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EP3475585A1 - Valve apparatus for influencing a flow of medium - Google Patents

Valve apparatus for influencing a flow of medium

Info

Publication number
EP3475585A1
EP3475585A1 EP17732747.5A EP17732747A EP3475585A1 EP 3475585 A1 EP3475585 A1 EP 3475585A1 EP 17732747 A EP17732747 A EP 17732747A EP 3475585 A1 EP3475585 A1 EP 3475585A1
Authority
EP
European Patent Office
Prior art keywords
valve
fluid
channel
control
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP17732747.5A
Other languages
German (de)
French (fr)
Other versions
EP3475585B1 (en
Inventor
Sascha Alexander Biwersi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hydac Systems and Services GmbH
Original Assignee
Hydac Systems and Services GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
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Application filed by Hydac Systems and Services GmbH filed Critical Hydac Systems and Services GmbH
Publication of EP3475585A1 publication Critical patent/EP3475585A1/en
Application granted granted Critical
Publication of EP3475585B1 publication Critical patent/EP3475585B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/026—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

  • Valve device for influencing a media flow
  • 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 travel directions within a valve housing and with its opposite end faces at least partially bounded two media chambers within the valve housing and in at least one closed position blocks the connection between the supply and the pressure port and releases the pertinent connection in at least one of its open positions, in which the pressure connection with at least one of two media chambers via a respective fluid guide is connected, one of which is formed of a valve spool extending in the fluid passage, which is at one end in a media chamber and with opens at another end into a fluid space in the valve housing, which is separated in the at least one closed position of the valve slide from the pressure port and disposed between the supply and pressure port.
  • a generic valve device is known from the solution according to FIGS. 3 ff together with the associated description pages of DE 10 2014 003 086 A1.
  • the known valve device also serves to influence a media flow between a supply connection to the a pressure supply source can be connected, and a pressure port, to which a hydraulic consumer can be connected, and has a valve device with a valve slide, which is guided longitudinally movable in a valve housing between end positions.
  • the pressure at the pressure connection regulated by the valve spool is limited from a predetermined displacement of the valve spool in the direction of one of its end positions so that overloading of the hydraulic load connected to the pressure port can no longer occur.
  • the fluid pressure at the pressure connection has a constant pressure difference to the supply connection until a permissible maximum pressure is reached.
  • the known valve device opens into the valve housing a control line, which is preferably part of a LS signal line or signal chain.
  • the control device has a control channel serving as a single fluid channel within the valve spool, which opens on a control side of the valve spool in a media chamber within the valve housing and from a predetermined displacement position of the valve spool, which preferably corresponds to a stop or end position, this Media chamber with a further media chamber within the valve housing fluid leading connects, to which the control line and the LS signal line is connected.
  • the invention has the object, while maintaining the advantages of the known solution, namely to achieve a limitation of the regulated by the valve spool pressure at the pressure or service port of the valve to further improve this to the effect that the Operating behavior is improved within the scheme at the same time cost-effective implementation.
  • the other fluid guide has at least one further fluid channel which is separated from the first fluid channel and which opens at least in one of the open positions of the valve spool with its one end in the other media chamber and the in each traversing position of the valve spool is permanently connected to the pressure port with its other end, the above-described known one-channel solution is replaced by a two-channel solution with shortened fluid paths per channel, with the result that it on the addressed control side of the valve not too Such high pressure losses can come as the instability in fluid control would be feared.
  • This also contributes to that the further fluid channel is permanently connected to the pressure connection of the valve to be regulated, so that the adjustment processes proceed directly and without pressure losses, due to the otherwise additionally necessary channel guides.
  • the respective further fluid channel is arranged to run parallel to the axial Verfahr- directions of the valve spool, so that when passing an assignable control edge transversely to the same by means of the valve spool, the fluid guide of the respective further fluid channel a deflection kung from this parallel direction , preferably at 90 ° experiences.
  • the two-channel solution with the further fluid channel which is permanently connected to the pressure connection in each displacement position of the displacement piston, 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 guide perpendicular in planes, parallel to the addressed control edge exits.
  • At least one control channel adjoins the one end of the respective further fluid channel, which points in the direction of the other medium chamber, which has a changed, in particular reduced, channel cross section with respect to the further fluid channel.
  • the respective control channel in the cross section in the direction of a free end face of the valve spool, which at least partially limits the other media chamber tapers conically and opens with its end facing the respectively assignable fluid channel to form a heel-like fluid guide stage in this ,
  • the control channel adjoining the respective fluid channel allows, with a slight change in the direction of the fluid relative to the parallel alignment at the control edge transversely to the same, a fluid flow path which allows the necessary control processes on the valve slide to be largely continuous without hindrance.
  • valve design such that in a fictitious development of a control edge of the valve spool in the region of at least one control edge in the valve housing in a plane whose total length is greater than the sum of the individual developments , relative to the same plane, of the free openings of the one valve slide extending in the fluid channel in the region of its other end, which opens into the fluid space in the valve housing.
  • a particularly high manufacturing quality with low manufacturing costs can be achieved if the respective further fluid channel is formed from a radial distance between the wall valve spool valve housing.
  • the radial distance between the valve housing and the valve slide is formed by a uniform diameter reduction in the valve spool, based on the diameter of the free end of the valve spool, in the direction of the other media chamber, with in case of need existing control channel this each in the thus formed Fluidring- channel permanently fluid leading opens. If the further fluid channel does not extend over the entire diameter in the outer wall of the valve slide, a fine-tuning for the control process in the fluid guide can be achieved by choosing this free diameter.
  • a defined control edge geometry can be achieved if, in the case of the valve device according to the invention, it is preferably provided that the control edge running in the valve housing is delimited in its direction by a groove-like recess in the valve housing facing away from the valve slide.
  • valve device is designed as a kind of individual pressure compensator.
  • the invention is explained in more detail with reference to exemplary embodiments illustrated in the figures. Show it:
  • FIG. 1 shows a hydraulic symbol representation of a volumetric flow regulator with a valve device according to the invention
  • FIG. 2 shows a longitudinal section through the valve device of Figure 1 with a valve slide in the left stop position in the direction of a media chamber.
  • FIG. 3 shows a longitudinal section through the valve device from FIG. 1 with a valve slide in the right stop position in the direction of the other medium chamber;
  • FIG. 4 is an enlarged view of a portion bordered by a circle X in FIG. 3;
  • FIG. 5 is an enlarged view of the area bordered by the circle X in FIG. 3 in a modified embodiment compared to the embodiment according to FIG. 4.
  • FIG. 1 shows in the form of a hydraulic symbol representation a pressure compensator 9 in conjunction with a metering orifice 12, which in the 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 in a frame-like block representation are summarized.
  • a valve housing 18 has a valve bore 20 in which a longitudinally movable valve slide 22 is arranged.
  • the valve bore 20 is at both Ends 24,26 closed by end screws 28,30, each engaging in a assignable internal thread 32 of the valve bore 20.
  • each annular sealing elements 34 are provided between the end screws 28,30 and the valve housing 18 .
  • the valve spool 22 is provided for controlling a fluid-conducting connection 36 between at least two fluid connection points 38, 40 accommodated 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 is connected to the supply connection 38, and a hydraulic consumer U (FIG.
  • valve device 10 for example in the form of a hydraulic working cylinder (not shown), is connected to the pressure connection 40 the connection point? ' the valve device 10 can be connected.
  • the valve spool 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 chamber 48 as part of the possible fluid-carrying connection 36 spaced from the first control part 42.
  • a control part for example, the control part 42, which brings disadvantages in the overall control behavior of the piston-like valve spool 22 with it.
  • the second control part 44 In the unactuated state of the valve spool 22, ie at zero stroke, in which the valve spool 22 is in the left end position (FIG. 2) in the image plane, the second control part 44 is in contact with a housing inner wall 52 of the housing by means of a cylindrical guide part 50 Valve housing 18.
  • a conically extending transition part 54 on the control part 44 thereby forms a flow guide for the fluid and causes a ramp-like deflection of the fluid flow from the first fluid chamber 48 in the direction of the pressure port 40.
  • the transition part 54 also contributes to the ungskomponungskung tion on the valve spool 22nd with at.
  • a further guide part 56 of the valve spool 22 is guided in the region of the pressure port 40 in the valve housing 18 through the inner wall 52.
  • a rod part 57 holding this at a distance is arranged between the first control part 42 and the second control part 44.
  • the flow around the valve spool 22 is now improved in the region of the second control part 44, whereby the pressure losses are reduced within the pressure compensator 9.
  • the second fluid chamber 58 improves the sealing behavior of the second control part 44 relative to the housing inner wall 52, since the sealing gap between the valve slide 22 and the housing inner wall 52 can be reduced by inserting the second fluid chamber 58 into the valve slide 22.
  • the two fluid chambers 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 punctures in the valve slide 22.
  • left end face 60 of the valve slide 22 adjoins a medium chamber 62 of variable volume, which is fluidly connected via a fluid guide 64 to the first fluid chamber 48.
  • the fluid guide 64 is formed by a valve spool 22 centrally extending fluid channel 68, with its one longitudinal end 70 in the one medium chamber 62 and with its other transverse end 72 via an opening 74 in the first fluid space 48 between the two control parts 42, 44th the valve spool 22 opens in the valve housing 18.
  • the first fluid chamber 48 is bordered by the two control parts 42, 44 of the valve spool 22 and the valve housing 18 at the edge.
  • the prevailing in the one medium chamber 62 fluid pressure then acts on the valve spool 22 toward one of its open positions in order to bring about a fluid connection with increased passage between the pressure supply port 38 and pressure port 40.
  • the fluid channel 68 in the valve spool 22 has in the region of its deflection of the longitudinal in the transverse channel guide on a throttle point 76.
  • a further throttle point 77 is formed in that, starting from the other end 72 of the fluid channel 68, the diameter of the fluid channel 68 expands stepwise in the direction of the one end 70 of the fluid channel 68. Due to these throttle points 76, 77, pressure fluctuations at the supply connection 38 are delayed and subdued to the one media chamber 62 when the valve slide 22 is in one of its open, fluid-passing positions.
  • the valve spool 22 adjoins another medium chamber 80 of variable volume, which, viewed in a predetermined opening displacement of the valve spool 22 as viewed in FIGS. 2 and 3, moves to the right and thus towards the other media chamber 80 via a other further fluid guide 82 is fluid-conductively connected to the pressure port 40, so that the one fluid chamber 62 can be connected to the other fluid chamber 68 via the one fluid passage 68 and the further fluid passage 84.
  • 3 shows the pertinent fluid-conducting connection between pressure port 40 and media chamber 80.
  • the end face 78 of the valve slide 22 is supported on the one free end of a compression spring 1 12, which is in contact with the end cap 30 with its other free end while the other media chamber 80 passes through.
  • the compression spring 1 12 with a predetermined bias even in the zero position of the valve spool 22 (Fig. 2) in abutment with the slider 22nd
  • 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 spool 22, based on a diameter 88 on the free other end face 78 of the valve spool 22 and limited by the further guide part 56 of the valve spool 22, extending parallel to the axial traversing directions thereof.
  • the further fluid channel 84 may be formed as at least one groove-shaped diameter reduction 86 in the valve spool 22 or preferably from a radial wall distance 89 between valve spool 22 and valve housing 18 over the entire outer circumference of the valve spool 22 in this area.
  • the radial wall distance 89 between valve housing 18 and valve slide 22 is formed by the uniform diameter reduction 86, based on the respective diameter 88 of the free other end face 78 of the valve spool 22 in the valve spool 22 in the direction of the pressure port 40 as this area.
  • the further, second fluid channel 84 is spatially separated from the one, first fluid channel 68 in terms of a two-channel solution and the fluid management concept with two spatially separate fluid guides 82, 64 and in each displacement position of the valve spool 22 with its one free end 94, which faces away from the media chamber 80, in a way which is essential to the invention, is permanently connected in a fluid-conducting manner to the pressure connection 40.
  • the diameter reduction 86 of the valve slide 22 formed in or on the further guide member 56 ends at one end 92, spaced from the other end face 78 of the valve slide 22, and abruptly moves in the region of an assignable control edge 90 in the valve housing 18 in the full diameter 88 of the other end face 78 of the valve spool 22nd subsequent end portion of the further guide member 56 of the valve spool 22, whereby a control edge 1 14 is formed at the location of the jump in the valve spool 22.
  • the stationary control edge 90 which in this respect is stationary, then forms with the movable control edge 14 the aperture or control cross section to be adjusted between the pressure or consumer connection 40 and the medium chamber 80, which is shown symbolically in FIG.
  • the total length of the development of the control edge 1 14 in a horizontally extending, notional plane is greater than the sum of the individual developments, with respect to the same horizontal plane, of the free openings 74 of the first fluid channel 68 in the valve slide 22 Area of its other end 72, which opens into the first fluid chamber 48 in the valve housing 18 through these openings 74.
  • Fig. 5 in a modified embodiment of the solution according to FIG. 4, adjoins the other media chamber 80 facing the other end 92 of the shown in Fig. 4 and described above further fluid channel 84, at least one control channel 96 which opposite the further fluid channel 84 has a reduced channel cross-section.
  • the respective control channel 96 tapers in the direction of the other free end face 78 of the valve slide 22 and opens with its end 100 facing the further fluid channel 84 to form a heel-like fluid guide stage 102 into the further fluid channel 84.
  • the right end of the control channel 86 forms with its conically reduced cross-section another control edge 1 1 5 at the free end of the valve spool 22, with the control edge 90 of the housing 18, a further throttle or aperture device for Fluid forms as soon as the further control edge 1 1 5 passes over the free cross section at the stationary control edge 90, which is the case when the valve spool 22 opens at the valve positions that open its zero position according to FIG. 2 moves in its regulating positions in the direction of the end or stop position of FIG. 3 to the right.
  • the respective control channel 96 opens permanently into the fluid channel formed by the radial wall clearance.
  • only one control channel space can be formed by a circumferential diameter reduction with a conical cross section in the valve slide 22.
  • the hydraulic consumer U is connected to the connection port 40 to the pressure connection 40 via a fluid-carrying line 104.
  • the valve device 10 is connected.
  • a regulating device in particular in the manner of the metering orifice 12 is provided, is provided.
  • a corresponding control line 106 in the form of a LS signal line 108 is provided, which is connected to the valve housing 18 and which opens into the other media chamber 80
  • the LS signal line 108 is connected to the variable displacement pump 41.
  • the swing angle of the hydraulic pump 41 that controls the pressure at the supply port 38 is controlled depending on 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 to the requirements of the hydraulic consumer U.
  • fluid via the LS signal line 108 into a tank connection or other, substantially ambient pressure Return connection R from the other media chamber 80 via an adjustable throttle or aperture 1 10 can drain.
  • a comparable throttle or aperture 10 also has the LS signal line 108.
  • a fluid pressure prevailing in the other medium 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 disconnects the pressure connection 40 from the supply connection 38 at zero stroke.
  • the valve spool 22 is also acted upon by the energy store in the form of the compression spring 1 12 on its other end face 78.
  • the pressure regulated by the valve spool 22 between the supply connection 38 and the pressure connection 40 is from a predeterminable displacement of the valve spool 22 in the direction can be limited to the other media chamber 80, namely by discharging excess fluid via the control line 106 in the LS signal line 108 from the other media chamber 80 out with the interposition of the throttle or aperture 99th
  • a fluid pressure present at the supply port 38 is forwarded via the one fluid channel 68 into the one media chamber 62. There he acts on the adjacent end face 60 of the valve spool 22 a. On the opposite other end face 78 of the valve spool 22 from the load pressure via the LS signal line 108 and the control line 106 and the compression spring 1 12 is applied.
  • the further fluid-conducting connection 48 is interrupted by closing the first control part 42 at a further closing edge 51 of the housing 1 8 and at the same time the fluid-conducting connection between the media chambers 62, 80, 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 other media chamber 80 facing the end of this control channel 96 to form a corresponding deflection for the other fluid guide 82 has crossed the control edge 90 in the valve housing 18, the valve housing 18 in its housing inner wall 52 and the an annular groove-like from the valve spool 22 pioneering ücksprung 1 16, in the direction but above, limited.
  • this further fluid-conducting connection 1 18 between the media chambers 62,80 there is a pressure equalization between these media chambers 62, 80th
  • valve spool 22 Under the action of the compression spring 1 12, the valve spool 22 is moved back to the left in the direction of its closed position SS, as long as a pressure equalization in the chambers 62, 80 consists. This effect is enhanced by the fact that fluid from the other media chamber 80 via the control line 106 in the direction of the LS signal line 108 and optionally in the direction of the return port R or tank port throttled only, so it can flow very limited.
  • the fluid pressure at the pressure connection 40 has a constant pressure difference to the supply connection 38 until the permissible maximum pressure is reached.
  • the aperture or control cross sections 90, 1 14 and optionally 90, 1 15 it is achieved that the pressure P 'can be set defined before the metering orifice 12, regardless of the current fluid demand at the consumer U.
  • a valve device is shown, the pressure fluctuations at the supply port 38 can not pass through the pressure balance 9 undamped and thus effectively prevents any overuse of the hydraulic load U and also advantageously improves the performance in the context of the scheme at the same cost-effective implementation.

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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)

Abstract

A valve apparatus for influencing a flow of medium between a supply port (38) and a pressure port (40), having a valve device (10) which, in at least one closed position, blocks the connection between the supply port (38) and the pressure port (40) and which opens this connection in at least one opened position, in which the pressure port (40) is connected to at least one of two medium chambers (62, 80) by a respective fluid channel (64, 82), of which one (64) consists of a fluid duct (68) in the valve slider (22), is characterized in that the other fluid channel (82) has at least one further fluid duct (84) which is separate from the first fluid duct (68) and which, at least in one of the opened positions of the valve slider (22), opens at one end (92) into the medium chamber (80) and which, in every displacement position of the valve slider (22), is permanently connected at the other end (94) to the pressure port (40).

Description

Ventilvorrichtung zum Beeinflussen eines Medienstromes  Valve device for influencing a media flow
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 travel directions within a valve housing and with its opposite end faces at least partially bounded two media chambers within the valve housing and in at least one closed position blocks the connection between the supply and the pressure port and releases the pertinent connection in at least one of its open positions, in which the pressure connection with at least one of two media chambers via a respective fluid guide is connected, one of which is formed of a valve spool extending in the fluid passage, which is at one end in a media chamber and with opens at another end into a fluid space in the valve housing, which is separated in the at least one closed position of the valve slide from the pressure port and disposed between the supply and pressure port.
Durch die Lösung nach den Fig.3 ff nebst den zugehörigen Beschreibungs- Seiten 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 Steuerein- richtung 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 Flu- iddruck am Druckanschluss eine konstante Druckdifferenz zum Versor- gungsanschluss auf, bis ein zulässiger maximaler Druck erreicht ist. A generic valve device is known from the solution according to FIGS. 3 ff together with the associated description pages of DE 10 2014 003 086 A1. The known valve device also serves to influence a media flow between a supply connection to the a pressure supply source can be connected, and a pressure port, to which a hydraulic consumer can be connected, and has a valve device with a valve slide, which is guided longitudinally movable in a valve housing between end positions. By means of a control device, the pressure at the pressure connection regulated by the valve spool is limited from a predetermined displacement of the valve spool in the direction of one of its end positions so that overloading of the hydraulic load connected to the pressure port can no longer occur. Advantageously, the fluid pressure at the pressure connection has a constant pressure difference to the supply connection until a permissible maximum pressure is reached.
Bei einer bevorzugten Ausführungsform der bekannten Ventilvorrichtung mündet in das Ventilgehäuse eine Steuerleitung ein, die bevorzugt Bestand- teil 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. 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 a preferred embodiment of the known valve device opens into the valve housing a control line, which is preferably part of a LS signal line or signal chain. In order to control this control line, the control device has a control channel serving as a single fluid channel within the valve spool, which opens on a control side of the valve spool in a media chamber within the valve housing and from a predetermined displacement position of the valve spool, which preferably corresponds to a stop or end position, this Media chamber with a further media chamber within the valve housing fluid leading connects, to which the control line and the LS signal line is connected. In the known solution, the only control or fluid channel of a system of longitudinal and transverse bores in the valve spool is constructed, the dimensions of her forth to perform the Ansteuervorgänge are formed as accurately as possible, resulting in correspondingly high production costs. Also, it has been shown in practice that it due to the relatively narrow-sized free channel cross sections of the mentioned control channel to problems in the immediate forwarding of the pressure connection pending hydraulic pressure can come to the actual control side of the valve, resulting in pressure losses within the fluid guide and thus 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' can not be tapped correctly by the position of the bore before the non-return edge, but is increased by the switching edge in dependence on the volume flow Q and the opening.
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. Based on this prior art, the invention has the object, while maintaining the advantages of the known solution, namely to achieve a limitation of the regulated by the valve spool pressure at the pressure or service port of the valve to further improve this to the effect that the Operating behavior is improved within the scheme at the same time cost-effective implementation.
Eine dahingehende Aufgabe löst eine Ventilvorrichtung mit den Merkmalen des Patentanspruchs 1 in seiner Gesamtheit. This object is achieved by a valve device having the features of patent 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 ande- re 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 ver- besserten 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. Characterized 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 opens at least in one of the open positions of the valve spool with its one end in the other media chamber and the in each traversing position of the valve spool is permanently connected to the pressure port with its other end, the above-described known one-channel solution is replaced by a two-channel solution with shortened fluid paths per channel, with the result that it on the addressed control side of the valve not too Such high pressure losses can come as the instability in fluid control would be feared. This also contributes to that the further fluid channel is permanently connected to the pressure connection of the valve to be regulated, so that the adjustment processes proceed directly and without pressure losses, due to the otherwise additionally necessary channel guides. Overall, this leads to an improved energy balance in the context of the desired control processes with the valve device and the instabilities mentioned due to excessive pressure losses are thus avoided with certainty. Despite the two-channel training, the overall manufacturing costs are reduced because the manufacturing effort is correspondingly reduced due to the channel design that is simpler to implement and, to that extent, the control and control geometries that are easier to control.
Bei einer bevorzugten Ausführungsform der erfindungsgemäßen Ventilvorrichtung ist der jeweils weitere Fluidkanal parallel zu den axialen Verfahr- richtungen des Ventilschiebers verlaufend angeordnet, so dass bei Überfahren einer zuordenbaren Regelkante quer zu derselben mittels des Ventilschiebers die Fluidführung des jeweils weiteren Fluidkanals eine Umlen- kung aus dieser Parallelrichtung, vorzugsweise um 90°, erfährt. Dergestalt lässt sich mit der Zwei-Kanal lösung mit dem weiteren Fluidkanal, der per- manent druckführend mit dem Druckanschluss in jeder Verfahrstellung des Verschiebekolbens in Verbindung steht, eine verbesserte Regelgüte respektive Regelqualität erreichen gegenüber der bekannten Ein-Kanal lösung, 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 Verfahr- directions of the valve spool, so that when passing an assignable control edge transversely to the same by means of the valve spool, the fluid guide of the respective further fluid channel a deflection kung from this parallel direction , preferably at 90 ° experiences. In this way, with the two-channel solution with the further fluid channel, which is permanently connected to the pressure connection in each displacement position of the displacement piston, 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 guide perpendicular in planes, parallel to the addressed control edge exits.
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 geän- derten, insbesondere verringerten Kanalquerschnitt verfügt. Vorzugsweise ist dabei vorgesehen, dass der Kanalquerschnitt sich, ausgehend vom je- weils 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. 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 er- möglicht. In a further preferred embodiment of the valve device according to the invention, at least one control channel adjoins the one end of the respective further fluid channel, which points in the direction of the other medium chamber, which has a changed, in particular reduced, channel cross section with respect to the further fluid channel. Preferably, it is provided that the channel cross-section, starting from the respective Weil further fluid channel, in the direction of the respective control channel at least in the region of the assignable control edge to form a diaphragm with the same reduced. In this way, with the respective further fluid channel in functional connection with the respectively further control channel, it is achieved that in the control position of the valve a type of pressure divider circuit is achieved, with which the required control pressure on the pressure delivery side of the valve can be increased noticeably. This has no equivalent in the prior art. In this case, it is particularly preferred that the respective control channel in the cross section in the direction of a free end face of the valve spool, which at least partially limits the other media chamber, tapers conically and opens with its end facing the respectively assignable fluid channel to form a heel-like fluid guide stage in this , With this arrangement, the control channel adjoining the respective fluid channel allows, with a slight change in the direction of the fluid relative to the parallel alignment at the control edge transversely to the same, a fluid flow path which allows the necessary control processes on the valve slide to be largely continuous without hindrance.
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. 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 ra- diale 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 Fluidring- kanal 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. 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. To maintain a particularly high control quality, it has proven to be advantageous to design the valve design such that in a fictitious development of a control edge of the valve spool in the region of at least one control edge in the valve housing in a plane whose total length is greater than the sum of the individual developments , relative to the same plane, of the free openings of the one valve slide extending in the fluid channel in the region of its other end, which opens into the fluid space in the valve housing. A particularly high manufacturing quality with low manufacturing costs can be achieved if the respective further fluid channel is formed from a radial distance between the wall valve spool valve housing. Particularly preferred for the purpose of simplified production is that the radial distance between the valve housing and the valve slide is formed by a uniform diameter reduction in the valve spool, based on the diameter of the free end of the valve spool, in the direction of the other media chamber, with in case of need existing control channel this each in the thus formed Fluidring- channel permanently fluid leading opens. If the further fluid channel does not extend over the entire diameter in the outer wall of the valve slide, a fine-tuning for the control process in the fluid guide can be achieved by choosing this free diameter. A defined control edge geometry can be achieved if, in the case of the valve device according to the invention, it is preferably provided that the control edge running in the valve housing is delimited in its direction by a groove-like recess in the valve housing facing 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. At the end position of the valve spool, in particular at a planned stop position in the direction of the other media chamber, has passed over the control edge for the control process of each further fluid channel to form a 90 ° deflection for the fluid guide, in which case the existing existing control channel at this level of the control edge in the thus each other fluid channel terminates at the end.
Bevorzugt ist die Ventileinrichtung als eine Art Individualdruckwaage konzipiert. Die Erfindung ist nachfolgend anhand von in den Figuren dargestellten Ausführungsbeispielen näher erläutert. Es zeigen: Preferably, the valve device is designed as a kind of individual pressure compensator. The invention is explained in more detail with reference to exemplary embodiments illustrated in the figures. Show it:
Fig. 1 eine hydraulische Symboldarstellung eines Volumenstromreglers mit einer erfindungsgemäßen Ventilvorrichtung; 1 shows a hydraulic symbol representation of a volumetric flow regulator with a valve device according to the invention;
Fig. 2 einen Längsschnitt durch die Ventilvorrichtung aus Fig. 1 mit einem Ventilschieber in linker Anschlagstellung in Richtung der einen Medienkammer; 2 shows a longitudinal section through the valve device of Figure 1 with a valve slide in the left stop position in the direction of a media chamber.
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 3 shows a longitudinal section through the valve device from FIG. 1 with a valve slide in the right stop position in the direction of the other medium chamber; FIG. 4 is an enlarged view of a portion bordered by a circle X in FIG. 3; FIG. and
Fig. 5 eine vergrößerte Darstellung des in Fig.3 mit dem Kreis X umrandeten Bereichs in einer geänderten Ausgestaltung gegenüber der Aus- führungsform nach der Fig. 4. 5 is an enlarged view of the area bordered by the circle X in FIG. 3 in a modified embodiment compared to the embodiment according to 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 erfindungs- gemäße Ventilvorrichtung mit der Ventileinrichtung 10 aufweist, deren wesentliche Komponenten in einer rahmenartigen Blockdarstellung zusam- mengefasst sind. 1 shows in the form of a hydraulic symbol representation a pressure compensator 9 in conjunction with a metering orifice 12, which in the 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 in a frame-like block representation are summarized.
Gemäß den Längsschnittdarstellungen nach den Fig. 2 und 3 weist ein Ventilgehäuse 18 eine Ventilbohrung 20 auf, in der ein längsverfahrbar geführ- ter 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. 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 Druck- anschluss 40, vorgesehen. An den Versorgungsanschluss 38 ist eine Druckversorgungsquelle P (Fig. 1 ) in Form einer Hydraulikpumpe 41 angeschlos- sen, und an den Druckanschluss 40 ist ein hydraulischer Verbraucher U (Fig. 1 ), beispielsweise in Form eines hydraulischen Arbeitszylinders (nicht dargestellt), über die Anschlussstelle ?' 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 An- läge 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 Ström ungskraftkompensa- tion am Ventilschieber 22 mit bei. 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 gegen- über 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. According to the longitudinal sectional views according to FIGS. 2 and 3, a valve housing 18 has a valve bore 20 in which a longitudinally movable valve slide 22 is arranged. The valve bore 20 is at both Ends 24,26 closed by end screws 28,30, each engaging in a assignable internal thread 32 of the valve bore 20. Between the end screws 28,30 and the valve housing 18 each annular sealing elements 34 are provided. The valve spool 22 is provided for controlling a fluid-conducting connection 36 between at least two fluid connection points 38, 40 accommodated 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 is connected to the supply connection 38, and a hydraulic consumer U (FIG. 1), for example in the form of a hydraulic working cylinder (not shown), is connected to the pressure connection 40 the connection point? ' the valve device 10 can be connected. The valve spool 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 chamber 48 as part of the possible fluid-carrying connection 36 spaced from the first control part 42. In principle, it is possible to implement the solution according to the invention only with a control part, for example, the control part 42, which brings disadvantages in the overall control behavior of the piston-like valve spool 22 with it. In the unactuated state of the valve spool 22, ie at zero stroke, in which the valve spool 22 is in the left end position (FIG. 2) in the image plane, the second control part 44 is in contact with a housing inner wall 52 of the housing by means of a cylindrical guide part 50 Valve housing 18. A conically extending transition part 54 on the control part 44 thereby forms a flow guide for the fluid and causes a ramp-like deflection of the fluid flow from the first fluid chamber 48 in the direction of the pressure port 40. The transition part 54 also contributes to the ungskomponungskung tion on the valve spool 22nd with at. By means of a further guide part 56 of the valve spool 22 is guided in the region of the pressure port 40 in the valve housing 18 through the inner wall 52. Between the first control part 42 and the second control part 44, a rod part 57 holding this at a distance is arranged. By a second fluid space 58 between the second control part 44 and the further guide part 56, the flow around the valve spool 22 is now improved in the region of the second control part 44, whereby the pressure losses are reduced within the pressure compensator 9. Furthermore, the second fluid chamber 58 improves the sealing behavior of the second control part 44 relative to the housing inner wall 52, since the sealing gap between the valve slide 22 and the housing inner wall 52 can be reduced by inserting the second fluid chamber 58 into the valve slide 22. The two fluid chambers 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 punctures in the valve slide 22.
Auf seiner einen, in der Bildebene linken Stirnseite 60 grenzt der Ventil- Schieber 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. 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 wei- tere 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 Medienkam- mer 62 weitergeleitet, wenn sich der Ventilschieber 22 in einer seiner geöffneten, fluiddurchlassenden Stellungen befindet. On its one, in the image plane left end face 60 of the valve slide 22 adjoins a medium chamber 62 of variable volume, which is fluidly connected via a fluid guide 64 to the first fluid chamber 48. The fluid guide 64 is formed by a valve spool 22 centrally extending fluid channel 68, with its one longitudinal end 70 in the one medium chamber 62 and with its other transverse end 72 via an opening 74 in the first fluid space 48 between the two control parts 42, 44th the valve spool 22 opens in the valve housing 18. The first fluid chamber 48 is bordered by the two control parts 42, 44 of the valve spool 22 and the valve housing 18 at the edge. The pressure, which is regulated by the valve spool 22 when the valve is open, between the supply connection 38 and the pressure connection 40 is forwarded via the fluid channel 68 into the one medium chamber 62. The prevailing in the one medium chamber 62 fluid pressure then acts on the valve spool 22 toward one of its open positions in order to bring about a fluid connection with increased passage between the pressure supply port 38 and pressure port 40. The fluid channel 68 in the valve spool 22 has in the region of its deflection of the longitudinal in the transverse channel guide on a throttle point 76. A further throttle point 77 is formed in that, starting from the other end 72 of the fluid channel 68, the diameter of the fluid channel 68 expands stepwise in the direction of the one end 70 of the fluid channel 68. Due to these throttle points 76, 77, pressure fluctuations at the supply connection 38 are delayed and subdued to the one media chamber 62 when the valve slide 22 is in one of its open, fluid-passing 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 1 12 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 1 12 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 spool 22 adjoins another medium chamber 80 of variable volume, which, viewed in a predetermined opening displacement of the valve spool 22 as viewed in FIGS. 2 and 3, moves to the right and thus towards the other media chamber 80 via a other further fluid guide 82 is fluid-conductively connected to the pressure port 40, so that the one fluid chamber 62 can be connected to the other fluid chamber 68 via the one fluid passage 68 and the further fluid passage 84. 3 shows the pertinent fluid-conducting connection between pressure port 40 and media chamber 80. Furthermore, the end face 78 of the valve slide 22 is supported on the one free end of a compression spring 1 12, which is in contact with the end cap 30 with its other free end while the other media chamber 80 passes through. Furthermore, the compression spring 1 12 with a predetermined bias even in the zero position of the valve spool 22 (Fig. 2) in abutment with the slider 22nd
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. 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 fluid- führend 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 Be- reich 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 1 14 an der Stelle des Sprunges im Ventilschieber 22 gebildet ist. Die insoweit stationär angeordnete Regelkante 90 bildet dann mit der verfahrbaren Steuerkante 1 14 den einzuregelnden Blenden- oder Steuerquerschnitt zwischen dem Druck- oder Verbraucher- anschluss 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 1 14 in einer horizontal verlaufenden, fiktiven Ebene (nicht dargestellt) größer als die Summe der ein- zelnen 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. 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 ver- fügt. 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 1 1 5 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 1 1 5 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 further shown in Figs. 4 and 5, 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 spool 22, based on a diameter 88 on the free other end face 78 of the valve spool 22 and limited by the further guide part 56 of the valve spool 22, extending parallel to the axial traversing directions thereof. Thus, the further fluid channel 84 may be formed as at least one groove-shaped diameter reduction 86 in the valve spool 22 or preferably from a radial wall distance 89 between valve spool 22 and valve housing 18 over the entire outer circumference of the valve spool 22 in this area. The radial wall distance 89 between valve housing 18 and valve slide 22 is formed by the uniform diameter reduction 86, based on the respective diameter 88 of the free other end face 78 of the valve spool 22 in the valve spool 22 in the direction of the pressure port 40 as this area. The further, second fluid channel 84 is spatially separated from the one, first fluid channel 68 in terms of a two-channel solution and the fluid management concept with two spatially separate fluid guides 82, 64 and in each displacement position of the valve spool 22 with its one free end 94, which faces away from the media chamber 80, in a way which is essential to the invention, is permanently connected in a fluid-conducting manner to the pressure connection 40. In the direction of the other medium chamber 80, the diameter reduction 86 of the valve slide 22 formed in or on the further guide member 56 ends at one end 92, spaced from the other end face 78 of the valve slide 22, and abruptly moves in the region of an assignable control edge 90 in the valve housing 18 in the full diameter 88 of the other end face 78 of the valve spool 22nd subsequent end portion of the further guide member 56 of the valve spool 22, whereby a control edge 1 14 is formed at the location of the jump in the valve spool 22. The stationary control edge 90, which in this respect is stationary, then forms with the movable control edge 14 the aperture or control cross section to be adjusted between the pressure or consumer connection 40 and the medium chamber 80, which is shown symbolically in FIG. 1 with the representation of a throttle or aperture 99 , The total length of the development of the control edge 1 14 in a horizontally extending, notional plane (not shown) is greater than the sum of the individual developments, with respect to the same horizontal plane, of the free openings 74 of the first fluid channel 68 in the valve slide 22 Area of its other end 72, which opens into the first fluid chamber 48 in the valve housing 18 through these openings 74. As shown in Fig. 5 in a modified embodiment of the solution according to FIG. 4, adjoins the other media chamber 80 facing the other end 92 of the shown in Fig. 4 and described above further fluid channel 84, at least one control channel 96 which opposite the further fluid channel 84 has a reduced channel cross-section. The respective control channel 96, viewed in cross-section, tapers in the direction of the other free end face 78 of the valve slide 22 and opens with its end 100 facing the further fluid channel 84 to form a heel-like fluid guide stage 102 into the further fluid channel 84. Seen in the direction of FIG. 5, the right end of the control channel 86 forms with its conically reduced cross-section another control edge 1 1 5 at the free end of the valve spool 22, with the control edge 90 of the housing 18, a further throttle or aperture device for Fluid forms as soon as the further control edge 1 1 5 passes over the free cross section at the stationary control edge 90, which is the case when the valve spool 22 opens at the valve positions that open its zero position according to FIG. 2 moves in its regulating positions in the direction of the end or stop position of FIG. 3 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 Flu- idringkanal permanent fluidführend ein. Anstelle eines einzelnen oder mehrerer Steuerkanäle 96 kann auch nur ein Steuerkanalraum durch eine umlaufende Durchmesserreduzierung mit konischem Querschnitt im Ventil- Schieber 22 gebildet sein. When forming the diameter reduction 86 as a radial wall distance between the valve spool 22 and the valve housing 18, the respective control channel 96 opens permanently into the fluid channel formed by the radial wall clearance. Instead of a single or multiple control channels 96, only one control channel space can be formed by a circumferential diameter reduction with a 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 ?' 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 Last- druck-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 Rücklaufan- schluss R aus der anderen Medienkammer 80 über eine einstellbare Drossel oder Blende 1 10 abfließen kann. Eine vergleichbare Drossel oder Blende 1 10 weist auch die LS-Signalleitung 108 auf. As FIG. 1 shows, the hydraulic consumer U is connected to the connection port 40 to the pressure connection 40 via a fluid-carrying line 104. the valve device 10 is connected. In the fluid-carrying line 104, a regulating device, in particular in the manner of the metering orifice 12 is provided, is provided. For "imaging" of the fluid pressure between the consumer U and the metering orifice 12 on the other end face 78 of the valve spool 22, a corresponding control line 106 in the form of a LS signal line 108 is provided, which is connected to the valve housing 18 and which opens into the other media chamber 80 In turn, the LS signal line 108 is connected to the variable displacement pump 41. The swing angle of the hydraulic pump 41 that controls the pressure at the supply port 38 is controlled depending on the system pressure in the LS signal line 108. By means of the load thus formed pressure-signaling system, the pressure fed in by the hydraulic pump 41 at the supply connection 38 can be adapted to the requirements of the hydraulic consumer U. In addition, it is provided that fluid via the LS signal line 108 into a tank connection or other, substantially ambient pressure Return connection R from the other media chamber 80 via an adjustable throttle or aperture 1 10 can drain. A comparable throttle or aperture 10 also has the LS signal line 108.
Ein in der anderen Medienkammer 80 herrschender Fluiddruck beauf- schlagt 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 1 12 beaufschlagt. A fluid pressure prevailing in the other medium 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 disconnects the pressure connection 40 from the supply connection 38 at zero stroke. The valve spool 22 is also acted upon by the energy store in the form of the compression spring 1 12 on its other end face 78.
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 vor- gebbaren 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 appropriate, the control channel 96 adjoining the further fluid channel 84, the pressure regulated by the valve spool 22 between the supply connection 38 and the pressure connection 40 is from a predeterminable displacement of the valve spool 22 in the direction can be limited to the other media chamber 80, namely by discharging excess fluid via the control line 106 in the LS signal line 108 from the other media chamber 80 out with the interposition of the throttle or aperture 99th
Nachfolgend wird die Funktionsweise der Ventilvorrichtung, soweit zum Verständnis der Erfindung notwendig, näher erläutert: Below, the operation of the valve device, as far as necessary for understanding the invention, explained in more detail:
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. In the unactuated state of the valve spool 22, ie at zero stroke (Fig. 2), in which the valve spool 22 is positioned in the stop position in the direction of a media chamber 62, the second control part 44 by means of the cylindrical guide member 50 in abutment with the housing inner wall 52 of the valve housing 18 in the region between supply port 38 and pressure port 40, so that the valve spool 22 is arranged in one of its closed positions SS, in which it blocks the fluid-carrying connection 36 between supply port 38 and pressure port 40. In this Position SS, the further fluid channel 84 and optionally the control channel 96 is covered by the housing inner wall 52 in a sealing manner and the further guide member 56 is with its the other media chamber 80 end facing in sliding contact with the assignable housing inner wall 52nd
Ein am Versorgungsansehl uss 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 1 12 beaufschlagt. Wenn der Fluiddruck am Versorgungsan- schluss 38 den Gegendruck durch den Lastdruck und die Druckfeder 1 12 übersteigt, bewegt sich der Ventilschieber 22, ausgehend von der Schließ- Stellung 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 Versorgungsansehl uss 38 und dem Druckan- schluss 40 auch zunehmend weiter geöffnet wird. A fluid pressure present at the supply port 38 is forwarded via the one fluid channel 68 into the one media chamber 62. There he acts on the adjacent end face 60 of the valve spool 22 a. On the opposite other end face 78 of the valve spool 22 from the load pressure via the LS signal line 108 and the control line 106 and the compression spring 1 12 is applied. When the fluid pressure at the supply port 38 exceeds the counter-pressure by the load pressure and the compression spring 12, the valve spool 22 moves from the closed position SS toward the other medium chamber 80, so that the valve is 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 1 8 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 ücksprung 1 16, in dessen Richtung jedoch vorstehend, begrenzt. Durch diese weitere fluidführende Verbindung 1 18 zwischen den Medienkammern 62,80 kommt es zu einer Druckangleichung zwischen diesen Medienkammern 62, 80. From a predetermined displacement of the valve spool 22, the further fluid-conducting connection 48 is interrupted by closing the first control part 42 at a further closing edge 51 of the housing 1 8 and at the same time the fluid-conducting connection between the media chambers 62, 80, 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 other media chamber 80 facing the end of this control channel 96 to form a corresponding deflection for the other fluid guide 82 has crossed the control edge 90 in the valve housing 18, the valve housing 18 in its housing inner wall 52 and the an annular groove-like from the valve spool 22 pioneering ücksprung 1 16, in the direction but above, limited. Through this further fluid-conducting connection 1 18 between the media chambers 62,80 there is a pressure equalization between these media chambers 62, 80th
Unter der Einwirkung der Druckfeder 1 12 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 zwi- sehen 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 Maximal- wert 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, 1 14 und gegebenenfalls 90, 1 15 wird erreicht, dass der Druck P' vor der Zumessblende 12 definiert eingestellt werden kann und zwar unabhängig von der aktuellen Fluidnachfrage am Verbraucher 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. Under the action of the compression spring 1 12, the valve spool 22 is moved back to the left in the direction of its closed position SS, as long as a pressure equalization in the chambers 62, 80 consists. This effect is enhanced by the fact that fluid from the other media chamber 80 via the control line 106 in the direction of the LS signal line 108 and optionally in the direction of the return port R or tank port throttled only, so it can flow very limited. If the valve spool 22 has moved sufficiently far in the direction of the closed position SS, at least partial sealing overlap of the further fluid channel 84 and optionally of the control channel 96 through the housing inner wall 52 of the valve housing 18 and subsequently to contact of the other media chamber occurs 80 facing end portion of the other guide member 56, whereby the fluid-conducting connection between see the media chambers 62,80 first throttled and subsequently completely separated with increasing displacement of the valve spool 22 to the left. As a result of this mode of operation described above, an equilibrium position normally sets in, which advantageously limits the pressure at the pressure port 40 to a predefinable maximum value. Consequently, overloading of the hydraulic consumer U can no longer occur. Advantageously, the fluid pressure at the pressure connection 40 has a constant pressure difference to the supply connection 38 until the permissible maximum pressure is reached. By the aperture or control cross sections 90, 1 14 and optionally 90, 1 15 it is achieved that the pressure P 'can be set defined before the metering orifice 12, regardless of the current fluid demand at the consumer U. As a result, a valve device is shown, the pressure fluctuations at the supply port 38 can not pass through the pressure balance 9 undamped and thus effectively prevents any overuse of the hydraulic load U and also advantageously improves the performance in the context of the scheme at the same cost-effective implementation.

Claims

P a t e n t a n s p r ü c h e P a n t a n s p r e c h e
Ventilvorrichtung zum Beeinflussen eines Medienstromes zwischen einem Versorgungsansehl uss (38), an den eine Druckversorgungsquelle (P) anschließbar ist, und einem Druckanschluss (40), an den ein hydraulischer Verbraucher (U) anschließbar ist, mit einer Ventileinrichtung (10), die einen Ventilschieber (22) aufweist, der in axialen Verfahrrichtungen innerhalb eines Ventilgehäuses (18) geführt ist und mit seinen gegenüberliegenden Stirnseiten (60, 78) zumindest teilweise zwei Medienkammern (62, 80) innerhalb des Ventilgehäuses (18) begrenzt und der in mindestens einer Schließstellung die Verbindung (36) zwischen dem Versorgungs- (38) und dem Druckanschluss (40) sperrt und der die dahingehende Verbindung (36) in mindestens einer seiner geöffneten Stellungen freigibt, bei denen der Druckanschluss (40) mit zumindest einer der beiden Medienkammern (62, 80) über jeweils eine Fluidführung (64, 82) verbunden ist, von denen eine (64) aus einem im Ventilschieber (22) verlaufenden Fluid- kanal (68) gebildet ist, der mit seinem einen Ende (70) in die eine Medienkammer (62) und mit seinem anderen Ende (72) in einen Fluid- raum (48) im Ventilgehäuse (18) einmündet, der in der zumindest einen Schließstellung des Ventilschiebers (22) vom Druckanschluss (40) getrennt ist und zwischen Versorgungs- (38) und Druckanschluss (40) angeordnet ist, dadurch gekennzeichnet, dass die andere Fluidführung (82) mindestens einen weiteren Fluidkanal (84) aufweist, der von dem ersten Fluidkanal (68) separiert ist und der zumindest in einer der geöffneten Stellungen des Ventilschiebers (22) mit seinem einen Ende (92) in die andere Medienkammer (80) einmündet und der in jeder Verfahrstellung des Ventilschiebers (22) mit seinem anderen Ende (94) permanent an den Druckanschluss (40) angeschlossen ist. Ventilvorrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass der jeweils weitere Fluidkanal (84) parallel zu den axialen Verfahrrichtungen des Ventilschiebers (22) verlaufend angeordnet ist und bei Überfahren einer zuordenbaren Regelkante (90) im Ventilgehäuse (18) quer zu derselben die Fluidführung (82) des jeweils weiteren Fluidkanals (84) eine Umlenkung aus dieser Parallelrichtung erfährt. Valve device for influencing a medium flow between a supply connection (38) to which a pressure supply source (P) can be connected, and a pressure connection (40) to which a hydraulic consumer (U) can be connected, with a valve device (10) having a Valve slide (22) which is guided in axial movement directions within a valve housing (18) and with its opposite end faces (60, 78) at least partially two media chambers (62, 80) within the valve housing (18) limited and in at least one closed position the connection (36) between the supply (38) and the pressure port (40) blocks and releases the pending connection (36) in at least one of its open positions, wherein the pressure port (40) communicates with at least one of the two media chambers (62 , 80) is connected in each case via a fluid guide (64, 82), of which one (64) consists of a fluid flowing in the valve slide (22) - Channel (68) is formed, which opens with its one end (70) in the one medium chamber (62) and with its other end (72) in a fluid chamber (48) in the valve housing (18) in the at least a closed position of the valve spool (22) is separated from the pressure port (40) and between supply (38) and pressure port (40) is arranged, characterized in that the other fluid guide (82) at least one further fluid channel (84), of the first fluid channel (68) is separated and at least in one of the open positions of the valve slide (22) opens with its one end (92) in the other medium chamber (80) and in each Verfahrstellung the valve spool (22) with its other end (94) is permanently connected to the pressure port (40). Valve device according to claim 1, characterized in that the respective further fluid channel (84) is arranged to run parallel to the axial directions of movement of the valve slide (22) and when passing a assignable control edge (90) in the valve housing (18) transversely to the same, the fluid guide (82 ) of the respective further fluid channel (84) undergoes a deflection from this parallel direction.
Ventilvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass an das eine Ende (92) des jeweils weiteren Fluidkanals (84), das in Richtung der anderen Medienkammer (80) weist, sich mindestens ein Steuerkanal (96) anschließt, der gegenüber dem weiteren Fluidkanal (84) über einen geänderten, insbesondere verringerten Kanalquerschnitt verfügt. Valve device according to claim 1 or 2, characterized in that at one end (92) of the respective further fluid channel (84) facing in the direction of the other medium chamber (80), at least one control channel (96) adjoins, with respect to the other Fluid channel (84) has a modified, in particular reduced channel cross-section.
Ventilvorrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Kanalquerschnitt sich, ausgehend vom jeweils weiteren Fluidkanal (84), in Richtung des jeweiligen Steuerkanals (96) zumindest im Bereich der zuordenbaren Regelkante (90) unter Bildung einer Blende (98) mit derselben verringert. Valve device according to one of the preceding claims, characterized in that the channel cross section, starting from the respective further fluid channel (84) in the direction of the respective control channel (96) at least in the region of the assignable control edge (90) to form a diaphragm (98) with the same reduced.
Ventil Vorrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der jeweilige Steuerkanal (96), im Querschnitt gesehen, in Richtung der einen freien Stirnseite (78) des Ventilschiebers (22), die zumindest teilweise die andere Medienkammer (80) begrenzt, sich konisch verjüngt und mit seinem dem jeweils zuordenbaren Fluidkanal (84) zugewandten Ende (100) unter Bildung einer absatzartigen Fluidführungsstufe (102) in diesen einmündet. Valve device according to one of the preceding claims, characterized in that the respective control channel (96), seen in cross-section, in the direction of a free end face (78) of the valve spool (22) which at least partially delimits the other medium chamber (80) itself conically tapered and with its the respective assignable fluid channel (84) facing the end (100) to form a heel-like fluid guide stage (102) opens into this.
6. Ventil Vorrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass bei einer Abwicklung einer Steuerkante (1 14) des Ventilschiebers (22) im Bereich der mindestens einen Regelkante (90) im Ventilgehäuse (18) in einer Ebene deren Gesamtlänge größer ist als die Summe der einzelnen Abwicklungen, bezogen auf dieselbe Ebene, der freien Öffnungen (74) des einen im Ventilschieber (22) verlaufenden Fluidkanals (68) im Bereich seines jeweils anderen Endes (72), das in den Fluidraum (48) im Ventilgehäuse (18) ausmündet. 7. Ventilvorrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der jeweils weitere Fluidkanal (84) aus einem radialen Wandabstand (89) zwischen Ventilschieber (22) und Ventilgehäuse (18) gebildet ist. 8. Ventilvorrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der radiale Wandabstand (89) zwischen Ventilgehäuse (18) und Ventilschieber (22) durch eine gleichförmig verlaufende Durchmesserreduzierung (86) im Ventilschieber (22), bezogen auf den Durchmesser (88) der freien Stirnseite (78) des Ventilschiebers (22), in Richtung der anderen Medienkammer (80) gebildet ist und dass bei im Bedarfsfall vorhandenem Steuerkanal (96) dieser jeweils in einen derart gebildeten Fluidringkanal permanent fluidführend einmündet. 9. Ventilvorrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die im Ventilgehäuse (18) verlaufende Regelkante (90) den in der Regelstellung befindlichen Ventilschieber (22) um- fasst und einen nutartigen vom Ventilschieber (22) wegweisenden Rücksprung (1 16) in dessen Richtung vorstehend begrenzt. 6. Valve device according to one of the preceding claims, characterized in that in a development of a control edge (1 14) of the valve spool (22) in the region of the at least one control edge (90) in the valve housing (18) in a plane whose overall length is greater than the sum of the individual settlements, related to the same Level, the free openings (74) of one in the valve spool (22) extending fluid channel (68) in the region of its other end (72), which opens into the fluid chamber (48) in the valve housing (18). 7. Valve device according to one of the preceding claims, characterized in that the respective further fluid channel (84) from a radial wall distance (89) between the valve slide (22) and the valve housing (18) is formed. 8. Valve device according to one of the preceding claims, characterized in that the radial wall distance (89) between the valve housing (18) and valve slide (22) by a uniform diameter reduction (86) in the valve slide (22), based on the diameter (88). the free end face (78) of the valve slide (22), in the direction of the other medium chamber (80) is formed and that in case of need existing control channel (96) this opens in each case in a fluid ring channel thus formed permanently fluid leading. 9. Valve device according to one of the preceding claims, characterized in that in the valve housing (18) extending control edge (90) surrounds the control valve located in the control position (22) and a groove-like from the valve spool (22) pioneering return (1 16) limited in the direction above.
10. Ventilvorrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass bei einer Endstellung, insbesondere bei einer Anschlagstellung des Ventilschiebers (22) in Richtung der anderen Medienkammer (80) der jeweils weitere Fluidkanal (84) unter Bildung einer 90°-Umlenkung für die Fluidführung (82) die Regelkante (90) überfahren hat und bei etwaig vorhandenem Steuerkanal (96) dieser in Höhe der Regelkante (90) in den jeweils weiteren Fluidkanal (84) end- seitig ausmündet. 10. A valve device according to one of the preceding claims, characterized in that at one end position, in particular at a stop position of the valve spool (22) in the direction of the other media chamber (80) of each further fluid channel (84) to form a 90 ° deflection for Fluid guide (82) has run over the control edge (90) and at any existing control channel (96) this at the level of the control edge (90) in the respective further fluid channel (84) terminates end side.
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

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

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

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* 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

Family Cites Families (12)

* 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
CH421639A (en) 1964-04-10 1966-09-30 Essa Maschinenfabrik Ag High pressure control valve
US3534774A (en) 1968-11-14 1970-10-20 Koehring Co Pressure compensated control valve
DE1955659A1 (en) 1969-11-05 1971-05-13 Linde Ag Control device for a hydraulic actuator
US3685540A (en) 1971-01-18 1972-08-22 Koehring Co Fluid flow controlling device for reversible fluid motors
US3747642A (en) 1971-10-26 1973-07-24 Koehring Co Throttle notches for control valve spools
US4941508A (en) 1989-12-28 1990-07-17 Dana Corporation Force balanced hydraulic spool valve
DE19851553B4 (en) * 1998-03-19 2008-03-20 Linde Material Handling Gmbh control valve
DE10258517B3 (en) 2002-12-14 2004-06-03 Sauer-Danfoss (Nordborg) A/S Hydraulic valve arrangement
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
DE102014003086A1 (en) 2014-03-01 2015-09-03 Hydac Filtertechnik Gmbh valve device

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WO2017220193A1 (en) 2017-12-28
US10914325B2 (en) 2021-02-09
DE102016007754A1 (en) 2018-01-11
US20190120260A1 (en) 2019-04-25
CN209925319U (en) 2020-01-10
EP3475585B1 (en) 2020-08-19

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