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EP3002462A1 - Systeme de commande hydraulique - Google Patents

Systeme de commande hydraulique Download PDF

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Publication number
EP3002462A1
EP3002462A1 EP15182018.0A EP15182018A EP3002462A1 EP 3002462 A1 EP3002462 A1 EP 3002462A1 EP 15182018 A EP15182018 A EP 15182018A EP 3002462 A1 EP3002462 A1 EP 3002462A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
pressure
line
valve
load
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP15182018.0A
Other languages
German (de)
English (en)
Other versions
EP3002462B1 (fr
Inventor
Manfred Kirchhoff
Thomas Fedde
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.)
Claas Tractors SAS
Original Assignee
Claas Tractors SAS
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Filing date
Publication date
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Publication of EP3002462A1 publication Critical patent/EP3002462A1/fr
Application granted granted Critical
Publication of EP3002462B1 publication Critical patent/EP3002462B1/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
    • 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
    • F15B11/168—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load with an isolator valve (duplicating valve), i.e. at least one load sense [LS] pressure is derived from a work port load sense pressure but is not a work port pressure itself
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • 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
    • F15B2211/322—Directional control characterised by the type of actuation mechanically actuated by biasing means, e.g. spring-actuated
    • 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
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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
    • F15B2211/6058—Load sensing circuits with isolator 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
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/651—Methods of control of the load sensing pressure characterised by the way the load pressure is communicated to the load sensing circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/653—Methods of control of the load sensing pressure the load sensing pressure being higher than the load pressure
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary 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
    • F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors
    • 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
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups

Definitions

  • the invention relates to a hydraulic control system for a working hydraulics of a land or building economical vehicle to which vehicle in its rear and / or front area a hydraulic adjusting and / or drive system having attachments can be coupled, wherein a hydraulic system of the respective attachment by means of a hydraulic Coupling system with a hydraulic circuit of the working hydraulics can be connected and both within the hydraulic circuit and within the hydraulic system each hydraulic control units are assigned functionally, wherein in the hydraulic circuit, an adjustable hydraulic pump is provided whose delivery volume in response to a load pressure of the hydraulic load of the hydraulic circuit and the Anbau réelle associated hydraulic system is regulated, wherein in the context of the control of the hydraulic pump, at least one hydraulic load signal line is provided, which composites with the control units n, and wherein between a first line section of the load signal line, which is connected to the arranged within the hydraulic circuit controllers, and a second line section of the load signal line, which is connected to the control units of the hydraulic system, a control valve is arranged, which is one of the control units the hydraulic
  • the invention also relates to a control valve for a designed as a closed-center system working hydraulics of a land or building economics usable machine, which amplifies a one or more control units in a load signal line generated load pressure signal by means of a pressure increase from a pressure line.
  • the hydraulic pump designed as a variable displacement pump is controlled by a so-called load-sensing system, which consists of a load signal line and a pressure compensator associated with the adjustment of the hydraulic pump.
  • load-sensing system which consists of a load signal line and a pressure compensator associated with the adjustment of the hydraulic pump.
  • load signal line of each of the control valves which are assigned to the individual consumers, the highest load pressure reported to the pressure compensator and the hydraulic pump only builds up the load pressure plus a low pressure surplus.
  • variable displacement pump This will allow the variable displacement pump to be returned to a stand-by condition when the control valves are in their neutral position and do not demand a flow.
  • the pump pressure settles so that the pressure difference ⁇ p LS between the load pressure p LS of the pressure compensator and the delivery pressure of the pump p p always remains the same. If one or more valves are actuated, the pressure is passed on via the load signal line to the pressure compensator, which determines the energy requirement of the system by comparing the load pressure p LS and the pump pressure p p . Pump pressure and pump flow are always automatically adapted to the respective requirements.
  • the respective highest load pressure p LS is reported by the corresponding control valve to the hydraulic pump, whereupon the hydraulic pump builds up only the load pressure plus a low pressure surplus (rule - ⁇ p).
  • the pump flow is divided by the use of so-called section pressure compensators regardless of the various load pressures on the consumer, as it corresponds to the ratio of the opening cross-sections of the control valves.
  • remote terminals work equipment which is at least two connections, namely for a Pressure line and a non-pressurized return line.
  • remote connections are provided, for example, in their front and rear areas, in which there is also a three-point power lift for receiving the respective implement.
  • the coupled implement may include hydraulic consumers in the form of hydraulic cylinders or hydraulic motors, each operating control valves associated therewith.
  • the connection of the tools is also referred to as a power beyond connection.
  • the power beyond connection system will be extended with a connection for a load signal line leading to the implements control units.
  • This ensures that the variable displacement pump of the agricultural vehicle supplies the control valves of the attachment only with pressure medium when the corresponding hydraulic power is needed. Therefore, this system regulates the flow rate and pressure to meet the needs.
  • the load signal line the load pressure increases when the operator of the implement retrieves one of its hydraulic functions.
  • considerable pressure losses can occur in the connecting elements, so that the control variable for the hydraulic pump ⁇ p LS collapses. This has the consequence that the variable displacement pump can not provide sufficient volume flow.
  • a hydraulic control system for a land or building economy vehicle of the type specified in the preamble of claim 1 is known from the DE 11 2004 002 768 B4 known.
  • This document discloses a hydraulic control system in which an implement is operated via power beyond ports.
  • the respective load pressure of the load can be reported as a load-sensing signal via a load signal line to the control system.
  • the control system has means to influence at least one of the load-sensing signals.
  • a compensation valve and a Shut-off valve existing compensator In order to change the load-sensing signal so that the consumer or consumers receive a larger flow of oil, resulting in a quick effect of the consumer or the consumer should be one of a compensation valve and a Shut-off valve existing compensator provided.
  • the compensation valve is intended to raise a load sensing pressure applied to it by a fixed amount ⁇ p, the sum of the load sensing pressure and the fixed amount ⁇ p representing the corrected load sensing pressure.
  • the shut-off valve should shut off the compensator when the load-sensing pressure applied to the compensation valve goes against the return line pressure.
  • the control valve has a load signal amplifying valve unit, which is designed as a directional control valve, wherein this Nutzan say for the pressure line, the first line section and a return line, and is controlled by the load pressure of the first line section, and wherein the control valve is a front side via a biasing spring Having on a valve spool of the directional control valve biasing stage, which is acted upon by a load pressure of the second line section.
  • the biasing stage which is acted upon by the load pressure from the second line section, thus acts permanently on the biasing spring on the valve spool of the directional control valve.
  • the biasing spring is tensioned by means of the applied with this load pressure biasing stage and moved over this, the valve spool of the directional control valve in a position in which from the pressure line Pressure medium is passed with the pump pressure p p in the first line section of the signal line.
  • the load pressure in this first line section is increased by the amount of the biasing force.
  • the pressure in the first line section is thus regulated via the regulating valve to the value set by the pretensioning spring, the load pressure correspondingly increased via the regulating valve being forwarded to a pressure compensator.
  • This pressure compensator ensures that the pressure difference ⁇ p LS between the load pressure p LS and the delivery pressure of the pump p p always remains the same. In this way, the pressure balance determines the energy requirement of the system by comparing the load pressure p LS and the pump pressure p p .
  • variable is adjusted to a higher delivery volume due to the increase of the load pressure, so that in a corresponding manner pressure means for a delay-free operation of the corresponding modules of the attachment via hydraulic cylinders or hydraulic motors can be provided.
  • a compensator which consists of a compensation valve and a shut-off valve.
  • the compensation valve is arranged between a first line section and a second line section of the signal line.
  • the compensation valve is acted upon at one end face with the pump pressure and at the other end side with the load pressure of the signal line.
  • the application of the pump pressure takes place depending on the position of the shut-off valve. From its initial position, in which the compensation valve ensures no pressure increase in the signal line, it is first moved to a middle position in which pressure medium is throttled fed into the entire signal line. Finally, in a third position of the compensation valve, the pressure medium from the pressure line is only fed into the branch of the signal line which leads to the adjustment of the variable displacement pump.
  • valve slide is acted upon at its side remote from the biasing stage end face with the load pressure of the first line section.
  • the in the first line section at a pressure increase increasing load pressure consequently acts against the force transmitted by the pretensioning stage. Therefore, the slider is moved back from its intended for a pressure increase position as soon as the force resulting from the pressure increase exceeds the force of the biasing spring.
  • valve slide has a hydraulic actuation parallel to the pretensioning stage via the load pressure of the second line section.
  • valve spool of the directional control valve is piloted parallel to the biasing stage directly with the pressure of the second line section.
  • the biasing stage may comprise a longitudinally displaceable sleeve, which is acted upon at a first end side with a load pressure of the second line section and is supported via the biasing spring at an end face of the valve spool of the load signal amplifying unit.
  • At its second line section facing the end of this control sleeve may be provided with a diaphragm, said diaphragm provides on the one hand for the displacement of the control sleeve and on the other hand via a corresponding throttle bore pressure means for direct hydraulic actuation of the valve spool available.
  • valve spool in the direction of the biasing voltage exciting means may be provided. It may be an additional compression spring, via which the valve spool is biased relative to the valve housing.
  • a further compression spring is provided within the biasing stage, which is supported on the diaphragm and acts via a piston and a plunger frontally on the valve spool. About this two acting in opposite directions on the valve spool springs this spring centering is effected.
  • a displaceable piston may be provided which acts directly or indirectly on the valve spool.
  • this piston can go out a plunger, surrounded by the biasing spring is. This plunger is supported at its other end on the facing him face of the valve spool.
  • the load signal amplification valve unit has a 3/2-way valve.
  • this 3/2-way valve In a first position at low load pressure of the second line section and a higher load pressure of the first line section, this 3/2-way valve will shut off the useful connection of the pressure line and connect the first line section to the return line.
  • the pressure line In a second position of the 3/2-way valve, as it assumes after an increase in the load pressure in the second line section, the pressure line is connected to the first line section to increase their load pressure.
  • the valve spool can also be in a position in which it blocks the first line section both with respect to the pressure line and to the return line.
  • the first line section can be arranged coaxially to a receiving bore of the valve slide, wherein a connecting piece receives the pressure spring acting on the valve slide.
  • the valve slide in this case preferably has a longitudinal bore, are provided by the two transverse bores with radially outer, circumferential on the circumference of the valve slide grooves.
  • the biasing spring should abut with its ends on the first and second spring plates, wherein the first spring plate is slidably disposed together with the control sleeve, wherein the second spring plate engages the front end on the valve spool and is supported radially on the inside of the plunger and radially outward on the biasing spring and wherein second spring plate, facing away from the plunger, engages the valve spool.
  • the pressure increase in the first line section according to the invention adapt to the respective requirements that a biasing spring is used which has a certain spring constant. Accordingly, the adjustment can be made by replacing one bias spring with another having a lower or higher spring constant.
  • a housing of the load signal amplifying valve unit and a housing of the biasing stage to be bolted together, with their mounting holes for the valve spool on the one hand and for the biasing spring, the plunger and the control sleeve on the other hand coaxially.
  • a hydraulic circuit which may be, for example, a working hydraulics of an agricultural tractor or system vehicle.
  • This hydraulic circuit 1 is designed as a closed-center system, wherein the pressure medium from a tank 2 via a variable displacement pump 3, which is preferably designed as axial piston unit according to the bent axis principle, two as a double-acting hydraulic cylinders 4 and 5 trained consumers 6 and 7 supplies.
  • the hydraulic cylinders 4 and 5 are associated with control devices 8 and 9, which are designed as electromagnetically operated, provided with spring centering 4/4-way valves.
  • the hydraulic cylinders 4 and 5 may be provided, for example, each for lifting devices of a front and a rear linkage.
  • the pressure medium is conveyed by the variable displacement pump 3 via a pressure line 10 to the control units 8 and 9, where it can enter into corresponding positions of these control units 8 and 9 in a return line 11 and thus back into the tank 2. In this position, the respective control units 8 and 9 whose working lines 12, 13, 14 and 15 are shut off.
  • the delivery volume of the variable displacement pump 3 can be adjusted, for which purpose a single-acting adjusting cylinder 16 is provided.
  • this adjusting cylinder 16 is connected to a load signal line 17 via a pressure compensator 18 and a pressure regulator 19.
  • the load signal line 17 is connected to each of the control units 8 and 9 in such a way that a pressure on the pressure compensator 18 can be passed through it, if via the respective control unit 8 or 9, a pressure medium applied to the hydraulic cylinder 4 or 5.
  • FIG. 1 is the variable displacement pump 3 in its standby mode, ie, in a variable displacement pump according to the bent axis principle, the corresponding axial piston unit is in a state with a small swing angle and thus low displacement volume.
  • the variable displacement pump 3 promotes only a very small amount of hydraulic oil and only builds up a low pressure.
  • the pump pressure p p settles in such a way that the pressure difference ⁇ p LS between the load pressure p LS of the pressure compensator 18 and the delivery pressure p p of the variable displacement pump 3 always remains the same.
  • Line sections 17a and 17b lead from the load signal line 17 to the respective control device 8 and 9, wherein a change-over valve 21 is arranged between the load signal line 17 and these line branches 17a and 17b. Furthermore, 10 section pressure compensators 22 and 23 are provided in the leading to the control units 8 and 9 sections of the pressure line. These are in a parallel operation of multiple consumers 6, 7 ensure that the pump flow independent of the various load pressures is distributed to the consumers 6, 7, as it corresponds to the ratio of the opening cross-sections of the control units 8 and 9.
  • variable displacement pump 3 is permanently adapted to the needs.
  • the efficiency is considerably greater, especially in the fine control range, than in a so-called open center system.
  • the actuating speeds of the consumers 6 and 7 is not influenced by changing load pressures, so that a countersteering is not required.
  • a so-called power beyond connection system 24 which serves for the hydraulic connection of the hydraulic circuit 1 with a hydraulic system 25 of an attachment.
  • the pressure line 10 has a remote terminal 26 labeled P
  • the load signal line 17 has a remote terminal 27 labeled LS
  • the return pipe 11 has a remote terminal 28 labeled T.
  • the load pressure in the corresponding section 17 'of the load signal line 17 should be monitored, because even of these controllers 29 and 30 in the event of an adjustment to their working position on the variable displacement pump 3, a higher delivery volume and a higher pressure to be requested.
  • Individual branches of the load signal line 17 ' are also associated with shuttle valves 21.
  • a control valve 37 which, in the event of actuation of the control devices 29 and / or 30, has a load pressure p LS38 in a first line section 38 of the load signal line 17 connected to the pressure compensator 18 should increase.
  • This pressure increase is necessary because the pressure losses between the variable displacement pump 3 and the hydraulic system 25 of the attachment due to the hydraulic couplings, hose lines, etc. may be greater than the control variable ⁇ p LS , so that a maximum flow for the supply of the load 31 and 32 not more can be provided.
  • the control valve 37 consists of a load signal amplifying valve unit 39 and a biasing stage 40.
  • the control valve 37 and its function is to the following Figures 2 and 3 directed.
  • FIG. 2 shows an enlarged section of the hydraulic scheme of FIG. 1 ,
  • the load valve-boosting valve unit 39 should be designed as a 3/2-way valve 41.
  • a pressure port 42 of the pressure line 10 is shut off via this 3/2-way valve 41, while a load pressure port 43 of the first line section 38 of the load signal line 17 is connected to a tank port 44 of the return line 11. It is thus a position of the 3/2-way valve 41, in which there is no increase in the load pressure p LS38 . How continues the FIG.
  • valve spool 45 of the 3/2-way valve 41 acted upon at one end face both via a line branch 38 'shown symbolically in the hydraulic diagram with a pressure from the first line section 38 and with the force of a compression spring 46.
  • the biasing stage 40 acts via a biasing spring 47th
  • This biasing stage 40 is thereby acted upon by a load pressure p LS48 of a second line section 48 of the load signal line 17.
  • this second line section 48 there is a load pressure p LS48 , which in the illustrated position of the valve slide 45 coincides with the load pressure p LS38 in the load signal line branch 38.
  • a load pressure p LS48 which in the illustrated position of the valve slide 45 coincides with the load pressure p LS38 in the load signal line branch 38.
  • the pressure port 42 communicates with the load pressure port 43, so that via the pump pressure of the pressure line 10, a pressure increase in the first line section 38 is effected.
  • this pressure acts together with the control spring 46 on the end face of the valve spool 45 in the sense of its provision.
  • the second conduit portion 48 due to an operation of the control devices 29 and / or 30 load caused signal p LS48 thus leads directly as well as indirectly via the biasing stage 40 and the biasing spring 47 cause the lossy only with low pressure losses pump pressure P P via the 3 / 2- Directional valve 41, the load pressure p LS38 in the first line section 38 lifts.
  • valve spool 45 locks in its normal position the passage of the pressure medium from the pressure line 10 in the first line section 38 of the load signal line 17.
  • the biasing spring 47 With an increase in the load pressure p LS48 in the biasing stage 40, the biasing spring 47, the front side of the valve spool 45 is applied tense, whereby the valve spool opens the connection between the pressure port 42 and the load pressure port 43.
  • the pressure p LS38 in the first line section 38 of the load signal line 17 is thereby increased by the amount of the biasing force, with the result that the pressure p LS38 is controlled at the load pressure port 43 to the set value.
  • the corresponding design of the control valve 37 shows. Thereafter, the 3/2-way valve 41 of the load signal amplifier unit 39, a housing 49, which is provided with a receiving bore 50 for the valve spool 45.
  • This receiving bore 50 merges into an enlarged bore section 51 into which a housing 52 of the pretensioning stage 40 is screwed.
  • This housing 52 is cylindrical and receives in its interior a control sleeve 53 which is displaceable in the housing 52 via the load pressure p LS48 in the direction of the housing 49 of the 3/2-way valve 41.
  • the control sleeve 53 is provided with a diaphragm 54 at its end facing the second conduit section 48.
  • a first spring plate 55 is arranged on the control sleeve 53, on which the biasing spring 47 is guided with its one end.
  • the other end of the biasing spring 47 is applied to a second spring plate 56, which is supported with an end facing away from the biasing spring 47 on an end face of the valve spool 45.
  • valve spool 45 In addition to this actuation of the valve spool 45 via the biasing spring 47, an immediate pressure actuation of the valve spool 45 is provided, which is effected by a piston 57 and by a push rod 58 emanating therefrom. An actuating force is transmitted directly to the valve spool 45 via the second spring plate 56 via the piston 57 acted upon by the pressure p LS48 and the push rod 58.
  • valve spool 45 is acted upon on its side facing away from the second spring plate 56 front side with the pressure p LS38 from the first conduit portion 38 and with the force of the compression spring 46th
  • the valve spool 45 has a longitudinal bore 59, two mutually offset in the axial direction of the transverse bores 60 and 61 and radially outwardly provided on these annular grooves 62 and 63. In the FIG.
  • valve spool 45 is in a position between its two positions, ie, the valve spool 45 is just moved over the biasing stage 40 in the direction of pressure increase, then then in this switching position of the pressure port 42 via the annular groove 62, the transverse bore 60 and the longitudinal bore 59 with the load pressure connection 43 is connected, so that the load pressure p LS38 is increased according to the pressure line 10.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP15182018.0A 2014-09-30 2015-08-21 Systeme de commande hydraulique Active EP3002462B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014114210.1A DE102014114210A1 (de) 2014-09-30 2014-09-30 Hydraulisches Steuersystem

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EP3002462A1 true EP3002462A1 (fr) 2016-04-06
EP3002462B1 EP3002462B1 (fr) 2024-11-13

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Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017109421A1 (de) 2017-05-03 2018-11-08 Claas Tractor Sas Hydrauliksystem einer land- oder bauwirtschaftlich nutzbaren Arbeitsmaschine
CN109779998B (zh) * 2017-11-14 2023-11-24 浙江三尚智迪科技有限公司 扭矩分配阀及车轮行走液压控制系统

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2302845A1 (de) * 1972-02-22 1973-08-30 Koehring Co Druckkompensationsventil fuer hydraulische kolbenschieber
WO1996037708A1 (fr) * 1995-05-26 1996-11-28 Husco International, Inc. Systeme de commande hydraulique a compensation de pression
WO2005093263A1 (fr) * 2004-03-09 2005-10-06 Bucher Hydraulics Gmbh Systeme de commande hydraulique
EP1783378A2 (fr) * 2005-11-08 2007-05-09 AGCO GmbH Système hydraulique de détection de charge pour tracteur agricole

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2302845A1 (de) * 1972-02-22 1973-08-30 Koehring Co Druckkompensationsventil fuer hydraulische kolbenschieber
WO1996037708A1 (fr) * 1995-05-26 1996-11-28 Husco International, Inc. Systeme de commande hydraulique a compensation de pression
WO2005093263A1 (fr) * 2004-03-09 2005-10-06 Bucher Hydraulics Gmbh Systeme de commande hydraulique
DE112004002768B4 (de) 2004-03-09 2009-02-12 Bucher Hydraulics Gmbh Hydraulisches Steuersystem
EP1783378A2 (fr) * 2005-11-08 2007-05-09 AGCO GmbH Système hydraulique de détection de charge pour tracteur agricole

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EP3002462B1 (fr) 2024-11-13

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