DE2160106A1 - Impact device - Google Patents

Description

Patent attorneys
Dr. Ing.H. Negendank

Dipl. Ing. H. * Huck

Dipl. Phys. VV. Schmitz

8 Mifcidwn 15, Mosarkir. 23

Tel. 5 3085 86

Frederick W. Ross

755 Klamath Drive December 1, 1971

Del Mar, California, USA Attorney File M-1824

Impact device

Deformation guns and other impact devices of comparable shape have been used for several years to break off pavement, for example, by means of an impact tool or to carry out other work in which chipping hammers and chisel hammers are used. Impact devices better known Art work with raw strength, as it were, to handle the individual blows granted. As a result, high-performance air compressors are required to keep one inside the impact device to give the existing combination of piston and cylinder sufficient impact energy. The need for large and powerful Air compressors limit the manageability of the Impact device and the possibility of easy access to some parts of the device. This is considered to be disadvantageous by large Noise generated by air compressors and the air blown off by the pneumatic hammer perceived; also through the Exhaust gases which persist in operation of the large internal combustion engines are to be regarded as disadvantageous because they contribute to air pollution.

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Electrically powered hammers can be used without the disadvantages described are used, however, can only be used for a relatively short time and are not suitable for striking with high To give impact.

As a result of the disadvantages mentioned, which are to be regarded as known Subject to impact devices, attempts have been made to improve these devices for a long time. There is a need for & Impact devices, which are to be regarded as known impact units are easier to handle or carry and which are suitable, stronger blows to more effective and more economical Way to issue. There is also a need for devices that operate more quietly and with reduced air pollution for easier handling for the operator are exposed to fewer vibrations, which turn out to be far less and are cheaper to manufacture.

Based on this, an impact device was developed with the present invention created, which is a double-acting air spring, as Arrangement consisting of piston and cylinder, between the power source or excitation device and the one carrying the impact tool Having impact device. The so-called air spring is used to transmit the output of the exciter device; the

, Excitation device consists in the illustrated embodiment as a rotating electric motor. It is possible to use the exciter to drive either the piston or the cylinder. To the

For purposes of simplicity, reference is made to the Drawings only show the excitation caused by the motor

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or actuation of the cylinder explained. The rotational output of the motor is converted into linear motion by a converter device implemented; In the embodiment shown, the converter device is in the form of two eccentrics, which on the opposite sides of the motor shaft are arranged and made of connecting rods, which extend from the eccentrics to the cylinder located bearings extend. The cylinder is arranged so that it moves in accordance with the direction of the connecting rods induced force can move. It is held in its linear movement by guides on the frame of the impact device are arranged. A piston rod attached to the piston extends from one end of the cylinder to the vicinity of the impact tool bearing output device.

The distance between the piston shaft and the output device is selected so that the piston shaft contacts the output device approximately in the middle of a piston stroke without impact. The mechanism described below includes double eccentric which drive the cylinder directly in its alternating movement, the piston being connected g only by the air spring, the combination of piston and cylinder. The device according to the invention is balanced in its mode of operation without the use of gears, insensitive to use and inexpensive. Direct drive without the use of gears requires a larger, slower speed motor. However, this additional weight is more than offset by the absence of gears. The cost of the device is also lower and the maintenance

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Ability is better, especially on impact devices, where the alternating loads significantly reduce the life expectancy of the gears reduce.

Among other things, the combination of piston and cylinder has a spring system , it works with its own resonance frequency, which is determined by a suitable selection of the cylinder and piston size and by a suitable Weight of the piston skirt can be changed. The resonance frequency can be determined to be that of the excitation device corresponds to the vibration frequency caused in the cylinder. When one can use the phenomena of resonance the impact device according to the invention strong impacts on more economical Way using an exciter device verliäH.ni Generate moderately little kiaft. The properties of resonance in pneumatic systems have been known for a long time than to watch. Nevertheless, these findings have not yet found their way into practice, since e ;; on suitable impact devices so far missing. Impact devices that are known to be roped on are not suitable for the unstable running of the piston exchange movement to eliminate their center. The mechanism described below addresses these problems. The instability of this Device is the result of air leakage along the piston when it comes from one end of the cylinder? on the other hand change movements executes. If the cause changes, the piston deflects more towards one side of the cylinder then the lectape is larger on one side of the bulb than on the other. The center of the piston change movement begins,

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towards the low gas pressure side of the cylinder to relocate. This displacement is slow at first and then progresses with increasing speed until the piston finally hits the end of the cylinder, which is consequently too high Stresses and can even lead to breakage known type in view of this unstable behavior have become due to their weight, their complex structure and their costs proved to be impractical, especially when used on devices which are to be operated by a single operator are. The present invention eliminates the existing problem of instability of reciprocating motion using two related Types of procedure.

The first method is to use a passive channel within the piston and cylinder combination, which the amount of gas in the opposite ends of the cylinder during its alternating movement and under the action of the same changes. The center of oscillation of the piston should be stabilized with respect to the longitudinal center. The various advantages " directions for performing this stabilization are described in more detail in co-pending US patent application "Oscillatory iJotion Coupler ". For the purpose of illustrating the present Invention is only a single, on the device according to the invention particularly applicable compensation system explained in detail. However, any compensation system can be used Form using passive channels on the impact device.

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In the device according to the invention, the cylinder has vents which lead from the inside to the outside of the cylinder approximately at the center of the cylinder. If the instability of the system results in the center of the piston change movement being offset with respect to the center of length, the gas pressure within the cylinder with the piston in the center position differs from one side of the piston to the other. On one side of the piston there is a pressure which is higher than the ambient pressure, while on the other side there is a pressure which is lower than the ambient pressure. When the piston continues its back and forth movement, it releases the ventilation on the cylinder and exposes it to the external atmospheric pressure via the ventilation opening. If the side of the cylinder exposed to atmospheric pressure is at a pressure less than atmospheric pressure, then flow occurs in the cylinder. When the piston moves in the opposite direction and the air vent releases which the opposite side of the cylinder with the outside air or atmos W phere combined then leave the located on this side higher pressure via the vent hole to the outside air. If the piston continues several alternating movements, the pressure comes into equilibrium again, which is why the center of oscillation of the piston returns to the center of length of the cylinder. In this way, the piston can be excited to resonance without the risk of being destroyed by hitting the cylinder.

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The second contemplated method of controlling instability the piston change movements consists in designing the combination of piston and cylinder in such a way that the center of oscillation the piston is always displaced in the same direction. In one embodiment according to the invention happens this using a piston shaft of relatively large diameter, which extends from only one end of the cylinder extends. This shape means that the gas volume within the cylinder on one side of the center of oscillation is considerable larger than on the opposite side. When the piston hits its ™ Performs alternating movements, the leakage along the interface between the piston and cylinder creates a greater pressure gradient in the lower volume side of the cylinder. This pressure gradient has the consequence that the piston oscillation point moved towards the low pressure side of the cylinder. As mentioned above, the piston skirt hits roughly in the middle of it Hubes to the output device on; if the tool tip is on the surface to be machined at this point in time Workpiece is present, the piston is prevented from hitting the Zy- | soothing ends if the piston skirt is a z \ i large Hub is subject to. The cylinder can be made strong enough to withstand a short blow, if the tool tip at the time in question, not on the workpiece is applied; the leaching device can also be provided with an anvil body v; r. will see who is taking the impact from the piston skirt. Jer Aiiiboss is in limited motion attached to the frame Guided tours and has a stop, ve1 rather

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prevents its movement beyond the point at which the Piston could come into contact with the cylinder ends.

All embodiments according to the invention can with the piston be provided with improved construction. The high stresses occurring at high piston speed lead to a large load on the piston. The stresses are greatest near the piston skirt. If you chamfer the piston side land so, that there is minimal thickness near the cylinder wall, the stresses are reduced to a minimum. Adequate waterproofing

is achieved by a lightweight flange that extends around the circumference of the piston.

With both methods of controlling the piston change movement can In addition, compensating devices using springs can be used. The springs are arranged so that it is the reaction force of the connecting rod on the cylinder oppose a force. The springs distribute the load on the cranks of the shaft and on the bearings of the rotary movement into the linear motion converting device, which is why the load is distributed over the entire rotation cycle. The size requirements the bearings can be reduced as a result.

The advantages of the device according to the invention are additionally asserted by using a counterweight system. The- ,

This system can be used with both of the above-described control ί systems can be used and can also be combined with the with springs'

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working compensation device are applied. '.

! The counterweight is driven by the same excitation device via a device which converts the rotary movement into a linear movement, but moves at every point in time in the opposite direction to the movement of the cylinder. In other words, the movement of the counterweight is 180 ° out of phase with the movement of the; Cylinder. The mass of the counterweight and its associated connecting rod is selected so that it approximates the Zylindersund its associated connecting rod or its connects g Denden rods der.Masse. The engine will work this way

a much more uniformly distributed torsional load. 'sets and does not need to be made as compact or fixed as previously required. There are also fewer vibrations from the engine to the frame and thus to the operator transfer.

I.

: The invention enables the use of a freely guided KoI-ben as well as the use of resonance, which can increase the impact energy at any point in time. Air springs are also low "

They are lower in weight, require less space, and are less subject to failure. They also transmit less high-frequency harmonics and support the isolation of the rest of the device and the operator from vibrations. If you look at j ι the resonance served, one can as a result of the relatively low; gen deflection of the cylinder, which is used to induce resonance in the

and piston is required, cheaper to manufacture / maintain Use an eccentric to convert the rotary movement into a linear movement. -10-

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It is therefore the object of the invention to provide a new and different ' to create better impact device. This should be able to give stronger blows than with known devices is possible. The device according to the invention should be easy to use and should not be used by heavy and expensive air compressor systems be dependent. The device according to the invention! should be less forces generated by vibration and alternating movements transferred to the operator and should make use of the advantages of double-acting air springs, which work at resonance. Of the forces associated with the reciprocating parts, a smaller proportion should act on the connecting parts and Bearings are transferred «The impact device should be light, simple in construction and easy to maintain and use. The piston of the impact device should be of high strength.

The invention is based on exemplary embodiments with reference Explained on the accompanying drawings.

Fig. 1 is a side view of the impact device; !

Fig. 2 is a top plan view of the impact device;

3 is an enlarged sectional view taken on line 3-3 in FIG. 1;

Fig. 4 is a sectional view taken on line 4-4 in Fig. 2;

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; Fig. 5 is a sectional view taken on line 5-5 in Fig. 1;

6 is a side view of a further embodiment the counterbalanced impact device according to the invention;

Fig. 7 is a partially broken plan view of another Embodiment according to the invention; and

Fig. 8 is a side view of an impact device for installation in associated devices.

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In FIGS. 1-5 of the drawings shows an embodiment according to the invention. A cylinder having a piston 10 is attached to a frame 12, which in turn is attached to the excitation device 14, in the present exemplary embodiment Electric motor, is rigidly attached. At the opposite end of the frame 12 with respect to the electric motor 14 is the output device 16. The cylinder 10 consists of a sleeve 18 which has end caps 20 and 22. There are bearing bores in the end cap 20 2.4 and 26 are provided, while bearing bores 28 and 30 are arranged in the end cap 22, respectively. The bearing bores work cooperates with frame 12 to maintain cylinder 10 in rectilinear motion along the frame. The derived via the shaft 32 Rotational movement of the motor 14 is converted into a linear movement via eccentrics 34 and connecting rods 36. the Connecting rods are by means of flanges 38 and pins 40 on the End plate 20 attached. The linear movement induced in the cylinder 10 has the consequence that the piston 42 under the action of im Cylinder 10 located air is moved back and forth. The piston shaft extending through a bore 46 in the end plate 20 transmits this reciprocating piston movement. When the piston deflection has reached a certain value, the end touches 48 of the piston shaft 44, the end 50 of the tool holder 52. The tool holder 42 is moved against the action of the spring 54 and drives the tool tip 56 into the material to be machined. The output device 16 carries j the tool holder 52 in straight motion by means of a guide

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- 13 holes 58 in flange 60.

The embodiment of the invention uses a series of ventilation openings 62 as passive line stabilization in the cylinder. The vents are located in the middle of the cylinder 10 and serve to relieve the pressure between the opposite ends of the cylinder. Since the piston 42 is in the vicinity of the cylinder means, the cylinder ends alternate released when it is free | are given. Any instability which could result in the center point of the piston changing movement from the cylinder center point deviates, it is compensated accordingly. The stabilization of the piston change movements enables safe operation of the System, especially at resonance frequencies, since the possibility of piston impact at the cylinder ends has been eliminated. By Appropriate dimensioning of the mass of the cylinder, the piston and the piston skirt can be the resonance frequency of the arrangement of pistons and cylinders are predetermined to suit the engine 14 corresponds to the induced excitation frequency. Another advantage of the work carried out at resonance can be seen in the fact that a relatively small excitation deflection is sufficient to causing a large deflection of the plunger, which makes it possible the use of cheap and easy-to-operate eccentrics on a system which generates impact shocks with a higher degree of efficiency. j

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Although eccentrics are particularly advantageous within the scope of the invention prove, other devices can also be used which convert a rotary movement into a linear movement, see above crank mechanisms are used, for example, in the embodiment shown in FIG. 6 of the drawings. Some of the advantages the balanced system of Fig. 1 can even be maintained when using a high speed running engine makes the use of a reduction gear or a belt drive necessary. One from each end of the engine using drive transmitted to an idle shaft a crank arm or eccentric can be used to maintain the benefits of balance.

Referring to Figure 3 of the drawings, there is the extremely solid construction of the piston j according to the invention. The high strength one Piston is important because the runout of piston skirt 44 ! at the output device triggers high voltages in the side web 66 of the piston. These tensions reach a maximum at the point the attachment to the piston skirt. As shown, the j piston is designed so that the mass of the piston flange in the Near the piston skirt centerline, while the mass near the cylinder walls is kept to a minimum. ι An effective seal is ensured by using a protruding flange 68 of light weight.

In connection with FIGS. 1-5 of the drawings Motor 14 is shown as an electric motor. As part of

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Various types of electric motors can be used according to the invention

; so capacitor start-up or auxiliary phase induction motors, '

^: wound rotor motors with commutators, or universal electric motors etc.

! An induction motor proves particularly advantageous for the ^; Use. Motors of this type work without any wear and tear, underlying brushes and, as a result, what is even more important, do not have any brush holders, which can cause material fatigue as a result of the relatively strong vibrations of the motor! can lie. AC induction motors with split phase and

the induction motors starting with the auxiliary phase with capacitive ι
Resistance do not have brushes or brush holders, which

^! could fail under vibrations. Induction motors with kapaj zitivem resistance of the type described have a starter switch. However, this is attached to the motor shaft and rotates with it, so that the vibrations triggered by the alternating frame movements of the impact device only slightly increase the centripetal forces on the switch. The switches are thus essentially free from damage caused by vibrations. Finally, there is a vibration filter effect at the air gap, whereby only the base or working frequency of the impact device is in the. Main frame is initiated. As a consequence, the ^Auswir-: effects of higher frequencies, which can be destructive reduced.

In addition, an internal combustion engine, a hydraulic rotary motor or any other

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j portable drive can be used.

6 shows a further embodiment according to the invention. As with the one in FIGS. 1-5 of the drawings, the embodiment shown in FIG. 6 has a cylinder 10 from which a piston shaft 44 extends. An output device 16 is assigned to the piston skirt. The cylinder is guided in linear motion along the frame 12 by end plates 20 and 70. In this embodiment of the invention, the motor 72 is arranged offset with respect to the center line and drives a crankshaft 74 which has three cranks 76, 78 and 80. The cranks 76 and 78 work together to drive the cylinder 10 via connecting rods 82 and 84. The crank 78 is phase shifted by 180 ° with respect to the cranks 76 and 80 and drives a counter-gear via a connecting rod 88 _; weight 86. The counterweight 86 is guided in linear motion along the frame 12 by a guide plate 90. By suitable selection of the total mass of the counterweight with the associated guide plate 90 and the ignition rod 88 in approximation to the mass of the cylinder 10 with associated plates and the connecting rods, the torque fluctuations which would be triggered on the crankshaft 78 during rotation can be substantially reduced. This leads to a smooth run and low vibration.

7 of the drawings depicts a third embodiment in accordance with of the invention. The motor 14, the eccentrics 34, the cylinder 10;

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ι and the connecting rods 91 of this embodiment correspond to J with reference to FIGS. 1-5 with the exception that the tubular frame is replaced by a frame 92 is, which also serves as an enclosing housing. The embodiment shown in Fig. 7 of the drawings has also springs 94, which are guided on rods 96; there are handles 98 on the rods, which are in the same line

are movable to the axis of the cylinder 10. By choosing the appropriate The spring constant of the springs 94 is used to move the handles ^ to secure or isolate against the vibrations of the main frame.

In this embodiment according to the invention, too, the cylinder 10 can move freely to and fro on sliding bodies 100; for this purpose the sliding bodies are inside a cylindrical Fastened recess in the frame. Counterweights 102 are on the Mo-j Gate shaft 104 attached and serve to compensate for vibrations jj which by the a.chsen »offset weights of the eccentric and the | Attachment of the connecting rods would be triggered.

The embodiment shown in Figure 7 of the drawings includes an exit device having an anvil 95 which extends along a cylindrical opening 97 in the frame 92 can be moved back and forth. The tool 99 is slidably guided in the anvil and is limited in its linear movement by the tool guide 101. The tool guide 101 is slidably attached to the pin 103 which in turn are attached to the frame 92. The tool guide

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tion acts as a spring-loaded stop, the springs 105 preventing excessive loads on the frame 92 when the Piston skirt 44 are present. The significance of the tool guide 101 as a stop can be taken from the description of the illustrated in FIG. 8 Embodiment clearly. A holding body 107 holds that Tool 99 releasable in its position. The holding body 107 can be rotated about the pin 109 in order to remove the tool to be able to.

Fig. 8 of the drawings shows an embodiment of the invention as a percussion unit, which with the previously described ^! Impact devices can be used. The motor 14 and the eccentrics 34 correspond to the corresponding components shown in FIGS. 1-5 of the drawings. The device shown in Fig. 8, however, has load-compensating spring means. Two springs 106 and two springs 108 are arranged on both sides of the plate 110; the plate 110 is rigidly attached to the end plate 112 of the cylinder by means of the shaft 114. The springs form a compensating device which works as follows: When the connecting rod moves the motor frame and the cylinder towards one another, the springs 106 are compressed. When the connecting rod further separates the motor and cylinder, the springs 108 are compressed. When the combined spring rate of the springs is chosen so that the natural frequency is near or above the operating frequency, these springs will cause the load on the eccentrics , on the rods and on the bearings can be reduced.

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The cylinder 118 shown in Figure 8 of the drawings is not vented. As a result, one could expect the piston to oscillate beyond the center point with possible stops at one end of the cylinder. However, according to a further proposal of the invention, the combination of piston and cylinder is constructed in such a way that the instability of the piston vibrations of the form described above is compensated for. The piston skirt 120 takes up a relatively large part (more than 15%) of half of the cylinder 118 at the cylinder end 122. This size ratio has the consequence that the offset of the center point of the reciprocating piston movement is always in the same direction, i.e. in the direction of the end 122. The reason is that the leakage from end 122 towards end 112 has the greater effect on the pressure at that end than a flow in the opposite direction. If the device shown in FIG. 8 is used with an impact device, then the force transmitted by the tool when it comes into contact with the workpiece prevents the piston deflection from being displaced to a point at which the piston 124 aa end 122 strikes. The unit can also be used in conjunction with an exit device of the embodiment shown in FIG. 7 using an anvil body 102. The anvil body is arranged at a distance from the tool guide 101 which is less by the distance of the piston deflection which the piston 124 would need to strike the cylinder end 122. By using; By using springs 105 or a fixed stop, the center of the piston oscillation can be guided within safe limits

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The spring balancer illustrated in Figure 8 of the drawings is most effective when within a narrow frequency range is used. Because of this, it will run along with a constant speed Motor used, such as with an induction motor.

Although the impact force is significant due to the resonance of the piston and cylinder can be increased, it proves to be useful in some applications to work without resonance; both the in FIGS. 1-7 shown, vented cylinder and the shown in Fig. 8, unventilated cylinder can in a state can be used without any response. When the resonance state is used then the greatest efficiency is obtained when the output device is arranged with the piston skirt first touches the anvil or tool holder near the center of the piston stroke without impact. At this point the Piston at its greatest speed.

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Claims (19)

Claims 1. Impact device for issuing blows, characterized by an exciter device (14, 72) which is a piston-cylinder device (10) vibrational movements issued, a frame (12) on which the piston-cylinder device is mounted and is movable relative to the exciter device, and an output device (16) which the oscillatory movements transfers from the piston-cylinder device to an impact tool (56). 2. Impact device according to claim 1, characterized in that the piston-cylinder device (10) has one inside the cylinder (18,20,22) reciprocable piston, wherein the piston shaft attached to the piston (44) extends through the cylinder extends, and that the piston-cylinder device passively acting channel means (62,62) are assigned to the amount of gas in the opposite cylinder ends under the effect of -22- 209825/0 7 96 Adjust the piston so that the position of the center of oscillation of the piston with respect to the cylinder can be stabilized i 3. Impact device according to claim 1, characterized in that the KoIben-ZyIindervorrichtung with one inside the cylinder reciprocating piston is provided, and that the piston-cylinder device Means are assigned to the center of oscillation due to the instability of the piston change movements of the piston in the direction of the output device at store. 4. Impact device according to claim 1, characterized in that the piston-cylinder device has a straight line along the frame (12) reciprocable cylinder (18) and a piston (42) which reciprocates within the cylinder is movable that at least one piston skirt on the piston j (44) is attached, which is through a bearing on little at least one end of the cylinder extends, and that the output device (16) is attached to the frame in such a way that, during part of its alternating movement, it is in: Touched. 5. Impact device according to claim 2, characterized in that the \ Excitation device (14,72) from a rotary motor and from; a converter device (34,36), which the rotary j converts movement into a linear alternating movement, and that the j output (36) of the converter device is connected to the cylinder which causes the cylinder to oscillate in a linear alternating motion when the engine is rotating. -23- 209825/0796 6. Impact device according to claim 5, characterized in that the rotary motor consists of an induction motor. 7. Impact device according to claim 5, characterized in that the converter device has at least one on the output shaft (32) of the motor (14) has attached eccentric (34) and at least one connecting rod (36) which the eccentric with connects to the cylinder. 8. Impact device according to claim 5, characterized in that the converter device has at least one crank (76,80) on the Output shaft of the engine and at least one connecting rod (82,84) which connects the crank with the cylinder. 9. Impact device according to claim 5, characterized in that the converter device has a rotary motor whose Shaft (32) extends on both sides of the motor, that an eccentric (34) with a connecting rod (36) on each shaft attached, and that each connecting rod with the cylinder * who is in communication. 10. Impact device according to claim 1, characterized in that the output device is provided with an anvil (95) which is movable back and forth on the frame and is axially aligned ι at a distance from the piston shaft (44) that the output device is also provided with a striking tool (99) which is in a guide (101) with respect to the frame -24-209825 / 0796 is reciprocable, and that the impact tool is axially aligned with the anvil (95). 11. Impact device according to claim 1, characterized in that the output device has a striking tool (56) which is reciprocable within a guide (52,101), and that the guide is fixed to the frame and the impact tool holds axially in alignment with the piston skirt. 12. Impact device according to claim 2, characterized in that the piston (42) from its thickest part at the point of attachment with the piston skirt (44) runs obliquely in the direction of the thinnest part on the cylinder walls. 13. Impact device according to claim 12, characterized in that the Piston has an enlarged edge portion (68) which is attached to the thinnest part of the piston and extends from this m extends parallel to the axis of the piston shaft (44). 14. Impact device according to claim 4, characterized in that a counterweight (86) can be moved back and forth with respect to the frame (12) is performed that the counterweight to an auxiliary converter device (78,88) is connected, which converts the rotary movement into a linear alternating movement, and that the auxiliary converter device is connected to the excitation device (14) generating a rotational movement in order to achieve one of the linear movement of the cylinder counteracting linear movement of the counterweight. _ ,, _ 15. Impact device according to claim 14, characterized in that the converter device and the auxiliary converter device are cranks (76,8O; 78), which are attached to the output of the exciter device, and that the counterweight (86) on the frame between the exciter and the cylinder is attached. 16. Impact device according to claim 5, characterized in that a spring balancing device (106,108) between the motor and the cylinder is arranged to generate a force on the engine gen, which is directed opposite to the force generated by the action of the converter device. 17. Impact device according to claim 16, characterized in that the natural frequency of the compensation device, the motor and the spring system formed by the cylinder is at least as high as the working frequency in the linear alternating movement of the Cylinder. 18. Impact device according to claim 1, characterized in that the natural frequency of the piston-cylinder device under impact has essentially resonance with the frequency of the excitation device. 19. Impact device according to claim 2, characterized in that the natural frequency of the piston-cylinder device under impact has essentially resonance with the frequency of the excitation device. 209825/0796