EP2641696B2 - Werkzeug zum Bearbeiten von Materialien - Google Patents

Werkzeug zum Bearbeiten von Materialien Download PDF

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Publication number
EP2641696B2
EP2641696B2 EP13159094.5A EP13159094A EP2641696B2 EP 2641696 B2 EP2641696 B2 EP 2641696B2 EP 13159094 A EP13159094 A EP 13159094A EP 2641696 B2 EP2641696 B2 EP 2641696B2
Authority
EP
European Patent Office
Prior art keywords
carrier body
apertures
abrasive wheel
inclusively
shell body
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.)
Not-in-force
Application number
EP13159094.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2641696A1 (de
EP2641696B1 (de
Inventor
Michael Schulze
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.)
Dr Mueller Diamantmetall AG
Original Assignee
Dr Mueller Diamantmetall AG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=47877911&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2641696(B2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Dr Mueller Diamantmetall AG filed Critical Dr Mueller Diamantmetall AG
Priority to PL13159094T priority Critical patent/PL2641696T5/pl
Publication of EP2641696A1 publication Critical patent/EP2641696A1/de
Publication of EP2641696B1 publication Critical patent/EP2641696B1/de
Application granted granted Critical
Publication of EP2641696B2 publication Critical patent/EP2641696B2/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24D—TOOLS FOR GRINDING, BUFFING OR SHARPENING
    • B24D5/00—Bonded abrasive wheels, or wheels with inserted abrasive blocks, designed for acting only by their periphery; Bushings or mountings therefor
    • B24D5/10—Bonded abrasive wheels, or wheels with inserted abrasive blocks, designed for acting only by their periphery; Bushings or mountings therefor with cooling provisions, e.g. with radial slots
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24D—TOOLS FOR GRINDING, BUFFING OR SHARPENING
    • B24D5/00—Bonded abrasive wheels, or wheels with inserted abrasive blocks, designed for acting only by their periphery; Bushings or mountings therefor
    • B24D5/16—Bushings; Mountings

Definitions

  • the invention relates to a tool for processing materials, preferably a grinding wheel, with a carrier body, wherein the tool has a hub for receiving a drive shaft.
  • the DE 298 19 006 U shows a tool with a support body, which has receiving slots on the circumference in a partially radial direction, are inserted into the diamond and, for example, held by a metallic coating.
  • the US 4,004,378 and the US 2,089,847 show a grinding wheel, the rotationally symmetrical support body is provided on its peripheral surface with an abrasive coating.
  • the carrier body also has feedthroughs for achieving a substantially parallel to the axis of rotation of the carrier body extending air flow.
  • the vibration damping known carrier body for suppressing vibrations during grinding operation is therefore often in the prior art in the form that the support body of the tool is made of a material which allows slight compression due to its material properties, such as a plastic or elastomer with a high degree of hardness.
  • material inhomogeneities of the solid material forming the carrier body can lead to uneven damping behavior and thus to defects in the processing result.
  • the problem of considerable unwieldiness of grinding wheels with large thicknesses D as used for example in centerless grinding, not overcome.
  • the present invention is therefore based on the object to provide a tool for processing materials of the type mentioned above, which overcomes the disadvantages of the prior art and in particular by ease of handling, especially with large thicknesses D, and improved suppression characterized by vibrations in grinding operation.
  • the tool in question for processing materials in particular a grinding wheel, with respect to a rotation axis substantially cylindrically symmetrical outer geometry, with an inner hub or axle receiving through the center of which the axis of rotation extends centrally, a concentric to this, outer shell body whose Peripheral surface is provided with an abrasive coating, and arranged between the hub and the jacket body support body, which is preferably integral with the hub and / or the jacket body.
  • the jacket body has an averaged outer radius R A and a thickness D which corresponds to the cylinder length of the jacket body and preferably also to the thickness of the carrier body.
  • the carrier body is configured with at least two feedthroughs arranged symmetrically about the axis of rotation within each section plane which extends from the inner region of the carrier body, ie from the edge region of the carrier body lying at the hub, in the direction of the outer edge of the carrier body. So to the jacket body.
  • the ratio A D / A T of the sum of the areas forming the passages A D and the surface A T forming the carrier body material is greater than 1, preferably greater than 2, preferably greater than 3 and preferably greater than 4 , that is, that the areas forming the passages A D in their sum is greater than the area A T forming the material of the carrier body, and preferably significantly larger.
  • the elasticity and the weight of a tool according to the invention are in this case in particular by means of the width, the radial extent and optionally the curvature of the bushings of the carrier body adjustable.
  • the reduced weight of the tools according to the invention also leads to better handling of the tools according to the invention and makes it possible, for example, to simplify the drives of the machines using the tools according to the invention, since the driven masses are significantly reduced and thus the complexity of the drives or drive components can be reduced ,
  • the reduction of the moving masses also allows a simplified vibration damping within the drive train and the tool guides, whether this is active or passive.
  • the carrier body according to the invention can be made of a variety of materials, such as steel, aluminum, copper, bronze or the like, since the vibration is not carried out by the material properties themselves, but by the geometric configuration of the bushings of the carrier body.
  • both a significant weight reduction can be achieved as a targeted vibration damping, especially in metallic support bodies, which have almost no radial elasticity in support bodies of solid material or support bodies with bushings of small geometric dimensions.
  • the tool according to the invention has a geometry which is characterized by a ratio D / R A of thickness D and average outer radius R A of the sheath body between 0.015 inclusive and 2.5 inclusive, preferably by a ratio between 0.03 inclusive and 1 , 6 inclusive, more preferably between 0.05 inclusive and 1 inclusive, and more preferably between 0.08 and 0.8.
  • the thickness D of the tool can also result from the precise assembly of a plurality of tools according to the invention of smaller thickness, so that the composite has a quasi-continuous and one-piece shell surface with a corresponding abrasive coating.
  • the sizes which are most preferably used in the context of the above ratios are thicknesses D between 10 mm inclusive and 600 mm inclusive and radii R A between 75 mm inclusive and 350 mm inclusive.
  • an odd number of feedthroughs are provided for optimizing the vibration behavior, as this, in conjunction with the intended speed, can lead to reduced resonant tooling.
  • the bushings are designed in the form of quadrilaterals in their base area, wherein the long sides are preferably connected in a radially extending manner to the short sides, and the short sides are arranged on the inner or outer region of the carrier body.
  • a straight course of the long sides of the bushings is preferred but not required.
  • a rounded design of the inner corners of the squares is preferred so that sharp-edged inner corners are present at the bushings.
  • At least one of the short sides in the plan view can be at least partially circular-segment-shaped, for example concentric with the outer circumference of the lateral surface.
  • the two long sides of the respective bushing are designed to be of equal length, so that the bushings of the carrier body in this embodiment of the invention appear substantially annular segment-shaped.
  • the quadrangular shape according to the invention also has, in plan view, a substantially delta-shaped configuration in which two corners of the quadrangular shape substantially coincide.
  • This embodiment of the grinding tool according to the invention is referred to as a spoke segment disc, in particular when a plurality of passages are provided, for example 12, since the material remaining between the passages is spoke-like, the spokes preferably having a thickness in the direction of the axis of rotation which is substantially the entire material thickness of the carrier body, and the corresponding, preferably also have the jacket body.
  • a spoke segment disc in particular when a plurality of passages are provided, for example 12, since the material remaining between the passages is spoke-like, the spokes preferably having a thickness in the direction of the axis of rotation which is substantially the entire material thickness of the carrier body, and the corresponding, preferably also have the jacket body.
  • the quadrangular bushings are distorted or bent around a point located outside the respective bushing, so that the long sides of the bushings in plan view are substantially arcuate or preferably circular segment-shaped.
  • the resulting from the remaining between adjacent passages material of this embodiment of the invention spokes are thus arcuately curved and preferably circularly curved and extend in the interior of the carrier body, ie substantially from the hub or axle initially substantially radially outward, then, by the curvature of which is a kind of asymptotic approach towards the periphery of the tool.
  • the degree or extent of the approach of the spokes to the circumference of the tool is different selectable and, as it were, an essential parameter for the radial elasticity of the tool.
  • the long sides of adjacent bushings are substantially parallel, and this applies equally to substantially radially extending long sides of the bushings as well as curved or even circular segment running. Nevertheless, for example, those embodiments are preferred within the scope of the invention, in which a tapering of the spokes is carried out towards the outer region of the carrier body by a non-parallel course of the long sides of passages, whereby further influencing the radial elasticity and the weight of the tools according to the invention this Embodiment can be achieved.
  • the longer of the short sides is arranged in the outer region of the carrier body, that is arranged close to or even adjacent to the jacket body and the shorter of the short sides in the inner region of the carrier body, ie near the hub or axle fitting or adjacent thereto.
  • the bushings of the carrier body from its opposite cylindrical top surfaces are incorporated substantially up to its center in the material of the carrier body, for example by milling. It is particularly advantageous, the bushings, which are incorporated from the second side, so for example, the upper cylinder top surface of the carrier body ago by a predetermined rotation angle ⁇ about the axis of rotation rotates with respect to those of the first side of the carrier body, so for example the lower cylinder top surface will be incorporated to rotate. As a result, the spokes between adjacent feedthroughs of one side of the carrier body are thus substantially not congruent with the spokes between adjacent feedthroughs of the other side of the carrier body.
  • the carrier and / or sheath body at least one, as needed, several balancing bores.
  • embodiments of the invention are also provided in which the thickness of the carrier body (in the direction of the axis of rotation) is smaller, that is, the thickness D of the jacket body, so that the carrier body so arranged in relation to the shell body or the cylinder top surfaces defined by this receding is.
  • the abrasive coating is applied by gluing or sintering or similar known methods on the outer peripheral surface of the sheath body and preferably selected from a group of diamond needles such as PCD, MKD, CVD, CBN needles, metal, plastic or ceramic bonded Diamonds, metal or plastic bonded boron nitride, in particular cubic boron nitride.
  • a group of diamond needles such as PCD, MKD, CVD, CBN needles, metal, plastic or ceramic bonded Diamonds, metal or plastic bonded boron nitride, in particular cubic boron nitride.
  • the Fig. 1 to 5 show grinding wheels according to the present invention.
  • the grinding wheel according to Fig. 1 has a centrally arranged hub or receptacle A for a - not shown - shaft of a machine tool, a sheath body 4 and arranged on the outer circumference of the sheath body 4 abrasive coating B with preferred thicknesses between 2mm and 30mm.
  • a support body 1 is arranged, this being made in one piece with the receptacle and the sheath body of a light metal, such as aluminum.
  • the sheath body and preferably also the carrier body have a thickness D and the grinding wheel is substantially cylindrically symmetrical with respect to the axis of rotation R, with the exception of the feedthroughs 2 arranged inside the carrier body 1.
  • the outer radius of the grinding wheel is R A.
  • the carrier body 1 has a plurality of feedthroughs 2, wherein the feedthroughs 2 extend from the inner region 1 'of the carrier body, namely from the region of the receptacle A, in the direction of the outer region 1 "of the carrier body 1, and which are embodied in the manner of a ring segment with long sides 2 ', which are substantially radial and are of equal length, and short sides 2 ", which extend substantially concentrically with respect to the axis of rotation R, whereby here also a rectilinear design of the short sides 2" comes into consideration
  • Material regions remaining between adjacent feedthroughs 2 are designed in the manner of spokes 3, which in the present case extend radially and whose thickness increases towards the outside due to the radial course of the long sides 2.
  • a balancing bore W can be seen in the outer region of the casing body.
  • a total of 10 bushings are provided here, which are arranged uniformly around the axis of rotation in the carrier body 1.
  • FIG. 2 and 3 shown second embodiment is derived from the embodiment of Fig. 1 from, in which case the bushings 2 coming from the two cylinder top surfaces of the grinding wheel coming forth are introduced up to half the thickness of the carrier body 1. Accordingly, it can be seen that the spokes 3 of the material regions of the carrier body 1 which have remained standing between adjacent feedthroughs 2 on the side of the observer Fig. 2 (Front) are formed, whereas the spokes 3 'of the remaining between adjacent passages 2 material areas of the support body 1 on the opposite side of the viewer Fig. 2 (so to speak, the back) are formed. Further, the bushings 2 of the front to the bushings 2 of the back are rotated by an angle ⁇ of 19 ° to each other.
  • Fig. 4 and 5 shown third embodiment of the present invention have the same reference numerals as in Fig. 1 Structurally and functionally similar elements, so that reference is made to the above.
  • the bushings 2 are distorted around a point located outside the respective bushing 2, so that the long sides 2 'in this embodiment are circular-segment-shaped and also have the same radius, which but not required.
  • the long sides 2 'of the bushings 2 can be designed such that the thickness of the spokes 3 between two adjacent bushings 2 extends substantially uniformly from the inner region 1' of the carrier body to its outer region 1 ''.
  • the short sides 2 are connected by radii with the long sides 2 ', wherein here a maximum extent up to the shell body 4 is exploited.
  • the long side 2' are designed so that these, if they are on the shell body However, this is likewise not necessary and, depending on the application and the radial elasticity to be generated, an asymptotic approach to the inner edge of the sheath body may also be made or at a shallow angle thereto tapered shape are preferred, as can be seen in Fig. 4 the case is.
  • the long sides 2 ' also extend substantially radially away from the inner region 1' of the carrier body 1 or the receptacle A, so that the spokes 3 also have such a shape, that is to say initially radially away from the receptacle A. extend to the outside then following the curvature at a shallow angle in the outer region 1 "of the carrier body to be substantially alslieaufen on the jacket body.
  • Fig. 5 shows that the present invention is particularly suitable for use in conjunction with tools of large thicknesses D, since on the one hand the considerable Reducing the weight leads to a simplified handling and equally causes the caused by the particular embodiment of the tools according to the invention radial elasticity leads to a significantly improved vibration behavior.
  • Fig. 5 also shows that the carrier body is slightly offset with respect to the sheath body, which results from a reduced in the direction of the rotation axis R material thickness of the carrier body compared to the thickness D of the sheath body.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Polishing Bodies And Polishing Tools (AREA)
EP13159094.5A 2012-03-13 2013-03-13 Werkzeug zum Bearbeiten von Materialien Not-in-force EP2641696B2 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL13159094T PL2641696T5 (pl) 2012-03-13 2013-03-13 Narzędzie do obróbki materiałów

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012005085A DE102012005085A1 (de) 2012-03-13 2012-03-13 Werkzeug zum Bearbeiten von Materialien

Publications (3)

Publication Number Publication Date
EP2641696A1 EP2641696A1 (de) 2013-09-25
EP2641696B1 EP2641696B1 (de) 2014-04-30
EP2641696B2 true EP2641696B2 (de) 2017-09-06

Family

ID=47877911

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13159094.5A Not-in-force EP2641696B2 (de) 2012-03-13 2013-03-13 Werkzeug zum Bearbeiten von Materialien

Country Status (3)

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EP (1) EP2641696B2 (pl)
DE (1) DE102012005085A1 (pl)
PL (1) PL2641696T5 (pl)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013105616A1 (de) 2013-05-31 2014-12-04 Dr. Müller Diamantmetall AG Werkzeug zum Bearbeiten von Materialien
DE102014103719A1 (de) * 2014-03-19 2015-09-24 Dr. Müller Diamantmetall AG Schälschleifwerkzeug
HUE043739T2 (hu) 2014-10-15 2019-09-30 Vk Invest Gmbh Gépi megmunkáló szerszám és eljárás szerszám elõállítására
DE102015122233A1 (de) * 2015-12-18 2017-06-22 Thyssenkrupp Ag Massereduzierter Schleif-Grundkörper
AT518908B1 (de) 2016-08-11 2019-04-15 Tyrolit Schleifmittelwerke Swarovski Kg Trägerkörper für Schleifwerkzeuge

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US579414A (en) † 1897-03-23 Grinding-wheel
US2089847A (en) † 1936-06-20 1937-08-10 Lancaster Machine Knife Works Grinding wheel
DE2717935A1 (de) † 1977-04-22 1978-10-26 Koenig J Gmbh & Co Werkzeugfab Kreissaegeblatt mit aussparungen zum spannungsausgleich
US4252481A (en) † 1979-06-21 1981-02-24 Widder Corporation Cutting tool
DE4243480A1 (de) † 1992-12-22 1994-06-23 Sanshu Press Kogyo Kk Trockensägeblatt
WO1999054089A1 (de) † 1998-04-21 1999-10-28 Tyrolit Schleifmittelwerke Swarovski Kg Schleifscheibe
EP1174207B1 (de) † 2000-07-20 2006-10-25 Wolfgang Reul Trennscheibe mit Trägheitsausnehmungen
DE102005034258A1 (de) † 2005-07-18 2007-01-25 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Rotationskörper und Zentriervorrichtung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4004378A (en) * 1975-07-18 1977-01-25 Engelhard Minerals & Chemicals Corporation Grinding wheel with integral blower
AT410912B (de) 2002-02-18 2003-08-25 Swarovski Tyrolit Schleif Abrichtrolle für schleifscheiben
FR2657280B1 (fr) * 1990-01-19 1994-05-27 Demurger & Cie Ets Outil de coupe circulaire et rotatif composite.
DE10033101A1 (de) * 2000-07-07 2002-01-17 Hilti Ag Scheibenförmiges Trennwerkzeug
US20030029296A1 (en) * 2001-08-13 2003-02-13 Luigi Donazzan Sound dampened ceramic clad diamond saw blade

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US579414A (en) † 1897-03-23 Grinding-wheel
US2089847A (en) † 1936-06-20 1937-08-10 Lancaster Machine Knife Works Grinding wheel
DE2717935A1 (de) † 1977-04-22 1978-10-26 Koenig J Gmbh & Co Werkzeugfab Kreissaegeblatt mit aussparungen zum spannungsausgleich
US4252481A (en) † 1979-06-21 1981-02-24 Widder Corporation Cutting tool
DE4243480A1 (de) † 1992-12-22 1994-06-23 Sanshu Press Kogyo Kk Trockensägeblatt
WO1999054089A1 (de) † 1998-04-21 1999-10-28 Tyrolit Schleifmittelwerke Swarovski Kg Schleifscheibe
EP1174207B1 (de) † 2000-07-20 2006-10-25 Wolfgang Reul Trennscheibe mit Trägheitsausnehmungen
DE102005034258A1 (de) † 2005-07-18 2007-01-25 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Rotationskörper und Zentriervorrichtung

Also Published As

Publication number Publication date
EP2641696A1 (de) 2013-09-25
EP2641696B1 (de) 2014-04-30
PL2641696T3 (pl) 2014-10-31
PL2641696T5 (pl) 2018-05-30
DE102012005085A1 (de) 2013-09-19

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