EP1216117B1 - Motor-powered portable grinding machine - Google Patents
Motor-powered portable grinding machine Download PDFInfo
- Publication number
- EP1216117B1 EP1216117B1 EP01960139A EP01960139A EP1216117B1 EP 1216117 B1 EP1216117 B1 EP 1216117B1 EP 01960139 A EP01960139 A EP 01960139A EP 01960139 A EP01960139 A EP 01960139A EP 1216117 B1 EP1216117 B1 EP 1216117B1
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- EP
- European Patent Office
- Prior art keywords
- eccentric
- rolling face
- braking
- sander according
- braking member
- 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
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- 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
- B24B23/00—Portable grinding machines, e.g. hand-guided; Accessories therefor
- B24B23/02—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor
- B24B23/03—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor the tool being driven in a combined movement
Definitions
- the invention relates to a motor-driven hand grinding machine, in particular eccentric disc grinding machine, according to the preamble of claim 1.
- the first rolling surface is formed as an outer toothed ring, which rotates with the driven grinding disc about the axis thereof
- the second rolling surface is formed of an inner toothed ring on an outer ring gear, which is rotationally fixed relative to the machine housing and axially is adjustable by means of an external actuating device between an inoperative position and a functional position cooperating with the first rolling surface. In the inoperative position, the second rolling surface is disengaged from the first rolling surface.
- the second rolling surface extends approximately in the same diametrical plane as the first rolling surface, so that the first rolling surface can roll on the second rolling surface during rotation of the grinding plate, so that the eccentric movement of the grinding plate is superimposed on this rotating about the eccentric axis movement ,
- the second rolling surface is in the functional position, increased workpiece abrasion can be achieved.
- the disadvantage of this hand grinder that the changeover between idle and positive drive not during operation of the hand grinder is possible. In the axial Relatiwerschiebung may result in the teeth of both Wälzvid damage. A disadvantage is also caused by this arrangement of the rolling surfaces relatively large height of the grinding machine.
- the EP 573 916 A1 discloses an eccentric disc grinding machine with a mounted in the machine housing work spindle and driven by this to an eccentric and rotatable sanding pad unit and with a rotating together with the sanding pad around the eccentric axis annular first rolling surface of an outer gear ring on the one hand and one of these associated annular second Wälz Chemistry on the other hand, the central axis coaxial extends to the central axis of the work spindle and at which the first rolling surface can roll, wherein the second rolling surface is rotatably mounted about a central axis in a bearing and this second rolling surface is associated with a braking device by means of a rotation of the second rolling surface about its central axis selectively suppressed or is releasable.
- the DE 199 52 108 A discloses a generic Exzentertellerschleifmaschine with a mounted in the machine housing work spindle and a driven by this to an eccentric and rotatable sanding pad and with a together with the sanding pad around the eccentric rotating circumferential first Wälz Chemistry an outer toothed ring on the one hand and an associated second annular Wälz Chemistry on the other hand, the central axis is coaxial with the central axis of the work spindle and at which the first rolling surface can roll, the second rolling surface is rotatably mounted about a central axis in a bearing and this second rolling surface is associated with a braking device by means of a rotation of the second rolling surface about its central axis selectively can be prevented or released, wherein the braking device has a trained as a brake band brake member having a braking surface for blocking the second rolling surface.
- Object of the present invention is to improve the band brake so that they can absorb higher forces faster. This problem is solved by the features of claim 1.
- the motor-driven hand grinder according to the invention in particular Exzentertellerschleifmaschine, with the features of claim 1 has the advantage that a switch between freewheel and forced driving during operation of the hand grinder without the risk of damage is possible and results in a reduced height with low gear costs.
- Another advantage is that the brake member to the machine housing in a first position in which it is in a form-locking engagement with the second rolling surface, and in a second position in which it is in no engagement with the second rolling surface.
- the braking device it is particularly advantageously possible for the braking device to be switchable between the first and second positions and vice versa in all operating states, in particular during idling, standstill and under load.
- the braking member is a band with a plurality of teeth, in particular a toothed belt, which can be brought into engagement with a ring gear of the second rolling surface. Compared to a pure friction occurs here no slip between the braking device and the second rolling surface. As a result, wear of the two interlocking parts is avoided and prevents heat generation.
- the brake member is designed as an elastic band, in particular as a toothed rim.
- the switching from freewheel to forced driving is easy and with little tolerance affected by such an elastic intermediate coupling.
- the actuating device actuates a brake member, z. B. hand-operated, eccentric lever with an eccentric acting on the brake member.
- the eccentric lever can be pivotally mounted in the machine housing and eccentric having an eccentric pin, which in an opening, for. B. in a loop at the end of the braking member, in particular a brake band, which wraps around the outer peripheral surface of the outer ring gear engages.
- the eccentric lever has a handle located outside of the machine housing for pivoting operation. It may be advantageous in this case that the eccentric lever is designed such that a tensioning of the brake band takes place by means of a pivoting about a circumferential angle of about 180. The handle of the eccentric lever can thus be easily pivoted between two positions when passing through a circumferential angle of 180 and thus the changeover between positive drive and freewheel are also made during operation of the hand grinder.
- the outer toothed ring is part, in particular one-piece part, the sanding pad unit, z. B. integral part of the grinding plate itself, on which the outer toothed ring is molded. This is particularly simple and inexpensive and contributes to a reduction in height additionally.
- the inner toothed ring of the outer ring gear has a larger number of teeth than the outer toothed ring.
- the number of teeth difference can z. B. 2 amount. This ensures that is driven in the setting forced drive the sanding disc with a predetermined speed. Is z. B. the number of oscillations 10,000, so results in teeth ratio of 50:48 in the positive drive a grinding disc speed of 417 U / min.
- the sanding pad unit coupled to the work spindle, in particular rotatably connected sleeve with a z. B. end eccentric and a held on the latter by means of a bearing sanding pad on; the z. B. is releasably connected by means of a screw with the eccentric pin.
- the outer ring gear has a bearing ring located along the central axis at an axial distance from the inner toothed ring and is rotatably mounted with the bearing ring by means of a bearing with respect to the sleeve coaxial with the axis of the work spindle.
- the camp can z. B. be pressed onto the sleeve, wherein the outer ring gear is pressed with its bearing ring on the outer ring of the bearing.
- a fan of an inner dust extraction is mounted on the sleeve.
- the fan can also sit directly against rotation on the work spindle and have an eccentric with respect to the spindle axis sleeve in which by means of a bearing a cylindrical sleeve for end-side mounting of the grinding plate is rotatably mounted.
- the sleeve is formed with end-side eccentric pin of a sintered part and thus designed particularly inexpensive. It may also be advantageous if the outer ring gear is formed from a light metal or zinc die-cast part, whereby a cost-effective design is also realized.
- the sanding pad with the one-piece, the first rolling surface forming outer toothed ring is formed from a one-piece plastic injection molded part, whereby a further cost reduction and simplification is achieved.
- the brake member in particular the elastic element, is rotatably connected to the machine housing at a fixing point about a fixed axis of rotation.
- the brake member is rotatably connected to the machine housing at a fixing point about a fixed axis of rotation.
- the braking device has a latching lever which is connected via a spring element to the machine housing, in particular when the spring element attempts to press the latching lever in a position in which the elastic element assumes its first position.
- the brake member is made of resilient material and having a first molded portion with a toothing, which is engageable with the outer peripheral surface engageable and a second molded portion, wherein the brake member is held by a bias in its first position and in its second position by an actuator bringbar.ist.
- a simple part for example a stamped part
- a simple operation with low operating force is possible by such a configuration.
- This design also acts as overload protection for forced operation and as a torsional shock. It requires only a small space requirement; In addition, a compensation of Division errors of the transmission part, for example, by the same, allows.
- the latching lever is displaceable by an eccentric pin which is rotatably mounted on the machine housing and can be operated by means of the protruding from the machine housing actuator.
- switching between the two positions of the elastic member is very easy for the operator without having to turn off the power, no matter what operating condition it is in, d. H. both in freewheeling mode (fine grinding) and in forced driving mode (rough grinding).
- the fixing point and the eccentric pin with respect to the central axis are substantially diametrically opposite and the angle between the fixing point and the teeth of the elastic member, which are in the first position in engagement with the second rolling surface, greater than 90 ° is. This prevents locking under load.
- the fixing point and the eccentric pin with respect to the central axis substantially diametrically opposite and strengthen the cooperating surfaces of the braking member and the second rolling surface under load, similar to a servo effect, the holding force.
- a large holding force is generated with little effort, whereby the reliability of the device is increased.
- the braking device in all operating states, in particular in idle, standstill and under load, between the first and second position and vice versa is switchable. As a result, it is not necessary to switch over from one operating state to another in order to enable the switching between the first and second position. This results in time savings and greater operator comfort.
- Fig. 1 schematically a first embodiment of a motor-driven hand grinder 10 is shown, which is designed here as Exzentertellerschleifmaschine.
- the hand grinder 10 has a total of 11 designated machine housing containing an electric drive motor 12 with work spindle 13, the means of a bearing 14, z. B. in the form of a ball bearing, is mounted in the machine housing 11.
- a designated generally 15 sanding pad unit is rotatably connected, which is driven by means of the work spindle 13 to an eccentric movement and is rotatable.
- the sanding pad unit 15 has a sleeve 16 which is rotatably and axially connected to the work spindle 13.
- the sleeve 16 extends coaxially to the central axis 17 of the work spindle 13 and has z. B. on in Fig. 1 lower end of an eccentric pin 18, the eccentric axis 19 with eccentricity e to the central axis 17 and parallel to this.
- On the eccentric pin 18 is by means of a bearing 20, z. B. a ball bearing, a sanding plate 21 rotatably mounted.
- the sanding pad 21 is by means of a to the eccentric axis 19 coaxial screw 22 which is screwed into the eccentric pin 18, axially fixed but rotatably connected to the sleeve 16 and the eccentric pin 19 and can be detached by loosening the screw 22.
- the hand grinder 10 is equipped with an internal dust extraction, to which a fan 24 is rotatably held on the sleeve 16.
- the fan 24 is located in a chamber 25 to which a Staubabsaugkanal 26 is connected.
- the sanding pad 21 is provided with channels and / or openings 27 for internal dust extraction.
- the hand grinding machine 10 has an annular first rolling surface 28 which revolves around the eccentric axis 19 together with the sanding pad unit 15 and which is designed here as an outer toothed ring 29.
- This outer toothed ring 29 may in an embodiment, not shown, an independent component, for. B. gear, represent, which is rotatably connected to the sleeve 16.
- the toothed ring 29 in a particularly simple manner part, in particular one-piece part, the sanding pad unit 15, and in this case in particular the sanding pad 21, which is advantageously formed in this one-piece design of a plastic injection molded part.
- the first rolling surface 28, in particular the outer toothed ring 29, is associated with an annular second rolling surface 30 which surrounds the first rolling surface 28 and whose center axis is coaxial with the central axis 17 of the work spindle 13.
- the second rolling surface 30 is preferably designed as an inner toothed ring 31 of an outer ring gear 32.
- the second rolling surface 30, in particular the outer ring gear 32 carrying it, is rotatably mounted about the central axis 17.
- the outer ring gear 32 has along the central axis 17 at an axial distance from the inner toothed ring 31 arranged bearing ring 33 of smaller diameter over which the outer ring gear 32 by means of a bearing 34, for. B. a ball bearing, is rotatably mounted on the sleeve 16 relative to this.
- the inner ring of the bearing 34 is rotatably connected to the sleeve 16, while the outer ring of the bearing 34 rotatably connected to the bearing ring 33 and thus to the outer rim 32.
- the second rolling surface 30 is associated with a generally designated 35 braking device by means of which a rotation of the second rolling surface 30 about its central axis, d. H. about the central axis 17, either can be prevented or released.
- the arrangement is such that the rotatability of the second rolling surface 30, in particular of the outer ring gear 32, by means of the braking device 35 during machine operation can be prevented or released.
- the outer ring gear 32 is designed as a one-piece component and is advantageously made of achtmetalltikgussteil.
- the sleeve 16 with end-side eccentric pin 18 is advantageously formed from a sintered part.
- the fan 24 is rotatably on the sleeve 16 as part of the internal dust extraction arranged.
- the fan 24 is instead formed on a fan sleeve which is rotatably mounted on the work spindle 13 and having an eccentric to the central axis 17 inner sleeve in which by means of a eccentric axis 19 coaxial bearing a cylindrical sleeve similar the sleeve 16 is rotatably and axially fixed, is releasably secured to the end of the sanding pad 21 by means of the screw 22.
- the braking device 35 has a braking member 36 which acts in a braking manner on the second rolling surface 30 and an actuating device 37 for actuating the brake member 36.
- the braking member 36 is provided with a braking surface 38, with which the braking member 36 can engage flat on the rotational blocking of the second rolling surface 30 on an associated surface 39 of the second rolling surface 30, said surface 39 is formed in particular as the outer surface of the outer ring gear 32.
- the second rolling surface 30 extends outside and surrounds the first rolling surface 28, wherein both extend substantially within a common, diametrical to the central axis 17 of the work spindle 13 level.
- the outer surface designed surface 39 of the second rolling surface 30 consists in particular of the outer peripheral surface 40 of the outer ring gear 32nd
- the brake member 36 generally consists of such a brake member which may abut with its designed as a braking surface 38 inside of the associated surface 39 of the second rolling surface 30, in particular on the outer peripheral surface 40 of the outer ring gear 32, for rotational blocking.
- the brake member 36 consists of a brake band, that wraps around the outer peripheral surface 40 of the outer ring gear 32 and can be clamped against the outer peripheral surface 40 for rotational blocking.
- the actuator 37 has an eccentric lever, which has a pivotally mounted in the machine housing 11 central part 41 and an eccentric pin 42 thereon, in an opening 43, z. B. a loop, engages one end of the brake band designed as a braking member 36.
- a located outside of the machine housing 11 handle 44 engages the pivoting operation.
- This actuating device 37 in the form of an illustrated eccentric lever, is designed such that a clamping of the braking member 36 designed as a brake band takes place by means of a pivoting of the central part 41 by a circumferential angle of approximately 180 °.
- the tensioned position and thus the rotation-locked state of the outer ring gear 32 is in Fig. 3 shown.
- the actuator 37 has a brake member 36 z. B. in the form of a brake band, in particular the brake band exciting, magnets, z. B. a controllable electromagnet.
- the inner toothed ring 31 of the outer ring gear 32 has a larger number of teeth than the outer toothed ring 29.
- the number of teeth difference can z. B. 2 amount. This causes that when braked Outer ring gear 32 of the rolling on the inner toothed ring 31 outer toothed ring 29 rotates per 180 ° eccentric movement by one tooth and thus with respect to the provided with the outer toothed ring 29 grinding plate 21, a speed of this rolling arises.
- the speed of the grinding plate 21 is at an assumed vibration number of 10,000 and a teeth ratio of 50:48 z. B. 417 rpm.
- the outer ring gear 32 is freely rotatable about the central axis 17 due to the storage by means of the bearing 34 on the sleeve 16.
- the outer ring gear 32 can now rotate due to the friction in the bearing 34.
- the speed of the sanding pad 21 depends on the load on the pad, ie how firmly fixed the hand grinder 10 with the sanding pad 21 and a detachable thereto, z , B. by means of Velcro, attached abrasive sheet is pressed against a workpiece to be machined.
- the speed of the grinding plate 21 can also be zero depending on the circumstances. At this stage results for the hand grinder 10 of the freewheeling operation.
- the described hand grinder 10 is simple, compact and inexpensive. It allows in a simple manner by lever actuation or in another, not shown embodiment by actuation of a magnet during operation of the machine switching to a continuous transition from forced driving to freewheel. Because of the outer- ⁇ ere Toothed ring 29 is molded onto a ring part of the grinding plate 21 as a one-piece part, there is the advantage of reduced components and low overall height. Also advantageous is the low cost of the implementation of the Abdozenslzgetriebes, consisting of outer ring gear 29 and inner ring gear 31st
- FIG. 5 schematically a second embodiment of a motor-driven hand grinder 10 is shown.
- the drive of the sanding pad unit 15 as well as this sanding pad unit 15 itself are in principle the same as those of the first embodiment.
- a work spindle 13 is rotatably driven by a drive motor 12, not shown, about a central axis 17.
- the work spindle 13 has an eccentric pin 18.
- Concentric about the eccentric axis 19 a first rolling surface 28 is formed, which engages with its outer toothed ring 29 in an inner toothed ring 31 of a second rolling surface 30, which is arranged concentrically about the central axis 17 around.
- the grinding plate unit 15 is connected via a coaxial screw 22 to an output shaft 4, which is arranged coaxially around the eccentric axis 19.
- the outer peripheral surface 40 of the second rolling surface 30 is not substantially smooth, but has a ring gear 8.
- the brake member 36 is formed as an elastic member 7 and with teeth 2, in contrast to the substantially smooth brake member 36 of the first embodiment, which are opposite to the ring gear 8.
- Fig. 6 the spatial arrangement between the teeth 2, which are formed on the side opposite the sprocket 8 side of the elastic member 7, well recognizable.
- the elastic element 7 is shown here in its second position, in which its teeth 2 are not in engagement with the ring gear 8 of the second rolling surface 30. As a result, the second rolling surface 30 can run free in this decoupled position.
- the sanding pad 21 performs only a swinging movement and a slight rotational movement, depending on the bearing friction in the bearing 20.
- the hand grinder 10 is thus in fine grinding mode. The higher the bearing friction, the stronger the rotational movement.
- the elastic element 7 has at its one end a fixing point 3, which is connected via a fixed axis of rotation 5 with the machine housing 11.
- the elastic element 7 is formed as a locking lever 6.
- the detent lever 6 is actuated by means of an eccentric pin 1, which is connected to an actuating device 37 (not shown) according to the first embodiment.
- the locking lever 6 is constantly pressed by a spring element 9, which is supported on the machine housing 11 against the eccentric pin 1.
- the teeth 2 on the elastic element 7 are formed closer to the locking lever 6 than at the fixing point 3.
- the fixing point 3 and the locking lever 6 are arranged substantially diametrically to the central axis 17. This means for the angle ⁇ between the fixing point 3 and the teeth 2, that it is greater than 90 °.
- Fig. 7 the elastic element 7 is shown in its first position.
- the teeth 2 of the elastic element 7 engage in a form-fitting manner in the ring gear 8 on the outer circumferential surface 40 of the second rolling surface 30.
- the oscillatory movement of the sanding plate 21 is thereby imposed a rotational movement. Due to the positive engagement between the teeth 2 and the ring gear 8, there is no slip between the braking device 35 and the second rolling surface 30, so that the wear and the heat development goes to zero.
- the engagement between the teeth 2 and the sprocket 8 is during the transition from the second position ( Fig. 6 ) to the first position ( Fig.
- the operator thus has the opportunity to switch from a fine-grained mode to a rough-cut mode via a selector lever without having to switch off the machine.
- the switching from freewheel to Zwangsmit Vietnamese is described by an elastic intermediate coupling in all operating conditions, d. H. Idling, standstill and under load, switchable.
- the switchover is also simple and with low tolerance.
- Fig. 8 is elastic element 7 formed in a particularly easy to implement embodiment. It is shown in its first position.
- the elastic member 7 is formed as a molded part of spring steel, which is substantially circular arc-shaped. At its first end 51, it is in a torsion spring joint 50, which is rigidly formed with the machine housing (not shown).
- the elastic element 7 has a first shaped region 45, which is formed as a toothing 46. In the illustrated embodiment, these are two teeth. But there are just as a single tooth as well as more than two teeth, for example, three or four teeth possible.
- the elastic element 7 is clamped in the torsion-spring joint 50 in such a way that due to its spring force with its toothing 46 it presses against the ring gear 8 of the outer peripheral surface 40 of the second rolling surface 30.
- the ring gear 8 engages in the toothing 46 of the elastic element 7 a.
- This form-fitting connection can be achieved by exerting a force 49 on the second end 48 of the elastic element 7, which releases the catch by moving the toothing 46 away from the ring gear 8. This is done against the spring force of the elastic member 7 due to its restraint in the torsion spring joint 50.
- the elastic Element 7 has a second shaped region 47 in addition to the first molded region 45. This second shaped region 47 has a tangential elasticity and thus serves as torsional shock suspension.
- Such an embodiment of the braking device 35 is very simple and inexpensive. It can be very easily operated with the application of low actuation force and further has a rotation shock absorption and overload protection for forced operation. In addition to the advantage of a small footprint can be compensated by them division errors of the gear part, which are caused for example by wear.
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Abstract
Description
Die Erfindung geht aus von einer motorgetriebenen Handschleifmaschine, insbesondere Exzentertellerschleifmaschine, nach der Gattung des Anspruchs 1.The invention relates to a motor-driven hand grinding machine, in particular eccentric disc grinding machine, according to the preamble of claim 1.
Es ist eine Handschleifmaschine dieser Art bekannt (
Die
Die
Aufgabe der vorliegenden Erfindung ist es, die Bandbremse derart zu verbessern, dass sie schneller höhere Kräfte aufnehmen kann. Gelöst wird diese Aufgabe durch die Merkmale des Anspruchs 1.Object of the present invention is to improve the band brake so that they can absorb higher forces faster. This problem is solved by the features of claim 1.
Die erfindungsgemäße motorgetriebene Handschleifmaschine, insbesondere Exzentertellerschleifmaschine, mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass eine Umschaltung zwischen Freilauf und Zwangsmitnahme während des Betriebs der Handschleifmaschine ohne die Gefahr einer Beschädigung möglich ist und sich eine reduzierte Bauhöhe bei geringem getrieblichen Aufwand ergibt.The motor-driven hand grinder according to the invention, in particular Exzentertellerschleifmaschine, with the features of claim 1 has the advantage that a switch between freewheel and forced driving during operation of the hand grinder without the risk of damage is possible and results in a reduced height with low gear costs.
Ein weiterer Vorteil ist, dass das Bremsglied zum Maschinengehäuse in einer ersten Position, in der es mit der zweiten Wälzfläche in einem formschlüssigen Eingriff steht, und in einer zweiten Position festlegbar ist, in der es mit der zweiten Wälzfläche in keinem Eingriff steht. Besonders vorteilhaft ist es dadurch möglich, dass die Bremseinrichtung in allen Betriebszuständen, insbesondere im Leerlauf, Stillstand und unter Last, zwischen der ersten und zweiten Position und umgekehrt schaltbar ist.Another advantage is that the brake member to the machine housing in a first position in which it is in a form-locking engagement with the second rolling surface, and in a second position in which it is in no engagement with the second rolling surface. In this way, it is particularly advantageously possible for the braking device to be switchable between the first and second positions and vice versa in all operating states, in particular during idling, standstill and under load.
Besonders vorteilhaft ist es dabei, dass das Bremsglied ein Band mit mehreren Zähnen ist, insbesondere ein Zahnriemen, die mit einem Zahnkranz der zweiten Wälzfläche in Eingriff bringbar sind. Gegenüber einem reinen Reibschluss tritt hier kein Schlupf zwischen der Bremseinrichtung und der zweiten Wälzfläche ein. Dadurch wird ein Verschleiß der beiden ineinandergreifenden Teile vermieden und eine Wärmeentwicklung unterbunden.It is particularly advantageous that the braking member is a band with a plurality of teeth, in particular a toothed belt, which can be brought into engagement with a ring gear of the second rolling surface. Compared to a pure friction occurs here no slip between the braking device and the second rolling surface. As a result, wear of the two interlocking parts is avoided and prevents heat generation.
Besonders vorteilhaft ist es, dass das Bremsglied als ein elastisches Band, insbesondere als ein Zahnrlemen, ausgebildet ist. Das Umschalten von Freilauf zur Zwangsmitnahme ist durch eine solche elastische Zwischenkupplung einfach und mit wenig Toleranz behaftet möglich.It is particularly advantageous that the brake member is designed as an elastic band, in particular as a toothed rim. The switching from freewheel to forced driving is easy and with little tolerance affected by such an elastic intermediate coupling.
Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen motorgetriebenen Handschleifmaschine möglich.The measures listed in the further claims advantageous refinements and improvements of claim 1 motor-driven hand grinder are possible.
Gemäß einer vorteilhaften Ausführungsform weist die Betätigungseinrichtung einen das Bremsglied betätigenden, z. B. handbetätigbaren, Exzenterhebel mit einem auf das Bremsglied wirkenden Exzenter auf.According to an advantageous embodiment, the actuating device actuates a brake member, z. B. hand-operated, eccentric lever with an eccentric acting on the brake member.
Hierbei kann der Exzenterhebel schwenkbar im Maschinengehäuse gelagert sein und als Exzenter einen exzentrischen Zapfen aufweisen, der in eine Öffnung, z. B. in eine Schlaufe, am Ende des Bremsgliedes, insbesondere eines Bremsbandes, das die äußere Umfangsflache des Außenzahnkranzes umschlingt, eingreift.Here, the eccentric lever can be pivotally mounted in the machine housing and eccentric having an eccentric pin, which in an opening, for. B. in a loop at the end of the braking member, in particular a brake band, which wraps around the outer peripheral surface of the outer ring gear engages.
Bei einer weiteren vorteilhaften Ausführungsform weist der Exzenterhebel eine außerhalb des Maschinengehäuses befindliche Handhabe zur Schwenkbetätigung auf. Vorteilhaft kann es dabei sein, dass der Exzenterhebel derart gestaltet ist, dass ein Spannen des Bremsbandes mittels einer Schwenkung um einen Umfangwinkel von etwa 180 erfolgt. Die Handhabe des Exzenterhebels kann somit leicht zwischen zwei Positionen bei Durchlaufen eines Umfangswinkels von 180 geschwenkt werden und damit die Umstellung zwischen Zwangsantrieb und Freilauf auch während des Betriebes der Handschleifmaschine vorgenommen werden.In a further advantageous embodiment, the eccentric lever has a handle located outside of the machine housing for pivoting operation. It may be advantageous in this case that the eccentric lever is designed such that a tensioning of the brake band takes place by means of a pivoting about a circumferential angle of about 180. The handle of the eccentric lever can thus be easily pivoted between two positions when passing through a circumferential angle of 180 and thus the changeover between positive drive and freewheel are also made during operation of the hand grinder.
Bei einer weiteren vorteilhaften Ausführungsform der Erfindung ist der äußere Zahnring Teil, insbesondere einstückiger Teil, der Schleiftellereinheit, z. B. einstückiger Bestandteil des Schleiftellers selbst, an dem der äußere Zahnring angespritzt ist. Dies ist besonders einfach und kostengünstig und trägt zu einer Reduzierung der Bauhöhe zusätzlich bei.In a further advantageous embodiment of the invention, the outer toothed ring is part, in particular one-piece part, the sanding pad unit, z. B. integral part of the grinding plate itself, on which the outer toothed ring is molded. This is particularly simple and inexpensive and contributes to a reduction in height additionally.
Gemäß einer weiteren vorteilhaften Ausführungsform weist der innere Zahnring des Außenzahnkranzes eine größere Zähnezahl als der äußere Zahnring auf. Die Zähnezahldifferenz kann z. B. 2 betragen. Hierdurch wird erreicht, dass in der Einstellung Zwangsantrieb der Schleifteller mit einer dadurch vorgegebenen Drehzahl angetrieben wird. Beträgt z. B. die Schwingzahl 10 000, so ergibt sich bei Zähnezahlverhältnis von 50:48 im Zwangsantrieb eine Schleiftellerdrehzahl von 417 U/min.According to a further advantageous embodiment, the inner toothed ring of the outer ring gear has a larger number of teeth than the outer toothed ring. The number of teeth difference can z. B. 2 amount. This ensures that is driven in the setting forced drive the sanding disc with a predetermined speed. Is z. B. the number of oscillations 10,000, so results in teeth ratio of 50:48 in the positive drive a grinding disc speed of 417 U / min.
Gemäß einer weiteren vorteilhaften Ausführungsform weist die Schleiftellereinheit eine mit der Arbeitsspindel gekuppelte, insbesondere drehfest verbundene, Hülse mit einem z. B. endseitigen Exzenterzapfen und einen auf letzterem mittels eines Lagers gehaltenen Schleifteller auf; der z. B. mittels einer Schraube lösbar mit dem Exzenterzapfen verbunden ist.According to a further advantageous embodiment, the sanding pad unit coupled to the work spindle, in particular rotatably connected sleeve with a z. B. end eccentric and a held on the latter by means of a bearing sanding pad on; the z. B. is releasably connected by means of a screw with the eccentric pin.
Vorteilhaft kann es ferner sein, wenn der Außenzahnkranz einen entlang der Mittelachse in axialem Abstand vom inneren Zahnring befindlichen Lagerring aufweist und mit dem Lagerring mittels eines Lagers in Bezug auf die zur Achse der Arbeitsspindel koaxiale Hülse, drehbar gelagert ist. Das Lager kann z. B. auf die Hülse aufgepresst sein, wobei der Außenzahnkranz mit seinem Lagerring auf den Außenring des Lagers aufgepresst ist.It may also be advantageous if the outer ring gear has a bearing ring located along the central axis at an axial distance from the inner toothed ring and is rotatably mounted with the bearing ring by means of a bearing with respect to the sleeve coaxial with the axis of the work spindle. The camp can z. B. be pressed onto the sleeve, wherein the outer ring gear is pressed with its bearing ring on the outer ring of the bearing.
Bei einer weiteren vorteilhaften Ausführung ist auf der Hülse ein Lüfterrad einer inneren Staubabsaugung befestigt. Alternativ dazu kann das Lüfterrad auch unmittelbar drehfest auf der Arbeitsspindel sitzen und eine in Bezug auf die Spindelachse exzentrische Hülse aufweisen, in der mittels eines Lagers eine zylindrische Hülse zur endseitigen Halterung des Schleiftellers drehbar gelagert ist.In a further advantageous embodiment, a fan of an inner dust extraction is mounted on the sleeve. Alternatively, the fan can also sit directly against rotation on the work spindle and have an eccentric with respect to the spindle axis sleeve in which by means of a bearing a cylindrical sleeve for end-side mounting of the grinding plate is rotatably mounted.
Bei einer weiteren vorteilhaften Ausführungsform ist die Hülse mit endseitigem Exzenterzapfen aus einem Sinterteil gebildet und damit besonders kostengünstig gestaltet. Von Vorteil kann es ferner sein, wenn der Außenzahnkranz aus einem Leichtmetall- oder Zinkdruckgussteil gebildet ist, wodurch ebenfalls eine kostengünstige Gestaltung verwirklicht ist.In a further advantageous embodiment, the sleeve is formed with end-side eccentric pin of a sintered part and thus designed particularly inexpensive. It may also be advantageous if the outer ring gear is formed from a light metal or zinc die-cast part, whereby a cost-effective design is also realized.
Bei einer anderen vorteilhaften Ausführungsform ist der Schleifteller mit dem damit einstückigen, die erste Wälzfläche bildenden äußeren Zahnring aus einem einstückigen Kunststoffspritzteil gebildet, wodurch eine weitere Kostenreduzierung und Vereinfachung erreicht ist.In another advantageous embodiment, the sanding pad with the one-piece, the first rolling surface forming outer toothed ring is formed from a one-piece plastic injection molded part, whereby a further cost reduction and simplification is achieved.
Bevorzugt ist das Bremsglied, insbesondere das elastische Element, an einem Fixierpunkt um eine feste Drehachse rotierbar mit dem Maschinengehäuse verbunden. Dadurch ist es beim Bewegen des elastischen Elements zwischen der ersten und zweiten Position nicht nötig, das elastische Band zu knicken, was einen geringen Verschleiß bedeutet.Preferably, the brake member, in particular the elastic element, is rotatably connected to the machine housing at a fixing point about a fixed axis of rotation. Thereby, when moving the elastic member between the first and second positions, it is not necessary to buckle the elastic band, which means little wear.
Vorteilhaft ist es, wenn die Bremseinrichtung einen Rasthebel aufweist, der über ein Federelement mit dem Maschinengehäuse verbunden ist, insbesondere wenn das Federelement versucht, den Rasthebel in eine Position zu drücken, in der das elastische Element seine erste Position einnimmt. Eine solche Ausgestaltung ist mechanisch einfach zu realisieren und trotzdem genügend stabil, so dass es zu keiner Fehlbedienung kommt.It is advantageous if the braking device has a latching lever which is connected via a spring element to the machine housing, in particular when the spring element attempts to press the latching lever in a position in which the elastic element assumes its first position. Such a design is mechanically simple to implement and still sufficiently stable, so that there is no maloperation.
Weiterhin ist es vorteilhaft, wenn das Bremsglied aus federelastischem Material ist und einen ersten ausgeformten Bereich mit einer Verzahnung aufweist, der mit der äußeren Umfangsfläche in Eingriff bringbar ist und einen zweiten ausgeformten Bereich, wobei das Bremsglied durch eine Vorspannung in seiner ersten Position gehalten wird und in seine zweite Position durch eine Betätigungseinrichtung bringbar.ist. Dadurch ist es möglich, ein einfaches Teil, beispielsweise ein Stanzteil, als Bremsglied zu verwenden. Somit ergibt sich eine kostengünstige Lösung. Außerdem ist durch eine solche Ausgestaltung eine einfache Betätigung mit geringer Betätigungskraft möglich. Diese Ausgestaltung wirkt gleichzeitig als Überlastungsschutz für den Zwangsbetrieb und als Drehstoßabfederung. Sie benötigt nur einen geringen Platzbedarf; zusätzlich wird ein Ausgleich von Teilungsfehlern des Getriebeteils, beispielsweise durch Verschleiß desselben, ermöglicht.Furthermore, it is advantageous if the brake member is made of resilient material and having a first molded portion with a toothing, which is engageable with the outer peripheral surface engageable and a second molded portion, wherein the brake member is held by a bias in its first position and in its second position by an actuator bringbar.ist. This makes it possible to use a simple part, for example a stamped part, as a braking member. This results in a cost-effective solution. In addition, a simple operation with low operating force is possible by such a configuration. This design also acts as overload protection for forced operation and as a torsional shock. It requires only a small space requirement; In addition, a compensation of Division errors of the transmission part, for example, by the same, allows.
Weiterhin ist es vorteilhaft, wenn der Rasthebel durch einen Exzenterbolzen verschiebbar ist, der drehbar am Maschinengehäuse gelagert ist und mittels der aus dem Maschinengehäuse herausragenden Betätigungseinrichtung bedienbar ist. Somit ist ein Umschalten zwischen den beiden Positionen des elastischen Elements sehr einfach für den Bediener möglich, ohne dass er das Gerät ausschalten muss, egal in welchem Betriebszustand es sich gerade befindet, d. h. sowohl im Freilaufbetrieb (Feinschliff) als auch im Zwangsmitnahmebetrieb (Grobschliff).Furthermore, it is advantageous if the latching lever is displaceable by an eccentric pin which is rotatably mounted on the machine housing and can be operated by means of the protruding from the machine housing actuator. Thus, switching between the two positions of the elastic member is very easy for the operator without having to turn off the power, no matter what operating condition it is in, d. H. both in freewheeling mode (fine grinding) and in forced driving mode (rough grinding).
Weiterhin ist es vorteilhaft, wenn sich der Fixierpunkt und der Exzenterbolzen bezüglich der zentrischen Achse im wesentlichen diametral gegenüber liegen und der Winkel zwischen Fixierpunkt und den Zähnen des elastischen Elements, die in der ersten Position in Eingriff mit der zweiten Wälzfläche sind, größer als 90° ist. Dadurch wird ein Überrasten unter Belastung verhindert.Furthermore, it is advantageous if the fixing point and the eccentric pin with respect to the central axis are substantially diametrically opposite and the angle between the fixing point and the teeth of the elastic member, which are in the first position in engagement with the second rolling surface, greater than 90 ° is. This prevents locking under load.
Weiterhin ist es vorteilhaft, wenn sich der Fixierpunkt und der Exzenterbolzen bezüglich der zentrischen Achse im wesentlichen diametral gegenüberliegen und die zusammenwirkenden Flächen vom Bremsglied und der zweiten Wälzfläche unter Belastung, ähnlich einem Servoeffekt, die Haltekraft verstärken. Dadurch wird mit geringem Aufwand eine große Haltekraft erzeugt, wodurch die Zuverlässigkeit der Vorrichtung vergrößert wird.Furthermore, it is advantageous if the fixing point and the eccentric pin with respect to the central axis substantially diametrically opposite and strengthen the cooperating surfaces of the braking member and the second rolling surface under load, similar to a servo effect, the holding force. As a result, a large holding force is generated with little effort, whereby the reliability of the device is increased.
Des weiteren ist es vorteilhaft, wenn die Bremseinrichtung in allen Betriebszuständen, insbesondere im Leerlauf, Stillstand und unter Last, zwischen der ersten und zweiten Position und umgekehrt schaltbar ist. Dadurch muß nicht erst von einem Betriebszustand in einen anderen umgeschaltet werden, um die Schaltung zwischen erster und zweiter Position zu ermöglichen. .Dies führt zu einer Zeitersparnis und zu einem größeren Komfort für den Bediener.Furthermore, it is advantageous if the braking device in all operating states, in particular in idle, standstill and under load, between the first and second position and vice versa is switchable. As a result, it is not necessary to switch over from one operating state to another in order to enable the switching between the first and second position. This results in time savings and greater operator comfort.
Weitere Vorteile und Einzelheiten der Erfindung sind Gegenstand der Unteransprüche.Further advantages and details of the invention are the subject of the dependent claims.
Die Erfindung ist anhand zweier in den Zeichnungen dargestellter Ausführungsbeispiele im folgenden näher beschrieben. Es zeigen:
- Fig. 1
- einen schematischen Schnitt durch ein erstes Ausführungsbeispiel einer Handschleifmaschine,
- Fig. 2
- eine schematische Draufsicht von Teilen einer Brems-einrichtung der Handschleifmaschine in der Ebene II-II in
Fig. 1 , - Fig. 3
- einen schematischen, teilweisen Schnitt entlang der Linie III-III in
Fig. 1 , - Fig. 4
- eine schematische Unteransicht von Teilen der Handschleifmaschine in Pfeilrichtung IV in
Fig. 1 ohne Schleifteller, - Fig. 5
- einen schematischen Schnitt durch ein zweites Ausführungsbeispiel einer Handschleifmaschine,
- Fig. 6
- einen schematischen Schnitt entlang der Linie A-A in
Fig. 5 , wobei sich die Bremseinrichtung nicht in Eingriff mit der zweiten Wälzfläche befindet, - Fig. 7
- einen schematischen Schnitt wie in
Fig. 6 , wobei sich die Bremseinrichtung in Eingriff mit der zweiten Wälzfläche befindet und - Fig. 8
- eine schematische Teilansicht eines dritten Ausführungsbeispiels einer Bremseinrichtung.
- Fig. 1
- a schematic section through a first embodiment of a hand grinder,
- Fig. 2
- a schematic plan view of parts of a brake device of the hand grinder in the plane II-II in
Fig. 1 . - Fig. 3
- a schematic, partial section along the line III-III in
Fig. 1 . - Fig. 4
- a schematic bottom view of parts of the hand grinder in the direction of arrow IV in
Fig. 1 without sanding pad, - Fig. 5
- a schematic section through a second embodiment of a hand grinder,
- Fig. 6
- a schematic section along the line AA in
Fig. 5 , wherein the braking device is not in engagement with the second rolling surface, - Fig. 7
- a schematic section as in
Fig. 6 , wherein the braking device is in engagement with the second rolling surface and - Fig. 8
- a schematic partial view of a third embodiment of a braking device.
In
Die Handschleifmaschine 10 weist eine zusammen mit der Schleiftellereinheit 15 um die Exzenterachse 19 umlaufende ringförmige erste Wälzfläche 28 auf, die hier als äußerer Zahnring 29 ausgebildet ist. Dieser äußere Zahnring 29 kann bei einem nicht gezeigten Ausführungsbeispiel ein eigenständiges Bauteil, z. B. Zahnrad, darstellen, das drehfest mit der Hülse 16 verbunden ist. Beim gezeigten Ausführungsbeispiel ist der Zahnring 29 in besonders einfacher Weise Teil, insbesondere einstückiger Teil, der Schleiftellereinheit 15, und hierbei insbesondere des Schleiftellers 21, der in dieser einstückigen Gestaltung mit Vorteil aus einem Kunststoffspritzteil gebildet ist. Der ersten Wälzfläche 28, insbesondere dem äußeren Zahnring 29, ist eine ringförmige zweite Wälzfläche 30 zugeordnet, die die erste Wälzfläche 28 umringt und deren Mittelachse koaxial zur zentrischen Achse 17 der Arbeitsspindel 13 verläuft. An der zweiten Wälzfläche 30 kann sich die erste Wälzfläche 28 bei eingeschaltetem Antriebsmotor 12 abwälzen. Die zweite Wälzfläche 30 ist mit Vorzug als innerer Zahnring 31 eines Außenzahnkranzes 32 ausgebildet. Die zweite Wälzfläche 30, insbesondere der diese tragende Außenzahnkranz 32, ist um die zentrische Achse 17 drehbar gelagert. Beim gezeigten ersten Ausführungsbeispiel weist der Außenzahnkranz 32 einen entlang der zentrischen Achse 17 in axialem Abstand vom inneren Zahnring 31 angeordneten Lagerring 33 kleineren Durchmessers auf, über den der Außenzahnkranz 32 mittels eines Lagers 34, z. B. eines Kugellagers, auf der Hülse 16 relativ zu dieser drehbar gelagert ist. Der Innenring des Lagers 34 ist drehfest mit der Hülse 16 verbunden, während der Außenring des Lagers 34 drehfest mit dem Lagerring 33 und damit mit dem Außenkranz 32 verbunden ist.The
Der zweiten Wälzfläche 30 ist eine allgemein mit 35 bezeichnete Bremseinrichtung zugeordnet, mittels der eine Drehung der zweiten Wälzfläche 30 um ihre Mittelachse, d. h. um die zentrische Achse 17, wahlweise unterbindbar bzw. freigebbar ist. Dabei ist die Anordnung so getroffen, dass die Drehbarkeit der zweiten Wälzfläche 30, insbesondere des Außenzahnkranzes 32, mittels der Bremseinrichtung 35 während des Maschinenbetriebes unterbindbar bzw. freigebbar ist.The
Der Außenzahnkranz 32 ist als einstückiges Bauteil gestaltet und besteht mit Vorteil aus einem Leichtmetalldruckgussteil. Die Hülse 16 mit endseitigem Exzenterzapfen 18 ist mit Vorteil aus einem Sinterteil gebildet.The
Beim gezeigten ersten Ausführungsbeispiel ist das Lüfterrad 24 als Teil der inneren Staubabsaugung auf der Hülse 16 drehfest angeordnet. Bei einem anderen, nicht gezeigten Ausführungsbeispiel ist statt dessen das Lüfterrad 24 an einer Lüfterhülse ausgebildet, die drehfest auf der Arbeitsspindel 13 angeordnet ist und die eine zur zentrischen Achse 17 exzentrische Innenhülse aufweist, in der mittels eines zur Exzenterachse 19 koaxialen Lagers eine zylindrische Hülse ähnlich der Hülse 16 drehbar und axial fest gehalten ist, an der endseitig der Schleifteller 21 mittels der Schraube 22 lösbar befestigt ist.In the first embodiment shown, the
Die Bremseinrichtung 35 weist ein auf die zweite Wälzfläche 30 bremsend einwirkendes Bremsglied 36 und eine Betätigungseinrichtung 37 zum Betätigen des Bremsgliedes 36 auf. Das Bremsglied 36 ist mit einer Bremsfläche 38 versehen, mit der das Bremsglied 36 flächig zum Drehblockieren der zweiten Wälzfläche 30 an einer zugeordneten Fläche 39 der zweiten Wälzfläche 30 angreifen kann, wobei diese Fläche 39 insbesondere als Außenfläche des Außenzahnkranzes 32 ausgebildet ist. Die zweite Wälzfläche 30 verläuft außen und umringt die erste Wälzfläche 28, wobei sich beide im Wesentlichen innerhalb einer gemeinsamen, zur zentrischen Achse 17 der Arbeitsspindel 13 diametralen Ebene erstrecken. Die als Außenfläche gestaltete Fläche 39 der zweiten Wälzfläche 30 besteht insbesondere aus der äußeren Umfangsfläche 40 des Außenzahnkranzes 32.The
Das Bremsglied 36 besteht ganz allgemein aus einem solchen Bremsteil, der mit seiner als Bremsfläche 38 ausgebildeten Innenseite an der zugeordneten Fläche 39 der zweiten Wälzfläche 30, insbesondere an der äußeren Umfangsfläche 40 des Außenzahnkranzes 32, zur Drehblockierung anliegen kann. In besonders einfacher Gestaltung besteht das Bremsglied 36 aus einem Bremsband, das die äußere Umfangsfläche 40 des Außenzahnkranzes 32 umschlingt und zur Drehblockierung gegen die äußere Umfangsfläche 40 gespannt werden kann.The
Die Betätigungseinrichtung 37 weist einen Exzenterhebel auf, der einen im Maschinengehäuse 11 schwenkbar gelagerten zentrischen Teil 41 und einen exzentrischen Zapfen 42 daran aufweist, der in eine Öffnung 43, z. B. eine Schlaufe, an einem Ende des als Bremsband gestalteten Bremsgliedes 36 eingreift. Am zentrischen Teil 41 greift eine außerhalb des Maschinengehäuses 11 befindliche Handhabe 44 zur Schwenkbetätigung an. Diese Betätigungseinrichtung 37, in Form eines erläuterten Exzenterhebels, ist so gestaltet, dass ein Spannen des als Bremsband ausgebildeten Bremsgliedes 36 mittels einer Schwenkung des zentrischen Teils 41 um einen Umfangswinkel von ca. 180° erfolgt. Die gespannte Stellung und damit der gegen Drehung blockierte Zustand des Außenzahnkranzes 32 ist in
Bei einem anderen, nicht gezeigten Ausführungsbeispiel weist die Betätigungseinrichtung 37 einen das Bremsglied 36 z. B. in Form eines Bremsbandes betätigenden, insbesondere das Bremsband spannenden, Magneten auf, z. B. einen steuerbaren Elektromagneten.In another embodiment, not shown, the
Eine weiteren Besonderheit der Handschleifmaschine 10 liegt darin, dass der innere Zahnring 31 des Außenzahnkranzes 32 eine größere Zähnezahl als der äußere Zahnring 29 aufweist. Die Zähnezahldifferenz kann z. B. 2 betragen. Dies führt dazu, dass bei gebremstem
Außenzahnkranz 32 sich der auf dessen innerem Zahnring 31 abwälzende äußere Zahnring 29 pro 180° Exzenterbewegung um einen Zahn weiter dreht und somit hinsichtlich des mit dem äußeren Zahnring 29 versehenen Schleiftellers 21 eine Drehzahl dieses beim Abwälzen entsteht. Die Drehzahl des Schleiftellers 21 beträgt bei einer angenommenen Schwingzahl von 10 000 und einem Zähnezahlverhältnis von 50:48 z. B. 417 U/min.Another special feature of the
Ist die Bremseinrichtung 35 in Bremsstellung entsprechend
Wird nun während des Betriebes der Handschleifmaschine 10 mittels der Betätigungseinrichtung 37 das Bremsglied 36 in den nicht bremsenden Zustand gem.
Während des Betriebs der eingeschalteten Handschleifmaschine 10 kann von diesem Freilaufbetrieb durch Betätigen der Bremseinrichtung 35 wieder auf den Zwangsantrieb umgeschaltet werden.During operation of the switched-on
Die beschriebene Handschleifmaschine 10 ist einfach, kompakt und kostengünstig. Sie ermöglicht in einfacher Weise durch Hebelbetätigung oder bei einem anderen, nicht gezeigten Ausführungsbeispiel durch Betätigung eines Magneten während des Betriebs der Maschine eine Umschaltung auf einen kontinuierlichen Übergang von Zwangsmitnahme auf Freilauf. Dadurch, dass der äu-βere Zahnring 29 an einem Ringteil des Schleiftellers 21 als damit einstückiges Teil angespritzt ist, ergibt sich der Vorteil reduzierter Bauteile und geringer Bauhöhe. Vorteilhaft ist ferner der geringe Aufwand für die Verwirklichung des Abwälzgetriebes, bestehend aus äußerem Zahnring 29 und innerem Zahnring 31.The described
In
Im Unterschied zum ersten Ausführungsbeispiel ist die äußere Umfangsfläche 40 der zweiten Wälzfläche 30 nicht im wesentlichen glatt ausgeführt, sondern weist einen Zahnkranz 8 auf. Das Bremsglied 36 ist als elastisches Element 7 ausgebildet und mit Zähnen 2, im Unterschied zum im wesentlichen glatten Bremsglied 36 des ersten Ausführungsbeispiels, versehen, die dem Zahnkranz 8 gegenüberliegen.In contrast to the first embodiment, the outer
In
In
Der Bediener hat somit die Möglichkeit, über einen Schalthebel vom Feinschliff-Modus in den Grobschliff-Modus zu wechseln, ohne die Maschine ausschalten zu müssen. Das Umschalten von Freilauf zu Zwangsmitnahme ist durch eine beschriebene elastische Zwischenkupplung in allen Betriebszuständen, d. h. Leerlauf, Stillstand und unter Last, schaltbar. Die Umschaltung ist au-βerdem einfach und mit geringer Toleranz behaftet.The operator thus has the opportunity to switch from a fine-grained mode to a rough-cut mode via a selector lever without having to switch off the machine. The switching from freewheel to Zwangsmitnahme is described by an elastic intermediate coupling in all operating conditions, d. H. Idling, standstill and under load, switchable. The switchover is also simple and with low tolerance.
In
Eine solche Ausgestaltung der Bremseinrichtung 35 ist sehr einfach und kostengünstig. Sie kann unter Aufwendung geringer Betätigungskraft sehr einfach betätigt werden und weist des weiteren eine Drehstoßabfederung sowie einen Überlastungsschutz für den Zwangsbetrieb auf. Neben dem Vorteil eines geringen Platzbedarfs können durch sie Teilungsfehler des Getriebeteils, die beispielsweise durch Verschleiß bedingt sind, ausgeglichen werden.Such an embodiment of the
- 11
- Exzenterbolzeneccentric
- 22
- Zähneteeth
- 33
- Fixierpunktfixation
- 44
- Abtriebswelleoutput shaft
- 55
- feste Drehachsefixed axis of rotation
- 66
- Rasthebellocking lever
- 77
- elastisches Elementelastic element
- 88th
- Zahnkranzsprocket
- 99
- Federelementspring element
- 1010
- Handschleifmaschinehand grinder
- 1111
- Maschinengehäusemachine housing
- 1212
- Antriebsmotordrive motor
- 1313
- Antriebsspindeldrive spindle
- 1414
- Lagercamp
- 1515
- SchleiftellereinheitGrinding plate unit
- 1616
- Hülseshell
- 1717
- zentrische Achsecentric axis
- 1818
- Exzenterzapfeneccentric
- 1919
- Exzenterachseeccentric
- 2020
- Lagercamp
- 2121
- Schleiftellersanding pad
- 2222
- koaxiale Schraubecoaxial screw
- 2323
- Manschettecuff
- 2424
- Lüfterradfan
- 2525
- Kammerchamber
- 2626
- StaubabsaugkanalStaubabsaugkanal
- 2727
- Durchbrechungperforation
- 2828
- erste Wälzflächefirst rolling surface
- 2929
- äußerer Zahnringouter toothed ring
- 3030
- zweite Wälzflächesecond rolling surface
- 3131
- innerer Zahnringinner tooth ring
- 3232
- AußenzahnkranzExternal gear
- 3333
- Lagerringbearing ring
- 3434
- Lagercamp
- 3535
- Bremseinrichtungbraking means
- 3636
- Bremsgliedbraking member
- 3737
- Betätigungseinrichtungactuator
- 3838
- Bremsflächebrake surface
- 3939
- Flächearea
- 4040
- äußere Umfangsflächeouter peripheral surface
- 4141
- zentrischer Teilcentric part
- 4242
- exzentrischer Zapfeneccentric pin
- 4343
- Öffnungopening
- 4444
- Handhabehandle
- 4545
- Erster ausgeformter BereichFirst formed area
- 4646
- Verzahnunggearing
- 4747
- Zweiter ausgeformter BereichSecond shaped area
- 4848
- Zweites EndeSecond end
- 4949
- Kraftforce
- 5050
- DrehfedergelenkTorsion spring hinge
- 5151
- Erstes EndeFirst end
Claims (14)
- Eccentric sander comprising a work spindle (13) mounted in the machine housing (11) and a rotatable sanding pad unit (15) which can be driven by said work spindle (13) to perform an eccentric movement, and comprising an annular first rolling face (28) of an externally toothed ring (29) on the one hand, said first rolling face (28) revolving together with the sanding pad unit (15) about the eccentric axis (19), and an annular second rolling face (30), assigned to said first rolling face (28), on the other hand, the centre axis of which second rolling face (30) runs coaxially to the central axis (17) of the work spindle (13) and on which the first rolling face (28) can roll, wherein the second rolling face (30) is rotatably mounted about its centre axis in a bearing (34), and a braking device (35) is assigned to this second rolling face (30), by means of which braking device (35) a rotation of the second rolling face (30) about its centre axis can be optionally prevented or enabled, wherein the braking device (35) has a braking member (36) designed as a brake band and having a braking surface (38) for locking the second rolling face (30), characterized in that the braking device has a braking member (36) designed as an elastic element (7) for locking the second rolling face (30), wherein the braking member (7, 36) has a first and a second setting position in which it is in positive-locking engagement with and disengaged from the second rolling face (30), wherein it is designed as a toothed belt (7) having a plurality of teeth (2) which can be brought into engagement with and disengaged from an outer toothed rim (8) of the second rolling face (30).
- Eccentric sander according to Claim 1, characterized in that the braking device (35) has a braking member (36), which has a braking effect on the second rolling face (30), and an actuating device (37) for actuating the braking member (36).
- Eccentric sander according to either of the preceding claims, characterized in that the second rolling face (30) runs on the outside and encircles the first rolling face (28) and in that both rolling faces (28, 30) extend substantially within a common diametral plane with respect to the axis (17) of the work spindle (13).
- Eccentric sander according to one of the preceding claims, characterized in that an outer surface, in particular an outer circumferential surface (40) of the second rolling face (30), in particular of the outer toothed rim (32), is designed as a surface interacting with the braking member (36) for rotary locking.
- Eccentric sander according to one of Claims 2 to 4, characterized in that the actuating device (37) has a magnet actuating the braking member (36), in particular a controllable electromagnet, or an eccentric lever, e.g. a manually actuable eccentric lever, with an eccentric (42) which acts on the braking member (36).
- Eccentric sander according to one of Claims 2 to 5, characterized in that the braking member (36) of the braking device (35) can bear with an inner surface designed as braking surface (38) against the associated surface (39), in particular against the outer circumferential surface (40) of the outer toothed rim (32), for rotary locking.
- Eccentric sander according to one of the preceding claims, characterized in that the braking member (36), in particular the elastic element (7), is connected to the machine housing (11) at a fixing point (3) in such a way as to be rotatable about a fixed rotation axis (5).
- Eccentric sander according to one of the preceding claims, characterized in that the braking device (35) has a latching lever (6) which is connected to the machine housing (11) via a spring element (9).
- Eccentric sander according to Claim 8, characterized in that the spring element (9) attempts to press the latching lever (6) into a position in which the elastic element (7) assumes its first position.
- Eccentric sander according to one of the preceding claims, characterized in that the braking element (36) is made of an elastic material and has a first shaped region (45) having a tooth system (46), which first shaped region (45) can be brought into engagement with the outer circumferential surface (40), and a second shaped region (47), wherein the braking member (36) is held in its first position by preloading and can be brought into its second position by an actuating device (37).
- Eccentric sander according to one of the preceding claims, characterized in that the latching lever (6) can be displaced by an eccentric pin (1) which is rotatably mounted on the machine housing (11) and can be operated by means of the actuating device (37) projecting from the machine housing (11).
- Eccentric sander according to one of Claims 7 to 11, characterized in that the fixing point (3) and the eccentric pin (1) are substantially diametrically opposite one another with respect to the central axis (17), and the angle (α) between the fixing point (3) and the teeth (2) of the elastic element (7), which in the first position are in engagement with the second rolling face (39), is greater than 90°.
- Eccentric sander according to one of Claims 7 to 12, characterized in that the fixing point (3) and the eccentric pin (1) are substantially diametrically opposite one another with respect to the central axis (17), and the interacting surfaces of the braking member (36) and of the second rolling face (30), under load, amplify the retaining force, similar to a servo effect.
- Eccentric sander according to one of the preceding claims, characterized in that the braking device (35) can be switched between the first and the second positions, and vice versa, in all operating states, in particular during idling, when stopped and under load.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10047202 | 2000-09-23 | ||
DE10047202A DE10047202A1 (en) | 2000-09-23 | 2000-09-23 | Motor-driven hand grinder |
PCT/DE2001/002944 WO2002024408A1 (en) | 2000-09-23 | 2001-08-02 | Motor-powered portable grinding machine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1216117A1 EP1216117A1 (en) | 2002-06-26 |
EP1216117B1 true EP1216117B1 (en) | 2012-03-21 |
Family
ID=7657373
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01960139A Expired - Lifetime EP1216117B1 (en) | 2000-09-23 | 2001-08-02 | Motor-powered portable grinding machine |
Country Status (5)
Country | Link |
---|---|
US (1) | US6726553B2 (en) |
EP (1) | EP1216117B1 (en) |
JP (1) | JP2004508961A (en) |
DE (1) | DE10047202A1 (en) |
WO (1) | WO2002024408A1 (en) |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2406815B (en) * | 2003-10-10 | 2006-04-19 | Bosch Gmbh Robert | Eccentric hand-held grinding machine tool |
DE10357836B4 (en) * | 2003-10-10 | 2021-06-24 | Robert Bosch Gmbh | Eccentric hand machine tool |
US20050221738A1 (en) * | 2004-04-06 | 2005-10-06 | Cooper Vincent P | Orbital sander with vertical handle |
US7128641B1 (en) * | 2005-06-08 | 2006-10-31 | Gison Machinery Co., Ltd. | Grinder capable of seizing rotary shaft |
DE102005057328B3 (en) * | 2005-12-01 | 2006-12-07 | Festool Gmbh | Eccentric plate grinder for grinding workpieces has arresting head of arresting slide with two arresting projections spaced out from each other |
FI129765B (en) * | 2007-03-21 | 2022-08-15 | Oy Kwh Mirka Ab | Compact electric grinding machine |
JP5327938B2 (en) * | 2008-01-11 | 2013-10-30 | 太朗 佐藤 | Polishing method for painted metal surface |
DE102010027205A1 (en) * | 2010-07-06 | 2012-01-12 | C. & E. Fein Gmbh | hand tool |
DE102010039637A1 (en) * | 2010-08-23 | 2012-02-23 | Robert Bosch Gmbh | Hand tool with a clamping neck |
DE102010043182A1 (en) * | 2010-10-29 | 2012-05-03 | Robert Bosch Gmbh | Portable machine tool |
DE102011075222A1 (en) * | 2011-05-04 | 2012-11-08 | Robert Bosch Gmbh | Machine tool braking device |
US9291133B2 (en) | 2011-12-20 | 2016-03-22 | Caterpillar Inc. | Shaft arrangement for an axial piston pump assembly |
US8881409B2 (en) * | 2012-01-16 | 2014-11-11 | Robert Bosch Gmbh | Articulating oscillating power tool |
DE102013100085A1 (en) * | 2013-01-07 | 2014-07-10 | C. & E. Fein Gmbh | Oscillating powered machine tool |
CA2925926C (en) * | 2013-10-10 | 2021-11-16 | Arbortech Industries Limited | Tool mechanism and tools using same |
WO2015077988A1 (en) | 2013-11-29 | 2015-06-04 | Black & Decker Inc. | Sander having two-piece fan |
JP6212433B2 (en) * | 2014-05-09 | 2017-10-11 | 株式会社マキタ | Sanda |
US20160121450A1 (en) * | 2014-11-04 | 2016-05-05 | Black & Decker Inc. | Power tool counterweight arrangement and mass member |
JP7117832B2 (en) * | 2017-07-24 | 2022-08-15 | 京セラインダストリアルツールズ株式会社 | Polisher |
DE102019112556A1 (en) * | 2019-05-14 | 2020-11-19 | Ferrobotics Compliant Robot Technology Gmbh | ORBITAL GRINDING MACHINE WITH BRAKE DEVICE |
Family Cites Families (13)
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DE3625655C1 (en) * | 1986-07-29 | 1988-01-07 | Festo Kg | Eccentric disc grinder |
DE3809930A1 (en) * | 1988-03-24 | 1989-10-05 | Bosch Gmbh Robert | Eccentric grinder |
DE4206753A1 (en) * | 1992-03-04 | 1993-09-09 | Bosch Gmbh Robert | Eccentric disc grinder |
JP3063872B2 (en) * | 1992-06-08 | 2000-07-12 | 株式会社マキタ | Polishing machine |
DE4233728A1 (en) * | 1992-10-07 | 1994-04-14 | Bosch Gmbh Robert | Eccentric disc grinder |
US5580302A (en) * | 1994-02-28 | 1996-12-03 | Black & Decker Inc. | Random orbit sander having air directing baffle |
GB9423848D0 (en) * | 1994-11-25 | 1995-01-11 | Black & Decker Inc | Improved oscillating hand tool |
US5595531A (en) * | 1995-07-26 | 1997-01-21 | Ryobi North America | Random orbit sander having speed limiter |
US5595532A (en) * | 1995-10-20 | 1997-01-21 | Waxing Corporation Of America, Inc. | Electrically-powered polisher |
DE19608969A1 (en) * | 1996-03-08 | 1997-09-11 | Bosch Gmbh Robert | Electric hand grinder |
DE19617478B4 (en) * | 1996-05-02 | 2006-06-29 | Robert Bosch Gmbh | hand grinder |
US5947804A (en) * | 1998-04-27 | 1999-09-07 | Ryobi North America, Inc. | Adjustable eccentricity orbital tool |
DE19952108B4 (en) * | 1999-10-29 | 2007-09-20 | Robert Bosch Gmbh | Exzentertellerschleifmaschine |
-
2000
- 2000-09-23 DE DE10047202A patent/DE10047202A1/en not_active Ceased
-
2001
- 2001-08-02 JP JP2002528460A patent/JP2004508961A/en active Pending
- 2001-08-02 EP EP01960139A patent/EP1216117B1/en not_active Expired - Lifetime
- 2001-08-02 WO PCT/DE2001/002944 patent/WO2002024408A1/en active Application Filing
- 2001-08-02 US US10/130,051 patent/US6726553B2/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
EP1216117A1 (en) | 2002-06-26 |
DE10047202A1 (en) | 2002-04-11 |
US20020193055A1 (en) | 2002-12-19 |
WO2002024408A1 (en) | 2002-03-28 |
JP2004508961A (en) | 2004-03-25 |
US6726553B2 (en) | 2004-04-27 |
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