Assembly for securing a wear

Abstract

A wear member for excavating equipment and which is particularly suited for a dredge cutterhead that includes a curved abutting surface that abuts a complementary curved bearing surface on the base. The curved bearing surfaces are able to maintain substantially full contact with each other under transverse loading. The base and adapter further having a plurality of complementary stops for resisting relative movement between them.

Description

FIELD OF THE INVENTION

The present invention pertains to an assembly for securing a wear member to excavating equipment. In one advantageous arrangement, the wear member is particularly suited for use in attaching an adapter to a dredge cutterhead. The present invention also pertains to an improved construction for welding a member to a support structure such as, for example, an arm of a dredge cutterhead or a lip of an excavating bucket.

BACKGROUND AND SUMMARY OF THE INVENTION

Dredge cutterheads are used for excavating earthen material that is underwater, such as a riverbed. One example of a dredge cutterhead is illustrated in FIG. 17. In general, a dredge cutterhead includes several arms 11 that extend forward from a base ring 16 to a hub 23. The arms are equally spaced about the base ring and formed with a broad spiral about the central axis of the cutterhead. Each arm is provided with a series of spaced apart teeth 12 to dig into the ground.

In use, the cutterhead is rotated about its central axis to excavate the earthen material. To excavate the desired swath of ground the cutterhead is moved side-to-side as well as forward. On account of swells and other movement of the water, the cutterhead will also tend to move up and down, and periodically impact the bottom surface. As a result of this unique cutting action, the teeth of a dredge cutterhead experience heavy transverse as well as axial loading and heavy impact jacking loads that thrust the tooth up, down and sideways. The heavy transverse loading of the tooth is further engendered by the operator's inability to see the ground that is being excavated underneath the water. Unlike other excavators (e.g., a front end loader), the operator of a dredge cutterhead cannot effectively guide the cutterhead along a path to best suit the terrain to be excavated.

Due to the rotative digging action of the cutterhead, each tooth penetrates the ground on the order of 30 times a minute as compared to about 1 time a minute for mining teeth. As a result, the teeth experience a great amount of wear during use. It is desirable therefore for the teeth to be easily removed and installed to minimize downtime for the cutterhead. As is common with wear assemblies for excavating equipment, dredge teeth comprise a plurality of integrally connected parts so as to minimize the amount of material needing replacement, i.e., only the worn components need to be replaced.

In the example of FIG. 17, each tooth includes a base 18, an adapter 13, a point or tip 17, and a lock 29. The base 18 is cast on the arm 11 at a particular location and orientation to maximize digging. Adapter 13 includes a rear end 22 that is received in a socket 14 defined in the base, and a forwardly projecting nose 15 to hold the point 17. A removable lock 29 is provided to facilitate the required frequent replacement of the tooth points 17. The adapter is held in the socket by a large fillet weld about the circumference of the rear end 22. In other known dredge cutterheads 1, the adapter 2 is bifurcated to define a pair of legs that are configured to wrap about the arm 3 (FIG. 18). These adapters are welded directly to the arm without a base member.

Although the tooth points require the most frequent replacement in a dredge cutterhead, the adapters still wear and need periodic replacement. However, replacing even a single adapter on a dredge cutterhead is a long process. The welded adapter must first be cut off with a torch. Then, portions of the arm and base that were damaged by the removal of the adapter must be repaired and rebuilt. Finally, a new adapter is welded into place. This process typically entails 10-12 man-hours per adapter. Hence, a lengthy delay in a dredging operation is unavoidable even when replacing only a single adapter. Moreover, in view of this lengthy delay, an operator will often wait until several adapters need replacement to take the cutterhead out of operation. As a result, the actual delay in operation that usually occurs is longer. Indeed, with a typical cutterhead having 50-60 teeth a rebuilding process of the entire cutterhead could require more than 600 man-hours. In an effort to avoid substantial loss of dredging time, most dredging operations maintain three or four cutterheads so that the entire cutterhead can be exchanged when one or more adapter needs to be replaced, the cutterhead needs to be rebuilt, or if the cutterhead breaks. However, a cutterhead is expensive. The maintaining of extra cutterheads that are not used, but held only when the one in use is serviced is an undesirable use of resources.

In one aspect of the present invention, the adapter is mechanically attached to the arm for easy installation and removal. The adapter is held to a base on the arm solely by a mechanical construction without the need for welding the adapter. In the preferred construction, the base and adapter are formed with complementary coupling configurations to prevent release of the adapter from the base except in a release direction. A removable lock is used to prevent undesired release of the adapter from the base in the release direction. With a mechanical attachment, the adapter can be easily replaced by simply removing the lock and moving the adapter in the release direction. There is no weld to be cut, no need to repair the base and arm, and no re-application of a weld. As opposed to 10-12 man-hours for replacing a welded adapter, a mechanically attached adapter in accordance with the present invention can be changed in as little as 10 minutes. This is a dramatic improvement which hot only substantially reduces downtime for the cutterhead, but can also make the elimination of an entire spare cutterhead at the dredging site possible. As a result, instead of typically needing three or four cutterheads at a dredge site, only two or three may be needed.

In a preferred construction of the present invention, the adapter includes a generally T-shaped slot that receives a complementarily-shaped tongue on the base, and an opening for receiving a lock. The lock, when inserted into the opening, opposes a wall of the base and a wall of the opening to prevent release of the tongue and slot, and thereby holds the adapter to the base.

It is common for adapters of various excavators, such as a front end loader, to be mechanically attached to the excavating bucket. For example, U.S. Pat. No. 5,653,048 discloses an adapter with a T-shaped slot that receives a T-shaped boss welded to the lip of an excavating bucket. A lock is fit within an opening in the top of the adapter to prevent loss of the adapter from the lip. A bearing surface is formed at the front end of the boss to provide axial support for the adapter. While this construction well supports an adapter on an excavating bucket, it is not well suited for use on a dredge cutterhead.

In an excavating bucket, the teeth are primarily subjected to axial loading as the bucket is driven forward through the ground. However, as discussed above, the teeth on a dredge cutterhead are subjected to heavy and frequent transverse loads due to the manner in which the cutterhead is operated. In the noted '048 patent, the adapter 4 is slid onto the boss 5 with a slight side clearance for ease of assembly. The application of a large side load L applied against the tooth point 6 tends to rotate the adapter about the received boss to the extent of the defined clearance between the parts (FIG. 16). This rotation of the adapter results in the generation of resistant forces R1-R4 and high stresses being generated through essentially “point” contacts in the corners of the assembly. Although true point contact is impossible, the term is used to identify large applications of force over a relatively small area. In particular, the application of large forces R2, R3 at “points” on the front of the base and the lock 7 place exceptionally high levels of stress on the components. Such high stress levels, in turn, cause greater wearing of the parts at these locations and a shortened usable life of the parts. The increased wearing also enlarges the clearance space, which can lead to rattling of the components during use. Such rattling of the parts further quickens wearing of the parts.

In ordinary digging, such as with a front end loader, fines become impacted between the adapter and base so that rattling is reduced or eliminated even when wearing has created large gaps between the parts. However, in a dredging operation, the water sweeps the fines in and out of the gaps, and prevents the build up of fines between the parts. Since the gaps between the parts would ordinarily remain in a dredging operation, an adapter mechanically attached to a boss on a dredge cutterhead by a known construction would continually rattle against the boss and repeatedly apply large loads in point contacts along the front and rear of the adapter. Moreover, since the fines are constantly swept into and out of the gaps between the parts with the water, the fines would actually function as a grinding compound on the parts to further exacerbate wearing of the parts. Consequently, adapters for dredging operations have not before been mechanically attached to the dredge cutterhead arms.

However, these shortcomings are overcome in the present invention so that adapters in dredging teeth can be mechanically attached to the arms. In particular, the front of the base is curved and in contact with a complementary abutment of the adapter. As a result, when side loads push the adapter in a rotative manner, the arcuate shape of the bearing surfaces enables the surfaces to remain in substantially full flush contact with each other. This full contact arrangement as opposed to a point contact greatly reduces the stress otherwise experienced in the corners of the components. Rather than having high loads applied essentially as point contacts, the loads are spread over substantially the entire bearing surface to greatly minimize the stress in the parts and, in turn, substantially lengthen the usable life of the parts.

In a preferred construction, the arcuate bearing surfaces define spherical segments to maintain substantially full contact between the bearing surfaces of the adapter and the base under both horizontal and vertical transverse loading. In addition, the rear bearing surface of the base and the front of the lock are also preferably formed with similar arcuate surfaces to likewise maintain substantially full contact between the lock and the base. Preferably, the radii of curvature for the bearing surface at the front and rear of the adapter originate from the same point.

In another aspect of the invention, the base and adapter are formed with a front bearing surface that is subdivided to define a transverse stop to resist rolling of the adapter on the base, which in turn reduces wearing of the parts.

In one other aspect of the invention, the base and adapter are formed with axially spaced complementary stops to resist relative sliding of the adapter on the base, and thereby reduce wearing of the components during use.

In another aspect of the invention, a wear member for use with excavators other than dredge cutterheads could also be benefited by incorporating the curved and/or multiple bearing surfaces described above for the adapter.

In another aspect of the present invention, the lock is formed to tighten the connection between the base and adapter. A tightened assembly alleviates rattling and thereby lengthens the useful life of the components. The above-noted '048, patent discloses a lock with a threaded plug that tightens the adapter on the boss. Nevertheless, the stress and strains of digging can work to loosen even an initially tightened arrangement such that the adapter will still shift and rattle against the base resulting in increased wear, particularly with the high frequency of penetration and varied loading of teeth on a dredge cutterhead. Further, with a loosening assembly, there would be nothing in a water environment to prevent the components from rattling during use.

Therefore, in accordance with another aspect of the present invention, the lock further includes a resilient element that cooperates with an actuator to maintain a tight engagement between the adapter and base even after loads have introduced wear between the parts. The resilient element is sandwiched between a pair of rigid members. The actuator initially pulls the adapter into a tight engagement with the base and draws the rigid members together to compress the resilient element. As looseness begins to develop in the assembly due to wearing, the resilient element expands to dampen any shifting or rattling of the adapter on the base and thereby maintain a tight engagement between the two components. The rigid members also preferably have at least one stop that prevents excessive compression of the resilient element. In this way, the rigid members initially form a rigid lock that is tightly set between the adapter and the base, and which also protect the internal resilient element from premature failure on account of being overloaded.

As discussed above, the arms in a dredge cutterhead have a broad spiraling configuration. As a result, the teeth each project from the arm at a unique orientation to maximize digging. Since the teeth are mounted in different orientations on the arm, care must be taken to ensure that each adapter is properly positioned on the arm. This additional positioning procedure further lengthens the time needed to install new adapters in past cutterheads. In the example illustrated in FIG. 17, a resin is poured into the socket to harden around the first mounted adapter to thus form a recess adapted to properly orient successive adapters for the dredging operation. Nevertheless, this design still requires a careful, time-consuming procedure to initially place the adapters properly on the arm as well as the extra work of pouring and curing the resin.

As can be appreciated, since there is no guiding base in the direct welding of adapters to the arms, such as in FIG. 18, it is nearly impossible to properly position each of the adapters for maximum digging efficiency. Moreover, arms on a dredge cutter do not have a uniform configuration as they extend from the base ring to the hub. To avoid the cost and trouble of having to make a specifically shaped adapter to custom fit each designated location along the arm, the adapters are formed to have a general fit on the arm. As a result, the fit is typically loose, thus making it even more difficult to properly position the adapter for welding. Digging efficiency is therefore usually lost in the improper mounting of such teeth to a dredge cutterhead.

In another aspect of the present invention, the arm is formed with a plurality of spaced apart locator formations along the front edge of the arm to properly position the teeth at the desired orientations. The locator formations each have the same structural configuration, although their orientations relative to the surrounding arm contour may differ so as to properly orient each tooth for the particular location along the arm. In one aspect of the invention, a separable base member is provided with a complementary coupling formation to matingly fit with the locator formations so as to support and position the adapter properly on the arm. As a result, each base can be formed with the same shape irrespective_of where along the arm it is to be mounted. Moreover, these bases are adapted to be positioned on the dredge cutterhead in an easy, accurate and quick manner. In an alternative embodiment of the invention, a weld-on adapter includes a coupling formation to match the locator formations provided on the arm so that weld-on adapters can be easily secured in proper position on the arms. As with the bases of the invention, these adapters can each be made to have the same shape and easily positioned correctly irrespective of where along the arm they are to be mounted.

Another aspect of the invention pertains to an improvement in welding parts to a base surface, such as the arm of an excavator or lip of a bucket. The welding of components to a base surface results in considerable heating of both the welded part and the base surface. As each weld bead cools, it contracts to leave a residual tensile stress along the sides of the joint, i.e., in the heat affected zone. The bottom of the joint is defined by the surface of the welded part and the base surface, which abut each other but are not welded together. These unbonded surfaces act as a gap in the union of the components, which in turn, reacts much as a crack when the welded part is loaded. As can be appreciated, loads transferred through the weld joint can produce extremely high stresses at the end of the gap (i.e., at the bottom of the weld joint). This is also at the start of the heat affected zone, which is already weakened due to the heat. As a result, any failure in the connection will often begin at this point.

To improve the strength and integrity of the welding of a part to a base surface, the bottom surface of the welded part is formed with a groove near the weld bead. With this construction, as the weld bead cools and contracts, it draws the lip of the welded part (i.e., the portion outside of the groove) outward. Now the residual stress is concentrated at the top of the groove, rather than at the end of the gap. The top of the groove has a smooth radius, which provides a much lower stress concentration factor than the sharp end of the gap. It is also formed in the parent metal of the part, which is stronger than the weld material at the end of the gap. This construction, then, greatly reduces the tendency of the weld to fail.

The use of a groove in the underside of the welded part can also ease and improve the removal of welded parts from a base surface. When cutting the welded part away from the base surface with a torch (e.g., an air arc) the user can more easily follow the groove. In this way, the contour that remains is very near the original weld prep shape, and little clean-up is required before welding on a replacement part.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a front perspective exploded view of an attachment assembly in accordance with the present invention.

FIG. 2 is a perspective view of a base in accordance with the present invention in conjunction with an imaginary sphere.

FIG. 3 is a top plan view of the base.

FIG. 4 is a side elevational view of the base.

FIG. 5 is a perspective view of a portion of an arm of a dredge cutterhead in accordance with the present invention.

FIG. 6 is a top perspective view of the base positioned on the arm.

FIG. 7 is a rear perspective view of an adapter in accordance with the present invention.

FIG. 8 is a side elevational view of the adapter.

FIG. 9 is a top plan view of the adapter.

FIG. 10 is an exploded perspective view of a lock in accordance with the present invention.

FIG. 11 is a side elevational view of the lock.

FIG. 12 is a top plan view of the lock.

FIG. 13 is a perspective view of the lock.

FIG. 14 is a cross-sectional view of the lock taken along line XIV-XIV in FIG. 13.

FIG. 15 is a top schematic view of a tooth in accordance with the present invention under side loading.

FIG. 16 is a top schematic view of a prior art tooth under side loading.

FIG. 17 is a perspective view of a prior art dredge cutterhead.

FIG. 18 is a perspective view of another prior art dredge cutterhead.

FIG. 19 is a perspective view of a weld-on adapter mounted on a dredge arm in another embodiment.

FIG. 20 is a side view of an alternative weld-on adapter.

FIG. 21 is a cross section of the base and lip without the weld bead taken along line 21-21 in FIG. 1.

FIG. 22 is an enlarged view of portion A from FIG. 21 with the weld bead included.

FIG. 23 is an axial cross sectional view of an alternative wear assembly in accordance with the present invention.

FIGS. 24 and 25 are perspective views of the base in FIG. 23.

FIGS. 26 and 27 are perspective views of the adapter in FIG. 23.

FIG. 28 is an axial cross sectional view of the adapter in FIG. 23.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

The present invention pertains to an assembly for securing a wear member to an excavator. The present invention is particularly suited for mounting a tooth on a dredge cutterhead because of the ability of the tooth in the preferred construction to better withstand heavy transverse loading typical of a dredging operation and dampen rattling of the parts. Nevertheless, a tooth in accordance with the present invention could be used with other excavators. Additionally, other wear members used in excavating equipment (e.g., shrouds) could be mounted using the present invention.

In accordance with the present invention, a tooth 30 includes a base or mount 32, an adapter 34, a point (not shown), and a lock 36 (FIG. 1). The tooth components will at times be described in relative terms, such as up and down, even though the operation of the dredging equipment will cause the teeth to assume many different orientations. These directions are used for explanation purposes only and should ordinarily be understood with respect to the orientation in FIG. 1.

In the preferred construction, base 32 has a lower leg 38, a front body 40 and an upper leg 42 in a generally U-shaped configuration (FIG. 14) that wraps around the front edge 44 of an arm 48 of a cutterhead for enhanced support. The base is preferably a cast one-piece product that is fixed to the arm by welding, but could be mechanically attached or constructed as a multi-piece component. Alternatively, the base could be fixed to the arm as a structure that is cast as a unitary part of the arm (not shown).

Lower leg 38 extends only a short distance along a lower side 47 of arm 48, although it may be omitted or provided with an extended construction. Upper leg 42 extends rearward along an upper side 55 of arm 48 and includes a coupling configuration 56 for securing the adapter. Since the lower or inner side 47 of an arm of a dredge cutterhead is more difficult to access, the coupling configuration is preferably formed to be on the upper or outer side 55 of the arm. Nevertheless, alternative constructions are possible. For instance, the legs could be reversed on the arm or a coupling configuration could be provided on both of the upper and lower sides of the arms. The legs 38, 42 and body 40 collectively define an inner surface 54 that faces the arm. To facilitate effective welding of the base to the arm, the inner surface 54 is shaped to substantially conform to the contour of the portion of arm 48 it opposes. The base is welded to the arm along substantially its entire perimeter to securely fix the base to the cutterhead.

In a preferred construction, the inner surface 59 of base 32 sets against seats 61 prepared in sides 47, 55 of arm 48. For illustration purposes, upper leg 42 of base 32 is shown engaged with seat 61 in side 55 of arm 48. While other seats or no seat could be used, seat 61 defines a recessed portion in the arm which is slightly wider than the lower end 62 of base 32. The seat defines a main surface 63 and inclined walls 67 extending upward to the upper surface 55 of the arm. On account of the spacing of walls 67, as can be seen in FIG. 21, a trough 81 is defined along each side of base 32. The trough preferably extends along the entire periphery of base 32, but it is not essential that it do so. As is known, a weld bead 82 is placed in trough 81 to secure base 32 to arm 48. The welding process forms a heat affected zone 83 all around the weld bead 82, including a heat affected zone 83a in base 32 and a heat affected zone 83b in arm 48. The heat affected zones of the components are weakened as compared to the portions outside of the heat affected zones.

In the preferred construction, upper leg 42 of base 32 includes foot 84 and a tongue 57 defined by a stem 85 and rails 87. The undersurface 89 of foot 84 sets against main surface 63 of seat 61. While a ridge 91 and valley 93 is preferably formed along the midpoint of foot 84 for positioning and additional lateral support, this construction is not essential. Also, the ridge and valley could be reversed.

The undersurface 89 of base 32 is further provided with a groove 95 that generally parallels the outer sidewall 99 of foot 84. As best seen in FIG. 22, groove 95 preferably has an outer wall 95a that is spaced from sidewall 99. Outer wall 95a, at the bottom of groove 95, transitions into a rounded dome wall 95b which, in turn, turns into an inclined inner wall 95c. The dome wall 95b is deemed to be the bottom of the groove irrespective of the actual orientation of the part. In general, in a preferred construction, the groove is preferably spaced from outer wall 99 of the welded part so as to be just outside of the heat affected zone, though the groove could be closer or farther from the outer wall so long as the groove is sufficiently far from wall 99 to avoid breakage and sufficiently close to redirect the stress concentrations to the material forming the groove. As can be appreciated, the welding process causes great heating of both base 32 and arm 48 along with the weld material. These portions are considered to have been weakened on account of this heating. The height H of the groove is variable, but in one preferred embodiment the height is slightly larger than the thickness of the heat affected zone 83a. Similarly, groove 95 can have different width dimensions, but in one preferred construction has a width W that is about 1½ times larger than the height. As one example only, in a base 32 with a foot 84 having a width of 69 mm and a height of 15 mm, the groove could have a height H of 2.7 mm, a width W of 4.8 mm and be spaced a distance S 2.3 mm from sidewall 99. Numerous variations in shape and size could be used in forming the foot 84 and groove 95.

As the weld bead cools, it contracts to leave a residual tensile stress along the sides of the joint. The abutment of undersurface 89 against main surface 63 defines unwelded surfaces within the uniting of base 32 and arm 48 by weld bead 82. These unbonded surfaces define a gap 102 (or the effect of a gap even if the surfaces are completely flush with each other), which acts like a crack when under load. As can be appreciated, loads transferred through weld bead 82 can produce high stresses at the end of the gap (i.e., at the bottom of the weld joint). This is also at the start of the heat affected zone 83, which is already weakened due to the heat.

The formation of groove 95 near weld bead 82 reduces the stress in the weld. As the weld bead cools and contracts, it draws the lip 111 (i.e., the portion of foot 84 between outer wall 95a and sidewall 99) outward. In this way, the residual stress is concentrated at the top of the groove (i.e., along dome surface 95b), rather than at the end of gap 102. The top of the groove has a smooth radius, which provides a much lower stress concentration factor than the sharp end of the gap. It is also formed in the parent metal of the part, which is stronger than the weld material at the end of the gap. This construction, then, greatly reduces the tendency of the weld to crack. Moreover, in the preferred construction, the stress concentration is resisted by material outside of the heat affected zone.

The provision of groove 95 in the underside of base 32 also eases and improves the removal of the base from arm 48. When cutting the welded part away from the base surface with a torch (not shown), the user can easily follow the groove by sight. In this way, the contour that remains after the cutting is very near the original weld prep shape, and little clean-up is required before welding on a replacement part. Groove 95 preferably extends along the edge portions of the part subject to being welded, in the illustrated embodiment it preferably extends along the entire periphery of base 32, but could be less if desired.

While the above-discussion describes the use of a groove in the underside of a base welded to an arm of a dredge cutterhead, the groove could be used to secure a base or other welded components to a wide array of excavators including, for example, front end loaders, electric shovels, hydraulic excavators, hydraulic shovels, clamshells, draglines, rock grapples, dragheads and other equipment. As examples only, the groove could be also be used to attach a weld-on adapter, shroud or other member to an excavator. Furthermore, the use of such a groove can provide benefits in attaching a wide array of welded parts to a support surface in a myriad of different structures inside and outside the dredging, mining and construction industries.

Upper leg 42 extends rearward of body 40 along upper side 55 of the arm to define coupling configuration 56 for securing the adapter. The coupling configuration is preferably an axial T-shaped tongue 57 that slidably engages a complementary construction 58 on adapter 34. Nonetheless, other constructions provided with at least one laterally extending shoulder could be used to couple the adapter and the base. As examples, the coupling configuration 56 could be formed as other generally T-shaped tongues such as a dovetail tongue and other tongues that laterally broaden in a symmetrical manner, other non-symmetrical shaped tongues, or a slot having T, dovetail or other shape. In any event, the upper leg preferably extends initially upward above body 40 to enable the adapter to slide past the body and couple with the tongue. The rear end wall of upper leg 42 defines a rear bearing surface 60 adapted to engage lock 36. As discussed more fully below, the rear bearing surface is preferably curved and most preferably defines a convex spherical segment (FIG. 2). Nonetheless, a flat rear bearing surface could be used, albeit with reduced benefits.

The body 40 projects forward from the front edge 44 of arm 48 to resist the forces applied to the tooth 30 during use. In the preferred construction, the body includes sidewalls 50, 52, top and bottom walls 64, 66 and a front bearing surface 68. The front bearing surface 68 has a convex, curved shape, as discussed more fully below, to maintain a substantially full face contact with a complementary surface on the adapter during transverse loading of the tooth. In the preferred construction, front bearing surface 68 defines a convex spherical segment (as illustrated by the shaded portion in FIG. 2) to accommodate transverse loading in any direction, such as, side loads, upward loads, downward loads or virtually any load that applies a force transverse to the longitudinal axis 69 of the tooth. Nevertheless, bearing surface 68 could be formed with a surface that is curved in both horizontal and vertical directions but is not spherical. In this type of construction the radii of curvature for either or both curved directions could be fixed or variable. Moreover, the bearing surface 68 could be provided with a curved shape in only one direction, although with reduced benefits. For instance, bearing surface 68 could be curved in only a horizontal or vertical direction or in any particular desired direction. However, when curved in only one direction, the desired full face contact can only be maintained for transverse loading in the same general direction as the curvature of the bearing surface.

The radius (or radii) of curvature defining bearing surface 68 is based upon the relative gap that exists between the base and the adapter. For instance, a clearance is formed between the parts to ensure the adapter can be coupled to the base, especially along the coupling configuration. When a lateral load is applied to the tooth tip, the adapter will rotate until the gaps along the sides close at diagonally opposing corners forming a couple to oppose the lateral load. If the gap between the base and the adapter is the same along the front end and the rear end of base 32, then the center of rotation of the adapter will be at about the mid point M of base 32 (i.e., the mid point between bearing surfaces 60, 68). However, if the gap is smaller at one end as compared to the other end, then the center of rotation will be closer to the end with the smaller gap depending on the amount of the disparity between the parts, i.e., the greater the disparity in the gaps, the greater the center of rotation shifts toward the end with the smaller gap. In the preferred construction, the center of rotation is used as the imaginary center point for the radius of curvature. As can be appreciated, the differences in the clearance along the sides could be different than the clearance along the top and bottom of the base and adapter. In this construction, the curvature in the horizontal direction is preferably different than the curvature in the vertical direction so as to correspond to the spacing of the different clearances.

In the preferred construction, as shown in FIG. 2, the rear bearing surface 60 is curved in the same way as front bearing surface 68, although they could be different. Accordingly, the rear bearing surface can be varied in the same manner as discussed above for front bearing face 68 (e.g., with curves in one or more directions). Preferably, the rear and front bearing surfaces 60, 68 are defined by radii of curvature that initiate from the same point that matches the center of rotation of the adapter. However, due to unavoidable deflection of the parts under heavy loads, there can be some divergence of the points defining the radii of curvature for the front and rear bearing surfaces. Further, rear bearing surface 60 can have a widely different starting point for defining the radius of curvature, or it can even be flat, though such a construction will impose higher stresses on the lock and rear of the base. Hence, the front and rear bearing surfaces may have the same curvature, but also may simply have corresponding curvatures, i.e., where the radius of curvature originates at the same point even though they may each have different lengths. For example, if the center of rotation of the adapter, as discussed above, is closer to the rear end than the front end, then rear bearing surface 60 will preferably have a smaller radius of curvature than front bearing surface 68.

The front edge 44 of arm 48 is preferably provided with a plurality of spaced apart locator formations 65 for mounting the excavating teeth. In a preferred embodiment, each locator formation includes a locator nose 70 (FIG. 5) that projects from a recess 71. In the preferred construction, each locator nose is cast as part of the arm with a particular shaped core in the mold. The core is placed in the mold in the orientation needed for positioning each tooth properly on the arm. In this way, there are no difficulties in positioning the adapters on the arms. The locator noses 70 cast in the arm 48 already provides the desired orientation for the tooth.

In the preferred construction, the locator nose projects from a recess 71 formed in the front edge of arm 48. The trough surfaces 72 in the bottom of the recesses oppose the inner edges 53, 54 of the sidewalls 50, 52 of the body of the base preferably leaving a small gap. This gap also enables the operator to more easily cut the base from the arm if needed. A space 73 preferably exists between the outer surfaces 74, 75 of sidewalls 50, 52 and the bevel surfaces 76 to accommodate the application of a weld. The adapter includes a coupling formation 78 that interacts with the locator formations 65 to properly position the excavating tooth for maximum cutting efficiency. In this construction, the body 40 of base 32 defines a pocket 77 that matingly receives the locator nose 70 to properly position and support the base on the arm. The side faces 79 and free end face 80 of nose 70 fit against complementary surfaces defining pocket 77 to properly orient the tooth on the arm and provide support for the boss in addition to the welds. For this reason, noses 70 preferably have a considerable forward extension. In a preferred construction, the noses extend approximately 1.50 inches beyond trough surfaces 72 and within a range of about 0.75 to 2.25 inches. Nevertheless, lesser or greater nose extensions could be used.

The wear member in the form of adapter 34 (FIGS. 1 and 7-9) has a rear portion 86 that mounts to base 32 and a front portion 88 for holding a point or tip (not shown). In the preferred construction, the front portion includes a forwardly projecting nose 90 that is received into the socket of a point. The nose can have any configuration for mounting a point. In this embodiment, the front portion further includes a slot 92 for receiving a lock pin (not shown) to hold the point to the adapter. The rear portion 86 includes an upper leg 94, a lower leg 96, and a mid portion 98. Lower leg 96 of adapter 34 overlies bottom wall 66. The rear end 97 of leg 96 opposes front wall 101 of the base so that under extreme loads wall 101 functions to stop the shifting of the adapter on the base. Upper leg 94 extends rearward to overlie top wall 64 and upper leg 42 of base 32. The upper leg of adapter 34 includes a coupling configuration 58 that is adapted to mate with the coupling configuration 56 of base 32. Hence, the coupling configuration of adapter 34 can be varied in the same way as the coupling configuration for base 32. In the preferred construction, upper leg 94 includes a T-shaped slot 103 that matingly receives T-shaped tongue 57. The T-shaped slot 103 is open along the inner surface 104 and in the rear wall 106 of upper leg 94 to facilitate receipt of tongue 57. Ribs 107 are preferably formed along the inner edge 108 of mid portion 98 for enhanced strength to resist cracking during use (FIGS. 1, 7 and 8).

The mid portion 98 of adapter 34 includes an interior recess 109 having an abutment or abutting surface 105 adapted to abut front bearing surface 68 of base 32. Abutment 105 is arcuate and concave in shape to match the arcuate front bearing surface 68. Accordingly, abutment 105 and bearing surface 68 each preferably define a spherical segment with essentially the same radius of curvature, although the curves could differ within a certain range of values primarily because of deflection that occurs in the parts under heavy loading. As discussed above, the preferred shape of abutment 105 and bearing surface 68 is defined by a radius of curvature that is determined by the clearance between the front and rear end portions of the adapter and base. In the most preferred configuration, the gaps between the base and the adapter are uniform from front to back along the sides and along the top and bottom so that the curved bearing surfaces 68, 105 each define a spherical segment. The actual desired size of the radius of curvature defining the spherical segments would depend on the gaps as well as the actual size of the part. As a general rule, the radius of curvature defining surfaces 68, 105 is preferably not larger than the length of base 32 (i.e., the distance between rear and front bearing surfaces 60, 68) to avoid having too broad of an arc.

As seen in FIG. 15, a side load L1 tends to rotate adapter 34 relative to base 32 about a center of rotation C. The radius of curvature defining bearing surfaces 68, 105 originate from the same center of rotation. Because of the mating arcuate configuration of abutment 105 and bearing surface 68, these surfaces remain in essentially full bearing contact with each other. Accordingly, no forces are applied as point contacts in the axial direction to prematurely wear the parts. Instead, the axial loads are spread out over substantially the whole of the abutment 105 and bearing surface 68 to greatly reduce the stress in the parts. As a result, the high stresses accompanying resultant forces R2, R3 (FIG. 16) are essentially eliminated.

Adapter 34 further includes an opening 110 in a rear portion of upper leg 94 (FIGS. 1 and 7-9). In the preferred construction, opening 110 has a generally rectangular configuration with a curved front wall 113 and a curved rear wall 115. Nevertheless, it is not necessary that the walls be curved or that the opening has an overall generally rectangular configuration. Rather, the opening can have virtually any shape so long as it receives the lock which, in turn, secures the adapter to the base. If there is any shifting of adapter 34 during use, the lock 36 tends to move with the adapter. Hence, there is ordinarily no significant shifting between the lock and the adapter and thus no undue wearing therebetween. Rear wall 115 preferably includes a hole 117 that extends through the rear end 106 of upper leg 94 to accommodate an adjustment assembly of lock 36. Nevertheless, hole 117 could have a variety of different shapes or be eliminated if an adjustment assembly is not used or one is used that does not require the space provided by hole 117.

Lock 36 is adapted to be received in opening 110 (FIGS. 1 and 10-14). In the preferred construction, lock 36 has a generally rectangular configuration with a curved front wall 123 and a curved rear wall 125 to match the configuration of opening 110. Although shifting between the adapter and lock is not likely, the curved walls 115, 125 tend to reduce any wearing in the event shifting occurs. Nevertheless, lock 36 may have a varied shape in the same way as discussed above for opening 110.

In the preferred construction, lock 36 comprises an outer part 127, an inner part 129, a resilient member 131 and an actuator, preferably in the form of a screw 133. Outer part 127 defines a cavity 134 for receiving the inner part 129 and resilient member 131. In general, outer part 127 is generally C-shaped to include a base wall 135, a top wall 137 and a bottom wall 139. A pair of lips 141, 143 extends toward each other from the top and bottom walls 137, 139 to contain the inner part 129 and resilient member 131 in cavity 134. Base wall 135 includes an aperture 136 for receiving screw 133. The inner part also has a generally C-shaped configuration with a center wall 147 and two sidewalls 149. The two C-shaped components fit together to generally define a box-like shape. In the preferred curved construction, sidewalls 149 are at obtuse angles to center wall 147 to match the side edges 150 of outer part 127. An internally threaded boss 151 extends rearward from the center of center wall 147 to receive screw 133. Resilient member 131 is preferably an elastomer. In the preferred construction, the elastomer is composed of neoprene or rubber, although other types of elastomeric materials can be used. The elastomer is shaped for receipt in inner part 129 about boss 151. In the preferred embodiment, resilient member 131 has a base portion 132 with an aperture 138 and a pair of arm portions 142. Nevertheless, other shapes could be used. Moreover, other kinds of resilient members could be used, such as Bellville springs or a coiled spring.

The lock is assembled by placing the resilient member 131 about boss 151 in inner part 129. The combined inner part and resilient member are then inserted laterally into the side of cavity 134 in outer part 127, i.e., by side edges 150. Once boss 151 is aligned with aperture 136, screw 133 is preferably back threaded into boss 151 until it is received into aperture 136. The screw ensures that the component parts do not become inadvertently disassembled.

In use, lock 36 is inserted into opening 110 after adapter 34 is placed over base 32 with tongue 57 received in slot 103 (FIG. 1). Screw 133 includes a head 153 with some means for engaging a tool (not shown) for turning the screw. In the preferred embodiment, screw head 153 has internal flats 155 for receiving an appropriate wrench. The free end of screw 133 includes a bearing surface 157 that abuts rear bearing surface 60 when the screw is advanced.

Further advancement of screw 133 against rear bearing surface 60 causes the rear face 125 of base wall 135 to push rearwardly against the rear wall 115 of opening 110. This expansion of the lock results in abutment 105 of adapter 34 being brought into tight abutting relationship with front bearing surface 68 of base 32. Further advancement of screw 133 following such abutment will then cause the inner part 129 to move toward the outer part 127 to compress resilient member 131 until sidewalls 149 abut base wall 135. The sidewalls will abut base wall 135 to prevent over-compression of the resilient member. If the elastomer is a non-compressible rubber material or the like, there is enough open space between the inner and outer parts to permit the inner part 129 to be drawn against the outer part 127. Depending on the resistance in coupling the adapter to the base, the resilient member may compress in some instances before the adapter is fully tightened onto the base. In any event, with inner part 129 in abutting contact with outer part 127, lock 36 initially is a rigid lock member. As wear begins to develop between adapter 34 and base 32, resilient member 131 expands to dampen movement of the adapter relative to the base and maintain a tight relationship between the components of the tooth. This expansion of lock 36 continues to hold the components tightly together until resilient member 131 reaches its fully expanded position (i.e., when the inner part abuts against lips 141, 143).

Bearing surface 157 on screw 133 preferably has a concave, arcuate surface to engage the corresponding rear bearing surface 60 (FIG. 14). In the most preferred construction, bearing surface 60 and 157 are each formed as a spherical segment. In this way, bearing surface 157 remains in substantially full contact with rear bearing surface 60 as adapter 34 shifts under transverse loading (i.e., as the adapter rotates about its center of rotation). While bearing surfaces 60 and 157 can be formed with the same radius of curvature, bearing surface 157 of screw 133 can alternatively be formed with a smaller radius of curvature so as to contact rear bearing surface 60 with a circular contact. The spherical configuration of the rear base surface still enables the circle contact of screw 133 to remain in substantially full contact with base 32 during any shifting of the adapter.

Alternatively, other locks could be used so long as they abut adapter 34 and base 32 so as to prevent the adapter from sliding forwardly off of the base. For example, a lock with a different adjustment assembly could be used, such as the fluid actuator as disclosed in U.S. Pat. No. 5,653,048 to Jones et al., herein incorporated by reference. Similarly, an opening and lock such as disclosed in U.S. Pat. No. 5,088,214 to Jones et al., herein incorporated by reference, without an adjustment assembly could also be used.

In an alternative construction, weld-on adapters 175 can be mounted on the locator formations 65 of the dredge cutterhead arm 48 without bases 32 (FIG. 19). While the use of such adapters does not provide the easy removal and installation procedures of the mechanically attached adapters discussed above, the locator formations still provide easy positioning of the adapters as well as additional support. In a preferred construction, adapters 175 include a pair of bifurcated legs 177, 178 that straddle the arm, although a single leg could be used (not shown). If a single leg is used, the leg will preferably be located on the upper side of the arm to enable easier welding of the adapter to the arm. The adapter includes a coupling formation 180 to matingly fit with the locator formations 65 so as to properly position the adapter, and thus, the tooth point (not shown) for maximum digging efficiency. As with base 32, adapters 175 include a pocket 183 that matingly receives nose 70 with surfaces that oppose side faces 79 and end face 80 to properly position and support the adapter in use. The adapter is then welded along all or parts of its periphery. Also, as with boss 32, the adapter is preferably spaced from the trough surfaces 72 for easier removal of the adapter from the arm.

In another alternative construction, adapter 175a includes a coupling formation 180a that does not rely upon nose 70 for positioning and support (FIG. 20). In this arrangement, each locator formation includes a pair of spaced apart surfaces having a particular shape and spacing to engage, support and properly position a wear member. For example, trough surfaces 72 to each side of nose 70 are formed with a shape that matches the inner edge surfaces of the bight 185a interconnecting legs 177a, 178a. The bight surface 185a, then, sets against trough surfaces to properly orient the tooth. An adapter with coupling formation 180a can include an enlarged pocket 183a that does not engage nose 70 or can be used with an arm that does not include a nose 70.

In another alternative construction, another weld-on adapter can be fit over base 32. In this construction, the adapter includes a pocket that matingly receives body 40 and includes a configuration, such as a recess, that enables the arm to fit over but not connect to the tongue of base 32. Alternatively, a base without a leg or with a leg having no coupling tongue could be used with such a weld-on adapter. In either case, the body 40 of base 32 properly orients and provides support to the adapter, which is then welded to the arm.

In another alternative construction (FIGS. 23-28), wear assembly 230 is secured to arm 48. As with assembly 30, assembly 230 is described in terms of mounting an adapter on a cutterhead, but it could be used to secure other wear members to other excavating equipment. Assembly 230 includes a base 232 fixed to arm 48 by welding, mechanical attachment or by being cast with the arm, and a wear member or adapter 234 fit over the base. Base 232 and adapter 234 are similar to base 32 and adapter 34 in construction and purpose, and are essentially the same except as described below.

Base 232 includes a front bearing surface 268 to engage a complementary abutting surface 305 of adapter 234 to primarily resist the heavy axial loading applied to tooth 230 during use. As discussed above in regard to assembly 30, bearing surface 268 and abutment 305 are curved, preferably about two perpendicular axes. However, unlike assembly 30, bearing surface 268 and abutment 305 are divided into sections by front stops 350, 351. In particular, bearing surface 268 includes a first section 268a above stop 350 and a second section 268b below stop 350. Likewise, abutting surface 305 is divided into a first section 305a above stop 351 and second section 305b below stop 351. In a preferred embodiment, bearing surface 268a and abutting surface 305a have complementary surfaces that conform to a spherical segment. Likewise, bearing surface 268b and abutting surface 305b have complementary surfaces that conform to a spherical segment, but one which is concentric to bearing and abutting surfaces 268a, 305a. In this way, sections 268a, 268b 305a, 305b function essentially as unified front bearing and abutting surfaces 268, 305 in resisting the axial loading.

As described above for assembly 30, the curved bearing and abutting surfaces 268, 305 enable to the parts to move relative to each other under load without creating undue stress concentrations in the corners of the components as in the past. Unrestricted motion between the components, however, can lead to undesirable wear rates. Loads with upward components are, without front stops 350, 351, resisted primarily by lower faces 370, 371 and by the tongue and slot arrangement 257, 303. However, flexing of the adapter 234 causes faces 305a, 305b to slide along faces 268a, 268b. The relative movement between the base and the adapter can be significant and lead to premature wearing of both components. The provision of stops 350, 351 at the front of the base (i.e., where the sliding occurs) and extending generally transverse to the direction the adapter rocks over the base is effective in resisting and reducing such relative motion and, in turn, reducing wearing of the components.

Flexing of leg 294 caused by upward loading of tooth 230 also tends to slide upper leg 294 of adapter 234 axially along leg 242 of base 232. However, complementary stops 355, 356, 360, 361 are preferably provided to resist such relative sliding of legs 242, 294. In a preferred construction, base 232 includes axially spaced stops 355, 360 along leg 242. A medial stop 355 projects upward at a medial portion of base 232, preferably around the intersection of legs 238, 242 (although other positions are possible), and a rear stop 360 projects upward proximate rear wall 260. Adapter 234 includes a recess 309 to at least partially receive base 232, and an opening 310 to receive lock 36 (FIG. 23). Recess 309 includes a plurality of complementary stops 356, 361 to abut stops 355, 360, respectively (FIGS. 23 and 26-28). Stops 356, 361 are to (i) be generally transverse to the axis and expected sliding of the leg, (ii) provide additional surface area to better resist rocking of adapter 234 under upward loads, and (iii) be spaced apart along the leg to better reduce relative shifting of all portions of the adapter under upward loading. While stops 355, 356, 360, 361 are intended to supplement front stops 350, 351, it is possible to rely upon only one or a pair of the front, medial or rear stops.

Base stops 355, 360 and adapter stops 356, 361 define tiers or stair-steps to resist the upward loads without unduly enlarging the size of the assembly and to facilitate easy casting of the component. For example, medial stop 355 extends farther from arm 48 than the front bearing surface 268, and rear stop 360 extends farther from arm 48 than medial stop 355. Stops 355, 356, 360, 361 could be laterally spaced relative to each other, instead of or in addition to being vertically spaced, in their medial and rear positions. Stops 355, 356, 360, 361 are preferably planar, but could alternatively be arcuate or conformed to a spherical segment. Moreover, stops 355, 356, 360, 361 can be vertical or somewhat inclined so long as they are generally transverse to the expected direction of shifting of the component.

For downward loads, lower leg 238 of base 232 includes a lower stop 365 adapted to abut complementary stop 366 formed on the end of lower leg 296 of adapter 234. In the same way as described for stops 355, 356, 360, 361 for upward loading, stops 365, 366 resist rocking of the adapter on the base for downward loading.

The above-discussion concerns the preferred embodiments of the present invention. Various other embodiments as well as many changes and alterations may be made without departing from the spirit and broader aspects of the invention as defined in the claims.

Claims

1. A wear member for mounting on a base fixed to excavating equipment, the wear member comprising:

a front end;

a curved abutting surface for abutting a front bearing surface of the base;

a rearwardly extending leg including an axial slot to receive a tongue of the base;

an opening for receiving a lock to releasably secure the wear member to the base; and

a stop extending generally transverse to the abutting surface and subdividing the abutting surface into a plurality of sections, the stop abutting a complementary stop on the base to resist movement of the wear member on the base under certain loading conditions.

2. A wear member in accordance with claim 1 wherein the abutting surface is curved about two perpendicular axes.

3. A wear member in accordance with claim 2 wherein a first section of the abutting surface is concentric to a second section of the abutting surface.

4. A wear member in accordance with claim 1 wherein the abutting surface generally conforms to a spherical segment.

5. A wear member in accordance with claim 4 wherein a first section of the abutting surface is concentric to a second section of the abutting surface.

6. A wear member in accordance with claim 5 further including at least one stop projecting from the leg in a generally transverse direction relative to the leg.

7. A wear member in accordance with claim 6 wherein said at least one stop includes a rear stop positioned in a rear portion of the wear member.

8. A wear member in accordance with claim 7 wherein said at least one stop includes a medial stop positioned in a mid portion of the wear member.

9. A wear member in accordance with claim 8 further including a second leg, wherein one said leg is an upper leg with said rear and medial stops, and the second leg is a lower leg provided with a lower stop.

10. A wear member in accordance with claim 6 wherein said at least one stop includes a medial stop positioned in a mid portion of the wear member.

11. A wear member in accordance with claim 6 further including a second leg, wherein said one leg is an upper leg with one said stop, and the second leg is a lower leg provided with one said stop.

12. A wear member in accordance with claim 1 further including at least one stop projecting from the leg in a generally transverse direction relative to the leg.

13. A wear member in accordance with claim 12 further including a second leg, wherein said one leg is an upper leg with one said stop, and the second leg is a lower leg provided with one said stop.

14. A wear member in accordance with claim 1 wherein the front end includes a nose for mounting a point.

15. A wear member for mounting on a base fixed to excavating equipment, the wear member comprising:

a front end;

a curved abutting surface for abutting a front bearing surface of the base;

at least one rearwardly extending leg including an opening to receive a lock to retain the wear member to the base, an axial slot to receive a tongue of the base, and at least one stop extending generally transverse to the leg between the opening and the abutting surface to abut a complementary stop on the base and resist movement of the wear member on the base under certain loading conditions.

16. A wear member in accordance with claim 15 wherein said at least one stop includes a rear stop proximate the opening and a medial stop proximate the front bearing surface.

17. A wear member in accordance with claim 16 wherein said stops are arranged in a tier along the leg.

18. A wear member in accordance with claim 15 further including another leg provided with a stop extending generally transverse to the leg between the opening and the abutting surface to abut a complementary stop on the base and resist movement of the wear member on the base under certain loading conditions.

19. A wear assembly for excavating equipment comprising:

a base fixed to the excavating equipment, and including a front curved bearing surface, a rearwardly extending tongue, and a stop extending generally transverse to the front bearing surface and subdividing the front bearing surface into a plurality of sections;

a wear member including a front end, a curved abutting surface for abutting the front bearing surface of the base, at least one rearwardly extending leg including an axial slot to receive the tongue of the base, an opening, and a stop extending generally transverse to the abutting surface, subdividing the abutting surface into a plurality of sections, and abutting the stop of the base to resist movement of the wear member on the base under certain loading; and

a lock received in the opening to releasably hold the wear member to the excavating equipment.

20. A wear assembly in accordance with claim 19 wherein the wear member further includes at least one stop projecting from the leg in a generally transverse direction relative to the leg.