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EP0331958B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP0331958B1
EP0331958B1 EP89102903A EP89102903A EP0331958B1 EP 0331958 B1 EP0331958 B1 EP 0331958B1 EP 89102903 A EP89102903 A EP 89102903A EP 89102903 A EP89102903 A EP 89102903A EP 0331958 B1 EP0331958 B1 EP 0331958B1
Authority
EP
European Patent Office
Prior art keywords
control
conduit
pressure
spring
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP89102903A
Other languages
German (de)
English (en)
Other versions
EP0331958A2 (fr
EP0331958A3 (fr
Inventor
Rudolf Brunner
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.)
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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 Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Priority to AT89102903T priority Critical patent/ATE101900T1/de
Publication of EP0331958A2 publication Critical patent/EP0331958A2/fr
Publication of EP0331958A3 publication Critical patent/EP0331958A3/fr
Application granted granted Critical
Publication of EP0331958B1 publication Critical patent/EP0331958B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—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
    • 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
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87177—With bypass
    • Y10T137/87185—Controlled by supply or exhaust valve

Definitions

  • the invention relates to a hydraulic control device of the type specified in the preamble of claim 1.
  • the flow resistance of the check valve causes the pressure increase, by means of which the pressure compensator keeps the pressure in the pump line continuously above the consumer pressure. Since spring loading of the closing element of the check valve remains the same over the entire working range, the pressure difference between the pressure in the pump line and the pressure in the consumer line also remains the same over the entire working range.
  • the pressure difference must be designed for the maximum output of the consumer so that the maximum output is achieved in the control position end position of the directional valve. In intermediate positions of the directional control valve, this pressure difference is therefore greater than required, so that power is wasted here, which e.g. an increased mechanical load on the pressure medium or its heating.
  • the invention has for its object to improve a hydraulic control device of the type mentioned in that the pressure difference between the pump line and the consumer line is precisely adapted to the respective needs of the consumer.
  • the pressure is increased at least over part of the stroke of the control element of the directional control valve as a function of the stepless preload of the spring of the check valve.
  • the pressure difference between the pump line and the consumer line is just large enough to allow the quantity in the consumer line to be easily reached for the quantity set with the directional valve.
  • the pressure difference increases so that a maximum pressure difference and thus the maximum quantity for the consumer can be reached in or shortly before reaching the control position end position.
  • the control characteristic curve ie the pressure medium quantity of the consumer via the stroke of the control element of the directional control valve, is also a harmonic curve which runs at least over the range of the increasing preload of the spring of the check valve with an almost constant increase.
  • the closing element of the check valve is initially hardly or not at all loaded by the spring in order to avoid unnecessary losses at the beginning of the fine control range of the directional valve.
  • the spring can even allow the closing element to have an idle stroke before prestressing begins.
  • the kickback function is ensured via the flow dynamics.
  • the embodiment according to claim 2 is structurally simple.
  • a mechanical adjusting device does not impair the working of the directional control valve, is reliable and can be easily implemented without fundamental modification of the directional control valve.
  • control element automatically biases the spring of the check valve.
  • the directional valve is not enlarged in size since the components that are important for the pressure increase are accommodated in the control element.
  • the interior of the control element which is usually not required for any other functions, can be used to advantage for the forced control of the pressure increase.
  • the back pressure on the control element resulting from the preload is negligible.
  • the embodiment according to claim 5 is also expedient because the coupling member effects the adjustment of the spring of the check valve in direct proportion to the stroke of the control member.
  • a small diameter of the tappet ensures low counter forces from the consumer pressure.
  • the embodiment according to claim 6 is expedient in view of the fact that the exact consumption-dependent power adjustment is only required over the fine control range of the directional valve.
  • This measure also has the advantage that the spring only has to be deformed over a part of the total travel of the control member and can work in a relatively linear range of its spring characteristic, even if it does not have a large overall length. The distance can be used to precisely determine the point from which the spring is pretensioned.
  • the starting point of the preload of the spring can be adjust according to claim 7 from the outside, also to be able to adjust the spring harder or softer in the deformation dependent on the stroke of the control member.
  • the embodiment of claim 8 is also expedient because by changing the effective length of the coupling element, an adaptation to the respective stroke of the control element of a directional control valve is possible.
  • the spring of the check valve can consist of two nested springs, one of which weaker only ensures the closed position in the depressurized state, while the other only takes effect from a larger stroke of the closing member - and then stronger.
  • the pretensioning of the closing element is only started when the control element has been adjusted to such an extent that a throughput of approximately 50 l / min is given to the consumer.
  • a hydraulic control device 1 for example, for a forklift or forklift truck with several hydraulic consumers, such as a lifting cylinder 2 that can be loaded on one side and a tilt cylinder 2 a that can be loaded on both sides, the number of consumers contains a corresponding number of directional control valves, in the present case two directional control valves 3 and 3a.
  • the two directional control valves 3 and 3a are connected in parallel to one another to a pump line 6, which is supplied from a pressure source P, for example a constant pump.
  • the directional control valves 3, 3a are connected to a common return line 7 to a tank R.
  • a pressure compensator 8 of conventional design which contains a slide 10 which is infinitely adjustable between a shut-off position (FIG. 1) and a passage position and which establish a direct, more or less throttled connection to the return line 7 can.
  • the slide 10 is loaded by a spring 9 in the direction of its locking position.
  • a connected control line circuit S is supplied with pressure medium from the pump line 6.
  • a first control line 12 branches off from the pump line 6 and leads via both directional valves 3, 3a to a relief connection 11 of the return line 7.
  • a control element 4, 4a is adjustable, which has a flow channel 29 which is in the neutral position 0 (FIG. 1) establishes the passage from the first control line 12 to the relief connection 11.
  • a second control line 14 leads from the spring side of the pressure compensator 8 to a connection point 12a with the first control line 12 and further to a load pressure tap connection 13 of the directional control valve 3.
  • a control line branch 14a to the load pressure tap connection is connected to the second control line 14 of the directional valve 3a guided.
  • a control line branch 14b leads via a pressure relief valve 20 for the system pressure from the control line branch 14a to the return line 7.
  • a third control line 15 leads from the pump line 6 to the other side of the slide 10 of the pressure compensator 8.
  • a first throttle point 16 is provided in the first control line 12 upstream of the connection point 12a. Their input pressure is transmitted via the third control line 15 to the side of the slide 10 in the pressure compensator 8 opposite the spring side.
  • a second throttle point 17 for the second control line 14 is e.g. provided in the control element 4, in the directional control valve 3. Their input pressure is transmitted in the second control line 14 to the spring side of the slide 10 of the pressure compensator 8. The flow resistance of the first throttle point 16 is less than the flow resistance of the second throttle point 17.
  • control element 4, 4a is infinitely adjustable from the neutral position 0 to two control positions a and b, with an intermediate position 0 / a of the control element 4 between the neutral position 0 and the control position end position a being indicated by the directional control valve 3 in FIG. 1 is indicated, in which the control element 4 has executed less than, for example, 80% of the stroke in the direction of the control position end position a.
  • the directional control valve 3 has a connection 25, to which a consumer line 5 to the lifting cylinder 2 is connected, from which a flow path 23 indicated by dashed lines branches, in which the pressure of the consumer line 5 is present. Between the load pressure tap connection 13 and the flow path 23 is one in the control member 4 Flow connection can be established as soon as the control element 4 is adjusted in the direction of the control position a.
  • a channel 13a is connected to a channel 28 in the control member 4 via the second throttle point 17, the channel 13a being connectable to the load pressure tap connection 13 and the channel 28 being able to be connected to the consumer line 5 via a flow connection 24 or the flow path 23.
  • the second throttle point 17 is a check valve 19 having a spring 18, a mechanical adjusting device 21 (see FIGS. 2, 3) being provided for pretensioning the spring 18.
  • a main flow path 22 is formed in the control member 4, which connects a connection 26 of the pump line 6 to the connection 25 of the consumer line 5 in the control position a.
  • a main flow path 56 connects the connection 25 to a connection 27 of the return line 7.
  • Lockable connections 30, 31 serve to shut off the flow path for the control line 12 during the stroke into the control position a.
  • the second directional valve 3a for the tilt cylinder 2a is connected to it via consumer lines 5a and 5b.
  • Its control element 4a contains main flow paths 32, 33 and 34, 35 in order to be able to control the alternating action on both sides of the tilt cylinder.
  • a further second throttle point 17a is contained in the control line branch 14a. Your input pressure is on the spring side of the slide 10 of the pressure compensator 8 when the second directional valve 2a is actuated. If necessary, a check valve is provided at the throttle point 17a.
  • control elements 4, 4a of the directional control valves 3, 3a are with Actuators 38 adjustable. It is also conceivable to adjust the control members by applying pressure at the ends.
  • the directional control valve 3 (FIGS. 2, 3) has, in a cuboid housing 36, a longitudinal bore 37 for the control element 4 designed as a slide piston.
  • the actuation 38 (arrow) acts on the upper end of the control element 4.
  • the bore 37 is closed by an end wall 39, which cooperates with the adjusting device 21 for the spring 18 of the check valve 19.
  • the check valve 19 is arranged in the interior of the control member 4, specifically in a chamber 40, in which a seat 41 is provided at the upper end for a spherical closing member 42 of the check valve 19.
  • a spring plate 43 is located at the lower end 18a of the spring 18 opposite the closing member 42.
  • the lower end 18b of the spring 18 is seated on a spring plate 48 which is supported on an insert 44 screwed into the chamber 40 from below. Between the spring plates 48 and 43, the spring 18 is held with a very small preload, if at all. If necessary, the closing member 42 can even carry out a slight idle stroke.
  • a coupling member 45 e.g. a longitudinally displaceable plunger, which projects with its free end 46 to the end wall 39. There is a distance x between the free end 46 and the end wall 39, which forms an abutment for the free end 46, in the neutral position of the control member 4.
  • the diameter of the ram is about 1mm.
  • the channel 13a indicated in FIG. 1 begins on the outer circumference of the control element 4 in a longitudinal flow pocket 47 and leads to the side of the seat 41 facing away from the closing member 42.
  • the channel 28 leads from the chamber 40 to the outer periphery of the control member 4.
  • the second control line 14 can be seen, which leads to the load pressure tap connection 13 in the wall the bore 37 leads.
  • a twist in the bore 37 represents the connection 25 to the consumer line 5 and forms the flow path or flow channel 23, 24 indicated in FIG. 1 during the stroke to the control position a.
  • the load pressure tap connection 13 connected to the channel 13a.
  • the bore wall covers the mouth of the channel 28, which is thus separated from the connection 25.
  • control member 4 is equipped with two diametrically opposed, longitudinal, large flow pockets, which form the main flow path 22 indicated in FIG. 1 in the control position a and are connected by a bore 49 (FIG. 3).
  • the flow pockets are in front of the connection 26 to the pressure source P.
  • the circumference of the control element 4 separates the connection 25 from the connection 26.
  • control position a When the control element 4 is moved downward (control position a), the flow pockets (flow path 22) work together in an aperture-like manner with the connection 25 in order to produce a more or less throttled connection from the pump line 6 to the consumer line 5.
  • control element 4 If the control element 4 is shifted upward from the neutral position, the outer periphery of the control element 4 separates the connection 25 from the connection 26, while the lower end (flow path 56) of the control element 4 connects the connection 25 to the connection 27 in the lower end of the bore 37 releases, so that the pressure medium flows out of the lifting cylinder 2.
  • the load pressure tap connection 13 is located in the peripheral region of the bore wall, along which the flow pocket 47 lying between the large flow pockets and separated therefrom is moved when the control member 4 is adjusted.
  • the control member 4 is secured against rotation. Between the neutral position and the control position a, the connection between the second control line 14 and the channel 13a is open.
  • the mouth of the channel 28 on the circumference of the control member 4 is in the neutral position (FIG. 3) at a distance above the recess forming the connection 25, which approximately corresponds to the distance x.
  • inclined surfaces 57 are formed which - offset in the circumferential direction - enter the circumference of the control member 4 at approximately the same axial height as the mouth of the channel 28.
  • connection 25 As soon as the surfaces 57 into the the connection 25 forming turn begin to occur, aperture-like openings arise through which the pressure medium flows from the connection 26 to the consumer line. At the same moment or even with a slight advance, the mouth of the channel 28 also enters the recess. The pressure prevailing in the connection 25 is always transmitted in this way into the chamber 40, where it presses the closing member 42 against the seat 41.
  • the flow channel 29 in the control element 4 is shut off beforehand, so that the first control line 12 is no longer connected to the relief connection 11.
  • the slide 10 the pressure compensator 8 is adjusted until it gradually throttles.
  • the pressure in the second control line 14 is present at the closing member 42 via the channel 13a. Pressure medium flows past the closing member 42 to the consumer line 5, so that the pressure in the second control line 14 adjusts to a value which is approximately the same as the consumer pressure.
  • the pressure in the second control line and, depending on it, in the pump line 6 is increased, not only as a function of the increasing load pressure in the consumer line 5, but also due to the progressive preload of the spring 18 the increase in the bias of the spring 18 is mainly effective in the so-called fine control range of the control element 4, ie between the stroke position in which the surfaces 57 are just beginning to enter the recess forming the connection 25, for example from 50 l / min, and the stroke position in which the large flow pockets of the flow path 22 are substantially unthrottled to the connection 25.
  • the pressure difference between the pressure in the pump line 6 and the pressure in the consumer line 5 increases steadily.
  • the pretension of the spring 18 decreases again in accordance with the stroke.
  • the flow path 56 connects the connection 25 to the connection 27, so that the pressure medium can flow out.
  • the check valve 19 is then without function and closed.
  • the second directional valve 3a is adjusted from its neutral position, the pressure in the pump line 6 is increased by the action of the second throttle point 17a for the entire working range of the directional valve 3a with a constant difference to the pressure in one of the consumer lines 5a or 5b. If both directional control valves 3, 3a are actuated at the same time, the pressure is increased as a function of the lower inlet pressure of one of the second throttle points 17 and 17a. If this is to be avoided, means (not shown) are provided which give the directional control valve 3 priority over the directional control valve 3a.
  • the check valve 19, the spring preload of which can be changed as a function of the stroke of the control element 4, can also be arranged outside the directional control valve or in the housing of the directional control valve in the second control line 14. Furthermore, it is easily possible to equip each of the directional control valve of the control device 1 for each direction of action with such a check valve with a prestressable spring, so that the pressure increase for exactly adjusted is effective for every consumer and even for each direction of work, possibly to a different extent. Change-over valves can also be provided in the control circuit, which ensure that the consumer or the consumer work direction takes precedence over the others that currently require the greatest amount of pressure medium.
  • a hydraulic or electrical adjustment device could also be provided.
  • the consumer pressure in the connection 25 can be brought to a piston on which the spring 18 is supported and which prestresses the spring 18 with increasing consumer pressure.
  • the pretension would be strictly dependent on the stroke of the control element, because with increasing stroke of the control element in the direction of the control position end position, the pressure in connection 25 increases accordingly.
  • a dashed screw 50 is indicated in the end wall 39, the end of which forms the abutment 39 'for the free end 45.

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

Claims (8)

  1. Dispositif de commande hydraulique (1), avec un distributeur (3, 3a), au moins, monté en amont d'un consommateur (2, 2a) et dont l'organe de commande (4, 4a) obture une conduite de consommateur (5, 5a, 5b), au moins, dans une position neutre (0), et relie cette conduite dans deux positions de commande (a, b), alternativement, avec une tuyauterie de pompage (6), alimentée par une source de pression (P), ou avec une conduite de retour (7), avec une balance de pression (8), raccordée à la tuyauterie de pompage et présentant un tiroir (10), chargé par ressort en direction de la position d'obturation, pour le retour du fluide sous pression non requis par le consommateur, avec un circuit de conduites pilotes (S), raccordé à la tuyauterie de pompage et présentant une première conduite pilote (12), qui mène de la tuyauterie de pompage à un raccordement de décharge, relié à la conduite de retour en position neutre, une deuxième conduite pilote (14), reliée à la première conduite pilote (12), pour a jonction du côté ressort du tiroir (10) de la balance de pression (8) avec au moins un raccordement de prise de pression de charge (13) du distributeur (3, 3a), et une troisième conduite pilote (15) en direction d'un côté du tiroir (10) de la balance de pression (8), le raccordement de prise de pression de charge (13) étant relié à la conduite de consommateur dans une position de commande (a), du moins, avec un premier point d'étranglement (16) dans la première conduite pilote (12), dont la pression d'entrée agit sur le tiroir (10) contre la charge du ressort, par l'intermédiaire de la troisième conduite pilote (15), et avec un deuxième point d'étranglement (17, 17a) en aval du point de jonction (12a) entre les première et deuxième conduites pilotes, dont la pression d'entrée peut être relevée par le déplacement de l'organe de commande (4, 4a) à partir de la position neutre (0) et être transmise au côté ressort du tiroir (10), le deuxième point d étranglement (17) étant au moins un clapet antiretour (19), qui comporte un ressort (18), agissant dans le sens de fermeture, et s'ouvre dans le sens d'écoulement en direction de la conduite de consommateur (5), pour l'écoulement de la deuxième conduite pilote (14), au travers au raccordement de prise de pression de charge (13), en direction de la conduite de consommateur (5), caractérisé en ce que le ressort (18) peut être soumis à une tension initiale sans intervalles et proportionnelle au mouvement de course et continue, sur une partie du moins de la course de l'organe de commande (4) de la position neutre dans la position fin de course de commande (a).
  2. Dispositif de commande hydraulique suivant la revendication 1, caractérisé en ce qu'un dispositif de réglage mécanique (21) est prévu pour la tension initiale du ressort 18).
  3. Dispositif de commande hydraulique suivant les revendications 1 et 2, caractérisé en ce que le clapet antiretour (19) est disposé à l'intérieur de l'organe de commande (4) du distributeur (3).
  4. Dispositif de commande hydraulique suivant l'une quelconque au moins des revendications 1 à 3, caractérisé en ce que le clapet antiretour (19) est disposé, dans l'organe de commande (4), dans un compartiment (40) entre un canal (13a) en direction du raccordement de prise de pression de charge (13) et un canal (28), qui peut être relié à la conduite de consommateur (5), et en ce que le ressort (18), associé sur une extrémité à l'organe de fermeture (42) du clapet antiretour (19), peut s'appuyer sur l'autre extrémité sur une butée (39, 39'), disposée d'une manière stationnaire par rapport à l'organe de commande (4), lors du mouvement de course de ce dernier.
  5. Dispositif de commande hydraulique suivant la revendication 4, caractérisé en ce qu'un organe d'accouplement rigide (45), un poussoir guidé avec une possibilité de déplacement, de préférence, qui transmet au ressort (18) le mouvement relatif entre l'organe de commande (4) et la butée (39, 39'), est prévu entre l'organe de fermeture (42) et le butée (39, 39').
  6. Dispositif de commande hydraulique suivant les revendications 4 et 5, caractérisé en ce que, dans la position neutre (0) de l'organe de commande (4), l'extrémité libre (46) de l'organe d'accouplement (45) et la butée (39, 39') sont séparées par une distance (x), inférieure à la course de l'organe de commande (4) de la position neutre (0) dans la position fin de course de commande (a).
  7. Dispositif de commande hydraulique suivant la revendication 6, caractérisé en ce que la butée (39') est ajustable pour modifier la distance (x).
  8. Dispositif de commande hydraulique suivant la revendication 5, caractérisé en ce que l'organe d'accouplement (45) est ajustable dans sa longueur active.
EP89102903A 1988-03-08 1989-02-20 Dispositif de commande hydraulique Expired - Lifetime EP0331958B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89102903T ATE101900T1 (de) 1988-03-08 1989-02-20 Hydraulische steuervorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3807583 1988-03-08
DE3807583A DE3807583C1 (fr) 1988-03-08 1988-03-08

Publications (3)

Publication Number Publication Date
EP0331958A2 EP0331958A2 (fr) 1989-09-13
EP0331958A3 EP0331958A3 (fr) 1991-04-10
EP0331958B1 true EP0331958B1 (fr) 1994-02-23

Family

ID=6349164

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89102903A Expired - Lifetime EP0331958B1 (fr) 1988-03-08 1989-02-20 Dispositif de commande hydraulique

Country Status (5)

Country Link
US (1) US4941321A (fr)
EP (1) EP0331958B1 (fr)
JP (1) JPH07109206B2 (fr)
AT (1) ATE101900T1 (fr)
DE (2) DE3807583C1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5081839A (en) * 1990-01-29 1992-01-21 Caterpillar Inc. Pressure compensated hydraulic system
DE19631803B4 (de) * 1996-08-07 2007-08-02 Bosch Rexroth Aktiengesellschaft Hydraulische Steuervorrichtung
JP3600936B2 (ja) * 1997-04-02 2004-12-15 フォイト トゥルボ ゲーエムベーハー ウント コンパニー コマンディトゲゼルシャフト バルブ装置、特に比例バルブ兼方向制御バルブ
DE19960302A1 (de) * 1999-12-14 2001-06-21 Meiller Fahrzeuge Steuerventilanordnung für einen hydraulischen Zylinder
DE10224741A1 (de) * 2002-06-04 2003-12-18 Linde Ag Hydraulische Hubvorrichtung
GB2501486A (en) * 2012-04-24 2013-10-30 Jc Bamford Excavators Ltd Work machine having a hydraulic system comprising variable orifice ratios
JP5978900B2 (ja) * 2012-06-07 2016-08-24 株式会社ジェイテクト 電磁弁

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US971216A (en) * 1909-05-29 1910-09-27 William C Robinson Fitting for electric conduits.
US3971216A (en) * 1974-06-19 1976-07-27 The Scott & Fetzer Company Load responsive system with synthetic signal

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2620041A1 (de) * 1976-05-06 1977-11-24 Bosch Gmbh Robert Hydraulische steuereinrichtung
DE2804045A1 (de) * 1978-01-31 1979-08-09 Bosch Gmbh Robert Steuervorrichtung fuer einen hydraulisch betriebenen verbraucher
US4436020A (en) * 1982-03-11 1984-03-13 Caterpillar Tractor Company Dual input pressure compensated fluid control valve
JPS60109604A (ja) * 1983-11-15 1985-06-15 Daikin Ind Ltd 流体回路
FR2569786B1 (fr) * 1984-08-31 1987-03-20 Vickers Systems Sa Distributeur hydraulique haute pression, a generateur de pression de pilotage
DE3611244A1 (de) * 1986-04-04 1987-10-08 Rexroth Mannesmann Gmbh Stromregelventil
DE3722083C1 (de) * 1987-07-03 1988-09-15 Heilmeier & Weinlein Hydraulische Steuervorrichtung

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US971216A (en) * 1909-05-29 1910-09-27 William C Robinson Fitting for electric conduits.
US3971216A (en) * 1974-06-19 1976-07-27 The Scott & Fetzer Company Load responsive system with synthetic signal

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
US-A3 971 216 *

Also Published As

Publication number Publication date
EP0331958A2 (fr) 1989-09-13
ATE101900T1 (de) 1994-03-15
JPH07109206B2 (ja) 1995-11-22
DE58907019D1 (de) 1994-03-31
EP0331958A3 (fr) 1991-04-10
DE3807583C1 (fr) 1989-03-09
JPH01279102A (ja) 1989-11-09
US4941321A (en) 1990-07-17

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