EP0016719B1 - Hydraulic motor control device - Google Patents

Hydraulic motor control device Download PDF

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Publication number
EP0016719B1
EP0016719B1 EP80710005A EP80710005A EP0016719B1 EP 0016719 B1 EP0016719 B1 EP 0016719B1 EP 80710005 A EP80710005 A EP 80710005A EP 80710005 A EP80710005 A EP 80710005A EP 0016719 B1 EP0016719 B1 EP 0016719B1
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EP
European Patent Office
Prior art keywords
valve
pressure
control
line
hydraulic motor
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.)
Expired
Application number
EP80710005A
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German (de)
French (fr)
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EP0016719A1 (en
Inventor
Roland Ewald
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Bosch Rexroth AG
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Mannesmann Rexroth AG
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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
    • F15B11/003—Systems with load-holding 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control

Definitions

  • the invention relates to a device for controlling a hydraulic motor with two lines, with a lowering brake valve arranged in the first line, the passage cross section of which can be controlled hydraulically by means of an associated control element, with a control valve connected to the control element and the second line and with a directional control valve. which is connected directly to the hydraulic motor via the second line and to the hydraulic motor via the first line via the throttle element.
  • a check valve opening in the direction of the hydraulic motor is connected in parallel with the lowering brake valve and a throttle point arranged between it and the directional valve.
  • the directional control valve has three defined switching positions.
  • the control valve is a 4/2-way valve, the control member in its one end position is controlled by the pressure prevailing in the two lines connected to the hydraulic motor, the pressure in the first line being reduced between the lowering brake valve and a throttling point connected downstream .
  • the pressure in the second line then acts on the control element of the lowering brake valve.
  • the pressure in the first line acts both on the two sides of the control element of the control valve and on the control member.
  • the control element of the control valve can take intermediate layers.
  • the lowering brake valve serves to dampen the movement of the hydraulic motor when it is under the effect of a load and does not allow any leakage-free shut-off. It is also controlled by changing pressures, which results in changing load-dependent equilibrium positions. Different lowering speeds occur with different loads (FR-A-2 254 728).
  • DE-A-2 209 506 shows a lowering brake shut-off valve whose control piston is acted upon in the closing direction by the pressure between the consumer and the lowering brake shutoff valve and in the opening direction by the pressure on one side of the consumer.
  • the control piston of the lowering brake check valve is thus controlled depending on the load.
  • the well-known lowering brake valve serves to dampen the movement of the hydraulic motor. If this is under the action of a load, different lowering speeds occur here also with different loads.
  • a pressure compensator has the disadvantage that it is fully open when the hydraulic motor is separated from the pressure medium source. When connecting the hydraulic motor to the pressure medium source, this leads to a disadvantageous jump in the starting of the hydraulic motor, since in the beginning open pressure medium paths are reduced in their cross-section and may have to be closed completely (DE-AS 1 650 312).
  • the present invention is based on the object of reliably compensating the load acting on the hydraulic motor in order to avoid different lowering speeds with different loads with the same opening cross section of the lowering brake check valve.
  • This object is achieved in that the directional control valve is designed as a throttling directional control valve, that the control valve is designed as a pressure reducing valve and that the lowering brake valve is designed as a lowering brake blocking valve which enables a leakage-free shut-off, the control piston of which is in the control member on one side with the pressure reducing valve and is connected on its other side to the part of the second line which is present between the lowering brake blocking valve and the directional control valve.
  • the compensation of the load is achieved in that the control pressure on the control device of the controllable valve designed as a lowering brake shut-off valve is kept the same by the pressure reducing valve, as a result of which the pressure drop at the throttle point of the proportional valve and thus the latter Flow current remains constant.
  • the lowering brake check valve also acts as a pressure compensator, 'which ensures load-independent lowering of the load.
  • the lowering brake check valve therefore has a double function.
  • the invention has the advantage that when the hydraulic motor is connected to the pressure medium source, a jump in the start of the hydraulic motor is avoided.
  • the lowering brake check valve is closed when the hydraulic motor is disconnected from the pressure medium source and only opens when the hydraulic motor is connected to the pressure medium source.
  • the lowering brake shut-off valve also shuts off the pressure medium passage leading to the hydraulic motor without leakage and prevents loads from leading with a double-acting hydraulic motor, e.g. a double-acting cylinder.
  • the arrangement of the pressure reducing valve enables a constant pressure to be maintained between two connecting lines of the directional valve, namely one from the hydraulic motor and one connecting line leading to the reservoir.
  • the spring side of the pressure reducing valve with the connection of the throttling directional control valve to the supply container connected so that even with changing pressure in the connection of the throttling directional control valve to the reservoir, the pressure difference controlled by the lowering brake valve on the directional control valve remains constant.
  • the check valve and the throttle device between the controllable valve and the pressure reducing valve are switched on in such a way that the check valve can be opened to the controllable valve, as a result of which the passage of the lowering brake check valve is opened quickly and allows this passage to be closed slowly.
  • a throttling 4/3-way valve 1 is designed as an electrohydraulic servo valve, also called a proportional valve, as it is e.g. is described in DE-AS 17 76 190.
  • the directional control valve 1 has two with a hydraulic motor 2 with a constant displacement and with a flow direction, e.g. a working cylinder or the like, connectable connections A1 and B1, to which lines 3 and 4 are connected.
  • a port P is connected to a pump 5 and a port T is connected to a reservoir 6.
  • the device described has a single reservoir 6 for all of its associated devices.
  • the slide of the directional control valve 1 can be controlled by means of an electromagnet.
  • the position of the armature of this magnet depends on the voltage applied.
  • the slide of the directional valve 1 does not have three specific control positions, but is continuously adjustable. The flows through the directional control valve 1 are, as shown, throttled.
  • the line 3 leads directly to the hydraulic motor 2, the line 4 to a connection A2 on a lowering brake check valve 7, the connection B2 of which is connected to the hydraulic motor 2 via a line 8.
  • the lowering brake check valve 7 has a control connection X, which is connected via a line 9 to a check valve 10 which can be opened to the connection X.
  • This check valve 10 is connected via a line 11 to a pressure reducing valve 12, which is also connected to line 3.
  • the check valve 10 can be bypassed via a bypass line 14 having an orifice 13 (viscosity-stable throttle point).
  • the pressure reducing valve 12 has a control line 15 which is connected to the line 11.
  • the control line 15 is connected to this line via a check valve 16 which can be opened in the direction of the line.
  • a control return line 17 of the pressure reducing valve 12 is connected to the reservoir 6.
  • the lowering brake check valve 7, the check valve 10 together with the orifice 13 and the pressure reducing valve 12 including the control line 15 and the check valve 16 are accommodated in a common, dash-dotted and possibly multi-part housing 8.
  • the lowering brake check valve 7 has a main valve member 19 designed as a conical closing member and a control piston 20 which can be actuated and which can be acted upon by the same cross sections from the connections X and A2.
  • a compression spring 21 is clamped between the side of the control piston 20 adjacent to the valve member 19 and the housing of the lowering brake check valve 7.
  • the control piston 20 also serves to actuate the pilot valve member accommodated in the main valve member 19 and under the load of a pilot spring.
  • In the main valve member 19 there is a 2/2-way valve which, in cooperation with the spherical pilot control member, connects the rear of the main valve member 19 to line 8 or line 4.
  • the control pressure at the connection point X is opposed by the force of the spring 21.
  • connection point B2 The flow from the connection point B2 to the connection point A2 begins at a certain pressure in the line 8.
  • the throttling effect of the main valve member 19 is determined by the respective position of the main valve member.
  • the main valve element 19 acts as a check valve element that can be opened by the pressure medium pressure.
  • the line 4 is connected to the pump 5 and pressure medium flows via the lowering brake check valve 7, through the check valve opening to the hydraulic motor 2, and via line 8 to the hydraulic motor 2.
  • the line 3 serves as a return line. If the load is to be reduced by the hydraulic motor, the feed pump 5 delivers pressure medium into the line 3, the lines 8, 4 serving as return lines.
  • the pressure reducing valve 12 keeps the pressure at port X of the lowering brake check valve 7 constant. The pressure at the connection A2 of the lowering brake shutoff valve 7 thus also remains constant, since the same cross sections are acted upon by the control piston 20 from the two ports X and A2 of the lowering brake shutoff valve 7.
  • the pressure in port A2 corresponds to the difference from the Pressure at the control port X and the pressure necessary to overcome the bias of the spring 21. If, for example, a pressure of 10 bar is required at port X in order to move the control piston 20 against the force of the spring 21, and if there is a pressure of 30 bar at port X of the lowering brake check valve 7, the pressure at port A2 of the lowering brake is -Lock valve 7 20 bar.
  • the lowering brake check valve 7 acts like a pressure compensator and reduces the excess pressure between the connections A2 and B2. In the open position of the main valve member 19 of the lowering brake check valve 7, there is practically no pressure drop when pressure medium flows through this valve between the connections A2 and B2.
  • connection of the control line 15 of the pressure reducing valve 12 via the check valve 16 to the line 3 enables pressure fluid from the control line 15 to overflow into this line 3 when the pressure in the line 3 drops rapidly, as a result of which the pressure at the connection point X of the lowering brake check valve 7 can be dismantled quickly.
  • a counterbalance check valve 7 of the type described above acts as a pressure compensator for loads regardless of their direction, that this prevents an advance of loads and that its main valve member shuts off the fluid passage it monitors, since the main valve member is on its seat is conical.

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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 bezieht sich auf eine Vorrichtung zum Steuern eines Hydromotors mit zwei Leitungen, mit einem in der ersten Leitung angeordneten Senkbremsventil, dessen Durchgangsquerschnitt mittels eines zugeordneten Steuerorgans hydraulisch steuerbar ist, mit einem mit dem Steuerorgan und der zweiten Leitung verbundenen Steuerventil und mit einem Wegeventil, das über die zweite Leitung unmittelbar mit dem Hydromotor und über die erste Leitung über das Drosselorgan mit dem Hydromotor verbunden ist.The invention relates to a device for controlling a hydraulic motor with two lines, with a lowering brake valve arranged in the first line, the passage cross section of which can be controlled hydraulically by means of an associated control element, with a control valve connected to the control element and the second line and with a directional control valve. which is connected directly to the hydraulic motor via the second line and to the hydraulic motor via the first line via the throttle element.

Bei einer bekannten Vorrichtung der vorgenannten Art ist dem Senkbremsventil und einer zwischen diesem und dem Wegeventil angeordneten Drosselstelle ein in Richtung zum Hydromotor öffnendes Rückschlagventil parallel geschaltet. Das Wegeventil hat drei definierte Schaltstellungen. Das Steuerventil ist ein 4/2-Wegeventil, dessen in seiner einen Endlage befindliches Steuerglied von dem in den beiden mit dem Hydromotor verbundenen Leitungen jeweils herrschenden Druck gesteuert wird, wobei in der ersten Leitung der Druck zwischen dem Senkbremsventil und einer diesem nachgeschalteten Drosselstelle abgenommen wird. Auf das Steuerorgan des Senkbremsventils wirkt dann der Druck in der zweiten Leitung. In der anderen Endlage des Steuergliedes des Steuerventiles wirkt der Druck in der ersten Leitung sowohl auf die beiden Seiten des Steuergliedes des Steuerventiles als auch auf das Steuerorgan. Das Steuerglied des Steuerventiles kann Zwischenlagen einnehmen. Das Senkbremsventil dient zum Dämpfen der Bewegung des Hydromotors, wenn dieser unter der Wirkung einer Last steht, und erlaubt keine leckmittelfreie Absperrung. Es wird auch von wechselnden Drücken gesteuert, wodurch sich wechselnde lastabhängige Gleichgewichtslagen ergeben. Bei unterschiedlichen Lasten treten somit unterschliedliche Senkgeschwindigkeiten auf (FR-A-2 254 728).In a known device of the aforementioned type, a check valve opening in the direction of the hydraulic motor is connected in parallel with the lowering brake valve and a throttle point arranged between it and the directional valve. The directional control valve has three defined switching positions. The control valve is a 4/2-way valve, the control member in its one end position is controlled by the pressure prevailing in the two lines connected to the hydraulic motor, the pressure in the first line being reduced between the lowering brake valve and a throttling point connected downstream . The pressure in the second line then acts on the control element of the lowering brake valve. In the other end position of the control element of the control valve, the pressure in the first line acts both on the two sides of the control element of the control valve and on the control member. The control element of the control valve can take intermediate layers. The lowering brake valve serves to dampen the movement of the hydraulic motor when it is under the effect of a load and does not allow any leakage-free shut-off. It is also controlled by changing pressures, which results in changing load-dependent equilibrium positions. Different lowering speeds occur with different loads (FR-A-2 254 728).

Die DE-A-2 209 506 zeigt ein Senkbrems-Sperrventil dessen Steuerkolben in Schließrichtung vom Druck zwischen dem Verbraucher und dem Senkbrems-Sperrventil und in Öffnungsrichtung vom Druck auf einer Seite des Verbrauchers beaufschlagt wird. Der Steuerkolben des Senkbrems-Sperrventils wird somit lastabhängig gesteuert. Das bekannte Senkbremsventil dient zum Dämpfen der Bewegung des Hydromotors Wenn dieser unter der Wirkung einer Last steht, treter auch hier bei unterschiedlichen Lasten unterschiedliche Senkgeschwindigkeiten auf.DE-A-2 209 506 shows a lowering brake shut-off valve whose control piston is acted upon in the closing direction by the pressure between the consumer and the lowering brake shutoff valve and in the opening direction by the pressure on one side of the consumer. The control piston of the lowering brake check valve is thus controlled depending on the load. The well-known lowering brake valve serves to dampen the movement of the hydraulic motor. If this is under the action of a load, different lowering speeds occur here also with different loads.

Eine andere bekannte Vorrichtung zum Steuern eines Hydromotors hat ein drosselndes Wegeventil und eine Ausgleichseinrichtung, die als Druckwaage ausgebildet ist. Eine Druckwaage hat den Nachteil, daß sie bei von der Druckmittelquelle getrenntem Hydromotor voll geöffnet ist. Dies führt beim Verbinden des Hydromotors mit der Druckmittelquelle zu einem nachteiligen Anfahrsprung des Hydromotors, da am Anfang offene Druckmittelwege in ihrem Querschnitt verringert, gegebenenfalls ganz geschlossen werden müssen (DE-AS 1 650 312).Another known device for controlling a hydraulic motor has a throttling directional control valve and a compensation device which is designed as a pressure compensator. A pressure compensator has the disadvantage that it is fully open when the hydraulic motor is separated from the pressure medium source. When connecting the hydraulic motor to the pressure medium source, this leads to a disadvantageous jump in the starting of the hydraulic motor, since in the beginning open pressure medium paths are reduced in their cross-section and may have to be closed completely (DE-AS 1 650 312).

Der vorliegenden Erfindung liegt ausgehend von der an erster Stelle gewürdigten, bekannten Vorrichtung die Aufgabe zugrunde, die auf den Hydromotor wirkende Last sicher zu kompensieren, um bei unterschiedlichen Lasten unterschiedliche Senkgeschwindigkeiten bei gleichem Öffnungsquerschnitt des Senkbrems-Sperrventils zu vermeiden. Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß das Wegeventil als drosselndes Wegeventil ausgebildet ist, daß das Steuerventil als Druckminderventil ausgebildet ist und daß das Senkbremsventil als ein eine leckmittelfreie Absperrung ermöglichendes Senkbrems-Sperrventil ausgebildet ist, dessen Steuerkolben im Steuerorgan auf seiner einen Seite mit dem Druckminderventil und auf seiner anderen Seite mit dem zwischen dem Senkbrems-Sperrventil und dem Wegeventil vorhandenen Teil der zweiten Leitung verbunden ist. Wenn der Hydromotor unter der Wirkung einer Last steht, wird die Kompensierung der Last dadurch erreicht, daß durch das Druckminderventil der Steuerdruck auf die Steuereinrichtung des als Senkbrems-Sperrventil ausgebildeten steuerbaren Ventils gleich gehalten wird, wodurch das Druckgefälle an der Drosselstelle des Proportionalsventils und damit dessen Durchflußstrom konstant bleibt. Das Senkbrems-Sperrventil wirkt zugleich als Druckwaage, 'wodurch ein lastunabhängiges Senken der Last gewährleistet ist. Das Senkbrems-Sperrventil hat somit eine doppelte Funktion. Gegenüber der vorstehend an dritter Stelle gewürdigten, bekannten Vorrichtung hat die Erfindung den Vorteil, daß beim Verbinden des Hydromotors mit der Druckmittelquelle ein Anfahrsprung des Hydromotors vermieder wird. Das Senkbrems-Sperrventil ist bei von der Druckmittelquelle getrenntem Hydromotor geschlossen und öffnet erst, wenn der Hydromotor mit der Druckmittelquelle verbunder wird. Das Senkbrems-Sperrventil sperrt außerder den zum Hydromotor führenden Druckmitteldurchgang leckmittelfrei ab und verhindert das Voreilen von Lasten bei einem doppelt wirkenden Hydromotor, z.B. einem doppelt wirkenden Arbeitszylinder. Die Anordnung des Druckminderventils ermöglicht die Beibehaltung eines konstanten Druckes zwischen zwei Anschlußleitungen des Wegeventils, nämlich einer vom Hydromotor und einer zum Vorratsbehälter führenden Anschlußleitung. Die Funktion der erfindungsgemäßen Vorrichtung ist übersichtlich. Sie läßt sich in einem einzigen Gerät preisgünstig zusammenfassen.On the basis of the known device that has been recognized in the first place, the present invention is based on the object of reliably compensating the load acting on the hydraulic motor in order to avoid different lowering speeds with different loads with the same opening cross section of the lowering brake check valve. This object is achieved in that the directional control valve is designed as a throttling directional control valve, that the control valve is designed as a pressure reducing valve and that the lowering brake valve is designed as a lowering brake blocking valve which enables a leakage-free shut-off, the control piston of which is in the control member on one side with the pressure reducing valve and is connected on its other side to the part of the second line which is present between the lowering brake blocking valve and the directional control valve. If the hydraulic motor is under the action of a load, the compensation of the load is achieved in that the control pressure on the control device of the controllable valve designed as a lowering brake shut-off valve is kept the same by the pressure reducing valve, as a result of which the pressure drop at the throttle point of the proportional valve and thus the latter Flow current remains constant. The lowering brake check valve also acts as a pressure compensator, 'which ensures load-independent lowering of the load. The lowering brake check valve therefore has a double function. Compared to the known device, which was recognized in third place above, the invention has the advantage that when the hydraulic motor is connected to the pressure medium source, a jump in the start of the hydraulic motor is avoided. The lowering brake check valve is closed when the hydraulic motor is disconnected from the pressure medium source and only opens when the hydraulic motor is connected to the pressure medium source. The lowering brake shut-off valve also shuts off the pressure medium passage leading to the hydraulic motor without leakage and prevents loads from leading with a double-acting hydraulic motor, e.g. a double-acting cylinder. The arrangement of the pressure reducing valve enables a constant pressure to be maintained between two connecting lines of the directional valve, namely one from the hydraulic motor and one connecting line leading to the reservoir. The function of the device according to the invention is clear. It can be summarized inexpensively in a single device.

In Weiterbildung der Erfindung ist die Federseite des Druckminderventils mit dem Anschluß des drosselnden Wegeventils an den Vorratsbehälter verbunden, wodurch auch bei sich änderndem Druck im Anschluß des drosselnden Wegeventils an den Vorratsbehälter die vom Senkbrems-Sperrventil am Wegeventil gesteuerte Druckdifferenz konstant bleibt.In a development of the invention, the spring side of the pressure reducing valve with the connection of the throttling directional control valve to the supply container connected, so that even with changing pressure in the connection of the throttling directional control valve to the reservoir, the pressure difference controlled by the lowering brake valve on the directional control valve remains constant.

Bei einer Vorrichtung mit einem Rückschlagventil, das über eine Drosseleinrichtung umgehbar ist, sind das Rückschlagventil und die Drosseleinrichtung zwischen das steuerbare Ventil und das Druckminderventil derart eingeschaltet, daß das Rückschlagventil zum steuerbaren Ventil öffenbar ist, Hierdurch wird ein schnelles Öffnen des Durchganges des Senkbrems-Sperrventils und ein langsames Schließen dieses Durchganges ermöglicht.In a device with a check valve, which can be bypassed via a throttle device, the check valve and the throttle device between the controllable valve and the pressure reducing valve are switched on in such a way that the check valve can be opened to the controllable valve, as a result of which the passage of the lowering brake check valve is opened quickly and allows this passage to be closed slowly.

Wenn zwischen die Steuerleitung des Druckminderventils und die das Druckminderventil mit-dem Hydromotor verbindende Leitung ein in Richtung zum Hydromotor öffenbares Rückschlagventil eingeschaltet ist, wird ein schneller Abbau des Druckes an der Steueranschlußstelle des Senkbrems-Sperrventils erreicht.If a check valve which can be opened in the direction of the hydraulic motor is connected between the control line of the pressure reducing valve and the line connecting the pressure reducing valve to the hydraulic motor, the pressure at the control connection point of the lowering brake blocking valve is rapidly released.

Weitere Vorteile ergeben sich aus der Beschreibung und der Zeichnung. In dieser ist eine Vorrichtung zum Steuern eines Verbrauchers als Ausführungsbeispiel des Gegenstandes der Erfindung in Form einer Schaltung dargestellt.Further advantages result from the description and the drawing. In this a device for controlling a consumer is shown as an embodiment of the subject of the invention in the form of a circuit.

Ein drosselndes 4/3-Wegeventil 1 ist als elektrohydraulisches Servoventil, auch Proportionalventil genannt, ausgebildet, wie es z.B. in der DE-AS 17 76 190 beschrieben ist. Das Wegeventil 1 hat zwei mit einem Hydromotor 2 mit konstantem Verdrängungsvolumen und mit einer Stromrichtung, z.B. einem Arbeitszylinder oder dgl., verbindbare Anschlüsse A1 und B1, an welche Leitungen 3 und 4 angeschlossen sind. Ein Anschluß P ist mit einer Pumpe 5 und ein Anschluß T is mit einem Vorratsbehälter 6 verbunden. Die beschriebene Vorrichtung hat für alle ihr zugehörigen Geräte einen einzigen Vorratsbehälter 6.A throttling 4/3-way valve 1 is designed as an electrohydraulic servo valve, also called a proportional valve, as it is e.g. is described in DE-AS 17 76 190. The directional control valve 1 has two with a hydraulic motor 2 with a constant displacement and with a flow direction, e.g. a working cylinder or the like, connectable connections A1 and B1, to which lines 3 and 4 are connected. A port P is connected to a pump 5 and a port T is connected to a reservoir 6. The device described has a single reservoir 6 for all of its associated devices.

Der Schieber des Wegeventils 1 ist mittels eines Elektromagneten steuerbar. Die jeweilige Lage des Ankers dieses Magneten hängt von der jeweils angelegten Spannung ab. Der Schieber des Wegeventils 1 hat damit nicht drei bestimmte Steuerlagen, sondern ist stufenlos verstellbar. Die Durchflüsse durch das Wegeventil 1 sind also, wie dargestellt, gedrosselt.The slide of the directional control valve 1 can be controlled by means of an electromagnet. The position of the armature of this magnet depends on the voltage applied. The slide of the directional valve 1 does not have three specific control positions, but is continuously adjustable. The flows through the directional control valve 1 are, as shown, throttled.

Die Leitung 3 führt unmittelbar zum Hydromotor 2, die Leitung 4 zu einem Anschluß A2 an einem Senkbrems-Sperrventil 7, dessen Anschluß B2 über eine Leitung 8 mit dem Hydromotor 2 verbunden ist.The line 3 leads directly to the hydraulic motor 2, the line 4 to a connection A2 on a lowering brake check valve 7, the connection B2 of which is connected to the hydraulic motor 2 via a line 8.

Das Senkbrems-Sperrventil 7 hat einen Steueranschluß X, der über eine Leitung 9 mit einem zum Anschluß X öffenbaren Rückschlagventil 10 verbunden ist. Dieses Rückschlagventil 10 ist über eine Leitung 11 mit einem Druckminderventil 12 verbunden, das auch an die Leitung 3 angeschlossen ist.The lowering brake check valve 7 has a control connection X, which is connected via a line 9 to a check valve 10 which can be opened to the connection X. This check valve 10 is connected via a line 11 to a pressure reducing valve 12, which is also connected to line 3.

Das Rückschlagventil 10 über eine eine Blende 13 (viskositätsstabile Drosselstelle) aufweisende Umgehungsleitung 14 umgehbar. Das Druckminderventil 12 hat eine Steuerleitung 15, die an die Leitung 11 angeschlossen ist. Die Steuerleitung 15 ist über ein in Richtung zur Leitung öffenbares Rückschlagventil 16 mit dieser Leitung verbunden. Eine Steuerrückflußleitung 17 des Druckminderventils 12 ist mit dem Vorratsbehälter 6 verbunden.The check valve 10 can be bypassed via a bypass line 14 having an orifice 13 (viscosity-stable throttle point). The pressure reducing valve 12 has a control line 15 which is connected to the line 11. The control line 15 is connected to this line via a check valve 16 which can be opened in the direction of the line. A control return line 17 of the pressure reducing valve 12 is connected to the reservoir 6.

Das Senkbrems-Sperrventil 7, das Rückschlagventil 10 samt Blende 13 und das Druckminderventil 12 samt Steuerleitung 15 und Rückschlagventil 16 sind in einem gemeinsamen, strichpunktiert dargestellten und gegebenenfalls mehrteiligen Gehäuse 8 untergebracht.The lowering brake check valve 7, the check valve 10 together with the orifice 13 and the pressure reducing valve 12 including the control line 15 and the check valve 16 are accommodated in a common, dash-dotted and possibly multi-part housing 8.

Das Senkbrems-Sperrventil 7 hat ein als kegelförmiges Schließglied ausgebildetes Hauptventilglied 19 und einer dieses betätigbaren Steuerkolben 20, der von den Anschlüssen X und A2 her jeweils mit gleichen Querschnitten beaufschlagbar ist. Eine Druckfeder 21 ist zwischen der dem Ventilglied 19 benachbarten Seite des Steuerkolbens 20 und dem Gehäuse des Senkbrems-Sperrventils 7 eingespannt. Der Steuerkolben 20 dient zugleich zum Betätigen des im Hauptventilglied 19 untergebrachten und unter der Last einer Vorsteuerfeder stehenden Vorsteuerventilglieds. In dem Hauptventilglied 19 befindet sich ein 2/2-Wegeventil, das im Zusammenwirken mit dem kugelförmigen Vorsteuerglied die Rückseite des Hauptventilgliedes 19 mit der Leitung 8 oder der Leitung 4 verbindet. Dem Steuerdruck an der Anschlußstelle X steht die Kraft der Feder 21 entgegen. Der Durchfluß von der Anschlußstelle B2 nach der Anschlußstelle A2 beginnt ab einem bestimmten Druck in der Leitung 8. Die Drosselwirkung des Hauptventilgliedes 19 ist beim Aufsteuern durch dessen jeweilige Lage bestimmt. Beim Durchfluß bei Druckmitttel durch das Senkbrems-Sperrventil von der Anschlußstelle A2 nach der Anschlußstelle B2 wirkt das Hauptventilglied 19 als vom Druckmitteldruck öffenbares Rückschlagventilglied.The lowering brake check valve 7 has a main valve member 19 designed as a conical closing member and a control piston 20 which can be actuated and which can be acted upon by the same cross sections from the connections X and A2. A compression spring 21 is clamped between the side of the control piston 20 adjacent to the valve member 19 and the housing of the lowering brake check valve 7. The control piston 20 also serves to actuate the pilot valve member accommodated in the main valve member 19 and under the load of a pilot spring. In the main valve member 19 there is a 2/2-way valve which, in cooperation with the spherical pilot control member, connects the rear of the main valve member 19 to line 8 or line 4. The control pressure at the connection point X is opposed by the force of the spring 21. The flow from the connection point B2 to the connection point A2 begins at a certain pressure in the line 8. The throttling effect of the main valve member 19 is determined by the respective position of the main valve member. When the pressure medium flows through the lowering brake check valve from the connection point A2 to the connection point B2, the main valve element 19 acts as a check valve element that can be opened by the pressure medium pressure.

Wenn vom Hyaromotor 2 eine Last gehoben werden soll, so wird die Leitung 4 mit der Pumpe 5 verbunden und Druckmittel fließt über das Senkbrems-Sperrventil 7, durch dessen zum Hydromotor 2 öffnendes Rückschlagventil hindurch, und über die Leitung 8 zum Hydromotor 2. Die Leitung 3 dient als Rückflußleitung. Wenn vom Hydromotor die Last gesenkt werden soll, fördert die Förderpumpe 5 Druckmittel in die Leitung 3, wobei die Leitungen 8, 4 als Rücklaufleitungen dienen. Bei druckbeaufschlagter Leitung 3 hält das Druckminderventil 12 den Druck am Anschluß X des Senkbrems-Sperrventils 7 konstant. Damit bleibt auch der Druck am Anschluß A2 des Senkbrems-Sperrventils 7 konstant, da von seiten der beiden Anschlüsse X und A2 des Senkbrems-Sperrventils 7 aus der Aufsteuerkolben 20 jeweils mit den gleichen Querschnitten beaufschlagt wird. Der Druck im Anschluß A2 entspricht der Differenz aus dem Druck am Steueranschluß X und dem Druck der zur Überwindung der Vorspannung der Feder 21 notwendig ist. Ist z.B. am Anschluß X ein Druck von 10 bar erforderlich, um den Steuerkolben 20 entgegen der Kraft der Feder 21 zu bewegen, und liegt am Anschluß X des Senkbrems-Sperrventils 7 ein Druck von 30 bar, so beträgt der Druck am Anschluß A2 des Senkbrems-Sperrventils 7 20 bar.If a load is to be lifted from the hyaromotor 2, the line 4 is connected to the pump 5 and pressure medium flows via the lowering brake check valve 7, through the check valve opening to the hydraulic motor 2, and via line 8 to the hydraulic motor 2. The line 3 serves as a return line. If the load is to be reduced by the hydraulic motor, the feed pump 5 delivers pressure medium into the line 3, the lines 8, 4 serving as return lines. When line 3 is pressurized, the pressure reducing valve 12 keeps the pressure at port X of the lowering brake check valve 7 constant. The pressure at the connection A2 of the lowering brake shutoff valve 7 thus also remains constant, since the same cross sections are acted upon by the control piston 20 from the two ports X and A2 of the lowering brake shutoff valve 7. The pressure in port A2 corresponds to the difference from the Pressure at the control port X and the pressure necessary to overcome the bias of the spring 21. If, for example, a pressure of 10 bar is required at port X in order to move the control piston 20 against the force of the spring 21, and if there is a pressure of 30 bar at port X of the lowering brake check valve 7, the pressure at port A2 of the lowering brake is -Lock valve 7 20 bar.

Mit Hilfe der vorbeschriebenen Vorrichtung wird das Druckgefälle zwischen den Anschlüssen B1 und T des Wegeventils 1 konstant gehalten. Das Senkbrems-Sperrventil 7 wirkt wie eine Druckwaage und baut den überschüssigen Druck zwischen den Anschlüssen A2 und B2 ab. In Öffnungslage des Hauptventilgliedes 19 des Senkbrems-Sperrventils 7 tritt beim Durchfluß von Druckmittel durch dieses Ventil zwischen den Anschlüssen A2 und B2 praktisch kein Druckabfall auf.With the aid of the device described above, the pressure drop between the connections B1 and T of the directional control valve 1 is kept constant. The lowering brake check valve 7 acts like a pressure compensator and reduces the excess pressure between the connections A2 and B2. In the open position of the main valve member 19 of the lowering brake check valve 7, there is practically no pressure drop when pressure medium flows through this valve between the connections A2 and B2.

Wegen der Verbindung des Druckminderventils 12 mit dem Vorratsbehälter 6 über die Steuerrückflußleitung 17 wirken Druckschwankungen im Vorratsbehälter 6 auf das Druckminderventil 12 darart ein, daß sich der Druck am Anschluß X des Senkbrems-Sperrventils 7 derart ändert, daß das Druckgefälle zwischen den Anschlüssen B1 und T des Wegeventils 1 konstant bleibt.Because of the connection of the pressure reducing valve 12 to the reservoir 6 via the control return line 17, pressure fluctuations in the reservoir 6 act on the pressure reducing valve 12 in such a way that the pressure at the port X of the counterbalance check valve 7 changes such that the pressure drop between the ports B1 and T of the directional control valve 1 remains constant.

Die Anordnung des Rückschlagventils 10, der dieses Ventil umgehenden Umgehungsleitung 14 und der darin eingeschalteten Blende 13 wirken derart, daß der Steuerkolben 20 in Richtung des Aufsteuerns des Hauptventiles 19 des Senkbrems-Sperrventils 7 schnell bewegt wird, da ein voller Durchgang zwischen den Leitungen 9 und 11 vorhanden ist, und der aufgesteuerte Steuerkolben 20 nur langsam in seine Ruhelage zurückkehrt, da durch die Blende 13 der Rückfluß gedrosselt ist.The arrangement of the check valve 10, the bypass line 14 bypassing this valve and the orifice 13 activated therein act in such a way that the control piston 20 is moved rapidly in the direction of opening the main valve 19 of the lowering brake check valve 7 since there is a full passage between the lines 9 and 11 is present, and the opened control piston 20 only slowly returns to its rest position, since the orifice 13 restricts the reflux.

Die Verbindung der Steuerleitung 15 des Druckminderventils 12 über das Rückschlagventil 16 mit der Leitung 3 ermöglicht beim schnellen Abfall des Druckes in der Leitung 3 ein Überfließen von Druckmittel aus der Steuerleitung 15 in diese Leitung 3, wodurch der Druck an der Anschlußstelle X des Senkbrems-Sperrventils 7 schnell abgebaut werden kann.The connection of the control line 15 of the pressure reducing valve 12 via the check valve 16 to the line 3 enables pressure fluid from the control line 15 to overflow into this line 3 when the pressure in the line 3 drops rapidly, as a result of which the pressure at the connection point X of the lowering brake check valve 7 can be dismantled quickly.

Der Vorteil der Verwendung eines Senkbrems-Sperrventils 7 der vorbeschriebenen Art besteht darin, daß dieses als Druckwaage für Lasten unabhängig von deren Richtung wirkt, daß dieses ein Voreilen von Lasten verhindert und daß dessen Hauptventilglied den von ihm überwachten Druckmitteldurchgang leckmittelfrei absperrt, da das Hauptventilglied an seinem Sitz kegelförmig ausgebildet ist.The advantage of using a counterbalance check valve 7 of the type described above is that it acts as a pressure compensator for loads regardless of their direction, that this prevents an advance of loads and that its main valve member shuts off the fluid passage it monitors, since the main valve member is on its seat is conical.

Claims (4)

1. A device for controlling a hydraulic motor (2) and provided with two lines (3; 4, 8) and with a lowering braking valve (7), which is arranged in the first line (4, 8) and whose cross- sectional area of passage is hydraulically controllable by means of an associated control member (20, 21), and with a control valve (12), which is connected to the control member (20, 21) and the second tine (3), and with a directional-control valve (1), which is connected via the second line (3) directly to the hydraulic motor (2) and via the first line (4), through the lowering braking valve (7), to the hydraulic motor (2), characterised in that the directional-control valve (1) is designed as a restricting directional-control valve, and in that the control valve (12) is designed as a pressure-reducing valve, and in that the lowering braking valve (7) is designed as a lowering braking check valve allowing a leak-proof shut-off and whose control piston (20) in the control member (20, 21) is connected, on its one side, to the pressure-reducing valve (12) and, on its other side, to the part of the second line (4) that is provided between the lowering braking check valve (7) and the directional-control valve (1).
2. A device as claimed in Claim 1, characterised in that the spring side of the pressure-reducing valve (12) is connected to the connection of the restricting directional-control valve (1) on the storage tank (6).
3. A device as claimed in Claim 1 or 2, provided with a non-return valve (10) which can be by-passed via a restricting unit (13), characterised in that the non-return valve (10) and the restricting unit (13) are inserted between the lowering braking valve (7) and the pressure-reducing valve (12) in such a way that the non-return valve (10) is openable towards the lowering braking valve (7).
4. A device as claimed in one of the preceding Claims, characterised in that there is inserted between the control line (15) of the pressure-reducing valve (12) and the line (3) connecting the pressure-reducing valve (12) to the hydraulic motor (2) a non-return valve (16) which is openable in the direction of the hydraulic motor (2).
EP80710005A 1979-03-26 1980-02-29 Hydraulic motor control device Expired EP0016719B1 (en)

Applications Claiming Priority (2)

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DE2911891A DE2911891C2 (en) 1979-03-26 1979-03-26 Device for controlling a hydraulic motor
DE2911891 1979-03-26

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EP0016719B1 true EP0016719B1 (en) 1985-01-09

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JPS608383B2 (en) * 1975-02-14 1985-03-02 株式会社多田野鉄工所 counterbalance valve
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US4132153A (en) * 1976-11-09 1979-01-02 Phd, Inc. Metering control valve and fluid power system
JPS5724965Y2 (en) * 1976-12-20 1982-05-31
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Also Published As

Publication number Publication date
DE2911891A1 (en) 1980-10-02
JPH034763B2 (en) 1991-01-23
US4732076A (en) 1988-03-22
EP0016719A1 (en) 1980-10-01
JPS55132401A (en) 1980-10-15
DE2911891C2 (en) 1983-10-13

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