EP2471600B1 - Rotor of a hammer crusher - Google Patents

Description

The invention is directed to a rotor of a hammer crusher with at least two rotor disks, which are arranged rotatably at a distance from each other on a shaft, wherein between two adjacent rotor disks several impact hammers are pivotally mounted at a radial distance from the shaft.

A hammer crusher with such a rotor is used for the comminution of various materials and has a high degree of comminution. Here, hammer crushers are performed with one or two rotors as a single or double shaft hammer crusher. A rotor of a hammer crusher is for example from DE 27 13 177 C2 known and comprises a shaft and a certain number of laterally spaced from each other on the shaft mounted circular rotor discs, between which five percussion hammers are arranged rotatably on the circumference. The shaft has a circular cross section, whereby the hammer projection, ie the extension, with which the impact hammers protrude beyond the radius of the rotor disc, turns out very small and also the transmission of torque from the shaft to the rotor disc due to the formed with keyways connection between Wave and the rotor discs is not optimal.

With regard to a safe entrainment of the rotor disks and with a view to improving the transmission of torque is from the DE 1 178 681 B a rotor of a hammer crusher is known, between whose rotor disks three impact hammers are arranged and whose drive shaft or shaft is hexagonal in cross section. However, the combination of the number of impact hammers and the cross-sectional shape of the drive shaft is not optimum with respect to a desired high hammer overhang. Furthermore, with this number of impact hammers there is a risk that the material to be shredded can penetrate dangerously deep between the impact hammers, causing wear the Increases impact hammers and affects areas that should not be exposed to wear. Although it is known to cover the components exposed to this wear by protective caps. However, this measure is accompanied by increased production costs and increased production costs of the hammer crusher.

Finally, also from the EP 1 128 908 B1 a rotor of a hammer crusher of the type mentioned above known. The rotor is formed by at least one rotor disc mounted on a shaft of the rotor, on which percussion hammers are arranged distributed regularly circumferentially. The impact hammers are freely rotatable within a separated vibration space, with five impact hammers are arranged on each rotor disk. The shaft of the rotor has a pentagonal cross section, wherein the surfaces of the pentagon are respectively facing the vibration chambers. Although this embodiment of the rotor allows the largest possible hammer projection. However, it has been found that the pentagonal cross-sectional shape of the shaft is not optimum with respect to the transmission of the torque of the shaft to the rotor disks and to the moment of resistance of the shaft. Also, the metrological verification of manufacturing accuracy in a pentagonal shaft is limited or difficult.

The invention is therefore based on the object, a rotor of a hammer crusher of the type mentioned in such a way that in a simple and inexpensive way, the transmission of torque between the shaft and rotor disk is improved and that the rotor has consistent good performance characteristics during a long service life. Also to be simplified and improved by the invention, the metrological verification of the manufacturing accuracy of the shaft.

In a rotor of a hammer crusher of the type described, this object is achieved in that the shaft of the rotor is formed in cross-section star-shaped with a plurality of tips, wherein a respective tip of two radially outwardly converging side surfaces is defined.

Advantageous and expedient refinements and developments of the invention will become apparent from the dependent claims.

The invention provides a safe and durable connection of the rotor disk and the shaft, by means of which a better and higher transmission of the torque compared to the known state of the art is possible. In addition, it has been found that the star-shaped cross-sectional shape of the shaft, unlike, for example, a known, in cross-section five- or hexagonal shaft has a higher resistance moment, whereby the star-shaped shaft higher loads, such as higher bending or torsional stresses stand. As a result of the cross-sectional shape of the shaft according to the invention, significantly higher overall performances of a hammer crusher provided with such a rotor can be achieved overall. In particular, the adhesion of the drive force transmitting surfaces of the star-shaped in cross-section wave is greater than in known cross-sectional shapes of the shaft, because the forces act more directly on the surfaces. In addition, the wear factor in terms of the durability of the shaft-rotor disk connection is a much cheaper, so that the running time of the rotor according to the invention in a hammer crusher is a multiple of the known from the prior art embodiments.

A spatially particularly favorable arrangement of percussion hammers with respect to the star-shaped wave is given in development of the invention when extension lines of adjacent peaks limit a swing radius of a corresponding percussion hammer, wherein a respective extension line from the center of the shaft passes through a respective tip of the shaft. These "imaginary" extension lines do not define separate or separated vibration spaces, as known in the art. Rather, it is expressed by the fact that the respective oscillation radii of the impact hammers are arranged spatially efficiently between the tips of the shaft, so that the oscillation radii of the impact hammers can have a minimum possible distance from each other and in addition a large Hammer supernatant is possible, which allows the use of impact hammers with large cross-section. As a result, the use of impact hammers with a comparison with the known prior art larger vibrating radius or Schlagkreisdurchmesser is possible, which increases the penetration of the impact hammers. Thus, the driving force of the shaft can be used economically efficient with greater wear mass of the impact hammers.

It is of particular advantage with regard to a cost-effective production of the shaft when, with respect to two adjacent tips of the star-shaped shaft, the side surfaces of the two tips facing away from the respective adjacent tip are designed to run parallel to one another. In other words, it is provided in the star-shaped in cross-section design of the shaft that always two surfaces opposite each other in parallel. From a manufacturing point of view, this is compared to a pentagonal cross-section wave of considerable advantage, since according to the invention the parallel surfaces greatly facilitate the clamping of the shaft for machining the cross-sectional shape and beyond a measurement of the machined shaft with much higher accuracy is possible.

In order to keep the penetration depth of material to be shredded, which can reach radially inwardly into the respective oscillation radii of the impact hammers during operation of the rotor of the hammer crusher, it is advantageous if five impact hammers are arranged between the at least two adjacent rotor disks and if Cross-section of the star-shaped shaft of the rotor is a five-star. With five percussion hammers and a shaft with a cross section in the form of a five-star thus the resonant circuits of the percussion hammers between the tips of the shaft can be optimally arranged exploiting space, which adjusts a Schlagwiederholfrequenz at a predetermined speed, which prevents deep penetration of material to be shredded.

In an alternative embodiment of the rotor is inventively provided that six impact hammers are arranged between the at least two rotor disks and that the cross section of the star-shaped shaft of the rotor is a six-star. The cross-sectional shape of a six-star provides a comparison with the prior art improved hammer supernatant with optimum utilization of the resonant circuits.

With regard to a particularly effective rotor, it is advantageous if adjacent rotor disks are held at a distance by at least one spacer element arranged between them and mounted on at least one of the rotor disks. In this case, the at least one spacer element prevents the impact hammers arranged between two adjacent rotor disks from being trapped by the rotor disks. It should be noted at this point that the rotor discs provided in this invention, in contrast to known from the prior art rotor discs have no separate vibrating chambers for the individual impact hammers. Rather, in the rotor according to the invention of a hammer crusher, the side surfaces of the rotor disks, between which the impact hammers are arranged rotatably, constitute a single oscillatory space.

The invention provides in a further embodiment that at least on one of the two side surfaces of a rotor disk, the shaft at least partially enveloping and adapted to the cross section of the shaft load-receiving element is attached. The load-bearing member may be fixedly connected to the rotor disk and increases the carrying capacity and load capacity of the shaft. It also serves to protect the shaft and may be formed of a wear-resistant material to counteract the signs of wear that could be caused by material to be crushed, if this material would pass radially inward to the shaft during the crushing process. In addition, such a load-receiving element can serve as a spacer to keep adjacent rotor disks at a distance.

In a refinement of the invention, a constructionally particularly suitable measure for holding the impact hammers in a rotatable manner is that each of the at least two adjacent rotor disks has a plurality of through bores corresponding to the number of impact hammers arranged between them, with corresponding through bores of the adjacent rotor disks are aligned with each other, and wherein an axle rod is passed through each of the aligned through holes, on each of which the impact hammers are pivotally mounted.

Finally, the invention provides in a further embodiment that at least on one of the two side surfaces of a rotor disk, a respective through hole extending extension element is mounted. The extension element can also serve as a spacer to keep adjacent rotor disks at a distance. Primarily, however, a respective extension element has the function of improving the bearing stress or better dividing the acting bearing pressure on the existing surfaces. The respective extension elements, which have a passage opening aligned with a corresponding through hole, can be welded to a corresponding rotor disk.

It should be noted that the rotor disks with their further structural features can be produced both as a cast or as a welded construction.

It is understood that the features mentioned above and those yet to be explained can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention. The scope of the invention is defined by the claims.

• Figur 1 einen erfindungsgemäßen Rotor eines Hammerbrechers in perspektivischer Ansicht,
• Figur 2 der Rotor aus Figur 1 in einer Schnittansicht,
• Figur 3 eine seitliche Ansicht einer Rotorscheibe gemäß einer ersten Ausführungsform der Erfindung,
• Figur 4 eine weitere seitliche Ansicht der Rotorscheibe gemäß der ersten Ausführungsform der Erfindung,
• Figur 5 eine Draufsicht auf die Rotorscheibe aus Figur 4 und eine Welle gemäß der ersten Ausführungsform der Erfindung, Figur 6 eine Schnittansicht der Welle aus Figur 5,
• Figur 7 eine Draufsicht auf eine Rotorscheibe und eine Welle gemäß einer zweiten Ausführungsform der Erfindung, und
• Figur 8 eine Schnittansicht der Welle aus Figur 7.

Further details, features and advantages of the subject matter of the invention will become apparent from the following description taken in conjunction with the drawings in which exemplary embodiments of the invention are shown. In the drawing shows:

• FIG. 1 a rotor of a hammer crusher according to the invention in a perspective view,
• FIG. 2 the rotor off FIG. 1 in a sectional view,
• FIG. 3 a side view of a rotor disk according to a first embodiment of the invention,
• FIG. 4 another side view of the rotor disk according to the first embodiment of the invention,
• FIG. 5 a plan view of the rotor disk FIG. 4 and a shaft according to the first embodiment of the invention, FIG. 6 a sectional view of the shaft FIG. 5 .
• FIG. 7 a plan view of a rotor disk and a shaft according to a second embodiment of the invention, and
• FIG. 8 a sectional view of the shaft FIG. 7 ,

A generally designated 1 rotor of a hammer crusher is in FIG. 1 in a perspective view and in FIG. 2 shown in a sectional view. The rotor 1 is part of a single or multi-rotor hammer or impact crusher. The rotor 1 essentially has a plurality of circular rotor discs 2 with a small axial width, wherein for reasons of clarity in the Figures 1 and 2 only three rotor disks 2 are provided with a reference numeral. The rotor 1 according to the invention has at least two rotor disks 2. The rotor disks 2 are mounted rotatably on a shaft 3. Between two adjacent rotor disks 2 a plurality of impact hammers 5 are arranged distributed uniformly over the circumference of the rotor disks 2, which are mounted freely rotatable. As in particular in the FIGS. 3 and 4 can be seen, a respective rotor disk 2 has a plurality of through holes 6, which are arranged uniformly over the circumference of the rotor disk 2. On the rotor disk 2, an extension element 4 is attached to the through holes 6, which has an aligned to the respective through hole 6 passage opening. The extension elements 4 are thus aligned over the through holes 6 of the rotor disk 2. Through a respective through hole 6 and an aligned passage opening of an attached to the rotor disk 2 extension element 4, an axle 7 is passed, which extends eccentrically and axially parallel to the shaft 3. On a respective axle rod 7 a percussion hammer 5 is pivotally mounted between two adjacent rotor disks 2 respectively. By the axle rods 7, the percussion hammers 5 parallel eccentric to the shaft 3 are rotatably mounted or mounted between adjacent rotor disks 2, wherein the axle rods 7 are secured end side of the rotor 1 against axial movement. The extension element 4 in this case extends the Through hole 6 in the longitudinal direction of the rotor 1 and reduces the acting during operation of the rotor 1 bearing pressure. Further, the extension member 4 serves as a spacer to hold the percussion hammers 5 centrally between the rotor disks 2. The extension elements 4 may be fixedly mounted on one of the two side surfaces 17 or on both side surfaces 17 of a respective rotor disk 2, for example by welding.

In order to keep the rotor disks 2 laterally or in the axial direction at a distance, a plurality of spacer elements 14 are mounted on at least one side surface 17 of a respective rotor disk 2, to which an adjacent rotor disk 2 or a spacer element 14 of an adjacent rotor disk 2 is applied, wherein in the FIG. 4 illustrated first embodiment, which will be described below, on the side surface 17 and the back of the rotor disk 2 spacers 14 are mounted. The spacer elements 14 have through openings which are aligned with through holes formed in the rotor disks 2. Through the through holes of the spacer elements 14 and the rotor disks 2 are axially parallel tie rods 18 with respect to the longitudinal axis of the rotor 1 (see FIG. 2 ), with which the rotor disks 2 are clamped together to form a so-called rotor body. The spacer elements 14 of adjacent rotor disks 2 are connected to each other by means of bolts 19, as in FIG. 2 is shown.

The shaft 3 is provided in the region of the outer rotor disks or end disks 2 ', each with an annular groove 20, as in FIG. 2 is shown. In the annular grooves 20, two half-discs 21a and 21b are used, which are connected by screwing or welding together. The half disks 21, 21b inserted into the annular grooves 20 fix the rotor disks 2 clamped together to form a rotor body against axial displacement.

It should be noted that in FIG. 1 for reasons of clarity, the viewer facing outer rotor disc 2 'is not shown.

In the FIGS. 3 to 6 a first embodiment of the invention is shown. For safe entrainment of the rotor disk 2, this has a cross-sectionally star-shaped passage opening 8, which further comprises a in the axial direction of at least one of the two side surfaces 17 of the rotor disk 2 extending from load receiving element 15, which surrounds the shaft 3 in sections substantially. The cross-section of the shaft 3 adapted load-receiving element 15 is fixedly connected to the rotor disk 2 and increases the carrying capacity and load capacity of the shaft 3 and also protects them from this to be shredded material which passes radially inward. The shaft 3 has a corresponding to the passage opening 8 star-shaped cross-section. The star-shaped cross-section of the shaft 3 comprises a plurality of tips 9, each defined by two radially outwardly converging side surfaces 10 and 11, the side surface 11 converging radially inward with a side surface 10 'of an adjacent tip 9', as in FIG FIG. 6 is shown. More specifically, it is in the in the FIGS. 5 and 6 illustrated star-shaped cross-section of the shaft 3 to a five-star with five tips 9, wherein the illustrated rotor disk 2 five impact hammers 5 has. The tips 9 of the shaft 3 are flattened, so that a sharp outer edge is avoided. In the FIGS. 5 and 6 Further extension lines 12 are shown extending from the center 16 of the star-shaped shaft 3 through a respective tip 9 of the shaft 3 therethrough. These "imaginary" extension lines 12 indicate the direction in which the respective tip 9 points. In doing so, two extension lines 12 of adjacent tips 9, 9 'delimit a resonant circuit or oscillation radius 13 of a respective percussion hammer 5 arranged in-between, as in particular FIG. 5 evident. An inventive feature of the star-shaped in cross section shaft 3 is that the respective adjacent tip 9 or 9 'facing away from side surfaces 10 and 11' are formed parallel to each other. In other words, the side 9 facing away from the tip 9 'of the tip 9' extends parallel to the side surface 10 of the tip 9 facing away from the tip 9 ' two parallel opposite side surfaces 10 and 11 'offer from a manufacturing point of view, a significant advantage over, for example, a known from the prior art pentagonal shaft, since when machining the shaft geometry always two parallel facing surfaces for clamping ready, whereas the non-clamped surfaces can be edited ,

In the FIGS. 7 and 8 a second embodiment of the invention is shown, which differs from the first embodiment in that the rotor disc 2 now instead of a through hole 8 for a star-shaped shaft 3 in the manner of a five-star now a through hole for a trained in cross section in the form of a six star star-shaped wave. 3 ' having. Furthermore, instead of five, six impact hammers 5 are now rotatably mounted on the rotor disk 2. Regardless of the differences mentioned, which essentially result from the fact that the cross section of the star-shaped shaft 3 'of the rotor 1 is a six-star, remain the same inventive features as in the FIGS. 3 to 6 obtained first embodiment, so that reference is hereby made to avoid repetition. Because even in the second embodiment, the tip 9 remote from the side surface 11 'of the tip 9' parallel to the tip 9 'facing away from side surface 10 of the tip 9, as seen FIG. 8 is apparent. Thus, the respective adjacent tip 9 and 9 'facing away from side surfaces 10 and 11' parallel to each other, which offers the advantages mentioned above from a production point of view.

Regardless of whether the cross section of the star-shaped shaft 3, 3 'is a five-star or a six-star, according to the present invention there is the advantage of an enlarged hammer projection, resulting from an enlarged oscillating radius, because of the star-shaped shaft 3 , 3 'of the space remaining on the rotor disk 2 space can be used much more space from the impact hammers 5, as is the case in the prior art. Next to it is the star shape formed shaft 3 or 3 'is an optimized shaft geometry, which has a higher resistance moment compared to the known from the prior art waves for hammer crusher, whereby the star-shaped shaft higher loads, such as higher bending or torsional stresses holds.

The extension elements 4 and / or the spacer elements 14 and / or the load-bearing elements 15 may be welded to the rotor disk 2, so that the rotor disk 2 is formed as a welded assembly. But it is also conceivable that the rotor disk 2 is made with extension elements 4 and / or the spacer elements 14 and / or the load-bearing elements 15 as a one-piece casting.

Of course, the invention described above is not limited to the described and illustrated embodiments. Numerous modifications which are obvious to a person skilled in the art according to the intended application can be made to the embodiments shown in the drawing, without departing from the scope of the invention. In this case, the invention includes everything that is contained in the description and / or shown in the drawing, including what, in deviation from the concrete embodiments, obvious to those skilled in the art.

Claims (9)

1. Rotor (1) of a hammer crusher having at least two rotor discs (2) which are mounted for co-rotation on a shaft (3; 3') at a spacing from one another, a plurality of percussion hammers (5) being swivel-mounted between two adjacent rotor discs (2) at a radial distance from the shaft (3; 3'),
   characterised in that
   the shaft (3; 3') of the rotor (1) in cross-section is star-shaped with a plurality of points (9; 9'), a respective point (9; 9') being defined by two radially outwardly converging side faces (10, 11; 10', 11').
2. Rotor (1) according to claim 1, characterised in that extension lines (12; 12') of adjacent points (9; 9') define a swing radius (13) of a corresponding percussion hammer (5), a respective extension line (12; 12') extending from the centre (16) of the shaft (3; 3') through a respective point (9; 9') of the shaft (3; 3').
3. Rotor (1) according to claim 1 or 2, characterised in that in relation to two adjacent points (9; 9') of the star-shaped shaft (3; 3'), the side faces (10; 11') of the two points (9; 9') remote from the respective adjacent point (9; 9') are embodied to run parallel to one another.
4. Rotor (1) according to one of the preceding claims, characterised in that five percussion hammers (5) are disposed between the at least two rotor discs (2) and in that the cross-section of the star-shaped shaft (3) of the rotor (1) is a five-pointed star.
5. Rotor (1) according to one of claims 1 to 3, characterised in that six percussion hammers (5) are disposed between the at least two rotor discs (2) and in that the cross-section of the star-shaped shaft (3') of the rotor (1) is a six-pointed star.
6. Rotor (1) according to one of the preceding claims, characterised in that adjacent rotor discs (2) are spaced apart by at least one spacer element (14) disposed between them and mounted on at least one of the rotor discs (2).
7. Rotor (1) according to one of the preceding claims, characterised in that a load-bearing element (15) that at least partly encases the shaft (3; 3') and is adapted to the cross-section of the shaft (3; 3') is mounted at least on one of the two side faces (17) of a rotor disc (2).
8. Rotor (1) according to one of the preceding claims, characterised in that each of the at least two adjacent rotor discs (2) comprises a plurality of through-bores (6) corresponding in number to the percussion hammers (5) disposed between them, corresponding through-bores (6) of the adjacent rotor discs (2) being aligned with one another, and an axial rod (7) on which the percussion hammers (5) are swivel-mounted passing through each of the aligned through-bores (6).
9. Rotor (1) according to claim 8, characterised in that an extension element (4) that extends a respective through-bore (6) is mounted on at least one of the two side faces (17) of a rotor disc (2).

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