DE102020129424A1 - percussion cylinder - Google Patents

Abstract

The invention relates to an impact cylinder with a cylindrical piston jacket 2, which encloses an inner piston chamber 4 circumferentially, a piston 14 which is arranged in the piston chamber 4 and can be moved longitudinally between a front impact position and a rear rest position, an anvil 40 which is movably received in a front impact cylinder plate, a between the anvil 40 and the piston 14 arranged compression spring 24, a compressed air reservoir 16, a connection 10 for supplying a fluid and with a control membrane 32 for selectively filling the compressed air reservoir 16 and actuating the piston 14.To simplify the structure, the invention proposes a sealing Flange 18 is provided at a rear end of the piston skirt 2, that the compressed air reservoir 16 is arranged behind the flange 18 and that a supply pipe 28 is provided at a flange opening of the flange, which extends from the flange opening to a rear end of the compressed air reservoir chers 16 extends.

Description

The invention relates to an impact cylinder for cleaning furnaces or heat exchangers, in particular for removing deposits on the built-in components.

Such a striking cylinder comprises a cylindrical piston skirt which encloses an inner piston chamber circumferentially, is closed at a front end by a front plate or by a front striking cylinder plate and at a rear end by a cylinder cover or by a rear striking cylinder plate.

A piston is arranged in the stationary piston chamber so that it can move relative to it and can be moved longitudinally along a longitudinal axis between a front impact position and a rear rest position. The piston divides the piston chamber into a front chamber facing the front impact cylinder plate and a rear chamber facing the rear impact cylinder plate.

A fluid, preferably compressed air, can be fed to a compressed air reservoir via a connection. An elastic control membrane, which forms a valve, controls whether the compressed air reservoir is filled with compressed air or the piston is actuated, i.e. an impact is performed, depending on the compressed air applied via the connection.

In the front percussion cylinder plate, an anvil, a percussion rod or the like is accommodated in a relatively movable manner, on which the piston impacts when the percussion is triggered in the percussion position. After the impact, a compression spring compressed by the impact and extending between the front impact cylinder plate and a face of the piston in the front chamber moves the piston back to the rear rest position.

State of the art

Such a percussion cylinder is, for example, from the patent DE 10 2009 051 089 B4 known to the applicant's predecessor company.

The percussion cylinder includes an inner, cylindrical inner piston jacket, which encloses an inner piston chamber in which a piston is movably mounted along a longitudinal axis between a forward percussion position and a retracted rest position. The inner piston skirt is bordered or surrounded by a coaxially arranged, cylindrical outer piston skirt, so that an annular space is formed between the inner piston skirt and the outer piston skirt, which acts as a ring accumulator. The compressed air flows through a connection past a flexible control membrane, which closes access to the piston chamber, past the surrounding ring accumulator.

The purpose of the compressed air reservoir is to receive and collect the fluid, preferably compressed air, initially flowing in via the connection and then, after the release of an impact through the closure valve with the control membrane, to allow it to flow directly into the rear chamber of the piston chamber in order to thus compress the piston spring against the anvil in the front impact cylinder plate so that the impact is released on impact. Then the piston is moved via the compression spring back into the rear end of the piston chamber up to the rear rest position. The process then begins again and the compressed air reservoir is again filled with fluid, preferably compressed air.

When a blow is released, the air escapes at the connection. The pressure conditions change in such a way that the control membrane deforms and releases access to the rear chamber of the piston chamber. At the same time, the control diaphragm of the compressed air located in the compressed air reservoir designed as a ring accumulator blocks the outlet via the connection. The deformation of the control membrane simultaneously opens the way to a rear chamber of the piston chamber. When triggered, the compressed air from the compressed air reservoir escapes abruptly into the rear chamber of the piston chamber and drives the piston forward against a compression spring which is clamped between the front end of the piston and a firing pin at the front end of the percussion cylinder.

Such an impact cylinder is used, for example, to remove flue gas residues in flue gas cleaning systems, for which purpose the impact cylinder is arranged on the outside of a flue gas duct and the impact cylinder hits the outside of the flue gas duct with its impact rod or its anvil in order to detach deposits from the inside that are Significantly reduce the efficiency of systems.

Disadvantages of the prior art

The design described requires the inner casing and the outer casing enclosing it in order to produce the annular space.

Since the two jackets have different diameters, the structure is relatively complex. In this respect, the known design requires two large pipes, namely an inner jacket and an outer jacket, which of course must have different diameters.

Known impact cylinders require relatively large compressed air reservoirs of about 3 liters, which requires a relatively large amount of air, which is expensive to manufacture. Long screw bolts are usually used to hold the front and rear impact cylinder plates together against the air pressure within the air pressure ring accumulator surrounding the piston chamber. However, since the ring accumulator thus extends over the entire length of the piston chamber, i.e. encloses the cylinder chamber on all sides, a relatively large area around the inner piston chamber is necessary for the ring accumulator, which requires a relatively large lateral distance or gap between two adjacent impact cylinders and why the Storage volume is also very large.

However, since a large amount of compressed air requires a long compressor duty cycle and filling time, a large compressed air reservoir is not very energy efficient. In practice, therefore, displacement bodies are sometimes used to reduce the volume in the compressed air reservoir.

However, a large storage volume always requires a large amount of air, which is expensive and time-consuming to provide. Furthermore, the design known from the prior art requires a total of four seals, which must always be checked for correct functionality and are generally prone to errors.

In the state of the art, impact cylinders with external compressed air reservoirs and interposed shut-off valves are sometimes also used, but their construction is therefore relatively complex and therefore also difficult to assemble. If hundreds of impact cylinders are installed in a system, which is not unusual, the effort is disproportionately high. Due to the longer distances that the fluid from the compressed air reservoir has to cover when the impact is triggered, they consistently have a lower performance.

task

Proceeding from the state of the art mentioned at the outset, the object of the invention is to at least partially avoid the disadvantages described and in particular to provide a percussion cylinder of simple design and particularly efficient operation.

invention

This object is already solved by the independent claims. Preferred but not mandatory features are set out in the dependent claims.

In the most abstract embodiment, this is done by arranging a preferably sealing flange, which forms a partition between the piston chamber and the compressed air chamber, at a rear end of the piston skirt, by arranging the compressed air reservoir behind the flange, and by arranging a feed pipe inside a flange opening of the flange is extending from the flange opening to a rear end of the air reservoir.

The invention already solves the problem in that a sealing flange is arranged between a piston jacket enclosing the piston chamber and a compressed air reservoir jacket enclosing the compressed air reservoir, which therefore separates the piston chamber from the compressed air reservoir, so that the compressed air reservoir extends directly behind this flange, so to speak in Continuation of the piston chamber to the rear. Within the flange, a flange opening penetrating the flange is preferably provided in the center, in which a feed pipe is arranged or seated, which therefore extends from this flange opening to a rear end of the compressed air reservoir. The feed pipe thus has approximately the length of the compressed air reservoir in the longitudinal direction.

When the compressed air reservoir is being filled, the compressed air flows in through the connection and presses the control membrane forwards against the feed tube and, after the rear end of the feed tube has been closed, is then pressed at the outer peripheral edge between the control membrane and the rear percussion cylinder plate or the cylinder cover into the compressed air reservoir located directly behind it . The feed tube thus acts as a contact surface for the elastic control membrane when pressure is applied, ie it supports the control membrane when the compressed air reservoir is being filled.

To trigger an impact, the connection is depressurized, which is done in the simplest case by opening a valve. The rear side of the control membrane now rests against a bulging inner surface of the rear impact cylinder plate/cylinder cover and thus suddenly opens up access through the feed tube, so that the compressed air can flow through the feed tube into the piston chamber and trigger the impact by driving the piston forward.

According to the invention, the compressed air reservoir is therefore no longer arranged circumferentially around the piston skirt, but rather along the longitudinal axis of the percussion cylinder immediately behind the piston chamber, specifically separated by the sealing Flange that seals the piston chamber at the rear end.

In the case of the invention, the compressed air is no longer stored in a ring accumulator or external compressed air accumulator as in the prior art, but in the immediate vicinity of the control membrane. This shortening of the paths for the fluid, in particular the compressed air, enables the percussion cylinder to be made smaller and lighter with the same performance. Or to put it another way: the impact cylinder is more powerful than in the prior art while maintaining the same size.

The volume within the compressed air reservoir can be easily influenced and changed by appropriately designing the diameter of the feed pipe. At the same time, however, a larger supply pipe also ensures that the fluid, preferably compressed air, flows more quickly from the compressed air reservoir into the rear chamber when the impact is triggered.

The impact energy to be achieved by the impact cylinder depends on the time in which the air can flow from the compressed air reservoir into the rear chamber of the piston chamber. If the air takes too long, the piston has already arrived at the front ram at low speed and the slow compressed air then only flows in because the paths for the compressed air are relatively long in the prior art. In the state of the art, hoses are sometimes required for connection to external compressed air reservoirs, and the same problem can arise.

The free cross-section for air to flow through hoses and valves is often too small.

The feed pipe, which extends backwards from the flange opening, realizes the shortest path for the compressed air with large free cross-sections. Since the diameter of the feed tube can be 30 to 50 percent, in particular 33 percent, of the diameter of the compressed air reservoir, the fluid or air can flow much faster into the rear chamber of the piston chamber when the impact is triggered, so that the piston can reach the required target speed within a shorter time is accelerated. Therefore, compared to the prior art, the front chamber can be shortened by up to 10 percent with the same performance, which in turn shortens the entire percussion cylinder and makes it lighter.

According to the invention, the piston can thus be accelerated to a predetermined speed in a shorter time with compressed air content, which shortens the front chamber and thus shortens the structure and makes it lighter.

All of the measures together result in a significant weight reduction of up to 60 percent and a shortening of the design by up to 10 percent.

The compressed air reservoir in the invention is therefore significantly smaller compared to the prior art, preferably 80 to 90 percent smaller. Since multiple beats are to be made in the shortest possible time, a smaller memory ensures shorter filling times, which enables smaller beat intervals.

Since the compressed air reservoir is significantly smaller, no displacement bodies have to be used to artificially reduce the volume.

Since the volume of the pressure accumulator is significantly smaller, the energy efficiency is significantly better than in the prior art.

In contrast to the prior art, displacement bodies and their attachments in the ring storage device are no longer required for this artificial size reduction, which leads to a significant reduction in weight.

This omission of the outer jacket for the outer ring memory in the prior art means a significant saving in material and thus weight.

In the prior art, the outer jacket had to be made of stainless steel because of the necessary strength.

In the percussion cylinder according to the invention, the piston jacket and the compressed air reservoir jacket, i.e. the jacket surrounding the compressed air reservoir, can be made from identical material, particularly preferably from a light aluminum tube with the same diameter and the same wall thickness, particularly preferably with an outside diameter of 105 mm and a wall thickness of 2 4 mm for all power ranges. The performance is varied by changing the length of the compressed air reservoir. This is much easier than changing other components.

Due to the configuration according to the invention, the weight of a percussion cylinder can be reduced by up to 60 percent with the same performance. A typical percussion cylinder no longer weighs 25 kilos as it used to, but now only 15 kilos. This makes a significant difference when transporting and assembling the percussion cylinder, because sometimes 500 such cylinders have to be mounted on the outside of a boiler.

The front striking cylinder plate and rear striking cylinder plate, sometimes simply "Flan called "sche" that are held together with the screw bolts can therefore have a smaller diameter, which in turn results in a reduction in weight.

Because of the smaller outer diameter, the impact cylinders according to the invention can thus be mounted in series with very small distances from one another on boiler walls. The smaller diameter also improves accessibility. If the percussion cylinders are used in series, hundreds of these cylinders can be installed.

A particular advantage of the invention can be seen in the fact that instead of four seals as before, only two seals are now required for the axial sealing of the compressed air reservoir at the front end facing the piston chamber and at the rear end facing the valve. This simplifies the assembly and testing time and reduces the susceptibility to errors.

Since pressure is only built up in the compressed air reservoir, the actual piston chamber of the impact cylinder no longer has to be sealed. A further advantage of the design according to the invention is that there are no seals between the front impact cylinder plate and the piston skirt and at the rear end between the piston skirt and the rear impact cylinder plate.

In the case of the invention, only the compressed air reservoir has to be sealed, because compressed air only has to be stored in this area for a certain period of time during filling. In the simplest and particularly preferred embodiment, the compressed air reservoir is sealed at the front by a sealing lip projecting radially outwards on the outer peripheral edge of the flange and at a rear end by a sealing ring or the like inserted on the cylinder cover.

Even higher pressing forces and thus higher impact forces, and thus higher performance, can be achieved by providing a fluid-permeable membrane support at a rear end of the feed tube. This diaphragm support increases the contact surface for the control diaphragm and prevents the elastic diaphragm from being pushed or pulled into the rear opening of the feed pipe even better when the compressed air reservoir is being filled. The membrane support thus functions as a further contact surface for the elastic control membrane when pressure is applied. However, the membrane support is designed in such a way that it enables the fluid to flow through easily, for which purpose it is designed in the manner of a lattice or sieve.

The area of the openings in the membrane support is particularly preferably 80 to 90 percent of the total area of the membrane support. Thus, when the control membrane is opened to trigger an impact, the fluid can suddenly flow through this fluid-permeable membrane support into the rear end of the feed tube and flow through the feed tube and the flange into the piston chamber to trigger the impact.

The control membrane is preferably seated in a membrane seat of the rear percussion cylinder plate/of the cylinder cover, which is preferably designed as a depression or a shoulder adapted to the size of the control membrane. When filling the compressed air reservoir, the compressed air flows past radially on the outside between the inner edge of the diaphragm seat and the outer edge of the control diaphragm inserted therein.

A rear pressure chamber is preferably formed in the rear percussion cylinder plate by forming a recess or curvature adjoining the membrane seat to the rear, which pressure chamber can be closed by the control membrane seated in the membrane seat.

The membrane support is preferably designed in the manner of a sieve, that is to say with a plurality of holes. So that the fluid can flow particularly well through the membrane support, the size of the passages or holes is significantly larger than the closed area of the membrane support, the holes particularly preferably make up about 90 percent of the total area of the membrane support.

In order to achieve a good hold and clean contact between the control membrane and the membrane support when the compressed air reservoir is being filled, the membrane support is placed on a collar at the rear end of the feed tube, in particular a collar that protrudes radially outwards in a ring shape and on which the outer tipping surface of the membrane support rests or is inserted is.

Particularly good seals between the control membrane and the feed tube are achieved when the feed tube has a sealing lip for bearing against a membrane front side of the control membrane. This sealing lip is preferably formed circumferentially around the collar and extends further backwards in the longitudinal direction, so that the sealing lip protrudes over the surface of the membrane support or the collar and the control membrane can act together with the sealing lip in a sealing manner.

In a particularly preferred embodiment, the sealing lip can be made of an elastic material, which improves the Tightness between the control membrane and sealing lip realized. When the supply tube is made of plastic, it can be produced using a 2-component plastic injection molding process.

A particular advantage lies in the fact that the piston jacket, which encloses the circumference of the piston chamber, and the compressed air jacket, which encloses the circumference of the compressed air reservoir, can be made of the same material and is preferably made of the same material. The preferred material is aluminum for weight reasons.

Furthermore, the two lateral surfaces, which are preferably designed as pipe sections of different lengths, namely a longer pipe section for the piston chamber and a shorter pipe section for the compressed air reservoir, have the identical diameter and identical wall thickness. A wall thickness of 2.5 mm, for example, is sufficient.

In practice, several such percussion cylinders are usually arranged on the outside of a wall, e.g. the wall of a combustion chamber, with the percussion cylinder then hitting a relatively movable rod mounted in the wall in the axial direction with its anvil or the percussion rod, which in turn pushes against a plate, a block, on the front side or the like in the collector of a furnace.

In another embodiment, multiple impact cylinders may be mounted on a carriage that is movable to various locations relative to the stationary wall.

• 1 einen Längsschnitt einer ersten Ausführungsform des erfindungsgemäßen Schlagzylinders mit Schlagstange beim Befüllen des Speichers mit einem Arbeitsfluid in Ausgangstellung;
• 2 den Schlagzylinder gemäß 1 bei gefülltem Speicher;
• 3 den Schlagzylinder gemäß 1 in Schlagstellung; und
• 4 einen isometrischen Längsschnitt einer zweiten Ausführungsform eines Schlagzylinders mit Amboss in der Ausgangsstellung.

Further details, advantages and features of the invention can be found in the following part of the description, in which a preferred exemplary embodiment of the percussion cylinder according to the invention is explained in more detail. All features shown here are disclosed individually and independently of the specific combination in the embodiment. Show it:

• 1 a longitudinal section of a first embodiment of the percussion cylinder according to the invention with percussion rod when filling the memory with a working fluid in the starting position;
• 2 according to the impact cylinder 1 when the storage tank is full;
• 3 according to the impact cylinder 1 in striking position; and
• 4 an isometric longitudinal section of a second embodiment of a percussion cylinder with anvil in the starting position.

Accordingly, the proposed percussion cylinder consists essentially of a cylindrical piston jacket 2 surrounding a longitudinal axis, which surrounds a piston chamber 4 and is closed at its front end by a front percussion cylinder plate 6 and at its rear end by a flange 18, behind which is then a compressed air storage jacket 22 is arranged, which is then closed at the rear by a rear percussion cylinder plate 8. A fluid, preferably compressed air, can be supplied to the percussion cylinder via a compressed air connection 10 .

In the front percussion cylinder plate 6, sometimes also referred to as the bottom, a percussion rod 26 is guided in a longitudinally displaceable manner by means of one or more slide bearings, the rear end of which is attached to a piston 14 and the front end protruding from the front percussion cylinder plate 6.

A front sleeve 30 encloses at a radial distance a through opening for the impact rod 26 in the front impact cylinder plate 6 to form an annular space. In this annular space between the wall sleeve 30 and the passage opening sits a compression spring 24 which extends between the wall sleeve 30 and a piston 14 and the percussion rod 26 encloses.

This piston 14 is guided in a longitudinally displaceable manner within the piston chamber 4 via sliding bearings and can also be sealed against the piston jacket 2 in a sealing manner via a sealing ring arranged in an outer peripheral groove of the piston 14 .

In the alternative embodiment according to 4 Instead of the percussion rod 26, an anvil 40 is arranged in the front plate 6 so that it can be displaced longitudinally, on which the piston 14 strikes when the percussion is triggered. According to the isometric section in 4 For example, the piston 14 can have a bore in the center of its front side, in which a mandrel 38 is accommodated, for example welded, pressed or glued. The mandrel 38 with a small cross-section than the bore is used to fix the compression spring 24, which is located between the piston 14 and a radial
protruding collar 41 extends to the inner end of the anvil 40 directed towards the piston chamber 4 and which serves as a return spring for the piston 14 . In this embodiment, the compression spring 24 thus extends between the mandrel 38 in the front side of the piston 14 and a radially projecting collar 40a on the anvil 40, which is accommodated in a longitudinally displaceable manner in a through opening in the front percussion cylinder plate 6.

The piston 14 divides the piston chamber 4, depending on the relative position of the movable piston 14 in relation to the stationary piston chamber 4, into a front chamber facing the front plate 6 and a rear chamber facing a - rear - compressed air reservoir 16.

This compressed air reservoir 16 is arranged in the axial direction behind the piston chamber 4, separated by a flange 18 which has a radially outwardly projecting sealing lip 20 on its outer peripheral edge. This compressed air reservoir is surrounded on all sides by a circular-cylindrical compressed air reservoir shell 22.

The compressed air reservoir 16 is sealed at the front end by the sealing lip 20 on the outer peripheral edge of the flange 18 and at the rear end by a sealing lip on the inside of the rear impact cylinder plate 8 . In comparison to the prior art, seals are no longer necessary in the piston chamber 4, ie neither at the front end nor at the rear end of the piston skirt 2 nor around the impact rod 26 or the anvil 40, which considerably simplifies construction and testing.

In the present, preferred embodiment, the piston jacket 2 and the compressed air storage jacket 22 of the compressed air storage are made from the same material, namely from an aluminum tube with an identical diameter and identical wall thickness, which simplifies production extremely.

A feed pipe 28 is arranged on the back of a central passage opening of flange 18, which thus functions as a partition wall, and extends from flange 18 and a passage opening, which preferably extends centrally and axially through it, to the rear end of compressed air reservoir 16, where it widens slightly towards the Formation of a radially outwardly projecting paragraph 29 passes. The fluid-permeable membrane support 42 is arranged in this rear end of the feed tube 28 and in the shoulder 29 formed on it, which in the present case is designed as a lattice with several openings.

An elastic control membrane 32 , which sits in a membrane seat 44 on the inside of the cylinder cover 8 , rests against the rear side of the feed tube 28 and the membrane support 42 covering this end but not closing it. The control membrane 32 is formed as a round, loose disc of the order of, for example, about 80 mm in diameter, made of a flexible material, for example fabric or fiber reinforced rubber or flexible plastic. In order to keep the control membrane in its central position relative to the compressed air connection 10 and the inlet opening, the cylinder cover 8 has a membrane seat 44 shaped to the size of the control membrane 32 in the form of a shoulder on the inside of the cylinder cover 8 .

Extending backwards from this membrane seat 44 is also a curved recess in the cylinder cover 8 for forming a rear pressure chamber 34 in the cylinder cover 8 .

The rear percussion cylinder plate 8, also sometimes referred to as the “cylinder cover”, is screwed to the front plate 6 by means of a plurality of screw bolts 36, in this case four, which are spaced apart from one another circumferentially.

the 1 shows the percussion cylinder when the compressed air reservoir 16 is being filled via an air line (not shown) that is connected to the compressed air connection 10 . The compressed air represented by arrows flows through the compressed air connection 10 and the rear pressure chamber 34 past the peripheral edge between the diaphragm seat 44 into the compressed air reservoir 16 and fills it. The elastic control membrane 32 is straight and rests against the rear end of the feed tube and closes it media-tight.

According to 2 the compressed air reservoir 16 has reached a preset and optionally also adjustable pressure. The control membrane 32 is still in contact with the rear side of the feed tube 28 and closes it media-tight. The impact cylinder is now ready for use.

To trigger one in the 3 Impact shown only the pressure in the compressed air connection 10 must be reduced, which can be done in the simplest case by opening a valve. Due to the reduced pressure, the control diaphragm 32 can rest against the cavity or inside of the small, rear pressure chamber 34 on the cylinder cover 8, ie goes from the to the 1 and 2 illustrated and straight closed position in the 3 shown, arched open position. Thus, the control membrane 32 releases the rear end of the feed tube 28 and the compressed air suddenly flows out of the compressed air reservoir 16 through the feed tube 28 into the piston chamber 4 and drives the piston 14 forward while compressing the compression spring 24.

To trigger an in 3 shock shown only the pressure in the compressed air connection 10 must be reduced, which is done in the simplest case by opening a valve.

Due to the reduced pressure, the control membrane 32 can deform and goes from the to the 1 and 2 illustrated straight closed position in the 3 shown, arched open position. The control diaphragm 32 thus releases the rear end of the feed tube 28, so that the fluid or the drive medium suddenly flows from the compressed air reservoir through the diaphragm support 42 and the feed tube 28 into the piston chamber and also exerts pressure on the rear of the piston 14, whereby the Piston 14 is thrown against the spring force of the compression spring 24 against the shoulder 30 on the front plate 6. In the impact position, the compression spring 24 is fully tensioned and the compressed air compressed in the front chamber escapes via an outlet channel.

After the impact, the compression spring 24 returns the piston 14 to the rearward starting position, during which return the compressed air in the rear chamber escapes through a piston channel 46 which extends through the piston 14 from the front to the rear end. At its inlet opening at the rear end of the piston 14, the piston channel 46 can have a reduced cross-section in order to avoid an undesirably rapid outflow of the fluid from the compressed air reservoir 16 into the front chamber and a resulting reduction in the impact force when the impact is triggered.

In contrast to the prior art, the arrangement of the compressed air reservoir directly behind the piston chamber enables a significant reduction in the size of the impact cylinder in width and length, because no second jacket surrounding the piston chamber has to be provided and a shorter acceleration path for the piston to impact on the anvil or face plate is needed.

Furthermore, a seal now only has to take place at the front and rear end of the compressed air reservoir, whereas the significantly longer piston chamber itself no longer has to be sealed at the front and rear. Due to the shorter distances and the large feed tube, the fluid can flow faster from the rear compressed air reservoir into the piston chamber when the impact is triggered, which means that the acceleration of the piston is faster than in the prior art. For this reason, up to 10 percent less acceleration travel is required, i.e. the distance between the rear resting position of the piston and the point of impact on the front plate. Thus, the impact cylinder can also be shortened in length by 25 percent or more compared to the prior art.

Reference List

2

piston skirt

4

piston chamber

6

front impact cylinder plate

8th

rear impact cylinder plate

10

compressed air connection

12

anvil

14

Pistons

16

compressed air storage

18

flange

20

sealing lip

22

compressed air storage jacket

24

compression spring

26

strike bar

28

feed tube

29

Unit volume

30

front sleeve

32

control membrane

34

pressure chamber

36

screw bolts

38

mandrel

40

anvil

41

Federation

42

membrane support

44

diaphragm seat

46

piston channel

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• DE 102009051089 B4 [0006]

Claims (12)

Impact cylinder with a cylindrical piston jacket (2) which encloses an inner piston chamber (4) circumferentially, is closed at a front end by a front impact cylinder plate (6) and at a rear end by a rear impact cylinder plate (8), a piston chamber (4) arranged and longitudinally displaceable along a longitudinal axis between a front percussion position and a rear rest position movable piston (14), which divides the piston chamber (4) into a front chamber facing the front percussion cylinder plate and a rear chamber facing the rear percussion cylinder plate, a in the front percussion cylinder plate (6) impact rod (26), anvil (40) or the like that is accommodated in a relatively movable manner, a compression spring (24) arranged between the front impact cylinder plate (6) and the piston (14), a compressed air reservoir (16), a connection (10) for supplying a fluid, in particular compressed air, and an elastic control membrane (32) for w optionally filling the compressed air reservoir (16) and actuating the piston (14) for an impact release, CHARACTERIZED IN that a flange (18) is arranged at a rear end of the piston skirt (2), that the compressed air reservoir (16) is located behind the flange (18 ) is arranged that within a flange opening of the flange (18) a feed pipe (28) is arranged, which extends from the flange opening in the flange (18) to a rear end of the compressed air reservoir (16). percussion cylinder claim 1 CHARACTERIZED IN THAT a fluid-permeable membrane support (42) is formed at a rear end of the delivery tube (28). percussion cylinder claim 2 CHARACTERIZED IN THAT the membrane support (42) is constructed in the manner of a lattice or sieve. percussion cylinder claim 2 or 3 CHARACTERIZED IN THAT the membrane support (42) is seated on a collar or shoulder (30) at the rear end of the feed tube (28). Percussion cylinder after one of Claims 1 until 4 CHARACTERIZED IN THAT a sealing lip is formed at the rear end of the feed tube (28) for abutment against a front side of the control membrane (32). percussion cylinder claim 5 CHARACTERIZED IN THAT the sealing lip circumferentially encloses the diaphragm support (42). Impact cylinder according to one of the preceding claims, CHARACTERIZED IN THAT the piston jacket (2) of the piston chamber (4) and a compressed air storage jacket (22) of the compressed air storage (16) are made of the same material. Impact cylinder according to one of the preceding claims, CHARACTERIZED IN THAT the piston jacket (2) and the compressed air storage jacket (22) are designed as pipe sections with the same diameter and the same wall thickness. Impact cylinder according to any one of the preceding claims, CHARACTERIZED IN THAT only the compressed air accumulator (16) is sealed at a front end adjacent to the piston chamber (4) and at a rear end to the rear impact cylinder plate (8). percussion cylinder claim 9 CHARACTERIZED IN THAT the sealing at the front end is realized by a sealing lip (20) on the flange (20). Impact cylinder according to one of the preceding claims, CHARACTERIZED IN THAT the rear impact cylinder plate (8) has a membrane seat (44) for receiving the control membrane (32). percussion cylinder claim 11 CHARACTERIZED IN THAT a recess or bulge is provided in the rear percussion cylinder plate (8), which forms a pressure chamber (34) when the control membrane (32) is inserted.

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