EP3538278B1 - Broyeur à deux arbres avec jeu de lames de coupe interchangeables et extrémités d'arbre détachables - Google Patents

Broyeur à deux arbres avec jeu de lames de coupe interchangeables et extrémités d'arbre détachables Download PDF

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Publication number
EP3538278B1
EP3538278B1 EP17801428.8A EP17801428A EP3538278B1 EP 3538278 B1 EP3538278 B1 EP 3538278B1 EP 17801428 A EP17801428 A EP 17801428A EP 3538278 B1 EP3538278 B1 EP 3538278B1
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EP
European Patent Office
Prior art keywords
shaft
cutting disc
dual
oil
stub
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17801428.8A
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German (de)
English (en)
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EP3538278A1 (fr
Inventor
Torsten BURHORST
Hugo Vogelsang
Paul Krampe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hugo Vogelsang Maschinenbau GmbH
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Hugo Vogelsang Maschinenbau GmbH
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Priority to PL17801428T priority Critical patent/PL3538278T3/pl
Publication of EP3538278A1 publication Critical patent/EP3538278A1/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
    • B02C18/00—Disintegrating by knives or other cutting or tearing members which chop material into fragments
    • B02C18/06—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives
    • B02C18/14—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives within horizontal containers
    • B02C18/142—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives within horizontal containers with two or more inter-engaging rotatable cutter assemblies
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C18/00—Disintegrating by knives or other cutting or tearing members which chop material into fragments
    • B02C18/0084—Disintegrating by knives or other cutting or tearing members which chop material into fragments specially adapted for disintegrating garbage, waste or sewage
    • B02C18/0092—Disintegrating by knives or other cutting or tearing members which chop material into fragments specially adapted for disintegrating garbage, waste or sewage for waste water or for garbage
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C18/00—Disintegrating by knives or other cutting or tearing members which chop material into fragments
    • B02C18/06—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives
    • B02C18/16—Details
    • B02C18/18—Knives; Mountings thereof
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C18/00—Disintegrating by knives or other cutting or tearing members which chop material into fragments
    • B02C18/06—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives
    • B02C18/16—Details
    • B02C18/18—Knives; Mountings thereof
    • B02C18/182—Disc-shaped knives
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C25/00—Control arrangements specially adapted for crushing or disintegrating

Definitions

  • the invention relates to a twin-shaft shredder for comminuting solids or solids in liquids, comprising: a housing which defines an internal comminuting space, an inlet opening in the housing for supplying solids into the comminuting space, an outlet opening in the housing for removing comminuted solids from the Comminution room, a first cutter disk block with a plurality of first cutter disks which are arranged on a first hub body in such a way that there is a space between two adjacent first cutter disks, a second cutter disk block with a plurality of second cutter disks which are arranged on a second hub body in such a way that there is a space between two adjacent second cutter disks, the first and second cutter disk blocks being axially offset from one another in such a way that at least some of the first cutter disks each enter a space between, for two adjacent second cutter disks engage and some of the second cutter disks each engage in a space between two adjacent first cutter disks, the first and second cutter disk blocks each
  • Two-shaft shredders of this design are used to cut solids, for example organic substances such as branches, twigs, plants or other materials such as Shred plastic waste.
  • the solids to be shredded can be fed to the twin-shaft shredder through the inlet opening in dry form or in a liquid stream.
  • twin-shaft shredders have two shafts, on each of which a large number of cutter disks are arranged. These cutter discs mutually interlock, which is made possible and achieved by the fact that there is an axial distance between two adjacent cutter discs of one shaft which is greater than the thickness of one cutter disc of the other shaft and the center distance of the two shafts from one another is smaller than the diameter of one cutter disc .
  • the two shafts of a twin-shaft shredder are typically driven in opposite directions and, for this purpose, are coupled to one another, for example, via a corresponding gear.
  • a good shredding result is achieved in particular when the two shafts rotate at different speeds. In this way, high shear forces and tearing forces are caused by the counter-rotating cutter disks in the space between the two shafts, which leads to an effective comminution of the solids.
  • different speeds have the effect that other knife segments of adjacent knife disks come into engagement with each other with each rotation, as a result of which the knife disks are automatically cleaned of adhering material to be shredded.
  • twin-shaft shredders with a quick-change system in which the knives can be removed from the shafts in order to replace such damaged knives. This ensures that the functionality of the twin-shaft shredder can be restored with a small amount of maintenance.
  • twin-shaft grinders Another disadvantage of known twin-shaft grinders is that a solid body that gets between two intermeshing knife disks or between one knife disk and the opposite shaft can lead to a considerable torque peak on these two knife disks or one of the knife disks. This torque peak can have the consequence that the torque-proof support of a cutter disk on a shaft can loosen. Such damage to the torque-proof anchoring of a knife disk on the shaft can make further operation of the twin-shaft shredder impossible or only continue with limited efficiency and in particular with the risk of further damage to other components of the twin-shaft shredder.
  • FIG US 5275342 A Another example of a twin-shaft shredder with one-piece cutter disk blocks is shown in FIG US 5275342 A known.
  • these one-piece cutter block blocks - also known as monolithic ripper rotors - are designed in several parts, because on the one hand the production of long, axial, precisely fitting receiving bores is complex and on the other hand assembly is very difficult with such long cutter block blocks, since both cutter blocks simultaneously on the long parallel shafts be postponed have to.
  • the space requirement for pushing on one-piece long knife disk blocks is also very large.
  • Two-shaft shredders of conventional designs with individual knife disks or knife disk blocks pushed onto shafts can only be produced in larger and thus more economical lengths if they have additional support bearings in the shredding chamber.
  • these additional support bearings have the disadvantage that they reduce the possible throughput because they take up a certain length of the crushing space, they also create problems because materials to be crushed can be supported on them so that they cannot be crushed and then additionally narrow or even completely block the passage cross-section.
  • these support bearings are exposed to the product on both sides, so that a reliable seal is very difficult to achieve, so that the bearings often fail and then have to be replaced at great expense. They also make it difficult to replace damaged or worn knives.
  • the support bearings also cause considerable additional costs in the manufacture of the twin-shaft shredder.
  • the invention solves the problem with a twin-shaft shredder according to claim 1.
  • the twin-shaft shredder comprises a first stub shaft that extends into the first axial recess of the first cutter block for transmitting torque, a second stub shaft that extends into the first axial recess of the second cutter block for Transmitting torque extends, a first clamping device for clamping the first stub shaft against the first cutter block, a second clamping device for clamping the second stub shaft against the second cutter block and a first and a second axle insert, the first and second cutter blocks each having a second have axial recess and the first axle insert is received in the second axial recess of the first cutter block and the second axle insert is received in the second axial recess of the second cutter block, the first and second axial recesses being connected to one another by an axial bore and the clamping devices means for bracing the first axle insert against the first shaft stub and the second axle insert against the second shaft stub exhibit.
  • the invention is based on the knowledge that in the case of cutter disk blocks which have a central hub body on which the individual cutter disks are arranged, it is not necessary to pass the drive shaft completely through the hub body of the corresponding cutter disk block. Rather, it is sufficient to provide stub shafts which extend into corresponding recesses on the cutter disk block, in particular the respective hub body of the cutter disk block, and transmit corresponding torques to the corresponding cutter disk block. As a result, the axial length of a cutter disk block with respect to the stub shaft is variable and independent of the precise design of the stub shaft.
  • first and second clamping devices are provided, by means of which the corresponding cutter disk blocks can be clamped against the stub shaft.
  • the stub shafts do not extend completely through the corresponding hub body of the respective cutter disk block, but rather have an axial length that is in a range from 5% to 30%, preferably in a range from 5% to 15%, particularly preferably around 10 % is.
  • the fixation between the shaft stub and the cutter block, in particular the axial fixation is realized by means of the clamping device.
  • This can, for example, comprise a radially expanding clamping body, such as a double cone or the like, in the interior of the recess in order to provide clamping.
  • the torque transmission is preferably implemented by means of a feather key or another conventional shaft-hub connection.
  • the individual cutter disks are preferably formed in one piece on the hub body, in particular the cutter disk block is entirely machined from solid material by means of machining, in particular turning and milling.
  • the second axial recesses are preferably provided on the opposite end with respect to the first axial recesses on the cutter disk block, in particular the hub body.
  • the first and second axial recesses are each connected to one another by an axial bore and the Tensioning devices have means for bracing the first axle insert against the first shaft stub and the second axle insert against the second shaft stub, the assembly is further simplified. If the corresponding cutter disk blocks are plugged onto the corresponding stub shaft, it is possible to clamp them from the free end of the cutter disk blocks by means of the clamping devices.
  • a pull rod, pull rope or other pulling means is provided for this purpose, which pulls the first or second axle insert against the first or second shaft stub.
  • Known tensioning means such as in particular screw connections or the like, can be provided for tensioning the pull rod, the pull rope or the like.
  • the first and second stub shafts each have a frustoconical section, which with a corresponding frustoconical section of the first axial recesses of the first and the second cutter block is in contact.
  • the frustoconical section on the first and second shaft stubs is preferably provided on their axial end face, that is to say the end facing away from a drive.
  • the frustoconical section is consequently provided at the end of the stub shaft that is received in the recess on the cutter block blocks.
  • the frustoconical section is designed in such a way that the stub shafts taper towards the axial end.
  • the first axial recesses have a corresponding frustoconical section in such a way that the recesses likewise taper slightly in the direction of the center of the cutter disk blocks.
  • Such a design of corresponding frustoconical sections can compensate for manufacturing tolerances. This significantly simplifies both production and assembly. Due to the corresponding frustoconical sections, self-centering of the cutter disk blocks with the corresponding stub shafts takes place at the same time.
  • the frustoconical section of the cutter disk blocks is preferably formed by a sleeve which is inserted in the first axial recess. This further simplifies production. It is also possible to manufacture the sleeve from a different material than the cutter block itself.
  • the sleeve is preferably pretensioned by means of a spring assembly.
  • a shoulder on which a spring assembly is supported is provided at the foot end of the recess.
  • the spring assembly preferably has a plurality of disc springs.
  • a mediating element is provided between the sleeve and the spring assembly, which is used, for example, to center the spring assembly. This compensates for further play and ensures that the two frustoconical surfaces bear against one another without play. The corresponding cutter disk block is therefore clamped against the corresponding stub shaft without play.
  • the means for bracing preferably have a first and a second threaded rod.
  • the first threaded rod is preferably received in a threaded bore in the first shaft stub and extends into or through a through bore in the first axle insert, and at the same time the second threaded rod is received in a second threaded bore in the second shaft stub and extends through a through bore in the second Axle insert.
  • the through bores in the axle inserts can be designed as threaded bores.
  • the through bores are provided without thread, and a nut is provided on the outer side of the axle inserts in relation to the cutter block blocks, by means of which the first and second axle inserts can be pretensioned in the direction of the first and second shaft stubs. This achieves a particularly simple bracing of the cutter disk blocks on the stub shafts.
  • first and second axle inserts are designed as axle stubs for mounting the first and second cutter disk blocks. This makes it possible to mount the cutter disk blocks in a simple manner on the side opposite the shaft stubs. Such a double bearing is preferred, since high bearing forces can sometimes occur when cutting solid material.
  • first and second axle inserts each have a frustoconical section that is matched with a corresponding frustoconical section Section in second recesses of the first and second cutter block blocks are in contact.
  • the first and second axial recesses in the cutter disk blocks are particularly preferably designed symmetrically to one another.
  • symmetrical means that both mirror and point symmetry are preferred, as is mirror symmetry in which the first and second recesses are rotated relative to one another with respect to a central axis. More than the symmetry, it is rather decisive that their internal geometry is essentially identical. This makes it possible to rotate each of the cutter disk blocks and, for example, to plug the first cutter disk block with the second axial recess onto the first stub shaft. This further simplifies assembly. Production is also simplified, since it is not necessary to provide two different recesses, but rather it is possible to form them identically. As a result, the same parts can still be used and production is simplified.
  • a sleeve and a corresponding spring assembly are also preferably provided in the second axial recess, so that the axle insert, which is preferably designed as an axle stub, can also be braced against the corresponding cutter disk block without play.
  • the first and second stub axles are accommodated in a bearing housing which, together with the stub axles, forms a unit and can be reversibly removed as a unit from the cutter disc blocks and / or the housing in which the cutter disc blocks are arranged.
  • the clamping devices are preferably accessible from outside the bearing housing or on it. In this way, the bearing housing can be plugged onto the two cutter disk blocks as a structural unit, module or assembly unit in such a way that the stub axles engage in the second axial recesses. Then the clamping devices are to be operated from outside the bearing housing so that the stub axles are clamped against the stub shafts and the cutter blocks are thus fixed. Due to the conicity of the stub shafts and the stub axles, self-centering takes place and, at the same time, the cutter blocks are clamped without play. This makes assembly very easy.
  • the twin-shaft grinder has an oil supply device for supplying a bearing of the first and / or second cutter disk block with oil through an oil duct, in particular through an oil duct that extends through the first cutter disk block.
  • Storage can be both Rolling bearings as well as plain bearings include.
  • the oil supply device is preferably set up to check the tightness of the oil supply and in this way to determine a leak in the seal.
  • the oil supply device is preferably accessible from the outside when the twin-shaft shredder is installed.
  • the oil supply device can be developed in that the oil channel has a first oil channel section which runs through the first axial bore of the first cutter disk block.
  • the oil supply device preferably has a second oil channel section which is in fluid connection with the first oil channel section and provides oil for mounting the second cutter disk block.
  • this oil routing allows a protected oil channel position that is insensitive to external influences.
  • this oil channel guide makes it possible to dismantle the first and second cutter disk blocks together with their end-side bearings without external oil lines having to be dismantled beforehand or without the need for complex feed-throughs from external oil lines to the bearings.
  • the oil guide according to the invention can prevent the entire twin-shaft grinder from first having to be removed from the channel in order to replace the knife disk blocks, but instead pull the knife disk blocks out of the housing of the twin-shaft grinder installed in the channel without the risk of oil escaping.
  • the first oil channel section particularly preferably runs through the first shaft stub and / or the first axle insert. It is particularly preferred here if the first oil channel section runs both through the first shaft stub and through the first axle insert.
  • the second oil channel section can also run through the second stub shaft and the second axle insert and / or can be designed as a connection between the lubrication space of the bearing of the first cutter disk block and the bearing of the second cutter disk block. In this way, no additional openings or connections are required on the bearings of the cutter disk blocks. This also makes it easier to replace the cutter block blocks.
  • the twin-shaft grinder by an oil monitoring device which is designed to detect a leak in a seal, which the bearing seals, to detect, wherein the oil monitoring device is designed to carry out the leak on the basis of a monitoring of the oil level or the oil pressure in the oil channel.
  • Such an oil monitoring device is used to detect insufficient lubrication of the bearing in good time in order to prevent damage to the bearing.
  • inadequate lubrication occurs as a result of a leak in a seal that seals the bearing.
  • Such a leak can have the effect, for example, that liquid is pressed from the interior of the twin-shaft shredder into the oil circuit, which can lead to an increase in the oil level or the oil pressure.
  • a leak causes a loss of oil from the oil circuit, which means that the oil level and the oil pressure drop. It should be understood that the leak test can be carried out by a user by manually monitoring a corresponding display.
  • the leak test can also be carried out in a fully or partially automated manner, for example by monitoring the oil level or oil pressure by means of a sensor and outputting a signal indicating insufficient lubrication if certain threshold values are not reached or exceeded.
  • This signal can be output to a user on a corresponding user interface, for example as an acoustic warning signal, or can intervene directly in the control of the twin-shaft shredder and, for example, trigger a stop.
  • a twin-shaft shredder 1 has a gear section 2 and a shredding section 4. Both a drive motor 6 and a gear 8, via which the two first and second cutter disk blocks 10, 12 are coupled to the drive motor 6, are provided in the gear section 2.
  • the transmission consists of two gears with different numbers of teeth (not shown) that mesh with one another. As a result, a counter-rotating movement of the two cutter disk blocks 10, 12 is generated, which run at different speeds. Only the corresponding drive shaft (also not shown) of the first cutter disk block 12 is coupled to the drive motor 6; the second drive shaft (not shown) for the second cutter disk block 12 is driven exclusively via the gearbox 8.
  • the drive motor 6 and the gear 8 are designed as in DE 20 2010 010 662 U1 described. In this respect, reference is made to this disclosure in its entirety and its disclosure content is incorporated herein.
  • the two cutter disk blocks 10, 12 are arranged in a housing 14 of the comminuting section 4.
  • the housing 14 has an inlet opening 16 and an outlet opening 18, which can each be connected to a pipe system or the like of an installation.
  • the inlet opening 16 and the outlet opening 18 are configured opposite one another and are identical in their geometry. It should be understood, however, that the inlet and outlet can be different, e.g. B. with so-called. Side Rails.
  • the housing 14 is coupled to the transmission 8 via a flange 20.
  • the housing 14 can also be removed from the transmission 8 via the flange 20.
  • FIG Fig. 2 When the housing 14 is removed, the twin-shaft shredder 1 is shown in FIG Fig. 2 shown.
  • the first and second cutter disk blocks 10, 12 are braced against the flange 20.
  • a bearing housing 24 is provided, which will be described in more detail below. The bearing housing 24 can be removed as a unit from the cutter disk blocks 10, 12.
  • FIG Fig. 3 The removed state of the bearing housing 24 is shown in FIG Fig. 3 shown.
  • Two stub axles 26, 28 protrude from the bearing housing 24.
  • Corresponding shaft stubs 30, 32 corresponding in their geometry to the stub shafts 26, 28 extend out from the transmission 8. While the stub shafts 30, 32 protrude into first axial recesses 34, 36 of the cutter disk blocks 10, 12, the stub axles 26, 28 are received in second axial recesses 38, 40 of the cutter disk blocks 10, 12.
  • the first axial recesses 34, 36 and the second axial recesses 38, 40 are designed symmetrically to one another, that is to say in particular geometrically identical or largely identical in the interior.
  • Fig. 4 only the first cutter block 10 is shown in section, while the second cutter block 12 is shown in plan view. However, it should be understood that, in section, the second cutting disk block 12 is formed identically to the first cutting disk block 10.
  • the cutting disk blocks 10, 12 are identical to one another, which is also the case for the first and second stub shafts 30, 32 and the first and second stub axles 26 , 28 applies.
  • the stub shaft 30 extends in the axial direction over a length L W and the two cutter disk blocks 10, 12 over an axial length L M.
  • the axial length L W is approximately 10% of the axial length L M. So it's over Fig. 4
  • the twin-shaft shredder 1 according to the present invention can be operated with cutter disk blocks 10, 12 of different lengths. Accordingly, only one housing 14, which is also axially adapted, is to be provided, in which the corresponding cutter disk blocks 10, 12 are received.
  • the stub shafts 30, 32 and also the drive 6 and the gear 8 are not to be changed.
  • the stub shaft 30 has a frustoconical section 42 at its free end.
  • a sleeve 44 is provided, which correspondingly has a frustoconical section on the inner diameter. This corresponds to the frustoconical section 42.
  • the sleeve 44 rests against an intermediary element 46, which in turn is provided with a spring assembly 48, in this exemplary embodiment consisting of a plurality of disc springs, is in contact.
  • the disc springs of the spring assembly 48 are then supported on an annular shoulder 50 in the cutter block 10.
  • the spring assembly 48 can also have only a single spring, in particular a disc spring.
  • a feather key 52 is provided for the transmission of torque from the stub shaft 30 to the cutter disk block 10.
  • a splined shaft connection or torque transmission by frictional engagement in the cone connection is also conceivable and preferred.
  • a second axial recess 38 is made on the opposite side of the cutter disk block 10.
  • An axle insert in the form of an axle stub 26 is received in this axial recess 38.
  • the stub axle 26 is overall identical in its external geometry to the stub shaft 30 and also has a frustoconical section 54.
  • a sleeve 56 with a frustoconical inner section, a switching element 58 and a spring assembly 60 are provided in the recess 38.
  • the spring assembly 60 is supported against a second annular shoulder 62.
  • the first and second axial recesses 34, 38 are connected to one another via a through bore 64.
  • a threaded rod 66 extends through the through hole 64.
  • a first end 68 of the threaded rod 66 is received in a corresponding threaded hole 70 of the shaft stub 30.
  • the threaded rod 66 runs through a through-hole 72 in the axle insert, which is designed as an axle stub 26, and is coupled to a nut 74 at the outer end.
  • the conical sections 54, 56 and 42, 44 ensure self-centering of the axle stub 26 or shaft stub 30 in the recesses 38, 34 achieved so that a backlash-free tension is achieved.
  • the stub axle 26 is also received in a roller bearing 76, which is supported accordingly in the bearing housing 24.
  • the access to the nut 74 is closed by means of a cover 78 which has a bayonet catch 80 and is provided with a hexagon socket 82 so that an operator can remove the cover 78.
  • the nut 74 can be tightened or be relaxed. If the nut 74 is loosened, the tensioning of the stub axle 26 against the stub shaft 30 is released, and when the nut 74 is removed it is possible to remove the bearing housing 24 as a whole, including the two stub axles 26, 28, as shown in FIG Fig. 3 is shown.
  • each cutter block 10, 12 is machined from a solid material by means of machining, in particular using turning and milling. This prevents voltage peaks and further increases the service life.
  • Each cutter disk block 10, 12 has a large number of individual cutter disks 101, 102, 103, 104 (only two of the cutter disks in block 10, 12 are provided with reference symbols).
  • the number of cutter disks 101, 102, 103, 104 depends on the overall size of the twin-shaft shredder 1 and on the shredding task to be carried out.
  • each cutter disk 101, 102, 103, 104 there are in turn several, in particular six, cutting elements 105 evenly distributed in the circumferential direction (cf. Fig. 1 and 4th ) educated.
  • the cutting elements form helical lines 106 of a six-start thread (smaller or larger numbers of turns are also possible) with a steep slope along the circumference of each cutter block 10, 12.
  • the cutting elements of the cutter block 10 here form a right-hand thread (although left-hand is also possible and preferred), the cutting elements of the cutter block 12 as well.
  • the two cutter disk blocks 10, 12 are of identical design.
  • FIGS. 5 , 6A and 6B now illustrate a second exemplary embodiment of a twin-shaft shredder 1. Identical and similar elements are given the same reference symbols as the first exemplary embodiment ( Figs. 1 to 4 ) so that reference is made to them in full. In the following, the differences from the first exemplary embodiment are particularly emphasized.
  • first and second cutter disk blocks 10, 12 are mounted on the housing 14 by means of the first and second shaft stubs 30, 32.
  • first stub shaft 30 is mounted in a first bearing, here designed as a roller bearing, more precisely as a first barrel bearing 202, and the second stub shaft 32 in a second bearing, here as a roller bearing, more precisely as a second barrel bearing 204, of which in Figure 6A only a part can be seen, but which is designed according to the first barrel bearing 202.
  • the first axle insert 26 is mounted in the roller bearing 76, which is supported on the bearing housing 24 (see FIG Figure 6B ).
  • the roller bearing 76 is designed as a first tapered roller bearing in order to be able to better absorb axial forces.
  • the second axle insert 28 is mounted in a corresponding roller bearing 206, which is designed as a second tapered roller bearing and is also supported on the bearing housing 24.
  • an oil connection 208 is now provided on the housing 14.
  • the oil connection 208 is connected to a hose 209, via which oil can be provided to the oil connection 208, preferably with a predetermined oil pressure.
  • corresponding mechanical seals 77, 207 assigned to them are preferably also supplied with oil.
  • the oil connection 208 opens inside the housing 14 into a sealed oil coupling 210, which in turn is connected in a fluid-conducting manner to a first axial channel 212 which runs through the first shaft stub 30.
  • This first axial channel 212 is connected to a first radial channel 214, which in turn is connected in a fluid-conducting manner to a second axial channel 216.
  • Radially outward is the first radial channel 214 with the Key 52 essentially closed. It can happen that a small amount of oil leaks and then collects in the area of the key or under it, but this does not affect the operation any further. This simplifies production.
  • the first radial channel 214 can be drilled radially into the first shaft stub 30 in the area of the groove for the feather key 52, and an additional closure is not required.
  • the second axial channel 216 then occurs on the front side (with reference to Figure 6A left) from the first stub shaft 30.
  • An inclined channel 218 is introduced into the switching element 46 which receives the spring assembly 48 and then opens into the first axial bore 64 in the first cutter block 10. In this way, the first axial bore 64 is connected to the oil connection 208.
  • the first axial passage 212, the first radial passage 214, the second axial passage 216, the inclined passage 218 and the bore 64 together form portions of a first oil passage 219 which runs through the bore 64.
  • the through hole 72 in the first axle insert 26 differs from the first exemplary embodiment ( Figure 4 ): in a first section 220, the through-bore 72 has an enlarged inside diameter, which is in particular larger than the outside diameter of the first threaded rod 66 the first threaded rod 66 is engaged.
  • a second radial channel 226 is introduced into the first axle insert 26 and opens radially into a first bearing space 228 and can thus supply the bearing 76 and preferably the mechanical seal 77 with oil.
  • the through bore 72 and the second radial channel 226 also form a section of the first oil channel 219.
  • connection unit 230 with a second oil channel 232 is provided.
  • This second oil channel 232 connects the first storage space 228 to a second storage space 234, which is the second cutter disk block 12 is assigned, more precisely to the roller bearing 206.
  • the second oil channel 232 provides oil for the second cutter block 12.
  • a leak test can be carried out in that a predetermined pressure is applied to the oil connection 208 and this pressure or the oil level is monitored. If a change in the oil level or the pressure is determined, there is a leak in the oil supply device 200, that is to say a seal which seals the oil circuit from the surroundings or from the interior of the twin-shaft shredder, which must be closed.
  • This oil supply device 200 is particularly advantageous when the twin-shaft shredder 1 is installed with the end in which the axle inserts 26, 28 are provided in a channel or the like so that the bearings 76, 206 are not readily accessible for lubrication.
  • This aspect makes particular use of the bore 64 and uses it as a section of the first oil channel 219. This achieves a particularly advantageous construction.

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  • Crushing And Pulverization Processes (AREA)

Claims (16)

  1. Broyeur à deux arbres (1) pour le broyage de corps solides ou de corps solides dans des liquides, comprenant :
    - un carter (14) qui définit une chambre de broyage disposé en son intérieur,
    - une ouverture d'entrée (16) dans le carter (14) pour l'introduction de corps solides dans la chambre de broyage,
    - une ouverture de sortie (18) dans le carter (14) pour évacuer les corps solides broyés de la chambre de broyage,
    - un premier bloc de disques porte-lames (10) avec une pluralité de premiers disques porte-lames (101, 102) qui sont disposés sur un premier corps de moyeu de sorte qu'il existe à chaque fois un interstice entre deux premiers disques porte-lames adjacents (101, 102),
    - un deuxième bloc de disques porte-lames (12) avec une pluralité de deuxièmes disques porte-lames (103, 104) qui sont disposés sur un deuxième corps de moyeu de sorte qu'il existe à chaque fois un interstice entre deux deuxièmes disques porte-lames adjacents (103, 104),
    - dans lequel les premier et deuxième blocs de disques porte-lames (10, 12) sont décalés axialement l'un par rapport à l'autre de sorte qu'au moins certains des premiers disques porte-lames (101, 102) s'engagent respectivement dans un interstice entre deux deuxièmes disques porte-lames (103, 104) adjacents et certains des deuxièmes disques porte-lames (103, 104) s'engagent respectivement dans un interstice entre deux premiers disques porte-lames (101, 102) adjacents,
    - dans lequel les premier et deuxième blocs de disques porte-lames (10, 12) présentent chacun un premier évidement axial (34, 36),
    - un premier bout d'arbre (30) qui s'étend dans le premier évidement axial (34) du premier bloc de disques porte-lames (10) pour transmettre des couples de rotation,
    - un deuxième bout d'arbre (32) qui s'étend dans le premier évidement axial (36) du deuxième bloc de disques porte-lames (12) pour transmettre des couples de rotation,
    - un premier dispositif de serrage pour caler sous serrage le premier bout d'arbre (30) contre le premier bloc de disques porte-lames (10),
    - un deuxième dispositif de serrage pour caler sous serrage le deuxième bout d'arbre (32) contre le deuxième bloc de disques porte-lames (12), caractérisé par
    - un premier et un deuxième insert d'axe (26, 28), dans lequel les premier et deuxième blocs de disques porte-lames (10, 12) présentent chacun un deuxième évidement axial (38, 40) et le premier insert d'axe (26) est logé dans le deuxième évidement axial (38) du premier bloc de disques porte-lames (10), et le deuxième insert d'axe (28) est logé dans le deuxième évidement axial (40) du deuxième bloc de disques porte-lames (12), dans lequel les premier et deuxième évidements axiaux (34, 36, 38, 40) sont chacun reliés l'un à l'autre par un alésage axial (64), et dans lequel les dispositifs de serrage présentent des moyens pour mettre sous contrainte le premier insert d'axe (26) contre le premier bout d'arbre (30) et le deuxième insert d'axe (28) contre le deuxième bout d'arbre (32).
  2. Broyeur à deux arbres selon la revendication 1,
    dans lequel le premier bloc de disques porte-lames (10) est fixé à résistance au couple de rotation sur le premier bout d'arbre (30), et le deuxième bloc de disques porte-lames (12) est fixé à résistance au couple de rotation sur le deuxième bout d'arbre (32), de préférence au moyen d'une liaison par complémentarité de formes arbre-moyeu.
  3. Broyeur à deux arbres selon la revendication 1 ou 2,
    dans lequel les premier et deuxième bouts d'arbre (30, 32) présentent chacun une section tronconique (42) qui est en appui avec une section tronconique correspondante des premiers évidements axiaux (34, 36) des premier et deuxième blocs de disques porte-lames (10, 12).
  4. Broyeur à deux arbres selon la revendication 3,
    dans lequel la section tronconique des blocs de disques porte-lames (10, 12) est formée par un manchon (44) qui est insérée dans les premiers évidements axiaux (34, 36).
  5. Broyeur à deux arbres selon la revendication 4,
    dans lequel le manchon (44) est précontraint au moins d'un ensemble de ressorts (48).
  6. Broyeur à deux arbres selon l'une quelconque des revendications précédentes, dans lequel les moyens de mise sous contrainte comprennent une première et une deuxième tiges filetées (66).
  7. Broyeur à deux arbres selon la revendication 6, dans lequel la première tige filetée (66) est logée dans un alésage taraudé (70) dans le premier bout d'arbre (30) et s'étend dans ou à travers un alésage débouchant (72) dans le premier insert d'arbre (26), et dans lequel la deuxième tige filetée est logée dans un alésage taraudé dans le deuxième bout d'arbre (32) et s'étend dans ou à travers un alésage débouchant dans le deuxième insert d'arbre (28).
  8. Broyeur à deux arbres selon l'une quelconque des revendications précédentes, dans lequel les premier et deuxième inserts d'axe (26, 28) se présentent sous la forme de bouts d'arbre (26, 28) pour supporter les premier et deuxième blocs de disques porte-lames (10, 12).
  9. Broyeur à deux arbres selon l'une quelconque des revendications précédentes, dans lequel les premier et deuxième inserts d'axe (26, 28) présentent chacun une section tronconique (54) qui sont en appui avec une partie tronconique correspondante des deuxièmes évidements axiaux (38, 40) des premier et deuxième blocs de disques porte-lames (10, 12).
  10. Broyeur à deux arbres selon l'une quelconque des revendications précédentes, dans lequel les premier et deuxième évidements axiaux (34, 36, 38, 40) dans les blocs de disques porte-lames (10, 12) se présentent sous une forme symétrique l'un par rapport à l'autre.
  11. Broyeur à deux arbres selon la revendication 8, dans lequel les premier et deuxième bouts d'arbre (26, 28) sont logés dans un logement de palier (24) qui forme une unité avec les bouts d'arbre (26, 28) et est amovible réversiblement, en tant qu'unité, des blocs de disques porte-lames (10, 12) et/ou du carter (14).
  12. Broyeur à deux arbres selon l'une quelconque des revendications précédentes, comprenant un dispositif d'alimentation (200) en huile pour alimenter en huile un palier (76, 206) et des joints d'étanchéité rotatifs (77, 207) associés de préférence à celui-ci, du premier et/ou du deuxième bloc(s) de disques porte-lames (10, 12) par un canal d'huile, en particulier par un canal d'huile s'étendant à travers le premier bloc de disques porte-lames.
  13. Broyeur à deux arbres selon la revendication 12, dans lequel le canal d'huile (200) comprend une première section (219) de canal d'huile s'étendant à travers le premier alésage axial (64) du premier bloc de disques porte-lames (10).
  14. Broyeur à deux arbres selon la revendication 13, dans lequel le dispositif d'alimentation (200) en huile comprend une deuxième section (232) de canal d'huile qui est en connexion fluidique avec la première section (219) de canal d'huile et fournit de l'huile pour un palier du deuxième bloc de disques porte-lames (12).
  15. Broyeur à deux arbres selon la revendication 13 ou 14, dans lequel la première section (219) de canal d'huile s'étend à travers le premier bout d'arbre (30) et/ou le premier insert d'axe (26).
  16. Broyeur à deux arbres selon la revendication 13, 14 ou 15, caractérisé par un dispositif de surveillance d'huile qui se présente sous une forme pour détecter un défaut d'étanchéité d'un joint d'étanchéité qui étanchéifie le palier, dans lequel le dispositif de surveillance d'huile se présente sous une forme pour effectuer la détection par surveillance du niveau d'huile ou de la pression d'huile dans le canal d'huile.
EP17801428.8A 2016-11-14 2017-11-14 Broyeur à deux arbres avec jeu de lames de coupe interchangeables et extrémités d'arbre détachables Active EP3538278B1 (fr)

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DE202016106367.1U DE202016106367U1 (de) 2016-11-14 2016-11-14 Zweiwellenzerkleinerer mit wechselbarem Schneidmessersatz und lösbaren Wellenenden
PCT/EP2017/079213 WO2018087398A1 (fr) 2016-11-14 2017-11-14 Déchiqueteur à double arbre à jeu de couteaux interchangeables et extrémités d'arbre amovibles

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PL3538278T3 (pl) 2021-11-08
CN110177624B (zh) 2021-03-30
JP6942800B2 (ja) 2021-09-29
JP2019535506A (ja) 2019-12-12
US11084042B2 (en) 2021-08-10
US20190366352A1 (en) 2019-12-05
ES2882505T3 (es) 2021-12-02
DK3538278T3 (da) 2021-08-02
MX2019005616A (es) 2019-08-21
WO2018087398A1 (fr) 2018-05-17
BR112019009542A2 (pt) 2019-07-30
CN110177624A (zh) 2019-08-27
EP3538278A1 (fr) 2019-09-18
DE202016106367U1 (de) 2018-02-15

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