Patent Publication Number: US-2020290849-A1

Title: Support system for hoist system

Description:
REFERENCE TO RELATED APPLICATION 
     This application claims the benefit of co-pending, prior-filed U.S. Provisional Patent Application No. 62/819,238, filed Mar. 15, 2019, the entire contents of which are incorporated by reference. 
    
    
     FIELD 
     The present disclosure relates to a hoist system, and more particularly to a support system for a hoist system. 
     BACKGROUND 
     A mining rope shovel may include a hoist system for lifting a digging attachment. 
     SUMMARY 
     In one independent aspect, a support system is provided for a gear case of a rope shovel. The gear case supports a gear drive configured to drive rotation of a hoist drum, and the gear case includes a first end, a second end, and a longitudinal axis extending between the first end and the second end. The support system includes: a coupling for securing the gear case against translational movement relative to a rotating frame, the coupling oriented orthogonally to the longitudinal axis and configured to engage the rotating frame and a portion of the gear case; and a support member configured to be coupled to the rotating frame of the rope shovel and supporting the gear case, the support member permitting translational movement of the gear case relative to the rotating frame to accommodate flexing of the rotating frame. 
     In another independent aspect, a support system is provided for a gear case of a rope shovel. The gear case supports a gear drive configured to drive rotation of a hoist drum, and the gear case further including a first end, a second end, and a longitudinal axis extending between the first end and the second end. The support system includes: a first coupling configured to be coupled between a rotating frame of the rope shovel and the first end of the gear case, the first coupling inhibiting movement of the gear case in a direction that is parallel to the longitudinal axis and inhibiting movement of the gear case in a direction that is perpendicular to the longitudinal axis; and a second coupling configured to be coupled between the rotating frame and the second end of the gear case, the second coupling inhibiting movement of the gear case in a direction that is perpendicular to the longitudinal axis while permitting movement of the gear case relative to the rotating frame in a direction parallel to the longitudinal axis to accommodate flexing of the rotating frame. 
     In yet another independent aspect, a transmission system for driving a hoist drum of a rope shovel includes: a housing having a first end, a second end, and a longitudinal axis extending therebetween; a plurality of gears supported within the housing, the gears transmitting a driving torque to the hoist drum to rotate the hoist drum; and structure for supporting the housing relative to a rotating frame of the rope shovel. The structure includes: a coupling between a rotating frame of the rope shovel and the housing, the coupling inhibiting translational movement of the housing in a direction parallel to the longitudinal axis, and a translating connection engaging a portion of the housing and supporting the housing for translational movement along the longitudinal axis. 
     Other aspects of the disclosure will become apparent by consideration of the detailed description and accompanying drawings. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a perspective view of a rope shovel. 
         FIG. 2  is a support system for a hoist system gear case for the rope shovel of  FIG. 1 . 
         FIG. 3  is a side view of a support system for a hoist system gear case according to another embodiment. 
         FIG. 4  is a side view of the gear case of  FIG. 3 . 
         FIG. 5  is a perspective view of a portion of the gear case of  FIG. 3   
         FIG. 6  is another perspective view of another portion of the gear case of  FIG. 3 . 
         FIGS. 7A and 7B  illustrate two cross-sectional views of the portion of the gear case of  FIG. 6 . 
         FIG. 8  is a support system for a hoist system gear case according to yet another embodiment. 
         FIG. 9  is a support system for a hoist system gear case according to still another embodiment. 
         FIG. 10  is a support system for a hoist system gear case according to yet another embodiment. 
         FIG. 11  is a support system for a hoist system gear case according to still another embodiment. 
         FIG. 12  is a support system for a hoist system gear case according to yet another embodiment. 
         FIG. 13  is a support system for a hoist system gear case according to still another embodiment. 
         FIG. 14A  is a support system for a hoist system gear case according to yet another embodiment, while  FIG. 14B  illustrates a cross-sectional view of the support system of  FIG. 14A . 
     
    
    
     DETAILED DESCRIPTION 
     Before any embodiments are explained in detail, it is to be understood that the disclosure is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the following drawings. The disclosure is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting. Use of “including” and “comprising” and variations thereof as used herein is meant to encompass the items listed thereafter and equivalents thereof as well as additional items. Use of “consisting of” and variations thereof as used herein is meant to encompass only the items listed thereafter and equivalents thereof. Unless specified or limited otherwise, the terms “mounted,” “connected,” “supported,” and “coupled” and variations thereof are used broadly and encompass both direct and indirect mountings, connections, supports, and couplings. 
     In general, the present disclosure relates to a support system for a hoist system, e.g., of a rope shovel. The support system assists in evenly distributing loads exerted on the connections between the hoist system gear case and the rotating frame of the shovel, while also permitting movement to accommodate flexing of the rotating frame. 
       FIG. 1  illustrates an excavating machine such as a rope shovel  10  including a base  14 , a boom  26 , an elongated member or handle  30 , and a digging attachment or dipper  34 . The base  14  includes a lower portion  16  supported by traction elements (e.g., crawlers  18 ) and an upper portion or rotating frame  22  supported for rotation relative to the lower portion  16  about an axis. 
     The boom  26  includes a first end coupled to the rotating frame  22 , a second end  50  opposite the first end. A boom sheave  54  is supported adjacent the second end  50  of the boom  26 . Saddle blocks  52  and a shipper shaft  56  are supported on the boom  26  between the first end and the second end  50 . The boom  26  is pivotable relative to the rotating frame  22  about the first end. In the illustrated embodiment, a support member  28  is coupled between the rotating frame  22  and the boom  26  and limits the pivoting movement of the boom  26  relative to the rotating frame  22 . In other embodiments, the boom  26  is supported by a gantry or other structure. 
     The handle  30  is movably coupled to the boom  26  and includes a first end  58  and a second end  60 . In the illustrated embodiment, the handle  30  is supported for translational and rotational movement relative to the boom  26  by the shipper shaft  56  and the saddle blocks  52 . In the illustrated embodiment, the dipper  34  is fixed to the second end  60  of the handle  30 . In other embodiments, the machine  10  includes a bucket that is pivotable relative to the handle  30  about the second end  60 . In other embodiments, the handle may be constructed in a different manner and/or may be supported with respect to the boom in a different manner. For example, the handle may be a telescoping member that is pivotally connected to the boom by a yoke, and the handle may be driven to extend and retract by actuation of one or more fluid cylinders. 
     The shovel  10  further includes a hoist system  38  supported on the rotating frame  22  for reeling in and paying out a hoist rope or cable  42 . The hoist system  38  includes a drum  40  about which a portion of the cable  42  is wrapped. The cable  42  is secured between the drum  40  and the dipper  34 , passing over the boom sheave  54 . The dipper  34  is raised or lowered relative to the boom sheave  54  as the cable  42  is reeled in or paid out, respectively. 
     The hoist drive system  38  includes one or more gears that form a gear drive or transmission for driving the drum  40  to take in or let out the cable  42 . As shown in  FIG. 3 , in the illustrated embodiment, the transmission is supported within a housing of a gear case  90  positioned adjacent an end of the drum  40 . The gear case  90  is supported on the rotating frame  22 . The gear case  90  includes a first end  94  and a second end  98 . In the illustrated embodiment, the first end  94  is positioned proximate the front end of the rotating frame  22  (i.e., proximate the boom  26 — FIG. 1 ), while the second end  98  is positioned toward a rear end of the rotating frame  22  (i.e., on a side opposite the boom  26 ). A tensile force or hoist force F ( FIG. 3 ) is exerted in the cable  42 , which extends from the drum  40  to the boom sheave  54  ( FIG. 1 ). 
       FIG. 2  illustrates a system for supporting the gear case  90  according to an embodiment. The gear case  90  is coupled to the rotating frame (not shown) by a pin  318  adjacent the second end  98 . The first end  94 , on the other hand, is not pinned to the rotating frame  22  but rather is permitted to slide in a direction parallel to a longitudinal axis of the gear case  90  extending between the first end  94  and the second end  98  (e.g., in a forward and rearward direction). In the illustrated embodiment, the first end  94  is supported for sliding movement by a pad (not shown) formed from a dissimilar material. In addition, a retainer  302  includes horizontal stop surfaces  304  to inhibit lateral movement and/or twisting of the gear case  90 . In some embodiments, the retainer  302  may include vertical stop surfaces to inhibit the gear case  90  from lifting away from the rotating frame  22 . 
     As shown in  FIGS. 3 and 4 , in another embodiment of a system for supporting a gear case  90  the rotating frame  22  includes a first lug  106  and a second lug  110 . A first pin  114  extends through the first lug  106  and through the gear case  90  proximate the first end  94 . Similarly, a second pin  118  extends through the second lug  110  and through the gear case  90  proximate the second end  98 . In addition, as shown in  FIG. 5 , a tensioning member (e.g., a rod bolt  126 ) is positioned adjacent to the first end  94  and is coupled between the gear case  90  and the rotating frame  22 . The bolt  126  applies a clamping force  75  in a direction substantially normal to the rotating frame  22  (i.e., vertically) and biases the first end  94  of the gear case  90  toward the rotating frame  22 . Also, as shown in  FIG. 6 , a wedge  130  is positioned adjacent the second end  98 , between the gear case  90  and the rotating frame  22 , and biases the second end  98  of the gear case  90  away from the rotating frame  22 . In the illustrated embodiment, the wedge  130  is a threaded pin wedge block. 
     During operation of the shovel  10 , the rotating frame  22  can flex and alter a distance between the first lug  106  and the second lug  110 . For example, the rotating frame  22  may be subjected to a bending load condition that causes the rotating frame  22  to flex about a flexure point  80  ( FIG. 4 ). The gear case  90  and/or the rotating frame  22  lugs  106 ,  110  provide a clearance fit with the first pin  114  and/or the second pin  118  to accommodate the movement of the lugs  106 ,  110 . The clearance fit may, for example, ease the assembly of the rotating frame  22 , lugs  106 ,  110 , and gear case  90 . In some embodiments, the clearance around the first pin  114  is greater than the maximum deflection of the lugs  106 ,  110 . In some embodiments, the total clearance around the pins  114 ,  118  is greater than the maximum deflection of the lugs  106 ,  110 , and the clearance around the first pin  114  is larger than the clearance around the second pin  118 . In some embodiments, the total clearance is less than the maximum deflection but sufficient to significantly reduce the lateral load transfer through the pin connections caused by deflection of the rotating frame  22 . 
     The clamp force  75  exerted by the bolt  126  biases the gear case  90  and the first pin  114  toward the lower surface of the first lug  106 , while the wedge  130  biases the gear case and second pin  118  toward the upper surface of the second lug  110  as shown in  FIG. 3  by wedge force  76 . As a result, the bolt  126  and the wedge  130  maintain a substantially uniform load flow through the pin connections  114 ,  118  even when the rotating frame  22  is subject to flexing. Stated another way, the hoist force F results in a first force  77  ( FIG. 3 ) exerted toward the rotating frame  22  at the first lug  106  (e.g., a forward lug), and a second force  78  exerted away from the rotating frame  22  at the second lug  110  (e.g., the rearward lug). A third force  79  is oriented in a direction from the second lug  110  to the first lug  106 . The bolt  126  provides clamping force  75 , which acts to pre-load the first pin  114  at the first lug  106 , and the wedge  130  acting with the wedge force  76  acts to pre-load the second pin  118  at the second lug  110 . The pre-load forces assist in maintaining a substantially uniform load at the pin connections  114 ,  118 . The clamping force  75  exerted by the bolt  126  also biases the first pin  114  tightly against the gear case  90  to reduce vibrations that may occur during operation (i.e., the bolt  126  removes the clearance between the first pin  114  and the gear case  90 ). In addition, horizontal or transverse loads such as the third force  79  can be accommodated by the sides of the lugs  106 ,  110 . The allowable deformation or stretch of the bolt  126  is greater than the deflection of the rotating frame  22  in order to avoid yielding of the bolt  126  or loss of clamp load. 
       FIGS. 7A and 7B  illustrate the operation of the wedge  130  as shown in  FIG. 6 . The wedge  130  is shown as a threaded pin wedge block and includes a wedge portion  601 , a block  602 , and a threaded adjustment or pin  603 . In the illustrated embodiment, the block  602  is fixed to the rotating frame  22  (for example, the block  602  may be bolted to the rotating frame  22 ). One or more threaded pins  603  are configured to pass through and engage the block  602  and to extend into the wedge portion  601 . The threaded pins  603  may be turned (i.e., threaded into or out of the block  602 ) to move the wedge portion  601  toward and away from the second end  98 . Movement of the wedge portion  601  adjusts a gap  604  (i.e., a clearance) between the second end  98  and the wedge portion  601 . For example,  FIG. 7A  illustrates the wedge portion  601  in a retracted position (e.g., creating a gap  604  of about 1.57 mm), and  FIG. 7B  illustrates the wedge portion  601  in an inserted position (e.g., creating a gap  604  of about 0 mm). In some embodiments, the gap  604  size may be adjusted to correspond to an anticipated maximum deflection of the rotating frame  22 . 
       FIG. 8  illustrates a system for supporting the gear case  90  according to yet another embodiment. In particular, the gear case second end (not shown) is coupled to the rotating frame  22  by a pin, while the first end  94  is permitted to slide in a direction parallel to the longitudinal axis of the gear case  90  extending between the first end  94  and the second end  98  (e.g., in a forward and rearward direction). In the illustrated embodiment, the first end  94  is supported for sliding movement by a pad  506  formed from a dissimilar material. In addition, a retainer or block  502  provides horizontal stop surfaces  504  to inhibit the gear case  90  from moving or pivoting away from the desired plane. 
       FIG. 9  illustrates a system for supporting the gear case  90  according to yet another embodiment. In particular, a bushing  708  is positioned between the first pin  114  and the first lug  106  to reduce stress in the pin joint while the rotating frame  22  flexes. In some embodiments, the bushing  708  may be made from a urethane material. In other embodiments, the bushing is a metal clad elastomer bushing. The bushing  708  is flexible to permit some movement/deflection of the first pin  114  in a direction parallel to the longitudinal axis, without inducing excessive longitudinal load into the gear case  90  or rotating frame  22  as the frame  22  flexes while also being sufficiently stiff to support the vertical load. In some embodiments, the bushing  708  may have a different stiffness in a first direction (i.e., the horizontal direction) compared to a stiffness in a second direction (i.e., the vertical direction). 
       FIG. 10  illustrates a system for supporting the gear case  90  according to yet another embodiment. In particular, the gear case second end is coupled to the rotating frame  22  by a pin, while the first end  94  is permitted to slide in a direction parallel to the longitudinal axis of the gear case  90  extending between the first end  94  and the second end  98  (e.g., in a forward and rearward direction). In the illustrated embodiment, the first end  94  is supported for sliding movement by a pad  906  formed from a dissimilar material (e.g., bronze, nylon, hardened steel, etc.). Dissimilar materials can be used to reduce friction at the interface and reduce the amount of wear in the joint. Additionally, the joint can be lubricated or coated. In addition, the pad  906  provides horizontal stop surfaces  912  to inhibit the gear case  90  from moving or pivoting away from the desired plane. Furthermore, a tether such as a chain  916  including a ratchet load binder  1025  is coupled between the rotating frame  22  and the first end  94  of the gear case  90  to bias the gear case  90  against the rotating frame  22  and limit vibrations. 
       FIG. 11  illustrates a system for supporting the gear case  90  according to yet another embodiment. In particular, the gear case second end is coupled to the rotating frame  22  by a pin  118 , while the first end  94  is permitted to move in a direction parallel to the longitudinal axis of the gear case  90  extending between the first end  94  and the second end  98  (e.g., in a forward and rearward direction relative to the excavation machine or the shovel  10 ). In the illustrated embodiment, the first end  94  is supported for movement by a roller element  1106 . For example, the roller element  1106  may include a roller element bearing ( 1106   a ), a bridge bearing ( 1106   b ), and/or a cylindrical roller ( 1106   c ). Alternatively, the roller element  1106  may be replaced by a sliding contact pad ( 1106   d ). Furthermore, a tether such as a chain  1116  including a ratchet load binder  1025  is coupled between the rotating frame  22  and the first end  94  of the gear case  90 . In other embodiments, another type of tensioning member (e.g., a fastener similar to the rod bolt  126  or a cable  1026 ) may be coupled between the rotating frame  22  and the first end  94  of the gear case  90 . 
       FIG. 12  illustrates a system for supporting the gear case  90  according to yet another embodiment. In particular, the gear case  90  is coupled to the rotating frame by one or more planar links or bars  1392 . Each link bar  1392  is pinned to the gear case  90  at one end and is pinned to the rotating frame  22  at another end, providing pivoting connections on each end of the link bar  1392  to permit movement of the gear case  90  in response to flexion of the rotating frame  22  during operation.  FIG. 12  illustrates the first end  94  of the gear case  90 , and the second end (not shown) can be coupled to the rotating frame  22  by a pin similar to pin  118  in  FIG. 11 . It is understood that other embodiments may include link bars coupled between the second end of the gear case  90  and the rotating frame with a pin coupling between the first end  94  and the rotating frame  22 . 
       FIG. 13  illustrates a system for supporting the gear case  90  according to yet another embodiment. In particular, the gear case  90  is coupled to the rotating frame  22  by one or more bolts  650 . In the illustrated embodiment, an attachment plate  651  is coupled to the second end  98  of the gear case  90 , and the bolts  650  extend through the attachment plate  651  and into the rotating frame  22 . The embodiment of  FIG. 13  illustrates five bolts  650 , although fewer or more bolts may be used in other embodiments. 
       FIGS. 14A and 14B  illustrate a system for supporting the gear case  90  according to yet another embodiment. In particular, the gear case  90  is coupled to the rotating frame  22  by one or more bolts  670 . An attachment plate  672  is coupled to the first end  94  of the gear case  90 , and the bolts  670  extend through the attachment plate  672  and attach to the rotating frame  22 . The embodiment of  FIG. 14A  illustrates two bolts  670 , although fewer or more bolts may be used in other embodiments. A bushing  671  is positioned between the attachment plate  672  and an associated one of the bolts  670 . Stated another way, each bolt  670  is inserted through the bushing  671 , and the bushing  671  and bolt  670  assembly is inserted through a slot  674  extending through the attachment plate  671 . 
       FIG. 14B  illustrates the slot  674 , the bushing  671 , and the bolt  670 . In some embodiments, the slot  674  may be non-circular; for example, in the illustrated embodiment the slot has an oval shape, which creates a gap  673  between the circular bushing  671  and the inners surface of the slot  647 . The gap  673  may allow for greater deflection of the bolt  670  and bushing  671  assembly in a first direction than a second direction. For example, as shown in  FIG. 14A , the semi-major axis of the oval slot  674  extends beyond the upper, larger diameter portion of the bushing  671  (when viewed from above the bolt  670 ) along a direction perpendicular to the first end  94 . Conversely, the oval gap  673  does not extend beyond the upper, larger diameter portion of the bushing  671  along a direction parallel to the first end  94  (i.e., along the semi-minor axis of the oval slot  674 ). 
     Similar to the bushing shown in  FIG. 9 , the bushing of  FIGS. 14A and 14B  is provided to reduce stress in the bolt  670  while the rotating frame  22  flexes. In some embodiments, the bushing  671  may be made from a urethane material. In other embodiments, the bushing is a metal clad elastomer bushing. The bushing  671  is flexible to permit some movement/deflection of the bolt  670  in a direction parallel to the longitudinal axis of the bolt  670 , without inducing excessive longitudinal load into the gear case  90  or rotating frame  22  as the frame  22  flexes while also being sufficiently stiff to support the vertical load. In some embodiments, the bushing  671  may have a different stiffness in a first direction (i.e., the horizontal direction) compared to a stiffness in a second direction (i.e., the vertical direction). 
     The embodiment(s) described above and illustrated in the figures are presented by way of example only and are not intended as a limitation upon the concepts and principles of the present disclosure. As such, it will be appreciated that variations and modifications to the elements and their configuration and/or arrangement exist within the spirit and scope of one or more independent aspects as described.