EP0799384A1 - 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

Info

Publication number
EP0799384A1
EP0799384A1 EP95937771A EP95937771A EP0799384A1 EP 0799384 A1 EP0799384 A1 EP 0799384A1 EP 95937771 A EP95937771 A EP 95937771A EP 95937771 A EP95937771 A EP 95937771A EP 0799384 A1 EP0799384 A1 EP 0799384A1
Authority
EP
European Patent Office
Prior art keywords
bore
hydraulic control
valve
control according
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.)
Granted
Application number
EP95937771A
Other languages
German (de)
French (fr)
Other versions
EP0799384B1 (en
Inventor
Hartmut Sandau
Werner Schumacher
Rainer Trucksess
Holger Lueues
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0799384A1 publication Critical patent/EP0799384A1/en
Application granted granted Critical
Publication of EP0799384B1 publication Critical patent/EP0799384B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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 in a monoblock design for lifting and lowering a load with at least two electromagnetically actuated proportional travel valve elements, a check valve and a pressure compensator for lifting the load independently of the load as an input element, the elements being at least partially housed in a housing are arranged, which has at least one pump connection, at least one consumer connection and at least one return connection.
  • the drives, actuating elements and connections are arranged on almost all housing sides of the monoblock in the case of hydraulic controls in a monoblock design.
  • controls with large external dimensions result, despite the compact design, since the drives in particular often lie opposite one another or protrude from the housings in a corner arrangement.
  • such controls usually have long and complicated designs
  • the hydraulic control according to the invention enables a small construction volume with regard to its housing dimensions and the overall size of the monoblock.
  • the individual valve elements are arranged closely next to one another and are connected to one another via short bores or channels.
  • 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 bore 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 aforementioned load is arranged in a second parallel bore in the form of a blind hole. It ends together with the first hole on a flat face of the common housing.
  • the electromagnetic drives are arranged directly next to one another on this end face, as a result of which the drives can also be controlled mechanically with simple means.
  • a check valve which prevents the pressure medium from flowing back from a consumer connection into the proportional directional valve element for lifting.
  • Figure 1 Hydraulic circuit diagram of a control device for an OC hydraulic system with two electromagnetically operated proportional directional control valve elements, a pressure compensator and a check valve without continued load carrying capacity;
  • Figure 2 Section through a control device according to Figure 1;
  • Figure 3 Section through the check valve of Figure 1;
  • FIG. 4 Side view of the control device according to Figures 2 and 3;
  • FIG. 5 hydraulic circuit diagram as in FIG. 1, but for a control device which can continue to run;
  • Figure 6 Section through a control device according to Figure 5;
  • Figure 7 Section through the check valve of Figure 5;
  • FIG. 8 Side view of the control device according to Figures 6 and 7;
  • FIG. 9 hydraulic circuit diagram as in FIG. 1, but for an LS hydraulic system
  • Figure 10 Section through a control device according to Figure 9.
  • FIG. 1 shows a basic structure of a hydraulic control device (1) for an OC hydraulic system with two electromagnetically actuated proportional directional control valve elements (90) and (120), a pressure compensator (70) and a check valve (170 ).
  • This control device (1) and also those from FIGS. 5 and 9 each serve to control a single-acting hydraulic cylinder (7), cf. Figure 3, which is part of a self-propelled machine, for example.
  • Both proportional directional control valve elements (90) and (120) are throttling directional control valves, the longitudinal spools of which can assume any intermediate positions in addition to the two end positions. They each have a proportional magnet (91, 121) on one side and a return spring (108, 155) on the other side.
  • the first proportional directional valve element (90) is a 3/2-way valve and the second (120) is a 2/2-way valve.
  • the pressure medium flow coming from a pump connection (49) flows via 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 single-acting hydraulic cylinder (7) for lifting a load.
  • the proportional directional valve element (90) is therefore described below
  • the 2/2-way valve (120) controls the pressure medium flow from the single-acting hydraulic cylinder (7) under load via the consumer connection (50) via 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 arranged in a secondary branch (10), which is open during a neutral circulation and guides the unnecessary pressure medium flow almost unthrottled into a second return line (17).
  • the return line (17) ends in a return connection (53).
  • a load signaling line (12) with a throttle valve (11) is connected to the pressure compensator (70) and branches off from the connecting line (13).
  • the load signal line (12) is connected to the return line (16) when the 3/2-way valve (90) is not actuated.
  • the proportional magnet (91) of the lifting module (90) is energized to lift a load.
  • the return cross line (14) is blocked and pressure medium is conducted via the lifting module (90), the connecting line (13) and the check valve (170) to the consumer connection (50). This is about the
  • Load signaling line (12) acts on the pressure compensator (70) on its spring-loaded side, whereby the pump current is throttled to the load pressure present at the consumer connection (50).
  • the proportional magnet (121) of the lowering module (120) is activated in the case of a normally undisturbed proportional magnet (91).
  • the pressure medium flows from the consumer connection (50) via the sink module (120) and the return line (16) to the return connection (52).
  • the implemented control device (1) is shown in section in FIG. It has a substantially cuboid housing (30) with two approximately square, flat surfaces as the top and bottom (31) and (33), cf. Figure 4.
  • the top and bottom (31) and (33) have two fastening bores (69, 69 '), cf. Figure 6, which penetrate the housing (30) perpendicular to the sectional plane.
  • the housing On the upper side (31), the housing has a housing extension (32) approximately in the center, cf. Figure 4.
  • the side surfaces (34, 35, 38, 39) oriented perpendicular to the cut surface each have a rectangular outline.
  • the front (34) and the back (35) are two flat, T-shaped and finely machined surfaces.
  • the two proportional magnets (91) and (121) are flanged to the front (34). Compared to the first proportional magnet (91) there is a screw plug (114) in the rear (35), cf. Figure 2.
  • the consumer connection (50) is located diagonally above it, cf. Figure 3.
  • the other two side surfaces (38, 39) have bulges which are formed around the fastening bores (69, 69 '), cf. 6.
  • the side surface lying at the bottom in FIG. 2 has a connecting piece for receiving the pump connection (49).
  • the pump connection (49) with an internal thread merges into an inlet ring channel (93) in the housing (30).
  • the annular channel (93) penetrates a cylindrical through bore (41), which extends from the front (34) to the rear (35).
  • the longitudinal slide (97) of the lifting module (90) is located in the left area of the through hole (41). There, two further channels (94, 95) meet the through hole (41).
  • the left one (94) is a return ring channel which is connected to a return transverse bore (59) leading to the lowering module (120).
  • To the right of this return ring channel (94) is the connecting ring channel (95) from which the connecting channel (56) branches off almost tangentially from the sectional plane.
  • the longitudinal slide (97) of the lifting module (90) either connects the connecting ring channel (95) with the return ring channel (94) or - in the actuated state - with the inlet ring channel (93) in the unactuated state with zero overlap.
  • the cylindrical outer contour of the longitudinal slide (97) has an annular groove (99).
  • the annular groove merges into fine control notches (103) in the area of its right-hand shaft collar, which have the function of a measuring throttle in connection with the pressure compensator (70).
  • the opening cross-sections of the fine control notches (103) decrease in the direction of the inlet ring channel (93), but without reaching them - when the proportional magnet (91) is de-energized.
  • the fine control notches (103) are round notches here, for example.
  • the longitudinal slide (97) On the left edge of the outer contour of the longitudinal slide (97) there is a recess in the area of the sealing ring between the proportional magnet (91) and the housing (30). Below this recess, the longitudinal slide (97) has a cylindrical recess (104), at the bottom of which the armature plunger (92) of the proportional magnet (91) is present. There are several short-circuit grooves in the outer contour between the groove and the ring groove (99).
  • the longitudinal slide (97) is drilled out in steps from its right end face (98).
  • the right area of the stepped bore (105) serves to guide the return spring (108).
  • the left area has a smaller diameter and connects the step bore (105) with the depression (104) via an oblique compensating bore (106).
  • the transition from the right to the left area of the stepped bore (105) is formed by a flat housing collar on which the return spring (108) is supported.
  • the other end of the return spring (108) rests on a stepped spring plate (109).
  • the spring plate (109) is star-shaped in cross section - perpendicular to the imaginary center line of the through bore - in order to allow the pressure medium to pass unthrottled for the pressure compensation at the longitudinal slide (97).
  • the cross section can also have a circular area in which at least one relief bore is arranged.
  • the spring plate (109) sits on a rod (110), the center line of which coincides with that of the through bore (41).
  • the spring plate (109) is either part of the rod (110) or it is centered on it, for example with the aid of a cross-press seat.
  • the rod (110) protrudes into the cup-shaped pressure compensator piston (80) arranged to the right of the longitudinal slide (97) in order to hit a threaded pin (111) there.
  • the rod (110) is guided in a bore (77) in the end face (81) of the pressure compensator piston (80) in a tightly sliding manner.
  • the outer envelope contour of the spring plate (109) is spherical. In this way, mutual tilting between the longitudinal slide (97) and the spring plate (109) is avoided, inter alia, when the return spring (108) is tilted.
  • the set screw (111) extends in the extension of the rod (110) and ends in the screw plug (114).
  • the locking screw (114) has an internal thread (116) in which it is screwed.
  • the head of the locking screw (114) has a cylindrical recess which serves to receive a lock nut (112).
  • the threaded pin (111) it has a hexagon socket (117) at its outer free end.
  • the through hole (41) merges at its right end into a screw hole (42).
  • the locking screw (114) is fastened in the internal thread of the bore (42).
  • a sealing ring (118) in the area between the head and the thread seals the screw plug bore (42) from the outside.
  • the cup-shaped pressure compensator piston (80) sits in the through hole (41) between the screw plug (114) and the longitudinal slide (97) in a tightly sliding manner.
  • the latter has a cylindrical outer contour which has a semicircular recess (84) at its right end, in which a spring ring (89) is inserted.
  • the spring ring (89) lies - for example when the control device is not flowed through - against an inner housing collar serving as a stop, which is formed between the through bore (41) and the larger diameter screw bore (42).
  • the adjusting screw (114) forms a right stop for the pressure compensator piston (80).
  • On the left edge of the outer contour of the pressure compensating piston (80) there are several fine control notches (83) distributed around the circumference, which are worked into the pressure compensating piston (80) from the left end face.
  • the pressure compensator piston (80) is chamfered behind the semicircular groove (84). In the area in front of the spring washer (89), it has a series of short-circuit grooves.
  • a guide bore (87) for receiving the regulating spring (88) is machined into the pressure compensator piston (80) from its right end.
  • the bottom of the guide bore (87) is narrowed in order to radially fix the control spring (88).
  • a bore (115) with a comparable contour is also in the left end of the adjusting screw (114).
  • the return ring channel (71) is adjacent to the inlet ring channel (93). This ring channel (71) is completely closed by the pressure compensator piston (80), for example when a load is lifted, when the lifting current is equal to the pump current, while it is open during neutral circulation.
  • the load signaling channel (74) is arranged between the return ring channel (71) and the adjusting screw (114). It is connected to the connecting bore (56) via a load signaling line (12) parallel to the through bore (41). A throttle point (11) is arranged in the load signaling line (12).
  • the sink module (120) has a blind hole (45) leading from the front (34) into the housing (30) and aligned parallel to the through hole (41) of the lifting module. As in the lifting module (90), the blind hole (45) is closed on the left with the aid of the proportional magnet (121) in a pressure-tight manner.
  • valve sleeve (130) In the right-hand area of the blind hole (45) there is a valve sleeve (130) which receives two nested longitudinal slides (140) and (147).
  • the valve sleeve (130) is axially secured in the blind hole (45) between a bore end and a screw ring (156) arranged on the left with an internal, continuous hexagon socket.
  • the left region of the blind hole (45) is provided with an internal thread (128).
  • valve sleeve (130) is surrounded by a consumer ring channel (125) which is hydraulically connected to the consumer connection (50) shown in FIG. 3.
  • a consumer ring channel (125) which is hydraulically connected to the consumer connection (50) shown in FIG. 3.
  • the consumer ring channel (125) leads from the consumer ring channel (125) in the area between the ken- (120) and lifting module (90) tangentially a consumer bore (54) away.
  • the consumer bore (54) opens into the check valve (170), which is higher in relation to FIG. 2, cf. Figure 3.
  • the check valve (170) has a valve bore (47) in the form of a blind hole, which is cut tangentially by the consumer bore (54) at approximately half the bore depth.
  • the valve bore (47) is designed at its left end as a tapered valve seat (171) and in the area of its right end as a consumer connection (50) with an internal thread.
  • a spring-loaded check valve (173) is located in the central, cylindrical area.
  • the latter has a tubular shaft (174), at the left end of which there is a truncated cone-shaped valve disc (175).
  • a coil spring (176) is arranged on the shaft and presses the check valve (173) against the valve seat (171). For this purpose, the coil spring (176) rests on the left via a sealing washer and a washer on the back of the valve plate (175).
  • the star disc (177) On the right, it is supported on a star-shaped disk (177) which bears against at least one spacer disk on a retaining ring (178) seated in the valve bore (47).
  • the star disc (177) has a central pin which projects to the left and on which the tubular shaft (174) of the check valve (173) is guided.
  • the adjusting screw (150) is shown to the left of the screw ring (156).
  • the adjusting screw (150) sits in the internal thread (128).
  • the internal thread is interrupted between the adjusting screw (150) and the screw ring (156) by a return ring channel (126).
  • the return ring channel (126) is connected to the underside (33) of the housing (30) via the return bore (66) and to the return ring channel (94) of the lifting module (90) via the return transverse bore (59).
  • the return cross bore (59) is from the side surface (39) delimiting the sink module (120) is closed by means of a sealing plug (61) in a pressure-tight manner.
  • the sink module (120) which primarily comprises the adjusting screw (150) and the valve sleeve (130) with the two longitudinal slides (140) and (147), is made with the exception of a toothing (151) arranged on the adjusting screw (150) the DE 41 40 604 AI known.
  • the structure of the sink module (120) is therefore described below solely on the basis of its mode of operation.
  • the sink module (120) is shown in FIG. 2 in the locked position.
  • the pressure medium which is present at the consumer connection (50) and thus via the consumer bore (54) on the consumer ring channel (125) cannot flow into the return ring channel (126).
  • Its main control notches (142) which are arranged at its left end, lie concealed under the cylinder seat (133) next to the annular space (134).
  • pressure medium under load pressure is present in a pressure chamber (135) on its right end.
  • 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 slide via a throttle bore (144) and a subsequent longitudinal bore (145).
  • the longitudinal bore (145) penetrates a control groove (143) with its bottom of the bore.
  • the contact pressure is reduced by the opposing force due to the pressure in a consumer pressure chamber (136).
  • the consumer pressure chamber (136) lies in the area of the outer contour of the main control spool (140) between the main valve plug (141) and short-circuit grooves.
  • the sink module (120) opens when the proportional solenoid (121) is energized. Its anchor plunger (122) pushes the inner longitudinal slide, a pilot spool (147) slightly to the right. As a result, its pilot spools (149) pass under the control groove (143) of the main spool (140). At the same time, its valve cone (148) located further to the left lifts off its valve seat (146) corresponding in the main control slide (140). The pressure chamber (135) is now connected to the return bore (66) via the longitudinal bore (145), the control groove (143), the pilot notches (149), the valve seat (146) and the return ring channel (126).
  • the pressure in the pressure chamber (135) drops.
  • the main valve plug (141) lifts off the main valve seat (132) and the main control notches (142) reach the area of the annular space (134).
  • the pressure medium flows between the valve sleeve (130) and the main control spool (140) in the direction of the return ring channel (126).
  • the main control slide (140) lags behind the pilot slide (147) due to its opening movement, as a result of which the opening cross section at the pilot notches (149) becomes smaller.
  • a higher pressure can thus build up in the pressure chamber (135) via the throttle bore (144).
  • the opening movement of the main control spool (140) is braked until an equilibrium state is reached. If the armature tappet (122) moves to the left, the pilot spool (147) follows it owing to a return spring (155) integrated in the adjusting screw (150).
  • the return spring (155) is supported on the pilot spool (147) and on the adjusting screw (150).
  • the pilot spool (147) moves, the pilot notches (149) are closed.
  • the pressure in the pressure chamber (135) increases.
  • the main valve cone (141) lies against the main valve seat (132).
  • the sink module (120) locks.
  • the sink module (120) thus operates in the manner of a sequence control.
  • the adjusting screw (150) has helical teeth in the central area of its outer contour, into which the teeth of an adjusting worm (152) engage at least temporarily.
  • the adjusting screw is seated in an adjusting bore (68) which here extends from the rear (35) into the blind bore (45) and affects the return transverse bore (59) and the return ring channel (126).
  • the adjusting worm (152) can be rotated with the aid of an adjusting spindle, the free end of which protrudes from the housing (30), or a special tool that can be temporarily coupled to the end of the adjusting worm (152).
  • the adjusting screw (150) is screwed to the right or left in the internal thread (128).
  • the length of the adjustment range largely corresponds to the width of the toothing (151) of the adjusting screw (150).
  • the proportional magnet (91) is switched off to end the lifting of the load.
  • the longitudinal slide (97) and the non-return slide (173) go into their closed positions, as shown in FIG. 2.
  • FIG. 5 shows the hydraulic circuit diagram for a control device (2) that is comparable to the control device (1). However, the pressure compensator (70) in FIG. 5 can continue to be loaded.
  • the previous return connection (53) thereby becomes a second consumer connection (51) which can withstand further operation.
  • the pressure medium flow directed from the 3/2-way valve (90) to the check valve (170) is controllably guided via the pressure compensator piston (80) of the pressure compensator (70).
  • the resilience of the pressure compensator (70) leads to changes in the control device (1). The changes are shown in FIGS. 6 to 8 in a control device (2).
  • a housing channel (64) leads in the lifting module (90) from the connecting ring channel (95), at least in some areas parallel to the through hole (41), into a load signaling channel (75) which is located between the locking screw (114) and the pressure compensating piston (80).
  • a consumer ring channel (72) and a load indicator ring channel (75) are arranged in the area of the pressure compensator (70).
  • further consumers can be connected to the return ring channel (71), 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 of the pressure compensator piston (80), which has been changed compared to the first embodiment, is almost on its left edge. At its right end it has a waist that merges into a stop flange (85) towards the right end.
  • the stop flange (85), the diameter of which exceeds the diameter of the pressure compensator piston in the zone with the short-circuit grooves, has a large number of openings (86). Via the openings (86), the pressure medium - if the stop flange is in contact with the left wall of the load signaling channel (75) - 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). For this purpose, the control edge sits approximately centrally in the consumer ring channel (72).
  • the chamfer which also forms a control edge, on the left edge of the outer contour ends shortly before the return ring channel (71).
  • a load pressure-independent control of the volume flow to the first consumer connection (50) is also possible when the continuation via the second consumer connection (51) is pressurized because the pressure compensator piston (80) has an additional control edge .
  • FIGS. 9 and 10 A third embodiment of the hydraulic control device can be seen in FIGS. 9 and 10.
  • the control device (3) shown here is suitable for an LS hydraulic system.
  • the pressure compensator (70) sits in contrast to the two previously described embodiments, cf. Figures 1 and 5, no longer in the secondary branch (10), but is upstream of the 3/2-way valve (90).
  • the rest of the circuit, including the load signaling system, corresponds to the circuit from FIG. 1.
  • a control line (19) branches off from the load signaling line (12) between the throttle point (11) and the pressure compensator (70), so that the control pressure gradient of the... Between the pump connection (49) and the control line (19) LS hydraulic system is present.
  • FIG. 10 shows the third control device (3) in section.
  • the pump connection (49) leads to an intermediate ring channel (73) which penetrates the through bore (41) in the central region of the pressure compensator piston (80).
  • a control groove (82) arranged in the outer contour begins with its right wall.
  • the control groove (82) extends to the left into the inlet ring channel (93).
  • There the control groove (82) merges into fine control notches (83).
  • the fine control notches (83) end in front of the end face (81) of the pressure compensator piston (80).

Abstract

The invention concerns a hydraulic control system with at least two electromagnetic proportional two-way valve elements, a non-return valve and a pressure balance for raising the load, as the input element, independently of the load pressure. The proportional two-way valve elements are parallel to each other, the electromagnetic drives being disposed adjacent each other on the same side and in particular at the same level. A pressure balance piston is disposed coaxially adjacent a longitudinal slide of the first proportional two-way valve element in a bore which houses both valve elements. The longitudinal slide of the first proportional two-way valve element is supported on the housing via a spring. To this end, at least one component is guided by the pressure balance piston in order to adjust the pretension of a spring. The structural volume of the hydraulic control system is small. The individual valve elements are grouped close to one another and the individual slides, including their linkages, are disposed in a space-saving manner. In addition, individual connections are doubled to allow a greater volumetric flow to pass.

Description

Hydraulische Steuerung in Monoblockbauweise zum Heben und Hydraulic control in monoblock construction for lifting and
Senken einer Last mit mindestens zwei elektromagnetisch betätigbaren ProportionalwegeventilelementenLowering a load with at least two electromagnetic directional control valve elements
Stand der Technik:State of the art:
Die Erfindung geht aus von einer hydraulischen Steuerung in Monoblockbauweise zum Heben und Senken einer Last mit minde¬ stens zwei elektromagnetisch betätigbaren Proportionalwegε- ventilelementen, einem Rückschlagventil und einer Druckwaage zum lastdruckunabhangigen Heben der Last als Eingangsεlement, wobei die Elemente zumindest teilweise in einem Gehäuse ange¬ ordnet sind, das mindestens einen Pumpenanschluß, mindestens einen Verbraucheranschluß und mindestens einen Rücklaufan- Schluß aufweist.The invention is based on a hydraulic control in a monoblock design for lifting and lowering a load with at least two electromagnetically actuated proportional travel valve elements, a check valve and a pressure compensator for lifting the load independently of the load as an input element, the elements being at least partially housed in a housing are arranged, which has at least one pump connection, at least one consumer connection and at least one return connection.
In der Regel werden bei hydraulischen Steuerungen in Mo¬ noblockbauweise die Antriebe, Betätigungselemente und An¬ schlüsse an fast allen Gehäuseseiten des Monoblocks angeord- net. Dabei ergeben sich nach dem Anbau der Antriebe, An¬ schlüsse und Einstellorgane für die Ventilfedern trotz kom¬ pakter Bauweise Steuerungen mit großen Außenabmessungen, da besonders die Antriebe oft gegenüberliegen oder über Eck an¬ geordnet aus den Gehäusen herausragen. Außerdem haben derar- tige Steuerungen meist lange und kompliziert gestalteteAs a rule, the drives, actuating elements and connections are arranged on almost all housing sides of the monoblock in the case of hydraulic controls in a monoblock design. In this case, after the drives, connections and setting members for the valve springs have been attached, controls with large external dimensions result, despite the compact design, since the drives in particular often lie opposite one another or protrude from the housings in a corner arrangement. In addition, such controls usually have long and complicated designs
Hydraulikkanäle, die den durch das Gehäuse fließenden Druck¬ mittelstrom 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. Vorteile der Erfindung:Hydraulic channels which additionally throttle the pressure medium flow flowing through the housing and thereby impair the dynamics of the control. Furthermore, with a compact design, the setting of the proportional directional valve elements is difficult or impossible to carry out. Advantages of the invention:
Die erfindungsgemäße hydraulische Steuerung ermöglicht bezüg- lieh ihrer Gehäuseabmessungen und der Gesamtgrδße des Mo- noblocks ein kleines Bauvolumen. Die einzelnen Ventilelemente sind eng nebeneinander angeordnet und sind über kurze Boh¬ rungen oder Kanäle miteinander verbunden.The hydraulic control according to the invention enables a small construction volume with regard to its housing dimensions and the overall size of the monoblock. The individual valve elements are arranged closely next to one another and are connected to one another via short bores or channels.
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 ei- ner Last neben einer Druckwaage. Die Bohrung, in der der Kol¬ ben der Druckwaage koaxial neben dem Längsschieber des Pro¬ portionalwegeventilelements angeordnet ist, ist eine Durchgangsbohrung ohne jede Stufung. Zwischen dem Kolben und dem Längsschieber sitzt eine auf letzteren wir- kende Rückstellfeder. Um die Rückstellfeder gegenüber dem Ge¬ häuse 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 bore 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 elektro- magnetischen Antriebe angeordnet, wodurch die Antriebe mit einfachen Mitteln auch mechanisch ansteuerbar sind. In einer dritten Bohrung sitzt ein Rückschlagventil, das ein Zurück¬ strömen des Druckmittels von einem Verbraucheranschluß in das Proportionalwegeventilelement zum Heben verhindert.A proportional directional valve element for lowering the aforementioned load is arranged in a second parallel bore in the form of a blind hole. It ends together with the first hole on a flat face of the common housing. The electromagnetic drives are arranged directly next to one another on this end face, as a result of which the drives can also be controlled mechanically with simple means. In a third bore there is a check valve which prevents the pressure medium from flowing back from a consumer connection into the proportional directional valve element for lifting.
Um einen großen Volumenstrom durchsetzen zu können, sind teilweise einzelne Anschlüsse doppelt ausgeführtTo 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 nach¬ folgenden Beschreibung von drei vereinfacht dargestellten Ausführungsformen:Further details of the invention result from the following description of three embodiments which are shown in simplified form:
Figur 1: Hydraulikschaltplan einer Steuervorrichtung für ein OC-Hydrauliksyste mit zwei elektromagnetisch betätigten Proportionalwegeventilelementen, einer Druckwaage und einem Rückschlagventil ohne Weiter- laufbelastbarkeit;Figure 1: Hydraulic circuit diagram of a control device for an OC hydraulic system with two electromagnetically operated proportional directional control valve elements, a pressure compensator and a check valve without continued load carrying capacity;
Figur 2: Schnitt durch eine Steuervorrichtung nach Figur 1;Figure 2: Section through a control device according to Figure 1;
Figur 3: Schnitt durch das Rückschlagventil nach Figur 1;Figure 3: Section through the check valve of Figure 1;
Figur 4: Seitenansicht der Steuervorrichtung nach Figur 2 und 3;Figure 4: Side view of the control device according to Figures 2 and 3;
Figur 5: Hydraulikschaltplan wie in Figur 1, jedoch für eine weiterlaufbelastbare Steuervorrichtung;FIG. 5: hydraulic circuit diagram as in FIG. 1, but for a control device which can continue to run;
Figur 6: Schnitt durch eine Steuervorrichtung nach Figur 5;Figure 6: Section through a control device according to Figure 5;
Figur 7: Schnitt durch das Rückschlagventil nach Figur 5;Figure 7: Section through the check valve of Figure 5;
Figur 8: Seitenansicht der Steuervorrichtung nach Figur 6 und 7;Figure 8: Side view of the control device according to Figures 6 and 7;
Figur 9: Hydraulikschaltplan wie in Figur 1, jedoch für ein LS-Hydrauliksystem; Figur 10: Schnitt durch eine Steuervorrichtung nach Figur 9.FIG. 9: hydraulic circuit diagram as in FIG. 1, but for an LS hydraulic system; Figure 10: Section through a control device according to Figure 9.
Beschreibung der Ausführungsbeispiele:Description of the embodiments:
Der in Figur 1 dargestellte Hydraulikschaltplan zeigt einen prinzipiellen Aufbau einer hydraulischen Steuervorrich¬ tung (1) für ein OC-Hydrauliksystem mit zwei elektromagne- tisch betätigbaren Proportionalwegeventilelementen (90) und (120) , einer Druckwaage (70) und einem Rückschlagven¬ til (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 FIG. 1 shows a basic structure of a hydraulic control device (1) for an OC hydraulic system with two electromagnetically actuated proportional directional control valve elements (90) and (120), a pressure compensator (70) and a check valve (170 ). This control device (1) and also those from FIGS. 5 and 9 each serve to control a single-acting hydraulic cylinder (7), cf. Figure 3, which is part of a self-propelled machine, for example.
Beide Proportionalwegeventilelemente (90) und (120) sind drosselnde Wegeventile, deren Längsschieber außer den beiden Endstellungen stufenlos beliebige Zwischenstellungen einneh- men können. Sie haben jeweils auf der einen Seite einen Pro¬ portionalmagneten (91, 121) und auf der anderen Seite eine Rückstellfeder (108, 155). Das erste Proportionalwegeventil¬ element (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 Verbraucheran¬ schluß (50) . Es steuert den Druckmittelstrom von einer Kon¬ stantpumpe (5), vgl. Figur 2, zum Verbraucher, einen einfach wirkenden Hydraulikzylinder (7) zum Heben einer Last. Das Proportionalwegeventilelement (90) wird daher im folgendenBoth proportional directional control valve elements (90) and (120) are throttling directional control valves, the longitudinal spools of which can assume any intermediate positions in addition to the two end positions. They each have a proportional magnet (91, 121) on one side and a return spring (108, 155) on the other side. The first proportional directional valve element (90) is a 3/2-way valve and the second (120) is a 2/2-way valve. Through the 3/2-way valve (90), the pressure medium flow coming from a pump connection (49) flows via 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 single-acting hydraulic cylinder (7) for lifting a load. The proportional directional valve element (90) is therefore described below
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 Proportionalwege- ventilelement (120) wird demnach als Senkenmodul bezeichnet. 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 Rücklauf¬ leitung (17) leitet. Die Rücklaufleitung (17) endet in einem Rücklaufanschluß (53) . An der Druckwaage (70) ist neben einer Regelfeder (88) eine Lastmeldeleitung (12) mit einem Drossel¬ ventil (11) angeschlossen, die von der Verbindungslei¬ tung (13) abzweigt.Called lifting module. The 2/2-way valve (120) controls the pressure medium flow from the single-acting hydraulic cylinder (7) under load via the consumer connection (50) via the return line (16) to the tank. The second proportional directional valve element (120) is therefore referred to as a sink module. Between the pump connection (49) and the lifting module (90), the pressure compensator (70) is arranged in a secondary branch (10), which is open during a neutral circulation and guides the unnecessary pressure medium flow almost unthrottled into a second return line (17). The return line (17) ends in a return connection (53). In addition to a control spring (88), a load signaling line (12) with a throttle valve (11) is connected to the pressure compensator (70) and branches off from the connecting line (13).
Mit Hilfe einer Rücklaufquerleitung (14) ist die Lastmelde¬ leitung (12) bei unbetätigtem 3/2-Wegeventil (90) über dieses mit der Rücklaufleitung (16) verbunden.With the aid of a return cross line (14), the load signal line (12) is connected to the return line (16) when the 3/2-way valve (90) is not actuated.
Zum Heben einer Last wird der Proportionalmagnet (91) des He¬ benmoduls (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 dieThe proportional magnet (91) of the lifting module (90) is energized to lift a load. The return cross line (14) is blocked and pressure medium is conducted via the lifting module (90), the connecting line (13) and the check valve (170) to the consumer connection (50). This is about the
Lastmeldeleitung (12) die Druckwaage (70) auf ihrer federbe¬ lasteten Seite beaufschlagt, womit der Pumpenstrom auf den am Verbraucheranschluß (50) anliegenden Lastdruck angedrosselt wird.Load signaling line (12) acts on the pressure compensator (70) on its spring-loaded side, whereby the pump current is throttled to the load pressure present at the consumer connection (50).
Zum Senken einer Last wird bei einem in der Regel unbestro - ten 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, the proportional magnet (121) of the lowering module (120) is activated in the case of a normally undisturbed proportional magnet (91). The pressure medium flows from the consumer connection (50) via the sink module (120) and the return line (16) to the return connection (52).
In Figur 2 wird die realisierte Steuervorrichtung (1) im Schnitt gezeigt. Sie hat ein im wesentlichen quaderför iges 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 Befestigungsboh¬ rungen (69, 69') auf, vgl. Figur 6, die senkrecht zur Schnittebene das Gehäuse (30) durchdringen. Auf der Ober¬ seite (31) hat das Gehäuse annähernd mittig eine Gehäuseer¬ weiterung (32), vgl. Figur 4.The implemented control device (1) is shown in section in FIG. It has a substantially cuboid housing (30) with two approximately square, flat surfaces as the 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), see. Figure 2. Furthermore, the top and bottom (31) and (33) have two fastening bores (69, 69 '), cf. Figure 6, which penetrate the housing (30) perpendicular to the sectional plane. On the upper side (31), the housing has a housing extension (32) approximately in the center, cf. Figure 4.
Die senkrecht zur Schnittfläche ausgerichteten Seitenflä- chen (34, 35, 38, 39) haben jeweils einen rechteckigen Umriß. Die Vorder- (34) und die Rückseite (35) sind zwei ebene, T- fδrmige und feinbearbeitete Flächen. An der Vorderseite (34) sind die beiden Proportionalmagnete (91) und (121) ange¬ flanscht. Gegenüber dem ersten Proportionalmagneten (91) sitzt in der Rückseite (35) eine Verschlußschraube (114) , vgl. Figur 2. Schräg über ihr befindet sich der Verbraucher¬ anschluß (50) , vgl. Figur 3.The side surfaces (34, 35, 38, 39) oriented perpendicular to the cut surface each have a rectangular outline. The front (34) and the back (35) are two flat, T-shaped and finely machined surfaces. The two proportional magnets (91) and (121) are flanged to the front (34). Compared to the first proportional magnet (91) there is a screw plug (114) in the rear (35), cf. Figure 2. The consumer connection (50) is located diagonally above it, cf. Figure 3.
Die beiden anderen Seitenflächen (38, 39) haben Ausbuch- tungen, die um die Befestigungsbohrungen (69, 69') gebildet sind, vgl. Figur 6. Außerdem weist die in Figur 2 unten lie¬ gende Seitenfläche einen Stutzen zur Aufnahme des Pumpenan¬ schlusses (49) auf.The other two side surfaces (38, 39) have bulges which are formed around the fastening bores (69, 69 '), cf. 6. In addition, the side surface lying at the bottom in FIG. 2 has a connecting piece for receiving the pump connection (49).
Der Pumpenanschluß (49) mit Innengewinde geht im Gehäuse (30) in einen Zulaufringkanal (93) über. Der Ringkanal (93) durch¬ dringt eine zylindrische Durchgangsbohrung (41) , die sich von der Vorderseite (34) bis zur Rückseite (35) erstreckt. Im linken Bereich der Durchgangsbohrung (41) sitzt der Längs¬ schieber (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 Sen¬ kenmodul (120) führenden Rücklaufquerbohrung (59) in Verbin- düng steht. Rechts von diesem Rücklaufringkanal (94) befindet sich der Verbindungsringkanal (95) , vom dem der Verbindungs- kanal (56) annähernd tangential aus der Schnittebene heraus abzweigt.The pump connection (49) with an internal thread merges into an inlet ring channel (93) in the housing (30). The annular channel (93) penetrates a cylindrical through bore (41), which extends from the front (34) to the rear (35). The longitudinal slide (97) of the lifting module (90) is located in the left area of the through hole (41). There, two further channels (94, 95) meet the through hole (41). The left one (94) is a return ring channel which is connected to a return transverse bore (59) leading to the lowering module (120). To the right of this return ring channel (94) is the connecting ring channel (95) from which the connecting channel (56) branches off almost tangentially from the sectional plane.
Der Längsschieber (97) des Hebenmoduls (90) verbindet entwe- der - im unbetätigten Zustand bei Nullüberdeckung - den Ver¬ bindungsringkanal (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 Me߬ drossel haben. Die Öffnungsquerschnitte der Feinsteuerker¬ ben (103) verringern sich in Richtung Zulaufringkanal (93) , ohne ihn jedoch - bei unbestromtem Proportionalmagne- ten (91) - zu erreichen. Die Feinsteuerkerben (103) sind hier beispielsweise Rundkerben.The longitudinal slide (97) of the lifting module (90) either connects the connecting ring channel (95) with the return ring channel (94) or - in the actuated state - with the inlet ring channel (93) in the unactuated state with zero overlap. For this purpose, the cylindrical outer contour of the longitudinal slide (97) has an annular groove (99). The annular groove merges into fine control notches (103) in the area of its right-hand shaft collar, which have the function of a measuring throttle in connection with the pressure compensator (70). The opening cross-sections of the fine control notches (103) decrease in the direction of the inlet ring channel (93), but without reaching them - when the proportional magnet (91) is de-energized. The fine control notches (103) are round notches here, for example.
Am linken Rand der Außenkontur des Längsschiebers (97) befin¬ det sich im Bereich des Dichtrings zwischen dem Proportional- magneten (91) und dem Gehäuse (30) ein Einstich. Unterhalb dieses Einstichs weist der Längsschieber (97) eine zylindri¬ sche Vertiefung (104) auf, an deren Grund der Ankerstδ- ßel (92) des Proportionalmagneten (91) ansteht. Zwischen dem Einstich und der Ringnut (99) befinden sich in der Außenkon- tur mehrere Kurzschlußnuten.On the left edge of the outer contour of the longitudinal slide (97) there is a recess in the area of the sealing ring between the proportional magnet (91) and the housing (30). Below this recess, the longitudinal slide (97) has a cylindrical recess (104), at the bottom of which the armature plunger (92) of the proportional magnet (91) is present. There are several short-circuit grooves in the outer contour between the groove and the ring groove (99).
Von seiner rechten Stirnseite (98) her ist der Längsschie¬ ber (97) gestuft aufgebohrt. Der rechte Bereich der Stufen¬ bohrung (105) dient der Führung der Rückstellfeder (108) . Der linke Bereich hat einen kleineren Durchmesser und verbindet über eine schräg verlaufende Ausgleichsbohrung (106) die Stu¬ fenbohrung (105) mit der Vertiefung (104) . Den Obergang vom rechten zum linken Bereich der Stufenbohrung (105) bildet ein ebener Gehäusebund, auf dem sich die Rückstellfeder (108) ab- stützt. Das andere Ende der Rückstellfeder (108) liegt an einem abge¬ stuften Federteller (109) an. Der Federteller (109) ist im Querschnitt - senkrecht zur gedachten Mittellinie der Durch¬ gangsbohrung - sternförmig ausgebildet, um für den Druckaus- gleich 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 Ent¬ lastungsbohrung angeordnet ist. Der Federteller (109) sitzt auf einer Stange (110) , deren Mittellinie mit der der Durch¬ gangsbohrung (41) zusammenfällt. Der Federteller (109) ist entweder ein Teil der Stange (110) oder er sitzt auf ihr mit¬ tig zentriert, beispielsweise mit Hilfe eines Querpreßsitzes. Die Stange (110) ragt in den rechts neben dem Längsschie- ber (97) angeordneten topffδrmigen Druckwaagenkolben (80) hinein, um dort auf einen Gewindestift (111) zu stoßen. Hier¬ bei ist die Stange (110) in einer Bohrung (77) in der Stirn¬ seite (81) des Druckwaagenkolbens (80) dichtgleitend geführt. Da der in Längsrichtung ortsfeste Federteller (109) zusammen mit der Stange (110) in den zwei längsbeweglichen Ventiltei¬ len (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 gegensei¬ tiges Verkanten zwischen dem Längsschieber (97) und dem Fe- derteller (109) vermieden.The longitudinal slide (97) is drilled out in steps from its right end face (98). The right area of the stepped bore (105) serves to guide the return spring (108). The left area has a smaller diameter and connects the step bore (105) with the depression (104) via an oblique compensating bore (106). The transition from the right to the left area of the stepped bore (105) is formed by a flat housing collar on which the return spring (108) is supported. The other end of the return spring (108) rests on a stepped spring plate (109). The spring plate (109) is star-shaped in cross section - perpendicular to the imaginary center line of the through bore - in order to allow the pressure medium to pass unthrottled for the pressure compensation at the longitudinal slide (97). For this purpose it has, for example, several notches (113) distributed over the circumference. The cross section can also have a circular area in which at least one relief bore is arranged. The spring plate (109) sits on a rod (110), the center line of which coincides with that of the through bore (41). The spring plate (109) is either part of the rod (110) or it is centered on it, for example with the aid of a cross-press seat. The rod (110) protrudes into the cup-shaped pressure compensator piston (80) arranged to the right of the longitudinal slide (97) in order to hit a threaded pin (111) there. In this case, the rod (110) is guided in a bore (77) in the end face (81) of the pressure compensator piston (80) in a tightly sliding manner. Since the spring plate (109), which is stationary in the longitudinal direction, is mounted together with the rod (110) in the two longitudinally movable valve parts (97) and (80), the outer envelope contour of the spring plate (109) is spherical. In this way, mutual tilting between the longitudinal slide (97) and the spring plate (109) is avoided, inter alia, when the return spring (108) is tilted.
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 Steu¬ ervorrichtung (1) kurz zu gestalten, hat der Kopf der Ver¬ schlußschraube (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. Die Durchgangsbohrung (41) geht an ihrem rechten Ende in eine Verschlußschraubenbohrung (42) über. Im Innengewinde der Boh¬ rung (42) ist die Verschlußschraube (114) befestigt. Ein im Bereich zwischen Kopf und Gewinde sitzender Dichtring (118) dichtet die Verschlußschraubenbohrung (42) nach außen ab.The set screw (111) extends in the extension of the rod (110) and ends in the screw plug (114). In order to be able to adjust the threaded pin (111) in the longitudinal direction, the locking screw (114) has an internal thread (116) in which it is screwed. In order to make the overall length of the control device (1) short, the head of the locking screw (114) has a cylindrical recess which serves to receive a lock nut (112). To adjust and lock the threaded pin (111), it has a hexagon socket (117) at its outer free end. The through hole (41) merges at its right end into a screw hole (42). The locking screw (114) is fastened in the internal thread of the bore (42). A sealing ring (118) in the area between the head and the thread seals the screw plug bore (42) from the outside.
In der Durchgangsbohrung (41) sitzt zwischen der Verschluß- schraube (114) und dem Längsschieber (97) dichtgleitend der topfförmige Druckwaagenkolben (80) . Letzterer hat eine zylin¬ drische Außenkontur, die an ihrem rechten Ende einen Halb¬ rundeinstich (84) aufweist, in dem ein Federring (89) einge¬ setzt ist. Der Federring (89) liegt - beispielsweise bei nicht durchstrδmter Steuervorrichtung - an einem als Anschlag dienenden inneren Gehäusebund an, der zwischen der Durch¬ gangsbohrung (41) und der im Durchmesser größeren Verschlu߬ schraubenbohrung (42) gebildet ist. Einen rechten Anschlag für den Druckwaagenkolben (80) bildet die Verstell- schraube (114) . Am linken Rand der Außenkontur des Druckwaa¬ genkolbens (80) befinden sich mehrere auf dem Umfang ver¬ teilte Feinsteuerkerben (83) , die von der linken Stirnseite her in den Druckwaagenkolben (80) eingearbeitet sind.The cup-shaped pressure compensator piston (80) sits in the through hole (41) between the screw plug (114) and the longitudinal slide (97) in a tightly sliding manner. The latter has a cylindrical outer contour which has a semicircular recess (84) at its right end, in which a spring ring (89) is inserted. The spring ring (89) lies - for example when the control device is not flowed through - against an inner housing collar serving as a stop, which is formed between the through bore (41) and the larger diameter screw bore (42). The adjusting screw (114) forms a right stop for the pressure compensator piston (80). On the left edge of the outer contour of the pressure compensating piston (80) there are several fine control notches (83) distributed around the circumference, which are worked into the pressure compensating piston (80) from the left end face.
Hinter dem Halbrundeinstich (84) ist der Druckwaagenkol¬ ben (80) angefast. Im Bereich vor dem Federring (89) trägt er eine Reihe von Kurzschlußnuten.The pressure compensator piston (80) is chamfered behind the semicircular groove (84). In the area in front of the spring washer (89), it has a series of short-circuit grooves.
In den Druckwaagenkolben (80) ist von seiner rechten Stirn- seite her eine Führungsbohrung (87) zur Aufnahme der Regelfe¬ der (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 Verstell- schraube (114) . Im Bereich der Druckwaage (70) befinden sich im Gehäuse (30) zwei Ringkanäle (71) und (74) . Benachbart zum Zulaufringka¬ nal (93) liegt der Rücklaufringkanal (71) . Dieser Ringka¬ nal (71) ist beispielsweise beim Heben einer Last, wenn der Hebenstrom gleich dem Pumpenstrom ist, durch den Druckwaagen¬ kolben (80) vollständig geschlossen, während er bei Neutral¬ umlauf geöffnet ist.A guide bore (87) for receiving the regulating spring (88) is machined into the pressure compensator piston (80) from its right end. The bottom of the guide bore (87) is narrowed in order to radially fix the control spring (88). A bore (115) with a comparable contour is also in the left end of the adjusting screw (114). In the area of the pressure compensator (70) there are two ring channels (71) and (74) in the housing (30). The return ring channel (71) is adjacent to the inlet ring channel (93). This ring channel (71) is completely closed by the pressure compensator piston (80), for example when a load is lifted, when the lifting current is equal to the pump current, while it is open during neutral circulation.
Zwischen dem Rücklaufringkanal (71) und der Verstell- schraube (114) ist der Lastmeldekanal (74) angeordnet. Er steht mit der Verbindungsbohrung (56) über eine zur Durch¬ gangsbohrung (41) parallele Lastmeldeleitung (12) in Verbin¬ dung. In der Lastmeldeleitung (12) ist eine Drossel¬ stelle (11) angeordnet.The load signaling channel (74) is arranged between the return ring channel (71) and the adjusting screw (114). It is connected to the connecting bore (56) via a load signaling line (12) parallel to the through bore (41). A throttle point (11) is arranged in the load signaling line (12).
Das Senkenmodul (120) hat eine, von der Vorderseite (34) her, in das Gehäuse (30) hineinführende Sacklochbohrung (45) , die parallel zur Durchgangsbohrung (41) des Hebenmoduls ausge- richtet ist. Die Sacklochbohrung (45) ist - wie auch im He¬ benmodul (90) - links mit Hilfe des Proportionalmagne¬ ten (121) druckmitteldicht verschlossen.The sink module (120) has a blind hole (45) leading from the front (34) into the housing (30) and aligned parallel to the through hole (41) of the lifting module. As in the lifting module (90), the blind hole (45) is closed on the left with the aid of the proportional magnet (121) in a pressure-tight manner.
Im rechten Bereich der Sacklochbohrung (45) sitzt eine Ven- tilbüchse (130) , die zwei ineinandergeschachtelte Längsschie¬ ber (140) und (147) aufnimmt. Die Ventilbüchse (130) ist in der Sacklochbohrung (45) zwischen einem Bohrungsende und ei¬ nem links angeordneten Schraubring (156) mit einem innenlie¬ genden, durchgehenden Innensechskant axial gesichert. Der linke Bereich der Sacklochbohrung (45) ist dazu mit einem In¬ nengewinde (128) versehen.In the right-hand area of the blind hole (45) there is a valve sleeve (130) which receives two nested longitudinal slides (140) and (147). The valve sleeve (130) is axially secured in the blind hole (45) between a bore end and a screw ring (156) arranged on the left with an internal, continuous hexagon socket. For this purpose, the left region of the blind hole (45) is provided with an internal thread (128).
Die Ventilbüchse (130) ist von einem Verbraucherringka¬ nal (125) umgeben, der mit dem in Figur 3 gezeigten Verbrau- cheranschluß (50) hydraulisch in Verbindung steht. Dazu führt vom Verbraucherringkanal (125) im Bereich zwischen dem Sen- ken- (120) und Hebenmodul (90) tangential eine Verbraucher¬ bohrung (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 surrounded by a consumer ring channel (125) which is hydraulically connected to the consumer connection (50) shown in FIG. 3. For this purpose leads from the consumer ring channel (125) in the area between the ken- (120) and lifting module (90) tangentially a consumer bore (54) away. The consumer bore (54) opens into the check valve (170), which is higher in relation to FIG. 2, cf. Figure 3.
Das Rückschlagventil (170) hat eine Ventilbohrung (47) in der Form eines Sackloches, die ungefähr in der halben Bohrungs¬ tiefe von der Verbraucherbohrung (54) tangential geschnitten wird. Die Ventilbohrung (47) ist an ihrem linken Ende als ke- gelmantelfδrmiger Ventilsitz (171) und im Bereich ihres rech¬ ten Endes als Verbraucheranschluß (50) mit Innengewinde aus¬ gebildet. Im mittleren, zylindrischen Bereich sitzt ein fe¬ derbelasteter Rückschlagschieber (173) . Letzterer hat einen rohrförmigen Schaft (174) , an dessem linken Ende sich ein ke¬ gelstumpffδrmiger Ventilteller (175) befindet. Auf dem Schaft ist eine Schraubenfeder (176) angeordnet, die den Rückschlag¬ schieber (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 Sicherungs¬ ring (178) anliegt. Die Sternscheibe (177) hat einen zentra- len, nach links kragenden Bolzen, auf dem der rohrfδrmige Schaft (174) des Rückschlagschiebers (173) geführt ist.The check valve (170) has a valve bore (47) in the form of a blind hole, which is cut tangentially by the consumer bore (54) at approximately half the bore depth. The valve bore (47) is designed at its left end as a tapered valve seat (171) and in the area of its right end as a consumer connection (50) with an internal thread. A spring-loaded check valve (173) is located in the central, cylindrical area. The latter has a tubular shaft (174), at the left end of which there is a truncated cone-shaped valve disc (175). A coil spring (176) is arranged on the shaft and presses the check valve (173) against the valve seat (171). For this purpose, the coil spring (176) rests on the left via a sealing washer and a washer on the back of the valve plate (175). On the right, it is supported on a star-shaped disk (177) which bears against at least one spacer disk on a retaining ring (178) seated in the valve bore (47). The star disc (177) has a central pin which projects to the left and on which the tubular shaft (174) of the check valve (173) is guided.
In Figur 2 ist links neben dem Schraubring (156) die Ein¬ stellschraube (150) dargestellt. Die Einstellschraube (150) sitzt im Innengewinde (128) . Das Innengewinde ist zwischen der Einstellschraube (150) und dem Schraubring (156) von ei¬ nem Rücklaufringkanal (126) unterbrochen. Der Rücklaufringka¬ nal (126) steht mit der Unterseite (33) des Gehäuses (30) über die Rücklaufbohrung (66) und mit dem Rücklaufringka- nal (94) des Hebenmoduls (90) über die Rücklaufquerboh- rung (59) in Verbindung. Die Rücklaufquerbohrung (59) ist von der das Senkenmodul (120) begrenzenden Seitenfläche (39) her mittels eines Verschlußstopfens (61) druckmitteldicht ver¬ schlossen.In Figure 2, the adjusting screw (150) is shown to the left of the screw ring (156). The adjusting screw (150) sits in the internal thread (128). The internal thread is interrupted between the adjusting screw (150) and the screw ring (156) by a return ring channel (126). The return ring channel (126) is connected to the underside (33) of the housing (30) via the return bore (66) and to the return ring channel (94) of the lifting module (90) via the return transverse bore (59). The return cross bore (59) is from the side surface (39) delimiting the sink module (120) is 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 Längsschie¬ bern (140) und (147) umfaßt, ist mit Ausnahme einer auf der Einstellschraube (150) angeordneten Verzahnung (151) aus der DE 41 40 604 AI bekannt. Im folgenden wird daher der Aufbau des Senkenmoduls (120) ausschließlich anhand seiner Wirkungs¬ weise beschrieben.The sink module (120), which primarily comprises the adjusting screw (150) and the valve sleeve (130) with the two longitudinal slides (140) and (147), is made with the exception of a toothing (151) arranged on the adjusting screw (150) the DE 41 40 604 AI known. The structure of the sink module (120) is therefore described below solely on the basis of its mode of operation.
Das Senkenmodul (120) ist in Figur 2 in Sperrstellung darge- stellt. Das Druckmittel, das am Verbraucheranschluß (50) und damit über die Verbraucherbohrung (54) am Verbraucherringka¬ nal (125) ansteht, kann nicht in den Rücklaufringkanal (126) strömen. Der in der Ventilbüchse (130) direkt gelagerte Längsschieber, der Hauptsteuerschieber (140) , steht mit sei- nem Hauptventilkegel (141) am Hauptventilsitz (132) der Ven¬ tilbüchse (130) an. Seine - an seinem linken Ende angeordne¬ ten - Hauptsteuerkerben (142) liegen verdeckt unter dem Zy¬ lindersitz (133) neben dem Ringraum (134) . Um den Hauptsteu¬ erschieber (140) auf dem Hauptventilsitz (132) zu halten, steht auf seiner rechten Stirnseite in einem Druckraum (135) Druckmittel unter Lastdruck an. Dorthin gelangt das Druckmit¬ tel aus dem Verbraucherringkanal (125) über Radialboh¬ rungen (131) in der Ventilbüchse (130) , sowie im Hauptsteuer- schieber über eine Drosselbohrung (144) und eine daran an- schließende Längsbohrung (145) . Die Längsbohrung (145) durch¬ dringt mit ihrem Bohrungsgrund eine Steuernut (143) . Die An¬ preßkraft wird vermindert durch die entgegengesetzt wirkende Kraft aufgrund des in einem Verbraucherdruckraum (136) anste¬ henden Druckes. Der Verbraucherdruckraum (136) liegt im Be- reich der Außenkontur des Hauptsteuerschiebers (140) zwischen Hauptventilkegel (141) und Kurzschlußnuten. Bei geschlossenem Senkenmodul (120) stehen beide Druckräume (135) und (136) un¬ ter dem am Verbraucheranschluß (50) anliegenden Lastdruck.The sink module (120) is shown in FIG. 2 in the locked position. The pressure medium which is present at the consumer connection (50) and thus via the consumer bore (54) on the consumer ring channel (125) cannot flow into the return ring channel (126). The longitudinal spool, the main control spool (140), which is mounted directly in the valve sleeve (130), rests with its main valve cone (141) on the main valve seat (132) of the valve sleeve (130). Its main control notches (142), which are arranged at its left end, lie concealed under the cylinder seat (133) next to the annular space (134). In order to hold the main control slide (140) on the main valve seat (132), pressure medium under load pressure is present in a pressure chamber (135) on its right end. 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 slide via a throttle bore (144) and a subsequent longitudinal bore (145). The longitudinal bore (145) penetrates a control groove (143) with its bottom of the bore. The contact pressure is reduced by the opposing force due to the pressure in a consumer pressure chamber (136). The consumer pressure chamber (136) lies in the area of the outer contour of the main control spool (140) between the main valve plug (141) and short-circuit grooves. When closed Sink module (120) both pressure chambers (135) and (136) are under the load pressure applied to the consumer connection (50).
Das Senkenmodul (120) öffnet mit der Bestromung des Propor- tionalmagneten (121) . Sein Ankerstδßel (122) schiebt den in¬ neren Längsschieber, einen Vorsteuerschieber (147) gering¬ fügig nach rechts. Dadurch gelangen seine Vorsteuerker¬ ben (149) unter die Steuernut (143) des Hauptsteuerschie¬ bers (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 Rück¬ laufringkanal (126) mit der Rücklaufbohrung (66) in Verbin- düng. In Abhängigkeit vom Öffnungsquerschnitt der Vorsteuer¬ kerben (149) sinkt der Druck im Druckraum (135) . Der dortige Druck stellt sich entsprechend dem Verhältnis des Quer¬ schnitts 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 Radialboh¬ rungen (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 Hauptsteuer- schieber (140) in Richtung Rücklaufringkanal (126) . Der Hauptsteuerschieber (140) eilt durch seine Öffnungsbewegung dem Vorsteuerschieber (147) nach, wodurch der Öffnungsquer¬ schnitt an den Vorsteuerkerben (149) kleiner wird. Damit kann sich im Druckraum (135) über die Drosselbohrung (144) ein hö¬ herer Druck aufbauen. Folglich wird die Öffnungsbewegung des Hauptsteuerschiebers (140) gebremst, bis sich ein Gleichge¬ wichtszustand einstellt. Bewegt sich der Ankerstδßel (122) nach links, folgt ihm auf¬ grund einer in der Einstellschraube (150) integrierten Rück¬ stellfeder (155) der Vorsteuerschieber (147) . Die Rückstell- feder (155) stützt sich am Vorsteuerschieber (147) und an der Einstellschraube (150) ab. Bei der Bewegung des Vorsteuer¬ schiebers (147) werden die Vorsteuerkerben (149) verschlos¬ sen. Der Druck im Druckraum (135) steigt. Der Hauptventilke¬ gel (141) legt sich am Hauptventilsitz (132) an. Das Senken- modul (120) sperrt. Das Senkenmodul (120) arbeitet somit nach Art einer Folgesteuerung.The sink module (120) opens when the proportional solenoid (121) is energized. Its anchor plunger (122) pushes the inner longitudinal slide, a pilot spool (147) slightly to the right. As a result, its pilot spools (149) pass under the control groove (143) of the main spool (140). At the same time, its valve cone (148) located further to the left lifts off its valve seat (146) corresponding in the main control slide (140). The pressure chamber (135) is now connected to the return bore (66) via the longitudinal bore (145), the control groove (143), the pilot notches (149), the valve seat (146) and the return ring channel (126). Depending on the opening cross section of the pilot notches (149), the pressure in the pressure chamber (135) drops. The pressure there arises in accordance with the ratio of the cross section of the throttle bore (144) and the opening cross section of the pilot notches (149). If, when the pilot spool (147) is pushed far to the right, the pressure in the pressure chamber (135) falls so far that the force exerted by the pressure medium on the main spool (140) in the area below the radial bores (131) to the right predominates, the main spool becomes (140) also shifted to the right. The main valve plug (141) lifts off the main valve seat (132) and the main control notches (142) reach the area of the annular space (134). Coming from the consumer, the pressure medium flows between the valve sleeve (130) and the main control spool (140) in the direction of the return ring channel (126). The main control slide (140) lags behind the pilot slide (147) due to its opening movement, as a result of which the opening cross section at the pilot notches (149) becomes smaller. A higher pressure can thus build up in the pressure chamber (135) via the throttle bore (144). As a result, the opening movement of the main control spool (140) is braked until an equilibrium state is reached. If the armature tappet (122) moves to the left, the pilot spool (147) follows it owing to a return spring (155) integrated in the adjusting screw (150). The return spring (155) is supported on the pilot spool (147) and on the adjusting screw (150). When the pilot spool (147) moves, the pilot notches (149) are closed. The pressure in the pressure chamber (135) increases. The main valve cone (141) lies against the main valve seat (132). The sink module (120) locks. The sink module (120) thus operates in the manner of a sequence control.
Um die Vorspannkraft der Rückstellfeder (155) bei montierter Steuervorrichtung einstellen zu können, weist die Einstell¬ schraube (150) im mittleren Bereich ihrer Außenkontur eine Schrägverzahnung auf, in die zumindest zeitweise die Verzah¬ nung einer Einstellschnecke (152) eingreift. Die Einstell¬ schnecke 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 Rück¬ laufringkanal (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 Ein¬ stellschraube (150) in dem Innengewinde (128) nach rechts oder links geschraubt. Die Länge des Verstellbereiches ent- spricht weitgehend der Breite der Verzahnung (151) der Ein¬ stellschraube (150) .In order to be able to adjust the pretensioning force of the return spring (155) when the control device is mounted, the adjusting screw (150) has helical teeth in the central area of its outer contour, into which the teeth of an adjusting worm (152) engage at least temporarily. For this purpose, the adjusting screw is seated in an adjusting bore (68) which here extends from the rear (35) into the blind bore (45) and affects the return transverse bore (59) and the return ring channel (126). The adjusting worm (152) can be rotated with the aid of an adjusting spindle, the free end of which protrudes from the housing (30), or a special tool that can be temporarily coupled to the end of the adjusting worm (152). Depending on the direction of rotation of the adjusting spindle or the adjusting screw (152), the adjusting screw (150) is screwed to the right or left in the internal thread (128). The length of the adjustment range largely corresponds to the width of the toothing (151) of the adjusting screw (150).
Beim Heben der Last strömt bei bestromtem Proportionalmagne- ten (91) Druckmittel über den Pumpenanschluß (49) , den Zu¬ laufringkanal (93) , den Längsschieber (97) und die Verbin- dungsbohrung (56) in die Ventilbohrung (47) vor den Rück¬ schlagschieber (173) des in Figur 3 gezeigten Rückschlagven¬ tils (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 Lastmeldelei¬ tung (12) und den Lastmeldekanal (74) auf die Rückseite des Druckwaagenkolbens (80) . Durch diese Beschaltung der Druck¬ waage (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 an¬ stehenden 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 auszufah¬ ren. Der Längsschieber (97) und der Druckwaagenkolben (80) ermöglichen eine lastunabhängige Steuerung des Volumenstroms zum Verbraucheranschluß (50) .When the load is lifted with the proportional solenoid (91) energized, pressure medium flows via the pump connection (49), the inlet ring channel (93), the longitudinal slide (97) and the connection Bore (56) in the valve bore (47) in front of the check valve (173) of the check valve (170) shown in Figure 3. The longitudinal slide (97) is opened via its fine control notches (103). They form the measuring throttle in relation to the pressure compensator (70). The pressure medium flows on the way to the check valve (170) via the load signaling line (12) and the load signaling channel (74) to the rear of the pressure compensator piston (80). Through this connection of the pressure balance (70) there is always a constant pressure drop in front of and behind the fine control notches (103), the size of which is determined by the spring force of the control spring (88). As soon as the force on the front of the valve plate (175) due to the pump pressure in excess of the sum of the spring force and the product of the load pressure and the rear valve plate area, the check valve (170) opens and the load begins to lift 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 Proportionalma¬ gnet (91) abgeschaltet. Der Längsschieber (97) und der Rück¬ schlagschieber (173) gehen in ihre Schließstellungen, wie sie in Figur 2 gezeigt sind.The proportional magnet (91) is switched off to end the lifting of the load. The longitudinal slide (97) and the non-return slide (173) go into their closed positions, as shown in FIG. 2.
Figur 5 zeigt den Hydraulikschaltplan für eine mit der Steu¬ ervorrichtung (1) vergleichbare Steuervorrichtung (2) . Die Druckwaage (70) in Figur 5 ist jedoch weiterlaufbelastbar.FIG. 5 shows the hydraulic circuit diagram for a control device (2) that is comparable to the control device (1). However, the pressure compensator (70) in FIG. 5 can continue to be loaded.
Dabei wird der bisherige Rücklaufanschluß (53) zu einem wei¬ terlaufbelastbaren, zweiten Verbraucheranschluß (51) . Ferner wird der vom 3/2-Wegeventil (90) zum Rückschlagventil (170) geleitete Druckmittelstrom steuerbar über den Druckwaagenkol- ben (80) der Druckwaage (70) geführt. Die Weiterlauf elastbarkeit der Druckwaage (70) führt zu ei¬ nigen Änderungen an der Steuervorrichtung (1) . Die Änderungen sind den Figuren 6 bis 8 in einer Steuervorrichtung (2) ver¬ wirklicht.The previous return connection (53) thereby becomes a second consumer connection (51) which can withstand further operation. Furthermore, the pressure medium flow directed from the 3/2-way valve (90) to the check valve (170) is controllably guided via the pressure compensator piston (80) of the pressure compensator (70). The resilience of the pressure compensator (70) leads to changes in the control device (1). The changes are shown in FIGS. 6 to 8 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 of the check valve (170) on the housing (30) of the control device (2) has changed, cf. Figures 7 and 8. The center line of the check valve (170) here still runs parallel to the plane formed by the two center lines of the lifting (90) and the sink module (120), but not parallel to the center lines themselves, but perpendicular to them . Consequently, the consumer connection (50) is on the side surface (39), which is now T-shaped.
Nach Figur 6 führt im Hebenmodul (90) von dem Verbindungs¬ ringkanal (95) ein Gehäusekanal (64) zumindest bereichsweise parallel zur Durchgangsbohrung (41) in einen Lastmelderingka¬ nal (75) , der sich zwischen der Verschlußschraube (114) und dem Druckwaagenkolben (80) befindet.According to FIG. 6, a housing channel (64) leads in the lifting module (90) from the connecting ring channel (95), at least in some areas parallel to the through hole (41), into a load signaling channel (75) which is located between the locking screw (114) and the pressure compensating piston (80).
Im Bereich des Druckwaage (70) ist neben dem Rücklaufringka¬ nal (71) ein Verbraucherringkanal (72) und ein Lastmeldering¬ kanal (75) angeordnet. An den Rücklaufringkanal (71) können bei dieser Ausführungsform weitere Verbraucher angeschlossen werden, vgl. Figur 5, Verbraucheranschluß (51). Der Verbrau¬ cherringkanal (72) führt über einen Flachkanal (62) zur Ven¬ tilbohrung (47) des Rückschlagventils (170) .In the area of the pressure compensator (70), in addition to the return ring channel (71), a consumer ring channel (72) and a load indicator ring channel (75) are arranged. In this embodiment, further consumers can be connected to the return ring channel (71), 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 Außenkσntur des Druckwaagenkolbens (80) ist an ihrem linken Rand ange- fast. 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 Kurz- schlußnuten übersteigt, weist eine Vielzahl von Durchbrü¬ chen (86) auf. Über die Durchbrüche (86) gelangt das Druck- mittel - 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 Verbrau¬ cherringkanal (72) . Die ebenfalls eine Steuerkante bildende Fase am linken Rand der Außenkontur endet kurz vor dem Rück¬ laufringkanal (71) .The outer contour of the pressure compensator piston (80), which has been changed compared to the first embodiment, is almost on its left edge. At its right end it has a waist that merges into a stop flange (85) towards the right end. The stop flange (85), the diameter of which exceeds the diameter of the pressure compensator piston in the zone with the short-circuit grooves, has a large number of openings (86). Via the openings (86), the pressure medium - if the stop flange is in contact with the left wall of the load signaling channel (75) - 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). For this purpose, the control edge sits approximately centrally in the consumer ring channel (72). The chamfer, which also forms a control edge, on the left edge of the outer contour ends shortly before the return ring channel (71).
Bei der Steuervorrichtung (2) ist somit eine lastdruckunab- hängige Steuerung des Volumenstroms zum ersten Verbraucheran¬ schluß (50) auch dann möglich, wenn der Weiterlauf über den zweiten Verbraucheranschluß (51) druckbelastet ist, da der Druckwaagenkolben (80) eine zusätzliche Steuerkante aufweist.In the control device (2), a load pressure-independent control of the volume flow to the first consumer connection (50) is also possible when the continuation via the second consumer connection (51) is pressurized because the pressure compensator piston (80) has an additional control edge .
Eine dritte Ausführungsform der hydraulischen Steuervorrich¬ tung ist den Figuren 9 und 10 zu entnehmen. Die hier gezeigte Steuervorrichtung (3) ist für ein LS-Hydrauliksystem ge- eignet. 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-We- geventil (90) direkt vorgeschaltet. Die übrige Schaltung, einschließlich dem Lastmeldesystem entspricht der Schaltung aus Figur 1. Zusätzlich wird zur Ansteuerung der die Steuer¬ vorrichtung (3) versorgenden Verstellpumpe (6), vgl. Fi¬ gur 10, eine Steuerleitung (19) aus der Lastmeldeleitung (12) zwischen der Drosselstelle (11) und der Druckwaage (70) abge¬ zweigt, womit zwischen dem Pumpenanschluß (49) und der Steu- erleitung (19) das Regeldruckgefälle des LS-Hydrauliksyste s anliegt.A third embodiment of the hydraulic control device can be seen in FIGS. 9 and 10. The control device (3) shown here is suitable for an LS hydraulic system. For this purpose, the pressure compensator (70) sits in contrast to the two previously described embodiments, cf. Figures 1 and 5, no longer in the secondary branch (10), but is upstream of the 3/2-way valve (90). The rest of the circuit, including the load signaling system, corresponds to the circuit from FIG. 1. In addition, for the control of the variable displacement pump (6) supplying the control device (3), cf. FIG. 10, a control line (19) branches off from the load signaling line (12) between the throttle point (11) and the pressure compensator (70), so that the control pressure gradient of the... Between the pump connection (49) and the control line (19) LS hydraulic system is present.
Die Figur 10 zeigt die dritte Steuervorrichtung (3) im Schnitt. Sie weicht konstuktiv im Bereich des Hebenmo- duls (90) und der Druckwaage (70) von der Steuervorrich¬ tung (1) ab. Der Pumpenanschluß (49) führt zu einem Zwischenringka¬ nal (73) , der die Durchgangsbohrung (41) im mittleren Bereich des Druckwaagenkolbens (80) durchdringt. In der Mitte des Zwischenringkanals (73) beginnt - bei der in Figur 10 darge¬ stellten Position des Druckwaagenkolbens - eine in der Außen¬ kontur 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) .Figure 10 shows the third control device (3) in section. In the area of the lifting module (90) and the pressure compensator (70), it deviates constructively from the control device (1). The pump connection (49) leads to an intermediate ring channel (73) which penetrates the through bore (41) in the central region of the pressure compensator piston (80). In the middle of the intermediate ring channel (73) - with the position of the pressure compensator piston shown in FIG. 10 - a control groove (82) arranged in the outer contour begins with its right wall. The control groove (82) extends to the left into the inlet ring channel (93). There the control groove (82) merges into fine control notches (83). 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 Ver- bindungsringkanal (95) und von dort über die Lastmeldelei¬ tung (12) , den Lastmelderingkanal (75) und die Steuerlei¬ tung (19) zur Pumpenregelung. Der Pumpendruck steigt entspre¬ chend der anstehenden Last an. Sobald Druckmittel zum Ver¬ braucher strömt, bestimmt das Druckgefälle am Längsschie- ber (97) und der Öffnungsquerschnitt der Feinsteuerker¬ ben (103) den Volumenstrom. Die Druckwaage (70) hält das Druckgefälle immer konstant. Dies gilt auch bei einer Paral¬ lelbetätigung von mehreren Verbrauchern. When the lifting module (90) is opened, pressure medium flows under standby pressure from the variable displacement pump (6) into the connecting ring channel (95) and from there via the load signaling line (12), the load signaling channel (75) and Control line (19) for pump control. The pump pressure rises in accordance with the pending load. As soon as pressure medium flows to the consumer, the pressure drop on the longitudinal slide (97) and the opening cross section of the fine control notches (103) determine the volume flow. The pressure compensator (70) always keeps the pressure drop constant. This also applies when several consumers are operated in parallel.

Claims

Patentansprüche: Claims:
1. Hydraulische Steuerung in Monoblockbauweise zum Heben und Senken einer Last mit mindestens zwei elektromagnetisch betä¬ tigbaren Proportionalwegeventilelementen, einem Rückschlag¬ ventil und einer Druckwaage zum lastdruckunabhangigen 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, dadurch ge¬ kennzeichnet,1. Hydraulic control in monoblock construction for lifting and lowering a load with at least two electromagnetically actuated proportional directional control valve elements, a check valve and a pressure compensator for lifting the load independently of the load pressure as an input element, the elements being at least partially arranged in a housing, the at least one Has pump connection, at least one consumer connection and at least one return connection, characterized ge indicates
- daß die Proportionalwegeventilelemente (90, 120) parallel zueinander angeordnet sind, wobei die elektromagnetischen Antriebe (91, 121) auf der gleichen Seite und insbesondere auf gleicher Höhe nebeneinander sitzen,- That the proportional directional control valve elements (90, 120) are arranged parallel to each other, the electromagnetic drives (91, 121) sitting next to each other on the same side and in particular at the same height,
- daß ein Kolben (80) der Druckwaage (70) koaxial neben einem Längsschieber (97) des ersten Proportionalwegeventilele¬ ments (90) in einer, beide Ventilelemente (80) und (97) führenden und lagernden Bohrung (41) angeordnet ist,- that a piston (80) of the pressure compensator (70) is arranged coaxially next to a longitudinal slide (97) of the first proportional directional control valve (90) in a bore (41) guiding and supporting both valve elements (80) and (97),
- daß der Längsschieber (97) des ersten Proportionalwegeven¬ tilelements (90) federbelastet ist, wobei mindestens ein Bauteil (109, 110) zur Verstellung der Vorspannung und Ab- stützung einer Feder (108) am Gehäuse (30) der Steue- rung (1, 2, 3) durch den Druckwaagenkolben (80) hindurchge¬ führt ist.- That the longitudinal slide (97) of the first proportional travel element (90) is spring-loaded, at least one component (109, 110) for adjusting the pretension and supporting a spring (108) on the housing (30) of the control ( 1, 2, 3) through the pressure compensator piston (80).
2. Hydraulische Steuerung gemäß Anspruch 1, dadurch gekenn- zeichnet, daß das Bauteil (109, 110) in einer Bohrung (105) des Längsschiebers (97) und einer Bohrung (77) des Druckwaa¬ genkolbens (80) gelagert und geführt ist.2. Hydraulic control according to claim 1, characterized in that the component (109, 110) in a bore (105) of the longitudinal slide (97) and a bore (77) of the pressure piston piston (80) is mounted and guided.
3. Hydraulische Steuerung gemäß Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Bauteil (109, 110) einen zylindri- sehen, stangenförmigen Abschnitt (110) aufweist, der in der Bohrung (77) geführt ist, und einen scheibenförmigen Ab¬ schnitt (109) umfaßt, der in der Bohrung (105) geführt ist.3. Hydraulic control according to claim 1 or 2, characterized in that the component (109, 110) has a cylindrical see, has rod-shaped section (110) which is guided in the bore (77), and comprises a disc-shaped section (109) which is guided in the bore (105).
4. Hydraulische Steuerung gemäß der Ansprüche 1 bis 4, da¬ durch gekennzeichnet, daß der scheibenförmige Ab¬ schnitt (109), an dem die Feder (108) anliegt, im Kontaktbe¬ reich zur Bohrung (105) ein ballige Außenkontur aufweist, wo- bei die Außenkontur ein Zone eines Ellipsoids ist, dessen Ro¬ tationsachse auf der gedachten Mittellinie des Bauteils (110) liegt.4. Hydraulic control according to claims 1 to 4, da¬ characterized in that the disc-shaped Ab¬ section (109) on which the spring (108) rests in the contact area to the bore (105) has a spherical outer contour where - The outer contour is a zone of an ellipsoid, the axis of rotation of which lies on the imaginary center line of the component (110).
5. Hydraulische Steuerung gemäß Anspruch 3, dadurch gekenn¬ zeichnet, daß der scheibenförmige Abschnitt (109) in seinem Querschnitt senkrecht zur rotationssymmetrischen Mittellinie seiner Außenkontur Durch- oder Ausbrüche aufweist.5. Hydraulic control according to claim 3, characterized gekenn¬ characterized in that the disc-shaped portion (109) in its cross section perpendicular to the rotationally symmetrical center line of its outer contour has openings or cutouts.
6. Hydraulische Steuerung gemäß Anspruch 5, dadurch gekenn¬ zeichnet, daß in dem scheibenförmigen Abschnitt (109) als Ausbrüche radial ausgerichtete Kerben (113) angeordnet sind.6. Hydraulic control according to claim 5, characterized gekenn¬ characterized in that radially aligned notches (113) are arranged in the disc-shaped section (109) as outbreaks.
7. Hydraulische Steuerung gemäß Anspruch 1, dadurch gekenn¬ zeichnet, daß die Bohrung (41) eine Durchgangsbohrung ist, deren Durchmesser zumindest im Bereich der Lagerung und Füh¬ rung der Ventilelemente (80) und (97) konstant ist.7. Hydraulic control according to claim 1, characterized gekenn¬ characterized in that the bore (41) is a through bore, the diameter of which is constant at least in the region of the bearing and guide of the valve elements (80) and (97).
8. Hydraulische Steuerung gemäß einem der vorangegangenen An¬ sprüche 1 bis 5, dadurch gekennzeichnet, daß an dem Ende der Bohrung (41) neben der Druckwaage (70) ein Verschlußele- ment (114) angeordnet ist, das ein Innengewinde (116) auf¬ weist, in dem ein Gewindestift (111) als verstellbarer An- schlag für das Bauteil (109, 110) eingeschraubt ist.8. Hydraulic control according to one of the preceding claims 1 to 5, characterized in that a closure element (114) is arranged at the end of the bore (41) next to the pressure compensator (70) and has an internal thread (116) ¬ points in which a threaded pin (111) as an adjustable impact for the component (109, 110) is screwed in.
9. Hydraulische Steuerung gemäß Anspruch 1, dadurch gekenn¬ zeichnet, daß bei einer Ausführungsform (1) und (2) für OC- Hydraulikkreisläufe sowohl das zweite Proportionalwegeventil¬ element (120) als auch die Druckwaage (80) jeweils einen se¬ paraten, hydraulisch nachgeschalteten Anschluß (53) und (53 oder 51) aufweist.9. Hydraulic control according to claim 1, characterized gekenn¬ characterized in that in one embodiment (1) and (2) for OC hydraulic circuits, both the second Proportionalwegeventil¬ element (120) and the pressure compensator (80) each have a separate, hydraulically downstream connection (53) and (53 or 51).
10. Hydraulische Steuerung gemäß Anspruch 1, dadurch gekenn¬ zeichnet, daß der innere Längsschieber (147) des zweiten Pro¬ portionalwegeventilelements (120) mit einer im Gehäuse (30) abgestützten Feder (155) belastet wird, wodurch er im Sperr¬ zustand an einem Ventilsitz (146) im äußeren Längsschie¬ ber (140) anliegt.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 with a spring (155) supported in the housing (30), as a result of which it is in the locked state a valve seat (146) rests in the outer longitudinal slide (140).
11. Hydraulische Steuerung gemäß Anspruch 10, dadurch gekenn¬ zeichnet, daß die Vorspannung der Feder (155) mit einer im Gehäuse (30) angeordneten Einstellschraube (150) einstellbar ist.11. Hydraulic control according to claim 10, characterized gekenn¬ characterized in that the bias of the spring (155) with an in the housing (30) arranged adjusting screw (150) is adjustable.
12. Hydraulische Steuerung gemäß Anspruch 10 und 11, dadurch gekennzeichnet, daß das Gehäuse (30) im Bereich der Einstell¬ schraube (150) eine Einstellbohrung (68) aufweist, deren Mit¬ tellinie sich windschief mit der Mittellinie der Längsschie- ber (140, 147) kreuzt, wobei der kürzeste Abstand der beiden Mittellinien dem Achsabstand zwischen der Einstell¬ schraube (150) und einem in der Einstellbohrung (68) einsetz¬ baren Einstellrad entspricht.12. Hydraulic control according to claim 10 and 11, characterized in that the housing (30) in the region of the adjusting screw (150) has an adjusting bore (68) whose center line is skewed with the center line of the longitudinal slide (140 , 147) crosses, the shortest distance between the two center lines corresponding to the center distance between the adjusting screw (150) and an adjusting wheel insertable in the adjusting hole (68).
13. Hydraulische Steuerung gemäß mindestens einem der Ansprü- ehe 1 bis 12, dadurch gekennzeichnet, daß die beiden Propor¬ tionalwegeventilelemente (90) und (120) über ein separates Rückschlagventil (170) untereinander verknüpft sind, das bei der Senkenfunktion als Weiche geschaltet ist.13. Hydraulic control according to at least one of the claims. before 1 to 12, characterized in that the two proportional directional valve elements (90) and (120) are linked to one another via a separate check valve (170) which is switched as a switch in the lowering function.
14. Hydraulische Steuerung gemäß einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, daß das erste Proportionalwege¬ ventilelement (90) ein einstufiges, direkt betätigtes Ventil ist, und das zweite Proportionalwegeventilelement (120) ein Ventil mit einer Vorstufe, dem inneren Längsschieber (147), und einer Hauptstufe, dem äußeren Längsschieber (140), ist, wobei auf der Außenkontur des Längsschiebers (140) ein Haupt¬ ventilkegel (141) und Hauptsteuerkerben (142) angeordnet sind, die in Serie in den Arbeitsstrom geschaltet sind. 14. Hydraulic control according to one of claims 1 to 13, characterized in that the first Proportionalwege¬ valve element (90) is a one-stage, directly operated valve, and the second proportional directional valve element (120) is a valve with a preliminary stage, the inner longitudinal slide (147 ), and a main stage, the outer longitudinal slide (140), whereby a main valve cone (141) and main control notches (142) are arranged on the outer contour of the longitudinal slide (140) and are connected in series in the working current.
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
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
DE4446145 1994-12-23
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 true EP0799384A1 (en) 1997-10-08
EP0799384B1 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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Also Published As

Publication number Publication date
JPH11500810A (en) 1999-01-19
JP3654364B2 (en) 2005-06-02
KR987000522A (en) 1998-03-30
CN1079917C (en) 2002-02-27
EP0799384B1 (en) 1998-07-22
WO1996020348A1 (en) 1996-07-04
DE4446145A1 (en) 1996-06-27
US5839345A (en) 1998-11-24
KR100409141B1 (en) 2004-04-03
DE59502932D1 (en) 1998-08-27
CN1171146A (en) 1998-01-21

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