EP2430319A1 - Dispositif de soupape hydraulique - Google Patents

Dispositif de soupape hydraulique

Info

Publication number
EP2430319A1
EP2430319A1 EP10717055A EP10717055A EP2430319A1 EP 2430319 A1 EP2430319 A1 EP 2430319A1 EP 10717055 A EP10717055 A EP 10717055A EP 10717055 A EP10717055 A EP 10717055A EP 2430319 A1 EP2430319 A1 EP 2430319A1
Authority
EP
European Patent Office
Prior art keywords
load
connection
consumer
control device
hydraulic 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.)
Granted
Application number
EP10717055A
Other languages
German (de)
English (en)
Other versions
EP2430319B1 (fr
Inventor
Winfried RÜB
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 Filtertechnik GmbH
Original Assignee
Hydac Fluidtechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP2430319A1 publication Critical patent/EP2430319A1/fr
Application granted granted Critical
Publication of EP2430319B1 publication Critical patent/EP2430319B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7761—Electrically actuated valve

Definitions

  • the invention relates to a hydraulic valve device with a Fluidan- circuit arrangement, comprising at least one pressure supply port P, a return port R, - a Se Erasmussloadsensing-LS, two control terminals P ⁇ and P'B and two Nutzan say A, B, to the at least one consumer with his fluid-carrying work spaces is connected and with a movable control device for at least partial driving of terminals of the fluid connection arrangement.
  • DE 10 2005 033 222 AI discloses a LU DV valve assembly in which a directional control valve forms a Zulaufmeßblende, which is followed by an individual dual pressure balance.
  • a LUDV control is considered a special case of a load sensing control in which the highest load pressure of the hydraulic load is reported to a variable displacement pump and this is controlled so that there is a pump pressure related to the pump performance by a certain pressure difference above the load pressure.
  • a hydraulic consumer is driven in the form of a hydraulic working or consumer cylinder, which is connected to two load terminals of the control arrangement. To my- set a rapid traverse the two pressure chambers of the consumer can be connected to each other and with a pressure medium source.
  • this connection of the two consumer connections takes place via a pressure medium flow path in which a check valve is arranged.
  • a check valve is arranged.
  • the connection of the other consumer connection to the pressure medium source and / or the first-mentioned consumer connection is possible only at rapid traverse via the pressure fluid flow path and the check valve.
  • this structural measure means that a flow of pressure medium from a piston rod-side annular space to a bottom-side cylinder space is only permitted in principle, as long as the pressure in the latter is less than or approximately equal to the pressure on the piston rod side.
  • EP 1 647 719 A2 A comparable solution to DE 10 2005 033 222 A1 is also shown by EP 1 647 719 A2, which relates to a regeneration valve device with an independent, separate regeneration valve, which responds when the consumer cylinder is extended, in order thus to form a fluid connection from the bottom side to produce the ring side of the consumer cylinder, wherein both said pressure chambers of the consumer cylinder are then connected to the return port R to counteract any acceleration pressure or to avoid that the cylinder is not slowed down by high loads or even stopped in rapid traverse.
  • said regeneration valve corresponding space is created in the valve housing. Also, the known regeneration valve builds complicated, which should lead to increased manufacturing costs.
  • EP 1 184 576 B1 describes a valve device for controlling a consumer, in particular in the form of a so-called mowing head for a consumer also usable in forestry full mower, wherein a pressure limit of the load applied to the respective consumer of the mowing head load pressure is made possible by a control piston or a movable control device of a hydraulic valve assembly when a limit load pressure is exceeded in a pressure limiting position can be brought in the the load pressure leading consumer terminal is connected to a tank port and the load pressure continues to act on this consumer port in the flow direction on the control piston.
  • a pressure limit of the load applied to the respective consumer of the mowing head load pressure is made possible by a control piston or a movable control device of a hydraulic valve assembly when a limit load pressure is exceeded in a pressure limiting position can be brought in the the load pressure leading consumer terminal is connected to a tank port and the load pressure continues to act on this consumer port in the flow direction on the control piston.
  • DE 603 04 663 T2 again describes a hydraulic valve arrangement with a supply connection arrangement which has a high-pressure connection P and a low-pressure connection T, a working connection arrangement which has two working or useful connections A, B, which in turn can be connected to a hydraulic consumer.
  • a directional valve and a compensation valve arranged between the directional valve and the supply connection arrangement P, T, the pressure output of which is connected to a pressure input of the directional valve.
  • the compensation valve has a discharge outlet, which is connectable to a pressure outlet and has a movable from an initial position in opposite directions valve element in the form of a slide, the line on one side of the pressure in the load sensing and the force of a spring and on the opposite side is acted upon by the pressure at the pressure outlet.
  • Valve element in one direction this performs a pressure control function and when moving in the opposite direction a pressure relief function true.
  • the spool has a longitudinal channel which is connected via a transverse bore to the pressure outlet and terminates in a first pressure chamber.
  • the longitudinal channel in turn goes beyond the transverse bore and leads via a closable opening to a second Pressure chamber, in which a relief pressure prevails.
  • the invention has for its object to provide in a cost effective and space-saving manner a functionally reliable hydraulic valve assembly, which avoids an acceleration pressure when switching from power stroke in a rapid traverse and allows monitoring of the load pressure.
  • the control device can be adjusted by a means for measuring the load pressure with the measurement at the same time in position, it is possible that in a rapid traverse position of the control device when a maximum pressure is exceeded, the control device in a Krafthteils is recycled. This is done smoothly, since it is provided according to the invention that a valve opening cross-section between a feed line and a working connection is not changed during the transition from power stroke to rapid traverse position. It is further provided, when switching, to connect the return flow from an assignable working space of the hydraulic consumer to a feed channel in the form of one of the utility connections.
  • the force on the means for measuring the load pressure also decreases and the movable control device assumes a proportional intermediate position between the power stroke and the rapid traverse.
  • the means for measuring the load pressure is a measuring cylinder with volumetric flask
  • the first working space is fluid leading connected to the Sekti- onsloadsensing port and pressurized in rapid and in the power stroke and the piston rod in a control room of the control housing of the movable control device protrudes.
  • the measuring piston is arranged to be axially movable relative to the control slide and a longitudinal channel in the control slide connects the load-sensing connection to the first working space of the measuring cylinder.
  • the measuring cylinder is an integral part of the spool, which can be moved in a particularly preferred embodiment of a maximum working position also in the rapid traverse position.
  • a control connection of the control slide with a control groove is fluid-conducting connected to one of the useful connections, in particular in the form of a working space of the hydraulic consumer. Furthermore, pocket-like connection channels in the control device extend between a load-signaling connection and another user connection for the consumer.
  • the moveable control device is preferably provided with further load-sensing and load-sensing connections, which connect a load-signaling connection to a load-sensing connection in pairs and connect at least part of the connections of the fluid connection arrangement to one another in a fluid-conducting manner as a function of the displacement position of the control device.
  • the consumer is formed from a consumer or working cylinder with an annular space and a piston space as fluid-conducting working rooms. It is further provided that in a change from power stroke to rapid traverse then the annular space of the consumer cylinder is connected to the Nutzanschluß A as a feed line.
  • the hydraulic valve device can also be used in other hydraulic drives, such as traction motors of electrohydraulic vehicles and more.
  • the pertinent paired hydraulic motor assembly then has fluid-carrying working spaces and a the annular space of the working cylinder corresponding working space of the respective hydraulic motor is then to connect to the supply line via the Nutzanschluß A with this and the other fluid-carrying spaces of the respective hydraulic motor are comparable to the piston chamber of said consumer cylinder as working space head for.
  • FIGURE shows a partial longitudinal section through the valve device according to the invention.
  • valve assembly 1 with a designated as a whole with 10 fluid connection assembly, which has, inter alia, a pressure supply port P, a return port R, a section load sensing LS, two control terminals P ⁇ and P'B and two Nutzan say A, B. ,
  • the fluid ports LS, P ⁇ , R, P and P'B, A and B are housed in a common control housing 12, wherein seen in the figure lower end of the control housing 12 is provided with a known pressure compensator 14 which the terminals LS , P ⁇ , R, P and P'B is upstream and controls them.
  • the pressure compensator 14 enables a so-called pressure medium quantity cut by means of a pressure, not shown.
  • a spring chamber 16 of the pressure compensator 14 in order to cut off the inflow quantity, for instance in the case of a fluidic consumer connected to the service connections A, B, at regular intervals in the form of a hydraulic consumer cylinder 4, in order to be able to overload the consumer avoid.
  • a moveable control device 18 of the valve arrangement 1 is actuated by two pilot valves 20, 22 which, for the sake of simplicity, are shown in the figure only insofar as their respectively assignable housing connections in the control housing 12 are indicated.
  • the pertinent control via pilot valves is common, so that will not be discussed in more detail here at this point.
  • the respective pilot valve 20,22 accommodated in a assignable housing 24,26 which are flanged on both sides of the center part of the control housing 12 and in addition to the usual ports To and PST on the bottom side connections have for the purpose of applying two counteracting control pressures XA and XB.
  • the pump control pressure is applied to the respective pilot valve 20, 22 via the connection PST and, furthermore, the pertinent pilot valves are connected to the named tank connection line To.
  • Said control device 18 has a horizontally displaceable control slide 28, viewed in the direction of the figure, which is shown in the figure in its floating position deflected to the left.
  • the neutral position is effected by two counteracting spring accumulators in the form of compression springs 30, which are integrated in a respective spring chamber through which pressure medium XA, XB flows in the pilot housings 24, 26.
  • the control device 18 with spool 28 is provided with load-sensing terminals 32,34 and load-sensing terminals 36,38, which are interconnected in pairs carrying fluid.
  • the first load-indicating connection 32 is connected in a fluid-conducting manner to the second load-sensing connection 38.
  • the and the second load-sensing connection 34 is in fluid-carrying connection with the first load-sensing connection 36.
  • the said connections are introduced as radial transverse bores in the control slide 18 and depending on the displacement position of the control slide 28 in each opening or blocking connection with the extent assignable ren Connections of the fluid connection assembly 10 as shown in the figure.
  • the spool 28 has along its outer periphery at least two longitudinally oriented, pocket-like control channels 48,50, which open in the neutral position of the spool 28 respectively in the Nutzanschluß A and the Nutzanschluß B. Further, in the control channel 48, a dividing partition 58 is retracted, at least in the area of the utility connection A, wherein in the figure shown floating position of the spool 28 of the Nutzanschluß A in fluid industrialder connection with even further in the outer periphery of the spool 28 introduced fluid carrying pockets 56 which in the position shown in a the spool 28 encompassing annular channel, which in turn is connected to the return port R.
  • the designated control channel 50 forms with its opening cross-section in the direction of the utility B the so-called. Orifice of the valve device and seen in the direction of the figure is left of the partition 58 of the further part of the pocket-like control channel 48 for the backflow into the feed P ⁇ in Rapidly responsible.
  • connecting channels 40, 42 arranged within the control slide 28 are used.
  • the one connecting channel 40 is designed as a so-called center channel which, in the neutral position of the control device 18 shown in the figure, covers the area between the sectional load sensing terminal LS and the user terminal B with its axial length.
  • the walking center channel 40 begins in the direction of the figure seen on the left side of the spool 28 and extends along the center axis to the bore of the measuring cylinder 5.
  • the connecting channel 42 is provided in parallel as a ring longitudinal channel, in the neutral position of the control device 18 with its axial length covers at least the area between the control terminal P ⁇ and user port A.
  • the middle channel 40 is delimited at the edge by an insert sleeve 44, which limits the annular longitudinal channel 42 at least partially along its outer circumference in a predeterminable central region with the inner wall of the control slide 28.
  • the annular longitudinal channel 42 may also be formed from a plurality of concentric with the central channel 40 individual channels (not shown in detail).
  • the axial position of the insert sleeve 44 extends according to the figure between the first load-sensing connection 32 and a narrowed offset point between the first load-sensing connection 36 and the second load-sensing connection 38 at the height of the return connection R.
  • a rapid traverse position for the connected hydraulic consumer 4 is achieved in that the spool valve 28 is moved to the right beyond the so-called lifting position as viewed in the direction of the figure, and the so-called floating position for the consumer can be determined by a type Overlift of the spool 28 on the so-called.
  • Lower position in the direction seen on the figure reach to the left. Starting from the neutral position shown in the figure, therefore, the spool 28 is first moved to the right first in the lifting and then in the rapid traverse position for the consumer or moved in the opposite direction, starting from the neutral position to the left over the lowering position in the floating position.
  • the control channel 50 comes with increasing movement of the spool 28 in the direction of lifting position in overlap with the control terminal P'B, which leads to an increase in the relevant Meßblendenqueritess.
  • a means 2 designed as a measuring cylinder 5 for measuring the load pressure in the useful connection B is present.
  • the measuring cylinder 5 has a measuring piston 6 and a piston rod 8, which is reduced in diameter relative to the measuring piston 6. Further, the piston rod 8 extends through at its right free end a bottom 9 of the spool 28 and the free right end of the piston rod 8 opens into the spring chamber, which is connected to the pilot control port XB.
  • the load-sensing connection 38 which opens into the return connection R in the center or neutral position of the control spool 28, is transferred on the opposite connection side into a longitudinal channel 15, which is in fluid-conducting connection with the center channel 40.
  • the longitudinal channel 15 terminates in a first working space 7 of the measuring cylinder 5, which is filled in the illustration shown by the measuring piston 6, which also closes the right channel end free cross section of the longitudinal channel 15.
  • the spool 28 moves the spool 28 as seen in the direction of the figure to the right, the spool takes the measuring cylinder 5 also to the right with the result that the load sensing port 38 in register with the Ring channel comes to which the user port B is connected, so that in the pertinent right position of the load-sensing 38 serves as Loadsen- sing connection LSB for the pending in the Nutzan gleich B load pressure, wherein the pertinent Loadsensing réelle LSB turn on the longitudinal channel 15 at the measuring cylinder 5 is passed. Consequently, the load-sensing connection 38 is continued via the longitudinal channel 15 as a section load-sensing connection LSB and opens into the first working space 7 of said measuring cylinder 5.
  • the measuring cylinder 5 is moved to the right, at least until the piston rod 8 abuts with its right free end 11 against the end wall 13 of the spring chamber of the pilot housing 26. This results in a counterforce on the spool 28 in the direction of a transition from a EiI- gangwolf in the lifting position. In this way, at an excessive load on the piston rod unit of the consumer cylinder 4 a jerk-free transition into a load application to a load-operatively connected to the load cylinder 4 load-bearing hoist reach and a maximum lifting force generating position for the control slide 28.
  • the load pressure decreases in Power stroke in turn, then decreases the pressure force acting on the volumetric flask 6 via the load sensing connection LSB, and the spool 28 assumes a proportional intermediate position between power stroke and rapid traverse, wherein a throttled connection of the annular space 3 of the consumer cylinder 4 to the rear - running connection R is created.
  • a throttle or non-return valve arrangement is preferably provided.
  • the free cross section of the valve opening 50 between see feed line P and working port B is not changed during the transition from the power stroke to rapid traverse.
  • the reflux of the ring side 3 of the consumer 4 no longer switched to T, but connected to the feed channel in the form of the user port A.
  • a monitoring of the load pressure with said measuring means 2 and a load-dependent changeover from rapid traverse to power stroke is performed. If the cylinder piston unit of the consumer 4 is driven in rapid traverse and the load pressure rises to the maximum permitted pressure, the measuring cylinder arrangement 5 in the control spool 28 switches it back into the power stroke. Then the maximum lifting force is available again and due to the connection of the return flow from the ring side 3 into the feed channel, there is no unintentional switching shock.
  • the consumer or working cylinder 4 may also be another hydraulic consumer, for example in the form of a hydraulic motor for a traction drive, be it in a vehicle, be it in a lifting device, such as an elevator, and the like.
  • a fluid-carrying working space of the consumer in correspondence to the annular space 3 of the consumer cylinder 4 when switching the control device 18 in the sense of a change from power stroke to rapid traverse to the user port A or B to connect as an effective feed line.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un dispositif de soupape hydraulique (1) pourvu d'un système de raccordement fluidique (10), comprenant une pluralité de points de raccordement fluidique qui peuvent être commandés au moins en partie au moyen d'un dispositif de commande (18). Du fait que le dispositif de commande (18) peut être déplacé par un moyen (2) pour mesurer la pression de charge dans une position de mouvement rapide lors du dépassement d'une pression de charge maximale dans une position de course de puissance et vice-versa et que lors d'une commutation du dispositif de commande (18) dans le sens d'un passage de la course de puissance au mouvement rapide, au moins une chambre de travail conductrice de fluide d'un consommateur (4) est reliée à un des raccordements utiles (A), une transition sans à-coups d'une course de puissance à un mouvement rapide est obtenue et un retour homogène sans à-coups à la course de puissance est possible lorsque survient une situation de surcharge en position de mouvement rapide.
EP20100717055 2009-05-13 2010-04-23 Dispositif de soupape hydraulique Not-in-force EP2430319B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910021103 DE102009021103A1 (de) 2009-05-13 2009-05-13 Hydraulische Ventilvorrichtung
PCT/EP2010/002501 WO2010130334A1 (fr) 2009-05-13 2010-04-23 Dispositif de soupape hydraulique

Publications (2)

Publication Number Publication Date
EP2430319A1 true EP2430319A1 (fr) 2012-03-21
EP2430319B1 EP2430319B1 (fr) 2013-05-29

Family

ID=42342004

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20100717055 Not-in-force EP2430319B1 (fr) 2009-05-13 2010-04-23 Dispositif de soupape hydraulique

Country Status (6)

Country Link
US (1) US20110308642A1 (fr)
EP (1) EP2430319B1 (fr)
JP (1) JP2012526952A (fr)
DE (1) DE102009021103A1 (fr)
DK (1) DK2430319T3 (fr)
WO (1) WO2010130334A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013010390A1 (de) * 2013-06-20 2014-12-24 Hydac Accessories Gmbh Steuervorrichtung für hydraulisch betätigbare Arbeitseinheiten

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2593265B1 (fr) * 1986-01-17 1988-04-22 Rexroth Sigma Distributeur de fluide hydraulique sous pression
DE4234037C2 (de) * 1992-10-09 2001-03-22 Mannesmann Rexroth Ag Ventilanordnung, insbesondere für mobile Arbeitsgeräte
DE19631803B4 (de) * 1996-08-07 2007-08-02 Bosch Rexroth Aktiengesellschaft Hydraulische Steuervorrichtung
DE10041168A1 (de) 2000-08-21 2002-03-07 Mannesmann Rexroth Ag Ventileinrichtung
DE10258517B3 (de) 2002-12-14 2004-06-03 Sauer-Danfoss (Nordborg) A/S Hydraulische Ventilanordnung
KR100611713B1 (ko) 2004-10-14 2006-08-11 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 재생기능을 구비한 유압제어밸브
DE102005033222B4 (de) 2005-07-15 2012-05-16 Bosch Rexroth Aktiengesellschaft LUDV-Ventilanordnung
DE102006007935A1 (de) * 2006-02-21 2007-10-25 Liebherr France Sas Steuervorrichtung und hydraulische Vorsteuerung
DE102007054138A1 (de) * 2007-11-14 2009-05-28 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102007054134A1 (de) * 2007-11-14 2009-05-20 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102007054137A1 (de) * 2007-11-14 2009-05-28 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102008006879A1 (de) * 2008-01-31 2009-08-06 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2010130334A1 *

Also Published As

Publication number Publication date
DK2430319T3 (da) 2013-07-22
EP2430319B1 (fr) 2013-05-29
WO2010130334A1 (fr) 2010-11-18
US20110308642A1 (en) 2011-12-22
JP2012526952A (ja) 2012-11-01
DE102009021103A1 (de) 2010-11-18

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