EP3135924B1 - Commande hydraulique - Google Patents

Commande hydraulique Download PDF

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Publication number
EP3135924B1
EP3135924B1 EP15182184.0A EP15182184A EP3135924B1 EP 3135924 B1 EP3135924 B1 EP 3135924B1 EP 15182184 A EP15182184 A EP 15182184A EP 3135924 B1 EP3135924 B1 EP 3135924B1
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EP
European Patent Office
Prior art keywords
pressure
signal circuit
load
consumer
spool valve
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.)
Active
Application number
EP15182184.0A
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German (de)
English (en)
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EP3135924A1 (fr
Inventor
Thomas Wechsel
Sascha Rümenap
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
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Hawe Hydraulik SE
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Priority to EP15182184.0A priority Critical patent/EP3135924B1/fr
Publication of EP3135924A1 publication Critical patent/EP3135924A1/fr
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Publication of EP3135924B1 publication Critical patent/EP3135924B1/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
    • 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
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
    • 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
    • F15B2211/30—Directional control
    • F15B2211/355—Pilot pressure control
    • 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
    • F15B2211/30—Directional control
    • F15B2211/36—Pilot pressure sensing

Definitions

  • the invention relates to a hydraulic control specified in the preamble of claim 1. Art.
  • the load pressure signal circuit is connected to the tank via at least one secondary pressure limiting valve which limits the load pressure tapped from the working line to an upper pressure limit which is significantly below the maximum consumer pressure.
  • the consumer port is assigned a hydraulically unlockable check valve, which is hydraulically unlocked even at maximum consumer pressure with the pressure limited in the load pressure signal circuit via the secondary pressure limiting valve.
  • the at least one secondary pressure limiting valve is required for these functions (fully deflecting, unlocking), which, due to its placement in a valve block and with the connecting bores, causes additional structural complexity and is a significant cost factor of the hydraulic control.
  • the invention has for its object to simplify a hydraulic control of the type mentioned structurally and cost-effective, and yet to ensure the same functions.
  • the proportional directional spool in the lowering position connects the pressure supply to the load pressure signal circuit and reports the pressure of the pressure supply into the load pressure signal circuit
  • the pressure source supplies sufficient pressure via the pressure from the pressure supply until the upper pressure limit is reached in the pressure supply.
  • the load pressure signal circuit is therefore no longer fed in the lowering position from a pressure line via the inlet pressure derived regulator, but from the pressure supply, so that initially only a limited pressure can prevail by the upper pressure limit in the load pressure signal circuit maintained by the pressure supply. This eliminates the need to incorporate at least one secondary pressure relief valve in the hydraulic control for this purpose.
  • the pressure supply can be supplied from the same pressure source as the proportional directional spool, or from a separate pressure source, such as an auxiliary pump.
  • a separate pressure source such as an auxiliary pump.
  • the pressure supply upstream of the proportional directional spool contains a pressure reducing valve connected to the pressure source, to which the upper pressure limit can be sensitively adjusted and by which this pressure limit can be reliably maintained.
  • the pressure reducing valve may also be useful for a separate pressure source for the pressure supply.
  • the consumer connection is assigned a blocking valve which closes in the lowering-outflow direction and which can be hydraulically unlocked in the lowering position of the proportional displacement valve by the pressure of the pressure supply reported in the load pressure signal circuit.
  • This check valve may be appropriate for safety reasons or according to the needs of the user.
  • the first and second flow paths can be continuously switched in the proportional directional valve in its lowering position.
  • the first flow path connects the pressure supply from the pressure source side to the consumer connection side.
  • the second flow path then connects the first flow path on the consumer side with the load pressure signal circuit on the pressure source side.
  • the pressure from the pressure supply is reported in the load pressure signal circuit.
  • the first flow path at the pressure source side in the proportional directional spool valve could be directly connected directly to the load pressure signal circuit at the beginning of the discharge into the lowered position. If a check valve is installed counter to, the first flow path leads the pressure of the pressure supply to unlock the check valve, while the second flow path feeds the pressure of the pressure supply into the load pressure signal circuit.
  • a third flow path is further provided in the proportional directional slide, which is continuously switchable in a neutral position and connects the first flow path or a port of the first flow path on the consumer side with the tank, so that not only the load pressure signal circuit is relieved, for example, to the tank pressure but then an unwanted hydraulic release of the check valve is excluded.
  • a constant displacement pump is used as the pressure source.
  • a circulation regulator which in the neutral position of the proportional directional spool via a largely pressureless circulation derived pressure fluid to the tank, although with minimal throttling loss and minimal heating of the pressure medium.
  • circulation regulators are standard in hydraulic controls with a constant-displacement pump as the pressure source if the non-pressurized circulation to the tank is not conducted via the proportional directional valve.
  • the pressure source is a variable displacement pump with a regulator of the variable displacement pump itself connected to the load pressure signal circuit.
  • the variable displacement pump delivers a low pressure of up to approximately 20 bar in stand-by mode.
  • the regulator automatically regulates the pressure of the variable displacement pump to the maximum consumer pressure according to the pressure in the load pressure signal circuit.
  • an upper pressure limit of the pressure supply ranges from 15 to 45 bar on average. This upper pressure limit ensures that, on the one hand, the proportional directional control valve is swiftly and fully deflected into the lowering position via its pressure precontrol, and also the required hydraulic unlocking of the optionally provided blocking valve.
  • the check valve on a Aufbericht fie with sufficient even with maximum consumer pressure of up to 400 bar a Entsperr founded corresponding to the upper pressure limit of the pressure supply.
  • Hydraulic controls (H) in the embodiments of Fig. 1 and 2 serve for example for controlling a single-acting hydraulic consumer (eg lifting cylinder), for example via a working line (31).
  • a double-acting hydraulic consumer could be controlled, the other working line is not shown.
  • FIG. 1 leads from a here designed as a fixed displacement pump with motor (M) for continuous operation pressure source (P) a pressure line (1) to a control line (1 ') and to a pressure supply (Z), which acted upon by a spring (10) in the opening direction pressure reducing valve (9). From the pressure source (P) also carries a pressure line (2) to a pressure regulator designed as a feed regulator (18) and from this to a port of a proportional directional spool (S). To the tank (R), not shown, a return line (3) is connected.
  • a circulation regulator (5) is arranged between the pressure line (1) and the return line (3), which is designed as a pressure balance, in the reverse direction by a spring (7) and a control line (8). and in the opening direction from the pressure line (1) via a control line (6) is acted upon.
  • the control line (8) is connected to a load pressure signal circuit (LS).
  • a system pressure limiting valve (4) is arranged between the pressure line (1) and the return line (3).
  • the pressure supply (Z) could not be supplied by the pressure source (P) but by a separate pressure source, e.g. an auxiliary pump.
  • a control line (11) leads to a connection of the proportional directional control valve (S) located at the pressure source side.
  • the proportional directional spool valve is shown in its neutral position (O), in which, apart from a third flow path (28) which is then connected continuously, all connections to the pressure source and consumer connection sides are shut off from a control line (21) to the return line (3).
  • a control line (12) leads to pressure pilot controls (16, 17) of the proportional directional spool (S), which are actuated by proportional magnets (14, 15) to the proportional directional spool in a lifting position (a) or to lower a lowering position (b).
  • the inlet regulator (18) is acted on its opening side by a spring and the load pressure signal circuit (LS) and on its closing side via a control line which branches off from the pressure line (2) downstream of the inlet regulator (18).
  • a pressure compensator (19) In the from the consumer side of the proportional directional spool (S) to the load port (A) extending working line (31) is a pressure compensator (19) and between the pressure compensator (19) and the consumer port (A) a hydraulically unlockable check valve (20) installed.
  • the pressure compensator (19) is acted upon via a control line (25) from the working line (31) on the closing side, and from a control line (24) and by a spring on the opening side.
  • From the check valve (20) can lead a leakage line (22) to the return line (3).
  • the control line (21) for the pressure pilot control (16, 17) leads to a connection (29) of the proportional directional spool on the consumer side and has a tap (21 ') there.
  • the load pressure signal circuit (LS) is optionally a shuttle valve (14 ') included, in the event that possibly load pressure signals of other, not shown and supplied by the pressure source (P) consumers, then fed into the load pressure signal circuit (LS), if these load pressure signals are higher than the pressure prevailing in the load pressure signal circuit (LS) only the proportional directional spool (S).
  • a flow path (23) is connected continuously, which connects the working line (31) with the return line (3).
  • a first flow path (26) is continuously connected, which connects the control line (11) from the pressure supply (Z) to the port (29) to the control line (21), and a second flow path (27 ) switched throughout, the here z. B. the tap (21 ') connects to the load pressure signal circuit (LS).
  • the check valve (20) could be omitted.
  • the embodiment of the hydraulic control (H) in Fig. 2 is different from that of Fig. 1 in that a variable displacement pump is used as the pressure source (P), which is adjustable via a conveyor controller (34) which is connected via a control line (30) to the load pressure signal circuit (LS).
  • the variable displacement pump eliminates the need for the circulation regulator (5) Fig. 1 ,
  • the further construction and the function of the hydraulic control (H) in Fig. 2 correspond to those of Fig. 1 ,
  • the pressure source (P) delivered a stand-by pressure of up to about 20 bar.
  • This pressure acts via the pressure reducing valve (9) approximately in the control line (11), so that deflected via the pressure pilot control (16) and the energized proportional magnet (14) of the proportional directional slide in the direction of the lowering position (b) becomes.
  • the first and second flow paths (26) and (27) are immediately switched continuously.
  • p-RK shut-off pressure
  • the pressure reducing valve (9) via the control line (1 ') in the control line (11) a pressure (pZ), for example, 45 bar a.
  • This pressure is sufficient to deflect the proportional directional spool (S) fully into the lowering position (b) via the pressure precontrol (16), in which the working line (31) in accordance with the energization of the proportional magnet (14) with the Return line (3) is connected, and also via a then continuous flow path (32), the control line (24) is connected to the return line (3).
  • the pressure reported via the pressure supply (Z) or the pressure reducing valve (9) into the load pressure signal circuit (LS) also prevails in the control line (21), so that the blocking valve (19) is hydraulically unlocked and the load pressure from the consumer connection (A) For example, (pA) up to about 400 bar at the pressure compensator (19) to the working line (31) is present.
  • the pressure in the load pressure signal circuit (LS) and in the control line (21) always remains at a maximum (pZ) of z. B. limited to 45 bar.
  • the consumer is lowered in accordance with the current flow of the proportional magnet (14) via the pressure compensator (19) volume controlled, regardless of the size of the load.
  • the spring of the pressure compensator (19) has a spring force corresponding to 7 bar, as well as the spring of the inlet regulator (18).
  • the return pressure p_R in the return line (3) is, for example, essentially constant at 5 bar.
  • the pressure (pP) of about 70 bar and pressure of about 25 bar in the control line (30) fed by the pressure source are only non-limiting examples. It is only expedient here to control a pressure which is higher than the pressure-reducing valve (9) limited pressure of for example 45 bar. Should be in the embodiments of Fig.
  • the blocking valve (20) is omitted, then in the lowered position (b) the first flow path (26) could be connected directly to the second flow path (27) via the tap (33), or possibly already at the pressure source side of the proportional Wegeschiebers (S) the control line (11) with the load pressure signal circuit (LS) are directly connected.
  • the function in the lowering position (b) of the proportional directional spool valve (S) is similar. It is different that before the deflection of the proportional directional spool (S) via the pressure pilot control (16) of the circulation controller (5) with its example corresponding to 9 bar spring (7) in the pressure lines (1) and (2) a pressure of only about 9 bar, because the load pressure signal circuit (LS) is relieved to the tank.
  • the circulation regulator (5) continuously increases the pressure in the pressure lines (1, 2) to, for example, 50 to 70 bar, so that the load pressure signal circuit (LS) and, if present, the control line (21) for hydraulically unblocking Block valve (20) also the set by the pressure reducing valve (9) at the upper pressure limit pressure, for example, 15 to 45 bar, on the one hand the full deflection of the proportional directional spool (S) and on the other hand, if available, the hydraulic unlocking of the check valve (20 ).
  • the proportional directional spool (S), the inlet regulator (18), the pressure compensator (19) and the check valve (20) (if provided) are included in a valve main block indicated in phantom in FIGS the system pressure limiting valve (4), if necessary, the circulation controller (5) and the pressure reducing valve (9) are installed in a likewise indicated connection block of the pressure source (P).
  • This terminal block also contains the corresponding lines and is connected to the main block.
  • the proportional directional spool (S) could additionally have a manual or emergency operation for manual deflection.
  • the invention consists in feeding the pressure of the pressure supply (Z) limited to the upper pressure limit into the load pressure signal circuit (LS) in order to achieve the effect of a secondary pressure limiting valve, at least in the lowering position (b), which can thus be saved.
  • the check valve (20) is an option and does not necessarily have to be provided. Appropriately, however, the lines are provided for inserting the check valve in the main block.

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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) pour un raccord de consommateur (A), en particulier d'un consommateur hydraulique à simple effet, comprenant un distributeur à commande proportionnelle (S) pouvant se déplacer au moins entre des positions levée et baissée (a, b) et raccordé à une source de pression (P) et à un réservoir (R), un circuit de signal de pression de charge (LS) associé au moins au distributeur à commande proportionnelle, et une balance manométrique (19) agencée entre le distributeur à commande proportionnelle et le raccord de consommateur (A) dans une conduite de travail (31), dans laquelle le distributeur à commande proportionnelle (S) comprend des commandes pilotes de pression (16, 17) destinées à le dévier vers les positions levée et baissée (a, b), dans laquelle le circuit de signal de pression de charge (LS) est raccordé à une régulation de fourniture de source de pression (5 ; 34) et dans laquelle une alimentation en pression (Z) limitée à une limite supérieure de pression (p-Z) nettement inférieure à la pression maximale de consommateur (p-A) est prévue au moins pour les commandes pilotes de pression (16, 17), caractérisée
    en ce que, lorsque le distributeur à commande proportionnelle (S) se trouve dans la position baissée (b), le distributeur à commande proportionnelle (S) relie l'alimentation en pression (Z) au circuit de signal de pression de charge (LS) et communique au maximum la pression limitée de l'alimentation en pression (Z) dans le circuit de signal de pression de charge (LS).
  2. Commande hydraulique selon la revendication 1, caractérisée en ce que l'alimentation en pression (Z) contient en amont du distributeur à commande proportionnelle (S) une vanne de détente (9).
  3. Commande hydraulique selon la revendication 1, caractérisée en ce qu'une soupape d'arrêt (20) effectuant un blocage dans la direction d'écoulement de position baissée est associée au raccord de consommateur (A), et peut être débloquée hydrauliquement dans la position baissée (b) du distributeur à commande proportionnelle (S) par la pression (p-Z) de l'alimentation en pression (Z) communiquée dans le circuit de signal de pression de charge (LS).
  4. Commande hydraulique selon au moins l'une des revendications précédentes, caractérisée en ce que des première et deuxième voies d'écoulement (26, 27) peuvent être commutées continuellement dans le distributeur à commande proportionnelle (S) en position baissée (b), parmi lesquelles la première voie d'écoulement (26) relie l'alimentation en pression (Z) du côté source de pression au côté raccord de consommateur, et la deuxième voie d'écoulement (27) relie la première voie d'écoulement (26) du côté raccord de consommateur au circuit de signal de pression de charge (LS) du côté source de pression.
  5. Commande hydraulique selon la revendication 1, caractérisée en ce que, dans le distributeur à commande proportionnelle (S) dans une position neutre (0), une troisième voie d'écoulement (28) peut être commutée continuellement, laquelle relie, du côté de raccord de consommateur, un raccord (29) de la première voie d'écoulement (26) au réservoir (R).
  6. Commande hydraulique selon au moins l'une des revendications précédentes, caractérisée en ce que la source de pression (P) est une pompe à débit constant, et en ce qu'un régulateur de circulation (5) relié au réservoir (R) et au circuit de signal de pression de charge (LS) est agencé en amont de l'alimentation en pression (Z).
  7. Commande hydraulique selon au moins l'une des revendications 1 à 5, caractérisée en ce que la source de pression (P) est une pompe à débit variable pourvue d'un régulateur (34) raccordé au circuit de signal de pression de charge (LS).
  8. Commande hydraulique selon la revendication 1, caractérisée en ce que la limite de pression supérieure (p-Z) de l'alimentation en pression (Z) est comprise entre environ 15 et 45 bars pour une pression maximale de consommateur allant jusqu'à environ 400 bars.
  9. Commande hydraulique selon la revendication 3, caractérisée en ce que la soupape d'arrêt (20) présente un rapport de pilotage hydraulique au moyen duquel la pression à la limite supérieure de pression (p-Z) de l'alimentation en pression (Z) débloque hydrauliquement la soupape d'arrêt (20), y compris lorsque la pression de consommateur (p-A) est maximale.
EP15182184.0A 2015-08-24 2015-08-24 Commande hydraulique Active EP3135924B1 (fr)

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EP15182184.0A EP3135924B1 (fr) 2015-08-24 2015-08-24 Commande hydraulique

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Application Number Priority Date Filing Date Title
EP15182184.0A EP3135924B1 (fr) 2015-08-24 2015-08-24 Commande hydraulique

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EP3135924A1 EP3135924A1 (fr) 2017-03-01
EP3135924B1 true EP3135924B1 (fr) 2018-01-10

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DE102020209387B3 (de) * 2020-07-24 2021-07-15 Hawe Hydraulik Se Vorwahlventil, Hydraulikventilverband und Hydrauliksteuervorrichtung
DK4019786T3 (da) 2020-12-28 2024-02-05 Danfoss Power Solutions Zhejiang Co Ltd Flervejsbelastningsventilarbejdssektion
CN115823038A (zh) * 2022-10-09 2023-03-21 三一汽车制造有限公司 控制油路、液压系统、作业臂和工程机械

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