FI75514B - SLAOENDE NUTTER- ELLER SKRUVDRAGARE. - Google Patents

Description

7551 4

Impact nut or screwdriver tool

The present invention is directed to assembly and assembly equipment, and more particularly to rotary impact tools.

The invention can be used very advantageously when assembling and disassembling devices for holding and moving threaded connections and objects, such as vices and levers.

10 Rotary Impact Tools are one of the most powerful machining tools used in assembly and installation work. The principle of operation of such a tool is based on the conversion of the continuous rotation of the drive motor into repetitive impulses (impacts) applied by the major rotating part (left-15 raela) to the main axis (spindle) of the tool.

Since the time during which the hammer member accumulates kinetic energy is much longer than the collision time (time the energy accumulated by the hammer member is transferred to the spindle), the force generated by the spindle is 400-500 times greater than the drive motor shaft force. This enables the production of high-power, small, low-weight tools. Another important advantage of rotating impact tools is that no reactive torque is transferred to the user's hands.

A rotary percussion tool is known in the art (cf. U.S. Pat. No. 2,718,803, U.S. Pat. No. 173-93.5), which comprises a housing surrounding a drive motor which transmits rotational movement through an intermediate member to a hammer member surrounding the mandrel. The spindle is coaxial with the intermediate member. It rests on one end 30 on the intermediate member and on the other end on the housing. Longitudinal projections are made on the outer surface of the mandrel, which co-operate with the corresponding projections on the inner surface of the hammer member. The hammer member is mounted to reciprocate along the guide portions in a plane perpendicular to the axis of rotation. The intermediate member which transmits the rotational movement of the hammer member is mounted directly on the drive motor shaft and has a fork-like knob which engages and projects the protrusion on the other end face of the hammer member. * pin on which the hammer member is mounted on the swivel. This bearing pin is attached to a holder surrounding the hammer member. As the hammer member rotates, the impact projections on the inner surface of the hammer member repeatedly engage, i.e., every 10 turns, the longitudinal projections on the outer surface of the mandrel, i.e., strike them. during rotation.

However, it can be seen from the above that in this known structure the advancing movement of the hammer member is caused by a group of components (intermediate member, holder, bearing pin), which significantly complicates the structure.

20 In addition, the fork-like crank of the intermediate member, which transmits the rotational movement to the hammer member, engages the end protrusion of the hammer member along a line, whereby a collision between the hammer member and the spindle along this line causes high contact loads

The reliability of the tool is also affected by the fact that one of the spindle supports is not rigid (the spindle rests against the shaft of the drive motor via an intermediate member). This causes, firstly, rapid wear of the spindle and hammer member projections in the event of a collision and, secondly, applies an additional dynamic load to the motor shaft.

A rotary percussion tool is also known in the art (cf. U.S. Patent 3,072,232, UK-Class 192-30.5), the structure of which is the closest prototype of the proposed structure. The tool has the same design of the intermediate and hammer members and the spindle projections 3 75514 as in the case described above »The rotational movement from the motor to the hammer member is also transmitted via the fork-shaped crank of the intermediate member and the end projection of the hammer member.

The main difference between this tool and that described above is that the holder containing the hammer member has a rectangular hole. The hammer member is also rectangular in its longitudinal section and mounted to move along the holder hole, thus acting as a guide for movement of the hammer member in a plane perpendicular to the axis of rotation.

10 Such a tool structure is simpler and more reliable than described above.

However, in order to achieve the movement of the hammer member, this structure also uses several components.

! In addition, the fork-like crank of the intermediate member engages the end projection of the hammer member 15 in the same way along a line which causes considerable contact loads which lead to rapid wear and malfunctions of the tool.

In this structure 20 as well, one of the spindle ends rests via the intermediate member on the shaft of the drive motor, which takes on dynamic loads when the hammer member impacts impacts on the spindle, which also affects the reliability of the tool.

The main object of the present invention is to provide a rotating percussion tool in which the intermediate member could be made to ensure a displaceable movement of the hammer member against the axis of rotation in a plane perpendicular to its rotation, which would improve reliability and simplify the tool structure compared to the known one.

In view of this main object, there is provided a rotary impact tool comprising a drive motor which transmits rotational movement through an intermediate member to a hammer member surrounding a coaxial mandrel 35 having protrusions on its outer surface corresponding to projections made on the inner surface of the impact member. parts for moving the hammer member against the axis of rotation in a perpendicular plane and a housing in which all parts of the tool are placed. The tool according to the invention is characterized in that the guide parts are made eccentric with respect to the axis of the rotor and are placed directly on the intermediate member which transmits the rotational movement to the hammer member.

Such a tool design allows its reliability to be improved due to the reduction of the contact loads between the hammer member and the intermediate member.

In one embodiment of the invention, the guide grooves are made along parallel tendons.

Such a structure of the guide parts is the simplest.

In another embodiment of the present invention, the guide members are made curved, having a common center of curvature.

Thanks to such a structure of the guide parts, the law of variation of the radius of curvature can be changed as the movement of the hammer member moves against the axis of rotation in a plane 20 perpendicular.

It is preferable to make the spacer a disc.

Such an intermediate body structure is the simplest.

In some cases, it is advantageous, when the spacer is made as a disc, to make the guide parts in two cuts on opposite outer surfaces of the disc and to form a groove in the end surface of the hammer member, the width of which corresponds to the distance between the cuts.

Such a structure of guide members is the simplest intermediate member for this embodiment.

When the intermediate member is made as a disc, it is most preferable to make the guide parts an end protrusion extending into a corresponding groove made in the end surface of the hammer member.

Such a structure of the guide parts makes it possible to improve the reliability of the tool 35, to reduce its dimensions and to expand its field of application.

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When the guide parts are made as end projections, it is preferable to provide the tool with a centering disc arranged on the free end surface of the hammer member coaxially with the main disc and having guide parts identical to the main disc guide parts and making both end surfaces of the hammer member identical.

Such a structure makes it possible to improve the reliability of the tool due to the more precise orientation of the projections of the hammer member with respect to the projections of the spindle.

In some cases, it is advantageous to make the intermediate member a holder surrounding the hammer member, to form the guide portions as a through groove and to make two cuts in the outer surface of the hammer member, the distance between which corresponds to the width of the groove.

With such a structure of the tool, its reliability can be improved due to the more precise orientation of the hammer member with respect to the axis of rotation and the reduction of the dynamic loads on the drive motor shaft.

It is also advantageous to mount the intermediate member on a mandrel which rests on both ends of the housing and to fit on the outer surface of the intermediate member a part which is kinematically connected to the drive motor.

This tool design improves its reliability due to the reduction in loads on the motor 25, as a result of which during collisions most of the loads are transferred from the spindle, hammer member and intermediate member directly to the housing. In addition, such a structure allows a significant reduction in the dimensions of the tool. In this construction, tool receiving arms can also be made at both ends of the spindle, which allows the direction of rotation of the tool to be changed by using one of the two arms.

The direction of rotation of the spindle, the hammer member and the drive motor still remains the same, i.e. a non-reversing motor with a much higher output power and reliability than the corresponding reversing motor can be used.

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It is preferable to make a Kinematic coupling part. as a bevel gear that engages a bevel gear mounted on the drive motor shaft, the shaft of which is inclined against the spindle axis * 5 This design of the tool allows its dimensions to be reduced along the vertical dimension.

In some cases, it is advantageous to make the kinematic clutch part a pulley connected by a belt to a pulley fitted to the motor shaft with the motor centerline parallel to the spindle centerline. Such a tool structure reduces the dynamic loads on the drive motor.

In many cases, it is preferable to make the kinematic clutch portion 15 into a spur gear that engages a spur gear mounted on the drive motor shaft, the center line of which is parallel to the center line of the spindle.

In such a structure, the transmission between the drive motor and the intermediate member is as tight and reliable as possible.

In some cases, it is advantageous to provide the mandrel with a threaded central hole fitted with a screw having a longitudinal keyway which cooperates with a key attached to the housing.

This design of the tool allows it to be used as a 25 force lever, rotary tensioner, screw clamp and other similar devices *

The present invention will become more apparent from the more detailed description of its embodiments with reference to the accompanying drawings.

Figure 1 is an overview of the tool in partial section.

Figure 2 is an exploded perspective view of the main part of the tool.

Fig. 3 is a sectional view taken along line 1-1 of Fig. 1 showing the mutual arrangement of the main parts of the tool at the moment of collision.

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Fig. 4 is a sectional view corresponding to Fig. 3 at the moment of release of the hammer member and the spindle projections,

Fig. 5 is a sectional view corresponding to Fig. 3 with the mandrel turned 180 °.

Fig. 6 is a sectional view corresponding to Fig. 3 before the collision.

Figure 7 shows a perspective view of the main part of the tool and the interaction of the intermediate member, the hammer member and the spindle in an embodiment of the guide parts.

Fig. 8 shows a partial sectional view of a tool made according to an embodiment with a centering disc.

Fig. 9 shows a partial sectional view of a tool made according to an embodiment in which the intermediate member is made as a holder.

Fig. 10 is a sectional view taken along line X-X in Fig. 9.

Fig. 11 shows a partial sectional view of a tool made according to an embodiment in which the outer surface of the intermediate member is provided with a part kinematically connected to the drive motor and made into a bevel gear.

Fig. 12 shows a partial sectional view of a tool made according to an embodiment in which the kinematic clutch part is made as a pulley.

Fig. 13 shows a partial sectional view of a tool made according to an embodiment in which the kinematic coupling part is made into a cylindrical gear ring.

A rotary impact tool made according to the invention comprises a drive motor 1 (Fig. 1) which transmits its rotational movement via an intermediate member 2 to a hammer member 3 surrounding a mandrel 4 coaxially with the intermediate member 2, the outer surface 7 of which is provided with projections 5 and 6 corresponding to the hammer member. 3 protrusions 8 and 9 made on the inner working surface 10 (Figs. 3-6). The tool also includes guide parts 11 for moving the hammer member 3 against a axis of rotation 35 (12) in a perpendicular plane (Fig. 2). All the above-mentioned 8 75514 parts of the tool are to be housed in the housing 13. The guide parts 11 (Fig. 3) are made eccentric with respect to the axis of rotation 12 (Fig. 2) and are located directly on the intermediate member 2 transmitting the rotational movement to the hammer member 3.

The intermediate member 2 is mounted directly on the shaft 14 of the drive motor 1 ak-5 (Fig. 1) and connected to it by, for example, a wedge 15, the spindle 4 resting on one end 16 on a bearing 17 in the housing 13 and extending on its other end 18 on a bearing 19 on the intermediate member 2. via to the shaft 14 of the drive motor 1.

An end 20 is made in the end 16 of the mandrel 4 for attaching a working member (not shown) in the drawing.

The guide parts 11 (Fig. 2) are most simply made along parallel tendons 21 and 22.

In another embodiment of the tool, the guide parts 11 15 (Fig. 4) are made curved, whereby their common center of curvature is located on the axis of symmetry 24 of the intermediate member 2.

Figure 2 shows an embodiment of a tool in which the intermediate member 2 is made as a disc 25 with a hub which is fitted to the shaft 14 of the drive motor 1.

Fig. 7 shows a case where the guide parts 11 are made in the disc 25 in two cuts 26 and 27 on the outer surface 28 of the disc 25. In this case, a groove 30 is made in the end surface 29 of the hammer member 3, the width corresponding to the distance between the cuts 25 26 and 27.

Both the sections 26 and 27 of the disc 25 and the respective surfaces 31 and 32 of the groove 30 have a common center of curvature 23 and a corresponding radius of curvature, respectively. Sections 26 and 27 may be made on the disc 25 equally well along rectilinear, parallel tendons (not shown in the drawing). In this case, the groove 30 of the end surface 29 of the hammer member 3 is also made straight.

In many cases, it is advantageous to make the guide parts 11 as end projections 33 (Fig. 2) which extend into a corresponding groove 34 made in the end surface 29 of the hammer member 35 3.

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The side surfaces of the protrusion 33 are in this case made rectilinear along parallel tendons 21 and 22. The end protrusion may just as well be made in the hammer member, whereby a corresponding groove is made in the end surface of the disc (not shown in the drawing).

It will be appreciated that in both of the above cases, the side surfaces of the protrusion 33 and the groove 34 may be made curved, thereby having a common center of curvature.

In the embodiment shown in Fig. 8, the tool 10 is further provided with a centering disc 35 arranged on the free end surface 36 of the hammer member 3 coaxially with the disc 25.

The end surface 37 of the centering disc 35 is provided with guide portions 38 which are identical to the guide portions 11 of the disc 25. The end surfaces 29 and 36 of the hammer member 3 are also made identical. The end surface 36 of the hammer member 3 is provided with a groove 39 which is identical to the groove 34 in the end surface 29 of the hammer member 3. The groove 39 receives the guide portion 38 formed as the end protrusion 40, and the groove 34 receives the guide portion 11 formed as the end protrusion 33.

Fig. 9 shows an embodiment of a tool in which the intermediate member 2 is made as a holder 41 surrounding the hammer member 3 (Fig. 10), the guide parts are represented by a through groove 42 and the outer surface of the hammer member 25 is provided with two cuts 44 and 45 spaced apart.

Fig. 11 shows an embodiment of a tool in which the intermediate member 2 is mounted on a spindle 4 resting at both ends 16 and 46 on bearings 30 17 and 47 arranged in the housing 13. The spindle ends 16 and 46 of the spindle 4 are provided with arms 20 and 48 supporting a working member such as a nut. a wrench (not shown in the drawing) fitted on top.

The outer surface of the intermediate member 2 is supplemented by a kinematic 35 coupling part 49 between the intermediate member 2 and the drive motor 1.

Fig. 11 shows an embodiment of a kinematic clutch part 49, 10 7551 4 made as a conical gear 50, the teeth of which are cut directly into an intermediate member 2 made of a disc 25. The gear 50 is geared by a bevel gear 51 fitted to the shaft 14 of the drive motor 1. to the shaft 14 by the wedge 15. The shaft 52 of the motor 1 is perpendicular to the shaft 12 of the spindle 4. Shaft 52 may as well form any other angle (not shown in the drawing) with shaft 12.

Fig. 12 shows an embodiment of a part 49 in which this part 10 is made as a pulley 53 connected by a belt 54 to a pulley 55 fitted to the shaft 14 of the motor 1. The shaft 52 of the motor 1 is parallel to the shaft 12 of the spindle 4.

Fig. 13 shows an embodiment of a part 49, in which this part 15 is made as a cylindrical gear 56 which is toothed on a cylindrical gear 57 arranged on the drive motor shaft 52 parallel to the shaft 12 of the spindle 4.

Figures 11, 12 and 13 show embodiments in which the intermediate part 2 is made as a disc 25. However, in these embodiments the intermediate member 20 can just as well be made as a holder (not shown in the drawing).

In another use of the tool, e.g. when used as a lever, the mandrel 4 (Fig. 13) is provided with a threaded hole 58 in which a screw 59 with a longitudinal keyway 25a 60 is inserted. The keyway 60 receives a key attached to the cover 62 of the housing 13. 4 is supported inside the housing 13 by a sleeve bearing 63 and a base bearing 64 fitted to the cover 65 of the housing 13.

The rotary percussion tool made in accordance with the present invention operates as follows.

In preparation for operation, the working member (not shown in the drawing) is connected to the arm 20 of the spindle 4. Power is then supplied to the motor 1, and the rotation of the shaft 35 is transmitted through the intermediate member 2 by the guide parts 11 (Fig. 2) to the hammer member 3. (Fig. 3) The protrusion 8 periodically (during each rotation) impacts the protrusion 5.

The hammer member 3 and the intermediate member 2 stop together with the spindle 4. However, the hammer member 3 continuously receives torque from the drive motor 1 (Fig. 1) through the intermediate member 2. As a result of this torque and spindle reaction P (Fig. 3), which is transmitted to the hammer member 3 at the point of contact between the projection 8 and the projection 5, the hammer member 3 begins to move in a plane perpendicular to the axis of rotation 2 along the guide members 11, This movement continues until the protrusion 9 on the inner working surface 10 of the hammer member 3 is forced against the surface 7 of the spindle 4 (Fig. 4). The hammer member 3 then begins to rotate together with the intermediate member 2 as a single unit and accumulates energy for the second impact. This rotation continues until the inner surface of the hammer member 3 contacts the protrusion on the outer surface of the mandrel 4, then simultaneously with the rotation due to the interaction between the inner working surface 10 and the protrusion 5 of the hammer member 3 moves along the guide portions 11 (Fig. 5) from the surface 7 and the projection 8 approaching it. The hammer member 3 moves along the guide parts 11 until the projection 8 is forced against the surface 7 of the spindle 4. This occurs at the moment when the protrusion 9 contacts the protrusion 5. Thereafter, the hammer member 3 (Fig. 6) and the intermediate member 2 again rotate as one unit without changing their mutual position. Thereafter, the protrusion 8 applies an impact to the protrusion 5, and the cycle is repeated. Before the impact occurs, the protrusion 8 disengages from the protrusion 6 (Fig. 3). This is necessary so that the hammer member 3 can move along the guide parts 11 after the impact with the projection 35 3 detaching from the projection 5. If the drive motor 1, intermediate member 12 7551 4 2 and hammer member 3 rotate in the opposite (counterclockwise) direction, the hammer member 3 projection 9 6, and in other respects the tool operation is similar to that described above ..

The intermediate member 2 together with the guide parts 11 thus provides the necessary mechanical path of movement of the hammer member 3 (rotation and forward movement in a plane perpendicular to the axis of rotation) when it cooperates with the spindle 4. This makes it possible to simplify the number of tool parts mini-10 and its structure. In addition, the guide parts of the intermediate member 2 and the hammer member 3 always work together along a certain plane, which reduces the contact stresses.

When the guide parts 11 (Fig. 2) are made along parallel tendons 21 and 22, the movement of the hammer member 3 (Fig. 3) 15 when the protrusion 8 detaches from the protrusion 5 takes place along a straight line.

Such a structure of the guide parts 11 is the simplest.

When the guide parts 11 (Fig. 7) are made curved with their common center of curvature 23 located on the axis of symmetry 24 of the intermediate member 2, the hammer member 2 moves along the guide parts 11 in an arc around the center of curvature 23 y. Such a structure of the guide parts 11 allows, due to the variation of the radius of curvature, a change in the mechanical trajectory of the hammer member as it moves against the axis of rotation in a straight-plane. This facilitates the detachment of the protrusion 8 of the hammer member 3 from the protrusion 5 of the spindle 4.

When the intermediate member 2 (Fig. 2) is made as a disc 25, the tool operates in exactly the order described above. Such a structure of the intermediate member 2 is the simplest.

When the guide parts 11 (Fig. 7) on the disc 25 are made in two cuts 26 and 27, the hammer member 3 moves along the cuts 26 and 27. After the impact, the hammer member 3 moves along the cuts 26 and 27. In doing so, it pivots around the center of curvature 23 and the protrusion 8 disengages from the protrusion 35 5. Forming the guide parts 11 in the disc 25 into two cuts is the simplest implementation.

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In the embodiment with the guide parts being made as the end protrusion 33 of the disc 25 (Fig. 2), the groove 34 made in the end surface 29 of the hammer member 3 slides over the protrusion 33 as the protrusion 8 disengages from the protrusion 5. In other respects the tool 5 is similar to described above.

This tool embodiment is the smallest in size and allows for the smallest overall dimensions of the tool. Since the outer surface of the disc 25 in this embodiment is free, the tool parts can be adapted in a new way, whereby the dynamic loads on the drive shaft 14 of the drive-10 can be reduced. If the centering disc 35 exists (Fig. 8), the rotation of the hammer member 3 passes through the groove 39 and the protrusion 40 in the second end face 36 to the centering disc 35. This causes the rotation of the disc 25, the hammer member 3 and the centering disc 35 simultaneously. As the hammer member 3 moves, the groove 34 slides along the protrusions 33 of the disc 25.

At the same time, the groove 39 slides along the protrusion 40. Thanks to the identity of the protrusions 33 and 40 and the grooves 34 and 39, both end faces of the hammer member move in synchronism throughout the operation of the tool.

When the intermediate member 2 is made into a holder 41 surrounding the hammer member 3 (Figs. 9, 10), the rotation from the drive motor 1 is transferred to the hammer member 3 through a through groove 42 made in the holder 41. As the hammer member 3 moves in a plane perpendicular to the axis of rotation, the cuts 44 and 45 slide along the groove 42, causing the protrusions of the hammer member 3 and the spindle 3 to disengage after impact. Since the cuts 44 and 45 are made along the entire length of the hammer member 3, the protrusions of the hammer member 3 are made more precisely positioned with respect to the protrusions of the mandrel 4.

In the clamping form of the tool, in which the intermediate member is mounted on a spindle 4 (Fig. 11) resting on both ends 16 and 46 of the housing 13, the rotation of the drive motor 1 is displaced when power is supplied to the intermediate member 2 via a kinematic coupling part 49.

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Because, the mandrel 4 both ends 16 and 46a are provided with working arms 20 and 48f, the rotation of the mouth can be modified by connecting either arm to the tool.

Due to collisions between the spindle 4, the hammer member 5 3 and the intermediate member 2 there will be no dynamic loads.

a large part moves directly to the housing 13, the dynamic loads acting on the motor are reduced. In addition, such an embodiment of the tool makes it possible to reduce the overall dimensions of the tool.

In the embodiment of the tool, in which the kinematic clutch part 49 is made as a bevel gear 50, the rotation from the drive motor 1 is transmitted to the intermediate member 2 through the bevel gear 51 and the gear 50. Such a tool structure allows the drive motor 1 to be fitted at any angle 15 against the axis of the spindle 4. In this case, the dimensions of the tool are as small as possible along its vertical dimension.

In another embodiment of the tool, where the kinematic clutch part 49 is made as a pulley 53 (Fig. 12), the rotor 20 from the drive motor 1 is transferred to the intermediate member 2 via a pulley 55, a belt 54 and a pulley 53 mounted on the shaft 14 of the drive motor 1. Due to the good damping properties of the belt drive, thanks to this structure, the dynamic loads on the drive motor 1 can still be reduced and thus the tool life can be extended.

In yet another embodiment of the tool, in which the kinematic clutch part 49 is made as a cylindrical gear 56 (Fig. 13), the rotation from the drive motor 1 is transmitted to the intermediate member 2 via the cylindrical gear 57 and the gear 56 30. Such a structure of the kinematic coupling part 49 is the simplest and smallest.

When the spindle 4 is provided with a threaded central hole 58 in which a screw 59 is placed (Fig. 13), the tool acts as a lifting device (such as a lever), the intermediate member 2, the hammer member 3 and the spindle 4 of the drive motor 1, 35 operating as described above. When the impact is applied to the spindle 4, 15 7551 4 it rotates through a certain angle and the screw 59 moves along the axis of the spindle 4. As the screws 59 move, the keyway 60 slides away from the key 61 attached to the cover 65 of the housing 13, which prevents the screw 59 from rotating together with the spindle 4. The direction of movement of the screw 5 59 is reversed by changing the direction of the drive motor 1.

Such an embodiment of a rotary percussion tool allows the tool to be moved forward and its field of application to be considerably expanded.

The invention has thus improved the service life and reliability of the tool, simplified its structure, reduced its dimensions and extended its field of application.

It is to be understood that the present invention is not limited to the particular embodiments set forth and described above, but that numerous other modifications may be made to the rotary impact tool without departing from the spirit and scope of the invention as defined in the appended claims.

Claims (8)

16 7551 4 An impact nut or screw turning tool comprising a drive motor (1) which transmits through a spacer (2) a rotational movement to a hammer member (3) surrounding a mandrel (4) coaxially fitted with the spacer (2) and having an outer surface there are projections (5, 6) corresponding to the projections (8, 9) made on the inner surface (10) of the hammer member (3), guide members (11) for moving the hammer member (3) against the rotary axis 10 in a perpendicular plane, and a housing (13) these parts of the torsion tool are arranged, characterized in that the guide members (11) are made eccentric with respect to the axis of rotation and are fitted directly to the intermediate member (2), which transmits the rotational movement to the hammer member (3). Torque tool according to Claim 1, characterized in that the guide elements (11) are formed along parallel spans (21, 22). Torque tool according to Claim 1, characterized in that the guide elements (11) are curved and have a common center of curvature (23). Torque tool according to one of Claims 1 to 3, characterized in that the intermediate element (2) is made as a disc (25). Torque tool according to Claim 4, characterized in that the guide members (11) are made in two sections (26, 27) on the outer surface of the disc (25) and in that the end surface (29) of the hammer member (3) is provided with a groove (30). corresponds to the distance between the cuts (26,27). . A torsion tool according to claim 4, characterized in that the guide members (11) are formed as an end protrusion (33) extending into a corresponding groove (34) made in the end surface of the hammer member (3). A torsion tool according to any one of claims 1 to 3, characterized in that the intermediate member (2) is formed as a holder (41) surrounding the hammer member (3), that the guide members (11) are formed as a through groove (42), and 17 7551 The outer surface of the 4 hinge members (3) is provided with two cuts (44,45), the distance between which corresponds to the width of the groove (42). Torsion tool according to one of Claims 1 to 7, characterized in that the spindle (4) is provided with a threaded central hole (58) for receiving a screw (59) with a longitudinal keyway (60) cooperating with a housing (13). with the wedge (61). 18 7551 4