WO1988001073A1 - Valve permettant de maintenir constant le debit d'un fluide - Google Patents

Valve permettant de maintenir constant le debit d'un fluide Download PDF

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Publication number
WO1988001073A1
WO1988001073A1 PCT/CH1987/000091 CH8700091W WO8801073A1 WO 1988001073 A1 WO1988001073 A1 WO 1988001073A1 CH 8700091 W CH8700091 W CH 8700091W WO 8801073 A1 WO8801073 A1 WO 8801073A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow
section
differential pressure
cross
pressure range
Prior art date
Application number
PCT/CH1987/000091
Other languages
German (de)
English (en)
Inventor
Jakob Rothenberger
Original Assignee
Jakob Rothenberger
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 Jakob Rothenberger filed Critical Jakob Rothenberger
Publication of WO1988001073A1 publication Critical patent/WO1988001073A1/fr

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Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/01—Control of flow without auxiliary power
    • G05D7/0106—Control of flow without auxiliary power the sensing element being a flexible member, e.g. bellows, diaphragm, capsule
    • G05D7/012—Control of flow without auxiliary power the sensing element being a flexible member, e.g. bellows, diaphragm, capsule the sensing element being deformable and acting as a valve

Definitions

  • Valve device for keeping a predetermined flow of fluids constant.
  • Fig. 1,2,3 it is a flow stabilizer, in which the constant or control current consists of two flows, a first with a fixed flow cross-section, the flow increases in proportion to the differential pressure and a second current falling with increasing differential pressure , with the sum of both flows remaining approximately constant starting at approx. 1.5 bar differential pressure and ending at approx. 7 bar.
  • the second stream rises steeply up to the differential pressure of 1.5 bar and then drops to zero at 6.5 bar at 1 to 1.5 bar.
  • the flow cross-section of the second flow is controlled by a soft, elastic, approx.
  • Flow stabilizers from effective pressures of 0.3 bar and above require cylindrical, compressible elastomers, which deform at these pressures and are thus able to reduce the flow cross-section, unless the drop in the complementary current flow should be delayed over a larger effective pressure range as the effective pressure increases or the direct current curve rises less rapidly during the differential pressure range than is normally the case with a fixed bore.
  • the sum of the two currents, the direct current and the complementary current remains constant or more or less the same, or that this sum corresponds to any X constant current, but the constant current must predetermined flow size in liters / minute or m3 / h.
  • the flow cross sections of the two partial flows and their flow rates must therefore be known and predetermined over the entire differential pressure range.
  • the direct current curve must first be defined over the entire differential pressure range, i.e. the differential pressures at the beginning and end of the range, as well as the currents corresponding to these pressures, the direct current flowing at maximum differential pressure having to be equal to the constant current determined in advance. Determining the corresponding flow cross-section is no problem.
  • This same cross-section for the direct flow now also applies to the beginning of the differential pressure range, be it at 0.3, 0.5, 1 or 3 bar etc., the flow rates of which can also be determined without a long calculation.
  • FIGS. 1, 2 and 3 show the nozzle body 1 with the partial circular ring seat surfaces 2 for the elastomer which lies loosely on the seat surfaces. Its flow ribs 4 have the task of channeling the water flow and fixing the elastomer radially and axially.
  • Elastomer 3 and nozzle body 1 are seated in a tube-like housing 10 with counter screw 11 and seal 12. A portion of the direct flow that increases with increasing differential pressure flows through the bore 5 in the direction of the outlet 13. Depending on the level of the direct flow, the diameter and the number of these bores can be increased that the gradations are within a liter / minute even for larger currents.
  • the axial bore 9 through the elastomer serves to increase the direct flow, the increase in the current curve being less steep as the differential pressure increases than with the direct flow with an unchangeable flow cross-section.
  • flow cross sections can also be passed through the nozzle screwing part of the body 11.
  • the elastomer 3 sits with its flat end face on the likewise flat annular or circular section-shaped seat surface 2 of the hollow cylindrical wall of the nozzle 1, which has diametrically symmetrical recesses 7 and 6, which together with the flat end face of the elastomer 3 form the Form triangles or circular sections and serve as a flow cross-section for the complement flow.
  • FIG. 4 shows in a diagram created on the basis of a sample test the course of the two partial flows, the direct flow 13 and the complementary flow 14 and the constant flow 15 within an effective pressure range from 0.5 bar to a maximum of 6 bar.
  • the constant current determined in advance already flows at an effective pressure of 0.5 bar.
  • the constant flow determined in advance at 10 liters / minute is equal to the direct flow at the end of the differential pressure range. This is a rule that is fully valid for all constant currents and in all differential pressure ranges. Without this requirement, the flow cross section of the complementary flow cannot be calculated. This cross-section must be calculated if the result of the flow control and constant flow should result in a predetermined quantity of the current in liters / minute.
  • this constant flow must have a predetermined size and this size must remain constant over the entire differential pressure range, ie its tolerance should be within plus / minus 4%. If tolerances of more than plus / minus 6% can no longer be spoken of as a constant current or as a regulation.
  • a second prerequisite for the calculability of the constant stronies and thus also of the two partial flows with their flow cross sections is the predictability of the flow cross sections, if necessary across the entire differential pressure range; which in turn presupposes that the flow cross-sections have a calculable shape and this also from the beginning of the differential pressure range to the end of it.
  • the size of the differential pressure range must also be determined in advance, ie start at X differential pressure and end at X differential pressure.
  • the size of the differential pressure range depends exclusively on the requirements made by the market. For example, it would be pointless to have a differential pressure range of 8, 10 or even 12 bar if the flow-through holder is used for commercial and household appliances, i.e. for an area where maximum effective pressures of 6 bar but minimum working pressures of 1 bar or below are the rule or for industrial water pump feeds, where it is a matter of eliminating the pressure fluctuations of the pump, for example between 6 and 8 bar, by using a flow stabilizer in the differential pressure range between 5 and 5 bar.
  • a bore 3 in the valve seat 1 with a diameter of 2.8 mm is required, which corresponds to a cross-sectional area of 6.16 mm 2 .
  • a direct flow of 3.3 liters / minute flows through this cross-sectional area.
  • the flow cross-section of the complementary flow has to produce the difference of up to 10 liters / minute, that is 6.7 liters. If 3.3 liters at 0.5 bar a flow cross section require a flow cross section of 6.16 mm, then.
  • the complementary flow requires a flow cross-section of 12.5 mm 2 for its 6.7 liters, plus an addition of 6.5 mm 2 for the significantly higher flow resistance, thus a total of 19 mm 2 . Since the nozzle 1 has two triangular flow cross-sections, 9.5 mm 2 cross-sectional area remain per triangle, this results in a triangle with an obtuse angle with a hypotenuse of 13 mm and a height of 1.45 mm and an obtuse angle of 155 degrees. The complementary stream therefore starts at
  • the power share of the direct current according to field ABFD in the constant current according to field ABFG is significantly higher than the complementary current share according to field ABC and that the flow characteristic of the direct current determines the control characteristic of the complementary flow and that the flow of the complementary flow 14 in same mass according to letter b decreases as the direct current 13 increases according to letter a.
  • the gate parts of this invention are:

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Safety Valves (AREA)

Abstract

Pour maintenir constant le débit d'un fluide dans un conduit, on divise le débit en deux débits partiaux: le plus grand est un courant direct dont l'importance augmente à pression croissante et l'autre est un courant complémentaire diminuant proportionnellement et qui traverse des orifices en forme triangulaire ou de segment de cercle. Ces orifices sont délimités, pour la pression effective, par des évidements (7, 6) et la face frontale plane de l'élastomère (3) compressible et commandé par la pression effective, et ils sont agencés de façon qu'une pression effective de 0,5 bar rétrécisse la section d'écoulement et que la pression effective maximum ferme cette section d'écoulement. La somme des débits partiaux est toujours égale au débit constant.
PCT/CH1987/000091 1986-07-25 1987-07-22 Valve permettant de maintenir constant le debit d'un fluide WO1988001073A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2989/86-3 1986-07-25
CH298986A CH672850A5 (fr) 1986-07-25 1986-07-25

Publications (1)

Publication Number Publication Date
WO1988001073A1 true WO1988001073A1 (fr) 1988-02-11

Family

ID=4246159

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CH1987/000091 WO1988001073A1 (fr) 1986-07-25 1987-07-22 Valve permettant de maintenir constant le debit d'un fluide

Country Status (3)

Country Link
EP (1) EP0276245A1 (fr)
CH (1) CH672850A5 (fr)
WO (1) WO1988001073A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10059386A1 (de) * 2000-11-30 2002-06-13 Aixtron Ag Verfahren und Vorrichtung zur dosierten Abgabe kleiner Flüssigkeitsvolumenströme
EP1321156A1 (fr) 2001-12-19 2003-06-25 WEX, Roland Soupape servant à maintenir sensiblement constant le débit d'un fluide

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2444677A (en) * 1946-12-14 1948-07-06 Dole Valve Co Flow control device
DE1049176B (de) * 1956-06-11 1959-01-22 Hays Mfg Company Selbsttaetige Vorrichtung zur Regelung der Durchflussmenge
US2989086A (en) * 1958-02-27 1961-06-20 Dole Valve Co Solid flow control valve
FR2507795A1 (fr) * 1981-06-16 1982-12-17 Thomson Brandt Regulateur de debit de fluide et machine a laver munie d'un tel regulateur

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2444677A (en) * 1946-12-14 1948-07-06 Dole Valve Co Flow control device
DE1049176B (de) * 1956-06-11 1959-01-22 Hays Mfg Company Selbsttaetige Vorrichtung zur Regelung der Durchflussmenge
US2989086A (en) * 1958-02-27 1961-06-20 Dole Valve Co Solid flow control valve
FR2507795A1 (fr) * 1981-06-16 1982-12-17 Thomson Brandt Regulateur de debit de fluide et machine a laver munie d'un tel regulateur

Also Published As

Publication number Publication date
EP0276245A1 (fr) 1988-08-03
CH672850A5 (fr) 1989-12-29

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