EP0759340B1 - Impact tool - Google Patents

Description

The invention relates to an impulse tool, in particular a screwdriver, with the features the preamble of claim 1.

Such a pulse tool is known from EP 0 353 106 B1. With this are next two sealing rollers two additional sealing wings or drive plates in the drive spindle the pulse unit is radially adjustable in appropriate grooves. These grooves run for the sealing wing along a diameter of the output shaft or spindle, while the corresponding grooves for the sealing rollers are an obtuse angle smaller Include as 180 ° with the longitudinal direction of the drive spindle. Because of this inclination The grooves for the sealing rollers to each other ensure that only one Rotation position one pulse is transmitted per 360 ° rotation. The effort to manufacture of such an impulse tool and the corresponding costs are relatively high.

Another pulse tool is known from EP 0 254 699 B1. With this previously known The sealing rollers are always in contact with a rolling surface and in particular tools every half a turn of the hydraulic cylinder with the corresponding Sealing strips or compression bars in the system. Offset by 90 ° to the sealing rollers projecting ribs are arranged on the output shaft or drive spindle an inclined axis of rotation of the output shaft. Corresponding rib-like projections are also provided on the inner wall of the hydraulic cylinder.

With this previously known pulse tool, too, the inclination of the ribs Output shaft and inner wall of the hydraulic cylinder ensured that only in one Rotational position of the cylinder, the sealing rollers and the ribs four separate from each other Limit the chambers between the output shaft and the inner wall of the hydraulic cylinder. Two of these chambers are high-pressure chambers or low-pressure chambers. The pressure difference between these chambers creates in a known manner an angular momentum that is applied via the output shaft to fasten or loosen a screw or mother is transferable.

By generating one pulse after a 360 ° rotation of the hydraulic cylinder, there is a longer acceleration phase during the rotary movement and so that a larger pulse can be generated.

A disadvantage of the pulse tool known from EP 0 254 699 B1 is that the Structure of the pulse unit is relatively complex. In addition to the two sealing rollers and radial grooves are additionally two ribs on the output shaft and on the inner wall of the To produce hydraulic cylinders that run inclined. This makes it more difficult and more expensive the production of the known pulse tool. Finally, the disadvantage is that the ribs must be made with high accuracy in order for the seal between the ribs of the output shaft and hydraulic cylinder is sufficiently good. On certain wear of the ribs and thus deterioration of the seal but not to be prevented after a certain period of use of the pulse tool.

The invention is based on the pulse tool known from EP 0 353 106 B1 based on the task of improving the known impulse tool in such a way that its construction is inexpensive while extending the operating time is simplified.

This task is related to an impulse tool with the features of the preamble of claim 1 solved in that the delayed radial movement a sealing roller serving as a compensating roller to the outside whose radial groove Stroke delay device.

In contrast, in EP 0 353 106 B1 identical sealing rolls are identical dovetail-shaped grooves are designed to prevent the rollers from emerge from their grooves.

The stroke delay device according to the invention ensures that the Compensating roller in its radial groove a radial movement outwards in the direction Performs hydraulic cylinder. However, this movement occurs during one revolution of the cylinder so delayed that the compensating roller in a single rotational position a sealing strip is in contact. The radial movement can be decelerated to the extent that even during the remaining rotation of the hydraulic cylinder, the compensating roller only and is partially in contact with a sealing surface. This allows a corresponding incompressible medium, such as a hydraulic fluid, unimpeded between the output shaft and hydraulic cylinders flow and only in the single rotary position, namely the pulse position, the interior between output shaft and hydraulic cylinder is divided into two Chambers, a high pressure and a low pressure chamber, separated.

In contrast to the known pulse tool, no additional ribs are on Output shaft and / or inner wall of the hydraulic cylinder with selected inclination required. By applying force to the sealing rollers towards the inner wall even when the pulse tool is in use for a long time, it is still in the pulse position the sealing strips in plant so that an impulse can be transmitted.

To further simplify the manufacture of the pulse tool according to the invention, are compensating roller and other sealing rollers, which serve as an impulse roller, and associated ones Radial grooves 180 ° offset from each other.

One exemplary embodiment of a stroke delay device is characterized in that that this is formed by the guide of the compensating roller in its radial groove, the Leveling roller compared to the impulse role with less play is guided in its radial groove. This game achieves that the exchange of hydraulic fluid over the low Play between radial groove and compensating roller during one complete rotation of the hydraulic cylinder is not complete can be carried out. This leads to the delayed fluid exchange in addition to a certain vacuum between the compensating roller and radial groove, which supports the stroke deceleration.

Instead, the game between radial groove and impulse roll is like this great that the exchange of hydraulic fluid is essentially already directly after contact with the associated sealing strip and thus the impulse role in its radial movement without restriction or is not delayed. It goes without saying that the Radial movement of the compensating roller at least so far without restrictions is that they are each in the pulse position with the associated Sealing strip is in plant.

A different game between radial grooves and sealing rollers can be produced by, for example, a compensating roller and pulse roller have the same dimensions and the radial grooves are different. It is also possible that the Radial grooves of the same dimensions and compensation and impulse roller have different diameters. The radial grooves with an open to the circumference of the output shaft, in be substantially rectangular cross-section.

In both cases, it is through appropriate choice of dimensions possible to use the compensating roller in comparison to the impulse roller lead to less play in their radial groove.

A simple application of force to the sealing roller towards the inside wall of the cylinder can be realized in that between the groove bottom and the sealing rollers, a spring element, in particular a leaf spring is arranged.

In this context, the stroke delay device can additionally to the guides mentioned above can be realized that to the limited radial movement of the compensating roller the spring constant of the associated spring element is less than the spring constant of the spring of the impulse roller.

Because in particular the inner wall of the hydraulic cylinder and the Sealing strips of heavy wear when operating the pulse tool exposed, it is advantageous if the inner wall of the hydraulic cylinder at least in the area of Sealing rollers is formed by a hydraulic sleeve on the Inside the sealing strips are arranged. If the Sealing strips, only the hydraulic sleeve is replaced. The rest Pulse unit can still be used.

Around the high pressure and low pressure chambers in the angular momentum position are easy to form on the inside of the Hydraulic sleeve formed between the sealing strips pockets. They can be identical or with different dimensions for High pressure and low pressure chamber are manufactured.

With a simple construction of the hydraulic sleeve, the pockets are by protruding radially from the inside of the hydraulic sleeve Inner ring flanges limited, along which at least the impulse roller rolls off while the balancing roller, for example only shortly before reaching the pulse position along the inner ring flanges rolls off. As a rule, the inner ring flanges formed by end portions of the hydraulic sleeve in the axial direction.

In order to enable safe and smooth guidance for the sealing rollers, determine the inner ring flanges two concentric to each other, arranged eccentrically within the cylinder, from circles touching the sealing strips. Rolls along these circles at least the impulse role.

The manufacture of the pulse tool and in particular the pulse unit to further simplify, it turns out to be convenient if ends of the sealing strips by diametrically opposite Sections of the inner ring flanges are formed. A separate Formation of sealing strips and inner ring flanges this way not necessary. The sealing strips extend thereby in the axial direction from an inner ring flange to other.

To easily hydraulic sleeve and sealing rollers inside to fix the hydraulic cylinder, these are within the Hydraulic cylinder arranged between two lateral contact discs, where the engine washer adjacent to one radially inward protruding shoulder of the hydraulic cylinder and the opposite contact disc on one in the hydraulic cylinder screw-in bearing ring.

For example, to fill the pulse unit with hydraulic fluid it is beneficial if a central hole is concentric to the output shaft and at least over part of the output wavelength is trained in this. Through appropriate openings between the central bore and the interior of the hydraulic sleeve the hydraulic fluid before the pulse tool is used for the first time and with appropriate pressure in the pulse unit be introduced.

The central bore can also be used to determine the pressure inside of the formed between the output shaft and hydraulic sleeve Fluid space can be used. It is beneficial if at least one connection hole each in the output shaft is formed between the radial grooves, which central bore and fluid space connects. The pressure determination can be done in a known manner Way done by an appropriate pressure sensor.

To make the connection hole easy, it is radial formed in the output shaft and by 90 ° to each Radial grooves offset.

To a sufficient pressure in the high pressure chamber until it is reached to build up the momentum, it is an advantage if a throttle bore between the central bore and a connecting bore with less compared to the rest of the connecting hole Cross section is formed.

For setting a passage cross section of the throttle bore and thus proves to adjust the hardness of a shock pulse it is particularly advantageous if a valve screw for stepless and adjustable closing of the throttle bore is screwed into the central bore.

To vibrate the pulse unit when generating the pulses dampen, it is still beneficial if a compensating piston on an end of the hydraulic cylinder facing the engine postponed and sealed against it.

Is for the relative displacement of the compensating piston and hydraulic cylinder a valve between the compensating piston and the fluid chamber for pressurizing the sealed against the hydraulic cylinder Area of the compensating piston arranged by the relative displacement between the compensation piston and Hydraulic cylinder builds up pressure while filling the pulse unit be monitored with hydraulic fluid. Likewise can from a reduction in the relative displacement after filling the Pulse unit with hydraulic fluid or from one The shift does not occur during filling that there is a leak in the pulse unit.

An embodiment of the invention is in following explained with reference to the accompanying figures and described.

Figur 1

einen Längsschnitt durch ein pistolenartiges Impulswerkzeug;

Figur 2

einen Längsschnitt durch eine vergrößerte Impulseinheit aus Figur 1;

Figur 3

einen Schnitt entlang der Linie III-III aus Figur 2 zur Darstellung einer ersten Bewegungsphase von Hydraulikzylinder relativ zu Abtriebswelle;

Figur 4

eine zweite Bewegungsphase analog zu Figur 3;

Figur 5

eine dritte Bewegungsphase analog zu Figur 3;

Figur 6

eine vierte Bewegungsphase analog zu Figur 3;

Figur 7

eine fünfte Bewegungsphase analog zu Figur 3; und

Figur 8

eine sechste Bewegungsphase analog zu Figur 3, wobei Abtriebswelle und Hydraulikzylinder in einer Impulsstellung sind.

Show it:

Figure 1

a longitudinal section through a pistol-like pulse tool;

Figure 2

a longitudinal section through an enlarged pulse unit of Figure 1;

Figure 3

a section along the line III-III of Figure 2 showing a first phase of movement of the hydraulic cylinder relative to the output shaft;

Figure 4

a second movement phase analogous to Figure 3;

Figure 5

a third movement phase analogous to Figure 3;

Figure 6

a fourth movement phase analogous to Figure 3;

Figure 7

a fifth movement phase analogous to Figure 3; and

Figure 8

a sixth movement phase analogous to Figure 3, wherein the output shaft and hydraulic cylinder are in a pulse position.

1 shows a longitudinal section through a pulse tool 1. The cut does not extend through in one housing 49 of the pulse tool 1 arranged components.

The pulse tool 1 has a pistol-like outline, wherein in a handle 50 a pusher 51 and connections 52 and 53 are arranged for compressed air and exhaust air. The pusher 51 is slidably mounted in the handle 50 by means of a plunger 54. The free end of the plunger 54 is adjacent to one Free end of a tilt valve 55 is arranged. By moving the Push button 51 to the right in FIG. 1 is the ram 54 Tilting valve 55 also tilted to the right. This will make a Valve plate 56 pivoted against the force of a compression spring 57 and gives an opening for the supply of compressed air via compressed air connection 52 to a motor 3 free.

The compressed air passes along a line 66 to the compressed air motor trained motor 3. Its direction of rotation is through a switch button 58 switchable.

With the motor 3 is a pulse unit via a connector 47 2 connected, which rotates accordingly with motor 3. A gearbox can be used between the motor 3 and the pulse unit 4 Coupling (not shown) may be arranged.

The pulse unit 2 is rotatably supported in the housing 49 Hydraulic cylinder 4, one on this on its engine side End fitted compensation piston 42, a bearing ring 35 and an output shaft 5 are formed. The output shaft 5 protrudes from the housing 49 like a pistol, on her protruding end a connector sleeve 44 is attached.

For rotatable mounting of hydraulic cylinder 4 and / or bearing ring 35 of the output shaft 5 is at least one slide bearing 46 shown between these and the housing 49.

The compressed air supplied to the motor 3 via line 66 becomes corresponding via the exhaust port 53 from the pulse tool 1 dissipated.

In FIG. 2, the pulse unit 2 from FIG. 1 is enlarged and shown in longitudinal section.

The hydraulic cylinder 4 of the pulse unit 2 is one-sided open cylinder. A hydraulic sleeve 21 is inserted in it, which bears against its inner wall 10. At both ends in Axial direction 23 of the hydraulic sleeve 21 are contact discs 32 and 33. The engine disk 33 closer to the engine is located on one in the radial direction 29 inwardly projecting paragraph 34 of the Hydraulic cylinder 4. This forms an annular one Stop against which in the direction of connector 47 to the engine a cylindrical cavity with compared to the cross section of the Hydraulic cylinder 4 reduced in the region of the hydraulic sleeve 21 Cross section connects.

Inside the hydraulic cylinder 4 and the hydraulic sleeve 21 the output shaft 5 is rotatably mounted. The output shaft 5 extends essentially from the connector 47 through the hydraulic cylinder 4 and protrudes from its open end. The output shaft 5 essentially has a circular shape Cross-section, two in the area of the hydraulic sleeve 21 diametrically opposite, extending in the axial direction 23 Radial grooves 8 and 9 are formed in the output shaft 5. Furthermore, one extends concentrically to the output shaft 5 extending central bore 36 approximately over half the length of the Output shaft 5. This central bore 36 is in the above End section of the output shaft 5 with a hexagon socket designed to accommodate nuts or screws.

The output shaft 5 is in the hydraulic cylinder 4 both in the cross section of the motor-side end section of the Hydraulic sleeve as well as in one in the open end of the hydraulic sleeve 4 screwed bearing ring 35 rotatably mounted. The Bearing ring 35 is with its larger diameter section screwed into the hydraulic sleeve 4 so far that it on the Contact disc 32 lies opposite the hydraulic sleeve 21. By screwing in the bearing ring 35, there are contact rings 32 and 33 and hydraulic sleeve 21 within the hydraulic cylinder 4 fixed in the axial direction.

In the radial grooves 8 and 9 are used as a compensating roller Sealing roller 6 and a sealing roller serving as an impulse role 7 slidably supported in radial directions 29. The length 24 of the sealing rollers 6 and 7 corresponds to the length of the hydraulic sleeve 21 in the axial direction 23. Between groove bottoms 17 and 18 the radial grooves 8 and 9 and the sealing rollers 6 and 7 are leaf springs 19 and 20 arranged radially after the sealing rollers pressurize outside.

On the side opposite the radial grooves 8, 9 are the Sealing rollers 6, 7 with radially inwardly projecting inner ring flanges 27 and 28 of the hydraulic sleeve 21 in contact, the ends form the hydraulic sleeve 21 in the axial direction 23.

The radial grooves 8, 9 extend over a greater length as sealing rollers 6, 7 in the axial direction 23 and are on both sides about this and the system discs 32 and 33 before.

To connect the radial grooves 8, 9 to the central bore 36 are filling openings 66 on the end of the radial grooves facing away from the motor educated. There is also an output shaft 5 and hydraulic sleeve 21 formed fluid space 39 via connecting holes 37 and 38 (not shown in Figure 2) with the central bore 36 connected. Connection bore 37 and a later described Throttle bore 40 are through a in the central bore 36 screwed valve screw 41 continuously and adjustable coverable. 2 is the Valve screw 41 is screwed into the central bore 36 only so far, that the illustrated connection bore 37 and covered is.

At the motor end of the hydraulic cylinder 4 is on this a compensating piston 42 is attached. To secure it and a relative displaceability between compensating pistons 42 and hydraulic cylinders 4 are a series of Shims 48 and shims 49 on the hydraulic cylinder plugged adjacent to connector 47. This Washers are in place by a snap ring 60 secured.

For sealing the compensating piston 42 from the hydraulic cylinder 4, two O-rings 61 are provided. More 0 rings 61 serve to seal the output shaft 5 within the hydraulic cylinder 4, to seal the in the hydraulic cylinder 4 screwed bearing rings 35 and for sealing the output shaft 5 compared to the bearing ring 35 or Valve screw 41.

Between the fluid space 39 and the compensating piston 42 is a Valve 43 is arranged inside the wall of the hydraulic cylinder 4. An associated valve ball lies on the contact disk 33 and is moved by an associated compression spring towards the system disc 33 powered. Via the valve 43 is below Pressurized hydraulic fluid between the sealed area Compensating piston 42 and hydraulic cylinder 4 can be supplied. As a result, the compensating piston 42 is relative to the hydraulic cylinder 4 in Figure 2 to the right depending on the prevailing pressure.

In the following Figures 3 to 8, six different movement phases represented by hydraulic cylinder 4 and output shaft 5, 3 shows a section along the line III-III from Figure 2 and Figures 4 to 8 a section analogous to Figure 3 in subsequent phases of movement. Same Parts are identified by the same reference numerals.

The inner ring flanges 27 and 28 according to FIG. 2 make two concentric to each other, eccentric to the hydraulic cylinder 4 arranged circles 30, 31 determined. With these circles are 3 pulse roller 7 and compensating roller 6 in the system. The Fluid space 39 between the output shaft 5 and the inside 22 of the hydraulic sleeve 21 is formed by two pockets 25 and 26 which between two radially projecting sealing strips 11 and 12 extend. In the axial direction 23, see FIG. 2, the pockets extend between the inner ring flanges 27 and 28. Since the bags communicate with each other, is even when the hydraulic cylinder 4 and the hydraulic sleeve 21 rotate in the direction of rotation 62 an exchange of the hydraulic fluid 63 between the bags possible. Only in the pulse position according to the figure 8 are the pockets created by the balance roller 6 and impulse roller 7 on sealing strips 11 and 12 from each other Cut. In this position, the cylinder 4 generates a pulse the output shaft 5 transmitted.

3 shows the connecting bores 37 and 38, which are offset by 90 ° relative to the sealing rollers 6, 7 and are arranged diametrically to each other. The connecting hole 38 is with a central bore 36 by means of a throttle bore 40 connected. The cross section of the throttle bore is less than the cross section of the connecting bore 38.

Figure 3 shows a 60 ° compared to a pulse position in Direction of rotation 62 represents twisted movement phase The way in the movement phases according to FIGS. 4 to 8 is the hydraulic cylinder 4 with sealing sleeve 21 by a further 60 ° each the output shaft 5 rotated.

In the next movement phase according to FIG. 4, the effect of the Stroke delay device 13 recognizable. During the impulse role 7 due to the force applied by leaf spring 40 and their leadership in radial groove 9 with a relatively large game 15 in plant with circles 30, 31, takes place at compensating roller 6 delayed radial movement towards circles 30, 31. This results from the stroke delay device 13, which by the leadership of the compensating roller in its radial groove 8 with in Comparison to game 15 of impulse role 7 less game 14 he follows. In addition to guiding the compensating roller 6 in its radial groove 8, the stroke delay device 13 can thereby additionally be formed that leaf spring 41 a compared to Leaf spring 40 has a lower spring constant, whereby the restoring force acting on compensating roller 6 less than at Pulse role 7 is.

In Figure 5, the pulse roller 7 is in contact with the sealing strip 11, while due to the stroke delay device 13, the compensating roller 6 arranged at a distance from the further sealing strip 12 is. As a result, hydraulic fluid continues to be exchanged 63, see Figure 3, between the pockets 25 and 26th

In Figure 6, hydraulic cylinder 4 and hydraulic sleeve 21 are around rotated another 60 ° in the direction of rotation 62 with respect to the output shaft 5.

After a further rotation of 60 °, the compensating roller 6 is in System with circles 30, 31, that is, it lies on the inner ring flanges 27 and 28 according to FIG. 2.

In the last movement phase according to FIG. 8, the pulse position, are both balancing role 6 and pulse role 7 with the corresponding sealing strips 11 or 12 in the system, so that the pockets 25, 26 are separated and an exchange of hydraulic fluid between these pockets no longer can take place. As a result, the pocket 26 becomes a high-pressure chamber 64 and the bag 25, see Figure 3, to a low pressure chamber 65. The different pressure conditions in the chambers are distinguished by a different number and one different sizes of circles to represent the hydraulic fluid 63 shown.

The connection of high pressure chamber 64 and low pressure chamber 65 via the connecting bores 37 and 38 and via the throttle bore 40 can be done by screwing in the valve screw 41 are limited according to Figure 2, whereby the hardness of the on the output shaft 5 in Figure 8 transmitted pulses adjustable is.

Subsequent to Figure 8 are the movement phases of the figures Run through 3 to 8 repeatedly, with the output shaft 5 after every pulse transmission by a small angle in the direction of rotation 62 is rotated further.

The sealing strips 11 and 12 are designed with different heights, so that due to the stroke delay device 13 Compensating roller 6 during one revolution of the hydraulic cylinder 4 so far from its radial groove over the circumference 16 of the output shaft 5 moved out that they only continue with the radial inwardly projecting sealing strip 11 comes into contact. Farther it should be noted that the sealing strips 11 and 12 between extend the inner ring flanges 27 and 28 and connect them. They are of the same height as this, so that in the pulse position according to FIG. 8 compensating roller 6 and pulse roller 7 over their entire length 24 with the inner ring flanges 27 and 28 and the sealing strips 11 and 12 are in the system.

It should also be noted that the sealing strips 11 and 12 are shown for emphasis with exaggerated height. For the same reason, the representation itself became better known Components, such as a shutdown device for the motor when a set torque is reached or the like, dispensed with in FIGS. 1 and 2.

In the following, the function of the pulse tool is referred to briefly described on the figures.

When screwing screws or nuts using the Hydraulic cylinder 4 and output shaft 5 become the pulse tool due to the friction between them and the rotational movement the motor 3 rotated. Starting from the screw or nut is only hydraulic cylinder 4 with hydraulic sleeve 21 through the Motor 3 rotated further, in each pulse position according to the figure 8, an angular momentum is transmitted to the output shaft 5, whereby Screw or nut by a certain angle of rotation be screwed in. The sum of all of these at each angular momentum The transmitted angle of rotation gives the entire tightening angle and similarly a tightening torque for the screw / nut. By monitoring the pressure within the high pressure chamber, the is related to the transmitted tightening torque, can when a predetermined maximum tightening torque is reached for example the movement coupling between pulse unit 4 and motor 3 or the compressed air supply to motor 3 is interrupted become.

The pulse unit 2 is with an incompressible medium to Example a hydraulic fluid filled. When the hydraulic cylinder rotates 4 and the hydraulic sleeve 21 are due to the eccentric arrangement of the circles 30, 31 the sealing rollers in their radial grooves, or by the spring elements and the stroke delay device controlled. The sealing rollers are only in a single rotational position of the hydraulic cylinder 4 along their entire length with the inside 22 of the hydraulic sleeve 21. In this position, the fluid space 39 separated into a high pressure chamber and a low pressure chamber. This position corresponds to the transmission of impulses to the output shaft 5. The transfer only takes so long until the Sealing strips 11, 12 have run over the sealing rollers and Output shaft by a certain angle of rotation due to the different Pressure conditions in the chambers. This is followed by the next rotation of the hydraulic cylinder 4 an acceleration of the pulse unit again.

So that it doesn't turn into a second after just another 180 ° rotation Impulse comes through the stroke delay device and the momentum of the momentum unit achieves that exchange hydraulic fluid through the relatively large clearance between the radial groove and impulse role takes place completely and the impulse role is unaffected in its radial movement. The small Game between the radial groove 17 and the compensating roller 6 allowed for during the short time one revolution of the hydraulic cylinder does not allow sufficient exchange of hydraulic fluid, so that due to the resulting negative pressure and possibly lower spring constant of the associated leaf spring 19, the radial movement of the compensating roller is limited or delayed.

Because of this, the pulse unit can be accelerated over a full revolution, what is the energy transfer to the bolt / nut compared to the transfer increased by two pulses per revolution.

One possibility, the pulse tool according to the invention as a multiple and in particular To use as a two-pulse unit is to use two in the latter case the compensating rollers and impulse rollers in radial grooves of the output shaft described above to be provided with appropriate stroke delay devices for the compensating rollers. In this way, each revolution of hydraulic cylinder 4 with hydraulic sleeve 21 each transmit two pulses to the output shaft.

Of course, appropriate sealing strips and connecting holes can be arranged analogously for two compensating rollers and two impulse rollers.

Claims (20)

1. A pulse tool (1), especially a nutsetter, comprising a pulse unit (2) which includes a hydraulic cylinder (4) driven by a motor (3) and a driven shaft (5) supported in said cylinder, two seal rollers (6, 7) being displaceably supported in radial grooves (8, 9) of said driven shaft and power-operated in the direction of the inner wall (10) of said cylinder (4), which seal rollers (6, 7) are simultaneously in contact in only one single rotary position of said cylinder (4) with seal strips (11, 12) radially projecting inwards to different extents relative to said inner wall (10) of said cylinder for producing an angular momentum,
   characterized in
   that for the outwardly oriented delayed radial movement of a seal roller which serves as a compensating roller (6), the radial groove (8) thereof comprises a lift delaying means (13).
2. A pulse tool according to claim 1,
   characterized in
   that said compensating roller (6) and said other seal roller serving as a pulse roller (7) as well as the associated radial grooves (8, 9) are arranged relative to one another such that they are offset by 180°.
3. A pulse tool according to claim 1 or 2,
   characterized in
   that said lift delaying means (13) is formed by said compensating roller (6) being guided in the radial groove (8) thereof, said compensating roller (6) being guided in its radial groove (8) with less play than said pulse roller (7).
4. A pulse tool according to any one of claims 1 to 3,
   characterized in
   that said compensating roller (6) and said pulse roller (7) have the same dimensions, and said radial grooves (8, 9) have different widths.
5. A pulse tool according to any one of claims 1 to 3,
   characterized in
   that said radial grooves (8, 9) have the same dimensions and a substantially rectangular cross-section which is open towards the circumference (16) of said driven shaft (5), and compensating and pulse rollers (6, 7) have different diameters.
6. A pulse tool according to any one of the preceding claims,
   characterized in
   that a spring element (19, 20), especially a leaf spring, is arranged between groove bottom (17, 18) and seal rollers (6, 7).
7. A pulse tool according to claim 6,
   characterized in
   that said spring element (19) of said compensating roller (6) has a smaller spring constant than that of said pulse roller (7).
8. A pulse tool according to any one of the preceding claims,
   characterized in
   that said inner wall (10) of said hydraulic cylinder (4) is formed at least in the area of said seal rollers (6, 7) by a hydraulic sleeve (21) on the inside (22) of which said seal strips (11, 12) are arranged.
9. A pulse tool according to any one of the preceding claims,
   characterized in
   that pockets (25, 26) are provided on the inside (22) of said hydraulic sleeve (21) between said seal strips (11, 12).
10. A pulse tool according to claim 9,
    characterized in
    that said pockets (25, 26) are defined by inner ring flanges (27, 28) which project radially from the inside (22) of said hydraulic sleeve (21) and along which at least said pulse roller (7) rolls.
11. A pulse tool according to claim 10,
    characterized in
    that said inner ring flanges (27, 28) define two circles (30, 31) which are concentric to one another and are eccentrically arranged within said cylinder (4) and touched by said seal strips (11, 12).
12. A pulse tool according to any one of claims 10 and 11,
    characterized in
    that diametrically opposite sections of said inner ring flanges (27, 28) form ends of said seal strips (11, 12).
13. A pulse tool according to any one of the preceding claims,
    characterized in
    that hydraulic sleeve (21) and seal strips (11, 12) are arranged within said hydraulic cylinder (4) between two lateral contact washers (32, 33), said contact washer (33) which is next to said motor (3) resting on a radially inwardly projecting shoulder (34) of said hydraulic cylinder (4) and said opposite contact washer (32) resting on a bearing ring (35) which is adapted to be screwed into said hydraulic cylinder (4).
14. A pulse tool according to any one of the preceding claims,
    characterized in
    that a central hole (36) is made concentric to said driven shaft (5) and is formed in said shaft at least over part of the length of said driven shaft.
15. A pulse tool according to claim 14,
    characterized in
    that at least one respective connection hole (37, 38) is formed in said driven shaft (5) between said radial grooves (8, 9), said connection hole connecting said central hole (36) and a fluid chamber (39) formed between driven shaft (5) and hydraulic sleeve (21).
16. A pulse tool according to claim 15,
    characterized in
    that said connection hole (37, 38) is radially formed in said driven shaft (5) and offset by 90° each relative to said radial grooves (8, 9).
17. A pulse tool according to any one of claims 15 and 16,
    characterized in
    that a throttle hole (40) is formed between central hole (36) and a connection hole (37) with a cross-section being reduced in comparison with the remaining connection hole (37).
18. A pulse tool according to claim 17,
    characterized in
    that a valve screw (41) is screwed into said central hole (36) for closing said throttle hole (40) in an infinitely variable and adjustable manner.
19. A pulse tool according to any one of the preceding claims,
    characterized in
    that a compensating piston (42) is slid onto an end of said hydraulic cylinder (4) facing said motor (3), and is sealed relative to said end.
20. A pulse tool according to claim 19,
    characterized in
    that for the relative displacement of compensating piston (42) and hydraulic cylinder (4) between compensating piston (42) and fluid chamber (39) a valve (43) is arranged for applying pressure to the area of said compensating piston that is sealed relative to said hydraulic cylinder (4).

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