EP0381809A2 - Quick clamping device for disc-like working-tools for electric tools - Google Patents

Quick clamping device for disc-like working-tools for electric tools Download PDF

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Publication number
EP0381809A2
EP0381809A2 EP89113940A EP89113940A EP0381809A2 EP 0381809 A2 EP0381809 A2 EP 0381809A2 EP 89113940 A EP89113940 A EP 89113940A EP 89113940 A EP89113940 A EP 89113940A EP 0381809 A2 EP0381809 A2 EP 0381809A2
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EP
European Patent Office
Prior art keywords
clamping
flange
adjusting ring
nut
quick
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.)
Ceased
Application number
EP89113940A
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German (de)
French (fr)
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EP0381809A3 (en
Inventor
Musa Göcmez
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Licentia Patent Verwaltungs GmbH
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Licentia Patent Verwaltungs GmbH
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Publication of EP0381809A2 publication Critical patent/EP0381809A2/en
Publication of EP0381809A3 publication Critical patent/EP0381809A3/en
Ceased legal-status Critical Current

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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B24GRINDING; POLISHING
    • B24BMACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B45/00Means for securing grinding wheels on rotary arbors
    • B24B45/006Quick mount and release means for disc-like wheels, e.g. on power tools

Definitions

  • the invention relates to a quick release device according to the preamble of claim 1.
  • EP 02 31 500 A2 discloses a device for the releasable fastening of a disk-shaped tool, in which the clamping flange resting on the tool can be relieved of the clamping pressure for the tool by the fact that support means designed as rolling bodies and introduced into a space between the work spindle and the clamping flange transversely are arbitrarily movable to a support direction in an escape space.
  • Support means designed as rolling bodies and movable into an alternative space lead axially to a relatively large overall height of the part of the device which projects beyond the plane of the machining tool.
  • the invention has for its object to provide a quick release device of the generic type with a comparatively low axial height in order to achieve the smallest possible angle between the plane of the disk-shaped machining tools and the imaginary connecting line from the periphery of the machining tools to the lower edge of the quick clamping device.
  • the smallest possible angle is e.g. important for angle grinders.
  • the quick-action clamping device essentially consists of a clamping nut 10, an adjusting ring 11, a clamping flange 12, two locking elements 13, four return and centering springs 14, two balls 15 for absorbing radial forces and three O-rings 16 , 17 and 18.
  • the number of locking elements 13 and springs 14 depends on the particular case.
  • Both the clamping nut 10 and the clamping flange 12 are provided with a number of jumps 19, 20, of which a suitable number is arranged distributed over the circumference.
  • the jumps or wedge-like elevations 19, 20 lie on the mutually assigned surfaces of the clamping nut 10 and the clamping flange 12 and correspond to one another (see also FIG. 3).
  • the adjusting ring 11 On the inner circumference of the adjusting ring 11 there are radially inwardly extending barriers 21, on each of which one end of a spring 14 of a pair of springs is supported. The other end of the spring comes to bear on a ball 15. The end of the second spring 14 engages on the surface of this ball 15 opposite this contact side, the other end of which is supported on the stop surface 23 obtained by a recess 22 in the clamping nut 10.
  • the adjusting ring 11 Offset in relation to each barrier 21 in the circumferential direction, the adjusting ring 11 has a nose-shaped or similarly shaped projection 24, which cooperates with a locking element 13, which has a pin 26 rotatably mounted in a bore 25 in the clamping nut 10 and in this area to a matching recess in the clamping nut adjoins.
  • the two locking elements 13 provided in the exemplary embodiment lie opposite one another and are designed as small cam disks which each act in their area facing away from the pin 26 on the clamping flange 12 provided with
  • the two locking elements 13 are in the position as is illustrated in the right half of FIG. 3 for the one locking element, they prevent a relative movement between the clamping flange 12 and the clamping nut 10 and thus also between the jumps 19 and 20.
  • the Loading of the clamping flange 12 with the clamping pressure for the tool 28 is thus ensured and is maintained by the action of the spring 14.
  • This clamping position is illustrated in the right half of FIG. 2 by the clamping flange 12 lying directly against the tool 28.
  • the clamping flange 12 can now perform a relative movement to the clamping nut 10, and due to the effective axial preload, the jumps 20 of the clamping flange 12 slide down on the jumps 19 of the clamping nut, so that the clamping flange 12 moves from the clamping plane of the tool 28 against the clamping nut 10 moved down. Clamping flange 12 and clamping nut 10 are thus fully relieved of the clamping pressure for the tool, so that the latter can easily be released by hand from the threaded pin 29 of the output spindle 30 of the angle grinder.
  • the counter flange is designated 31.
  • the space between the surface of the clamping flange 12 and the opposite surface of the tool 28, which is created during the loosening process, is designated LS in the left half of FIG.
  • the right-hand half of FIG. 2 shows the clamping state.
  • the plane of the clamping flange 12 facing away from the tool 28 and the plane of the clamping nut 10 opposite this plane have a distance VS caused by the relative position of the jumps 19 and 20.
  • the locking elements 13 ' are approximately club-shaped.
  • the end face 32 of the locking elements 13 ' is each supported on a flank 33 of the clamping nut 10.
  • the clearance angle designated ⁇ in FIG. 7 between the two surfaces 32, 33 of the clamping nut 10 and the locking element 13 'coming into contact with one another is chosen in such a way that favorable friction conditions result, for example: ⁇ min ⁇ Ag ⁇ . If necessary, the use of ceramic materials with a low friction factor can reduce the friction.
  • the clearance angle ⁇ can be, for example, in the order of magnitude between 12 ° and 16 °, for locking elements made of ceramic, for example, 8 ° -12 °.
  • the locking elements 13 'can - but need not - be rotatably centered here by means of pins 25 in bores of the clamping flange 12 and the formation of the jumps 19 on the clamping nut 10 and the jumps 20 on the opposite surface of the clamping flange 12 corresponds to that after the first Embodiment explained The same applies to the arrangement and number of ski jumps 19 and 20, with various possibilities in this regard.
  • a total of two return springs 14 ' are provided.
  • one of the two return springs 14 ' is tensioned in the unloaded state of the clamping flange 12 (see right side of FIG. 5) and the locking element 13' comes as a result of the forces acting after the manual rotation of the adjusting ring 11 into the release position while being overcome the friction up to the stop on the inner surface of the collar 11 to the outside.
  • the exemplary embodiment according to FIGS. 4 to 7 has the advantage that standard counter flanges 31 can be used. It has proven to be expedient to provide the clamping nut 10 and the clamping flange 12 with three jumps (wedges) 19 and 20, respectively, which are offset by 120 ° to one another. Basically the number of jumps (wedges) depends on the respective requirements.
  • the number of ski jumps 19 and 20 is six in each of the two exemplary embodiments (FIGS. 1 to 6).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jigs For Machine Tools (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
  • Clamps And Clips (AREA)

Abstract

In known quick-clamping devices for the said purpose, the clamping flange bearing against the working tool is relieved of the clamping pressure for the tool owing to the fact that supporting means designed as roller bodies can be moved at will in an escape space. The novel quick-clamping device is to permit a lower overall height while avoiding rolling supporting means which can be moved into an escape space. The clamping pressure is applied by breast pieces (19, 20) which are attached to the clamping nut (10) and the clamping flange (12), correspond with one another and are prevented from moving relative to one another by means of at least one locking element (13, 13') on which the adjusting ring (11), which is under the effect of a restoring force, acts. Movement of the clamping flange (12) relative to the clamping nut (10), which movement results in the clamping flange (12) being relieved of the clamping pressure for the working tool (28), is obtained by releasing the locking element (13, 13') by means of the adjusting ring (11). <IMAGE>

Description

Die Erfindung bezieht sich auf eine Schnellspanneinrichtung ge­mäß dem Oberbegriff des Anspruchs 1.The invention relates to a quick release device according to the preamble of claim 1.

Durch die EP 02 31 500 A2 ist eine Vorrichtung zum lösbaren Be­festigen eines scheibenförmigen Werkzeugs bekannt, bei der am Werkzeug anliegende Spannflansch dadurch vom Einspanndruck für das Werkzeug entlastbar ist, daß als Rollkörper ausgebildete, in einen Raum zwischen der Arbeitsspindel und dem Spannflansch ein­gebrachte Stützmittel quer zu einer Stützrichtung willkürlich in einen Ausweichraum bewegbar sind.EP 02 31 500 A2 discloses a device for the releasable fastening of a disk-shaped tool, in which the clamping flange resting on the tool can be relieved of the clamping pressure for the tool by the fact that support means designed as rolling bodies and introduced into a space between the work spindle and the clamping flange transversely are arbitrarily movable to a support direction in an escape space.

Als Rollkörper ausgebildete und in einen Ausweichraum bewegbare Stützmittel führen axial gesehen zu einer relativ großen Bau­höhe des über die Ebene des Bearbeitungswerkzeugs überstehenden Teils der Vorrichtung.Support means designed as rolling bodies and movable into an alternative space lead axially to a relatively large overall height of the part of the device which projects beyond the plane of the machining tool.

Der Erfindung liegt die Aufgabe zugrunde, eine Schnellspannein­richtung der gattungsgemäßen Art mit vergleichsweise geringer axialer Bauhöhe zu schaffen, um einen möglichst kleinen Winkel zwischen der Ebene der scheibenförmigen Bearbeitungswerkzeuge und der gedachten Verbindungslinie von der Peripherie der Bearbeitungswerkzeuge zur Unterkante der Schnellspannein­richtung zu erzielen. Ein möglichst kleiner Winkel (Schleifwinkel) ist z.B. bei Winkelschleifern von Wichtigkeit.The invention has for its object to provide a quick release device of the generic type with a comparatively low axial height in order to achieve the smallest possible angle between the plane of the disk-shaped machining tools and the imaginary connecting line from the periphery of the machining tools to the lower edge of the quick clamping device. The smallest possible angle (grinding angle) is e.g. important for angle grinders.

Diese Aufgabe ist erfindungsgemäß mit den kennzeichnenden Merk­malen des Anspruchs 1 gelöst. Weiterbildungen und zweckmäßige Ausgestaltungen der Erfindung sind in den Unteransprüchen gekennzeichnet.This object is achieved with the characterizing features of claim 1. Further developments and expedient refinements of the invention are characterized in the subclaims.

Die Erfindung wird im nachstehenden anhand der Zeichnung, die zwei Ausführungsbeispiele einer Schnellspanneinrichtung veran­schaulicht, erläutert.The invention is explained below with reference to the drawing, which illustrates two embodiments of a quick release device.

Es zeigen:

  • Fig. 1 eine Explosionsdarstellung der Schnellspann­einrichtung
  • Fig. 2 einen Schnitt durch die Schnellspannvor­richtung gemäß Fig. 1 im auf der Abtriebsspindel eines Winkelschleifers befindlichen Zustand,
  • Fig. 3 eine Ansicht der Schnellspanneinrichtung längs des Schnittes A-A durch Fig. 2,
  • Fig. 4 eine Ausführungsvariante der Schnellspannein­richtung im Schnitt,
  • Fig. 5 eine Ansicht der Schnellspanneinrichtung ge­mäß Fig. 4 längs des Schnittes B-B durch Fig. 4,
  • Fig. 6 eine Ansicht entlang des Schnittes C-C durch Figur 5,
  • Fig. 7 Ausschnitt aus Fig. 5 in vergrößerter Darstellung.
Show it:
  • Fig. 1 is an exploded view of the quick release device
  • 2 shows a section through the quick release device according to FIG. 1 in the state located on the output spindle of an angle grinder,
  • 3 is a view of the quick release device along the section AA through Fig. 2,
  • 4 shows an embodiment variant of the quick release device in section,
  • 5 is a view of the quick release device according to FIG. 4 along the section BB through FIG. 4,
  • 6 shows a view along the section CC through FIG. 5,
  • Fig. 7 detail of Fig. 5 in an enlarged view.

Wie die Figur 1 zeigt, besteht die Schnellspanneinrichtung im wesentlichen aus einer Spannmutter 10, einem Stellring 11, einem Spannflansch 12, aus zwei Sperrelementen 13, vier Rückstell- und Zentrierfedern 14, zwei Kugeln 15 für die Aufnahme von Radial­kräften und drei O-Ringen 16,17 und 18. Die Anzahl der Sperrele­mente 13 und der Federn 14 richtet sich dabei nach dem jeweiligen Bedarfsfall.
Sowohl die Spannmutter 10 als auch der Spannflansch 12 sind mit einer Anzahl Schanzen 19,20 versehen, von denen jeweils eine geeignete Anzahl am Umfang verteilt angeordnet ist. Die Schanzen bzw. keilartigen Erhebungen 19,20 liegen auf den einan­der zugeordneten Flächen der Spannmutter 10 und des Spann­flanschs 12 und korrespondieren miteinander (siehe hierzu auch Figur 3).
As FIG. 1 shows, the quick-action clamping device essentially consists of a clamping nut 10, an adjusting ring 11, a clamping flange 12, two locking elements 13, four return and centering springs 14, two balls 15 for absorbing radial forces and three O-rings 16 , 17 and 18. The number of locking elements 13 and springs 14 depends on the particular case.
Both the clamping nut 10 and the clamping flange 12 are provided with a number of jumps 19, 20, of which a suitable number is arranged distributed over the circumference. The jumps or wedge-like elevations 19, 20 lie on the mutually assigned surfaces of the clamping nut 10 and the clamping flange 12 and correspond to one another (see also FIG. 3).

Am Innenumfang des Stellrings 11 sind sich radial nach innen erstreckende Barrieren 21 angebracht, an denen sich jeweils ein Ende einer Feder 14 eines Federpaares abstützt. Das andere Feder­ende kommt dabei an einer Kugel 15 zur Anlage. An der dieser Anlageseite gegenüberliegenden Fläche dieser Kugel 15 greift das Ende der zweiten Feder 14 an, deren anderes Ende sich an der durch eine Ausnehmung 22 in der Spannmutter 10 gewonnenen An­schlagfläche 23 abstützt.
Gegenüber jeder Barriere 21 in Umfangsrichtung versetzt, weist der Stellring 11 einen nasenförmig oder ähnlich geformten Ansatz 24 auf, der mit einem Sperrelement 13 zusammenwirkt, das einen drehbar in einer Bohrung 25 in der Spannmutter 10 gelagerten Zapfen 26 besitzt und das in diesem Bereich an eine passende Aus­nehmung in der Spannmutter angrenzt. Die beim Ausführungs­beispiel vorgesehenen zwei Sperrelemente 13 liegen einander gegenüber und sind als kleine Kurvenscheiben ausgebildet, die jeweils in ihrem dem Zapfen 26 abgewandten Bereich auf den mit einer korrespondierenden Ausnehmung 27 versehenen Spann­flansch 12 einwirken.
On the inner circumference of the adjusting ring 11 there are radially inwardly extending barriers 21, on each of which one end of a spring 14 of a pair of springs is supported. The other end of the spring comes to bear on a ball 15. The end of the second spring 14 engages on the surface of this ball 15 opposite this contact side, the other end of which is supported on the stop surface 23 obtained by a recess 22 in the clamping nut 10.
Offset in relation to each barrier 21 in the circumferential direction, the adjusting ring 11 has a nose-shaped or similarly shaped projection 24, which cooperates with a locking element 13, which has a pin 26 rotatably mounted in a bore 25 in the clamping nut 10 and in this area to a matching recess in the clamping nut adjoins. The two locking elements 13 provided in the exemplary embodiment lie opposite one another and are designed as small cam disks which each act in their area facing away from the pin 26 on the clamping flange 12 provided with a corresponding recess 27.

Wenn sich die beiden Sperrelemente 13 in der Position befinden, wie sie in der rechten Hälfte der Figur 3 für das eine Sperrelement veranschaulicht ist, verhindern sie eine Relativbewegung zwischen dem Spannflansch 12 und der Spannmutter 10 und damit auch zwischen den Schanzen 19 und 20. Die Belastung des Spannflanschs 12 mit dem Einspanndruck für das Werkzeug 28 ist damit gewährleistet und wird durch die Wirkung der Feder 14 aufrechterhalten. Diese Ein­spannlage ist in der rechten Hälfte der Figur 2 durch den un­mittelbar am Werkzeug 28 anliegenden Spannflansch 12 veranschau­licht.If the two locking elements 13 are in the position as is illustrated in the right half of FIG. 3 for the one locking element, they prevent a relative movement between the clamping flange 12 and the clamping nut 10 and thus also between the jumps 19 and 20. The Loading of the clamping flange 12 with the clamping pressure for the tool 28 is thus ensured and is maintained by the action of the spring 14. This clamping position is illustrated in the right half of FIG. 2 by the clamping flange 12 lying directly against the tool 28.

Soll der Spannflansch 12 vom Einspanndruck entlastet werden, z.B. wegen eines erforderlichen Werkzeugwechsels, so ist der Stellring 11 in Pfeilrichtung gegen die Rückstellkraft der Federn 14 zu verdrehen. Dadurch kommt der dem Drehzapfen abge­wandte Bereich der Sperrelemente 13 außer Eingriff mit den An­sätzen 24 des Stellrings 11 so daß die auf den Spannflansch 12 einwirkenden Sperrelemente nach außen ausweichen können und nach entsprechender Verschwenkung an der Innenfläche des Stell­rings zur Anlage kommen. Diese Position der Sperrelemente 13 ist in der linken Hälfte der Fig. 3 dargestellt. Der Spannflansch 12 kann nunmehr eine Relativbewegung zur Spannmutter 10 ausführen, und infolge der wirksamen axialen Vorspannung gleiten die Schanzen 20 des Spannflanschs 12 auf den Schanzen 19 der Spannmutter abwärts, so daß sich der Spannflansch 12 von der Einspann­ebene des Werkzeugs 28 gegen die Spannmutter 10 zu nach unten weg­bewegt. Spannflansch 12 und Spannmutter 10 sind damit vom Einspann­druck für das Werkzeug voll entlastet, so daß die letztere von Hand leicht vom Gewindezapfen 29 der Abtriebsspindel 30 des Winkel­schleifers gelöst werden kann. Der Gegenflansch ist mit 31 bezeichnet. Der beim Lösevorgang entstehende Zwischenraum zwischen der Ober­fläche des Spannflanschs 12 und der gegenüberliegenden Ober­fläche des Werkzeugs 28 ist in der linken Hälfte der Figur 2 mit LS bezeichnet.
Den Einspannzustand zeigt die rechte Hälfte der Figur 2. Die dem Werkzeug 28 abgewandte Ebene des Spannflanschs 12 und die dieser Ebene gegenüberliegende Ebene der Spannmutter 10 weisen hier einen durch die Relativposition der Schanzen 19 und 20 zueinander bewirkten Abstand VS auf.
If the clamping flange 12 is to be relieved of the clamping pressure, for example because of a necessary tool change, the adjusting ring 11 is in the direction of the arrow against the restoring force Twist springs 14. As a result, the area of the locking elements 13 facing away from the pivot comes out of engagement with the lugs 24 of the adjusting ring 11 so that the locking elements acting on the clamping flange 12 can move outward and come into contact with the inner surface of the adjusting ring after appropriate pivoting. This position of the locking elements 13 is shown in the left half of FIG. 3. The clamping flange 12 can now perform a relative movement to the clamping nut 10, and due to the effective axial preload, the jumps 20 of the clamping flange 12 slide down on the jumps 19 of the clamping nut, so that the clamping flange 12 moves from the clamping plane of the tool 28 against the clamping nut 10 moved down. Clamping flange 12 and clamping nut 10 are thus fully relieved of the clamping pressure for the tool, so that the latter can easily be released by hand from the threaded pin 29 of the output spindle 30 of the angle grinder. The counter flange is designated 31. The space between the surface of the clamping flange 12 and the opposite surface of the tool 28, which is created during the loosening process, is designated LS in the left half of FIG.
The right-hand half of FIG. 2 shows the clamping state. The plane of the clamping flange 12 facing away from the tool 28 and the plane of the clamping nut 10 opposite this plane here have a distance VS caused by the relative position of the jumps 19 and 20.

Beim Ausführungsbeispiel gemäß den Figuren 4 bis 6 sind das bzw. sind die Sperrelemente 13′ angenähert keulenförmig ausgebildet. Im verspannten Zustand der Einrichtung pressen die nasenförmigen Ansätze 24 des Stellrings 11 das Sperrelement 13′ jeweils nach innen. Dabei stützt sich die Stirnfläche 32 der Sperrelemente 13′ jeweils an einer Flanke 33 der Spannmutter 10 ab. Der in Figur 7 mit α bezeichnete Freiwinkel zwischen den beiden zur Anlage aneinander kommenden Flächen 32, 33 der Spannmutter 10 und des Sperrelements 13′ wird dabei so gewählt, daß sich günstige Reibungsverhältnisse ergeben, z.B.: α min ≈ Agαµ. Erforderlichenfalls kann die Reibung durch die Verwendung von keramischen Werkstoffen mit geringem Reibungsfaktor verringert werden. Bei aus Stahl bestehenden Sperrelementen 13, 13′ kann der Freiwinkel α beispielsweise in der Größenordnung zwischen 12° bis 16° liegen, bei Sperrelementen aus Keramik beispielsweise 8°-12° betragen.In the embodiment according to Figures 4 to 6 that or the locking elements 13 'are approximately club-shaped. In the clamped state of the device press the nose-shaped lugs 24 of the collar 11, the locking element 13 'in each case. The end face 32 of the locking elements 13 'is each supported on a flank 33 of the clamping nut 10. The clearance angle designated α in FIG. 7 between the two surfaces 32, 33 of the clamping nut 10 and the locking element 13 'coming into contact with one another is chosen in such a way that favorable friction conditions result, for example: α min ≈ Agαµ. If necessary, the use of ceramic materials with a low friction factor can reduce the friction. In the case of locking elements 13, 13 'made of steel, the clearance angle α can be, for example, in the order of magnitude between 12 ° and 16 °, for locking elements made of ceramic, for example, 8 ° -12 °.

Es kommt darauf an, daß zwischen den Berührungsflächen 32 und 33 der Sperrelemente 13′ und der Spannmutter 10 im Sperrzustand Selbsthemmung vermieden ist, so daß auf die Sperrelemente nach Freigabe durch den Stellring 11 eine Kraftkomponente einwirkt, die ein Ausschwenken der Sperrelemente 13′ gegen die Innenwan­dung des Stellrings hin bewirkt. Um dies zu erreichen, ist es erforderlich, daß die in Figur 7 mit 34 bezeichnete Ebene zu der auf den Radialstrahl 35 bezogenen Normalebene 36 um einen Freiwinkel α geneigt ist.It is important that self-locking is avoided in the locked state between the contact surfaces 32 and 33 of the locking elements 13 'and the clamping nut 10, so that a force component acts on the locking elements after release by the adjusting ring 11, which swings out the locking elements 13' against the The inner wall of the collar causes. To achieve this, it is necessary that the plane denoted by 34 in FIG. 7 is inclined by a clearance angle α to the normal plane 36 related to the radial beam 35.

Die Sperrelemente 13′ können - müssen aber nicht - auch hierbei mittels Zapfen 25 in Bohrungen des Spannflanschs 12 drehbar zentriert sein und die Ausbildung der Schanzen 19 an der Spannmutter 10 und der Schanzen 20 an der dieser gegenüberliegenden Fläche des Spannflanschs 12 entspricht derjenigen nach dem ersten erläuterten Ausführungsbeispiel Entsprechendes gilt für die Anordnung und Anzahl der Schanzen 19 und 20, wobei diesbezüglich verschiedene Möglichkeiten bestehen.The locking elements 13 'can - but need not - be rotatably centered here by means of pins 25 in bores of the clamping flange 12 and the formation of the jumps 19 on the clamping nut 10 and the jumps 20 on the opposite surface of the clamping flange 12 corresponds to that after the first Embodiment explained The same applies to the arrangement and number of ski jumps 19 and 20, with various possibilities in this regard.

Beim Ausführungsbeispiel nach den Figuren 4 bis 7 sind insge­samt zwei Rückstellfedern 14′ vorgesehen. Wie insbesondere Figur 5 erkennen läßt, ist die eine der beiden Rückstellfedern 14′ im Entlastungszustand des Spannflanschs 12 (siehe rechte Seite der Figur 5) gespannt und das Sperrelement 13′ gelangt infolge der nach manueller Drehung des Stellrings 11 in die Löseposition wirkenden Kräfte unter Überwindung der Reibung bis zum Anschlag an die Innenfläche des Stellrings 11 nach außen. Dadurch kann sich der Spannflansch 12 unter dem Einfluß der wirkenden Axial­kraft relativ zur Spannmutter 10 verdrehen, wobei er sich axial auf die Spannmutter 10 hinbewegt, so daß zwischen der Einspann­ebene des Spannflanschs 12 und dem Bearbeitungswerkzeug 28 ein kleiner Spalt LS entsteht. Damit ist der Spannflansch 10 vom Ein­spanndruck für das Werkzeug entlastet.
Im Einspannzustand nimmt die Feder 14′ die in der linken Hälfte der Figur 5 dargestellte entsprechende Lage ein, und eine Relativbewegung zwischen dem Spannflansch 12 und der Spannmutter 10 wird durch die zwischen diesen beiden Bauteilen befindlichen Sperrelemente 13′ verhindert, welche die Spannmutter 10 und den Spannflansch 12 in ihrer gegenseitigen Lage fixieren.
In the embodiment of Figures 4 to 7, a total of two return springs 14 'are provided. As can be seen in particular in FIG. 5, one of the two return springs 14 'is tensioned in the unloaded state of the clamping flange 12 (see right side of FIG. 5) and the locking element 13' comes as a result of the forces acting after the manual rotation of the adjusting ring 11 into the release position while being overcome the friction up to the stop on the inner surface of the collar 11 to the outside. This can the clamping flange 12 rotates relative to the clamping nut 10 under the influence of the acting axial force, wherein it moves axially towards the clamping nut 10, so that a small gap LS is created between the clamping plane of the clamping flange 12 and the machining tool 28. The clamping flange 10 is thus relieved of the clamping pressure for the tool.
In the clamped state, the spring 14 'takes the corresponding position shown in the left half of Figure 5, and a relative movement between the clamping flange 12 and the clamping nut 10 is prevented by the locking elements 13' located between these two components, which the clamping nut 10 and Fix the clamping flange 12 in their mutual position.

Das Ausführungsbeispiel nach den Figuren 4 bis 7 weist den Vorteil auf, daß normgerechte Gegenflansche 31 verwendet werden können. Als zweckmäßig hat es sich erwiesen, die Spannmutter 10 und den Spannflansch 12 mit jeweils drei um 120° zueinander versetzt ange­ordneten Schanzen (Keilen) 19 bzw. 20 zu versehen. Grundsätzlich richtet sich die Anzahl der Schanzen (Keile) nach den jeweiligen Erfordernissen.The exemplary embodiment according to FIGS. 4 to 7 has the advantage that standard counter flanges 31 can be used. It has proven to be expedient to provide the clamping nut 10 and the clamping flange 12 with three jumps (wedges) 19 and 20, respectively, which are offset by 120 ° to one another. Basically the number of jumps (wedges) depends on the respective requirements.

Die Anzahl der Schanzen 19 und 20 beträgt bei beiden Aus­führungsbeispielen (Fig. 1 bis 6) jeweils sechs.The number of ski jumps 19 and 20 is six in each of the two exemplary embodiments (FIGS. 1 to 6).

Auch im Falle des Ausführungsbeispiels gemäß den Figuren 1 bis 3 kommt es darauf an, daß eine Selbsthemmung zwischen den Sperr­elementen 13 und dem Spannflansch 12 vermieden ist.Also in the case of the exemplary embodiment according to FIGS. 1 to 3, it is important that self-locking between the locking elements 13 and the clamping flange 12 is avoided.

Claims (7)

1. Eine Spannmutter und Spannflansche umfassende Schnellspann­einrichtung für scheibenförmige Bearbeitungswerkzeuge von Elektrowerkzeugen, bei welcher ein Flansch mit dem Ein­spanndruck für das Bearbeitungswerkzeug mit Hilfe eines manuell betätigbaren Stellrings belastbar und vom Ein­spanndruck wieder entlastbar ist, dadurch gekennzeichnet, daß der Einspanndruck durch an der Spannmutter (10) und am Spannflansch (12) angebrachte, miteinander korrespon­dierende Schanzen (19,20) aufgebracht ist, die mit Hilfe wenigstens eines Sperrelements (13,13′) auf das der unter der Wirkung einer Rückstellkraft stehenden Stellring (11) ein­wirkt, an einer Relativbewegung zueinander gehindert sind, und daß eine zur Entlastung des Spannflansches (12) vom Einspanndruck führende Relativbewegung des Spannflansches (12) zur Spannmutter (10) durch Freigabe des Sperrelements (13,13′) durch den Stellring (11) ermöglicht wird.1. A clamping nut and clamping flanges comprising quick-action clamping device for disc-shaped machining tools of power tools, in which a flange can be loaded with the clamping pressure for the machining tool with the aid of a manually actuated adjusting ring and can be relieved of the clamping pressure, characterized in that the clamping pressure is applied to the clamping nut (10 ) and on the clamping flange (12) attached, mutually corresponding jumps (19, 20) is applied, which acts with the aid of at least one locking element (13, 13 ') on the adjusting ring (11) under the action of a restoring force, on a relative movement are prevented from each other, and that a leading to the relief of the clamping flange (12) from the clamping pressure relative movement of the clamping flange (12) to the clamping nut (10) by releasing the locking element (13,13 ') by the adjusting ring (11). 2. Schnellspanneinrichtung nach Anspruch 1 dadurch gekenn­zeichnet, daß das Sperrelement (13,13′) als lagedefiniert angeordnete Kurvenscheibe ausgebildet ist, mit der ein nasenförmiger Ansatz (24) am Innenumfang des unter der Wirkung von Rückstellfedern (14,14′) stehenden Stellrings (11) zu­sammenwirkt.2. Quick release device according to claim 1, characterized in that the locking element (13,13 ') is designed as a position-defined cam, with which a nose-shaped projection (24) on the inner circumference of the under the action of return springs (14,14') standing ring ( 11) interacts. 3. Schnellspanneinrichtung nach Anspruch 2, dadurch gekenn­zeichnet, daß die Kurvenscheibe mittels eines Zapfens (26) drehbar in einer Aufnahmebohrung (25) in der Spannmutter (10) zentriert ist.3. Quick clamping device according to claim 2, characterized in that the cam disc is rotatably centered by means of a pin (26) in a receiving bore (25) in the clamping nut (10). 4. Schnellspanneinrichtung nach den Ansprüchen 1 bis 4, dadurch gekennzeichnet, daß sie mit zwei einander gegenüberliegen­den Sperrelementen (13,13′) ausgerüstet ist.4. Quick release device according to claims 1 to 4, characterized in that it is equipped with two opposing locking elements (13,13 '). 5. Schnellspanneinrichtung nach den Ansprüchen 1 bis 4, dadurch gekennzeichnet, daß die Rückstellfedern durch vier Schrauben­federn (14) verkörpert sind, von denen jeweils ein Paar eine Kugel (15) zwischen sich einschließt und das Ende der einen Feder an der Spannmutter (10) und das Ende der anderen Feder am Stellring (11) abgestützt ist.5. Quick release device according to claims 1 to 4, characterized in that the return springs are embodied by four coil springs (14), each of which a pair includes a ball (15) between them and the end of a spring on the clamping nut (10) and the end of the other spring is supported on the adjusting ring (11). 6. Schnellspanneinrichtung nach den Ansprüchen 1 bis 4, da­durch gekennzeichnet, daß zwei einander gegenüberliegende Rückstellfedern (14′) vorgesehen sind, deren eines Ende jeweils am Stellring (11) anliegt und deren anderes Ende jeweils an der Spannmutter (10) abgestützt ist.6. Quick release device according to claims 1 to 4, characterized in that two opposing return springs (14 ') are provided, one end of which rests on the adjusting ring (11) and the other end is supported on the clamping nut (10). 7. Schnellspanneinrichtung nach den Ansprüchen 1 bis 6, dadurch gekennzeichnet, daß die Spannmutter (10) und der Spann­flansch (12) jeweils mit drei um 120° zueinander versetzt angeordneten Schanzen (19 bzw. 20) versehen sind.7. Quick clamping device according to claims 1 to 6, characterized in that the clamping nut (10) and the clamping flange (12) are each provided with three jumps (19 and 20) arranged offset by 120 ° to one another.
EP19890113940 1989-02-09 1989-07-28 Quick clamping device for disc-like working-tools for electric tools Ceased EP0381809A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19893903766 DE3903766A1 (en) 1989-02-09 1989-02-09 QUICK RELEASE DEVICE FOR DISC-SHAPED MACHINING TOOLS OF ELECTRIC TOOLS
DE3903766 1989-02-09

Publications (2)

Publication Number Publication Date
EP0381809A2 true EP0381809A2 (en) 1990-08-16
EP0381809A3 EP0381809A3 (en) 1990-10-17

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Family Applications (1)

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EP19890113940 Ceased EP0381809A3 (en) 1989-02-09 1989-07-28 Quick clamping device for disc-like working-tools for electric tools

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EP (1) EP0381809A3 (en)
DE (1) DE3903766A1 (en)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0558277A1 (en) * 1992-02-28 1993-09-01 Black & Decker Inc. Improvements in or relating to flange locks
DE4238466C1 (en) * 1992-11-16 1994-01-20 Metabowerke Kg Quick acting clamping nut for securing grinding wheels etc. - has wheel forced against spindle flange by spring loaded disk which holds wheel away from nut face after nut is loosened by spindle braking
DE4243328C1 (en) * 1992-12-22 1994-06-09 Metabowerke Kg Quick clamping device for axial fixture of disc-shaped tool, partic. grinding disc - has flange of driven spindle with clamping component provided with thread screwable with thread of spindle
DE4305317A1 (en) * 1993-02-20 1994-09-01 Metabowerke Kg Clamping nut
WO1994025221A1 (en) * 1993-04-29 1994-11-10 Filip Kozelj Clamping device for fast axial mounting of tools, especially the disk-shaped ones
EP0631844A1 (en) * 1993-07-01 1995-01-04 Black & Decker Inc. Improvements in or relating to flange locks
US5545078A (en) * 1992-11-16 1996-08-13 Metabowerke Gmbh & Co. Quick-action clamping device for axially securing a disk shaped tool
WO1997021519A1 (en) * 1995-12-11 1997-06-19 INA Wälzlager Schaeffler oHG Quick-gripping coupling with radially acting clamping members
US5871322A (en) * 1994-12-22 1999-02-16 Power Tool Holders Incorporated Clamp screw
US6050741A (en) * 1998-01-30 2000-04-18 Power Tool Holders Incorporated Tool clamping device
US6179512B1 (en) 1998-05-29 2001-01-30 Power Tool Holders Incorporated Collet nut
EP1281478A2 (en) * 2001-08-03 2003-02-05 Neudecker &amp; Jolitz GmbH &amp; Co. Quick-change nut
EP2103383A3 (en) * 2008-03-20 2013-01-16 Metabowerke GmbH Hand tool device
CN104044062A (en) * 2013-03-15 2014-09-17 昆山齐升磨料磨具有限公司 Novel grinding tool

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4029744A1 (en) * 1990-09-20 1992-03-26 Metabowerke Kg Quick-release clamping ring for grinding wheels - has split nut allowing release of clamping force by moving two halves apart
US5577872A (en) * 1993-03-15 1996-11-26 Power Tool Holders Incorporated Torque enhancing tightening screw
US5567100A (en) * 1993-03-15 1996-10-22 Power Tool Holders Incorporated Torque enhancing clamping nut
JPH0727121A (en) * 1993-06-30 1995-01-27 Jacobs Japan Inc Screw for tightening
DE19511184A1 (en) * 1995-03-27 1996-10-02 Schaeffler Waelzlager Kg Detachable fixture for disc, such as grinding wheel, to drive spindle
US7343841B2 (en) 2002-02-15 2008-03-18 Black & Decker Inc. Blade clamp assembly

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US4637170A (en) * 1985-01-17 1987-01-20 Aleck Block Abrasive apparatus
EP0231500B1 (en) * 1986-02-05 1994-04-13 Robert Bosch Gmbh Device for releasably mounting a disc-like working-tool
WO1988004976A1 (en) * 1986-12-24 1988-07-14 Robert Bosch Gmbh Clamping device for releasably holding a tool, in particular a disk
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Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5388942A (en) * 1992-02-28 1995-02-14 Black & Decker Inc. Flange locks
EP0558277A1 (en) * 1992-02-28 1993-09-01 Black & Decker Inc. Improvements in or relating to flange locks
DE4238466C1 (en) * 1992-11-16 1994-01-20 Metabowerke Kg Quick acting clamping nut for securing grinding wheels etc. - has wheel forced against spindle flange by spring loaded disk which holds wheel away from nut face after nut is loosened by spindle braking
US5545078A (en) * 1992-11-16 1996-08-13 Metabowerke Gmbh & Co. Quick-action clamping device for axially securing a disk shaped tool
DE4243328C1 (en) * 1992-12-22 1994-06-09 Metabowerke Kg Quick clamping device for axial fixture of disc-shaped tool, partic. grinding disc - has flange of driven spindle with clamping component provided with thread screwable with thread of spindle
DE4305317A1 (en) * 1993-02-20 1994-09-01 Metabowerke Kg Clamping nut
WO1994025221A1 (en) * 1993-04-29 1994-11-10 Filip Kozelj Clamping device for fast axial mounting of tools, especially the disk-shaped ones
US5518440A (en) * 1993-07-01 1996-05-21 Black & Decker Inc. Power tool flange lock
EP0631844A1 (en) * 1993-07-01 1995-01-04 Black & Decker Inc. Improvements in or relating to flange locks
US5871322A (en) * 1994-12-22 1999-02-16 Power Tool Holders Incorporated Clamp screw
WO1997021519A1 (en) * 1995-12-11 1997-06-19 INA Wälzlager Schaeffler oHG Quick-gripping coupling with radially acting clamping members
US6050741A (en) * 1998-01-30 2000-04-18 Power Tool Holders Incorporated Tool clamping device
US6179512B1 (en) 1998-05-29 2001-01-30 Power Tool Holders Incorporated Collet nut
EP1281478A2 (en) * 2001-08-03 2003-02-05 Neudecker &amp; Jolitz GmbH &amp; Co. Quick-change nut
EP1281478A3 (en) * 2001-08-03 2004-03-17 Neudecker &amp; Jolitz GmbH &amp; Co. Quick-change nut
EP2103383A3 (en) * 2008-03-20 2013-01-16 Metabowerke GmbH Hand tool device
CN104044062A (en) * 2013-03-15 2014-09-17 昆山齐升磨料磨具有限公司 Novel grinding tool

Also Published As

Publication number Publication date
EP0381809A3 (en) 1990-10-17
DE3903766A1 (en) 1990-08-16

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