EP2001639A2 - Power screwdriver - Google Patents

Power screwdriver

Info

Publication number
EP2001639A2
EP2001639A2 EP07727134A EP07727134A EP2001639A2 EP 2001639 A2 EP2001639 A2 EP 2001639A2 EP 07727134 A EP07727134 A EP 07727134A EP 07727134 A EP07727134 A EP 07727134A EP 2001639 A2 EP2001639 A2 EP 2001639A2
Authority
EP
European Patent Office
Prior art keywords
friction
output shaft
power
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.)
Granted
Application number
EP07727134A
Other languages
German (de)
French (fr)
Other versions
EP2001639B1 (en
Inventor
Paul-Heinz Wagner
Bernd Thelen
Andreas Niemietz
Klaus Rüssmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wanger Vermoegensver & Co GmbH
Wagner Vermoegensverwaltungs GmbH and Co KG
Original Assignee
Wanger Vermoegensver & Co GmbH
Wagner Vermoegensverwaltungs GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Wanger Vermoegensver & Co GmbH, Wagner Vermoegensverwaltungs GmbH and Co KG filed Critical Wanger Vermoegensver & Co GmbH
Priority to PL07727134T priority Critical patent/PL2001639T3/en
Priority to EP12195434.1A priority patent/EP2567787B1/en
Publication of EP2001639A2 publication Critical patent/EP2001639A2/en
Application granted granted Critical
Publication of EP2001639B1 publication Critical patent/EP2001639B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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.
  • the invention has for its 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 contains 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 bolting operations performed with power screwdrivers.
  • 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. One Jamming of the screwing tool after the last stroke does not take place. 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.
  • 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 the rotation angle of To indicate output shaft.
  • the scale ring is first adjusted by manually turning to the respective position of the marker to memorize the initial position. During the screwing operation, the marking moves relative to the scale ring, wherein the respective screw angle can be easily read.
  • Fig. 1 is a side view of a first embodiment of the
  • Fig. 5 is an end view of the power wrench from the direction of the arrow V of
  • FIG. 10 is an enlarged view of the detail X of FIG. 9 and
  • FIG. 11 shows a section through the tensioning device of the friction brake along the line XI-XI of FIG. 8.
  • the Kraftsch rauber of the embodiment of Figures 1-3 has a housing 10 which is formed substantially L-shaped and in one leg a drive member 11 and in the other leg includes a driven member 12.
  • 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), which contains a hexagon socket profile 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 outer 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, in which a clamping screw 25, which is held in the housing wall 1OB, is screwed. By tightening the clamping screw 25, the clamping wedge 24 is pulled outwards (according to FIG. 3 to the right), as a result of which it presses against a rear wedge surface of the friction shoe 21 and drives it in the direction of the friction surface 22.
  • 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.
  • the housing 10 also includes a drive member 11 and an output member 12.
  • a drive member 11 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 is to prevent rotation of the housing 10 in 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.
  • the intermediate bushing 40 connected to the output shaft 14 in a rotationally fixed manner has a radial flange 41 at the outer end.
  • the latter presses against a friction surface 42 of an annular friction part 43 connected to the housing 10 from the outside.
  • the friction surface 42 can also be formed by a friction lining become.
  • the flange 41 thus forms a friction brake 20 with the friction surface 42.
  • This also includes a plate spring 49, which presses the intermediate sleeve 40 against 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 is visible in Figure 4.
  • 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 rotatably connected to the output shaft 14 and thus it indicates the respective rotational position of the screw as a relative position.
  • the scale ring 50 is manually zeroed to memorize the initial position.
  • 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 mark 52 has an independent meaning and is not bound to the presence of a friction brake.
  • the embodiment of Figures 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 contains an internal hexagonal profile 15. In this, one screw head is inserted from one end (according to FIGS. 9 and 10 from the left), while the friction brake 20 and the scale ring 50 are located at the opposite end (right).
  • 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 fastened 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 ( Figure 8), 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)

Abstract

The invention relates to a hydraulic power screwdriver comprising a ratchet lever (16) driven by a hydraulic cylinder. According to the invention, said power screwdriver is provided with a friction brake (20) which operates continuously between the housing (10) and the output shaft (14). In this way, reversed rotations of the output shaft following the individual working strokes are avoided.

Description

Kraftschrauber power wrench
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.
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.Are known hydraulic power wrench, which operate on the ratchet lever principle. Such power wrenches can be used when using correspondingly high hydraulic pressures for very high torques. After a stroke of the hydraulic piston-cylinder unit, there is a tendency that the output shaft rotates back by a smaller angular amount. This is because the screw design partially after each stroke relaxed. To prevent such a relaxation, it is already known to let act on the output shaft a blocking stone, which engages in an external toothing of the output shaft and prevents turning back. There is the disadvantage of a security risk due to unreliable holding systems. When stopping the hydraulic power unit, which supplies the power screwdriver with pressure, in the event of a power failure or if the stroke length is incomplete, the devices can be released from the screw to be turned during the working process. This means an accident risk. Devices with retention pawl system can become tense after reaching the end torque and then have to be released from the fitting object with a high expenditure of time. A renewed start of the screwdriver to the maximum set torque is necessary and can lead to torque inaccuracies. After each stroke, the device and screw connection are again subjected to the full clamping force. This results in high loads in the system and constant bending loads on the screw connection.
Der Erfindung liegt die Aufgabe zugrunde, einen Kraftschrauber zu schaffen, der ein gleichmäßiges Anziehen von Schrauben ohne Sicherheitsrisiko ermöglicht.The invention has for its object to provide a power wrench that allows a uniform tightening screws without security risk.
Der erfindungsgemäße Kraftschrauber ist durch den Anspruch 1 bezeichnet. Er enthält eine kontinuierlich wirkende Reibbremse, 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 Kraftschraubem 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.The power wrench according to the invention is characterized by the claim 1. It contains 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 bolting operations performed with power screwdrivers. 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. One Jamming of the screwing tool after the last stroke does not take place. 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 may be provided a plurality of 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.
Gemäß einem weiteren Aspekt 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 Schraubwinkel leicht abgelesen werden kann.According to a further aspect of 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 the rotation angle of To indicate output shaft. The scale ring is first adjusted by manually turning to the respective position of the marker to memorize the initial position. During the screwing operation, the marking moves relative to the scale ring, wherein the respective screw angle can be easily read.
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 :Show it :
Fig. 1 Eine Seitenansicht einer ersten Ausführungsform desFig. 1 is a side view of a first embodiment of the
Kraftsch raubers,Power schauberz,
Fig. 2 eine Stirnansicht aus Richtung des Pfeiles II von Fig. 1,2 is an end view from the direction of the arrow II of Fig. 1,
Fig. 3 einen Schnitt entlang der Linie III-III von Fig. 1,3 is a section along the line III-III of Fig. 1,
Fig. 4 eine Seitenansicht einer zweiten Ausführungsform,4 is a side view of a second embodiment,
Fig. 5 eine Stirnansicht des Kraftschraubers aus Richtung des Pfeiles V vonFig. 5 is an end view of the power wrench from the direction of the arrow V of
Fig. 4,4,
Fig. 6 einen Schnitt entlang der Linie VI-VI von Fig. 4,6 is a section along the line VI-VI of Fig. 4,
Fig. 7 eine vergrößerte Darstellung eines Schnitts durch die Reibbremse und durch die Drehwinkelanzeige bei der zweiten Ausführungsform,7 is an enlarged view of a section through the friction brake and the rotation angle display in the second embodiment,
Fig. 8 eine Seitenansicht einer dritten Ausführungsform,8 is a side view of a third embodiment,
Fig. 9 einen Schnitt entlang der Linie IX-IX von Fig. 8, _ C _9 is a section along the line IX-IX of Fig. 8, _ C _
Fig. 10 eine vergrößerte Darstellung der Einzelheit X aus Fig. 9 und10 is an enlarged view of the detail X of FIG. 9 and
Fig. 11 einen Schnitt durch die Spannvorrichtung der Reibbremse entlang der Linie XI-XI von Fig. 8.11 shows a section through the tensioning device of the friction brake along the line XI-XI of FIG. 8.
Der Kraftsch rauber des Ausführungsbeispiels der Figuren 1 - 3 weist ein Gehäuse 10 auf, das im wesentlichen L-förmig ausgebildet ist und in einem Schenkel einen Antriebsteil 11 und in dem anderen Schenkel einen Abtriebsteil 12 enthält. Der Antriebsteil enthält eine (nicht dargestellte) hydraulische Kolben-Zylinder- Einheit mit einer hin- und hergehend bewegten Kolbenstange. Die Kolbenstange treibt einen Ratschenhebel. Der Abtriebsteil 12 enthält eine in dem Gehäuse gelagerte Abtriebswelle 14, bei der es sich hier um eine Hohlwelle handelt (Figur 3), die ein Innensechskantprofil 15 enthält. Zwischen zwei Seitenwänden 10A, 1OB des Gehäuses 10 befindet sich der Ratschenhebel 16, der über eine Verzahnung 17 mit einer Außenverzahnung der Abtriebswelle 14 gekoppelt ist. Der Ratschenhebel 16 nimmt bei einem Arbeitshub die Abtriebswelle 14 in der einen Drehrichtung mit, während er bei dem Rückwärtshub leer zurückgleitet. Auf diese Weise wird die Abtriebswelle 14 in Intervallen gedreht.The Kraftsch rauber of the embodiment of Figures 1-3 has a housing 10 which is formed substantially L-shaped and in one leg a drive member 11 and in the other leg includes a driven member 12. 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), which contains a hexagon socket profile 15. Between two side walls 10A, 10B of the housing 10 is the ratchet lever 16, which is coupled via a toothing 17 with an outer 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.
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 1OB gehalten ist, eingeschraubt ist. Durch Festziehen der Spannschraube 25 wird der Spannkeil 24 nach außen (gemäß Figur 3 nach rechts) gezogen, wodurch er gegen eine rückwärtige Keilfläche des Reibschuhs 21 drückt und diesen in Richtung auf die Reibfläche 22 vortreibt.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, in which a clamping screw 25, which is held in the housing wall 1OB, is screwed. By tightening the clamping screw 25, the clamping wedge 24 is pulled outwards (according to FIG. 3 to the right), as a result of which it presses against a rear wedge surface of the friction shoe 21 and drives it in the direction of the friction surface 22.
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 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.
Bei dem Ausführungsbeispiel der Figuren 5 - 7 enthält das Gehäuse 10 ebenfalls einen Antriebsteil 11 und einen Abtriebsteil 12. Auf dem zylindrischen Antriebsteil 11 befindet sich eine Keilverzahnung 30, auf die ein (nicht dargestellter) Abstützfuß aufgesteckt werden kann, der gegen ein ortsfestes Widerlager gesetzt wird, um ein Drehen des Gehäuses 10 bei dem Schraubvorgang zu vermeiden.In the embodiment of Figures 5-7, the housing 10 also includes a drive member 11 and an output member 12. 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 is to prevent rotation of the housing 10 in the screwing.
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 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 Mitnehmersteines 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 Mitnehmerstein 34, the sleeve 32 and the output shaft 14, wherein the sleeve and the output shaft are taken only in one direction of rotation.
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. Wie Figur 7 zeigt, hat die mit der Abtriebswelle 14 drehfest verbundene Zwischenbuchse 40 am äußeren Enden einen radialen Flansch 41. Dieser drückt von außen gegen eine Reibfläche 42 eines mit dem Gehäuse 10 verbundenen ringförmigen Reibteils 43. Die Reibfläche 42 kann auch von einem Reibbelag gebildet werden. Der Flansch 41 bildet somit mit der Reibfläche 42 eine Reibbremse 20. Zu dieser gehört auch eine Tellerfeder 49, welche die Zwischenbuchse 40 gegen die Reibfläche 42 drückt.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. Thereby, 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. As FIG. 7 shows, the intermediate bushing 40 connected to the output shaft 14 in a rotationally fixed manner has a radial flange 41 at the outer end. The latter presses against a friction surface 42 of an annular friction part 43 connected to the housing 10 from the outside. The friction surface 42 can also be formed by a friction lining become. The flange 41 thus forms a friction brake 20 with the friction surface 42. This also includes a plate spring 49, which presses the intermediate sleeve 40 against the friction surface 42.
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 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. In this way, 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
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 Figur 4 sichtbar ist. Der Skalenring ist an dem Gehäuse 10 drehbar und konzentrisch zur Abtriebswelle angeordnet. Er weist ein zentrisches Fenster 53 auf, durch das eine Markierung 52 der Abtriebswelle sichtbar ist. Er kann auf dem Überwurfring reibend in eine beliebige Winkelstellung gedreht werden, so dass er mit der Position 0° auf die Markierung 52 an dem Druckknopf 36 eingestellt werden kann. Der Druckknopf 36 ist drehfest mit der Abtriebswelle 14 verbunden und er gibt somit die jeweilige Drehposition der Schraube als Relativposition an. Der Skalenring 50 wird manuell genullt, um die Anfangsstellung zu memorieren. Danach wandert beim Schraubvorgang die Markierung 52 entsprechend dem Schraubfortschritt, so dass der Benutzer den jeweiligen Drehwinkel, der seit Beginn des Schraubvorgangs oder seit einem anderen Punkt des Schraubvorgangs überstrichen wurde, ablesen kann. Der Skalenring in Verbindung mit der zur Abtriebswelle gehörenden Markierung 52 hat eine selbstständige Bedeutung und ist nicht an das Vorhandensein einer Reibbremse gebunden.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 is visible in Figure 4. 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 rotatably connected to the output shaft 14 and thus it 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 mark 52 has an independent meaning and is not bound to the presence of a friction brake.
Das Ausführungsbeispiel der Figuren 8 - 11 enthält eine zwischen den Gehäusewänden 10a und 10b drehbar gelagerte Abtriebswelle 14 mit einer (nicht dargestellten) Außenverzahnung, in die ein hin- und hergehend bewegbarer Ratschenhebel 16 eingreift. Die Abtriebswelle 14 enthält ein Innen- Sechskantprofil 15. In dieses wird vom einen Ende her (gemäß Figur 9 und 10 von links) ein Schraubenkopf eingesetzt, während sich am entgegengesetzten Ende (rechts) die Reibbremse 20 und der Skalenring 50 befinden. Die Reibbremse 20 weist ein Reibteil 60 auf mit einer Buchse, die verdrehungssicher mit der hohlen Abtriebswelle 14 verbunden ist. Von der Buchse steht radial eine ringförmige Reibscheibe 61 ab, die einen Umfangsbereich 62 mit zwei radialen Reibflächen 62a und 62b aufweist. An diesen Reibflächen greifen die Bremsbeläge 63a, 63b der Reibbremse 20 an. Der Reibbelag 63a ist an einer inneren Bremsbacke 64 und der Reibbelag 63b an einer äußeren Bremsbacke 65 befestigt, wobei die Bremsbacken einander parallel gegenüber liegen und zwischen sich den Rand 62 des Reibteils 60 einklemmen. Die Klemmwirkung wird hervorgerufen durch zwei Spannschrauben 66 (Figur 8), die die Bremsbacken 64 und 64 gegeneinander ziehen und verstellt werden können, um die Bremskraft der Reibbremse 20 einzustellen. Zwischen den beiden Spannschrauben 66 ist eine Halteschraube 67 angeordnet, die in die Gehäusewand 10b eingeschraubt ist und die Reibbremse 20 an dem Gehäuse 10 festhält.The embodiment of Figures 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 contains an internal hexagonal profile 15. In this, one screw head is inserted from one end (according to FIGS. 9 and 10 from the left), while the friction brake 20 and the scale ring 50 are located at the opposite end (right). 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. At these friction surfaces, 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 fastened 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 (Figure 8), the brake shoes 64 and 64 against each other and can be adjusted to adjust the braking force of the friction brake 20. Between the two clamping screws 66, a retaining screw 67 is arranged, which is screwed into the housing wall 10b and the friction brake 20 holds on the housing 10.
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 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.

Claims

Ansprüche claims
1. Kraftsch rauber mit einem einen Hydraulikzylinder enthaltenden Antriebsteil (11) und einem Abtriebsteil (12), wobei der Abtriebsteil eine in einem Gehäuse (10) drehbar gelagerte Antriebswelle (14) aufweist, die von einem Ratschenhebel (16) in Intervallen gedreht wird,1. power wiper with a hydraulic cylinder containing a drive part (11) and a driven part (12), wherein the driven part in a housing (10) rotatably mounted drive shaft (14) which is rotated by a ratchet lever (16) at intervals,
d a d u r c h g e k e n n z e i c h n e t,characterized,
dass eine kontinuierlich wirkende Reibbremse (20) vorgesehen ist, die eine Reibkraft der Abtriebswelle (14) und dem Gehäuse (10) erzeugt.in that a continuously acting friction brake (20) is provided which generates a frictional force of the output shaft (14) and the housing (10).
2. Kraftschrauber nach Anspruch 1, dadurch gekennzeichnet, dass die Reibbremse (20) mindestens einen Reibschuh (21) aufweist, der im wesentlichen radial zu der Abtriebswelle (14) ausgerichtet ist und gegen eine umlaufende Reibfläche (22) drückt.2. Power wrench according to claim 1, characterized in that the friction brake (20) has at least one friction shoe (21) which is aligned substantially radially to the output shaft (14) and against a circumferential friction surface (22) presses.
3. Kraftschrauber nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass mehrere umfangsmäßig verteilt angeordnete Reibschuhe (21) vorgesehen sind.3. power wrench according to claim 1 or 2, characterized in that a plurality of circumferentially distributed friction shoes (21) are provided.
4. Kraftschrauber nach einem der Ansprüche 1 - 3, dadurch gekennzeichnet, dass der Reibschuh (21) durch eine verstellbare Spannvorrichtung (25) gegen die Abtriebswelle (14) gedrückt wird.4. power wrench according to one of claims 1-3, characterized in that the friction shoe (21) by an adjustable clamping device (25) against the output shaft (14) is pressed.
5. Kraftschrauber nach Anspruch 4, dadurch gekennzeichnet, dass die Spannvorrichtung (23) einen Spannkeil (24) aufweist.5. power wrench according to claim 4, characterized in that the clamping device (23) has a clamping wedge (24).
6. Kraftschrauber nach Anspruch 1, dadurch gekennzeichnet, dass die Reibbremse einen gegen ein gehäusefestes Reibteil (43) drückenden Flansch (41) der Abtriebswelle aufweist. 6. power screwdriver according to claim 1, characterized in that the friction brake has a against a housing-fixed friction member (43) pushing flange (41) of the output shaft.
7. Kraftsch rauber nach Anspruch 6, dadurch gekennzeichnet, dass eine Feder (49) vorgesehen ist, die die Abtriebswelle (14) bzw. eine mit dieser verbundene Zwischenbuchse (40), in Richtung auf das Reibteil (43) drückt.7. power wiper according to claim 6, characterized in that a spring (49) is provided, which presses the output shaft (14) or an intermediate sleeve connected thereto (40), in the direction of the friction member (43).
8. Kraftschrauber nach Anspruch 6 oder 7, dadurch gekennzeichnet, dass das Reibteil (43) drehfest mit einem Überwurfring (45) verbunden ist, welcher über ein Axiallager (47) gegen die Feder (49) drückt.8. power wrench according to claim 6 or 7, characterized in that the friction part (43) rotatably connected to a coupling ring (45) which presses via a thrust bearing (47) against the spring (49).
9. Kraftschrauber nach Anspruch 8, dadurch gekennzeichnet, dass der Überwurfring (45) eine Spannvorrichtung (23) bildet und über ein Schraubgewinde (44) mit dem Reibteil (43) verbunden ist.9. power wrench according to claim 8, characterized in that the coupling ring (45) forms a clamping device (23) and via a screw thread (44) with the friction member (43) is connected.
10. Kraftschrauber nach Anspruch 9, gekennzeichnet durch einen Sicherungsstift (46) zur Sicherung der Spannvorrichtung (23).10. power screwdriver according to claim 9, characterized by a locking pin (46) for securing the clamping device (23).
11. Kraftschrauber nach Anspruch 1, dadurch gekennzeichnet, dass die Reibbremse (20) nach Art einer Sattelbremse ausgebildet ist und eine mit der Abtriebswelle verbundene radiale Reibscheibe (61) aufweist, an der von entgegengesetzten Seiten her Bremsbacken (64, 65) angreifen.11. A power wrench according to claim 1, characterized in that the friction brake (20) is designed in the manner of a caliper brake and connected to the output shaft radial friction disc (61) on which brake shoes from opposite sides attack (64, 65).
12. Kraftschrauber nach dem Oberbegriff des Anspruchs 1, dadurch gekennzeichnet, dass an dem Gehäuse (10) ein reibend gehaltener drehbarer Skalenring (50) konzentrisch zur Abtriebswelle (14) angeordnet ist, der ein zentrisches Fenster (53) aufweist, durch das eine Markierung (52) der Abtriebswelle sichtbar ist. 12. power wrench according to the preamble of claim 1, characterized in that on the housing (10) a frictionally held rotatable scale ring (50) is arranged concentrically to the output shaft (14) having a central window (53) through which a mark (52) of the output shaft is visible.
EP07727134A 2006-03-21 2007-03-20 Power screwdriver Active EP2001639B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PL07727134T PL2001639T3 (en) 2006-03-21 2007-03-20 Power screwdriver
EP12195434.1A EP2567787B1 (en) 2006-03-21 2007-03-20 Electric screwdriver

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202006004380U DE202006004380U1 (en) 2006-03-21 2006-03-21 power wrench
PCT/EP2007/052657 WO2007107575A2 (en) 2006-03-21 2007-03-20 Power screwdriver

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP12195434.1A Division EP2567787B1 (en) 2006-03-21 2007-03-20 Electric screwdriver

Publications (2)

Publication Number Publication Date
EP2001639A2 true EP2001639A2 (en) 2008-12-17
EP2001639B1 EP2001639B1 (en) 2012-12-05

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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

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EP12195434.1A Active EP2567787B1 (en) 2006-03-21 2007-03-20 Electric screwdriver

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US (1) US8024996B2 (en)
EP (2) EP2567787B1 (en)
JP (1) JP2009530124A (en)
DE (1) DE202006004380U1 (en)
PL (1) PL2001639T3 (en)
WO (1) WO2007107575A2 (en)

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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
GB1572568A (en) * 1976-08-23 1980-07-30 Harmat Nominees Pty Ltd Wrench
US4201099B1 (en) 1978-08-14 1993-12-07 K. Junkers John Hydraulic wrench
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DE69726430T2 (en) * 1996-09-05 2004-09-16 Crane Electronics Ltd., Hinckley Simulation test bench with variable torque rate
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 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

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See references of WO2007107575A2 *

Also Published As

Publication number Publication date
WO2007107575A2 (en) 2007-09-27
EP2567787A2 (en) 2013-03-13
PL2001639T3 (en) 2013-05-31
JP2009530124A (en) 2009-08-27
US20090107298A1 (en) 2009-04-30
EP2567787A3 (en) 2013-03-20
EP2567787B1 (en) 2015-12-09
DE202006004380U1 (en) 2007-07-26
US8024996B2 (en) 2011-09-27
EP2001639B1 (en) 2012-12-05
WO2007107575A3 (en) 2007-12-21

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