EP3042087A2 - Valve components - Google Patents
Valve componentsInfo
- Publication number
- EP3042087A2 EP3042087A2 EP14765869.4A EP14765869A EP3042087A2 EP 3042087 A2 EP3042087 A2 EP 3042087A2 EP 14765869 A EP14765869 A EP 14765869A EP 3042087 A2 EP3042087 A2 EP 3042087A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- fluid
- control part
- guide
- control
- 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
Links
- 239000012530 fluid Substances 0.000 claims abstract description 69
- 230000003247 decreasing effect Effects 0.000 claims abstract description 4
- 238000010276 construction Methods 0.000 claims description 13
- 230000007704 transition Effects 0.000 claims description 11
- 230000009467 reduction Effects 0.000 claims description 10
- 230000002093 peripheral effect Effects 0.000 claims description 5
- 238000004146 energy storage Methods 0.000 claims description 3
- 238000007789 sealing Methods 0.000 description 6
- 230000008901 benefit Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 210000000629 knee joint Anatomy 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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 first valve component, in particular designed in the manner of a pressure compensator, with a longitudinally movable in a valve housing valve slide, which has a control part for controlling a fluid 2015- the connection between at least two fluid connection points accommodated in the valve housing, the at least one pocket-like depression which is at least partially bounded by a fluid guide surface which runs at least between two vertexes of the depression and which, starting from one vertex in the direction of the other vertex, has a gradient increasing in magnitude.
- the invention further relates to a second valve component, in particular designed in the manner of a pressure compensator, having a valve housing in a longitudinally movable valve slide, which has two control parts for driving a fluid-carrying connection between at least two fluid connection points accommodated in the valve housing, of which at least one control part at least has a pocket-like recess, wherein the further control part in the unactuated state by means of a guide member into contact with a housing inner wall, along which the valve slide is movably guided.
- the invention relates to a third valve construction component, in particular designed in the manner of a pressure compensator, with one in a Ven- Tilgephaseuse longitudinally movable guided valve spool, which len for driving a fluid-carrying connection between at least two housed in Venti housing Fl uid Anschlußstel len a first control part and a second Steuerertei l, wherein the second Steuerertei l by means of a guide Stel ls into contact with a housing inner wall along which the valve slide is movably guided, wherein by means of a further disruptsstei ls the Venti lschieber in the region of the fluid outlet Rastel le in Venti lgephaseuse is guided through the inner wall and wherein between the first and second Steuerertei l this Steuerertei le on distance retaining fluid guide is arranged.
- EP 1 500 825 A2 discloses a pressure compensator with a valve slide guided in a longitudinally movable manner in a valve housing, which has a control part for driving a fluid-conducting connection between at least two fluid-immersed housings in the valve housing, which is at least one pocket-like Recess which is delimited at least partially by a Fl uid guide surface, the at least runs between two vertices of the depression and extending from one vertex to the other vertex with initially increasing and then constant slope, the other vertex on the Output of the pocket-like recess is arranged, the edge or Eckstel le of a right Wi nkels limited as a transition between the fluid guide surface and a transverse thereto extending collar surface of the Venti l or spool.
- such pressure compensators have shown that, starting from the neutral stroke, the course of the active control cross section over the opening stroke increases very sharply and, at least in the further course, has at least one knee joint. Due to this course of the control cross-section over the opening stroke, the control quality and the stability are the known Pressure balances in need of improvement to increase the precision of fluid control.
- the invention is based on the prior art based on the object to show at least one valve component with improved control quality and increased stability, which reacts delay.
- the first Venti lbaukomponente is characterized in that the fluid guide surface extends from a predetermined distance from the other vertex, starting from its largest slope with decreasing in magnitude slope in the direction of the other vertex.
- the pocket-like recess does not open at an edge, but flows flußing in a collar-like, adjacent to the recess end face of the Steuerertei ls as part of the Venti lschiebers over.
- control cross section over the opening stroke also no kink, but it is realized via the opening stroke of the valve spool with its control part a steady, monotonically increasing control cross section with very flat initial slope, so that especially at the beginning of the opening process a very high control quality prevails , over a relatively long opening stroke of the Venti lschiebers away.
- control quality is considerably higher than in known solutions, and the stability of the control is also improved.
- the fluid guide surface has a steady course and the least amount of slope or amount of slope, preferably assuming the value zero, at the respective other vertex.
- the fluid guide surface is curved (S-shape) and the different gradient gradients between the vertexes are implemented by the transition from a concave to a convex curve.
- the course of the curve is defined by other shapes of curves, in particular semicircles.
- a guide surface of such a rounded design also contributes to a continuous, "kink-free" control behavior of the valve component, in particular two adjoining fl uid guide surfaces, which merge into one another at the pocket, the edge boundary for this pocket ,
- the respective guide surface is formed by a plurality of planar surface sections arranged one behind the other, wherein each surface section preferably has a uniform gradient, that of the slope of the curve of the fluid guide surface in a central region of the respective area section corresponds.
- the course of the fluid guiding 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.
- the course of the guide surfaces is accordingly wel lenförmig. Each well go there without any distance over INEI ⁇ Nander.
- a groove-like depression adjoins the pocket-like depression on the bottom side.
- the largest opening cross-section of jewei time pocket-like depressions is directed to that Fl uid-Anschl ussstel le, which serves the Fl uidauslass from the Venti lgetudeuse.
- the control cross section can be continuously adjusted to the increasing fluid quantities.
- the second valve component is characterized in that the guide part has a paragraph-like extending switching edge surface, which faces the first control part.
- a defined trailing edge is formed at which the flow surface of an extending in the radial plane, annular transverse surface at one edge merges into a coaxial with the longitudinal axis of the valve spool extending outer peripheral surface. Due to the paragraph-like extending switching edge surface an improvement of the sealing function is achieved within the second valve construction component.
- a load-holding function for a pressure compensator or a valve can be achieved with simultaneous flow force compensation, which is the case if the outflow edge is both a flow guide, in particular in the form of a flow cone, and a defined vertical edge.
- the switching edge surface extending in a stepped manner in the guide part of the second control part can be formed in the direction of the first control part via a diameter reduction between the outer peripheral side of the guide part and a preferably conically extending transition part of the valve slide.
- a flow guide is formed, which serves the flow force compensation.
- the third valve component is characterized in that a further fluid guide is provided, which holds the second Steuerertei l to the second guide member at a distance.
- a puncture advantageously improves the flow around the second control part and facilitates the return of the valve spool.
- the sealing gap between the first guide part and the housing reduced inside wall, which favors the load-holding function of the second valve component described above.
- the two fluid guides which form axial distances between the first control part and the second control part and between the second Steuertei l and the second guide part are obtained by groove-like circumferential diameter reductions in the valve spool. These diameter reductions result in a wider, free, annular cross-section, through which the fluid can flow with low pressure losses, which also counteracts rapid activation behavior due to low mass.
- the valve spool can be supported on its one free end face against an energy storage and adjacent to its other free end to a volume volume variable volume into which an inner channel of the valve spool opens with its one end, the other end with the fluid guide between the two Steuertei len FL uid- leading connected. In this way, the fluid pressure at the fluid inlet can be imaged efficiently on the other free end face. Further elaborate holes in the valve housing are not required.
- FIG. 1 is a longitudinal section through a Tei l a valve, in particular in the manner of a pressure compensator, designed with three inventions according to the invention differently constructed valve components;
- Fi g- 3 is a schematic representation of an enlarged detail of Figure 2;
- FIGS 4 and 5 show two detailed representations of the switching edge course of the second control part.
- FIG. 6 shows a graph reproducing the course of the control cross-section over the opening stroke of the valve spool for its first control part.
- a part of a valve construction 10 in particular designed in the manner of a pressure compensator shown.
- a valve housing 12 has a valve bore 14, in which a longitudinally movable guided valve slide 16 is arranged.
- the valve bore 14 is closed at both ends 18 by end screws 20, 22, which engage in a respective assignable internal thread 24 of the valve bore 14.
- each annular sealing elements 26 are provided between the end screws 20, 22 and the valve housing 12.
- the valve slide 16 is provided for driving a fluid-carrying connection 28 between at least two fluid connection points 30, 32 accommodated in the valve housing 12.
- the valve slide 16 has a cylindrical first control part 34 which has on the outer circumference 36 coaxial to the longitudinal axis LA of the valve spool 16 extending, pocket-like recesses 38 (see also Fig.
- the respective fluid-guiding: surface 40 has a continuous profile so far and the lowest gradient value (S1, S7; Si l, S1 7), preferably the value N l l assuming the respective other vertex M2, M3; MI.
- the fluid guide surface 40 is curved and the different pitch curves S2, S3, S4, S5, S6; S12, S1 3, S14, S1 5, S1 6 between the vertices M1, M2, M3 are realized 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 a closed cosinusoidal curve along this outer circumference 36 bi lden.
- a groove-like depression 50 adjoins the pocket-like recess 38 in the region of the vertex M 1 on the bottom side.
- the largest opening cross-section 52 of the respective pocket-type depression 38 is directed to that fluid connection point 32, which corresponds to the fluid outlet 54 from the valve housing 1 2 is used. Thanks to the groove-like recess 50, the driving behavior of the Venti lschiebers 1 6 is improved overall.
- the valve slide 1 6 has a total of two control parts 34, 56, of which the first control part 34 has at least the pocket-like recesses 38 and the second Steuerertei l 56 is arranged by a first fluid guide 58 from the first control part 34 spaced.
- the second Steuertei l 56 is shown in the unactuated state of the Venti lschiebers 1 6, ie at N ul lhub in the lken in the image plane end position and by means of a cylindrical effetsstei ls 60 in abutment with a housing inner wall 62.
- the guide member 60 has a paragraph-like extending switching edge surface 64, which is the first Steuerertei l 34 faces.
- the switching edge surface 64 is by a reduction in diameter 66 between the outer peripheral side 68 of the chiefsstei ls 60 and egg nem preferably conically Mattergangsstei l 70 of the Venti lschiebers 1 6 in the direction of the first Steuerertei ls 34 gebi LEN.
- the conically extending transitional part 70 bi directs a flow guide for the fluid flowing through the valve component 10 and effects a deflection of the fluid flow in the direction of the fluid outlet 54. It also contributes to the flow force compensation.
- the transitional part 70 can transition either directly at the diameter reduction 66 (FIG. 4) or via a reduction in diameter 66 in the form of a recess (FIG.
- valve slide 16 is guided in the region of the fluid outlet 54 serving as a fluid port in the valve housing 1 2 through its inner wall 62.
- a first fluid guide 58 which holds this at a distance is already arranged.
- 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 1 6 and housing inner wall 62 can be reduced by the introduction of the second fluid guide 76 in the valve slide 1 6.
- the two fluid guides 58, 76 which form 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 1 6. Such diameter reductions 78, 80 are also referred to as punctures.
- the valve slide 16 is supported on its one free end face 82 with respect to an energy store 84 in the form of a compression spring. At the valve spool 1 6 and at the opposite end cap 22 guides 86, 88 are formed for the energy storage 84. On its other free end face 90, the valve slide 16 adjoins a volume volume 92 of variable volume, into which an inner channel 94 of the valve slide 16 opens with its one end 96, whose other end 98 into the first fluid guide 58 between the two control parts 34, 56, immediately adjacent to the transition part 70, opens.
- a corresponding fluid channel 100 is provided in the valve housing 12.
- the graph of FIG. 6 shows the course of the control cross section over the opening stroke. From a defined opening stroke, the first stressessstei l 60 out of engagement with the housing inner wall 62, so that the load-holding function is overcome and fluid from the fluid port 30, which forms the fluid inlet 102, to the fluid Anschlußstel le 32, which forms the fluid outlet 54, can flow. Starting from this opening stroke, the control cross-section increases disproportionately with increasing opening stroke until, starting from a kink-free transition, the control cross-section increases proportionally to the opening stroke.
- the control quality and stability are substantially improved according to the invention by a continuous, monotonically increasing control cross section over the opening stroke without kinks and with a very flat initial gradient.
- valve construction components 10 are shown by the invention.
- the pocket-like recesses 38 no longer open at an edge, but flow into the end face 104 of the first control part 34.
- This has the advantage that the control cross section does not change abruptly at one edge. Therefore, the course of the control cross section over the opening stroke has no kink (compare Fig. 6). Consequently, the control quality of the valve components 10 is considerably higher and the stability of the control is also improved.
- An outflow edge 72 is provided on the second control part, at which the flow surface transitions from an annular switching edge surface 64 running in the radial plane into an outer circumferential surface 68 running coaxially to the longitudinal axis LA of the valve slide 16.
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)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013014671.2A DE102013014671A1 (en) | 2013-09-03 | 2013-09-03 | Ventilbaukomponenten |
PCT/EP2014/002382 WO2015032492A2 (en) | 2013-09-03 | 2014-09-02 | Valve components |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3042087A2 true EP3042087A2 (en) | 2016-07-13 |
EP3042087B1 EP3042087B1 (en) | 2020-11-25 |
Family
ID=51539229
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14765869.4A Active EP3042087B1 (en) | 2013-09-03 | 2014-09-02 | Valve elements |
Country Status (5)
Country | Link |
---|---|
US (1) | US10167881B2 (en) |
EP (1) | EP3042087B1 (en) |
CN (1) | CN205956083U (en) |
DE (1) | DE102013014671A1 (en) |
WO (1) | WO2015032492A2 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9260842B2 (en) | 2012-06-22 | 2016-02-16 | Kohler Mira Limited | Valve with heating element |
DE102016007754A1 (en) | 2016-06-24 | 2018-01-11 | Hydac System Gmbh | Valve device for influencing a media flow |
GB2568271B (en) | 2017-11-09 | 2020-04-22 | Kohler Mira Ltd | A plumbing component for controlling the mixture of two supplies of water |
JP6452791B1 (en) * | 2017-11-28 | 2019-01-16 | 三菱ロジスネクスト株式会社 | Control valve and forklift |
US11680649B2 (en) | 2020-11-16 | 2023-06-20 | Parker-Hannifin Corporstion | Proportional valve spool with linear flow gain |
Family Cites Families (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3181386A (en) | 1962-11-13 | 1965-05-04 | Gen Motors Corp | Transmission |
DE2604208A1 (en) | 1976-02-04 | 1977-08-11 | Friedrich Wilhelm I Friedrichs | Grooved rotary piston valve - has widening grooves which offer continuously adjustable pulse width for transfer of pressure fluid |
DE3515563C1 (en) | 1985-04-30 | 1986-11-06 | Parker Hannifin "NMF" GmbH, 5000 Köln | Hydraulic control valve in piston-slide design |
US4667930A (en) | 1986-06-09 | 1987-05-26 | Caterpillar Inc. | Metering slot configuration for a valve spool |
GB8717963D0 (en) * | 1987-07-29 | 1987-09-03 | Vickers Systems Ltd | Spool |
DE4005967C2 (en) | 1990-02-26 | 1996-05-09 | Rexroth Mannesmann Gmbh | Control arrangement for several hydraulic consumers |
DE4040603A1 (en) * | 1990-12-19 | 1992-06-25 | Bosch Gmbh Robert | HYDRAULIC DIRECTIONAL VALVE FOR CONTROLLING A HYDROMOTOR |
DE4239643C2 (en) | 1992-11-26 | 1997-01-30 | Voith Gmbh J M | Throttling device for throttling a liquid flow |
JPH0710650U (en) * | 1993-07-26 | 1995-02-14 | 株式会社小松製作所 | Directional control valve for all hydraulic steering system |
JP3407565B2 (en) | 1996-10-28 | 2003-05-19 | 株式会社豊田中央研究所 | Spool valve |
JPH11201107A (en) | 1998-01-12 | 1999-07-27 | Hitachi Constr Mach Co Ltd | Pressure compensation valve |
US6397890B1 (en) * | 1999-02-15 | 2002-06-04 | Case Corp. | Variable metering fluid control valve |
DE19957952A1 (en) * | 1999-12-02 | 2001-06-07 | Mannesmann Rexroth Ag | Hydraulic directional control valve for load-independent control of a hydraulic consumer, especially of a mobile machine |
US6742629B2 (en) | 2000-07-03 | 2004-06-01 | Wittur Ag | Valve control unit for a hydraulic elevator |
US6450194B1 (en) * | 2000-09-26 | 2002-09-17 | Case Corporation | Spool notch geometry for hydraulic spool valve |
DE10218783A1 (en) | 2002-03-04 | 2003-09-25 | Bosch Rexroth Ag | valve assembly |
DE10334056A1 (en) | 2003-07-25 | 2005-02-10 | Bosch Rexroth Ag | way valve |
DE102005002699B4 (en) | 2005-01-19 | 2011-02-17 | Sauer-Danfoss Aps | Bremsventilanordung |
US7856999B2 (en) | 2005-03-17 | 2010-12-28 | Borgwarner Inc. | Automatic transmission having hydraulic valves with flow force compensation |
KR100929421B1 (en) | 2007-10-22 | 2009-12-03 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | Heavy Equipment Hydraulic Control Valve |
DE102007054138A1 (en) | 2007-11-14 | 2009-05-28 | Hydac Filtertechnik Gmbh | Hydraulic valve device |
DE102009021831A1 (en) | 2009-05-19 | 2010-11-25 | Robert Bosch Gmbh | Way valve arrangement |
US8800399B2 (en) | 2009-09-10 | 2014-08-12 | Borgwarner Inc. | Hydraulic circuit for automatic transmission having area controlled shift actuator valve with flow force compensation |
DE102010053805A1 (en) | 2010-12-08 | 2012-06-14 | Robert Bosch Gmbh | Directional control valve for controlling hydraulic load, has channel portion which is formed from axial hole to outer surface of control piston, by radial hole that is formed with constant diameter of axial hole to piston outer surface |
US20140026546A1 (en) * | 2012-07-25 | 2014-01-30 | Caterpillar, Inc. | Regeneration Valve for a Hydraulic Circuit |
-
2013
- 2013-09-03 DE DE102013014671.2A patent/DE102013014671A1/en not_active Withdrawn
-
2014
- 2014-09-02 WO PCT/EP2014/002382 patent/WO2015032492A2/en active Application Filing
- 2014-09-02 CN CN201490000970.5U patent/CN205956083U/en active Active
- 2014-09-02 EP EP14765869.4A patent/EP3042087B1/en active Active
- 2014-09-02 US US14/912,419 patent/US10167881B2/en active Active
Non-Patent Citations (1)
Title |
---|
See references of WO2015032492A2 * |
Also Published As
Publication number | Publication date |
---|---|
US10167881B2 (en) | 2019-01-01 |
DE102013014671A1 (en) | 2015-03-05 |
EP3042087B1 (en) | 2020-11-25 |
CN205956083U (en) | 2017-02-15 |
WO2015032492A3 (en) | 2015-07-30 |
WO2015032492A2 (en) | 2015-03-12 |
US20160201695A1 (en) | 2016-07-14 |
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