EP0718504B1 - Mono-block hydraulic control system - Google Patents

Mono-block hydraulic control system Download PDF

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Publication number
EP0718504B1
EP0718504B1 EP95118187A EP95118187A EP0718504B1 EP 0718504 B1 EP0718504 B1 EP 0718504B1 EP 95118187 A EP95118187 A EP 95118187A EP 95118187 A EP95118187 A EP 95118187A EP 0718504 B1 EP0718504 B1 EP 0718504B1
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EP
European Patent Office
Prior art keywords
control device
directional valve
hydraulic control
proportional directional
valve element
Prior art date
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Expired - Lifetime
Application number
EP95118187A
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German (de)
French (fr)
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EP0718504A3 (en
EP0718504A2 (en
Inventor
Hartmut Dipl.-Ing. Sandau
Werner Dipl.-Ing. Schumacher
Horst Dr. Dr. Ing. Hesse
Rainer Dipl.-Ing. Trucksess (Fh)
Holger Dipl.-Ing. Lueues
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0718504A2 publication Critical patent/EP0718504A2/en
Publication of EP0718504A3 publication Critical patent/EP0718504A3/en
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Publication of EP0718504B1 publication Critical patent/EP0718504B1/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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices

Definitions

  • the invention is based on a hydraulic control in monoblock design for lifting and lowering a load that out at least two electromagnetic directional control valve elements and a pressure compensator as an input element to the load-independent lifting of the load exists, the elements at least are partially arranged in a housing that at least a pump connection, at least one consumer connection and has at least one return connection.
  • such control devices have a monoblock design the drives, actuators and connections arranged on almost all housing sides of the monoblock. Surrender after mounting the drives and connections despite being more compact Construction valve blocks with large external dimensions, because special the drives are often opposite or arranged in a corner protrude from the monoblock housings.
  • the hydraulic control device enables regarding their housing dimensions and the overall size of the monoblock a small build volume.
  • the individual valve elements are arranged closely next to each other and sometimes sit in a production-friendly way constructed and arranged holes, with which weight and processing time can be saved. To do this all valve parts are housed in just two holes.
  • a proportional directional valve element for lifting is located in a bore a load next to a pressure compensator.
  • the hole is a through hole without any gradation.
  • parallel to this Bore is a proportional directional valve element for lowering the aforementioned load arranged next to a seat valve.
  • Both holes have the same length and end next to each other on the corresponding end faces of the common housing. On one of the end faces are the electromagnetic drives arranged, which drives the drives can also be controlled mechanically with simple means.
  • the Control device includes, for example, a simple cast housing, that only requires a few screw connections.
  • the proportional directional valve elements are in their Combination through a corresponding hydraulic connection and a selected electrical circuit for very short response times designed.
  • Regarding the hydraulic connection is located between the proportional directional valve elements connecting channel dividing into two channel sections, the flows through both when lifting and when lowering the load becomes.
  • the two channel sections stand over two control edges the longitudinal slide of the valve element for lifting the load with the Return in connection. Since the return flow divides, the longitudinal slide has a smaller stroke.
  • the valve element for lowering the load is for damping the lowering function a control oil throttle. About this control oil throttle becomes necessary to initiate the closing movement Pressure medium passed.
  • a load control valve is arranged to lower the load during the Closing phase of the valve element hydraulically to the control oil throttle is connected in parallel.
  • the check valve is in the form of a Valve cartridge immediately behind the valve element in the same Drilling. The cross-sectional enlargement due to the parallel connection accelerates the closing movement of the valve element considerably, so that it functions as a the consumer connection Execute the shut-off check valve better and faster can.
  • the proportional directional valve element for lowering the load protrudes a load detection system hydraulically connected to the pressure compensator.
  • the electromagnetic drive of this valve element is to accelerate the closing movement of the pressure compensator while the actuation of the electromagnetic drive of the other valve element to lift the load after blocking the return, at least briefly energized. This speeds up a large volume flow in a short period of time the closing movement the pressure compensator.
  • the hydraulic circuit diagram shown in Figure 1 shows one basic structure of a control device for a OC hydraulic system with two electromagnetically actuated proportional directional valve elements (90, 120) and a pressure compensator (70).
  • the control device is used to control a single-acting hydraulic cylinder, for example part a self-propelled work machine is like this with the power lift an electro-hydraulic hoist control device Case is.
  • Both proportional directional valve elements (90) and (120) are throttling Directional control valves, the longitudinal slide of which besides the two end positions can take any intermediate positions. They each have a proportional magnet on their left side (91, 121) and on their right side a return spring (108, 155).
  • the first proportional directional valve element (90) is a 3/2-way valve and the second (120) is a 2/2-way valve, wherein both are connected in series via a connecting line (13) are so that the pressure medium flow pump / consumer in flows in both directions via both directional valves.
  • the 3/2-way valve controls the pressure medium flow from the pump to the consumer, a single-acting hydraulic cylinder for lifting one Load.
  • the proportional directional valve element (90) is therefore described below Called lifting module.
  • the 2/2-way valve controls the from single-acting hydraulic cylinder returning to the tank under load Pressure medium flow.
  • the second proportional directional valve element (120) is therefore called the sink module. It is trained in seat valve type and also works as a die Check valve with load protection.
  • the pressure compensator (70) which at a neutral circuit is open and the pressure medium flow that is not required leads almost unthrottled into the return line (16).
  • the control spring (88) Load signaling line (12) connected by the connecting line (13) branches.
  • the proportional magnet (91) of the lifting module is used to lift a load (90) energized.
  • the return flow is blocked and pressure medium is via the lifting module (90), the connecting line (13) and the check valve (21) of the sink module (120) to the consumer connection (50) headed.
  • This is done via the load reporting line (12) the pressure compensator (70) on its spring-loaded side with which the pump current corresponds to that at the consumer connection (50) applied load pressure is throttled and a load-independent lifting known per se is achieved.
  • Proportional magnet (91) the proportional magnet (121) of the sink module (120) activated.
  • the pressure medium flows from the consumer connection (50) via the two modules (120, 90) and the return line (17) to the return connection (52).
  • the implemented control device is partially Longitudinal section shown. It has an essentially cuboid shape - Here shown in simplified form - housing (30) with two approximately square, flat surfaces, here as the top and bottom (31) and (33), cf. Figure 3, are referred to in the In practice, however, another in a flanged block Can take position.
  • a consumer connection (50) and two slot-shaped return channels (65) and (66) arranged in the finely machined bottom are a consumer connection (50) and two slot-shaped return channels (65) and (66) arranged.
  • the return channels open into an elongated hole flange (36).
  • the consumer connection (50) and the elongated hole flange (36) each point towards the bottom a recess on which the receiving of a sealing ring (37) and (37 ') serves.
  • There are also three mounting holes (69, 69 ', 69 ") can be seen perpendicular to the underside (33) of the housing (30) penetrate.
  • the side surfaces aligned perpendicular to the cut surface (34, 35, 38, 39) each have a rectangular outline.
  • the front (34) and the back (35) are flat, finely machined Surfaces.
  • On the front are the two proportional magnets (91) and (121) flanged. Sitting opposite you in the Back (35) the locking screws (114) and (157) for the Bores (41, 42) and (44).
  • the other two faces (38) and (39) have bulges around the mounting holes (69, 69 ') are formed.
  • the one in FIG top side surface (38) a nozzle for receiving the Pump connection (49).
  • the pump connection is provided with an internal thread (49) in the housing (30) into an inlet ring channel (93).
  • the ring channel (93) penetrates a cylindrical through hole (41) extending from the front (34) to the back (35) extends.
  • the longitudinal slide (97) of the lifting module (90) is seated.
  • the middle one (94) is a return ring channel, the on the return channel formed in the bottom (33) (65) opens.
  • On both sides of this return ring channel (94) are the two ring channels (95) and (96) to which the two channel sections (57) and (58) are connected, the in turn unite to form the connecting channel (55).
  • the longitudinal slide (97) of the lifting module (90) connects either - in the unactuated state - the connecting channel (55) with the Return ring channel (94) or - when actuated - with the Inlet ring channel (93) behind the pump connection (49).
  • the cylindrical outer contour of the longitudinal slide (97) the two Ring grooves (99) and (100).
  • the right ring groove (100) which i.a. can connect the inlet ring channel (93) to the ring channel (96), goes into fine control notches in the area of their right shaft collar (103), which in connection with the pressure compensator (70) Function as a measuring choke.
  • the opening cross sections of the Fine control notches (103) decrease in the direction of the feed ring channel (93), but without it - with de-energized proportional magnet (91) - to achieve.
  • the fine control notches (103) are here for example round notches.
  • the left wall of the right annular groove (100) forms one of two Control edges (101) and (102) on the longitudinal slide (97) the return from the connecting channel (55) into the return ring channel (94) controls.
  • the other control edge (101) is the left wall of the left ring groove (99). It opens or closes the path from the canal section (57) to the return ring channel (94).
  • the right wall the annular groove (99) is located over the entire stroke of the longitudinal slide (97) in the area of the return ring channel (94) and closes not this one.
  • the longitudinal slide Located on the left edge of the outer contour of the longitudinal slide (97) in the area of the sealing ring between the proportional magnet (91) and the housing (30) a puncture. Below this The longitudinal slide has a cylindrical recess (104), at the bottom of which the armature plunger (92) of the proportional magnet (91) is pending.
  • the longitudinal slide (97) is from the right end face (98) bored in stages.
  • the right area of the stepped bore (105) serves to guide the return spring (108).
  • the left area has a smaller diameter and connects at an angle running compensation bore (106) with the stepped bore (105) the recess (104). The transition from the right to the left area the stepped hole forms a flat collar on which the return spring (108) is supported.
  • the other end of the return spring (108) lies on a stepped Spring plate (109).
  • the spring plate (109) is in cross section formed in a star shape for pressure equalization on Longitudinal slide (97) pass the pressure medium unthrottled to let. He is sitting on a pole (110) that faces right extends centrally in the through hole (41).
  • the Rod (110) protrudes into a right of the longitudinal slide (97) arranged, pot-shaped pressure compensator piston (80) into encounter a grub screw (111) there.
  • the Rod (110) in a bore in the end face (81) of the pressure compensator piston (80) guided tightly.
  • the threaded pin (111) extends in the extension of the Rod (110) and ends in the screw plug (114).
  • the screw plug (114) has an internal thread in which this is screwed in.
  • the head of the locking screw (114) a cylindrical recess that accommodates a lock nut (112) serves.
  • the setscrew (111) it has one at its outer free end Hexagon on.
  • the through hole (41) goes into one at its right end Screw hole (42) over.
  • the screw plug (114) is attached.
  • One in the area sealing ring (118) between head and thread seals the screw plug bore (42) from the outside.
  • the Pressure balance piston (80) In the through hole (41) sits between the adjusting screw (114) and the longitudinal slide (97) tightly sliding the Pressure balance piston (80).
  • the latter has a cylindrical outer contour, which has a semicircular cut at its right end (84) has, in which a spring washer (89) is inserted.
  • the spring ring (89) lies - for example in the case of a control device free of pressure medium -
  • the right stop for the pressure compensator piston (80) forms the screw plug (114).
  • Located on the left edge of the outer contour several fine notches distributed around the circumference (83) into the pressure compensator piston from the left end (81) (80) are incorporated.
  • the pressure compensator piston (80) is behind the semicircular groove (84) chamfered. In the area in front of the spring washer (89) it carries a row of relief grooves.
  • the bottom of the guide bore (87) is narrowed, to fix the control spring (88) radially.
  • a hole (115) with a comparable contour is also in the left end of the adjusting screw (114).
  • a load reporting channel (74) is arranged between the return ring channel (71) and the adjusting screw (114). He's standing with the channel section (58) via a through hole (41) parallel load detection hole (63) in connection.
  • the sink module (120) has an end that crosses the housing (30) Stepped bore (44) parallel to the through bore (41) of the Lifting module (90) is aligned.
  • the stepped bore (44) is left - as in the lifting module - through the proportional magnet (121) and on the right through a screw plug (157) with hexagon socket and sealing ring arranged between the head and the thread (158) sealed pressure-tight.
  • a valve sleeve is located in the central area of the stepped bore (44) (130), the two nested longitudinal slides records.
  • the valve sleeve (130) is in the stepped bore (44) between a left housing collar (124) and a right one Screw ring (156) with an internal, continuous Hexagon socket secured axially.
  • the right area of the stepped bore (44) is provided with an internal thread (129).
  • valve sleeve (130) is supported by a consumer ring channel (125) surrounded, with the consumer connection shown in Figure 3 (50) is hydraulically connected.
  • Left of the Valve sleeve (130) has an adjusting screw (150) in the internal thread (128). In the area of this adjusting screw (150) opens the connecting channel (55) in the stepped bore (44).
  • the sink module (120) is shown in the locked position.
  • Around the main spool (140) on the main valve seat To hold (132) is in on his right face a pressure chamber (135) to pressure medium.
  • the pressure medium gets there from the consumer ring channel (125) via radial bores (131) in the valve sleeve (130) and in the main control spool via a throttle bore (144) and an adjoining one Longitudinal bore (145).
  • the longitudinal bore (145) penetrates with a control groove (143) at the bottom of the hole.
  • the contact pressure is reduced by the opposing force due to the in the area of the outer contour of the main control spool (140) between Main valve cone (141) and relief grooves are present Pressure.
  • the sink module (120) opens when the proportional solenoid is energized (121). Its anchor plunger (122) pushes the inner one Longitudinal spool, a pilot spool (147) slightly behind right. As a result, his input tax notches (149) get under the Control groove (143) of the main control spool (140). At the same time lifts his valve cone (148) further left from his in the main control slide (140) corresponding valve seat (146) from. The pressure chamber (135) now stands over the longitudinal bore (145), the control groove (143), the pilot control notches (149), the valve seat (146) and the connecting channel (55) with the return ring channel (94) in conjunction.
  • the pilot control notch (149) Depending on the opening cross-section the pilot control notch (149) the pressure in the pressure chamber (135) drops. The pressure there arises according to the ratio of the Cross section of the throttle bore (144) and the opening cross section the pilot notches (149). Falls accordingly the pilot spool (147) pushed far to the right is the pressure in the pressure chamber (135) so far that the pressure medium on the Main control spool (140) in the area below the radial bores (131) the force exerted to the right predominates, the Main control spool (140) also moved to the right. The Main valve plug (141) lifts off the main valve seat (132) and the Main control notches (142) reach the area of the annulus (134).
  • the pressure medium flows between the valve sleeve (130) and the main control spool (140) towards the connecting channel (55).
  • the main spool (140) hurries through its opening movement to the pilot spool (147) after, whereby the opening cross-section at the pilot notches (149) becomes smaller. This can over in the pressure chamber (135) the throttle bore (144) build up a higher pressure. Hence the opening movement of the main control slide (140) is braked, until a state of equilibrium is established.
  • the anchor plunger (122) moves to the left, it follows due to a return spring integrated in the adjusting screw (150) (155) the pilot spool (147).
  • the return spring (155) is supported by the pilot spool (147) and the adjusting screw (150).
  • the pilot notches (149) are closed.
  • the pressure in Pressure chamber (135) increases.
  • the main valve plug (141) lies on Main valve seat (132).
  • the sink module (120) locks.
  • the proportional directional valve element (120) thus works like a Sequence control.
  • the adjusting screw (150) one in the middle area of its outer contour Helical toothing (151) into which the toothing is at least temporarily engages an adjusting screw.
  • the adjusting screw sits in an adjustment hole (68), which is here from the Front (34) extends into the stepped bore (44) and the Connection channel (55) tangent.
  • the adjusting screw can be used with Using an adjusting spindle, the free end of which from the housing (30) protrudes, or a special tool that sometimes comes with the adjustment screw can be coupled on the face, in rotation be transferred.
  • the length the adjustment range largely corresponds to the width of the toothing (151) the adjusting screw (150).
  • the sink module (120) which is in the control device during the Lifting the load has the function of a check valve due to the high demands on the fine controllability of the Lowering of the load damped relatively strongly by the throttle bore (144). This damping slows down the closing movement during the kickback function.
  • the throttle bore (144) can be lifted by a seat valve (160) can be connected in parallel.
  • FIG. 4 is to the right of the valve sleeve (130) instead of Screw ring (156), cf. Figure 2, this seat valve (160) arranged.
  • the seat valve has a disk-shaped body with a molded hexagon.
  • the cylindrical part of its outer contour carries a thread with an inserted sealing ring with which it is screwed into the right area of the stepped bore (44).
  • the screw ring (156) from FIG. 2 it fixes the valve sleeve (130).
  • an annular channel (161) is formed between the bottom of the seat valve.
  • the channel (161) is at an inclined hole (162) with this the side surface (39) of the housing (30) formed in a nozzle shape Consumer connection (51) in connection.
  • the seat valve (160) has a longitudinal bore (165) on which a valve seat in the shape of a cone towards the valve sleeve (130) is trained.
  • a Sliding piston (164) stored and guided.
  • the right section the slide piston (164) has a cylindrical shape. That is followed by a valve plate on the left, which has a waist is connected to the cylindrical portion.
  • a hub of the Slide piston (164) to the right is through the contact between Valve disc and valve seat limited during one stroke on the left by striking one sitting on the slide piston Circlip terminated on the front of the hexagon becomes. From the longitudinal bore (165) go in the area of the waist of the Sliding piston (164) approximately star-shaped several holes (166) gone.
  • annular groove for receiving a sealing ring (167) incorporated in the stepped bore (44) is located between the seat valve (160) and the screw plug (157) an annular channel (163) that connects to the load signaling hole (63) communicates.
  • the proportional magnet When lifting the load, the proportional magnet is energized (91), cf. also Figure 2, pressure medium via the pump connection (49), the inlet ring channel (93), the longitudinal slide (97), and the connecting channel (55) in front of the longitudinal slide (140) and (147) of the sink module (120).
  • the longitudinal slide (97) initially only opens the load on its fine tax notches (103). They form in relation to the Pressure compensator (70) the measuring throttle.
  • the pressure medium flows on the Path to the sink module (120) via the load reporting hole (63) and the Load signaling channel (74) on the back of the pressure compensator piston (80).
  • the control pressure drop generated by the pressure compensator (70) during the closing process lies not only on the fine control notches (103), but also on both sides of the pressure compensator piston (80).
  • the low pressure drop that is present, as well as the low volume flow which may be additionally reduced by a throttle point integrated in the load reporting bore (63) to stabilize the movement of the pressure compensator piston (80), necessitates a slow closing movement of the pressure compensator piston (80).
  • the proportional magnet (121) of the sink module can be energized briefly, for example.
  • FIG. 5 shows a simplified representation of the energization of the two proportional magnets (91) and (121) when the load is raised and then lowered.
  • the time t is plotted on the abscissa.
  • the current I 91 for the proportional magnet (91) is shown on the positive branch of the ordinate and the current I 121 for the proportional magnet (121) is shown on the negative branch.
  • the load is raised over the period t 91 and lowered over the period t 121 .
  • the proportional magnet (121) energized for the time t 2 .
  • pressure medium flows from the consumer connection (50) or (51) under load pressure via the main control spool (140) and the connecting channel (55), the load signaling bore (63) and the load signaling channel (74) to the rear of the pressure compensator piston (80).
  • the large volume flow set in motion causes the pressure compensator piston (80) to quickly block the return ring channel (71).
  • the proportional magnet (91) is used to stop lifting the load. switched off.
  • the longitudinal slide (97) wants to due to the Move the return spring (108) to the left to find the path between the Block inlet ring channel (93) and the channel section (58).
  • the longitudinal slide (97) is locked in unfavorable conditions but before locking the main spool (140) of the because of the fine control of the damped sink module (120).
  • the pressure medium flows back into the consumer connection (51) In the direction of the inlet ring channel (93). The flow forces disrupt the longitudinal slide (97) when closing. Fixed this problem the poppet valve (160).
  • This control device is due to the parallel arrangement the modules (90) and (120) the possibility in front of the back Ends of the two proportional magnets (91) and (121) a manual control element (25), for example in a swivel joint bearing (26) to be stored, cf. Figure 2.
  • the hand control (25) acts on the manual override elements (24) the proportional magnets (91) and (121). With the hand control (25) can either manually lift (90) or the sink module (120) can be controlled.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Servomotors (AREA)
  • Multiple-Way Valves (AREA)

Description

Stand der Technik:State of the art:

Die Erfindung geht von einer hydraulischen Steuerung in Monoblockbauweise zum Heben und Senken einer Last aus, die aus mindestens zwei elektromagnetisch betätigbaren Proportionalwegeventilelementen und einer Druckwaage als Eingangselement zum lastunabhängigen Heben der Last besteht, wobei die Elemente zumindest teilweise in einem Gehäuse angeordnet sind, das mindestens einen Pumpenanschluß, mindestens einen Verbraucheranschluß und mindestens einen Rücklaufanschluß aufweist.The invention is based on a hydraulic control in monoblock design for lifting and lowering a load that out at least two electromagnetic directional control valve elements and a pressure compensator as an input element to the load-independent lifting of the load exists, the elements at least are partially arranged in a housing that at least a pump connection, at least one consumer connection and has at least one return connection.

In der Regel werden bei solchen Steuervorrichtungen in Monoblockbauweise die Antriebe, Betätigungselemente und Anschlüsse an fast allen Gehäuseseiten des Monoblocks angeordnet. Dabei ergeben sich nach dem Anbau der Antriebe und Anschlüsse trotz kompakter Bauweise Ventilblöcke mit großen Außenabmessungen, da besonders die Antriebe oft gegenüberliegen oder über Eck angeordnet aus den Monoblockgehäusen herauskragen.As a rule, such control devices have a monoblock design the drives, actuators and connections arranged on almost all housing sides of the monoblock. Surrender after mounting the drives and connections despite being more compact Construction valve blocks with large external dimensions, because special the drives are often opposite or arranged in a corner protrude from the monoblock housings.

Vorteile der Erfindung:Advantages of the invention:

Die erfindungsgemäße hydraulische Steuervorrichtung ermöglicht bezüglich ihrer Gehäuseabmessungen und der Gesamtgröße des Monoblocks ein kleines Bauvolumen. Die einzelnen Ventilelemente sind eng nebeneinander angeordnet und sitzen teilweise in fertigungsgünstig konstruierten und angeordneten Bohrungen, womit Gewicht und Bearbeitungszeit eingespart werden können. Dazu werden alle Ventilteile in nur zwei Bohrungen untergebracht. In der einen Bohrung sitzt ein Proportionalwegeventilelement zum Heben einer Last neben einer Druckwaage. Die Bohrung ist eine Durchgangsbohrung ohne jede Stufung. In der anderen, zu dieser parallelen Bohrung ist ein Proportionalwegeventilelement zum Senken der zuvor genannten Last neben einem Sitzventil angeordnet. Beide Bohrungen haben die gleiche Länge und enden jeweils nebeneinander an den entsprechenden Stirnseiten des gemeinsamen Gehäuses. Auf einer der Stirnseiten sind direkt nebeneinander die elektromagnetischen Antriebe angeordnet, wodurch die Antriebe mit einfachen Mitteln auch mechanisch ansteuerbar sind. Die Steuervorrichtung umfaßt beispielsweise ein einfaches Gußgehäuse, das nur wenige Verschraubungen benötigt.The hydraulic control device according to the invention enables regarding their housing dimensions and the overall size of the monoblock a small build volume. The individual valve elements are arranged closely next to each other and sometimes sit in a production-friendly way constructed and arranged holes, with which weight and processing time can be saved. To do this all valve parts are housed in just two holes. In the a proportional directional valve element for lifting is located in a bore a load next to a pressure compensator. The hole is a through hole without any gradation. In the other, parallel to this Bore is a proportional directional valve element for lowering the aforementioned load arranged next to a seat valve. Both holes have the same length and end next to each other on the corresponding end faces of the common housing. On one of the end faces are the electromagnetic drives arranged, which drives the drives can also be controlled mechanically with simple means. The Control device includes, for example, a simple cast housing, that only requires a few screw connections.

Des weiteren sind die Proportionalwegeventilelemente in ihrer Kombination durch eine entsprechende hydraulische Verschaltung und eine ausgewählte elektrische Beschaltung für sehr kurze Ansprechzeiten ausgelegt. Bezüglich der hydraulischen Verschaltung befindet sich zwischen den Proportionalwegeventilelementen ein sich in zwei Kanalabschnitte aufteilender Verbindungskanal, der sowohl beim Heben als auch beim Senken der Last durchströmt wird. Die beiden Kanalabschnitte stehen über zwei Steuerkanten des Längsschiebers des Ventilelements zum Heben der Last mit dem Rücklauf in Verbindung. Da sich der Rücklaufstrom aufteilt, kommt der Längsschieber mit einem kleineren Hub aus.Furthermore, the proportional directional valve elements are in their Combination through a corresponding hydraulic connection and a selected electrical circuit for very short response times designed. Regarding the hydraulic connection is located between the proportional directional valve elements connecting channel dividing into two channel sections, the flows through both when lifting and when lowering the load becomes. The two channel sections stand over two control edges the longitudinal slide of the valve element for lifting the load with the Return in connection. Since the return flow divides, the longitudinal slide has a smaller stroke.

Im Ventilelement zum Senken der Last befindet sich zur Dämpfung der Senkenfunktion eine Steueröldrossel. Über diese Steueröldrossel wird das zur Einleitung der Schließbewegung erforderliche Druckmittel geleitet. Koaxial neben dem Ventilelement zum Senken der Last ist ein Sperrventil angeordnet, das während der Schließphase des Ventilelements hydraulisch zur Steueröldrossel parallel geschaltet ist. Das Sperrventil sitzt in Form einer Ventilpatrone unmittelbar hinter dem Ventilelement in der gleichen Bohrung. Die Querschnittsvergrößerung aufgrund der Parallelschaltung beschleunigt die Schließbewegung des Ventilelements erheblich, so daß es seine Funktion als ein den Verbraucheranschluß absperrendes Rückschlagventil besser und schneller ausführen kann.The valve element for lowering the load is for damping the lowering function a control oil throttle. About this control oil throttle becomes necessary to initiate the closing movement Pressure medium passed. Coaxially next to the valve element A load control valve is arranged to lower the load during the Closing phase of the valve element hydraulically to the control oil throttle is connected in parallel. The check valve is in the form of a Valve cartridge immediately behind the valve element in the same Drilling. The cross-sectional enlargement due to the parallel connection accelerates the closing movement of the valve element considerably, so that it functions as a the consumer connection Execute the shut-off check valve better and faster can.

Das Proportionalwegeventilelement zum Senken der Last steht über ein Lastmeldesystem mit der Druckwaage hydraulisch in Verbindung. Der elektromagnetische Antrieb dieses Ventilelements wird zur Beschleunigung der Schließbewegung der Druckwaage, während der Betätigung des elektromagnetischen Antriebs des anderen Ventilelements zum Heben der Last, nach dessen Sperrung des Rücklaufs, zumindest kurzzeitig bestromt. Dadurch beschleunigt ein großer Volumenstrom in einer kurzen Zeitspanne die Schließbewegung der Druckwaage.The proportional directional valve element for lowering the load protrudes a load detection system hydraulically connected to the pressure compensator. The electromagnetic drive of this valve element is to accelerate the closing movement of the pressure compensator while the actuation of the electromagnetic drive of the other valve element to lift the load after blocking the return, at least briefly energized. This speeds up a large volume flow in a short period of time the closing movement the pressure compensator.

Zeichnungen:Drawings:

Weitere Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung zweier vereinfacht dargestellter Ausführungsformen:

Figur 1:
Hydraulikschaltplan für eine Steuervorrichtung mit elektromagnetisch betätigten Proportionalwegeventilelementen und einer Druckwaage;
Figur 2:
Schnitt durch eine Steuervorrichtung nach Figur 1;
Figur 3:
Unteransicht der Steuervorrichtung nach Figur 2;
Figur 4:
Schnitt durch eine Steuervorrichtung nach Figur 1 mit einem zusätzlichen Sitzventil;
Figur 5:
Strombeaufschlagung der elektromagnetischen Antriebe.
Further details of the invention result from the following description of two simplified embodiments:
Figure 1:
Hydraulic circuit diagram for a control device with electromagnetically operated proportional directional control valve elements and a pressure compensator;
Figure 2:
Section through a control device according to Figure 1;
Figure 3:
Bottom view of the control device according to Figure 2;
Figure 4:
Section through a control device according to Figure 1 with an additional seat valve;
Figure 5:
Current applied to the electromagnetic drives.

Beschreibung der Ausführungsbeispiele:Description of the embodiments:

Der in Figur 1 dargestellte Hydraulikschaltplan zeigt einen prinzipiellen Aufbau einer Steuervorrichtung für ein OC-Hydrauliksystem mit zwei elektromagnetisch betätigbaren Proportionalwegeventilelementen (90, 120) und einer Druckwaage (70). Die Steuervorrichtung dient der Ansteuerung eines einfach wirkenden Hydraulikzylinders, der beispielsweise Teil einer selbstfahrenden Arbeitsmaschine ist, wie dies beim Kraftheber einer elektrohydraulischen Hubwerksregeleinrichtung der Fall ist.The hydraulic circuit diagram shown in Figure 1 shows one basic structure of a control device for a OC hydraulic system with two electromagnetically actuated proportional directional valve elements (90, 120) and a pressure compensator (70). The control device is used to control a single-acting hydraulic cylinder, for example part a self-propelled work machine is like this with the power lift an electro-hydraulic hoist control device Case is.

Beide Proportionalwegeventilelemente (90) und (120) sind drosselnde Wegeventile, deren Längsschieber außer den beiden Endstellungen stufenlos beliebige Zwischenstellungen einnehmen können. Sie haben auf ihrer linken Seite je einen Proportionalmagneten (91, 121) und auf ihrer rechten Seite je eine Rückstellfeder (108, 155). Das erste Proportionalwegeventilelement (90) ist ein 3/2-Wegeventil und das zweite (120) ein 2/2-Wegeventil, wobei beide über eine Verbindungsleitung (13) hintereinandergeschaltet sind, so daß der Druckmittelstrom Pumpe/Verbraucher in beiden Richtungen über beide Wegeventile fließt. Das 3/2-Wegeventil steuert den Druckmittelstrom von der Pumpe zum Verbraucher, einen einfach wirkenden Hydraulikzylinder zum Heben einer Last. Das Proportionalwegeventilelement (90) wird daher im folgenden Hebenmodul genannt. Das 2/2-Wegeventil steuert den vom einfach wirkenden Hydraulikzylinder unter Last zum Tank zurücklaufenden Druckmittelstrom. Das zweite Proportionalwegeventilelement (120) wird folglich als Senkenmodul bezeichnet. Es ist in Sitzventilbauart ausgebildet und arbeitet zudem als ein die Last absicherndes Rückschlagventil.Both proportional directional valve elements (90) and (120) are throttling Directional control valves, the longitudinal slide of which besides the two end positions can take any intermediate positions. They each have a proportional magnet on their left side (91, 121) and on their right side a return spring (108, 155). The first proportional directional valve element (90) is a 3/2-way valve and the second (120) is a 2/2-way valve, wherein both are connected in series via a connecting line (13) are so that the pressure medium flow pump / consumer in flows in both directions via both directional valves. The 3/2-way valve controls the pressure medium flow from the pump to the consumer, a single-acting hydraulic cylinder for lifting one Load. The proportional directional valve element (90) is therefore described below Called lifting module. The 2/2-way valve controls the from single-acting hydraulic cylinder returning to the tank under load Pressure medium flow. The second proportional directional valve element (120) is therefore called the sink module. It is trained in seat valve type and also works as a die Check valve with load protection.

Zwischen dem Pumpenanschluß (49) und dem Hebenmodul (90) ist in einem Nebenzweig (10) die Druckwaage (70) angeordnet, die bei einem Neutralumlauf geöffnet ist und den nicht benötigten Druckmittelstrom nahezu ungedrosselt in die Rücklaufleitung (16) leitet. An der Druckwaage (70) ist neben der Regelfeder (88) eine Lastmeldeleitung (12) angeschlossen, die von der Verbindungsleitung (13) abzweigt.Between the pump connection (49) and the lifting module (90) is in an auxiliary branch (10) arranged the pressure compensator (70), which at a neutral circuit is open and the pressure medium flow that is not required leads almost unthrottled into the return line (16). On the pressure compensator (70) there is one next to the control spring (88) Load signaling line (12) connected by the connecting line (13) branches.

Zum Heben einer Last wird der Proportionalmagnet (91) des Hebenmoduls (90) bestromt. Der Rücklauf wird gesperrt und Druckmittel wird über das Hebenmodul (90), die Verbindungsleitung (13) und das Rückschlagventil (21) des Senkenmoduls (120) zum Verbraucheranschluß (50) geleitet. Hierbei wird über die Lastmeldeleitung (12) die Druckwaage (70) auf ihrer federbelasteten Seite beaufschlagt, womit der Pumpenstrom entsprechend dem am Verbraucheranschluß (50) anliegenden Lastdruck angedrosselt wird und ein an sich bekanntes lastdruckunabhängiges Heben erreicht wird.The proportional magnet (91) of the lifting module is used to lift a load (90) energized. The return flow is blocked and pressure medium is via the lifting module (90), the connecting line (13) and the check valve (21) of the sink module (120) to the consumer connection (50) headed. This is done via the load reporting line (12) the pressure compensator (70) on its spring-loaded side with which the pump current corresponds to that at the consumer connection (50) applied load pressure is throttled and a load-independent lifting known per se is achieved.

Zum Senken einer Last wird bei einem in der Regel unbestromten Proportionalmagnet (91) der Proportionalmagnet (121) des Senkenmoduls (120) aktiviert. Das Druckmittel fließt vom Verbraucheranschluß (50) über die beiden Module (120, 90) und die Rücklaufleitung (17) zum Rücklaufanschluß (52).To lower a load, one is usually de-energized Proportional magnet (91) the proportional magnet (121) of the sink module (120) activated. The pressure medium flows from the consumer connection (50) via the two modules (120, 90) and the return line (17) to the return connection (52).

In Figur 2 wird die realisierte Steuervorrichtung im teilweisen Längsschnitt gezeigt. Sie hat ein im wesentlichen quaderförmiges - hier vereinfacht dargestelltes - Gehäuse (30) mit zwei annähernd quadratischen, ebenen Flächen, die hier als Ober- und Unterseite (31) und (33), vgl. Figur 3, bezeichnet sind, in der Praxis aber in einem zusammengeflanschten Block auch eine andere Lage einnehmen können. In der feinbearbeiteten Unterseite sind ein Verbraucheranschluß (50) und zwei langlochförmige Rücklaufkanäle (65) und (66) angeordnet. Die Rücklaufkanäle münden in einen Langlochflansch (36). Der Verbraucheranschluß (50) und der Langlochflansch (36) weisen jeweils zur Unterseite hin je eine Ausnehmung auf, die der Aufnahme je eines Dichtrings (37) und (37') dient. Ferner sind drei Befestigungsbohrungen (69, 69', 69") zu sehen, die senkrecht zur Unterseite (33) das Gehäuse (30) durchdringen.In Figure 2, the implemented control device is partially Longitudinal section shown. It has an essentially cuboid shape - Here shown in simplified form - housing (30) with two approximately square, flat surfaces, here as the top and bottom (31) and (33), cf. Figure 3, are referred to in the In practice, however, another in a flanged block Can take position. In the finely machined bottom are a consumer connection (50) and two slot-shaped return channels (65) and (66) arranged. The return channels open into an elongated hole flange (36). The consumer connection (50) and the elongated hole flange (36) each point towards the bottom a recess on which the receiving of a sealing ring (37) and (37 ') serves. There are also three mounting holes (69, 69 ', 69 ") can be seen perpendicular to the underside (33) of the housing (30) penetrate.

Die senkrecht zur Schnittfläche ausgerichteten Seitenflächen (34, 35, 38, 39) haben jeweils einen rechteckigen Umriß. Die Vorder- (34) und die Rückseite (35) sind ebene, feinbearbeitete Flächen. An der Vorderseite sind die beiden Proportionalmagnete (91) und (121) angeflanscht. Ihnen gegenüber sitzen in der Rückseite (35) die Verschlußschrauben (114) und (157) für die Bohrungen (41, 42) und (44). Die beiden anderen Seitenflächen (38) und (39) haben Ausbuchtungen, die um die Befestigungsbohrungen (69, 69') gebildet sind. Außerdem weist die in Figur 3 oben liegende Seitenfläche (38) einen Stutzen zur Aufnahme des Pumpenanschlusses (49) auf.The side surfaces aligned perpendicular to the cut surface (34, 35, 38, 39) each have a rectangular outline. The front (34) and the back (35) are flat, finely machined Surfaces. On the front are the two proportional magnets (91) and (121) flanged. Sitting opposite you in the Back (35) the locking screws (114) and (157) for the Bores (41, 42) and (44). The other two faces (38) and (39) have bulges around the mounting holes (69, 69 ') are formed. In addition, the one in FIG top side surface (38) a nozzle for receiving the Pump connection (49).

Nach Figur 2 geht der mit einem Innengewinde versehene Pumpenanschluß (49) im Gehäuse (30) in einen Zulaufringkanal (93) über. Der Ringkanal (93) durchdringt eine zylindrische Durchgangsbohrung (41), die sich von der Vorderseite (34) bis zur Rückseite (35) erstreckt. Im linken Bereich der Durchgangsbohrung (41) sitzt der Längsschieber (97) des Hebenmoduls (90). Dort treffen auf die Durchgangsbohrung (41) drei weitere Kanäle (94, 95, 96). Der mittlere (94) ist ein Rücklaufringkanal, der auf den in die Unterseite (33) ausgebildeten Rücklaufkanal (65) mündet. Beidseits von diesem Rücklaufringkanal (94) befinden sich die beiden Ringkanäle (95) und (96), an die die beiden Kanalabschnitte (57) und (58) angeschlossen sind, die sich wiederum zum Verbindungskanal (55) vereinigen.According to Figure 2, the pump connection is provided with an internal thread (49) in the housing (30) into an inlet ring channel (93). The ring channel (93) penetrates a cylindrical through hole (41) extending from the front (34) to the back (35) extends. In the left area of the through hole (41) the longitudinal slide (97) of the lifting module (90) is seated. There, three more meet the through hole (41) Channels (94, 95, 96). The middle one (94) is a return ring channel, the on the return channel formed in the bottom (33) (65) opens. On both sides of this return ring channel (94) are the two ring channels (95) and (96) to which the two channel sections (57) and (58) are connected, the in turn unite to form the connecting channel (55).

Der Längsschieber (97) des Hebenmoduls (90) verbindet entweder - im unbetätigten Zustand - den Verbindungskanal (55) mit dem Rücklaufringkanal (94) oder - im betätigten Zustand - mit dem Zulaufringkanal (93) hinter dem Pumpenanschluß (49). Dazu weist die zylindrische Außenkontur des Längsschiebers (97) die beiden Ringnuten (99) und (100) auf. Die rechte Ringnut (100), die u.a. den Zulaufringkanal (93) mit dem Ringkanal (96) verbinden kann, geht im Bereich ihres rechten Wellenbundes in Feinsteuerkerben (103) über, die im Zusammenhang mit der Druckwaage (70) die Funktion einer Meßdrossel haben. Die Öffnungsquerschnitte der Feinsteuerkerben (103) verringern sich in Richtung Zulaufringkanal (93), ohne ihn jedoch - bei unbestromtem Proportionalmagnet (91) - zu erreichen. Die Feinsteuerkerben (103) sind hier beispielsweise Rundkerben.The longitudinal slide (97) of the lifting module (90) connects either - in the unactuated state - the connecting channel (55) with the Return ring channel (94) or - when actuated - with the Inlet ring channel (93) behind the pump connection (49). To do so the cylindrical outer contour of the longitudinal slide (97) the two Ring grooves (99) and (100). The right ring groove (100), which i.a. can connect the inlet ring channel (93) to the ring channel (96), goes into fine control notches in the area of their right shaft collar (103), which in connection with the pressure compensator (70) Function as a measuring choke. The opening cross sections of the Fine control notches (103) decrease in the direction of the feed ring channel (93), but without it - with de-energized proportional magnet (91) - to achieve. The fine control notches (103) are here for example round notches.

Die linke Wandung der rechten Ringnut (100) bildet eine von zwei Steuerkanten (101) und (102) am Längsschieber (97) die den Rücklauf vom Verbindungskanal (55) in den Rücklaufringkanal (94) steuert. Die andere Steuerkante (101) ist die linke Wandung der linken Ringnut (99). Sie öffnet oder verschließt den Weg vom Kanalabschnitt (57) zum Rücklaufringkanal (94). Die rechte Wandung der Ringnut (99) befindet sich über den gesamten Hub des Längsschiebers (97) im Bereich des Rücklaufringkanals (94) und verschließt diesen nicht.The left wall of the right annular groove (100) forms one of two Control edges (101) and (102) on the longitudinal slide (97) the return from the connecting channel (55) into the return ring channel (94) controls. The other control edge (101) is the left wall of the left ring groove (99). It opens or closes the path from the canal section (57) to the return ring channel (94). The right wall the annular groove (99) is located over the entire stroke of the longitudinal slide (97) in the area of the return ring channel (94) and closes not this one.

Am linken Rand der Außenkontur des Längsschiebers (97) befindet sich im Bereich des Dichtrings zwischen dem Proportionalmagnet (91) und dem Gehäuse (30) ein Einstich. Unterhalb dieses Einstichs weist der Längsschieber eine zylindrische Vertiefung (104) auf, an deren Grund der Ankerstößel (92) des Proportionalmagneten (91) ansteht.Located on the left edge of the outer contour of the longitudinal slide (97) in the area of the sealing ring between the proportional magnet (91) and the housing (30) a puncture. Below this The longitudinal slide has a cylindrical recess (104), at the bottom of which the armature plunger (92) of the proportional magnet (91) is pending.

Von der rechten Stirnseite (98) her ist der Längsschieber (97) gestuft aufgebohrt. Der rechte Bereich der Stufenbohrung (105) dient der Führung der Rückstellfeder (108). Der linke Bereich hat einen kleineren Durchmesser und verbindet über eine schräg verlaufende Ausgleichsbohrung (106) die Stufenbohrung (105) mit der Vertiefung (104). Der Übergang vom rechten zum linken Bereich der Stufenbohrung bildet ein ebener Gehäusebund, auf dem sich die Rückstellfeder (108) abstützt. The longitudinal slide (97) is from the right end face (98) bored in stages. The right area of the stepped bore (105) serves to guide the return spring (108). The left area has a smaller diameter and connects at an angle running compensation bore (106) with the stepped bore (105) the recess (104). The transition from the right to the left area the stepped hole forms a flat collar on which the return spring (108) is supported.

Das andere Ende der Rückstellfeder (108) liegt an einem abgestuften Federteller (109) an. Der Federteller (109) ist im Querschnitt sternförmig ausgebildet, um für den Druckausgleich am Längsschieber (97) das Druckmittel ungedrosselt passieren zu lassen. Er sitzt auf einer Stange (110), die sich nach rechts zentral in der Durchgangsbohrung (41) erstreckt. Die Stange (110) ragt in einen rechts neben dem Längsschieber (97) angeordneten, topfförmigen Druckwaagenkolben (80) hinein, um dort auf einen Gewindestift (111) zu stoßen. Hierbei ist die Stange (110) in einer Bohrung in der Stirnseite (81) des Druckwaagenkolbens (80) dichtgleitend geführt. Da der in Längsrichtung ortsfeste Federteller (109) zusammen mit der Stange (110) in den zwei längsbeweglichen Ventilteilen (97) und (80) gelagert ist, ist die äußere Hüllkontur des Federtellers (109) ballig ausgeführt. Auf diese Weise wird ein gegenseitiges Verkanten zwischen dem Längsschieber (97) und der Stange (110) vermieden.The other end of the return spring (108) lies on a stepped Spring plate (109). The spring plate (109) is in cross section formed in a star shape for pressure equalization on Longitudinal slide (97) pass the pressure medium unthrottled to let. He is sitting on a pole (110) that faces right extends centrally in the through hole (41). The Rod (110) protrudes into a right of the longitudinal slide (97) arranged, pot-shaped pressure compensator piston (80) into encounter a grub screw (111) there. Here is the Rod (110) in a bore in the end face (81) of the pressure compensator piston (80) guided tightly. Since the lengthways stationary spring plate (109) together with the rod (110) stored in the two longitudinally movable valve parts (97) and (80) is, the outer envelope contour of the spring plate (109) is spherical executed. In this way, mutual tilting avoided between the longitudinal slide (97) and the rod (110).

Der Gewindestift (111) erstreckt sich in der Verlängerung der Stange (110) und endet in der Verschlußschraube (114). Um den Gewindestift (111) in der Längsrichtung verstellen zu können, weist die Verschlußschraube (114) ein Innengewinde auf, in dem dieser eingeschraubt sitzt. Um die Baulänge der Steuervorrichtung kurz zu gestalten, hat der Kopf der Verschlußschraube (114) eine zylindrische Vertiefung, die der Aufnahme einer Kontermutter (112) dient. Zum Verstellen und Kontern des Gewindestifts (111), weist dieser an seinem äußeren freien Ende einen Innensechskant auf.The threaded pin (111) extends in the extension of the Rod (110) and ends in the screw plug (114). To the To be able to adjust the set screw (111) in the longitudinal direction, the screw plug (114) has an internal thread in which this is screwed in. To the overall length of the control device to make it short, the head of the locking screw (114) a cylindrical recess that accommodates a lock nut (112) serves. For adjusting and locking the setscrew (111), it has one at its outer free end Hexagon on.

Die Durchgangsbohrung (41) geht an ihrem rechten Ende in eine Verschlußschraubenbohrung (42) über. Im Innengewinde der Bohrung (42) ist die Verschlußschraube (114) befestigt. Ein im Bereich zwischen Kopf und Gewinde sitzender Dichtring (118) dichtet die Verschlußschraubenbohrung (42) nach außen ab. The through hole (41) goes into one at its right end Screw hole (42) over. In the internal thread of the bore (42) the screw plug (114) is attached. One in the area sealing ring (118) between head and thread seals the screw plug bore (42) from the outside.

In der Durchgangsbohrung (41) sitzt zwischen der Verstellschraube (114) und dem Längsschieber (97) dichtgleitend der Druckwaagenkolben (80). Letzterer hat eine zylindrische Außenkontur, die an ihrem rechten Ende einen Halbrundeinstich (84) aufweist, in den ein Federring (89) eingesetzt ist. Der Federring (89) liegt - beispielsweise bei druckmittelfreier Steuervorrichtung - an einem als Anschlag dienenden inneren Gehäusebund an, der zwischen der Durchgangsbohrung (41) und der im Durchmesser größeren Verschlußschraubenbohrung (42) gebildet ist. Den rechten Anschlag für den Druckwaagenkolben (80) bildet die Verschlußschraube (114). Am linken Rand der Außenkontur befinden sich mehrere auf dem Umfang verteilte Feinsteuerkerben (83), die von der linken Stirnseite (81) her in den Druckwaagenkolben (80) eingearbeitet sind.In the through hole (41) sits between the adjusting screw (114) and the longitudinal slide (97) tightly sliding the Pressure balance piston (80). The latter has a cylindrical outer contour, which has a semicircular cut at its right end (84) has, in which a spring washer (89) is inserted. The spring ring (89) lies - for example in the case of a control device free of pressure medium - On an inner housing collar serving as a stop to that between the through hole (41) and in Diameter larger screw hole (42) formed is. The right stop for the pressure compensator piston (80) forms the screw plug (114). Located on the left edge of the outer contour several fine notches distributed around the circumference (83) into the pressure compensator piston from the left end (81) (80) are incorporated.

Hinter dem Halbrundeinstich (84) ist der Druckwaagenkolben (80) angefast. Im Bereich vor dem Federring (89) trägt er eine Reihe von Entlastungsnuten.The pressure compensator piston (80) is behind the semicircular groove (84) chamfered. In the area in front of the spring washer (89) it carries a row of relief grooves.

In den Druckwaagenkolben (80) ist von seiner rechten Stirnseite her eine Führungsbohrung (87) zur Aufnahme der Regelfeder (88) eingearbeitet. Die Führungsbohrung (87) ist in ihrem Grund verengt, um die Regelfeder (88) radial zu fixieren. Eine Bohrung (115) mit einer vergleichbaren Kontur befindet sich auch in der linken Stirnseite der Verstellschraube (114).In the pressure compensator piston (80) is from its right end forth a guide bore (87) for receiving the control spring (88) incorporated. The bottom of the guide bore (87) is narrowed, to fix the control spring (88) radially. A hole (115) with a comparable contour is also in the left end of the adjusting screw (114).

Im Bereich der Druckwaage befinden sich im Gehäuse (30) zwei Kanäle (71) und (74). Benachbart zum Zulaufringkanal (93) liegt ein Rücklaufringkanal (71). Die Verbindung vom Zulaufringkanal (93) zum Rücklaufringkanal (71) ist beispielsweise beim Heben einer Last - nach dem Erreichen des Lastdruckes - durch den Druckwaagenkolben (80) mehr oder weniger vollständig geschlossen, während sie bei Neutralumlauf voll geöffnet ist.In the area of the pressure compensator there are two in the housing (30) Channels (71) and (74). Adjacent to the inlet ring channel (93) a return ring channel (71). The connection from the inlet ring channel (93) to the return ring channel (71) is, for example, when lifting a load - after reaching the load pressure - by the Pressure balance piston (80) more or less completely closed, while it is fully open in neutral circulation.

Zwischen dem Rücklaufringkanal (71) und der Verstellschraube (114) ist ein Lastmeldekanal (74) angeordnet. Er steht mit dem Kanalabschnitt (58) über eine zur Durchgangsbohrung (41) parallele Lastmeldebohrung (63) in Verbindung.Between the return ring channel (71) and the adjusting screw (114) a load reporting channel (74) is arranged. He's standing with the channel section (58) via a through hole (41) parallel load detection hole (63) in connection.

Auf der Höhe der Lastmeldebohrung (63) liegt die Stelle, an der sich der Verbindungskanal (55) in die beiden Kanalabschnitte (57) und (58) aufteilt. Innerhalb der in Figur 2 und 4 dargestellten Schnittfläche haben die beiden Kanalabschnitte zur Verbindung der beiden Ringkanäle (95) und (96) eine strömungsgünstige, u-förmige Kontur. Am Verbindungsabschnitt zwischen den beiden U-Schenkeln vereinigen sich die Kanalabschnitte (57) und (58) mit dem Verbindungskanal (55). Letzterer führt annähernd senkrecht in den Bereich des Senkenmoduls (120).At the level of the load reporting hole (63) is the point at which the connecting channel (55) into the two channel sections (57) and (58). Within the in Figures 2 and 4 Cut area shown have the two channel sections Connection of the two ring channels (95) and (96) a streamlined, u-shaped contour. At the connecting section between the the two U-legs unite the channel sections (57) and (58) with the connecting channel (55). The latter leads approximately vertically into the area of the sink module (120).

Das Senkenmodul (120) hat eine das Gehäuse (30) durchquerende Stufenbohrung (44), die parallel zur Durchgangsbohrung (41) des Hebenmoduls (90) ausgerichtet ist. Die Stufenbohrung (44) ist links - wie auch im Hebenmodul - durch den Proportionalmagnet (121) und rechts durch eine Verschlußschraube (157) mit Innensechskant und zwischen Kopf und Gewinde angeordnetem Dichtring (158) druckmitteldicht verschlossen.The sink module (120) has an end that crosses the housing (30) Stepped bore (44) parallel to the through bore (41) of the Lifting module (90) is aligned. The stepped bore (44) is left - as in the lifting module - through the proportional magnet (121) and on the right through a screw plug (157) with hexagon socket and sealing ring arranged between the head and the thread (158) sealed pressure-tight.

Im mittleren Bereich der Stufenbohrung (44) sitzt eine Ventilbüchse (130), die zwei ineinandergeschachtelte Längsschieber aufnimmt. Die Ventilbüchse (130) ist in der Stufenbohrung (44) zwischen einem linken Gehäusebund (124) und einem rechts angeordneten Schraubring (156) mit einem innenliegenden, durchgehenden Innensechskant axial gesichert. Der rechte Bereich der Stufenbohrung (44) ist dazu mit einem Innengewinde (129) versehen.A valve sleeve is located in the central area of the stepped bore (44) (130), the two nested longitudinal slides records. The valve sleeve (130) is in the stepped bore (44) between a left housing collar (124) and a right one Screw ring (156) with an internal, continuous Hexagon socket secured axially. The right area of the stepped bore (44) is provided with an internal thread (129).

Die Ventilbüchse (130) wird von einem Verbraucherringkanal (125) umgeben, der mit dem in Figur 3 gezeigten Verbraucheranschluß (50) hydraulisch in Verbindung steht. Links neben der Ventilbüchse (130) sitzt eine Einstellschraube (150) in dem Innengewinde (128). Im Bereich dieser Einstellschraube (150) mündet der Verbindungskanal (55) in die Stufenbohrung (44). The valve sleeve (130) is supported by a consumer ring channel (125) surrounded, with the consumer connection shown in Figure 3 (50) is hydraulically connected. Left of the Valve sleeve (130) has an adjusting screw (150) in the internal thread (128). In the area of this adjusting screw (150) opens the connecting channel (55) in the stepped bore (44).

Die Einstellschraube (150) - mit Ausnahme einer auf ihr angeordneten Verzahnung (151) - und die Ventilbüchse (130) mit ihren beiden Längsschiebern ist aus der DE 41 40 604 A1 bekannt. In Figur 4 sind diese Bauteile geschnitten gezeigt.The adjusting screw (150) - with the exception of one arranged on it Toothing (151) - and the valve sleeve (130) with their Both longitudinal slides are known from DE 41 40 604 A1. In FIG. 4 shows these components in section.

Das Senkenmodul (120) ist in Sperrstellung dargestellt. Das Druckmittel, das am Verbraucheranschluß (50), bzw. in Figur 4 am Anschluß (51), und damit am Verbraucherringkanal (125) ansteht, kann nicht in den Verbindungskanal (55) strömen. Der in der Ventilbüchse (130) direkt gelagerte Längsschieber, der Hauptsteuerschieber (140), steht mit seinem Hauptventilkegel (141) am Hauptventilsitz (132) der Ventilbüchse (130) an. Seine - an seinem linken Ende angeordneten - Hauptsteuerkerben (142) liegen verdeckt unter dem Zylindersitz (133) neben einem Ringraum (134). Um den Hauptsteuerschieber (140) auf dem Hauptventilsitz (132) zu halten, steht auf seiner rechten Stirnseite in einem Druckraum (135) Druckmittel an. Dorthin gelangt das Druckmittel aus dem Verbraucherringkanal (125) über Radialbohrungen (131) in der Ventilbüchse (130), sowie im Hauptsteuerschieber über eine Drosselbohrung (144) und eine daran anschließende Längsbohrung (145). Die Längsbohrung (145) durchdringt mit ihrem Bohrungsgrund eine Steuernut (143). Die Anpreßkraft wird vermindert durch die entgegengesetzt wirkende Kraft aufgrund des im Bereich der Außenkontur des Hauptsteuerschiebers (140) zwischen Hauptventilkegel (141) und Entlastungsnuten anstehenden Druckes.The sink module (120) is shown in the locked position. The Pressure medium on the consumer connection (50), or in Figure 4 on Connection (51), and thus on the consumer ring channel (125), cannot flow into the connecting channel (55). The one in the valve sleeve (130) directly mounted longitudinal slide, the main control slide (140) stands with its main valve cone (141) on Main valve seat (132) of the valve sleeve (130). His - on his arranged on the left end - main control notches (142) are located hidden under the cylinder seat (133) next to an annulus (134). Around the main spool (140) on the main valve seat To hold (132) is in on his right face a pressure chamber (135) to pressure medium. The pressure medium gets there from the consumer ring channel (125) via radial bores (131) in the valve sleeve (130) and in the main control spool via a throttle bore (144) and an adjoining one Longitudinal bore (145). The longitudinal bore (145) penetrates with a control groove (143) at the bottom of the hole. The contact pressure is reduced by the opposing force due to the in the area of the outer contour of the main control spool (140) between Main valve cone (141) and relief grooves are present Pressure.

Das Senkenmodul (120) öffnet mit der Bestromung des Proportionalmagneten (121). Sein Ankerstößel (122) schiebt den inneren Längsschieber, einen Vorsteuerschieber (147) geringfügig nach rechts. Dadurch gelangen seine Vorsteuerkerben (149) unter die Steuernut (143) des Hauptsteuerschiebers (140). Gleichzeitig hebt sein weiter links angeordneter Ventilkegel (148) von seinem im Hauptsteuerschieber (140) korrespondierenden Ventilsitz (146) ab. Der Druckraum (135) steht nun über die Längsbohrung (145), die Steuernut (143), die Vorsteuerkerben (149), den Ventilsitz (146) und den Verbindungskanal (55) mit dem Rücklaufringkanal (94) in Verbindung. In Abhängigkeit vom öffnungsquerschnitt der Vorsteuerkerben (149) sinkt der Druck im Druckraum (135). Der dortige Druck stellt sich entsprechend dem Verhältnis des Querschnitts der Drosselbohrung (144) und dem Öffnungsquerschnitt der Vorsteuerkerben (149) ein. Fällt bei entsprechend weit nach rechts geschobenem Vorsteuerschieber (147) der Druck im Druckraum (135) so weit, daß die vom Druckmittel auf den Hauptsteuerschieber (140) im Bereich unterhalb der Radialbohrungen (131) nach rechts ausgeübte Kraft überwiegt, wird der Hauptsteuerschieber (140) ebenfalls nach rechts verschoben. Der Hauptventilkegel (141) hebt vom Hauptventilsitz (132) ab und die Hauptsteuerkerben (142) gelangen in den Bereich des Ringraumes (134). Das Druckmittel strömt, vom Verbraucher kommend, zwischen der Ventilbüchse (130) und dem Hauptsteuerschieber (140) in Richtung Verbindungskanal (55). Der Hauptsteuerschieber (140) eilt durch seine Öffnungsbewegung dem Vorsteuerschieber (147) nach, wodurch der Öffnungsquerschnitt an den Vorsteuerkerben (149) kleiner wird. Damit kann sich im Druckraum (135) über die Drosselbohrung (144) ein höherer Druck aufbauen. Folglich wird die Öffnungsbewegung des Hauptsteuerschiebers (140) gebremst, bis sich ein Gleichgewichtszustand einstellt.The sink module (120) opens when the proportional solenoid is energized (121). Its anchor plunger (122) pushes the inner one Longitudinal spool, a pilot spool (147) slightly behind right. As a result, his input tax notches (149) get under the Control groove (143) of the main control spool (140). At the same time lifts his valve cone (148) further left from his in the main control slide (140) corresponding valve seat (146) from. The pressure chamber (135) now stands over the longitudinal bore (145), the control groove (143), the pilot control notches (149), the valve seat (146) and the connecting channel (55) with the return ring channel (94) in conjunction. Depending on the opening cross-section the pilot control notch (149) the pressure in the pressure chamber (135) drops. The pressure there arises according to the ratio of the Cross section of the throttle bore (144) and the opening cross section the pilot notches (149). Falls accordingly the pilot spool (147) pushed far to the right is the pressure in the pressure chamber (135) so far that the pressure medium on the Main control spool (140) in the area below the radial bores (131) the force exerted to the right predominates, the Main control spool (140) also moved to the right. The Main valve plug (141) lifts off the main valve seat (132) and the Main control notches (142) reach the area of the annulus (134). Coming from the consumer, the pressure medium flows between the valve sleeve (130) and the main control spool (140) towards the connecting channel (55). The main spool (140) hurries through its opening movement to the pilot spool (147) after, whereby the opening cross-section at the pilot notches (149) becomes smaller. This can over in the pressure chamber (135) the throttle bore (144) build up a higher pressure. Hence the opening movement of the main control slide (140) is braked, until a state of equilibrium is established.

Bewegt sich der Ankerstößel (122) nach links, folgt ihm aufgrund einer in der Einstellschraube (150) integrierten Rückstellfeder (155) der Vorsteuerschieber (147). Die Rückstellfeder (155) stützt sich am Vorsteuerschieber (147) und an der Einstellschraube (150) ab. Bei der Bewegung des Vorsteuerschiebers (147) werden die Vorsteuerkerben (149) verschlossen. Der Druck im Druckraum (135) steigt. Der Hauptventilkegel (141) legt sich am Hauptventilsitz (132) an. Das Senkenmodul (120) sperrt. Das Proportionalwegeventilelement (120) arbeitet somit nach Art einer Folgesteuerung. If the anchor plunger (122) moves to the left, it follows due to a return spring integrated in the adjusting screw (150) (155) the pilot spool (147). The return spring (155) is supported by the pilot spool (147) and the adjusting screw (150). When moving the spool (147) the pilot notches (149) are closed. The pressure in Pressure chamber (135) increases. The main valve plug (141) lies on Main valve seat (132). The sink module (120) locks. The proportional directional valve element (120) thus works like a Sequence control.

Um die Vorspannkraft der Rückstellfeder (155) bei montierter Steuervorrichtung einstellen zu können, weist die Einstellschraube (150) im mittleren Bereich ihrer Außenkontur eine Schrägverzahnung (151) auf, in die zumindest zeitweise die Verzahnung einer Einstellschnecke eingreift. Die Einstellschnecke sitzt dazu in einer Einstellbohrung (68), die sich hier von der Vorderseite (34) bis in die Stufenbohrung (44) erstreckt und den Verbindungskanal (55) tangiert. Die Einstellschnecke kann mit Hilfe einer Einstellspindel, deren freies Ende aus dem Gehäuse (30) ragt, oder einem Spezialwerkzeug, das zeitweise mit der Einstellschnecke stirnseitig gekuppelt werden kann, in Drehung versetzt werden. Je nach Drehrichtung der Einstellspindel bzw. der Einstellschnecke wird die Einstellschraube (150) in dem Innengewinde (128) nach rechts oder links geschraubt. Die Länge des Verstellbereiches entspricht weitgehend der Breite der Verzahnung (151) der Einstellschraube (150).To the preload force of the return spring (155) when the To be able to adjust the control device has the adjusting screw (150) one in the middle area of its outer contour Helical toothing (151) into which the toothing is at least temporarily engages an adjusting screw. The adjusting screw sits in an adjustment hole (68), which is here from the Front (34) extends into the stepped bore (44) and the Connection channel (55) tangent. The adjusting screw can be used with Using an adjusting spindle, the free end of which from the housing (30) protrudes, or a special tool that sometimes comes with the adjustment screw can be coupled on the face, in rotation be transferred. Depending on the direction of rotation of the adjusting spindle the adjusting screw (150) in the Internal thread (128) screwed to the right or left. The length the adjustment range largely corresponds to the width of the toothing (151) the adjusting screw (150).

Das Senkenmodul (120), das in der Steuervorrichtung während des Hebens der Last die Funktion eines Rückschlagventils hat, ist aufgrund der hohen Anforderungen an die Feinsteuerbarkeit beim Senken der Last durch die Drosselbohrung (144) relativ stark gedämpft. Diese Dämpfung bremst die Schließbewegung bei der Rückschlagfunktion. Zur Beschleunigung der Schließbewegung beim Lastheben kann der Drosselbohrung (144) ein Sitzventil (160) parallel geschaltet werden.The sink module (120), which is in the control device during the Lifting the load has the function of a check valve due to the high demands on the fine controllability of the Lowering of the load damped relatively strongly by the throttle bore (144). This damping slows down the closing movement during the kickback function. To accelerate the closing movement when The throttle bore (144) can be lifted by a seat valve (160) can be connected in parallel.

In Figur 4 ist rechts neben der Ventilbüchse (130) anstelle des Schraubringes (156), vgl. Figur 2, dieses Sitzventil (160) angeordnet. Das Sitzventil hat einen scheibenförmigen Körper mit einem angeformten Sechskant. Der zylindrische Teil seiner Außenkontur trägt ein Gewinde mit eingesetztem Dichtring, mit dem es in den rechten Bereich der Stufenbohrung (44) eingeschraubt ist. Wie der Schraubring (156) aus Figur 2 fixiert es die Ventilbüchse (130). Zwischen dem Boden des Sitzventils, dem rechten Randbereich der Außenkontur der Ventilbüchse (130) und dem Gehäuse (30) ist ein ringförmiger Kanal (161) ausgebildet. Der Kanal (161) steht über eine Schrägbohrung (162) mit dem hier an der Seitenfläche (39) des Gehäuses (30) stutzenförmig angeformten Verbraucheranschlusses (51) in Verbindung.In Figure 4 is to the right of the valve sleeve (130) instead of Screw ring (156), cf. Figure 2, this seat valve (160) arranged. The seat valve has a disk-shaped body with a molded hexagon. The cylindrical part of its outer contour carries a thread with an inserted sealing ring with which it is screwed into the right area of the stepped bore (44). Like the screw ring (156) from FIG. 2, it fixes the valve sleeve (130). Between the bottom of the seat valve, the right one Edge area of the outer contour of the valve sleeve (130) and the housing (30) an annular channel (161) is formed. The channel (161) is at an inclined hole (162) with this the side surface (39) of the housing (30) formed in a nozzle shape Consumer connection (51) in connection.

Das Sitzventil (160) weist eine Längsbohrung (165) auf, an der zur Ventilbüchse (130) hin ein kegelmantelförmiger Ventilsitz ausgebildet ist. Im rechten Teil der Längsbohrung (165) ist ein Schieberkolben (164) gelagert und geführt. Der rechte Abschnitt des Schieberkolbens (164) hat eine zylindrische Form. Daran schließt sich links ein Ventilteller an, der über eine Taille mit dem zylindrischen Abschnitt verbunden ist. Ein Hub des Schieberkolbens (164) nach rechts wird durch den Kontakt zwischen Ventilteller und Ventilsitz begrenzt, während ein Hub nach links durch das Anschlagen eines auf dem Schieberkolben sitzenden Sicherungsrings an der Stirnseite des Sechskants beendet wird. Von der Längsbohrung (165) gehen im Bereich der Taille des Schieberkolbens (164) annähernd sternförmig mehrere Bohrungen (166) weg. Sie enden im Übergangsbereich von Außengewinde und Boden des Sitzventils. Des weiteren ist im Bereich des Sechskants von der Längsbohrung aus eine Ringnut zur Aufnahme eines Dichtrings (167) eingearbeitet. In der Stufenbohrung (44) befindet sich zwischen dem Sitzventil (160) und der Verschlußschraube (157) ein Ringkanal (163), der mit der Lastmeldebohrung (63) in Verbindung steht.The seat valve (160) has a longitudinal bore (165) on which a valve seat in the shape of a cone towards the valve sleeve (130) is trained. In the right part of the longitudinal bore (165) is a Sliding piston (164) stored and guided. The right section the slide piston (164) has a cylindrical shape. That is followed by a valve plate on the left, which has a waist is connected to the cylindrical portion. A hub of the Slide piston (164) to the right is through the contact between Valve disc and valve seat limited during one stroke on the left by striking one sitting on the slide piston Circlip terminated on the front of the hexagon becomes. From the longitudinal bore (165) go in the area of the waist of the Sliding piston (164) approximately star-shaped several holes (166) gone. They end in the transition area from the external thread and bottom of the seat valve. Furthermore, in the area of Hexagon from the longitudinal bore an annular groove for receiving a sealing ring (167) incorporated. In the stepped bore (44) is located between the seat valve (160) and the screw plug (157) an annular channel (163) that connects to the load signaling hole (63) communicates.

Beim Heben der Last strömt bei bestromtem Proportionalmagnet (91), vgl. auch Figur 2, Druckmittel über den Pumpenanschluß (49), den Zulaufringkanal (93), den Längsschieber (97), und den Verbindungskanal (55) vor die Längsschieber (140) und (147) des Senkenmoduls (120). Um ein ruckfreies Anfahren der Last zu ermöglichen, öffnet der Längsschieber (97) zunächst nur über seine Feinsteuerkerben (103). Sie bilden im Bezug auf die Druckwaage (70) die Meßdrossel. Das Druckmittel fließt auf dem Weg zum Senkenmodul (120) über die Lastmeldebohrung (63) und den Lastmeldekanal (74) auf die Rückseite des Druckwaagenkolbens (80). Folglich bewegt sich dieser nach links und verringert zunehmend den Druckmittelstrom vom Zulaufringkanal (93) zum Rücklaufringkanal (71), bis der am Verbraucheranschluß (50) bzw. (51) anstehende Lastdruck erreicht ist. Beim Heben wird die Rückschlagventilfunktion des Proportionalwegeventilelements (120) ausgenutzt, um die Last abzusichern.When lifting the load, the proportional magnet is energized (91), cf. also Figure 2, pressure medium via the pump connection (49), the inlet ring channel (93), the longitudinal slide (97), and the connecting channel (55) in front of the longitudinal slide (140) and (147) of the sink module (120). To start the The longitudinal slide (97) initially only opens the load on its fine tax notches (103). They form in relation to the Pressure compensator (70) the measuring throttle. The pressure medium flows on the Path to the sink module (120) via the load reporting hole (63) and the Load signaling channel (74) on the back of the pressure compensator piston (80). As a result, it moves to the left and decreases increasing the pressure medium flow from the inlet ring channel (93) to Return ring channel (71) until the on the consumer connection (50) or (51) pending load pressure is reached. When lifting the Check valve function of the proportional directional valve element (120) used to secure the load.

Hierbei liegt das durch die Druckwaage (70) erzeugte Regeldruckgefälle bei dem Schließvorgang nicht nur an den Feinsteuerkerben (103), sondern auch beidseits des Druckwaagenkolbens (80) an. Das dabei vorhandene geringe Druckgefälle, sowie der geringe Volumenstrom, der ggf. durch eine zur Stabilsierung der Bewegung des Druckwaagenkolbens (80) in der Lastmeldebohrung (63) integrierten Drosselstelle zusätzlich verringert wird, bedingt eine langsame Schließbewegung des Druckwaagenkolbens (80). Zur Beschleunigung der Schließbewegung kann beispielsweise kurzzeitig der Proportionalmagnet (121) des Senkenmoduls bestromt werden. In Figur 5 wird dazu die Bestromung der beiden Proportionalmagnete (91) und (121) bei einem Heben und anschließenden Senken der Last in vereinfachter Darstellung gezeigt. Auf der Abszisse ist die Zeit t aufgetragen. Auf dem positiven Ast der Ordinate ist der Strom I91 für den Proportionalmagnet (91) und auf dem negativen Ast der Strom I121 für den Proportionalmagnet (121) dargestellt. Die Last wird über den Zeitraum t91 gehoben und über den Zeitraum t121 abgesenkt. Während des Hebevorgangs wird innerhalb des Zeitraums t91 nach der Zeit t1, in der der Längsschieber (97), vgl. Figur 2, soweit nach rechts geschoben worden ist, daß die Verbindungen von den Kanalabschnitten (57) und (58) zum Rücklaufringkanal (94) gesperrt sind, der Proportionalmagnet (121) für die Zeit t2 bestromt. Dadurch strömt vom Verbraucheranschluß (50) bzw. (51) Druckmittel unter Lastdruck über den Hauptsteuerschieber (140) und den Verbindungskanal (55), die Lastmeldebohrung (63) und den Lastmeldekanal (74) auf die Rückseite des Druckwaagenkolbens (80). Der dabei in Bewegung gesetzte große Volumenstrom läßt den Druckwaagenkolben (80) den Rücklaufringkanal (71) schnell sperren.In this case, the control pressure drop generated by the pressure compensator (70) during the closing process lies not only on the fine control notches (103), but also on both sides of the pressure compensator piston (80). The low pressure drop that is present, as well as the low volume flow, which may be additionally reduced by a throttle point integrated in the load reporting bore (63) to stabilize the movement of the pressure compensator piston (80), necessitates a slow closing movement of the pressure compensator piston (80). To accelerate the closing movement, the proportional magnet (121) of the sink module can be energized briefly, for example. For this purpose, FIG. 5 shows a simplified representation of the energization of the two proportional magnets (91) and (121) when the load is raised and then lowered. The time t is plotted on the abscissa. The current I 91 for the proportional magnet (91) is shown on the positive branch of the ordinate and the current I 121 for the proportional magnet (121) is shown on the negative branch. The load is raised over the period t 91 and lowered over the period t 121 . During the lifting process, within the period t 91 after the time t 1 in which the longitudinal slide (97), cf. Figure 2, as far as has been pushed to the right that the connections from the channel sections (57) and (58) to the return ring channel (94) are blocked, the proportional magnet (121) energized for the time t 2 . As a result, pressure medium flows from the consumer connection (50) or (51) under load pressure via the main control spool (140) and the connecting channel (55), the load signaling bore (63) and the load signaling channel (74) to the rear of the pressure compensator piston (80). The large volume flow set in motion causes the pressure compensator piston (80) to quickly block the return ring channel (71).

Zum Beenden des Hebens der Last wird der Proportionalmagnet (91) abgeschaltet. Der Längsschieber (97) will sich aufgrund der Rückstellfeder (108) nach links bewegen, um den Weg zwischen dem Zulaufringkanal (93) und dem Kanalabschnitt (58) zu sperren. Das Sperren des Längsschiebers (97) erfolgt bei ungünstigen Bedingungen aber vor dem Sperren des Hauptsteuerschiebers (140) des wegen der Feinsteuerung stark gedämpften Senkenmoduls (120). Bei einem zu langsamen Schließen des Hauptsteuerschiebers (140) fließt vom Verbraucheranschluß (51) das Druckmittel zurück in Richtung Zulaufringkanal (93). Dabei können die Strömungskräfte den Längsschieber (97) beim Schließen stören. Dieses Problem beseitigt das Sitzventil (160). Bei der Hebenfunktion der Steuervorrichtung, wenn also das Senkenmodul (120) als Rückschlagventil arbeitet, ist der Druck in Durchflußrichtung gesehen vor dem Senkenmodul (120) größer als hinter ihm. Aufgrund dieses Druckunterschieds öffnet das Sitzventil (160), das zusätzlich parallel zur Steueröldrossel (144) geschaltet ist und beim Heben der Last den Drosselquerschnitt vergrößert. Folglich schließt der Hauptsteuerschieber (140) nahezu ungedämpft.The proportional magnet (91) is used to stop lifting the load. switched off. The longitudinal slide (97) wants to due to the Move the return spring (108) to the left to find the path between the Block inlet ring channel (93) and the channel section (58). The The longitudinal slide (97) is locked in unfavorable conditions but before locking the main spool (140) of the because of the fine control of the damped sink module (120). At too slow closing of the main control slide (140) the pressure medium flows back into the consumer connection (51) In the direction of the inlet ring channel (93). The flow forces disrupt the longitudinal slide (97) when closing. Fixed this problem the poppet valve (160). With the lifting function of the control device, if so the sink module (120) as a check valve works, the pressure is seen in the flow direction before Sink module (120) larger than behind it. Because of this pressure difference opens the seat valve (160), which is also parallel to the control oil throttle (144) and when lifting the Load increases the throttle cross section. Consequently, the Main control spool (140) almost undamped.

Bei dieser Steuervorrichtung besteht aufgrund der parallelen Anordnung der Module (90) und (120) die Möglichkeit, vor den rückseitigen Enden der beiden Proportionalmagneten (91) und (121) ein Handbedienungselement (25) beispielsweise in einem Schwenkgelenklager (26) zu lagern, vgl. Figur 2. Das Handbedienungselement (25) wirkt jeweils auf die Handnotbetätigungselemente (24) der Proportionalmagnete (91) und (121). Mit dem Handbedienungselement (25) kann manuell wahlweise entweder das Heben- (90) oder das Senkenmodul (120) angesteuert werden. This control device is due to the parallel arrangement the modules (90) and (120) the possibility in front of the back Ends of the two proportional magnets (91) and (121) a manual control element (25), for example in a swivel joint bearing (26) to be stored, cf. Figure 2. The hand control (25) acts on the manual override elements (24) the proportional magnets (91) and (121). With the hand control (25) can either manually lift (90) or the sink module (120) can be controlled.

Da der Hub des Proportionalmagneten (91) sehr kurz ist, wird der vom Senkenmodul (120) kommende Volumenstrom beim Senken auf die beiden Ringkanäle (95) und (96) geteilt und über die zwei Steuerkanten (101) und (102) in den Rücklaufringkanal (94) abgeführt. Hierdurch können relativ große Volumenströme bei einer kompakten und trotzdem einfachen Bauweise beherrscht werden.Since the stroke of the proportional magnet (91) is very short, the volume flow coming from the sink module (120) when lowering to the two ring channels (95) and (96) divided and over the two control edges (101) and (102) discharged into the return ring channel (94). As a result, relatively large volume flows at a compact, yet simple design.

Claims (12)

  1. Hydraulic control device of monobloc design for raising and lowering a load, with at least two electromagnetically actuable proportional directional valve elements (90, 120) and with a pressure balance (70) as an input element for the load-independent raising of the load, the elements being arranged at least partially in a housing which has at least one pump connection, at least one consumer connection and at least one return connection,
    characterized
    in that the proportional directional valve elements (90, 120) are arranged parallel to one another, the electromagnetic drives (91, 121) being located on the same side and, in particular, at the same height next to one another,
    in that the pressure balance (70) is arranged coaxially next to the first proportional directional valve element (90),
    in that the first proportional directional valve element (90) is connected to the second proportional directional valve element (120) via a connecting duct (55) which is divided, in the region between the valve elements (90) and (120), into two individual duct portions (57) and (58), the two duct portions intersecting the bore (41) for mounting and guiding the longitudinal slide (97) of the first proportional directional valve element (90) and in each case meeting control edges (101 and 102) of the longitudinal slide (97) which are capable of blocking a return duct (94).
  2. Hydraulic control device according to Claim 1, characterized in that annular ducts (95) and (96), into which the duct portions (57) and (58) open, are arranged in the passage bore (41) in the region of the longitudinal slide (97).
  3. Hydraulic control device according to Claim 1 or 2, characterized in that the two duct portions (57) and (58) lead away from the annular ducts (95) and (96) in parallel and converge in the region between the valve elements (90) and (120), the imaginary centre lines of the converged duct portions (57) and (58) having a U-shaped profile.
  4. Hydraulic control device according to Claim 3, characterized in that the connecting duct (55) centrally meets the connecting point between the two duct portions (57) and (58), the imaginary centre line of the connecting duct (55) being oriented approximately parallel and centrally in relation to the centre lines of the duct portions (57) and (58).
  5. Hydraulic control device according to Claim 1, characterized in that the pressure balance (70) and the first proportional directional valve element (90) are arranged coaxially next to one another in the passage bore (41), the pump pressure bearing on the mutually associated end faces (81) and (98) of the pressure-balance piston (80) and of the longitudinal slide (97).
  6. Hydraulic control device according to Claim 1 or 5, characterized in that the longitudinal slide (97) of the first proportional directional valve element (90) is spring-loaded, at least one component (110) for adjusting the spring prestress and for supporting the corresponding spring (108) being led through a bore (77) in the pressure-balance piston (80).
  7. Hydraulic control device according to Claim 1, characterized in that the second proportional directional valve element (120) is a non-return valve which opens towards the consumer connection (51) and the closing movement of the longitudinal slide (140) of which takes place hydraulically, the pressure medium necessary for initiating the closing movement being directed via a control-oil throttle (144).
  8. Hydraulic control device according to Claim 1 or 7, characterized in that next to the longitudinal slides (140, 147) of the second proportional directional valve element (120) is arranged a stop valve (160) which is hydraulically switched in parallel with the control-oil throttle (144) during the closing phase of the longitudinal slide (140).
  9. Hydraulic control device according to Claim 1, characterized in that the second proportional directional valve element (120) is connected hydraulically to the pressure balance (90) via a load signalling system (11, 63, 74), and, in order to accelerate the closing movement of the pressure-balance piston (80), the electromagnetic drive (121) of this proportional directional valve element (120) is made live, at least for a short time, during the actuation of the electromagnetic drive (91) of the first proportional directional valve element (90), after the latter has blocked the annular return duct (94).
  10. Hydraulic control device according to Claim 1, characterized in that the inner longitudinal slide (147) of the second proportional directional valve element (120) is loaded by a spring (155) supported in the housing (30), with the result that, in the blocking state, the said inner longitudinal slide bears on a valve seat (146) in the outer longitudinal slide (140).
  11. Hydraulic control device according to Claim 10, characterized in that the prestress of the spring (155) is adjustable by means of an adjusting screw (150) arranged in the housing (30).
  12. Hydraulic control device according to Claims 10 and 11, characterized in that the housing (30) has, in the region of the adjusting screw (150), an adjusting bore (68), the centre line of which intersects the centre line of the longitudinal slides (140, 147) askew, in particular transversely, the shortest distance between the two centre lines corresponding to the axial distance between the adjusting screw (150) and an adjusting wheel capable of being inserted in the adjusting bore (68).
EP95118187A 1994-12-23 1995-11-18 Mono-block hydraulic control system Expired - Lifetime EP0718504B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4446144A DE4446144A1 (en) 1994-12-23 1994-12-23 Hydraulic control in monoblock design from at least two interlinked electromagnetically actuated proportional directional control valve elements
DE4446144 1994-12-23

Publications (3)

Publication Number Publication Date
EP0718504A2 EP0718504A2 (en) 1996-06-26
EP0718504A3 EP0718504A3 (en) 1997-01-22
EP0718504B1 true EP0718504B1 (en) 2000-05-03

Family

ID=6536810

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95118187A Expired - Lifetime EP0718504B1 (en) 1994-12-23 1995-11-18 Mono-block hydraulic control system

Country Status (3)

Country Link
EP (1) EP0718504B1 (en)
JP (1) JP3639657B2 (en)
DE (2) DE4446144A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29810860U1 (en) 1998-06-17 1998-08-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulic control device
AT407662B (en) * 1999-03-18 2001-05-25 Hoerbiger Hydraulik HYDRAULIC CONTROL UNIT
DE10006141A1 (en) 2000-02-11 2001-09-06 Zf Lenksysteme Gmbh Electro-hydraulic control device
KR100912597B1 (en) * 2009-05-13 2009-08-19 신우공업 주식회사 Parallel type complex control valve body for a fluid control valve
CN106949110B (en) * 2017-04-10 2018-10-19 四川长江液压件有限责任公司 A kind of pump flow stabilizing valve

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3415265A (en) * 1966-03-03 1968-12-10 Parker Hannifin Corp Directional control valve with priority flow divider
US3827453A (en) * 1972-05-05 1974-08-06 Parker Hannifin Corp Directional control valve
DE3317605A1 (en) * 1981-11-17 1984-11-15 Robert Bosch Gmbh, 7000 Stuttgart Arrangement for controlling pressure medium
DE3844336A1 (en) * 1988-12-30 1990-07-05 Bosch Gmbh Robert ELECTROHYDRAULIC PORPORTIONAL WAY VALVE
DE4234742A1 (en) * 1992-10-15 1994-04-21 Deere & Co Valve unit for position control of harvester - has pressure-limiting valve and non-return valve, spring for latter being weaker than for former

Also Published As

Publication number Publication date
DE59508271D1 (en) 2000-06-08
EP0718504A3 (en) 1997-01-22
DE4446144A1 (en) 1996-06-27
EP0718504A2 (en) 1996-06-26
JPH08233147A (en) 1996-09-10
JP3639657B2 (en) 2005-04-20

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