Patent Abstract:
A lubricating system is affixed to and rotates with a rotary drive shaft, and provides automatic lubrication of the rotating bearings of a universal joint or similar articulated juncture in the shaft while the shaft is rotating. The present system includes a series of conventional automatic lubricators which are affixed to the shaft by a novel bracket. The bracket components provide for installation from the sides of the shaft, in order to avoid any requirement to disconnect the shaft at one end to pass the bracket over the end of the shaft. Each component group securing each side of the bracket portions together is configured to closely balance the weight of one lubricator in a partially depleted state, in order to avoid any undue balance problems on the shaft.

Full Description:
BACKGROUND OF THE INVENTION 
   1. Field of the Invention 
   The present invention relates generally to automated lubricating systems, and more specifically to a lubricating system which is affixed to a rotating drive shaft or the like and which rotates with the shaft. The present lubricating system supplies lubrication at intervals for bearings located at rotating universal joints and similar driveline junctures where it is not possible to provide a stationary lubrication fitting. 
   2. Description of the Related Art 
   Universal joints, constant velocity (CV) joints, and similar components are often designed to require periodic lubrication. While the automotive industry has generally turned to permanently lubricated joints, many types of large machinery utilize relatively large U-joints and the like, with such large joints generally requiring periodic lubrication for the bearings therein. This is true in many industries, e.g. maritime shipping and various machines used in heavy industry, most particularly large paper manufacturing machines. In many cases such machines are run essentially continually, as starting and stopping the machines and their production at the end of a workday or workweek cannot be justified economically. 
   Conventional lubricating systems for such drive line fittings, require the machine to be shut down periodically in order to stop the joint and access the lubrication fitting(s) thereon. Down time for such a machine may be on the order of $300 per minute or $18,000 per hour, depending upon the size and production capacity of the machine. The requirement to employ mechanics to lubricate the driveline systems adds further to the cost of maintaining such a machine. The alternative of running the machine until damage occurs due to lack of lubrication is even less desirable. The down time noted above is only one of the factors, which must be considered when a machine is shut down due to damage. The removal, repair, and installation time and costs involved in the repair of a large driveline are considerable in very large machinery. 
   Accordingly, a need will be seen for a lubrication system which may be affixed to a rotary shaft, and which provides periodic lubrication on demand for universal joints and/or other fittings on the shaft, which require periodic lubrication. The present invention responds to this need by means of a bracket assembly affixed around the diameter of the drive shaft, with the bracket holding a plurality of automated lubrication dispensers therein. The conventional lubrication or grease fittings located at the universal joint trunnions are removed, and lubricant distribution and supply lines are connected between the universal join grease fitting receptacles and the lubrication dispensers secured within the bracket of the present invention. The dispensers may be controlled by internal timers, radio signals, or other means which do not require any form of direct physical connection between the rotating apparatus and a stationary controller, to dispense lubricant periodically as required by the equipment without any requirement to shut down or stop the operation of the equipment. 
   A discussion of the related art of which the present inventors are aware, and its differences and distinctions from the present invention, are provided below. 
   U.S. Pat. No. 4,700,808 issued on Oct. 20, 1987 to Walter D. Haentjens, titled “Shaft Mounted Bearing Lubricating Device,” describes an annular lubrication system wherein the lubricant supply surrounds a stationary housing. A set of impeller blades attached to the rotating inner shaft dips into the lubricant supply to splash oil to the bearings in the assembly. The Haentjens lubrication system can only be used with shaft assemblies having essentially vertical orientations, due to the annular oil supply surrounding the stationary external housing; no means is provided for lubricating multiple points on a rotating shaft. In contrast, the present lubrication system is not sensitive to orientation, and the entire system is affixed to the rotating shaft, rather than having a portion of the system affixed to a stationary structure as in the Haentjens device. 
   U.S. Pat. No. 4,799,574 issued on Jan. 24, 1989 to Johan C. M. Bras, titled “Lubrication Device,” describes a generally conventional lubricant reservoir for affixing to a stationary lubrication port on a machine or the like. The Bras device includes a spring motor for periodically opening a passage to allow lubricant to flow from the device, with the motor being controlled by an electronic timing circuit. The Bras apparatus is incapable of lubricating multiple points on a rotating shaft and cannot be secured in its entirety to such a rotating shaft, as provided by the present invention. 
   U.S. Pat. No. 5,333,704 issued on Aug. 2, 1994 to John Hoff, titled “Rotating Lubricating Technique For Equipment,” describes a lubricating system for the chain drive of a wheeled irrigation machine. The Hoff lubricating system comprises an oil reservoir which rotates with wheel rotation, to dispense a measured amount of oil to a distribution channel which provides oil to the chain drive. The Hoff system can only operate at relatively low wheel rotational speeds, as centrifugal force would result in the oil being thrown to the outer or upper portion of the reservoir and dispensed constantly. It is also noted that the distribution channels of the Hoff lubrication system are fixed relative to the rest of the structure, and do not rotate with wheel rotation. 
   U.S. Pat. No. 5,558,180 issued on Sep. 24, 1996 to Kiyoshi Yanagisawa, titled “Bearing Lubricating Apparatus For Rotary Machine,” describes a system having a rotary mechanism and shaft disposed within a stationary housing. The Yanagisawa apparatus includes a disc which passes through the oil reservoir during rotation of the shaft, to throw oil where it can be gathered for distribution to the bearings. As with other similar systems, the Yanagisawa system cannot operate with heavier viscosity lubricants and includes stationary components. 
   U.S. Pat. No. 5,732,794 issued on Mar. 31, 1998 to Anton T. Orlitzky, titled “Auger-Driven Automatic Lubricator,” describes an oiling device similar to that of the Bras &#39;574 U.S. Patent discussed further above. The Orlitzky lubricator includes an electronic timing device to direct the lubricator to deliver lubrication at certain predetermined times. However, the Orlitzky lubricator still cannot be installed upon a rotating device or structure, and cannot deliver lubrication to a plurality of bearings simultaneously, as can the present invention. 
   U.S. Pat. No. 5,950,764 issued on Sep. 14, 1999 to Claus Helbig, titled “Lubricating Device For Rotating Parts, Especially A Rotating Hollow Shaft,” describes a relatively complex system which is completely contained concentrically within a rotating assembly. The Helbig device includes centrifugal switches which in turn causes a gas to be generated to pressurize the lubricant delivery system. The system provides lubrication for two concentric telescoping shafts, and cannot lubricate the plurality of separate bearings of a universal joint trunnion or the like, as provided by the present lubrication system. 
   U.S. Pat. No. 5,971,229 issued on Oct. 26, 1999 to Anton May et al., titled “Automatic Lubricant Dispenser,” describes another lubricator device with lubricant reservoir, configured for a stationary installation. The May et al. device closely resembles the lubricator of the Orlitzky &#39;794 U.S. Patent discussed further above, but is actuated by a manually operated switch on the top of the device. Accordingly, the May et al. cannot be installed on a rapidly rotating piece of equipment, as the actuation switch would not be accessible. 
   U.S. Pat. No. 6,102,804 issued on Aug. 15, 2000 to Horst Kretschmer et al., titled “Lubricating Device For Lubricating The Profiled Tubes Of A Telescopic Shaft,” describes a lubrication system performing a similar function to that of the Helbig &#39;764 U.S. Patent discussed further above. While FIG. 1 of the Kretschmer et al. drawings shows a telescoping tube assembly with a U-joint on each end, no lubrication to the U-joint bearings is provided. The Kretschmer et al. lubrication system is directed only to lubrication of the two sliding telescoping tubes, and not to any external bearings at either end of the tube assembly. 
   U.S. Pat. No. 6,125,969 issued on Oct. 3, 2000 to Walter Graf et al., titled “Method Of And Apparatus For Lubricating An Apparatus Having A Number Of Lubricant Locations,” describes a lubricating device quite similar to that described in the &#39;229 U.S. Patent to May, described further above. It is noted that May is the second inventor in the Graf 969 U.S. Patent. The primary difference between the two devices is that the lubricator of the Graf et al. &#39;969 U.S. patent includes electronic means to count the number of revolutions of a rotating component and dispense lubricant accordingly. The Graf et al. &#39;969 U.S. Patent also describes the use of a plurality of such devices to lubricate a corresponding plurality of lubrication points. However, no mounting or attachment to a rotating structure is disclosed, as provided by the present invention. 
   U.S. Pat. No. 6,179,470 issued on Jan. 30, 2001 to H. Mike Huddleston et al., titled “Self-Lubricating Bearing,” describes a lubrication system for a sleeve bearing in a centrifugal clutch assembly. The bearing is described as being porous, i.e., an Oilite® bearing or the like. One or more circumferential grooves are formed in the structure surrounding the bearing, and the grooves are packed with grease. Huddleston et al. do not provide any means for lubricating the bearing at predetermined periodic intervals, nor for lubricating a series of separate rotating bearings, as provided by the present invention. 
   U.S. Pat. No. 6,405,810 issued on Jun. 18, 2002 to Ayzik Grach et al., titled “Method Of Lubricating And Lubricant Spraying Apparatus,” describes a lubricant spray device which is synchronized with the rotation of a rotating object to spray lubricant only upon a certain portion of the object at each revolution. The lubricant supply and sprayer components are stationary relative to the rotating object and are not in direct contact with the object being lubricated, unlike the present lubrication system. 
   U.S. Pat. No. 6,478,116 issued on Nov. 12, 2002 to Jorn H. Klausen et al., titled “Lubricating Oil Supplying Arrangement For An Apparatus Having A Rotating Apparatus Shaft,” describes a multi-lobe rotary oil pump which is internally installed and concentric with a rotating shaft. The Klausen et al. pump cannot provide lubrication to multiple bearing locations from a corresponding number of externally disposed lubricating devices, as provided by the present lubricating system invention. 
   U.S. Pat. No. 6,557,651 issued on May 6, 2003 to Duane E. Norby et al., titled “Automated Lubricant Dispensing System And Method For A Horizontal Directional Drilling Machine,” describes a lubricating system for use with machine tools, for lubricating the workpiece and cutting tool during machining operations. Such lubrication is completely different than that used in the present invention, as cutting tool lubrication is contaminated by material removed from the workpiece and must be filtered and processed if it is to be reused. The cutting oils or lubricants used for such operations are also considerably lighter than the lubricants used in bearings and the like. In any event, the Norby et al. lubrication system is stationary and does not rotate with the cutting tool, but sprays the lubricant onto the rotating cutting tool during the machining operation. 
   U.S. Patent Application Publication No. 2002/79,336 published on Jun. 27, 2002 to Michael Weigand et al., titled “Lubricant Dispenser,” describes a device similar to those disclosed in the &#39;229 U.S. Patent to May and &#39;969 U.S. Patent to Graf, both of which have been described further above. While such lubricators may be used with the present invention, it is noted that Weigand et al. do not provide any means for securing their lubricator to a rotating object, nor do they provide an installation having a series of such lubricators installed on a rotating object and connected to a corresponding series of separate bearings on the rotating object, as provided by the present lubricating system invention. 
   U.S. Patent Application Publication No. 2002/144,864 published on Oct. 10, 2002 to Siegfried Kramer, titled “Multi-Point Lubrication Distribution System,” describes a single, centrally located lubricant reservoir and pump which supplies lubricant to a series of bearings or the like by means of a manifold and rotary distributor which sequences the delivery of lubricant to each location. The lubricant reservoir and pump of the Kramer system appear to be quite similar to those described in the &#39;229 U.S. Patent to May, the &#39;969 U.S. Patent to Graf, and the &#39;336 U.S. Patent Publication to Weigand et al., each of which have been described further above. As in the other devices of which the present inventors are aware, Weigand et al. do not disclose any means of mounting such a lubricant system on a rotating object. Moreover, the Kramer et al. device teaches away from such an installation, due to the imbalance which would be created by attaching only one such lubricator to one side of a rotating object. 
   U.S. Patent Application Publication No. 2003/10,572 published on Jan. 16, 2003 to Mark S. Henry et al., titled “Lubrication System For A Bearing,” describes a device having a single stationary oil supply which delivers oil to a fan installed within the hub of the rotating assembly. The fan draws air and oil from the lubricant system into the rotating assembly, to lubricate the bearings therein. Henry et al. do not disclose any specific type of lubrication reservoir and pump system for use with their invention, and disclose only a single such lubrication supply. 
   U.S. Patent Application Publication No. 2003/31,554 published on Feb. 13, 2003 to Robert E. Rockwood, titled “Centrifugal Pump Having Oil Misting System With Pivoting Blades,” describes a device having a series of radially disposed oil splash blades hingedly secured to a rotary shaft. The blades pick up oil from a stationary reservoir, and sling the oil within the reservoir and housing to lubricate components therein. Rockwood does not provide a series of lubricant reservoirs and dispensing units affixed to a rotating shaft for lubricating a series of separate bearings on the shaft, as provided by the present lubricating system invention. 
   U.S. Patent Application Publication No. 2003/75,043 published on Apr. 24, 2003 to Brad Rake, titled “Apparatus And Method For Lubricant Condition Control And Monitoring From A Remote Location,” describes a device for detecting humidity buildup in an oil supply, and drying the oil by injecting dry air into the system. The Rake system includes a stationary dryer system which is connected to a stationary oil supply at the bearings of the shaft of the device being lubricated. None of the components of the Rake assembly are affixed to any of the rotating components of the device being lubricated, nor does Rake disclose multiple lubricators servicing a corresponding number of lubrication points on a rotating shaft, as provided by the present invention. 
   European Patent Application Publication No. 704,654 published on Apr. 3, 1996 to Anton Orlitzky, titled “Auger-Driven Automatic Lubricator,” is the European filing of the &#39;794 U.S. Patent to the same inventor, discussed further above. The same points of difference between the &#39;794 U.S. Patent to Orlitzky and the present invention are seen to apply here as well. 
   Finally, German Patent Publication No. 10,054,712 published on May 29, 2002, describes a device which is very similar to the lubricator of the Helbig &#39;764 U.S. Patent discussed further above. The same points of difference noted in the discussion of the Helbig &#39;764 U.S. Patent are seen to apply here as well. 
   None of the above inventions and patents, taken either singly or in combination, is seen to describe the instant invention as claimed. Thus a lubricating system affixed to a rotary shaft solving the aforementioned problems is desired. 
   SUMMARY OF THE INVENTION 
   The present lubricating system is affixed to a rotary shaft and includes a series of lubricator devices which supply lubrication to a corresponding number of bearings which rotate with the shaft. The present invention may be adapted to a number of different shaft configurations, but is particularly well suited for installation on a relatively large shaft to provide lubrication for the trunnion bearings of a large universal joint or joints on the shaft. The lubricators used with the present invention are conventional and commercially available. Such lubricators may be configured to dispense their lubricant automatically by means of a timer mechanism installed in each lubricator, or alternatively by electromagnetic signal or other means which does not require physical connection between the lubricators and a stationary control point. The lubricators are secured to the rotating shaft by a novel bracket, which captures the lubricators on the shaft and also secures the lubrication lines extending from the lubricators toward their corresponding bearings. The bracket of the present invention is configured to allow it to be assembled from the sides of the shaft, in order to preclude any need to disassemble the shaft and pass a closed bracket over one end of the shaft. Each component group securing each side of the bracket portions together is configured to closely balance the weight of one lubricator in a partially depleted state, in order to avoid any undue balance problems on the shaft. 
   Accordingly, it is a principal object of the invention to provide a multiple point lubricating system for a rotating shaft, which lubricating system in its entirety is affixed to and rotates with the rotating shaft. 
   It is another object of the invention to provide such a lubrication system which automatically lubricates the rotating lubrication points on the shaft, without need to stop the rotary motion of the shaft in order to perform the lubrication. 
   It is a further object of the invention to provide a bracket for such a lubrication system for securing a plurality of lubricating devices to the shaft, each of which devices is connected to a corresponding lubrication point on the shaft. 
   Still another object of the invention is to provide such a lubrication system which bracket may be secured around and removed from the shaft as desired without need to disconnect the shaft from its attachment points. 
   It is an object of the invention to provide improved elements and arrangements thereof for the purposes described which is inexpensive, dependable and fully effective in accomplishing its intended purposes. 
   These and other objects of the present invention will become readily apparent upon further review of the following specification and drawings. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1  is an environmental, perspective view of a lubricating system affixed to a rotary shaft according to the present invention, showing its various features. 
       FIG. 2  is a side elevation view of the present lubricating system installed on a rotary shaft, showing further details thereof. 
       FIG. 3  is an exploded perspective view of the various components comprising the present lubricating system. 
   

   Similar reference characters denote corresponding features consistently throughout the attached drawings. 
   DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
   The present invention comprises a system or apparatus for lubricating the rotating bearings of a rotating shaft. The device is particularly well suited for the lubrication of relatively large roller or ball bearings as used in the trunnions of universal joints in very large drive shafts and the like, as used in various types of heavy machinery such as papermaking machines, mining machinery and equipment, large ships, and other equipment using very large articulated drive shafts. Such equipment is often in operation round the clock, with shutdown for maintenance and lubrication being costly due to the loss of productivity. The present invention provides a solution to the problem of lubricating the rotating bearings in a rotating shaft, by providing a bracket holding a series of automated lubricators therein, with the bracket and lubricators being affixed to and rotating with the drive shaft. 
     FIGS. 1 and 2  respectively provide environmental perspective and environmental side elevation views of the present lubricating system installed on a large rotating drive shaft D, as used in large papermaking machines and the like. The drive shaft D is conventional, having a first bearing end E 1  and an opposite second bearing end, not shown but understood to be essentially a mirror image configuration to the first end E 1 . Each end has an articulated attachment to its respective connection point, e.g. a drive motor or gear reduction system or driven element of the machine, etc. The articulated attachment may be a conventional universal joint structure J having four trunnions T (two of which are shown in  FIG. 1 ), each having a conventional internal roller or ball bearing assembly (not shown) which requires periodic lubrication. Such assemblies are conventionally provided with a lubrication (grease) fitting, to which grease or other lubricant is applied periodically when the drive system is stopped. 
   The present invention removes any need to stop the machinery in order to lubricate the bearings of the universal joint trunnions T, by means of a bracket assembly  10  which is affixed to the drive shaft D and rotates therewith. The bracket assembly  10  comprises a series of first through fourth bracket portions, respectively  12  through  18 , with each bracket portion having a semicircular configuration with a first end  20 , opposite second end  22 , an inner diameter  24  dimensioned to fit closely about the drive shaft D, and a larger outer diameter  26 ; the ends  20  and  22  and the inner and outer diameters  24  and  26  are indicated in  FIG. 3 . The various bracket portions  12  through  18  are preferably formed of aluminum, in order to reduce the rotational mass of the assembly. However, other materials (e.g., steel plate, heavy plastics, etc.) may be used as desired, depending upon the diameter and rotational speed of the drive shaft, the masses of the lubrication devices and attachment hardware installed in the bracket, etc. 
   The various bracket portions  12  through  18  are assembled about the drive shaft D with the first and second bracket portions  12  and  14  placed opposite one another to essentially encircle the drive shaft D, and in the same plane. The third and fourth bracket portions  16  and  18  are placed about the drive shaft D in the same manner, but spaced apart from the first and second bracket portions  12  and  14 . A series of bracket portion spacer fittings are installed between the parallel first and third bracket portions  12  and  16  and between the parallel second and fourth bracket portions  14  and  18 , to secure those parallel components in their proper relationship to one another. The bracket portion spacer fittings comprise a series of medial spacers  28 , with each of the spacers  28  having a threaded concentric axial passage  30  therethrough. A corresponding number of medial spacer attachment passages  32  are formed through the medial portion of each of the bracket portions  12  through  18 , with these passages  32  preferably being counterbored in their facing surfaces to the diameter of the medial spacers  28  to facilitate assembly. 
   At least one, and preferably a pair, of such medial spacers  28  are placed between the corresponding parallel bracket portions  12 ,  16  and  14 ,  18 , seated in the counterbores of the medial spacer attachment passages  32  and secured in place by opposed bracket assembly bolts  34  installed through each of the parallel bracket portions  12 ,  16  and  14 ,  18  and into the opposite ends of the medial spacers  28 . The bracket assembly bolts  34  have drilled heads (not shown) for safety wiring, or other means to prevent the bolts  34  from backing out while installed in the bracket assembly  10  as it rotates on the shaft D. Details of the medial spacers  28  and bracket assembly bolts  34  are shown most clearly in  FIG. 3  of the drawings. 
   It will be seen that additional fittings must be installed between the various bracket portions  12  through  18  to provide adequate attachment, and also to provide for securing the opposed bracket portions  12 ,  14  and  16 ,  18  to one another around the drive shaft D. Accordingly, a series of bracket portion clamp fittings are provided for this purpose, as shown in detail in  FIG. 3 . 
   The clamp fittings comprise a series of identical first and second end spacers  36 , with their only difference being the location of their installation in either the first ends  20  or the second ends  22  of the spacer portions  12  through  18 . Each of the first and second end spacers  36  also includes a threaded axial passage  30  formed concentrically therethrough; the end spacers  36  may be substituted for the medial spacers  28 , if so desired. However, each of the end spacers  36  also includes a diametric passage  38  formed therethrough for the installation of bracket clamping bolts, as explained further below. 
   Each of the ends  20  and  22  of the bracket portions  12  through  18  includes at least one, and preferably two, end spacer attachment passages  40  formed therethrough. These end spacer attachment passages  40  are also preferably counterbored in their facing surfaces, in the manner of the medial passages  32  described further above. The end spacers  36  are placed in the counterbores of the end spacer attachment passages  40  of the facing bracket portions  12  through  18 , to secure the first and second ends  20 ,  22  of the first and third bracket portions  12 ,  16  and the first and second ends  20 ,  22  of the second and fourth bracket portions  14 ,  18  together. The bracket and spacer assemblies are secured by additional bracket assembly bolts  34 , identical to the bolts  34  used with the medial spacers  28 . As in the case of the bolts  34  used to secure the medial spacers  28  between their respective bracket portions, these end spacer bracket assembly bolts  34  have drilled heads for safety wiring, or some other means is provided to prevent their backing out during operation of the machine. 
   The diametric holes  38  of corresponding spacers  36  are aligned with one another during assembly, to provide for the attachment of the two subassemblies comprising first and third bracket portions  12  and  16  and second and fourth bracket portions  14  and  18  to one another. A corresponding number of bracket first and second end clamping bolts  42  are installed through each pair of end spacers  36 , with each spacer pair comprising an opposed spacer of the first end  20  of the first and third bracket portion  12 ,  14 , an opposed spacer of the second end  22  of the those bracket portions  12  and  14 , an opposed spacer of the first end  20  of the second and fourth bracket portion  16 ,  18 , and an opposed spacer of the second end  22  of the those bracket portions  16  and  18 . Each of the bracket end clamping bolts  42  includes a head  44  which abuts one of the end spacers  36  when installed therewith, and a lock nut  46  secured to the opposite end of each clamping bolt  42  and abutting the corresponding opposite end spacer  36 . The lock nuts  46  are tightened on the clamping bolts  42  to clamp the corresponding end spacers  36  to one another and affix the bracket subassemblies  12 ,  16  and  14 ,  18  to the shaft D. 
   Each of the bracket portions  12  through  18  includes at least one, and preferably a series of, lubricator installation passages  48  formed therethrough, in a circumferential pattern between the first and second ends  20  and  22  and between the inner and outer diameters  24  and  26  of the bracket portions. The number of lubricator passages  48  is equal to twice the number of automatic lubricator devices L to be installed therein, with each lubricator device L being captured by a pair of axially concentric passages  48  in adjacent parallel bracket portions, e.g. first and third bracket portions  12  and  16 , etc. The number of lubricator devices L to be provided is dependent upon the number of lubrication points to be serviced. Where the present invention is installed between two universal joints to lubricate both joints, a total of eight lubricators L will be required for the four bearing assemblies of each of the two joints. Obviously, the present lubricating system may be configured to hold other numbers of lubricators L, as desired. 
   The lubricator devices L used with the present invention are conventional, with the present invention being capable of accepting and operating with a number of different types and models. An exemplary model is the Perma Star®, which provides lubrication intermittently at predetermined intervals in accordance with an integral timer mechanism in each unit. Such lubricators may be adjusted at the time of installation (or at other times as desired) to provide lubrication over a time period ranging from a few days up to a year. Other models of automatic lubricators, e.g. those where the dispensing of lubricant is controlled by an integral receiver which receives a signal from a remotely located and relatively stationary transmitter, or automatic lubricators manufactured by another manufacturer(s), may be substituted for the exemplary Perma Stars lubricator L, as desired. In any event, a critical feature of the automatic lubricators used with the present invention is that they be capable of dispensing lubricant at intervals over a relatively lengthy period of time, without need for any structural physical connection (e.g., electrical wiring) to a triggering device, as the lubricators L rotate with the rotating drive shaft D during operation. 
   The lubricators L are installed in the lubricator passages  48  of the bracket portions  12  through  18  before those portions are assembled to one another. Rubber or plastic grommets  50  are installed in each of the lubricator passages  48 , to hold the lubricators L firmly within the device without applying clamping pressures which might distort or damage the devices. The exemplary Perma Star® lubricators used with the present invention, include a medial band M having a somewhat larger diameter than the majority of the device. This larger diameter medial band M facilitates the installation of the lubricators L in the bracket portions  12  through  18 , as the medial band M is captured between the two spaced apart and axially concentric lubricator passages  48  to prevent axial movement of the lubricators L within the lubricator passages  48 . Other means of preventing lubricator movement may be provided alternatively, e.g. hose clamps or the like secured about the lubricators, etc. 
   Assembly of the present lubrication system  10  is accomplished by first installing the grommets  50  in the lubricator passages  48  in each of the lubricator passages  48 , and then passing one of the axially concentric lubricator passages  48  of two opposed bracket portions, i.e. portions  12  and  16  or  14  and  18 , over the opposite ends of the lubricators L. The medial spacers  28  and first and second end spacers  36  are then placed between the opposed bracket portions  12 ,  16  and  14 ,  18 , and secured in place by the bracket assembly bolts  34 . These bolts  34  may be safety wired or in pairs or otherwise secured at this time, to prevent their backing out during operation of the machine. 
   When the parallel bracket portions  12 ,  16  and  14 ,  18  have been assembled with the lubricators L captured therein, the bracket portion subassemblies  12 ,  16  and  14 , 18  may be assembled on the drive shaft D. This is accomplished by installing the first and second end clamping bolts  42  through the diametric passages  38  of the first and second end spacers  36 , and tightening the lock nuts  46  thereon. The inner circumference of the bracket portions is slightly less than the circumference of the drive shaft D, so the bracket portion assemblies  12 ,  16  and  14 ,  18  may be drawn up tightly on the drive shaft D without their adjacent first and second ends  20  and  22  contacting one another. 
   At this point, the lubrication supply lines may be installed, generally as indicated in  FIGS. 1 and 2  of the drawings. Each of the bracket portions  12  through  18  includes a series of lubrication line passages therethrough. All four of the bracket portions  12  through  18  are identical to one another with the exception of the arrangement of the lubrication line passages therethrough, shown in  FIG. 3 . The coplanar first and third bracket portions  12  and  16  each include two relatively smaller lubrication line anchor passages  52  placed toward the inner edge of the bracket portions  12  and  16 , and two relatively larger lubrication line clearance passages  54  positioned radially outwardly from the bulkhead fitting passages  52 . These passages are reversed in the second and fourth bracket portions  14  and  18 , with the smaller anchor passages  52  being placed toward the outboard edges and the larger line clearance passages placed toward the inboard edges of the two portions  14  and  18 . 
   The reason for this placement is shown more clearly in  FIG. 1 . The series of automatic lubricators L installed in the apparatus  10  are placed with their outlet ports  56  staggered in opposite directions, i.e. every other unit L has the port  56  oriented to the right side of the installation, with those units L in between, having their ports  56  oriented to the left side. Each of the lubricators L has an outlet elbow  58  installed thereon, to which a lubricant supply line is connected. 
   As the entire apparatus and drive line D are rotating at perhaps a relatively high RPM, it is critical that the lubricant supply lines be anchored securely in some manner. Otherwise, the mass of the supply lines would impose a significant outward radial load on the lubricator L outlet ports, possibly damaging the assembly. Accordingly, each of the lubricant supply lines is supported by a bulkhead pass through fitting  60  installed in the smaller anchor passages  52  of the bracket portions  12  through  18 , with the lines passing through the larger clearance passages  54  which are axially aligned with the corresponding anchor passages and bulkhead fittings  60 . 
   It will be noted in  FIGS. 1 and 2  that the lubrication supply lines  62  extending from the right hand lubricator outlets  56  and elbows  58 , reverse direction to pass through the larger diameter clearance passages  54  to the inboard in the second and fourth bracket portions  16  and  18  to the right, and are anchored by the inboard bulkhead fittings  60  installed in the first and third bracket portions  12  and  14  to the left before extending to the left where they are connected to elbows  64  extending from the universal joint trunnions T and their bearing assemblies therein. The lubricant supply lines  66  extending from the left hand lubricator outlets  56  and elbows  58 , reverse direction to pass through the larger diameter clearance passages  54  to the outboard in the first and third bracket portions  12  and  14  to the left, and are anchored by the outboard bulkhead fittings  60  installed in the second and fourth bracket portions  16  and  18  to the right before extending to the right where they connect to a universal joint assembly (not shown) similar to the assembly J illustrated in  FIG. 1 , or other apparatus on the drive shaft D which requires periodic lubrication. 
   The lubrication supply lines  62  and  66  may be formed of relatively rigid material, such as the tubing used to form the supply lines  66 , or may alternatively be formed of relatively flexible line material, as used to form the supply lines  62 . The material and configuration of the lines is not critical, so long as they are supported or secured to the remainder of the rotating structure in order to avoid damage due to centrifugal loads during operation. 
   In conclusion, the present lubricating system serves to greatly reduce down time on large rotating machine components, by significantly reducing the manual maintenance which would otherwise be required to lubricate various bearings and components periodically. The present system also assures that each separate bearing assembly receives lubrication as required from a separate, dedicated lubrication source or supply, which rotates in unison with the bearing and supplies lubrication as needed while the machine is in operation. The automatic lubricators used with the present invention are capable of supplying lubricant for extended periods of time, perhaps up to a year. Lubricant quantity may be checked while the machine is in operation by means of a strobe light synchronized with the rotation speed of the shaft, or perhaps a digital camera or other means as desired. When the lubricant is depleted, the bracket assembly is easily removed and the lubricators refilled or replaced as desired. Alternatively, replacement bracket subassemblies with fresh lubricators installed therein may be provided, which would only require the connection of the first and second end clamping bolts and the lubricant supply lines to the lubricators. Such prefabricated subassemblies would save further on the limited down time which is infrequently required when using the present invention. 
   The present lubrication system is particularly well suited for installation on very large papermaking machinery, where operation is continuous or nearly so. Such machines generally produce significant revenue during their operation. Accordingly, the downtime associated with the periodic maintenance of such machinery, and the downtime associated with repair when damage occurs due to lack of lubrication, is economically significant to operations using such machinery. Thus, the present lubrication system will be greatly appreciated by various industries where continuous or nearly continuous, maintenance free operation of rotating machinery is critical to the industry. 
   It is to be understood that the present invention is not limited to the embodiment described above, but encompasses any and all embodiments within the scope of the following claims.

Technology Classification (CPC): 5