EP3135924B1 - Hydraulic device - Google Patents

Hydraulic device 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
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Active
Application number
EP15182184.0A
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German (de)
French (fr)
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EP3135924A1 (en
Inventor
Thomas Wechsel
Sascha Rümenap
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Hawe Hydraulik SE
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Hawe Hydraulik SE
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Priority to EP15182184.0A priority Critical patent/EP3135924B1/en
Publication of EP3135924A1 publication Critical patent/EP3135924A1/en
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    • 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)

Description

Die Erfindung betrifft eine Hydrauliksteuerung der im Oberbegriff des Patentanspruchs 1 angegebenen Art.The invention relates to a hydraulic control specified in the preamble of claim 1. Art.

Zwei Beispiele solcher Hydrauliksteuerungen sind aus der technischen Informationsschrift D 7700-3, Seite 14, der Firma HAWE Hydraulik SE, Streitfeldstraße 25, 81673 München, DE (einzusehen im Internet unter: info@hawe.de), rechts unten durch Blockschaltbilder angedeutet. Der Lastdrucksignalkreis ist über mindestens ein SekundärdruckBegrenzungsventil mit dem Tank verbunden, das den aus der Arbeitsleitung abgegriffenen Lastdruck auf eine obere Druckgrenze begrenzt, die deutlich unterhalb des maximalen Verbraucherdrucks liegt. In der Senk-Stellung des Proportional-Wegeschiebers wird der zunächst der Rücklaufdruck von wenigen bar entsprechende Lastdruck in den Lastdrucksignalkreis gemeldet, [zunächst der Rücklaufdruck von wenigen bar], wodurch die Druckquelle über einen Zulaufregler des Proportional-Wegeschiebers den Druck im Lastdrucksignalkreis anhebt, bis schließlich das Sekundärdruckbegrenzungsventil anspricht. Der Druck im Lastdrucksignalkreis bleibt dann an der oberen Druckgrenze. Dadurch lässt sich auch ohne Last auf den am Verbraucheranschluss angeschlossenen Verbraucher der Proportional-Wegeschieber zügig und voll bis in die Senk-Stellung hydraulisch auslenken.Two examples of such hydraulic controls are from the technical information D 7700-3, page 14, the company HAWE Hydraulik SE, Streitfeldstraße 25, 81673 Munich, DE (available on the Internet at: info@hawe.de) , indicated at the bottom right by block diagrams. 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. In the lowering position of the proportional directional spool first of the return pressure of a few bar corresponding load pressure is reported in the load pressure signal circuit, [first, the return pressure of a few bar], whereby the pressure source via a flow control of the proportional directional spool valve raises the pressure in the load pressure signal circuit until finally the secondary pressure relief valve responds. The pressure in the load pressure signal circuit then remains at the upper pressure limit. As a result, the proportional directional spool can be hydraulically deflected quickly and fully into the lowered position, even without load on the load connected to the consumer connection.

Im zweiten Beispiel ist dem Verbraucheranschluss ein hydraulisch entsperrbares Sperrventil zugeordnet, das selbst bei maximalem Verbraucherdruck mit dem über das Sekundärdruckbegrenzungsventil begrenzten Druck im Lastdrucksignalkreis hydraulisch entsperrbar ist. In beiden Beispielen wird jedoch für diese Funktionen (voll Auslenken, Entsperren) das zumindest eine Sekundärdruckbegrenzungsventil benötigt, das durch seine Unterbringung beispielsweise in einem Ventilblock und mit den Verbindungsbohrungen zusätzlichen baulichen Aufwand bedingt und ein deutlicher Kostenfaktor der Hydrauliksteuerung ist.In the second example, 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. In both examples, however, 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.

Von Interesse sind ferner:

  • EP159 8560 A , EP135 5065 A , EP215 7319 A , EP164 3138 A , DE104 49 787 A ,
  • DE 196 46427 A , WO02/075 162 A und DE 38 44 405 A .
Also of interest are:
  • EP159 8560 A . EP135 5065 A . EP215 7319 A . EP164 3138 A . DE104 49 787 A .
  • DE 196 46427 A . WO02 / 075 162 A and DE 38 44 405 A ,

Der Erfindung liegt die Aufgabe zugrunde, eine Hydrauliksteuerung der eingangs genannten Art baulich zu vereinfachen und kostengünstiger zu gestalten, und dennoch die gleichen Funktionen sicherzustellen.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.

Die gestellte Aufgabe wird mit den Merkmalen des Patentanspruchs 1 gelöst.
Da der Proportional-Wegeschieber in der Senkstellung die Druckversorgung mit dem Lastdrucksignalkreis verbindet und den Druck der Druckversorgung in den Lastdrucksignalkreis meldet, die Druckquelle über den Druck aus der Druckversorgung genügend Druck liefert, bis in der Druckversorgung die obere Druckgrenze erreicht wird. Der Lastdrucksignalkreis wird also in der Senk-Stellung nicht mehr aus einer Druckleitung über den Zulaufregler abgeleitetem Druck gespeist, sondern aus der Druckversorgung, so dass durch die von der Druckversorgung eingehaltene obere Druckgrenze im Lastdrucksignalkreis zunächst nur ein begrenzter Druck herrschen kann. Dadurch entfällt die Notwendigkeit, für diesen Zweck wenigstens ein Sekundärdruckbegrenzungsventil in die Hydrauliksteuerung einzugliedern. Dabei kann die Druckversorgung von derselben Druckquelle wie der Proportional-Wegeschieber gespeist werden, oder von einer separaten Druckquelle, wie einer Hilfspumpe. Der Wegfall des Sekundärdruckbegrenzungsventils und dessen Anschlusskanäle vereinfacht die Hydrauliksteuerung und sichert dennoch die gleichen Funktionen. Es entstehen keine Mehrkosten, da Druckvorsteuerungen des Proportional-Wegeschiebers wie auch die Druckversorgung für diese meist ohnedies vorhandene Ausstattungen solcher Hydrauliksteuerungen sind.The stated object is achieved with the features of claim 1.
Since 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. In this case, 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. The elimination of the secondary pressure relief valve and its connection channels simplifies the hydraulic control and still ensures the same functions. There are no additional costs, since pressure pilot controls of the proportional directional spool valve as well as the pressure supply for these usually without any existing equipment such hydraulic controls.

Zweckmäßig enthält die Druckversorgung stromauf des Proportional-Wegeschiebers ein an die Druckquelle angeschlossenes Druckminderventil, an welchem die obere Druckgrenze feinfühlig einstellbar und durch das diese Druckgrenze zuverlässig einhaltbar ist. Das Druckminderventil kann auch bei einer separaten Druckquelle für die Druckversorgung zweckmäßig sein.Expediently, 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.

In einer weitergebildeten Ausführungsform der Hydrauliksteuerung ist dem Verbraucheranschluss ein in Senk-Abströmrichtung sperrendes Sperrventil zugeordnet, das in der Senk-Stellung des Proportional-Wegeschiebers vom in den Lastdrucksignalkreis gemeldeten Druck der Druckversorgung hydraulisch entsperrbar ist. Dieses Sperrventil kann aus Sicherheitsgründen oder entsprechend dem Bedarf des Anwenders zweckmäßig sein. Mit dem von der Druckversorgung aufgebauten Druck lässt sich nicht nur der Proportional-Wegeschieber zügig voll in die Senkstellung auslenken, selbst wenn der an den Verbraucheranschluss angeschlossene Verbraucher keine Last trägt, und wird das Sperrventil selbst bei maximalem Verbraucherdruck durch den Druck von der Druckversorgung hydraulisch entsperrt. Günstig ist hierbei, dass der eigentlich für die lastunabhängige Hebefunktion gebrauchte Zulaufregler auf diese Funktion keinen Einfluss zu nehmen braucht.In a further developed embodiment of the hydraulic control, 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. With the pressure built up by the pressure supply not only the proportional directional spool can quickly fully deflect into the lowering position, even if the consumer connected to the load port carries no load, and the check valve is hydraulically unlocked even at maximum consumer pressure by the pressure from the pressure supply , It is advantageous here that the actually used for the load-independent lifting function inlet regulator needs to take this function no influence.

In einer baulich einfachen Ausführungsform der Hydrauliksteuerung sind im Proportional-Wegeschieber in dessen Senk-Stellung erste und zweite Strömungswege durchgängig schaltbar. Der erste Strömungsweg verbindet die Druckversorgung von der Druckquellen-Seite her mit der Verbraucheranschluss-Seite. Der zweite Strömungsweg verbindet dann den ersten Strömungsweg an der Verbraucherseite mit dem Lastdrucksignalkreis an der Druckquellen-Seite.In a structurally simple embodiment of the hydraulic control, 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.

Auf diese Weise wird der Druck aus der Druckversorgung in den Lastdrucksignalkreis gemeldet. Sollte kein Sperrventil vorgesehen sein, könnte schon zu Beginn der Ausleitung in die Senkstellung der erste Strömungsweg an der Druckquellen-Seite im Proportional-Wegeschieber gleich unmittelbar mit dem Lastdrucksignalkreis verbunden werden. Ist entgegen ein Sperrventil verbaut, führt der erste Strömungsweg den Druck der Druckversorgung zum Entsperren an das Sperrventil, während der zweite Strömungsweg den Druck der Druckversorgung in den Lastdrucksignalkreis einspeist.In this way, the pressure from the pressure supply is reported in the load pressure signal circuit. If no check valve is provided, 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.

Zweckmäßig ist ferner im Proportional-Wegeschieber ein dritter Strömungsweg vorgesehen, der in einer Neutralstellung durchgängig schaltbar ist und den ersten Strömungsweg oder einen Anschluss des ersten Strömungswegs an der Verbraucherseite mit dem Tank verbindet, so dass nicht nur der Lastdrucksignalkreis beispielsweise bis auf den Tankdruck entlastet wird, sondern dann eine ungewollte hydraulische Entsperrung des Sperrventils ausgeschlossen ist.Appropriately, 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.

In einer Ausführungsform wird eine Konstantpumpe als Druckquelle verwendet. In diesem Fall ist es zweckmäßig, einen Umlaufregler vorzusehen, der in der Neutralstellung des Proportional-Wegeschiebers über einen weitgehend drucklosen Umlauf gefördertes Druckmittel zum Tank ableitet, zwar mit minimalem Drosselverlust und minimaler Erwärmung des Druckmittels. Solche Umlauf-Regler sind im Übrigen in Hydrauliksteuerungen mit einer Konstantpumpe als Druckquelle Standardausstattung, falls der drucklose Umlauf zum Tank nicht über den Proportional-Wegeschieber geführt wird.In one embodiment, a constant displacement pump is used as the pressure source. In this case, it is expedient to provide 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. Incidentally, such 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.

Alternativ ist die Druckquelle eine Verstellpumpe mit einem an den Lastdrucksignalkreis angeschlossenen Regler der Verstellpumpe selbst. Die Verstellpumpe liefert im stand-by-Betrieb einen geringen Druck von bis zu etwa 20 bar. Der Regler regelt den Druck der Verstellpumpe nach Maßgabe des Drucks im Lastdrucksignalkreis bis auf den maximalen Verbraucherdruck automatisch hoch.Alternatively, 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.

Für maximale Verbraucherdrücke bis zu etwa 400 bar reicht eine obere Druckgrenze der Druckversorgung von durchschnittlich 15 bis 45 bar. Diese obere Druckgrenze stellt sicher, dass einerseits der Proportional-Wegeschieber über seine Druckvorsteuerung zügig und voll in die Senkstellung ausgelenkt wird, und auch die erforderliche hydraulische Entsperrung des gegebenenfalls vorgesehenen Sperrventils.For maximum consumer pressures up to about 400 bar, 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.

Zweckmäßig weist das Sperrventil ein Aufsteuerverhältnis auf, mit dem selbst bei maximalem Verbraucherdruck von bis zu 400 bar ein Entsperrdruck entsprechend der oberen Druckgrenze der Druckversorgung zuverlässig ausreicht.Suitably, the check valve on a Aufsteuerverhältnis, with sufficient even with maximum consumer pressure of up to 400 bar a Entsperrdruck corresponding to the upper pressure limit of the pressure supply.

Anhand der Zeichnung werden Ausführungsformen des erfindungsgemäßen Gegenstands erläutert. Es zeigen:

Fig. 1
ein Blockschaltbild einer ersten Ausführungsform einer Hydrauliksteuerung, in drucklosem Zustand,
Fig. 2
ein Blockschaltbild einer zweiten Ausführungsform der Hydrauliksteuerung, in drucklosem Zustand, und
Fig. 3
ein Blockschaltbild der Hydrauliksteuerung der Fig. 2, unter Druck, und in einer SenkStellung eines Proportional-Wegeschiebers der Hydrauliksteuerung.
Reference to the drawings embodiments of the subject invention are explained. Show it:
Fig. 1
1 is a block diagram of a first embodiment of a hydraulic control, in a pressureless state,
Fig. 2
a block diagram of a second embodiment of the hydraulic control, in a pressureless state, and
Fig. 3
a block diagram of the hydraulic control of Fig. 2 , under pressure, and in a lowered position of a proportional directional spool of the hydraulic control.

Hydrauliksteuerungen (H) in den Ausführungsformen der Fig. 1 und 2 dienen beispielsweise zum Steuern eines einfach wirkenden Hydroverbrauchers (z. B. Hubzylinder), beispielsweise über eine Arbeitsleitung (31). Alternativ könnte auch ein doppelseitig beaufschlagbarer Hydroverbraucher gesteuert werden, dessen andere Arbeitsleitung nicht gezeigt wird.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). Alternatively, a double-acting hydraulic consumer could be controlled, the other working line is not shown.

In der Ausführungsform in Fig. 1 führt von einer hier als Konstantpumpe mit Motor (M) für Dauerbetrieb ausgebildeten Druckquelle (P) eine Druckleitung (1) zu einer Steuerleitung (1') und zu einer Druckversorgung (Z), die ein durch eine Feder (10) in Öffnungsrichtung beaufschlagtes Druckminderventil (9) enthält. Von der Druckquelle (P) führt ferner eine Druckleitung (2) zu einem als Druckwaage ausgebildeten Zulaufregler (18) und von diesem zu einem Anschluss eines Proportional-Wegeschiebers (S). An den nicht gezeigten Tank (R) ist eine Rücklaufleitung (3) angeschlossen. Im Falle der Konstantpumpe als Druckquelle (P) ist zwischen der Druckleitung (1) und der Rücklaufleitung (3) ein Umlaufregler (5) angeordnet, der als Druckwaage ausgebildet ist, in Sperrrichtung von einer Feder (7) und aus einer Steuerleitung (8) und in Öffnungsrichtung aus der Druckleitung (1) über eine Steuerleitung (6) beaufschlagt wird. Die Steuerleitung (8) ist an einen Lastdrucksignalkreis (LS) angeschlossen. Ferner ist zwischen der Druckleitung (1) und der Rücklaufleitung (3) ein Systemdruckbegrenzungsventil (4) angeordnet.In the embodiment in FIG 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. In the case of the fixed displacement pump as a pressure source (P), 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). Further, a system pressure limiting valve (4) is arranged between the pressure line (1) and the return line (3).

Die Druckversorgung (Z) könnte alternativ nicht von der Druckquelle (P) gespeist werden, sondern von einer separaten Druckquelle, z.B. einer Hilfspumpe.Alternatively, the pressure supply (Z) could not be supplied by the pressure source (P) but by a separate pressure source, e.g. an auxiliary pump.

Von der Druckversorgung (Z) führt eine Steuerleitung (11) zu einem an der Druckquellen-Seite liegenden Anschluss des Proportional-Wegeschiebers (S). Der Proportional-Wegeschieber ist in seiner Neutralstellung (O) dargestellt, in der bis auf einen dann durchgängig geschalteten dritten Strömungsweg (28) von einer Steuerleitung (21) zur Rücklaufleitung (3) sämtliche Anschlüsse an den Druckquellen- und Verbraucheranschluss-Seiten abgesperrt sind.From the pressure supply (Z), 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).

Von der Steuerleitung (11) führt eine Steuerleitung (12) zu Druckvorsteuerungen (16, 17) des Proportional-Wegeschiebers (S), die über Proportional-Magneten (14, 15) betätigbar sind, um den Proportional-Wegeschieber in eine Hebe-Stellung (a) oder eine Senk-Stellung (b) auszulenken. Der Zulaufregler (18) wird an seiner Öffnungsseite von einer Feder und aus dem Lastdrucksignalkreis (LS) sowie an seiner Schließseite über eine Steuerleitung beaufschlagt, die von der Druckleitung (2) stromab des Zulaufreglers (18) abzweigt.
In der von der Verbraucherseite des Proportional-Wegeschiebers (S) zum Verbraucheranschluss (A) verlaufenden Arbeitsleitung (31) ist eine Druckwaage (19) und zwischen der Druckwaage (19) und dem Verbraucheranschluss (A) ein hydraulisch entsperrbares Sperrventil (20) verbaut. Die Druckwaage (19) wird über eine Steuerleitung (25) aus der Arbeitsleitung (31) an der Schließseite beaufschlagt, und aus einer Steuerleitung (24) und von einer Feder an der Öffnungsseite. Vom Sperrventil (20) kann eine Leckageleitung (22) zur Rücklaufleitung (3) führen. Die Steuerleitung (21) für die Druckvorsteuerung (16, 17) führt zu einem Anschluss (29) des Proportional-Wegeschiebers an der Verbraucherseite und weist dort eine Anzapfung (21') auf. Im Lastdrucksignalkreis (LS) ist gegebenenfalls ein Wechselventil (14') enthalten, für den Fall, dass ggf. Lastdrucksignale weiterer, nicht gezeigter und von der Druckquelle (P) versorgter Verbraucher, dann in den Lastdrucksignalkreis (LS) eingespeist werden, wenn diese Lastdrucksignale höher sind als der im Lastdrucksignalkreis (LS) nur des Proportional-Wegeschiebers (S) herrschende Druck.
In der Senk-Stellung (b) des Proportional-Wegeschiebers (S) ist ein Strömungsweg (23) durchgängig geschaltet, der die Arbeitsleitung (31) mit der Rücklaufleitung (3) verbindet. Ferner ist in der Senk-Stellung (b) ein erster Strömungsweg (26) durchgängig geschaltet, der die Steuerleitung (11) von der Druckversorgung (Z) mit dem Anschluss (29) zur Steuerleitung (21) verbindet, und ein zweiter Strömungsweg (27) durchgängig geschaltet, der hier z. B. die Anzapfung (21') mit dem Lastdrucksignalkreis (LS) verbindet. Das Sperrventil (20) könnte entfallen.
Die Ausführungsform der Hydrauliksteuerung (H) in Fig. 2 unterscheidet sich von der der Fig. 1 dadurch, dass als Druckquelle (P) eine Verstellpumpe verwendet wird, die über einen Förderregler (34) verstellbar ist, der über eine Steuerleitung (30) an den Lastdrucksignalkreis (LS) angeschlossen ist. Bei der Verstellpumpe entfällt die Notwendigkeit des Umlaufreglers (5) der Fig. 1. Der weitere Aufbau und die Funktion der Hydrauliksteuerung (H) in Fig. 2 entsprechen denen der Fig. 1.From the control line (11), 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).
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. In 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).
In the lowering position (b) of the proportional directional spool (S), a flow path (23) is connected continuously, which connects the working line (31) with the return line (3). Further, in the lowering position (b), 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 ,

Die Funktion der Hydrauliksteuerung (H) der Fig. 2 in der Senk-Stellung (b) des Proportional-Wegeschiebers (S) bei im Dauerbetrieb laufender Druckquelle (P), mit oder ohne Last auf dem am Verbraucheranschluss (A) angeschlossenen Verbraucher wird anhand Fig. 3 erläutert.The function of the hydraulic control (H) of Fig. 2 in the lowering position (b) of the proportional directional spool valve (S) with the pressure source (P) running continuously, with or without load on the load connected to the load connection (A) Fig. 3 explained.

Vor dem Auslenken des Proportional-Wegeschiebers (S) in Fig. 3 lieferte die Druckquelle (P) beispielsweise einen stand-by-Druck von etwa bis zu 20 bar. Dieser Druck wirkt über das Druckminderventil (9) in etwa auch in der Steuerleitung (11), so dass über die Druckvorsteuerung (16) und den bestromten Proportional-Magneten (14) der Proportional-Wegeschieber in Richtung zur Senk-Stellung (b) ausgelenkt wird. Bei dieser anfänglichen Auslenkung werden sofort die ersten und zweiten Strömungswege (26) und (27) durchgängig geschaltet. Dadurch wirkt der niedrige stand-by-Druck in der Steuerleitung (21), der aber ggf. noch keinen Einfluss auf das Sperrventil (20) nimmt, und wird auch der Lastdrucksignalkreis (LS), der bis dahin unter dem Tankdruck von etwa 5 bar stand, geladen, so dass in der Steuerleitung (30) Druck von bis zu etwa 25 bar aufgebaut wird, mit dem der Förderregler (34) die Verstellpumpe als Druckquelle (P) soweit hochsteuert, dass in den Druckleitungen (1) und (2) ein Druck (p-P) von beispielsweise etwa 70 bar herrscht. Daraus erzeugt der Zulaufregler (18) in dem stromab liegenden Teil der Druckleitung (2) einen abgesperrten Druck (p-RK) von etwa 60 bar. Gleichzeitig stellt das Druckminderventil (9) über die Steuerleitung (1') in der Steuerleitung (11) einen Druck (p-Z) von beispielsweise 45 bar ein. Dieser Druck reicht aus, um über die Druckvorsteuerung (16) den Proportional-Wegeschieber (S) voll in die Senk-Stellung (b) auszulenken, in der die Arbeitsleitung (31) nach Maßgabe der Bestromung des Proportional-Magneten (14) mit der Rücklaufleitung (3) verbunden ist, und auch über einen dann durchgängig geschalteten Strömungsweg (32) die Steuerleitung (24) mit der Rücklaufleitung (3) verbunden ist. Der über die Druckversorgung (Z) bzw. das Druckminderventil (9) so in den Lastdrucksignalkreis (LS) gemeldete Druck herrscht auch in der Steuerleitung (21), so dass das Sperrventil (19) hydraulisch entsperrt wird und der Lastdruck vom Verbraucheranschluss (A), beispielsweise (p-A) bis zu etwa 400 bar an der Druckwaage (19) zur Arbeitsleitung (31) ansteht. In der Senk-Stellung (b) des Proportional-Wegeschiebers (S) bleibt der Druck im Lastdrucksignalkreis (LS) und in der Steuerleitung (21) stets auf maximal (p-Z) von z. B. 45 bar begrenzt. Der Verbraucher wird nach Maßgabe der Bestromung des Proportional-Magneten (14) über die Druckwaage (19) mengengeregelt gesenkt, unabhängig von der Größe der Last.Before deflecting the proportional directional spool (S) into Fig. 3 For example, 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. In this initial displacement, the first and second flow paths (26) and (27) are immediately switched continuously. As a result, the low stand-by pressure in the control line (21), but possibly still has no effect on the check valve (20), and is also the load pressure signal circuit (LS), which until then under the tank pressure of about 5 bar stand, loaded so that in the control line (30) pressure of up to about 25 bar is built up, with which the conveyor controller (34) the variable displacement pump as a pressure source (P) so far controls that in the pressure lines (1) and (2) a pressure (pP) of, for example, about 70 bar prevails. From this, the inlet regulator (18) in the downstream part of the pressure line (2) generates a shut-off pressure (p-RK) of about 60 bar. At the same time, 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. In the lowering position (b) of the proportional directional spool (S), 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.

In der Hebe-Stellung (a) des Proportional-Wegeschiebers (S) werden Druck und Menge am Verbraucheranschluss (A) auf in dieser Technik übliche Weise geregelt, worauf hier nicht näher eingegangen wird.In the lifting position (a) of the proportional directional spool valve (S), the pressure and quantity at the consumer port (A) are regulated in a manner customary in this art, which will not be discussed further here.

In Fig. 3 hat beispielsweise die Feder der Druckwaage (19) eine Federkraft entsprechend 7 bar, wie auch die Feder des Zulaufreglers (18). Der Rücklaufdruck p_R in der Rücklaufleitung (3) beträgt beispielsweise im Wesentlichen konstant 5 bar. Der von der Druckquelle eingespeiste Druck (p-P) von etwa 70 bar und Druck von etwa 25 bar in der Steuerleitung (30) sind nur nicht beschränkende Beispiele. Es ist nur zweckmäßig, hier einen Druck einzusteuern, der höher ist als der vom Druckminderventil (9) begrenzte Druck von beispielsweise 45 bar. Sollte in den Ausführungsformen der Fig. 1 und 2 das Sperrventil (20) entfallen, dann könnte in der Senk-Stellung (b) der erste Strömungsweg (26) über die Anzapfung (33) direkt mit dem zweiten Strömungsweg (27) verbunden sein, oder ggf. schon an der Druckquellenseite des Proportional-Wegeschiebers (S) die Steuerleitung (11) mit dem Lastdrucksignalkreis (LS) direkt verbunden werden.In Fig. 3 for example, 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. 1 and 2 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.

Bei der Ausführungsform der Fig. 1 mit der Konstantpumpe als Druckquelle (P) läuft die Funktion in der Senk-Stellung (b) des Proportional-Wegeschiebers (S) gleichartig ab. Unterschiedlich ist, dass vor dem Auslenken des Proportional-Wegeschiebers (S) über die Druckvorsteuerung (16) der Umlaufregler (5) mit seiner beispielsweise 9 bar entsprechenden Feder (7) in den Druckleitungen (1) und (2) einen Druck von nur etwa 9 bar hält, weil der Lastdrucksignalkreis (LS) zum Tank entlastet ist. Da beim Auslenken des Proportional-Wegeschiebers (S) jedoch über die ersten und zweiten Strömungswege (26, 27) der Lastdrucksignalkreis (LS) mit 9 bar geladen wird, die über die Steuerleitung (8) parallel zur Feder (7) im Umlaufregler (5) zur Wirkung kommen, erhöht der Umlaufregler (5) den Druck in den Druckleitungen (1, 2) fortlaufend auf beispielsweise 50 bis 70 bar, so dass der Lastdrucksignalkreis (LS) und, falls vorhanden, die Steuerleitung (21) zum hydraulischen Entsperren des Sperrventils (20) ebenfalls den vom Druckminderventil (9) an der oberen Druckgrenze eingestellten Druck von beispielsweise 15 bis 45 bar führen, der einerseits das volle Auslenken des Proportional-Wegeschiebers (S) und andererseits, falls vorhanden, das hydraulische Entsperren des Sperrventils (20) sicherstellt.In the embodiment of the Fig. 1 with the constant pump as pressure source (P), 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. However, since during deflection of the proportional directional spool valve (S) the load pressure signal circuit (LS) is charged with 9 bar via the first and second flow paths (26, 27), which are connected via the control line (8) parallel to the spring (7) in the circulation regulator (5 ), 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 ).

In den gezeigten Ausführungsformen sind der Proportional-Wegeschiebers (S), der Zulaufregler (18), die Druckwaage (19) und das Sperrventil (20) (falls dieses vorgesehen ist), in einem in den Figuren strichpunktiert angedeuteten Ventil-Hauptblock enthalten, während das Systemdruckbegrenzungsventil (4), ggf. der Umlaufregler (5) und das Druckminderventil (9) in einem ebenfalls angedeuteten Anschlussblock der Druckquelle (P) verbaut sind. Dieser Anschlussblock enthält auch die entsprechenden Leitungen und ist an den Hauptblock angeschlossen.In the embodiments shown, 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.

Wie in Fig. 3 angedeutet, könnte der Proportional-Wegeschiebers (S) zusätzlich eine Hand- oder Notbetätigung zur manuellen Auslenkung aufweisen.As in Fig. 3 indicated, the proportional directional spool (S) could additionally have a manual or emergency operation for manual deflection.

Im Kern besteht die Erfindung darin, den bis zur oberen Druckgrenze begrenzten Druck der Druckversorgung (Z) in den Lastdrucksignalkreis (LS) einzuspeisen, um zumindest in der Senk-Stellung (b) die Wirkung eines Sekundärdruckbegrenzungsventils zu erzielen, das somit eingespart werden kann. Das Sperrventil (20) ist eine Option und muss nicht notwendigerweise vorgesehen sein. Zweckmäßig sind jedoch im Hauptblock die Leitungen zum Einsetzen des Sperrventils vorgesehen.In essence, 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.

Claims (9)

  1. A hydraulic controller (H) for a consumer connection (A), particularly a single acting hydraulic consumer, with a proportional spool valve (S), which is connected to a pressure source (P) and a tank (R) and is movable at least between raised and lowered positions (a, b), a load pressure signal circuit (LS) associated with at least the proportional spool valve and a pressure compensator (19) arranged in a working line (31) between the proportional spool valve and the consumer connection (A), wherein the proportional spool valve (S) includes pressure pilot controls (16, 17) for moving into the raised and lowered positions (a, b), wherein the load pressure signal circuit (LS) is connected to a pressure source output controller (5; 34) and wherein a pressure supply (Z) is provided, at least for the pressure pilot control (16, 17), which is limited to an upper pressure threshold (p-Z) significantly below the maximum consumer pressure (p-A), characterised in that in the lowered position (b) of the proportional spool valve (S), the proportional spool valve (S) connects the pressure supply (Z) to the load pressure signal circuit (LS) and signals at most the limited pressure of the pressure supply (Z) to the load pressure signal circuit (LS).
  2. A hydraulic controller as claimed in Claim 1, characterised in that the pressure supply (Z) includes a pressure reducing valve (9) upstream of the proportional spool valve (S).
  3. A hydraulic controller as claimed in Claim 1, characterised in that associated with the consumer connection (A) there is a non-return valve (20), which blocks in the lowering-discharge direction and which in the lowered position (b) of the proportional spool valve (S) is hydraulically releasable by the pressure (p-Z) of the pressure supply (Z) signalled to the load pressure signal circuit (LS).
  4. A hydraulic controller as claimed in at least one of the preceding claims, characterised in that first and second flow paths (26, 27) in the proportional spool valve (S) are switchable, in the lowered position (b), to be open, of which the first flow path (26) connects the pressure supply (Z) of the pressure source side to the consumer connection side and the second flow path (27) connects the first flow path (26) on the consumer connection side to the load pressure signal circuit (LS) on the pressure source side.
  5. A hydraulic controller as claimed in Claim 1, characterised in that a third flow path (28) in the proportional spool valve (S) is switchable, in a neutral position (O) to be open, which connects a connection (29) on the consumer connection side of the first flow path (26) to the tank (R).
  6. A hydraulic controller as claimed in at least one of the preceding claims, characterised in that the pressure source (P) is a fixed output pump and that arranged upstream of the pressure supply (Z) there is a speed controller (5) connected to the tank (R) and the load pressure signal circuit (LS).
  7. A hydraulic controller as claimed in at least one of Claims 1 to 5, characterised in that the pressure source (P) is a variable displacement pump with a controller (34) connected to the load pressure signal circuit (LS).
  8. A hydraulic controller as claimed in Claim 1, characterised in that the upper pressure threshold (p-Z) of the pressure supply (Z) is between about 15 and 45 bar at a maximum consumer pressure of up to about 400 bar.
  9. A hydraulic controller as claimed in Claim 3, characterised in that the non-return valve (20) includes a hydraulic release ratio, with which the pressure at the upper pressure threshold (p-Z) of the pressure supply (Z) hydraulically releases the non-return valve (20), even at maximum consumer pressure (p-A).
EP15182184.0A 2015-08-24 2015-08-24 Hydraulic device Active EP3135924B1 (en)

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EP15182184.0A EP3135924B1 (en) 2015-08-24 2015-08-24 Hydraulic device

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DE102020209387B3 (en) * 2020-07-24 2021-07-15 Hawe Hydraulik Se Preselection valve, hydraulic valve bank and hydraulic control device
DK4019786T3 (en) 2020-12-28 2024-02-05 Danfoss Power Solutions Zhejiang Co Ltd MULTI-WAY LOAD VALVE WORK SECTION

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DE3844405C2 (en) * 1988-12-30 1995-07-06 Rexroth Mannesmann Gmbh Valve arrangement for a hydraulic system
DE19646427B4 (en) * 1996-11-11 2006-01-26 Bosch Rexroth Aktiengesellschaft valve assembly
DE10149787B4 (en) * 2000-10-23 2012-06-06 Linde Material Handling Gmbh Valve arrangement with floating position
EP1370773B1 (en) * 2001-03-21 2005-06-22 Bucher Hydraulics GmbH Control valve
DE10216958B8 (en) * 2002-04-17 2004-07-08 Sauer-Danfoss (Nordborg) A/S Hydraulic control
DE102004025322A1 (en) * 2004-05-19 2005-12-15 Sauer-Danfoss Aps Hydraulic valve arrangement
DE102004048642A1 (en) * 2004-10-04 2006-04-06 Bosch Rexroth Aktiengesellschaft Hydraulic control arrangement
ES2394389T3 (en) * 2008-08-20 2013-01-31 Hawe Hydraulik Se Hydraulic control for a hydraulic motor

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