EP3475585B1 - Dispositif soupape servant à influencer un flux de fluide - Google Patents

Dispositif soupape servant à influencer un flux de fluide Download PDF

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

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/026—Pressure compensating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/008—Throttling member profiles

Definitions

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

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

Claims (10)

  1. Système de soupape pour influencer une courant de fluide entre un raccord (38) d'alimentation, auquel une source (P) d'alimentation en pression peut être raccordée, et un raccord (40) de pression, auquel un consommateur (U) hydraulique peut être raccordé, comprenant un dispositif (10) de soupape ayant un obturateur (22) de soupape, qui est guidé, dans des directions de déplacement axiales, dans un corps (18) de soupape, qui délimite, par ses côtés (60, 78) frontaux opposés, au moins en partie, deux chambres (62, 80) pour des fluides à l'intérieur du corps (18) de soupape et qui, dans au moins une position de fermeture, barre la liaison (36) entre le raccord (38) d'alimentation et le raccord (40) de pression et dégage la liaison (36) dans au moins l'une de ses positions d'ouverture, pour lesquelles le raccord (40) de pression communique avec au moins l'une des deux chambres (62, 80) pour des fluides par l'intermédiaire respectivement d'une conduite (64, 82) de fluide, dont l'une (64) est formée d'un conduit (68) pour du fluide s'étendant dans l'obturateur (22) de soupape et débouchant, par l'une de ses extrémités (70), dans la une chambre (62) pour des fluides, par son autre extrémité (72), dans un espace (48) pour du fluide dans le corps (18) de la soupape, espace qui, dans au moins une position de fermeture de l'obturateur (22) de soupape, est séparé du raccord (40) sous pression et est disposé entre le raccord (38) d'alimentation et le raccord (40) de pression, caractérisé en ce que l'autre conduite (82) de fluide a au moins un autre conduit (84) pour du fluide, qui est séparé du premier conduit (68) pour du fluide et qui débouche, au moins dans l'une des positions d'ouverture de l'obturateur (22) de soupape, par l'une de ses extrémités (92) dans l'autre chambre (80) pour des fluides et qui est raccordé dans chaque position de déplacement de l'obturateur (22) de soupape de la soupape par son autre extrémité (94) en permanence au raccord (40) de pression.
  2. Système de soupape suivant la revendication 1, caractérisé en ce que le respectivement autre conduit (84) pour du fluide est disposé en s'étendant parallèlement aux directions de déplacement axiales de l'obturateur (22) de soupape et, lors du passage sur un bord (90) de réglage pouvant être associé dans le corps (18) de soupape transversalement à celui-ci, la conduite (82) de fluide de l'autre conduit (84) pour du fluide subit une déviation hors de cette direction parallèle.
  3. Système de soupape suivant la revendication 1 ou 2, caractérisé en ce que, à l'une des extrémités (92) de respectivement l'autre conduit (84) pour du fluide, qui est tournée vers la direction de l'autre chambre (80) pour des fluides, se raccorde au moins un autre conduit (96) de commande, qui, par rapport à l'autre conduit (84) pour du fluide, dispose d'une section transversale de conduit modifiée, notamment diminuée.
  4. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que la section transversale de conduit, en partant de respectivement l'autre conduit (84) pour du fluide, diminue dans la direction du conduit (96) de commande respectif, au moins dans la région du bord (90) de réglage pouvant être associé, avec formation d'un diaphragme (98) avec celui-ci.
  5. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que le conduit (96) de commande respectif se rétrécit coniquement, considéré en section transversale, dans la direction du un côté (78) frontal libre de l'obturateur (22) de soupape délimitant, au moins en partie, l'autre chambre (80) pour des fluides et débouche par son extrémité (100) tournée vers le conduit (84) pour du fluide respectif pouvant être associé, avec formation d'un gradin (102) de conduite de fluide de type en ressaut, dans celui-ci.
  6. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que, dans un développement d'un bord (114) de commande de l'obturateur (22) de soupape, dans la région du au moins un bord (90) de réglage dans le corps (18) de soupape dans un plan dont la longueur totale est plus grande que la somme des développements individuels rapportée à ce même plan, l'ouverture (74) libre du un conduit (68) pour du fluide s'étendant dans l'obturateur (22) de soupape dans la région de son autre extrémité (72) débouche dans l'espace (48) pour du fluide du corps (18) de la soupape.
  7. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que l'autre conduit (84) respectif pour du fluide est formé d'une distance (89) radiale de paroi entre l'obturateur (22) de soupape et le corps (18) de soupape.
  8. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que la distance (89) radiale de paroi entre le corps (18) de soupape et l'obturateur (22) de soupape est formée par une réduction (86) de diamètre s'étendant uniformément dans l'obturateur (82) de soupape, rapportée au diamètre (88) du côté (78) frontal libre de l'obturateur (22) de soupape, dans la direction de l'autre chambre (80) pour des fluides et en ce que, dans le cas d'un conduit (96) de commande présent en cas de besoin, celui-ci débouche fluidiquement en permanence dans un conduit annulaire pour du fluide ainsi formé.
  9. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que le bord (90) de réglage s'étendant dans le corps (18) de soupape comprend l'obturateur (22) de soupape se trouvant en la position de réglage et délimite un ressaut (116) de type en rainure s'éloignant de l'obturateur (22) de soupape en saillie dans la direction de ce ressaut.
  10. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que, en une position finale, notamment en une position de butée de l'obturateur (22) de soupape, dans la direction de l'autre chambre (80) pour des fluides, l'autre conduit (84) respectif pour du fluide est passé au-dessus en formant une déviation de 90° de la conduite (82) de fluide du bord (90) de réglage et, si un conduit (96) de commande est éventuellement présent, celui-ci débouche au niveau du bord (90) de réglage dans l'autre conduit (84) respectif pour du fluide du côté de l'extrémité.
EP17732747.5A 2016-06-24 2017-06-16 Dispositif soupape servant à influencer un flux de fluide Active EP3475585B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016007754.9A DE102016007754A1 (de) 2016-06-24 2016-06-24 Ventilvorrichtung zum Beeinflussen eines Medienstromes
PCT/EP2017/000700 WO2017220193A1 (fr) 2016-06-24 2017-06-16 Dispositif soupape servant à influencer un flux de fluide

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

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EP (1) EP3475585B1 (fr)
CN (1) CN209925319U (fr)
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WO (1) WO2017220193A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102019101133A1 (de) * 2019-01-17 2020-07-23 Gkn Automotive Limited Ventilanordnung mit zumindest einem wegeventil sowie kupplungseinrichtung mit einer solchen ventilanordnung
DE102019211004A1 (de) * 2019-07-25 2021-01-28 Festo Se & Co. Kg Ventil

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DE1956621A1 (de) 1968-11-14 1970-07-23 Koehring Company Inc Steuerschieber
DE1955659A1 (de) 1969-11-05 1971-05-13 Linde Ag Steuereinrichtung fuer eine hydraulische Stelleinrichtung
DE2200568A1 (de) 1971-01-18 1972-08-03 Koehring Co Durchflussregler
DE2248891C3 (de) 1971-10-26 1981-08-13 Koehring Co., Milwaukee, Wis. Schieberkolben für ein hydraulisches Mehrwegeventil
DE4040523A1 (de) 1989-12-28 1991-07-04 Dana Corp Kraftausgeglichener, hydraulischer kolbenschieber
DE19851553A1 (de) 1998-03-19 1999-09-23 Linde Ag Steuerventil
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DE60304663T2 (de) 2002-12-14 2006-08-31 Sauer-Danfoss Aps Hydraulische Ventileinrichtung
DE102013014671A1 (de) 2013-09-03 2015-03-05 Hydac Technology Gmbh Ventilbaukomponenten
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DE1090044B (de) 1958-05-29 1960-09-29 Her Majesty The Queen In The R Steuerschieber zur selbsttaetigen, sich wiederholenden Zufuehrung eines Druckmittels von einem Einlass zu zwei verschiedenen Anschluessen
DE6600855U (de) 1964-04-10 1969-01-23 Essa Maschinenfabrik Ag Vorm S Hochdruck-steuerschieber
DE1956621A1 (de) 1968-11-14 1970-07-23 Koehring Company Inc Steuerschieber
DE1955659A1 (de) 1969-11-05 1971-05-13 Linde Ag Steuereinrichtung fuer eine hydraulische Stelleinrichtung
DE2200568A1 (de) 1971-01-18 1972-08-03 Koehring Co Durchflussregler
DE2248891C3 (de) 1971-10-26 1981-08-13 Koehring Co., Milwaukee, Wis. Schieberkolben für ein hydraulisches Mehrwegeventil
DE4040523A1 (de) 1989-12-28 1991-07-04 Dana Corp Kraftausgeglichener, hydraulischer kolbenschieber
DE19851553A1 (de) 1998-03-19 1999-09-23 Linde Ag Steuerventil
DE60304663T2 (de) 2002-12-14 2006-08-31 Sauer-Danfoss Aps Hydraulische Ventileinrichtung
DE102004003893A1 (de) 2003-01-31 2004-08-12 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Schieber für ein Schieberventil sowie Verfahren und Formwerkzeug zum Herstellen eines Schiebers
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DE102014003086A1 (de) 2014-03-01 2015-09-03 Hydac Filtertechnik Gmbh Ventilvorrichtung

Also Published As

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

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