EP2567787B1 - Electric screwdriver - Google Patents
Electric screwdriver Download PDFInfo
- Publication number
- EP2567787B1 EP2567787B1 EP12195434.1A EP12195434A EP2567787B1 EP 2567787 B1 EP2567787 B1 EP 2567787B1 EP 12195434 A EP12195434 A EP 12195434A EP 2567787 B1 EP2567787 B1 EP 2567787B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- friction
- output shaft
- power wrench
- brake
- housing
- 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.)
- Active
Links
- 230000008878 coupling Effects 0.000 description 7
- 238000010168 coupling process Methods 0.000 description 7
- 238000005859 coupling reaction Methods 0.000 description 7
- 238000005452 bending Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 230000000994 depressogenic effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 239000004575 stone Substances 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
- B25B21/004—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose of the ratchet type
- B25B21/005—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose of the ratchet type driven by a radially acting hydraulic or pneumatic piston
Definitions
- the invention relates to a power wrench with a hydraulic cylinder containing a driving part and a driven part, wherein the driven part has a rotatably mounted in a housing output shaft which is rotated by a ratchet lever at intervals.
- a power wrench according to the introductory part of claim 1 is known from US 4137800 known.
- a frictionally held rotatable scale ring is arranged concentrically to the drive shaft having a central window through which a mark of the output shaft is visible.
- Such a scale ring can be used to indicate the angle of rotation of the output shaft.
- the scale ring is first adjusted by manually turning to the respective position of the mark to memorize the initial position. During the screwing operation, the marking moves relative to the scale ring, whereby the respective screw angle can be read off easily.
- the invention has the additional object to provide a power wrench that allows a uniform tightening screws without security risk.
- the power wrench according to the invention is characterized by the claim 1.
- the friction brake may include a continuously acting friction brake which generates a frictional force between the drive shaft and the housing. This frictional force is generated permanently and during the power stroke it is overcome by the hydraulic drive.
- the friction brake causes a uniform tightening of the screw. It allows an installer to simultaneously monitor multiple screwdriving operations performed with power wrenches.
- the power wrench is reliably positioned and held in any working position regardless of the phase of the respective stroke. There is no incremental locking.
- the restraint system is constantly active. Switching the hydraulic system on and off is not required. There are no additional bending moments on the screw, as is the case with systems with pawl. There is no jamming of the screwing tool after the last stroke. Therefore, time-consuming solution procedures are eliminated.
- the safe removal of the device is guaranteed. Due to the elimination of a latching and disengagement, the device is secured in any working position.
- the friction brake may comprise at least one friction shoe, which is arranged substantially radially to the output shaft and presses against a circumferential friction surface.
- the friction surface is preferably arranged on the output shaft or on a component connected thereto. But it is also possible to provide the friction shoe on the output shaft and to let it act on a friction surface of the housing.
- each friction shoe is pressed by an adjustable clamping device against the drive shaft. In this way an adjustment or adjustment of the friction brake is possible.
- the tensioning device preferably has a clamping wedge.
- the friction brake has a flange of the drive shaft which presses against a housing-fixed friction part. By acting on the flange friction force the output shaft is braked.
- a spring is provided which presses the output shaft in the direction of the friction part.
- the friction member may be rotatably connected to a coupling ring which presses axially against the spring via a thrust bearing.
- the power screwdriver according to the Figures 1 - 3 has a housing 10 which is formed substantially L-shaped and contains a drive part 11 in one leg and a driven part 12 in the other leg.
- the drive member includes a hydraulic piston-cylinder unit (not shown) with a reciprocating piston rod.
- the piston rod drives a ratchet lever.
- the output part 12 includes an output shaft 14 mounted in the housing, which is a hollow shaft ( FIG. 3 ) containing a hexagon socket 15.
- the ratchet lever 16 Between two side walls 10A, 10B of the housing 10 is the ratchet lever 16, which is coupled via a toothing 17 with an external toothing of the output shaft 14.
- the ratchet lever 16 takes in a working stroke, the output shaft 14 in the one direction with, while it slides back empty in the return stroke. In this way, the output shaft 14 is rotated at intervals.
- the friction brake 20 has a friction shoe 21, which is arranged radially to the output shaft 14 and presses against a friction surface 22 on the circumference of the output shaft.
- a tensioning device 23 has a clamping wedge 24, which is provided with a threaded bore into which a clamping screw 25, which in the Housing wall 10B is held, is screwed. By tightening the clamping screw 25 of the clamping wedge 24 to the outside (in accordance with FIG. 3 pulled to the right), whereby it presses against a rear wedge surface of the friction shoe 21 and this drives in the direction of the friction surface 22.
- friction shoe 21 In the present case, only a single friction shoe 21 is provided, however, there may be a plurality of friction shoes, which are preferably distributed uniformly around the circumference of the output shaft 14.
- the continuously acting friction brake 20 exerts a constant braking force on the output shaft upon rotation of the output shaft, so that it is prevented from turning back.
- a spline 30 On the cylindrical drive member 11 is a spline 30, on which a (not shown) support foot can be plugged, which is set against a stationary abutment to a rotation of the housing 10th to avoid during the screwing.
- the housing 10 also contains here two parallel housing walls 10a, 10b with holes in which the output shaft 14 is mounted.
- the output shaft 14 is fully formed here and it protrudes on one side out of the housing 10, where on the output shaft is a slip-on square 26, on which a key nut can be attached.
- On a spline 31 of the output shaft 14 is rotatably seated a sleeve 32, which is additionally provided with an external toothing 33. In this external teeth engages the teeth of a Mit freelancesteines 34, which is housed in the interior of the housing 10 and engages with the ratchet lever 16.
- the reciprocating ratchet lever 16 drives on the Mit predominantlystein 34, the sleeve 32 and the output shaft 14, wherein the sleeve and the output shaft are taken only in one direction of rotation.
- a slider 35 In an axial recess of the output shaft 14 slides a slider 35 whose end wall 36 forms a push button.
- a spring 37 pushes the slider 35 to the outside.
- the slide has a circumferential groove 38 which, when the slide is pushed in, partially receives a ball 39, which is movable in an axial bore of the output shaft.
- an intermediate sleeve 40 which is unlocked on a shaft of the output shaft 14, of the output shaft, so that the intermediate sleeve can be removed when the push button 36 is depressed.
- FIG. 7 shows, which is rotatably connected to the output shaft 14 intermediate sleeve 40 at the outer ends of a radial flange 41.
- the friction surface 42 may also be formed by a friction lining.
- the flange 41 thus forms a friction brake 20 with the friction surface 42.
- the coupling ring 45 On a thread 44 of the friction member 43 sits a coupling ring 45 which is secured with a locking pin 46.
- the coupling ring 45 engages around a needle bearing 47 which is axially supported on the coupling ring 45 and which presses on the opposite side with a disc 48 against the plate spring 49.
- the coupling ring 45 together with the plate spring 49 is part of a clamping device 23 for adjusting the frictional force of the friction brake 20th
- the scale ring 50 On the coupling ring 45 sits a scale ring 50 which is secured with an O-ring 51 latching.
- the scale ring 50 has an angle scale of 0 ° - 360 °, which in FIG. 4 is visible.
- the scale ring is rotatable on the housing 10 and arranged concentrically to the output shaft. It has a centric window 53, through which a mark 52 of the output shaft is visible. It can be rotated on the coupling ring rubbing in any angular position, so that it can be adjusted with the position 0 ° to the mark 52 on the push button 36.
- the push button 36 is rotationally fixed to the output shaft 14th connected and he thus indicates the respective rotational position of the screw as a relative position.
- the scale ring 50 is manually zeroed to memorize the initial position. Thereafter, during the screwing operation, the marking 52 moves in accordance with the progress of the screwing, so that the user can read off the respective angle of rotation which has been swept over since the start of the screwing operation or since another point of the screwing operation.
- the scale ring in conjunction with the output shaft belonging to the mark 52 has an independent meaning and is not bound to the presence of a friction brake.
- FIGS. 8-11 includes a rotatably mounted between the housing walls 10a and 10b output shaft 14 with an external toothing (not shown), in which a reciprocally movable ratchet lever 16 engages.
- the output shaft 14 includes a réelleSechskantprofil 15. In this is from one end (according FIG. 9 and 10 from the left) a screw head is inserted, while at the opposite end (right) the friction brake 20 and the scale ring 50 are located.
- the friction brake 20 has a friction part 60 with a bush, which is rotationally secured to the hollow output shaft 14 is connected.
- An annular friction disk 61 projects radially from the bush and has a circumferential region 62 with two radial friction surfaces 62a and 62b.
- the brake pads 63a, 63b of the friction brake 20 engage.
- the friction lining 63 a is fixed to an inner brake shoe 64 and the friction lining 63 b is attached to an outer brake shoe 65, the brake shoes lying parallel to one another and clamping the edge 62 of the friction part 60 between them.
- the clamping effect is caused by two clamping screws 66 (FIG. FIG. 8 ), which pull the brake shoes 64 and 64 against each other and can be adjusted to adjust the braking force of the friction brake 20.
- a retaining screw 67 is arranged, which is screwed into the housing wall 10b and the friction brake 20 holds on the housing 10.
- the friction brake 20 is formed in the third embodiment in the manner of a caliper brake, wherein the two brake shoes 64, 65 form a brake caliper, which engages with the friction linings 63a, 63b astride the edge of the friction disc 61.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
- Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
Description
Die Erfindung betrifft einen Kraftschrauber mit einem einen Hydraulikzylinder enthaltenden Antriebsteil und einem Abtriebsteil, wobei der Abtriebsteil eine in einem Gehäuse drehbar gelagerte Abtriebswelle aufweist, die von einem Ratschenhebel in Intervallen gedreht wird.The invention relates to a power wrench with a hydraulic cylinder containing a driving part and a driven part, wherein the driven part has a rotatably mounted in a housing output shaft which is rotated by a ratchet lever at intervals.
Ein Kraftschrauber gemäß dem einleitenden Teil des Anspruchs 1 ist aus der
Bekannt sind hydraulische Kraftschrauber, die nach dem Ratschenhebel-Prinzip arbeiten. Solche Kraftschrauber können bei Anwendung entsprechend hoher Hydraulikdrücke für sehr hohe Drehmomente benutzt werden. Nach einem Hub der hydraulischen Kolben-Zylinder-Einheit besteht die Tendenz, dass die Abtriebswelle sich um einem geringeren Winkelbetrag zurückdreht. Dies liegt daran, dass die Schraubenkonstruktion sich nach jedem Arbeitshub teilweise entspannt. Um ein solches Entspannen zu verhindern, ist es bereits bekannt, an der Abtriebswelle einen Blockierstein angreifen zu lassen, der in einer Außenverzahnung der Abtriebswelle eingreift und ein Zurückdrehen verhindert. Hierbei besteht der Nachteil eines Sicherheitsrisikos aufgrund unzuverlässiger Haltesysteme. Bei einem Stoppen des Hydraulikaggregates, das den Kraftschrauber mit Druck versorgt, bei Stromausfall oder bei unvollständiger Hublänge können sich die Geräte beim Arbeitsprozess von der zu drehenden Schraube lösen. Dies bedeutet eine Unfallgefahr. Geräte mit Rückhalte-Klinkensystem können sich nach Erreichen des Endmomentes verspannen und müssen dann mit hohen Zeitaufwand von dem Verschraubungsobjekt gelöst werden. Ein erneutes Anfahren des Schraubers auf das maximale eingestellte Drehmoment ist notwendig und kann zu Drehmoment-Ungenauigkeiten führen. Nach jedem Hub werden Gerät und Schraubverbindung erneut mit der vollen Klemmkraft beaufschlagt. Es entstehen hohe Belastungen im System und stetige Biegebelastungen an der Schraubverbindung. Auch aus der
Gemäß der Erfindung ist bei einem Kraftschrauber der eingangs genannten Art an dem Gehäuse ein reibend gehaltener drehbarer Skalenring konzentrisch zur Antriebswelle angeordnet, der ein zentrisches Fenster aufweist, durch das eine Markierung der Abtriebswelle sichtbar ist. Ein derartiger Skalenring kann dazu benutzt werden, den Drehwinkel der Abtriebswelle anzuzeigen. Der Skalenring wird zunächst durch manuelles Verdrehen auf die jeweilige Stellung der Markierung eingestellt, um die Anfangsstellung zu memorieren. Während des Schraubvorgangs wandert die Markierung relativ zu dem Skalenring, wobei der jeweilige Schraubenwinkel leicht abgelesen werden kann. Der Erfindung liegt die zusätzliche Aufgabe zugrunde, einen Kraftschrauber zu schaffen, der ein gleichmäßiges Anziehen von Schrauben ohne Sicherheitsrisiko ermöglicht. Der erfindungsgemäße Kraftschrauber ist durch den Anspruch 1 bezeichnet. Er kann eine kontinuierlich wirkende Reibbremse enthalten, die eine Reibkraft zwischen der Antriebswelle und dem Gehäuse erzeugt. Diese Reibkraft wird permanent erzeugt und beim Arbeitshub wird sie von dem Hydraulikantrieb überwunden. Die Reibbremse bewirkt ein gleichmäßiges Anziehen der Schraube. Sie ermöglicht es einem Monteur, mehrere Schraubvorgänge, die mit Kraftschraubern ausgeführt werden, gleichzeitig zu überwachen. Der Kraftschrauber wird zuverlässig positioniert und in jeder Arbeitsposition unabhängig von der Phase des jeweiligen Hubes festgehalten. Es findet keine stufenweise Verrastung statt. Das Rückhaltesystem ist stetig aktiv. Ein Ein- und Ausschalten des Hydrauliksystems ist nicht erforderlich. Es wirken auch keine zusätzlichen Biegemomente auf die Schraubverbindung, wie dies bei Systemen mit Sperrklinke der Fall ist. Ein Verklemmen des Verschraubungswerkzeugs nach dem letzten Hub findet nicht statt. Daher entfallen zeitraubende Lösungsprozeduren. Das sichere Abnehmen des Gerätes ist gewährleistet. Wegen des Entfallens einer Einrastung und Ausrastung wird das Gerät in jeder beliebigen Arbeitsposition gesichert.According to the invention, in a power wrench of the type mentioned on the housing a frictionally held rotatable scale ring is arranged concentrically to the drive shaft having a central window through which a mark of the output shaft is visible. Such a scale ring can be used to indicate the angle of rotation of the output shaft. The scale ring is first adjusted by manually turning to the respective position of the mark to memorize the initial position. During the screwing operation, the marking moves relative to the scale ring, whereby the respective screw angle can be read off easily. The invention has the additional object to provide a power wrench that allows a uniform tightening screws without security risk. The power wrench according to the invention is characterized by the claim 1. It may include a continuously acting friction brake which generates a frictional force between the drive shaft and the housing. This frictional force is generated permanently and during the power stroke it is overcome by the hydraulic drive. The friction brake causes a uniform tightening of the screw. It allows an installer to simultaneously monitor multiple screwdriving operations performed with power wrenches. The power wrench is reliably positioned and held in any working position regardless of the phase of the respective stroke. There is no incremental locking. The restraint system is constantly active. Switching the hydraulic system on and off is not required. There are no additional bending moments on the screw, as is the case with systems with pawl. There is no jamming of the screwing tool after the last stroke. Therefore, time-consuming solution procedures are eliminated. The safe removal of the device is guaranteed. Due to the elimination of a latching and disengagement, the device is secured in any working position.
Die Reibbremse kann mindestens einen Reibschuh aufweisen, der im wesentlichen radial zu der Abtriebswelle angeordnet ist und gegen eine umlaufende Reibfläche drückt. Die Reibfläche ist vorzugsweise an der Abtriebswelle oder an einem damit verbundenen Bauteil angeordnet. Es besteht aber auch die Möglichkeit, den Reibschuh an der Abtriebswelle vorzusehen und ihn auf einer Reibfläche des Gehäuses wirken zu lassen. Es können mehrere umfangsmäßig verteilt angeordnete Reibschuhe vorgesehen sein. Vorzugsweise ist jeder Reibschuh durch eine verstellbare Spannvorrichtung gegen die Antriebswelle gedrückt. Auf diese weise ist ein Nachstellen bzw. Einstellen der Reibbremse möglich. Die Spannvorrichtung weist vorzugsweise einen Spannkeil auf.The friction brake may comprise at least one friction shoe, which is arranged substantially radially to the output shaft and presses against a circumferential friction surface. The friction surface is preferably arranged on the output shaft or on a component connected thereto. But it is also possible to provide the friction shoe on the output shaft and to let it act on a friction surface of the housing. There can be several Be provided circumferentially distributed friction shoes. Preferably, each friction shoe is pressed by an adjustable clamping device against the drive shaft. In this way an adjustment or adjustment of the friction brake is possible. The tensioning device preferably has a clamping wedge.
Bei einer axial wirkenden Reibbremse ist gemäß einer Weiterbildung der Erfindung vorgesehen, dass die Reibbremse einen gegen ein gehäusefestes Reibteil drückenden Flansch der Antriebswelle aufweist. Durch die auf den Flansch einwirkende Reibkraft wird die Abtriebswelle gebremst.In an axially acting friction brake, according to a development of the invention, it is provided that the friction brake has a flange of the drive shaft which presses against a housing-fixed friction part. By acting on the flange friction force the output shaft is braked.
Vorzugsweise ist eine Feder vorgesehen, die die Abtriebswelle in Richtung auf das Reibteil drückt. Das Reibteil kann drehfest mit einem Überwurfring verbunden sein, welcher über ein Axiallager axial gegen die Feder drückt.Preferably, a spring is provided which presses the output shaft in the direction of the friction part. The friction member may be rotatably connected to a coupling ring which presses axially against the spring via a thrust bearing.
Im Folgenden werden unter Bezugnahme auf die Zeichnungen Ausführungsbeispiele der Erfindung näher erläutert.In the following, embodiments of the invention will be explained in more detail with reference to the drawings.
Es zeigen:
- Fig. 1
- Eine Seitenansicht des Kraftschraubers,
- Fig. 2
- eine Stirnansicht aus Richtung des Pfeiles II von
Fig. 1 , - Fig. 3
- einen Schnitt entlang der Linie III-III von
Fig. 1 , - Fig. 4
- eine Seitenansicht einer zweiten Ausführungsform,
- Fig. 5
- eine Stirnansicht des Kraftschraubers aus Richtung des Pfeiles V von
Fig. 4 , - Fig. 6
- einen Schnitt entlang der Linie VI-VI von
Fig. 4 , - Fig. 7
- eine vergrößerte Darstellung eines Schnitts durch die Reibbremse und durch die Drehwinkelanzeige bei der zweiten Ausführungsform,
- Fig. 8
- eine Seitenansicht einer dritten Ausführungsform,
- Fig. 9
- einen Schnitt entlang der Linie IX-IX von
Fig. 8 , - Fig. 10
- eine vergrößerte Darstellung der Einzelheit X aus
Fig. 9 und - Fig. 11
- einen Schnitt durch die Spannvorrichtung der Reibbremse entlang der Linie XI-XI von
Fig. 8 .
- Fig. 1
- A side view of the power wrench,
- Fig. 2
- an end view from the direction of arrow II of
Fig. 1 . - Fig. 3
- a section along the line III-III of
Fig. 1 . - Fig. 4
- a side view of a second embodiment,
- Fig. 5
- an end view of the power wrench from the direction of the arrow V of
Fig. 4 . - Fig. 6
- a section along the line VI-VI of
Fig. 4 . - Fig. 7
- an enlarged view of a section through the friction brake and by the rotation angle display in the second embodiment,
- Fig. 8
- a side view of a third embodiment,
- Fig. 9
- a section along the line IX-IX of
Fig. 8 . - Fig. 10
- an enlarged view of the detail X from
Fig. 9 and - Fig. 11
- a section through the tensioning device of the friction brake along the line XI-XI of
Fig. 8 ,
Der Kraftschrauber gemäß der
Die Reibbremse 20 weist einen Reibschuh 21 auf, der radial zu der Abtriebswelle 14 angeordnet ist und gegen eine Reibfläche 22 am Umfang der Abtriebswelle drückt. Eine Spannvorrichtung 23 weist einen Spannkeil 24 auf, der mit einer Gewindebohrung versehen ist, in welche eine Spannschraube 25, die in der Gehäusewand 10B gehalten ist, eingeschraubt ist. Durch Festziehen der Spannschraube 25 wird der Spannkeil 24 nach außen (gemäß
Im vorliegenden Fall ist nur ein einziger Reibschuh 21 vorgesehen, es können jedoch mehrere Reibschuhe vorhanden sein, die vorzugsweise gleichmäßig um den Umfang der Abtriebswelle 14 verteilt sind. Die kontinuierlich wirkende Reibbremse 20 übt bei Drehung der Abtriebswelle permanent eine gleichbleibende Bremskraft auf die Abtriebswelle aus, so dass diese am Zurückdrehen gehindert wird.In the present case, only a
Bei dem Ausführungsbeispiel der
Das Gehäuse 10 enthält auch hier zwei parallele Gehäusewände 10a, 10b mit Löchern, in denen die Abtriebswelle 14 gelagert ist. Die Abtriebswelle 14 ist hier voll ausgebildet und sie ragt an der einen Seite aus dem Gehäuse 10 heraus, wo sich auf der Abtriebswelle ein Aufsteck-Vierkant 26 befindet, auf den eine Schlüsselnuss aufgesteckt werden kann. Auf einer Keilverzahnung 31 der Abtriebswelle 14 sitzt drehfest eine Hülse 32, die zusätzlich mit einer Außenverzahnung 33 versehen ist. In diese Außenverzahnung greift die Verzahnung eines Mitnehmersteines 34 ein, der im Innern des Gehäuses 10 untergebracht ist und mit dem Ratschenhebel 16 zusammengreift. Der hin- und hergehende Ratschenhebel 16 treibt über den Mitnehmerstein 34 die Hülse 32 und die Abtriebswelle 14 an, wobei die Hülse und die Abtriebswelle nur in der einen Drehrichtung mitgenommen werden.The
In einer axialen Ausnehmung der Abtriebswelle 14 gleitet ein Schieber 35, dessen Stirnwand 36 einen Druckknopf bildet. Eine Feder 37 drückt den Schieber 35 nach außen. Der Schieber weist eine Umfangsnut 38 auf, die bei eingedrücktem Schieber eine Kugel 39, die in einer Axialbohrung der Abtriebswelle bewegbar ist, teilweise aufnimmt. Dadurch wird eine Zwischenbuchse 40, die auf einem Schaft der Abtriebswelle 14, von der Abtriebswelle entriegelt, so dass die Zwischenbuchse abgezogen werden kann, wenn der Druckknopf 36 eingedrückt ist.In an axial recess of the
Wie
Auf einem Gewinde 44 des Reibteils 43 sitzt ein Überwurfring 45, der mit einem Sicherungsstift 46 gesichert ist. Der Überwurfring 45 umgreift ein Nadellager 47, das an dem Überwurfring 45 axial abgestützt ist und das auf der gegenüberliegenden Seite mit einer Scheibe 48 gegen die Tellerfeder 49 drückt. Auf diese Weise ist der Überwurfring 45 zusammen mit der Tellerfeder 49 Bestandteil einer Spannvorrichtung 23 zum Einstellen der Reibungskraft der Reibbremse 20.On a
Auf dem Überwurfring 45 sitzt ein Skalenring 50, der mit einem O-Ring 51 rastend gesichert ist. Der Skalenring 50 weist eine Winkelskala von 0° - 360° auf, die in
Das Ausführungsbeispiel der
Die Reibbremse 20 ist bei dem dritten Ausführungsbeispiel nach Art einer Sattelbremse ausgebildet, wobei die beiden Bremsbacken 64, 65 einen Bremssattel bilden, der mit den Reibbelägen 63a, 63b rittlings über den Rand der Reibscheibe 61 greift.The
Claims (10)
- A power wrench with a drive portion (11) including a hydraulic cylinder and with a driven portion (12), the driven portion comprising a drive shaft (14) rotatably supported in the housing (10) and rotated at intervals by a ratchet lever (16), a rotatable index ring (50) being arranged concentrically with the output shaft (14),
characterized in that
the rotatable index ring (50) is frictionally supported at the housing (10), and that the index ring (50) has a centric window (53) through which a mark (52) on the output shaft (14) is visible. - The power wrench of claim 1, characterized in that the index ring is adapted to be set, by manual turning, to a position of the mark (52) to memorize the initial position.
- The power wrench of one of the preceding claims, characterized in that a continuously active friction brake (20) is provided that generates a friction force between the output shaft (14) and the housing (10).
- The power wrench of claim 3, characterized in that the friction brake (20) has at least one friction shoe (21) that is oriented substantially radially with respect to the output shaft (14) and presses against a circumferential friction surface (22).
- The power wrench of claim 3 or 4, characterized in that a plurality of circumferentially arranged friction shoes (21) is provided.
- The power wrench of one of claims 3 to 5, characterized in that the friction shoe (21) is pressed against the output shaft (14) by an adjustable tensioning device (25), the tensioning device (23) preferably comprising a tensioning wedge (24).
- The power wrench of claim 3, characterized in that the friction brake comprises a flange (41) of the output shaft that presses against a friction member (43) fixed to the housing, wherein, preferably, a spring (49) is provided for pressing the output shaft (14) or an intermediate bushing (40) connected therewith towards the friction member (43).
- The power wrench of claim 7, characterized in that the friction member (43) is connected with a swivel ring (45) in a manner secured against rotation, which ring presses against the spring (49) via an axial bearing (47).
- The power wrench of claim 8, characterized in that the swivel ring (45) forms a tensioning device (23) and is connected with the friction member (43) via a thread (44), wherein, preferably, a safety pin (46) is provided for securing the tensioning device (23).
- The power screw driver of claim 3, characterized in that the friction brake (20) is designed in the manner of a calliper brake and has a radial friction disc (61) connected with the output shaft, which disc is engaged by brake jaws (64, 65) from opposite sides.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE202006004380U DE202006004380U1 (en) | 2006-03-21 | 2006-03-21 | power wrench |
EP07727134A EP2001639B1 (en) | 2006-03-21 | 2007-03-20 | Power screwdriver |
Related Parent Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07727134.4 Division | 2007-03-20 | ||
EP07727134A Division EP2001639B1 (en) | 2006-03-21 | 2007-03-20 | Power screwdriver |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2567787A2 EP2567787A2 (en) | 2013-03-13 |
EP2567787A3 EP2567787A3 (en) | 2013-03-20 |
EP2567787B1 true EP2567787B1 (en) | 2015-12-09 |
Family
ID=38229085
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12195434.1A Active EP2567787B1 (en) | 2006-03-21 | 2007-03-20 | Electric screwdriver |
EP07727134A Active EP2001639B1 (en) | 2006-03-21 | 2007-03-20 | Power screwdriver |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07727134A Active EP2001639B1 (en) | 2006-03-21 | 2007-03-20 | Power screwdriver |
Country Status (6)
Country | Link |
---|---|
US (1) | US8024996B2 (en) |
EP (2) | EP2567787B1 (en) |
JP (1) | JP2009530124A (en) |
DE (1) | DE202006004380U1 (en) |
PL (1) | PL2001639T3 (en) |
WO (1) | WO2007107575A2 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
USD1042067S1 (en) * | 2023-02-28 | 2024-09-17 | Primesource Consulting Llc | Limited clearance tool |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2890612A (en) * | 1956-06-15 | 1959-06-16 | Francis J Kelly | Hydraulic ratchet wrench |
DE1944797U (en) * | 1966-04-26 | 1966-08-18 | Gardner Denver Co | DEVICE FOR TIGHTENING THREADED PARTS. |
US3604292A (en) * | 1968-02-08 | 1971-09-14 | Riken Seiki Kk | Bolt and nut fastening device |
DE6602839U (en) * | 1968-05-02 | 1969-06-26 | Premag Gmbh | ROTARY SCREWDRIVER |
FR2362704A1 (en) * | 1976-08-23 | 1978-03-24 | Harmat Nominees Pty Ltd | TORQUE WRENCH |
US4201099B1 (en) * | 1978-08-14 | 1993-12-07 | K. Junkers John | Hydraulic wrench |
US4970919A (en) * | 1987-11-05 | 1990-11-20 | Raymond Engineering Inc. | Torquing apparatus |
US5398574A (en) * | 1992-12-23 | 1995-03-21 | Unex Corporation | Fluid operating tool |
WO1998010260A1 (en) * | 1996-09-05 | 1998-03-12 | Crane Electronics Ltd. | Variable torque rate simulated test joint |
US20050011313A1 (en) * | 2001-06-20 | 2005-01-20 | Norwolf Tool Works | Compact hydraulic torque wrench reaction arm |
DE20111326U1 (en) * | 2001-07-07 | 2001-09-27 | Wagner, Paul-Heinz, 53804 Much | Hydraulic power wrench |
DE10236585A1 (en) * | 2002-08-08 | 2004-02-19 | Paul-Heinz Wagner | Hydraulically driven screw-driver has ratchet lever, cog wheel with cogging, block in form of detent pawl, with two blocking teeth |
US7069819B2 (en) * | 2003-10-28 | 2006-07-04 | Albertson Robert V | Air motor socket wrench with quick socket release and muffler |
-
2006
- 2006-03-21 DE DE202006004380U patent/DE202006004380U1/en not_active Expired - Lifetime
-
2007
- 2007-03-20 PL PL07727134T patent/PL2001639T3/en unknown
- 2007-03-20 WO PCT/EP2007/052657 patent/WO2007107575A2/en active Application Filing
- 2007-03-20 EP EP12195434.1A patent/EP2567787B1/en active Active
- 2007-03-20 EP EP07727134A patent/EP2001639B1/en active Active
- 2007-03-20 JP JP2009500858A patent/JP2009530124A/en active Pending
- 2007-03-20 US US12/225,433 patent/US8024996B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
US8024996B2 (en) | 2011-09-27 |
WO2007107575A2 (en) | 2007-09-27 |
WO2007107575A3 (en) | 2007-12-21 |
JP2009530124A (en) | 2009-08-27 |
EP2567787A3 (en) | 2013-03-20 |
EP2567787A2 (en) | 2013-03-13 |
EP2001639A2 (en) | 2008-12-17 |
US20090107298A1 (en) | 2009-04-30 |
PL2001639T3 (en) | 2013-05-31 |
DE202006004380U1 (en) | 2007-07-26 |
EP2001639B1 (en) | 2012-12-05 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE69423045T2 (en) | FASTENING SCREW | |
EP2476929B2 (en) | Adjustment device for a disc brake | |
EP0271864B1 (en) | Actuating mechanism with an automatic adjustment for brakes, especially for juggernauts | |
DE2608502B2 (en) | Release device for the interruption and automatic return of the operating function of a spring-loaded brake cylinder | |
DE3005420A1 (en) | AUTOMATIC ADJUSTMENT FOR A DISC BRAKE | |
EP0188710A1 (en) | Brake gear for vehicle brakes | |
DE2606303B2 (en) | Manual adjustment device for the brake lining wear of a mechanically operated floating caliper disc brake | |
EP2567787B1 (en) | Electric screwdriver | |
EP3202533A1 (en) | Clamping device | |
DE29708201U1 (en) | Step-by-step force-intensifying vice in planetary gear train design | |
DE1475501B2 (en) | MECHANICALLY ACTIVATED PARTIAL DISC BRAKE WITH SELF-REINFORCING BRAKING EFFECT | |
DE956008C (en) | Collet chuck with a pull ring screwed onto the collet and secured against rotation | |
DE2052037C3 (en) | Power-operated chuck with several radially guided clamping jaws | |
DE2218929A1 (en) | ADJUSTMENT DEVICE | |
EP3279492A1 (en) | Tensioning device for tools | |
DE3142799A1 (en) | Mechanically actuated sliding-calliper disc brake | |
EP0305724A1 (en) | Clamping device with a mechanical power booster | |
DE20204741U1 (en) | Device for resetting a brake piston | |
DE3445564A1 (en) | ADJUSTMENT DEVICE FOR A DISC BRAKE, ESPECIALLY FOR MOTOR VEHICLES | |
DE2543930B2 (en) | Automatic adjustment device for the actuating piston of a brake cylinder that can be acted upon by pressure medium, in particular for hydraulically actuated block or disc brakes of vehicles | |
DE3625107C1 (en) | Automatic adjusting device for the expansion cams of a drum brake | |
EP2801446A1 (en) | Tool with exchangeable tool component | |
EP2210720B1 (en) | Frictional rotation tool attachment device | |
DE923709C (en) | Tool holder for screw fastening of milling cutters or similar rotating tools | |
DE3631035A1 (en) | Actuating device for a disc brake, in particular for motor vehicles |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AC | Divisional application: reference to earlier application |
Ref document number: 2001639 Country of ref document: EP Kind code of ref document: P |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: B25B 21/00 20060101AFI20130211BHEP |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: RUESSMANN, KLAUS Inventor name: NIEMIETZ, ANDREAS Inventor name: WAGNER, PAUL-HEINZ Inventor name: THELEN, BERND |
|
17P | Request for examination filed |
Effective date: 20130911 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20150618 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AC | Divisional application: reference to earlier application |
Ref document number: 2001639 Country of ref document: EP Kind code of ref document: P |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 764358 Country of ref document: AT Kind code of ref document: T Effective date: 20151215 Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502007014456 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 10 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20151209 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160310 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20160322 Year of fee payment: 10 Ref country code: AT Payment date: 20160323 Year of fee payment: 10 Ref country code: FR Payment date: 20160322 Year of fee payment: 10 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160411 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160331 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160409 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502007014456 Country of ref document: DE |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 Ref country code: LU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160320 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
26N | No opposition filed |
Effective date: 20160912 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160320 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160331 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160331 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 764358 Country of ref document: AT Kind code of ref document: T Effective date: 20170320 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20170320 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20171130 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170320 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170331 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170320 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20070320 Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151209 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240315 Year of fee payment: 18 |