EP0060181B1 - Vorgespannter hydropneumatischer Druckspeicher mit Überdrucksicherung - Google Patents

Vorgespannter hydropneumatischer Druckspeicher mit Überdrucksicherung Download PDF

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Publication number
EP0060181B1
EP0060181B1 EP82400344A EP82400344A EP0060181B1 EP 0060181 B1 EP0060181 B1 EP 0060181B1 EP 82400344 A EP82400344 A EP 82400344A EP 82400344 A EP82400344 A EP 82400344A EP 0060181 B1 EP0060181 B1 EP 0060181B1
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EP
European Patent Office
Prior art keywords
plug
accumulator
cylindrical body
pressure
plugs
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
Application number
EP82400344A
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English (en)
French (fr)
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EP0060181A1 (de
Inventor
Louis-Claude Porel
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.)
Hydro Rene Leduc SA
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Hydro Rene Leduc SA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from FR8103926A external-priority patent/FR2500892A1/fr
Priority claimed from FR8109206A external-priority patent/FR2505417A2/fr
Application filed by Hydro Rene Leduc SA filed Critical Hydro Rene Leduc SA
Priority to AT82400344T priority Critical patent/ATE18933T1/de
Publication of EP0060181A1 publication Critical patent/EP0060181A1/de
Application granted granted Critical
Publication of EP0060181B1 publication Critical patent/EP0060181B1/de
Expired 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F15B1/22—Liquid port constructions
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F15B1/10—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means
    • F15B1/106—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means characterised by the way housing components are assembled
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F15B1/10—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means
    • F15B1/12—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means attached at their periphery
    • F15B1/125—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means attached at their periphery characterised by the attachment means
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/20—Accumulator cushioning means
    • F15B2201/205—Accumulator cushioning means using gas
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/315—Accumulator separating means having flexible separating means
    • F15B2201/3151—Accumulator separating means having flexible separating means the flexible separating means being diaphragms or membranes
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/41—Liquid ports
    • F15B2201/411—Liquid ports having valve means
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/415—Gas ports
    • F15B2201/4155—Gas ports having valve means
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/43—Anti-extrusion means
    • F15B2201/435—Anti-extrusion means being fixed to the separating means

Definitions

  • the present invention relates to improvements in oleopneumatic accumulators of the type comprising two enclosures separated by a deformable wall, made of rubber, one of the enclosures being filled with gas under pressure and the other receiving hydraulic fluid under pressure; the parts constituting said accumulator being kept assembled by a prestressed device.
  • the object of the present invention is to combine the advantages of the two manufacturing methods described above, which makes it possible to obtain a prestressed hydraulic accumulator which in the event of overpressure produces a leak of liquid and which can therefore withstand very high pressures while being of a much lower manufacturing price than that of the hydraulic accumulators currently used.
  • This combination also has other advantages relating to the precision and reliability of the construction which will be explained below.
  • the oleopneumatic accumulator according to the present invention is of the type comprising two chambers separated by a flexible membrane, one of the two chambers being filled with a pressurized gas, the other being in communication with the hydraulic circuit in which is placed the accumulator, the latter being constituted by a cylindrical body disposed between two upper and lower plugs after interposition of the rim of a flexible membrane between one of the plugs and said cylindrical body, the two plugs being held tight on the cylindrical body by at at least one tie rod, one end of which is integral in traction with one of the two plugs and the other end of which is provided with a thread on which is screwed a nut bearing on the other plug, characterized in that each tie rod is put, before screwing its nut under a prior tension equal to the separation force caused by the maximum hydraulic pressure to be admitted into the accumulator so as to ensuring an assembly of the two plugs on the central body under a determined prestress; so that when the pressure admitted into said oleopneumatic accumulator exceeds
  • the two plugs are held tight on the cylindrical body by a plurality of tie rods arranged outside and around said cylindrical body.
  • the two plugs are connected to each other by a single central tie passing through them at their centers.
  • the tie (s) is tensioned by hydraulic means before the nut is screwed, which makes it possible to precisely determine the prestress and to determine it as a function of the maximum hydraulic pressure at which must work the accumulator.
  • the central cylindrical body is beveled at at least one of its ends in order on the one hand to have a self-centering of the parts and on the other hand, to introduce into the assembly a radial component which, at the Longitudinal prestress superimposes a radial prestress.
  • the accumulator is constituted by a tubular body 1 closed at its two ends by plugs 2 and 3, the flexible membrane 4 being anchored by blocking its periphery 5, provided with a heel , between the upper rim of the cylindrical body 1 and the inner face of the plug 2.
  • the two plugs 2 and 3 are of a diameter greater than that of the cylindrical body 1 and are connected one to the other by a plurality of tie rods 6 so that the body 1 is compressed by the traction exerted by these tie rods.
  • these tie rods 6 are constituted by threaded rods, one end 6a being screwed into a thread formed in the mass of the plug 2, the other end 6b being provided with a thread on which a nut 7 engages which bears against the external wall of the plug 3.
  • the bolts 7 can engage in housings 8 hollowed out in the wall of the plug 3.
  • one of the ends of the central body 1 has a conical surface 1a which comes to bear against a conical surface of the same slope 3a formed in the internal wall of the corresponding plug.
  • the plug 2 is provided with a gas filling valve 9 and the plug 3 with a conduit 10 intended to be connected to a hydraulic circuit.
  • the prestressing is carried out by means of a hydraulic jack whose body 11 is coupled by means of tie rods 12 to the tie rods 6 previously described; the piston 13 of the jack is supported on the external face of the plug 3; while by the tie rods 12 and 6, the cylinder body exerts traction on the plug 2.
  • the internal bore of the jack body 11 is strictly equal to the internal bore of the central body 1.
  • the hydraulic pressure is introduced into the chamber 14 of the jack and, when the desired value "p" of prestressing is reached, the bolts 7 are screwed until they come into contact with the outer wall of the plug 3 and the hydraulic pressure is released.
  • Figures 3 to 9 show a second embodiment of the invention consisting in replacing the tie rods 6 placed around the tube 1 outside thereof by a single tie rod axially passing through the two plugs 2 and 3, the cylindrical body 1 and the membrane 4.
  • the accumulator is constituted by a hollow cylindrical central body 1, between two upper and lower plugs 2 and 3.
  • the upper plug 2 is placed flat on the upper end of the cylindrical body 1; while the lower plug 3 comprises a skirt 3b connecting with the lower end of said cylindrical body 1.
  • the upper plug 2 has an opening 15, formed in its center and the lower plug 3 an opening 16, also formed in its center.
  • the three parts 1, 2, 3 constituting the accumulator are assembled by a central tie-rod 17.
  • This tie-rod 17 comprises a head 18 bearing against the external wall of the plug 3 and a threaded end 19 on which a nut 20 is screwed bearing on the outer wall of the plug 2.
  • the membrane 4 is fixed by anchoring and pinching its heel 5, formed over its entire periphery, between the plug 2 and the upper end of the central cylindrical body.
  • the membrane additionally comprises a sort of central chimney or sleeve 21 which forms a hollow tube in which the tie rod 17 is housed.
  • the upper edge of the sleeve 21 comprises a bead 22 which engages in a correspondingly shaped groove 23 formed in the wall of the central opening 15 of the plug 2.
  • the base 4a of the membrane has an annular shape practically matching the shape of the annular space 24 formed by the internal wall of the skirt 3b of the plug 3 and the tie rod 17.
  • the plug 3 has a bore 25 which communicates with the space 24 by a plurality of orifices 26.
  • the bore 25 is provided with a thread 27 which allows the accumulator to be screwed onto a socket (not shown) putting said bore 25 in communication with any suitable hydraulic circuit (also not shown) .
  • the lower part 4a of the membrane 4 is provided with pads 28 opposite the openings 26.
  • the plug 2 is provided with a lateral opening 29 which by means of a bent pipe 30, provided with a non-return valve 31, communicates with the enclosure to be filled with pressurized gas.
  • FIG. 4 shows two alternative embodiments according to which the central sleeve of the membrane does not rise over the entire height of the interior volume of the accumulator but only over a portion of this height.
  • the central sleeve 21 of the membrane 4 only rises over about a quarter of the height of the internal volume and is simply fixed by a rod 32 which blocks it in a groove 33 formed on the tie rod 17.
  • a rod 32 which blocks it in a groove 33 formed on the tie rod 17.
  • pads 36 being in two parts riveted one on the other instead of being included in the mass of the rubber like the pads 28 of FIG. 3.
  • the central tie-rod keeps the parts 1, 2 and 3 assembled under prestressing so that when the pressure of the hydraulic fluid exceeds a predetermined value, the elongation of the tie-rod 17 is such that a leak appears between the connection between the cylindrical body 1 and plug 2 or plug 3; this has the result that the hydraulic pressure cannot in any case exceed a predetermined maximum value, a value which is a function of the elastic characteristics of the tie rod 17 and of the prestressing to which the parts are subjected.
  • Figure 6 shows an alternative embodiment of the accumulator described in Figures 3 to 5 which has the advantage of improving the operation of said accumulator in the event of overpressure.
  • a chamfer 1a is formed at the base of the body 1, at the junction between the body 1 and the skirt 3b of the plug 3, a chamfer 1a is formed at the base of the body 1, at the junction between the body 1 and the skirt 3b of the plug 3, a chamfer 1a is formed at the base of the body 1, at the junction between the body 1 and the skirt 3b of the plug 3, a chamfer 1a is formed at the base of the body 1, at the junction between the body 1 and the skirt 3b of the plug 3, a chamfer 1a is formed at the base of the body 1 and of the skirt 3b are equal.
  • the section D2 of the base of the cylindrical body 1 is then greater than the sectin D1 subjected, at the top of the body 1 to the hydraulic pressure located in the space 24: this will have the result that in the event of overpressure the leak will occur always between the body 1 and the skirt 3b and never between the body 1 and the plug 2.
  • Figure 7 shows another alternative embodiment.
  • the method of anchoring the membrane 4 by means of a heel 5 as shown in FIGS. 3 to 6, has the drawback that the surface of the section D1, mentioned above, is not rigorously determined . Indeed, a greater or lesser tightness of this pinching can allow the hydraulic fluid to creep between the membrane and the upper body 1, which will have the effect that the section D1 on which the hydraulic pressure acts will always be slightly higher to the section of the internal bore of the cylindrical body 1, but of an amount which cannot be determined in a rigorous manner. It is for this reason that in FIG. 6, the section D1 has been represented as being larger than the internal diameter of the cylindrical body 1, but this indication is an approximation.
  • This arrangement is particularly advantageous, because it is very economical while being very reliable.
  • the accumulators shown in Figures 3 to 7 are prestressed.
  • Figure 8 we screw on the threaded end 19 of the tie rod 17, the end of the rod 37a of the piston 37 a hydraulic cylinder 38 which is supported by a cylindrical wedge 39 on the plug 2. Thanks to this actuator, on the one hand a compressive force is applied to the parts 2, 1 and 3, force collected by the elasticity of the metal of which these parts are made and on the other hand a tensile force on the tie rod 17, force also cashed in by the elasticity of the metal from which the tie rod is made 17. When the predetermined maximum force is reached, the nut 20 is blocked on the plug 2 and then the pressure is released in the jack 38. The elasticity of the parts 1 , 2 and 3 on the one hand and the tie rod 17 has the result that the assembly of parts 1, 2 and 3 is carried out with prestressing.
  • an oleopneumatic accumulator having a capacity of 1 liter has been produced.
  • hydraulic fluid was introduced under a pressure of 100 bars; then, the nut 20 has been locked on the thread 19 by means of a dynamometric key so as to have a determined tightening torque; then the mounting cylinder 38 was disassembled and the accumulator was placed on a test bench and hydraulic fluid was forced at 25, 26, 24, until a hydraulic fluid leak appeared between the base 1a of the cylindrical body 1 and the skirt 3a of the plug; the pressure P1 for which this leak occurred was then noted.
  • the accumulator is then adjusted to operate with a maximum pressure of 400 bar.
  • the accumulator tested underwent 5 million cycles and did not show the slightest trace of deterioration upon dismantling, while the usual accumulators show traces of deterioration after approximately 150,000 cycles.
  • the extraordinary reliability of the accumulator thus described makes it possible to use it not only as an accumulator but also as a pressure relief valve.
  • a pressure relief valve is a known, extremely simple member, constituted by a valve held by a calibrated spring: when the hydraulic pressure exceeds a predetermined value, the ball lifts and the hydraulic fluid flows towards the reservoir.
  • a pressure relief valve of perfectly functioning is obtained. satisfactory.
  • the capacity of the accumulator is determined experimentally as a function of the maximum flow rate of the circuit for which it is intended.
  • Such a pressure relief valve will be cheaper than a large spring-loaded valve, will not be sensitive to dirt that may be in the liquid, will have a leakage section such that there will be no more fluid flow at high speed which erodes the metal and will work without causing overpressure.
  • the two ends of the central body 1 are bevelled as has been described for the conical surface 1a in conjunction with FIG. 1.
  • the two ends of the central body 1 are bevelled as has been described for the conical surface 1a in conjunction with FIG. 1.
  • the separation membrane 4 in a form such that it is cylindrical at its upper part, as shown, and that this cylindrical part is disposed inside the upper part of the central body 1, itself cylindrical, it follows that the diameter D 3 of the circle according to which the pressure acts on the upper plug 2 is slightly smaller (due to the thickness of the membrane) than the diameter D 4 of the circle according to which the pressure acts on the lower plug 3; it follows that when the pressure admitted into the accumulator exerts on the central rod 17 a force greater than that of the prestress, the cylindrical body 1 and the lower plug 3 separate slightly, which causes a leakage of the liquid, the separation never occurring at the connection between the plug 2 and the body 1.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Claims (13)

1. Ölpneumatischer Druckspeicher, umfassend zwei von einer nachgiebigen Membran (4) getrennte Behälter, wobei der eine mit unter Druck stehendem Gas und der andere mit Flüssigkeit gefüllt ist, gebildet durch einen zylindrischen Körper (1), welcher zwischen einer oberen Kappe (2) und einer unteren Kappe (3) nach Zwischenschaltung des Randes (5) der nachgiebigen Membran (4) zwischen einer der Kappen (2) und dem zylindrischen Körper (1) angeordnet ist, wobei die beiden Kappen (2, 3) auf dem zylindrischen Körper (1) durch mindestens einen Bolzen (6 oder 17) festgehalten werden, von dem ein Ende (6a, 18) mit einer der beiden Kappen (2 oder 3) auf Zugbelastung fest verbunden ist und das andere Ende (6b, 19) mit einem Gewinde versehen ist, auf das eine Mutter (7, 20) geschraubt ist, welche auf der anderen Kappe (2 oder 3) aufliegt, dadurch gekennzeichnet, dass jeder Bolzen (6, 17) vor Festschrauben der jeweiligen Mutter (7, 20) einer Vorspannung unterworfen wird, die gleich der Trennkraft ist, die durch den hydraulischen Maximaldruck verursacht wird, welcher in dem Druckspeicher vorgesehen ist, um die Verbindung der beiden Kappen (2, 3) mit dem Mittelkörper (1) unter einer vorher bestimmten Vorspannung zu gewährleisten, so dass sich der zylindrische Körper (1) geringfügig von der einen oder der anderen unteren (3) und/oder oberen (2) Kappe löst, wenn der zulässige Druck in dem ölpneumatischen Druckspeicher den vorher bestimmten Maximaldruck überschreitet, was eine hydraulische Undichtheit verursacht, die den hydraulischen Druck absenkt, der somit den vorher bestimmten Wert nie überschreiten kann.
2. Hydraulischer Druckspeicher nach Anspruch 1, dadurch gekennzeichnet, dass er eine Mehrzahl von um den zylindrischen Mittelkörper (1) angeordneten Bolzen (6) aufweist, wobei jeder Bolzen (6) an einem seiner Enden (6a) auf dem Rand einer der Kappen (2) angeschraubt ist und an seinem anderen Ende (6b) mit einem Gewinde versehen ist, auf das eine Mutter (7) geschraubt wird, die auf dem Rand der anderen Kappe (3) aufliegt.
3. Druckspeicher nach Anspruch 2, bei dem das untere Ende des zylindrischen Körpers (1) einen konischen Rand (1a) aufweist, der an einer entsprechenden konischen Oberfläche (3a) aufliegt, welche auf der Innenfläche der unteren Kappe (3) derart vorgesehen ist, dass die Zentrierung des zylindrischen Körpers gewährleistet ist und dass diese Zentrierung beibehalten wird, wenn sich die konischen Oberflächen (1a, 3a) unter der Einwirkung eines über dem vorher bestimmten Maximaldruck liegenden Druckes geringfügig voneinander lösen.
4. Verfahren zum unter Vorspannung Setzen der Mittel zum Verbinden nach den Ansprüchen 1 bis 3, bei dem der Körper (11) eines hydraulischen Arbeitszylinders mit den Bolzen (6) des Druckspeichers verbunden wird, welche mit einer der Kappen (2) verbunden sind, wobei der Kolben (13) des Zylinders an der äusseren Oberfläche der anderen Kappe (3) aufliegt; wonach der hydraulische Arbeitszylinder bis zum Erreichen des gewünschten Wertes unter Druck gesetzt wird; wonach die Muttern (7) der Bolzen (6) derart festgeschraubt werden, dass sie mit der Aussenwand der Kappe (3) in Berührung stehen und wonach der Druck abgebaut wird, so dass einerseits die Bolzen (6) unter die gewünschte Vorspannung gesetzt werden und anderseits die Bestandteile (1, 2, 3) des Druckspeichers zunächst unter der Einwirkung der gleichen Kraft zusammengepresst werden.
5. Hydraulischer Druckspeicher nach Anspruch 1, dadurch gekennzeichnet, dass er nur einen mittleren Bolzen (17) umfasst, der die beiden Kappen (2, 3) und über eine Manschette (21) die elastische Membran (4) durchquert, wobei dieser mittlere Bolzen (17) vor dem Festschrauben der Mutter (20) gegen die Wand der Kappe (2) unter eine Vorspannung gesetzt wird, die gleich der Trennkraft ist, die durch den hydraulischen Maximaldruck verursacht wird, welcher in dem Druckspeicher vorgesehen ist, um die Verbindung der beiden Kappen (2, 3) des zylindrischen Körpers (1) und der Membran (4) unter einer vorher bestimmten Vorspannung zu gewährleisten.
6. Druckspeicher nach Anspruch 5, bei dem sich die Manschette (21) über die gesamte Höhe des inneren Volumens des Druckspeichers erstreckt und an ihrem oberen Ende an der Kappe (2) verankert ist.
7. Druckspeicher nach Anspruch 5 oder 6, bei dem die Austrittsöffnungen (26) der Flüssigkeit rund um den Mittelbolzen (17) auf der Kappe (3) angeordnet sind.
8. Druckspeicher nach Anspruch 3, bei dem der ringförmige Boden (4a) der Membran (4) gegenüber den Öffnungen (26) mit Plättchen (28, 36) versehen ist.
9. Druckspeicher nach einem der vorhergehenden Ansprüche, bei dem die innere Bohrung des zylindrischen Körpers (1) an der Basis einen grösseren Querschnitt als in dem oberen Teil hat, so dass die von dem Innendruck auf die Basis des zylindrischen Körpers (1) ausgeübte Kraft geringer ist als jene, die auf den oberen Teil ausgeübt wird, und woraus sich ergibt, dass sich der zylindrische Körper (1) geringfügig von der unteren Kappe (3) löst, wobei er mit der oberen Kappe (2) in Kontakt bleibt.
10. Druckspeicher nach Anspruch 9, bei dem die innere Bohrung des zylindrischen Körpers (1) an der Basis eine Abschrägung (1a) aufweist, wobei die Verbindung zwischen dem genannten zylindrischen Körper (1) und der Kappe (3) durch eine Schürze (3a) der Kappe erfolgt, welche die gleiche Dicke wie die abgeschrägte Basis des zylindrischen Körpers hat.
11. Druckspeicher nach Anspruch 9 oder 10, bei dem die Membran (4) mittels einer in der Mitte durchbrochenen elastischen Scheibe (40) fixiert ist, deren äusserer peripherer Rand (40b) den äusseren Rand (4b) der Membran in dem durch die Verbindung zwischen der oberen Kappe (2) und dem oberen Teil des zylindrischen Körpers bestimmten Winkel festklemmt, und deren Rand (40a) der inneren Öffnung den oberen Teil der Manschette (21) der Membran (4) in einer in dem Bolzen (17) vorgesehenen Vertiefung (33) festsetzt.
12. Verfahren zum unter Vorspannung Setzen eines Druckspeichers nach den Ansprüchen 5 bis 11, dadurch gekennzeichnet, dass mittels eines hydraulischen Arbeitszylinders (38) ein Druck auf die den Druckspeicher bildenden Teile (1, 2, 3) und ein Zug auf den Mittelbolzen (17) ausgeübt wird, dass danach die Mutter (20) auf den mit einem Gewinde versehenen Bolzen bis zur Festsetzung gegen die obere Kappe (2) geschraubt wird, wonach der hydraulische Druck so abgebaut wird, dass einerseits der Mittelbolzen (17) unter die gewünschte Vorspannung gesetzt wird und anderseits die Bestandteile (1, 2, 3) des Druckspeichers unter der Einwirkung der gleichen Kraft zunächst zusammengepresst werden.
13. Verwendung eines Druckspeichers nach einem der Ansprüche 1 bis 3 und 5 bis 11 als Überdruckventil für einen hydraulischen Kreislauf.
EP82400344A 1981-02-27 1982-02-26 Vorgespannter hydropneumatischer Druckspeicher mit Überdrucksicherung Expired EP0060181B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82400344T ATE18933T1 (de) 1981-02-27 1982-02-26 Vorgespannter hydropneumatischer druckspeicher mit ueberdrucksicherung.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR8103926 1981-02-27
FR8103926A FR2500892A1 (fr) 1981-02-27 1981-02-27 Perfectionnements aux accumulateurs oleo-pneumatiques a assemblage par precontrainte
FR8109206A FR2505417A2 (fr) 1981-05-08 1981-05-08 Perfectionnements aux accumulateurs oleo-pneumatiques a assemblage par precontrainte
FR8109206 1981-05-08

Publications (2)

Publication Number Publication Date
EP0060181A1 EP0060181A1 (de) 1982-09-15
EP0060181B1 true EP0060181B1 (de) 1986-04-02

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EP82400344A Expired EP0060181B1 (de) 1981-02-27 1982-02-26 Vorgespannter hydropneumatischer Druckspeicher mit Überdrucksicherung

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US (1) US4449552A (de)
EP (1) EP0060181B1 (de)
CA (1) CA1165663A (de)
CH (1) CH652174A5 (de)
DE (1) DE3270209D1 (de)
ES (1) ES509907A0 (de)
YU (1) YU43068B (de)

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US6116585A (en) * 1997-08-11 2000-09-12 Mannesmann Sachs Ag Pressure holder with an enclosed gas mass
DE10027244C1 (de) * 2000-05-31 2001-10-31 Mannesmann Sachs Ag Füllventil für einen Druckbehälter
DE10029150C1 (de) * 2000-06-14 2001-08-16 Mannesmann Sachs Ag Druckbehälter, insbesondere für einen Schwingungsdämpfer
US6651698B1 (en) * 2002-05-31 2003-11-25 Wilkes & Mclean Ltd. Suppressor for manifold fluid line
DE102007042865B4 (de) * 2007-09-08 2011-09-22 Zf Friedrichshafen Ag Selbstpumpendes hydropneumatisches Federbein
FR2938308B1 (fr) * 2008-11-07 2012-04-20 Hydro Leduc Perfectionnements aux accumulateurs oleopneumatiques a piston
US8640314B2 (en) * 2010-08-03 2014-02-04 Federal-Mogul Corporation Piston assembly transportation and installation apparatus and methods of transporting and installing a piston assembly therewith
EP2453140A3 (de) * 2010-11-10 2013-10-09 Norgren GmbH Flüssigkeitsbetriebener Aktuator mit verformbarem Abdichtelement
DE102011102978B4 (de) 2011-05-23 2018-05-17 Phoenix Contact Gmbh & Co. Kg Strommessumformer
EP2722575B1 (de) * 2012-10-16 2017-08-30 Water Powered Technologies Limited Gasfederakkumulator
US9127811B2 (en) 2013-06-05 2015-09-08 Louis P. Vickio, Jr. Hydraulic accumulator
CN105889145B (zh) * 2014-12-11 2018-11-16 西安航天发动机厂 微压响应储液器
USD867986S1 (en) * 2017-11-07 2019-11-26 Energy2Go Srl Accumulator charging apparatus
USD902153S1 (en) * 2018-08-03 2020-11-17 Aktsionerno Droujestvo “Start” Ad Insert for accumulator recirculation

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DE2430073A1 (de) * 1974-06-22 1976-01-08 Kloeckner Werke Ag Arbeitszylinder
DE2430261A1 (de) * 1974-06-24 1976-01-15 Kloeckner Werke Ag Ringfoermig ausgebildete kolben-zylinder-einheit
EP0035427A2 (de) * 1980-02-27 1981-09-09 Etablissements René Leduc & Fils (Société Anonyme) Verfahren zur Herstellung eines vorgespannten Druckspeichers und Druckspeicher gemäss diesem Verfahren

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US2947326A (en) * 1955-03-14 1960-08-02 Mercier Jean Pressure device
US3140729A (en) * 1956-02-23 1964-07-14 Mercier Jean Valve assembly
FR1150762A (fr) * 1956-04-05 1958-01-17 Perfectionnements aux enceintes de fluides pouvant être mises sous pression et comportant un séparateur
FR1378955A (fr) * 1963-09-28 1964-11-20 Perfectionnements apportés aux soupapes notamment pour réservoirs de pression
DE1525485A1 (de) * 1966-02-17 1969-08-14 Jean Mercier Druckbehaelter mit einer nachgiebigen Trennwand
DE2453026A1 (de) * 1974-11-08 1976-05-13 Maschf Augsburg Nuernberg Ag Vorrichtung zum spannen und loesen von schrauben-mutter-verbindungen

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DE2430073A1 (de) * 1974-06-22 1976-01-08 Kloeckner Werke Ag Arbeitszylinder
DE2430261A1 (de) * 1974-06-24 1976-01-15 Kloeckner Werke Ag Ringfoermig ausgebildete kolben-zylinder-einheit
EP0035427A2 (de) * 1980-02-27 1981-09-09 Etablissements René Leduc & Fils (Société Anonyme) Verfahren zur Herstellung eines vorgespannten Druckspeichers und Druckspeicher gemäss diesem Verfahren

Also Published As

Publication number Publication date
ES8303623A1 (es) 1983-02-01
CH652174A5 (fr) 1985-10-31
YU43068B (en) 1989-02-28
CA1165663A (en) 1984-04-17
EP0060181A1 (de) 1982-09-15
YU43982A (en) 1985-03-20
ES509907A0 (es) 1983-02-01
DE3270209D1 (en) 1986-05-07
US4449552A (en) 1984-05-22

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