DE1939262A1 - Impact device, preferably for impact wrenches - Google Patents

Description

PATENT ADVOCATE I9392ß2

PATENT Attorney DIPL.-ING. R. MOLLER-BORNER PATENT Attorney DIPL-ING. HANS-H. WEY IBER Ll N-ÖAHLEM 33. PODBI E LS KIALLE E 68 8 MON CH EN 22- Wl DENM AY ER ST ROSSE TEL. 03U- 762907 TELEGR. PROPINDUS TELEX 0184057 TEL. 0811 -225585 TELEGR. PROPINDUS TELEX 0524244

21 951

INGERSOLL-RAND COMPANY New York, N.Y. (UNITED STATES)

Impact device, preferably for impact wrenches

The invention relates to an impact device, preferably for impact wrenches, with a rotating, driven and mounted on an axis carrier, a adjacent to this arranged rotatably mounted AmboA with stops extending radially from this, clubs pivotally mounted on the carrier and adjoining the anvil, which from a first position, in which they rotate around the anvil are free from this are pivotable radially inward to a second position in which they contact the anvil and exercise on this one stroke

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The main field of application of this impact devices is their use in S chi ag a ore au · * bern, at its projecting to its housing Full a function of a socket wrench engaged nut is placed _t in order screws, nuts or other · attachment means to tighten or loosen . The striking elements are alternately guided against the anvil and released from the anvil, since this process is repeated after the increased speed of the striking elements executing the striking and released from the anvil. Such devices have become known in many versions.

A known percussion device, the so-called "Patt *" mechanism, which is named after the inventor, is known from the American patents 2,012,9i6 _t ² ° ^ 9 and 2,158,303. A more recent version of this mechanism is from the American patent 2 160 150 disclosed · According to this last known device, a hammer element is arranged on a motor-driven shaft and between the hammer and the shaft driving balls are arranged in narrowing grooves. A · spiral spring presses the striking element into contact with the anvil in which the balls after the striking elements strike the anvil, the rotating shaft causes a relative rotation between the shaft and the hammer and causes the balls to jam so that the hammer is moved axially into its free position, whereby a Considerable energy is stored in the spring pressing the hammer

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Hannner is released from the anvil, arranged by the The compressed spring and the rotating shaft generated energy by pushing the hammer forward again for the purpose of executing another blow on the anvil "

This "pot" mechanism has several disadvantages aufι one of which is that when using two diametrically opposed striking elements performed one strike with every half revolution of the same is excluded, reaching a sufficient speed between the individual strokes is·

Another? known percussion device is disclosed in the American patent specification 2,881,884 · This device has a abgedrückten by a spring by the armature hammer, a cam control which is Nmer operated by the relative rotation between the Ank®r and uou H, the hammer periodically axial in a Movement displaced, with this executes a rotational strike on the anvil · This device is known under the name "ski-jump ^tt mechanism ·

A disadvantage of this latter device is that when the hammer is at a lower than that intended speed is operated with its teeth not moved axially far enough from the anvil to fed up with engaging the teeth of the anvil · The defective one Engagement of the teeth causes enormous wear and tear of the same «Another disadvantage is below certain circumstances in that through the hammer one

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Flutter on the anvil vox * dem Vorbtidrthen d ·· Humtra on this at a first sleep occurs before a Sufficient speed has been reached for a subsequent blow · This flutter also leads excessive wear and tear and loss of energy, as well as loss of time, and is therefore undesirable «

A third bearing device is known as a "rocking weight" mechanism from American patent specification 2,285,6 * 38 became known "In this device a pair of diametrically opposite oscillations will swing" the Schlage elements used, which revolve around a wing-like anvil and in the wing or approaches the Engage the sole elements and thereby execute a blow on the anvil prior to the execution of the blow released by teasing, appropriate elements are woven for the execution of a Torques are provided on the striking elements in order to bring them into a neutral position, after carrying out a · Blow to bring "

The "Scnwinggewichf-Mechaniamu · has the disadvantage, that with every half turn of the striking elements eim Impact is carried out if two impact elements are used achieved «As it is desired, two striking elements for the purpose To achieve a balanced stroke, which hit the opposite sides of the anvils, can be described as the power of the game

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do not remove «,

Other disadvantages of the "swing weight" mechanism exist by the rebounding of the striking elements after the individual strikes, causing even strikes in the rear Direction are executed, whereby an undesirable impact occurs in the wrong direction of rotation.

To eliminate the above disadvantages is the object of the present invention, in addition to eliminating the same additional advantages for rotating impact devices are to be achieved.

The impact device according to the invention should be free from severe wear and tear on impact elements or teeth, it is supposed to make a balanced blow on the anvil during one full turn of the hammer, it is supposed to Do not perform any blows in the undesired direction by rebounding, it should be radially pivotable Have striking elements which are arranged around an anvil and a neutral position for the striking elements allow in which the blow laments free from the anvil can circulate, an automatically operating device for securing the striking elements against pivoting in the operating position in the wrong direction, a radially pivotable impact element is intended automatically into its neutral position, following an executed stroke, the striking elements without the Applying a torque to the pivot pin of the striking element, and the striking device is designed be able to make a first strike, which is stronger

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all subsequent normal strokes.

The object set is according to the invention and in general expressed by the fact that in a rotating percussion device one with a pair of stops equipped anvil is present, which may also have teeth or may have claws, as well as a hammer support surrounding the anvil with a pair of them diametrically opposing striking elements «The striking elements assume a middle or neutral position, in which they free around the anvil without attacking it

™ and out of which they can run for the purpose of execution a blow on the anvil can be brought out in any direction of rotation. The impact elements are there connected by a yoke which allows joint movement and with the anvil and the Cam control devices cooperating with striking elements are provided to guide the striking elements inward to pivot into their striking position during each revolution of the hammer carrier. Automatically working lifting gear prevent the flapping elements from pivoting into the undesired flapping position in any direction Rotation, with the impact elements dimensioned and appropriately

fe are arranged so that they automatically switch into swing their neutral position

Xn the accompanying drawings is an embodiment of the impact device according to the invention shown schematically, which is explained in detail with reference to the following description, with from the description and the drawings the aforementioned

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ORKsINAL iMSPEGTED

• owl · further advantage · of the invention-ageaäfien striking device result · Ss point

1 shows a partially sectioned representation of an impact wrench, whereby the sole plate clutch is exposed

is ι . ■

Fig. 2 to 5 sections through the representation according to Fig. after lines 2-2 to 5-51

Fig. 6 shows a section along the line 6-6 in Fig. I ₉

where the beacons are shown in their free position}

FIG. 7 · 1η section along the line 7-7 in FIG. 31 Figures 8 through 10 show the movement of one of the impact components

enter Sinbesiehung dos Aebosses umd der Moeken « systeao in their different stables before executing a blow]

11 to 13 successive positions of the aforesaid Parts during and after the execution • a blow test

FIGS. 14 and 15 are representations of that shown in FIGS. 8-10. Part _9, however, in these opposing Ualaufι and

Fig. 16 the trajectory of an · eccentric pin ·· during • a movement mm driver for the · ground contact ■ element and past a rabble contact point «

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The impact wrench 1 shown in FIG. 1 consists of a housing 2 which is divided into a Hainmer part 3, a motor part k and a handle 5. That hammered! 1 3 accommodates a spindle 6 which protrudes the front of de "end of the housing 2, the nut member k nimt an air motor with a drive shaft 7 * uf and the handle 5 is provided with a switch 8 and an inlet coupling 9 for attachment of an air hoses · sum Supply of the air required for the air motor. «The spindle 6 is equipped with flats 10, the arrangement and dimensions of which correspond in arrangement and dimensions to a socket wrench, a so-called nut, commonly used in these screwdrivers * All of the above parts are known from known blowers ·

The drive shaft 7 i * t to the spindle 6 by a new rotary impacting clutch 12 is connected, which is the subject of the present invention is · The essential parts of the clutch 12 are referred to as hammer 14 striking member which rotates about an anvil 15 "The hammer Ik is driven by the drive shaft 7 and the anvil 15 is firmly connected to the spindle 6 "

The hammer Ik has a hammer carrier 17, which comprises a back plate 18, a front plate 19 and a pair of struts 20 connecting them Diameter on «the front plate 19

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«9-

is rotatably mounted in an enlarged annulus on the front part of the anvil 15 up to this point the description of the hammer support 17 is free to Anvil 15 rotatable *

The anvil 15 carries a pair of axially extending wing-like claws, teeth or lugs, referred to below as stops 24 and diametrically opposed to each other. These stops 2k are arranged between the back plate 18 and the front plate 19 of the hammer carrier 17. When mentioned the Iflügelartigkeit the stops 2k is meant that these ergtrecken substantially radially outwardly voaa anvil 15, wherein the rare similar © in "s part of a cylinder diverge * the stoppers 24 are arranged so that they rotate" shocks or impacts of the hammer Ik be able to record*

The hammer carrier 17 carries a pair of arc-shaped clubs 25 which are pivotably attached to elongated pivot pins 26 which extend between the back plate 18 and the front plate 19 of the hammer carrier 17 The clubs 25 are arranged diametrically opposite one another in the hammer carrier 17, wherein the struts 20 wan are offset 90 ° to the pivot pin 26 so that the racket 25 without in K & llosion with the struts 20 to move, pivot or swing can ".The racket 25 have radially diverging end surfaces 27, which in * significant correspond to the circumferential shape of the stops 2k , so that they swing inwardly and rest against the stops 2k

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can be seen, as can be seen in FIG. It should be noted that the end surfaces 27 are kept slightly arcuate. The beaters 25 move in three positions, including a central position, as shown in Fig. 6 , in which the Haooior Ik can freely rotate the anvil without that the racquet 25 to perform a stroke, while in the embodiment shown in FIG. 3, taking place in the clockwise stroke position, the rackets 25 pivot forward and inward, and thereby execute a stroke in the Uhrzeigerrich- W processing. In the counterclockwise rotation, the clubs also swivel inwards, but in the corresponding opposite direction

As can be seen from Fig. 2, the back plate 18 of the hammer carrier 17 is cross-shaped in cross section and has a pair of larger diametrically extending arms 29 in which the pivot pins 26 are fastened. A drive fork 30 is fastened to the drive shaft 7 by means of a wedge and comprises drivers 31 which extend elongated in the direction of the front side of the housing 2 and in doing so reach through between the cross-shaped lugs of the rear plate 18 of the hammer support 17. The drivers 30 are arranged in such a way that that they rest against the side edges of the larger arms 29 of the back plate 18 in order to drive the hammer 14. The drivers 31 are arranged at a distance from one another in order to create a certain play between the drive fork 30 and the hammer % h «

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Each driver 31 of the drive fork 30 carries a stop pin 32 (Fie 7) which extends forward from the end of the driver 31 and is set up so that it engages a shoulder 33 (see FIG. 8) The shoulder 33 is arranged at the end of the hammer 25 to prevent it from pivoting in the wrong direction in one direction of rotation. The play between the drive fork 30 and the hammer 14 enables the stop pins 32 to move from one stop position to another »Relative to the clubs 25» if the direction of rotation of the hammer Ik is reversed.

The Schiftger 25 are togetherness through a rod-like Yoke 35 connected, the center of which is pivotably mounted on the Yellen stump 21 at the rear end of the anvil 15 is and the diametrically extending arm «it Yoke pins 36 has «The Soch pins 36 are in Guides of forks 37t which are fixedly arranged on the inside of the Schiftger 25 and extend from there extend «The yoke 35 holds or locks the Schiftger 25 in identical positions · In addition, the yoke ae are pivoted that the bat 25 in their stroke division be swiveled "This movement is achieved by a special cam system"

The center of the anvil 15t which "the attacks it is provided 2k, 1st bit dea rear end of the Wellenstumpfea 21 connected by a Amboßexzenter 39 · Am Xxxenterring kO is heruagelegt to the Amboflexsenter 39 and carries a pair of Ezsenterstiften kl ■ ■ which dia- are arranged etrally opposite and look

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rear circular in di · web de · yoke * 35 extend "A Since · dee yokes 35 carries a pair of hook-like cams kk, which are arranged on the calibration opposite ends of the yokes 35 ', the back plate 18 a carrier iet old k $ provided, which extends into the circular path of the yokes 35 and the eccentric pins kl

When the hammer rotates, the cam system rotates with it. The yoke 35, the eccentric ring kO and the driver 45 are also in motion. When the eccentric ring rotates, it also rotates eccentrically around the hammer shaft Movement can cause the eccentric pins 41 to lie between an edge of the driver k5 and the cam kk on the yoke 35 and thereby force the yoke 35 to pivot the hammer 25 forward and inward into a striking position. The anvil eccentric 39 i «t arranged so that di * · ·· swinging the bat 25 occurs when the close ·· · · are the stop Zk the anvil 15 · This swinging the racket inward stroke iniihre division occurs only once during one full rotation of hammer · de · Ik «in. Give after d 'm Einwärtsschwenken the racket 25 di · eccentric "tift · kl the yoke 35 freely before the racket 25 contact the stops Zk so that di · racket 25 free zurückechwenken in its" center position subsequent to the executed shock, can"

The continuous representations of FIGS. 8, 9 and 10 show the mode of operation of the Nookanay system. In FIG. 8, a striker 25 is shown in its neutral position, which slides over one of the stops Zk and

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is located about 100 ° before its impact position in relation to the stop 24. At this point in time, one of the eccentric pins 41 is immediately in front of its contact with the cam kk _t while the other eccentric pin 41 is in contact with the driver k5, "Both sxccentric pins kl must be in contact with the surfaces of the cam 44 and driver 45 assigned to them" before they exert a force Moving the strikers 25, inwardly in their striking position, can cause ·

When the hammer 25 continues its rotation, the yoke 35 », the eccentric ring 45 and the driver 45 with the hammer 25 also revolve. In FIG. 9 , the racket is 30 ° away from its striking position in relation to the stop 24. At this time, the racket pivots inward into a stroke division. This pivoting movement is caused by the stationary anvil eccentric 39 which forces the eccentric ring 40 to displace the hammer axis 47 to the left in relation to FIG. to pivot the racket 25 inward As soon as the racket 25 completes the inward pivoting movement, which occurs after reaching the inner apex of the cam 44, the relative movement of the yoke 35 to the driver 45 is interrupted by the shape of the cam 44 and the eccentric pin 41 released so that the yoke 35 is free of any force which compels it to swivel movement.

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stroke 24 is located, as can be seen from Fig. 10 * In this way it is prevented that the hammer 25 after the strike on the anvil 15 is carried out can swivel outside *

At the moment the impact is generated , which is shown in FIG. 10, the eccentric pins 41 are released from the cams kk and the drivers k5, so that the strikers 45 can swing freely outwards as soon as the impact has occurred. The back plate 18 is provided with a stop pin 48 which is arranged outside of the driver 45 and prevents the rotation of the eccentric ring 40 behind the driver 45 to the other side of the driver during the rebound of the club 45 following the blow «

At this point in the description it is appropriate to explain the operation of the club 25 during the strike and then in more detail the engine is started and these surfaces are in contact "This is achieved by dimensioning the hammer, which determines the line of force between the end surface 27 and the stop radially upward from the axis of the pivot pin 26." This line of force is shown in Fig. 10 as a broken line $ 0 shown and runs perpendicular to the contact line of the end surface 27 and the stop 24 Due to the arcuate design of the end surface 27, the contact between the end surface 27 and the stop 24 is limited to a linear contact that extends essentially parallel to the tool axis.

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In fact, di ··· linear investment · is made by "in." Really · linear due to the resilience of the Metal surface reinforces · The line of force 50 becomes referred to as "non-locking line of force".

As a result of the non-locking line of force 50, it could be expected that the impact system τοη Schiftger 25 and stop 24 "has a tendency to interrupt the system and thereby reduces the effectiveness of the performed impact" but is not the case, but la On the contrary, the SehlKger 25 is exposed to forces which have the tendency to pivot it even further inwards when the blow is actually carried out. This result is brought about by the fact that the center k9 of the impact of the Sohlftgera 25 protrudes radially outwards Τοη of the line of force and the Ach

In general it can be said that the inertial forces of the racket 25 produce a force result which runs forward through the center k9 of the inertia of the racket 25 at the moment of the strike. This force real, which runs through the center of inertia k9 , is strong enough at the moment of the impact to overcome the contact force, which runs along the line of force 50, the force from the torque which passes through the pivot pin 26 is generated in order to form a force assembly mn which forces the club further inward into its division of the stroke «

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This force is indicated in Fig. 10.

11, 12 and 13 show the positions occurring in the course of the movement of the club 25 following the executed stroke Counterclockwise rebound movement. After the blow has been carried out, the hammer 25 is moved backwards in an anti-clockwise direction, which is a result of the rebound of the W elements which meet under the load of the blow.These elements are the anvil 15, the base (not shown) connected to the spindle 6 and the through the impact wrench 1 moving attachment, for example a nut or a screw. At the same time, the motor is supplying clockwise torque to the striker 25 *, thereby reducing its backward movement and causing it to move in the forward clockwise direction. The combination of these measures leads to the formation of a force connection which gives the racket 25 the tendency to move radially outwards into its neutral position. This force connection is described below.

When the striker 25 is moved in its rebound direction, as shown in Fig. 12, and is exposed to a force reducing the speed, moments of inertia occur which trigger a force result which is effective essentially running backwards through the center k9 «. This reducing force is supplied by the motor via the axis of the pivot pin 26

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leads. The two forces form a force connection, which are shown in Figures 12 and 13.

The force connection continues to have an effect on it during the rebound and during the beginning of the forward movement of the same. When the racket 25 finishes its counterclockwise reverse movement, the moments of inertia resist the acceleration by the pivot pin 26 »thus maintaining the creation of the force connection a sufficient period of time before the leading end of the racket 25 approaches the stop Zk and overflows it, as shown in FIG. 13, so that the racket 25 can move freely past the stop Zk without grasping it *

It should be noted that the automatic swing out of the racket 25 after the execution of the blow in its neutral position the result of the arrangement of the The center of impact of the striker 25 is radially outward from the axis of the pivot pin 26

It must be taken into account that the force result of the club 25 does not run exactly through the center k9 of the blow, which is due to the effect of other inertial forces that are connected to the hammer system.However , this resultant is arranged close enough to this center k9 that the shown center k9 as a starting point for explaining the mode of operation of the device according to the invention.

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After the hit, the striker 25 runs one full turn around the anvil 15 before striking the anvil 15 again. This is due to the fact that the cam system hits the strikers 25 only once during the revolution of the hammer 14 inwards into its striking position pivots.

It should also be noted that the hammer Ik can rebound two full revolutions before it will strike backwards rearward impact during the rebound movement «

The reason why the hammer did not strike backwards for less than two full revolutions the rebounding movement is made below by explaining the movement of the hammer in a reverse Direction of rotation understandable "

Assuming that the impact clutch 12 is in the position shown in Fig. 10 position and the engine environmentally _B is switched, the hammer rotates Ik in the counter-clockwise direction, comprises two turns before the racket 25 is pivoted inwardly to to touch the opposite side of the stop Zk «During one full revolution, the eccentric ring kO swings relatively clockwise behind the stop pin k8. To achieve this, the eccentric ring kO is offset to the left to remove the stop pin k8 from

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To release eccentric pin kl , which is only possible during a full turn of the hammer 14 around the anvil.

Fig. \ K shows the eccentric pin hl when releasing dee Anechlagetifts kB during its first rotation in the counter-clockwise direction "Fig x 16 shows the path of the eccentric pin kl between its position of FIG. 10 and the position shown in Fig. 15, when the Bat 25 executes a blow to the anvil 15 * After the eccentric pin kl releases the stopper pin k8, this is held in the hollow rear side of the driver 45 during a portion of the hammer movement 14 · After the hammer has about executed a full rotation moves the Eccentric pin, based on FIG. 16, in a position to the left of the driver 4 * 5, whereby this can push the hammer 25 into its striking position during the next rotation of the hammer Ik.

One advantage of the two full revolutions requirement before the first strike is that the motor drives the hammer Can bring to a relatively high speed to produce a stronger first blow su «This can turn out to be special beneficial effects if z. B. bolts or nuts should be loosened, which is a first strong Need a blow to cause it to loosen · If the first blow does not cause it to loosen, can the motor can be reversed, run a few revolutions in the opposite direction and then again by reversing repeat another strong blow «If necessary, this can be carried out as long as required should be. The impact wrench according to the

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Finding is thus able, in addition to the -normal impact to generate a far stronger impact that can occasionally be exploited in a valuable way «

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Claims (1)

Godfather ta η sayings 1 ») Impact device, preferably for impact wrenches, with a rotating, driven and mounted on an axle support, one adjacent to this arranged rotatably mounted anvil with stops extending radially from this, on the carrier pivotable and adjacent to the anvil mounted racket, which from a first position in which they are free from the anvil during their rotation about the anvil, radially inward to a second position are pivotable, in which they touch the anvil and exert a blow on it, characterized in that that for the inward pivoting of the bat one such cam control device (35 * 39, ^ 0,41) is provided is that the racket fcü) after generated blow out of the area of the anvil (15) via part of the rotation and guided past it. 2. Impact device according to claim 1, characterized in that the anvil (15) is provided with a pair of diametrically opposed stops (24) and the carrier (i * l ·) carries a pair of bats (25) which at the opposite side of the axis of the carrier (14) are arranged and are set up so that they can pivot inwardly at the same time to execute an impact on the stops (2k) of the anvil (15). 009809/1095 3 impact device according to claim 2, characterized in that that the anvil (15) is arranged coaxially with the carrier and is surrounded by it. 4 «impact device according to claim 3» characterized in that that the rackets are pivotably mounted on pivot pins (26) which are parallel to the Extend the axis of rotation of the beam (i4) * 5 »Impact device according to claim 3» characterized by B | shows that the beaters (25) can be moved into a neutral position that allows free rotation of the Carrier (i4) and the attached racket (25) allowed around the anvil (15). 6. Impact device according to claim 5, characterized in that the carrier (14) has a back plate (18) and a front plate (19) which are rotatably mounted in parts of the anvil (15). 7. Striking device according to claim 1, characterized in that the beaters (25) are pivotably mounted near the anvil so that they can be pivoted into a neutral ψ middle position in which they rotate around the anvil (15) from the latter are free, and can be pivoted into a second striking position, in which they, rotating clockwise, strike against the anvil (15) and that they can be pivoted into a further third striking position, in which they, rotating counterclockwise, also counter-clockwise hit the anvil and that a stop device (30,32,33) is assigned, 009809/1095 the «in pivoting the racket (25) into the third Prevent position as it rotates clockwise. 8 «impact device according to claim 7ι, characterized in that the stop device includes a drive fork (30) which simultaneously drives the carrier (Ik). 9. Impact device according to claim 7t, characterized in that that the anchor device (30,32,33) den Rackets (25) is assigned so that when they rotate counterclockwise a pivoting in the second position is prevented. 10. Striking device according to claim 9 »characterized in that the stop device engages the carrier (Ik) and includes a stop pin (32) which secures the associated bat (23) during its revolution in its neutral position. 11. Impact device according to claim 10, characterized in that the drive fork (30) of the stop _{device is designed so that a limited play between the drive fork (30) and the driven T r} Hger (1 ^ i) is given in the direction of rotation, so that the drive fork is movable relative to the carrier between two positions which result from the ear direction. 12 «Impact device according to claim 11, characterized in that that the stop pins (32) of the drive 0.0 9 80 9/109 5 fork (30) at an arcuate distance from one another are arranged so that they are relative to the associated Beaters (25) in alternating positions opposite to the direction of rotation of the beaters (25) are movable 13 · Striking device according to claim 1, characterized in that the hammer (25) is mounted on a pivot pin (26) near the anvil (15) extending essentially parallel to the axis of the carrier (ik) and radially when the carrier (14) rotates is pivotable inward in contact with the stop (Zk) of the anvil (15) and that the hammer (25) is designed and arranged so that the center (4- °) of the impact is located radially outward from the pivot axis, so that a The club (25) automatically swings outwards into its neutral position as soon as the club releases itself from the stop (Zk) of the anvil (15) after the blow and the club remains in this position during its downward acceleration. Ika striking device according to claim 13 »characterized in that a further racket (25) is arranged on the carrier (14) diametrically opposite the one racket (25). 15 · Impact device according to claim 2, characterized in that the cam control device for the purpose of following the control of the strikers (25) when they approach the stops (Zk) 0 0 9809/1095 1938262 Execution of a blow works automatically and following the executed blow, the bat over part of the orbit, without blow execution, past the stops {2k) and is provided with a yoke (35), which the beaters (25) for the purpose of simultaneous rotation with one another connects * 16. Impact device according to claim 15, characterized in that the cam control device has a control surface (39) which is arranged on the anvil 05) and transmission elements (4O ₈ 41) which establish a connection between the control surface (39) and the contact surfaces on the carrier ( Ik) and the yoke (35) and bring the beaters (25) inside into their striking position. 17 · Impact device according to claim 16, characterized in that that the yoke (35) rotates on the anvil surface. 18 «Impact device according to claim 17, characterized in that the control surface is located on an eccentric (39) attached to the anvil (15) and the transmission element is a ring (ko) rotatable on this eccentric, 19 · Impact device according to claim 18, characterized in that that the yoke (35) is rotatably mounted on the anvil (T5) and flows with the hammer (25). 009809/1095 20 «Striking device according to claim 19», characterized in that the ring (4o) located on the eccentric (39) is arranged so that it comes out of the system after the clubs (25) have been pivoted in and before they strike the stops (24) is released with the support surface and the yoke (35). 0G9809 / 1Ö95