EP2985470A1 - Dispositif de commande pour un cylindre de travail actionné par un fluide ayant au moins une fonction de levage et d'abaissement - Google Patents

Dispositif de commande pour un cylindre de travail actionné par un fluide ayant au moins une fonction de levage et d'abaissement Download PDF

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Publication number
EP2985470A1
EP2985470A1 EP15002101.2A EP15002101A EP2985470A1 EP 2985470 A1 EP2985470 A1 EP 2985470A1 EP 15002101 A EP15002101 A EP 15002101A EP 2985470 A1 EP2985470 A1 EP 2985470A1
Authority
EP
European Patent Office
Prior art keywords
valve
directional
control device
spool
control
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
EP15002101.2A
Other languages
German (de)
English (en)
Other versions
EP2985470B1 (fr
Inventor
Harald BÄR
Georg Komma
Josef Christian Schäfer
Philipp Gandner
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.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP2985470A1 publication Critical patent/EP2985470A1/fr
Application granted granted Critical
Publication of EP2985470B1 publication Critical patent/EP2985470B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control

Definitions

  • the invention relates to a control device for a fluidly actuable working cylinder with at least one lifting and lowering function, of which at least the lowering function can be controlled by a directional spool valve which has at least two fluid connection points to which the working cylinder with its work spaces is fluid-conducting connected.
  • the present invention seeks to provide contrast, solutions that make it possible to relieve both working spaces of a working cylinder in a functionally reliable manner, in particular in the context of a sink function.
  • a control device for a fluidly actuable working cylinder having at least one lifting and lowering function, which has the features of claim 1 in its entirety.
  • a significant feature is that in at least one neutral position, the directional spool valve in a predetermined partial flow ratio, the two working chambers of the working cylinder together and at the same time produces a fluid-conducting connection with a tank or return port of the directional spool valve ,
  • This neutral position makes it possible to relieve the two working spaces of the working cylinder, in particular for a lowering function when the directional spool valve is not actuated, to a common tank or return connection.
  • the partial flow ratio by means of two counter-acting on the spool of the valve energy storage, preferably in the form of compression springs, predetermined, of which at least one energy storage is adjustable.
  • the possible spring preloads of the two compression springs are adjustable by means of a spindle drive.
  • the one compression spring is part of a magnetic actuation system.
  • the directional slide valve in each case by means of the magnetic actuation system, can be brought into a further valve position, which allows a kind of floating position for the connected fluidic working cylinder.
  • a further valve position can be created with little effort, for example, by merely displacing the control edges of the valve relative to the neutral position into a floating position that opens the tank or return port even further.
  • the way-slide valve in an advantageous embodiment, in addition to the neutral position and the floating position still have a blocking position.
  • the spool of the directional spool valve via a control pressure, in particular in the form of a load sensing pressure, from a control line, driven by a directional valve with Fluid predeterminable pressure is supplied.
  • a shuttle valve may be provided to prevent unwanted bridging of these switching positions associated connections.
  • the control line to the shuttle valve connected, which forwards the respective higher input pressure to the control line.
  • the shuttle valve may be connected to the tank outlet side of the directional control valve.
  • At least a portion of an already existing control line for controlling the directional spool valve can be found with relatively little effort additional benefit by a load-sensing pump is used for the pressure supply of the overall device, which is connected to control its pivot angle to the control line for the directional spool valve ,
  • the directional spool valve is a 3/3-way spool valve and the directional control valve is formed from a 4/3-way valve.
  • the control device according to the invention can be used, for example, in tractors and comparable agricultural machines which, as universal tools, lift various loads, in particular in the field of agriculture, by means of a working cylinder and lower as well as realize a kind of floating position for a functional operation for the implement, in which the implement, for example in the form of a harrow, can be pulled force-free over the crop soil to be processed by means of the tractor to their weight.
  • Fig. 1 shows a control device 10 for a fluidly actuable working cylinder 12 with a lifting, lowering and floating function.
  • a load 14 can, inter alia, be actively raised and lowered by a correspondingly switched directional control valve 16 in the manner of a 4/3-way proportional valve, a supply pressure of a supply source 18 in the manner of a hydraulic pump to one of the two working spaces 20, 21st of the working cylinder 12 and simultaneously relieves the other of the two working chambers 21, 20 of the working cylinder 12 in the direction of a supply tank 22.
  • Parallel to the directional control valve 16 is a directional spool valve 23 in the manner of a 3/3-way spool valve hydraulically connected via connecting lines 32, 33 and connected thereto access lines 24, 25 to the working cylinder 12, so that at least the lowering function of the directional slide valve 23 is controlled.
  • the directional control valve 16 can actuate the directional spool valve 23 into a blocking position 28 via a control line system 27 having a shuttle valve 26 and at the same time control the pump pressure and delivery flow of the hydraulic pump 18 designed as a load-sensing pump as part of the fluid supply device.
  • the working cylinder 12 has a differential piston 29, the longitudinally movable within a cylinder housing 30, the piston-side working space 20 of the rod-side working space 21 media-tight manner.
  • a piston rod 31 of the differential piston 29 can be acted upon by a force resulting from the load 14. If the piston-side working chamber 20 is pressurized with simultaneous pressure relief of the rod-side working chamber 21, then the piston rod 31 of the differential piston 29 extends and, with its load 14 acting on it, lifts it. Similarly, pressurization of the rod-side working space 21 results in pressure relief of the piston-side working chamber 20 for retracting the piston rod 31. If both working chambers 20, 21 at attacking load 14 relieved of pressure, the differential piston 29 also moves as a result of the load.
  • the two working chambers 20, 21 are connected via the access lines 24, 25 and in each case one output side of the directional control valve 16 associated working port 35, 36 with the directional control valve 16, which has a locking center position 37 and two of these immediately adjacent Wegend einen 38, 39. Due to the proportional characteristic of this valve, the transitions between the valve positions are "flowing", so that in the following, for the sake of simplicity, only the three characteristic shift or shift positions will be considered in greater detail, which shows the two shift end positions 38, 39 and the locked center position 37 as shown in FIG Fig. 1 exhibit. In the locked center position 37 all inputs and outputs of the directional control valve 16 are locked.
  • the directional control valve 16 For switching to the two switching end positions 38, 39 is on both sides of the directional control valve 16 each have a solenoid 41, 42 provided with a parallel effective compression spring 43, 44, so that the two oppositely acting spring forces the directional control valve 16 automatically and in a self-centering manner in the locked center position 37 hold, provided that neither of the two electromagnets 41, 42 switches the directional control valve 16.
  • the directional control valve 16 leads from the supply pump 18 via a supply line 45 to a supply port 46 input side of the directional control valve 16 supply pressure for extending the piston rod 31 on the piston-side working chamber 20 and relieves the rod-side working chamber 21 via a drain path 47 to the supply tank 22 out.
  • the rod-side working space 21 is pressure-loaded for retracting the differential piston 31, whereas the piston-side working space 21 is relieved via the discharge path 47 to the supply tank 22.
  • These two shift end positions 38, 39 are realized by their function valve internally with four switching paths 49, 50, 51, 52. From each of the two switching paths 50, 51 leading from the supply connection 46 to the respective working space 20, 21 branches off a secondary path 53, 54 which leads to a control line connection 55, 56 assigned to only this respective secondary path 53, 54 on a tank outlet side 60 of the directional control valve 16.
  • Each of the two control line connections 55, 56 is connected to an input 57, 58 of the shuttle valve 26, which are respectively assigned to these ports, so that the shuttle valve 26 is connected to the tank outlet side 60 of the directional control valve 16.
  • a control line LS connected to the shuttle valve 26, which forwards the respective higher input pressure to this control line LS.
  • the pressure applied to the control line LS acts on the supply pump 18 designed as a load-sensing pump such that its pump pressure and delivery flow are automatically adapted to the requirements of the control device.
  • the load-sensing pump 18 is exclusively used for the pressure supply of the entire device, which in turn is connected to the control line LS for the hydraulic actuation of the directional spool valve 23 for controlling its pivoting angle.
  • control line LS goes via a node 59 from a line section 61, which leads to a hydraulically actuated actuator 62 for displacement of a spool 63 of the directional spool valve 23 in one of the possible traversing directions.
  • a hydraulically actuated actuator 62 for displacement of a spool 63 of the directional spool valve 23 in one of the possible traversing directions.
  • the spool 63 is displaceable by means of a magnetic actuation system 64 in the opposite direction to this direction in an associated valve housing 65 (FIG. Fig. 2 ) guided.
  • the spool 63 in addition to the solenoid actuation system 64 is still hydraulically controllable via the control pressure formed by the load-sensing pressure from the control line LS, which can be supplied from the directional control valve 16 with fluid presettable pressure.
  • FIG. 2 now shows the directional spool valve 23 with the spool 63 in a longitudinal sectional view, which is held in a neutral position 69 within the valve housing 65 by means of two end to this valve housing 65, each of the solenoid actuation system 64 and a spindle drive 66 associated compression springs 67, 68 ,
  • the magnetic actuation system 64 has a "pushing" electromagnet 71, the armature 72 of which is guided axially displaceable within a pole tube 73 integrally formed with a pole tube 74.
  • a coil 75 for displacement of the armature 72, a coil 75, not shown in the same outside of the pole tube 74 is provided, which is energized, so that a current through the resulting magnetic field the armature 72 in the direction of the pole core 73, in the direction of the Fig. 2 seen from left to right, looking to move.
  • the central bore 76 having pole core 73 is penetrated by an attached to the armature 72 actuating tappet 77, which is supported on the end face 78 of the spool 63, so that the latter within the fixedly bolted to the pole core 73 housing 65 from the electromagnet 71 axially displaceable actuated is.
  • the magnetic actuation system 64 associated compression spring 67 is supported on the one hand on the pole core 73 and on the other hand on the end face 78 at the first end 79 of the spool 63, so that this compression spring 67 strives to move the spool 63 in the same direction as the Electromagnet 71 with energized coil 75th
  • the spindle drive 66 has a spindle housing 82 screwed in at the end 80 of the bushing 65, within which a spindle 83 is in turn axially displaceable by a rotational movement which has a thread pairing 84 with the spindle housing 82 for this purpose.
  • a lock nut 85 is screwed onto an outwardly projecting region 86 of the spindle 83 and tightened against the spindle housing 82.
  • the compression spring 68 which is supported on the one hand in the blind hole bottom 88 and the other hand at the bottom 89 of an adjusting bolt 91, the axial displacement within the blind hole 87 by means of a in an inner ring groove 92nd the blind hole 87 inserted snap ring 93 is axially limited.
  • the adjusting bolt 91 supports Furthermore, on its side facing away from the compression spring 68 side with its own end face 94 on a facing end face 95 at the second end of the spool 63 from.
  • the one compression spring 68 is part of the magnetic actuation system 64.
  • the spool 63 has three axially spaced control grooves 103, 104, 105, which are consequently separated from each other by means of two webs 106, 107.
  • the two axially outer control grooves 103, 105 are delimited by guide pistons 108, 109 of the spool piston 63.
  • the one web 106 at its left control edge 110 closes flush with the region 111 of the transverse bore wall 112 of the tank connection T2 that is closest to the first working connection A.
  • a throttle body 113 which throttles the flow of fluid between the first working port A and the tank port T2.
  • the other web 107 terminates at its left control edge 114 without overlapping flush with the area 115 of the transverse bore wall 116 of the second working port B which is closest to the tank connection T2.
  • this control edge 114 and the transverse bore wall 116 forms a throttle point 117, which throttles the flow of fluid between the second working port B and the tank port T2.
  • the partial flow ratio is predetermined by means of two counter-acting on the spool 63 of the directional spool valve 23 energy storage in the form of the two compression springs 67, 68, which, as already stated, are adjustable by means of the spindle drive 66.
  • the hydraulic path discharges via this annular space 125, on the one hand, into the receiving space 122 and, on the other hand, into the leakage oil space 126. In this way, fluid can be exchanged between the two chambers 122, 126 in the case of volume changes of the two chambers 122, 126 as a result of displacements of the spool piston 63.
  • a pressure equalization with respect to the pressure applied to the supply tank 22 atmospheric pressure is made possible via the pressure equalization bore 123.
  • the directional spool valve 23 is brought into a further valve position by means of the magnetic actuation system 64, which allows a kind of floating position 118 for the connected fluidic cylinder 12.
  • This floating position 118 is shown symbolically in the drawing as the left switching end position.
  • the spool 63 is opposite the housing 65 in the direction of the Fig. 3 shifted to the right, so that its two webs 106, 107 are arranged opposite the neutral position 69 further to the right.
  • the respective narrow web 106, 107 is arranged relatively centrally to the respective associated transverse bore 98, 99.
  • the directional spool valve 23 produces a virtually unthrottled hydraulic connection between the two working ports A, B and the tank port T2.
  • the differential piston 31 is retracted or extended as a result of the pressurization of the respective one working space 20, 21 and pressure relief of the respective other working space 21, 20 . Because part of the supply pressure is guided over the respective secondary path 53, 54 to the input side of the shuttle valve 23, the control pressure guided by this via the control line LS and the line section 61 on the end face 95 of the spool 63 holds the directional spool valve 23 in the blocking position 28, as long as the Differential piston 29 executed working piston driven by the directional control valve 16 is retracted or extended.
  • the magnetic actuation system 64 is not able to move the directional slide valve 23 into the floating position 118 or the neutral position 28, as the maximum force which can be introduced by the magnetic actuation system 64 onto the valve piston 63 is smaller than the force due to the pending on the relatively large end face 95 control pressure.
  • the blocking position 28 of the directional spool valve 23 the lifting and lowering function without throttling by the directional control valve 16 is exclusively caused.
  • An undesirable rapid lowering of the load 14 by means of pressure discharge via the two throttle bodies 113, 117 is equally excluded as a Druckaustechnisch in the floating position 118 of the directional spool valve 23.
  • control pressure can be placed in the floating position 118 formed by the left Endschaltwolf with appropriate energization of the coil 75 of the magnetic actuation system 64 of the spool 63.
  • the pressurized fluid from the two working chambers 20, 21 of the working cylinder 12 is brought together unthrottled and returned to the supply tank 22 via the common tank connection T2.
  • the differential piston 29 follows within the limits of its end stops all the axial forces introduced to the piston rod 31 from the outside, whereupon any residual fluid remaining in the work spaces 20, 21 is expelled to the supply tank 22 with a corresponding passive displacement of the differential piston 29.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
EP15002101.2A 2014-08-12 2015-07-15 Dispositif de commande pour un cylindre de travail actionné par un fluide ayant au moins une fonction de levage et d'abaissement Active EP2985470B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014012117.8A DE102014012117A1 (de) 2014-08-12 2014-08-12 Steuerungsvorrichtung für einen fluidisch betätigbaren Arbeitszylinder mit zumindest einer Heben- und Senkenfunktion

Publications (2)

Publication Number Publication Date
EP2985470A1 true EP2985470A1 (fr) 2016-02-17
EP2985470B1 EP2985470B1 (fr) 2018-12-19

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Application Number Title Priority Date Filing Date
EP15002101.2A Active EP2985470B1 (fr) 2014-08-12 2015-07-15 Dispositif de commande pour un cylindre de travail actionné par un fluide ayant au moins une fonction de levage et d'abaissement

Country Status (2)

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EP (1) EP2985470B1 (fr)
DE (1) DE102014012117A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105757027A (zh) * 2016-04-22 2016-07-13 青神格林维尔流体动力控制技术有限公司 一种自动启停式液压站的插装式系统集成块

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06128983A (ja) * 1992-10-14 1994-05-10 Kubota Corp 作業車のドーザ装置
EP1108895A1 (fr) * 1999-12-02 2001-06-20 Mannesmann Rexroth AG Valve hydraulique pour la commande d'un consommateur indépendant de la charge
US20070246112A1 (en) * 2006-04-24 2007-10-25 Aranovich Felix E Three position solenoid valve
DE102013014673A1 (de) 2013-09-04 2015-03-05 Hydac Fluidtechnik Gmbh Lasthalteventil

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2514915B2 (ja) * 1989-03-08 1996-07-10 油谷重工株式会社 建設機械のブ―ム用フロ―ト回路
DE19504886C2 (de) * 1995-02-14 1999-01-07 Mannesmann Rexroth Ag Einstellbares Druckventil
DE10340505B4 (de) * 2003-09-03 2005-12-15 Sauer-Danfoss Aps Ventilanordnung zur Steuerung eines Hydraulikantriebs

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06128983A (ja) * 1992-10-14 1994-05-10 Kubota Corp 作業車のドーザ装置
EP1108895A1 (fr) * 1999-12-02 2001-06-20 Mannesmann Rexroth AG Valve hydraulique pour la commande d'un consommateur indépendant de la charge
US20070246112A1 (en) * 2006-04-24 2007-10-25 Aranovich Felix E Three position solenoid valve
DE102013014673A1 (de) 2013-09-04 2015-03-05 Hydac Fluidtechnik Gmbh Lasthalteventil

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105757027A (zh) * 2016-04-22 2016-07-13 青神格林维尔流体动力控制技术有限公司 一种自动启停式液压站的插装式系统集成块

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Publication number Publication date
DE102014012117A1 (de) 2016-02-18
EP2985470B1 (fr) 2018-12-19

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