EP3990225A1

EP3990225A1 - Handheld setting tool

Info

Publication number: EP3990225A1
Application number: EP20704811.7A
Authority: EP
Inventors: Arno Mecklenburg
Original assignee: Rhefor GbR
Current assignee: Rhefor GbR
Priority date: 2019-06-26
Filing date: 2020-02-06
Publication date: 2022-05-04
Also published as: US20220355451A1; US11883938B2; US20240173832A1; CN114269518A; AU2020306332A1; CA3145144A1; WO2020259870A1; JP2022538435A

Abstract

A handheld setting tool for setting a nail or a pin into a substrate, comprising: a drive, preferably a gas spring drive or an electrodynamic drive, which drives an actuator (11), which actuator is used to drive the nail or the pin into the substrate; characterized by: a decoupling device, which at least partially decouples a first motion process of a first movable part or piston (111) in the actuator (11), driven by the drive, from a second motion process of a second movable part or piston (112) in the actuator (11) so as to drive the nail or the pin in.

Description

Hand-held setting tool

Technical area

The present invention relates to hand-held setting tools for setting a nail or a bolt.

background

Setting devices or nailing devices, which store the energy required for the setting process in a pre-tensioned gas spring, are generally known from WO 2009/046076 A1, for example, and are marketed by Senco under the trade name "Fusion Technologie" Devices are also offered by HITACHI and should achieve driving energies of 120J.

Such nailers ("gas spring setting devices") are well suited for setting nails in wood, but have various disadvantages compared to internal combustion-powered setting devices, which severely limit their range of applications.

For example, gas spring setting tools appear to be unsuitable for driving bolts into solid surfaces such as steel or concrete, on the one hand because of the insufficient driving energy and on the other hand because of the possible kickback. The latter can be illustrated using the following borderline case: A nail of length s is to be driven into a substrate, but the substrate and the nail do not yield at all. In this case, the subsurface forms an abutment for the relaxing gas spring. The relaxation of the gas spring then accelerates the gas device during driving over the path s, the gas spring doing a work w = J (F * ds) with its force F. With driving energies such as those required for setting in concrete and steel, this can quickly become disastrous for the user Runback energies. The problem of kickback also exists for setting tools with electrodynamic drives.

Another shortcoming of known gas spring setting tools is their comparatively low drive-in energy and their relatively high weight and volume compared to internal-combustion-powered setting tools with the same drive-in energy. This deficiency is essentially due to the comparatively low operating pressures of the devices. It is not for nothing that WO 2009/046076 A1 expressly recommends low operating pressures between 100 psig and 120 psig, i.e. pressures which correspond to the normal operating pressures of pneumatic actuators: The demands on the piston rings in gas spring setting devices are enormous. They should reduce the leakage-related pressure loss in the working gas reservoir over the entire service life of the setting tool, i.e. in the gas spring, to a negligible extent, but withstand extremely high sliding speeds during a setting process for pneumatic systems - and also cause the lowest possible friction force when sliding. If, for example, pressures of 1.2 kpsig instead of 120psig were used, then approximately ten times higher contact pressures would have to be applied to the seals for sealing, and the pv values would already be - for setting tools - moderate piston speeds of the order of magnitude of 30 m / s of all the piston seals commonly used in pneumatics. It is thus understandable that WO 2009/046076 A1 expressly teaches away from operating pressures that are significantly higher than 120 psig.

The company HILTI proposed in DE 10 2007 000 219 B4 to solve the sealing problem with the help of a rolling membrane; the service life of such a membrane appears questionable in view of the enormous dynamic stress in the setting tool.

Another disadvantage of known gas spring setting devices can be seen in the fact that the drive-in energy is difficult to set, whereas this is easier, for example, in the case of devices powered by internal combustion Way is possible. For example, the injected fuel quantity can be varied in a setting device driven by the combustion of an ignitable gas-air mixture. In powder devices, cartridges can be loaded with a propellant charge adapted to the application.

Finally, a further disadvantage of known setting devices that include a piston drive is that they have a pronounced kickback and kickback, which can reduce the setting quality and physically stress the user.

Summary

The present invention aims to solve the above-mentioned problems.

These problems are solved by a hand-held setting tool with the features according to claim 1. Preferred embodiments are defined in the subclaims.

Further advantages and developments of the invention emerge from the following detailed description and the entirety of the claims.

Brief description of the figures

1 shows a hand-held setting tool according to one embodiment.

2 shows an actuator according to an embodiment.

3 shows an actuator according to an embodiment.

4a-4c show an embodiment of a tensioning device.

5 shows an actuator according to an embodiment. Fig. 6 shows a hand-held setting tool according to a

Embodiment.

Fig. 7 shows a hand-held setting tool according to a

Embodiment.

Description of the embodiments

The invention is described below on the basis of further embodiments and examples, based on the known gas spring setting devices and setting devices with an electrodynamic drive. The examples serve to better understand the invention: they are in no way to be understood as restrictions. In the following description, the same reference symbols are used for the same or corresponding elements and a repetitive description is largely avoided.

A hand-operated setting device for setting a nail or a bolt in a substrate (eg steel or concrete) according to one embodiment comprises a drive or a piston drive, preferably a gas spring drive or an electrodynamic drive, which drives an actuator 11. The driven actuator 11 is used to drive the nail or the bolt into the ground. The hand-held setting tool further comprises a decoupling device, which a first movement process of a first movable part or piston III in the actuator 11, driven by the drive, by a second movement process of a second movable part or piston II2 in the actuator 11 for driving the nail or the Bolt at least partially or partially decoupled. (To improve understanding, the reference numbers here refer only by way of example to features in FIG. 1, which shows a setting device with a gas spring drive. The concept of the decoupling device can, however, also be used for other drives, in particular electrodynamic drives). The decoupling device can advantageously be designed so that kinetic or translational energy (caused by the drive) of the first movable part or piston III is transferred to the second movable part or piston II2 and kinetic or translational energy of the second movable part or piston II2 for driving nail or bolt is used.

The drive (gas spring drive or electrodynamic drive, as explained in detail below) thus serves to drive an actuator 11, in other words a stroke control element, which in the present case can be designed as a pneumatic actuator.

The decoupling device decouples a movement process of the first movable part (e.g. an armature) or the first movable piston III, which is caused by the drive (e.g. a translational movement of the movable part / piston in a cylinder) from a movement process of the second movable part (eg a setting element) or of the second movable piston II2 (eg a setting piston).

The partial or partial decoupling of the movement processes can e.g. can be achieved in that a translational movement of the first piston does not lead directly or synchronously or simultaneously to a translational movement of the second piston, and vice versa. In other words, the movement process of the first piston preferably leads to a movement of the second piston only after a certain time delay. A (direct) kickback is therefore not transmitted directly to the first piston and thus to the drive.

In an advantageous embodiment, the decoupling device can be designed in that the first movable part or the first movable piston III is not rigidly connected to the second movable part or the second movable piston II2 or there is no direct contact between them. The person skilled in the art recognizes that in this embodiment translational movement of the first piston does not lead directly or synchronously to a translational movement of the second piston.

In a further advantageous embodiment, the decoupling device can be designed in that a compressible fluid, for example a compressible fluid, is located between the first movable part or piston III and the second movable part or piston II2. Air is located. Compared to an incompressible fluid where translational movement of the first piston due to the incompressible fluid, e.g. Lubricant would lead directly or synchronously to a translational movement of the second piston, a compressible fluid can at least partially decouple the movement processes of the first and second pistons. Those skilled in the art understand that e.g. only reaching a certain smaller distance between the first and second piston, combined with a compression of the compressible fluid, leads to overcoming the moment of inertia of the second movable part or piston so that it can be moved for the setting process.

A stroke length ("stroke length", distance between a first and second dead center) of the first movable part or piston III is therefore advantageous independent of a stroke length of the second movable part or piston II2. This allows the setting energy of the drive to be independent of a setting stroke of the second movable part or piston II2 can be adjusted.

In a further advantageous embodiment, the actuator 11 can furthermore have a cylinder, the first piston III and the second piston II2 being arranged opposite one another in the cylinder and with at least one piston seal being formed in the cylinder. The piston seals can be one or more piston rings and / or a gas dynamic seal. The gas dynamic seal is preferably of the type of a labyrinth piston seal (as will be explained in more detail below). In a further advantageous embodiment, the actuator 11 can furthermore be designed in such a way that a restoring device (eg a spiral compression spring) is designed for the second movable part or the second movable piston II2. After the nail or bolt has been set, the second movable part or the second movable piston can thus be returned to an initial position, largely independently of the first movable part or the first movable piston of the actuator 11.

In a further advantageous embodiment, the drive can have a further actuator 10. The actuator 10 is e.g. Part of a gas spring (as will be explained further below) and is coupled to the first movable part or piston 11, so that the driven further actuator 10 leads to the first movement process in the actuator 11. In this embodiment, the setting stroke of the second movable part or piston II2 in the actuator 11 is independent of a travel of the further actuator 10, so that the setting energy can be set independently of the setting stroke with which the nail or bolt is driven.

Fig. 1 shows schematically the structure of a setting tool according to a further embodiment. Its function is initially explained using the following components and / or assemblies:

- Actuator 11 with a first piston III and a second piston II2

- Pneumatic actuator 10 with piston rod 01 and a third piston 10i

- working gas reservoir 20

- Electrochemical energy storage 90

- Motor control 80

- engine 70

- reduction gear 60

- Jig 50

- Lock 40 The hand-held setting tool shown in FIG. 1 is a setting tool with a gas spring drive which, in a further advantageous embodiment, has at least one working gas reservoir 20 with a working gas and wherein the actuator 10 is a pneumatic actuator. The pneumatic actuator 10 has a third piston 10 i which is connected to a piston rod 01. The third piston 10i is in fluid connection with the working gas reservoir 20 and, together with the working gas reservoir 20, forms a gas spring.

The pneumatic actuator 10 can be moved between a stroke start position area in which the gas spring is stretched to the maximum and a stroke end position area in which the gas spring is at least partially relaxed. A person skilled in the art recognizes that this driven movement of the pneumatic actuator 10 leads to a movement of the movable part or piston III in the actuator 11 (first movement process), but this movement is at least dependent on the movement of the second movable part or piston II2 (second movement process) is partially decoupled.

In other words, the pneumatic actuator 10 (first actuator), together with the working gas reservoir 20, forms a pretensioned gas spring and thus the gas spring drive. To tension the gas spring, the motor 70 is supplied with electrical power from the energy store 90 (for example an accumulator or a fuel cell) by means of the motor control 80. Motor 70 drives reduction gear 60. Reduction gear 60 drives jig 50. Clamping device 50 translates the rotary movement of reduction gear 60 into a translational one, acts on piston rod 01 of pneumatic actuator 10, and moves its piston to deliver working gas from pneumatic actuator 10 to working gas reservoir 20, i.e. to tension the gas spring. Lock 40 can lock the gas spring in the tensioned state. To set the nail or bolt 140, the lock 40 is unlocked, for example with the aid of an electromagnetic actuator 41. That volume which is displaced by the piston of the pneumatic actuator 10 when the gas spring is tensioned is referred to as the stroke volume. Further optional components of a setting tool according to FIG. 1 are explained below:

Reference numeral 30 represents a valve which can connect the working gas reservoir 20 and the pneumatic actuator 10 to one another. It can, for example, like to use a fast electromagnetic actuator 31. DE 10 2009 031 665 A1 plus a spring, are positively controlled to pass a gas pulse from the working gas reservoir 20 into the actuator 10 and close it again before the setting process is completed, the valve preferably opening automatically when the pressure in the actuator's displacement 10 exceeds a certain value which is greater than the pressure in the working gas reservoir 20. The person skilled in the art understands that in this way the kickback of the device when setting it in solid ground can be reduced and the setting energy can be varied by the user by selecting the opening time of the valve; However, this at the expense of the electrical efficiency of the device. Valve 30 can preferably also be formed by the piston of actuator 10, which then serves as a shut-off body or has such a piston, the cylinder of actuator 10 being designed to have a valve seat, with the sealing being carried out with the aid of force from lock 40, which is used to generate force, for example can have a spring or be resilient (this variant will be explained later with reference to FIG. 2).

Reference numeral 120 represents a thermocouple with which the temperature in working gas reservoir 20 can be measured. Reference numeral 100 represents a manometer, in particular an electrical or electronic one, with which the static pressure in the working gas reservoir 20 can be measured. Reference number 21 represents a second working gas reservoir, which is normally under excess pressure compared to the working gas reservoir 20, the static pressure of which can be measured, for example, by means of a manometer 101. Working gas reservoir 21 serves the purpose of compensating for any leakage losses in working gas reservoir 20. This can take place via a pressure reducing valve 32. To Temperature compensation, the working gas can be heated or cooled in the working gas reservoir 20, for example by means of a Peltier element 110 (instead of which, for example, a heat pump can also be used), which with the cooling or heating elements 111 and 112 also creates a thermal connection between the working gas in Working gas reservoir 20 and the environment creates. Reference numeral 130 also shows a valve via which working gas reservoir 21 - the "refill reservoir" - can be filled externally with working gas.

In a particularly advantageous embodiment, the piston of the actuator 10 with the piston rod 01 does not itself (directly) act on the nail or bolt 140 in order to drive it in. Rather, actuator 10 acts with its piston rod 01 on a hammer mechanism, with kinetic energy (including parts mechanically connected to it) from actuator 10 from the first piston (e.g. piston III in FIG. 1) to a moving part, e.g. a second piston (e.g. piston II2 in Fig. 1), and the nail or bolt 140 is driven entirely or predominantly with the aid of the kinetic energy of the movable part, the first piston III and the movable part or second piston II2 not being rigidly connected to one another ("Decoupling Device").

For example, with the aid of actuator 10 (first actuator) via piston rod 01, a first piston III is driven in a further pneumatic actuator 11 ("hammer mechanism", second actuator), which can for example be filled with air (ambient pressure) In addition to the first piston III, a second piston II2, as shown in Fig. 1. The first piston III can, as explained, be driven by actuator 10 and is, for example, single-acting. The second piston II2 from actuator 11 - by means of a decoupling device from the first Piston III at least partially decoupled - is preferably double-acting and equipped with a restoring device, shown here in the form of a spiral compression spring, for example.

For sealing purposes, the first and second pistons of actuator 11 can be designed in the manner of the pistons of labyrinth piston compressors be, the required - temporary - sealing can thus be achieved gas-dynamically.

To set a nail or bolt 140, the piston rod 01 and consequently the piston of actuator 10 and the first piston 11 connected to piston rod 01 of actuator 11 can be accelerated by loosening the lock 40 by means of the pretensioned gas spring. As a result, the pressure between the first and second pistons of actuator 11 rises almost exponentially: the gas buffer that forms between the first and second pistons of actuator 11 generates momentum and kinetic energy from the part of the setting device that is directly driven by gas springs (piston 10i of actuator 10, piston rod 01, first piston III of actuator 11) is transferred to the second piston II2 of actuator 11 and consequently also to its piston rod and parts connected to it (for example the return spring). For this purpose, the movable masses must be expertly matched to one another, taking into account any reduced masses. The nail or bolt 140 is thus ultimately set via the piston rod of the second piston II2 of actuator 11. If this second piston II2 of actuator 11 is double-acting, that is, the side of the cylinder of actuator 11 facing the nail is closed sufficiently tightly On the side of the second piston II2 facing the nail, a second fluid or gas cushion resetting the second piston can be built up during a setting process in the cylinder of actuator 11 (as shown in FIG. 1). This prevents the second piston II2 of the actuator 11 from striking the nail or bolt 140 hard.

There should be clearance between the piston rod of the second piston II2 of actuator 11 driving in the nail or bolt 140 and the nail 140 itself to allow sufficient momentum transfer (of preferably at least 50%) from the first to the second piston of actuator 11 before acceleration and finally the driving in of the nail begins: The driving energy mainly comes from the kinetic energy of the second piston of actuator 11 (including its piston rod, etc.).

In order to achieve a short overall length of actuator 11 and / or to require only a small amount of play between the piston rod and nail, the energy transfer from the first to the second piston of actuator 11 should be as abrupt as possible, which can be achieved in at least two practical ways: ( i) First, one or more ventilation openings can be arranged in the cylinder so that the first piston can start moving and convey gas or air through this opening (s), for example into the device housing, so that initially the movement of the first piston is not blocked leads to a significant pressure increase in the space between the first and the second piston. These (openings) are largely closed only when the first piston lli accelerated by the piston drive or its actuator 10 passes over the ventilation openings in the actuator 11, which can result in a much greater, in particular steeper-edged pressure increase in the space between the two pistons of the actuator 11 than it would be in the absence of the vent (s). (ii) Second, the second piston II2 of the actuator 11 can be blocked with the help of a mechanism so that it can only start moving after a certain breakaway force has been exceeded. Corresponding mechanisms can function positively or non-positively and are known, for example, from so-called force limiters and from the locks of guns. Both variants can be combined with each other.

Due to the actuator 11, the setting stroke and the travel by which the gas spring (formed by the actuator 10 and the working gas reservoir 20) is tensioned are largely independent of one another. This simplifies the provision of variable setting energies: only the travel by which the gas spring is tensioned, and thus the stroke volume, have to be set accordingly. This does not change the setting stroke, which is determined by the actuator 11. Further aspects of embodiments with regard to structural features of components of setting devices according to the invention are explained below.

FIG. 2 shows a possible further embodiment of a pneumatic actuator 10 (first actuator) from FIG. 1 for the gas spring.

As explained in detail below, the third piston 10a comprises a plurality of piston rings 15a, with cavities 16a being arranged axially, that is to say along the direction of movement of the third piston 10a, between the piston rings 15a or the piston being designed to have such, the cavities 16a are preferably partially, but not completely, filled with an incompressible fluid.

In Fig. 2, piston 10a with piston rod 11a is arranged in cylinder 12a. Cylinder 12a is designed to have a valve seat 13a towards the high pressure side p1, that is towards the working gas reservoir. Piston 10a is designed as an associated shut-off body. If the clamping device 40 from Fig. 1, preferably by a spring, can exert a sufficient contact pressure on the piston 10a in the locked state, the working gas reservoir is additionally in the locked, cocked (ready-to-fire) state through the valve (formed from piston and cylinder as described) sealed. The role of the valve here corresponds to that of valve 30 from FIG. 1. Piston rod 11a from FIG. 2 is identical to piston rod 01 from FIG. 1.

In FIG. 2, piston 10a has, for example, two piston guide rings 14a. On the other hand, it is characteristic of preferred pistons according to FIG. 2 that piston 10a also has several piston rings 15a, the contact pressure of which can be applied, for example, by O-rings, but also in all other known ways. In FIG. 2 four piston rings 15a are shown, but more or fewer piston rings 15a can be provided. The piston 10a is located between the piston rings 15a further designed to have a plurality of cavities or cavities 16a. These cavities are preferably partially, but not completely, filled with a liquid lubricant.

The multiple cavities in the form of a cascade (i.e. cavities in a row, so that the effect of each cavity is derived from a previous cavity and acts on a subsequent cavity) enable reliable lubrication and even distribution of the pressure to be sealed onto the various seals . The contact pressure per seal can be reduced accordingly and consequently the p * v stress on each individual seal can be reduced accordingly. In the stroke start position shown in Fig. 2, the valve formed by cylinder 12a and piston 10a is closed. In this position, therefore, working gas in order to escape from the working gas reservoir at pressure pl to the low-pressure side pO must first overcome the valve and then the complete cascade of lubricated piston rings and cavities. The leakage from the cascaded, "buffered" and lubricated piston rings (mechanical seals) is determined only during an adjustment process up to the subsequent, complete return of piston 10a to its stroke start position.

A sufficiently tough, hard, particularly wear-resistant and highly polishable steel is proposed as the material for the piston 10a and cylinder 12a. Steels such as 1.4108, i.e. cold work steels and, in particular, pressure-stitched steels with a very fine martensitic structure, further characterized by the absence of coarse-grained carbides or carbonitrides, are particularly suitable, whereby under "coarse-grained" a maximum expansion along a direction of more than 20pm and even with cellular precipitated carbides preferably more than 10pm.

When using steel 1.4108 (material number) for piston 10a and cylinder 12a, a somewhat higher Rockwell hardness is preferred through a corresponding tempering treatment for cylinder 12a set than for piston 10a (e.g. 56-58HRC for the piston, 58-60HRC for the cylinder or its running surface).

In addition to the cold work steels mentioned, newer materials that can be processed with the means of so-called additive manufacturing (e.g. laser sintering) are particularly suitable for pistons and / or cylinders. Particularly noteworthy here are very hard powder-metallurgical steels of sufficient toughness (e.g. Vibenite 290) as well as metallic glasses based on elements of the 4th subgroup.

Piston 10a and the running surface of cylinder 12a can, with great preference, be coated with hard material layers or tribological layers. CVD-deposited, predominantly tetrahedrally coordinated carbon (ta-C) is particularly suitable for coating cylinder 12a or its running surface. Ta-C is also suitable as a coating for the piston 10a, but also aC / WC, TiN, TiMoN (as a solid phase solution or MoN / TiN “superlattice”), TiN-MoS2, and the nitrides, carbides and carbonitrides of Cr, Ti , Zr, Hf and also aluminum oxide (and / or aluminum oxynitride) in amorphous form or as nano- or microcrystalline corundum. Expertly selected, particularly temperature-resistant and abrasion-resistant plastics from the group of polyetheretherketones (PEEK) and / or polyimides are particularly suitable for the piston rings (PI), and / or ultra-high molecular weight polyethylene (UHMWPE), and / or liquid crystalline polyethylene terephthalate, preferably filled with solid lubricants such as PTFE and / or graphite and / or hexagonal boron nitride (hBN) and / or MoS2 and possibly (esp. ceramic) reinforced, in particular with glass fiber, short carbon fiber, pyrogenic silica; more preferably, the piston ring material is also selected according to the friction partner, i.e. the running surface v on cylinder 12a, to have a low coefficient of sliding friction, if possible not to enter into any noticeable adhesion with that, even to have a relatively high thermal conductivity and a low coefficient of thermal expansion. Come for the guide rings Materials based on carbon are particularly suitable, for example graphite impregnated with antimony.

A professional implementation of an actuator 10 (from Fig. 1) like. Fig. 2 allows with outstandingly high pressures (for example at least 10 bar, more preferably at least 20 bar, more preferably at least 40 bar, more preferably at least 60 bar, more preferably at least 80 bar, more preferably at least 100 bar, and more preferably at least 120 bar) and piston speeds (for example at least 30 m / s, preferably more than 50 m / s) without compromising the tightness of working gas reservoir 20 (from FIG. 1).

FIG. 3 shows a further possible embodiment of a pneumatic actuator 10 (first actuator) from FIG. 1.

As explained in detail below, the pneumatic actuator 10 comprises, in addition to the third piston 10b, a fourth piston 11b, a reservoir 13b being formed between the third piston 10b and the fourth piston 11b, which is filled with an incompressible fluid, which is preferably the one below Has executed properties and is matched to the working gas as explained below.

This embodiment according to FIG. 3 thus shows a completely different and novel possibility of realizing the seal of a gas spring. The piston 10i connected or even identical to the piston rod 01 of the actuator 10 (from FIG. 1) is provided in FIG. 3 with the reference symbol 11b. There is also a second piston 10b, which has, for example, two guide rings 14b and, for example, a piston ring 15b. The two pistons 10b and 11b are not rigidly connected to one another. 12b represents the cylinder of the pneumatic actuator (first actuator 10). Added is a reservoir 13b which is arranged in cylinder 12b between the two pistons and is filled with a fluid (incompressible fluid). This is preferably a liquid lubricant in which polymers or oligomers are dissolved and / or solid Lubricants such as MoS2 and / or hBN and / or graphite are dispersed, possibly with the addition of stabilizers, so that the fluid has pronounced shear thinning properties and possibly also shows thixotropic properties (a thixotropy of the fluid in reservoir 13b can cause locking 40 during unlocking mechanically relieve). Reference number 16b refers to a sealing ring, for example a so-called armored carbon ring. The same applies to the selection of materials with regard to the piston and the cylinder, also with regard to any coatings, as stated above for FIG. 2. The person skilled in the art recognizes that this seal is not a decoupling device (as explained above), because the pistons 10b and 11b are not decoupled via the incompressible fluid, but move synchronously with one another. A movement of the piston 10b leads directly to a movement of the piston 11b and vice versa.

FIGS. 4a-c show a possible embodiment of the clamping device, symbolized by 50 in FIG. 1, which moves the piston 10 (FIG. 1). In Fig. 4a, 10c denotes the piston rod 01 from Fig. 1, 11c a lifting member of the piston rod, 20c and 30c two toothed wheels with freewheeling devices located thereon from the components 21-23c and 31-33c (designations in Fig. 4b and 4c analogously with additions d and e).

The gearwheels can be set in rotation by an electric motor marked 70 in FIG. 1 via a reduction gear 60, it being sufficient to drive one of the two interlocking gearwheels. Particularly suitable as the gear 60 is an epicyclic gear, preferably designed with multiple stages (all stages in two-shaft operation). As a result of the engagement of the freewheel device in the piston rod, the rotational movement of the gear 60 and thus also of the gears can be converted into a linear movement. The three images symbolize different operating states of the clamping device. Fig. 4a shows the clamping process in which the piston rod is moved against the working gas (over) pressure pl in the pneumatic actuator 10 (Fig. 1). Here, the travel of the piston and thus the energy stored in the gas spring can be selected: after the desired piston position has been reached, the piston rod is locked against the force of the gas spring with the aid of the locking unit 40 (FIG. 1). The gear wheel 20c with pawl freewheel is driven in a first direction of rotation (by motor 70 via gear 60 from Fig.l), the gear 30c toothed with 20c is thereby moved, but can also be driven by a motor like 20c. Force is transmitted to the piston rod 10c via the pawl freewheel 21c / 22c / 23c or 31c / 32c / 33c. With the power transmission on both sides shown, transverse loads on the associated bearings and / or seals on the piston and / or piston rod 10c can be avoided or reduced. In principle, however, a one-sided drive is sufficient, for example only via gear 20c.

Fig. 4b shows an opposite direction of rotation in which the piston rod is not driven, since the drive links of the freewheel do not interlock with the lifting links of the piston rod. Thus, by operating the electric motor 70 in opposite directions via the intermediate position from FIG. 4b, a position as shown in FIG. 4c can be approached in which any contact between piston rod 10e and freewheel 21-23e / 31-33e on gears 20e / 30e is avoided becomes. During a setting process, that is to say an abrupt axial movement of the piston rod 10e in the direction of the arrow, contact between the drive and lifting links is excluded. The gear wheel position from FIG. 4c can be ensured, for example, by the self-locking of the drive (motor 70 with high gear ratio 60 from FIG. 1); an additional locking is not required.

The pawl freewheel consists of drive members 21c, which are rotatably mounted and have a stop or some form of locking, whereby the piston rod 10c is moved in a direction of rotation of 20c when the drive member 21c and lifting member 11c of the piston rod interlock. In the opposite In the direction of rotation of 20c, however, drive link 21c can be moved largely without resistance via lifting links 11c by moving the drive link around its axis of rotation to such an extent that the lifting link can be moved past. This state is shown in FIG. 4b: drive link 21d gives way to lifting link lld.

The drive links are preferably designed as pawls of a pawl freewheel and can be designed to match the corresponding lifting links (e.g. "teeth") on the piston rod, whereby linear loads between the drive and lifting links are avoided and surface loads are aimed at (Stribeck pressure instead of Hertzian Pressing).

In addition to the drive links and their rotatable mounting with stop / locking device, the freewheel also includes means to move the drive links from an evasive position (as shown in FIG. 4b based on the relative position of 21d and 11d) back into a driving position (as in FIG. 4a). to deliver. This can be, for example, springs 22c with an abutment 23c. One possible implementation would be e.g. Torsion springs (leg springs) coaxially with the rotatable mounting of the drive links, one spring leg being firmly connected to the drive link and the second leg to the gear 20c.

By means of actuator 11 (second actuator) from FIG. 1, the driving energy can now be set independently of the setting stroke simply by means of the travel and thus the stroke volume by which the gas spring is pretensioned. The piston rod 01 preferably has a stiffener perpendicular to the lifting links with which the drive links of the tensioning device 50 interlock or which they engage. This stiffening is used to increase the buckling force which piston rod 01 can safely withstand; it can at the same time be designed to have latching elements on which the latch 40 can act. As an additional means for stiffening, the piston rod can be designed to have stiffening rings. FIG. 5 shows a further alternative embodiment of an actuator, in particular a variant of an actuator 10 (first actuator) from FIG. 1 that is easy to implement. Fig. 2.

As explained in detail below, the pneumatic actuator 10 here comprises a cylinder 12f, the cylinder 12f being designed to have a valve seat 13f, the third piston lOf being designed to act as a shut-off body for this valve seat or to have a corresponding shut-off body so that the third piston lOf and the cylinder 12f together form a valve which can be closed by pressing the third piston lOf and therefore the shut-off body against the valve seat 13f formed by the cylinder 12f or attached to it by means of a sufficient external force.

In Fig. 5, 13f thus shows the valve formed from piston lOf and cylinder 12f, 14f and 17f are guide rings (e.g. made of antimony-impregnated graphite), 15f are piston rings e.g. from the sealing materials already discussed above with regard to FIG. 2. Reference symbols 16f represent rings with a U or also double U profile, which form the cavities already explained with regard to FIG. 2, preferably partially filled with lubricant; these rings are literally threaded onto the piston via the piston rod llf. The pressure required for sealing can then be applied with the aid of the force of the pretensioned (plate) spring assembly 18f and a nut 19f. There is preferably a screw locking lacquer in the thread of nut 19f, which can be filled with metal powder.

In the following, further aspects of the embodiments of the invention are explained, which make it easier for the person skilled in the art to implement the invention in a particularly advantageous manner:

So-called brushless direct current motors are particularly suitable as motor 70, specifically preferably those with axial flux guidance. These achieve the highest power densities with high electrical Efficiency, and their polarization by the permanent magnets causes a sufficient detent torque to - after reduction by gear 60 - a clamping device 50 like. FIGS. 4a-c to be held securely in the state shown in FIG. 4c; the person skilled in the art is therefore not dependent on the self-locking due to the inherent friction of the gear 60 and does not have to provide any additional locking for the tensioning device 50 (for locking 40). The motor 70 can advantageously be designed asymmetrically to have a higher electrical efficiency in the direction of rotation at a rated shaft power in which the gas spring is tensioned (ie, for example, the freewheel device is toothed with the piston rod 01). The motor 70, like the motor control 80, can be actively or passively cooled with air; For particularly demanding applications with particularly high setting frequencies and / or setting energies, evaporative cooling can also be used to cool both assemblies.

The working gas reservoir 20 preferably includes a volume Va for which the following applies with regard to the maximum stroke volume Vh of actuator 10 from FIG. 1: It is preferably Va> = Vh, more preferably Va> = 2 * Vh, more preferably Va> = 3 * Vh and more preferably Va> = 4 * Vh. The operating pressure in the working gas reservoir 20 in the fully tensioned state is preferably at least 10 bar, more preferably at least 20 bar, more preferably at least 40 bar, more preferably at least 60 bar, more preferably at least 80 bar, more preferably at least 100 bar, and more preferably at least 120 bar. Maraging steels are particularly suitable as the material for the working gas reservoir (s). Among these, particularly corrosion-resistant (colloquially "rust-free") types are to be preferred, or appropriate corrosion protection must be provided in some other way. Alternatively, instead of steel, fiber-reinforced plastics, in particular, come into question, which also form one or more diffusion barriers to avoid diffusion losses Layers can be provided. As materials for the working gas reservoirs, hardenable aluminum Wrought alloys such as aluminum 7068 and titanium alloys such as Ti-6A1-V4.

Nitrogen as dry as possible is suitable as the working gas ("as dry as possible" is to be understood here in such a way that the formation of dew can be safely excluded over the entire operating range) (possibly also the risk of hydrogen embrittlement) instead of nitrogen offers the advantage that, due to its high speed of sound, even at comparatively very high piston speeds, gas dynamics play a subordinate role: with heavy gases and high piston speeds, the piston movement initially occurs during a setting process a non-vanishing drop in the working gas pressure felt by the piston crown (the working piston of actuator 10), followed by an increase in pressure ("overshoot") when the piston is suddenly decelerated; this process is associated with irreversibilities, so it reduces the effect degree, and also distributes the force unfavorably over the travel of the gas spring.

On the other hand, polyatomic gases and in particular more than diatomic gases such as CF4 have the advantage of having a lower isentropic exponent, which, given the same starting conditions and the same compression ratio, leads to a lower temperature increase in the working gas during compression (i.e. the tensioning of the gas spring) and thus to lower heat losses - and consequently leads to lower irreversibilities than is the case with monatomic gases. Gas mixtures should also be considered. For example, nitrogen CO 2 can be added to increase the isentropic exponent of the gas mixture. The use of CO 2 as the working gas (working medium) also offers the advantage of being able to store working medium with a very high density in a refill reservoir (reference number 21 from FIG. 1) to compensate for leakage losses. In view of the high operating pressures according to the invention, it is preferable to consider when designing the gas spring: that the respective working gases can no longer be regarded as ideal gases: cohesive pressure and co-volume do not disappear. In any case, it is preferable to coordinate the working gas (whether a pure gas or a mixture) with piston rings and lubricants: The working gas (s) should dissolve in them as little as possible and have the lowest possible diffusivity in them in order to achieve the lowest possible leakage rate to reach. In the present case, a leak rate is to be considered as low as possible if the setting tool enables at least 10,000 subsidence under all normal ambient conditions and can be stored for at least 5 years without refilling with working gas being necessary.

The cylinder and working gas reservoir can be regarded as a piston drive and suffer from a fundamental problem with regard to setting tools with setting pistons: The abrupt movement of the piston mass can lead to a pronounced upward stroke of the setting tool during the setting process and especially when driving the nail or bolt, which affects the quality of the setting can affect.

With regard to fastening quality, this problem is also well known and has already been addressed, see e.g. WO 2019/121016 Al.

In addition, the strong ups and downs lead to a high level of physical strain on the worker. The cause of the high impact is on the one hand that the extended path of movement of the center of gravity of the piston does not usually meet the center of gravity of the setting tool. On the other hand, by holding the setting tool on a handle, which is also next to the path of movement of the center of gravity of the piston, a pivot point D1 is given (constraint). A well-known result is that the setting tool hits hard up and back during a setting process, even while it is being driven in. The present invention is not exempt from this problem. The problem described can, however, at least largely be remedied, as is shown below by way of example, whereby the example is again in no way to be understood as restrictive:

Fig. 6 shows a further preferred embodiment of a hand-held nailing device.

The setting piston 610 (e.g. the second movable part or piston II2 (from FIG. 1) when using the decoupling device) here has at most a quarter of the mass of the drive 600. The drive 600 is particularly advantageously arranged so that it can move axially in the setting device, for example on guides 690.

The piston drive 600 (e.g. gas spring drive, electrodynamic drive or the like) is designed here in such a way that it has a significantly higher mass than the piston 610 itself, preferably at least four times the mass and particularly preferably more than ten times the mass.

The piston drive 600 (in this case, for example (see Fig. 1), motor 70, reduction gear 60, clamping device 50, lock 40, the piston of actuator 10, possibly with valve 30 and working gas reservoir 20) is in or on the setting device along the axis of movement of the piston 610 arranged to be movable, for example with the aid of one or more rails or other guides 690, the extended path of movement of the center of gravity S1 of the piston preferably leading through the center of gravity S2 of the piston drive 600, insofar as this is structurally possible and within the scope of manufacturing accuracy, and the piston drive 600 having at least one stroke start position A and one stroke end position region B. An additional lock 620 fixes the piston drive in a stroke start position A with respect to the remaining parts of the setting device and in particular with respect to its handle 630, provided that no setting process takes place. During a setting process, the lock 620 becomes either active (e.g. with the help of an actuator) or passive (e.g. through the kickback itself), which initially caused the piston drive 600 to return during the setting process a certain travel s' is made possible. The travel s 'is particularly preferably dimensioned so that the driving in of the nail or bolt is completed before the travel is "used up", i.e. before the piston drive 600 has moved backwards by the travel s'. Then shock absorber 640 (e.g. hydraulic damper with Elastomer stop 650 and return spring 660) to become effective, and to brake the piston drive 600 (which can be connected, for example, via flexible strands to the motor control 80 from FIG. 1) via a damping path s ″. Shock absorber 640 is preferably operated in the aperiodic borderline case. The described arrangement requires a resetting device to move the piston drive 600 back into a stroke start position after a setting process and to lock it there with the aid of a lock 620. The simplest way of doing this is by means of a spring, in particular a spiral compression or corrugated ring spring, analogous to the so-called Firing springs of self-loading firearms The return energy can also be used in a known manner for "ammunition transport" (cartridges, nails). During the damping of the return of the piston drive 600, the user experiences a torque on the handle 630 of the setting tool, which, among other things, mechanically stresses his wrist. This torque can also be reduced to the benefit of the worker in that the handle 630 of the setting tool is rotatably connected, for example by means of a joint 670, to, for example, the housing 680 of the setting tool, in which the piston drive 600 is displaceably arranged. This rotary movement can in turn be dampened and reset, which is just as possible with the aid of polymer dampers as with the aid of one or more hydraulic shock absorbers 641 with resetting spring or springs; a lock 621 analogous to lock 620 is possible and may be advantageous if necessary. This locking, if present, preferably unlocks immediately before the still returning piston drive 600 is dampened and in particular after (!) The setting process has been completed. After resetting to the stroke start position by the spring of the second damper 641, for example, the lock 621 closes. In contrast to the prior art, the method described not only improves the setting quality but also greatly reduces the biomechanical stress on the worker, in particular with regard to force peaks occurring during the setting process, which can prevent fatigue and injuries.

It goes without saying that a setting tool which is damped with the above method is heavier than an undamped one due to the components necessary to carry out this method. Roughly, however, the additional weight should be in the range of 3 ... 10% of typical setting tools. Setting devices designed in accordance with the main claim of this application are characterized by a high setting energy density and can in any case be built lighter than e.g. conventional gas spring setting tools. The piston drives of combustion-powered and especially powder-powered setting devices as well as those based on electrodynamic drives (e.g. Thomson coils) can have very high gravimetric setting energy densities and / or very high rates of force increase on the piston, so that the damping method described above appears particularly useful for such devices too, workers from fatigue and protect injuries. The latter may become even more relevant in the future due to stricter occupational safety regulations.

As a result of friction and possibly the force of a return spring 660, for example, holding the handle 630 and the pivot point D1 provided thereby at the joint 670 will still result in a certain, slight upward stroke; To reduce this further, the extended path of the center of gravity S1 of piston 610 cannot be guided precisely through the center of gravity of piston drive 600, but rather be shifted a little in the direction of pivot point D1 parallel to the direction of movement of the piston.

A decoupling device, for example designed with the aid of actuator 11 from FIG. 1, is also capable of other setting devices allow as such with gas spring. For example, extremely powerful electrodynamic drives with movable, mutually repelling coils are known, for example from WO 2012/079572 A2 and WO 2014/056487 A2. For example, a setting device can be implemented in which an electrodynamic drive is preferred instead of a gas spring or a gas spring drive. Fig. 2 from WO 2012/079572 A2 is used, with its movable armature together with its exciter coil A serving as the movable "piston". However, the electrodynamic drives mentioned are not readily suitable as drives for setting tools for the following reasons:

(A) designed for strokes corresponding to the setting strokes of nail setting tools, prohibitively high masses result for the drive;

(B) the piston speeds required in setting tools lead to high dynamic loads on the flexible strands via which the drive is supplied with electrical power;

(C) when using powder composite materials ("SMC") for the armature ("piston"), which enables particularly high electrical efficiency, there is a risk of uncontrolled deceleration of the armature (e.g. when setting in a solid base or incorrectly setting) that this breaks.

Against this background, a further embodiment of a hand-held setting tool comprises an electromagnetic drive, preferably with a Thomson coil actuator, e.g. according to WO 2018/104406 A1 (see e.g. FIG. 1 therein), ie an electrodynamic drive with a first excitation coil, a soft magnetic frame , and a squirrel-cage rotor mounted movably along an axis or a movably mounted short-circuit winding, the soft magnetic frame having a saturation flux density of at least 1.0 T and / or an effective specific electrical conductivity of at most 10 ^L 6 S / m. In this electromagnetic drive, the frame is designed as a "flux concentrator", the first Excitation coil is directly or indirectly counter-supported on the frame and is formed, for example, from fiber-reinforced flat wire. In this embodiment, the hand-held setting tool also has the decoupling device explained above, wherein the movably mounted squirrel-cage rotor or the movably mounted short-circuit winding is formed in a (e.g. slidably mounted) movable element (piston, armature) that controls the movement process of the first movable part or As explained above, the movement process of the first movable part or piston, caused or driven by the moving squirrel-cage rotor, is at least partially decoupled from the movement of the second movable part or piston in the actuator for driving of the nail or bolt, which leads to a reduction in recoil when setting in solid ground.

Another alternative embodiment of a hand-held setting tool comprises an electromagnetic drive according to, for example, WO 2012/079572 A2 or WO 2014/056487 A2 (as explained further below), i.e. an electromagnetic drive with at least a first coil and a second coil, wherein the first coil is formed on or in a flux concentrator and the second coil is a movable coil. In this embodiment, the movable coil is formed in or on a movable element (piston, armature) which effects the movement process of the first movable part or piston in the actuator ("striking mechanism"). As explained above, the movement process of the first movable part is or Piston, caused or driven by the moving coil, at least partially decoupled from the movement of the second movable part or piston in the actuator for driving the nail or the bolt, which leads to a reduction in the recoil.

By means of these embodiments, the problem (A) is eliminated by the decoupling device. The problem (B) with regard to the electrodynamic drive with moving coils can also be eliminated by the decoupling device, since with a short, limited stroke of the electric drive (compared to the setting stroke) the strands can be much shorter and are accordingly exposed to lower inertia forces during operation ; In addition, the supply of electrical power to the movable coil (s) can be released, if necessary, by sliding contacts.

The problem (C) can also be solved by the decoupling device, since the armature (“piston”) is now decelerated in a defined manner: the “armature” or piston is felt by the gas cushion that forms between the two pistons of actuator 11 during a setting process e.g. the electric drive does not have a hard stop.

In further embodiments of electrodynamic drives with moving coils, the drive can be reset in a simple manner: To set, the coils are at least temporarily supplied with current in opposite directions (particularly preferably with the aid of a capacitor discharge) so that repulsive forces act between the coils. The flow of current in opposite directions preferably also leads to mutual compensation of the electromagnetic far field that is generated, so that fewer requirements have to be placed on the shielding properties of a housing of the setting tool. To reset, however, the coils can be energized in the same direction, so that an attractive (Lorentz) force acts between the coils.

FIG. 7 shows, in a further embodiment, an electrodynamic piston drive with moving coils in combination with a decoupling device, for example actuator 11 from FIG. 1. This is a particularly powerful variant of the electrodynamic drive which, with the help of at least one moving coil, predominantly Non-metallic working piston can accelerate with a very high efficiency, and compared with the prior art by a higher electrical efficiency and a lower device mass with the same setting energy. Again, the following statements are in no way to be understood as restrictions. Fig. 7 symbolically shows the setting tool in the "ready to fire" position.

The reference numbers in Fig. 7 represent:

700: supply lines (highly flexible strands)

710: Iron circle (also "flux concentrator"), ie a body made of soft magnetic material. The iron circle preferably has a saturation flux density of at least IT, preferably at least 1.5T and more preferably at least 1.9T and in particular an effective electrical conductivity of at most 10 6S / m, more preferably at most 10 5S / m and more preferably at most 10 4S / m; various soft magnetic composite materials meet these requirements. Because of their brittleness, a soft magnetic composite material is used for iron circle 701, which may be segmented professionally, a crack of 701. The segmentation thus serves the purpose of preventing the tensile strength (and preferably also the yield point) of the soft magnetic composite material from being locally exceeded during a setting process

711: First flat coil attached to the iron circle ("support coil")

720: Drive piston, preferably formed entirely or predominantly from a plastic, in particular a glass fiber-filled liquid crystal polymer, which can be designed to have at least one guide axis

721: Second, movable flat coil ("push coil") fastened to the drive piston or cast in it or overmolded with its material 730: Setting piston with piston rod. Driving energy is transferred to the nail via the piston rod from the setting piston 730

740: Base plate made of soft magnetic solid material, in particular a ferritic steel, is used for shielding (EMC, EMC) and as a heat sink

750: tube made of CFRP, used in particular to relieve strain on iron circuit 710 and to center 710 and 780

760: Tube made of an aluminum alloy, which preferably has the highest possible electrical conductivity, and which in the present case serves to shield alternating electromagnetic fields

761: Tube-shaped, soft magnetic material with a high saturation flux density, in particular ferritic steel. Is used to shield electromagnetic fields. Opposite, tube 761 is shown in a top view with discrete air gaps 762 distributed around the circumference, which in the present case can serve as slots to reduce eddy currents

770: device housing

780: cylinder, for example made of a high-strength steel that can be polished well

790: Armored coal or other guide ring for the piston rod of the setting piston 730

In order to use the in Fig. 7 symbolically illustrated arrangement to set a nail or bolt in a subsurface, capacitor CI is first charged via switching converter SMPS (with a battery-operated setting device, of course, with the help of electrical energy from the battery or batteries BAT). The capacitor CI should have the highest possible energy density and the lowest possible electrical series resistance and a particularly high one Have short-circuit strength. Corresponding capacitors are commercially available as film capacitors especially for pulse applications.

After reaching the desired charging voltage via CI, the thyristor SCR can be ignited to set a nail. Current now flows into the (flat) coils via the leads 700. Both coils are preferably connected in series in such a way that the current in both coils flows in opposite directions during the setting process, so they repel each other. For the coils, Cu flat wire is particularly suitable for achieving the highest possible degree of filling with minimal electrical resistance.

The feed lines 700 can be guided directly through the piston 720 or its (rear) "guide axis"; the feed lines are very preferably made of an aluminum alloy or copper, in particular in the form of fine, highly flexible strands, and are strain-relieved outside the piston 720, for example with Aid of carbon fibers or carbon fiber fabric: It is essential that the strain relief, which is mechanically connected in parallel with the supply lines, consists of a material with sufficient tensile strength - i.e. does not tear under the given conditions - and has a higher tensile modulus than the electrical supply lines themselves, which it is intended to relieve. The strain relief is preferably dimensioned to protect the electrical conductors from tensile stress (during or as a result of a setting process) that exceeds their yield point or even tensile strength. More preferably, the material of the strain relief should have a high specific strength Tissues can meet these requirements. The drive piston 720 (first piston) is designed to form an actuator 11 with the setting piston 730 (second piston) and cylinder 780, i.e. a decoupling device as explained above (e.g. according to FIG. 1).

The preferably gas-dynamic seal in the manner of the pistons of labyrinth piston compressors is also not shown in FIG. 7 drawn in as well as any necessary guide elements and similar details. Devices for resetting the pistons are also not shown.

The invention can be implemented in practice as follows: The drawing, including the circuit diagram, is transferred to an FEM model and the geometry is parameterized, with corresponding (material) properties being assigned to the individual components in the list of reference symbols. Real properties are assumed for the electrical components, i.e. the circuit diagram is shown in the model with a corresponding equivalent circuit diagram. For the gas spaces at least the Van der Waals equation is applied and solved in order to approximate the corresponding gas forces on the surfaces; if necessary, the gas dynamics can also be taken into account. The number of turns of the first flat coil 711 and of the second movable flat coil 721 are preferably the same, so that, as a result of being connected in series, they always generate (almost) the same flux. Then a parametric optimization is carried out ("parametric sweeps"), whereby constructive, e.g. production-related requirements - for example minimum wall thicknesses, representable (flat) wire thicknesses, etc. - are taken into account; otherwise, (all) geometric parameters and the number of turns are varied and it becomes Looking for a Pareto optimum, also taking into account the prices for parts, components, materials and approval requirements (EMC, EMC, etc.). Based on the optimum found in this way, a mechanical engineering design can then take place, which is already due to questions of assembly and production differ from the initially simple FEM model, be more complicated and possibly contain other components to be taken into account. Based on this construction, a new parametric FEM optimization is carried out. This process, carried out professionally, results in an extraordinary one after a few iterations h powerful setting tool. For example, drives with an iron circle with a diameter of only d = 60mm can easily achieve driving energies of over 500J with efficiencies in the range of 50%. This energy range has been reserved for internal combustion-powered setting tools, in particular powder tools.

Further embodiments are given by:

El. Hand-held setting tool for setting nails and / or bolts in a substrate, comprising:

at least one electrochemical energy store 90, for example an accumulator or a fuel cell

at least one motor controller 80, preferably comprising an inverter

at least one electric motor 70, preferably a brushless direct current motor, more preferably with axial flux guidance

at least one reduction gear 60, preferably a multi-stage epicyclic gear

- At least one tensioning device 50, preferably comprising a pawl freewheel

- at least one lock 40

- At least one working gas reservoir 20 containing a working gas, which can also be a mixture of different pure gases, as well

- At least one pneumatic actuator 10, wherein

the pneumatic actuator 10 comprises at least one piston with a piston rod 01, is in fluid connection with the working gas reservoir 20, and forms a gas spring together with the working gas reservoir 20,

wherein the actuator 10 has a stroke start position in which the gas spring is stretched to the maximum, and a stroke end position range in which the gas spring is less stretched, characterized in that the working gas reservoir 20 with the gas spring stretched to the maximum under a working gas pressure of more than 10 bar, more preferably more than 20 bar, more preferably more than 40 bar, more preferably more than 60 bar, more preferably more than 80 bar, more preferably more than 100 bar and particularly preferably more than 120 bar, and the volume of the working gas reservoir 20 is at least the same , preferably more than twice the size, further is preferably more than three times as large, and more preferably more than four times as large as the maximum stroke volume of the pneumatic actuator 10, wherein the gas spring is first tensioned to set a nail by the electric motor 70 with the help of motor control 80 with electrical power Energy storage 90 is supplied and controlled to drive via reduction gear 60 clamping device 50, which in turn can convert the torque of reduction gear 60 into a force to move the piston of actuator 10 against the pressure of the working gas, after reaching a desired piston position actuator 10 by means of locking 40 is locked, the gas spring consisting of actuator 10 and working gas reservoir 20 is held in a higher tensioned state, and locking 40 is released to set a nail, so that the gas spring relaxes, actuator 10 is set in motion, and then kinetic energy of the moving parts of actuator 10, including de This piston is used to drive in the nail, either directly or with the aid of an additional hammer mechanism 11.

E2. Setting device according to E1 characterized in that the setting device is dimensioned such that the maximum kinetic energy of the moving parts of actuator 10, expressly including all parts firmly connected to the piston of actuator 10, reaches at least half of the ultimately effective driving energy during an actuating process.

E3. Piston for a pneumatic actuator and in particular a gas spring, characterized in that it comprises a plurality of piston rings, and that axially, that is, along the direction of movement of the piston, cavities are arranged between the piston rings or the piston is designed to have cavities, which are preferably partially are filled with a lubricant, but not completely.

E4. Piston for a pneumatic actuator and in particular a gas spring characterized in that it has several, for example comprises two pistons which are not rigidly connected to one another and between which there is a fluid.

E5. Piston for a pneumatic actuator according to E4, characterized in that the fluid is a liquid lubricant.

E6. Piston for a pneumatic actuator according to claim E5, characterized in that the fluid is a non-Newtonian fluid, in particular a shear-thinning fluid, which preferably also has thixotropic properties.

E7. Piston for a pneumatic actuator according to E6, characterized in that the non-Newtonian and in particular structurally viscous fluid, which is preferably also thixotropic, is produced by dispersing one or more solid lubricants such as, for example, hBN and / or graphite and / or MoS2 and / or the Dissolving one or more oligomers or polymers in the liquid lubricant is represented.

E8. Pneumatic actuator comprising a cylinder and a piston according to one or more of the pistons according to E3 to E7, characterized in that the cylinder is designed to have a valve seat, and that the piston is designed to act as a shut-off body for this valve seat or a corresponding shut-off body so that the piston and cylinder together form a valve which can be closed by pressing the piston and thus the shut-off body against the valve seat formed by the cylinder or attached to it by means of a sufficient external force.

E9. Impact mechanism for a setting tool characterized in that it transfers kinetic energy of a first piston of a piston drive to a movable part, for example a second piston, and the nail or bolt is driven entirely or predominantly with the aid of the kinetic energy of the movable part, the first Piston and moving part not rigid are connected to one another, whereby the first piston and the movable part are decoupled with respect to their stroke lengths.

E10. Impact mechanism for a setting tool, comprising at least a first and a second piston and a cylinder, the pistons being arranged opposite one another, i.e. as in opposed piston engines, in the cylinder, with gas-dynamic seals such as labyrinth seals preferably being provided as sealing means instead of piston rings , and wherein the first piston is driven to transmit momentum to the second piston via gas located between the pistons, and, for example via a piston rod, the kinetic energy of the second piston can be used to drive a nail and / or bolt or for hammer drilling can.

Hurry. Impact mechanism according to E10, characterized in that a reset device is provided for a second piston.

E12. Striking mechanism according to claim E10 or Eil, characterized in that the pistons and / or the running surface of the cylinder are hard chrome-plated.

E13. Hand-held setting tool comprising at least

an axially movable piston drive mounted in or on the setting tool with one or more stroke start positions and a stroke end position area

- A piston which can be driven by the piston drive and which preferably has at most a quarter of the mass of the piston drive

- An openable lock which is able to fix the piston drive in one or more stroke start positions

a shock absorber such as a hydraulic shock absorber

- A resetting device, for example a resetting spring, which is able to move the piston drive back from its stroke end position range to a stroke start position with respect to the setting tool, characterized in that the lock opens or can be opened during a setting process, so that the Piston drive can move through the kickback felt by it from a stroke start position in the direction of the stroke end position range, this return of the piston drive can be braked by the shock absorber, whereby the piston drive is preferably only braked after a return by a certain return distance from the shock absorber, and the return distance so is dimensioned that the nail or bolt is predominantly or, preferably, fully driven in before the shock absorber becomes effective and brakes the return of the piston drive.

E14. Hand-operated setting tool according to E13, characterized in that in the reference system of the setting tool the extended paths of the centers of gravity of the piston or pistons is or are parallel to the extended movement path of a movable piston drive.

E15. Hand-operated setting tool according to E13 or E14, characterized in that the extended path (s) of the center of gravity (s) of the piston or pistons lead or lead through the center of gravity of the piston drive at least during the driving in of the nail or bolt, which in the present case leads to It should be understood that during driving the minimum distance of the said extended path (s) to the center of gravity of the piston drive is always at least five times, but preferably more than ten times less than the minimum distance of those same elongated paths to the center of gravity of the entire setting tool.

E16. Hand-operated setting tool according to one or more of E13 to E15, characterized in that the setting tool has at least one handle, and that this handle is rotatably mounted with respect to a part of the setting tool, in or on which a piston drive is axially movably arranged, with at least one mechanical damper , for example a hydraulic shock absorber or a polymer damper, is provided to dampen a rotary movement between the handle and the part to which the handle is rotatably connected, whereby a lock can be provided that such a rotary movement is blocked while none Setting process takes place. E17. Setting device comprising an impact mechanism according to one or more of E9 to E13, the piston drive being an electrodynamic drive and the mass accelerated by the piston drive is to be understood as a piston or comprises the mass of the first movable part of the impact mechanism according to E9.

E18. Setting tool according to E17, characterized in that the electrodynamic claim comprises at least one excitation coil and at least one movable second coil or one movable short-circuit winding, which can preferably be arranged on a part made of soft magnetic material that is displaceable along a movement axis, the soft magnetic material preferably having a saturation flux density of has at least 1.5T and more preferably an effective specific electrical conductivity of at most 10 ^L 6 S / m.

E19. Hand-held setting tool for setting a nail or a bolt in a substrate, comprising: a drive 600, preferably a gas spring drive or an electrodynamic drive, which drives a setting piston 610 which is used to drive the nail or the bolt into the substrate; characterized in that the setting piston 610 has at most a quarter of the mass of the drive 600.

E20. Hand-operated setting tool according to E19, the drive 600 being arranged in the setting tool so that it can move axially, preferably on guide elements 690.

E21. Hand-operated setting tool according to E20, an openable lock 620, which is designed to fix the drive in one or more stroke start positions; a shock absorber 640 such as a hydraulic shock absorber; a restoring device, for example a restoring spring, which is designed to move the drive back from a stroke end position to a stroke start position with respect to the setting tool; being in the course of a Setting process, the lock 620 opens or can be opened, so that the drive 600 can move from a stroke start position A in the direction of the stroke end position area due to the kickback felt by it, whereby this return of the drive 600 can be braked by the shock absorber 640, whereby the drive 600 is preferred is only braked by the shock absorber 640 after a return by a predetermined return distance s', and the return distance is dimensioned so that the nail or bolt is predominantly or, preferably, completely driven in before the shock absorber 640 becomes effective and brakes the return of the drive.

Claims

Expectations

1. Hand-held setting tool for setting a nail or a bolt in a ground, comprising: a drive, preferably a gas spring drive or an electrodynamic drive, which drives an actuator (11) which is used to drive the nail or the bolt into the ground; characterized by: a decoupling device having a first

Movement process of a first movable part or piston (III) in the actuator (11), driven by the drive, at least partially by a second movement process of a second movable part or piston (II2) in the actuator (11) for driving in the nail or bolt decoupled.

2. Hand-held setting tool according to claim 1, wherein the

Decoupling device is designed such that kinetic energy of the first movable part or piston (III) is transferred to the second movable part or piston (H2), and kinetic energy of the second movable part or piston (H2) is used to drive in the nail or the bolt becomes.

3. Hand-held setting tool according to one of claims 1-2, wherein the first movable part or piston (III) is not rigidly connected to the second movable part or piston (II2).

4. Hand-held setting tool according to one of claims 1-3, wherein a compressible fluid, preferably air, is located between the first movable part or piston (III) and the second movable part or piston (H2).

5. Hand-held setting tool according to one of claims 1 - 4, wherein the first movable part or piston (lli) has a first

Has stroke length and the second movable part or piston (112) has a second stroke length, the first and second stroke lengths being decoupled.

6. Hand-held setting tool according to one of claims 1-5, wherein the actuator (11) further comprises a cylinder, wherein the first piston (lli) and the second piston (H2) are arranged opposite one another in the cylinder, and in which Cylinder is formed at least one piston seal.

7. Hand-held setting tool according to claim 6, wherein the

Piston seal at least comprises: one or more piston rings and / or

a gas dynamic seal, preferably from the labyrinth

Piston compressor type.

8. Hand-held setting tool according to one of claims 1 - 7, wherein for the second movable part or piston (H2) one

Reset device is formed.

9. Hand-held setting tool according to one of claims 1 - 8, wherein the first movable part or piston (III), the second movable part or piston (H2) and / or a cylinder running surface are hard chrome-plated.

10. Hand-held setting tool according to one of claims 1 - 9, further with a further actuator (10) in the drive, the further actuator (10) causing the first movement process in the actuator (11).

11. Hand-held setting tool according to claim 10, wherein a setting stroke of the second movable part or piston (II2) in the actuator (11) of a travel of the further actuator (10) are independent of one another.

12. Hand-held setting tool according to one of claims 10-11, wherein the drive is a gas spring drive, further comprising: at least one working gas reservoir (20) with a working gas, wherein the further actuator (10) is a pneumatic actuator (10), the pneumatic Actuator (10) comprises a third piston (10i) with a piston rod (01), the third piston (10i) being in fluid connection with the working gas reservoir (20) and, together with the working gas reservoir (20), forming a gas spring, the pneumatic spring The actuator (10) can be moved between a stroke start position area in which the gas spring is tensioned to the maximum and a stroke end position area in which the gas spring is at least partially relaxed.

13. Hand-held setting tool according to claim 12, wherein the third

Piston (10i, 10a) comprises a plurality of piston rings (15a), and wherein axially, that is to say along the direction of movement of the third piston (10i, 10a), between the piston rings

(15a) cavities (16a) are arranged or the piston is designed to have such, wherein the cavities (16a) are preferably partially, but not completely, filled with an incompressible fluid.

14. Hand-held setting tool according to claim 12, wherein the pneumatic actuator (10) next to the third piston (10i, 11b) has a fourth piston (10b), wherein between the third piston (10i, 11b) and the fourth piston (10b) Reservoir (13b) is formed which is filled with an incompressible fluid.

15. Hand-held setting tool according to claim 13 or 14, wherein the incompressible fluid is a liquid lubricant.

16. Hand-held setting tool according to claim 13 or 14, wherein the incompressible fluid is a non-Newtonian fluid, preferably a shear-thinning fluid and / or a fluid with thixotropic properties.

17. Hand-held setting tool according to claim 16, wherein the non-

Newtonian and in particular pseudoplastic fluid, which is also preferably thixotropic, is formed by dispersing one or more solid lubricants, preferably hexagonal boron nitride and / or graphite and / or MoS2 and / or dissolving one or more oligomers or polymers in a liquid lubricant.

18. Hand-held setting tool according to one of claims 12-17, wherein the pneumatic actuator (10) comprises a cylinder (12a, 12f), wherein the cylinder (12a, 12f) is formed, one

To have valve seat, and wherein the third piston (10i, 10a) is designed to be able to act as a shut-off body for this valve seat or to have a corresponding shut-off body, so that the third piston (10i, 10a) and the cylinder together form a valve which is closed can be by means of a sufficient external force of the third piston (10i, 10a) and thus the

Shut-off body is pressed against the valve seat formed by the cylinder (12a, 12f) or attached to it.

19. Hand-held setting tool according to one of claims 1-11, wherein the drive is an electrodynamic drive, comprising: a first excitation coil; a soft magnetic frame, and one mounted movably along an axis

Squirrel-cage rotor or movably mounted

Short-circuit winding that is formed in a movable element that causes the movement process of the first movable part or piston (III) in the actuator (11), the soft magnetic frame having a saturation flux density of at least 1.0 T and / or an effective has a specific electrical conductivity of at most 10 ^L 6 S / m.

20. Hand-held setting tool according to one of claims 1-11, wherein the drive is an electrodynamic drive which has at least a first coil (711) and a second coil (721), the first coil (711) on and / or in one Flux concentrator (710) is formed and the second coil (721) is a movable coil which is formed in or on a movable element (720) which is the

Movement process of the first movable part or piston (lli) in the actuator (11) causes.

21. Hand-held setting tool according to claim 20, wherein, during a setting process, an electrical current flow in the first coil (711) is at least temporarily opposite to an electrical current flow in the second coil (721), whereby the two coils repel one another.

22. Hand-held setting tool according to one of claims 1 - 21, wherein the second movable part or piston (H2) as

Setting piston (610) has at most a quarter of the mass of the drive (600).

23. Hand-held setting tool according to one of claims 1 - 22, wherein the drive (600) is arranged to be axially movable in the setting tool.

24. Hand-held setting tool according to one of claims 1 - 23, further comprising an openable lock (620) which is designed to fix the drive in one or more stroke start positions; a shock absorber (640), for example a hydraulic shock absorber, a return device, for example a

Return spring which is designed to move the drive back from a stroke end position area to a stroke start position with respect to the setting tool; during the course of a setting process, the lock (620) opens or can be opened so that the drive (600) can move from an initial stroke position (A) in the direction of the end-of-stroke position due to the kickback it senses, with this return of the drive (600) can be braked by the shock absorber (640), the drive (600) preferably not being braked by the shock absorber (640) until it has returned a predetermined return distance (s'), and the return distance is dimensioned such that the nail or bolt predominantly or , preferably, is fully driven before the shock absorber (640) takes effect and the

Return of the drive brakes.

25. Hand-held setting tool according to one of claims 1-24, wherein in the reference system of the setting tool an extended path of the center of gravity (Sl) of the second movable part or Piston (H2, 610) is parallel to the extended path of movement of a movable drive.

26. Hand-held setting tool according to claim 25, wherein the extended path of the center of gravity (Sl) of the second movable part or piston (H2, 610) at least during the

Driving in the nail or bolt leads as close as possible through the center of gravity (S2) of the drive, with a minimum distance of the extended path (S1) to the center of gravity (S2) of the drive always at least five times, but preferably more than ten times is less than the minimum distance between the extended track and the center of gravity of the entire setting tool.

27. Hand-held setting tool according to one of claims 1 - 26, wherein the setting tool has at least one handle (630), and wherein the handle (630) is rotatably mounted relative to a part of the setting tool, an axially movable drive being arranged in or on the setting tool is, wherein at least one mechanical damper (641), for example a hydraulic shock absorber or a polymer damper, is provided to dampen a rotary movement between the handle (630) and the part to which the handle is rotatably connected, with at least one device (621) is provided to block a rotary movement while no setting process takes place.