EP0284831B1 - Dispositif de commande hydraulique pour des groupes de consommateurs - Google Patents

Dispositif de commande hydraulique pour des groupes de consommateurs Download PDF

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Publication number
EP0284831B1
EP0284831B1 EP88103532A EP88103532A EP0284831B1 EP 0284831 B1 EP0284831 B1 EP 0284831B1 EP 88103532 A EP88103532 A EP 88103532A EP 88103532 A EP88103532 A EP 88103532A EP 0284831 B1 EP0284831 B1 EP 0284831B1
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EP
European Patent Office
Prior art keywords
line
control
valve
pressure
consumer
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
EP88103532A
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German (de)
English (en)
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EP0284831A2 (fr
EP0284831A3 (en
Inventor
Rudolf Brunner
Harald Dipl.-Ing. Klemens (Fh)
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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 AT88103532T priority Critical patent/ATE79448T1/de
Publication of EP0284831A2 publication Critical patent/EP0284831A2/fr
Publication of EP0284831A3 publication Critical patent/EP0284831A3/de
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Publication of EP0284831B1 publication Critical patent/EP0284831B1/fr
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    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/88—Safety gear
    • B66C23/90—Devices for indicating or limiting lifting moment
    • 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
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional 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
    • F15B2211/30—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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means 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
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/60—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
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using 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
    • F15B2211/60—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
    • F15B2211/7053—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

Definitions

  • the invention relates to a hydraulic control device of the type specified in the preamble of claim 1.
  • the monitoring valve limits the pressure in the relief control line, only a volume flow reduced according to the action of the overgrowth valve is available for the directional control slide to move the consumer back, although the consumer might need a larger volume flow to move back. A direction-dependent for each consumer and for both directions of movement Individual monitoring is not possible with this hydraulic control device.
  • the control line branch is connected directly to the tank via a single relief control line.
  • a pressure-controlled limit valve is included in the relief control line as a monitoring valve. The consumer is monitored regardless of the direction in which it is applied, i.e. regardless of the control position in which the control spool is moved.
  • a relief control line is not connected directly to the tank but to the directional control slide in such a way that it only connects the relief control line to the tank when it is in a control position is moved in which the hydraulic motor would be moved beyond a load limit.
  • This has the advantage that the hydraulic motor can be moved unaffected by the monitoring valve in the relief control line in the opposite direction in which it falls below the load limit again. Since the Relief control line maintains the pressure for the inflow controller of the control device, if the control device were expanded by adding several directional control slides for additional consumers, none of the further directional control slides would work if the monitoring valve responded and the relief control line was relieved.
  • the invention has for its object to provide a hydraulic control device of the type mentioned, in which consumers supplied by several directional spool valves can be monitored without mutual interference and depending on their direction of action.
  • the associated directional control slide valve is only switched off when it is brought into a control position which would cause the consumer to move beyond the pressure or stroke limit.
  • the directional control spool at which the monitoring valve has responded is adjusted to a control position in which its consumer is in one of the If the direction of the pressure limit or the stroke limit is undershot, the monitoring valve mentioned is automatically ignored because the directional control slide then does not connect the relief control line to the tank. If the consumer is to be monitored in both directions, and in different ways, e.g. to different pressure limits or to a pressure limit in one direction of movement and a stroke limit in the other direction of movement, this can be achieved in a simple manner by two relief control lines on the directional spool connected and in each of its two control positions one is unloaded to the tank, and that a monitoring valve is provided and individually adjusted in each unloading control line.
  • the hydraulic control device offers increased safety and is particularly useful for mobile cranes or similar machines or devices equipped with several hydraulic motors and cylinders as consumers.
  • the control device of the hydraulic control device can, in the case of a constant pump as a pressure source, be a 3-way controller or a control device for a pump (control pump) which can be regulated with regard to the volume flow.
  • the embodiment of claim is also advantageous 3, because the pressure relief valve as a monitoring valve directly monitors the pressure prevailing in the control line branch without requiring a direct connection to the consumer or actuation.
  • the monitoring valve is a 2/2-way valve which is actuated by the consumer or by an element which can be moved or influenced by the consumer when a stroke limit (linear stroke or rotary stroke) is reached.
  • the 2/2-way valve automatically resumes its blocking position when the stroke limit is undershot again.
  • Another useful embodiment is set out in claim 5.
  • the two monitoring valves work together so that a path and a pressure limit for the consumer are monitored simultaneously, depending on the direction.
  • Proportional directional spool valves of this type are well suited for the additional function of relieving the relief control line to the tank due to their design.
  • the measures of claim 7 are expedient because the relief control lines are each relieved prematurely to act on the respective consumer line, so that the directional control slide is switched off immediately without supplying the consumer with harmful pressure medium.
  • the relief control line is connected so that the spool of the Directional control valve establishes the connection to the return channel on the side opposite the consumer connection with respect to the pump connection, which would subsequently be connected to the pump connection in order to pressurize the consumer beyond the pressure or stroke limit.
  • the main control line is relieved in a simple manner when the passage is depressurized, i.e. when all directional control spools are in the neutral position.
  • a hydraulic control device 1 for a group of consumers V has a control device R (FIG. 1) and five proportional directional spool valves S1 - S5, each with its own two-way inflow controller Z1 - Z5.
  • the consumers V are a double-acting cylinder 2, a hydraulic motor 3, a double-acting cylinder 4, a double-acting cylinder 5 with stroke limitation and a double-acting cylinder 6 with stroke limitation.
  • a common pressure medium source, here a constant pump 7, is provided to act on the consumers V.
  • the volume flow that flows from the pump to the individual directional spool valves S1-S5 is regulated in a control device R.
  • a 3-way controller 8 of conventional design is provided for this purpose.
  • a pump line 9 leads on the one hand to the control device R and on the other hand to the inlet regulators Z1 - Z5 of the control slides S1 - S5, which are connected in parallel to one another.
  • a tank line 10 is connected via branch lines to the directional control valve S1-S5 on the one hand and the control device R on the other hand.
  • the maximum system pressure is limited by an adjustable pressure relief valve 11 incorporated in the control device R.
  • a main control line 12 also leads to the control device R, which is supplied with a consumer pressure-dependent control pressure from the directional control spools S1-S5 in a manner explained later and which serves to control the 3-way controller 8 and to pilot the pressure limiting valve 11.
  • An auxiliary control line 13, which branches off from the pump line 9 and is guided over all directional control slides S1-S5, contains a pressure reducing valve 54, with which a certain pressure in the auxiliary control line 13 is maintained in the unpressurized passage.
  • the directional control valve S1 - S5 are designed identically in this embodiment, so that only the Directional spool valve S1 is explained in detail (see also Fig. 3).
  • the directional control slide valve S1 contains a piston slide valve 14 which can be adjusted between a zero position with zero pressure circulation via the 3-way controller 8 in two control positions a and b.
  • consumer lines 15, 16 lead to the two sides of the double-acting cylinder 2.
  • branch lines 17, 18 are arranged in the housing, which are outside of taps 19, 20 of the consumer lines 15, 16.
  • Flow paths 21, 22 and 23, 24 are formed in the slide piston.
  • the taps 19, 20 and the connecting lines 26 and 27 are drawn out of the housing of the directional control slide S1 in FIG. 1. In practice, however, these are contained inside the directional control slide (see FIG. 3 and as will be explained later).
  • the connecting lines 25 and 28, which in the two control positions can be connected to the branch lines 17, 18 via the channels 21 and 24 and are shown as connected to the tank line 19, run inside the directional control valve S1.
  • the spool 14 is adjusted either by pressure pre-control (control lines 29, 30) and a control 31 indicated only schematically from the control line 13 or by a hand lever 32.
  • a control line branch 34 is connected to the connecting lines 26, 27 of the taps 19, 20 and leads via a throttle to the control side of the two-way inlet controller Z1, the inlet controller Z1 on the other hand piloting from the part of the pump line 9 lying between the inlet controller and the directional control valve S1 becomes.
  • the control line branch 34 is connected to the main control line 12 via a spur line 33 and a check valve 35 blocking in the direction of the directional control valve S1.
  • a relief control line 37 branches off from the control line branch 34 and is divided into two branches 36, 38.
  • Monitoring branches 39, 40 are contained in both branches 36, 38, in the present exemplary embodiment in each case individually adjustable pressure relief valves which are pilot-controlled from the relief control line 37.
  • the two branches 36, 38 are connected to the spur lines 17, 18 of the housing of the directional control valve S1. They are locked in the neutral position shown.
  • an adjustable pressure limiting valve 41 which is pilot-controlled from the relief control line 37, is also contained as a monitoring valve 41. Downstream of the monitoring valve 41, the relief control line 37 opens directly into the tank 42.
  • the relief control line 37 is connected to the branch line 17 only via the branch 38.
  • a monitoring valve 43 is provided, again an adjustable pressure relief valve 43 that is pilot-controlled from the relief control line 37.
  • the relief control line 37 is connected to the branch 36 and the branch line 18 via a monitoring valve 44.
  • the monitoring valve 44 is a 2/2-way valve which can be actuated by a stop 45 of the double-acting cylinder at a stroke limit of the latter in such a way that it gives up its shut-off position, which is normally held by spring force, and into a through position switches.
  • the relief line 37 is in turn connected to the branch line 18 via the branch 36.
  • two monitoring valves 46, 47 are connected in series, namely a 2/2-way valve that can be actuated by the stop 45 as with the directional control slide S4, and an adjustable pressure relief valve piloted from the relief control line 37.
  • the hydraulic control device works as follows: In the illustrated zero position of all directional control slides S1 - S5, the pressure medium flows in a pressureless circuit via the 3-way controller 8, which switches to the through position, to the tank line 10 From the pump line 9 to the consumer line 15 via the open inlet regulator Z1.
  • the consumer line 16 is connected to the tank line 10 via the slide piston 14.
  • the piston rod extends to the right in FIG. 1.
  • the control line branch 34 is acted upon by control pressure via the tap 19 and the channel 22 and the connecting line 26. This control pressure, together with the pilot pressure from the pump line 9, controls the inflow regulator Z1 with regard to the volume flow required for the cylinder 2.
  • the pressure in the control line branch 34 also reaches the main control line 12 via the check valve 35, where it is used to control the 3-way controller 8, which on the other hand is directly pilot-controlled from the pump line.
  • the 3-way controller 8 provides at least the volume flow ready that the consumer 2 needs.
  • the branch 38 of the relief control line 37, 38 is connected via the branch line 17 and the channel 21 to the connecting line 25 to the tank line 10. However, the pressure relief valve 40 has not responded, so that the pressure in the relief control line 37 is maintained.
  • the branch 36 is still blocked off from the tank line 10.
  • each other of the directional control slide S2 - S5 can be actuated in the same way. If a larger volume flow is required for one of the consumers V of the further directional control slide S2 - S5, the pressure in the main control line 12 rises accordingly, so that the 3-way controller 8 provides a larger volume flow.
  • the inflow controller Z1 of the first directional control slide S1 regulates the volume flow for the consumer 2 assigned to it, regardless of the volume flow in the pump line.
  • the monitoring valve 40 responds and leaves the relief control line 37 via the branch 38, the branch line 17. the channel 21 and the tank line 10 from so much pressure medium that the inlet controller Z1 throttles the volume flow to such an extent that the cylinder 2 can no longer extend. This pressure limit is maintained. If the directional control slide S1 is then adjusted to its control position b, the piston rod of the cylinder 2 can be retracted again, since this direction of movement of the cylinder 2 is monitored by the other monitoring valve 39, which has not responded. To this The pressure limit can be fallen below again and the piston rod of the cylinder 2 can be retracted accordingly.
  • the monitoring valve 39 responds and limits the pressure in the relief control line 37 so that the inflow regulator Z1 in turn only provides a throttled volume flow which prevents the piston rod from being drawn in too far. Then the branch 36 is relieved via the stub 18 and the channel 24 to the tank line 10. The work of the other consumers V is not impaired by the above-mentioned functions, because the directional control slide S1 acts independently of the other directional control slides S2 -S5 through its inflow controller Z1. If the pressure in the control line branch 34 is limited or reduced in the aforementioned manner, this change in pressure is not communicated to the main control line 12 since the check valve 35 then blocks. The check valve 35 also prevents the control line circuit associated with the directional control slide, for example S1, from being influenced at higher pressure in the main control line.
  • the hydraulic motor 3 is monitored by the monitoring valve 41 for the same pressure limit in both directions of movement, so that the inlet controller Z2 throttles the volume flow when the same pressure is reached and stops the hydraulic motor 3 as soon as the monitoring valve 41 has responded.
  • the cylinder 4 is only monitored in the extension direction of the piston rod by the monitoring valve 43. If a dangerous pressure limit is reached in the control position a of the directional spool valve S3, this is caused by the Monitoring valve 43 discharged through pressure medium via the branch 38, the branch line 17 and the spool 14 to the tank. If the directional control slide S3 is moved into its second control position b, the piston rod of the cylinder 4 is retracted without pressure monitoring.
  • the piston rod of the cylinder 5 is extended in the second control position b until the stop 45 actuates the monitoring valve 44, so that the relief control line 37 is suddenly relieved to the tank line 10 via the branch 36, the branch line 18 and the spool 14.
  • the inlet regulator Z4 switches off completely.
  • the cylinder 5 no longer receives pressure medium, unless the directional control slide S4 is moved into its first control position a, in which the piston rod of the cylinder 5 can be retracted.
  • the piston rod of the cylinder is extended in the second control position b until the stop 45 actuates the monitoring valve 46.
  • the pressure in the relief control line 37 is not reduced entirely, but only to the extent specified by the downstream pressure-limiting monitoring valve 47, namely via branch 36, branch line 18 and spool 14 to tank line 10 an additional safety function is given because the piston rod of the cylinder 6 can be moved beyond the stroke limit, provided that the pressure in the relief control line 37 does not rise above a dangerous pressure limit (monitored by the pressure limit monitoring valve 47).
  • Control device R ⁇ instead of the control device R of FIG. 1 is provided. It is a so-called control pump 7 ⁇ , which for larger volume flows, for example 120l / min. and more is used because then the pump delivery for the unpressurized circulation can be regulated to a low pressure or low volume flow. From the pump 7 ⁇ , the pump line 9 leads to the inlet regulators Z1 - Z5. The tank line 10 leads back to the tank.
  • the main control line 12 supplied from the taps of the directional control valve S1 - S5 leads in the control device R ⁇ via a pressure-independent quantity regulator 51, which serves to relieve the main control line 12 when the directional control valve is not actuated (pressureless circulation), to a servo cylinder 52 which has a control valve 53 actuated in a pump branch line 9..
  • the control part of the pump 7 ⁇ is actuated by an actuating cylinder 48 supplied from the pump line branch 9 ⁇ in one direction and by a spring-loaded cylinder 49 in the other direction.
  • the spring-loaded cylinder 49 is connected to the control slide 53.
  • the volume flow in the pump line 9 is controlled with these components as a function of the required volume of the consumers.
  • a pressure relief valve 50 for limiting the system pressure is also provided between the pump line 9 and the tank line 10. Furthermore, a pressure reducing valve 54 is connected to the pump line 9, which regulates the control pressure in the control line 13 to a fixed pressure value (eg 35 bar).
  • the control line 13 is used for the regulation of the control elements 31 when the slide piston 14 of the directional control valves S1-S5 is actuated by pressure.
  • the control pump in the control device R ⁇ is used for example for mobile cranes of larger types, in which volume flows over 120l / min. are needed because the control pump for these cases operates with less loss than the constant pump 7 of FIG. 1.
  • the check valves 35 which are arranged between the main control line 12 and each branch line 33 to form a control line branch 34 and which block in the direction of flow to the directional control spools S1-S5, as shuttle valves (35 ⁇ ) , as indicated in Fig. 4. Furthermore, the main control line 12 is then connected behind the last directional control valve S5 (in an end plate) to the tank line 10 and from the branch line 33 a branch 33ön to the directional control valve, e.g. S5, connected, the piston valve 14 ⁇ is equipped with a channel 33 ⁇ in the neutral position open to a tank connection 33 ′′′.
  • the shuttle valve 35 ⁇ the closing member of which shuts off one of two end connections 12b, 33a, is inserted into the main control line 12 with its central connection 12a and one end connection 12b.
  • the other end connection 33a is connected to the stub 33 to the control line branch 34.
  • the proportional directional control valve S1 is recognizable in its structure, which corresponds to the proportional directional control valve S2 - S5. It has a housing 55 with a bore 56 for the slide piston 14. End caps 57 and 58 contain springs 59 which define the zero position of the slide piston 14 and at the same time ensure that it is secured against rotation.
  • the actuating lever 32 is mounted on the end cap 58 and is connected to the slide piston 14 via a coupling member 60.
  • chambers are formed in which the movement of the slide piston 14 can be controlled in a pressure-dependent manner via the control lines 29, 30 is.
  • the control element 31 is expediently attached to the housing 55.
  • the spool 14 has on both sides of a central sealing zone annular grooves 61 and 62 which are separated by control edges 63, 64 and 65, 66 from the adjacent sealing zones.
  • the pump connection P which is connected to the pump line 9, is provided in the center of the housing 55.
  • Consumer connections A and B are provided on both sides of the pump connection P as circumferential grooves in the bore 56, which are connected to the consumer lines 15 and 16.
  • return connections R designed as tap holes are provided, which are connected to the tank line 10 and form the connection lines 25, 28 for the relief control line branches 36, 38.
  • the spur lines 17, 18 are drilled from a housing outside to the bore 56, the mouths of which are indicated by dashed lines.
  • the mouths of the branch lines 17, 18 are a short distance behind the control edges 63 and 66 and are shut off from the sealing zones of the spool 14 there.
  • the two connecting lines 26, 27 of the taps can also be seen, which are connected together to the control line branch 34 (indicated by a bore).
  • the branch 38 of the relief line 37 is connected to the spur line 17 and the branch 36 to the spur line 18, ie the branches are connected crosswise, so at Connection of the pump connection P to the consumer connection A of the branch 38 is relieved via the branch line 17, while when the pump connection P is connected to the consumer connection B the branch 36 is relieved of the branch line 18 to the tank line.
  • the spool 14 can not only be adjusted to the control positions a and b to act on the cylinder 2 accordingly, but intermediate positions of the spool 14 are possible in which the volume flow to the consumer is proportional to the displacement of the spool 14. A very sensitive control of the movement of the cylinder 2 is possible in this way, the inflow controller Z1 being controlled accordingly.
  • the channel 33 ⁇ must also be provided, which connects the branch 33 ⁇ to R only in the neutral position.
  • the particular advantage of the hydraulic control device according to the embodiments of FIGS. 1 to 4 is that different maximum consumer pressures are limited at the same time, and consumers with higher pressure levels can be driven, because the response of a monitoring valve has no influence on simultaneously driven consumers with higher or has lower pressure in terms of volume flow or pressure.
  • a relief control line to the main control line 12 and to route the directional control spool S1-S5 via a branch line 17 or 18 and also in the relief control line to use a 2/2-way solenoid valve, which is controlled by a pressure sensor that taps the pressure in any consumer line of a consumer. If the consumers of the directional control valve connected to the relief line would then be acted upon and the load torque would be exceeded, the 3-way controller between the pump and the tank line is switched off via the relief control line, so that none of the consumers can work as long as it is not in a direction reducing the load moment is moved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Lifting Devices For Agricultural Implements (AREA)

Claims (9)

  1. Dispositif de commande hydraulique pour un groupe de consommateurs (V), avec deux distributeurs à tiroir (S1 - S5) au moins pour un consommateur (V) au moins, alimentés par une source de pression commune (7, 7') et montés en parallèle par l'intermédiaire d'une conduite de pompe et de réservoir (9, 10), avec un dispositif de réglage aval (R, R') pour le débit volumique dans la conduite de pompe (9), avec une dérivation de conduite pilote (34), associée à chaque distributeur (S1 - S5), et prévue entre des soutirages (26, 27) de la conduite de consommateur (15, 16) alimentée en pression de pompe, dans le distributeur à tiroir, et un côté commande d'un régulateur à 2 voies (Z1 - Z5), monté en amont du distributeur et piloté par la conduite de pompe (9), avec une conduite pilote principale (12) pour le dispositif de réglage (R, R'), raccordée aux dérivations (34) par l'intermédiaire de clapets de non-retour (35), et avec une conduite pilote de détente (36, 37, 38) au moins en direction du réservoir, associée à un régulateur à 2 voies (Z1 - Z5), qui couvre les besoins en débit volumique du consommateur (V), dans le sens d'alimentation respectif, la conduite précitée étant raccordée à la dérivation (34) et comportant une soupape de contrôle (39 - 44, 46, 47) au moins, pour limiter la course ou la pression des consommateurs, cette soupape permettant de détendre ou de limiter la pression dans la dérivation (34), pour le réglage du régulateur à 2 voies (Z1 - Z5), dès que le consommateur (V) atteint la limite de course ou de pression, caractérisé en ce que la dérivation (34) est raccordée en permanence aux distributeurs à tiroir (S1 - S5), par l'intermédiaire de la conduite pilote de détente (37, 36, 38), et peut être raccordée directement au réservoir, à l'intérieur du distributeur, en vue de déconnecter ce dernier dans la position de commande (a ou b), dans laquelle le consommateur (V) dépasserait par le haut la limite de course ou de pression, avec une alimentation ultérieure.
  2. Dispositif de commande suivant la revendication 1, caractérisé en ce que la dérivation (34) est raccordée aux distributeurs à tiroir (S1 - S5) par l'intermédiaire de deux conduites pilotes de détente parallèles (36, 37, 38), en ce que chaque conduite de détente (36, 37 ou 36, 38) peut être raccordée au réservoir dans une position de commande (a ou b), dans le distributeur à tiroir (S1 - S5), et en ce qu'une soupape de contrôle (39, 40) au moins est montée dans chaque conduite pilote de détente (36, 37 ou 36, 38).
  3. Dispositif de commande hydraulique suivant les revendications 1 et 2, caractérisé en ce que la soupape de contrôle (39, 40, 41, 43) est un limiteur, réglable de préférence, piloté par la pression dans la dérivation de conduite pilote (34).
  4. Dispositif de commande hydraulique suivant les revendications 1 et 2, caractérisé en ce que la soupape de contrôle (44, 46) est un distributeur à deux voies, qui peut être actionné à partir d'une position de fermeture, contre la force de ressort, indépendamment de la course des consommateurs.
  5. Dispositif de commande hydraulique suivant les revendications 1 à 4, caractérisé en ce qu'un distributeur à deux voies (46) et un limiteur (47) sont montés en série dans la conduite pilote de détente (37, 36, 38).
  6. Dispositif de commande hydraulique suivant l'une au moins des revendications 1 à 5, caractérisé en ce que chaque distributeur à tiroir (S1 - S5) est un distributeur proportionnel, avec un piston (14) mobile dans un alésage (56) de sa cage (55), d'une position de repos dans deux positions de commande (a, b), en ce qu'un raccord de consommateur (A, B) et un raccord de retour (R25, 28) sont disposés dans l'alésage (56), en déport axial à partir d'une arrivée centrale de pompe (P), en ce que le piston de tiroir (14) présente une section d'étanchéité centrale et une rainure circulaire (61, 62), située de part et d'autre de cette section et prolongée par des zones d'étanchéité externes, par l'intermédiaire de bords de commande (63, 66), et en ce que deux branchements de conduites pilotes de détente (17, 18) sont prévus dans la cage (55), de la face externe dans l'alésage (56), les ouvertures de ces branchements se situant dans la paroi de l'alésage, en déport par rapport aux raccords de retour (R25, 28) dans le sens périphérique, dans des zones axiales de l'alésage recouvertes par les zones d'étanchéité externes, en position de repos du piston (14).
  7. Dispositif de commande hydraulique suivant la revendication 6, caractérisé en ce que les ouvertures, en position de repos du piston (14), sont limitrophes aux bords de commande (63, 66), de telle sorte que chaque bord de commande relie l'une des ouvertures des branchements de conduites de détente (17, 18), en avance de la jonction du raccord de pompe (P) avec l'un des raccords de consommateur (A, B), avec le raccord de retour (R25, 28) associé à l'autre raccord de consommateur (B, A).
  8. Dispositif de commande hydraulique suivant les revendications 1 à 7, caractérisé en ce que la dérivation de conduite pilote (34) est raccordée en supplément, par l'intermédiaire d'une dérivation (33'), à un canal (33") du distributeur (S1 - S5), relié à la conduite de réservoir (10) et exclusivement ouvert en position neutre du distributeur (S1 - S5), et en ce que le clapet de non-retour entre la conduite pilote principale (12) et la dérivation (34) est réalisé sous forme de sélecteur de circuit (35'), qui est monté dans la conduite pilote principale (12) par un raccord central (12a) et l'un (12b) de deux raccords extrêmes (12b, 33a), obturables alternativement, et qui est raccordé à la dérivation (34) par l'autre raccord extrême (33a), par l'intermédiaire d'un branchement (33).
  9. Dispositif de commande hydraulique suivant les revendications 1 à 8, caractérisé en ce que la conduite pilote principale (12) est raccordée à la conduite de réservoir (10), en aval du dernier distributeur à tiroir (S5).
EP88103532A 1987-03-31 1988-03-07 Dispositif de commande hydraulique pour des groupes de consommateurs Expired - Lifetime EP0284831B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88103532T ATE79448T1 (de) 1987-03-31 1988-03-07 Hydraulische steuervorrichtung fuer verbrauchergruppen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3710699A DE3710699C1 (de) 1987-03-31 1987-03-31 Hydraulische Steuervorrichtung fuer eine Verbrauchergruppe
DE3710699 1987-03-31

Publications (3)

Publication Number Publication Date
EP0284831A2 EP0284831A2 (fr) 1988-10-05
EP0284831A3 EP0284831A3 (en) 1990-08-16
EP0284831B1 true EP0284831B1 (fr) 1992-08-12

Family

ID=6324472

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88103532A Expired - Lifetime EP0284831B1 (fr) 1987-03-31 1988-03-07 Dispositif de commande hydraulique pour des groupes de consommateurs

Country Status (4)

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EP (1) EP0284831B1 (fr)
AT (1) ATE79448T1 (fr)
DE (2) DE3710699C1 (fr)
ES (1) ES2033959T3 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3841507C1 (fr) * 1988-01-22 1989-06-29 Danfoss A/S, Nordborg, Dk
DE3901207C2 (de) * 1989-01-17 1994-06-23 Rexroth Mannesmann Gmbh Ventilanordnung für mehrere hydraulische Antriebe, insbesondere für die Antriebe eines Krans
DE4127327A1 (de) * 1991-02-20 1993-02-25 Teves Gmbh Alfred Hydraulikanlage
EP0684388B1 (fr) * 1991-12-25 1999-02-24 Kayaba Industry Co., Ltd. Système de commande hydraulique de détection de la charge
DE9210647U1 (de) * 1992-08-10 1993-12-16 Heilmeier & Weinlein Hydraulische Steuervorrichtung
DE4243973C1 (de) * 1992-12-23 1994-07-07 Heilmeier & Weinlein Hydraulische Steuervorrichtung
DE9310857U1 (de) * 1993-07-20 1993-09-30 Heilmeier & Weinlein Hydraulisches Steuerventil
DE19714141A1 (de) * 1997-04-05 1998-10-08 Mannesmann Rexroth Ag Hydraulische Steueranordnung
US5813226A (en) * 1997-09-15 1998-09-29 Caterpillar Inc. Control scheme for pressure relief
DE19828963A1 (de) * 1998-06-29 1999-12-30 Mannesmann Rexroth Ag Hydraulische Schaltung
DE102004014113A1 (de) * 2004-03-23 2005-10-20 Sauer Danfoss Aps Nordborg Hydraulische Ventilanordnung
DE102004028437B3 (de) * 2004-06-14 2006-03-02 Sauer-Danfoss Aps Ventilanordnung
CN105840574B (zh) 2015-01-16 2018-04-06 徐工集团工程机械股份有限公司 负载敏感多路阀及工程机械液压系统
EP3093505B1 (fr) * 2015-05-11 2017-08-23 HAWE Hydraulik SE Dispositif de commande hydraulique et sélecteur

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DE2656059A1 (de) * 1976-01-23 1977-07-28 Caterpillar Tractor Co Stroemungsmittelsystem
DE3022592A1 (de) * 1980-06-16 1981-12-24 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München Hydraulische steuervorrichtung

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US3911942A (en) * 1974-03-28 1975-10-14 Gen Signal Corp Compensated multifunction hydraulic system
DE2601999C3 (de) * 1976-01-21 1980-02-21 Danfoss A/S, Nordborg (Daenemark) Anordnung zur Beeinflussung der Arbeitsmenge eines Servomotors

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DE2656059A1 (de) * 1976-01-23 1977-07-28 Caterpillar Tractor Co Stroemungsmittelsystem
DE3022592A1 (de) * 1980-06-16 1981-12-24 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München Hydraulische steuervorrichtung

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Title
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Also Published As

Publication number Publication date
DE3873576D1 (de) 1992-09-17
ES2033959T3 (es) 1993-04-01
DE3710699C1 (de) 1988-08-18
ATE79448T1 (de) 1992-08-15
EP0284831A2 (fr) 1988-10-05
EP0284831A3 (en) 1990-08-16

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