Abstract:
A fluid transfer machine includes a positive displacement, rotary-type pumping mechanism. The pumping mechanism is driven by a drive shaft. The drive shaft is lubricated and cooled by locating the drive shaft in the primary flow path through the machine. The primary flow is directed from the inlet through a passage that intersects the drive shaft, at a location between a pair of journal bearings or sleeves. The fluid then continues directly to the suction side of the pumping mechanism. The drive shaft could also be located on the pressure side of the pumping mechanism. The primary flow cools and lubricates the drive shaft (and drive shaft bearings), and reduces the size and complexity of the machine, as additional cooling and lubrication flow passage(s) are not necessary.

Description:
CROSS-REFERENCE TO RELATED CASES  
       [0001]    The present application claims the benefit of the filing date of U.S. Provisional Application Serial No. 60/298,301, filed June 14, the disclosure of which is expressly incorporated herein by reference. 
     
    
     
       BACKGROUND OF THE INVENTION  
         [0002]    The present invention relates generally to a fluid transfer machine, and more particularly to a fluid transfer machine that can be used as a pump or motor.  
           [0003]    Fluid transfer machines can have different types of pumping mechanisms to move fluid through the machine. One type of pumping mechanism useful for a variety of fluid transfer machines is a positive displacement rotary pump. Conventional positive displacement rotary pumps include single rotors (vane, piston, progressing cavity, screw or peristaltic), or multiple rotors (internal/external gear, lobe, circumferential piston or screw). The mechanisms all have advantages and drawbacks, depending on the fluid to be pumped, and the particular application.  
           [0004]    During movement of the pumping mechanisms, friction can cause wear and heating of the moving parts, which can degrade the machine over time, and lead to failure and/or costly and time-consuming repairs.  
           [0005]    Fluid is typically used for lubricating the moving parts of the pumping mechanism. It is particularly advantageous to use a portion of the fluid being transferred through the machine as the cooling and lubricating fluid. It is well-known to provide additional flow passages through the housing of the machine and to tap or bleed off a portion of the fluid from the primary flow for use in lubrication and cooling. It is also known to intentionally provide leak paths between the moving components and then collect the fluid for return to the primary flow path. Examples of such machines are shown in Ishizuka, U.S. Pat. No. 6,048,185; Riddle, U.S. Pat. No. 3,994,634; and Zieg, U.S. Pat. No. 2,940,399.  
           [0006]    It is also known to provide grooves in rotating shafts to assist in moving the cooling and lubrication fluid between the components in the fluid transfer machine, such as shown in Sluijters, U.S. Pat. No. 3,368,799.  
           [0007]    While the machines shown and described above are useful in some applications, forming (e.g., drilling) the flow passages in the machine to direct the cooling and lubricating fluid to the various components can be labor-intensive and difficult. A number of angled passages are typically required, which requires multiple drilling steps. This is shown particularly in Janczak, U.S. Pat. No. 4,548,557, where complex passages requiring multiple drilling steps are used to avoid connecting the primary fluid flow path directly with the drive shaft. Janczak points out that high pressure fluid around the drive shaft could damage or weaken the seals along the shaft.  
           [0008]    Providing such complex passages also increases the size of the machine and the space necessary for locating the machine in the fluid transfer system. With the demand for smaller and lighter pumps and motors, and smaller fluid transfer systems, it has become increasingly difficult to manufacture such machines in a cost-effective, compact manner, particularly for high-performance applications which require high flow rates.  
           [0009]    One partial solution is shown in Dworak, U.S. Pat. No. 4,038,000, where the primary flow path through the machine is directed from the inlet, through the gear mechanism (stub shafts and bearings), to the outlet. There are no additional lubrication and cooling passages for the bearings and stub shafts, beyond what is used to direct the primary flow through the machine. The Dworak machine has the advantage in that the machine is smaller and easier to construct, and keeps the pumping mechanism properly lubricated and cooled. Nevertheless, the Dworak machine does not address friction and wearing of the drive shaft, as the primary flow path in Dworak is limited to only the stub shaft and associated bearings. The drive shaft is also rotating, and particularly in high-performance applications, also has friction and wear issues.  
           [0010]    Thus, it is believed there is a further demand for an improved fluid transfer machine, particularly a machine that can be used as a pump or motor, where the drive shaft is properly lubricated and cooled, and which has a compact design that is easily-manufactured.  
         SUMMARY OF THE INVENTION  
         [0011]    The present invention provides a novel and unique fluid transfer machine, particularly useful as a pump or motor, where the drive shaft (as well as the pump mechanism) is properly lubricated and cooled, and which has a compact design that is easily-manufactured.  
           [0012]    According to the present invention, the fluid transfer machine has a pumping mechanism that is a positive displacement, rotary (single or multiple rotor) type pump appropriate for the particular application. An external gear-type pump is used in a preferred form of the invention. The machine can be run as a motor or as a pump, as should be well know, typically by reversing the rotation of the pumping mechanism.  
           [0013]    The pumping mechanism includes a typical arrangement of components such as bearings and stub shafts, which are preferably lubricated in a conventional manner, such as by allowing a slight leak path between the moving components.  
           [0014]    The pumping mechanism is driven by a drive shaft, which extends out of the housing and is acted upon by (or acts upon) an external device. To lubricate and cool the drive shaft, and in particular the portion of the drive shaft internal to the housing, the drive shaft is located in the primary flow path through the fluid transfer machine. In a preferred embodiment, the drive shaft is located in the inlet flow path of the primary flow. The primary flow is directed from the inlet port to a cavity that surrounds the drive shaft, at a location between a pair of journal bearings or sleeves. The flow then continues to the suction side of the pumping mechanism. Alternatively, the drive shaft could be located in the outlet flow path of the primary flow path, between the pressure side of the pumping mechanism and the outlet port. In either case, the primary flow cools and lubricates the drive shaft (and drive shaft bearings), and reduces the size of the fluid transfer machine, as additional cooling and lubrication flow passage(s) are not necessary. This also reduces the complexity of manufacture of the machine.  
           [0015]    The present invention thereby addresses many of the issues with prior machines, and provides a fluid transfer machine, particularly useful as a pump or motor, where the drive shaft (as well as the pump mechanism) is lubricated and cooled, and which has a compact design that is easily-manufactured.  
           [0016]    Further features of the present invention will become apparent to those skilled in the art upon reviewing the following specification and attached drawings 
       
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
       [0017]    [0017]FIG. 1 is an elevated perspective view of a positive displacement rotary fluid transfer machine constructed according to the principles of the present invention;  
         [0018]    [0018]FIG. 2 is a side view of the machine of FIG. 1;  
         [0019]    [0019]FIG. 3 is a cross-sectional end view of the machine taken substantially along the plane describe by the lines  3 - 3  of FIG. 2;  
         [0020]    [0020]FIG. 4 is a cross-sectional side view of the machine taken substantially along the plane describe by the lines  4 - 4  of FIG. 3;  
         [0021]    [0021]FIG. 5 is a cross-sectional side view of the machine taken substantially along the plane describe by the lines  5 - 5  of FIG. 3;  
         [0022]    [0022]FIG. 6 is a cross-sectional side view of the machine taken substantially along the plane describe by the lines  6 - 6  of FIG. 3;  
         [0023]    [0023]FIG. 7 is a cross-sectional side view of the machine taken substantially along the plane describe by the lines  7 - 7  of FIG. 3; and  
         [0024]    [0024]FIG. 8 is a cross-sectional side view of the machine taken substantially along the plane describe by the lines  8 - 8  of FIG. 3.  
     
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT  
       [0025]    Referring to the drawings, and initially to FIGS. 1 and 2, a positive displacement, rotary-type fluid transfer machine is indicated generally at  20 . The machine has a housing or body  21 , with a first, inlet port  22 , and a second, outlet port  23 . A drive shaft  26  projects outwardly from the housing and can be rotated to operate a pumping mechanism internal to the housing.  
         [0026]    While a preferred form of machine will be described herein, it is to be noted that the machine could have any type of positive displacement rotary-type pump such as a single rotor (e.g., vane, piston, progressing cavity, screw or peristaltic); or multiple rotor (e.g., internal/external gear, lobe, circumferential piston or screw) pump. It should also be well-known that the machine could be operated as a pump or a motor, depending on the rotation of the drive shaft  26 , and the connections to ports  22  and  23 .  
         [0027]    As can be seen in FIGS.  3 - 8 , the housing  21  consists of three cylindrical sections  30 ,  31  and  32 , which are arranged end-to-end in a conventional manner, and screwed together such as with elongated bolts  35 . Inlet port  22  is provided in end section  32 , while outlet port  23  is provided in end section  30 . It is noted that inlet and outlet ports  22 ,  23  could alternatively be formed in only one of the sections and/or in middle section  31 , or could be located at one or both of the axial ends of the housing. In any case, appropriate seals  36  are provided between the sections to prevent fluid leakage.  
         [0028]    Middle section  31  includes a central chamber  37 , which receives a pumping mechanism, indicated generally at  40 . Chamber  37  is closed at either end by opposing end surfaces of sections  30  and  32 . Pumping mechanism  40  preferably comprises an external gear-type mechanism, with three gears  42 ,  43 ,  44  supported for rotation on stub shafts  46 ,  47 , and drive shaft  26 , respectively (see, e.g., FIG. 7). Stub shafts  46 ,  47  are closely received, preferably with press-fit, in blind end bores  48 ,  49 , respectively, extending inwardly from one end of the housing, such that shafts  46 ,  47  are prevented from rotating relative to the housing. Gears  42 ,  43  are received for rotation on stub shafts  46 ,  47 ; while drive shaft  26  is received with a key-in-groove or is fixed by other appropriate means to central gear  44 . Gear  44  is interposed between gears  42  and  43 , such that gears gear pair  42 ,  44  have teeth that intermesh during rotation, and gear pair  43 ,  44  also have teeth that intermesh during rotation. When drive shaft  26  is rotates, central gear  44  rotates both outer gears  42 ,  43 , simultaneously which in turn, create expanding and contracting pockets for transfer of fluid.  
         [0029]    Inlet port  22  is fluid connected to the suction side of the pumping mechanism, that is, at a location where the pockets between the gear teeth are expanding. Outlet port  23 , in contrast, is fluidly connected to the pressure side of the pumping mechanism, that is, at a location where the pockets in the gear teeth are contracting. To this end, inlet port  22  is fluidly connected to a single inlet passage portion  49 , which divides into a pair of passages  50   a,    50   b,  each of which is fluidly connected to the suction side of each gear pair  42 ,  44  and  43 ,  44 , respectively. A pair of passages  53   a,    53   b,  are fluidly-connected to the pressure side of the pumping mechanism, and then combine and lead to a single outlet passage portion  54 , which is fluidly connected to outlet port  23 . A primary flow path is thereby established from the inlet port  22  through inlet passages  49 ,  50   a,    50   b;  through the expanding and contracting pockets of the gears  42 - 44 ; and through outlet passages  53   a ,  53   b,    54  to outlet port  23 .  
         [0030]    The structure describe above is fairly conventional in three-gear, external gear-type pumping mechanism, as should be appreciated by those skilled in the art. Again, the three-gear pumping mechanism is only exemplary in nature, and other pumping mechanisms could be used, depending upon the particular application. For example, only two intermeshing gears could be provided, with only a single passage leading to the suction side, and a single passage leading from the pressure side; or an entirely different type of pumping mechanism, such as a single rotor (vane, piston, progressing cavity, screw or peristaltic), or other multiple rotor (internal/external gear, lobe, circumferential piston or screw), could be used.  
         [0031]    As should be appreciated, small clearances could be included between the moving parts of the pumping mechanism to allow slight leakage. The leakage would enable a thin layer of fluid to enter between the gears and the adjacent walls, and between the stub shafts and the gears, and provide lubrication and cooling of the components.  
         [0032]    The present invention provides a means to cool and lubricate the drive shaft during rotation of the gears. The drive shaft is typically supported on annular bearings, such as sleeve or journal bearings  60 ,  61 . Bearings  60 ,  61  are spaced apart axially along the drive shaft, with bearing  60  located closer to the pumping mechanism, and bearing  61  located closer to the distal end of the drive shaft. A cavity  65  is provided in housing section  32  in surrounding relation to shaft  26 , and between the bearings  60 ,  61 . Cavity  65  can be easily formed during the manufacture of the end housing section  32 . Cavity  65  is located in the primary flow path and received fluid directly from the inlet passage  49 , and then delivers the fluid directly to inlet passages  50   a ,  50   b  to the pumping mechanism.  
         [0033]    Fluid entering the inlet port  22  thereby flows through the port and completely surrounds drive shaft  26 , where the fluid provides lubrication and cooling of the drive shaft. The fluid seeps through bearings  60 ,  61 , and thereby also provides cooling and lubrication of the drive shaft bearings. Helical or spiral grooves, such as at  68  (FIGS. 5, 6,  8 ) assist in directing fluid along the shaft to cool and lubricate the shaft, as well as the bearings  60 ,  61 . If necessary or desirable, a fluid seal surrounding shaft  26  can be provided axially outward from outer bearing  61 , or a seal could be provided on an external component engaging shaft  26  and sealing against housing section  32  in the area surrounding shaft  26 .  
         [0034]    Of course, the machine could be operated in a reverse manner, such that port  22  is an outlet port, and the fluid is provided from the pressure side of the pumping mechanism  40  through passages  50   a,    50   b  to cavity  65 , and then to passage  49  and port  22 . The direction of rotation of drive shaft  26  determines whether the machine operates as a pump or motor, as should be well-known to those skilled in the art.  
         [0035]    In any case, as described above, the present invention addresses many of the issues with prior machines, and provides a fluid transfer machine, particularly useful as a pump or motor, where the drive shaft (as well as the pump mechanism) is lubricated and cooled, and which has a compact design that is easily-manufactured. The primary flow path is used to cool and lubricate the drive shaft (and drive shaft bearings) without the need for additional passages through the housing.  
         [0036]    The principles, preferred embodiments and modes of operation of the present invention have been described in the foregoing specification. The invention which is intended to be protected herein should not, however, be construed as limited to the particular form described as it is to be regarded as illustrative rather than restrictive. Variations and changes may be made by those skilled in the art without departing from the scope and spirit of the invention as set forth in the appended claims.