EP2241763B1 - Dispositif de commande hydraulique et balance de pression pour ledit dispositif - Google Patents

Dispositif de commande hydraulique et balance de pression pour ledit dispositif Download PDF

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Publication number
EP2241763B1
EP2241763B1 EP20090007207 EP09007207A EP2241763B1 EP 2241763 B1 EP2241763 B1 EP 2241763B1 EP 20090007207 EP20090007207 EP 20090007207 EP 09007207 A EP09007207 A EP 09007207A EP 2241763 B1 EP2241763 B1 EP 2241763B1
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EP
European Patent Office
Prior art keywords
pressure
valve
control device
hydraulic control
restrictor
Prior art date
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Active
Application number
EP20090007207
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German (de)
English (en)
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EP2241763A3 (fr
EP2241763A2 (fr
Inventor
Georg Neumair
Johann König
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Hawe Hydraulik SE
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Hawe Hydraulik SE
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Publication date
Application filed by Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP20090007207 priority Critical patent/EP2241763B1/fr
Priority to US12/748,954 priority patent/US8549853B2/en
Priority to CN2010101674249A priority patent/CN101956731B/zh
Publication of EP2241763A2 publication Critical patent/EP2241763A2/fr
Publication of EP2241763A3 publication Critical patent/EP2241763A3/fr
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Publication of EP2241763B1 publication Critical patent/EP2241763B1/fr
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/026—Pressure compensating valves
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves

Definitions

  • the invention relates to a hydraulic control device according to the preamble of patent claim 1.
  • Hydraulic control devices with a pressure switch are known in various embodiments in practice.
  • the pressure switch between the pressure source and the valve assembly is arranged in a main flow path and formed as a 3/2-way slide valve which connects the pressure source to the valve assembly in one control position and separates the valve assembly from the reservoir, whereas in the other control position, the pressure source shut off and connects the valve assembly with the reservoir.
  • the slide valve needs a sliding fit which causes inaccurate leakage losses to the reservoir in units, for example with a pump with a low flow rate, at a high supply pressure or delivery volume flow.
  • leakage at driven pressure source are not tolerable.
  • the reason for a pressure switch in such hydraulic control devices is that after switching off the pressure source of the pressure applied to the valve assembly pressure is to be reduced to the reservoir, for example, so that the drive motor acting as a pressure source pump when switching does not have to work immediately against relatively high resistance.
  • a single-phase AC motor can bad start against impending pressure, which requires an oversized design of the drive motor so that it is able to properly perform the start-up phase despite counter-pressure.
  • auxiliary volume in a control pressure channel which contains the control pressure acting on the control member in the first adjustment direction.
  • This auxiliary volume is defined in a chamber in which a piston against spring force yields so that when the drive motor starts and the pressure switch has separated the valve assembly from the reservoir and connected to the pressure source, the pressure source fills the auxiliary volume, whereby the drive motor initially only has to overcome low resistance.
  • This auxiliary volume means additional structural complexity and provides the desired effect at most up to a maximum pressure of, for example, about 300 bar. At higher maximum pressures of eg up to 700 bar, however, the effect is no longer satisfactory.
  • a generic hydraulic control device wherein the consumers are fed from a variable displacement, which is cooled in a stand-by operating situation without switched consumers by a flushing valve in a small flow rate to the reservoir effluent hydraulic medium.
  • the flush valve has the function of a pressure switch with a throttle as an integral part and is arranged in a slide of a pressure compensator. If the variable displacement pump is switched off, then the flushing valve opens the outflow path to the reservoir, so that the pressure line leading to the valve arrangements is depressurized.
  • the invention has for its object to provide a hydraulic control device of the type mentioned above, in which no loss losses occur when shut off to the reservoir Abströmweg and working pressure source, and in which the starting resistance of the drive motor is minimized.
  • valve cone for the two control pressures on differently sized loading surfaces such that the loading surface for the valve cone of the first adjustment acting on the control pressure is smaller than the loading surface for the valve cone acting in the second adjustment control pressure.
  • the ratio of the loading areas may be between about 2: 1 and 4: 1, but is preferably about 3: 1.
  • the loading surfaces may be about the same size.
  • a throttle which causes a higher pressure difference.
  • valve cone between the smaller loading surface and the valve seat is sealed by at least one ring seal.
  • the ring seal dampens the movement of the valve cone, and on the other hand ensures that no leakage occurs between the possibly high control pressure P1, possibly high application pressure and the reservoir R in the shut-off position, which could falsify the control pressure acting on the smaller or different application area.
  • the throttle has a fixed throttle cross-section, which specifies a suitable for the respective supply pressure flow rate or pressure difference.
  • the throttle may be, for example, a screw-in in a main channel connecting the pressure source and the valve assembly, and can be replaced if necessary against another Einschraubdrossel with another throttle cross-section.
  • the size of the throttle is selected depending on the flow rate.
  • the throttle may have a variable throttle cross-section, which can be adapted to the respective operating condition or flow rate.
  • the valve cone has a first piston defining the larger loading area and a second piston defining the smaller loading area. Between the first and second pistons is a annular seat, preferably provided with at least approximately the size of the smaller loading surface.
  • the two pistons are guided displaceably sealed in corresponding bores and control the movements of the valve cone in dependence on the two pilot pressures and the force of a spring acting in the opening direction.
  • a concavely rounded cone transition is provided between the seating surface on the valve cone and the first piston.
  • the cone transition ensures a clean flow when opening the seat valve.
  • a constriction may be provided between the seat surface and the second piston, preferably a concavely rounded constriction. This flow channel defined via the constriction serves to guide the flow when opening the directional seat valve.
  • the seat is conical, preferably with a cone angle of about 70 °.
  • the valve seat may also be correspondingly conical, or slightly spherical, to ensure the leak-free shut-off. On the seat can follow in the direction of the cone transition, a cylindrical approach, and then another conical surface. This is due to manufacturing (grinding) and also represents an advantageous Hubhoff for the opening process.
  • the valve cone is arranged in one of the stepped bore contained in the valve seat.
  • the stepped bore has, preferably, two stepped bore portions, with lateral channels leading to the stepped bore.
  • the stepped bore is contained in a bush, which has a plurality of outer and spaced sealing regions, and can be inserted into a simple inner bore, for example, of a housing.
  • the bush is arranged sealed in the housing in an inner bore having two annular channels.
  • To an annular channel pass channels which are connected to a pressure source port and a valve assembly port of the housing, while the other annular channel is connected via a channel with a reservoir port of the housing.
  • a continuous Buchommes screw can be set, for. B. for ease of installation, while a free inner bore end is closed by a screw plug, on the one hand allows the convenient mounting of the components of the directional seat valve in the housing, and on the other hand with the derived between the pressure source and the throttle Control pressure acted upon control chamber limited.
  • the control pressure acts on the larger actuation surface of the valve cone via the continuous Buchsentechnischsschraube.
  • the piston of the valve cone defining the larger loading surface may be guided with a sliding fit in the stepped bore, without any special further sealing, since the control pressure in the control chamber is in the shut-off position of the directional seat valve in contrast to the supply pressure.
  • the spring which holds the poppet in the open position in the depressurized state of the control device can advantageously be arranged on the second piston defining the smaller impingement surface and be supported on the base of the inner bore. Thanks to the guidance of the second piston in the stepped bore, the spring is also aligned.
  • the throttle, the spring and the loading surfaces on the valve cone are matched to one another such that upon switching on the pressure source with a start of a drive motor of the pressure source, preferably a single-phase AC motor, facilitating delay first a predetermined pressure difference across the throttle or a predetermined volume flow through the throttle is generated before the outflow to the reservoir is shut off leak-free.
  • a "soft" response of the pressure switch is achieved without having to arrange further structural measures for this function in the control device.
  • both the pressure applied by the valve assembly pressure decreases to the reservoir, as well as the pending from the pressure source forth pressure, the latter via the throttle.
  • the pressure applied to the valve assembly may possibly be maintained via a check valve.
  • the throttle For smaller units with low flow and high pressure, the throttle generates only a negligible back pressure or a small pressure difference when starting the drive motor. Only at approx. 3 ⁇ 4 of the pump delivery flow is the ⁇ p large enough (approx. 5 to 10 bar) and the directional seat valve moves into the shut-off position. Now promotes the pressure source through the throttle to the valve assembly, with only a negligible loss of a few percent is to be accepted.
  • a hydraulic control device H has in Fig. 1 a 3/2-way spool valve 1 between a pressure source P and a valve assembly, not shown (from the valve assembly pending pressure P1) on.
  • the control member of the 3/2-way spool valve 1 connects in the pressureless state of the hydraulic control device H P1 with a reservoir R, while P is shut off. This control position is supported by a spring.
  • the control member of the 3/2-way shift valve 1 is acted upon from a pilot control line 2 with a control pressure derived from P in the direction of the second control position, and acted upon by a derived from P1 via a control line 3 control pressure parallel to the spring to the first control position.
  • the pressure source P is for example a pump and is driven by a not shown on and off electric motor. From the valve arrangement, not shown, at least one hydraulic consumer is controlled.
  • the pressure P1 to R is reduced.
  • the connection from P to P1 is blocked.
  • the counterforce of a spring until the 3/2-way spool valve switches to the second control position.
  • This back pressure must overcome the drive motor, which can lead to problems, for example, with a single-phase AC motor.
  • the pressure switch W can therefore be assigned an auxiliary volume 4. In a chamber in the control line 3 is against the force of a spring 6, a piston 5 slidably.
  • the auxiliary volume 4 is filled via the control line 3, wherein the piston 5 is displaced against the spring 6, so that the drive motor can start more easily.
  • Purpose of the pressure switch W is also to reduce the pressure applied by the valve assembly P1 then to the reservoir R when the drive motor is turned off.
  • Fig. 2 shows a hydraulic control device H according to the invention with a pressure switch W, which has a "soft" response without additional structural measures to allow a drive motor M of the pressure source P, regardless of the respective maximum pressure, eg to about 700 bar, initially without significant back pressure start , And only then build the desired supply pressure P1 to the valve assembly V when the drive motor M has reached a certain speed and is powerful enough or reaches the flow rate about 3 ⁇ 4 of the respective maximum.
  • a pressure switch W which has a "soft" response without additional structural measures to allow a drive motor M of the pressure source P, regardless of the respective maximum pressure, eg to about 700 bar, initially without significant back pressure start , And only then build the desired supply pressure P1 to the valve assembly V when the drive motor M has reached a certain speed and is powerful enough or reaches the flow rate about 3 ⁇ 4 of the respective maximum.
  • a main channel 10, 12 is provided in a housing 21 of the pressure switch W.
  • a discharge path 13 branches off to a reservoir line 20 and a reservoir R.
  • a 2/2-way seat valve 14 is arranged, the pressure-dependent between a first control position (passage position) as in Fig. 2 shown, and a second control position (leak-free shut-off position, not shown) is switchable, and a control member 16 includes.
  • the second control position (leak-free shut-off position) is leak-tight in this case in both directions of flow.
  • the control member 16 of the 2/2-way seat valve 14 is acted upon in the direction of the first control position by a spring 17 and parallel thereto from a control line 15 by a control pressure.
  • the control line 15 branches off from the Abströmweg 13.
  • the control member 16 is acted upon by the pilot pressure in a control line 18 which branches off at a node 19 of the portion 10 of the main channel 10, 12, between the pressure source P and a throttle D, which is between the node 19th and 11 is arranged.
  • the throttle D is used to produce a predetermined pressure drop .DELTA.p, even while the pressure source P still promotes the reservoir line 20, and is built up in the control line 18 sufficient control pressure against adjusts the control pressure in the control line 15 and against the force of the spring 17, the second control position (leak-free shut-off). Only then is the supply pressure P1 to the valve assembly V built up in full and the maximum delivery rate is reached. This facilitates the drive motor M starting from a standstill, since the pressure build-up in the main channel 10, 12 takes place with a predetermined delay, ie, after a predetermined pressure difference Ap (eg, about 5-10 bar) or a certain volume flow with delay through the throttle D was built.
  • a predetermined pressure difference Ap eg, about 5-10 bar
  • the throttle D may have a fixed throttle cross section 30, or, as indicated at 30 'by dashed lines, an adjustable throttle cross section, and is e.g. depending on the maximum flow rate selected.
  • the Fig. 3 to 6 illustrate a concrete embodiment of the pressure switch W, for example, in the in Fig. 2 indicated block-shaped housing 21 is housed.
  • the housing 21 has an inner bore 22 which terminates blind, and in which a socket 23 is fixed sealed.
  • a valve plug 24 is guided displaceably and sealed, which cooperates with a formed in the socket 23 valve seat 25.
  • the bushing 23 is positioned in the stepped bore 22, for example, by a continuous bolt lock screw 26.
  • the free end of the inner bore 22 is closed by a sealing screw plug 27, delimiting a control chamber to which the control line 18 leads from the node 19.
  • the control line 15, however, leads to the lower blind end of the inner bore 22.
  • the spring 17 is arranged.
  • the inner bore 22 has, for example, two ring channels.
  • the upper ring channel in Fig. 3 is connected to the sections 10, 12 of the main channel, while the lower annular channel is connected to the reservoir line 20.
  • the socket 23 ( Fig. 6 ) has in alignment with the annular channels in the housing 21 corresponding lateral passages.
  • Fig. 4 are in a parallel opposite Fig. 3 offset vertical section in another sectional plane two passages 28 visible, which serve for securing the housing 21, for example, to the pressure source and / or to the valve assembly.
  • the throttle D in the form of a throttle screw 29 with the fixed throttle section 30 (eg, 0.8 mm diameter) screwed, for example, adjacent to the node 11 at which branches off the Abströmweg 13.
  • the poppet 24 has a first piston 32 defining a larger engagement surface A1 (diameter d1) and a second piston 50 axially spaced therefrom defining a smaller engagement surface A2 (pressure gauge d2).
  • a seat 34 is formed, for example, a seat with a conical shape and a cone angle ⁇ of about 70 °.
  • a circular-cylindrical projection 35 adjoins the seat surface 34, followed by another short, conical surface 36.
  • the conical surface 36 is converted into a concave rounded cone transition 37, which eventually enters the first piston 32 with increasing diameter.
  • a constriction 38 is provided, which, preferably, is concavely rounded.
  • a projection 33 is formed, which is used for positioning and supporting the spring 17 (FIG. Fig. 3 ) serves.
  • the poppet 24 is in the in Fig. 6 shown socket 23 (see Fig. 3 ) mounted displaceably.
  • the bushing 23 has a plurality of sealing grooves 40 on the outside, and optionally also an undercut 48 at the lower end, each for positioning a ring seal (not shown) to the different pressure ranges of the sleeve 23 in the inner bore 22 in the housing 21 (FIGS. Fig. 3 ) against each other.
  • a stepped bore 39 is formed, which has an overhead stepped bore portion 41 for the piston 32, an intermediate portion 42 to the valve seat 25, and a smaller diameter stepped bore portion 44 for guiding the second piston 50.
  • annular groove 46 is formed for at least one annular seal 47, which seals the second piston 50 on the outer periphery and pressure tightness between side inlets 45 in the stepped bore portion 44 and the lower end of the sleeve 23 ensures.
  • annular seal 47 In the intermediate section 42 open lateral inlets 43rd
  • the lateral passages 43 and 45 respectively open into an annular channel in the housing 21 (FIG. Fig. 3 ) wherein a ring channel 49 for the lateral passages 45 dashed in Fig. 6 is indicated.
  • the side passages 43 are connected to the pressure source P and the pressure P present at the valve assembly V, while in the annular chamber 49 and the lateral passages 45, the connection to the reservoir R is established.
  • the two pressures P and P1 are in the shut-off position in the stepped bore section 41 or intermediate section 42 and the constriction 37 at.
  • the larger Beaufschlagungs constitutional A1 is from the control line 18 with the control pressure acted upon, while the second piston 50 can be acted upon on the smaller loading surface A2 with the control pressure from the control line 15.
  • the spring 17 acts via the projection 33 on the second piston 50 in the opening direction of the valve cone 24.
  • the closing force generated depends on the pressure difference across the throttle 30.
  • the closing force could also be selected as a function of pressure, if d2 is chosen smaller than the seat cross-section. Then, the force of the spring 17 (for opening) can be set higher.
  • A1 and A2 (d1 and d2) could be made approximately equal in size, and / or the seat cross-section (d3) could be made larger than A1 (d2).
  • the relative dimensions are e.g. However, depending on the application and / or start-up behavior of the drive motor, all are included in the invention.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Regulating Braking Force (AREA)
  • Safety Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)
  • Control Of Fluid Pressure (AREA)

Claims (14)

  1. Dispositif de commande hydraulique (H) comprenant un parcours d'écoulement d'échappement (13) et un étranglement (D), dispositif de commande hydraulique (H)
    qui, en service, pour l'alimentation en pression d'au moins un élément récepteur ou consommateur à partir d'une source de pression (P) pouvant être mise à l'arrêt et par l'intermédiaire d'au moins un agencement de vanne (V), est agencé entre la source de pression (P) et un réservoir (R) d'une part et l'agencement de vanne (V) d'autre part, et présente une balance de pression (W), qui est agencée dans le parcours d'écoulement d'échappement (13) au moins de l'agencement de vanne (V) au réservoir (R), et qui, pour une source de pression (P) à l'arrêt, relie l'agencement de vanne (V) au réservoir (R) par l'intermédiaire du parcours d'écoulement d'échappement (13), et pour une source de pression (P) en marche et établissant une pression d'alimentation, ferme le parcours d'écoulement d'échappement (13) vers le réservoir (R),
    dans lequel la balance de pression (W) renferme un organe de commande (16) réglable, qui, dans une première direction de réglage vers une position de commande ouvrant le parcours d'écoulement d'échappement (13) vers le réservoir (R), est sollicité par un ressort (17) et une pression de commande dérivée de la pression régnant au niveau de l'agencement de vanne (V), et, dans une deuxième direction de réglage vers une position de commande fermant le parcours d'écoulement d'échappement (13), est sollicité par une pression de commande dérivée de la pression d'alimentation, et
    dans lequel la balance de pression (W) est une vanne à siège 2/2 voies (14) comprenant une position de fermeture exempte de fuites, un cône de vanne (24) qui forme l'organe de commande (16), et un siège de vanne (25) agencé dans le parcours d'écoulement d'échappement (13), et la commande de pression sollicitant le cône de vanne (24) dans la deuxième direction de réglage vers le siège de vanne (25), est dérivée de la pression d'alimentation entre la source de pression (P) et l'étranglement (D),
    caractérisé en ce que la source de pression (P) est reliée en permanence à l'agencement de vanne (V) par l'intermédiaire de l'étranglement (D), en ce que le parcours d'écoulement d'échappement (13) renfermant la balance de pression (W) est dérivé vers le réservoir (R) entre l'étranglement (D) et l'agencement de vanne (V), et en ce que la pression de commande sollicitant le cône de vanne (24) de la balance de pression (W) dans la première direction de réglage, est dérivée de la pression régnant entre l'étranglement (D) et l'agencement de vanne (V).
  2. Dispositif de commande hydraulique selon la revendication 1, caractérisé en ce que le cône de vanne (24) présente pour les deux pressions de commande, des surfaces sollicitées en pression (A1, A2) différentes, de manière telle, que la surface sollicitée en pression (A2) pour la pression de commande sollicitant le cône de vanne (24) dans la première direction de réglage, soit plus petite que la surface sollicitée en pression (A1) pour la pression de commande sollicitant le cône de vanne (24) dans la deuxième direction de réglage, le rapport des surfaces sollicitées en pression A1 : A2, prenant de préférence une valeur entre 2 : 1 et 4 : 1, de préférence d'environ 3 : 1.
  3. Dispositif de commande hydraulique selon la revendication 1, caractérisé en ce que le cône de vanne (24) présente pour les deux pressions de commande, des surfaces sollicitées en pression (A1, A2) au moins approximativement de même grandeur.
  4. Dispositif de commande hydraulique selon la revendication 2, caractérisé en ce que le cône de vanne (24) est rendu étanche entre la surface sollicitée en pression (A2) la plus petite et le siège de vanne (25), par au moins un élément d'étanchéité annulaire (47).
  5. Dispositif de commande hydraulique selon la revendication 1, caractérisé en ce que l'étranglement (D) présente une section d'étranglement (30) fixée, et est agencé, de préférence de manière interchangeable, dans un canal principal reliant la source de pression (P) et l'agencement de vanne (V).
  6. Dispositif de commande hydraulique selon la revendication 1, caractérisé en ce que l'étranglement (D) présente une section d'étranglement (30') variable.
  7. Dispositif de commande hydraulique selon l'une au moins des revendications précédentes, caractérisé en ce que le cône de vanne (24) présente un premier piston (32) définissant la plus grande surface sollicitée en pression (A1, d1), et un deuxième piston (50) définissant la plus petite surface sollicitée en pression (A2, d2), et en ce qu'entre les pistons (32, 50) est prévue une surface de siège (34, d3) de forme annulaire, de préférence avec une grandeur correspondant environ à celle de la surface sollicitée en pression la plus petite (A2) ou plus grande que celle-ci.
  8. Dispositif de commande hydraulique selon la revendication 7, caractérisé en ce qu'entre la surface de siège (34) et le premier piston (32), est prévu une transition conique arrondie (37), concave, et entre la surface de siège (34) et le deuxième piston (50), est prévu un rétrécissement (38), de préférence un rétrécissement arrondi de manière concave.
  9. Dispositif de commande hydraulique selon la revendication 7, caractérisé en ce que a surface de siège (34) est conique, de préférence avec un angle de cône (a) d'environ 70°, et en ce qu'à la surface de siège (34) succèdent, en direction de la transition conique (37), un embout cylindrique (35) et une autre surface conique (36).
  10. Dispositif de commande hydraulique selon l'une au moins des revendications précédentes, caractérisé en ce que le cône de vanne (24) est agencé dans un alésage étagé (39) contenant le siège de vanne (25), de préférence dans une douille (23), qui renferme l'alésage étagé (39) comprenant deux tronçons d'alésage étagé (41, 44) ainsi que des canaux latéraux (43, 45) menant aux tronçons d'alésage étagé (42, 44), et qui, de préférence, possède sur l'extérieur, des zones d'élément d'étanchéité annulaire (40, 48) espacées mutuellement.
  11. Dispositif de commande hydraulique selon la revendication 10, caractérisé en ce que la douille (23) est logée dans un alésage intérieur (22) d'un boitier (21), qui présente deux canaux annulaires, en ce qu'à un canal annulaire sont raccordés des canaux vers un raccord de source de pression (P) et un raccord d'agencement de vanne (P1), et à l'autre canal annulaire est raccordé un canal vers un raccord de réservoir (R), en ce que dans l'alésage intérieur (22) est fixée une vis d'arrêt de douille (26) à passage traversant, et en ce qu'une extrémité libre d'alésage intérieur est fermée par une vis d'obturation (27) délimitant une chambre de commande, qui est destinée au piston (32) définissant la plus grande surface sollicitée en pression (A1), et qui peut être alimentée par la pression de commande dérivée entre la source de pression (P) et l'étranglement (D).
  12. Dispositif de commande hydraulique selon l'une au moins des revendications précédentes, caractérisé en ce que l'étranglement (D) se présente sous la forme d'un étranglement à visser, et est vissé dans le canal (31) du boitier (21), qui est relié au raccord de source de pression (P).
  13. Dispositif de commande hydraulique selon la revendication 1, caractérisé en ce que le ressort (17) est agencé au niveau du deuxième piston (50) pouvant être sollicité par la pression de commande dérivée de la pression (P1) régnant au niveau de l'agencement de vanne (V).
  14. Dispositif de commande hydraulique selon l'une au moins des revendications précédentes, caractérisé en ce que l'étranglement (D), le ressort (17) et les surfaces sollicitées en pression (A1, A2) sur le cône de vanne (24), sont adaptés mutuellement les uns aux autres de façon telle, que lors de la mise en marche de la source de pression (P), on engendre tout d'abord une différence de pression (ΔP) prédéterminée par l'intermédiaire de l'étranglement (D) ou un débit volumique prédéterminé à travers l'étranglement (D), avant la fermeture sans fuites du parcours d'écoulement d'échappement (13) vers le réservoir (R), en définissant ainsi un retard facilitant le démarrage du moteur d'entraînement (M) de la source de pression, de préférence un moteur à courant alternatif monophasé.
EP20090007207 2009-04-17 2009-05-29 Dispositif de commande hydraulique et balance de pression pour ledit dispositif Active EP2241763B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP20090007207 EP2241763B1 (fr) 2009-04-17 2009-05-29 Dispositif de commande hydraulique et balance de pression pour ledit dispositif
US12/748,954 US8549853B2 (en) 2009-04-17 2010-03-29 Hydraulic control device and pressure switch
CN2010101674249A CN101956731B (zh) 2009-04-17 2010-04-19 液压控制装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP09005476 2009-04-17
EP20090007207 EP2241763B1 (fr) 2009-04-17 2009-05-29 Dispositif de commande hydraulique et balance de pression pour ledit dispositif

Publications (3)

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EP2241763A2 EP2241763A2 (fr) 2010-10-20
EP2241763A3 EP2241763A3 (fr) 2012-10-24
EP2241763B1 true EP2241763B1 (fr) 2014-05-14

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US (1) US8549853B2 (fr)
EP (1) EP2241763B1 (fr)
CN (1) CN101956731B (fr)
ES (1) ES2471920T3 (fr)

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EP2674626B1 (fr) * 2012-06-12 2015-09-30 HAWE Hydraulik SE Circuit hydraulique
DE102017200212B4 (de) * 2017-01-09 2021-12-16 Hawe Hydraulik Se Zweistufenpumpe mit Umschaltventil
CN111577677B (zh) * 2020-05-28 2022-03-01 中国铁建重工集团股份有限公司 一种压力补偿系统

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Also Published As

Publication number Publication date
US20100263363A1 (en) 2010-10-21
CN101956731A (zh) 2011-01-26
EP2241763A3 (fr) 2012-10-24
CN101956731B (zh) 2013-10-30
EP2241763A2 (fr) 2010-10-20
ES2471920T3 (es) 2014-06-27
US8549853B2 (en) 2013-10-08

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