EP3831494B1 - Broyeur à découper destiné au broyage par découpage des échantillons - Google Patents

Broyeur à découper destiné au broyage par découpage des échantillons Download PDF

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Publication number
EP3831494B1
EP3831494B1 EP20209556.8A EP20209556A EP3831494B1 EP 3831494 B1 EP3831494 B1 EP 3831494B1 EP 20209556 A EP20209556 A EP 20209556A EP 3831494 B1 EP3831494 B1 EP 3831494B1
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EP
European Patent Office
Prior art keywords
cutting
grinding chamber
labyrinth
support bearing
bearing element
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Application number
EP20209556.8A
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German (de)
English (en)
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EP3831494A1 (fr
Inventor
Wolfgang Mutter
Juri Dinges
Markus Bund
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Fritsch GmbH
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Fritsch GmbH
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Publication of EP3831494A1 publication Critical patent/EP3831494A1/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
    • B02C18/144—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives within horizontal containers with axially elongated 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
    • 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
    • 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
    • B02C2018/162—Shape or inner surface of shredder-housings

Definitions

  • the invention relates to a cutting mill for the cutting comminution of samples, in particular on a laboratory scale, with a cutting rotor rotating about a horizontal axis.
  • Cutting mills comminute the samples by a scissors-like cutting effect, typically between a rotating cutting rotor with one or more essentially axially extending blades and one or more stationary counter-blades also essentially axially extending.
  • Such laboratory cutting mills are particularly suitable for comminuting tough or fibrous samples, for example biological samples such as straw, but also plastic films, to name just a few.
  • Examples of such laboratory cutting mills are, for example, the Applicant's Pulverisette® 19 and Pulverisette® 25, the basic design of which is hereby referred to. Corresponding product descriptions of the Pulverisette ® 19 and the Pulverisette ® 25 can be found, for example, at www.fritsch.de.
  • a cutting edge running essentially axially is not limited to the cutting edge running strictly parallel to the axis of rotation, but should also include cutting edges running at an angle with an axis-parallel component.
  • the essentially axially running cutting edges can also run at an angle to the axis of rotation, which in principle corresponds to a helical line.
  • a screen for example a screen cassette, through which the sample material that is already has been crushed sufficiently, can trickle through to be collected in a receptacle below.
  • the grinding chamber is typically closed axially at the front (front) with a pivoted sealing cover.
  • the counter bearing of the cutting rotor in the closure cover is typically sealed against the inside of the grinding chamber by means of felt rings or lip seals.
  • the felt rings or lip seals used on the closure cap may not have been easy to replace.
  • the seal using felt rings or lip seals has basically proven itself, which is why these seals have been used in laboratory cutting mills for decades, depending on the sample, waxes, oils or resins could also get to the seal and contaminate the seal or the sealing effect possibly affect.
  • the DE 297 13 097 U1 discloses a granulator according to the preamble of the independent claim.
  • a further aspect of the object of the invention is to provide a cutting mill which generates little heat in the area of the closure cover and nevertheless has a good sealing effect.
  • the invention relates to a cutting mill for cutting up samples with a cutting rotor.
  • the cutting mill is in particular a cutting mill on a laboratory scale, which cuts sample material between sheaths and counter-sheaths.
  • Such cutting mills for the cutting comminution of samples work according to the scissors principle.
  • the cutting edges of the cutting rotor and the counter-cutting edges run essentially axially and radially offset from the axis of rotation of the cutting rotor.
  • the grinding chamber therefore preferably has counter-knives that are axially offset on the circumferential side and run essentially axially, which interact with the cutting knives of the cutting rotor in such a way that the samples are cut up between the cutting knives of the cutting rotor and the counter-knives according to the scissor principle when the cutting edges of the cutting rotor and the stationary blades slide past each other.
  • the granulator comprises a device housing which accommodates, for example, a grinding chamber with a granulator, a drive motor and/or an electronic controller for the granulator.
  • the drive motor drives the cutting rotor in rotation, with the blades of the cutting rotor running past the stationary counter-blades, which surround the cutting rotor, according to the scissors principle, cutting the sample material between the blades and counter-blades according to the scissors principle.
  • the cutting edges and counter cutting edges run essentially axially.
  • “running essentially axially” should not be limited to cutting edges that run strictly parallel to the axis of rotation. Rather, the cutting edges can in particular also run obliquely, for example along a helical line, or have a twist.
  • cutting rotors with so-called V-cutting edges can be used, in which the cutting edges are offset axially to the axis of rotation and run essentially axially, but obliquely along a helix, so that the cutting edges have a twist.
  • Laboratory cutting mills of this type are known in principle to a person skilled in the art, see, for example, www.fritsch.de .
  • the cutting rotor which is driven in rotation by the drive shaft, rotates about an axis of rotation within the grinding chamber.
  • the grinding chamber is limited axially on the motor side, i.e. axially in relation to the axis of rotation or on the front side of the motor, by a rear wall of the grinding chamber.
  • the cutting rotor is preferably generally cylindrical and the motor-side end face of the cylindrical cutting rotor preferably runs parallel to the grinding chamber rear wall.
  • the grinding chamber rear wall preferably has a shaft passage opening through which the cutting rotor can be driven by a drive shaft.
  • the drive shaft extends through the shaft passage opening in order to drive the cutting rotor in rotation in the grinding chamber.
  • the drive shaft and/or the axis of rotation of the cutting rotor preferably run horizontally and/or the rear wall of the milling chamber runs vertically.
  • the device housing On the side of the cutting rotor axially opposite the rear wall of the milling chamber, the device housing has an axially frontal closure cover, by means of which the milling chamber can be closed and opened again. Accordingly, the closure cover can be opened in order to open the grinding chamber, specifically in order, among other things, to remove the cutting rotor.
  • the cutting rotor can preferably be pulled off the drive shaft axially when the closure cover is open.
  • the closure lid forms a door to the grinding chamber.
  • the closure cover is e.g. pivotably suspended on the device housing. This means that the cutting rotor can be easily cleaned or replaced with another cutting rotor. Furthermore, e.g. the sieve cassette can also be cleaned or replaced.
  • the closure lid also has a rotatably mounted support bearing element for the cutting rotor, with which the cutting rotor on the rear wall of the grinding chamber or the Drive motor opposite axial end face of the grinding chamber is rotatably mounted on the closure cap when the axially front closure cap is closed.
  • a first labyrinth seal is arranged on the closure cover, by means of which the bearing of the cutting rotor and the support bearing element on the closure cover is sealed against the milling chamber.
  • the first labyrinth seal serves as a seal for the grinding chamber on the front side of the grinding chamber opposite the rear wall of the grinding chamber or the drive motor, between rotating parts of the cutting mill and areas of the closure lid that are to be kept clean, such as the bearing on the closure lid.
  • Labyrinth seals are also sometimes referred to as gap seals because they provide a non-contact shaft seal.
  • the sealing effect is based on the lengthening of the flow path through the sealing gap, which increases the flow resistance. This lengthening of the path can be achieved, for example, by meshing labyrinth shaped elements of the rotor and stator, the so-called intermeshing.
  • the rotational speed of the cutting rotor in the cutting mill can be, for example, in the interval from 20 rpm to 5000 rpm, preferably between 50 and 3000 rpm. It has been found that in some cutting mills the radius or circumference of the seals on the closure cover is relatively large due to the design, which causes a relatively high peripheral speed on the seal.
  • the use of a labyrinth seal on the closure cover is advantageous, among other things, since it can significantly reduce the heat development on the closure cover that occurs in a cutting mill due to the special structural conditions.
  • a further advantage of using a labyrinth seal on the closure cover is that the cutting mill is easy to maintain and, in particular, cleaning in the area of the support bearing can be simplified and improved. This can be particularly helpful in a cutting mill, for example when crushing oily or resinous samples, since with conventional cutting mills this could lead to oily and and/or resinous residues could diffuse into the area of the seal in the cap.
  • Another advantage of using a labyrinth seal in the granulator's cover is its durability and ease of maintenance. Furthermore, the first labyrinth seal can be installed and removed easily, e.g. in order to clean, check and/or replace it.
  • the cutting mill designed as a laboratory cutting mill preferably comprises the drive shaft protruding into the grinding chamber on the motor side, the cutting rotor being coaxially pluggable onto the drive shaft by hand and being removable again when the grinding chamber or the sealing cover is open.
  • This has the advantage that the user only needs to open the cover and can then remove the cutting rotor by hand without tools, e.g. to clean the cutting rotor and the grinding chamber or to be able to exchange the cutting rotor for another cutting rotor.
  • the grinding chamber rear wall preferably has a shaft passage opening through which the drive shaft extends in order to drive the cutting rotor.
  • the support bearing element applies a force or preload to the cutting rotor, preferably axially in the direction of the grinding chamber rear wall, in order to avoid undesired play between the cutting rotor and the static elements of the cutting mill.
  • the device housing preferably comprises an axially effective spring, in particular in the closure lid, which applies force directly or indirectly to the support bearing element axially in the direction of the grinding chamber rear wall when the closure lid is closed.
  • an axially effective spring in particular in the closure lid, which applies force directly or indirectly to the support bearing element axially in the direction of the grinding chamber rear wall when the closure lid is closed.
  • the axial spring force on the support bearing element and/or the axial force of the support bearing element on the cutting rotor is greater than 100 N, preferably greater than 200 N, preferably greater than 500 N, according to one embodiment, for example about 1000 N.
  • the support bearing element is designed as a shaft piece which is rotatably mounted on the closure cover by means of a bearing, e.g. a ball bearing.
  • the closure cap has an axial stop against which the bearing is prestressed axially in the direction of the grinding chamber by means of the spring when the closure cap is open.
  • the axial stop also serves to secure the bearing in the closure cap axially in the direction of the grinding chamber.
  • the support bearing element has a stop against which the bearing is also prestressed axially in the direction of the grinding chamber by means of the spring.
  • the cutting rotor when the closure cover is closed, can displace the support bearing element axially in the direction away from the grinding chamber against the tension of the spring, thereby further tensioning the spring.
  • the support bearing element also displaces the bearing axially against the tension of the spring in the direction away from the grinding chamber and in the process releases the bearing axially from the stop in the closure lid, so that the bearing, e.g. ball bearing, during operation of the cutting mill is not unduly tightened.
  • the support bearing element preferably has a bearing fitting, eg a bearing cone, which engages in a corresponding fitting receptacle, eg a conical receptacle, of the cutting rotor when the closure cover is closed, such that during operation the support bearing element is rotated by the cutting rotor.
  • the support bearing element designed as a shaft piece forms a shaft continuation of the drive shaft or of the cutting rotor, which is rotatably mounted in the closure cover by means of the bearing.
  • the support bearing element is also preferably mounted in an axially displaceable manner on the closure cover, e.g. in order to be able to compensate for axial length tolerances and/or to enable the longitudinal displacement of the support bearing element caused by the application of force by means of the spring.
  • the first labyrinth seal has an axial play which is sufficiently large to allow an axial displacement of the support bearing element while maintaining the sealing effect of the first labyrinth seal, in particular to compensate for the axial displacement of the support bearing element when the spring is tensioned when the closure lid is closed.
  • the first labyrinth seal has a smaller axial gap dimension when the closure lid is closed than when the closure lid is open. In other words, the axial gap dimension is reduced when the closure cover is closed.
  • the axial play of the first labyrinth seal is selected to be large enough that the first labyrinth seal has a smaller radial gap than the axial gap when the closure cover is open and closed.
  • the sealing effect of the first labyrinth seal preferably takes place mainly on the annular, axially extending gaps (radial gap size) and less on the annular, radially extending (frontal) gaps (axial gap size).
  • the radial gap dimension of the circumferentially axially extending gaps of the first labyrinth seal is preferably between 0.05 mm and 1 mm, more preferably between 0.1 mm and 0.5 mm, preferably in the range of 0.2 mm.
  • the axial gap dimension of the circumferentially radially extending (frontal) gap of the first labyrinth seal is preferably between 5 mm and 0.5 mm, more preferably between 3 mm and 1 mm, preferably in the range of 1.8 mm +/-0 when the closure cover is open ,5 mm. These dimensions are "interlocked" with the tolerances to be considered.
  • the compression of the axial gap size when closing the closure lid is preferably between 3 mm and 0.2 mm, preferably between 1.5 mm and 0.4 mm, preferably in the range of 0.8 mm +/- 0.4 mm.
  • the axial gap is preferably between 3 mm and 0.1 mm, preferably between 2 mm and 0.3 mm, preferably in the range of 1 mm +/- 0.5 mm.
  • the axial gap is preferably between 3 mm and 0.1 mm, preferably between 2 mm and 0.3 mm, preferably in the range of 1 mm +/- 0.5 mm.
  • the first labyrinth seal is preferably meshed exclusively in the axial direction. This has the advantage that the first and second labyrinth rings, which form the two halves of the first labyrinth seal, can simply be pulled off axially from one another, e.g. to be able to clean the first labyrinth seal.
  • the first labyrinth seal in addition to the axial interlocking, it can also have at least one, but preferably several, e.g. three, radially circumferential groove or grooves that extend the fluid path, which is or are not interlocked, so the parts can be pulled apart axially.
  • the groove or grooves form radial labyrinth shaped elements and can be arranged, for example, on the outer circumference of the support bearing element.
  • Such an arrangement of circumferential non-intermeshing grooves is also sometimes referred to as a circumferential "open labyrinth" or so-called see-through labyrinth.
  • the first labyrinth seal preferably has a first and second labyrinth ring, which are interlocked with one another exclusively in the axial direction, i.e. can be separated from one another axially, with the first or inner labyrinth ring of the grinding chamber preferably being fastened to the support bearing element, which offers design advantages.
  • the meshing of the first labyrinth seal is designed in such a way that, while maintaining the sealing effect of the first labyrinth seal, an axial displacement between the first and second labyrinth rings within a predefined path is made possible, in particular in order to permit or prevent an axial displacement of the support bearing element while maintaining the sealing effect of the first labyrinth seal .to be able to compensate.
  • the axial displaceability between the first and second labyrinth ring of at least 0.2 mm, preferably at least 0.4 mm, preferably at least 0.8 mm and/or preferably at most 20 mm, preferably at most 10 mm, preferably at most 5mm
  • the second labyrinth ring is preferably arranged in a stationary manner on the closure cover.
  • the first labyrinth ring is preferably arranged on the support bearing element, in particular fastened, and rotates, together with the support bearing element, in meshing engagement in the second stationary labyrinth ring on the closure cover.
  • the labyrinth seal rotates horizontally and the first and second labyrinth rings are in horizontal meshing engagement with each other.
  • the first labyrinth ring is preferably arranged or fixed on the peripheral cylinder wall of the support bearing element.
  • the support bearing element On its axial side facing the grinding chamber, can have a grinding-chamber-side section with a larger diameter than on a closure-lid-side section on the axial side facing away from the grinding chamber, and the first labyrinth ring is preferably arranged or fastened on the grinding-chamber-side section with the larger diameter.
  • the gap of the first labyrinth seal connects the grinding chamber to the pivot bearing of the support bearing element.
  • the rotating first labyrinth ring arranged on the support bearing element is preferably arranged on the side of the first labyrinth seal facing the grinding chamber and the stationary second labyrinth ring arranged on the closure cover is arranged on the side of the first labyrinth seal facing away from the grinding chamber.
  • the rear side of the first labyrinth ring, which is axially opposite the labyrinth comb, preferably faces the grinding chamber and is preferably located axially adjacent to the cutting rotor or the cutting rotor core.
  • the first labyrinth ring is inseparably attached to the support bearing element for the user, eg shrunk (press fit). This has the advantage that the first labyrinth ring is held securely in the desired position.
  • the second labyrinth ring is preferably provided on the closure cover, which also offers design advantages.
  • the second labyrinth ring can be integrally molded into the closure cap, e.g., turned by turning.
  • the meandering rings of the second labyrinth ring can be milled directly into the closure cover, which saves an additional component for the second labyrinth ring.
  • the support bearing element is frictionally engaged on the closure cap, in particular in which the bearing or ball bearing is mounted, on the one hand to ensure axial mobility and on the other hand to prevent the support bearing element from falling out of the closure cap by itself when the closure cap is open.
  • This frictional mounting can be achieved, for example, by means of an O-ring in a circumferential groove in an extension of the support bearing element, in which the extension is held in an axially clamping manner by means of the O-ring in the bearing, but is held in an axially displaceable manner when the clamping force is overcome.
  • the support bearing element can preferably be pressed out of the closure cover by overcoming the frictional force of the frictional connection or the clamping force of the O-ring. This has the advantage that the support bearing element can be easily removed from the closure cap, e.g. for cleaning, in particular without loosening a screw connection.
  • the closure cap preferably has an opening, e.g. a central opening, through which the support bearing element can be pressed out of the closure cap, e.g. by inserting a pin or screwdriver into the opening and pushing the support bearing element axially out of the bearing by overcoming the frictional connection.
  • an opening e.g. a central opening
  • the support bearing element is therefore only inserted into the closure cap and is not screwed tightly into the closure cap even during operation, which facilitates handling during cleaning.
  • the cutting mill preferably has a second labyrinth seal, by means of which the shaft passage opening in the rear wall of the grinding chamber is sealed, so that the grinding chamber with the cutting rotor is sealed axially on both sides by means of the first and second labyrinth seals, as a result of which heat development can be further reduced, particularly at high speeds.
  • the grinding chamber of the cutting mill has, at least in certain areas, preferably at least at the bottom, a peripheral screen wall which separates the grinding chamber from a collection container in such a way that the screen wall collects sample particles that have been comminuted below a particle size predefined by the screen openings directly during the cutting comminution of the samples through the sieve openings into the collection container.
  • the screen wall is preferably designed as part of a screen cassette, with the screen cassette being able to be inserted into the grinding chamber as a unit below the cutting rotor.
  • the cutting rotor can preferably be pushed coaxially or concentrically onto the drive shaft and removed by hand when the closure cover or the grinding chamber is open.
  • the connection between the support bearing and the cutting rotor is opened and the cutting rotor can then be pulled off the drive shaft by hand.
  • the cutting rotor is simply plugged onto the drive axle.
  • Torque is preferably transmitted from the drive shaft to the cutting rotor by a positive coupling when the milling chamber is closed.
  • driver elements are included, for example, which engage in a form-fitting manner in the cutting rotor when the cutting rotor is placed on the drive shaft in order to transmit the torque to the cutting rotor by means of the driver elements.
  • the drive shaft is designed in several parts and includes at least one primary shaft, which can be the motor shaft directly, for example, and an intermediate piece coaxially mounted on the primary shaft, the so-called rotor receiving element.
  • the rotor receiving element is then plugged coaxially onto the primary shaft and coupling means are included between the primary shaft and the rotor receiving element, which transmit the torque from the primary shaft cause the rotor receiving element, such as a feather key.
  • the cutting rotor is slipped onto the rotor receiving element and can be pulled off the rotor receiving element easily and without tools when the grinding chamber is open.
  • the rotor receiving element can also be pulled off the primary shaft, in which case a removal tool may be required, for example a central screw to push the rotor receiving element off the primary shaft, with parts of the second labyrinth seal possibly being pulled off the rear wall of the grinding chamber as well.
  • a removal tool may be required, for example a central screw to push the rotor receiving element off the primary shaft, with parts of the second labyrinth seal possibly being pulled off the rear wall of the grinding chamber as well.
  • a driver flange is included, which extends around the drive shaft and has a substantially larger diameter than the motor shaft.
  • the driver elements e.g. driver pins, engage on the one hand in the driver flange and on the other hand in the cutting rotor in order to effect the transmission of torque from the drive shaft to the cutting rotor at the largest possible radius.
  • the driver elements are preferably designed as axially extending driver pins, the radially outer limit of which is at least 10 mm, preferably at least 15 mm, preferably at least 20 mm or preferably at least 25 mm, e.g Torque can be transmitted.
  • the driver flange is preferably designed as part of the rotor receiving element and the rotor receiving element can be pushed onto the primary shaft with the driver flange as a unit. This has proven itself for transmitting the torque required for the cutting mill.
  • the driver flange is at least partially arranged inside the shaft passage opening. This has proven to be advantageous in terms of size. A relatively large shaft passage opening is required for this, but this is easy to handle with the second labyrinth seal.
  • the second labyrinth seal comprises an inner labyrinth ring rotating along with the drive shaft and a labyrinth ring cover on the milling chamber side, wherein a milling chamber side axial end face of the inner labyrinth ring of the second labyrinth seal is meshed with an axial end face of the grinding chamber side labyrinth ring cover of the second labyrinth seal.
  • the second labyrinth seal preferably comprises the inner labyrinth ring rotating with the drive shaft and a labyrinth ring cover on the motor side, with an axial end face of the inner labyrinth ring on the motor side meshing with an axial face of the labyrinth ring cover on the motor side.
  • the grinding chamber rear wall preferably has an annular recess on the grinding chamber side, in which the labyrinth ring cover of the second labyrinth seal on the grinding chamber side is fixed. It is particularly advantageous if the closing surface of the labyrinth ring cover on the grinding chamber side of the second labyrinth seal ends flush with the rear wall of the grinding chamber.
  • the labyrinth ring cover of the second labyrinth seal on the grinding chamber side is preferably clamped in the annular recess on the grinding chamber side, so that when the cutting rotor is pulled off the drive shaft or the rotor receiving element, the second labyrinth seal remains assembled.
  • the inner labyrinth ring of the second labyrinth seal can basically be pulled off in the direction from the motor to the grinding chamber if the clamping of the labyrinth ring cover on the grinding chamber side of the second labyrinth seal in the annular recess on the grinding chamber side is overcome and the labyrinth ring cover on the grinding chamber side of the second labyrinth seal with the inner labyrinth ring of the second labyrinth seal from the drive shaft is removed.
  • the rotor receiving element is preferably pulled off the primary shaft while overcoming a certain clamping force, whereby the inner labyrinth ring of the second labyrinth seal and the labyrinth ring cover of the second labyrinth seal on the grinding chamber side are also pulled off the drive shaft, e.g. supported by the driver flange on the motor side.
  • the labyrinth ring cover of the second labyrinth seal on the milling chamber side can be clamped by means of an O-ring, preferably inserted in a form-fitting manner, in the rear wall of the milling chamber or in the annular recess on the milling chamber side of the rear wall of the milling chamber and can be pulled off by overcoming the clamping force caused thereby.
  • the inner labyrinth ring of the second labyrinth seal is preferably arranged radially on the outside on the rotor receiving element, in particular radially on the outside on the driver flange.
  • an air flow generating device is included, which generates an air flow through the gap of the second labyrinth seal, preferably from the motor in the direction of the grinding chamber.
  • the inner labyrinth ring of the second labyrinth seal can have fan blades which generate an air flow through the gap of the second labyrinth seal when the inner labyrinth ring of the second labyrinth seal rotates.
  • the large radius of the seal which initially appears to be disadvantageous for the seal as such, proves to be advantageous since the associated high peripheral speed can have a positive effect on the generation of an air flow.
  • the fan blades are conveniently located on the radially outer peripheral wall of the inner labyrinth ring of the second labyrinth seal.
  • An air-supplying ventilation duct is preferably provided between the grinding chamber rear wall and the drive motor, eg in the motor side of the grinding chamber rear wall, through which the air flow is guided in the direction of the grinding chamber through the second labyrinth seal.
  • an “open labyrinth” or so-called through-view labyrinth can also be provided on the circumference.
  • the second labyrinth seal in turn comprises an inner labyrinth ring rotating with the drive shaft and the shaft passage opening has an inner radial annular wall within which the inner labyrinth ring of the second labyrinth seal is arranged, so that the inner radial annular wall encloses the inner labyrinth ring of the second labyrinth seal in a ring shape.
  • the open labyrinth or view labyrinth is characterized in that either the inner radial ring wall or the outer radial ring wall of the inner labyrinth ring define a meandering shape in axial cross-section, but the inner radial ring wall and the outer radial ring wall of the inner labyrinth ring are not intertwined such that the inner labyrinth ring of the second labyrinth seal can nevertheless be pulled out axially from the shaft passage opening.
  • the meandering shape of the open labyrinth or transparent labyrinth tapers radially in the axial cross-section, e.g. is triangular in the axial cross-section, possibly tapering to a triangular point.
  • the cutting mill 10 has a device housing 12, of which the parts of the cutting mill are housed.
  • the device housing 12 of the cutting mill on a laboratory scale can, for example, be placed on a tripod 8 ( 1 ).
  • a commercially available electric drive motor 14 is located in the rear part 12a of the device housing 12 (cf. 9 ). In this example, it is the in 9 illustrated drive motor 14 to a geared motor for a cutting mill 10 with a Speed range from 50 to 700 rpm.
  • a further embodiment of the cutting mill 10 works with a drive motor 14 without a gear for a speed range of 300 to 3000 rpm (not shown).
  • the grinding chamber 16 is located in the front part 12b of the device housing 12, in which the samples to be crushed or the material to be ground can be filled during operation via a hopper 18 through a filling opening 19.
  • the milling chamber 16 can be opened from the side by opening the milling chamber cover 20 .
  • the milling chamber 16 can be opened even further by opening a milling chamber side wall and a housing upper part, sometimes also referred to collectively as the milling chamber upper part 21, to which the hopper 18 is fastened.
  • terms such as "front”, “rear” or “side” refer to the point of view and are therefore not to be understood in absolute terms.
  • the drive motor 14 is flanged to the motor side 24a of the grinding chamber rear wall 24 with a motor flange 22 and threaded bolt 23 .
  • the motor shaft 26 as the primary shaft runs horizontally and extends through a passage opening 28 in the grinding chamber rear wall 24 and extends into the grinding chamber 16.
  • an intermediate shaft piece is placed on the motor shaft 26 and forms the rotor receiving element 30 .
  • the torque is transmitted between the motor shaft 26 and the rotor receiving element 30 by means of a form fit, for example by means of a feather key 32 .
  • the torque is therefore transmitted from the motor shaft 26 directly to the rotor receiving element 30 by means of the feather key 32 .
  • the rotor mounting element 30 has a driver flange 34 on the motor side, the diameter of which is considerably larger than the diameter of the motor shaft 26.
  • eccentrically arranged driver pins 36 are fastened in the driver flange 34, by means of which the torque is transmitted to the cutting rotor 38. Due to the relatively large distance between the driver pins 36 and the axis of rotation A, a large torque can be transmitted to the cutting rotor 38 .
  • the cutting rotor 38 has corresponding receiving bores 40 for positive engagement of the driver pins 36 in the cutting rotor 38 .
  • the rotor receiving element 30 and the In this example, the motor shaft 26 (which can also be referred to as the primary shaft) together form the drive shaft 42 for the cutting rotor 38.
  • the driver flange 34 of the rotor receiving element 30 or of the drive shaft 42 runs at least partially within the rear wall of the grinding chamber 24 or within the through-opening 28. Therefore, in this example, the diameter of the through-opening 28 is also relatively large, which in turn requires a relatively large diameter of the seal of the through-opening 28 requires.
  • the grinding chamber rear wall 24 is designed in two parts and consists of a body part 44 made of aluminum and a plate 46 made of stainless steel that is attached or inserted on the grinding chamber side.
  • the cutting rotor 38 has a cutting rotor core 48 which is slipped onto the drive shaft 42 and has rotor blades 50 running axially on the circumference of the cutting rotor core 48 ( 4 ).
  • the rotor blades 50 are formed in one piece.
  • the rotor cutters 50 can also be produced as separate cutting strips, possibly made of a different material than the rotor cutter core 48 and connected to the rotor cutter core 48 .
  • the cutting rotor core 48 can also be designed in two or more parts (not shown).
  • the cutting rotor 38 can also be designed as a disc rotor, possibly with indexable inserts (not shown).
  • the cutting rotor 38 rotates horizontally, ie about a horizontal axis A.
  • the cutting rotor 38 is mounted on the drive shaft 42 on the motor side.
  • the cutting rotor 38 is supported by a support bearing element 54 in the form of a conical bearing element, which in turn is rotatably supported in a ball bearing 56 in the grinding chamber closure cover 20 .
  • the cutting rotor 38 includes a support bearing element receptacle 55, which is designed here as a conical bearing element receptacle.
  • the grinding chamber 16 and the grinding chamber cover 20 are sealed by means of a first labyrinth seal 160.
  • the cutting mill comminutes the material to be ground or the sample by cutting action between the essentially axially extending cutting edges 50 of the cutting rotor 38 and the stationary counter-knives 52, which also extend essentially axially 50, 52 is cut up.
  • substantially axially running" cutting edge or “axially running” cutting edge does not necessarily mean that the cutting edges 50, 52 must run exactly parallel to the axis of rotation A; the cutting edges 50, 52 can also run axially at an angle (with a twist), as in in the 2 and 4 illustrated example of a cutting rotor 38.
  • the in the 2 and 4 The example shown shows a cutting rotor 38 with so-called V-shaped cutting edges 50.
  • these cutting edges 50 also run at an angle (with a twist) but are still axial or essentially axial, i.e. in any case not transverse or perpendicular to the axis of rotation A.
  • the V-shaped cutting edges 50 of the cutting rotor 38 run along an acute-angled helix, which, however, can generally still be defined as an axial or essentially axial course.
  • the grinding chamber sealing cover 20 can be opened, which means that the grinding chamber 16 is accessible at the front for removing the cutting rotor 38 when the grinding chamber sealing cover 20 is open. Folding away the upper part 21 of the milling chamber also improves the accessibility of the opened milling chamber 16.
  • the cutting rotor 38 can be pulled off the drive shaft 42 horizontally by hand. For this purpose, the cutting rotor 38 is pushed onto the drive shaft 42 only axially and is clamped axially against the drive shaft 42 by the support bearing element 54 when the grinding chamber closure cover 20 is closed.
  • the cutting rotor 38 is only rotationally coupled to the drive shaft 42 in a form-fitting manner via the driver pins 36 and can be pulled off the drive shaft 42 without tools after opening the grinding chamber closure cover 20 .
  • the cutting rotor 38 is thus pressed in the direction of the rotor receiving element 30 and sits there on the likewise conical opponent 29 of the cone support bearing element 54 .
  • the small conical section 29 of the rotor receiving element 30 is, for example, in 6 and 11 shown. The cutting rotor 38 is thus clamped between the two cones 29 and 54 .
  • the torque transmission by means of the driver pins 36 is relatively far out in this exemplary construction, which means that sealing is carried out over a fairly large diameter.
  • the diameter of the circular ring on which the driver pins 36 are arranged is 56.5 mm, so with a driver pin diameter of 8 mm the outer outer diameter is 64.5 mm.
  • the radially outer boundary of the driver pins 36 is 32.25 mm radially away from the axis of rotation A.
  • a large diameter means a relatively high peripheral speed of the seal, compared to a seal that would hypothetically be closer to the axis of rotation A, which is disadvantageous for the seal.
  • the rotor mount could only be removed with great effort, and typically not for regular cleaning.
  • the cutting mill 10 now also has a second labyrinth seal 60 which can be easily removed by the user, for example for cleaning.
  • the second labyrinth seal 60 has an inner labyrinth ring 62 which, in this example, is placed as a separate part on the drive shaft 42, more precisely on the driver flange 34.
  • the inner labyrinth ring 62 of the second labyrinth seal 60 extends circumferentially completely around the drive shaft 42 or the driver flange 34, has labyrinth shaped elements 60b in the form of a meander shape 64b on its grinding chamber-side front side 62b and rotates with the drive shaft 42.
  • the inner labyrinth ring 62 is there radially outside of the torque-transmitting driver pins 36.
  • rotor receiving element 30 or the driver flange 34 directly with corresponding labyrinth shapes on the milling chamber side and/or on the motor side or form meanderings, ie to produce the rotor receiving element 30 and the inner labyrinth ring 62 in one piece.
  • a grinding chamber side labyrinth ring cover 66 is embedded in a corresponding recess 68 as a labyrinth receptacle in the grinding chamber rear wall 24 or the stainless steel front plate 46.
  • the labyrinth ring cover 66 on the milling chamber side and the milling chamber rear wall 24 or the stainless steel plate 46 run flush in order to jointly form an essentially flat milling chamber rear wall inside 24b in the area of the cutting rotor 38 .
  • the rotor receiving element 30 is fastened to the motor shaft 26 by means of a central screw 31, although this is not absolutely necessary depending on the embodiment.
  • the rotor receiving element 30 sits with a typical transition fit, i.e. clamping tight, on the motor shaft or primary shaft 26, it can still be pulled off the primary shaft 26 axially in the direction of the opened grinding chamber closure cover 20 by overcoming the clamping force if the screw that may be present has been loosened.
  • the rotor receiving element 30 has a central bore 33 for the central fastening screw 31 .
  • the bore 33 can be designed as a threaded bore with a larger thread diameter. Then, for example, a corresponding threaded screw in the threaded hole 33 can be used for removing (not shown).
  • the inner labyrinth ring 62 is also pulled off with the rotor receiving element 30 and with it the labyrinth ring cover 66 on the grinding chamber side, so that the passage opening 28 in the grinding chamber rear wall 24 is relatively easily accessible annularly around the primary shaft 26, e.g. to clean it.
  • the rotor receiving element 30 automatically takes the second labyrinth seal 60 with it when it is pulled off the primary shaft 26 .
  • the rotor receiving element 30, the inner labyrinth ring 62 and/or the labyrinth ring cover 66 on the grinding chamber side can be separated and cleaned, for example in an ultrasonic bath.
  • the labyrinth shot 68 for the second After the removal of the rotor receiving element 30 with the inner labyrinth ring 62 and the labyrinth ring cover 66 on the grinding chamber side, the labyrinth seal 60 is easily accessible from the open grinding chamber 16 and can likewise be cleaned.
  • the second labyrinth seal 60 designed in this way is therefore advantageously easy to maintain, since on the one hand it is easy to clean and on the other hand it is very durable, since the parts of the second labyrinth seal 60 rotating in opposite directions, i.e. the inner labyrinth ring 62 rotating with the cutting rotor on the one hand and the stationary one on the grinding chamber side
  • the labyrinth ring cover 66 as in the case of the first labyrinth seal 160 described in greater detail below, do not touch one another, but rather work according to the principle of the gap seal, i.e. there is an air gap between the interlocked labyrinth shaped elements 60a, 60b.
  • the heat development at the second labyrinth seal 60 is low despite the relatively large seal diameter at this point, since the second labyrinth seal 60 is a non-contacting gap seal and as long as the gaps remain clean, no increased friction is generated here. Nevertheless, the seal that runs on the rotor receiving element 30 or the driver flange 34 as in previous seals far out, so that the compatibility with older cutting rotors can be maintained.
  • the parts of the rear wall 24 of the grinding chamber that directly face the grinding chamber 16, i.e. at least the plate 46 and the labyrinth ring cover 66 embedded therein can be made of stainless steel, so that FDA compatibility, for example, is possible.
  • the second labyrinth seal 60 has additional radial labyrinth shaped elements 82 in the form of radially circumferential grooves.
  • the inner labyrinth ring 62 used for this has meandering formations formed by the grooves 82 on its radially outer circumference 62c.
  • the meandering formations are formed by two rings 84, 86 which are triangular in axial cross section.
  • the radially circumferential outer surface 62c of the inner labyrinth ring 62 is accordingly provided with sharp-edged points.
  • this geometry can create vortices that can cause air pockets and thus the passage of Can complicate or prevent particles from the grinding chamber 16 in the direction of the area surrounding the motor 14.
  • An advantage of this inner labyrinth ring 62 is that it can be manufactured purely as a turned part and does not need to be milled.
  • the labyrinth receptacle 68 has no counter-labyrinth rings engaging in the grooves 82 or intermediate spaces between the projections 84, 86, so that one can speak of an open labyrinth on the peripheral side or a transparent labyrinth.
  • the radially outwardly extending annular projections 84, 86 are not interdigitated with corresponding mating labyrinth elements.
  • the inner labyrinth ring 62 can thus advantageously be pulled out axially from the passage opening 28 or the labyrinth receptacle 68 .
  • the labyrinth ring cover 66 on the milling chamber side is inserted in a form-fitting manner with an O-ring 88 in the recess 68 or in the plate 46 in a clamping manner.
  • the elastic O-ring 88 ensures that the labyrinth ring cover 66 is clamped in the grinding chamber rear wall 24, but also allows the rotor receiving element 30 to be pulled out axially together with the inner labyrinth ring 62 and the labyrinth ring cover 66 on the grinding chamber side, overcoming the forces caused by the O-ring 88 clamping force too.
  • the user can thus pull out the parts 30, 62 and 66 from the through-opening 28 by applying appropriate axial force to overcome the clamping force of the clamp, so that the through-opening 28 and the labyrinth receptacle 68 are accessible from the front for cleaning.
  • the second labyrinth seal 60 can be pulled apart axially relatively easily, in particular by hand, in order to be cleaned.
  • the grinding chamber 16 has a further labyrinth seal on the side of the grinding chamber closure cover 20, which is referred to here as the first labyrinth seal 160.
  • the first labyrinth seal 160 on the grinding chamber cover 20 seals the grinding chamber 16 against the area of the grinding chamber cover 20 in which the cover-side bearing of the cutting rotor 38 is located, which in the present example is brought about by the ball bearing 56 .
  • the grinding chamber closure cover 20 is designed in several parts and has an outer cover part 122 with a central opening and an inner cover part 124 inserted therein.
  • the outer cover part 122 forms the main part of the Grinding chamber closure cover 20, in the form of an aluminum door.
  • the inner annular cover part 124 has an axially directed away from the grinding chamber 16 annular projection 126 which engages in a central opening 128 of the outer cover part 122 from the inside.
  • the inner cover part 124 is closed from the outside by means of a central attachment cover 130 .
  • the central attachment cover 130 is fastened from the outside, in this example by means of screws 132, to the grinding chamber closure cover 20, more precisely to the inner cover part 124, in order to be able to be loosened and removed from the outside.
  • the milling chamber closure cap 20 or inner cap portion 124 and center closure cap 130 house the ball bearing 56 and allow for its external installation and removal.
  • the ball bearing 56 is designed as a double-row angular contact ball bearing. "Oblique" because of the better absorption of axial forces. Doubly so that the angular play is significantly reduced compared to a simple deep groove ball bearing.
  • the ball bearing 56 is axially subjected to a force in the direction of the grinding chamber 16 by a spring 140 which, in the present example, is designed as a spring assembly made up of two plate springs layered in opposite directions.
  • the spring 140 is supported on the central attachment cover 130 , that is to say in general terms on an inside of the grinding chamber closure cover 20 .
  • the support bearing element 54 which has a bearing fit in the present example in the form of a cone 156 on the grinding chamber side and a bearing extension 158 pointing away from the grinding chamber 16, is rotatably mounted on the grinding chamber closure cover 20 by means of the ball bearing 56.
  • the support bearing element 54 is generally mushroom-shaped and the bearing extension 158 is mounted in the ball bearing 56 .
  • the cone 156 on the milling chamber side fits into the conical support bearing element receptacle 55 of the cutting rotor 38 in order to clamp the cutting rotor 38 on the sealing cover side and to form the counter bearing for the motor shaft 26 .
  • an O-ring 152 is inserted in a circumferential annular groove 150, with which the support bearing element 54 is clamped in the ball bearing 56 so that it does not fall out when the grinding chamber cover 20 is opened. Nevertheless, the support bearing element 54 can pass through a central bore 154 in the grinding chamber closure cover 20, more specifically in the central lid attachment 130, for example by means of a bolt or screwdriver overcoming the clamping or frictional force caused by the O-ring 152 when the grinding chamber closure lid 20 is opened.
  • a grinding chamber side or inner labyrinth ring 162 of the first labyrinth seal 160 is supported axially on a ring stop 172 of the support bearing element 54 . When the support bearing element 54 is pressed out, the labyrinth ring 162 on the grinding chamber side is thereby also pressed out.
  • the inner labyrinth ring 162 engages with its axial labyrinth shaped elements 182 in the form of two annular axial projections 182a, 182b in corresponding axial labyrinth shaped elements 184 in the form of axial grooves 184a, 184b of the outer labyrinth ring 164.
  • the axial labyrinth features 182 of the inner labyrinth ring 162 are axially interleaved with the axial labyrinth features 184 of the outer labyrinth ring 164 .
  • the axial gap dimension 204 of the labyrinth seal 160 is considerably larger than the radial gap dimension 205.
  • the first labyrinth seal 160 has sufficient axial play to prevent the compression of the bearing on the closure cover side when the grinding chamber Cap 20 to compensate.
  • the support bearing element 54 presses against the support bearing element receptacle 55 in order to axially brace the cutting rotor 38 .
  • the support bearing element 54 tensions the spring 140 via the ball bearing 56.
  • the spring tension of the spring 140 ensures that the ball bearing 56 is moved in the direction of the cutting rotor 38 until this a stop 190 of the grinding chamber closure cover 20, more precisely the inner cover part 124 strikes.
  • the ball bearing 56 disengages axially from the stop 190 when the support bearing element 54 with the ball bearing 56 deflects against the spring 140 away from the cutting rotor 38, so that the ball bearing 56 is not unduly twisted during operation during rotation.
  • the outer labyrinth ring 164 is not designed as a separate part, but is screwed integrally into the grinding chamber closure cover 20, more precisely into the inner cover part 124, as a result of which a separate component can be saved.
  • Both the inner cover part 124 and the inner labyrinth ring 162, and thus the second labyrinth seal 160 are preferably made of stainless steel and/or manufactured as turned parts, which offers advantages with regard to administrative approvals and on the other hand is inexpensive to manufacture.
  • the grinding chamber sealing cover 20 seals against the end face of the housing part 12b surrounding the grinding chamber 16 by means of an O-ring 192 .
  • the support bearing element 54 has further labyrinth shaped elements 194 on its radial outer side 54a.
  • the radially encircling labyrinth shaped elements 194 are formed by grooves 196, between which radially encircling projections 198 relative to the grooves 196 are formed.
  • the radially circumferential projections 198 have a triangular cross section and are pointed radially on the outside in order to possibly generate flow vortices, which can improve the sealing effect.
  • the receiving opening 202 for the support bearing element 54 in the grinding chamber closure cover 20 has no labyrinth form elements intermeshing with the labyrinth form elements 194 of the support bearing element 54 .
  • the access opening 202 is smooth on its inside, so that the radial labyrinth shaped elements 194 of the support bearing element 54 together with the opening 202 form an open (radially uninterlocked) labyrinth or a clear labyrinth.
  • the support bearing element 54 can be pressed axially inwards out of the grinding chamber closure cover 20 without complex dismantling.
  • the support bearing element 54 takes the inner labyrinth ring 162 with it via the stop 172 . Subsequently, both the labyrinth sealing surfaces and at least partially the ball bearing 56 are exposed, so that cleaning is simplified.
  • the support bearing element 54 and the inner labyrinth ring 162 can be removed in one be cleaned in an ultrasonic bath.
  • a reverse geometry of the radial perspective labyrinth is also possible, in that the radial labyrinth shaped elements 194 are arranged radially on the inside in the opening 202 instead of radially on the outside on the support bearing element 54 .
  • a radially uninterlocked or see-through labyrinth is formed by radial form elements 194 either on the radial outer circumference of the support bearing element 54 or on a radial inner circumference of the grinding chamber closure cover 20 .
  • FIG. 12 to 14 shows the deflection of the support bearing element 54 together with the ball bearing 56 when closing the grinding chamber cover 20 in more detail.
  • the 12 shows the open state of the grinding chamber closure cover 20, in which the spring 140 tensions the ball bearing 56 against the axial stop 190. In this state, the spring 140 is tensioned the least and the first labyrinth seal 160 has the maximum axial gap dimension 204 .
  • the closed state of the grinding chamber closure cover 20 is shown, in which the support bearing element 54 tensions the ball bearing 56 against the spring 140 by means of an axial stop 206 resting on the ball bearing 56 and is correspondingly deflected.
  • the support bearing element 54 clamps with its axial ring stop 206 against the inner end face of the ball bearing 56 in order to clamp it against the spring 140 and thus forms an axial counter bearing for the spring 140.
  • the axial gap dimension 204 of the first labyrinth seal 160 is smaller than in the open state according to 12 .
  • the first labyrinth seal 160 thus has an axial displaceability of the interlocking labyrinth shaped elements 182, 184, whereby the deflection of the support bearing element 54, which occurs when the cutting rotor 38 is braced or when the grinding chamber cover 20 is closed, can be compensated.
  • the 14 shows a maximum extreme state in which the maximum deflection of the support bearing element 54 and the ball bearing 56 is shown, so that the axial play of the first labyrinth seal 160 in the form of the axial gap 204 is completely consumed. This A condition in which the first labyrinth seal 160 would rub should not be reached during operation.
  • the first labyrinth seal 160 has axially relatively long labyrinth shaped elements 182, 184 that intermesh with one another in order to achieve a good labyrinth sealing effect on the one hand and to allow sufficient axial play or sufficient axial spring travel on the other hand to be able to compensate for axial tolerances of the cutting rotor 38, for example .
  • the aspect ratio of the axially intermeshing labyrinth shaped elements 182, 184 is greater than 1, preferably greater than 2, in the present example approximately between 3 and 4.
  • the axial displacements that occur on the grinding chamber closure cover 20 can be relatively large, for example due to tolerances and/or deflection.
  • One reason for this is the support bearing element 54 or the so-called conical support bearing that has to absorb the length tolerances that occur between itself and the motor output shaft.
  • the cutting rotor 38 is pushed in the direction of the drive motor 14 with a force of, for example, 1000 N. This force should also be applied safely and, due to the spring deflection of the spring 140 required for this, causes further axial length tolerances.
  • these special requirements can be met in a generic cutting mill with a labyrinth seal which has a sufficiently large axial play or gap size. Although the labyrinth seal is not absolutely tight, it can be easily dismantled and cleaned by the user.
  • the described plug-in solution for the support bearing element 54 instead of a screw connection also offers the advantage that the support bearing element 54, which carries one of the two labyrinth rings, can be pushed out of its holder in the direction of the grinding chamber 16 without for example having to loosen a screw connection.
  • the clamping element between the support bearing element 54 in the grinding chamber closure cover 20 in the form of the additional O-ring 152 ensures that the support bearing element 54 is held in place in the bearing without having to provide a positive fit.
  • the support bearing element 54 which is designed as a cone support bearing in the present example, is pushed back in and does not need to be locked any further, since it is held in place by the O-ring 152 in a clamping or frictional manner in the grinding chamber -Cap 20, more precisely in which ball bearing 56 is retained.
  • the cutting rotor 38 or the axial clamping force also ensures that the support bearing element 54 is clamped axially between the ball bearing 56 and the cutting rotor 38 .
  • the sealing concept presented here has a number of advantages, e.g. compared to the felt seals previously used.
  • the sealing concept is maintenance-friendly and, on the other hand, hardly requires any maintenance. Nevertheless, the sealing concept keeps dust well in the grinding chamber and only allows a small amount of dust or other dirt to get through the first labyrinth seal to the ball bearing 56 and, if also present, possibly also through the second labyrinth seal in the area of the drive motor 14. Furthermore, the sealing concept shows low heat development.
  • Another advantage is the avoidance of material abrasion (with clean labyrinth seals 60, 160) and the possibility of administrative approvals (e.g. an FDA approval), especially if e.g. the parts of the first and/or second labyrinth seal are made of stainless steel.
  • the production of such labyrinth seals has proven to be technologically feasible and has surprising advantages. For example, efforts are currently being made in some regions of the world to allow cannabis products for various uses. This has led to an increased demand for granulators in cannabis processing.
  • the first labyrinth seal proposed here in the grinding chamber sealing cover 20 can effectively prevent the seal from becoming oily or resinous, or at least the cleaning options for the Bearing on the grinding chamber cover 20 has been significantly improved.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Grinding (AREA)
  • Crushing And Pulverization Processes (AREA)

Claims (15)

  1. Broyeur à découper (10) destiné au broyage par découpage d'échantillons avec un rotor de découpage (38), comprenant
    un carter d'appareil (12),
    un moteur d'entraînement (14) destiné à l'entraînement en rotation du rotor de découpage (38),
    une chambre de broyage (16) avec le rotor de découpage (38) qui est disposé dans celle-ci et est destiné à broyer par découpage les échantillons dans la chambre de broyage (16), le rotor de découpage (38) définissant un axe de rotation (A), et la chambre de broyage (16) étant délimitée axialement côté moteur par une paroi arrière de chambre de broyage (24),
    le carter d'appareil (12) comportant, sur le côté du rotor de découpage (38) axialement opposé à la paroi arrière de chambre de broyage (24), un couvercle de fermeture (20) qui peut être ouvert pour ouvrir la chambre de broyage (16), le couvercle de fermeture (20) présentant un élément formant palier de support (54) pour le rotor de découpage (38),
    caractérisé en ce que
    sur le côté du couvercle de fermeture (20), il est prévu un premier joint d'étanchéité labyrinthe (160).
  2. Broyeur à découper (10) selon la revendication 1,
    comprenant en outre un arbre d'entraînement (42) avançant dans la chambre de broyage (16), le rotor de découpage (38) pouvant être rapporté et retiré manuellement de façon coaxiale de l'arbre d'entraînement (42) lorsque la chambre de broyage (16) est ouverte, la paroi arrière de chambre de broyage (24) présentant notamment une ouverture de passage d'arbre (28), et l'arbre d'entraînement (42) s'étendant à travers l'ouverture de passage d'arbre (28), en vue de l'entraînement du rotor de découpage (38).
  3. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel l'élément formant palier de support (54) exerce une force sur le rotor de découpage (38), axialement en direction la paroi arrière de chambre de broyage, lorsque le couvercle de fermeture (20) est fermé.
  4. Broyeur à découper (10) selon l'une des revendications précédentes, comprenant un ressort (140) qui exerce une force sur l'élément formant palier de support (54), de façon directe ou indirecte, axialement en direction de la paroi arrière de chambre de broyage, lorsque le couvercle de fermeture (20) est fermé, sachant que la force de ressort axiale agissant sur l'élément formant palier de support (54) et/ou la force axiale exercée par l'élément formant palier de support (54) sur le rotor de découpage (38) est/sont de préférence supérieure(s) à 100 N, de préférence supérieure(s) à 200 N, et de préférence supérieure(s) à 500 N.
  5. Broyeur à découper (10) selon l'une des revendications précédentes, présentant au moins une, plusieurs ou toutes les caractéristiques suivantes :
    l'élément formant palier de support (54) est réalisé sous forme de tronçon d'arbre qui est monté à l'aide d'un palier (56) sur le couvercle de fermeture (20).
    le couvercle de fermeture (20) présente une butée (190) contre laquelle le palier (56) est mis sous précontrainte à l'aide du ressort, axialement en direction de la chambre de broyage (16), lorsque le couvercle de fermeture (20) est ouvert, et/ou
    l'élément formant palier de support (54) présente une butée (206) contre laquelle le palier (56) est mis sous précontrainte à l'aide du ressort (140), axialement en direction de la chambre de broyage (16), et/ou
    lors de la fermeture du couvercle de fermeture (20), le rotor de découpage (38) déplace l'élément formant palier de support (54) à l'encontre de la tension du ressort (140), axialement dans la direction opposée à celle de la chambre de broyage (16), et/ou
    lors de la fermeture du couvercle de fermeture (20), l'élément formant palier de support (54) déplace le palier (56) à l'encontre de la tension du ressort (140), axialement dans la direction opposée à la chambre de broyage (16), et sépare le palier (56) axialement de la butée (190) dans le couvercle de fermeture (20).
  6. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel l'élément formant palier de support (54) présente un moyen d'ajustement de palier (156) qui s'engage dans un logement d'ajustement (55) correspondant du rotor de découpage (38) lorsque le couvercle de fermeture (20) est fermé.
  7. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel l'élément formant palier de support (54) est monté avec possibilité de déplacement axial sur le couvercle de fermeture (20).
  8. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel le premier joint labyrinthe (160) présente un jeu axial qui compense notamment un déplacement axial de l'élément formant palier de support (54).
  9. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel, lorsque le couvercle de fermeture (20) est fermé, le premier joint labyrinthe (160) présente une dimension d'interstice axiale (204) plus faible que lorsque le couvercle de fermeture (20) est ouvert, et/ou
    dans lequel, lorsque le couvercle de fermeture (20) est ouvert et/ou fermé, le premier joint labyrinthe (160) présente une dimension d'interstice radiale (205) qui est plus faible que la dimension d'interstice axiale (204).
  10. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel le premier joint labyrinthe (160) engrène exclusivement dans la direction axiale et/ou dans lequel le premier joint labyrinthe (160) présente au moins une rainure radiale (196) prolongeant le parcours du fluide.
  11. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel le premier joint labyrinthe (160) présente une première et une deuxième bague labyrinthe (162, 164) qui engrènent l'une avec l'autre, de préférence la première bague labyrinthe (162) étant fixée à l'élément formant palier de support, notamment avec serrage axial, et la deuxième bague labyrinthe (164) étant de préférence prévue sur le couvercle de fermeture (20).
  12. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel l'engrènement du premier joint labyrinthe (160) est conçu de manière à permettre un déplacement axial entre la première et la deuxième bague labyrinthe (162, 164), à l'intérieur d'une course prédéfinie, notamment pour pouvoir compenser un déplacement axial de l'élément formant palier d'appui (54), en conservant l'effet d'étanchéité du premier joint labyrinthe (160).
  13. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel l'élément formant palier de support (54) est monté avec serrage axial (150, 152) sur le couvercle de fermeture (20), afin de garantir d'une part la possibilité de déplacement axial et d'empêcher d'autre part que l'élément formant palier de support (54) ne tombe spontanément du couvercle de fermeture (20) lorsque le couvercle (20) est ouvert, et dans lequel, de préférence, l'élément formant palier de support (54) peut être poussé hors du couvercle de fermeture (20), en surmontant le serrage (152), et dans lequel, de préférence, le couvercle de fermeture (20) présente une ouverture (154) à travers laquelle l'élément formant palier de support (54) peut être poussé hors du couvercle de fermeture (20).
  14. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel l'élément formant palier de support (54) est simplement inséré dans le couvercle de fermeture (20) et n'est pas vissé dans le couvercle de fermeture (20), même lors du fonctionnement.
  15. Broyeur à découper (10) selon l'une des revendications précédentes,
    dans lequel l'ouverture de passage d'arbre (28) est rendue étanche dans la paroi arrière de chambre de broyage (24) à l'aide d'un deuxième joint labyrinthe (60).
EP20209556.8A 2019-12-06 2020-11-24 Broyeur à découper destiné au broyage par découpage des échantillons Active EP3831494B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102019133437.3A DE102019133437A1 (de) 2019-12-06 2019-12-06 Schneidmühle zum schneidenden Zerkleinern von Proben

Publications (2)

Publication Number Publication Date
EP3831494A1 EP3831494A1 (fr) 2021-06-09
EP3831494B1 true EP3831494B1 (fr) 2022-08-17

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EP20209556.8A Active EP3831494B1 (fr) 2019-12-06 2020-11-24 Broyeur à découper destiné au broyage par découpage des échantillons

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DE102022115335A1 (de) * 2022-06-20 2023-12-21 Fritsch Gmbh Labormühle
DE102022115334B4 (de) 2022-06-20 2025-08-14 Fritsch Gmbh Labormühle
WO2025088197A1 (fr) * 2023-10-25 2025-05-01 Retsch Gmbh Broyeur de laboratoire
DE102024113618B4 (de) * 2024-05-15 2026-03-12 Fritsch Gmbh Labormühle und Mahlguteinfüllstempel für eine Labormühle

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DE19706425C1 (de) * 1997-02-19 1998-04-09 Fritsch Gmbh Laborgeraetebau Zerlegbare Laborschneidmühle
DE29713097U1 (de) * 1997-07-23 1998-11-26 Fritsch GmbH Laborgerätebau, 55743 Idar-Oberstein Labormühle mit Befestigungseinrichtung für eine Gutauffangvorrichtung
DE202016005405U1 (de) * 2016-05-18 2017-08-21 Retsch Gmbh Mahlbecher und Labormühle mit einem Mahlbecher

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EP3831494A1 (fr) 2021-06-09

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