EP0799384B1 - Hydraulic control system of monobloc construction for raising and lowering a load with at least two electromagnetic proportional two-way valve elements - Google Patents

Hydraulic control system of monobloc construction for raising and lowering a load with at least two electromagnetic proportional two-way valve elements Download PDF

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Publication number
EP0799384B1
EP0799384B1 EP95937771A EP95937771A EP0799384B1 EP 0799384 B1 EP0799384 B1 EP 0799384B1 EP 95937771 A EP95937771 A EP 95937771A EP 95937771 A EP95937771 A EP 95937771A EP 0799384 B1 EP0799384 B1 EP 0799384B1
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EP
European Patent Office
Prior art keywords
bore
hydraulic control
control according
pressure
longitudinal slide
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP95937771A
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German (de)
French (fr)
Other versions
EP0799384A1 (en
Inventor
Hartmut Sandau
Werner Schumacher
Rainer Trucksess
Holger Lueues
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members

Definitions

  • the invention is based on a hydraulic control Monoblock construction for lifting and lowering a load with at least two electromagnetic directional control valve elements, a check valve and a pressure compensator for lifting the load independently of the load pressure as an input element, wherein the elements are at least partially arranged in a housing are at least one pump connection, at least a consumer connection and at least one return connection has, as known for example from document DE-A-4 201 114.
  • the hydraulic control according to the invention enables with respect their housing dimensions and the overall size of the monoblock a small build volume.
  • the individual valve elements are arranged close to each other and are over short holes or channels connected together.
  • the movable valve elements are seated in bores that are constructed and arranged for easy production, thus saving weight and machining time.
  • all valve parts are housed in just three holes.
  • a proportional directional valve element for lifting a load sits in one bore next to a pressure compensator.
  • the bore in which the piston of the pressure compensator is arranged coaxially next to the longitudinal slide of the proportional directional valve element is a through hole without any gradation.
  • a return spring acting on the latter sits between the piston and the longitudinal slide. In order to be able to support the return spring in relation to the housing in a space-saving manner, at least one component is guided through the piston of the pressure compensator to support and adjust the preload.
  • a proportional directional valve element for lowering the previously called load arranged. It ends with the first Hole on a flat face of the common housing. The electromagnetic ones are directly next to each other on this front side Drives arranged, whereby the drives with simple means can also be controlled mechanically.
  • a Third hole sits a check valve that allows a backflow the pressure medium from a consumer connection in the Proportional directional valve element for lifting prevented.
  • FIG. 1 shows one basic structure of a hydraulic control device (1) for an OC hydraulic system with two electromagnetic actuatable proportional directional valve elements (90) and (120), a pressure compensator (70) and a check valve (170).
  • This control device (1) and also from the Figures 5 and 9 each serve to control a simple acting hydraulic cylinder (7), cf. Figure 3, at> for example part of a self-propelled work machine.
  • Both proportional directional valve elements (90) and (120) are throttling directional control valves, their longitudinal spools besides the two End positions continuously take any intermediate positions can. They each have a proportional magnet on one side (91, 121) and on the other side one Return spring (108, 155).
  • the first proportional directional valve element (90) is a 3/2-way valve and the second (120) is one 2/2 way valve.
  • the flows through the 3/2-way valve (90) Pressure medium flow coming from a pump connection (49) a separate check valve (170) to a consumer connection (50). It controls the pressure medium flow from a constant pump (5), cf. Figure 2, to the consumer, a simple acting hydraulic cylinder (7) for lifting a load.
  • the Proportional directional valve element (90) is therefore described below Called lifting module.
  • the 2/2-way valve (120) controls the from single-acting hydraulic cylinder (7) under load over the Consumer connection (50) flowing pressure medium flow over the Return line (16) to the tank.
  • the second proportional directional valve element (120) is therefore referred to as a sink module.
  • the pressure compensator (70) is open during a neutral circulation and the not required Pressure medium flow almost unrestricted in a second return line (17) directs.
  • the return line (17) ends in one Return connection (53).
  • On the pressure compensator (70) is next to one Control spring (88) a load signaling line (12) with a throttle valve (11) connected by the connecting line (13) branches.
  • a return cross line (14) is the load signaling line (12) when the 3/2-way valve (90) is not actuated, via this connected to the return line (16).
  • the proportional magnet (91) of the lifting module is used to lift a load (90) energized.
  • the return cross line (14) locked and pressure medium is via the lifting module (90) Connection line (13) and the check valve (170) to Consumer connection (50) passed. This is about the Load signaling line (12) the pressure compensator (70) on its spring-loaded Side, with which the pump current on the am Throttled consumer connection (50) applied load pressure becomes.
  • Proportional magnet (91) Proportional magnet (121) of the sink module (120) activated.
  • the pressure medium flows from Consumer connection (50) via the sink module (120) and Return line (16) to the return connection (52).
  • 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 two flat, T-shaped and finely worked surfaces.
  • the two proportional magnets (91) and (121) are flanged.
  • the consumer connection is located diagonally above it (50), cf.
  • the other two side surfaces (38, 39) have bulges, formed around the mounting holes (69, 69 ') are, cf. Figure 6.
  • the one in Figure 2 shows below Side face a socket for receiving the pump connection (49).
  • the pump connection (49) with internal thread goes in the housing (30) into an inlet ring channel (93).
  • the ring channel (93) penetrates a cylindrical through hole (41) which extends from the front (34) extends to the rear (35).
  • the longitudinal slide is located on the left-hand area of the through hole (41) (97) of the lifting module (90).
  • Meet there Through hole (41) two further channels (94, 95).
  • the left one (94) is a return ring channel that connects to the sink module (120) leading return cross bore (59) in connection stands.
  • the connecting ring channel (95) From the right of this return ring channel (94) the connecting ring channel (95), from which the connecting channel (56) almost tangentially out of the section plane branches.
  • the longitudinal slide (97) of the lifting module (90) connects either - in the unactuated state with zero overlap - the connecting ring channel (95) with the return ring channel (94) or - in the actuated state - with the inlet ring channel (93).
  • annular groove (99) goes in the area of your right shaft collar in fine control notches (103), which in Connection with the pressure compensator (70) the function of a measuring throttle to have.
  • the opening cross sections of the fine control notches (103) decrease in the direction of the inlet ring channel (93), without it, however - with the de-energized proportional magnet (91) - to achieve.
  • the fine control notches (103) are here for example round notches.
  • the longitudinal slide is from its right end face (98) (97) drilled in stages.
  • the right area of the stepped bore (105) serves to guide the return spring (108).
  • Of the left area has a smaller diameter and connects the stepped bore via an oblique compensation bore (106) (105) with the recess (104).
  • the transition from right to left area of the stepped bore (105) forms 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 the Cross section - perpendicular to the imaginary center line of the through hole - Star-shaped to compensate for pressure on the longitudinal slide (97) the pressure medium is not throttled to let happen. For this purpose, it has, for example, several notches (113) distributed around the circumference.
  • the cross section can also have a circular area in which at least one relief hole is arranged.
  • the spring plate (109) is seated on a rod (110), the center line of which is that of the through hole (41) coincides.
  • the spring plate (109) is either part of the rod (110) or it sits in the middle of it centered, for example with the help of a cross-press fit.
  • the rod (110) protrudes into the right of the longitudinal slide (97) arranged cup-shaped pressure balance pistons (80) inside to hit a grub screw (111).
  • 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 (116), in which it sits screwed.
  • the head of the locking screw (114) a cylindrical recess that the Includes a lock nut (112).
  • a hexagon socket (117) To adjust and He counters the set screw (111) on its outer free end of a hexagon socket (117).
  • the through hole (41) goes into one at its right end Screw hole (42) over.
  • the screw plug (114) is attached.
  • An im Area between head and thread seated sealing ring (118) seals the screw plug bore (42) to the outside.
  • the Pot-shaped pressure balance pistons (80) In the through hole (41) sits between the screw plug (114) and the longitudinal slide (97) tightly sliding the Pot-shaped pressure balance pistons (80).
  • the latter has a cylindrical one Outer contour that has a semicircular recess at its right end (84), in which a spring ring (89) is used is.
  • the spring ring (89) is included - for example not flowed through control device - on one as a stop serving inner collar, which is between the through hole (41) and the larger diameter screw hole (42) is formed.
  • a right stop The adjusting screw forms for the pressure compensator piston (80) (114).
  • the pressure compensator piston is behind the half-round groove (84) (80) chamfered. He carries in the area in front of the spring washer (89) a series of short-circuit grooves.
  • the guide hole (87) is in her Reason narrowed to fix the control spring (88) radially.
  • a bore (115) with a comparable contour is located in the left front of the adjustment screw (114).
  • ring channels (71) and (74) Adjacent to the inlet ring channel (93) is the return ring channel (71).
  • This ring channel (71) is, for example, when lifting a load when the Lifting current is equal to the pump current through the pressure compensator piston (80) fully closed while in neutral circulation is open.
  • the load reporting channel (74) is arranged between the return ring channel (71) and the adjusting screw (114) between the return ring channel (71) and the adjusting screw (114) the load reporting channel (74) is arranged. He stands with the connecting hole (56) over a through hole (41) parallel load signaling line (12) in connection. There is a choke point in the load signaling line (12) (11) arranged.
  • the sink module (120) has, from the front (34), in the housing (30) leading blind hole (45), the aligned parallel to the through hole (41) of the lifting module is.
  • the blind hole (45) is - as in the lifting module (90) - on the left with the help of the proportional magnet (121) sealed pressure-tight.
  • a valve sleeve is located in the right area of the blind hole (45) (130), the two nested longitudinal slides (140) and (147).
  • the valve sleeve (130) is in the blind hole (45) between a bore end and a screw ring (156) on the left with an internal continuous hexagon socket axially secured.
  • the left area of the blind hole (45) has an internal thread (128).
  • valve sleeve (130) is from a consumer ring channel (125) surround that with the consumer connection shown in Figure 3 (50) is hydraulically connected. This leads from the consumer ring channel (125) in the area between the sink (120) and lifting module (90) tangentially a consumer bore (54) gone.
  • the consumer bore (54) opens into the with reference to FIG. 2, higher-lying check valve (170), see. Figure 3.
  • the check valve (170) has a valve bore (47) in the Shape of a blind hole that is roughly half the depth of the hole cut tangentially from the consumer bore (54) becomes.
  • the valve bore (47) is conical at its left end Valve seat (171) and in the area of your right End designed as a consumer connection (50) with an internal thread.
  • a spring-loaded Check valve (173) In the middle, cylindrical area sits a spring-loaded Check valve (173).
  • the latter has one tubular shaft (174), at the left end of which is a frustoconical Valve disc (175) is located.
  • a coil spring (176) is arranged, which the check valve (173) presses against the valve seat (171). This lies the coil spring (176) on the left via a seal and a Washer on the back of the valve plate (175) on.
  • the star disc (177) On the right it is supported by a star-shaped one Disc (177) from at least one spacer a circlip located in the valve bore (47) (178) is present.
  • the star disc (177) has a central, left cantilevered bolt on which the tubular Shaft (174) of the check valve (173) is guided.
  • the adjusting screw is to the left of the screw ring (156) (150).
  • the adjusting screw (150) sits in the internal thread (128).
  • the internal thread is between the adjusting screw (150) and the screw ring (156) from one Return ring channel (126) interrupted.
  • the return ring channel (126) stands with the underside (33) of the housing (30) over the return bore (66) and with the return ring channel (94) of the lifting module (90) via the return cross bore (59) in connection.
  • the return cross bore (59) is from the side surface (39) delimiting the sink module (120) closed by means of a sealing plug (61) in a pressure-tight manner.
  • the sink module (120) primarily the adjusting screw (150) and the valve sleeve (130) with the two longitudinal slides (140) and (147), with the exception of one on the Adjusting screw (150) arranged toothing (151) from the DE 41 40 604 Al known.
  • the following is therefore the structure of the sink module (120) solely on the basis of its mode of action described.
  • the sink module (120) is shown in Figure 2 in the locked position.
  • the pressure medium at the consumer connection (50) and thus via the consumer bore (54) on the consumer ring channel (125) is present, cannot enter the return ring channel (126) stream.
  • the main control notches (142) are hidden under the cylinder seat (133) next to the annulus (134).
  • Around the main spool (140) on the main valve seat (132) stands on its right end in a pressure chamber (135) Pressure medium under load pressure.
  • 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 a control groove (143) with the bottom of its bore.
  • the contact pressure is diminished by the opposite Force due to the pressure in a consumer pressure chamber (136) Pressure.
  • the consumer pressure space (136) is in the range the outer contour of the main control spool (140) between Main valve plug (141) and short-circuit grooves.
  • 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 to the right. This will get his input tax notches (149) under the control groove (143) of the main control spool (140). At the same time, the one on the left lifts Valve plug (148) from its in the main spool (140) corresponding valve seat (146). The pressure room (135) is now over the longitudinal bore (145), the control groove (143), the pilot notches (149), the valve seat (146) and the return ring channel (126) in connection with the return bore (66).
  • the pressure in the pressure chamber (135) drops.
  • the one there Pressure arises according to the ratio of the cross section the throttle bore (144) and the opening cross-section the pilot notches (149). Falls accordingly far to the right pushed pilot spool (147) the pressure in 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 from the main valve seat (132) and the main control notches (142) enter the area of the Annulus (134).
  • the pressure medium flows from the consumer coming, between the valve sleeve (130) and the main spool (140) towards the return ring channel (126).
  • Main control spool (140) hurries through its opening movement the pilot spool (147), whereby the opening cross-section on the pilot notches (149) becomes smaller. So that can a higher one in the pressure chamber (135) via the throttle bore (144) Build up pressure. Consequently, the opening movement of the Main spool (140) braked until there is an equilibrium sets.
  • 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 on the pilot spool (147) and on the Adjusting screw (150).
  • the pilot control notches (149) are closed.
  • the pressure in the pressure chamber (135) increases.
  • the main poppet (141) puts on the main valve seat (132).
  • the sink module (120) locks. The sink module (120) thus reworks Kind of a sequential control.
  • the adjusting screw (150) engages.
  • the adjusting screw sits in an adjustment hole (68) here from the back (35) into the blind hole (45) extends and the return cross bore (59) and the return ring channel (126) affects.
  • the adjusting screw (152) can with the help of an adjusting spindle, the free end of which Housing (30) protrudes, or a special tool that temporarily be coupled on the face side with the adjusting screw (152) can be rotated.
  • Adjusting spindle or the adjusting screw (152) becomes the adjusting screw (150) in the internal thread (128) to the right or screwed left.
  • the length of the adjustment range corresponds largely the width of the toothing (151) of the adjusting screw (150).
  • the proportional magnet When lifting the load, the proportional magnet is energized (91) Pressure medium via the pump connection (49), the inlet ring channel (93), the longitudinal slide (97) and the connecting hole (56) in the valve bore (47) in front of the check valve (173) of the check valve shown in Figure 3 (170).
  • the longitudinal slide (97) is opened via his fine tax scores (103). They form in relation to the Pressure compensator (70) the measuring throttle.
  • the pressure medium flows on the way to the check valve (170) via the load signaling line (12) and the load signaling channel (74) on the back of the Pressure balance piston (80).
  • Through this connection of the pressure compensator (70) is in front of and behind the fine control notches (103) always a constant pressure drop, the size of which by the Spring force of the control spring (88) is determined.
  • the proportional magnet is used to stop lifting the load (91) switched off.
  • the longitudinal slide (97) and the non-return slide (173) go into their closed positions like them are shown in Figure 2.
  • Figure 5 shows the hydraulic circuit diagram for a with the control device (1) comparable control device (2).
  • the pressure compensator (70) in FIG. 5 can, however, continue to be loaded.
  • the previous return connection (53) becomes a loadable, second consumer connection (51). Further becomes from the 3/2-way valve (90) to the check valve (170) guided pressure medium flow controllable via the pressure compensator piston (80) of the pressure compensator (70).
  • FIG. 6 leads in the lifting module (90) from the connecting ring channel (95) a housing channel (64) at least in some areas parallel to the through hole (41) in a load signaling ring channel (75), which is between the screw plug (114) and the pressure compensator piston (80).
  • a consumer ring channel (72) and a load signaling channel (75) arranged in the area of the pressure compensator (70) in the area of the pressure compensator (70) in the area of the pressure compensator (70) in the area of the pressure compensator (70) in the area of the pressure compensator (70) in the area of the pressure compensator (70) in the area of the pressure compensator (70) is next to the return ring channel (71) .
  • a consumer ring channel (72) and a load signaling channel (75) arranged to the return ring channel (71) in this embodiment.
  • additional consumers are connected be, cf. Figure 5, consumer connection (51).
  • the consumer ring channel (72) leads via a flat channel (62) to the valve bore (47) of the check valve (170).
  • the outer contour changed compared to the first embodiment of the pressure compensator piston (80) is chamfered on its left edge.
  • At her right end she has a waist that to the right end in a stop flange (85) transforms.
  • the pressure medium passes through the openings (86) - if the stop flange on the left wall of the Load signaling channel (75) lies - in the area of the waist and via a chamfered control edge adjoining it via the consumer ring channel (72) into the flat channel (62).
  • the control edge sits approximately in the middle of the consumer ring channel (72).
  • the one that also forms a control edge Chamfer on the left edge of the outer contour ends just before the return ring channel (71).
  • the control device (2) is therefore independent of the load pressure Control of the volume flow to the first consumer connection (50) also possible if the continuation via the second consumer port (51) is pressurized because of Pressure balance piston (80) has an additional control edge.
  • a third embodiment of the hydraulic control device can be seen in Figures 9 and 10.
  • the one shown here Control device (3) is suitable for an LS hydraulic system.
  • the pressure compensator (70) sits in contrast to the two previously described embodiments, cf. Figure 1 and 5, no longer in the secondary branch (10), but is the 3/2-way valve (90) directly upstream.
  • the rest of the circuit, including the load reporting system corresponds to the circuit from Figure 1.
  • FIG. 10 shows the third control device (3) in the Cut. It constructively gives way in the area of the lifting module (90) and the pressure compensator (70) from the control device (1) off.
  • the pump connection (49) leads to an intermediate ring channel (73) of the through hole (41) in the central area of the pressure compensator piston (80).
  • Intermediate ring channel (73) begins - at that shown in Figure 10
  • the control groove (82) extends to the left into the inlet ring channel (93).
  • the control groove (82) goes in there Fine control notches (83) over.
  • the fine control notches (83) end in front of the end face (81) of the pressure compensator piston (80).

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Magnetically Actuated Valves (AREA)
  • Safety Valves (AREA)

Description

Stand der Technik:State of the art:

Die Erfindung geht aus von einer hydraulischen Steuerung in Monoblockbauweise zum Heben und Senken einer Last mit mindestens zwei elektromagnetisch betätigbaren Proportionalwegeventilelementen, einem Rückschlagventil und einer Druckwaage zum lastdruckunabhängigen Heben der Last als Eingangselement, wobei die Elemente zumindest teilweise in einem Gehäuse angeordnet sind, das mindestens einen Pumpenanschluß, mindestens einen Verbraucheranschluß und mindestens einen Rücklaufanschluß aufweist, wie zum Beispiel aus Dokument DE-A-4 201 114 bekannt.The invention is based on a hydraulic control Monoblock construction for lifting and lowering a load with at least two electromagnetic directional control valve elements, a check valve and a pressure compensator for lifting the load independently of the load pressure as an input element, wherein the elements are at least partially arranged in a housing are at least one pump connection, at least a consumer connection and at least one return connection has, as known for example from document DE-A-4 201 114.

In der Regel werden bei hydraulischen Steuerungen in Monoblockbauweise die Antriebe, Betätigungselemente und Anschlüsse an fast allen Gehäuseseiten des Monoblocks angeordnet. Dabei ergeben sich nach dem Anbau der Antriebe, Anschlüsse und Einstellorgane für die Ventilfedern trotz kompakter Bauweise Steuerungen mit großen Außenabmessungen, da besonders die Antriebe oft gegenüberliegen oder über Eck angeordnet aus den Gehäusen herausragen. Außerdem haben derartige Steuerungen meist lange und kompliziert gestaltete Hydraulikkanäle, die den durch das Gehäuse fließenden Druckmittelstrom zusätzlich drosseln und dabei die Dynamik der Steuerung beeinträchtigen. Ferner ist bei einer kompakten Bauweise die Einstellung der Proportionalwegeventilelemente nur schwer oder überhaupt nicht durchführbar. As a rule, hydraulic controls in monoblock construction the drives, actuators and connections arranged on almost all housing sides of the monoblock. This results in connections after the drives are attached and setting elements for the valve springs despite being more compact Control systems with large external dimensions, because especially the drives are often opposite or arranged in a corner protrude from the housings. They also have Controls are usually long and complicated Hydraulic channels, which the flow of pressure medium flowing through the housing additionally throttle and thereby the dynamics of the Control affect. Furthermore, a compact Design the setting of the proportional directional valve elements difficult or impossible at all.

Vorteile der Erfindung:Advantages of the invention:

Die erfindungsgemäße hydraulische Steuerung ermöglicht bezüglich ihrer Gehäuseabmessungen und der Gesamtgröße des Monoblocks ein kleines Bauvolumen. Die einzelnen Ventilelemente sind eng nebeneinander angeordnet und sind über kurze Bohrungen oder Kanäle miteinander verbunden.The hydraulic control according to the invention enables with respect their housing dimensions and the overall size of the monoblock a small build volume. The individual valve elements are arranged close to each other and are over short holes or channels connected together.

Die beweglichen Ventilelemente sitzen in fertigungsgünstig konstruierten und angeordneten Bohrungen, womit Gewicht und Bearbeitungszeit eingespart werden können. Dazu werden alle Ventilteile in nur drei Bohrungen untergebracht. In der einen Bohrung sitzt ein Proportionalwegeventilelement zum Heben einer Last neben einer Druckwaage. Die Bohrung, in der der Kolben der Druckwaage koaxial neben dem Längsschieber des Proportionalwegeventilelements angeordnet ist,
ist eine Durchgangsbohrung ohne jede Stufung. Zwischen dem Kolben und dem Längsschieber sitzt eine auf letzteren wirkende Rückstellfeder. Um die Rückstellfeder gegenüber dem Gehäuse bauraumsparend abstützen zu können, ist mindestens ein Bauteil zu ihrer Abstützung und Verstellung der Vorspannung durch den Kolben der Druckwaage hindurchgeführt.The movable valve elements are seated in bores that are constructed and arranged for easy production, thus saving weight and machining time. For this purpose, all valve parts are housed in just three holes. A proportional directional valve element for lifting a load sits in one bore next to a pressure compensator. The bore in which the piston of the pressure compensator is arranged coaxially next to the longitudinal slide of the proportional directional valve element
is a through hole without any gradation. A return spring acting on the latter sits between the piston and the longitudinal slide. In order to be able to support the return spring in relation to the housing in a space-saving manner, at least one component is guided through the piston of the pressure compensator to support and adjust the preload.

In einer zweiten parallelen Bohrung in Form eines Sackloches ist ein Proportionalwegeventilelement zum Senken der zuvor genannten Last angeordnet. Sie endet zusammen mit der ersten Bohrung an einer ebenen Stirnseite des gemeinsamen Gehäuses. Auf dieser Stirnseite sind direkt nebeneinander die elektromagnetischen Antriebe angeordnet, wodurch die Antriebe mit einfachen Mitteln auch mechanisch ansteuerbar sind. In einer dritten Bohrung sitzt ein Rückschlagventil, das ein Zurückströmen des Druckmittels von einem Verbraucheranschluß in das Proportionalwegeventilelement zum Heben verhindert.In a second parallel hole in the form of a blind hole is a proportional directional valve element for lowering the previously called load arranged. It ends with the first Hole on a flat face of the common housing. The electromagnetic ones are directly next to each other on this front side Drives arranged, whereby the drives with simple means can also be controlled mechanically. In a Third hole sits a check valve that allows a backflow the pressure medium from a consumer connection in the Proportional directional valve element for lifting prevented.

Um einen großen Volumenstrom durchsetzen zu können, sind teilweise einzelne Anschlüsse doppelt ausgeführt.To be able to enforce a large volume flow, are some of the connections are duplicated.

Zeichnungen:Drawings:

Weitere Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung von drei vereinfacht dargestellten Ausführungsformen:

Figur 1:
Hydraulikschaltplan einer Steuervorrichtung für ein OC-Hydrauliksystem mit zwei elektromagnetisch betätigten Proportionalwegeventilelementen, einer Druckwaage und einem Rückschlagventil ohne Weiterlaufbelastbarkeit;
Figur 2:
Schnitt durch eine Steuervorrichtung nach Figur 1;
Figur 3:
Schnitt durch das Rückschlagventil nach Figur 1;
Figur 4:
Seitenansicht der Steuervorrichtung nach Figur 2 und 3;
Figur 5:
Hydraulikschaltplan wie in Figur 1, jedoch für eine weiterlaufbelastbare Steuervorrichtung;
Figur 6:
Schnitt durch eine Steuervorrichtung nach Figur 5;
Figur 7:
Schnitt durch das Rückschlagventil nach Figur 5;
Figur 8:
Seitenansicht der Steuervorrichtung nach Figur 6 und 7;
Figur 9:
Hydraulikschaltplan wie in Figur 1, jedoch für ein LS-Hydrauliksystem;
Figur 10:
Schnitt durch eine Steuervorrichtung nach Figur 9
Further details of the invention result from the following description of three embodiments which are shown in simplified form:
Figure 1:
Hydraulic circuit diagram of a control device for an OC hydraulic system with two electromagnetically actuated proportional directional control valve elements, a pressure compensator and a check valve without resilience;
Figure 2:
Section through a control device according to Figure 1;
Figure 3:
Section through the check valve of Figure 1;
Figure 4:
Side view of the control device according to Figures 2 and 3;
Figure 5:
Hydraulic circuit diagram as in Figure 1, but for a further loadable control device;
Figure 6:
Section through a control device according to Figure 5;
Figure 7:
Section through the check valve of Figure 5;
Figure 8:
Side view of the control device according to Figures 6 and 7;
Figure 9:
Hydraulic circuit diagram as in Figure 1, but for an LS hydraulic system;
Figure 10:
Section through a control device according to FIG. 9

Beschreibung der Ausführungsbeispiele:Description of the embodiments:

Der in Figur 1 dargestellte Hydraulikschaltplan zeigt einen prinzipiellen Aufbau einer hydraulischen Steuervorrichtung (1) für ein OC-Hydrauliksystem mit zwei elektromagnetisch betätigbaren Proportionalwegeventilelementen (90) und (120), einer Druckwaage (70) und einem Rückschlagventil (170). Diese Steuervorrichtung (1) und auch die aus den Figuren 5 und 9 dienen jeweils der Ansteuerung eines einfach wirkenden Hydraulikzylinders (7), vgl. Figur 3, der bei> spielsweise Teil einer selbstfahrenden Arbeitsmaschine ist.The hydraulic circuit diagram shown in Figure 1 shows one basic structure of a hydraulic control device (1) for an OC hydraulic system with two electromagnetic actuatable proportional directional valve elements (90) and (120), a pressure compensator (70) and a check valve (170). This control device (1) and also from the Figures 5 and 9 each serve to control a simple acting hydraulic cylinder (7), cf. Figure 3, at> for example part of a self-propelled work machine.

Beide Proportionalwegeventilelemente (90) und (120) sind drosselnde Wegeventile, deren Längsschieber außer den beiden Endstellungen stufenlos beliebige Zwischenstellungen einnehmen können. Sie haben jeweils auf der einen Seite einen Proportionalmagneten (91, 121) und auf der anderen Seite eine Rückstellfeder (108, 155). Das erste Proportionalwegeventilelement (90) ist ein 3/2-Wegeventil und das zweite (120) ein 2/2-Wegeventil. Durch das 3/2-Wegeventil (90) fließt der Druckmittelstrom von einem Pumpenanschluß (49) kommend über ein separates Rückschlagventil (170) zu einem Verbraucheranschluß (50). Es steuert den Druckmittelstrom von einer Konstantpumpe (5), vgl. Figur 2, zum Verbraucher, einen einfach wirkenden Hydraulikzylinder (7) zum Heben einer Last. Das Proportionalwegeventilelement (90) wird daher im folgenden Hebenmodul genannt. Das 2/2-Wegeventil (120) steuert den vom einfach wirkenden Hydraulikzylinder (7) unter Last über den Verbraucheranschluß (50) fließenden Druckmittelstrom über die Rücklaufleitung (16) zum Tank. Das zweite Proportionalwegeventilelement (120) wird demnach als Senkenmodul bezeichnet. Both proportional directional valve elements (90) and (120) are throttling directional control valves, their longitudinal spools besides the two End positions continuously take any intermediate positions can. They each have a proportional magnet on one side (91, 121) and on the other side one Return spring (108, 155). The first proportional directional valve element (90) is a 3/2-way valve and the second (120) is one 2/2 way valve. The flows through the 3/2-way valve (90) Pressure medium flow coming from a pump connection (49) a separate check valve (170) to a consumer connection (50). It controls the pressure medium flow from a constant pump (5), cf. Figure 2, to the consumer, a simple acting hydraulic cylinder (7) for lifting a load. The Proportional directional valve element (90) is therefore described below Called lifting module. The 2/2-way valve (120) controls the from single-acting hydraulic cylinder (7) under load over the Consumer connection (50) flowing pressure medium flow over the Return line (16) to the tank. The second proportional directional valve element (120) is therefore referred to as a sink module.

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 eine zweite Rücklaufleitung (17) leitet. Die Rücklaufleitung (17) endet in einem Rücklaufanschluß (53). An der Druckwaage (70) ist neben einer Regelfeder (88) eine Lastmeldeleitung (12) mit einem Drosselventil (11) angeschlossen, die von der Verbindungsleitung (13) abzweigt.Is between the pump connection (49) and the lifting module (90) arranged in a secondary branch (10), the pressure compensator (70) is open during a neutral circulation and the not required Pressure medium flow almost unrestricted in a second return line (17) directs. The return line (17) ends in one Return connection (53). On the pressure compensator (70) is next to one Control spring (88) a load signaling line (12) with a throttle valve (11) connected by the connecting line (13) branches.

Mit Hilfe einer Rücklaufquerleitung (14) ist die Lastmeldeleitung (12) bei unbetätigtem 3/2-Wegeventil (90) über dieses mit der Rücklaufleitung (16) verbunden.With the help of a return cross line (14) is the load signaling line (12) when the 3/2-way valve (90) is not actuated, via this connected to the return line (16).

Zum Heben einer Last wird der Proportionalmagnet (91) des Hebenmoduls (90) bestromt. Die Rücklaufquerleitung (14) wird gesperrt und Druckmittel wird über das Hebenmodul (90), die Verbindungsleitung (13) und das Rückschlagventil (170) zum Verbraucheranschluß (50) geleitet. Hierbei wird über die Lastmeldeleitung (12) die Druckwaage (70) auf ihrer federbelasteten Seite beaufschlagt, womit der Pumpenstrom auf den am Verbraucheranschluß (50) anliegenden Lastdruck angedrosselt wird.The proportional magnet (91) of the lifting module is used to lift a load (90) energized. The return cross line (14) locked and pressure medium is via the lifting module (90) Connection line (13) and the check valve (170) to Consumer connection (50) passed. This is about the Load signaling line (12) the pressure compensator (70) on its spring-loaded Side, with which the pump current on the am Throttled consumer connection (50) applied load pressure becomes.

Zum Senken einer Last wird bei einem in der Regel unbestromten Proportionalmagneten (91) der Proportionalmagnet (121) des Senkenmoduls (120) aktiviert. Das Druckmittel fließt vom Verbraucheranschluß (50) über das Senkenmodul (120) und die Rücklaufleitung (16) zum Rücklaufanschluß (52).To lower a load, one is usually de-energized Proportional magnet (91) Proportional magnet (121) of the sink module (120) activated. The pressure medium flows from Consumer connection (50) via the sink module (120) and Return line (16) to the return connection (52).

In Figur 2 wird die realisierte Steuervorrichtung (1) im Schnitt gezeigt. Sie hat ein im wesentlichen quaderförmiges Gehäuse (30) mit zwei annähernd quadratischen, ebenen Flächen als Ober- und Unterseite (31) und (33), vgl. Figur 4. In die feinbearbeitete Unterseite (31) münden ein Rücklaufkanal (65) und eine Rücklaufbohrung (66), vgl. Figur 2. Ferner weisen Ober- und Unterseite (31) und (33) zwei Befestigungsbohrungen (69, 69') auf, vgl. Figur 6, die senkrecht zur Schnittebene das Gehäuse (30) durchdringen. Auf der Oberseite (31) hat das Gehäuse annähernd mittig eine Gehäuseerweiterung (32), vgl. Figur 4.In Figure 2, the implemented control device (1) in Cut shown. It has an essentially cuboid shape Housing (30) with two approximately square, flat surfaces as top and bottom (31) and (33), cf. Figure 4. In the finely machined bottom (31) open a return channel (65) and a return bore (66), cf. Figure 2. Also point Top and bottom (31) and (33) two mounting holes (69, 69 '), cf. Figure 6, perpendicular to Cut through the housing (30). On the top (31) the housing has a housing extension approximately in the middle (32), cf. Figure 4.

Die senkrecht zur Schnittfläche ausgerichteten Seitenflächen (34, 35, 38, 39) haben jeweils einen rechteckigen Umriß. Die Vorder- (34) und die Rückseite (35) sind zwei ebene, T-förmige und feinbearbeitete Flächen. An der Vorderseite (34) sind die beiden Proportionalmagnete (91) und (121) angeflanscht. Gegenüber dem ersten Proportionalmagneten (91) sitzt in der Rückseite (35) eine Verschlußschraube (114), vgl. Figur 2. Schräg über ihr befindet sich der Verbraucheranschluß (50), vgl. Figur 3.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 two flat, T-shaped and finely worked surfaces. At the front (34) the two proportional magnets (91) and (121) are flanged. Compared to the first proportional magnet (91) there is a screw plug (114) in the back (35), see. Figure 2. The consumer connection is located diagonally above it (50), cf. Figure 3.

Die beiden anderen Seitenflächen (38, 39) haben Ausbuchtungen, die um die Befestigungsbohrungen (69, 69') gebildet sind, vgl. Figur 6. Außerdem weist die in Figur 2 unten liegende Seitenfläche einen Stutzen zur Aufnahme des Pumpenanschlusses (49) auf.The other two side surfaces (38, 39) have bulges, formed around the mounting holes (69, 69 ') are, cf. Figure 6. In addition, the one in Figure 2 shows below Side face a socket for receiving the pump connection (49).

Der Pumpenanschluß (49) mit Innengewinde geht 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) zwei weitere Kanäle (94, 95). Der linke (94) ist ein Rücklaufringkanal, der mit einer zum Senkenmodul (120) führenden Rücklaufquerbohrung (59) in Verbindung steht. Rechts von diesem Rücklaufringkanal (94) befindet sich der Verbindungsringkanal (95), vom dem der Verbindungskanal (56) annähernd tangential aus der Schnittebene heraus abzweigt.The pump connection (49) with internal thread goes in the housing (30) into an inlet ring channel (93). The ring channel (93) penetrates a cylindrical through hole (41) which extends from the front (34) extends to the rear (35). in the The longitudinal slide is located on the left-hand area of the through hole (41) (97) of the lifting module (90). Meet there Through hole (41) two further channels (94, 95). Of the the left one (94) is a return ring channel that connects to the sink module (120) leading return cross bore (59) in connection stands. To the right of this return ring channel (94) the connecting ring channel (95), from which the connecting channel (56) almost tangentially out of the section plane branches.

Der Längsschieber (97) des Hebenmoduls (90) verbindet entweder - im unbetätigten Zustand bei Nullüberdeckung - den Verbindungsringkanal (95) mit dem Rücklaufringkanal (94) oder - im betätigten Zustand - mit dem Zulaufringkanal (93). Dazu weist die zylindrische Außenkontur des Längsschiebers (97) eine Ringnut (99) auf. Die Ringnut 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 Proportionalmagneten (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 with zero overlap - the connecting ring channel (95) with the return ring channel (94) or - in the actuated state - with the inlet ring channel (93). To has the cylindrical outer contour of the longitudinal slide (97) an annular groove (99). The ring groove goes in the area of your right shaft collar in fine control notches (103), which in Connection with the pressure compensator (70) the function of a measuring throttle to have. The opening cross sections of the fine control notches (103) decrease in the direction of the inlet ring channel (93), without it, however - with the de-energized proportional magnet (91) - to achieve. The fine control notches (103) are here for example round notches.

Am linken Rand der Außenkontur des Längsschiebers (97) befindet sich im Bereich des Dichtrings zwischen dem Proportionalmagneten (91) und dem Gehäuse (30) ein Einstich. Unterhalb dieses Einstichs weist der Längsschieber (97) eine zylindrische Vertiefung (104) auf, an deren Grund der Ankerstößel (92) des Proportionalmagneten (91) ansteht. Zwischen dem Einstich und der Ringnut (99) befinden sich in der Außenkontur mehrere Kurzschlußnuten.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 puncture has the longitudinal slide (97) a cylindrical Indentation (104), at the bottom of which the anchor plunger (92) of the proportional magnet (91). Between the The groove and the ring groove (99) are in the outer contour several short-circuit grooves.

Von seiner 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). Den Übergang vom rechten zum linken Bereich der Stufenbohrung (105) bildet ein ebener Gehäusebund, auf dem sich die Rückstellfeder (108) abstützt. The longitudinal slide is from its right end face (98) (97) drilled in stages. The right area of the stepped bore (105) serves to guide the return spring (108). Of the left area has a smaller diameter and connects the stepped bore via an oblique compensation bore (106) (105) with the recess (104). The transition from right to left area of the stepped bore (105) forms 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 - senkrecht zur gedachten Mittellinie der Durchgangsbohrung - sternförmig ausgebildet, um für den Druckausgleich am Längsschieber (97) das Druckmittel ungedrosselt passieren zu lassen. Dazu weist er beispielsweise mehrere auf dem Umfang verteilte Kerben (113) auf. Der Querschnitt kann auch eine Kreisfläche haben, in der mindestens eine Entlastungsbohrung angeordnet ist. Der Federteller (109) sitzt auf einer Stange (110), deren Mittellinie mit der der Durchgangsbohrung (41) zusammenfällt. Der Federteller (109) ist entweder ein Teil der Stange (110) oder er sitzt auf ihr mittig zentriert, beispielsweise mit Hilfe eines Querpreßsitzes. Die Stange (110) ragt in den 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 (77) 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 u.a bei Schiefstellung der Rückstellfeder (108) ein gegenseitiges Verkanten zwischen dem Längsschieber (97) und dem Federteller (109) vermieden.The other end of the return spring (108) lies on a stepped Spring plate (109). The spring plate (109) is in the Cross section - perpendicular to the imaginary center line of the through hole - Star-shaped to compensate for pressure on the longitudinal slide (97) the pressure medium is not throttled to let happen. For this purpose, it has, for example, several notches (113) distributed around the circumference. The cross section can also have a circular area in which at least one relief hole is arranged. The spring plate (109) is seated on a rod (110), the center line of which is that of the through hole (41) coincides. The spring plate (109) is either part of the rod (110) or it sits in the middle of it centered, for example with the help of a cross-press fit. The rod (110) protrudes into the right of the longitudinal slide (97) arranged cup-shaped pressure balance pistons (80) inside to hit a grub screw (111). Here is the rod (110) in a bore (77) in the end face (81) of the pressure compensator piston (80) guided tightly. Since the spring plate (109), which is stationary in the longitudinal direction, comes together with the rod (110) in the two longitudinally movable valve parts (97) and (80) is stored, the outer envelope contour of the Spring plates (109) crowned. That way inter alia if the return spring (108) is tilted Tilt between the longitudinal slide (97) and the spring plate (109) avoided.

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 (116) auf, in dem dieser eingeschraubt sitzt. Um die Baulänge der Steuervorrichtung (1) 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 er an seinem äußeren freien Ende einen Innensechskant (117) 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 (116), in which it sits screwed. To the overall length of the control device (1) to make it short, the head of the locking screw (114) a cylindrical recess that the Includes a lock nut (112). To adjust and He counters the set screw (111) on its outer free end of a hexagon socket (117).

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. An im Area between head and thread seated sealing ring (118) seals the screw plug bore (42) to the outside.

In der Durchgangsbohrung (41) sitzt zwischen der Verschlußschraube (114) und dem Längsschieber (97) dichtgleitend der topfförmige Druckwaagenkolben (80). Letzterer hat eine zylindrische Außenkontur, die an ihrem rechten Ende einen Halbrundeinstich (84) aufweist, in dem ein Federring (89) eingesetzt ist. Der Federring (89) liegt - beispielsweise bei nicht durchströmter Steuervorrichtung - an einem als Anschlag dienenden inneren Gehäusebund an, der zwischen der Durchgangsbohrung (41) und der im Durchmesser größeren Verschlußschraubenbohrung (42) gebildet ist. Einen rechten Anschlag für den Druckwaagenkolben (80) bildet die Verstellschraube (114). Am linken Rand der Außenkontur des Druckwaagenkolbens (80) befinden sich mehrere auf dem Umfang verteilte Feinsteuerkerben (83), die von der linken Stirnseite her in den Druckwaagenkolben (80) eingearbeitet sind.In the through hole (41) sits between the screw plug (114) and the longitudinal slide (97) tightly sliding the Pot-shaped pressure balance pistons (80). The latter has a cylindrical one Outer contour that has a semicircular recess at its right end (84), in which a spring ring (89) is used is. The spring ring (89) is included - for example not flowed through control device - on one as a stop serving inner collar, which is between the through hole (41) and the larger diameter screw hole (42) is formed. A right stop The adjusting screw forms for the pressure compensator piston (80) (114). On the left edge of the outer contour of the pressure compensator piston (80) there are several distributed around the circumference Fine control notches (83) from the left face ago are incorporated into the pressure compensator piston (80).

Hinter dem Halbrundeinstich (84) ist der Druckwaagenkolben (80) angefast. Im Bereich vor dem Federring (89) trägt er eine Reihe von Kurzschlußnuten.The pressure compensator piston is behind the half-round groove (84) (80) chamfered. He carries in the area in front of the spring washer (89) a series of short-circuit 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 hole (87) for receiving the control spring (88) incorporated. The guide hole (87) is in her Reason narrowed to fix the control spring (88) radially. A bore (115) with a comparable contour is located in the left front of the adjustment screw (114).

Im Bereich der Druckwaage (70) befinden sich im Gehäuse (30) zwei Ringkanäle (71) und (74). Benachbart zum Zulaufringkanal (93) liegt der Rücklaufringkanal (71). Dieser Ringkanal (71) ist beispielsweise beim Heben einer Last, wenn der Hebenstrom gleich dem Pumpenstrom ist, durch den Druckwaagenkolben (80) vollständig geschlossen, während er bei Neutralumlauf geöffnet ist.In the area of the pressure compensator (70) there are in the housing (30) two ring channels (71) and (74). Adjacent to the inlet ring channel (93) is the return ring channel (71). This ring channel (71) is, for example, when lifting a load when the Lifting current is equal to the pump current through the pressure compensator piston (80) fully closed while in neutral circulation is open.

Zwischen dem Rücklaufringkanal (71) und der Verstellschraube (114) ist der Lastmeldekanal (74) angeordnet. Er steht mit der Verbindungsbohrung (56) über eine zur Durchgangsbohrung (41) parallele Lastmeldeleitung (12) in Verbindung. In der Lastmeldeleitung (12) ist eine Drosselstelle (11) angeordnet.Between the return ring channel (71) and the adjusting screw (114) the load reporting channel (74) is arranged. He stands with the connecting hole (56) over a through hole (41) parallel load signaling line (12) in connection. There is a choke point in the load signaling line (12) (11) arranged.

Das Senkenmodul (120) hat eine, von der Vorderseite (34) her, in das Gehäuse (30) hineinführende Sacklochbohrung (45), die parallel zur Durchgangsbohrung (41) des Hebenmoduls ausgerichtet ist. Die Sacklochbohrung (45) ist - wie auch im Hebenmodul (90) - links mit Hilfe des Proportionalmagneten (121) druckmitteldicht verschlossen.The sink module (120) has, from the front (34), in the housing (30) leading blind hole (45), the aligned parallel to the through hole (41) of the lifting module is. The blind hole (45) is - as in the lifting module (90) - on the left with the help of the proportional magnet (121) sealed pressure-tight.

Im rechten Bereich der Sacklochbohrung (45) sitzt eine Ventilbüchse (130), die zwei ineinandergeschachtelte Längsschieber (140) und (147) aufnimmt. Die Ventilbüchse (130) ist in der Sacklochbohrung (45) zwischen einem Bohrungsende und einem links angeordneten Schraubring (156) mit einem innenliegenden, durchgehenden Innensechskant axial gesichert. Der linke Bereich der Sacklochbohrung (45) ist dazu mit einem Innengewinde (128) versehen.A valve sleeve is located in the right area of the blind hole (45) (130), the two nested longitudinal slides (140) and (147). The valve sleeve (130) is in the blind hole (45) between a bore end and a screw ring (156) on the left with an internal continuous hexagon socket axially secured. Of the The left area of the blind hole (45) has an internal thread (128).

Die Ventilbüchse (130) ist von einem Verbraucherringkanal (125) umgeben, der mit dem in Figur 3 gezeigten Verbraucheranschluß (50) hydraulisch in Verbindung steht. Dazu führt vom Verbraucherringkanal (125) im Bereich zwischen dem Senken- (120) und Hebenmodul (90) tangential eine Verbraucherbohrung (54) weg. Die Verbraucherbohrung (54) mündet in das, im Bezug auf Figur 2, höher liegende Rückschlagventil (170), vgl. Figur 3.The valve sleeve (130) is from a consumer ring channel (125) surround that with the consumer connection shown in Figure 3 (50) is hydraulically connected. This leads from the consumer ring channel (125) in the area between the sink (120) and lifting module (90) tangentially a consumer bore (54) gone. The consumer bore (54) opens into the with reference to FIG. 2, higher-lying check valve (170), see. Figure 3.

Das Rückschlagventil (170) hat eine Ventilbohrung (47) in der Form eines Sackloches, die ungefähr in der halben Bohrungstiefe von der Verbraucherbohrung (54) tangential geschnitten wird. Die Ventilbohrung (47) ist an ihrem linken Ende als kegelmantelförmiger Ventilsitz (171) und im Bereich ihres rechten Endes als Verbraucheranschluß (50) mit Innengewinde ausgebildet. Im mittleren, zylindrischen Bereich sitzt ein federbelasteter Rückschlagschieber (173). Letzterer hat einen rohrförmigen Schaft (174), an dessem linken Ende sich ein kegelstumpfförmiger Ventilteller (175) befindet. Auf dem Schaft ist eine Schraubenfeder (176) angeordnet, die den Rückschlagschieber (173) gegen den Ventilsitz (171) drückt. Dazu liegt die Schraubenfeder (176) links über eine Dichtungs- und eine Unterlagsscheibe auf der Rückseite des Ventiltellers (175) an. Rechts stützt sie sich an einer sternförmigen Scheibe (177) ab, die über mindestens eine Distanzscheibe an einem in der Ventilbohrung (47) sitzenden Sicherungsring (178) anliegt. Die Sternscheibe (177) hat einen zentralen, nach links kragenden Bolzen, auf dem der rohrförmige Schaft (174) des Rückschlagschiebers (173) geführt ist.The check valve (170) has a valve bore (47) in the Shape of a blind hole that is roughly half the depth of the hole cut tangentially from the consumer bore (54) becomes. The valve bore (47) is conical at its left end Valve seat (171) and in the area of your right End designed as a consumer connection (50) with an internal thread. In the middle, cylindrical area sits a spring-loaded Check valve (173). The latter has one tubular shaft (174), at the left end of which is a frustoconical Valve disc (175) is located. On the shaft a coil spring (176) is arranged, which the check valve (173) presses against the valve seat (171). This lies the coil spring (176) on the left via a seal and a Washer on the back of the valve plate (175) on. On the right it is supported by a star-shaped one Disc (177) from at least one spacer a circlip located in the valve bore (47) (178) is present. The star disc (177) has a central, left cantilevered bolt on which the tubular Shaft (174) of the check valve (173) is guided.

In Figur 2 ist links neben dem Schraubring (156) die Einstellschraube (150) dargestellt. Die Einstellschraube (150) sitzt im Innengewinde (128). Das Innengewinde ist zwischen der Einstellschraube (150) und dem Schraubring (156) von einem Rücklaufringkanal (126) unterbrochen. Der Rücklaufringkanal (126) steht mit der Unterseite (33) des Gehäuses (30) über die Rücklaufbohrung (66) und mit dem Rücklaufringkanal (94) des Hebenmoduls (90) über die Rücklaufquerbohrung (59) in Verbindung. Die Rücklaufquerbohrung (59) ist von der das Senkenmodul (120) begrenzenden Seitenfläche (39) her mittels eines Verschlußstopfens (61) druckmitteldicht verschlossen.In Figure 2, the adjusting screw is to the left of the screw ring (156) (150). The adjusting screw (150) sits in the internal thread (128). The internal thread is between the adjusting screw (150) and the screw ring (156) from one Return ring channel (126) interrupted. The return ring channel (126) stands with the underside (33) of the housing (30) over the return bore (66) and with the return ring channel (94) of the lifting module (90) via the return cross bore (59) in connection. The return cross bore (59) is from the side surface (39) delimiting the sink module (120) closed by means of a sealing plug (61) in a pressure-tight manner.

Das Senkenmodul (120), das primär die Einstellschraube (150) und die Ventilbüchse (130) mit den beiden Längsschiebern (140) und (147) umfaßt, ist mit Ausnahme einer auf der Einstellschraube (150) angeordneten Verzahnung (151) aus der DE 41 40 604 Al bekannt. Im folgenden wird daher der Aufbau des Senkenmoduls (120) ausschließlich anhand seiner Wirkungsweise beschrieben.The sink module (120), primarily the adjusting screw (150) and the valve sleeve (130) with the two longitudinal slides (140) and (147), with the exception of one on the Adjusting screw (150) arranged toothing (151) from the DE 41 40 604 Al known. The following is therefore the structure of the sink module (120) solely on the basis of its mode of action described.

Das Senkenmodul (120) ist in Figur 2 in Sperrstellung dargestellt. Das Druckmittel, das am Verbraucheranschluß (50) und damit über die Verbraucherbohrung (54) am Verbraucherringkanal (125) ansteht, kann nicht in den Rücklaufringkanal (126) 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 dem Ringraum (134). Um den Hauptsteuerschieber (140) auf dem Hauptventilsitz (132) zu halten, steht auf seiner rechten Stirnseite in einem Druckraum (135) Druckmittel unter Lastdruck 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 in einem Verbraucherdruckraum (136) anstehenden Druckes. Der Verbraucherdruckraum (136) liegt im Bereich der Außenkontur des Hauptsteuerschiebers (140) zwischen Hauptventilkegel (141) und Kurzschlußnuten. Bei geschlossenem Senkenmodul (120) stehen beide Druckräume (135) und (136) unter dem am Verbraucheranschluß (50) anliegenden Lastdruck.The sink module (120) is shown in Figure 2 in the locked position. The pressure medium at the consumer connection (50) and thus via the consumer bore (54) on the consumer ring channel (125) is present, cannot enter the return ring channel (126) stream. The one stored directly in the valve sleeve (130) Longitudinal slide, the main control slide (140), stands with his Main valve cone (141) on the main valve seat (132) of the valve sleeve (130). His - arranged at his left end - The main control notches (142) are hidden under the cylinder seat (133) next to the annulus (134). Around the main spool (140) on the main valve seat (132), stands on its right end in a pressure chamber (135) Pressure medium under load pressure. 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 a control groove (143) with the bottom of its bore. The contact pressure is diminished by the opposite Force due to the pressure in a consumer pressure chamber (136) Pressure. The consumer pressure space (136) is in the range the outer contour of the main control spool (140) between Main valve plug (141) and short-circuit grooves. When closed Sink module (120) are under both pressure chambers (135) and (136) the load pressure present at the consumer connection (50).

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 Rücklaufringkanal (126) mit der Rücklaufbohrung (66) 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 Rücklaufringkanal (126). 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 to the right. This will get his input tax notches (149) under the control groove (143) of the main control spool (140). At the same time, the one on the left lifts Valve plug (148) from its in the main spool (140) corresponding valve seat (146). The pressure room (135) is now over the longitudinal bore (145), the control groove (143), the pilot notches (149), the valve seat (146) and the return ring channel (126) in connection with the return bore (66). Depending on the opening cross section of the pilot notches (149) the pressure in the pressure chamber (135) drops. The one there Pressure arises according to the ratio of the cross section the throttle bore (144) and the opening cross-section the pilot notches (149). Falls accordingly far to the right pushed pilot spool (147) the pressure in 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 from the main valve seat (132) and the main control notches (142) enter the area of the Annulus (134). The pressure medium flows from the consumer coming, between the valve sleeve (130) and the main spool (140) towards the return ring channel (126). Of the Main control spool (140) hurries through its opening movement the pilot spool (147), whereby the opening cross-section on the pilot notches (149) becomes smaller. So that can a higher one in the pressure chamber (135) via the throttle bore (144) Build up pressure. Consequently, the opening movement of the Main spool (140) braked until there is an equilibrium sets.

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 Senkenmodul (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 on the pilot spool (147) and on the Adjusting screw (150). When moving the spool (147) the pilot control notches (149) are closed. The pressure in the pressure chamber (135) increases. The main poppet (141) puts on the main valve seat (132). The sink module (120) locks. The sink module (120) thus reworks Kind of a sequential control.

Um die Vorspannkraft der Rückstellfeder (155) bei montierter Steuervorrichtung einstellen zu können, weist die Einstellschraube (150) im mittleren Bereich ihrer Außenkontur eine Schrägverzahnung auf, in die zumindest zeitweise die Verzahnung einer Einstellschnecke (152) eingreift. Die Einstellschnecke sitzt dazu in einer Einstellbohrung (68), die sich hier von der Rückseite (35) bis in die Sacklochbohrung (45) erstreckt und die Rücklaufquerbohrung (59) sowie den Rücklaufringkanal (126) tangiert. Die Einstellschnecke (152) kann mit Hilfe einer Einstellspindel, deren freies Ende aus dem Gehäuse (30) ragt, oder einem Spezialwerkzeug, das zeitweise mit der Einstellschnecke (152) stirnseitig gekuppelt werden kann, in Drehung versetzt werden. Je nach Drehrichtung der Einstellspindel bzw. der Einstellschnecke (152) 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 gearing, at least temporarily the gearing an adjusting screw (152) engages. The adjusting screw sits in an adjustment hole (68) here from the back (35) into the blind hole (45) extends and the return cross bore (59) and the return ring channel (126) affects. The adjusting screw (152) can with the help of an adjusting spindle, the free end of which Housing (30) protrudes, or a special tool that temporarily be coupled on the face side with the adjusting screw (152) can be rotated. Depending on the direction of rotation Adjusting spindle or the adjusting screw (152) becomes the adjusting screw (150) in the internal thread (128) to the right or screwed left. The length of the adjustment range corresponds largely the width of the toothing (151) of the adjusting screw (150).

Beim Heben der Last strömt bei bestromtem Proportionalmagneten (91) Druckmittel über den Pumpenanschluß (49), den Zulaufringkanal (93), den Längsschieber (97) und die Verbindungsbohrung (56) in die Ventilbohrung (47) vor den Rückschlagschieber (173) des in Figur 3 gezeigten Rückschlagventils (170). Das Öffnen des Längsschiebers (97) erfolgt über seine Feinsteuerkerben (103). Sie bilden im Bezug auf die Druckwaage (70) die Meßdrossel. Das Druckmittel fließt auf dem Weg zum Rückschlagventil (170) über die Lastmeldeleitung (12) und den Lastmeldekanal (74) auf die Rückseite des Druckwaagenkolbens (80). Durch diese Beschaltung der Druckwaage (70) liegt vor und hinter den Feinsteuerkerben (103) immer ein konstantes Druckgefälle an, dessen Größe durch die Federkraft der Regelfeder (88) bestimmt ist. Sobald die Kraft auf der Vorderseite des Ventiltellers (175) aufgrund des anstehenden Pumpendrucks die Summe aus der Federkraft und dem Produkt aus Lastdruck und rückseitiger Ventiltellerfläche übersteigt, öffnet das Rückschlagventil (170) und die Last beginnt sich zu heben bzw. der Kolben (8) beginnt auszufahren. Der Längsschieber (97) und der Druckwaagenkolben (80) ermöglichen eine lastunabhängige Steuerung des Volumenstroms zum Verbraucheranschluß (50).When lifting the load, the proportional magnet is energized (91) Pressure medium via the pump connection (49), the inlet ring channel (93), the longitudinal slide (97) and the connecting hole (56) in the valve bore (47) in front of the check valve (173) of the check valve shown in Figure 3 (170). The longitudinal slide (97) is opened via his fine tax scores (103). They form in relation to the Pressure compensator (70) the measuring throttle. The pressure medium flows on the way to the check valve (170) via the load signaling line (12) and the load signaling channel (74) on the back of the Pressure balance piston (80). Through this connection of the pressure compensator (70) is in front of and behind the fine control notches (103) always a constant pressure drop, the size of which by the Spring force of the control spring (88) is determined. Once the strength on the front of the valve plate (175) due to the upcoming Pump pressure the sum of the spring force and the Product of load pressure and rear valve plate surface the check valve (170) opens and the load begins to rise or the piston (8) begins to extend. The longitudinal slide (97) and the pressure compensator piston (80) enable load-independent control of the volume flow to the consumer connection (50).

Zum Beenden des Hebens der Last wird der Proportionalmagnet (91) abgeschaltet. Der Längsschieber (97) und der Rückschlagschieber (173) gehen in ihre Schließstellungen, wie sie in Figur 2 gezeigt sind.The proportional magnet is used to stop lifting the load (91) switched off. The longitudinal slide (97) and the non-return slide (173) go into their closed positions like them are shown in Figure 2.

Figur 5 zeigt den Hydraulikschaltplan für eine mit der Steuervorrichtung (1) vergleichbare Steuervorrichtung (2). Die Druckwaage (70) in Figur 5 ist jedoch weiterlaufbelastbar. Dabei wird der bisherige Rücklaufanschluß (53) zu einem weiterlaufbelastbaren, zweiten Verbraucheranschluß (51). Ferner wird der vom 3/2-Wegeventil (90) zum Rückschlagventil (170) geleitete Druckmittelstrom steuerbar über den Druckwaagenkolben (80) der Druckwaage (70) geführt. Figure 5 shows the hydraulic circuit diagram for a with the control device (1) comparable control device (2). The The pressure compensator (70) in FIG. 5 can, however, continue to be loaded. The previous return connection (53) becomes a loadable, second consumer connection (51). Further becomes from the 3/2-way valve (90) to the check valve (170) guided pressure medium flow controllable via the pressure compensator piston (80) of the pressure compensator (70).

Die Weiterlaufbelastbarkeit der Druckwaage (70) führt zu einigen Änderungen an der Steuervorrichtung (1). Die Änderungen sind den Figuren 6 bis 8 in einer Steuervorrichtung (2) verwirklicht.The resilience of the pressure compensator (70) leads to some Changes to the control device (1). The changes Figures 6 to 8 are realized in a control device (2).

Am Gehäuse (30) der Steuervorrichtung (2) hat sich die Lage des Rückschlagventils (170) verändert, vgl. Figur 7 und 8. Die Mittellinie des Rückschlagventils (170) verläuft hier zwar immer noch parallel zu der aus den beiden Mittellinie des Heben- (90) und des Senkenmoduls (120) gebildeten Ebene, aber nicht parallel zu deren Mittellinien selbst, sondern senkrecht dazu. Folglich liegt der Verbraucheranschluß (50) auf der Seitenfläche (39), die nun T-förmig gestaltet ist.The position on the housing (30) of the control device (2) of the check valve (170) changed, cf. Figures 7 and 8. The center line of the check valve (170) runs here still parallel to that from the two center lines the lifting (90) and the lowering module (120) formed plane, but not parallel to their center lines themselves, but perpendicular to it. Consequently, the consumer connection (50) on the side surface (39), which is now T-shaped.

Nach Figur 6 führt im Hebenmodul (90) von dem Verbindungsringkanal (95) ein Gehäusekanal (64) zumindest bereichsweise parallel zur Durchgangsbohrung (41) in einen Lastmelderingkanal (75), der sich zwischen der Verschlußschraube (114) und dem Druckwaagenkolben (80) befindet.According to Figure 6 leads in the lifting module (90) from the connecting ring channel (95) a housing channel (64) at least in some areas parallel to the through hole (41) in a load signaling ring channel (75), which is between the screw plug (114) and the pressure compensator piston (80).

Im Bereich des Druckwaage (70) ist neben dem Rücklaufringkanal (71) ein Verbraucherringkanal (72) und ein Lastmelderingkanal (75) angeordnet. An den Rücklaufringkanal (71) können bei dieser Ausführungsform weitere Verbraucher angeschlossen werden, vgl. Figur 5, Verbraucheranschluß (51). Der Verbraucherringkanal (72) führt über einen Flachkanal (62) zur Ventilbohrung (47) des Rückschlagventils (170).In the area of the pressure compensator (70) is next to the return ring channel (71) a consumer ring channel (72) and a load signaling channel (75) arranged. To the return ring channel (71) in this embodiment, additional consumers are connected be, cf. Figure 5, consumer connection (51). The consumer ring channel (72) leads via a flat channel (62) to the valve bore (47) of the check valve (170).

Die gegenüber der ersten Ausführungform geänderte Außenkontur des Druckwaagenkolbens (80) ist an ihrem linken Rand angefast. An ihrem rechten Ende weist sie eine Taille auf, die zur rechten Stirnseite hin in einen Anschlagflansch (85) übergeht. Der Anschlagflansch (85), dessen Durchmesser den Durchmesser des Druckwaagenkolbens in der Zone mit den Kurzschlußnuten übersteigt, weist eine Vielzahl von Durchbrüchen (86) auf. Über die Durchbrüche (86) gelangt das Druckmittel - sofern der Anschlagflansch an der linken Wandung des Lastmelderingkanals (75) anliegt - in den Bereich der Taille und über eine an sie anschließende, angefaste Steuerkante über den Verbraucherringkanal (72) in den Flachkanal (62). Die Steuerkante sitzt dazu annähernd mittig in dem Verbraucherringkanal (72). Die ebenfalls eine Steuerkante bildende Fase am linken Rand der Außenkontur endet kurz vor dem Rücklaufringkanal (71).The outer contour changed compared to the first embodiment of the pressure compensator piston (80) is chamfered on its left edge. At her right end she has a waist that to the right end in a stop flange (85) transforms. The stop flange (85), the diameter of which Diameter of the pressure compensator piston in the zone with the short-circuit grooves has a variety of breakthroughs (86). The pressure medium passes through the openings (86) - if the stop flange on the left wall of the Load signaling channel (75) lies - in the area of the waist and via a chamfered control edge adjoining it via the consumer ring channel (72) into the flat channel (62). The control edge sits approximately in the middle of the consumer ring channel (72). The one that also forms a control edge Chamfer on the left edge of the outer contour ends just before the return ring channel (71).

Bei der Steuervorrichtung (2) ist somit eine lastdruckunabhängige Steuerung des Volumenstroms zum ersten Verbraucheranschluß (50) auch dann möglich, wenn der Weiterlauf über den zweiten Verbraucheranschluß (51) druckbelastet ist, da der Druckwaagenkolben (80) eine zusätzliche Steuerkante aufweist.The control device (2) is therefore independent of the load pressure Control of the volume flow to the first consumer connection (50) also possible if the continuation via the second consumer port (51) is pressurized because of Pressure balance piston (80) has an additional control edge.

Eine dritte Ausführungsform der hydraulischen Steuervorrichtung ist den Figuren 9 und 10 zu entnehmen. Die hier gezeigte Steuervorrichtung (3) ist für ein LS-Hydrauliksystem geeignet. Dazu sitzt die Druckwaage (70) im Gegensatz zu den beiden zuvor beschriebenen Ausführungsformen, vgl. Figur 1 und 5, nicht mehr im Nebenzweig (10), sondern ist dem 3/2-Wegeventil (90) direkt vorgeschaltet. Die übrige Schaltung, einschließlich dem Lastmeldesystem entspricht der Schaltung aus Figur 1. Zusätzlich wird zur Ansteuerung der die Steuervorrichtung (3) versorgenden Verstellpumpe (6), vgl. Figur 10, eine Steuerleitung (19) aus der Lastmeldeleitung (12) zwischen der Drosselstelle (11) und der Druckwaage (70) abgezweigt, womit zwischen dem Pumpenanschluß (49) und der Steuerleitung (19) das Regeldruckgefälle des LS-Hydrauliksystems anliegt.A third embodiment of the hydraulic control device can be seen in Figures 9 and 10. The one shown here Control device (3) is suitable for an LS hydraulic system. In addition, the pressure compensator (70) sits in contrast to the two previously described embodiments, cf. Figure 1 and 5, no longer in the secondary branch (10), but is the 3/2-way valve (90) directly upstream. The rest of the circuit, including the load reporting system corresponds to the circuit from Figure 1. In addition, for controlling the control device (3) supplying variable displacement pump (6), cf. Figure 10, a control line (19) from the load reporting line (12) branched off between the throttle point (11) and the pressure compensator (70), with which between the pump connection (49) and the control line (19) the control pressure drop of the LS hydraulic system is present.

Die Figur 10 zeigt die dritte Steuervorrichtung (3) im Schnitt. Sie weicht konstuktiv im Bereich des Hebenmoduls (90) und der Druckwaage (70) von der Steuervorrichtung (1) ab. FIG. 10 shows the third control device (3) in the Cut. It constructively gives way in the area of the lifting module (90) and the pressure compensator (70) from the control device (1) off.

Der Pumpenanschluß (49) führt zu einem Zwischenringkanal (73), der die Durchgangsbohrung (41) im mittleren Bereich des Druckwaagenkolbens (80) durchdringt. In der Mitte des Zwischenringkanals (73) beginnt - bei der in Figur 10 dargestellten Position des Druckwaagenkolbens - eine in der Außenkontur angeordnete Steuernut (82) mit ihrer rechten Wandung. Die Steuernut (82) erstreckt sich nach links bis hinein in den Zulaufringkanal (93). Dort geht die Steuernut (82) in Feinsteuerkerben (83) über. Die Feinsteuerkerben (83) enden vor der Stirnseite (81) des Druckwaagenkolbens (80).The pump connection (49) leads to an intermediate ring channel (73) of the through hole (41) in the central area of the pressure compensator piston (80). In the middle of Intermediate ring channel (73) begins - at that shown in Figure 10 Position of the pressure compensator piston - one in the outer contour arranged control groove (82) with its right wall. The control groove (82) extends to the left into the inlet ring channel (93). The control groove (82) goes in there Fine control notches (83) over. The fine control notches (83) end in front of the end face (81) of the pressure compensator piston (80).

Mit dem Öffnen des Hebenmoduls (90) fließt Druckmittel unter Stand-by-Druck von der Verstellpumpe (6) kommend in den Verbindungsringkanal (95) und von dort über die Lastmeldeleitung (12), den Lastmelderingkanal (75) und die Steuerleitung (19) zur Pumpenregelung. Der Pumpendruck steigt entsprechend der anstehenden Last an. Sobald Druckmittel zum Verbraucher strömt, bestimmt das Druckgefälle am Längsschieber (97) und der Öffnungsquerschnitt der Feinsteuerkerben (103) den Volumenstrom. Die Druckwaage (70) hält das Druckgefälle immer konstant. Dies gilt auch bei einer Parallelbetätigung von mehreren Verbrauchern.When the lifting module (90) is opened, pressure medium flows in Stand-by pressure from the variable displacement pump (6) coming into the connecting ring channel (95) and from there via the load reporting line (12), the load signaling channel (75) and the control line (19) for pump control. The pump pressure rises accordingly the pending load. As soon as pressure medium to the consumer flows, determines the pressure drop at the longitudinal slide (97) and the opening cross section of the fine control notches (103) the volume flow. The pressure compensator (70) holds that Pressure drop always constant. This also applies to parallel operation from multiple consumers.

Claims (14)

  1. Hydraulic control of monobloc design for raising and lowering a load, with at least two electromagnetically actuable proportional directional valve elements, with a non-return valve and with a pressure balance for raising the load independently of the load pressure, the said pressure balance functioning as an input element, 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 next to one another on the same side and, in particular, at the same height,
    in that a piston (80) of the pressure balance (70) is arranged coaxially, next to a longitudinal slide (97) of the first proportional directional valve element (90), in a bore (41) guiding and supporting the two valve elements (80) and (97),
    in that the longitudinal slide (97) of the first proportional directional valve element (90) is spring-loaded, at least one component (109, 110) for adjusting the prestress and supporting a spring (108) on the housing (30) of the control (1, 2, 3) being led through the pressure-balance piston (80).
  2. Hydraulic control according to Claim 1, characterized in that the component (109, 110) is mounted and guided in a bore (105) of the longitudinal slide (97) and in a bore (77) of the pressure-balance piston (80).
  3. Hydraulic control according to Claim 1 or 2, characterized in that the component (109, 110) has a cylindrical rod-shaped portion (110), which is guided in the bore (77), and a disc-shaped portion (109), which is guided in the bore (105).
  4. Hydraulic control according to Claims 1 to 4, characterized in that the disc-shaped portion (109), on which the spring (108) bears, has a convex outer contour, in the region of contact with the bore (105), the outer contour being a zone of an ellipsoid, the rotational axis of which lies on the imaginary centre line of the component (110).
  5. Hydraulic control according to Claim 3, characterized in that the disc-shaped portion (109) has perforations or indentations in its cross-section perpendicular to the rotationally symmetrical centre line of its outer contour.
  6. Hydraulic control according to Claim 5, characterized in that radially oriented notches (113) are arranged as indentations in the disc-shaped portion (109).
  7. Hydraulic control according to Claim 1, characterized in that the bore (41) is a passage bore, the diameter of which is constant at least in the region of the mounting and guidance of the valve elements (80) and (97).
  8. Hydraulic control according to one of the preceding Claims 1 to 5, characterized in that there is arranged next to the pressure balance (70) at the end of the bore (41) a closing element (114) having an internal thread (116), in which a setscrew (111) is screwed as an adjustable stop for the component (109, 110).
  9. Hydraulic control according to Claim 1, characterized in that, in an embodiment (1) and (2) for OC hydraulic circuits, both the second proportional directional valve element (120) and the pressure balance (80) each have a separate connection (53) and (53 or 51) located hydraulically downstream.
  10. Hydraulic control 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 shut-off state, the said inner longitudinal slide bears on a valve seat (146) in the outer longitudinal slide (140).
  11. Hydraulic control according to Claim 10, characterized in that the prestress of the spring (155) can be adjusted by means of an adjusting screw (150) arranged in the housing (30).
  12. Hydraulic control 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, 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).
  13. Hydraulic control according to at least one of Claims 1 to 12, characterized in that the two proportional directional valve elements (90) and (120) are interlinked via a separate non-return valve (170) which is connected as a switch during the lowering function.
  14. Hydraulic control according to one of Claims 1 to 13, characterized in that the first proportional directional valve element (90) is a single-stage, directly actuated valve, and the second proportional directional valve element (120) is a valve with a preliminary stage, namely the inner longitudinal slide (147), and with a main stage, namely the outer longitudinal slide (140), there being arranged on the outer contour of the longitudinal slide (140) a main valve cone (141) and main control notches (142) which are connected in series into the working stream.
EP95937771A 1994-12-23 1995-11-16 Hydraulic control system of monobloc construction for raising and lowering a load with at least two electromagnetic proportional two-way valve elements Expired - Lifetime EP0799384B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4446145 1994-12-23
DE4446145A DE4446145A1 (en) 1994-12-23 1994-12-23 Hydraulic control in monoblock design for lifting and lowering a load with at least two electromagnetically actuated proportional directional control valve elements
PCT/DE1995/001595 WO1996020348A1 (en) 1994-12-23 1995-11-16 Hydraulic control system of monobloc construction for raising and lowering a load with at least two electromagnetic proportional two-way valve elements

Publications (2)

Publication Number Publication Date
EP0799384A1 EP0799384A1 (en) 1997-10-08
EP0799384B1 true EP0799384B1 (en) 1998-07-22

Family

ID=6536811

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95937771A Expired - Lifetime EP0799384B1 (en) 1994-12-23 1995-11-16 Hydraulic control system of monobloc construction for raising and lowering a load with at least two electromagnetic proportional two-way valve elements

Country Status (7)

Country Link
US (1) US5839345A (en)
EP (1) EP0799384B1 (en)
JP (1) JP3654364B2 (en)
KR (1) KR100409141B1 (en)
CN (1) CN1079917C (en)
DE (2) DE4446145A1 (en)
WO (1) WO1996020348A1 (en)

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DE19649833A1 (en) * 1996-12-02 1998-06-04 Bosch Gmbh Robert Electro-hydraulic control device
DE29713294U1 (en) 1997-07-25 1997-09-25 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulic control device for a tipper vehicle
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JP2007263142A (en) * 2006-03-27 2007-10-11 Toyota Industries Corp Hydraulic control device
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JP4729456B2 (en) * 2006-08-21 2011-07-20 株式会社豊田自動織機 Hydraulic control device
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KR987000522A (en) 1998-03-30
US5839345A (en) 1998-11-24
JP3654364B2 (en) 2005-06-02
DE4446145A1 (en) 1996-06-27
EP0799384A1 (en) 1997-10-08
JPH11500810A (en) 1999-01-19
CN1079917C (en) 2002-02-27
CN1171146A (en) 1998-01-21
KR100409141B1 (en) 2004-04-03
WO1996020348A1 (en) 1996-07-04
DE59502932D1 (en) 1998-08-27

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