EP3415236B1 - Barre de percussion - Google Patents

Barre de percussion Download PDF

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Publication number
EP3415236B1
EP3415236B1 EP18177911.7A EP18177911A EP3415236B1 EP 3415236 B1 EP3415236 B1 EP 3415236B1 EP 18177911 A EP18177911 A EP 18177911A EP 3415236 B1 EP3415236 B1 EP 3415236B1
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EP
European Patent Office
Prior art keywords
rotor
impact bar
flanks
bar
impact
Prior art date
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Active
Application number
EP18177911.7A
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German (de)
English (en)
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EP3415236A1 (fr
Inventor
Frederik HOOGENDOORN
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Keestrack NV
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Keestrack NV
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Publication date
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Priority to PL18177911T priority Critical patent/PL3415236T3/pl
Publication of EP3415236A1 publication Critical patent/EP3415236A1/fr
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    • 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
    • B02C13/02—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft
    • B02C13/06—Disintegrating by mills having rotary beater elements ; Hammer mills with horizontal rotor shaft with beaters rigidly connected to the rotor

Definitions

  • the invention relates to a blow bar for an impact crusher with the features of claim 1 and relates to a rotor with such a blow bar according to the features of claim 7 and an impact crusher according to claim 13.
  • Impact crushers are used for crushing mineral materials (natural stone or recycled material) and for producing fine or coarse aggregate. In this case, the material is brought in free fall in the range of impact bars of a rotor and thrown from there against baffles. There it breaks.
  • the blow bars are wearing parts and must be replaced regularly.
  • the direction of rotation of the rotor can be changed so that the front and back sides of the blow bars can be used alternately until the wear limit is reached. Then the blow bars can be turned around their own longitudinal axis. A not yet worn end of the blow bars, which was in a blow bar recording in the rotor, thereby passes outwards, so that the blow bar can be used to reach the wear limit of this end area.
  • the state of the art is the JP S61 132042 U to call. It is a blow bar for insertion into an axially parallel rasp bar recording a rotor of an impact crusher described.
  • the blow bar has a longitudinal axis extending parallel to the blow bar receptacle and longitudinal sides exposed to wear.
  • the blow bar has on each of its longitudinal sides two end faces and between the end faces of a front and a rear holding portion, wherein the holding portions are each bounded by longitudinal webs.
  • the arrangement is mirror-symmetrical.
  • the longitudinal webs are trapezoidal in cross section. In the installation position, the radially outer longitudinal webs protrude relatively far out of the blow bar receptacle and are thus exposed to increased wear.
  • the invention has for its object to show a blow bar for an impact crusher, which has a long service life and a high degree of utilization.
  • a suitable rotor for such a blow bar to be shown as well as an impact crusher with a rotor with a longer service life.
  • the first object is achieved with a blow bar with the features of claim 1.
  • a suitable rotor that solves this problem is the subject of claim 7 and a corresponding impact crusher is the subject of claim 13.
  • blow bar for insertion into an axially parallel blow bar recording a particular reversible rotor of an impact crusher.
  • a maximum degree of utilization results when the blow bar can be turned.
  • the blow bar has a holding area in the middle and adjacent to the holding area each have a beating area.
  • One of the two impact areas on the front sides of a blow bar is in an insert position, ie it protrudes from the rotor.
  • the other impact area is protected in the rotor and can be brought by turning the blow bar in the operating position.
  • the blow bar has a longitudinal axis extending in the z-direction, which runs parallel to the rasp bar mount of the rotor in the installed position, a vertical axis extending in the y-direction, which is directed onto a radial head surface of the blow bar and a direction extending in the x direction Transverse axis, which is directed to a longitudinal side of the blow bar.
  • the origin of this coordinate system is in the middle of the cross-sectional area of the blow bar.
  • the blow bar has on each of its longitudinal sides (front and back) two end faces, which serve as striking surfaces, and between the end faces of a front and a back holding area. Which side is the front and which side is the back depends on the installation position and the direction of rotation of the rotor.
  • the invention is based on identical front and rear sides with respect to the active surfaces there. This allows a reversible operation of the rotor, without the blow bar would have to be turned manually when reversing.
  • the holding areas are each bounded by two identical longitudinal webs, i. the holding areas are located between the longitudinal bars.
  • the longitudinal webs are opposite the front surfaces. Based on the y-z plane and on the x-z plane, the longitudinal webs are arranged mirror-symmetrically.
  • the blow bar is characterized rotationally symmetrical. It can be rotated by 180 ° about the x, y or z axis and thereby forms on itself.
  • the longitudinal webs are trapezoidal in cross section. They have a wide base on the beater bar and a narrower top in the distance to the base. The top is parallel to the yz plane. The end faces are also substantially parallel to the yz plane. "Essentially” in this context means “within the scope of manufacturing tolerances".
  • the blow bar can be a cast component. Cast components have surfaces that can be slightly inclined or uneven due to production. The invention covers both surfaces which have been produced by casting and those which have been processed by forming or material-removing processes, eg forged or milled surfaces.
  • the blow bar according to the invention can consist of a metallic cast material, a ceramic material or a hybrid material made of steel with ceramic components. The invention is not limited to a particular material, if this material can break with sufficient life mineral material.
  • the trapezoidal longitudinal webs each have two flanks extending from the base to the top.
  • the mutually facing inner flanks of adjacent longitudinal webs each include a flank angle of 20 ° to 27 °, to the x-axis.
  • the flank angle is 23 ° to 26 ° and preferably 25 °. This flank angle has proved to be particularly suitable for the transmission of forces from the blow bar to the rotor and for transmitting the torque from the rotor to the blow bar.
  • flank angles of the two inner flanks on one longitudinal side are identical, but also the flank angles of the two outer flanks.
  • the flank angle of the inner and outer edges may be identical and also be 20 ° to 27 °, in particular 23 ° to 26 °, preferably 25 °.
  • the pairwise diagonally opposite inner flanks extend in a common plane.
  • the outer flanks have this by approximately 25 ° from the x-axis deviating angle, so that the forces introduced into the longitudinal webs in the transition from the base to the flanks must not be deflected by 90 °, but by about 65 °.
  • the transitions of the flanks are rounded towards the base, which also avoids voltage spikes in the material.
  • the blow bar has a measured width in the x-direction, wherein the width between the longitudinal webs is at least as large as the width in the region of the end faces. Preferably, the width between the longitudinal webs is greater than the width in the region of the end faces, in particular by an order of magnitude of from 4 to 10%.
  • the width of the blow bar in the impact area deviates only relatively little from the width between the longitudinal webs, for example, 80 mm / 85 mm or 100 mm / 108mm (width faces / width between the longitudinal webs).
  • the larger width between the longitudinal webs is appropriate because the longitudinal webs in the inventive type the application of force are exposed to higher loads and because the loads of the longitudinal webs should be transmitted as low tension on the central area of the blow bar on the other longitudinal webs.
  • the central area of the blow bar between the longitudinal webs should therefore have a greater width.
  • the invention is based on the fact that the width of a not worn blow bar is essentially constant both in the region of the end faces and between the longitudinal webs.
  • the holding area that area in which the blow bar is held. It starts at an upper contact area at the outer longitudinal web and ends at a lower contact area at the lower longitudinal web.
  • the blow bar is held between the longitudinal webs by positive engagement.
  • the invention avoids weakening of the cross section of the blow bar by lateral indentations.
  • the different widths cause that the central area between the longitudinal bars appears like a depression, but actually does not weaken the cross section of the blow bar, but even reinforced. There is no notch effect.
  • More material in the central area provides the basis for secure anchoring of a reversible blow bar.
  • the combination of the slightly wider central area with the said flank angles of the inner flanks allows a blow bar, which as a result requires less material at high load capacity and therefore achieves a high degree of utilization of at least 50%.
  • the degree of utilization is greater than 55% and in particular greater than 60%.
  • the mutually facing inner flanks of the longitudinal webs are shorter than the outer flanks, provided that the inner and outer flanks have the same flank angle.
  • centrifugal forces are transmitted to the beater bars in the rasp bar holder via the inner flanks of the radially inner longitudinal webs.
  • the blow bars effect by their high Dead weight and the high rotational speeds very high centrifugal forces.
  • the positive engagement between the rotor and blow bars causes a secure fixation in the radial direction of the rotor.
  • the blow bars are mechanically easily interchangeable at standstill, because they are in contact only via the edges of the longitudinal webs with the rotor.
  • the blow bars can be pulled axially out of the blow bar recordings. Since the axial load is relatively small, sufficient for axial fixation simple fixing, such as screwed to the rotor axial securing. They are easily detachable and allow immediate access to the blow bar.
  • the beater bar holder is limited on both sides by baffle bar holders.
  • the blow bar holders are welded to the rotor.
  • the rotor may be constructed of a plurality of rotor disks arranged parallel to one another, the impact bar holders extending from rotor disk to rotor disk.
  • the blow bar holders are those components with which the blow bars are in contact via their flanks.
  • the inner flanks of the radially inner longitudinal webs are loaded not only by centrifugal forces, but especially by the fact that material to be crushed hits the blow bar and is greatly accelerated by the blow bar. Since the circle of the rotor is larger than the rotor itself, a torque is applied to a claimed blow bar. This torque is transmitted via the flanks of the longitudinal webs in the rotor. Conversely, the driven rotor transmits forces in the impact bar holder and this in turn on the said flanks in the longitudinal webs of the blow bar.
  • the inner, mutually facing flanks of the longitudinal webs are the most important surfaces of the blow bars in addition to the striking surfaces because they, and according to the invention only participate in the power transmission. It is not excluded within the scope of the invention that there is an additional or indirect force transmission by mineral material that has penetrated into gaps and joints between blow bar and blow bar holder. Primarily, the forces are transmitted via the flanks.
  • the flanks are according to the invention oriented so that the male torques around the longitudinal axis (axis of rotation / z-axis) meet the blow bar on surfaces that extend in the radial direction to the axis of rotation. It is ideal if these surfaces have a large radial distance to the axis of rotation.
  • the lever arm is increased, thereby reducing the surface pressures at the support point, ie the force vector is smaller.
  • a large lever arm is achieved in the case of a slender impact strip in that the flanks serving as support points or support surfaces have a large radial distance from the longitudinal axis (z-axis).
  • the inner flanks are arranged in a manner X-shaped with respect to the center of the blow bar or the z-axis about which the torque is applied, and which lies in the same plane in which the diametrically arranged inner flanks are located.
  • the two radially outer flanks can form a shoulder in the installed position for the protection of adjacent components of the rotor.
  • the radially outer flanks may wear to a certain extent for this purpose. This is not detrimental to the function of the blow bar because the outer flanks have no contact surfaces with the rotor. Deviation in dimensional accuracy or wear in this area does not affect the secure fit or life of the blow bar.
  • a geometry of the blow bar is considered particularly favorable when the ratio between the width of the striking area and the minimum distance of the flanks in the central area is 1.8-2.2 to 1, in particular 2 to 1.
  • Said width in the striking area is preferably larger as 70 to 80 mm.
  • the width is essentially constant over the entire impact area.
  • the ratio between the minimum distance of the inner flanks between the longitudinal webs and the height of the longitudinal webs is preferably 1.8-2.2 to 1, in particular 2 to 1.
  • the longitudinal webs should have a width in the x-direction of 40% - 60%, in particular 50%, of the height of the blow bar. Their tops should have a height in the y-direction of preferably 40% - 60%, in particular 50% of the minimum distance of the inner flanks between the longitudinal webs.
  • the width of the beater bar in the region of the longitudinal webs is preferably 40% -60%, in particular 50% larger than the width of the beater bar in the beating area.
  • the length of the blow bar in the z direction is independent of the other proportions.
  • the invention proposes for fastening a suitable rotor, in which the blow bar recording has opposing blow bar holder with projections to grasp between the longitudinal webs.
  • the projections in this case preferably have the same flank angles as the inner flanks of the longitudinal webs. This ensures that the surface pressure is as low and uniform as possible, both on the rotor and on the blow bar.
  • the material is optimally utilized with uniform load. This material can be saved on the rotor and on the blow bar.
  • rotor protection plates are arranged on the rotor, which cover the beater bars radially peripherally.
  • the rotor protection plates are exchangeable wear parts, which however have much longer service life than the blow bars, because they are less heavily loaded.
  • the rotor protection plates can be brought in the invention very close to the blow bar.
  • An edge side of a rotor protection plate is preferably directly opposite to the upper sides of the radially outer Longitudinal ridges arranged.
  • the contact area between the blow bar and the blow bar holders is very limited in height.
  • the radially innermost contact areas between the blow bar and the blow bar holders are located on the inner flanks of the radially inner longitudinal webs.
  • the radially outermost contact areas between the blow bar and the blow bar holder on the inner edge of the radially outer longitudinal webs.
  • the blow bar receptacle may have a radially inner area for receiving the second end face or the second striking section of the blow bar, this area being widened in the x direction, and a narrower area in the x direction extending between the projections located. It is located radially further out. Between these areas a rounded transition region is arranged which extends over at least 50% of the width of the upper side of the inner longitudinal webs. The rounded area is very large so that as far as possible no notch stresses can arise in this area. The upper sides of the longitudinal webs do not touch the inner areas of the rasp bar recording and therefore do not transmit any forces. However, the pairwise directly opposite longitudinal webs wide shoulder belts are created, which transmit the centrifugal forces of the blow bar in the rotor.
  • the blow bar according to the invention has the following advantages: In the installed position, the opposite, radially outer longitudinal webs form a region of maximum width as a shoulder belt. At the radially outer shoulder belt, the largest torques of the blow bar attack. They are optimized by Edge geometries effectively initiated in the adjacent components. The wide shoulder also protects the rotor itself from wear.
  • the blow bar is simply profiled, has clear proportions and is therefore inexpensive to manufacture.
  • the blow bar Due to the diametrically arranged flanks of the same direction, the blow bar has the greatest possible support width, which reduces the load on the blow bar.
  • the largest possible radius in the blow bar holder prevents voltage peaks in the blow bar holder and ensures maximum stability.
  • the flank angle of about 20 to 27 °, preferably 25 ° has the advantage that the spreading forces are low within the rasp bar recording. As the flank angle increases, the spreading forces would increase, i. the forces acting transversely to the rasp bar recording. Flank angle below 20 ° would increase the width of the blow bar with the same radial distance of the flanks, whereby the utilization rate decreases. If the width should not be greater, the radial distance of the flanks would have to be smaller, which is associated with shorter lever arms and higher surface pressure. The range between 20 ° and 27 ° is considered optimal.
  • the rotor can be equipped with two, three or more identical blow bars distributed evenly around the circumference. It is also possible to combine blow bars of different heights with each other, eg two blow bars of greater height with two blow bars of lesser height, each in turn.
  • the blow bars are used especially in reversible impact crushers. Use in non-reversible impact crushers is also possible.
  • FIG. 1 shows a rotor 1 of an otherwise not shown impact crusher.
  • the rotor 1 has a horizontal rotor shaft 2, which is mounted in bearings 3, 4.
  • the rotor shaft 2 extends horizontally between the bearings 3, 4. It is driven by a pulley 5.
  • blow bars 6 are arranged distributed over the circumference. The in the picture plane the FIG. 1 top blow bar 6 runs like all other blow bars 6 parallel to the axis of rotation D of the rotor shaft. 2
  • blow bars 6 reference is made to a Cartesian coordinate system.
  • the origin of the coordinate system is located in the middle of the bar 6, that is, half the length (z-axis), height (y-axis) and width (x-axis) of the said bar 6.
  • the x-direction extends tangentially to the rotor 1.
  • the y-axis is the radial direction and points away from the rotor shaft 2.
  • the z-axis is parallel to the axis of rotation D.
  • FIG. 2 From the sectional view of FIG. 2 shows that the circumference of the rotor 1 a total of four blow bars 6 are arranged evenly distributed.
  • the four blow bars 6 are identical, as are the associated blow bar receivers 7 within the rotor 1.
  • the blow bars recordings 7 are in the longitudinal direction of the rotor, that is, parallel to the axis of rotation D of the rotor shaft 2 extending pockets.
  • coordinate system run the pockets in the z direction.
  • the blow bars 6 are configured substantially rectangular in cross-section. They are mirror-symmetric with respect to the y-z plane and also with respect to the x-z plane. They each have radial head surfaces 8, which extend substantially parallel to the x-z plane. Since the blow bars 6 are cast components, the top surfaces 8 may have a slight draft due to casting technology. The longitudinal sides 9, 10 of the blow bar 6 extend parallel to each other and are thus substantially perpendicular to the top surfaces 8.
  • the holding areas 15, 16 are each bounded by two longitudinal webs 17, 18, 19, 20, as well as with reference to the illustration of FIGS. 2 to 4 can be seen.
  • All longitudinal webs 17 - 20 are identically configured and have the same cross-section.
  • the longitudinal webs 17-20 are trapezoidal in cross-section and have a widened base 21 and a narrower upper side 22 (FIG. FIG. 4 ). Between the base 21 and the upper side 22 each oblique flanks extend. Inner flanks 23-26 face one another and delimit the holding regions 15, 16.
  • Outer flanks 27 form the transition to the end faces 11-14. All edges are rounded.
  • the arrow P1 in FIG. 2 symbolizes the direction of rotation of the rotor shaft 2 and thus of the rotor 1. Due to the direction of rotation, the end face 11 is claimed as a striking surface. In this direction of rotation, the names front and back of the blow bar 6 could be used. Since the direction of rotation is reversible, the opposite end face 14 can, as it were, serve as a striking surface in reversing operation.
  • blow bars 6 are in a manner not shown in the z-direction, that is in the longitudinal direction of the rotor 1 in the Blow bar recordings 7 inserted. They are secured in the installation position against axial displacement. Due to the positive engagement of blow bar holders 28, 29 between the longitudinal webs 17 - 20, the blow bars 6 are held captive in the rotor 1.
  • the beater bars 28, 29 abut the respective inner flanks 23-26 of the beater bar 6. Due to the inclined inner flanks 23-26, the undercut region, that is to say the respective holding region 15, 16, is trapezoidal in cross-section with rounded corners.
  • the blow bar holders 28, 29 for this purpose have opposite projections 30, 31 whose geometry and in particular their support surfaces are adapted to the flank angles of the inner flanks 23-26.
  • the flank angle W1 is in FIG. 4 located.
  • FIG. 3 shows that the radially outermost contact area between the impact bar holders 28, 29 and the blow bar 6, the radially inner flanks 23, 24 of the radially outer longitudinal webs 17, 19 are.
  • the radially innermost contact areas between the inner flanks 25, 26 and the corresponding projections 30, 31 of the blow bar holders 28, 29 are located radially above or below said areas, there are no further contact areas.
  • the radially outer longitudinal webs 17, 19 protrude beyond the blow bar holders 28, 29 and to a certain extent lie radially on the outside of the rotor 1. They are protected by rotor protection plates 32, which are screwed radially from the outside onto the rotor 1.
  • the rotor protection plates 32 cover the beater bars 28, 29 and protect them from wear.
  • the rotor protection plates 32 each have an edge side 33 which faces the upper sides 22 of the longitudinal webs 17, 19. As a result, the longitudinal webs 17, 19 are protected against wear in this area.
  • the rotor protection plates 32 are attached exchangeably.
  • FIG. 3 shows in the enlargement the area III according to FIG. 2 ,
  • the wear lines show that the rotor 1 was initially operated in a counterclockwise direction, since the upper left corner of the bar 6 is removed first has been. Subsequently, the direction of rotation has been reversed, so that the right in the image plane end face 11 serves as a clubface. Accordingly, the upper right corner of the bar 6 was removed.
  • the wear limit V is reached.
  • the wear limit V is approximately in extension of the radially outer flanks 27.
  • the wear limit V is the limit for the maximum utilization of the blow bar 6.
  • the blow bar 6 has in this state has an approximately triangular residual cross-section at the wear limit V.
  • the blow bar 6 is pulled out in the longitudinal direction of the rotor 1 from the blow bar receptacle 7 and can be turned about its longitudinal axis, so that the previously inner end faces 13, 14 pass outwards. In this turning by 180 degrees, there is no preferred direction of the blow bar 6. It is irrelevant whether the blow bar 6 is rotated only about its longitudinal axis or at the same time also turned around its vertical axis (y-axis). The rotational symmetry of the blow bar 6 allows both directions of insertion in the blow bar recording. 7
  • FIG. 3 shows that the beater bar receptacle 7 is designed to be relatively wide for the non-engaged area of the beater bar 6.
  • the width of this inner region 34 is greater than the width of the blow bar 6, measured over the longitudinal webs 18, 20.
  • An area 35 narrower in the x direction is located between the protrusions 30, 31.
  • the widened region 34 is connected to the narrower region 35 via a transition region 36.
  • the transition region 36 is rounded. The rounding of the transition region 36 extends over at least 50% of the height of the upper side 22 of the inner longitudinal webs. Due to the large radius of curvature stresses in this area of the blow bar holder 28, 29 are avoided.
  • blow bar according to the invention has this special proportions, which are described below with reference to the FIG. 4 be explained.
  • the blow bar 6 has in this embodiment, a height H1 of 320 mm at a width B1 in their field of impact of 80 mm.
  • the ratio of height to width is 4: 1.
  • the blow bar 6 is slightly wider in their not intended for wear, middle support portion than in the impact area.
  • the longitudinal webs 17-20 each have a height of 20 mm, measured from the end-side end faces 11-14 (width B2).
  • Their tops 22 have a height H2 of 20 mm.
  • the height H3 is measured at the base 21 and indicates the minimum distance of the inner flanks 23-26 of the longitudinal webs 17-20.
  • FIG. 4 shows further that the flank angle W1 are identical for all marked flanks of the longitudinal webs 17-20. They are 25 degrees.
  • the inner flanks 23-26 each extend radially from a center M of the blow bar 6. Therefore, the illustrated dash-dotted lines intersect as an extension of the respective inner flanks 23 - 26 in the center M.
  • the center M is located on the longitudinal axis of the beater bar 6 (z-axis), around which the mounted blow bar 6 during operation theoretically within the intended Tolerances within the blow bar receptacle 7 can pivot.
  • FIG. 4 further shows that the width B3 of the beater bar 6, which is measured over the tops 22 of the longitudinal webs 18, 20, is 1.5 times as large as the width B1 of the beater bar 6 in the region of their playing surfaces.
  • the width B4 is at least as large as the width B1 in the region of the end faces 11, 12, so that no indentation in the sense of material weakening is present.
  • the width B4 in the area between the longitudinal webs 17-20 is 85 mm in this embodiment compared to 80 mm in the impact areas.

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Claims (13)

  1. Barre de percussion à insérer dans un logement de barre de percussion parallèle à l'axe (7) d'un rotor (1) d'un concasseur à percussion avec les caractéristiques suivantes :
    a. la barre de percussion (6) dispose à l'intérieur d'un système de coordonnées cartésien d'un axe longitudinal s'étendant dans la direction z, qui s'étend dans la position de montage parallèlement au logement de barre de percussion (7), d'un axe vertical s'étendant dans la direction y, qui est dirigé sur une surface de tête radiale (8) de la barre de percussion (6) et d'un axe transversal s'étendant dans la direction x, qui est dirigé sur un côté longitudinal (9) de la barre de percussion (6) ;
    b. la barre de percussion (6) dispose au niveau de chacun de ses côtés longitudinaux (9, 10) de deux surfaces frontales côté extrémité (11, 12, 13, 14) et entre les surfaces frontales (11, 12, 13, 14) d'une zone de retenue côté avant et côté arrière (15, 16), dans laquelle les zones de retenue (15, 16) sont délimitées respectivement par deux nervures longitudinales (17, 18, 19, 20), qui font saillie par rapport aux surfaces frontales (11, 12, 13, 14), dans laquelle les nervures longitudinales (17, 18, 19, 20) sont agencées en symétrie de miroir par rapport au plan y-z et au plan x-z ;
    c. les nervures longitudinales (17 - 20) sont à section transversale trapézoïdale, avec une base large (21) au niveau de la barre de percussion (6) et un côté supérieur plus étroit (22) à distance de la base (21) ainsi qu'avec respectivement un flanc incliné intérieur (23, 24, 25, 26) et un flanc extérieur (27), dans laquelle les flancs (23 - 27) s'étendent entre la base et le côté supérieur (22) et dans laquelle les flancs intérieurs (23 - 26) s'étendent selon un angle de flanc (W1) de 20° à 27° par rapport à la direction x ;
    d. des flancs intérieurs (23 - 26) agencés par paire diagonalement l'un en face de l'autre s'étendent dans un plan commun ;
    e. seuls les flancs intérieurs (23 - 26) peuvent s'appuyer dans la position de montage pour la transmission de forces dans le logement de barre de percussion (7) au niveau du rotor (1).
  2. Barre de percussion selon la revendication 1, caractérisée en ce qu'elle dispose d'une largeur mesurée dans la direction x, dans laquelle la largeur (B4) dans la zone entre les deux nervures longitudinales (17 - 20) est au moins aussi grande que la largeur (B1) dans la zone des surfaces frontales (11 - 14).
  3. Barre de percussion selon la revendication 1 ou 2, caractérisée en ce que les deux flancs radialement extérieurs (27) forment dans la position de montage un épaulement pour la protection de composants adjacents du rotor (1).
  4. Barre de percussion selon l'une quelconque des revendications 1 à 3, caractérisée en ce qu'une section transversale de la barre de percussion (6) dans le plan x-y dispose d'une partie d'usure et d'une partie non d'usure, dans laquelle la partie d'usure comprend au moins 50 %, en particulier 55 % de la section transversale totale.
  5. Barre de percussion selon la revendication 4, caractérisée en ce que le rapport entre la largeur (B1) de la partie d'usure de la barre de percussion (6) et la distance minimum (H3) des flancs intérieurs (23 - 26) des nervures longitudinales (17 - 20) est de 1,8 - 2,2 pour 1.
  6. Barre de percussion selon l'une quelconque des revendications 1 à 5, caractérisée en ce que le rapport entre la distance minimum (H3) des flancs (23-26) des nervures longitudinales (17-20) et la hauteur (H2) des nervures longitudinales (17-20) est de 1,8 - 2,2 pour 1.
  7. Rotor avec au moins deux barres de percussion selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le logement de barre de percussion (7) présente des supports de barre de percussion (28, 29) opposés l'un à l'autre avec des saillies (30, 31), pour saisir entre les nervures longitudinales (17 - 20), dans lequel les saillies (30, 31) ont les mêmes angles de flanc (W1), que les flancs intérieurs (23 - 26) des nervures longitudinales (17 - 20).
  8. Rotor selon la revendication 7, caractérisé en ce que la zone de contact radialement la plus à l'intérieur se trouve entre la barre de percussion (6) et les supports de barre de percussion (28, 29) au niveau des flancs intérieurs (25, 26) des nervures longitudinales radialement intérieures (18, 20).
  9. Rotor selon la revendication 7 ou 8, caractérisé en ce que la zone de contact radialement la plus à l'extérieur se trouve entre la barre de percussion (6) et les supports de barre de percussion (28, 29) au niveau des flancs intérieurs (23, 24) des nervures longitudinales radialement extérieures (17, 19).
  10. Rotor selon l'une quelconque des revendications 7 à 9, caractérisé en ce que le logement de barre de percussion (7) présente une zone intérieure, élargie dans la direction x (34), pour la réception de la deuxième surface frontale (12, 13) de la barre de percussion (6) et une zone plus étroite dans la direction x (35), qui se trouve entre les saillies (30, 31), dans lequel une zone de transition arrondie (36) est agencée entre lesdites zones (34, 35), qui s'étend sur au moins 50 % de la hauteur (H2) du côté supérieur (22) des nervures longitudinales intérieures (18, 20).
  11. Rotor selon l'une quelconque des revendications 7 à 10, caractérisé en ce que des plaques de protection de rotor (32) sont agencées au niveau du rotor (1), lesquelles recouvrent les supports de barre de percussion (28, 29), dans lequel un côté marginal (33) d'une plaque de protection de rotor (32) est agencé directement en face d'un côté supérieur (22) des nervures longitudinales (17, 19).
  12. Rotor selon l'une quelconque des revendications 7 à 11, caractérisé en ce que des barres de percussion (6) à hauteur (H1) divergente l'une de l'autre peuvent être insérées dans le rotor (1).
  13. Concasseur à percussion avec un rotor selon l'une quelconque des revendications 7 à 12, caractérisé en ce que le concasseur à percussion est réversible.
EP18177911.7A 2017-06-16 2018-06-15 Barre de percussion Active EP3415236B1 (fr)

Priority Applications (1)

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PL18177911T PL3415236T3 (pl) 2017-06-16 2018-06-15 Listwa udarowa

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102017113238.4A DE102017113238B4 (de) 2017-06-16 2017-06-16 Schlagleiste, Rotor und Prallbrecher

Publications (2)

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EP3415236A1 EP3415236A1 (fr) 2018-12-19
EP3415236B1 true EP3415236B1 (fr) 2019-11-20

Family

ID=62684654

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EP18177911.7A Active EP3415236B1 (fr) 2017-06-16 2018-06-15 Barre de percussion

Country Status (7)

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US (1) US10792664B2 (fr)
EP (1) EP3415236B1 (fr)
CN (1) CN109127001B (fr)
DE (1) DE102017113238B4 (fr)
ES (1) ES2773715T3 (fr)
LT (1) LT3415236T (fr)
PL (1) PL3415236T3 (fr)

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CN109999957B (zh) * 2019-03-07 2021-07-30 孙红勤 一种多级立式破碎机

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US3510076A (en) * 1966-12-27 1970-05-05 Esco Corp Impact device
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DE2317692B2 (de) * 1973-04-07 1978-07-27 Bhs-Bayerische Berg-, Huetten- Und Salzwerke Ag, 8000 Muenchen Schlagwerkzeug aus Verbundmetall fur Prall- und Hammerbrecher
CH584067A5 (fr) * 1974-03-15 1977-01-31 Andreas E Dr Hazemag Kg
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Also Published As

Publication number Publication date
US20190015838A1 (en) 2019-01-17
US10792664B2 (en) 2020-10-06
DE102017113238B4 (de) 2020-09-24
LT3415236T (lt) 2020-05-25
CN109127001B (zh) 2020-10-27
PL3415236T3 (pl) 2020-06-29
EP3415236A1 (fr) 2018-12-19
CN109127001A (zh) 2019-01-04
ES2773715T3 (es) 2020-07-14
DE102017113238A1 (de) 2018-12-20

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