EP2895308A1 - Dispositif de découpe - Google Patents

Dispositif de découpe

Info

Publication number
EP2895308A1
EP2895308A1 EP13776798.4A EP13776798A EP2895308A1 EP 2895308 A1 EP2895308 A1 EP 2895308A1 EP 13776798 A EP13776798 A EP 13776798A EP 2895308 A1 EP2895308 A1 EP 2895308A1
Authority
EP
European Patent Office
Prior art keywords
cutting blade
blade
balancing
imbalance
balancing mass
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.)
Granted
Application number
EP13776798.4A
Other languages
German (de)
English (en)
Other versions
EP2895308B1 (fr
Inventor
Josef Mayer
Jörg SCHMEISER
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.)
Textor Maschinenbau GmbH
Original Assignee
Textor Maschinenbau GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Textor Maschinenbau GmbH filed Critical Textor Maschinenbau GmbH
Priority to EP20164910.0A priority Critical patent/EP3702118B1/fr
Publication of EP2895308A1 publication Critical patent/EP2895308A1/fr
Application granted granted Critical
Publication of EP2895308B1 publication Critical patent/EP2895308B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D7/00—Details of apparatus for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D7/26—Means for mounting or adjusting the cutting member; Means for adjusting the stroke of the cutting member
    • B26D7/2614—Means for mounting the cutting member
    • B26D7/2621—Means for mounting the cutting member for circular cutters
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D1/00—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor
    • B26D1/01—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work
    • B26D1/12—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis
    • B26D1/14—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis with a circular cutting member, e.g. disc cutter
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D1/00—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor
    • B26D1/01—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work
    • B26D1/12—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis
    • B26D1/25—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis with a non-circular cutting member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D1/00—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor
    • B26D1/01—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work
    • B26D1/12—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis
    • B26D1/25—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis with a non-circular cutting member
    • B26D1/26—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis with a non-circular cutting member moving about an axis substantially perpendicular to the line of cut
    • B26D1/28—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis with a non-circular cutting member moving about an axis substantially perpendicular to the line of cut and rotating continuously in one direction during cutting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D7/00—Details of apparatus for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D7/26—Means for mounting or adjusting the cutting member; Means for adjusting the stroke of the cutting member
    • B26D7/2614—Means for mounting the cutting member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D1/00—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor
    • B26D1/0006—Cutting members therefor
    • B26D2001/0046—Cutting members therefor rotating continuously about an axis perpendicular to the edge
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D2210/00—Machines or methods used for cutting special materials
    • B26D2210/02—Machines or methods used for cutting special materials for cutting food products, e.g. food slicers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D2210/00—Machines or methods used for cutting special materials
    • B26D2210/02—Machines or methods used for cutting special materials for cutting food products, e.g. food slicers
    • B26D2210/08—Idle cutting
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/869—Means to drive or to guide tool
    • Y10T83/8789—With simple revolving motion only

Definitions

  • the invention relates to a device for slicing food products, in particular high-performance slicers, having at least one about an axis rotating, unbalanced cutting blade, a rotary drive for the cutting blade, which is arranged on a drive side of the cutting blade, and at least one balancing mass comprehensive counterweight to compensate for the imbalance of the cutting blade.
  • sickle blades can be used, which rotate at a speed of about 600 to about 2,500 revolutions per minute.
  • the sickle blade has an asymmetrical contour with respect to the axis of rotation.
  • the knife's center of gravity ie the center of mass of the knife, is thus shifted with respect to the axis of rotation.
  • the knife shape and / or the knife contour thus results in an imbalance with a certain imbalance mass or imbalance.
  • WO 2010/01 1237 A1 shows in FIG. 44 B two counterweights, of which viewed in the axial direction a counterweight is arranged in front of the knife and a counterweight behind the knife.
  • imbalance in the following also generally depending on the context an imbalance mass, an imbalance position and / or at the rotation due to the imbalance mass effective force in terms of magnitude and direction to understand.
  • Axial distances ie distances measured along the axis of rotation of the knife, relative to a cutting blade here, unless otherwise indicated, relate to a cutting plane defined by the knife, while the axial position of a balancing mass or imbalance refers to a plane which is perpendicular to the axis of rotation of the knife and in which the center of mass of the balancing mass or imbalance.
  • a balancing mass or imbalance refers to a plane which is perpendicular to the axis of rotation of the knife and in which the center of mass of the balancing mass or imbalance.
  • the counterweight is arranged exclusively on one side of the cutting blade.
  • all balancing masses are arranged only on one side of the cutting blade, i. the invention means a departure from known from the prior art balancing concepts, in which the counterweight divided on both sides of the knife, so at least one balance mass before and at least one further balancing mass behind the knife is arranged.
  • the side on which the counterweight is located may be the drive side of the knife. This is not mandatory.
  • the side of the counterweight can also be the knife side from which the products are fed to the knife.
  • this feed side can be identical to the drive side, although this is not mandatory.
  • the invention provides that all balancing masses are not located on the side of the knife, which is provided for disassembly of the knife, ie seen from the disassembly side of the knife from all balancing masses are on the other side of the knife. If, for example, the knife has to be removed forwards, all the balancing masses are behind the knife, so that no balancing mass needs to be moved to disassemble the knife. On the dismounting side of the knife thus no balancing mass is provided.
  • components such as a part of a hub or fasteners, such as screws, this serve only the attachment of the cutting blade or other purposes, but not the balancing of imbalance of the cutting blade.
  • the balancing mass-free side of the knife in particular so the disassembly side, may be identical to the side on which the cut products are transported away, but this is not mandatory and depends on the particular slicer concept. Slicer concepts exist in which the drive side and the dismounting side of the knife lie on the same side of the knife and thus opposite the product feed side.
  • the counterweight is adapted to the blade mass or blade shape, which determines the imbalance of the cutting blade.
  • the cutting blade is removably attached to a blade receptacle.
  • the blade holder forms a balancing mass and has an asymmetrical rotational geometry with respect to the axis of rotation.
  • the blade holder itself that forms a balancing mass for balancing the blade.
  • This concept makes it possible to position the required balancing mass on the one hand axially close to the knife and on the other hand radially relatively far outward, which makes a particularly efficient balance concept feasible overall. Due to the asymmetrical design of the blade holder a sufficiently large imbalance can be generated at a relatively low total weight of the blade holder.
  • This asymmetric shape of the blade receptacle with respect to the axis of rotation means a departure from known from the prior art concepts for the blade holder, in which it crucially important to provide a blade holder with a symmetrical with respect to the rotation axis rotation geometry, in particular with a concentric to the axis of rotation circular outer contour , which is needed to seal a corresponding circular opening in a housing or frame of the slicer or to form a narrow annular gap with this opening.
  • the blade receptacle can deviate extremely from a circular outer contour and to a certain extent be highly top-heavy - with respect to the radial direction - ie be affected by a relatively large imbalance or imbalance mass, for example - as figuratively speaking a rotating hammer.
  • the blade receptacle may, for example, comprise a first section and a second section, the first section forming the largest radius of the blade receptacle, the axis of rotation passing through the second section, and the center of mass of the first section radially outward of the center of mass of the second Section lies.
  • the blade holder can be formed, for example, at least approximately in the manner of an armature, with a relatively heavy circular ring section being arranged radially on the outside at a comparatively slight central section, through which the axis of rotation runs.
  • the outer circular ring section may, for example, extend over at least 1/7, 1/6, 1/5, 1/4 or 1/3 of the outer circumference of the blade receptacle.
  • the blade holder itself forms a balancing mass, the design is particularly simple.
  • the balancing mass is also in this way axially particularly close to the cutting plane. Another, separate balancing mass in the axial vicinity of the cutting blade is therefore not necessary.
  • the knife holder thus fulfills a dual function, since on the one hand it carries the knife and on the other hand at least compensates for a part of the imbalance of the cutting knife.
  • the slicing device is thus particularly easy to adapt to various applications. This makes it easy to use knives of different sizes.
  • the other components of the slicing device can be retained. be.
  • an optionally additionally provided further balancing mass can remain in the same position.
  • the balancing mass or one of the balancing masses is formed by the rotary drive, in particular by a drive pulley or by a hub which can be set in rotation by means of a drive motor via a drive belt.
  • the rotary drive fulfills a dual function, since on the one hand causes the cutting blade in rotation and on the other hand compensates for at least a portion of the imbalance of the cutting blade.
  • the rotational drive due to the imbalance together with the cutting blade forms a mass system that can be dimensioned and arranged such that the overall center of gravity of the rotating system is on the side of the cutting blade on which also the rotary drive is located. In other words, this center of gravity is "pulled” on its side by the imbalance in the rotary drive. Consequently, it is possible to have another one
  • the balancing mass formed by the rotary drive can bring about optimum balancing of the rotating overall system in all planes and both statically and dynamically, and with an extremely compact design overall arrangement.
  • Another advantage is that by modifying the rotary drive, for example, by replacing the drive pulley or the hub, a knife with a different size and thus a different imbalance can be balanced.
  • An optionally in addition to the rotary drive serving as a balancing mass blade holder itself does not necessarily have to be replaced, but it is possible to change in a blade change both the blade holder and the drive pulley or the hub, the latter in particular if it is not possible or not it is desired to compensate for the change in the imbalance to be compensated associated with a blade change exclusively by exchanging the blade receptacle.
  • the drive disk may be, for example, a toothed belt pulley, which is set into rotary motion by a motor-driven toothed belt.
  • the drive pulley may, for example, drive a shaft which carries the blade receptacle and thus the blade and sets in rotation and which is rotatably mounted in a fixed hub.
  • a particularly hollow cylindrical hub can be provided, which is for example placed on a motor-driven toothed belt in a rotary motion and which carries the blade holder and thus the knife and set in rotation, wherein the hub is rotatably mounted on a shaft or spindle, which rotatable relative to the knife itself is.
  • the driven shaft or the driven hub may carry the trained as a separate component blade receptacle or be designed as a blade holder itself.
  • the hub can in each case contain a balancing mass at at least two axially spaced locations or act as imbalance in order to compensate for the imbalance of the blade.
  • the counterweight formed by the imbalance masses or imbalances is provided by a single component - namely, the one hand rotationally driven and on the other hand bearing the balance to be compensated with the imbalance bearing hub - which is arranged on one side of the knife, so that also in this variant all to balance the Messerunwucht provided balancing masses or imbalances need to be arranged only on one side of the knife.
  • the rotary drive is in particular axially spaced from the cutting blade, for example in a range between 150 mm and 500 mm, preferably from 150 mm to 300 mm.
  • the counterweight in all aspects of the invention mentioned here, provision is made in particular for the counterweight to comprise not just a single balancing mass but a plurality of balancing masses spaced apart axially from one another.
  • exactly two balancing masses are provided.
  • a counterweight is provided to compensate for the imbalance of the cutting blade, comprising at least two axially spaced-apart balancing masses.
  • a first balance mass and the imbalance of the cutting blade are at least approximately effective in opposite radial directions, while a second
  • Balancing mass at least approximately in the same radial direction is effective as the imbalance of the cutting blade.
  • the first balancing mass is arranged closer to the cutting blade in the axial direction than the second balancing mass.
  • a first balancing mass is arranged at an axial distance from the cutting blade, which is smaller by a multiple than the axial distance of a second balancing mass from the cutting blade.
  • the first balancing mass is in particular very close to the cutting blade and can be integrated, for example, in a knife holder, be a part of the blade holder or be formed by the blade holder.
  • the second balancing mass can be chosen relatively small due to the relatively large leverage present thereby. As a result, only a small mass needs to be accelerated or set in rotation.
  • a first balancing mass (or its imbalance or imbalance of a component or assembly comprising the first balancing mass) is at an axial distance of at most 50 mm, 40 mm, 35 mm, 30 mm or 25 mm, preferably of maximum 20 mm, arranged by the cutting blade.
  • a second balancing mass (or its imbalance or the imbalance of a component or assembly comprising the second balancing mass) is at an axial distance of
  • the distance between the first balance mass and the second balance mass may be, for example, at least 50 mm, 75 mm, 100 mm, 150 mm, 200 mm, 300 mm, 500 mm, 1,000 mm, 1,500 mm or 2,000 mm.
  • a first balancing mass or its imbalance is greater than the imbalance of the cutting blade.
  • the sum of the imbalance of the cutting blade and a second balancing mass or their imbalance is equal to or approximately equal to the first balancing mass or its imbalance.
  • a first balancing mass extends up to a radial distance from the axis of rotation, which amounts to at least 75%, in particular 90% and preferably at least approximately 100% of the smallest radius of the cutting blade, wherein in particular the first balancing mass is arranged closer to the cutting blade in the axial direction is as a second balancing mass.
  • the largest radius of the blade holder is at least 75%, in particular 90% and preferably at least approximately 100% of the smallest radius of the cutting blade.
  • the blade holder can thus extend at least in a partial region of its circumference in the radial direction to the smallest radius of the cutting blade, which is impossible in arrangements known from the prior art due to a fundamentally different from the invention overall concept. This is e.g. then the case when the blade holder has to close a relatively small housing or frame opening and therefore must have a circular shape with a relatively small radius, or if the knife has a comparatively large opening for attachment of the blade holder.
  • the first balancing mass is located radially relatively far outward, ie it is spaced relatively far from the axis of rotation of the cutting blade.
  • the first balancing mass can be comparatively small. be guided. This in turn makes it possible to place the first balancing mass in the axial direction comparatively close to the imbalance of the knife and thus close to the cutting plane.
  • a second balancing mass can be chosen comparatively small, and this in particular all the more, the further the second balancing mass is axially removed from the cutting blade.
  • such a balancing concept can be realized in a particularly simple yet effective manner by forming the first balancing mass from a knife receptacle and the second balancing mass from the rotary drive of the knife.
  • a blade holder and the rotary drive are arranged on different sides of a fixed frame or frame part.
  • the frame or frame part is used in particular for axially spaced fastening of the blade receptacle via a hub, through which a drive shaft extending from the rotary drive to the blade receptacle is passed.
  • the blade holder is thus spaced from the frame or frame part in the axial direction. In this way There is a gap between the blade holder and the Gestelloder frame part.
  • a first balancing mass and a second balancing mass are arranged on different sides of a fixed frame or frame part.
  • the frame or frame part forms at least part of an outer wall facing the cutting blade of a drive housing for the rotary drive.
  • second balance mass which is located axially further away from the cutting blade than the other balancing mass, is preferably arranged in a hygienically uncritical region, for example in a drive housing.
  • the device according to the invention is designed such that a so-called fine balancing can be carried out in order to be able to balance the system as accurately as possible.
  • the fine balancing may e.g. by adding or removing small weights, in particular on or in the area of at least one provided anyway
  • the rotating cutting blade for performing at least one additional function, in particular for performing blank cuts and / or for cutting gap adjustment, by means of an axial drive in the axial direction adjustable. All balancing weights are adjustable together with the cutting blade.
  • the cutting blade is removably attached to a driven by the rotary drive rotor shaft which carries a blade receptacle for the cutting blade or is formed as a blade receptacle, wherein the rotor shaft is passed through a fixed frame or frame part, on one side of the rotary drive and on the other side of the cutting blade is arranged.
  • the rotor shaft is mounted on a hub which is supported by the fixed frame or frame part.
  • the hub is exposed to the outside and the bearing between the hub and the rotor shaft is sealed from the environment.
  • the seal may, for example, be a fende seal, eg from a rubber material, act. This open arrangement does not exclude that a protective hood surrounding the cutting region is at least partially present.
  • the hub extends in the axial direction between the fixed frame or frame part and the cutting blade.
  • the imbalance of the cutting blade can be compensated according to the invention by a special geometric arrangement of several balancing masses, preferably two balancing masses, which can also be integrated into already existing components of the slicer.
  • the balancing concepts according to the invention also have the advantage, among many others, that no material with a high density, for example tungsten or lead, is necessary for balancing. Because of the geometrical arrangement, comparatively small balancing masses can be used, and consequently standard materials such as e.g. Stainless steel can be used.
  • FIG. 1 is a partial side view of an embodiment of a slicing device according to the invention
  • Fig. 2 is a sickle blade
  • Fig. 3 is a sectional view of the slicing according to
  • Fig. 1 is a perspective view of the slicing apparatus of FIG. 1
  • Fig. 4 is a perspective view of the slicing apparatus of FIG. 1
  • FIG. 5 is a plan view of the blade receptacle of the
  • slicing apparatus also referred to as a knife or cutting head, for slicing food products, in particular sausage, ham or cheese.
  • a sickle blade 10 (see also Fig. 2) is rotatably mounted about a rotation axis D on a rotor shaft 12, which may be inclined at least in the cutting operation inclined to the horizontal.
  • the sickle blade 10 defines a cutting plane 14 which is perpendicular to the axis of rotation D.
  • the sickle blade 10 is fixed by means of screws 18 to a blade holder 20.
  • the sickle blade 10 is rotatably connected to the rotor shaft 12.
  • the rotor shaft 12 in turn is rotatably mounted in a rotor hub 22 and connected at its end facing away from the blade 10 with a rotary drive 24.
  • the drive is effected by means of a toothed belt pulley 26 as a drive pulley, which is rotated by a drive belt 28 in rotation and rotatably connected to the rotor shaft 12.
  • the belt 28 is driven by means of a motor, not shown.
  • the holder used is a frame or frame part of the slicer, not shown here, on which the hub 22 is fastened.
  • the axial distance between the cutting plane 14 and the plane of the rotary drive 24 is bridged by the rotor shaft 12 and the rotor hub 12 rotatably supporting rotor hub 22.
  • the sickle blade 10, which in particular has a weight of around 8 to 15 kg, is not rotationally symmetrical in shape and consequently has an imbalance UM (see FIGS. 2 and 4).
  • the knife 10 has a smallest radius r and a largest radius R.
  • two axially spaced balancing masses 32, 34 are provided which are each integrated into an already provided Slicerkomponente such that overall at low total weight of the balancing masses 32, 34 formed counterweight and with optimal space utilization, a balance of the knife imbalance UM is achieved.
  • the knife holder 20 comprises the first balancing mass 32 and thus causes a first unbalance Ul (see also FIGS. 3 and 4).
  • the first balancing mass 32 is arranged with respect to the axis of rotation D on the opposite side of the imbalance UM of the blade 10 (see Fig.
  • the largest radius of the blade holder 20 in relation to the smallest radius r of the blade is substantially larger than in known from the prior art blade receptacles, which have a symme- fresh rotational geometry with respect to the axis of rotation, in particular a circular outer contour.
  • the center of gravity of the blade receptacle 20 lies relatively far radially outward, with the radial position of the center of gravity of the mass - as a function of the largest radius of the blade receptacle 20 - depending on the particular concrete circumstances is selected and is located at a relevant distance from the rotation axis D targeted.
  • the blade receiving means 20 forming the first balancing mass 32 or provided with the first balancing mass 32 is designed overall in such a way that a plane containing the center of gravity of the blade receptacle 20 and running perpendicularly to the axis of rotation D is formed, for example. not axially more than 20 mm away from the cutting plane 14.
  • a preferred range for this distance LI extends approximately from 10 mm to 25 mm.
  • the second balancing mass 34 is integrated in the toothed belt pulley 26. As a result, the second balancing mass 34 is spaced substantially further axially from the cutting plane 14 than the first balancing mass 32 (see also FIG. 3). Both balancing masses 32, 34 are located with respect to the cutting plane 14 on the rear side of the cutting blade 10, ie on the side coinciding here with the side of the rotary drive 24, which is not the disassembly or assembly side of the cutting blade 10: Disassembly of the cutting blade 10 takes place in Fig. 1 to the left, while the balancing masses 32, 34 are arranged in Fig. 1 to the right of the cutting blade 10.
  • the second balancing mass 34 or its imbalance U2 with respect to the axis of rotation D on the same side and in approximately the same angular position as the imbalance UM of the blade 10 is located.
  • the second imbalance U2 is thus arranged rotated relative to the first imbalance U 1 of the first balance mass 32 provided blade holder 20 by approximately 180 ° with respect to the rotation axis D (see also Fig. 4).
  • the distances, measured in each case from the cutting plane 14, of the individual imbalances UM of the blade 10, U1 of the first imbalance 32 and U2 of the second imbalance 34 are indicated in FIG. 3 by LM, LI or L2. It can be seen that L2 is a multiple of LI and a multiple of LM and that LM and LI are approximately of the same order of magnitude.
  • a sliding seal 36 is provided for sealing the bearings 35, which serve for the rotatable mounting of the rotor shaft 12 in the rotor hub 22.
  • FIG. 4 shows a perspective view of the slicing apparatus according to FIG. 1.
  • the sickle blade 10 and the toothed belt pulley 26 each have pockets or recesses 38, 40, which on the one hand reduces the weight and, on the other hand, selectively influences the mass distribution.
  • the vectors are also shown, which illustrate the imbalance UM and the imbalances Ul, U2 of the balancing masses 32, 34.
  • Fig. 5 shows the blade holder 20 with the sickle blade 10.
  • the blade holder 20 includes screw holes 42 to which the sickle blade 10 is fastened by means of screws 18 (see Fig. 1), and
  • the radial displacement of the center of mass of the blade holder 20 is achieved relatively far outward by an anchor-like or hammer-shaped configuration.
  • a relatively heavy section 44 forming the balancing mass 32 in the form of a part-circle ring which extends about one third of the outer circumference of the measuring ring. has a larger outer radius A than a comparatively light central portion 46 with an outer radius a, which is also substantially thinner than the outer pitch ring portion 44.
  • the Mes- serfact 20 is comparable to a certain extent with a hammer, ie highly top-heavy with a radially outer head.
  • a first balancing mass 32 is integrated into a blade receptacle 20 having a relatively large radial extent and can therefore be arranged axially very close to the blade 10 and radially far away from one another. As a result, the first balancing mass 32 can be selected to be comparatively small.
  • a second balancing mass 34 is arranged axially far away from the blade 10 in comparison to the first balancing mass 32. This also allows the second balance mass 32 is relatively small and significantly smaller than the first
  • Balancing mass 32 can be selected. This in turn allows the integration of the second balancing mass 34 into the rotary drive 24 of the knife 10.
  • the rotary drive 24 may be arranged in a housing which has a housing wall as a fixed frame or frame part, which extends on the side facing the blade 10 of the rotary drive 24 axially close to the rotary drive 24 perpendicular to the axis of rotation D.
  • a merely indicated by a double arrow and basically arbitrarily cleanedstalteteter axial drive L can engage the rotor shaft 12 and be supported on this housing wall or at another point of the frame or frame. If the sickle blade 10 is to be moved axially, for example, to carry out blank cuts, the axial drive L is activated.
  • the sickle blade 10 together with the blade holder 20 as well as all the balancing masses 32, 34 are adjusted together with the rotor shaft 12 relative to the housing wall or the frame or frame and relative to the rotor hub 22.
  • the drive belt 28 is deflected slightly obliquely during this movement.
  • the slicing device according to the invention is therefore always perfect even with an axial movement of the knife 10 and balanced in all relevant planes and thus statically and dynamically.
  • the inventive arrangement of the balancing masses 32, 34 allows an extremely compact and thus space-saving design of the rotor and the slicing device as a whole. LIST OF REFERENCE NUMBERS

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  • Life Sciences & Earth Sciences (AREA)
  • Forests & Forestry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Food-Manufacturing Devices (AREA)

Abstract

L'invention concerne un dispositif de découpe de produits alimentaires, en particulier une trancheuse hautes performances, comprenant au moins un couteau (10), en particulier un couteau à lame falciforme, présentant un balourd (UM) tournant autour d'un axe de rotation (D), un entraînement en rotation (24) pour le couteau (10), et un contrepoids comprenant au moins une masse d'équilibrage (32, 34) pour compenser le balourd (UM) du couteau (10).
EP13776798.4A 2012-10-16 2013-10-14 Dispositif de découpe Active EP2895308B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP20164910.0A EP3702118B1 (fr) 2012-10-16 2013-10-14 Dispositif de coupe équilibré

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012218853.3A DE102012218853A1 (de) 2012-10-16 2012-10-16 Aufschneidevorrichtung
PCT/EP2013/071397 WO2014060340A1 (fr) 2012-10-16 2013-10-14 Dispositif de découpe

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP20164910.0A Division-Into EP3702118B1 (fr) 2012-10-16 2013-10-14 Dispositif de coupe équilibré
EP20164910.0A Division EP3702118B1 (fr) 2012-10-16 2013-10-14 Dispositif de coupe équilibré

Publications (2)

Publication Number Publication Date
EP2895308A1 true EP2895308A1 (fr) 2015-07-22
EP2895308B1 EP2895308B1 (fr) 2021-01-13

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EP20164910.0A Active EP3702118B1 (fr) 2012-10-16 2013-10-14 Dispositif de coupe équilibré
EP13776798.4A Active EP2895308B1 (fr) 2012-10-16 2013-10-14 Dispositif de découpe

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Application Number Title Priority Date Filing Date
EP20164910.0A Active EP3702118B1 (fr) 2012-10-16 2013-10-14 Dispositif de coupe équilibré

Country Status (5)

Country Link
US (1) US10661466B2 (fr)
EP (2) EP3702118B1 (fr)
DE (1) DE102012218853A1 (fr)
ES (2) ES2862449T3 (fr)
WO (1) WO2014060340A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102014105130A1 (de) * 2014-04-10 2015-10-15 Weber Maschinenbau Gmbh Breidenbach Messer und Messeraufnahme für eine Schneidemaschine
DE102016108346A1 (de) 2016-05-04 2017-11-09 Weber Maschinenbau Gmbh Breidenbach Vorrichtung und verfahren zum aufschneiden von lebensmittelprodukten
IT201800004970A1 (it) * 2018-04-27 2019-10-27 Metodo, impianto e struttura di lama per il taglio di log di carta e simili materiali
CN111873022A (zh) * 2020-06-30 2020-11-03 中山市科多隆自动化设备有限公司 一种蔬果切片机
CN112497311B (zh) * 2020-11-23 2022-04-15 山东欧乐食品有限公司 一种红薯条自动成型切条成型设备
DE102021115267A1 (de) 2021-06-14 2022-12-15 Multivac Sepp Haggenmüller Se & Co. Kg Messer, ggfs. inkl. Schneidkanten-Schutz sowie Verfahren zum Wuchten des Messers
US20230125230A1 (en) 2021-10-25 2023-04-27 Provisur Technologies, Inc. Pivoting loading tray assembly for food product slicing apparatus and method of use

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DE19514407A1 (de) * 1995-04-19 1996-10-24 Biforce Anstalt Vorrichtung zum scheibenförmigen Aufschneiden von Lebensmittelprodukten mittels eines Sichelmessers
DE10030691A1 (de) * 2000-06-23 2002-01-03 Dixie Union Gmbh & Co Kg Schneidvorrichtung insbesondere zum Schneiden von Lebensmitteln
US6974362B2 (en) * 2002-05-14 2005-12-13 Skf Autobalance Systems Ab System and method for automatically compensating for unbalanced resistance forces
DE10333661A1 (de) * 2003-07-23 2005-02-10 Cfs Kempten Gmbh Axial verschiebbares Messer
EP2072197A1 (fr) * 2003-07-23 2009-06-24 CFS Kempten GmbH Trancheuse avec une lame se déplaceant axialement
DE202004013648U1 (de) * 2004-09-01 2004-11-11 Schmidt, Uwe Antrieb eines eine Unwucht erzeugenden Schneidwerkzeugs in Schneidemaschinen, insbesondere in Brotschneidemaschinen
DE102006043697A1 (de) * 2006-09-18 2008-03-27 Weber Maschinenbau Gmbh & Co. Kg Verstelleinheit
US8549966B2 (en) 2007-10-22 2013-10-08 Formax, Inc. Output conveyor for a food article slicing machine
DE102008019776A1 (de) 2008-04-18 2009-10-22 CFS Bühl GmbH Verfahren, Vorrichtung sowie Messer zum Aufschneiden von Lebensmitteln
DE102008020293A1 (de) * 2008-04-22 2009-10-29 Maschinenbau Heinrich Hajek Gmbh & Co. Hochgeschwindigkeitsschneidmaschine mit Halterung eines Sichelmesserrotors
DE102009048056B4 (de) * 2009-10-02 2024-10-02 Weber Food Technology Gmbh Messerkopf mit integrierten Antrieben
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Also Published As

Publication number Publication date
EP2895308B1 (fr) 2021-01-13
EP3702118B1 (fr) 2021-07-28
DE102012218853A1 (de) 2014-04-17
ES2895916T3 (es) 2022-02-23
US20150283721A1 (en) 2015-10-08
ES2862449T3 (es) 2021-10-07
US10661466B2 (en) 2020-05-26
EP3702118A1 (fr) 2020-09-02
WO2014060340A1 (fr) 2014-04-24

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