WO2020069696A1 - Handheld tool for deforming and/or separating plastic or metal workpieces, in particular plastic or metal pipes - Google Patents

Abstract

The invention relates to a handheld tool (100; 200) for reshaping and/or separating plastic or metal workpieces, in particular plastic or metal pipes, comprising a working head (30), an electromechanical drive (10) for actuating the working head (30), and a support (40) which supports the electromechanical drive (10) and/or the working head (30). The electromechanical drive (10) comprises an electric motor (11) with an output shaft (11.1), at least one reduction stage (12) downstream of the electric motor (11), a mechanical converter (13), and an actuation element (14). The actuation element (14) is designed to be moved in a translational manner in the direction of a movement axis (15) in order to actuate the working head (30). The electric motor (11) is designed to rotate the output shaft (11.1) about a drive axis (16) in order to drive the actuation element (14). The mechanical converter (13) is designed to convert a rotational drive movement emanating from the output shaft (11.1) into a translational drive movement for driving the actuation element (14). The at least one reduction stage (12) comprises an epicyclic gearing system (17) with a central rotational axis (18) which is coaxial with the movement axis (15) and/or the drive axis (16).

Description

 Hand tool for forming and / or separating processing of plastic or metal workpieces, in particular

 Plastic or metal pipes

The invention relates to a hand tool for shaping and / or separating processing of plastic or

Metal workpieces, in particular plastic or metal pipes, with a working head and an electromechanical drive for actuating the working head.

Such hand tools are usually mobile

used and can be held in the hand of a user. The hand tools are used, among other things, in the heating and / or sanitary area and are used, for example, to process pipes. For this purpose, the hand tools have a working head which, depending on the type, enables, for example, radial pressing of a pipe connection, widening of a pipe end or cutting a pipe to length. In order to carry out these activities, is the one under consideration here

Hand tools usually have an electric drive

provided which drives the working head.

The electric drive comprises an electric motor and usually additionally a hydraulic unit, which actuates the actuator via a translatory movement

Working head drives and even from the electric motor

is driven. In this way, such a large actuating force can be provided that the working head has sufficient manpower to machine the workpieces as desired. However, the hydraulic unit adds weight to the entire hand tool, which makes operation more difficult, for example when the hand tool is used in overhead positions.

A technical concept without a hydraulic unit is known from EP 0 860 220 A2. Inside is a hand tool

described, which is used for pressing pipe connections. The hand tool has an electric drive with an electric motor, which drives a screw jack. The screw jack converts a rotary drive movement generated by the electric motor into a translatory drive movement, which is used to actuate the working head. To be big enough

Applying actuating force for the working head, a spur gear is additionally provided, which the

Electric motor is connected downstream and a reduction in the speed of the electric motor in favor of a higher

Torque causes.

The spur gear is designed in two stages and has an intermediate shaft which is offset from the output shaft of the electric motor and which is rotatably mounted in two separate bearings. Due to the spur gear, especially the axially offset intermediate shaft, the electric drive is relatively spatial, which means that the

Hand tool is difficult, for example, in narrow and / or poorly accessible work areas.

An object of the invention is to provide at least one alternative embodiment for a hand tool to propose the type mentioned. In particular, that should

Hand tool in terms of size and / or

Weight be optimized.

The object is achieved with a hand tool, which has the features of claim 1. The task is also solved with a hand tool, which the characteristics of

Claim 5 has. In addition, a use with the features of claim 18 and a use with the features of claim 19 are proposed to achieve the object. Advantageous embodiments and / or

Refinements and / or aspects result from the

Subclaims, the following description and the

Characters .

A basic hand tool for shaping and / or separating machining of plastic or metal workpieces, in particular plastic or metal pipes, includes one

Working head, an electromechanical drive for actuating the working head and preferably a carrier carrying the electromechanical drive and / or the working head. Of the

Electromechanical drive comprises an electric motor with an output shaft, at least one of the electric motor

downstream reduction stage, a mechanical converter and an actuator. The actuator is

set up to be moved translationally in the direction of a movement axis in order to actuate the working head. Of the

Electric motor is set up to drive the

Actuating element to rotate the output shaft about a drive axis. Furthermore, the mechanical converter is set up, one starting from the output shaft

rotary drive movement in a translational Convert drive motion to drive the actuator.

In particular, the at least one reduction stage is connected directly and / or directly downstream of the electric motor.

In particular, the mechanical converter is connected directly and / or directly after the at least one reduction stage. In particular, the actuating element is the mechanical one

Transducers immediately and / or directly downstream and / or part of the mechanical converter. The above information “connected downstream” relates to the sequence which relates to the power flow emanating from the electric motor

Electromechanical drive around a purely electromechanical drive, which is therefore free of a hydraulic unit and / or a pneumatic unit, which affects the whole

Hand tool has a favorable weight.

In one embodiment, it is provided that the at least one reduction stage comprises an epicyclic gear. In particular, it is provided that the

Orbital gear has a central axis of rotation, which is coaxial with the axis of movement and / or the drive axis. For example, the epicyclic gear mechanism is arranged coaxially with the movement axis and / or the drive axis. The selection of the epicyclic gear is on

Gearbox used, which takes up a relatively small volume and thus favors a compact design of the hand tool. The possible is also aimed in this direction

Measure that the central axis of the epicyclic gearbox is coaxial with the movement axis and / or the drive axis, that is, an axis offset is avoided. At the same time allows the epicyclic gearbox a relatively large reduction in the speed of the electric motor and a

Transmission of relatively high torques. By using the epicyclic gear as a reduction step, the achievement of such a large workforce of the working head is favored in order to process workpieces as desired.

Under the name "hand tool" is in the

present description in particular a tool

understand which is mobile, for example can be carried and / or driven by hand, and / or can be guided by hand, for example, during a machining process of a workpiece. The machining of the workpiece itself, which of the

Working head of the tool is carried out, however, takes place at least partially or completely by actuation via the electromechanical drive. To this extent, the invention also includes semi-stationary tools. In the present description, the term “tool” is to be understood in particular to mean that the tool for machining a

Workpiece serves. The processing can be a forming process, for example pressing a pipe connection or expanding a pipe or pipe end. Editing can also be a

separating processing, in particular cutting without cutting

Processing, such as shearing or cutting a workpiece, such as a pipe, act.

In order to achieve the required actuating force for actuating the working head, so that the working head performs the desired shaping or separating machining of the

If the workpiece is executed correctly, the electromechanical drive must be dimensioned accordingly. It has emphasized that the at least one reduction stage, in particular the planetary gear, should have a reduction value between approximately 1: 8 and approximately 1: 400. It has proven advantageous that the at least one

Reduction stage, in particular the epicyclic gear, should have a reduction value between about 1: 8 and about 1:85, if, for example, metallic workpieces

are edit. It has also proven advantageous

emphasized that the at least one reduction stage, in particular the planetary gear, should have a reduction value between approximately 1: 180 and approximately 1: 400, if

For example, workpieces containing plastic are to be processed. Furthermore, it has been found that the for

The electric motor used has a nominal torque between approximately 0.1 Nm and 1 Nm, in particular approximately 1.0 Nm and one

Nominal speed should be between about 9,000 rpm and about 24,000 rpm.

If the hand tool for the forming and / or separating processing of metal workpieces, such as for

If metal pipes, in particular copper, steel or stainless steel pipes or multi-layer composite pipes are to be pressed, a possible design of the hand tool can be provided such that the electric motor has a nominal torque between 0.1 Nm and 1.0 Nm and a nominal speed between 9,000 Rpm and 20,000 rpm. It can also be provided that the electric motor has a nominal torque between between 0.2 Nm and 0.8 Nm and a nominal speed between 10,000 1 / min and 14,000 1 / min. In addition, it can be provided that the planetary gear transmission

Has a reduction ratio between 1: 8 and 1:85, in particular between 1:20 and 1:60, in particular between 1:25 and 1:40. As a result, a maximum actuating force for actuating the working head, in particular in the direction of the

Axial force between 30 kN and 40 kN, for example about 34 kN to 35 kN, acting on the axis of movement.

If the hand tool is to be used for the shaping and / or separating processing of plastic workpieces, such as, for example, for expanding plastic pipes, in particular pipes made of plastics of class PE-X or XLPE, a possible design of the hand tool can be made in this way

It is provided that the electric motor has a nominal torque between 0.1 Nm and 0.4 Nm and a nominal speed between 11,000 1 / min and 24,000 1 / min. It can also be provided that the electric motor has a nominal torque between 0.15 Nm and 2.5 Nm and a nominal speed between 15,000 rpm and 20,000 rpm. In addition, it can be provided that the

Epicyclic gearbox has a reduction ratio between 1: 180 and 1: 400, in particular between 1: 220 and 1: 340, in particular between 1: 260 and 1: 310. This means that a maximum actuating force for actuating the working head, in particular a maximum actuating force acting in the direction of the axis of movement

Axial force between 5 kN and 15 kN, for example about 9 kN to 10 kN, can be applied.

According to one embodiment, the epicyclic gear set is constructed at least in one stage. For example, that is

Orbital gearboxes are two-stage or three-stage or four-stage. As a result, it is advantageous to achieve or achieve the desired high reduction ratio. Because in this case the reduction is made up as a total reduction from the individual reductions of the individual levels. One possible embodiment is that the epicyclic gear is or comprises a planetary gear. For example, the planetary gear has a sun gear, at least one planet gear, one of which is at least one

Planet gear carrier and in particular a ring gear. For example, there are at least one

Planet gear and the sun gear received in the ring gear, the at least one planet gear meshing with the ring gear and the sun gear. For example, the sun gear is connected to the central axis of rotation in a rotationally fixed manner or is integrally formed thereon. For example, the planetary gear is for one

Two-shaft operation interconnected. For this purpose, the planet gear carrier or the ring gear can be fixed to the housing and, accordingly, either the ring gear or the planet gear carrier with the

Input of the mechanical converter or be connected in a rotationally fixed manner to the output shaft of the electric motor. Depending on

The sun gear can then be connected to the output shaft of the electric motor or the input of the mechanical converter in a rotationally fixed manner. Basically, instead of a planetary gear, another epicyclic gear, such as a tension shaft gear, which is also referred to as a harmony drive gear, can be used.

In addition to the planetary gear, at least one further reduction stage can be provided. After a

Embodiment can be provided that a further

Reduction stage by the mechanical converter

is provided, for example the mechanical converter performs a reduction function. The reduction function can be implied by the type of mechanical transducer or be provided by a device associated with the mechanical transducer.

Instead of the one epicyclic gear it is provided according to another embodiment that the mechanical

Converter performs a reduction function, which the

Reduction level forms and is provided as the only reduction level. This measure can also

Weight advantages and advantages in the size of the hand tool can be achieved because a separate

Reduction level, such as that described above

Epicyclic gearbox is saved and instead the

necessary reduction is provided by the reduction function of the mechanical converter.

According to one embodiment, it is provided that the mechanical converter comprises a cam mechanism or is formed by a cam mechanism. In particular that is

Cam gear set up, in a rotary operation of the electric motor, in which the output shaft rotates, for example, in a direction of rotation, to use the translational drive movement for a deployment movement of the actuating element from a starting position to an extended position. In particular, the cam mechanism is also set up in which

Rotating operation of the electric motor to allow a return movement of the actuating element.

Under the name "cam gear" is in the

the present description in particular to understand a mechanism which converts a uniform input movement into a translatory back and forth movement as an output movement or a uniform input movement into a converts translatory output movement, which comprises a back-and-forth movement, the back-and-forth movement being actively effected by the mechanism and the back and forth movement being actively effected by the mechanism or passively at least permitted by the mechanism. In the present description, the translatory back-and-forth movement is also to be understood in particular as a back-and-forth movement.

According to one embodiment, the cam mechanism uses a cam carrier, which is one on a cam track

Has gear axis extending guide surface for a tap. The tap element is in particular set up to be moved along the cam track on the guide surface relative to the cam carrier. In order to enable a compact construction of the cam mechanism, it is provided in particular that the guide surface is arranged transversely to the gear axis, for example essentially orthogonally or orthogonally to the gear axis. This favors the curve holder and the tap

arrange axially aligned axes and

in particular to provide the input and the output of the cam mechanism opposite one another. In this respect, a measure has been taken to ensure a compact structure of the

electromechanical drive, for example, in radial

To reach direction with respect to the gear axis.

The associated tap element can have a contact finger or a contact element or a transmission element for scanning the curved path of the cam carrier, in particular for

preferably continuous contact with the guide surface, the contact finger or the transmission element on a base body extending along the gear axis is arranged. Such a design of the tap member allows a simple scanning of the guide surface of the cam carrier along the curved path when the

Guide surface has the orientation described above, namely is transverse to the gear axis. For this purpose, it makes sense that the contact finger comprises a contact surface which is arranged corresponding to the guide surface transversely to the gear axis, in particular is provided essentially orthogonally or orthogonally to the gear axis.

According to another embodiment, it is provided that the mechanical converter is a lifting gear, in particular a

Lift spindle gear comprises or is formed thereby. Such a lifting spindle gear can be a planetary roller screw drive, which is also referred to below as a planetary roller screw drive. In particular, the

 Planetary roller screw drive a threaded spindle, at least one, a planetary roller having a thread and a spindle nut. In particular, seen in the radial direction, the at least one planetary roller between the threaded spindle and the

Threaded nut arranged and lies with both

Threaded spindle as well as with the threaded nut in

Thread engagement before. For example, the threaded spindle and the spindle nut are arranged coaxially with respect to the central axis of the mechanical transducer, the threaded spindle being, for example, concentrically surrounded by the threaded nut.

In particular, it is provided that the threaded spindle of the lifting spindle gear, in particular the threaded spindle of the

Planetary roller screw gear, a thread pitch between about 0.5 mm and about 4.5 mm, in particular between 1 mm and 4 mm, in particular between 1.5 mm and 3.5 mm, for example about 2 mm, such as 1.9 mm or 2.0 mm or 2.1 mm or 2.2 mm. In particular, a thread pitch between 0.6 mm and 2.8 mm has proven to be advantageous. Due to the thread pitch of the threaded spindle, the

mechanical converter itself a reduction function. The aforementioned values for the thread pitch relate to those embodiments of the hand tool which have the at least one reduction step described above.

If there is no such reduction level and the reduction is only possible through a

 Reduction function of the mechanical converter, in particular the lifting gear described above is provided, has the threaded spindle of the lifting spindle gear, in particular the threaded spindle of the planetary roller screw gear,

for example a thread pitch between approximately 0.2 mm and approximately 1.0 mm, in particular between 0.2 mm and 1.0 mm.

In one configuration, the threaded nut is connected in a rotationally fixed manner to an output shaft of the at least one reduction stage or directly to the output shaft of the electric motor. In this case, the threaded spindle exercises

translatory drive movement or the drive force acting in the direction of the movement axis against the working head in order to actuate or drive the working head. The threaded spindle can be secured against rotation by an anti-rotation device, so that the threaded spindle only acts in a translatory manner.

The electric motor can be a direct current motor.

For example, according to one embodiment, that the electric motor is a brushed and in particular permanently excited DC motor. As a result, a measure is taken to optimize the costs for the hand tool, since such a direct current motor is relative

is offered inexpensively. Alternatively, it can be provided that the electric motor is a brushless DC motor. As a result, a measure is taken to optimize the service life for the hand tool, as such

DC motor due to missing contact brushes or

Carbon brushes are less sensitive to wear. The electric motor can have a nominal voltage of 18 volts or 12 volts.

According to one embodiment, it is provided that the hand tool is a wireless device. In the present description, “wireless” means that the

Hand tool without a dedicated electrical

Power cable and / or power cord gets along. The

Hand tools can therefore be operated without being connected to the electrical power grid, so it is a

Power tool independent operation possible.

For example, the hand tool is designed for battery operation and / or for battery operation.

One possible configuration is that the

Hand tool at least one electrical energy storage or accumulator for electrical power supply to the

Has electric motor or at least one receptacle,

in particular has a housing and / or an electrical connection for an accumulator. The accumulator can be rechargeable, that is, the above

Provide described battery operation. If the Accumulator does not provide recharging, the battery operation described above is thereby provided.

For example, the rechargeable battery is exchangeably mounted on the hand tool, in particular on the carrier, with electrical contact with the electric motor, or

attached. Basically, the accumulator in the

Hand tools must also be permanently installed. Basically, the hand tool can also include a power supply. That’s it

Hand tools to a power grid, especially public ones

Power grid, preferably connectable directly.

According to one embodiment, the electric motor is permanently installed in the hand tool. Alternatively, it can be provided that the electric motor is part of a separate one

Drive device is and for example via a

mechanical coupling is detachably connected to the hand tool and / or is detachably operatively connected or drive-connected. This favors the use of an external device as the drive for the hand tool. Such an external

The device can be a cordless screwdriver, a drill or the like, for example with a dismantled working head, in particular a drill chuck. In principle, the

Working head of the external device, such as the drill chuck can be used as a clutch or part of the clutch. So in this embodiment that is

Hand tool on an add-on unit or adapter unit

reduced, which uses the external device as a drive.

In particular, it is provided that the

Epicyclic gearbox a component of the add-on unit or

Adapter unit. In practical tests with commercially available Cordless screwdrivers or other battery-operated handheld devices have been found to be sufficient if that

Planetary gearbox has a reduction ratio between about 1: 1.5 and about 1:12. Already with one

Reduction can be a maximum actuating force for actuating the working head, especially one in the direction of

Maximum axial force between 5 kN and 15 kN, in particular about 9 kN to 10 kN, acting on the axis of movement can be applied, for example in order to process and / or cut plastic workpieces. This is particularly due to that

to be attributed to the fact that the commercially available cordless screwdrivers or other battery-operated handheld devices usually have at least their own reduction stage.

For the hand tool, for example, a housing is provided which at least partially houses at least the electromechanical drive and / or the working head. The housing can be assigned to the carrier or be formed on the carrier or be formed by the carrier.

For example, it is provided that the carrier and / or the housing has a grip surface, for example on a handle. The handle can be a pistol grip or a T-grip.

Depending on the design of the working head, the hand tool can carry out different machining operations on a workpiece. For example, the working head on the hand tool

Replaceably attached, is thus designed as an interchangeable head, which can be screwed onto the hand tool or a housing of the hand tool or the carrier, for example. In one possible version, the working head is as

Expander head designed to expand pipes serves or is usable. The hand tool then forms

Expanding tool.

In an alternative embodiment, the working head is designed as a press head which is used or can be used for the radial and / or axial pressing of pipe connections. In this case, the hand tool forms a pressing tool.

In particular, the one equipped with the press head

Hand tool an electrical and / or mechanical control to control the electric motor, for example to control the electric motor to perform a reversal of the direction of rotation. For example, the actuating element can be moved back after a pressing operation by moving the electric motor in the opposite direction of rotation

Direction of rotation when pressing and in this way the opening of the press head is supported or carried out.

In the case of yet another alternative version, the

The working head is designed as a cutting head, which is used or can be used, for example, to cut a workpiece, in particular a pipe, to a predetermined size. In this case, the hand tool forms a separating tool. In another alternative embodiment, the working head is designed as a butt bending head, which is used or can be used for butt bending a workpiece, in particular a tube.

One aspect of the invention relates to the use of a planetary roller screw drive for converting a rotary drive movement into a translatory drive movement in a hand tool for reshaping and / or separating

Processing of plastic or metal workpieces, in particular plastic or metal pipes, in particular in a pressing tool for pressing pipe connections. The hand tool can be the hand tool described above.

Another aspect of the invention relates to the use of a cam mechanism for converting a rotary one

Drive movement in a translatory drive movement in a hand tool for reshaping and / or separating

Processing of plastic or metal workpieces,

especially tubular plastic or metal tubes

Workpieces, especially for an expander tool

Expanding pipes. The hand tool can be the hand tool described above. In particular, the cam mechanism uses a cam carrier which runs on a cam track around a gear axis

Has guide surface for a tap and the

Guide surface is arranged transversely to the gear axis.

Further details and features of the invention emerge from the following description of several

Exemplary embodiments with reference to the drawings. Show it:

Fig. 1 shows a possible embodiment of a hand tool for shaping processing of tubular

 Workpieces in perspective,

Fig. 2 shows the hand tool of Figure 1 in a

 Sectional view,

Fig. 3 shows another possible embodiment of a

Hand tool for shaping machining tubular workpieces in perspective

 Presentation,

Fig. 4 shows a possible embodiment of a

 electromechanical drive, which in the

 3 is used, in a perspective sectional view,

5 shows a possible embodiment of a cam carrier, which is a component of a cam mechanism of the electromechanical drive of FIG. 4, in a perspective view,

Fig. 6 shows the course of a curved path of the curve carrier

 Figure 5 using a representation of the rolled cam track and

7 the electromotive drive of FIG. 2,

 installed in the expansion device of Figure 3 in a sectional view.

FIGS. 1 and 2 show a possible embodiment of a hand tool 100 for the shaping machining of tubular workpieces. The hand tool 100 includes one

electromechanical drive 10 and a working head 30, the electromechanical drive 10 for actuating the

Working head 30 is used. The hand tool 100 further includes the electromechanical drive 10 and / or the

Working head 30 carrying carrier 40.

The hand-held tool 100 is the electromechanical drive

10 designed so that a sufficient operating force to Actuation of the working head 30 is provided without the need to use auxiliary units, such as hydraulic units and / or pneumatic units. Of the

For this purpose, electromechanical drive 10 comprises an electric motor 11 with an output shaft 11.1, at least one of which

Electric motor 11 downstream reduction stage 12, a mechanical converter 13 and an actuating element 14. The actuating element 14 is designed to be moved translationally in the direction of a movement axis 15 in order to actuate the working head 30. The electric motor 11 is

set up to drive the actuating element 14 to rotate the output shaft 11.1 about a drive axis 16. The mechanical converter 13 is set up, a rotary one starting from the output shaft 11.1

 Convert drive movement into a translational drive movement for driving the actuating element 14. In this respect, the electric motor 11 acts via the at least one

Reduction stage 12 and the mechanical converter 13 and the actuating element 14 preferably directly on the

Working head 30.

In order to convert the speed of the electric motor 11 in a compact manner in favor of a higher torque, the at least one reduction stage 12 is by

Orbital gear 17 formed or includes one

Epicyclic gear 17. The epicyclic gear 17 is

for example, constructed at least in two stages and can be a planetary gear. This is preferred

Orbital gear 17 with its central axis of rotation 18 arranged coaxially to the axis of movement 15 and / or the drive axis 16. The mechanical converter 13 is also preferably coaxial with the movement axis 15 and / or the drive axis 16 arranged. In particular, the mechanical converter 13 is arranged with a central axis 19 coaxial with the movement axis 15 and / or the drive axis 16.

The mechanical converter 13 is preferred as

Planetary roller screw drive 22 formed or includes such a planetary roller screw drive 22. Preferably, the planetary roller screw drive 22 comprises a threaded spindle 24, at least one threaded planetary roller 25 or 25 'and a spindle nut 26. The threaded spindle 24 preferably has a thread pitch between 1 mm and 4 mm. For example, the threaded spindle 24 and the spindle nut 26 are arranged coaxially with respect to the central axis 19 of the mechanical converter 13. Between the threaded spindle 24 and the

Spindle nut 26 is arranged the at least one thread roll 25 or 25 ', which seen in the radial direction,

is in threaded engagement with the threaded spindle 24 on the one hand and with the spindle nut 26 on the other and rotates concentrically about the central axis 19 during operation, for example with its central axis.

In the case of the hand tool 100, the working head 30 and the electromechanical drive 10 are designed to press round tubular workpieces into a pipe connection. Such workpieces are, for example, sleeve-shaped press fittings which are pushed onto one end of a pipe and then pressed against the pipe or pipe end by means of the hand tool 100 in order to produce a pipe connection. The press fittings consist, for example, of a deformable material such as stainless steel, copper, brass or plastic. The tubes can be copper, steel or stainless steel tubes or Be multilayer pipes. Such a workpiece 300 to be pressed is indicated by way of example in FIG.

In order to properly press such workpieces, the working head 30 is designed as a press head and the

The electromechanical drive 10 is dimensioned such that a maximum actuating force for actuating the working head 30, in particular a maximum axial force between 30 kN and 40 kN acting in the direction of the movement axis 15,

for example about 34 kN to 35 kN, can be applied. For example, it is provided that the electric motor 11 has a nominal torque, for example between 0.1 Nm and 1.0 Nm and a nominal speed, for example between 9,000 rpm and 20,000 rpm. Furthermore, the planetary gear 17 has a reduction value, for example between 1: 8 and 1:85.

According to a possible design, the electric motor 11 can have a nominal speed between 10,000 1 / min and 14,000 1 / min and a nominal torque between 0.5 Nm and 0.8 Nm.

For example, the electric motor 11 is a DC motor with a nominal voltage of approximately 18 volts. With this design it can be provided that the reduction stage 12 or the epicyclic gear 17 has a reduction value between 1: 8 and 1:55. Furthermore, it can be provided that the threaded spindle 24 of the

Planetary roller screw drive 22 has a thread pitch between 0.5 mm and 2.9 mm.

For example, the epicyclic gear 17 have one

Reduction value between 1:10 and 1:20 and the

Threaded spindle 24 has a thread pitch between 0.6 mm and 0.9 mm. For example, the epicyclic gear 17 have one Reduction value between 1:15 and 1:30 and the

Threaded spindle 24 has a thread pitch between 0.9 mm and 1.3 mm. For example, the epicyclic gear 17 have a reduction ratio between 1:25 and 1:40 and

Threaded spindle 24 has a thread pitch between 1.3 mm and 2.0 mm. For example, the epicyclic gear 17 have a reduction ratio between 1:35 and 1:50 and

Threaded spindle 24 has a thread pitch between 2.0 mm and 2.8 mm.

According to another possible interpretation, the

Electric motor 11 have a nominal speed between 10,000 1 / min and 14,000 1 / min and a nominal torque between 0.2 Nm and 0.5 Nm. For example, the electric motor 11 is a DC motor with a nominal voltage of approximately 12 volts. With this design it can be provided that the reduction stage 12 or the epicyclic gear 17 has a reduction ratio between 1:14 and 1:85. Furthermore, it can be provided that the threaded spindle 24 of the

Planetary roller screw drive 22 has a thread pitch between 0.5 mm and 2.9 mm.

For example, the epicyclic gear 17 have one

Reduction value between 1:15 and 1:30 and the

Threaded spindle 24 has a thread pitch between 0.6 mm and 0.9 mm. For example, the epicyclic gear 17 have a reduction ratio between 1:20 and 1:40 and

Threaded spindle 24 has a thread pitch between 0.9 mm and 1.3 mm. For example, the epicyclic gear 17 have a reduction ratio between 1:30 and 1:60 and

Threaded spindle 24 has a thread pitch between 1.3 mm and 2.0 mm. For example, the epicyclic gear 17 have one Reduction value between 1:40 and 1:80 and the

Threaded spindle 24 has a thread pitch between 2.0 mm and 2.8 mm.

The mechanical converter 13 is preferably coupled on the input side to the epicyclic gear 17, for example in that an output shaft 17.1 of the epicyclic gear 17, which is coaxial with respect to the axis of rotation 18, for example, is connected in a rotationally fixed manner to the spindle nut 26.

 For this purpose, for example, the output shaft 17.1 is provided with a polygonal cross-section which fits into it

corresponding recording at one end of one at the

Spindle nut 26 molded extension 27 engages rotatably. As a result, the spindle nut 26 is driven directly by the output shaft 17.1 of the epicyclic gear 17. About the

Output shaft 17.1 of the epicyclic gear 17 is the

Spindle nut 26 is set into a rotational movement, by means of which the at least one planetary roller 25 or 25 'is likewise set into a rotational movement, so that there is one via the at least one planetary roller 25 or 25'

translational movement of the threaded spindle 24 comes along the movement axis 15.

The threaded spindle 24 is preferably with a

Anti-rotation device 28 provided, for example by the

Threaded spindle 24 with one end rotatably on the

Actuator 14 is connected. In the present case of pressing, the actuating element 14 is, for example, a roller carrier 29, on which at least two roller elements 29.1, 29.2 are rotatably mounted in order to actuate the working head 30. The rotationally fixed connection of the threaded spindle 24 to the roller carrier 29 can be realized in that the Threaded spindle 24 is inserted at one end into a receptacle of the roller carrier 29 and a pin element 29.3 is inserted into a bore or a hole which extends through a wall of the roller carrier 29 forming the receptacle into or through the threaded spindle 24. Alternatively, it can also be provided that the threaded spindle 24 is screwed and / or glued to the roller carrier 29 at one end in order to implement the anti-rotation device 28.

The planetary roller screw drive 22 is preferably in a housing 22.1 or housing part, in particular tubular

Housing 22.1 or housing part, housed. For example, the housing 22.1 is fastened at one end to a housing 12.1, in particular a tubular housing 12.1, in which the reduction stage 12 is housed, for example.

Basically, the reduction level 12 and

mechanical converter 13, in particular the

 Planetary roller screw drive 22, can also be accommodated in a common housing. The housing 22.1 for the planetary roller screw drive 22 is preferably designed to be open at the end in the direction of the working head 30, so that the

 Planetary roller screw drive 22 is to be or has been mounted in the housing 22.1 via this open side, for example. For example, the housing 22.1 and / or the housing 12.1 form at least part of the carrier 40 of the

Hand tool 100.

A bearing arrangement is preferably provided in the planetary roller screw drive 22, which has at least two

preferably comprises three bearings 26.1, 26.2, 26.3. One of the bearings 26.1, 26.2, 26.3, in particular the bearing 26.2, is preferably an axial bearing and the other of the bearings 26.1, 26.2, 26.3, in particular the bearings 26.1, 26.3, are radial bearings. The planetary roller screw drive 22 is preferred

on the drive side, two of the bearings 26.1, 26.2, 26.3, which are each supported against the housing 22.1 and support the spindle nut 26, for example via the extension 27. These are preferably the bearings 26.2 and 26.3, of which one is used, for example, as an axial bearing and the other bearing 26.3 as a radial bearing. The bearing used as a thrust bearing

26.2 can be an axial plain bearing or an axial roller bearing, such as an axial ball bearing or a

Thrust roller bearings. The bearing used as a radial bearing

26.3 can be a needle bearing or a plain bearing.

In principle, the bearing 26.3 can also be a roller bearing.

Preference is given to the planetary roller screw drive 22

On the output side, at least one of the bearings 26.1, 26.2, 26.3 or a single one of the bearings 26.1, 26.2, 26.3 is provided, which is supported against the housing 22.1 or a housing part fastened, for example, against the housing 22.1 and supports the threaded spindle 24. This is preferably the bearing 26.1, which is used as a radial bearing and is, for example, a roller bearing, in particular a ball bearing. For example, the housing part is part of the roller carrier 29. For example, this is

Housing part by screwing against the housing 22.1

attached and / or in the housing 22.1 end

screwed in. The bearing arrangement is preferably preloaded. For this purpose, a spring element, such as one

Disc spring, provided by the biasing force

Bearing arrangement is clamped in the axial direction.

For example, the spring element is arranged on an end of the threaded spindle 24 facing the working head 30 and for example, the spring element preferably presses directly against one bearing 26.1.

The working head 30 preferably comprises at least two

Press jaws 30, 31, each part of a

Have press die 33. For example, the pressing jaws 30, 31 are pivotably mounted on a base body 34 in order to be pivoted from an open position into a closed position. For example, the open position serves to hold the workpiece between the parts of the press die 33.

For example, the parts of the press die 33 are in the closed position in the closed position. The base body 34 is preferably received in a receptacle, in particular a jaw receptacle 41, of the hand tool 100 and, for example, interchangeably fastened therein. For example, the jaw holder 41 is a component of the carrier 40 and / or the housing 22.1 of the mechanical transducer 13 or is fastened to it.

The respective pressing jaw 30, 31 is preferably assigned an actuating surface 35, for example, which runs obliquely. Through a translatory movement of the

Actuating element 14, in particular of the roller carrier 29, the roller elements 29.1 and 29.2 come into contact with the actuating surfaces 35 and cause them to progress

Path of movement of the actuating element 14 a pivoting of the pressing jaws 30, 31 in the direction of the closed position while exerting a pressing action by the parts of the

Press die 33. Around the press jaws 30, 31 again in the

To move back to the open position, a spring element can be provided, the restoring force of which brings about or at least supports the return of the pressing jaws 30, 31. The hand tool 100 is preferably a cordless hand tool, which has an electrical energy store, in particular an accumulator 23, for electrical purposes

Energy supply of the electric motor 11 uses. The accumulator 23 is preferably rechargeable and, for example, detachably mounted on the hand tool 100 as an exchangeable module. For this purpose, for example, a corresponding electrical contact is provided, by means of which, in the assembled state, a

electrical connection between the battery 23 and the electric motor 11 is established. An on / off switch 11.2 is preferably provided to switch the electric motor 11

to turn on or off.

The electromechanical drive 10 is preferably at least partially surrounded by an outer skin, which is indicated in FIG. 2 by the dashed line 110. The outer skin can be an outer housing which is fastened, for example, to the carrier 40. The outer case can by

at least two housing shells fastened against one another. The outer skin preferably has at least one grip surface, via which the hand tool 100 can be held in the hand by a user and / or can be guided during operation.

FIG. 3 shows a further possible embodiment of a hand tool 200 which can be used for the shaping machining of tubular workpieces. Figure 4 shows a possible embodiment of an electromechanical

Drive 10 ', which is used in the hand tool 200. The hand tool 200 of FIGS. 3 and 4 differs from the hand tool 100 of FIGS. 1 to 2, inter alia, in that the working head 30 as an expanding head or

Expander head 30.2 is formed so that, for example, the ends of a tube can be radially expanded.

For this purpose, for example, the expander head 30.2 has a plurality of clamping jaws 37 which are arranged about a central axis 36 and which can be expanded radially outward with respect to the central axis 36. The clamping jaws 37 are preferably movable on a base part 38, in particular mounted radially outward or pivotable. The base part 38 is set up, for example, to be mounted on a housing part 59 (FIG. 4). For example, the base part 33 is provided with a thread in order to be screwed or screwed onto the housing part 59.

to be screwed on. For example, the housing part 59 is assigned to a front part 250 of the hand tool 200.

The hand tool 200 preferably has at least one

Grip surface 210 or 220. For example, that

Hand tool 200 has a design with a T-handle on which the at least one gripping surface 210 or 220 is formed. Alternatively, the hand tool 200 can also have a design with a pistol grip (not shown in FIGS. 3 and 4). The hand tool 200 is preferably battery-operated. For this purpose, the hand tool 200 preferably has a receptacle 240 for a (not shown in FIGS. 3 and 4)

for example, rechargeable battery. To the

Switching on or off or starting hand tool 200 is preferably provided with a switch 230.

In the hand tool 200, the expander head 30.2 and the electromechanical drive 10 ′ provided there are at least for this purpose designed to expand tubular workpieces from a material having a shape memory. Such a material tends to deform, such as

for example, an expansion to return to its original shape. The material is

for example, a plastic with a pronounced spatial network, which belongs to the PE-X or XLPE class, for example. Due to this material property, a pipe connection can already be created by a

One end of the tubular element is inserted into a radially widened end of another tubular element. Due to the reshaping or shrinking of the widened pipe end, the nested ones become inserted after a certain time

Tube ends are in a press connection to each other.

The construction and / or the dimensions of the electromechanical drive 10 'of the hand tool 200 can be basically identical to the electromechanical drive 10 of the hand tool 100 of FIGS. 1 and 2 and, for example, an electric motor 11' with an output shaft 11.1 ', a mechanical converter 13 ' and a

Have actuating element 14 '. The actuating element 14 'is set up to be moved translationally in the direction of a movement axis 15' in order to actuate the expander head 30.2. The electric motor 11 'is set up

Output shaft 11.1 'to rotate a drive axis 16', in particular in a rotary operation

Output shaft 11.1 'to rotate in a direction of rotation about the drive axis 16'. The mechanical converter 13 'is set up to convert a rotary drive movement starting from the output shaft 11.1' into a translational one Convert drive movement for driving the actuator 14 '.

The electric motor 11 'is preferred

Reduction gear 12 'connected downstream to convert the speed of the electric motor 11' in favor of a higher torque. The reduction gear 12 'is preferably between the electric motor 11' and the mechanical converter 13 '

interposed. The reduction gear 12 'preferably has a central axis of rotation 18' which is coaxial with the axis of movement 15 'and / or the drive axis 16'. The reduction gear 12 'is preferably formed at least in two stages. This is preferred

 Reduction gear 12 'housed in a preferably separate gear housing 12.1' and forms, for example, its own gear unit. For example, the reduction gear 12 'is a planetary gear 17', in particular a planetary gear.

To tubular workpieces such as the

Workpieces described above from one

Material with shape memory, properly

to expand, the electromechanical drive 10 '

for example dimensioned such that a maximum

Actuating force for actuating the expander head 30.2, in particular a maximum axial force between 5 kN and 15 kN, for example approximately 9 kN to 10 kN, acting in the direction of the movement axis 15 'can be applied. For example, it is provided that the electric motor 11 'is on

Has nominal torque, for example, between 0.1 Nm and 0.4 Nm and a nominal speed, for example, between 11,000 1 / min and 24,000 1 / min. Furthermore, the reduction gear 12 ' a reduction ratio between 1: 180 and 1: 400, for example.

In contrast to the mechanical converter 13 of the

Hand tool 100 of Figures 1 and 2, the mechanical transducer 13 'of the hand tool 200 is designed to a uniform rotary input movement in a

to translate back and forth movement. For this purpose, the mechanical transducer 13 ′ of the hand tool 200 includes

Cam gear 21 or is formed thereby. This back-and-forth movement is preferably used to ensure that the

Actuating element 14 'executes an opening movement and a return movement of the actuating element 14' is permitted. For example, the outward movement or forwards movement for issuing the actuating element 14 ′ is carried out by one

Starting position, which is shown in Figure 4, used in an issued position. For example, the forward or backward movement is used to allow the actuating element 14 'to be reset from the exhibited position to the starting position.

The actuating element 14 'is preferably actively activated by the cam mechanism 21. The force is preferred for resetting the actuating element 14 '

used at least one spring element 20. For example, the electromechanical drive 10 'is set up in such a way that the actuating element 14' is raised against the force of the at least one spring element 20 and for

Resetting the actuating element 14 to use a restoring force of the at least one spring element 20. The cam mechanism 21 preferably comprises two members 21.1 and 21.2, which along a gear axis 21.3,

in particular a common gear axis 21.3 are arranged. One of the links 21.1, 21.2 is set up for translatory movement along the gear axis 21.3. The other of the links 21.1 and 21.2 is set up for rotational movement about the gear axis 21.3. The gear axis 21.3 preferably runs along the movement axis 15 'and / or the drive axis 16'. For example, the gear axis 21.3 is arranged coaxially with the movement axis 15 'and / or the drive axis 16'.

In the electromechanical drive 10 ', for example, the translationally movable member 21.1 is a cam carrier 50 and the rotationally movable member 21.2 is one with the

Curve carrier 50 interacting tap 51. Preferably, the curve carrier 50 is slidably mounted and

provided on the output side. The tap member 51 is preferably rotatably mounted and provided on the drive side. Of the

Curve carrier 50 has a guide surface 52 which runs on a curved path 53 (FIG. 5) around the gear axis 21.3. The tap member 51 is set up to be moved along the cam track 53 on the guide surface 52 relative to the cam carrier 51, for example in this way to continuously scan the cam track 53 of the cam carrier 50.

Both the cam carrier 50 and the tap member 51 are preferably constructed along the gear axis 21.3.

The one provided on the cam carrier 50 is preferred

Guide surface 52 arranged transversely to the gear axis 21.3, in particular orthogonally or substantially orthogonally to the Gear axis 21.3 arranged. The is preferred

Guide surface 52 at an end 66

Curve carrier 50 formed, for example a

opposite end 67 of the front

 Actuator 14 'is facing. For example, the curve carrier 50 is cylindrical. For example, the curve carrier 50 is cup-shaped and has a bottom 68 and a circumferential wall 69 delimiting the bottom 68, the wall preferably being concentric around one

The central axis of the curve carrier 50 runs. The central axis of the cam carrier 50 is preferably on the gear axis 21.3.

In the case of the cup-shaped curve carrier 50 is the

Guide surface 52 is formed on the front end of the wall 69, which is opposite the bottom 68

is present.

The tap member 51 preferably comprises a contact finger 54 or the like contact element or transmission element for scanning the curved path 53 of the cam carrier 50.

For example, the contact finger 54 or that

Transmission element arranged on a base body 55 extending along the gear axis 21.3. Of the

Contact finger 54 has a contact surface in order to come into contact against the guide surface 52 of the cam carrier 50. The contact surface preferably corresponds to that

Guide surface 52 of the cam carrier 50 is aligned and is, for example, transverse to the gear axis 21.3, in particular orthogonal or substantially orthogonal to the

Gear axis 21.3, in front. The contact surface on the outside of a bearing 56, for example one, is preferred

Plain bearing or a roller bearing, which for example, is pushed onto an end region of the contact finger 54.

The base body 55 is preferably cylindrical, the central axis of which lies, for example, on the gear axis 21.3. The contact finger 54 is preferably from the

Base body 55 in the radial direction to the outside.

For example, the base body 55 has a bore 71, in particular a through bore, into which the

Contact finger 54 is inserted with an end portion, in particular is attached. For example, the

Base body 55 also has a further bore 72 which runs coaxially to its central axis and in which a shaft 70 or a shaft section is accommodated, shaft 70 preferably being connected in a rotationally fixed manner to base body 55.

For example, the shaft 70 has an output of the

Reduction gear 12 'or rotatably connected directly to the electric motor 11'. In the latter case, the non-rotatable connection can also be achieved in that the output shaft 11.1 'of the electric motor 11' is received in a rotationally fixed manner in the further bore 72 of the base body 55.

The translationally movable member 21.1 of the cam mechanism 21 is preferably guided translationally in a guide 57. For this purpose, the guide 57 preferably has at least one

Pin element 58, which is attached to a housing part or the housing part 59, for example by means of a screw element 73, and is slidably received in a corresponding receptacle 60 of the translationally movable member 21.1. This is preferably at least one

Pin element 58 coaxial or axially displaced to the

Gear axis 21.3 arranged. At least that is preferred a spring element 20 arranged so that it is on the one hand against the housing part 59 and on the other hand against the

supports translatory movable member 21.1. For example, this is at least one spring element 20 as a compression spring

formed and the at least one pin element 58 is inserted into a free interior of the spring element 20.

The translationally movable member 21.1 of the cam mechanism 21 is preferably secured against rotation about the gear axis 21.3. For this purpose, the pin element 58 is preferably at least twice and, accordingly, the associated one

Recording 60 provided at least twice, the

there are at least two pin elements 58 at a distance in the radial direction with respect to the gear axis 21.3 in order in this way to secure the translationally movable member 21.1 against rotation about the gear axis 21.3.

The mechanical converter 13 'is preferably in one

preferably housed tubular housing part 62.

The housing part 62 preferably serves as a carrier for the

mechanical converter 13 '. This is supported, for example

Tap member 51 against the housing part 62 in the radial direction, is rotatably mounted on the housing part 62, for example via a radial bearing 61, in particular a single radial bearing 61. The housing part 59 preferably forms one

End piece, which with the preferably tubular

Housing part 62 in a plug connection and / or one

There is a screw connection. The housing part 59 preferably has a central passage in which the

Actuating element 14 'is received and / or guided.

The actuating element 14 'is preferably piston-shaped

trained and has to actuate the jaws 37 thorn-shaped end, which protrudes, for example, from the housing part 59.

The actuating element 14 'and that are preferred

Link 21.1 of the cam mechanism 21 which can be moved in translation can be rotated relative to one another about the axis of movement 15 '. For this purpose, an intermediate element 74 can be provided, which is for example molded onto the translationally movable member 21.1 or connected in a rotationally fixed manner. For example, that is

Intermediate element 74 in an insertion receptacle 75 of

Actuating element 14 'inserted and thereby

Actuator 14 'rotatable relative to the non-rotatable

present intermediate element 74 stored.

Preferably, the rotatability of the actuating element 14 'about the axis of movement 15' is realized in order to consciously rotate the actuating element 14 'over a

to cause predetermined angle of rotation and thereby possibly caused by the jaws 37 of the expander head 30.2

To counter embossing lines. For example, a link control is provided for this purpose, which is set up to rotate the actuating element 14 'relative to the

Housing part 62 about the axis of movement 15 'over a

to effect predetermined rotation angle. The link control has, for example, a link 63 and an engagement element 64 guided in the link 63, the link 63 being the actuating element 14 'and the engagement element 64 being the

Housing part 62 can be assigned.

Figure 5 shows a possible embodiment of the

Curve carrier 50, which for example in the

electromechanical drive 10 'is used. Of the Curve carrier 50 has the cup shape already described above with the bottom 68 and the circumferential wall 69, which runs concentrically around the central axis 76 of the curve carrier 50. The guide surface 52 for the cam track 53 is formed on the front end 66 of the wall 69, which is opposite the floor 68.

FIG. 6 shows the course of the curved path 53 of the

Curve carrier 50 in a representation of the unrolled

Curve 53. This shows the axial extent S of the

Curve carrier 50, shown starting from its bottom 68 or rear end 67 over an angle of rotation W. As can be seen from FIG. 5, the cam track 53 of the cam carrier 50 has a first cam section 53.1 and a second

Curve section 53.2. Viewed in a direction of rotation, which is identified by the arrows 90, 91, the first curve section 53.1 has an incline and the second

Curve section 53.2 a slope. The amount of the gradient is preferably greater than the amount of the slope in order to ensure a uniform movement of the output shaft 11.1 ′ of the

Electric motor 11 'the return movement of the

Actuator 14 'faster than his time

Exhibit movement.

According to a possible design of the electric motor drive 10 'of the hand tool 200, the electric motor 11' can have a nominal speed between 12,000 1 / min and 22,000 1 / min and a nominal torque between 0.1 Nm and 0.4 Nm.

For example, the electric motor 11 'is a DC motor with a nominal voltage of approximately 18 volts or with a nominal voltage of approximately 12 volts. At this

Interpretation it can be provided that the reduction stage 12 'or the epicyclic gear 17' has a reduction ratio between 1: 180 and 1: 400.

For example, the electric motor 11 'has a nominal speed between 12,000 1 / min and 22,000 1 / min and a nominal torque between 0.1 Nm and 0.4 Nm and the epicyclic gear 17' has a reduction ratio between 1: 200 and 1: 370.

 For example, the electric motor 11 'has a nominal speed between 14,000 1 / min and 20,000 1 / min and a nominal torque between 0.1 Nm and 0.3 Nm and the epicyclic gear 17' has a reduction ratio between 1: 220 and 1: 335.

 For example, the electric motor 11 'has a nominal speed between 16,000 rpm and 18,000 rpm and a nominal torque between 0.1 Nm and 0.2 Nm and the epicyclic gear 17' has a reduction ratio between 1: 265 and 1: 300.

Furthermore, it can be provided that the curve carrier 50 has a diameter between 2 cm and 8 cm in the region of its curved path 53 and that the first curve section 53.1 of the curved path 53 of the curve carrier 50 has an incline between 5 degrees and 15 degrees. The “diameter” is to be understood as the greatest possible distance between two points which lie on the center line of the curved track 50, that is to say in the middle of the track.

FIG. 7 shows an example of the electric motor drive 10 ′, installed in the hand tool 200 of FIG. 3, in a sectional illustration. As can be seen from this, the preferably tubular housing part 62, in which the mechanical transducer 13 'is accommodated, can form the front part 250 described in relation to FIG. Furthermore, it can be provided that the electric motor 11 'in a grip part

is housed. The possible reduction gear 12 'can also be assigned to the handle part. For example, the front part 250 and the handle part form a fixed structural unit.

Alternatively, the front part 250 and the handle part can each form separate structural units, it being possible for a possible connection point to be provided, which is indicated in FIG. 7 by a dividing line 92. In this case, for example, the handle part is part of a separate drive device 400, which, for example, also as

Drive device for a screwdriver, in particular

Cordless screwdriver, or other tools, for example

battery operated tools can be used.

A mechanical coupling 65 (not shown in FIG. 7) can be provided in the region of the dividing line 92 in order to drive-link the members of the electromechanical drive 10 'assigned to the drive device 400 and the members of the electromotive drive 10' assigned to the front part 250 and preferably also connected to each other in terms of housing. For example, the mechanical clutch 65 is a

Quick coupling. The mechanical coupling 65 is preferably a positive coupling, such as, for example

Claw clutch. The mechanical coupling 65 preferably has a locking device, by means of which the associated coupling parts are prevented from being pulled out in the axial direction. Such a coupling with locking can be in the manner of a

Baj onettkupplung be built.

If such a separate drive device 400 is used, the reduction gear 12 'can do so

be dimensioned so that there is a reduction value between 1: 1.5 and 1:12. This against the background that the

separate drive device 400, for example, already has at least one of its own reduction stages. If the separate drive device 400 has a nominal voltage of 18 volts, the reduction gear 12 'has one

Reduction value for example between 1: 1.5 and 1:10, in particular between 1: 2 and 1: 9, in particular between 1: 2.5 and 1: 7. If the separate drive device 400 has a nominal voltage of 12 volts, the reduction gear 12 ′ has a reduction value, for example between 1: 2 and 1:12, in particular between 1: 3 and 1:10, in particular

between 1: 5 and 1: 9.

The above design of the curve carrier 50 can be retained in this variant. So it can

Curve carrier 50 in the region of its curved path 53

Have diameters between 2 cm and 8 cm and the first curve section 53.1 of the curve path 53 of the curve carrier 50 can have an incline between 5 degrees and 15 degrees. The “diameter” is to be understood as the greatest possible distance between two points which lie on the center line of the curved track 50, that is to say in the middle of the track.

Another hand tool for the shaping processing of tubular workpieces is in the patent application filed by the applicant on the same day as the present application to the German Patent and Trademark Office with the title “Electromechanical drive for an expanding device for expanding tubular workpieces, attachment unit,

Expanding device and method for producing a

Pipe connection ". The content of this patent application is hereby fully incorporated into the present description.

Under the designation "nominal voltage" is in the

present description in particular the voltage or

Understanding the operating voltage of the electric motor at maximum or maximum power. In the present description, the term “nominal torque” or “nominal speed” is to be understood in particular as the torque or the speed at the highest or maximum output of the electric motor. The values given in the present description for the

Nominal torque are in the physical unit

"Newton meters" indicated, which are abbreviated as "Nm". The values for the nominal speed given in the present description are given in the physical unit "revolutions per minute", which are abbreviated as "1 / min".

In the present description, the term "reduction value" means in particular the value of a

To understand the transmission ratio, at which one

Slow translation takes place, which in the

Description is called reduction. Of the

Reduction value or the value of the gear ratio is, for example, the ratio of the speed of the

Output shaft to the speed of the drive shaft (h ^: h _Ah ) or as a ratio of the torque of the drive shaft to that

Output shaft torque (M _Ah : M ^).

For those named in the present description

Basic parameters for the areas include, in particular, the basic parameters themselves for the respective area. Are also through the named areas include any individual values contained therein.

In the present description, reference to a certain aspect or a certain

Embodiment or a particular design that a particular feature or property associated with that particular aspect or particular

Embodiment or the respective embodiment is described, at least is included there, but does not necessarily have to be included in all aspects or embodiments or embodiments of the invention. It is expressly pointed out that any combination of the various features and / or structures and / or properties described in relation to the invention are encompassed by the invention, unless this is expressly or clearly contradicted by the context.

The use of individual or all examples or an exemplary expression in the text is only intended to illuminate the invention and does not place any restriction

with respect to the scope of the invention unless otherwise stated. Also there is no expression or

To understand the wording of the description in such a way that it is an element not claimed but essential for the practice of the invention. List of reference symbols

10 electromechanical drive

 11 electric motor

 11.1 Output shaft

 11.2 On / off switch

 12 reduction stage

 12.1 Housing

 13 mechanical transducers

 14 actuator

 15 axis of movement

 16 drive axle

 17 epicyclic gear

 17.1 Output shaft

 18 axis of rotation

 19 central axis

10 'electromechanical drive

 11 'electric motor

 11.1 'output shaft

 12 'reduction gear

 12.1 'housing

 13 'mechanical converter

 14 'actuator

 15 'axis of movement

 16 'drive axle

 17 'epicyclic gear

 18 'axis of rotation

20 spring element

21 cam mechanism 21.1 translationally movable member

21.2 rotatably movable member

21.3 Gear axis

22 planetary roller screw drive

 22.1 Housing

 23 accumulator

 24 threaded spindle

 25 planetary roller

25 'planetary roller

 26 spindle nut

 26.1 bearings

 26.2 Bearings

 26.3 bearings

 27 extension

 28 Anti-rotation device

 29 roller carriers

 29.1 Roller element

 29.2 Roller element

 29.3 pin element

30 working head

 30.1 press head

 30.2 Expander head

 31 press jaw

 32 press jaw

 33 press die

 34 basic body

 35 operating area

 36 central axis

 37 jaws

38 base part 40 carriers

 41 jaw holder

50 curve bearers

 51 tap

 52 guide surface

 53 cam track

 53.1 first curve section

53.2 second curve section

54 contact fingers

 55 basic body

 56 bearings

 57 leadership

 58 pin element

 59 housing part

 60 recording

 61 radial bearings

 62 housing part

 63 backdrop

 64 engagement element

 65 mechanical coupling

66 front end

67 front end

68 bottom

 69 wall

 70 wave

 71 hole

 72 more holes

 73 screw element

 74 intermediate element

75 plug-in receptacle 76 central axis

90 arrow

 91 arrow

92 dividing line

100 hand tools

 110 dashed line (outer skin) 2 00 hand tool

210 grip surface

220 grip area

230 switches

240 recording

250 front part

300 workpiece

400 drive device

S axial extension

 W angle of rotation

Claims

Patent claims 1. Hand tool (100; 200) for forming and / or  separating machining of plastic or  Metal workpieces, especially plastic or  Metal pipes, with a working head (30), one  electromechanical drive (10) for actuating the  Working head (30) and one of the electromechanical  Drive (10) and / or the working head (30) carrying  Carrier (40), the electromechanical drive (10) comprising an electric motor (11) with an output shaft (11.1), at least one reduction stage (12) downstream of the electric motor (11), a mechanical converter (13) and an actuating element (14), being the  Actuating element (14) is set up to be moved translationally in the direction of a movement axis (15) in order to actuate the working head (30), the  The electric motor (11) is set up to drive the actuating element (14) to rotate the output shaft (11.1) about a drive axis (16), and the mechanical converter (13) is set up to rotate the output shaft (11.1)  Converting the drive movement into a translatory drive movement for driving the actuating element (14), characterized in that the at least one Reduction stage (12) comprises an epicyclic gear (17) with a central axis of rotation (18) which is coaxial with the axis of movement (15) and / or the drive axis (16). 2. Hand tool according to claim 1, characterized in that the planetary gear (17) has a reduction ratio between 1: 8 and 1:85 and the electric motor (11)  Nominal torque between 0.1 Nm and 1 ° Nm and one  Have a nominal speed between 9,000 rpm and 24,000 rpm. 3. Hand tool according to claim 1, characterized in that the planetary gear (17 ') has a reduction ratio between 1: 180 and 1: 400 and the electric motor (11') has a nominal torque between 0.1 Nm and 1 ° Nm and a  Have a nominal speed between 9,000 rpm and 24,000 rpm. 4. Hand tool according to one of the preceding claims,  characterized in that the epicyclic gear (17) is an at least two-stage planetary gear. 5. Hand tool according to one of the preceding claims,  characterized in that the mechanical transducer (13) performs a reduction function. 6. Hand tool (100; 200) for forming and / or  separating machining of plastic or  Metal workpieces, especially plastic or  Metal pipes, with a working head (30), one  electromechanical drive (10) for actuating the  Working head (30) and one of the electromechanical  Drive (10) and / or the working head (30) carrying  Carrier (40), the electromechanical drive (10) comprising an electric motor (11) with an output shaft (11.1), one downstream of the electric motor (11) Reduction stage, a mechanical transducer (13) and an actuator (14), the actuator (14) is set up in the direction of an axis of movement (15) to be moved in translation to actuate the working head (30), the electric motor (11)  is set up to drive the actuating element (14) to rotate the output shaft (11.1) about a drive axis (16), and the mechanical transducer (13) is set up to convert a rotary drive movement emanating from the output shaft (11.1) into a  translational drive movement to drive the  Convert actuator (14), thereby  characterized in that the mechanical transducer (13) performs a reduction function which the  Reduction level forms and the only one  Reduction level is provided. 7. Hand tool according to one of claims 1 to 6, characterized  characterized in that the mechanical converter (13) comprises a planetary roller screw drive (20.2). 8. Hand tool according to claim 7, characterized in that the planetary roller screw drive (20.2) comprises a threaded spindle (24) which has a thread pitch between 0.5 mm and 4.5 mm. 9. Hand tool according to claim 7, characterized in that the planetary roller screw drive (20.2) comprises a threaded spindle (24) which has a thread pitch between 0.2 mm and 1.0 mm. 10. Hand tool according to one of claims 1 to 6, characterized characterized in that the mechanical transducer (13 ') Cam gear (20.1) includes. 11. Hand tool according to one of the preceding claims,  characterized in that the electric motor (11) is a brushless DC motor. 12. Hand tool according to one of the preceding claims,  characterized in that the hand tool (100; 200) is battery-operated and has an exchangeable accumulator (23) for the electrical power supply of the electric motor (11). 13. Hand tool according to one of the preceding claims,  characterized in that the electric motor (11) is part of a separate drive device and is releasably operatively connected to the hand tool (100; 200) via a mechanical coupling. 14. Hand tool according to one of claims 1 to 13, characterized in that the working head (30) as a press head (30.1) is designed for the radial pressing of pipe connections. 15. Hand tool according to one of claims 1 to 13, characterized in that the working head (30) is designed as a press head for the axial pressing of pipe connections. 16. Hand tool according to one of claims 1 to 13, characterized in that the working head (30) as an expander head (30.2) is designed to expand pipes. 17. Hand tool according to one of claims 1 to 13, characterized in that the working head (30) is designed as a cutting head or butt bending head. 18. Use of a planetary roller screw drive (22) for  Converting a rotary drive movement into a translatory drive movement in a hand tool (100) for the shaping and / or separating machining of plastic or metal workpieces, in particular in a hand tool (100) according to one of Claims 1 to 17. 19. Use of a cam mechanism (21) for converting a rotary drive movement into a translatory drive movement in a hand tool (200)  reshaping and / or separating processing of  Plastic or metal workpieces, especially one Hand tool (200) according to one of claims 1 to 17.