EP0362539A1 - Hydraulic control device - Google Patents

Hydraulic control device Download PDF

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Publication number
EP0362539A1
EP0362539A1 EP19890115655 EP89115655A EP0362539A1 EP 0362539 A1 EP0362539 A1 EP 0362539A1 EP 19890115655 EP19890115655 EP 19890115655 EP 89115655 A EP89115655 A EP 89115655A EP 0362539 A1 EP0362539 A1 EP 0362539A1
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EP
European Patent Office
Prior art keywords
connection
control device
control
pressure
pump
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
EP19890115655
Other languages
German (de)
French (fr)
Other versions
EP0362539B1 (en
Inventor
Gottfried Dipl.-Ing. Olbrich
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0362539A1 publication Critical patent/EP0362539A1/en
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Publication of EP0362539B1 publication Critical patent/EP0362539B1/en
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • F15B2211/35—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
    • F15B2211/60—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
    • F15B2211/60—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
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit 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
    • F15B2211/70—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 is based on a hydraulic control device for load pressure-independent control of at least one hydraulic motor according to the preamble of the main claim.
  • Such a hydraulic control device is already known from US Pat. No. 3,774,635, in particular FIGS. 6 and 7, which is designed in the so-called LS technology and can optionally be used in connection with a constant pump or with a variable displacement pump for supplying pressure medium.
  • This control device already has a 2-way throttle valve working as a pressure compensator and connected in a shunt channel, as well as a control pressure connection, from which a maximum load pressure can be fed externally to a regulator of the variable pump.
  • Such control devices are also used in towed mobile machines, such as harvesting machines, on which hydraulic control functions are installed. These towed machines are hydraulically connected to the tractor, in particular a tractor, via hose couplings and fed by their pump system. Now different tractors also have different pump systems.
  • the disadvantage is that the known control device for this changeover interventions in the control device are necessary, which require a relatively high cost.
  • a pressure limiting valve must be provided instead of the throttle valve, changes also being necessary in the course of the control pressure line system.
  • this control device only has a return connection, which cannot be used as a continue connection.
  • variable pumps as well as variable pumps are used as a pressure medium source.
  • changes from one system to the other system are only possible with relatively complex interventions in the control device, so that it is poorly suited for use with towed mobile machines.
  • the hydraulic control device according to the invention with the characterizing features of the main claim has the advantage that it can be converted to different pump systems in a simple, safe and cost-effective manner by using externally controllable locking means.
  • the function of the throttle valve operating as a pressure compensator can be maintained or blocked by externally or internally provided hydraulic locking means in order to adapt it to the different pump systems are sufficient without interfering with the directional valve block itself.
  • the switchable control device is therefore particularly suitable for use in rough, agricultural operations.
  • FIG. 1 shows a first control device 10, which essentially consists of a directional valve block 11 and a constant pump 12 serving as a pressure medium source.
  • the directional valve block 11 is designed for load pressure-independent control of two consumers and, for this purpose, has a single-acting, first directional valve 13 and a double-acting second directional valve 14, which are flanged between a connecting plate 15 and an end plate 16.
  • the two directional control valves 13, 14 are connected with their inlet connections 17 in parallel to one another to an inlet channel 18 which starts from a pump connection 19 denoted by P in the connection plate 15 and pulls through the directional valve block 11.
  • both directional control valves 13, 14 are connected with their drain connections 21 in parallel to a return channel 22, which leads to a return connection 23 denoted by R in the connection plate 15.
  • a shunt channel 24 branches off from the inlet channel 18 and leads to a continuation connection 25 denoted W in the connection plate 15.
  • a two-way throttle valve 26 operating as a pressure compensator is connected into this shunt channel 24.
  • the throttle valve 26 can be acted upon in a manner known per se by a spring and in the opposite direction by a pressure difference which is effective via a measuring throttle point in the respective directional control valves 13, 14 when controlling the connected hydraulic consumers.
  • the directional control valves 13, 14 and the throttle valve 26 are connected in a control line system 27 which is known per se and which selects the maximum load pressure in each case during operation and leads to the throttle valve 26.
  • This maximum load pressure is also available in a control pressure connection 28 labeled Y; this control pressure connection Y is shut off in the control device 10 with a screw 29 to the outside.
  • the control line system 27 is relieved via the end plate 16 to the return channel 22. Furthermore, a pressure limiting valve 31 is provided in the control line system 27, which, together with the throttle valve 26, performs a pilot-controlled pressure limiting function.
  • the pump connection 19 is connected via a pressure line 32 to the pressure side of the constant pump 12, while a return line 33 leads from the return connection 23 to a tank 34.
  • the flow connection 25 is connected to the return line 33 via a hydraulic cross-connection 35, a two-way valve 36 being connected to this cross-connection 35 and assuming its open position shown in FIG. 1.
  • control device 10 The mode of operation of the control device 10 is explained as follows, the basic function of the load pressure-independent control being assumed to be known per se.
  • control spools of the two directional control valves 13 and 14 are each in their center positions 37, the inlet connections 17 are blocked and the spring-loaded end face of a throttle slide in the throttle valve 26 is relieved via the control line system 27 to the return channel 22.
  • the pressure medium conveyed into the inlet channel 18 by the constant pump 12 opens the throttle valve 26, so that the entire pressure medium flow can flow out to the tank 34 via the shunt channel 24 and the further connection 25 as well as the cross connection 35 with the opened tap 36.
  • the constant pump delivers against a relatively low circulation pressure influenced by the throttle valve 26.
  • FIG. 2 now shows the first control device 10 according to FIG. 1 after its changeover to another pump system if a variable displacement pump 45 is used instead of a constant pump.
  • the screw plug 29 is only removed at the control pressure connection Y and this connection 28 is connected via a control line 46 to the control device of the variable displacement pump 45.
  • the valve 36 lying in the cross connection 35 is rotated into its drawn blocking position.
  • FIG. 3 shows part of a second control device 50, which is also intended for operation with a constant pump and which differs from the first control device 10 according to FIG. 1 as follows, the same reference numerals being used for the same components:
  • the same first plug-in couplings 51 are inserted into the pressure line 32, the return line 33 and the cross connection 35, by means of which open pressure medium connections are made in the lines concerned will.
  • the two-way valve 36 in the first control device 10 is omitted in the second control device 50.
  • an externally arranged second plug connection 52 takes over the blocking of the control pressure connection Y.
  • the function of this second control device 50 corresponds to that of the first control device 10 according to FIG. 1 .
  • Figure 4 shows the second control device 50 after its conversion for operation with a variable displacement pump 45.
  • This can be achieved simply by the control pressure connection Y also being connected to the regulating device of the variable displacement pump 45 via a first plug-in coupling 51 and the control line 46 the cross connection 35 is blocked by a third plug-in coupling 53.
  • the third plug-in coupling 53 can be achieved very easily by a double arrangement of the second plug-in coupling 52, so that the changeover can only be carried out by opening or connecting plug-in couplings.
  • the function of the second control device 50 with the variable displacement pump 45 corresponds to that of the first control device 10 according to FIG. 2. This changeover with the aid of plug connections arranged outside the directional valve block 11 can also be carried out inexpensively, simply and safely by using standard parts.
  • FIG. 5 shows part of a third control device 60 which differs from the previous control devices 10, 50 as follows, the same reference numerals being used for the same components.
  • the cross-connection 35 is laid from the flow connection 25 to the return connection 23 into the connection plate 15.
  • the 2-way valve 36 is connected to this cross connection 35, which runs internally in the directional valve block 11.
  • the return line 33 are first plug-in couplings gene 51 arranged while the control pressure port Y is shut off by a second plug-in coupling 52.
  • the flow connection 25 is now blocked off from the outside by a plug 61.
  • the function of the third control device 60 according to FIG. 5 corresponds to the first control device 10 according to FIG. 1.
  • FIG. 6 shows the third control device 60 converted to operation with a variable displacement pump 45.
  • the internally arranged 2-way valve 36 is brought into its blocking position and the control pressure connection Y is connected to the control device via a first plug-in coupling 51 and a control line 46 Variable pump 45 connected.
  • the third control device 60 according to FIG. 6, the function of which corresponds to the function of the first control device 10 according to FIG. 2, can also be changed over to different pump systems with a constant pump or variable displacement pump in a few simple steps.
  • FIGS. 7 and 8 each show part of a fourth control device 70 for constant or variable pump operation, which differ from the second control device 50 as follows, the same parts being provided with the same reference numerals.
  • the output 71 of the throttle valve 26 is connected to the return connection 23 instead of a continuation circuit.
  • a 3/2-way solenoid valve 73 is connected into the control connection 72 and can relieve a pressure chamber of the throttle valve 26 to the return connection 23.
  • the 3/2-solenoid valve 73 is controlled via an electromechanical switch 74 which is assigned to the plug connections 51, 52 at the control connection 28 and can be actuated by the latter.
  • the solenoid valve 73 is in its rest position and the throttle valve 26 can operate normally as a pressure compensator.
  • the switch 74 and the solenoid valve 73 are actuated, as a result of which the function of the throttle valve 26 is blocked.
  • a constant pressure system can also be used for the variable displacement pumps.

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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

A hydraulic control device (10) for controlling a motor independently of the load pressure is proposed, which can be converted inexpensively to different pump systems. As manometric balance, the control device (10) has a two-way throttle valve (26) with a run-on circuit (24, 25) in whose cross connection (35) to the return side (23, 33) hydraulic blocking means (36) are arranged which, in the blocking position, block the function of the manometric balance. The control device (10) is suitable for controlling hydraulic functions on mobile machines which are supplied with pressure medium by tractors having different pressure medium supply systems such as a fixed displacement pump (12) or a variable displacement pump (45). <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer hydraulischen Steuereinrichtung zur lastdruckunabhängigen Steuerung wenigstens eines hydraulischen Motors nach der Gattung des Hauptanspruchs.The invention is based on a hydraulic control device for load pressure-independent control of at least one hydraulic motor according to the preamble of the main claim.

Es ist schon eine solche hydraulische Steuereinrichtung aus der US-PS 3 774 635, insbesondere Figur 6 und 7, bekannt, die in der so­genannten LS-Technik ausgebildet ist und wahlweise im Zusammenhang mit einer Konstantpumpe oder mit einer Verstellpumpe zur Druckmit­telversorgung verwendbar ist. Diese Steuereinrichtung weist bereits ein als Druckwaage arbeitendes, in einen Nebenschlußkanal geschalte­tes 2-Wege-Drosselventil sowie einen Steuerdruckanschluß auf, von dem ein maximaler Lastdruck extern zu einem Regler der Verstellpumpe führbar ist. Solche Steuereinrichtungen werden auch bei gezogenen Mobil-Maschinen, wie z.B. Erntemaschinen, verwendet, auf denen hy­draulische Steuerfunktionen installiert sind. Diese gezogenen Ma­schinen werden über Schlauchkupplungen hydraulisch mit der Zug­maschine, insbesondere einem Schlepper verbunden und von deren Pum­pensystem gespeist. Nun weisen verschiedene Schlepper auch verschie­dene Pumpensysteme auf. Dies kann eine Konstantpumpe mit Neutralum­lauf, eine bei LS-Technik verwendete Druck-Strom-geregelte Verstell­ pumpe oder eine im Konstantdrucksystem verwendete druckgeregelte Verstellpumpe sein. Werden also die Zugmaschinen gewechselt, so muß eine auf der gezogenen Mobil-Maschine installierte Steuereinrichtung durch möglichst geringe Maßnahmen für diese verschiedenen Pumpen­systeme umstellbar sein. Von Nachteil ist nun, daß bei der vorbe­kannten Steuereinrichtung für diese Umstellung Eingriffe in die Steuereinrichtung notwendig sind, die einen relativ hohen Aufwand erfordern. So muß bei einer Umstellung von einem Konstantpumpen­system auf eine Verstellpumpe anstelle des Drosselventils ein Druck­begrenzungsventil vorgesehen werden, wobei auch im Verlauf des Steuer-Druckleitungssystems Änderungen notwendig sind. Zudem weist diese Steuereinrichtung lediglich einen Rücklaufanschluß auf, der nicht als Weiterlaufanschluß verwendbar ist.Such a hydraulic control device is already known from US Pat. No. 3,774,635, in particular FIGS. 6 and 7, which is designed in the so-called LS technology and can optionally be used in connection with a constant pump or with a variable displacement pump for supplying pressure medium. This control device already has a 2-way throttle valve working as a pressure compensator and connected in a shunt channel, as well as a control pressure connection, from which a maximum load pressure can be fed externally to a regulator of the variable pump. Such control devices are also used in towed mobile machines, such as harvesting machines, on which hydraulic control functions are installed. These towed machines are hydraulically connected to the tractor, in particular a tractor, via hose couplings and fed by their pump system. Now different tractors also have different pump systems. This can be a constant-flow pump with neutral circulation, a pressure-current-controlled adjustment used in LS technology pump or a pressure-controlled variable displacement pump used in the constant pressure system. So if the tractors are changed, a control device installed on the towed mobile machine must be convertible for these different pump systems by means of the smallest possible measures. The disadvantage is that the known control device for this changeover interventions in the control device are necessary, which require a relatively high cost. Thus, when changing over from a constant pump system to a variable displacement pump, a pressure limiting valve must be provided instead of the throttle valve, changes also being necessary in the course of the control pressure line system. In addition, this control device only has a return connection, which cannot be used as a continue connection.

Ferner sind aus der DE-OS 22 31 217 und der US-PS 3 989 062 hydrau­lische Steuereinrichtungen zur lastdruckunabhängigen Steuerung meh­rerer hydraulischer Motoren bekannt, bei denen als Druckmittelquelle neben einer Konstantpumpe auch Verstellpumpen verwendet werden. Auch hier sind Umstellungen von einem System auf das andere System nur mit relativ aufwendigen Eingriffen in die Steuereinrichtung möglich, so daß es sich zur Verwendung bei gezogenen Mobil-Maschinen schlecht eignet.Furthermore, from DE-OS 22 31 217 and US Pat. No. 3,989,062 hydraulic control devices for load pressure-independent control of several hydraulic motors are known, in which variable pumps as well as variable pumps are used as a pressure medium source. Here too, changes from one system to the other system are only possible with relatively complex interventions in the control device, so that it is poorly suited for use with towed mobile machines.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße hydraulische Steuereinrichtung mit den kenn­zeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vor­teil, daß sie durch Verwendung von extern ansteuerbaren Sperrmit­teln auf einfache, sichere und kostengünstige Weise auf unterschied­liche Pumpensysteme umstellbar ist. Dabei kann durch extern oder intern vorgesehene hydraulische Sperrmittel die Funktion des als Druckwaage arbeitenden Drosselventils erhalten oder blockiert wer­den, um eine Anpassung an die unterschiedlichen Pumpensysteme zu er­ reichen, ohne daß hierbei Eingriffe in den Wegeventilblock selbst notwendig werden. Die umstellbare Steuereinrichtung eignet sich daher besonders zum Einsatz im rauhen, landwirtschaftlichen Betrieb.The hydraulic control device according to the invention with the characterizing features of the main claim has the advantage that it can be converted to different pump systems in a simple, safe and cost-effective manner by using externally controllable locking means. The function of the throttle valve operating as a pressure compensator can be maintained or blocked by externally or internally provided hydraulic locking means in order to adapt it to the different pump systems are sufficient without interfering with the directional valve block itself. The switchable control device is therefore particularly suitable for use in rough, agricultural operations.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vor­teilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Steuereinrichtung möglich. Sie begünstigen eine Steuer­einrichtung, bei der die Umstellung mit geringen Maßnahmen, kosten­günstig und sicher gegen Bedienungsfehler durchführbar ist. Beson­ders vorteilhaft ist eine Ausbildung nach Anspruch 2, da sich eine Weiterlaufschaltung gut mit einem Baukastensystem realisieren läßt. Ferner ist es nach Anspruch 9 zweckmäßig, das Drosselventil selbst für die Sperrfunktion zu verwenden.Advantageous further developments and improvements of the control device specified in the main claim are possible through the measures listed in the subclaims. They favor a control device in which the changeover can be carried out inexpensively and safely against operating errors using small measures. An embodiment according to claim 2 is particularly advantageous, since a continuation circuit can be implemented well with a modular system. Furthermore, it is expedient according to claim 9 to use the throttle valve itself for the blocking function.

Zeichnungdrawing

Vier Ausführungsbeispiele der Erfindung sind in der Zeichnung darge­stellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen

  • Figur 1 als erstes Ausführungsbeispiel eine Steuereinrichtung für lastdruckunabhängige Steuerung zur Verwendung mit einer Kon­stantpumpe in vereinfachter Darstellung und
  • Figur 2 die Steuerein­richtung nach Figur 1 bei Verwendung einer Regelpumpe,
  • Figur 3 einen Teil einer zweiten Steuereinrichtung mit Konstantpumpe und
  • Figur 4 die zweite Steuereinrichtung umgestellt auf einen Betrieb mit Ver­stellpumpe,
  • Figur 5 einen Teil einer dritten Steuereinrichtung für Konstantpumpen-Betrieb und
  • Figur 6 die dritte Steuereinrichtung um­gestellt auf Regelpumpen-Betrieb.
  • Figur 7 und 8 zeigen einen Teil einer vierten Steuereinrichtung für Konstant- bzw. Regelpumpe, wo­bei das Drosselventil selbst die Sperrfunktion übernimmt.
Four embodiments of the invention are shown in the drawing and explained in more detail in the following description. Show it
  • Figure 1 as a first embodiment of a control device for load pressure independent control for use with a constant pump in a simplified representation and
  • FIG. 2 shows the control device according to FIG. 1 when using a regulating pump,
  • Figure 3 shows a part of a second control device with a constant pump and
  • FIG. 4 the second control device converted to operation with a variable displacement pump,
  • Figure 5 shows part of a third control device for constant pump operation and
  • Figure 6 shows the third control device switched to control pump operation.
  • FIGS. 7 and 8 show part of a fourth control device for a constant or regulating pump, the throttle valve itself taking over the blocking function.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die Figur 1 zeigt eine erste Steuereinrichtung 10, die im wesent­lichen aus einem Wegeventilblock 11 und einer als Druckmittelquelle dienenden Konstantpumpe 12 besteht.FIG. 1 shows a first control device 10, which essentially consists of a directional valve block 11 and a constant pump 12 serving as a pressure medium source.

Der Wegeventilblock 11 ist zur lastdruckunabhängigen Steuerung zweier Verbraucher ausgebildet und weist zu diesem Zweck ein ein­fachwirkendes, erstes Wegeventil 13 sowie ein doppeltwirkendes zwei­tes Wegeventil 14 auf, die zwischen eine Anschlußplatte 15 und eine Endplatte 16 geflanscht sind. Die beiden Wegeventile 13, 14 sind mit ihren Zulaufanschlüssen 17 parallel zueinander an einen Zulaufkanal 18 angeschlossen, der von einem mit P bezeichneten Pumpenanschluß 19 in der Anschlußplatte 15 ausgeht und den Wegeventilblock 11 durch­zieht. Ferner sind beide Wegeventile 13, 14 mit ihren Ablaufan­schlüssen 21 parallel an einen Rücklaufkanal 22 angeschlossen, der zu einem mit R bezeichneten Rücklaufanschluß 23 in der Anschlußplat­te 15 führt.The directional valve block 11 is designed for load pressure-independent control of two consumers and, for this purpose, has a single-acting, first directional valve 13 and a double-acting second directional valve 14, which are flanged between a connecting plate 15 and an end plate 16. The two directional control valves 13, 14 are connected with their inlet connections 17 in parallel to one another to an inlet channel 18 which starts from a pump connection 19 denoted by P in the connection plate 15 and pulls through the directional valve block 11. Furthermore, both directional control valves 13, 14 are connected with their drain connections 21 in parallel to a return channel 22, which leads to a return connection 23 denoted by R in the connection plate 15.

In der Anschlußplatte 15 zweigt von dem Zulaufkanal 18 ein Neben­schlußkanal 24 ab, der zu einem mit W bezeichneten Weiterlaufan­schluß 25 in der Anschlußplatte 15 führt. In diesen Nebenschlußkanal 24 ist ein als Druckwaage arbeitendes 2-Wege-Drosselventil 26 ge­schaltet. Für die Funktion als Druckwaage ist das Drosselventil 26 in an sich bekannter Weise von einer Feder und in entgegengesetzter Richtung von einer Druckdifferenz beaufschlagbar, die über eine Meß­drosselstelle in den jeweiligen Wegeventilen 13, 14 beim Steuern der angeschlossenen hydraulischen Verbraucher wirksam ist. Zu diesem Zweck sind die Wegeventile 13, 14 sowie das Drosselventil 26 in ein an sich bekanntes Steuerleitungssystem 27 geschaltet, das im Betrieb den jeweils maximalen Lastdruck auswählt und zum Drosselventil 26 führt. Dieser maximale Lastdruck steht auch in einem mit Y bezeich­neten Steuerdruckanschluß 28 zur Verfügung; dieser Steuerdruckan­schluß Y ist bei der Steuereinrichtung 10 mit einer Schraube 29 nach außen hin abgesperrt.In the connection plate 15, a shunt channel 24 branches off from the inlet channel 18 and leads to a continuation connection 25 denoted W in the connection plate 15. A two-way throttle valve 26 operating as a pressure compensator is connected into this shunt channel 24. For the function as a pressure compensator, the throttle valve 26 can be acted upon in a manner known per se by a spring and in the opposite direction by a pressure difference which is effective via a measuring throttle point in the respective directional control valves 13, 14 when controlling the connected hydraulic consumers. For this purpose, the directional control valves 13, 14 and the throttle valve 26 are connected in a control line system 27 which is known per se and which selects the maximum load pressure in each case during operation and leads to the throttle valve 26. This maximum load pressure is also available in a control pressure connection 28 labeled Y; this control pressure connection Y is shut off in the control device 10 with a screw 29 to the outside.

Das Steuerleitungssystem 27 ist über die Endplatte 16 zum Rücklauf­kanal 22 entlastet. Ferner ist im Steuerleitungssystem 27 ein Druck­begrenzungsventil 31 vorgesehen, das zusammen mit dem Drosselventil 26 eine vorgesteuerte Druckbegrenzungsfunktion ausübt.The control line system 27 is relieved via the end plate 16 to the return channel 22. Furthermore, a pressure limiting valve 31 is provided in the control line system 27, which, together with the throttle valve 26, performs a pilot-controlled pressure limiting function.

Von den in der Anschlußplatte 15 liegenden Anschlüssen steht der Pumpenanschluß 19 über eine Druckleitung 32 mit der Druckseite der Konstantpumpe 12 in Verbindung, während vom Rücklaufanschluß 23 eine Rücklaufleitung 33 zu einem Tank 34 führt. Der Weiterlaufanschluß 25 steht über eine hydraulische Querverbindung 35 mit der Rücklauflei­tung 33 in Verbindung, wobei in diese Querverbindung 35 ein Zwei­wege-Hahn 36 geschaltet ist, der seine in Figur 1 gezeichnete Auf-Stellung einnimmt.From the connections located in the connection plate 15, the pump connection 19 is connected via a pressure line 32 to the pressure side of the constant pump 12, while a return line 33 leads from the return connection 23 to a tank 34. The flow connection 25 is connected to the return line 33 via a hydraulic cross-connection 35, a two-way valve 36 being connected to this cross-connection 35 and assuming its open position shown in FIG. 1.

Die Wirkungsweise der Steuereinrichtung 10 wird wie folgt erläutert, wobei die grundsätzliche Funktion der lastdruckunabhängigen Steue­rung als an sich bekannt vorausgesetzt wird.The mode of operation of the control device 10 is explained as follows, the basic function of the load pressure-independent control being assumed to be known per se.

Befinden sich die Steuerschieber der beiden Wegeventile 13 und 14 jeweils in ihren gezeichneten Mittelstellungen 37, so sind die Zu­laufanschlüsse 17 blockiert und die federbelastete Stirnseite eines Drosselschiebers im Drosselventil 26 über das Steuerleitungssystem 27 zum Rücklaufkanal 22 entlastet. Das von der Konstantpumpe 12 in den Zulaufkanal 18 geförderte Druckmittel öffnet das Drosselventil 26, so daß der gesamte Druckmittelstrom über den Nebenschlußkanal 24 und den Weiterlaufanschluß 25 sowie die Querverbindung 35 mit dem geöffneten Hahn 36 zum Tank 34 abströmen kann. Die Konstantpumpe fördert dabei gegen einen relativ niedrigen, vom Drosselventil 26 beeinflußten Umlaufdruck.If the control spools of the two directional control valves 13 and 14 are each in their center positions 37, the inlet connections 17 are blocked and the spring-loaded end face of a throttle slide in the throttle valve 26 is relieved via the control line system 27 to the return channel 22. The pressure medium conveyed into the inlet channel 18 by the constant pump 12 opens the throttle valve 26, so that the entire pressure medium flow can flow out to the tank 34 via the shunt channel 24 and the further connection 25 as well as the cross connection 35 with the opened tap 36. The constant pump delivers against a relatively low circulation pressure influenced by the throttle valve 26.

Wird einer der Steuerschieber der Wegeventile 13, 14 in eine seiner Arbeitsstellungen 38 bzw. 39 ausgelenkt, so fließt ein Druckmittel­strom von der Konstantpumpe 12 über einen der Motoranschlüsse 41 zu einem der nicht näher gezeichneten hydraulischen Motoren. Der je­weils herrschende Lastdruck wird dabei über das Steuerleitungssystem 27 zum Drosselventil 26 zurückgeführt, so daß es als Druckwaage ar­beiten kann, indem es den über den Nebenschlußkanal 24 abströmenden Teilstrom entsprechend androsselt. Durch den in seiner offenen Stel­ lung befindlichen 2-Wege-Hahn 36 wird dabei gewährleistet, daß die Funktion der Druckwaage erhalten bleibt. Vom Motor über ein Wegeven­til 13 bzw. 14 zurückströmendes Druckmittel kann dabei unabhängig von der Querverbindung 35 über den Rücklaufkanal 22 zum Tank 34 ab­strömen.If one of the control spools of the directional control valves 13, 14 is deflected into one of its working positions 38 or 39, a flow of pressure medium flows from the constant pump 12 via one of the motor connections 41 to one of the hydraulic motors (not shown). The prevailing load pressure is fed back via the control line system 27 to the throttle valve 26, so that it can operate as a pressure compensator by throttling the partial flow flowing off via the shunt channel 24 accordingly. By the in its open position tion located 2-way valve 36 ensures that the function of the pressure compensator is retained. Pressure medium flowing back from the engine via a directional control valve 13 or 14 can flow out to the tank 34 via the return channel 22 independently of the cross connection 35.

Die Figur 2 zeigt nun die erste Steuereinrichtung 10 nach Figur 1 nach ihrer Umstellung auf ein anderes Pumpensystem, wenn anstelle einer Konstantpumpe eine Verstellpumpe 45 benutzt wird. Für diese Umstellung wird lediglich am Steuerdruckanschluß Y die Verschluß­schraube 29 entfernt und dieser Anschluß 28 über eine Steuerlei­tung 46 mit der Regeleinrichtung der Verstellpumpe 45 verbunden. Ferner wird der in der Querverbindung 35 liegende Hahn 36 in seine gezeichnete Sperrstellung gedreht. Mit diesen einfachen und kosten­günstig durchführbaren Maßnahmen wird erreicht, daß durch die Ab­sperrung des Nebenschlußkanals 24 das Drosselventil 26 in seiner Funktion blockiert ist. Eine lastdruckkompensierte Steuerung kann nun in an sich bekannter Weise mit den Wegeventilen 13 und 14 in Verbindung mit der lastdruckgeregelten Verstellpumpe 45 vorgenom­men werden. Ein besonderer Eingriff oder ein Umbau im Wegeventil­block 11 selbst ist für diese Umstellung auf ein anderes Pumpen­system nicht erforderlich.FIG. 2 now shows the first control device 10 according to FIG. 1 after its changeover to another pump system if a variable displacement pump 45 is used instead of a constant pump. For this changeover, the screw plug 29 is only removed at the control pressure connection Y and this connection 28 is connected via a control line 46 to the control device of the variable displacement pump 45. Furthermore, the valve 36 lying in the cross connection 35 is rotated into its drawn blocking position. With these simple and inexpensive measures, it is achieved that the function of the throttle valve 26 is blocked by the blocking of the shunt channel 24. A load pressure-compensated control can now be carried out in a manner known per se with the directional control valves 13 and 14 in connection with the load pressure-controlled variable displacement pump 45. A special intervention or a modification in the directional valve block 11 itself is not necessary for this conversion to another pump system.

Die Figur 3 zeigt einen Teil einer zweiten Steuereinrichtung 50, die ebenfalls für einen Betrieb mit Konstantpumpe vorgesehen ist und die sich von der ersten Steuereinrichtung 10 nach Figur 1 wie folgt un­terscheidet, wobei für gleiche Bauelemente gleiche Bezugszeichen verwendet werden:FIG. 3 shows part of a second control device 50, which is also intended for operation with a constant pump and which differs from the first control device 10 according to FIG. 1 as follows, the same reference numerals being used for the same components:

Bei der zweiten Steuereinrichtung 50 sind in die Druckleitung 32, die Rücklaufleitung 33 und die Querverbindung 35 untereinander gleiche, erste Steckkupplungen 51 eingesetzt, über welche offene Druckmittelverbindungen in den betreffenden Leitungen hergestellt werden. Der 2-Wege-Hahn 36 bei der ersten Steuereinrichtung 10 entfällt bei der zweiten Steuereinrichtung 50. Anstelle einer Ver­schlußschraube übernimmt eine extern angeordnete zweite Steckver­bindung 52 das Absperren des Steuerdruckanschlusses Y. Die Funktion dieser zweiten Steuereinrichtung 50 entspricht derjenigen der ersten Steuereinrichtung 10 nach Figur 1.In the second control device 50, the same first plug-in couplings 51 are inserted into the pressure line 32, the return line 33 and the cross connection 35, by means of which open pressure medium connections are made in the lines concerned will. The two-way valve 36 in the first control device 10 is omitted in the second control device 50. Instead of a screw plug, an externally arranged second plug connection 52 takes over the blocking of the control pressure connection Y. The function of this second control device 50 corresponds to that of the first control device 10 according to FIG. 1 .

Die Figur 4 zeigt nun die zweite Steuereinrichtung 50 nach ihrer Um­stellung für einen Betrieb mit Verstellpumpe 45. Dies läßt sich ein­fach dadurch erreichen, daß der Steuerdruckanschluß Y ebenfalls über eine erste Steckkupplung 51 und die Steuerleitung 46 mit der Regel­einrichtung der Verstellpumpe 45 verbunden wird, während die Quer­verbindung 35 durch eine dritte Steckkupplung 53 blockiert wird. Die dritte Steckkupplung 53 läßt sich sehr einfach durch eine doppelte Anordnung der zweiten Steckkupplung 52 erreichen, so daß die Umstel­lung lediglich durch Öffnen bzw. Verbinden von Steckkupplungen durchführbar ist. Die Funktion der zweiten Steuereinrichtung 50 mit Verstellpumpe 45 entspricht derjenigen der ersten Steuereinrichtung 10 nach Figur 2. Auch diese Umstellung mit Hilfe von außerhalb des Wegeventilblocks 11 angeordneten Steckverbindungen läßt sich durch die Verwendung von Normteilen kostengünstig sowie einfach und sicher vornehmen.Figure 4 shows the second control device 50 after its conversion for operation with a variable displacement pump 45. This can be achieved simply by the control pressure connection Y also being connected to the regulating device of the variable displacement pump 45 via a first plug-in coupling 51 and the control line 46 the cross connection 35 is blocked by a third plug-in coupling 53. The third plug-in coupling 53 can be achieved very easily by a double arrangement of the second plug-in coupling 52, so that the changeover can only be carried out by opening or connecting plug-in couplings. The function of the second control device 50 with the variable displacement pump 45 corresponds to that of the first control device 10 according to FIG. 2. This changeover with the aid of plug connections arranged outside the directional valve block 11 can also be carried out inexpensively, simply and safely by using standard parts.

Die Figur 5 zeigt einen Teil einer dritten Steuereinrichtung 60, die sich von den vorhergehenden Steuereinrichtungen 10, 50 wie folgt un­terscheidet, wobei für gleiche Bauelemente gleiche Bezugszeichen verwendet werden.FIG. 5 shows part of a third control device 60 which differs from the previous control devices 10, 50 as follows, the same reference numerals being used for the same components.

Bei der dritten Steuereinrichtung 60 ist die Querverbindung 35 vom Weiterlaufanschluß 25 zum Rücklaufanschluß 23 in die Anschlußplatte 15 hinein verlegt. In diese intern im Wegeventilblock 11 verlaufende Querverbindung 35 ist der 2-Wege-Hahn 36 geschaltet. In der Druck­leitung 32, der Rücklaufleitung 33 sind wiederum erste Steckkupplun­ gen 51 angeordnet, während der Steuerdruckanschluß Y durch eine zweite Steckkupplung 52 abgesperrt wird. Ferner ist nun der Weiter­laufanschluß 25 durch einen Verschlußstopfen 61 nach außen abge­sperrt. Die Funktion der dritten Steuereinrichtung 60 nach Figur 5 entspricht der ersten Steuereinrichtung 10 nach Figur 1.In the third control device 60, the cross-connection 35 is laid from the flow connection 25 to the return connection 23 into the connection plate 15. The 2-way valve 36 is connected to this cross connection 35, which runs internally in the directional valve block 11. In the pressure line 32, the return line 33 are first plug-in couplings gene 51 arranged while the control pressure port Y is shut off by a second plug-in coupling 52. Furthermore, the flow connection 25 is now blocked off from the outside by a plug 61. The function of the third control device 60 according to FIG. 5 corresponds to the first control device 10 according to FIG. 1.

Die Figur 6 zeigt die dritte Steuereinrichtung 60 umgestellt auf einen Betrieb mit Verstellpumpe 45. Zu diesem Zweck wird der intern angeordnete 2-Wege-Hahn 36 in seine Sperrstellung gebracht und der Steuerdruckanschluß Y über eine erste Steckkupplung 51 und eine Steuerleitung 46 mit der Regeleinrichtung der Verstellpumpe 45 ver­bunden. Auch die dritte Steuereinrichtung 60 nach Figur 6, deren Funktion der Funktion der ersten Steuereinrichtung 10 nach Figur 2 entspricht, läßt sich mit wenigen und geringen Handgriffen auf unterschiedliche Pumpensysteme mit Konstantpumpe oder Verstellpumpe umstellen.FIG. 6 shows the third control device 60 converted to operation with a variable displacement pump 45. For this purpose, the internally arranged 2-way valve 36 is brought into its blocking position and the control pressure connection Y is connected to the control device via a first plug-in coupling 51 and a control line 46 Variable pump 45 connected. The third control device 60 according to FIG. 6, the function of which corresponds to the function of the first control device 10 according to FIG. 2, can also be changed over to different pump systems with a constant pump or variable displacement pump in a few simple steps.

Die Figuren 7 und 8 zeigen jeweils einen Teil einer vierten Steuer­einrichtung 70 für Konstant- bzw. Verstellpumpen-Betrieb, die sich von der zweiten Steuereinrichtung 50 wie folgt unterscheiden, wobei gleiche Teile mit gleichen Bezugszeichen versehen sind.FIGS. 7 and 8 each show part of a fourth control device 70 for constant or variable pump operation, which differ from the second control device 50 as follows, the same parts being provided with the same reference numerals.

Bei der vierten Steuereinrichtung 70 ist anstelle einer Weiterlauf­schaltung der Ausgang 71 des Drosselventils 26 mit dem Rücklaufan­schluß 23 verbunden. In die Steuerverbindung 72 ist ein 3/2-Magnet­ventil 73 geschaltet, das eine Druckkammer des Drosselventils 26 zum Rücklaufanschluß 23 entlasten kann. Das 3/2-Magnetventil 73 wird über einen elektromechanischen Schalter 74 angesteuert, der den Steckverbindungen 51, 52 am Steueranschluß 28 zugeordnet und von diesem betätigbar ist. In Figur 7 bei Konstantpumpen-Betrieb befin­det sich das Magnetventil 73 in seiner Ruhestellung und das Drossel­ventil 26 kann normal als Druckwaage arbeiten. In Figur 8 bei Regel­pumpen-Betrieb wird der Schalter 74 und das Magnetventil 73 betä­tigt, wodurch die Funktion des Drosselventils 26 gesperrt ist.In the fourth control device 70, the output 71 of the throttle valve 26 is connected to the return connection 23 instead of a continuation circuit. A 3/2-way solenoid valve 73 is connected into the control connection 72 and can relieve a pressure chamber of the throttle valve 26 to the return connection 23. The 3/2-solenoid valve 73 is controlled via an electromechanical switch 74 which is assigned to the plug connections 51, 52 at the control connection 28 and can be actuated by the latter. In Figure 7 with constant pump operation, the solenoid valve 73 is in its rest position and the throttle valve 26 can operate normally as a pressure compensator. In FIG. 8 during control pump operation, the switch 74 and the solenoid valve 73 are actuated, as a result of which the function of the throttle valve 26 is blocked.

Selbstverständlich sind an den gezeigten Ausführungsformen Änderun­gen möglich, ohne vom Gedanken der Erfindung abzuweichen. So kann bei den Verstellpumpen neben einem LS-System auch ein Konstantdruck­system Verwendung finden.Of course, changes are possible in the embodiments shown without departing from the spirit of the invention. In addition to an LS system, a constant pressure system can also be used for the variable displacement pumps.

Claims (9)

1. Hydraulische Steuereinrichtung zur lastdruckunabhängigen Steue­rung wenigstens eines hydraulischen Motors mit wenigstens einem Wegeventil, dessen Zulaufanschluß in einer Mittelstellung gesperrt ist und bei dem mindestens ein Motoranschluß in Arbeitsstellungen abwechselnd mit dem Zulaufanschluß oder mit einem Tank verbindbar ist und mit einem vom Zulaufanschluß des Wegeventils zu einem Pum­penanschluß führenden Zulaufkanal, von dem ein Nebenschlußkanal ab­zweigt und zu einem als Druckwaage arbeitenden Drosselventil führt, das zum lastdruckkompensierten Steuern eines Volumenstroms zum Motor dient und über ein Steuerleitungssystem mit dem Lastdruck des Motors beaufschlagbar ist, wobei das Steuerleitungssystem einen Steuer­druckanschluß aufweist, und mit einem Rücklaufanschluß in der Steuereinrichtung, dadurch gekennzeichnet, daß extern ansteuerbare, das Drosselventil (26) hydraulisch blockierende Sperrmittel (36; 51, 53; 73, 74) angeordnet sind.1.Hydraulic control device for load pressure-independent control of at least one hydraulic motor with at least one directional control valve, the inlet connection of which is blocked in a central position and in which at least one motor connection in working positions can be connected alternately to the inlet connection or to a tank and to one of the inlet connection of the directional valve Pump connection leading inlet channel, from which a bypass branch branches and leads to a throttle valve working as a pressure compensator, which serves for load pressure-compensated control of a volume flow to the engine and can be acted upon via a control line system with the load pressure of the engine, the control line system having a control pressure connection, and with a return connection in the control device, characterized in that externally controllable blocking means (36; 51, 53; 73, 74) which hydraulically block the throttle valve (26) are arranged. 2. Steuereinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß ein vom Rücklaufanschluß (23) getrennter Weiterlaufanschluß (25) vorgesehen ist, zu dem der Nebenschlußkanal (24) stromabwärts vom Drosselventil (26) geführt ist, daß eine hydraulische Querverbindung (35) vom Weiterlaufanschluß (25) zum Rücklaufanschluß (23) angeord­net ist und in diese Querverbindung hydraulische Sperrmittel (36; 51, 53) geschaltet sind.2. Control device according to claim 1, characterized in that a from the return port (23) separate continuation connection (25) is provided, to which the shunt channel (24) is guided downstream of the throttle valve (26) that a hydraulic cross connection (35) from the continuation connection (25) to the return port (23) is arranged and in this cross-connection hydraulic locking means (36; 51, 53) are connected. 3. Steuereinrichtung nach Anspruch 2, dadurch gekennzeichnet, daß die Sperrmittel als 2-Wege-Hahn (36) ausgebildet sind.3. Control device according to claim 2, characterized in that the locking means are designed as a 2-way valve (36). 4. Steuereinrichtung nach Anspruch 2, dadurch gekennzeichnet, daß die Sperrmittel als Steckverbindung (51, 53) ausgebildet sind, mit denen die Querverbindung (35) wahlweise offen oder blockierbar ist.4. Control device according to claim 2, characterized in that the locking means are designed as a plug connection (51, 53) with which the cross connection (35) is optionally open or can be blocked. 5. Steuereinrichtung nach einem der Ansprüche 2 bis 4, dadurch ge­kennzeichnet, daß das Drosselventil (26) ein 2Wege-2Stellungs-Ventil ist.5. Control device according to one of claims 2 to 4, characterized in that the throttle valve (26) is a 2-way 2-position valve. 6. Steuereinrichtung nach einem oder mehreren der Ansprüche 2 bis 5, dadurch gekennzeichnet, daß die hydraulische Querverbindung (35) in einer Anschlußplatte (15) angeordnet ist, die den Pumpenanschluß (19), den Rücklaufanschluß (23), den Steuerdruckanschluß (28) und den Weiterlaufanschluß (25) aufweist.6. Control device according to one or more of claims 2 to 5, characterized in that the hydraulic cross connection (35) is arranged in a connecting plate (15) which the pump connection (19), the return connection (23), the control pressure connection (28) and the continuation connection (25). 7. Steuereinrichtung nach einem der Ansprüche 2 bis 6, dadurch ge­kennzeichnet, daß die Druckmittelquelle eine Konstantpumpe (12) ist, die Sperrmittel (36; 51) ihre offene Stellung aufweisen und der Steuerdruckanschluß (28) blockiert ist.7. Control device according to one of claims 2 to 6, characterized in that the pressure medium source is a constant pump (12), the locking means (36; 51) have their open position and the control pressure connection (28) is blocked. 8. Steuereinrichtung nach einem der Ansprüche 2 bis 6, dadurch ge­kennzeichnet, daß die Druckmittelquelle eine Verstellpumpe (45) ist, deren Regeleinrichtung mit dem Steuerdruckanschluß (28) Verbindung hat und die Sperrmittel (36; 53) ihre geschlossene Stellung aufwei­sen.8. Control device according to one of claims 2 to 6, characterized in that the pressure medium source is a variable displacement pump (45), the control device with the control pressure connection (28) has connection and the locking means (36; 53) have their closed position. 9. Steuereinrichtung nach Anspruch 1, bei welcher der Ausgang des Drosselventils mit dem Rücklaufanschluß verbunden ist, dadurch ge­kennzeichnet, daß die Sperrmittel als ein das Drosselventil (26) vorsteuerndes 3/2-Magnetventil (73) und als elektrischer Schalter (74) ausgebildet sind, der von einer dem Steueranschluß (28) zuge­ordneten Steckverbindung (51, 52) betätigbar ist.9. Control device according to claim 1, wherein the output of the throttle valve is connected to the return connection, characterized in that the blocking means are designed as a 3/2 solenoid valve (73) piloting the throttle valve (26) and as an electrical switch (74) which can be actuated by a plug connection (51, 52) assigned to the control connection (28).
EP89115655A 1988-10-06 1989-08-25 Hydraulic control device Expired - Lifetime EP0362539B1 (en)

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DE3833999 1988-10-06
DE3833999A DE3833999A1 (en) 1988-10-06 1988-10-06 HYDRAULIC CONTROL DEVICE

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EP0125425A1 (en) * 1983-04-12 1984-11-21 Robert Bosch Gmbh Control device
DE3505623A1 (en) * 1985-02-19 1986-08-21 Robert Bosch Gmbh, 7000 Stuttgart HYDRAULIC DIRECTION VALVE FOR A LOAD PRESSURE COMPENSATED CONTROL
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DE3611244A1 (en) * 1986-04-04 1987-10-08 Rexroth Mannesmann Gmbh Flow-control valve

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DE58903600D1 (en) 1993-04-01
DE3833999A1 (en) 1990-04-12
EP0362539B1 (en) 1993-02-24

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