halves  14 ,  16 . Although the housing  12  and other components of the pump  10  are generally described and shown herein as being constructed of metal, many other materials, such as plastic or polymeric materials, could be used as well, depending upon the application of the device  10  and would be appreciated by those skilled in the art. Accordingly, the invention should not be limited to the particular types of materials that are used in its construction. 
   Each half  14 ,  16  of the housing  12  is generally configured the same as the other and has a hemispherical interior cavity  18  ( FIG. 2 ), which forms a spherical interior of the housing  12  when the two halves  14 ,  16  are joined together. Each housing half interior piece  14 ,  16  is provided with a circular flange  20  having a flat facing surface  21  which extends around the perimeter of the cavity  18  and which abuts against and engages the corresponding flange  20  of the other housing piece  14 ,  16 . The flange face  21  lies in a plane that generally divides the spherical housing interior  18  into two equal hemispherical halves when the housing halves  14 ,  16  are joined together. 
   A fluid tight seal is formed between the housing halves  14 ,  16  when the halves  14 ,  16  are joined together. A gasket or seal (not shown) may be interposed between the flange faces  21  to accomplish this. The flange  20  may be provided with holes  22  to accommodate bolts or fasteners (not shown) for joining the housing halves  14 ,  16  together. Alternatively, the halves  14 ,  16  may be welded, glued or otherwise joined together in a conventional manner as would be readily known to those skilled in the art. Preferably, however, the housing halves  14 ,  16  are secured together in a nonpermanent manner to allow access to the housing interior if necessary. 
   Formed in each housing piece  14 ,  16  are rear and front fluid ports  24 ,  26  that communicate between the exterior of the housing and the housing interior  18 . In the preferred embodiment, the fluid ports  24 ,  26  are circumferentially spaced apart approximately 90° from the next adjacent port, with the approximate center of each fluid port being contained in a plane oriented perpendicular to the flange faces  21  and that bisects the interior of the housing  12  when the housing halves  14 ,  16  are joined together. Preferably, the ports  24 ,  26  are positioned about 45° from the flange faces  21  on each housing half  14 ,  16 . 
   Formed at the rearward end of each housing half  14 ,  16  adjacent to the rearward port  24  is a recessed area  28  formed in the circular flange  20  for receiving a main input shaft  32  ( FIG. 1 ), which extends for a distance into the housing interior  18 . The primary axis or axis of rotation  33  of the input shaft  32  lies generally in the same plane as the flange faces  21 . An input shaft collar  34  extends outwardly from the housing halves  14 ,  16  and is provided with a similarly flanged surface  36  for facilitating joining the housing halves together. 
   Located at the forward end of the housing  12  opposite the collar  34  in each housing half  14 ,  16  is a recessed area  38  formed in the circular flange  20  to form a shaftway for receiving a fixed shaft  40  ( FIG. 1 ). A neck piece  42  extends outwardly from the circular flange  20  and is also provided with a flanged surface  44  to facilitate joining of the housing halves together. 
   In the particular embodiment shown, the exterior of the housing  12  is provided with a plurality of parallel spaced apart fins or ribs  48  which provide structural rigidity to the housing while reducing the weight of the device. The fins or ribs  48  also provide an increased surface area of the housing to facilitate heat transfer. 
   The housing  12  houses primary and secondary vane assemblies  52 ,  54 , respectively. Referring to  FIG. 3 , the primary vane assembly, designated generally at  52 , is formed into two metal halves  56 ,  58 . The primary vane halves  56 ,  58  are generally configured the same, each having a generally flat inner surface  59  that abuts against the inner surface of the other half. The primary vane halves  56 ,  58  each have opposite vane members  62 ,  64 , that are joined together at opposite ends by integral hinge portions  66 ,  68  to define a central circular opening  69 . When the primary vane halves  56 ,  58  are joined together, the vane members  62 ,  64  form single opposing vanes  50 . Bolt holes  65  for receiving sunken bolts or screws (not shown) are provided for this purpose. The vane halves  56 ,  58  may be joined together, however, by many other fastening means, and may be glued, welded or otherwise secured together in any conventional manner known by those skilled in the art. Alignment dowels  67  received within dowel holes formed in the faces  59  may also be provided to ensure that the vane halves  56 ,  58  are properly mated and fastened together. 
   The vane members  62  are each provided with an input shaft recess  60  formed in the flat surface  59  for receiving and coupling to the input shaft  32  when the vane halves  56 ,  58  are joined together. The primary vane assembly  52  is rigidly coupled to the input shaft  32  so that rotation of the input shaft  32  is imparted to the primary vane assembly  52  to rotate the opposing vanes  50  within the housing interior  18 . 
   Similarly, the vane members  64  are provided with a fixed shaft recess  70  formed in the flat surface  59  for receiving the fixed shaft  40 . The fixed shaft recess  70  is configured to allow the primary vane assembly  52  to freely rotate about the fixed shaft  40 . The outer ends of the vane members  62 ,  64  have a generally convex spherical lune surface configuration corresponding to the spherical interior  18  of the housing  12 . 
   The hinge portions  66 ,  68  are each provided with a stub shaft recess  72 . A stub shaft  74  is shown provided with the hinge portion  66  of the vane half  56 . This stub shaft  74  may be integrally formed with one of the vane halves  56 ,  58  or may be a separate member that is fixed in place. As is shown, the stub shaft  74  projects a distance outward beyond the hinge portion  66 . The hinge portions  66 ,  68  are each squared or flat along the outer side edges. 
   Referring to  FIG. 4 , the secondary vane assembly  54  is also shown being formed in two halves  76 ,  78 , each half  76 ,  78  being generally similar in construction. The secondary vane halves  76 ,  78  are formed of metal and are generally configured the same, each having an inner surface  80 , which is generally flat and which abuts against the inner surface of the other vane half. The secondary vane halves  76 ,  78  each have opposite vane members  82 ,  84 , that are joined together at opposite ends by integral hinge portions  86 ,  88  to define a central circular opening  90 . When the secondary vane halves  76 ,  78  are joined together, the vane members  82 ,  84  form single opposing vanes  98 . The vane halves  76 ,  78  may be joined together by bolts, screws or other fasteners, or may be glued or otherwise secured together in any conventional manner well known by those skilled in the art. Bolt holes  97  are provided for this purpose. Additionally, dowel holes  99  for receiving alignment dowels, such as the alignment dowels  67  of  FIG. 3 , may also be provided. 
   The vane members  82 ,  84  are each provided with pivot post recesses  92  formed in the inner surfaces  80  of each vane half  76 ,  78 . The outermost ends of the vane members  82 ,  84  also have a generally convex spherical lune surface configuration corresponding to the spherical interior  18  of the housing  12 . 
   The hinge portions  86 ,  88  are each provided with a stub shaft recess  94 . A second stub shaft  96  is shown provided with the hinge portion  88  of the vane half  78 . This stub shaft  96  may be integrally formed with one of the vane halves  76 ,  78  or may be a separate member that is fixed in place. As is shown, the stub shaft  96  projects a distance inward from the hinge portion  88 . Both the hinge portions  86 ,  88  are squared or flat along the inner side edge to correspond to the flat exterior side edges of the hinge portions  66 ,  68  of the primary vane halves  56 ,  58 . The exterior of the hinge portions  86 ,  88  are in the form of a convex spherical segment or sector that is contoured smoothly with the curved surface of the outer ends of the vane members  82 ,  84 , and corresponds in shape to the spherical interior  18  of the housing  12 . 
   When the primary and secondary vanes  52 ,  54  are coupled together ( FIG. 1 ) and mounted to the main input shaft  32 , the stub shafts  74 ,  96  are generally concentric. The stub shaft  74  of the primary vane assembly  52  is received within the recesses  94  of the hinge portion  86  of the secondary vane assembly  54  to allow relative rotation of the secondary vane assembly  54  about the stub shaft  74 . Likewise, the stub shaft  96  of the secondary vane assembly  54  is received within the recesses  72  of the hinge portion  68  of the primary vane assembly  52  and allows relative rotation of the primary vane assembly  52  about the stub shaft  96 . In this way, the primary and secondary vanes assemblies  52 ,  54  remain interlocked together while the secondary vane assembly  54  is allowed to pivot relative to the primary vane assembly  52  about an axis that is perpendicular to the primary axis  33  of the input shaft  32 . 
     FIG. 5  shows an exploded view of a fixed shaft or race assembly  100 . The fixed shaft assembly  100  is comprised of the cylindrical shaft  40 , which is received in the recesses  38  of the housing halves  14 ,  16 , as discussed previously. The cylindrical shaft  40  is coaxial with the primary axis  33  of the input shaft  32  when mounted to the housing  12 . At the inner end of the shaft  40  is a spherical shaft portion  102  in the form of a sphere section. Projecting from the inner side of the spherical shaft portion  102  is a cylindrical carrier ring shaft  104 . The longitudinal axis of the carrier ring shaft  104  is oriented at an oblique angle with respect to the axis of shaft  40 . This angle may vary, but is preferably between about 30° to 60°, with 45° being the preferred angle. A boss  106  projects from the end of the shaft  104  to facilitate mounting of an end cap  108 , which is in the form of a spherical section. The end cap  108  is provided with a recess  110  for receiving the boss  106  of shaft  104 . In the embodiment shown, a pair of threaded fasteners  112 , such as screws or bolts, which are received within eccentrically disposed threaded bolt holes  114  formed in the boss  106 , are used to secure and fix the end cap  108  to the shaft  104 . Two or more fasteners may be used. Because the fasteners are eccentrically located with respect to the axis of the shaft  40 , they prevent relative rotation of the end cap  108  with respect to the shaft  40 . 
   The end cap  108  is used to secure a central carrier ring  116 , which is rotatably mounted on the carrier ring shaft  104 . The carrier ring  116  is configured with an outer surface in the form of a spherical segment so that when the carrier ring  116  is mounted on the shaft  104  and the end cap  108  is secured in place, the combination of the spherical portion  102 , carrier ring  116  and end cap  108  generally form a complete sphere that is joined to the end of the shaft  40 . The diameter of this sphere generally corresponds to the diameter of the central openings  69 ,  90  of the primary and secondary vane assemblies  52 ,  54 , respectively, to allow the vane assemblies  52 ,  54  to rotate about this spherical portion of the fixed shaft assembly  100 , while being in close engagement thereto. The carrier ring  116  is centered between the spherical portion  102  and the end cap  108 . 
   The carrier ring  116  is provided with oppositely projecting pivot posts  118  which project radially outward from the outer surface of the carrier ring  116 . The posts  118  are concentrically oriented along an axis that is perpendicular to the axis of rotation of the carrier ring  116 . The posts  118  are received within the pivot post recesses  92  of the secondary vane halves  76 ,  78  when the vane assembly  50  is mounted over the spherical portion of the fixed shaft assembly  100  formed by the spherical portion  102 , carrier ring  104  and end cap  108 . 
   Coupled to the shaft  40  opposite the spherical portion  102  is a flow capacity control lever  120  for manually rotating the shaft  40  and spherical portion  102 . The control lever  120 , shown in more detail in  FIGS. 6 and 7 , has a generally circular-shaped body portion  122 . A lever arm  124  extends from the body portion  122 . Formed generally in the center of the body portion  122  is a bolt hole  126  for receiving a bolt  128  for fastening the lever  120  to the shaft  40  by means of a central, threaded bolt hole  130  formed in the outer end of the shaft  40 . Spaced around the bolt hole  126  are dowel holes  132  which correspond to dowel holes  134  formed in the shaft. Dowels  136  are received within the dowel holes  132 ,  134  to prevent relative rotation of the control lever  120  with respect to the shaft  40 . Although one particular method of coupling the lever  120  to the shaft  40  is shown, it should be apparent to those skilled in the art that other means may be used as well. 
   An arcuate slot  138  which extends in an arc of about 180° is formed in the body portion  122  of the lever  120  for receiving a set screw or bolt  140 . The arcuate slot  138  overlays a threaded bolt hole  142  formed in the housing neck piece  42  of the housing half  14 , when the shaft assembly  100  is mounted to the housing  12 . The set screw  140  is used to fix the position of the lever  120  to prevent rotation of the shaft  40  once it is in the desired position. By loosening the set screw  140 , the lever  120  can be rotated to various positions to rotate the shaft assembly  100 , with the set screw  140  sliding within the slot  138 . 
     FIG. 8A  is a longitudinal cross-sectional view of the assembled pump  10  shown in more mechanical detail. Although one particular embodiment is shown, it should be apparent to those skilled in that a variety of different configurations and components, such as bearings, seals, fasteners, etc., could be used to ensure the proper operation of the pump  10 . The embodiment described is for ease of understanding the invention and should in no way be construed to limit the invention to the particular embodiment shown. 
   As can be seen, the input shaft  32  extends through the collar  34  at the rearward end of the housing  12 . The collar  34  defines a cavity  144  that houses a pair of longitudinally spaced input shaft roller bearing assemblies  146 ,  148 . Each of the roller bearing assemblies  146 ,  148  is comprised of an inner race  154  and an outer race  156 , which houses a plurality of circumferentially spaced tapered roller bearings  158  positioned therebetween. Spacers  150 ,  152  maintain the roller bearing assemblies  146 ,  148  in longitudinally spaced apart relationship along the input shaft  32 , with the inner race  154  of the roller bearing assembly  148  abutting against an outwardly projecting annular step  160  of the drive shaft  32 , and the outer race  156  abutting against a inwardly projecting annular shoulder  162  of the collar  34 . 
   A bearing nut  164  threaded onto a threaded portion  165  of the input shaft  32  abuts against the inner race  154  of bearing assembly  146  and preloads the inner races  154 . Bolted to the end of the collar  34  is a bearing retainer ring  166 . The bearing retainer ring  166  abuts against the outer race  156  of bearing assembly  146  and preloads the outer bearing races  156 . The retainer ring  166  also serves to close off the cavity  144  of the housing collar  34 . An annular oil seal  168  seated on the annular lip  170  of the retainer ring  166  bears against the exterior of the bearing nut  164  to prevent leakage of oil or lubricant from the bearing cavity  144 . 
   Located within the recessed area  28  and surrounding the input shaft  32  is a washer  172  that abuts against the inner race  154  of the bearing assembly  148 . A compressed coiled spring  174  abuts against the washer  172  and bears against a carbon sleeve  176 . The sleeve  176  is provided with an O-ring seal  178  located within an inner annular groove of the sleeve  176 . The sleeve  176  abuts against a fixed annular ceramic plate  180 , which seats against an annular lip  182  projecting into the recessed area  28 . The low coefficient of friction between the interfacing carbon sleeve  176  and ceramic plate  180  allows the sleeve  176  to rotate with the input shaft  32 , while providing a fluid-tight seal to prevent fluid flow between the pump interior  18  and the collar cavity  144 . 
   The input shaft  32  extends into the interior  18  of the housing  12  a short distance and is coupled to the primary vane assembly  52  within the recesses  60  formed in vane halves  56 ,  58 . The end of the shaft  32  is provided with an annular collar  184  received in grooves  186  formed in the recesses  60  of the vane halves  56 ,  58  to prevent relative axial movement of the shaft  32  and vane assembly  52 . Rotational movement of the vane assembly  52  and shaft  32  is prevented by key members  188  received in key slots of the vane assembly  52  and shaft  32 , respectively. 
   Surrounding the fixed shaft portion  40  within the recess  70  of the primary vane assembly  52  are longitudinal roller bearings  206 . Seals  208 ,  210  are provided at either end of the roller bearing assembly  206  to prevent fluid from escaping along the fixed shaft  40  through recesses  70 . A static O-ring seal  212  surrounds the shaft  40  at the interface of the lever arm  120  with housing neck piece  42  to prevent fluid loss through shaftway  38 . 
   Surrounding the carrier ring shaft  104  are roller bearing assemblies  214 ,  216 . Each roller bearing assembly  214 ,  216  is comprised of an inner race  218  and an outer race  220  with a plurality of tapered roller bearings  222  therebetween. The inner races  218  of assemblies  214 ,  216  are spaced apart by means of a spacer  224 . The inner face of the carrier ring  116  rests against the outer races  220 . An annular web  226  projects radially inward from the inner annular face of the carrier ring  116  and serves as a spacer between the outer races  220  and prevents axial movement of the carrier ring  116  along the shaft  104 . 
   Lip seals  230 ,  232  provided in inner faces of the end cap  108  and spherical portion  102 , respectively, engage the side edges of the carrier ring  116  to prevent fluid from entering the annular space surrounding the carrier ring shaft  104  where the bearing assemblies  214 ,  216  are housed and which contains a suitable lubricant for lubricating the bearing assemblies  214 ,  216 . 
   Axially oriented roller bearings  234  surround the pivot posts  118  to allow the secondary vanes  54  to rotate. Fluid seals  236  are provided at the base of posts  118 . Radially oriented thrust bearings  238  located at the terminal ends of posts  118  and are held in place by thrust caps  240 . The thrust caps  240  are held in place within annular grooves  242  formed in the pivot post recesses  92 . 
   As can be seen, the outer ends of the primary vanes  52  and secondary vanes  54  are in close proximity or a near touching relationship to provide a clearance with the interior  18  of the housing  12 . There is also a slight clearance between the spherical end portion of the fixed shaft assembly  100  and the central openings  69 ,  90  of the primary and secondary vanes  52 ,  54 . These clearances should be as small as possible to allow free movement of the vanes  52 ,  54  within the interior  18 , while minimizing slippage or fluid loss across the clearances. 
     FIG. 8B  illustrates the relationship of the various rotational axes of the pump components. As shown, the secondary vane  84  rotates about a secondary vane rotational axis, which is the same as the carrier ring axis  246 . The axis  246  intersects the primary vane axis  33  at an oblique angle and defines a control plane  247 . The secondary vane  54  pivots around the pivot posts  118  about a secondary vane pivot axis  245  that remains perpendicular to the carrier ring axis  246 . 
     FIG. 8C  shows an end view of the pump  10  as viewed along the primary axis, and showing the various orientations of the timing or control plane  247  that may be achieved by rotating the fixed shaft assembly  100 , as is described below. 
   Referring to  FIGS. 9–14 , the pump  10  is shown with the upper housing  16  removed to reveal the internal components of the pump  10 . The ports  24 ,  26  of the upper housing  16 , however, are shown to indicate their relative position if the upper housing  16  were present. Further, although the input shaft  32  may be rotated in either a clockwise or counterclockwise direction, for purposes of the following description the operation of the pump  10  is described wherein the input shaft  32  is rotated in a clockwise direction, as indicated by the arrow  244 . 
   Referring to  FIGS. 9A–9D , the pump  10  is shown with the lever  120  fully rotated to an initial 0° position. With the lever  120  in this position, the fixed shaft assembly  100  is oriented so that the carrier ring or secondary axis  246  is oriented at a 45° angle to the right of the primary axis  33 , as viewed in  FIG. 9C , so that the control plane  247  ( FIGS. 8B and 8C ) lies in a substantially horizontal plane that is generally the same or parallel to the plane of the flanges  20  which bisect the housing  12 . 
     FIGS. 9A–9D  show the primary and secondary vanes  50 ,  98  with the secondary vane  98  at a central intermediate position of its stroke. The forward port  26  of the upper housing  16  and the rearward port  24  of the lower housing  14  serve as discharge ports, while the rearward port  24  of the upper housing  16  and the forward port  26  of the lower housing  14  serve as intake ports. The primary and secondary vanes  50 ,  98  divide the spherical interior  18  of the housing into four chambers, as defined by the spaces between the primary and secondary vanes  50 ,  98  designated at  248 ,  250 . Although not visible, corresponding spaces or chambers would be present in the lower housing half  14 . 
     FIGS. 10A–10E  show sequenced views of the pump  10  in operation with the control lever  120  in the 0° position as the input shaft is rotated through 180° of revolution. For ease in describing the operation, the opposing secondary vanes are labeled  98 A,  98 B, with the opposing primary vanes being designated  50 A,  50 B. As shown in  FIGS. 9A and 9C , as the input shaft  32  is rotated, the primary and secondary vanes assemblies  52 ,  54  are rotated about the primary axis  33  within the housing interior  18 . Because the secondary vane assembly  54  is pivotally mounted to the carrier ring  116  by means of pivot posts  118 , the secondary vane assembly  54  causes the carrier ring  116  to rotate on the carrier ring shaft  104  (not shown) about the carrier ring axis  245 . Because the carrier ring axis  245  is oriented at an oblique angle with respect to the primary axis  33 , the carrier ring  116  causes each secondary vane  98 A,  98 B to reciprocate or move back and forth between a fully open position and a fully closed position. 
     FIG. 10A  shows the pump  10  with the secondary vane  98 A in the fully closed position with respect to primary vane  50 A. In the fully closed position, the secondary vane  98 A abuts against or is in close proximity to the primary vane  50 A, so that the volume therebetween is minimal. In contrast, with respect to the opposing primary vane  50 B, the vane  98 A is in a fully open position so that the space between the vanes  98 A and  50 B is at its maximum. Any fluid within the space between vanes  98 A,  50 A is fully discharged through the port  26  of the upper housing. There is a slight overlap or communication of the interfacing primary and secondary vanes  50 A,  98 A with the port  26  along its edge when in the fully closed position to accomplish this. In the preferred embodiment, the primary vanes  50 A,  50 B are sized to completely cover and seal the ports  24 ,  26  so that slight rotation beyond this point causes the primary vanes  50 A,  50 B to close off communication with the chambers  248 ,  250  momentarily during rotation. 
     FIG. 10B  illustrates the pump  10  with the shaft  32  rotated approximately 45° from that of  FIG. 10A . Here the secondary vane  98 A begins to move to the open position with respect to the primary vane  50 A. This draws fluid into the opening space through the lower inlet port  26  of the lower housing  14 . The secondary vane  98 B also begins to move to the closed position with respect to the primary vane  50 A. Fluid located in the chamber between the primary vane  50 A and secondary  98  is thus compressed or forced out of the upper discharge port  26  of the upper housing  16 . 
   In a like manner, fluid located between the secondary vane  98 A and primary vane  50 B is discharged through the lower port  24  of the lower housing  14 , as the secondary vane  98 A begins to move to the closed position with respect to the primary vane  50 B. Fluid is also drawn through the inlet port  24  of the upper housing  16  as the secondary vane  98 B is moved towards an open position with respect to the primary vane  50 B. 
     FIGS. 10C and 10D  show further rotation of the shaft  32  in approximately 45° increments. When the fixed shaft  100  is in the 0° position, the timing is such that the chambers created by the primary and secondary vanes  50 ,  98  remain in continuous communication with ports  24 ,  26  during generally the entire stroke of the vane  50  between the closed and open positions. In this way fluid continues to be drawn into or discharged from the chambers as the secondary vanes  98  are moved to either the open or closed positions during rotation of the shaft  32 . 
     FIG. 10E  shows the pump  10  after the shaft  32  is rotated 180°. The secondary vane  98 B is in the fully closed position with respect to the primary vane  50 A, just as the secondary vane  98 A was when the shaft  32  was at the 0° position in  FIG. 10A . By continuing to rotate the shaft  32 , the process is repeated so that the fluid is taken into the pump, compressed and discharged by the reciprocation of the secondary vane between the open and closed positions, which is caused by the rotation of the carrier ring  116  about its oblique axis  246 . 
   By rotating the fixed shaft  100  to different fixed positions, the flow of fluid through the pump  10  can be adjusted and even reversed without changing the direction of rotation of the input shaft  32 .  FIG. 11A  shows the pump  10  with the lever  120  rotated fully 180° from the 0° position of  FIGS. 9A–9D . In this position, the fixed shaft assembly  100  is oriented so that the carrier ring axis  246  is oriented at an approximately 45° angle to the left of the primary axis  33 , as viewed in  FIG. 11C , or about 90° 0  from that orientation of the axis  246  as shown in  FIG. 9C . In this position, the control plane  247  lies in a substantially horizontal plane that is generally the same or parallel to the plane of the flanges  20  which bisect the housing  12 . 
   In the configuration of  FIGS. 11A–11D , the forward port  26  of the upper housing  16  and the port  24  of the lower housing  14  serve as intake ports, while the port  24  of the upper housing  16  and the port  26  of the lower housing  14  serve as discharge ports. 
     FIGS. 12A–12E  show sequenced views of the pump  10 , with the control lever  120  rotated to the 180° position, as the input shaft  32  is rotated through 180° of rotation. In  FIG. 12A , the pump  10  is shown with the secondary vane  98 A in the fully closed position against the primary vane  50 A. The vane  98 A is also in a fully open position with respect to primary vane  50 B. Referring to  FIG. 12B , as the input shaft  32  is rotated, as shown by the arrow, the secondary vane  98 A begins to move to the open position with respect to the primary vane  50 A. The space or chamber formed between the secondary vane  98 A and vane  50 A is in continuous communication with the port  26  of the upper housing  16  as it is moved to the open position. The increasing volume of this chamber as the shaft  32  is rotated, as shown in  FIGS. 12C and 12D , draws fluid through the upper forward port  26 . As this is occurring, the secondary vane  98 B moves to the closed position with respect to the primary vane  50 A forcing fluid between these vanes  98 B,  50 A through the forward port  26  of the lower housing  14 . 
     FIG. 12E  shows the pump after the shaft  32  is rotated 180°. The secondary vane  98 B is now in the closed position with respect to the primary vane  50 A so that the process can be repeated. With the lever  120  in the 180° position, fluid is also discharged through rearward port  24  in the upper housing  16  and introduced through rearward port  24  of the lower housing  14  in the similar manner as that already described with respect to the forward ports  26 . The ports  24 ,  26  remain in generally constant communication with one of the chambers created by the vanes  50 ,  98  during the entire stroke of the vane  98  between the open and closed positions. 
     FIGS. 13A–13D  illustrate the pump  10  in an intermediate or neutral mode, with the control lever  120  oriented at an upright 90° position. In this position, the fixed shaft assembly  100  is oriented so that the carrier ring axis  246  lies in a plane perpendicular to the housing flanges  20  and is oriented at an angle of 45° below the primary axis  33 , as viewed in  FIG. 13D . In this orientation, the control plane  247  is in the 90° or vertical position, as seen in  FIG. 8C . In this mode, the ports  24 ,  26  only communicate approximately 50% of the time with the chambers created by the vanes  50 ,  98 . 
     FIG. 14A  shows the secondary vane  98  in a center or intermediate position, with the primary vane  50  oriented so that it covers and seals the ports  24 ,  26 . As the input shaft  32  rotates from this intermediate position, as shown in  FIG. 14B , the port  26  of the upper housing  16  begins to communicate with the chamber between secondary vane  98 B and primary vane  50 A, and the port  26  of the lower housing  14  communicates with the chamber between the secondary vane  98 A and primary vane  50 A. As the secondary vane  98 B is moved towards the open position with respect to the primary vane  50 A, some fluid is drawn through the port  26  of the upper housing  16 . In a similar manner, the secondary vane  98 A is moved to the closed position with respect to the primary vane  50 A so fluid therein is forced out of the lower port  26 . 
     FIG. 14C  shows the secondary vane  98 B in the fully open position with respect to the primary vane  50 A. The secondary vane  98 A, which is hidden from view, is in the fully closed position with respect to primary vane  50 A, with the closed space between the primary vane  50 A and secondary vane  98 A being in communication with the lower forward port  26  of the lower housing  14 . 
   As the shaft  32  is rotated further, as seen in  FIG. 14D , some fluid is forced out of the upper housing  16  through port  26  as the secondary vane  98 B now moves to the closed position with respect to vane  50 A. Fluid is also drawn in through the lower port  26  as the secondary vane  98 A is moving to the open position in relation to the primary vane  50 A. 
     FIG. 14E  shows the pump  10  after rotation of the shaft  32  180° from its original position of  FIG. 14A . The secondary vane  98  is once again in the intermediate position, like that of  FIG. 14A , and the process is repeated. With the control lever  120  in the 90° position, as described, the ports  26  of the lower and upper housing  14 ,  16  only communicate with the chambers defined by the primary and secondary vanes  50 ,  98  approximately 50% of the time. This results in equal volumes of fluid being both drawn and discharged through each of the forward ports  26  in the upper and lower housing during this neutral mode. The operation is the same with respect to the fluid flow through the rearward ports  24  in the lower and upper housing  14 ,  16 . The net fluid flow through the pump  10  is therefore essentially zero. 
   By rotating the control lever  120  between the 0° and 180° positions, the fluid flow can be increased or decreased precisely in a smooth and continuous manner, and can be directed in either flow direction. This is due to the increased amount of time the inlet ports and outlet ports communicate with the chambers  248 ,  250  formed by the vanes  50 ,  98  during the expansion and compression strokes, respectively, of the secondary vane  98 . Thus, for example, as the lever  120  is rotated from the 90° or neutral position towards the 0° position of  FIG. 10A , the length of time the forward port  26  of the upper housing  16  communicates with the chamber formed by the primary vane  50 A and secondary vanes  98 , as the secondary vanes  98  are moved to the closed position, is lengthened, resulting in more and more fluid flow through this port. As described previously, when the lever is at the full 0° position, the port  26  of the upper housing  16  is in communication with the chamber formed by the primary vane  50 A secondary vanes  98  during almost the entire compression stroke of the secondary vanes  98  with respect to the vane  50 A so that full flow is achieved when the pump  10  is in this mode. Similar results in the reverse-flow direction are achieved by rotating the lever  120  between the 90° and the 180° position, which is shown in  FIG. 12A . 
     FIGS. 15 and 16  show the pump  10  used in different fluid flow systems. As shown in  FIG. 15 , the pump  10  is powered by a suitable motor  254  that rotates the input shaft  32  of the pump. The pump  10  is connected to a fluid reservoir or vessel  256 . Here, the lever  120  is oriented in the 0° position. As the pump  10  is operated, fluid is pumped from the vessel  256  to the storage vessel  258 .  FIG. 16  shows generally the same system, except that the lever  120  is rotated 180° so that reverse fluid flow is achieved, while the motor  254  continues to rotate the input shaft  32  in the same direction as that of  FIG. 15 . 
     FIGS. 17–21  illustrate another embodiment wherein a fluid capacity control plate  260  is used instead of the control lever  120 . The control plate  260  is a flat, circular metal plate having a central bolt hole  262  for receiving a bolt  264  ( FIG. 18 ). The bolt  264  is used to secure the control plate  260  to the fixed shaft  40  of the fixed shaft assembly  100  by means of the threaded bolt hole  130  formed in the fixed shaft  40 . Dowel holes  266  are formed in the plate  260  around the bolt hole  262  and correspond to the dowel holes  134  of the fixed shaft  40  for receiving dowels  136 . The dowel holes  266  are circumferentially spaced 90° apart. The dowels  136  received within the dowel holes  266  prevent relative rotation of the control plate  260  with respect to the shaft  40 . 
   Formed along the perimeter of the plate  260  are spaced apart bolt holes  268 . The bolt holes  268  are configured to overlay the threaded bolt holes  270  ( FIGS. 1 and 2 ) formed in the neck piece  42  of the housing  12 . As shown in FIG.  20 , the dowel holes  266  are generally aligned along vertical and horizontal lines when the plate  260  is mounted to the neck portion  42  of the housing  12 . 
   Using the control plate  260 , the fixed shaft assembly  100  can be rotated to different fixed positions in 90° increments with respect to the housing  12  by repositioning and bolting the control plate  260  to the housing  12 . 
     FIG. 19  shows another control plate  260 ′. The control plate  260 ′ is generally the same as the plate  260  of  FIG. 17 , with like components having the same numeral designated with a prime symbol. The control plate  260 ′ has the four dowel holes  266 ′ aligned at approximately 30° from the vertical and horizontal positions when the plate  260 ′ is mounted to the housing  12 , as shown in  FIG. 21 . The plate  260 ′ may even be reversed so that the underside faces outwards. This orients the dowel holes  266 ′ so that they are approximately 60° from the vertical and horizontal positions. As will be appreciated by those skilled in the art, many different control plates having different dowel hole configurations may be provided with the pump  10  to orient the fixed shaft assembly  100  to provide the optimal compression or fluid flow. 
   Other means could be provided for rotating the fixed shaft assembly  100 . For instance, shaft  40  could be coupled to a worm and worm gear to rotate the fixed shaft to various positions. This is shown in  FIG. 1  as an alternative. Worm gear  121  would be attached to end of shaft  40  and worm  123 , powered by motor  125 , would turn, turning worm gear  121 . This in turn could be coupled to a controller that would cause the fixed shaft assembly to be rotated to automatically control and adjust the fluid flow or capacity of pump  10 . 
   In another embodiment, the vanes may be configured with recesses or hollowed out areas to reduce the weight of the vane, as shown in  FIG. 23A . This is particularly important with respect to the secondary vane because the secondary vane is both rotated and reciprocated along the primary axis. Because the secondary vane is reciprocated between the open and closed positions, it undergoes numerous and rapid changes in angular velocity during operation. The inertial forces created by these changes in angular velocity place a large amount of stress on the vane. By reducing the weight of the vane, the inertial forces can be reduced. This is particularly advantageous in pumps that operate at high speed and low pressures. 
     FIGS. 22 and 23  illustrate primary and secondary vane halves  271 ,  272 , respectively. The primary and secondary vane halves  271 ,  272  are similar to the vane halves  56 ,  58 ,  76  and  78 , with similar components numbered the same and designated with a prime symbol. Although only one of the primary and secondary vane halves is shown, the other matching vane half would be similarly constructed. 
   As can be seen in  FIG. 23 , the secondary vane half  271 , used for the reciprocating secondary vane, is provided with recessed or cutout areas  274 ,  276  in the outer surface of the vane members  82 ′,  84 ′ to provide a reduction in weight. A central rib  278  divides the recessed areas  274 ,  276  and provides structural support to strengthen the vane members  82 ′,  84 ′. The rib  278  increases in thickness from the inward end to the outer end of the vane members  82 ′,  84 ′. This creates greater strength near the outer extent of the vane member where it is most needed due to the higher velocity and centrifugal forces encountered near the ends of the vanes. 
   As shown in  FIG. 23 , the primary vane half  272  is constructed to correspond to the configuration of the secondary vane half  271 . The primary vane members  62 ′,  64 ′ each have projecting members  280 ,  282 , which are shaped to be closely received within the recesses  274 ,  276  of the secondary vanes. A channel  284  formed between the members  280 ,  282  receives the rib  278 . 
   The pump  10  may be used as a compressor for compressing compressible fluids. When used in this mode, a check valve (not shown) can be coupled to the discharge ports or the discharge ports can be provided with valves (not shown) timed to open during a given point in the compression stroke of the vanes so that the desired compression is achieved. It may also be possible to provide pre-compression within the pump  10  itself by delaying communication of the chambers between the vanes during the compression stroke. This may be accomplished by configuring the primary vane or the outlet port itself so that communication with the compression chamber formed by the vanes is delayed during the compression stroke. By rotating the fixed shaft assembly to different positions, as already described, the compression and fluid flow can also be adjusted. 
   The pump  10  may also be used to pump incompressible or hydraulic fluids. When the pump  10  is fluid tight so that there is substantially no fluid slippage across the vanes, the timing should be set so that the outlet ports are in communication with the compression chamber during the entire compression stroke, such as when the control lever is in one of the full flow modes, i.e. the full 0° or 180° positions as previously described. Otherwise, the possibility of fluid lock may occur as the vanes act on the fluid. It may also be possible to configure the pump so that some slippage of fluid flow across the vanes occurs during operation to avoid such hydraulic fluid lock. In such cases, the communication of the outlet ports with the compression chambers could be delayed to some degree without the occurrence of fluid lock. 
   The device  10  could also function as a motor wherein pressurized fluids are introduced into the device and then exhausted. The operation would be reversed so that the action of the expanding or pressurized fluids introduced into the pump would act upon the vanes to thus turn or rotate the shaft  32 . 
   The fluid device of the invention has several advantages. The pump itself is highly efficient, pumping substantially twice the free volume of the pump interior for every revolution of the input shaft, when used in the full flow mode. The device does not need to be primed, as in many prior art devices. It can be used for many different applications and with a variety of different fluids, both compressible and noncompressible. It can be used as a vacuum pump. The device may even be used as a motor. 
   In prior art spherical pumps, the vane assemblies had to be positioned and oriented properly during manufacture to ensure proper timing of suction and discharge and to ensure proper operation of the pump. This timing could not be varied after the pump was assembled. Further, the flow of fluid could not be changed other than by varying the speed at which the drive shaft was rotated. The device of the present invention allows the timing or pump capacity to be easily and simply controlled with a greater degree of precision by adjusted or rotating the orientation of the fixed shaft assembly and without adjusting or varying the rotation of the drive or input shaft. Further, the timing can be adjusted easily after the pump is manufactured and fully assembled. The direction of fluid flow can even be reversed during operation and without altering the direction of rotation of the input shaft. Both the lever  120  and control plate  260  provide an easy means for orienting the fixed shaft assembly and adjusting and ensuring the proper timing of suction and discharge. It should be noted that although the race assembly is shown located within the center of the housing interior to guide the reciprocating secondary vane as the secondary vane is rotated about the race assembly, a race assembly could also be employed that is exterior to the secondary vane, with a carrier ring that is positionable at various positions exterior to the secondary vane. 
   The pump employs other advantages, such as the ribs or fins of the outer housing that reduce weight and provide increased surface area for heat transfer. The hollowed or recessed secondary vanes, which reduce the weight of the vane, also contribute to the smooth and efficient operation of the device. 
   Having thus described the present invention by reference to certain of its preferred embodiments, it is noted that the embodiments disclosed are illustrative rather than limiting in nature and that a wide range of variations, modifications, changes, and substitutions are contemplated in the foregoing disclosure and, in some instances, some features of the present invention may be employed without a corresponding use of the other features. Many such variations and modifications may be considered obvious and desirable by those skilled in the art based upon a review of the foregoing description of preferred embodiments. Accordingly, it is appropriate that the appended claims be construed broadly and in a manner consistent with the scope of the invention.