EP0219052B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP0219052B1
EP0219052B1 EP86113895A EP86113895A EP0219052B1 EP 0219052 B1 EP0219052 B1 EP 0219052B1 EP 86113895 A EP86113895 A EP 86113895A EP 86113895 A EP86113895 A EP 86113895A EP 0219052 B1 EP0219052 B1 EP 0219052B1
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EP
European Patent Office
Prior art keywords
pressure
control
line
valve
diaphragm
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
EP86113895A
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German (de)
English (en)
Other versions
EP0219052A2 (fr
EP0219052A3 (en
Inventor
Rudolf Brunner Obering
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
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Priority to AT86113895T priority Critical patent/ATE73905T1/de
Publication of EP0219052A2 publication Critical patent/EP0219052A2/fr
Publication of EP0219052A3 publication Critical patent/EP0219052A3/de
Application granted granted Critical
Publication of EP0219052B1 publication Critical patent/EP0219052B1/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
    • F15B13/0416—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
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation 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
    • F15B11/003—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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with 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
    • 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out 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
    • F15B2211/40—Flow control
    • F15B2211/465—Flow control with pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve

Definitions

  • the invention relates to a hydraulic control device of the type specified in the preamble of claim 1.
  • the three-way flow regulator with its measuring orifice is arranged in the working pressure line and in the direction of flow to the hydraulic motor upstream of the check valve.
  • the bypass line bypasses the check valve and is also connected to the control outlet of the three-way flow regulator.
  • the two-way flow controller with its measuring orifice is located in the bypass line.
  • the current regulators are characterized by the fact that they keep the pressure medium quantity constant depending on the current applied to the proportional magnet of their measuring orifice regardless of the load, and by changing the current applied to their proportional magnet they allow the speed of the hydraulic motor to be changed, again independently of the load.
  • a control device was developed, as is known from DE-A-3233 046, Fig. 1.
  • a two-way current regulator with a measuring orifice actuated by a single proportional magnet is only provided in the bypass line.
  • the current regulator influences the quantity flowing away from the pressure source to the hydraulic motor or from the hydraulic motor in that it discharges a quantity of pressure medium, which is dependent on the current applied to the proportional magnet, into the tank.
  • the pressure source is a pump that only runs against the load when the hydraulic motor is working and is driven by a shunt-electric motor, in which the delivery rate per unit of time changes with increasing back pressure.
  • the two-way flow controller towards the tank cannot compensate for these changes, which means that the hydraulic motor works slower with increasing load and faster with decreasing load. This is undesirable in practice, where sensitive speed control is important. In addition, an undesirable shift jerk occurs when starting.
  • the invention has for its object to provide a control device of the type mentioned, which is characterized by a reduced structural complexity and by a load-independent speed control of the hydraulic motor in both directions.
  • a second proportional magnet and a second measuring orifice are dispensed with because the single measuring orifice works with its proportional magnet, depending on the selected direction of movement of the hydraulic motor, either with the three-way or with the two-way flow controller. Since only a single proportional magnet needs to be controlled, the control effort is reduced.
  • the control device works independently of the load, because the three-way flow controller, when the hydraulic motor works against the load, conducts the pressure medium quantity predetermined by the proportional magnet to the hydraulic motor independently of the back pressure generated by the load and thereby varies the quantity of pressure medium discharged to the return line.
  • the three-way flow controller compensates for changes in the delivery rate of the pressure medium pump under load. The speed of the hydraulic motor can be controlled sensitively.
  • the embodiment of claim 2 is expedient because the shut-off valve, which saves a separate load holding valve, prevents the pressure medium from flowing out via the control orifice of the two-way flow regulator when the three-way flow regulator is actuated.
  • the two control orifices do not interfere with each other despite the common orifice because one only works if the pressure in front of the orifice plate is higher than behind it, while the other only works with reverse pressure conditions.
  • the feature of claim 3 is also important so that the work of the three-way flow controller is not impaired when the shut-off valve is closed. There is then a free flow connection from the three-way flow controller to the tank despite the bypass line being shut off.
  • This embodiment is characterized by a compact design in which the control piston has a double function, since it forms both the pressure compensator for the three-way flow regulator and the pressure compensator for the two-way flow regulator.
  • the control piston has a double function, since it forms both the pressure compensator for the three-way flow regulator and the pressure compensator for the two-way flow regulator.
  • the two pressure compensators use is made of the fact that when the hydraulic motor moves against the load, the pressure in front of the orifice plate must be higher than behind the orifice plate, while the pressure behind the orifice plate when the hydraulic motor moved under the load is higher than before Orifice plate.
  • a structurally simple embodiment is further evident from claim 5.
  • the pump input channel takes over the pressure medium supply to the control orifice of the three-way flow regulator formed by the control edge of the control piston and the tank connection, while the side inlet with the pump input channel takes over the function of the control orifice when the two-way flow regulator is working.
  • the feature of claim 6 also contributes to the structural simplification, because the springs required for the opposite working of the pressure compensators in both directions are united in a spring arrangement.
  • the feature of claim 7 is also expedient.
  • the solenoid-operated shut-off valve is expediently coupled in terms of control technology to the proportional magnet of the measuring orifice.
  • a further advantageous embodiment is set out in claim 8.
  • the pressure compensator of the two-way flow controller can be used to hold the load, because it either takes over a travel or control function while its control function is switched off.
  • This also has the advantage that there is no shift jerk when starting in one or the other direction of movement of the hydraulic motor, because when the load is held in the pressure compensator, no significant pressure medium volumes flow out that would have to be compensated for when the hydraulic motor started to move.
  • the pressure effective on the other side of the pressure compensator brings the control orifice into its shut-off position, which it maintains reliably even over longer load holding periods, because none in the opening direction counter pressure can occur.
  • the 2/3-way valve is small and inexpensive as a seat valve and almost leak-free. It only has to process small amounts of pressure medium.
  • the measure of claim 12 is also important because it creates the possibility of stopping the hydraulic motor by means of the path or control function of the pressure compensator and to switch off its control function. This has the advantage that the orifice plate can be released from this task, so that the hydraulic motor, so to speak stops against the pressure compensator. This also avoids a stop jerk, which in connection with the other measures which bring about a jerk-free start-up leads to an almost ideal control of the movement of the hydraulic motor.
  • the lifting module component requires little space for accommodation and contains all the components necessary for the control device to work properly.
  • a control device previously operated with conventional control devices can be converted with little effort because the lifting module component can have essentially the same connections and connection diagrams as the conventional control devices.
  • a hydraulic control device 1 is part of a lifting device, not shown, e.g. a forklift, and serves to actuate a hydraulic motor 2, e.g. a single-acting hydraulic cylinder, with a piston 3, which can be extended against a load F and retracted under the effect of the load F.
  • a pressure source 4 e.g. a pump driven by a shunt electric motor is provided, which promotes pressure medium from a tank 5.
  • a measuring orifice 7 is arranged in a housing 6 and is actuated by a proportional magnet 8, in proportion to an electrical signal (control current) which can be changed in the control range according to any profile.
  • a pressure compensator arrangement 10 with two pressure compensators is also provided in a housing 9 that is either combined with the housing 6 or separated from it.
  • the metering orifice 7 forms with the upstream pressure compensator arrangement 10 a three-way flow controller and a two-way flow controller, the three-way flow controller for controlling the speed of the hydraulic motor 2 against the load F and the two-way flow controller for controlling the speed of the hydraulic motor 2 under the load F is provided.
  • the pressure source 4 is connected to the hydraulic motor 2 via a working pressure line 11, which consists of three successive line sections 11a, 11b, 11c.
  • the first power section 11a is connected to the housing 9 and contains a check valve 12 opening in the flow direction to the hydraulic motor 2.
  • a pressure relief valve 14 is provided in a parallel line 13 branching from the line section 11a to the housing 9 to limit the maximum system pressure.
  • branches in the housing 9 in an annular channel 22 from the line section 11a branches in the housing 9 in an annular channel 22 from the line section 11a a bypass line 15, in which a two-position shut-off valve 16 is installed, which, for example at 17 by means of a magnet (not shown), can be switched from the drawn shut-off position against spring pressure into a through position.
  • the bypass line 15 leads to a connection bore 24 in the housing 9 and, like the parallel line 13, is connected to the tank 5 via a tank line 18.
  • a control sleeve 20 is fixed in a housing chamber 19, which has a pump inlet channel 21 in the form of several bores distributed in the circumferential direction and the ring channel 22 on the outer circumference, to which the line section 11a is connected on one side and the bypass line on the other side. Furthermore, a further outer ring channel 23 is provided in the control sleeve 20 at a distance from the ring channel 22, from which tank connections 25 distributed over the circumference lead to the interior of the control sleeve 20.
  • the annular channel 23 is connected to the line 18 and the tank 5 via the connection bore 24.
  • the side 26 of the housing chamber 19 adjacent to the tank connection 25 is connected to the housing 6 of the measuring orifice 7 via the second line section 11b.
  • the side 27 of the housing chamber 29 facing away from the tank connection 25 is separated from the side 26 by a regulating piston 28 belonging to two pressure compensators, the regulating piston 28 being displaceably sealed in the control sleeve 20.
  • Fig. 1 the control piston 28 is in its basic position, in which it is aligned with a side inlet 29, which is for example an annular channel, to the pump inlet channel 21.
  • the inlet 29 communicates with the interior of the control piston 28, ie with the side 26 of the housing chamber 19.
  • the control piston 28 In the area of the tank connection of the control sleeve 20, the control piston 28 has a circumferential control edge 30.
  • the control piston 28 covers the tank connection 25 in a sealing manner.
  • a spring 31 In the side 27 of the housing chamber 19 there is a spring 31 which is supported between spring abutments 32 and 33 and is connected to the control piston 28 via a pull rod 34.
  • Both spring abutments 32 and 33 are supported in the housing 9 and can move when the Control piston 28 are lifted from its basic position on each side, so that the control piston 28 must move in both directions of movement against the force of the spring 31.
  • a control line 35 leads from the side 27 of the housing chamber 19 through a throttle 36 to the measuring orifice 7.
  • the measuring orifice 7 has an annular channel 37 in the housing 6, which is connected to the side 26 of the housing chamber 19 of the pressure compensator arrangement 10 via the second line section 11b.
  • the ring channel 37 belongs to a housing bore 46 and is separated from a bore section 47 by a control edge 38.
  • an orifice piston 39 can be displaced in a sealed manner and is provided in its lower edge region with triangular notches 40 which, together with the control edge 38, form the actual orifice plate.
  • a spring 41 loads the orifice piston 39 in the upward direction into the end position shown in FIG. 1.
  • a pin 42 is provided which plunges into a through hole 43, via which the pressure under the orifice piston 39 is transmitted to the other side, so that the orifice piston 39 is pressure-balanced.
  • an actuating pin 44 of the proportional magnet 8 engages, which is designed so that when excited it pushes the orifice piston 39 into a lower and shut-off position, in which the lower end of the actuating pin 44 rests on a stop.
  • the bore section 47 from which the third line section 11c leads to the hydraulic motor 2, is connected to the side 27 of the housing chamber 19 via the control line 35 and closed to the outside by a sealing plug 48.
  • FIG. 2 shows the structure of the essential components of the control device 1 from FIG. 1 in a symbolic representation, these components forming a lifting module component M, which all work together in and on a housing Contains components, including the actuating magnet 45 for the shut-off valve 16 in the bypass line 15.
  • the control device works as follows: 1 and 2, the control device is in its passive position; both the proportional magnet 8 and the actuating magnet 45 are de-energized.
  • the orifice 7 is fully open.
  • the shut-off valve 16 is closed.
  • the pump 4 is stopped.
  • a load F resting on the piston 3 is absorbed by the check valve 12 on the one hand and by the shut-off valve 16 on the other. Since the orifice plate 7 is open, the same pressure prevails on both sides of the control piston 28, so that it remains in the basic position shown.
  • the proportional magnet 8 is fully excited; the orifice piston 39 moves downward; the orifice plate 7 is closed.
  • the shut-off valve 16 remains in the shut-off position.
  • the pressure medium flow coming from the pump 4 in the line section 11a is divided on the one hand via the line sections 11b, c and the measuring orifice 7 into the hydraulic motor 2 and on the other hand via the control orifice 25, 30 and the tank line 18 to the tank 5 flowing partial flows.
  • the size of the partial flow flowing to the hydraulic motor 2 results from the pressure equilibrium, at which the pressure difference across the control orifice 30, 25 is equal to the pressure difference across the measuring orifice 7 plus the pressure generated by the load F.
  • the cross section of the measuring orifice 7 is determined by the proportional magnet 8 selected.
  • the pressure difference across the orifice plate 7 produces on the control piston 28 a force directed to the left in FIG. 1, which displaces it against the force of the spring 31 until the pressure difference required for the above-mentioned pressure balance is established on the control orifice 25.30. Changes then the load, then with the position of the control piston 28 unchanged, the partial flow through the control orifice 30, 25 would change, which would also result in a change in the partial flow flowing through the orifice 7 and thus the pressure difference across the orifice 7.
  • the partial flow flowing to the hydraulic motor 2 through the line section 11c is also kept constant when the pump 4 decreases in its delivery rate or reduces its delivery rate due to the back pressure. Then, correspondingly less pressure medium flows into the tank via the control orifice 25, 30 and the line 18, so that the hydraulic motor 2 receives the unchanged partial flow.
  • the triangular notches 40 of the orifice piston 39 ensure a steady or linear control characteristic.
  • the pump 4 is first switched off and, when the proportional magnet 8 is fully excited, the shut-off valve 16 in the bypass line 15 is switched to its open position.
  • the excitation of the proportional magnet 8 is reduced according to the desired speed.
  • the pressure medium flow displaced by the hydraulic motor 2 by the load F flows via the measuring orifice 7 to the right side 26 of the housing chamber 19 and from there through the control orifice 21, 29 into the bypass line 15, through the shut-off valve 16 and the tank line 18 to the tank 5 Via the pressure orifice 7, the pressure difference in front of the orifice (bore section 47) is greater than the pressure in the annular space 37, so that the control piston 28 is displaced to the right in FIG.
  • control orifice 21, 29 form.
  • the size of the pressure medium flow to the tank 5 results from the pressure equilibrium at which the pressure caused by the load is the same as the pressure difference across the orifice plate 7 plus the pressure difference through the control orifice 21, 29.
  • the control piston 28 is shifted to the right until the required pressure difference at the control orifice 21, 29 is constant over the measuring orifice 7 and thus also the pressure medium flow to the tank 5, i.e. for the pressure equilibrium mentioned above. the speed of the hydraulic motor 2 remain constant.
  • shut-off valve 16 is simultaneously brought into the blocking position, so that the load is held by the shut-off valve 16 and the check valve 12.
  • the measuring orifice 7 could also be arranged in the working pressure line in the flow direction to the hydraulic motor 2 in front of the pressure compensator arrangement 10.
  • the function would be the same.
  • the shut-off valve 16 could also be another control element that can be brought from a blocking position into a through position.
  • all components i.e. also the check valve 12 and the pressure limiter 14 and the shut-off valve 16, combined in a lifting module element housing, which also contains the pressure compensator arrangement 10 and the measuring orifice 7. This has structural advantages.
  • FIG. 3 shows a modified hydraulic control device 1 'which is constructed similarly to the control device 1 according to FIGS. 1 and 2.
  • the pressure compensator arrangement 10' is different because one with the measuring orifice 7 is the two-way flow controller (53). forming pressure compensator 50 with its control orifice in the first bypass line 15 'to the tank 5, while another pressure compensator 52 forming the three-way flow regulator (54) with the measuring orifice 7 with its control orifice in a second, upstream of the check valve 12 from the working pressure line 11 to the tank 5 branching bypass line 51 is arranged.
  • the two control orifices are actuated in opposite directions to one another, ie the control orifice of the pressure compensator 50 is drawn in the closing direction via a control line 55 with a control pressure drawn between the measuring orifice 7 and the hydraulic motor 2 and in the opening direction via a control line 56 with one between the check valve 12 and the measuring orifice 7 tapped control pressure and the force of a spring 59, while the control orifice of the other pressure compensator 52 is tapped in the closing direction by the force of a spring 63 and a tapped between the orifice plate 7 and the hydraulic motor 2 and transmitted by a control line 62 control pressure and in the Opening direction is acted upon by a control pressure tapped from the bypass line 51 via a control line 61.
  • the control piston provided there is indicated at 64 in the pressure compensator 52.
  • a 2/3 way valve 57 is provided, which is expediently a seat valve, and in the illustrated shut-off position interrupts the control line 56 and the side of the pressure compensator 50, on which its control piston is actuated in the opening direction, via a line 58 to Relieved tank.
  • the tank line 58 is disconnected and the passage through the control line 56 is free.
  • the control orifice of the pressure compensator 52 is also reliably in the shut-off position when the load is held, so that the part of the working pressure line 11 lying in front of the check valve 12 is not involuntarily relieved of pressure.
  • a preload valve 60 is provided in the first bypass line 15 ′, which is set to a preload pressure that is greater than the opening pressure of the regulating orifice of the pressure compensator 50, which pressure is predetermined by the force of the spring 59, in the event that that the piston 3 of the hydraulic motor 2 moved to the stop can be, whereby the pressure in the working line 11 may drop below the opening pressure of the control orifice of the pressure compensator 50 and this could go into its open position in an uncontrolled manner.
  • the pressure medium would then flow unhindered through the open control orifice of the pressure compensator 50 and the hydraulic motor would not start its travel movement.
  • control line 61 ′ is connected downstream of the check valve 12 and the biasing valve 60 ′ is dependent on the pressure between the measuring orifice 7 and the hydraulic motor 2 Hydraulically controlled via a control line 66 against a spring 65, which is designed so strong that it automatically brings the biasing valve 60 'into the shut-off position as soon as the pressure in the control line 66 drops below the opening pressure of the regulating orifice of the pressure compensator 50.
  • the biasing valve 60 ' can be designed in the manner of a spring-loaded slide. Instead of the pressure pre-control via the control line 66, an actuating magnet should also be provided, which is de-energized when the pressure drops.
  • the control devices 1 'and 1'' operate as follows: When the hydraulic motor 2 is moved against the load, the hydraulic pump 4 delivers pressure medium into the working pressure line 11.
  • the 2/3 way valve 57 in the control line 56 is in its blocking position; the control orifice of the pressure compensator 50 is relieved on the opening side and works like a directional control valve in the blocking position.
  • the pressure built up in the working pressure line 11 is present at the control orifice of the pressure compensator 50.
  • the hydraulic motor 2 is moved at the selected speed. Excess pressure medium will drained into the tank 5 through the control orifice of the pressure compensator 52 via the bypass line 51.
  • this regulating orifice ensures that the pressure difference set on the orifice 7 is kept constant and thus the constant speed of the hydraulic motor 2. If the hydraulic motor 2 is to be stopped, the hydraulic pump 4 turned off and, if necessary, also brought the orifice plate 7 into the shut-off position, so that the control orifice of the pressure compensator 52 opens until it is moved into the shut-off position by the spring 63 and the pressure in the control line 62 after the pump 4 has been switched off. The load pressure is held by the check valve 12 and by the control orifice of the pressure compensator 50.
  • the proportional magnet 8 of the orifice plate 7 can be de-energized so that it opens and is released from load holding tasks.
  • the proportional magnet 8 is excited to completely close the measuring orifice 7 when the pump 4 is switched off and then partially de-energized again in accordance with the desired speed, so that the measuring orifice 7 generates a certain pressure difference for the outflow of the pressure medium .
  • the 2/3-way valve 57 is switched into the through position, so that the control orifice of the pressure compensator 50 takes over its control function again, that is, it allows so much pressure medium to flow into the tank via the bypass line 15 'that the set orifice 7 is set Pressure difference is maintained regardless of whether the load pressure changes or not. If the piston 3 of the hydraulic motor 2 moves to its lower end position, the pressure in the working pressure line 11 would drop to 0.
  • the control device 1 ′′ according to FIG. 4 works essentially the same as the control device 1 ′.
  • the effective control pressure on the pressure compensator 52 of the three-way flow regulator 54 when the pump 4 in the control line 61 'is switched off cannot open the regulating orifice of the pressure compensator 52 because the control pressure in the control line 62 and the force of the spring 63 are effective in the closing direction.
  • the biasing valve 60 ′ is brought into the shut-off position by the spring 65 as a function of pressure if the pressure in the working pressure line threatens to drop too far.
  • the other functions run as described above.
  • FIGS. 3 and 4 are distinguished by the omission of a separate load-holding valve on the one hand and by an almost ideal jerk-free control behavior on the other.
  • a fixedly set orifice plate 7 could also be provided for both pressure compensators, for example in a tail lift control in which the same and working from the set speeds.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Lifting Devices For Agricultural Implements (AREA)
  • Servomotors (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (13)

  1. Dispositif de commande hydraulique (1, 1', 1'') pour un moteur hydraulique (2) fonctionnant dans une direction contre une charge (F), et mobile dans le sens opposé sous l'effet de la charge (F), dans un appareil de levage notamment, avec une conduite de pression de service (11), qui relie une source de pression (4) au moteur hydraulique (2), et dont part une conduite de bipasse (15, 15', 51) au moins en direction d'un réservoir (5), avec un régulateur de débit à trois voies (54), présentant un diaphragme de mesure (7) commandé par un aimant proportionnel, et un premier diaphragme de réglage (25, 30) prévu entre la conduite de pression de service (11) et le réservoir (5), et sur lequel le diaphragme de réglage (25, 30), pour déplacer le moteur hydraulique (2) contre la charge (F), est ajustable hydrauliquement dans un agencement de balances de pression (10; 10'), entre une position de fermeture et une position de passage en direction du réservoir (5), en fonction de la pression différentielle réglée sur le diaphragme de mesure (7) au moyen de l'aimant proportionnel (8), avec un régulateur de débit à deux voies (53), présentant un diaphragme de mesure (7) commandé par un aimant proportionnel, et un deuxième diaphragme de réglage (21, 29) disposé entre la conduite de pression de service (11) et la conduite de bipasse (15, 15'), et sur lequel le diaphragme de réglage (21, 29) est ajustable hydrauliquement dans un agencement de balances de pression (10, 10'), entre une position de fermeture et une position de passage dans la conduite de bipasse (15, 15'), en fonction de la pression différentielle sur un diaphragme de mesure (7), réglée au moyen de l'aimant proportionnel (8), le régulateur de débit à trois voies et le régulateur de débit à deux voies pouvant être commandés alternativement, en fonction du sens de mouvement du moteur hydraulique (2), et avec un clapet de non-retour (12), s'ouvrant en direction du moteur hydraulique (2) et disposé dans la conduite de pression de service (11), entre le départ de la conduite de bipasse (15, 15') et la source de pression (4), caractérisé en ce qu'un unique diaphragme de mesure (7), commun, ajustable par un aimant proportionnel unique (8), est prévu dans la conduite de pression de service (11), entre le clapet de non-retour (12) et le moteur hydraulique (2), pour le premier et pour le deuxième diaphragme de réglage (25, 30; 21, 29).
  2. Dispositif de commande hydraulique suivant la revendication 1, caractérisé en ce qu'une soupape d'arrêt (16) est prévue dans la conduite de bipasse (15), entre le diaphragme de réglage (21, 29) du régulateur de débit à deux voies et le réservoir (5), cette soupape pouvant être commutée dans une position de fermeture, pour maintenir la charge et lors d'un mouvement du moteur hydraulique (2) contre la charge (F), et dans la position de passage lors d'un mouvement du moteur hydraulique (2) sous l'effet de la charge.
  3. Dispositif de commande hydraulique suivant les revendications 1 et 2, caractérisé en ce que le diaphragme de réglage (25, 30) du régulateur de débit à trois voies est raccordé au réservoir (5) par l'intermédiaire d'une conduite (18), en contournant la soupape d'arrêt (16).
  4. Dispositif de commande hydraulique suivant les revendications 1 à 3, caractérisé en ce que le premier et le deuxième diaphragme de réglage (25, 30; 21, 29) sont regroupés dans un agencement unique de balances de pression (10), qui présente un piston de réglage (28), pouvant être sollicité sur ses deux côtés et dévié dans les deux sens de mouvement, contre la force d'un ressort, à partir d'une position de base stable, et comportant deux éléments de diaphragme de réglage (29, 30) latéraux, fonctionnant alternativement, et en ce que le piston de réglage (28) est soumis sur ses deux côtés à des pressions de commande ayant proportionnelles aux pressions en amont et en aval du diaphragme de mesure (7).
  5. Dispositif de commande hydraulique suivant la revendication 4, caractérisé en ce que le piston de réglage (28) est mobile dans une douille de commande (20), fixée dans un compartiment de carter (19) et présentant un conduit d'entrée de pompe (21), raccordé à un conduit annulaire (22), et un raccord de réservoir (25), distant des conduits précités dans le sens longitudinal, le conduit d'entrée et le raccord de réservoir constituant des parties des deux diaphragmes de réglage, en ce que le piston de réglage (28) présente une admission latérale (29) et un bord de commande (30), qui passe sur le raccord de réservoir (25), l'admission et le bord de commande formant les autres parties des deux diaphragmes de réglage, en ce que la conduite de bipasse (15), qui part du conduit annulaire (22), débouche dans une section d'alésage (24) reliée au raccord de réservoir (25), en ce qu'un côté du diaphragme de mesure (7) est raccordé au compartiment de carter (19), sur le côté (26) de ce dernier adjacent au raccord de réservoir (25), et en ce que l'autre côté du diaphragme de mesure (7) est relié au moteur hydraulique (2), et au côté (27) du compartiment de carter (19), par l'intermédiaire d'une conduite pilote (35), le côté (27) étant séparé du côté (26) par le piston de réglage (28).
  6. Dispositif de commande hydraulique suivant la revendication 5, caractérisé en ce qu'un montage de ressort (31, 32, 33, 34) à double effet, définissant la position de base du piston de réglage (28), est disposé sur le côté (27) du compartiment de carter (19), et est relié au piston de réglage (28).
  7. Dispositif de commande hydraulique suivant les revendications 2 à 6, caractérisé en ce que la soupape d'arrêt (16) est à commande magnétique, et est couplée judicieusement, sur le plan de la technique de commande, à l'aimant proportionnel (8) du diaphragme de mesure (7).
  8. Dispositif de commande hydraulique suivant la revendication 1, caractérisé en ce que la balance de pression (52) du régulateur de débit à trois voies (54), comportant le premier diaphragme de réglage, est disposée dans une deuxième conduite de bipasse (51), qui part de la conduite de pression de service (11) en direction du réservoir, entre le clapet de non-retour (12) et la source de pression (4), cette balance étant commandée, dans le sens de fermeture, par la pression régnant entre le diaphragme de mesure (7) et le moteur hydraulique (2), dans la conduite de travail (11), ainsi que par un ressort (63), et, dans le sens d'ouverture, par la pression entre la source de pression (4) et le diaphragme de mesure (7), en ce que la balance de pression (50) du régulateur de débit à deux voies (53), disposée dans la première conduite de bipasse (15') et comportant le deuxième diaphragme de réglage, est commandée, dans le sens d'ouverture, par la pression régnant dans la conduite de travail (11), entre la source de pression (4) et le diaphragme de mesure (7), et, dans le sens de fermeture, par la pression régnant dans la conduite (11), entre le diaphragme de mesure (7) et le moteur hydraulique (2), ainsi que par un ressort (59), et en ce que le côté de la balance de pression (50) du régulateur de débit à deux voies (53), sur lequel le diaphragme de réglage est sollicité dans le sens d'ouverture, est détendu par une vanne (57), pour remplacer sélectivement la fonction de réglage par une fonction de commande, pour soutenir la charge, et pour maintenir la position de fermeture du deuxième diaphragme de réglage, indépendamment du réglage du diaphragme de mesure (7), lors d'un mouvement du moteur hydraulique contre la charge (F).
  9. Dispositif de commande hydraulique suivant la revendication 8, caractérisé en ce que la vanne (57) est une vanne à trois voies, une soupape à siège de préférence, montée dans une conduite pilote (56) en direction de la balance de pression (50), qui fait partie du régulateur de débit à deux voies (53), sur le côté de cette balance (50), sollicitant dans le sens d ouverture le deuxième diaphragme de réglage, cette soupape fermant la conduite pilote (56) dans sa position de fermeture, et détendant le côté de cette balance (50) en direction du réservoir (5).
  10. Dispositif de commande hydraulique suivant les revendications 8 et 9, caractérisé en ce qu'une soupape de précharge (60, 60'), commutable en position de passage, est prévue dans la conduite de bipasse (15'), entre le diaphragme de réglage de la balance de pression (50), qui fait partie du régulateur de débit à deux voies (53), et le réservoir (5), cette soupape étant réglée sur une pression supérieure à la pression d'ouverture du diaphragme de réglage de cette balance (50), définie par le ressort (59) prévu sur la balance (50) précitée.
  11. Dispositif de commande hydraulique suivant la revendication 10, caractérisé en ce que la soupape de précharge (60, 60') est une soupape à ressort, une soupape à siège à deux voies à commande magnétique, contre la force d'un ressort, ou un tiroir à ressort, qui peut être sollicité par la pression de commande (conduite pilote 66) entre le diaphragme de mesure (7) et le moteur hydraulique (2), contre la force d un ressort (65), de telle sorte que la conduite de bipasse (15') est fermée avant la baisse de la pression de commande (conduite pilote 55), sollicitant le diaphragme de réglage de la balance de pression (50) dans le sens de fermeture, au-dessous de la pression d'ouverture, déterminée par le ressort (59) agissant dans le sens d'ouverture.
  12. Dispositif de commande hydraulique suivant la revendication 9, caractérisé en ce que la soupape à siège à trois voies (57) peut être commutée dans sa position de fermeture, avant le déplacement du diaphragme de mesure (7) en position de fermeture.
  13. Dispositif de commande hydraulique suivant l'une quelconque au moins des revendications 1 à 12, caractérisé en ce que le diaphragme de mesure (7) avec son aimant proportionnel (8), le régulateur de débit à trois voies et le régulateur à deux voies, un limiteur de pression (14), limitant la pression du système, et la soupape d'arrêt (16) ou la vanne (57), ainsi que la soupape de précharge (60, 60'), éventuellement, sont intégrés dans un élément modulaire de levage (M), dans lequel est également logé le clapet de non-retour (12), le cas échéant.
EP86113895A 1985-10-10 1986-10-07 Dispositif de commande hydraulique Expired - Lifetime EP0219052B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86113895T ATE73905T1 (de) 1985-10-10 1986-10-07 Hydraulische steuervorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853536219 DE3536219A1 (de) 1985-10-10 1985-10-10 Hydraulische steuervorrichtung
DE3536219 1985-10-10

Publications (3)

Publication Number Publication Date
EP0219052A2 EP0219052A2 (fr) 1987-04-22
EP0219052A3 EP0219052A3 (en) 1989-10-25
EP0219052B1 true EP0219052B1 (fr) 1992-03-18

Family

ID=6283298

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86113895A Expired - Lifetime EP0219052B1 (fr) 1985-10-10 1986-10-07 Dispositif de commande hydraulique

Country Status (7)

Country Link
US (1) US4711155A (fr)
EP (1) EP0219052B1 (fr)
JP (1) JPS6298005A (fr)
AT (1) ATE73905T1 (fr)
DE (2) DE3536219A1 (fr)
ES (1) ES2030384T3 (fr)
GR (1) GR3004569T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4423644A1 (de) * 1994-07-06 1996-01-11 Buchholz Hydraulik Hydraulische Steuervorrichtung

Families Citing this family (7)

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Publication number Priority date Publication date Assignee Title
DE3712716A1 (de) * 1986-08-01 1988-02-04 Man Nutzfahrzeuge Gmbh Verfahren zum verlustarmen veraendern des foerderstromes einer konstantspeisepumpe und vorrichtung zur durchfuehrung des verfahrens
US5046310A (en) * 1989-04-04 1991-09-10 Mannesmann Rexroth Gmbh Load-independent control device for hydraulic load devices
US6116263A (en) * 1998-07-23 2000-09-12 Hydraforce, Inc. Proportional priority flow regulator with reverse flow control
AT408208B (de) * 2000-02-22 2001-09-25 Hoerbiger Hydraulik Anordnung zur hydraulischen betätigung eines bewegten teils an fahrzeugen, insbesondere eines verdecks, eines heckdeckels, einer abdeckklappe oder dgl.
US9328832B2 (en) * 2012-12-25 2016-05-03 Zhejiang Dunan Hetian Metal Co., Ltd. Wheatstone bridge check valve arrangement
JP2018155341A (ja) * 2017-03-17 2018-10-04 Ｋｙｂ株式会社 ソレノイドバルブ及びこれを備える流体圧アクチュエータの制御装置
JP7304205B2 (ja) * 2019-05-31 2023-07-06 Ｋｙｂ株式会社 流体圧装置

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Publication number Priority date Publication date Assignee Title
SE309834B (fr) * 1965-12-28 1969-04-08 Asea Ab
JPS504958U (fr) * 1973-05-16 1975-01-20
DE2659870C3 (de) * 1976-01-21 1980-10-02 Danfoss A/S, Nordborg (Daenemark) Anordnung zur Beeinflussung der Arbeitsmenge eines Servomotors
US4249641A (en) * 1978-11-14 1981-02-10 Hitachi, Ltd. Speed control system for hydraulic elevator
DE3103745A1 (de) * 1981-02-04 1982-09-02 Sperry-Vickers Zweigniederlassung der Sperry GmbH, 6380 Bad Homburg Hydraulische hubeinrichtung
JPS5925761B2 (ja) * 1982-05-06 1984-06-21 工業技術院長 衣料害虫用防虫剤
DE3233046C2 (de) * 1982-09-06 1985-12-12 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München Hydraulische Steuervorrichtung
DE3434014A1 (de) * 1984-09-15 1986-03-20 Beringer-Hydraulik GmbH, Neuheim, Zug Hydraulische steuerung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4423644A1 (de) * 1994-07-06 1996-01-11 Buchholz Hydraulik Hydraulische Steuervorrichtung
DE4423644C2 (de) * 1994-07-06 1998-10-01 Buchholz Hydraulik Hydraulische Steuervorrichtung

Also Published As

Publication number Publication date
ES2030384T3 (es) 1992-11-01
DE3684402D1 (de) 1992-04-23
ATE73905T1 (de) 1992-04-15
EP0219052A2 (fr) 1987-04-22
DE3536219A1 (de) 1987-04-16
GR3004569T3 (fr) 1993-04-28
DE3536219C2 (fr) 1988-03-17
JPS6298005A (ja) 1987-05-07
US4711155A (en) 1987-12-08
EP0219052A3 (en) 1989-10-25

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