EP2906375B1 - Vibrating hammer having rebound damping - Google Patents

Description

The invention relates to a vibrating hammer, comprising a cylinder, a percussion element movably mounted in relation to the cylinder with an external striking surface and a piston mounted displaceably in the cylinder, drivable with a pressurized fluid or electromechanically driven piston, the displacement of which extends to the percussion element. The hammer is received in a cavity which is arranged in a hammer holder coupled to the cylinder. In particular, the vibrating hammer can comprise a connection for a fluid as well as a channel which connects the connection to a displacement that is formed by the cylinder and a side of the piston facing away from the hammer.

In this context, the WO 1997/021523 A1 a pneumatically operated hammer for incorporation into a foundry sand removal device. The arrangement comprises a cylinder and a piston displaceably mounted therein. A pulsed air supply moves the piston back and forth and hits a movably mounted hammer.

Another vibrating hammer, known in principle from the prior art, is sold, for example, by the Olmer company. Such hammers are used, for example, to smash molds such as those used for metal casting. The vibrating hammer is placed with the striking face of the striking piece on the workpiece and the piston is then accelerated in the cylinder in the direction of the striking piece - usually with the help of compressed air. When the piston hits the hammer, the impulse is transmitted to the workpiece via the impact surface and thus leads to the casting mold being shattered.

Due to the high stress on the parts, an overhaul of the vibrating hammer is necessary after around 300 hours of operation, which is of course disadvantageous for efficiency in a production facility.

It is therefore an object of the invention to provide an improved vibrating hammer. In particular, the service life of the vibrating hammer or the time interval between two revisions should be extended.

The object of the invention is achieved with a vibrating hammer according to patent claim 1.

The proposed measures significantly reduce the repercussions on the cylinder, which means that the service life of the vibrating hammer or the time between two revisions is considerably increased. By providing a collar on the hammer, a radial overlap area is also formed between the hammer and the cylinder, in which the first damping element can be arranged in order to reduce axial impacts on the cylinder and its mounting. Because the first damping element surrounds the collar of the hammer or the projection of the hammer holder in cross section and has a first section facing the cylinder and a second section facing the striking surface, the hammer is virtually embedded in the first damping element, which means that not only axial Strikes / kickbacks but also radial components of the same are transmitted to the cylinder in a lighter manner. When tilting the vibrating hammer, the kickback does not occur exactly in the axis of the cylinder but leads to a twisting of the hammer and thus, in known systems, to severe wear of the bearing surfaces.

It should be noted that a “side of the hammer facing the piston” does not necessarily mean that surface of the hammer which the piston strikes. In the context of the invention, a “side of the hammer facing the piston” is to be understood quite generally to mean those surfaces of the hammer which are oriented towards the rear or which face away from the hammer.

Advantageous refinements and developments of the invention emerge from the dependent claims and from the description in conjunction with the figures.

It is advantageous if the said first damping element has a sleeve-shaped or tubular section arranged between the cylinder and the hammer. This means that the hammer does not need to be fitted exactly into the cylinder, or there is a significant reduction in the repercussions on the cylinder and the wear on the bearing surfaces, especially when the vibrating hammer is tilted.

It is beneficial if the first damping element projects beyond the outside diameter of the cylinder. In this way, play can be provided between the hammer holder and the cylinder, so that the hammer holder can be more easily mounted on the cylinder without the hammer holder having to have a complicated shape. This can, for example, simply have the shape of an inner cylinder in the area mentioned.

It is favorable if the first damping element has at least one rounded edge in the region of the collar of the hammer. As a result, the formation of cracks in a damping element can be effectively avoided or at least delayed.

It is also favorable if the collar of the hammer has at least one rounded edge. As a result, the formation of cracks in the hammer can be effectively avoided or at least delayed.

It is favorable if the first damping element has a third section arranged between the cylinder and the hammer holder. In this way, repercussions from the hammer holder on the cylinder can be avoided or at least mitigated.

It is also favorable if the vibrating hammer comprises a third damping element between the cylinder and the hammer holder. In this way, repercussions from the hammer holder on the cylinder can also be avoided or at least mitigated.

It is also favorable if the hammer holder is constructed in several parts, in particular in two parts. This allows the hammer holder to be easily mounted on the cylinder, or the hammer and damping elements in the hammer holder. In this context, it is beneficial if the axis of rotation of the cylinder lies in a partial plane of the hammer holder. In this way, the hammer holder can be mounted on the cylinder particularly easily. In addition, the blows are not directed over the sub-level. However, it would also be beneficial if a partial plane of the hammer holder is arranged normal to the axis of rotation of the cylinder. This allows the parts mentioned to be assembled even more easily.

It is advantageous if the vibrating hammer comprises a fourth damping element which is arranged on the hammer holder and which holds the parts of a multi-part hammer holder together. In this way, the hammer holder can be easily mounted on the cylinder.

It is favorable if the first and / or third and / or fourth damping element is / are made from an elastomer. For example, rubber or silicone rubber can be used for the damping element or the damping elements. It is advantageous if an elastomer with good sliding properties is selected because this reduces the friction between the cylinder and the hammer or a bushing arranged between them and the performance of the system can be improved.

It is advantageous if the third and / or fourth damping element is / are designed as an O-ring, since an O-ring is a readily available and proven means. In the context of the invention, the elastic and damping properties are used. The sealing function, on the other hand, plays no role or plays a subordinate role.

• das erste dämpfende Element mit dem Schlagstück und/oder dem Zylinder verklebt oder auf dieses/diesen aufvulkanisiert ist/sind beziehungsweise
• das dritte und/oder vierte dämpfende Element mit dem Schlagstückhalter und/oder dem Zylinder verklebt oder auf dieses/diesen aufvulkanisiert ist/sind.

It is beneficial if

• the first damping element is glued to the hammer and / or the cylinder or is / are vulcanized onto this / these
• the third and / or fourth damping element is glued to the hammer holder and / or the cylinder or is / are vulcanized onto this / these.

As a result, a shear force can also be transmitted well by a damping element and the kickback can be alleviated in this way.

It is also favorable if the piston and / or the hammer is / are made of metal. In this way, a long service life of the vibrating hammer is achieved.

It is advantageous if the piston and the hammer lie directly against one another when the piston is pushed towards the hammer. As a result, the impulse of the piston is transmitted particularly well to the hammer because the elastic component of the impact is particularly high here.

It is also particularly advantageous if a contact surface of the piston with the hammer is convex / concave and a contact surface of the hammer with the piston is concave / convex. As a result, the piston and the hammer still lie flat against one another during the impact even if the hammer is twisted or tilted in the cylinder. In particular, the surfaces mentioned can be designed spherically.

Finally, it is particularly advantageous if the cylinder is slidably mounted in a housing. In this way, the striking piece, which can usually only be moved slightly with respect to the cylinder, can be placed on the workpiece, even if the housing is permanently mounted. This means that the entire cylinder with piston and hammer can be telescoped out of the housing or retracted into it.

Fig. 1

einen Längsschnitt eines schematisch dargestellten Rüttelhammers;

Fig. 2

eine Detailansicht des in Fig. 1 dargestellten Rüttelhammers;

Fig. 3

einen Längsschnitt, eine Seitenansicht und eine Vorderansicht eines zweiten beispielhaften Rüttelhammers;

Fig. 4

den aus dem Gehäuse herausgezogenen und isoliert dargestellten Zylinder des Rüttelhammers aus Fig. 3;

Fig. 5

eine Detailansicht des in Fig. 3 dargestellten Rüttelhammers;

Fig. 6

wie Fig. 5, nur mit einem ersten dämpfenden Element, das einen zwischen Zylinder und Schlagstückhalter angeordneten Abschnitt aufweist;

Fig. 7

ähnlich wie Fig. 5, nur mit einer Nut im Schlagstück, in die ein Vorsprung des Schlagstückhalters eingreift (nicht Teil der Erfindung) und

Fig. 8

wie Fig. 7, nur mit einem ersten dämpfenden Element, das einen zwischen Zylinder und Schlagstückhalter angeordneten Abschnitt aufweist.

For a better understanding of the invention, it is explained in more detail with reference to the following figures. Show it

Fig. 1

a longitudinal section of a vibrating hammer shown schematically;

Fig. 2

a detailed view of the in Fig. 1 illustrated vibrating hammer;

Fig. 3

a longitudinal section, a side view and a front view of a second exemplary vibrating hammer;

Fig. 4

the cylinder of the vibrating hammer pulled out of the housing and shown in isolation Fig. 3 ;

Fig. 5

a detailed view of the in Fig. 3 illustrated vibrating hammer;

Fig. 6

how Fig. 5 , only with a first damping element which has a section arranged between the cylinder and the hammer holder;

Fig. 7

similar to Fig. 5 , only with a groove in the hammer into which a projection of the hammer holder engages (not part of the invention) and

Fig. 8

how Fig. 7 , only with a first damping element which has a section arranged between the cylinder and the hammer holder.

At the outset, it should be noted that the same parts are provided with the same reference symbols or the same component designations, it being possible for the disclosures contained in the entire description to be transferred accordingly to the same parts with the same reference symbols or the same component designations. The location details chosen in the description, such as above, below, laterally, etc. refer to the figure immediately described and shown and are to be transferred accordingly to the new position in the event of a change in position. Furthermore, individual features or combinations of features from the exemplary embodiment shown and described can also represent independent, inventive or inventive solutions.

• einen Zylinder 2 mit einer Zylinderachse 3,
• ein in Bezug auf den Zylinder 2 beweglich gelagertes Schlagstück 4 mit einer außen liegenden Schlagfläche 5,
• einen im Zylinder 2 verschiebbar gelagerten, mit einem druckbeaufschlagten Fluid oder elektromechanisch antreibbaren Kolben 6, dessen Verschiebeweg bis zum Schlagstück 4 reicht und
• einen mit dem Zylinder 2 gekoppelten Schlagstückhalter 7, welcher einen Hohlraum aufweist, der das Schlagstück 4 aufnimmt.

The Figures 1 and 2 show a first example, not according to the invention, of a vibrating hammer 100, with FIG Fig. 1 a longitudinal section of the vibrating hammer 100 and in the Fig. 2 an enlarged detail of the front region of the vibrating hammer 100 is shown. The vibrating hammer 100 includes:

• a cylinder 2 with a cylinder axis 3,
• a striking piece 4 which is movably mounted in relation to the cylinder 2 and has an external striking surface 5,
• a piston 6 displaceably mounted in the cylinder 2 and drivable with a pressurized fluid or electromechanically, the displacement path of which extends to the hammer 4 and
• a hammer holder 7 which is coupled to the cylinder 2 and has a cavity which receives the hammer 4.

In this example, the cylinder 2 is slidably mounted in an optional housing 8 which has a connection 9. The connection 9 is connected to the displacement 11 via the bore 10.

• einen im Bereich des Schlagstücks 4 vorgesehenen Innendurchmesser des Zylinders 2 quer zur Bewegungsrichtung des Schlagstücks 4 beziehungsweise quer zur Zylinderachse 3 überragt,
• eine dem Kolben 6 zugewandte Seite 15 und eine der Schlagfläche 5 zugewandte Seite 16 ausbildet und
• im Hohlraum des Schlagstückhalters 7 aufgenommen ist.

The hammer 4 is damped in both directions with regard to an axial movement along the axis 3 of the cylinder 2. For this purpose, the vibrating hammer 100 in this example comprises a first damping element 12 and a second damping element 13 (note: the second damping element 13 is not part of the scope of protection). In addition, the hammer 4 in this example has a collar 14 which

• projects beyond an inside diameter of the cylinder 2 provided in the area of the hammer 4 transversely to the direction of movement of the hammer 4 or transversely to the cylinder axis 3,
• a side 15 facing the piston 6 and a side 16 facing the striking face 5 and
• is received in the cavity of the hammer holder 7.

The first damping element 12 is arranged between the cylinder 2 and the side 15 of the hammer 4 facing the piston 6 and the second damping element 13 is arranged between the hammer holder 7 and a side 16 of the hammer 4 facing the striking surface 5. Specifically, the first damping element is formed by a bushing 12 arranged between cylinder 2 and hammer 4 and the second damping element is formed by a disk 13. The bush 12 has a tubular section 17 and also a collar 18 which is arranged between the cylinder 2 and a side 15 of the hammer 4 facing the piston 6.

The function of the Fig. 1 The vibrating hammer 100 shown is now as follows:
In a first step, the striking piece 4 is placed with its striking surface 5 on a workpiece (not shown). For this purpose, the cylinder 2 is correspondingly pushed out of or into the housing 8, which in this example is considered to be fixedly mounted. A longitudinal offset can therefore be compensated for by the displaceably mounted cylinder 2.

To execute an impact, a fluid (for example compressed air or pressurized oil) is passed through the connection 9, which enters the displacement 11 through a rear opening 10 in the cylinder and accelerates the piston 6 in the direction of the hammer 4. This then strikes the striking piece 4, which transmits the mechanical impulse to the workpiece via the striking surface 5 and there, for example, leads to the shattering of a cast core.

Striking with the aid of a pressurized fluid is an advantageous but by no means the only option. It is also conceivable, for example, that the impact is carried out with the aid of an electromechanical drive, for example with a linear motor. The core of an electromagnet can be thrown at the hammer 4 and thus execute the blow. Rotary motors can also be used. For example, the piston 6 can be driven by a connecting rod attached to a crankshaft and perform the impact.

For optimal transmission of the impact energy, the piston 6 and / or the impact piece 4 are made from metal (for example from hardened steel). Furthermore, the piston 6 and the striking piece 4 lie directly against one another when the piston 6 is pushed up to the striking piece 4, that is to say the impact occurs from metal to metal.

In the Fig. 1 the front part of the piston 6 is somewhat offset. This has the advantage, among other things, that if the piston 6 is upset on the striking surface, the piston 6 does not immediately get stuck in the cylinder 2, but this still has some radial air.

The second damping element 13 prevents the hammer 4 from striking the hammer holder 7 when it hits, for example if it does not hit properly the workpiece is in place. In this way, the vibrations transmitted to the cylinder 2 can be reduced.

After the impact, the impact piece 4 springs back from the workpiece - so a "kickback" occurs. The kickback to the cylinder 2 is dampened by the bushing 12. Specifically, the axial kickback is predominantly reduced by the collar 18, a radial kickback, as can occur, for example, when the vibrating hammer 100 is placed on the workpiece at an angle, primarily by the tubular part 17 of the bushing 12. This also reduces the wear on the cylinder 2 and the hammer 4 compared to known systems in which the hammer 4 is mounted directly in or on the cylinder 2 and the contact surfaces, which are usually metallic, wear.

In addition, the vibrations introduced into the vibrating hammer 100 and its anchoring are significantly reduced. This also increases the service life of the components of the vibrating hammer 100 not directly involved in the impact and of devices in the area of the anchoring of the vibrating hammer 100. For example, pneumatic or hydraulic valves and controls as well as electronic components are protected in this way.

In the Fig. 1 the surfaces of the hammer 4 and the piston 6, which touch each other during impact, are flat. In particular, if the bush 12 is relatively soft, the hammer 4 can easily tilt, so that the piston 6 and the hammer 4 no longer lie flat on one another during impact. In order to avoid damage to the surfaces mentioned, they can also be curved, in particular spherical. For example, the piston 6 can have a convex surface and the hammer can have a concave surface, or vice versa. In this way, the piston 6 and the striking piece 4 are still flat on one another when the striking piece 4 is tilted or twisted.

Instead of the one in the Fig. 1 The special bush 12 shown with collar 18, a bush without collar 18 can also be used. It should be noted in this regard that a collar 18 is not absolutely necessary for damping axial impacts, but that these can also be dampened by an end face facing the hammer 4. It is also possible to glue the bush 12 to the hammer 4 or the bush 12 to the hammer 4 vulcanize. In this case, the kickback can also be alleviated by the shear forces occurring in the bushing 12. A collar 14 on the hammer 4 can then also be omitted.

As an alternative or in addition to this, the first damping element can also be formed by a disk which is arranged between the cylinder 2 and the side 15 of the hammer 4 facing the piston 6.

At this point it should be noted that the vibrating hammer 100 is shown in a greatly simplified manner for better visualization of the invention and, for example, a return mechanism for the piston 6 is missing in the illustration (however, see FIG Fig. 3 ). This can for example be moved back to its original position with the help of a spring or by reversing the pressure medium, whereupon the front displacement is pressurized.

It should also be noted that the pressurization during the execution of the impact in the case of the Fig. 1 The vibrating hammer 100 shown leads to the fact that not only the piston 6 but also the cylinder 2 is pushed forward without further measures. This can be quite desirable in order to press the hammer 4 against the workpiece. However, it is also conceivable, for example, that the cylinder 2 is pressed out of the housing 8 with the aid of a spring in order to press the hammer 4 against the workpiece. However, a lock can also be provided, for example a clamping screw, in order to hold the cylinder 2 in a position that has once been set.

It is also noted that the cylinder 2 and the hammer holder 7 are designed as separate parts in the example shown, the piston 6 being mounted in the cylinder 2 and the hammer 4 in the hammer holder 7. Of course, this is only an exemplary embodiment. It is of course also conceivable that both the piston 6 and the hammer 4 are mounted in the cylinder 2 and this is made in one piece or, for example, is divided longitudinally. It is of course also conceivable that the vibrating hammer 100 has more parts than shown, or is divided at a different point.

The Figures 3 and 5 now show a second example of a vibrating hammer 101, with FIG Fig. 3 a longitudinal section of the vibrating hammer 101, and a side view and a front view and in the Fig. 5 an enlarged detail of the front area of the vibrating hammer 101 is shown. The Fig. 4 shows the part of the vibrating hammer 101 removed from the housing 8 also shown in isolation.

The vibrating hammer 101 has a very similar structure to that in the Figures 1 and 2 shown vibrating hammer 100. In contrast to this, a return spring 19 for and a holding device 20 for the vibrating hammer 101 is now specifically shown.

Furthermore, both the hammer 4 and the hammer holder 7 are damped in both directions with regard to an axial movement along the cylinder axis 3. For this purpose, the vibrating hammer 101 comprises a first damping element 21, which surrounds the collar 14 of the hammer 4 in cross section and has a first section 22 facing the cylinder 2 and a second section 23 facing the striking face 5. The first damping element 21 is constructed in one piece in this example, but this is not absolutely essential. In addition, the first damping element 21 has rounded edges 24 and 25 in the region of the collar 14. In this example, the collar 14 also has correspondingly rounded edges. In this example, the first damping element 21 also projects beyond the outer diameter of the cylinder 2, but this is not mandatory.

In this example, the vibrating hammer 101 further comprises a third damping element 26 between the cylinder 2 and the hammer holder 7, which is specifically designed as an O-ring, which is advantageous but not mandatory. The hammer holder 7 is axially secured to the cylinder 2 by this O-ring 26, and repercussions on the cylinder 2 are dampened. The O-ring 26 connects the cylinder 2 and the hammer holder 7 in particular in a form-fitting manner, in particular in the axial direction. The O-ring 26 is in particular also subjected to shear stress, unlike the first damping element 21, which is mainly subjected to pressure.

The hammer holder 7 is constructed in several parts (in particular in two parts), the axis of rotation 3 of the cylinder 2 in the case of the Figs. 3 to 5 The example shown lies in a partial plane 27 of the hammer holder 7. For example, the partial plane of the hammer holder 7 could also be normal to the axis of rotation 3 of the cylinder 2.

The vibrating hammer 101 finally also has fourth elastic and damping elements 28 arranged on the hammer holder 7, which hold the parts of the multi-part hammer holder 7 together and which in turn are specifically designed as an O-ring. Instead of the O-rings 28, (open) metal rings or clasps can be provided for holding the parts of the multi-part hammer holder 7 together. The assembly of the hammer holder 7 on the cylinder 2 is simple in both cases. For this purpose, the rings / clasps are simply pushed onto the hammer holder 7. The use of screws, for example, would of course also be conceivable to hold the parts of the hammer holder 7 together or to mount it on the cylinder.

Fig. 6 now shows a detail of a vibrating hammer 102, which is in the Figures 3 to 5 shown vibrating hammer 101 is very similar. In contrast to this, however, the first damping element 21 has a third section 29 which is arranged between the cylinder 2 and the hammer holder 7 and which is provided instead of the O-ring 26.

Fig. 7 also shows a detail of a vibrating hammer 103 not according to the invention, which is also the one in the Figures 3 to 5 The vibrating hammer 101 shown is similar. In the case of the vibrating hammer 103, however, the striking piece 4 has a groove 30 which forms a side 15 facing the piston 6 and a side 16 facing the striking surface 5 and in which a projection 31 of the striking piece holder 7 engages. The first damping element 21 encloses the projection 31 of the hammer holder 7 in cross section and has a first section 22 facing the cylinder 2 and a second section 23 facing the striking surface 5. In addition, the first damping element 21 has rounded edges in the region of the groove 30. In this example, the groove 30 also has correspondingly rounded edges.

In the example shown, the projection 31 protrudes relatively far from the main body of the hammer holder 7, which also results in a certain spring effect, which also mitigates the repercussions on the cylinder 2. Of course, the projection 31 can also protrude less than shown, whereby the durability of the hammer holder 7 is improved. For this purpose, the inner diameter in the area of the first damping element 21 can be compared to the illustration in FIG Fig. 7 be reduced. The hammer holder 7 then has a shoulder.

Fig. 8 now shows a detail of a vibrating hammer 104, which corresponds to the in Fig. 7 shown vibrating hammer 103 is very similar. In contrast to this, the first damping element 21 has a third section 29 which is arranged between the cylinder 2 and the hammer holder 7 and which is provided instead of the O-ring 26.

In general, this applies to the vibrating hammer 100 of the Figures 1 and 2 disclosed teaching analogously for those in the Figures 3 to 8 shown vibrating hammers 101..104. In particular, it can also be used in the Figures 3 to 8 Shaking hammers 101..104 shown the first and / or third and / or fourth damping element 21, 26, 28 can be made of an elastomer. The first damping element 21 can be glued to the hammer 4 and / or the cylinder 2 or can be vulcanized onto this / them. Accordingly, the third and / or fourth damping element 26, 28 can also be glued to the hammer holder 7 and / or the cylinder 2 or be vulcanized onto this / these. The piston 6 and / or the hammer 4 are advantageously made of metal, and the piston 6 and the hammer 4 lie directly against one another when the piston 6 is pushed against the hammer 4. A contact surface of the piston 6 with the hammer 4 and a contact surface of the hammer 4 with the piston 6 can in turn be concave / convex.

It is also conceivable that the vibrating hammers 101..104 comprise a first damping element 21, which has a sleeve-shaped or tubular section arranged between the cylinder 2 and the hammer 4, analogous to that in FIG Figures 1 to 2 tubular section 17 of the first damping element 12 shown.

The element engaging in the groove 30 can also be formed by an elastic disk, for example by a two-part disk made of an elastomer. The impact and / or the kickback can also be dampened by this disk. What has already been said is therefore also to be applied accordingly to this embodiment. Accordingly, the bush 12 can also have an inwardly projecting collar 18 which engages in the groove 30 of the hammer 4. For better assembly, said bushing 12 can also be divided into two parts. Of course, this teaching can also be used in connection with the vibrating hammer 100 of Figures 1 and 2 can be applied

The exemplary embodiments show a possible variant of a vibrating hammer according to the invention 100..104, it being noted at this point that the invention is not restricted to the variant of the same specifically shown.

In particular, it is stated that the arrangement shown can in reality also include more or fewer components than those shown.

The task on which the independent inventive solutions are based can be found in the description.

List of reference symbols

100..104

Vibrating hammer

2

cylinder

3

Cylinder axis

4th

Impact piece

5

Clubface

6th

piston

7th

Striker holder

8th

casing

9

connection

10

drilling

11

Displacement

12

first damping element (socket)

13

second damping element

14th

Collar (on hammer)

15th

the side of the collar facing the piston

16

side of the collar facing the clubface

17th

tubular section

18th

Collar (on socket)

19th

Return spring

20th

Holding device

21st

first damping element

22nd

first section

23

second part

24

rounded edge

25th

rounded edge

26th

third damping element (O-ring)

27

Partial plane of the hammer holder

28

fourth damping element

29

third section of the first damping element

30th

Groove

31

head Start

Claims (9)

1. A vibrating hammer (100.. 104), comprising:

   - a cylinder (2) with a cylinder axis (3),

   - a striker (4), movably mounted relative to the cylinder (2), with a flange (14) which protrudes beyond an inner diameter of the cylinder (2) provided in the region of the striker (4) transversely to the direction of movement of the striker (4), and with a striking surface (5) arranged on the outside, wherein the striker (4) is damped in both directions along the cylinder axis (3) with regard to an axial movement,

   - a piston (6), displacably mounted in the cylinder (2), which can be driven by a pressurized fluid or electromechanically, whose displacement extends to the striker (4), wherein the flange (14) of the striker (4) forms a side (15) facing the piston (6) and a side (16) facing the striking surface (5), and

   - a striker holder (7) coupled with the cylinder (2), which has a cavity accommodating the striker (4) and its flange (14),
   characterized by

   - a first damping element (21), in particular formed in a single piece, which encloses the flange (14) of the striker (4) in the cross section, and which has a first section (22) facing the cylinder (2) and a second section (23) facing the striking surface (5).
2. The vibrating hammer (100..104) according to claim 1, characterized in that the first damping element (12, 21) has a third section (29) arranged between the cylinder (2) and the striker holder (7).
3. The vibrating hammer (100..104) according to claim 1, characterized by a third damping element (26) between the cylinder (2) and the striker holder (7).
4. The vibrating hammer (100.. 104) according to one of claims 1 to 3, characterized in that the striker holder (7) is formed in multiple pieces, in particular in two pieces, and a partial plane of the striker holder (7) is arranged perpendicular to the axis of rotation (3) of the cylinder (2).
5. The vibrating hammer (100.. 104) according to one of claims 1 to 4, characterized by a fourth damping element (28) arranged on the striker holder (7), which element (28) holds the parts of a multi-piece striker holder (7) together.
6. The vibrating hammer (100.. 104) according to one of claims 1 to 5, characterized in that the first and/or third and/or fourth damping element (12, 13, 21, 26, 28) is made from an elastomer.
7. The vibrating hammer (100.. 104) according to one of claims 3 to 6, characterized in that the third and/or fourth damping element (26, 28) is formed as an O-ring.
8. The vibrating hammer (100.. 104) according to one of claims 1 to 7, characterized in that

   - the first damping element (12, 13, 21) is glued to the striker (4) and/or the cylinder (2) or is vulcanized onto either or both of them and/or

   - the third and/or fourth damping element (26, 28) is/are glued to the striker holder (7) and/or the cylinder (2) or vulcanized onto either or both of them.
9. The vibrating hammer (100.. 104) according to one of claims 1 to 8, characterized in that a contact surface of the piston (6) with the striker (4) is formed to be convex/concave and a contact surface of the striker (4) with the piston (6) is formed to be concave/convex.

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