EP0906175B1 - Manually driven machine - Google Patents
Manually driven machine Download PDFInfo
- Publication number
- EP0906175B1 EP0906175B1 EP97942809A EP97942809A EP0906175B1 EP 0906175 B1 EP0906175 B1 EP 0906175B1 EP 97942809 A EP97942809 A EP 97942809A EP 97942809 A EP97942809 A EP 97942809A EP 0906175 B1 EP0906175 B1 EP 0906175B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tool
- shaft
- powered hand
- saw
- axial
- 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
Links
Classifications
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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
- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B27—WORKING OR PRESERVING WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES IN GENERAL
- B27B—SAWS FOR WOOD OR SIMILAR MATERIAL; COMPONENTS OR ACCESSORIES THEREFOR
- B27B5/00—Sawing machines working with circular or cylindrical saw blades; Components or equipment therefor
- B27B5/29—Details; Component parts; Accessories
- B27B5/30—Details; Component parts; Accessories for mounting or securing saw blades or saw spindles
- B27B5/32—Devices for securing circular saw blades to the saw spindle
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/929—Tool or tool with support
- Y10T83/9372—Rotatable type
- Y10T83/9377—Mounting of tool about rod-type shaft
- Y10T83/9379—At end of shaft
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T83/00—Cutting
- Y10T83/929—Tool or tool with support
- Y10T83/9457—Joint or connection
- Y10T83/9464—For rotary tool
Definitions
- the invention is based on a handheld power tool according to the preamble of claim 1 (see e.g. WO-A-88 04975).
- a hand grinding tool known from DE-OS 44 21 480 carries a grinding wheel on its output shaft between two clamping flanges.
- the outer clamping flange can be clamped against the grinding wheel via a thread.
- the inner flange is mounted so that it can be rotated against the output spindle by means of a solid lubricant.
- the inner clamping flange can easily be rotated together with the grinding wheel. This allows the outer clamping flange to be loosened with little force and the grinding wheel can be changed easily.
- This solution has the disadvantage that when the grinding spindle abruptly brakes, the outer flange tries to loosen and there is a risk that the grinding wheel will be thrown away from the grinding spindle with high energy, with a corresponding risk of injury to persons in the vicinity.
- EP 0 231 500 discloses quick-action clamping systems for easy loosening of grinding wheels, saw blades or the like from hand-held power tools, which work satisfactorily, but which do not automatically reduce the clamping torque when the tool shaft is at a standstill, so that the tool can be easily released by turning the outer clamping flange by hand is.
- the hand tool according to the invention with the characterizing features of claim 1 has the advantage that when the tool shaft is at a standstill, the outer clamping flange or clamping bolt can be easily released by hand without any additional auxiliary tool. Because the self-releasing or tensioning clamping mechanism is arranged inside the handheld power tool, it is captive and safe from contamination by dust and chips. It also makes it possible to use an inexpensive mass or standard part as a clamping screw or outer clamping flange.
- the tensioning mechanism essentially consists of a pair of disks with rolling elements arranged in between, which are held in a certain position by a torsion spring, assembly as an assembly is particularly easy to accomplish.
- clamping mechanism can be prefabricated as a structural unit with the drive pinion for the tool shaft means that the assembly effort is low.
- the flat head of the cap screw and the particularly flat outer flange prevent a reduction in the depth of cut for miter cuts of more than 45 ° compared to straight cuts because, despite the inclined position of the saw shaft, the axially outermost part of the cap screw or the outer flange does not hit the workpiece before reaching for straight cuts greatest depth of cut threatens.
- a particularly large bearing dimension can be selected by arranging the saw shaft bearing on the outer circumference of the sleeve region of the outer disk. Such a large needle bearing behaves more wear-resistant than needle bearings of comparable smaller diameter.
- Another advantage of the invention is that the depressions in the pair of disks can be contoured so that the rolling elements pass through a noticeable pressure point from which the clamping torque no longer increases. This simplifies the handling of the clamping device because the operator receives clear information when the clamping position has been reached and that the clamping is finished.
- FIG. 1 shows a spatial representation of a circular saw according to the invention
- FIG. 2 shows a partial longitudinal section of the circular saw according to FIG. 1 in the area of the saw shaft with the clamping mechanism
- FIGS. 3, 4, 5, 6 show exemplary embodiments of the design options for the pair of disks in the area of the rolling element bearings
- Figure 7 shows the special contour of a rolling element bearing in one of the disks, which causes a noticeable pressure point as soon as the clamping position is reached.
- the hand-held circular saw 10 shown in FIG. 1 has a housing 11 with a handle 12 which contains an on / off switch 13 and an electrical connection cable 14.
- the housing 11 is pivotably arranged on a base plate 15 on a joint 16.
- the housing 11 contains a motor, not shown. This drives a saw shaft 17 via a drive pinion 28 (FIG. 2) of a motor shaft. This is rotatably mounted about an axis 18.
- the saw blade 22 is encompassed by a saw blade housing 24 in its area arranged above the base plate 15 and emerges from the bottom through a through slot 25 arranged in the base plate.
- Figure 2 shows the sectional view of the hand-held circular saw 10 in the area of the saw shaft 17. This is in the housing 11 via saw shaft bearings 32, 34 rotatably and axially immovable.
- the saw shaft 17 is driven by a pinion 28 of the motor shaft, which is mounted in a motor bearing 29 in the housing 11 and which is arranged parallel to the saw shaft 17.
- the pinion 28 is in engagement with an output pinion 30, which sits on the saw shaft 17 in a rotationally fixed manner.
- the output pinion 30 carries an inner disk 36 of a pair of disks 35 in a rotationally fixed manner on its left-hand end in the viewing direction.
- Axially to the inner disk 36 is an outer disk 37 of the pair of disks 35, a plurality of spaced-apart rolling elements 38 being rotatable between the inner and outer disks 36, 37 or are supported and guided such that they can be passed around their respective axis of rotation 39.
- the inner and outer disks 36, 37 are biased relative to one another via a torsion spring 40, which engages axially in the disks 36, 37 with legs (not shown).
- the outer disk 37 continues in a sleeve-like shaft 37 ', which is coupled in a form-fitting manner on the end face to the right-hand end face of the inner flange 23 in the viewing direction, the saw shaft bearing 34, which is a needle bearing with a large diameter, seated on the outside of its cylindrical surface.
- the outer disc 37 is rotatably mounted together with the inner flange 23 relative to the saw shaft 17.
- the saw blade 22 is supported on the left side of the inner flange 23 in the viewing direction, preferably with increased friction, e.g. through areas of increased roughness.
- the saw shaft 17 has in its left end in the viewing direction an internally threaded section 19 into which the threaded shaft 19 'of the cap screw 20 engages in a screwed manner.
- the head screw 20 is supported axially with its head 19 ′′ against the outer flange 21, which, with a central polygonal hole 46, engages tightly around the outside of the end of the saw shaft 17, which is designed as a flat surface, one flat side of which can be seen as a flattening 44.
- the outer flange 21 is thereby secured against rotation held against the saw shaft 17.
- FIGS. 3, 4, 5 and 6 show pairs of disks 35 rotated by 90 ° in accordance with the sectional arrows X-X according to FIG. 2 with differently contoured depressions for receiving the rolling elements 38.
- Figure 3 shows that the inner disc 36 has a recess 49 with an inclined surface 48 and rounded flanks on which the rolling element 38 can roll as on an inclined plane, delimited on the left and right by rounded flanks.
- a recess 50 arranged in the outer pane 37 with an angular contour and without an inclined surface holds the rolling element 38 in a cage-like manner, so that it can change its position relative to the outer pane 37 only minimally.
- Figure 4 shows the reverse arrangement compared to Figure 3, i.e. H. the inner pane 36 carries a flat recess 149 and the outer pane 37 a recess 150 provided with a bevel 151 and with rounded flanks.
- the inner and outer disks 36, 37 bear offset and oppositely arranged depressions 49, 150 with inclined surfaces 48, 151.
- the rolling element 38 in FIG. 6 is guided in a separate, disk-like cage 53.
- an oblique recess 249 with an unevenness 260 is arranged, which, when rolled over by the rolling element 38, causes a pressure point on the tensioning device, from which the tensioning torque no longer increases and which facilitates handling with the tensioning device.
- the unevenness is to be dimensioned such that rolling the rolling elements 38 back into the release position can always be carried out easily.
- the tensioning device according to the invention works in the following way: The cap screw 20 is rotated by hand relative to the saw shaft 17, the outer flange 21 being axially supported on the saw blade 22, which is thereby pressed against the inner flange 23 with increasing axial force.
- the inner flange 23 is supported axially to the right in the viewing direction against the outer disk 37 of the disk pair 35 and via the rolling elements 38 against the inner disk 36, the driven pinion 30 and the bearing 32.
- the torsion spring 40 is preloaded in such a way that it attempts to turn the pair of disks 35 against one another in such a way that the rolling bodies 38 are mounted at the lowest point of the recesses 50 or recess 49 and that the axial distance between the inner and outer disks 36, 37 is therefore minimal. If the motor and thus the motor shaft 28 are set in motion by actuating the on / off switch 13, the saw shaft 17 rotates together with the driven pinion 30, the pair of discs 35, the rolling elements 38, the inner flange 23, the saw blade 22, and the outer flange 21 and the screw 20. As a result of the screw 20 being tightened only by hand, there is initially a relatively large amount of slip between the saw blade 22 and the inner and outer flanges 21, 23.
- the saw blade 22 Because of its inertia, the saw blade 22 tries to stop relative to the saw shaft 17. The saw blade 22 also tries to hold or delay the inner and outer flange 23, 21. This is only possible with respect to the inner flange 23 because it can be rotated with respect to the saw shaft 17 is. In the case of the outer flange 21, a delay with respect to the saw shaft 17 is not possible because there is a positive fit between the outer flange 21 and the saw shaft 17 via the double surface 19 'and the polygonal recess. As a result, only the inner flange 23 together with the outer disk 37 is decelerated relative to the saw shaft 17.
- the clamping torque of the saw blade 22 has thus reached a maximum. If the drive motor or the motor shaft 28 is now switched off via the on / off switch 13, the reverse process occurs, as previously described for starting the machine or during machining of the workpiece. This effect is further enhanced if a spindle stop is actuated, which abruptly stops the saw shaft 17 by positive engagement. As a result of the inertial forces of the saw blade 22 acting in the opposite direction as when starting up, the inner flange 23 is rotatably entrained, the axial spacing of the disk pair 35 decreasing to its minimum. Supported by the torsion spring 40, the clamping torque drops to a minimum value.
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- Life Sciences & Earth Sciences (AREA)
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Wood Science & Technology (AREA)
- Forests & Forestry (AREA)
- Sawing (AREA)
Description
Die Erfindung geht aus von einer Handwerkzeugmaschine nach der Gattung des Anspruchs 1 (siehe z.B. WO-A-88 04975).The invention is based on a handheld power tool according to the preamble of claim 1 (see e.g. WO-A-88 04975).
Ein durch die DE-OS 44 21 480 bekanntes Handschleifwerkzeug trägt auf seiner Abtriebswelle zwischen zwei Spannflanschen eine Schleifscheibe. Der äußere Spannflansch ist über ein Gewinde gegen die Schleifscheibe spannbar. Der innere Flansch ist über ein festes Schmiermittel gegenüber der Abtriebsspindel besonders reibarm verdrehbar gelagert. Beim Drehen des äußeren Spanaflansches in Löserichtung läßt sich der innere Spannflansch gemeinsam mit der Schleifscheibe leicht verdrehen. Dadurch läßt sich der äußere Spannflansch mit geringer Kraft lösen und ein Schleifscheibenwechsel leicht bewerkstelligen.A hand grinding tool known from DE-OS 44 21 480 carries a grinding wheel on its output shaft between two clamping flanges. The outer clamping flange can be clamped against the grinding wheel via a thread. The inner flange is mounted so that it can be rotated against the output spindle by means of a solid lubricant. When turning the outer span flange in the loosening direction, the inner clamping flange can easily be rotated together with the grinding wheel. This allows the outer clamping flange to be loosened with little force and the grinding wheel can be changed easily.
Diese Lösung hat den Nachteil, daß bei abruptem Abbremsen der Schleifspindel der äußere Flansch sich zu lösen sucht und die Gefahr besteht, daß die Schleifscheibe mit hoher Energie von der Schleifspindel weggeschleudert wird, mit entsprechender Verletzungsgefahr für in der Umgebung befindliche Personen.This solution has the disadvantage that when the grinding spindle abruptly brakes, the outer flange tries to loosen and there is a risk that the grinding wheel will be thrown away from the grinding spindle with high energy, with a corresponding risk of injury to persons in the vicinity.
Da der bisherige Selbstspanneffekt durch Drehmitnahme der Spannschraube durch das Sägeblatt so stark sein konnte, daß die Spannschraube nicht von Hand, sondern nur mittels Hilfswerkzeug lösbar war, mußte stets ein Hilfswerkzeug mitgeführt und in den meisten Fällen zum Sägeblattwechsel verwendet werden. Dadurch ergab sich ein entsprechend hoher Zeitaufwand.Since the previous self-tightening effect could be so strong that the clamping screw could be loosened by the saw blade so that the clamping screw could not be removed by hand, but only with the help of an auxiliary tool, an auxiliary tool always had to be carried and used in most cases to change the saw blade. This resulted in a correspondingly high expenditure of time.
Aus der EP 0 231 500 sind Schnellspannsysteme zum leichten Lösen von Schleifscheiben, Sägeblättern oder dergleichen von Handwerkzeugmaschinen bekannt, die zufriedenstellend arbeiten, die jedoch nicht selbsttätig bei Stillstand der Werkzeugwelle das Spannmoment so verringern, daß das Werkzeug durch Drehen des äußeren Spannflansches von Hand leicht lösbar ist.EP 0 231 500 discloses quick-action clamping systems for easy loosening of grinding wheels, saw blades or the like from hand-held power tools, which work satisfactorily, but which do not automatically reduce the clamping torque when the tool shaft is at a standstill, so that the tool can be easily released by turning the outer clamping flange by hand is.
Die erfindungsgemäße Handwerkzeugmaschine mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, daß bei Stillstand der Werkzeugwelle der äußere Spannflansch bzw. Spannbolzen leicht von Hand ohne weiteres Hilfswerkzeug lösbar ist. Dadurch, daß der selbsttätig lösende bzw. spannende Spannmechanismus im Inneren der Handwerkzeugmaschine angeordnet ist, ist er unverlierbar und vor Verschmutzung durch Staub und Späne sicher. Außerdem ist es dadurch möglich, als Spannschraube bzw. äußeren Spannflansch ein preisgünstiges Massen- bzw. Normteil zu verwenden.The hand tool according to the invention with the characterizing features of claim 1 has the advantage that when the tool shaft is at a standstill, the outer clamping flange or clamping bolt can be easily released by hand without any additional auxiliary tool. Because the self-releasing or tensioning clamping mechanism is arranged inside the handheld power tool, it is captive and safe from contamination by dust and chips. It also makes it possible to use an inexpensive mass or standard part as a clamping screw or outer clamping flange.
Dadurch, daß der Spannmechanismus im wesentlichen aus einem Scheibenpaar mit dazwischen angeordneten Wälzkörpern besteht, die durch eine Verdrehfeder in einer bestimmten Position gehalten werden, ist eine Montage als Baugruppe besonders einfach zu bewerkstelligen.Because the tensioning mechanism essentially consists of a pair of disks with rolling elements arranged in between, which are held in a certain position by a torsion spring, assembly as an assembly is particularly easy to accomplish.
Dadurch, daß der Spannmechanismus als bauliche Einheit mit dem Antriebsritzel für die Werkzeugwelle vorgefertigt montierbar ist, ist der Montageaufwand gering.The fact that the clamping mechanism can be prefabricated as a structural unit with the drive pinion for the tool shaft means that the assembly effort is low.
Durch den flachen Kopf der Kopfschraube und den besonders flachen Außenflansch wird eine Schnittiefenverringerung bei Gehrungsschnitten von mehr als 45 ° gegenüber Geradschnitten ausgeschlossen, weil trotz der Schrägstellung der Sägewelle kein Anschlagen des axial äußersten Teils der Kopfschraube bzw. des Außenflansches am Werkstück vor Erreichen der für Geradschnitte größten Schnittiefe droht.The flat head of the cap screw and the particularly flat outer flange prevent a reduction in the depth of cut for miter cuts of more than 45 ° compared to straight cuts because, despite the inclined position of the saw shaft, the axially outermost part of the cap screw or the outer flange does not hit the workpiece before reaching for straight cuts greatest depth of cut threatens.
Durch die Anordnung des Sägewellenlagers auf dem Außenumfang des Hülsenbereichs der äußeren Scheibe kann eine besonders große Lagerdimension gewählt werden. Ein derartig großes Nadellager verhält sich verschleißgünstiger als Nadellager vergleichbaren kleineren Durchmessers.A particularly large bearing dimension can be selected by arranging the saw shaft bearing on the outer circumference of the sleeve region of the outer disk. Such a large needle bearing behaves more wear-resistant than needle bearings of comparable smaller diameter.
Der Zeitaufwand für den Sägeblattwechsel ist in jedem Fall zuverlässig verringert. Außerdem ist die bisherige Gefahr beseitigt, daß beim abrupten Stop der Sägewelle sich das Sägeblatt ungewollt von der Sägewelle löst.The time required to change the saw blade is reliably reduced in any case. In addition, the previous risk is eliminated that the saw blade unintentionally detaches from the saw shaft when the saw shaft stops suddenly.
Ein weiterer Vorteil der Erfindung besteht darin, daß die Vertiefungen im Scheibenpaar so konturierbar sind, daß die Wälzkörper einen spürbaren Druckpunkt durchlaufen, von dem an das Spannmoment nicht mehr zunimmt. Das erleichtert die Handhabung der Spannvorrichtung, weil der Bedienende eine deutliche Information erhält, wann die Spannposition erreicht und daß das Spannen damit beendet ist.Another advantage of the invention is that the depressions in the pair of disks can be contoured so that the rolling elements pass through a noticeable pressure point from which the clamping torque no longer increases. This simplifies the handling of the clamping device because the operator receives clear information when the clamping position has been reached and that the clamping is finished.
Ein Ausführungsbeispiel der Erfindung ist in der nachfolgen den Beschreibung anhand der zugehörigen Zeichnung näher er läutert.An embodiment of the invention is in the follow he explains the description with reference to the accompanying drawing.
Es zeigen Figur 1 eine räumliche Darstellung einer erfindungsgemäßen Handkreissäge, Figur 2 einen Teil-Längsschnitt der Handkreissäge gemäß Figur 1 im Bereich der Sägewelle mit dem Spannmechanismus, die Figuren 3, 4, 5, 6 Ausführungsbeispiele für die Ausgestaltungsmöglichkeit des Scheibenpaares im Bereich der Wälzkörperlagerung und Figur 7 die besondere Kontur einer Wälzkörperlagerung in einer der Scheiben, die einen spürbaren Druckpunkt bewirkt, sobald die Spannposition erreicht ist.1 shows a spatial representation of a circular saw according to the invention, FIG. 2 shows a partial longitudinal section of the circular saw according to FIG. 1 in the area of the saw shaft with the clamping mechanism, FIGS. 3, 4, 5, 6 show exemplary embodiments of the design options for the pair of disks in the area of the rolling element bearings and Figure 7 shows the special contour of a rolling element bearing in one of the disks, which causes a noticeable pressure point as soon as the clamping position is reached.
Die in Figur 1 gezeigte Handkreissäge 10 hat ein Gehäuse 11 mit Griff 12, der einen Ein- und Ausschalter 13 und ein Elektroanschlußkabel 14 enthält. Das Gehäuse 11 ist an einer Grundplatte 15 an einem Gelenk 16 schwenkbar angeordnet. Das Gehäuse 11 enthält einen nicht dargestellten Motor. Dieser treibt über ein Antriebsritzel 28 (Figur 2) einer Motorwelle eine Sägewelle 17 an. Diese ist drehbar um eine Achse 18 gelagert. Eine in einen Innengewindeabschnitt 19 (Fig. 2) der Sägewelle 17 schraubbare Kopfschraube 20 mit besonders flachem Kopf 19" spannt einen besonders flachen Außenflansch 21 axial gegen ein Sägeblatt 22.The hand-held circular saw 10 shown in FIG. 1 has a housing 11 with a handle 12 which contains an on / off switch 13 and an electrical connection cable 14. The housing 11 is pivotably arranged on a base plate 15 on a joint 16. The housing 11 contains a motor, not shown. This drives a saw shaft 17 via a drive pinion 28 (FIG. 2) of a motor shaft. This is rotatably mounted about an axis 18. A head screw 20, which can be screwed into an internally threaded section 19 (FIG. 2) of the saw shaft 17 and has a particularly flat head 19 ″, axially clamps a particularly flat outer flange 21 against a saw blade 22.
Das Sägeblatt 22 wird in seinem oberhalb der Grundplatte 15 angeordneten Bereich von einem Sägeblattgehäuse 24 umgriffen und tritt durch einen in der Grundplatte angeordneten Durchtrittsschlitz 25 unten aus dieser heraus.The saw blade 22 is encompassed by a saw blade housing 24 in its area arranged above the base plate 15 and emerges from the bottom through a through slot 25 arranged in the base plate.
Figur 2 zeigt die Schnittdarstellung der Handkreissäge 10 im Bereich der Sägewelle 17. Diese ist im Gehäuse 11 über Sägewellenlager 32, 34 drehbar und axial unverschieblich gelagert. Der Antrieb der Sägewelle 17 erfolgt über ein Ritzel 28 der Motorwelle, die in einem Motorlager 29 im Gehäuse 11 gelagert ist und die parallel zur Sägewelle 17 angeordnet ist.Figure 2 shows the sectional view of the hand-held circular saw 10 in the area of the saw shaft 17. This is in the housing 11 via saw shaft bearings 32, 34 rotatably and axially immovable. The saw shaft 17 is driven by a pinion 28 of the motor shaft, which is mounted in a motor bearing 29 in the housing 11 and which is arranged parallel to the saw shaft 17.
Das Ritzel 28 steht im Eingriff mit einem Abtriebsritzel 30, das drehfest auf der Sägewelle 17 sitzt. Das Abtriebsritzel 30 trägt auf seiner in Betrachtungsrichtung linken Stirnseite drehfest eine Innenscheibe 36 eines Scheibenpaars 35. Axial an die Innenscheibe 36 schließt sich eine Außenscheibe 37 des Scheibenpaars 35 an, wobei zwischen der Innen- und der Außenscheibe 36, 37 mehrere voneinander beabstandete Wälzkörper 38 drehbar bzw. sich um ihre jeweilige Drehachse 39 abwälzbar gelagert und geführt sind.The pinion 28 is in engagement with an output pinion 30, which sits on the saw shaft 17 in a rotationally fixed manner. The output pinion 30 carries an inner disk 36 of a pair of disks 35 in a rotationally fixed manner on its left-hand end in the viewing direction. Axially to the inner disk 36 is an outer disk 37 of the pair of disks 35, a plurality of spaced-apart rolling elements 38 being rotatable between the inner and outer disks 36, 37 or are supported and guided such that they can be passed around their respective axis of rotation 39.
Innen- und Außenscheibe 36, 37 sind über eine Drehfeder 40 zueinander verdreht vorgespannt, die mit nicht näher bezeichneten Schenkeln axial in die Scheiben 36, 37 eingreift.The inner and outer disks 36, 37 are biased relative to one another via a torsion spring 40, which engages axially in the disks 36, 37 with legs (not shown).
Die Außenscheibe 37 setzt sich in einem hülsenartigen Schaft 37' fort, der stirnseitig formschlüssig mit der in Betrachtungsrichtung rechten Stirnseite des Innenflansches 23 gekoppelt ist, wobei außen auf dessen Zylindermantelfläche das Sägewellenlager 34 sitzt, das ein Nadellager mit großem Durchmesser ist. Die Außenscheibe 37 ist gemeinsam mit dem Innenflansch 23 gegenüber der Sägewelle 17 verdrehbar gelagert. An die in Betrachtungsrichtung linke Seite des Innenflansches 23 stützt sich das Sägeblatt 22 ab, vorzugsweise mit erhöhter Reibung, z.B. durch Bereiche erhöhter Rauhigkeit.The outer disk 37 continues in a sleeve-like shaft 37 ', which is coupled in a form-fitting manner on the end face to the right-hand end face of the inner flange 23 in the viewing direction, the saw shaft bearing 34, which is a needle bearing with a large diameter, seated on the outside of its cylindrical surface. The outer disc 37 is rotatably mounted together with the inner flange 23 relative to the saw shaft 17. The saw blade 22 is supported on the left side of the inner flange 23 in the viewing direction, preferably with increased friction, e.g. through areas of increased roughness.
Die Sägewelle 17 trägt in ihrem in Betrachtungsrichtung linken Ende einen Innengewindeabschnitt 19, in den der Gewindeschaft 19' der Kopfschraube 20 schraubbar eingreift.The saw shaft 17 has in its left end in the viewing direction an internally threaded section 19 into which the threaded shaft 19 'of the cap screw 20 engages in a screwed manner.
Die Kopfschraube 20 stützt sich mit ihrem Kopf 19" axial gegen den Außenflansch 21, der mit einem zentralen Mehrkantloch 46 das außen als Zweiflach ausgestaltete Ende der Sägewelle 17 eng umgreift, von dem eine Flachseite als Abplattung 44 erkennbar ist. Der Außenflansch 21 ist dadurch verdrehsicher gegenüber der Sägewelle 17 festgehalten.The head screw 20 is supported axially with its head 19 ″ against the outer flange 21, which, with a central polygonal hole 46, engages tightly around the outside of the end of the saw shaft 17, which is designed as a flat surface, one flat side of which can be seen as a flattening 44. The outer flange 21 is thereby secured against rotation held against the saw shaft 17.
Die in den Figuren 3, 4, 5 und 6 dargestellten Varianten zeigen Scheibenpaare 35 ausschnittsweise entsprechend den Schnittpfeilen X-X gemäß Figur 2 um 90° gedreht mit unterschiedlich konturierten Vertiefungen zur Aufnahme der Wälzkörper 38 .The variants shown in FIGS. 3, 4, 5 and 6 show pairs of disks 35 rotated by 90 ° in accordance with the sectional arrows X-X according to FIG. 2 with differently contoured depressions for receiving the rolling elements 38.
Figur 3 läßt erkennen, daß die Innenscheibe 36 eine Vertiefung 49 mit einer Schrägfläche 48 und abgerundeten Flanken trägt, auf der der Wälzkörper 38 wie auf einer schiefen Ebene, links und rechts durch abgerundete Flanken begrenzt, rollen kann. Eine in der Außenscheibe 37 angeordnete Vertiefung 50 mit eckiger Kontur, ohne Schrägfläche hält den Wälzkörper 38 käfigartig fest, so daß dieser seine Position gegenüber der Außenscheibe 37 nur minimal verändern kann.Figure 3 shows that the inner disc 36 has a recess 49 with an inclined surface 48 and rounded flanks on which the rolling element 38 can roll as on an inclined plane, delimited on the left and right by rounded flanks. A recess 50 arranged in the outer pane 37 with an angular contour and without an inclined surface holds the rolling element 38 in a cage-like manner, so that it can change its position relative to the outer pane 37 only minimally.
Figur 4 zeigt die umgekehrte Anordnung im Vergleich zu Figur 3, d. h. die Innenscheibe 36 trägt eine ebene Vertiefung 149 und die Außenscheibe 37 eine mit einer Schräge 151 sowie mit abgerundeten Flanken versehene Ausnehmung 150.Figure 4 shows the reverse arrangement compared to Figure 3, i.e. H. the inner pane 36 carries a flat recess 149 and the outer pane 37 a recess 150 provided with a bevel 151 and with rounded flanks.
In Figur 5 und 6 tragen die Innen- und Außenscheiben 36, 37 versetzt und gegengeläufig zueinander angeordnete Vertiefungen 49, 150 mit Schrägflächen 48, 151. Darüber hinaus ist der Wälzkörper 38 in Figur 6 in einem gesonderten, scheibenartigen Käfig 53 geführt.In FIGS. 5 and 6, the inner and outer disks 36, 37 bear offset and oppositely arranged depressions 49, 150 with inclined surfaces 48, 151. In addition, the rolling element 38 in FIG. 6 is guided in a separate, disk-like cage 53.
In Figur 7 ist eine schräge Vertiefung 249 mit einer Unebenheit 260 angeordnet, die bei Überrollen durch den Wälzkörper 38 einen Druckpunkt an der Spannvorrichtung bewirkt, ab dem das Spannmoment nicht mehr zunimmt und der das Hantieren mit der Spannvorrichtung erleichtert. Die Unebenheit ist so zu dimensionieren, daß ein Zurückrollen der Wälzkörper 38 in die Löse-Position immer leicht vonstatten gehen kann.
Die erfindungsgemäße Spanneinrichtung arbeitet auf folgende Weise: Die Kopfschraube 20 wird von Hand gegenüber der Sägewelle 17 verdreht, wobei sich der Außenflansch 21 axial am Sägeblatt 22 abstützt, das dadurch mit zunehmender Axialkraft an den Innenflansch 23 gedrückt wird. Der Innenflansch 23 stützt sich in Betrachtungsrichtung axial nach rechts gegen die Außenscheibe 37 des Scheibenpaars 35 und über die Wälzkörper 38 gegen die Innenscheibe 36, das Abtriebsritzel 30 und das Lager 32.In FIG. 7, an oblique recess 249 with an unevenness 260 is arranged, which, when rolled over by the rolling element 38, causes a pressure point on the tensioning device, from which the tensioning torque no longer increases and which facilitates handling with the tensioning device. The unevenness is to be dimensioned such that rolling the rolling elements 38 back into the release position can always be carried out easily.
The tensioning device according to the invention works in the following way: The cap screw 20 is rotated by hand relative to the saw shaft 17, the outer flange 21 being axially supported on the saw blade 22, which is thereby pressed against the inner flange 23 with increasing axial force. The inner flange 23 is supported axially to the right in the viewing direction against the outer disk 37 of the disk pair 35 and via the rolling elements 38 against the inner disk 36, the driven pinion 30 and the bearing 32.
Die Drehfeder 40 ist derart vorgespannt, daß sie das Scheibenpaar 35 so gegeneinander zu verdrehen sucht, daß die Wälzkörper 38 am tiefsten Punkt der Ausnehmungen 50 bzw. Vertiefung 49 gelagert sind und daß damit der Axialabstand der Innen- und Außenscheibe 36, 37 minimal ist. Wird durch Betätigen des Ein- und Ausschalters 13 der Motor und damit die Motorwelle 28 in Bewegung gesetzt, dreht sich zugleich die Sägewelle 17 gemeinsam mit dem Abtriebsritzel 30, dem Scheibenpaar 35, den Wälzkörpern 38, dem Innenflansch 23, dem Sägeblatt 22, dem Außenflansch 21 und der Schraube 20. Infolge der nur handfest angezogenen Schraube 20 besteht zwischen dem Sägeblatt 22 sowie dem Innen- und Außenflansch 21, 23 zunächst ein verhältnismäßig starker Schlupf. Wegen seiner Massenträgheit sucht das Sägeblatt 22 gegenüber der Sägewelle 17 stehen zu bleiben. Dabei sucht das Sägeblatt 22 den Innen- und Außenflansch 23, 21 ebenfalls festzuhalten bzw. zu verzögern. Dies gelingt nur gegenüber dem Innenflansch 23, weil dieser gegenüber der Sägewelle 17 verdrehbar ist. Beim Außenflansch 21 ist eine Verzögerung gegenüber der Sägewelle 17 nicht möglich, weil zwischen dem Außenflansch 21 und der Sägewelle 17 über den Zweiflach 19' und die Mehrkantausnehmung Formschluß besteht. Demzufolge wird nur der Innenflansch 23 gemeinsam mit der Außenscheibe 37 gegenüber der Sägewelle 17 verzögert. Dies führt zu einer Relativdrehung zwischen der Außenscheibe 37 und der Innenscheibe 36, wobei die Wälzkörper 38 in den Vertiefungen 49 bzw. den Ausnehmungen 50 in erhöhte Positionen rollen und so den Axialabstand der Innen- und Außenscheibe 36, 37 zu vergrößern suchen. Dadurch wird die Außenscheibe 37 axial gemeinsam mit dem Innenflansch 23 in Richtung zum Sägeblatt 22 bzw. gegen den Außenflansch 21 bewegt. Dies führt zu einer Erhöhung des Spannmoments zwischen den Flanschen 21, 23 und dem Sägeblatt 22.The torsion spring 40 is preloaded in such a way that it attempts to turn the pair of disks 35 against one another in such a way that the rolling bodies 38 are mounted at the lowest point of the recesses 50 or recess 49 and that the axial distance between the inner and outer disks 36, 37 is therefore minimal. If the motor and thus the motor shaft 28 are set in motion by actuating the on / off switch 13, the saw shaft 17 rotates together with the driven pinion 30, the pair of discs 35, the rolling elements 38, the inner flange 23, the saw blade 22, and the outer flange 21 and the screw 20. As a result of the screw 20 being tightened only by hand, there is initially a relatively large amount of slip between the saw blade 22 and the inner and outer flanges 21, 23. Because of its inertia, the saw blade 22 tries to stop relative to the saw shaft 17. The saw blade 22 also tries to hold or delay the inner and outer flange 23, 21. This is only possible with respect to the inner flange 23 because it can be rotated with respect to the saw shaft 17 is. In the case of the outer flange 21, a delay with respect to the saw shaft 17 is not possible because there is a positive fit between the outer flange 21 and the saw shaft 17 via the double surface 19 'and the polygonal recess. As a result, only the inner flange 23 together with the outer disk 37 is decelerated relative to the saw shaft 17. This leads to a relative rotation between the outer disk 37 and the inner disk 36, the rolling elements 38 rolling in the recesses 49 or the recesses 50 into elevated positions and thus trying to enlarge the axial distance between the inner and outer disks 36, 37. As a result, the outer disk 37 is moved axially together with the inner flange 23 in the direction of the saw blade 22 or against the outer flange 21. This leads to an increase in the clamping torque between the flanges 21, 23 and the saw blade 22.
Wird nun das rotierende Sägeblatt 22 gegen ein Werkstück geführt und kommt in spanenden Eingriff mit diesem, wird das Sägeblatt 22 nochmals gegenüber der Sägewelle 17 verzögert, so daß sich das eben geschilderte selbsttätige Spannen nun verstärkt durch Reibungsmitnahme wiederholt bzw. fortsetzt.If the rotating saw blade 22 is now guided against a workpiece and comes into machining engagement with it, the saw blade 22 is again decelerated with respect to the saw shaft 17, so that the automatic tensioning just described is now repeated or continued by frictional entrainment.
Damit hat das Spannmoment des Sägeblatts 22 ein Maximum erreicht. Wird nun der Antriebsmotor bzw. die Motorwelle 28 über den Ein- und Ausschalter 13 ausgeschaltet, tritt der umgekehrte Vorgang ein, wie zuvor zum Starten der Maschine bzw. beim spanenden Werkstückeingriff geschildert. Dieser Effekt wird noch weiter verstärkt, falls ein Spindelstopp betätigt wird, der die Sägewelle 17 durch Formschlußeingriff abrupt zum Anhalten bringt. Durch die dadurch in umgekehrter Richtung wie beim Anlaufen wirkenden Trägheitskräfte des Sägeblatts 22 wird der Innenflansch 23 drehend mitgenommen, wobei der Axialabstand des Scheibenpaars 35 auf sein Minimum zurückgeht. Unterstützt durch die Verdrehfeder 40, geht das Spannmoment auf einen Minimalwert zurück. Aufgrund des Formschlusses zwischen dem Außenflansch 21 und der Sägewelle 17 besteht nicht die Gefahr, daß sich die Kopfschraube 19 durch eine in Löserichtung wirkende Trägheitskraft des Sägeblatts 22 gelöst wird. Ein ungewolltes Lösen des Sägeblatts bzw. Werkzeugs von der Sägewelle 17 ist damit auszuschließen und ein erheblicher Gewinn an Arbeitssicherheit in Verbindung mit einer handbetätigten Schnellspann- bzw. -löse-Vorrichtung für eine Handkreissäge bzw. eine Scheibenschleifmaschine oder dergl. erreicht.The clamping torque of the saw blade 22 has thus reached a maximum. If the drive motor or the motor shaft 28 is now switched off via the on / off switch 13, the reverse process occurs, as previously described for starting the machine or during machining of the workpiece. This effect is further enhanced if a spindle stop is actuated, which abruptly stops the saw shaft 17 by positive engagement. As a result of the inertial forces of the saw blade 22 acting in the opposite direction as when starting up, the inner flange 23 is rotatably entrained, the axial spacing of the disk pair 35 decreasing to its minimum. Supported by the torsion spring 40, the clamping torque drops to a minimum value. Due to the form fit there is no danger between the outer flange 21 and the saw shaft 17 that the cap screw 19 is loosened by an inertial force of the saw blade 22 acting in the loosening direction. An unintentional loosening of the saw blade or tool from the saw shaft 17 can thus be ruled out and a considerable gain in occupational safety in connection with a manually operated quick-action clamping or releasing device for a hand-held circular saw or a disk grinding machine or the like is achieved.
Claims (8)
- Powered hand tool (10) having a rotationally driven, disc-like tool (22), for example a portable circular saw, cutting-off grinder or the like, having a housing (12) which accommodates a drive motor and a tool shaft (17) which carries the tool (22), which can be clamped between a clamping nut, clamping screw (19) or the like and supporting flanges (21, 23), the supporting flange (23) being rotatable relative to the tool shaft (17) in an easy-running manner without an auxiliary tool and being supported on the tool (22) with high friction, characterized in that adjusting means (35) are coupled to the supporting flange (23), which adjusting means (35), during rotation relative to the tool shaft (17) as a result of rotary driving by the tool (22) during operation of the powered hand tool (10), displace the supporting flange (23) axially towards the tool (22) - and thus clamp the tool (22) with increasing force - and which, when the tool (22) is stopped, attempt to axially displace the supporting flange (23) away from the tool (22) automatically - and thus withdraw the clamping force.
- Powered hand tool according to Claim 1, characterized in that the clamping screw (19) or the like is fastened so as to be secured against rotary driving relative to the tool shaft (17).
- Powered hand tool according to Claim 1, characterized in that the adjusting means (35) consist of a disc pair (35), the discs (36, 37) of which are supported on one another via axial sloping surfaces (48, 151) and, rotated relative to one another in a preloaded manner via a spring (40), attempt to assume a position having a minimum axial dimension of the disc pair (35) and, during mutual rotation, are displaced from this position to a certain maximum axial dimension, one disc (37) being rotatable and being coupled to the supporting flange (23) in a rotary-driving manner, and the other disc (36) being coupled to the saw shaft (17) in a rotationally fixed manner.
- Powered hand tool according to Claim 1, characterized in that rolling bodies (38) are arranged in a rollable manner between the disc pair (35).
- Powered hand tool according to Claim 3, characterized in that at least the axial sloping surfaces (48, 151) of one of the discs (36, 37) serve to accommodate the rolling bodies (38).
- Powered hand tool according to Claim 3 or 4, characterized in that the axial sloping surfaces (48, 151) for accommodating the rolling bodies (38) are arranged in recesses (49) of the axial surfaces of the discs (36, 37).
- Powered hand tool according to Claim 3 or 4, characterized in that the axial sloping surfaces (248) have unevenness points (260) for producing a pressure point during the clamping or release of the clamping device.
- Powered hand tool according to Claim 3, 4 or 5, characterized in that the outer disc (37) is arranged with an axial sleeve (37') on the saw shaft (17), the outer circumference of which axial sleeve (37') forms the bearing seat for a saw-shaft bearing (34).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19649514 | 1996-11-29 | ||
DE19649514A DE19649514A1 (en) | 1996-11-29 | 1996-11-29 | Hand tool |
PCT/DE1997/001980 WO1998023410A1 (en) | 1996-11-29 | 1997-09-06 | Manually driven machine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0906175A1 EP0906175A1 (en) | 1999-04-07 |
EP0906175B1 true EP0906175B1 (en) | 2002-02-27 |
Family
ID=7813135
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97942809A Expired - Lifetime EP0906175B1 (en) | 1996-11-29 | 1997-09-06 | Manually driven machine |
Country Status (5)
Country | Link |
---|---|
US (1) | US6148526A (en) |
EP (1) | EP0906175B1 (en) |
JP (1) | JP2000504282A (en) |
DE (2) | DE19649514A1 (en) |
WO (1) | WO1998023410A1 (en) |
Families Citing this family (27)
Publication number | Priority date | Publication date | Assignee | Title |
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US7055417B1 (en) * | 1999-10-01 | 2006-06-06 | Sd3, Llc | Safety system for power equipment |
US7707920B2 (en) | 2003-12-31 | 2010-05-04 | Sd3, Llc | Table saws with safety systems |
US7827890B2 (en) | 2004-01-29 | 2010-11-09 | Sd3, Llc | Table saws with safety systems and systems to mount and index attachments |
US7024975B2 (en) | 2000-08-14 | 2006-04-11 | Sd3, Llc | Brake mechanism for power equipment |
US7836804B2 (en) | 2003-08-20 | 2010-11-23 | Sd3, Llc | Woodworking machines with overmolded arbors |
US7210383B2 (en) | 2000-08-14 | 2007-05-01 | Sd3, Llc | Detection system for power equipment |
US7472634B2 (en) * | 2003-08-20 | 2009-01-06 | Sd3, Llc | Woodworking machines with overmolded arbors |
US7350444B2 (en) * | 2000-08-14 | 2008-04-01 | Sd3, Llc | Table saw with improved safety system |
US7712403B2 (en) | 2001-07-03 | 2010-05-11 | Sd3, Llc | Actuators for use in fast-acting safety systems |
US8061245B2 (en) | 2000-09-29 | 2011-11-22 | Sd3, Llc | Safety methods for use in power equipment |
AU2001255364A1 (en) * | 2000-04-12 | 2001-10-30 | Jore Corporation | Power work tools having a slim profile |
US7013987B2 (en) * | 2000-09-08 | 2006-03-21 | Black & Decker | Clutch assembly and clamp mechanism for rotary tool disc |
US6645058B2 (en) | 2000-11-30 | 2003-11-11 | Black & Decker Inc. | Clamp mechanism for rotary tool disc |
TWI268188B (en) * | 2005-03-28 | 2006-12-11 | Quarton Inc | Cut line indicator |
DE102006001986A1 (en) | 2006-01-16 | 2007-07-19 | Robert Bosch Gmbh | Clamping device for releasably securing a disc-shaped tool |
JP4964642B2 (en) * | 2007-03-27 | 2012-07-04 | 株式会社マキタ | Rotating blade fixing device |
US8695224B2 (en) * | 2007-09-13 | 2014-04-15 | Black & Decker Inc. | Saw with increased depth of cut |
US8230607B2 (en) | 2008-05-09 | 2012-07-31 | Milwaukee Electric Tool Corporation | Keyless blade clamp for a power tool |
US7952073B2 (en) * | 2008-08-01 | 2011-05-31 | Direct Electron, Lp | Apparatus and method including a direct bombardment detector and a secondary detector for use in electron microscopy |
US20110039482A1 (en) * | 2009-07-29 | 2011-02-17 | Terry Timmons | Grinder |
WO2011035062A2 (en) | 2009-09-16 | 2011-03-24 | Velico Medical, Inc. | Spray dried human plasma |
JP2014079874A (en) * | 2012-09-26 | 2014-05-08 | Makita Corp | Power tool |
JP2015020237A (en) * | 2013-07-18 | 2015-02-02 | 株式会社ディスコ | Cutting device |
JP6069122B2 (en) | 2013-07-22 | 2017-02-01 | 株式会社ディスコ | Cutting equipment |
US10118308B2 (en) | 2013-10-17 | 2018-11-06 | Sawstop Holding Llc | Systems to mount and index riving knives and spreaders in table saws |
US10875109B1 (en) | 2018-04-30 | 2020-12-29 | Kreg Enterprises, Inc. | Adaptive cutting system |
FR3118431B1 (en) * | 2020-12-29 | 2023-03-24 | Renault Georges Ets | Portable tool, grinder or grinder type. |
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Publication number | Priority date | Publication date | Assignee | Title |
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US2586530A (en) * | 1948-07-08 | 1952-02-19 | Stanley Works | Saw blade holding means |
FR1360283A (en) * | 1963-03-26 | 1964-05-08 | Head and brush clearing tool | |
DE1289292B (en) * | 1964-01-25 | 1969-02-13 | Metabowerke Kg | Clamping device, especially for circular saws |
DE3603384A1 (en) * | 1986-02-05 | 1987-08-06 | Bosch Gmbh Robert | DEVICE FOR DETACHABLE FASTENING OF A DISC-SHAPED TOOL |
DE3644440A1 (en) * | 1986-12-24 | 1988-07-07 | Bosch Gmbh Robert | TENSIONING DEVICE FOR DETACHABLE FASTENING OF A TOOL, IN PARTICULAR A DISC |
IT1238239B (en) * | 1990-02-08 | 1993-07-12 | Selco Srl | DISK BLADE HOLDER SPINDLE PARTICULARLY FOR CUTTING MACHINES. |
EP0569767B1 (en) * | 1992-05-13 | 1996-01-03 | SCHOBER GmbH Werkzeug- und Maschinenbau | Knife support |
GB9304539D0 (en) * | 1993-03-05 | 1993-04-21 | Black & Decker Inc | A device having a flange lock |
GB9313633D0 (en) * | 1993-07-01 | 1993-08-18 | Black & Decker Inc | A clamp nut |
JPH0768464A (en) * | 1993-09-03 | 1995-03-14 | Hitachi Koki Co Ltd | Fixing side flange |
-
1996
- 1996-11-29 DE DE19649514A patent/DE19649514A1/en not_active Withdrawn
-
1997
- 1997-09-06 US US09/117,320 patent/US6148526A/en not_active Expired - Lifetime
- 1997-09-06 DE DE59706502T patent/DE59706502D1/en not_active Expired - Lifetime
- 1997-09-06 WO PCT/DE1997/001980 patent/WO1998023410A1/en active IP Right Grant
- 1997-09-06 EP EP97942809A patent/EP0906175B1/en not_active Expired - Lifetime
- 1997-09-06 JP JP10524112A patent/JP2000504282A/en active Pending
Also Published As
Publication number | Publication date |
---|---|
DE19649514A1 (en) | 1998-06-04 |
EP0906175A1 (en) | 1999-04-07 |
JP2000504282A (en) | 2000-04-11 |
DE59706502D1 (en) | 2002-04-04 |
US6148526A (en) | 2000-11-21 |
WO1998023410A1 (en) | 1998-06-04 |
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