EP2865814B1

EP2865814B1 - Wear assembly for excavating equipment

Info

Publication number: EP2865814B1
Application number: EP14180150.6A
Authority: EP
Inventors: Charles G. Ollinger VI.; Chris D. Snyder; John S. Kreitzberg
Original assignee: Esco Group LLC
Current assignee: Esco Group LLC
Priority date: 2007-05-10
Filing date: 2008-05-06
Publication date: 2019-01-02
Anticipated expiration: 2028-05-06
Also published as: PL2865814T3; NZ581007A; CN103147480A; DK2889434T3; LT2889434T; EP2910692A3; CN102720244B; AU2008251647A1; KR101618022B1; CA2686620A1; MX2009012181A; PT2865814T; BR122015006394B1; HK1138893A1; EP2889434A1; SI2910692T1; CO6241176A2; CN101688385B; KR20150044974A; PT2910692T

Description

The present invention pertains to a wear member and to a wear assembly for securing said wear member to excavating equipment, and in particular to a wear assembly that is well suited for attachment and use on a dredge cutterhead.
In EP 1 239 088 A1 is disclosed a wear assembly having a base portion and a wear member for excavating equipment. A working section and a mounting section generally aligned along a longitudinal axis are provided. The mounting section includes a socket for receiving a base fixed to the excavating equipment. The working section is located forward of the socket. A leading side is adapted to be a forward surface during advance of the wear member through the ground during a digging operation. A trailing side is adapted to be a rearward surface during advance of the wear member through the ground.
Furthermore, dredge cutterheads are used for excavating earthen material that is underwater, such as a riverbed. In general, a dredge cutterhead 1 includes several arms 2 that extend forward from a base ring 3 to a hub 4, see 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 releasably attached to the bases by locks 8.
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. 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 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.
The cutterheads are rotated such that the teeth are driven into and through the ground at a rapid rate. Consequently, considerable power is needed to drive the cutterhead, particularly when excavating in rock. In an effort to minimize the power requirements, dredge points are typically provided with elongate, slender bits for easier penetration of the ground. However, as the bit becomes shorter due to wear, the mounting sections of the points will begin to engage the ground in the cutting operation. The mounting section is wider than the bit and is not shaped for reduced drag. On account of the resulting increased drag the mounting sections impose on the cutterhead, the points are usually changed at this time before the bits are fully worn away.
According to the first aspect of the invention, a wear member for excavating equipment comprises a working section and a mounting section. The mounting section includes a socket for receiving a base fixed to the excavating equipment to mount the wear member on the excavating equipment. The socket includes a front end and a main portion rearward of the front end, wherein the front end has a front bearing surface generally transverse to the longitudinal axis. The main portion of the socket and an external surface of the mounting section each have a generally trapezoidal configuration transverse to the longitudinal axis.
Especially, the socket has upper, lower and side surfaces that are bowed inwardly across substantially their entire widths.
According to a further preferred embodiment the front bearing surface in the front end of the socket is generally hemispherical.
According to a further aspect of the invention, the wear member includes an opening for receiving a lock to secure the wear member to the base.
In a preferred embodiment the socket includes an upper surface, a lower surface and sidewalls that are each bowed inwardly to be received into a trough formed on the base.
Especially, the socket and the external surface of the mounting section each has a generally trapezoidal configuration transverse to the longitudinal axis at substantially any point along the entire length of the socket and mounting section.
According to a further aspect of the invention, the leading side has a greater width than the trailing side in transverse cross sections perpendicular to the longitudinal axis along at least the front end of the mounting section.
In accordance with an aspect of the invention a wear assembly for excavating equipment comprises a base fixed to the excavating equipment, a wear member as mentioned above and a lock for releasably holding the wear member to the base.
Especially, the base includes a nose which has a generally trapezoidal configuration transverse to the longitudinal axis to substantially conform to the shape of the socket.
According to a further aspect of the invention the base includes mounting portion adapted for attachment to an arm of a dredge cutterhead.
Further advantages and possible applications of the present invention become apparent from the following detailed description with reference to the exemplifying embodiments illustrated by way of example in the drawings.
In the description, the appended claims, the abstract and in the drawings, use is made of the terms and corresponding reference numerals summarised in the list provided at the end of the description. In the drawings is shown

Fig. 1: a wear assembly in accordance with the present invention;
Fig. 2: a side view of a wear member of the invention;
Fig. 2A: a side view of a conventional wear member;
Fig. 3: a cross-sectional view taken along line 3-3 in Fig. 2;
Fig. 3A: a cross-sectional view taken along line 3A-3A in Fig. 2A;
Fig. 4: a cross-sectional view taken along line 4-4 in Fig. 2;
Fig. 5: a cross-sectional view taken along line 5-5 in Fig. 2;
Fig. 6: a cross-sectional view taken along line 6-6 in Fig. 2;
Fig. 6A: the cross-sectional view taken along line 6A-6A in Fig 2A;
Fig. 7: a cross-sectional view taken along line 7-7 in Fig. 2;
Fig. 8: a cross-sectional view taken along line 8-8 in Fig. 2;
Fig. 9: a cross-sectional view taken along line 9-9 in Fig. 1;
Fig. 10: a top view of the wear member;
Fig. 11: a rear view of the wear member;
Fig. 12: a perspective view of a nose of a base of the invention;
Fig. 13: a front view of the nose;
Fig. 14: a side view of the nose;
Fig. 15: an enlarged perspective view of a lock in the wear assembly;
Fig. 16: an enlarged perspective view of the lock in the wear assembly prior to tightening;
Fig. 17: a perspective view of the lock;
Fig. 18: a side view of the lock;
Fig. 19: an exploded, perspective view of the lock;
Fig. 20: a perspective view of the lock with the nose - the point has been omitted, and
Fig. 21: 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. In this application, 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.
The assembly is at times described in relative terms such as up, down, horizontal, vertical, front and rear; such terms are not considered essential and are provided simply to ease the description. The orientation of a wear member in an excavating operation, and particularly in a dredge operation, can change considerably. These relative terms should be understood with reference to the orientation of wear assembly 10 as illustrated in Fig. 1 unless otherwise stated.
Wear assembly 10 includes a base 12 secured to a dredge cutterhead, a wear member 14, and a lock 16 to releasably hold the wear member to base 12, Fig. 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, Fig. 1, 9 and 11-14. The base may be cast as part of the arm, welded to the arm, or attached by mechanical means. As examples only, 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 / EP 1 469 713 A2 .
In a dredge tooth, 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 18, see Fig. 1-10). Point 14 is rotated by the cutterhead such that it engages the ground in generally the same way with each digging pass. As a result, 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. In the present invention, 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, see Fig. 5) and at least partially through mounting section 23, see Fig. 4. In a preferred embodiment, trailing side 27 has a smaller width than leading side 25 throughout the length of point 14, see Fig. 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, see 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. On account of this narrowing of the point, sidewalls 29, 31 follow in the shadow of leading side 25 during digging and thereby create little drag on the cutting operation. In a preferred construction, sidewalls 29, 31 converge toward trailing side 27 at an angle 9 of about 16 degrees, see 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.
In use, dredge point 14 penetrates the ground to a certain depth with each digging pass - i.e., with each rotation of the cutterhead. During much of the point's useful life, the bit alone penetrates the ground. As one example, the ground level in one digging cycle extends generally along line 3-3, see 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.
In a preferred construction, 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 (ii) 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. As one example only, the cross-sectional configuration illustrated in Fig. 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.
As bit 21 wears away, the ground level gradually creeps rearward so that more rearward, thicker portions of the point 14 are pushed through the ground with each digging cycle. More power is therefore required to drive the cutterhead as the points wear. Eventually, enough of the bit wears away such that the mounting section 23 of the point 14 is being driven through the ground with each digging pass. In the present invention, the mounting section 23 continues to include side relief at least at the front end 40 of the mounting section, see Fig. 4, and preferably throughout the mounting section, see Fig. 4 and 7. As seen in Fig. 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. The inclination of sidewalls 29, 31 along line 4-4 is, in this one example, at an angle of about 26 degrees, see Fig. 4, but other inclinations can also be used. As discussed above, the desired side relief in the digging profile depends on the relation between the transverse inclination of the sidewalls and the axial expansion of the point.
In one conventional point 14a, 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 Fig. 3A, the digging profile 35a, i.e. along line 3A-3A, in Fig. 2A does not have sidewalls 29a, 31a that converge toward trailing side 27a, see Fig. 2A and 3A. Rather, sidewalls 29a, 31a in digging profile 35a expand outward at an increasingly greater slope as the sidewalls extend toward the trailing side. This outward flaring of sidewalls 29a, 31a will generate an increased drag on the cutterhead. The effective use of side relief in point 14 for the digging profile is a better reduction of drag than simply using sidewalls that convey in a transverse configuration.
In one other example, bit 21 has worn down to an extent where the portion of mounting section 23 along line 6-6, see 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. In conventional point 14a, mounting section 23a does not have a trapezoidal transverse configuration with sidewalls 29a, 31a that converge toward trailing side 27a, Moreover, as seen in Fig. 6A, sidewalls 29a, 31a diverge from leading side 25a in digging profile 45a taken along line 6a-6a encompassing the front end 40a of mounting section 23a. The lack of side relief in the digging profile imposes a heavy drag on the point 14a as it is driven through the ground especially as compared to the present inventive point 14. With the heavy drag produced by points 14a in this condition, many operators will replace the points when the mounting sections 23a begin to be driven through the ground even though bits 21a are not fully worn out. With the present invention, points 14 can stay on bases 12 until bits 21 are further worn out.
In a preferred construction, the tapering of sidewalls 29, 31 continue from front end 37 to rear end 47 of point 14. As seen in Fig. 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 8-8, see Fig. 2 and 8, i.e., sidewalls 29, 31 converge toward trailing side 27 even in this rearward digging profile 55.
The use of a point 14 with side relief in bit 21 and mounting end 23 as described above can be used with virtually any nose and socket configuration. Nonetheless, in one preferred construction, front end 58 of nose 18 includes a forward-facing bearing face 60 that is convex and curved about two perpendicular axes, see Fig. 1, 9 and 11-14. Likewise, the front end 62 of socket 20 is formed with a complementary concave and curved bearing face 64 to set against bearing face 60, see Fig. 1, 7, 9 and 11. In the illustrated construction, 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 .
Preferably, 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 ball surface of base 12. In a conventional tooth 10a, see Fig. 2A, the point shifts 14a around on the nose as the tooth is forced through the ground. The front ends of the socket and nose are angular with flat bearing surfaces and hard corners. During use, 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, In the present invention, 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, see 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. The term "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, see Fig. 11-14. Body 66 is defined by an upper surface 68, a lower surface 69 and side surfaces 70, 71. In a preferred construction, 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. In a preferred embodiment, 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.
Also, in a preferred embodiment, at least one of the body surfaces 68-71 and socket walls 78-81 - and preferably all of them - have mutually bowed configurations, see 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. Likewise, 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. While the bowed surfaces 68-71 and walls 78-81 are preferred, other trough and projection configurations such as disclosed in U.S. Patent Application No. 11/706,592 could also be used. Other rotation resisting constructions could also be used.
The use of 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. For example, if point 14 is initially installed on nose 18 out of proper alignment with the nose as it is fit onto the nose, 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. Some variations could also be used between the shapes of the socket and the nose so long as the socket predominantly matches the shape of the nose.
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. Likewise, 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. While contact between the various socket surfaces and the nose will likely occur during an excavating operation, contact between the corresponding front bearing surfaces 60, 64 and rear stabilizing surfaces 85, 95 is intended to provide primary resistance to the applied loads on the tooth and thereby provide the desired stability. While 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 light 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. 5,709,043 . With stabilizing surfaces 85, 95 extending about the entire perimeter of nose 18 or at least substantially about the entire perimeter, see Figs. 7, 9 and 11-14, they are also able to resist the non-axially directed loads applied in any direction.
Main portion 76 of socket 20 preferably has a generally trapezoidal transverse configuration to receive a matingly shaped nose 18, see 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 releasably 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, see Figs. 1, 9 and 15-20. Opening 101 preferably has an axially elongated shape and includes a front wall 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. In a preferred construction, 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. Further, 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 14 onto base 12, and to tighten the fit of wear member 14 onto nose 18. The use of a linear lock oriented axially increases the capacity of the lock to tighten the fit of the wear member on the nose; i.e., it provides for a greater length of take up. In a preferred embodiment, 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, see Fig. 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. Moreover, 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. Other tool engaging structures could be used in lieu of the illustrated head 134.
In use, wear member 14 is slid over nose 18 so that nose 18 is fit into socket 20, see Fig. 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. In any event, 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. The stability of the preferred nose 18 and point 14 enables the use of an axial lock, i.e., no substantial bending forces will be applied to the lock so that the high axial compressive strength of the bolt can be used to hold the wear member to the base. Lock 16 is lightweight, hammerless, easy to manufacture, does not consume much space, and does not require any openings in the nose.
In a preferred construction, lock 16 also includes an indicator 146 fit onto shaft 130 in association with nut 136, see Fig. 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. Alternatively, 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. In a preferred construction, 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.
When shaft 130 is turned and nut 136 drawn rearward, indicator 146 moves rearward - from the position in Fig. 16 - with nut 136 within opening 101. When indicator 146 aligns with marker 152, see Fig. 15, the operator knows that tightening can be stopped. At this position, lock 16 applies a predetermined pressure on wear member 14 irrespective of the wear on the nose and/or in the socket 20. Hence, both under-tightening and over-tightening of the lock can be easily avoided. As an alternative, indicator 146 can be omitted and shaft 130 tightened to a predetermined amount of torque.
The various aspects of the invention are preferably used together for optimal performance and advantage. Nevertheless, the different aspects can be used individually to provide the benefits they each provide.

Listofreferencesigns

10: wear assembly
12: base
14: wear member
16: lock
18: nose
20: socket
21: working section, bit
23: mounting section
25: leading side
27: trailing side, trailing wall
28: longitudinal axis
29: sidewalls
31: sidewalls
35: digging profile
37: front end
40: front end
45: digging profile
47: rear end
55: digging profile
58: front end
60: bearing face
62: front end
64: bearing surface"
65: small band
66: body
67: corner
68: upper surface
69: lower surface
70: side surface
71: side surface
76: main portion
77: corner
78: upper wall
79: lower wall
80: sidewalls
81: sidewalls
84: throughs
85: rear stabilizing surface
86: projection
95: rear stabilizing surfaces
97: exterior
101: opening
103: front wall
105: rear wall
107: side wall
109: side wall
111: rim
113: hole
115: stop
118: depression
119: rear face
121: recess
123: front end
124: rear end with head
130: shaft
134: rear end, head
136: nut
138: spring
140: disk
142: spacer, washer
146: indicator, marker
148: side edge
149: side edge
152: marker

Claims

A wear member (14) for excavating equipment comprising
a working section (21) and a mounting section (23) generally aligned along a longitudinal axis (28), the mounting section (23) including a socket (20) for receiving a base fixed to the excavating equipment, to mount the wear member (14) on the excavating equipment,
a leading side (25) adapted to be a forward surface during advance of the wear member (14) through the ground during a digging operation, and
a trailing side (27) adapted to be a rearward surface during advance of the wear member (14) through the ground,
the leading and trailing sides (25, 27) extending axially across the working and mounting sections (21; 23), characterized in that the leading side (25) having a greater width than the trailing side (27) in transverse cross sections perpendicular to the longitudinal axis (28) along at least part of the mounting section (23), and the socket (20) is formed with a generally trapezoidal transverse shape that generally corresponds to the transverse trapezoidal exterior profile of the wear member (14).
A wear member according to claim 1, characterized in that each wall of the socket (20) is bowed inwardly across substantially their entire widths.
The wear member according to claim 1 or 2, characterized in that the socket (20) in the front end (62) having a front bearing surface (64) which is generally hemispherical.
The wear member according to anyone of the preceding claims, characterized that an opening (101) for receiving a lock (16) to secure the wear member (14) to the base (12) is provided.
A wear assembly for excavating equipment comprising:
a base (12) fixed to the excavating equipment;

a wear member (14) according to anyone of the preceding claims and

a lock (16) for releasably holding the wear member (14) to the base (12).
The wear assembly according to claim 5, characterized in that the base (12) includes a nose (18) which has a generally trapezoidal configuration transverse to the longitudinal axis (28) to substantially conform to the shape of the socket (20).
The wear assembly according to claim 5 or 6, characterized in that the base (12) includes a mounting portion (23) adapted for attachment to an arm of a dredge cutterhead.