WO1996020789A1 - Improved rotor design - Google Patents
Improved rotor design Download PDFInfo
- Publication number
- WO1996020789A1 WO1996020789A1 PCT/NZ1995/000135 NZ9500135W WO9620789A1 WO 1996020789 A1 WO1996020789 A1 WO 1996020789A1 NZ 9500135 W NZ9500135 W NZ 9500135W WO 9620789 A1 WO9620789 A1 WO 9620789A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- guide edge
- template
- rock
- exit
- 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
- B02C19/00—Other disintegrating devices or methods
- B02C19/0012—Devices for disintegrating materials by collision of these materials against a breaking surface or breaking body and/or by friction between the material particles (also for grain)
- B02C19/0018—Devices for disintegrating materials by collision of these materials against a breaking surface or breaking body and/or by friction between the material particles (also for grain) using a rotor accelerating the materials centrifugally against a circumferential breaking surface
- B02C19/0031—Devices for disintegrating materials by collision of these materials against a breaking surface or breaking body and/or by friction between the material particles (also for grain) using a rotor accelerating the materials centrifugally against a circumferential breaking surface by means of an open top rotor
Definitions
- This invention relates to an improved rotor design.
- the first consideration is to achieve maximum force of impact either between the rocks or by the rocks on the impact plates and thus maximising crushing activity.
- the second design consideration is to have minimum wear on the parts of the rock crusher.
- An alternative rock crusher has an open top rotor as described in New Zealand Patent Application No. 242378. This has an annular bed or beds surrounding the central rotor. Rock fed into the rotor spins around the inside of the rotor and exits over the radial wall of the rotor.
- This rock has both vertical and horizontal components of movement but the exit velocity of the rock from an open top rotor is comparatively slower than that achieved with closed top rotors as described above.
- the guide edge can indirectly change the angular acceleration as a consequence of rock interacting with rock build-up formed under the guide edge.
- the present invention is directed towards providing a means by which greater exit velocities and hence greater rock impacts can be achieved with open top rotors, without the need to increase the speed of the rotor.
- the guide edge may come in a variety of forms.
- the guide edge may be part of a template which fits on the top of the rotor.
- the term template can be interpreted to mean a number of templates as well - depending on the context of the text.
- guide edge may take other forms, for instance it may be an integral part of the rotor, reference throughout the specification shall now be made to it as being part of a template.
- the template may have a variety of shapes.
- the template may be comprised of flat steel which defines a pentagonal aperture at the top of the rotor.
- the sides of the pentagon may each act as a guide edge serving to modify the travel of the rocks exiting the rotor.
- the rocks encountering the rock buildup under the sides of the pentagon are effectively collected and guided to the corners of the pentagon at the periphery of the rotor at which point the rocks exit the rotor.
- a prime number of exit points (such as that achieved by triagonal, pentagonal and heptagonal templates) has a greater stabilising effect on the rotor than any even number of exit points (as would be achieved with square or hexagonal shaped apertures). It should be appreciated that the prime number of exit points includes two exit points.
- the template defines a fully bounded aperture within the rotor, then the possible change of acceleration provided by the guide edge and its associated buildup is limited by the total radius of the rotor and the number of sides defined by the template.
- a pentagon having its points defined by a circle (such as the periphery of the rotor) has the angle of its side with respect to the circle defined by the circle.
- the aperture formed by the template on the rotor may not be a polygon having its points defined by a circle.
- the template may be continuous in that it has a border around the edge of the rotor, but in addition it also has guide edges which intrude closer to the central axis of the rotor than those provided by a template which has its points defined by the peripheral edge of the rotor.
- the guide edges are not continuous with each other and instead are provided by more than one template associated with the rotor.
- an open rotor may have five templates with guide edges which intrude closer to the central axis of the rotor than can be achieved by having a continuous template as described previously. This can provide a greater change in radius and therefore a greater exit velocity.
- some embodiments of the present invention incorporate a non-radial vane which extends substantially downwardly from the template into the body of the rotor.
- the provision of the vane has two main effects on the operation of the rotor.
- the first effect is that the vane in combination with the guide edge of the template retains and directs the rocks through the exit points (in the general vicinity where the guide edge meets the periphery of the rotor).
- a second effect of the vane is that in combination with the template, a pocket is formed within the rotor in which a certain amount of rock is trapped.
- This trapped rock forms a protective layer covering the inner circumference of the rotor and the adjacent surface of the vane, thus reducing the chances of these eroding as the result of direct contact from fresh rock entering the rotor.
- the vane does not extend towards the centre of the rotor further out than the edge of the template to which the vane is attached.
- the shape of the templates, their size and position relative to the centre of the rotor all depends upon a number of factors including rock density and size, the speed of the rotor, processing rate desired and the size of the tube feeding the rotor.
- one particular type of rock may require a feed tube which is approximately a minimum of 2.5 times the diameter of the rock being fed into the rotor.
- the corner template which intrudes furthest into the rotor may be a minimum clearance distance (say 10 mm) from the edge of the feed tube.
- the distance at the peripheral edge of the rotor between the two closest templates may then be a minimum of 1.5 times the maximum feed size entering the rotor.
- the guide edge is provided by a template as previously described which has portions that extend towards the centre of the rotor.
- the guide edge of the template has a line of symmetry which passes through the point of the guide edge which is closest to the centre of the rotor. For ease of reference this point shall be referred to as the innermost point of the template as opposed to the outermost point which is on the periphery of the rotor.
- Moving the innermost point as close to the centre of the rotor as possible enables the rock material entering the rotor to be channelled more accurately.
- the rock should impact on a build up of material not on the wear parts of the rotor. Moving the innermost point of the template ensures that the rock entering the rotor impacts on the build up of material some distance from the exit point of the rotor thus achieving the above objective.
- radial trail plates used. These may be vertical radial trail plates commonly used in rotors to adjust the rock wave build up in the rotor for different feeds and materials entering the rotor.
- the radial trail plates used are considerably smaller in size than those used for the non-radial vanes.
- Templates of various shapes may be used, but in preferred embodiments the template defines an aperture in the form of a clover leaf. /20789 PCI7NZ95/00135
- a clover leaf has rounded edges near the exit points which reduces the chances of fines building up or rocks wedging in the corner which could unbalance the rotor.
- an advantageous construction is a clover leaf aperture which is configured so that the exit points for the material within the rotor through the aperture are between 23° - 24° from the central axis of each leaf in the clover leaf aperture.
- an exit point greater than 24° causes the rock to flow over the top of the template.
- An exit point at less than 23' provides little build up of material and what build up there is, is undercut by exiting rock.
- the distributor plate at the bottom of the rotor is of similar shape to the template above it and thus acts as a wear part.
- the aforementioned embodiment has a number of advantages. Provision of a symmetrical template around the innermost point provides an even build up of material and a balanced rotor. Thus, less material and wear plates are required which leads to a less expensive rotor and a lighter one.
- Figures la & lb respectively illustrate a plan and cross-sectional view of a conventional open top rotor
- Figures 2a &2b respectively illustrate a plan and cross-sectional view of one embodiment of the present invention.
- Figures 3a &3b respectively illustrate a plan and cross-sectional view of an alternative embodiment of the present invention.
- Figure 4 is a three dimensional view of the embodiment illustrated in Figures 3a & 3b.
- Figure 5 is an exploded view of a rotor in accordance with a further embodiment of the present invention.
- Figure 6 illustrates wear parts for use with the embodiment of the present invention in Figure 5.
- Figures la and lb illustrate a conventional open rotor generally indicated by arrow 1.
- a feed tube (not illustrated) deposits rock at the distributor plate 2 whereby centrifugal force causes the rock 3 to bank up along the inner peripheral wall 4 of the rotor 1.
- the rock 3 provides protection for the wall 4 against the contact of fresh rocks entering the rotor 1.
- Fresh rock entering the rotor 1 tends to roll around the bank of rock 3 until it exits the rotor 1 at any point along the peripheral edge 5. Thus, there is no channelling of the rock towards a defined exit point.
- the rotor 6 illustrated in Figures 2a and 2b is substantially the same as the rotor 1.
- the main difference is that the rotor 6 also includes a template 7.
- the template 7 fits on the top of the rotor 6 and defines a pentagonal aperture 8.
- Rock entering the rotor 6 behaves in a similar manner to the rock entering the rotor 1 until it meets the build-up under guide edges 9 of the template 7.
- the build-up causes the rock to move from the position of least radial distance from the central axis of the rotor 6 (for example at point 10) to the position of greatest radial distance from the centre of the rotor 6 (for example point 11). It is at point 11 that the rock exits the rotor 6.
- the second effect is that by changing the angular acceleration of the rock, greater velocity is achieved of the rock exiting the rotor 6 leading to greater impacts.
- the rotor 12 illustrated in Figures 3a, 3b and 4 has similar advantages to that illustrated in figures 2a and 2b, but more so.
- the rotor 12 is essentially the same as the rotor 1 except that in addition it has a number of templates 13 to which are attached vertical vanes 14.
- the guide edges 15 of the templates 13 protrude further into the rotor 12 than the guide edges 9 of the rotor 6. This enables greater velocity of the rock to be achieved as a result of changing angular acceleration.
- the vertical vanes 14 in combination with the templates 13 serve to form a pocket into which rock collects. Not only does this provide wear protection for the inside 4 of the rotor 12, but also ensures that the rock is channelled by the guide edges 15 to the periphery 5 of the rotor 12.
- the rotor 21 consists of rotor shell 22 on top of which is fitted a template 23.
- the template 23 has a substantially clover leaf shaped aperture 24.
- the aperture 24 is not quite symmetrical about the innermost points 25 of the template 23. However, in some embodiments of the present invention it is necessary to include wear parts to protect the edges of the template. Suitable wear plates 28,29,30 for one embodiment of the present invention are shown in Figure 6 and it can be seen that the addition of the same effectively makes the template aperture 24 a symmetrical clover shape.
- the distributor plate 26 is in some embodiments a similar shape to the aperture 24 thus acting as a wear part for the bottom surface of the rotor 21.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP95941940A EP0796148A4 (en) | 1995-01-06 | 1995-12-21 | Improved rotor design |
NZ297910A NZ297910A (en) | 1995-01-06 | 1995-12-21 | Vertical axis impact crusher rotor guide edge positioned to influence acceleration of discharging material |
AU43187/96A AU703411B2 (en) | 1995-01-06 | 1995-12-21 | Improved rotor design |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NZ26094895 | 1995-01-06 | ||
NZ260948 | 1995-01-06 | ||
NZ27056895 | 1995-02-24 | ||
NZ270568 | 1995-02-24 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1996020789A1 true WO1996020789A1 (en) | 1996-07-11 |
Family
ID=26651348
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/NZ1995/000135 WO1996020789A1 (en) | 1995-01-06 | 1995-12-21 | Improved rotor design |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0796148A4 (en) |
AU (1) | AU703411B2 (en) |
WO (1) | WO1996020789A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0835690A1 (en) | 1996-10-11 | 1998-04-15 | Van der Zanden, Johannes Petrus Andreas Josephus | Method and device for synchronously impact milling of material |
US5911370A (en) * | 1996-09-04 | 1999-06-15 | Barmac Associates Limited | Rotary mineral breaker tip assembly and components therefor |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4090673A (en) * | 1977-02-18 | 1978-05-23 | Canica Crushers Ltd. | Centrifugal impact rock crushers |
US4151959A (en) * | 1978-01-30 | 1979-05-01 | Clifford E. Rawlings | Apparatus for comminuting pulverizable material |
DE2901769A1 (en) * | 1978-02-24 | 1979-09-06 | Voest Ag | IMPACT MILL FOR CRUSHING ROCK OR DGL. |
WO1989004720A1 (en) * | 1987-11-20 | 1989-06-01 | Impact Technology Limited | Machine for comminuting materials |
US4844365A (en) * | 1988-06-06 | 1989-07-04 | Rossouw Pieter J | Rotary impact crusher |
US4844364A (en) * | 1988-06-06 | 1989-07-04 | Rossouw Pieter J | Rotary impact crusher |
US4896838A (en) * | 1988-10-31 | 1990-01-30 | Cedarapids, Inc. | Rotor for vertical shaft impact crushers |
DE3826039A1 (en) * | 1988-07-30 | 1990-02-01 | Henkel Kgaa | WHEELMILL |
US5044567A (en) * | 1988-12-27 | 1991-09-03 | Thyssen Industrie Ag | Scrap crushing machine |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1963485A1 (en) * | 1969-04-30 | 1970-11-12 | Schwermaschb Kom Ernst Thaelma | Rotating centrifugal drum for centrifugal impact crusher |
US3834631A (en) * | 1973-04-18 | 1974-09-10 | T King | Spin breaking process |
AT370011B (en) * | 1981-03-05 | 1983-02-25 | Mannsberger E Masch App | IMPACT CRUSHERS OR -MILL |
-
1995
- 1995-12-21 EP EP95941940A patent/EP0796148A4/en not_active Withdrawn
- 1995-12-21 AU AU43187/96A patent/AU703411B2/en not_active Ceased
- 1995-12-21 WO PCT/NZ1995/000135 patent/WO1996020789A1/en not_active Application Discontinuation
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4090673A (en) * | 1977-02-18 | 1978-05-23 | Canica Crushers Ltd. | Centrifugal impact rock crushers |
US4151959A (en) * | 1978-01-30 | 1979-05-01 | Clifford E. Rawlings | Apparatus for comminuting pulverizable material |
DE2901769A1 (en) * | 1978-02-24 | 1979-09-06 | Voest Ag | IMPACT MILL FOR CRUSHING ROCK OR DGL. |
WO1989004720A1 (en) * | 1987-11-20 | 1989-06-01 | Impact Technology Limited | Machine for comminuting materials |
US4844365A (en) * | 1988-06-06 | 1989-07-04 | Rossouw Pieter J | Rotary impact crusher |
US4844364A (en) * | 1988-06-06 | 1989-07-04 | Rossouw Pieter J | Rotary impact crusher |
DE3826039A1 (en) * | 1988-07-30 | 1990-02-01 | Henkel Kgaa | WHEELMILL |
US4896838A (en) * | 1988-10-31 | 1990-01-30 | Cedarapids, Inc. | Rotor for vertical shaft impact crushers |
US5044567A (en) * | 1988-12-27 | 1991-09-03 | Thyssen Industrie Ag | Scrap crushing machine |
Non-Patent Citations (1)
Title |
---|
See also references of EP0796148A4 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5911370A (en) * | 1996-09-04 | 1999-06-15 | Barmac Associates Limited | Rotary mineral breaker tip assembly and components therefor |
EP0835690A1 (en) | 1996-10-11 | 1998-04-15 | Van der Zanden, Johannes Petrus Andreas Josephus | Method and device for synchronously impact milling of material |
Also Published As
Publication number | Publication date |
---|---|
AU4318796A (en) | 1996-07-24 |
AU703411B2 (en) | 1999-03-25 |
EP0796148A1 (en) | 1997-09-24 |
EP0796148A4 (en) | 1998-12-09 |
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