EP2865814B1 - Verschleißanordnung für Erdbewegungsmaschinen - Google Patents

Verschleißanordnung für Erdbewegungsmaschinen Download PDF

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Publication number
EP2865814B1
EP2865814B1 EP14180150.6A EP14180150A EP2865814B1 EP 2865814 B1 EP2865814 B1 EP 2865814B1 EP 14180150 A EP14180150 A EP 14180150A EP 2865814 B1 EP2865814 B1 EP 2865814B1
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EP
European Patent Office
Prior art keywords
wear member
socket
wear
nose
base
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP14180150.6A
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English (en)
French (fr)
Other versions
EP2865814A3 (de
EP2865814A2 (de
Inventor
Charles G. Ollinger VI.
Chris D. Snyder
John S. Kreitzberg
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Esco Group LLC
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Esco Group LLC
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Application filed by Esco Group LLC filed Critical Esco Group LLC
Priority to PL14180150T priority Critical patent/PL2865814T3/pl
Priority to SI200832038T priority patent/SI2865814T1/sl
Publication of EP2865814A2 publication Critical patent/EP2865814A2/de
Publication of EP2865814A3 publication Critical patent/EP2865814A3/de
Application granted granted Critical
Publication of EP2865814B1 publication Critical patent/EP2865814B1/de
Priority to HRP20190291TT priority patent/HRP20190291T1/hr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

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

Definitions

  • the present invention pertains to a wear 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.
  • 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.
  • dredge cutterheads are used for excavating earthen material that is underwater, such as a riverbed.
  • a dredge cutterhead 1 includes several arms 2 that extend forward from a base ring 3 to a hub 4, 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.
  • the cutterhead In use, the cutterhead is rotated about its central axis to excavate the earthen material. A suction pipe is provided near the ring to remove the dredged material. 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.
  • dredge points are typically provided with elongate, slender bits for easier penetration of the ground.
  • the mounting section is wider than the bit and is not shaped for reduced drag.
  • the points are usually changed at this time before the bits are fully worn away.
  • 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.
  • the socket has upper, lower and side surfaces that are bowed inwardly across substantially their entire widths.
  • the front bearing surface in the front end of the socket is generally hemispherical.
  • the wear member includes an opening for receiving a lock to secure the wear member to the base.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the base includes mounting portion adapted for attachment to an arm of a dredge cutterhead.
  • the present invention pertains to a wear assembly 10 for excavating equipment, and is particularly well suited for dredging operations.
  • the invention is described in terms of a dredge tooth adapted for attachment to a dredge cutterhead. Nevertheless, the different aspects of the invention can be used in conjunction with other kinds of wear assemblies, e.g., shrouds, and for other kinds of excavating equipment, e.g., buckets.
  • 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.
  • 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 .
  • 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.
  • point 14 includes a leading side 25 and a trailing side 27.
  • Leading side 25 is the side that first engages and leads the penetration of the ground with each rotation of the cutterhead.
  • trailing side 27 has a smaller width than leading side 25 - i.e., along a plane perpendicular to the longitudinal axis 28 of point 14 - through bit 21, see Fig.
  • 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.
  • 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.
  • 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.
  • 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.
  • side relief in the digging profile is dependent on the angle at which the sidewalls converge toward the trailing side and the axial slope or expansion of the point surfaces in a rearward direction.
  • the intention is to provide a width that generally narrows from the leading side to the trailing side when considered from the perspective of the digging profile.
  • Side relief in the digging profile preferably extends across the expected cutterhead digging angles, but benefit can still be obtained if such side relief exists in at least one digging angle.
  • the cross-sectional configuration illustrated in Fig. 3 represents one digging profile 35 for a portion of point 14 being driven through the ground.
  • bit 21 is still provided with side relief even in the digging profile as sidewalls 29, 31 converge toward trailing side 27 for reduced drag.
  • the mounting section 23 continues to include side relief at least at the front end 40 of the mounting section, 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.
  • 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.
  • bit 21a has a trapezoidal transverse configuration with a leading side 25a that is wider than trailing side 27a.
  • bit 21a does not provide side relief in the digging profile.
  • 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 .
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 .
  • 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 .
  • 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 .
  • 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.
  • 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.
  • point 14a shifts around on the nose such that the front of the socket 20a rattles around and against the front end of the nose, and the rear end of the socket shifts around and rattles against the rear end of the nose.
  • This shifting and rattling causes the point and base to wear
  • the use of generally hemispherical front bearing faces 60, 64 substantially reduces the rattle at the front end of the socket 20 and nose 18, 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.
  • 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.
  • body surfaces 68-71 diverge rearwardly so that nose 18 expands outward from front end 58 to provide a more robust nose to withstand the rigors of digging. Nevertheless, it is possible for only the upper and lower surfaces 68, 69 to diverge from each other and for the side surfaces 70, 71 to axially extend substantially parallel to each other.
  • Socket 20 has a main portion 76 rearward of front end 62 to receive body 66.
  • Main portion 76 includes an upper wall 78, lower wall 79 and sidewalls 80, 81 that conform to body surfaces 68-71.
  • body 66 and main portion 76 each have a trapezoidal transverse configuration.
  • the use of a trapezoidal shape predominantly along the length of nose 18 and socket 20 provides four corners 67, 77, which act as spaced ridges to resist turning of wear member 14 about axis 28.
  • 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.
  • 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.
  • troughs 84 and projections 86 and particularly those that are gradually curved and extending substantially across the entire widths of the surfaces 68-71 and walls 78-81 eases the assembly of point 14 onto nose 18; i.e., the troughs 84 and projections 86 cooperatively direct point 14 into the proper assembled position on nose 18 during assembly.
  • the engagement of projections 86 being received into the troughs 84 will tend to rotate the point into proper alignment as the point is fed rearward onto nose 18.
  • This cooperative effect of troughs 84 and projections 86 greatly eases and speeds installation and the setting of corners 67 into corners 77.
  • Nose surfaces 68-71 with troughs 84 are each preferably inclined axially to expand outward as they extend rearward to provide strength to nose 18 until reaching a rear stabilizing surface 85 of nose 18.
  • socket walls 78-81 with projections 86 also each expand to conform to surfaces 68-71.
  • Socket walls 78-81 also define rear stabilizing surfaces 95 to bear against stabilizing surfaces 85.
  • Rear stabilizing surfaces 85, 95 are substantially parallel to longitudinal axis 28. In one preferred embodiment, each stabilizing surface 85, 95 diverges axially rearward at an angle to axis 28 of about 7 degrees.
  • the rear stabilizing surfaces 85, 95 also preferably encircle - or at least substantially encircle - nose 18 and socket 20 to better resist non-axial loads.
  • stabilizing surfaces 85, 95 are preferably formed with short axial extensions, they could have longer or different constructions. Also, in certain circumstances, e.g., in 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 .
  • 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.
  • 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.
  • opening 101 is long enough and trailing wall 27 sufficiently inclined to provide clearance for stop 115 when wear member 14 is installed onto nose 18. Nevertheless, a relief or other forms of clearance could be provided in socket 20 if needed for the passage of stop 115.
  • the projection of stop 115 is preferably limited by the provision of a depression 118 to accommodate a portion of lock 16.
  • Lock 16 is a linear lock oriented generally axially to hold wear member 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.
  • 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.
  • 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.
  • shaft 130 is inserted through hole 113 and its front end 123 set in recess 121 of stop 115.
  • Lock 16 is positioned to lie along the exterior of nose 18 so that no holes, slots or the like need to be formed in the nose to contain the lock for resisting the loads.
  • Head 134 is engaged and turned by a tool to tighten the lock to a compressive state to hold the wear member; i.e., shaft 130 is turned relative to nut 136 so that front end 123 presses against stop 115. This movement, in turn, draws nut 136 rearward against spring 138, which is compressed between nut 136 and rear wall 105. This tightening of lock 16 pulls wear member 14 tightly onto nose 18 - i.e., with front bearing faces 60, 64 engaged - for a snug fit and less wear during use. Continued turning of shaft 130 further compresses spring 138. The compressed spring 138 then urges wear member 14 rearward as the nose and socket begin to wear.
  • Lock 16 is lightweight, hammerless, easy to manufacture, does not consume much space, and does not require any openings in the nose.
  • lock 16 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.
  • the indicator could have a threaded bore to function as the nut; if the indicator were omitted, other means would be required to hold nut 136 from turning.
  • Indicator 146 could also be discrete from nut 136.
  • Indicator 146 provides a visual indication of when shaft 130 has been suitably tightened to apply the desired pressure to the wear member without placing undue stress on shaft 130 and/or spring 138.
  • indicator 146 cooperates with a marker 152 formed along opening 101, e.g., along rim 111 and/or sidewalls 107, 109.
  • Marker 152 is preferably on rim 111 along one or both sidewalls 107, 109, but could have other constructions.
  • Marker 146 is preferably a ridge or some structure that is more than mere indicia so that it can be used to retighten lock 16 when wear begins to develop as well as at the time of initial tightening.
  • indicator 146 moves rearward - from the position in Fig. 16 - with nut 136 within opening 101.
  • indicator 146 aligns with marker 152, see Fig. 15 , the operator knows that tightening can be stopped.
  • 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.
  • indicator 146 can be omitted and shaft 130 tightened to a predetermined amount of torque.

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

Claims (7)

  1. Verschleißelement (14) für Erdbauausrüstung, umfassend
    einen Arbeitsteilabschnitt (21) und einen Montageteilabschnitt (23), die im Allgemeinen entlang einer Längsachse (28) ausgerichtet sind, wobei der Montageteilabschnitt (23) eine Muffe (20) umfasst, um eine Basis aufzunehmen, die an der Erdbauausrüstung befestigt ist, um das Verschleißelement (14) an der Erdbauausrüstung zu montieren,
    eine vordere Seite (25), die geeignet ist, um während des Vortriebs des Verschleißelements (14) durch den Boden während eines Aushubvorgangs eine nach vorne gerichtete Oberfläche zu sein, und
    eine hintere Seite (27), die geeignet ist, um während des Vortriebs des Verschleißelements (14) durch den Boden eine nach hinten gerichtete Oberfläche zu sein, und
    wobei sich die vorderen und hinteren Seiten (25, 27) axial über die Arbeits- und Montageteilabschnitte (21; 23) axial erstrecken;
    dadurch gekennzeichnet, dass die vordere Seite (25) eine größere Breite als die hintere Seite (27) in Querschnitten, die zur Längsachse (28) rechtwinklig sind, entlang mindestens einem Teil des Montageteilabschnitts (23) aufweist, und die Muffe (20) mit einer im Allgemeinen trapezförmigen Querform gebildet ist, die im Wesentlichen dem äusseren trapezförmigen Querprofil des Verschleißelements (14) entspricht.
  2. Verschleißelement nach Anspruch 1, dadurch gekennzeichnet, dass jede Wand der Muffe (20) über im Wesentlichen ihre gesamte Breite nach innen gebogen ist.
  3. Verschleißelement nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Muffe (20) in dem vorderen Ende (62) eine vordere Auflagefläche (64) aufweist, die im Allgemeinen halbkugelförmig ist.
  4. Verschleißelement nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass eine Öffnung (101) zum Aufnehmen eines Riegels (16), um das Verschleißelement (14) an der Basis (12) zu sichern, bereitgestellt wird.
  5. Eine Verschleißbaugruppe für eine Erdbauausrüstung, umfassend:
    eine Basis (12), die an der Erdbauausrüstung befestigt ist;
    ein Verschleißelement (14) nach einem der vorhergehenden Ansprüche, und
    einen Riegel (16) zum lösbaren Halten des Verschleißelements (14) an der Basis (12).
  6. Die Verschleißbaugruppe nach Anspruch 5, dadurch gekennzeichnet, dass die Basis (12) eine Nase (18) umfasst, die eine im Allgemeinen trapezförmige Konfiguration quer zur Längsachse (28) aufweist, um sich im Wesentlichen der Form der Muffe (20) anzupassen.
  7. Die Verschleißbaugruppe nach Anspruch 5 oder 6, dadurch gekennzeichnet, dass die Basis (12) einen Montageabschnitt (23) umfasst, der zur Anbringung an einem Arm eines Baggerschneidkopfs geeignet ist.
EP14180150.6A 2007-05-10 2008-05-06 Verschleißanordnung für Erdbewegungsmaschinen Active EP2865814B1 (de)

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PL14180150T PL2865814T3 (pl) 2007-05-10 2008-05-06 Zespół podlegający zużyciu dla sprzętu wydobywczego
SI200832038T SI2865814T1 (sl) 2007-05-10 2008-05-06 Sklop za obrabo za opremo za izkopavanje
HRP20190291TT HRP20190291T1 (hr) 2007-05-10 2019-02-13 Potrošni sklop, namijenjen za opremu za iskapanje

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Application Number Priority Date Filing Date Title
US92882107P 2007-05-10 2007-05-10
US92878007P 2007-05-10 2007-05-10
US93048307P 2007-05-15 2007-05-15
EP08747674.3A EP2160498B1 (de) 2007-05-10 2008-05-06 Verschleissanordnung für aushubausrüstung
PCT/US2008/062724 WO2008140993A1 (en) 2007-05-10 2008-05-06 Wear assembly for excavating equipment

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP08747674.3A Division EP2160498B1 (de) 2007-05-10 2008-05-06 Verschleissanordnung für aushubausrüstung
EP08747674.3A Division-Into EP2160498B1 (de) 2007-05-10 2008-05-06 Verschleissanordnung für aushubausrüstung

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EP2865814A2 EP2865814A2 (de) 2015-04-29
EP2865814A3 EP2865814A3 (de) 2015-10-28
EP2865814B1 true EP2865814B1 (de) 2019-01-02

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EP15151786.9A Active EP2889434B1 (de) 2007-05-10 2008-05-06 Verschleißteil und Verschleißanordnung für Erdbewegungsmaschinen
EP14180148.0A Active EP2910692B1 (de) 2007-05-10 2008-05-06 Verschleißanordnung für Erdbewegungsmaschinen
EP08747674.3A Active EP2160498B1 (de) 2007-05-10 2008-05-06 Verschleissanordnung für aushubausrüstung
EP14180150.6A Active EP2865814B1 (de) 2007-05-10 2008-05-06 Verschleißanordnung für Erdbewegungsmaschinen

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Application Number Title Priority Date Filing Date
EP15151786.9A Active EP2889434B1 (de) 2007-05-10 2008-05-06 Verschleißteil und Verschleißanordnung für Erdbewegungsmaschinen
EP14180148.0A Active EP2910692B1 (de) 2007-05-10 2008-05-06 Verschleißanordnung für Erdbewegungsmaschinen
EP08747674.3A Active EP2160498B1 (de) 2007-05-10 2008-05-06 Verschleissanordnung für aushubausrüstung

Country Status (23)

Country Link
EP (4) EP2889434B1 (de)
JP (4) JP5620263B2 (de)
KR (5) KR101651385B1 (de)
CN (3) CN103147480A (de)
AP (1) AP2751A (de)
AU (1) AU2008251647C1 (de)
BR (4) BR122015006394B1 (de)
CA (2) CA2686620C (de)
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CY (4) CY1116392T1 (de)
DK (4) DK2910692T3 (de)
EA (1) EA015217B1 (de)
ES (4) ES2748327T3 (de)
HK (1) HK1138893A1 (de)
HR (4) HRP20150541T1 (de)
LT (3) LT2889434T (de)
MX (1) MX2009012181A (de)
MY (3) MY184361A (de)
NZ (2) NZ581007A (de)
PL (4) PL2865814T3 (de)
PT (4) PT2865814T (de)
SI (4) SI2865814T1 (de)
WO (1) WO2008140993A1 (de)

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CN102535545B (zh) * 2012-01-12 2014-06-25 广西大学 一种可控机构式高承载能力重型装载机
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US10589278B2 (en) * 2013-03-18 2020-03-17 Esco Group Llc Wear cap for an earth working roll
US10508418B2 (en) 2016-05-13 2019-12-17 Hensley Industries, Inc. Stabilizing features in a wear member assembly
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KR20150020673A (ko) 2015-02-26
HRP20190291T1 (hr) 2019-04-05
HRP20190616T1 (hr) 2019-05-31
EP2865814A3 (de) 2015-10-28
EP2910692A3 (de) 2015-11-04
ES2537085T3 (es) 2015-06-02
BR122015006394A2 (pt) 2018-04-03
CN101688385B (zh) 2013-08-14
DK2889434T3 (en) 2019-04-23
JP2015135052A (ja) 2015-07-27
PL2865814T3 (pl) 2019-05-31
NZ597854A (en) 2013-05-31
PL2160498T3 (pl) 2015-07-31
KR20150044974A (ko) 2015-04-27
CN101688385A (zh) 2010-03-31
BRPI0811427B1 (pt) 2018-10-16
KR101618022B1 (ko) 2016-05-03
AP2751A (en) 2013-09-30
AU2008251647A1 (en) 2008-11-20
CN102720244B (zh) 2015-05-06
PT2160498E (pt) 2015-06-08
KR20100023857A (ko) 2010-03-04
CY1116392T1 (el) 2017-02-08
JP2010526953A (ja) 2010-08-05
JP2017166320A (ja) 2017-09-21
BRPI0811427A2 (pt) 2017-05-02
MY184361A (en) 2021-04-01
PL2910692T3 (pl) 2020-01-31
MY171629A (en) 2019-10-22
CA2686620C (en) 2016-02-16
ES2748327T3 (es) 2020-03-16
PT2865814T (pt) 2019-02-25
CN103147480A (zh) 2013-06-12
SI2865814T1 (sl) 2019-03-29
JP5620263B2 (ja) 2014-11-05
BR122015006403A2 (pt) 2018-04-03
KR101595577B1 (ko) 2016-02-18
AU2008251647B2 (en) 2012-12-06
SI2910692T1 (sl) 2019-11-29
PT2910692T (pt) 2019-10-18
BR122015006403B1 (pt) 2018-10-23
BR122015006401B1 (pt) 2018-10-16
JP5813068B2 (ja) 2015-11-17
BR122015006394B1 (pt) 2018-10-16
HRP20191616T1 (hr) 2019-12-13
KR101589007B1 (ko) 2016-01-26
PL2889434T3 (pl) 2019-07-31
NZ581007A (en) 2012-02-24
KR101528984B1 (ko) 2015-06-15
EP2889434B1 (de) 2019-03-06
EP2160498A4 (de) 2011-12-28
WO2008140993A1 (en) 2008-11-20
DK2865814T3 (en) 2019-03-11
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ES2719133T3 (es) 2019-07-08
CY1122085T1 (el) 2020-11-25
ES2711820T3 (es) 2019-05-07
CY1121239T1 (el) 2020-05-29
AU2008251647C1 (en) 2016-12-22
LT2865814T (lt) 2019-02-25
CO6241176A2 (es) 2011-01-20
JP2014001625A (ja) 2014-01-09
EA015217B1 (ru) 2011-06-30
PT2889434T (pt) 2019-05-03
KR101651385B1 (ko) 2016-08-25
HRP20150541T1 (hr) 2015-07-03
EA200901511A1 (ru) 2010-06-30
EP2160498A1 (de) 2010-03-10
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CN102720244A (zh) 2012-10-10
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JP6378803B2 (ja) 2018-08-22
AP2009005034A0 (en) 2009-12-31
CA2880205C (en) 2016-09-27
SI2160498T1 (sl) 2015-07-31
EP2889434A1 (de) 2015-07-01
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