Patent Grant
9999891
The invention relates to the field of reducing machines and in particular pulverizing machines. More particularly, the present invention relates to rotating discs and disc mill assemblies for use in such machines.
In the past, reducing machines, including pulverizing systems, have used disc mill assemblies to grind, shred or pulverize various types of materials such as plastics, nylons, polyesters and other polymers into powder, amongst other industrial applications. Typically, reducing machines have cooperating cutting discs having opposed cutting surfaces. Typically, one cutting disc is stationary, often referred to as the stationary disc, and one cutting disc is rotating, often referred to as the rotating disc. Input material to be reduced passes between the cutting surfaces of the discs radially from the centre to the circumference by virtue of centrifugal force, often assisted by a vacuum created by a fan forming a part of the reducing machine.
A major problem with reducing machines in general is the management of heat. As the input material is ground, shredded or pulverized by the relative rotation of the cutting discs, heat is generated and must be dissipated to avoid damage to the discs as well as potentially melting or degrading of the input materials. To facilitate cooling of the disc assembly, prior art reducing machines have generally utilized a water cooling system, including a water jacket assembly, for cooling the stationary disc as disclosed for instance in U.S. Pat. No. 8,282,031 B2 to Sly. The water jacket cooling assembly would permit water, or another liquid, to be circulated on the non-cutting surface of the stationary reducing disc to dissipate heat generated by the cutting surfaces of the disc assembly, and in particular the stationary disc when it is in facing operative relation the rotating disc arranged.
However, water jacket assemblies can be rather expensive to design, build and maintain, thereby increasing the cost of the overall machine. Also, water jackets leak regularly thereby causing rusting of the disc assembly, and/or contaminate the input material being reduced.
A further difficulty with water cooling of the stationary disc is that, invariably, the temperature of the stationary disc near the water inlet will be lower than the temperature of the stationary disc at a location remote from the water inlet due to the fact that the water will absorb heat while it is circulating and in thermal contact with the stationary disc. This can cause temperature variations and thermal imbalances in the stationary disc which can cause structural stress.
Furthermore, if the operators of the reducing machines are not careful and turn on the water cooling system when the stationary disc has been operating for some time and is at an elevated temperature, the stationary disc could experience “thermal shock” from a sudden temperature decrease. This often results in damage to the stationary disc and, in some cases, a catastrophic failure of the stationary disc.
Furthermore, because of the risk of “thermal shock” and other damage that could be caused by water cooling, the material used for the cutting discs, and in particular the stationary disc, would need to be selected such as to decrease the possibility of such “thermal shock” for safety purposes. In particular, the material of the stationary disc would need to be of a softer material to decrease the possibility of cracking.
A further disadvantage of the prior reducing machines is that considerable time is required in which to initially heat up the reducing machine prior to use. Typically, the reduced material generated while the reducing machine is warming up, is often called “off-spec” or “off specification” reduced material, and is usually discarded or blended back with the input material for further processing. At present, many prior art reducing machines are run with material for about 20 to 30 minutes in order to heat the reducing machine prior to producing useful reduced material. During the initial heating process, raw material is inserted into the machine and then the resulting off-spec material is discarded. Throughout the initial heating process, the stationary disc must be continuously cooled using the water cooling system, otherwise thermal shock could arise if the water cooling is suddenly commenced after the reducing machine, including the stationary disc, has been heated to an operating temperature. Because of this, the water cooling acts against the initial heating of the reducing machine thereby lengthening the amount of time required in order to heat the reducing machine to a useable temperature and generating additional off-spec material that is generally discarded or blended back with the input material. This also increases the wear and tear of the mill assembly as a whole because it must be operated for a longer period of time to heat the reducing machine.
Another disadvantage with prior art discs, and in particular rotating discs, is that cracks may develop, which could eventually lead to a failure, and eventually a catastrophic failure. While cracks may appear in both the stationary disc and the rotating disc, crack development and propagation are more common with rotating discs because of the increased stress caused by the rotation. Cracks can develop particularly near openings or orifices because of increased localized stress levels. Therefore, for safety concerns, it is important to decrease crack generation and propagation, particularly near openings or orifices in the rotating disc.
In addition, while rotating discs are cooled as a result of their rotation, this air cooling is often inefficient. This is the case, in part, because the rotating disc is often contained within a structural member, such as a carrying plate, which inherently insulates the rotating disc. In other cases, even if the rotating disc may be exposed to the air, the air is not efficiently channelled over the rotating disc. Furthermore, prior art devices may recirculate heated air within the disc chamber, decreasing cooling efficiency.
Furthermore, heat generation is a limiting factor of most reducing machines. Increased heat generation limits productivity and, conversely, increased heat dissipation increases productivity. Furthermore, increased heat generation limits the types of material which can be reduced.
Accordingly, the prior art reducing machines suffer from several disadvantages related to the manner in which the mill assembly, and in particular the stationary and rotating discs, are cooled. Furthermore, the method of cooling of the mill assembly, and in particular the stationary disc according to the prior art assembly, increases the cost of manufacture, assembly and operation and also restricts the nature of the material used for the discs.
Accordingly, it is an object of this invention to at least partially overcome some of the disadvantages of the prior art. In particular, an object of the invention to provide an improved type of rotating disc and stationary disc for use in mill assembly for a reducing machine, and in particular a pulverizing machine, with improved heat management.
Accordingly, in one of its aspects, the present invention resides in a disc mill assembly of a reducing apparatus, said disc mill assembly comprising: a stationary disc having a stationary cutting surface; a rotating disc having a rotating cutting surface on a first side for operative interaction with the stationary cutting surface of the opposed stationary disc, and, a second side having a rotating air cooling surface in thermal contact with the rotating cutting surface; a carrying plate having air inlets; an attaching mechanism for operatively attaching the rotating disc to the carrying plate with the rotating air cooling surface facing the air inlets and axially separated therefrom to permit air flow between said carrying plate and the rotating air cooling surface; wherein, during operation, the carrying plate and rotating disc rotate, and, air enters through the air inlets and passes between the carrying plate and the rotating air cooling surface, to cool the rotating disc.
In a further aspect, the present invention resides in a rotating disc for use in a disc mill assembly of a reducing machine, said rotating disc comprising: an annular rotating cutting surface for operative interaction with cutting surfaces of an opposed stationary disc; a solid centre support portion extending radially inwardly from the annular rotating cutting surface for supporting the annular rotating cutting surface; an attaching mechanism for attaching the rotating disc to a carrying plate, said attaching mechanism comprising an inner attaching mechanism located radially within the annular rotating cutting surface.
In a still further aspect, the present invention provides a carrying plate for carrying a rotating disc in a disc mill assembly, said rotating disc having a first side comprising a rotating cutting surface for operative interaction with a stationary cutting surface of an opposed stationary disc, and, a second side having a rotating air cooling surface in thermal contact with the rotating cutting surface, the carrying plate comprising: air inlets permitting air flow therethrough; an attaching mechanism for operatively attaching the rotating disc to the carrying plate with the rotating air cooling surface facing the air inlets and axially separated therefrom to permit air flow between the carrying plate and the rotating air cooling surface; wherein, during operation, the carrying plate and the rotating disc rotate, and air enters through the air inlets passes between the carrying plate and the rotating air cooling surface, to cool the rotating disc.
Accordingly, one advantage of the present invention is that the stationary disc is air cooled rather than water cooled. In this way, the risk of thermal shock is eliminated as air cooling is a less aggressive form of cooling than water cooling. Also, air cooling according to the present invention utilizes the vacuum created by a fan, or the fan of the reducing machine itself such that it is inherently active at all times that the machine is active. In this way, sudden temperature differences are avoided because air cooling is active whenever the fan is active. Furthermore, air cooling provides more uniform heat transfer rates over time and also over the surface of the stationary disc.
A further advantage of the present invention is that the rotating disc is air cooled directly, rather than indirectly, such as by air cooling the carrying plate or other structural elements. Moreover, the air is channelled across a rotating cooling surface on the opposite side of the rotating disc from the rotating cutting surface. This is accomplished, in one preferred embodiment, by having the rotating air cooling surface facing the air inlets in the carrying plate and axially separated therefrom. This increases the air flow near the rotating cooling surface during rotation of the rotating disc and carrying plate. In a further preferred embodiment, air passages are formed by backward curved support ribs at a location radially past the rotating air cooling surface to channel the air as the rotating disc and carrying plate rotate.
Furthermore, air cooling involves fewer component parts and, in particular, separate chilling and pumping units common with water cooling are not required. Rather, in a preferred embodiment, the vacuum generated by the fan of the reducing machine is used to cause airflow across the cooling surface of the stationary disc, and/or rotating disc thereby decreasing the costs of the overall machine and also the operation. Furthermore, because there is no water jacket and no corresponding connections to the water jacket that must be removed when the stationary disc is replaced, the replacement of this stationary disc becomes easier and less time consuming.
A further advantage of the present invention is that because thermal shock is of lessened concern, the material used for the discs in the mill assembly, and in particular the stationary disc, can be changed to improve performance and durability as safety concerns due to cracking are lessened. In particular, a harder material can be used, particularly for the stationary disc.
A further advantage of the present invention is that the stationary disc no longer needs to have a flat surface in contact with the water jacket for cooling. Rather, it is preferable if the cooling surface is ribbed or has fins to promote air cooling. Because of this, the shape of the side of the disc which is not operatively facing the rotating disc can be changed and need not be flat. In one preferred embodiment, the cooling surface comprises a plurality of radial ridges which are also sharpened and can act as a second cutting surface when the first cutting surface becomes dull. In this way, the stationary disc can have two operational cutting surfaces for use at different times. In this way, the ridges of the cutting surfaces can perform the dual purpose of acting as a heat sink, when they are facing the air inlets for the housing and not facing the cutting surface of the rotating disc, and, can act as a cutting surface when facing the cutting surface of the rotating disc.
A further advantage of the present invention is that the rotating disc can also be made to have rotating cutting surfaces on either side similar to the preferred embodiment of the stationary disc. In this way, the rotating disc and the stationary disc can effectively double the service life of the discs used in the disc mill assembly as compared to discs having cutting surfaces on only a single side of the stationary disc and rotating disc. In addition, in the embodiment where the rotating disc has a radial flange for attaching radially to a carrying plate, the rotating disc and stationary disc can be substantially identical, decreasing manufacturing, storage and shipping costs.
A further advantage, in another embodiment, is that the rotating disc can be made of a substantially continuous solid disc and without a center orifice. This can decrease structural stresses on the rotating disc by eliminating the center orifice and the resulting stresses. Rather, having a central support portion creating a substantially continuously rotating disc can decrease cracking and failure of the rotating disc. Furthermore, the central portion can have a thickness which is less than the thickness along the cutting surface to decrease weight, the cost of manufacture and the associated shipping cost.
In a further preferred embodiment, the stationary disc and rotating disc are designed not to be resharpened. In this way, once the rotating disc and the stationary disc are used until the cutting surfaces on both sides are dull, they can be discarded. In this way, lighter material can be used for the stationary disc and rotating disc which also facilitates cooling of the stationary disc and rotating disc. Furthermore, using a lighter material decreases transportation costs and manufacturing cost of both the stationary disc and rotating disc. By effectively doubling the service life of each disc, there are financial and logistical benefits which arise from one disc being shipped and purchased, but used effectively two times.
Furthermore, because the weight of the rotating disc is considerably less, the centrifugal force that is generated by it also decreases, resulting in less stress on the disc and the wear and tear on the rotating disc assembly.
A further advantage of the present invention is that because the rotating disc has cutting surfaces on both sides, the rotating disc can be substantially symmetrical about the radial axis and the plane of rotation, whether or not the rotating disc has an orifice or supporting portion in the center. In this way, the rotating disc can be symmetric about the radial plane such that the centre of mass will lay on the axis or rotation. This decreases flexing of the rotating disc in either direction while it is rotating. Furthermore, the stationary disc is also preferably a symmetrical about the radial axis which facilitates the manufacturing process.
A further advantage of the present invention is that there are no cooling liquids such as water used within the reducing machine. In this way, the risk of contamination, as well as rusting, which have occurred with water leaking in the prior art water cooling systems, is avoided. The only components used in the cooling of the stationary disc according to preferred embodiments of the present invention is air, preferably drawn in through the same negative pressure caused by a fan or, in a preferred embodiment, the fan of the reducing machine itself.
A further advantage of the present invention is that the reducing machine can be initially heated to a useable temperature much more quickly. This is the case, at least because the air cooling of the stationary disc is less aggressive and does not interfere with the initial heating of the overall system. Thus, initial heating time can be reduced and the amount of off-spec material produced during the initial heating time can be lessened. Furthermore, the wear and tear on the entire reducing machine, including the rotating and stationary disc, is lessened because less material must be inputted during the initial heating stage.
A further advantage of the embodiment of the invention is that air flow over the stationary disc can be controlled to better manage the temperature of the reducing machine as a whole. This is particularly useful at the initial heating stage where heat is preferably retained in the system.
A further advantage of this embodiment of the invention is that air flow over the rotating disc can also be controlled to better manage the temperature of the reducing machine. Moreover, the air flow over the stationary disc and rotating disc can be independently controlled to better manage the temperature of each disc and the machine as a whole.
A further advantage of the present invention is that the design of the disc mill assembly permits cooler air to enter the disc chamber and also decreases recycling of hot air in the disc chamber. This facilitates cooling of the pulverized material exiting from between the discs and the disc assembly as a whole. In this way, pulverized material is less likely to agglomerate. Thus, a wider range of materials may be pulverized, such as nylon and polypropylene, which could melt after pulverizing and agglomerate into large masses if not kept below their melting temperature after pulverizing.
Further aspects of the invention will become apparent upon reading the following detailed description and drawings, which illustrate the invention and preferred embodiments of the invention.
In the drawings, which illustrate embodiments of the invention:
Preferred embodiments of the invention and its advantages can be understood by referring to the present drawings. In the present drawings, like numerals are used for like and corresponding parts of the accompanying drawings.
As shown in
The reducing machine 100 also comprises a motor 132 for rotating a rotating shaft 136 (shown in
The system 100 comprises a fan 150 which creates a negative air pressure in the duct 140 and causes air to flow along a path shown generally by the dashed arrow and identified generally by reference numeral 155. The reduced material (shown generally by reference numeral 11 in
The reduced material 11 entrained in the air flow 155 passes through the duct 140, the cyclone 142 into a separator 144. Generally, there is a filter (not shown) from the fan 150 exhaust to prevent reduced material 11 exiting to the environment. The separator 144 will direct the properly reduced material 11 to the “good” material chute 148 where it can be then used as required. Any reduced material 11 that has not been properly reduced is directed through the “oversized” material chute 146 and re-fed into the funnel 122 together with the input material 10 to be processed in the mill assembly 200. A controller, shown generally by reference numeral 160 controls the reducing machine 100 and may comprise sensors, such as temperature sensors (not shown) to sense the temperature of the reducing machine 100 at different locations.
As illustrated in
In operation, raw material 10 enters the mill assembly 200 through the funnel 122, the lower portion of which is illustrated in
Accordingly, in one preferred embodiment, the air cooling surface 321 preferably comprises a plurality of radially extending cooling ridges, shown generally by reference numeral 323. This facilitates air cooling of the stationary disc 300 and acts essentially as a heat sink as air flow 155 entering through the air inlets 235 passes between the housing 232 and the air cooling surface 321 to cool the stationary disc 300. Similarly, the cutting surface 311 on the first side 301 has cutting edges 312 which, when the stationary disc 300 is attached to the housing lid 232 in a first orientation, are arranged in facing operative interaction with the rotating cutting surface 511 of the opposed rotating disc 500 to reduce the input material 10.
Preferably, the air cooling surface 321 is in thermal contact with the stationary cutting surface 311. This can be accomplished, for instance, by having a material, generally a metal that is a thermal conductor to conduct heat generated by the cutting surface 311 to the cooling surface 321.
In the preferred embodiment where the stationary disc 300 is substantially symmetrical about the stationary radial plane SRP, the plurality of ridges on the air cooling surface 321 also comprises cutting edges 322. In this preferred embodiment, the cutting surface 311 has cutting edges 312, which are themselves oriented on a second plurality of radially extending cooling ridges 313. In this way, the disc 300 can be attached to the housing lid 232 in a second orientation with the first side 301 facing the housing lid 232 and the second side 302 facing the rotating disc 500 to reduce input material 10. In the further preferred embodiment, as illustrated in
As also illustrated in
As illustrated in the exploded perspective view of
In a further preferred embodiment, the attaching ribs 440 extend from the interior surface of the lid housing 232 the same predetermined distance PD as the supporting ribs 233. In this way, the supporting ribs 233 and the attaching ribs 440 support the stationary disc 300 a predetermined distance from the interior surface 242 of the housing lid 232 to permit the air to flow from the air inlets 235 over the air cooling surface 321, between the gaps 239 of the support ribs 233, and where present between the attaching rib 440 and the support rib 233, to form an air channel 245 from the air inlet 235 to the duct 140. The support ribs 233 thereby form gaps or air passages 239 for the passage of air from the stationary air inlets 235.
In a preferred embodiment, where the stationary disc 300 is substantially symmetrical about the radial plane SRP, once the cutting edges 313 on the cutting surface 311 are dulled, the stationary disc 300 can be removed from the housing lid 232. In a preferred embodiment, the attaching mechanism 430 operatively releasably attaches the stationary disc 300 to the lid housing 232 in the first orientation with the cutting surface facing 311 the rotating disc 500 and can then re-attach the stationary disc 300 in a second orientation with the cooling surface 321 facing the rotating disc 500. In this preferred embodiment, as indicated above, the cooling surface 321 will have cutting edges 323 on the plurality of cooling ridges 322 such that the cooling surface 321 can act as a second cutting surface 311′. Similarly, the cutting surface 311 will have a plurality of cooling ridges 312 upon which the cutting edges 313 are oriented, such that the cutting surface 311 can also act as a second cooling surface 321′. In this way, the longevity of the stationary disc 300 can be effectively doubled. In a further preferred embodiment, the stationary disc 300 has a relatively thin thickness, such that once the cutting edges 313 on the cutting surface 311 and the cutting edges 323 or the cooling surface 321 are dulled, the stationary disc 300 can simply be discarded and a new disc 300 can be operatively attached to the housing lid 232 for continued use in the milling assembly 200.
Furthermore, as also illustrated in
Similar to the stationary disc 300, the rotating disc 500 can be attached to the carrying plate 540 and then fixed to the rotating shaft 136 in a first orientation, where the first cutting surface 511 is facing the stationary disc 300 to reduce input material 10. This would be the case, for instance, when the first side 501 is facing away from the carrying plate 540. In this first orientation, the first cutting surface 511 can interact with the corresponding cutting surface 311 of the stationary disc 300 to reduce input material 10. Once the first rotating cutting surface 511 is no longer functional for reducing input material 10, such as if the edges 513 have become dull, the rotating disc 500 can be detached from the carrying plate 540 and re-attached in a second orientation, with the second rotating cutting surface 521 facing the stationary disc 300 to reduce input material 10. In this way, the effective useful life of the rotating cutting disc 500 can be doubled. Preferably, the rotating disc 500 and the stationary disc 300 are changed from their respective first orientation to their respective second orientation, at the same time, to minimize maintenance time.
As with the stationary disc 300, the rotating disc 500 has cooling ridges 513, 523 on each sides 501, 502. In this way, the cutting edges 512, 522 are oriented on the cooling ridges 513, 523. Furthermore, the rotation of the rotating disc 500 cause air to flow over the surface 511, 521 which is not operatively facing the stationary disc 300, and the ridges 513, 523 facilitate cooling of the rotating disc 500. In this way, the side 501, 502 facing away from the stationary disc 500 acts as the rotating cooling surface 521 and the side 502, 501 facing the stationary disc 300 acts as the rotating cutting surface 511.
As with the stationary disc 300, in a preferred embodiment, the rotating disc 500 has a relatively thin thickness, such that once the cutting edges 511, 521 are dulled, the rotating disc 500 can be simply discarded. A further advantage of having a relatively thin rotating disc 500 is that the weight of the rotating disc can be reduced, decreasing the transportation cost of the rotating disc 500, as well as, decreasing the thrust load on the bearing block 238 and the associate wear and tear, and also will be easier to cool because of its lower mass.
A further advantage of the preferred embodiment, where the rotating disc 500 is substantially symmetrical about the central radial disc radial plane RRP, is that the rotating disc 500 will also be substantially symmetrical about the plane of rotation of the rotating disc PRP as shown generally by the symbol PRP, and, substantially coincides with the dashed lines of the central radial disc radial plane RRP. This facilitates stability of the central rotating disc 500 as it rotates with respect to the stationary disc 300. Also, having the radial disc radial plane RRP substantially coincident with the plane of rotation of the rotating disc PRP when the rotating disc 500 is attached at rotating shaft 136, avoids flexing of the rotating disc 500 due to centrifugal force, which could be caused, for instance, if the radial disc 500 has a centre of mass which deviated from the plane of rotation of the rotating disc 500.
During initial operation, when the reducing machine 100 is cold and not yet warmed up to the optimal operating temperature, reducing material 10 will be inserted into the hopper 110 and reduced in order to initially heat or warm up the reducing machine 100. As indicated above, the fan 150 will draw air through the air inlets 235 and across the air cooling surface 321 of the stationary disc 300. As the air passes between the housing lid 232 and the air cooling surface 321, the air will absorb heat from the air cooling surface 321 that is generated from the cutting surface 311 of the stationary disc 300. This warmed air will then travel through the ducts 140 with the entrained reduced material 11 and facilitate warming the reducing machine 100 so that it may more quickly reach the optimal operating temperature to properly process input material 10. In this way, the air cooling surface 321 facilitates the initial warming of the reducing machine 100 thereby lessening the warm up time, the off-spec material prior to the system 100 reaching the optimal operating temperature and the corresponding wear and tear on the discs 300, 500. It is understood that in the preferred embodiment where the stationary disc 300 is substantially symmetrical about the stationary disc radial plane SRP, the same effect will arise if the stationary disc 300 is in the second orientation with the cutting surface 311 facing the air inlets 235 of the housing lid 232 and acting as the second stationary air cooling surface 321′.
As described above, in a preferred embodiment, the stationary disc 300, rotating disc 500 and mill assembly 200 are used in a reducing machine or system 100 which is preferably a pulverizing apparatus to reduce the input material 10 to essentially powder. It is understood, however, that the stationary disc 300, rotating disc 500 and milling machine 200 could be used in other types of reducing machines or systems 100 and are not necessarily restricted to pulverizing machines. It is also understood that in one embodiment, the air inlets 235 could be periodically closed or obstructed intentionally. This can be the case, for instance, to control the temperature of the mill assembly 200 and the reducing machine 100 as a whole. For instance, at the initial start up, one or more of the air inlets 235 could be blocked in order to decrease the air passing over the air cooling surface 321 of the stationary disc 300 to facilitate initial heating of the reducing machine 100.
In a further preferred embodiment, as illustrated in
Preferably, the air restricting device 700 comprises an air baffle as shown generally by reference numeral 710, which has a central orifice 712, which is coincident with the input orifice 204 to permit input material 10 to enter the mill assembly 200.
The air baffle 710 is in fluid communication with an air damper, as shown generally by reference numeral 720. The air damper 720 has a flange 722 or other type of air restricting member which has an open position, permitting air flow through the damper opening 723 of the damper 720, and a closed position restricting air flow through the damper opening 723 of the damper 720. Preferably, the air restricting device 700 comprises a mechanical control, such as a solenoid or stepper motor as shown generally by reference numeral 730, to control movement of the flange 722 from the open position to the closed or restricted position. In a preferred embodiment, the mechanical motor 730 can adjust the position of the flange 722 at a plurality of different angles to more precisely control the air flow 155 through the damper 720 and therefore through the air inlets 235.
In operation, when it is desired to raise the temperature of the reducing machine 100, the damper 720 is moved to the closed or restricted position to restrict the air flow 155 through the damper 720, the air baffle 710 and the air inlets 235. In this way, the air cooling effect of the air cooling surface 321 on the stationary disc 300 is limited as the air flow 155 across the air cooling surface 321 is decreased thereby preventing the dissipation of heat through convection across the plurality of radially extending cooling ridges 323. When the reducing machine 100 is at a desired temperature and further heating is not required, the damper 720 is moved to the open position permitting air flow 155 through the damper opening 723, through the air baffle 710 to the air inlets 235 and across air cooling surface 321 thereby facilitating cooling of the stationary disc 300. It is understood that because air is a less aggressive form of cooling compared to water or other liquids which have a higher heat capacity, opening the air damper 720 when the reducing machine 100 and, in particular, the stationary disc 300 is at an optimal temperature, will not damage or adversely affect the stationary disc 300.
In a further preferred embodiment, during initial start up, the air restricting device 700 restricts the flow of air through the air inlet 235. This can be accomplished in the preferred embodiment by moving the flange 722 to the closed position restricting air flow 155 through the damper 720. In this way, as input material 10 is passed through the reducing machine 100 during initial start up, the heat generated by the disc mill assembly 200 will be retained within the reducing machine 100 in order to facilitate initial heating at start up. Once the initial heating of the reducing machine 100 is completed and the reducing machine 100 is at the operating temperature, the air control device 700 will permit air flow 155 through the air inlets 235 to cool the stationary disc 300. Because the heat capacity of air is not as high as liquids, such as water, the stationary disc will not experience thermal shock when the air restricting device 700 permits air flow 155 through the air inlets 235 even if the stationary disc 300 and reducing machine 100 are at the operating temperature. In this way, preheating at initial start up, as well as the generation of off spec material and the corresponding wear and tear on the reducing machine 100, can be reduced. In a preferred embodiment the controller 160 will comprise temperature sensors (not shown) to sense the temperature of the reducing machine 100 at different locations. The controller 160 may then also automatically control the air restricting device 700 to permit air flow 155 through the air inlets 235 when initial heating of the reducing machine 100 is completed. For instance, the controller 160 may send a signal to the motor 730 to move the flange 722 permitting air flow through the damper 720 as the temperature of the reducing machine 100 approaches the optimal operating temperature.
As also illustrated in
The rotating air restricting device 1700 controls air flow to the rotating disc 1500. To accomplish this, air baffle member 1000 is shown fixed to the inside surface of the housing body 234 and is designed to direct air from the lower air inlets 237 to cool the rotating disc 1500 through rotating air inlets 835 in the carrying plate 840 discussed below. The air baffle member 1000 may have any shape to permit this function. In a preferred embodiment, the air baffle member 1000 is preferably an air baffle ring 1010 (shown in
The carrying plate 840 also preferably comprises an attaching mechanism, shown generally by reference numeral 930, for operatively attaching the rotating disc 1500 to the carrying plate 840. The rotating disc 1500 is preferably attached to the carrying plate 840 with the non-operating surface, also referred to as the rotating air cooling surface 1521, facing the air inlets 835 and axially separated therefrom to permit air flow from the air inlets 835, between the carrying plate 840 and the rotating air cooling surface 1521 of the rotating disc 1500.
The carrying plate 840 also preferably comprises air passages, shown generally by reference numeral 839, located between the rotating disc 1500 and the carrying plate 840. More preferably, the air passages 839 are located radially remotely from the air cooling surface 1521. In a further preferred embodiment, the air passages 839 are located along the outer perimeter of the carrying plate 840 and radially distant from the air inlets 835. In this way, as the carrying plate 840 and rotating disc 1500 attached thereto rotate in a rotating direction RD, air is channeled from the air inlets 835, between the carrying plate 840 and the rotating air cooling surface 1521, and through the plurality of air passages 839. The air path is shown by dashed lines and identified by reference numeral 1155. The centripetal force caused by the rotation of the carrying plate 840 and disc 1500, together with the vacuum caused by the fan 150, cause air to enter the air inlets 835 and flow along the air path 1155 and through the air passage 839. In a further preferred embodiment, the air passages 839 are angled backward from the direction of rotation RD of the carrying plate 840, as illustrated in
In a further preferred embodiment, a plurality of support ribs, shown generally by reference numeral 833, extend axially into the disc chamber 220, a predetermined distance PD from an inside surface 842 of the carrying plate 840. The plurality of support ribs 833 may form the plurality of air passages 839 therebetween. In this embodiment, the rotating disc 1500 may comprise a rotating flange 1503 which rests against the support ribs 833 when the disc 1500 is attached to the carrying plate 840. Preferably, the ribs 833 are arranged radially about the inside surface 842 at a radial position corresponding to the position of radial flange 1503 when the disc 1500 is attached to the carrying plate 840 so that the disc 1500 may be supported by the flange 1503 resting on the ribs 833. In this way, in a preferred embodiment, the ribs 833 and air passages 839 are located radially distant from the air inlets 835. This causes the air to be channelled along the air path 1155 radially outwardly from the air inlets 835, between the carrying plate 840 and the cooling surface 1521 of the rotating disc 1500 and through the air passages 839 to cool the disc 1500.
In a further preferred embodiment, the plurality of support ribs 833 are backward curved from a direction of rotation RD of the carrying plate 840 and rotating disc 1500, as shown in
As also illustrated in
In a further preferred embodiment, the attaching ribs 940 have a similar shape to the plurality of backward curved support ribs 933. In this preferred embodiment, the attaching ribs 940 and support ribs 933 may also be located at the same radial position on the carrying plate 840 and corresponding to the radial position of the radial flange 1503 when the rotating disc 1500 is attached to the carrying plate 840. In this way, the attaching ribs 940 perform a similar function to the support ribs 933, namely to form angled backward passages 839 in addition to operatively attaching the rotating disc 1500 to the carrying plate 840 with the rotating air cooling surface 1521 of the rotating disc 1500 separated from the inside surface 842 of the carrying plate 840 to assist in channelling the air therebetween. In this preferred embodiment, the support ribs 933 may be located between the attaching ribs 940. An air path according to this preferred embodiment is shown by dashed lines and identified by reference numeral 1155 in
In a further preferred embodiment, the air inlets 835 of the carrying plate 840 have a leading edge 835L in the rotating direction RD which forms an angle of incidence, illustrated generally by reference symbol a of
Returning to the continuous rotating disc 1500 illustrated in
As illustrated in
Accordingly, in one preferred embodiment, the rotating air cooling surface 1521 acts as a heat sink as air flow 1155 entering through the air inlets 835 passes between the carrying plate 840 and the rotating air cooling surface 1521. In a preferred embodiment, the rotating air cooling surface 1521 comprises a plurality of radially extending cooling ridges 1523 which facilitates cooling of the rotating disc 1500. Similarly, the cutting surface 1511 on the first side 1501 has cutting edges 1512 which, when the rotating disc 1500 is attached to the carrying plate 840 in a first orientation, are arranged in facing operative interaction with the stationary cutting surface 311 of the opposed stationary disc 300 to reduce the input material 10.
Preferably, the rotating air cooling surface 1521 is in thermal contact with the rotating cutting surface 1511. This can be accomplished, for instance, by having a material, generally a metal that is a relatively good thermal conductor in thermal contact with rotating cutting surface 1511 and the rotating air cooling surface 1521 to conduct heat generated by the rotating cutting surface 1511 to the rotating cooling surface 1521. In the further preferred embodiment, the rotating cooling surface 1500 is made of a continuous metal or metal alloy which has both relatively good thermal conducting characteristics to transfer or conduct heat, but also has the required degree of strength to perform the cutting action.
In a further preferred embodiment, the continuous rotating disc 1500 is substantially symmetrical about the continuous rotating radial plane CRRP, with the plurality of ridges 1523 on the air cooling surface 1521 also comprises cutting edges 1522. In this preferred embodiment, the rotating cutting surface 1511 has cutting edges 1512, which are themselves oriented on a second plurality of radially extending cooling ridges 1513. In this way, the rotating disc 1500 can be attached to the carrying plate 840 in a second orientation with the first side 1501 facing the carrying plate 840 and the second side 1502 facing the stationary disc 300 to reduce input material 10. In this further preferred embodiment, as illustrated in
Accordingly, in this preferred embodiment, in the second orientation, the plurality of cooling ridges 1523 have cutting edges 1522 which are arranged in facing operative interaction with the stationary cutting surface 311 of the opposed stationary disc 300 to reduce material 10. Similarly, the plurality of ridges 1513 of the first side 1501 face the carrying plate 840 and the air inlet 835 in the second orientation, such that air drawn through the air inlets 835 of the carrying plate 840 cross or pass over the plurality of ridges 1513 of the first side 1501, such that the first side 1501 then comprises rotating cooling surface 1521 to cool the rotating disc 1500 in the second orientation. Thus, the rotating disc 1500 can be re-oriented from the first orientation to the second orientation when the cutting edges 1512 of the rotating cutting surface 1511 become dull.
As indicated in
Nevertheless, the rotating disc 1500 with an orifice could still operate and in this case would have a shape and function similar to the stationary disc 300. As such, as also indicated above, a single type of disc 300 could be used for both the rotating and stationary disc 300. This could decrease the cost of manufacture, shipping and inventory because only a single type of disc 300 would be required.
However, when a continuous rotating disc 1500 is used, it is preferred that the solid or continuous center portion 1560 supports the annular rotating cutting surface 1511 for operative interaction with the cutting surface 311 of the opposed stationary disc 300. The center portion 1560 extends radially inwardly from the annular rotating cutting surface 1511 for supporting the annular rotating cutting surface 1511. It is also preferred if the solid center portion 1560 has a first thickness T1 which is less than the thickness T2 of the rotating cutting surface 1511 as shown in
As illustrated in
Accordingly, as indicated above, the rotating disc 1500, whether it has a center portion 1560 or a center orifice, can be attached. The rotating disc 1500 is preferably symmetrical about the continuous rotating disc radial plane CRRP and also symmetrical about the plane of rotation of the continuous rotating disc PCRP. As with the stationary disc 300, the rotating disc 1500 can preferably be attached to the carrying plate 840 in a first orientation or a second orientation, such that both sides of the substantially symmetrical disc 1500 can be used alternatively for cutting action and for cooling. The rotating disc 1500 has a cutting surface 1511 on the first side 1501, in the first orientation, for operative interaction with the stationary cutting surface 311, and, a second side 1502 having the rotating air cooling surface 1521 in thermal contact with the rotating cutting surface 1511, attached to the carrying plate 840 to permit in the mill housing 230 to engage the air inlets 835 and passes between the inside surface 842 of the carrying plate 840 and the cooling surface 1521 of the rotating disc 1500. The attaching mechanism 930 preferably operatively attaches the rotating disc 1500 to the carrying plate 840 and the rotating air cooling surface 1521. During operation, the carrying plate 840 and rotating disc 1500 rotate and air entering through the air inlets 835 pass between the carrying plate 840 and rotating air cooling surface 1521 to cool the rotating disc 1500.
It is understood that as discusses above, in a preferred embodiment the stationary disc 300 is also air cooled. It is understood that the air cooled stationary disc 300 and air cooled rotating disc 1500 of the present invention can operate together in the same mill assembly, as illustrated in
It is also understood that the housing lid 232 is part of the housing 230 to house the mill assembly 200. As indicated above, reference to housing lid 232 is understood to be a portion of the overall housing 200 and therefore it could be referred to as the housing 230 of the mill assembly 200. Also, the portion of the housing 230 to which the stationary disc 300 is attached, need not necessarily be the top portion, but rather the housing lid 232 may be any portion of the housing 230 to which the stationary disc 300 is attached. Similarly, the rotating disc 500 or 1500 need not be on the lower portion. Furthermore, the lower air inlets 237 need not be lower than the stationary air inlets 235. Rather, the disc mills 200, 800 may have any orientation with either of the discs 300, 500 being on top, and indeed, the discs 300, 500, 1500 may have other orientations, such as vertical.
To the extent that a patentee may act as its own lexicographer under applicable law, it is hereby further directed that all words appearing in the claims section, except for the above defined words, shall take on their ordinary, plain and accustomed meanings (as generally evidenced, inter alia, by dictionaries and/or technical lexicons), and shall not be considered to be specially defined in this specification. Notwithstanding this limitation on the inference of “special definitions,” the specification may be used to evidence the appropriate, ordinary, plain and accustomed meanings (as generally evidenced, inter alia, by dictionaries and/or technical lexicons), in the situation where a word or term used in the claims has more than one pre-established meaning and the specification is helpful in choosing between the alternatives.
It will be understood that, although various features of the invention have been described with respect to one or another of the embodiments of the invention, the various features and embodiments of the invention may be combined or used in conjunction with other features and embodiments of the invention as described and illustrated herein.
Although this disclosure has described and illustrated certain preferred embodiments of the invention, it is to be understood that the invention is not restricted to these particular embodiments. Rather, the invention includes all embodiments, which are functional, electrical or mechanical equivalents of the specific embodiments and features that have been described and illustrated herein.
The present application is a continuation-in-part of, and claims the benefit under any applicable U.S. statute to, U.S. patent application Ser. No. 13/742,773 filed Jan. 16 2013, titled Stationary Disc, Rotating Disc and Mill Assembly For Reducing Machines. This application incorporates by reference U.S. application Ser. No. 13/742,773, as if fully set forth herein.
| Number | Name | Date | Kind |
|---|---|---|---|
| 3926380 | Musgrove et al. | Dec 1975 | A |
| 4081147 | Seifert et al. | Mar 1978 | A |
| 5941467 | McArdle et al. | Aug 1999 | A |
| 8282031 | Sly et al. | Oct 2012 | B2 |
| 20060086856 | Pallmann | Apr 2006 | A1 |
| 20110318440 | Zollitsch et al. | Dec 2011 | A1 |
| Number | Date | Country |
|---|---|---|
| 373524 | Sep 1930 | BE |
| 373 524 | Oct 1930 | BE |
| 1 028 808 | Nov 2006 | EP |
| 2 399 716 | Dec 2011 | EP |
| 417 479 | Nov 1910 | FR |
| 417479 | Nov 1910 | FR |
| 869 144 | Feb 1945 | FR |
| 896144 | Feb 1945 | FR |
| 467196 | Jun 1937 | GB |
| H05345131 | Dec 1993 | JP |
| WO 9912647 | Mar 1999 | WO |
| WO 2011106115 | Sep 2011 | WO |
| Entry |
|---|
| European Examiner's Report and Supplemental Search Report dated Aug. 25, 2016 issued in related European application No. 14 740 327.3. |
| “Stationary Disc, Rotating Disc and Mill Assembly for Reducing Machines” Specification, Drawings, Claims and Prosecution History, of U.S. Appl. No. 13/742,773, filed Jan. 16, 2013, by Hristos Lefas, et al., which is stored in the United States Patent and Trademark Office (USPTO) Image File Wrapper (IFW) system. |
| “Stationary Disc, Rotating Disc and Mill Assembly for Reducing Machines” Specification, Drawings, Claims and Prosecution History, of U.S. Appl. No. 15/283,369, filed Oct. 1, 2016, by Hristos Lefas, et al., which is stored in the United States Patent and Trademark Office (USPTO) Image File Wrapper (IFW) system. |
| Australian Office Action dated Jun. 21, 2017 issued in corresponding Australian Application No. 2014207206. |
| Extended European Search Report dated Jan. 31, 2018, issued in corresponding European Application No. 14896324.2. |
| Chinese Office Action dated Mar. 26, 2018 issued in the corresponding Chinese Application No. 201480080000.5. |
| Number | Date | Country | |
|---|---|---|---|
| 20150076262 A1 | Mar 2015 | US |
| Number | Date | Country | |
|---|---|---|---|
| Parent | 13742773 | Jan 2013 | US |
| Child | 14323273 | US |
