EP0211423B1 - Outil rotatif en forme de disque - Google Patents

Outil rotatif en forme de disque Download PDF

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Publication number
EP0211423B1
EP0211423B1 EP86110691A EP86110691A EP0211423B1 EP 0211423 B1 EP0211423 B1 EP 0211423B1 EP 86110691 A EP86110691 A EP 86110691A EP 86110691 A EP86110691 A EP 86110691A EP 0211423 B1 EP0211423 B1 EP 0211423B1
Authority
EP
European Patent Office
Prior art keywords
tool according
tool
segments
pressurising
width
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.)
Expired - Lifetime
Application number
EP86110691A
Other languages
German (de)
English (en)
Other versions
EP0211423A2 (fr
EP0211423A3 (en
Inventor
Berthold Fries
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.)
Individual
Original Assignee
Individual
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
Priority claimed from DE19853542364 external-priority patent/DE3542364A1/de
Priority claimed from DE19858534533 external-priority patent/DE8534533U1/de
Application filed by Individual filed Critical Individual
Priority to AT86110691T priority Critical patent/ATE59799T1/de
Publication of EP0211423A2 publication Critical patent/EP0211423A2/fr
Publication of EP0211423A3 publication Critical patent/EP0211423A3/de
Application granted granted Critical
Publication of EP0211423B1 publication Critical patent/EP0211423B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D61/00—Tools for sawing machines or sawing devices; Clamping devices for these tools
    • B23D61/02—Circular saw blades
    • B23D61/025—Details of saw blade body
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B27—WORKING OR PRESERVING WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES IN GENERAL
    • B27B—SAWS FOR WOOD OR SIMILAR MATERIAL; COMPONENTS OR ACCESSORIES THEREFOR
    • B27B1/00—Methods for subdividing trunks or logs essentially involving sawing

Definitions

  • the invention relates to a disk-shaped, rotating tool according to the preamble of claim 1; see e.g. BE-A 26 25995.
  • Expansion slots or corresponding fields and spoke-like, segment-defining shapes can reduce the plane blade plane deformations to a limited extent by the use of tension compensation options, but they solve them also at the same time the internal stress mode and they lead to poor center fixation due to general instabilities or they are fundamentally not a means to bring about the always desirable and so important tensile stresses in the outer rim area.
  • Flangeless drives through a type of spline shaft and without conventional flanges that take over the axial fixation, also have the disadvantage that the classic mode of operation of internal stresses is disturbed.
  • the periphery is stabilized by guides with the aim of leveling out the vibrations in the loose, flangeless center.
  • the guides cause additional peripheral heating and thus lead to all the known disadvantages.
  • a number of guide arrangements attempt to dampen vibrations, in general the flangeless technology is considered to be a system with relatively high inaccuracies in work.
  • Re f) and g) A number of composite designs are known, but in which no systems for permanent and permanent external ring tensile stresses are integrated. Only the composite construction is aimed at a more favorable vibration behavior. This is certainly advantageous, but there are no means that influence vibration behavior more positively than targeted tensile stresses in the periphery.
  • Re h It is known that the internal tension (e.g. by rolling, hammering) cannot be reproduced in operation.
  • the so-called thermal stress method wants to solve this disadvantage by the temperature differences between the periphery and the center being determined by measuring devices and, from this, the interior being heated up by a heat coil.
  • the thermal expansions lead to a certain pressure to the outside, but they cannot be defined in the necessary manner (depending on the rotation data and the size of the heat zone actually achieved) and the heat coil effect also leads to the dissolution of the constantly necessary center fixation.
  • the invention has for its object to design a tool so that the expansion and deformation resulting from temperature differences and centrifugal forces do not lead to any disadvantages, that tensile stresses prevail in the peripheral area and that a good vibration behavior means that smooth working procedures with thin disks and long service lives are to be practiced and this can ultimately also be carried out with lower tool costs and energy savings, without assemblies in the sheet-disk plane stressing the tool shapes.
  • a pressure transducer is thus arranged in the central opening, which acts on the individual segments (spokes) of the tool with a controllable pressure force.
  • the tool advantageously has a closed outer rim on which, for example, the teeth for a saw blade can be placed.
  • the recesses are arranged in the tool, which divide the blade level into individual segments up to a certain rim area, similar to a spoked wheel.
  • the tool can be axially fixed on the drive shaft in a known manner by means of flanges be.
  • a disk-shaped tool according to the invention consists of an outer ring, on which a plurality of segments are arranged, which are connected to one another only by the outer ring. This creates a loose, fan-shaped center, with the stiffness of the disc only being restored by the pressure transducer.
  • the pressure transmitter In addition to the rotary drive and the radial pressure force, the pressure transmitter also has the task of axially and centrally fixing the rotating tool.
  • the pressure force can be applied to the individual segments / spokes via strips, bolts or pistons which are acted upon by spring action or hydraulic or pneumatic systems.
  • a differentiated application of the individual segments with different compressive forces is always necessary when the tool is subject to high shape irregularities.
  • a pressure transducer is sufficient that makes a uniform stroke change and thus stroke-dependent pressurization over 360 °.
  • the application of the compressive force to the individual sheet / disc segments does not necessarily have to be carried out with individual pistons and guide elements, but, since the expansion and necessary lifting movements are relatively small, can also be carried out by elastic material deformations within the compressive force design.
  • the solution according to the invention can be used in all areas in which disk-shaped tools - primarily high-speed running and with large diameters - are used.
  • the solution according to the invention and the pressure force effect also leads to the sawing in wood saws that the disk-shaped tools do not usually have to be shaped in their blade thickness below the kerf width, but can have an extreme strength dimensioning of a carrier part receiving the working collar.
  • the extremely strong design of the support structure with the conical contours, from what An overall tool thickness that exceeds the kerf width several times results in loads, particularly through side pressures and temperature influences, which would result in a complete loss of function after a few minutes (seconds) with any conventional circular saw blade - and without a pressure transducer.
  • the circular saw blade 1 and 2 show a circular saw blade 1 with a closed outer ring 2, on which the saw teeth 3 are molded or attached. Segments 4 are connected to the ring gear 2, which are separated from one another by cutouts 5 and which open into the central opening 6.
  • the circular saw blade 1 thus consists of a closed ring gear, on which segments in the form of spokes are arranged, which end in the central center 6 without being connected to one another.
  • the segment 7 is rectangular in side view formed, while the segment 8 has its greatest width in the central center 6, as a modification, while it then tapers continuously towards the ring gear 2.
  • the two segments 9 shown are separated from one another by cutouts 5, which initially run essentially radially and then bend tangentially, so that the connecting surface of the segment 9 on the outer rim 2 is designed to be relatively small, so that the latter is not significantly impeded by the web 9 can expand according to the warming.
  • the segment 10 is likewise delimited by cutouts 5, which initially run approximately radially and are then tangentially angled in the same direction, so that here again a small connection width is obtained on the outer ring 2.
  • a saw blade 1 is shown, in which the segments 4 are formed uniformly.
  • a pressure force generator 11 is arranged in the central opening 6 and is provided with displaceable pistons 12 which press on the end faces 13 of the segments 4.
  • the compressive force for displacing the pistons 12 can be generated either by spring assemblies or by hydraulic or pneumatic systems.
  • the circular saw blade 1 is held laterally on the drive shaft 14, not shown, by means of a flange 15 in a known manner.
  • the pressure transducer and flange can be designed separately. However, the pressure transducer is advantageously integrated into the flange 15.
  • the circular saw blade 1 can be due to the constantly existing Preload, which is maintained even when the periphery of the circular saw blade 1 is strongly heated, is made substantially thinner in cross section than has been the case up to now.
  • the outer ring 2, which carries the saw teeth 3, is advantageously made thinner than the segments 4, which considerably facilitates the flow of the chips to be discharged.
  • the application of pressure to the individual pistons 12 of the pressure transducers, which act on the segments 4 of the circular saw blade 1, permits an independent lifting movement. In the case of circular saw blades in which no local warping is to be feared, the same lifting movement can also act on all segments, which significantly reduces the manufacturing effort of the pressure force generator.
  • material expansions can also be used to apply the compressive force, since the changes in length that have to be compensated for by the compressive force are only in the range of a few tenths of a millimeter.
  • support or round guide-like slides or guide surfaces can be provided in the pressure force generator.
  • the force exerted on each spoke 7 or segment 8 by the pressure force transducer 11 in the exactly radial direction leads to a lifting movement which is carried out in accordance with the division and without tension, in that the expansion region 23 leading to the lifting movement is arranged under the spoke / segmentation center 24.
  • the lifting movement, the outward stretching, is carried out without changing the central fixation.
  • the center seat through the hub part 25 is retained.
  • the 11 shows, as an example, the side view of one of many possible forms of pressure transducers (with the 11 division shown - piston pin only drawn 1 ⁇ ).
  • the radial force exerted by the piston 12 executes the necessary stroke movement (H) by elastic deformation of the blade receiving parts 26, the strength of the pressure force generator 11 being shaped and dimensioned differently.
  • the sheet receiving parts 26 show fastening holes 27 for receiving the segments 4.
  • Piston bolts 28 are screwed in, which axially stabilize the blade receiving part 26, which has been released, for example by wire erosion 30, and at the same time exert a spreading force (H) through oil supply (bore channel system in the inner housing) due to penetration into the inner housing 29 of the pressure force generator 11.
  • the task of a pressure transducer 11 lies in the conversion of the rotational energy (E d ), in the extensibility (D p ), which is adapted to the division of the blade in accordance with the division, and in the center fixation achieved in a positive manner in the example via the inner housing extension 31.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Wood Science & Technology (AREA)
  • Forests & Forestry (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Polishing Bodies And Polishing Tools (AREA)

Claims (18)

1. Outil rotatif en forme de disque (1) avec des dents (3), des couteaux ou des parties abrasives disposées à sa périphérie, et une ouverture centrale (6) destinée à recevoir un arbre d'entraînement, et avec, dans le plan de la lame, des évidements qui définissent plusieurs segments (rayons) (4) dans l'outil (1), caractérisé en ce qu'un organe presseur (11) est disposé dans l'ouverture centrale, et chaque segment (4) peut être sollicité par une pression réglable, par l'intermédiaire de cet organe presseur.
2. Outil selon la revendication 1, caractérisé en ce que l'outil présente une couronne extérieure fermée, à laquelle se raccordent les segments (4), et en ce que ces derniers se terminent dans l'ouverture centrale et délimitent celle-ci.
3. Outil selon la revendication 1 ou 2, caractérisé en ce que la largeur de la surface de raccordement du segment (4) à la couronne extérieure (2) est plus petite que la largeur maximale du segment (4), ou au plus égale à celle-ci.
4. Outil selon l'une des revendications 1 à 3, caractérisé en ce que les évidements (5), à partir de l'ouverture centrale, s'étendent d'abord essentiellement dans le sens radial, et ensuite se courbent dans une direction essentiellement tangentielle.
5. Outil selon l'une des revendications 1 à 4, caractérisé en ce que les forces de pression sont transmises aux segments (4) au moyen de ressorts.
6. Outil selon l'une des revendications 1 à 5, caractérisé en ce que les forces de pression sont transmises aux segments (4) au moyen de systèmes hydrauliques ou pneumatiques.
7. Outil selon l'une des revendications 1 à 6, caractérisé en ce que les forces de pression centrales agissant sur les segments (4) sont réglables individuellement.
8. Outil selon l'une des revendications 1 à 7, caractérisé en ce que l'organe presseur (11) immobilise les segments (4) dans les directions radiale, tangentielle et axiale, et transmet le couple de rotation de l'arbre à l'outil (1).
9. Outil selon l'une des revendications 1 à 8, caractérisé en ce que la sollicitation des segments par l'organe presseur (11) dépend de l'échauffement et de la déformation de l'outil (1).
10. Outil selon l'une des revendications 1 à 9, caractérisé en ce que la section de l'outil (1) est plus mince sous les couteaux (S2) que dans le reste du plan (S1) de la lame.
11. Outil selon l'une des revendications 1 à 10, caractérisé en ce que la largeur de la zone amincie (B1) est environ trois fois la hauteur des dents (B2).
12. Outil selon l'une des revendications 1 à 11, caractérisé en ce que la pression radiale est transmise par une expansion d'un boîtier auquel sont attachés les segments.
13. Outil selon l'une des revendications 1 à 12, caractérisé en ce que l'organe presseur comprend des coulisseaux ou des surfaces de guidage en forme de support ou d'organes agissant en toutes directions.
14. Outil selon l'une des revendications 1 à 13, caractérisé en ce qu'il comporte une structure porteuse en cône obtus, qui se relie au autre à l'organe presseur (11) et vers l'extérieur à la couronne, les épaisseurs (20, 21) de la structure porteuse étant plus grandes que celle (22) des dents.
15. Outil selon l'une des revendications 1 à 14, caractérisé en ce que la forme des segments-rayons (7, 8) et/ou la structure porteuse (4) sollicitée par l'organe presseur et la couronne extérieure (2), y compris les dents (3) présentent des nombres et des largeurs-­épaisseurs-longueurs différentes.
16. Outil selon l'une des revendications 1 à 15, caractérisé en ce que les formes coniques (19) se trouvent sur une ou deux faces.
17. Outil selon l'une des revendications 1 à 16, caractérisé en ce que les phénomènes (17) d'écartement d'une pièce ou d'une planche repoussée par les formes coniques (19) sont contenus par une table de guidage pourvu de coins.
18. Outil selon l'une des revendications 1 à 17, caractérisé en ce qu'il travaille aussi bien en coupe supérieure qu'en coupe inférieure, en rotation à sens concordants qu'en rotation à sens opposés.
EP86110691A 1985-08-09 1986-08-01 Outil rotatif en forme de disque Expired - Lifetime EP0211423B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86110691T ATE59799T1 (de) 1985-08-09 1986-08-01 Scheibenfoermiges, rotierendes werkzeug.

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE3528639 1985-08-09
DE3528639 1985-08-09
DE3542364 1985-11-30
DE19853542364 DE3542364A1 (de) 1985-08-09 1985-11-30 Schnittwerkzeug, insbesondere kreissaegeblatt
DE19858534533 DE8534533U1 (de) 1985-12-07 1985-12-07 Kreissäge mit Minimalschnittfuge
DE8534533U 1985-12-07

Publications (3)

Publication Number Publication Date
EP0211423A2 EP0211423A2 (fr) 1987-02-25
EP0211423A3 EP0211423A3 (en) 1988-04-27
EP0211423B1 true EP0211423B1 (fr) 1991-01-09

Family

ID=27193377

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86110691A Expired - Lifetime EP0211423B1 (fr) 1985-08-09 1986-08-01 Outil rotatif en forme de disque

Country Status (2)

Country Link
EP (1) EP0211423B1 (fr)
DE (1) DE3676754D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4328482A1 (de) * 1993-08-24 1995-03-02 Fgw Forsch Werkzeuge Werkstoff Kreissägeblatt

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3804400A1 (de) * 1988-02-12 1989-08-24 Fritz Seeber Vorrichtung zum erzeugen einer mehrzahl von parallelen schnittfugen
DK4790A (da) * 1989-01-13 1990-07-14 Michael J Pappas Kirurgisk sav
JP2002292519A (ja) * 2001-03-30 2002-10-08 Kanefusa Corp 丸鋸およびその主軸取付け方法
PL1872918T3 (pl) * 2006-06-30 2009-05-29 Nordpan Rubner Holzbauelemente Gmbh Cięcie desek z drewna za pomocą piły tarczowej

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1262737B (de) * 1961-07-31 1968-03-07 Ingersoll Milling Machine Co Spanndorn
DE2625995A1 (de) * 1976-06-10 1977-12-22 Wurster & Dietz Maschinenfabri Kreissaegeblatt
DE2654625A1 (de) * 1976-12-02 1978-06-08 Jansen Fa R Kreis- bzw. spiralsaegeblatt
DE2717935A1 (de) * 1977-04-22 1978-10-26 Koenig J Gmbh & Co Werkzeugfab Kreissaegeblatt mit aussparungen zum spannungsausgleich
FI771847A (fi) * 1977-06-13 1978-12-14 Ahlstroem Oy Saogmaskin
DE3232778A1 (de) * 1982-09-03 1984-03-08 Fa. Röttger Jansen-Herfeld, 5630 Remscheid Spannungsausgleichsschlitze
DE8534533U1 (de) * 1985-12-07 1986-03-13 Fries, Berthold, 5920 Bad Berleburg Kreissäge mit Minimalschnittfuge
DE8533710U1 (de) * 1985-11-30 1986-03-06 Fries, Berthold, 5920 Bad Berleburg Schnittwerkzeug, insbesondere Kreissägeblatt

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4328482A1 (de) * 1993-08-24 1995-03-02 Fgw Forsch Werkzeuge Werkstoff Kreissägeblatt
DE4328482C2 (de) * 1993-08-24 1998-01-29 Fgw Forsch Werkzeuge Werkstoff Kreissägeblatt

Also Published As

Publication number Publication date
DE3676754D1 (de) 1991-02-14
EP0211423A2 (fr) 1987-02-25
EP0211423A3 (en) 1988-04-27

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