DE20100122U1 - Pressure translator - Google Patents

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

European Patent Attorneys * Mandataires agrees before the Office europoen des brevets European Trademark Attorneys * Mandataires en marques europeennes

Patent attorneys

Georg Viel, graduate engineer

Christof Viel, graduate engineer EHICS,

Conseil en proprieto industrial (France) Thilo Wieske, graduate engineer

Günter Reiplinger

At the Roman Villa 5a ^{PO Box} ^ ⁰ - ^Box > ^{65 04} ° ³

D-66143 Saarbrücken

54669 Bollendorf Weinbergweg 15

D-66119 Saarbrücken

Telephone: ++49-(0)681-58 59 59 Fax: ++49-(0)681-58 59 81 eMail: saarpatent@t-online.de home: http://www.saarpatent.de

01003/5 January 2001 1
Pressure intensifier

The invention relates to a pressure intensifier according to the preamble of the 4*eteHtMisprüche and 2.

Such pressure intensifiers are known to the applicant and are offered as pneumatic/hydraulic components, for example as shown in the figure. Pneumatic pressure is exerted on a piston with a larger surface area. This creates a greater pressure on the piston with the smaller surface area. A hydraulic oil can be used on the pressure side, for example. With such pressure intensifiers, pressures in a ratio of 1:40 can be generated. Such pressure intensifiers can be used wherever high pressures must be present at

VAT ID No. DE 81 21 16 997

United Volksbanken Saarbrücken/St. Ingbert (bank code 591 901 0O) No. 11 39 78 00 07 Deutsche Bank Saar (bank code 590 700 70) No. 0 742 700

Cooperation with / cooperation with I cooperation avec: Cabinet

VIEL Patent Attorney Firm

Conseil en propriete industrial Dr. rer. nat. Dipl.-Biol. Ulrike Rudolph

F-57520 Grosbliederstroff D-69198 Schriesheim / Heidelberg

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01003 Reiplinger

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 a pressurization is transferred to the transmission piston of the pressure cylinder by a mechanical connection of this piston with a transmission piston of a pressure cylinder (here, the smaller piston is meant). The transmission piston of the pressure cylinder has a smaller surface area than the piston of the cylinder that is pressurized.

Different media can be used to transmit pressure, 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 with one piston on the low pressure side shown in Figure 1, several cylinders with several pistons can be used.

The present invention is based on the object of designing a pressure intensifier in such a way that it can be used in a wider variety of ways with regard to its possible applications.

This object is achieved according to the invention according to claim 1 in that at least one further piston of at least one further cylinder is present, wherein this at least one further cylinder as well as the at least one associated piston are designed as hollow cylinders, wherein the pressure cylinder is 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, wherein the pressure is built up by the movement of the pressure cylinder relative to the transmission piston in the pressure cylinder, wherein the transmission piston of the pressure cylinder has a smaller area than the at least one piston of the at least one cylinder, wherein at least one

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further piston of at least one further cylinder is present, wherein this at least one further cylinder as well as the at least one associated piston are hollow cylindrical, wherein the transmission piston is arranged in the hollow cylindrical recess.

Both the design according to claim 1 and the design according to claim 2 result in a significantly more compact design of the pressure intensifier compared to the designs known from the prior art. In this case, 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 essentially determined by the larger radius of the cylinder into which the pressure is fed. The installation space around the thinner pressure cylinder is wasted.

In the described embodiments according to the present invention, it proves to be advantageous that the space surrounding the pressure cylinder is used as an additional cylinder space to supply pressure.

In the embodiment according to claim 3, the transmission piston has a bore in the axial direction, which is designed as an oil channel between the pressure cylinder and the working cylinder.

This advantageously avoids the need to provide an additional channel to guide the printing medium from the printing cylinder into a working cylinder, for example of 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.

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This allows the pressure to be introduced into the individual cylinders by the pistons being able to support themselves accordingly in order to be able to pass the movement on to the pressure cylinder.

In the embodiment according to claim 5, the pressure in the cylinders is set pneumatically. The pressure cylinder is designed hydraulically. The pneumatic and hydraulic systems are atmospherically separated from one another 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.

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

Fig. 1: a representation of a pressure intensifier according to the prior art, Fig. 2: a first embodiment of a pressure intensifier according to the invention,

Fig. 3: another embodiment of a pressure intensifier according to the invention with a punching tool and

Fig. 4: the punching tool in a detailed view.

Figure 1 shows a pressure intensifier 1. In the pressure intensifier 1, a movement of the piston 2 of the cylinder 3 as a result of a pressure application is transmitted to the transmission piston 4 of the pressure cylinder 5 by a mechanical connection of this piston 2 with a transmission piston 4 of a pressure cylinder 5. The transmission piston 4 of the pressure cylinder 5 has a smaller area than the piston 2 of the cylinder 3, which is subjected to pressure. A connection 6 can also be seen, into which the pressure is fed in order to set the piston 2 of the cylinder 3 in motion. Furthermore,

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an opening 7 can be seen, through which the top of the cylinder 3 is connected to atmospheric pressure.

Figure 2 shows a first embodiment of the pressure intensifier according to the invention. It shows a section through a hydropneumatic pressure intensifier 201, which has a pneumatic piston 202, which in the embodiment shown is connected to a pneumatic ring piston 204 by two pull rods 203. The pull rods are provided with air channels 206, so that external connecting channels between the two pneumatic pistons can be omitted.

Both pneumatic systems are separated from each other by the separating flange 205. Furthermore, a pressure piston 211 can be seen, which is firmly connected to the piston 202.

The pressure cylinder 207 contains the oil reservoir 208. The pressure cylinder 207 is firmly connected to the separating flange 214 and together with the separating flange 214 forms the support bearing of the working piston 209.

Furthermore, a leakage channel 210 is present, through which the pneumatic part is atmospherically separated from the hydraulic part.

Furthermore, an opening 212 for the pressure medium can be seen again as well as openings 213 which connect the space of the cylinders behind the working volume of the pistons 202 and 204 with atmospheric pressure.

In this embodiment according to the invention, it proves to be advantageous that the conventional systems described at the outset can be modified to the system according to the invention without major design effort.

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Figure 3 shows a further embodiment of the pressure intensifier 301 according to the invention. It shows a section through a hydropneumatic pressure intensifier 301, which shows a pneumatic piston 302 that is firmly connected to another pneumatic piston 304 via the pressure cylinder 303. The oil reservoir 305 is located inside the pressure cylinder 303. Both pneumatic pistons 302 and 304 are divided into two pressure systems by the separating flange 306, with both surfaces of the pneumatic pistons 302 and 304 adding up.

The transmission piston 307 extends into the pressure cylinder 303. This transmission piston 307 is firmly connected to the working piston 308. This transmission piston 307 supports the support bearing 309 in the hydraulic separation flange 310 when there are lateral forces from the working piston 308. The working piston 308 is in turn equipped with a leak channel 311 so that air leakage cannot pass into the oil and vice versa.

In both embodiments of the invention, it proves to be advantageous that the force can be increased by up to 80% with the same size of the pressure intensifier. If the force is to remain the same, the design space can be reduced by up to 40%.

Furthermore, a punching tool is shown in Figure 3. This punching tool is driven by the working chamber 308 of the pressure intensifier 301 and will be described in more detail below.

It has proven to be advantageous that the punching tool is only open on the insertion side 312 and the waste side 313. The waste chutes that were previously used in punching tools are no longer required due to the compact design. This also means that a blockage in these waste chutes can no longer occur.

The accident safety zones are ensured by minimising the insertion gap on the insertion side 312 and by extending the dies of both the intermediate die and the counter flange die on the output side 313 without hindering the waste.

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Here you can see the protective projections 314 and 315 on the intermediate die 316 and the counter flange die 317.

The double cutting punch 320 is equipped with a window 321 on the insertion side so that the lower of the two cutting materials can be cut to length by the first cutting edge 323. The window 321 prevents the upper cutting material from being cut to length at this point. This ensures that the lower cutting material is shorter than the upper cutting material after the cutting process.

Some of the cuttings have raised areas. To avoid reduced safety on the loading side, the danger zone is covered by the safety flange 318 with protective shield tongue 319.

Furthermore, a hole punch 321 with an anti-twisting device 322 can be seen.

It is clear that this punching tool, which advantageously satisfies safety aspects through many detailed designs, can also be used with a drive other than the pressure intensifier according to the invention and provides protection independently. In this case, only individual details of the described details can be used.

A detailed view of the punching tool is shown again enlarged in Figure 4. Such punching tools are often used for cutting to length and finishing the ends of window fittings. With these fittings, the punched material consists of the upper flat bar 326 and the lower flat bar 327, which are firmly connected to one another at one end and can only be spread apart for punching. The lower bar 327 is cut to a shorter length than the upper bar 326. The upper bar 326 is usually also provided with a round hole, elongated hole or countersunk hole.

It has proven to be advantageous that the punching tool is only open on the insertion side 312 and the waste side 313. The internal

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Waste chutes that can lead to waste backlogs, as well as those that are
The compact design means that the required attachments are no longer
necessary.

The accident safety zones are achieved by minimizing the input gap at the
Insertion side 312 and the die extension of both the intermediate die 316 and
the counter flange die 317 on the waste side 313 without damaging the waste
The protective projections 314 and 315 on the intermediate die 316 and the counter flange die 317 can be seen here.

The double cutting punch 320 is a follow-on cutting tool with an optimized
cutting force utilization. The front cutting edge 323 is provided with a window 321
broken so that the lower rod 327 first independently of the upper rod 326
can be cut to length. Next, the hole punch 324 penetrates the upper rod 326. Finally, the upper rod 326 is cut to length from the cutting edge 327.

Often, cut goods have elevations 328. In order to reduce safety at the
To avoid the insertion side, the danger zone is defined by the safety flange 318 with
Protective shield tongue 319 covered.

To simplify assembly, the punch 324 is only inserted into the double-cutting punch 320 and screwed together with the piston 308.
An anti-twisting device is required for long hole punching. This device is secured by the
Hollow pin 322 ensures that the hole is securely fastened into the hole in the hole punch 324.

Claims (5)

1. Pressure intensifier ( 1 , 201 ), in which a movement of at least one piston ( 2 , 202 ) of at least one cylinder ( 3 ) as a result of a pressurization is transmitted to the transmission piston ( 4 , 211 ) of the pressure cylinder ( 5 , 207 ) by a mechanical connection of the at least one piston ( 2 , 202 ) with a transmission piston ( 4 , 211 ) of a pressure cylinder ( 5 , 207 ), wherein the transmission piston ( 4 , 211 ) of the pressure cylinder ( 5 , 207 ) has a smaller area than the at least one piston ( 2 , 202 ) of the at least one cylinder ( 3 ), characterized in that at least one further piston ( 204 ) of at least one further cylinder is present, wherein this at least one further cylinder as well as the at least one associated piston ( 204 ) are hollow-cylindrical, wherein the pressure cylinder ( 207 ) is arranged in the hollow-cylindrical recess. 2. Pressure intensifier ( 1 , 301 ), in which a pressure is built up as a result of a movement of at least one piston ( 2 , 302 ) of at least one cylinder ( 3 ) as a result of a pressurization in a pressure cylinder ( 5 , 303 ), characterized in that the at least one piston ( 302 ) is mechanically connected to the pressure cylinder ( 303 ), the pressure being built up by the movement of the pressure cylinder ( 303 ) relative to the intensifier piston ( 307 ) in the pressure cylinder ( 303 ), the intensifier piston ( 307 ) of the pressure cylinder ( 303 ) having a smaller area than the at least one piston ( 302 ) of the at least one cylinder, at least one further piston ( 304 ) of at least one further cylinder being present, this at least one further cylinder as well as the at least one associated piston ( 304 ) being of hollow cylindrical design. wherein the transmission piston ( 307 ) is arranged in the hollow cylindrical recess. 3. Pressure intensifier according to claim 2, characterized in that the intensifier piston ( 307 ) has a bore in the axial direction, which is designed as an oil channel between the pressure cylinder ( 303 ) and the working cylinder ( 308 ). 4. Pressure intensifier according to one of claims 1 to 3, characterized in that the individual cylinders are separated by separating flanges ( 306 , 310 ) which act as support surfaces for the respective pistons. 5. Pressure intensifier according to one of claims 1 to 4, characterized in that the pressure in the cylinders is set pneumatically and that the pressure cylinder is designed hydraulically, the pneumatic and hydraulic systems being atmospherically separated from one another by a leakage channel ( 210 , 311 ).