Vertical shaft type impact crusher

Abstract: A combination of anvils (32) with deadstock spaces (34) enables the an extension in the lifetimes of the tips mounted on a rotor. A combination of hard tips (72L1) with soft tips (72L2) overcomes the inconsistency where the hard tips (72L1) are easy to be chipping-worn but ordinarily hard to be worn by collision with stones of a large grain size accelerated by the rotor, while the soft tips (72L2) are hard to be chipping-worn but ordinarily easy to be worn by collision with stones of a small grain size accelerated by the rotor. Crushers have anvils (32) and dead stock spaces (34). Crushers still have a pair of hard tips and soft tips mounted on a reversibly rotatable rotor. The pair of hard tips and soft tips are located in symmetry with respect to one of the center lines (L,M,N) in the angular orientations with respectively equal angular intervals, the center lines extending from the axis line of the rotor in the radial direction.

Description: The invention relates to a vertical shaft type impact crusher according to the preamble of the claim. An impact crusher of this type is known from the US-A-4 844 354. Particularly, the invention relates to an impact crusher for crushing bulk materials, for example natural rock, into grains or particles of desired size. Bulk materials, e.g., natural rock, are crushed in accordance with various uses, for example, aggregate for concrete, paving stone, subgrade material, etc. One type of crusher used for such a crushing process is known as a vertical shaft type impact crusher. Impact crushers operate on the basis of the principle that rock is accelerated at a high speed so as to collide with an impact surface, thereby crushing the rock. Such impact crushers may be generally divided into two types according to the mode of crushing: anvil type and dead stock type. The anvil type impact crusher includes a rotor having a plurality of wings or blades on the upper side thereof being rotated at a high speed, whereby raw stones cast into the crusher are accelerated by the blades and centrifugally discharged so as to collide with anvils which are disposed in a ring shape around the rotor, thereby crushing the raw stones. Such an anvil type impact crusher is mainly used for the purpose of crushing raw stones having a relatively large diameter by collision to thereby reduce the size of the raw stones. On the other hand, the dead stock type impact crusher is mainly used to smooth surfaces of raw stones which has already been crushed into gravel of desired size and to make the grain size uniform. Such a dead stock type impact crusher is similar to the anvil type impact crusher in that raw stones are accelerated by blades, but different from the latter in that dead stocks are formed from crushed raw stones at the periphery of the rotor, and the surfaces having angles of rest formed by this dead stock are used as impact surfaces for crushing raw stones. Aggregate for concrete is nedded to be made of crushed stone of a large grain size and crushed sand of small grain size. According to JIS(Japanese Industrial Standard), it is needed for both stone and sand to be in given definite grain size distributions. The distribution of Crushed Stone JIS 5005 is defined as the weight-percentage of stones passing through sieves as follows: 60mm 100%; 50mm 95 100%; 25mm 35 70%; 15 mm 10 30%; 5 mm 0 5%;. It is difficult for the anvil type impact crusher to produce stones of a large grain size and to produce stones in good shapes, while it is difficult for the dead stock type impact crusher to produce stones of a small grain size. A further problem is in that tips are worn by accelerated stones. A rotor is provided with pairs of tips mounted on the wings thereof. Stones of a large size, the diameter of which is larger than 40 mm, generate more chipping-wearing than stones of a small size. Material harder to chip is preferably applied for tips which are used in a crusher for crushing stones of a large size. Stones of small size, the diameter of which is smaller than 40 mm, generate more ordinal wearing than stone of a large size. A higher degree of wear-resistant material is preferably applied for tips which are used in a crusher for crushing stones to a small size. As such, there is an inconsistency in the tips used in impact crushers for large sized stone-crushing and those used for small sized stone-crushing. Summary of the Invention An object of the present invention is to provide a vertical shaft type impact crusher for crushing stones of various sized which overcomes the inconsistency of stones of a large size generating more chipping-wearing than those of a small size, thereby material hard to chip being preferably applied for tips which are used in a crusher for crushing stones of a large size while stones of a small size generate more ordinal wearing than stones of a large size, thereby a higher degree of wear-resistant material being preferably applied for tips which are used in a crusher for crushing stones of a small size. Another object of the present invention is to provide a vertical shaft type impact crusher for crushing stones of various sizes which has a high production efficiency. To comply with these objects, the impact crusher according to the invention is characterized by the features of the claim. In one aspect of the invention, the vertical shaft type impact crushers have a rotor mounted on a casing body and which is reversely rotatable for giving thrown stones centrifugal force. The crushers have dead stock spaces for crushed stones to be accumulated therein. The dead stock spaces are located in the circumferential area around the rotor. Anvils for crushing stones discharged from the rotor are mounted in the circumferential area around the rotor. The respective anvils are located between said respective dead stock spaces with respective intervals given in the peripheral direction around the rotor which includes multiple pairs of tips, the respective pairs of tips being located in symmetry with respect to central lines extending radially from the axis line of the rotor in equal angular intervals. Respective tips of the pairs which point forward in the rotational direction with respect to the respective center lines, when the rotor is rotated in the anti-clockwise direction, are made of hard material in comparison with the tips of the pairs which point backward in the rotational direction with respect to the respective center lines, said backward pointing tips being made of soft material in comparison with the above hard material. In the vertical shaft type impact crushers of the present invention, stones are crushed by collision with not only anvils but also dead stocks. The dead stocks are formed with the respective angles of rest. Some stones are smoothed by the dead stocks, while the other stones are crushed into stones of a small grain size. Stones of a large size collide with less hard tips, while stones of a small size collide with harder tips. The wearing of harder tips brought about by the collision with stones of a large size is less because of the regularly rotational direction. The wearing of softer tips brought about by the collision with stones of a small size is less because of the reversely or irregularly rotational direction. The other aspects and operations of the present invention are explained in detail through emobodiments of the present invention in what follows. Brief Description of the Drawings Fig.1 is a top view of a first embodiment of a vertical shaft type impact crusher in accordance with the present invention. Fig.2 is a cross-sectional view of the crusher of Fig.1. Fig.3 is a top view of a dead stock space of another embodiment. Fig.4 is a horizontal cross-sectional view of Fig.1. Fig.5 is a vertical cross-sectional view of the rotor of the crusher of Fig.1. Detailed Description of Embodiments Referring now to the figures, an embodiment of a veritcal shaft-type impact crusher constructed in accordance with the present invention is described in what follows. Figs. 1 and 2 illustrate a vertical shaft-type impact crusher. A casing 1 includes a casing body 1a and a covering lid 1b. Covering lid 1b is rotatably mounted on the upper portion of the casing body 1a by means of a mounting means( not shown ). Covering lid 1b is opened and closed relative to the casing body 1a by means of a lever 5 which rotates together with a rotating axis and is forced upwardly and downwardly by a hydraulic cylinder 4. Covering lid 1b has a shooting opening 2. Two guiding shoots 7 and 8 are located at respective lower positions of the shooting opening 2, affixed to the suspended portion of the casing body 1a. Lower guiding shoot 8 is attached to a multiple number of vertically suspended libs 8a located on a circular line. Vertically suspended libs 8a are provided as a portion of the casing body 1a. A rotor 10 is located under the guiding shoot 8. Rotor 10 is mounted on a top surface of the vertical rotating shaft 11. Vertical rotating shaft 11 is rotably supported in an axle-housing 15 through bearings 13 and 14. Axle-housing 15 is mounted on the casing body 1a through brackets 16. A pulley 17 is attached to the lower portion of the vertical rotating shaft 11. Pulley 17 is connected to a reversible motor( not shown ) through a belt( not shown ). Vertical rotating shaft 11 is rotated back and forth in response to the operation of the motor. Rotor 10 includes a rotor body 21, a distributing cone-like body 22, three wings 23, 23, 23 and three pairs of liners 24. Distributing cone-like body 22 is mounted on the upper side of the central portion of the rotor body 21. Respective three wings 23, 23, 23 are adjustably provided in three angular orientations with respective equal angular intervals of 120 degrees there between. Respective pairs of liners are respectively placed between the respective wings of the respective 120 degrees-angular intervals. Casing 1 is generally a square in the sectional view. As shown in Fig.1, four protecting liners 40 are fixedly mounted on the respective inner side surfaces of the respective walls constructing the casing 1. A dead stock forming plate 30 is horizontally disposed in the casing body 1a. Dead stock forming plate 30 is designed as a square plate of which the circumferential edge portion is affixed against the inner surface of the casing body 1a. As shown Fig.1, dead stock forming plate 30 has a circular opening 31, the diameter of which is designed to be larger than that of the rotor 10. Circular opening 31 and rotor10 have a common central axis-line. Four anvils 32a, 32b, 32c, 32d are located upwardly apart from the dead stock forming plate 30. Respective anvils 32a, 32b, 32c, 32d have respective anvil members 33 affixed to the respective central portions of the inner surfaces of the casing body 1a. Each anvil member is made of an ordinary wear-resitant material, e.g., manganese steel. The location of anvils 32 creates four dead stock spaces 34a, 34b, 34c, 34d to be formed therebetween. Respective dead stock spaces 34a, 34b, 34c, 34d are respectively provided as four coneer portions partly forming the inner space of the casing 1. Each horizontal distance between each anvil and the rotor 10 is adjustable as follows. Spacers 35 are replaceably inserted between the respective surfaces of the casing body 1a and the respective anvil members. The number of the spacers 35 enables the above distance in the horizontal direction to be adjustable. The volume of the dead stock spaces 34a, 34b, 34c, 34d are also adjustable as follows. As shown in Figs 1 and 2, diameter-adjusting ring 36 is located at the circumferential edge of the circular openig 31. Adjusting ring 36 is in the circumferential direction divided into a multiple of pieces of segments 37. Each segment is replaceably affixed to the dead stock forming plate 30 by means of each bolt 38. Each flange 41 is formed as each inner circumferential edge portion of the respective segment 37. Many kinds of segment groups, the radiuses of which are different from one another, are allowable to be prepared. The replacement of the segment group allows the above volumes of the dead stock spaces 34 to be altered. A multiple number of one-body rings may be used for alternation of the ring diameter. Another embodiment of a diameter-adjusting ring is illustrated in Fig.3. A segment 37 has an elongated hole 37a extending in the radial direction. The mounting position of the segment 37 relative to the dead stock forming plate 30 is aligned in the radial direction. Each segment is secured to the dead stock forming plate 30 by means of a bolt( not shown in Fig.3 ) passing through the elongated hole 37a. In this case, a space is formed between the neighborhood relation of segments 37,37. Such a space does not cause any trouble, each space being filled with crushed rocks. Figs.4 and 5 illustrate the detailed structure of rotor 10. A liner 50 to protect the rotor body 21 is fittedly mounted on the outer periphery of the rotor body 21. Liner 50 is bolted to the rotor body. A flat plane 52 is formed as the top surface of the distributing cone-like body in the center of the upper side of the distributing cone-like body 22. The outer periphery of the distributing cone-like body 22 is formed to be tapered as a tapered surface 53 around the rotor axis line. A circular recess 54 is formed on the lower side of the distributing cone-like body 22. Recess 30 engages with a circular step portion 55 formed on the top surface of the rotor body 21, thereby causing the distributing cone-like body 22 to be located at the proper position. The distributing cone-like body 22 has a bore 56 in the center thereof, allowing an engaging portion of a suspending means( not shown ) to be engaged therewith during assembly and disassembly. Each wing 23 includes respective support 57. Supports 57 are fixedly mounted on the rotor body 21. Supports 57 are disposed on the outer peripheral zone around the distributing cone-like body 22. Supports 57 are provided as three bodies disposed in the three angular orientations with the respectively equal angular intervals of 120 degrees therebetween. Each supports 57 includes a radially extending portion 58, circumferentially extending portion 59 and a plate portion 60. Radially extending portion 58 extends in the radial direction on the rotor body 21, while the circumferentially extending portion 59 generally extends in the circumferential back-and-forth directions on the rotor body 21 from the outer portion of the radially extending portion 58. By means of the plate portion 60 are secured in one body the radially extending portion 58 to the circumferentially extending portion 59. Discharge passage liners 24 are located between a pair of supports 57,57 with the above descrived respective angular intervals. There is a projection 61 provided on the lower side of the discharge passage liner 24. Projection 61 is fitted into a recess 62 provided on the upper side of the rotor body 21, thereby effecting the positioning of the discharge passage liner 24. When the discharge passage liner 24 is disposed on the rotor body 21 with the distributing cone-like body 22 placed at the proper position, a notch portion 63 is engaged with the discharge passage liner 24. This causes the distributing cone-like body 22 to press the discharge passage liner 24 against the rotor body 21. A first wall liner 64 is fixedly mounted on the outside of the support 57. Studbolts 65 as screwed portions in one body are provided with the first wall liner 64. Nuts are fittedly inserted into the studbolts 65 of the first wall liner 64, by which the first wall liner 64 is secured to the circumferentially extending portion 59 of the supports 57. On the circumferentially extending portion 59 of the supports 57 are mounted second wall liners 66, third wall liner 67 and outer tip plates 68. Studbolts 71 as screwed portions in one body are provided with the second wall liner 66. Third wall liner 67 is secured at the medium position between the second wall liner 66 and the circumferentially extending portion 59 by means of the studbolts 71 and nuts( not shown ) fitted into the studbolts 71. As shown in Fig.4, super-hardness tips or non-super-hardness tips 72 are mounted on the base body 69 of the outer tip plates 68. Non-super-hardness tip 72 is made of hard steel or hard alloy, e.g., Cr-steel, Ni-Cr-steel, that is, more easily worn but hard to chip because of its pliability. The expression "to be hard to chip" means, in strength of material, that chipping wear is comparably less. On the other hand, the expression "super-hardnes" in Japanese wording means that the super-hardness of steel or super-hardness of alloy is not easier to wear but is easier to chip. The expression "to be easy to chip" means, in strength of material, that chipping wear is comparably more. Examples of super-hard alloys are known as sintered alloys, included in WC-Co series, WC-TiC-Co series, WC-TiC-TaC( NbC )-Co series, TaC-Ni series, Cr - Ni series that are correspondent in hardness to diamond and made by means of a sintering method where Fe-composition combined with soft carbide is molded under pressure and sintered after molding. It is apparent from the above definition that not only alloy is applied for super-hardness tips, but fine ceramics is also. Two circumferentially extending portions 59 extending in the circumferential back-and-forth directions are the same in structure. Inner tip plates 73 are disposed on the inner peripheral portion of the supports 57. Innner tip plates 73 are U-shaped with the radially extending portion 58 conceived thereby. Each inner tip plate 73 includes an inside tip and right and left side tips. These tips are made of material of the same kind as the above material for tips 72, that is super-hardness alloy or non-super-hardness alloy as described above. In the state where inner tip plate 73 is mounted on the support 57, the lower portion of the inside tip plate 73 is engaged with the chipping portion of the distributing cone-like body 22. Support 57 is covered by means of a top covering plate 77. A step portion 78 for positioning is designed on the lower side of the top covering plate 77. Step portion 78 is fitted into the recess designed on the plate portion 60 of the support 57, thereby the top covering plate 77 is positioned at the proper engaged position. A downwardly bended portion 79 is designed as an inner side edge of the top covering plate 77. Inner tip plate 73 is secured to and between the downwardly bended portion 79 and the distributing cone-like body 22.Top covering plate 77 is affixed to the plate portion 60 of the support 57 and the base body 69 of the outer tip plates 68 by means of a bolt 80 and another bolts( not shown ) at four positions. Fig.4 illustrates three center lines L,M,N which are in different angular positions. Line L is different from line M by 120 degrees. Line M is different from Line N by 120 degrees. Line N is different from Line L by 120 degrees. Respective center lines L,M and N are identical to the center lines of the respective radially extending portions 58,58,58 of the supports and are perpendicular to the axis line K of the rotor 10, meeting at one point on the axis line K. The three rotor portions 10LM, 10MN and 10NL of the rotor 10 between one voluntary center line and the 2 other center lines next to it and between the 2 other center lines are substantially congruent to each other. Wings 23L has symmetry with respect to the center line L. Wing 23M has symmetry with respect to the center line M. Wings 23N has symmetry with respect to the center line N. As an example, the base bodies 69 are given as a set of two base bodies 69L1 and 69L2 that are symmetrical in circumference with respect to the center line L. The other base bodies 69 are given as a set of two base bodies 69M1 and 69M2 that are symmetrical in circumference with respect to the center line M. The still other base bodies 69 are given as a set of two base bodies 69N1 and 69N2 that are symmetrical in circumference with respect to the center line N. As such, all parts included in the rotor 10 are located in symmetry with respect to the center line L,M or N. Such symmetry is needed for high speed rotation of the rotor 10. The tips 72 are fixedly mounted on the two respective base bodies 69L1 and 69L2 as a set of two tips 72L1 and 72L2 that are symmetrical to each other with respect to the center line L. The other tips 72 are fixedly mounted on the respective two base bodies 69M1 and 69M2 as a setof two tips 72M1 and 72M2 that are symmetrical to each other with respect to the center line M. The still other tips 72 are fixedly mounted on the respective two base bodies 69N1 and 69N2 as a set of two tips 72N1 and 72N2 that are symmetrical to each other with respect to the center line N. According to such a location of the tips, tip 72L1 and tip 72M2 are located in the rotor portion 10LM, tip 72M1 and tip 72N2 are located in the rotor portion 10MN and tip 72N1 and tip 72L2 are located in the rotor portion 10NL. One group of tips 72L1, 72M1 and 72N1 that have the respective phases identical with one another in the rotational direction are made of super-hardness material as defined above. The other group of tips 72L2, 72M2 and 72N2 that have the respective phases identical with one another in the rotational direction are made of ordinal material that is non-super-hardness material as defined above. One group of tips 72L1, 72M1,72N1 and the other group of tips 72L2, 72M2, 72N2 are all replaceable. It is not so necessary to apply a super-hardness-tip for the inner tips 73. Dead spaces 91L, 91M and 91N are given in the respective wings 23L, 23M and 23N on the both sides in the rotational(circumferential) direction. One group of dead spaces 91L1, 91M1 and 91N1 are in the same phase in the rotational direction. The other group of dead spaces 91L2, 91M2 and 91N2 are in the same phase in the rotational direction. Dead spaces 91L1 and dead spaces 91L2 are in the respective phases different from each other. Dead space 91L1 and dead space 91L2 are in symmetry with respect to the center line L. Dead space 91M1 and dead space 91M2 are in symmetry with respect to the center line M. Dead space 91N1 and dead space 91N2 are in symmetry with respect to the center line N. Each dead space is located between one of the wings 23 and one of the discharge passage liners 24. ( Operation of the Embodiment ) Rotor 10 is driven at a high speed by a driving motor ( not shown ). Raw rocks are thrown down onto the rotor from the shooting opening 2 through the guiding shoots 7 and 8. The thrown raw rocks are distributed by the distributing cone-like body 22 towards any of the discharge passages formed between the respective two neighboring wings. Such distributed raw rocks are accelerated with a given centrifugal force. This causes the rocks to be discharged from the peripheral end. Such discharged raw stones are crushed into stones with smaller diameters by collision with one of the anvils 32a, 32b, 32c, 32d. Some crushed stones are accumulated on the dead stock forming plate 30 of the dead stock spaces 34a, 34b, 34c, 34d. At the beginning of operation, accumulated crushed stones do not perfectly form a dead stock. In a short time, a sufficent amount of stones accumulated on the dead stock forming plate 30 form a perfect dead stock. As shown in Fig.2, four dead stocks 42, 42, 42, 42 are formed with the respective angles of rest. As a result, discharged raw stones are crushed by collosion with such formed dead stocks. Other dead stocks are also formed on the rotor 10 by stones that are prevented from discharging by the supports 57 and the circumferentially extending portion 59. Such dead stocks have the respectively specified angles of rest under operation of centrifugal force and gravitational force. Collision of raw stones with anvil 32 which has a high degree of hardness and is made of manganese steel causes discharged stones to be crushed into a comparably small radia of stones, while collision of raw stones with dead stock 42 which has a low degree of hardness and is formed of accumulated stones causes discharged stones to be crushed into a comparably large radia of stones. It is not suitable that the collision of a stone with a dead stock is expressed as "crush". A stone colliding with a dead stock is reduced little in radius, but is merely made smooth because of surface wear. Changing horizontal distance between each anvil 32 and the rotor 10 not only makes stones different in material or size to be of the same grain size, but also makes stones equivalent in material or size to be of different grain size. A decrease in the number of the spacers 35 enables the obtainment of crushed stones of a small grain size, while an increase in the number the spacers 35 enables the obtaiment of crushed stones of a large grain size. Otherwise, alternation of the inner radius of the adjusting ring 36 enables the change of the grain size of crushed stones. Raw stones, that are accelerated and rolled on the surfaces of the dead stocks accumulated on the dead stock forming plate 30 in the dead stock spaces 34a, 34b, 34c, 34d, collide with tips 72. Tips 72 wear less easily but are easier to chip when thrown raw stones are of large grain size. On the other hand, tips 72 are harder to chip but easier to wear when thrown raw stones are of small grain size. Cotrolling the operation of a crusher according to the present invention enables the production efficiency to increase. Super-hardness tips 72L1, 72M1, 72N1 are applied as tips mounted in the dead stock spaces 91L1, 91M1, 91N1 where dead stocks are formed on the rotor rotating in a given direction(clockwise direction), while non-super-hardness tips 72L2, 72M2, 72N2 are applied as tips mounted in the dead stock spaces 91L2, 91M2, 91N2 where dead stocks are formed on the rotor rotating in the reverse direction(anti-clockwise direction). Operation control includes an operation to rotate the rotor 10 in the clockwise direction or to rotate the rotor 10 in the anti-clockwise direction in correspndence to the grain size or grain size distribution of raw stones. For the large size of stones being produced, that is, raw stones being of large size, the rotor is rotated in the clockwise direction as seen in Fig.4. Most stones collide with the non-super-hardness tips 72L2, 72M2, 72N2 that are less worn because of a lower collision frequency and hard to chip because of its physical properties. For the small size of stones being produced, that is, raw stones being of small size, the rotor is rotated in the anti-clockwise direction. Most stones collide with the super-hardness tips 72L1, 72M1, 72N1 that are hard to chip because of their small moments and of less wear because of their physical properties, despite a higher collision frequency. Such an operation method is regular but may not be regular in combination with the regular operation. When large sized stones are produced, the rotor may be rotated in the clockwise direction and when small sized stones are produced, the rotor may be rotated in the anti-clockwise direction. In consideration of the abration degree of super-hardness tips 72L1, 72M1, 72N1 to non-super-hardness tips 72L2, 72M2, 72N2, regular rotation or irregular rotation may be operated. Such a combination of regular operation with irregular operation results in an extension in the common tip life. A single crusher is not always used. A multiple number of crushers according to the present invention may be simultaneously or synchronously operated. It is normal that a multiple number of crushers are operated in relation to each other. Simultaneous operation enables processes to be synchronous in which stones of a large grain size are in multi-processes crushed into stones of a small grain size of stones. Rortors are rotated in the respective rotational direction in the respective processes: a first step crusher being rotated in the clockwise direction; a second step crusher being rotated in the regular or irregular direction; a third step crusher being rotated in the anti-clock direction. Such a group-control operation results in the extension of the tip life.

Claims: Vertical shaft type impact crusher comprising: a casing body (1), a rotor (10) mounted on said casing body (1), being rotatable in either a clockwise or an anti-clockwise direction for giving thrown stones centrifugal force, dead stock spaces (34a,34b,34c,34d) for crushed stones to be accumulated therein, said dead stock spaces being located in the circumferential area around said rotor (10), anvils (32a,32b,32c,32d) for crushing stones discharged from said rotor, said anvils being mounted in the circumferential area around said rotor (10) characterized in that said anvils (32a,32b,32c,32d) are located between said dead stock spaces (34a,34b,34c,34d) in the peripheral direction around said rotor (10), said rotor (10) includes multiple pairs of tips (72L,72M,72N), the pairs of tips being located in symmetry with respect to central lines (L,M,N) extending radially from the axis line of the rotor (10) in equal angular intervals, the tips (72L1,72M1,72N1) of said pairs of tips pointing forward in the rotational direction with respect to the center lines (L,M,N), when the rotor is rotated in said anti-clockwise direction, being made of hard material in comparison with the tips (72L2,72M2,72N2) pointing backward in the rotational direction with respect to the center lines (L,M,N), said backward pointing tips being made of soft material in comparison with said hard material.

Inventors: NAKAYAMA HIROSHI, WATAJIMA TERUJI, NAKAYAMA, HIROSHI, WATAJIMA, TERUJI
Applicants: NAKAYAMA IRON WORKS LTD, NAKAYAMA IRON WORKS, LTD.
Application year: 1995
Main classification: B02C13
IPC codes: B02C13