EP2365888B1 - Multiplicateur de pression et ensemble de coulée sous pression - Google Patents

Multiplicateur de pression et ensemble de coulée sous pression Download PDF

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Publication number
EP2365888B1
EP2365888B1 EP09795981A EP09795981A EP2365888B1 EP 2365888 B1 EP2365888 B1 EP 2365888B1 EP 09795981 A EP09795981 A EP 09795981A EP 09795981 A EP09795981 A EP 09795981A EP 2365888 B1 EP2365888 B1 EP 2365888B1
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EP
European Patent Office
Prior art keywords
pressure booster
valve
piston
pressure
valve seat
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Active
Application number
EP09795981A
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German (de)
English (en)
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EP2365888A2 (fr
Inventor
Daniel Hauser
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Buehler Druckguss AG
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Buehler Druckguss AG
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Publication of EP2365888A2 publication Critical patent/EP2365888A2/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D17/00—Pressure die casting or injection die casting, i.e. casting in which the metal is forced into a mould under high pressure
    • B22D17/20—Accessories: Details
    • B22D17/32—Controlling equipment
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D17/00—Pressure die casting or injection die casting, i.e. casting in which the metal is forced into a mould under high pressure
    • B22D17/20—Accessories: Details
    • B22D17/2015—Means for forcing the molten metal into the die
    • B22D17/2069—Exerting after-pressure on the moulding material
    • 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
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers

Definitions

  • the invention relates to a pressure intensifier according to the preamble of claim 1, in particular a pressure booster in drive means for die casting machines. Furthermore, the invention relates to an arrangement for die casting with such a pressure booster and a working or casting cylinder.
  • the pressure booster can also be used in drive devices for presses or other machines.
  • Pressure intensifier with a pressure booster piston and a check valve integrated therein or with an external bypass check valve have long been known and in use. Such a check valve prevents the backflow of hydraulic medium from a high-pressure chamber of a consumer to the piston chamber of the pressure booster.
  • a pressure booster with a built-in pressure intensifier piston check valve is for example from the DE 1 949 360 A known.
  • the known solutions are characterized by a disabled flow cross-section and relatively high production costs.
  • the spring preload usually used in the check valve is also at risk of failure.
  • WO 2006/042508 is described a pilot operated, lockable check valve, which is not integrated into the pressure booster, but is designed as an external bypass device between the pressure booster and the casting cylinder.
  • the Printer Overloader is characterized by a compact and at the same time simple construction. This solution is also favorable in terms of flow.
  • the inventive check valve or check valve allows comparatively large flow cross-sections in the open position. The casting facilities can thus be operated more dynamically and efficiently.
  • the mentioned pressure booster piston may preferably be configured as a stepped piston, which essentially consists of a piston part accommodated in a cylinder and a piston rod connected coaxially therein with a smaller diameter than the piston part.
  • the cylinder is then closed in the region of the piston part facing end side and forms with this a "piston chamber" designated working space.
  • the cylinder in the region of the piston rod before an annular working space. This working space is referred to below as the annulus of the pressure booster.
  • the pressure booster piston may be formed on a front side facing the valve seat as a valve cone with a sealing surface. Together with a valve seat arranged on the corresponding sealing surface, a seat valve can be formed. The pressure booster piston can thus rest tightly against the valve seat in a closed position.
  • valve seat is preferably limitedly displaceable from an initial position in the axial direction. This allows in a first step, a closing stroke of the pressure booster piston for closing the check valve or check valve, while in a further step in the effective Working stroke of the pressure booster piston, the valve seat is moved together with the pressure booster piston.
  • valve seat has, for example, a conical sealing surface in the region of the end face facing the pressure booster piston, on which the preferably complementary valve cone of the pressure booster piston rests flat in the blocking position.
  • valve seat In principle, it is possible to hold the valve seat in an initial position using mechanical spring means for generating a biasing force. However, it may be particularly advantageous if hydraulic means are provided, by means of which the valve seat can be hydraulically held in its initial position.
  • the hydraulic means can advantageously produce a restoring force with which a displaced valve seat can automatically return to its original position. With the exception of the valve seat, no further moving mechanical components are required with this arrangement. The flow opening of the valve body can thus remain free of mechanical installations. As a result, the reliability and mechanical reliability, as well as the life of the pressure booster can be increased. Hydraulic positioning can additionally reduce the bounce of the valve seat when the pressure translator piston is hit hard against the valve seat.
  • the valve seat can be equipped with an annular space which is connected without pressure to the tank. This annulus of the valve seat However, it can also be connected to a pressure source. The pressure effect in the annulus must keep the valve seat against the flow force of the main media flow in the basic position.
  • the valve seat is configured such that the hydraulically effective surfaces on the valve seat, formed by, for example, an annular surface, leads to a force effect of the valve seat on a stroke stop facing the pressure booster piston.
  • the valve seat may be designed so that a ratio of the annular surface of the pressure translator piston side facing the valve seat to the annular surface of the pressure booster piston side facing away from the valve seat, so that in the normal operating condition of the pressure booster, the valve seat in the direction of the pressure booster piston and / or in the Starting position is biased.
  • the annular surfaces are dimensioned such that the resultant force from the pressure of the side facing the pressure booster piston side of the valve seat, and the corresponding annular surface is greater than the resultant force from the pressure of the pressure booster piston side facing the valve seat with the corresponding annular surface.
  • valve seat and / or the pressure booster may have a limiting means which limits the stroke of the valve seat in the pressure booster.
  • the limiting means may for example be an annular collar arranged on the outer wall of the valve seat, which cooperates with an annular groove of the pressure booster and thus limits the stroke of the valve seat in the pressure booster in a robust, simple and cost-effective construction.
  • the pressure booster piston may have a preferably axial bore, via which a piston chamber with a battery directly or indirectly connected or connectable.
  • This embodiment allows a particularly generous and therefore low-loss sizing of the holes, which supply the piston chamber of the pressure booster with hydraulic pressure. This allows a very dynamic response of the pressure booster piston.
  • Such a pressure booster piston is easy to produce. Furthermore, a particularly safe operation and a favorable flow guidance are possible with this arrangement.
  • the bore may be configured as a blind hole, wherein the bore extending in the axial direction, starting from the piston-chamber-side end of the pressure booster piston.
  • the bore cross section can be comparatively large and, for example, reach between 25% and 50% of the rod cross section.
  • the bore does not necessarily have to have a constant diameter over its entire length.
  • the bore may also have, for example, a conical or a tapered by a different shape insertion section, which is arranged at the piston chamber side end and adjoins the direction of the piston rod in a bore portion with a constant diameter.
  • the pressure booster piston may have at least one passage extending transversely with respect to the axial direction, in particular in the form of a bore.
  • the passage bore may be inclined at a right angle or at any inclination angle to the longitudinal center axis.
  • the at least one passage can be arranged in the region of the valve seat facing the end of the pressure booster piston. It is particularly advantageous if several, preferably uniformly distributed over the circumference passages are provided.
  • the passages allow a connection of the bore with an inflow space of the check valve or check valve. These passage holes open directly into the inflow space of the check valve or check valve without affecting the sealing surface of the pressure booster piston.
  • the triggering of the pressure booster piston from a starting position on the piston-side stop in a working position with a closed seat valve can be actuated by a switchable pressure booster Zuschaltventil the annulus of the pressure booster.
  • the pressure booster can be designed so that a closing stroke of the pressure booster piston is executable to close the check valve or check valve.
  • the closing stroke of the pressure booster piston forms the valve opening of the check valve or check valve.
  • a movement within the closing stroke is understood to mean that the pressure booster piston moves in the direction of the working cylinder connected downstream of the pressure booster, but that due to the still open check valve, no additional pressure is generated in the piston chamber of the working cylinder.
  • Another aspect of the invention relates to an arrangement for die casting with the previously described pressure booster.
  • the arrangement further comprises a working cylinder, which is connected to the pressure increase in the piston chamber of the working cylinder with the working cylinder.
  • Working cylinder, pressure booster piston and valve seat of the pressure booster can be aligned coaxially with each other.
  • the annular space of the pressure booster can be connected via a connecting line with the annular space of the working cylinder such that the respective annular spaces can be acted upon by means of an annular space valve with a pressure bias.
  • This has the advantage that both the working piston as well as the pressure booster can be influenced in its respective mode of action in a wide range of applications.
  • the discharge pressure of the pressure booster i. the piston pressure in the working cylinder is lowered by the pressure at the annulus of the pressure booster.
  • the force effect of the working cylinder is reduced by the pressure in the annular space of the working cylinder. If both influences interact together, the force effect of the working piston is much more pronounced, since the annular space pressure at the pressure booster also has a lowering effect on the piston pressure of the working cylinder.
  • the arrangement may have as a hydraulic energy source a pressure accumulator.
  • This accumulator can be connected via a line to the inflow space of the check valve or check valve.
  • a further pressure medium source for example in the form of a hydraulic pump, a hydraulic medium or at most be removed.
  • a connecting valve for controlling the annular space of the pressure booster is further arranged in the mentioned connection line.
  • the connecting line between the Zuschaltventil and annulus valve can via a feed valve with the hydraulic energy source connected or connectable.
  • the connecting line can be further connected or connectable between the connecting valve and annular space valve by means of a differential valve with the inflow space of the check valve or check valve.
  • the annular space of the pressure booster, the annular space of the working cylinder and the inflow space of the check valve can be connected to each other via lines, that a return movement of the working piston, the valve seat and the pressure booster piston of the pressure booster via a valve assembly containing feed valve, Zuschaltventil and tank valve in a simple way and can be brought about.
  • This refinement also has the advantage that the return movement of the working piston, of the valve seat and of the pressure booster piston can be brought about in a simple manner purely hydraulically via a valve arrangement containing an open feed valve, an open switch valve and a closed tank valve. Particularly commonly used actuating rods omitted, which are on the one hand default and reduce the flow of the check valve or check valve.
  • Another aspect of the invention relates to a pressure booster for increasing the pressure in a piston chamber of a working cylinder, wherein a pressure booster piston together with a valve seat form a pressure booster.
  • FIG. 1 shows a designated pressure intensifier 1, which can be used to increase the pressure in a piston chamber of a (not shown here) working cylinder.
  • a pressure booster can be installed, for example, in a die casting machine or a press.
  • FIG. 1 Various lines are provided for integration into an arrangement for a die casting machine.
  • FIG. 1 are the respective connections for supplying and discharging a hydraulic medium simplified indicated by dashes.
  • approximately annular inflow space for example, two connections to the pressure medium supply can be seen.
  • the individual interfaces and the connected components are in the following FIGS. 2 to 6 shown and explained.
  • the printer translator 1 includes a pressure booster piston 4, which consists of a piston part and a coaxial thereto adjoining piston rod.
  • the piston part has a larger diameter than the piston rod and defines on one end face the piston chamber designated 2.
  • the annular space 3 of the printer translator On the other side of the piston part is the annular space 3 of the printer translator.
  • a in the axial direction in the pressure translator housing slidably disposed valve seat 7 recognizable.
  • This in FIG. 1 only schematically illustrated pressure booster housing may be composed of several cylinder sections.
  • the locking or non-return valve which is integrated in the pressure intensifier and denoted by 6, is formed by the mutually movable pressure translating pistons 4 and valve seat 7.
  • the pressure booster piston 4 and the valve seat 7 have sealing surfaces 25 and 26.
  • the pressure booster piston 4 is formed at the valve seat 7 facing end side, apparently as a valve cone. This valve cone forms a seat valve together with the valve seat 7. In the closed position, the blocking or check valve brings about a blockage of the hydraulic fluid connection between the flow opening designated 8 and the inflow space 27 (cf. Fig. 4 and 6 ).
  • the pressure booster piston has a bore 5 extending in the axial direction.
  • this supply bore 5 has an approximately conical insertion section in the region of the piston chamber-side end face, to which a section with an approximately constant diameter adjoins.
  • the bore 5 is designed as a blind hole; one or more through holes 21 arranged transversely to the axial direction serve for the hydraulic connection. These through bores 21 can be arranged at any desired angle to the axial direction, here by way of example 60 °. They connect the blind bore 5 in the pressure booster piston 4 with the inflow space 27 of the check valve 6.
  • the valve seat 7 consisting of a single component has a smaller outer diameter on the side of the sealing surface 26 and a larger outer diameter on the side facing the outlet. These two different diameters form a hydraulically effective annular surface, which leads via a pressure difference to an axial force action in the direction of the basic position.
  • this annular surface is connected to the tank. The acting on the remaining surfaces higher operating pressure then causes the return force on this area difference to keep the valve seat in the normal position.
  • a shoulder 33 adjoining this annular surface serves to limit the stroke.
  • FIG. 2 shows the printer translator 1 in an assembly for die casting.
  • This arrangement has as a consumer via a working cylinder 12 in which a working piston 23 is slidably disposed.
  • the arrangement has a hydraulic energy source 10, for example, an accumulator, which is connected via a line which is connected to the inflow space 27 of the check valve or check valve.
  • the hydraulic energy source is connected to another working space of the arrangement.
  • the line after an accumulator-Zuschaltventil 11 also open into the piston chamber 2 of the pressure booster 1.
  • the hydraulic energy source 10 is connected via the accumulator-Zuschaltventil 11 and the check valve or check valve 6 with the working cylinder 12.
  • the flow conditions in the accumulator-Zuschaltventil 11, the check valve or check valve 6 and the valve seat 7 thereby influence the maximum flow rate of the hydraulic medium.
  • the pressure booster piston 4 is executed at the piston rod side end as a valve cone of the check valve or check valve 6.
  • the valve seat 7 of the check valve 6 is axially displaceable, so that the pressure booster 1 together with the valve seat 7, the working pressure at the consumer, i. can increase in the cylinder 12.
  • valve seat 7 Due to the previously mentioned hydraulic operative connection between the valve seat 7 and the connected via a hydraulic line to the tank T 1 annular surface for the surface difference at the valve seat keeps the valve seat 7 even at very high flow rate safely in the normal position.
  • the flow opening 8 of the valve seat 7 can thereby remain free of mechanical installations, which increases the flow rate and the mechanical reliability of the construction.
  • the hydraulic positioning additionally reduces the bounce of the valve seat during hard impact of the pressure booster piston 4 on the valve seat 7, since in contrast to the mechanical retention a defined force counteracts the bouncing of the valve seat 7.
  • FIG. 2 In addition to the already mentioned tank T 1 are in FIG. 2 two further tanks (T, T 2 ) recognizable.
  • the annular space 3 of the pressure booster is connected via a connecting line 18 with the annular space 22 of the working cylinder 12. This ensures that the respective annular spaces 3 and 22 are acted upon by means of an annular space valve 15 with a compressive bias.
  • This pressure bias in the connection line 18 can be formed by means of a pressure divider by the hydraulic valves 15 and 17 or generated by a separate pressure relief or pressure reducing valve.
  • a connection valve 13 for driving the annular space 3 is further arranged.
  • the connecting line 18 between the Zuschaltventil 13 and annular space valve 15 is then connected via a feed valve 17 with a hydraulic power source P.
  • the pressure feed can take place both from a second pressure accumulator or, in the extreme case, also from the accumulator 10 via the valves 11 and 16. This minimal variant is energetic but not optimal.
  • a "differential valve" designated switching valve 16.
  • the return of the working piston 23, the valve seat 7 and the pressure booster piston 4 is effected by pressure feed via a feed valve 17, with an open Zuschaltventil 13 and 14 open tank valve.
  • the annulus valve 15 and the differential valve 16 must be closed.
  • FIGS. 3 to 6 For a better understanding of the operation of the new pressure booster 1 show the FIGS. 3 to 6 the different sequences of a casting process.
  • the basic pouring process is known per se to the person skilled in the art and has already been implemented in conventional casting arrangements for some time. Starting point is the in FIG. 2 illustrated basic position.
  • both the pressure booster piston 4 By opening the valves 13, 14 and 17, both the pressure booster piston 4, the valve seat 7 and the casting piston 23 moved to the normal position. The remaining hydraulic valves remain closed.
  • a first ancestor of the casting piston 23 takes place at a slow speed.
  • the casting piston 23 moves after opening the valves 11 and 16 energy-saving with initially reduced casting force in the direction of a. All other valves remain closed during this ancestor phase.
  • valves 11 and 15 By opening the valves 11 and 15, a fast ancestor of the casting piston then takes place with full casting force. All other valves are closed.
  • the pressure booster piston 5 By opening the valve 13, the pressure booster piston 5 is set in motion.
  • the check valve 6 is closed. This position is in FIG. 4 shown.
  • the valve cone of the pressure booster piston 4 abuts on the valve seat 7.
  • the conical sealing surface of the valve seat 7 is in the closed position, as is apparent, flat on also conical valve cone portion of the pressure booster piston 4, whereby an advantageous and practically leak-free barrier can be achieved.
  • the valves 11 and 13 remain open in this step.
  • the casting piston is moved further forward to release the casting from the solid mold half.
  • the connection valve 13 of the pressure booster is closed.
  • the pressure booster piston 4 stops.
  • the valve seat 7 can move further forward in the a direction, which again creates a valve opening between the pressure booster piston 4 and the valve seat 7, i. the check valve 6 is now in an open position again.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Braking Systems And Boosters (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (20)

  1. Multiplicateur de pression (1) pour augmenter la pression dans un espace de piston (20) d'un cylindre de travail (12), comprenant un piston de multiplicateur de pression (4), caractérisé en ce que le multiplicateur de pression (1) présente un siège de soupape (7), le piston de multiplicateur de pression (4) coopérant avec le siège de soupape (7) pour former une soupape d'arrêt ou un clapet anti-retour (6).
  2. Multiplicateur de pression (1) selon la revendication 1, caractérisé en ce que le piston de multiplicateur de pression (4) est réalisé au niveau d'un côté frontal tourné vers le siège de soupape (7) sous forme de cône de soupape avec une surface d'étanchéité (25) qui coopère avec une surface d'étanchéité (26) disposée sur le siège de soupape (7) et qui forme une soupape à siège.
  3. Multiplicateur de pression (1) selon la revendication 1 ou 2, caractérisé en ce que le siège de soupape (7) peut être déplacé dans la direction axiale (a) depuis une position de départ.
  4. Multiplicateur de pression (1) selon la revendication 3, caractérisé en ce que le siège de soupape (7) est configuré de telle sorte que les surfaces hydrauliquement actives sur le siège de soupape (7) provoquent une application de force du siège de soupape (7) sur une butée de levage tournée vers le piston de multiplicateur de pression (4).
  5. Multiplicateur de pression (1) selon la revendication 3, caractérisé en ce que le siège de soupape (7), dans l'état de fonctionnement normal, est précontraint au moyen d'un moyen de précontrainte séparé dans la direction du piston de multiplicateur de pression (4).
  6. Multiplicateur de pression (1) selon l'une quelconque des revendications 3 à 5, caractérisé en ce que le siège de soupape (7) et/ou le multiplicateur de pression (1) présentent un moyen de limitation qui limite là course du siège de soupape (7) dans le multiplicateur de pression (1).
  7. Multiplicateur de pression (1) selon la revendication 6, caractérisé en ce que le moyen de limitation est un collet annulaire (33) disposé sur la paroi extérieure du siège de soupape (7), qui coopère avec une rainure annulaire (30) du multiplicateur de pression (1) et qui limite ainsi la course du siège de soupape (7) dans le multiplicateur de pression (1).
  8. Multiplicateur de pression (1) selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le piston de multiplicateur de pression (4) présente un alésage par le biais duquel un espace de piston (2) est connecté ou peut être connecté directement ou indirectement à un accumulateur (10).
  9. Multiplicateur de pression (1) selon la revendication 8, caractérisé en ce que l'alésage (5) est réalisé sous forme de trou borgne, l'alésage (5) s'étendant dans la direction axiale (a) depuis l'extrémité du piston de multiplicateur de pression (4) du côté de l'espace de piston.
  10. Multiplicateur de pression (1) selon la revendication 8 ou 9, caractérisé en ce que pour la connexion hydraulique de la cavité formée par l'alésage (5) avec l'accumulateur (10) et/ou avec le cylindre de travail (12), le piston de multiplicateur de pression (4) présente au moins un passage (21) s'étendant transversalement par rapport à la direction axiale.
  11. Multiplicateur de pression (1) selon l'une quelconque des revendications 8 à 10, caractérisé en ce que l'au moins un passage (21) permet une connexion de l'alésage (5) à un espace d'afflux (27) de la soupape d'arrêt (6).
  12. Multiplicateur de pression (1) selon l'une quelconque des revendications 1 à 11, caractérisé en ce que pour actionner le piston de multiplicateur de pression (4) d'une position de départ dans une position de travail avec la soupape d'arrêt fermée (6), une soupape de raccordement (13) du multiplicateur de pression connectée à un espace annulaire (3) du multiplicateur de pression (1) peut être actionnée.
  13. Multiplicateur de pression (1) selon l'une quelconque des revendications 1 à 12, caractérisé en ce que le multiplicateur de pression (1) est réalisé de telle sorte qu'avant la fermeture de la soupape d'arrêt ou du clapet anti-retour (6), une course de fermeture du piston de multiplicateur de pression (4) peut être effectuée.
  14. Multiplicateur de pression (1) selon l'une quelconque des revendications 1 à 13, caractérisé en ce qu'une conduite (18) avec une soupape hydraulique (13) commandée ou commandable électriquement relie un espace annulaire (3) du piston de multiplicateur de pression (4) à une soupape d'espace annulaire (15) allant à un réservoir (T2) ou à une précontrainte de pression dans la conduite (18).
  15. Agencement de coulée sous pression comprenant un cylindre de travail (12) et un multiplicateur de pression (1) selon l'une quelconque des revendications 1 à 14, dans lequel le multiplicateur de pression (1) est connecté au cylindre de travail (12) pour augmenter la pression dans l'espace de piston (20) du cylindre de travail (12).
  16. Agencement selon la revendication 15, caractérisé en ce que le cylindre de travail (12) ainsi que le piston de multiplicateur de pression (4) et le siège de soupape (7) du multiplicateur de pression (1) sont orientés coaxialement les uns aux autres.
  17. Agencement selon la revendication 15 ou 16, caractérisé en ce qu'un espace annulaire (3) du multiplicateur de pression (1) peut être connecté par le biais d'une conduite de liaison (18) à un espace annulaire (22) du cylindre de travail (22) de telle sorte que les espaces annulaires respectifs (3, 22) puissent être sollicités au moyen d'une soupape d'espace annulaire (15) avec une précontrainte de pression.
  18. Agencement selon la revendication 17, caractérisé en ce que dans la conduite de liaison (18) est en outre disposée une soupape de raccordement (13) pour la commande de l'espace annulaire (3) du multiplicateur de pression (1), et en ce que la conduite de liaison (18) entre la soupape de raccordement (13) et la soupape d'espace annulaire (15) peut être connectée par le biais d'une soupape d'alimentation (17) à une source d'énergie hydraulique (P).
  19. Agencement selon la revendication 17 ou 18, caractérisé en ce que la conduite de liaison (18) entre la soupape de raccordement (13) et la soupape d'espace annulaire (15) peut être connectée au moyen d'une soupape de commutation (16) à un espace d'afflux (27) de la soupape d'arrêt ou du clapet anti-retour (6).
  20. Agencement selon la revendication 19, caractérisé en ce que l'espace annulaire (3) du multiplicateur de pression (1), l'espace annulaire (22) du cylindre de travail (12) et l'espace d'afflux (27) de la soupape d'arrêt ou du clapet anti-retour (6) sont connectés les uns aux autres par le biais de conduites (18), de telle sorte qu'un mouvement de retour du cylindre de travail (12), du siège de soupape (7) et du piston de multiplicateur de pression (4) du multiplicateur de pression (1) puisse être réalisé par le biais d'un agencement de soupape contenant la soupape d'alimentation (17), la soupape de raccordement (13) et la soupape de réservoir (14).
EP09795981A 2008-12-17 2009-12-17 Multiplicateur de pression et ensemble de coulée sous pression Active EP2365888B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810055542 DE102008055542A1 (de) 2008-12-17 2008-12-17 Druckübersetzer mit integriertem Rückschlagventil
PCT/EP2009/067462 WO2010070073A2 (fr) 2008-12-17 2009-12-17 Multiplicateur de pression et ensemble de coulée sous pression

Publications (2)

Publication Number Publication Date
EP2365888A2 EP2365888A2 (fr) 2011-09-21
EP2365888B1 true EP2365888B1 (fr) 2013-03-06

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EP09795981A Active EP2365888B1 (fr) 2008-12-17 2009-12-17 Multiplicateur de pression et ensemble de coulée sous pression

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US (1) US8887502B2 (fr)
EP (1) EP2365888B1 (fr)
JP (1) JP5675640B2 (fr)
CN (1) CN102256726B (fr)
DE (1) DE102008055542A1 (fr)
WO (1) WO2010070073A2 (fr)

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EP3421155A1 (fr) 2017-06-28 2019-01-02 Parker Hannifin Manufacturing Germany GmbH & Co. KG Système de commutation hydraulique pour une machine de moulage sous pression à chambre froide

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CN102949934B (zh) * 2012-11-14 2014-07-09 中冶海水淡化投资有限公司 反渗透海水淡化能量回收装置及其切换器
CN103671301B (zh) * 2013-12-03 2015-09-16 广东电网公司电力科学研究院 一种机械式小位移压力转换器
US9926178B2 (en) 2014-08-20 2018-03-27 Crown Equipment Corporation Actuator in a lift truck

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DE102015202273A1 (de) 2015-02-09 2016-08-11 Oskar Frech Gmbh + Co. Kg Druckübersetzervorrichtung und Druckgießmaschinen-Gießaggregat
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EP3421155A1 (fr) 2017-06-28 2019-01-02 Parker Hannifin Manufacturing Germany GmbH & Co. KG Système de commutation hydraulique pour une machine de moulage sous pression à chambre froide

Also Published As

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US20110247485A1 (en) 2011-10-13
CN102256726A (zh) 2011-11-23
US8887502B2 (en) 2014-11-18
DE102008055542A1 (de) 2010-07-01
JP2012512033A (ja) 2012-05-31
CN102256726B (zh) 2014-12-24
EP2365888A2 (fr) 2011-09-21
WO2010070073A3 (fr) 2010-10-28
WO2010070073A2 (fr) 2010-06-24
JP5675640B2 (ja) 2015-02-25

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