EP1423614B1 - Transmetteur de pression - Google Patents

Transmetteur de pression Download PDF

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Publication number
EP1423614B1
EP1423614B1 EP02701161A EP02701161A EP1423614B1 EP 1423614 B1 EP1423614 B1 EP 1423614B1 EP 02701161 A EP02701161 A EP 02701161A EP 02701161 A EP02701161 A EP 02701161A EP 1423614 B1 EP1423614 B1 EP 1423614B1
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EP
European Patent Office
Prior art keywords
pressure
piston
cylinder
transformer
cylinders
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02701161A
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German (de)
English (en)
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EP1423614A2 (fr
Inventor
Günter Reiplinger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Reiplinger & Cokg GmbH
Original Assignee
Reiplinger & Co KG GmbH
Reiplinger & Cokg GmbH
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Publication of EP1423614A2 publication Critical patent/EP1423614A2/fr
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Publication of EP1423614B1 publication Critical patent/EP1423614B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids

Definitions

  • the invention relates to a pressure intensifier according to the preamble of patent claim 1.
  • Such pressure booster are known to the applicant and are offered as a pneumatic / hydraulic component, for example, according to the illustration of Figure 1.
  • a pneumatic pressure is exerted on a piston with a larger area. This results in a larger pressure on the piston with the smaller area.
  • On the pressure side for example, a hydraulic oil can be used.
  • pressure intensifiers prints can be produced in the ratio of 1:40.
  • the type pressure intensifier can be used wherever high pressures must be present for short strokes. Applications include punching, embossing, signing, deep drawing, clamping, shearing, bending and straightening.
  • a movement of the piston of the cylinder (meaning here the larger piston) due to a pressurization by a mechanical connection of this piston with a translation piston of a pressure cylinder (meaning here the smaller piston) is transmitted to the translation piston of the impression cylinder.
  • the translation piston of the impression cylinder has a smaller area than the piston of the cylinder, which is pressurized.
  • Various media can be used for pressure transmission, such as compressed air, oil, water or other gases and liquids. These media may also be different on the low pressure side than the high pressure side.
  • a cylinder with a piston on the side of low pressure there may also be used a plurality of cylinders with a plurality of pistons.
  • a pressure booster is known in which by means of two interconnected pistons a transmission piston is driven.
  • the two pistons are connected to one another in such a way that in the connection there is a hollow cylindrical receptacle which forms the pressure cylinder.
  • the translation piston is arranged to be movable.
  • the present invention has for its object to provide a pressure intensifier in such a way that it is more versatile in terms of its applications.
  • 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 translation piston in the pressure cylinder, wherein the translation piston of the pressure cylinder has a smaller area than the at least one piston of at least one cylinder, wherein at least one further piston of at least one further cylinder is present, wherein said at least one further cylinder as well as the at least one associated piston are formed as a hollow cylinder, wherein the transmission piston is arranged in the hollow cylindrical recess.
  • the space surrounding the pressure cylinder is used as an additional cylinder space to feed pressure.
  • the transmission piston has a bore in the axial direction, which is formed as a channel for the pressure medium between the pressure cylinder and the working cylinder.
  • an additional channel must be provided to direct the print medium from the printing cylinder in a working cylinder, for example a punching device or the like.
  • the individual cylinders are separated by separating flanges, which act as support surfaces for the respective pistons.
  • the pressure can be introduced into the individual cylinders, in that the pistons can then be supported accordingly in order to be able to pass on the movement into the pressure cylinder.
  • the pressure setting in the cylinders takes place pneumatically.
  • the impression cylinder is hydraulically formed.
  • the pneumatic and hydraulic systems are atmospherically separated by a leakage channel.
  • the translation piston forms a pressure cylinder on both sides of the piston surface, each of these pressure cylinder is connected via a check valve with a supply of the pressure medium and with an output line for the pressure medium, wherein during the movement of the piston of the cylinder the pressure cylinder compresses the pressure medium to the output line and the other pressure cylinder sucks pressure medium.
  • both cylinders are hollow cylindrical with the associated piston, wherein a translation piston is connected on both sides by support rods with support flanges, wherein the support rods are guided by the hollow cylindrical recesses, wherein two pressure cylinders are formed, one of which in each case one Side of the transmission piston is formed with an annular chamber in the cylinder wall.
  • the transmission piston is connected by means of a pull rod with one of the piston of the cylinder, wherein the pull rod extends in the opening of an annular chamber, which with the Translation piston forms a first pressure cylinder, wherein the side wall of the transmission piston with the support flange and the other side of the transmission piston forms a second pressure cylinder.
  • a pressure relief valve in the transmission piston is provided for feeding of pressure medium in the first pressure cylinder.
  • both pressure chambers of the pressure cylinders can advantageously be supplied with pressure medium via an external connection of the pressure booster.
  • a plurality of printing cylinders are coupled with respect to their moving parts.
  • a pressure booster with at least one cylinder and at least one pressure cylinder on a sealing system such, consisting of a first seal, a receiving chamber and a second seal, wherein the first seal between the low-pressure chamber and the receiving chamber is arranged and at an overpressure of Low-pressure chamber against the receiving chamber has a sealing effect and continues with an overpressure of the receiving chamber opposite the low-pressure chamber is permeable, the second seal acts sealingly regardless of the pressure conditions between the receiving chamber and the chamber of the at least one pressure cylinder.
  • the pressure medium in the low-pressure chamber can be sealingly held by the first seal in the low-pressure chamber during compression. Any losses lead to a compression of the pressure medium in the low pressure chamber that the pressure medium from the low pressure chamber flows into the receiving chamber. If the pressure medium of the low-pressure chamber is relaxed again, the pressure medium from the receiving chamber flows back into the low-pressure chamber due to the first seal. Leakage losses can be largely avoided. Due to the second seal, the pressure medium in the pressure cylinder is sealed against the receiving chamber.
  • a pressure booster with at least one cylinder and at least one pressure cylinder is designed so that a damping material is applied to the abutment surface of the piston on the cylinder wall and / or on the abutting in the end position of the piston surface and that on the abutment surface of the piston the cylinder wall and / or on the abutting in the end position of the piston surface a nose is attached.
  • the stop is advantageously damped when reaching the end position of the piston relative to the cylinder.
  • FIG. 1 shows a pressure booster 1.
  • a movement of the low-pressure piston 2 of the cylinder 3 is transmitted to the transmission piston 4 of the pressure cylinder 5 as a result of pressurization by a mechanical connection of this low-pressure 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 low-pressure piston 2 of the cylinder 3, which is pressurized.
  • 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 booster with two low-pressure pistons 2, which are firmly connected to one another by the pressure cylinder 5.
  • the two low-pressure piston 2 almost doubling of the achievable high pressure is achieved with the same space with the same Baurum.
  • the transmission piston 4 is extended as a pull rod 12 and bolted to the Nieder Kunststoffstützflansch 10 firmly. On the opposite side of the transmission piston 4 is guided through the intermediate flange 11 and bolted to the nut 54.
  • the Switzerlandstangenverinrung 12 of the transmission piston 4 allows a translation to almost infinite, which is not possible with the known pressure intensifier by an extremely thin translation piston.
  • the translation piston 4 itself can be particularly advantageous as shown here simultaneously designed as a pull rod 12, which makes the pressure intensifier much cheaper.
  • the pressure cylinder 5 is formed as an annular chamber between the connection of the two low-pressure piston 2 and the extension of the tie rod 12. Through the pull rod 12 through a high pressure passage 8 is stirred, via which the pressure medium can be output to a working cylinder.
  • a sealing system is shown in the pressure booster shown in Figure 2.
  • the sealing system is designed for leakage return so that leakage from the low pressure chamber 50 via the one-way (first) seal 51 is held back by the double-acting (second) seal 52 and initially collects in the receiving chamber 53 and builds up a pressure.
  • the pressure from the receiving chamber 53 builds up into the receiving chamber 53 via the (first) seal 51, which opens like a check valve.
  • the pressure medium for example oil
  • the provision of the system is carried out by the pressurization of port 13, a spring, not shown here or by the backward displacement of the oil by a working cylinder, not shown here.
  • the leakage return system of the first seal 51 and the second seal 52 replaces the otherwise costly pressure medium separation through a channel to the free atmosphere.
  • the pressure booster can also be equipped with a Oszilliersteuerung as this will be explained in the following figures.
  • the pressure translator shown in Figure 3 is double-acting. This means that in each of the two directions of movement, the high-pressure medium is displaced, wherein at the same time high-pressure medium is sucked in on the other side.
  • the difference to the pressure booster of Figure 2 also consists in that the transmission piston 4 acts as a separating and supporting piston between the two sides and it is formed on both sides as Glasankerverinrung 12. On both inner sides of the low-pressure flanges 10 elastic stop damping 14 are installed.
  • the low-pressure piston 2 is designed with the wedge-shaped and rounded nose 55,
  • the Oszilliersteuerung 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 may also be a 4/2-way valve.
  • the suction valves 18 and pressure valves 19 are used for external pressure medium separation.
  • the reservoir 20 can be an open or closed system. Gases can also be a supply line.
  • control valve 15 By pressurizing the control valve 15, the movement of the piston 2 with the pressure cylinder 5 begins. The direction is dictated by the initial position of the control valve. The pressure medium is sucked from one side via the suction valve 18 and discharged at the other via the pressure valve 19 to the consumer. After touching the low-pressure piston 2 with the pilot valve 16, the control valve 15 is switched over from the signal pressure and the pistons move in the opposite direction until the signal venting valve on the opposite side touches and the signal pressure is vented and the control valve switches back.
  • the illustrated nose 55 of the low-pressure piston 2 in conjunction with the stop damping 14 brings next to the extremely short damping and a scrubprallefFeh-t, which has a higher stroke frequency and life extension result.
  • the schematic representation of a pressure booster of Figure 4 differs from the illustrations of Figures 2 and 3, characterized in that the transmission piston 4 is movable and connected to the low-pressure piston 2 via the piston rod 23 fixed is.
  • a check valve 22 is arranged, which can flow the pressure medium only in the annular chamber 56. The discharge of this pressure medium via the annular channel 24, through the high pressure passage 8 and the double check valve 21 to the consumer.
  • the two low-pressure pistons 2 are firmly connected to each other by the connecting cylinder 25.
  • the connecting cylinder can also be replaced by at least two tie rods similar to the representation of FIG.
  • the double check valve 21 replaces two individual check valves and a T-connection.
  • the control valve 57 which is designed as a pulse valve and secured in both positions with magnets which each prevent a dead center position of the valve spool, an oscillating movement is achieved. But it is also a control comparable to that shown in Figure 3 possible.
  • control valves can also be used in other pressure intensifiers.
  • the main advantage of these control valves is that the moving parts of the control valve are pulled or pushed defined by the magnets in the end position.
  • the control valve is mechanically actuated (directly or by pressurization), so that the movable parts of the control valve against the magnetic force from the one end position can be solved and moved at least as far in the direction of the other end position, that this through there as well defined magnetic forces defined is achieved. So it is always a defined operating point of the control valve achieved without this "hangs" between the operating points.
  • the low-pressure piston 2 is moved in the direction Niederdruckstützflansch 10.
  • the transmission piston 4 is taken along, wherein the pressure medium from the annular chamber 56 is displaced by the annular channel 24 and the high pressure passage 8 via the double check valve 21 to the consumer.
  • 18 pressure medium is sucked into the chamber 58 via the suction valve.
  • the print medium is partly displaced via the check valve 22 in the annular chamber 56 and the other part corresponding to the volume of the piston rod 23 through the pressure support flange 9 and the high pressure passage 8 via the double check valve 21 to the consumer.
  • the direction reversal takes place.
  • the movable, double-acting transmission piston 4 with the integrated check valve 22 and the annular channel 24 allows to attach all ports on one side. This results in a simple Anflanschönkeit without sacrificing space savings or pressure increase by the multiple drive concept.
  • control valve 57 is formed as a pulse valve. This is integrated into the intermediate flange 11, whereby Um. tenuventile can be avoided with the necessary line expense.
  • a pressure booster can be seen, which corresponds to the essential principles of the representation of Figure 3.
  • a pressure intensifier according to the illustration of Figure 5 has in addition to the translation and a flow divider function or a metering function. It can be brought into a very precise, same position so independent working cylinder with very inexpensive means. In this case, a possible different reaction force does not matter.
  • the number of printing cylinders can be arbitrary and, for example, more than two. Also, the print volumes may be different if differential positions are required.
  • This multiple pressure translator system can in principle also be used in other embodiments of pressure intensifiers. It is essential that the moving parts of the pressure booster - in the example shown in Figure 5, the impression cylinder 5 - are interconnected.
  • FIG. 6 shows a further embodiment of the pressure booster. You can see a section through a hydropneumatic. Pressure booster, which has a low-pressure piston 2, which is connected in the embodiment shown with 2 tie rods 26 with a low-pressure ring piston 59. The tie rods are provided with air channels 27, so that external connection channels between the two low-pressure piston can be omitted.
  • Both pneumatic systems are separated by the separating flange 28.
  • a translation piston 4 can be seen, which is firmly connected to the low-pressure piston 2.
  • the pressure cylinder 5 includes the oil reservoir 60.
  • the pressure cylinder 5 is fixedly connected to the separating flange 28 and forms together with the separating flange 28, the support bearing of the working piston 29th
  • the low-pressure pistons 2 connected to at least two tie rods 28.
  • the pressure cylinder 5 is advantageously connected fixedly to the intermediate flange of the working cylinder. This requires a high stability and a fast transfer of pressure medium.
  • FIG. 7 shows a representation of a pressure booster and a working cylinder combination, which consists of a combination of the representation according to FIGS. 2 and 6.
  • the transmission piston 4 is fixedly connected to the working piston 29 and extended to the stopper rod 33 and is guided through the pressure cylinder 5 and the low-pressure flange 10 therethrough.
  • the protruding end is provided with an adjustable stop 34. This stop actuates when striking the valve 36, from which the end of the lifting process is acknowledged to a process control.
  • the protective hood 37 avoids a 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 separation flange 28. In the working piston 29, the bolt is sealed on both sides. The bolt is advantageously guided tangentially through the leakage channel 30, whereby a pressure medium mixing is prevented.
  • This anti-rotation pin 38 proves to be advantageous. It can be seen that this can also be used in other pressure translators.
  • the stop allows a precise, adjustable stroke limitation, which is absolutely necessary for example in a label punching.
  • the effort for this is minimal, since most parts are already needed for the pressure intensifier.
  • Advantageously can be replaced by the anti-rotation bolt, the usual complex ancillary equipment.
  • the valve 36 receives its supply energy from the pressure chamber, so that only one signal line is required and the diversion is saved. Without much additional effort can be used by the valve, the pressure booster in an automatic sequence.
  • Figure 8 shows a schematic representation of a pressure booster working cylinder combination.
  • This combination includes a working cylinder comparable to the representation of Figure 6 and a pressure booster comparable to the representation of Figure 7. It can be seen here that the transmission 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 Niederbuchstützflansch 10 as filling and venting stub 40 and closed with a cap 41.
  • the spring 43 sets the pressure medium in the rest position and at start under a pressure which is slightly above that of the free atmosphere. By removing the cap 41, the spring is relaxed and thus allows safe venting and filling. Advantageously, therefore, the spring 43 can be relaxed.
  • the rod flange 39 and the rod end 42 are formed directly as a tool holder and guide.
  • the filling and bleeding nozzle simplifies the filling with liquid pressure medium, the fill level control and during service the bleeding after the entry of air into the hydraulic fluid.
  • the rod flange is also designed as a tool guide, whereby the tool costs are reduced and the tool can be downsized. This is the tool that is to be attached to the intensifier.
  • the pressure medium is pressurized, whereby a seepage of air is prevented.
  • the bias is released by unscrewing the cap.
  • Figure 9 shows the representation of a working cylinder side portion of a pressure booster.
  • the high-pressure medium does not act on the piston but on the rod side.
  • the pressure medium is passed through the piston 29 and exits the rod side.
  • the working piston performs a relative movement to the direction of movement of the printing cylinder 5.
  • the working piston 29 acts pulling in contrast to the figures 6 to 8, in which it acts oppressive.
  • the reversal of the direction of force is basically possible with all pressure intensifiers with working cylinders. This applies in particular to pressure intensifiers, which are already known in the art from the prior art.
  • the pressure medium channel can exit on the piston side in a pushing or rod-like manner.
  • FIG. 10 shows the illustration 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 drawbar 12 is designed as a pure connecting rod without piston. It is also used as a control channel 45. The connecting cylinder 25 is only a pure connection of the piston 2. The suction valves 18 and the pressure valves 19 are installed in the intermediate flange 11. The two pressure cylinders 61, 64 are bounded on the outside by the cylinder tubes 47.
  • the pressure medium which may be compressed air, for example, is fed by the control valve 15 into the cylinder 64 and the cylinder 61.
  • the cylinders 64 and the cylinder 61 collectively compress the air in the cylinder 63 to a little over twice the pressure exiting via the exhaust valve 19a.
  • the control valve 15 is switched.
  • the cylinder 64 is vented via the quick exhaust valve.
  • In the cylinder 62 and the cylinder 63 is fed by the control valve 15 compressed air.
  • the cylinders 62, 63 compress the compressed air present in the cylinder 61 to just over twice the pressure. This compressed air exits via the outlet valve 19b.
  • 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 central pull rod is present, which can also be used as a control line. All flanges can thus be produced in the much cheaper round design.
  • the flange 10 can be designed as a base plate for an ISO standardized base plate valve, which greatly simplifies worldwide service.
  • the quick exhaust valves 46 increase the output by 20-30%.
  • the damping lugs 55 cause a progressive stop, which prolongs the life considerably.
  • inputs and outputs are advantageously connected with valves, so that the volume acting as a pressure cylinder in the compression phase of the pressure medium in the pressure cylinder is connected to an output line for the pressure medium, wherein in the return movement in the relaxation phase of the pressure cylinder forming volume there new pressure medium is sucked.
  • a wiring can take place such that a different volume acts as a pressure cylinder.
  • the upper and lower boundary surfaces are interconnected by a tie rod in the middle of the volumes.
  • a control line can be guided through this pull rod, through which a pressure medium can be conveyed, can be controlled with control valves, which are mounted in the region of the boundary surfaces for connecting the printing cylinder.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Measuring Fluid Pressure (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Discharge Heating (AREA)
  • Actuator (AREA)
  • Punching Or Piercing (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Measurement Of The Respiration, Hearing Ability, Form, And Blood Characteristics Of Living Organisms (AREA)
  • Coupling Device And Connection With Printed Circuit (AREA)
  • Measuring Pulse, Heart Rate, Blood Pressure Or Blood Flow (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)

Claims (11)

  1. Transmetteur de pression (1), dans lequel il se forme une pression dans un cylindre de pression (5) suite à un déplacement d'au moins un piston (2) d'au moins un cylindre (3) sous l'effet de l'application d'une pression, caractérisé en ce que le au moins un piston (2) est relié mécaniquement au cylindre de pression (5), la pression dans le cylindre de pression (5) étant créée par le mouvement du cylindre de pression (5) par rapport au piston de transmission (4), le cylindre de transmission (4) du cylindre de pression (5) ayant une plus petite surface que l'au moins un piston (2) du au moins un cylindre (3), au moins un piston (2) supplémentaire d'au moins un cylindre (3) supplémentaire étant prévu, ce au moins un cylindre supplémentaire (3), de même que le au moins un piston supplémentaire correspondant, ayant la forme d'un cylindre creux, le piston de transmission (4) étant reçu dans le creux cylindrique, le volume du cylindre de pression (5) étant formé par une chambre annulaire, le piston de transmission (4) étant prolongé le long du diamètre intérieur de la chambre annulaire par une tige de traction (12) qui est reliée à un flasque d'appui.
  2. Transmetteur de pression (1) selon la revendication 1, caractérisé en ce que le piston de transmission (4) est muni d'un orifice en direction axiale qui est conçu comme un canal (8) pour le fluide de pression entre le cylindre de pression (5) et le cylindre de travail.
  3. Transmetteur de pression (1) selon l'une des revendications 1 ou 2, caractérisé en ce que les différents cylindres (3) sont séparés les uns des autres par des flasques de séparation (11) qui servent de surfaces d'appui pour les pistons (2) correspondants.
  4. Transmetteur de pression (1) selon l'une des revendications précédentes, caractérisé en ce que la pression est appliquée dans le cylindre (3) par voie pneumatique et en ce que le cylindre de pression (5) est conçu hydraulique, le système pneumatique et le système hydraulique étant séparés l'un de l'autre atmosphériquement par un canal de fuite (30).
  5. Transmetteur de pression (1) selon l'une des revendications 1 à 4, caractérisé en ce que le piston de transmission (4) forme des deux côtés de la surface de piston un cylindre de pression (5), chacun de ces cylindres de pression (5) étant relié via une valve anti-retour (18, 19) à un réservoir (20) de fluide de pression, ainsi qu'à une conduite de sortie pour le fluide de pression, lors du mouvement du piston (2) du cylindre (3) l'un des cylindres de pression (5) comprimant le fluide de pression en direction de la conduite de sortie et l'autre cylindre de pression (5) aspirant le fluide de pression.
  6. Transmetteur de pression (1) selon la revendication 5, caractérisé en ce que les deux cylindres (3) ont la forme d'un cylindre creux avec le piston (2) correspondant, un piston de transmission (4) étant relié aux flasques d'appui des deux côtés par l'intermédiaire de tiges d'appui (12), les tiges d'appui (12) étant guidées à travers les creux cylindriques, deux cylindres de pression (5) étant formés dont à chaque fois un est formé dans la paroi de cylindre sur chacun une face du piston de transmission (4) avec une chambre annulaire.
  7. Transmetteur de pression (1) selon la revendication 5, caractérisé en ce que le piston de transmission (4) est relié à un des pistons (2) des cylindres (3) au moyen d'une tige de traction (12), la tige de poussé s'étendant dans l'ouverture d'une chambre annulaire qui forme avec le piston de transmission (4) un premier cylindre de pression (5), la paroi latérale du piston de transmission (4) formant avec le flasque d'appui (10) et l'autre côté du piston de transmission (4) un deuxième cylindre de pression (5).
  8. Transmetteur de pression (1) selon la revendication 7, caractérisé en ce que pour alimenter le premier cylindre de pression (5) en fluide de pression, il est prévu une valve de surpression (22) dans le piston de transmission (4).
  9. Transmetteur de pression (1) selon l'une des revendications précédentes, caractérisé en ce que plusieurs cylindres de pression (5) sont reliés ensemble du point de vue de leurs pièces mobiles (4, 5).
  10. Transmetteur de pression (1) selon l'une des revendications précédentes, caractérisé en ce qu'un système d'étanchéité (51, 52, 53) est disposé entre la chambre basse pression (50) du au moins un cylindre (3) et la chambre du au moins un cylindre de pression, lequel système se compose d'un premier joint (51), d'une chambre réceptrice (53) et d'un second joint (52), le premier joint (51) étant disposé entre la chambre basse pression et la chambre réceptrice (53) et rendant étanche la chambre basse pression vis-à-vis de la chambre réceptrice (53) en cas de surpression et de plus laissant passante la chambre réceptrice (53) vis-à-vis de la chambre basse pression (50) en cas de surpression, le deuxième joint (52) rendant étanche entre elles la chambre réceptrice (53) et la chambre du au moins un cylindre de pression (5) indépendamment de la pression.
  11. Transmetteur de pression (1) selon l'une des revendications précédentes, caractérisé en ce qu'un matériau amortisseur est disposé sur la surface de butée du piston (2), sur la paroi de cylindre et/ou sur la surface de butée en position finale du piston (2), et en ce qu'un taquet (55) est disposé sur la surface de butée du piston (2), sur la paroi de cylindre et/ou sur la surface de butée en position finale du piston.
EP02701161A 2001-01-05 2002-01-04 Transmetteur de pression Expired - Lifetime EP1423614B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE20100122U DE20100122U1 (de) 2001-01-05 2001-01-05 Druckübersetzer
DE20100122U 2001-01-05
PCT/DE2002/000007 WO2002053920A2 (fr) 2001-01-05 2002-01-04 Transmetteur de pression

Publications (2)

Publication Number Publication Date
EP1423614A2 EP1423614A2 (fr) 2004-06-02
EP1423614B1 true EP1423614B1 (fr) 2006-07-26

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP02701161A Expired - Lifetime EP1423614B1 (fr) 2001-01-05 2002-01-04 Transmetteur de pression

Country Status (6)

Country Link
EP (1) EP1423614B1 (fr)
AT (1) ATE334314T1 (fr)
AU (1) AU2002234494A1 (fr)
DE (4) DE20100122U1 (fr)
PL (1) PL369414A1 (fr)
WO (1) WO2002053920A2 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011111533A1 (de) * 2011-08-31 2013-02-28 Wsengineering Gmbh & Co.Kg Druckerzeuger für eine Zug- oder Pressvorrichtung sowie Zug- oder Pressvorrichtung
CN109799141A (zh) * 2018-05-08 2019-05-24 中国石油天然气股份有限公司 增压装置和试压系统
DE102011111535B4 (de) * 2011-08-31 2020-06-18 WS Wieländer + Schill Engineering GmbH & Co. KG Nietgerät
DE102011123087B3 (de) 2011-08-31 2022-09-08 WS Wieländer + Schill Engineering GmbH & Co. KG Druckerzeuger mit einem Griffstück und einer Zug- oder Pressvorrichtung sowie Werkzeugsystem

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004102010A1 (fr) * 2003-05-13 2004-11-25 Rang Jiao Verin electrique multiplicateur de pression hydraulique
DE202004008541U1 (de) 2004-05-29 2004-08-12 Reiplinger, Roswitha Stanzpresse, insbesondere zur Ablängung und Endenbearbeitung von Flachstabmaterial für Fensterbeschläge
DE102008010383B4 (de) 2007-02-24 2023-01-05 Günter Reiplinger Stanzwerkzeug, insbesondere zur Ablängung und Endenbearbeitung von Flachstabmaterial für Fensterbeschläge
DE202008003948U1 (de) 2008-03-14 2009-04-16 Lischka, Peter Hydropulsvorrichtung
DE102008014152B4 (de) 2008-03-14 2012-09-27 Peter Lischka Hydropulsvorrichtung und Verfahren zur Erzeugung eines zeitvarianten Fluiddrucks mittels einer Hydropulsvorrichtung
DE102010015952B4 (de) * 2010-03-12 2012-01-05 Reiplinger Gmbh & Co. Kg Verfahren zum Stanzen eines Fensterbeschlages sowie Stanze
DE102010016047B4 (de) * 2010-03-19 2014-08-28 Reiplinger Gmbh & Co. Kg Verfahren zum Betreiben einer Stanze
DE202011052463U1 (de) 2011-12-23 2012-01-26 Peter Lischka Hydropulsvorrichtung, insbesondere Innendruckpulser
DE102012021643B4 (de) 2012-11-03 2014-12-24 Peter Lischka Preiswerter Druckübersetzer für hohe Drücke
US9334857B2 (en) 2013-05-02 2016-05-10 The Boeing Company Hydraulic pump
DE102015202273A1 (de) 2015-02-09 2016-08-11 Oskar Frech Gmbh + Co. Kg Druckübersetzervorrichtung und Druckgießmaschinen-Gießaggregat
JP2018084260A (ja) * 2016-11-22 2018-05-31 Smc株式会社 増圧装置
DE102017125902A1 (de) 2017-11-06 2019-05-09 Michael Ludwig Stanze für die Bearbeitung zweier Flachstäbe, die an einem Ende punktförmig miteinander verbunden sind
DE102017125895A1 (de) 2017-11-06 2019-05-09 Michael Ludwig Stanze für die Bearbeitung zweier Flachstäbe, die an einem Ende punktförmig miteinander verbunden sind
DE202018101531U1 (de) 2018-03-20 2019-03-22 Michael Ludwig Stanze für die Bearbeitung zweier Flachstäbe, die an einem Ende punktförmig miteinander verbunden sind

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH378687A (de) * 1959-02-21 1964-06-15 Straumann Inst Ag Druckübertrager
DE1266090B (de) * 1964-10-17 1968-04-11 Wilhelm Sihn Jun K G Pneumatisch-hydraulischer Druckumsetzer
FR1469854A (fr) * 1965-02-23 1967-02-17 Practica A G Dispositif de serrage à commande hydropneumatique
DE2017007A1 (de) * 1970-04-09 1971-10-21 Geisel K Pneumatisch hydraulischer Kolben trieb
DE2625884A1 (de) * 1976-06-09 1977-12-15 Transform Verstaerkungsmasch Verfahren und vorrichtung zum hydropneumatischen erzeugen einer druck- bzw. presskraft
JPS63106401A (ja) * 1986-10-24 1988-05-11 Tokyo Keiki Co Ltd 空液圧変換装置
DE4122204A1 (de) * 1991-07-04 1993-01-07 Weiss Maschf Johann Pneumatisch-hydrostatischer druckuebersetzer
DE4337991A1 (de) * 1993-10-02 1995-04-06 Eduard Lemacher Hydropneumatisches Antriebssystem
JPH1061601A (ja) * 1996-08-14 1998-03-06 Taiyo Ltd 増圧装置
DE29615383U1 (de) * 1996-09-04 1996-11-28 Reiplinger, Günter, 54669 Bollendorf Stanze mit einem c-förmig offenen Stanzschnittwerkzeug zur Herstellung von zwei gegeneinander versetzten Schnitten mit zusätzlicher Lochung oder Prägung von zwei miteinander verbundenen Werkstücken

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011111533A1 (de) * 2011-08-31 2013-02-28 Wsengineering Gmbh & Co.Kg Druckerzeuger für eine Zug- oder Pressvorrichtung sowie Zug- oder Pressvorrichtung
DE102011111535B4 (de) * 2011-08-31 2020-06-18 WS Wieländer + Schill Engineering GmbH & Co. KG Nietgerät
DE102011111533B4 (de) 2011-08-31 2020-06-25 WS Wieländer + Schill Engineering GmbH & Co. KG Druckerzeuger für eine Zug- oder Pressvorrichtung sowie Zug- oder Pressvorrichtung
DE102011123087B3 (de) 2011-08-31 2022-09-08 WS Wieländer + Schill Engineering GmbH & Co. KG Druckerzeuger mit einem Griffstück und einer Zug- oder Pressvorrichtung sowie Werkzeugsystem
DE102011111533C5 (de) * 2011-08-31 2025-12-11 WS Wieländer + Schill Engineering GmbH & Co. KG Druckerzeuger für eine Zug- oder Pressvorrichtung sowie Zug- oder Pressvorrichtung
CN109799141A (zh) * 2018-05-08 2019-05-24 中国石油天然气股份有限公司 增压装置和试压系统
CN109799141B (zh) * 2018-05-08 2021-08-27 中国石油天然气股份有限公司 增压装置和试压系统

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DE10290018D2 (de) 2003-12-04
DE20100122U1 (de) 2001-06-21
DE50207661D1 (de) 2006-09-07
WO2002053920A3 (fr) 2004-03-18
DE10200137B4 (de) 2006-12-07
DE10200137A1 (de) 2002-09-12
PL369414A1 (en) 2005-04-18
EP1423614A2 (fr) 2004-06-02
ATE334314T1 (de) 2006-08-15
AU2002234494A1 (en) 2002-07-16
WO2002053920A2 (fr) 2002-07-11

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