US20220056662A1 - Device to couple members of a heavy-duty machine - Google Patents

Device to couple members of a heavy-duty machine Download PDF

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Publication number
US20220056662A1
US20220056662A1 US17/415,297 US201917415297A US2022056662A1 US 20220056662 A1 US20220056662 A1 US 20220056662A1 US 201917415297 A US201917415297 A US 201917415297A US 2022056662 A1 US2022056662 A1 US 2022056662A1
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United States
Prior art keywords
heavy equipment
equipment frame
frame
hydraulic valve
stick
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Pending
Application number
US17/415,297
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English (en)
Inventor
David Arnold
David Asjes
Paul Pietig
Jerry Vogel
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Gilmore Work Tools Inc D/b/a Ruckus Corp
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Gilmore Work Tools Inc D/b/a Ruckus Corp
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Priority to US17/415,297 priority Critical patent/US20220056662A1/en
Publication of US20220056662A1 publication Critical patent/US20220056662A1/en
Pending legal-status Critical Current

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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
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3654—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat with energy coupler, e.g. coupler for hydraulic or electric lines, to provide energy to drive(s) mounted on the tool
    • 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
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3663—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat hydraulically-operated
    • 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
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/369—Devices to connect parts of a boom or an arm
    • 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
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/30—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom
    • 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
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3622—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat with a hook and a locking element acting on a pin
    • 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
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3631—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat with a hook and a transversal locking element
    • 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
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3636—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat using two or four movable transversal pins
    • 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
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/3604—Devices to connect tools to arms, booms or the like
    • E02F3/3609—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/364—Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat using wedges

Definitions

  • the present invention relates generally to a coupling device and corresponding method of use in at least the construction and heavy equipment industries.
  • An excavator is a construction vehicle used to facilitate work tool operations on various natural and man-made elements in our environment, to include such tasks as earth moving, demolition of structures, material handling, general grading/landscaping, forestry work, lifting and placing of pipes, mining, and river dredging.
  • Excavators come in a wide range of sizes and capacities depending upon the type and general magnitude of the scheduled excavator task.
  • the excavator incorporates three basic parts: a prime mover, a powerful boom arm, and a stick.
  • the prime mover comprises a diesel engine that burns fuel to provide power for excavator operations.
  • the boom arm is used to position the stick to which the work tool is attached.
  • These components connect by means of a series of steel pins through which work forces transfer.
  • a hydraulic system comprising pumps, fluid lines, valves, cylinders, and hydraulic fluid mass provides the system forces necessary to maneuver and operate the attached work tool per operator instructions.
  • Swapping work tools for an excavator involves removal and replacing of steel pins and the coupling/uncoupling of hydraulic lines, both of which are time consuming and potentially dangerous.
  • excavators quickly became work tool dedicated, leading to incorporation of multiple excavators, each serving a particular work tool for most construction jobs.
  • the requirement for increased excavator system numbers creates a downside impact on individual excavator efficiency and associated increase in job costs.
  • Such procedures have necessarily become an integral part of construction equipment distribution and scheduling paradigms for most current construction jobs.
  • the advent of the excavator bucket coupler with the ability to quickly interchange various sized buckets provided greater productivity for the excavator.
  • the coupler also known as a third member coupler resides at the working end of the excavator stick and allows rapid bucket interchange without having to physically remove and reinsert massive pins, thus quickly matching bucket with the excavator job at hand.
  • the concept eventually morphed into to a quick coupler system that extends coupling processes to many other work tools, some of which require hydraulic line interconnections.
  • the third member location of the coupler mass does limit the size of viable work tools for construction jobs. Increasing coupler size to accommodate larger work tools leads to excessive loads on the excavator system, thus limiting applications of the bucket coupler concept to the smaller excavator classes.
  • This type boom/coupler/stick arrangement generally provides a less strenuous work environment for the excavator by virtue of an improved coupler mass location.
  • the second member coupler system comprises two primary structures, the boom frame coupling member and the stick frame coupling member.
  • the boom-side frame is attached to the excavator boom and stick cylinder via steel pins that transfer excavator loads between boom and stick.
  • the stick-side frame is pinned to the excavator stick in a similar fashion.
  • the two frames join at a common plane region, termed the mating plane, by means of appropriate hydraulic/mechanical components controlled by the excavator operator, thus providing attachment of the excavator stick to the boom upon command.
  • the second member coupler configuration provides an opening in the excavator marketplace for the enhanced productivity of second member work tool operations.
  • a larger size excavator is employed with multiple interchangeable second member work tools, thus eliminating the need for dedicated excavator-work tool combinations that otherwise decrease productivity of the overall construction process.
  • the case for morphing to these more productive configurations is made by Jack Roberts, Equipment Manager, Komatsu, in his article entitled, Productivity Guide: Excavators 45 to 50 Metric Tons. Roberts contends that the traditional construction operations paradigm will be shifting to a more productive paradigm in which the concept of dedicated excavator systems will be replaced with second member coupler systems that incorporate multiple second member work tool sets utilized by a single, larger excavator. This is precisely the market the inventors of the technology disclosed herein intend to service.
  • Couplers commonly known in the art have yet to solve these issues.
  • the coupler systems disclosed in U.S. Pat. Nos. 4,938,651, 5,108,252, 5,360,313, 5,484,250, 6,301,811, and 6,428,265 represent permissible system with respect to expected second member coupler performance standards however are in no way optimal configuration designs.
  • Much of the non-optimal character stems from the fact that several subcomponents are inherently inferior in the context of their contribution to overall system performance. These subcomponents were badly synthesized and/or improperly sized to perform optimal function for coupler operation.
  • a coupler system to facilitate carrying or operating a working tool comprises a first heavy equipment frame comprising simulated pins located at corners of the first heavy equipment frame, a second heavy equipment frame comprising rotational devices at corners of the second heavy equipment frame to mate with the simulated pins, and a latching or locking mechanism to secure the first heavy equipment frame to the second heavy equipment frame.
  • the rotational devices rotate between a grabber state and a picker state and have approximately 1800 of freedom in rotation.
  • the latching or locking mechanism comprises translatable pins in a carrier hollow shaft or pin sleeve associated with the second heavy equipment frame, the pins having one degree of freedom to slide between a disconnect position and a connect position.
  • translation of the pins is caused by a hydraulic ram.
  • the latching or locking mechanism is located at a top, or picker end of the second heavy equipment frame and an additional latching or locking mechanism is located at a bottom, or grabber end opposite the picker end of the second heavy equipment frame.
  • the coupler system further comprises a rotary cam receiver and a cam lifter mechanism, the cam lifter mechanism capable of rotating (e.g. 90°) to engage the rotary cam receiver and thereby pull the first heavy equipment frame and the second heavy equipment frame together.
  • the rotary cam receiver and the cam lifter mechanism located at the approximate longitudinal middle of the frames.
  • the rotary cam receiver and the cam lifter mechanism comprise steel.
  • the heavy equipment frame consists of one or more components that singularly or collectively provide adequate load paths for the equipment working loads.
  • the heavy equipment frame consists of one or more components that singularly or collectively provide the framework upon which other subsystems are mounted.
  • the coupler system further comprises a mechanical mating feature such as teeth on the first heavy equipment frame to interlock with a corresponding reciprocal mechanical mating feature such as teeth on the second heavy equipment frame.
  • the coupler system further comprises a power pass-through system comprising hydraulic fluid passing between the first heavy equipment frame and the second heavy equipment frame, an actuatable valve set on the boom frame and a fixed valve set on the stick frame capable of engaging and coupling with the valves actuated on the boom frame such that hydraulic power circuits are completed.
  • a power pass-through system comprising hydraulic fluid passing between the first heavy equipment frame and the second heavy equipment frame, an actuatable valve set on the boom frame and a fixed valve set on the stick frame capable of engaging and coupling with the valves actuated on the boom frame such that hydraulic power circuits are completed.
  • the coupler system further comprises a valve actuation mechanism on the boom frame that advances a valve set to a fixed set on the stick frame for the purpose of coupling, holds the coupled valves together for the purpose of tool operation in accordance with the nominal heavy machinery design, and retracts the valve set for the purpose of disconnecting the valves.
  • the power-pass through system further comprises a hydraulic valve containment system comprising a first hydraulic valve isolation box containing the female hydraulic valve, a first hydraulic valve mounting plate attached to the heavy equipment frame associated with the female hydraulic valve and the first hydraulic valve isolation box, the first hydraulic valve mounting plate including a first box sliding plate within, a second hydraulic valve isolation box containing the male hydraulic valve, and a second hydraulic valve mounting plate attached to heavy equipment frame opposite the heavy equipment frame associated with the female hydraulic valve and the second hydraulic valve isolation box, the second hydraulic valve mounting plate including a second box sliding plate within.
  • the first and second box sliding plates are actuatable between an open and a closed position and include apertures allowing the actuatable male hydraulic valve to pass through when the first and second box sliding plates are in the open position.
  • a heavy-duty machine comprises the coupler system according to any of the aspects described above, a boom including the first heavy equipment frame, a stick or tool including the second heavy equipment frame, a cab for operating the boom and the stick, and wheels or a track drive for supporting the cab.
  • the heavy-duty machine further comprises a boom cylinder for moving the boom vertically.
  • the heavy-duty machine further comprises a working tool cylinder for moving the working tool in relation to the stick.
  • the heavy-duty machine further comprises a stick cylinder for moving the stick or tool in relation to the boom.
  • a method of placing two components of a heavy-duty machine under pre-stress loads while negating cyclical workloads comprises pre-loading static stress onto a pulling mechanism which secures a first heavy equipment frame to a second heavy equipment frame to prevent failure, and dispersing dynamic stresses onto a compression mechanism to mitigate fatigue.
  • the method further comprises first rotating the first heavy equipment frame about a master pin location to mate with the second heavy equipment frame at a picker end and coupling the first heavy equipment frame to the second heavy equipment frame with a latching or locking mechanism at the picker end.
  • the method further comprises further rotating the first heavy equipment frame about the master pin location to mate with the second heavy equipment frame at a grabber end opposite the picker end and coupling the first heavy equipment frame to the second heavy equipment frame with an additional latching or locking mechanism at the grabber end.
  • the method further comprises passing hydraulic fluid between the first heavy equipment frame and the second heavy equipment frame and maintaining cleanliness in a hydraulic valve environment while coupling the second heavy equipment frame to the first heavy equipment frame.
  • the pulling mechanism comprises a rotary cam receiver and a cam lifter mechanism
  • the cam lifter mechanism capable of rotating (e.g. 90°) to engage the rotary cam receiver and thereby pull the first heavy equipment frame and the second heavy equipment frame together.
  • the compression mechanism comprises a mechanical mating system such as teeth.
  • FIG. 1 shows a side elevational view of a heavy-duty machine having a boom that is connected by the quick-disconnect coupling of the present invention to a stick having a tool, according to some aspects of the present disclosure.
  • FIG. 2 shows an enlarged side elevational view of the stick lying horizontally on the ground and being supported by a stand beneath a fragmentary side elevational view of the boom illustrating the manner in which the coupling members are brought together when the grabber of the boom frame coupling member is used, according to some aspects of the present disclosure.
  • FIG. 3 shows a front, top perspective view of a boom frame including a latching or locking mechanism and a mounting mechanism.
  • FIG. 4 shows a perspective view of a boom frame and a stick frame coupled at the picker end, according to some aspects of the present disclosure.
  • FIG. 5 shows a detailed view of the rotational devices of boom frame and locking pins located within a carrier hollow shaft or pin sleeve, according to some aspects of the present disclosure.
  • FIG. 6 shows a detailed view of the locking pins of the boom frame fully extended to couple the boom frame to the stick frame at the picker end, according to some aspects of the present disclosure.
  • FIG. 7 shows a perspective view of the boom frame rotating about a master pin location to eventually mate with the stick frame at the grabber end, the rotational devices being in a picker configuration, according to some aspects of the present disclosure.
  • FIG. 8 shows a perspective view of the boom frame coupled to the stick frame at both the picker end and the grabber end, the locking pins being fully extended at the picker end and located inside the carrier hollow shaft the grabber end, according to some aspects of the present disclosure.
  • FIG. 9 shows a perspective view of the boom frame coupled to the stick frame at both the picker end and the grabber end, according to some aspects of the present disclosure.
  • FIG. 10 shows a detailed view of a boom frame rotary cam receiver, according to some aspects of the present disclosure.
  • FIG. 11 shows a perspective view of the boom frame coupled to the stick frame at both the picker end and the grabber end, the coupler system also including a boom frame cam lifter mechanism midway through its rotational path to engage the rotary cam receiver and thereby pull the boom frame and the stick frame together, according to some aspects of the present disclosure.
  • FIG. 12 shows a detailed view of a boom frame cam lifter mechanism midway through its rotational path to engage the rotary cam receiver and thereby pull the boom frame and the stick frame together, according to some aspects of the present disclosure.
  • FIG. 13 shows a perspective view of a coupler system with interlocking teeth, according to some aspects of the present disclosure.
  • FIG. 14 illustrates stresses applied to the interlocking teeth while a central cam lifter mechanism engages the rotary cam receiver without an oscillating load, according to some aspects of the present disclosure.
  • FIG. 15 illustrates stresses applied to the interlocking teeth while two cam lifter mechanisms at each end of the frames engage the rotary cam receivers without an oscillating load, according to some aspects of the present disclosure.
  • FIG. 16 illustrates stresses applied to the interlocking teeth while a central cam lifter mechanism engages the rotary cam receiver with an oscillating load, according to some aspects of the present disclosure.
  • FIG. 17 illustrates stresses applied to the interlocking teeth while two cam lifter mechanisms at each end of the frames engage the rotary cam receivers with an oscillating load, according to some aspects of the present disclosure.
  • FIG. 18 depicts various components of a power-pass through system, according to some aspects of the present disclosure.
  • FIG. 19 shows a perspective view a hydraulic valve containment system or subsystem wherein the box sliding plate is in an open position, according to some aspects of the present disclosure.
  • FIG. 20 shows a perspective view a hydraulic valve containment system or subsystem wherein the box sliding plate is in a closed position, according to some aspects of the present disclosure.
  • FIG. 21 shows a perspective view of a power-pass through system wherein male hydraulic valves associated with the boom frame are actuated to pass through apertures in the box sliding plates while the box sliding plates are in an open position to mate with female hydraulic valves associated with the stick frame, according to some aspects of the present disclosure.
  • FIG. 22 depicts a rear perspective view of a boom frame such that details of the apparatus to connect the hydraulic fittings remotely on a heavy-duty machine can be seen, according to aspects of the present disclosure.
  • FIG. 23 depicts a front perspective view of a boom frame such that details of the apparatus to connect the hydraulic fittings remotely on a heavy-duty machine can be seen, according to aspects of the present disclosure.
  • FIG. 24 depicts a representative quick-connector and guide pins as installed on a boom assembly, but with the model of the moveable plate removed for clarity, according to aspects of the present disclosure.
  • FIG. 25 shows reciprocal installation on the stick frame, according to aspects of the present disclosure.
  • FIG. 26 shows a plan view along cross-section A-A of FIG. 22 and engagement of the guide pins during extension and retraction, according to aspects of the present disclosure.
  • invention or “present invention” as used herein are not intended to refer to any single embodiment of the particular invention but encompass all possible embodiments as described in the specification and the claims.
  • the term “configured” describes an apparatus, system, or other structure that is constructed to perform or capable of performing a particular task or to adopt a particular configuration.
  • the term “configured” can be used interchangeably with other similar phrases such as constructed, arranged, adapted, manufactured, and the like.
  • Terms characterizing a sequential order e.g., first, second, etc.
  • a position e.g., top, bottom, lateral, medial, forward, aft, etc.
  • an orientation e.g., width, length, depth, thickness, vertical, horizontal, etc.
  • An excavator second member coupler is a complex system designed to enable expeditious interchange of machine sticks without having to resort to the traditional manual manipulation of interconnection pins and connection/disconnection of hydraulic lines.
  • the anticipated stick interchange would be accomplished quickly, safely, and solely by the operator while in the machine cab and without additional work force requirements.
  • the coupler system comprises two primary structures, the boom-side frame and the stick-side frame as depicted in the figure below for the coupler.
  • the boom-side frame is attached to the excavator boom and stick cylinder via steel pins that transfer excavator loads between boom and stick.
  • the stick-side frame is pinned to the excavator stick or work tool adapter in a similar fashion.
  • the two frames join at a common plane region, termed the mating plane, by means of appropriate hydraulic/mechanical components controlled by the excavator operator, thus providing attachment of the excavator stick to the boom upon command.
  • Coupler subsystem designs should exhibit properly sized features that preclude excessive weight and complexity that would otherwise compromise excavator efficiency.
  • the coupler control system should be robust to include reliable feedback sensors, generous operator instruction sets with corresponding visualizations, adequate operational redundancies, and overall high-quality system components.
  • a good coupler system handles system loads efficiently with respect to coupler weight, cost and ease of operation, and has a predictable safe life expectancy.
  • Rational analysis and design processes used to synthesize systems with these characteristics inevitably originate from erudite application of fundamental laws of physics that govern the force in both the coupling/operational processes and the cyclic workloads encountered in normal coupled operation.
  • design personnel must fully understand details of force systems subjected to the coupler to synthesize an optimal coupler system, its various modes of operation, and associated system subcomponents.
  • a primary function of coupler frames is to always enable transmission of forces between the excavator boom and stick while simultaneously maintaining boom/stick connectivity. Therefore, a coupling mechanism that guarantees structural unification of frames under all potential loading conditions while avoiding material deformation or failure becomes a primary focal point in coupler design.
  • the fact that the coupling forces are temporal in nature generates a dual consideration with respect to failure modes: maximum static load failures and fatigue-based failures. Design solutions for each of these structural behaviors tend to be contradictory with respect to subcomponent design constraints.
  • the deformations cause resistive internal forces much like a common spring due to material intermolecular forces that propagate with material deformation state per Hooke's law.
  • the magnitude and distribution characteristics of the internal forces become strong functions of the deformation generator's functionality, output power, and location/distribution throughout the coupler mass.
  • the deformation generators i.e. the lock and reaction components
  • their interaction with the coupler frames represent a major focus of optimal coupler design efforts.
  • the deformation generators as defined in the above discussions fall into two categories: locking force generators and reaction force generators.
  • the locking force generator provides the clamping forces pulling the coupler frames together and the reaction force generator provides the balancing internal forces for overall coupler equilibrium.
  • the criteria used to construct constraint systems necessary for formulating design processes that ultimately define these mechanical devices are largely dependent upon the nature of the forces that they must generate.
  • the locking force required for maintaining coupler-frame connectivity is generally singular in value and more than the greatest frame-separating load expected during coupler operations. The designer specifies this load based on expected operating environment for the coupler and consummates a deformation generator design to accomplish the task. The maximum locking force systematically occurs every time the coupler executes a coupling action.
  • the reaction forces that the coupler frames generate will have a much different character than the locking forces in that they are generally temporal.
  • External working forces applied to the locked coupler frames are normally periodic in nature and can range as high as the maximum locking force that connects the frames. They can originate on either side of the coupler and must pass through the coupler mass to the opposing side in the form of strain-field-generated stress waves that facilitate the external force transfer.
  • the cyclic nature of the internal stress fields gives rise to a fatigue failure mode potential wherein any internal structural cracks will tend to grow unbounded in intensity, eventually terminating in structural failure.
  • the locking force must react without failure the largest coupler-separation load provided by the excavator system. It remains at a constant level to preclude high-stress reversal situations that quickly lead to fatigue failures. These requirements in conjunction with a minimum coupler weight imply that the locking force generator must deform a relatively small region of the adjoining coupler frames with large strain fields that give rise to stresses commensurate with locking force requirements.
  • the reacting force generators must spawn dynamic strain fields that permit cyclically applied forces at one frame of the coupler to pass through to the opposing frame in the form of stress waves that cycle through interior coupler regions.
  • the magnitude of these stress waves must be commensurate with the requirement that the ensuing stress reversals reside within the fatigue endurance limit of the material used in coupler construction.
  • the following figures provide a graphic representation of the locking and reacting forces associated with excavator coupler dynamics.
  • the locking force generators comprising the tension elements serve to lock the two frames together.
  • the tension elements generate a high stress state that persists throughout the cyclic loading subjected to the coupler thus mitigating fatigue failure tendencies caused by high stress reversals.
  • the reaction force generators can provide regions of stress wave passage that are distant from the locking force generators and permit stress wave characteristics that lie within the endurance range for the coupler material.
  • the improved adaptive coupler 10 is a second element quick-disconnect coupling 15 specifically designed for large excavators, making it possible to change any stick-mounted or second element tool in three to five minutes without leaving the cab or manually connecting lines.
  • the versatility of the excavator means the heavy-duty machine 16 may attach to any powered tool, up to the full weight limit of the excavator.
  • the excavator then becomes a mobile power source for a wide variety of tasks and stays online during tool maintenance. Changing tools ensures an operator can continue work on the same area of a construction worksite and allows the operator to adapt to specific site conditions with different tools.
  • a common stick interface ensures every tool will work on any excavator with a coupler of the present disclosure.
  • Increased productivity and return on investment of the heavy-duty machine 16 is achieved through the use of one larger, more powerful machine which replaces two or more smaller machines having one tool each, thereby reducing the number of machines sitting idle on worksites or being transported.
  • the heavy-duty machine 16 may employ the most efficient tool for the task and rapidly change when necessary, thereby always providing the optimum tool option available.
  • the life of the excavator may be extended and maintenance may be reduced with optimized excavator and tool combinations. More specifically, there is no extra wear on the working tool cylinder due to the weight of the working tool coupler, and no decrease in breakout force on the working tool curl. Finally, 10-15% of fuel costs may be conserved compared to implementation of the existing art with the same work being performed.
  • the present disclosure also presents more agile embodiments than are known in the art. Such embodiments are also able to reduce total shipping weight for an equivalent job site functionality, allowing for the use of smaller trailers, and enabling a smaller footprint onsite.
  • an improved adaptive coupler 10 is illustrated on a heavy-duty machine 16 having a boom 17 and a stick 18 with a hydraulically operated working tool thereon.
  • the stick 18 and boom 17 are connected by a quick-disconnect coupling 15 that is constructed for use on any heavy-duty machine having a boom for quick interchangeability of sticks having various tools or working members.
  • the heavy-duty machine includes a cab or operator station 20 on a carriage or base 21 which in turn is rotatably supported on wheels or a track drive 22 .
  • While the present disclosure shows a heavy-duty machine having a boom and a stick, it is appreciated other heavy-duty machines may be used, such as farm equipment, an excavator, a back-hoe, or any other heavy-duty machinery capable of interchanging tools.
  • the boom 17 is pivotally connected to the heavy-duty machine 16 at a first end of the boom 23 and is articulated in a vertical direction by a double-acting hydraulic cylinder 24 pivotally connected at an end 25 of the base or carriage and a central connection 26 of the boom in a known manner.
  • a double-acting hydraulic cylinder 24 pivotally connected at an end 25 of the base or carriage and a central connection 26 of the boom in a known manner.
  • operation of the hydraulic cylinder 24 swings the boom 17 vertically up or down.
  • the boom 17 also includes on its upper side a stick cylinder 30 pivotally connected to an upper connection 31 of the boom and pivotally connected to an upper end 32 of the quick-disconnect coupling.
  • the quick-disconnect coupling 15 is pivotally connected to the upper end 32 of the quick-disconnect coupling and a second end 33 of the boom.
  • a pin-connection helps secure the quick-disconnect coupling 15 to the stick 18 at a lower end 34 of the quick-disconnect coupling.
  • An eccentric bushing (not shown) having a pin hole may be received in a pin boss and adjustably rotated within a circular bore to compensate for minor spacing and/or misalignment differences that may occur in different sticks 18 between the pin hole boss and a pin at an outer end 35 of the stick.
  • the stick 18 includes a working tool 36 (exemplified as a bucket) and a double-acting working tool cylinder 37 .
  • the working tool 36 is pivotally connected to a second end 38 of the stick and includes linkage 39 which is pivotally connected to a lower end 40 of the cylinder.
  • An upper end 41 of the cylinder is pivotally connected to the stick 18 . It will be understood that the coupling may be coupled while the stick is on the ground and underneath the boom, or while the stick is in the extended position on the ground.
  • a stand 42 may be mounted on the coupling end of the stick and on the working tool operating cylinder side to provide support for the coupling end when the stick is placed on the ground as shown in FIG. 2 .
  • a protector hood may be provided on the boom frame coupling member to protect the hydraulic lines against damage during handling.
  • other types of couplings such as suction, pneumatic or electric, can be used with the present disclosure.
  • the stick is shown as including a bucket as the working tool, other sticks having other working tools may be provided with stick frame coupling members to be interchangeable so that the heavy-duty machine may serve to easily accomplish different working functions.
  • a work tool independent of a stick but equipped with an appropriate mounting adapter common to the tool configuration can be used with the present disclosure.
  • the quick-disconnect coupling 15 preferably includes a boom frame coupling member 45 pivotally connected to stick cylinder 30 via the second end 33 of the boom and the upper end 32 of the quick-disconnect coupling. Additionally, the quick-disconnect coupling 15 can include a stick frame coupling member 46 mountable on the stick 18 .
  • the parallel spaced-apart side frame plates 49 and 50 of the boom frame coupling member 45 are connected together near their opposite ends by end walls 51 and 52 , as seen in FIG. 3 .
  • the side frame plates include a mating face 55 and a backside 56 .
  • a series of teeth 58 are provided along the edges of plates 49 and 50 that can mate with teeth on the stick frame coupling member. These teeth are preferably in the form of gear teeth and take the appearance of a rack gear at each side of the coupling member.
  • the mating face 55 is adapted to mate with the mating face 57 of the stick frame coupling member 46 .
  • the boom frame coupling member includes at the upper or head end (herein referred to as the picker end 60 ) a picker and at the lower or toe end (herein referred to as the grabber end 61 ) a grabber, each of which may guidably assist in bringing together the coupling members 45 , 46 during the coupling operation depending on which end is desired to be used during the coupling and which end of the stick frame coupling member includes a pin.
  • the grabber is mounted at the grabber end 61 of the boom frame coupling member to assist in guidably interconnecting the boom and stick frame coupling members 45 , 46 when the pin on the stick frame coupling member 46 is located at the grabber end 61 of the stick frame coupling member.
  • the grabber end 61 may be in the form of a hook that receives the pin of the stick frame coupling member and positions the respective ends of the coupling members so as the members come together in an angular relation, the intermeshing elements of each member may matingly engage.
  • the overall operation of the improved coupler 10 in connecting the excavator boom 17 and stick 18 occurs in the form of three modes, as follows: 1. stick pickup and carry mode; 2. boom-stick lockup mode; and 3. system hydraulic and signal hookups.
  • the coupler subsystem identifications and descriptions occur within the context of the system operational modes they serve.
  • FIG. 4 starts by showing basic coupler frame components, including the boom frame 45 and the stick frame 46 coupled together at the picker end 60 .
  • the boom frame 45 is configured to first rotate about a master pin location to the stick frame 46 at the picker end 60 and then to rotate further about the master pin location to eventually mate with the stick frame 46 at the grabber end 61 .
  • FIG. 7 best shows the boom frame 45 during rotation
  • FIG. 8 best shows the boom frame 45 coupled to and properly aligned with the stick frame 46 at both the picker end 60 and the grabber end 61 .
  • FIG. 5 further illustrates how the connection is made, including simulated pins 72 at each of the four corners of the stick frame 46 and rotational devices 74 (also called pin receptors) at each of the four corners of the boom frame 45 .
  • the simulated pins 72 are typically cylindrical members and extend from a distal location of the stick frame 46 towards the central portion of the stick frame 46 .
  • the rotational devices 74 are half-moon shaped members that extend outwards from a central location of the boom frame 45 and are meant to engage and intersect with the each of the rotational devices 74 .
  • the shapes of these members is not meant to be limiting and the present disclosure contemplates both the simulated pins 72 and the rotational devices 74 may take any known three-dimensional shape, and particularly three-dimensional shapes known to facilitate mating engagement to one another, movement between in a locked position and an unlocked position, and the simplification of the coupler design.
  • the simulated pins 72 and rotational devices 74 may be solid, partially hollow, or completely hollow so long as they are a sufficient structural strength to carry out their intended functions.
  • the rotational devices 74 can rotate between a latched and unlatched states (between grabber and picker states) and have approximately 180° of freedom in rotation. While the rotational devices 74 are in a picker state they allow a connection to be made between the boom frame 45 and the stick frame 46 at the picker end 60 . While the rotational devices 74 are in a grabber state they allow a connection to be made between the boom frame 45 and the stick frame 46 at the grabber end 61 .
  • a pair of translatable pins 76 reside within a carrier hollow shaft 78 (also known as a pin sleeve) associated with or attached to the boom frame 45 .
  • Each translatable pin 76 has one degree of freedom that allows the pin to slide between a disconnect (unlocked) position within the carrier hollow shaft 78 of the boom frame 45 to a connect (locked) position within the simulated pins 74 in the stick frame 46 .
  • Movement of the locking pins 76 is typically caused by a hydraulic ram system, including a ram or a piston (not shown), however the present disclosure contemplates that movement of the locking pins 76 may be caused by any known actuation means.
  • FIG. 6 shows the locking pins 76 of the boom frame fully extended (locked) to couple the boom frame 45 to the stick frame 46 at the picker end 60
  • FIG. 8 shows the locking pins 76 being fully extended (locked) at the picker end 60 and the locking pins 76 being not extended (unlocked, located inside the carrier hollow shaft 78 ) at the grabber end 61 .
  • the coupler system 10 is said to be in the stick pickup and carry mode, sometimes referred to as the “tool carry mode.” This allows the working tool to be carried by the excavator without any danger of the working tool falling off.
  • the next fundamental mode of operation is the boom-stick lockup mode, which is sometimes referred to as the tool operational mode. This is the mode of operation where the working tool can be used without any danger of the working tool being separated from the excavator.
  • a rotary cam receiver 80 (as shown in FIGS. 9 and 10 ) is provided on the boom frame 45 to enable this mode of operation.
  • the rotary cam receiver 80 is generally comprised of a steel housing 82 and a shaft 84 within a cavity of the steel housing 82 and acts a receiver for a cam lifter mechanism 90 (as shown in FIGS. 11 and 12 ) of the stick frame 46 .
  • the cam lifter mechanism 90 is a rotary cam which includes a cam lifter mechanism housing 92 and a cam lifter mechanism shaft 94 much like the rotary cam receiver 80 .
  • the cam lifter mechanism 90 also includes a cam lifter mechanism hook 96 which is able to rotate at least 90° and attach to or otherwise engage the rotary cam receiver shaft 84 , thereby pulling the boom frame 45 and the stick frame 46 together very tightly.
  • the forces that are generated by the cam lifter mechanism 90 and rotary cam receiver 80 must be reacted by some other portions of the coupler system 10 to maintain equilibrium. In the coupler system that is shown in the figures, these forces are particularly strong and cause a lot of shear within the locking pins 76 of the coupler system 10 . This amount of shear can be undesirable and if not appropriately dealt with, the resulting friction can prevent the locking pins 76 from being able to move into and out of the hollow carrier shaft 78 . Additionally, these shear forces can cause a severe fatigue problem, causing failure of the locking pins 76 .
  • FIG. 13 uses teeth 58 attached to the boom frame 45 and the stick frame 46 .
  • the teeth 58 will interlock when the boom frame 45 and the stick frame 46 are coupled to one another. This provides a path for force reaction that is removed from the locking pins 76 and puts it through the teeth 58 .
  • FIGS. 14-17 illustrate this concept by showing the stresses applied to the interlocking teeth (also referred to as a stress field) while a central cam lifter mechanism engages the rotary cam receiver 80 with or without an oscillating load.
  • FIGS. 14-15 show the stresses associated with fixing upper force application points on the upper frame
  • FIGS. 16-17 show the stresses associated while additionally applying an oscillating load at lower force application points on the lower frame.
  • the rotary cam receiver 80 (in blue) acts as a tension device or pulling mechanism in a constant state of high tension, holding the frames 45 , 46 together.
  • the locking force that is generated through the pulling mechanism is counteracted by the teeth 58 (in red), which act as a pushing mechanism.
  • the teeth 58 can run the full length between the pulling mechanisms (as is shown in FIGS. 15 and 17 ) or only a partial distance along the frames 45 , 46 (as is shown in FIGS. 14 and 16 ).
  • the central teeth 58 in FIGS. 15 and 17 have very little stress and thus it may be preferred that the coupler system 10 have no central teeth to save costs associated with manufacturing extra teeth and to reduce the overall weight of the coupler system 10 .
  • one inventive aspect of the present disclosure is the ability to apply a pre-loading static stress onto a pulling mechanism which secures a first heavy equipment frame to a second heavy equipment frame to prevent failure and to effectively disperse dynamic stresses onto a compression mechanism to mitigate fatigue.
  • FIGS. 18-26 show several components of the power pass through system 140 , including fixed coupler plates 142 , quick connect fittings 144 , guide bushings 145 , hydraulic pass through valves 146 (including male and female valves), guide pins 148 , hydraulic valve containment system 150 , hydraulic valve isolation box 152 , box sliding plate 154 , apertures 156 , hydraulic valve mounting plate 158 , hydraulic cylinder 160 , ball and socket connection 162 , hydraulic cylinder mounting frame/cylinder bracket 164 .
  • the improved coupler system 10 disclosed herein is designed to address hydraulic valve cleanliness during the coupling process and to have reliable single-axis physical coupling of the male and female hydraulic valves without significant fluid loss. Concepts and processes associated with cleanliness relate most closely to the systems shown in FIGS. 18-21 , while the physical coupling of the male and female hydraulic valves relates most closely to the system shown in FIGS. 22-26 .
  • the hydraulic valve containment systems 150 which contain male and female hydraulic coupling pairs 146 are secured on flat plates attached to boom frame 45 and the stick frame 46 .
  • the coupling valves 144 are placed in hydraulic valve isolation boxes 152 that shields them from a corrupted operating environment that could otherwise cause valve malfunctions.
  • the hydraulic valve containment system 150 also comprises a valve mounting plate 158 attached to boom frame 45 or the stick frame 46 .
  • the mounting plate 158 including a box sliding plate 154 with apertures 156 that can switch the isolation box 152 between a “box closed” position and a “box open” position, depending on operational needs.
  • the apertures 156 allow the actuatable male hydraulic valve 144 to pass through when the box sliding plates 154 are in the open position.
  • FIGS. 22-26 an apparatus to connect hydraulic fittings remotely on heavy equipment is shown.
  • the main design effects the mechanical connection of two working elements of a piece of heavy machinery, for example between the boom and stick of an excavator.
  • This apparatus comprises a hydraulic actuation sub-assembly that provides safe and reliable connection of the power sources required by the tool, to include hydraulic circuits, electrical supply (high and low voltage), pneumatic supply, and lubrication supply.
  • FIGS. 22-23 show the part of the apparatus that is installed on the boom frame 45 .
  • the installation on the stick frame 46 is not depicted, for clarity.
  • the boom frame 45 installation includes (i) a plate 142 bolted to the boom frame at a specific location, with a section of material removed from the interior portion; (ii) a smaller, moveable plate 158 designed to fit inside the fixed plate; (iii) guide pins 148 installed in the moveable plate 158 ; (iv) quick-connect fittings 144 installed in the moveable plate 158 (nominally hydraulic, but suitable for other media as mentioned above); (v) a hydraulic cylinder 160 mounted on a frame “behind” the plates, and attached to the moveable plate 158 by a ball-and-socket connection 162 .
  • FIGS. 22-23 show the fully retracted position.
  • the guide pins 148 accomplish the proper alignment between the quick-connect fittings 144 as they engage and disengage, to provide safe and secure connections under working conditions, and to prevent damage during connection and disconnection.
  • the fixed plate 142 and cylinder bracket 164 provide the base for the hydraulic cylinder 160 , allowing the cylinder 160 to provide and maintain a positive connection force through all work conditions, and to provide adequate retraction force. Other motive devices can be used for this function.
  • FIG. 24 shows representative quick-connector 144 and guide pins 148 as installed on the boom assembly, but with the model of the moveable plate removed for clarity.
  • FIG. 25 shows the reciprocal installation on the stick frame, to include (i) the fixed (attached) plate 142 ; (ii) the quick-connect fittings 144 as installed in the fixed plate 142 ; (iii) the guide bushings 145 as installed in the fixed plate.
  • extension/connection and retraction/disconnection operations are design to occur only when the boom frame 45 and stick frame 46 are securely locked together, so that in the operation described above, the position and orientation of the fixed boom plate 142 and the fixed stick plate 142 are not allowed to change.
  • This fixed relationship allows the apparatus to achieve precise connection of the quick-connect fittings 144 .
  • the guide pins 148 engage with bushings 145 in the cylinder mounting frame 164 to ensure movement on the correct path for the operation.
  • the guide pins 148 disengage from the bushings 145 in the cylinder mount and engage the bushings 145 in the fixed stick plate 142 at approximately the same point, providing uninterrupted alignment, as depicted in FIG. 26 below.
  • the features of the installation holes machined into the plates 142 for the fittings 144 are designed to achieve proper connection alignment between fitting halves to a high degree of precision.
  • the features of the facing surfaces of the stick plate 142 and the boom plate 142 are also located by tight tolerance, to achieve the required depth of engagement required by the quick connect manufacturer.
  • a benefit of the quick-connect coupling apparatus is the ability to accommodate all types of connections—hydraulic, electrical, etc.
  • the primary motivation of the design is related to hydraulic circuit applications, since those connections occur and must support the most demanding physical requirements. Due to those requirements, hydraulic quick-connectors 144 require precise alignment and precise depth-of-engagement. This design can achieve these connection requirements in a reasonable method, and at an acceptable cost in material and installation.
  • connections can be made with almost no risk of damage to the fittings 144 .
  • the operation requires direct human involvement to reliably connect without damage to equipment.
  • the quick-connect fittings 144 are fixed on the stick frame 46 , so that hydraulic hard lines (pipe/tube) can be used to a much greater extent downstream of the connector, instead of less reliable hoses.
  • Implementation of this apparatus decouples the connection of the fittings 144 from the physical mating and lock of the supporting frames of the attachment system.
  • the frames 142 come together and lock before any quick-connect couplings 144 are commanded.
  • the couplings 144 are disconnected before the frames 142 are unlocked which allows (i) the quick-connect fittings 144 to join in a proper linear fashion, eliminating the requirement for a gimballing installation, (ii) the operation of frame mating and lock to be accomplished without concern for damage to the quick-connect fittings, thereby also allowing for much greater leeway in operator technique, and (iii) the operator the ability to position components after a physical frame lock but before the quick-connect extension.
  • the operator can reduce gravity loads on the equipment components (e.g. stick, tool, etc.) that might put undesirable hydraulic back-pressure on the lines to which the quick-connect fittings are attached.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Earth Drilling (AREA)
US17/415,297 2018-12-21 2019-12-23 Device to couple members of a heavy-duty machine Pending US20220056662A1 (en)

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US201862783855P 2018-12-21 2018-12-21
US17/415,297 US20220056662A1 (en) 2018-12-21 2019-12-23 Device to couple members of a heavy-duty machine
PCT/US2019/068263 WO2020132667A1 (fr) 2018-12-21 2019-12-23 Dispositif d'accouplement d'éléments d'une machine pour gros travaux

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5108252A (en) * 1988-04-04 1992-04-28 Gilmore Transportation Services, Inc. Quick-disconnect coupling for a machine having a boom and a stick
US5382110A (en) * 1992-12-30 1995-01-17 Esco Corporation Quick coupling device
US6301811B1 (en) * 2000-07-28 2001-10-16 Gilmore Industries, Inc. Coupler for a heavy-duty machine
US6428265B1 (en) * 2000-10-30 2002-08-06 Gilmore Industries, Inc. Power coupling mounting for a quick-disconnect coupling on a heavy-duty machine
US20050184510A1 (en) * 2004-02-06 2005-08-25 Langenfeld Joseph W. Hydraulic line attachment device and method
US20100229956A1 (en) * 2009-03-16 2010-09-16 Caterpillar Inc. Extendable fluid coupler
US9885167B2 (en) * 2013-07-16 2018-02-06 Clark Equipment Company Implement interface
US20210148080A1 (en) * 2019-11-20 2021-05-20 University Of Science And Technology Beijing Multi-degree-of-freedom automatic center-adjusting device, hydraulic quick-coupling device, and rescue equipment

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Publication number Priority date Publication date Assignee Title
US4938651A (en) 1988-04-04 1990-07-03 Gilmore Transportation Service, Inc. Gear lock quick disconnect mechanism for articulated machine
DE4208245C2 (de) * 1992-03-14 1994-01-20 Schaeff Karl Gmbh & Co Auslegersystem für Bagger
DE69328026T2 (de) 1992-07-27 2000-11-16 Gilmore Transp Ation Services Kupplungsvorrichtung für schwere erdbewegungsmaschinen
DE102014009908B3 (de) * 2014-07-06 2015-09-24 Johannes Burde Vorrichtung zum Kuppeln von Fluid-führenden Leitungen an einer Auslegertrennstelle von mobilen Arbeitsmaschinen

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5108252A (en) * 1988-04-04 1992-04-28 Gilmore Transportation Services, Inc. Quick-disconnect coupling for a machine having a boom and a stick
US5382110A (en) * 1992-12-30 1995-01-17 Esco Corporation Quick coupling device
US6301811B1 (en) * 2000-07-28 2001-10-16 Gilmore Industries, Inc. Coupler for a heavy-duty machine
US6428265B1 (en) * 2000-10-30 2002-08-06 Gilmore Industries, Inc. Power coupling mounting for a quick-disconnect coupling on a heavy-duty machine
US20050184510A1 (en) * 2004-02-06 2005-08-25 Langenfeld Joseph W. Hydraulic line attachment device and method
US20100229956A1 (en) * 2009-03-16 2010-09-16 Caterpillar Inc. Extendable fluid coupler
US9885167B2 (en) * 2013-07-16 2018-02-06 Clark Equipment Company Implement interface
US20210148080A1 (en) * 2019-11-20 2021-05-20 University Of Science And Technology Beijing Multi-degree-of-freedom automatic center-adjusting device, hydraulic quick-coupling device, and rescue equipment

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