EP0203100A1 - Hydraulic installation. - Google Patents

Hydraulic installation.

Info

Publication number
EP0203100A1
EP0203100A1 EP85905393A EP85905393A EP0203100A1 EP 0203100 A1 EP0203100 A1 EP 0203100A1 EP 85905393 A EP85905393 A EP 85905393A EP 85905393 A EP85905393 A EP 85905393A EP 0203100 A1 EP0203100 A1 EP 0203100A1
Authority
EP
European Patent Office
Prior art keywords
pressure
line
control valve
pump
directional
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
EP85905393A
Other languages
German (de)
French (fr)
Other versions
EP0203100B1 (en
Inventor
Wolfgang Kotter
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0203100A1 publication Critical patent/EP0203100A1/en
Application granted granted Critical
Publication of EP0203100B1 publication Critical patent/EP0203100B1/en
Expired legal-status Critical Current

Links

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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • 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
    • F15B2211/20507—Type of prime mover
    • F15B2211/20523—Internal combustion engine
    • 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
    • F15B2211/25—Pressure control functions
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow 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
    • F15B2211/505—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
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing 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
    • F15B2211/51—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
    • F15B2211/575—Pilot pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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

Definitions

  • the invention is based on a hydraulic system according to the type of the main claim.
  • a hydraulic system according to the type of the main claim.
  • the pump In order to operate hydraulic systems economically, it is known to set the pump so that it produces the pressure and the flow rate required by the consumer.
  • the load pressure prevailing in the consumer is fed to a flow control valve which, for example, controls an actuating device for the pump in such a way that the above-mentioned requirement is met.
  • Such known systems and devices are sometimes expensive because a variable pump must be used, or they do not yet work optimally economically.
  • a pressure control valve which generates a control pressure which adjusts an actuating cylinder for a speed controller of an internal combustion engine driving the pump.
  • this turned out to be difficult speed with regard to the vibration behavior of the pressure control valve and thus the control of the speed controller, this meant that a practical operation of such a system was not feasible.
  • the hydraulic system according to the invention with the characterizing features of the main claim has the advantage that it is relatively simple and allows problem-free use in a very economical manner for practical operation.
  • FIGS. 1 and 2 Two embodiments of the invention are shown in the drawing and explained in more detail in the following description. These show a schematic representation of hydraulic systems in FIGS. 1 and 2, and a diagram in FIG.
  • 10 denotes a non-adjustable pump that draws pressure medium from a container 11 and displaces it into a delivery line 12.
  • the pump 10 is driven by an internal combustion engine 13, in particular a diesel engine, the member 14 determining the fuel supply - in the case of a diesel engine, therefore, the injection pump or its speed controller - by means of a hydraulic be opened actuating cylinder 15 is set, this is pressurized via a line 16 with pressure medium, which leads to a valve control block 17.
  • this three series valves 18 to 20 are arranged in series, of which the directional valve 18 controls a single-acting consumer, the directional valves 19, 20 control double-acting consumers.
  • the delivery line 12 also leads to the control block 17.
  • a neutral circulation line 12A is connected to it, which starts from an end plate 22 which closes the control block and ends at a pressure relief valve 23. From this line 24 leads to a return line 25, which is also passed through the control block 17. From the delivery line 12 branch off in the control block 17 a line 26 which leads to the pressure relief valve, further a line 27 which leads to a pressure control valve 28, a line 29 which leads to the directional control valve 18, a line 30 which leads to the directional control valve 19 and a line 31 leading to the directional valve 20.
  • a first line 32 leads to a single-acting consumer (not shown), a second line 33 to line 16 and a line 34 to a line 35, which leads from the return line to the outflow side of the pressure control valve 28.
  • a line 37 branches off from the line 33 and leads to one end 28A of the pressure regulating valve 28, on the opposite end 28B of which a control spring 38 acts.
  • a throttle 39 is arranged in the line 33 shortly before the junction with the line 16.
  • the pressure regulating valve 28 either makes a connection from the line 27 connected to the delivery line 12 to the line 16 or to the line 35 connected to the return line 25. Controlled is the pressure control valve 28 against the force of the spring 38 by the liquid pressure acting on its end face 28 A.
  • the directional control valve 18 can assume three switch positions I, II and III, position II being the blocking position, position I the working position, position III the relief position.
  • This directional valve is designed as a 6/3-way valve and in its position I on the one hand establishes a connection from line 29 to line 32 and thus to the consumer and on the other hand from line 34 to line 33 and thus to line 16.
  • a line 41 leads to the return line 25 and two lines 42, 43 to a double-acting consumer, not shown.
  • the situation is similar with the directional control valve 20; here a line 44 to the return line 25 and two lines 45, 46 also lead to a double-acting consumer.
  • the directional control valves 19, 20 are also designed as 6/3 directional control valves and have the same switching positions I to III as the directional control valve 18. This differs from the directional control valves 19, 20, however, in that in the working position I between the connections a and b , d, h, an adjustable throttle 48 is formed between the lines 33 and 34. In reality, this looks like that - as is known per se - there is a control groove on the spool valve which opens more and more with increasing displacement of the spool valve, so that the flow cross-section from line 33 to line 34 is increasingly opened.
  • pressure medium flows from the consumers connected to the directional control valves 19, 20 via the line 43 or, 46 to the container. If the directional control valve 18 is now shifted from its neutral position II in the direction of the working position I - either alone or with simultaneous actuation of one of the valves 19, 20, pressure medium flows on the one hand via the line 32 to the consumer, and on the other hand from the pressure surface 28A of the pressure control valve 28 via the line 37 and the line 33 as well as the directional control valve 18 and the line 34 increasingly to the return line 25. This flow is limited by the throttle 48 in the directional valve 18.
  • the exemplary embodiment according to FIG. 2 differs from that according to FIG. 1 essentially only in that it is a so-called load-sensing hydraulic circuit which has a flow control valve 55 which is connected to the delivery line 12 and which has a connecting line 56 to the return line 25 Has.
  • a control line 57 is provided in the control block, in which each directional control valve Alternating check valve 58 is assigned.
  • the directional valves essentially correspond to those described above, but with the difference that there is still a connecting line to the shuttle valve 58. The highest pressure prevailing at a consumer is selected in each case via these alternating non-return valves and is brought to the flow control valve 55 via a line 60.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'installation hydraulique comporte une pompe (10), entraînée par exemple par un moteur diesel (13), qui transmet les moyens de pression aux utilisateurs par l'intermédiaire de distributeurs (18 à 20) à plusieurs voies. Le régulateur de vitesse (14) de la pompe d'injection du moteur diesel est commandé par un cylindre de positionnement (15) actionné par la pression, sur lequel agit, dans une ligne de commande (16), la pression produite pour augmenter la vitesse de rotation du moteur à combustion interne. Cette pression est commandée conjointement à l'aide de l'un des distributeurs à plusieurs voies (18) pour un utilisateur opérant seul et d'un régulateur de pression (28), de sorte que, lors du fonctionnement d'un distributeur à plusieurs voies normal, une pression constante est produite dans la ligne (16). Lors du fonctionnement de l'autre distributeur à plusieurs voies (18) pour l'utilisateur opérant seul, un rebord de commande spécial (48) se déclanche, ce qui produit une pression croissante dans la ligne (16), proportionnelle au débattement du tiroir de distribution. Il s'ensuit que la vitesse de rotation du moteur à combustion interne et par conséquent de la pompe (10) est augmentée et réglée de telle sorte que les utilisateurs reçoivent exactement la pression nécessaire. Ce système permet un fonctionnement économique.The hydraulic installation comprises a pump (10), driven for example by a diesel engine (13), which transmits the pressure means to the users via distributors (18 to 20) with several channels. The speed regulator (14) of the diesel engine injection pump is controlled by a pressure-actuated positioning cylinder (15), on which acts, in a control line (16), the pressure produced to increase the pressure. rotational speed of the internal combustion engine. This pressure is controlled jointly with the aid of one of the multi-way valves (18) for a single user and a pressure regulator (28), so that when operating a multi-way valve normal channels, constant pressure is produced in the line (16). When operating the other multi-way valve (18) for the single user, a special control flange (48) is triggered, which produces increasing pressure in the line (16), proportional to the travel of the spool. of distribution. As a result, the rotational speed of the internal combustion engine and hence of the pump (10) is increased and adjusted so that the users receive exactly the required pressure. This system allows economical operation.

Description

HydraulikanlageHydraulic system
Stand der TechnikState of the art
Die Erfindung geht aus von einer Hydraulikanlage nach der Gattung des Hauptanspruchs. Um Hydraulikanlagen wirtschaftlich betreiben zu können, ist es bekannt, die Pumpe so einzustellen, daß sie gerade den vom Verbraucher benötigten Druck und den von ihm benötigten Förderstrom erbringt. Zu diesem Zweck wird der im Verbraucher herrschende Lastdruck einem Stromregelventil zugeleitet, das beispielsweise eine Stelleinrichtung für die Pumpe so steuert, daß die obengenannte Forderung erfüllt wird. Solche bekannten Anlagen und Einrichtungen sind zum Teil teuer, da eine Verstellpumpe verwendet werden muß, oder sie arbeiten noch nicht wirtschaftlich optimal.The invention is based on a hydraulic system according to the type of the main claim. In order to operate hydraulic systems economically, it is known to set the pump so that it produces the pressure and the flow rate required by the consumer. For this purpose, the load pressure prevailing in the consumer is fed to a flow control valve which, for example, controls an actuating device for the pump in such a way that the above-mentioned requirement is met. Such known systems and devices are sometimes expensive because a variable pump must be used, or they do not yet work optimally economically.
Um derartige Anlagen zu vereinfachen, ist schon vorgeschlagen worden, die Drehzahl der Pumpe so zu steuern, daß diese die obengenannte Bedingung erfüllt. Zu diesem Zwecke ist ein Druckregelventil vorgesehen, das einen Steuerdruck erzeugt, welcher einen Stellzylinder für einen Drehzahlregler einer die Pumpe antreibenden Brennkraftmaschine einstellt. Dabei ergaben sich jedoch Schwierig keiten hinsichtlich des Schwingungsverhaltens des Druckregelventils und damit der Steuerung des Drehzahlreglers, Dies führte dazu, daß ein praktischer Betrieb einer solchen Anlage nicht durchführbar war.In order to simplify such systems, it has already been proposed to control the speed of the pump so that it fulfills the condition mentioned above. For this purpose, a pressure control valve is provided which generates a control pressure which adjusts an actuating cylinder for a speed controller of an internal combustion engine driving the pump. However, this turned out to be difficult speed with regard to the vibration behavior of the pressure control valve and thus the control of the speed controller, this meant that a practical operation of such a system was not feasible.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Hydraulikanlage mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß sie verhältnismäßig einfach ausgebildet ist und einen für den praktischen Betrieb problemlosen Einsatz auf sehr wirtschaftliche Weise erlaubt.The hydraulic system according to the invention with the characterizing features of the main claim has the advantage that it is relatively simple and allows problem-free use in a very economical manner for practical operation.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Merkmale möglich.The measures listed in the subclaims enable further developments and improvements to the features specified in the main claim.
Zeichnungdrawing
Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Diese zeigen in den Figuren 1 und 2 Hydraulikanlagen in schematischer Darstellung, in Figur 3 ein Diagramm.Two embodiments of the invention are shown in the drawing and explained in more detail in the following description. These show a schematic representation of hydraulic systems in FIGS. 1 and 2, and a diagram in FIG.
Beschreibung des AusführungsbeispielesDescription of the embodiment
In Figur 1 ist mit 10 eine nicht verstellbare Pumpe bezeichnet, die Druckmittel aus einem Behälter 11 ansaugt und in eine Förderleitung 12 verdrängt. Die Pumpe 10 ist von einer Brennkraftmaschine 13 angetrieben, insbesondere einem Dieselmotor, deren die Kraft stoffzufuhr bestimmendes Glied 14 - bei einem Dieselmotor also die Einspritzpumpe bzw. deren Drehzahlregler - mittels eines hydraulisch be aufschlagten Stellzylinders 15 eingestellt wird, Dieser ist über eine Leitung 16 mit Druckmittel beaufschlagt, welche zu einem Ventil-Steuerblock 17 führt. In diesem sind in Serie drei Wegeventile 18 bis 20 angeordnet, von denen das Wegeventil 18 einen einfach wirkenden Verbraucher steuert, die Wegeventile 19, 20 dagegen doppelt wirkende Verbraucher steuern.In FIG. 1, 10 denotes a non-adjustable pump that draws pressure medium from a container 11 and displaces it into a delivery line 12. The pump 10 is driven by an internal combustion engine 13, in particular a diesel engine, the member 14 determining the fuel supply - in the case of a diesel engine, therefore, the injection pump or its speed controller - by means of a hydraulic be opened actuating cylinder 15 is set, this is pressurized via a line 16 with pressure medium, which leads to a valve control block 17. In this three series valves 18 to 20 are arranged in series, of which the directional valve 18 controls a single-acting consumer, the directional valves 19, 20 control double-acting consumers.
Die Förderleitung 12 führt ebenfalls zum Steuerblock 17. An sie ist eine Neutralumlaufleitung 12A angeschlossen, die von einer den Steuerblock verschließenden Endplatte 22 ausgeht und an einem Druckbegrenzungsvent il 23 endet. Von diesem führt eine Leitung 24 zu einer Rücklaufleitung 25, die ebenfalls durch den Steuerblock 17 hindurchgeführt ist. Von der Förderleitung 12 zweigen im Steuerblock 17 eine Leitung 26 ab, die zum Druckb egrenzungsventil führt, weiterhin eine Leitung 27, die zu einem Druckregelventil 28 führt, eine Leitung 29, die zum Wegeventil 18 führt, eine Leitung 30, die zum Wegeventil 19 führt und eine Leitung 31, die zum Wegeventil 20 führt. Vom Wegeventil 18 führt eine erste Leitung 32 zu einem nicht dargestellten einfach wirkenden Verbraucher, eine zweite Leitung 33 zur Leitung 16 und eine Leitung 34 zu einer Leitung 35, die von der Rücklaufleitung zur Abflußseite des Druckregelventils 28 führt. Von der Leitung 33 zweigt eine Leitung 37 ab, die an die eine Stirnseite 28A des Druckregelventils 28 führt, auf dessen entgegengesetzte Stirnseite 28B eine Regelfeder 38 einwirkt. In der Leitung 33 ist kurz vor der Einmündung in die Leitung 16 eine Drossel 39 angeordnet. Das Druckregelventil 28 stellt je nach Stellung entweder Verbindung von der mit der Förderleitung 12 verbundenen Leitung 27 zur Leitung 16 her oder zu der mit der Rücklaufleitung 25 verbundenen Leitung 35. Gesteuert wird das Druckregelventil 28 durch den auf seine Stirnfläche 28 A einwirkenden Flüssigkeitsdruck entgegen der Kraft der Feder 38.The delivery line 12 also leads to the control block 17. A neutral circulation line 12A is connected to it, which starts from an end plate 22 which closes the control block and ends at a pressure relief valve 23. From this line 24 leads to a return line 25, which is also passed through the control block 17. From the delivery line 12 branch off in the control block 17 a line 26 which leads to the pressure relief valve, further a line 27 which leads to a pressure control valve 28, a line 29 which leads to the directional control valve 18, a line 30 which leads to the directional control valve 19 and a line 31 leading to the directional valve 20. From the directional control valve 18, a first line 32 leads to a single-acting consumer (not shown), a second line 33 to line 16 and a line 34 to a line 35, which leads from the return line to the outflow side of the pressure control valve 28. A line 37 branches off from the line 33 and leads to one end 28A of the pressure regulating valve 28, on the opposite end 28B of which a control spring 38 acts. A throttle 39 is arranged in the line 33 shortly before the junction with the line 16. Depending on the position, the pressure regulating valve 28 either makes a connection from the line 27 connected to the delivery line 12 to the line 16 or to the line 35 connected to the return line 25. Controlled is the pressure control valve 28 against the force of the spring 38 by the liquid pressure acting on its end face 28 A.
Das Wegeventil 18 vermag drei Schaltstellungen I, II und III einzunehmen, wobei die Stellung II die Sperrstellung ist, die Stellung I die Arbeits Stellung, die Stellung III die Entlastungsstellung. Dieses Wegeventil ist als 6/3¬Wegeventil ausgebildet und stellt in seiner Stellung I einerseits Verbindung her von der Leitung 29 zur Leitung 32 und damit zum Verbraucher und andererseits von der Leitung 34 zur Leitung 33 und damit zur Leitung 16 .The directional control valve 18 can assume three switch positions I, II and III, position II being the blocking position, position I the working position, position III the relief position. This directional valve is designed as a 6/3-way valve and in its position I on the one hand establishes a connection from line 29 to line 32 and thus to the consumer and on the other hand from line 34 to line 33 and thus to line 16.
Vom Wegeventil 19 führen eine Leitung 41 zur Rücklaufleitung 25 und zwei Leitungen 42, 43 zu einem nicht dargestellten doppeltwirkenden Verbraucher. Ähnlich sieht es beim Wegeventil 20 aus; hier führen eine Leitung 44 zur Rücklaufleitung 25 und zwei Leitungen 45, 46 ebenfalls zu einem doppeltwirkenden Verbraucher. Die Wegeventile 19, 20 sind ebenfalls als 6/3-Wegeventile ausgebildet und weisen dieselben Schaltstellungen I bis III auf wie das Wegeventil 18. Dieses unterscheidet sich von den Wegeventilen 19, 20 jedoch dadurch, daß der in Arbeitsstellung I zwischen den Anschlüssen a und b, d, h, zwischen der Leitung 33 und 34 eine verstellbare Drossel 48 ausgebildet ist. Diese sieht in Wirklichkeit so aus, daß sich - wie an sich bekannt - an der Steuerschieberkaate eine Steuernut befindet, die bei zunehmender Verschiebung des Steuerschiebers immer weiter öffnet, so daß der Durchflußquerschnitt von der Leitung 33 zur Leitung 34 zunehmend aufgesteuert wird.From the directional control valve 19, a line 41 leads to the return line 25 and two lines 42, 43 to a double-acting consumer, not shown. The situation is similar with the directional control valve 20; here a line 44 to the return line 25 and two lines 45, 46 also lead to a double-acting consumer. The directional control valves 19, 20 are also designed as 6/3 directional control valves and have the same switching positions I to III as the directional control valve 18. This differs from the directional control valves 19, 20, however, in that in the working position I between the connections a and b , d, h, an adjustable throttle 48 is formed between the lines 33 and 34. In reality, this looks like that - as is known per se - there is a control groove on the spool valve which opens more and more with increasing displacement of the spool valve, so that the flow cross-section from line 33 to line 34 is increasingly opened.
Befinden sich sämtliche Wegeventile in Heutralstellung II, so fließt das von der Pumpe 10 geförderte Druckmittel von der Leitung 12 über die Leitung 26 in die Neutralumlauf leitung 12a und von dieser in die Rücklaufleitung 25a zum Behälter. Dabei herrscht ein niedriger Neutralumlaufdruck von beispielsweise 3 bar in den Leitungen 12, 12a, 27 und 16, wobei die beiden letzten Leitungen nun durch das Druckregelventil 28 miteinander verbunden sind. Die Feder 50 im Stellzylinder 25 verschiebt den Kolben 51 nach rechts und stellt damit den Drehzahlregler 13 auf Leerlaufdrehzahl. Das bedeutet, daß nun die Drehzahl der Pumpe niedrig ist und diese - wie oben ausgeführt - nur den niedrigen Umlaufdruck erzeugt, welcher im Diagramm nach Figur 3 mit P1 bezeichnet ist. In diesem Diagramm ist auf der Abszisse der Hub des Steuerschiebers des Wegeventils 18 aufgetragen, auf der Ordinate die Drehzahl der Brennkraftmaschine 13 bzw. der Steuerdruck in der Leitung 16.If all the directional valves are in the neutral position II, the pressure medium delivered by the pump 10 flows from the line 12 via the line 26 into the neutral circulation line 12a and from this into the return line 25a to the container. There is a low neutral circulation pressure of, for example, 3 bar in lines 12, 12a, 27 and 16, the last two lines now being connected to one another by pressure control valve 28. The spring 50 in the actuating cylinder 25 displaces the piston 51 to the right and thus sets the speed controller 13 to idling speed. This means that the speed of the pump is now low and, as stated above, it only generates the low circulating pressure, which is designated P 1 in the diagram according to FIG. 3. In this diagram, the stroke of the control slide of the directional control valve 18 is plotted on the abscissa, and the rotational speed of the internal combustion engine 13 or the control pressure in the line 16 is plotted on the ordinate.
Wird eines der Wegeventile 19 oder 20 in Arbeitsstellung I verstellt, dann wird die Verbindung von der Leitung 26 zur Neutralumlaufleitung 12a unterbrochen, der Druck in der Leitung 27 steigt an und damit ebenfalls in der Leitung 16, in letzterer bis auf den Druck P2 von beispielsweise 6 bar. Dieser Druck entspricht der Kraft der Reglerfeder 38. Bei weiter steigendem Druck in der Leitung 27 bleibt der Druck in der Leitung 16 konstant, da er durch das Druckregelventil 28 auf diesem Wert gehalten wird. Druckmittel fließt nun von der Leitung 12 über eine der Leitungen 42 oder 45 des Wegeventils 19 bzw. 20 zum Verbraucher. Durch den in der Leitung 16 angestiegenen Druck wird der Kolben 51 des Stellzylinders 15 entgegen der Federkraft 15 verschoben, wodurch der Drehzahlregler 14 die Brennkraftmaschine 13 auf eine höhere Drehzahl einstellt. Damit steigen der Förderdruck und die Fördermenge der Pumpe 10. Es ist noch zu erwähnen, daß von den an die Wegeventile 19, 20 angeschlossenen Verbrauchern Druckmittel über die Le itung 43 bzw, 46 zum Behälter fließt. Wird nun das Wegeventil 18 von seiner Neutralstellung II in Richtung Arbeitsstellung I verschoben - entweder alleine oder bei gleichzeitiger Betätigung eines der Ventil 19, 20, dann fließt einerseits Druckmittel über die Leitung 32 zum Verbraucher, andererseits von der Druckfläche 28A des Druckregelventils 28 über die Leitung 37 und die Leitung 33 sowie das Wegeventil 18 und die Leitung 34 zunehmend zur Rücklaufleitung 25. Dieser Strom ist begrenzt durch die Drossel 48 im Wegenventil 18. Gleichzeitig fließt auch aus der Leitung 16 Druckmittel durch die Drossel 39 in begrenztem Ausmaß in die Leitung 33, wodurch der Druck an der Druckfläche 28 A des Druckregelventils sinkt, worauf die Regelfeder 38 zunehmend Verbindung von der Leitung 27 zur Leitung 16 herstellt. Hierdurch steigt der Druck in der Leitung 16, so daß der Drehzahlregler 14 die Brennkraftmaschine 13 auf noch höhere Drehzahl ansteigen läßt. Die Drehzahl wird umso größer, je weiter das Wegeventil 18 in seine Arbeitsstellung I verstellt wird. Die Drehzahl der Brennkraftmaschine 13 steigt also proportional zur Auslenkung des Wegeventils 18. Dies ist im Diagramm nach der Figur 3 durch die ansteigende Kurve P3 zu erkennen. Beim Zurückstellen des Wegeventils 18 von seiner Schaltstellung I in II sinkt der Druck in der Leitung 16 wieder ab, so daß die Drehzahl der Brennkraftmaschine verringert wird.If one of the directional control valves 19 or 20 is adjusted in working position I, then the connection from line 26 to neutral circulation line 12a is interrupted, the pressure in line 27 increases and thus also in line 16, in the latter up to the pressure P 2 of for example 6 bar. This pressure corresponds to the force of the regulator spring 38. If the pressure in the line 27 increases further, the pressure in the line 16 remains constant since it is kept at this value by the pressure control valve 28. Pressure medium now flows from line 12 via one of lines 42 or 45 of directional control valve 19 or 20 to the consumer. Due to the increased pressure in the line 16, the piston 51 of the actuating cylinder 15 is displaced counter to the spring force 15, whereby the speed controller 14 sets the internal combustion engine 13 to a higher speed. This increases the delivery pressure and the delivery rate of the pump 10. It should also be mentioned that pressure medium flows from the consumers connected to the directional control valves 19, 20 via the line 43 or, 46 to the container. If the directional control valve 18 is now shifted from its neutral position II in the direction of the working position I - either alone or with simultaneous actuation of one of the valves 19, 20, pressure medium flows on the one hand via the line 32 to the consumer, and on the other hand from the pressure surface 28A of the pressure control valve 28 via the line 37 and the line 33 as well as the directional control valve 18 and the line 34 increasingly to the return line 25. This flow is limited by the throttle 48 in the directional valve 18. At the same time, pressure medium flows from line 16 through the throttle 39 to a limited extent into line 33, whereby the pressure at the pressure surface 28 A of the pressure control valve drops, whereupon the control spring 38 increasingly establishes a connection from line 27 to line 16. As a result, the pressure in the line 16 increases, so that the speed controller 14 allows the internal combustion engine 13 to rise to an even higher speed. The speed increases the further the directional control valve 18 is moved into its working position I. The speed of the internal combustion engine 13 thus increases in proportion to the deflection of the directional valve 18. This can be seen in the diagram according to FIG. 3 by the rising curve P 3 . When the directional control valve 18 is reset from its switching position I in II, the pressure in the line 16 drops again, so that the speed of the internal combustion engine is reduced.
Das Ausführungsbeispiel nach Figur 2 unterscheidet sich gegenüber demjenigen nach Figur 1 im wesentlichen nur dadurch, daß es sich hier um einen sogenannten loadsensing-Hydraulikkreis handelt, der ein Stromregelventil 55 aufweist, das an die Förderleitung 12 angeschlossen ist und das eine Verbindungsleitung 56 zur Rücklaufleitung 25 hat. Außerdem ist eine Steuerleitung 57 im Steuerblock vorgesehen, in der jedem Wegeventil ein Wechselrückschlagventil 58 zugeordnet ist. Die Wegeventile entsprechen im wesentlichen wieder den oben beschriebenen, jedoch mit dem Unterschied, daß jeweils noch eine Verbindungsleitung zum Wechselrückschlagventil 58 besteht. Über diese Wechselrückschlagventile wird jeweils der höchste, an einem Verbraucher herrschende Druck ausgewählt und über eine Leitung 60 an das Stromregelventil 55 herangeführt. Derartige Anordnungen sind an sich bekannt und haben den Zweck, in Neutralstellung der Wegeventile das Stromregelventil 55 so einzustellen, daß es in seiner Schaltstellung II eine direkte Verbindung von der Pumpe zur Rücklaufleitung herstellt, so daß keine Verlustleistung entsteht. Der Versorgungsdruck des Druckregelventils 28 kommt aus der Steuerleitung 60 für das Stromregelventil 55, d. h. in Neutralstellung des Wegeventils 18 sinkt der Druck im Stellzylinder 15 bzw. in der Leitung 16 auf Behälterdruck, siehe hierzu in Figur 3 die gestrichelte Linie. The exemplary embodiment according to FIG. 2 differs from that according to FIG. 1 essentially only in that it is a so-called load-sensing hydraulic circuit which has a flow control valve 55 which is connected to the delivery line 12 and which has a connecting line 56 to the return line 25 Has. In addition, a control line 57 is provided in the control block, in which each directional control valve Alternating check valve 58 is assigned. The directional valves essentially correspond to those described above, but with the difference that there is still a connecting line to the shuttle valve 58. The highest pressure prevailing at a consumer is selected in each case via these alternating non-return valves and is brought to the flow control valve 55 via a line 60. Such arrangements are known per se and have the purpose of setting the flow control valve 55 in the neutral position of the directional control valves so that it produces a direct connection from the pump to the return line in its switching position II, so that there is no power loss. The supply pressure of the pressure control valve 28 comes from the control line 60 for the flow control valve 55, ie in the neutral position of the directional control valve 18, the pressure in the actuating cylinder 15 or in the line 16 drops to the tank pressure, see the dashed line in FIG. 3.

Claims

Ansprüche Expectations
1. Hydraulikanlage mit einer von einem Motor (13) angetriebenen Pumpe (10), dessen seine Drehzahl einstellender Regler ( 14 ) von einem über eine Leitung (16) druckmittelbeaufschlagten Stellzylinder (15) derart einstellbar ist, daß die Drehzahl des Motors und damit die Fördermenge der Pumpe gerade so groß ist, wie von der Pumpe über Wegeventile (18 bis 20) versorgte Verbraucher gerade benötigen, sowie mit einem Druckregelventil (28), das den Druck in der Leitung (16) erzeugt, dadurch gekennzeichnet, daß das Druckregelventil so ausgelegt ist, daß es beim Betätigen eines üblichen Wegeventils (19, 20) für einen der Verbraucher einen konstanten Druck erzeugt und daß es beim Betätigen eines besonderen Wegeventils (18) für einen anderen Verbraucher, das eine spezielle verstellbare Drosselkante ( 48 ) aufweist, einen proportional der Schieberauslenkung ansteigenden Druck erzeugt.1. Hydraulic system with a motor (13) driven pump (10), its speed-adjusting controller (14) from a line (16) pressurized actuating cylinder (15) is adjustable such that the speed of the motor and thus the Flow rate of the pump is just as large as the consumers supplied by the pump via directional valves (18 to 20) just need, and with a pressure control valve (28) that generates the pressure in the line (16), characterized in that the pressure control valve is designed so that when a conventional directional control valve (19, 20) is actuated it generates a constant pressure for one of the consumers and that it actuates a special directional control valve (18) for another consumer which has a special adjustable throttle edge (48) pressure increasing in proportion to the slide deflection.
2. Anlage nach Anspruch 1, dadurch gekennzeichnet, daß die spezielle Steuerkante (48) des Wegeventils (18) eine Feinsteuerfase ist. 2. Plant according to claim 1, characterized in that the special control edge (48) of the directional valve (18) is a fine control chamfer.
3. Anlage nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß das besondere Wegeventil (18) zur Steuerung eines einfach wirkenden Verbrauchers dient und in Arbeitsstellung eine Verbindung von der Leitung ( 1 6 ) zur Rücklaufleitung (25) steuert.3. Plant according to claim 1 and / or 2, characterized in that the special directional control valve (18) serves to control a single-acting consumer and controls a connection from the line (1 6) to the return line (25) in the working position.
4. Anlage nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das Druckregelventil (28) im Wegeventil (18) integriert ist. 4. Plant according to one of claims 1 to 3, characterized in that the pressure control valve (28) is integrated in the directional control valve (18).
EP85905393A 1984-11-28 1985-10-28 Hydraulic installation Expired EP0203100B1 (en)

Applications Claiming Priority (2)

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DE3443354 1984-11-28
DE19843443354 DE3443354A1 (en) 1984-11-28 1984-11-28 HYDRAULIC SYSTEM

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EP0203100B1 EP0203100B1 (en) 1989-09-20

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JP (1) JPH0625561B2 (en)
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JPH0625561B2 (en) 1994-04-06
EP0203100B1 (en) 1989-09-20
DE3443354A1 (en) 1986-05-28
DE3573154D1 (en) 1989-10-26
US4716727A (en) 1988-01-05
WO1986003264A1 (en) 1986-06-05
JPS62500798A (en) 1987-04-02

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