EP0153711B1 - Power-driven screw-driving tool with a fine-toothed chuck - Google Patents

Power-driven screw-driving tool with a fine-toothed chuck Download PDF

Info

Publication number
EP0153711B1
EP0153711B1 EP85101941A EP85101941A EP0153711B1 EP 0153711 B1 EP0153711 B1 EP 0153711B1 EP 85101941 A EP85101941 A EP 85101941A EP 85101941 A EP85101941 A EP 85101941A EP 0153711 B1 EP0153711 B1 EP 0153711B1
Authority
EP
European Patent Office
Prior art keywords
power
latch
arm
axis
wrench according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP85101941A
Other languages
German (de)
French (fr)
Other versions
EP0153711A3 (en
EP0153711A2 (en
Inventor
Hans-Bernd Mierbach
Gustav Frohn
Olaf Blockisch
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.)
Enerpac Tool Group Corp
Original Assignee
Applied Power Inc
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 Applied Power Inc filed Critical Applied Power Inc
Publication of EP0153711A2 publication Critical patent/EP0153711A2/en
Publication of EP0153711A3 publication Critical patent/EP0153711A3/en
Application granted granted Critical
Publication of EP0153711B1 publication Critical patent/EP0153711B1/en
Expired legal-status Critical Current

Links

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 the features specified in the preamble of claim 1.
  • a power wrench of this type is known from DE-A-3 008 381.
  • the bore for the cylinder of the hydraulic drive is in the power arm, so that the hydraulic connection must participate in its swiveling movement in the course of the screwing process.
  • the piston of the hydraulic drive acts on the reaction arm via a multiple ball-supported articulated arm, and the pawl interacting with the tensioning wheel in the power arm is also supported in the power arm via a similarly constructed articulated arm.
  • This entails long distances for the transmission of the reaction forces, which necessitates a relatively frequent readjustment of the pivot point for the pawl.
  • the overall construction comprises a large number of individual parts, with some moving parts being exposed and being exposed to undesirable soiling, against which additional measures have to be taken.
  • a pneumatically operated hammer screwdriver which has a shock ring rotatably mounted in a housing with an internal toothing which, in cooperation with a plurality of spring-loaded pawls, a screw head which can be placed on a screw to be tightened when the shock ring rotates in Takes housing in only one direction.
  • a pneumatic hammer is provided as the drive for the corresponding rotation of the shock ring, the percussion piston of which rotates step by step when it hits a radial shoulder on the shock ring, a pneumatically sprung buffer piston acting on the other side of the shoulder of the shock ring preventing the shock ring from turning back without taking the Screw head takes over.
  • This construction also contains a large number of individual parts, which are also subject to intermittent loads, which entails additional maintenance requirements.
  • the invention is therefore based on the object of designing a power wrench of the type mentioned at the outset in such a way that a power transmission from the hydraulic drive to the tensioning wheel can be achieved in a short way and with a minimum number of individual parts.
  • the driving force of the piston acting on the power arm acts on the power arm practically at an angle of 90 °
  • the power arm can be designed to be particularly simple in construction.
  • the power transmission takes place largely symmetrically, the piston is located in mirror image to a connecting line between the axis and the drive head of the power arm.
  • a largely closed construction is achieved in which the power arm is located entirely within the reaction arm, which has a suitable recess for this.
  • the piston has at least one, preferably two partially cylindrical, concave, first contact surfaces in the region of its recess, the center of which is located on the axis line.
  • the drive head likewise has at least one, preferably convex, partially cylindrical, second contact surface. The center of these second contact surfaces not only shifts axially when desired, but also somewhat radially when the power arm moves. In order to keep this radial displacement as small as possible, it is averaged on both sides of the axis line, so that the center of the drive head extends beyond the axis in the middle position of the power arm, while it is in the edge positions of the power arm below this axis line.
  • strongly eccentric gradients can also be selected for the second contact surfaces, in which the center point of the circular arc is far from the axis line of the cylinder and the gradient is selected such that starting from a central position of the power arm when moving to the left or right The point of contact between the drive head and the first contact surface remains essentially on the axis line of the cylinder.
  • the force arm is essentially fold-symmetrical to a straight line running through the axis and the center of its drive head, its general course being approximately pear-shaped.
  • the force arm preferably has a cutout for a pawl, this cutout has a reaction surface with a snap-in flank and an essentially radial transmission area which adjoins it flush.
  • the snap-in flank ensures, due to an oblique course, that the pawl is inevitably pressed into engagement with the teeth of the tensioning wheel in a pivoting direction of the power arm, the actual power transmission then takes place in a particularly short way over the essentially radial transmission range, which is in the immediate vicinity the circumference of the tensioning wheel.
  • the pawl is advantageously connected to the power arm via a spring. Farther it has the shape of a three-quarter moon, with the reaction surface having the same diameter as the outer circle of the pawl, the toothing of the pawl is on the boundary line with the larger diameter of the pawl. Overall, this results in a construction that is as simple as possible and that offers special advantages in terms of production technology.
  • the power wrench has a reaction arm 1 and a power arm 2, which are arranged so as to be pivotable relative to one another about an axis 3.
  • the reaction arm 1 has a partially cylindrical guide surface 4, which extends over approximately 180 ° and on which a corresponding outer surface of the force arm 2 lies in register.
  • the power arm 2 in turn has a cylindrical guide surface 5 which extends over approximately 270 ° and serves to guide and mount a tensioning wheel 7. This can thus be rotated about the axis 3 at least in one direction of rotation with respect to the force arm 2, the latter in turn can be pivoted by an angle of approximately ⁇ 10 ° from the shown central position with respect to the fixed reaction arm 1.
  • the tensioning wheel 7 has a hexagon socket for the transmission of a power-driven screwing movement to a nut, a screw bolt or the like.
  • the tensioning wheel 7 also has fine-toothing, for example there are four teeth within the total pivoting range of the power arm of approximately 20 °.
  • a pawl 8 in the form of a three-quarter moon interacts with these teeth, the one, lower, larger radius of which is provided with a plurality of teeth, for example five teeth.
  • the design and shape of these teeth of the pawl 8 corresponds to the design and shape of the teeth of the tensioning wheel 7.
  • the power arm is essentially pear-shaped, it merges upwards into a spherical drive head 9, which is delimited by a circular arc extending over a little more than 180 ° around a center point 10, which lies on an axis running parallel to the axis 3.
  • the force arm 2 is essentially fold-symmetrical with respect to a straight line connecting this center 10 with the passage of the axis 3.
  • a cylinder 11 is arranged in the reaction arm 1, the axis line 12 of which extends at right angles to the connection line mentioned between the center point 10 and the point of passage of the axis 3.
  • the center 10 is in the shown central position of the power arm 2 somewhat above the axis line 12, it cuts the axis line on the way to the left or right end position.
  • the piston 13 has approximately in its central region a recess 14 into which the drive head 9 of the power arm 2 engages in a largely adapted form.
  • the recess 14 forms two concave contact surfaces 15, which run transversely to the axis line 12, hereinafter referred to as first contact surfaces, on which the drive head 9 is supported with its diameter-equal second contact surface 16 around the center point 10.
  • These two surfaces 15, 16 should always be placed at a point that is largely exactly on the axis line 12 of the cylinder 11. In practice, however, this requirement cannot be met exactly, but it can largely be met.
  • the course, in particular of the second contact surface can be selected such that the point of contact of the contact surfaces 15, 16 remains essentially on the axis line.
  • a circular arc with a larger radius must be selected for the course of the second contact surface 16, the center point of which lies outside the drive head 9.
  • the piston is sealed off from the cylinder 11 by means of a seal 17; beyond this seal there is a pressure medium space 18 which can be filled with hydraulic fluid via a channel and a suitable connecting piece 19.
  • the piston has an axial bore 21, which is made from its end surface 20 facing away from the pressure medium chamber and in which a helical compression spring 22 is arranged for the piston return. Because of the axial bore 21, a relatively long helical compression spring 22 can be selected. This is supported with its other end on a nut 23 which is screwed into the open end of the cylinder 11, for this purpose an internal thread is provided in the cylinder 11. A pin 24 with a plate-like end piece is pressed against the end of the axial bore 21 of the piston 13 by the helical compression spring 22. It is located at least partially within a sleeve 25 which is encompassed by the helical compression spring 22 and is held in the nut 23. The nut 23 has a through bore 26 for the pin 24. Overall, a practically tight construction is achieved to the outside.
  • the pawl 8 has the shape of a flat circular disc which has an edge-side, concave recess with the diameter of the teeth of the tensioning wheel 7. Overall, this creates the three-quarter moon shape already mentioned.
  • the boundary line with the larger diameter, that is, the diameter of the toothing of the tensioning wheel 7, does not extend to the center of the boundary circle 27 of the pawl 8, but is at a distance from this which is one tenth of the diameter of the boundary circle 27.
  • a pawl spring 29 is arranged slightly above a horizontal through the center of the limiting circle 27 and in the left edge area on a pin 28, which is largely in a channel of the power arm 2 and is held there with its other end.
  • the recess A has in its left area a reaction surface with which the pawl 8 interacts. It is composed of a largely radial transmission area 30 and an adjoining snap-in flank 31.
  • the transmission area 30 is partially cylindrical, it extends over approximately 90 ° and merges tangentially into the latching flank 31, which intersects the connecting line from the center 10 and axis 3 at an angle of approximately 70 °.
  • Shown in the drawing is a drive position as it occurs when the pressure medium chamber 18 is filled with hydraulic fluid under pressure, which moves the piston 13 further to the right.
  • the pawl 8 is in the engaged position, it rests on the transmission area 30. This transmits the actuating forces to the pawl 8, the power transmission takes place at a favorable angle and over a short distance.
  • the working stroke described is ended when the piston 13 has taken the drive head 9 to the right into the right end position and the pin 24 can be seen in the through bore 26.
  • the return stroke movement of the piston 13 takes place under the action of the helical compression spring 22 as soon as the pressure medium chamber 18 is depressurized.
  • the pawl 8 initially remains in the engagement position shown.
  • the pawl spring 29 expands and strives to pull the pawl 9 back.
  • a spring can protrude into the recess A, which engages under and picks up the pawl 8 or its rod 32 if the pawl 8 remains too far relative to the transmission area 30.
  • a pin arranged parallel to the axis 3 can protrude from the power arm 2 into the recess 14, which optionally causes a run-up slope and releases the pawl 8 from its engagement with the toothing of the tensioning wheel 7.
  • the pawl 8 When the pivoting movement continues, the pawl 8 thus slips over the teeth of the tensioning wheel 7 until the piston 13 is in its left end position. In this state, the pawl 8 is generally not in an engaged position, as shown in the drawing. Rather, it is only preloaded into this engagement position due to the inclined engagement flank 31 and the tensile force of the pawl spring 29. An intervention is restored when a new working stroke begins. The latching flank and the pawl spring 29 then pull the pawl 8 into the engaged position as soon as the teeth of the pawl 8 and the toothing of the tensioning wheel 7 are in the correct position relative to one another. Then the processes already described run again.
  • the transmission area 30 and / or the snap-in flank 31 can be delimiting surfaces of separate parts, which can be held on the power arm 2 by means of suitable screws and can be adjusted slightly in relation to this, in order to have an adjustment possibility in the event of wear.
  • the power wrench consists of relatively few individual parts, which are also easy to manufacture. A large part can even be made as simple sheet metal stampings. Due to the arrangement of the cylinder 11 in the stationary reaction arm 1, in contrast to the known power screwdriver, it is avoided that the hydraulic line connected to the connecting piece 19 moves with each stroke.
  • a double-acting piston can also be used, in which case there is also a pressure medium space on the other side.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Transmission Devices (AREA)

Description

Die Erfindung betrifft einen Kraftschrauber mit im Oberbegriff des Patentanspruchs 1 im einzelnen angegebenen Merkmalen.The invention relates to a power wrench with the features specified in the preamble of claim 1.

Ein Kraftschrauber dieser Art ist aus DE-A-3 008 381 bekannt. Bei diesem bekannten Kraftschrauber befindet sich die Bohrung für den Zylinder des Hydraulikantriebs im Kraftarm, so daß der Hydraulikanschluß dessen Schwenkbewegung im Zuge des Schraubvorganges mitmachen muß. Der Kolben des Hydraulikantriebs wirkt über einen mehrfach kugelgestützten Gelenkarm auf den Reaktionsarm, und auch die mit dem Spannrad im Kraftarm zusammenwirkende Sperrklinke ist im Kraftarm über einen ähnlich gebauten Gelenkarm abgestützt. Dies bringt lange Wege für die Übertragung der Reaktionskräfte mit sich, wodurch eine relativ häufige Nachverstellung des Schwenkpunktes für die Sperrklinke notwendig wird. Die Gesamtkonstruktion umfaßt eine Vielzahl von Einzelteilen, wobei einige bewegte Teile frei liegen und unerwünschter Verschmutzung ausgesetzt sind, gegen die zusätzliche Maßnahmen getroffen werden müssen.A power wrench of this type is known from DE-A-3 008 381. In this known power screwdriver, the bore for the cylinder of the hydraulic drive is in the power arm, so that the hydraulic connection must participate in its swiveling movement in the course of the screwing process. The piston of the hydraulic drive acts on the reaction arm via a multiple ball-supported articulated arm, and the pawl interacting with the tensioning wheel in the power arm is also supported in the power arm via a similarly constructed articulated arm. This entails long distances for the transmission of the reaction forces, which necessitates a relatively frequent readjustment of the pivot point for the pawl. The overall construction comprises a large number of individual parts, with some moving parts being exposed and being exposed to undesirable soiling, against which additional measures have to be taken.

Aus US-A-2 112 693 ist weiter ein pneumatisch betätigter Hammerschrauber bekannt, der einen in einem Gehäuse drehbar gelagerten Stoßring mit einer Innenverzahnung aufweist, die in Zusammenwirken mit einer Vielzahl von federbelasteten Sperrklinken einen auf eine anzuziehende Schraube aufsetzbaren Schraubkopf bei Drehung des Stoßrings im Gehäuse in nur einer Richtung mitnimmt. Als Antrieb für die entsprechende Verdrehung des Stoßrings ist ein pneumatischer Hammer vorgesehen, dessen Schlagkolben unter Auftreffen auf einen radialen Ansatz am Stoßring diesen schrittweise verdreht, wobei ein auf der anderen Seite des Ansatzes des Stoßrings angreifender, pneumatisch abgefederter Pufferkolben die Rückdrehung des Stoßrings ohne Mitnahme des Schraubkopfes übernimmt. Auch diese Konstruktion enthält eine Vielzahl von Einzelteilen, die zudem stoßweiser Belastung unterliegen, was zusätzlichen Wartungsbedarf mit sich bringt.From US-A-2 112 693 a pneumatically operated hammer screwdriver is also known, which has a shock ring rotatably mounted in a housing with an internal toothing which, in cooperation with a plurality of spring-loaded pawls, a screw head which can be placed on a screw to be tightened when the shock ring rotates in Takes housing in only one direction. A pneumatic hammer is provided as the drive for the corresponding rotation of the shock ring, the percussion piston of which rotates step by step when it hits a radial shoulder on the shock ring, a pneumatically sprung buffer piston acting on the other side of the shoulder of the shock ring preventing the shock ring from turning back without taking the Screw head takes over. This construction also contains a large number of individual parts, which are also subject to intermittent loads, which entails additional maintenance requirements.

Der Erfindung liegt daher die Aufgabe zugrunde, einen Kraftschrauber der eingangs erwähnten Art so auszubilden, daß eine Kraftübertragung vom Hydraulikantrieb zum Spannrad auf kurzem Wege und mit einer Minimalzahl von Einzelteilen erreicht werden kann.The invention is therefore based on the object of designing a power wrench of the type mentioned at the outset in such a way that a power transmission from the hydraulic drive to the tensioning wheel can be achieved in a short way and with a minimum number of individual parts.

Die gestellte Aufgabe wird gemäß der Erfindung gelöst durch die im kennzeichnenden Teil des Patentanspruchs 1 angegebenen Merkmale; vorteilhafte Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen.The object is achieved according to the invention by the features specified in the characterizing part of claim 1; advantageous developments of the invention result from the subclaims.

Bei einem Kraftschrauber gemäß der Erfindung ist eine ausgesprochen direkte und kompakte Kraftübertragung gewährleistet; die am Kraftarm angreifende Antriebskraft des Kolbens greift praktisch im Winkel von 90° am Kraftarm an, und der Kraftarm kann konstruktiv besonders einfach ausgebildet werden. In bevorzugter Ausbildung erfolgt die Kraftübertragung weitgehend symmetrisch, der Kolben befindet sich spiegelbildlich zu einer Verbindungslinie zwischen der Achse und dem Antriebskopf des Kraftarms. Insgesamt wird eine weitgehend geschlossene Konstruktion erreicht, bei der sich der Kraftarm vollständig innerhalb des Reaktionsarmes, der hierfür eine geeignete Aussparung aufweist, befindet.In a power wrench according to the invention, an extremely direct and compact power transmission is guaranteed; the driving force of the piston acting on the power arm acts on the power arm practically at an angle of 90 °, and the power arm can be designed to be particularly simple in construction. In a preferred embodiment, the power transmission takes place largely symmetrically, the piston is located in mirror image to a connecting line between the axis and the drive head of the power arm. Overall, a largely closed construction is achieved in which the power arm is located entirely within the reaction arm, which has a suitable recess for this.

In besonders vorteilhafter Ausbildung der Erfindung hat der Kolben im Bereich seiner Ausnehmung mindestens eine, vorzugsweise zwei teilzylindrische, konkave, erste Anlageflächen, deren Zentrum sich auf der Achslinie befindet. Ebenso hat der Antriebskopf mindestens eine, vorzugsweise konvexe, teilzylindrische, zweite Anlageflächen. Der Mittelpunkt dieser zweiten Anlageflächen verschiebt sich bei einer Bewegung des Kraftarms nicht nur axial, wie gewünscht, sondern auch etwas radial. Um diese radiale Verschiebung möglichst gering zu halten, wird sie beidseits der Achslinie ausgemittelt, so daß die Mitte des Antriebskopfes in der Mittelstellung des Kraftarmes über die Achse hinausreicht, während sie sich in den Randstellungen des Kraftarmes unterhalb dieser Achslinie befindet.In a particularly advantageous embodiment of the invention, the piston has at least one, preferably two partially cylindrical, concave, first contact surfaces in the region of its recess, the center of which is located on the axis line. The drive head likewise has at least one, preferably convex, partially cylindrical, second contact surface. The center of these second contact surfaces not only shifts axially when desired, but also somewhat radially when the power arm moves. In order to keep this radial displacement as small as possible, it is averaged on both sides of the axis line, so that the center of the drive head extends beyond the axis in the middle position of the power arm, while it is in the edge positions of the power arm below this axis line.

Alternativ können für die zweiten Anlageflächen aber auch stark exzentrische Verläufe gewählt werden, bei denen also der Mittelpunkt des Kreisbogens weitab von der Achslinie des Zylinders liegt und der Verlauf so gewählt ist, daß ausgehend von einer Mittelstellung des Kraftarms bei einer Bewegung nach links oder rechts der Berührungspunkt zwischen Antriebskopf und der ersten Anlagefläche im wesentlichen auf der Achslinie des Zylinders bleibt.Alternatively, strongly eccentric gradients can also be selected for the second contact surfaces, in which the center point of the circular arc is far from the axis line of the cylinder and the gradient is selected such that starting from a central position of the power arm when moving to the left or right The point of contact between the drive head and the first contact surface remains essentially on the axis line of the cylinder.

In einer weiteren, bevorzugten Ausbildung der Erfindung ist der Kraftarm im wesentlichen klappsymmetrisch zu einer durch die Achse und den Mittelpunkt seines Antriebskopfes verlaufenden Geraden, dabei ist sein allgemeiner Verlauf etwa birnenförmig.In a further preferred embodiment of the invention, the force arm is essentially fold-symmetrical to a straight line running through the axis and the center of its drive head, its general course being approximately pear-shaped.

Der Kraftarm hat vorzugsweise eine Aussparung für eine Sperrklinke, diese Aussparung hat eine Reaktionsfläche mit einer Einrastflanke und einem sich hieran bündig anschliessenden, im wesentlichen radialen Übertragungsbereich. Die Einrastflanke sorgt auf Grund eines schrägen Verlaufs dafür, daß die Sperrklinke in einer Schwenkrichtung des Kraftarms zwangsläufig in Eingriff mit den Zähnen des Spannrades gedrückt wird, die eigentliche Kraftübertragung erfolgt dann auf besonders kurzem Wege über den im wesentlichen radialen Übertragungsbereich, der sich in unmittelbarer Nähe des Umfangs des Spannrades befindet.The force arm preferably has a cutout for a pawl, this cutout has a reaction surface with a snap-in flank and an essentially radial transmission area which adjoins it flush. The snap-in flank ensures, due to an oblique course, that the pawl is inevitably pressed into engagement with the teeth of the tensioning wheel in a pivoting direction of the power arm, the actual power transmission then takes place in a particularly short way over the essentially radial transmission range, which is in the immediate vicinity the circumference of the tensioning wheel.

Die Sperrklinke ist vorteilhafterweise über eine Feder mit dem Kraftarm verbunden. Weiterhin hat sie die Form eines Dreiviertel-Mondes, wobei die Reaktionsfläche denselben Durchmesser hat wie der Außenkreis der Sperrklinke, die Verzahnung der Sperrklinke befindet sich auf der Begrenzungslinie mit dem größeren Durchmesser der Sperrklinke. Insgesamt wird hierdurch eine möglichst einfache Konstruktion erreicht, die fertigungstechnisch besondere Vorteile bietet.The pawl is advantageously connected to the power arm via a spring. Farther it has the shape of a three-quarter moon, with the reaction surface having the same diameter as the outer circle of the pawl, the toothing of the pawl is on the boundary line with the larger diameter of the pawl. Overall, this results in a construction that is as simple as possible and that offers special advantages in terms of production technology.

Für die weitere Erläuterung der Erfindung wird nun mehr auf die Zeichnung Bezug genommen, in der ein bevorzugtes Ausführungsbeispiel veranschaulicht ist. Dabei zeigt die einzige Figur der Zeichnung ein Schnittbild quer zur Achse eines Kraftschraubers nach der Erfindung.For further explanation of the invention, reference is now made more to the drawing, in which a preferred exemplary embodiment is illustrated. The single figure of the drawing shows a sectional view transverse to the axis of a power wrench according to the invention.

Der Kraftschrauber hat einen Reaktionsarm 1 und einen Kraftarm 2, die um eine Achse 3 gegeneinander schwenkbar angeordnet sind. Hierfür hat der Reaktionsarm 1 eine sich über etwa 180° erstreckende, teilzylindrische Führungsfläche 4, an der eine entsprechende Außenfläche des Kraftarms 2 paßgenau anliegt. Der Kraftarm 2 wiederum hat eine sich über circa 270° erstreckende, zylindrische Führungfläche 5, die der Führung und Lagerung eines Spannrades 7 dient. Dieses ist damit zumindest in einer Drehrichtung gegenüber dem Kraftarm 2 um die Achse 3 drehbar, letztere wiederum kann um einen Winkel von etwa ± 10° aus der gezeigten Mittelstellung gegenüber dem feststehenden Reaktionsarm 1 verschwenkt werden.The power wrench has a reaction arm 1 and a power arm 2, which are arranged so as to be pivotable relative to one another about an axis 3. For this purpose, the reaction arm 1 has a partially cylindrical guide surface 4, which extends over approximately 180 ° and on which a corresponding outer surface of the force arm 2 lies in register. The power arm 2 in turn has a cylindrical guide surface 5 which extends over approximately 270 ° and serves to guide and mount a tensioning wheel 7. This can thus be rotated about the axis 3 at least in one direction of rotation with respect to the force arm 2, the latter in turn can be pivoted by an angle of approximately ± 10 ° from the shown central position with respect to the fixed reaction arm 1.

Das Spannrad 7 hat einen Innensechskant für die Übertragung einer kraftangetriebenen Schraubbewegung auf eine Mutter, einen Schraubenbolzen oder dergleichen. Das Spannrad 7 hat weiterhin eine feinstufige Verzahnung, beispielsweise befinden sich vier Zähne innerhalb des Gesamtschwenkbereichs des Kraftarms von circa 20°. Mit diesen Zähnen wirkt eine Sperrklinke 8 in Form eines Dreiviertel-Mondes zusammen, deren eine, untere, einen größeren Radius aufweisende Begrenzungslinie mit mehreren Zähnen, beispielsweise fünf Zähnen versehen ist. Die Ausbildung und Form dieser Zähne der Sperrklinke 8 entspricht der Ausbildung und Form der Verzahnung des Spannrades 7.The tensioning wheel 7 has a hexagon socket for the transmission of a power-driven screwing movement to a nut, a screw bolt or the like. The tensioning wheel 7 also has fine-toothing, for example there are four teeth within the total pivoting range of the power arm of approximately 20 °. A pawl 8 in the form of a three-quarter moon interacts with these teeth, the one, lower, larger radius of which is provided with a plurality of teeth, for example five teeth. The design and shape of these teeth of the pawl 8 corresponds to the design and shape of the teeth of the tensioning wheel 7.

Der Kraftarm ist im wesentlichen birnenförmig, er geht nach oben hin in einen balligen Antriebskopf 9 über, der durch einen sich über etwas mehr als 180° erstreckenden Kreisbogen um einen Mittelpunkt 10 begrenzt ist, der auf einer parallel zur Achse 3 verlaufenden Achse liegt. Der Kraftarm 2 ist im wesentlichen klappsymmetrisch in Bezug auf eine diesen Mittelpunkt 10 mit dem Durchtritt der Achse 3 verbindende Gerade.The power arm is essentially pear-shaped, it merges upwards into a spherical drive head 9, which is delimited by a circular arc extending over a little more than 180 ° around a center point 10, which lies on an axis running parallel to the axis 3. The force arm 2 is essentially fold-symmetrical with respect to a straight line connecting this center 10 with the passage of the axis 3.

Im Reaktionsarm 1 ist ein Zylinder 11 angeordnet, dessen Achslinie 12 rechtwinklig zu der genannten Verbindungslinie von Mittelpunkt 10 und Durchtrittspunkt der Achse 3 verläuft. Wie die Zeichnung zeigt, befindet sich der Mittelpunkt 10 in der gezeigten Mittelstellung des Kraftarms 2 etwas oberhalb der Achslinie 12, er schneidet die Achslinie auf dem Wege in die linke oder rechte Endstellung.A cylinder 11 is arranged in the reaction arm 1, the axis line 12 of which extends at right angles to the connection line mentioned between the center point 10 and the point of passage of the axis 3. As the drawing shows, the center 10 is in the shown central position of the power arm 2 somewhat above the axis line 12, it cuts the axis line on the way to the left or right end position.

In dem Zylinder 11 ist ein Kolben 13 geführt, der als Plunger ausgebildet ist. Er bildet zusammen mit dem Zylinder 11 einen hydraulischen Kraftzylinder, der die für eine Verschraubung notwendige Kraft aufbringt. Der Kolben 13 hat etwa in seinem Mittelbereich eine Ausnehmung 14, in die der Antriebskopf 9 des Kraftarms 2 formmäßig weitgehend angepaßt eingreift. Dabei bildet die Ausnehmung 14 zwei quer zur Achslinie 12 verlaufende, konkave Anlageflächen 15, im folgenden erste Anlageflächen, aus, an denen sich der Antriebskopf 9 mit seiner genannten, durchmessergleichen zweiten Anlagefläche 16 um den Mittelpunkt 10 abstützt. Die Anlage dieser beiden Flächen 15, 16 soll immer möglichst in einem Punkt erfolgen, der weitgehend exakt auf der Achslinie 12 des Zylinders 11 liegt. In der Praxis ist diese Forderung jedoch nicht exakt zu realisieren, es kann ihr aber weitgehend nachgekommen werden.A piston 13, which is designed as a plunger, is guided in the cylinder 11. Together with the cylinder 11, it forms a hydraulic power cylinder that applies the force required for a screw connection. The piston 13 has approximately in its central region a recess 14 into which the drive head 9 of the power arm 2 engages in a largely adapted form. In this case, the recess 14 forms two concave contact surfaces 15, which run transversely to the axis line 12, hereinafter referred to as first contact surfaces, on which the drive head 9 is supported with its diameter-equal second contact surface 16 around the center point 10. These two surfaces 15, 16 should always be placed at a point that is largely exactly on the axis line 12 of the cylinder 11. In practice, however, this requirement cannot be met exactly, but it can largely be met.

So kann in geänderter Ausbildung gegenüber der Zeichnung der Verlauf insbesondere der zweiten Anlagefläche so gewählt werden, daß der Berührungspunkt der Anlageflächen 15, 16 im wesentlichen auf der Achslinie bleibt. Hierzu muß für den Verlauf der zweiten Anlagefläche 16 ein Kreisbogen mit einem größeren Radius gewählt werden, dessen Mittelpunkt außerhalb des Antriebskopfes 9 liegt.Thus, in a modified configuration compared to the drawing, the course, in particular of the second contact surface, can be selected such that the point of contact of the contact surfaces 15, 16 remains essentially on the axis line. For this purpose, a circular arc with a larger radius must be selected for the course of the second contact surface 16, the center point of which lies outside the drive head 9.

In bekannter Weise ist der Kolben mittels einer Dichtung 17 gegenüber dem Zylinder 11 abgedichtet, jenseits dieser Dichtung befindet sich ein Druckmittelraum 18, der über einen Kanal und ein geeignetes Anschlußstück 19 mit Hydraulikflüssigkeit gefüllt werden kann.In a known manner, the piston is sealed off from the cylinder 11 by means of a seal 17; beyond this seal there is a pressure medium space 18 which can be filled with hydraulic fluid via a channel and a suitable connecting piece 19.

Der Kolben hat eine, von seiner dem Druckmittelraum abgewandten Endfläche 20 her ausgeführte Axialbohrung 21, in der eine Schraubendruckfeder 22 für die Kolbenrückstellung angeordnet ist. Auf Grund der Axialbohrung 21 kann eine relativ lange Schraubendruckfeder 22 gewählt werden. Diese stützt sich mit ihrem anderen Ende an einer Mutter 23 ab, die in das offene Ende des Zylinders 11 eingeschraubt ist, hierzu ist im Zylinder 11 ein Innengewinde vorgesehen. Gegen das Ende der Axialbohrung 21 des Kolbens 13 wird durch die Schraubendruckfeder 22 ein Stift 24 mit tellerartigem Endstück gedrückt. Er befindet sich zumindest teilweise innerhalb einer Hülse 25, die von der Schraubendruckfeder 22 umgriffen wird und in der Mutter 23 gehalten ist. Die Mutter 23 hat eine Durchlaßbohrung 26 für den Stift 24. Insgesamt wird eine nach außen praktisch dichte Konstruktion erreicht.The piston has an axial bore 21, which is made from its end surface 20 facing away from the pressure medium chamber and in which a helical compression spring 22 is arranged for the piston return. Because of the axial bore 21, a relatively long helical compression spring 22 can be selected. This is supported with its other end on a nut 23 which is screwed into the open end of the cylinder 11, for this purpose an internal thread is provided in the cylinder 11. A pin 24 with a plate-like end piece is pressed against the end of the axial bore 21 of the piston 13 by the helical compression spring 22. It is located at least partially within a sleeve 25 which is encompassed by the helical compression spring 22 and is held in the nut 23. The nut 23 has a through bore 26 for the pin 24. Overall, a practically tight construction is achieved to the outside.

Mit dem Stift 24 hat es folgende Bewandnis: Nach Abschluß eines Schwenkhubes befindet sich der Kolben 13 weiter rechts als in der Zeichnung gezeigt, er nimmt dabei den Stift 24 mit, bis dessen vorderes Ende in der Durchlaßbohrung 26 sichtbar ist. Hierdurch wird der Schwenkzustand des Kraftarms 2, insbesondere aber die Endstellung sichtbar. Ein Benutzer kann damit feststellen, ob ein Schraubvorgang abgeschlossen ist. Wird nämlich bei mit vorgegebenem Hydraulikdruck beaufschlagtem Kolben 13 der Stift 24 nicht in der Durchlaßbohrung 26 sichtbar, so reicht der aufgebrachte Druck nicht für eine weitere Verschraubung aus, das gewünschte Maß der Verschraubung ist also erreicht.With the pin 24, the following is true: after the completion of a swivel stroke, the piston 13 is located further to the right than shown in the drawing, taking the pin 24 with it until its front end is visible in the through bore 26. As a result, the pivoting state of the power arm 2, but in particular the end position, is visible. A user can use it to determine whether a Screwing is completed. If the pin 24 is not visible in the passage bore 26 when the piston 13 is pressurized with a predetermined hydraulic pressure, the pressure applied is not sufficient for a further screw connection, and the desired amount of screw connection is therefore achieved.

Die Sperrklinke 8 hat die Form einer flachen Kreisscheibe, die eine randseitige, konkave Aussparung mit dem Durchmesser der Verzahnung des Spannrades 7 hat. Insgesamt entsteht dadurch die schon angesprochene Dreiviertel-Mond-Form. Die Begrenzungslinie mit dem größeren Durchmesser, also dem Durchmesser der Verzahnung des Spannrades 7, reicht nicht bis zum Mittelpunkt des Begrenzungskreises 27 der Sperrklinke 8, sondern hat von diesem einen Abstand, der ein Zehntel des Durchmessers des Begrenzungskreises 27 beträgt. An der Sperrklinke 8 ist etwas oberhalb einer durch den Mittelpunkt des Begrenzungskreises 27 gehenden Waagrechten und im linken Randbereich an einem Stift 28 eine Klinkenfeder 29 angeordnet, die sich größtenteils in einem Kanal des Kraftarms 2 befindet und an diesem mit ihrem anderen Ende gehalten ist.The pawl 8 has the shape of a flat circular disc which has an edge-side, concave recess with the diameter of the teeth of the tensioning wheel 7. Overall, this creates the three-quarter moon shape already mentioned. The boundary line with the larger diameter, that is, the diameter of the toothing of the tensioning wheel 7, does not extend to the center of the boundary circle 27 of the pawl 8, but is at a distance from this which is one tenth of the diameter of the boundary circle 27. On the pawl 8 a pawl spring 29 is arranged slightly above a horizontal through the center of the limiting circle 27 and in the left edge area on a pin 28, which is largely in a channel of the power arm 2 and is held there with its other end.

Die Ausnehmung A hat in ihrem linken Bereich eine Reaktionsfläche, mit der die Sperrklinke 8 zusammenwirkt. Sie setzt sich aus einem größtenteils radial verlaufenden Übertragungsbereich 30 und einer sich an diesen anschließenden Einrastflanke 31 zusammen. Der Übertragungsbereich 30 ist teilzylindrisch, er erstreckt sich über etwa 90° und geht tangential in die Einrastflanke 31 über, die die Verbindungslinie von Mittelpunkt 10 und Achse 3 etwa in einem Winkel von 70° schneidet.The recess A has in its left area a reaction surface with which the pawl 8 interacts. It is composed of a largely radial transmission area 30 and an adjoining snap-in flank 31. The transmission area 30 is partially cylindrical, it extends over approximately 90 ° and merges tangentially into the latching flank 31, which intersects the connecting line from the center 10 and axis 3 at an angle of approximately 70 °.

Gezeigt ist in der Zeichnnung eine Antriebsposition, wie sie auftritt, wenn der Druckmittelraum 18 mit Hydraulikflüssigkeit unter Druck gefüllt ist, die den Kolben 13 weiter nach rechts bewegt. Die Sperrklinke 8 befindet sich in der Eingriffstellung, sie liegt am Übertragungsbereich 30 an. Dieser überträgt die Stellkräfte auf die Sperrklinke 8, die Kraftübertragung erfolgt dabei unter günstigem Winkel und auf kurzem Wege.Shown in the drawing is a drive position as it occurs when the pressure medium chamber 18 is filled with hydraulic fluid under pressure, which moves the piston 13 further to the right. The pawl 8 is in the engaged position, it rests on the transmission area 30. This transmits the actuating forces to the pawl 8, the power transmission takes place at a favorable angle and over a short distance.

Der beschriebene Arbeitshub ist dann beendet, wenn der Kolben 13 den Antriebskopf 9 nach rechts in die rechte Endstellung mitgenommen hat und der Stift 24 in der Durchlaßbohrung 26 zu sehen ist. Nun erfolgt die Rückhubbewegung des Kolbens 13 unter der Wirkung der Schraubendruckfeder 22, sobald der Druckmittelraum 18 drucklos ist. In diesem Fall bleibt die Sperrklinke 8 zunächst in der gezeichneten Eingriffstellung. Mit fortschreitender Rückbewegung des Kolbens 13 und damit Rückschwenkung des Kraftarms 2 dehnt sich aber die Klinkenfeder 29 und ist bestrebt, die Sperrklinke 9 zurückzuziehen. Sollte die Sperrklinke 8 in der Verzahnung des Spannrades 7 hängenbleiben, so wird sie spätestens dann aus dieser Verzahnung herausgedrückt, wenn ein mit der Sperrklinke 8 fest verbundener Stab 32, der auf einer durch den Mittelpunkt des Begrenzungskreises 27 verlaufenden Waagerechten angeordnet ist und nach rechts einige Millimeter vorragt, gegen die Innenwand der Ausnehmung A schlägt.The working stroke described is ended when the piston 13 has taken the drive head 9 to the right into the right end position and the pin 24 can be seen in the through bore 26. Now the return stroke movement of the piston 13 takes place under the action of the helical compression spring 22 as soon as the pressure medium chamber 18 is depressurized. In this case, the pawl 8 initially remains in the engagement position shown. With progressive return movement of the piston 13 and thus pivoting back of the power arm 2, the pawl spring 29 expands and strives to pull the pawl 9 back. Should the pawl 8 get stuck in the toothing of the tensioning wheel 7, then it will be pushed out of this toothing at the latest when a rod 32 which is firmly connected to the pawl 8 and which is arranged on a horizontal extending through the center of the limiting circle 27 and to the right some Protrudes millimeters, strikes the inner wall of the recess A.

Auch andere Mittel zur Unterstüzung des Ausklinkens der Sperrklinke 8 können vorgesehen sein: Beispielsweise kann in die Ausnehmung A eine Feder vorspringen, die die Sperrklinke 8 oder ihren Stab 32 untergreift und hochhebt, falls die Sperrklinke 8 zu weit gegenüber dem Übertragungsbereich 30 zurückbleibt. Auch kann ein parallel zur Achse 3 angeordneter Stift vom Kraftarm 2 in die Ausnehmung 14 vorspringen, der gegebenenfalls eine Auflaufschräge bewirkt und die Sperrklinke 8 aus ihrem Eingriff mit der Verzahnung des Spannrades 7 befreit.Other means for supporting the release of the pawl 8 can also be provided: for example, a spring can protrude into the recess A, which engages under and picks up the pawl 8 or its rod 32 if the pawl 8 remains too far relative to the transmission area 30. Also, a pin arranged parallel to the axis 3 can protrude from the power arm 2 into the recess 14, which optionally causes a run-up slope and releases the pawl 8 from its engagement with the toothing of the tensioning wheel 7.

Bei Fortsetzung der Rückschwenkbewegung rutscht somit die Sperrklinke 8 über die Verzahnung des Spannrades 7, bis sich der Kolben 13 in seiner linken Endstellung befindet. In diesem Zustand befindet sich die Sperrklinke 8 im allgemeinen nicht in einer Eingriffsstellung, wie sie in der Zeichnung gezeigt ist. Vielmehr wird sie auf Grund der schräg verlaufenden Einrastflanke 31 und der Zugkraft der Klinkenfeder 29 lediglich in diese Eingriffstellung vorbelastet. Ein Eingriff wird dann wiederhergestellt, wenn ein erneuter Arbeitshub beginnt. Die Einrastflanke und die Klinkenfeder 29 ziehen dann die Sperrklinke 8 in die Eingriffstellung, sobald die Zähne der Sperrklinke 8 und die Verzahnung des Spannrades 7 in der hierfür richtigen Position zueinander stehen. Dann laufen wieder die bereits geschilderten Vorgänge ab.When the pivoting movement continues, the pawl 8 thus slips over the teeth of the tensioning wheel 7 until the piston 13 is in its left end position. In this state, the pawl 8 is generally not in an engaged position, as shown in the drawing. Rather, it is only preloaded into this engagement position due to the inclined engagement flank 31 and the tensile force of the pawl spring 29. An intervention is restored when a new working stroke begins. The latching flank and the pawl spring 29 then pull the pawl 8 into the engaged position as soon as the teeth of the pawl 8 and the toothing of the tensioning wheel 7 are in the correct position relative to one another. Then the processes already described run again.

Der Übertragungsbereich 30 und/oder die Einrastflanke 31 können Begrenzungsflächen separater Teile sein, die mittels geeigneter Schrauben am Kraftarm 2 gehalten und diesem gegenüber geringfügig verstellt werden können, um eine Nachstellmöglichkeit im Falle von Abnutzung zu haben.The transmission area 30 and / or the snap-in flank 31 can be delimiting surfaces of separate parts, which can be held on the power arm 2 by means of suitable screws and can be adjusted slightly in relation to this, in order to have an adjustment possibility in the event of wear.

Der Kraftschrauber besteht aus relativ wenigen Einzelteilen, die zudem noch einfach zu fertigen sind. Ein Großteil kann sogar als einfache Blechstanzteile ausgeführt werden. Auf Grund der Anordnung des Zylinders 11 im ortsfesten Reaktionsarm 1 wird im Gegensatz zum vorbekannten Kraftschrauber vermieden, daß sich die am Anschlußstück 19 angeschlossene Hydraulikleitung bei jedem Hub bewegt.The power wrench consists of relatively few individual parts, which are also easy to manufacture. A large part can even be made as simple sheet metal stampings. Due to the arrangement of the cylinder 11 in the stationary reaction arm 1, in contrast to the known power screwdriver, it is avoided that the hydraulic line connected to the connecting piece 19 moves with each stroke.

Anstelle der eingezeichneten Rückstellung des Kolbens 13 mittels einer Schraubendruckfeder 22 kann auch ein doppelt wirkender Kolben eingesetzt werden, dann befindet sich auch auf der anderen Seite ein Druckmittelraum.Instead of the shown resetting of the piston 13 by means of a helical compression spring 22, a double-acting piston can also be used, in which case there is also a pressure medium space on the other side.

Man könnte dafür sorgen, daß der Antriebskopf 9 stets oben an der Innenfläche der Ausnehmung 14 anliegt, wenn man dafür sorgte, daß sich der Kraftarm 2 etwas gegenüber dem Reaktionsarm 1 verschieben könnte, und zwar in Längsrichtung dieses Kraftarms 2. Hierzu dürfte die Führungfläche 4 des Reaktionsarms 1 sich lediglich über 180° erstrecken und müßte dann noch wenige Millimeter tangential weitergeführt werden, damit sich der Kraftarm 2 etwas nach oben bewegen kann und zwischen 4 und 5 ein kleiner Spalt entstehen kann, wenn der Kolben 13 den Kraftarm nach links oder rechts, jedenfalls aus der gezeigten Mittelstellung heraus, drückt. Dabei könnte der Antriebskopf 9 entweder formschlüssig im Kolben 13 gehalten sein oder durch eine Feder an die obere Wand der Ausnehmung 14 vorbelastet werden. Auf diese Weise wird erreicht, daß bei der gezeigten Geometrie im Bereich des Antriebskopfes 9 dessen Mittelpunkt 10 stets auf der Achslinie 12 bleibt.You could make sure that the drive head 9 is always on top of the inner surface of the recess 14, if you made sure that the power arm 2 could move slightly relative to the reaction arm 1, namely in the longitudinal direction of this power arm 2. This should be the guide surface 4 of the reaction arm 1 only extends over 180 ° and would then have to be continued tangentially for a few millimeters so that the force arm 2 can move somewhat upwards and between 4 and 5 there can be a small gap when the piston 13 follows the force arm presses left or right, at least from the middle position shown. The drive head 9 could either be held positively in the piston 13 or be preloaded by a spring on the upper wall of the recess 14. In this way it is achieved that in the geometry shown in the area of the drive head 9, its center 10 always remains on the axis line 12.

Claims (11)

1. Power wrench, comprising
- a power arm (2) and a reaction arm (1) being swivable relative to each other about a common swivel axis (3),
- a tensioning wheel (7) which is entrained by the power arm (2) upon swivel motion thereof about the swivel axis (3) in a first direction through engagement of a multi-tooth latch (8) with a fine toothing of the tensioning wheel (7), whereas upon swivel motion of the power arm (2) in opposite direction the latch (8) is sliding over the toothing of the tensioning wheel (7)
and
- hydraulic driving means consisting of a cylinder (11) and of a piston (13) and being effective between the power arm (2) and the reaction arm (1),
characterised in
that the cylinder (11) of the hydraulic driving means is fixedly located within the supported reaction arm (1),
that the power arm (2) comprises a driving head (9) engaging in a recess (14) of the piston (13) within the bore of the cylinder (11)
and
that the axis (12) of the cylinder (11) extends crossways, particularly perpendicular, to the connecting line between the driving head (9) and the swivel axis (3).
2. Power wrench according to claim 1, characterised in that the driving head (9) is ball- shaped and/or is located on the axis (12) of the cylinder (11).
3. Power wrench according to claim 1 or 2, characterised in that the piston (13) in the region of its recess (14) comprises at least one, preferably two, partially cylindrical concave first engagement surfaces (15) the center of which is situated on the axis (12) and that the driving head (9) is terminated by a convex, partially cylindrical second engagenent surface (16).
4. Power wrench according to one of the claims 1 to 3, characterised in that a center point (10) of the driving head (9) is always situated on the axis (12), at any rate its relative motion crossways to this axis (12) is slight.
5. Power wrench according to one of the claims 1 to 4, characterised in that the power arm (2) is formed essentially symmetrical about an axis and is approximately pear-shaped.
6. Power wrench according to one of the claims 1 to 5, characterised in that the power arm comprises a recess (A) formed for receiving the latch (8) and comprising a reaction surface including an engagement flank (31) and an essentially radially extending transmission portion (30).
7. Power wrench according to one of the claims 1 to 6, characterised in that the latch (8) is connected to the power arm (2) through a latch spring (29).
8. Power wrench according to one of the claims 1 to 7, characterised in that the latch (8) is three- quarter-moon-shaped, that the reaction surface (30, 31) is of a diameter equal to that of the circle (27) limiting the latch (8) and that the toothing of the latch (8) is situated on the limiting surface having the larger diameter.
9. Power wrench according to one of the claims 1 to 8, characterised in that the latch (8) is provided with means for an enforced disengagement, e. g. with a rod (32), cooperating with the power arm (2).
10. Power wrench according to one of the claims 1 to 9, characterised in that the piston (13) has assigned thereto a pin (24) which in one end position of the piston (13) has its end portion filling a passage bore (26).
11. Power wrench according to one of the claims 1 to 10, characterised in that the geometrical extension of the transmission portion (30) corresponds to the contour of the latch (8) and that the engagement flank in cooperation with the latch spring (29) urges the latch into the engagement position.
EP85101941A 1984-02-28 1985-02-22 Power-driven screw-driving tool with a fine-toothed chuck Expired EP0153711B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843407126 DE3407126A1 (en) 1984-02-28 1984-02-28 POWER SCREWDRIVER WITH A TENSION WHEEL WITH A FINE-STAGE TOOTHING
DE3407126 1984-02-28

Publications (3)

Publication Number Publication Date
EP0153711A2 EP0153711A2 (en) 1985-09-04
EP0153711A3 EP0153711A3 (en) 1985-10-09
EP0153711B1 true EP0153711B1 (en) 1988-10-12

Family

ID=6228994

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85101941A Expired EP0153711B1 (en) 1984-02-28 1985-02-22 Power-driven screw-driving tool with a fine-toothed chuck

Country Status (6)

Country Link
US (1) US4709600A (en)
EP (1) EP0153711B1 (en)
JP (1) JPS61501256A (en)
DE (2) DE3407126A1 (en)
ES (1) ES8606805A1 (en)
WO (1) WO1985003897A1 (en)

Families Citing this family (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3413202A1 (en) * 1984-04-07 1985-10-17 Wagner, Paul-Heinz, 5203 Much POWER SCREWDRIVER
DE3420446A1 (en) * 1984-06-01 1985-12-05 Applied Power, Inc., Milwaukee, Wis. POWER SCREWDRIVER WITH A POWER ARM AND PREFERRED REAR ARM
GB8525983D0 (en) * 1985-10-22 1985-11-27 Hydra Tight Ltd Power tools
US5203238A (en) * 1989-10-27 1993-04-20 Raymond Engineering Inc. Low profile rack and pinion wrench
DE4210512C2 (en) * 1992-03-31 1994-04-28 Wagner Paul Heinz Hydraulic power wrench
DE4210511C2 (en) * 1992-03-31 1994-06-16 Wagner Paul Heinz Hydraulic power wrench
US6148695A (en) 1999-08-03 2000-11-21 Hu; Bobby Ratchet wheel with asymmetric arcuate concave teeth or non-arcuate concave teeth and ratcheting tools with such ratchet wheel
US6568299B2 (en) 1999-12-16 2003-05-27 Bobby Hu Reversible ratcheting tool with a smaller head
US6431031B1 (en) 1999-12-16 2002-08-13 Bobby Hu Reversible ratcheting tool with a smaller head
TW418748U (en) 2000-01-11 2001-01-11 Hu Hou Fei Ratchet wrench
TW408653U (en) 2000-02-03 2000-10-11 Hu Hou Fei Ratcheting tool
JP3515763B2 (en) 2000-03-13 2004-04-05 厚飛 胡 Reversible ratchet tool with small head and improved drive torque
TW428513U (en) 2000-07-21 2001-04-01 Hu Hou Fei Locating device of a direction switch and ratchet tools using the same
TW437521U (en) 2000-08-22 2001-05-28 Hu Hou Fei Ratchet driven tool
TW444633U (en) 2000-09-01 2001-07-01 Hu Hou Fei Ratchet tool
US6745647B2 (en) 2000-11-29 2004-06-08 Mei-Chen Wang Wrench having a universal-joint ratchet wheel
TW489701U (en) 2001-02-19 2002-06-01 Hou-Fei Hu A ratchet driven wrench capable of easily manufacturing and fabricating
US6807882B2 (en) 2001-05-07 2004-10-26 Bobby Hu Wrench with a simplified structure
US6722234B2 (en) 2001-05-14 2004-04-20 Bobby Hu Easy-to-operate and easy-to-assemble ratcheting-type wrench
US20030131691A1 (en) * 2001-06-20 2003-07-17 Norwolf Tool Works Compact hydraulic torque wrench and reaction arm
US20050011313A1 (en) * 2001-06-20 2005-01-20 Norwolf Tool Works Compact hydraulic torque wrench reaction arm
TW483365U (en) 2001-07-13 2002-04-11 Hou-Fei Hu High torque wrench
TW483377U (en) 2001-07-13 2002-04-11 Hou-Fei Hu Micro small torque wrench with constant torque value
US6647832B2 (en) 2001-07-27 2003-11-18 Bobby Hu Wrench having two rigid supporting areas for a pawl
US6539825B1 (en) 2001-09-20 2003-04-01 Yen-Wen Lin Single direction ratcheting wrench with stuck prevention and ratcheting direction indication
TW503802U (en) 2001-10-17 2002-09-21 Hou-Fei Hu Invertible ratchet wrench
US6450066B1 (en) 2001-10-19 2002-09-17 Bobby Hu Head of a wrench handle
US6520051B1 (en) 2001-12-27 2003-02-18 Bobby Hu Head of a wrench handle
US6715381B2 (en) * 2002-01-22 2004-04-06 John K. Junkers Adjustable reaction arm for torque power tool, and torque power tool provided therewith
TW506308U (en) 2002-02-08 2002-10-11 Hou-Fei Hu Improved structure for ratchet wrench
US6945141B2 (en) 2002-04-22 2005-09-20 Bobby Hu Reversible ratchet type wrench
TW567123B (en) 2002-07-22 2003-12-21 Hou-Fei Hu Ratchet wrench capable of fast rotation
TWI245684B (en) 2002-08-05 2005-12-21 Yan-Wen Lin Simple ratchet wrench
US6912933B2 (en) * 2003-04-11 2005-07-05 Brian Knopp Hydraulic torque wrench system
US7497147B2 (en) * 2006-09-12 2009-03-03 Unex Corporation Torque tool for tightening or loosening connections, and method of tightening or loosening the same
US9550282B2 (en) * 2014-04-22 2017-01-24 John D. Davis Compact hydraulic torque wrench cartridge

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2112693A (en) * 1937-06-16 1938-03-29 Independent Pneumatic Tool Co Portable hammer wrench
DE2626923A1 (en) * 1976-06-16 1977-12-29 Mock Geraetebau Gmbh & Co Kg Wrench for countersunk head fasteners - comprises nut engaging wrench with counter bearing to resist drive torque
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
DE3008381A1 (en) * 1980-03-05 1981-09-10 Wagner, Paul-Heinz, 5203 Much TURNING TOOL
US4339968A (en) * 1980-07-21 1982-07-20 Willard Krieger Hydraulic torque multiplier wrench
US4409865A (en) * 1981-01-15 1983-10-18 Unex Corporation Continuous ratchet drive
SU1082610A1 (en) * 1982-12-27 1984-03-30 Skripnyak Ilya K Power nut driver
DE3323904A1 (en) * 1983-07-02 1985-01-10 Paul-Heinz 5203 Much Wagner TURNING TOOL

Also Published As

Publication number Publication date
ES8606805A1 (en) 1986-05-16
US4709600A (en) 1987-12-01
DE3407126A1 (en) 1985-08-29
DE3565487D1 (en) 1988-11-17
EP0153711A3 (en) 1985-10-09
JPS61501256A (en) 1986-06-26
WO1985003897A1 (en) 1985-09-12
EP0153711A2 (en) 1985-09-04
ES540821A0 (en) 1986-05-16

Similar Documents

Publication Publication Date Title
EP0153711B1 (en) Power-driven screw-driving tool with a fine-toothed chuck
EP0507147B1 (en) Coupling
DE3620753C2 (en)
EP1688654B1 (en) Vacuum valve
DE2916497A1 (en) HYDRAULIC WRENCH
DE2338304A1 (en) TORQUE WRENCH
DE4042070A1 (en) Hydraulic screwdriver operating mechanism - comprises piston and cylinder aggregate activating lever which controls ring in head
DE2927423C2 (en) Dual circuit pressure regulator
DE2643552A1 (en) SCREW WRENCHES, IN PARTICULAR RATCHET WRENCHES
EP0163009B1 (en) Power-driven wrench with an action arm and a reaction arm, preferably constructed as a housing
DE1800976A1 (en) Universal chuck
EP0035165B1 (en) Rotary tool
DE2837676A1 (en) LOCKING DEVICE FOR A PISTON ROD
DE8435272U1 (en) HYDRAULIC SCREWDRIVER
EP0035164B1 (en) Power wrench
AT523901B1 (en) Self-locking preload ring for shock absorbers
DE4042154C2 (en) Pressure operated power wrench
DE3941752A1 (en) TORQUE DEVICE
DE3408188C1 (en) Fluid medium-actuated swivelling clamping device
EP0062195B1 (en) Power-driven screw-driving tool
DE4028950A1 (en) TORQUE DEVICE
DE1075921B (en) Boring bar
DE3014744A1 (en) HYDRAULIC TENSIONER
DE3416879C2 (en)
DE4111631A1 (en) POWER SCREWDRIVER

Legal Events

Date Code Title Description
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

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): DE FR GB IT SE

AK Designated contracting states

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19860402

17Q First examination report despatched

Effective date: 19870415

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REF Corresponds to:

Ref document number: 3565487

Country of ref document: DE

Date of ref document: 19881117

ITF It: translation for a ep patent filed

Owner name: GUZZI E RAVIZZA S.R.L.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
ET Fr: translation filed
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

26N No opposition filed
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19900426

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19900820

Year of fee payment: 6

Ref country code: FR

Payment date: 19900820

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19900822

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19910222

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19910223

GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19911031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19911101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

EUG Se: european patent has lapsed

Ref document number: 85101941.4

Effective date: 19911008