EP2339185B1 - Commande hydraulique - Google Patents

Commande hydraulique Download PDF

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Publication number
EP2339185B1
EP2339185B1 EP20090015873 EP09015873A EP2339185B1 EP 2339185 B1 EP2339185 B1 EP 2339185B1 EP 20090015873 EP20090015873 EP 20090015873 EP 09015873 A EP09015873 A EP 09015873A EP 2339185 B1 EP2339185 B1 EP 2339185B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
line
switched
pumps
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP20090015873
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German (de)
English (en)
Other versions
EP2339185A1 (fr
Inventor
Georg Neumair
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.)
Hawe Hydraulik SE
Original Assignee
Hawe Hydraulik SE
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
Application filed by Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP20090015873 priority Critical patent/EP2339185B1/fr
Priority to ES09015873T priority patent/ES2401560T3/es
Publication of EP2339185A1 publication Critical patent/EP2339185A1/fr
Application granted granted Critical
Publication of EP2339185B1 publication Critical patent/EP2339185B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low capacity
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20592—Combinations of pumps for supplying high and low pressure
    • 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
    • F15B2211/265—Control of multiple pressure sources
    • F15B2211/2654—Control of multiple pressure sources one or more pressure sources having priority
    • 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
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • 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
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control 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
    • 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
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
    • 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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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

Definitions

  • the invention relates to a hydraulic control specified in the preamble of claim 1. Art.
  • the larger flow rate of a pump via a circulation valve to the tank is derived as soon as there is a predetermined pressure value in the main line.
  • the circulation valve is switched by a spring into the blocking position, so that the blocking position is present as long as there is no system pressure. Consequently, the common drive motor of the pumps must start against counterpressure, which is unfavorable for an AC motor, for example. Further, since the circulation valve operates leak-prone, after the pump with the larger flow rate promotes the tank, the pump with the smaller flow rate compensate for this leakage, which may mean that the total achievable with the smaller flow maximum pressure is limited or achieved only slowly or can not be kept.
  • the invention has for its object to improve a hydraulic control of the type mentioned in that u. a.
  • the following requirements can be met: When the pumps are switched off, the main line and the pumps should be depressurised. When starting, there should be no back pressure until a high-performance speed is reached. If only the pump with the smaller flow rate feeds the main line, no leakage should occur to achieve very high working pressures at the consumer with relatively small flow and can hold.
  • the pressure switch always works the same way and so that with the pressure unit off the pump, the discharge lines from the pumps and the main line to Tank are relieved, and the locking position with a delay and soft is switched so that the drive motor is able to start without counter-pressure. As soon as the blocking position is switched, all flow rates can be used by the consumer. Once the predetermined pressure level is reached in the main line, the larger pressure flow is derived from the pressure switch to the tank, and is generated with the smaller flow rate very high working pressure.
  • the throttle which is assigned to only one pump or pressure stage, advantageously with the lowest flow or for the maximum pressure, always acts so that the same pressure difference generated and from this pressure difference, the control pressures are generated, which switch the pressure switch to the blocking position, wherein of the
  • Cross section of the restrictor specifically for the pump with the smaller flow rate or the smallest flow rate or the highest Pressure level is matched, on the one hand, the correct soft switching of the pressure switch is ensured, and on the other hand, the pressure difference at high working pressure is negligible.
  • Leakage is reliably avoided in the blocking position of the pressure switch when the pressure switch is a 2/2-way seat valve with leak-tight dense blocking position, which has a valve seat arranged to the passage position of a spring-loaded valve cone and arranged in the discharge line.
  • valve cone has different sized pressurizing surfaces, for example, such that the loading surface for acting in the switching direction to the passage position control pressure is smaller than the loading surface for acting in the switching direction to the blocking position control pressure, for example, with the lowest possible pressure difference to ensure the proper functioning of the pressure switch via the throttle.
  • the ratio of the loading areas may be between about 2: 1 and 4: 1, and is, preferably, about 3: 1.
  • valve cone in the pressure switch for at least two control pressures could have at least approximately equal loading surfaces.
  • the throttle cross-section of the throttle is fixed.
  • the throttle is arranged interchangeable in the pressure line, for example, depending on the lower flow rate and the maximum expected maximum pressure to use a suitable throttle.
  • the throttle could be an adjusting throttle whose throttle cross-section is adjustable as needed.
  • the throttle cross-section of the throttle, the force of the spring of the valve cone and the loading surfaces on the valve cone are matched to one another such that when switching on by a common drive motor, preferably a single-phase AC motor, drivable pumps at first via the pressure switch located in the passage position to the tank unloaded main line the delay of the start of the drive motor facilitating delay is generated up to the blocking position from a pressure of only about 5 bar to 10 bar pressure difference across the throttle.
  • a common drive motor preferably a single-phase AC motor
  • the resulting delay is sufficient to first accelerate the drive motor to a sufficiently powerful speed, or to compensate for the poor efficiency of, for example, the pump with the lower or lowest flow rate forming gear pump at a speed up to 300 U / min before the blocking position the pressure switch is switched and the pressure build-up in the main line begins.
  • a further non-return valve blocking in the flow direction to the discharge line can be arranged between the main line and the control valve device of the hydraulic consumer so that the system pressure is maintained at the control valve device and only the main line, the pressure lines and the pumps are depressurized when the pressure source unit is switched off.
  • An expedient embodiment of the hydraulic control may be composed of a plurality of connected block sections, wherein a first block section ports for the pumps and the tank and the shut-off valve, the maximum pressure relief valve, the check valve and the throttle, a second block section the pressure switch, and a third block section the further check valve and the control valve means for the hydraulic consumer.
  • These block sections can be equipped with inexpensive standard hydraulic components.
  • a hydraulic control which is fed from a pressure source unit with several pumps of different flow rates, relieve the main line and the pumps with switched-off pressure source unit via a pressure switch to the tank and switch the pressure switch via a throttle with delay to the blocking position, which is associated with the pump with the lowest flow rate or the maximum pressure level and is not affected by the flow rate of each additional pump.
  • a hydraulic control H in Fig. 1 for at least one consumer V (for example, a double-acting differential cylinder) is fed by operated in shutdown pressure source unit Q having at least two pumps P1, P3 with different flow rates, which suck from a tank R and are driven by a common drive motor M.
  • the drive motor M may be a single-phase AC motor, which starts with difficulty against load.
  • the hydraulic control H is composed, for example, in block construction of three block sections I, II, III, which are penetrated by a continuous main line P and a continuous tank line 6.
  • the pumps P1, P3 are connected via separate pressure lines 2, 3 to a node 1 of the main line P.
  • the pump P1 has a smaller flow rate than the pump P3.
  • the pump P1 is, for example, a high-pressure pump, for example a gear pump, with which a working pressure up to, for example, 800 bar can be generated.
  • a drain line 5 from the tank R in which a shut-off valve 7 (spring-loaded pressure relief valve) is arranged, which can be controlled against the spring from a pilot line 9 with control pressure, the a node 8 is tapped off downstream of the node 1 in the main line P via a diaphragm 10.
  • a check valve 40 is arranged, which blocks in the flow direction to the pump P3.
  • a throttle 23 is arranged in the pressure line 2, however, upstream of the node 1 and downstream of a node 22, a throttle 23 is arranged.
  • the throttle 23 may, if it has a fixed throttle cross section, be placed interchangeably in the pressure line 2, or may be an adjusting throttle whose throttle cross-section can not be changed as needed.
  • the throttle cross section of the throttle 23 is adapted to the smaller flow rate of the pump P1 so that a certain pressure difference, for example of about 5 bar to 10 bar, is generated, which is used to a arranged in the block section II pressure switch 16 only in dependence To control operation of the pump P1 with the lower flow rate and the lowest flow rate.
  • a further discharge line 12 branches off at a node 11 to the tank R, in which a maximum pressure limiting valve 13 is arranged, which can be actuated against an adjustable spring from the main line P.
  • the shut-off valve 7 is designed for example to a response pressure between 10 bar and 150 bar, while the maximum pressure relief valve 13 is set to a response pressure up to 800 bar can be.
  • node 14 of the main line P branches off a discharge line 15 to the tank R (to the tank line 6), in which the pressure switch 16 is arranged.
  • the pressure switch 16 has the task, with switched-off pressure source unit Q, the pressure lines 2, 3 and the main line P to relieve the tank, and shut off the discharge line 15 after switching on the pressure source unit Q with a predetermined delay, namely leak-tight shut off.
  • a predetermined delay namely leak-tight shut off.
  • the pressure switch 16 is a 2/2-way seat valve with a leakage-tight in both directions of flow blocking position 17 and a substantially unthrottled passage position 18.
  • the 2/2-way seat valve is connected by a spring 19 in the switching direction to the passage position 18 and parallel to it from a control line 20th acted upon by the node 14 and the pressure line P forth, ie the pressure downstream of the aperture 23, and in the switching direction to the blocking position 17 from a control line 21 which is connected to the node 22 and a control pressure corresponding to the pressure upstream of the aperture 23 picks up.
  • a further check valve 24 is arranged in the main line P, which blocks in the flow direction to the node 14.
  • the block section III includes a control valve device 25 for the consumer V, which is connected via working lines A, B to the control valve device 25.
  • the working line B leads a connecting line 26 to the tank R and the tank line 6, via a pressure relief valve 27, which is adjustable to a response pressure of 10 bar to 300 bar, for example.
  • the control valve device 25 is in the embodiment shown, a 4/2-way valve, which is operated either manually or by a magnet or a magnet and a pressure precontrol against spring force and at least for directional control of the consumer V is used.
  • the pumps P1, P3 deliver different flow rates, the summed act on the main line P and, since the pressure switch 16 is in the passage position shown, are led to the tank R.
  • a predetermined pressure difference which acts on the pressure switch 16 via the control lines 21 and 20, occurs at the throttle 23. Since the control pressure in the control line 21 is higher than the control pressure in the control line 20, as soon as a predetermined pressure difference of, for example, 5 bar to 10 bar has been generated at the throttle 23, and the pressure switch 16 is switched to the blocking position, so that the Relief line 15 is shut off.
  • both pumps pump P1, P3, the pressure switch 16 is switched with a predetermined delay in the blocking position, which lasts until the predetermined pressure difference has been generated via the throttle 23 from the pump P1.
  • an increasing pressure builds up in the main line P, which, when a predetermined pressure value is reached, causes the shut-off valve 7 to be switched from the blocking position shown (via the control line 9), so that the larger flow rate of the pump P3 is discharged to the tank R and the check valve 40 is in the blocking position, so that the pressure line 3 is isolated at node 1 from the main line P and the pressure line 2. Only the lower flow rate of the pump P1 is passed in the main line P to the control valve device 25.
  • the pressure switch 16 in the shut-off position 17 leak-tight, no leaks occur on the pressure switch 16, so that (the check valve 40 closes leak-tight from tight) the lower flow rate of the pump P1 is sufficient to reach the desired maximum pressure up to 800 bar. Only then does the maximum pressure limiting valve 13 respond.
  • the required maximum pressure for the consumer V is expediently at about 700 bar, so that the maximum pressure relief valve 13 only responds, if the risk of damage should occur.
  • the load V can be moved thanks to the large total delivery, for example, in rapid traverse. Thereafter, the pressure is built up to the required maximum pressure only with the lower flow rate of the pump P1.
  • the further check valve 24 blocks and eliminates the pressure difference across the throttle 23, so that the Pressure switch 16 is switched by the spring 19 back into the passage position shown.
  • the pressure lines 2, 3 and the main line P are relieved again via the discharge line 15 to the tank R and the tank line 6.
  • the pressure switch 16 (corresponding to the block section II in Fig. 1 ) is formed with a block-shaped housing 28 in which a valve seat 29 is provided in an inner chamber (a sleeve inserted into a bore), which cooperates with a seat surface 35 of a valve cone 32.
  • the poppet 32 (shown in the blocking position of the pressure switch 16) has at both ends Beaufschlagungs vom A1, A2 for the control pressures from the control lines 21, 20 which are connected to housing chambers 33 and 34, respectively.
  • the loading surface A1 for the control pressure from the control line 21 is formed on the valve cone 32 larger than the loading surface A2 for the control pressure from the control line 20.
  • the ratio A1: A2 for example, be about 3: 1.
  • An annular chamber 30 in the housing 28 is connected, for example, to the main pipe P, while an annular chamber 31 in the housing 28 is connected to the tank pipe 6 and the tank R.
  • Fig. 3 illustrates the connection diagram on an outer side of the housing 28, wherein the control pressure is fed from the upstream of the throttle 23 to a connection representing the control line 21, from the pressure line P an opening is visible, as well as from the working lines A, B and the connecting line 26th , which pass through the housing 28, as well as the tank line 6, which is connected to the tank R.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (9)

  1. Commande hydraulique (H), comprenant au moins un consommateur (V), au moins deux pompes (P1, P3), des conduites sous pression (2, 3) séparées, un noeud (1), un système de soupape de distribution (25), une conduite principale (P), une soupape anti-retour (40), une conduite d'échappement (5) et une soupape d'arrêt (7), le consommateur (V) pouvant être alimenté à partir d'un groupe de sources de pression, qui présente les au moins deux pompes (P1, P3) de débits de refoulement différents, connectables ou déconnectables conjointement, et dont les pompes (P1, P3) sont raccordées par l'intermédiaire des conduites sous pression séparées (2, 3) à un noeud (1) de la conduite principale (P), guidée en direction d'un système de soupape de distribution (25) du consommateur (V), une soupape anti-retour (40), qui ferme en direction de la pompe (P3), étant disposée dans la conduite sous pression (3) de la pompe (P3) de débit de refoulement plus élevé et une conduite d'échappement (5) étant montée en dérivation de cette conduite sous pression (3) en direction du réservoir (R), laquelle conduite d'échappement comporte une soupape d'arrêt (7) actionnable par la pression pilote de la conduite principale (P), pour dériver, dès qu'une valeur de pression prédéfinie dans la conduite principale (P) est atteinte, le débit de refoulement plus élevé en direction du réservoir (R), caractérisée en ce qu'un aiguillage de pression (16), commutable entre une position de passage (18) et une position d'arrêt (17) étanche et sans fuite, est disposé dans une conduite de détente (15) s'étendant de la conduite principale (P) en direction du réservoir (R), lequel aiguillage peut être sollicité, dans le sens de commutation de la position de passage, au moins par une pression pilote dérivée de la conduite principale (P) et, dans le sens de commutation de la position d'arrêt, par une pression pilote générée exclusivement par la pompe (P1) de débit de refoulement moins élevé, et se situe dans la position de passage lorsque les pompes (P1, P3) sont déconnectées, que la pression pilote, pour la sollicitation de l'aiguillage de pression (16) dans le sens de commutation de la position d'arrêt, est dérivée d'une différence de pression, qui peut être générée sur un étranglement (23), disposé dans la conduite sous pression (2) de la pompe (P1) de débit de refoulement moins élevé, en amont du noeud (1), et que la section transversale de l'étranglement (23) est adaptée au débit de refoulement moins élevé de telle sorte que l'aiguillage de pression (16), lors de la connexion des pompes (P1, P3), peut être amené avec retard dans la position d'arrêt (17).
  2. Commande hydraulique selon la revendication 1, caractérisée en ce que l'aiguillage de pression (16) est une soupape à siège à 2/2 voies avec un cône de soupape (32), sollicité par un ressort (19) en direction de la position de passage, et un siège de soupape (35), disposé dans la conduite de détente (15).
  3. Commande hydraulique selon la revendication 2, caractérisée en ce que le cône de soupape (32) présente des surfaces de sollicitation en pression (A1, A2) différemment grandes pour les pressions pilotes, la surface de sollicitation (A2), pour la pression pilote sollicitant dans le sens de commutation de la position de passage, étant plus petite que la surface de sollicitation (A1), pour la pression pilote sollicitant dans le sens de commutation de la position d'arrêt, de préférence avec un rapport des surfaces de sollicitation (A1, A2) compris entre environ 2 : 1 et 4 : 1, de préférence environ 3 : 1.
  4. Commande hydraulique selon la revendication 2, caractérisée en ce que le cône de soupape (32) présente pour les deux pressions pilotes des surfaces de sollicitation de dimensions au moins à peu près égales.
  5. Commande hydraulique selon la revendication 1, caractérisée en ce que la section transversale de l'étranglement (23) est fixée, et que l'étranglement (23) est disposé de façon interchangeable dans la conduite sous pression (2).
  6. Commande hydraulique selon la revendication 1, caractérisée en ce que la section transversale de l'étranglement (23) est ajustable.
  7. Commande hydraulique selon l'une au moins des revendications précédentes, caractérisée en ce que la section transversale de l'étranglement (23), la force du ressort (19) et les surfaces de sollicitation (A1, A2) sur le cône de soupape (32), sont mutuellement adaptées de telle sorte que, lors de la commutation du moteur de commande (M) commun des pompes (P1, P3), de préférence un moteur à courant alternatif monophasé, lorsque la conduite principale (P) est d'abord détendue en direction du réservoir (R) par l'intermédiaire de l'aiguillage de pression (16) situé dans la position de passage, le retard facilitant le démarrage du moteur de commande jusqu'à la position d'arrêt est généré par l'intermédiaire de l'étranglement (23) à partir d'une différence de pression d'environ 5 bars à 10 bars.
  8. Commande hydraulique selon la revendication 1, caractérisée en ce qu'une soupape anti-retour (24) supplémentaire, fermant dans la direction d'écoulement en direction de la conduite de détente (16), est disposée entre la conduite principale (P) et le système de soupape de distribution (25) du consommateur hydraulique (V).
  9. Commande hydraulique selon l'une au moins des revendications précédentes, caractérisée en ce qu'elle se compose de plusieurs sections de bloc assemblées (I, II, III), une première section de bloc (I) présentant des raccords pour les pompes (P1, P3) et le réservoir (R), ainsi que la soupape d'arrêt (7), la soupape de délimitation de pression limite (13), la soupape anti-retour (40) et l'étranglement (23), une deuxième section de bloc (II) présentant l'aiguillage de pression (16), et une troisième section de bloc (III) présentant la soupape anti-retour supplémentaire (29) et le système de soupape de distribution (25) pour le consommateur hydraulique (V).
EP20090015873 2009-12-22 2009-12-22 Commande hydraulique Not-in-force EP2339185B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20090015873 EP2339185B1 (fr) 2009-12-22 2009-12-22 Commande hydraulique
ES09015873T ES2401560T3 (es) 2009-12-22 2009-12-22 Control hidráulico

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20090015873 EP2339185B1 (fr) 2009-12-22 2009-12-22 Commande hydraulique

Publications (2)

Publication Number Publication Date
EP2339185A1 EP2339185A1 (fr) 2011-06-29
EP2339185B1 true EP2339185B1 (fr) 2013-02-13

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ES (1) ES2401560T3 (fr)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4112821A (en) 1976-12-03 1978-09-12 Caterpillar Tractor Co. Fluid control system for multiple circuited work elements
KR870000506B1 (ko) 1981-05-02 1987-03-12 니시모도 후미히라(西元文平) 토목 건설기계의 유압회로 시스템
DE69319400T2 (de) 1992-04-20 1998-12-03 Hitachi Construction Machinery Co., Ltd., Tokio/Tokyo Hydraulische schaltungsanordnung für erdbewegungsmaschinen

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ES2401560T3 (es) 2013-04-22

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