EP2985470B1 - 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
EP2985470B1
EP2985470B1 EP15002101.2A EP15002101A EP2985470B1 EP 2985470 B1 EP2985470 B1 EP 2985470B1 EP 15002101 A EP15002101 A EP 15002101A EP 2985470 B1 EP2985470 B1 EP 2985470B1
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EP
European Patent Office
Prior art keywords
valve
way
control device
pressure
slide valve
Prior art date
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Active
Application number
EP15002101.2A
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German (de)
English (en)
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EP2985470A1 (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
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Hydac Fluidtechnik GmbH
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Publication of EP2985470A1 publication Critical patent/EP2985470A1/fr
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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 having at least one lifting and lowering function with the features in the preamble of claim 1.
  • the EP 1 108 895 A1 describes a control device for a fluid-actuated working cylinder having at least one lifting and lowering function, of which at least the lowering function is controllable by a directional spool valve having at least two fluid connection points to which the working cylinder is fluid-connected with its working spaces, wherein at least one neutral position, the directional spool valve in a predetermined partial flow ratio connects the two working chambers of the working cylinder and simultaneously produces a fluid-conducting connection with a tank or return port of the directional spool valve, wherein the partial flow ratio by means of two oppositely acting on the spool of the directional spool valve energy storage is predetermined.
  • the energy storage based on each end of the valve housing and on respective covers fixed from, which are mounted on the valve housing.
  • the invention has the object to provide an improved control device that is better adaptable to different purposes.
  • 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 at least one of the energy storage is adjustable. This is to adapt to different purposes or to ensure a low production spread.
  • the directional spool valve in at least one neutral position, connects the two working chambers of the working cylinder together while simultaneously establishing 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 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, in that only the control edges of the valve are displaced relative to the neutral position into a floating position which still further opens the passage to the tank or return port.
  • 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 is connected to the shuttle valve, 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 that raise and lower a variety of loads, especially in the field of agriculture by means of a working cylinder and realize a functional floating operation for the implement a kind of floating position, in which the working device, for example in the form of a harrow, except for its weight, can be pulled without force over the tractor to be processed soil by means of the tractor.
  • 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.
  • a directional spool valve 23 in the manner of a 3/3-way spool valve is hydraulically connected via connecting lines 32, 33 and access lines 24, 25 connected thereto to the working cylinder 12, so that at least the lowering function of the way Slider 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.
  • 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 Wegendhrenen 38, 39. Due to the proportional characteristic of this valve, the transitions between the valve positions are "fluent", so that for the sake of simplicity, only the three characteristic switching or displacement positions are considered in more detail below, which the two Wegend einen 38, 39 and the locking center position 37 as shown to 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.
  • Each of the two control line connections 55, 56 is connected to an input 57, 58 of the shuttle valve 26 assigned only to these ports, so that the shuttle valve 26 is connected to the direction of the tank outlet side 60 of the directional control valve 16.
  • a control line LS is 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.
  • 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 is in addition to the solenoid actuation system 64 via the control pressure from the control line LS formed by the load sensing pressure hydraulic can be controlled, 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 plunger 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 solenoid 71 axially slidably 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 is also supported 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 opens via this annulus 125 on the one hand into the receiving space 122 and on the other hand into the leakage oil space 126 off. 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 by means of the magnetic actuation system 64 in a further valve position, 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 , Since a part of the supply pressure via the respective secondary path 53, 54 is guided on 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 working as a differential piston piston 29 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 fluid under pressure 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.

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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)

Claims (10)

  1. Dispositif de commande d'un cylindre (12) de travail pouvant être actionné fluidiquement et ayant au moins une fonction de levage et d'abaissement, dont au moins la fonction d'abaissement peut être commandée par une soupape (23) à coulisse à plusieurs voies, qui a au moins deux points de raccordement de fluide, où le cylindre (12) de travail est raccordé fluidiquement par ses espaces (20, 21) de travail, dans lequel dans au moins une position (69) neutre de la soupape (23) à coulisse à plusieurs voies, les deux espaces (20, 21) de travail du cylindre (12) de travail communiquent entre eux suivant un rapport de courant partiel pouvant être prescrit et procurent ainsi, en même temps, une liaison fluidique avec un raccord de réservoir ou de retour de la soupape (23) à coulisse à plusieurs voies, le rapport de courant partiel étant prescrit au moyen de deux accumulateurs (67, 68) d'énergie agissant en sens contraire sur le piston (63) coulissant de la soupape (3) coulissante à plusieurs voies, caractérisé en ce qu'au moins l'un des accumulateurs (67, 68) d'énergie est réglable.
  2. Dispositif de commande suivant la revendication 1,
    caractérisé
    en ce qu'il est prévu des accumulateurs d'énergie sous la forme de ressorts (67, 68) de compression.
  3. Dispositif de commande suivant la revendication 2,
    caractérisé
    en ce que les précontraintes éventuelles des deux ressorts (67, 68) de compression sont réglables au moyen d'un entraînement (66) par vis sans fin, le un ressort (68) de compression faisant partie d'un système (64) d'actionnement par aimant.
  4. Dispositif de commande suivant la revendication 3,
    caractérisé
    en ce qu'au moyen du système (64) d'actionnement par aimant, la soupape (23) à coulisse à plusieurs voies peut être mise dans une autre position de soupape, qui rend possible une sorte de position (118) flottante du cylindre (12) de travail raccordé fluidiquement.
  5. Dispositif de commande suivant la revendication 4,
    caractérisé
    en ce que la soupape (23) à coulisse à plusieurs voies a, outre la position (69) neutre et la position (118) flottante, encore une position (28) d'arrêt.
  6. Dispositif de commande suivant l'une des revendications 3 à 5,
    caractérisé
    en ce qu'il a, en outre, une soupape (16) à plusieurs voies, dans lequel, outre le système (64) d'actionnement à aimant, le piston (63) coulissant de la soupape (23) à coulisse à plusieurs voies peut être commandé encore par une pression de commande, notamment une pression loadsensing, à partir d'un conduit (LS) de commande, auquel peut être appliquée la pression pouvant être prescrite par du fluide à partir de la soupape (16) à plusieurs voies.
  7. Dispositif de commande suivant la revendication 6,
    caractérisé
    en ce qu'il a, en outre, une soupape (26) à deux voies, dans lequel le conduit (LS) de commande est raccordé à la soupape (26) à deux voies, qui achemine la pression d'entrée plus haute au conduit (LS) de commande, et en ce que la soupape (26) à deux voies est raccordée du côté (60) de la sortie de réservoir de la soupape (16) à plusieurs voies.
  8. Dispositif de commande suivant la revendication 7,
    caractérisé
    en ce que, dans la position (28) d'arrêt de la soupape (23) à coulisse à plusieurs voies, la fonction de levage et d'abaissement est provoquée exclusivement sans étranglement par la soupape (16) à plusieurs voies, en ce que, dans la position (69) neutre de la soupape (23) coulissante à plusieurs voies, l'étranglement a lieu au moins pendant la fonction d'abaissement du cylindre de travail alors que la soupape (16) à plusieurs voies est fermée.
  9. Dispositif de commande suivant l'une des revendications 6 à 8,
    caractérisé
    en ce qu'il a, en outre, une pompe (18) loadsensing, qui, pour la commande de son angle de basculement, est raccordée au conduit (LS) de commande de la soupape (23) à coulisse à plusieurs voies.
  10. Dispositif de commande suivant l'une des revendications 6 à 9,
    caractérisé
    en ce que la soupape (23) à coulisse à plusieurs voies est une soupape à coulisse à 3/3 voies et en ce que la soupape (16) à plusieurs voies est formée d'une soupape à 4/3 voies.
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 EP2985470A1 (fr) 2016-02-17
EP2985470B1 true 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)

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

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105757027B (zh) * 2016-04-22 2018-06-15 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

Family Cites Families (7)

* 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
JPH06128983A (ja) * 1992-10-14 1994-05-10 Kubota Corp 作業車のドーザ装置
DE19504886C2 (de) * 1995-02-14 1999-01-07 Mannesmann Rexroth Ag Einstellbares Druckventil
DE19957952A1 (de) * 1999-12-02 2001-06-07 Mannesmann Rexroth Ag Hydraulisches Wegeventil zur lastunabhängigen Steuerung eines hydraulischen Verbrauchers von insbesondere einer mobilen Arbeitsmaschine
DE10340505B4 (de) * 2003-09-03 2005-12-15 Sauer-Danfoss Aps Ventilanordnung zur Steuerung eines Hydraulikantriebs
US8434516B2 (en) * 2006-04-24 2013-05-07 Parker-Hannifin Corporation Three position solenoid valve
DE102013014673A1 (de) 2013-09-04 2015-03-05 Hydac Fluidtechnik Gmbh Lasthalteventil

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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EP2985470A1 (fr) 2016-02-17
DE102014012117A1 (de) 2016-02-18

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