EP0581156B1 - Distributeur hydraulique type robinet à piston - Google Patents

Distributeur hydraulique type robinet à piston Download PDF

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Publication number
EP0581156B1
EP0581156B1 EP93111507A EP93111507A EP0581156B1 EP 0581156 B1 EP0581156 B1 EP 0581156B1 EP 93111507 A EP93111507 A EP 93111507A EP 93111507 A EP93111507 A EP 93111507A EP 0581156 B1 EP0581156 B1 EP 0581156B1
Authority
EP
European Patent Office
Prior art keywords
control
piston
control valve
hydraulic directional
notch
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.)
Expired - Lifetime
Application number
EP93111507A
Other languages
German (de)
English (en)
Other versions
EP0581156A3 (fr
EP0581156A2 (fr
Inventor
Eckard Schuttenberg
Berthold Dipl.-Ing. Pfuhl (Fh)
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0581156A2 publication Critical patent/EP0581156A2/fr
Publication of EP0581156A3 publication Critical patent/EP0581156A3/xx
Application granted granted Critical
Publication of EP0581156B1 publication Critical patent/EP0581156B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves

Definitions

  • the invention is based on a hydraulic directional control valve in the spool design according to the type specified in the preamble of claim 1.
  • Generic directional valves have become known from DB 27 17 384 C2 and DE-GM 88 01 058. These hydraulic directional control valves are so-called continuous valves, in which the valve can be precisely controlled by the fact that the control edges have essentially triangular control notches, which, based on the cross-section of the control surfaces, usually have the spatial shape of a half-cone, a half-pyramid or a similar shape exhibit. With such control notches, which extend over the full stroke range of the longitudinal slide, fine control of the valve can be achieved with the desired accuracy. With such geometries of the control notches, a square course of the volume flow over the stroke can be achieved especially in the area of small opening cross sections and thus in the area of small pressure medium flows.
  • the disadvantage with these control notches is that with increasing volume flow the influence of the losses in the valve housing is getting bigger and as a result the characteristic curve flattens out.
  • the characteristic curve of the volumetric flow therefore mostly changes into a straight section in the middle setpoint ranges and, when the directional control valve is fully actuated, can have a degressive end section, in which the slope decreases.
  • Such a characteristic curve is particularly unfavorable for braking operations involving large masses, where braking is usually to be carried out first quickly and then slowly.
  • it is undesirable that the drift that usually occurs in such valves leads to larger relative errors with smaller setpoint values.
  • the hydraulic directional control valve according to the invention in piston spool construction with the characterizing features of the main claim has in contrast the advantage that it gives a quadratic function for the volume flow over the entire stroke range.
  • the influence of the housing losses can be compensated for in such a way that the volume flow characteristic curve has a steadily increasing, essentially square course in the range from 0 to 100% of the setpoint.
  • the quadratic volume flow curve is particularly advantageous for the control of large masses, particularly when accelerating and braking them. Due to the steadily increasing volume flow characteristic, the directional control valve can be used in connection with a simpler control electronics.
  • the geometry of the control notches allows particularly precise and sensitive control with small pressure medium flows.
  • Another advantage of the directional control valve is that the drift that usually occurs with such valves in the area of small modulation has less influence. It is also favorable that the control notches have no discontinuities, as is the case with composite notch shapes at the transition of the notch shapes. In addition, the control slide can be produced relatively easily and inexpensively with these control notches.
  • FIG. 1 shows a generic hydraulic directional valve in a simplified representation
  • FIG. 2 shows a view of the longitudinal slide according to the invention with part of the adjacent control chambers fixed to the housing
  • FIG. 3 shows a perspective view of the longitudinal slide according to FIG. 2 and FIG Stroke for the directional valve according to the invention.
  • FIG. 1 the so-called main stage of a hydraulic continuous directional control valve 10 is shown with directional control in the spool design, which can be controlled by a pilot control, not shown.
  • the directional control valve 10 has a housing 11 in which a longitudinal slide 12 is guided in a sealing and sliding manner.
  • the longitudinal slide 12 is held in its central position by two centering springs 13 supported on the housing 11, pressure spaces 14 for receiving the centering springs 13 being formed in the housing 11 at the opposite ends of the longitudinal slide 12.
  • the pressure chambers 14 have bores 15, which each establish a connection to the hydraulic pilot control, not shown.
  • An axial slide bore 16 for the longitudinal slide 12 is formed in the housing 11 of the directional control valve 10.
  • the longitudinal slide 12 has 3 circumferential recesses 17 which are arranged at a distance from one another, so that there are two piston sections 18 with the full piston cross section between them.
  • the recesses 17 comprise an annular piston core 19, so that there are radially protruding front control surfaces 21 on the piston sections 18 from the piston core 19, the outer edge of which, as a control edge 22, slides sealingly on the inner surface of the axial slide bore 16.
  • the control edges 22 have triangular recesses 23, several of which are arranged at a distance from one another in the course of the control edge 22 surrounding the piston section 18.
  • the cutouts 22 have a substantially semi-conical shape which is known per se in the direction of the piston core.
  • the longitudinal slide 12 is surrounded by control chambers 24 formed in the housing 11 and annularly surrounding the longitudinal slide 12, which are connected via connection bores 25 to 28 to units, such as tank, pump, consumer, which are located outside the directional control valve and are therefore not shown.
  • 25 are the connection to the tank, 26 to the connection to the pump and 27 and 28 each to a connection to a consumer.
  • housing webs 29 are arranged, which cooperate with the control edges 22 of the longitudinal slide 12 during its axial movement.
  • the two external control chambers 24 are connected to one another via a control channel 31 and thus also to the connection bore 25 to the tank.
  • control notches 32 are now arranged instead of the recesses 23 according to FIG The shape and design of Figure 2 in connection with Figure 3 can be seen.
  • the control notches 32 for the 4-way valve are in principle identical to one another, so that a single control notch 32 is described below.
  • the control notch 32 has a triangular shape at the beginning of the notch.
  • control notch 32 has a base surface 34, which extends between the lateral surface 33 of the piston section 18 and the longitudinal axis of the longitudinal slide 12, and which has a diameter which is slightly larger than the diameter of the piston core 19.
  • the base surface 34 also has a triangular shape , the legs of which open toward the front control surface 21 and remain essentially in the region of an acute angle.
  • side walls 35 extend outwards to the outer surface 33, wherein the control notch 32 forms a butterfly-shaped jacket opening 36 in the outer jacket surface 33 and thus has a geometric shape with which a square volume flow curve is made possible.
  • the side walls 35 are designed so that their spacing increases increasingly in the radial direction and in the longitudinal direction, so that the flow cross-section formed by the control notch 32 undergoes a multi-dimensional expansion.
  • the jacket opening 36 formed by the control notch 32 in the outer circumferential surface 33 therefore runs in a funnel-shaped manner, seen in the radial direction, lies above the base surface 34 and is considerably larger than this base surface 34. Due to this geometry of the control notch 32, the volume flow curve over this control notch corresponds to a function higher Order, which corresponds here at least to the fourth order.
  • FIG. 2 clearly shows in connection with the perspective illustration of the longitudinal slide 12 according to FIG. 3, two control notches 32 are arranged diametrically to one another on the right piston section 18 on its two control surfaces 21.
  • control notches 32 are each arranged uniformly distributed along the circumference on the left piston section 18 on its two control surfaces 21, the opening cross section of which is made smaller in accordance with the larger number of control notches.
  • an undercut 37 is arranged on each of the front control surfaces 21, which is designed here as a turned-around circumferential cone.
  • the mode of operation of the directional valve 10 is explained as follows, the basic function of a hydraulic continuous directional valve being assumed to be known per se and reference being made to FIG.
  • the course of the volume flow between two adjacent control chambers 24 is plotted in FIG. 4 via a control notch 32 in relation to the desired value, which can be understood here as the stroke of the longitudinal slide 12.
  • the characteristic curve 41 shows the conditions for the longitudinal slide 12 according to the invention with a control notch 32, while the dashed characteristic curve 42 illustrates the conditions for a generic valve with simple, triangular cutouts 23.
  • the dashed curve 42 shows the situation in the generic state of the art, where the characteristic curve becomes increasingly flatter due to the housing losses with increasing volume flow and, after a rectilinear section, finally takes a degressive curve, in which even the slope decreases.
  • the housing losses can therefore be compensated for in the directional control valve 10 according to the invention, so that approximately the square course of the characteristic curve 41 is ensured over the entire actuation range.
  • the quadratic volume flow curve is of particular advantage when controlling large masses, where, especially when braking, first a rapid and then a slow braking should take place.
  • This configuration of the control notches 32 advantageously means that the slope of the characteristic curve 41 increases linearly with the desired value. The consequence of this is that small volume flows can be controlled particularly sensitively. It is also advantageous that the drift occurring in such continuous directional valves in the area small modulation has less influence than conventional notches; in addition, the relative error caused by the drift is the same over the entire setpoint range.
  • the design of the control notches 32 also avoids discontinuities in the notch shape, so that no abrupt changes in functions as in the case of composite notch shapes can occur.
  • the longitudinal slide 12 with the control notches 32 can also be produced relatively easily and inexpensively.
  • the notch shape can be produced inexpensively on automatic lathes without the triangle tip, with the main drive included in the path control.
  • the triangle tip can then be produced relatively easily by eroding or by stamping.

Landscapes

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

Claims (12)

  1. Distributeur hydraulique du type robinet à piston avec un boîtier (11) dans l'alésage duquel on fait passer de façon étanche et glissante un tiroir longitudinal (12) et dans le cas duquel sont constitués, dans l'alésage du tiroir, au moins deux chambres de commande (24) se trouvant côte à côte et qui enserrent entre elles une entretoise de boîtier (29) dans laquelle une section de piston (18) du tiroir longitudinal (12) commande la liaison entre les deux chambres de commande (24), le tiroir longitudinal (12) présentant pour cela au moins une entaille de commande (32) servant d'évidement de commande fine, et constituée géométriquement ainsi, entaille de commande qui s'étend sur toute la course du tiroir longitudinal (12), l'entaille de commande (32) au début de l'ouverture présentant, du fait d'une forme sensiblement triangulaire, une évolution quadratique du débit,
    caractérisé en ce que
    l'entaille de commande (32) avec une course d'ouverture croissante grâce à un élargissement pluridimensionnel, transforme le débit en une fonction d'un ordre supérieur, l'entaille de commande (32) présentant pour cela une surface de base (34) située entre l'axe longitudinal et la surface enveloppe (33) du tiroir longitudinal (12) et de forme sensiblement triangulaire, surface de base (34) qui s'ouvre en direction d'une face de commande (21) située du côté frontal de la section (18) du piston et à partir de laquelle s'étendent des parois latérales (35) allant vers l'extérieur en direction de la surface enveloppe (33), parois latérales qui s'étendent radialement dans le sens longitudinal avec une distance allant en augmentant dans les deux sens, grâce quoi on forme, dans la surface enveloppe (33) de la section (18) du piston, une ouverture (36) de l'entaille de commande (32) qui se trouve au dessus de la surface de base (34) et va en s'élargissant en forme d'entonnoir.
  2. Distributeur hydraulique selon la revendication 1,
    caractérisé en ce que
    le débit déterminé seulement par la section transversale d'ouverture de l'entaille de commande (32) se transforme, avec une course croissante du tiroir longitudinal (12), en une fonction du quatrième ordre au moins.
  3. Distributeur hydraulique selon la revendication 1 ou 2,
    caractérisé en ce que
    la surface de base (34) s'étend de façon sensiblement parallèle à l'axe longitudinal du tiroir longitudinal (12) et se trouve en particulier, dans le sens radial, dans la surface enveloppe du noyau du piston (19).
  4. Distributeur hydraulique selon l'une des revendications 1 à 3,
    caractérisé en ce que
    plusieurs entailles de commande (32), en particulier deux à six, sont disposées de façon régulièrement répartie sur le pourtour de la section (18) du piston.
  5. Distributeur hydraulique selon l'une ou plusieurs des revendications 1 à 4,
    caractérisé en ce que
    le tiroir longitudinal (12) présente plusieurs sections de piston (18) avec des entailles de commande (32) et présente, en particulier, pour une fonction de position de vanne à 4 et 3 voies, quatre arêtes de commande (22).
  6. Distributeur hydraulique selon l'une ou plusieurs des revendications 1 à 5,
    caractérisé en ce que
    les lignes de délimitation de la surface de base (34), y compris jusque dans les faces de commande (21) situées du côté frontal, forment les unes avec les autres un angle aigu.
  7. Distributeur hydraulique selon la revendication 6,
    caractérisé en ce que
    les extrémités de la surface de base (34) qui se trouvent à l'intérieur et la surface enveloppe (33) se trouvent dans le sens radial sensiblement les unes au dessus de l'autre.
  8. Distributeur hydraulique selon l'une des revendications 1 à 7,
    caractérisé en ce que
    l'évolution (41) du débit en volume sur toute la zone de la valeur de consigne se déroule sensiblement selon une fonction quadratique.
  9. Distributeur hydraulique selon l'une des revendications 1 à 8,
    caractérisé en ce que
    l'on dispose une contre-dépouille (37) sur une face de commande (21) située du côté frontal.
  10. Distributeur hydraulique selon l'une des revendications 1 à 9,
    caractérisé en ce que
    au début de l'entaille de commande (32) on dispose une fine entaille de commande supplémentaire dont la profondeur est plus petite que celle de l'entaille de commande (32).
  11. Distributeur hydraulique selon l'une des revendications 1 à 10,
    caractérisé en ce que
    la surface d'écoulement axiale de l'entaille de commande (32) dans la face de commande (21), située du côté frontal, atteint à peu près le triple de l'ouverture (36) dont on dispose pour l'écoulement radial.
  12. Utilisation du distributeur hydraulique selon l'une des revendications 1 à 5, pour une vanne en continu (10).
EP93111507A 1992-07-24 1993-07-17 Distributeur hydraulique type robinet à piston Expired - Lifetime EP0581156B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4224469 1992-07-24
DE4224469A DE4224469A1 (de) 1992-07-24 1992-07-24 Hydraulisches Wegeventil in Kolbenschieber-Bauweise

Publications (3)

Publication Number Publication Date
EP0581156A2 EP0581156A2 (fr) 1994-02-02
EP0581156A3 EP0581156A3 (fr) 1994-03-16
EP0581156B1 true EP0581156B1 (fr) 1997-05-28

Family

ID=6464002

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93111507A Expired - Lifetime EP0581156B1 (fr) 1992-07-24 1993-07-17 Distributeur hydraulique type robinet à piston

Country Status (3)

Country Link
EP (1) EP0581156B1 (fr)
JP (1) JPH06185659A (fr)
DE (2) DE4224469A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0710650U (ja) * 1993-07-26 1995-02-14 株式会社小松製作所 全油圧式ステアリングシステムの方向制御弁
US6460561B1 (en) * 1998-10-28 2002-10-08 Luk Getriebe-Systeme Gmbh Valve piston and valve equipped with same
KR100506367B1 (ko) * 1999-01-27 2005-08-10 현대자동차주식회사 자동 변속기 압력 제어 밸브의 노치 구조
DE10041168A1 (de) * 2000-08-21 2002-03-07 Mannesmann Rexroth Ag Ventileinrichtung
DE102009041859A1 (de) * 2009-09-16 2011-03-24 Robert Bosch Gmbh Steuerschieber eines Hydraulikventils
DE102011080667A1 (de) 2011-08-09 2013-02-14 Robert Bosch Gmbh Schieberventil mit einem Ventilschieber
CN104534124B (zh) * 2014-12-01 2017-01-18 浙江工业大学 位移可放大2d电液比例换向阀
JP6700137B2 (ja) * 2016-07-28 2020-05-27 住友精密工業株式会社 流量制御弁
CN111089090A (zh) * 2019-10-30 2020-05-01 润琛液压机械南通有限公司 一种微型挖掘机手动液压多路阀
CN111255917B (zh) * 2020-02-04 2022-01-14 内蒙古西部天然气管道运行有限责任公司 一种天然气压缩机控制装置
DE102020208933A1 (de) 2020-07-16 2022-01-20 Robert Bosch Gesellschaft mit beschränkter Haftung Regelventil mit radialer Ausnehmung im Bereich der ersten und der zweiten Blende
US11680649B2 (en) * 2020-11-16 2023-06-20 Parker-Hannifin Corporstion Proportional valve spool with linear flow gain
DE102021207650A1 (de) 2021-07-19 2023-01-19 Robert Bosch Gesellschaft mit beschränkter Haftung Schieberventil mit geringer Neigung zum hydraulischen Klemmen

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2717384C2 (de) * 1977-04-20 1983-12-22 Mannesmann Rexroth GmbH, 8770 Lohr Hydraulisch betätigtes Steuerventil
DE3226809A1 (de) * 1982-07-17 1984-01-19 Robert Bosch Gmbh, 7000 Stuttgart Hydraulisches wegeventil
DE3504268A1 (de) * 1985-02-08 1986-08-14 Heller Hydraulik GmbH, 7440 Nürtingen Ventil mit vorsteuerung
DE3737392A1 (de) * 1987-11-04 1989-05-24 Bosch Gmbh Robert Hydraulisches steuerventil
DE3802672C2 (de) * 1988-01-29 1993-12-16 Danfoss As Hydraulisches Steuerventil mit Druckfühleinrichtung
DE3915584A1 (de) * 1989-05-12 1990-11-15 Volker Siems Hydraulischer drosselschieber mit einem in der zylinderbohrung axial bewegbaren kolben
US4941508A (en) * 1989-12-28 1990-07-17 Dana Corporation Force balanced hydraulic spool valve

Also Published As

Publication number Publication date
EP0581156A3 (fr) 1994-03-16
DE4224469A1 (de) 1994-01-27
JPH06185659A (ja) 1994-07-08
EP0581156A2 (fr) 1994-02-02
DE59306565D1 (de) 1997-07-03

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