Patent Publication Number: US-2020282404-A1

Title: Helical gear well for crushing apparatus

Description:
FIELD OF THE INVENTION 
     This disclosure relates generally to the field of crushing and pertains to industrial crushing equipment applicable for use in the mining and aggregate industries. 
     In particular, disclosed is novel apparatus for facilitating the lubrication of gears in crushers whilst minimizing the probability of oil frothing. 
     More particularly, an improved helical recess design for a gear well component of a cone crusher is disclosed. The helical recess design aims to reduce stress concentrations in castings, mitigate frothing of oil, and improve the overall robustness and effectiveness of a gear well. 
     BACKGROUND OF THE DISCLOSURE 
     Conventional cone crushers  1  and related crushing devices typically employ an externally-threaded bowl  3 , a complementary internally-threaded adjustment ring  9  which surrounds a lower portion of the bowl  3 , and a complementary internally-threaded clamping ring  2  located above the adjustment ring  9  which also surrounds the bowl  3 . 
     During normal crushing operation, the clamping ring  2  remains fixed to the adjustment ring  9  and is held static in relation thereto, wherein the external threads of the bowl  3  are secured therebetween and the bowl  3  is therefore also held static in relation to the adjustment ring  9  and clamping ring  2 . 
     To remove a bowl  3  from a crushing device  1  for maintenance, install a bowl  3  into a crushing device  1 , or adjust a gap size between a mantle  19  and a cone  20  in situ (which, in turn, sets a material crush size), the bowl  3  is rotated via a peripheral drive motor  13  which turns a ring gear  11  attached to the bowl  3  via a web  10 . The bowl  3  is turned whilst the clamping ring  2  and adjustment ring  9  are held in a vertically stationary configuration, thus resulting in simultaneous linear vertical and rotational movement/displacement of the bowl  3 . The displacement of the bowl  3  sets a crushing gap distance between the mantle  19  and cone  20 , thereby setting the size of a comminuted product. 
     As shown in  FIG. 1 , a cone crusher  1  may have a clamping ring  2  connected to an adjustment ring  9  via fastening means  14 . The inside diameter portion of the clamping ring  2  and adjustment ring  9  may each comprise female threads which may comprise exaggerated flanks (e.g., buttress threads), without limitation. The threads of each of the components may be similar or identical, and they may compliment an external thread of a bowl  3 , without limitation. 
     The outside diameter portion of the bowl  3  may comprise a male thread (i.e., the bowl  3  may be externally-threaded). The outer thread of the bowl  3  may correspond to the thread provided to each of the adjustment ring  9  and the clamping ring  2  as shown in  FIG. 1 . The bowl  3  may be provided with a web  10  or other flange-like member which serves as a connection to an outer ring gear  11 . Alternatively, a ring gear  11  may be directly connected to the bowl  3 . 
     A drive motor  13  provided with a pinion  12  may cooperatively engage the ring gear  11  to drive/rotate the ring gear  11  and rotate the bowl  3 . By virtue of the drive motor  13  turning both the pinion  12  and the ring gear  11 , the web  10  and bowl  3  collectively rotate in unison with respect to the crushing device  1 , adjustment ring  9 , and clamping ring  2 . As the bowl  3  rotates, surfaces between the thread of the bowl  3  and the thread of the clamping ring  2  move with respect to each other. 
     The ring gear  11  may comprise external teeth which mate with complementary teeth on the pinion  12 . It is envisaged that other drive mechanisms (e.g., worm gears, helical gears, spur gears, and like arrangements) may be equally employed between the drive motor  13  and bowl  3 , without limitation. 
     To facilitate installation of the bowl  3  to the crushing device  1 , removal of the bowl  3  from the crushing device  1 , or vertical movement of the bowl  3  relative to the crushing device  1  (i.e., in order to set or adjust a crush size or open/close the crushing gap between a mantle  19  and a cone  20 ), fastening means  14  connecting the clamping ring  2  to the adjustment ring  9  may be disengaged to allow the drive motor  13  to more easily turn the bowl  3  via the pinion  12  and ring gear  11 . To set a fixed crushing gap size for crushing operations, the clamping ring  2  may be secured to the adjustment ring  9  via re-engagement of the fastening means  14 . 
     As shown, fastening means  14  may comprise fasteners which pass through the clamping ring  2  and threadedly engage the adjustment ring  9 . By securing the clamping ring  2  to the adjustment ring  9  with the fastening means  14 , the bowl  3  can be held against both rotational and vertical movement with respect to the clamping ring  2  and neighboring adjustment ring  9 . 
     Industrial crushers such as cone crushers  1  also traditionally have gear wells  100  comprising a body  106 , and a uniform-depth partially-annular recess  110 . The partially-annular recess  110  generally comprises a non-helical, partially-annular floor (which may be planar, frusto-conical, or otherwise radially-inwardly tapered as shown). The conventional gear well  100  is generally configured to receive an annular driven gear  15  (e.g., which is typically provided as a miter or bevel gear). 
     Traditionally, a large cutout  120  extends downwardly from a portion of the partially-annular recess  110  at an abrupt right angle or similar, forming a sharp corner transition  112  between the generally horizontally positioned partially-annular recess floor  111  and the substantially vertical wall  126  of the large cutout  120 . The large cutout  120  serves to provide ample clearance space for a drive pinion  18  to be situated and rotate unhindered—the purpose of the drive pinion  18  being to move the driven gear  15 . The large cutout  120  is normally configured as a substantially rectangular cavity as shown in  FIGS. 2-5 . 
     A drive motor (not shown or labeled) rotates a drive shaft  17  which is provided with the drive pinion gear  18  at its distal end. The drive pinion gear  18  in turn, drives/rotates the driven gear  15  which may be integrally-provided to or attached to an eccentric  4  having a central opening. A shaft  16  may pass through the eccentric  4 , driven gear  15 , and body  106  of the gear well  100 . A central opening  128  in the gear well  100  may be tapered and serve as a thrust bearing for supporting shaft  116  as suggested in  FIGS. 1, 4, and 5 . 
     Often, the sharp angle transition  112  between the partially-annular recess  110  and the rectangular cavity  120  can cause a significant rise in stress concentration during operation and can be a common mode of failure of a gear well  100  (e.g., via cracking). Thin wall sections adjacent the sharp angle transition  112  may be present from castings formed by current methods and designs; and, over time, even ductile gear well  100  castings can begin to see evidence of hairline cracks and formation of stress fractures originating near the sharp angle transition  112 . 
     Another problem with this sharp angle transition or corner  112 , is that oil lubricating the gearing couple  15 ,  18  can become turbulent as it flows over the sharp angle transition  112  from the floor  111  of the partially-annular recess  110 , past the vertical side wall  126 . This “spilling over” or “waterfalling” can lead to undesirable frothing in the power train of the crusher  1 . 
     OBJECTS OF THE INVENTION 
     It is, therefore, an object of the invention to circumvent the aforementioned drawbacks associated with prior art gear wells for crushers. 
     It is a further object of some non-limiting embodiments of the invention to extend the useful and/or serviceable life of a gear well, without limitation. 
     It is yet a further object of some non-limiting embodiments of the invention to improve the hydrodynamic performance of a gear well and reduce lubricating oil frothing during continuous operation, without limitation. 
     These and other objects of the invention will be apparent from the drawings and description herein. Although every object of the invention is believed to be attained by at least one embodiment of the invention, there is not necessarily any one embodiment of the invention that achieves all of the objects of the invention. 
     BRIEF SUMMARY OF THE INVENTION 
     Disclosed, is a gear well  200  for a crusher  1 . According to some preferred embodiments, the gear well  200  may comprise a body  206 , a recess  210 , and a pinion clearance floor  222 . The recess  210  is preferably configured to be positioned adjacent a driven gear  15  for an eccentric  4 . The recess further  210  comprises a floor  211 . The gear well  200  may be characterized in that its recess  210  comprises a helical, non-uniform depth recess having a high point  212 A and a low point  212 B (and a distance along a Z-axis or centerline axis  206  of the gear well  200  separating the high point  212 A from the low point  212 B). Accordingly, rather than extending to a sharp corner transition  112  and then to an orthogonal sidewall  126  as done with prior art designs, the helical floor  211  of the improved helical recess  210  instead intersects or blends with the pinion clearance floor  222  adjacent the low point  212 B (e.g., without vertical sidewall  126  and/or without sharp corner transition  112 ). The helical, non-uniform depth recess  210  may be configured for improving the strength of a gear well  200  by removing sharp corner transition  112  and the stress rising factors associated with employing a right-angle thin wall in a casting. Alternatively, or in addition to this, the helical recess  210  may be configured to reduce or otherwise mitigate oil frothing within the gear well  200 . 
     According to some embodiments, an angular distance theta (e) representing the angular span of the recess  210  around a centerline axis  206  of the gear well  200  and extending between the low point  212 B of the recess  210  and the high point  212 A of the recess  210 , may be greater than  45  degrees, but less than 335 degrees, without limitation. In other words, the helix/spiral path of the recess  210  is less than one revolution around axis  206 . 
     For example, according to some embodiments, the angular distance theta (e) representing the angular span of the recess  210  around a centerline axis  206  of the gear well  200  and extending between the low point  212 B of the recess  210  and the high point  212 A of the recess  210 , may be greater than 90 degrees, but less than 270 degrees, without limitation. 
     As another example, in some embodiments, the angular distance theta (e) representing the angular span of the recess  210  around a centerline axis  206  of the gear well  200  and extending between the low point  212 B of the recess  210  and the high point  212 A of the recess  210 , may be greater than 135 degrees, but less than 225 degrees, without limitation. 
     As yet another example, in some embodiments, and as shown in exemplary and non-limiting  FIGS. 6-9 , the angular distance theta (e) representing the angular span of the recess  210  around a centerline axis  206  of the gear well  200  and extending between the low point  212 B of the recess  210  and the high point  212 A of the recess  210  may be approximately  180  degrees, without limitation. 
     A crusher  1  is also disclosed. The crusher  1  may comprise a cone  20  supported by a shaft  16 —the cone  20  forming a first crushing surface. The crusher  1  may further comprise a mantle  19  positioned adjacent the cone  20  the mantle  19  forming a second crushing surface. The shaft  16  may be disposed within an eccentric  4  and supported by a gear well. The eccentric  4  may be operably coupled to a driven gear  15 . The driven gear  15  may be situated within or positioned adjacent a recess  210  of the gear well  100 . 
     The gear well  200  may have a body  206 ; a recess  210  configured to be positioned adjacent the driven gear  15  associated with the eccentric  4 ; and a pinion clearance floor  222 . Moreover, the recess  210  may comprise a floor  211  which may be configured to convey oil. 
     The crusher  1  may be characterized in that the floor  211  of the recess  210  in the gear well  200  is preferably helical in nature (i.e., in the form of a spiral, coil, helix, or the like) as shown in  FIGS. 6-9 . In other words, the gear well  200  may be characterized in that it comprises a helical, non-uniform depth recess having a high point  212 A and a low point  212 B, rather than existing in the same plane along a Z-axis or centerline axis  106  as seen with the prior art design of  FIGS. 2-5 . A vertical distance along a Z-axis or a distance along centerline axis  206  separates the high point  212 A from the low point  2128 . Accordingly, rather than extending to a sharp corner transition  112  and then to an orthogonal sidewall  126 , the floor  211  of the recess  210  according to present embodiments instead intersects or blends with the pinion clearance floor  222  adjacent the low point  212 B. 
     The helical, non-uniform depth recess  210  may be configured for improving the strength of a gear well  200 . Alternatively, or in addition to this, the recess  210  may be configured to reduce or otherwise mitigate oil frothing within the gear well  200 . 
     The above-described gear well  200  having a helical non-uniform depth recess  210  may be installed into a crusher  1  according to some embodiments. Steps may include providing a replacement gear well  200  as described above, and having a body  206 , a recess  210  configured to be positioned adjacent a driven gear  15  for an eccentric  4 , a pinion clearance floor  222 , and a floor  211  provided to the recess  210 . Steps may also include removing a gear well  100  having a partially-annular recess  110  from a crusher  1  and installing the replacement gear well  200  into the crusher  1 , without limitation. 
    
    
     
       BRIEF SUMMARY OF THE DRAWINGS 
       To complement the description which is being made, and for the purpose of aiding to better understand the features of the invention, a set of drawings illustrating new and novel gear well apparatus for improving crushers is attached to the present specification as an integral part thereof, in which the following has been depicted with an illustrative and non-limiting character. It should be understood that like reference numbers used in the drawings (if any are used) may identify like components. 
         FIG. 1  illustrates a crusher  1  according to the prior art which may benefit from embodiments of the invention. 
         FIG. 2  illustrates a partial zoom cutaway view of a traditional gear well  100  found in the crusher  1  shown in  FIG. 1 . 
         FIG. 3  shows a side view of the gear well  100  shown in  FIGS. 1 and 2 . 
         FIG. 4  shows a side cutaway view of the gear well  100  shown in  FIG. 3 . 
         FIG. 5  is an isometric cutaway view of the gear well  100  shown in  FIGS. 1-4 . 
         FIG. 6  illustrates a partial zoom cutaway view of a gear well  200  according to some exemplary non-limiting embodiments, which may be used to improve the crusher  1  shown in  FIG. 1 . 
         FIG. 7  shows a side view of the gear well  200  shown in  FIG. 6 . 
         FIG. 8  shows a side cutaway view of the gear well  200  shown in  FIG. 7 . 
         FIG. 9  is an isometric cutaway view of the gear well  200  shown in  FIGS. 6-8 . 
         FIG. 10  is a schematic diagram showing a possible exemplary range of angular span for a helical recess  210  according to some non-limiting embodiments. 
         FIG. 11  suggests a method for installing a gear well  200  according to some embodiments. 
     
    
    
     In the following, the invention will be described in more detail with reference to drawings in conjunction with exemplary embodiments. 
     DETAILED DESCRIPTION 
     While the present invention has been described herein using exemplary embodiments of a gear well  200  for a crusher  1  and a method of installing the same, it should be understood that numerous variations and adaptations will be apparent to those of ordinary skill in the field from the teachings provided herein. 
     The detailed embodiments shown and described in the text and figures should not be construed as limiting in scope; rather, all provided embodiments should be considered to be exemplary in nature. Accordingly, this invention is only limited by the appended claims. 
     The disclosure of every patent, patent application, and publication cited, listed, named, or mentioned herein is hereby incorporated by reference in its entirety, for any and all purposes, as if fully set forth herein. 
     While this subject matter has been disclosed with reference to specific embodiments, it is apparent that other embodiments and variations can be devised by others skilled in the art without departing from the true spirit and scope of the subject matter described herein. The appended claims may include some, but not all of such embodiments and equivalent variations. 
     The described embodiments are to be considered in all respects only as illustrative and not restrictive. The scope of the invention is, therefore, indicated and governed only by the appended claims, rather than by the foregoing description. All embodiments which come within the meaning and range of equivalency of the claims are to be embraced within their scope. 
     The inventors have recognized a novel and heretofore unappreciated design for a gear well  200  of crushing devices  1 —in particular, those used in cone crusher drive trains, without limitation. 
     Turning now to prior art  FIG. 1 , a crusher  1  (e.g., a cone crusher) may comprise an internally-threaded clamping ring  2  and an externally-threaded bowl  3  threadedly-engaging the clamping ring  2 . The bowl  3  may operatively engage a mantle  19  which forms an upper crushing surface. An internally-threaded adjustment ring  9  also threadedly-engages the bowl  3 . A web  10  may extend from the bowl  3  and connect the bowl  3  to an outer ring gear  11 . The outer ring gear  11  may communicate with a pinion  12  driven by a peripheral drive motor  13 . 
     Upon powering the peripheral drive motor  13 , the pinion  12  rotates and thus turns the outer ring gear  11 , web  10 , and connected bowl  3 . Upon rotational movement of the bowl  3 , a crushing gap (i.e., distance between the mantle  19  and cone  20 ) may be adjusted, thereby changing the size of comminuted product produced. 
     Fastening means  14  may be provided between the adjustment ring  9  and the clamping ring  2  to prevent relative movement between parts  2 ,  9 ,  3  of the crusher  1  during operation. The fastening means  14  may be loosened or removed to allow removal or adjustment of the parts  2 ,  9 ,  3  of the crusher  1 . 
     On a lower internal section of the crusher  1 , a cone  20  forming a lower crushing surface is supported by a shaft  16  guided by an eccentric  4  which surrounds the shaft  16 . The eccentric  4  is coupled to a driven gear  15  (e.g., at a lower portion of the eccentric  4 ). Driven gear  15  may alternatively be formed monolithically with the eccentric  4 . A drive shaft  17  configured to be coupled to a drive motor/transmission output (not shown), powers the crusher  1  by rotating a drive pinion  18  thereon. The drive pinion  18  makes contact with the driven gear  15 . The driven gear  15  and drive pinion  18  are typically of the miter or bevel gear type, without limitation. 
     A conventional gear well  100  (e.g., the one shown in  FIGS. 2-5 ) may be placed below the eccentric  4  and may support the eccentric  4  and/or serve as a lower support bearing (e.g., a thrust bearing) for shaft  16 , without limitation. A bearing may allow relative rotational movement between eccentric  4  and conventional gear well  100 . The conventional gear well  100  comprises first drive shaft bearing  102  (e.g., sleeve, journal, or race), a second drive shaft bearing  103  (e.g., sleeve, journal, or race), and an opening  124  therebetween, in order to support drive shaft  17  and provide lubrication or reduce friction between portions of the conventional gear well  100  and the drive shaft  17 . 
     The body  106  of the conventional gear well  100  is provided with a non-helical, uniform-depth, partially-annular recess  110  which has a partially-annular recess floor  111 . Points along the partially-annular recess floor  111 , may be defined as a series of polar coordinates that share a similar radius and also substantially fall within the same horizontally-oriented plane along a height axis of the crusher or centerline axis  106  of the conventional gear well  100 . In other words, points along the partially-annular recess floor  111  may share a similar elevation or “Z-axis” position within crusher  1 , if they share a similar radial location. In other words, with prior gear wells  100 , two separate points on the floor  111  of the recess  110  which are equidistant from centerline axis  106  would also share a common position along centerline axis  106 , without limitation. 
     A junction/interruption in the non-helical, uniform depth partially-annular recess  110  exists, where there is a conventional sharp corner transition  112  to a substantially vertical sidewall  126  forming a portion of a large cutout  120 . The large cutout  120  further comprises a floor  122  which provides a clearance for drive pinion  18 . The large cutout  120  may at least partially serve as a basin for lubricating oil intended for drive pinion  18  and driven gear  15 . The sidewall  126  and floor  111  are generally perpendicular/orthogonal to each other and joined by the sharp corner transition  112  at their intersection as shown in the drawings. 
     A problem with the prior art gear well  100  design shown in  FIGS. 1-5  is that high stresses within the gear well  100  may cause cracking along or adjacent the conventional sharp corner transition  112 , which tends to comprise a thin wall of cast iron. 
     Another problem with the prior art gear well  100  design shown in  FIGS. 1-5  is that oil contained on surfaces of the driven gear  15  drip down into the top surfaces of partially-annular recess  110  and due to a small clearance therebetween, the oil may be churned by teeth of the driven gear  15  as the driven gear  15  rotates. Moreover, the churned oil may further froth due to high turbulence as it cascades over the sharp corner transition  112  and splashes into the catch basin formed by large cutout  120 , sidewall  126 , and pinion clearance floor  122 . 
     Turning now to  FIGS. 6-9 , an improved gear well  200  according to some embodiments may similarly comprise a first drive shaft bearing  202  (e.g., sleeve, journal, or race) and a second drive shaft bearing  204  (e.g., sleeve, journal, or race) which are configured to support drive shaft  17  and a drive pinion  18  thereon. An opening  224  may extend therebetween. 
     A driven gear  15  (to which the pinion  18  engages to rotate the eccentric  4 ) is configured to spin freely within a helical recess  210  of substantially non-uniform depth. As shown, the helical recess  210  may comprise a helical recess floor  211  which blends with a pinion clearance floor  222  located under and providing clearance for drive pinion  18 . The helical recess floor  211  extends from a high point  212 A (e.g., at the start of the helical recess  210 ) to a low point  212 B (e.g., at the end of the helical recess  210 ) as shown. The helical recess  210  removes the sharp corner transition  112  and large vertical wall  126 , and instead blends recess  210  into the large cutout area configured to receive pinion  18 . 
     By virtue of the sloped floor  211 , oil lubricating the drive pinion  18  and driven gear  15  can slide down, via gravity, with little turbulence, and re-lubricate the drive pinion  18 . The oil may pool adjacent the pinion within a basin area formed by pinion clearance floor  222 . Oil received by surfaces of the drive pinion  18  while the pinion  18  is rotating may be subsequently brought into contact with the driven gear  15 , thereby lubricating the gearing couple and tooth surfaces therebetween. The floor  211  of the helical recess  210  may thereby be configured to reduce frothing of lubricating oil, since the gear well  200  substitutes prior art features  110 ,  111 ,  112 ,  126  which allow oil to splash around inside the crusher  1  (e.g., spill over a conventional sharp corner transition  112  between a conventional partially-annular recess floor  111  and a sidewall  126  of a conventional large cutout  120 ). 
     Moreover, due to the helical design, overall strength of the gear well  200  may be increased, and the clearance between pooled oil and rotating teeth of the driven gear  15  may be increased due to the gradual increase in separation between high point  212 A and low point  212 B as the recess  210  traverses around centerline axis  206 . 
     Turning now to  FIG. 10 , it will be appreciated that a helical, non-uniform depth recess  210  described herein may start at a high point  212 A, and extend to a low point  212 B as it traverses around a gear well  200 , without limitation. The shortest angular distance between the high point  212 A and low point  212 B may be set to just slightly more or greater than the width of the drive pinion  18 , so as to configure cutout  220  to provide enough clearance for drive pinion  18  to turn, whilst maximizing the circumferential length/span of the helical recess  210 . By making helical recess  210  longer, its slope can be made more gradual. By making helical recess  210  shorter, its slope can be made steeper. It should be understood that the rise over run (e.g., relative slope, grade, steepness) of the floor  211  of the helical recess  210  may be constant as shown, or it may vary at different angular locations around axis  206 . Accordingly, embodiments of a gear well  200  wherein recesses  210  comprise “compound” or “variable pitch” helix geometries are completely within the scope of this disclosure. 
     An angular distance theta (e) may represent the angular span of a helical recess  210  for a gear well  200  according to certain embodiments of the invention. This theta θ angle may be conceptualized as the circular distance the helical recess  210  spans or travels circumferentially, around the centerline axis  206  of the gear well  200  in its spiral/helical path. Theta θ angle may alternatively be conceptualized as the circular distance the helical recess  210  spans or travels circumferentially, around the Z-Axis or centerline axis  206 . Theta θ angle may, as shown, be represented in degrees with respect to polar coordinates for purposes of this disclosure, without limitation; wherein zero degrees may be representative of the location of intersection between the helical recess floor  211  and the pinion clearance floor  222 . 
     Most-preferred envisaged embodiments within the scope of this disclosure may have a theta θ angle (e.g., an absolute theta θ angle) which is greater than approximately 90 degrees, but less than approximately 270 degrees, for example, 180 degrees as shown, without limitation. 
     In the non-limiting embodiment shown in  FIGS. 6-9 , the helical recess  210  is shown to extend 180 degrees around the gear well  200 , wherein theta θ may be approximated as 180 degrees. This is because the high point  212 A of the helical recess floor  211  is positioned at a polar angular coordinate comprising 180 degrees and the low point  212 B of the helical recess floor  211  is positioned at a polar angular coordinate comprising zero degrees, and therefore, the two points  212 A,  212 B are polar opposites. 
     It should be noted that the two points  212 A,  212 B do not share the same location along a central centerline axis  206  of the gear well, and therefore, also have different vertical locations within a crusher  1  along a Z-axis. Accordingly, the helical recess  210  disclosed encourages oil to flow less-turbulently downward along the floor  211  surface, via gravity, and into the large cavity sump area defined by pinion clearance floor  222 . In this regard, pinion  18  can remain well-lubricated without the negative effects of oil frothing common with traditional gear wells  100 . 
       FIG. 9  suggests that theta θ may exceed 180 degrees in some preferred embodiments (e.g., approximately 335 degrees) or be less than 180 degrees; however envisaged embodiments within the scope of this disclosure comprise theta θ angles which do not approach 360 degrees. Preferred embodiments of a gear well  200  may comprise a theta θ angle which is at least 90 degrees, but no more than 270 degrees. For example, a theta θ angle too small may result in too steep of a helical recess  210 , thereby reducing the effectiveness of oil froth mitigation. 
     In some embodiments, a method of installing a gear well  200  may be performed. In some embodiments, the method may involve assembling parts of a crusher  1  with a gear well  200  described herein, to form an improved crusher  1  comprising a gear well  200  having a helical recess  210 . 
     Turning now to  FIG. 11 , in some embodiments, a method of retrofitting a crusher  1  with a gear well  200  according to embodiments of the invention described herein may be performed. As suggested in the figure, the method may involve removing an old gear well  100  having a non-helical uniform depth partially-annular recess  110  from a crusher  1  (e.g., a gear well  100  as shown and described in prior art  FIGS. 2-5 ), and then replacing it with a gear well  200  described herein (e.g., a gear well  200  as shown and described in  FIGS. 6-9 ), to form an improved crusher  1  comprising a gear well  200  having a helical recess  210 . 
     A contractor or other entity may provide a gear well  200  as substantially described herein, or may practice any one of the methods or method steps described herein, without limitation. Moreover, a contractor or other entity may provide portions or components of a gear well  200  as substantially described herein, or may practice one or more of the method steps described herein, without limitation. A contractor may modify retrofit an existing gear well  100  by welding, machining, adding material, melt-casting, or using other fabrication techniques in order to arrive at a gear well  200  according to present embodiments. 
     A contractor or other entity may provide a crushing device  1 , such as a cone crusher which contains a gear well  200  according to embodiments described herein. Or, a contractor or other entity—such as a client, customer, or user of a crusher  1 , may operate the same in whole, or in part. A contractor or other entity may install a gear well  200  according to embodiments described herein, into a crusher  1 , without limitation. 
     A contractor or other entity may receive a bid request for a project related to designing, fabricating, delivering, installing, operating, or performing maintenance on a gear well  200  disclosed herein, without limitation. A contractor or other entity may offer to design a similar system, device, or apparatus, or provide a process or service pertaining thereto, for a client. A contractor or other entity may offer to retrofit or may actually retrofit an existing gear well  100  with any one or more of the components or physical features described herein (e.g., helical recess  210 , sloped floor  211 , high  212 A and low  212 B points, or the like, without limitation), to make an improved gear well  200  for a crusher  1  or to improve or refurbish a crusher  1 . It is further anticipated that a contractor or other entity may, in accordance with the inventive concepts and teachings described herein, offer for sale, sell to, deliver to, and/or install one or more of the gear wells  200  described herein for an end user, client, or customer, without limitation. 
     Although the invention has been described in terms of particular embodiments and applications, it should be appreciated that one of ordinary skill in the art, in light of this teaching, can generate additional embodiments and modifications without departing from the spirit of or exceeding the scope of the claimed invention. 
     REFERENCE NUMERAL IDENTIFIERS 
     
         
           1 . Crusher 
           2 . Internally-threaded clamping ring 
           3 . Externally-threaded bowl 
           4 . Eccentric 
           9 . Internally-threaded adjustment ring 
           10 . Web 
           11 . Outer ring gear 
           12 . Pinion 
           13 . Peripheral drive motor 
           14 . Fastening means 
           15 . Driven gear 
           16 . Shaft 
           17 . Drive shaft 
           18 . Drive pinion 
           19 . Mantle 
           20 . Cone 
           100 . Gear well (conventional) 
           102 . First drive shaft bearing (e.g., sleeve, journal, or race) 
           103 . Second drive shaft bearing (e.g., sleeve, journal, or race) 
           106 . Body (conventional) 
           108 . Centerline axis (conventional) 
           110 . Non-helical partially-annular recess (conventional, e.g., of “uniform depth”) 
           111 . Non-helical, uniform depth partially-annular recess floor (conventional) 
           112 . Sharp corner transition (conventional) 
           120 . Large cutout (conventional) 
           122 . Pinion clearance floor (conventional) 
           124 . Opening 
           126 . Sidewall of large cutout (conventional) 
           128 . Tapered opening/thrust bearing (conventional) 
           200 . Gear well 
           202 . First drive shaft bearing (e.g., sleeve, journal, or race) 
           204 . Second drive shaft bearing (e.g., sleeve, journal, or race) 
           206 . Centerline axis 
           210 . Helical recess (i.e., of “non-uniform” depth) 
           211 . Helical recess floor 
           212 A. High point (e.g., start of Helical, non-uniform depth recess) 
           212 B. Low point (e.g., end of Helical, non-uniform depth recess) 
           222 . Pinion clearance floor 
           224 . Opening 
           228 . Tapered opening/thrust bearing