EP3475585B1 - Valve apparatus for influencing a flow of medium - Google Patents

Valve apparatus for influencing a flow of medium Download PDF

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Publication number
EP3475585B1
EP3475585B1 EP17732747.5A EP17732747A EP3475585B1 EP 3475585 B1 EP3475585 B1 EP 3475585B1 EP 17732747 A EP17732747 A EP 17732747A EP 3475585 B1 EP3475585 B1 EP 3475585B1
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EP
European Patent Office
Prior art keywords
valve
channel
fluid
valve slide
fluid channel
Prior art date
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Application number
EP17732747.5A
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German (de)
French (fr)
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EP3475585A1 (en
Inventor
Sascha Alexander Biwersi
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Hydac Systems and Services GmbH
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Hydac Systems and Services GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B13/026—Pressure compensating valves
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • 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
    • 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
    • F15B2013/008—Throttling member profiles

Definitions

  • the invention relates to a valve device for influencing a media flow between a supply connection to which a pressure supply source can be connected and a pressure connection to which a hydraulic consumer can be connected, with a valve device which has a valve slide which is guided in axial directions of travel within a valve housing and with its opposite end faces at least partially delimit two media chambers within the valve housing and which blocks the connection between the supply and pressure connection in at least one closed position and which releases the relevant connection in at least one of its open positions in which the pressure connection with at least one of the the two media chambers are each connected via a fluid guide, one of which is formed from a fluid channel running in the valve slide, one end of which into the one media chamber and the other At the end it opens into a fluid space in the valve housing which, in the at least one closed position of the valve slide, is separated from the pressure connection and is arranged between the supply and pressure connection.
  • the known valve device also serves to influence a media flow between a supply connection, to which a pressure supply source can be connected, and a pressure connection, to which a hydraulic consumer can be connected, and has a valve device with a valve slide that can be moved longitudinally between end positions in a valve housing.
  • a control device By means of a control device, the pressure at the pressure connection regulated by the valve slide is limited in the direction of one of its end positions from a predetermined displacement of the valve slide, so that the hydraulic consumer connected to the pressure connection can no longer be overloaded.
  • the fluid pressure at the pressure connection advantageously has a constant pressure difference to the supply connection until a maximum permissible pressure is reached.
  • a control line opens into the valve housing, which is preferably part of an LS signal line or signal chain.
  • the control device has a single fluid channel serving as a control channel within the valve slide, which opens out on a control side of the valve slide into a media chamber within the valve housing and which, from a predetermined displacement position of the valve slide, which preferably corresponds to a stop or end position, this Media chamber with another media chamber within the valve housing fluidly connects, to which the control line or the LS signal line is connected.
  • the only control or fluid channel is made up of a system of longitudinal and transverse bores in the valve slide, which must be designed as precisely as possible in terms of their dimensions for performing the control processes, which leads to correspondingly high manufacturing costs. It has also been shown in practice that, due to the relatively narrowly dimensioned free channel cross-sections of the control channel in question, there are problems with the immediate forwarding of the pressure connection pending hydraulic pressure can come to the actual control side of the valve, which leads to pressure losses within the fluid guide and thus to instabilities in the fluid control, which is disadvantageous for the desired constant pressure reduction on the pressure supply side of the valve.
  • the pressure p' cannot be tapped correctly due to the position of the hole in front of the non-return edge, but is increased by the switching edge depending on the volume flow Q and the opening.
  • the invention is therefore based on the object of achieving the objective of maintaining the advantages of the known solution, namely a limitation of the pressure regulated by the valve slide at the pressure or useful connection of the valve, to further improve this so that the Operating behavior is improved within the framework of the scheme while at the same time being cheaper to implement.
  • a pertinent object is achieved by a valve device with the features of claim 1 in its entirety.
  • the other fluid guide has at least one further fluid channel which is separated from the first fluid channel and which at least one end opens into the other media chamber in one of the open positions of the valve slide and which in every displacement position of the valve slide is permanently connected to the pressure connection with its other end, the known one-channel solution described above is replaced by a two-channel solution with shortened fluid paths per channel, with the result that it is on the addressed control side of the valve such high pressure losses cannot occur as instabilities in the fluid control are to be feared.
  • the further fluid channel is permanently connected to the pressure connection of the valve that is to be regulated, so that the regulation processes take place immediately and without pressure losses due to the channel guides otherwise required.
  • the respective further fluid channel is arranged to run parallel to the axial movement directions of the valve slide, so that when an assignable control edge is crossed by means of the valve slide, the fluid guide of the respective further fluid channel is deflected from this parallel direction, preferably by 90 °, learns.
  • the two-channel solution with the additional fluid channel which is permanently connected to the pressure connection in every displacement position of the sliding piston, under pressure, an improved control quality or control quality can be achieved compared to the known single-channel solution, in which the channel during the control process with its Fluid guidance emerges vertically in planes, parallel to the mentioned control edge.
  • At least one control channel connects to one end of the respective further fluid channel, which points in the direction of the other media chamber, which has a changed, in particular reduced channel cross-section compared to the further fluid channel.
  • the channel cross-section starting from the respective further fluid channel, decreases in the direction of the respective control channel at least in the area of the associated control edge, forming a diaphragm with the same.
  • the respective control channel seen in cross section in the direction of the one free end face of the valve slide, which at least partially delimits the other media chamber, tapers conically and opens into this with its end facing the respective assignable fluid channel, forming a step-like fluid guide step .
  • the control channel adjoining the respective fluid channel allows, with a slight change in the fluid direction compared to the parallel alignment at the control edge transversely to the same, a fluid flow path that enables the necessary adjustment processes on the valve slide continuously, largely without obstruction.
  • valve design in such a way that with a fictitious development of a control edge of the valve slide in the area of the at least one control edge in the valve housing in one plane, the total length of the latter is greater than the sum of the individual developments , based on the same plane, of the free openings of one fluid channel running in the valve slide in the region of its respective other end which opens into the fluid space in the valve housing.
  • the respective additional fluid channel is formed from a radial wall distance between the valve slide and valve housing.
  • the radial wall distance between the valve housing and the valve slide is formed by a uniformly extending diameter reduction in the valve slide, based on the diameter of the free end face of the valve slide, in the direction of the other media chamber, this being the case if there is a control channel opens permanently in a fluid-carrying manner into the fluid ring channel formed in this way. If the further fluid channel does not extend over the entire diameter in the outer wall of the valve slide, fine tuning for the control process in the fluid guide can be achieved by selecting this free diameter.
  • a defined control edge geometry can be achieved if, in the valve device according to the invention, it is preferably provided that the control edge running in the valve housing is delimited in the direction of the valve housing by a groove-like recess pointing away from the valve slide.
  • the respective further fluid channel has passed the control edge for the control process, forming a 90 ° deflection for the fluid guide, with the control channel that may be present at this height of the control edge into which such further fluid channel opens at the end.
  • the valve device is preferably designed as a type of individual pressure compensator.
  • a pressure compensator 9 is shown in connection with a metering orifice 12, which in its overall function form a volume flow regulator 14 which has the valve device according to the invention with the valve device 10, the essential components of which are summarized in a frame-like block diagram.
  • a valve housing 18 has a valve bore 20 in which a valve slide 22 which is guided so as to be longitudinally displaceable is arranged.
  • the valve bore 20 is closed at both ends 24, 26 by end screws 28, 30 which each engage in an assignable internal thread 32 of the valve bore 20.
  • Annular sealing elements 34 are provided between the end screws 28, 30 and the valve housing 18.
  • the valve slide 22 is provided for controlling a fluid-carrying connection 36 between at least two fluid connection points 38, 40 received in the valve housing 18, a supply connection 38 and a pressure connection 40.
  • a pressure supply source P ( Fig. 1 ) in the form of a hydraulic pump 41
  • a hydraulic consumer U ( Fig. 1 )
  • a hydraulic working cylinder (not shown)
  • the valve slide 22 has a total of two outwardly projecting control parts 42, 44, of which the first control part 42 has at least one pocket-like recess 46 in the direction of the second control part 42 and the second control part 44 is through a first fluid space 48 as part of the possible fluid-carrying connection 36 from the first control part 42 arranged at a distance.
  • the solution according to the invention with only one control part, for example the control part 42, which, however, has disadvantages in the overall control behavior of the piston-like valve slide 22.
  • the non-actuated state of the valve slide 22 i.e. at zero stroke, in which the valve slide 22 is in the end position on the left in the plane of the drawing ( Fig.
  • the second control part 44 is in contact with a housing inner wall 52 of the valve housing 18 by means of a cylindrical guide part 50.
  • a conical transition part 54 on the control part 44 forms a flow guide for the fluid and causes a ramp-like deflection of the fluid flow from the first fluid space 48 in the direction of the pressure connection 40.
  • the transition part 54 also contributes to the flow force compensation on the valve slide 22.
  • valve slide 22 is guided in the area of the pressure connection 40 in the valve housing 18 through its inner wall 52.
  • a rod part 57 keeping them at a distance.
  • the flow around the valve slide 22 in the area of the second control part 44 is improved, as a result of which the pressure losses within the pressure compensator 9 are reduced.
  • the sealing behavior of the second control part 44 with respect to the housing inner wall 52 is improved by the second fluid chamber 58, since the sealing gap between the valve slide 22 and the housing inner wall 52 can be reduced by introducing the second fluid chamber 58 into the valve slide 22.
  • the two fluid spaces 48, 58 which form axial distances between the first control part 42 and the second control part 44 or between the second control part 44 and the further guide part 56, are formed by groove-like diameter reductions 59 in the valve slide 22.
  • Such diameter reductions 59 are also referred to in technical terms as recesses in the valve slide 22.
  • the valve slide 22 On its one end face 60 on the left in the image plane, the valve slide 22 adjoins a media chamber 62 of variable volume, which is connected to the first fluid chamber 48 in a fluid-carrying manner via a fluid guide 64.
  • the fluid guide 64 is formed by a fluid channel 68 running centrally in the valve slide 22, which with its one longitudinal end 70 into the one media chamber 62 and with its other transverse end 72 via an opening 74 into the first fluid space 48 between the two control parts 42, 44 of the valve slide 22 opens into the valve housing 18.
  • the first fluid space 48 is delimited at the edge by the two control parts 42, 44 of the valve slide 22 and the valve housing 18.
  • the pressure between the supply connection 38 and the pressure connection 40 which is regulated by the valve slide 22 when the valve is open, is passed on via the fluid channel 68 into the one media chamber 62.
  • the fluid pressure prevailing in one media chamber 62 then acts on the valve slide 22 further in the direction of one of its open positions for the purpose of bringing about a fluid connection with an increased flow rate between pressure supply connection 38 and pressure connection 40.
  • the fluid channel 68 in the valve slide 22 has a throttle point 76 in the area of its deflection from the longitudinal to the transverse channel guide.
  • a further throttle point 77 is formed in that the diameter of the fluid channel 68, starting from the other end 72 of the fluid channel 68, widens in a step-like manner towards the one end 70 of the fluid channel 68.
  • the valve slide 22 adjoins another media chamber 80 of variable volume, which in the case of a predetermined opening displacement of the valve slide 22 in the viewing direction Fig. 2 and 3 viewed to the right and therefore in the direction of the other media chamber 80 via another further fluid duct 82 with the pressure connection 40 in a fluid-carrying manner, so that one media chamber 62 can be connected to the other media chamber 80 via the one fluid channel 68 and the further fluid channel 84.
  • the Fig. 3 shows the pertinent fluid-carrying connection between pressure connection 40 and media chamber 80.
  • the end face 78 of the valve slide 22 is supported on one free end of a compression spring 112, the other free end of which is in contact with the locking screw 30 and the other media chamber 80 takes action.
  • the compression spring 112 is also in the zero position of the valve slide 22 with a predefinable preload ( Fig. 2 ) in contact with slide 22.
  • the other fluid guide 82 is formed by the further fluid channel 84, which is in the form of a diameter reduction 86 of the valve slide 22, based on a diameter 88 on the free other end face 78 of the valve slide 22 and limited by the further guide part 56 of the valve slide 22, parallel to the axial directions of travel of the same.
  • the further fluid channel 84 can be formed as at least one groove-shaped diameter reduction 86 in the valve slide 22 or preferably from a radial wall distance 89 between valve slide 22 and valve housing 18 over the entire outer circumference of valve slide 22 in this area.
  • valve housing 18 and valve slide 22 The radial wall distance 89 between valve housing 18 and valve slide 22 is formed by the uniformly extending diameter reduction 86, based on the respective diameter 88 of the other free end face 78 of valve slide 22, in valve slide 22 in the direction of pressure connection 40 as this area.
  • the further, second fluid channel 84 is completely separated from the one, first fluid channel 68 in the sense of a two-channel solution spatially and in terms of the fluid guide concept with two fluid guides 82, 64 that are spatially separated from one another and in each displacement position of the valve slide 22 with its one free end 94, which faces away from the media chamber 80, is permanently connected to the pressure connection 40 in a manner essential to the invention in a fluid-conducting manner.
  • the control edge 90 which is arranged in a stationary manner, then forms, with the movable control edge 114, the diaphragm or control cross section to be regulated between the pressure or consumer connection 40 and the media chamber 80, which is shown in FIG Fig.
  • Fig. 5 in a modified embodiment of the solution after Fig. 4 shown, connects to the other media chamber 80 facing other end 92 of the in Fig. 4 further fluid channel 84 shown and described above, at least one control channel 96, which has a reduced channel cross-section compared to the further fluid channel 84.
  • the respective control channel 96 tapers conically, viewed in cross section, in the direction of the other free end face 78 of the valve slide 22 and, with its end 100 facing the further fluid channel 84, opens into the further fluid channel 84, forming a step-like fluid guide step 102. Looking towards the Fig.
  • the right end of the control channel 86 with its conically reduced cross-section forms a further control edge 115 at the free end of the valve slide 22, which with the control edge 90 of the housing 18 forms a further throttle or diaphragm device for the fluid as soon as the further control edge 115 denies traverses free cross section at the stationary control edge 90, which is the case when the valve slide 22 from its zero position to the opening valve positions Fig. 2 in its regulating positions in the direction of the end or stop position after Fig. 3 moves to the right.
  • the respective control channel 96 opens into the fluid ring channel formed by the radial wall distance in a permanent fluid-carrying manner.
  • a single control channel or a plurality of control channels 96 only one control channel space can be passed through a be formed circumferential diameter reduction with conical cross section in the valve slide 22.
  • a control device in particular designed in the manner of the metering orifice 12, is provided in the fluid-carrying line 104.
  • a corresponding control line 106 in the form of an LS signal line 108 is provided which is connected to valve housing 18 and which opens into the other media chamber 80 .
  • the LS signal line 108 is in turn connected to the hydraulic pump 41 in the form of a variable displacement pump.
  • the swivel angle of the hydraulic pump 41 which also specifies the pressure at the supply connection 38, is regulated as a function of the system pressure in the LS signal line 108.
  • the pressure fed in by the hydraulic pump 41 at the supply connection 38 can be adapted promptly to the requirements of the hydraulic consumer U.
  • fluid can flow out of the other media chamber 80 via an adjustable throttle or diaphragm 110 via the LS signal line 108 into a tank connection or some other return connection R having essentially ambient pressure.
  • the LS signal line 108 also has a comparable throttle or diaphragm 110.
  • a fluid pressure prevailing in the other media chamber 80 acts on the other end face 78 of the valve slide 22 to the left in the direction of the closed position SS, in which the valve slide 22 completely separates the pressure connection 40 from the supply connection 38 at zero stroke.
  • the valve slide 22 is also acted upon on its other end face 78 by the energy store in the form of the compression spring 112.
  • the pressure regulated by the valve slide 22 between the supply connection 38 and the pressure connection 40 from a predeterminable displacement of the valve slide 22 in the direction of the other media chamber 80 can be limited, namely by discharging excess fluid via the control line 106 into the LS signal line 108 from the other media chamber 80 with the interposition of the throttle or diaphragm 99.
  • valve slide 22 When the valve slide 22 is not actuated, i.e. at zero stroke ( Fig. 2 ), in which the valve slide 22 is positioned in the stop position in the direction of one media chamber 62, the second control part 44 is by means of the cylindrical guide part 50 in contact with the housing inner wall 52 of the valve housing 18 in the area between supply connection 38 and pressure connection 40, so that the valve slide 22 is arranged in one of its closed positions SS, in which the latter blocks the fluid-carrying connection 36 between supply connection 38 and pressure connection 40. In this position SS, the further fluid channel 84 and possibly the control channel 96 are covered in a sealing manner by the housing inner wall 52 and the further guide part 56 is in sliding contact with the assignable housing inner wall 52 with its end region facing the other media chamber 80.
  • a fluid pressure present at the supply connection 38 is passed on via the one fluid channel 68 into the one media chamber 62. There it acts on the adjoining end face 60 of the valve slide 22.
  • On the opposite other end face 78 is the valve slide 22 from the load pressure via the LS signal line 108 and the control line 106 and the compression spring 112 is applied.
  • the valve slide 22 moves, starting from the closed position SS, in the direction of the other media chamber 80, so that the valve arrives in one of its open positions.
  • the second control part 44 is brought out of engagement with the housing inner wall 52, so that the fluid-carrying connection 36 between the supply connection 38 and the pressure connection 40 is also increasingly opened.
  • the further fluid-carrying connection 48 is interrupted by closing the first control part 42 on a further closing edge 51 of the housing 18 and at the same time the fluid-carrying connection between the media chambers 62, 80 is established because, if no control channel 96 is provided, the other end 94 of the further fluid channel 84 or, if a control channel 96 is provided, the end of this control channel 96 facing the other media chamber 80, forming a corresponding deflection for the other fluid guide 82, has passed over the control edge 90 in the valve housing 18 which the valve housing 18 has in its housing inner wall 52 and which limits an annular groove-like recess 116 pointing away from the valve slide 22, but protruding in the direction thereof.
  • This further fluid-carrying connection 118 between the media chambers 62, 80 results in a pressure equalization between these media chambers 62, 80.
  • valve slide 22 Under the action of the compression spring 112, the valve slide 22 is again shifted to the left in the direction of its closed position SS as long as there is pressure equalization in the chambers 62, 80.
  • This effect is reinforced by the fact that fluid from the other media chamber 80 is only throttled via the control line 106 in the direction of the LS signal line 108 and possibly in the direction of the return port R or tank port, so can flow very limited.
  • the further fluid channel 84 and possibly the control channel 96 are at least partially covered again by the inner wall 52 of the valve housing 18 and then the other media chamber comes into contact 80 facing end region of the further guide part 56, whereby the fluid-carrying connection between the media chambers 62, 80 is initially throttled and then completely separated with increasing displacement of the valve slide 22 further to the left.
  • an equilibrium position is normally established which advantageously limits the pressure at the pressure connection 40 to a predeterminable maximum value. This means that the hydraulic consumer U can no longer be overloaded.
  • the fluid pressure at the pressure connection 40 advantageously has a constant pressure difference to the supply connection 38 until the maximum permissible pressure is reached.
  • the diaphragm or standard cross-sections 90, 114 and possibly 90, 115 ensure that the pressure P 'in front of the metering diaphragm 12 can be set in a defined manner, regardless of the current fluid demand at the consumer U.
  • valve device that no longer allows pressure fluctuations at the supply connection 38 to pass unattenuated via the pressure compensator 9 and thus effectively prevents any overstressing on the hydraulic consumer U and also advantageously improves the operating behavior within the framework of the control while at the same time being cost-effective.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Multiple-Way Valves (AREA)

Description

Die Erfindung betrifft eine Ventilvorrichtung zum Beeinflussen eines Medienstromes zwischen einem Versorgungsanschluss, an den eine Druckversorgungsquelle anschließbar ist, und einem Druckanschluss, an den ein hydraulischer Verbraucher anschließbar ist, mit einer Ventileinrichtung, die einen Ventilschieber aufweist, der in axialen Verfahrrichtungen innerhalb eines Ventilgehäuses geführt ist und mit seinen gegenüberliegenden Stirnseiten zumindest teilweise zwei Medienkammern innerhalb des Ventilgehäuses begrenzt und der in mindestens einer Schließstellung die Verbindung zwischen dem Versorgungs- und dem Druckanschluss sperrt und der die dahingehende Verbindung in mindestens einer seiner geöffneten Stellungen freigibt, bei denen der Druckanschluss mit zumindest einer der beiden Medienkammern über jeweils eine Fluidführung verbunden ist, von denen eine aus einem im Ventilschieber verlaufenden Fluidkanal gebildet ist, der mit seinem einen Ende in die eine Medienkammer und mit seinem anderen Ende in einen Fluidraum im Ventilgehäuse einmündet, der in der zumindest einen Schließstellung des Ventilschiebers vom Druckanschluss getrennt und zwischen Versorgungs- und Druckanschluss angeordnet ist.The invention relates to a valve device for influencing a media flow between a supply connection to which a pressure supply source can be connected and a pressure connection to which a hydraulic consumer can be connected, with a valve device which has a valve slide which is guided in axial directions of travel within a valve housing and with its opposite end faces at least partially delimit two media chambers within the valve housing and which blocks the connection between the supply and pressure connection in at least one closed position and which releases the relevant connection in at least one of its open positions in which the pressure connection with at least one of the the two media chambers are each connected via a fluid guide, one of which is formed from a fluid channel running in the valve slide, one end of which into the one media chamber and the other At the end it opens into a fluid space in the valve housing which, in the at least one closed position of the valve slide, is separated from the pressure connection and is arranged between the supply and pressure connection.

Durch die Lösung nach den Fig. 3 ff. nebst den zugehörigen Beschreibungsseiten der DE 10 2014 003 086 A1 ist eine gattungsgemäße Ventilvorrichtung bekannt. Die bekannte Ventilvorrichtung dient gleichfalls dem Beeinflussen eines Medienstroms zwischen einem Versorgungsanschluss, an den eine Druckversorgungsquelle anschließbar ist, und einem Druckanschluss, an den ein hydraulischer Verbraucher anschließbar ist, und weist eine Ventileinrichtung mit einem Ventilschieber auf, der in einem Ventilgehäuse zwischen Endstellungen längsverfahrbar geführt ist. Mittels einer Steuereinrichtung wird der durch den Ventilschieber eingeregelte Druck an dem Druckanschluss, ab einer vorgegebenen Verschiebung des Ventilschiebers, in Richtung auf eine seiner Endstellungen zu begrenzt, so dass es nicht mehr zu Überlastungen des am Druckanschluss angeschlossenen hydraulischen Verbrauchers kommen kann. Vorteilhafterweise weist dabei der Fluiddruck am Druckanschluss eine konstante Druckdifferenz zum Versorgungsanschluss auf, bis ein zulässiger maximaler Druck erreicht ist.By solving the Fig. 3 ff. together with the associated description pages of the DE 10 2014 003 086 A1 a generic valve device is known. The known valve device also serves to influence a media flow between a supply connection, to which a pressure supply source can be connected, and a pressure connection, to which a hydraulic consumer can be connected, and has a valve device with a valve slide that can be moved longitudinally between end positions in a valve housing. By means of a control device, the pressure at the pressure connection regulated by the valve slide is limited in the direction of one of its end positions from a predetermined displacement of the valve slide, so that the hydraulic consumer connected to the pressure connection can no longer be overloaded. The fluid pressure at the pressure connection advantageously has a constant pressure difference to the supply connection until a maximum permissible pressure is reached.

Bei einer bevorzugten Ausführungsform der bekannten Ventilvorrichtung mündet in das Ventilgehäuse eine Steuerleitung ein, die bevorzugt Bestandteil einer LS-Signalleitung oder Signalkette ist. Zwecks Ansteuern dieser Steuerleitung weist die Steuereinrichtung einen als Steuerkanal dienenden einzigen Fluidkanal innerhalb des Ventilschiebers auf, der auf einer Steuerseite des Ventilschiebers in eine Medienkammer innerhalb des Ventilgehäuses ausmündet und der ab einer vorgegebenen Verschiebestellung des Ventilschiebers, die vorzugsweise einer Anschlag- oder Endstellung entspricht, diese Medienkammer mit einer weiteren Medienkammer innerhalb des Ventilgehäuses fluidführend verbindet, an die die Steuerleitung respektive die LS-Signalleitung angeschlossen ist.In a preferred embodiment of the known valve device, a control line opens into the valve housing, which is preferably part of an LS signal line or signal chain. In order to control this control line, the control device has a single fluid channel serving as a control channel within the valve slide, which opens out on a control side of the valve slide into a media chamber within the valve housing and which, from a predetermined displacement position of the valve slide, which preferably corresponds to a stop or end position, this Media chamber with another media chamber within the valve housing fluidly connects, to which the control line or the LS signal line is connected.

Bei der bekannten Lösung ist der einzige Steuer- oder Fluidkanal aus einem System von Längs- und Querbohrungen im Ventilschieber aufgebaut, die von ihrer Dimensionierung her zum Durchführen der Ansteuervorgänge möglichst exakt auszubilden sind, was zu entsprechend hohen Herstellkosten führt. Auch hat es sich in der Praxis gezeigt, dass es aufgrund der relativ eng bemessenen freien Kanalquerschnitte des angesprochenen Steuerkanals zu Problemen bei der unmittelbaren Weiterleitung des am Druckanschluss anstehenden Hydraulikdruckes auf die eigentliche Regelseite des Ventils kommen kann, was zu Druckverlusten innerhalb der Fluidführung und mithin zu Instabilitäten bei der Fluidregelung führt, was nachteilig für die erwünschte konstante Druckreduzierung auf der Druckversorgungsseite des Ventils ist. Zur Steigerung des Volumenstroms mit einer Druckteilerschaltung p' nach LS kann der Druck p' durch die Position der Bohrung vor der Rückschlagkante nicht korrekt abgegriffen werden, sondern wird durch die Schaltkante in Abhängigkeit von dem Volumenstrom Q und der Öffnung erhöht.In the known solution, the only control or fluid channel is made up of a system of longitudinal and transverse bores in the valve slide, which must be designed as precisely as possible in terms of their dimensions for performing the control processes, which leads to correspondingly high manufacturing costs. It has also been shown in practice that, due to the relatively narrowly dimensioned free channel cross-sections of the control channel in question, there are problems with the immediate forwarding of the pressure connection pending hydraulic pressure can come to the actual control side of the valve, which leads to pressure losses within the fluid guide and thus to instabilities in the fluid control, which is disadvantageous for the desired constant pressure reduction on the pressure supply side of the valve. To increase the volume flow with a pressure divider circuit p 'to LS, the pressure p' cannot be tapped correctly due to the position of the hole in front of the non-return edge, but is increased by the switching edge depending on the volume flow Q and the opening.

Eine weitere Ventilvorrichtung geht aus der DE 10 2013 014 671 A1 hervor.Another valve device goes from the DE 10 2013 014 671 A1 emerged.

Ausgehend von diesem Stand der Technik liegt daher der Erfindung die Aufgabe zugrunde, unter Beibehalten der Vorteile der bekannten Lösung, nämlich eine Begrenzung des durch den Ventilschieber eingeregelten Drucks an dem Druck- oder Nutzanschluss des Ventils zu erreichen, diese dahingehend weiter zu verbessern, dass das Betriebsverhalten im Rahmen der Regelung bei gleichzeitig kostengünstiger Realisierung verbessert ist.Proceeding from this prior art, the invention is therefore based on the object of achieving the objective of maintaining the advantages of the known solution, namely a limitation of the pressure regulated by the valve slide at the pressure or useful connection of the valve, to further improve this so that the Operating behavior is improved within the framework of the scheme while at the same time being cheaper to implement.

Eine dahingehende Aufgabe löst eine Ventilvorrichtung mit den Merkmalen des Patentanspruchs 1 in seiner Gesamtheit.A pertinent object is achieved by a valve device with the features of claim 1 in its entirety.

Dadurch, dass gemäß dem kennzeichnenden Teil des Patentanspruchs 1 die andere Fluidführung mindestens einen weiteren Fluidkanal aufweist, der von dem ersten Fluidkanal separiert ist und der zumindest in einer der geöffneten Stellungen des Ventilschiebers mit seinem einen Ende in die andere Medienkammer einmündet und der in jeder Verfahrstellung des Ventilschiebers mit seinem anderen Ende permanent an den Druckanschluss angeschlossen ist, ist die vorstehend beschriebene bekannte Ein-Kanallösung durch eine Zwei-Kanallösung mit verkürzten Fluidwegen pro Kanal ersetzt, was zur Folge hat, dass es auf der angesprochenen Regelseite des Ventils nicht zu derart hohen Druckverlusten kommen kann, als das Instabilitäten bei der Fluidregelung zu befürchten wären. Hierzu trägt auch mit bei, dass der weitere Fluidkanal permanent an den einzuregelnden Druckanschluss des Ventils angeschlossen ist, so dass die Einregelvorgänge unmittelbar und ohne Druckverluste, bedingt durch die ansonsten zusätzlich notwendigen Kanalführungen, vonstatten gehen. Dies führt auch insgesamt zu einer verbesserten Energiebilanz im Rahmen der angestrebten Regelvorgänge mit der Ventilvorrichtung und die angesprochenen Instabilitäten aufgrund von übergroßen Druckverlusten sind dergestalt mit Sicherheit vermieden. Trotz der Zwei-Kanalausbildung sind insgesamt die Herstellkosten verringert, da aufgrund der einfacher durchzuführenden Kanalgestaltung und insoweit auch einfacher zu beherrschenden Regel- und Ansteuergeometrien der Herstellaufwand entsprechend verringert ist.In that, according to the characterizing part of claim 1, the other fluid guide has at least one further fluid channel which is separated from the first fluid channel and which at least one end opens into the other media chamber in one of the open positions of the valve slide and which in every displacement position of the valve slide is permanently connected to the pressure connection with its other end, the known one-channel solution described above is replaced by a two-channel solution with shortened fluid paths per channel, with the result that it is on the addressed control side of the valve such high pressure losses cannot occur as instabilities in the fluid control are to be feared. This is also helped by the fact that the further fluid channel is permanently connected to the pressure connection of the valve that is to be regulated, so that the regulation processes take place immediately and without pressure losses due to the channel guides otherwise required. This also leads overall to an improved energy balance within the framework of the desired control processes with the valve device and the mentioned instabilities due to excessive pressure losses are thus definitely avoided. Despite the two-channel design, the overall manufacturing costs are reduced, since the manufacturing effort is correspondingly reduced due to the channel design, which is easier to implement and, in this respect, also easier to master control and control geometries.

Bei einer bevorzugten Ausführungsform der erfindungsgemäßen Ventilvorrichtung ist der jeweils weitere Fluidkanal parallel zu den axialen Verfahrrichtungen des Ventilschiebers verlaufend angeordnet, so dass bei Überfahren einer zuordenbaren Regelkante quer zu derselben mittels des Ventilschiebers die Fluidführung des jeweils weiteren Fluidkanals eine Umlenkung aus dieser Parallelrichtung, vorzugsweise um 90°, erfährt. Dergestalt lässt sich mit der Zwei-Kanallösung mit dem weiteren Fluidkanal, der permanent druckführend mit dem Druckanschluss in jeder Verfahrstellung des Verschiebekolbens in Verbindung steht, eine verbesserte Regelgüte respektive Regelqualität erreichen gegenüber der bekannten Ein-Kanallösung, bei der der Kanal während des Regelvorgangs mit seiner Fluidführung senkrecht in Ebenen, parallel zur angesprochenen Regelkante austritt.In a preferred embodiment of the valve device according to the invention, the respective further fluid channel is arranged to run parallel to the axial movement directions of the valve slide, so that when an assignable control edge is crossed by means of the valve slide, the fluid guide of the respective further fluid channel is deflected from this parallel direction, preferably by 90 °, learns. In this way, with the two-channel solution with the additional fluid channel, which is permanently connected to the pressure connection in every displacement position of the sliding piston, under pressure, an improved control quality or control quality can be achieved compared to the known single-channel solution, in which the channel during the control process with its Fluid guidance emerges vertically in planes, parallel to the mentioned control edge.

Bei einer weiteren bevorzugten Ausführungsform der erfindungsgemäßen Ventilvorrichtung schließt sich an das eine Ende des jeweils weiteren Fluidkanals, das in Richtung der anderen Medienkammer weist, mindestens ein Steuerkanal an, der gegenüber dem weiteren Fluidkanal über einen geänderten, insbesondere verringerten Kanalquerschnitt verfügt. Vorzugsweise ist dabei vorgesehen, dass der Kanalquerschnitt sich, ausgehend vom jeweils weiteren Fluidkanal, in Richtung des jeweiligen Steuerkanals zumindest im Bereich der zuordenbaren Regelkante unter Bildung einer Blende mit derselben verringert. Dergestalt ist mit dem jeweils weiteren Fluidkanal in Funktionsverbindung mit dem jeweils weiteren Steuerkanal erreicht, dass in der Regelposition des Ventils eine Art Druckteilerschaltung erreicht ist, mit der sich der benötigte Regeldruck auf der Druckabgabeseite des Ventils sinnfällig vergrößern lässt. Dies hat so keine Entsprechung im Stand der Technik.In a further preferred embodiment of the valve device according to the invention, at least one control channel connects to one end of the respective further fluid channel, which points in the direction of the other media chamber, which has a changed, in particular reduced channel cross-section compared to the further fluid channel. Preferably it is provided that the channel cross-section, starting from the respective further fluid channel, decreases in the direction of the respective control channel at least in the area of the associated control edge, forming a diaphragm with the same. In this way, with the respective further fluid channel in functional connection with the respective further control channel, a type of pressure divider circuit is achieved in the control position of the valve, with which the required control pressure on the pressure output side of the valve can be increased significantly. This has no equivalent in the prior art.

Hierbei ist besonders bevorzugt vorgesehen, dass der jeweilige Steuerkanal im Querschnitt gesehen in Richtung der einen freien Stirnseite des Ventilschiebers, die zumindest teilweise die andere Medienkammer begrenzt, sich konisch verjüngt und mit seinem dem jeweils zuordenbaren Fluidkanal zugewandten Ende unter Bildung einer absatzartigen Fluidführungsstufe in diesen einmündet. Bei der dahingehenden Anordnung erlaubt der an den jeweiligen Fluidkanal sich anschließende Steuerkanal bei geringer Änderung der Fluidrichtung gegenüber der Parallelausrichtung an der Regelkante quer zu derselben einen Fluidströmungsverlauf, der weitgehend hemmnisfrei kontinuierlich die benötigten Einregelvorgänge am Ventilschieber ermöglicht.Here, it is particularly preferred that the respective control channel, seen in cross section in the direction of the one free end face of the valve slide, which at least partially delimits the other media chamber, tapers conically and opens into this with its end facing the respective assignable fluid channel, forming a step-like fluid guide step . With the pertinent arrangement, the control channel adjoining the respective fluid channel allows, with a slight change in the fluid direction compared to the parallel alignment at the control edge transversely to the same, a fluid flow path that enables the necessary adjustment processes on the valve slide continuously, largely without obstruction.

Für das Einhalten einer besonders hohen Regelgüte hat es sich als vorteilhaft erwiesen, die Ventilgestaltung derart zu konzipieren, dass bei einer fiktiven Abwicklung einer Steuerkante des Ventilschiebers im Bereich der mindestens einen Regelkante im Ventilgehäuse in einer Ebene deren Gesamtlänge größer ist als die Summe der einzelnen Abwicklungen, bezogen auf dieselbe Ebene, der freien Öffnungen des einen im Ventilschieber verlaufenden Fluidkanals im Bereich seines jeweils anderen Endes, das in den Fluidraum im Ventilgehäuse ausmündet.To maintain a particularly high control quality, it has proven to be advantageous to design the valve design in such a way that with a fictitious development of a control edge of the valve slide in the area of the at least one control edge in the valve housing in one plane, the total length of the latter is greater than the sum of the individual developments , based on the same plane, of the free openings of one fluid channel running in the valve slide in the region of its respective other end which opens into the fluid space in the valve housing.

Eine besonders hohe Fertigungsqualität bei geringem Herstellaufwand lässt sich erreichen, wenn der jeweils weitere Fluidkanal aus einem radialen Wandabstand zwischen Ventilschieber und Ventilgehäuse gebildet ist. Besonders bevorzugt zwecks vereinfachter Herstellung ist dabei, dass der radiale Wandabstand zwischen Ventilgehäuse und Ventilschieber durch eine gleichförmig verlaufende Durchmesserreduzierung im Ventilschieber, bezogen auf den Durchmesser der freien Stirnseite des Ventilschiebers, in Richtung der anderen Medienkammer gebildet ist, wobei bei im Bedarfsfall vorhandenem Steuerkanal dieser jeweils in den derart gebildeten Fluidringkanal permanent fluidführend einmündet. Sofern der weitere Fluidkanal sich nicht über den gesamten Durchmesser in der Außenwand des Ventilschiebers erstreckt, kann über die Wahl dieses freien Durchmessers eine Feinabstimmung für den Regelvorgang in der Fluidführung erreicht werden.A particularly high manufacturing quality with little manufacturing effort can be achieved if the respective additional fluid channel is formed from a radial wall distance between the valve slide and valve housing. For the purpose of simplified production, it is particularly preferred that the radial wall distance between the valve housing and the valve slide is formed by a uniformly extending diameter reduction in the valve slide, based on the diameter of the free end face of the valve slide, in the direction of the other media chamber, this being the case if there is a control channel opens permanently in a fluid-carrying manner into the fluid ring channel formed in this way. If the further fluid channel does not extend over the entire diameter in the outer wall of the valve slide, fine tuning for the control process in the fluid guide can be achieved by selecting this free diameter.

Eine definierte Regelkantengeometrie lässt sich erreichen, wenn bei der erfindungsgemäßen Ventilvorrichtung vorzugsweise vorgesehen ist, dass die im Ventilgehäuse verlaufende Regelkante durch einen nutartigen, vom Ventilschieber wegweisenden Rücksprung im Ventilgehäuse in dessen Richtung vorstehend begrenzt ist.A defined control edge geometry can be achieved if, in the valve device according to the invention, it is preferably provided that the control edge running in the valve housing is delimited in the direction of the valve housing by a groove-like recess pointing away from the valve slide.

Bei der Endstellung des Ventilschiebers, insbesondere bei einer vorgesehenen Anschlagstellung in Richtung der anderen Medienkammer, hat für den Regelvorgang der jeweils weitere Fluidkanal unter Bildung einer 90°-Umlenkung für die Fluidführung die Regelkante überfahren, wobei dann der etwaig vorhandene Steuerkanal in dieser Höhe der Regelkante in den derart jeweils weiteren Fluidkanal endseitig ausmündet.In the end position of the valve slide, in particular with a planned stop position in the direction of the other media chamber, the respective further fluid channel has passed the control edge for the control process, forming a 90 ° deflection for the fluid guide, with the control channel that may be present at this height of the control edge into which such further fluid channel opens at the end.

Bevorzugt ist die Ventileinrichtung als eine Art Individualdruckwaage konzipiert.The valve device is preferably designed as a type of individual pressure compensator.

Die Erfindung ist nachfolgend anhand von in den Figuren dargestellten Ausführungsbeispielen näher erläutert. Es zeigen:

Fig. 1
eine hydraulische Symboldarstellung eines Volumenstromreglers mit einer erfindungsgemäßen Ventilvorrichtung;
Fig. 2
einen Längsschnitt durch die Ventilvorrichtung aus Fig. 1 mit einem Ventilschieber in linker Anschlagstellung in Richtung der einen Medienkammer;
Fig. 3
einen Längsschnitt durch die Ventilvorrichtung aus Fig. 1 mit einem Ventilschieber in rechter Anschlagstellung in Richtung der anderen Medienkammer;
Fig. 4
eine vergrößerte Darstellung eines in Fig. 3 mit einem Kreis X umrandeten Bereichs; und
Fig. 5
eine vergrößerte Darstellung des in Fig. 3 mit dem Kreis X umrandeten Bereichs in einer geänderten Ausgestaltung gegenüber der Ausführungsform nach der Fig. 4.
The invention is explained in more detail below with reference to the exemplary embodiments shown in the figures. Show it:
Fig. 1
a hydraulic symbol representation of a volume flow controller with a valve device according to the invention;
Fig. 2
a longitudinal section through the valve device Fig. 1 with a valve slide in the left stop position in the direction of one media chamber;
Fig. 3
a longitudinal section through the valve device Fig. 1 with a valve slide in the right stop position in the direction of the other media chamber;
Fig. 4
an enlarged view of an in Fig. 3 area surrounded by a circle X; and
Fig. 5
an enlarged view of the in Fig. 3 with the circle X bordered area in a modified configuration compared to the embodiment according to FIG Fig. 4 .

In der Fig. 1 ist in Form einer hydraulischen Symboldarstellung eine Druckwaage 9 in Verbindung mit einer Zumessblende 12 gezeigt, die in der Gesamtfunktion einen Volumenstromregler 14 bilden, der die erfindungsgemäße Ventilvorrichtung mit der Ventileinrichtung 10 aufweist, deren wesentliche Komponenten in einer rahmenartigen Blockdarstellung zusammengefasst sind.In the Fig. 1 In the form of a hydraulic symbol representation, a pressure compensator 9 is shown in connection with a metering orifice 12, which in its overall function form a volume flow regulator 14 which has the valve device according to the invention with the valve device 10, the essential components of which are summarized in a frame-like block diagram.

Gemäß den Längsschnittdarstellungen nach den Fig. 2 und 3 weist ein Ventilgehäuse 18 eine Ventilbohrung 20 auf, in der ein längsverfahrbar geführter Ventilschieber 22 angeordnet ist. Die Ventilbohrung 20 ist an beiden Enden 24,26 durch Abschlussschrauben 28,30 verschlossen, die jeweils in ein zuordenbares Innengewinde 32 der Ventilbohrung 20 eingreifen. Zwischen den Abschlussschrauben 28,30 und dem Ventilgehäuse 18 sind jeweils ringförmige Dichtelemente 34 vorgesehen.According to the longitudinal sections according to Fig. 2 and 3 a valve housing 18 has a valve bore 20 in which a valve slide 22 which is guided so as to be longitudinally displaceable is arranged. The valve bore 20 is closed at both ends 24, 26 by end screws 28, 30 which each engage in an assignable internal thread 32 of the valve bore 20. Annular sealing elements 34 are provided between the end screws 28, 30 and the valve housing 18.

Der Ventilschieber 22 ist zum Ansteuern einer fluidführenden Verbindung 36 zwischen mindestens zwei im Ventilgehäuse 18 aufgenommenen Fluid-Anschlussstellen 38,40, einem Versorgungsanschluss 38 und einem Druckanschluss 40, vorgesehen. An den Versorgungsanschluss 38 ist eine Druckversorgungsquelle P (Fig. 1) in Form einer Hydraulikpumpe 41 angeschlossen, und an den Druckanschluss 40 ist ein hydraulischer Verbraucher U (Fig. 1), beispielsweise in Form eines hydraulischen Arbeitszylinders (nicht dargestellt), über die Anschlussstelle P' der Ventileinrichtung 10 anschließbar. Der Ventilschieber 22 weist insgesamt zwei nach außen vorspringende Steuerteile 42, 44 auf, von denen das erste Steuerteil 42 mindestens eine taschenartige Vertiefung 46 in Richtung des zweiten Steuerteils 42 aufweist und das zweite Steuerteil 44 ist durch einen ersten Fluidraum 48 als Teil der möglichen fluidführenden Verbindung 36 vom ersten Steuerteil 42 beabstandet angeordnet. Grundsätzlich besteht die Möglichkeit die erfindungsgemäße Lösung auch nur mit einem Steuerteil, beispielsweise dem Steuerteil 42 zu realisieren, was jedoch Nachteile im Gesamt-Ansteuerverhalten des kolbenartigen Ventilschiebers 22 mit sich bringt. Im unbetätigten Zustand des Ventilschiebers 22, also bei Nullhub, bei dem sich der Ventilschieber 22 in der in der Bildebene linken Endlage (Fig. 2) befindet, ist das zweite Steuerteil 44 mittels eines zylinderförmigen Führungsteils 50 in Anlage mit einer Gehäuseinnenwand 52 des Ventilgehäuses 18. Ein konisch verlaufendes Übergangsteil 54 am Steuerteil 44 bildet dabei eine Strömungsführung für das Fluid und bewirkt eine rampenartige Umlenkung des Fluidstroms von dem ersten Fluidraum 48 in Richtung des Druckanschlusses 40. Das Übergangsteil 54 trägt dabei auch zur Strömungskraftkompensation am Ventilschieber 22 mit bei.The valve slide 22 is provided for controlling a fluid-carrying connection 36 between at least two fluid connection points 38, 40 received in the valve housing 18, a supply connection 38 and a pressure connection 40. At the supply connection 38 is a pressure supply source P ( Fig. 1 ) in the form of a hydraulic pump 41, and a hydraulic consumer U ( Fig. 1 ), for example in the form of a hydraulic working cylinder (not shown), can be connected via the connection point P ′ of the valve device 10. The valve slide 22 has a total of two outwardly projecting control parts 42, 44, of which the first control part 42 has at least one pocket-like recess 46 in the direction of the second control part 42 and the second control part 44 is through a first fluid space 48 as part of the possible fluid-carrying connection 36 from the first control part 42 arranged at a distance. In principle, it is also possible to implement the solution according to the invention with only one control part, for example the control part 42, which, however, has disadvantages in the overall control behavior of the piston-like valve slide 22. In the non-actuated state of the valve slide 22, i.e. at zero stroke, in which the valve slide 22 is in the end position on the left in the plane of the drawing ( Fig. 2 ), the second control part 44 is in contact with a housing inner wall 52 of the valve housing 18 by means of a cylindrical guide part 50. A conical transition part 54 on the control part 44 forms a flow guide for the fluid and causes a ramp-like deflection of the fluid flow from the first fluid space 48 in the direction of the pressure connection 40. The transition part 54 also contributes to the flow force compensation on the valve slide 22.

Mittels eines weiteren Führungsteils 56 ist der Ventilschieber 22 im Bereich des Druckanschlusses 40 im Ventilgehäuse 18 durch dessen Innenwand 52 geführt. Zwischen dem ersten Steuerteil 42 und dem zweiten Steuerteil 44 ist ein diese auf Abstand haltendes Stangenteil 57 angeordnet. Durch einen zweiten Fluidraum 58 zwischen dem zweiten Steuerteil 44 und dem weiteren Führungsteil 56 wird nun die Umströmung des Ventilschiebers 22 im Bereich des zweiten Steuerteils 44 verbessert, wodurch die Druckverluste innerhalb der Druckwaage 9 verringert werden. Weiterhin wird durch den zweiten Fluidraum 58 das Dichtverhalten des zweiten Steuerteils 44 gegenüber der Gehäuseinnenwand 52 verbessert, da der Dichtspalt zwischen Ventilschieber 22 und Gehäuseinnenwand 52 durch das Einbringen des zweiten Fluidraums 58 in den Ventilschieber 22 hinein verkleinert werden kann. Die beiden Fluidräume 48,58, die axiale Abstände zwischen dem ersten Steuerteil 42 und dem zweiten Steuerteil 44 bzw. zwischen dem zweiten Steuerteil 44 und dem weiteren Führungsteil 56 bilden, sind durch nutartig verlaufende Durchmesserreduzierungen 59 im Ventilschieber 22 gebildet. Derartige Durchmesserreduzierungen 59 werden fachsprachlich auch als Einstiche im Ventilschieber 22 bezeichnet.By means of a further guide part 56, the valve slide 22 is guided in the area of the pressure connection 40 in the valve housing 18 through its inner wall 52. Between the first control part 42 and the second control part 44 there is arranged a rod part 57 keeping them at a distance. Through a second fluid space 58 between the second control part 44 and the further guide part 56, the flow around the valve slide 22 in the area of the second control part 44 is improved, as a result of which the pressure losses within the pressure compensator 9 are reduced. Furthermore, the sealing behavior of the second control part 44 with respect to the housing inner wall 52 is improved by the second fluid chamber 58, since the sealing gap between the valve slide 22 and the housing inner wall 52 can be reduced by introducing the second fluid chamber 58 into the valve slide 22. The two fluid spaces 48, 58, which form axial distances between the first control part 42 and the second control part 44 or between the second control part 44 and the further guide part 56, are formed by groove-like diameter reductions 59 in the valve slide 22. Such diameter reductions 59 are also referred to in technical terms as recesses in the valve slide 22.

Auf seiner einen, in der Bildebene linken Stirnseite 60 grenzt der Ventilschieber 22 an eine Medienkammer 62 veränderlichen Volumens an, die über eine Fluidführung 64 mit dem ersten Fluidraum 48 fluidführend verbunden ist. Die Fluidführung 64 ist durch einen im Ventilschieber 22 zentral verlaufenden Fluidkanal 68 gebildet, der mit seinem einen längsverlaufenden Ende 70 in die eine Medienkammer 62 und mit seinem anderen querverlaufenden Ende 72 über eine Öffnung 74 in den ersten Fluidraum 48 zwischen den beiden Steuerteilen 42, 44 des Ventilschiebers 22 im Ventilgehäuse 18 einmündet. Der erste Fluidraum 48 ist dabei randseitig von den beiden Steuerteilen 42, 44 des Ventilschiebers 22 und dem Ventilgehäuse 18 mit begrenzt.On its one end face 60 on the left in the image plane, the valve slide 22 adjoins a media chamber 62 of variable volume, which is connected to the first fluid chamber 48 in a fluid-carrying manner via a fluid guide 64. The fluid guide 64 is formed by a fluid channel 68 running centrally in the valve slide 22, which with its one longitudinal end 70 into the one media chamber 62 and with its other transverse end 72 via an opening 74 into the first fluid space 48 between the two control parts 42, 44 of the valve slide 22 opens into the valve housing 18. The first fluid space 48 is delimited at the edge by the two control parts 42, 44 of the valve slide 22 and the valve housing 18.

Der bei geöffnetem Ventil durch den Ventilschieber 22 eingeregelte Druck zwischen dem Versorgungsanschluss 38 und dem Druckanschluss 40 wird über den Fluidkanal 68 in die eine Medienkammer 62 weitergeleitet. Der in der einen Medienkammer 62 herrschende Fluiddruck beaufschlagt dann den Ventilschieber 22 weiter in Richtung einer seiner geöffneten Stellungen zwecks Herbeiführen einer Fluidverbindung mit vergrößerter Durchlassmenge zwischen Druckversorgungsanschluss 38 und Druckanschluss 40. Der Fluidkanal 68 im Ventilschieber 22 weist im Bereich seiner Umlenkung von der Längs- in die Querkanalführung eine Drosselstelle 76 auf. Eine weitere Drosselstelle 77 ist dadurch ausgebildet, dass sich der Durchmesser des Fluidkanals 68 ausgehend von dem anderen Ende 72 des Fluidkanals 68 in Richtung des einen Endes 70 des Fluidkanals 68 endseitig stufenartig erweitert. Durch diese Drosselstellen 76, 77 werden Druckschwankungen am Versorgungsanschluss 38 verzögert und gedämpft an die eine Medienkammer 62 weitergeleitet, wenn sich der Ventilschieber 22 in einer seiner geöffneten, fluiddurchlassenden Stellungen befindet.The pressure between the supply connection 38 and the pressure connection 40, which is regulated by the valve slide 22 when the valve is open, is passed on via the fluid channel 68 into the one media chamber 62. The fluid pressure prevailing in one media chamber 62 then acts on the valve slide 22 further in the direction of one of its open positions for the purpose of bringing about a fluid connection with an increased flow rate between pressure supply connection 38 and pressure connection 40. The fluid channel 68 in the valve slide 22 has a throttle point 76 in the area of its deflection from the longitudinal to the transverse channel guide. A further throttle point 77 is formed in that the diameter of the fluid channel 68, starting from the other end 72 of the fluid channel 68, widens in a step-like manner towards the one end 70 of the fluid channel 68. By means of these throttling points 76, 77, pressure fluctuations at the supply connection 38 are delayed and passed on in a damped manner to the one media chamber 62 when the valve slide 22 is in one of its open, fluid-permeable positions.

Auf seiner anderen Stirnseite 78 grenzt der Ventilschieber 22 an eine andere Medienkammer 80 veränderlichen Volumens an, die bei einer vorgegebenen öffnenden Verschiebung des Ventilschiebers 22 in Blickrichtung auf die Fig. 2 und 3 gesehen nach rechts und mithin hin in Richtung der anderen Medienkammer 80 über eine andere weitere Fluidführung 82 mit dem Druckanschluss 40 fluidführend verbunden ist, so dass die eine Medienkammer 62 über den einen Fluidkanal 68 und den weiteren Fluidkanal 84 mit der anderen Medienkammer 80 verbindbar ist. Die Fig. 3 zeigt die dahingehende fluidführende Verbindung zwischen Druckanschluss 40 und Medienkammer 80. Ferner stützt sich die Stirnseite 78 des Ventilschiebers 22 an dem einen freien Ende einer Druckfeder 112 ab, die mit ihrem anderen freien Ende in Anlage mit der Abschlussschraube 30 ist und dabei die andere Medienkammer 80 durchgreift. Ferner ist die Druckfeder 112 mit einer vorgebbaren Vorspannung auch in der Nulllage des Ventilschiebers 22 (Fig. 2) in Anlage mit dem Schieber 22.On its other end face 78, the valve slide 22 adjoins another media chamber 80 of variable volume, which in the case of a predetermined opening displacement of the valve slide 22 in the viewing direction Fig. 2 and 3 viewed to the right and therefore in the direction of the other media chamber 80 via another further fluid duct 82 with the pressure connection 40 in a fluid-carrying manner, so that one media chamber 62 can be connected to the other media chamber 80 via the one fluid channel 68 and the further fluid channel 84. The Fig. 3 shows the pertinent fluid-carrying connection between pressure connection 40 and media chamber 80. Furthermore, the end face 78 of the valve slide 22 is supported on one free end of a compression spring 112, the other free end of which is in contact with the locking screw 30 and the other media chamber 80 takes action. Furthermore, the compression spring 112 is also in the zero position of the valve slide 22 with a predefinable preload ( Fig. 2 ) in contact with slide 22.

Wie in den Fig. 4 und 5 weiter dargestellt ist, ist die andere Fluidführung 82 durch den weiteren Fluidkanal 84 gebildet, der sich in Form einer Durchmesserreduzierung 86 des Ventilschiebers 22, bezogen auf einen Durchmesser 88 an der freien anderen Stirnseite 78 des Ventilschiebers 22 und begrenzt durch das weitere Führungsteil 56 des Ventilschiebers 22, parallel zu den axialen Verfahrrichtungen desselben erstreckt. So kann der weitere Fluidkanal 84 als mindestens eine nutförmige Durchmesserreduzierung 86 in dem Ventilschieber 22 oder bevorzugt aus einem radialen Wandabstand 89 zwischen Ventilschieber 22 und Ventilgehäuse 18 über den gesamten Außenumfang des Ventilschiebers 22 in diesem Bereich gebildet sein. Der radiale Wandabstand 89 zwischen Ventilgehäuse 18 und Ventilschieber 22 ist dabei durch die gleichförmig verlaufende Durchmesserreduzierung 86, bezogen auf den jeweiligen Durchmesser 88 der freien anderen Stirnseite 78 des Ventilschiebers 22, in dem Ventilschieber 22 in Richtung des Druckanschlusses 40 als diesem Bereich gebildet.As in the Figures 4 and 5 is further shown, the other fluid guide 82 is formed by the further fluid channel 84, which is in the form of a diameter reduction 86 of the valve slide 22, based on a diameter 88 on the free other end face 78 of the valve slide 22 and limited by the further guide part 56 of the valve slide 22, parallel to the axial directions of travel of the same. The further fluid channel 84 can be formed as at least one groove-shaped diameter reduction 86 in the valve slide 22 or preferably from a radial wall distance 89 between valve slide 22 and valve housing 18 over the entire outer circumference of valve slide 22 in this area. The radial wall distance 89 between valve housing 18 and valve slide 22 is formed by the uniformly extending diameter reduction 86, based on the respective diameter 88 of the other free end face 78 of valve slide 22, in valve slide 22 in the direction of pressure connection 40 as this area.

Der weitere, zweite Fluidkanal 84 ist von dem einen, ersten Fluidkanal 68 im Sinne einer Zwei-Kanallösung räumlich und vom Fluidführungskonzept her mit zwei voneinander räumlich getrennten Fluidführungen 82, 64 vollständig separiert und in jeder Verfahrstellung des Ventilschiebers 22 mit seinem einen freien Ende 94, das der Medienkammer 80 abgewandt ist, in erfindungswesentlicher Weise permanent mit dem Druckanschluss 40 fluidführend verbunden. In Richtung der anderen Medienkammer 80 endet an einem Ende 92 die in oder an dem weiteren Führungsteil 56 ausgebildete Durchmesserreduzierung 86 des Ventilschiebers 22, beabstandet von der anderen Stirnseite 78 des Ventilschiebers 22, und geht sprunghaft im Bereich einer zuordenbaren Regelkante 90 im Ventilgehäuse 18 in den vollen Durchmesser 88 des sich an die andere Stirnseite 78 des Ventilschiebers 22 anschließenden Endbereichs des weiteren Führungsteils 56 des Ventilschiebers 22 über, wodurch eine Steuerkante 114 an der Stelle des Sprunges im Ventilschieber 22 gebildet ist. Die insoweit stationär angeordnete Regelkante 90 bildet dann mit der verfahrbaren Steuerkante 114 den einzuregelnden Blenden- oder Steuerquerschnitt zwischen dem Druck- oder Verbraucheranschluss 40 und der Medienkammer 80, was in Fig. 1 symbolisch mit der Darstellung einer Drossel oder Blende 99 wiedergegeben ist. Dabei ist die Gesamtlänge der Abwicklung der Steuerkante 114 in einer horizontal verlaufenden, fiktiven Ebene (nicht dargestellt) größer als die Summe der einzelnen Abwicklungen, bezogen auf dieselbe horizontale Ebene, der freien Öffnungen 74 des ersten im Ventilschieber 22 verlaufenden Fluidkanals 68 im Bereich seines anderen Endes 72, das in den ersten Fluidraum 48 im Ventilgehäuse 18 über diese Öffnungen 74 ausmündet.The further, second fluid channel 84 is completely separated from the one, first fluid channel 68 in the sense of a two-channel solution spatially and in terms of the fluid guide concept with two fluid guides 82, 64 that are spatially separated from one another and in each displacement position of the valve slide 22 with its one free end 94, which faces away from the media chamber 80, is permanently connected to the pressure connection 40 in a manner essential to the invention in a fluid-conducting manner. In the direction of the other media chamber 80, the diameter reduction 86 of the valve slide 22, which is formed in or on the further guide part 56, ends at one end 92, spaced from the other end face 78 of the valve slide 22, and jumps into the area of an assignable control edge 90 in the valve housing 18 full diameter 88 of the end region of the further guide part 56 of the valve slide 22 adjoining the other end face 78 of the valve slide 22, whereby a control edge 114 is formed at the point of the jump in the valve slide 22. The control edge 90, which is arranged in a stationary manner, then forms, with the movable control edge 114, the diaphragm or control cross section to be regulated between the pressure or consumer connection 40 and the media chamber 80, which is shown in FIG Fig. 1 is symbolically reproduced with the representation of a throttle or diaphragm 99. Here is the Total length of the development of the control edge 114 in a horizontally running, fictitious plane (not shown) greater than the sum of the individual developments, based on the same horizontal plane, of the free openings 74 of the first fluid channel 68 running in the valve slide 22 in the area of its other end 72, which opens into the first fluid space 48 in the valve housing 18 via these openings 74.

Wie in Fig. 5 in einer geänderten Ausgestaltung der Lösung nach der Fig. 4 dargestellt, schließt sich an das der anderen Medienkammer 80 zugewandte andere Ende 92 des in Fig. 4 gezeigten und voranstehend beschriebenen weiteren Fluidkanals 84, mindestens ein Steuerkanal 96 an, der gegenüber dem weiteren Fluidkanal 84 über einen verringerten Kanalquerschnitt verfügt. Der jeweilige Steuerkanal 96 verjüngt sich, im Querschnitt betrachtet, in Richtung der anderen freien Stirnseite 78 des Ventilschiebers 22 konisch und mündet mit seinem dem weiteren Fluidkanal 84 zugewandten Ende 100 unter Bildung einer absatzartigen Fluidführungsstufe 102 in den weiteren Fluidkanal 84 ein. In Blickrichtung auf die Fig. 5 gesehen bildet das rechte Ende des Steuerkanals 86 mit seinem konisch verringerten Querschnitt eine weitere Steuerkante 115 am freien Ende des Ventilschiebers 22 aus, die mit der Regelkante 90 des Gehäuses 18 eine weitere Drossel- oder Blendeneinrichtung für das Fluid bildet, sobald die weitere Steuerkante 115 den freien Querschnitt an der stationären Regelkante 90 überfährt, was der Fall ist, wenn bei sich öffnenden Ventilstellungen der Ventilschieber 22 aus seiner Null-Lage nach der Fig. 2 in seine regelnden Stellungen in Richtung der End- oder Anschlagstellung nach der Fig. 3 nach rechts verfährt.As in Fig. 5 in a modified embodiment of the solution after Fig. 4 shown, connects to the other media chamber 80 facing other end 92 of the in Fig. 4 further fluid channel 84 shown and described above, at least one control channel 96, which has a reduced channel cross-section compared to the further fluid channel 84. The respective control channel 96 tapers conically, viewed in cross section, in the direction of the other free end face 78 of the valve slide 22 and, with its end 100 facing the further fluid channel 84, opens into the further fluid channel 84, forming a step-like fluid guide step 102. Looking towards the Fig. 5 seen, the right end of the control channel 86 with its conically reduced cross-section forms a further control edge 115 at the free end of the valve slide 22, which with the control edge 90 of the housing 18 forms a further throttle or diaphragm device for the fluid as soon as the further control edge 115 denies traverses free cross section at the stationary control edge 90, which is the case when the valve slide 22 from its zero position to the opening valve positions Fig. 2 in its regulating positions in the direction of the end or stop position after Fig. 3 moves to the right.

Bei Ausbildung der Durchmesserreduzierung 86 als radialer Wandabstand zwischen Ventilschieber 22 und Ventilgehäuse 18 mündet der jeweilige Steuerkanal 96 in den durch den radialen Wandabstand ausgeformten Fluidringkanal permanent fluidführend ein. Anstelle eines einzelnen oder mehrerer Steuerkanäle 96 kann auch nur ein Steuerkanalraum durch eine umlaufende Durchmesserreduzierung mit konischem Querschnitt im Ventilschieber 22 gebildet sein.When the diameter reduction 86 is designed as a radial wall distance between valve slide 22 and valve housing 18, the respective control channel 96 opens into the fluid ring channel formed by the radial wall distance in a permanent fluid-carrying manner. Instead of a single control channel or a plurality of control channels 96, only one control channel space can be passed through a be formed circumferential diameter reduction with conical cross section in the valve slide 22.

Wie Fig. 1 zeigt, ist an den Druckanschluss 40 über eine fluidführende Leitung 104 der hydraulische Verbraucher U an die Anschlussstelle P' der Ventileinrichtung 10 angeschlossen. In der fluidführenden Leitung 104 ist eine Regel-Einrichtung, insbesondere in der Art der Zumessblende 12 ausgebildet, vorgesehen. Zur "Abbildung" des Fluiddruckes zwischen Verbraucher U und der Zumessblende 12 auf die andere Stirnseite 78 des Ventilschiebers 22 ist eine entsprechende Steuerleitung 106 in Form einer LS-Signalleitung 108 vorgesehen, die an das Ventilgehäuse 18 angeschlossen ist und die in die andere Medienkammer 80 ausmündet. Die LS-Signalleitung 108 ist wiederum an die Hydraulikpumpe 41 in Form einer Verstellpumpe angeschlossen. Der Schwenkwinkel der Hydraulikpumpe 41, der den Druck am Versorgungsanschluss 38 mit vorgibt, wird abhängig vom Systemdruck in der LS-Signalleitung 108 geregelt. Mittels des derart ausgebildeten Lastdruck-Meldesystems lässt sich der durch die Hydraulikpumpe 41 eingespeiste Druck am Versorgungsanschluss 38 an die Erfordernisse des hydraulischen Verbrauchers U zeitnah anpassen. Des Weiteren ist vorgesehen, dass Fluid über die LS-Signalleitung 108 in einen Tankanschluss oder einen sonstigen, im Wesentlichen Umgebungsdruck aufweisenden Rücklaufanschluss R aus der anderen Medienkammer 80 über eine einstellbare Drossel oder Blende 110 abfließen kann. Eine vergleichbare Drossel oder Blende 110 weist auch die LS-Signalleitung 108 auf.How Fig. 1 shows, the hydraulic consumer U is connected to the connection point P ′ of the valve device 10 at the pressure connection 40 via a fluid-carrying line 104. In the fluid-carrying line 104, a control device, in particular designed in the manner of the metering orifice 12, is provided. To "map" the fluid pressure between consumer U and metering orifice 12 to the other end face 78 of valve slide 22, a corresponding control line 106 in the form of an LS signal line 108 is provided which is connected to valve housing 18 and which opens into the other media chamber 80 . The LS signal line 108 is in turn connected to the hydraulic pump 41 in the form of a variable displacement pump. The swivel angle of the hydraulic pump 41, which also specifies the pressure at the supply connection 38, is regulated as a function of the system pressure in the LS signal line 108. By means of the load pressure reporting system designed in this way, the pressure fed in by the hydraulic pump 41 at the supply connection 38 can be adapted promptly to the requirements of the hydraulic consumer U. Furthermore, it is provided that fluid can flow out of the other media chamber 80 via an adjustable throttle or diaphragm 110 via the LS signal line 108 into a tank connection or some other return connection R having essentially ambient pressure. The LS signal line 108 also has a comparable throttle or diaphragm 110.

Ein in der anderen Medienkammer 80 herrschender Fluiddruck beaufschlagt die andere Stirnseite 78 des Ventilschiebers 22 nach links in Richtung der Schließstellung SS, in welcher der Ventilschieber 22 bei Nullhub den Druckanschluss 40 von dem Versorgungsanschluss 38 vollständig trennt. Der Ventilschieber 22 ist auf seiner anderen Stirnseite 78 außerdem von dem Energiespeicher in Form der Druckfeder 112 beaufschlagt.A fluid pressure prevailing in the other media chamber 80 acts on the other end face 78 of the valve slide 22 to the left in the direction of the closed position SS, in which the valve slide 22 completely separates the pressure connection 40 from the supply connection 38 at zero stroke. The valve slide 22 is also acted upon on its other end face 78 by the energy store in the form of the compression spring 112.

Mittels des einen Fluidkanals 68, des weiteren Fluidkanals 84 und gegebenenfalls des an sich an den weiteren Fluidkanal 84 anschließenden Steuerkanals 96 ist der durch den Ventilschieber 22 eingeregelte Druck zwischen dem Versorgungsanschluss 38 und dem Druckanschluss 40 ab einer vorgebbaren Verschiebung des Ventilschiebers 22 in Richtung auf die andere Medienkammer 80 begrenzbar, nämlich durch Abführen von überschüssigem Fluid über die Steuerleitung 106 in die LS-Signalleitung 108 aus der anderen Medienkammer 80 heraus unter Zwischenschaltung der Drossel oder Blende 99.By means of the one fluid channel 68, the further fluid channel 84 and, if applicable, the control channel 96 adjoining the further fluid channel 84, the pressure regulated by the valve slide 22 between the supply connection 38 and the pressure connection 40 from a predeterminable displacement of the valve slide 22 in the direction of the other media chamber 80 can be limited, namely by discharging excess fluid via the control line 106 into the LS signal line 108 from the other media chamber 80 with the interposition of the throttle or diaphragm 99.

Nachfolgend wird die Funktionsweise der Ventilvorrichtung, soweit zum Verständnis der Erfindung notwendig, näher erläutert:
Im unbetätigten Zustand des Ventilschiebers 22, also bei Nullhub (Fig. 2), bei dem der Ventilschieber 22 in Anschlagstellung in Richtung der einen Medienkammer 62 positioniert ist, ist das zweite Steuerteil 44 mittels des zylinderförmigen Führungsteils 50 in Anlage mit der Gehäuseinnenwand 52 des Ventilgehäuses 18 im Bereich zwischen Versorgungsanschluss 38 und Druckanschluss 40, so dass der Ventilschieber 22 in einer seiner Schließstellungen SS angeordnet ist, in der dieser die fluidführende Verbindung 36 zwischen Versorgungsanschluss 38 und Druckanschluss 40 sperrt. In dieser Stellung SS wird der weitere Fluidkanal 84 und gegebenenfalls der Steuerkanal 96 von der Gehäuseinnenwand 52 in abdichtender Weise überdeckt und das weitere Führungsteil 56 ist mit seinem der anderen Medienkammer 80 zugewandten Endbereich in gleitender Anlage mit der zuordenbaren Gehäuseinnenwand 52.The mode of operation of the valve device is explained in more detail below, insofar as is necessary to understand the invention:
When the valve slide 22 is not actuated, i.e. at zero stroke ( Fig. 2 ), in which the valve slide 22 is positioned in the stop position in the direction of one media chamber 62, the second control part 44 is by means of the cylindrical guide part 50 in contact with the housing inner wall 52 of the valve housing 18 in the area between supply connection 38 and pressure connection 40, so that the valve slide 22 is arranged in one of its closed positions SS, in which the latter blocks the fluid-carrying connection 36 between supply connection 38 and pressure connection 40. In this position SS, the further fluid channel 84 and possibly the control channel 96 are covered in a sealing manner by the housing inner wall 52 and the further guide part 56 is in sliding contact with the assignable housing inner wall 52 with its end region facing the other media chamber 80.

Ein am Versorgungsanschluss 38 anstehender Fluiddruck wird über den einen Fluidkanal 68 in die eine Medienkammer 62 weitergeleitet. Dort wirkt er auf die angrenzende Stirnseite 60 des Ventilschiebers 22 ein. Auf der gegenüberliegenden anderen Stirnseite 78 ist der Ventilschieber 22 vom Lastdruck über die LS-Signalleitung 108 sowie die Steuerleitung 106 und der Druckfeder 112 beaufschlagt. Wenn der Fluiddruck am Versorgungsanschluss 38 den Gegendruck durch den Lastdruck und die Druckfeder 112 übersteigt, bewegt sich der Ventilschieber 22, ausgehend von der Schließstellung SS in Richtung der anderen Medienkammer 80, so dass das Ventil in einer seiner geöffneten Stellungen gelangt. Durch diese zunehmende Verschiebung des Ventilschiebers 22 wird das zweite Steuerteil 44 außer Eingriff mit der Gehäuseinnenwand 52 gebracht, so dass die fluidführende Verbindung 36 zwischen dem Versorgungsanschluss 38 und dem Druckanschluss 40 auch zunehmend weiter geöffnet wird.A fluid pressure present at the supply connection 38 is passed on via the one fluid channel 68 into the one media chamber 62. There it acts on the adjoining end face 60 of the valve slide 22. On the opposite other end face 78 is the valve slide 22 from the load pressure via the LS signal line 108 and the control line 106 and the compression spring 112 is applied. When the fluid pressure at the supply connection 38 exceeds the counter pressure caused by the load pressure and the compression spring 112, the valve slide 22 moves, starting from the closed position SS, in the direction of the other media chamber 80, so that the valve arrives in one of its open positions. As a result of this increasing displacement of the valve slide 22, the second control part 44 is brought out of engagement with the housing inner wall 52, so that the fluid-carrying connection 36 between the supply connection 38 and the pressure connection 40 is also increasingly opened.

Ab einer vorgegebenen Verschiebung des Ventilschiebers 22 wird die weitere fluidführende Verbindung 48 durch Schließen des ersten Steuerteils 42 an einer weiteren Schließkante 51 des Gehäuses 18 unterbrochen und gleichzeitig die fluidführende Verbindung zwischen den Medienkammern 62, 80 hergestellt, weil, falls kein Steuerkanal 96 vorgesehen ist, das andere Ende 94 des weiteren Fluidkanals 84 oder, falls ein Steuerkanal 96 vorgesehen ist, das der anderen Medienkammer 80 zugewandte Ende dieses Steuerkanals 96 unter Bildung einer entsprechenden Umlenkung für die andere Fluidführung 82 die Regelkante 90 im Ventilgehäuse 18 überfahren hat, die das Ventilgehäuse 18 in seiner Gehäuseinnenwand 52 aufweist und die einen ringnutartigen vom Ventilschieber 22 wegweisenden Rücksprung 116, in dessen Richtung jedoch vorstehend, begrenzt. Durch diese weitere fluidführende Verbindung 118 zwischen den Medienkammern 62,80 kommt es zu einer Druckangleichung zwischen diesen Medienkammern 62, 80.From a predetermined displacement of the valve slide 22, the further fluid-carrying connection 48 is interrupted by closing the first control part 42 on a further closing edge 51 of the housing 18 and at the same time the fluid-carrying connection between the media chambers 62, 80 is established because, if no control channel 96 is provided, the other end 94 of the further fluid channel 84 or, if a control channel 96 is provided, the end of this control channel 96 facing the other media chamber 80, forming a corresponding deflection for the other fluid guide 82, has passed over the control edge 90 in the valve housing 18 which the valve housing 18 has in its housing inner wall 52 and which limits an annular groove-like recess 116 pointing away from the valve slide 22, but protruding in the direction thereof. This further fluid-carrying connection 118 between the media chambers 62, 80 results in a pressure equalization between these media chambers 62, 80.

Unter der Einwirkung der Druckfeder 112 wird der Ventilschieber 22 wieder nach links in Richtung seiner Schließstellung SS verschoben, solange ein Druckausgleich in den Kammern 62, 80 besteht. Dieser Effekt wird dadurch verstärkt, dass Fluid aus der anderen Medienkammer 80 über die Steuerleitung 106 in Richtung der LS-Signalleitung 108 und gegebenenfalls in Richtung des Rücklaufanschlusses R oder Tankanschlusses nur gedrosselt, also sehr eingeschränkt abfließen kann. Hat sich der Ventilschieber 22 hinreichend weit in Richtung der Schließstellung SS bewegt, so kommt es wieder zunächst zu einer zumindest teilweisen abdichtenden Überdeckung des weiteren Fluidkanals 84 und gegebenenfalls des Steuerkanals 96 durch die Gehäuseinnenwand 52 des Ventilgehäuses 18 und darauffolgend zu einer Anlage des der anderen Medienkammer 80 zugewandten Endbereichs des weiteren Führungsteils 56, wodurch die fluidführende Verbindung zwischen den Medienkammern 62,80 zunächst gedrosselt und darauffolgend mit zunehmender Verschiebung des Ventilschiebers 22 weiter nach links vollständig getrennt wird. Aufgrund dieser vorstehend beschriebenen Funktionsweise stellt sich im Normalfall eine Gleichgewichtslage ein, die den Druck am Druckanschluss 40 vorteilhaft auf einen vorgebbaren Maximalwert begrenzt. Mithin kann es nicht mehr zu Überlastungen am hydraulischen Verbraucher U kommen. Vorteilhaft weist der Fluiddruck am Druckanschluss 40 eine konstante Druckdifferenz zum Versorgungsanschluss 38 auf, bis der zulässige maximale Druck erreicht ist. Durch die Blenden- oder Regelquerschnitte 90, 114 und gegebenenfalls 90, 115 wird erreicht, dass der Druck P' vor der Zumessblende 12 definiert eingestellt werden kann und zwar unabhängig von der aktuellen Fluidnachfrage am Verbraucher U.Under the action of the compression spring 112, the valve slide 22 is again shifted to the left in the direction of its closed position SS as long as there is pressure equalization in the chambers 62, 80. This effect is reinforced by the fact that fluid from the other media chamber 80 is only throttled via the control line 106 in the direction of the LS signal line 108 and possibly in the direction of the return port R or tank port, so can flow very limited. If the valve slide 22 has moved sufficiently far in the direction of the closed position SS, the further fluid channel 84 and possibly the control channel 96 are at least partially covered again by the inner wall 52 of the valve housing 18 and then the other media chamber comes into contact 80 facing end region of the further guide part 56, whereby the fluid-carrying connection between the media chambers 62, 80 is initially throttled and then completely separated with increasing displacement of the valve slide 22 further to the left. Due to the above-described mode of operation, an equilibrium position is normally established which advantageously limits the pressure at the pressure connection 40 to a predeterminable maximum value. This means that the hydraulic consumer U can no longer be overloaded. The fluid pressure at the pressure connection 40 advantageously has a constant pressure difference to the supply connection 38 until the maximum permissible pressure is reached. The diaphragm or standard cross-sections 90, 114 and possibly 90, 115 ensure that the pressure P 'in front of the metering diaphragm 12 can be set in a defined manner, regardless of the current fluid demand at the consumer U.

Im Ergebnis wird so eine Ventilvorrichtung aufgezeigt, die Druckschwankungen am Versorgungsanschluss 38 nicht mehr ungedämpft über die Druckwaage 9 passieren lässt und somit etwaige Überbeanspruchungen am hydraulischen Verbraucher U wirksam verhindert sowie zudem vorteilhaft das Betriebsverhalten im Rahmen der Regelung bei gleichzeitig kostengünstiger Realisierung verbessert.As a result, a valve device is shown that no longer allows pressure fluctuations at the supply connection 38 to pass unattenuated via the pressure compensator 9 and thus effectively prevents any overstressing on the hydraulic consumer U and also advantageously improves the operating behavior within the framework of the control while at the same time being cost-effective.

Claims (10)

  1. Valve apparatus for influencing a flow of medium between a supply port (38), to which a pressure supply source (P) can be connected, and a pressure port (40), to which a hydraulic load (U) can be connected, comprising a valve device (10) having a valve slide (22) which is guided in axial displacement directions within a valve housing (18), and the opposing end faces (60, 78) of which define two media chambers (62, 80) within the valve housing (18), at least in part, said valve slide blocking the connection (36) between the supply (38) and pressure port (40) in at least one closed position, and releasing the connection (36), to this effect, in at least one of the open positions thereof, in which the pressure port (40) is connected to at least one of the two media chambers (62, 80) by means of one fluid guide (64, 82) in each case, one (64) of which is formed by a fluid channel (68) extending in the valve slide (22), one end (70) of said channel leading into one media chamber (62), and the other end (72) of said channel leading into a fluid space (48) in the valve housing (18), which is separated from the pressure port (40) in the at least one closed position of the valve slide (22) and arranged between the supply (38) and pressure port (40), characterised in that the other fluid guide (82) comprises at least one further fluid channel (84) which is separated from the first fluid channel (68) and one end (92) of which leads into the other media chamber (80), at least in one of the open positions of the valve slide (22), and the other end (94) of which is permanently connected to the pressure port (40) in each displacement position of the valve slide (22).
  2. Valve apparatus according to claim 1, characterised in that the further fluid channel (84) in each case is arranged so as to extend in parallel with the axial displacement directions of the valve slide (22), and, in the event of an assignable regulating edge (90) in the valve housing (18), transverse thereto, being crossed, the fluid guide (82) of the relevant further fluid channel (84) experiences a deflection out of said parallel direction.
  3. Valve apparatus according to either claim 1 or claim 2, characterised in that at least one control channel (96) adjoins one end (92) of the respective further fluid channel (84) which faces in the direction of the other media chamber (80), said control channel having a different, in particular reduced, channel cross-section compared with the further fluid channel (84).
  4. Valve apparatus according to any one of the preceding claims, characterised in that, proceeding from the further fluid channel (84) in each case, the channel cross-section reduces in the direction of the respective control channel (96), at least in the region of the assignable regulating edge (90), forming a diaphragm (98) therewith.
  5. Valve apparatus according to any one of the preceding claims, characterised in that, viewed in cross-section, the respective control channel (96) tapers conically in the direction of one free end face (78) of the valve slide (22) which defines the other media chamber (80), at least in part, and leads into the respective assignable fluid channel (84) by the end (100) thereof facing said fluid channel, forming a shoulder-like fluid guide step (102).
  6. Valve apparatus according to any one of the preceding claims, characterised in that, with a winding of a control edge (114) of the valve slide (22) in the region of the at least one regulating edge (90) in the valve housing (18) in one plane, the total length of said winding is greater than the sum of the individual windings, referred to said same plane, of the free openings (74) of the fluid channel (68) extending in the valve slide (22), in the region of the respective other end (72) thereof, which leads into the fluid space (48) in the valve housing (18).
  7. Valve apparatus according to any one of the preceding claims, characterised in that the further fluid channel (84), in each case, is formed by a radial wall clearance (89) between the valve slide (22) and the valve housing (18).
  8. Valve apparatus according to any one of the preceding claims, characterised in that the radial wall clearance (89) between the valve housing (18) and the valve slide (22) is formed by a uniformly extending diameter reduction (86) in the valve slide (22), with respect to the diameter (88) of the free end face (78) of the valve slide (22), in the direction of the other media chamber (80), and in that, if a control channel (96) is provided as required, said control channel in each case leads, in a permanently fluid-conducting manner, into an annular fluid channel formed in this manner.
  9. Valve apparatus according to any one of the preceding claims, characterised in that the regulating edge (90) extending in the valve housing (18) surrounds the valve slide (22) in the regulation position and defines a groove-like recess (116), pointing away from the valve slide (22), protruding in the direction thereof.
  10. Valve apparatus according to any of the preceding claims, characterised in that, in an end position, in particular in a stop position of the valve slide (22) in the direction of the other media chamber (80), the further fluid channel (84) in each case has passed the regulating edge (90), forming a 90° deflection for the fluid guide (82), and if a control channel (96) is provided, said control channel leads, at the end face, into the further fluid channel (84) in each case, at the height of the regulating edge (90).
EP17732747.5A 2016-06-24 2017-06-16 Valve apparatus for influencing a flow of medium Active EP3475585B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016007754.9A DE102016007754A1 (en) 2016-06-24 2016-06-24 Valve device for influencing a media flow
PCT/EP2017/000700 WO2017220193A1 (en) 2016-06-24 2017-06-16 Valve apparatus for influencing a flow of medium

Publications (2)

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EP3475585A1 EP3475585A1 (en) 2019-05-01
EP3475585B1 true EP3475585B1 (en) 2020-08-19

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EP17732747.5A Active EP3475585B1 (en) 2016-06-24 2017-06-16 Valve apparatus for influencing a flow of medium

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US (1) US10914325B2 (en)
EP (1) EP3475585B1 (en)
CN (1) CN209925319U (en)
DE (1) DE102016007754A1 (en)
WO (1) WO2017220193A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019101133A1 (en) * 2019-01-17 2020-07-23 Gkn Automotive Limited VALVE ARRANGEMENT WITH AT LEAST ONE WAY VALVE AND CLUTCH DEVICE WITH SUCH A VALVE ARRANGEMENT
DE102019211004A1 (en) * 2019-07-25 2021-01-28 Festo Se & Co. Kg Valve

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DE1090044B (en) 1958-05-29 1960-09-29 Her Majesty The Queen In The R Control slide for the automatic, repetitive supply of a pressure medium from one inlet to two different connections
DE6600855U (en) 1964-04-10 1969-01-23 Essa Maschinenfabrik Ag Vorm S HIGH PRESSURE VALVE
DE1956621A1 (en) 1968-11-14 1970-07-23 Koehring Company Inc Control spool
DE1955659A1 (en) 1969-11-05 1971-05-13 Linde Ag Control device for a hydraulic actuator
DE2200568A1 (en) 1971-01-18 1972-08-03 Koehring Co Flow regulator
DE2248891C3 (en) 1971-10-26 1981-08-13 Koehring Co., Milwaukee, Wis. Slide piston for a hydraulic multi-way valve
DE4040523A1 (en) 1989-12-28 1991-07-04 Dana Corp FORCE-BALANCED, HYDRAULIC PISTON
DE19851553A1 (en) 1998-03-19 1999-09-23 Linde Ag Control valve for hydraulic load e.g. for lifting cylinders of load handling vehicle
DE102004003893A1 (en) 2003-01-31 2004-08-12 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Slide for slide valve has section guided in bore and ending in control edge through which it merges into smaller diameter section, and from control edge extends notch formed in outer face of larger diameter section and running into point
DE60304663T2 (en) 2002-12-14 2006-08-31 Sauer-Danfoss Aps Hydraulic valve device
DE102013014671A1 (en) 2013-09-03 2015-03-05 Hydac Technology Gmbh Ventilbaukomponenten
DE102014003086A1 (en) 2014-03-01 2015-09-03 Hydac Filtertechnik Gmbh valve device

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1090044B (en) 1958-05-29 1960-09-29 Her Majesty The Queen In The R Control slide for the automatic, repetitive supply of a pressure medium from one inlet to two different connections
DE6600855U (en) 1964-04-10 1969-01-23 Essa Maschinenfabrik Ag Vorm S HIGH PRESSURE VALVE
DE1956621A1 (en) 1968-11-14 1970-07-23 Koehring Company Inc Control spool
DE1955659A1 (en) 1969-11-05 1971-05-13 Linde Ag Control device for a hydraulic actuator
DE2200568A1 (en) 1971-01-18 1972-08-03 Koehring Co Flow regulator
DE2248891C3 (en) 1971-10-26 1981-08-13 Koehring Co., Milwaukee, Wis. Slide piston for a hydraulic multi-way valve
DE4040523A1 (en) 1989-12-28 1991-07-04 Dana Corp FORCE-BALANCED, HYDRAULIC PISTON
DE19851553A1 (en) 1998-03-19 1999-09-23 Linde Ag Control valve for hydraulic load e.g. for lifting cylinders of load handling vehicle
DE60304663T2 (en) 2002-12-14 2006-08-31 Sauer-Danfoss Aps Hydraulic valve device
DE102004003893A1 (en) 2003-01-31 2004-08-12 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Slide for slide valve has section guided in bore and ending in control edge through which it merges into smaller diameter section, and from control edge extends notch formed in outer face of larger diameter section and running into point
DE102013014671A1 (en) 2013-09-03 2015-03-05 Hydac Technology Gmbh Ventilbaukomponenten
WO2015032492A2 (en) 2013-09-03 2015-03-12 Hydac Technology Gmbh Valve components
US20160201695A1 (en) 2013-09-03 2016-07-14 Hydac Technology Gmbh Valve components
DE102014003086A1 (en) 2014-03-01 2015-09-03 Hydac Filtertechnik Gmbh valve device

Also Published As

Publication number Publication date
WO2017220193A1 (en) 2017-12-28
DE102016007754A1 (en) 2018-01-11
CN209925319U (en) 2020-01-10
EP3475585A1 (en) 2019-05-01
US10914325B2 (en) 2021-02-09
US20190120260A1 (en) 2019-04-25

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