EP2987556B1 - Grinding machine - Google Patents

Description

The invention relates to a crushing machine, wherein the crushing machine comprises a rotor and a housing, the housing forming a crushing space, a feed chute and an output chute, wherein the rotor is rotatably arranged for crushing feed within the crushing space, such that feed material via the feed chute feedable in the crushing space and crushed feed material via the output shaft from the crushing chamber ausleitbar

Such a crusher is from the DE2516014 known.

In the crushers known from the prior art can be distinguished between crushing machines with rotatable hammers on a rotor and crushing machines without rotatable hammers.

The crushing machines, which include a disk consisting of rotor, are also referred to as a so-called hammer crusher, since between the discs or support disks rotatable impact tools or hammers are stored, by means of which a crushing of, for example, metal scrap, plastic waste, wood waste or similar fractions. Crushing machines without rotatable hammers are regularly referred to as impact mills and have cutting or edges, which also cause a crushing of the crusher fed feedstock. A comminuting of feed pieces, takes place essentially by means of the hammers by impact, wherein by means of the edges or blow bars of the rotor comminution by impact of the feed pieces.

The rotors with hammers serve a comparatively coarse shredding of the feedstock fed, wherein a sieve is regularly arranged below a rotor. The screen serves to fractionate the shredded feed so that shredded feed of a certain size can pass through the wire below the rotor and fall from a shredding space into an output chute below the shredding space. There, the crushed feedstock is collected and can optionally be fed to a further processing step. Larger pieces of the feed still remain above the sieve in the crushing space and are as long as smashed by the hammers until they can also pass through the sieve.

The rotors with cutting edges or edges serve for a comparatively fine comminution of the feed material supplied, the cutting edges or blow bars interacting with an impact rocker or baffle plates in the comminuting space. The impact rocker is formed substantially plate-shaped and arranged in the crushing space relative to the rotor so that a gap of a certain size is formed between the impact rocker or a lower edge of the impact rocker and the rotor. Among other things, feed material fed to the comminution chamber through a feed chute falls onto the rotor and is thrown by the blow bars onto the impact rocker in accordance with the direction of rotation of the rotor and crushed by impact. Pieces of Feed material that is larger than the formed gap can not pass this and remain in the crushing space until they have a corresponding size for passing through the gap. Thereafter, as in the case of a hammer mill, they enter an output shaft located below the shredding chamber. The impact rocker itself may, inter alia, be resiliently mounted and suspended from a fixed swingarm bearing in the comminuting space.

Depending on the nature and size of the feed material, comminution of the feed material may require the use of two different comminution machines. A first crushing machine for crushing large pieces of a feedstock or comminuted material and a downstream, second crushing machine for example, granulation of the crushed material.

Especially in the field of building rubble recycling regularly steel-reinforced concrete is crushed, which often leads to breakage or component failure of a blow bar in conventional crushing machines or impact mills, which are equipped only with blow bars, as reinforced concrete has a very high strength. Crushers with hammers or blow bars are therefore only suitable for a particular, limited type of feed material, wherein for certain feed material, neither of the two embodiments of a crushing machine is advantageously used. This can lead to high material costs and long downtimes as a result of frequent component failure.

Furthermore, downtimes can arise because so-called contaminants are within the crusher. Thus, for example, a manhole cover made of cast steel or other contaminants, which may be contained in a building waste, are not readily crushed. These contaminants can then lead to a standstill of the crushing machine when the contaminant jammed between the impact rocker and the rotor. In this case it is necessary Clear the comminution space of feed material to remove the contaminant from the comminution space. Since this happens manually, this entails risks for the persons in the milling room as well as long downtimes and thus high costs.

Since outer surfaces of the discs can suffer considerable damage due to a collision of material during comminution, it is known to provide the discs with a protective agent. The protective means can extend over a length of the rotor and thus form a wear-resistant, roller-shaped jacket for the disks of the rotor.

The protective means are regularly designed as so-called protective caps and, like the hammers of the rotor, are subject to wear even though they are not actively involved in the comminuting process. The protective caps are therefore also known as inactive wear parts. The protective caps are fastened together with the hammers, which are also referred to as active wear parts, on an axle which is passed through the washers so that the hammers can swing freely and the protective caps substantially completely clear the spaces between the hammers Completion. By removing or extracting the axle from the support disks, the protective caps and the hammers can be exchanged or replaced in case of advanced wear. The axle thus forms a first fastening device for the protective caps and the hammers. The basic structure of such a rotor of a crushing machine is for example from the DE 2 605 751 A1 known.

Thus, it is also known to produce protective caps by casting, wherein a surface exposed to wear of the protective cap, which forms a partial circumferential surface of a lateral surface of the cylindrical shell, can be protected by tempering the surface. So For example, the portions of the protective cap which are not exposed to wear immediately, for example a hub for attachment to an axle, can be made comparatively tough in order to prevent a possible breakage of the protective cap at this point.

The present invention is therefore based on the object to propose a crushing machine, which is universally applicable and which has a long service life.

This object is achieved by a crusher with the features of claim 1.

The crushing machine according to the invention comprises a rotor and a housing, wherein the housing forms a comminuting space, a feed chute and an output chute, wherein the rotor is rotatably arranged for comminuting feed material within the comminuting space, such that feed material can be supplied to the comminution space and comminuted feed material via the feed chute the crushing machine comprises an impact swing device and a screening device, wherein the impact swing device has a movable impact rocker, wherein the impact rocker and the screening device are arranged in the crushing space and associated with the rotor.

Thus, the crusher includes the impact rocker assemblies with the impact rocker as commonly used in an impact mill and the screening apparatus as commonly used in a hammer mill. The screening device is used for fractionation or separation of crushed feed, so that only crushed feed of a desired size from the crushing space can get into the output shaft. The impact rocker, which also serves for the comminution of feed material, is adjacent to the rotor in the comminuting space together with the screening device arranged. Depending on the rotor used, it is possible to grind raw material or comparatively finely, or at the same time make a coarse and fine crushing with the crushing machine. The rotor may have, for example, impact tools and / or blow bars. The crusher is thus universally applicable and can be adapted in connection with the corresponding rotor to a variety of types of feed. Also, it is then no longer necessary to keep ready several types of crushing machines, such as hammer mills and impact mills, for the treatment of feed material.

Advantageously, the impact rocker can be spatially positionable relative to the rotor, such that a gap between the impact rocker and the rotor is adjustable. Thus, the gap can then be adjusted or adjusted so that only in accordance with the size of the gap crushed feed pass through the gap and can get into the output shaft. In addition, removal of contaminants is substantially facilitated by the adjustability of the impact rocker relative to the rotor, since any impurities jammed in the gap can be more easily removed by increasing the gap or adjusting the impact rocker relative to the rotor.

Furthermore, the gap between the impact rocker and the rotor can be adjustable so that feed material and, in particular, contaminants can pass through the gap, wherein a gap width of the gap is 25%, preferably 50%, and particularly preferably 75% of a width of the comminution space (22, 77, 106).

Thus, the impact swinging device can have an impact swinging device with a positioning unit, by means of which the impact swinging rocker can be spatially positioned relative to the rotor. The positioning unit may, for example, comprise a hydraulic cylinder which can move the impact rocker into or out of the comminuting space. The impact rocker can be stored in a swing bearing and also have a spring and / or damping. The rocker bearing may preferably be formed at an upper end of the impact rocker, such that feed material filled into the feed shaft is directed onto the rotor along the impact rocker. By means of the hydraulic cylinder, a comparatively large displacement of the impact rocker can be realized, so that possibly jammed in the gap contaminants can be easily solved by an adjustment of the impact rocker relative to the rotor. If appropriate, the contaminants can then be conveyed into the output shaft alone by the comminution machine, without persons having to get into the comminuting space. Thus, it is then possible to machine-clear the crushing space and to eliminate the contaminants, whereby risks to persons and downtime of the crushing machine can be minimized.

Preferably, the impact swing device can have at least two impact swing device, each with a bumper. The impact wings can then be arranged in series succession, relative to a direction of rotation of the rotor in the crushing space, wherein a first gap relative to the rotor and by means of the second impact rocker, a second gap can be formed relative to the rotor by means of the first impact rocker. In particular, the first gap can then be made larger than the second gap. Thus, then a two-stage crushing of feed material by means of the impact wings done. Advantageously, comparatively larger feed material can be entered via the feed chute than in the case of a comminution machine with only a single impact rocker.

The impact rocker may comprise at least one replaceable baffle plate, which may form a baffle for feedstock. In particular, the impact rocker can also have a plurality of baffle plates for forming the baffle surface. Since the baffles come directly in contact with the feed material, they are a comparatively high Exposed to wear. The fact that the baffles interchangeable, that is, are easily solved by the impact rocker device, they can therefore also be easily replaced when they are worn. The baffles may also be arranged relative to each other so that a plurality of baffles are formed. This can be effected that a guidance of the feed material is effected towards the rotor. The baffles may be disposed at an angle relative to an axis of the rotor so that the feedstock thrown from the rotor onto the baffle is thrown back in a desired direction into the comminution space or onto the rotor.

Furthermore, the sieve device can have a dish-shaped sieve, which can be arranged below the rotor and on the rotor such that an annular gap is formed between the rotor and the sieve. Accordingly, the sieve can be formed in a substantially semicircular cross section, wherein crushed feed material can accumulate in the annular gap and, depending on its size, can pass through the sieve into the dispensing shaft. The sieve can then be used particularly advantageously if the rotor has striking tools or hammers. Even if the rotor has blow bars, these can be used to clear the annular gap to prevent blockage of the screen.

The sieve device can be designed so that the sieve is exchangeable. In principle, the shredding machine can be operated without the sieve, such as an impact mill.

The rotor may be formed of a rotor shaft with spaced apart in the axial direction of the rotor shaft arranged support disks, wherein the rotor comprises a first fastening device, which then serves for rotatably supporting impact tools between the support disks of the rotor, wherein the rotor comprises a second fastening device, which then for fixed mounting of blow bars serves on the support disks of the rotor, wherein the rotor may include striking tools and / or blow bars.

On the rotor, in addition to the first attachment device for the striking tools or hammers, the second fastening device is formed, wherein the second fastening device fixed the blow bars, d. H. unmoved against the support disks of the rotor. Since the rotor then has two fastening devices for impact tools or hammers and blow bars, striking tools and / or blow bars can optionally be attached to the rotor. The second fastening device is in particular designed alone for receiving or holding blow bars. It is provided that the second fastening device allows easy replacement of the blow bars, for example in the case of a component failure. The blow bar may be a strip-shaped component or element.

Due to the fact that the rotor has blow bars, feed material can first be coarsely crushed on the one hand by means of the percussion tools or hammers of the rotor, whereby a finer size reduction of the coarsely comminuted feed material can take place at the same time by means of the blow bars. The finer crushing results on the one hand by a beating effect of the blow bars on the Aufgabegut and on the other hand by an impact effect of the blow bars. The feed material is thus conveyed away from the jacket of the rotor, into a comminuting space. The blow bars consequently lead to a more even distribution of the feed material in the comminution space, which in turn enables improved comminution results to be achieved. Overall, such a rotor is universally applicable, since not pre-shredded, coarse feed material can be crushed comparatively finely with the rotor. Due to the universal properties of the rotor, it can be used in principle for all shredding tasks, such as biomass preparation, waste recycling, wood recycling, stones and soils, building rubble recycling, etc. Also, it is possible the Rotor for shredding tasks only to be equipped with hammers. Alternatively, the rotor can only be operated with blow bars. Accordingly, the rotor can be well adapted to the particular task, optimizing comminution, throughput and possible costs of wear.

In a crushing of, for example, steel-reinforced concrete, the reinforced concrete is pre-shredded by the impact tools, which is carried out by the blow bars nachzerkleinerung on the desired end product. Due to the pre-shredding of the striking tools, it is possible to crush larger pieces of work than in a known from the prior art rotor, which alone has blow bars. On a pre-shredding with another crushing machine can therefore be dispensed with, while at the same time the probability of a component failure of the blow bars can be minimized.

Preferably, the second fastening device for fixed support of the blow bar can be formed directly on or between the support disks. The blow bar can then be attached directly and directly to a support disc, or alternatively be supported by means of the second attachment device in the manner of a hammer or impact tool between the support disks.

The blow bars may be designed to extend in the axial direction of the rotor over an entire length of the rotor. The blow bars can continuously extend across the rotor axis parallel to a rotational axis of the rotor or even partially interrupted by impact tools. Further, the blow bars relative to each other in the radial and axial directions can be arranged offset from one another on the rotor or extend helically over the jacket. Advantageously, the blow bars form a V-shaped pattern on the jacket, so that the feed material can be concentrated in a central region of the jacket.

The blow bars can be arranged distributed in regular, radial intervals over the jacket. Thus, a uniform concentricity of the rotor can be ensured.

An averaged outer diameter or rotational diameter of the blow bars can be formed by the impact tools or hammers radially überragbar. As a result, the impact tools in each case project beyond the outer diameter of the blow bars when swinging through. This ensures that during operation of a rotor, no feed material can concentrate directly on the rotor, since the feed material constantly bounces off the beater bars and is conveyed in the direction of, for example, the hammers.

It when the blow bar is attached to the second fastening device form-fitting and replaceable is particularly advantageous. The blow bar can then be easily replaced by a new blow bar in case of wear or material failure. It is also possible to disassemble the blow bar completely from the rotor and to operate the rotor alone with striking tools. The formation of the second fastening device in the manner that the blow bar is held positively in the second fastening device, allows a particularly stable and resistant attachment of the blow bar on the rotor.

Further, the second fastening device may be formed such that the blow bars are arranged variably in the radial direction relative to the rotor shaft. The blow bar can therefore be adjusted or adjusted in height by means of the second fastening device relative to the rotor shaft, so that a rotation diameter or outer diameter of the blow bars is variably adjustable. The blow bars can therefore be adapted to a wide variety of types and unit sizes of feed material. For example, a continuous height adjustment of a blow bar can be provided by means of the second fastening device.

The second fastening device can be particularly easily formed from two profile elements, wherein the profile elements can then form a receiving groove for the blow bar. The formation of the receiving groove is particularly advantageous since the blow bar can then at least partially inserted into the receiving groove and secured in this. For example, the receiving groove is easy to produce by arranging the profile elements in parallel at a distance relative to each other. Further, a particularly stable attachment of the profile elements can result from the arrangement of the support disks. Also, the profile elements can be welded to the support disks.

Thus, at least one longitudinal groove can be formed in the blow bar, into which engages a projection within the receiving groove. Accordingly, a positive reception or attachment of the blow bar in the receiving groove can be realized particularly easily. The blow bar can then be easily inserted into the longitudinal groove. By the projection within the receiving groove then falling out of the blow bar from the receiving groove in the radial direction is reliably prevented. The projection may be formed, for example, in the manner of a nose, wherein the nose can then engage in the longitudinal groove, which has a matching shape.

In order to prevent premature wear, an application coating may be formed on the profile elements and at least partially on the surface sections of wear elements adjacent to the profile elements. Such an application coating may consist of a wear-reducing, suitable coating material. For example, the application coating can also be formed by welding material onto the profile elements and the adjacent surface sections.

It is also possible to replace the blow bar with a cover strip, wherein the cover strip can then close the receiving groove.

The rotor can then have instead of the blow bars cover strips, not all blow bars must be replaced by cover strips. The cover strip can in principle be designed in the manner of a blow bar, wherein the cover strip can fill the longitudinal groove at least partially without the cover strip projects beyond the longitudinal groove or the receiving groove in the radial direction. Thus, it can be ensured that with disassembled blow bars damage to the second fastening device or the receiving groove and the profile elements is avoided by feed material.

Advantageously, the rotor may include protective caps, wherein the protective caps may be attached to or between support disks, wherein a plurality of radially arranged on or between the support disks protective caps, a roller-shaped shell of the rotor may be formed with openings for the striking tools. The protective caps can thus form a substantially closed jacket, which is broken only by the openings for the impact tools or hammers. The protective caps thus prevent damage to the support disks, in that they are substantially completely covered by the jacket or the protective caps.

The protective cap may be formed from a plurality of elements joined together. The elements may preferably be joined by welding, although other suitable joining techniques may be provided. So it is then also possible to form the elements or wear elements each of materials that are most suitable for a determination of the Schleißelemente.

The wear elements can further have a hardness of 350 to 550 Brinell (HB). Preferably, the hardness can be 430 to 550 Brinell. This ensures that the wear elements or surface sections of the protective cap formed by the wear elements are sufficiently resistant to damage and wear.

The Schleißelemente can be particularly wear resistant and yet inexpensive to produce if they are made of fine-grained structural steel. Fine-grained structural steel is also particularly suitable for a temperature treatment to achieve a desired hardness.

Consequently, the protective caps can form a partial lateral surface of a lateral surface of the jacket, wherein the partial lateral surface of the protective cap can then be formed from at least two planar surface sections. In this case, the protective caps can be distributed in the axial as well as in the radial direction relative to the rotor over the shell and form this by segment-shaped partial circumferential surfaces. The segment-shaped partial circumferential surfaces can be of different size or shape. Also, impact tools do not necessarily have to be arranged between all support disks of the rotor. It is essential, however, that the partial jacket surface of the protective cap or of the respective protective caps of the rotor can be formed from at least two planar surface sections. Because planar surface sections can be used to form the partial jacket surface, it is not necessary to bend a steel sheet to form a partial lateral surface adapted to the rotor or its circular cylindrical form. Any cracking caused by existing segregations in the steel sheet and tensile and compressive stress during bending can thus be effectively avoided. Furthermore, the protective cap can then also be produced in a particularly cost-effective manner, since it is possible to dispense with a complex bending of a comparatively thick steel sheet associated with a machine insert. So it is also possible to achieve a significant cost savings in the production of the protective cap and an extension of a service life of the cap. In further embodiments, the protective cap can also form more than two planar surface sections. It is essential that the entire partial circumferential surface of the protective cap can be composed almost completely or predominantly of flat surface sections.

In a particular embodiment, the protective cap may have support elements, wherein the support elements may be arranged on a support side of the protective cap facing away from the partial lateral surface such that the protective cap can be adapted to a shape of the support plates. In particular, if the support disks have a round or circular outer contour, the protective caps can then be adapted by means of the support elements to the respective outer contour of the support disks so that the protective caps each rest on at least two points on the support disks or their outer contour. The protective caps can then be supported by means of the support elements on the support disks, wherein moreover a tilting of the protective caps or an undesirable relative movement to the support disks can be easily avoided. Preferably, it can be provided to use three support elements for supporting a protective cap on an outer contour of a support disk. However, the protective cap can also rest on the support disks at other points of the protective cap on which no support elements are arranged.

A fastening web of the protective cap may be formed of a connecting plate for the Schleißelemente, wherein the connecting plate may also be reinforced with reinforcing plates. Consequently, the Schleißelemente can be connected to each other via the fastening web, wherein the Schleißelemente can be welded to the fastening web or the connecting plate. For example, to ensure a particularly durable attachment of the Schleißelemente to the connection plate, the reinforcing plates can be arranged on both sides of the connecting plate and also connected or joined with two Schleißelementen. Thus, it is also possible to realize a particularly good attachment of the protective cap on, for example, an axis of a rotor, since the axis can be passed through a passage opening in the connecting plate and the reinforcing plates.

It is particularly advantageous if the surface sections are each formed from a plate-shaped or straight-shaped wear element. The plate-shaped Schleißelement can be particularly easily made of a steel sheet by cutting. Furthermore, the plate-shaped wear element can then also be subjected to a temperature treatment, such as, for example, annealing, hardening and / or tempering. A possible deformation of the plate-shaped Schleißelemente due to the temperature treatment is not important in contrast to curved Schleißelementen.

The protective cap can be designed so that surface normal of the surface portions can intersect in a rotational axis of the rotor. Thus, a possible imbalance of the rotor can be prevented, wherein the jacket of the rotor can be further approximated to a circular shape.

The surface portions may preferably be arranged such that surface normals of the surface portions extend relative to each other at an angle α. The angle α can be a deviating from 0 °, acute angle. Thus, it is then also possible to form a rotor from a plurality of protective caps, which forms a comparatively round cross-section.

The angle α may be defined by 360 ° divided by the number of area sections relative to a circumference of the shell. The angle α can then be the same for all the protective caps forming the sheath. Thus, the surface portions may then each have a respect to the circumference of the shell same radial length. The flat surface sections are made even easier.

It is particularly advantageous if the wear elements are welded directly to each other. Thus, a completely closed partial circumferential surface can be formed for a protective cap. In the case, that the protective cap is formed of a plurality of elements, all elements can be welded together.

Alternatively, the protective cap can also be designed as a one-piece cast element, wherein the protective cap can then also have the shape of a welded or otherwise joined protective cap. Thus, the advantages arising from the planar surface sections with regard to a treatment of the feed material can also be used for cast protective caps.

Preferably, the protective cap can be firmly fixed to the first fastening device. Thus, the protective cap can form a fastening web with a hub for fastening the protective cap on or between carrying disks. The fastening web can then be arranged in the radial direction relative to a surface section at right angles to this. If the rotor has axles which are inserted through openings of the support disks or the support disks themselves form axles or projections, the protective cap can easily be attached to the hub on an axle and thus securely fastened.

Alternatively, at least one protective cap can also form the second fastening device. The protective cap can then support at least one blow bar. If the protective cap forms the second fastening device, the blow bar can be attached to the second fastening device in a form-fitting and replaceable manner. Since the blow bar is exposed due to their exposed position on the jacket of a particularly high stress, the blow bar can then be easily replaced according to a wear of the blow bar. Depending on the design of the positive attachment of the blow bar on the cap, it may not even be necessary to disassemble the cap from the rotor, but the respective worn blow bars can be dismantled by the rotor by itself.

The blow bar can thus cause a rebound of feed material from the jacket when the rotor rotates. An undesirable concentration of feed material directly on the lateral surface can be avoided alone by the formation of the protective caps with the second fastening device and the blow bar. It is basically irrelevant whether the blow bar runs as an element over the entire jacket of the rotor or only a protective cap. In this case, then a plurality of protective caps each hold blow bars. A blow bar can then project beyond the jacket or a protective cap in a comminution chamber so that the blow bar can come into direct contact with feed material during a rotation of the rotor.

Alternatively, the second fastening device may be formed on at least one support disk. Then it is not necessary to use protective caps for forming the second fastening device. However, protective caps may be attached to the rotor at the first attachment device. It is also entirely possible to dispense with protective caps, with the carrying discs then being able to come into contact with the feed material. Depending on the nature of the feedstock, however, this can be conducive to a comminution process. An embodiment of the second fastening device on the support disk can be effected, for example, in that a recess for the positive reception of a blow bar is formed in the support disk. Also, a receptacle for mounting a blow bar welded to one or more support disks, which then forms the second fastening device.

Further, the rotor may comprise a third fastening device, which serves for the immovable or fixed support of protective plates on each of the support disks of the rotor, wherein the protective plates then form a partial circumferential surface of a lateral surface of the jacket, and wherein the third fastening device adjacent to the second fastening device can be trained. Accordingly, the rotor may also comprise protective plates which are inserted in or attached to the third fastening device. The protective plates can then like the protective caps cover the support plates and protect them from wear. Thus, the protective plates can also form the lateral surface of the jacket adjacent to the blow bar. The third fastening device may for example be formed as a groove, which allows a positive fastening of the protective plates on the support disks. The protective plates can then be easily inserted into the groove in the longitudinal direction of the rotor. The groove can in each case be formed in the support disks, for example in the form of a T-slot, or from elements welded to the support disks.

The blow bar may consist of a cast material, a fine-grained structural steel or a ceramic insert, wherein the blow bar may have a hardness of 150 to 600 Brinell (HB), preferably a hardness of 350 to 550 Brinell (HB). Particularly preferably, the blow bar can also have a hardness of 430 to 550 Brinell. The hardness of the blow bar or the material can be selected so that the blow bar is adapted to the respective feed material.

The jacket of the rotor may be polygonal in the radial direction, based on a cross section of the rotor. By using three or more surface portions for a protective cap or more than six protective caps for the cross section, the polygonal shape of the shell can be further approximated to a circular shape. Furthermore, it can be provided to select the polygonal shape of the jacket as a function of the nature of the feedstock. Unlike an all-round shell, the feedstock can not slide along the shell upon rotation of the rotor and cause abrasive wear. A concentration of feed material directly on the jacket is thus prevented.

In particular, the jacket in the radial direction, based on a cross section of the rotor, have at least six protective caps. When each of the protective caps forms two surface portions of the sheath, the sheath may be formed in the cross section of twelve straight surface portions.

Hereinafter, preferred embodiments of the invention will be explained in more detail with reference to the accompanying drawings.

Fig. 1

eine Querschnittansicht einer ersten Ausführungsform eines Rotors mit Schlagleisten in einer ersten Ausführungsform;

Fig. 2

eine Seitenansicht der ersten Ausführungsform des Rotors;

Fig. 3

eine Längsschnittansicht des Rotors aus Fig. 1 ;

Fig. 4

eine Detailansicht des Rotors aus Fig. 1 ;

Fig. 5

eine Abwicklung eines Mantels des Rotors aus Fig. 1 ;

Fig. 6

eine perspektivische Ansicht einer Schutzkappe in einer zweiten Ausführungsform;

Fig. 7

eine perspektivische Ansicht einer Schutzkappe in einer dritten Ausführungsform;

Fig. 8

eine Prinzipdarstellung des Rotors aus Fig. 1 mit Schutzkappen in der zweiten Ausführungsform;

Fig. 9

eine Querschnittansicht einer zweiten Ausführungsform eines Rotors mit Schlagleisten in einer zweiten Ausführungsform und mit Schutzkappen in einer vierten Ausführungsform;

Fig. 10

eine perspektivische Ansicht einer Schlagleiste in der zweiten Ausführungsform mit einer Schutzkappe in der vierten Ausführungsform;

Fig. 11

eine perspektivische Ansicht einer Schlagleiste in der zweiten Ausführungsform mit einer Schutzkappe in einer fünften Ausführungsform;

Fig. 12

eine Seitenansicht der Schlagleiste aus Fig. 9 ;

Fig. 13

eine Seitenansicht einer Schlagleistenaufnahme der Schutzkappe aus Fig. 9 ;

Fig. 14

eine Querschnittansicht einer Ausführungsform einer Zerkleinerungsmaschine.

Show it:

Fig. 1

a cross-sectional view of a first embodiment of a rotor with blow bars in a first embodiment;

Fig. 2

a side view of the first embodiment of the rotor;

Fig. 3

a longitudinal sectional view of the rotor Fig. 1 ;

Fig. 4

a detailed view of the rotor Fig. 1 ;

Fig. 5

a settlement of a shell of the rotor Fig. 1 ;

Fig. 6

a perspective view of a protective cap in a second embodiment;

Fig. 7

a perspective view of a protective cap in a third embodiment;

Fig. 8

a schematic diagram of the rotor Fig. 1 with protective caps in the second embodiment;

Fig. 9

a cross-sectional view of a second embodiment of a rotor with blow bars in a second embodiment and with protective caps in a fourth embodiment;

Fig. 10

a perspective view of a blow bar in the second embodiment with a protective cap in the fourth embodiment;

Fig. 11

a perspective view of a blow bar in the second embodiment with a protective cap in a fifth embodiment;

Fig. 12

a side view of the blow bar Fig. 9 ;

Fig. 13

a side view of a rasp bar recording of the cap Fig. 9 ;

Fig. 14

a cross-sectional view of an embodiment of a crushing machine.

A synopsis of Fig. 1 to 3 shows a rotor 10 in different views. The rotor 10 is arranged in a crusher, not shown here, and formed from a rotor shaft 11, support disks 12 and designed as a hammer 13 striking tools 14. Furthermore, the rotor 10 comprises protective caps 15 which at least partially form a cylindrical shell 16 of the rotor 10, openings 17 for the hammers 13 being provided in the shell 16. The protective caps 15 and the hammers 13 are attached to a first fastening device 18 on the support disks 12. The first fastening device 18 is formed in each case by an axle 19, which is inserted into through holes 20 of the support disks 12 and connects the not further illustrated, further support disks together. Consequently, the protective caps 15 and the hammers 13 between the support disks 12 are secured to the axles 19. The protective caps 15 lie on the support disks 12, wherein the hammers 13 are freely rotatably mounted and can swing through. The rotor 10 is rotatable in a direction of rotation indicated by an arrow 21. In a crushing space 22, the boundary walls not shown here in detail, is to be crushed, and here also not shown in detail feed material, which rebound from a lateral surface 23 of the shell 16 and can reach into an effective range of the hammers 13. The protective caps 15 form a partial circumferential surface 24 of the lateral surface 23 with two planar surface portions 25. The surface portions 25 are each formed of a plate-shaped Schleißelement 26, wherein the Schleißelemente 26 are joined by means of a weld 27 directly to each other.

Further, two second fastening devices 28 are formed on the rotor 10 for receiving a respective blow bar 29. Like the detail view in Fig. 4 can be seen, the second fastening device 28 is formed as a recess 30 in the support plate 12, wherein profile elements 31 and 32 form a receiving groove 33 for the positive reception of the blow bar 29. The blow bar 29 in turn has grooves 34 and 35 into which a nose 36 of the profile element 31 can engage. The profile elements 31 and 32 are each welded directly to the support plate 12. The profile elements 31 and 32 are so far apart that between the profile elements 31 and 32, a blow bar receptacle 37 is formed, in which the blow bar 29 can be inserted laterally. Depending on the intervention of the nose 36 in the groove 34 or the groove 35, the blow bar can be inserted at different heights in the blow bar receptacle 37. A positive fixation of the blow bar 29 is effected by the engagement of the nose 26 in one of the grooves 34 and 35th

Further, third fastening devices 38 are formed on the rotor 10 for fixed support of protective plates 39 on the support disks 12. The protective plates likewise form a partial circumferential surface 40 of the lateral surface 23. The third fastening device 38 is substantially formed as a T-shaped groove 41, in which the protective plate 39 can each engage positively with a sliding block 42 or a correspondingly formed extension. The third fastening device 38 is reinforced by welded to the support plate 12 profile elements 43 and 44, respectively.

The Fig. 5 shows a development of the shell 16 of the rotor 10. The shell 16 covers the support plates 12, which are here indicated, completely off, and is essentially from the hammers 13, the protective caps 15, the beaters 29 and the protective plates 39 is formed. A rotational direction of the rotor 10 is indicated by an arrow 45. The hammers 13 are arranged in the direction of rotation V-shaped, so that feed material can be concentrated during a rotation of the rotor 10 essentially in a central region of the jacket 16 or of the rotor 10. The protective caps 15 are adapted to the arrangement of the hammers 13 in terms of their axial length.

The blow bar 29 can be replaced if necessary by a cover strip, not shown here, which is flush with the profile elements 31 and 32. Furthermore, it is also possible to disassemble the hammers 13 and to close the remaining openings 17 with further protective caps 15. This makes it possible for the rotor 10 to be variably adjusted as needed and requirements arising from the respective task. It can, such as in Fig. 1 represented, an outer diameter 46 and a rotational diameter of the blow bars 29 are surmounted by an outer diameter 47 of the hammers 13.

The Fig. 6 shows a protective cap 48 for a rotor not shown here with polygonal support disks, the protective cap 48 is formed of two plate-shaped Schleißelementen 49, a connecting plate 50 and reinforcing elements 51. The connecting plate 50 and the reinforcing elements 51 form a fastening web 52 with a through-opening 53 for an axis 54 shown here in an indicative manner for fastening the protective cap 48 to the rotor. The connecting plate 50, the reinforcing elements 51 and the Schleißelemente 49 are completely on welded joints connected to each other, wherein in particular the Schleißelemente 49 are directly connected to each other with a weld 55. On the weld 55 a wear material 56 is additionally applied. Further, the Schleißelemente 49 via the connecting plate 50 and the reinforcing elements 51 are interconnected. The connecting plate 50 and the reinforcing elements 51 and the fastening web 52 can be used in a space not shown in detail between two support disks of a rotor, wherein the Schleißelemente 49 then rest with a support side 57 on the respective support disks.

The Fig. 7 shows a protective cap 58, the Schleißelemente 59 and a fastening web 60 for attachment to an axis 61 has. The Schleißelemente 59 are also directly connected via a weld 62 with an order of wear material 63. Furthermore, the protective cap 58 comprises support elements 65 and 66 arranged on a support side 64 of the wear elements 59. The support elements 65 are each arranged at radial ends 67 of the protective cap 58, the support elements 66 being arranged in the region of the weld 62. The support elements 65 and 66 form concave bearing surfaces 68 and 69 for supporting the protective cap 58 on a circular support disk, not shown here.

The Fig. 8 shows a schematic diagram of the rotor 10 with a protective cap 15 and a support plate 12. The measure of a distance X results from a radius r of the support plate 12 divided by cos β - r. The angle β is defined by a surface normal 70 of a surface portion 71 of the protective cap 15 and a tangent 72 of the protective cap 15, wherein the tangent 72 and the surface normal 70 intersect in an axis of rotation 73 of the rotor 10.

The Fig. 9 shows a rotor 74, which differs from the rotor Fig. 1 Protective caps 75 having a blow bar 76. The blow bars 76 protrude into a crushing space 77, so that feed material 78 of the blow bar 76, as hinted here, rebound and can be crushed by impact.

The Fig. 10 shows a protective cap 79, which has two Schleißelemente 80 and the Schleißelemente 80 connecting fastening web 81. The Schleißelemente 80 are each spaced so far apart that between the Schleißelementen 80 profile elements 82 and 83 are arranged, which form a rasp bar holder 84 in the form of a longitudinal groove 85 for a whip bar 86. The protective cap 79 thus forms with the blow bar holder 84, a second fastening device 87 for holding the blow bar 86 from. The profile element 83 has a nose 88 extending along the profile element 83, which engages in a matching groove 89 of the beater strip 86. Furthermore, an application coating 90 is provided which completely covers the profile elements 82 and 83 and the wear elements 80 at least partially.

The Fig. 11 shows a protective cap 91 as in Fig. 10 described cap is formed, but as in Fig. 7 described protective cap on support members 92 and 93 has.

The FIGS. 12 and 13 show a blow bar 94 and profile elements 95 and 96 respectively in enlarged side views. The blow bar 94 has a groove 97 into which a nose 98 of the profile element 96 can engage. The blow bar 94 is formed substantially rectangular in shape and consists of fine-grained structural steel with a hardness of up to 550 Brinell. The profile elements 95 and 96 are each welded directly to a support element 99 and wear elements 100. The profile elements 95 and 96 are spaced apart so far that between the profile elements 95 and 96, a blow bar receptacle 101 is formed, in which the blow bar 94 can be inserted laterally. An interlocking fixation of the beater bar 94 takes place through the groove 97 and the nose 98 in the blow bar receptacle 101. Next, a coating coating 102 is formed.

The Fig. 14 shows a cross-sectional view of a crushing machine 103. The crushing machine 103 comprises a housing 104 which forms a feed slot 105 for receiving feed material not shown here. The feed chute 105 opens into a comminution chamber 106 in which a rotor 107 is rotatably arranged. The rotor 107 substantially corresponds to that in FIG Fig. 2 represented rotor. The comminuting space 106 is adjoined by an output shaft 108, via which the comminuted feed material can be discharged from the comminuting machine 103. Further, the crushing machine comprises a screening device 109, which is essentially formed by a dish-shaped screen 110 and is arranged below the rotor 107 so that an annular gap 111 is formed between the rotor 107 and the screen 110. In the screen 110, a plurality of through holes 112 are formed, can fall through the crushed feed material. The passage openings 112 determine a grain size of the comminuted feedstock and are designed here as round, but may in principle have any desired cross-section.

The crushing machine 103 further includes an impact swinging device 113, which in turn has two impact swinging devices 114 and 115, wherein the impact swinging devices 114 and 115 each have an impact rocker 116 or 117 and a positioning unit 118 or 119. The impact wings 116 and 117 are rotatably mounted respectively in swingarm bearings 120 and 121 on the housing 104. Further, the impact wings 116 and 117 by means of hydraulic cylinders 122 and 123 of the positioning units 118 and 119 into the crushing chamber 106 or optionally be moved out. At the impact wings 116 and 117, a plurality of baffles 124, 125 and 126 are releasably attached, so that they can be easily replaced.

Moreover, in the crushing space 106 and the feed chute 105, wedging members 127 are arranged to be damaged of the housing 104 and the feed shaft 105 and the crushing chamber 106 to avoid. The rotor 107 is provided with hammers 128 and blow bars 129, so that the hammers 128 define an outer diameter 130 of the rotor 107. The impact rocker 116 is now arranged by means of the hydraulic cylinder 122 relative to the rotor 107 so that between the impact rocker 116 and the outer diameter 130, a first gap 131 is formed. The impact rocker 117 is arranged relative to the rotor by means of the positioning unit 119 such that a second gap 132, which follows the first gap 131, is formed between the impact rocker 117 and the outer diameter 130 relative to a direction of rotation of the rotor 107. Preferably, the first gap 131 is larger than the second gap 132 is formed.

Claims (15)

1. A grinding machine (103), the grinding machine comprising a rotor (10, 107) and a housing (104), the housing forming a grinding chamber (22, 106), a feed shaft (105) and an output shaft (108), the rotor being disposed rotatably within the grinding chamber for grinding feed material in such a manner that feed material can be fed to the grinding chamber via the feed shaft and ground feed material can be discharged from the grinding chamber via the output shaft, the grinding machine comprising a screening device (109), the screening device being disposed in the grinding chamber and being associated with the rotor, the rotor being formed by a rotor shaft (11) having support discs (12) disposed in a spaced apart manner in the axial direction of the rotor shaft, the rotor comprising a first fixing device (18) which serves to rotatably support impact tools (14, 128) between the support discs of the rotor, the grinding machine comprising an impact rocker device (113), the impact rocker device having a movable impact rocker (116, 117), the impact rocker being disposed in the grinding chamber and being associated with the rotor,
   characterized in that
   the rotor comprises a second fixing device (28), the second fixing device being formed at least at one support disc (12) and serving to firmly mount impact bars (29, 129) on the support discs of the rotor, the rotor comprising impact tools and/or impact bars.
2. The grinding machine according to claim 1,
   characterized in that
   the impact rocker (116, 117) is formed to be spatially positionable relative to the rotor (10, 74, 107) in such a manner that a gap (131, 132) between the impact rocker and the rotor is adjustable.
3. The grinding machine according to claim 2,
   characterized in that
   the gap (131, 132) between the impact rocker (116, 117) and the rotor (10, 107) is adjustable in such a manner that feed material can pass the gap, a gap width of the gap corresponding to 25 %, preferably 50 %, and especially preferably 75 %, of a width of the grinding chamber (22, 106).
4. The grinding machine according to any one of the preceding claims,
   characterized in that
   the impact rocker device (113) has an impact rocker means (114, 115) with a positioning unit (118, 119) by means of which the impact rocker (116, 117) can be spatially positioned relative to the rotor (10, 107).
5. The grinding machine according to claim 4,
   characterized in that
   the impact rocker device (113) has at least two impact rocker means (114, 115), each having one impact rocker (116, 117).
6. The grinding machine according to any one of the preceding claims,
   characterized in that
   the impact rocker (116, 117) has at least one exchangeable impact plate (124, 125, 126) which forms an impact surface for feed material.
7. The grinding machine according to any one of the preceding claims,
   characterized in that
   the screening device (109) has a shell-shaped screen (110) which is disposed below the rotor (10, 107) and on the rotor in such a manner that an annular gap (111) is formed between the rotor and the screen.
8. The grinding machine according to claim 7,
   characterized in that
   the screening device (109) is formed in such a manner that the screen (110) is exchangeable.
9. The grinding machine according to any one of the preceding claims,
   characterized in that
   the impact tools (14, 128) can radially project beyond an outside diameter (46) of the impact bars (29, 129).
10. The grinding machine according to any one of the preceding claims,
    characterized in that
    the impact bar (29, 129) is fixed in a positive-locking and exchangeable manner on the second fixing device (28).
11. The grinding machine according to any one of the preceding claims,
    characterized in that
    the second fixing device (28) is formed in such a manner that the impact bars (29, 129) can be disposed variably in the radial direction relative to the rotor shaft (11).
12. The grinding machine according to any one of the preceding claims,
    characterized in that
    the second fixing device (28) forms a receiving groove (33) for the impact bar (29, 129), the impact bar being replaced by a cover strip, the cover strip closing the receiving groove.
13. The grinding machine according to any one of the preceding claims,
    characterized in that
    the rotor (10, 107) comprises protective caps (15, 48, 58), the protective caps being fixed on or between support discs (12), a cylindrical shell (16) of the rotor with openings (17) for the impact tools (14, 128) being formed by a plurality of protective caps which are disposed radially on or between the support discs.
14. The grinding machine according to claim 13,
    characterized in that
    the protective cap (15, 48, 58) is formed by a plurality of elements joined together, the protective cap forming a partial shell surface (24, 40) of a shell surface (23) of the shell (16), the partial shell surface of the protective cap being formed by at least two plane surface sections (25, 71).
15. The grinding machine according to claim 13 or 14,
    characterized in that
    the protective caps (15, 48, 58) are firmly fixed on the first fixing device (18).

Images