EP1423614B1 - Pressure transformer - Google Patents

Pressure transformer Download PDF

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Publication number
EP1423614B1
EP1423614B1 EP20020701161 EP02701161A EP1423614B1 EP 1423614 B1 EP1423614 B1 EP 1423614B1 EP 20020701161 EP20020701161 EP 20020701161 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.)
Not-in-force
Application number
EP20020701161
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German (de)
French (fr)
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EP1423614A2 (en
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 GMBH & CO.KG
Original Assignee
Reiplinger & Cokg GmbH
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Publication date
Priority to DE20100122U priority Critical
Priority to DE20100122U priority patent/DE20100122U1/en
Application filed by Reiplinger & Cokg GmbH filed Critical Reiplinger & Cokg GmbH
Priority to PCT/DE2002/000007 priority patent/WO2002053920A2/en
Publication of EP1423614A2 publication Critical patent/EP1423614A2/en
Application granted granted Critical
Publication of EP1423614B1 publication Critical patent/EP1423614B1/en
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Anticipated expiration legal-status Critical

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B3/00Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids

Description

  • 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. In this case, 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. With such 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.
  • In the pressure booster, 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.
  • Instead of the one shown in Figure 1, 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.
  • From FR-A-1469854 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. In this hollow cylindrical recording of the connection of the two pistons thus the translation piston is arranged to be movable.
  • DE 43 37 991 A1 shows an arrangement in which, in contrast to the arrangement shown, the translation piston stands still and the translation cylinder is movable against the stationary translation piston.
  • 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.
  • According to the inventive solution according to claim 1, 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.
  • This results in a much more compact design of the pressure booster over the known from the prior art designs. There, the pressure cylinder projects out of the cylinder, into which the pressure is fed. This pressure cylinder is significantly thinner than the other cylinder. The outer dimensions of the component are thus determined essentially by the larger radius of the cylinder, in which the pressure is fed. The space around the thinner pressure cylinder around is given away.
  • In the described embodiments according to the present invention, on the other hand, it proves to be advantageous that the space surrounding the pressure cylinder is used as an additional cylinder space to feed pressure.
  • Due to the design with the annular chamber can be achieved with sufficient stability of the components and high pressure ratios by a corresponding design of the annular chamber. In other embodiments, this can only be done by reducing the piston area of the printing cylinder. If this becomes smaller and smaller, the translation piston becomes more and more unstable, so that in such a construction due to the stability of the components conditionally limits are set regarding the accessibility of pressure ratios.
  • In the embodiment according to claim 2, 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.
  • This can advantageously be avoided that 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.
  • In the embodiment according to claim 3, 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, in that the pistons can then be supported accordingly in order to be able to pass on the movement into the pressure cylinder.
  • In the embodiment according to claim 4, 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.
  • Advantageously, it can be avoided that, in the event of a leak in the hydraulic part, oil can enter the pneumatic part and vice versa.
  • In the embodiment of a pressure booster according to claim 5, 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.
  • Thus, while in conventional printing cylinders after a power stroke of the transmission piston relative to the printing cylinder has to be moved back first, results with the proposed embodiment as an advantage that quasi-continuous pressure medium can be conveyed because two pressure cylinders are present, of which in each direction of movement just one the pressure medium compacted.
  • In the embodiment according to claim 6, 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.
  • As a result, it is advantageously achieved that virtually continuous pressure medium can be conveyed, wherein a high pressure transmission can again be achieved by the embodiment with the annular chambers.
  • In the embodiment of the pressure booster according to claim 7, 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.
  • This is an alternative embodiment for the realization of a pressure intensifier according to claim 6. It can be advantageously placed in a simple manner, all external connections on one side of the printing cylinder.
  • In the embodiment of the pressure booster according to claim 8, a pressure relief valve in the transmission piston is provided for feeding of pressure medium in the first pressure cylinder.
  • As a result, both pressure chambers of the pressure cylinders can advantageously be supplied with pressure medium via an external connection of the pressure booster.
  • In a pressure intensifier according to claim 9, a plurality of printing cylinders are coupled with respect to their moving parts.
  • This allows movements to be synchronized. By configuring the volumes of the printing cylinders, it is possible, for example, to realize in a simple manner the same travel paths of control elements or also certain ratios of control paths of control elements, in which case the volumes are adapted accordingly. By coupling the moving parts, weight loads on the parts to be adjusted then play no role.
  • According to claim 10, 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.
  • As a result, 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.
  • In accordance with claim 11, 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.
  • As a result, the stop is advantageously damped when reaching the end position of the piston relative to the cylinder.
  • It can be seen that the subject matter of claims 10 and 11 can be used meaningfully also in other pressure translators.
  • Below are some drawings to be described. Figure 1 time an embodiment of the prior art. FIGS. 2 and 5 show an embodiment according to the invention. Figures 3, 4 and 6 to 10 show Exemplary embodiments, which do not fall under the wording of the claims, but facilitate the understanding of the invention. It shows in detail:
  • Fig. 1:
    a representation of a pressure intensifier according to the prior art,
    Fig. 2-10:
    Various embodiments of pressure intensifiers, partly with working cylinders.
  • In the following figures, the following components are uniformly provided with the following listed reference numerals:
  • 1
    Pressure intensifier
    2
    Low-pressure piston
    3
    cylinder
    4
    translation piston
    5
    pressure cylinder
    6
    Low pressure port
    7
    Atmospheric pressure opening
    8th
    High pressure passage
    9
    Hochdruckstützflansch
    10
    Niederdruckstützflansch
    11
    Wafer
    12
    Draw bar
    13
    Return port
    14
    cushioning
    15
    control valve
    16
    pilot valve
    17
    Signal vent valve
    18
    suction
    19
    pressure valve
    20
    storage reservoir
    21
    Double check valve
    22
    check valve
    23
    piston rod
    24
    annular channel
    25
    connecting cylinder
    26
    drawbars
    27
    air duct
    28
    separating flange
    29
    working piston
    30
    leak channel
    31
    openings
    32
    support bearings
    33
    stop dancing
    34
    attack
    36
    Valve
    37
    guard
    38
    Verdrehsicherungsbolzen
    39
    control flange
    40
    Filling and bleeding pipe
    41
    cap
    42
    rod end
    43
    feather
    44
    Pressure fluid channel
    45
    control channel
    46
    Quick exhaust valve
    47
    cylinder tube
    50
    Low-pressure chamber
    51
    first seal
    52
    second seal
    53
    receiving chamber
    54
    mother
    55
    nose
    56
    annular chamber
    57
    control valve
    58
    chamber
    59
    Low pressure annular piston
    60
    Oil supply amount
    61
    cylinder
    62
    cylinder
    63
    cylinder
    64
    cylinder
  • FIG. 1 shows a pressure booster 1. In the 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. It can also be seen a low pressure port 6, in which the pressure is fed to move 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 booster with two low-pressure pistons 2, which are firmly connected to one another by the pressure cylinder 5. By using 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 Niederdruckstützflansch 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 Zugstangenverlängerung 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.
  • Furthermore, 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. In the case of a pressureless low-pressure chamber 50, 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. By 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 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 Zugankerverlängerung 12. On both inner sides of the low-pressure flanges 10 elastic stop damping 14 are installed. To extend the progressive path of the stop without requiring additional space, 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.
  • 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 double use by two low-pressure pistons 2 and the narrow, used on both sides of the translation piston 4 bring a space reduction by about 70% and a more economical use of low-pressure medium by about 30%.
  • 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 RückprallefFeh-t, which has a higher stroke frequency and life extension result.
  • By the Oszilliersteuerung with the pilot valve 16 in combination with the signal vent valve 17, a standstill in a dead switching point is avoided.
  • 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. In the transmission piston 4, 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. By 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.
  • It can be seen that such 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. In this case, 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.
  • By the pressurization of the control valve 57, 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. At the same time 18 pressure medium is sucked into the chamber 58 via the suction valve. After touching the low-pressure piston 2 with the actuating plunger of the control valve 57, this is switched abruptly against the magnetic holding force. The direction of movement of the transmission piston 4 changes. 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. By touching the low-pressure piston 2 with the control valve 57, 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 Anflanschmöglichkeit without sacrificing space savings or pressure increase by the multiple drive concept.
  • In the illustrated control, it proves to be particularly advantageous that the control valve 57 is formed as a pulse valve. This is integrated into the intermediate flange 11, whereby Um.steuerventile can be avoided with the necessary line expense.
  • In the illustration of Figure 5, a pressure booster can be seen, which corresponds to the essential principles of the representation of Figure 3. As an essential difference is to be seen that here two impression cylinder 5 are present. 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.
  • Furthermore, 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
  • Furthermore, there is a leakage channel 30 through which the low-pressure part is atmospherically separated from the hydraulic part.
  • Furthermore, again a low-pressure connection 6 can be seen for the pressure medium and openings 31 which connect the space of the cylinder behind the working volume of the piston 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 pistons 2 connected to at least two tie rods 28. As a result, no additional lines are required for the air channels, since 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 connected fixedly to the intermediate flange of the working cylinder. This requires a high stability and a fast transfer of pressure medium. Furthermore, it proves to be advantageous that results in a precise and stable guidance of the working piston 29 through the support bearing 32. Through the leak channel 30 a secure print media separation is achieved. In particular, therefore, their mixing is prevented.
  • 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 difference to the two figures mentioned is that 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.
  • In the embodiment shown, 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 Niederdruckstützflansch 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.
  • By the spring, 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 difference to the representations of FIGS. 6 to 8 here is that the high-pressure medium does not act on the piston but on the rod side. In the channel 44, 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. Depending on the working direction requirement, 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. After touching the piston 2 with the pilot valve 16, 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. After touching the signal venting 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.
  • The applicant is in connection with the figure 10, a pressure intensifier known, which is complex in the production and the power is lower. This is due to the existing there four outer tie rods and consequent more expensive Vierkantflanschbauweise. The exhaust air is dissipated by the working valve, which makes the system slow. The stopper dampenings are not progressive, as is the case with the nose 55 in the present invention.
  • In the proposed embodiment, it proves to be advantageous that 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.
  • So here it is a pressure booster with multiple cylinders in which pistons are movable, wherein at a pressurization of the piston at least one of the piston forms on its back with the cylinder wall another cylinder which acts as a pressure cylinder in which the pressure medium is compressed ,
  • To this end, 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. Advantageously, as shown in FIG. 10, in this relaxation phase of the one volume, 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. Advantageously, 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.

Claims (11)

  1. Pressure transformer (1) in which the movement- resulting from pressurization - of at least one piston (2) in at least one cylinder (3) causes pressure to be built up in a pressure cylinder (5),
    characterised in that the at least one piston (2) is mechanically connected with the pressure cylinder (5), the movement of the pressure cylinder (5) relative to the transformer piston (4) causing pressure to be built up in the pressure cylinder (5), said transformer piston (4) in the pressure cylinder (5) having a smaller surface area than the at least one piston (2) in the at least one cylinder (3), there being provided at least one further piston (2) in at least one further cylinder (3), this at least one further cylinder (3) and the at least one piston (2) belonging thereto having the shape of a hollow cylinder, and the transformer piston (4) being arranged in the hollow cylindrical recess; the volume of the pressure cylinder (5) is formed by an annular chamber, along the interior diameter of which the transformer piston (4) is extended by a connecting rod (12) that is connected with a supporting flange (10).
  2. Pressure transformer (1) according to claim 1,
    characterised in that the transformer piston (4) has an axial hole configured as a channel (8) for the pressure medium between the pressure cylinder (5) and the working cylinder.
  3. Pressure transformer (1) according to claims 1 or 2,
    characterised in that the individual cylinders (3) are separated by separating flanges (11) that act as supporting surfaces for the respective pistons (2).
  4. Pressure transformer (1) according to one of the claims 1 to 3,
    characterised in that the specified pressure in the cylinders (3) is effected pneumatically and that the pressure cylinder (5) is configured hydraulically, the pneumatic and hydraulic systems being atmospherically separated from each other by a leakage channel (30).
  5. Pressure transformer (1) according to one of the claims 1 to 4,
    characterised in that the transformer piston (4) forms a pressure cylinder (5) on both sides of the piston surface, each of these pressure cylinders (5) being connected via a non-return valve (18, 19) with a supply (20) of the pressure medium and with a dispensing line for the pressure medium; on movement of the pistons (2) in the cylinders (3), one of the pressure cylinders (5) compresses the pressure medium towards the dispensing line and the other pressure cylinder (5) draws in pressure medium.
  6. Pressure transformer (1) according to claim 5,
    characterised in that both cylinders (3), together with the pistons (2) belonging thereto, are configured as hollow cylinders; a transformer piston (4) is connected at each end with supporting flanges (10) by means of supporting rods (12) that pass through the hollow cylindrical recesses; two pressure cylinders (5) are formed, one on each side of the transformer piston (4) with an annular chamber in the cylinder wall.
  7. Pressure transformer (1) according to claim 5,
    characterised in that the transformer piston (4) is connected by means of a connecting rod (12) with one of the pistons (2) in the cylinders (3), said connecting rod (12) being accommodated in the opening of an annular chamber which, together with the transformer piston (4), forms a first pressure cylinder (5); the side wall of the transformer piston (4) together with the supporting flange (10) and the other side of the transformer piston (4) forms a second pressure cylinder (5).
  8. Pressure transformer of claim 7,
    characterised in that, for supplying pressure medium to the first pressure cylinder (5), the transformer piston (4) is provided with a pressure relief valve (22).
  9. Pressure transformer according to one of the preceding claims,
    characterised in that a plurality of pressure cylinders (5) are coupled with each other in respect of their movable parts (4, 5).
  10. Pressure transformer (1) according to one of the preceding claims,
    characterised 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), said sealing system consisting of a first seal (51), a receiving chamber (53) and a second seal (52); the first seal (51) is fitted between the low-pressure chamber (50) and the receiving chamber (53) and performs a sealing function when the pressure in the low-pressure chamber (50) is higher than in the receiving chamber (53); when the pressure in the receiving chamber (53) is higher than in the low-pressure chamber (50), this seal does not perform a sealing function; the second seal (52) seals off the receiving chamber (53) from the chamber of the at least one pressure cylinder (5) irrespective of the pressure conditions.
  11. Pressure transformer (1) according to one of the preceding claims,
    characterised in that a damping material (14) is applied to that surface of the piston (2) that contacts the cylinder wall and/or to that surface of the piston (2) that makes contact when the piston is in its end position, and that a projection (55) is provided on that surface of the piston (2) that contacts the cylinder wall and/or on that surface of the piston that makes contact when the piston is in its end position.
EP20020701161 2001-01-05 2002-01-04 Pressure transformer Not-in-force EP1423614B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE20100122U 2001-01-05
DE20100122U DE20100122U1 (en) 2001-01-05 2001-01-05 Pressure translator
PCT/DE2002/000007 WO2002053920A2 (en) 2001-01-05 2002-01-04 Pressure transformer

Publications (2)

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

Family

ID=7951225

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20020701161 Not-in-force EP1423614B1 (en) 2001-01-05 2002-01-04 Pressure transformer

Country Status (6)

Country Link
EP (1) EP1423614B1 (en)
AT (1) AT334314T (en)
AU (1) AU2002234494A1 (en)
DE (4) DE20100122U1 (en)
PL (1) PL369414A1 (en)
WO (1) WO2002053920A2 (en)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
DE102011111533A1 (en) * 2011-08-31 2013-02-28 Wsengineering Gmbh & Co.Kg Pressure generator for a pulling or pressing device and pulling or pressing device
DE102011111535B4 (en) * 2011-08-31 2020-06-18 WS Wieländer + Schill Engineering GmbH & Co. KG Riveting tool

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WO2004102010A1 (en) * 2003-05-13 2004-11-25 Rang Jiao A hydraulic intensifier electromotion cylinder
DE202004008541U1 (en) 2004-05-29 2004-08-12 Reiplinger, Roswitha Punching press, in particular for cutting and finishing flat bar material for window fittings
DE202008003948U1 (en) 2008-03-14 2009-04-16 Lischka, Peter Hydropulse device
DE102008014152B4 (en) 2008-03-14 2012-09-27 Peter Lischka Hydropulse device and method for generating a time-variant fluid pressure by means of a hydraulic pulse device
DE102010015952B4 (en) * 2010-03-12 2012-01-05 Reiplinger Gmbh & Co. Kg Method for punching a window fitting and punch
DE102010016047B4 (en) * 2010-03-19 2014-08-28 Reiplinger Gmbh & Co. Kg Method for operating a punch
DE202011052463U1 (en) 2011-12-23 2012-01-26 Peter Lischka Hydropulsvorrichtung, in particular internal pressure pulse
DE102012021643B4 (en) 2012-11-03 2014-12-24 Peter Lischka Inexpensive pressure booster for high pressures
US9334857B2 (en) 2013-05-02 2016-05-10 The Boeing Company Hydraulic pump
DE102015202273A1 (en) * 2015-02-09 2016-08-11 Oskar Frech Gmbh + Co. Kg Pressure translator device and die casting machine
JP2018084260A (en) * 2016-11-22 2018-05-31 Smc株式会社 Booster
DE102017125895A1 (en) 2017-11-06 2019-05-09 Michael Ludwig Punch for machining two flat bars, which are connected point-like at one end
DE102017125902A1 (en) 2017-11-06 2019-05-09 Michael Ludwig Punch for machining two flat bars, which are connected point-like at one end
DE202018101531U1 (en) 2018-03-20 2019-03-22 Michael Ludwig Punch for machining two flat bars, which are connected point-like at one end

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011111533A1 (en) * 2011-08-31 2013-02-28 Wsengineering Gmbh & Co.Kg Pressure generator for a pulling or pressing device and pulling or pressing device
DE102011111535B4 (en) * 2011-08-31 2020-06-18 WS Wieländer + Schill Engineering GmbH & Co. KG Riveting tool
DE102011111533B4 (en) 2011-08-31 2020-06-25 WS Wieländer + Schill Engineering GmbH & Co. KG Pressure generator for a pulling or pressing device and pulling or pressing device

Also Published As

Publication number Publication date
DE10200137A1 (en) 2002-09-12
AT334314T (en) 2006-08-15
DE10290018D2 (en) 2003-12-04
AU2002234494A1 (en) 2002-07-16
DE20100122U1 (en) 2001-06-21
DE50207661D1 (en) 2006-09-07
PL369414A1 (en) 2005-04-18
WO2002053920A2 (en) 2002-07-11
WO2002053920A3 (en) 2004-03-18
DE10200137B4 (en) 2006-12-07
EP1423614A2 (en) 2004-06-02

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