EP0336930B1 - Dispositif de serrage pour la fixation amovible d'un outil, notamment d'un disque abrasif - Google Patents

Dispositif de serrage pour la fixation amovible d'un outil, notamment d'un disque abrasif Download PDF

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Publication number
EP0336930B1
EP0336930B1 EP19870907666 EP87907666A EP0336930B1 EP 0336930 B1 EP0336930 B1 EP 0336930B1 EP 19870907666 EP19870907666 EP 19870907666 EP 87907666 A EP87907666 A EP 87907666A EP 0336930 B1 EP0336930 B1 EP 0336930B1
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EP
European Patent Office
Prior art keywords
flange
annular part
tool
axially
clamping fixture
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
EP19870907666
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German (de)
English (en)
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EP0336930A1 (fr
Inventor
Winfried Helm
Manfred STÄBLE
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0336930A1 publication Critical patent/EP0336930A1/fr
Application granted granted Critical
Publication of EP0336930B1 publication Critical patent/EP0336930B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B45/00—Means for securing grinding wheels on rotary arbors
    • B24B45/006—Quick mount and release means for disc-like wheels, e.g. on power tools

Definitions

  • the invention is based on a clamping device for releasably fastening a tool, in particular a disk, according to the generic preamble of the main claim.
  • Clamping devices for, in particular, disk-shaped tools are particularly suitable for portable hand-held machine tools, and here in particular for grinding machines.
  • a clamping device is known (DE-PS 30 12 836), in which the one flange, which is arranged on the side of the tool facing the housing of the hand-held power tool, is displaceable relative to the spindle and is coupled to this in a torque-transmitting manner.
  • This rear support flange is supported against an axial displacement in an axial end position by a shoulder of the spindle forming a support element therefor.
  • the other flange which can be screwed onto the end of the spindle, consists of a nut with a in cross section approximately hat-shaped, separate clamping element, which is supported axially via a helical spring against the flange of the clamping nut.
  • the hat-shaped clamping element When screwing and tightening this clamping nut, the hat-shaped clamping element is pressed axially against the tool via the axially compressed spring, thereby tightening the tool against the spindle-side flange, the end face of a cylinder shoulder of the clamping nut coming directly into contact with a facing axial side of the rear flange and when further tightening the clamping nut, this rear, spindle-side flange is tightened together with the clamping nut, possibly until the rear flange axially comes to rest on the shoulder surface of the spindle, which forms the supporting element.
  • the aim of this is to clamp the grinding wheel with a defined contact pressure on an angle grinder and to ensure this contact pressure.
  • This clamping device is also intended to enable the grinding wheel to be replaced quickly and easily and at the same time to avoid overloading the hand-held power tool, in particular the angle grinder. If the torque applied to the grinding wheel becomes too large, the grinding wheel stops, while the rear flange and the clamping nut with clamping element execute a relative movement.
  • This clamping device counteracts the effect that the clamping nut continues to tighten itself during operation, which would otherwise make it considerably more difficult to loosen the clamping nut when changing the grinding wheel. Nevertheless, loosening the clamping nut is only possible with the help of a special auxiliary tool, and depending on the design of the machine, the spindle must be countered accordingly with a second auxiliary tool, for example a wrench.
  • a tool change is made possible without any auxiliary tool, which, moreover, can be carried out quickly and safely.
  • Another advantage is that existing handheld power tools can be converted without major modifications. For this, e.g. a simple exchange of the existing rear support flange for a ring part with an adapted flange.
  • the front clamping nut is unchanged in a known manner, so that standardized, inexpensive parts can be used here.
  • attach a key to it and loosen the clamping nut with this auxiliary tool for particularly stubborn cases, e.g. with a rusted clamping nut, attach a key to it and loosen the clamping nut with this auxiliary tool.
  • the rear ring part has a non-rotatable form fit with the spindle, so that relevant regulations are met. It is also advantageous that the clamping device is not arranged on the working side of the tool, but in the area between the tool and the housing-side bearing flange, so that any risk of damage, e.g. by abrasion on the workpiece. This also prevents any axial protrusion on the working side of the tool that could impair work.
  • FIG. 1 schematically shows the lower part of a portable hand-held power tool designed, for example, as an angle grinder shown, which has a motor-driven and gearbox-driven spindle 10, which at the end merges via an annular shoulder 11 into a cylindrical shoulder 12 of smaller diameter and then into an end threaded shoulder 13 with an external thread 14.
  • the spindle 10 serves to drive a tool 15 which, for example, consists of the indicated grinding wheel or another tool wheel, a rubber plate or the like.
  • the tool 15 is axially clamped and clamped between two flanges 16 and 17.
  • the flange 17 located at the spindle end is designed as a conventional clamping nut 18 which has a hub part 19 adjoining the flange and is provided on the inside with a continuous internal thread 20 with which the clamping nut 18 is screwed onto the threaded shoulder 13.
  • the tool 15 is centered on the outer peripheral surface of the hub part 19.
  • the other flange 16 is displaceable relative to the spindle 10 and is coupled to the spindle 10 in a manner to transmit torque in a manner described below. It is secured against axial displacement by a support element 21 and can be relieved of the clamping pressure for the tool 15.
  • the support element 21 consists of a ring part 22 with bottom 23 and cylinder part 24, which is approximately inverted in cross section, with the bottom 23 of the ring part 22 is axially supported on the ring shoulder 11 and radially centered on the cylindrical shoulder 12.
  • the ring part 22 has non-rotatable positive engagement with the spindle 10, from which it is rotatably carried in the direction of rotation according to arrow 25 when the motor is switched on.
  • the flange 16 consists essentially of a relatively flat bill. It is relative to the spindle 10 on the outer peripheral surface of the hub part 19 Ring part 22 axially displaceable and rotatable within limits.
  • the ring part 22 and the flange 16 are coupled by means of a spring 26, which is designed here as a torsion spring, one end 27 of which engages the ring part 22 and the other end 28 of the flange 16.
  • a spring is only indicated schematically in FIGS. 2 and 3, which engages with the end 28 on the flange 16 and acts on it in the direction of the indicated arrow 29 in a resilient manner relative to the ring part 22.
  • the ring part 22 and the flange 16 have several, e.g. three, in the circumferential direction successive, left-rising inclined surfaces 32 and 33, with which the flange 16 and the ring portion 22 axially abut.
  • the inclined surfaces 32 of the ring part 22 are located on the end face 30 of the cylinder part 24 facing the flange 16.
  • the wedge angle of both inclined surfaces 32, 33 is chosen to be so large that it lies in the area of self-locking.
  • the flange 16 strikes with the step surfaces 34 associated locking surfaces 35 on the step surfaces while limiting the pivoting angle. This state is shown in FIG. 3, in which the clamping device is released and thus the screwed-on flange 17 is relieved of the axial clamping pressure acting on the tool 15 from the flange 16.
  • the flange 16 faces the axially parallel end of the respective inclined surface 33 located downstream directed locking lugs 36, the front side of which is adjacent to the inclined surface 33 is in each case designed as a locking surface 35.
  • the opposite end face of each locking lug 36 of the flange 16 is designed as an approximately parallel driving surface 37.
  • the ring part 22 has, in the circumferential direction of each inclined surface 32, upstream, approximately axially parallel driver surfaces 38 which, when the tool 15 (FIG. 2) is clamped, abut against an associated driving surface 37 of the locking lug 36 while driving the flange 16.
  • the step surfaces 34 and driving surfaces 38 of the ring part 22, which are spaced apart in the circumferential direction, are formed by the two end faces of respective latching recesses 39, which consist of openings in the wall of the cylinder part 24.
  • the locking recesses 39 adjoin the wedge-upward end of each inclined surface 32 and are open axially and in the direction of the flange 16.
  • the opening width of each latching recess 39 measured in the circumferential direction is greater than the width of each locking lug 36 engaging therein.
  • rolling elements 40 are arranged between the axially adjacent inclined surfaces 32 and 33 of the ring part 22 and the flange 16, respectively, which make the sliding friction between the inclined surfaces 32, 33 a rolling friction and thus significantly reduce the friction.
  • the rolling elements 40 here consist of balls which are inserted into recessed grooves 41 in the inclined surfaces 32.
  • the flange 16 is fastened to a cylinder sleeve 42 enclosing it, for example screwed into it.
  • the cylinder sleeve 42 also extends axially over the cylinder part 24 of the ring part 22, which has an axial stop in the form of an axial stop at the end facing away from the tool 15 an annular shoulder 43 is overlapped.
  • the flange 16 together with the cylinder sleeve 42 on the ring part 22 is secured against detachment in the axial direction, which faces away from the ring part 22.
  • the flange 16 and the ring part 22 are held together by means of the cylinder sleeve 42.
  • the tensioning device also has at least one releasable locking device 44, via which the flange 16 is positively secured with respect to the ring part 22 in the position shown in FIG. 2, in which the tool 15 is clamped.
  • the locking device 44 has a tongue 45 which is fastened at one end to the ring part 22 by means of screw 46, specifically on the side which points towards the flange 16.
  • the tongue 45 is directed approximately radially. It acts approximately like a spring leaf and is additionally pressed down by means of a spring 47 in the form of a cylindrical coil spring in FIGS. 2 and 3.
  • the tongue 45 contains a recess 48 for holding and centering the end of the spring 47.
  • the spring 47 engages at a relatively large radial distance from the fastening point of the tongue 45 by means of the screw 46.
  • the tongue 45 is dimensioned with respect to the cross-sectional thickness such that it is bent downwards under the action of the relaxing spring 47 in the manner of a spring tongue in FIGS. 2 and 3 and can be bent up in opposite directions by means of manual actuation by compressing the spring 47. It is understood that the tongue 45 is also shaped, e.g. bent, can be that it is tension-free and relieved in the position shown in FIG. 2, brought down in the axial direction and can be lifted axially upwards against the action of the spring 47 into the position shown in FIG. 3.
  • the tongue 45 rests in a recess 49 which extends in the foot region of the latching recess 39 and in the region the spring 47 is provided with a recess 50 receiving and centering this end.
  • the width of the tongue 45 and the locking lug 36 together is chosen approximately as large as the total width of the locking recess 39, so that the locking lug 36 and the tongue 45 can be placed side by side within the locking recess 39 when the tool 15 is in the tensioned state.
  • the tongue 45 thus engages in the position of the flange 16 clamping the tool 16 in the latching recess 39, namely between the step surface 34 and the locking surface 35 of the locking lug 36. In this way, the tongue 45 secures in this position (FIG. 2) the contact of the locking lug 36 with its driving surface 37 on the driving surface 38 of the ring part 22.
  • the spring 26 additionally causes the flange 16 and of the ring part 22 relative to each other so that both parts slide up on the inclined surfaces 32, 33 and are thereby pressed apart axially.
  • the ring part 22 is rotationally blocked by suitable means, which can be done by appropriately blocking the spindle 10, for example by means of a spindle locking device integrated in the handheld power tool.
  • suitable means which can be done by appropriately blocking the spindle 10, for example by means of a spindle locking device integrated in the handheld power tool.
  • the friction in the transmission up to the motor is sufficient to prevent the spindle 10 from rotating in the direction of the arrow 25, at least within limits.
  • this is raised with one hand against the action of the spring 47 into the position shown in FIG. 3, in which the tongue 45 enters the recess 49, which is deep enough that the Tongue 45 now releases the locking lug 36, which can drive over the tongue 45 with its axially facing end.
  • the tool 15 is rotated by hand in the same direction according to arrow 25, thus counterclockwise.
  • the flange 17 and the flange 16 are also entrained via the friction.
  • the rotation of the flange 16 in this direction causes its inclined surfaces 33 to wedge down the inclined surfaces 32 of the rotationally blocked ring part 22, whereby due to the rolling elements 40 this sliding movement becomes a rolling movement with reduced rolling friction.
  • the flange 16 moves axially in the direction of the ring part 22, which leads to a corresponding axial relaxation.
  • the clamping nut 18 can then be easily unscrewed by hand.
  • the rolling bodies 40 arranged between the inclined surfaces 32, 33 have the advantage that the fore-end friction between the two is reduced to rolling friction and is thus practically negligible.
  • the clamping device described is simple, inexpensive and quick, safe and easy to use. It enables a quick and safe change of the tool 15 without the need for additional special tools.
  • Another advantage is that existing hand tool machines, especially grinding machines, can also be retrofitted without any major changes Conversion can be equipped with this clamping device.
  • the existing rear flange has to be exchanged for the unit consisting of the ring part 22 and flange 16, held together via the cylinder sleeve 42.
  • the existing, for example standardized, clamping nut 18 in other machines is retained unchanged, as is also the fact that the part supporting the tool 17 with the spindle 10 has a rotationally fixed positive fit. This complies with the relevant regulations.
  • the clamping device is not limited to grinding wheels as a tool 15. Rather, other tools, for example cup wheels, brushes, rubber plates or the like, can be clamped in the same way without tools.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)

Abstract

Dispositif de serrage pour ponceuses portatives, dans lequel la bride arrière (16) est supportée de manière à transférer le couple de rotation sur la broche (10) mais à être déplaçable axialement et peut être soulagée de la pression de serrage du disque abrasif (15) au moyen d'une pièce annulaire (22). Cette dernière est supportée axialement sur la broche (10) à laquelle elle est accouplée solidairement en rotation. La bride (16) est, dans certaines limites, axialement déplaçable et rotative par rapport à la pièce annulaire. Toutes deux possédent des faces inclinées (32, 33) à gauche et tournées axialement l'une vers l'autre, par lesquelles elles sont axialement contiguës. Lors du blocage en rotation de la pièce annulaire (22) avec la broche (10), la bride (16) peut, en cas de rotation à gauche du disque (16) avec cette dernière, s'éloigner, par ses faces inclinées (33) en aval de la clavette, des faces inclinées (32) de la pièce annulaire (22) et axialement par rapport à cette dernière, et l'écrou de serrage (18) peut être soulagé de la pression de serrage. Ce dispositif de serrage permet un changement rapide, sûr et sans outil du disque.

Claims (11)

1. Dispositif de fixation amovible d'un outil (15) notamment d'un disque sur une broche entraînée (10), caractérisé en ce que l'outil (15) peut être serré axialement entre deux brides (16, 17) dont l'une (16) est coulissante par rapport à la broche (10) et est couplée à la broche (10) notamment par une pièce annulaire (22), pour la transmission du couple, en étant bloquée en coulissement axial par un élément d'appui (21) et en étant déchargée de la pression de serrage de l'outil (15), l'élément d'appui (21) étant formé par la pièce annulaire (22) qui s'appuie axialement sur la brocha (10) du côté de la bride (16), opposé de celui de l'outil (15), la bride (16) étant maintenue coulissante axialement et mobile en rotation par rapport à la pièce annulaire (22), la pièce annulaire (22) et la bride (16) comportant des surfaces inclinées (32, 33) sur leurs faces frontales (30, 31) tournées axialemant l'une vers l'autre, surfaces inclinées par lesquelles la bride (16) et la pièce annulaire (22) s'appliquent axialement l'une contre l'autre, la pièce annulaire (22) étant couplée à la bride (16) par un ressort (26) notamment un ressort de rotation, dont une extrémité (27) est reliée à la pièce annulaire (22) et dont l'autre extrémité (28) est reliée à la bride (16), l'angle des multiples surfaces inclinées (32, 33), à pas à gauche, étant compris dans la plage d'autoblocage, et au niveau de l'extrémité du coin, les surfaces inclinées (32) respectives de la pièce annulaire (22) sa poursuivent respectivement par des surfaces an gradins (34) sensiblement parallèles à l'axe, contre lesquelles bute la bride (16) par ses surfaces de blocage (35) correspondantes, en limitant l'angle de rotation de la bride (16) par rapport à la pièce annulaire (22) lors du mouvement vers l'aval du coin, et de la décharge axiale de la pression de serrage, la bride (16) ayant à son extrémité, en aval du coin de la surface inclinée (33) respective, de façon adjacente, un bec de blocage (36) sensiblement parallèle à l'axe et dont la surface frontale voisine de la surface inclinée (33) constitue une surface de blocage (35), la pièce annulaire (22) ayant dans la direction périphérique de chaque surface inclinée (32), des surfaces d'entraînement (38) sensiblement parallèles à l'axe et qui, lorsque l'outil (15) est serré, viennent buter contre les surfaces d'entraînement associées (37) de la bride (16), avec entraînement en rotation, et en ce qu'au moins un dispositif de blocage (44) amovible, qui fixe la bride (16) par une liaison de forme par rapport à la pièce annulaire (22) lorsque la bride est dans sa position prête au serrage de l'outil (15), fait partie du dispositif de fixation.
2. Dispositif de fixation selon la revendication 1, caractérisé en ce que la face frontale de chaque bec de blocage (36) de la bride (16) en regard de la surface de blocage (35) correspondante est réalisée comme surface d'entraînement (37).
3. Dispositif de fixation selon l'une des revendications 1 et 2, caractérisé en ce que la pièce annulaire (22) comporte des cavités d'encliquetage (39) adjacentes respectivement à l'extrémité aval de chaque surface inclinée (32), cavités qui sont ouvertes axialement et vars la bride (16) et dont une face frontale forme une surface de gradin (34) et dont l'autre face frontale forme une surface d'entraînement (38).
4. Dispositif de fixation selon la revendication 3, caractérisé en ce que la largeur d'ouverture mesurée dans la direction périphérique de chaque cavité d'encliquetage (39) est supérieure à la largeur de chaque bec de blocage (36) de la bride gui vient prendre dans cette cavité.
5. Dispositif de fixation selon l'une des revendications 1 à 4, caractérisé en ce que la pièce annulaire (22) a une section sensiblement en forme de pot renversé et ses surfaces inclinées (32) sont sur la face frontale (30) de sa partie cylindrique (24), face tournée vers la bride (16).
6. Dispositif de fixation selon la revendication 5, caractériel en ce que les cavités d'encliquetage (39) sont constituées par des ouvertures réalisées dans la paroi de la partie cylindrique (24).
7. Dispositif de fixation selon l'une des revendications 1 à 6, caractérisé en ce qu'entre les surfaces inclinées (32, 33) de la pièce annulaire (22), axialement adjacentes, et la bride (16) il y a des organes de roulement (40) par exemple des billes logées dans des rainures enfoncées (41).
8. Dispositif de fixation selon l'une des revendications 1 à 7, caractérisé en ce que la bride (16) est fixée à un manchon cylindrique (42) gui l'entoure, ce manchon étant bloqué par une butée axiale par exemple un épaulement annulaire (43) sur la pièce annulaire (22) pour être solidarisé dans la direction axiale à l'outil (15).
9. Dispositif de fixation selon la revendication 8, caractérisé en ce que sur la pièce annulaire (22) le dispositif de blocage (44) comprend une languette (45) dirigée sensiblement radialement, et soumise à un ressort, cette languette venant prendra dans la cavité d'encliquetage (39) entre la surface en gradin (34) et le bec de blocage (36) qui y pénètre, lorsque la bride (16) est en position préparatoire à la fixation de l'outil (15), et bloquant la position de rotation relative entre la bride (16) et la pièce annulaire (22), languette qui libère le bec de blocage (35) lorsqu'elle est rentrée axialement par rapport à la pièce annulaire (22), en position non active, hors de la trajectoire du bec de blocage (35), et peut être entourée dans la direction périphérique par le bec de blocage (35).
10. Dispositif de fixation selon la revendication 9, caractérisé en ce que la largeur totale d'une languette (45) et d'un bec de blocage (36) est sensiblement égale à la largeur d'une cavité d'encliquetage (39).
11. Dispositif de fixation selon la revendication 9 ou 10, caractérisé en ce que la cavité d'encliquetage (39) comporte, à sa base, une découpe (49) qui reçoit la languette (45).
EP19870907666 1986-12-24 1987-11-28 Dispositif de serrage pour la fixation amovible d'un outil, notamment d'un disque abrasif Expired - Lifetime EP0336930B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863644440 DE3644440A1 (de) 1986-12-24 1986-12-24 Spanneinrichtung zum loesbaren befestigen eines werkzeuges, insbesondere einer scheibe
DE3644440 1986-12-24

Publications (2)

Publication Number Publication Date
EP0336930A1 EP0336930A1 (fr) 1989-10-18
EP0336930B1 true EP0336930B1 (fr) 1991-06-05

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870907666 Expired - Lifetime EP0336930B1 (fr) 1986-12-24 1987-11-28 Dispositif de serrage pour la fixation amovible d'un outil, notamment d'un disque abrasif

Country Status (5)

Country Link
EP (1) EP0336930B1 (fr)
JP (1) JPH02501128A (fr)
BR (1) BR8707952A (fr)
DE (2) DE3644440A1 (fr)
WO (1) WO1988004975A1 (fr)

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Also Published As

Publication number Publication date
WO1988004975A1 (fr) 1988-07-14
DE3770641D1 (de) 1991-07-11
DE3644440A1 (de) 1988-07-07
BR8707952A (pt) 1990-02-13
EP0336930A1 (fr) 1989-10-18
JPH02501128A (ja) 1990-04-19

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