|Publication number||US7121920 B1|
|Application number||US 11/191,445|
|Publication date||Oct 17, 2006|
|Filing date||Jul 27, 2005|
|Priority date||Jul 29, 2002|
|Also published as||US7056188, US7232361|
|Publication number||11191445, 191445, US 7121920 B1, US 7121920B1, US-B1-7121920, US7121920 B1, US7121920B1|
|Inventors||Kevin R. Triplett, Mark C. Adamson, Steven J. Erickson, Mark W. Snedden|
|Original Assignee||Robinson Brick|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (21), Non-Patent Citations (2), Referenced by (6), Classifications (18), Legal Events (5)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This application continuation of application Ser. No. 10/629,412 filed Jul. 29, 2003 which claims the benefits of provisional application No. 60/399,340 filed Jul. 29, 2002
Saws that cut rock, brick and similar materials are well known in the art. Using a conveyor belt to carry the material to the blade is also well known in the art. One of the common problems with conveyor belt systems is that the conveyor carries the material to the blade at a given speed. With rock in particular, the material can have irregular shapes and varying degrees of hardness and/or thickness, resulting in a wide variation in the difficulty of cutting a given piece. It is well known in the art to control the pressure of the saw blade, so that the saw blade does not change speed as the blade encounters harder and softer substances, thereby increasing blade efficiencies and extending equipment/tooling life.
The problem presented by the prior art is that the conveyor belt continued to present the material at a given rate of speed, regardless of how hard the saw motor has to work. This increases the wear on the saw and can cause premature blade segment wear and even blade segment separation from the blade core, which is a distinct hazard. Furthermore, as the material being cut is forced upon a blade already working at maximum capacity, drive train components, and eventually the prime mover, may prematurely fail.
Another problem in rock saws is that there is a demand for “corner pieces” of facing rock to use for building faces. The corner pieces need to have an interior corner cut into the rock so that the rock can be placed on the corner of the building. At the present time these pieces need to be cut by hand using freestanding rock saws. This is time consuming, costly and can result in large amounts of spoilage while forcing the saw operator to work in close proximity to a rotating, exposed saw blade.
The disclosed device solves these problems by using a saw motor load sensor to control the speed of the conveyors bringing the rock to the saw blade. As the saw motor works harder to cut a given rock, the controller automatically slows the conveyor belts, reducing the load on the saw blade. If the saw blade is easily cutting a given rock and not working at optimum speed, the conveyors will be sped up, increasing production.
Also provided in an alternate embodiment is a horizontal blade that can be moved into place to cut the “bottom” of a corner piece, then the standard, vertical blade cuts the other side of the corner.
Common in all manual rock cutting operations is the need to produce a clean finished product. Manual sawing of stone produces fines, a gritty, slurry like material of rock dust and water. As the water dries from the finished product, a thin film of rock dust remains on the product changing the color of the slab. In manual operations, this slurry like material is often sprayed onto the saw operator becomes airborne as a mist. Without proper respirators this mist can expose the operator to silicosis. A water spray that both cleans the finished product and causes the mist to be directed away from the operators can be incorporated in all embodiments, potentially reducing the risk of silicosis.
The primary aspect of the device is to provide a rock saw that has variable speed conveyor belts which are controlled by the work load on the saw motors.
Other aspects of this invention will appear from the following description and appended claims, reference being made to the accompanying drawings forming a part of this specification wherein like reference characters designate corresponding parts in the several views.
Before explaining the disclosed embodiment of the present invention in detail, it is to be understood that the invention is not limited in its application to the details of the particular arrangement shown, since the invention is capable of other embodiments. Also, the terminology used herein is for the purpose of description and not of limitation.
The disclosed saw can be used to cut rock, concrete, block, clay brick or any similar hard material. For simplicity, only the cutting of rock will be specifically mentioned, but it is understood that the cutting of all of the other materials is included within the scope of this disclosure.
Referring first to
The vertical conveyor 6 is located behind the vertical blade 4 and is spaced a given distance D1 from the vertical blade 4. D1 will be the thickness of the rock slice B that is cut by the rock saw, as shown in
As shown in
Both the rocking panel arm 15 and the roller arm 16 are pivotally attached to the frame 2 and are sprung towards the vertical conveyor 6 with springs (Not shown) in boxes 14.1.
As best shown in
Blade 4 is water-cooled and cleaned with jets with water in a known manner and is therefore not shown. The water drains-into trough 18 and is drained from there by drain 19. In addition, final jets 25, shown in
An alternate embodiment of the present invention is shown in
The rock saw 100 has a main conveyor 300 and a vertical conveyor 600, which are both driven by conveyor motor 700, again in a known manner.
The main conveyor 300 has rollers 800,900 and a conveyor belt 1000. The conveyor belt 1000 is made of a durable material to hold the heavy rocks and so that any accidental contact of the vertical blade 400 not cut the conveyor belt 1000. The main conveyor 300 can either be fixed in place or can be adapted (not shown) to move vertically in relation to the vertical blade 400. Conveyor 300 can be moved in the vertical positions relative to blade 400 at the same time by incorporating a series of interconnected jackscrews mounted on frame 200 or other known adjustable mechanisms. The adjustable mechanism must be capable of being exactly adjusted to a given location and the adjustment mechanism must be able to withstand the vibrations of the operation of the saw 100 without moving.
The vertical conveyor 600 is located behind the vertical blade 400 and is spaced a given distance D1 from the vertical blade 400. D1 will be the thickness of the rock slice C that is cut by the rock saw. The vertical conveyor 600 is mounted on frame 1100. The vertical conveyor 6 can be moved closer to or away from the vertical blade 4 at adjustment points 120, 130 as shown in
As shown in
The horizontal blade mechanism 2000 in the disclosed embodiment is pivotally mounted to frame 200 at point 201 via mounting arm (not shown). The horizontal blade 2001 is powered by horizontal blade motor 2002 and connected to the blade 2001 in a known manner. In operation to cut a corner piece both blades 400 and 2001 will be in operation simultaneously as shown in
An additional alternate embodiment is shown in
The conveyor belt 1210 is formed of durable material to hold the heavy rocks and is divided into two pieces 1210 a and 1210 b, as best seen in
If desired, the gap 1210 c can be covered with metal plates on those areas in front of and after the blade 1210 to reduce the risk of debris falling between the sections 1210 a and 1210 b. The two sections are driven by cam 1218, shown in
The vertical conveyor 1206 is located behind the vertical blade 1204 and is spaced a given distance D1 from the vertical blade 1204. D1 will be the thickness of the rock slice B that is cut by the rock saw, as shown in FIG. 14. The vertical conveyor 1206 is mounted on frame 1211, which is attached to frame 1202. The vertical conveyor 1206 can be moved closer to or away from the vertical blade 1204 at adjustment points 1212, 1213 as shown in
As shown in
The roller arms 1215 and 1216 have rollers 1221 rotatably mounted on arms 1215 and 1216. Arms 1215 have four rollers each. Arm 1216 only has rollers 1221 on the bottom side, as best shown in
Blade 1204 is water-cooled and cleaned with jets with water in a known manner and is therefore not shown. The water drains into trough 18 and is drained from there. In addition, final jets 1225, shown in
As mentioned above the speed of the conveyors in all embodiments is controlled automatically by the load on the saw motor 5, 500 and 1205. The flowcharts 600 a of
The wiring is connected to wires Z, which connect the control box to the relevant parts of the present invention. It is to be understood that the specific electronics disclosed were selected for the power of the present embodiment and are discussed for illustration only: No limitation should be inferred. If a larger or smaller saw were needed then different components may well be required. The layout of the control box 555 disclosed is for illustration only and no limitation should be inferred. There are many potential ways to layout the components of the control box 555 depending on the particular application. Various considerations could affect the layout of the control box 555, including, but not limited to, space, options available to operators vs. supervisors, cost of components, cultural layout preferences and other known human factor considerations.
As shown in
The safety cover 21 can be locked closed by an electromagnetic locking switch that is controlled by a power supply 508, and a lock release solenoid control relay 509. If the machine senses that the blade or blades are moving, it will not allow the lock to be opened. Only once the blades are no longer moving can the safety covers be opened. In addition, if the safety covers are not closed, the machine will not start the saw motors, as shown in box 607 of
The variable frequency drive (VFD) 513 is controlled by control relays 510, including a start forward control, a selector control relay, a manual feed select control relay, a run enable control relay and a jog reverse select control relay. The water solenoid can be controlled by control relay 511. The saw motor is started with starter 512, which has an overload relay to sense if the saw motor is overloaded as shown by line 608 in
The saw motor 5, 500 and 1205, the variable frequency drive 513 and the control power transformer (not shown) are provided with separate fuses, 514, 515, and 516 respectively.
One possible control panel C is shown in
The manual operations are shown in box 601 of
In the manual mode the speed of the conveyors in either forward or reverse is not controlled by the load on the saw motor, the conveyors are run at one continuous speed.
The conveyors can be run in reverse in the manual mode, this is provided to allow the operator to clear a jam or any debris out of the path of the blade. The conveyors can be set to run continuously in reverse by switching conveyor direction switch 1107 to reverse if one is provided. The conveyors can also be temporarily run in reverse by holding down conveyor jog button 1110, in which case the conveyors will run in reverse as long as the button 1110 is held down, as indicated on flowcharts 600 by box 613.
In some operation conditions, it may be desirable to not allow manual forward operation, but only reverse operation to clear jams. In some cases the operators may try to clear to a jam by manually running the saw forward, instead of reversing the saw to pull the blockage. This is particularly likely if the jam occurs near the end of a cutting operation for a particular rock A. Running the saw forward to try clear a jam can cause significant motor or blade wear. Therefore, in some operating conditions it may be desirable to either not have a forward manual mode, shown in
The automatic run is started by pressing the power on button 1101, as indicated at box 602 and ensuring that selector switch 1104 is set to automatic as indicated in box 610. Next the automatic start button 1111 is pushed, box 618 and the machine checks the status of the necessary machinery as shown in box 603. The machine, as shown in box 607 in
The automatic start button 1111 being pressed starts the saw motor timer, box 620
In the embodiment shown in
The conveyors are then moved forward at a rate of speed inversely proportional to the load on the saw motor, box 604 all, controlled by the conveyor variable speed-drive 513. A 50 Amp maximum current sensor 504 determines the saw motor load and sends it to a 4–20 milliAmp current loop output device which sends the saw motor load current to the PLC analog input. A PLC analog output card, 4–20 milliAmp current loop to the variable frequency drive 513 is the current loop speed control input.
There is a range of operational conditions set for the saw motor and the conveyors, boxes 604 a, 604 b and 604 c, which will be determined by the exact equipment used and the material to be cut by the saw. Normally, these operational conditions will be set into the machine and are not easily variable. However, if desired, a programmable capability could be built into the present invention to allow the operator to set the operating conditions. This might be particularly advantageous in a large embodiment of the present invention that might be cutting a wide variety of materials and a wide range of sizes and thicknesses of material.
The speed of the conveyor is controlled in the disclosed embodiment on a mathematical curve relating to the motor load, as shown in box 628 in
The PLC program uses a “Scale” instruction to produce a certain output to the VFD speed control determined by the saw motor load. The Rate is −15022 and the offset is 25450, which is the slope of the saw motor load vs. the VFD speed. The −15022 (Rate) is the result of the range of the input divided by the range of the output (11750−5020)/(9120−13600)=6730/−4480=−1.5022 and is multiplied by 1000. These values are in engineering units, and represent the actual milliAmp input and output (times 1000). The 11750 represents the maximum current to send to the VFD for the desired maximum speed set point of 30 hertz. The 5020 is the minimum current to send to the VFD for the desired minimum (except for 0) speed of 4 hertz. The 9120 represents the minimum saw motor load current of 16 amps at which it is desirable to start decreasing the speed of the conveyor. The 13600 is the maximum saw motor load current of 30 amps at which the conveyor feed reduced to a minimum until the load decreases again. The negative Rate means that as one parameter goes up, the controlled parameter goes down, an inverse relationship.
The 25450 (Offset) is the scaled minimum (minimum speed current output)−input minimum (minimum saw load current)×slope (Rate figured above) as shown in box 628.
Box 604 c of
When the hardness is set to soft line 641 if the saw motor load sensed is greater than or equal to 16 Amps, then the VDF is set to 30 Hz box 643. As shown in box 644, if the saw motor load sensed is greater than 16 Amps the speed is set using the algorithm in box 628. If the load is less than 24 Amps, then the speed is increased from its last value by 2 Hz until the saw load approaches 24 Hz. If the load is greater than 24 Amps then control returns to box 643.
When the hardness is set to hard, if the saw motor load is less than or equal to 16 Amps, then the VDF is set to 10 Hz box 646. As shown in box 647, if the saw load is greater than 16 Amps, but less than 30 Amps, then the speed is set using the algorithm in box 628. However, the speed is never set less than 10 Hz box 648. If the saw load is less than 24 Amps then the speed in increased by 1 Hz until the saw load approaches 24 Amps. If the load is greater than 24 Amps, then control returns to box 628.
In an alternate embodiment of the present invention shown in
All of the examples of motor load and VDF and the exact conversion algorithm are given using the values for the currently used motors and drives and are given for demonstrative purposes and are provide by way of example and not of limitation. The values and algorithm could differ for different equipment and different material to be cut.
When rock A contacts the blade 4, as seen in
If the motor current was less than 40-amps for 1.5 second or 30-amps for 10 seconds box 605 operation transfers to box 640. Operation resumes with calculating a new feed speed using equation 1550 in box 628. If current was greater than 40-amps for 1.5 second or 30-amps for 10 seconds then operation stops box 605 requiring a operator to clear the fault and restart the machine.
If speed calculation 1551 requests a speed increase, an additional 2-Hz offset is added for new transfer function 1552 line 1512. If new speed calculation 1551 requests no speed increase, the last speed is used. This continues until the nominal set current 1524 is exceeded in decision box 652 (
If the hard material is selected, line 642, operation is the same as taught for soft above except for the following changes: Low current maximum drive frequency/speed 1522 is ⅓ of 1502 (30 Hz) or 10 Hz. Adaptation offset frequency 1531 is 1 Hz. Hard material transfer function 1560 has a gain of −3/7 Amps/Hz and 118/7 and Hz offset.
The actual motor currents and feed speeds are offered by way of example and not limitation. Values are offered by way of example taught are a function of the specific machine capacity, gear-box ratios and types of materials being cut. Algorithm 604 may be replaced with a dedicated PID (proportional integral derivative) controller if higher performance is required. A controller such as the Gefran model 2301 made by Gefran ISI Inc. of 8 Lowell Ave. Winchester, Mass. 01890 USA is offered by way of example. This way the system continuously servos to the nominal current thereby adapting to material size or hardness variations. Reduces stress on feed drive components, increases cutter life and smother operation. Fast acting over current fault protection increases machine safety. The fast acting servo taught above automatically reduces feed rates, reducing the chances for a catastrophic fault. A two material selector is offered by way of example and not limitation. The simple two material switch may be replaced with continuous controls for nominal current set point 1524, minimum current 1516, maximum speed 1522 and offset 1531 parameters.
Although the present invention has been described with reference to disclosed embodiments, numerous modifications and variations can be made and still the result will come within the scope of the disclosure. No limitation with respect to the specific embodiments disclosed herein is intended or should be inferred. Each apparatus embodiment described herein has numerous equivalents.
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|U.S. Classification||451/5, 125/13.01|
|International Classification||B28D1/04, B24B49/16|
|Cooperative Classification||B28D1/046, B24B27/06, B23D59/001, B28D7/04, B28D7/005, B24B49/16, B23D47/045|
|European Classification||B28D7/04, B24B27/06, B28D1/04F, B28D7/00B, B23D59/00B, B24B49/16, B23D47/04C|
|Jan 26, 2006||AS||Assignment|
Owner name: ROBINSON BRICK COMPANY, COLORADO
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TRIPLETT, KEVIN R;ERICKSON, STEVEN J.;ADAMSON, MARK C.;AND OTHERS;REEL/FRAME:017068/0360;SIGNING DATES FROM 20030728 TO 20030731
|Jun 5, 2008||AS||Assignment|
Owner name: GENERAL SHALE, TENNESSEE
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:ROBINSON BRICK COMPANY;REEL/FRAME:021050/0069
Effective date: 20080604
|Feb 10, 2009||AS||Assignment|
Owner name: PARK INDUSTRIES, INC., MINNESOTA
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:GENERAL SHALE;REEL/FRAME:022235/0722
Effective date: 20080623
|Mar 23, 2010||FPAY||Fee payment|
Year of fee payment: 4
|Mar 26, 2014||FPAY||Fee payment|
Year of fee payment: 8