EP3042087B1 - Éléments de vanne - Google Patents

Éléments de vanne Download PDF

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Publication number
EP3042087B1
EP3042087B1 EP14765869.4A EP14765869A EP3042087B1 EP 3042087 B1 EP3042087 B1 EP 3042087B1 EP 14765869 A EP14765869 A EP 14765869A EP 3042087 B1 EP3042087 B1 EP 3042087B1
Authority
EP
European Patent Office
Prior art keywords
fluid
pocket
apex
valve
control part
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.)
Active
Application number
EP14765869.4A
Other languages
German (de)
English (en)
Other versions
EP3042087A2 (fr
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 Technology GmbH
Original Assignee
Hydac Technology GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydac Technology GmbH filed Critical Hydac Technology GmbH
Publication of EP3042087A2 publication Critical patent/EP3042087A2/fr
Application granted granted Critical
Publication of EP3042087B1 publication Critical patent/EP3042087B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B13/04—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
    • 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
    • F15B2013/008—Throttling member profiles

Definitions

  • the invention relates to a pressure compensator with the features in the preamble of claim 1.
  • the EP 1 500 825 A2 a pressure compensator with a valve slide which is longitudinally displaceable in a valve housing and which has a control part for controlling a fluid-carrying connection between at least two fluid connection points received in the valve housing, which has at least one pocket-like recess that is at least partially delimited by a fluid-guiding surface that at least runs between two vertices of the recess and which, starting from one vertex to the other vertex, runs with an initially increasing and then constant slope, the other vertex, which is located at the exit of the pocket-like recess, delimiting the edge or corner of a right angle as a transition between the Fluid guide surface and a transverse collar surface of the valve or control slide.
  • the invention is based on the object of providing a pressure compensator with improved control quality and increased stability, which reacts with little delay.
  • the pressure compensator is characterized in that, starting from a predeterminable distance from the other vertex, the fluid guide surface runs from its greatest slope with a decreasing slope in the direction of the other vertex.
  • the pocket-like depression does not open out at one edge, but rather flows smoothly into a collar-like recess adjacent to the depression Front face of the control part as part of the valve slide.
  • This has the advantage that the standard cross section does not change abruptly at an edge, as shown in the prior art. Therefore, the course of the standard cross-section over the opening stroke does not have a kink, but a steady, monotonically increasing standard cross-section with a very flat initial slope is implemented over the opening stroke of the valve slide with its control part, so that there is a very high control quality, especially at the beginning of the opening process, and over a relatively long opening stroke of the valve slide. The control quality is therefore considerably higher than with known solutions and the stability of the control is also improved.
  • the fluid guide surface has a steady course and the smallest amount of slope or amount of slope, preferably assuming the value zero, at the respective other vertex.
  • the fluid guide surface is particularly preferably designed in a curve (S-shape) and the different gradient profiles between the vertices are implemented by the transition from a concave to a convex curve profile.
  • the curve shape is formed by other arc shapes, in particular semicircles.
  • Such a rounded guide surface also contributes to a constant, "kink-free" control behavior of the valve component.
  • two fluid guide surfaces which are adjacent to one another and which merge into one another at the bottom of the pocket form the edge-side boundary for this pocket.
  • the respective fluid guide surface can be formed by several flat surface sections arranged one behind the other is formed, each surface section preferably having a uniform slope which corresponds to the slope of the curve profile of the fluid guide surface in a central region of the respective surface section.
  • the course of the fluid guide surface can also be iteratively approximated by step-like shoulders, wherein the surfaces of the shoulders can be aligned coaxially or transversely to the longitudinal axis of the valve slide.
  • a groove-like depression adjoins the pocket-like depression on the bottom side in the region of an apex.
  • the largest opening cross-section of the respective pocket-like depressions is directed towards that fluid connection point which is used for the fluid outlet from the valve housing. In this way, as the opening stroke of the valve slide increases, the standard cross section can be continuously adapted to the increasing amounts of fluid.
  • Another valve component is characterized in that the guide part has a stepped switching edge surface which faces the first control part.
  • a defined trailing edge is formed at which the flow surface merges from an annular transverse surface running in the radial plane at one edge into an outer circumferential surface running coaxially to the longitudinal axis of the valve slide.
  • the stepped switching edge surface improves the sealing function within the second valve component.
  • the step-like switching edge surface running in the guide part of the second control part can be formed via a diameter reduction between the outer circumferential side of the guide part and a preferably conical transition part of the valve slide in the direction of the first control part.
  • the conically running transition part forms a flow guide that serves to compensate for the flow force.
  • Another valve component is characterized in that there is a further fluid guide which keeps the second control part at a distance from the second guide part.
  • Such a puncture advantageously improves the flow around the second control part and facilitates the resetting of the valve slide.
  • the sealing gap between the first guide part and the inner wall of the housing is reduced, which promotes the load-holding function of the second valve component described above.
  • the two fluid guides, the axial distances between the first control part and the second control part and between the second control part and the second guide part are obtained by groove-like circumferential diameter reductions in the valve slide. These diameter reductions result in a broad, free, ring-shaped cross section through which the fluid can flow with low pressure losses, which is also beneficial to rapid control behavior due to the low mass.
  • the valve slide can be supported on its one free end face against an energy store and on its other free end face it can be adjacent to a volume space of variable volume into which one end of an inner channel of the valve slide opens, the other end of which is connected to the fluid guide between the two control parts in a fluid-carrying manner is. In this way, the fluid pressure at the fluid inlet can be mapped efficiently on the other free end face. No further complex holes in the valve housing are required.
  • FIG. 1 a part of a valve construction 10, especially designed in the manner of a pressure compensator, is shown.
  • a valve housing 12 has a valve bore 14 in which a valve slide 16 which is guided so that it can be moved longitudinally is arranged.
  • the valve bore 14 is closed at both ends 18 by end screws 20, 22 which each engage in an assignable internal thread 24 of the valve bore 14.
  • Annular sealing elements 26 are provided between the end screws 20, 22 and the valve housing 12.
  • the valve slide 16 is provided for controlling a fluid-carrying connection 28 between at least two fluid connection points 30, 32 received in the valve housing 12.
  • the valve slide 16 has a cylindrical first control part 34, which on the outer circumference 36 has pocket-like depressions 38 running coaxially to the longitudinal axis LA of the valve slide 16 (see also FIG Fig.
  • the respective fluid guide surface 40 thus has a steady course and the smallest slope amount (S1, S7; S11, S17), preferably assuming the value zero, at the respective other vertex M2, M3; M1.
  • the fluid guide surface 40 is designed in the shape of a curve and the different gradients S2, S3, S4, S5, S6; S12, S13, S14, S15, S16 between the vertices M1, M2, M3 are implemented by a transition at the reversal points UP1, UP2 from a concave to a convex curve.
  • the fluid guide surfaces 40 between the individual vertices M1, M2, M3 form a closed, cosine-shaped curve along this outer circumference 36.
  • a groove-like depression 50 adjoins the pocket-like depression 38 on the bottom side in the region of the apex M1.
  • the largest opening cross-section 52 of the respective pocket-like depression 38 is directed towards that fluid connection point 32 which is used for the fluid outlet 54 from the valve housing 12. Thanks to the groove-like recess 50, the control behavior of the valve slide 16 is improved overall.
  • the valve slide 16 has a total of two control parts 34, 56, of which the first control part 34 has at least the pocket-like depressions 38 and the second control part 56 is arranged at a distance from the first control part 34 by a first fluid guide 58.
  • the second control part 56 is in the unactuated state of the valve slide 16, that is to say in the zero stroke shown in the left end position in the image plane and by means of a cylindrical guide part 60 in contact with an inner wall 62 of the housing.
  • the guide part 60 has a stepped switching edge surface 64 which faces the first control part 34.
  • the switching edge surface 64 is formed by a diameter reduction 66 between the outer peripheral side 68 of the guide part 60 and a preferably conical transition part 70 of the valve slide 16 in the direction of the first control part 34.
  • the conically running transition part 70 forms a flow guide for the fluid flowing through the valve component 10 and causes the fluid flow to be deflected in the direction of the fluid outlet 54. It also contributes to the flow force compensation.
  • the transition part 70 can either be attached directly to the diameter reduction 66 ( Fig. 4 ) or via a diameter reduction 66 in the form of a recess ( Fig. 5 ) merge into the annular transverse surface to the longitudinal axis LA in the form of the switching edge surface 64, which adjoins the switching edge 72 on the outer peripheral side 68 of the cylindrical guide part 60. Through the recess 66 in Fig. 5 the switching edge area 64 is displaced downstream.
  • valve slide 16 is guided through its inner wall 62 in the region of the fluid connection point 32 serving the fluid outlet 54 in the valve housing 12.
  • a first fluid guide 58 keeping them at a distance.
  • a second fluid guide 76 between the second control part 56 and the second guide part 74 now improves the flow around the valve slide 16 in the region of the second control part 56, as a result of which the pressure losses within the valve component 10 are reduced.
  • the sealing behavior of the first guide part 60 with respect to the housing inner wall 62 is improved by the second fluid guide 76, since the sealing gap between the valve slide 16 and the housing inner wall 62 can be reduced by introducing the second fluid guide 76 into the valve slide 16.
  • the two fluid guides 58, 76 which form the axial distances ASS, ASF between the first control part 34 and the second control part 56 and between the second control part 56 and the second guide part 74, are obtained by groove-like diameter reductions 78, 80 in the valve slide 16. Such diameter reductions 78, 80 are also referred to as recesses.
  • the valve slide 16 is supported on its one free end face 82 against an energy store 84 in the form of a compression spring. Guides 86, 88 for the energy store 84 are formed on the valve slide 16 and on the opposite end screw 22. On its other free end 90, the valve slide 16 adjoins a volume space 92 of variable volume, into which an inner channel 94 of the valve slide 16 opens at its one end 96, the other end 98 of which enters the first fluid guide 58 between the two control parts 34, 56, directly adjacent to the transition part 70 opens out.
  • a corresponding fluid channel 100 is provided in the valve housing 12 to map the fluid pressure according to at least one fixed or adjustable measuring orifice 99 on the one free end face 82 of the valve slide 16.
  • the graph of the Fig. 6 shows the course of the standard cross-section over the opening stroke. From a defined opening stroke, the first guide part 60 is out of contact with the housing inner wall 62, so that the load-holding function is overcome and fluid from the fluid connection point 30, which forms the fluid inlet 102, to the fluid connection point 32, which forms the fluid outlet 54, can flow. Starting from this opening stroke, the standard cross section increases disproportionately with the increasing opening stroke, until the standard cross section increases proportionally to the opening stroke from a kink-free transition. According to the invention, the control quality and the stability are essentially due to a monotonically increasing increase over the opening stroke Standard cross-section without kinks and with a very flat initial slope improved.
  • the invention therefore shows particularly advantageous pressure balances.
  • the pocket-like depressions 38 no longer open out at an edge, but rather merge smoothly into the end face 104 of the first control part 34.
  • This has the advantage that the standard cross-section does not change abruptly at an edge. Therefore, the course of the standard cross-section does not have a kink over the opening stroke (cf. Fig. 6 ).
  • the control quality of the valve components 10 is therefore considerably higher and the stability of the control is also improved.
  • a trailing edge 72 is provided on the second control part, at which the flow surface merges from an annular switching edge surface 64 extending in the radial plane into an outer circumferential surface 68 extending coaxially to the longitudinal axis LA of the valve slide 16.
  • a load-holding function for the valve is implemented particularly favorably by the step-like switching edge surface 64. This prevents fluid from flowing from the fluid outlet 54 to the fluid inlet 102 against the normal flow direction.
  • the further fluid guide 76 advantageously improves the flow around the second control part 56 and facilitates the resetting of the valve slide 16.
  • the further fluid guide 76 advantageously reduces the sealing gap between the first guide part 60 and the housing inner wall 62.

Landscapes

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

Claims (6)

  1. Balance manométrique, comprenant un tiroir (16) de vanne, qui est guidé avec possibilité de se déplacer longitudinalement dans un corps (12) de vanne et qui, pour commander une liaison (28) fluidique entre au moins deux points (30, 32) de raccord pour du fluide reçus dans le corps (12) de la vanne, a une partie (34) de commande, qui a au moins une cavité de type en poche, délimitée au moins en partie par une surface (40) de conduite de fluide, qui s'étend au moins entre deux points (M1, M2, M3) culminents de la cavité (38) et qui a, à partir d'un point (M1, M2, M3) culminent, en direction de l'autre point (M2, M3 ; M1) culminent, une pente (S1, S2, S3, S4 ; S11, S12, S13, S14) croissante en valeur absolue, caractérisée en ce que la surface (40) de conduite de fluide s'étend à partir d'une distance (A1 ; A2) pouvant être donnée à l'avance de l'autre point (M2, M3 ; M1) culminent, en partant de sa pente (S4 ; S14) la plus grande, avec une pente (S4, S5, S6, S7 ; S14, S15, S16, S17) diminuant en valeur absolue, en direction de cet autre point (M2, M3 ; M1) culminent.
  2. Balance manométrique suivant la revendication 1, caractérisée en ce que la surface (40) de conduite de fluide a un tracé constant et a la valeur absolue de pente la plus petite, en prenant, de préférence, la valeur zéro, à l'autre point (M1, M2, M3) culminent respectif.
  3. Balance manométrique suivant la revendication 1 ou 2, caractérisée en ce que la surface (40) de conduite de fluide est de forme incurvée et en ce que les tracés de pente différents entre les points (M1, M2, M3) culminents sont réalisés par la transition d'un tracé concave à un tracé convexe de la courbe.
  4. Balance manométrique suivant l'une des revendications précédentes, caractérisée en ce que plusieurs cavités (38) de type en poche sont disposées suivant le pourtour (36) extérieur de la partie (34) de commande du tiroir (16) de vanne, de manière à ce que les surfaces (40) de conduite de fluide entre les divers points (M1, M2, M3) culminents forment, le long de ce pourtour (36) extérieur, un tracé de courbe fermé, sinusoïdal ou cosinusoïdal.
  5. Balance manométrique suivant l'une des revendications précédentes, caractérisée en ce qu'une cavité (50) de type en rainure se raccorde, au moins pour une partie des cavités (38) de type en poche dans la région d'un point (M2) culminent, du côté du fond, à la cavité (38) de type en poche.
  6. Balance manométrique suivant l'une des revendications précédentes, caractérisée en ce que la section (52) transversale d'ouverture la plus grande de la cavité (38) respective de type en poche est dirigée vers le point (32) de raccord pour du fluide, qui sert à faire sortir (54) le fluide du corps (12) de la vanne.
EP14765869.4A 2013-09-03 2014-09-02 Éléments de vanne Active EP3042087B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013014671.2A DE102013014671A1 (de) 2013-09-03 2013-09-03 Ventilbaukomponenten
PCT/EP2014/002382 WO2015032492A2 (fr) 2013-09-03 2014-09-02 Composants de soupape

Publications (2)

Publication Number Publication Date
EP3042087A2 EP3042087A2 (fr) 2016-07-13
EP3042087B1 true EP3042087B1 (fr) 2020-11-25

Family

ID=51539229

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14765869.4A Active EP3042087B1 (fr) 2013-09-03 2014-09-02 Éléments de vanne

Country Status (5)

Country Link
US (1) US10167881B2 (fr)
EP (1) EP3042087B1 (fr)
CN (1) CN205956083U (fr)
DE (1) DE102013014671A1 (fr)
WO (1) WO2015032492A2 (fr)

Families Citing this family (5)

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US9476188B2 (en) 2012-06-22 2016-10-25 Kohler Mira Limited System and method for remotely disinfecting plumbing fixtures
DE102016007754A1 (de) * 2016-06-24 2018-01-11 Hydac System Gmbh Ventilvorrichtung zum Beeinflussen eines Medienstromes
GB2568271B (en) 2017-11-09 2020-04-22 Kohler Mira Ltd A plumbing component for controlling the mixture of two supplies of water
JP6452791B1 (ja) * 2017-11-28 2019-01-16 三菱ロジスネクスト株式会社 コントロールバルブおよびフォークリフト
US11680649B2 (en) * 2020-11-16 2023-06-20 Parker-Hannifin Corporstion Proportional valve spool with linear flow gain

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Also Published As

Publication number Publication date
EP3042087A2 (fr) 2016-07-13
DE102013014671A1 (de) 2015-03-05
WO2015032492A2 (fr) 2015-03-12
CN205956083U (zh) 2017-02-15
US10167881B2 (en) 2019-01-01
WO2015032492A3 (fr) 2015-07-30
US20160201695A1 (en) 2016-07-14

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