Classifications

• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F3/00—Dredgers; Soil-shifting machines
  • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
  • E02F3/88—Dredgers; Soil-shifting machines mechanically-driven with arrangements acting by a sucking or forcing effect, e.g. suction dredgers
  • E02F3/90—Component parts, e.g. arrangement or adaptation of pumps
  • E02F3/92—Digging elements, e.g. suction heads
  • E02F3/9212—Mechanical digging means, e.g. suction wheels, i.e. wheel with a suction inlet attached behind the wheel
  • E02F3/9225—Mechanical digging means, e.g. suction wheels, i.e. wheel with a suction inlet attached behind the wheel with rotating cutting elements
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F3/00—Dredgers; Soil-shifting machines
  • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
  • E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F3/00—Dredgers; Soil-shifting machines
  • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
  • E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
  • E02F3/961—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements with several digging elements or tools mounted on one machine
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/28—Small metalwork for digging elements, e.g. teeth scraper bits
  • E02F9/2808—Teeth
  • E02F9/2816—Mountings therefor
  • E02F9/2833—Retaining means, e.g. pins
  • E02F9/2841—Retaining means, e.g. pins resilient
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/28—Small metalwork for digging elements, e.g. teeth scraper bits
  • E02F9/2808—Teeth
  • E02F9/2858—Teeth characterised by shape
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/28—Small metalwork for digging elements, e.g. teeth scraper bits
  • E02F9/2866—Small metalwork for digging elements, e.g. teeth scraper bits for rotating digging elements
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/28—Small metalwork for digging elements, e.g. teeth scraper bits
  • E02F9/2883—Wear elements for buckets or implements in general

Definitions

• the present invention pertains to a wear assembly for securing a wear member to excavating equipment, and in particular to a wear assembly that is well suited for attachment and use on a dredge cutterhead.
• Dredge cutterheads are used for excavating earthen material that is underwater, such as a riverbed.
• a dredge cutterhead 1 includes several arms 2 that extend forward from a base ring 3 to a hub 4 (Fig, 21). The arms are spaced about the base ring and formed with a broad spiral about the central axis of the cutterhead.
• Each arm 2 is provided with a series of spaced apart teeth 5 to dig into the ground.
• the teeth are composed of adapters or bases 6 that are fixed to the arms, and points 7 that are releasabty attached to the bases by locks 8.
• the cutterhead In use, the cutterhead is rotated about its central axis to excavate the earthen material.
• a suction pipe is provided near the ring to remove the dredged material.
• the cutterhead is moved side-to- side as well as forward.
• the cutterhead On account of swells and other movement of the water, the cutterhead also tends to move up and down, and periodically impact the bottom surface. Further difficulties are caused by the operator's inability to see the ground that is being excavated underneath the water; i.e., unlike most other excavating operations, the dredge cutterhead cannot be effectively guided along a path to best suit the terrain to be excavated. In view of the heavy loads and severe environment, the point and base interconnection needs to be stable and secure.
• a wear member for excavating equipment is formed with side relief in the working and mounting sections to minimize the drag associated with the digging operation and, in turn, minimize the power needed to drive the equipment. Reduced power consumption, in turn, leads to a more efficient operation and a longer usable life for the wear member.
• the wear member has a transverse configuration where the width of the leading side is larger than the width of the corresponding trailing side so that the sidewalls of the wear member follow in the shadow of the leading side to decrease drag.
• This use of a smaller trailing side is provided not only through the working end but also at least partially into the mounting end.
• the drag experienced by a worn wear member of the invention is less than that of a conventional wear member. Less drag translates into less power consumption and a longer use of the wear member before it needs to be replaced. Accordingly, the working ends of the wear member can be further worn away before replacement is needed.
• the wear member has a digging profile that is defined by the transverse configuration of that portion of the wear member that penetrates the ground in one digging pass and in the direction of motion through the ground.
• side relief in the wear member is provided in the digging profile to lessen the drag experienced during a digging operation.
• side relief is provided in every digging profile expected through the life of the wear member including those which encompass the mounting section.
• the wear member in another aspect of the invention, includes a socket for receiving a nose of a base fixed to the excavating equipment.
• the socket is formed with a generally trapezoidal transverse shape that generally corresponds to the transverse trapezoidal exterior profile of the wear member. This general matching of the socket to the exterior of the mounting section eases manufacture, maximizes the size of the nose, and enhances the strength to weight ratio.
• one or more of the top, bottom or side surfaces of a trapezoidal shaped nose and the corresponding walls of the socket are each bowed to fit together. These surfaces and walls have a gradual curvature to ease installation, enhance stability of the wear member, and resist rotation of the wear member about the longitudinal axis during use.
• the socket and nose each includes rear stabilizing surfaces that extend substantially parallel to the longitudinal axis of the wear member and substantially around the perimeter of the socket and nose to resist rearward loads applied in all directions.
• the socket and nose are formed with complementary front bearing faces that are substantially hemispherical to lessen stress in the components and to better control the rattle that occurs between the wear member and the base.
• the socket and nose are formed with front curved bearing faces at their front ends, and with generally trapezoidal transverse shapes rearward of the front ends to improve stability, ease manufacture, maximize the size of the nose, reduce drag, stress and wear, and enhance the strength to weight ratio.
• the wear assembly includes a base, a wear member that mounts to the base, and an axially oriented lock that in a compressive state holds the wear member to the base in a manner that is secure, easy to use, readily manufactured, and can tighten the fit of the wear member on the base.
• the wear assembly includes an adjustable axial lock.
• the wear member includes an opening into which the lock is received, and a hole that is formed in a rear wall of the opening to accommodate passage of a iock to stabilize the lock and facilitate easy tightening of the lock.
• the base interacts with the lock solely through the use of a projecting stop.
• a projecting stop there is no need for a hole, recess or passage in the nose such as is typically provided to receive the lock.
• the nose strength is thus enhanced.
• the locking arrangement for securing the wear member to the base can be adjusted to consistently apply a predetermined tightening force to the wear member irrespective of the amount of wear that may exist in the base and/or wear member.
• the wear member inciudes a marker that can be used to identify when the lock has been adequately tightened.
• the wear member is installed and secured to the base through an easy to use, novel process involving an axial lock.
• the wear member fits over a nose of a base fixed to the excavating equipment.
• the base inciudes a stop that projects outward from the nose.
• An axial lock is received into an opening in the wear member and extends between the stop and a bearing surface on the wear member to releasably hold the wear member to the nose.
• the wear member is first slid over a base fixed to the excavating equipment.
• a lock to releasably hold a wear member to a base includes a threaded linear shaft, with a bearing end and a tool engaging end, a nut threaded onto the shaft, and a spring including a plurality of alternating annular elastomeric disks and annular spacers fit about the threaded shaft between the bearing end and the nut.
• Figure 1 is a wear assembly in accordance with the present invention.
• Figure 2 is a side view of a wear member of the invention.
• Figure 2A is a side view of a conventional wear member.
• Figure 3 is a cross-sectional view taken along line 3-3 in Figure 2.
• Figure 3A is a cross-sectional view taken along line 3A-3A in Figure 2A.
• Figure 4 is a cross-sectional view taken along line 4-4 in Figure 2.
• Figure 5 is a cross-sectional view taken along line 5-5 in Figure 2.
• Figure 6 is a cross-sectiona! view taken along line 6-6 in Figure 2.
• Figure 6A is the cross-sectional view taken along line 6A-6A in Figure
• Figure 7 is a cross-sectional view taken along line 7-7 in Figure 2.
• Figure 8 is a cross-sectional view taken along line 8-8 in Figure 2.
• Figure 9 is a cross-sectional view taken along line 9-9 in Figure 1.
• Figure 10 is a top view of the wear member.
• Figure 11 is a rear view of the wear member.
• Figure 12 is a perspective view of a nose of a base of the invention.
• Figure 13 is a front view of the nose.
• Figure 14 is a side view of the nose.
• Figure 15 is an enlarged perspective view of a lock in the wear assembly.
• Figure 16 is an enlarged perspective view of the lock in the wear assembly prior to tightening.
• Figure 17 is a perspective view of the lock.
• Figure 18 is a side view of the lock.
• Figure 19 is an exploded, perspective view of the lock
• Figure 20 is a perspective view of the lock with the nose ⁇ the point has been omitted).
• Figure 21 is a side view of a conventional dredge cutterhead.
• the present invention pertains to a wear assembly 10 for excavating equipment, and is particularly well suited for dredging operations.
• the invention is described in terms of a dredge tooth adapted for attachment to a dredge cutterhead. Nevertheless, the different aspects of the invention can be used in conjunction with other kinds of wear assemblies (e.g., shrouds) and for other kinds of excavating equipment (e.g., buckets).
• Wear assembly 10 includes a base 12 secured to a dredge cutterhead, a wear member 14, and a lock 16 to reteasably hold the wear member to base 12 (Figs. 1-10).
• Base 12 includes a forwardly projecting nose 18 onto which wear member 14 is mounted, and a mounting end (not shown) that is fixed to an arm of a dredge cutterhead (Figs. 1, 9 and 11-14).
• the base may be cast as part of the arm, welded to the arm, or attached by mechanical means.
• the base may be formed and mounted to the cutterhead such as disclosed in U.S. Patent No. 4,470,210 or U.S. Patent No. 6,729,052.
• wear member 14 is a point provided with a working section 21 in the form of an elongate slender bit and a mounting section 23 that defines a socket 20 to receive nose IS ⁇ Rgs. 1-10).
• Point 14 is rotated by the cutterhead such that it engages the ground in generally the same way with each digging pass.
• point 14 includes a leading side 25 and a trailing side 27.
• Leading side 25 is the side that first engages and leads the penetration of the ground with each rotation of the cutterhead.
• trailing side 27 has a smaller width than leading side 25 (i.e., along a plane perpendicular to the longitudinal axis 28 of point 14) through bit 21 (Fig. 5) and at least partially through mounting section 23 (Fig. 4).
• trailing side 27 has a smaller width than leading side 25 throughout the length of point 14 (Ftgs. 4, 5 and 7).
• Bit 21 of point 14 preferably has a generally trapezoidal transverse configuration with a leading side 25 that is wider than trailing side 27 (Fig. 5).
• the term "transverse configuration" is used to refer to the two-dimensional configuration along a plane perpendicular to the longitudinal axis 28 of wear member 14.
• sidewalts 29, 31 follow in the shadow of leading side 25 during digging and thereby create little drag on the cutting operation.
• sidewafls 29, 31 converge toward trailing side 27 at an angle ⁇ of about 16 degrees (Fig. 5); however, other angular configurations are possible.
• the leading side 25, trailing side 27 and sidewalls 29, 31 can be planar, curved or irregular. Moreover, shapes other than trapezoidal can be used that provide side relief.
• dredge point 14 penetrates the ground to a certain depth with each digging pass (i.e., with each rotation of the cutterhead).
• the bit aione penetrates the ground.
• the ground level in one digging cycle extends generally along line 3-3 (Fig. 2) at the center point of a digging pass. Since only the bit penetrates the ground and the bit is relatively thin, the drag placed on the digging operation is within manageable limits. Nevertheless, with many teeth being constantly driven through the ground at a rapid rate, power requirements are always high and reducing the drag even in the bit is beneficial to the operation, especially when digging through rock.
• sidewalls 29, 31 not only converge toward trailing side 27, but are configured so that the sidewalls lie within the shadow of the leading side 25 in the digging profile.
• the "digging profile” is used to mean the cross-sectional configuration of the portion of point 14 that penetrates the ground along a plane that is (i) parallel to the direction of travel 34 at the center point of a digging pass through the ground and ⁇ ) laterally perpendicular to the longitudinal axis.
• the digging profile is a better indication of the drag to be imposed on the point during use than a true transverse cross section.
• the provision of side relief in the digging profile is dependent on the angle at which the sidewalls converge toward the trailing side and the axial slope or expansion of the point surfaces in a rearward direction.
• the intention is to provide a width that generally narrows from the leading side to the trailing side when considered from the perspective of the digging profile.
• Side relief in the digging profile preferably extends across the expected cutterhead digging angles, but benefit can still be obtained if such side relief exists in at least one digging angle.
• the cross-sectional configuration illustrated in Figure 3 represents one digging profile 35 for a portion of point 14 being driven through the ground. As can be seen, bit 21 is still provided with side relief even in the digging profile as sidewalls 29, 31 converge toward trailing side 27 for reduced drag.
• the mounting section 23 continues to include side relief at least at the front end 40 of the mounting section (Fig. 4), and preferably throughout the mounting section (Figs, 4 and 7). As seen in Figure 4, mounting section 23 is larger than bit 21 to accommodate the receipt of nose 18 into socket 20 and to provide ample strength for the interconnection between point 14 and base 12. Sidewalls 29, 31 are inclined so as to converge toward trailing side 27.
• bit 21a has a trapezoidal transverse configuration with a leading side 25a that is wider than trailing side 27a. However, bit 21a does not provide side relief in the digging profile. As seen in Figure 3A, the digging profile 35a (i.e. along iine 3A-3A) in Figure 2A does not have sidewalls 29a, 31a that converge toward trailing side 27a (Figs.
• bit 21 has worn down to an extent where the portion of mounting section 23 along line 6-6 (Figs. 2 and 6) is driven through the ground.
• Even the mounting section 23 provides side relief for reduced drag; i.e., sidewalls 29, 31 converge toward trailing side even in digging profile 45.
• the presence of side relief in digging profile 45 imposes less drag and, hence, requires less power to be driven through the ground.
• the reduced drag in turn, enables the cutterhead to continue to operate with points worn to the point where the mounting section penetrates the ground.
• mounting section 23a does not have a trapezoidal transverse configuration with sidewails 29a, 31a that converge toward trailing side 27a.
• the tapering of sidewalls 29, 31 continues from front end 37 to rear end 47 of point 14. As seen in Figure 7, sidewalls 29, 31 converge toward trailing side 27 even at the rear of mounting section 23. Moreover, side relief is provided even in a digging profile 55 along line 8- ⁇ ⁇ Figs. 2 and 8), i.e., sidewalls 29, 31 converge toward trailing side 27 even in this rearward digging profile 55.
• front end 58 of nose 18 includes a forward-facing bearing face 60 that is convex and curved about two perpendicular axes (figs. 1, 9 and 11-14).
• front end 62 of socket 20 is formed with a complementary concave and curved bearing face 64 to set against bearing face 60 (Figs. 1, 7, 9 and 11).
• front bearing faces 60, 64 each conforms to a spherical segment to lessen stress in the components due to the application of non-axial loads such as disclosed in US Patent No. 6,729,052, which is incorporated in its entirety herein by reference.
• front ends 58, 62 are each generally hemispherical to reduce the rattle between point 14 and base 12 and more effectively resist loads from all directions.
• Front bearing surface 64 of socket 20 is preferably slightly broader than hemispherical at its ends and center to accommodate reliably mounting of points 14 on different bases (i.e., without binding or bottoming out), but which under common loads or following wear operate as a true hemispherical socket surface on the hemispherical bail surface of base 12.
• a conventional tooth 10a Fig. 2A
• the front ends of the socket and nose are angular with flat bearing surfaces and hard corners.
• point 14a shifts around on the nose such that the front of the socket 20a rattles around and against the front end of the nose, and the rear end of the socket shifts around and rattles against the rear end of the nose.
• This shifting and rattling causes the point and base to wear.
• the use of generally hemispherical front bearing faces 60, 64 substantially reduces the rattle at the front end of the socket 20 and nose 18 (Figs. 1 and 9). Rather, the use of smooth, continuous front bearing faces enables the point to roll about the nose to reduce wear.
• a small band 65, substantially parallel to the longitudinal axis 28, preferably extends directly rearward of the generally hemispherical bearing surfaces to provide additional capacity for the nose to wear and still maintain the desired support.
• substantially parallel is intended to include parallel surfaces as well as those that axially diverge rearwardly from axis 28 at a small angle (e.g., of about 1-7 degrees) for manufacturing or other purposes.
• the small band 65 Is preferably axially inclined no more than 5 degrees to axis 28, and most preferably is axially inclined about 2-3 degrees.
• Nose 18 includes a body 66 rearward of front end 58 (Figs. 11-14).
• Body 66 is defined by an upper surface 68, a lower surface 69 and side surfaces 70, 71.
• body surfaces 68-71 diverge rearwardly so that nose 18 expands outward from front end 58 to provide a more robust nose to withstand the rigors of digging. Nevertheless, it is possible for only the upper and lower surfaces 68, 69 to diverge from each other and for the side surfaces 70, 71 to axially extend substantially parallel to each other.
• Socket 20 has a main portion 76 rearward of front end 62 to receive body 66.
• Main portion 76 includes an upper wall 78, lower wall 79 and sidewalls 80, 81 that conform to body surfaces 68-71.
• body 66 and main portion 76 each have a trapezoidal transverse configuration.
• the use of a trapezoidal shape predominantly along the length of nose 18 and socket 20 provides four corners 67, 77, which act as spaced ridges to resist turning of wear member 14 about axis 28.
• socket walls 78-81 have mutually bowed configurations (Figs. 7, 11 and 13); that is, body surfaces 68-71 are preferably concave and curved across substantially their entire widths to define a trough 84 on each of the four sides of body 66.
• socket walls 78-81 are preferably convex and curved across substantially their entire widths to define projections 86 received into troughs 84.
• the preferred bowing of nose surfaces 68-71 and socket walls 78-81 across substantially their entire widths accentuate corners 67, 77 to provide increased resistance to the rotation of point 14 about base 12 during operation.
• the troughs and projections will also reduce rotational rattle of the point on the base.
• troughs 84 and projections 86 and particularly those that are gradually curved and extending substantially across the entire widths of the surfaces 68-71 and walls 78-81 eases the assembly of point 14 onto nose 18; i.e., the troughs 84 and projections 86 cooperatively direct point 14 into the proper assembled position on nose 18 during assembly.
• the engagement of projections 86 being received into the troughs 84 will tend to rotate the point into proper alignment as the point is fed rearward onto nose 18.
• This cooperative effect of troughs 84 and projections 86 greatly eases and speeds installation and the setting of corners 67 into corners 77.
• Nose surfaces 68-71 with troughs 84 are each preferably inclined axially to expand outward as they extend rearward to provide strength to nose 18 until reaching a rear stabilizing surface 85 of nose 18.
• socket walls 78-81 with projections 86 also each expand to conform to surfaces 68-71.
• Socket walls 78-81 also define rear stabilizing surfaces 95 to bear against stabilizing surfaces 85.
• Rear stabilizing surfaces 85, 95 are substantially parallel to longitudinal axis 28. In one preferred embodiment, each stabilizing surface 85, 95 diverges axially rearward at an angle to axis 28 of about 7 degrees.
• the rear stabilizing surfaces 85, 95 also preferably encircle (or at least substantially encircle) nose 18 and socket 20 to better resist non-axial loads.
• stabilizing surfaces 85, 95 are preferably formed with short axial extensions, they could have longer or different constructions. Also, in certain circumstances, e.g., in tight duty operations, benefits can be achieved without stabilizing surfaces 85, 95.
• Front bearing faces 60, 64 and rear stabilizing surfaces 85, 95 are provided to stabilize the point on the nose and to lessen stress in the components.
• the generally hemispherical bearing faces 60, 64 at the front ends 58, 62 of the nose 18 and socket 20 are able to stably resist axial and non-axial rearward forces in direct opposition to the loads irrespective of their applied directions.
• This use of curved, continuous front bearing surfaces reduces rattling of the point on the nose and reduces the stress concentrations that otherwise exist when corners are present.
• Rear stabilizing surfaces 85, 95 complement the front bearing faces 60, 64 by reducing the rattle at the rear of the point and providing stable resistance to the rear portions of the point, as described in U.S. Patent No.
• Main portion 76 of socket 20 preferably has a generally trapezoidal transverse configuration to receive a matingly shaped nose 18 (Figs. 7 and 11).
• the generally trapezoidal transverse configuration of socket 20 generally follows the generally trapezoidal transverse configuration of the exterior 97 of point 14. This cooperative shaping of the socket 20 and exterior 97 maximizes the size of the nose 18 that can be accommodated within point 14, eases the manufacturing of point 14 in a casting process, and enhances the strength to weight ratio.
• a wide variety of different locks can be used to reteasably secure wear member 14 to base 12. Nonetheless, in a preferred embodiment, lock 16 is received into an opening 101 in wear member 14, preferably formed in trailing wall 27 though it could be formed elsewhere (Figs. 1, 9 and 15-20).
• Opening 101 preferably has an axially elongated shape and includes a front wail 103, a rear wall 105, and sidewalls 107, 109.
• a rim 111 is built up around opening 101 for protection of the lock and for additional strength.
• Rim 111 is also enlarged along rear wall 105 to extend farther outward of exterior surface 97 and define a hole 113 for passage of lock 16. The hole stabilizes the position of lock 16 and permits easy access to it by the operator.
• Nose 18 includes a stop 115 that projects outward from upper side 68 of nose 18 to engage lock 16.
• Stop 115 preferably has a rear face 119 with a concave, curved recess 121 into which a front end 123 of lock 16 is received and retained during use, but other arrangements could be used to cooperate with the lock.
• opening 101 is long enough and trailing wall 27 sufficiently inclined to provide clearance for stop 115 when wear member 14 is installed onto nose 18. Nevertheless, a relief or other forms of clearance could be provided in socket 20 if needed for the passage of stop 115.
• the projection of stop 115 is preferably limited by the provision of a depression 118 to accommodate a portion of lock 16.
• Lock 16 is a linear lock oriented generally axially to hold wear member
• lock 16 includes a threaded shaft 130 having a front end 123 and a rear end with head 134, a nut 136 threaded to shaft 130, and a spring 138 (Figs. 1, 9 and 15-20).
• Spring 138 is preferably formed of a series of elastomeric disks 140 composed of foam, rubber or other resilient material, separated by spacers 142 which are preferably in the form of washers.
• Multiple disks 140 are used to provide sufficient force, resiliency and take up.
• the washers isolate the elastomeric disks so that they operate as a series of individual spring members.
• Washers 142 are preferably composed of plastic but could be made of other materials.
• the spring of the preferred construction is economical to make and assemble on shaft 130. Nevertheless, other kinds of springs could be used.
• a thrust washer 142a or other means is preferably provided at the end of the spring to provide ample support.
• Shaft 130 extends centrally through spring 138 to engage nut 136.
• Front end 123 of shaft 130 fits into recess 121 so that the shaft 130 is set against stop 115 for support.
• Rear end 134 of lock 16 extends through hole 113 in wear member 14 to enable a user to access the lock outside of opening 101.
• the shaft is preferably set at an angle to axis 28 so that head 134 is more easily accessed.
• Spring 138 sets between rear wall 105 and nut 136 so that it can apply a biasing force to the wear member when the lock is tightened.
• Hole 113 is preferably larger than head 134 to permit its passage during installation of lock 16 into assembly 10.
• Hole 113 could also be formed as an open slot to accommodate insertion of shaft 130 simply from above.
• wear member 14 is slid over nose 18 so that nose 18 is fit into socket 20 (Figs. 1 and 9).
• the lock can be temporarily held in hole 113 for shipping, storage and/or installation by a releasable retainer (e.g., a simple twist tie) fit around shaft 130 outside of opening 101 or it can be installed after the wear member is fit onto the nose.
• a releasable retainer e.g., a simple twist tie
• shaft 130 is inserted through hole 113 and its front end 123 set in recess 121 of stop 115.
• Lock 16 is positioned to lie along the exterior of nose 18 so that no holes, slots or the like need to be formed in the nose to contain the lock for resisting the loads.
• Head 134 is engaged and turned by a tool to tighten the lock to a compressive state to hold the wear member; i.e., shaft 130 is turned relative to nut 136 so that front end 123 presses against stop 115. This movement, in turn, draws nut 136 rearward against spring 138, which is compressed between nut 136 and rear wall 105. This tightening of lock 16 pulls wear member 14 tightly onto nose 18 (i.e., with front bearing faces 60, 64 engaged) for a snug fit and less wear during use. Continued turning of shaft 130 further compresses spring 138. The compressed spring 138 then urges wear member 14 rearward as the nose and socket begin to wear.
• lock 16 is lightweight, hammerless, easy to manufacture, does not consume much space, and does not require any openings in the nose.
• lock 16 aiso includes an indicator 146 fit onto shaft 130 in association with nut 136 (Figs. 15-20).
• Indicator 146 is preferably a plate formed of steel or other rigid material that has side edges 148, 149 that fit closely to sidewalls 107, 109 of opening 101, but not tightly into opening 101.
• Indicator 146 includes an opening that fully or partially receives nut 136 to prevent rotation of the nut when shaft 130 is turned. The close receipt of side edges 148, 149 to sidewalls 107, 109 prevents indicator 146 from turning.
• the indicator could have a threaded bore to function as the nut; if the indicator were omitted, other means would be required to hold nut 136 from turning. Indicator 146 could also be discrete from nut 136.
• Indicator 146 provides a visual indication of when shaft 130 has been suitably tightened to apply the desired pressure to the wear member without placing undue stress on shaft 130 and/or spring 138.
• indicator 146 cooperates with a marker 152 formed along opening 101, e.g., along rim 111 and/or sidewalls 107, 109.
• Marker 152 is preferably on rim 111 along one or both sidewalls 107, 109, but could have other constructions.
• Marker 146 is preferably a ridge or some structure that is more than mere indicia so that it can be used to retighten lock 16 when wear begins to develop as well as at the time of initial tightening.

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• Engineering & Computer Science (AREA)
• Mining & Mineral Resources (AREA)
• Civil Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Structural Engineering (AREA)
• Mechanical Engineering (AREA)
• Component Parts Of Construction Machinery (AREA)
• Earth Drilling (AREA)
• Bending Of Plates, Rods, And Pipes (AREA)
• Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
• Forging (AREA)
• Grinding-Machine Dressing And Accessory Apparatuses (AREA)
• Clamps And Clips (AREA)
• Shovels (AREA)
• Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
• Braking Arrangements (AREA)
• Mechanical Operated Clutches (AREA)
• Rolls And Other Rotary Bodies (AREA)

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• 2008
  • 2008-05-06 PL PL15151786T patent/PL2889434T3/pl unknown
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  • 2008-05-06 DK DK15151786.9T patent/DK2889434T3/en active
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