|Publication number||USRE36023 E|
|Application number||US 08/454,520|
|Publication date||Jan 5, 1999|
|Filing date||Mar 30, 1995|
|Priority date||Apr 28, 1989|
|Also published as||US5108040|
|Publication number||08454520, 454520, US RE36023 E, US RE36023E, US-E-RE36023, USRE36023 E, USRE36023E|
|Inventors||Larry E. Koenig|
|Original Assignee||Koenig; Larry E.|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (17), Referenced by (11), Classifications (9), Legal Events (2)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This is a . .continuation.!. .Iadd.CONTINUATION .Iaddend.. .application.!. of . .co-pending.!. application Ser. No. . .345,157,.!. .Iadd.08/053,142, .Iaddend.filed Apr. . .8, 1989.!. .Iadd.27, 1993, and .Iaddend.now abandoned, .Iadd.which is a reissue of application Ser. No. 07/576,091, filed Aug. 28, 1990, and now U.S. Pat. No. 5,108,040, which in turn is a continuation of application Ser. No. 07/345,157, filed Apr. 28, 1989, and now abandoned.Iaddend..
The present invention relates to auger shredding devices and, more particularly, to auger shredding devices utilizing a tapered screw in a side discharge grinding chamber.
In order to crush and shred large, rigid objects such as wooden pallets, crates, utility poles, railroad ties, 55-gallon oil drums of concrete and the like, it is necessary to utilize a heavy duty device which typically includes one or more rotating augers within a grinding chamber shaped to conform to the auger flight. An example of such device is disclosed in Koenig U.S. Pat. No. 4,253,615. That device includes a grinding chamber within which is rotatably mounted a single auger having a cylindrical shaft and a tapered flight. The front wall of the chamber includes a centrally-located discharge opening which is coaxial with the rotational axis of the auger and the top of the grinding chamber is open to receive material to be crushed and shredded.
In operation, material deposited into the grinding chamber is pulled downwardly by teeth projecting from the periphery or the auger night and is crushed and shredded by the interaction of the auger flight with the grinding chamber walls, as well as meshing action of the auger teeth with breaker bars mounted on the grinding chamber walls.
Since the auger flight is tapered and is supported on a cylindrical shaft, the volume defined by the auger flight and outer shaft surface--the pumping volume--decreases along the length of the auger to the discharge opening. Accordingly, material which is crushed and shredded is at the same time compressed as it progresses along the grinding chamber to the discharge opening.
A similar device is disclosed in Worthington U.S. Pat. No. 4,227,849. That device is a garbage compactor which is attachable to a garbage truck and includes a conical chamber which houses a powered auger having a cylindrical shaft and a tapered flight. The auger projects the length of the housing and extends outwardly beyond the discharge opening.
The top of the housing is open to receive residential refuse and the refuse is broken up and compressed as it is pumped by the rotating auger along the housing. With both the Worthington and Koenig devices, material is compressed by a tapered auger as it is pumped along the grinding chamber or housing to a discharge opening.
A disadvantage with these designs is that the compression of pumped material may, in some instances, cause jamming of the auger. In addition, a buildup of material at the front wall may result from the overcompression of material by the tapered flight, causing clogging of the discharge opening.
Another disadvantage of the aforementioned devices is that material often jams behind the first turn of the auger flight. The space beneath the first turn of the auger flight typically forms a wedge-shaped void with a disc-shaped auger mounting plate or rear wall of the grinding chamber which supports the auger shaft. When material is fed downwardly into the grinding chamber and is broken up, there is a tendency for material to enter that wedge-shaped void and build up. Accordingly, it is necessary to stop rotation of the auger and remove material from the space.
Another disadvantage with present designs is that torque transmitted from the auger motor to the auger flights must pass substantially entirely through the auger shaft, which places a strain on the weldments or other connections between the shaft and flight. With large diameter flights, a large shear stress is placed on the connection between the flight and shaft, resulting in failure of the weldment or connection in high torque operating situations. One solution to this problem is to increase the diameter of the shaft. However, such a solution is costly, greatly adds to the overall weight of the device, and reduces the volume of usable space within a grinding chamber of given dimensions.
Accordingly, there is a need for an auger shredder which provides an even and consistent flow of material along the grinding chamber to the discharge opening. There is also a need for an auger shredder in which the auger is capable of withstanding high torque loads with a minimum shaft diameter.
The present invention is an auger shredder which is capable of crushing and shredding large scale items such as wood pallets, wood crates, railroad ties, utility poles, washing machines and the like, and includes an auger which is capable of pumping the crushed and shredded material in an even and consistent manner to a discharge opening. The auger shredder includes a frame defining a grinding chamber having a front wall with a centrally-located discharge opening, and an auger, rotatably mounted on a rear wall, which includes a flighted shaft extending the length of the grinding chamber and into the discharge opening.
In a preferred embodiment, the flight is tapered from the base to the tip of the shaft, and the shaft is correspondingly tapered so that the pumping volume defined by the shaft and flight is substantially constant along the length of the grinding chamber. As a result, the compression that normally occurs with tapered augers is greatly reduced, which results in a more even and consistent flow of crushed and shredded material to the discharge opening.
The auger shredder includes an extrusion tube which extends outwardly from the front wall and communicates with the discharge opening. An outer segment of the auger extends into the extrusion tube and the pumping volume defined by the flights and shaft of that outer segment is reduced from the pumping volume of the remainder of the auger. As a result, once material has entered the extrusion tube, it is compressed at a greater rate and forms a plug of material within the extrusion tube. This plug of material is acted upon by the leading edge of the auger flight, which further reduces the particle size of the crushed and shredded material.
Also in the preferred embodiment, the auger includes a disc-shaped base plate which is driven by a hydraulic motor and supports the auger shaft, and a torque transmission collar which extends from the base plate to the underside of the first flight of the auger. To obtain the greatest mechanical advantage, the torque transmission collar is spaced from the axis of rotation a maximum distance so that it is adjacent to the periphery of the base plate. The collar is made sufficiently strong such that torsional forces exceeding one percent and not more than approximately 15 percent of the total load are transmitted from the base plate to the auger. As a result of this design, the auger shaft can be reduced in diameter, which provides more room within a given grinding chamber, and reduces the buildup of material beneath the first turn of the auger flight.
Accordingly, it is an object of the present invention to provide an auger shredder for shredding and crushing large, rigid objects in a smooth and efficient manner and preventing a buildup of material on the front wall of the grinding chamber surrounding the discharge opening: an auger shredder in which the pumping volume is maintained substantially constant along the length of the auger through the grinding chamber; an auger shredder in which the pumping volume is decreased within an extrusion tube to compress and reduce particles further; an auger shredder which can withstand high torsional loads and shear stresses with a relatively small diameter shaft; and an auger shredder which requires relatively low maintenance and is relatively simple to construct.
Other objects and advantages will be apparent from the following description, the accompanying drawings and the appended claims.
FIG. 1 is a side elevation, partially broken away, of a preferred embodiment of the tapered auger shredder of the present invention;
FIG. 2 is a side elevation of the tapered auger of the auger shredder of FIG. 1;
FIG. 3 is a side elevation in section of the tapered auger of FIG. 2; and
FIG. 4 is an end elevation in section of the tapered auger, taken at line 4--4 of FIG. 3.
As shown in FIG. 1, the tapered auger shredder of the present invention includes a frame, generally designated 10, which defines a grinding chamber 12 and motor housing 14. The grinding chamber 12 includes rear wall 16, front wall 18 and downwardly converging side walls 20 (only one of which is shown in FIG. 1). The side walls 20 include arcuate portions which meet to form a semicircular trough 22. The front wall 18 includes a centrally-positioned discharge opening 24 and the trough 22 is sloped upwardly from the rear wall to the discharge opening. The top of the grinding chamber is open and a hopper extension 26 is attached to the frame 10 to surround the grinding chamber opening 28.
An extrusion tube 30 is mounted on the exterior surface of the front wall 18. The extrusion tube 30 includes a conical segment 32, which communicates with the discharge opening 24, and a cylindrical segment 34 which extends outwardly from the conical segment.
An auger screw, generally designated 36, is rotatably mounted within the grinding chamber 12 on the rear wall 16. The auger screw includes a shaft 38, a flight 40 supported on the shaft and a disc-shaped base plate 42. A hydraulic drive motor 44 is mounted on the rear surface of the rear wall 16 and rotates the auger 36. A source of high pressure hydraulic fluid (not shown) is also contained within the motor housing, along with an appropriate power control system (also not shown). An example of an appropriate power control system and source of pressurized hydraulic fluid is disclosed in Koenig U.S. Pat. No. 4,253,615, hereby incorporated by reference.
As shown in FIGS. 2, 3 and 4, the shaft 38 of the auger screw 36 includes three components: a base portion 46, an intermediate conical portion 48 and an outer cylindrical portion 50. The base portion 46 extends through an opening 52 formed in the center of the base plate 42 and is secured thereto by welding. The base plate 42 includes a plurality of bolt holes 54 which receive bolts (not shown) for mounting the auger to a bearing disc (not shown) driven by the motor 44.
The flight 40 extends along the length of the shaft 38 and includes a plurality of radially projecting teeth 56 which extend outwardly from and are spaced along the outer periphery 58 of the flight. As shown in FIG. 1, the trough 22 includes a plurality of breaker bars 60 which extend inwardly from the trough and are spaced along the length of the trough to mesh with the teeth 56. Also shown in FIG. 1, the outer cylindrical portion 50 of the shaft 38 includes a segment 62 which extends into the extrusion tube 30.
The diameter of the flight 40 is tapered such that the volumes A, A', A" defined by the turns of the flight and portions of the shaft 38 associated with those turns (see FIG. 3) are substantially equal to each other along the length of the auger screw 36 within the grinding chamber 12. Thus, as the auger screw 36 is rotated by the motor 44, the pumping volumes A, A', A" of the flight 40 pump a substantially constant volume along the grinding chamber 20 to the discharge opening 24.
The segment 62 of the outer cylindrical portion 50 defines pumping volumes B, B', B" with the associated portion of the flight 40 which is reduced from the pumping volumes A, A', A" for the remainder of the auger screw 36. Consequently, once material has entered the extrusion tube 30, it is further compressed and shredded. Additional shredding is effected by action of the leading edge 63 of flight 40.
It should be noted that it is within the scope of the invention to provide a shaft 38 which is continuously tapered from the base plate 42 to the outer segment 62. However, the construction shown in the figures is preferred since it is less expensive to fabricate.
In an alternate embodiment, the intermediate portion 48 is sized to form a volumes A', A" which are progressively less than the volume A so that a volume reduction on the order or 2:1 to 4:1 occurs along the length of the grinding chamber 12. In addition, volumes B, and B" decrease at a greater ratio, by virtue of the cylindrical outer portion 50 combined with the associated portion of the flight 40. As shown in FIG. 1, this increased rate of reduction occurs substantially entirely in the extrusion tube 30.
As a result of adding the cylindrical outer portion 50 to the auger 36, the rate of compression can be increased in the extrusion tube 30 while maintaining a relatively low rate of compression in the grinding chamber 12. This not only prevents build up of material on the front wall but allows the grinding chamber to be made longer to accept larger objects to be shredded.
The auger screw 36 also includes a torque transmission collar 64 which extends between the base plate 42 and the rear surface 66 of the first turn 68 of the flight 40 (see FIGS. 2, 3 and 4). The torque transmission collar 64 is substantially cylindrical in shape and is dimensioned to contact the base plate 42 as close to the periphery of the base plate as possible.
As shown in FIG. 4, the collar 64 extends around substantially the entire periphery of the first flight 68. In a preferred embodiment, the collar 64 extends approximately 315° about the circumference of the first flight 68. The collar 64 is made up of two components: a first component 70 which extends semi-circumferentially about the first flight, and a second component 72 which has a reduced radius of curvature and curves inwardly to be attached to the shaft 38 along a longitudinal edge 74.
While the specific dimensions--such as thickness and diameter--will vary with respect to the diameters of the shaft and flight of the auger on which it is mounted, the collar must be sized to absorb more than one percent to approximately 15 percent of the overturning moment load transmitted to the auger 36 from the base plate 42, and more than one percent to approximately 20 percent of the torquional shock load transmitted to the auger from the base plate. If the collar 64 is sized to transmit less than the aforementioned values, there is a significant likelihood that, under high torque loads, the collar will shear from the base plate and/or first flight and, in severe situations, allow the shaft 38 to shear from the base plate or snap in two.
The operation of the tapered auger shredder is as follows. Prior to depositing material within the grinding chamber 12, the motor 44 is activated to begin rotation of the screw 36. The device shown in the figures is designed to operate at low speeds, preferably in the range of 1 to 30 revolutions per minute. Once the desired rotating speed of the auger 36 has been reached, material is dumped downwardly through the hopper extension 26 and into the grinding chamber 12. There, the material, which may be large, rigid objects such as pallets or 55 gallon oil drums of hardened material, is grabbed by the teeth 56 and pulled downwardly between the auger 36 and the side wall 20, where the material is crushed and shredded by the action of the screw flight 40 and the meshing of the teeth 56 with breaker bars 60.
The shredded material is pumped along the length of the grinding chamber by the flight 40 and, while there is some compression of material due to the tapered flight, this compression is minimized as a result of the constant pumping volume along the length of the grinding chamber. Once the material has progressed along the grinding chamber, it has been shredded and crushed sufficiently to enter the extrusion tube 30 where, as a result of the decreased pumping volume, it is compressed further and forms a plug 76 (FIG. 1) in the cylindrical segment of the tube. This plug of material is further reduced in particulate size by the shearing action of the leading edge 63 of the flight 40 as it rotates against the rear face of the plug. As a result of the constant pumping volume along the length of the grinding chamber 12, material is caused to flow more consistently, which reduces the likelihood of jamming or build up at the front wall 18, and requires less input energy by the motor 44.
The collar 64 provides a shield for the underside 66 of the first flight 68, thereby preventing jamming of material in the wedge-shaped void formed between the first flight and the base plate 42 and rear wall 16. Additionally, the collar 64 transmits torque to the first flight and shaft from the base plate 42, thereby reducing the stresses imparted to the base portion 46 of the shaft 38 by the base plate.
While the forms of apparatus herein described constitute preferred embodiments of this invention, it is to be understood that the invention is not limited to these precise forms of apparatus, and that changes may be made therein without departing from the scope of the invention.
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|US8708266||Jan 17, 2011||Apr 29, 2014||Mark E. Koenig||System for crushing with screw porition that increases in diameter|
|US8720330||Jul 29, 2010||May 13, 2014||Larry E. Koenig||System and method for adjusting and cooling a densifier|
|US8720805||Jul 29, 2010||May 13, 2014||Larry E. Koenig||System and method for cooling a densifier|
|US8726804||Jul 29, 2010||May 20, 2014||Larry E. Koenig||System and method for adjusting and cooling a densifier|
|US8851409||Oct 21, 2011||Oct 7, 2014||Mark E. Koenig||System for crushing|
|US9032871||Jul 29, 2010||May 19, 2015||Larry E. Koenig||System and method for adjusting and cooling a densifier|
|US9132968||Nov 2, 2012||Sep 15, 2015||Mark E. Koenig||Cantilevered screw assembly|
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|U.S. Classification||241/260.1, 175/394, 100/145|
|International Classification||B02C19/22, B30B11/24|
|Cooperative Classification||B02C19/22, B30B11/246|
|European Classification||B30B11/24E, B02C19/22|
|Sep 20, 1999||FPAY||Fee payment|
Year of fee payment: 8
|Apr 28, 2003||FPAY||Fee payment|
Year of fee payment: 12