WO2008030436A2 - Procédé de surveillance d'un roulement - Google Patents

Procédé de surveillance d'un roulement Download PDF

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Publication number
WO2008030436A2
WO2008030436A2 PCT/US2007/019308 US2007019308W WO2008030436A2 WO 2008030436 A2 WO2008030436 A2 WO 2008030436A2 US 2007019308 W US2007019308 W US 2007019308W WO 2008030436 A2 WO2008030436 A2 WO 2008030436A2
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
stator
monitoring
isolator
rotor
Prior art date
Application number
PCT/US2007/019308
Other languages
English (en)
Other versions
WO2008030436A3 (fr
Inventor
David C. Orlowski
Neil F. Hoehle
Original Assignee
Isotech Of Lllinois, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US11/825,409 external-priority patent/US20080078648A1/en
Priority claimed from US11/881,881 external-priority patent/US20080063330A1/en
Application filed by Isotech Of Lllinois, Inc. filed Critical Isotech Of Lllinois, Inc.
Publication of WO2008030436A2 publication Critical patent/WO2008030436A2/fr
Publication of WO2008030436A3 publication Critical patent/WO2008030436A3/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G43/00—Control devices, e.g. for safety, warning or fault-correcting
    • B65G43/02—Control devices, e.g. for safety, warning or fault-correcting detecting dangerous physical condition of load carriers, e.g. for interrupting the drive in the event of overheating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G39/00—Rollers, e.g. drive rollers, or arrangements thereof incorporated in roller-ways or other types of mechanical conveyors 
    • B65G39/02—Adaptations of individual rollers and supports therefor
    • B65G39/09—Arrangements of bearing or sealing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/74—Sealings of sliding-contact bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G2201/00—Indexing codes relating to handling devices, e.g. conveyors, characterised by the type of product or load being conveyed or handled
    • B65G2201/04—Bulk
    • B65G2201/045—Sand, soil and mineral ore
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G2203/00—Indexing code relating to control or detection of the articles or the load carriers during conveying
    • B65G2203/04—Detection means
    • B65G2203/041—Camera
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G2207/00—Indexing codes relating to constructional details, configuration and additional features of a handling device, e.g. Conveyors
    • B65G2207/22—Heat or fire protection
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G2207/00—Indexing codes relating to constructional details, configuration and additional features of a handling device, e.g. Conveyors
    • B65G2207/40—Safety features of loads, equipment or persons

Definitions

  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • Figure IA presents an exploded view of a conveyor roller bearing arrangement known to those practiced in the 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.
  • 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.
  • ferrous metal to ferrous metal contact 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.
  • 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.
  • 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.
  • FIGS. 3, 4A-4C, 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.
  • the bearing seals of the conveyor rollers of the prior art may be replaced with the present art.
  • the improved bearing isolator is a substitute for lube containment shields, and the improved bearing isolator will not wear or degrade in use.
  • 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.
  • centrifugates i.e., migrates through and by centrifugal acceleration
  • 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.
  • 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.
  • 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.
  • 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, 4A-4C, 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.
  • 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.
  • 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. Patent 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a non-ferrous metal such as bronze
  • non- sparking metals other than bronze may be chosen for their non-ferrous qualities such as gold, silver, nickel, copper, and combinations thereof.
  • 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.
  • 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.
  • 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. Patent No. 4,647,710 issued to Davis for "Heat Sensitive Cable and Method of Making Same,” which is incorporated herein by reference.
  • FIG. 1 is a sectional view of a conveyor roller and primary bearing assembly as found in the prior art.
  • FIG. IA 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. 3 A 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.
  • FIGS. 1 and IA illustrate the prior art as taught by U.S. Patent No. 6,802,410 issued to Dyson et al. for "Conveyor Roller Bearing Housing,” which is incorporated by reference herein.
  • FIGS. 1 and IA of the prior art bearing assembly There are two principal sections shown in FIGS. 1 and IA of the prior art bearing assembly; one external and one internal.
  • the external section is comprised of a cover 8A and stone guard 8B.
  • cover 8A and stone guard 8B 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.
  • 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.
  • 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 IA.
  • the primary bearing 5 is of the sealed type, and as with the embodiment shown in FIGS. 1 and IA, 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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, 4A-C, 6, 7, and 8 is a frictionless, non-contacting improved bearing isolator 12.
  • 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.
  • 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.
  • 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.
  • 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.
  • O-rings 23 fit into first and second stator O-ring grooves 25 and 27, respectively.
  • 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.
  • 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.
  • 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.
  • 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 1 to the intermediate annular chamber 19 for such substances.
  • 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.
  • 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.
  • the exterior interface passage 17 is parallel with the axis of the shaft 2, as it was in the embodiment shown in FIG. 3 A.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 TeflonTM 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.
  • the frictional loses incurred by using sealed bearings are higher.
  • the prior art conveyor rollers 40 as shown in FIG.
  • IA 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.
  • 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.
  • 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 13 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • sensors include electronic transducers, transmitters, and thermal sensing conductors or connectors as exemplified by U.S. Patent 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.
  • 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.
  • 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.
  • 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 berween ⁇ the stator 13 and the rotor 14.
  • the improved bearing isolator 12 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.
  • the intermediate annular chamber 19 may be filled with long- lasting (preferably synthetic) grease, as known to those practiced 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.
  • 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. Patent No. 6,419,233, which is incorporated by reference herein, so as to prevent possible ingress of vapor contamination into the primary bearings 5.
  • a vapor blocking ring component such as that described in U.S. Patent 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 8A 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.
  • a first bearing housing 3 is positioned within the conveyor roller shell 1 at the first end of the conveyor roller shell 1.
  • 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.
  • 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.
  • 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 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.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • the scan path 47 of the IR camera 43 is broad enough to monitor five bearing isolators 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.
  • 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 43 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Rollers For Roller Conveyors For Transfer (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Abstract

L'invention concerne un procédé de surveillance d'un roulement. Le procédé met en œuvre le positionnement d'un isolateur de roulement sans contact adjacent à un roulement sur une pièce d'un équipement tournant de telle sorte qu'au moins un paramètre de fonctionnement dudit roulement soit communiqué au dit isolateur de roulement ainsi que le positionnement d'un détecteur d'énergie dans la portée dudit isolateur de roulement de telle sorte que ledit détecteur d'énergie puisse surveiller ledit ou lesdits paramètres de fonctionnement dudit roulement en détectant au moins un paramètre de fonctionnement dudit isolateur de roulement.
PCT/US2007/019308 2006-09-07 2007-09-05 Procédé de surveillance d'un roulement WO2008030436A2 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US84271806P 2006-09-07 2006-09-07
US60/842,718 2006-09-07
US11/825,409 US20080078648A1 (en) 2006-09-07 2007-07-06 Bearing isolator and conveyor roller
US11/825,409 2007-07-06
US11/881,881 2007-07-30
US11/881,881 US20080063330A1 (en) 2006-09-07 2007-07-30 Bearing monitoring method

Publications (2)

Publication Number Publication Date
WO2008030436A2 true WO2008030436A2 (fr) 2008-03-13
WO2008030436A3 WO2008030436A3 (fr) 2008-06-12

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PCT/US2007/019358 WO2008030470A2 (fr) 2006-09-07 2007-09-05 Isolateur de palier et rouleau de transporteur
PCT/US2007/019308 WO2008030436A2 (fr) 2006-09-07 2007-09-05 Procédé de surveillance d'un roulement

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Application Number Title Priority Date Filing Date
PCT/US2007/019358 WO2008030470A2 (fr) 2006-09-07 2007-09-05 Isolateur de palier et rouleau de transporteur

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Cited By (3)

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WO2012057680A1 (fr) * 2010-10-25 2012-05-03 Eistec Ab Rouleau pour transporteur à courroie comprenant des capteurs pour surveiller l'état du rouleau
WO2016161473A1 (fr) * 2015-04-10 2016-10-13 Orontide Group Ltd Appareil de contrôle de poulie de transporteur
CN108733095A (zh) * 2018-04-03 2018-11-02 河南大有能源股份有限公司 基于机器视觉的煤矿成套运输设备智能调速系统及方法

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BR112019024395A2 (pt) * 2017-06-08 2020-06-09 Laitram Llc montagem em um sistema transportador e vedação para um pinhão
KR101858588B1 (ko) 2018-01-18 2018-05-16 김정연 이송 장치의 샤프트에 고정되는 이송용 롤러

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US4484754A (en) * 1984-01-31 1984-11-27 Ballard Michael J Ring seal with overlapping flanges for contaminant trapping
WO1997011871A1 (fr) * 1995-09-29 1997-04-03 Science Applications International Corporation Appareil et procede pour detecter des temperatures elevees dans les roues et les coussinets de roues de vehicules ferroviaires
US20010039835A1 (en) * 2000-04-19 2001-11-15 Jurgen Scholl Method and device for monitoring a bearing arrangement
WO2004045127A2 (fr) * 2002-11-12 2004-05-27 Motorola, Inc., A Corporation Of The State Of Delaware Appareil detecteur sans fil, et procede correspondant

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US5655642A (en) * 1995-05-22 1997-08-12 Fmc Corporation Idler roll for use in belt conveyor systems
CN1237140A (zh) * 1996-08-08 1999-12-01 流量操纵(私人)有限公司 导辊
US6076647A (en) * 1997-09-29 2000-06-20 Interroll Holding Ag Stub shaft conveyor roller

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US4484754A (en) * 1984-01-31 1984-11-27 Ballard Michael J Ring seal with overlapping flanges for contaminant trapping
WO1997011871A1 (fr) * 1995-09-29 1997-04-03 Science Applications International Corporation Appareil et procede pour detecter des temperatures elevees dans les roues et les coussinets de roues de vehicules ferroviaires
US20010039835A1 (en) * 2000-04-19 2001-11-15 Jurgen Scholl Method and device for monitoring a bearing arrangement
WO2004045127A2 (fr) * 2002-11-12 2004-05-27 Motorola, Inc., A Corporation Of The State Of Delaware Appareil detecteur sans fil, et procede correspondant

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012057680A1 (fr) * 2010-10-25 2012-05-03 Eistec Ab Rouleau pour transporteur à courroie comprenant des capteurs pour surveiller l'état du rouleau
WO2016161473A1 (fr) * 2015-04-10 2016-10-13 Orontide Group Ltd Appareil de contrôle de poulie de transporteur
CN108733095A (zh) * 2018-04-03 2018-11-02 河南大有能源股份有限公司 基于机器视觉的煤矿成套运输设备智能调速系统及方法
CN108733095B (zh) * 2018-04-03 2020-11-17 河南大有能源股份有限公司 基于机器视觉的煤矿成套运输设备智能调速系统及方法

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WO2008030470A2 (fr) 2008-03-13
WO2008030470A3 (fr) 2008-06-26
WO2008030470A9 (fr) 2008-12-04
WO2008030436A3 (fr) 2008-06-12

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