Abstract:
A method for monitoring a bearing is disclosed. The method involves positioning a non-contacting bearing isolator adjacent a bearing on a piece of rotating equipment so that at least one operating parameter of said bearing is communicated to said bearing isolator; and, positioning an energy detector within range of said bearing isolator so that said energy detector is able to monitor said at least one operating parameter of said bearing by detecting at least one operating parameter of said bearing isolator.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     This application is a continuation of U.S. patent application Ser. No. 11/881,881 filed on Jul. 30, 2007 now abandoned, from which Applicant claims priority, and which prior application claimed priority from Provisional U.S. Pat. App. Ser. No. 60/842,718 filed on Sep. 7, 2006, all of which are incorporated by reference herein. 
    
    
     FIELD OF INVENTION 
     The present invention relates to both an improved bearing isolator that may be used alone or in combination with a conveyor roller type arrangement for improved contaminant exclusion in industrial applications and an improved monitoring method and system allowed by said apparatus. When the improved bearing isolator is used in combination with a conveyor roller, the exterior end face of the improved bearing isolator provides an indicator surface for monitoring. 
     STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT 
     No federal funds were used to develop or create the invention disclosed and described in the patent application. 
     REFERENCE TO SEQUENCE LISTING, A TABLE, OR A COMPUTER PROGRAM LISTING COMPACT DISK APPENDIX 
     Not Applicable 
     BACKGROUND OF THE INVENTION 
     Conveyors all over the world are in constant use handling a wide variety of usually solid materials that are in need of being transferred from one point to another. Materials include, but are not limited to, coal, sand, rocks, steeped corn, packages, and mined ores. Alternative means to conveyors for transporting solid materials include trucks or other vehicles, or conversion of the material to a slurry so that it may be pumped from one place to another. 
     Conveyors handling bulk solids such as coal or ores can extend across mountainous terrain, over roads and streams for many miles. These conveyors are made up of belts that are normally supported by three rollers positioned at the bottom and sides of the belt. One roller is usually horizontal and the two side rollers are at an angle of approximately 35 degrees from the horizontal plane. 
     Typically, the three rollers are supported by a frame that engages the shaft ends of the rollers (which shaft is generally concentric with the roller and of a slightly larger axial dimension than the roller) so as to keep the roller assemblies in line and in position for accommodating the belt and its load. The frames are normally positioned three feet or one meter from each other in a line, which equates to approximately 1,760 sets of three rollers per mile of conveyor run, or 1,100 sets per kilometer. Accounting for two bearing and bearing seals per roller, this approximation yields 10,560 bearings and bearing seals per mile of conveyor. Any one of the seals or bearings could severely degrade and cause the system to shut down. A stalled roller may put undue strain on the belt being used for holding the product, and when a bearing grinds to a halt, the resulting heat produced from the increased friction may initiate combustion of various combustible materials in and around the bearing location. 
     Rollers of the prior art are normally fitted with sealed bearings at either end. Sealed bearings have integral rubber sealing components on either side of the inner and outer race that contact the inner race in a frictional manner, often with a lubricant packed between the inner and outer races. At the axial extremity of the roller, rubber or composite seals are applied so as to protect the sealed bearings from dust, dirt, silicon or other foreign matter that may contaminate the bearings and their lubricant. The seals, so described, are of the contacting type and frictionally engaged with the stationary component of the roller, which is usually the stationary shaft, or the stationary seal component. As soon as wear occurs, sealing efficiency degrades so as to be completely ineffective. Reliability of the system suffers because of the very large number (as calculated above) of wearing and vulnerable components. The prior art contacting seals are prone to wear and are energy consumptive because of the frictional drag inherent in their design. This frictional drag increases the operating costs through increased maintenance and electrical energy costs; therefore, reliability and energy consumption must be addressed and are two of the integral and useful subjects of this invention.  FIG. 1A  presents an exploded view of a conveyor roller bearing arrangement known to those practiced in the art. 
     As taught by the prior art, conveyor rollers of this type are particularly suited to conveyors that operate in very difficult conditions. Typical environmentally difficult applications are mines, cement works, coal-fired electric utilities and dock installations, among others. The roller sealing system, as taught by the prior art, is designed to solve problems associated with the environmental challenges of dust, dirt, water, or other contaminants, low and high temperatures, or applications where a large temperature imbalance between day and night may be present. The principal task of the seals of the prior art used in conveyor rollers is to protect the primary bearing from harmful elements that may interfere with the primary bearing or impinge from the outside or the inside of the conveyor roller system and damage or shorten the useable life of the primary bearing. As found by applicant, the prior art fails to achieve the objective. 
     Given the large numbers of conveyor rollers typically installed and used, it is difficult for operators to be alerted to a primary bearing failure until a secondary event occurs. Many times, this secondary event is initiation of a smoldering fire or smoke from conveyed materials deposited in close proximity to the conveyor due to the heat often generated from primary bearing failure. This heat generation that may cause a smoldering fire typically occurs from ferrous metal to ferrous metal contact, as does sparking, both of which are allowed by primary bearing failure. The typical bearing seal is hidden from external inspection/view and is made of plastic so that it does not only conduct heat poorly but is prone to fail upon rapid heating from either combustion or ferrous metal to ferrous metal contact. As is well known to those practiced in the art, ferrous metal to ferrous metal contact (rubbing) may be severe enough to raise the metal temperatures to 2500 degrees Fahrenheit (1370 degrees Celsius) and result in partial or full melting of the primary bearing and the destruction thereof. Furthermore, this source of heat may support ignition of conveyed materials, such as the carbon in coal, which has a temperature of ignition in the range of 765 degrees Fahrenheit (407 degrees Celsius), in contact with or exposed to the primary bearing. 
     SUMMARY OF THE INVENTION 
     It is an objective of the present art to claim and disclose an improvement on the prior art and present viable solutions to the disadvantages of the prior art, including increased reliability of and reduction of energy consumed by roller assemblies and conveyor systems of the prior art. 
     It is a further objective of the present art to claim and disclose a method of monitoring the improved bearing isolator in all its embodiments. In this method, the improved bearing isolator may be used as an indicator in connection with a detector system that collects operational data useful in operating the equipment associated with the improved bearing isolator and cooperatively engaged with the improved bearing isolator. The disclosed method may also be used for predictive and preventative maintenance of the improved bearing isolator and any equipment associated or systematically engaged therewith. 
     One embodiment of the present invention as illustrated in  FIGS. 3 ,  4 A- 4 C,  6 , and  7  is a non-contacting, non-wearing, and non-energy consumptive sealing system that provides adequate protection for primary bearings as may be found in the prior art and particularly those primary bearings used in combination with conveyor roller bearings as found in the prior art. In a first embodiment of the present invention, the bearing seals of the conveyor rollers of the prior art may be replaced with the present art. In this first embodiment, the improved bearing isolator is a substitute for lube containment shields, and the improved bearing isolator will not wear or degrade in use. Since the roller housing rotates around a stationary shaft, high quality and long lasting grease lubricant centrifugates (i.e., migrates through and by centrifugal acceleration) during rotation to the inner track of the outer race of the primary bearing and interacts with the rolling components of the primary bearings. In the embodiments disclosed, at all times there will be no frictional engagement with the sealing components or the improved bearing isolator assemblies. 
     The new conveyor roller and improved bearing isolator have numerous advantages over the prior art, including substantially lower friction operation. This reduction in friction lowers energy required to operate a conveyor. Another advantage is improved contaminant exclusion. The improved bearing isolator portion of the conveyor roller has a massive intermediate annular chamber that accumulates granular material (or other external contaminants) attempting to infiltrate the primary bearing of the conveyor roller. This internal intermediate chamber limits the passage of the granular material that is present in the conveyed loads into the primary bearing. The design as disclosed is not limited to a single intermediate annular chamber, but extends to conveyor rollers and improved bearing isolators with a plurality of intermediate annular chambers since it is possible to position more than one of the intermediate annular chambers within the improved bearing isolator. The intermediate annular chamber(s) interrupt the interface passage between the stationary and rotating elements of the improved bearing isolator and have specifically designed entrance and exit locations for contaminants. In one embodiment, the interface passage entrance to the intermediate annular chamber is at the upper quartile of the intermediate annular chamber. The interface passage may exit the intermediate annular chamber at the lower quartile of the intermediate annular chamber. As a result, passage of the contaminants into the primary bearing will be counter to the flow of possible contaminants (which is inward to outward) because of the centrifugal force due to the orientation of increasing diameters in the improved bearing isolator. When handling dry powders, the intermediate chambers will not have a hydraulic ram effect as would be the case with liquids. Other embodiments exist in which the interface passage may exit the intermediate annular chamber in another area of the intermediate annular chamber, and the specific orientation of the interface passage with respect to the intermediate annular chamber in no way limits the scope of the present invention. 
     The improved bearing isolator portion of the conveyor roller is designed with a long and tortuous passage in the interface between the stationary (stator) and rotating (rotor) components of the bearing isolation seal, which is the subject of this disclosure.  FIGS. 3A-3D  provide simple illustrations of various orientations of entrance and exit locations to and from the intermediate chamber that may be employed in the present invention without departure from the spirit and intent of the invention. Further variations and modifications on the entrance and exit locations to and from the intermediate chamber and to the passage in the interface between the stator and rotor will occur to those of ordinary skill in the art without departure from the spirit and scope of the invention. 
     As shown in the accompanying figures, the interface between the stator and the rotor may be selected so that various portions of the interface between the stator and rotor form a circumferential annular channel transverse the axial direction of the shaft and other portions of the interface form a circumferential annular channel parallel the axial direction of the shaft. 
     The passage between the stator and the rotor will include a series of ninety degree turns that will prohibit free flow of the possible contaminants into the bearing environment. The embodiment of the present invention illustrated in  FIGS. 3 ,  4 A- 4 C,  6 , and  7  has nine of the prescribed ninety degree turns. It is contemplated more or less turns may be incorporated in the design as disclosed as necessitated by operating conditions without departing from the spirit or intent of the present art. During operation, the intermediate annular chamber may be filled with long-lasting, preferably synthetic, grease, as known to those practiced in the art. As is known to those skilled in the art, the grease may be filled at the time of initial assembly or after initial assembly by an external zerk fitting employing a passage from the external surface of the stator into the intermediate annular chamber. 
     In most embodiments, the passage between the rotor and stator will have constantly increasing diameters from the inside of the improved bearing isolator to the outside of the improved bearing isolator to discourage flow of granular material or contaminants in the direction towards the primary bearing. That is, the design as disclosed promotes outward contaminant flow as previously described. As disclosed, the end face angle relative to the horizontal may be steeper and more severe than the angle of repose that exists with the conveyed material. 
     The entrance to the exterior interface passage may be angled with respect to the axis of the conveyor roller so as to deflect water spray and to not offer a surface for direct impingement of external contaminants to the exterior interface passage entrance. The angled end face also increases surface area available for thermal detection by external monitoring systems, as will be described in further detail herein. 
     The rotor and stator may be unitized by a VBX ring or other snap lock type design as is the method of Inpro/Seal prior art as claimed and disclosed in U.S. Pat. No. 6,419,233. The design as disclosed will accommodate arrangement and combination of the improved conveyor roller and/or improved bearing isolator with double-shielded bearings rather than sealed bearings for superior and long-lasting lubrication of the bearings. This is an advantage because shielded bearings do not experience frictional engagement between the inner and outer races of the bearing, which increases operating efficiencies and reduces energy consumption during operation. 
     As disclosed herein, the improved bearing isolator is a further improvement upon the prior art conveyor roller bearing seals because the improved bearing isolator may act as a secondary sleeve or journal bearing assembly to the primary bearing in the event the primary rolling element bearing should fail and collapse. The angled exterior end face of the improved bearing isolator increases internal axial surface area available between the rotor and stator of the conveyor roller bearing seal. The improved bearing isolator will serve as an emergency sleeve-type bearing for a limited time and prevent overheating of the failed primary bearing. However, unmonitored operation in this mode is not recommended, and in the event of primary bearing failure it is recommended that the primary bearing be replaced as soon as possible. During temporary operation as an emergency sleeve or journal bearing, the ensuing heat conducted from the primary bearing to the improved bearing isolator may liquefy the stored grease; thereby allowing the grease to lubricate the rubbing surfaces along the interface passage of the improved bearing isolator. This lubrication during emergency operation should greatly extend the useful life of the improved bearing isolator. Again, unmonitored operation in this mode is not recommended. 
     During the emergency-type service of the improved bearing isolator described above, less heat is produced than otherwise would occur using conveyor bearing seals of the prior art because the improved bearing isolator acts as a secondary bearing, thereby reducing the frictional load on the primary bearing and prohibiting heat produced from ferrous metal to ferrous metal contact. Furthermore, the heat produced by the improved bearing isolator, when acting as an emergency sleeve bearing, will be conducted to the outer portions of the improved bearing isolator and the exterior of the conveyor itself, which is typically positioned at a location exterior to the primary bearing and conveyor roller. Conduction to the outer surfaces will allow some heat dissipation caused by primary bearing failure and may provide operators with a means for earlier detection of abnormal operating conditions. If the intermediate annular chamber has been filled with grease, liquefaction of the grease will also dissipate a portion of the heat produced. This heat conduction occurs because the improved bearing isolator is composed of bronze rather than plastic, as is typical with most conveyor bearing seals. 
     A further advantage of the present art is that if the improved bearing isolator is made from a non-ferrous metal, such as bronze, and therefore contact between the improved bearing isolator and ferrous elements such as ferrous components of the conveyor roller, the primary bearings, or the roller frame will not produce an ignition source (i.e., no sparks will result), which inhibits combustion. As is well known to those practiced in the arts, primary bearing failure in an environment with combustible conveyed materials, such as coal, can lead to ignition and fire. It should be noted that although bronze is a preferred non-ferrous metal, in other embodiments of the present art, non-sparking metals other than bronze may be chosen for their non-ferrous qualities such as gold, silver, nickel, copper, and combinations thereof. 
     Finally, it is another advantage of the invention and the intent of the inventor to disclose and claim a method of utilizing a monitoring system, which are well known to those practiced in the art, in combination with the improved bearing isolator and improved conveyor roller arrangement. In the method, the monitoring system is located externally of the conveyor and any elements thereof, and upon installation, the failure of the primary bearing may be detected based on the increased temperature of the improved bearing isolator, and an alert may be observed by the conveyor operator before an unsafe situation arises. During service as an emergency secondary bearing, the improved bearing isolator may also provide notice of the failure of the primary bearing. The improved bearing isolator angled end face serves as an improved indicator of the emergency situation using any number of monitoring means, including thermal detection by external monitoring systems. Thermal detection means could be as simple as direct operator inspection of the improved bearing isolator (i.e., physical contact with the improved bearing isolator to detect whether the external surface temperature of the improved bearing isolator has increased), or use by an operator of a hand-held thermal imager or infrared (“IR”) camera, which are well known to those in the art as found in products offered by Fluke Corporation and FLIR Systems, respectively, and as taught by U.S. Patent Applications having publication number 20060152737 for “Method and Apparatus for Electronically Generating an Outline Indicating the Size of an Energy Zone Imaged onto the IR Detector of a Radiometer” and publication number 20040196372 for “IR Camera,” both of which are incorporated by reference herein. 
     Another embodiment as disclosed and claimed herein provides for a networked system of at least one thermal scanner or IR camera positioned around the conveyer system to pan and scan (i.e., continually move back and forth in a predetermined, two- or three-dimensional path) the operational areas and detect thermal changes at the angled exterior end face areas of the improved bearing isolator, which serve as operation indicator surfaces. 
     In another embodiment of the present disclosure, the improved bearing isolator may be fitted with a transducer port or electrode for interconnectivity with a digital linear heat detection system as well known to those in the art and found in U.S. Pat. No. 4,647,710 issued to Davis for “Heat Sensitive Cable and Method of Making Same,” which is incorporated herein by reference. 
    
    
     
       BRIEF DESCRIPTION OF THE FIGURES 
         FIG. 1  is a sectional view of a conveyor roller and primary bearing assembly as found in the prior art. 
         FIG. 1A  is an exploded, side view of the conveyor roller and primary bearing assembly of the prior art shown in  FIG. 1 . 
         FIG. 2  is a side view of another conveyor roller and bearing assembly as found in the prior art. 
         FIG. 3  is a cross-sectional view of a first embodiment of the improved bearing isolator of the present art. 
         FIG. 3A  provides a simplified view of the orientation of the interface passage shown in  FIG. 3 . 
         FIG. 3B  provides a simplified view of another orientation of the interface passage shown in  FIG. 3 . 
         FIG. 3C  provides a simplified view of another orientation of the interface passage shown in  FIG. 3 . 
         FIG. 3D  provides a simplified view of another orientation of the interface passage shown in  FIG. 3 . 
         FIG. 4A  provides a side view of the improved bearing isolator disclosed herein. 
         FIG. 4B  provides a front view of the improved bearing isolator disclosed herein. 
         FIG. 4C  provides a perspective, cut-away view of the improved bearing isolator disclosed herein. 
         FIG. 5A  is a side view of a primary bearing element with seals. 
         FIG. 5B  is a side view of a semi-shielded primary bearing element. 
         FIG. 5C  is a side view of a fully-shielded primary bearing element. 
         FIG. 6  provides a sectional view of another embodiment of the improved bearing isolator as disclosed herein. 
         FIG. 7  provides a sectional view of another embodiment of the improved bearing isolator as disclosed, wherein the available axial engagement surface between the rotor and the stator has been enlarged. 
         FIG. 8  provides an exploded view of the arrangement of the improved bearing isolator as disclosed herein for use in combination with a conveyor roller. 
         FIG. 9  is a perspective view of a thermal scanner as taught by the prior art that may be used in combination with the present art for an improved method of monitoring bearing systems. 
         FIG. 10  is a perspective view of an IR camera as taught by the prior art. 
         FIG. 11  is a perspective view of an IR camera as taught by the prior art arranged in combination with the present art for an improved method of monitoring bearing systems. 
         FIG. 12  is a perspective view of an IR camera as taught by the prior art arranged in combination with the present art to facilitate monitoring a plurality of primary bearings. 
       
         
           
                 
                 
                 
               
             
                 
                     
                     
                 
                 
                     
                   ELEMENT DESCRIPTION 
                   ELEMENT NUMBER 
                 
                 
                     
                     
                 
               
               
                 
                     
                   Conveyor roller shell 
                    1 
                 
                 
                     
                   Shaft 
                    2 
                 
                 
                     
                   Bearing Housing 
                    3 
                 
                 
                     
                   Inner Seal 
                    4 
                 
                 
                     
                   Primary Bearing 
                    5 
                 
                 
                     
                   Labyrinth Seal 
                    6 
                 
                 
                     
                   Circlip 
                    7 
                 
                 
                     
                   Cover 
                    8A 
                 
                 
                     
                   Stone guard 
                    8B 
                 
                 
                     
                   Weather seal 
                    9 
                 
                 
                     
                   Improved bearing isolator 
                   12 
                 
                 
                     
                   Stator 
                   13 
                 
                 
                     
                   Rotor 
                   14 
                 
                 
                     
                   Stator exterior end face 
                   15 
                 
                 
                     
                   Rotor interior end face 
                   16 
                 
                 
                     
                   Exterior interface passage 
                   17 
                 
                 
                     
                   Interior interface passage 
                   18 
                 
                 
                     
                   Intermediate annular chamber 
                   19 
                 
                 
                     
                   Immediate interface passage 
                   20 
                 
                 
                     
                   Rotor uniting ring groove 
                   21 
                 
                 
                     
                   Stator unitizing ring groove 
                   22 
                 
                 
                     
                   O-ring 
                   23 
                 
                 
                     
                   Rotor O-ring groove 
                   24 
                 
                 
                     
                   First stator O-ring groove 
                   25 
                 
                 
                     
                   Axial engagement surface area 
                   26 
                 
                 
                     
                   Second stator O-ring groove 
                   27 
                 
                 
                     
                   Ramped shoulder 
                   28 
                 
                 
                     
                   Axial interface passage 
                   29 
                 
                 
                     
                   Inner side of stator 
                   30 
                 
                 
                     
                   Inner side of rotor 
                   31 
                 
                 
                     
                   Unitizing ring 
                   32 
                 
                 
                     
                   Inner bearing race 
                   35 
                 
                 
                     
                   Outer bearing race 
                   36 
                 
                 
                     
                   Primary bearing shield 
                   38 
                 
                 
                     
                   Primary bearing seal 
                   39 
                 
                 
                     
                   Conveyor roller 
                   40 
                 
                 
                     
                   Polyurethane structure 
                   41 
                 
                 
                     
                   Thermal scanner 
                   42 
                 
                 
                     
                   IR camera 
                   43 
                 
                 
                     
                   Sensor port 
                   44 
                 
                 
                     
                   Grease zerk 
                   45 
                 
                 
                     
                   Grease passage 
                   46 
                 
                 
                     
                   Line of sight 
                   48 
                 
                 
                     
                     
                 
               
            
           
         
       
     
    
    
     DETAILED DESCRIPTION 
       FIGS. 1 and 1A  illustrate the prior art as taught by U.S. Pat. No. 6,802,410 issued to Dyson et al. for “Conveyor Roller Bearing Housing,” which is incorporated by reference herein. 
     There are two principal sections shown in  FIGS. 1 and 1A  of the prior art bearing assembly; one external and one internal. The external section is comprised of a cover  8 A and stone guard  8 B. As taught by the prior art, the design of the cover  8 A and stone guard  8 B and the shape of the bearing housing  3 , are intended to be self-cleaning when rotating (i.e., centrifugally expel all pollutants). Applicant has not found this to be the case. 
     As illustrated in  FIG. 1 and 1A , the internal section is typically comprised of a triple lip labyrinth seal  6  (sometimes referred to as a lip ring), often made of nylon PA6, which is greased to give further primary bearing  5  protection. In other applications, the labyrinth seal  6  is made from soft, anti-abrasive rubber with a large contact surface that provides an ineffective hermetic seal, which thereby reduces the working life of the seal. Behind the primary bearing  5  is an inner seal  4 , also composed of nylon PA6, to provide a grease reservoir and retain the grease near to the primary bearing  5  fixed to the shaft  2  even when there is a depression due to an abrupt change in temperature (which results in a pumping effect). This inner seal  4  is also intended to mitigate the eventual formation of condensation on, and oxidation of the shaft  2  and/or primary bearing  5 , which normally takes place inside the tube-like structure of the conveyor roller shell  1  due to failure of the bearing seal arrangement. The seal locking system is provided for by circlips  7 , which are also known as a snap rings by those practiced in the art. 
       FIG. 2  illustrates another conveyor roller  40 , shaft  2 , and primary bearing  5  combination as taught by the prior art. This combination suffers from similar weaknesses as the configuration shown in  FIGS. 1 and 1A . In the embodiment shown in  FIG. 2 , the primary bearing  5  is of the sealed type, and as with the embodiment shown in  FIGS. 1 and 1A , the primary bearing  5  is positioned within the conveyor roller  40 , with the outer bearing race  36  secured to the bearing housing  3  and the inner bearing race  35  secured the shaft  2 . The primary bearing  5  is protected from exterior contaminants with a polyurethane structure  41 . In the event of deterioration or seizing of the primary bearing  5 , which is a common problem in most applications using conveyors, the heat produced from increased friction will rapidly degrade the polyurethane structure  41 , thereby increasing the potential for ferrous metal to metal contact between the primary bearing  5 , shaft  2 , and conveyor roller  40 . The increase in potential for ferrous metal to metal contact promotes spark production, creating a potentially dangerous situation. 
       FIG. 3  presents an embodiment of the present art. The primary bearing  5  is secured to the conveyor roller  40  and the shaft  2  in the same manner as are the prior art embodiments shown in  FIGS. 1-2 , or any other method known to those skilled in the art. For example, the present design as disclosed may be installed with a blunt, wide area set screw for maximum engagement with the surface of the shaft  2  to prevent and limit axial or rotational movement of the improved bearing isolator  12  or conveyor roller  40  with respect to the shaft. Furthermore, a hardened point set screw may be used to dimple engage the shaft  2  for assembly of the shaft  2  onto the frame (not shown) supporting the conveyor roller  40 . In the embodiment shown in  FIG. 3 , the external entrance to the exterior interface passage  17  leading to the intermediate annular chamber  19  is parallel with the axial dimension of the shaft  2  and positioned nearly perpendicular to the exterior of the stator face  15 . 
     In the embodiment shown in  FIG. 3 , the stator exterior end face  15  is angled with respect to the radial dimension of the shaft  2 . The improved bearing isolator  12  is mounted on the shaft  2  axially distal from the primary bearing  5  in the conveyor roller  40 , and is designed with a long and tortuous passage in the exterior interface passage  17 , interior interface passage  18 , and immediate interface passage  20  between the stator  13  (non-rotating portion of the improved bearing isolator  12 ) and rotor  14  (rotating portion of the improved bearing isolator  12 ), which passages cooperate to form a non-contacting labyrinth seal. The improved bearing isolator  12  shown in  FIGS. 3 ,  4 A-C,  6 ,  7 , and  8  is a frictionless, non-contacting improved bearing isolator  12 . That is, the rotor  14  rotates relative to the stator  13 , but each interface between the stator  13  and the rotor  14  maintains a predetermined clearance under normal operating conditions. As shown in  FIGS. 3 ,  4 C,  6 , and  7 , the exterior interface passage  17 , interior interface passage  18 , and immediate interface passage  20  may have many angles and turns of varying orientation. Subsequently, the specific orientation of the angles or turns in the exterior interface passage  17 , interior interface passage  18 , intermediate annular channel  19 , and immediate interface passage  20  in any particularly embodiment in no way limits the scope of the present invention. Furthermore, the improved bearing isolator  12  may be fashioned so that the external entrance to the exterior interface passage  17  and the portion of the exterior interface passage  17  adjacent the intermediate annular chamber  19 , the portion of the immediate interface passage  20  adjacent the shaft  2  and the portion of the immediate interface passage  20  adjacent the unitizing ring  32 , and the portion of the interior interface passage  18  adjacent the unitizing ring  32  and the portion of the interior interface passage  18  adjacent the intermediate annular chamber  19  are orientated along different angles with respect to the shaft  2  than the particular angles pictured herein without departing from the spirit and scope of the present invention. 
     As shown at  FIGS. 3 ,  4 C,  6 , and  7 , the stator  13  is affixed to the shaft  2  by at least one, and preferably a plurality, of O-rings  23  fit into first and second stator O-ring grooves  25  and  27 , respectively. Those practiced in the art will appreciate that other means of affixation may be used without departure from the spirit and intent of this disclosure. Sealing qualities of the improved bearing isolator  12  during rotation of the shaft  2  and rotor  14  and at rest thereof may be further improved by insertion of unitizing ring  32  interrupting the interior interface passage  18  at a location between the intermediate annular chamber  19  and the shaft  2 . At rest, the unitizing ring  32  seats in the stator unitizing ring groove  22  to seal the exterior interface passage  17 , interior interface passage  18 , and intermediate annular chamber  19  from the shaft  2  and immediate interface passage  20 . During rotation, the unitizing ring  32  expands to seat in rotor unitizing ring groove  21 , allowing contaminants in the interior interface passage  18 , intermediate annular chamber  19 , and/or exterior interface passage  17  to centrifugate (due to a number of increasing diameters in the radial dimension in the elements of the improved bearing isolator  12 , which cause a pumping action in the direction of increasing diameters) towards the stator exterior end face  15  and out of the improved bearing isolator  12 . 
       FIGS. 3A-3D  provide simple illustrations of various orientations of entrance and/or exit locations (depending on whether the shaft  2  is stationary or rotating) to and from the intermediate annular chamber  19 . When the shaft  2  is rotating, the exterior interface passage  17  serves as an exit from the intermediate annular chamber  19  for substances located between the exterior interface passage  17  and the unitizing ring  32 ; and the interior interface passage  18  serves as an entrance to the intermediate annular chamber  19  for such substances. When the shaft  2  is stationary, the interior interface passage  18  serves as an exit from the intermediate annular chamber  19  and the exterior interface passage  17  serves as an entrance into the intermediate annular chamber  19 . These several orientations may be employed in the present disclosure without departure from the spirit and intent of the invention. Further modifications and variations to the entrances/exits described and disclosed herein will occur to those skilled in the art without departing from the spirit and scope of the present invention. 
       FIG. 3A  illustrates an exterior interface passage  17  communicating with the intermediate annular chamber  19  in the first quartile of the intermediate annular chamber  19 . At the junction of the intermediate annular chamber  19  and the exterior interface passage  17 , the exterior interface passage  17  is parallel with the axis of the shaft  2 .  FIG. 3A  also illustrates the interior interface passage  18  junction with the intermediate annular chamber  19 , and further shows that junction may be positioned at the fourth quartile of the intermediate annular chamber  19 . 
       FIG. 3B  illustrates an exterior interface passage  17  communicating with the intermediate annular chamber  19  in the first quartile of the intermediate annular chamber  19 . At the junction of the intermediate annular chamber  19  and the exterior interface passage  17 , the exterior interface passage  17  is parallel with the axis of the shaft  2 , as it was in the embodiment shown in  FIG. 3A .  FIG. 3B  also illustrates the interior interface passage  18  junction with the intermediate annular chamber  19 , and shows that junction positioned at the third quartile of the intermediate annular chamber  19 . 
       FIG. 3C  illustrates an exterior interface passage  17  communicating with the intermediate annular chamber  19  in the first quartile of the intermediate annular chamber  19 . At the junction of the intermediate annular chamber  19  and the exterior interface passage  17 , the exterior interface passage  17  is oriented transversely from the axis of the shaft  2 .  FIG. 3C  also illustrates the interior interface passage  18  junction with the intermediate annular chamber  19 , and shows that junction positioned at the third quartile of the intermediate annular chamber  19 . 
       FIG. 3D  illustrates an exterior interface passage  17  communicating with the intermediate annular chamber  19  between the first and fourth quartiles of the intermediate annular chamber  19 . At the junction of the intermediate annular chamber  19  and the exterior interface passage  17 , the exterior interface passage  17  is oriented transversely from the axis of the shaft  2 .  FIG. 3D  also illustrates the interior interface passage  18  junction with the intermediate annular chamber  19 , and shows that junction positioned between the first and fourth quartiles of the intermediate annular chamber  19  and oriented transversely from the axis of the shaft  2 . 
     As illustrated in  FIGS. 6 and 7 , the improved bearing isolator  12  is designed for sealing engagement between a shaft  2  and a bearing housing  3 , and as noted previously, comprises a stator  13  and rotor  14 . In this embodiment shown in  FIGS. 3 ,  4 A-C,  6 , and  7  both the stator  13  and the rotor  14  surround the shaft  2 . The rotor  14  is interference fit (sometimes referred to as a press fit) within a portion of the bearing housing  3  in the conveyor roller shell  1 . The rotor  14  may be press fitted into the bearing housing  3  adjacent and axially distal from the primary bearing  5 , as indicated in the embodiment shown in  FIG. 8 . Alternatively, in an embodiment not pictured herein, the rotor  14  could press fit into a separate portion of the conveyor roller shell  1  axially distal of the primary bearing  5  or other structure of the conveyor roller  40  located axially distal of the primary bearing  5  adapted to receive the rotor  14 . An O-ring  23  seated in the rotor O-ring groove  24  in the periphery of the rotor  14  serves as a gasket, which seals the rotor interior end face  16  and the interior of the conveyor roller shell  1  from the exterior of the conveyor roller shell  1 . The O-ring seated in the rotor O-ring groove  24  also serves to affix the rotor  14  to the conveyor roller shell  1  so that the rotor  14  is rotatable therewith. Selection of a metal, preferably bronze instead of plastic, as used by the prior art, allows an improved, secure fit and seal between the improved bearing isolator  12  and conveyor roller shell  1 . 
     As illustrated in  FIGS. 3 ,  4 A-C,  6 , and  7 , the rotor  14  and stator  13  are cooperatively engaged and form an exterior interface passage  17 , interior interface passage  18 , intermediate annular chamber  19 , and an immediate interface passage  20 . The rotor  14  is designed for both engagement with (under certain operating conditions) and rotation within stator  13  at the exterior interface passage  17 , interior interface passage  18 , intermediate annular chamber  19 , and immediate interface passage. Under typical operating conditions, the stator  13  and the rotor  14  do not come in contact with each other. These elements also serve as a conduit for inwardly and outwardly flowing contaminants to meet at the intermediate annular chamber  19  for both collection and outward flow away from the intermediate annular chamber  19  upon rotation of the rotor  14 . Whether the contaminants are flowing inwardly or outwardly in an axial direction with respect to the primary bearing  5  will generally depend on whether the shaft  2  is rotating or stationary. When the shaft  2  is rotating, contaminants located in the exterior interface passage  17 , interior interface passage  18 , and intermediate annular chamber  19  will flow in an outwardly axial direction with respect to the primary bearing  5 , eventually exiting the improved bearing isolator  12  through the exterior interface passage  17  to an environment external to the improved bearing isolator  12 . When the shaft  2  is stationary, contaminants located in the exterior interface passage  17  will gather in the intermediate annular chamber  19 , and contaminants in the interior interface passage  18  will generally remain stationary due to the barrier the unitizing ring  32  creates to ingress of contaminants into the primary bearing  5  environment. Contaminants collected in the intermediate annular chamber  19 , in the interior interface passage  18 , and in the exterior interface passage  17  will be expelled from the improved bearing isolator  12  through the exterior interface passage  17  when the conveyor roller shell  1  (and subsequently, the rotor  14 ) is again put into a rotational state. 
       FIGS. 5A-5C  illustrate another operational feature of the present art.  FIG. 5A  is a side view of a sealed primary bearing  5  with contact seals. This type of primary bearing  5  is typically constructed with a Teflon™ or rubber lip seal that contacts the inner bearing race  35  and outer bearing race  36  of the primary bearing  5 . The primary bearing  5  is typically packed with heavy grease. The primary bearing seal  39  is fashioned to seal the primary bearing  5  from the external environment and retain the grease within the primary bearing  5 . Compared to semi-shielded bearings (shown in  FIG. 5B ) or fully-shielded bearings (shown in  FIG. 5C ), the frictional loses incurred by using sealed bearings are higher. The prior art conveyor rollers  40  as shown in  FIG. 1 ,  1 A and  2  typically employ sealed primary bearings  5  because the bearing seals of the prior art are do not adequately isolate the primary bearing  5  from contaminants. However, any type of prior art primary bearing  5  may be used with the improved bearing isolator  12  become of its superior isolation and contaminant exclusion capabilities. Therefore, the improved bearing isolator  12  reduces operating costs by reducing the instances of primary bearing  5  failure; and since the improved bearing isolator facilitates the use of primary bearings that require less energy to rotate because of fewer frictional losses, the energy costs are reduced. 
     The bearing sealing mechanism of the conveyor rollers  40  of the prior art may be replaced with the present art improved bearing isolator  12 . Replacing the prior art sealing mechanism typically used with the primary bearings  5  with improved bearing isolators  12  will provide lube containment shields that will not wear or degrade in use.  FIG. 5B  is a side view of a semi-shielded primary bearing  5  as may be used in the present art.  FIG. 5C  is a side view of a fully-shielded primary bearing  5  as may be used in the present art. Replacing the prior art primary bearing  5  lube retention and contaminant exclusion seals (or contact seals, as explained above) with lube retention shields (or improved bearing isolators  12 , as explained above) reduces system energy use through reduction in frictional losses. 
     The improved bearing isolator  12  is a further improvement upon the prior art conveyor roller bearing sealing mechanisms because the improved bearing isolator  12  may act as a secondary sleeve bearing assembly to the primary bearing  5  in the event the primary bearing  5  should fail and collapse. The angled stator exterior end face  15  of the improved bearing isolator  12  increases internal axial surface area available between the stator  13  and rotor  14  of the improved bearing isolator  12 , which reduces pressure between the stator  13  and rotor  14  when those elements are in contact with one another. However, as previously noted, under normal operating parameters respective elements of the stator  13  are not in contact with corresponding elements of the rotor  14 . The present improved bearing isolator  12  may serve as an emergency sleeve-type or journal bearing and serve to mitigate overheating of the failed primary bearing  5 . However, unmonitored operation in this mode is not recommended; and in the event of primary bearing  5  failure it is recommended that the primary bearing  5  be replaced as soon as possible. During temporary operation as an emergency sleeve or journal bearing, the ensuing heat conducted from the primary bearing  5  to the rotor interior end face  16  and through the improved bearing isolator  12 , or the heat generated between the stator  13  and rotor  14  may liquefy the grease stored in the improved bearing isolator  12 ; thereby allowing the grease to lubricate the surfaces between the stator  13  and rotor  14  that may come into contact due to primary bearing  5  failure. The lubrication of these surfaces during emergency operation should greatly extend the useful life of the improved bearing isolator  12  in the event of primary bearing  5  failure. Again, unmonitored operation in this mode is not recommended. 
       FIGS. 6 and 7  illustrate cross-sectional views of another embodiment of the improved bearing isolator  12  as disclosed herein. As illustrated in  FIGS. 6 and 7 , the external contaminant entrance to the exterior interface passage  17  may be axially positioned between an inner side of stator  31  and an inner side of rotor  30 , which entrance is referred to in this embodiment as the axial interface passage  29 . As illustrated in  FIGS. 6 and 7 , the axially positioned external contaminant entrance to the axial interface passage  29  is also positioned to face an axially opposite direction from the stator exterior end face  15 .  FIG. 6  demonstrates one embodiment in which the stator exterior end face  15  is modified to allow for a sensor to be placed therein via a sensor port  44 . The sensor may be of any type known to those skilled in the art for indicating an increase in temperature of the improved bearing isolator  12 , particularly during operation as an emergency sleeve bearing, as described above. Examples of sensors include electronic transducers, transmitters, and thermal sensing conductors or connectors as exemplified by U.S. Pat. No. 4,647,710, previously referenced herein. Sensors designed to monitor other operational parameters, such as vibrations, frequencies, or other pertinent information may also be inserted into a sensor port  44 , and the type of sensor in no way limits the scope of the present invention. Because the stator exterior end face  15  is typically not rotating when affixed to a non-rotating shaft  2 , the position of the sensor port  44  may be stationary, which allows for interconnection of the improved bearing isolators  12  in a network. This network facilitates automation and integration with a dedicated data processing system for a continuous or semi-continuous monitoring and alert system, which is not shown herein, but which systems and networks are known to those skilled in the art. The adjacent positioning of an improved bearing isolator  12  in relation to primary bearing  5  and the cooperative engagement of the rotor  14  with the bearing housing  3  (which is also cooperatively engaged with the primary bearing  5 ) promotes transmission of heat from the interior of the improved bearing isolator  12  to the exterior of the improved bearing isolator  12 , where the sensor may be located. 
       FIG. 7  provides a cross-sectional view of another embodiment of the improved bearing isolator  12  as disclosed herein wherein the available axial engagement surface area  26  between the stator  13  and rotor  14  has been further increased along the interior interface passage  18 . Again, the angled stator exterior end face  15  facilitates increased available axial engagement surface area  26  to support the improved bearing isolator  12  in the event of degradation of the primary bearing  5 . As with the other embodiments of the improved bearing isolator pictured and disclosed herein, in the embodiment shown in  FIG. 7 , during normal operation there should be no contact between the stator  13  and rotor  14  along the available axial engagement surface area  26  or any other interface portions between the stator  13  and the rotor  14 . When the improved bearing isolator  12  is used in combination with a primary bearing  5 , such as found in a conveyor roller  40 , the improved bearing isolator  12  may serve as an emergency sleeve or journal bearing as described above, and the increased available axial engagement surface area  26  may prolong the useful life of the improved bearing isolator  12  during such operation. During operation, the intermediate annular chamber  19  may be filled with long-lasting (preferably synthetic) grease, as known to those practiced in the art. As is also obvious to those skilled in the art, the grease may be filled at the time of initial assembly or after initial assembly of the improved bearing isolator  12  through the use of an external grease zerk  45  fitting employing a grease passage  46  in the stator  13  running from the stator exterior end face  15  into the intermediate annular chamber  19 . 
     In another embodiment not pictured herein, the improved bearing isolator  12 , as disclosed herein, may be used in combination with a vapor blocking ring component such as that described in U.S. Pat. No. 6,419,233, which is incorporated by reference herein, so as to prevent possible ingress of vapor contamination into the primary bearings  5 . 
       FIG. 8  provides an exploded view of one end of an arrangement of the improved bearing isolator  12  as disclosed herein for use in combination with a conveyor roller  40  wherein the improved bearing isolator  12  serves as both an improved bearing isolator  12  and end cap (similar to the function of the stone guard  8 A as taught by the prior art). An improved conveyor roller  40 , as shown in  FIG. 8 , has a conveyor roller shell  1  with first and second ends. A shaft  2  also having first and second ends is inserted through and surrounded by the conveyor roller shell  1 . As shown, a first bearing housing  3  is positioned within the conveyor roller shell  1  at the first end of the conveyor roller shell  1 . Although not shown, a second bearing housing  3  is also placed within the conveyor roller shell and positioned at the second end (opposite the first end) of the conveyor roller shell  1 , which is a mirror image of the arrangement shown in  FIG. 8  and configured in the same manner as that described for the end shown in  FIG. 8 . A primary bearing  5  is then inserted within the first bearing housing  3  and cooperatively affixed with the shaft  2  adjacent the first end of the shaft  2 . Although not shown, a second primary bearing  5  is then inserted within the second bearing housing  3  and also cooperatively engaged with the shaft  2  adjacent the second end of the shaft  2 . A first improved bearing isolator  12 , having primary bearing  5  isolation functionality, has a stator  13  (as explained in more detail above) affixed to the shaft  2  and a rotor  14  affixed to the conveyor roller shell  1 , both of which are positioned proximate the first end of the shaft  2 . The first improved bearing isolator  12  is positioned adjacent and axially outward with respect to the primary bearing  5 . In the embodiment shown in  FIG. 8 , the first improved bearing isolator  12  isolates the first primary bearing  5  from contaminant exposure but allows heat transmission from the primary bearing  5  to the stator interior end face  16 , through the improved bearing isolator  12  to the stator exterior end face  15 . A second improved bearing isolator  12 , not shown, also has a stator  13  affixed to the shaft  2  and a rotor affixed to the conveyor roller shell  1 , both of which are positioned proximate the second end of the shaft  2 . In the same manner as for the first end of the shaft  2 , the second primary bearing  5  is positioned axially inward of, and adjacent to, the second improved bearing isolator  12  to isolate the second primary bearing  5  from contaminant exposure, while allowing transmission of heat from the primary bearing  5  to the rotor interior end face  16 , through the improved bearing isolator  12  to the stator exterior end face  15 . Because the stator exterior end face  15  is external to the elements of the conveyor roller  40 , the temperature of the stator exterior end face  15  may easily be observed and detected. 
       FIG. 9  is a perspective view of a thermal scanner  42  as taught by the prior art, and  FIG. 10  is a view of an IR camera  43 , both of which may be used in combination with the present art for an improved method of monitoring bearing systems such as those claimed and disclosed herein. 
     One embodiment of a monitoring system and method would include first positioning a primary bearing  5  adjacent a bearing isolator  12  in a manner similar to that shown in  FIG. 8 , wherein the surface of the bearing isolator  12  that is not adjacent the primary bearing  5  is fashioned with a stator exterior end face  15  that may function as an indicator surface. In this method for monitoring, the adjacent arrangement of the primary bearing  5  and the bearing isolator  12  promotes thermal energy transfer from the primary bearing  5  to the rotor interior end face  16 , through the bearing isolator  12 , and finally to the stator exterior end face  15 . A detector means may then be positioned at a range that allows collection of data from the stator exterior end face  15 . The detector means may be a thermal scanner  42 , IR camera  43 , or any other detector means known to those skilled in the art. The stator exterior end face  15  may communicate other specific operating parameters of the primary bearing  5  or a plurality of operating parameters, such as vibration frequencies and/or amplitudes or other parameters indicating the operational state of the primary bearing  5 . 
     The detector means would then be monitored during operation of the conveyor roller  40  to detect any deleterious change in the operation of the primary bearing  5  as reflected by energy accumulation at the stator exterior end face  15 , or other relevant information that provides insight to the operational parameters of the primary bearing  5 . Deleterious changes in the operation of the primary bearing  5  may be indicated by accumulation of excess heat or vibration at the stator exterior end face  15 . The preceding system could incorporate a single mobile thermal scanner or IR camera, or any other portable heat sensing device, operated by a human as available.  FIG. 11  shows an IR camera  43  positioned so that the IR camera  43  is capable of detecting the temperature of the bearing isolator  12 . This arrangement could be replicated for each bearing isolator  12  on each conveyor roller  40 , or different detector means could be employed for different bearing isolators  12 , depending on the detector means that best serves a particular application. 
     In this method, the detector means would then be monitored during operation of the conveyor roller  40  to detect any deleterious change in the operation of the primary bearing  5  as reflected by energy accumulation at the stator exterior end face  15 . Deleterious changes in the operation of the primary bearing  5  may be indicated by accumulation of excess heat or vibration at the stator exterior end face  15 . The preceding system could incorporate a single mobile thermal scanner or IR camera, or any other portable heat sensing device, operated by a human or automated, as available. 
     In another embodiment of this method, at least one detection means could be positioned within range of a plurality of stator exterior end faces  15  and programmed to pan and scan in a semi-autonomous manner at a pre-selected frequency.  FIG. 12  provides one view of this embodiment of the method, wherein the detection means is an IR camera  43 . In the embodiment shown in  FIG. 12 , the scan path  47  of the IR camera  43  is broad enough to monitor five bearing isolators  12 . As shown by the dashed lines in  FIG. 12 , the IR camera  43  is positioned so that a line of sight  48  may be established between the IR camera  43  and the stator exterior end faces  15  of five bearing isolators  12 . Alternatively, the scan path  47  could be programmed so that the IR camera  43  moved in two (or even three) dimensions so that it is capable of monitoring additional bearing isolators  12  and the scan path  47  may be considerably more complicated than that shown in  FIG. 12 . The detecting means would be in communication with either an alarm (not shown) to signal an operator of deleterious conditions, or the detecting means would be in communication with a user interface (not shown) that displays real-time information to the operator regarding the operating parameters the detecting means is configured to detect. The preceding monitoring and indicator system and method may also be networked allowing connection with a data processing system (not shown) to allow data collection, monitoring, alerts and even controlled shutdowns of the conveyor system as necessitated by operating conditions. 
     It should be noted that the present invention is not limited to the specific embodiments pictured and described herein, but is intended to apply to all similar methods for monitoring relevant operational parameters of primary bearings  5 , conveyor systems, thermal accumulation related to primary bearing  5  failure, or deterioration of a bearing or conveyor system during operation. Accordingly, modifications and alterations from the described embodiments will occur to those skilled in the art without departure from the spirit and scope of the present invention.