CA1089428A - Centrifugal mill - Google Patents
Centrifugal millInfo
- Publication number
- CA1089428A CA1089428A CA288,301A CA288301A CA1089428A CA 1089428 A CA1089428 A CA 1089428A CA 288301 A CA288301 A CA 288301A CA 1089428 A CA1089428 A CA 1089428A
- Authority
- CA
- Canada
- Prior art keywords
- grinding drum
- rocker
- drum
- centrifugal mill
- mill according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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
- B02C17/00—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls
- B02C17/04—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls with unperforated container
- B02C17/08—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls with unperforated container with containers performing a planetary movement
Landscapes
- Engineering & Computer Science (AREA)
- Food Science & Technology (AREA)
- Crushing And Grinding (AREA)
- Preparation Of Compounds By Using Micro-Organisms (AREA)
- Polysaccharides And Polysaccharide Derivatives (AREA)
- Grinding Of Cylindrical And Plane Surfaces (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE:
A centrifugal mill comprising a cylindrical grinding drum, which rotates about its own drum axis and simultaneously revolves on a circular orbit around a stationary axis of revolu-tion, which is parallel to the drum axis, at a constant angular velocity ratio, whereby the grinding drum is mounted in a substan-tially horizontal position in at least one rocker, each limb of the rocker is mounted in an eccentric bearing, each eccentric bearing is secured to an eccentric driving shaft, the eccentric driving shafts are provided with counterweights and are mounted in bearings, a charging device is, provided on one end portion of the grinding drum and a discharge device is provided at the other end portion, characterized in that the grinding drum is mounted in at least one U-shaped rocker, a bearing is provided at a lower portion of the at least one U-shaped rocker, the bearing being rigidly connected in vertical direction to the lower portion and being movable in all other directions, two abatments are associated with the respective limbs of the at least one rocker, the grinding drum being mounted between the two abatments.
A centrifugal mill comprising a cylindrical grinding drum, which rotates about its own drum axis and simultaneously revolves on a circular orbit around a stationary axis of revolu-tion, which is parallel to the drum axis, at a constant angular velocity ratio, whereby the grinding drum is mounted in a substan-tially horizontal position in at least one rocker, each limb of the rocker is mounted in an eccentric bearing, each eccentric bearing is secured to an eccentric driving shaft, the eccentric driving shafts are provided with counterweights and are mounted in bearings, a charging device is, provided on one end portion of the grinding drum and a discharge device is provided at the other end portion, characterized in that the grinding drum is mounted in at least one U-shaped rocker, a bearing is provided at a lower portion of the at least one U-shaped rocker, the bearing being rigidly connected in vertical direction to the lower portion and being movable in all other directions, two abatments are associated with the respective limbs of the at least one rocker, the grinding drum being mounted between the two abatments.
Description
'Jt~
The present invention relates to a centrifugal mill and particularly to a centrifugal mill comprising a cylindrical grind-ing drum, which rotates about its own drum axis and simultaneously revolves on a cricular orbit around a stationary axis of revolution, which is parallel to the drum axis, at a constant anguIar velocity ratio.
Centrifugal mills for intermittent pilot operation have been described in "Rock Product", February 1951, pages 93-97.
Printed German Application 10 13 946 describes a cen-trifugal mill which is used for batch operation and in which the distance betwèen the drum axis and the axis of revolution'is less than the radius of the grinding drum so that'there is allegedly no critical or limited speed of revolution of the mill. The - critical velocity is the velocity above which the material being ' ' ground and the grinding elements form under the action of centrifugal force a covering on the wall of the grinding drum so that ~here is no longer a grinding action. On the other hand, the spacing of ~' the drum axis and the axis of revolution by a distance which is j~ smaller than the radius of the grinding drum does not in itself ensure sub-critical conditions and a high grinding rate. '' The present invention provides a centrifugal mill which enables a continuous operation in the sub-critical range at '~
a high grinding rate per unit of volume of the grinding drum and ' in which the grinding drum is readily accessible and can be replaced ~ ' quickly and simply and in which a simple mounting for the drum is provided and the transmission of uncontrolled stresses'and vibra-tion is avoided while the structural expenditure is small.
According to the present invention, there is provided '~
a'centrifugal mill comprising a cylindrical grinding drum, which rotates about its own drum axis and simultaneously revolves on a circular orbit'around a stationary axis of revolution, which is ~J~
': . '~ . :
~''3~
parallel to the drum axis, at a constant angular velocity ratio, whereby the grinding drum is mounted in substantially horizontal position in at least one rocker, each limb of the rocker is mounted in an eccentric bearing, each eccentric bearing is secured to an eccentric driving shaft, the eccentric driving shafts are provided with courlterweights and are mounted in bearings, a charging device is provided on one end portion of the grinding drum and a discharge device is provided at the other end portion, characterized in that~
- said grinding drum is mounted in at least one U-shaped rocker, ~ a bearing is provided at a lower portion of said at least one ` U-shaped rocker, said bearing being rigidly connected in ver-tical direction to said lower portion and being movable in all ~ `
other directions, ~` -- two abatments are associated with the respective limbs of said ;~
at least one rocker, said grinding drum being mounted between said two abatments. ~;
, The limbs of the U-shaped rocker may extend at right -~
;~ angles or at another angle to the lower portion of ~he rocker or -may extend along arcs of circles to the lower portion of the rocker.
;~ Alternatively, the entire rocker may have the configuration of an arc of a circle.
The bearing in the lower portian of the rocker may :i `
consist of a ball-type pivot bearing or of a pin having a suitable ~ play on that side of the bearing which faces the :r r .
' ` .~. -2-r ~:
-;
grinding drum and on which the ~earing is connected to the grinding drum. That side of the bearing which faces the lower portion of the rocker may be suitably connected to the rocker - by a screw-threaded joint.
The abu-tments provided on the limbs of the rocker extend suitably horizontally but may alternately be somewhat inclided.
There is either a small play between the abutments and the grinding drum or the abutments contact the grinding ~ 10 drum.
! The eccentric bearings may consist suitably of roller-type pivot bearings.
The drive shafts may ~e suitably connected to one or more trancmissions by highly elastic couplings, which are torsionally rigid, and these transmissions may be driven by one motor or a pl~rality of motors< Where two transmissions ff are provided, they must be coupled to each other so that a synchronous operation of both eccentric shafts is ensured.
According to a preferred feature, the bearings of 'f one eccentric-driving shaft are pivotally connected to a base frame at one point. This ensures that manufacturing tolerances of the rockers and levers cannot result in additional loads ~` on these parts.
According to another preferred feature, one abutment ~1 of each rocker consists of a resilient bearing. The resiliency .f~, of the bearings may be due to the provision of springs or of pneumatic or hydraulic means. This ensures that the grinding ~ drum is held by a defined force and that a transmission of `~ forces due to thermal expansion to the rockers is avoided.
According to another preferred feature, one abutment of each rocker is provided with a sensor for measuring the reaction force of the grinding drum. The sensor consists ` ~ _ 3 _ ., :, ~ . . .
B
suitably of a load cell. Such arrangemen-t enables a simple and accurate monitoring and automatic control of the operating conditions of the grinding drum.
According to another preferred feature the grinding drum is mounted in two interconnected rockers. Two rockers constitute a structurally simple, satisfactory holder. The connection between the rockers prevents a parallel displacement thereof.
A preferred embodiment of the invention will be explained more fully and by way of example with reference to the drawings, in which Fig. 1 is a top plan view showing a mill, ~ ~-Fig. 2 is a side elevation showing a mill viewed from its discharge side, -`
Fig. 3 is a side elevation like Fig. 2 but partly in section and Fig. 4 shows the mechanical movement of the rocker and of the grinding drum.
The illustrated grinding drum 1 has a smooth lining. -In practice, however, lifting bars are provided on the inside or a lining is provided which has an irregular surface so that the movement of the material to be ground in the drum is improved. These means are not shown for the sake of clearness.
The grinding drum 1 is mounted in two U-shaped rockers 2, 2a, which have limbs extending at right angles to the lower portion of the rocker. The bearing 3 provided in the lower portion of each of the rockers 2, 2a is designed to be rigid in the vertical direction and to be movable in all other ; directions. On the side facing the grinding drum 1, the bearing ' 30 3 consists of a ball-type pivot bearing. On its side facing ~` the lower portion of each rocker 2, 2a, the bearing 3 is screw-connected to the lower portion by means of a screw-~ :, .
threaded pin, which extends through the bearing, and lock nuts.
As a result, the bearing 3 is vertically rigid and is movable in all other directions owing to the provision of the ball-type pivot bearing.
Two abutmen-ts 4, 5 are secured -to the inside of the limbs of each of the rockers 2, 2a. The abutments 4 on one side constitute resilient bearings comprising built-in springs.
The abutments 5 on the other side are provided with load cells 18. The bearings 3, 4 and 5 retain the grinding drum 1 at its end walls 22, 23. When it is desired to remove the drum 1, it is sufficient to eliminate the screw connections of the bearings 3. The limbs of the roc]cers 2, 2a are mounted in respective eccentric bearings 6, 7, which consist of self-aligning roller bearings~ The eccentric bearings 6, 7 are secured to respective ...
eccentric-driving shafts 8, 9, which are provided with counter- ~ .
weights 10, 11 an~l mounted in bearings 12, 13, 14, 15. Lead plates 24 are mounted in the counterweights 10, 11 and may be .
used to control the mass of the counterweights 10, 11~ The ::
bearings 12, 13 are firmly screw-connected to the base frame 16.
The bearings 14, 15 are pivoted to the base frame 16 by pins having centers 17. The lower portions of the two rockers 2, 2a are interconnected by a flanged tube 19. The eccentric-driving shafts 8, 9 are connected to the transmission and drive unit by couplings 24, 25.
Fig. 4 shows only the rocker 2, the grinding drum 1, the eccentric-driving shafts 8, 9, and the eccentric bearings 6l 7. The di3tances between t:he centers 26 of the eccenbric-driving sha.fts 8, 9 and the centers 27 of the eccentric bearings 6, 7 define the radii of the circular orbits of revolution G.
In the embodiment shown by way of example, the ratio of the diameter of the circular orbits of revolution G to the inside diameter D of the grincling drum is about 0.4. The distance between the axis 28 of the grinding drum 1 and the imaginary stationary axis of revolution 29 of the gringind drum 1 is smaller than the radius of the grinding drum 1. ~`
The advant~ges afforded by the invention reside in that -owing to the rat~o R = -1 (R being the ratio of the angular ~ -velocity of the grinding drum 1 on the circular orbit about the stationary axis of revolution to the angular velocity of the grinding drum about its own drum axis) a particularly high grinding :~
rate is ensured, the centrifugal forces are equal at all points ~`
of the cross~section of the grinding drum, and the vectors of j acceleration àt all points are parallel and have the same direc- ~.
tion, that the mill operates always in the sub-critical range even at a high grinding rate, the design ensures an exactly . circular motion in a simple manner, the grinding drum can be.
.. mounted and replaced quickly and simply wlthout need for a high ~ :
expenditure of work, the shut-down tlmes are short, a satisfac-tory mounting and holding of the grinding drum is ensured with a small structural expenditure, a transmission of uncontrolled ~:. vibration to the rockers and other parts is avoi.ded, the grinding ~.
drum and the charging and emptying devices are well accessible, ` and additional drive means Eor rotating the grinding drum on its ;
own axis are not rèquired.
` ,~
,:
.~ ' . ~ ;. ~-3;.`i.
',"3 '`:
,:, , ., _ j; -6-
The present invention relates to a centrifugal mill and particularly to a centrifugal mill comprising a cylindrical grind-ing drum, which rotates about its own drum axis and simultaneously revolves on a cricular orbit around a stationary axis of revolution, which is parallel to the drum axis, at a constant anguIar velocity ratio.
Centrifugal mills for intermittent pilot operation have been described in "Rock Product", February 1951, pages 93-97.
Printed German Application 10 13 946 describes a cen-trifugal mill which is used for batch operation and in which the distance betwèen the drum axis and the axis of revolution'is less than the radius of the grinding drum so that'there is allegedly no critical or limited speed of revolution of the mill. The - critical velocity is the velocity above which the material being ' ' ground and the grinding elements form under the action of centrifugal force a covering on the wall of the grinding drum so that ~here is no longer a grinding action. On the other hand, the spacing of ~' the drum axis and the axis of revolution by a distance which is j~ smaller than the radius of the grinding drum does not in itself ensure sub-critical conditions and a high grinding rate. '' The present invention provides a centrifugal mill which enables a continuous operation in the sub-critical range at '~
a high grinding rate per unit of volume of the grinding drum and ' in which the grinding drum is readily accessible and can be replaced ~ ' quickly and simply and in which a simple mounting for the drum is provided and the transmission of uncontrolled stresses'and vibra-tion is avoided while the structural expenditure is small.
According to the present invention, there is provided '~
a'centrifugal mill comprising a cylindrical grinding drum, which rotates about its own drum axis and simultaneously revolves on a circular orbit'around a stationary axis of revolution, which is ~J~
': . '~ . :
~''3~
parallel to the drum axis, at a constant angular velocity ratio, whereby the grinding drum is mounted in substantially horizontal position in at least one rocker, each limb of the rocker is mounted in an eccentric bearing, each eccentric bearing is secured to an eccentric driving shaft, the eccentric driving shafts are provided with courlterweights and are mounted in bearings, a charging device is provided on one end portion of the grinding drum and a discharge device is provided at the other end portion, characterized in that~
- said grinding drum is mounted in at least one U-shaped rocker, ~ a bearing is provided at a lower portion of said at least one ` U-shaped rocker, said bearing being rigidly connected in ver-tical direction to said lower portion and being movable in all ~ `
other directions, ~` -- two abatments are associated with the respective limbs of said ;~
at least one rocker, said grinding drum being mounted between said two abatments. ~;
, The limbs of the U-shaped rocker may extend at right -~
;~ angles or at another angle to the lower portion of ~he rocker or -may extend along arcs of circles to the lower portion of the rocker.
;~ Alternatively, the entire rocker may have the configuration of an arc of a circle.
The bearing in the lower portian of the rocker may :i `
consist of a ball-type pivot bearing or of a pin having a suitable ~ play on that side of the bearing which faces the :r r .
' ` .~. -2-r ~:
-;
grinding drum and on which the ~earing is connected to the grinding drum. That side of the bearing which faces the lower portion of the rocker may be suitably connected to the rocker - by a screw-threaded joint.
The abu-tments provided on the limbs of the rocker extend suitably horizontally but may alternately be somewhat inclided.
There is either a small play between the abutments and the grinding drum or the abutments contact the grinding ~ 10 drum.
! The eccentric bearings may consist suitably of roller-type pivot bearings.
The drive shafts may ~e suitably connected to one or more trancmissions by highly elastic couplings, which are torsionally rigid, and these transmissions may be driven by one motor or a pl~rality of motors< Where two transmissions ff are provided, they must be coupled to each other so that a synchronous operation of both eccentric shafts is ensured.
According to a preferred feature, the bearings of 'f one eccentric-driving shaft are pivotally connected to a base frame at one point. This ensures that manufacturing tolerances of the rockers and levers cannot result in additional loads ~` on these parts.
According to another preferred feature, one abutment ~1 of each rocker consists of a resilient bearing. The resiliency .f~, of the bearings may be due to the provision of springs or of pneumatic or hydraulic means. This ensures that the grinding ~ drum is held by a defined force and that a transmission of `~ forces due to thermal expansion to the rockers is avoided.
According to another preferred feature, one abutment of each rocker is provided with a sensor for measuring the reaction force of the grinding drum. The sensor consists ` ~ _ 3 _ ., :, ~ . . .
B
suitably of a load cell. Such arrangemen-t enables a simple and accurate monitoring and automatic control of the operating conditions of the grinding drum.
According to another preferred feature the grinding drum is mounted in two interconnected rockers. Two rockers constitute a structurally simple, satisfactory holder. The connection between the rockers prevents a parallel displacement thereof.
A preferred embodiment of the invention will be explained more fully and by way of example with reference to the drawings, in which Fig. 1 is a top plan view showing a mill, ~ ~-Fig. 2 is a side elevation showing a mill viewed from its discharge side, -`
Fig. 3 is a side elevation like Fig. 2 but partly in section and Fig. 4 shows the mechanical movement of the rocker and of the grinding drum.
The illustrated grinding drum 1 has a smooth lining. -In practice, however, lifting bars are provided on the inside or a lining is provided which has an irregular surface so that the movement of the material to be ground in the drum is improved. These means are not shown for the sake of clearness.
The grinding drum 1 is mounted in two U-shaped rockers 2, 2a, which have limbs extending at right angles to the lower portion of the rocker. The bearing 3 provided in the lower portion of each of the rockers 2, 2a is designed to be rigid in the vertical direction and to be movable in all other ; directions. On the side facing the grinding drum 1, the bearing ' 30 3 consists of a ball-type pivot bearing. On its side facing ~` the lower portion of each rocker 2, 2a, the bearing 3 is screw-connected to the lower portion by means of a screw-~ :, .
threaded pin, which extends through the bearing, and lock nuts.
As a result, the bearing 3 is vertically rigid and is movable in all other directions owing to the provision of the ball-type pivot bearing.
Two abutmen-ts 4, 5 are secured -to the inside of the limbs of each of the rockers 2, 2a. The abutments 4 on one side constitute resilient bearings comprising built-in springs.
The abutments 5 on the other side are provided with load cells 18. The bearings 3, 4 and 5 retain the grinding drum 1 at its end walls 22, 23. When it is desired to remove the drum 1, it is sufficient to eliminate the screw connections of the bearings 3. The limbs of the roc]cers 2, 2a are mounted in respective eccentric bearings 6, 7, which consist of self-aligning roller bearings~ The eccentric bearings 6, 7 are secured to respective ...
eccentric-driving shafts 8, 9, which are provided with counter- ~ .
weights 10, 11 an~l mounted in bearings 12, 13, 14, 15. Lead plates 24 are mounted in the counterweights 10, 11 and may be .
used to control the mass of the counterweights 10, 11~ The ::
bearings 12, 13 are firmly screw-connected to the base frame 16.
The bearings 14, 15 are pivoted to the base frame 16 by pins having centers 17. The lower portions of the two rockers 2, 2a are interconnected by a flanged tube 19. The eccentric-driving shafts 8, 9 are connected to the transmission and drive unit by couplings 24, 25.
Fig. 4 shows only the rocker 2, the grinding drum 1, the eccentric-driving shafts 8, 9, and the eccentric bearings 6l 7. The di3tances between t:he centers 26 of the eccenbric-driving sha.fts 8, 9 and the centers 27 of the eccentric bearings 6, 7 define the radii of the circular orbits of revolution G.
In the embodiment shown by way of example, the ratio of the diameter of the circular orbits of revolution G to the inside diameter D of the grincling drum is about 0.4. The distance between the axis 28 of the grinding drum 1 and the imaginary stationary axis of revolution 29 of the gringind drum 1 is smaller than the radius of the grinding drum 1. ~`
The advant~ges afforded by the invention reside in that -owing to the rat~o R = -1 (R being the ratio of the angular ~ -velocity of the grinding drum 1 on the circular orbit about the stationary axis of revolution to the angular velocity of the grinding drum about its own drum axis) a particularly high grinding :~
rate is ensured, the centrifugal forces are equal at all points ~`
of the cross~section of the grinding drum, and the vectors of j acceleration àt all points are parallel and have the same direc- ~.
tion, that the mill operates always in the sub-critical range even at a high grinding rate, the design ensures an exactly . circular motion in a simple manner, the grinding drum can be.
.. mounted and replaced quickly and simply wlthout need for a high ~ :
expenditure of work, the shut-down tlmes are short, a satisfac-tory mounting and holding of the grinding drum is ensured with a small structural expenditure, a transmission of uncontrolled ~:. vibration to the rockers and other parts is avoi.ded, the grinding ~.
drum and the charging and emptying devices are well accessible, ` and additional drive means Eor rotating the grinding drum on its ;
own axis are not rèquired.
` ,~
,:
.~ ' . ~ ;. ~-3;.`i.
',"3 '`:
,:, , ., _ j; -6-
Claims (17)
1. A centrifugal mill comprising a cylindrical grinding drum, which rotates about its own drum axis and simultaneously revolves on a circular orbit around a stationary axis of revolu-tion, which is parallel to the drum axis, at a constant angular velocity ratio, whereby the grinding drum is mounted in a substan-tially horizontal position in at least one rocker, each limb of the rocker is mounted in an eccentric bearing, each eccentric bearing is secured to an eccentric driving shaft, the eccentric driving shafts are provided with counterweights and are mounted in bearings, a charging device is provided on one end portion of the grinding drum and a discharge device is provided at the other end portion, characterized in that:
- said grinding drum is mounted in at least one U-shaped rocker, - a bearing is provided at a lower portion of said at least one U-shaped rocker, said bearing being rigidly connected in ver-tical direction to said lower portion and being movable in all other directions, - two abatments are associated with the respective limbs of said at least one rocker, said grinding drum being mounted between said two abatments.
- said grinding drum is mounted in at least one U-shaped rocker, - a bearing is provided at a lower portion of said at least one U-shaped rocker, said bearing being rigidly connected in ver-tical direction to said lower portion and being movable in all other directions, - two abatments are associated with the respective limbs of said at least one rocker, said grinding drum being mounted between said two abatments.
2. A centrifugal mill according to claim 1, wherein said grinding drum is mounted in two U-shaped rockers.
3. A centrifugal mill according to claim 1, wherein said rocker has limbs extending at right angles to the lower portions of said rocker.
4. A centrifugal mill according to claim 2, wherein a bearing is provided at the lower portion of each rocker.
5. A centrifugal mill according to claim 1 or 4, wherein said bearing consists of a ball-type pivot bearing.
6. A centrifugal mill according to claim 1 or 4, wherein said bearing is screw-connected to said lower portion by means of a screw-threaded pin, which extends through the bearing, and lock nuts.
7. A centrifugal mill according to claim 1, wherein one of the abutments located on one side of the grinding drum constitute resilient bearings comprising built-in springs and the abutments located on the other side of the grinding drum are provided with load cells.
8. A centrifugal mill according to claim 1, wherein the distance between the drum axis and the axis of revolution is smaller than the radius of the grinding drum, a drive mechanism is provided for rotating the grinding drum about the drum axis and for revolving the grinding drum on the circular orbit about the stationary axis of revolution, and wherein the ratio of the diameter G of the circular orbit to the inside diameter D of the grinding drum is between 0.3 and 1.0, the ratio R of the angular velocity of the grinding drum on the circular orbit about the stationary axis of revolution to the angular velocity of the grinding drum about its own drum axis being equal to R = -1.
9. A centrifugal mill according to claim 1, characterized in that the bearings of one eccentric-driving shaft are pivoted to a base frame at a point.
10. A centrifugal mill according to claim 2, characterized in that one abutment of each rocker is pivoted with a sensor for measuring the reaction force of the grinding drum.
11. A centrifugal mill according to claim 1, characterized in that the grinding drum is mounted in two rockers, which are interconnected by a flanged tube.
12. A centrifugal mill according to claim 1, wherein said rocker has limbs which extend along arcs of circles to the lower portion of the rocker.
13. A centrifugal mill according to claim 1, wherein said rocker have the configuration of an arc of a circle.
14. A centrifugal mill according to claim 1, wherein there are plays between said two abutments and said grinding drum.
15. A centrifugal mill according to claim 1, wherein said two abutments contacts said grinding drum.
16. A centrifugal mill according to claim 1, wherein said eccentric bearings arc roller-type pivot bearings.
17. A centrifugal mill according to claim 1, wherein said driving shaft is connected to at least one transmission by highly elastic couplings, which are torsionably rigid.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP26475785 | 1976-10-21 | ||
| DE2647578A DE2647578C2 (en) | 1976-10-21 | 1976-10-21 | Centrifugal mill |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1089428A true CA1089428A (en) | 1980-11-11 |
Family
ID=5991022
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA288,301A Expired CA1089428A (en) | 1976-10-21 | 1977-10-07 | Centrifugal mill |
Country Status (11)
| Country | Link |
|---|---|
| JP (1) | JPS6057376B2 (en) |
| AT (1) | AT357850B (en) |
| BE (1) | BE859952A (en) |
| CA (1) | CA1089428A (en) |
| DE (1) | DE2647578C2 (en) |
| FR (1) | FR2368300A1 (en) |
| GB (1) | GB1586851A (en) |
| IT (1) | IT1086907B (en) |
| NO (1) | NO144285C (en) |
| SE (1) | SE425551B (en) |
| ZA (1) | ZA775871B (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5029760A (en) * | 1989-10-26 | 1991-07-09 | Gamblin Rodger L | Centrifugal grinding and mixing apparatus |
| US5205499A (en) * | 1989-10-26 | 1993-04-27 | Gamblin Rodger L | Planetary grinding apparatus |
| US5375783A (en) * | 1993-05-03 | 1994-12-27 | Gamblin; Rodger L. | Planetary grinding apparatus |
| WO2011000048A1 (en) * | 2009-07-02 | 2011-01-06 | John Charles Turner | A centrifugal grinding system |
| US8603441B2 (en) | 2008-09-12 | 2013-12-10 | Indiana Nanotech Llc | Functionalized calcium phosphate hybrid systems for confectionery and foodstuff applications |
| US9205036B2 (en) | 2007-01-31 | 2015-12-08 | Robert Karlinsey | Dental composition |
| US10130561B2 (en) | 2006-01-31 | 2018-11-20 | Robert L. Karlinsey | Functionalized calcium phosphate hybrid systems for confectionery and foodstuff applications |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3224098A1 (en) * | 1982-06-29 | 1983-12-29 | Metallgesellschaft Ag, 6000 Frankfurt | Centrifugal mill with horizontal, cylindrical grinding drum |
| JPS6253748A (en) * | 1985-09-02 | 1987-03-09 | 株式会社徳寿工作所 | Horizontal revolving type grinder |
| GB2257379B (en) * | 1991-07-09 | 1995-04-19 | Ecc Int Ltd | Comminution in a planetary mill |
| US7513843B2 (en) * | 2005-04-18 | 2009-04-07 | Borgwarner Inc. | Mechanical chain tensioner with ratcheting device |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2650033A (en) * | 1948-06-14 | 1953-08-25 | F S Smidth & Co | Method and apparatus for vibratory grinding |
| AT188194B (en) * | 1952-06-26 | 1957-01-10 | Kaspar Engels | Process for grinding and mixing grist by means of a planetary ball mill and planetary ball mill to carry out this process |
| GB730494A (en) * | 1953-02-11 | 1955-05-25 | Frank Limb O B E | Improvements in and relating to ball mills and like rotary chamber apparatus |
| DE2631826A1 (en) * | 1975-09-10 | 1977-03-24 | Chamber Of Mines Services Ltd | CENTRIFUGAL MILL |
-
1976
- 1976-10-21 DE DE2647578A patent/DE2647578C2/en not_active Expired
-
1977
- 1977-06-30 AT AT467277A patent/AT357850B/en not_active IP Right Cessation
- 1977-07-15 NO NO772528A patent/NO144285C/en unknown
- 1977-08-12 FR FR7724904A patent/FR2368300A1/en active Granted
- 1977-10-03 ZA ZA00775871A patent/ZA775871B/en unknown
- 1977-10-07 CA CA288,301A patent/CA1089428A/en not_active Expired
- 1977-10-17 GB GB43171/77A patent/GB1586851A/en not_active Expired
- 1977-10-18 IT IT28712/77A patent/IT1086907B/en active
- 1977-10-19 SE SE7711792A patent/SE425551B/en not_active IP Right Cessation
- 1977-10-20 BE BE6046185A patent/BE859952A/en not_active IP Right Cessation
- 1977-10-20 JP JP52126390A patent/JPS6057376B2/en not_active Expired
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5029760A (en) * | 1989-10-26 | 1991-07-09 | Gamblin Rodger L | Centrifugal grinding and mixing apparatus |
| US5205499A (en) * | 1989-10-26 | 1993-04-27 | Gamblin Rodger L | Planetary grinding apparatus |
| US5375783A (en) * | 1993-05-03 | 1994-12-27 | Gamblin; Rodger L. | Planetary grinding apparatus |
| US10130561B2 (en) | 2006-01-31 | 2018-11-20 | Robert L. Karlinsey | Functionalized calcium phosphate hybrid systems for confectionery and foodstuff applications |
| US9205036B2 (en) | 2007-01-31 | 2015-12-08 | Robert Karlinsey | Dental composition |
| US8603441B2 (en) | 2008-09-12 | 2013-12-10 | Indiana Nanotech Llc | Functionalized calcium phosphate hybrid systems for confectionery and foodstuff applications |
| WO2011000048A1 (en) * | 2009-07-02 | 2011-01-06 | John Charles Turner | A centrifugal grinding system |
Also Published As
| Publication number | Publication date |
|---|---|
| NO144285C (en) | 1981-08-19 |
| FR2368300A1 (en) | 1978-05-19 |
| AT357850B (en) | 1980-08-11 |
| IT1086907B (en) | 1985-05-31 |
| JPS6057376B2 (en) | 1985-12-14 |
| NO144285B (en) | 1981-04-27 |
| SE425551B (en) | 1982-10-11 |
| NO772528L (en) | 1978-04-24 |
| SE7711792L (en) | 1978-04-22 |
| FR2368300B1 (en) | 1982-04-02 |
| DE2647578A1 (en) | 1978-05-03 |
| DE2647578C2 (en) | 1982-06-09 |
| BE859952A (en) | 1978-04-20 |
| ZA775871B (en) | 1978-05-30 |
| GB1586851A (en) | 1981-03-25 |
| ATA467277A (en) | 1979-12-15 |
| JPS5351567A (en) | 1978-05-11 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |