US20060054453A1 - Roller track device for moving a load in a substantially horizontal plane - Google Patents
Roller track device for moving a load in a substantially horizontal plane Download PDFInfo
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- US20060054453A1 US20060054453A1 US10/532,145 US53214505A US2006054453A1 US 20060054453 A1 US20060054453 A1 US 20060054453A1 US 53214505 A US53214505 A US 53214505A US 2006054453 A1 US2006054453 A1 US 2006054453A1
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- Prior art keywords
- rail
- counter
- roller
- load
- designed
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
- B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
- B66F9/075—Constructional features or details
- B66F9/12—Platforms; Forks; Other load supporting or gripping members
- B66F9/19—Additional means for facilitating unloading
- B66F9/195—Additional means for facilitating unloading for pushing the load
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60P—VEHICLES ADAPTED FOR LOAD TRANSPORTATION OR TO TRANSPORT, TO CARRY, OR TO COMPRISE SPECIAL LOADS OR OBJECTS
- B60P1/00—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading
- B60P1/52—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading using rollers in the load-transporting element
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G13/00—Roller-ways
- B65G13/11—Roller frames
- B65G13/12—Roller frames adjustable
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G39/00—Rollers, e.g. drive rollers, or arrangements thereof incorporated in roller-ways or other types of mechanical conveyors
- B65G39/02—Adaptations of individual rollers and supports therefor
- B65G39/025—Adaptations of individual rollers and supports therefor having spherical roller elements
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
- B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
- B66F9/075—Constructional features or details
- B66F9/12—Platforms; Forks; Other load supporting or gripping members
Abstract
The invention concerns a roller track device based on simple kinematics without energy input, enabling reduction of the number of parts, of production cost of the assembly and of its space requirement, easy maintenance, and designed for being fitted on new handling apparatuses as well as for retrofitting. The roller track device (100) comprises a rail (310) bearing the static load, a guard rail (210) housed in the rail (310) and wherein are mounted rolling members (230) bearing the moving load. The guard rail (210) is coupled to a pivoting lever (410) co-operating with a lift bar (450) directly mounted on a machine (20) for moving the guard rail (210) relative to the rail (310) between a low position and a high position, wherein the load is supported either by the rail (310) or by the guard rail (210). The pivoting lever (410) transforms the vertical upward force exerted by the lift bar (450) into a horizontal force on the guard rail (210) to move it in horizontal translation (Th). The rail (310) comprises inclined ramps (331) co-operating with the rolling members (230) to move it in vertical translation (Tv) simultaneously with its horizontal movement (Th). The invention is useful for transferring heavy loads in a substantially horizontal plane between a fork handling apparatus and a machine such as a machine-tool, a press, and injection machine and the like.
Description
- The present invention concerns a roller track device for moving a load in a substantially horizontal plane between a load handling apparatus and a machine, said device being used to equip the forks on said handling apparatus and comprising at least one rail defining at least one plane contact surface capable of supporting said load when it is static, said rail being hollow, substantially horizontal, and having a longitudinal opening, at least one counter-rail housed within said rail within which roller devices are attached opposite said longitudinal opening, said roller elements being contained in a plane that is generally parallel to said surface and being capable of supporting said load when it is moving, at least one of the structures being associated with actuation means so to be movable relative to the other between at least a lower position and an upper position, in which positions the load is supported either by the rail or by the counter-rail, said actuation means displacing the structure known as the movable structure in at least horizontal translation, and lifting means located between the two structures so as to generate vertical displacement of the structure known as the movable structure simultaneous with its horizontal displacement. The present invention also concerns a handling device with forks that is equipped with such a roller device.
- In industry, load handling platforms such as, for example, elevator cars and stacking equipment are currently used to handle heavy loads. These heavy loads might consist of tools for machine tools, presses used to cut or stamp metal, or molds or forms used in the injection of synthetic material, etc. Generally, loads of less than two tons are transported on load handling platforms, while loads from two to ten tons are transported using fork apparatuses. Loads of over ten tons are transported by cranes.
- To facilitate the transfer of loads in the horizontal plane from the handling platform to the machine tool or vice versa, handling equipment now in use is provided with a roller device integral with the forks, designed to support the load and displace it without friction on the free roller devices. This handling equipment may also be provided with articulated arms designed to push or pull the load. The roller device generally comprises a “roller support structure” surmounted by a “load support structure.” The function of the load support structure is to support the load while the handling apparatus moves, whereas the function of the roller support structure is to support it without friction in order to effect the transfer. Passing the load from one structure to the other and vice versa is accomplished through the displacement of one structure relative to the other so that the roller devices on the roller-support structure can be retracted or extended relative to the load support structure, said relative displacement being controlled by means of manual or automatic actuators.
- In load handling devices using forks, this relative movement is generally controlled automatically either by a block provided on the machine tool and cooperating with said movable structure when the forks are attached, or by a cylinder integrated within the handling apparatus.
- In Publication DE-A-36 20 964 displacement of the structure called the movable structure is generated by a stop when the forks are attached to the machine tool, which causes the roller support structure to rise by making it pivot on an axle located in the tablet of the load handling apparatus. This is not a satisfactory solution because it requires a broad amplitude of movement, which increases the time required to transfer the load and necessitates use of large fork due to this amplitude. Moreover, the load is not uniformly distributed and there is no guaranty of simultaneous movement between the roller support structures, leading to premature wear and deterioration of the roller device. In addition, this system cannot be adapted to equip load handling apparatuses already in use.
- In Publications U.S. Pat. No. 3,243,029, U.S. Pat. No. 4,930,612 and U.S. Pat. No. 5,915,515, displacement of the structure called the movable structure is accomplished by a cylinder that raises the roller support structure through the intermediary of inclined ramp systems or bearings. These solutions are unsatisfactory as well, since they require a specific external energy source for supplying the cylinder or cylinders. These approaches are complex, expensive, and require a lot of space. Moreover, their design does not facilitate cleaning and maintenance of the roller devices, since the roller support device is difficult to disassemble. Finally, they are not suitable for retrofitting load handling apparatuses already in use.
- The present invention proposes overcoming these disadvantages with a roller device based on simple kinematics without any outside energy source which limits the number of pieces, reduces both the cost and space requirements for the unit, facilitates maintenance and cleaning, and which is suitable for both new apparatus and retrofitting existing ones.
- To achieve this, the invention concerns a roller device of the type indicated in the preamble characterized in that the actuation means comprises at least one block designed to be installed on said machine and at least one actuator located between the two structures which cooperates with said block so as to transform a vertical force exerted by said block on said actuator into a horizontal force exerted by said actuator onto said structure called the movable structure, displacing it in horizontal translation when the forks of the load handling devices are attached to said machine.
- In a preferred embodiment the lifting means comprises inclined ramps integral with said rail which cooperate with said roller elements on said counter-rail. These inclined ramps define at least a first zone which allows at least the tops of the roller elements to project, a second zone designed to cover the roller elements, and an intermediate zone designed to form, in combination with the roller elements, the lifting ramps. Each roller element advantageously comprises at least one roller designed to support the load in position for motion, said roller being attached to a generally horizontal axle between two rollers of smaller diameter, with the rollers being in contact with the inclined ramps.
- In a variation the lifting means may comprise articulated bearings having one extremity connected to said rail and other extremity connected to said counter-rail.
- Said actuator may be chosen from the group comprising at least a pivoting lever, a ball and socket, a rotating device, or a cylinder.
- Preferably the rail is fixed and the counter-rail supporting the roller elements is movable and cooperates with said actuator, the purpose of said actuator being to displace the counter-rail from its lower position to its upper position when it is in contact with the block and to allow the counter-rail to descend by gravity when it is no longer in contact with the block.
- In a first variation, the actuator comprises at least one pivoting lever attached to the rail by an axle oriented in a generally perpendicular to the direction of horizontal displacement of the counter-rail, said pivoting lever comprising at least two contact zones located on either side of the axle, one of which is in contact with the counter-rail and the other of which cooperates with said block. This pivoting lever comprises at least one roller located between the two contact zones and designed to supplement the roller elements on the counter-rail when it is in the upper position.
- In a second variation the actuator comprises at least one pivoting lever attached to said counter-rail by an axle oriented generally perpendicular to the direction of horizontal displacement of the counter-rail, said pivoting lever comprising at least two contact zones, one of which is in contact with the rail and the other of which cooperates with said block. One of the contact zones preferably constitutes a ramp capable of cooperating with a rotating element integral with said rail.
- In a third variation, the actuator comprises at least one rotating element attached to said counter-rail by an axle oriented generally perpendicular to the direction of horizontal displacement of the counter-rail, said rotating element being designed to move along an inclined ramp integral with said block, said rail being guided in vertical translation within said block by a tenon-slide system.
- In a fourth variation the actuator comprises at least one ball and socket consisting of at least one contact zone located at the intersection of two articulated lever arms and respectively connected to said rail and said counter-rail along two axles generally perpendicular to the direction of horizontal displacement of said counter-rail, with the contact zone being designed to cooperate with said block. The contact zones advantageously consist of rotating elements.
- In a fifth embodiment the actuator comprises at least one double cylinder, a first piston of which cooperates with said counter-rail and is oriented generally perpendicular to the direction of its horizontal displacement, with the second piston cooperating with said block and oriented generally perpendicular to said first piston. The second piston is preferably associated with a recall device. The piston chambers may be separate and connected by at least one conduit housed within the rail.
- In a sixth embodiment the actuator comprises at least one rotating element attached to the rail by an axle oriented generally perpendicular to the direction of horizontal displacement of the counter-rail and guided translationally within the rail by grooves, said rotating element cooperating with two ramps that are provided on the rail and the counter-rail, respectively, at least one of the ramps being inclined. This rotating element comprises at least three coaxial rollers of different diameters, at least two of which are movable in relation to each other, said rollers cooperating respectively with the ramp integral with the rail, the ramp integral with the counter-rail, and the block.
- The block is preferably selected from among at least a tie rod which can receive the front extremity of said forks and a machine table, said block being at least partially shaped to be compatible with the actuator.
- For the same purpose, the invention concerns a load handling apparatus with forks of the type indicated in the preamble characterized in that it comprises at least one roller device as defined above.
- The advantages of the present invention will be more apparent from the following description of several embodiments cited by way of non-limiting examples, with reference to the attached drawings, wherein:
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FIG. 1 is a perspective of a roller device according to the invention in the shape of a fork; -
FIG. 2 is a partial perspective of the device ofFIG. 1 ; -
FIG. 3 is a functional schema of the device ofFIG. 1 ; -
FIGS. 4A and 4B are partial side views of the device ofFIG. 1 , shown respectively in the extended and retracted positions; -
FIG. 5 is a functional schema of a first variation of the device of the invention; -
FIGS. 6A and 6B and partial side views of the device corresponding toFIG. 5 shown respectively in the retracted and extended positions; -
FIGS. 7A, 7B and 7C are schematic views of a second variation of the device according to the invention, respectively showing a side view in the retracted position, a top view and a side view in the extended position; -
FIGS. 8A and 8B are schematic views of a third variation of the device of the invention shown respectively in retracted and extended positions; -
FIGS. 9A and 9B are views similar toFIGS. 8A and 8B with other lifting means; -
FIGS. 10A, 10B and 11A, 11B are schematic views of a fourth and fifth variation of the device of the invention shown respectively in the retracted positions and extended; and -
FIGS. 12A, 12B , 13A and 13B are schematic views of a sixth and seventh variation of the invention shown respectively in the retracted and extended positions. - With reference to
FIGS. 1 through 4 roller device 100 according to the invention is fork-shaped and designed to equip a conventional load handling device with two parallel forks (not shown). It performs two functions: static support with friction of veryheavy loads 1 weighing up to about 10 tons while the load handling apparatus is moving, and dynamic support of theseloads 1 without friction while they are being transferred in a plane A parallel to the forks to or from amachine 20 which may be a machine tool, a press, an injection machine, or any other fixed or movable plane surface. - This
roller device 100 comprises aroller support structure 200 comprisingroller elements 230 surmounted by aload support structure 300 having a plane contact surface S provided with anopening 320 which allows at least the tops of theroller devices 230 to be visible. In this embodiment, and as shown schematically byFIG. 3 ,roller support structure 200 is movable, in relation to loadsupport structure 300 which is fixed, between two positions, at least one of which is stable: a lower position in which it retractsroller devices 230, withload 1 being in plane contact on surface S ofload support structure 300, and an upper position in which it releases the tops ofroller devices 230, withload 1 being either in linear contact or contact at some points onroller elements 230. Obviously the reverse configuration is also possible, that is, having theload support structure 300 movable relative toroller support structure 200. -
Roller support structure 200 is associated with actuation means 400 which displace it in horizontal translation Th along a course Ch and with lifting means 500 which displace it in vertical translation Tv on a course Cv simultaneously with horizontal displacement Th, with course Cv being shorter than course Ch. The originality ofroller device 100 of the invention resides in the fact that the actuating means 400 is mechanical and automatic, integrated withinroller device 100, occupies only a small space, and does not require any energy input. The other originality resides in the lifting means 500 which, rather than consisting of supplemental expensive and complicated mechanisms, is directly integrated withinload support structure 300 androller support structure 200. It is the specific result of moving contact betweenpieces load support structure 300 androller support structure 200, saidpieces - In the example shown,
load support structure 300 consists of a hollow,U-shaped rail 310 for use in the horizontal position defining alongitudinal opening 320 in the upper portion and an interior housing receivingroller support structure 200. Saidrail 310 comprises at its rear extremity avertical support 340 forming afork 10, said support being equipped withjaws 341 allowing saidfork 10 to be attached to the same place and in the same position as the existing forks on a standard load handling device. At its front extremity, saidrail 310 comprises alower notch 350 capable of engaging with a tie rod on amachine 20, for example. Insiderail 310blocks 330 withinclined ramps 331 are attached, eachblock 330 comprising two parallelinclined ramps 331. Theseinclined ramps 331 define at least onefirst zone 331 a which allows at least the tops ofroller elements 230 to project, asecond zone 331 b for coveringroller elements 230, and anintermediate zone 331 c which forms, in combination withroller elements 230, the lifting means 500. - The
roller support structure 200 constitutes a counter-rail 210 open from side to side and with dimensions that are complementary to those of the interior housing inrail 310 so as to be freely movable within saidrail 310 in horizontal translation Th and in vertical translation Tv.Said counter rail 210 is guided withinrail 310 by their respective lateral sides. It comprises a plurality ofrollers 230 aligned along its median axle in a plane parallel to plane contact surface S ofrail 310, saidrollers 230 being essentially cylindrical and constituting the roller elements. Eachroller 230 is freely attached to atransverse axle 220 integral with counter-rail 210. Eachtransverse axle 220 also supports tworollers 240 located on either side ofroller 230, having a smaller diameter thanroller 230 and positioned opposite and in contact withramps 331 on ablock 330. -
Roller support structure 200 is associated with an actuation means 400 which, in the example shown, is mechanical and automatic, and comprises a block consisting of thetie rod 450 attached tomachine 20 and an actuator in the form of a pivotinglever 410 integral withroller device 100 and cooperating with said block. The tie rod may be attached tomachine 20 withclamps 451 or any other appropriate means. Pivotinglever 410 is generally triangular with three tips and located in front of counter-rail 210 in the area of the front extremity ofrail 310. This pivotinglever 410 is attached to anaxle 420 integral withrail 310 and perpendicular to direction Th. It is designed to transform a vertical force exerted bytie rod 450 whenforks 10 are attached tomachine 20 into a horizontal force capable of displacing counter-rail 210 in horizontal translation. Therefore, the force transmitted by this pivotinglever 410 to counterrail 210 is generally proportionate to the size ofload 1. Said pivotinglever 410 comprises three distinct contact zones forming the three tips of the triangle and constituting roller elements: aroller 430 located oppositelower notch 350 onrail 310 and disposed to contacttie rod 450, aroller 440 in moving contact with the front extremity ofcounter-rail 210, and aroller 230 disposed to complementroller elements 230 onroller support structure 200. Obviously the actuator may consist of any other equivalent means such as, for example, a cylinder (cf.FIGS. 10 and 11 ), a nut and bolt, a ball and socket (cf.FIGS. 8 and 9 ), a simplified lever (cf.FIGS. 5 and 6 ), a roller element associated with an inclined ramp (cf.FIG. 7 ), etc. -
FIGS. 4A and 4B illustrate the operation of this pivotinglever 410. InFIG. 4B pivoting lever 410 is at rest, which corresponds to counter-rail 20 being in the lowered position in whichrollers 230 are retracted insiderail 310. This lowered position is stable. InFIG. 4A pivoting lever 410 is actuated bytie rod 450 added tomachine 20 whileforks 10 descend as the load handling device attaches tomachine 20.Tie rod 450 exerts on pivotinglever 410 throughroller 430 an upward vertical force causing it to rotate in a counterclockwise direction at an angle of about 45°, movingroller 230 onlever 410 into the extension of theother rollers 230 and pushing counter-rail 210 in horizontal translation Th, said counter-rail simultaneously effecting vertical translation Tv by virtue of the displacement ofrollers 240 oninclined ramps 331.Counter-rail 210 is moved to the upper position in whichrollers 230 project above surface S ofrail 310. This upper position is not stable since whenforks 10 are disengaged fromtie rod 450, counter-rail 210 descendsinclined ramps 331 due to gravity and returns to the lower position, simultaneously returning pivotinglever 410 to its resting position (cf.FIG. 4B ). -
FIGS. 5 and 6 illustrate aroller device 110 similar to the preceding one with only the actuation means 400′ being different. Actuation means 400′ comprises anupright pivoting lever 410′ with two extremities cooperating with a mechanical block consisting of table 20′ ofmachine 20. This pivotinglever 410′ is attached at one end to anaxle 420′ integral with counter-rail 210 and oriented in a generally perpendicular direction to the direction of horizontal displacement Th of said counter-rail 210. As before, it is designed to transform the vertical force exerted directly by table 20′ ofmachine 20 whenforks 10 are attached into a horizontal force capable of displacing counter-rail 210 in horizontal translation Th. This pivotinglever 410′ comprises twocontact areas 430′, 440′.Contact area 430′ is located at the free extremity of pivotinglever 410′ and enters into contact with table 20′ ofmachine 20 whenforks 10 become attached totie rod 450′.Contact zone 440′ consists of a ramp extending between the two extremities of pivotinglever 410′ in a slight curve and capable of cooperating with arotating element 441′ integral withrail 310 and attached to the extremity ofsupport arm 442′. -
FIGS. 6A and 6B illustrate the operation of this pivotinglever 410′. InFIG. 6A the pivotinglever 410′ is at rest, corresponding to counter-rail 210 being in the lower position in whichrollers 230 are retracted insiderail 310. This lower position is stable. InFIG. 6B pivoting lever 410′ is actuated by table 20′ onmachine 20 which transmits an upward vertical force, causing it to rotate clockwise at an angle of about 30°, withramp 440′ being displaced relative to fixedrotating element 441′ and generating the displacement ofcounter-rail 210 in horizontal translation Th. The latter simultaneously effects vertical translation Tv due to the displacement ofrollers 240 alonginclined ramps 331.Counter-rail 210 is moved to the upper position in whichrollers 230 project above surface S ofrail 310. This upper position is not stable because whenforks 10 are disengaged frommachine 20, counter-rail 210 descendsinclined ramps 331 due to gravity, returning to the lower position, and returning pivotinglever 410′ to its resting position (cf.FIG. 6B ). -
FIGS. 7A through 7C illustrate athird roller device 120 wherein the actuation means 600 comprises an actuator in the form of a movingdevice 610 integral with counter-rail 210 and associated with a block formed of aninclined ramp 620 provided in atie rod 650 added tomachine 20. Movingdevice 610 may consist, for example, of a roller attached to an axle at the front extremity ofcounter-rail 210 andinclined ramp 620 is situated between two lateral sides oftie rod 650. These lateral sides comprise the parallel andvertical slides 640 which receivetenons 630 provided on either side of the front extremity ofrail 310 to ensure thatforks 10 are mechanically attached tomachine 20. -
FIGS. 7A and 7C illustrate the operation of this actuation means 600. InFIG. 7A roller device 120 is at rest, corresponding to counter-rail 210 being in the lower position whereinrollers 230 are retracted insiderail 310. This lower position is stable. InFIG. 7C ,roller 610 moves alonginclined ramp 620 whileforks 10 descend to attach the load handling device tomachine 20. The vertical force exerted bytie rod 650 is transformed into horizontal force against counter-rail 210 because of the combination ofinclined ramp 620 withroller 610. Counter-rail 210 effects, simultaneously with its horizontal translation Th, vertical translation Tv due to the displacement ofrollers 240 alonginclined ramps 331.Counter-rail 210 is moved to the upper position in whichrollers 230 project above surface S ofrail 310. This upper position is not stable because whenforks 10 are disengaged frommachine 20 toward the top, rollingelement 610 again travels upinclined ramp 620, allowing counter-rail 210 to descendinclined ramps 331 due to gravity and return to the lower position (cf.FIG. 7A ). -
FIGS. 8A and 8B are schematic representations of afourth roller device 130 in which the actuation means 700 comprises an actuator in the form of a ball andsocket 710 integral withroller device 130 and associated with a block formed of atie rod 750 added tomachine 20. Ball and socket joint 710 comprises a rollingelement 720 attached to the intersection of two articulatedlever arms 730. The extremities of theselever arms 730 are respectively attached to rail 310 and to counter-rail 210 by anarticulation 740. InFIG. 8A ball andsocket 710 is at rest, corresponding to counter-rail 210 being in the lower position in whichrollers 230 are retracted insiderail 310. This lower position is stable. InFIG. 8B ball andsocket 710 is actuated bytie rod 750 which exerts an upward vertical force on rollingelement 720 asforks 10 descend to attach the load handling device tomachine 20. This upward vertical force is transformed into horizontal force againstcounter-rail 210 due to leverarms 730 andarticulations 740. Counter-rail 210 effects simultaneously with its horizontal translation Th, vertical translation Tv due to the displacement ofrollers 240 oninclined ramps 331.Counter-rail 210 is moved to the upper position in whichrollers 230 project above surface S ofrail 310. This upper position is not stable because whenforks 10 are disengaged frommachine 20, counter-rail 210 descends includeramps 331 due to gravity to return to the lower position and simultaneously return ball andsocket 710 to its resting position (cf.FIG. 8A ). -
FIGS. 9A and 9B are schematic representations of afifth roller device 140 using the same actuations means 700 as the previous device. The difference resides in the lifting means 500′ which comprises articulatedbearings 510 disposed betweenrail 310 and counter-rail 210. When counter-rail 210 is displaced in horizontal translation Th by ball andsocket 710 in contact withtie rod 750, it simultaneously effects vertical translation Tv due to the pivoting ofbearings 510 between their fixed point, integral withrail 310, and their movable point, integral with counter-rail 210.FIGS. 9A and 9B showroller device 140 in retracted and extended positions, respectively. -
FIGS. 10A and 10B are schematic representations of asixth roller device 150 in which the actuation means 800 comprises an actuator in the form of acylinder 810 integral withroller device 150 and associated with a block formed of atie rod 850 added tomachine 20.Cylinder 810 is a double cylinder, hydraulic or pneumatic, consisting of one chamber and twoperpendicular pistons piston 820 is essentially vertical and enters into contact withtie rod 850. It is associated with arecall spring 830. Theother piston 840 is generally horizontal and attached to the front extremity ofcounter-rail 210. InFIG. 10A ,cylinder 810 is at rest, which corresponds to counter-rail 210 being in the lower position in whichrollers 230 are retracted insiderail 310. This lower position is stable. InFIG. 10B cylinder 810 is actuated bytie rod 850 which exerts an upward vertical force onpiston 820, causing it to rise by compressing itsrecall spring 830 and causing the fluid in its chamber to pushpiston 840 out, saidpiston 840 then exerting horizontal force oncounter-rail 210. Counter-rail 210 effects simultaneously with its horizontal translation Th, vertical translation Tv due to the displacement ofrollers 240 alonginclined ramps 331.Counter-rail 210 is moved to the upper position in whichrollers 230 project above surface S ofrail 310. This upper position is not stable because whenforks 10 are disengaged frommachine 20,piston 820 again moves down due to the action of itsrecall spring 230, allowing counter-rail 210 to descendinclined ramps 331 due to gravity and return to the lower position, whilecylinder 810 is returned to the resting position (cf.FIG. 10A ). -
FIGS. 11A and 11B are schematic representations of aseventh roller device 160 similar to the preceding one, with the actuation means 900 also comprising an actuator in the form of acylinder 910 integral withroller device 150 and associated with a block formed of atie rod 950 added tomachine 20. In thisvariation cylinder 910 is a double cylinder, hydraulic or pneumatic, consisting of twopistons separate chamber conduit 912. One of thepistons 920 is generally vertical in order to enter into contact withtie rod 950. It is associated with arecall spring 930. Theother piston 940 is generally horizontal and attached to the rear extremity ofcounter-rail 210. In this variation inclinedramps 331 are reversed in relation to those ofFIGS. 10A and 10B . The functioning of thisroller device 160 is the same as the preceding one and will not be repeated. -
FIGS. 12A and 12B are schematic representations of aneighth roller device 170 in which the actuation means 1000 comprises an actuator in the form of arotating element 1010 cooperating with aninclined ramp 1020 integral withroller device 170 and associated with a block formed of atie rod 1050 added tomachine 20.Inclined ramp 1020 is provided in the area of the front extremity ofrail 310 and oriented in the direction ofinclined ramps 331 onrail 310.Rotating element 1010 is attached so as to be movable in rotation and in translation withinrail 310 and guided by itsaxle 1011 insidegrooves 1021 provided in the lateral walls ofrail 310 and extending generally parallel toinclined ramp 1020. It is formed of threecoaxial rollers first roller 1010 designed to move alonginclined ramp 1020, asecond roller 1013 designed to move along avertical ramp 211 located at the front ofcounter-rail 210, and athird roller 1014 designed to move along the horizontal plane oftie rod 1050. InFIG. 12A ,roller device 170 is at rest, corresponding to counter-rail 210 being in the lower position in whichrollers 230 are retracted insiderail 310. This lower position is stable. InFIG. 12B rotating element 1010 is actuated bytie rod 1050 which exerts an upward vertical force on it using itsthird roller 1014, causing it to move up by moving alonginclined ramp 1020 using itsfirst roller 1012 and simultaneously onvertical ramp 211 of counter-rail 210 using itssecond roller 1013 and then exerting horizontal force oncounter-rail 210. Counter-rail 210 effects simultaneously with horizontal translation Th, vertical translation Tv due to the displacement ofrollers 240 alonginclined ramps 331.Counter-rail 210 is moved to the upper position in whichrollers 230 project above surface S ofrail 310. This upper position is not stable because whenforks 10 are disengaged frommachine 20, rotatingelement 1010 redescends due to gravity alonginclined ramp 1020, while counter-rail 210 simultaneously descendsinclined ramps 331 due to gravity to return to the lower position, withroller device 170 being returned to the resting position (cf.FIG. 12A ). -
FIGS. 13A and 13B are schematic representations of aninth roller device 180 similar to the preceding one, with the actuating means 1100 also comprising an actuator in the form of arotating element 1110 cooperating with aninclined ramp 1120 integral withroller device 180 and associated with a block formed of atie rod 1150 added tomachine 20. In this variation inclinedramp 1120 is provided at the front extremity ofcounter-rail 210 and oriented in the opposite direction frominclined ramps 331 onrail 310.Rotating element 1110 is attached to be movable in rotation and in translation insiderail 310 and guided by itsaxle 1111 ingroves 1121 provided in the lateral walls ofrail 310 and extending generally vertically. It is formed of threecoaxial rollers first roller 1112 designed to move along avertical ramp 311 provided in the zone of the front extremity ofrail 310, asecond roller 1113 designed to move alonginclined ramp 1120 ofcounter-rail 210, and athird roller 1114 designed to contact the horizontal plane oftie rod 1150. Thisthird roller 1114 may be a non-rotating one, since its displacement is limited to vertical translation. The operation of thisroller device 180 is similar to thepreceding device 170. - It is clearly apparent that the roller device according to the invention originates from a simple kinematic concept. For this reason it is economical to buy as well as to maintain; it occupies a small amount of space and it is durable. More specifically, counter-rail 210 can be easily removed from
rail 310 to facilitate cleaning and maintenance. Because the actuator is integral withrail 310, it does not interfere with the performance of the load handling device. The advantage of this actuator is that it is automatically and mechanically activated by a block while the forks are being attached to the machine, without any energy input. - The roller device as described can be sold with forks to retrofit load-handling apparatuses already in use, or integrated into new equipment. It is for this reason that the invention also applies to load-handling apparatuses (not shown) equipped with such a roller device.
- The present invention is not limited to the exemplary embodiments described, but extends to any modification and variation obvious to a person skilled in the art while still remaining within the scope of protection defined by the attached claims.
Claims (22)
1-21. (canceled)
22. A roller device (100-180) for displacing a load (1) in a generally horizontal plane between a load handling apparatus with forks and a machine (20), the device being designed to equip the forks (10) of a handling device, the roller device comprising;
at least one rail (310) defining at least one plane contact surface (S) capable of supporting the load (1) when the load is static, the rail (310) being hollow, generally horizontal, and provided with a longitudinal opening (320);
at least one counter-rail (210) housed inside the rail (310) and inside of which roller elements (230) are attached opposite the longitudinal opening (320), the roller elements (230) being located in a plane that is generally parallel to the surface (S) and capable of supporting the load (1) when the load is moving; and
an actuating means (400, 400′, 600-1000) being connected to at least one of the rail (310) and the counter-rail (210) so as to be movable relative to another of the rail (310) and the counter-rail (210) between at least one lower position and one upper position, in the upper and the lower positions, the load is supported either by the rail (310) or by the counter-rail (210), the actuating means being disposed to displace the at least one rail (210) and the at least one counter rail (310) in at least a horizontal translation (Th), with lifting means (500, 500′) being disposed between the at least one rail (210) and the at least one counter rail (310) to cause the at least one rail (210) and the at least one counter rail (310) to move in a vertical displacement (Tv) simultaneously with the horizontal displacement (Th), the actuating means (400, 400′, 610-1100) comprises,
at least one block (450, 20′, 650-1150) designed to be attached to the machine (20), and
at least one actuator (410, 410′, 610-1110) disposed between the at least one rail (210) and the at least one counter rail (310) and designed to cooperate with the block and to transform a vertical force exerted by the block on the actuator into a horizontal force exerted by the actuator on the at least one rail (210) and the at least one counter rail (310) to displace the load in the horizontal translation (Th) when the forks (10) on the load handling apparatus are connected to the machine (20).
23. The roller device (100-130, 150-180) according to claim 22 , wherein the lifting means (500) comprises inclined ramps (331) integral with the rail (310) and designed to cooperate with the roller elements (230) on the counter-rail (210).
24. The roller device according to claim 23 , wherein the inclined ramps (331) define at least a first zone (331 a) designed to allow at least tops of the roller elements (230) to project, a second zone (331 b) designed to cover the roller elements (230), and an intermediate zone (331 c) forming, in combination with the roller elements, the lifting ramps.
25. The roller device according to claim 24 , wherein each of the roller elements comprise at least one roller (230) designed to support the load (1) in a moving position, the roller (230) being attached to a generally horizontal axle (220) between two other rollers (240) of smaller diameter, the two other rollers (240) being in contact with the inclined ramps (331).
26. The roller device (140) according to claim 22 , wherein the lifting means (500′) comprises articulated bearings (510) having a first extremity connected to the rail (310) and a second extremity connected to the counter-rail (210).
27. The roller device according to claim 22 , wherein the actuator is chosen from a group comprising at least a pivoting lever (410, 410′), a ball and socket (710), a rotating element (610), and a cylinder (810, 910).
28. The roller device according to claim 22 , wherein the rail (310) is fixed and the counter-rail (210) supporting the roller elements (230) is movable and cooperates with the actuator (410, 410′, 610-1110), the actuator being designed to displace the counter-rail (210) from the lower position to the upper position when in contact with the block (450, 20′, 650-1150) and to allow the counter-rail (210) to descend into the lower position by gravity when the counter-rail (210) is no longer in contact with the block.
29. The roller device (100) according to claim 28 , wherein the actuator comprises at least one pivoting lever (410) attached to the rail (310) by an axle (420) oriented in a generally perpendicular direction to a direction of the horizontal displacement (Th) of the counter-rail (210), the pivoting lever (410) comprising at least two contact zones (430, 440) located on either side of the axle (420), a first contact zone (440) is in contact with the counter-rail (210) and a second contact zone (430) is designed to cooperate with the block (450).
30. The roller device according to claim 29 , wherein the pivoting lever (410) comprises at least a first roller element (230) located between the two contact zones (430, 440) and designed to complement the roller elements (230) on the counter-rail (210) when the counter-rail (210) is in the upper position.
31. The roller device (110) according to claim 28 , wherein the actuator comprises at least one pivoting lever (410′) attached to the counter-rail (210) by an axle (420′) oriented in a generally perpendicular direction to a direction of horizontal displacement (Th) by the counter-rail (210), the pivoting lever (410) comprising at least two contact zones (430′, 440′), a first contact zone (440′) is in contact with the rail (310) and a second contact zone (430′) is designed to cooperate with the block
32. The roller device according to claim 31 , wherein the first contact zone (440′) consists of a travel ramp capable of cooperating with a rotating element (441′) integral with the rail (310).
33. The roller device (120) according to claim 28 , wherein the actuator comprises at least one rotating element (610) attached to the counter-rail (210) by an axle oriented in a generally perpendicular direction to a direction of horizontal displacement (Th) of the counter-rail, the rotating element (610) being designed to move along an inclined ramp (620) integrated within the block (650), the rail (310) being guided in vertical translation within the block (650) by a tenon (630) and a slide (640) system.
34. The roller device (130, 140) according to claim 28 , wherein the actuator comprises at least one ball and socket (710) having at least one contact zone (720) disposed at an intersection of two articulated lever arms (730) respectively connected to the rail (310) and to the counter-rail (210) along axles that are generally perpendicular to the horizontal displacement (Th) of the counter-rail (210), the contact zone (720) being designed to cooperate with the block (750).
35. The roller device according to claim 29 , wherein the contact zones (430, 440, 430′, 720) are comprised of rotating elements.
36. The roller device (150, 160) according to claim 28 , wherein the actuator comprises at least one double cylinder (810, 910), a first piston (840, 940) of which cooperates with the counter-rail (210) and is generally parallel to the horizontal displacement (Th), and a second piston (820, 920) of which is designed to cooperate with the block (850, 950) and is generally perpendicular relative to the first piston (840, 940).
37. The roller device according to claim 36 , wherein the second piston (820, 920) is associated with a recall means (830, 930).
38. The roller device (160) according to claim 36 , wherein chambers (911, 913) of the first and the second pistons (920, 940) are separate and interconnected by at least one conduit (912) housed in the rail (310).
39. The roller device (170, 180) according to claim 28 , wherein the actuator comprises at least one rotating element (1010, 1110) attached to the rail (310) by an axle (1011, 1111) oriented generally perpendicular to the horizontal displacement (Th) of the counter-rail (210) and guided in translation within the rail (310) by grooves (1021, 1121), the rotating element (1010, 1110) being designed to cooperate with two ramps (1020, 211; 311, 1120) provided on the rail (310) and the counter-rail (210), respectively, at least one of the ramps (1020, 1120) being inclined.
40. The roller device according to claim 39 , wherein the rotating element (1010, 1110) comprises at least three coaxial rollers (1012, 1013, 1014; 1112, 1113, 1114) of different diameters, at least two of the three coaxial rollers are movable in relation to each other, the two of the three coaxial rollers being designed to respectively cooperate with the ramp (1021, 311) integral with the rail (310), the ramp (211, 1120) integral with the counter-rail (210), and the block (1050, 1150).
41. The roller device according to claim 22 , wherein the block is selected from among at least a tie rod (450, 650-1150) capable of receiving a front extremity of the forks (10) and a machine table (10′), and is at least partially shaped to be compatible with the actuator (410, 410′, 610-1110).
42. A load handling device with forks for displacing a load (1) in a generally horizontal plane between the load handling device and a machine (20), the forks (10) comprise the roller device (100-180), the device being designed to equip the forks (10) of a handling device, the roller device comprising;
at least one rail (310) defining at least one plane contact surface (S) capable of supporting the load (1) when the load is static, the rail (310) being hollow, generally horizontal, and provided with a longitudinal opening (320);
at least one counter-rail (210) housed inside the rail (310) and inside of which roller elements (230) are attached opposite the longitudinal opening (320), the roller elements (230) being located in a plane that is generally parallel to the surface (S) and capable of supporting the load (1) when the load is moving; and
an actuating means (400, 400′, 600-1000) being connected to at least one of the rail (310) and the counter-rail (210) so as to be movable relative to another of the rail (310) and the counter-rail (210) between at least one lower position and one upper position, in the upper and the lower positions, the load is supported either by the rail (310) or by the counter-rail (210), the actuating means being disposed to displace the at least one rail (210) and the at least one counter rail (310) in at least a horizontal translation (Th), with lifting means (500, 500′) being disposed between the at least one rail (210) and the at least one counter rail (310) to cause the at least one rail (210) and the at least one counter rail (310) to move in a vertical displacement (Tv) simultaneously with the horizontal displacement (Th), the actuating means (400, 400′, 610-1100) comprises,
at least one block (450, 20′, 650-1150) designed to be attached to the machine (20), and
at least one actuator (410, 410′, 610-1110) disposed between the at least one rail (210) and the at least one counter rail (310) and designed to cooperate with the block and to transform a vertical force exerted by the block on the actuator into a horizontal force exerted by the actuator on the at least one rail (210) and the at least one counter rail (310) to displace the load in the horizontal translation (Th) when the forks (10) on the load handling apparatus are connected to the machine (20).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR02/13075 | 2002-10-21 | ||
FR0213075A FR2845980B1 (en) | 2002-10-21 | 2002-10-21 | BEARING DEVICE FOR MOVING A LOAD IN A SUBSTANTIALLY HORIZONTAL PLANE AND HANDLING APPARATUS PROVIDED WITH SUCH A DEVICE |
PCT/FR2003/003127 WO2004037704A1 (en) | 2002-10-21 | 2003-10-21 | Roller track device for moving a load in a substantially horizontal plane |
Publications (1)
Publication Number | Publication Date |
---|---|
US20060054453A1 true US20060054453A1 (en) | 2006-03-16 |
Family
ID=32050575
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/532,145 Abandoned US20060054453A1 (en) | 2002-10-21 | 2003-10-21 | Roller track device for moving a load in a substantially horizontal plane |
US10/532,144 Expired - Lifetime US7237667B2 (en) | 2002-10-21 | 2003-10-21 | Load handling platform provided with retractable rollers |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
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US10/532,144 Expired - Lifetime US7237667B2 (en) | 2002-10-21 | 2003-10-21 | Load handling platform provided with retractable rollers |
Country Status (7)
Country | Link |
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US (2) | US20060054453A1 (en) |
EP (2) | EP1556306B1 (en) |
AT (1) | ATE339385T1 (en) |
AU (2) | AU2003285431A1 (en) |
DE (2) | DE60308400T2 (en) |
FR (1) | FR2845980B1 (en) |
WO (2) | WO2004037687A1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140178165A1 (en) * | 2012-12-20 | 2014-06-26 | Caterpillar Inc. | Fork with rollers |
US20150298951A1 (en) * | 2014-02-10 | 2015-10-22 | Rehrig Pacific Company | Pallet lift rails |
US9309053B2 (en) | 2014-02-18 | 2016-04-12 | Abb Inc. | Conveyor system and associated product carrier |
US20170183161A1 (en) * | 2015-12-29 | 2017-06-29 | Guangdong Oufulong Automatic Shelf Technology Co., Ltd. | Automatic roller shaft transmission device |
US10364135B1 (en) * | 2017-04-10 | 2019-07-30 | S.A.S. Of Luxemburg | Protection bumper for a vehicle handling fork |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
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DE202004020224U1 (en) * | 2004-12-31 | 2005-05-19 | Fischer, Frank D. | Device for transport, transfer, weighing and reloading of air freight transport units |
US8108989B2 (en) * | 2007-06-28 | 2012-02-07 | Crown Equipment Corporation | Manufacturing cell and elements of the cell |
FR2928610A1 (en) * | 2008-03-11 | 2009-09-18 | Renault Sas | Floor pan for e.g. loading, object, has displacement device with series of ramps whose shape is determined, so that rollers are in lower rest and higher rolling positions when axles are in bottom and top of ramps, respectively |
AT508038B1 (en) * | 2009-04-02 | 2012-01-15 | Schelling Anlagenbau Gmbh | sawing machine |
CN201907831U (en) * | 2010-06-15 | 2011-07-27 | 鸿富锦精密工业(深圳)有限公司 | Workpiece feeding device |
DE102011053456A1 (en) * | 2011-09-09 | 2013-03-14 | Ulrich Christophersen | Land vehicle, particularly crane for transporting large-volume cargo, such as parts of wind turbines, has two cargo carriers arranged behind each other in vehicle longitudinal direction on chassis supported by multi-axis platform |
US10245192B2 (en) * | 2016-04-13 | 2019-04-02 | Bobby Allan Burkeen | Extendable and retractable gurney |
US11124358B2 (en) * | 2016-08-18 | 2021-09-21 | Super Micro Computer, Inc. | Roller platform transport system |
CN110963232B (en) * | 2019-12-14 | 2021-03-16 | 深圳市开步电子有限公司 | Automatic coating machine for resistor machining |
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2002
- 2002-10-21 FR FR0213075A patent/FR2845980B1/en not_active Expired - Fee Related
-
2003
- 2003-10-21 EP EP03778432A patent/EP1556306B1/en not_active Expired - Lifetime
- 2003-10-21 US US10/532,145 patent/US20060054453A1/en not_active Abandoned
- 2003-10-21 WO PCT/FR2003/003126 patent/WO2004037687A1/en active IP Right Grant
- 2003-10-21 AU AU2003285431A patent/AU2003285431A1/en not_active Abandoned
- 2003-10-21 WO PCT/FR2003/003127 patent/WO2004037704A1/en not_active Application Discontinuation
- 2003-10-21 AT AT03778432T patent/ATE339385T1/en not_active IP Right Cessation
- 2003-10-21 AU AU2003285430A patent/AU2003285430A1/en not_active Abandoned
- 2003-10-21 US US10/532,144 patent/US7237667B2/en not_active Expired - Lifetime
- 2003-10-21 EP EP03778431A patent/EP1554199B1/en not_active Expired - Lifetime
- 2003-10-21 DE DE60308400T patent/DE60308400T2/en not_active Expired - Lifetime
- 2003-10-21 DE DE60311127T patent/DE60311127T2/en not_active Expired - Lifetime
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US3243029A (en) * | 1964-10-13 | 1966-03-29 | Emerson T Oliver | Retractable conveyor rollers |
US3625158A (en) * | 1968-11-11 | 1971-12-07 | Blaser Hebe Foerderanlagen | Trolley for overhead monorail conveyor |
US4911279A (en) * | 1987-09-08 | 1990-03-27 | Talson Transport Engineering, B.V. | Roller track |
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US20140178165A1 (en) * | 2012-12-20 | 2014-06-26 | Caterpillar Inc. | Fork with rollers |
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US9908761B2 (en) * | 2014-02-10 | 2018-03-06 | Rehrig Pacific Company | Pallet lift rails |
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US20170183161A1 (en) * | 2015-12-29 | 2017-06-29 | Guangdong Oufulong Automatic Shelf Technology Co., Ltd. | Automatic roller shaft transmission device |
US10364135B1 (en) * | 2017-04-10 | 2019-07-30 | S.A.S. Of Luxemburg | Protection bumper for a vehicle handling fork |
Also Published As
Publication number | Publication date |
---|---|
FR2845980B1 (en) | 2005-09-23 |
DE60311127D1 (en) | 2007-02-22 |
WO2004037687A1 (en) | 2004-05-06 |
ATE339385T1 (en) | 2006-10-15 |
DE60311127T2 (en) | 2007-11-08 |
WO2004037704A1 (en) | 2004-05-06 |
FR2845980A1 (en) | 2004-04-23 |
EP1554199A1 (en) | 2005-07-20 |
DE60308400T2 (en) | 2007-09-13 |
AU2003285430A1 (en) | 2004-05-13 |
US20060054452A1 (en) | 2006-03-16 |
EP1556306A1 (en) | 2005-07-27 |
EP1554199B1 (en) | 2007-01-10 |
AU2003285431A1 (en) | 2004-05-13 |
EP1556306B1 (en) | 2006-09-13 |
US7237667B2 (en) | 2007-07-03 |
DE60308400D1 (en) | 2006-10-26 |
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Owner name: ROTOBLOC S.A.R.L., FRANCE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:MARCELLI, PIERRE;REEL/FRAME:015979/0115 Effective date: 20050321 |
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Free format text: ABANDONED -- FAILURE TO PAY ISSUE FEE |