Work apparatus including electro-pneumatic impact mechanism

Abstract

An operating device includes an electro-pneumatic impact mechanism (100) and a compressor. The air-spring impact mechanism has at least one vent, wherein the compressor is connected to at least one vent of the impact mechanism and is capable of compressing ambient air and supplying it as compressed air to the impact mechanism. The operating device preferably has an air filter (132) connected in series with the compressor, enabling the compressor to supply filtered compressed air to the impact mechanism. The operating device also preferably has at least one first pressure reducing valve (141, 142) capable of reducing the pressure p1 of the compressed air generated by the compressor to a specific value p2 before the compressed air is supplied to the impact mechanism. The compressor and / or the first pressure reducing valve are preferably controllable.

Description

Technical Field

[0001] This invention relates to working equipment including an electro-pneumatic impact mechanism. The working equipment refers to a working equipment having an electrically driven air spring impact mechanism. Background Technology

[0002] Electro-pneumatic impact mechanisms typically use an electric motor to drive a first piston to perform axial reciprocating motion. The first piston then drives a second piston, also known as a floating piston, via an air spring, which also performs reciprocating motion.

[0003] The floating piston is thus caused to periodically impact the end face of the hammer or tool. An air spring between the floating piston and the first piston protects the actuator—including an electric motor and optional gears—from mechanical backlash, particularly hard impacts. The floating piston thus strikes the end face of the tool like a hammer, either directly or by means of an intermediate hammer. These impacts, for example, allow for effective drilling or chiseling in hard materials with high energy input and consistent impact force.

[0004] Such devices are commonly known in the prior art, for example, as hydraulic breakers, chisels, and drill hammers. The disadvantages and limitations of such devices are also generally known. Summary of the Invention

[0005] Technical issues In this application, the object of the present invention is to provide a general improvement to working equipment including an electro-pneumatic impact mechanism. At least, Its power-to-weight ratio should be improved, and / or Its efficiency should be improved, and / or The pressure peaks occurring in the air spring impact mechanism should be reduced.

[0006] Furthermore, the user should preferably be effectively protected from harmful arm vibrations caused by the impact mechanism. Additionally, the tool should preferably be protected against dust ingress; in particular, the actual impact mechanism should preferably be highly protected against dust contamination.

[0007] Solution This objective is achieved by a working device comprising an electro-pneumatic impact mechanism according to any one of claims 1 to 18. The working device according to this disclosure is, for example, a working device comprising an electrically driven air spring impact mechanism, such as a hydraulic breaker, chisel hammer, or drill hammer. Attached Figure Description

[0008] Figure 1 An example configuration of the impact mechanism component according to the present invention is shown schematically.

[0009] Figure 2An alternative linear actuator (instead of, as shown in) is illustrated for the impact mechanism assembly according to the invention. Figure 1 Example configuration of a rotary motor (in the example).

[0010] Figure 3 The cross-section of an impact mechanism that can be advantageously used in a working device according to the invention is shown schematically.

[0011] Figure 4 An example configuration of a working device (e.g., a hydraulic breaker or chisel) according to the invention, including an electro-pneumatic impact mechanism, is schematically shown. Detailed Implementation

[0012] The objective of this invention is achieved by pressurizing the impact mechanism with the aid of a compressor, that is, by increasing the amount of air contained in the impact mechanism and thus increasing the so-called filling level.

[0013] In the device according to the invention, the drive is preferably performed directly by a motor, which is configured, for example, a linear drive or a rotary motor. Direct drive eliminates the (reduction) gears required in conventional equipment. This saves the weight of gears, as well as the weight of the gearbox and lubricant. This also saves installation space. There are no gears, and therefore no gear losses, which can account for as much as 20% of the drive power in a conventional arrangement.

[0014] The device according to the invention can be constructed without an external power source, in a manner where power is supplied by batteries. The savings in weight and installation space allow for the use of more batteries while maintaining the same total weight of the device. As a result, the operating time or instantaneous power of the battery-powered device can be increased. At a given electrical power, increasing the number of batteries results in lower ohmic losses at the battery's internal resistance during operation, thereby improving overall efficiency.

[0015] The operating device according to the invention preferably comprises both an electrically driven air spring impact mechanism and a compressor, the air spring impact mechanism including at least one vent. The compressor draws in ambient air, compresses the ambient air, and can supply it to the air spring impact mechanism via the vents (multiple). The air spring impact mechanism can thus be supplied with compressed air. Preferably, at least one air filter is provided to filter the air drawn in by the compressor before and / or after compression, such that the air can be assumed to be substantially dust-free.

[0016] As a result, the air spring impact mechanism can initially operate at a much higher fill level than existing technologies.

[0017] At first glance, the invention seems incredible in several respects: The power-to-weight ratio should be improved, i.e. reduced. However, the compressor is an additional component or part and therefore adds to the weight.

[0018] The heat loss of a compressor is generally known. By compressing the working gas, the compressor not only increases the pressure but also its internal energy and thus its temperature. As a result, most of the compression work usually manifests as waste heat, even in the absence of friction. Compressed air powered machines are therefore known for their low overall efficiency.

[0019] Increasing the pressure and fill level of the air spring impact mechanism also seems like a far-fetched way to reduce pressure peaks.

[0020] Regarding (1): The present invention can be understood based on known working devices including electro-pneumatic impact mechanisms. A preliminary examination of such an impact mechanism reveals the following: increasing the fill level by a factor of N, where N > 1, if the mass of the floating piston is also increased by a factor of N, results in a factor of N increase in the same pressure ratio in the air spring and the impact energy at the same impact frequency (assuming the impact mechanism is supplied with a factor of N average mechanical power during operation).

[0021] However, if the mass of the floating piston does not increase by N times or increases by less than N times when the fill level increases by N times, a lower compression ratio and therefore a lower pressure ratio can be achieved in the impact mechanism, resulting in a correspondingly lower heat loss.

[0022] For example, if the fill level increases by a factor of N and N > 1, the cross-section of the impact mechanism can be reduced to 1 / N of its original size. If the mass of the floating piston remains constant, for example, because its length increases by a factor of N, the pressure ratio in the impact mechanism does not need to change. The impact energy also does not necessarily change. However, the inner diameter of the impact mechanism can be reduced to 1 / N of its original size. .

[0023] One advantage of this invention is the ability to use long floating pistons. In a narrow sense, a long floating piston refers to a floating piston whose length L is subject to the formula: L > ΔPmax / * 9.81 Nkg -1 ),in is the average density of the floating piston, and ΔPmax is the maximum pressure difference experienced by the floating piston during operation when it is attracted by the excitation piston.

[0024] In a broad sense, a floating piston is considered long if its length is at least twice its diameter.

[0025] Using a long floating piston has several advantages: Long (“slender”) floating pistons can generate a more favorable form of impact at the hammer or in the tool, characterized by a more sustained compression wave followed by a steeper transition to a decompression wave, resulting in increased crushing performance while maintaining the same impact energy.

[0026] Furthermore, a long floating piston facilitates the achievement of the required seal in a contactless manner, especially with the aid of aerodynamic seals, such as the type used in so-called labyrinthine axial piston compressors. Conventional, simple (single-stage) mechanical seals inevitably suffer wear, which can be exacerbated when their so-called pv value is exceeded (the pv value is the product of the pressure p to be sealed and the displacement velocity v). Contactless seals are virtually wear-free and do not have any pv value that can be exceeded. Contactless seals also enable operation of such impact mechanisms at higher floating piston speeds, allowing for the use of lighter floating pistons and thus lower recoil at the same impact energy. When determining the size of the floating piston in an impact mechanism, its elastic deformation during impact (against the impact hammer) must be considered. This dynamic deformation must under no circumstances cause the floating piston to jam in the cylinder (or the excitation piston configured as the cylinder).

[0027] Regarding (2): No compressor power is actually required during the operation of the impact mechanism, which is why the inherent inefficiency of the compressor is irrelevant in this application. At most, the frictional power of the compressor must be considered. The compressed air available from the compressor is preferably filtered, making further improvements possible: For example, compressed air can be used as sealing air to prevent dusty ambient air from entering the impact mechanism and thus prevent it from becoming contaminated with dust. Compressed air can also be used to compensate for the gap between the driving tool and the substrate: because the tool uses compressed air to continuously press against the substrate via the impact hammer, a firm contact between the tool and the substrate can be ensured even at high impact frequencies during the impact of the floating piston (against the impact hammer). In addition, compressed air can be used to provide pneumatic or electro-pneumatic vibration isolation.

[0028] The pressurized impact mechanism according to the present invention has further advantages. For example, after the floating piston impacts, more pneumatic energy can be used to reset the floating piston (in the direction of the excitation piston).

[0029] Regarding (3): In the adiabatic approximation, using a pressurized gas spring, when the deflection x of the gas spring reaches a certain reaction force F(x), corresponding to a certain pressure p_x, it results in a smaller difference from the initial pressure p_0 of the gas spring in the neutral position where there is no force F(x=0)=0: F(x)=A* (p_0* (V_0 / V_x)^gamma-p_0). Therefore, the quotient p_0 / p_x increases with increasing p_0, and the temperature rise in the compressed gas associated with the deflection of the gas spring is correspondingly lower, which reduces wall losses (heat loss and therefore energy loss and efficiency reduction).

[0030] The present invention will now be described with reference to several embodiments, which should not be construed as limiting, but are merely intended to facilitate the implementation of the invention.

[0031] In the example, the excitation piston of the impact mechanism is driven directly or indirectly by a linear or rotary motor. The same motor can drive a compressor or function as a compressor itself. The compressed air thus available can, among other things, influence the (pressurized) air spring impact mechanism.

[0032] Figure 1 The embodiments illustrated herein represent possible configurations of an impact mechanism assembly according to the invention, comprising an (air spring) impact mechanism 100 for driving a tool, an electric motor 110, a compressor 120, two air filters 131 and 132, two pressure reducing valves 141 and 142, an optional heat exchanger 150, and a fan 160 for cooling the electric motor. Both the compressor 120 and the pressure reducing valves 141 and 142 can be configured to be controllable. The first air filter 131 can be larger and coarser than the smaller and finer second air filter 132.

[0033] The rotary motor or electric motor 110 according to the invention preferably has a lower base speed range (e.g., a lower base speed range than a conventional radial flux synchronous motor with the same power). Alternatively, one or more gear stages may be provided between the motor 110 and the impact mechanism 100. Axial flux motors, especially those without a yoke (so-called "YASA motors"), can have a suitable speed range and a good power-to-weight ratio. Also suitable for carrying out the invention are vernier motors configured as radial flux motors, particularly permanent magnet-excited motors, and among these are external rotor motors. Transverse flux motors and synchronous motors with radial flux guidance and dual rotors are also suitable.

[0034] If the motor 110 is a rotary motor, it is preferably mechanically connected to the excitation piston via a crank or oscillating drive mechanism in order to convert the rotational motion of the motor into linear oscillation of the excitation piston.

[0035] The compressor 120 is also driven via the output shaft of the motor or electric motor 110; an eccentric pump, particularly a rotary vane pump, which can be directly mounted on the shaft, is particularly suitable for this purpose. Greater integration of components can be achieved by combining parts of the same function, for example, if the motor housing also serves as the pump housing. Air filters 131 and 132 remove dust from the outside air before it is supplied to the compressor or impingement mechanism.

[0036] Valves 141 and 142 can be used to reduce the pressure of the generated compressed air to a certain level or predetermined value before it is supplied to the compartment of the air spring impact mechanism 100, or before it is converted into sealing air. Depending on the compression ratio and the thermal coupling of the wiring network with the surrounding environment, a heat exchanger 150 may be required to cool the compressed air. Preferably, a fan 160 is also mounted on the motor shaft, which is used to cool the motor using uncompressed ambient air (“cooling air”) filtered by air filter 131. The motor 110 can thus be configured to be directly air-cooled, or, for example, a liquid-cooled heat exchanger (not shown) for the motor 110 can be supplied with cooling air. By accordingly directing this cooling air, an air curtain can also be formed to limit / direct dust when handling substrates, for example, to protect users from dust exposure.

[0037] Use as in Figure 2 The linear driver in the illustrated embodiment replaces that in Figure 1 The rotary motor eliminates the need for a crank or oscillating drive mechanism, which would otherwise be necessary. In the device according to the invention, the linear-acting machine is advantageously combined with a double-acting gas spring. This gas spring is tensioned as the drive piston of the linear machine approaches its respective end positions (which are also the reversal points of the linear motion), resulting in the drive piston being first braked and then accelerated in the opposite direction. As a result, the necessary reversal of motion is advantageously achieved mechanically without a “hard impact,” while imparting a high initial acceleration to the drive piston in the opposite direction, which increases the electrical efficiency of the linear actuator. It is also advantageous for the efficiency of the linear machine that current is supplied only at high drive piston speeds, i.e., when the drive piston speed is above a predetermined threshold.

[0038] Figure 2 It includes a linear motor 210, which in turn consists of a stator 211 and a rotor with permanent magnets 212, which drives the excitation piston of the impact mechanism on one hand. Figure 2On the left side, the rotor may be configured such that, on the other hand, the rotor is configured to (drive) piston 213 or mechanically connected to such a piston, or directly or indirectly (e.g. via an incompressible fluid) connected to such a piston that divides volume 220 into two variable partial volumes 221 and 222. Partial volumes 221 and 222 together with piston 213 form a gas or air spring having a double-acting piston 213.

[0039] Due to the connection of the two check valves 231 and 232, the partial volume 222 is further divided into the area on the right side of the valve connection, which acts as a gas or air spring, and the working volume between the piston 213 and the valve connection.

[0040] The volume 220 thus combines the functions of a compressor and a double-acting gas spring, which allows the rotor 212 to return to the middle position of its stroke.

[0041] Intermittently supplied and compressed air can be stored in a compressed air reservoir (not shown) and used for the same purpose as in the foregoing embodiments, namely, it can be supplied to the compartment of the air spring impact mechanism 100, which allows the impact mechanism to start more quickly.

[0042] By combining a gas spring with a linear actuator 210, the stroke end position of the linear actuator is defined; more specifically, the rotor brakes and reverses its direction of motion as it approaches the stroke end position. The kinetic energy of the rotor and the components connected thereto can thus be recovered. In embodiments of the invention with a linear motor, the gas spring functionally replaces a crank or oscillating drive mechanism (in embodiments of the invention with a rotary motor) and, together with a valve, can also function as a compressor according to the invention. By means of a double gas spring acting toward the middle position of the stroke or a gas spring with a double-acting piston supporting the reciprocating motion of the rotor, it is possible to achieve high rotor speeds in both directions of motion (i.e., parallel or antiparallel to the impact direction) for a large portion of the stroke during operation; the incremental characteristics of the gas spring have a beneficial effect. For the purposes of the invention, "high" means that the rotor speed is at least in the upper range of the linear motor's base speed range and / or even within the field weakening range. According to the invention, during operation, electrical power is supplied to the linear motor entirely or primarily if and only if the rotor has been reversed by the action of the gas spring and the rotor has a high speed according to numerical values. Electrical power is therefore preferably supplied to the linear motor in the upper range of the base speed range and / or in the field weakening range (of the rotor). It is also highly preferred that operation occurs entirely or primarily in the upper power range of at least 50%, and preferably at least 80%, of the linear motor's rated power; according to the invention, prolonged operation at low currents is to be avoided. Furthermore, the rotor is preferably electromagnetically driven in both directions of motion, i.e., when moving in the direction of impact and when moving in the opposite direction of impact.

[0043] Operate as follows: Electrical power is supplied entirely or primarily at speeds above a specific minimum rotor speed (i.e., at high speeds); and / or The motor operates entirely or primarily in the high power range, i.e., is supplied with high current; and / or The motor is driven (i.e. supplied with electrical power) in two directions of motion. This enables higher electrical efficiency, higher power density, and a favorable power-to-weight ratio for linear machines.

[0044] Figure 3 It is a schematic and cross-sectional representation of the impact mechanism, as it can be advantageously used in the working device according to the invention. Figure 3 Specifically shown are the excitation piston 300, cylinder 310, tool (e.g., chisel) 320, hammer 330, annular space 340 between hammer and tool, (long) floating piston 350, mechanical seal 360, non-sealed guide ring 370, stop 380 (e.g., made of polymer), vents 391 and 392 of the actual impact mechanism, vents 393 and 394 of the hammer guide, and air supply section 395 of the annular space.

[0045] During operation, compressed air can be supplied to the impact mechanism via vents 392 and 391 between the floating piston 350 and the hammer 330, and between the floating piston 350 and the excitation piston 300, which are thereby connected to a common volume that can be formed by the housing. According to the invention, the floating piston is preferably long (see above). Unlike the conventional floating piston of known air spring impact mechanisms, it includes, for example, multiple “cascaded” mechanical seals instead of a single seal. These “cascaded” seals are pneumatically connected in series. The contact pressures Ppress(i) (where i = 1, 2, ..., n of the n mechanical seals) are each too low for them to seal individually relative to the maximum pressure difference ΔPmax that occurs during operation (between the two sides of the floating piston). Ppress(i) < ΔPmax therefore applies individually to each of all n mechanical seals. However, (Ppress(1) + Ppress(2) + ... + Press(n)) > ΔPmax also applies to the configuration according to the invention. In this way, the pv value of the mechanical seal is only achieved at a correspondingly higher (floating piston) piston speed. This allows for the configuration of the impact mechanism with a higher maximum floating piston speed (during operation) and a lower floating piston mass, which correspondingly reduces recoil and thus vibration. Instead of cascaded mechanical seals, the type of aerodynamic seal used in labyrinthine axial piston compressors can also be used for the same purpose (i.e., enabling higher floating piston speeds with acceptable wear).

[0046] Amorphous and partially amorphous alloys are particularly suitable as materials for the floating piston 350 and / or the hammer 330 because they have very high elastic limits and very high springback coefficients. They can also possess other advantageous properties, such as excellent corrosion resistance, wear resistance, and formability. Amorphous alloys are referred to as “metallic glasses,” for example, in golf clubs, where a high springback coefficient is utilized. High-density amorphous or partially amorphous alloys, whose density is preferably adapted to the density of tool materials (typically tool steel), are particularly suitable for carrying out the present invention. An example of particularly suitable materials for the floating piston and / or hammer is the partially amorphous iron-based alloy SAM2x5-630 (nanosteel), which can be processed by spark plasma sintering, and heavy metal powders, especially (crystalline) tungsten powder, can be added to the powder to adjust the density.

[0047] In one embodiment, a portion of the cylinder in which the excitation piston and floating piston operate can be configured as a hammer guide to accommodate the hammer. Regarding mechanical properties, tribological properties, and corrosion resistance, so-called "carbide-free" nanostructured bainitic steel with a hard chrome plating is particularly considered for the cylinder. These steels are readily machinable, at least prior to bainitic transformation treatment, and achieve a significantly lightweight structure, particularly by allowing for thinner-walled configurations of the cylinder and, possibly, the tool holder.

[0048] The hammer guide preferably also includes vents 393 and 394. By applying different (air) pressures to the two vents, the required contact pressure of the tool can be adjusted. Another opening 395 on the cylinder allows dust-free compressed air at a known pressure to be supplied as sealing air, for example, into the annular space 340 between the tool and the hammer. This prevents dust from entering the impact mechanism, thus increasing its service life.

[0049] Figure 4 The diagram schematically illustrates the working device according to the invention, namely a breaker or chisel hammer, including an electro-pneumatic impact mechanism. Figure 4 Specifically shown are impact mechanism assembly 410, tool (e.g., chisel) 411, (vibration-isolated) equipment housing 420, bellows 421, guide member 422, air filter 430, outlet 431 for sealing air through the gap between the tool and tool holder, lateral outlet 432 for cooling air, spring (especially air spring, e.g., diaphragm air spring or spring bellows) 441, linear motor (especially moving coil drive (optional)) 442, compartment for electrical and electronic components 450, motor controller 451, Class D amplifier (optional) 452, acceleration sensor (optional) 453, microprocessor (optional) 454, handle 460 (optional), spring (especially mechanical spring) 461 (optional), and damper (e.g., oil damper (optional)) 462.

[0050] Impact mechanism component 410 may, for example, be configured as follows: Figure 1 As shown, although filter 131 is not attached to the impact mechanism assembly, it is attached to the device housing 420 as filter 430. Impact mechanism assembly 410 may, for example, include components according to… Figure 3An air spring impact mechanism. The impact mechanism assembly 410 is movably mounted on the equipment housing 420 via a guide member 422, which allows the entire impact mechanism assembly 410 to recoil. Furthermore, the guide member acts as a stop and limits the travel of the impact mechanism assembly 410 relative to the equipment housing 420. Due to the seal provided by the bellows 421, the compressor (not shown) of the impact mechanism assembly 410 can only draw in filtered air through the air filter 430. The sealed air 431 can escape along the tool. Motor cooling air can be discharged from the impact mechanism assembly 410 into the surrounding environment. A spring 441 is preferably arranged between the equipment housing 420 and the impact mechanism housing 410, by which, for example, a user can press the impact mechanism and the tool (e.g., chisel 411) accompanying it against the substrate to be processed. This spring is preferably a gas spring, particularly an air spring, wherein the air spring can be configured, for example, a pneumatic cylinder or—preferably—a spring bellows or a diaphragm air spring. The air spring can be supplied with compressed air via a compressor of the impact mechanism assembly 410, for example, via one or more (control) valves. It can also, or alternatively, be used for... Figure 2 The compressed air reservoir discussed is considered for embodiments of the invention with a rotating motor as well as those with a linear direct drive. An (air) spring already provides vibration isolation between the impact mechanism assembly 410 and the device housing 420. Further active vibration isolation can be achieved by operating a linear drive 442 mechanically parallel to the spring 441. A highly dynamic direct drive, such as a moving-coil drive, is particularly suitable as a linear drive for this purpose. This linear drive is preferably used to generate a time-dependent force that largely compensates for the force transmitted by the spring 441. The signal required for this can be calculated from the signal of an accelerometer 453, also attached to the device housing 420, by a microprocessor 454 attached to the device housing 420, and generated by a Class D amplifier 452. Advantageously, the mechanical power of the moving-coil drive used for vibration isolation is not wasted but necessarily excites the impact mechanism. All electrical and electronic components are preferably arranged on or in one or more compartments 450 of the vibration-isolated device housing, thereby reducing mechanical stresses that could shorten the lifespan of the electrical and electronic components. This is particularly relevant to battery-powered embodiments of the invention, where the battery is also highly preferably attached to a vibration-isolated device housing. The handle 460 can be mounted to the device housing via a damper, enabling it to move perpendicular to (or at least with a vertical component) the impact axis, for example, via a combination of a mechanical spring 461 and an oil damper 462. Active vibration isolation of the handle is not ideal.

[0051] In embodiments of the invention as a drill hammer, it is suitable to drive the tool holder independently by means of a second motor. In this case, both motors (i.e., the one driving the impact mechanism and the one driving the tool holder) are preferably liquid-cooled and share (at least partially) a cooling circuit or cooling system. The tool holder can also be driven directly or by means of a reduction gear. Planetary gears coaxial with the impact axis or the tool arrangement are particularly suitable as reduction gears. In this case, the drive can preferably be via the sun gear, and the output via the ring gear, while the planet carrier is repositioned, for example, on the housing of the impact mechanism assembly 410.

[0052] In the controllable charging pressure electric hammer with impact mechanism according to the invention, the use of a separate second motor to drive the tool holder allows the user to independently select the impact frequency, impact energy and rotation speed, and thus adapt them to the corresponding application.

[0053] If the accelerometer 453 measures a value higher than a certain limit within a specific time period, the microprocessor 454 can initiate an emergency shutdown of the operating equipment to protect the user (and the equipment).

Claims

1. A working apparatus comprising an electro-pneumatic percussion mechanism, characterized by, The working device includes an impact mechanism and a compressor. The impact mechanism is preferably an air spring impact mechanism and has at least one vent. The compressor is connected to the at least one vent of the impact mechanism and is capable of compressing ambient air and supplying it to the impact mechanism as compressed air.

2. The work apparatus according to claim 1, characterized by The operating equipment includes at least one first air filter connected in series with the compressor, such that the compressor can supply filtered compressed air to the impact mechanism.

3. The working equipment according to one or more of claims 1 to 2, characterized in that, The operating equipment includes at least one first pressure reducing valve, which is capable of reducing the pressure p1 of the compressed air discharged by the compressor to a specific value p2 before the compressed air is supplied to the impact mechanism, where p0 < p2 < p1, and where p0 is the ambient pressure.

4. The operating equipment according to claim 3, characterized in that, The operating equipment includes at least one second pressure reducing valve to further reduce the pressure p2 to a value p3, where p0 < p3 < p2 < p1.

5. The operating equipment according to one or more of claims 1 to 4, characterized in that, The hammer guide includes independent vents, to which different pressures can be applied.

6. The working equipment according to one or more of claims 1 to 5, characterized in that, The operating equipment includes linear or rotary direct drives.

7. The operating equipment according to claim 6, characterized in that, The direct drive of the impact mechanism is implemented by one or more rotary motors, and the rotational motion of the rotary motors is converted into the linear reciprocating motion of the excitation piston by a first mechanism, wherein the excitation piston can also be configured as an excitation cylinder.

8. The operating equipment according to claim 7, characterized in that, The first mechanism is a crank-slider mechanism, wherein the crank-slider mechanism may also be configured with a double crankshaft.

9. The operating equipment according to claim 7, characterized in that, The first mechanism is a swing drive mechanism.

10. A working device, comprising an electro-pneumatic impact mechanism, characterized in that, The excitation piston of the impact mechanism can also be configured as an excitation cylinder and directly driven by an electric linear motor, wherein the rotor of the linear motor is connected to a gas spring system, or operates on a system capable of driving the rotor from two stroke end positions that can be determined by the gas spring system toward a stroke midpoint, such that during operation, the gas spring system causes the rotor to reverse in the region of the two end positions.

11. The operating equipment according to claim 10, characterized in that, The working device includes a motor controller, and during operation, if, according to numerical values, the speed of the rotor is in the upper range of the basic speed range of the linear motor and / or even in the field weakening range of the linear motor, then at least 50% and preferably at least 80% of the rated power of the linear motor is supplied entirely or primarily by means of the motor controller to the linear motor, and wherein the rotor is electrically driven in two directions of motion.

12. The working equipment according to claim 10 or 11 and one or more of claims 1 to 6, characterized in that, With the aid of at least two valves, the variable volume of the gas spring system serves as the compressor of claim 1.

13. The operating equipment according to claim 1, characterized in that, The floating piston of the impact mechanism is long.

14. The operating equipment according to claim 13, characterized in that, Floating pistons include the type of gas dynamic seals used in labyrinthine axial piston compressors.

15. The operating equipment according to claim 13, characterized in that, The floating piston includes multiple mechanical seals pneumatically connected in series.

16. A working device, comprising an electro-pneumatic impact mechanism, characterized in that, The floating piston and / or the hammer are formed wholly or partially of an amorphous or semi-crystalline alloy, or lined with such an alloy, wherein the density of the floating piston and / or the hammer is preferably adapted to the tool of the working device, which is preferably a drill bit or a chisel.

17. A working device, comprising an electro-pneumatic impact mechanism, characterized in that, The working device includes a cylinder and a tool holder, further characterized in that the cylinder and tool holder are made entirely or primarily of a preferably corrosion-resistant, carbide-free, nanostructured bainitic steel.

18. The working equipment according to claim 1 and one or more of claims 2 to 17.

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