WO2008123910A1 - Conical-shaped impact mill - Google Patents
Conical-shaped impact mill Download PDFInfo
- Publication number
- WO2008123910A1 WO2008123910A1 PCT/US2008/002939 US2008002939W WO2008123910A1 WO 2008123910 A1 WO2008123910 A1 WO 2008123910A1 US 2008002939 W US2008002939 W US 2008002939W WO 2008123910 A1 WO2008123910 A1 WO 2008123910A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- mill
- impact
- conical
- casing
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
- B02C13/14—Disintegrating by mills having rotary beater elements ; Hammer mills with vertical rotor shaft, e.g. combined with sifting devices
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
- B02C13/14—Disintegrating by mills having rotary beater elements ; Hammer mills with vertical rotor shaft, e.g. combined with sifting devices
- B02C13/18—Disintegrating by mills having rotary beater elements ; Hammer mills with vertical rotor shaft, e.g. combined with sifting devices with beaters rigidly connected to the rotor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
- B02C13/26—Details
- B02C13/28—Shape or construction of beater elements
- B02C13/2804—Shape or construction of beater elements the beater elements being rigidly connected to the rotor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
- B02C13/26—Details
- B02C13/282—Shape or inner surface of mill-housings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
- B02C13/26—Details
- B02C13/286—Feeding or discharge
- B02C2013/28618—Feeding means
- B02C2013/28681—Feed distributor plate for vertical mill
Definitions
- the present invention is directed to a device for comminution of solids. More particularly, the present invention relates to a conically-shaped impact mill.
- Jet mills effectuate comminution by utilization of a working fluid which is accelerated to high speed using fluid pressure and accelerated venturi nozzles.
- the particles collide with a target, such as a deflecting surface, or with other moving particles in the chamber, resulting in size reduction.
- Operating speeds of jet milled particles are generally in the 150 and 300 meters per second range. Jet mills, although effective, cannot control the extent of comminution. This oftentimes results in the production of an excess percentage of undersized particles.
- Impact mills on the other hand, rely on centrifugal force, wherein particle comminution is effected by impact between the circularly accelerated particles, which are constrained to a peripheral space, and a stationary outer circumferential wall. Again, although control of particle size distribution is improved and can be manipulated compared to jet mills, the particle size range of the comminuted product of an impact mill is fixed by the dimensions of the device and other operating parameters. [0005] A major advance in impact mill design is provided by a design of the type disclosed in German Patent Publication 2353907.
- That impact mill includes a base portion which carries a rotor, mounted in a bearing housing having an upwardly aligned cylindrical wall portion coaxial with the rotational axis, and a mill casing which surrounds the rotor, defining a conical grinding path.
- the mill of this design includes a downwardly aligned cylindrical collar which may be displaced axially in the cylindrical wall portion and may be adjusted axially to set the grinding gap between the rotor and the grinding path.
- Impact mills when utilized in the communition of elastic particles, such as rubber, are usually operated at cryogenic temperatures, utilizing cryogenic fluids, in order to make feasible effective comminution of the otherwise elastic particles.
- cryogenic fluids such as liquid nitrogen
- this temperature gradient results in a rapid temperature rise of the particles.
- maximum comminution in an impact mill, or any other mill should begin immediately after particles freezing.
- impact mills including the conically shaped design discussed supra, initially require the particles to move outwardly toward the periphery before comminution begins.
- Three expedients are generally utilized to change the particle size of an elastic solid whose initial size is fixed.
- the first expedient employed in changing particle size is changing the feedstock temperature by contact with a cryogenic fluid, e.g. liquid nitrogen, to freeze the elastic solid particles to a crystalline state.
- a cryogenic fluid e.g. liquid nitrogen
- the coldest temperature achievable by the particles is limited to the temperature of the cryogenic fluid.
- a means of controlling particle temperature is to adjust the quantity of cryogenic fluid delivered to the elastic solid particles.
- a second expedient of changing product particle size is to alter the peripheral velocity of the rotor. This is usually difficult or impractical given the physical limits of the impact mill design.
- a third expedient of altering particle size is to change the grinding gap between the impact elements. Generally, this step requires a revised rotor configuration.
- a new impact mill has now been developed which addresses problems associated with conically-shaped impact, adjustable gap comminution mills of the prior art.
- the impact mill of the present invention provides means for initiation of comminution of solid particles therein at a lower cryogenic temperature than heretofore obtainable. That is, comminution in the impact mill of the present invention is initiated at the point of introduction of the solid particles into the impact mill even before the particles reach the grinding path formed between the rotor and the stationary mill casing utilizing the lowest particle temperature. Therefore, comminution efficiency is maximized.
- an impact mill which includes a base portion upon which is disposed a rotor rotatably mounted in a bearing housing.
- the conical shaped rotor has an upwardly aligned conical surface portion coaxial with the rotational axis.
- a plurality of impact knives are mounted on the conical surface.
- the impact mill is provided with an outer mill casing within which is located a conical track assembly which surrounds the rotor.
- the mill casing has a downwardly aligned cylindrical collar which may be axially adjusted to set a grinding gap between the rotor and the grinding track assembly.
- the top surface of the rotor is provided with a plurality of impact knives complimentary with a plurality of stationary impact knives disposed on the top inside surface of the mill casing.
- the impact mill of the present invention also addresses the issue of adjustability of comminution of different sizes and grades of selected solids. This problem is addressed by providing segmented internal conical grinding track sections which are provided with variable impact knive configurations. This solution also addresses maintenance and replacement issues.
- an impact mill in which a base portion disposed beneath a rotor rotatably mounted in a bearing housing.
- the conical shaped rotor has an upwardly aligned conical surface portion coaxial with a rotational axis.
- a plurality of impact knives are mounted on the conical surface.
- the impact mill is provided with an outer mill casing which supports a conical grinding track assembly which surrounds the rotor.
- the mill casing has a downwardly aligned cylindrical collar which may be axially adjusted to set a grinding gap between the rotor and the grinding track assembly wherein the mill casing is formed of separate conical sections.
- the internal grinding track assembly composed of separate conical sections offers the selection of alternate tooth configurations through a series of interlocking frustum cones. Each cone assembly configuration is selected to match a particular feedstock characteristic or desired comminuted end product. Each section of the grinding track assembly can increase or decrease the number of impacts with any peripheral velocity of rotary knives thus providing a matrix of operating parameters. The changing of the shape and angle of the conical grinding track assembly alters particle directions and provide additional particle- to-particle collisions. An ergonomic feature of this invention allows the replacement of worn or damaged frustum conical cones without the necessity of replacing the entire grinding track assembly.
- the impact mill of the present invention also addresses the issue of effective power transmission without accompanying noise pollution.
- an impact mill is provided with a base portion upon which is disposed a rotor rotably mounted in a bearing assembly.
- the conical shaped rotor has an upwardly aligned conical surface portion coaxial with the rotational axis.
- a plurality of impact knives are mounted on the conical surface.
- the impact mill is provided with an outer mill casing which supports a conical grinding track assembly which surrounds the rotor.
- the mill casing has a downwardly aligned cylindrical collar which may be axially adjusted to set a grinding gap between the rotor and the grinding track assembly.
- the rotor shaft of the impact mill is provided with a sprocketed drive sheave wherein the rotor is rotated by a synchronous sprocketed belt, in communication with a power source, accommodated on the sprocketed drive sheave.
- FIG. 1 is an axial sectional view of the impact mill of the present invention
- FIG. 2 is an axial sectional view of a portion of the impact mill demonstrating feedstock introduction therein;
- FIG. 3 is a plan view of impact knives disposed on the top of the upper housing section of the impact mill and on the top of the rotor;
- FIG. 4a, 4b and 4c are plan views of rotating and stationary impact knife arrays of alternate configurations shown in Fig. 3;
- FIG. 5a, 5b and 5c are cross sectional views, taken along plane A-A of FIGS. 4a and 4b, demonstrating three impact knife designs;
- FIG. 6 is a sectional view of an embodiment of a rotor of an outer concentric grinding track of the impact mill
- FIG. 7 is a sectional view showing alignment of a typical interconnected grinding track
- FIG. 8 is a schematic representation of a transmission means for rotating the rotor of the impact mill.
- FIG. 9 is an isometric view of a synchronous belt and a sprocketed drive sheave in communication with said belt utilized in the transmission of power to the impact mill.
- An impact mill 100 includes three housing sections: a lower base portion section Ia, a center housing section Ib and a top housing section Ic.
- the lower base portion section Ia carries a bearing housing 2 in which a rotor 3 is rotatably mounted.
- the center housing section Ib is concentrically nested 7 in the lower housing section Ia and provides concentric vertical alignment for the upper housing section Ic.
- a plurality of bolts 8 is provided for the detachable connection of the two housing sections.
- the top housing section 1 c provides a concentric tapered nest for a conical grinding track assembly 5.
- the conical grinding track assembly 5 is securely connected to the top housing section Ic at its lower end 6.
- the rotor 3 is driven by a motor 34 by means of a belt 32 and a sheave 4 provided at the lower end of the rotor shaft.
- the top section Ic includes the conical grinding track assembly 5.
- the grinding track assembly 5 has the shape of a truncated cone. Grinding track assembly 5 surrounds rotor 3 such that a grinding gap S is formed between grinding knives 3 a fastened to rotor 3 and the grinding track assembly 5.
- the top section Ic also includes a downwardly aligned cylindrical collar 11 which may be displaced axially within the center housing section Ib. The cylindrical collar 11 forms an integral component of the top section Ic.
- An outwardly aligned flange 12 is provided at the upper end of the cylindrical collar 11.
- a plurality of spacer blocks 14 is disposed between flange 12 and a further flange 13 which is disposed at the upper end of center section Ib.
- spacer blocks 14 define the axial setting between flanges 12 and 13. Therefore, spacer blocks 14 define the width of the grinding gap S. As such, this width is adjustable.
- Cryogenically frozen feedstock 18 enters the impact mill 100 through entrance 20 by means of a path, defined by top 16 of upper housing section Ic, which takes the feedstock 18 to a labyrinth horizontal space 40 between the upper section Ic and rotor 3.
- Feedstock 18 moves to the peripheral space defined by gap S by means of centrifugal force through a path defined by the inner housing surface of the top 16 of the upper housing section Ic and the top portion 17 of rotor 3.
- the feedstock 18 is at its minimum temperature as it enters horizontal space 40.
- impact knives 19, connected to the top portion 17 of rotor 3, as well as the stationary impact knives 21 , disposed on the inner housing surface of the top 16 of upper housing section Ic, provide immediate comminution of the feedstock 18, which in prior art embodiments were subject to later initial comminution in the absence of the plurality of impact knives 19 and 21.
- impact knives 19 and 21 are disposed in a radial direction outwardly from axial axis A to the circumferential edge on the top portion 17 of rotor 3 and the inner housing surface of top 16 of top housing section 1 c. It is preferred that three to seven knife radii be provided. In one particularly preferred embodiment, impact knives 21 are radially positioned on the inner housing surface of top 16 of the top housing section Ic and impact knives 19 are positioned on top portion 17 of rotor 3 in five equiangular radii, 72° apart from each other.
- greater numbers of impact knives such as six knive radii, 60° apart or seven knive radii, 51.43° apart, may also be utilized, hi addition, a lesser number of impact knives, such as three knife radii, 120° apart, may similarly be utilized.
- impact knives 21 and 19 disposed on the inner housing surface of top 16 of upper housing section Ic and the top portion 17 of rotor 3, respectively, are identical.
- Their shape may be any convenient form known in the art.
- a tee-shape 21b or 19b, a curved tee-shape 21a or 19a or a square edge 21c or 19c may be utilized.
- the impact knives 21 and 19 may also have tapered tips to maximize impact efficiency.
- the taper may be any acute angle 23. An angle of 30°, for example, is illustrated in the drawings.
- Impact knives 19 are fastened to the top portion 17 of rotor 3 and impact knives 21 are fastened to the inner housing surface of top 16 of upper housing section Ic.
- Frozen feedstock 18 is charged into mill 100 by means of a stationary funnel 24, which is provided at the center of inner housing surface of top 16 of upper housing section Ic. Feedstock 18 immediately encounters the top portion 17 of rotor 3 and is accelerated radially and tangentially. In this radial and tangential movement feedstock 18 encounters the plurality of stationary and rotating impact knives 21 and 19. This impact, effected by the rotating knives, shatters some of the radially accelerated feedstock 18 as it disturbs the flow pattern so that turbulent radial and tangential solid particle flow toward the stationary knives results.
- feedstock 18 After impact in the aforementioned space, denoted by reference numeral 40, feedstock 18 continues its turbulent radial and tangential movement toward the series of rotating knives 3 a mounted on the outer rim of the rotor 3. These impacts increase the tangential release velocity as feedstock 18 undergoes its final particle size reduction within conical grinding path 10 whose volume is controlled by gap S.
- the conically shaped impact mill 100 utilizes a conical grinding track assembly formed of separate conical sections.
- This design advance permits a series of mating interlocking frustum cones to alter the grinding track pattern within mill 100.
- each conical grinding track assembly section 5 is selected to match a particular feedstock or desired end product.
- Each section of the assembly 5 is provided with alternate impact knife configurations which provides capability of either increasing or decreasing the number of impacts to which feedstock 18 is subjected.
- the adjustment of the shape and angle of the impact surfaces of the conical assembly sections 5 also permit alteration of the direction of the feedstock particles.
- Another advantage of this preferred embodiment of mill 100 is economic. The replacement of worn or damaged conical sections, without the requirement of replacing the entire conical assembly, reduces maintenance costs.
- Interconnection of the conical grinding track assembly sections 5 may be provided by any connecting means known in the art.
- One such preferred design utilizes key interlocks, as illustrated in Figure 7.
- complementary shapes of sections 26 and 27 result in an interlocking assembly.
- sections 26 and 27 are interlocking mating frustum cones.
- impact mill 100 is divided into a plurality of sections.
- the drawings illustrate a typical design, a plurality of three sections: a top section 26, a middle section 27 and a bottom section 28 with the grinding track assembly secured in place at its lower end 6. This configuration allows for the external adjustment of the grinding gap by adding or subtracting spacer blocks 14.
- impact mill 100 includes a power transmission means which provides direct power transmission at lower noise levels than heretofore obtainable.
- noise associated therewith is reduced by up to about 20 dbA.
- a synchronous sprocketed belt 32 accommodated on a sprocketed drive sheave 4 on rotor 3, effectuates rotation of rotor 3.
- the belt 32 is in communication with a power source, such as engine 34, which rotates a shaft 35 that terminates at a sheave 30, identical to sheave 4.
- belt 32 is provided with a plurality of helical indentations 33 which engage helical teeth 31 on sheaves 4 and 30.
- the chevron-like design allows for the helical teeth 31 to gradually engage the sprocket instead of slapping the entire tooth all at once. Moreover, this design results in self-tracking of the drive belt and, as such, flanged sheaves are not required.
- a power source which may be engine 34, turns shaft 35 connected thereto.
- Shaft 35 is fitted with sheave 30, identical to sheave 4.
- the belt 32 communicates between sheaves 4 and 30, effecting rotation of rotor 3. Substantially all contact between belt 32 and sheaves 4 and 30 occurs by engagement of teeth 31 of the sheaves with grooves 33 of belt 32 which significantly reduces noise generation.
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- Engineering & Computer Science (AREA)
- Food Science & Technology (AREA)
- Crushing And Pulverization Processes (AREA)
Abstract
Description
Claims
Priority Applications (9)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP14179367.9A EP2818247B1 (en) | 2007-04-05 | 2008-03-05 | Conical-shaped impact mill |
ES08726465.1T ES2559419T3 (en) | 2007-04-05 | 2008-03-05 | Tapered Impact Mill |
CN2008800160662A CN101687196B (en) | 2007-04-05 | 2008-03-05 | Conical-shaped impact mill |
JP2010502076A JP5520810B2 (en) | 2007-04-05 | 2008-03-05 | Conical impact mill |
CA2682728A CA2682728C (en) | 2007-04-05 | 2008-03-05 | Conical-shaped impact mill |
AU2008236851A AU2008236851C1 (en) | 2007-04-05 | 2008-03-05 | Conical-shaped impact mill |
EP08726465.1A EP2139603B1 (en) | 2007-04-05 | 2008-03-05 | Conical-shaped impact mill |
MX2009010770A MX2009010770A (en) | 2007-04-05 | 2008-03-05 | Conical-shaped impact mill. |
BRPI0809965-0A BRPI0809965B1 (en) | 2007-04-05 | 2008-03-05 | IMPACT MILL IN CONICAL FORM |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/784,032 | 2007-04-05 | ||
US11/784,032 US7900860B2 (en) | 2007-04-05 | 2007-04-05 | Conical-shaped impact mill |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008123910A1 true WO2008123910A1 (en) | 2008-10-16 |
Family
ID=39826115
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2008/002939 WO2008123910A1 (en) | 2007-04-05 | 2008-03-05 | Conical-shaped impact mill |
Country Status (10)
Country | Link |
---|---|
US (1) | US7900860B2 (en) |
EP (2) | EP2139603B1 (en) |
JP (1) | JP5520810B2 (en) |
CN (1) | CN101687196B (en) |
AU (1) | AU2008236851C1 (en) |
BR (1) | BRPI0809965B1 (en) |
CA (1) | CA2682728C (en) |
ES (2) | ES2559419T3 (en) |
MX (1) | MX2009010770A (en) |
WO (1) | WO2008123910A1 (en) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2377618A1 (en) * | 2010-04-14 | 2011-10-19 | Air Products And Chemicals, Inc. | Rotary impact mill |
US9339148B2 (en) | 2010-08-31 | 2016-05-17 | Healthy Foods, Llc | Supply assembly for a food homogenizer |
US9282853B2 (en) | 2010-08-31 | 2016-03-15 | Healthy Foods, Llc | Food homogenizer |
US8550390B2 (en) | 2010-08-31 | 2013-10-08 | Healthy Foods, Llc | Food based homogenizer |
DE102011050789A1 (en) * | 2011-06-01 | 2012-12-06 | RoTAC GmbH | Device for the mechanical separation of material conglomerates from materials of different density and / or consistency |
FR2982519B1 (en) * | 2011-11-10 | 2020-02-21 | Arkema France | PROCESS OF CRUSHING POLYARYL ETHER CETONES |
KR101336713B1 (en) | 2013-05-28 | 2013-12-04 | 성안이엔티주식회사 | Screw cone crusher and mill |
US10675634B2 (en) | 2015-08-13 | 2020-06-09 | Lehigh Technologies, Inc. | Systems, methods, and apparatuses for manufacturing micronized powder |
CN105618214B (en) * | 2016-03-14 | 2018-07-27 | 蔡惠文 | A kind of ring crush device for staged helical conveyer crushing plant |
CA3037967A1 (en) * | 2016-09-23 | 2018-03-29 | Seed Terminator Holdings PTY LTD | A multistage hammer mill and a residue processing system incorporating same |
CN107930805A (en) * | 2017-11-21 | 2018-04-20 | 嘉善信息技术工程学校 | A kind of pulverizer crushing part |
CN107744860A (en) * | 2017-11-21 | 2018-03-02 | 嘉善信息技术工程学校 | A kind of feed grinder |
JP6544672B1 (en) * | 2018-02-13 | 2019-07-17 | 株式会社ティーフォース | Dry crusher |
CN108855310A (en) * | 2018-05-12 | 2018-11-23 | 福建省中坚环保科技有限公司 | A kind of novel environment friendly machinery solid waste treatment device |
CN112387388A (en) * | 2020-10-27 | 2021-02-23 | 羊彬 | Powder block crushing device |
CN113522449B (en) * | 2021-09-13 | 2021-12-14 | 徐州鼎和固废工程技术研究院有限公司 | Kitchen garbage crushing treatment device |
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GB780748A (en) * | 1953-08-07 | 1957-08-07 | Peter Willems | Improvements in and relating to mills particularly granulating and colloiding mills |
US4022749A (en) * | 1964-05-18 | 1977-05-10 | Entoleter, Inc. | Formation of composite particulate material using high energy rotary impact milling |
US4117984A (en) * | 1977-05-16 | 1978-10-03 | Olin Corporation | Granulator with beater bar and deflector |
EP0787528A1 (en) | 1996-02-01 | 1997-08-06 | Josef Fischer | Vortex mill |
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US626125A (en) * | 1899-05-30 | Feed-mill | ||
US31492A (en) * | 1861-02-19 | William stewart | ||
US447596A (en) * | 1891-03-03 | Grinding-mill | ||
US283518A (en) * | 1883-08-21 | Grinding-mill | ||
US2738930A (en) * | 1949-10-31 | 1956-03-20 | Equip Ind Et Laitiers Soc D | Dispersion machine with preliminary comminuting system and a plurality of dispersion systems of different constructional form |
US3155326A (en) * | 1962-04-16 | 1964-11-03 | Richard E Rhodes | Ore pulverizer and sizing device |
JPS5139823Y2 (en) * | 1971-06-25 | 1976-09-29 | ||
DE2353907C3 (en) * | 1973-10-27 | 1980-01-31 | Krauss-Maffei Ag, 8000 Muenchen | Impact mill |
DE2736349A1 (en) * | 1977-08-12 | 1979-02-22 | Krauss Maffei Ag | Plastic or fibrous material crusher - has wear resistant liner rings with sharp cutting edges on recesses producing rasping effect |
JPS634451U (en) * | 1986-02-10 | 1988-01-12 | ||
JP2000126629A (en) * | 1998-10-22 | 2000-05-09 | Ishikawajima Harima Heavy Ind Co Ltd | Metal separating device |
JP2000250279A (en) * | 1999-03-03 | 2000-09-14 | Fuji Xerox Co Ltd | Image forming device |
JP2000346138A (en) * | 1999-06-01 | 2000-12-12 | Bando Chem Ind Ltd | Toothed belt, timing belt pulley for toothed belt, toothed belt transmission, toothed belt manufacturing device, and manufacture of toothed belt |
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-
2007
- 2007-04-05 US US11/784,032 patent/US7900860B2/en active Active
-
2008
- 2008-03-05 CN CN2008800160662A patent/CN101687196B/en not_active Expired - Fee Related
- 2008-03-05 BR BRPI0809965-0A patent/BRPI0809965B1/en active IP Right Grant
- 2008-03-05 EP EP08726465.1A patent/EP2139603B1/en not_active Not-in-force
- 2008-03-05 JP JP2010502076A patent/JP5520810B2/en not_active Expired - Fee Related
- 2008-03-05 EP EP14179367.9A patent/EP2818247B1/en active Active
- 2008-03-05 ES ES08726465.1T patent/ES2559419T3/en active Active
- 2008-03-05 WO PCT/US2008/002939 patent/WO2008123910A1/en active Application Filing
- 2008-03-05 CA CA2682728A patent/CA2682728C/en not_active Expired - Fee Related
- 2008-03-05 ES ES14179367T patent/ES2735350T3/en active Active
- 2008-03-05 MX MX2009010770A patent/MX2009010770A/en active IP Right Grant
- 2008-03-05 AU AU2008236851A patent/AU2008236851C1/en not_active Ceased
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB780748A (en) * | 1953-08-07 | 1957-08-07 | Peter Willems | Improvements in and relating to mills particularly granulating and colloiding mills |
US4022749A (en) * | 1964-05-18 | 1977-05-10 | Entoleter, Inc. | Formation of composite particulate material using high energy rotary impact milling |
US4117984A (en) * | 1977-05-16 | 1978-10-03 | Olin Corporation | Granulator with beater bar and deflector |
EP0787528A1 (en) | 1996-02-01 | 1997-08-06 | Josef Fischer | Vortex mill |
Non-Patent Citations (1)
Title |
---|
See also references of EP2139603A4 |
Also Published As
Publication number | Publication date |
---|---|
EP2139603A1 (en) | 2010-01-06 |
BRPI0809965B1 (en) | 2020-03-10 |
CA2682728A1 (en) | 2008-10-16 |
JP2010523313A (en) | 2010-07-15 |
EP2818247B1 (en) | 2019-05-08 |
CN101687196A (en) | 2010-03-31 |
AU2008236851C1 (en) | 2013-12-05 |
EP2818247A1 (en) | 2014-12-31 |
MX2009010770A (en) | 2010-05-19 |
BRPI0809965A2 (en) | 2018-04-03 |
ES2735350T3 (en) | 2019-12-18 |
US7900860B2 (en) | 2011-03-08 |
CA2682728C (en) | 2015-10-27 |
JP5520810B2 (en) | 2014-06-11 |
US20080245913A1 (en) | 2008-10-09 |
AU2008236851B2 (en) | 2013-03-14 |
EP2139603B1 (en) | 2015-11-18 |
EP2139603A4 (en) | 2014-01-29 |
CN101687196B (en) | 2012-05-30 |
AU2008236851A1 (en) | 2008-10-16 |
ES2559419T3 (en) | 2016-02-12 |
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