WO1990012232A1 - Soupape pour milieux sous pression - Google Patents

Soupape pour milieux sous pression Download PDF

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Publication number
WO1990012232A1
WO1990012232A1 PCT/DE1990/000280 DE9000280W WO9012232A1 WO 1990012232 A1 WO1990012232 A1 WO 1990012232A1 DE 9000280 W DE9000280 W DE 9000280W WO 9012232 A1 WO9012232 A1 WO 9012232A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
valve according
bores
outflow
diameter
Prior art date
Application number
PCT/DE1990/000280
Other languages
German (de)
English (en)
Inventor
Götz-Dieter MACHAT
Eugen Ebert
Hans WÖLFGES
Original Assignee
Mannesmann Rexroth 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 Mannesmann Rexroth Gmbh filed Critical Mannesmann Rexroth Gmbh
Publication of WO1990012232A1 publication Critical patent/WO1990012232A1/fr

Links

Classifications

    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/10—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with auxiliary valve for fluid operation of the main valve

Definitions

  • the invention relates to a pressure medium valve, in particular to a pilot-controlled pressure limiting and pressure switching valve.
  • the invention relates to a pressure relief valve according to the preamble of claim 1.
  • Valves of this type are already known and are explained in the description of the figures with reference to FIGS. 1 to 4.
  • the additional force in the opening direction causes an additional stroke which the piston would not carry out under the same conditions, but without the lateral screwing in on the cylindrical surface of the piston.
  • the control deviation of this known valve is reduced by this additional stroke.
  • a major disadvantage of the lateral screwing in on the piston is, however, that the additional force generated by the dynamic pressure in the outflow area in the opening direction is dependent on the stroke or volume flow, which
  • REPLACEMENT LEAF "S" -shaped characteristic curve results.
  • Another disadvantage is the poor repeatability in the production of the concave profile of the lateral surface, so that deviations in the characteristic curves occur in valves from different production lots.
  • the present invention has for its object to form a pressure medium valve according to the preamble of claim 1 and other claims while avoiding the disadvantages of the prior art.
  • the invention aims to design the pressure medium valve in such a way that the control deviation of the valve is low in the entire quantity range of the respective nominal size, with good stability being achieved at the same time. According to the invention, this is done by effectively compensating the axial component of the flow force in the outflow region of the valve bushing.
  • the pressure medium valve according to the invention should be able to be manufactured with good repeatability. Furthermore, favorable noise behavior is sought.
  • the invention provides a pressure medium valve according to claim 1.
  • FIG. 1 shows a known main valve of a pilot-controlled pressure relief valve with a conventional ring channel
  • Fig. 2 control characteristics for the valve of FIG. 1;
  • FIG 3 shows another known main valve with a concave piston surface for a pilot operated pressure relief valve (e.g. DB 20K series 4x);
  • a pilot operated pressure relief valve e.g. DB 20K series 4x
  • FIG. 5 schematically shows a first exemplary embodiment of a main valve according to the invention for a pilot-controlled pressure limiting valve
  • Fig. 7 is a schematic, partially sectioned detail of the valve of Fig. 5;
  • Fig. 8 is a section along line 8-8 in Fig. 7;
  • FIG. 9 shows a detail from FIG. 7 for accommodating the numerous reference numerals
  • FIG. 10 shows a second exemplary embodiment of a main valve, although this is not a seat valve as in FIG. 5, but a slide valve;
  • FIG. 11 shows a section along line 11-11 in FIG. 10;
  • FIG. 13 shows the same representation as FIG. 10, but here the pressure medium flow is indicated by arrows;
  • FIG. 15 shows a section of the known valve according to FIG. 1;
  • FIG. 16 shows a detail of the valve according to the invention according to FIG. 5;
  • FIG. 17 shows a comparison of the control characteristic curve for the valves according to FIGS. 15 and 16 (similar to FIGS. 2 and 6);
  • FIG. 21 shows a fourth embodiment of the invention
  • Fig. 22 shows a fifth embodiment of the invention
  • REPLACEMENT LEAF 23 shows a representation similar to FIG. 7 to illustrate an essential feature of the invention.
  • 24 shows a sixth exemplary embodiment of the invention.
  • main stage valves main stage valves
  • FIGS. 1 to 4 main stage valves
  • FIGS. 7 to 9 a first exemplary embodiment of a pressure medium valve according to the invention is described with reference to FIG. 5, in the context of a pressure relief valve, as is preferably to be used in a pilot-controlled pressure relief valve of FIG. 14.
  • FIGS. 10 and 11 A second exemplary embodiment of the invention will then be described with reference to FIGS. 10 and 11, but in contrast to FIGS. 5 to 9 it is not a seat valve but a slide valve.
  • FIGS. 12 to 19 show three further exemplary embodiments of the invention, which illustrate a further principle of the invention.
  • FIG. 1 shows in section a known pressure relief valve 10, which has a bushing 11 with an inflow bore 12 running symmetrically to the longitudinal or valve axis 13 and outflow bores 14 running transversely to the valve axis 13.
  • a valve piston 16 is mounted so that it can be moved back and forth and is biased against the valve seat by a spring 17.
  • FIG. 3 shows another known pressure relief valve 20, in which the piston 22, which is mounted so that it can move back and forth in the sleeve 11, has a concave piston jacket surface 21.
  • Fig. 4 shows, somewhat exaggerated, the control characteristics for the valve of Fig. 3.
  • the lateral screwing in on the piston has the effect that the additional force generated by the dynamic pressure in the outflow region is dependent on the stroke or volume flow in the opening direction, which leads to the S-shaped characteristic curve shown.
  • FIG. 5-9 show a first exemplary embodiment of a pressure limiting valve 24 according to the invention with a bush 25 in which a plurality of outflow bores 26 running perpendicular to the longitudinal axis 13 of the valve 24 and an inflow bore 12 parallel to the valve axis 13 are formed.
  • the annular channel 19 already present in the valve of FIG. 1 is improved.
  • the ring channel is identified by 27, on the basis of whose use the favorable control characteristics shown in FIG. 6 are obtained.
  • the first embodiment of the invention is shown enlarged and it can be seen that the annular channel 27 has a width b2.
  • the ring channel 27 consists of an actual ring channel 30 with the width b 1 and a so-called ring channel section 37.
  • the ring channel section 37 is part of a conical valve seat surface 35 which, through the valve seat 36, leads into the already mentioned ring channel section 37 and a connecting section 38 is divided.
  • the conical valve seat surface 35 merges upstream into the inflow bore 12.
  • the valve piston 16 is preferably circular cylindrical in cross section.
  • the actual ring channel 30 has a ring channel start
  • an overall inflow slope is designated, which runs between the valve seat 36 and the beginning of the annular channel bottom surface 32.
  • a piston edge 40 formed by the piston 16 sits on the valve seat 36.
  • the width of the total inflow slope 39 is designated by c.
  • annular channel-free zone 43 (see, for example, FIG. 7) with a width f is formed between the end of the annular channel 27 in the flow direction and the apex line of the outflow bore 26 which is furthest away in the direction of fluid flow.
  • the distance or the width between the valve seat 36 and the central axis 41 is denoted by a.
  • annular control cross-section 45 is formed between the piston edge 40 and the total inlet slope 39.
  • annular channel 27 runs largely in webs 47 remaining between the outflow bores 6.
  • the annular channel start slope 39 forms an angle beta with respect to the valve axis 13, while the conical valve seat surface 35 forms an angle alpha.
  • Q _ p funding stream Q H - volume flow main stage; Q v - volume flow pilot stage; P A - inlet pressure; P ⁇ - pilot stage; 1 - orifice for control volume flow (usually several resistors are connected in series); 2 - orifice to dampen the movement of the main piston; 3.4 - relief orifices (DBW)
  • FIGS. 10, 11 and 13 show a so-called poppet valve
  • a slide valve 50 will now be described as a second exemplary embodiment of the invention with reference to FIGS. 10, 11 and 13.
  • the difference between the second exemplary embodiment and the first exemplary embodiment is that no conical valve seat surface 35 is provided here and that the valve seat 36 is formed directly at the intersection of the annular channel bevel 31 and the inflow bore 12. Accordingly, the same reference numerals are used as in the previous embodiment.
  • a / dl 0.18 to 0.35
  • b / dl 0.16 to 0.25
  • valves 24, 50 according to the invention have a particularly low control deviation in the stationary area and good stability behavior, and they are used especially as main stages in both pressure limiting valves and pressure connection valves.
  • the geometric dimensions are characterized by the above-mentioned ratio values. Taking these ratio values into account, comparably good results can be achieved with valves with different piston diameters.
  • the pressure set In the case of pilot operated pressure relief valves, the pressure set generally increases with the volume flow. This pressure increase, based on the range of change of the volume flow, represents the control deviation of the valve in the steady operating state
  • the force of the main piston spring 17 increases. Its pretensioning force and rigidity are designed to be low, since the main piston 16 is piloted or "preloaded” by an oil volume under pressure.
  • the high flow rate in the variable control cross section 45 requires only small changes in stroke in the case of large setting pressures and large changes in volume flow.
  • the increase in spring force with the piston stroke is therefore very small.
  • the increase in the spring force due to the amplification by the effect chain of the control volume flow control deviation of the pilot control pressure limiting valve can result in a not insignificant increase in the control deviation of the overall valve.
  • the change in the spring force influences the control deviation in a direct and indirect way: directly through the change in the spring force alone, and indirectly through the increase in the control volume flow.
  • An increase in the control volume flow results in an increase in the control pressure (control deviation of the pilot pressure relief valve 5), which in turn causes an increase in the inlet pressure at the main connection of the valve 24.
  • the liquid jet In order to be able to pass through the narrowest cross section of the throttle, the liquid jet must be strongly accelerated. For this purpose, the potential energy of the static pressure is converted into kinetic acceleration energy. The resulting pressure loss is synonymous with the flow force.
  • a constant control pressure is applied to the main stage of a pilot-controlled pressure relief valve (e.g. by supplying the control volume flow to the pilot pressure relief valve via a quantity regulator), an increase in the set pressure P setpoint is measured with increasing volume flow over the main stage .
  • the flow force acts on the piston 16 in the closing direction and is the main cause of the rise in pressure.
  • the resulting pressure increase proportional to the volume flow downstream of the variable control cross-section largely compensates for the pressure loss responsible for the flow flow upstream in the inflow area in the vicinity of the variable control cross-section 45. In other words: due to the increased pressure in the The gap between piston 16 and bore webs 47 (eg FIG. 11) the integral pressure difference at the control cross section is smaller.
  • the piston 16 will therefore perform a larger opening stroke, or the same increase in volume flow corresponds to a greater increase in the control cross-sectional area than in the case of an annular duct of the conventional design with a lower dynamic pressure in this outflow annular gap. This significantly reduces the increase in inlet pressure with the volume flow.
  • FIG. 15-18 shows a comparison of the characteristic curves of the pressure as a function of the volume flow and of the control volume flow as a function of the flow rate with the pressure as parameters for a main stage of the old, conventional construction (FIG. 15) and a main stage shown with new seat geometry (Fig. 16).
  • FIG. 19 shows the course of the flow force for three cases, A, B and C. With A and B the resistance of the inner ring channel is negligible. In Fig. 19c, 99 denotes the inner outflow channel.
  • the measurements relating to the change in the flow force with the piston stroke basically have the same course (FIG. 19).
  • the flow force initially rises sharply with the piston stroke and the volume flow, from the maximum of the flow force the volume flow remains constant in the further course and the flow force then drops hyperbolically with the piston stroke.
  • the maximum could be considerably reduced (FIG. 19, dashed curve), hence the good stability and low tendency to flutter.
  • the effect of the flow force on the control deviation of the valve is - similar to that of the force of the main piston spring - amplified by the control deviation of the pilot control, i. H. an increase in the flow force causes an increase in the pressure drop at the orifice for the control volume flow, this increases and causes an increase in the control pressure and thus the inlet pressure.
  • REPLACEMENT LEAF 20 shows in section a third exemplary embodiment of the invention, of which only one valve sleeve 60 is shown in section, while the piston has been omitted.
  • an inflow bore 12 and a plurality of outflow bores 26 with the diameter d3, which are arranged in a plane perpendicular to the longitudinal axis 13 of the valve and are arranged at a radial distance, are provided.
  • this is a poppet valve
  • only an annular channel bevel 61 is provided, similarly to the exemplary embodiment according to FIG. 10, which coincides with the conical valve seat surface and forms the valve seat 63.
  • the ring channel is designated 64 here and has a width b2. It can be seen that an annular channel-free zone 43 with the width f remains, which, despite the fact that here b2 is approximately equal to d3, results in an advantageous mode of operation for the valve.
  • the angle beta is preferably 30 ° here.
  • FIG. 21 shows a fourth exemplary embodiment of the invention, specifically in a modification of FIG. 20 insofar as here again a conical valve seat surface 65 with a valve seat 66 is provided separately. An annular channel slope 67 is then provided. The width b2 of the ring channel 69 is larger here than the diameter d3 of the outflow bores 26. Nevertheless, the valve can be operated advantageously.
  • the ring channel-free zone is again designated 43 and has a width f.
  • annular channel 71 in turn has a width b2 which is substantially larger, approximately 50% larger than the diameter d3 of the outflow bores 73.
  • annular channel-free zone 43 with a width f.
  • outflow bores 73 and 74 with different diameters are provided.
  • REPLACEMENT BATT A merma er prior to the transition in the control area of the control piston from the inlet bore to the ring channel.
  • This measure already achieves a substantial improvement in the control behavior of the pressure valve. See Fig. 23, which was derived from Fig. 7 to illustrate this measure.
  • the level shown in Fig. 7 results in practice from grinding. However, it should be pointed out that the diameter d2 is larger than that of the inflow bore 12.
  • a stepless transition region 31, 35 is provided in the control region of the control or control edge 40 between the inflow bore 12 and the annular channel 27 .
  • transition region 31, 35 is composed of two conical partial regions, which simultaneously form the one boundary wall of the annular channel 27, the one partial region 35 adjoining the inflow opening 12 at an angle oi. runs between 10 ° and 25 ° and the second partial area 31 runs at an angle, which corresponds to the angle, or an angle ⁇ . + 7.5 ° to 15 °.
  • transition region 35 adjoining the inflow opening 12 forms the seat 36 for the control or piston edge 40 and is ground. It is preferred that the longitudinal extent of the two partial areas 31, 37 is approximately the same. It should be pointed out that the zone (width f) of the outflow bores 26 free of the annular channel is preferably at least 30% of the diameter d3 of the outflow bores 26.
  • the width b 7 of the ring channel 27 is smaller than the diameter d3 of the outflow bores 26. At least 6, preferably 8, outflow bores are preferably provided. The one facing away from the inflow opening 12
  • the annular channel width b 2 is larger than the diameter d3 of the outflow bores 73. These dimensions are preferred.
  • a good dependency on the pressure quantity with stable control behavior is preferably achieved if the following conditions are met:
  • the width of the ring channel 27 is the diameter d, the inflow or piston bore 12 in a ratio of less than 1: 4. At least 6 outflow bores 26 are provided.
  • the diameters d 2 / d- are in a ratio of 1.05 to 1.15.
  • FIG. 24 shows a sixth exemplary embodiment of the invention in which the outflow openings are arranged in two rows compared to the previous exemplary embodiments, with a favorable influence on the noise behavior.
  • an inlet bore 117 with a diameter d2 and two rows 118, 119 of exhaust bores 120 and 121 are provided in a bush 116.
  • the bores in the two rows 118 and 119 are preferably offset from one another (as shown).
  • the bores 120 and 121 have different diameters.
  • An annular channel 127 has a width b "such that a zone 43 free of an annular channel remains with a width f.
  • the general statements mentioned above also apply analogously to this exemplary embodiment.
  • the outflow bores 120, 121 can also open "Several levels are arranged on the circumference. Preferably, more than 8 outflow bores are arranged on each level.
  • the outflow bores in the row facing the seat surface have a diameter which is smaller than the width b 2 of the ring channel, and they lie in the latter Area, the row 118 of the outflow bores 120 facing away from the seat surface lying partly in the upper area of the ring channel and partly in the area of the zone 43 free of the ring channel. It is further preferred that the outflow holes 120 facing away from the seat surface have a larger diameter than that facing the seat surface outflow bores 121.
  • the invention provides a pressure medium valve with an inlet bore, an annular channel and a control piston, in which an annular channel is provided on the outflow side in order to achieve a low control deviation and good stability, the axial extent of which is smaller than the outflow area formed by bores.
  • the valve piston Preferential meadow the outflow bores run perpendicular to the longitudinal axis of the valve.
  • the valve piston preferably has a circular cylindrical cross section without, for example, a concave jacket surface as in FIG. 3.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)
  • Lift Valve (AREA)

Abstract

Une soupape pour milieux sous pression comprend un alésage d'entrée (12), un canal annulaire (27) et un piston de commande (16). Afin d'obtenir des écarts minimes de réglage et une bonne stabilité, la dimension axiale d'un canal annulaire (17) agencé côté sortie de la soupape est inférieure à la dimension axiale de la zone de sortie formée par des alésages (26).
PCT/DE1990/000280 1989-04-07 1990-04-09 Soupape pour milieux sous pression WO1990012232A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP3911426.0 1989-04-07
DE3911426A DE3911426C2 (de) 1989-04-07 1989-04-07 Druckventil

Publications (1)

Publication Number Publication Date
WO1990012232A1 true WO1990012232A1 (fr) 1990-10-18

Family

ID=6378161

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1990/000280 WO1990012232A1 (fr) 1989-04-07 1990-04-09 Soupape pour milieux sous pression

Country Status (3)

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JP (1) JP2898088B2 (fr)
DE (1) DE3911426C2 (fr)
WO (1) WO1990012232A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008119374A1 (fr) * 2007-03-29 2008-10-09 Hydac Fluidtechnik Gmbh Valve de distribution pour systèmes hydrauliques

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19505129A1 (de) * 1995-02-16 1996-08-22 Rexroth Mannesmann Gmbh Vorgesteuertes Druckbegrenzungsventil
DE19540529B4 (de) * 1995-10-31 2004-10-28 Deutz Ag Absteuerventil des Schmierölkreislaufs einer Brennkraftmaschine
DE10155422A1 (de) * 2001-11-12 2003-05-22 Bosch Rexroth Ag Rückschlagventil
DE102011118257A1 (de) 2011-11-11 2013-05-16 Robert Bosch Gmbh Druckventil
DE102014107708A1 (de) * 2014-06-02 2015-12-03 Lisega SE Ventil für Hydraulikdämpfer

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2164736A1 (de) * 1971-02-11 1972-08-24 Orsta Hydraulik Veb K Druckventil, vorzugsweise zum Einschrauben oder Einstecken, mit Steuerölstrom
DE3318246A1 (de) * 1983-05-19 1984-11-22 Mannesmann Rexroth GmbH, 8770 Lohr Druckbegrenzungsventil
DE3824089A1 (de) * 1988-04-22 1989-11-02 Rexroth Mannesmann Gmbh Vorgesteuertes proportional-druckbegrenzungsventil

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB990038A (en) * 1961-04-13 1965-04-22 Brakeshoe Internat S A Improvements in high speed fluid control valves
GB1347730A (en) * 1971-09-22 1974-02-27 Circle Seal Corp Pilot-controlled pressure relief valve
DE2827128A1 (de) * 1978-06-21 1980-01-03 Zahnradfabrik Friedrichshafen Kompaktes, vorgesteuertes druckbegrenzungsventil

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2164736A1 (de) * 1971-02-11 1972-08-24 Orsta Hydraulik Veb K Druckventil, vorzugsweise zum Einschrauben oder Einstecken, mit Steuerölstrom
DE3318246A1 (de) * 1983-05-19 1984-11-22 Mannesmann Rexroth GmbH, 8770 Lohr Druckbegrenzungsventil
DE3824089A1 (de) * 1988-04-22 1989-11-02 Rexroth Mannesmann Gmbh Vorgesteuertes proportional-druckbegrenzungsventil

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008119374A1 (fr) * 2007-03-29 2008-10-09 Hydac Fluidtechnik Gmbh Valve de distribution pour systèmes hydrauliques

Also Published As

Publication number Publication date
DE3911426A1 (de) 1991-08-01
DE3911426C2 (de) 1994-09-08
JPH04500551A (ja) 1992-01-30
JP2898088B2 (ja) 1999-05-31

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