JPS58126073A - Rotary impact tool - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to mounting and assembly devices, and more particularly to rotary impact tools.

The present invention can be most advantageously used in devices for assembling and disassembling screw coupling members, thread cutting members, and for holding and moving eyelid items, such as vises, jacks, etc.

Rotary impact tools are the most effective means used to perform assembly and installation tasks. The basic surface action of such a tool is the continuous rotation of the drive motor at each in/? It is to convert into Luz (impact), and such in/IF
The force is applied to the output shaft (spindle) of the tool by a rotating member (hammer member) with a large mass.

Since the time for the accumulation of mechanical energy by the hammer member is much greater than the time of impact (the time for transferring the energy stored by the hammer member to the spindle), the force generated on the spindle is power) will also be 400 to 500 times greater. This in turn makes it possible to produce very high power percussion devices with low mass. Another important advantage of rotary impact tools is that less reaction torque is transferred to the operator's hands.

A rotary impact tool known in the prior art (U.S. Patent No. 2)
, 718.803 USCj81-523)a includes a case housing a drive motor, which transmits its rotation via an intermediate member to a hammer member surrounding the spindle. The spindle is coaxial with the intermediate member. The spindle has one end supported by the intermediate member and the other end supported by the case. Spindle K
It is provided with a longitudinal protrusion formed on the outer circumferential surface.

These projections cooperate with corresponding projections provided on the inner surface of the hammer member. The hammer is mounted so as to reciprocate along a guide means in a plane perpendicular to the rotating shaft. The intermediate member that transmits the rotation to the hammer member is directly attached to the shaft of the drive motor and has a fork-like drive part, which engages with a protrusion on the - side of the end face of the hammer member. By fitting together, rotation is transmitted to the hammer member via this protrusion. In this structure, the transition of the hammer member in the plane perpendicular to the rotation axis is
This is done by the pivoting of the hammer member relative to it. This peat is fixed in a holder surrounding the hammer part. When the hammer member rotates, the impact protrusion on the inner surface of the hammer member
It swivels, ie, each rotation, engages a longitudinal projection on the outer surface of the spindle (ie, imparts an impact force to the longitudinal projection). The rocking of the hammer part around the bit (transfer of the hammer part) releases the protrusion of the hammer part from the spindle protrusion after the collision and causes the hammer part to move with respect to the spindle protrusion during rotation. The protrusion swings as necessary.

However, as is clear from the above description, according to the configuration of this prior art, the transition of the hammer member is provided by a group of component members (intermediate member, holder, biggft), but the structure of the kana is complicated. becomes.

Moreover, the fork-like drive member of the intermediate member, which transmits the rotation to the hammer member, engages the end projection of the hammer member along a straight line and the collision of the hammer member with the spindle along this straight line. resulting in higher contact stresses, resulting in
This may cause dents on the surface of the fork-like drive, the hammer member may become stuck, or the tool may become damaged.

The reliability of the tool is also influenced by the fact that one of the supports of the spindle is not rigid (the spindle is supported via an intermediate member to the shaft of the drive motor). This results, firstly, in collisions causing premature wear of the protrusions on the spindle and hammer parts, and secondly in the application of additional dynamic loads on the motor shaft.

Other rotary impact tools known in the prior art (U.S. Pat. No. 3,072,232 US, C1173-93,5
) is most similar to the structure disclosed here. This tool is similar to the one described above with respect to the intermediate part and hammer part and projections on the spindle. Rotation from the motor to the hammer member is also transmitted via the fork-like drive member of the intermediate member and the end protrusion on the hammer member.

The main difference between this tool and the tool described above is that the holder, which receives the hammer part, is provided with an enlarged rectangular hole. Further, the hammer member has a rectangular cross section in the longitudinal direction, and is mounted so as to be movable along the hole in the holder. In other words, the hole in the holder is
It acts as a guide means for moving the hammer member in a plane perpendicular to the axis of rotation.

The construction of such a tool is simpler69 and more reliable than the devices described above.

However, this structure also uses a large number of components to transfer the hammer part.

Moreover, the fork-like drive of the intermediate part also engages in a straight line with the end projection of the hammer part, which causes high contact stresses, resulting in premature wear of the tool or This may cause damage.

One end of the spindle in this arrangement is also supported via an intermediate member on the drive motor shaft in the same way as in the previously described device. This means that the nozzle member will not take on the dynamic load when applying an impact to the spindle, which will affect the reliability of the system.

The basic object of the invention is to provide a rotary impact tool in which the intermediate member is configured in such a way that it is ensured that the transition of the hammer member in a plane perpendicular to the axis of rotation is synchronized with its rotation. The objective is to improve reliability and simplify the structure of the tool compared to the prior art.

In view of this objective, the present invention includes a drive motor, the rotation of which is transmitted to a nozzle member through an intermediate member, the nozzle member surrounds a spindle, and the spindle is connected to an intermediate member. It is arranged coaxially with the member and has protrusions on its outer peripheral surface, and these protrusions correspond to the protrusions formed on the inner surface of the hammer member. In the rotary impact tool, the guide means is provided eccentrically with respect to the axis of rotation and is arranged directly on the intermediate member. A rotary impact tool is provided.

If the tool is constructed in this way, it is possible to improve its reliability. This is because the contact stress when the hammer member contacts and engages the intermediate member can be reduced.

According to one embodiment of the invention, the guide means are formed along parallel cathodes.

Configuring the guide means in this way makes its construction the simplest.

According to another embodiment of the invention, the guide means are formed along a curved surface with a common center of curvature.

By configuring the guide means in this way, by changing the radius of the curved surface, it is possible to change the mechanical trajectory of the hammer member when it moves within the outer surface perpendicular to the rotation axis. Become.

Preferably, the intermediate part is constructed as a disc.

Configuring the intermediate member in this way results in the simplest structure to expand.

In the case where the intermediate member is configured as a disk, it is preferable that the guide means is formed of two notches facing the outer surface of the disk, and that a slot is formed in the end face of the hashim member, and the slot is configured as described above. It is desirable to have a width that matches the distance between the notches.

The structure of such a guide means is the simplest in this embodiment of the intermediate member.

In the case where the intermediate member is configured as a tube disc, the guide means is configured as an end protrusion, which protrusion extends into a corresponding hole formed in the end face of the hammer member.
It is most desirable to do so.

By configuring the guide means in this way, it is possible to increase the reliability of the tool, reduce its dimensions and expand its field of application.

If the guide means are configured as end projections, it is advantageous to provide an alignment disk, which alignment disk is arranged concentrically with the main disk at the free end face of the hammer member;
It is desirable to have the same guide means on the main disk and to have the same configuration on both end faces of the hammer member.

With such a configuration, it is possible to improve the reliability of the tool. This is because the hammer member can be more accurately oriented with respect to the spindle projection.

In one embodiment, the intermediate part is configured as a holder surrounding the normal part, the guide means is configured as a through hole, and the intermediate part is designed as a through hole, and the intermediate part is designed as a holder that surrounds the normal part. Preferably, two cutouts are formed in the outer surface of one member, the distance between which corresponds to the width of the slot.

Such an embodiment of the tool makes it possible to increase its reliability. This is because the orientation of the hammer member is more accurate with respect to the axis of rotation and the dynamic loads on the shaft of the drive motor can be reduced.

Preferably, the intermediate member is mounted on spindle bearings supported at both ends in the case, and an element for mechanical coupling with the drive motor is provided on the outer surface of the intermediate member.

By configuring the tool in this way, its reliability can be improved. This is because it reduces the load on the motor so that in the event of a collision, a large portion of the load is transferred directly from the spindle, hammer member and intermediate member to the case. Furthermore, such an arrangement makes it possible to significantly reduce the dimensions of the tool. Such a construction also allows the tool to be constructed such that the shank is mounted at both ends of the spindle, one or the other in the same direction with respect to the rotation of the spindle, hammer member, and drive motor. The use of two shanks allows reversal of the rotation of the tool. In other words, it is possible to use a non-reversible motor, and its output and reliability are much higher than those of a reversible motor.

It is preferable that the element of the mechanical coupling with the drive motor is configured as a bevel gear ring that meshes with the fitted bevel gear of the drive motor, and that the axis of the bevel gear ring is arranged at right angles to the axis of the spindle. .

By configuring the tool in this way, it is possible to reduce the dimensions along the vertical range.

In some embodiments, it may be desirable to construct the element of the mechanical coupling as a pulley, which is connected via a belt to another pulley mounted on the motor axis parallel to the spindle axis.

By configuring the tool in this way, it is possible to reduce the power load acting on the drive motor.

In many embodiments, it is desirable to configure the element of the mechanical coupling as a spur gear meshing with the shaft of the drive motor, the axis of which is arranged parallel to the spindle axis.

Such an arrangement provides the most consistent and reliable transmission between the drive motor and the intermediate member.

In some embodiments, it may be desirable to have a centrally tapped hole in the spindle into which a screw having a longitudinal keyway is threaded to cooperate with a key secured to the case.

By configuring the tool in this way, it becomes possible to use the tool as a jack, turnbuckle, vise or other similar device.

Hereinafter, embodiments will be described in detail with reference to the accompanying drawings.

A nine-turn impact tool constructed according to the invention comprises a drive motor l (FIG. 1), the rotation of which is transmitted via an intermediate member to a hammer member 3 surrounding a spindle 4.

Its spindle 4 is arranged concentrically with the intermediate member 2 and has projections 5 formed on its outer surface 7 and corresponding to projections 8, 9 (FIGS. 3-6) formed on the inner working surface of the hammer member 3. 6 (Figure 2). The tool also includes a guide means 11 for moving the hammer member 3 in a plane perpendicular to the rotating shaft 12 (FIG. 2). The case 13 houses all the components of the tool described above.

The guide means 11 (FIG. 3) has a rotating shaft 12. (FIG. 2) and is arranged directly on the intermediate member 2 which transmits the rotation to the hammer member 3.

The intermediate member 2 is the shaft 14 of the drive motor l (Fig. 1).
and is coupled thereto, for example by means of a key 15. The spindle 4 is supported at its one end 16 in a bearing 17 of the case 13, and its other end 18 passes through a bearing 19 of the intermediate member 2. That is, its spindle is supported via an intermediate member on the drive motor (14). End 16 of spindle 4
A rounded shank 20 is formed which secures a KFi actuating member (not shown).

The simplest structure is to form the guide means 11 (FIG. 2) along parallel cords 21 and 22.

In another embodiment of the tool, the guide means 11 (FIG. 7) are designed as curved surfaces with a common center of curvature on the axis of symmetry 24 of the intermediate part 2.

FIG. 2 shows an embodiment of the tool in which the intermediate member 2 is formed as a disc 25. The disc 25 has a hub that fits into the shaft 14 of the drive motor I.

FIG. 7 shows an embodiment in which the guide means 11 are formed on the disk 25 as two cutouts 26, 27 on the outer surface 28 of the disk 25. FIG. In this case, the hammer part 3 is formed on the end face 29 and has nine slots 30, the slots having a width corresponding to the distance between the cutouts 26,27.

The notches 26, 27 on the disk 25 and the respective surfaces 31, 320 of the grooves 30 have a common center of curvature 2.
3, each having the same radius of curvature. The cutouts 26,27 in the disc 25 can also be formed by straight parallel cords (not shown) of a parallelogram.

In this case the slot 30 in the end face 29 of the hammer part 3 is also formed straight.

In many cases, it will be desirable to form the guide means 1 as end projections 33 (FIG. 2) extending into respective slots 34 formed in the end face 29 of the hammer member 3.

In this case, the side surface of the protrusion 33 is parallel to the cord 21
．． It is formed in a straight line along 22. The end protrusion may also be formed on the hammer member and a corresponding slot may be formed on the end face of the disk (not shown).

In both the aforementioned cases, the protrusion 33 and the slot 34
The side surfaces of can be formed by curved surfaces having a common center of curvature.

In the embodiment shown in FIG. 8, the tool is provided with an additional alignment disc 35, which
It is arranged on the free end face 36 of the hammer member 3 coaxially with the hammer member 5 .

...The end surface 37 of the alignment disk 35 is provided with a guide means 3B that is the same as the ten guide stages 11 of the disk 250. The end faces 29.36 of the hammer part 3 are also of identical construction. Hammer part 30mm 36Kti Hammer part 3
A slot 39 identical to the slot 34 of the end face 29 is provided. The slot 39 receives a guiding means wing configured as an end projection 40, and the slot 34 receives a guiding means 11 formed as a base projection 33.

In the embodiment of the tool shown in FIG. 9, the intermediate part 2 is formed as a holder 41 (FIG. 1 theta) surrounding the hammer part 3, the guide means being shown as a through slot 42, and the outer surface of the hammer part 3. 43 has two O notches 44.
45 are provided, and the distance between these notches is equal to the slot 4
Corresponds to 20 width.

In the embodiment of the tool shown in FIG.
is attached to the spindle 4, and the spindle 4 has bearings 17.47 whose both ends 16.46 are fitted into the case 13.
is supported by Each end 16.46 of the spindle 4 is provided with a shank 20.48 for carrying an actuating member, for example a wrench (not shown) for engaging a nut.

The outer surface of the intermediate member 2 is constituted by an element 49 of the mechanical coupling between the intermediate member 2 and the drive motor 1.

FIG. 11 shows an embodiment of the mechanical coupling element 49 in the form of a bevel gear 50, whose teeth are cut directly into the intermediate part 2, which is designed as a disk 25. FIG. The gear ring 50 is the drive motor l
It meshes with the bevel gear 51 which is fitted into the 7th gear (7) 14. Bevel gear 51 is held on shaft 14 by key 15. The axis 52 of the motor 1 is perpendicular to the axis 12 of the spindle 4. Axis 52 is also axis 12
Other angles (not shown) with respect to the angle can also be set.

FIG. 12 shows an embodiment of nine elements 49 formed as a pulley 53 which is connected by a belt 54 to a pulley 55 which is fitted onto the shaft 14 of the motor 1. FIG. The motor lO axis 52 is the axis 1 of the spindle 4.
It is parallel to 2.

51113 shows an embodiment of the element 49, which is designed as a spur gear ring 56, which meshes with a spur gear 57 which is fitted on the shaft 14 of the drive motor l, the shaft 52 of the drive motor l being connected to the shaft 14 of the spindle 4. parallel to axis 12;

In the embodiment shown in FIG. 11.12.13, the intermediate member 2
is formed as a disk 25.

However, in these embodiments the intermediate part can also be formed as a holder (not shown).

In other applications of the tool, for example when the tool is used as a jack, the spindle 4 (FIG. 13) is provided with a tapped hole 58, which is fitted with a screw thread 59 with a longitudinal keyway 60. The reception is accepted.

The keyway 60 receives a key 61 secured to the inner cover 62 of the case 13. The spindle 4 is supported by the case 13 by a sleeve bearing 63 and a thrust pair cylinder 64 fitted into a cap 65 of the case 13.

A rotary impact tool constructed according to the present invention operates as follows.

In operation, an actuating tool (not shown) is connected to the shank 20 of the spindle 4. Thereafter, the motor 1 is energized and the rotation from the shaft 14 is controlled by the guide means 11 (1
(Fig. 112), the force is transmitted to the hammer member 3 via the intermediate member 2. As the hammer member 3 rotates clockwise (FIG. 3), the protrusion 8 periodically (with each rotation) distributes an impact to the protrusion 5.

In that case, the mechanical energy stored by the normal part 3 in the course of its rotation is distributed to the spindle 4, which rotates through an angle, thereby imparting a motion to the actuating member and then stopping.

The hammer member 3 and the intermediate member 2 are stopped together with the spindle 4. However, the gauge member 3 receives torque from the drive motor l (FIG. 1) via the intermediate member 2. Under the influence of this torque and the spindle reaction force P (FIG. 3) transmitted to the normal hammer member 3 at the point where the projection 8 engages the projection 5, the hammer member 3 moves towards the guide means 11 of the intermediate member 2. The protrusion 8 begins to move in a plane perpendicular to the axis of rotation along the axis of rotation, and the protrusion 8 is released from the protrusion 5. This movement causes the protrusion 9 on the inner working surface 10 of the hammer member 3 to move towards the spindle 4.
This continues until it is forced against 0-side 7 (illustration 4). The hammer member 3 then begins to rotate as a single unit with the intermediate member 2, storing energy for the next impact force. The rotation continues until the inner surface lO of the hammer part 3 engages a projection on the outer surface of the spindle 4, while simultaneously with the rotation, due to the reaction force between the inner working surface lO of the hammer part 3 and the projection 5. The hammer part 3 moves along the guide means 11 and the projection 9 (FIG. 5) moves away from the surface 7 of the spindle 40 and the projection 8 approaches that surface 7. The hammer member 3 moves along the guide means 11 until the projection 8 is forced against the spindle 40 surface 7. This occurs at the same time that projection 9 engages projection 5. Thus, the normal member 3 (FIG. 6) and the intermediate member 2 are rotated again as a single unit, and their relative positions do not change. The protrusion 8 then distributes the impact force to the protrusion 5 and the cycle is repeated.

The protrusion 9 separates from the protrusion 6 (FIG. 3) before the impact occurs. This requires that the projection 8 is able to move along the hammer part 3 guide means 11 when released from the projection 5 after the impact. When the drive motor 1, the intermediate member 2 and the hammer member 3 rotate in opposite directions (counterclockwise direction 1), the impact force is distributed by the protrusion 9 of the hammer member 3 to the protrusion 6 of the spindle 4, but the impact force is distributed to the protrusion 6 of the spindle 4. Other aspects of the action are the same as described above.

In this way, the intermediate part 2 together with the guide means 11 completely provides the required mechanical trajectory (rotation and displacement in a plane perpendicular to the axis of rotation) of the hammer part 3 in the course of its interaction with the spindle 4. It is. This minimizes the number of component parts of the tool and simplifies its construction.

Furthermore, the guide means ll of the intermediate member 2 and the hammer member 3
always interact along the plane, which reduces the contact stress.

If the guide means 11 (FIG. 2) are formed along parallel cords 21 and 22, the guide means 11 (FIG. 2)
The movement of FIG. 1 is carried out along a straight line when the projection 8 is released from the projection 5.

This configuration of the guide means is the simplest.

When the guide means 111ET (Fig. move along. By configuring the guide means 11 in this way, by changing the radius of curvature, when the hammer moves in a plane perpendicular to the axis of rotation,
It becomes possible to change the mechanical trajectory of the part. This makes it easier to release the protrusion of the hammer member 3 from the protrusion 5 of the spindle 4.

If the intermediate member 2 (FIG. 2) is constructed as a disc 25, it will work exactly in accordance with the above-mentioned Kuseiho. Configuring the intermediate member 2 in this way is the simplest.

If the guide means 11 (FIG. 7) on the disk 25 are configured as two recesses 26.27, the hammer part 3 moves along the recesses 26.27. After the impact, the hammer member 3 moves along the notches 26 and 27. In that case, the hammer member 3 rotates around the center of curvature 23 and the projection 8 is released from the projection 5. Configuring the guide means 11 as two cutouts on the disc 25 is the simplest.

In the embodiment in which the guide means 11 is configured as an end projection 38 (FIG. 2) on the disk 25, when the projection 8 is released from the projection 5, the slot 34 formed in the end face 29 of the hammer part 3 is inserted into the projection. 33. The operation of the tool is otherwise identical to the embodiment described above.

This tool embodiment is the most compact 69 and allows for the smallest overall tool size.

Due to the fact that the disk 250 surface is free in such an embodiment, a new arrangement of the tool components is possible to reduce the dynamic loads on the drive motor shaft. If there is an alignment disk 35 (FIG. 8), during the operation of the tool the rotation of the hammer part 3 is transmitted to the alignment disk 35 via the slot 39 in the other end face 36 and via the projection 40 to each other. This causes the disk 25, hammer member 3, and alignment disk 35 to rotate simultaneously. When the hammer member 3 moves, the slot 34 is inserted into the protrusion 3 of the disk 25.
Slide along 3.

At the same time, it moves along the slot 39Fi protrusion 40.

Because the projections 33, 40 and the slots 34, 39 are identical, both end faces of the hammer part move synchronously throughout the entire course of tool action.

When the intermediate member 2 is constructed as a hole holder 41 (FIGS. 9 and 810) that surrounds the hammer member 3, the rotation of the drive motor l is formed in the hole holder 41 and is transmitted to the hammer member 3 through a through hole 42. transmitted to. When the hammer member 3 moves in a plane perpendicular to the axis of rotation, the notches 44, 45 slide against the slot 42Ka, so that after a collision, the protrusion of the hammer member 3 and the protrusion of the spindle are separated. It will be released. The cutouts 44 , 45 are formed along the entire length of the hammer part 3 so that the projection of the hammer part 3 can be positioned more precisely with respect to the projection of the spindle 4 .

In an embodiment of the tool in which the intermediate member 2 (FIG. 11) is attached to a spindle 4 whose ends 16.46 are supported in the case 13, after the drive motor l is excited its rotation is controlled by a mechanical coupling element. 49t- to the intermediate member 2.

At both ends 16.46 of the spindle 40 there is an actuating shank 20.
48, the rotation of which can be reversed by connecting one or the other shank to the tool.

In the event of an impact, the main part of the dynamic loads from the spindle 4, the hammer part 3 and the intermediate part 2 are transferred directly to the case 13, so that the dynamic loads acting on the motor are reduced. Moreover, such a tool O embodiment makes it possible to reduce the overall dimensions of the tool.

In an embodiment of the tool in which the mechanical coupling element 49 is configured as a bevel gear ring 50, the rotation of the drive motor I is transmitted to the intermediate part 2 via a bevel gear 51 and a bevel gear cylinder 50.

By configuring the tool in this way, it becomes possible to arrange the K-axis drive motor 1 at an arbitrary angle with respect to the axis of the spindle 4. This allows the dimensions of the tool along its vertical extent to be minimized.

In another embodiment of the tool with an element 49 consisting of a pulley 53 (FIG. 12) as the element 49 of the mechanical coupling with the drive motor l, the rotation from the drive motor l is coupled to the shaft 14 of the drive motor l. The installation is 9 pulleys 55,
It is transmitted to the intermediate member 2 via the belt 54 and pulley 53. In embodiments of such tools, it is possible to further reduce the dynamic loads on the drive motor, since the belt drive provides a damping effect.
The useful life of the tool is therefore extended.

In a further embodiment of the tool having an element 49 of mechanical coupling with the drive motor 1 configured as a spur gear ring 56 (FIG. 13), the rotation from the drive motor 1 is transmitted via the spur gear 57 and the gear ring 56. It is transmitted to the intermediate member 2. Element 4 of the mechanical coupling with the drive motor
9 such a structure is the simplest and most compact.

When a center tapped hole 58 is provided in the spindle 4 and a screw 59 (Fig. 13) is installed therein, the tool is attached to the lifting device (
The drive motor 1, the intermediate member 2, the hammer member 3 and the spindle 4 act as described above. After an impact is applied to the spindle 4, the spindle rotates through an angle and the screw 59 moves along the axis of the spindle 4. During the movement of the screw 59, the keyway 60 slides along the key 61. This key 61 is fixed to a cap 65 of the case 13 and is screwed 5
9 is held so as to rotate together with the spindle 4.

The movement of the screw 59 is reversed by reversing the drive motor 1.

Such an embodiment of a rotary impact tool makes it possible to transfer the tool driven thereby and to significantly expand its field of application.

In this way, something is provided which increases the useful life and durability of the tool, simplifies its construction, reduces its dimensions and expands its field of application.

The present invention is not limited to the embodiments described above, and it is of course possible to configure various aspects, embodiments, and modifications of the rotary impact tool without departing from the spirit and scope of the present invention.

[Brief explanation of the drawing]

Figure 1 is an overall view of the tool, partially shown in cross section, Figure 2 is an exploded perspective view showing the main parts of the tool, and Figure 3 shows the main components of the tool and their mutual arrangement at the moment of collision. 4 is a sectional view corresponding to FIG. 3 at the moment when the hammer member and the spindle protrusion are released; FIG. 5 is a sectional view corresponding to FIG. 3 after the spindle has rotated 1800 times; 6 is a sectional view corresponding to FIG. 3 before the collision; FIG. 7 is a perspective view of the main parts of the tool showing the interaction of the intermediate member, the hammer member and the spindle in one embodiment of the guide means; Figure 8 is a partial sectional view of a tool in an embodiment with alignment discs, Figure 9 is a partial sectional view of a tool in an embodiment in which the intermediate member is formed as a holder, and Figure 1θ is aX-X of Figure 9. FIG. 11 is a partial sectional view of an embodiment of the tool with a member of the mechanical coupling with the drive motor configured as a bevel gear on the outer surface of the intermediate member, and FIG. 12 shows the mechanical cup. FIG. 13 is a partial cross-sectional view of a tool in an embodiment in which the ring elements are composed of pulleys, and FIG. 13 is a partial cross-sectional view of a tool in an embodiment in which the mechanical coupling elements are composed of spur gears. l... Drive motor, 2... Intermediate member, 3... Hammer member, 4... Spindle, 5... Protrusion, 6...
・Protrusion, 7...Inner surface of hammer part, 7...Protrusion, 9
...Protrusion, 11...Guiding means, 13...Case,
16... One end of spindle, 21. 22... Parallel cord, 23... Center of curvature, 25... Disk, 26
．． 27... Notch, 29 Kawahafuma one part end i1m, 3
0...Slot, 33...Protrusion, 34...S Oy
), 35... Aligning disk, 36... Between ends of hammer member, 38... Guide means, 41... Holder, 42
... Through hole, 44.45 ... Notch, 46 ... Spindle other end, 49 ... Element of mechanical coupling,
50・°・Heheru af Yarin/, 51... Bevel gear, 53... Pulley, 54... Belt, 55... Pulley, group... Flat gear ring, 57... Spur gear, 58
...tag hole, 59...screw, 60...key path,
61...key. Continued from the first page in the margin below Priority claim @January 19, 1982 ■Soviet Union (SU)■
3371053 ■January 19, 1982■Soviet Union (SU)■337105
4 ■January 19, 1982■Soviet Union (SU)■337105
5 ■January 19, 1982■Soviet Union (SU)■337105
6 ■January 19, 1982■Soviet Union (SU)■337105
7 ■January 19, 1982■Soviet Union (SU)■337115
1 0 Inventor Valery Ivanovich Yutskepich Soviet Union Ningrad Prospekt Narodnogo Opolchenia 241 Korpus 2 Kwarchila 28 Applicant Anatoly Isakovich Rabinov Soviet Union Ningrad Novochelkassky Prospekt 68 Kwarchila 50 ■Applicant: Mikhail Ivanovich Sharyapin, Soviet Union, Ningrad Uritsutsa Stasovoy 2 Kwarchila 164 ■Applicant: Valery Ivanovich Yutskepich, Soviet Union, Leningranid Plos 1. , Pecto Narodnogo Oporchenia 241 Corpus 2 Kulchira Road

Claims (1)

[Claims] 1. A drive motor is provided, the rotation of which is transmitted to the hammer member through an intermediate member, the hammer member surrounds the spindle, and the shell spindle is disposed coaxially with the intermediate member. It has a central origin on its outer circumferential surface, these protrusions correspond to protrusions formed on the inner surface of the hammer member, and guide means are provided for moving the hammer member in a plane perpendicular to the axis of rotation. In the rotary impact tool, the guide means is eccentrically formed with respect to the rotating shaft, and the intermediate member (2) transmits the rotation to the hammer member (3). ) A rotating impact tool characterized in that it is directly disposed in the 2. The tool according to claim 1, wherein the guide means (11) is formed along parallel cords (2, 22). 3. The tool according to claim 1, wherein the guide means (11) are constituted by curved surfaces having a common center of curvature (23). 4. Tool according to claim 1, 2 or 3, wherein the intermediate member (2) is formed as a disk (25). 4 The guide means (11) are arranged on the outer surface of the disk (25).
A slot (30) is provided at the end 1j (29) of the hammer member (3), and the distance between the width cut arrow parts (26, 27) of the ζOX lot is A tool according to corresponding claim 4. 6. The guide means (11) is connected to the end face (
4. The tool according to claim 4, wherein the tool is formed as an end protrusion (33) formed in (29) and extending into a corresponding slot (34). An alignment disk (35) is formed on the free end surface (36) of the 7° hammer member (3) concentrically with the disk (25), and this alignment disk (35) is the same as the guide means (11). (31), and both end faces (29, 36) of the handle I-member (3) are also formed identically. & The intermediate part (2) is formed as a holder (41) surrounding the hammer part (3), the guide means (11)' being formed as a through hole (42), and furthermore the intermediate part (2) is formed as a holder (41) surrounding the hammer part (3);
) are provided with two notches (44, 45) on the outer surface of the slot, and the distance between these notches corresponds to the width of the slot) (42). Tools described in Paragraph 3 of the company. 9. The intermediate member (2) is formed on a spindle (4), which ends (16, 46) are connected to the case (1).
3), and on the outer surface of the intermediate member (2) there is a dynamic coupling element (1) connected to the drive motor (1).
49) is provided. The tool according to any one of claims 1 to 8. 10. The mechanical coupling element X (49) is formed as a bevel gear ring (50), and the ring (50)
is engaged with a bevel gear (51) fitted to the shaft of the drive motor (1), and its shaft is connected to the spindle (4).
10. The tool according to claim 9, wherein the tool is arranged at right angles to the axis of the tool. 11. The mechanical coupling element (49) is formed as a pulley (53), which is a pulley (54) fitted on the shaft of the belt (54)
55), and the shaft of the motor (1) is connected to the spindle (
9. The tool according to claim 9, which is parallel to the axis of 4). 12. The element (49) of the mechanical coupling is formed as a spur gear ring (56), the flat gear ring being a spur gear (57) fitted on the shaft of the drive motor (1).
10. Tool according to claim 9, in which the tool meshes with the spindle (4) and whose axis is parallel to the axis of the spindle (4). 13. The spindle (4) has a central tapped hole (58), and a screw (59) having a longitudinal keyway (6o) is inserted into the wrinkled tapped hole, and the keyway is inserted into the case (1).
3) The tool according to any one of claims 9 to 12, which cooperates with the K-fixed key (61).