EP0764785A2 - Distributeur à tiroir avec siège de clapet étendu - Google Patents

Distributeur à tiroir avec siège de clapet étendu Download PDF

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Publication number
EP0764785A2
EP0764785A2 EP96106249A EP96106249A EP0764785A2 EP 0764785 A2 EP0764785 A2 EP 0764785A2 EP 96106249 A EP96106249 A EP 96106249A EP 96106249 A EP96106249 A EP 96106249A EP 0764785 A2 EP0764785 A2 EP 0764785A2
Authority
EP
European Patent Office
Prior art keywords
valve
longitudinal slide
cone
fine control
control area
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96106249A
Other languages
German (de)
English (en)
Other versions
EP0764785B1 (fr
EP0764785A3 (fr
Inventor
Hartmut Dipl.-Ing. Sandau (Fh)
Werner Dipl.-Ing. Schumacher
Rainer Dipl.-Ing. Trucksess (Fh)
Holger Dipl.-Ing. Lueues
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 EP0764785A2 publication Critical patent/EP0764785A2/fr
Publication of EP0764785A3 publication Critical patent/EP0764785A3/fr
Application granted granted Critical
Publication of EP0764785B1 publication Critical patent/EP0764785B1/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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve

Definitions

  • the invention is based on a longitudinal slide valve with two longitudinal slide valves arranged coaxially in a valve housing according to the preamble of the main claim.
  • DE 41 40 604 A1 discloses a longitudinal slide valve with two longitudinal slide valves arranged coaxially in a valve housing.
  • the first of the two longitudinal slides guides the pressure medium flow between a return connection and at least one consumer connection.
  • the second longitudinal slide which is mounted and guided in the center of the first, is electromagnetically controlled when necessary for the hydraulic opening of the first longitudinal slide.
  • pressure medium branched off from the consumer connection is primarily diverted in front of one end face of the first longitudinal slide, while a pressure chamber in front of the other end face is hydraulically connected to the consumer connection in the blocking position.
  • the diameter of the valve seat corresponds to the diameter of the fine control region connected downstream.
  • the sealing surface between the valve seat and valve cone is a very narrow ring surface, so that there is almost line contact between the valve seat and valve cone. This prevents, when the longitudinal slide is opened while the fine control area is still closed, that an axial force on the longitudinal slide disturbs the valve control behavior due to pressure medium flowing in between the valve seat and the fine control area exercises. Due to the narrow sealing surface, the surface pressure in the sealing zone is very high. Consequently, the first longitudinal slide must be stored in a hardened and ground steel sleeve embedded in the valve housing.
  • the hardened steel sleeve for guiding and seat formation of the first longitudinal slide can be dispensed with.
  • the average diameter of the seat surface of this longitudinal slide is designed to be larger than the maximum diameter of the fine control area downstream in the closing direction. Due to the graduated design of the longitudinal slide and the corresponding guide and seat surface bore, the collar lying between the mainly cylindrical fine control area and the guide area can be designed over a large area.
  • the surface pressure, adapted to the uncured materials used can remain a fraction of the maximum permissible compressive stress.
  • the bore including the fine control area can be machined with a step reamer.
  • the valve housing can be manufactured in a less complex manner - that is, also more cost-effectively.
  • the cost advantage also arises in the case of constructions which, for example, require a guide sleeve due to the flow channel guidance, since hardening of the sleeve and the subsequent finishing by internal grinding are not required here.
  • the proportional directional control valve element (120) shown in FIG. 1 is a throttling 2/2-way valve, the longitudinal slide (140, 147) of which can assume any intermediate positions in addition to the two end positions. It has a proportional magnet (121) on its left side.
  • the 2/2-way valve controls, for example, the pressure medium flow that returns from the single-acting hydraulic cylinder to the tank under load. Therefore, it is called the sink module. It is designed as a poppet valve and also works as a check valve that protects the load.
  • the proportional magnet (121) of the lowering module (120) is activated.
  • the pressure medium flows from the consumer connection (50) via the sink module (120) to the return connection (52).
  • the proportional directional control valve element is essentially cuboid - Here shown in simplified form - valve housing (30) with two approximately square, flat outer surfaces which are aligned as top and bottom parallel to the cutting plane. In the sectional plane, fastening bores (69, 69 ') can be seen which penetrate the valve housing (30) perpendicular to the top and bottom.
  • the side surfaces (34, 35, 38, 39) aligned perpendicular to the cut surface each have a rectangular outline.
  • the front (34) and the back (35) are flat surfaces.
  • the proportional magnet (121) is flanged to the front. Opposite him sits in the back (35) in a depression a screw plug (157) for a bore (44) receiving the longitudinal slide (140).
  • the two other side surfaces (38) and (39) each have a recess provided with an internal thread, the lower one representing the return connection (52) and the upper one representing the consumer connection (50).
  • the proportional directional control valve (120) has a stepped bore (44) passing through the valve housing (30). It is closed on the left by the proportional magnet (121) and on the right by a locking screw (157) provided with a hexagon socket.
  • the first or outer longitudinal slide (140) is guided and supported in the central region of the stepped bore (44). At the left edge of the guide area, the cylindrical bore part merges into a consumer ring channel (125). The latter is hydraulically connected directly to the consumer connection (50).
  • adjusting screw (150) In the left area of the stepped bore (44) there is an adjusting screw (150) in an internal thread (128). Nearly A return ring channel (126) is arranged between the adjusting screw (150) and the outer longitudinal slide (140), into which the return connection (52) opens.
  • the adjusting screw (150) is known from DE 41 40 604 A1 with the exception of a toothing (151) arranged on it.
  • the sink module (120) is shown in the locked position.
  • the pressure medium that is present at the consumer connection (50) and thus at the consumer ring channel (125) cannot flow into the return ring channel (126).
  • the outer longitudinal slide (140) which has the function of a main control slide, stands with its main valve cone (141) against the cone-shaped main valve seat (132) incorporated in the valve housing (30).
  • the fine control area (141a) is arranged at the left end of the main valve spool (140).
  • the latter is separated from the main valve cone by means of a constriction (141b) with an approximately trapezoidal individual cross section.
  • the constriction serves among other things a favorable flow and the ease of processing for the main valve cone (141).
  • An annular space (134) lies between the constriction (141b) and the valve housing (30).
  • a plurality of main control notches (142) distributed around the circumference are worked into the fine control area (141a) from the left end. In the closed position of the main control spool (140) they are completely covered by a cylinder seat (133) incorporated in the valve housing.
  • the diameter D F of the cylinder seat (133) lies below the average diameter D S of the adjacent sealing surface of the main valve seat (132). Since the stepped bore (44), in particular the bearing and sealing surfaces, are to be machined from the rear of the housing (35) with only one tool, the smallest diameter of the sealing surface is the main valve seat (132) the same size or larger than the diameter D F of the cylinder seat (133).
  • a pressure chamber (135) on its right end In order to hold the main control slide (140) on the main valve seat (132), pressure medium is present in a pressure chamber (135) on its right end.
  • a bore (161) extending to the end face and receiving the second or inner longitudinal slide (147) is sealed by means of a plug (162).
  • the pressure medium from the consumer ring channel (125) reaches the right front side via a throttle bore (144) running radially in the main control slide (140) and a longitudinal bore (145) connected to it.
  • the longitudinal bore (145) penetrates a control groove (143) in the area of its base.
  • the hydraulic oil pressure present at the consumer connection (52) is present.
  • the hydraulic oil pressure acting on the right face of the main control spool (140) keeps it in the closed position.
  • the closing force acting to the left is reduced by the force acting in the opposite direction due to the pressure existing in the area of the outer contour of the main control slide (140) between the main valve plug (141) and the relief grooves.
  • the hydraulic oil pressure acts on an annular surface, which is formed on the one hand by the maximum diameter of the contact area between the main valve cone (141) and its main valve seat (132) and on the other hand by the diameter D of the right front side.
  • the sink module (120) opens when the proportional magnet (121) is energized. Its anchor tappet (122) pushes the inner longitudinal slide, a pilot spool (147) slightly to the right. As a result, its pilot control notches (149) come under the control groove (143) of the main control spool (140). At the same time, its valve cone (148) located further to the left lifts from its valve seat corresponding to the main control slide (140) (146). The pressure chamber (135) is now connected to the return connection (52) via the longitudinal bore (145), the control groove (143), the pilot control notches (149), the valve seat (146) and the return ring channel (126). Depending on the opening cross section of the pilot notches (149), the pressure in the pressure chamber (135) drops. The pressure there is adjusted according to the ratio of the cross section of the throttle bore (144) and the opening cross section of the pilot notches (149).
  • the pilot spool (147) is pushed far enough to the right, the pressure in the pressure chamber (135) drops so far that the force exerted by the pressure medium on the main spool (140) in the area of the consumer ring channel (125) predominates to the right, the main spool (140 ) also shifted to the right.
  • the main valve plug (141) lifts off from the main valve seat (132). With the main control notches (142) still closed, the oil pressure-loaded annular surface in the sealing zone, in the area between the consumer ring channel (125) and the annular space (134), thus increases to its maximum.
  • the ring area is now limited by the diameters D F and D. Consequently, the main control spool (140) makes a small jerky stroke to the right. Only after this stroke do the fine-control main control notches (142) reach the area of the annular space (134).
  • the pressure medium now flows along the main control slide (140) in the direction of the return ring channel (126).
  • the main control slide valve (140) lags behind the pilot control slide valve (147) due to its opening movement, as a result of which the opening cross section at the pilot control notches (149) becomes smaller.
  • This allows a higher pressure to build up in the pressure chamber (135) via the throttle bore (144).
  • the opening movement of the main spool (140) is braked until sets a state of equilibrium.
  • the return spring (155) is supported on the pilot spool (147) and on the adjusting screw (150).
  • the pilot notches (149) are closed when the pilot spool (147) moves.
  • the pressure in the pressure chamber (135) increases.
  • the main valve plug (141) lies against the main valve seat (132).
  • the sink module (120) locks.
  • the proportional directional control valve element (120) thus operates in the manner of a sequence control.
  • the adjusting screw (150) has helical teeth (151) in the central area of its outer contour, which at least temporarily engage the teeth of an adjusting worm.
  • the adjusting screw is not visible in the section shown in FIG. 1.
  • the adjusting worm can be rotated with the aid of an adjusting spindle, the free end of which protrudes from the valve housing (30), or a special tool that can be temporarily coupled to the end of the adjusting worm.
  • the adjusting screw (150) is screwed to the right or left in the internal thread (128).
  • the length of the adjustment range largely corresponds to the width of the toothing (151) of the adjusting screw (150).

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Sliding Valves (AREA)
EP96106249A 1995-09-22 1996-04-20 Distributeur à tiroir avec siège de clapet étendu Expired - Lifetime EP0764785B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19535223 1995-09-22
DE19535223A DE19535223A1 (de) 1995-09-22 1995-09-22 Längsschieberventil mit großflächigem Ventilsitz

Publications (3)

Publication Number Publication Date
EP0764785A2 true EP0764785A2 (fr) 1997-03-26
EP0764785A3 EP0764785A3 (fr) 1998-06-03
EP0764785B1 EP0764785B1 (fr) 2001-11-28

Family

ID=7772862

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96106249A Expired - Lifetime EP0764785B1 (fr) 1995-09-22 1996-04-20 Distributeur à tiroir avec siège de clapet étendu

Country Status (2)

Country Link
EP (1) EP0764785B1 (fr)
DE (2) DE19535223A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1128109A1 (fr) 2000-02-22 2001-08-29 Siemens Building Technologies AG Vanne pour dispositif de commande
WO2004092591A1 (fr) * 2003-04-10 2004-10-28 Bosch Rexroth Ag Soupape de distribution a variation continue

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2334906C1 (ru) * 2006-12-26 2008-09-27 Валерий Владимирович Бодров Запорно-регулирующий клапан
RU2552211C1 (ru) * 2014-05-05 2015-06-10 Валерий Владимирович Бодров Запорно-регулирующий клапан
RU2766379C1 (ru) * 2021-07-12 2022-03-15 Артур Олегович Бурков Предохранительное устройство непрямого действия для гидросистем

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4140604A1 (de) * 1991-12-10 1993-06-17 Bosch Gmbh Robert Steuervorrichtung fuer den volumenstrom eines hydraulischen arbeitsmittels

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1128109A1 (fr) 2000-02-22 2001-08-29 Siemens Building Technologies AG Vanne pour dispositif de commande
WO2004092591A1 (fr) * 2003-04-10 2004-10-28 Bosch Rexroth Ag Soupape de distribution a variation continue
US7392971B2 (en) 2003-04-10 2008-07-01 Bosch Rexroth Ag Infinitely variable directional valve

Also Published As

Publication number Publication date
EP0764785B1 (fr) 2001-11-28
DE59608303D1 (de) 2002-01-10
DE19535223A1 (de) 1997-03-27
EP0764785A3 (fr) 1998-06-03

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