DE102020108873A1 - Tool for pressing and / or expanding a pipe section - Google Patents

Abstract

A tool (1) is proposed for pressing and / or expanding a pipe section for a pressing process and / or expanding process on a pipe, the tool (1) comprising two jaws (3, 4) which are used for a pressing process and / or Expanding process with a drive (5) of the tool (1) can be driven relative to one another. According to the invention, the drive has one side of a mechanical interface (7) to a drill and / or to a screwdriver (2), the drill and / or the screwdriver (2) having an opposite side that matches the side of the mechanical interface (7), with in a state in which the drill and / or the screwdriver (2) is connected to the tool (1), the interface (7) is able to simultaneously transmit a counter-torque to a drive torque via support means and a driven, movable one The feed element (20) of the tool (1) is linearly guided so that it can be moved back and forth along a sliding guide, the feed element (20) being coupled in terms of movement to a jaw (4).

Description

State of the art

Hand-held tools for pressing and / or for expanding a pipe section are known.

In some cases, comparatively high forces are necessary for machining the pipe section.

Object and advantages of the invention

The object of the present invention is to provide a tool of the type mentioned in the introduction which enables comfortable and safe work when pressing and / or expanding a pipe section. In particular, a compact, powerful and flexibly applicable tool is to be provided.

This problem is solved by the independent claim.

Expedient and advantageous developments of the invention are set out in the dependent claims.

The invention is based on a tool for pressing and / or expanding a pipe section for a pressing process and / or expanding process on a pipe, the tool comprising two jaws that are driven relative to one another for a pressing process and / or expanding process with a drive of the tool are movable. Preferably only exactly one of the two jaws can be driven. The other jaw, for example a fixed jaw, is preferably present in a fixed position on the tool, for example on a tool housing of the tool.

The essence of the invention is that the drive has one side of a mechanical interface to a drill and / or to a screwdriver, the drill and / or the screwdriver having an opposite side that matches the side of the mechanical interface, wherein in a state in to which the drill and / or the screwdriver is connected to the tool, the interface is capable of simultaneously transmitting a counter-torque to a drive torque via support means and wherein a driven, movable feed element of the tool is linearly guided along a sliding guide so that it can be moved back and forth, wherein the advancing element is coupled for movement with a jaw. The feed element can be moved in a driven manner by means of the drive of the tool.

The term “tool” is used below for the tool according to the invention, not for the drill or screwdriver.

This provides a compact solution. In addition, due to the electrical or machine drive with a drive motor of the drill or screwdriver, defined and comparatively high forces and torques can be applied to drive the at least one jaw. The application of the force or the moments takes place advantageously without jolts, evenly and / or continuously.

The drive is part of the tool and must be distinguished from a drive unit such as an electric motor of the drill or screwdriver. When the tool is in operation, when the tool is connected to the drill or screwdriver via the interface with the support means, the drive effect for the tool is generated by the motor of the drill or screwdriver in cooperation with the drive of the tool. The screwdriver is, for example, a cordless screwdriver.

With the sliding linear movement of the advancing element, a defined movement guidance of the advancing element and thus the jaw is realized along an exactly straight or predetermined movement path.

The feed element is preferably rigidly coupled in terms of movement to exactly one or first jaw. A second jaw is preferably fixed in position. Alternatively, both jaws can be driven by one or two feed elements in such a way that both jaws move linearly while being driven. In one operating state, the two jaws move simultaneously towards one another and in another operating state, when the direction of rotation of the drive shaft is reversed, they move away from one another or apart.

In particular, there is preferably an exclusively linear movement of the feed element. The linear movement of the feed element takes place, for example, between a starting point of the feed element and a reversal point of the feed element, alternating or reversible in a first direction from the starting point to the reversing point and back from the reversing point to the starting point in a second direction opposite to the first direction.

The drive of the tool is characterized in that an externally provided rotational movement, preferably by a rotating shaft or with a rotating shaft of the drill or screwdriver, is continuously converted into a Direction of the rotationally rotating component of the drive of the tool can be transmitted. In the tool or by means of the drive of the tool, the rotating component leads to the movement drive of the at least one jaw of the tool. The rotating component of the tool drive is converted in the tool into the sliding linear movement of the feed element.

The support means are preferably present integrally on or in the interface, in particular present essentially within a housing of the tool that encloses the tool on the outside. Only sections of the support means reach up to the tool-side side of the interface for contacting the opposite side on the drilling machine or the screwdriver when the interface is closed.

The interface is preferably a known interface of a known drill or a known screwdriver, in particular in order to arrange a suitable angular gear for a drill drive or a screw drive on the drill or screwdriver at the interface. Instead of z. B. the angular gear, the tool according to the invention is advantageously attachable to the drill or screwdriver. The tool according to the invention can thus be used universally or flexibly with known hand-held drive machines.

A drill or a screwdriver, which are widely available, can advantageously be used as the drive motor for the tool according to the invention. Otherwise, the drill can be used for other purposes as usual. It is advantageous that the tool itself does not have a motorized drive unit or does not require an electric motor. The tool is therefore comparatively inexpensive. In addition, the tool has a lower weight compared to a tool with its own drive unit or its own motor. Finally, the tool is compact or space-saving when not in use when the tool is separated from the drill or screwdriver. This is particularly advantageous with regard to transport.

It is also advantageous that in known drills or screwdrivers, one side of the interface is already integrated ex works on the drill, for example to be able to attach an angular gear so that the drill can be used at an angle to the longitudinal or rotational axis of a rotary shaft or Drill shaft can be worked or drilled. The interface side of the tool is matched to the interface side integrated in the drilling machine. With the transmission of the counter-torque when the tool is attached to the drill or the screwdriver or with the interface closed, a safe, structurally closed unit of the tool with the drill or the screwdriver is provided.

Advantageously, with the accommodation of the counter-torque transmission integrated in the tool, components that are otherwise particularly disruptive or that act on the outside of the drill or screwdriver can be dispensed with, which relatively cause parts of the tool to rotate with the rotating rotary shaft or the rotating drill head of the drilling machine during operation to prevent the drill. According to the invention, this function is integrated in the interface or is present without an interfering contour.

The interface is preferably designed in such a way that the tool can be used as an attachment or quick-change tool. In this way, the tool can be attached to the drill or screwdriver in a simple or uncomplicated manner, preferably without further aids, and removed again.

The sliding guide advantageously comprises a rail element, the advancing element being received on the rail element in a displaceably movable manner. The sliding guide preferably comprises a linear or sliding guide for the linear movement of the advancing element. The linear or sliding guide comprises the at least one rail element. On the rail element, which is preferably in a fixed position on the tool, the feed element is reversible or can be moved back and forth. The feed element is z. B. formed as a slide element with a feed element or slide profile section. The linearly movable advancing element is, for example, slidably movable or held in a guided manner along the straight, profiled rail element, which has a rail profile section that is matched to the advancing element profile section.

The rail element and the feed or slide element have mutually coordinated sliding surfaces on their profile sections facing each other and, for example, flatly abutting each other, so that a comparatively large surface contact is provided by guide surfaces that are flat against each other. This is advantageous for a clean, uniform motion control.

An advantage is obtained if the rail element has a plurality of guide surfaces at an angle to one another, the guide surfaces extending over a length of the rail element. The rail element has, for example, a web that is rectangular in cross section. Of the Steg sets up two or three strip-shaped guide surfaces, with two adjacent guide surfaces each being aligned at right angles to one another. The feed element is guided on the web and engages around the three guide surfaces in contact, for example with a groove or channel-shaped section or a rectangular groove with corresponding three guide surfaces. The web on the rail element engages appropriately in the groove on the feed element.

A sliding path of the feed element can thus be predetermined over the length of the rail element or the feed element over the length of the guide surfaces. Preferably there are exactly two or exactly three or more guide surfaces on the rail element and on the feed element. A plurality of counter-guide surfaces for sliding contact on the rail element guide surfaces are preferably provided on the feed element. The entire surface provided by the guide surfaces on the advancing element is preferably in contact with the guide surface or surfaces on the rail element in all sliding positions of the advancing element.

The sliding guide advantageously comprises two rail elements which are spaced apart from one another and which are aligned parallel to one another and wherein the advancing element is received on the two rail elements so as to be displaceable. This provides a mechanically loadable and / or low-play and / or tilt-proof and / or stable guide.

There are preferably exactly two rail elements. The rail elements are preferably designed in the same way or preferably identically. Preferably, several, preferably three, guide surfaces at an angle to one another are provided on both rail elements. The movable feed element preferably has for each rail element or z. B. for both rail elements a respective counter-guide surface per guide surface on the rail element.

According to another advantageous modification, the drive has a transmission unit, the transmission unit being designed to pick up a rotary movement of a rotary shaft of the drill or of the screwdriver and to convert it into a linear movement of a ram element of the drive of the tool. This represents a mechanically highly resilient and / or compact design, in particular in a width direction and / or a longitudinal direction of the plunger element. Starting from the torque that can be tapped off on the rotating shaft, high forces can be provided on the ram element, which are effective as a pressing force during pressing or as an expanding force during expansion with the drivable jaw. Finally, a tappet element can advantageously be designed as a component that can withstand high mechanical loads. The transmission unit preferably has components that interact in the manner of a gear. The transmission unit is advantageously accommodated within a housing of the tool that is at least substantially closed to the outside. The housing is preferably flat or flat and plate-shaped on both sides. The transmission unit is preferably designed so that when the tool is connected to the drill or screwdriver, the axis of rotation of the rotary shaft is at right angles to the axis of movement of the plunger element, preferably the two axes intersect.

The plunger element is preferably elongated or pin-like.

It is also advantageous if the transmission unit comprises an eccentric arrangement with a rotatable eccentric element, the eccentric arrangement being designed to convert a rotary movement of the eccentric element into a linear movement of the plunger element. The eccentric arrangement is preferably a first eccentric arrangement of the transmission unit. Advantageously, the eccentric arrangement can be used to convert a continuously rotary rotary movement of the eccentric element in one direction of rotation, the rotary movement of the eccentric element being initiated by the rotating rotary shaft of the drill or screwdriver, into a linear movement of the plunger element or into a linear reciprocating movement.

The eccentric element has an axis of rotation about which the eccentric element can be rotated. The eccentric element is preferably disk-shaped with a transmission section present outside a center of the disk. The axis of rotation of the eccentric element can lead through the center of the disk or through the transmission section.

Another advantage is that the drive acts on a ratchet arrangement with which the advancing element can be driven. Accordingly, the advancing element and thus the drivable jaw is linearly displaceable along the sliding guide. According to the ratchet principle, when the advancing element is moved in a driven manner in a first sliding direction, the advancing element is secured in a shifted position against a sliding movement in a second sliding direction opposite to the first sliding direction. Pushing the advancing element is then only possible in the first pushing direction, which determines the pressing or expanding direction, as long as no release mechanism is actuated. Moves when you slide in the first slide direction the jaw on the feed element towards the other jaw or the fixed jaw, so that a pipe section and / or fitting present in the area between the jaws is pressed or expanded.

The transmission unit preferably comprises a second eccentric arrangement, for example between the plunger element and the ratchet arrangement. The second eccentric arrangement preferably acts on the ratchet arrangement. The second eccentric arrangement preferably comprises a reciprocating or a second eccentric element. The second eccentric element is preferably pivoted back and forth by the linearly reciprocating plunger element, about an axis of rotation of the second eccentric element. The second eccentric element is pivoted back and forth, for example, by approximately 60 to 100 angular degrees when the plunger element moves back and forth.

The second eccentric element is, for example, a receiving element, since an arm of the ratchet arrangement is received on this, for example, it is articulated on a pin section. The second eccentric element or the receiving element is preferably received pivotably in a recess. The recess is preferably designed in a housing section of the tool, for example as an opening or as a blind hole with a remaining axial base. The preferably cylindrical recess is preferably present in the housing section of the tool, axially open inwards, for easy insertion or for pivotable mounting of the second eccentric element or the receiving element. Between the z. B. cylindrical inner wall of the recess and a cylindrical outer side of the second eccentric element or the receiving element adjacent therein is preferably a plain bearing arrangement with a plastic plain bearing ring made of a plain bearing plastic or polymer material or another material with comparatively good plain bearing properties.

Accordingly, the first and / or the second eccentric element is or are preferably rotatably mounted with a sliding bearing arrangement, preferably with a plastic sliding bearing comprising, for example, a hollow cylindrical sliding bearing element made of the plastic material.

It is advantageous that the plunger element can be moved back and forth linearly when the eccentric element rotates through 360 degrees about an axis of rotation of the eccentric element. The eccentric element is preferably the first eccentric element or the eccentric element of the first eccentric arrangement. The plunger element driven by the first eccentric element has a self-driving effect on the second eccentric element, which drives the ratchet arrangement.

The ratchet arrangement can advantageously be operated with the reciprocating plunger element. The plunger element preferably acts to drive or to pivot the second eccentric element or the receiving element to and fro. An arm of the ratchet arrangement is preferably articulated on the second eccentric element. The arm of the ratchet assembly has a driving effect on the feed element. For this purpose, a tooth section of the arm engages in a matching mating tooth section on the feed element.

When the plunger element moves forward, it acts in such a way that the advancing element or the drivable jaw is moved in a first sliding direction, with the jaw being held in a fixed position in its reached sliding position at the end of the forward movement. During the subsequent forward movement of the plunger element, the advancing element and thus the drivable jaw attached to it remain unmoved. Only with the next or renewed movement of the plunger element is the feed element with the drivable jaw moved again in the first sliding direction, which is repeated several times when the first eccentric element is rotated and the second eccentric element is pivoted back and forth. With the further movement of the feed element and thus the jaw, this is moved towards the fixed or counter-jaw and the pipe section is pressed or expanded.

An axial end of the plunger element is advantageously coupled to the eccentric arrangement. A first axial end of the plunger element is advantageously coupled to the first eccentric arrangement or to the first eccentric element. Another or second axial end of the plunger element is coupled to the second eccentric arrangement or to the second eccentric element or the receiving element.

This is space-saving and structurally advantageous.

For example, the first axial end of the plunger element is connected to a transmission ring which can be moved back and forth within a distance in the direction of the longitudinal axis of the plunger element by contact with the rotating eccentric element of the first eccentric arrangement. As a result, the plunger element itself is also moved back and forth.

According to an alternative advantageous modification, the plunger element is connected to a rotatably mounted receiving element, with the Receiving element is received an arm of the ratchet assembly. The receiving element is preferably the second eccentric element or the eccentric element of the second eccentric arrangement which can be rotated back and forth or pivoted back and forth. The arm of the ratchet arrangement is articulated on this second eccentric element. The arm has the tooth contour, which engages in the opposing tooth contour on the feed element and displaces this linearly when the second eccentric element moves outwards.

With the forward movement of the plunger element, the receiving element is pivoted in a first direction and with the forward movement of the plunger element, the receiving element is pivoted in a second direction. The second direction is opposite to the first direction.

Depending on the direction of rotation or pivoting of the receiving element, the arm is also moved to or fro. With the pivoting movement of the receiving element in the first pivoting direction, the arm is moved from an initial position to an end position, so that the feed element and thus the driven jaw are driven in the direction of the other jaw. With the pivoting movement of the receiving element in the second direction of rotation, the arm is moved from the end position back into the starting position without the advancing element being moved along with it. When the arm is moved back into the starting position, another mechanism, for example a locking mechanism with a locking element that acts on the opposing tooth contour on the feed element, ensures that the feed element or the driven jaw is not adjusted or cannot be pushed back.

The arm is preferably mounted in an articulated manner on the receiving element, preferably outside the axis of rotation of the receiving element. On the arm, the z. B. is designed as a lever arm, there is an engagement section or the tooth contour, which engages in a force-transmitting manner in the counter-section or counter-tooth contour on the feed element, for example, positively fitting to the engagement section or the tooth contour, and this moves when the arm moves from the starting position into the End position.

It is also advantageous that the eccentric element and a transmission ring of the tool are connected to one another via a slide bearing arrangement. The sliding bearing arrangement preferably comprises a plastic sliding bearing, preferably with a plastic sliding bearing ring made of a plastic material with excellent sliding bearing properties. The transmission ring can preferably be moved back and forth in the longitudinal direction of the tappet element with the rotation of the eccentric element.

The first eccentric element is preferably mounted so as to be movable relative to the transmission ring of the tool via the sliding bearing arrangement.

The second eccentric element or the receiving element is preferably also rotatably or pivotably mounted with a sliding bearing arrangement, preferably in a recess in the housing section of the tool. The plain bearing is preferably carried out with a plastic plain bearing ring made of a plastic material with excellent plain bearing properties. The second eccentric element is the eccentric element which can be reciprocated or pivoted back and forth and which belongs to the second eccentric arrangement. The arm of the ratchet arrangement is attached to the second eccentric element.

It is also advantageous if the transmission ring has a protruding tab which is connected to the tappet element. The tab and the tappet element are preferably connected in an articulated manner or the tab is hinged to the tappet element. A lateral movement of the transmission ring transversely to the longitudinal axis of the plunger element, which takes place in addition to the to-and-fro movement, can thus be compensated for.

An alternative advantageous variant consists in that the tappet element can be driven by an eccentric element arranged laterally to the longitudinal axis of the tappet element, with a driver that can be moved by the movement of the eccentric element.

The eccentric element is preferably present as an extension of the rotary shaft of the drill or screwdriver, in particular present laterally next to the plunger element. The driver is preferably positioned between the longitudinal outside of the plunger element and the eccentric element.

The plunger element is connected to the driver by a connection which engages laterally on the plunger element or transversely to the longitudinal axis of the plunger element, for example by a screw connection. The driver transfers its linear movement to the ram element. The linear back and forth movement or displacement of the driver is brought about by the continuous rotational movement of the eccentric element or the first eccentric element. The driver and the eccentric element are matched to one another in such a way that the driver experiences a linear movement during the rotary movement of the eccentric element and transfers this movement to the plunger element. In the direction of the linear movement, the driver represents a stop for the eccentric element. In a direction perpendicular to the direction of the linear movement Direction, the driver forms a freewheel for the movement of the eccentric element.

One advantage is that the driver is designed as a U-profile. Accordingly, the plunger element is coupled to the driver or the U-profile in which the eccentric element engages.

This enables a relative movement between the eccentric element and the driver or the U-profile element in a first direction transverse to the axis of rotation of the eccentric element when the eccentric element is rotated. In a second direction transverse to the axis of rotation of the eccentric element, the relative movement is prevented or the eccentric element and the driver move together.

Finally, it is advantageous that the feed element has a counter-tooth contour in which a matching tooth contour engages, which is present on the arm of the ratchet arrangement. A reliable transmission of force or movement from the arm of the ratchet arrangement to the feed element is thus achieved.

It is also advantageous that a reset arrangement is provided which is designed to reset the feed element from an end position to an initial position after a machining operation carried out with the tool, the reset of the feed element being triggered solely by actuating an operating element of the drill or screwdriver is and takes place automatically after triggering by the reset arrangement. This enables ergonomically advantageous work with the pressing or expanding tool.

The reset arrangement is advantageously coordinated for an advantageous ergonomic operation of the tool. When operating the tool, it is often necessary to work bent over or kneeling, so that at the end of a work process or pressing or expanding a manual action on a release mechanism or a release lever to release a detent z. B. the ratchet assembly including arm and latch and the resetting of the feed element and thus the jaw is difficult or inconvenient. This is because manual operation is required, which is also cumbersome when holding the drill or screwdriver. This situation is avoided with the reset arrangement. The user only has to continue to operate the drill or screwdriver for a short time after the end of the machining process.

Finally, it is advantageous that a locking mechanism acting on a pivotable locking pawl of the tool is provided with which, when the locking pawl reaches a predetermined pivoting position when the locking pawl is pivoted in a first pivoting direction of the locking pawl, the locking pawl is held in a pivoting position from which the The locking pawl cannot be pivoted back against the first pivoting direction of the locking pawl. The safety mechanism preferably acts on the release lever on which the latch is attached.

The held pivot position of the latching pawl or the release lever on which the latching pawl is attached, which is assumed by the release lever or the latching pawl when the feed element is returned to the starting position, can be canceled, preferably manually. This is done e.g. B. by acting on the release lever.

The first pivoting direction of the latch means in this context a removal of the tooth contour of the latch from the opposing tooth contour on the feed element.

It is also advantageous that the receiving element is rotatably mounted with a sliding bearing arrangement in a recessed mounting of the tool.

For a stable and clean sliding bearing or sliding guide of the rotatable or reciprocating receiving element, a sliding bearing arrangement is provided, which is preferably designed as a plastic sliding bearing arrangement.

The receiving element is in its basic form, for. B. cylindrical or circular disk-shaped. The slide bearing arrangement accordingly preferably comprises a receptacle for mounting the receptacle element. The receptacle has, for example, two matching depressions, which are located at opposite points, for example a housing such as, for. B. two housing plates are formed. The receiving element is enclosed between the housing plates. The housing plates are connected to one another, for example screwed. The depressions are preferably formed by a material recess with a residual base thickness in the housing section or the housing plates. The cylindrical or round recesses are, for example, like blind holes and have a slightly larger diameter D1 than the outer diameter D2 of a respective bearing section of the receiving element that engages in the recesses and is located opposite on the receiving element.

A section of the plunger element is advantageously guided in a linearly displaceable manner in a linear guide of the tool. The support means can thus be provided in a space-saving and simple manner. In particular, a section of the plunger element designed as a joint driver, which serves for the articulated connection of the first eccentric arrangement to the receiving element or the second eccentric arrangement provided therewith, and sections of the linear guide serve as support means.

The plunger element or the joint driver is guided in a linearly displaceable manner in the linear guide of the tool surrounding the joint driver. The joint driver is z. B. slidably or with a plain bearing guided in the tool or the housing plates. The joint driver is preferably embedded in the sections forming the linear guide, the linear guide being formed on the inside in the tool or on the inside on the opposite housing plates. The linear guide preferably comprises two matching guide tracks, which are approximately rectangular or, for example, have a flat bottom, and extend over a maximum or possible movement path for the reciprocating movement of the plunger element or the joint driver.

With the joint driver guided in the linear guide, forces and / or moments can be absorbed in the drive mode of the tool. In particular, with the articulated driver, which is guided displaceably in the linear guide, a torque support is provided up to the side of the interface relating to the tool or, in particular, a counter-torque is transmitted via support means. The counter-torque is transmitted at the same time as the drive torque is transmitted.

Another advantage is obtained if the linear guide comprises a guide track in which the section of the plunger element is received in a guided manner, one side of the section facing a guide surface of the guide track. The respective tappet element section and the associated guide surface are preferably in sliding surface contact with one another.

Figure list

Further features and advantages of the invention are explained in more detail on the basis of the exemplary embodiments shown in the figures.

• 1 ein erfindungsgemäßes Verpress-Werkzeug an einem Akku-Schrauber perspektivisch schräg von unten mit einem teilweise dargestellten Griffbereich,
• 2 die Anordnung gemäß 1 im Längsschnitt,
• 3 ein weiteres Verpress-Werkzeug in einer Endposition von der Seite ohne einen Gehäuseabschnitt,
• 4 das Verpress-Werkzeug gemäß dem Schnitt A-A in 3,
• 5 die Anordnung gemäß 3 in einer Lösestellung,
• 6 das Verpress-Werkzeug gemäß dem Schnitt A-A in 5,
• 7 die Anordnung gemäß 3 in einer Freigabestellung,
• 8 das Verpress-Werkzeug gemäß dem Schnitt A-A in 7,
• 9 die Anordnung gemäß 3 in einer Ausgangsstellung,
• 10 das Verpress-Werkzeug gemäß dem Schnitt A-A in 9,
• 11 ein weiteres Verpress-Werkzeug in einer Endposition von der Seite ohne einen Gehäuseabschnitt,
• 12 das Verpress-Werkzeug gemäß dem Schnitt A-A in 11,
• 13 die Anordnung gemäß 11 in einer Lösestellung,
• 14 das Verpress-Werkzeug gemäß dem Schnitt A-A in 13,
• 15 die Anordnung gemäß 11 in einer Freigabestellung,
• 16 das Verpress-Werkzeug gemäß dem Schnitt A-A in 15,
• 17 die Anordnung gemäß 11 in einer Ausgangsstellung,
• 18 das Verpress-Werkzeug gemäß dem Schnitt A-A in 17.
• 19 einen Schnitt durch das Verpress-Werkzeug gemäß 7,
• 20 eine Gehäuseplatte des Verpress-Werkzeugs gemäß der 3-19 in perspektivischer Ansicht,
• 21 in perspektivischer Ansicht ein vergrößert dargestellter Abschnitt bzw. Gelenkmitnehmer eines Stößelelements des Verpress-Werkzeugs,
• 22 in perspektivischer, stark schematisierter Ansicht einen Ausschnitt des Verpress-Werkzeugs gemäß der 3-19, wobei eine Gehäuseplatte teilweise freigeschnitten ist und ein Verbindungsglied transparent dargestellt ist,
• 23 ein Aufweit-Werkzeug von der Seite und
• 24 den in 23 umrandet dargestellten Bereich B vergrößert mit einem angedeuteten daran angebrachten Rohrabschnitt.

In detail shows:

• 1 a pressing tool according to the invention on a cordless screwdriver in perspective obliquely from below with a partially shown grip area,
• 2 the arrangement according to 1 in longitudinal section,
• 3 Another pressing tool in an end position from the side without a housing section,
• 4th the pressing tool according to section AA in 3 ,
• 5 the arrangement according to 3 in a release position,
• 6th the pressing tool according to section AA in 5 ,
• 7th the arrangement according to 3 in a release position,
• 8th the pressing tool according to section AA in 7th ,
• 9 the arrangement according to 3 in a starting position,
• 10 the pressing tool according to section AA in 9 ,
• 11 Another pressing tool in an end position from the side without a housing section,
• 12th the pressing tool according to section AA in 11 ,
• 13th the arrangement according to 11 in a release position,
• 14th the pressing tool according to section AA in 13th ,
• 15th the arrangement according to 11 in a release position,
• 16 the pressing tool according to section AA in 15th ,
• 17th the arrangement according to 11 in a starting position,
• 18th the pressing tool according to section AA in 17th .
• 19th a section through the pressing tool according to 7th ,
• 20th a housing plate of the pressing tool according to FIG 3-19 in perspective view,
• 21 a perspective view of an enlarged section or joint driver of a ram element of the pressing tool,
• 22nd a perspective, highly schematic view of a section of the pressing tool according to FIG 3-19 , wherein a housing plate is partially cut free and a connecting member is shown transparent,
• 23 a widening tool from the side and
• 24 the in 23 Area B shown in a bordered manner enlarged with an indicated pipe section attached thereto.

In the following, corresponding elements of different exemplary embodiments are given the same reference symbols in some cases.

the 1 and 2 show a tool 1 according to the invention, which is designed as an attachment tool and attached to an in 2 cordless screwdriver indicated by dashed lines 2 is detachably present and functionally connected to it. Instead of the cordless screwdriver 2 a wired screwdriver or a drill can also be provided.

The tool 1 is designed as a pressing tool and has two jaws 3 and 4th on, including the fixed jaw 3 and the driven jaw 4th . The cheeks 3 and 4th work together to press a pipe section (not shown) of a pipe. The jaw moves 4th driven in direction P1 on the jaw 3 to (s. 2 ) to one according to 1 and 2 shown end position of the jaw 4th . After a pressing process, the jaw moves 4th back again in the return direction P2.

The cheeks 3 , 4th are preferably interchangeable on the tool 1 available and can, for example, by fitting on the tool 1 attachable other attachments such. B. expansion attachments for expanding a pipe section are replaced.

The tool 1 has a drive 5 for the cheek 4th on. The drive 5 owns a side 6th a mechanical interface 7th to the handheld cordless screwdriver indicated by dashed lines 2 with a rotating shaft D of the cordless screwdriver 2 . The cordless screwdriver 2 is held by hand and by pressing a control element 56 of the screwdriver 2 its drive unit is activated, so that the cordless screwdriver is in operation 2 z. B. an electric motor of the cordless screwdriver 2 the screwdriver rotary shaft D drives continuously rotating around its longitudinal axis.

The mechanical interface 7th shows an opposite side 8th on that to the cordless screwdriver 2 heard, being the opposite side 8th and the side 6th of the tool 1 are matched to one another.

The cordless screwdriver 2 with that to the side 6th matching opposite side 8th and the tool 1 are designed so that the interface 6th is able to do that in the working mode of the cordless screwdriver 2 an acting drive force or an acting drive torque at the same time via support means 9 a counter-torque on the tool 1 is transmitted. The props 9 act with counter-props on the opposite side 8th at the cordless screwdriver 2 attached tool 1 or when the interface is closed 7th together.

The drive 5 of the tool 1 has a transmission unit 10 on, the transmission unit 10 is designed, a rotary movement of the rotary shaft D of the cordless screwdriver 2 to tap and in a linear movement of a plunger element 11 of the drive 5 to convict. The linear movement of the plunger element 11 is a reciprocating movement in the direction of a longitudinal axis L of the plunger element 11 with a linear movement direction R1 and a linear movement direction R2 opposite to the direction R1. The rotation of the rotary shaft D takes place via a drive unit or an electric motor of the cordless screwdriver 2 .

The transmission unit 10 comprises a first eccentric arrangement for this purpose 12th with a rotatable eccentric element 13th . The eccentric element 13th is non-rotatably with a pin via an intermediate piece 14th in the area of the page 6th coupled. The pencil 14th is in the connected state of the tool 1 with the cordless screwdriver 2 when the interface is closed 7th with the rotary shaft D of the cordless screwdriver 2 non-rotatably connected and corresponding to a drive speed of the connected electric motor of the cordless screwdriver 2 can be driven in rotation. The eccentric element 13th rotates around an axis of rotation D1 of the drive 5 . The axis of rotation D1 coincides with the axis of rotation of the rotary shaft D of the cordless screwdriver 2 together.

With the eccentric arrangement 12th becomes the rotational movement of the rotary shaft D and thus the rotation of the eccentric element 13th in the linear movement according to the directions R1, R2 of the plunger element 11 convicted. A first axial end to the longitudinal axis L is for this purpose 11a of the plunger element 11 with the eccentric arrangement 12th or with a transmission ring 15th the eccentric arrangement 12th coupled. One on the outside of the transmission ring 15th protruding tab 16 is about a joint 17th hinged at the axial end 11a of the plunger element 11 (see 2 ). Between the eccentric element 13th and the transmission ring 15th is a plain bearing arrangement 18th provided, which is preferably designed as a plastic plain bearing with a bearing element in a hollow cylindrical shape with an outer collar made of a suitable plastic or polymer material.

With the drive 5 becomes a ratchet assembly 19th operated with which the jaw 4th or a feed element designed as a slide element 20th of the drive 5 on which the cheek 4th is fixed, in the direction P1 relative to the remaining fixed part of the tool 1 is displaceably drivable. The feed element 20th is on a linear or sliding guide with preferably two spaced parallel guides Rail elements 21 and 22nd Slidably movably added.

The plunger element 11 is with a receiving element mounted so that it can be pivoted back and forth or rotated in the direction of R3 and R4 23 a second eccentric arrangement 24 on a radially outwardly protruding projection 23a of the receiving element 23 hinged connected. Eccentric on the receiving element 23 is an arm 25th the ratchet assembly 19th articulated. The arm 25th acts as a feed pawl for the feed element that can be driven in direction P1 20th educated.

Even with the second eccentric arrangement 24 is a plain bearing arrangement 26th for the swivel mounting of the receiving element 23 on the tool 1 or a section of the drive 5 intended. The plain bearing arrangement 26th is preferably designed as a plastic plain bearing with a bearing element in a hollow cylindrical shape made of a suitable plastic or polymer material. The receiving element is located in a hollow volume of the plastic bearing element 23 pivotally included.

During an outward movement of the plunger element 11 in the direction R1, which is due to the driving effect of the rotating shaft D with the eccentric 12th with half a revolution of the eccentric element 13th results, the receiving element 23 moved in direction R3, with a tooth contour 27 at a front end of the arm 25th automatically disengaged from an opposing tooth contour 28 that is on the outside of a straight side of the feed element 20th is trained (s. 2 ).

To block a movement of the feed element 20th in the direction of P2, especially when the arm 25th with its tooth contour 27 is disengaged from the opposing tooth contour 28 , is a latch 29 intended. The latch 29 is so coordinated hinged z. B. on a release lever 31 on a housing part of the tool 1 or the drive 5 is hinged that the latch 29 with a tooth contour formed on it 43 at its front end due to a spring action on the latch 29 with a pulling force acting spring 30th automatically into the opposing tooth contour 28 on the feed element 20th intervenes and blocks its movement in direction P2. The mainspring or spring 30th grabs the arm on the one hand 25th and on the other hand on the manually operated release lever 31 where the latch 29 is appropriate.

When pressing one into the 1 and 2 pipe section, not shown, in a pressing region V of the tool 1 between the cheeks 3 and 4th , during the short intermediate phases that occur during ratcheting without any drive effect on the feed element 20th so if the arm 25th no force for the driven sliding movement of the jaw 4th in the direction of P1 or from the opposing tooth contour 28 is lifted, the feed element remains 20th and with it the cheek 4th due to the force applied to the tooth contour 43 in the opposing tooth contour 28 gripping latch 29 stand.

As soon as the reciprocating movement of the plunger element 11 in direction R2 begins and the receiving element 23 is moved in direction R4, the arm tilts 25th in the direction of the feed element 20th or to the mating tooth contour 28 so that the tooth contour 27 automatically engages in force-transmitting engagement with the opposing tooth contour 28 . When moving the plunger element 11 in the direction of R2 and the receiving element 23 the arm brings in the direction of R4 25th the feed element 20th in a sliding movement in direction P1, so that in the pressing area V there is a distance between the jaw 3 and the cheek 4th and the pressing process takes place. At the same time, through the movement of the feed element 20th in direction P1, the tooth contour comes 43 on the latch 29 automatically evading against the spring action of the spring 30th out of engagement with the opposing tooth contour 28 on the feed element 20th , thus blocking the feed element 20th is canceled.

With the ram element reciprocating movement, the advancing element 20th or the cheek 4th according to a ratchet movement or in alternating driven movement phases and stationary phases successively moved in the direction P1 and the pipe section is pressed.

When the electric motor of the cordless screwdriver 2 switched off z. B. at the end of the pressing process, the release lever 31 operated manually by pressing against an operating section 31a on the release lever 31 . The one with the latch 29 connected pivoting release levers 31 serves to open the jaws 3 and 4th . The release lever 31 is done manually against the force of the spring 30th twisted or offset so that the latch 29 with the tooth contour 43 of the mating tooth contour 28 comes free and also comes into contact with the arm 25th this takes with it, so that its tooth contour 27 also from the opposing tooth contour 28 comes out or stands out from this. The feed element 20th with the cheek 4th becomes in direction P2 under the action of a tension spring 36 pushed back. As soon as no more on the release lever 31 acted or this is no longer pressed manually, causes the spring 30th that arm 25th again in the direction of the feed element 20th pivots towards and with the tooth contour 27 again in the opposing tooth contour 28 engages and the feed element 20th is being held. At the same time the arm pushes 25th by contact with the latch 29 this also to the feed element 20th so that the Tooth contour 43 in the opposing tooth contour 28 hooks or engages. So that the feed element 20th is moved to its mechanically limited starting position or a maximum of far in the direction P2, it is necessary that the release lever 31 remains actuated manually for as long. For this or for manual release and resetting, the operator must use the cordless screwdriver with one hand 2 and with the other hand on the release lever 31 act.

The web-like rail elements 21 and 22nd are designed identically and each have several guide surfaces at an angle to one another 32 , 33 and 34 a protruding web on the respective rail element 21 , 22nd on, which extends over the length of the rail element 21 respectively. 22nd extend.

Each web represents the three strip-shaped guide surfaces, for example 32-34 ready, with two adjacent guide surfaces aligned at right angles to each other. The feed element 20th has two matching deeper or channel-shaped sections 35 or z. B. two rectangular grooves with corresponding three guide surfaces. Both sections 35 are guided on the associated web and encompass the three guide surfaces 32-34 adjacent or the web on the respective rail element 21 , 22nd engages appropriately in the sections 35 or the groove on the feed element 20th a.

The embodiments of the tool 1 according to the 3 until 10 or according to the 11 until 18th differ from the embodiment of the tool 1 according to 1 and 2 by one about the cordless screwdriver 2 actuatable reset mechanism with a reset arrangement 37 according to the 3 until 10 or with a reset arrangement 38 according to the 11 until 18th .

For an advantageous ergonomic operation of the tool 1 are the reset arrangement 37 or the reset arrangement 38 intended. It is often when operating the tool 1 necessary to work stooped or kneeling, so that at the end of a work process or pressing to reset the feed element 20th a hand-operated action on the release lever 31 for releasing the locking of the ratchet assembly 19th including arm 25th and latch 29 can only be difficult or inconvenient. This is where the tools set 1 with the reset arrangement 37 respectively. 38 according to the 3 until 10 respectively. 11 until 18th at.

3 shows an end position of the tool 1 or the feed element 20th with the cheek 4th at the end of a pressing process, as is the case with the 1 and 2 demonstrate.

Accordingly, at the end of the machining process or the pressing process, the feed element at the end of the machining process 20th is in a corresponding end position according to the tool end position, the feed element 20th with the driving cordless screwdriver 2 a comparatively short or slight release distance a (see Sect. 3 ) from its with the latch 29 secured end position moved in direction P1. There is a stop surface 39 on the feed element 20th in pressing contact with a counter-stop surface 40 on the latch 29 . The contact of the tooth contour 43 the latch 29 with the opposing tooth contour 28 on the feed element 20th is thereby canceled (s. 3 , 5 ).

Thereby the latch 29 with the release lever 31 pivoted slightly in the direction of R5, so that the latch 29 with their tooth contour 43 comes out of engagement at or from the opposing tooth contour 28 on the feed element 20th . The tooth contour 43 and the mating tooth contour 28 are suitable for this purpose or designed to be matched to one another, so that tooth flanks of the tooth contour that touch one another slide along one another 43 on the one hand and the opposing tooth contour 28 on the other hand is possible. This is when the feed element is moving 20th possible in direction P1. A movement of the feed element 20th in the opposite direction P2 is with interlocking tooth contours 43 , 28 however blocked.

With progressive pivoting of the latch 29 a contact section pushes in the direction of R5 41 on the latch 29 (see 3 ) on one as a contact flank 42 trained section on the arm 25th (see 5 ). The arm 25th is thereby also slightly pivoted in the direction R6 relative to the receiving element 23 so that the arm 25th or its tooth contour 27 also disengaged from or with the opposing tooth contour 28 on the feed element 20th comes (s. 7th ).

With the lifting of the tooth contour 27 of the mating tooth contour 28 is the mating tooth contour 28 free or without engagement and the feed element 20th is under the action of the tensile force of the tensioned mainspring 36 in the direction P2 along the rail elements 21 , 22nd moved or moved back. At the end of the return movement of the feed element 20th when the tension spring is contracted or almost completely relaxed 36 according to 9 takes the tool 1 or the feed element with a limit stop 20th a starting position. This corresponds to the starting point of the feed element 20th for a processing or pressing process.

So that the latch 29 when pushing back the feed element 20th when the stop surface 39 on the feed element 20th away from the counter-stop surface 40 separates, does not pivot back again against the pivoting direction R5 or the Tooth contour 43 not back into the opposing tooth contour 28 can intervene and also the arm 25th does not pivot back or thus the tooth contour 27 not in the contours of the opposing teeth 28 can intervene is a safety mechanism 44 provided between a stationary component of the tool 1 and the release lever 31 works. The safety mechanism 44 is in particular with the sectional views according to FIG 4th , 6th , 8th and 10 evident.

The safety mechanism 44 , which can be set up automatically and can be manually released again in the set-up state, is designed so that when a predetermined pivot position of the release lever is reached 31 when pivoting with the latch 29 in direction R5 of the release lever 31 can no longer pivot back against the pivoting direction R5. In this way it is achieved that when moving back or when withdrawing the advancing element 20th in the direction of P2 or the latch 29 remains away and not with the tooth contour 43 in the opposing tooth contour 28 intervenes. Otherwise the feed element would 20th from the latch 29 are fixed and the feed element 20th could not get into the starting position.

The safety mechanism 44 comprises one on the stationary component of the tool 1 recorded and force-loaded securing element 45 , for example a locking or latching element such as a ball. The security element 45 is according to the directions P3 (s. 8th ) movably mounted in a receptacle 46 like a recess in which, for example, a helical compression spring to provide the force 48 sits and the locking element 45 pushes in a securing direction or in the direction of a securing contour 47 of the release lever 31 . The safety contour 47 preferably has a recess, for example a tapping.

The safety contour 47 is for an interaction with the securing element 45 appropriately designed so that the securing element 45 into the safety contour 47 can be placed in it or can be immersed therein and is kept in a shape-adapted manner. This takes place in a controlled manner under the application of force or under the action of the helical compression spring 48 so that the fuse element 45 in the safety contour 47 locked in place is in the secured state of the securing mechanism 44 . In the secured state of the safety mechanism 44 is the release lever 31 and with it the latch 29 in the pivot position pivoted in the direction R5 according to FIG 8th and 10 Fig. Secured against pivoting back against the pivoting direction R5.

For a subsequent working operation of the tool only has to be on the operating section 31a of the release lever 31 are acted, so that with little manual effort the release lever 31 is pivoted somewhat, with which the securing element 45 against the force of the helical compression spring 48 from the safety contour 47 is pushed out. The release lever then swivels 31 and with it the latch 29 and the arm 25th in the direction of the reset feed element 20th so that the tooth contours 43 and 27 in the opposing tooth contour 28 rest. The next pressing process can begin.

The tool 1 according to the 11-18 differs from the tool 1 according to the 3-10 solely through your safety mechanism 49 that differ from the security mechanism 44 differs.

Therefore, the following is a description of the 11-18 essentially the safety mechanism 49 described, in particular with the sectional views according to 12th , 14th , 16 and 18th .

The safety mechanism 49 is between a fixed component of the tool 1 and the release lever 31 effective.

The safety mechanism 49 is according to the safety mechanism 44 can be set up automatically and manually detached again when set up.

The safety mechanism 49 comprises one on the stationary component of the tool 1 recorded and force-loaded securing element 50 , for example a locking or latching element such as a locking pin. The security element 50 is movably mounted in a receptacle in the directions P3 51 like a sleeve which is open at the end and in which, for example, a helical compression spring to provide the force 53 sits and the locking element 50 pushes in a securing direction or in the direction of a securing contour 52 of the release lever 31 . The safety contour 52 preferably has one to adjacent outside areas of the release lever 31 deeper recess, for example with a stepped shoulder 57 with flanks aligned at right angles to one another.

By a transverse to the longitudinal direction of the fuse element 50 through opening in the locking element 50 a return element engages 55 for manual relocation of the safety element 50 towards P4 (see p. 18th ).

The safety contour 52 is for an interaction with the securing element 50 appropriately designed so that the securing element 50 into the safety contour 52 is displaceable or can be immersed in it and is held. This takes place in a controlled manner under the application of force or under the action of the helical compression spring 53 , so that the fuse element 50 in the safety contour 52 locked in place is in the secured state of the securing mechanism 49 .

Upon reaching a bevel 54 at one edge of the heel 57 at the transition of the safety contour 52 to the surrounding non-recessed area of the release lever 31 becomes the release lever 31 by means of the securing element 50 under the force of the helical compression spring 53 pushed or pivoted so that the latch 29 towards the arm 25th pushes and so disengages the tooth contour 27 on the arm 25th of the mating tooth contour 28 is supported automatically. The bevel 54 is preferably circumferential or closed circumferentially at the front end of the securing element 50 educated.

To cancel the safety status of the safety mechanism 49 is externally on the restoring member 55 Pulled in direction P4 and on the release lever 31 acted or against the operating section 31a pressed. The security element 50 comes from the safety contour 52 free.

the 19-22 illustrate a linear guide or a linear guide 58 a portion of the plunger element 11 in the tool 1 . This is done in two opposite housing plates 59 of the grouting tool 1 the linear guide 58 formed, in which the joint driver 60 formed portion of the plunger element 11 is linearly displaceable.

The joint driver 60 serves for the articulated connection of the first eccentric arrangement 12th with the receiving element 23 or the second eccentric arrangement thus provided 24 . Accordingly, the hinge driver forms 60 with sections of the linear guide 58 as props 9 .

The plunger element 11 or the joint driver 60 is in the the joint driver 60 surrounding linear guide 58 of the tool 1 linearly displaceable. The joint driver 60 is guided in the tool in a sliding manner or with a plain bearing 1 . The joint driver 60 is embedded in the linear guide 58 forming sections, the sections of the linear guide 58 inside the tool 1 or on the inside at opposite points on the housing plates 59 is trained. The linear guide preferably comprises 58 two matching guideways 61 each in a housing plate 59 , which are approximately rectangular or groove-shaped with a flat bottom and extend over a maximum or possible path of movement of the plunger element 11 or the joint driver 60 extend.

With the one in the linear guide 58 guided joint driver 60 forces and / or moments can be absorbed in the drive mode of the tool 1 . In particular, with the one in the leadership 58 displaceably guided joint driver 60 a torque support up to the tool-related side of the interface 7th provided or in particular via support means 9 transmit a counter-torque. The counter-torque is transmitted at the same time as the drive torque is transmitted.

The guideways 61 include areas in which the portion of the plunger element 11 or the joint driver 60 is received guided, with one side of the joint driver 60 a guide surface 62 the guideway 61 is facing.

The plunger element 11 is preferably in several parts. In the exemplary embodiment, the plunger element is 11 in two parts and includes the one on the flap 16 over a peg 63 articulated joint driver 60 , which is enlarged in single view in 21 is shown. Between the joint driver 60 and the receiving element 23 or the projection 23a of the receiving element 23 is a link 64 hinged (s. 22nd ). The connecting link 64 is about a tenon 65 with the joint driver 60 and about a tenon 66 with the projection designed as a tongue 23a connected (s. 22nd ). The cones 65 and 66 or their central longitudinal axes are aligned in parallel and provide parallel joint axes. The cone 63 or its central longitudinal axis between the transmission ring 15th or the tab 16 and the joint driver 60 stands perpendicular to the longitudinal or hinge axes of the pin 65 and 66 . This is with the plunger element 11 a multi-joint or a three-joint realized.

The joint driver 60 is therefore suitable for an articulated connection with two joint elements such as the two pins 63 and 65 that each have an associated pin receptacle 67 respectively. 68 of the joint driver 60 intervene (s. 21 ).

The journal mount 67 at the end 11a or a first end portion of the joint driver 60 includes two flat sections 67a and 67b each with a round hole, the round holes being aligned with one another with the same diameter, based on one of the pin receptacle 67 provided central receiving axis A1.

The journal mount 68 at a second end portion of the joint driver 60 includes two sleeve sections 68a and 68b each with a round hole, whereby the round holes with the same diameter are aligned with each other on one of the journal mounts 68 provided central mounting axis A2. The diameters of the cylinder bores are preferably the pin receptacle 67 identical to the diameters of the cylinder bores of the journal mount 68 .

The flat sections 67a , 67b are via a middle section with the sleeve sections 68a , 68b tied together.

Between the parallel aligned flat sections 67a and 67b a gap-like or slot-like material-free area is formed. Also between the sleeve sections 68a and 68b a gap-like or slot-like material-free area is formed. The slots are at right angles to each other.

The receiving axes A1 and A2 are accordingly over the length of the joint driver 60 spaced from each other and aligned perpendicular to each other. The joint driver 60 forms a compact double joint element with joint axes that are perpendicular to one another. The associated joint elements are preferably cylindrical pegs like the pegs 63 , 65 or hinge pins are provided, with a hinge element or the pin 63 through the two round bores of the pin holder 67 engages and another joint element or the pin 65 through the two round bores of the pin holder 68 engages.

The round hole in the flat section 67b is in 21 not visible or covered by the flat section 67a .

The plunger element 11 or at least its section that of the joint driver 60 is formed is in the the joint driver 60 surrounding linear guide 58 of the tool 1 linearly displaceable. The joint driver 60 is guided in the tool in a sliding manner or with a plain bearing 1 .

The linear guide preferably comprises 58 the two matching guideways 61 , which are approximately rectangular or groove-shaped with a flat bottom and extend over a maximum or possible path of movement of the plunger element 11 or the joint driver 60 extend.

With the one in the lead 58 guided joint driver 60 forces and / or moments can be absorbed in the drive mode of the tool 1 . In particular, with the one in the leadership 58 displaceably guided joint driver 60 a torque support up to the side 6th the interface 7th provided or, in particular, a counter-torque to the drive torque transmitted by the rotary shaft D is transmitted via support means.

When guiding the moving joint driver 60 come flat sides or opposite outer sides 69 and 70 and other opposite sides 71 and 72 of the joint driver 60 in contact with guide surfaces 73 until 75 the guide surface 62 the guideway 61 on the housing plate 59 or in contact with guide surfaces of a guide track on the further opposite housing plate 59 (see 1 ).

On the roughly cuboid joint driver 60 are the outsides 69 and 70 parallel to each other and facing each other and the outsides 71 and 72 also parallel to one another and opposite one another or the outsides 69 and 70 are each at right angles to the outside 71 and 72 .

At the guideway 61 forms the guide surface 73 a bottom surface and the guide surfaces 74 , 75 Edge surfaces protruding at right angles to the side of the floor surface (s. 20th ).

Another guideway is accordingly 61 in the other housing plate 59 designed.

While the tool is in operation 1 slides the outside 70 adjacent to the guide surface 73 the guideway 61 and a portion of the outside 72 slides close to the guide surface 74 the guideway 61 and a further guide surface of the other guide track in the other housing plate 59 .

A section of the outside 71 slides close to the guide surface 75 the guideway 61 and on a further guide surface of the other guide track.

The outside 69 slides adjacent to a floor guide surface of the other guide track.

This provides a clean surface or sliding guide with support means for transmitting the counter-torque.

The receiving element 23 is cylindrical or circular disk-shaped in its basic shape. The plain bearing arrangement 26th accordingly comprises a receptacle 76 for the storage of the receiving element 23 . The recording 76 has two matching recesses 77 and 78 on that at opposite points of the housing plates 59 and the other housing plate 59 are trained. The aligned depressions 77 and 78 are preferably formed by a material recess with a residual base thickness in the respective housing plate. the cylindrical or round recesses 77 and 78 are blind hole-like and have a slightly larger diameter D1 than the outer diameter D2 of a respective one in the depressions 77 and 78 engaging opposite on the receiving element 23 existing warehouse section 23b and 23c of the receiving element 23 .

Between the cylindrical outside of the bearing section 23b and the inner wall of the recess 78 is an annular plastic bearing ring 80 or a plastic bearing sleeve of the plain bearing arrangement 26th suitable available. The plastic bearing ring 80 with a material or ring thickness corresponding to the difference between D1 and D2 consists, for example, of a suitable polymer plastic material with comparatively good sliding bearing properties or with comparatively high friction-reducing or lubricating properties.

Correspondingly, there is between the cylindrical outside of the bearing section 23c and the inner wall of the recess 77 an annular plastic bearing ring 79 or a plastic bearing sleeve of the plain bearing arrangement 26th suitable available. The plastic bearing ring 79 consists, for example, of a suitable polymer plastic material with comparatively good sliding bearing properties or with comparatively high friction-reducing or lubricating properties. In 22nd is the plastic bearing ring 80 only hinted at.

23 shows a tool 1 , which is designed as an expanding tool for expanding a pipe section R of a pipe. The pipe section R, which is attached or attached to the expansion tool and at the end of the pipe, is in the 23 , 24 only indicated by dashed lines.

The basic structure of the expansion tool corresponds to the tool 1 according to the 1-22 built up, taking in place of the jaws 3 , 4th a detachable expansion attachment 81 is available.

The expansion attachment 81 comprises two in the direction of movement of the feed element 20th or different outer sections formed one behind the other in the direction P1 82 and 83 . The outer section 82 has a larger, preferably cylindrical, outer diameter here than the likewise outer cylindrical outer diameter of the outer section located at the free end or the front outer section 83 .

The hollow plugged-on pipe section R is based on FIG 23 , 24 of its unmachined, continuously identical cylindrical shape with the expanding tool in its end section with the aid of the outer section 82 widened.

Both outer sections 82 and 83 are slotted like lamellae in the longitudinal direction parallel to the direction P1 and each have several, preferably six, such widening sections 82a respectively. 83a .

In principle, three, four, five or more than six widening sections can also be formed.

Inside the hollow expansion sections 82a respectively. 83a is a linear with the feed element 20th Movement-coupled or drivable expanding mandrel 84 present, the one of a broad base opposite to a point 85 of the expanding mandrel is, on the outside, conical or otherwise shaped expanding in the direction of the tip 85 of the expanding mandrel 84 .

The six circumferentially adjacent expansion sections 82a are designed in this way or with one another and with the expanding mandrel 84 coupled or cooperating in such a way that when the expanding mandrel moves 84 in the direction P1 the six expansion sections located in a basic position 82a according to 23 , 24 preferably move together in the same way and simultaneously or outwards in the direction P5 and push the deformable pipe section R outwards and plastically deform it by pressing it against a cylindrical inner wall of the pipe section R. This is shown in FIG 24 indicated.

When the feed element moves back 20th and thus the expanding mandrel 84 in direction P2, the widening sections also move 82a contrary to the direction P5 back into the according to the 23 , 24 shown basic or. Starting position.

According to the expansion of the pipe section R, a pipe section of a thinner pipe (not shown) with a smaller outer diameter than the pipe section R or with an inner diameter in the range of the outer diameter of the outer section 83 to edit. For this purpose, with the expanding mandrel retracted in direction P2 84 , the thinner tube or the end region of the tube section on the front outer section 83 attached and then by moving the expanding mandrel 84 in the direction P1, a frontal section-wise enlargement of the diameter of the pipe section is achieved.

List of reference symbols

1

tool

2

Cordless screwdriver

3, 4

jaw

5

drive

6th

page

7th

interface

8th

Opposite side

9

Props

10

Transmission unit

11

Plunger element

11a

end

12th

Eccentric arrangement

13th

Eccentric element

14th

Pen

15th

Transmission ring

16

Tab

17th

joint

18th

Plain bearing arrangement

19th

Ratchet assembly

20th

Feed element

21-22

Rail element

23

Receiving element

23a

head Start

23b

Warehouse section

23c

Warehouse section

24

Eccentric arrangement

25th

poor

26th

Plain bearing arrangement

27

Tooth contour

28

Opposing tooth contour

29

Latch

30th

feather

31

Release lever

31a

Operating section

32-34

Guide surface

35

section

36

Tension spring

37

Reset arrangement

38

Reset arrangement

39

Stop surface

40

Counter stop surface

41

Contact section

42

Contact edge

43

Tooth contour

44

Safety mechanism

45

Fuse element

46

recording

47

Safety contour

48

Coil compression spring

49

Safety mechanism

50

Fuse element

51

recording

52

Safety contour

53

Coil compression spring

54

chamfer

55

Return device

56

Control element

57

unit volume

58

Linear guide

59

Housing plate

60

Joint driver

61

Guideway

62

Guide surface

63

Cones

64

Connecting link

65

Cones

66

Cones

67

Spigot mount

67a

Flat section

67b

Flat section

68

Spigot mount

68a

Sleeve section

68b

Sleeve section

69-72

Outside

73

Guide surface

74

Guide surface

75

Guide surface

76

recording

77

deepening

78

deepening

79

Plastic bearing ring

80

Plastic bearing ring

81

Expansion attachment

82

Outer section

82a

Expansion section

83

Outer section

83a

Expansion section

84

Expanding mandrel

85

top

Claims (20)

Tool (1) for pressing and / or expanding a pipe section for a pressing process and / or expanding process on a pipe, the tool (1) comprising two jaws (3, 4) which are used for a pressing process and / or expanding process with a drive (5) of the tool (1) can be driven relative to one another, characterized in that the drive (5) has a side (6) of a mechanical interface (7) to a drill and / or to a screwdriver (2), the The drilling machine and / or the screwdriver (2) has an opposite side (8) that matches the side (6) of the mechanical interface (7) ) is connected, the interface (7) is able to simultaneously transmit a counter-torque to a drive torque via support means (9) and wherein a driven, movable feed element (20) of the tool (1) can be moved back and forth along a sliding guide linearly r is guided, wherein the feed element (20) is coupled in terms of movement to a jaw (4). Tool after Claim 1 , characterized in that the sliding guide comprises a rail element (21, 22), the advancing element (20) being received on the rail element (21, 22) so as to be displaceable. Tool after Claim 1 or Claim 2 , characterized in that the rail element (21, 22) has several guide surfaces (32-34) at an angle to one another, the guide surfaces (32-34) extending over a length of the rail element (21, 22). Tool according to one of the preceding claims, characterized in that the sliding guide comprises two spaced apart rail elements (21, 22) which are aligned parallel to one another and wherein the feed element (20) is slidably received on the two rail elements (21, 22). Tool according to one of the preceding claims, characterized in that the drive (5) has a transmission unit (10), the transmission unit (10) being designed to pick up a rotary movement of a rotary shaft of the drill or the screwdriver (2) and to convert it into a linear movement To transfer the plunger element (11) of the drive (5) of the tool (1). Tool according to one of the preceding claims, characterized in that the transmission unit (10) comprises an eccentric arrangement (12) with a rotatable eccentric element (13), the eccentric arrangement (12) being designed to convert a rotary movement of the eccentric element (13) into a linear movement of the To transfer the plunger element (11). Tool according to one of the preceding claims, characterized in that the drive (5) acts on a ratchet arrangement (19) with which the feed element (20) can be driven. Tool according to one of the preceding claims, characterized in that the ram element (11) can be moved linearly back and forth when the eccentric element (13) rotates through 360 degrees around an axis of rotation of the eccentric element (13). Tool according to one of the preceding claims, characterized in that an axial end of the ram element (11) is coupled to the eccentric arrangement (12, 24). Tool according to one of the preceding claims, characterized in that the plunger element (11) is connected to a rotatably mounted receiving element (23), an arm (25) of the ratchet arrangement (19) being received on the receiving element (23). Tool according to one of the preceding claims, characterized in that the eccentric element (13) and a transmission ring (15) of the tool (1) are connected to one another via a slide bearing arrangement (18). Tool according to one of the preceding claims, characterized in that the transmission ring (15) has a protruding tab (16) which is connected to the plunger element (11). Tool according to one of the preceding claims, characterized in that the ram element (11) can be driven by an eccentric element arranged laterally to the longitudinal axis of the ram element (11), with a driver movable by the movement of the eccentric element. Tool according to one of the preceding claims, characterized in that the driver is designed as a U-profile. Tool according to one of the preceding claims, characterized in that the feed element (20) has a counter-tooth contour (28) in which a matching tooth contour (27) engages, which is present on an arm (25) of the ratchet arrangement (19). Tool according to one of the preceding claims, characterized in that a reset arrangement (37, 38) is provided which is designed to reset the feed element (20) from an end position to a starting position after a machining operation carried out with the tool (1), wherein the return of the feed element (20) can be triggered solely by actuating an operating element (56) of the drill or the screwdriver (2) and takes place automatically after triggering by the return arrangement (37, 38). Tool according to one of the preceding claims, characterized in that a safety mechanism (44, 49) acting on a pivotable detent pawl (29) of the tool (1) is provided, with which when the detent pawl (29) reaches a predetermined pivot position when the detent pawl is pivoted 29 in a first pivoting direction of the latching pawl (29), the latching pawl (29) is held in a pivoting position from which the latching pawl (29) cannot be pivoted back against the first pivoting direction of the latching pawl (29). Tool according to one of the preceding claims, characterized in that the receiving element (23) is rotatably mounted with a sliding bearing arrangement (26) in a recessed seat (76) of the tool (1). Tool according to one of the preceding claims, characterized in that a section (60) of the plunger element (11) is guided so as to be linearly displaceable in a linear guide (58) of the tool (1). Tool according to one of the preceding claims, characterized in that the linear guide (58) comprises a guide track (61) in which the section (60) of the plunger element (11) is received in a guided manner, one side (69-71) of the section ( 60) facing a guide surface (73-75) of the guide track (61).

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