EP1980369B1 - Manually operated fastener driving device - Google Patents

Manually operated fastener driving device Download PDF

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Publication number
EP1980369B1
EP1980369B1 EP08103315A EP08103315A EP1980369B1 EP 1980369 B1 EP1980369 B1 EP 1980369B1 EP 08103315 A EP08103315 A EP 08103315A EP 08103315 A EP08103315 A EP 08103315A EP 1980369 B1 EP1980369 B1 EP 1980369B1
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EP
European Patent Office
Prior art keywords
drive
spring
driving device
propelling
propelling spring
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EP08103315A
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German (de)
French (fr)
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EP1980369A2 (en
EP1980369A3 (en
Inventor
Harald Fielitz
Walter Odoni
Robert Spasov
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Hilti AG
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Hilti AG
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Priority to PL08103315T priority Critical patent/PL1980369T3/en
Publication of EP1980369A2 publication Critical patent/EP1980369A2/en
Publication of EP1980369A3 publication Critical patent/EP1980369A3/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25C—HAND-HELD NAILING OR STAPLING TOOLS; MANUALLY OPERATED PORTABLE STAPLING TOOLS
    • B25C1/00—Hand-held nailing tools; Nail feeding devices
    • B25C1/06—Hand-held nailing tools; Nail feeding devices operated by electric power
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25C—HAND-HELD NAILING OR STAPLING TOOLS; MANUALLY OPERATED PORTABLE STAPLING TOOLS
    • B25C5/00—Manually operated portable stapling tools; Hand-held power-operated stapling tools; Staple feeding devices therefor
    • B25C5/10—Driving means
    • B25C5/15—Driving means operated by electric power

Definitions

  • the present invention relates to a hand-held tacker of the type mentioned in the preamble of claim 1.
  • Such hand-held tackers have a displaceably guided Eintreibstössel about the fasteners are driven into a ground.
  • the drive source for the drive ram is a mechanical drive spring, which can be tensioned via a clamping mechanism.
  • the advantage here is that the mechanical drive spring is inexpensive, whereby such a tacker is inexpensive to manufacture.
  • mechanical springs compared to gas springs have the advantage that it does not cause temperature increases during tensioning of the mechanical spring gas springs as well as that a tensioned spring does not lose the stored energy for a long time, while in a gas spring, the energy is gradually lost by leakage.
  • a generic tacker is from the DE 40 13 022 A1 known, which has a propelled by a spring to an orifice impact device for driving a nail.
  • An adjusting device for transferring the impact device to an initial position has an electric motor and a speed reduction mechanism for this.
  • a rotational movement of the electric motor is transmitted via the speed reduction mechanism and a meshing toothed disc on a hammer body of the impact device to convert this against the force of the spring in the starting position in which the impact device is ready for a beating operation.
  • a disadvantage of the known driving tool is that the maximum impact energy that can be exerted on the hammer body via the spring is rather low at about 5 to 10 joules, which is why such a tacker is not suitable for use on hard substrates such as steel and concrete suitable. If you want to increase the impact energy of Eintreibuzes, so you have to provide a stronger spring, which can store correspondingly more energy. As a result, however, the net mass of the spring is increased, which in turn increases the recoil of the tacker.
  • the object of the present invention is to develop a tacker of the aforementioned type, which avoids the aforementioned disadvantages and in which the recoil is small even when using stronger drive springs.
  • the drive means comprises a first drive spring member having a first expansion direction and a second drive spring member having a second expansion direction opposite to the first expansion direction. This ensures that during a setting process, the masses of the springs are moved in opposite directions, so that the recoil accelerations of the drive spring elements compensate at least partially.
  • the drive spring elements can be z. B. be designed as coil springs, leaf springs, disc springs, torsion springs or torsion springs.
  • the first drive spring element and the second drive spring element each define a spring axis, both of which run coaxially with one another, whereby rotational accelerations of the tacker can be avoided during drive-in processes.
  • both the first drive spring element and the second drive spring element are supported opposite each other with a first end on a housing-fixed support element.
  • the support element can be z. B. be designed as a housing transverse wall or housing strut. Due to the mirror-symmetrical arrangement of the drive spring elements whose force vectors act exactly opposite, so that not only cancel the recoil with appropriately balanced spring mass on both sides exactly, but also act no high loads on the housing-fixed support.
  • the spring axes of the first drive spring element and of the second drive spring element each extend axially parallel to an axis defined by the drive ram, whereby a compact design is made possible.
  • the second drive spring element to a mass which is at least as large as the mass of the first drive spring element, whereby the recoil accelerations of both drive spring elements compensate almost completely.
  • the second drive spring element has a mass which corresponds to a tolerance of +/- 10% of the total mass of driving ram and the first drive spring element.
  • first drive spring element and the second drive spring element are coupled to each other via a transmission device, wherein the transmission device is coupled on the output side with the drive-in ram.
  • the transmission device can be z. B. be designed as a cable transmission.
  • the transmission device may also have a translation between input movement and output movement, such. Example, a transmission ratio of about 1: 4, whereby for a given expansion path of the drive spring elements, a 4 times longer stroke of Eintreibstössels is achieved.
  • FIGS. 1 and 2 illustrated tackle 10 has a housing 11 and disposed therein, generally designated 30 drive arrangement for a drive-in ram 13 which is guided in a guide 12 displaceable.
  • the drive-in ram 13 has a drive-in section 14 and a head section 15.
  • end of the guide 12 is a coaxial with the guide 12 extending bolt guide 17 connects to this.
  • a fastener magazine 61 is arranged in the fasteners 60 are stored.
  • the drive arrangement 30 includes a first drive spring element 31 and a second drive spring element 32, both of which have substantially the same spring mass and which are supported opposite one another on a housing-fixed support element 36, which in the present case is designed as a housing strut.
  • Both drive spring elements 31, 32 are formed here as coil springs.
  • Each of the two drive spring elements 31, 32 each defines a spring axis F1, F2 which are arranged coaxially with each other in the illustrated drive arrangement 30.
  • the spring axes F1 and F2 also still run parallel to an axis A defined by the drive-in ram 13 Fig.
  • both drive spring elements 31, 32 have expansion directions 37, 38, which are opposite to each other, ie at a relaxation of the drive spring elements 31, 32 move their, the support member 36 facing away from free ends in exactly opposite directions, causing their oppositely acting recoil accelerations Compensate each other in a drive-in.
  • Both drive spring elements 31, 32 engage mediated via a total of 39 designated gear means on the head portion 15 of the drive-in ram 13.
  • the transmission device 39 is in the embodiment according to the FIGS. 1 and 2 it is designed as a cable transmission.
  • the first drive spring element 31 and the second drive spring element 32 are in each case clamped between the housing-fixed support element 36 and in each case a spring output element 35.
  • the ring-shaped spring output elements 35 carry on their side facing away from the associated drive spring element 31, 32 side rollers 34 for a rope or band-shaped transmission means 33 of the transmission device 39th
  • the rope or band-shaped transmission means 33 which is fixed with its first and second free end 42, 43 on the support member fixed to the housing 36, is above this Rollers 34 are guided around the spring output element 35. At the same time, the transmission means 33 is guided around the free end of the head section 15 of the drive rod 13.
  • a generally designated 50 locking device having a pawl 51 which in a blocking position 54 (see Fig. 1 ) engages a locking surface 53 on a projection 58 of the drive-in ram 13 and holds it against the force of the drive spring element 31.
  • the pawl 51 is mounted on a servomotor 52 and about this in a Fig. 2 apparent release position 55 can be transferred, as will be described below.
  • the servomotor 52 is connected via an electrical first control line 56 to a control unit 23.
  • the tacker 10 further includes a handle 20 on which a trigger switch 19 is arranged to trigger a driving operation with the tacker 10.
  • a handle 20 on which a trigger switch 19 is arranged to trigger a driving operation with the tacker 10.
  • the handle 20 is also still a total designated 21 power supply arranged, via which the tacker 10 is supplied with electrical energy.
  • the power supply 21 includes at least one accumulator.
  • the power supply 21 is connected via electrical supply lines 24 both to the control unit 23 and to the trigger switch 19.
  • the control unit 23 is further connected via a switch line 57 to the trigger switch 19.
  • a switching means 29 is arranged, which is electrically connected via a switching means 28 to the control unit 23.
  • the switching means 29 sends an electrical signal to the control unit 23 as soon as the tacker 10 is pressed against a workpiece U, as shown Fig. 2 can be seen, thus ensuring that the tacker 10 can be triggered only when it has been properly pressed against a workpiece U.
  • This tensioning device 70 comprises a motor 71, via which a drive roller 72 is drivable.
  • the motor 71 is electrically connected to the control unit 23 via a second control line 74 and can be put into operation via this, z. B. when the driving ram 13 is in its lying in the driving direction 27 end position or when the tacker is lifted off the ground again.
  • the motor 71 has an output means 75, such as a driven wheel, which can be coupled to the drive roller 72.
  • the drive roller 72 is rotatably mounted on a longitudinally adjustable actuating arm 78 of a solenoid 76 designed as a solenoid.
  • the adjusting means 76 is connected via an actuating line 77 to the control unit 23. In operation, the drive roller 72 rotates in the direction of the arrow 73 indicated by dashed lines.
  • the control unit 23 first ensures that the drive-in ram 13 is in its off Fig. 1 apparent starting position 22 is located. If this is not the case, then the drive roller 72 is moved up by the adjusting means 76 to the output means 75, which has already been rotated via the motor 71, and is engaged therewith. At the same time, the drive roller 72 engages the drive-in ram 13 so that it is offset in the direction of the drive arrangement 30 via the drive roller 72 rotating in the direction of the arrow 73. In this case, the drive spring element 32 of the drive assembly 30 is tensioned.
  • the motor 71 can then be turned off via the control unit 23 and the actuating means 76 moves the Drive roller 72 also controlled by the control unit 23 from its engaged position on the output means 75 and the drive tappet 13 in its disengaged position (see. Fig. 2 ).
  • the control unit 23 is first set in Setzrschaft via the switching means 29. If the trigger switch 19 is then actuated by an operator, then the blocking device 50 is displaced into its release position 55 via the control unit 23, wherein the pawl 51 is lifted off the blocking surface 53 on the drive ram 13 via the positioning motor 52.
  • the pawl 51 may be spring-loaded in the direction of the drive-in ram 13 in order to automatically move it back into its blocking position 54.
  • the drive-in ram 13 is then moved via the transmission device 39 via the drive spring elements 31, 32 of the drive arrangement 30 in the drive-in direction 27, wherein a fastening element 60 is driven into the workpiece U.
  • the first drive spring element 31 expands in the direction of the first expansion direction 37, the coincides with the driving direction 27 of the drive rod 13.
  • the second drive spring element 32 expands in exactly the opposite direction, ie in the direction of the second expansion direction 38, as a result of which the recoil of both drive spring elements 31, 32 is canceled out.
  • the expansion path of the drive spring elements 31, 32 is translated via the transmission device 39 such that the acceleration travel of the drive tappet 13 is longer than the respective expansion travel of the drive spring elements 31, 32.
  • the transmission ratio of the transmission device 39 is approximately 1: 4 in the exemplary embodiment ,
  • the clamping device 70 is activated via the control unit 23 at the end of a drive-in operation when the drive-in device 10 is lifted off the workpiece U again.
  • the switching means 29 supplies to a signal to the control unit 23.
  • About the tensioning device 70 of the driving ram 13 is driven in the manner already described against the drive spring element 31 of the drive assembly 30 and the drive spring member 31 while again clamped to the pawl 51 back to its blocking position 54 at the blocking surface 53 on Eintreibstössel 13 can occur.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Portable Nailing Machines And Staplers (AREA)
  • Steering Controls (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Manipulator (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)

Abstract

The device has a drive arrangement (30) for a driving plunger (13) that is supported shiftably in a guide (12). The plunger includes a drive spring (31) e.g. helical spring or flat spring, with an expansion direction clampable over a clamping device (70). Another drive spring (32) includes another expansion direction that is opposite to the former expansion direction. The drive springs define spring axes (F1, F2), which run coaxially to each other. The total volume of the latter drive spring is larger than the total volume of the former drive spring.

Description

Die vorliegende Erfindung betrifft ein handgeführtes Eintreibgerät der im Oberbegriff von Patentanspruch 1 genannten Art. Derartige handgeführte Eintreibgeräte verfügen über einen versetzbar geführten Eintreibstössel über den Befestigungselemente in einen Untergrund eintreibbar sind.The present invention relates to a hand-held tacker of the type mentioned in the preamble of claim 1. Such hand-held tackers have a displaceably guided Eintreibstössel about the fasteners are driven into a ground.

Als Antriebsquelle für den Eintreibstössel dient dabei eine mechanische Antriebsfeder, die über einen Spannmechanismus spannbar ist. Von Vorteil ist dabei, dass die mechanische Antriebsfeder kostengünstig ist, wodurch ein derartiges Eintreibgerät preiswert herzustellen ist. Ferner haben mechanische Federn gegenüber Gasfedern den Vorteil, dass es beim Spannen der mechanischen Feder nicht wie bei Gasfedern zu Temperaturerhöhungen kommt, sowie dass eine gespannte Feder die gespeicherte Energie über lange Zeit nicht verliert, während bei einer Gasfeder die Energie durch Leckage allmählich verloren geht.The drive source for the drive ram is a mechanical drive spring, which can be tensioned via a clamping mechanism. The advantage here is that the mechanical drive spring is inexpensive, whereby such a tacker is inexpensive to manufacture. Furthermore, mechanical springs compared to gas springs have the advantage that it does not cause temperature increases during tensioning of the mechanical spring gas springs as well as that a tensioned spring does not lose the stored energy for a long time, while in a gas spring, the energy is gradually lost by leakage.

Dagegen haben mechanische Federn gegenüber Gasfedern den Nachteil, dass sie einen erheblichen Anteil am Rückstoss des Eintreibgerätes bei einem Setzvorgang verursachen.In contrast, mechanical springs compared to gas springs have the disadvantage that they cause a significant proportion of the recoil of the tacker in a setting process.

Ein gattungsgemässes Eintreibgerät ist aus der DE 40 13 022 A1 bekannt, das eine durch eine Feder zu einer Mündung hin vorgestossene Schlagvorrichtung zum Einschlagen eines Nagels aufweist. Eine Stellvorrichtung zum Überführen der Schlagvorrichtung in eine Ausgangsstellung weist einen Elektromotor und einen Drehzahluntersetzungsmechanismus für diesen auf. Eine Drehbewegung des Elektromotors wird dabei über den Drehzahluntersetzungsmechanismus und eine diesen kämmende Zahnscheibe auf einen Hammerkörper der Schlagvorrichtung übertragen, um diesen gegen die Kraft der Feder in die Ausgangsstellung zu überführen, in der die Schlagvorrichtung bereit für einen Schlagvorgang ist.A generic tacker is from the DE 40 13 022 A1 known, which has a propelled by a spring to an orifice impact device for driving a nail. An adjusting device for transferring the impact device to an initial position has an electric motor and a speed reduction mechanism for this. A rotational movement of the electric motor is transmitted via the speed reduction mechanism and a meshing toothed disc on a hammer body of the impact device to convert this against the force of the spring in the starting position in which the impact device is ready for a beating operation.

Von Nachteil bei dem bekannten Eintreibgerät ist, dass die maximale Schlagenergie, die über die Feder auf den Hammerkörper ausübbar ist, mit ca. 5 bis 10 Joule eher niedrig ist, weshalb sich ein derartiges Eintreibgerät nicht für den Einsatz auf harten Untergründen wie Stahl und Beton eignet. Will man die Schlagenergie des Eintreibgerätes erhöhen, so muss man eine stärkere Feder vorsehen, die entsprechend mehr Energie speichern kann. Dadurch wird aber auch die Eigenmasse der Feder erhöht, was wiederum den Rückstoss des Eintreibgerätes erhöht.A disadvantage of the known driving tool is that the maximum impact energy that can be exerted on the hammer body via the spring is rather low at about 5 to 10 joules, which is why such a tacker is not suitable for use on hard substrates such as steel and concrete suitable. If you want to increase the impact energy of Eintreibgerätes, so you have to provide a stronger spring, which can store correspondingly more energy. As a result, however, the net mass of the spring is increased, which in turn increases the recoil of the tacker.

Die Aufgabe der vorliegenden Erfindung liegt darin, ein Eintreibgerät der vorgenannten Art zu entwickeln, das die vorgenannten Nachteile vermeidet und bei dem der Rückstoss auch bei Verwendung stärkerer Antriebsfedern klein ist.The object of the present invention is to develop a tacker of the aforementioned type, which avoids the aforementioned disadvantages and in which the recoil is small even when using stronger drive springs.

Diese Aufgabe wird erfindungsgemäss durch die in Anspruch 1 genannten Massnahmen gelöst. Demnach weist die Antriebseinrichtung ein erstes Antriebsfederelement mit einer ersten Expansionsrichtung und ein zweites Antriebsfederelement mit einer zweiten Expansionsrichtung auf, die der ersten Expansionsrichtung entgegengesetzt ist. Dadurch wird erreicht, dass während eines Setzvorganges die Massen der Federn in entgegengesetzte Richtungen bewegt werden, so dass die Rückstossbeschleunigungen der Antriebsfederelemente sich zumindest teilweise kompensieren. Die Antriebsfederelemente können dabei z. B. als Schraubenfedern, Blattfedern, Tellerfedern, Schenkelfedern oder Torsionsfedern ausgebildet sein.This object is achieved according to the invention by the measures mentioned in claim 1. Accordingly, the drive means comprises a first drive spring member having a first expansion direction and a second drive spring member having a second expansion direction opposite to the first expansion direction. This ensures that during a setting process, the masses of the springs are moved in opposite directions, so that the recoil accelerations of the drive spring elements compensate at least partially. The drive spring elements can be z. B. be designed as coil springs, leaf springs, disc springs, torsion springs or torsion springs.

Vorteilhaft definieren das erste Antriebsfederelement und das zweite Antriebsfederelement jeweils eine Federachse, die beide koaxial zueinander verlaufen, wodurch bei Eintreibvorgängen auch Drehbeschleunigungen des Eintreibgerätes vermieden werden können.Advantageously, the first drive spring element and the second drive spring element each define a spring axis, both of which run coaxially with one another, whereby rotational accelerations of the tacker can be avoided during drive-in processes.

In einer konstruktiv einfachen Lösung stützen sich dabei sowohl das erste Antriebsfederelement als auch das zweite Antriebsfederelement sich gegenüberliegend jeweils mit einem ersten Ende an einem gehäusefesten Abstützelement ab. Das Abstützelement kann dabei z. B. als Gehäusequerwand oder Gehäusestrebe ausgebildet sein. Durch die spiegelsymmetrische Anordnung der Antriebsfederelemente wirken deren Kraft-Vektoren exakt entgegengesetzt, so dass sich nicht nur der Rückstoss bei entsprechend ausgeglichener Federmasse auf beiden Seiten genau aufhebt, sondern auch keine hohen Belastungen auf das gehäusefeste Abstützelement einwirken.In a structurally simple solution, both the first drive spring element and the second drive spring element are supported opposite each other with a first end on a housing-fixed support element. The support element can be z. B. be designed as a housing transverse wall or housing strut. Due to the mirror-symmetrical arrangement of the drive spring elements whose force vectors act exactly opposite, so that not only cancel the recoil with appropriately balanced spring mass on both sides exactly, but also act no high loads on the housing-fixed support.

Von Vorteil ist es ferner, wenn die Federachsen des ersten Antriebsfederelements und des zweiten Antriebsfederelements jeweils achsparallel zu einer durch den Eintreibstössel definierten Achse verlaufen, wodurch eine kompakte Bauweise ermöglicht wird.It is also advantageous if the spring axes of the first drive spring element and of the second drive spring element each extend axially parallel to an axis defined by the drive ram, whereby a compact design is made possible.

Vorteilhaft weist das zweite Antriebsfederelement eine Masse auf, die wenigstens so gross ist wie die Masse des ersten Antriebsfederelements, wodurch sich die Rückstossbeschleunigungen beider Antriebsfederelemente nahezu vollständig kompensieren.Advantageously, the second drive spring element to a mass which is at least as large as the mass of the first drive spring element, whereby the recoil accelerations of both drive spring elements compensate almost completely.

Günstig ist es ferner, wenn das zweite Antriebsfederelement eine Masse aufweist, die mit einer Toleranz von +/- 10 % der Gesamtmasse aus Eintreibstössel und erstem Antriebsfederelement entspricht. Durch diese Massnahme kann über das zweite Antriebsfederelement nicht nur die Rückstossbeschleunigung des ersten Antriebsfederelements sondern auch die durch den Eintreibstössel hervorgerufene Rückstossbeschleunigung innerhalb der Toleranz nahezu vollständig kompensiert werden. Das erste Antriebsfederelement ist dabei das Federelement dessen Expansionsrichtung der Eintreibrichtung des Eintreibstössels entspricht.It is also favorable if the second drive spring element has a mass which corresponds to a tolerance of +/- 10% of the total mass of driving ram and the first drive spring element. By this measure, not only the recoil acceleration of the first drive spring element but also the recoil acceleration caused by the drive-in ram can be almost completely compensated for within the tolerance via the second drive spring element. The first drive spring element is the spring element whose expansion direction corresponds to the driving direction of the drive-in ram.

Von Vorteil ist es ferner, wenn das erste Antriebsfederelement und das zweite Antriebsfederelement über eine Getriebeeinrichtung miteinander gekoppelt sind, wobei die Getriebeeinrichtung abtriebsseitig mit dem Eintreibstössel gekoppelt ist. Durch diese Massnahme kann die Bewegungsenergie beider Antriebsfederelemente auf einfache Weise zusammengefasst und auf den Eintreibstössel übertragen werden. Die Getriebeeinrichtung kann dabei z. B. als Seilzuggetriebe ausgebildet sein. Die Getriebeeinrichtung kann ausserdem eine Übersetzung zwischen Eingangsbewegung und Abtriebsbewegung aufweisen, wie z. B. ein Übersetzungsverhältnis von ca. 1:4, wodurch bei gegebenem Expansionsweg der Antriebsfederelemente ein 4 mal so langer Hubweg des Eintreibstössels erzielt wird.It is also advantageous if the first drive spring element and the second drive spring element are coupled to each other via a transmission device, wherein the transmission device is coupled on the output side with the drive-in ram. By this measure, the kinetic energy of both drive spring elements can be summarized in a simple manner and transmitted to the drive ram. The transmission device can be z. B. be designed as a cable transmission. The transmission device may also have a translation between input movement and output movement, such. Example, a transmission ratio of about 1: 4, whereby for a given expansion path of the drive spring elements, a 4 times longer stroke of Eintreibstössels is achieved.

In den Zeichnungen ist die Erfindung in einem Ausführungsbeispiel dargestellt.In the drawings, the invention is shown in one embodiment.

Es zeigen:

Fig. 1
ein erfindungsgemässes Eintreibgerät im Längsschnitt in seiner Ausgangsstellung,
Fig. 2
das Eintreibgerät aus Fig. 1 in einer betätigten Stellung.
Show it:
Fig. 1
an inventive driving tool in longitudinal section in its initial position,
Fig. 2
the tacker off Fig. 1 in an actuated position.

Das in den Figuren 1 und 2 dargestellte Eintreibgerät 10 weist ein Gehäuse 11 und eine darin angeordnete, insgesamt mit 30 bezeichnete Antriebsanordnung für einen Eintreibstössel 13 auf, der in einer Führung 12 versetzbar geführt ist. Der Eintreibstössel 13 weist dabei einen Eintreibabschnitt 14 und einen Kopfabschnitt 15 auf.That in the FIGS. 1 and 2 illustrated tackle 10 has a housing 11 and disposed therein, generally designated 30 drive arrangement for a drive-in ram 13 which is guided in a guide 12 displaceable. The drive-in ram 13 has a drive-in section 14 and a head section 15.

An das in Eintreibrichtung 27 liegenden Ende der Führung 12 schliesst sich eine koaxial zu der Führung 12 verlaufende Bolzenführung 17 an diese an. Seitlich von der Bolzenführung 17 abragend ist ein Befestigungselementemagazin 61 angeordnet in dem Befestigungselemente 60 bevorratet sind.At the lying in the driving direction 27 end of the guide 12 is a coaxial with the guide 12 extending bolt guide 17 connects to this. On the side of the bolt guide 17 abragend a fastener magazine 61 is arranged in the fasteners 60 are stored.

Die Antriebsanordnung 30 beinhaltet ein erstes Antriebsfederelement 31 und ein zweites Antriebsfederelement 32 die beide im Wesentlichen die gleiche Federmasse aufweisen und die sich einander gegenüberliegend an einem gehäusefesten Abstützelement 36 abstützen, welches vorliegend als Gehäusestrebe ausgebildet ist. Beide Antriebsfederelemente 31, 32 sind hier als Schraubenfedern ausgebildet. Jedes der beiden Antriebsfederelemente 31, 32 definiert jeweils eine Federachse F1, F2 die in der dargestellten Antriebsanordnung 30 koaxial zueinander angeordnet sind. Die Federachsen F1 und F2 verlaufen ferner noch parallel zu einer durch den Eintreibstössel 13 definierten Achse A. Wie insbesondere aus Fig. 2 ersichtlich ist, weisen beide Antriebsfederelemente 31, 32 Expansionsrichtungen 37, 38 auf, die einander entgegengesetzt sind, d. h. bei einer Entspannung der Antriebsfederelemente 31, 32 bewegen sich ihre, dem Abstützelement 36 abgewandten freien Enden in genau entgegengesetzte Richtungen, wodurch sich ihre entgegengesetzt wirkenden Rückstossbeschleunigungen bei einem Eintreibvorgang gegenseitig kompensieren.The drive arrangement 30 includes a first drive spring element 31 and a second drive spring element 32, both of which have substantially the same spring mass and which are supported opposite one another on a housing-fixed support element 36, which in the present case is designed as a housing strut. Both drive spring elements 31, 32 are formed here as coil springs. Each of the two drive spring elements 31, 32 each defines a spring axis F1, F2 which are arranged coaxially with each other in the illustrated drive arrangement 30. The spring axes F1 and F2 also still run parallel to an axis A defined by the drive-in ram 13 Fig. 2 it can be seen, both drive spring elements 31, 32 have expansion directions 37, 38, which are opposite to each other, ie at a relaxation of the drive spring elements 31, 32 move their, the support member 36 facing away from free ends in exactly opposite directions, causing their oppositely acting recoil accelerations Compensate each other in a drive-in.

Beide Antriebsfederelemente 31, 32 greifen vermittelt über eine insgesamt mit 39 bezeichnete Getriebeeinrichtung am Kopfabschnitt 15 des Eintreibstössels 13 an. Die Getriebeeinrichtung 39 ist in dem Ausführungsbeispiel gemäss den Figuren 1 und 2 dabei als Seilzuggetriebe ausgebildet. Das erste Antriebsfederelement 31 und das zweite Antriebsfederelement 32 sind dabei jeweils zwischen dem gehäusefesten Abstützelement 36 und jeweils einem Federabtriebselement 35 eingespannt. Die ringförmig ausgebildeten Federabtriebselemente 35 tragen an ihren jeweils dem zugeordneten Antriebsfederelement 31, 32 abgewandten Seite Rollen 34 für ein seil- oder bandförmiges Transmissionsmittel 33 der Getriebeeinrichtung 39.Both drive spring elements 31, 32 engage mediated via a total of 39 designated gear means on the head portion 15 of the drive-in ram 13. The transmission device 39 is in the embodiment according to the FIGS. 1 and 2 it is designed as a cable transmission. The first drive spring element 31 and the second drive spring element 32 are in each case clamped between the housing-fixed support element 36 and in each case a spring output element 35. The ring-shaped spring output elements 35 carry on their side facing away from the associated drive spring element 31, 32 side rollers 34 for a rope or band-shaped transmission means 33 of the transmission device 39th

Das seil- oder bandförmige Transmissionsmittel 33, welches mit seinem ersten und zweiten freien Ende 42, 43 an dem gehäusefesten Abstützelement 36 festgelegt ist, ist über diese Rollen 34 um das Federabtriebselement 35 herumgeführt. Gleichzeitig ist das Transmissionsmittel 33 um das freie Ende des Kopfabschnitts 15 des Eintreibstössels 13 herumgeführt.The rope or band-shaped transmission means 33, which is fixed with its first and second free end 42, 43 on the support member fixed to the housing 36, is above this Rollers 34 are guided around the spring output element 35. At the same time, the transmission means 33 is guided around the free end of the head section 15 of the drive rod 13.

In der aus Fig. 1 ersichtlichen Ausgangsstellung 22 des Eintreibstössels 13 ist dieser über die Getriebeeinrichtung 39 und die Antriebsfederelemente 31, 32 elastisch vorgespannt, und ist mit seinem Kopfabschnitt 15 und dem um diesen herumgeführten Transmissionsmittel 33 durch die Öffnungen der Federabtriebselemente 35, die Antriebsfederelemente 31, 32 und eine Öffnung im gehäusefesten Abstützelement 36 hindurchgeführt.In the out Fig. 1 apparent starting position 22 of the drive rod 13 is this via the transmission device 39 and the drive spring elements 31, 32 elastically biased, and is with its head portion 15 and the guided around this transmission means 33 through the openings of the spring output elements 35, the drive spring elements 31, 32 and an opening in housing-fixed support member 36 passed.

In der Ausgangsstellung 22 ist der Eintreibstössel 13 durch eine insgesamt mit 50 bezeichnete Sperreinrichtung gehalten, die eine Klinke 51 aufweist, die in einer Sperrstellung 54 (siehe Fig. 1) an einer Sperrfläche 53 an einem Vorsprung 58 des Eintreibstössels 13 angreift und diesen gegen die Kraft des Antriebsfederelements 31 festhält. Die Klinke 51 ist dabei an einem Stellmotor 52 gelagert und über diesen in eine aus Fig. 2 ersichtliche Freigabestellung 55 überführbar, wie nachfolgend noch beschrieben werden wird. Der Stellmotor 52 ist über eine elektrische erste Steuerleitung 56 mit einer Steuereinheit 23 verbunden.In the initial position 22 of the drive-in ram 13 is held by a generally designated 50 locking device having a pawl 51 which in a blocking position 54 (see Fig. 1 ) engages a locking surface 53 on a projection 58 of the drive-in ram 13 and holds it against the force of the drive spring element 31. The pawl 51 is mounted on a servomotor 52 and about this in a Fig. 2 apparent release position 55 can be transferred, as will be described below. The servomotor 52 is connected via an electrical first control line 56 to a control unit 23.

Das Eintreibgerät 10 weist ferner noch einen Handgriff 20 auf, an dem ein Auslöseschalter 19 zum Auslösen eines Eintreibvorganges mit dem Eintreibgerät 10 angeordnet ist. In dem Handgriff 20 ist ferner noch eine insgesamt mit 21 bezeichnete Stromversorgung angeordnet, über die das Eintreibgerät 10 mit elektrischer Energie versorgt wird. Vorliegend beinhaltet die Stromversorgung 21 wenigstens einen Akkumulator. Die Stromversorgung 21 ist über elektrische Versorgungsleitungen 24 sowohl mit der Steuereinheit 23 als auch mit dem Auslöseschalter 19 verbunden. Die Steuereinheit 23 ist dabei ferner noch über eine Schalterleitung 57 mit dem Auslöseschalter 19 verbunden.The tacker 10 further includes a handle 20 on which a trigger switch 19 is arranged to trigger a driving operation with the tacker 10. In the handle 20 is also still a total designated 21 power supply arranged, via which the tacker 10 is supplied with electrical energy. In the present case, the power supply 21 includes at least one accumulator. The power supply 21 is connected via electrical supply lines 24 both to the control unit 23 and to the trigger switch 19. The control unit 23 is further connected via a switch line 57 to the trigger switch 19.

An einer Mündung 62 des Eintreibgerätes 10 ist ein Schaltmittel 29 angeordnet, das über eine Schaltmittelleitung 28 elektrisch mit der Steuereinheit 23 verbunden ist. Das Schaltmittel 29 sendet ein elektrisches Signal an die Steuereinheit 23, sobald das Eintreibgerät 10 an ein Werkstück U angedrückt wird, wie aus Fig. 2 ersichtlich ist, und stellt so sicher, dass das Eintreibgerät 10 nur ausgelöst werden kann, wenn es ordnungsgemäss an ein Werkstück U angedrückt worden ist.At a mouth 62 of the tacker 10, a switching means 29 is arranged, which is electrically connected via a switching means 28 to the control unit 23. The switching means 29 sends an electrical signal to the control unit 23 as soon as the tacker 10 is pressed against a workpiece U, as shown Fig. 2 can be seen, thus ensuring that the tacker 10 can be triggered only when it has been properly pressed against a workpiece U.

An dem Eintreibgerät 10 ist ferner noch eine insgesamt mit 70 bezeichnete Spanneinrichtung angeordnet. Diese Spanneinrichtung 70 umfasst einen Motor 71, über den eine Antriebsrolle 72 antreibbar ist. Der Motor 71 ist über eine zweite Steuerleitung 74 elektrisch mit der Steuereinheit 23 verbunden und kann über diese in Betrieb gesetzt werden, z. B. wenn sich der Eintreibstössel 13 in seiner in Eintreibrichtung 27 liegenden Endposition befindet oder wenn das Eintreibgerät wieder vom Untergrund abgehoben wird. Der Motor 71 weist ein Abtriebsmittel 75, wie ein Abtriebsrad, auf, das mit der Antriebsrolle 72 koppelbar ist. Die Antriebsrolle 72 ist dazu drehbar an einem längsverstellbaren Stellarm 78 eines als Solenoid ausgebildeten Stellmittels 76 gelagert. Das Stellmittel 76 ist dabei über eine Stellmittelleitung 77 mit der Steuereinheit 23 verbunden. Im Betrieb dreht sich die Antriebsrolle 72 in Richtung des gestrichelt angedeuteten Pfeils 73.At the tacker 10 is also still a total of 70 designated clamping device is arranged. This tensioning device 70 comprises a motor 71, via which a drive roller 72 is drivable. The motor 71 is electrically connected to the control unit 23 via a second control line 74 and can be put into operation via this, z. B. when the driving ram 13 is in its lying in the driving direction 27 end position or when the tacker is lifted off the ground again. The motor 71 has an output means 75, such as a driven wheel, which can be coupled to the drive roller 72. The drive roller 72 is rotatably mounted on a longitudinally adjustable actuating arm 78 of a solenoid 76 designed as a solenoid. The adjusting means 76 is connected via an actuating line 77 to the control unit 23. In operation, the drive roller 72 rotates in the direction of the arrow 73 indicated by dashed lines.

Wird das Eintreibgerät 10 über einen hier nicht dargestellten Hauptschalter in Betrieb genommen, dann stellt die Steuereinheit 23 zunächst sicher, dass sich der Eintreibstössel 13 in seiner aus Fig. 1 ersichtlichen Ausgangsstellung 22 befindet. Ist dieses nicht der Fall, dann wird die Antriebsrolle 72 vom Stellmittel 76 an das bereits über den Motor 71 in Drehung versetzte Abtriebsmittel 75 heranbewegt und mit diesem eingekuppelt. Gleichzeitig kuppelt die Antriebsrolle 72 an dem Eintreibstössel 13 ein, so dass dieser über die sich in Richtung des Pfeils 73 drehende Antriebsrolle 72 in Richtung zur Antriebsanordnung 30 hin versetzt wird. Dabei wird das Antriebsfederelement 32 der Antriebsanordnung 30 gespannt. Hat der Eintreibstössel 13 seine Ausgangsstellung 22 erreicht, dann fällt die Klinke 51 der Sperreinrichtung 50 in die Sperrfläche 53 am Eintreibstössel 13 ein und hält diesen in der Ausgangsstellung 22. Der Motor 71 kann dann über die Steuereinheit 23 abgeschaltet werden und das Stellmittel 76 fährt die Antriebsrolle 72 ebenfalls gesteuert von der Steuereinheit 23 von ihrer eingekuppelten Stellung an dem Abtriebsmittel 75 und dem Eintreibstössel 13 in seine ausgekuppelte Stellung (vgl. Fig. 2).If the tacker 10 is put into operation via a main switch, not shown here, then the control unit 23 first ensures that the drive-in ram 13 is in its off Fig. 1 apparent starting position 22 is located. If this is not the case, then the drive roller 72 is moved up by the adjusting means 76 to the output means 75, which has already been rotated via the motor 71, and is engaged therewith. At the same time, the drive roller 72 engages the drive-in ram 13 so that it is offset in the direction of the drive arrangement 30 via the drive roller 72 rotating in the direction of the arrow 73. In this case, the drive spring element 32 of the drive assembly 30 is tensioned. Has the drive tappet 13 reaches its initial position 22, then falls the pawl 51 of the locking device 50 in the blocking surface 53 on Eintreibstössel 13 and holds it in the starting position 22. The motor 71 can then be turned off via the control unit 23 and the actuating means 76 moves the Drive roller 72 also controlled by the control unit 23 from its engaged position on the output means 75 and the drive tappet 13 in its disengaged position (see. Fig. 2 ).

Wird nun das Eintreibgerät 10 an ein Werkstück U angedrückt, wie aus Fig. 2 ersichtlich ist, dann wird zunächst über das Schaltmittel 29 die Steuereinheit 23 in Setzbereitschaft versetzt. Wird dann der Auslöseschalter 19 von einem Bediener betätigt, dann wird über die Steuereinheit 23 die Sperreinrichtung 50 in ihre Freigabestellung 55 versetzt, wobei die Klinke 51 über den Stellmotor 52 von der Sperrfläche 53 am Eintreibstössel 13 abgehoben wird. Die Klinke 51 kann in Richtung auf den Eintreibstössel 13 federbelastet sein, um diese automatisch wieder in ihre Sperrstellung 54 zu verfahren.Now, the tacker 10 is pressed against a workpiece U, as shown Fig. 2 it can be seen, then the control unit 23 is first set in Setzbereitschaft via the switching means 29. If the trigger switch 19 is then actuated by an operator, then the blocking device 50 is displaced into its release position 55 via the control unit 23, wherein the pawl 51 is lifted off the blocking surface 53 on the drive ram 13 via the positioning motor 52. The pawl 51 may be spring-loaded in the direction of the drive-in ram 13 in order to automatically move it back into its blocking position 54.

Der Eintreibstössel 13 wird daraufhin vermittelt über die Getriebeeinrichtung 39 über die Antriebsfederelemente 31, 32 der Antriebsanordnung 30 in Eintreibrichtung 27 bewegt, wobei ein Befestigungselement 60 in das Werkstück U eingetrieben wird. Das erste Antriebsfederelement 31 expandiert dabei in Richtung der ersten Expansionsrichtung 37, die mit der Eintreibrichtung 27 des Eintreibstössels 13 übereinstimmt. Das zweite Antriebsfederelement 32 hingegen expandiert in genau entgegengesetzter Richtung, d. h. in Richtung der zweiten Expansionsrichtung 38, wodurch der Rückstoss beider Antriebsfederelemente 31, 32 sich aufhebt.The drive-in ram 13 is then moved via the transmission device 39 via the drive spring elements 31, 32 of the drive arrangement 30 in the drive-in direction 27, wherein a fastening element 60 is driven into the workpiece U. The first drive spring element 31 expands in the direction of the first expansion direction 37, the coincides with the driving direction 27 of the drive rod 13. By contrast, the second drive spring element 32 expands in exactly the opposite direction, ie in the direction of the second expansion direction 38, as a result of which the recoil of both drive spring elements 31, 32 is canceled out.

Vorteilhaft ist der Expansionsweg der Antriebsfederelemente 31, 32 dabei über die Getriebeeinrichtung 39 derart übersetzt, dass der Beschleunigungsweg des Eintreibstössels 13 länger ist als der jeweilige Expansionsweg der Antriebsfederelemente 31, 32. Das Übersetzungsverhältnis der Getriebeeinrichtung 39 beträgt dabei in dem Ausführungsbeispiel ca. 1:4.Advantageously, the expansion path of the drive spring elements 31, 32 is translated via the transmission device 39 such that the acceleration travel of the drive tappet 13 is longer than the respective expansion travel of the drive spring elements 31, 32. The transmission ratio of the transmission device 39 is approximately 1: 4 in the exemplary embodiment ,

Zur Rückführung des Eintreibstössels 13 und zum Spannen der Antriebsfederelemente 31, 32 wird am Ende eines Eintreibvorganges die Spanneinrichtung 70 über die Steuereinheit 23 aktiviert, wenn das Eintreibgerät 10 wieder vom Werkstück U abgehoben wird. Das Schaltmittel 29 liefert dazu ein Signal an die Steuereinheit 23. Über die Spanneinrichtung 70 wird der Eintreibstössel 13 in der bereits beschriebenen Weise gegen das Antriebsfederelement 31 der Antriebsanordnung 30 gefahren und das Antriebsfederelement 31 dabei erneut gespannt bis die Klinke 51 wieder in ihre Sperrstellung 54 an der Sperrfläche 53 am Eintreibstössel 13 einfallen kann.For returning the drive-in ram 13 and for tensioning the drive spring elements 31, 32, the clamping device 70 is activated via the control unit 23 at the end of a drive-in operation when the drive-in device 10 is lifted off the workpiece U again. The switching means 29 supplies to a signal to the control unit 23. About the tensioning device 70 of the driving ram 13 is driven in the manner already described against the drive spring element 31 of the drive assembly 30 and the drive spring member 31 while again clamped to the pawl 51 back to its blocking position 54 at the blocking surface 53 on Eintreibstössel 13 can occur.

Claims (7)

  1. Hand-held driving device for fasteners, having a propelling arrangement (30) for a driving plunger (13) which is displaceably mounted in a guide (12), which propelling arrangement (30) has at least one first propelling spring-member (31) which has a first direction of expansion (37) and which can be tensed by means of a tensing means (70), characterised in that there is provided at least one second propelling spring-member (32) which has a second direction of expansion (38) which is opposite from the first direction of expansion (37).
  2. Driving device according to claim 1, characterised in that the first propelling spring-member (31) and the second propelling spring-member (32) define respective spring axes (F1, F2) which both extend on a common axis.
  3. Driving device according to claim 1 or 2, characterised in that the first propelling spring-member (31) and the second propelling spring-member (32) are supported by respective first ends against a supporting member (36) secured to a housing, in opposite positions.
  4. Driving device according to claim 1 or 2, characterised in that the spring axes (F1, F2) of the first propelling spring-member (31) and second propelling spring-member (32) each extend parallel to an axis (A) which is defined by the driving plunger (13).
  5. Driving device according to claim 1, characterised in that the mass of the second propelling spring-member (32) is at least as great as the mass of the first propelling spring-member (31).
  6. Driving device according to claim 1 or 5, characterised in that the mass of the second propelling spring-member (32) corresponds to the total mass of the driving plunger (13) and the first propelling spring-member (31) with a tolerance of +/- 10%.
  7. Driving device according to one of claims 1 to 6, characterised in that the first propelling spring-member (31) and second propelling spring-member (32) are coupled together by a transmission arrangement (39), the transmission arrangement (39) being coupled at the output end to the driving plunger (13).
EP08103315A 2007-04-13 2008-04-02 Manually operated fastener driving device Active EP1980369B1 (en)

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PL08103315T PL1980369T3 (en) 2007-04-13 2008-04-02 Manually operated fastener driving device

Applications Claiming Priority (1)

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DE102007000226A DE102007000226A1 (en) 2007-04-13 2007-04-13 Hand-guided tacker

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EP1980369A2 EP1980369A2 (en) 2008-10-15
EP1980369A3 EP1980369A3 (en) 2010-05-26
EP1980369B1 true EP1980369B1 (en) 2011-05-25

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US (1) US7815088B2 (en)
EP (1) EP1980369B1 (en)
JP (1) JP5192275B2 (en)
CN (1) CN101284375B (en)
AT (1) ATE510661T1 (en)
AU (1) AU2008201446B2 (en)
DE (1) DE102007000226A1 (en)
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DE102007000226A1 (en) 2008-10-16
JP2008260124A (en) 2008-10-30
AU2008201446A1 (en) 2008-10-30
PL1980369T3 (en) 2011-10-31
ATE510661T1 (en) 2011-06-15
AU2008201446B2 (en) 2010-08-05
CN101284375B (en) 2011-08-31
CN101284375A (en) 2008-10-15
JP5192275B2 (en) 2013-05-08
ES2363652T3 (en) 2011-08-11
US20080296339A1 (en) 2008-12-04
EP1980369A2 (en) 2008-10-15
US7815088B2 (en) 2010-10-19
EP1980369A3 (en) 2010-05-26

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