WO2002053920A2

WO2002053920A2 - Pressure transformer

Info

Publication number: WO2002053920A2
Application number: PCT/DE2002/000007
Authority: WO
Inventors: Günter Reiplinger
Original assignee: Reiplinger Guenter
Priority date: 2001-01-05
Filing date: 2002-01-04
Publication date: 2002-07-11
Also published as: EP1423614B1; DE50207661D1; ATE334314T1; DE10200137B4; EP1423614A2; PL369414A1; DE10290018D2; WO2002053920A3; DE20100122U1; AU2002234494A1; DE10200137A1

Abstract

The invention relates to a pressure transformer (1). A movement of at least one piston (2) in at least one cylinder (3), as a result of a pressurisation, is transmitted to a transformer piston (4) in a pressure cylinder (5), by means of a mechanical connection of the at least one piston (2) to the transformer piston (4) in the pressure cylinder (5). The transformer piston (4) in the pressure cylinder (5) has a smaller area than the at least one piston (2) in the at least one cylinder (3). At least one further piston in at least one further cylinder is provided, whereby said at least one further cylinder (3), as well as the one further corresponding piston (2) is embodied in a hollow cylindrical form, with the pressure cylinder (5) arranged in the hollow cylindrical recess. The invention also relates to an arrangement, whereby the pressure cylinder (5) moves relative to the transformer piston (4).

Description

Pressure intensifier

The invention relates to a pressure intensifier according to the preamble of claims 1 and 2.

Such pressure intensifiers are known to the applicant and are offered as a pneumatic / hydraulic component, for example according to the illustration in FIG. 1. In this case, pneumatic pressure is exerted on a piston with a larger area. This creates greater pressure on the piston with the smaller area. For example, hydraulic oil can be used on the pressure side. With such pressure translators, prints in the ratio of 1:40 can be generated. This type of pressure intensifier can be used wherever high pressures are required for short strokes. Areas of application include punching, embossing, signing, deep drawing, clamping, shearing, bending and straightening.

In the pressure intensifier, a movement of the piston of the cylinder (here the larger piston is meant) as a result of pressurization by a mechanical connection of this piston with a translation piston of a pressure cylinder (here the smaller piston is meant) is transmitted to the translation piston of the pressure cylinder. The translation piston of the pressure cylinder has a smaller area than the piston of the cylinder which is pressurized.

Different media can be used for pressure transmission such as compressed air, oil, water or other gases and liquids. These media can also be different on the low pressure side compared to the high pressure side.

Instead of the one cylinder shown in FIG. 1 with a piston on the low pressure side, several cylinders with several pistons can also be used there. The object of the present invention is to design a pressure intensifier in such a way that it can be used in a variety of ways with regard to its possible uses.

According to the invention, this object is achieved in that at least one further piston of at least one further cylinder is present, this at least one further cylinder as well as the at least one associated piston being of hollow-cylindrical design, the pressure cylinder being arranged in the hollow-cylindrical recess.

According to a further solution according to the invention according to claim 2, the at least one piston is mechanically connected to the pressure cylinder, the pressure being built up in the pressure cylinder by the movement of the pressure cylinder relative to the translation piston, the translation piston of the pressure cylinder having a smaller area than the at least one piston of the at least one cylinder, at least one further piston of at least one further cylinder being present, this at least one further cylinder as well as the at least one associated piston being of hollow-cylindrical design, the translation piston being arranged in the hollow-cylindrical recess.

Both in the configuration according to claim 1 and in the configuration according to claim 2, the pressure intensifier has a considerably more compact design compared to the designs known from the prior art. There the pressure cylinder protrudes from the cylinder into which the pressure is fed. This pressure cylinder is significantly thinner than the other cylinder. The external dimensions of the component are therefore largely determined by the larger radius of the cylinder into which the pressure is fed. The space around the thinner pressure cylinder is wasted.

In contrast, in the described embodiments according to the present invention, it proves advantageous that the space surrounding the pressure cylinder is used as an additional cylinder space in order to supply pressure. In the embodiment according to claim 3, the translation piston has a bore in the axial direction, which is designed as a channel for the pressure medium between the pressure cylinder and the working cylinder.

This advantageously avoids the need to provide an additional channel in order to guide the printing medium from the printing cylinder into a working cylinder, for example a punching device or the like.

In the embodiment according to claim 4, the individual cylinders are separated by separating flanges which act as support surfaces for the respective pistons.

As a result, the pressure can be introduced into the individual cylinders by the pistons then being supported accordingly in order to be able to pass on the movement into the pressure cylinder.

In the embodiment according to claim 5, the pressure is given pneumatically in the cylinders. The pressure cylinder is hydraulic. The pneumatic and hydraulic systems are separated from each other by a leak channel. This advantageously prevents oil from getting into the pneumatic part in the event of a leak in the hydraulic part and vice versa.

In the embodiment of the pressure intensifier according to claim 6, the volume of the pressure cylinder is formed by an annular chamber, the translation piston being extended along the inner diameter of the annular chamber by a pull rod which is connected to a support flange.

Through the design with the annular chamber, high pressure ratios can also be achieved with a sufficient stability of the components by appropriate design of the annular chamber. In other configurations, this can only be done by reducing the piston area of the pressure cylinder. If this becomes smaller and smaller, the translation piston becomes more and more unstable, so that with such a construction the The stability of the components imposes limits on the accessibility of pressure ratios.

In the embodiment of a pressure intensifier according to claim 7, the translation piston forms a pressure cylinder on both sides of the piston surface, each of these pressure cylinders being connected via a check valve to a supply of the pressure medium and to an output line for the pressure medium, one of the cylinders moving when the piston is moving the printing cylinder compresses the printing medium to the output line and the other printing cylinder sucks in the printing medium.

Thus, while in conventional pressure cylinders the translation piston has to be moved back relative to the pressure cylinder after one work cycle, the proposed design has the advantage that pressure medium can be conveyed quasi continuously because two pressure cylinders are available, one of which is the pressure medium in each direction of movement compacted.

In the embodiment according to claim 8, both cylinders with the associated pistons are hollow-cylindrical, a transmission piston being connected on both sides by means of support rods with support flanges, the support rods being guided through the hollow-cylindrical recesses, two pressure cylinders being formed, one of which is in each case one Side of the translation piston is formed with an annular chamber in the cylinder wall.

It is thereby advantageously achieved that pressure medium can be conveyed quasi continuously, a high pressure translation again being achievable through the configuration with the annular chambers.

In the embodiment of the pressure intensifier according to claim 9, the translation piston is connected by means of a pull rod to one of the pistons of the cylinders, the pull rod running in the opening of an annular chamber which connects with the Translation piston forms a first pressure cylinder, wherein the side wall of the translation piston forms a second pressure cylinder with the support flange and the other side of the translation piston.

This is an alternative embodiment for realizing a pressure intensifier. All external connections can advantageously be placed on one side of the pressure cylinder in a simple manner.

In the embodiment of the pressure booster according to claim 10, a pressure relief valve is provided in the translation piston for feeding pressure medium into the first pressure cylinder.

As a result, both pressure chambers of the pressure cylinder can advantageously be supplied with pressure medium via an external connection of the pressure booster.

In a pressure intensifier according to claim 11, a plurality of pressure cylinders are coupled to one another with regard to their movable parts,

This allows movements to be synchronized. By designing the volumes of the pressure cylinders, for example, the same actuating paths of actuating elements can be realized in a simple manner, or certain ratios of actuating paths of actuating elements can also be achieved by then adjusting the volumes accordingly. Due to the coupling of the moving parts, weight loads on the parts to be adjusted then play no role.

According to claim 12, a pressure intensifier with at least one cylinder and at least one pressure cylinder has a sealing system such that consists of a first seal, a receiving chamber and a second seal, the first seal being arranged between the low-pressure chamber and the receiving chamber and at an overpressure Low-pressure chamber acts sealingly against the receiving chamber and continues to oppose the receiving chamber when there is overpressure the low pressure chamber is permeable, the second seal acting independently of the pressure conditions sealing between the receiving chamber and the chamber of the at least one pressure cylinder.

As a result, the pressure medium in the low-pressure chamber can be held sealingly during compression by the first seal in the low-pressure chamber. In the event of compression, the pressure medium in the low-pressure chamber leads to possible losses of the pressure medium flowing from the low-pressure chamber into the receiving chamber. If the pressure medium in the low-pressure chamber is relaxed again, the pressure medium flows from the receiving chamber back into the low-pressure chamber due to the first seal. Leakage losses can thus be largely avoided. Due to the second seal, the pressure medium in the pressure cylinder is sealed against the receiving chamber.

According to claim 13, a pressure intensifier with at least one cylinder and at least one pressure cylinder is configured such that a damping material is applied to the stop surface of the piston on the cylinder wall and / or to the surface in the end position of the piston, and that to the stop surface of the piston a lug is attached to the cylinder wall and / or to the surface abutting in the end position of the piston.

This advantageously dampens the stop when the piston reaches the end position relative to the cylinder.

It can be seen that the subjects of claims 12 and 13 can also be usefully used with other pressure translators.

An embodiment of the invention is shown in the drawing. It shows in detail:

1: a representation of a pressure translator according to the prior art, Fig. 2-10: different versions of pressure intensifiers, some with working cylinders.

In the following figures, the following components are provided with the reference numbers listed below:

1 pressure intensifier

2 low pressure pistons

3 cylinders

4 translation pistons

5 printing cylinders

6 low pressure connection

7 atmospheric pressure opening

8 high pressure duct

9 high pressure support flange

10 low pressure support flange

11 intermediate flange

12 drawbar extension

13 return connection

14 cushioning

15 control valve

16 pilot valve

17 Signal vent valve

18 suction valve

19 pressure valve

20 storage tanks

21 double check valve

22 check valve

23 piston rod

24 ring channel

25 connecting cylinders

26 tie rods Air duct separating flange Working piston Leak channel openings Support bearing Stop punch Stop valve Protective cover Anti-twist lock bolt Control flange Filling and venting connector Sealing cap Rod end Spring Pressure medium duct Control duct Quick exhaust valve Cylinder tube Low pressure chamber first seal Second seal Receiving chamber Nut Nose Annular chamber Control valve Chamber Low pressure annular piston Oil supply quantity 61 cylinders

62 cylinders

63 cylinders

64 cylinders

1 shows a pressure intensifier 1. In the pressure intensifier 1, a movement of the low-pressure piston 2 of the cylinder 3 as a result of pressurization is transmitted to the translation piston 4 of the pressure cylinder 5 by a mechanical connection of this low-pressure piston 2 with a translation piston 4 of a pressure cylinder 5. The translation piston 4 of the pressure cylinder 5 has a smaller area than the low-pressure piston 2 of the cylinder 3, which is pressurized. A low-pressure connection 6 can also be seen, into which the pressure is fed in order to set the low-pressure piston 2 of the cylinder 3 in motion. Furthermore, an atmospheric pressure opening 7 can be seen, with which the upper side of the cylinder 3 is connected to atmospheric pressure.

FIG. 2 shows a pressure intensifier with two low-pressure pistons 2, which are firmly connected to one another by the pressure cylinder 5. By using the two low-pressure cylinders 2 with the same installation space, the achievable high pressure is almost doubled with the same installation space.

The translation piston 4 is extended as a tie rod 12 and screwed to the low-pressure support flange 10. On the opposite side, the translation piston 4 is guided through the intermediate flange 11 and screwed to the nut 54. The tie rod extension 12 of the translation piston 4 enables a translation to almost infinite, which is not possible with the known pressure intensifier due to an extremely thin translation piston. The translation piston 4 itself can be designed particularly advantageously as shown here as a tie rod 12, which significantly reduces the pressure intensifier. The pressure cylinder 5 is designed as an annular chamber between the connection of the two low-pressure cylinders 2 and the extension of the pull rod 12. A high-pressure duct 8 is guided through the pull rod 12, via which the pressure medium can be discharged to a working cylinder.

Furthermore, a sealing system is shown in the pressure intensifier shown in FIG. 2. The sealing system is designed for the return of leakage in such a way that leakage from the low-pressure chamber 50 is held back by the double-acting (second) seal 52 via the single-acting (first) seal 51 and initially collects in the receiving chamber 53 and builds up pressure. When the low-pressure chamber 50 is depressurized, the pressure in the receiving chamber 53 decreases via the (first) seal 51, which opens like a check valve, into the receiving chamber 53. Due to the simultaneous pressurization of the low-pressure connections 6, the pressure medium (for example oil) is displaced from the annular chamber of the pressure cylinder 5 through the high-pressure channel 8. The system is reset by pressurizing port 13, a spring, not shown here, or by pushing the oil back through a working cylinder, not shown here. The leakage feedback system of the first seal 51 and the second seal 52 replaces the otherwise cost-intensive pressure medium separation by a channel to the free atmosphere. The pressure intensifier can also be equipped with an oscillation control as will be explained in the following figures.

The pressure intensifier shown in Figure 3 is double-acting. This means that the high-pressure medium is displaced in each of the two directions of movement, high-pressure medium being sucked in on the other side at the same time. The difference from the pressure intensifier according to FIG. 2 is also that the translation piston 4 acts as a separating and supporting piston between the two sides and that it is designed as a tie rod extension 12 on both sides. Elastic stop dampers 14 are installed on both inner sides of the low-pressure flanges 10. In order to extend the progressive path of the stop without requiring additional installation space, the low-pressure piston 2 is designed with the wedge-shaped and rounded nose 55. The oscillation control consists of a control valve 15, which is designed as a 3/2 way valve, the pilot valve 16 and the signal venting valve 17. The control valve 15 can also be a 4/2 way valve. The suction valves 18 and pressure valves 19 are used for external pressure medium separation. The storage reservoir 20 can be an open or closed system. Gases can also be a supply line.

When the control valve 15 is pressurized, the movement of the pistons 2 with the pressure cylinder 5 begins. The direction is determined by the starting position of the control valve. The pressure medium is sucked in from one side via the suction valve 18 and delivered to the consumer via the pressure valve 19 on the other. After the low-pressure piston 2 has touched the pilot valve 16, the control valve 15 is switched over by the signal pressure and the pistons move in the opposite direction until the signal venting valve on the opposite side is touched and the signal pressure is vented and the control valve switches back.

The dual use shown by two low-pressure pistons 2 and the narrow transmission piston 4 used on both sides result in a reduction in installation space by approximately 70% and a more economical use of the low-pressure medium by approximately 30%.

The illustrated nose 55 of the low-pressure piston 2 in connection with the stop damping 14 brings not only the extremely short damping but also a rebound effect, which results in a higher stroke frequency and longer life.

The oscillation control with the pilot valve 16 in combination with the signal vent valve 17 prevents a standstill in a dead switching point.

The schematic representation of a pressure intensifier according to FIG. 4 differs from the representations of FIGS. 2 and 3 in that the translation piston 4 is movable and is fixedly connected to the low-pressure pistons 2 via the piston rod 23 is. A check valve 22 is arranged in the translation piston 4 and only allows the pressure medium to flow into the annular chamber 56. This pressure medium emerges via the ring channel 24, through the high pressure channel 8 and via the double check valve 21 to the consumer. The two low-pressure cylinders 2 are firmly connected to one another by the connecting cylinder 25. The connecting cylinder can also be replaced by at least two tie rods similar to the illustration in FIG. 6. The double check valve 21 replaces two single check valves and a T-connection. An oscillating movement is achieved by the control valve 57, which is designed as a pulse valve and is secured in both positions with magnets, which in each case prevent the valve spool from reaching a dead center position. However, control comparable to that shown in FIG. 3 is also possible.

It can be seen that such control valves can also be used with other pressure intensifiers. The main advantage of these control valves is that the moving parts of the control valve are pulled or pushed into the end position by the magnets. The control valve is actuated mechanically (directly or by pressurization) so that the moving parts of the control valve can be released from the one end position against the magnetic force and at least moved so far in the direction of the other end position that they also move there acting magnetic forces is achieved. A defined operating point of the control valve is therefore always reached without it "hanging" between the operating points.

The pressurization of the control valve 57 moves the low-pressure piston 2 in the direction of the low-pressure support flange 10. The translation piston 4 is carried along, the pressure medium being displaced from the annular chamber 56 through the annular channel 24 and the high-pressure channel 8 to the consumer via the double check valve 21. At the same time, pressure medium is drawn into the chamber 58 via the suction valve 18. After touching the low-pressure piston 2 with the actuating plunger of the control valve 57, the latter is suddenly switched over against the magnetic holding force. The direction of movement of the translation gear 4 changes. The print medium will partly displaced into the annular chamber 56 via the check valve 22 and partly based on the volume of the piston rod 23 through the pressure support flange 9 and the high-pressure channel 8 via the double check valve 21 to the consumer. The direction is reversed by touching the low-pressure piston 2 with the control valve 57.

The movable, double-acting translation piston 4 with the integrated check valve 22 and the ring channel 24 enables all connections to be made on one side. This results in a simple flange mounting option without sacrificing space or increasing pressure due to the multiple drive concept.

In the control shown, it proves particularly advantageous that the control valve 57 is designed as a pulse valve. This is integrated in the intermediate flange 1 1 ^• , which means that reversing valves can be avoided with the necessary wiring.

In the illustration in FIG. 5, a pressure intensifier can be seen, which corresponds to the essential principles of the illustration in FIG. 3. The main difference is that there are two pressure cylinders 5 here. In addition to the translation function, a pressure intensifier according to the illustration in FIG. 5 also has a quantity divider function or a quantity metering function. In this way, independent working cylinders can be brought into a very exact, same position using very inexpensive means. A possible different counterforce does not matter here. The number of printing cylinders can be arbitrary and, for example, can also be more than two. The print volumes can also be different if differential positions are required. This multiple pressure translator system can in principle also be used with other forms of pressure translator. It is essential that the moving parts of the pressure intensifiers - in the example shown in FIG. 5, the pressure cylinders 5 - are connected to one another. FIG. 6 shows a further embodiment of the pressure intensifier. A section through a hydropneumatic pressure intensifier can be seen, which has a low-pressure piston 2, which in the exemplary embodiment shown is connected to a low-pressure ring piston 59 by means of two tie rods 26. The tie rods are provided with air channels 27, so that external connecting channels between the two low-pressure cylinders can be omitted.

Both pneumatic systems are separated from one another by the separating flange 28.

Furthermore, a translation piston 4 can be seen, which is firmly connected to the low-pressure piston 2.

The pressure cylinder 5 contains the oil supply quantity 60. The pressure cylinder 5 is fixedly connected to the separating flange 28 and, together with the separating flange 28, forms the support bearing of the working piston 29.

There is also a leakage channel 30 through which the low-pressure part is atmospherically separated from the hydraulic part.

Furthermore, a low-pressure connection 6 for the pressure medium can be seen again, as well as openings 31 which connect the space of the cylinders behind the working volume of the pistons 2 with atmospheric pressure.

In this embodiment according to the invention, it proves to be advantageous that the conventional systems described at the outset in connection with the prior art can be changed to the system according to the invention without major design effort.

This is achieved, on the one hand, by the low-pressure coils 2 connected to at least two tie rods 28. As a result, no additional lines are required for the air ducts, in that at least one of these tie rods has a corresponding opening, through which the pressure medium can flow. Furthermore, the pressure cylinder 5 is advantageously firmly connected to the intermediate flange of the working cylinder. This requires high stability and fast pressure medium transfer. Furthermore, it proves to be advantageous that the support bearing 32 results in a precise and stable guidance of the working piston 29. The leakage channel 30 ensures reliable pressure medium separation. In particular, their mixing is prevented.

FIG. 7 shows a representation of a pressure intensifier and a working cylinder combination, which consists of a combination of the representation according to FIGS. 2 and 6. The difference to the two figures mentioned is that the translation piston 4 is fixedly connected to the working piston 29 and extended by the stop rod 33 and is guided through the pressure cylinder 5 and the low pressure flange 10. The protruding end is provided with an adjustable stop 34. This stop actuates the valve 36 when struck, from which the end of the lifting process is acknowledged to a process control. The protective hood 37 avoids the risk of injury.

The working piston 29 is provided with an anti-rotation pin 38. This is supported in the rod flange 39 and in the separating flange 28. The pin is sealed on both sides in the working piston 29. The bolt is advantageously guided tangentially through the leakage channel 30, as a result of which pressure medium mixing is prevented.

This anti-rotation pin 38 proves to be advantageous. It can be seen that this can also be used with other pressure intensifiers.

In the exemplary embodiment shown, the stop enables an exact, adjustable stroke limitation, which is absolutely necessary, for example, in the case of label punching. The effort for this is minimal, since most of the parts are already required for the pressure intensifier. Advantageously, the usual complex additional devices can be replaced by the anti-rotation pin. The valve 36 receives its supply energy from the pressure chamber, so that only one signal line is required and the diversion is saved. With the valve, the pressure intensifier can be used in an automatic process without much additional effort.

FIG. 8 shows a schematic representation of a pressure intensifier / working cylinder combination. This combination contains a power cylinder comparable to the illustration in FIG. 6 and a pressure intensifier comparable to the illustration in FIG. 7. It can be seen here that the translation piston 4 is not extended by other functional parts. The pressure cylinder 5 is guided out through the low-pressure piston 2 and through the low-pressure support flange 10 as a filling and venting nozzle 40 and closed with a closure cap 41. The spring 43 sets the pressure medium in the rest position and at start-up under a pressure which is slightly above that of the free atmosphere. By removing the closure cap 41, the spring is relaxed and a safe venting and filling is possible. The spring 43 can therefore advantageously be relaxed. The rod flange 39 and the rod end 42 are designed directly as a tool holder and guide.

The filling and venting nozzle simplifies filling with liquid pressure medium, filling level control and, in the case of service, venting after air has entered the pressure fluid.

The rod flange is at the same time designed as a tool guide, as a result of which the tool costs are reduced and the tool can be downsized. It is the tool that is to be attached to the pressure intensifier.

The spring pressurizes the pressure medium, preventing air from seeping in. The preload is released by unscrewing the cap. FIG. 9 shows the representation of a partial area of a pressure intensifier on the working cylinder side. The difference to the illustrations in FIGS. 6 to 8 is that the high-pressure medium does not act on the piston side but on the rod side. In the channel 44, the pressure medium is passed through the piston 29 and emerges on the rod side. The working piston leads a relative movement to the direction of movement of the pressure cylinder 5. The working piston 29 has a pulling action in contrast to FIGS. 6 to 8, in which it has a pushing action.

The reversal of the direction of force is fundamentally possible with all pressure intensifiers with working cylinders. This also applies in particular to pressure intensifiers which are already known from the prior art in terms of their design. Depending on the direction of work, the pressure medium channel can emerge on the piston side or pull on the rod side.

FIG. 10 shows the representation of a further exemplary embodiment of a pressure intensifier, which differs from the representations of FIGS. 2 to 8. It can be seen that the pull rod 12 is designed as a pure connecting rod without a piston. It is also used as a control channel 45. The connecting cylinder 25 is only a pure connection of the pistons 2. The suction valves 18 and the pressure valves 19 are installed in the intermediate flange 11. The two pressure cylinders 61, 64 are delimited on the outside by the cylinder tubes 47.

The pressure medium, which can be compressed air, for example, is fed through the control valve 15 into the cylinder 64 and the cylinder 61. The cylinders 64 and the cylinder 61 together compress the air in the cylinder 63 to slightly more than twice the pressure exiting through the exhaust valve 19a. After the piston 2 has touched the pilot valve 16, the control valve 15 is switched over. The cylinder 64 is vented via the quick exhaust valve. Compressed air is fed into the cylinders 62 and the cylinder 63 through the control valve 15. The cylinders 62, 63 compress the compressed air present in the cylinder 61 to slightly more than twice the pressure. This compressed air exits via the outlet valve 19b. After touching the signal Ventilation valve 17, the pressure in the control channel 45 is reduced. The control valve 15 switches over and the system compresses again in the other direction.

A pressure intensifier is known to the applicant in connection with FIG. 10, which is more complex to manufacture and whose output is lower. This is due to the four outer tie rods there and the more expensive square flange design. The exhaust air is broken down by the working valve, which makes the system slow. The stop dampers do not act progressively, as is the case in the present invention due to the design with the nose 55.

In the proposed embodiment, on the other hand, it proves advantageous that a central pull rod is present, which can also be used as a control line. This means that all flanges can be manufactured in the much cheaper round design. The flange 10 can be designed as a base plate for an ISO standardized base plate valve, which considerably simplifies worldwide service. The quick exhaust valves 46 increase the output by 20-30%. The damping lugs 55 cause a progressive stop, which considerably extends the service life.

It is therefore a pressure intensifier with a plurality of cylinders in which pistons can be moved, wherein when the pistons are pressurized, at least one of the pistons forms on its rear side with the cylinder wall another cylinder which acts as a pressure cylinder in which the pressure medium is compressed ,

For this purpose, inputs and outputs are advantageously connected to valves, so that the volume acting as a pressure cylinder is connected to an output line for the pressure medium in the compression phase of the pressure medium in the pressure cylinder, with new pressure medium there during the backward movement in the relaxation phase of the volume forming the pressure cylinder is suckable. As illustrated in FIG. 10, in this relaxation phase of one volume, wiring can advantageously take place in such a way that another volume acts as a pressure cylinder. The upper and lower boundary surfaces are connected to each other with a tie rod in the middle of the volumes. A control line, through which a pressure medium can be conveyed, can advantageously be guided through this tie rod, with control valves which can be actuated in the region of the boundary surfaces for connecting the pressure cylinders.

Claims

1. pressure intensifier (1), in which a movement of at least one piston (2) at least one cylinder (3) as a result of pressurization by a mechanical connection of the at least one piston (2) with a translation piston (4) of a pressure cylinder (5) on the Transmission piston (4) of the pressure cylinder (5) is transmitted, the translation piston (4) of the pressure cylinder (5) having a smaller area than the at least one piston (2) of the at least one cylinder (3), characterized in that at least one further Piston (2) of at least one further cylinder (3) is provided, this at least one further cylinder (3) and the at least one associated piston (2) being hollow-cylindrical, the pressure cylinder (5) being arranged in the hollow-cylindrical recess.

2. Pressure intensifier (1), in which a pressure is built up as a result of a movement of at least one piston (2) of at least one cylinder (3) as a result of pressurization in a pressure cylinder (5), characterized in that the at least one piston (2) is connected to is mechanically connected to the pressure cylinder (5), the pressure being built up in the pressure cylinder (5) by the movement of the pressure cylinder (5) relative to the translation piston (4), the translation piston (4) of the pressure cylinder (5) having a smaller area than the at least one piston (2) of the at least one cylinder (3), at least one further piston (2) of at least one further cylinder (3) being present, this at least one further cylinder (3) as well as the at least one associated piston (2) are hollow cylindrical, the translation piston (4) being arranged in the hollow cylindrical recess.

3. Pressure intensifier (1) according to claim 2, characterized in that the translation piston (4) has a bore in the axial direction, which is designed as a channel (8) for the pressure medium between the pressure cylinder (5) and the working cylinder.

4. Pressure intensifier (1) according to one of claims 1 to 3, characterized in that the individual cylinders (3) are separated by separating flanges (11) which act as support surfaces for the respective pistons (2).

5. Pressure intensifier (1) according to one of claims 1 to 4, characterized in that the pressure in the cylinders (3) is pneumatic and that the pressure cylinder (5) is hydraulic, the pneumatic and hydraulic systems through a leakage channel ( 30) are separated from each other atmospherically.

6. Pressure intensifier (1) according to one of claims 1 to 5, characterized in that the volume of the pressure cylinder (5) is formed by an annular chamber, the translation piston (4) being extended along the inner diameter of the annular chamber by a pull rod (12) which is connected to a support flange (10).

7. Pressure intensifier (1) according to one of claims 1 to 6, characterized in that the translation piston (4) forms a pressure cylinder (5) on both sides of the piston surface, each of these pressure cylinders (5) via a check valve (18, 19) is connected to a supply (20) of the pressure medium and to an output line for the pressure medium, with the movement of the pistons (2) the cylinder (3) one of the pressure cylinders (5) compressing the pressure medium to the output line and the other pressure cylinder (5) Media is sucked in.

8. Pressure intensifier (1) according to claim 7, characterized in that both cylinders (3) with the associated pistons (2) are hollow-cylindrical, wherein a transmission piston (4) is connected on both sides by means of support rods (12) to support flanges (10), the support rods (12) being guided through the hollow cylindrical recesses, two pressure cylinders (5) being formed, one of which is formed on each side of the transmission piston (4) with an annular chamber in the cylinder wall.

9. pressure intensifier (1) according to claim 7, characterized in that the translation piston (4) by means of a pull rod (12) with one of the pistons (2) of the cylinder (3) is connected, the pull rod (12) in the opening of a Annular chamber runs, which forms a first pressure cylinder (5) with the translation piston (4), the side wall of the translation piston (4) forming a second pressure cylinder (5) with the support flange (10) and the other side of the translation piston (4).

10. Pressure intensifier according to claim 9, characterized in that a pressure relief valve (22) is provided in the transmission piston (4) for feeding pressure medium into the first pressure cylinder (5).

11. Pressure intensifier according to one of the preceding claims, characterized in that a plurality of pressure cylinders (5) are coupled to one another with regard to their movable parts (4, 5).

12. Pressure intensifier (1) according to one of the preceding claims, characterized in that a sealing system (51, 52, 53) is arranged between the low-pressure chamber (50) of the at least one cylinder (3) and the chamber of the at least one pressure cylinder (5) , which consists of a first seal (51), a receiving chamber (53) and a second Seal (52), wherein the first seal (51) is arranged between the low-pressure chamber (50) and the receiving chamber (53) and acts as a seal against the receiving chamber (53) if the low-pressure chamber (50) is overpressured and furthermore if the receiving chamber is overpressured (53) is permeable to the low pressure chamber (50), the second seal (52) acting independently of the pressure conditions in a sealing manner between the receiving chamber (53) and the chamber of the at least one pressure cylinder (5).

13. Pressure intensifier (1) according to one of the preceding claims, characterized in that a damping material (14) is applied to the stop surface of the piston (2) on the cylinder wall and / or to the surface in the end position of the piston (2) and that a nose (55) is attached to the stop surface of the piston (2) on the cylinder wall and / or on the surface abutting in the end position of the piston.