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EP0167818A1 - Hydraulic control device - Google Patents

Hydraulic control device Download PDF

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Publication number
EP0167818A1
EP0167818A1 EP85106903A EP85106903A EP0167818A1 EP 0167818 A1 EP0167818 A1 EP 0167818A1 EP 85106903 A EP85106903 A EP 85106903A EP 85106903 A EP85106903 A EP 85106903A EP 0167818 A1 EP0167818 A1 EP 0167818A1
Authority
EP
European Patent Office
Prior art keywords
line
valve
pipe
pressure
control device
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.)
Granted
Application number
EP85106903A
Other languages
German (de)
French (fr)
Other versions
EP0167818B1 (en
Inventor
Friedrich-Wilhelm Höfer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19843435304 external-priority patent/DE3435304A1/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0167818A1 publication Critical patent/EP0167818A1/en
Application granted granted Critical
Publication of EP0167818B1 publication Critical patent/EP0167818B1/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—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
    • F15B2211/3144—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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid 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
    • F15B2211/50—Pressure control
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/513—Pressure 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure 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
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention relates to a control device according to the preamble of the main claim.
  • relief of the spring chamber of the pressure compensator is only possible with a certain delay when the directional control valves are in the neutral position.
  • pressure medium can also leak to the tank, which affects the position of the consumer. This increases the risk of accidents.
  • control device with the characterizing features of the main claim has the advantage that no pressure medium can leak to the tank and in the switching transition load reduction and pressure increase "is avoided a quick change of direction of the consumers connected to the directional control valves is possible.
  • FIG. 1 shows a circuit diagram of a control device and FIG. 2 shows a structural design of a detail.
  • a pump 11 draws pressure medium from a tank 13 via an inlet line 12 and conveys it into a pump line 14. From a point 15 shortly behind the pump 11 and from a second point 16, a line branches off from the pump line 14 17 and 18 to the respective 7/3-way valves 19, 20 from.
  • the directional control valves 19, 20 are identical to one another, so that only the directional control valve 1.9 is described in more detail. It has the switch positions I, II, III and the connections a, b on one side and c, d, e, f, g on the other side.
  • switch position II which corresponds to the neutral position of the associated control slide 23
  • the connections a, b, e, f, g are blocked and the connections c, d are connected to one another.
  • switch position I connections a and e, b and c, f and g are connected to one another and connection d is blocked.
  • On the spool 23 is in egg ner connection 24 of the connection f with the connection g a throttle 25 is formed.
  • switch position III the connections a and c, b and e are connected to one another.
  • a line 27 branches off from the point 15 and leads to a return line 28 running to the tank 13.
  • a line 27 there is a hydraulically pilot-controllable 2/2 switching valve 29 which has a flow position I and a blocking position II and is loaded by a spring 30.
  • a line 32 branches off from the line 27 to one end of the switching valve 29.
  • a second line 33 leads from the point 31 to the other end face of the switching valve 29 loaded by the spring 30.
  • a throttle 34 is arranged in this line 33.
  • a line 37 leading to line 27 and opening after switching valve 29 is connected, in which a pressure relief valve 38 is arranged.
  • a line 39 leads from the branch 36 to a shuttle valve 40.
  • This has a central connection 41, at which the line 39 opens, and two connections 42, 43.
  • a return line 46 leads to a second shuttle valve 47.
  • a line 48 branches off from the connection 43 and leads to the connection e of the directional control valve 19.
  • the shuttle valve 40 has a freely movable ball 49 without spring loading as a closing member.
  • a throttle 50 and a check valve 51 are arranged in series.
  • the check valve 5J secures the line 48 to the shuttle valve 40 between the throttle 50 and the directional control valve J9.
  • throttle 50 and check valve 51 leads from one Position 52 a line 53 from line 48 to connection f of directional control valve 19.
  • line 48 branches off from line 48, which leads to connection d of directional control valve 19.
  • the return line 28 opens at the connection c and the line 17 at the connection g.
  • a line 57 leads from the connection a of the directional control valve 19 to a pressure chamber 58 of a double-acting working cylinder 59. Its pressure chamber 60 on the piston rod side is connected via a line 61 to the connection b of the directional control valve 19.
  • the return line 46 opens at the central connection 62 of the shuttle valve 47. From the connection 63, the return line 46 leads further to the tank 13.
  • the connection 64 is connected via a line 65 to the connection f of the second directional valve 20.
  • the shuttle valve 47 has a freely movable ball 66 without spring loading as a closing member.
  • a line 68 branches off from a point 67 and leads to the connection d of the second directional valve 20.
  • a line 70 leads from a second point 69 of the line 65, located between point 67 and directional control valve 20, to the connection e of the directional control valve 20.
  • the line 70 is protected by a check valve 71 to the line 65.
  • a return line 73 leading to the tank 13 opens at the connection c and the line 18 at the connection g.
  • a line 74 leads from the connection a of the directional control valve 20 to the pressure chamber 75 of a second double-acting working cylinder 76. Its pressure chamber 77 on the piston rod side is connected via a line 78 to the connection b of the directional control valve 20.
  • both directional control valves 19, 20 are in switch position II, lines 17, 18, 53, 48, 65, 70 are blocked.
  • the lines 53 and 48 are relieved of pressure via the line 56, the directional control valve 19 and the return line 28 to the tank 13.
  • Lines 65 and 70 are also relieved via line 68, directional control valve 20 and return line 73 to tank 13.
  • the pressure medium conveyed by the pump 11 flows from the pump line 14 into the line 27, via the switching valve 29 in the flow position I into the return line 28 and back into the tank 13.
  • the pressure medium also flows from line 27 into line 32 and into line 33.
  • the pressure difference occurring at the throttle 34 keeps the switching valve 29 in its flow position I against the force of the spring 30. As a result, only a small amount occurs at the switching valve 29 , largely caused by the spring 30 pressure drop, so that the pump 11 delivers at low pressure loss to the tank 13.
  • the pressure medium delivered by the pump 11 flows via the pump line 14 and the line 17 to the directional control valve 19, further via the connection 24 and the throttle 25 to line 53. From there it flows further via line 48, check valve 51 and line 57 into pressure chamber 58 of working cylinder 59. If an external load now acts on the piston rod of working cylinder 59, a corresponding load pressure acts in lines 57, 48. This closes the check valve 51 so that no pressure medium can flow out of the pressure chamber 58 of the working cylinder 59.
  • the pressure building up in the pump line 14 due to the pressure medium delivered by the pump 11 can, however, now vary from the pump Propagate pen line 14 via line 53, line 48, shuttle valve 40, line 39 and line 33 to the side of switching valve 29 loaded by spring 30.
  • the ball 49 of the shuttle valve 40 shuts off the connection 42. Due to the pressure building up on the switching valve 29, this is shifted into its blocking position II.
  • the pump 11 can now build up further pressure in the pump line 14 and in the line 17. If this is greater than the load pressure, the check valve 51 opens and the pressure medium can flow via the line 57 into the pressure chamber 58 of the working cylinder 59.
  • the load acting on the working cylinder 59 is raised.
  • the pressure at the switching valve 29 is not raised.
  • the pressure medium delivered by the pump 11 flows from the pump line 14 into the line 18 and further via the connection 24 and the throttle 25 on the control slide 23 of the directional control valve 20 into line 65.
  • the check valve 71 is closed by the load pressure.
  • the current delivery pressure moves the ball 66 of the shuttle valve 47 to the port 63 and shuts it off.
  • the ball 49 of the shuttle valve 40 is pressed onto the connection 43 and shuts it off, so that the delivery pressure can act on the side of the switching valve 29 loaded by the spring 30.
  • the switching valve 29 is shifted into the blocking position II.
  • the check valve 71 opens and the pressure medium flows via line 74 into pressure chamber 75 of working cylinder 76.
  • the pressure medium flowing out of the other pressure chamber 77 flows through lines 78, 73 into tank 13.
  • the directional control valves 19, 20 instead of the double-acting working cylinders 59, 76. It has proven to be advantageous not to raise the pressure at the switching valve 29 in the case of double-acting working cylinders and to increase this pressure only in the case of single-acting working cylinders.
  • the directional control valve 20 can also be designed as a 6/3 directional control valve. Of course, it is also possible that the pressure increase on the side opposite the spring 30 on the switching valve 29 is effective. The switching positions of the switching valve 29 are to be changed accordingly.
  • FIG. 2 shows a constructive embodiment of a detail of the exemplary embodiment according to FIG. 1 with a single-acting working cylinder.
  • the same components are again identified with the same reference numbers as before.
  • An approximately central longitudinal bore 82 is formed in a housing 81 of the directional control valve 19 or 20, in which the control slide 23 is slidably guided.
  • Eight annular grooves 84 to 91 are formed in the longitudinal bore 82.
  • the control slide 23 has five piston parts 94, 95, 96, 97, 98, which are separated from one another by annular grooves 99 to 102.
  • a control edge J05 facing the annular groove 99 is located on the piston part 94.
  • a control edge on the piston part 97 facing the annular groove 101 corresponds in its function to the throttle 25 in FIG. 1.
  • a line 107 connects the annular groove 85 to the pressure chamber 108 of a single-acting working cylinder 109.
  • the line 17 opens into the annular groove 90 and the return line 28 opens into the annular groove 84.
  • a channel corresponding to the line 56 connects the annular groove 87 to the connection 43 of the shuttle valve 40 and further via the throttle 50 to the line 48.
  • annular groove 87 can be connected to the annular groove 88 via the annular groove 100 on the control slide 23. A connection corresponding to line 56 in FIG. 1 can thereby be controlled.

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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)

Abstract

1. Hydraulic control device (10) having at least one way valve (19) adapted to control a consumer (59), the control element (23) of which, in a neutral position, shuts off at least one pipe (57, 61) leading to the consumer (59), and in tow work position (I, III) connects them selectively to an inlet pipe (14, 17) or to a first return pipe (28), having a changeover valve (29) for the direct return of the pressurized medium delivered into the inlet pipe (14, 17) from a pressurized medium source (11) into the first return pipe (28) having a control pipe (32, 33) associated with the changeover valve (29) and branching from the inlet pipe (14, 17), into which at least a first throttle point (34) is connected, the pressure differential of which acts upon a closure element of the changeover valve (29) counter to the force of a spring (30), having a first change valve (40), which is connected through a central connection (41) and a first pipe (39) connected thereto issuing between the first throttle point (34) and the spring chamber of the spring (30) of the changeover valve (29), to the control pipe (32, 33), the first seat connection (42) of which is connected to a second return pipe (46), and the second seat connection (43) of which communicates through a second pipe (48) whith the first way valve (19), characterized in that a second throttle point (50) is arranged in the second pipe (48) leading to the first way valve (19), the pressure of which prevailing on the side of the first change valve (40) acts through this first change valve (40) upon that side of the changeover valve (29) loaded by the spring (30), that this second pipe (48) is secured by a first non-return valve (51) towards the second throttle point (50), and that, at least in one work position (I, III) of the first way valve (19) the inlet pipe (14, 17) communicates through first said way valve with the second pipe (48).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Steuereinrichtung nach der Gattung des Hauptanspruchs. Bei einer derartigen bekannten Steuereinrichtung ist bei Neutralstellung der Wegeventile eine Entlastung des Federraums der Druckwaage nur mit einer gewissen Verzögerung möglich. Während des Abgriffs des Lastdrucks kann auch Druckmittel zum Tank durchlecken, wodurch die Position des Verbrauchers beeinträchtigt wird. Die Unfallgefahr ist dadurch erhöht.The invention relates to a control device according to the preamble of the main claim. In such a known control device, relief of the spring chamber of the pressure compensator is only possible with a certain delay when the directional control valves are in the neutral position. During the tapping of the load pressure, pressure medium can also leak to the tank, which affects the position of the consumer. This increases the risk of accidents.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Steuereinrichtung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß kein Druckmittel zum Tank durchlecken kann und im Schaltübergang Lastabsinken sowie Drucküberhöhung" vermieden wird. Der an der Druckwaage angehobene Druck fällt bei Rückstellung der Wegeventile in die Neutralstellung sofort wieder ab, wodurch ein schneller Richtungswechsel der an den Wegeventilen angeschlossenen Verbrauchern möglich ist.The control device according to the invention with the characterizing features of the main claim has the advantage that no pressure medium can leak to the tank and in the switching transition load reduction and pressure increase "is avoided a quick change of direction of the consumers connected to the directional control valves is possible.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Maßnahmen möglich. Bei mehreren Wegeventilen ist es möglich, daß die Druckanhebung an der Druckwaage nur an bestimmten Verbrauchern wirksam ist. Die Steuereinrichtung kann somit gleichzeitig für Verbraucher mit und ohne Druckanhebung an der Druckwaage verwendet werden.Advantageous further developments and improvements of the measures specified in the main claim are possible through the measures listed in the subclaims. With several directional control valves, it is possible that the pressure increase on the pressure compensator is only effective for certain consumers. The control device can thus be used simultaneously for consumers with and without pressure increase on the pressure compensator.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein Schaltschema einer Steuereinrichtung und Figur 2 eine konstruktive Ausgestaltung einer Einzelheit.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. FIG. 1 shows a circuit diagram of a control device and FIG. 2 shows a structural design of a detail.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Bei einer hydraulischen Steuereinrichtung 10 saugt eine Pumpe 11 über eine Zulaufleitung 12 Druckmittel aus einem Tank 13 an und fördert es in eine Pumpenleitung 14. Von einer Stelle 15 kurz hinter der Pumpe 11 und von einer zweiten Stelle 16 zweigt von der Pumpenleitung 14 je eine Leitung 17 bzw. 18 zu den jeweiligen 7/3-Wegeventilen 19, 20 ab. Die Wegeventile 19, 20 sind untereinander gleich, so daß nur das Wegeventil 1.9 näher beschrieben wird. Es hat die Schaltstellungen I, II, III und die Anschlüsse a, b auf der einen Seite und c, d, e, f, g auf der anderen Seite. In Schaltstellung II, die der Neutralstellung des zugeordneten Steuerschiebers 23 entspricht, sind die Anschlüsse a, b, e, f, g gesperrt und die Anschlüsse c, d miteinander verbunden.
In Schaltstellung I haben jeweils die Anschlüsse a und e, b und c, f und g miteinander Verbindung und der Anschluß d ist gesperrt. Am Steuerschieber 23 ist in einer Verbindung 24 des Anschlusses f mit dem Anschluß g eine Drossel 25 ausgebildet. In Schaltstellung III sind jeweils die Anschlüsse a und c, b und e miteinander verbunden.In the case of a hydraulic control device 10, a pump 11 draws pressure medium from a tank 13 via an inlet line 12 and conveys it into a pump line 14. From a point 15 shortly behind the pump 11 and from a second point 16, a line branches off from the pump line 14 17 and 18 to the respective 7/3-way valves 19, 20 from. The directional control valves 19, 20 are identical to one another, so that only the directional control valve 1.9 is described in more detail. It has the switch positions I, II, III and the connections a, b on one side and c, d, e, f, g on the other side. In switch position II, which corresponds to the neutral position of the associated control slide 23, the connections a, b, e, f, g are blocked and the connections c, d are connected to one another.
In switch position I, connections a and e, b and c, f and g are connected to one another and connection d is blocked. On the spool 23 is in egg ner connection 24 of the connection f with the connection g a throttle 25 is formed. In switch position III, the connections a and c, b and e are connected to one another.

Von der Pumpenleitung 14 zweigt von der Stelle 15 eine Leitung 27 ab und führt zu einer zum Tank 13 verlaufenden Rücklaufleitung 28. In der Leitung 27 ist ein hydraulisch vorsteuerbares 2/2-Schaltventil 29 angeordnet, das eine Durchflußstellung I und eine Sperrstellung II hat und von einer Feder 30 belastet ist. Von einer Stelle 31 vor dem Schaltventil 29, das als Druckwaage dient, zweigt von der Leitung 27 eine Leitung 32 zur einen Stirnseite des Schaltventils 29 ab. Eine zweite Leitung 33 führt von der Stelle 31 zur anderen, von der Feder 30 belasteten Stirnseite des Schaltventils 29. In dieser Leitung 33 ist eine Drossel 34 angeordnet. An einer Zweigstelle 36 der Leitung 33 ist eine zur Leitung 27 führende und nach dem Schaltventil 29 mündende Leitung 37 angeschlossen, in der ein Druckbegrenzungsventil 38 angeordnet ist. Ferner führt von der Zweigstelle 36 eine Leitung 39 zu einem Wechselventil 40. Dieses hat einen Mittelanschluß 41, an dem die Leitung 39 mündet, und zwei Anschlüsse 42, 43. Am Anschluß 42 mündet eine Rücklaufleitung 46, die zu einem zweiten Wechselventil 47 führt. Vom Anschluß 43 zweigt eine Leitung 48 ab, die zum Anschluß e des Wegeventils 19 führt. Das Wechselventil 40 weist eine frei bewegliche Kugel 49 ohne Federbelastung als Schließglied auf.From the pump line 14 a line 27 branches off from the point 15 and leads to a return line 28 running to the tank 13. In the line 27 there is a hydraulically pilot-controllable 2/2 switching valve 29 which has a flow position I and a blocking position II and is loaded by a spring 30. From a point 31 in front of the switching valve 29, which serves as a pressure compensator, a line 32 branches off from the line 27 to one end of the switching valve 29. A second line 33 leads from the point 31 to the other end face of the switching valve 29 loaded by the spring 30. A throttle 34 is arranged in this line 33. At a branch 36 of line 33, a line 37 leading to line 27 and opening after switching valve 29 is connected, in which a pressure relief valve 38 is arranged. Furthermore, a line 39 leads from the branch 36 to a shuttle valve 40. This has a central connection 41, at which the line 39 opens, and two connections 42, 43. At the connection 42, a return line 46 leads to a second shuttle valve 47. A line 48 branches off from the connection 43 and leads to the connection e of the directional control valve 19. The shuttle valve 40 has a freely movable ball 49 without spring loading as a closing member.

In der Leitung 48 sind in Reihe eine Drossel 50 und ein Rückschlagventil 51 angeordnet. Das Rückschlagventil 5J sichert zwischen der Drossel 50 und dem Wegeventil J9 die Leitung 48 zum Wechs.elventil 40 hin ab. Zwischen Drossel 50 und Rückschlagventil 51 führt von einer Stelle 52 eine Leitung 53 von der Leitung 48 zum Anschluß f des Wegeventils 19. Von einer Stelle 55 zwisehen Wechselventil 40 und Drossel 50 zweigt von der Leitung 48 eine Leitung 56 ab, die zum Anschluß d des Wegeventils 19 führt. Am Anschluß c mündet die Rücklaufleitung 28 und am Anschluß g die Leitung 17.In line 48, a throttle 50 and a check valve 51 are arranged in series. The check valve 5J secures the line 48 to the shuttle valve 40 between the throttle 50 and the directional control valve J9. Between throttle 50 and check valve 51 leads from one Position 52 a line 53 from line 48 to connection f of directional control valve 19. From a position 55 between shuttle valve 40 and throttle 50, line 48 branches off from line 48, which leads to connection d of directional control valve 19. The return line 28 opens at the connection c and the line 17 at the connection g.

Vom Anschluß a des Wegeventils 19 führt eine Leitung 57 zum einen Druckraum 58 eines doppeltwirkenden Arbeitszylinders 59. Dessen kolbenstangenseitiger Druckraum 60 ist über eine Leitung 61 mit dem Anschluß b des Wegeventils 19 verbunden.A line 57 leads from the connection a of the directional control valve 19 to a pressure chamber 58 of a double-acting working cylinder 59. Its pressure chamber 60 on the piston rod side is connected via a line 61 to the connection b of the directional control valve 19.

Die Rücklaufleitung 46 mündet am Mittelanschluß 62 des Wechselventils 47. Von dessen Anschluß 63 führt die Rücklaufleitung 46 weiter zum Tank 13. Der Anschluß 64 ist über eine Leitung 65 mit dem Anschluß f des zweiten Wegeventils 20 verbunden. Das Wechselventil 47 weist eine frei bewegliche Kugel 66 ohne Federbelastung als Schließglied auf. Kurz hinter dem Wechselventil 47 zweigt von einer Stelle 67 eine Leitung 68 ab, die zum Anschluß d des zweiten Wegeventils 20 führt. Ferner führt von einer zweiten, zwischen Stelle 67 und Wegeventil 20 gelegenen Stelle 69 der Leitung 65 eine Leitung 70 zum Anschluß e des Wegeventils 20. Die Leitung 70 ist durch ein Rückschlagventil 71 zur Leitung 65 hin abgesichert. Am Anschluß c mündet eine zum Tank 13 führende Rücklaufleitung 73 und am Anschluß g die Leitung 18.The return line 46 opens at the central connection 62 of the shuttle valve 47. From the connection 63, the return line 46 leads further to the tank 13. The connection 64 is connected via a line 65 to the connection f of the second directional valve 20. The shuttle valve 47 has a freely movable ball 66 without spring loading as a closing member. Shortly behind the shuttle valve 47, a line 68 branches off from a point 67 and leads to the connection d of the second directional valve 20. Furthermore, a line 70 leads from a second point 69 of the line 65, located between point 67 and directional control valve 20, to the connection e of the directional control valve 20. The line 70 is protected by a check valve 71 to the line 65. A return line 73 leading to the tank 13 opens at the connection c and the line 18 at the connection g.

Vom Anschluß a des Wegeventils 20 führt eine Leitung 74 zum Druckraum 75 eines zweiten doppeltwirkenden Arbeitszylinders 76. Dessen kolbenstangenseitiger Druckraum 77 ist über eine Leitung 78 mit dem Anschluß b des Wegeventils 20 verbunden.A line 74 leads from the connection a of the directional control valve 20 to the pressure chamber 75 of a second double-acting working cylinder 76. Its pressure chamber 77 on the piston rod side is connected via a line 78 to the connection b of the directional control valve 20.

Befinden sich beide Wegeventile 19, 20 in Schaltstellung II, so sind die Leitungen 17, 18, 53, 48, 65, 70 gesperrt. Die Leitungen 53 und 48 sind über die Leitung 56, das Wegeventil 19 und die Rücklaufleitung 28 zum Tank 13 hin druckentlastet. Ebenfalls sind die Leitungen 65 und 70 über die Leitung 68, das Wegeventil 20 und die Rücklaufleitung 73 zum Tank 13 hin entlastet. Das von der Pumpe 11 geförderte Druckmittel strömt von der Pumpenleitung 14 in die Leitung 27, über das sich in Durchflußstellung I befindende Schaltventil 29 in die Rücklaufleitung 28 und in den Tank 13 zurück. Das Druckmittel fließt aber auch von der Leitung 27 in die Leitung 32 und in die Leitung 33. Die dabei an der Drossel 34 auftretende Druckdifferenz hält das Schaltventil 29 entgegen der Kraft der Feder 30 in seiner Durchflußstellung I. Dadurch tritt am Schaltventil 29 nur ein geringer, weitgehend durch die Feder 30 bewirkter Druckabfall auf, so daß die Pumpe 11 bei geringem Druckverlust zum Tank 13 fördert.If both directional control valves 19, 20 are in switch position II, lines 17, 18, 53, 48, 65, 70 are blocked. The lines 53 and 48 are relieved of pressure via the line 56, the directional control valve 19 and the return line 28 to the tank 13. Lines 65 and 70 are also relieved via line 68, directional control valve 20 and return line 73 to tank 13. The pressure medium conveyed by the pump 11 flows from the pump line 14 into the line 27, via the switching valve 29 in the flow position I into the return line 28 and back into the tank 13. However, the pressure medium also flows from line 27 into line 32 and into line 33. The pressure difference occurring at the throttle 34 keeps the switching valve 29 in its flow position I against the force of the spring 30. As a result, only a small amount occurs at the switching valve 29 , largely caused by the spring 30 pressure drop, so that the pump 11 delivers at low pressure loss to the tank 13.

Wird nun nur das Wegeventil 19 betätigt und in seine Schaltstellung I verschoben, so strömt das von der Pumpe 11 geförderte Druckmittel über die Pumpenleitung 14 und die Leitung 17 zum Wegeventil 19, weiter über die Verbindung 24 und die Drossel 25 zur Leitung 53. Von dort fließt es weiter über die Leitung 48, das Rückschlagventil 51 und die Leitung 57 in den Druckraum 58 des Arbeitszylinders 59. Wirkt nun auf die Kolbenstange des Arbeitszylinders 59 eine äußere Last, so wirkt in den Leitungen 57, 48 ein entsprechender Lastdruck. Dieser verschließt das Rückschlagventil 51, so daß kein Druckmittel aus dem Druckraum 58 des Arbeitszylinders 59 abströmen kann. Der sich in der Pumpenleitung 14 durch das von der Pumpe 11 geförderte Druckmittel aufbauende Druck kann sich jetzt aber von der Pumpenleitung 14 über die Leitung 53, die Leitung 48, das Wechselventil 40, die Leitung 39 und die Leitung 33 zur von der Feder 30 belasteten Seite des Schaltventils 29 fortpflanzen. Die Kugel 49 des Wechselventils 40 sperrt den Anschluß 42 ab. Durch den sich am Schaltventil 29 aufbauenden Druck wird dieses in seine Sperrstellung II verschoben. Dadurch kann die Pumpe 11 nun weiter Druck in der Pumpenleitung 14 und in der Leitung 17 aufbauen. Ist dieser größer als der Lastdruck, so öffnet das Rückschlagventil 51, und das Druckmittel kann über die Leitung 57 in den Druckraum 58 des Arbeitszylinders 59 strömen. Die am Arbeitszylinder 59 wirkende Last wird angehoben. Gleichzeitig strömt aber auch ein kleinerer Teilstrom des von der Pumpe 11 geförderten Druckmittels von der Pumpenleitung 14 über die Leitung 27, die Leitungen 33, 39, über das Wechselventil 40 und die Leitung 48 zum Wegeventil 19. Der an der Drossel 34 abfallende Druck wirkt auf das Schaltventil 29 und verschiebt dieses in Durchflußstellung I. Gleichzeitig wirkt aber auch der an der Drossel 50 abfallende Druck auf die von der Feder 30 belastete Seite des Schaltventils 29 und erhöht dadurch den Druck an dieser Seite des Schaltventils 29. Der wirksame Druckunterschied zwischen den beiden Seiten des Schaltventils 29 wird dadurch verkleinert. Dadurch ist es möglich, daß bei Neutralstellung des Wegeventils 19 an der durch die Feder 30 belasteten Seite des Schaltventils 29 nur die geringere Kraft der Feder 30 wirkt, und daß bei betätigtem Wegeventil 19 der Druck an dieser Seite durch den Druckabfall an der Drossel 50 erhöht ist. Somit kann das Druckmittel bei unbetätigtem Wegeventil 19 mit geringerem Druckverlust zum Tank 13 zurückströmen; bei betätigtem Wegeventil 19 wird das Druckmittel stärker angedrosselt, und es kann sich ein dem Lastdruck entsprechender Förderdruck schnell aufbauen. Über das Schaltventil 29 kann überschüssiges Druckmittel von der Pumpenleitung 14 über die Leitung 27 und die Rücklaufleitung 28 in den Tank 13 abströmen. Durch die Drossel 24 am Steuerschieber 23 des Wegeventils 19 wird die Größe der Druckmittelmenge zum Arbeitszylinder 59 gesteuert. Am Arbeitszylinder 59 auftretende Druckschwankungen werden durch das Schaltventil 29 ausgeglichen.If now only the directional control valve 19 is actuated and shifted into its switching position I, the pressure medium delivered by the pump 11 flows via the pump line 14 and the line 17 to the directional control valve 19, further via the connection 24 and the throttle 25 to line 53. From there it flows further via line 48, check valve 51 and line 57 into pressure chamber 58 of working cylinder 59. If an external load now acts on the piston rod of working cylinder 59, a corresponding load pressure acts in lines 57, 48. This closes the check valve 51 so that no pressure medium can flow out of the pressure chamber 58 of the working cylinder 59. The pressure building up in the pump line 14 due to the pressure medium delivered by the pump 11 can, however, now vary from the pump Propagate pen line 14 via line 53, line 48, shuttle valve 40, line 39 and line 33 to the side of switching valve 29 loaded by spring 30. The ball 49 of the shuttle valve 40 shuts off the connection 42. Due to the pressure building up on the switching valve 29, this is shifted into its blocking position II. As a result, the pump 11 can now build up further pressure in the pump line 14 and in the line 17. If this is greater than the load pressure, the check valve 51 opens and the pressure medium can flow via the line 57 into the pressure chamber 58 of the working cylinder 59. The load acting on the working cylinder 59 is raised. At the same time, however, a smaller partial flow of the pressure medium delivered by the pump 11 flows from the pump line 14 via the line 27, the lines 33, 39, via the shuttle valve 40 and the line 48 to the directional control valve 19. The pressure drop at the throttle 34 acts the switching valve 29 and moves it to the flow position I. At the same time, however, the pressure drop across the throttle 50 also acts on the side of the switching valve 29 loaded by the spring 30 and thereby increases the pressure on this side of the switching valve 29. The effective pressure difference between the two Sides of the switching valve 29 is thereby reduced. This makes it possible that when the directional control valve 19 is in the neutral position, only the lower force of the spring 30 acts on the side of the switching valve 29 loaded by the spring 30, and that when the directional control valve 19 is actuated, the pressure on this side increases due to the pressure drop at the throttle 50 is. Thus, when the directional control valve 19 is not actuated, the pressure medium can flow back to the tank 13 with less pressure loss; when the directional control valve 19 is actuated, the pressure medium is throttled to a greater extent, and a delivery pressure corresponding to the load pressure can build up quickly. Excess pressure medium can be transferred from the pump line 14 via the switching valve 29 the line 27 and the return line 28 flow into the tank 13. The size of the pressure medium quantity to the working cylinder 59 is controlled by the throttle 24 on the control slide 23 of the directional control valve 19. Pressure fluctuations occurring on the working cylinder 59 are compensated for by the switching valve 29.

Wird nur das Wegeventil 20 betätigt, z.B. in Schaltstellung I verschoben, und ist das Wegeventil 19 nicht betätigt, so wird der Druck am Schaltventil 29 nicht angehoben. Das von der Pumpe 11 geförderte Druckmittel strömt von der Pumpenleitung 14 in die Leitung 18 und weiter über die Verbindung 24 und die Drossel 25 am Steuerschieber 23 des Wegeventils 20 in die Leitung 65. Wie oben beschrieben, ist durch den Lastdruck das Rückschlagventil 71 geschlossen. Der momentane Förderdruck verschiebt die Kugel 66 des Wechselventils 47 zum Anschluß 63 und sperrt diesen ab. Die Kugel 49 des Wechselventils 40 wird auf den Anschluß 43 gedrückt und sperrt diesen ab, so daß der Förderdruck auf die von der Feder 30 belasteten Seite des Schaltventils 29 einwirken kann. Das Schaltventil 29 wird in Sperrstellung II verschoben. Hat der Förderdruck den Lastdruck erreicht, so öffnet das Rückschlagventil 71, und das Druckmittel strömt über die Leitung 74 in den Druckraum 75 des Arbeitszylinders 76. Das aus dem anderen Druckraum 77 abströmende Druckmittel fließt über die Leitungen 78, 73 in den Tank 13 ab.If only the directional control valve 20 is actuated, e.g. shifted into switching position I, and the directional control valve 19 is not actuated, the pressure at the switching valve 29 is not raised. The pressure medium delivered by the pump 11 flows from the pump line 14 into the line 18 and further via the connection 24 and the throttle 25 on the control slide 23 of the directional control valve 20 into line 65. As described above, the check valve 71 is closed by the load pressure. The current delivery pressure moves the ball 66 of the shuttle valve 47 to the port 63 and shuts it off. The ball 49 of the shuttle valve 40 is pressed onto the connection 43 and shuts it off, so that the delivery pressure can act on the side of the switching valve 29 loaded by the spring 30. The switching valve 29 is shifted into the blocking position II. When the delivery pressure has reached the load pressure, the check valve 71 opens and the pressure medium flows via line 74 into pressure chamber 75 of working cylinder 76. The pressure medium flowing out of the other pressure chamber 77 flows through lines 78, 73 into tank 13.

Werden die beiden parallel geschalteten Wegeventile 19, 20 gleichzeitig betätigt, so wird der jeweils größere Lastdruck über die Wechselventile 40, 47 und die Leitung 39 zum Schaltventil 29 zurückgemeldet. Abhängig davon, an welchem Wegeventil 19 oder 20 dieser höhere Lastdruck wirkt, wird der Druck am Schaltventil 29 angehoben oder nicht.If the two parallel directional control valves 19, 20 are actuated simultaneously, the greater load pressure in each case is reported back to the switching valve 29 via the shuttle valves 40, 47 and the line 39. Depending on which directional control valve 19 or 20 this higher load pressure acts on, the pressure at the switching valve 29 is raised or not.

Selbstverständlich ist es auch möglich, statt der doppeltvirkenden Arbeitszylinder 59, 76 einfachwirkende Arbeitszylinder an die Wegeventile 19, 20 anzuschließen. Es hat sich als vorteilhaft erwiesen, bei doppeltvirkenden Arbeitszylindern den Druck am Schaltventil 29 nicht anzuheben und nur bei einfachwirkenden Arbeitszylindern diesen Druck zu erhöhen. Das Wegeventil 20 kann auch als 6/3-Wegeventil ausgebildet sein. Selbstverständlich ist es auch möglich, daß die Druckanhebung auf der der Feder 30 gegenüberliegenden Seite am Schaltventil 29 wirksam ist. Dementsprechend sind die Schaltstellungen des Schaltventils 29 zu ändern.Of course, it is also possible to connect single-acting working cylinders to the directional control valves 19, 20 instead of the double-acting working cylinders 59, 76. It has proven to be advantageous not to raise the pressure at the switching valve 29 in the case of double-acting working cylinders and to increase this pressure only in the case of single-acting working cylinders. The directional control valve 20 can also be designed as a 6/3 directional control valve. Of course, it is also possible that the pressure increase on the side opposite the spring 30 on the switching valve 29 is effective. The switching positions of the switching valve 29 are to be changed accordingly.

In Figur 2 ist eine konstruktive Ausgestaltung einer Einzelheit des Ausführungsbeispiels nach Figur mit einem einfachwirkenden Arbeitszylinder dargestellt. Gleiche Bauteile sind wieder wie zuvor mit denselben Bezugsziffern bezeichnet. In einem Gehäuse 81 des Wegeventils 19 bzw. 20 ist eine etwa mittige Längsbohrung 82 ausgebildet, in der der Steuerschieber 23 gleitend geführt ist. In der Längsbohrung 82 sind acht Ringnuten 84 bis 91 ausgebildet. Der Steuerschieber 23 weist fünf Kolbenteile 94, 95, 96, 97, 98 auf, die durch Ringnuten 99 bis 102 voneinander getrennt sind. Am Kolbenteil 94 befindet sich eine der Ringnut 99 zugewandte Steuerkante J05. Eine der Ringnut 101 zugewandte Steuerkante am Kolbenteil 97 entspricht in ihrer Funktion der Drossel 25 in Figur 1. Eine Leitung 107 verbindet die Ringnut 85 mit dem Druckraum 108 eines einfachwirkenden Arbeitszylinders 109.FIG. 2 shows a constructive embodiment of a detail of the exemplary embodiment according to FIG. 1 with a single-acting working cylinder. The same components are again identified with the same reference numbers as before. An approximately central longitudinal bore 82 is formed in a housing 81 of the directional control valve 19 or 20, in which the control slide 23 is slidably guided. Eight annular grooves 84 to 91 are formed in the longitudinal bore 82. The control slide 23 has five piston parts 94, 95, 96, 97, 98, which are separated from one another by annular grooves 99 to 102. A control edge J05 facing the annular groove 99 is located on the piston part 94. A control edge on the piston part 97 facing the annular groove 101 corresponds in its function to the throttle 25 in FIG. 1. A line 107 connects the annular groove 85 to the pressure chamber 108 of a single-acting working cylinder 109.

In die Ringnut 90 mündet die Leitung 17 und in die Ringnut 84 mündet die Rücklaufleitung 28. Von der Ringnut 89 führt ein Kanal, der der Leitung 53 entspricht, zu einem der Leitung 48 entsprechenden Kanal. Dieser mündet in die Ringnut 86. Ein der Leitung 56 entsprechender Kanal verbindet die Ringnut 87 mit dem Anschluß 43 des Wechselventils 40 und weiter über die Drossel 50 mit der Leitung 48.The line 17 opens into the annular groove 90 and the return line 28 opens into the annular groove 84. A channel, which corresponds to the line 53, leads from the annular groove 89 to a channel corresponding to the line 48. This ends in the annular groove 86. A channel corresponding to the line 56 connects the annular groove 87 to the connection 43 of the shuttle valve 40 and further via the throttle 50 to the line 48.

Da nur ein einfachwirkender Arbeitszylinder 109 über die Leitung 107 an der Ringnut 85 angeschlossen ist, kann über die Ringnut 100 am Steuerschieber 23 die Ringnut 87 mit der Ringnut 88 verbunden werden. Dadurch kann eine der Leitung 56 in Figur 1 entsprechende Verbindung gesteuert werden.Since only a single-acting working cylinder 109 is connected to the annular groove 85 via the line 107, the annular groove 87 can be connected to the annular groove 88 via the annular groove 100 on the control slide 23. A connection corresponding to line 56 in FIG. 1 can thereby be controlled.

Claims (7)

1. Hydraulische Steuereinrichtung (10) mit mindestens einem zum Steuern eines Verbrauchers (59) geeigneten Wegeventils (19), dessen Steuerglied (23) in einer Neutralstellung mindestens eine zum Verbraucher (59) führende Leitung (57, 61) absperrt und in zwei Arbeitsstellungen (I, III) wechselweise mit einer Zulaufleitung (14, 17) oder einer Rücklaufleitung (28) verbindet, mit einem Umschaltventil (29) zur unmittelbaren Rückleitung des in die Zulaufleitung (14, 17) von einer Druckmittelquelle (11) geförderten Druckmittels in die Rücklaufleitung (28), mit einer dem Umschaltventil (29) zugeordneten Steuerleitung (33), in die mindestens eine Drosselstelle (34) geschaltet ist, deren Druckdifferenz an einem Schließglied des Umschaltventils (29) entgegen der Kraft einer Feder (30) wirksam ist, mit mindestens einem Wechselventil (40), das über einen Mittelanschluß (41) und eine Leitung (39) an die Steuerleitung (33) angeschlossen ist, dessen erster Sitzanschluß (42) mit einer Rücklaufleitung (46) verbunden ist und dessen zweiter Sitzanschluß (43) über eine Leitung (48) mit dem ersten Wegeventil (19) Verbindung hat und mit Mitteln zur lastunabhängigen Steuerung des Verbrauchers (59), dadurch gekennzeichnet, daß in der zum ersten Wegeventil (19) führenden Leitung (48) eine zweite Drosselstelle (50) angeordnet ist, deren Druckgefälle auf die durch die Feder (30) belastete Seite des Umschaltventils (29) einwirkt, daß diese Leitung (48) durch ein Rückschlagventil (51) abgesichert ist, und daß die Pumpenleitung (14, 17) mit dieser Leitung (48) Verbindung hat.1. Hydraulic control device (10) with at least one directional control valve (19) suitable for controlling a consumer (59), the control member (23) of which blocks at least one line (57, 61) leading to the consumer (59) in a neutral position and in two working positions (I, III) alternately connects to an inlet line (14, 17) or a return line (28), with a changeover valve (29) for direct return of the pressure medium conveyed into the inlet line (14, 17) from a pressure medium source (11) into the Return line (28), with a control line (33) assigned to the changeover valve (29), into which at least one throttle point (34) is connected, the pressure difference of which acts on a closing element of the changeover valve (29) against the force of a spring (30), with at least one shuttle valve (40), which is connected to the control line (33) via a center connection (41) and a line (39), the first seat connection (42) of which has a return line (4 6) is connected and its second seat connection (43) has a line (48) with the first directional valve (19) and means for load-independent control of the consumer (59), characterized in that in the first directional valve (19) leading line (48) a second throttle point (50) is arranged, the pressure drop on the spring (30) loaded side of the changeover valve (29) acts that this line (48) is secured by a check valve (51) and that the pump line (14, 17) with this line (48) has a connection. 2. Steuereinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Leitung (48) zwischen erstem Wechselventil (40) und Rückschlagventil (51) über eine Leitung (56) bei Neutralstellung (II) des ersten Wegeventils (19) zum Tank (13) hin entlastbar ist, und daß diese Leitung (56) in mindestens einer Arbeitsstellung (I, III) gesperrt ist.2. Control device according to claim 1, characterized in that the line (48) between the first shuttle valve (40) and check valve (51) via a line (56) with the neutral position (II) of the first directional valve (19) to the tank (13) can be relieved, and that this line (56) is blocked in at least one working position (I, III). 3. Steuereinrichtung nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß die Pumpenleitung (14, 17) zwischen der Drossel (50) und dem Rückschlagventil (51) in die Leitung (48) mündet.3. Control device according to claim 1 and / or 2, characterized in that the pump line (14, 17) between the throttle (50) and the check valve (51) opens into the line (48). 4. Steuereinrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Leitung (56) zwischen dem Wechselventil (40) und der Drossel (50) in die Leitung (48) mündet.4. Control device according to one of claims 1 to 3, characterized in that the line (56) between the shuttle valve (40) and the throttle (50) opens into the line (48). 5. Steuereinrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß ein zweites Wegeventil (20) über ein zweites Wechselventil (47) an die Rücklaufleitung (46) anschließbar ist, daß in einer Leitung (70), die vom Wechselventil (47) zum Wegeventil (20) führt, ein Rückschlagventil (71) angeordnet ist, und daß die Leitung (70) mit der Pumpenleitung (14, 18) verbindbar ist.5. Control device according to one of claims 1 to 4, characterized in that a second directional valve (20) via a second shuttle valve (47) to the return line (46) can be connected, that in a line (70) from the shuttle valve (47 ) leads to the directional control valve (20), a check valve (71) is arranged, and that the line (70) can be connected to the pump line (14, 18). 6. Steuereinrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß an das erste Wegeventil (19) ein einfachwirkender Verbraucher angeschlossen ist.6. Control device according to one of claims 1 to 5, characterized in that a single-acting consumer is connected to the first directional valve (19). 7. Steuereinrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß an das zweite Wegeventil (20) ein doppeltwirkender Verbraucher (76) angeschlossen ist.7. Control device according to one of claims 1 to 6, characterized in that a double-acting consumer (76) is connected to the second directional valve (20).
EP19850106903 1984-07-10 1985-06-04 Hydraulic control device Expired EP0167818B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3435304 1984-07-10
DE19843435304 DE3435304A1 (en) 1983-10-10 1984-09-26 METHOD AND DEVICE FOR ENLARGING THE BANDWIDTH OF A HIGH-SPEED MODULATOR

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Publication Number Publication Date
EP0167818A1 true EP0167818A1 (en) 1986-01-15
EP0167818B1 EP0167818B1 (en) 1988-06-01

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0297401A2 (en) * 1987-07-03 1989-01-04 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Hydraulic control device
GB2210678A (en) * 1987-10-05 1989-06-14 Rexroth Mannesmann Gmbh Control system for a hydraulic lift
US4967554A (en) * 1987-10-05 1990-11-06 Mannesmann Rexroth Gmbh Commonly-piloted directional control valve and load pressure signal line relieving switching valve

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9111233U1 (en) * 1991-09-10 1991-10-31 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München Directional spool valves for hydraulic controls

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Publication number Priority date Publication date Assignee Title
DE2457451A1 (en) * 1974-12-05 1976-06-10 Bosch Gmbh Robert HYDRAULIC CONTROL DEVICE
US3971216A (en) * 1974-06-19 1976-07-27 The Scott & Fetzer Company Load responsive system with synthetic signal
DE2620041A1 (en) * 1976-05-06 1977-11-24 Bosch Gmbh Robert Hydraulic controller with load control valve - has valve control element which cuts off line passing to load and has two positions
US4089169A (en) * 1976-08-19 1978-05-16 The Scott & Fetzer Company Pressure actuated signal fluid control for load responsive systems

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3971216A (en) * 1974-06-19 1976-07-27 The Scott & Fetzer Company Load responsive system with synthetic signal
DE2457451A1 (en) * 1974-12-05 1976-06-10 Bosch Gmbh Robert HYDRAULIC CONTROL DEVICE
DE2620041A1 (en) * 1976-05-06 1977-11-24 Bosch Gmbh Robert Hydraulic controller with load control valve - has valve control element which cuts off line passing to load and has two positions
US4089169A (en) * 1976-08-19 1978-05-16 The Scott & Fetzer Company Pressure actuated signal fluid control for load responsive systems

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0297401A2 (en) * 1987-07-03 1989-01-04 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Hydraulic control device
EP0297401A3 (en) * 1987-07-03 1991-03-13 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Hydraulic control device
GB2210678A (en) * 1987-10-05 1989-06-14 Rexroth Mannesmann Gmbh Control system for a hydraulic lift
US4960035A (en) * 1987-10-05 1990-10-02 Mannesmann Rexroth Gmbh Control system for a hydraulic lift driven by a variable displacement pump
US4967554A (en) * 1987-10-05 1990-11-06 Mannesmann Rexroth Gmbh Commonly-piloted directional control valve and load pressure signal line relieving switching valve
GB2210678B (en) * 1987-10-05 1991-12-04 Rexroth Mannesmann Gmbh Control system for a hydraulic lift driven by a variable displacement pump

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