EP1597023A2 - Befestigungseinrichtung und zugeordnetes werkzeug - Google Patents
Befestigungseinrichtung und zugeordnetes werkzeugInfo
- Publication number
- EP1597023A2 EP1597023A2 EP04714263A EP04714263A EP1597023A2 EP 1597023 A2 EP1597023 A2 EP 1597023A2 EP 04714263 A EP04714263 A EP 04714263A EP 04714263 A EP04714263 A EP 04714263A EP 1597023 A2 EP1597023 A2 EP 1597023A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- tool
- fastening device
- projection
- axially
- cam
- 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.)
- Granted
Links
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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B24—GRINDING; POLISHING
- B24D—TOOLS FOR GRINDING, BUFFING OR SHARPENING
- B24D7/00—Bonded abrasive wheels, or wheels with inserted abrasive blocks, designed for acting otherwise than only by their periphery, e.g. by the front face; Bushings or mountings therefor
- B24D7/16—Bushings; Mountings
-
- 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
- Y10T483/00—Tool changing
- Y10T483/10—Process
-
- 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
- Y10T483/00—Tool changing
- Y10T483/17—Tool changing including machine tool or component
- Y10T483/1733—Rotary spindle machine tool [e.g., milling machine, boring, machine, grinding machine, etc.]
- Y10T483/1736—Tool having specific mounting or work treating feature
Definitions
- the invention relates to a fastening device for a machine tool, with which a tool can be fastened to the machine tool and an associated tool.
- the tool can in particular be a cutting, thrust, diamond, brush, polishing or flap disc.
- German laid-open specification DE 100 174581 describes a grinding machine tool holder with a driving device, via which a tool can be operatively connected to a drive shaft.
- the insert tool can be connected to the entraining device via at least one detent element movably mounted against a spring element, the detent element engaging in an operating position of the insert tool and the insert tool being positively fixed for the insert.
- a fastening device which can be mounted on a machine tool, the fastening device having projections of a closure which can be operated without tools and which, in a closed position, engage over closure surfaces of the tool, as a result of which the tool body is axially secured and held in a rotationally fixed manner.
- the projections of the fastening device and a support for the tool are arranged so as to be axially displaceable relative to one another, the axial displacement path being able to be blocked by a centrifugal force device, as a result of which a positive fit is fixed in the closed position between the fastening device and the associated tool for use.
- the object of the invention is to provide a slight play between the tool and the fastening device in the closed position in the rest position and / or during operation when using such a quick-action clamping system to increase safety.
- the fastening device for a machine tool comprises at least one, in particular radially outwardly projecting, projection of a closure which can be actuated without tools, with which the fastening device can be detachably connected to the tool, in the closed position the projection of the fastening device via an associated, in particular radially inwardly facing Closing surface of the tool engages and the tool body is axially secured and held in a rotationally fixed manner.
- the machine tool on the tool is equipped with a drive surface which extends at an angle to the axis, the tool resting on the drive surface in its operating position.
- a drive surface which extends at an angle to the axis, the tool resting on the drive surface in its operating position.
- the fastening device comprises a centrifugal force device that blocks or blocks the axial displaceability of the at least one projection and the support for the tool.
- the centrifugal force device has at least one centrifugal force element which is acted upon radially outwardly by a force means and a means that converts the force to the at least one centrifugal force element in order to generate an axially directed force for clamping the tool in the fastening device. It is also achieved here by the specified design of the fastening device according to the invention that when the fastening device is operated, in addition to a force means acting in the rest position, an operating force acting in the axial direction is generated which presses the tool against its support on the fastening device.
- the fastening device is constructed in such a way that the at least one centrifugal force element has an essentially identical position in the radial direction both when the machine tool is at a standstill and when the machine is rotating.
- a positive connection between the tool and the fastening device can be provided by axially acting force means when the machine is at a standstill, this positive connection being secured and / or stabilized during operation by the action of the centrifugal force device.
- a continuous and uniform, axially directed force during operation of the tool can thus also be provided, since the force reversal from the centrifugal force to the axially directed force for clamping the tool can take place essentially without movement.
- the centrifugal force element cannot build up high kinetic energy, which accordingly does not have to be reduced. Furthermore, since the centrifugal element is biased in the same direction in which the centrifugal force acts, a continuous transfer of power from an operational rest area to a work operation is ensured.
- any tool which is designed to interact with one of the fastening devices according to the invention.
- this comprises a circular disk-shaped tool body, which has a central opening for attachment to a machine tool and at least one, in particular radially inwardly facing, closure surface of a closure that can be actuated without a tool, with which the tool can be brought into a form-fit with the fastening device and the tool body is axially secured and is held in a rotationally fixed manner.
- the tool according to the invention can have a cam control, which is designed such that when the tool is rotated relative to the fastening device in order to establish a closed position between the tool and the fastening device, a cam over a surface that has a control surface with at least two Ramps can be performed, with at least one projection of the fastening device being axially raised and lowered axially to support the tool on the fastening device against a mechanical force.
- the cam of the cam control can either be on
- the control surface is located either on the tool or on the fastening device.
- the tool according to the invention can in particular be a cutting, thrust, diamond, brush, polishing or flap disc.
- a tool according to the invention can be characterized in that the at least closure surface is characterized by a partially is provided, which furthermore has a means for axially guiding a cam during the clamping process on the at least one projection on the fastening device.
- a pure rotary movement during the clamping process for the tool with a torque reduction can be converted into an axial displacement of the support to the at least one projection on the fastening device. This enables manual clamping of the tool even against large axial preloads, for example against axially acting springs with a large spring constant.
- the invention is based on the idea of designing a quick clamping of a tool on a machine tool in a particularly secure manner by the axial distance between the support for the tool and the at least one radial projection which is necessary for setting a positive connection between the fastening device and the tool Fastening device is kept low and / or it is ensured that an additional force is generated on the tool during operation, in particular when external forces such as braking or tipping forces occur, which holds the tool down on the support, thus maintaining the positive engagement described and can be stabilized.
- the term “radially outward projection” comprises a section or a region of the fastening device which, when the closure is closed, that is, in the closed position, overlaps a section or an area of the tool which provides the said closed surface.
- a plurality of radially outwardly projecting projections on the fastening device are preferably provided for the closure, each of which overlaps an associated, radially inwardly directed closure surface of the tool, so that an essentially rotationally symmetrical axial fixation of the tool can be achieved.
- the components providing the positive locking should preferably be arranged symmetrically on the tool and on the fastening device.
- a symmetrical application of the driving force to the tool and thus a symmetrical generation of an axially directed force on the tool can be provided in that several drivers are provided for transmitting the driving force to the tool.
- drivers can be spaced circumferentially, in particular on an annular flange which is rigidly connected to the support, each driver having its drive surface oriented obliquely to the axis on an assigned drive surface of the
- the direct connection of the support and the driver has the advantage that the drivers press the tool directly onto the support without the need to transmit power via other components. To achieve an optimal pressure distribution and a stable position, everyone lies
- Carrier with its drive surface on its associated drive surface of the tool can take any convenient form to provide the drive torque transmission. It may be sufficient if the driver extends a few millimeters relative to the height of the support of the tool, whereby the drive surface preferably runs radially.
- the at least one centrifugal force element can expediently have a radially outwardly extending cone or wedge surface which, in the case of a non-rotating machine tool, that is to say in an idle operating position by a radially acting force means such as a correspondingly arranged spring in contact with an associated cone or wedge surface of an axially movable one Be brought segment that is operatively connected to the at least one projection of the fastening device.
- a radially acting force means such as a correspondingly arranged spring in contact with an associated cone or wedge surface of an axially movable one Be brought segment that is operatively connected to the at least one projection of the fastening device.
- the at least one projection of the fastening device is rigidly connected to the segment which bears on the assigned surface of the centrifugal force element.
- a particularly wear-free transmission can be achieved if the centrifugal force element has a radially outer conical surface, in particular at an angle of 45 ° to the axis, which bears against an associated conical surface of the axially movable segment, so that both surfaces essentially extend over their entire extent touch.
- conical surfaces for force deflection is advantageous in the present case, since the components are constructed in a rotationally symmetrical manner and thus a large surface area with conical surfaces can be provided.
- the centrifugal force element is positively guided immovably in the axial direction and the associated cone segment is positively guided immovably in the direction perpendicular to the axis of the fastening device. Accordingly, the centrifugal force element can only move in the radial direction and the cone segment can only move in the axial direction, so that a motion coupling is designed such that if a centrifugal force does not occur on the centrifugal force, force element and a relative axial movement of the at least one projection away from the support of the tool, the centrifugal force element moves radially inward, this movement being counteracted by a force means described above, such as a spring.
- a fastening device with a particularly low overall height, it can be provided that it comprises a base element that has the support for the tool and an annular element that can be inserted axially into the base part and that can be displaced axially relative to this, on its outer casing a plurality of circumferentially spaced, radially outwards Pointing projections are arranged, which, as described above, overlap the closure surfaces of the tool in a closed position in order to form a positive connection with the tool.
- a plurality of circumferentially spaced cone segments can be formed on the inner surface of the ring element, each with a radially extending contact surface, which cooperates with one of the described radially outer surfaces of a centrifugal force element.
- a plurality of circumferentially spaced flange segments are formed on the inner jacket of the ring element, in which axially acting force means such as springs for clamping the tool in the fastening device are supported. It can thus be achieved that even when the fastening device is at rest, a holding or clamping force is provided to maintain the positive connection between the tool and the fastening device, for example if the
- Machine tool is transported with the tool clamped.
- the gap on the ring element which is formed by two circumferentially adjacent cone, wedge or flange segments, into one with the base element. ment rigidly connected, extensively extended and extending in the axial direction engaging web. This web thus forms a positive guide for the ring element in the base element.
- the ring element is therefore carried along by the base element during a rotation and is axially displaceable against the spring force and / or the centrifugal force.
- angle grinders Due to the usual high centrifugal forces, angle grinders are operated at 13,000 revolutions / min, but an axial displacement of the centrifugal force element inwards and thus a loosening of the positive connection between tool and fastening device can be reliably prevented.
- the ring element In order to seal the ring element from the base element, it can be provided that the ring element has a circumferential groove for receiving a seal against the base element. In order to prevent the ring element from hitting the bottom of the base element when the tool is not clamped, it can be provided that the ring element is supported on the drivers on the base element.
- the base element must therefore be rigidly connected to the machine tool in order to transmit the drive torque of the machine to the drivers.
- the fastening device according to the invention is designed in such a way that the axial displaceability between the support of the fastening device, which is necessary for adjusting the form fit between the tool and the fastening device, can be sensed by the radially outwardly pointing projection.
- this has a radially extended cam of a cam control which extends towards the machine tool and has a front and a rear contact surface.
- Projection of the fastening device can be provided that a horizontally extending web extends from the cam in the direction of rotation to an associated driver. In this way, the projection can be supported on the driver when the tool is not clamped.
- the construction described is particularly advantageous because the axial displaceability of the projection to the support, that is to say here the ring element to the base element, can compensate for fluctuations in thickness of the tool, so that a positive fit is nevertheless provided between the fastening device and the tool, which is secured by the application of the axial force for clamping the tool during operation of the machine.
- An extremely advantageous fastening device can be provided by combining the two specified solutions, i.e. not only has at least one driver running obliquely to the axis, but also the specified centrifugal force device.
- the means for axially guiding the cam during the clamping process has an obliquely designed first ramp that runs away from the machine tool and behind the first ramp in the direction of rotation a second ramp formed obliquely in the plane perpendicular to the axis and running towards the machine tool.
- the control surface designed in this way ensures that during the clamping process, which takes the form of a pure rotation of the tool to the fastening device, the axial distance between the support surface and the projection is first increased and then decreased again.
- the special design of the first ramp which serves as a ramp, means that the projection on the fastening device is increased axially by the axial extension of the ramp exactly specified and further determined by its circumferential extension, the torque to be applied manually against the axially acting power means. Accordingly, a torque reduction can be provided, which makes it possible to use very strong axially acting force means in the fastening device, which, even without the support of the operating forces described, in the axial direction keep the tool in a form-fitting manner with the fastening device. It goes without saying that the advantageous torque reduction described can also be provided if the control surface, as indicated above, is arranged on the fastening device and thus the cam to be guided is arranged on the tool.
- the first ramp of the control surface is designed at the same time as a drive surface interacting with a driver, via which the motor torque can be transmitted to the tool.
- the first ramp with an angle between 25 ° and 45 °, preferably 30 °, in a plane perpendicular to the axis, the second ramp advantageously having an angle of ⁇ 30 °.
- the segment on the tool in the direction of rotation at its circumferential end has a web over the radial width, which provides a cover for the positive connection and extends axially to the end face that the Machine tool is turned away.
- the front boundary surface of the web in the direction of rotation can expediently be designed in such a way that an air flow is generated which enables the abrasive particles to be blown off from the quick-action clamping system during its operation.
- this web can be used to provide connection means for a cover which can be connected to the tool on the end face facing away from the machine tool, as a result of which a particularly advantageous dust protection can be provided.
- the at least one segment on the tool which provides the at least one closure surface of the tool, can either be formed directly on the tool body or else on a support device which is provided in an opening of the tool body and is fastened to it.
- the carrying device can be made of plastic and can be securely attached to a tool body using an adhesive process.
- the support device can also be made of metal and pressed, for example, during the manufacture of the tool body.
- the advantageous method according to the invention for tool-free clamping of a tool is characterized in that after the tool and the fastening device have been brought together axially in a conventional manner, the axial distance between the support surface and the projection on the fastening device is not increased by the fact that in the axial direction an axial force must be applied to the support by pressing on the tool. Instead, an axial displacement is generated by a pure rotary movement by means of a force redirection by the axial distance between the two
- the cam When turning to produce a locking position via a cam control between the tool and the fastening device, the cam is advantageously guided over a control surface with at least two ramps, with at least one projection of the fastening device being axially raised and lowered again against a mechanical force means for supporting the tool on the fastening device becomes.
- the cam is guided continuously over the control surface during the entire clamping process, so that the cam control also for the unclamping process, i.e. releasing the tool from the fastening device can be used.
- a relative rotation of the tool relative to the fastening device can be generated in a simple manner, which is opposite to that during clamping.
- Embodiment a cam on the tool via a control surface on the fastening device.
- the cam can be attached to a projection on the fastening device, the control surface being arranged on the closure surface of the tool.
- the control surface can be arranged on the projection of the fastening device, while the cam is arranged on the closure surface of the tool.
- Fig. ' 1 in an exploded view a first fastening device according to the invention together with the associated tool
- FIG. 2 is a top view of the fastening device shown in FIG. 1,
- FIG. 3 is a sectional view taken along line A-A of the fastener shown in FIG. 2;
- FIG. 4 is a sectional view along line B-B of the fastening device shown in FIG. 2,
- FIG. 5 is a sectional view taken along the line C-C of the fastening device shown in FIG. 2,
- FIG. 6a shows a base element of the fastening device according to the invention in a perspective view
- 6c shows the detail of a carrier web on the base element
- 7c is an enlarged view of the structure of a partially circumferential projection on the ring element
- 10a is a top view of a carrying device of a tool designed according to the invention.
- FIG. 11 is an exploded view of a second embodiment of a fastening device according to the invention with associated tool
- FIG. 12 shows the fastening device shown in FIG. 11 in assembly in a top view
- Fig. 13 shows the fastening device shown in Fig. 12 in a sectional view along the line A-A.
- the fortified cleaning device comprises as essential components a base element 3, a ring element 4, four centrifugal elements 5, each of which supports two springs 6 and a cover 7 which can be screwed onto the base element 3.
- screws 8 extend through the cover in threaded bores 310 on the base element.
- the spindle of the machine tool extends through a central opening 320 beyond the cover 7, which has a circumferential depression 710 at its central opening, into which the nut has a circumferential cone directed towards the machine tool for centering the entire device on the machine tool intervenes.
- the base element 3 has four cylinder segment webs 330, circumferentially spaced apart at an angle of 90 °, which taper radially inwards and merge into a socket part 340 of the base element.
- the cylinder segment webs 330 and the bushing part 340 extend to the bottom 350 of the base element 3.
- Four driver webs 370 extend on a flange 360 which is axially raised relative to the bottom and are circumferentially spaced at an angle of 90 °.
- the webs extend in the axial direction by a few millimeters, in the present case by 5 millimeters.
- the driver webs In the direction of rotation S, the driver webs have a drive surface 372 arranged obliquely to the axis, via which the drive torque of the machine is transmitted to the tool 2.
- the drive surfaces are arranged radially for optimal transmission of the force, that is, they are parallel to a radius of the device.
- a circumferential gap is formed between the cylinder segment webs 330 and the axial extension of the flange 360 down to the machine tool, into which the ring element 4 can be inserted.
- the ring element points on the inner jacket of the base element 3 directed end four cone segments 420, a circumferential gap being formed between each two adjacent cone segments, into which the cylinder segment webs 330 engage when the base element 3 is brought together, so that the ring element is connected in a rotationally fixed manner to the base element and is therefore carried along by it.
- the ring element has a degree of freedom in the base element, ie in the axial direction.
- the latter has a circumferential groove 430 in the axial height of the cone segments, into which an x-seal, not shown, is introduced.
- the axial extension of the cylinder segment webs 330 is greater than the axial extension of the cone segments 420, which are flush with the bottom of the cylinder segment 4.
- the axial displaceability of the ring element which is necessary for setting the closed position between the tool and the fastening device, can be made very small in the design according to the invention, and can be, for example, two to four millimeters.
- a centrifugal force element 5 is provided in each case for a cone segment 420, which element lies against the cone segment with a cone surface that extends radially outwards.
- the centrifugal force element lies with its lower boundary surface 520 on the bottom 350 of the base element and with its upper boundary surface 520 on the underside of the cover 7. This ensures that the centrifugal force elements 5 are independent of the position of the ring element. mentes 4 can essentially not move axially, but only radially.
- the centrifugal force elements On the side surface 540 facing the axis and arranged parallel to it, the centrifugal force elements each have two blind holes into which a spring 6 is introduced, which extends outward from the blind hole.
- the dimension of the spring is such that it is supported in every operating position by a flat side surface 380 of the socket part of the base element 3.
- the described design ensures that the centrifugal force elements 5 are coupled in motion to the ring element 4 in every operating position and that a means for deflecting the force is also provided. Since the centrifugal force elements rest under spring force on the cone segments 420 of the ring part, an axially directed force acts downwards towards the base element even in the rest position. In the case of a non-rotating base element, the ring element 4 can be moved upward against the spring force of the springs 6 away from the support 390 on the base element on which the tool 2 rests.
- FIG. 2 shows the fastening device shown in FIG. 1 in the assembled state in a top view in the event that a tool 2 is clamped in the fastening device.
- a protective hood 9 which has a horizontally running flange and an axially extending jacket surface, is clipped onto the tool 2 in order to cover the radial section in the region of the projections 410 and the closure segments 210.
- the protective hood 9 shown in FIG. 2 can also be integrally formed on the tool or the carrying device of the tool.
- Fig. 3 shows the fastening device shown in Fig. 1 with the tool clamped in a sectional view along the line A-A, wherein a spindle 11 is shown, to which the fastening device is fastened via the nut 10.
- the tool 2 lies on the support 390 of the base part, wherein in the illustrated locking position the locking segments 210 pointing axially inwards are overlapped by projections 410 pointing radially outwards.
- the centrifugal force elements lie with their conical surfaces on the associated conical surfaces of the segments on the ring element, as a result of which the tool 2 is held down with a spring force in the rest position.
- the protective hood 9 already described first runs horizontally inwards and then extends axially downwards with a sealing lip 910 supported on the cover 7.
- Fig. 4 shows the fastening device shown in Fig. 2 with clamped tool in a sectional view along the line B-B.
- the screws 8 can be seen, which are screwed into the threaded bore 310 of the base part 3 and with which the cover 7 is fastened to the base element.
- the drawing shows the sealing of the ring element 4 with the seal 440 in the region of cylinder segment webs 330.
- FIG. 5 shows a section along the line CC from FIG. 2, that is to say in a radial region in which, when the tool is clamped in, a form fit between the outwardly pointing projections 410 of the fastening device and the radially inwardly facing closure surface 220 of the tool, which is provided by a closure segment 210 is set.
- the specified form fit also lies in each case a driver web 370 of the base element on a drive surface 230 of the locking segment for transmitting the drive torque to the tool.
- the projection 410 has a braking surface 411 which bears on a correspondingly designed surface of the tool and which absorbs the braking forces which occur on the tool.
- FIG. 6 shows the base element 3 in a perspective view (a) and a bottom view (b) which has already been shown, FIG. 6 showing the structure of a driving web 370 in detail in a side view.
- a central recess 355 in the form of a rectangle is formed on the underside of the base 350 of the base element 3, into which a correspondingly designed driver of the spindle of the machine tool engages, see for example FIG. 4.
- FIG. 6 c the design of a driver web 370 with its associated drive surface 372 is shown, which lies flat against the drive surface 230 of the tool.
- the angle of the drive surfaces to the axis is 45 °.
- FIG. 7 the ring element 4 is shown again in a perspective view (a) and also in a view from the underside (b), in FIG. 7 c) a lateral sectional view of the structure of a structure which extends radially outwards Projection is shown as part of the tool-free closure.
- the cone segments 420 extend to the end face of the ring element 4.
- the design according to the invention on the underside, that is to say in the direction of the tool of the circumferentially extending projections 410, is shown in the illustrations in FIGS. 7 b) and c).
- the projections On the side facing the tool, the projections each have a cam 411, which is designed for the clamping process for driving over an assigned locking surface of the tool.
- a horizontal web 413 is arranged opposite to the direction of rotation, with which web When the tool is not clamped, the projection is supported on an associated driver web 370, see FIG. 5.
- the braking surface 411 shown in FIG. 7 for transmitting a braking torque from the tool to the ring element has an angle of 30 ° in the present case.
- the cover 7 of the fastening device according to the invention is shown in different perspectives.
- the cover is designed essentially flat on its underside, so that the centrifugal force elements 5 rest against it and, as described, are positively guided in the radial direction.
- the lid 9 shows different views of the dirt hood 9. On its underside, this has circumferentially equidistantly spaced and axially extending pins 920 which can be inserted into suitably arranged holes 260 on the locking segments 210 of the tool, see FIG. 1.
- the lid 9 can advantageously be made of a transparent plastic that is elastic is so that the sealing lip 910 can be integrally formed on the cover.
- the cover is made of a transparent material and, in addition, a convex elevation 930, which has the function of a lens, is formed circumferentially adjacent to the pins.
- these lenses are arranged such that they allow a view of the contact of the respective projection 411 with the associated closure segment 210, as a result of which an optical control of the closure position between the tool and the fastening device is provided.
- closure segments designed according to the invention with the closure surface which cooperates with the projection on the fastening device to provide a positive fit, can be designed directly on the tool body or also on a carrying device which supports the tool body carries.
- FIG. 10 shows an example of such a carrying device, which is constructed similarly to that shown in FIG. 1.
- 10 a) shows a top view
- FIGS. 10 b) or c) show a sectional view along the line A-A or B-B.
- the tool 2 each has a closure segment 210 which also extends in the direction of the projection 410 of the ring element a structured closure surface 220.
- This closure surface 220 comprises a first ramp 230, which at the same time is designed as a drive surface for abutment against a driver web 370 and accordingly has an angle to the horizontal of 45 ° and is designed to increase axially. After reaching an axial maximum, the surface drops axially again in a second ramp 240.
- this ramp has an angle of 30 ° to the horizontal and serves as an abutment for the braking surface 411 of the cam 412, see FIG. 5.
- the angle of the second ramp is kept lower in comparison to the first ramp, so that a worn tool is still can easily be braced by the fastening device. It should be taken into account that a worn tool generally has a smaller diameter, so that the user can develop a lower torque when unclamping with the same amount of force compared to clamping. This disadvantage is compensated for by the lower slope of the second ramp.
- FIG. 11 shows an embodiment of the fastening device of the invention which does not require a centrifugal force device, that is to say the operating force for holding down the tool is achieved solely by the inclined contact of the drivers 370 on the drive surface 230 of the locking segment 210 of the tool reached.
- a form fit is only realized during operation, that is to say when the fastening device rotates.
- the tool can only be held securely on its support by the occurrence of an additional axial force, either caused by the carrier webs or by the flying force device and the carrier webs.
- a plurality of springs 13 are provided which are supported on the cover 7 and press on horizontal segments 450 which extend radially inwards and circumferentially on the inside of the ring element 4. Since the further structure of the fastening device shown in FIG. 11 is essentially identical to that of the one shown in FIG. 1, reference can be made to the first embodiment with regard to the further structure and the mode of operation.
- FIGS. 12 and 13 show a top view and a sectional illustration of the fastening device shown in FIG. 11, reference being made to FIG. 13 to the springs 13 which are clearly visible in section and which rest on the horizontal segments 450 and thus hold the ring element down, with which the tool 2 is held on its support 390.
- a tool designed according to the invention can be brought into a closed position with the fastening device according to the invention by bringing the tool with its locking segments into the circumferential gaps between the projections of the fastening device, here the ring element, and placing it on the support 390. Now the tool and the fastening device are moved relative to one another, for example the tool against the direction of rotation of the machine tool with the fastening device held. It should be noted that the user does not have to apply any direct axial force during the clamping process.
- the cam strikes the Fastening device against the first ramp on the tool, which as a result of the further rotation has the result that the cam of the projection is moved upwards on the first ramp of the tool, as a result of which the ring element is axially displaced in the same way.
- the cam runs down on the second ramp due to the axially acting spring force, as a result of which the cam comes to lie in a radially inwardly open pocket, which passes through the second ramp and the web of the locking segment, see FIG. 5.
- This position of the cams relative to the locking segments in the locking position corresponds to a positive locking which is secured by the occurrence of the axially directed operating forces as described.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
- Gripping On Spindles (AREA)
- Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
- Automatic Tool Replacement In Machine Tools (AREA)
- Paper (AREA)
- Portable Nailing Machines And Staplers (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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DE10308223 | 2003-02-25 | ||
DE10308223A DE10308223A1 (de) | 2003-02-25 | 2003-02-25 | Befestigungseinrichtung und zugeordnetes Werkzeug |
PCT/DE2004/000345 WO2004076123A2 (de) | 2003-02-25 | 2004-02-25 | Befestigungseinrichtung und zugeordnetes werkzeug |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1597023A2 true EP1597023A2 (de) | 2005-11-23 |
EP1597023B1 EP1597023B1 (de) | 2008-10-29 |
Family
ID=32891795
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04714263A Expired - Lifetime EP1597023B1 (de) | 2003-02-25 | 2004-02-25 | Befestigungseinrichtung und zugeordnetes werkzeug |
Country Status (6)
Country | Link |
---|---|
US (1) | US20070293380A1 (de) |
EP (1) | EP1597023B1 (de) |
AT (1) | ATE412491T1 (de) |
DE (2) | DE10308223A1 (de) |
ES (1) | ES2320889T3 (de) |
WO (1) | WO2004076123A2 (de) |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7343841B2 (en) | 2002-02-15 | 2008-03-18 | Black & Decker Inc. | Blade clamp assembly |
EP1782917A1 (de) * | 2005-11-08 | 2007-05-09 | sia Abrasives Industries AG | Aufnahme für ein Schleifwerkzeug, Schleifwerkzeug und Tragkörper für ein Schleifwerkzeug |
US8992113B2 (en) * | 2009-06-08 | 2015-03-31 | Re2, Inc. | Robust manual connector for robotic arm end effector |
US8382177B2 (en) * | 2009-06-11 | 2013-02-26 | Re2, Inc. | Quick-change finger for robotic gripper |
US8408974B2 (en) * | 2009-07-14 | 2013-04-02 | Black & Decker Inc. | Adapter for abrasive cutting wheels |
WO2011019742A1 (en) | 2009-08-10 | 2011-02-17 | Re2, Inc. | Automated tool change assembly for robotic arm |
AT510920B1 (de) * | 2010-12-15 | 2014-01-15 | Gissing Gerhard | Vorrichtung umfassend ein rotierend antreibbares werkzeug und ein aufspannelement |
JP5701405B2 (ja) * | 2011-12-16 | 2015-04-15 | 豊田バンモップス株式会社 | 砥石車の取付装置 |
JP5701406B2 (ja) * | 2011-12-16 | 2015-04-15 | 豊田バンモップス株式会社 | 砥石車の取付装置 |
KR101483963B1 (ko) * | 2014-11-25 | 2015-01-20 | 김창성 | 핸드 그라인더의 연마디스크 탈,부착장치 |
DE102017213669A1 (de) * | 2016-08-22 | 2018-02-22 | Robert Bosch Gmbh | Werkzeugeinrichtung für eine Handwerkzeugmaschine |
US10596680B2 (en) * | 2017-01-16 | 2020-03-24 | E&Q One-Tough Co., Ltd. | Hand grinder and method of coupling grinding disc of hand grinder |
JP6918535B2 (ja) * | 2017-03-22 | 2021-08-11 | キヤノン株式会社 | ロボット装置、交換ツール、ロボットアーム、ロボット装置を用いた物品の製造方法、ロボット装置の制御方法、制御プログラムおよび記録媒体 |
CN108747821A (zh) * | 2018-06-27 | 2018-11-06 | 盐城市久恒工贸有限公司 | 一种用于砂布轮快速安装的安装底座 |
JP7356948B2 (ja) | 2020-04-10 | 2023-10-05 | スガツネ工業株式会社 | 回転支持装置 |
JP7418270B2 (ja) | 2020-04-10 | 2024-01-19 | スガツネ工業株式会社 | 回転支持装置 |
EP3960384A1 (de) | 2020-08-28 | 2022-03-02 | Black & Decker Inc. | Luftansaugkonfiguration in einem elektrowerkzeug |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
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FR2063429A5 (de) * | 1969-10-14 | 1971-07-09 | Cybeo Aldigero | |
US4657428A (en) * | 1985-09-10 | 1987-04-14 | Wiley Edward R | Quick change mechanism for circular saw blades and other spinning disc devices |
US4787147A (en) * | 1986-08-28 | 1988-11-29 | Wiley Edward R | Quick change mechanism for diamond arbor circular saw blades and other spinning disc devices using radially sliding locks |
DE4129090A1 (de) * | 1991-09-02 | 1993-03-04 | Rueggeberg August Fa | Schleifscheibe |
SE510981C2 (sv) * | 1996-05-07 | 1999-07-19 | Atlas Copco Tools Ab | Portabel slipmaskin med utbytbar slitdel |
DE29923017U1 (de) * | 1999-12-30 | 2000-02-24 | Koenig J Gmbh & Co Werkzeugfab | Vorrichtung zum lösbaren Befestigen eines Schleifkörpers an einer Schleifmaschine |
DE10017458A1 (de) * | 2000-04-07 | 2001-10-18 | Bosch Gmbh Robert | Schleifmaschinenwerkzeugaufnahme |
DE10030586A1 (de) * | 2000-06-21 | 2002-01-10 | Bruno Schmitz Schleifmittelwer | Werkzeug |
DE20205495U1 (de) * | 2001-06-21 | 2002-08-01 | Bruno Schmitz Schleifmittelwer | Befestigungseinrichtung, Spannsystem und zugeordnetes Werkzeug |
DE102004061871B4 (de) * | 2004-12-22 | 2007-05-31 | Erwin Junker Maschinenfabrik Gmbh | Spannvorrichtung mit Zentriervorrichtung an einem Schleifspindelrotor und Rotationsteil mit einer derartigen Zentriervorrichtung |
US7147550B2 (en) * | 2005-05-10 | 2006-12-12 | Sunmatch Industrial Co., Ltd. | Holding apparatus for grinding members |
US7578730B2 (en) * | 2007-10-10 | 2009-08-25 | Sunmatch Industrial Co., Ltd. | Grinding brush fixing device |
US7465222B1 (en) * | 2007-12-10 | 2008-12-16 | Storm Pneumtic Tool Co., Ltd. | Grinding wheel |
-
2003
- 2003-02-25 DE DE10308223A patent/DE10308223A1/de not_active Ceased
-
2004
- 2004-02-25 AT AT04714263T patent/ATE412491T1/de not_active IP Right Cessation
- 2004-02-25 ES ES04714263T patent/ES2320889T3/es not_active Expired - Lifetime
- 2004-02-25 DE DE502004008345T patent/DE502004008345D1/de not_active Expired - Lifetime
- 2004-02-25 EP EP04714263A patent/EP1597023B1/de not_active Expired - Lifetime
- 2004-02-25 WO PCT/DE2004/000345 patent/WO2004076123A2/de active Application Filing
- 2004-02-25 US US10/547,433 patent/US20070293380A1/en not_active Abandoned
Non-Patent Citations (1)
Title |
---|
See references of WO2004076123A2 * |
Also Published As
Publication number | Publication date |
---|---|
EP1597023B1 (de) | 2008-10-29 |
WO2004076123A3 (de) | 2004-11-25 |
US20070293380A1 (en) | 2007-12-20 |
ES2320889T3 (es) | 2009-05-29 |
DE502004008345D1 (de) | 2008-12-11 |
DE10308223A1 (de) | 2004-09-23 |
WO2004076123A2 (de) | 2004-09-10 |
ATE412491T1 (de) | 2008-11-15 |
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