WO1982003436A1 - Procede d'equilibrage des forces d'ecoulement dans un tiroir plan et tiroir plan fonctionnant selon ce procede - Google Patents

Procede d'equilibrage des forces d'ecoulement dans un tiroir plan et tiroir plan fonctionnant selon ce procede Download PDF

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Publication number
WO1982003436A1
WO1982003436A1 PCT/DE1982/000073 DE8200073W WO8203436A1 WO 1982003436 A1 WO1982003436 A1 WO 1982003436A1 DE 8200073 W DE8200073 W DE 8200073W WO 8203436 A1 WO8203436 A1 WO 8203436A1
Authority
WO
WIPO (PCT)
Prior art keywords
control
flat slide
valve
pressure medium
flat
Prior art date
Application number
PCT/DE1982/000073
Other languages
German (de)
English (en)
Inventor
Gmbh Robert Bosch
Original Assignee
Meier Dietmar
Pfuhl Berthold
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 Meier Dietmar, Pfuhl Berthold filed Critical Meier Dietmar
Publication of WO1982003436A1 publication Critical patent/WO1982003436A1/fr

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/0655—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with flat slides

Definitions

  • the invention is based on a method for flow force compensation in a flat slide valve according to the preamble of the main claim.
  • a method for flow force compensation in a flat slide valve is already known from the book "Fluid Power Control", John F. Blackburn, Krausskopf-Verlag 1962, page 191, picture 10.17, which uses deflection surfaces in a control sleeve and associated flat slide valve with the same size bores, with which the pressure medium flow passing the control edges is diverted to achieve flow force compensation
  • a disadvantage of this method is that specially shaped guide profiles which are arranged in the housing and carry the deflection surfaces and which penetrate the control bores in the flat slide valve are required. This method of balancing flow forces therefore requires a relatively high level of structural complexity.
  • it can be disadvantageous for the method for flow force compensation that the flat slide valve is flowed through from both sides.
  • the method on one Flat slide valve is carried out with a longitudinally movable flat slide valve.
  • a flat slide valve is known from US Pat. No. 2,875,782, in particular FIG. 15, in which control sleeves in the flat slide through which pressure medium flows interact with control holes of the same size in the housing.
  • control edges should be easy and accurate to manufacture.
  • the control holes in the housing are closed on the side opposite the consumer connections by plugs.
  • the plugs are used solely to close bores; a teaching to carry out a method for flow force compensation in a flat slide valve with these plugs can not be found in this document. This is also evident from the fact that the spacing of the plugs from the respectively assigned control edges is too large.
  • control sleeves still have their full wall thickness in the area of the control plane, which is also a hindrance to a method for balancing flow forces.
  • the main disadvantage is that the annular control edges of the control sleeves lie in a curved surface and not in one plane.
  • a flat slide valve is known from DE-PS 2 160 490, which is constructed in two stages.
  • this valve with a flat slide valve designed as a rotary slide valve meets very high requirements, it is too expensive to build for many applications with lower requirements because it works with an electro-hydraulic converter and a hydraulic servomotor.
  • the method according to the invention with the characterizing features of the main claim has the advantage that, when used, a single-stage control valve in flat slide valve design can control relatively high volume flows with a high pressure drop at the same time and thus advance into areas that are no longer manageable by comparable, single-stage control valves. According to the method according to the invention, therefore, flat slide valves can be built which are relatively compact and simple to build and which also have a stable working behavior.
  • FIG. 1 shows a longitudinal section through a flat slide valve with the. the method according to the invention can be carried out;
  • FIG. 2 shows a longitudinal section through a deflected flat slide valve according to FIG. 1 in a simplified manner FIG. 3 and characteristic curves for the valve according to FIG. 1 working according to the method according to the invention in comparison to a comparable single-stage control valve on the market.
  • the flat slide valve 11 has a three-part housing 13 which essentially consists of a connecting part 14, an intermediate plate 15 and a cover part 16.
  • the intermediate plate 15 includes with the end faces of the connecting part 14 and cover part 16 a slide recess 17, which is relieved of the tank 18.
  • a flat slide 19 designed as a rotary slide is pivotably guided in the housing 13 by means of a shaft 21.
  • a first control sleeve 22 and a second control sleeve 23 are arranged in the Fla.c.hsehieber 19.
  • control sleeves 22, 23 run parallel to the longitudinal axis of the shaft 21 and thus perpendicular to a control plane 24 which extends between the flat slide 19 and the cover part 19.
  • this control plane 24 are the annular control edges 25 of the control sleeves 22, 23 and the control edges 26 of two control bores 27, 28, which are each assigned to the control sleeves 22, 23 and are coaxial to the flat slide valve 19 in the neutral position shown.
  • the diameter of the control bores 27, 23 is the same size as the outer diameter of the control sleeves, so that their control edges 25, 26 result in a zero overlap in the neutral position shown.
  • Both control bores 27, 23 lie in the cover part 16 and each take a plug 29, 31, which each form a flat deflection surface 32 or 33, which is located towards the control edges 25, 26.
  • the control sleeves 22, 23 also each have conical indentations 34 at their ends, so that their control edges 25 are formed by tapered walls.
  • connection part 1 4 runs coaxially to the control sleeves 22, 23, a channel 35 to a first consumer connection 36 and a channel 37 to a second consumer connection 38.
  • the diameter of the channels 35, 37 is smaller than the outer diameter of the associated control sleeves 22, 23, so that these channels are always and exclusively connected to the interior of the control sleeves 22, 23 even in the deflected positions of the flat slide 19.
  • an inlet space 39 is delimited by the control sleeves 22, 23 in the slide recess 17 and is connected to the inlet connection 41, into which a pump 42 delivers pressure medium.
  • the control sleeves 22, 23 delimit a return space 42, which is relieved to the tank 18.
  • the shaft 21 is firmly connected both to the flat slide 19 and to an armature 43 in the electromagnetic drive, so that the pivoting movement exerted by a coil 44 of the rotary drive 12 is transmitted to the flat slide 19 via the armature 43.
  • this pulse of the pressure medium flow flowing through the control edges 25, 26 on the inlet side is shown in a simplified manner as force F1, while the pressure medium flow guided into the first control sleeve 22 by the deflection surface 32 causes a force F2.
  • a force F3 for the pressure medium flow through the control edges 25, 26 and a force 74 for the pressure medium flow toward the deflection surface 33 are indicated.
  • components of the forces F1 and F3 counteract the movement of the flat slide 19 in the direction of arrow 45, while components of the forces F2 and 74 act in the direction of movement, that is to say in the direction of arrow 45.
  • the force components which act on the flat slide 19 as actuating forces are essentially influenced by three factors.
  • the angle 46 can now be set such that the force components of the forces F1 and F2 acting on the inflow side on the flat slide valve 19 cancel each other out, and in a corresponding manner those acting on the slide valve 19 Force components of the forces F3 and F4 can be compensated on the discharge side.
  • Such compensation of the impulse forces on the flat slide valve 19 can be achieved with the control valve 10 at a distance 47 which is approximately 1.4 mm.
  • the flow force compensation at each control edge can thus be achieved in a simple manner.
  • the flow force compensation can be set so that a small flow force has a closing or opening effect.
  • the inner diameter of the control sleeves 23, 22 is chosen so that it does not cause excessive throttling of the pressure medium flow flowing through, but rather that the cross-section opened at the control edges 25, 26 is decisive for this.
  • the inside diameter must also not be excessively large, so that a force due to F4 is generated on the flat slide valve 19 and can compensate for the force due to F3.
  • the distance 47 to the inner diameter of the control sleeve 22, 23 must be relatively small; good results were obtained with a ratio of about 1: 4.
  • a characteristic curve 48 shows the behavior of a control valve on the market, which is also designed in one stage and works with a flat slide valve in a rotary slide valve construction.
  • the influence of the flow forces on the slide valve becomes larger with larger pressure medium flows and larger P. so large that the characteristic curve U8 deviates strongly from a parabolic shape. This valve therefore no longer works stably in this limit range.
  • a characteristic curve 49 can be achieved by using the method according to the invention with the control valve 10.
  • the flow force compensation of the flat slide valve 19 means that even larger pressure medium flows can be controlled with larger pressure differences.
  • the control valve 10 can thus work stably in a much larger area and is particularly suitable for position control of the flat slide.
  • This method can be implemented in a particularly simple manner if plugs are inserted into the control bores 27, 28 with which the respective distance between the deflecting surfaces 32 and 33 can be set.
  • a particularly advantageous flat slide valve can be produced in a single-stage construction if the flat slide designed as a rotary slide valve is actuated directly by an electromagnetic rotary drive and the flat slide valve is only flowed through on one side.
  • the control edge of each control sleeve lies in a flat control surface, to which the associated deflection surface also runs parallel.
  • the method can also be applied to a longitudinally movable flat slide valve, wherein a proportional magnet can be used as a drive.
  • the method is also not limited to a valve with two control sleeves; it Multiple arrangements thereof are also conceivable.
  • the deflection surfaces can be arranged almost in the housing or in the movable control member. A combination of a flat control surface with a curved deflection surface or vice versa is not excluded.

Landscapes

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

Abstract

Des douilles de commande (22, 23) disposees dans le tiroir proprement dit (19) et traversees par le fluide sous pression, cooperent avec des alesages de commande (27, 28) situes coaxialement dans le corps (13). Des surfaces de deviation planes (32, 33) se trouvent a petite distance d'une surface de commande parallele (24) formee par des bords de commande circulaires (25, 26). En reglant cette distance (47) on peut modifier l'angle (46) de l'ecoulement du fluide de facon que les forces agissant sur le tiroir (19) soient equilibrees. Ainsi on peut regler de facon stable des grands ecoulements de fluide a des chutes de pression importantes sur les bords de commande (25, 26) au moyen d'une soupape de reglage (10) a commande directe.
PCT/DE1982/000073 1981-04-01 1982-03-30 Procede d'equilibrage des forces d'ecoulement dans un tiroir plan et tiroir plan fonctionnant selon ce procede WO1982003436A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3113116810401 1981-04-01
DE19813113116 DE3113116A1 (de) 1981-04-01 1981-04-01 "verfahren zum stroemungskraftausgleich bei einem flachschieberventil sowie nach diesem verfahren arbeitendes flachschieberventil"

Publications (1)

Publication Number Publication Date
WO1982003436A1 true WO1982003436A1 (fr) 1982-10-14

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ID=6129041

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1982/000073 WO1982003436A1 (fr) 1981-04-01 1982-03-30 Procede d'equilibrage des forces d'ecoulement dans un tiroir plan et tiroir plan fonctionnant selon ce procede

Country Status (4)

Country Link
JP (1) JPS58500451A (fr)
DE (1) DE3113116A1 (fr)
FR (1) FR2503314A1 (fr)
WO (1) WO1982003436A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3620818A1 (de) * 1986-06-21 1987-12-23 Asys Gmbh Ges Fuer Die Herstel Magnetventil fuer fluessige und gasfoermige medien

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3704189A1 (de) * 1987-02-11 1988-08-25 Bosch Gmbh Robert Stelleinrichtung fuer ein hydraulisches, elektrisch steuerbares proportionalventil

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2964058A (en) * 1957-03-21 1960-12-13 Cleveland Pneumatic Ind Inc Hydraulic valve with controlled bypass to reduce operational sensitivity
US2986165A (en) * 1956-01-23 1961-05-30 Cleveland Pneumatic Ind Inc Balanced slide valve
US3370611A (en) * 1964-11-21 1968-02-27 Dowty Hydraulic Units Ltd Slide valves

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2986165A (en) * 1956-01-23 1961-05-30 Cleveland Pneumatic Ind Inc Balanced slide valve
US2964058A (en) * 1957-03-21 1960-12-13 Cleveland Pneumatic Ind Inc Hydraulic valve with controlled bypass to reduce operational sensitivity
US3370611A (en) * 1964-11-21 1968-02-27 Dowty Hydraulic Units Ltd Slide valves

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3620818A1 (de) * 1986-06-21 1987-12-23 Asys Gmbh Ges Fuer Die Herstel Magnetventil fuer fluessige und gasfoermige medien

Also Published As

Publication number Publication date
FR2503314B1 (fr) 1985-05-17
JPS58500451A (ja) 1983-03-24
FR2503314A1 (fr) 1982-10-08
DE3113116A1 (de) 1982-10-21

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