Abstract
A planetary roller mill for processing a feed material includes a vessel with a grinding ring having an opening therethrough and a first area. The grinding ring is in sealing engagement with the inside surface of the vessel assembly. At least two non-circular support plates are secured to a rotatable shaft. Each plate has an axially facing surface. A plurality of rollers rotatably are mounted to and positioned between the two support plates. Each of the plurality of rollers are in grinding communication with the grinding surface. The planetary roller mill includes an air supply system having an outlet in communication with the opening in the grinding ring. Areas of the two support plates are of magnitudes which configure a flow area through the opening of at least 30 percent of the first area to provide a predetermined quantity of heated air to remove moisture from the feed material in the grinding assembly.
Claims
1. A planetary roller mill for processing a feed material, the roller mill comprising: a vessel assembly mounted to a stationary frame and having an inside surface; a material feed supply in communication with the vessel assembly; a grinding assembly positioned in the vessel assembly below the material feed supply, the grinding assembly comprising: an annular grinding ring having an opening extending therethrough, the opening being defined by a radially inward facing grinding surface and having a first area, the grinding ring being in sealing engagement with the inside surface of the vessel assembly; a shaft rotatably and vertically mounted to the frame; a sleeve connected to the shaft and being concentric about a center axis of the vessel assembly; a first support plate having a first central area coaxial with the center axis, the first support plate being secured to the sleeve and having a first axially facing surface defining a second area, the first support plate having at least three first lobes extending radially outward from the first central area; a second support plate having a second central area coaxial with the center axis, the second support plate being secured to the sleeve and having a second axially facing surface defining a third area, the second support plate being spaced axially apart from the first support plate, the second support plate having at least three second lobes extending radially outward from the second central area; and a plurality of rollers rotatably mounted to and positioned between the first support plate and the second support plate, each of the plurality of rollers having a radially outer surface that is in grinding communication with the grinding surface of the grinding ring, each of the plurality of rollers having a bore axially extending therethrough, the bore having an inside diameter, each of the plurality of rollers being mounted on a corresponding pin secured to and extending between the first support plate and the second support plate, the corresponding pin extending through the bore, the corresponding pin having an outside diameter that is less than the inside diameter of the bore, each of the plurality of rollers being configured to move radially outward from the corresponding pin and radially outward from the shaft during and as a result of rotation of the shaft; and an air supply system having an outlet in communication with the opening in the grinding ring for supplying air through the opening; wherein the first support plate is of a non-circular shape such that the second area of the first support plate is of a first magnitude which configures a first flow area through the opening of at least 30 percent of the first area to provide a predetermined quantity of heated air to remove moisture from the feed material in the grinding assembly, wherein the second support plate is of a non-circular shape such that the third area of the second support plate is of a second magnitude which configures a second flow area through the opening of at least 30 percent of the first area to provide a predetermined quantity of heated air to remove moisture from the feed material in the grinding assembly; and wherein each of the at least three first lobes and each of the at least three second lobes have an asymmetrical shape and have an area for receiving the corresponding pin of one of the plurality of rollers, the area having a center point, the asymmetric shape comprising a trailing edge and a leading edge opposite the trailing edge, and the trailing edge extends further away from the center point than does the leading edge.
2. The planetary roller mill of claim 1, wherein the first flow area is from 40 to 70 percent of the first area and the second flow area is from 40 to 70 percent of the first area so that the predetermined quantity of heated air is sufficient to at least one of dry and calcine synthetic gypsum, natural gypsum or mixtures of synthetic gypsum and natural gypsum.
3. The planetary roller mill of claim 1, wherein the first flow area is from 40 to 70 percent of the first area and the second flow area is from 40 to 70 percent of the first area so that the predetermined quantity of heated air is sufficient to at least one of dry and calcine synthetic gypsum having about 10 wt % surface moisture and about 20 wt % chemical bond moisture, natural gypsum having about 5% surface moisture and about 20 wt % chemical bond moisture or a mixture of synthetic gypsum and natural gypsum about 5 wt % to about 10 wt % surface moisture and about 20 wt % chemical bond moisture, while the planetary roller mill is configured to provide sufficient dwell time in the grinding area to produce a ground calcined product of a predetermined particle size.
4. The planetary roller mill of claim 1, wherein the predetermined quantity of heated air is sufficient to at least one of dry and calcine the feed material when the feed material has a particle size of less than 1 millimeter.
5. The planetary roller mill of claim 1, wherein the first flow area is from 30 to 60 percent of the first area and the second flow area is from 30 to 60 percent of the first area so that the predetermined quantity of heated air is sufficient to remove moisture from the feed material when the feed material comprises at least one of Kaolin clay, bentonite, limestone, pet coke and coal.
6. The planetary roller mill of claim 1, wherein the first flow area is from 30 to 60 percent of the first area and the second flow area is from 30 to 60 percent of the first area so that the predetermined quantity of heated air is sufficient to remove moisture from the feed material when the feed material has a moisture content of greater than 5 wt %, while the planetary roller mill provides sufficient grinding area to produce a ground dried product of a predetermined particle size.
7. The planetary roller mill of claim 1, wherein the first flow area is from 30 to 60 percent of the first area and the second flow area is from 30 to 60 percent of the first area so that the predetermined quantity of heated air is sufficient to remove moisture from the feed material when the feed material has a particle size of about 0.05 mm to about 50 mm.
8. The planetary roller mill of claim 1, wherein the radially outer surface of each of the rollers is convex and the grinding surface of the grinding ring is concave.
9. The planetary roller mill of claim 1, wherein the radially outer surface of each of the rollers is substantially straight and the grinding surface of the grinding ring is substantially straight.
10. The planetary roller mill of claim 1, wherein the each of the rollers has a conical outer surface and the grinding surface of the grinding ring is sloped to receive the rollers having a conical outer surface.
11. The planetary roller mill of claim 1, further comprising at least one wear member removably disposed between the roller and at least one of the first support plate and the second support plate.
12. The planetary roller mill of claim 1, wherein the outlet of the air supply system is connected to a bottom portion of the opening of the grinding ring, beneath the plurality of rollers.
13. The planetary roller mill of claim 1, wherein the grinding assembly comprises a plow assembly rotatable with the shaft and configured to transport the feed material from below the grinding assembly to the plurality of rollers and grinding ring.
14. The planetary roller mill of claim 13, wherein the plow assembly is secured to the second support plate.
15. The planetary roller mill of claim 1, further comprising: at least one additional support plate secured to the shaft, the at least one additional support plate being spaced axially apart from the first support plate and the second support plate; and an additional plurality of rollers mounted to and positioned between the at least one additional support plate and one of the first support plate and the second support plate, each of the plurality of additional rollers having a radially outer surface that is in grinding communication with the grinding surface of the grinding ring, each of the plurality of additional rollers having an additional bore axially extending therethrough, the additional bore having an inside diameter, each of the plurality of additional rollers being mounted on a corresponding pin of one of each of the plurality of rollers, the corresponding pin further extending through the additional bore and to the additional support plate, the outside diameter of the corresponding pin being less than the inside diameter of the additional bore, each of the plurality of additional rollers being configured to move radially outward from the corresponding pin and radially outward from the shaft during and as a result of rotation of the shaft.
16. The planetary roller mill of claim 1, wherein the grinding assembly is configured for grinding the feed material at a grinding zone air temperature of at least 177 degrees Celsius.
17. The planetary roller mill of claim 1, wherein the material feed supply comprises an outlet that extends through the vessel assembly into an interior area thereof and comprising a ramp secured to the inside surface and extending downwardly and radially inward relative to the outlet and at least partially between the outlet and the grinding ring.
18. The planetary roller mill of claim 17, further comprising a cover positioned over the outlet and at least a portion of the ramp.
19. The planetary roller mill of claim 17, further comprising a means for adjusting the vertical position of the rollers relative to the grinding ring.
20. The planetary roller mill of claim 1, wherein: each of the plurality of rollers has at least one axial end; and the center point is positioned on a corresponding one of the at least three first lobes and the at least three second lobes such that during rotation of the first support plate and the second support plate in a direction from the trailing edge to the leading edge, the corresponding one of the at least three first lobes and the at least three second lobes covers at least a portion of the at least one axial end adjacent to the leading edge and the trailing edge.
21. The planetary roller mill of claim 20, wherein the corresponding one of the at least three lobes covers an entirety of the at least one axial end adjacent to the leading edge and the trailing edge.
22. The planetary roller mill of claim 1, wherein a first central axis of the bore of each of the plurality of rollers is configured to be misaligned with a second central axis of the corresponding pin during and as a result of the rotation of the shaft.
23. The planetary roller mill of claim 1, wherein a first central axis of the bore of each of the plurality of rollers rotates and is configured to orbit a second central axis of the corresponding pin during and as a result of the rotation of the shaft.
24. A method of retrofitting a roller mill, the method comprising providing the planetary roller mill according to claim 1.
25. The method of claim 24, further comprising: providing a first plow assembly secured to a hub of the shaft; removing the first plow assembly from the roller mill; and providing at least one second plow assembly and securing the at least one second plow assembly to the second support plate.
26. The method of claim 24, further comprising: removing the first grinding ring from the roller mill; providing a second grinding ring having a first opening defined by a first radially inward facing grinding surface and having a portion of the first area; and installing the second grinding ring in sealing engagement with the inside surface of the vessel assembly.
27. The method of claim 26, further comprising: adjusting a vertical position of the rollers relative to the first and second grinding rings.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
(1) FIG. 1A is a perspective view of the planetary roller mill of the present invention with four contoured rollers;
(2) FIG. 1B is a perspective view of the planetary roller mill of the present invention with four straight rollers;
(3) FIG. 2A is a cross sectional view of the planetary roller mill of FIG. 1A, taken across line 2A-2A;
(4) FIG. 2B is a cross sectional view of the planetary roller mill of FIG. 1B, taken across line 2B-2B;
(5) FIG. 2C is a cross sectional view of a portion of a planetary roller mill with two layers of the contoured rollers;
(6) FIG. 2D is an enlarged cross sectional view of one of the rollers of FIG. 2A taken across line 2D-2D;
(7) FIG. 2E is cross sectional view of another embodiment of the planetary roller mill of the present invention with contoured rollers, wear plates and an alternative plow mounting configuration;
(8) FIG. 2F is cross sectional view of another embodiment of the planetary roller mill of the present invention with conical rollers, wear plates and an alternative plow mounting configuration;
(9) FIG. 3A is a top view of an embodiment of the grinding assembly of the planetary roller mill of the present invention having three rollers;
(10) FIG. 3B is a top view of another embodiment of the grinding assembly of the planetary roller mill of the present invention having three rollers;
(11) FIG. 3C is a top view of another embodiment of the grinding assembly of the planetary roller mill of FIG. 2A shown with asymmetric support and wear plates;
(12) FIG. 3D is an enlarged view of a wear plate for use on the support plates of FIG. 3C;
(13) FIG. 3E is an enlarged view of one of the rollers and lobes of the support plate of FIG. 3D, shown in a neutral state;
(14) FIG. 3F is an enlarged view of one of the rollers and lobes of the support plate of FIG. 3D, shown in a rotating state;
(15) FIG. 4A is a top view of an embodiment of the grinding assembly of the planetary roller mill of the present invention having six rollers;
(16) FIG. 4B is a top view of an embodiment of the grinding assembly of the planetary roller mill of the present invention having six rollers;
(17) FIG. 5 is a perspective view of the three roller embodiment of the planetary roller mill of the present invention;
(18) FIG. 6 is a cross sectional view of a prior art pendulum mill;
(19) FIG. 7 is an enlarged cross sectional view of one of the pendulum and roller assemblies of FIG. 6;
(20) FIG. 8 is a schematic view of a prior art planetary roller mill for ultra-fine grinding with air flow outside the grinding mill assembly;
(21) FIG. 9 is a cross sectional view of the planetary roller mill of FIG. 8 taken across line 9-9; and
(22) FIG. 10 is a cross sectional view of a prior art pulverizer mill;
(23) FIG. 11 is a perspective view of an interior area of a prior art grinding mill;
(24) FIG. 12 is a perspective view of an interior area of a grinding mill of the present invention shown with a ramp extending from the material feed chute;
(25) FIG. 13 is a perspective view of the interior area of the grinding mill of FIG. 12 shown with a cover installed over the chute;
(26) FIG. 14 is a cross sectional view of the grinding mill of FIG. 13; and
(27) FIG. 15 is a cross sectional view of another embodiment of a ramp and chute installed in the grinding mill of FIG. 12.
DETAILED DESCRIPTION
(28) As shown in FIG. 1A, a planetary roller mill (also referred to as “roller mill” herein) for processing (e.g., grinding, drying, and/or calcining) a feed material such as, but not limited to, synthetic gypsum, natural gypsum, mixtures of synthetic gypsum and natural gypsum, Kaolin clay, bentonite, limestone, pet coke and coal, is generally designated by element number 10. Thus, the roller mill 10 has utility in removing moisture from the feed material in the grinding assembly. The roller mill 10 includes a vessel assembly 20 mounted to a stationary frame 21. The vessel assembly 20 is shown in a vertical orientation about an axis A10. The vessel assembly 20 includes: 1) a grinding section 20A located at a bottom portion of the vessel assembly; 2) a material feed section 20B located axially above the grinding section 20A; and 3) a classifier housing 20C located axially above the feed section 20B. A material feed apparatus 22 is in communication with and secured to the material feed section 20B. The material feed apparatus 22 has an inlet 22A for receiving material to be supplied thereto; and an outlet 22B for supplying the feed material to the feed section 20B. The outlet 22B of the material feed apparatus 22 is positioned axially above the grinding section 20A such that the feed material enters the grinding section 20A axially above the rollers 50 and above an axial upper edge 32X of a grinding ring 32. A turbine classifier 40 is rotationally mounted to a top portion of the vessel assembly 20 via a shaft 40A that is coupled to a drive assembly 40B for rotation of the shaft 40A and the turbine classifier 40. The turbine classifier 40 is in communication with an outlet 41 of the vessel assembly 20. The turbine classifier 40 allows properly ground material to be discharged through the outlet 41 while returning material that requires additional grinding, back to the grinding section 20A. While the turbine classifier 40 is shown and described, the present invention is not limited in this regard as other classifiers may be employed including but not limited to the whizzer separator shown and described in U.S. Pat. No. 2,108,609 that issued on Feb. 15, 1938 to R. F. O'Mara and also described in PCT Application No. PCT/US2017/23560, with reference to FIGS. 2 and 3 contained therein.
(29) As shown in FIG. 11, the outlet 22B in the feed section 20B provides a communication between the material feed apparatus 22 and the outlet 22B that extends to an inside surface 20D of the of the vessel assembly 20. Material fed by the material feed apparatus 22 travels through the outlet 22B and falls, with the assistance of the force of gravity, onto the axial upper edge 32X of the grinding ring 32, as indicated by the arrow R20. A portion of the material to be ground (e.g., larger and/or heavier particles) can fall off of the axial upper edge 32X into the grinding section 20A, as indicated by the arrow R21. However, smaller particles and fines (e.g., synthetic gypsum and limestone) can be drawn away from the grinding section 20A by an updraft of air as indicated by the arrow 51A, thereby bypassing the grinding section 20A.
(30) As shown in FIGS. 12 and 14, a ramp 49 extends from a bottom edge 22X of the outlet 22B and slopes downwardly and radially inward to the axial upper edge 32X of the grinding ring 32 of a planetary type roller mill, such as those shown in FIGS. 1A and 1B. While the ramp 49 is shown and described as being employed with the planetary type roller mill, the ramp 49 may also be employed in a pendulum type roller mill, such as those shown in FIGS. 6 and 7. In one embodiment, the ramp 49 may be employed in any type of grinding mill. In one embodiment, an upper end 49U of the ramp 49 is secured to the inside surface 20D of the of the vessel assembly 20 by a weld 22W, for example, the weld 22W located at the bottom edge of the outlet 22B. In one embodiment, a bottom end 49B of the ramp 49 rests on the axial upper edge 32X of the grinding ring 32. In one embodiment, the ramp 49, including the bottom end 49B and upper end 49U, is positioned radially outward of an inner radial edge (e.g., proximate the grinding surface 46) of the grinding ring 32. While the welds 22W and 32W are shown and described as securing the ramp 49 to the inside surface 20D and the axial upper edge 32X of the grinding ring 32, the present invention is not limited in this regard as other configurations may be employed including but not limited to the use of mechanical fasteners, a ramp integrally formed with the inside surface 20D or the grinding ring 32, the ramp 49 can be spaced apart from the grinding ring 32 and/or the ramp 49 can be secured to the inside surface 20D and/or the grinding ring 32 with one or more brackets, fixtures or covers. As shown in FIG. 14, the bottom end 49B of the ramp 49 terminates a distance G30 from an edge of the grinding surface 46. The distance G30 is determined based upon a maximum allowable wear of the grinding ring 32.
(31) As shown in FIGS. 13 and 14, a cover 59 is positioned over the ramp 49 and the outlet 22B. The cover 59 includes a ramped surface 59F supported by opposing triangular shaped side walls 59E. The ramped surface 59F slopes downward and radially inward from an upper edge 59U thereof. The ramped surface 59F terminates at a bottom edge 59B of the cover 59. In one embodiment, the bottom edge 59B terminates a distance G33 above the axial upper edge 32X of the grinding ring 32. In one embodiment, the distance G33 is zero and the bottom edge terminates at a horizontal plane that is coplanar with the axial upper edge 32X of the grinding ring 32. The bottom edge 59B of the cover 59 extends radially inward from the grinding surface 46 by a distance G31 to allow ample area for discharge of the material to be ground. While the bottom edge 59B of the cover 59 is shown and described as extending radially inward from the grinding surface 46, the present invention is not limited in this regard as the bottom edge 59B of the cover 59 may terminate radially outward from the grinding surface 46.
(32) The Applicant has discovered that while covers and ramps are generally not needed in configurations (e.g., planetary grinding mills and pendulum grinding mills) where the grinding area is directly below the outlet of the material feed, that the cover 59 illustrated in FIGS. 13 and 14 is aerodynamic, minimizes disruption to the air flow, and has utility for grinding and drying fine feed materials such as synthetic gypsum and limestone. The Applicant has discovered that use of the ramp 49 and the cover 59 cooperate to provide a direct and unobstructed flow path R22 between the outlet 22B and the grinding area 20A for the material to be ground. The ramp 49 and the cover 59 allow the material to be ground to travel more quickly from the outlet 22B to the grinding section 20A, compared to a configuration as shown in FIG. 11 that has no ramp or cover. The Applicant has further discovered that use of the ramp 49 and the cover 59 cooperate to reduce the quantity of material carried away by the updraft 51A, thereby increasing the percentage of material discharged through the outlet 22B that enters the grinding section 20A, compared to a configuration as shown in FIG. 11 that has no ramp or cover.
(33) FIG. 15 illustrates another embodiment of a ramp 49′ and cover 59′ that results in a greater interior area compared to that created by the ramp 49 and cover 59 configuration of FIGS. 12 and 14. The ramp 49′ has an upper edge 49U′ that is secured to the inside wall 20B at a position between the bottom edge 22X of the outlet 22B and the axial upper edge 32X of the grinding ring 32. The bottom edge 49B′ is configured similar to the bottom edge 49B of the ramp 49 and is secured to the axial upper edge 32X of the grinding ring 32 and/or the inside surface 20B similar to the described for the bottom edge 49B shown in FIG. 14. The cover 59′ includes a ramped surface 59F′ that extends downward and radially inward from an upper edge 59U′ thereof. The ramped surface 59F′ transitions into a vertical surface 59G′. The vertical surface 59G′ terminates at a bottom edge 59B′ of the cover 59′. In one embodiment, the bottom edge 59B′ terminates a distance G33 above the axial upper edge 32X of the grinding ring 32. In one embodiment, the distance G33 is zero and the bottom edge terminates at a horizontal plane that is coplanar with the axial upper edge 32X of the grinding ring 32. The bottom edge 59B extends radially inward from the grinding surface 46 by a distance G31 to allow ample area for discharge of the material to be ground.
(34) The Applicant has discovered that the cover 59′ illustrated in FIG. 15, is aerodynamic, minimizes disruption to the air flow, and has utility for fine grinding limestone with fine feed sizes. The Applicant has discovered that use of the ramp 49′ and the cover 59′ cooperate to provide a direct and unobstructed flow path R22 between the outlet 22B and the grinding area 20A for the material to be ground. The ramp 49′ and the cover 59′ allow the material to be ground to travel more quickly from the outlet 22B to the grinding area, compared to a configuration as shown in FIG. 11 that has no ramp or cover. The Applicant has further discovered that use of the ramp 49′ and the cover 59′ cooperate to reduce the quantity of material carried away by the updraft 51A (see e.g., FIG. 13), thereby increasing the percentage of material discharged through the outlet 22B that enters the grinding area 20A, compared to a configuration as shown in FIG. 11 that has no ramp or cover.
(35) In one embodiment, the ramp 49 or 49′ is secured (e.g., welded) to the cover 59 or 59′ to create an integral one piece ramp and cover assembly. In one embodiment, the side walls 59E or 59E′ flare outwardly from the cover 59 or 59′. In one embodiment, the side walls 59E or 59E′ have flanges extending outwardly therefrom. In one embodiment, the cover 59 or 59′; the ramp 49 or 49′; and/or the integral one piece ramp and cover assembly are removably secured to the inside wall 20B. For example, in one embodiment, clamps and lugs are secured to the inside wall 20B and the flange slides into the clamps and the cover 59 or 59′ seat on the lugs so that the cover 59 or 59′ and/or the ramp 49 or 49′ are removably secured to the inside wall 20B and located at a predetermined position from the grinding ring 32.
(36) The Applicant has discovered that the ramps 49 and 49′ and/or the covers 59 and 59′ can be employed in the planetary roller mills 10 illustrated in FIGS. 1A, 1B, 2A-2F, 3A-3C, 4A, 4B, 5 as well as the pendulum mills of FIGS. 6 and 7. They may also be used in any other configuration of grinding mill where fine feed raw material is to be gravity fed from an outlet port toward a grinding section.
(37) As shown in FIG. 1A, a grinding assembly 30 is positioned in the grinding section 20A of the vessel assembly 20 below the outlet 22B. The grinding assembly 30 includes the annular grinding ring 32 that is secured to the inside surface 20D of the vessel assembly 20 via suitable fasteners 32F. The grinding ring 32 has an outside surface 32Q that is arranged in sealing engagement with the inside surface 33Y of a support ring 33 of the vessel assembly 20. Thus, there is no annular gap between the grinding ring 32 and the support ring 33 of the grinding section 20A of the vessel assembly 20 for air to flow through and bypass the grinding assembly 30. In one embodiment, the grinding ring 32 is a continuous annular ring with no circumferential openings or material feed inlets extending therethrough. A plurality of vanes 34 are positioned between the support ring 33 and a base plate 36 that is secured to the frame 21. The vanes 34 are positioned below the grinding assembly 30 and extend an angled length from a position radially outward from the grinding ring 32 to a position radially inward from the grinding ring 32. The vanes 34 are positioned in a circumferential configuration around the support ring 33. Adjacent pairs of the vanes 34 define channels 35 (e.g., nozzles) therebetween for conveying heated air designated by the arrows 35A into the grinding assembly 30 at velocities and flow rates sufficient to dry and/or calcining the material to be ground, as described herein.
(38) As shown in FIG. 1A, the vessel assembly 20 includes an air supply manifold 45 that has an inlet 45A that extends into a circumferential duct 45B that surrounds and opens into the grinding section 20A as described herein. In one embodiment, the outlet of the air supply manifold 45 is connected to a bottom portion of the opening 44 of the grinding ring 32, axially beneath the plurality of rollers 50.
(39) As best shown in FIGS. 3A and 4A the grinding ring 32 has an opening 44 extending therethrough from the axial upper edge 32X to an axial lower edge 32Y thereof. The opening 44 is defined by a radially inward facing grinding surface 46 and having a first area A1. The first area A1 is the area defined by the equation A1=π/4 (D7).sup.2, where D7 is the nominal inside diameter of the grinding ring 32 measured at the radially inward facing grinding surface 46.
(40) Referring to FIGS. 1A, 2A, 2E and 2F, the grinding assembly 30 includes a drive shaft 39 rotatably mounted to the frame 21. A hub 43 is secured to an upper portion of the drive shaft 39 by a key connection (not shown). The hub 43 includes a flange 43F on a lower end thereof. The grinding assembly 30 includes a sleeve 43C that extends axially downward from another flange 43G. A shim stack 43J is positioned between the flange 43F and the flange 43G. A plurality of fasteners secure the flanges 43F and 43G to one another. A plurality of gussets 47 are secured to and extend radially from the sleeve 43C. The shim stack 43J includes a predetermined number of shims (e.g., annular discs, for example 0.0625 inches (1.5875 mm) thick). Variation of the number of shims in the shim stack 43J adjusts the vertical position of the rollers 50 relative to the grinding ring 32, as described herein. While the shim stack 43J is shown and described as being employed to adjust the vertical position of the rollers 50 relative to the grinding ring 32, the present invention is not limited in this regard as other means for adjusting the rollers 50 relative to the grinding ring 32 may be employed including but not limited to washers and jacking screws or indeed by appropriate sizing of parts determining the position of the rollers 50 relative to the grinding ring 32.
(41) As shown in FIGS. 1A, 2A, 2E and/or 2F, the grinding assembly 30 includes a first support plate 52 secured to the shaft 39 via the hub 43, the sleeve 43C and the gussets 47. The first support plate 52 has a first axially facing surface 52A defining a second area A2. The first support plate 52 is of a generally non-circular shape configured to establish an optimum magnitude of the area A2. In one embodiment, as shown in FIGS. 3B and 4B, the area A2′ of the first support plate 52 is increased over the area A2 shown in FIGS. 3A and 4A, by extending the area A2′ outwardly to cover an entire axial end 50Z of each of the rollers 50, without reducing the flow area FA. Use of the increased area A2′ reduces the contact pressure between the axial end 50Z and the first axially facing surface 52A (i.e., underside) of each of the lobes 52L. While the area A2′ of the first support plate 52 is shown and described as being increased, the present invention is not limited in this regard as the area of the second support plate 54 can be increased in a manner similar to that described for the first support plate 52. The Applicant has discovered that circular shaped support plates are not suitable to provide the optimum magnitude of the area A2. In one embodiment, as shown in FIG. 3A, the support plate 52 has a central area 52C with three lobes 52L extending radially outwardly therefrom. While FIG. 3A illustrates the support plate 52 having three lobes 52L, the present invention is not limited in this regard as the support plate may have any number of lobes, for example, as shown in FIG. 4A, the support plate 52 has the central area 52C with six lobes 52L extending radially outwardly therefrom.
(42) As shown in FIGS. 1A, 2A, 2E and 2F the grinding assembly 30 includes a second support plate 54 secured to the shaft 39 via the hub 43, the sleeve 43C and the gussets 47. The second support plate 54 has a second axially facing surface 54A defining a third area A3. The second support plate 54 is of a generally non-circular shape configured to establish an optimum magnitude of the area A3. The Applicant has discovered that circular shaped support plates are not suitable to provide the optimum magnitude of the area A3. The second support plate 54 is spaced axially apart from the first support plate 52 by a gap G10. The second support plate 54 is configured in a shape similar to that shown (e.g., FIGS. 3A, 3B, 4A and 4B) and described for the first support plate 52.
(43) As shown in FIGS. 1A and 2A, a plurality of rollers 50 are rotatably mounted to and positioned between the first support plate 52 and the second support plate 54. Adding shims to the shim stack 43J causes the sleeve 43C, the first and second support plates 52 and 54 and the rollers 50 to move vertically downward to vertically align the rollers 50 in the grinding ring 32. Reducing the number shims in the shim stack 43J causes the sleeve 43C, the first and second support plates 52 and 54 and the rollers 50 to move vertically upward to vertically align the rollers 50 in the grinding ring 32.
(44) As shown in FIG. 2D, the first support plate 52 is shown in a cut away view to expose the axial end 50Z of the roller 50. Each of the plurality of rollers 50 is configured to move between the first and second support plates 52 and 54, for example move between the first and second support plates 52 and 54 in the direction of the arrow R1, (as shown by the dashed lines 50 version of the roller 50) as a result of rotation of the shaft 39 in the clockwise direction of the arrow R9. Each of the plurality of rollers 50 has a bore 50B extending axially therethrough. The bore 50B has an inside diameter D50. Each of the plurality of rollers 50 is mounted on a pin 60 secured to and extending between the first support plate 52 and the second support plate 54 in the area of the respective lobe 52L (e.g., FIGS. 3 and 4). Referring back to FIG. 2D, the pin 60 has an outside diameter D60 that is less than the inside diameter D50 of the bore 50B. Each of the plurality of rollers has a radially outer surface 50X. Due to rotation of the shaft 39 in the clockwise direction R9, the roller 50 moves circumferentially backward towards a trailing edge 54T of the second support plate 54 and away from the pin 60 as shown by the arrow R1. As a result of the rotation of the shaft 39 the roller 50 moves between the first and second support plates 52 and 54. For example, the roller 50 moves between the first support plate 52 and the second support plate 54 in the direction of the arrow R1 (see FIG. 2D) to the roller position indicated by the dashed lines 50 so that the radially outer surface 50X is in grinding communication with the grinding surface 46 of the grinding ring 32, for example, the outer surface 50X′ rollingly engages the grinding surface 46 of the grinding ring 32 or the outer surface 50X′ is in sufficient proximity to the grinding surface 46 of the grinding ring 32 to effectuate grinding. In one embodiment, as a result of the rotation of the shaft 39, the roller 50 is forced radially outward in the direction of the arrow R2 by centrifugal force to increase the contact pressure between the outer surface 50X of the roller and the grinding surface 46. If the roller 50 encounters very large or abnormally hard chunks of material, the roller 50 may temporarily move radially inward in a direction opposite to the arrow R2.
(45) As shown in FIG. 2D, when the shaft 39 is not rotating, the roller may attain a neutral state wherein the bore 50B is centered around the pin 60. In the neutral state the radially outer surface 50X of the roller 50 is equidistant from lateral edges of the lobes 52L and 54L, as indicated by the distances D10 and D11. However, when the shaft 39 rotates in the direction of the arrow R9, the roller 50 moves in the general direction of the arrow R1. As a result, the radially outer surface 50X of the roller 50 is asymmetrically spaced from the lateral edges (i.e., the leading edge 54U and trailing edges 54T) of the lobes 54L, as indicated by the unequal distances D12 and D13. Since D13 is greater that D12, a lesser area of the second axially facing surface 54A slidingly engages the axial end 50Y (see FIG. 2E, for example) of the roller 50, compared to the neutral position. This results in higher contact pressures and increased wear during operation when the shaft 39 is rotating, compared to a configuration in which a greater percentage of the area of the second axially facing surface 54A slidingly engages the axial end 50Y of the roller 50. While the asymmetric spacing of the lateral edges (i.e., the leading edge 54U and trailing edges 54T) of the lobes 54L relative to the radially outer surface 50X of the roller 50 is shown to decrease the contact area between the second axially facing surface 54A and the axial end 50Y of the roller 50 as shown and described, a similar configuration exists between the axial end 50X of the roller 50 and the first axially facing surface 52A.
(46) As shown in FIG. 3C, the support plate 152 is similar to the first and second support plates 52 and 54 of FIGS. 3A and 3B, thus similar elements of the first support plate 52 are designated with similar element numbers preceded by the numeral 1. The rollers 50 shown in FIG. 3C are contoured with convex exterior surfaces 50X, similar to the rollers 50 shown in FIG. 2E.
(47) As shown in FIG. 3C, the area A2″ of the first support plate 152 is increased over the area A2 shown in FIG. 3A, by extending the area A2″ asymmetrically outwardly to cover a portion of (i.e., less than the area A2′ shown in FIG. 3B and greater than the area A2 of FIG. 3A) the axial end 50Z of each of the rollers 50, without reducing the flow area FA. Use of the increased area A2″ reduces the contact pressure between the axial end 50Z and the first axially facing surface 152A of each of the lobes 152L, as described herein.
(48) As shown in FIG. 3C, the direction of rotation of the shaft 39, the first support plate 152 and the second support plate 154 (only a portion of the second support plate 154 is shown under the cut away portion of the first support plate 152) is clockwise, relative to the stationary grinding ring 32, is indicated by the arrow R9. The first support plate 152 has a central area 152C that defines a center of rotation about the axis A10. Three lobes 152L extend radially outward from the central area 152C. As shown in FIGS. 3E and 3F, each of the lobes 152L has an asymmetrical shape and an area 152Q (e.g., a recess, an opening or surface) for receiving a roller mounting pin 60. The area for receiving the roller mounting pin 60 has a center point 60P. The asymmetric shape of the lobes 152L is defined by a trailing edge 152T and a leading edge 152U, generally opposite the trailing edge 152T. The trailing edge 152T extends further away from the center point 60P than does the leading edge 152U. For example, as shown in FIG. 3E, the trailing edge 152T extends away from the center point 60P a distance D21 and the leading edge 152U extends away from the center point 60P by a distance D20. The distance D21 is greater than the distance D20.
(49) As shown in FIGS. 3E and 3F, the lobe 152L has a straight section 152V that transitions at transition point R12 to the trailing edge 152T. The trailing edge 152T transitions into the leading edge 152U which transitions into a straight section 152W at transition point R13. The trailing edge 152T and the leading edge 152U have has a radius of curvature R15 measured from a center point 152P of the lobe 152L. The transition point R12 is located at about a 10 o'clock to 11 o'clock position; and the transition point R13 is located at about a 7 o'clock position.
(50) As shown in FIG. 3F, the center point 60P is positioned on the lobe 152L such that during rotation of the support plate in a direction from the trailing edge 152T to the leading edge 152 U (i.e., in the direction of the arrow R9), the lobe 152L is configured to cover at least a portion of the axial end 50Z of the roller 50, adjacent to the leading edge 152U and the trailing edge 152T, thereby leaving the arcuate segment 157A of the axial end 50Z uncovered. As shown in FIG. 3F, the uncovered segment 157A extends around the lobe 152L from the transition point R12 to the transition point R13 at a substantially uniform width W57 between an edge of the axial end 50Z of the roller 50 and a transition 50ZZ to the exterior surface 50Z of the roller 50. Thus, as shown in FIG. 3F the lobe 152L covers a portion of the axial end 50Z adjacent to the leading edge 152U and the trailing edge 152T.
(51) As shown in FIG. 3E, the center point 60P is positioned on the lobe 152L such that in a neutral state with the center point 60P positioned coaxially with the axial center line 50P of the roller 50. The lobe 152L is configured to cover at least a portion of the axial end 50Z of the roller 50, adjacent to the leading edge 152U but none or less of the axial end 50Z adjacent to the trailing edge 152T, thereby leaving the arcuate segment 157B of the axial end 50Z, uncovered. As shown in FIG. 3E, the uncovered arcuate segment 157B extends around the leading edge 152U of the lobe 152L a non-uniform width W56 between an edge of the axial end 50Z of the roller 50 and a transition 50ZZ to the exterior surface 50Z of the roller 50. Thus, as shown in FIG. 3E the lobe 152L covers a portion of the axial end 50Z adjacent to the leading edge 152U. As shown in FIG. 3F, in the rotating state, the roller 50 moves in the direction of the arrow R1 and an uncovered segment 157A extends around the leading edge 152U and trailing edge 152T of the lobe 152L a uniform width W57 between an edge of the axial end 50Z of the roller 50 and a transition 50ZZ to the exterior surface 50Z of the roller 50.
(52) The Applicant has discovered that use of the asymmetric shape of the lobe 152L disclosed herein allows the bore 50B to wear radially outward while maintaining the axial end 50Z of the roller 50 partially covered. This is because as the wear occurs and the roller 50 migrates further away from the trailing edge 152T, the greater distance D21 that the trailing edge 152T extends away from the center point 60P compared to the distance D22, the lobe 152L maintains greater coverage of the axial end 50Z, compared to the lobes 52L shown in FIG. 3A.
(53) While the asymmetric lobes 152L are shown and described for the first support plate 152, similar asymmetric lobes may be employed for the second support plate 154.
(54) As shown in FIG. 3D, wear plates 169A, 169B is similar to the wear plates 69A, 69B illustrated in FIGS. 2E and 2F, except that the wear plates 169A and 169B have an asymmetric shape complementary to the asymmetric shape of the lobes 152L described herein with reference to FIGS. 3C, 3E and 3F. The wear plates 169A, 169B are installed in the grinding section 20A similar to that shown and described herein with reference to FIGS. 2E and 2F for the wear plates 69A and 69B. Similar to the wear plates 69A and 69B, the wear plates 169A, 169B have holes 171H extending there through for receiving fasteners 69F that are threaded into the respective first and/or second support plates 52, 152, 54, 154 for securing the wear plates 169A, 169B thereto. The Applicant has overcome difficulty in mounting (e.g., wear plates are too hard to form threads therein and may require periodic replacement) the wear members 69A and 69B to the respective one of the first support plate 52 and the second support plate 54, by employing the fasteners 69F proximate a radially inward edge thereof while employing spot welds on a radially outer edge thereof.
(55) As shown in FIG. 1A, the air supply manifold 45 has an outlet in the form of the circumferential duct 45B that is in communication with the opening 44 in the grinding ring 32 for supplying heated air through the opening 44 at a velocity and flow rate sufficient for drying and calcining the moist material to be ground. As shown in FIGS. 1A, 1B, 2A, and 2B, the heated air flows upward through the grinding section 20A and the feed section 20B as indicated by the arrows 51A. The feed material flows in a generally downward direction from the feed outlet 22B in the general direction of the arrows 51F and generally opposite to the direction indicated by the arrows 51A.
(56) As shown in FIGS. 2E and 2F a first wear member 69A (e.g., a plate) is removably secured to an first axially facing surface 52A of each of the lobes 52L of the first support plate 52 by suitable fasteners 69F. The first wear member 69A is manufactured from a heat treated alloy steel that has a hardness of about 500-600 BHN. An axial end 50Z of the roller 50 slidingly engages the first wear member 69A. Each of the first wear members 69A has a shape that is complementary to the shape of a portion of the lobe 52L.
(57) As shown in FIGS. 2E and 2F, a second wear member 69B (e.g., a plate) is removably secured to second axially facing surface 54A (i.e., upper side) of each of the lobes 54L of the second support plate 54 by suitable fasteners 69F. The second wear member 69B is manufactured from a heat treated alloy steel that has a hardness of about 500-600 BHN. An axial end 50Y of the roller 50 slidingly engages and is seated on the second wear member 69B. Each of the second wear members 69B has a shape that is complementary to the shape of a portion of the lobe 52L. In one embodiment, the wear members 69A and/or 69B are about ½ inch thick. In one embodiment, there is a small gap G9 (e.g., about 0.10 to 0.15 inches) between the underside of the first wear member 69A and the axial end 50Z of the roller 50.
(58) As shown in FIG. 2F, the grinding assembly 430 has conical rollers 450 that have the radially outer surface 450X sloped at an angle δ relative to reference line A12 that is parallel to an axial center line A11 of the roller 450. The grinding ring 432 has conical grinding surface 446 that is sloped radially inward and axially downward from the axial upper edge 432X of a grinding ring 432 to the axial lower edge 432Y of the grinding ring 432 at the angle δ measured relative to a vertical reference line A12. The roller 450 is installed in the grinding ring 432 with the axial end 450Y (i.e., smaller diameter end compared to the axial end 450Z) facing down and below the axial end 450Z. The angle δ is between 5 and 15 degrees. The use of the conical rollers 450 and the conical grinding surface 446 has utility in providing a vertical lifting force which lifts the roller 450 to reduce the vertical force (e.g., about equal to 50-100% of the weight of the roller 450) applied to the wear member 69B. Reduction of the vertical force applied to the wear plate 69B reduces friction, wear and power consumption. Use of the conical rollers 450 and the conical grinding surface 446 also has utility in compensating for misalignment of the rollers 450 relative to the grinding ring 432 during assembly, because after a period of operation the rollers 450 migrate to a position favorable to grinding performance. The conical rollers 450 and conical grinding surface 446 can also be employed in configurations without the wear plates 69A and 69B, for example, in the grinding assemblies 30 of FIGS. 2A, 2B and 2C. The conical rollers 450 have an overlay 450K applied thereto, such as a cobalt based weld overlay (e.g., Stoody® 100 registered to Stoody Company or Stellite® registered to Kennametal Inc.). While the overlay 450K is shown and described as being applied to the conical rollers 450, the present invention is not limited in this regard as the overlay 450K can be applied to any of the rollers 50 shown in FIGS. 1A, 1B, 2A, 2B, 2C and 2E. The overlay 450K increases surface roughness and increases life of the rollers 450, 50 and helps prevent skidding or sliding of the rollers 450, 50 on the grinding surface 446, 46.
(59) Employing the shim stack 43J, as described herein and shown in FIG. 2F, has utility in positioning the conical rollers 450 relative to the grinding ring 432 to maximize grinding surface area therebetween. Employing the shim stack 43J also has utility in vertically positioning the contoured rollers 50 of FIG. 2E in the grinding ring 32 to maximize the grinding surface area therebetween.
(60) The first support plate and the second support plate are of a non-circular shape such that the optimum second area A2 of the first support plate 52 and the optimum third area A3 of the second support plate 54 are of magnitudes which configure a flow area FA (see FIGS. 3 and 4, for example showing the flow area FA as being the area A1 minus the area A2) through the opening of at least 30 percent of the first area A1 to provide a predetermined quantity of heated air in a ratio of 2-4 mass flow rate of air to mass flow rate of material being dried, to dry and/or calcining the feed material in the grinding assembly 30 and transport the ground material upwards through the grinding assembly 30 at a velocity (e.g., a velocity of about 20 feet per second to 40 feet per second) sufficient to entrain the ground material, in an air stream flowing upwardly through the grinding assembly 30. In one embodiment, the flow area FA is from 40 to 70 percent of the first area A1 so that the predetermined quantity of heated air is sufficient to dry and calcining synthetic gypsum, natural gypsum or mixtures of synthetic gypsum and natural gypsum. In one embodiment, the flow area FA is from 40 to 50 percent of the first area A1 so that the predetermined quantity of heated air is sufficient to dry and calcining synthetic and natural gypsum. The flow area FA extends from a radially outer edge 52E (see FIGS. 1A, 1B, 2A, 2B, 2C, 3A, 3B) of the first support plate 52 to the grinding surface 46. The flow area FA extends from a radially outer edge 54E (see FIGS. 1A, 1B, 2A, 2B, 2C, 3A, 3B) of the second support plate 54 to the grinding surface 46. The flow area FA extends from a radially outer edge 56E (see FIG. 2C) of the third support plate 56 to the grinding surface 46. The flow area FA includes an outlet of the grinding section 20A that transitions into the feed section 20B.
(61) Configuring the flow area FA from 40 to 70 percent or from 40 to 50 percent of the first area A1 yields the surprising result of providing the predetermined quantity of heated air sufficient to dry and calcining synthetic gypsum having about 10 wt % (i.e., weight percent) surface moisture and about 20 wt % chemical bond moisture (i.e., collectively referred to as high moisture). Configuring the flow area FA from 40 to 70 percent or from 40 to 50 percent of the first area A1 yields the surprising result of providing the predetermined quantity of heated air sufficient to dry and calcining natural gypsum having about 5 wt % (i.e., weight percent) surface moisture and about 20 wt % chemical bond moisture (i.e., collectively referred to as high moisture). Configuring the flow area FA from 40 to 70 percent or from 40 to 50 percent of the first area A1 yields the surprising result of providing the predetermined quantity of heated air sufficient to dry and calcining a mixture of synthetic gypsum and natural gypsum having about 5 wt % to about 10 wt % (i.e., weight percent) surface moisture and about 20 wt % chemical bond moisture (i.e., collectively referred to as high moisture). In addition, configuring the flow area FA from 40 to 70 percent or from 40 to 50 percent of the first area A1 yields the surprising result of providing the predetermined quantity of heated air is sufficient to dry and calcining the feed material having about 10 wt % surface moisture and about 20 wt % chemical bond moisture. In one embodiment, the predetermined quantity of heated air is sufficient to dry and calcining the feed material having a particle size of less than 1 millimeter. In one embodiment, the predetermined quantity of heated air is sufficient to dry and calcining the feed material having a particle size of about 40 to about 80 microns.
(62) In one embodiment, the flow area FA is from 30 to 60 percent of the first area A1 so that the predetermined quantity of heated air is sufficient to dry the feed material that includes one or more of Kaolin clay, bentonite, limestone, pet coke and coal. Configuring the flow area FA from 30 to 60 percent of the first area A1 yields the surprising result of providing the predetermined quantity of heated air sufficient to dry the feed material having a moisture content of greater than 5 wt %. Configuring the flow area FA from 30 to 60 percent of the first area A1 yields the surprising result of providing the predetermined quantity of heated air sufficient to dry the feed material having a moisture content of greater than 5 wt % and having a particle size of about 0.05 mm to about 50 mm.
(63) In one embodiment, the flow area FA is from 30 to 40 percent of the first area A1 so that the predetermined quantity of heated air is sufficient to dry the feed material that includes one or more of Kaolin clay, bentonite, limestone, pet coke and coal. Configuring the flow area FA from 30 to 40 percent of the first area A1 yields the surprising result of providing the predetermined quantity of heated air sufficient to dry the feed material having a moisture content of greater than 5 wt %. Configuring the flow area FA from 30 to 40 percent of the first area A1 yields the surprising result of providing the predetermined quantity of heated air sufficient to dry the feed material having a moisture content of greater than 5 wt % and having a particle size of about 0.05 mm to about 50 mm.
(64) For grinding, drying and calcining synthetic or natural gypsum or mixtures thereof, the Applicant discovered that the 40-70% flow area are required to provide sufficient air flow with enough heating capacity, while providing sufficient dwell time in the grinding area to produce a ground calcined product of a predetermined particle size. The Applicant has discovered that for grinding and drying of other material such as Kaolin clay, bentonite, limestone, pet coke and coal, that the 30-60% flow area is required to provide sufficient air flow with enough heating capacity, while providing sufficient grinding area to produce a ground dried product of a predetermined particle size.
(65) As shown in FIGS. 1A and 2A, the radially outer surface 50X of each of the rollers is contoured (e.g., convex) and the grinding surface 46 of the grinding ring is contoured (e.g., concave). The present invention is not limited in this regard as in one embodiment, the radially outer surface 50X′ of each of the rollers 50′ is substantially straight and the grinding surface 46′ of the grinding ring 32′ is substantially straight, as shown in FIGS. 1B and 2B. FIGS. 1B and 2B are similar to FIGS. 1A and 2A with the exception of the aforementioned straight configuration and therefor include the same element numbers for identical components. Through computational analysis, the Applicant has found that the roller mills 10 (FIG. 1A) with the rollers 50 having the convex radially outer surface 50X and the concave grinding surface 46 consume less energy compared to the roller mills 10′ (FIG. 1B) having straight radially outer surface 50X′ and straight grinding surface 46′.
(66) As best shown in FIG. 5, the grinding assembly 30 includes a plow assembly 70 rotatable with the shaft 39 and configured to transport the feed material from below the grinding assembly 30 upwards to the plurality of rollers 50′ and grinding ring 32′. As shown in FIGS. 2E and 2F, the second support plate 54 is utilized as a mounting site for a plow support structure 77 to receive the plow assembly 70. Adjusting the number of shims in the shim stack 43J also adjusts the vertical position of the plow assembly 70, similar to that described herein for adjusting the vertical position of the rollers 50.
(67) As shown in FIG. 2C, in one embodiment, the roller mill 30″ has a multiple roller layered configuration (e.g., 2 layers of contoured rollers are shown) includes a third support plate 56 secured to the shaft 39 via the sleeve 43C (and the hub 43 shown in FIG. 2A). A plurality of contoured rollers 50 is shown positioned between the first support plate and the second support plate 54. The contoured rollers 50 have an arcuate curved circumferential surface 50X. The third support plate 56 is spaced axially apart from the first support plate 52 and the second support plate 54. An additional plurality of contoured rollers 50″, similar to the contoured rollers 50, is mounted to and positioned between the third support plate and the second support plate 54. Each of the additional plurality of rollers 50″ is configured to move between the first support plate, the second support plate and/or the additional support plate as a result of rotation of the shaft 39. Each of the plurality of contoured rollers 50 has the radially outer surface 50X that is in grinding communication with the contoured grinding surface 46 of the grinding ring 32, for example, the outer surface 50X rollingly engages the contoured grinding surface 46 of the grinding ring 32″ or the outer surface 50X is in sufficient proximity to the contoured grinding surface 46 of the grinding ring 32 to effectuate grinding. Each of the plurality of additional rollers 50″ has the radially outer surface 50X″ that is in grinding communication with the contoured grinding surface 46″ of the grinding ring 32″, for example, the outer surface 50X″ rollingly engages the contoured grinding surface 46″ of the grinding ring 32″ or the outer surface 50X″ is in sufficient proximity to the contoured grinding surface 46″ of the grinding ring 32″ to effectuate grinding. The Applicant has found that the use of the multiple roller layer configuration shown in FIG. 2C, preferably a limit of two layers, is adequate because the two layers do not impede the upward flow of material to be ground as provided by the plow assembly 70, compared to prior art mills 200 (FIG. 8) that employ a top to bottom path for material being fed through the grinding assembly 280.
(68) While FIG. 2C illustrates a first support plate 52 and a second support plate 54 with a plurality of rollers 50 there between and the plurality of additional rollers 50″ positioned between the second support plate 54 and the third support plate 56, the present invention is not limited in this regard as any number of rows or layers of plurality of rollers between any number of support plates may be employed without departing from the broader aspects of the present invention.
(69) The grinding assembly 30 has no lubrication system that provides a lubricant such as oil to the pin 60 and the bore 50B of the rollers 50, 50′ or 50″. As a result, the grinding assembly 30 is configured for grinding the feed material that requires an airstream supplied at a temperature that the pin 60 and the bore 50B of the rollers 50, 50′ or 50″ operate at greater than 177 degrees Celsius (350 degrees Fahrenheit) or higher (e.g., 232 degrees Celsius (450 degrees Fahrenheit)). Moreover, since the weight of the rollers 50, 50′ or 50″ is significantly less (e.g., 40 percent of) than a comparably sized journal assembly 188 of the prior art pendulum mill 100 shown and described with reference to FIGS. 6 and 7, with less grinding pressure and thus less vibration, but still able to achieve throughput required. As a result, the planetary roller mill 10 with the grinding assembly 30 is configured to grind, dry and calcining materials such as synthetic gypsum, natural gypsum or mixtures of synthetic gypsum and natural gypsum having a feed material particle size of 40 to 80 microns and a ground particle size of 25 to 35 microns.
(70) The present invention includes a method of retrofitting a roller mill such as the pendulum mill 100 shown in FIG. 6. The method includes providing a roller mill, such as the pendulum mill 100, that has a vessel assembly 105 mounted to a stationary frame or base assembly 110 and a grinding assembly 180 positioned in the vessel assembly 105. The grinding assembly 180 includes a first grinding ring 133 that has a first opening extending therethrough. The first opening is defined by a first radially inward facing grinding surface 129 and has a first area. The first grinding ring 133 is in sealing engagement with the inside surface of the vessel assembly 105. A shaft 182 is rotatably mounted to the frame 110, for example by suitable bearings. A hub 186 is mounted to one end of the shaft 182, for example via a key and keyway configuration. A plurality of arms 187 (e.g., spider plates) extend from the hub 186. The grinding assembly 180 includes a plurality of journal assemblies 188 as shown in detail in FIG. 7. One of the plurality of journal assemblies 188 is pivotally secured to each of the plurality of arms 187. The grinding assembly 180 includes a plurality of first rollers 189. One of the plurality of first rollers 189 is rotatingly coupled to each journal assembly 188. The method of retrofitting the roller mill includes removing the plurality of arms 187, the plurality of journal assemblies 188 and the plurality of first rollers 189 from the roller mill. The shaft 189 and the hub 186 may be employed in the retrofitted roller mill, modified or replaced with the hub 43 and shaft 39 illustrated in FIGS. 1A, 2A, 2E and 2F, for example. The method includes providing a sleeve 43C, a first support plate 52, a second support plate 54 and a plurality of second rollers 50 such as, for example, those shown in FIGS. 1A, 2A, 2E and 2F. The sleeve 43C is positioned over the shaft 39 and the sleeve 43C is secured to the shaft 39 via the hub 43. The method includes securing the first support plate 52 to the sleeve 43C, for example by welding and use of the gussets 47. The first support plate 52 has a first axially facing surface 52A that defines a second area A2. The method includes securing the second support plate 54 to the sleeve 43C, for example by welding. The second support plate 54 has a second axially facing surface 54A that defines a third area A3. The second support plate 54 is spaced axially apart from the first support plate 52. The method includes rotatably mounting the plurality of second rollers 50 to and between the first support plate 52 and the second support plate 54 so that each of the plurality of rollers 50 is configured to move between the first support plate 52 and the second support plate 54 as a result of rotation of the shaft, as shown and described herein with reference to FIG. 2D. Each of the plurality of rollers 50 has a radially outer surface 50X. The first support plate 52 and the second support plate 54 are of a non-circular shape such that the second area A2 of the first support plate 52 and the third area A3 of the second support plate 54 are of magnitudes which configure a flow area FA through the first opening 44 of at least 30 percent of the first area A1 to provide a predetermined quantity of heated air to remove moisture from the feed material in the grinding assembly 20A.
(71) In one embodiment, the method includes providing a first plow assembly 190 secured to the hub 186 by the plow support 191, as shown in FIG. 6. The first plow assembly 190 is removed from the pendulum mill 100. The method includes providing one or more second plow assemblies 70 and securing the second plow assembly 70 or assemblies to a bottom portion of the second support plate 54.
(72) In one embodiment, the method includes removing the first grinding ring 133 (FIG. 6) from the mill 100. A second grinding ring 32 is provided, such as that shown in FIGS. 1A, 2A, 2E and 2F. The second grinding ring 32 has the first opening defined by the first radially inward facing grinding surface 46 and has the first area A1. The first area A1 of the first and second grinding rings 133, 32 may be equal or different in magnitude. The method includes installing the second grinding ring 32 in sealing engagement with the inside surface of the vessel assembly.
(73) In one embodiment, the method includes installing the second grinding ring 32 in sealing engagement with the inside surface 20D of the vessel assembly 20.
(74) In one embodiment, the method includes adjusting the vertical position of the rollers 50 relative to the grinding ring 32, for example, with the use of the shim stack 43J.
(75) Although this invention has been shown and described with respect to the detailed embodiments thereof, it will be understood by those of skill in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In addition, modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiments disclosed in the above detailed description, but that the invention will include all embodiments falling within the scope of the appended claims.
