EP0324357B1 - Dispositif pour le serrage d'un outil en forme de disque - Google Patents

Dispositif pour le serrage d'un outil en forme de disque Download PDF

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Publication number
EP0324357B1
EP0324357B1 EP89100067A EP89100067A EP0324357B1 EP 0324357 B1 EP0324357 B1 EP 0324357B1 EP 89100067 A EP89100067 A EP 89100067A EP 89100067 A EP89100067 A EP 89100067A EP 0324357 B1 EP0324357 B1 EP 0324357B1
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EP
European Patent Office
Prior art keywords
clamping
tool
machine according
tool spindle
flange
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
EP89100067A
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German (de)
English (en)
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EP0324357A3 (en
EP0324357A2 (fr
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C&E Fein GmbH and Co
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C&E Fein GmbH and Co
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Publication date
Application filed by C&E Fein GmbH and Co filed Critical C&E Fein GmbH and Co
Publication of EP0324357A2 publication Critical patent/EP0324357A2/fr
Publication of EP0324357A3 publication Critical patent/EP0324357A3/de
Application granted granted Critical
Publication of EP0324357B1 publication Critical patent/EP0324357B1/fr
Anticipated expiration legal-status Critical
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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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/929—Tool or tool with support
    • Y10T83/9372—Rotatable type
    • Y10T83/9377—Mounting of tool about rod-type shaft
    • Y10T83/9379—At end of shaft

Definitions

  • the invention relates to a hand-held machine tool with a device for clamping a disk-shaped tool on a motor-driven rotating tool spindle, in particular for clamping a grinding wheel on an angle grinder, with a clamping anchor arranged in the tool spindle, which is provided with an axial recess, and can be displaced axially relative to it and connected to it in a rotationally fixed manner , with a clamping flange that can be detachably attached to the free end of the clamping anchor, with an abutment arranged on the tool-side end of the tool spindle and with a device that can be actuated by means of a manual actuation mechanism for releasably pressing the clamping flange against the abutment with intermediate clamping of the tool.
  • Such a device is known from DE-PS 34 05 855.
  • the clamping anchor arranged in the tool spindle designed as a hollow spindle is displaced by a compression spring also arranged in the tool spindle in such a way that a clamping flange which can be fastened to the clamping anchor clamps the disk-shaped tool against an abutment on the tool spindle.
  • the clamping force is generated by a spring arranged in the hollow spindle.
  • the tensioning of the tensioning anchor by means of the known spring requires a manual actuation mechanism which is fixed to the housing on the opposite side of the tool and which allows a force which counteracts the spring to be applied manually, so that this type of actuation prevents the most compact construction of the entire device.
  • the invention is therefore based on the object of making the known device for fastening a disk-shaped grinding tool, in which no auxiliary tool is required for loosening or tightening the tool fastening, as compact as possible, in particular hydraulically actuable. Reliable clamping should also be ensured in those cases in which changing torques act on the tool spindle.
  • the device has a first pressure cylinder, comprising a first cavity between the clamping anchor and the tool spindle, and a second Pressure cylinder, comprising a second cavity arranged in the clamping anchor or in the tool spindle and a connecting channel between the two cavities, that the second pressure cylinder comprises a piston arranged in the second cavity, which is adjustable for clamping from a tool-side end of the tool spindle by the manual actuation mechanism and in its position exciting the tool can be determined that the manual operating mechanism has a holding device which can be releasably attached to the tension anchor, which can be operated manually for pressing the clamping flange against the abutment, and that the holding device can be fixed in a rotationally fixed manner on the tool spindle.
  • a clamping device for clamping a tool arranged on a machine part by interaction of a first and a second pressure cylinder and an actuating device is known.
  • this clamping device is always arranged so that the tool between it itself and the machine part, that is, for example the tool spindle, is arranged so that the entire clamping device is arranged opposite the tool of the tool spindle and sits directly on the tool and consequently this against the Tool spindle can press.
  • the DE-U 69 18 532 can not anticipate the special design of the tool spindle and the tension anchor guided therein, as well as the arrangement and the two pressure cylinders within the tool spindle provided with an axial recess, as is the subject of the present invention.
  • a hydraulic clamping device for clamping a tool on a stationary machine tool has also become known.
  • the tool is hydraulically clamped between a fixed machine-side abutment and a clamping flange, which is screwed onto the outer free end of a central piston of the clamping device.
  • the actual clamping process is carried out by tightening a central clamping screw on the outer free end of the piston, whereby a hydraulic pressure is generated in a pressure chamber behind it, which is transmitted via a connecting channel to an annular chamber between the piston and the stationary abutment.
  • the tool is hydraulically clamped against the fixed abutment via the clamping flange.
  • GB-A 2 074 056 also does not anticipate or suggest the design of the hand-held power tool according to the invention, since the known clamping device relates to a machine tool of another type which does not have a manual operating mechanism.
  • both pressure cylinders are arranged in the tool spindle, which is necessary anyway, and can also be actuated from an end of the tool spindle on the tool side, the two pressure cylinders being correspondingly connected to one another both in the position that clamps the tool and in the position that does not clamp the tool, and during clamping the actuatable piston of the second pressure cylinder acts on a pressure medium arranged in both pressure cylinders and in the connecting channel, which in turn then causes in the second pressure cylinder that the tension anchor moves from its position not exciting the tool into its position exciting the tool.
  • the manual actuation mechanism has a holding device which can be fastened to the clamping anchor and can be pressed against the abutment, which can be locked in a form-fitting manner on the tool spindle.
  • first cavity is defined by mutually facing and axially spaced boundary surfaces of the tool spindle and the tension anchor and corresponding lateral surfaces of the tension anchor and the tool spindle.
  • a structurally particularly simple solution can be achieved in that the boundary surface of the tension anchor faces the tool, while the boundary surface of the tool spindle is arranged facing away from the tool, so that a volume dilation in the first cavity leads to the boundary surface of the tension anchor facing away from the tool is moved and thus the Anchors can perform an axial displacement directly exciting the tool.
  • the manual control device according to the invention can be integrated particularly well into a hand-held power tool if the manual control device comprises an adjustable clamping element which acts on the piston for clamping.
  • the tendon can be directly loaded with the hand and locked in its actuated position. Easier and, above all, less forceful operability of the tendon is possible if it has a surface that is oriented obliquely to an adjustment direction of the piston.
  • This surface can be, for example, the lateral surface of an eccentric, via which the piston can be actuated, for example, by means of a piston rod.
  • the inclined surface can also be a run-up surface which can be displaced transversely to the direction of adjustment of the piston and which also acts, for example, on a piston rod and thereby displaces the piston.
  • the simplest possibility of realizing the inclined surface is when the tendon has a thread, the threaded surfaces of which then form the inclined surfaces.
  • the tendon itself can be arranged at different points within the scope of the manual control device.
  • the tendon is arranged in the tension anchor or in the tool spindle, in particular in the bore extending up to the piston.
  • the holding device comprises the clamping flange.
  • the holding device has a holding member which can be positively fastened to the tensioning anchor against axial displacement and which, together with the tensioning flange, can be fixed in a rotationally fixed manner to the tool spindle by form-locking elements.
  • the holding member can be designed in a wide variety of ways. It is possible, for example, if the holding member can be connected to the tension anchor in the form of a bayonet catch.
  • a constructive alternative to this provides that the holding member can be screwed into the tension anchor.
  • a particularly preferred embodiment of a manual actuation mechanism provides that the tensioning member and the holding member are the same screw, so that by screwing this screw into the tensioning anchor both the tensioning flange is fastened to the same and the piston is simultaneously actuated.
  • the screw can be screwed into a first and an adjoining second threaded section of the tension anchor and if the piston can be actuated when screwing into the second threaded section.
  • Such a constructive solution has the great advantage that first of all a rough securing of the clamping flange on the clamping anchor can take place and, when the screw is screwed in further, the piston is actuated, which then leads to the final clamping of the tool.
  • the clamping flange is rotatably held on the holding member and can be acted upon by it in the direction of the tool. This is necessary in order to avoid, when fastening the tool, that the rotation of the holding member is made difficult by frictional forces between the tool and the screw itself.
  • the holding member can still be designed so that it can be easily rotated with respect to the clamping flange, even if, for example, a shoulder is applied to the clamping flange.
  • a particularly easy turning of the holding member can be achieved if an axial pressure bearing is arranged between the screw and the clamping flange.
  • a form-fitting securing of the holding member can be achieved, for example, by providing a detent that can be displaced in the radial direction of the tool spindle.
  • the tendon can be secured by a locking element which can be displaced in the axial direction, which can be, for example, a bolt which engages in bores in both the tendon and the tensioning flange.
  • the securing element is held in a rotationally fixed and axially displaceable manner on the tensioning member or on the tensioning flange and can be brought into engagement with a toothed ring of the tensioning flange or tensioning member which is coaxial with its axis of rotation. It is thus possible to secure the tendon at an angular position corresponding to an angular distance between successive teeth of the ring gear.
  • the securing element can be locked in its position securing the screw.
  • the first and second cavities and the connecting channel are filled with a plastic mass for hydraulic pressure transmission.
  • a plastic mass for hydraulic pressure transmission. This is particularly expedient because handheld power tools are to be used when there are large temperature differences and these are then to function reliably. When using a conventional hydraulic oil, this leads to sealing problems in the pressure cylinders that are difficult or almost impossible to control.
  • the plastic mass has the advantage that this type of tightness problem can be avoided.
  • a particularly preferred plastic mass is a polyvinyl chloride with a relatively low degree of polymerization.
  • the first cavity, the second cavity and the connecting channel can be filled with a viscous mass, since the above-mentioned tightness problems can also be avoided with this.
  • the viscous mass is preferably a silicone mass, in particular a silicone lubricant.
  • plastic or viscous masses are compressible, since these then become elastic and different The dimensions of the individual parts lead to the tension of the tool being adjusted.
  • an elastic element allowing an axial displacement of the clamping flange is provided relative to the tool spindle.
  • This element can be arranged in a wide variety of locations. For example, it is conceivable to arrange this element between the clamping flange and the holding member acting on it.
  • This elastic element is preferably dimensioned such that it can be compressed to inelasticity when the tool is clamped. This enables an even greater distance to be reached when clamping and that this elastic element also ensures that if the tool according to the invention has not been completely clamped, it ensures that the tool nevertheless rotates with the tool spindle and thus not to all possible accidents caused by insufficient tension.
  • the elastic element is a volume-elastic element arranged in one of the cavities, so that it is first compressed and then the tool is finally clamped by the volume compression.
  • a first exemplary embodiment of an angle grinding machine according to the invention shown in FIG. 1, comprises a drive motor 10, partially shown in the drawing, the drive shaft 12 of which drives a bevel gear 16 of a tool spindle 20 rotatably mounted in a gear housing 18 via a drive pinion 14.
  • This tool spindle 20 has at one end a flange 24 serving as an abutment for a tool, in particular a grinding wheel 22.
  • the tool spindle 20 is mounted in the gear housing 18 on a side facing the flange 24 by means of a lower bearing 26 and on a side facing away from the flange 24 by means of an upper bearing 28 arranged at a distance from the lower bearing 26.
  • the tool spindle 20 is one Axis 30 rotatable.
  • the tool spindle 20 which is designed as a hollow spindle, comprises a coaxial central recess 32 which, with a widened section 36, extends into the tool spindle 20 from an end 34 opposite the flange 24 and thus the tool 22, via a step surface 38 into a central section 40 passes into a smaller diameter with respect to the widened section 36 and, following the central section 40, widens in the region of the flange 24 to form a toothed section 44 which is provided with internal teeth 42 and which is open towards the tool 22.
  • a tension anchor 46 is displaceable in the axial direction, but is mounted in a rotationally fixed manner, which has a center piece 48 guided in the central section 40 of the coaxial recess 32, which carries on its end facing away from the tool 22 a tension anchor head 50 which has a larger diameter than the middle piece 48 and is guided in the expanded section 36.
  • this tension anchor head 50 On its side facing the step surface 38, this tension anchor head 50 has an annular surface 54 which extends up to a lateral surface 52 of the central piece 48, which together with the lateral surface 52 of the central piece 48, the step surface 38 and the widened section 36 of the coaxial recess 32 has a first Cavity 56 of a first pressure cylinder, formed by the tool spindle 20 and the clamping anchor 46 displaceable therein, is limited.
  • the middle piece 48 is provided with an annular seal 58 which is effective with respect to the central section 40 of the coaxial recess
  • the tension anchor head 50 is provided with an annular seal 60 which is effective with respect to the expanded section 36.
  • the tension anchor 46 is in turn also provided with a central bore 62 penetrating it from the side of the tension anchor head 50, into which a screw plug 64 is screwed in the area of the tension anchor head 50.
  • a central bore 62 penetrating it from the side of the tension anchor head 50, into which a screw plug 64 is screwed in the area of the tension anchor head 50.
  • connecting channels 66 extending in the radial direction and arranged in a region of the central piece 48 facing the tension anchor head 50 extend to the first cavity 56.
  • a piston 68 is sealingly arranged in the central bore 62 and defines a second cavity 70 which is delimited on the one hand by the piston 68, on the other hand by the screw plug 64 and by a bore section 72 of the central bore 62 lying between the two .
  • the piston 68 itself is acted upon from its side facing the tool 22 by a piston rod 74 which extends away from the piston 68 through the central bore 62 in the direction of the tool 22.
  • the tension anchor 46 is provided with a threaded bore 76 into which the central bore 62 originating from the tension anchor head 50 merges, the threaded bore 76 has a larger diameter than the central bore 62.
  • the piston rod 74 is dimensioned such that it projects out of the central bore 62 into a second threaded section 78 of the threaded bore 76, which adjoins the central bore 62.
  • This second threaded section 78 is followed in the axial direction towards the tool 22 by a first threaded section 80 of the threaded bore 76.
  • the tool that is to say the grinding wheel 22 in this case, is held by means of a clamping flange 82, which is part of a holding device designated as a whole by 84.
  • This holding device 84 comprises a holding screw 86 which can be screwed into the threaded bore 76 from the side of the tool 22 using a threaded bolt 88.
  • a cylindrical piece 90 Connected to this threaded bolt 88 of the holding device 84 is a cylindrical piece 90, which carries on its end opposite the threaded bolt 88 a circular disk-shaped screw head 92 which extends essentially parallel to the flange 24 and has a diameter approximately comparable to this.
  • This screw head 92 acts on the clamping flange 82 via an axial pressure bearing 94 arranged on its side facing the flange 24, which clamps the grinding wheel 22 between it and the flange 24 designed as an abutment in order to hold the grinding wheel 22.
  • a sleeve 96 which surrounds the cylindrical piece 90 and is rotatably mounted on the cylindrical piece 90, is formed on the clamping flange 82.
  • This sleeve 96 carries one External teeth 98, which can be brought into engagement with the internal teeth 42 of the toothed section 44 of the coaxial recess 32.
  • the sleeve 96 can thus be displaced in the axial direction into the toothed section 44, but is held non-rotatably in the latter relative to the tool spindle 20.
  • both the screw head 92 and the clamping flange 82 have the same diameter and both are provided with teeth 100 and 102 on their surfaces lying radially outside with respect to the axis 30, both teeth 100 and 102 with one another are identical.
  • the two toothings 100, 102 preferably have teeth arranged at an angular distance of approximately 5 °.
  • This cover cap 106 is mounted on the retaining screw 86 by means of a pin 108 in that this pin 108 engages in an inner bore 110 which extends from the end face 112 into the retaining screw 86.
  • the entire cover cap can be displaced in the direction of the axis 30 by the pin 108 guided in the inner bore 110, so that the inner toothed ring 104 either engages only with the toothing 100 of the screw head 92 or both with the toothing 100 of the screw head 92 as as well as with the toothing 102 of the clamping flange 82.
  • the pin 108 is provided with a first annular groove 114 into which a retaining ring 118 mounted in a circumferential groove 116 of the inner bore 110 engages when both toothings 100 and 102 are engaged with the internal ring gear 104.
  • the pin 108 is additionally provided with a second annular groove 120, into which the retaining ring 118 engages when the internal ring gear 104 is only engaged with the toothing 100.
  • FIG. 1 The exemplary embodiment according to the invention shown in FIG. 1 now functions as follows:
  • the entire holding device 84 is removed by unscrewing the threaded bolt 88 from the threaded bore 76.
  • a new grinding wheel 22 can now be placed on the flange 24.
  • the holding device 84 is inserted, the sleeve 96 integrally formed on the clamping flange 82 being rotated such that its external toothing 98 comes into engagement with the internal toothing 42 of the toothed section 44 of the coaxial recess 32.
  • This sleeve 96 thus ensures that the clamping flange 82 is non-rotatably connected to the tool spindle 20.
  • the retaining screw 86 is then screwed with its threaded bolt 88 into the threaded bore 76 of the tensioning anchor 46 with the cover cap only engaged with the toothing 100, whereby the threaded bolt 88 first turns into the first threaded section 80 and then reaches the adjoining second threaded section 78.
  • the clamping anchor 46 is pulled in the direction of the tool 22 until the movement of the clamping anchor 46 itself and the displacement of Pressure transmission medium from the first cavity 56 into the second cavity 70 via the piston 68 which have brought the piston rod 74 into contact with the front surface 122.
  • the reverse process takes place when the front surface 122 abuts the piston rod 74 before the clamping flange 82 contacts the grinding wheel 22 on the flange 24.
  • the threaded bolt 88 pulls the entire tension anchor 46 in the direction of the flange 24 by engaging in the threaded bore 76, so that the first cavity 56 of the first pressure cylinder is reduced, since the annular surface 54 and the step surface 38 towards each other be moved.
  • the front surface 122 presses the piston 68 in the direction of the tension anchor head 50 via the piston rod 74, so that the second cavity 70 is also reduced.
  • the first cavity 56, the second cavity 70 and also the connecting channels 66 are filled with a plastic mass, preferably a polyvinyl chloride with a relatively low degree of polymerization.
  • This plastic mass is pressurized by the reduction in the first cavity 56 and the simultaneous reduction in the second cavity 70 when the retaining screw 86 is screwed in, so that this plastic mass tends to move the tension anchor 46 as a whole away from the flange 44, and thereby exerts an additional axial tensile force on the retaining screw 86 so that it presses the grinding wheel 22 firmly against the flange 24 via the thrust bearing 94 and the clamping flange 82 and thus clamps the grinding wheel with the necessary force between the clamping flange 82 and the flange 24.
  • the advantageous effect of the two pressure cylinders working together can be seen in the fact that when the threaded bolt 88 begins to act on the piston rod 74 with its front surface 122, a slight rotation of the retaining screw 86 reduces both the first cavity 56 and the second cavity 70 and thus prestresses the plastic mass with high forces, the transmission ratio between the action of the piston 68 with a small piston area and the circular ring surfaces 54 and 38 acting as large piston areas also being effective.
  • the plastic mass has a certain elasticity and thus serves as a volume-compressible elastic element, which allows the grinding wheel 22 to be held tensioned when the retaining screw 86 is turned on.
  • the cover cap 106 is moved so far in the axial direction after tightening that the internal ring gear 104 also comes into engagement with the toothing 102, so that the screw head 92 can no longer rotate relative to the clamping flange 82, the latter for its part is held on the external toothing 98, which is in engagement with the internal toothing 42 of the tool spindle 20, so that no turning of the screw head 92 relative to the tool spindle 20 is possible.
  • a piston ring 130 is provided at a distance from the step surface 38 and extends between the widened section 36 of the coaxial recess 32 and the outer surface 52 of the center piece 48, which seals between these two surfaces and is sealed by means of disc springs 132 is supported on the step surface 38.
  • the first cavity 56 'of the second embodiment is therefore not limited by the step surface 38, but by a piston ring surface 134 facing the annular surface 54.
  • the plate springs 132 have the task of acting as an additional elastic element when tightening the retaining screw 86, so that when the threaded bolt 88 acts on the piston surface 74 with its front surface 122, further rotation is possible by a considerable angle, since the tightening of the Retaining screw 86 is not limited by the elasticity of the plastic mass, but first the disk springs 132 are compressed when the screw is turned further until the piston ring 130 is supported by the stepped surface 38 via the compressed disk springs 132. Only then is there a slight compression of the plastic mass arranged in the first cavity 56 ', the second cavity 70 and the connecting channels 66 in order to achieve a final tensioning of the grinding wheel 22.
  • the thrust bearing 94 is sealed against contamination by a felt ring 95 surrounding it.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)

Claims (26)

  1. Machine-outil portative avec un dispositif pour serrer un outil (22) en forme de disque sur une broche d'outil (20) susceptible d'être entraînée en rotation au moyen d'un moteur, en particulier pour serrer un disque de meulage sur une meuleuse d'angle, avec un tirant de serrage (46) disposé dans la broche d'outil (20), pourvue d'un évidement axial, déplaçable axialement par rapport à celle-ci et lui étant liée en rotation, avec une bride de serrage (82) susceptible d'être fixée de façon amovible à l'extrémité libre du tirant de serrage (46), un contre-appui, disposé sur l'extrémité côté outil de la broche d'outil (20) et avec un dispositif actionnable au moyen d'un mécanisme d'actionnement manuel, en vue de presser de façon amovible la bride de serrage (82) contre le contre-appui, avec serrage intermédiaire de l'outil (22), caractérisée en ce que le dispositif présente un premier vérin comprenant un premier espace creux (56), entre le tirant de serrage (46) et la broche d'outil (20), un deuxième vérin comprenant un deuxième espace creux (70), disposé dans le tirant de serrage (46) ou la broche d'outil (20), ainsi qu'un canal de liaison (66) ménagé entre les deux espaces creux (56, 70), en ce que le deuxième vérin comprend un piston (68) délimitant le deuxième espace creux (70) et réglable, en vue d'assurer le serrage amovible de l'outil (22), depuis une extrémité côté outil de la broche d'outil (20), au moyen du mécanisme d'actionnement manuel, et susceptible d'être fixé dans sa position de serrage de l'outil (22), en ce que le mécanisme d'actionnement manuel présente un dispositif de maintien (84) susceptible d'être fixé amovible sur le tirant de serrage (46) et susceptible d'être manoeuvré manuellement pour presser la bride de serrage (82) contre le contre-appui, et en ce que le dispositif de maintien (84) est susceptible d'être fixé, assujetti en rotation et par ajustement de forme, sur la broche d'outil (20).
  2. Machine selon la revendication 1, caractérisée en ce que le premier espace creux (56) est défini par des surfaces de limitation (38, 54), tournées l'une vers l'autre et espacées axialement l'une de l'autre, de la broche d'outil (20) ainsi que du tirant de serrage (46).
  3. Machine selon la revendication 2, caractérisée en ce que la surface de limitation (54) du tirant de serrage (46) est tournée vers l'outil (22), tandis que la surface de limitation (38) de la broche d'outil (20) est opposée à l'outil (22).
  4. Machine selon l'une des revendications précédentes, caractérisée en ce qu'un déplacement de réglage du piston (68) s'effectue par l'intermédiaire d'un alésage (62) ouvert côté outil et s'étendant jusqu'au piston, et ménagé dans le tirant de serrage (46) ou dans la broche d'outil (20) et que traverse le mécanisme d'actionnement manuel.
  5. Machine selon la revendication 1, caractérisée en ce que le mécanisme d'actionnement manuel est disposé dans une zone côté outil du tirant de serrage (46) ou de la broche d'outil (20).
  6. Machine selon l'une des revendications précédentes, caractérisée en ce que le mécanisme d'actionnement manuel comprend un organe de serrage (86, 144) réglable, sollicitant le piston (68) en vue d'assurer le serrage.
  7. Machine selon la revendication 5, caractérisée en ce que l'organe de serrage (86, 144) présente une surface inclinée obliquement par rapport à la direction de réglage du piston (68).
  8. Machine selon la revendication 5, caractérisée en ce que l'organe de serrage (86, 144) présente un filetage.
  9. Machine selon l'une des revendications 6 à 8, caractérisée en ce que l'organe de serrage (86, 144) est disposé sur le dispositif de maintien (84).
  10. Machine selon l'une des revendications précédentes, caractérisée en ce que le dispositif de maintien (84) entoure la bride de serrage (82).
  11. Machine selon l'une des revendications précédentes, caractérisée en ce que le dispositif de maintien (84) comprend un organe de maintien (86) susceptible d'être fixé sur le tirant de serrage (46) et susceptible d'être fixé, assujetti en rotation, conjointement à la bride de serrage (82), sur la broche d'outil (20), au moyen d'éléments à ajustement de forme (42, 98).
  12. Machine selon la revendication 11, caractérisée en ce que l'organe de maintien (86) est susceptible d'être vissé dans le tirant de serrage (46).
  13. Machine selon la revendication 12, caractérisée en ce que l'organe de serrage et l'organe de maintien sont la même vis (86).
  14. Machine selon la revendication 13, caractérisée en ce que la vis (86) est vissable dans un premier tronçon fileté (80) et un deuxième tronçon fileté (78), s'y raccordant, du tirant de serrage (46) et en ce que lors du vissage dans le deuxième tronçon fileté (78) le piston (68) est susceptible d'être actionné.
  15. Machine selon l'une des revendications 11 à 14, caractérisée en ce que, sur l'organe de maintien (86), la bride de serrage (82) est maintenue libre en rotation et susceptible d'être sollicitée par l'outil (22), dans la direction de ce dernier.
  16. Machine selon la revendication 15, caractérisée en ce qu'entre l'organe de maintien (86) et la bride de serrage (82) est disposé un palier à pression axiale (94).
  17. Machine selon l'une des revendications 11 à 16, caractérisée en ce que l'organe de maintien (86) est susceptible d'être fixé au moyen d'un élément de blocage (106) déplaçable en direction axiale.
  18. Machine selon la revendication 17, caractérisée en ce que l'élément de blocage (106) est maintenu, assujetti en rotation et déplaçable axialement sur l'organe de maintien (86) ou sur la bride de serrage (82) et susceptible d'être mis en contact avec une couronne dentée, coaxiale par rapport à son axe de rotation (30), de la bride de serrage (102) ou de l'organe de serrage (100).
  19. Machine selon l'une des revendications 17 ou 18, caractérisée en ce que l'organe de blocage (106) est susceptible d'être encliqueté dans sa position assurant la fixation de l'organe de serrage (86).
  20. Machine selon l'une des revendications précédentes, caractérisée en ce que le premier et le deuxième espaces creux (56, 70) ainsi que le canal de liaison (66) sont remplis d'une masse plastique, en vue d'assurer la transmission hydraulique de la pression.
  21. Machine selon la revendication 20, caractérisée en ce que la masse plastique est du chlorure de polyvinyle à degré de polymérisation relativement faible.
  22. Machine selon l'une des revendications 1 à 19, caractérisée en ce que le premier espace creux (56), le deuxième espace creux (70) et le canal de liaison (66) sont remplis d'une masse visqueuse.
  23. Machine selon la revendication 22, caractérisée en ce que la masse visqueuse est une masse de silicone, en particulier un lubrifiant aux silicones.
  24. Machine selon l'une des revendications précédentes, caractérisée en ce qu'est prévu un élément élastique (130, 132), permettant un déplacement axial de la bride de serrage (82) par rapport à la broche d'outil (20).
  25. Machine selon la revendication 24, caractérisée en ce que l'élément élastique (130, 132) est susceptible d'être comprimé, jusqu'à atteindre son état de non-élasticité, lors du serrage de l'outil (22).
  26. Machine selon la revendication 24 ou 25, caractérisée en ce que l'élément élastique est un élément (130, 132) présentant une élasticité en volume et disposé dans l'un des espaces creux (56).
EP89100067A 1988-01-09 1989-01-04 Dispositif pour le serrage d'un outil en forme de disque Expired - Lifetime EP0324357B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3800437 1988-01-09
DE3800437 1988-01-09

Publications (3)

Publication Number Publication Date
EP0324357A2 EP0324357A2 (fr) 1989-07-19
EP0324357A3 EP0324357A3 (en) 1990-06-13
EP0324357B1 true EP0324357B1 (fr) 1993-05-19

Family

ID=6345008

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89100067A Expired - Lifetime EP0324357B1 (fr) 1988-01-09 1989-01-04 Dispositif pour le serrage d'un outil en forme de disque

Country Status (4)

Country Link
US (1) US5199223A (fr)
EP (1) EP0324357B1 (fr)
JP (1) JPH01216770A (fr)
DE (1) DE58904372D1 (fr)

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IT1238239B (it) * 1990-02-08 1993-07-12 Selco Srl Mandrino porta lama a disco particolarmente per macchine sezionatrici.
JPH0663284U (ja) * 1993-02-05 1994-09-06 リョービ株式会社 動力工具の駆動部構造
IT1279651B1 (it) * 1995-10-11 1997-12-16 Selco Srl Macchina sezionatrice di pezzi.
SE511905C2 (sv) * 1997-07-08 1999-12-13 Anders Johnsen Anordning för fastsättning av två för samfälld rotation kring en axel anordnade enheter
DE10258372B4 (de) 2001-12-12 2004-12-30 S-B Power Tool Company, Broadview Spannaufbau
ES2261795T3 (es) * 2002-01-10 2006-11-16 Black & Decker Inc. Caja de engranajes.
US20060201492A1 (en) * 2002-03-18 2006-09-14 Anthony Baratta Methods and apparatus for movable machining tools including for wall saws
US7179156B2 (en) * 2005-03-23 2007-02-20 Gison Machinery Co., Ltd. Grinder with easily installable/detachable grinding disc and a linkage effect
US20070163412A1 (en) * 2006-01-15 2007-07-19 Anthony Baratta Methods and apparatus for movable machining tools, including for wall saws
EP1990146A3 (fr) * 2007-05-09 2013-02-27 Felder KG Dispositif de fixation d'un outil de rotation
DE102007035045A1 (de) * 2007-07-19 2009-01-29 C. & E. Fein Gmbh Kraftgetriebenes Handwerkzeug
US8328475B2 (en) * 2007-11-28 2012-12-11 Milwaukee Electric Tool Corporation Cutting tool assembly including a release mechanism
AT507775B1 (de) 2009-01-21 2010-08-15 Felder Kg Reibschlüssige rotationswerkzeugbefestigungsvorrichtung
US8925931B2 (en) 2010-04-29 2015-01-06 Black & Decker Inc. Oscillating tool
US9073195B2 (en) 2010-04-29 2015-07-07 Black & Decker Inc. Universal accessory for oscillating power tool
US9186770B2 (en) 2010-04-29 2015-11-17 Black & Decker Inc. Oscillating tool attachment feature
DE102010017721A1 (de) * 2010-07-05 2010-12-30 SEVERIN ELEKTROGERÄTE GmbH Mahlwerk
US9149923B2 (en) 2010-11-09 2015-10-06 Black & Decker Inc. Oscillating tools and accessories
JP5852901B2 (ja) * 2012-02-24 2016-02-03 株式会社マキタ 往復回転式電動工具
USD832666S1 (en) 2012-07-16 2018-11-06 Black & Decker Inc. Oscillating saw blade
CN102962706A (zh) * 2012-11-16 2013-03-13 安阳鑫盛机床股份有限公司 一种船用柴油机活塞加工用变椭圆车床夹具
US10265778B2 (en) 2017-01-16 2019-04-23 Black & Decker Inc. Accessories for oscillating power tools
USD814900S1 (en) 2017-01-16 2018-04-10 Black & Decker Inc. Blade for oscillating power tools
CN109623457A (zh) * 2018-12-14 2019-04-16 咸阳圣亚机电设备有限公司 变速器操纵装置壳体车床专用夹具以及加工方法

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Also Published As

Publication number Publication date
DE58904372D1 (de) 1993-06-24
EP0324357A3 (en) 1990-06-13
EP0324357A2 (fr) 1989-07-19
JPH01216770A (ja) 1989-08-30
US5199223A (en) 1993-04-06

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