EP2985470B1 - Control device for a fluid operated work cylinder with at least one lifting and lowering function - Google Patents
Control device for a fluid operated work cylinder with at least one lifting and lowering function Download PDFInfo
- 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
- 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.)
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- 239000012530 fluid Substances 0.000 title claims description 16
- 230000007935 neutral effect Effects 0.000 claims description 19
- 230000006835 compression Effects 0.000 description 13
- 238000007906 compression Methods 0.000 description 13
- 238000006073 displacement reaction Methods 0.000 description 8
- 230000000903 blocking effect Effects 0.000 description 7
- 238000004146 energy storage Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 230000036316 preload Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000000977 initiatory effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
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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
- F15B11/02—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"
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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
- 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
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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
- 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
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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
- 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
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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
- 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)
Description
Die Erfindung betrifft eine Steuerungsvorrichtung für einen fluidisch betätigbaren Arbeitszylinder mit zumindest einer Heben- und Senkenfunktion mit den Merkmalen im Oberbegriff von Anspruch 1.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.
Eine dahingehende Steuerungsvorrichtung für einen fluidisch betätigbaren Arbeitszylinder mit zumindest einer Heben- und Senkenfunktion ist in der Anmeldeschrift
- einer Lasthaltestellung ist mittels der beiden Kolben eine fluidführende Verbindung zwischen mindestens zwei Anschlussstellen gesperrt, von denen eine der Medienzufuhr oder -abfuhr dient und von denen die andere zu einem hydraulischen Verbraucher führt,
- einer Lasthebenstellung bewegen sich die beiden Kolben relativ zueinander in eine Freigabestellung, bei der die Verbindung zwischen Medienzufuhr und Verbraucher hergestellt ist, und
- einer Lastsenkenstellung nehmen die beiden Kolben derart einen vorgebbaren Abstand zueinander ein, dass die Verbindung zwischen Medienabfuhr und Verbraucher hergestellt ist.
- a load-holding position is blocked by means of the two pistons a fluid-carrying connection between at least two connection points, one of which serves for the media supply or removal and of which the other leads to a hydraulic consumer,
- a load lifting position, the two pistons move relative to each other in a release position, in which the connection between the media supply and consumer is made, and
- a load depression position, the two pistons take such a predeterminable distance from one another that the connection between media removal and consumer is made.
In dieser Lastsenkenstellung wird zur Ausübung einer Kraft mittels des Verbrauchers in der Art eines Arbeitszylinders dessen kolbenseitiger Arbeitsraum mit einem Druck beaufschlagt, während der stangenseitige Arbeitsraum des Verbrauchers mit der Medienabfuhr verbunden wird.In this load lowering position is applied to exert a force by means of the consumer in the manner of a working cylinder whose piston-side working space with a pressure, while the rod-side working space of the consumer is connected to the Medienabfuhr.
Die
Weitere Steuerungsvorrichtungen gehen aus der
Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, eine verbesserte Steuerungsvorrichtung aufzuzeigen, die besser an unterschiedliche Einsatzzwecke anpassbar ist.Based on this prior art, the invention has the object to provide an improved control device that is better adaptable to different purposes.
Diese Aufgabe wird durch eine Steuerungsvorrichtung für einen fluidisch betätigbaren Arbeitszylinder mit zumindest einer Heben- und Senkenfunktion gelöst, welche die Merkmale von Patentanspruch 1 in seiner Gesamtheit aufweist.This object is achieved by 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.
Nach dem kennzeichnenden Teil des Anspruchs 1 besteht eine wesentliche Besonderheit darin, dass mindestens einer der Energiespeicher einstellbar ist. Dies dient der Anpassung an verschiedene Einsatzzwecke oder auch zur Sicherstellung einer geringen Serienstreuung.According to the characterizing part of claim 1, 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.
Es ist ferner vorgesehen, dass in mindestens einer Neutralstellung das Wege-Schieberventil in einem vorgebbaren Teilstromverhältnis die beiden Arbeitsräume des Arbeitszylinders miteinander verbindet und dabei gleichzeitig eine fluidführende Verbindung mit einem Tank- oder Rücklaufanschluss des Wege-Schieberventils herstellt. Diese Neutralstellung ermöglicht es, die beiden Arbeitsräume des Arbeitszylinders insbesondere für eine Senkenfunktion bei unbetätigtem Wege-Schieberventil zu einem gemeinsamen Tank- oder Rücklaufanschluss zu entlasten.It is further contemplated that in at least one neutral position, the directional spool valve in a predetermined partial flow ratio 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.
In einer vorteilhaften Ausführungsform sind die möglichen Federvorspannungen der beiden Druckfedern mittels eines Spindeltriebes einstellbar. Dabei ist die eine Druckfeder Teil eines Magnet-Betätigungssystems.In an advantageous embodiment, 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.
Bei weiteren vorteilhaften Ausführungsformen ist jeweils mittels des Magnet-Betätigungssystems das Wege-Schieberventil in eine weitere Ventilposition bringbar, die eine Art Schwimmstellung für den angeschlossenen fluidischen Arbeitszylinder ermöglicht. Somit lässt sich ausgehend von der Neutralstellung mit geringem Aufwand eine weitere Ventilposition beispielsweise dadurch schaffen, dass lediglich die Steuerkanten des Ventils gegenüber der Neutralstellung in eine den Durchlass zum Tank- oder Rücklaufanschluss noch weiter freigebende Schwimmstellung verlagert werden.In further advantageous embodiments, in each case by means of the magnetic actuation system, the directional slide valve can be brought into a further valve position, which allows a kind of floating position for the connected fluidic working cylinder. Thus, starting from the neutral position, 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.
Um das Wege-Schieberventil im Bedarfsfall wirkungslos zu "schalten", kann das Wege-Schieberventil bei einer vorteilhaften Ausführungsform neben der Neutralstellung und der Schwimmstellung noch eine Sperrstellung aufweisen.In order to "switch" the directional slide valve in case of need ineffective, the way-slide valve in an advantageous embodiment, in addition to the neutral position and the floating position still have a blocking position.
Zum Erzielen vorzugsweise erwünschter Schaltkombination der beiden Ventile ist bei einer weiteren vorteilhaften Ausführungsform neben dem Magnet-Betätigungssystem der Schieberkolben des Wege-Schieberventils noch über einen Steuerdruck, insbesondere in Form eines Loadsensing-Drucks, aus einer Steuerleitung, ansteuerbar, die von einem Wegeventil aus mit Fluid vorgebbaren Druckes versorgbar ist.To achieve preferably desired switching combination of the two valves, in a further advantageous embodiment, in addition to the magnetic actuating system, 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.
Insbesondere bei solchen Ausführungsformen, bei denen jeweils der Steuerdruck in mehreren Schaltstellungen des Wegeventils auf das Wege-Schieberventil wirken soll, kann zum Verhindern einer unerwünschten Überbrückung der diesen Schaltstellungen zugeordneten Anschlüsse ein Wechselventil vorgesehen sein. Dabei ist die Steuerleitung an das Wechselventil angeschlossen, das den jeweils höheren Eingangsdruck an die Steuerleitung weiterleitet. Ferner kann das Wechselventil an die Tankausgangsseite des Wegeventils angeschlossen sein.In particular, in such embodiments in which in each case the control pressure is to act in several switching positions of the directional control valve on the directional spool valve, a shuttle valve may be provided to prevent unwanted bridging of these switching positions associated connections. In this case, the control line is connected to the shuttle valve, which forwards the respective higher input pressure to the control line. Further, the shuttle valve may be connected to the tank outlet side of the directional control valve.
Zur Verwirklichung einer Sicherheitsfunktion, die ein unerwünschtes Senken einer Last verhindert, während der Arbeitszylinder vom Wegeventil angesteuert wird, kann bei einer vorteilhaften Ausgestaltung vorgesehen sein, dass in der Sperrstellung des Wege-Schieberventils die Heben- und Senkenfunktion ohne Androsselung durch das Wegeventil ausschließlich veranlasst ist, und dass in der Neutralstellung des Wege-Schieberventils die Ablaufdrosselung zumindest für die Senkenfunktion des Arbeitszylinders bei gesperrtem Wegeventil erfolgt.To achieve a safety function that prevents unwanted lowering of a load while the working cylinder is controlled by the directional control valve can be provided in an advantageous embodiment, that in the blocking position of the directional spool valve, the lifting and lowering function without throttling by the directional valve is exclusively caused , And that in the neutral position of the directional spool valve, the drain throttling takes place at least for the lowering function of the working cylinder when the directional control valve is locked.
Zumindest ein Abschnitt einer ohnehin vorhandenen Steuerleitung zur Steuerung des Wege-Schieberventils kann mit relativ geringem Aufwand zusätzlichen Nutzen finden, indem für die Druckversorgung der Gesamtvorrichtung eine Loadsensing-Pumpe eingesetzt ist, die zur Ansteuerung ihres Schwenkwinkels an die Steuerleitung für das Wege-Schieberventil angeschlossen ist.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 ,
Ventile mit drei Schaltstellungen haben sich bewährt, da die Hydraulikteile dieser Ventile mit relativ kurzen Axialwegen des Schieberkolbens verwirklicht werden können, so dass diese Ventile insbesondere bei der elektromagnetischen Betätigung mit kostenmäßig vertretbarem Aufwand hergestellt werden können. Insofern ist in vorteilhaften Ausgestaltungen das Wege-Schieberventil ein 3/3-Wege-Schieberventil und das Wegeventil ist aus einem 4/3-Wegeventil gebildet.Valves with three switching positions have been proven, since the hydraulic parts of these valves can be realized with relatively short axial paths of the spool, so that these valves can be made in cost-effective cost, especially in the electromagnetic actuation. In this respect, in advantageous embodiments, the directional spool valve is a 3/3-way spool valve and the directional control valve is formed from a 4/3-way valve.
Die erfindungsgemäße Steuerungsvorrichtung kann beispielsweise Anwendung finden bei Traktoren und vergleichbaren landwirtschaftlichen Arbeitsmaschinen, die als universelle Arbeitsgeräte verschiedenste Lasten insbesondere im Bereich der Landwirtschaft mittels eines Arbeitszylinders heben und senken sowie für einen funktionsgerechten Betrieb für das Arbeitsgerät eine Art Schwimmstellung realisieren, bei der das Arbeitsgerät, beispielsweise in Form einer Egge, bis auf ihre Gewichtskraft, kräftefrei über den zu bearbeitenden Ackerboden mittels des Traktors gezogen werden kann.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.
Nachstehend ist die Erfindung anhand eines in der Zeichnung dargestellten Ausführungsbeispiels im Einzelnen erläutert. Es zeigen:
- Fig. 1
- anhand eines hydraulischen Schaltplans eine Steuerungsvorrichtung für einen fluidisch betätigbaren Arbeitszylinder mit einer Heben-, Senken- und Schwimmfunktion;
- Fig. 2
- in einem Längsschnitt und darunter als symbolisches Schaltbild dargestellt ein in einer Neutralstellung befindliches WegeSchieberventil, welches Anwendung in einer Steuerungsvorrichtung gemäß
Fig. 1 findet; - Fig. 3
- in einer Darstellung analog
Fig. 2 deren Wege-Schieberventil, welches jedoch in die Schwimmstellung geschaltet ist; und - Fig. 4
- in einer Darstellung analog
Fig. 2 deren Wege-Schieberventil, welches jedoch in die Sperrstellung geschaltet ist.
- Fig. 1
- by means of a hydraulic circuit diagram, a control device for a fluid-actuated working cylinder with a lifting, lowering and floating function;
- Fig. 2
- in a longitudinal section and shown below as a symbolic circuit diagram located in a neutral position directional control valve, which application in a control device according to
Fig. 1 place; - Fig. 3
- in a representation analog
Fig. 2 the way slide valve, which is, however, connected in the floating position; and - Fig. 4
- in a representation analog
Fig. 2 the way-slide valve, which, however, is connected in the blocking position.
Das Wegeventil 16 kann über ein ein Wechselventil 26 aufweisendes Steuerleitungssystem 27 zum einen das Wege-Schieberventil 23 in eine Sperrstellung 28 betätigen, halten und zugleich den Pumpendruck und Förderstrom der als Loadsensing-Pumpe ausgeführten Hydraulikpumpe 18 als Teil der Fluid-Versorgungseinrichtung regeln.The
Der Arbeitszylinder 12 weist einen Differentialkolben 29 auf, der innerhalb eines Zylindergehäuses 30 längsverfahrbar geführt den kolbenseitigen Arbeitsraum 20 von dem stangenseitigen Arbeitsraum 21 mediendicht trennt. Eine Kolbenstange 31 des Differentialkolbens 29 ist dabei mit einer sich aus der Last 14 ergebenden Kraft beaufschlagbar. Wird der kolbenseitige Arbeitsraum 20 bei gleichzeitiger Druckentlastung des stangenseitigen Arbeitsraumes 21 druckbeaufschlagt, so fährt die Kolbenstange 31 des Differentialkolbens 29 aus und hebt bei an ihr angreifender Last 14 diese an.The working
Analog dazu führt eine Druckbeaufschlagung des stangenseitigen Arbeitsraumes 21 bei Druckentlastung des kolbenseitigen Arbeitsraumes 20 zum Einfahren der Kolbenstange 31. Werden beide Arbeitsräume 20, 21 bei angreifender Last 14 druckentlastet, so fährt der Differentialkolben 29 infolge der Belastung ebenfalls ein.Similarly, pressurization of the rod-
Die beiden Arbeitsräume 20, 21 sind über die Zugangsleitungen 24, 25 und jeweils einem ausgangsseitig dem Wegeventil 16 zugeordneten Arbeitsanschluss 35, 36 mit dem Wegeventil 16 verbunden, welches eine Sperr-Mittenstellung 37 und zwei dieser unmittelbar benachbarte Schaltendstellungen 38, 39 aufweist. Aufgrund der Proportionalcharakteristik dieses Ventils sind die Übergänge zwischen den Ventilstellungen "fließend", so dass im Folgenden der Einfachheit halber nur die drei charakteristischen Schalt- oder Verschiebestellungen näher betrachtet werden, welche die beiden Schaltendstellungen 38, 39 und die Sperr-Mittenstellung 37 gemäß der Darstellung nach
Jeder der beiden Steuerleitungsanschlüsse 55, 56 ist an einen nur diesen Anschlüssen jeweils zugeordneten Eingang 57, 58 des Wechselventils 26 angeschlossen, so dass das Wechselventil 26 in Richtung der Tankausgangsseite 60 des Wegeventils 16 an dieses angeschlossen ist. Ferner ist eine Steuerleitung LS an das Wechselventil 26 angeschlossen, das den jeweils höheren Eingangsdruck an diese Steuerleitung LS weiterleitet. Der an der Steuerleitung LS anliegende Druck wirkt dabei derart auf die als Loadsensing-Pumpe ausgebildete Versorgungspumpe 18 ein, dass deren Pumpendruck und -förderstrom an den Bedarf der Steuerungsvorrichtung automatisch angepasst wird. Mithin ist für die Druckversorgung der Gesamtvorrichtung die Loadsensing-Pumpe 18 ausschließlich eingesetzt, die wiederum zur Ansteuerung ihres Schwenkwinkels an die Steuerleitung LS für das hydraulische Betätigen des Wege-Schieberventils 23 angeschlossen ist.Each of the two
Von der Steuerleitung LS geht über einen Knotenpunkt 59 ein Leitungsabschnitt 61 ab, der zu einem hydraulisch betätigbaren Stellglied 62 zur Verschiebung eines Schieberkolbens 63 des Wege-Schieberventils 23 in eine der möglichen Verfahrrichtungen führt. Alternativ zu dieser Verschiebemöglichkeit mittels des hydraulisch betätigbaren Stellgliedes 62 in diese eine Richtung ist der Schieberkolben 63 mittels eines Magnet-Betätigungssystems 64 in die dieser Richtung entgegengesetzten Richtung verschiebbar in einem zugeordneten Ventilgehäuse 65 (
Das Magnet-Betätigungssystem 64 weist einen "drückend wirkenden" Elektromagneten 71 auf, dessen Anker 72 innerhalb eines mit einem Polkern 73 einteilig ausgestalteten Polrohres 74 axial verschiebbar geführt ist. Zur Verschiebung des Ankers 72 ist eine nicht näher dargestellte Spule 75 bei radialer Umfassung desselben außerhalb des Polrohres 74 vorgesehen, die bestrombar ist, so dass ein durch die Bestromung sich hieraus ergebendes Magnetfeld den Anker 72 in Richtung auf den Polkern 73, in Blickrichtung auf die
Der Spindeltrieb 66 weist ein am Ende 80 der Buchse 65 eingeschraubtes Spindelgehäuse 82 auf, innerhalb dessen eine Spindel 83 durch eine Drehbewegung ihrerseits axial verlagerbar ist, die dazu eine Gewindepaarung 84 mit dem Spindelgehäuse 82 aufweist. Zur axialen Festlegung der Spindel 83 ist eine Kontermutter 85 auf einen außen überstehenden Bereich 86 der Spindel 83 aufgeschraubt und gegen das Spindelgehäuse 82 angezogen. Innerhalb der Spindel 83 nimmt eine in die auf den Schieberkolben 63 weisende Richtung ausmündende Sacklochbohrung 87 die Druckfeder 68 auf, die sich einerseits im Sacklochgrund 88 und andererseits am Boden 89 eines Stellbolzens 91 abstützt, dessen Axialverschiebung innerhalb der Sacklochbohrung 87 mittels eines in einer Innenringnut 92 der Sacklochbohrung 87 eingesetzten Sprengringes 93 axial begrenzt ist. Der Stellbolzen 91 stützt sich ferner auf seiner von der Druckfeder 68 abgewandten Seite mit dessen eigener Stirnfläche 94 an einer ihm zugewandten Stirnfläche 95 am zweiten Ende des Schieberkolbens 63 ab. Da der Schieberkolben 63 am anderen bzw. ersten Ende 79 an der vorgespannten Druckfeder 67 anliegt, erfolgt eine Vorgabe der möglichen Federvorspannungen der beiden Druckfedern 67, 68 mittels des Spindeltriebes 66. Dabei ist die eine Druckfeder 68 Teil des Magnet-Betätigungssystems 64.The
Das Ventilgehäuse 65 weist fünf axial zueinander beabstandete Querbohrungen 96, 97, 98, 99, 100 auf, so dass von dem Ventilgehäuse 65 in folgender Reihenfolge aufeinanderfolgend:
- ein Druckausgleichsanschluss T1,
- ein erster zum stangenseitigen Arbeitsraum führender Arbeitsanschluss A,
- ein Tankanschluss T2,
- ein zweiter zum kolbenseitigen Arbeitsraum führender Arbeitsanschluss B und
- ein Steuerleitungsanschluss port-LS
- a pressure equalization port T1,
- a first working connection A leading to the rod-side working space,
- a tank connection T2,
- a second leading to the piston-side working space working port B and
- a control line port-LS
Korrespondierend zu den Querbohrungen 96 bis 100 weist der Schieberkolben 63 drei axial zueinander beabstandete Steuernuten 103, 104, 105 auf, die infolgedessen mittels zwei Stegen 106, 107 voneinander getrennt sind. Endseitig sind die beiden axial äußeren Steuernuten 103, 105 hingegen von Führungskolben 108, 109 des Schieberkolbens 63 begrenzt.Corresponding to the transverse bores 96 to 100, the
Im Längsschnitt des Gehäuses 63 gesehen, schließt der eine Steg 106 an dessen linker Steuerkante 110 ohne Überdeckung bündig mit dem dem ersten Arbeitsanschluss A nächststehenden Bereich 111 der Querbohrungswand 112 des Tankanschlusses T2 ab. Somit bildet sich zwischen dieser Steuerkante 110 und der Querbohrungswand 112 infolge eines Laufspiels des Schieberkolbens 63 gegenüber dem Gehäuse 65 eine Drosselstelle 113, die den Fluidstrom zwischen dem ersten Arbeitsanschluss A und dem Tankanschluss T2 drosselt. Ebenfalls im Längsschnitt des Gehäuses 65 gesehen schließt der andere Steg 107 an dessen linker Steuerkante 114 ohne Überdeckung bündig mit dem dem Tankanschluss T2 nächststehenden Bereich 115 der Querbohrungswand 116 des zweiten Arbeitsanschlusses B ab. Somit bildet sich zwischen dieser Steuerkante 114 und der Querbohrungswand 116 eine Drosselstelle 117, die den Fluidstrom zwischen dem zweiten Arbeitsanschluss B und dem Tankanschluss T2 drosselt.As seen in the longitudinal section of the
Wie aus einer Zusammenschau von
Der Tankanschluss T2 ist außerhalb des Ventilgehäuses 65 in nicht näher dargestellter Weise mit dem Druckausgleichsanschluss T1 zusammengeführt, so dass Fluid zwischen diesen beiden Anschlüssen T1, T2 ausgetauscht werden kann. Über die dem Druckausgleichsanschluss T1 zugeordnete Querbohrung 96 ist das Fluid in einen Aufnahmeraum 122 für
- die dem Magnet-
Betätigungssystem 64 zugehörigen beweglichen Teile 72, 77; - die
Druckfeder 67; und - das zapfenförmig ausgeführte erste Ende 79 des
Schieberkolbens 63
- the
72, 77 associated with themovable parts solenoid operating system 64; - the
compression spring 67; and - the pin-shaped executed
first end 79 of the spool 63rd
Der dieser fluidischen Aus- und Einleitung zugehörige hydraulische Pfad zwischen der Querbohrung 96 und dem Aufnahmeraum 122 bzw. dem Leckageölraum 126 führt über eine im Durchmesser entsprechend reduzierte Druckausgleichsbohrung 123, welche die Wand des buchsenförmigen Einsatzes 124 durchsetzt und in einen schmalen Ringraum 125 führt, der innenseitig von dem zapfenförmigen ersten Ende 79 des Schieberkolbens 63 begrenzt ist. Der hydraulische Pfad mündet über diesen Ringraum 125 einerseits in den Aufnahmeraum 122 und andererseits in den Leckageölraum 126 aus. Damit kann bei Volumenänderungen der beiden Räume 122, 126 infolge von Verlagerungen des Schieberkolbens 63 Fluid zwischen den beiden Räumen 122, 126 ausgetauscht werden. Am Druckausgleichsanschluss T1 wird dabei über die Druckausgleichsbohrung 123 ein Druckausgleich gegenüber dem am Versorgungstank 22 anliegenden atmosphärischen Druck ermöglicht.The fluidic discharge and initiation associated hydraulic path between the
Gemäß der Darstellung nach der
Das Wege-Schieberventil 23 weist neben der Neutralstellung 69 und der Schwimmstellung 118 noch die Sperrstellung 28 auf, welche folgend anhand der
Im Folgenden werden die wichtigsten Funktionen der Steuerungsvorrichtung insbesondere anhand der
Wird das Wegeventil 16 mittels eines der beiden Elektromagneten 41, 42 in eine der beiden gezeigten Schaltendstellungen 38, 39 verschoben, so wird der Differentialkolben 31 infolge der Druckbeaufschlagung des jeweiligen einen Arbeitsraumes 20, 21 und Druckentlastung des jeweiligen anderen Arbeitsraumes 21, 20 eingefahren oder ausgefahren. Da ein Teil des Versorgungsdruckes über den jeweiligen Nebenpfad 53, 54 auf die Eingangsseite des Wechselventils 23 geführt ist, hält der von diesem über die Steuerleitung LS und den Leitungsabschnitt 61 auf die Stirnfläche 95 des Schieberkolbens 63 geführte Steuerdruck das Wege-Schieberventil 23 in der Sperrstellung 28, solange der als Differentialkolben 29 ausgeführte Arbeitskolben vom Wegeventil 16 angesteuert eingefahren oder ausgefahren wird.If the
Bei diesen Arbeitshüben des Arbeitskolbens 29 vermag das Magnet-Betätigungssystem 64 nicht das Wege-Schieberventil 23 in die als Schaltendstellung ausgeführte Schwimmstellung 118 oder die Neutralstellung 28 zu verfahren, da die maximal vom Magnet-Betätigungssystem 64 auf den Schieberkolben 63 einleitbare Kraft kleiner ist, als die Kraft infolge des an der relativ großen Stirnfläche 95 anstehenden Steuerdruckes. Infolgedessen ist in der Sperrstellung 28 des Wege-Schieberventils 23 die Heben- und Senkenfunktion ohne Androsselung durch das Wegeventil 16 ausschließlich veranlasst. Ein unerwünschtes schnelles Absenken der Last 14 mittels Druckausleitung über die beiden Drosselstellen 113, 117 wird ebenso sicher ausgeschlossen, wie eine Druckausleitung in der Schwimmstellung 118 des Wege-Schieberventils 23. Sobald jedoch das Wegeventil 16 bei unbetätigten Elektromagneten 41, 42 infolge der beidseitig anstehenden Federkraft in dessen Sperr-Mittenstellung 37 geschaltet wird, steht kein Druck mehr an der Steuerleitung LS an, so dass das Wege-Schieberventil 23 federkraftbetätigt in die Neutralstellung 69 zurückkommt. Mithin erfolgt in dieser Neutralstellung 69 des Wege-Schieberventils 23 die Ablaufdrosselung für die Senkenfunktion des Arbeitszylinders 12 bei gesperrtem Wegeventil 16.In these working strokes of the working
Infolge des Fortfalls des am Schieberkolben 63 anstehenden Steuerdruckes kann bei entsprechender Bestromung der Spule 75 des Magnet-Betätigungssystems 64 der Schieberkolben 63 in die von der linken Endschaltstellung gebildete Schwimmstellung 118 gebracht werden. Dabei wird das unter Druck stehende Fluid aus den beiden Arbeitsräumen 20, 21 des Arbeitszylinders 12 ungedrosselt zusammengeführt und über den gemeinsamen Tankanschluss T2 zum Versorgungstank 22 zurückgeführt. Nach dem Abbau des Druckes folgt der Differentialkolben 29 in den Grenzen seiner Endanschläge allen auf die Kolbenstange 31 von außen eingeleiteten Axialkräften, wobei gegebenenfalls noch drucklos in den Arbeitsräumen 20, 21 vorhandenes Restfluid bei entsprechender passiver Verschiebung des Differentialkolbens 29 zum Versorgungstank 22 ausgeleitet wird.Due to the omission of the pending on the
Claims (10)
- A control device for a fluidically actuatable power cylinder (12) with at least one lifting and lowering function, of which at least the lowering function can be operated by a way slide valve (23) which has at least two fluid connection points at which the power cylinder (12) is connected fluidically with its working spaces (20, 21), wherein, in at least one neutral position (69), the way slide valve (23) connects the two working spaces (20, 21) of the power cylinder (12) to one another at a predeterminable partial current supply and in so doing simultaneously produces a fluidic connection to a tank or return port of the way slide valve (23), wherein the partial current supply is predetermined by means of two energy stores (67, 68) acting in opposite directions on the sliding piston (63) of the way slide valve (23), characterised in that at least one of the energy stores (67, 68) can be set.
- The control device according to claim 1, characterised in that energy stores are provided in the form of pressure springs (67, 68).
- The control device according to claim 2, characterised in that the possible spring pre-tensionings of the two pressure springs (67, 68) can be set by means of a spindle operation (66), wherein the one pressure spring (68) is part of a magnet actuation system (64).
- The control device according to claim 3, characterised in that the way slide valve (23) can be brought into a further valve position by means of the magnet actuation system (64), which valve position makes possible a type of floating position (118) for the connected fluidic power cylinder (12).
- The control device according to claim 4, characterised in that, in addition to the neutral position (69) and the floating position (118), the way slide valve (23) also has a locked position (28).
- The control device according to one of claims 3 to 5, characterised in that it also has a way valve (16) wherein, in addition to the magnet actuation system (64), the sliding piston (63) of the way slide valve (23) can also be operated via a control pressure, in particular a load sensing pressure, from a control line (LS) which can be supplied, by the way valve (16), with fluid predeterminable pressure.
- The control device according to claim 6, characterised in that it also has a two-way valve (26), wherein the control line (LS) is connected to the two-way valve (26), which valve passes on the respectively higher input pressure to the control line (LS), and that the two-way valve (26) is connected to the tank outlet side (60) of the way valve (16).
- The control device according to claim 7, characterised in that, in the locked position (28) of the way slide valve (23), the lifting and lowering function is prompted exclusively by the way valve (16) without throttling, that, in the neutral position (69) of the way slide valve (23), the throttle draining takes place at least for the lowering function of the power cylinder when the way valve (16) is blocked.
- The control device according to one of claims 6 to 8, characterised in that it also has a load sensing pump (18) which is connected to the control line (LS) for the way slide valve (23) to control its swing angle.
- The control device according to one of claims 6 to 9, characterised in that the way slide valve (23) is a 3/3-way slide valve and that the way valve (16) is formed from a 4/3-way valve.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014012117.8A DE102014012117A1 (en) | 2014-08-12 | 2014-08-12 | Control device for a fluid-actuated working cylinder with at least one lifting and lowering function |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2985470A1 EP2985470A1 (en) | 2016-02-17 |
EP2985470B1 true EP2985470B1 (en) | 2018-12-19 |
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ID=53717859
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15002101.2A Active EP2985470B1 (en) | 2014-08-12 | 2015-07-15 | Control device for a fluid operated work cylinder with at least one lifting and lowering function |
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EP (1) | EP2985470B1 (en) |
DE (1) | DE102014012117A1 (en) |
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CN105757027B (en) * | 2016-04-22 | 2018-06-15 | 青神格林维尔流体动力控制技术有限公司 | A kind of plug-in system integration block of automatic start-stop formula hydraulic station |
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JP2514915B2 (en) * | 1989-03-08 | 1996-07-10 | 油谷重工株式会社 | Floor circuit for construction machine boom |
JPH06128983A (en) * | 1992-10-14 | 1994-05-10 | Kubota Corp | Dozer device for service car |
DE19504886C2 (en) * | 1995-02-14 | 1999-01-07 | Mannesmann Rexroth Ag | Adjustable pressure valve |
DE19957952A1 (en) * | 1999-12-02 | 2001-06-07 | Mannesmann Rexroth Ag | Hydraulic directional control valve for load-independent control of a hydraulic consumer, especially of a mobile machine |
DE10340505B4 (en) * | 2003-09-03 | 2005-12-15 | Sauer-Danfoss Aps | Valve arrangement for controlling a hydraulic drive |
US8434516B2 (en) * | 2006-04-24 | 2013-05-07 | Parker-Hannifin Corporation | Three position solenoid valve |
DE102013014673A1 (en) | 2013-09-04 | 2015-03-05 | Hydac Fluidtechnik Gmbh | Load-holding valve |
-
2014
- 2014-08-12 DE DE102014012117.8A patent/DE102014012117A1/en not_active Withdrawn
-
2015
- 2015-07-15 EP EP15002101.2A patent/EP2985470B1/en active Active
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EP2985470A1 (en) | 2016-02-17 |
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