Abstract:
A circulating lubrication system for a centrifugal pump, or other rotating equipment utilizing an oil sump, is disclosed. The lubrication system includes an external reservoir located distant from the main lubrication chamber, so that lubricating fluid from the main misting chamber is forced out of the main chamber, cooled and cleaned (i.e. filtered) in the external reservoir, and thereafter fed back into the main lubricating chamber. In such a manner, the lubrication system maintains substantially clean, cool, and moisture free lubricating fluid in the main misting chamber and reduces the required downtime of the device. Thus, the life span of the device is lengthened while at the same time production is increased.

Description:
[0001]    This invention relates to a lubrication system for use in a pump or the like. More particularly, this invention relates to an oil misting system for a centrifugal chemical processing pump including an external reservoir provided for the purpose of reducing maintenance requirements, and maintaining clean and temperature efficient lubricating fluid in the pump misting chamber.  
         BACKGROUND OF THE INVENTION  
         [0002]    Environmentally hazardous fluids, such as acids, oils, and toxins, which can cause serious harm to the environment often need to be pumped throughout fluid flow systems from one location to another. Centrifugal pumps including a motor driven impeller affixed to a pump shaft are typically utilized in, pumping such fluids. The shafts of such pumps are typically rotatably supported against radial movement and vibration by conventional pump shaft bearings (e.g. ball bearings). These bearings must be continually lubricated throughout the operation of the pump in order to reduce maintenance requirements and maintaining a satisfactory operating life of the bearings and thus the pump.  
           [0003]    Conventional lubricating fluids, such as oils, are typically used to lubricate such pump shaft bearings. See, for example, commonly owned U.S. Pat. No. 5,340,273, the disclosure of which is hereby incorporated herein by reference. The lubricating fluid is generally housed in a bearing lubrication or misting chamber surrounding the pump shaft. Conventional pumps typically include ball bearings, as disclosed in the &#39;273 patent, located within or adjacent the misting or lubricating chamber, for supporting the pump shaft. In the prior art, these shaft supporting bearings are often lubricated by positioning the lubricant level within the lubrication chamber at a level or position about half-way up the bottom bearing ball. Maintaining the lubricating oil level at such a position necessarily translates into the bearing balls plowing through the lubricating fluid (e.g. oil) when the shaft and supporting bearings are rotated. This results in undesirable heat generation within the bearings and adjacent the pump shaft, such heat generation being caused by the friction created by the bearing balls continually passing through the lubricating oil. Such heat generation increases maintenance requirements and reduces the operating life of the bearings.  
           [0004]    Dirt, contaminants, and moisture in the lubricant is also a problem. The presence of such contaminants in the lubricating fluid results in increased wear and greatly reduced life of the bearings and thus additional maintenance.  
           [0005]    In the prior art, when it is time to “change the oil” in such pumps, it is necessary to shut down the pump, remove an oil plug typically located at the bottom of the misting chamber, drain the oil, close the plug, and thereafter fill the chamber with clean oil from the top. Unfortunately, this results in substantial downtime of the pump, undesirable labor requirements, and strong reliance upon operators in the field for inserting/removing the proper amount and type of lubricating fluid. Also, an undesirably large amount of oil is used over time.  
           [0006]    It is apparent from the above that there exists a need in the art for a lubrication system wherein: (i) the system is easily retrofitable to all pumps and similar equipment with a simple and easy to use installation kit; (ii) the lubricating fluid in the system is maintained in a clean and moisture free state without requiring frequent “oil changes”; (iii) the temperature of the lubricating fluid in the misting chamber is maintained at the lowest possible level so as to increase the life of the mechanical components therein; (iv) the system permits an operator to visually check the oil level and visual appearance of the oil in the pump without having to shut it down; and (v) a larger capacity lubricant reservoir is provided.  
           [0007]    It is the purpose of this invention to fulfill the above-described needs in the art as well as other needs apparent to the skilled artisan from the following detailed description of this invention.  
         SUMMARY OF THE INVENTION  
         [0008]    Generally speaking, this invention fulfills the above-described needs in the art by providing a universal, easy to install circulating lubrication system retrofit kit for lubricating shaft supporting bearings which rotatingly support a shaft, the circulating lubrication system comprising:  
           [0009]    a misting chamber surrounding the shaft and located proximate the bearings to be lubricated;  
           [0010]    a member affixed to and rotating with the shaft for causing lubricant to lubricate the bearings;  
           [0011]    a reservoir located remote from and in fluid communication with the misting chamber;  
           [0012]    an oil level in the misting chamber maintained below the lower balls of the bearings;  
           [0013]    circulating means for circulating the lubricant from the misting chamber to the reservoir and thereafter back to the misting chamber from the reservoir; and  
           [0014]    means for filtering the lubricant in the reservoir in order to maintain filtered lubricant in the misting chamber so as to prolong the operating life of the bearings;  
           [0015]    a reservoir which includes heat removing fins for reducing the temperature of the oil;  
           [0016]    a reservoir fitted with a moisture removing desiccant chamber for removing moisture from the air within the chamber preventing that moisture from contaminating the oil;  
           [0017]    an easy to use installation kit with instructions, charts, easily adjustable oil mister blade assembly, versatile finned reservoir multiple entry and exit port choices, drain valve, all required fittings and tubing, desiccant chamber, adjustable level arrow, full length sight glass, replaceable filter, optional adjustable support screws and installation slide template used to determine and set the appropriate oil height for any pump or similar equipment.  
           [0018]    According to certain preferred embodiments of this invention, the circulating lubrication system including the external reservoir is used in conjunction with a chemical processing centrifugal pump.  
           [0019]    This invention still further fulfills the above-described needs in the art by providing a method of maintaining substantially clean and moisture free lubricating fluid in a misting chamber of a pump, the pump including a rotatable shaft and bearings to be lubricated for supporting the shaft, the method comprising the steps of:  
           [0020]    providing the pump including the rotatable shaft and supporting bearings;  
           [0021]    providing lubricating fluid in the misting chamber proximate the bearings to be lubricated;  
           [0022]    lubricating the bearings by dispersing-the lubricating fluid throughout the misting chamber;  
           [0023]    forcing the fluid out of the misting chamber, through a first conduit, and into a fluid reservoir spaced from the misting chamber;  
           [0024]    removing moisture from the air within the chamber before it contaminates the oil;  
           [0025]    removing heat by way of the fins on the reservoir;  
           [0026]    filtering the fluid in the reservoir; and  
           [0027]    causing the filtered fluid to flow back into the misting chamber thereby maintaining substantially clean lubricating fluid in the misting chamber.  
           [0028]    This invention will now be described with respect to certain embodiments thereof, accompanied by certain illustrations, wherein: 
       
    
    
     IN THE DRAWINGS  
       [0029]    [0029]FIG. 1 is a side partial cross-sectional view of a typical pump with the oil level set half way up the lower bearing ball;  
         [0030]    [0030]FIG. 2 is an exemplary embodiment of the invention wherein the conventional pump shown in FIG. 1 is fitted with the easily adjustable oil misting blade assembly;  
         [0031]    [0031]FIG. 3 is an alternate view of the pump shown in FIG. 2 showing the external oil reservoir with fins, adjustable oil level arrow, adjustable support screws, and cover with desiccant chamber;  
         [0032]    [0032]FIG. 4 is a cross sectional end view taken along section line IV-IV of FIG. 3 showing the adjustable oil misting blade assembly mounted on the shaft, as well as fittings, tubing, drain valve, plugs, reservoir with fins, adjustable support screws, filter inside the reservoir, and reservoir cover with desiccant chamber.  
         [0033]    [0033]FIGS. 5 a - 5   d  show the details of the oil mister blade assembly.  
         [0034]    [0034]FIGS. 6 a - 6   c  show the oil reservoir with the fins, adjustable oil lever arrow, embossed oil level presets (lettered “A” through “O”), and versatile multiple entry and exit ports.  
         [0035]    [0035]FIG. 7 shows the provided installation template for setting a correct spatial relation for the lubrication components in conjunction with the pump.  
         [0036]    [0036]FIG. 8 shows the relationship of the installation template as used to measure the position of the outlet fitting for the pump.  
         [0037]    [0037]FIG. 9 shows the relationship of the installation template as used to measure the correct setting of the adjustable oil level arrow and adjustable support screws.  
         [0038]    [0038]FIGS. 10 a  and  10   b  illustrate how the slide rule template  180  can alternatively be used to measure the proper size of the blade  8  of the dispenser  4 .  
         [0039]    [0039]FIG. 11 shows the preferred design of the slide rule template of this invention.  
     
    
     DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS  
       [0040]    Referring now more particularly to the accompanying drawings in which like reference numerals indicate like parts throughout the several views.  
         [0041]    Below described is a circulating lubrication system according to certain embodiments of this invention used in conjunction with a centrifugal pump including a centrally located rotating shaft. However, it will be understood by those skilled in the art that the lubrication system and corresponding external reservoir according to certain embodiments of this invention may be used in conjunction with other rotating equipment that utilize a lubricant sump for the purpose of lubricating shaft supporting bearings.  
         [0042]    [0042]FIG. 1 illustrates a conventional centrifugal pump including bearings designed for oil lubrication. Bearing lubrication may be accomplished by internal oil misting, internal ring oil lubrication, external sources of oil, and/or flood oil.  
         [0043]    Referring to FIG. 1, the pump includes bearing frame  200 , lubrication oil  203 , reservoir chamber  201 , rotatable pump shaft  202 , bearings  204  and  205 , rigid frame adapter  209 , and conventional mechanical seal  211 . Lubricant  203  is provided in the lubricant oil reservoir chamber  201  and preferably maintained at a suitable level  208  depending on the operating characteristics of the pump and bearings  204 ,  205 .  
         [0044]    [0044]FIG. 2 is a side elevational partial cross-sectional view of the lubrication system of a centrifugal chemical processing pump according to a particular embodiment of this invention. Illustrated in FIG. 1 is surrounding pump housing  3 , in which misting or lubricating chamber  11  is defined. The centrifugal pump includes central rotating shaft  202  disposed between the pump motor and pump impeller. The fluid to be pumped is actually pumped by the impeller  213 , which in turn is driven by the motor (not shown) via elongated shaft  202 .  
         [0045]    The misting or lubricating system illustrated in FIG. 2 includes dispenser  4  made up of supporting band  6  to which a plurality of lubricant dispensing members or blades  8  are attached through a vane holder  9 . Blades  8  are collapsible in that they are pivotally attached to vane holder  9  so that they may pivot or flop (i.e. collapse) downward during both (i) insertion of the dispenser  4  into misting chamber  201  through bore  32 ; and (ii) during non-use of the pump when shaft  202  is not moving. In other words, blades  8  are collapsible by way of their mounting arrangement so as to allow the dispenser  4  to pass through the annular bore  32  that the bearing fits through during installation. The pitch of blades  8  can be altered from a flat pitch or angularity to a heavy pitch in order to produce different misting effects.  
         [0046]    One unique feature of the dispenser  4  is the split supporting band  6  that permits the dispenser to be mounted to an existing shaft without removing existing bearings. The collar is adjustable to fit a wide range of shaft diameters with one standard kit.  
         [0047]    Alternatively, when the annular bore  32  through which the dispenser  4  may be inserted is defined by the inner or interior diameter of a hole in the pump frame  3  (on either side of chamber  201 ), the diameter of dispenser  4  when members  8  are collapsed is less than the diameter of the bore. Thus, the dispenser with collapsed blades  8  may be inserted through the bore and into misting chamber  201 . However, once in chamber  201 , during pump operation when shaft  202  is rotated, blades  8  “stand up” so that the operating outer diameter of dispenser  4  is greater than the diameter of the bore  32  (and greater than the inner diameter of bearing frame(s)  3 , and greater than the diameter defined by the radius at which bearing balls  21  roll in their raceways). The operating diameter of dispenser  4  is of course defined by the diameter around the outer periphery of blades  8  as they rotate within chamber  201 .  
         [0048]    When the pump shaft  202  is driven by the pump motor, supporting band  6  and blades  8  affixed thereto rotate along with shaft  202  within annular lubricating chamber  201  thereby dispersing lubricating fluid (e.g. oil) throughout chamber  201  as shown in FIG. 1. When shaft  202  is rotated, the blades  8  are caused to extend radially away from shaft  202  (i.e. stand up) due to the centrifugal force created by rotation of the shaft  202 . Thus, during rotation of shaft  202  when the pump is pumping, the outer diameter of the dispenser (defined by the outer diameter of blades  8 ) is greater than the inner diameter of the stationary hole or bore through which it was inserted.  
         [0049]    Dispensing members or blades  8  dip into the lubricating fluid  203  below fluid level  19  when shaft  202  is rotated thereby dispensing or flinging the lubricant  203  throughout chamber  201  so that the lubricant makes its way into auxiliary passageways and therefrom down into auxiliary chambers (not mentioned herein). It is noted that the passageways and chambers defining a lubricant delivery passageway may take many forms not discussed herein.  
         [0050]    As shown in FIG. 2, the lubricating fluid level  19  within chamber  201  is, according to certain embodiments of this invention, maintained at a level below bearing rollers  21 . This lower lubricant level  19  requires a dispenser  4  with a larger working outer diameter than would otherwise be necessary so that the members  8  can reach into the lubricant below level  19 .  
         [0051]    Outer bearing portions or outer races  25  work in conjunction with inner bearing portions (i.e. inner races)  27  (affixed to shaft  202 ) so as to define roller raceways therebetween in which bearing rollers  21  move during shaft  202  rotation. Together, bearing rollers  21  in combination with bearing races  25  and  27  make up the bearings  29  of the centrifugal pump which are provided for the purpose of supporting shaft  202  during rotation thereof.  
         [0052]    When the lubricant  13  is dispensed throughout chamber  201  by blades  8 , the lubricant makes it way through bearings  29  and also down auxiliary passageways, which may be present in some pumps and into chambers on both ends of chamber  201 . Once in auxiliary chambers, the lubricant is permitted to lubricate the bearing raceways, frames, and balls on all sides thereby improving performance. From auxiliary chambers, some of the lubricating fluid makes its way back into main chamber  201  through the gap between bearing races or frames  25  and  27 . However, some of the lubricant from annular auxiliary chambers makes its way back into main chamber  201  by way of passageways (not shown) disposed below outer bearing races  25 . Auxiliary passageways, auxiliary chambers, and passageways are designed so that the lubricating fluid makes its way through chambers and passageways due to the force of gravity and back into main misting chamber  201 .  
         [0053]    As will be discussed in detail below, main chamber  201  may, according to certain embodiments, be provided with an outlet and inlet in communication with an external lubricant reservoir. These are provided so that the lubricating fluid (e.g. oil) from chamber  201  may be circulated out of the pump, cooled and filtered in the external reservoir, and thereafter recirculated back into chamber  201  by way of the inlet (see FIGS. 3 and 4).  
         [0054]    Discussion will now be made of the specific structure and function of the dispenser  4  shown generally in FIG. 2 and shown in greater detail in FIGS. 5 a - 5   d . FIG. 5 a  is an end view illustrating the lubricant dispenser  4  of FIG. 2. In FIG. 2, pump shaft  202 , supporting band  6  and vane holder  9  are illustrated cross-sectionally, while the blade  8  is illustrated in an elevational manner. As shown, a plurality of dispensing members or blades  8  is attached to shaft  202  for rotation therewith by way of base support band  6 . Support band  6  is wrapped around and affixed to pump shaft  202  for rotation therewith. Support band  6  mounts a plurality of vane holders  9  extending radially outward therefrom. Vane holders  9  are provided for pivotally mounting the dispensing blades  8 . Each holder  9  includes a mounting base  9   a  through which the support band  6  passes and a pair of support legs  9   b  having an aperture defined therein for the purpose of receiving elongated support shaft or dowel  10  (see FIGS. 5 b  and  5   c ).  
         [0055]    With reference to FIGS. 5 b  and  5   c , the vane holder and mounting structure will now be described. The vane holder  9  is a u-shaped member having a base portion through which the band  6  passes and support legs  9   b  formed with an aperture. A spring insert  22  in the form of a u-shaped resilient member is disposed between the two support legs  9   b . The spring insert  22  is also formed with a pair of apertures that align with the apertures of the support legs  9   b . The dispensing blade  8  is fitted onto a bearing sleeve  20 , and the bearing sleeve  20  is aligned with the apertures of the support legs  9   b . The support shaft  10  passes through one support leg  9   b  then through the spring insert  22  and the bearing sleeve  20 , through the second end of the spring insert  22  and then through the second support leg  9   b . The shaft  10  is retained in place by a suitable fastener, preferably a retaining clip  12 .  
         [0056]    The spring insert  22  is designed to retain the vane holder  9  in place relative to the support band  6  via a friction-fit arrangement. With this arrangement, the vane holder  9  may be slid along the band  6  to a desired location where the holder  9  is retained in place using the friction-fit arrangement. Of course, other retention systems may be employed to selectively retain the vane holder  9  relative to the band  6 .  
         [0057]    Each blade  8  is free to pivot about the axis defined by the shaft  10  so that each blade  8  can pivot in either direction about the shaft  10  to which it is pivotally and movably attached. Because each blade  8  can pivot downward in either direction about 90° relative to its extended or “stand up” position (FIG. 5 a ), the lubricant dispenser  4  may be inserted into chamber  201  through the opening defined by bore  32 . This is advantageous in that a dispenser  4  may be inserted into chamber  201 , with the operating outer diameter of dispenser  4  (defined by the outer diameter of blades  8 ) being greater than the diameter of the opening through which the dispenser is originally fed. Typically, dispenser  4  will be inserted into chamber  11  with the shaft and bearings through the annular opening defined by hole or bore  32  in the pump housing.  
         [0058]    [0058]FIG. 5 d  is a sectional view taken along section line VI-VI of FIG. 5 b  showing the vane holder assembly of the dispensing element including the vane or blade  8 , vane holder  9 , bearing sleeve  20  and shaft  202 . As shown in FIG. 5 d , the blade  8  is formed to wrap around the bearing sleeve  20 .  
         [0059]    The blade(s)  8  in its operating position is caused to extend radially away from the center of shaft  202  due to the centrifugal force created by rotation of the shaft. In other words, each dispensing member or blade  8  is in the position of FIG. 5 d  when pump shaft  202  is caused to rotate during operation by the pump motor. However, as discussed above, because each blade  8  is pivotally mounted to holder  9 , during non-rotation of shaft  202 , the blades  8  on the upper side of the pump shaft flop or pivot downward about the axis defined by holder  9 . As illustrated by the arrow in FIG. 5 d , each blade  8  may pivot about the axis defined by shaft  10  about 90° in either direction from its illustrated operating position.  
         [0060]    Also illustrated in FIG. 5 a  are the two ends  70  of band  6 . Each end  70  are adapted to receive a fastener  73 , such as a locking fastener, bolt and corresponding nut or other retainer, for the purpose of securing band  6  around the external periphery of shaft  202 . In such a manner, support band  6  is wrapped around the outside of shaft  202 , with the two ends  70  of band  6  being secured to one another by way of fastener  73 . A corresponding nut may be provided on the end of fastener  73  for the purpose of maintaining support band  6  in a secured position affixed around the pump shaft for rotation therewith.  
         [0061]    It is also important to note, relative to FIGS. 5 a - 5   d , that during operation, the distal, or radially most outward, edge  80  of blades  8  is curved or arc-shaped. The curves of the edge  80  of blades  8  are formed so that, as shown in FIG. 5 a , if the blades were connected, the center of the resulting circle would be outside the center of shaft  202 . Also, it is edges  80  of blades  8  which slice into the lubricating fluid (below level  19 ) during rotation of shaft  202  thereby flinging or dispensing the fluid  13  throughout chamber  201  so as to lubricate the adjacent ball bearings. Due to the shape of the edges  80 , an intermediate portion  82  engages the lubricating fluid before the terminal ends  84 ,  85  of each blade  8 . It has been found that the prior art blade configuration causes the leading edge to strike the lubrication fluid during operation, and this prior art arrangement causes undesirable splashing or spraying of lubricating fluid. Because the blades  8  of this invention are designed to strike the lubricating fluid at an intermediate portion  82  and not the leading edge, the undesirable splashing or spraying is substantially reduced or eliminated.  
         [0062]    [0062]FIG. 3 is an alternate view of the pump shown in FIG. 2 showing the external oil reservoir  100  with fins  101 , adjustable oil level arrow  102 , adjustable support screws  104 , and cover with desiccant chamber  106  (see also FIGS. 6 a - 6   c ). The present invention uniquely provides a kit assembly that may be retrofit onto an existing pump. To install the external reservoir to an existing pump, one simply removes the existing sight glass or constant level oiler from the side of the bearing frame. The reservoir  100  simply installs into the same port on the side of the bearing frame, and the reservoir  100  automatically adjusts the oil level downward so that the bearings are no longer flooded and not plowing through the lubricant.  
         [0063]    Once mounted to the pump bearing frame, the position of the oil level set point arrow  102  is set on the face of the reservoir  100  according to a predetermined position set by the manufacturing specifications for the pump. The adjustable support screws  104  are used to support the reservoir  100 . These adjustable support screws  104  function as mounting feet to alleviate stress on the connecting pipes leading to and from the reservoir  100 .  
         [0064]    [0064]FIG. 4 is a cross sectional end view taken along section line IV-IV of FIG. 3 showing the adjustable oil misting blade assembly  4  mounted on the shaft, as well as fittings  106 - 108 , tubing  109 - 110 , drain valve  112 , plugs, reservoir  100  with fins  101 , adjustable support screws  104 , filter  120  inside the reservoir  100 , and reservoir cover  130  with desiccant chamber  134 .  
         [0065]    The reservoir  100  shown in FIG. 4 provides a remote lubricant flow path that passes from the main lubricating chamber  201  through tubing  109  where it passes through filter  120  and is returned via tubing  110  to the lubricating chamber  201 . Desiccant chamber  134  is provided to remove water content from the air within chamber  201  and reservoir  100 . The desiccant chamber  134  includes a substance, such as calcium oxide, that has a high affinity for water and is used as a drying agent.  
         [0066]    One important aspect of this invention is the slide rule template used to measure the correct positioning of the components of the present invention. For example with reference to FIG. 7, with the shaft still mounted in the bearing frame, one can use the slide rule template  180  provided in the retrofit kit as follows: position the bearing frame/shaft assembly on a flat surface with the shaft  202  parallel to the surface, then position the slide rule vertically on the surface as shown. Next, move the vertical slide up or down until the arrow marked shaft centerline  181  is positioned exactly at the centerline of the shaft. Take note of the position of the slide template relative to the ruler printed on the template so that if the slide moves, it can be repositioned (fasten with tape if desired).  
         [0067]    Next, with reference to FIG. 8 move the slide rule template  180  to the side of the bearing frame outlet ‘o’ where the reservoir tubing  109  will be mounted (see FIG. 4), and locate the line  182  on the template corresponding to the size of the bearings in the pump. If the bearings are different sizes, the line corresponding to the largest of the two bearings (i.e. the lowest of the two lines on the template) is used. The best vertical position of the threaded hole in which the reservoir tubing  109  will be mounted will be at height indicated according to the bearing size in the pump. If the vertical position of the existing hole for tubing  109  differs by more than ¼″, optimal performance can be achieved by drilling and tapping a new hole (¼″-18 NPT) at the preferred height (although not required) as close as possible to half way between the two bearings in the pump. The preferred height as indicated on the template  180  is where the oil level will be set later regardless of the actual position of the mounting hole for the reservoir.  
         [0068]    Next, with reference to FIG. 9, set the position of the “oil level set point arrow”  102  in FIG. 3 on the face of the reservoir  100 . With the shaft mounted in the bearing frame, use the slide rule template  180  provided in the kit as follows: position the bearing frame/shaft assembly on a flat surface with the shaft parallel to the surface. Position the slide rule vertically on the surface as shown. Move the vertical slide  180   a  up or down until the arrow marked shaft centerline  181  is positioned exactly at the centerline of the shaft  202 . Take note of the position of the slide  180   a  relative to the ruler printed on the template so that if the slide moves, it can be repositioned (fasten with tape if desired). Move the slide rule template close to the face of the reservoir where the oil level set point arrow  102  is located. Locate the line on the template corresponding to the size of the bearings in the pump. If the bearings are different sizes, use the line corresponding to the largest of the two bearings (i.e. the lowest of the tow lines on the template). Fasten the arrow to the face of the reservoir so that the point of the arrow is at the same height as the line corresponding to the bearing size. Install and adjust as necessary the height of the adjustment bolts  104  (see FIGS. 3 and 4). These bolts  104  only function as “mounting feet” for the reservoir to alleviate the weight of the reservoir from pulling down on the connection pipe. Adjust these bolts accordingly so as not to apply stress to the connection pipe.  
         [0069]    [0069]FIGS. 10 a  and  10   b  illustrate how the slide rule template  180  can alternatively be used to measure the proper size of the blade  8  of the dispenser  4 . The cut line  184  shows where the blades should be trimmed to a maximum diameter.  
         [0070]    Numerous advantages are provided by the aforementioned lubrication system for pumps and other rotating components. The invention allows the bearings to operate as much as 50-60° F. cooler by eliminating the viscous drag and plowing effect created by submerged bearings. The invention reduces power consumption slightly by reducing viscous drag that was converted to non-productive heat. The invention adds reserve oil capacity (in most cases doubles) to the pump. The invention continuously filters the oil as it circulates. The invention continuously removes water from the air in the bearing frame and reservoir. The invention adds cooling capacity to the system, both by the external reservoir and by utilizing the entire internal surface of the bearing frame as a heat sink. The invention continuously coats the internals of the bearing frame with oil to minimize any oxidation of iron and steel parts. Because bearing and oil operating temperatures are significantly lower, condensate formation is minimized due to lower differential temperatures. The system allows the use of a closed frame without vents or breathers, which are a prime source for moisture infiltration. When combined with bearing isolators (labyrinth oil seals) which are very effective at keeping oil in, and keeping contaminants out, at the shaft level, the invention makes a significant contribution to any plant program aimed at productivity and cost reduction.  
         [0071]    While the foregoing invention has been shown and described with reference to the preferred embodiments, it will be understood by those of skill in the art that various changes in form and detail may be made therein without departing from the spirit and scope of the instant invention.