EP1979627B1 - Hydraulisches system - Google Patents

Hydraulisches system Download PDF

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Publication number
EP1979627B1
EP1979627B1 EP06847165.5A EP06847165A EP1979627B1 EP 1979627 B1 EP1979627 B1 EP 1979627B1 EP 06847165 A EP06847165 A EP 06847165A EP 1979627 B1 EP1979627 B1 EP 1979627B1
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EP
European Patent Office
Prior art keywords
hydraulic system
piston
compression chamber
axis
pressure
Prior art date
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EP06847165.5A
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English (en)
French (fr)
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EP1979627A2 (de
Inventor
Stefan Klotz
Gérard Hamel
Joël FRELAT
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Centre National de la Recherche Scientifique CNRS
Universite Pierre et Marie Curie Paris 6
Original Assignee
Centre National de la Recherche Scientifique CNRS
Universite Pierre et Marie Curie Paris 6
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B11/00—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses
    • B30B11/004—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses involving the use of very high pressures
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1414—Characterised by the construction of the motor unit of the straight-cylinder type with non-rotatable piston
    • F15B15/1419—Characterised by the construction of the motor unit of the straight-cylinder type with non-rotatable piston of non-circular cross-section
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—Pistons; Piston to piston rod assemblies

Definitions

  • the present invention relates to hydraulic systems and more particularly those operating with relatively high fluid pressures, for example greater than or equal to 100 MPa.
  • the pressure of the hydraulic fluid in the compression chamber allows the piston to be subjected to a force that can be used to move it.
  • the hydraulic system In certain fields of application, for reasons of space and weight, the hydraulic system must be compact and have a high capacity relative to its mass and its dimensions.
  • the maximum pressure of the fluid is not as high as desirable in the known compact hydraulic systems, otherwise the compression chamber may be deformed with a risk of leakage of hydraulic fluid, for example due to the failure of the hydraulic fluid. extrusion seal between the piston and the wall of the compression chamber.
  • a self-compensated press is disclosed in the European patent EP 0 509 928 .
  • This press has four tie rods to support the plate against which the piston is applied, so that the stresses induced by the tie rods are axisymmetric.
  • a disadvantage of such a press is the less accessibility to its central region, given the opening angle between the tie rods seen from the axis thereof.
  • the two-tie presses offer greater access but they are limited in pressure due to the deformation of the base part under the effect of the reaction of the tie rods under load, which induces non-axisymmetric constraints.
  • the invention aims to provide an improved hydraulic system to overcome all or some of the disadvantages mentioned above.
  • the invention applies more particularly but not exclusively to compact hydraulic systems.
  • the compression chamber may be defined in a base portion of the hydraulic system and the latter may comprise a plate connected by two tie rods to the base portion, the piston being arranged to exert a force in the direction of the plate.
  • the seal is arranged to compensate for non-axisymmetric constraints induced by the reaction of the tie rods under the effect of the force exerted by the piston on the plate.
  • the two tie rods may for example leave between them two openings each of angular extent between 130 ° and 150 ° in an equatorial plane around the Z axis.
  • the piston can support a first anvil and the plate a second anvil against which can be applied the first anvil.
  • the piston may comprise a groove in which the seal is received. This groove can have a wavy shape.
  • the corrugations may have vertices, corresponding to a maximum distance from the bottom of the compression chamber, located substantially opposite the tie rods.
  • z 0 may be between 0.1. h and 0.3. h , where h is the height of the piston.
  • A may be between 0.25. h and 0.4. h .
  • the piston may have a larger transverse dimension, in particular a diameter d , of between 0.9. h and 1.1. h .
  • a larger transverse dimension of the hydraulic system may be between 1.1 and 1.5 times the largest transverse dimension of the piston, in particular its diameter.
  • the seal may be positioned such that the relative variation of a larger internal transverse dimension, in particular an inside diameter, of the compression chamber, as the fluid pressure changes from atmospheric pressure to a pressure of 200 MPa is less than or equal to plus or minus 1 per 1,000.
  • the fluid pressure during operation of the hydraulic system may be, for example, between 1 and 2500 bar, in particular between 100 and 2500 bar.
  • the hydraulic system may include a polarizer for positioning the piston with a predefined angular orientation relative to the compression chamber.
  • the invention can also make it possible to produce a hydraulic system with a piston having a non-symmetrical cross section of revolution, which is capable of operating with a relatively high fluid pressure, even in the case of non-axisymmetric constraints induced by the fluid pressure. .
  • the cross section may for example have an elongation factor of between 1.1 and 4, the elongation factor being defined as the ratio of the length to the width.
  • the base portion 2 comprises a compression pot 7 which defines a compression chamber 8 in which a piston 10 can slide along an axis Z.
  • the compression chamber 8 can be fed with a fluid under pressure through a conduit 13 to be connected with a pressure source.
  • the pot 7 has a lower portion 16 which is enlarged and which is threaded externally.
  • the two tie rods 3 are made in a monolithic manner with the plate 4 and with a mounting skirt 18 arranged to screw on the lower part 16 of the pot 7.
  • the plate 4 comprises a central housing 20 which is internally threaded and which receives an insert 22 screwed into it.
  • the piston 10 supports a first anvil 23 and the insert 22 a second anvil 24 against which can be applied the first anvil 23 when the piston 10 moves upwards under the effect of the fluid pressure.
  • the anvils 23, 24 may carry, for example, at least one sample to be compressed by the press.
  • the latter can for example be described as compact, with ⁇ greater than or equal to 1.
  • a seal 30 is interposed between the piston 10 and the wall of the compression chamber 8 to prevent leakage of hydraulic fluid by the clearance between the piston 10 and this wall.
  • the compression chamber 8 is delimited by a lateral surface 32 which is cylindrical of revolution about the Z axis and the piston 10 has a facing lateral surface 33 which is also cylindrical with a Z axis revolution. .
  • the seal 30 is housed in a groove 35 of the piston 10 which extends in a curve not entirely contained in a plane perpendicular to the Z axis.
  • the constants z 0 and A are for example as defined above.
  • the peaks 38 of the corrugations lie substantially opposite the tie rods 3.
  • the piston may comprise as shown in FIG. figure 1 at least one first relief 36 intended to cooperate with a second relief 37 of the base part or tie rods.
  • the piston comprises a longitudinal groove 36 extending parallel to the axis Z, forming a polarizer, in which engages a rib 37 formed on the upper part of the inner surface of the compression pot, the above the seal 30.
  • the corrugated shape of the seal 30 allows the pressure of the fluid contained in the compression chamber 8 to exert a non-axisymmetric force thereon, which compensates the non-axisymmetric forces related to the reaction of the tie rods 3 on the part basic 2.
  • the invention is not limited to a particular form of joint and it will be adapted through a finite element calculation, for example, the distribution of stresses that are exerted on the compression chamber during operation.
  • the invention makes it possible to produce a two-link press which has access to its central region having a relatively wide opening angle ⁇ seen from the Z axis, as illustrated in FIG. figure 5 .
  • the angle ⁇ is for example about 140 ° and the angle ⁇ under which is seen each drawing about 40 °.
  • the invention applies not only to the production of a compact two-tie press, but also to the production of a jack in which the piston 10 has, for example, a non-symmetrical cross section of revolution, in particular a flattened cross-section. as shown in figure 6 .
  • the forces exerted on the wall of the compression chamber are non-axisymmetrical and can deform it.
  • the invention is still applicable in the case where in a press or cylinder the compression chamber 8 is defined by a wall which has a resistance, in particular a thickness, e ( ⁇ ) which is not constant around the axis Z, for example due to the presence of two opposite outer plane faces 40 joined by cylindrical faces 41 of revolution about the Z axis.
  • the ratio e max / e min is for example greater than or equal to 1.1, even 1.2, even 1.5 or 2 or more.
  • the non-constant thickness e can make it possible to produce a hydraulic system, in particular a jack, in which the base part has a small bulk.
  • the piston 10 may have a circular cross section, as illustrated in FIG. figure 8 , as well as the surface facing the compression chamber 8, but in a variant not shown, the piston 10 has a non-circular cross section, for example of oblong shape.
  • the seal may be housed in a groove formed on the side surface of the compression chamber.
  • the piston may be monolithic or formed by the assembly of several parts, as well as the base part, the tie rods and the plate.
  • the seal may be an O-ring as illustrated or any other seal to achieve the desired seal.
  • the piston may comprise more than one seal.
  • the hydraulic fluid can be an oil or any other liquid.

Landscapes

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

Claims (20)

  1. Hydrauliksystem (1) mit
    einer Kompressionskammer (8), die dazu ausgelegt ist, unter den Druck eines Hydraulikfluids gesetzt zu werden,
    einem in der Kompressionskammer (8) entlang einer Achse (Z) beweglichen Kolben (10),
    wenigstens einer Abdichtverbindung (30), die zwischen dem Kolben (10) und einer Wand der Kompressionskammer (8) angeordnet ist, um die nicht axialsymmetrischen Spannungen zu kompensieren, die durch den Druck des Fluids erzeugt werden,
    dadurch gekennzeichnet, dass die Verbindung (30) eine Axialposition aufweist deren Umfang um die Achse (Z) variiert.
  2. Hydrauliksystem (1) nach Anspruch 1, wobei die Kompressionskammer (8) in einem Basisabschnitt (2) untergebracht ist und das Hydrauliksystem (1) eine über zwei Träger (3) an dem Basisabschnitt (2) befestigte Platte (4) aufweist, wobei der Kolben (10) dazu eingerichtet ist, eine Kraft in Richtung der Platte (4) auszuüben, und die Abdichtverbindung (30) dazu ausgelegt ist, die nicht axialsymmetrischen Spannungen zu kompensieren, die aufgrund der durch den Kolben (10) auf die Platte (4) ausgeübten Kraft durch die Gegenkraft der Träger (3) erzeugt wird.
  3. Hydrauliksystem (1) nach Anspruch 2, wobei die zwei Träger (3) zwischen sich zwei Öffnungen freilassen, deren Winkelbereich (α) zwischen 130° und 150° in der Äquatorialebene gesehen von der Achse (Z) liegt.
  4. Hydrauliksystem (1) nach einem der vorstehenden Ansprüche, wobei der Kolben (10) einen ersten Amboss (23) und die Platte (4) einen zweiten Amboss (24) trägt, gegen den der erste Amboss (23) angewendet werden kann.
  5. Hydrauliksystem (1) nach einem der vorstehenden Ansprüche, wobei der Kolben (10) eine Vertiefung (35) aufweist, in der die Abdichtverbindung (30) aufgenommen ist.
  6. Hydrauliksystem (1) nach dem vorstehenden Anspruch, wobei die Vertiefung (35) eine wellige Form aufweist.
  7. Hydrauliksystem (1) nach den Ansprüchen 2 und 6, wobei die Wellenform Erhebungen (38) aufweist, die einer maximalen Distanz von dem Boden der Kompressionkammer (8) entsprechen und im Wesentlichen gegenüber den Trägem (3) angeordnet sind.
  8. Hydrauliksystem (1) nach einem der vorstehenden Ansprüche, wobei die Axialposition (z(φ)) der Verbindung (30) durch die folgende Formel gegeben ist: z φ = z 0 + A sin 4 φ ,
    Figure imgb0004
    wobei φ der Winkel um die Achse (Z), und z0 und A Konstanten sind,
    oder durch Formeln gegeben ist, die ähnliche Variationen z(φ) ausführen.
  9. Hydrauliksystem (1) nach dem vorstehenden Anspruch, wobei z0 zwischen 0,1.h und 0,3.h liegt, wobei h die Höhe des Kolbens (10) bezeichnet.
  10. Hydrauliksystem (1) nach Anspruch 8, wobei A zwischen 0,25.h und 0,4.h liegt, wobei h die Höhe des Kolbens (10) bezeichnet.
  11. Hydrauliksystem (1) nach einem der vorstehenden Ansprüche, wobei der Kolben (10) in Querrichtung zur Achse (Z) eine größte Abmessung, insbesondere einen Durchmesser (d), aufweist, die zwischen 0,9.h und 1,1.h liegt, wobei h die Höhe des Kolbens (10) bezeichnet.
  12. Hydrauliksystem (1) nach einem der vorstehenden Ansprüche, wobei in Querrichtung zu der Achse (Z) eine größte Abmessung des Hydrauliksystems zwischen dem 0,1 und 0,5-fachen der größten Abmessung in Querrichtung, insbesondere des Durchmessers, des Kolbens (10) liegt.
  13. Hydrauliksystem (1) nach einem der vorstehenden Ansprüche, wobei die Dichtungsverbindung (30) so positioniert ist, dass die relative Variation der größten Innenabmessung in Querrichtung zu der Achse (Z), insbesondere des Innendurchmessers, der Kompressionskammer (8), bei einem Anstieg des Fluiddrucks von Atmosphärenduck bis zu einem Druck von 200 MPa höchstens ± 1‰ beträgt.
  14. Hydrauliksystem nach einem der vorstehenden Ansprüche, wobei η ≥ 1 tn.kg-3/2, wobei η = Cm-3/2, C die Kapazität des Hydrauliksystem in Tonnen und m dessen Masse in kg ist.
  15. Hydrauliksystem nach einem der Ansprüche 1 bis 14, wobei der Kolben (10) in Querrichtung zu der Achse (Z) einen nicht-symmetrischen Drehquerschnitt aufweist.
  16. Hydrauliksystem nach Anspruch 15, wobei der Querschnitt des Kolbens ein Zerrungsverhältnis zwischen 1,1 und 4 aufweist.
  17. Hydrauliksystem nach einem der Ansprüche 1 bis 16, wobei die Kompressionkammer durch eine Widerstandswand begrenzt ist, deren Dicke e(φ) insbesondere nicht konstant ist, wobei φ der Winkel um die Achse (Z) ist.
  18. Hydrauliksystem nach Anspruch 17, wobei die Dicke e(φ) mit einem Verhältnis emax/emin ≥ 1,1 variiert, insbesondere 1,2, ferner insbesondere 1,5 oder 2.
  19. Hydrauliksystem (1) nach einem der vorstehenden Ansprüche, wobei die Kompressionskammer mit einem Fluid unter Druck gefüllt ist, wobei der Fluiddruck zwischen 1 und 2500 bar, insbesondere zwischen 100 und 2500 bar liegt.
  20. Hydrauliksystem (1) nach einem der Ansprüche 1 bis 19, mit einer Erkennungseinrichtung, die die Positionierung des Kolbens mit einer vorbestimmten Winkelorientierung relativ zu der Kompressionskammer (8) ermöglicht.
EP06847165.5A 2005-12-21 2006-12-18 Hydraulisches system Active EP1979627B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0513073A FR2895038B1 (fr) 2005-12-21 2005-12-21 Systeme hydraulique.
PCT/FR2006/051375 WO2007074282A2 (fr) 2005-12-21 2006-12-18 Presse hydraulique

Publications (2)

Publication Number Publication Date
EP1979627A2 EP1979627A2 (de) 2008-10-15
EP1979627B1 true EP1979627B1 (de) 2013-04-10

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US (1) US8127661B2 (de)
EP (1) EP1979627B1 (de)
FR (1) FR2895038B1 (de)
WO (1) WO2007074282A2 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9840450B2 (en) * 2015-09-08 2017-12-12 The United States Of America As Represented By The Secretary Of The Army Energetic high pressure polymorph of croconic acid and high energy compositions formed therefrom

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3841644A (en) * 1972-12-20 1974-10-15 C White Low friction sealing ring
ZA755683B (en) * 1975-09-05 1977-04-27 Morrison Pumps Sa Presses
FR2675425B1 (fr) 1991-04-18 1995-08-04 Centre Nat Rech Scient Presse haute pression.
US6502880B1 (en) * 2000-03-08 2003-01-07 Btm Corporation Pin part locator
JP2006068620A (ja) * 2004-09-01 2006-03-16 National Institute Of Advanced Industrial & Technology 高圧発生装置

Also Published As

Publication number Publication date
FR2895038B1 (fr) 2012-04-20
EP1979627A2 (de) 2008-10-15
US20090091090A1 (en) 2009-04-09
FR2895038A1 (fr) 2007-06-22
WO2007074282A2 (fr) 2007-07-05
US8127661B2 (en) 2012-03-06
WO2007074282A3 (fr) 2007-08-16

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