EP1290351B1 - Hydraulische steuereinrichtung - Google Patents
Hydraulische steuereinrichtung Download PDFInfo
- Publication number
- EP1290351B1 EP1290351B1 EP01981923A EP01981923A EP1290351B1 EP 1290351 B1 EP1290351 B1 EP 1290351B1 EP 01981923 A EP01981923 A EP 01981923A EP 01981923 A EP01981923 A EP 01981923A EP 1290351 B1 EP1290351 B1 EP 1290351B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control
- pressure
- control device
- longitudinal bore
- slide
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
- F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
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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
- F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
- F15B2013/006—Modular components with multiple uses, e.g. kits for either normally-open or normally-closed valves, interchangeable or reprogrammable manifolds
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/5109—Convertible
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/87169—Supply and exhaust
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/87169—Supply and exhaust
- Y10T137/87177—With bypass
- Y10T137/87185—Controlled by supply or exhaust valve
Definitions
- the invention is based on a hydraulic Control device for load pressure independent control of a double acting motor according to the in the preamble of Claim 1 specified genus.
- From DE 19 44 822 A1 is a hydraulic Control device for load pressure independent control of a known double-acting engine, in which a pressure compensator upstream of that formed on the spool Orifice plate is switched.
- a pressure compensator upstream of that formed on the spool Orifice plate is switched.
- This directional valve with the Orifice plate upstream pressure compensator is Throttle slide in the closing direction from the pressure upstream of the Orifice plate on the control slide and in the opening direction from Pressure downstream of the orifice plate, i.e. plus the load pressure acted upon by the force of a spring.
- the pressure compensator holds thus the pressure difference across the measuring throttle on the directional valve constant even with different load pressure and therefore also the associated flow, so that the on the directional valve set working speed is kept constant.
- Such a directional valve is also called LS (Load Sensing) Valve called primary individual pressure compensator, one Control independent of load pressure allowed.
- LS Load Sensing
- a disadvantage of this control device is that it has none supply-dependent oil flow distribution enables. Become with such directional valves, multiple motors in parallel operation controlled at the same time, so the motor with the lowest load pressure supplied with a pressure medium flow, while the rest of the volume flow to the others Motors is headed. This changes with the load pressure Ratio of the distribution of the volume flows, which is not here remains constant. This can happen especially when there is a shortage cause the function of the least stressed Motors is maintained while a heavily loaded, parallel one actuated motor stops, which in many Use cases is not desirable.
- Such a LS directional control valve builds relatively complex and expensive, its Housing is specially equipped for this type and its Components such as housings, flange patterns and sliders only for this LS directional control valve with primary individual pressure compensator is suitable is.
- Such a hydraulic control device is also for load pressure compensated control of a double acting Motors known from DE 36 34 728 A1, two of which Directional control valves for parallel actuation of the assigned Motors from a common variable displacement pump with pressure medium are supplied, the controller with a control line a shuttle valve chain with the maximum load pressure of the two motors is applied.
- the pressure compensator used for load pressure compensation downstream of a metering orifice on the control slide
- the Pressure compensator also used for direction control Piston sections of the control spool is connected upstream.
- the Throttle valve in the downstream pressure compensator is in Opening direction from the pressure downstream of the orifice plate and in Closing direction of the highest load pressure and the Control pressure difference applied by the control spring.
- EP 0 877 169 A2 is a hydraulic one Control device for load pressure independent control of a double-acting motor known with such LC directional valves for oil flow distribution in the event of undersupply works and for this purpose secondary individual pressure compensators having. Furthermore, this directional valve points between Control spool and pressure compensator an additional Check valve on, with the higher one Security requirements can be met.
- This too Directional control valve has a housing that is only for one LC type is suitable and not with an LS directional control valve Primary individual pressure compensator can be used.
- the hydraulic control device load pressure independent control of a double acting Motors with the characterizing features of claim 1 on the other hand the advantage that with it both valves in Manufacture LS and LC technology with the same housing let by just another throttle valve for the Pressure compensator is installed.
- An LS directional control valve can thus be used with primary individual pressure compensator for load-independent control with the same housing manufacture like an LC directional valve Secondary individual pressure compensator for the oil flow distribution at Undersupply.
- the flange patterns remain on the housing and the control spool in the housing is the same.
- FIG. 1 shows a longitudinal section through a hydraulic control device with an LS directional control valve and primary individual pressure compensator in a simplified representation
- Figure 2 as a detail a shuttle valve from a Control circuit according to II-II in Figure 1
- Figure 3 is a schematic Representation of a control block for two double-acting Motors with two control devices in LS technology
- Figure 4 shows a longitudinal section through a hydraulic Control device with an LC directional valve and combined Simplified representation of the secondary individual pressure compensator
- FIG. 5 shows a schematic illustration of a control block for two double-acting engines with two Control devices in LC technology according to FIG. 4.
- Figure 1 shows a longitudinal section through a hydraulic Control device 10 in LS technology for load pressure independent Control of a double-acting engine.
- the Control device 10 are the actual directional valve 11 in Load sensing (LS) - execution as well as the assigned Pressure compensator 12 in a version as Primary individual pressure compensator in a common housing 13 arranged.
- LS Load sensing
- the housing 13 has one between the two end faces continuous longitudinal bore 14, in the by annular Extensions trained a total of seven chambers 15 to 21 , of which the five adjacent chambers 15 to 19 serve to control the direction of the pressure medium flow, while the two outer chambers 20, 21 one Measuring aperture 22 are assigned, which of Speed control of the engine is used.
- the five adjacent chambers 15 to 19 serve the middle one Chamber as inlet chamber 17, while those lying next to it Chambers a first motor chamber 16 and a second Form motor chamber 18 with a motor connection 23rd or 24 are connected.
- Beside everyone Motor chamber 16, 18 is a return chamber 15 or 19, which are not shown in detail are connected to a return port in the housing 13.
- 21 is used in addition to the first orifice chamber 20 located in the second return chamber 19 as the outlet-side orifice chamber and the other as inlet-side, second orifice chamber 21.
- a spool 25 is tight and slidably guided.
- the control slide 25 is by annular grooves divided into six piston sections 27 to 32.
- the three adjacent piston sections 27, 28, 29 are with Control edges equipped and serve the direction control.
- An adjoining fourth piston section 30, which in the drawn neutral position of the spool 25 in the outlet-side measuring orifice chamber 20 is used all to relieve a control circuit.
- the one about it subsequent fifth piston section 31 is part of the Measuring aperture 22 and determines with its control edges Deflection of the control spool in both working positions the size of the volume flow to the motor and thus its speed.
- the outer sixth piston section 32 protrudes from the longitudinal bore 14 so that a attack actuator not shown can.
- Control slide 25 with the first piston section 27 in one double-acting return device 33, the type of which is known per se and which the spool in its Neutral position 34 centered, out of which he in two Working positions 35 and 36 can be deflected. Furthermore, the Control slide 25 to a fourth switching position 37, which as Free position is executed.
- FIG. 1 also shows, are in the housing 13 below the first longitudinal bore 14 has a blind hole-like bore 39 and a second longitudinal bore 41 arranged underneath, which all run parallel to the first longitudinal bore 14.
- the Blind hole 39 is inside Check valve 42 with its spherical closing member 43 on.
- there is the second one set off several times Longitudinal bore 41 between the first, located on the operator side End face 38 and the return device 33, second end face 40 of the housing 13 and takes the inside Primary individual pressure compensator 12.
- the outlet-side measuring orifice chamber 20 in substantially perpendicular to the spool 25 itself extending extension 45 which is the second Longitudinal bore 41 intersects.
- a circulation chamber 46 in the end near the slide opens the blind hole-like bore 38, while the circulation chamber 46 with its from the spool 25th opposite end penetrates the second longitudinal bore 41.
- a Ring web 47 On this forms one between the extension 45 and the Circulation chamber 46 extending wall of the housing 13 a Ring web 47, the first on both sides of the housing Control edge 48 in the extension 45 and a second Control edge 49 has in the circulation chamber 46.
- the second flows Longitudinal bore 41 at three axially spaced apart Make a first (51), second (52) or third Control pressure opening (53).
- the inlet channel 55 runs between the two Flange surfaces of the housing 13 and stands with the inlet, second orifice chamber 21 in connection.
- the channel 54 with its control pressure opening 51 lies in a portion of the housing 13 that is between the extension 45 and the operator-side end face 38. It is the distance of the first control pressure opening 51 from the first End face 38 chosen essentially the same size as that Distance of the third control pressure opening 53 from it assigned second end face.
- the third Control pressure opening 53 is part of a Y ' designated control line 57, via which a maximum Load pressure of a control circuit in the second longitudinal bore 41 is feasible.
- the third control pressure opening 53 is in accordingly in a second expanded section 58, which corresponds to the first expanded section 56.
- In the area of the second longitudinal bore 41 between the an inner is located in both enlarged sections 56, 58 Section 59, in which the second control pressure port 52 in the second longitudinal bore 41 opens.
- the second control pressure port 52 is at a short distance from the circulation chamber 46.
- the second control pressure opening 52 is for tapping the maximum load pressure of the connected motor.
- Shuttle valve 61 and control pressure channel 63 form parts of a known Control pressure circuit 64, in a manner known per se the maximum load pressure selected via shuttle valve chains and is used for load sensing control.
- the second continuous longitudinal bore is in the housing 13 41 closed to the outside by sealing plug 65, which in Two types are available, namely as sealing plug 66 and Shut-off plug 67.
- sealing plug 65 in Two types are available, namely as sealing plug 66 and Shut-off plug 67.
- the sealing plug 66 in the first expanded section 56 screwed in and serves at the same time as a stop for a throttle slide 68 Primary individual pressure compensator 12.
- the one in the second extended section 58 screwed shut-off plugs 67 protrudes with a collar 69 into the inner section 59 the second longitudinal bore 41 so that it is the third Control pressure opening 53 overlaps and thus hydraulically shuts off.
- Sealing plug 66 and shut-off plug 67 are formed together with the second longitudinal bore 41 so that the two plugs 65 also interchanged can be arranged in the second longitudinal bore 41.
- FIG. 1 also shows, the second Longitudinal bore 41 between the two plugs of the Throttle slide 68 slidably guided.
- the throttle slide 68 has a control edge 72 on a first piston section 71 on with the first control edge 48 fixed to the housing Ring web 47 works together.
- the first piston section 71 has a measuring surface 73 facing the sealing plug 66 which of the throttle slide 68 over the first Control pressure opening 51 from the pressure in the inlet channel 55 is applied.
- the throttle slide 68 is a compression spring 75th acted upon, which is arranged in a spring chamber 76 and the throttle slide 68 with its stop pin 77 holds against the sealing plug 66 in a starting position.
- the spring chamber 76 is inside the Throttle slide 68 extending bores 78 with the pressure in the extension 45, ie with the pressure downstream of the orifice 22, applied in the opening direction.
- the outlet-side orifice chamber 20 is in this way via a transverse channel 79 with the inlet chamber 17 in Connection, wherein in this transverse channel 79 in succession Pressure compensator 12 and the check valve 42 are switched.
- the throttle slide 68 is so downstream of the Measuring aperture 22, but is on its measuring surface 73 from Inlet pressure is applied so that it is in an LS directional control valve 11 assume the function of a primary individual pressure compensator can.
- FIG. 3 shows a schematic representation of a Control block in which, in addition to the first control device 10 a similar, second control device 62 are flanged together so that at least two are double Acting motors can be operated in parallel.
- the Control devices 11, 62 are between one Connection plate 81 and an end plate 82 arranged and connected in parallel to the continuous inlet channel 55.
- the inlet channel 55 is one Pressure medium supply unit 83 supplied with pressure medium, the maximum load pressure via the control circuit 64 is returned.
- the shuttle valves 61 form in both Control devices 10, 62 a valve chain, via which the maximum load pressure selected and forwarded or a relief of the control circuit 64th he follows.
- FIG. 3 there are components with the same function as indicated in Figure 1, so that the interconnection of the Control pressure ports 51, 52 and 53 and the function of Shut-off plug 67 becomes recognizable.
- control device 10 is as follows explained, the basic function of such LS directional control valves is assumed to be known per se.
- Both identical to each other, connected in parallel Control devices 10, 62 is the respective one Primary individual pressure compensator 12 of the orifice 22 each downstream and is also upstream from the directional control edges in the directional control valve 11.
- the throttle valve 68 so designed and arranged and is by the Control pressures applied so that the function of a Primary individual pressure compensator is reached. This is how the pressure works from the inlet channel 55 and thus upstream from the metering orifice 22 via the channel 54 and the first control pressure opening 51 the measuring surface 73 of the throttle slide 68 in closing Direction.
- the pressure downstream of the orifice 22 in the Extension 45 is on the holes 78 in Throttle slide 68 guided into the spring chamber 76, where it together with the spring 75, the throttle slide 68 in opening direction.
- the shuttle valve 61 the pressure is compared between the pressure Y1 im Spring chamber 76 and the pressure Y2 from the neighboring Control device 62.
- the one in the control pressure circuit 64 The selected, highest load pressure becomes pump 83 on the one hand and on the other hand passed into the control line 57.
- This Control line 57 is in each control device 10 or 62 shut off by the stopper 67, the respective collar 69 sealing against the spring space 76 takes over.
- the sealing plug 66 acts on the opposite side as a stop for the throttle slide 68.
- control device 10 If the control device 10 is operated by itself and deflected into one of the working positions 35 or 36, so a load pressure independent control of the connected motor.
- the one from the Pressure medium supply unit 83 via the inlet channel 55 incoming volume flow then flows over the controlled one Orifice plate 22 and the downstream primary pressure compensator and the check valve 43 into the inlet chamber 17 and further back to the engine or from the engine to the return.
- the fourth controls Piston section 30 the connection to the second return chamber 19 so that there is no oil loss to the return.
- the control edge 72 on the first Piston section 71 with the first control edge fixed to the housing 48 works together.
- the opening of the measuring throttle 22 in the extension 45 can build up pressure over the Build up bores 78 also in the spring chamber 76 and load the throttle slide 68 in the opening direction. at one flowing over the transverse channel 79 to the engine Volume flow thus holds the pressure compensator 12 the pressure drop constant via the measuring orifice 22 in a manner known per se, so that the speed of the motor is proportional to Deflection of the control slide 25 and thereby independent of Load pressure fluctuations is controlled.
- the check valve 42 in the transverse channel 79 also provides for any Faults for a safe holding of the load.
- both control devices 10, 62 become simultaneous actuated, so prevent the inlet pressure Primary individual pressure compensators 12 a mutual Influencing at different consumer pressures in the Parallel operation as long as the volume flow is sufficiently large from the pressure medium supply unit 83 is provided.
- there is an undersupply Volume flow this can become known per se Disadvantages, with the function of the lowest loaded engine is maintained while it becomes a A motor with high pressure comes to a standstill, which comes in many applications is not desired.
- FIG. 4 now shows the second embodiment of FIG Invention a third control device 90, which acts as an LC directional valve 91 for oil flow distribution in the event of undersupply is executed and for this purpose with a Secondary individual pressure compensator 92 works.
- This third Control device 90 differs from the first Control device 10 according to Figure 1 as follows, wherein for same components same reference numerals are used.
- this third control device 90 with the exception of another throttle valve 93 same parts as in the first control device 10 are used, in particular the housing 13 with its Control slide 25, the check valve 42 and the Shuttle valve 61 according to Figure 2 and also the two Plug 65.
- the stopper 67 which is also a stop for the throttle slide 93 serves, the first one is hydraulically blocked Control pressure opening 51.
- the sealing plug allows 66, that now the third control pressure opening 53 with the Spring chamber 76 is connected.
- the second throttle valve 93 for the Secondary individual pressure compensator 92 now has a first Piston section 94 has a control edge 95 which is connected to the second Control edge 49 fixed to the housing cooperates.
- the Measuring surface 73 on the same side of the piston section 94 as the control edge 95 is formed and is thus from the pressure acted upon in the extension 45.
- a second Piston section 96 is the throttle valve 93 in the range of inner portion 59 of the second longitudinal bore 41 sliding guided and hydraulically separates the one with the third Control pressure opening 53 connected spring chamber 76 from the second control pressure port 52.
- This second Control pressure opening 52 is an annular groove 97 in the Throttle slide 93 constantly with the circulation chamber 46 connected.
- the first piston section 94 of the Throttle valve 93 arranged a notch 98, over which in Starting position of the throttle slide 93, the circulation chamber 46 constantly to the extension 45 and thus to the second Return chamber 19 is relieved.
- FIG. 5 shows in a manner corresponding to FIG. 3 in schematic representation of a control block in which in addition the third control device 90 a similar, second Control device 100 are flanged together so that at least two double-acting motors can be operated in parallel are.
- the connection plate 81, the end plate 82 and the Pressure medium supply unit 83 are the same as in FIG. 3.
- FIG. 4 in connection with FIG to achieve an LC directional valve with Secondary individual pressure compensator the location of the Control pressure taps 51, 52, 53 in the housing 13 have not changed and only changed the throttle valve 93 itself.
- the secondary pressure compensator 92 now acts on the measuring surface 73 Pressure of the extension 45 and thus the pressure downstream of the orifice plate 22.
- the spring chamber 76 acts the highest load pressure Y '. This tap of the Load pressure signal comes from the circulation chamber 46, via the Ring groove 97 in the throttle valve 93, the second Control pressure port 52 and the shuttle valve 61, from where that Load pressure signal also in the control line 57 and thus for third control pressure opening 53 can reach.
- the third control device 90 is in the neutral position the second control pressure port 52 via the notch 98 and the Control slide 25 relieved to the second return chamber 19.
- the shut-off plug 67 blocks the one not required Control pressure in front of the orifice 22 hydraulically by Bund 69 blocked the connection to extension 45.
- the operation of the third control device 90 is as follows explained, the basic function of a such LC directional valve provided as known per se becomes.
- the third control device 90 becomes by itself actuated, and in one of the working positions 35 or 36 deflected, so a load pressure independent control of the connected motor.
- the Secondary pressure compensator 92 keeps the pressure drop across Measuring aperture 22 constant so that the speed of the engine controlled proportional to the deflection of the control slide 25 becomes.
- Both control devices 90 and 100 become parallel actuated, there is a supply-dependent Oil flow sharing, also known as social Behavior is called.
- the highest one is on one of the motors occurring load pressure on the spring side 76 of all secondary pressure compensators 92 of the control devices 90 and 100 created.
- the throttle slide 93 both pressure compensators 92 so that at their respective Measuring aperture 22 facing end face 73 also different loads on the motors always the same pressure prevails, so that the orifice plates 22 in proportion constant amounts of pressure medium flow through each other become.
- it is one Valve arrangement for dividing the pump flow into individual, partial flows flowing to each motor, whereby also at different load on the engines Division ratio remains constant and thus the desired Speed is maintained.
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Description
Claims (17)
- Hydraulische Steuereinrichtung (10, 90) zur lastdruckunabhängigen Steuerung eines doppelt wirkenden Motors mit einem Wegeventile (11, 91), dessen Gehäuse (13) in einer Längsbohrung (14) einen Steuerschieber (25) aufnimmt, der zur Steuerung von Richtung und Geschwindigkeit des Motors dienende Kolbenabschnitte (27-32) aufweist und mit einem den Kolbenabschnitten (27-29) für die Richtungssteuerung vorgeschalteten Querkanal (79), in den eine Zwei-Wege-Druckwaage (12, 92) geschaltet ist, deren DruckwaageDrosselschieber (68, 93) von einer Feder (75) entgegen einer Differenzkraft aus zwei Steuerdrücken beaufschlagbar ist, wobei der Drosselschieber (68, 93) in einer zweiten Längsbohrung (41) angeordnet ist, die stirnseitig durch mindestens einen Verschlußstopfen (65) nach außen absperrbar ist, dadurch gekennzeichnet, daß die Steuereinrichtung (10, 90) bei gleichbleibendem Gehäuse (13) durch Austausch der Druckwaage-Drosselschieber (68, 93) von einem Wegeventil (11) mit Primärindividualdruckwaage (12) für lastdruckunabhängige Steuerung auf ein Wegeventil (91) mit Sekundärindividualdruckwaage (92) für eine Ölstromaufteilung bei Unterversorgung umstellbar ist.
- Hydraulische Steuereinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die den Drosselschieber (68, 93) aufnehmende zweite Längsbohrung (41) im Gehäuse (13) durchgehend ausgebildet ist und stirnseitig von zwei Verschlußstopfen (65) absperrbar ist, von denen einer als Dichtstopfen (66) und der andere als Absperrstopfen (67) ausgeführt sind.
- Hydraulische Steuereinrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Absperrstopfen (67) und der Dichtstopfen (66) gegenseitig vertauscht in der zweiten Längsbohrung (41) befestigbar sind.
- Hydraulische Steuereinrichtung nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß in der zweiten Längsbohrung (41) axial verteilt an drei Stellen Steuerdrucköffnungen (51, 52, 53) angeordnet sind, wovon die beiden außenliegenden Steuerdrucköffnungen (51, 53) von dem Absperrstopfen (67) hydraulisch absperrbar sind.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der als Meßblende (22) für die Geschwindigkeitssteuerung dienende Kolbenabschnitt (31) am Steuerschieber (25) über den gehäuseseitigen Querkanal (79) mit dem davon getrennt angeordneten Kolbenabschnitt (28) für die Richtungssteuerung am Steuerschieber (25) verbunden ist, wobei die der Meßblende (22) zugeordneten Meßblendenkammern (20, 21) in der ersten Längsbohrung (14) seitlich neben den fünf Arbeitskammern (15 bis 19) für die Richtungssteuerung im Gehäuse (13) angeordnet sind.
- Hydraulische Steuereinrichtung nach Anspruch 5, dadurch gekennzeichnet, daß die stromabwärts liegende Meßblendenkammer (20) eine sich etwa senkrecht zum Kolbenschieber (25) erstreckende Verlängerung (45) hat, die im wesentlichen parallel zu einer Umlaufkammer (46) verläuft und daß die Verlängerung (45) und die Umlaufkammer (46) die zweite Längsbohrung (41) durchdringen, während die stromaufwärts liegende Meßblendenkammer (21) mit einem Zulaufkanal (55) Verbindung hat und über einen Kanal (54) in die zweite Längsbohrung (41) ragt zur Bildung einer ersten Steuerdrucköffnung (51).
- Hydraulische Steuereinrichtung nach Anspruch 6, dadurch gekennzeichnet, daß in einem inneren Abschnitt (59) der zweiten Längsbohrung (41) eine zweite Steuerdrucköffnung (52) mündet, die mit einem Wechselventil (61) eines Steuerdruckkreises (64) in Verbindung steht, wobei insbesondere die zweite Steuerdrucköffnung (52) neben der Umlaufkammer (46) angeordnet ist.
- Hydraulische Steuereinrichtung nach Anspruch 7, dadurch gekennzeichnet, daß zwischen der zweiten Steuerdrucköffnung (52) und einem stirnseitigen Gehäuseende (40) eine dritte Steuerdrucköffnung (53) in die zweite Längsbohrung (41) mündet.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 4 oder 8, dadurch gekennzeichnet, daß die erste und dritte Steuerdrucköffnung (51, 53) jeweils in einen aufgeweiteten Abschnitt (56, 58) der zweiten Längsbohrung (41) münden und ihre jeweiligen Abstände von den zugeordneten Stirnseiten (38, 40) des Gehäuses (13) im wesentlichen gleich groß sind.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 6 bis 8 oder 9, falls von 8 abhängig, dadurch gekennzeichnet, daß die im Gehäuse (13) zwischen Umlaufkammer (46) und ablaufseitiger Meßblendenkammer (20) liegende Wand in der zweiten Längsbohrung (41) einen Ringsteg (47) bildet, der auf beiden Seiten die gehäuseseitigen Steuerkanten (48, 49) für die Druckwaage-Schieber (68, 93) bildet.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß das Gehäuse zwischen den zwei parallelen Längsbohrungen (14, 41) für den Steuerschieber (25) und den Drosselschieber (68, 93) eine dritte Bohrung (39) aufweist, die alle in einer Ebene liegen und von denen die dritte, mittlere Bohrung (39) ein Rückschlagventil (42) aufnimmt.
- Hydraulische Steuereinrichtung nach Ansprüche 6 und 11, dadurch gekennzeichnet, daß die mittlere Bohrung (39) sacklochartig ausgebildet ist und mit ihrem inneren Ende in die im wesentlichen senkrecht zur Längsachse des Steuerschiebers (25) verlaufende Umlaufkammer (46) ragt, welche die zweite Längsbohrung (41) durchdringt.
- Hydraulische Steuereinrichtung nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, daß der Steuerschieber (25) als Vollschieber ohne Verbindungsleitungen für Arbeitsoder Steuerdruckmittel in seinem Inneren ausgeführt ist.
- Hydraulische Steuereinrichtung nach Anspruch 6, dadurch gekennzeichnet, daß zur Ausbildung einer Primärindividualdruckwaage (12) die zweite Längsbohrung (41) einen Drosselschieber (68) aufnimmt, der auf seiner von einem Federraum (76) abgewandten Meßfläche (73) über die erste Steuerdrucköffnung (51) vom Druck im Zulauf (55) beaufschlagbar ist und der im Federraum (76) über Bohrungen (78) im Drosselschieber (68) vom Druck stromabwärts der Meßblende (22) sowie der Kraft einer Feder (75) beaufschlagbar ist und daß die Steuerkante (72) des Drosselschiebers (68) mit der in der ablaufseitigen Meßblendenkammer (20) liegenden, gehäusefesten Steuerkante (48) zusammenarbeitet.
- Hydraulische Steuereinrichtung nach Ansprüche 2 und 14, und nach Anspruch 4 oder 8 dadurch gekennzeichnet, daß die zweite, den Drosselschieber (68) aufnehmende Längsbohrung (41) an der bedienseitig gelegenen Stirnseite (38) vom Dichtstopfen (65) und auf der anderen Stirnseite (40) vom Absperrstopfen (67) verschlossen ist, der zugleich die dritte Steuerdrucköffnung (53) von der zweiten Steuerdrucköffnung (52) absperrt.
- Hydraulische Steuereinrichtung nach Anspruch 4 und 6, oder nach Anspruch 8, dadurch gekennzeichnet, daß zur Ausbildung einer Sekundärindividualdruckwaage (92) die zweite Längsbohrung (41) einen Drosselschieber (93) aufnimmt, der auf seiner zum Federraum (76) entgegengesetzt liegenden Meßfläche (73) vom Druck in der stromabwärts liegenden Meßblendenkammer (20) beaufschlagbar ist und der im Federraum (76) über die dritte Steuerdrucköffnung (53) vom Lastdruck und der Kraft der Feder (75) beaufschlagbar ist und daß die Steuerkante (95) des Drosselschiebers (93) mit der in der Umlaufkammer (46) liegenden, gehäusefesten Steuerkante (49) zusammenarbeitet.
- Hydraulische Steuereinrichtung nach Ansprüche 2 und 16, dadurch gekennzeichnet, daß die zweite, den Drosselschieber (93) aufnehmende Längsbohrung (41) an der bedienseitig gelegenen Stirnseite (38) vom Absperrstopfen (67) verschlossen ist, der die erste Steuerdrucköffnung (51) von der ablaufseitigen Meßblendenkammer (20) trennt, während die dritte Steuerdrucköffnung (53) mit dem Federraum (76) verbunden ist, welcher vom Dichtstopfen (66) in der anderen Stirnseite (40) verschlossen ist und daß der Drosselschieber (93) die zweite Steuerdrucköffnung (52) von der dritten Steuerdrucköffnung (53) absperrt und über eine Ringnut (97) im Drosselschieber (93) stets mit der Umlaufkammer (46) in Verbindung hält.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10027382 | 2000-06-02 | ||
DE10027382A DE10027382A1 (de) | 2000-06-02 | 2000-06-02 | Hydraulische Steuereinrichtung |
PCT/DE2001/001274 WO2001092729A1 (de) | 2000-06-02 | 2001-03-29 | Hydraulische steuereinrichtung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1290351A1 EP1290351A1 (de) | 2003-03-12 |
EP1290351B1 true EP1290351B1 (de) | 2004-02-25 |
Family
ID=7644465
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01981923A Expired - Lifetime EP1290351B1 (de) | 2000-06-02 | 2001-03-29 | Hydraulische steuereinrichtung |
Country Status (5)
Country | Link |
---|---|
US (1) | US6874526B2 (de) |
EP (1) | EP1290351B1 (de) |
JP (1) | JP2003535274A (de) |
DE (2) | DE10027382A1 (de) |
WO (1) | WO2001092729A1 (de) |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003091576A1 (de) * | 2002-04-26 | 2003-11-06 | Bosch Rexroth Ag | Ls-wegeventilanordnung |
DE10245836B4 (de) * | 2002-04-26 | 2013-03-14 | Bosch Rexroth Aktiengesellschaft | LS-Wegeventilanordnung |
DE10342037A1 (de) | 2003-09-11 | 2005-04-07 | Bosch Rexroth Ag | Steueranordnung und Verfahren zur Druckmittelversorgung von zumindest zwei hydraulischen Verbrauchern |
US7380491B2 (en) * | 2004-01-07 | 2008-06-03 | Bosch Rexroth Ag | Flow valve and flow distributor comprising several flow valves |
WO2006048900A1 (en) * | 2004-11-08 | 2006-05-11 | Duplomatic Oleodinamica S.P.A. | Load sensing directional hydraulic valve |
DE102006060326B4 (de) * | 2006-12-20 | 2008-11-27 | Sauer-Danfoss Aps | Hydraulische Ventilanordnung |
US7905089B2 (en) * | 2007-09-13 | 2011-03-15 | Caterpillar Inc. | Actuator control system implementing adaptive flow control |
ITBS20080025A1 (it) * | 2008-02-07 | 2009-08-08 | Camozzi S P A | Dispositivo valvolare con regolatore di pressione |
JP6338428B2 (ja) * | 2014-04-11 | 2018-06-06 | Kyb株式会社 | バルブ構造 |
CN109611403B (zh) * | 2019-01-23 | 2023-08-15 | 洛阳理工学院 | 一种具有减振功能的溢流型液压平衡阀 |
USD902969S1 (en) * | 2019-04-29 | 2020-11-24 | The Boeing Company | Hydraulic manifold for semi-levered gear actuator |
USD900896S1 (en) * | 2019-05-09 | 2020-11-03 | The Boeing Company | Supply boss for a hydraulic manifold for actuator control with dual solenoids |
USD900897S1 (en) * | 2019-05-09 | 2020-11-03 | The Boeing Company | Return boss for a hydraulic manifold for actuator control with dual solenoids |
USD900899S1 (en) * | 2019-05-09 | 2020-11-03 | The Boeing Company | Flow passage contours for a hydraulic manifold for actuator control with dual solenoids |
USD900898S1 (en) * | 2019-05-09 | 2020-11-03 | The Boeing Company | Supply port boss and return port boss for a hydraulic manifold for actuator control with dual solenoids |
USD900894S1 (en) * | 2019-05-09 | 2020-11-03 | The Boeing Company | Hydraulic manifold for actuator control with dual solenoids |
USD900895S1 (en) * | 2019-05-09 | 2020-11-03 | The Boeing Company | Mounting pads for a routing box on a hydraulic manifold for actuator control with dual solenoids |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ZA695984B (en) | 1968-09-06 | 1971-03-31 | Borg Warner | Control circuit |
US4176521A (en) | 1976-12-06 | 1979-12-04 | Tadeusz Budzich | Load responsive fluid control valves |
US4519419A (en) | 1982-06-15 | 1985-05-28 | Commercial Shearing, Inc. | Hydraulic valves |
DE3603811C2 (de) | 1986-02-07 | 1995-12-21 | Bosch Gmbh Robert | Hydraulisches Wegeventil |
DE3634728A1 (de) | 1986-10-11 | 1988-04-21 | Rexroth Mannesmann Gmbh | Ventilanordnung zum lastunabhaengigen steuern mehrerer gleichzeitig betaetigter hydraulischer verbraucher |
DE19719228A1 (de) | 1997-05-07 | 1998-11-12 | Bosch Gmbh Robert | Hydraulische Steuereinrichtung zur lastdruckunabhängigen Steuerung eines doppeltwirkenden Motors |
-
2000
- 2000-06-02 DE DE10027382A patent/DE10027382A1/de not_active Withdrawn
-
2001
- 2001-03-29 EP EP01981923A patent/EP1290351B1/de not_active Expired - Lifetime
- 2001-03-29 JP JP2002500108A patent/JP2003535274A/ja active Pending
- 2001-03-29 DE DE50101561T patent/DE50101561D1/de not_active Expired - Lifetime
- 2001-03-29 US US10/297,215 patent/US6874526B2/en not_active Expired - Fee Related
- 2001-03-29 WO PCT/DE2001/001274 patent/WO2001092729A1/de active IP Right Grant
Also Published As
Publication number | Publication date |
---|---|
DE10027382A1 (de) | 2001-12-06 |
WO2001092729A1 (de) | 2001-12-06 |
DE50101561D1 (de) | 2004-04-01 |
US6874526B2 (en) | 2005-04-05 |
US20040099316A1 (en) | 2004-05-27 |
JP2003535274A (ja) | 2003-11-25 |
EP1290351A1 (de) | 2003-03-12 |
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