EP2910692B1 - Wear assembly for excavating equipment - Google Patents

Wear assembly for excavating equipment Download PDF

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Publication number
EP2910692B1
EP2910692B1 EP14180148.0A EP14180148A EP2910692B1 EP 2910692 B1 EP2910692 B1 EP 2910692B1 EP 14180148 A EP14180148 A EP 14180148A EP 2910692 B1 EP2910692 B1 EP 2910692B1
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EP
European Patent Office
Prior art keywords
lock
wear member
opening
wear
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
EP14180148.0A
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German (de)
English (en)
French (fr)
Other versions
EP2910692A2 (en
EP2910692A3 (en
Inventor
Charles G. Ollinger VI.
Chris D. Snyder
John S. Kreitzberg
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Esco Group LLC
Original Assignee
Esco Group LLC
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Application filed by Esco Group LLC filed Critical Esco Group LLC
Priority to PL14180148T priority Critical patent/PL2910692T3/pl
Priority to SI200832091T priority patent/SI2910692T1/sl
Publication of EP2910692A2 publication Critical patent/EP2910692A2/en
Publication of EP2910692A3 publication Critical patent/EP2910692A3/en
Application granted granted Critical
Publication of EP2910692B1 publication Critical patent/EP2910692B1/en
Priority to HRP20191616 priority patent/HRP20191616T1/hr
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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 assembly with the wear member to excavating equipment, and in particular to a wear assembly that is well suited for attachment and use on a dredge cutterhead.
  • EP 1 239 088 A1 discloses 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.
  • WO 03/080946 A1 discloses a wear member for excavating equipment comprising a working section and a mounting section generally aligned along a longitudinal axis.
  • the mounting section includes a socket for receiving a base fixed to the excavating equipment.
  • An opening is provided and in communication with the socket. In this opening a wall as a counter support could be inserted to fix a lock in a generally axial direction within the socket to releasably hold the wear member to the excavating equipment.
  • 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 comprising a working section and a mounting section generally aligned along a longitudinal axis.
  • the mounting section includes a socket for receiving a base fixed to the excavating equipment.
  • the mounting section includes an opening in communication with the socket.
  • the opening is provided for receiving the lock in a generally axial direction to releasably hold the wear member to the excavating equipment.
  • the lock is oriented in the same general direction as the longitudinal axis.
  • the opening has a front wall and a rear wall.
  • the rear wall defines a surface to maintain the lock in a compressive state.
  • the rear wall includes a hole through which the lock extends from the opening at an inclination to the longitudinal axis for easy access outside of the opening by an operator for tightening of the lock.
  • the rear wall defines a bearing surface for the lock.
  • the opening is an elongated shape.
  • the opening is in a trailing side of the wear member and the trailing side is adapted to be a rearward surface during advance of wear member through the ground.
  • a marker is provided adjacent the opening to provide a visual indicating to the operator when the lock has been sufficiently tightened.
  • the marker is formed as a ridge.
  • the socket includes rear stabilizing surfaces axially extending substantially parallel to the longitudinal axis and positioned rearward of the hole.
  • a wear assembly for excavating equipment is as set out in claim 8.
  • the elongate lock is generally parallel to the longitudinal axis in a first plane and inclined to the longitudinal axis in a second transverse plane.
  • the lock includes a threaded shaft to bear against the first surface, a nut threaded to the shaft, and a spring about the shaft to be compressed between the rear wall and the nut.
  • the front end of the lock and the rear end of the lock move apart along an axis inclined to the longitudinal axis.
  • the base is free of through holes.
  • the first surface of the base includes a recess that accepts at least a portion of the front end of the lock.
  • the lock in the opening accepts a tool to tighten the lock and the tool rotates at least a portion of the lock to tighten the lock.
  • 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, see 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, 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. 5 , and at least partially through mounting section 23, see Fig. 4 .
  • 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.
  • 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. Moreover, shapes other than trapezoidal can be used that provide side relief.
  • dredge point 14 penetrates the ground to a certain depth with each digging pass - i.e., with each rotation of the cutterhead.
  • the bit alone penetrates the ground.
  • 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.
  • 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.
  • 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 Fig. 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.
  • the tapering of sidewalls 29, 31 continues 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 bail 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 Fig. 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 , see 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.
  • At least one of the body surfaces 68-71 and socket walls 78-81 - and preferably all of them - have mutually bowed configurations, see Fig. 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 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 tight duty operations, benefits can be achieved without stabilizing surfaces 85, 95.
  • Front bearing faces 60, 64 and rear stabilizing surfaces 85, 95 are provided to stabilize the point on the nose and to lessen stress in the components.
  • the generally hemispherical bearing faces 60, 64 at the front ends 58, 62 of the nose 18 and socket 20 are able to stably resist axial and non-axial rearward forces in direct opposition to the loads irrespective of their applied directions.
  • This use of curved, continuous front bearing surfaces reduces rattling of the point on the nose and reduces the stress concentrations that otherwise exist when corners are present.
  • Rear stabilizing surfaces 85, 95 complement the front bearing faces 60, 64 by reducing the rattle at the rear of the point and providing stable resistance to the rear portions of the point, as described in U.S. Patent No. 5,709,043 .
  • stabilizing surfaces 85, 95 extending about the entire perimeter of nose 18 or at least substantially about the entire perimeter, see Fig. 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 Fig. 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 Fig. 1 , 9 and 15-20 .
  • Opening 101 preferably has an axially elongated shape and includes a front wail 103, a rear wall 105, and sidewalls 107, 109.
  • a rim 111 is built up around opening 101 for protection of the lock and for additional strength.
  • Rim 111 is also enlarged along rear wall 105 to extend farther outward of exterior surface 97 and define a hole 113 for passage of lock 16. The hole stabilizes the position of lock 16 and permits easy access to it by the operator.
  • Nose 18 includes a stop 115 that projects outward from upper side 68 of nose 18 to engage lock 16.
  • Stop 115 preferably has a rear face 119 with a concave, curved recess 121 into which a front end 123 of lock 16 is received and retained during use, but other arrangements could be used to cooperate with the lock.
  • opening 101 is long enough and trailing wall 27 sufficiently inclined to provide clearance for stop 115 when wear member 14 is installed onto nose 18. Nevertheless, a relief or other forms of clearance could be provided in socket 20 if needed for the passage of stop 115.
  • the projection of stop 115 is preferably limited by the provision of a depression 118 to accommodate a portion of lock 16.
  • Lock 16 is a linear lock oriented generally axially to hold wear member 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 Figs. 1 and 9 .
  • the lock can be temporarily held in hole 113 for shipping, storage and/or installation by a releasable retainer - e.g., a simple twist tie - fit around shaft 130 outside of opening 101 or it can be installed after the wear member is fit onto the nose.
  • shaft 130 is inserted through hole 113 and its front end 123 set in recess 121 of stop 115.
  • Lock 16 is positioned to tie 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.

Landscapes

  • 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)
  • Clamps And Clips (AREA)
  • Shovels (AREA)
  • Braking Arrangements (AREA)
  • Mechanical Operated Clutches (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Grinding-Machine Dressing And Accessory Apparatuses (AREA)
EP14180148.0A 2007-05-10 2008-05-06 Wear assembly for excavating equipment Active EP2910692B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PL14180148T PL2910692T3 (pl) 2007-05-10 2008-05-06 Zespół podlegający zużyciu do sprzętu wydobywczego
SI200832091T SI2910692T1 (sl) 2007-05-10 2008-05-06 Obrabni sestav za opremo za izkopavanje
HRP20191616 HRP20191616T1 (hr) 2007-05-10 2019-09-06 Potrošni sklop opreme za jaružanje

Applications Claiming Priority (5)

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 (en) 2007-05-10 2008-05-06 Wear assembly for excavating equipment
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 (en) 2007-05-10 2008-05-06 Wear assembly for excavating equipment
EP08747674.3A Division-Into EP2160498B1 (en) 2007-05-10 2008-05-06 Wear assembly for excavating equipment

Publications (3)

Publication Number Publication Date
EP2910692A2 EP2910692A2 (en) 2015-08-26
EP2910692A3 EP2910692A3 (en) 2015-11-04
EP2910692B1 true EP2910692B1 (en) 2019-08-07

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ID=40002579

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EP15151786.9A Active EP2889434B1 (en) 2007-05-10 2008-05-06 Wear member and wear assembly for excavating equipment
EP14180150.6A Active EP2865814B1 (en) 2007-05-10 2008-05-06 Wear assembly for excavating equipment
EP14180148.0A Active EP2910692B1 (en) 2007-05-10 2008-05-06 Wear assembly for excavating equipment
EP08747674.3A Active EP2160498B1 (en) 2007-05-10 2008-05-06 Wear assembly for excavating equipment

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Application Number Title Priority Date Filing Date
EP15151786.9A Active EP2889434B1 (en) 2007-05-10 2008-05-06 Wear member and wear assembly for excavating equipment
EP14180150.6A Active EP2865814B1 (en) 2007-05-10 2008-05-06 Wear assembly for excavating equipment

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP08747674.3A Active EP2160498B1 (en) 2007-05-10 2008-05-06 Wear assembly for excavating equipment

Country Status (23)

Country Link
EP (4) EP2889434B1 (zh)
JP (4) JP5620263B2 (zh)
KR (5) KR101618022B1 (zh)
CN (3) CN102720244B (zh)
AP (1) AP2751A (zh)
AU (1) AU2008251647C1 (zh)
BR (4) BR122015006394B1 (zh)
CA (2) CA2686620C (zh)
CO (1) CO6241176A2 (zh)
CY (4) CY1116392T1 (zh)
DK (4) DK2910692T3 (zh)
EA (1) EA015217B1 (zh)
ES (4) ES2748327T3 (zh)
HK (1) HK1138893A1 (zh)
HR (4) HRP20150541T1 (zh)
LT (3) LT2889434T (zh)
MX (1) MX2009012181A (zh)
MY (3) MY171629A (zh)
NZ (2) NZ581007A (zh)
PL (4) PL2865814T3 (zh)
PT (4) PT2865814T (zh)
SI (4) SI2889434T1 (zh)
WO (1) WO2008140993A1 (zh)

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TWI509131B (zh) * 2009-10-30 2015-11-21 Esco Corp 用於挖掘設備之磨耗總成
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JP5210415B2 (ja) * 2011-05-09 2013-06-12 株式会社小松製作所 建設機械のバケットツース
JP5504205B2 (ja) * 2011-05-09 2014-05-28 株式会社小松製作所 建設機械のバケットツース組立体、およびこれを備えたバケット
JOP20200019A1 (ar) * 2011-07-14 2017-06-16 Esco Group Llc مجموعة بطانه
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US8943717B2 (en) 2011-10-08 2015-02-03 Caterpillar Inc. Implement tooth assembly with tip and adapter
US9057177B2 (en) 2011-10-08 2015-06-16 Caterpillar Inc. Implement tooth assembly with tip and adapter
US8943716B2 (en) 2011-10-10 2015-02-03 Caterpillar Inc. Implement tooth assembly with tip and adapter
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
CN102535537B (zh) * 2012-01-12 2014-05-07 广西大学 一维转动动臂二维转动铲斗空间可控机构式装载机
CN102535547B (zh) * 2012-01-12 2014-06-25 广西大学 一种高承载能力可控机构式装载机
RS58247B1 (sr) * 2012-06-01 2019-03-29 Esco Group Llc Rub kašike za iskopavanje
CN105229243B (zh) * 2013-03-18 2018-11-20 埃斯科集团有限责任公司 用于土方作业辊的磨损帽
US10508418B2 (en) 2016-05-13 2019-12-17 Hensley Industries, Inc. Stabilizing features in a wear member assembly
US10407880B2 (en) * 2016-06-24 2019-09-10 Caterpillar Inc. Wear member retention system for an implement
CN108505580B (zh) * 2018-03-27 2023-12-26 浙江澳德耐磨零部件有限公司 一种挖掘机和疏浚机械用齿头结构
US11634892B2 (en) 2019-11-27 2023-04-25 Hensley Industries, Inc. Excavating tooth assembly with releasable lock pin assembly
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Also Published As

Publication number Publication date
KR101651385B1 (ko) 2016-08-25
EP2865814B1 (en) 2019-01-02
BR122015006394A2 (pt) 2018-04-03
SI2889434T1 (sl) 2019-06-28
AU2008251647C1 (en) 2016-12-22
ES2537085T3 (es) 2015-06-02
CN101688385A (zh) 2010-03-31
CY1121239T1 (el) 2020-05-29
CA2686620A1 (en) 2008-11-20
LT2889434T (lt) 2019-04-25
JP5620263B2 (ja) 2014-11-05
CN103147480A (zh) 2013-06-12
EP2865814A3 (en) 2015-10-28
ES2711820T3 (es) 2019-05-07
SI2910692T1 (sl) 2019-11-29
EP2910692A2 (en) 2015-08-26
PT2910692T (pt) 2019-10-18
EA015217B1 (ru) 2011-06-30
PL2160498T3 (pl) 2015-07-31
DK2910692T3 (da) 2019-10-07
JP2017166320A (ja) 2017-09-21
EP2889434B1 (en) 2019-03-06
JP5813068B2 (ja) 2015-11-17
MY154678A (en) 2015-07-15
HRP20190291T1 (hr) 2019-04-05
EP2889434A1 (en) 2015-07-01
KR20150020673A (ko) 2015-02-26
EP2160498B1 (en) 2015-02-25
BRPI0811427A2 (pt) 2017-05-02
KR101618022B1 (ko) 2016-05-03
CO6241176A2 (es) 2011-01-20
PT2160498E (pt) 2015-06-08
KR20100023857A (ko) 2010-03-04
MY171629A (en) 2019-10-22
KR101595577B1 (ko) 2016-02-18
BR122015006403A2 (pt) 2018-04-03
KR101589007B1 (ko) 2016-01-26
KR20150020674A (ko) 2015-02-26
ES2748327T3 (es) 2020-03-16
PT2889434T (pt) 2019-05-03
WO2008140993A1 (en) 2008-11-20
EP2160498A4 (en) 2011-12-28
PT2865814T (pt) 2019-02-25
JP2014001625A (ja) 2014-01-09
HRP20150541T1 (hr) 2015-07-03
HRP20190616T1 (hr) 2019-05-31
PL2889434T3 (pl) 2019-07-31
EP2910692A3 (en) 2015-11-04
PL2865814T3 (pl) 2019-05-31
BRPI0811427B1 (pt) 2018-10-16
JP2010526953A (ja) 2010-08-05
JP2015135052A (ja) 2015-07-27
AU2008251647A1 (en) 2008-11-20
MX2009012181A (es) 2009-12-09
CY1122000T1 (el) 2020-10-14
AP2009005034A0 (en) 2009-12-31
CA2880205C (en) 2016-09-27
EA200901511A1 (ru) 2010-06-30
BR122015006403B1 (pt) 2018-10-23
AP2751A (en) 2013-09-30
SI2160498T1 (sl) 2015-07-31
CY1122085T1 (el) 2020-11-25
LT2910692T (lt) 2019-10-25
EP2160498A1 (en) 2010-03-10
CY1116392T1 (el) 2017-02-08
CA2880205A1 (en) 2008-11-20
CN102720244B (zh) 2015-05-06
CN102720244A (zh) 2012-10-10
SI2865814T1 (sl) 2019-03-29
BR122015006401B1 (pt) 2018-10-16
KR20150044974A (ko) 2015-04-27
ES2719133T3 (es) 2019-07-08
KR20130079578A (ko) 2013-07-10
DK2889434T3 (en) 2019-04-23
DK2160498T3 (en) 2015-05-11
EP2865814A2 (en) 2015-04-29
AU2008251647B2 (en) 2012-12-06
LT2865814T (lt) 2019-02-25
HRP20191616T1 (hr) 2019-12-13
HK1138893A1 (en) 2010-09-03
JP6378803B2 (ja) 2018-08-22
CN101688385B (zh) 2013-08-14
NZ597854A (en) 2013-05-31
BR122015006394B1 (pt) 2018-10-16
DK2865814T3 (en) 2019-03-11
MY184361A (en) 2021-04-01
PL2910692T3 (pl) 2020-01-31
BR122015006401A2 (pt) 2018-04-03
NZ581007A (en) 2012-02-24
KR101528984B1 (ko) 2015-06-15
CA2686620C (en) 2016-02-16

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