WO2007098630A1 - Soupape de régulation du debit et procede d'elimination des oscillations - Google Patents

Soupape de régulation du debit et procede d'elimination des oscillations Download PDF

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Publication number
WO2007098630A1
WO2007098630A1 PCT/CH2007/000104 CH2007000104W WO2007098630A1 WO 2007098630 A1 WO2007098630 A1 WO 2007098630A1 CH 2007000104 W CH2007000104 W CH 2007000104W WO 2007098630 A1 WO2007098630 A1 WO 2007098630A1
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WO
WIPO (PCT)
Prior art keywords
valve
throttle body
flow
control
drive motor
Prior art date
Application number
PCT/CH2007/000104
Other languages
German (de)
English (en)
Inventor
Urs Keller
Giuseppe Pulli
Marc Thuillard
Original Assignee
Belimo Holding Ag
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 Belimo Holding Ag filed Critical Belimo Holding Ag
Publication of WO2007098630A1 publication Critical patent/WO2007098630A1/fr

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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
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/08—Details
    • F16K5/12—Arrangements for modifying the way in which the rate of flow varies during the actuation of the valve
    • 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member
    • F16K47/045—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member and the closure member being rotatable

Definitions

  • the invention relates to a valve for liquid and / or gaseous, flowing media, with a valve housing, which forms a valve chamber provided with at least one inlet and one outlet, and a movable therein and positionable throttle body for controlling the hydraulic cross section, wherein at least one flow path is formed. Furthermore, the invention relates to a method for eliminating vibrations in a control loop with this valve. State of the art
  • Regulators such as gate valves, valves or valves, are used to control the flow rates in the piping to ensure optimum operating conditions and environmental safety.
  • Generic valves are used in particular in the field heating-ventilation-climate, short HVAC.
  • Flow requirement can not be met. If the flow opening of the valve is too large, the flow rate can not be regulated precisely enough and / or control oscillations occur if the flow rate is low. All these effects are undesirable.
  • control quality can be improved with the arrangement of different sized valves for summer and winter.
  • Fig. 1 shows a progressively increasing characteristic K of a known rotary valve.
  • Each valve has characteristic curves K, with the abscissa representing the setting angle or the linear displacement, and the ordinate the percentage of the maximum flow rate. Within an angle ⁇ of 90 °, the flow is increased from 0 to 100% of the maximum flow through the valve.
  • ⁇ 90 °
  • the flow is increased from 0 to 100% of the maximum flow through the valve.
  • the flow rate is low, it may be necessary to switch to a parallel-connected valve with a lower maximum flow rate.
  • US 5,983,937 A Proposes a three-way valve with two inlets and one outlet for the controlled mixing of cold and hot water streams.
  • a rotatable hollow cylinder In the valve housing while a rotatable hollow cylinder is mounted with different and separate flow openings on the lateral surface.
  • the various flow openings of the hollow cylinder can be aligned with a motor relative to the inlets. Due to an increasing in the direction of rotation flow opening the flow area can be controlled continuously in a single control range.
  • the other flow openings are either completely open or completely closed and are intermittently opened and closed for fine adjustment.
  • Such valves are therefore only of limited suitability, in particular for low flow rates to regulate precisely.
  • the fine adjustment through digital "A ⁇ f-Zu" cycles leads to a discontinuous flow of fluid flows through the valve, which in turn leads to control oscillations.
  • the present invention is therefore an object of the invention to provide a valve of the type mentioned and a method for its operation, which eliminate the disadvantages mentioned.
  • the object is achieved according to the invention in that, when moving in the valve chamber, the throttle body alternatively forms at least two different characteristic curves per flow path.
  • a valve which can be used for a wide variety of applications or for a wide variety of control circuits.
  • the characteristic curve is preferably selected automatically (by an intelligent controller).
  • a control oscillation eliminated or at least mitigated.
  • the unwanted vibrations can z. B. be suppressed by the method which is known from WO 2006 / 105677A2 (Belimo). It is also possible to actuate the valve with a cost-effective drive, because the fine control in various flow areas is substantially facilitated by the proper or adapted characteristic curve.
  • the characteristic curve is determined by the valve design (design of the movable throttle body and interaction with the static flow openings of the housing). defined functional dependence of the flow cross-section or hydraulic cross-section of the valve of the position (eg., Angular graduation, position) of the throttle body understood.
  • the valve according to the invention is a module which he uses as part of his control circuit. So z.
  • the temperature is measured at a location of the HVAC system and the system control circuit determines a system control signal V HVAC (eg as an analog voltage value, as a pulse sequence, as a digital value) which serves as input for the valve according to the invention , Due to this system control signal, the position x of the throttle body is adjusted.
  • V HVAC system control signal
  • the appropriate characteristic K so that the gain G is optimal:
  • , x) is the hydraulic cross section or effective flow and x is the position (eg the angular position) of the throttle body.
  • the position x can be varied per characteristic within a lower and an upper limit x u or X 0 , whereby the areas belonging to different characteristic lines completely, partially or not overlap depending on the construction of the valve. It is understood that G ⁇ O must be in order for a regulation is possible.
  • a flow path in the sense of the invention is a path that the medium (when used as intended) in the valve can take from the inlet to the outlet if the path is not blocked due to the position of the throttle body.
  • the medium (when used as intended) in the valve can take from the inlet to the outlet if the path is not blocked due to the position of the throttle body.
  • valve has control ranges (I, II, III) with different flow openings.
  • the position x of the throttle body is selected by means of at least one drive motor connected to the valve.
  • valves according to the invention are therefore more cost-effective to produce, since expensive precision components, additional valves connected in parallel and complex controls can be dispensed with.
  • the throttle body of the valve according to the invention has at least two (eg separate) control ranges, the control range being different for each control range.
  • a setting range in the sense of the invention allows the continuous adjustment of the flow rate (controlled variable) between zero and a range-specific maximum value. value (u 0 A) which is less than or equal to the maximum possible flow rate (100%) through the valve.
  • the valve according to the invention has two or more control ranges of the throttle body, which operate optimally for different flow rates. At low flow rates, the throttle body can be positioned so that the smaller flow port is in use. If the flow rates increase, the drive motor autonomously moves the throttle body into a different setting range, which is created for larger flow rates.
  • the fine adjustment is preferably carried out by means of the same drive motor, but it can also be used two drive motors. This results in different characteristics for the different control ranges with the same movement of the throttle body.
  • This has the advantage that with a conventional valve drive an extremely precise regulation of the flow rate is achieved without several different valves must be installed in parallel. It is essential that, unlike a conventional valve, an unchangeable throttle body be moved by a motor over a 0 to 100% range.
  • the preferred throttle body according to the invention with at least two selectable separate and substantially equal control ranges with different flow openings allows the position of the throttle body, ie the flow cross-section, to be optimally adapted to the flow rate.
  • valve according to the invention can be realized in various embodiments, for example by
  • the solid disc may be part of the housing.
  • the one disc has at least one passage opening, the other disc has at least two different sizes
  • the one plate has at least one flow opening, the other plate at least two different sized flow openings.
  • the flow cross-section can be set with 0 to 100% of the largest flow opening.
  • the flow cross section is formed by the flow opening and the corresponding counterpart in the valve.
  • a second, smaller flow opening allows only a flow area of 0 to u% of the largest flow opening, where u ⁇ 100.
  • u is in the range of 1 to 50.
  • the first setting range can again be set to a flow cross section from 0 to 100% of the largest flow opening.
  • the flow cross-section is 0 to v% of the largest flow opening, with a third control range 0 to w% of the largest flow opening, ie always related to the first control range, v is preferably in the range of 30 to 60, w in the range from 1 to 20.
  • a throttle body with three actuator An optimal control is possible, but the entire valve is correspondingly more complicated. This is especially true for valves with more than three control ranges, which theoretically allow an even more differentiated control, but in practice increasingly encounter difficulties of a constructive nature. ,
  • Switching to different setting ranges can be done automatically, according to given data, but also manually.
  • control oscillations can occur which are sensitive to normal operation and must be eliminated.
  • control oscillations are eliminated by autonomously guiding the throttle body to a different control range for selecting the operating point by the process-controlled drive motor and adjusting the appropriate characteristic curve by motor.
  • control circuit is designed so that the throttle body is guided by the drive motor autonomously in a lower control range, z. B. by a frequency analysis such as wavelet, Fourier or Min / Max analysis an oscillation is detected.
  • a frequency analysis such as wavelet, Fourier or Min / Max analysis an oscillation is detected.
  • Each setting range of a throttle body has a characteristic curve, as mentioned, depending on the operating point, the appropriate characteristic is selected, for example, the large or small at two control ranges or the large, medium or small at three control ranges:
  • the shapes of the curves can be set independently within certain limits, these are in particular straight or progressive increasing.
  • the choice of the appropriate characteristic at a given operating point is preferably carried out programmatically, in particular by an external controller or a control. Particularly suitable are ASIC (Application Specific Integrated Circuits) or ⁇ P (microprocessor).
  • ASIC Application Specific Integrated Circuits
  • ⁇ P microprocessor
  • the throttle body is autonomously guided by the drive motor into a lower setting range where the throttle body has a smaller flow opening , It should therefore be detected an oscillation before switching to another setting range.
  • the object with respect to the device according to a variant is achieved in that the throttle body has a single flow opening with at least two selectable by means of a drive motor control ranges.
  • the throttle body consists for example of a valve disc fixed to the housing or integrated first disc and a sealingly resting, motor-freely rotatable second disc.
  • the second disc is not only rotatable but also displaceable in the radial direction.
  • a valve housing may have two or more actuator ranges on two plates with a single flow port. This variant includes - if they can be used - all in the dependent claims and the drawings illustrated embodiments of the valve.
  • a valve with the throttle body according to the invention also called a multi-range valve, has a wide range of uses, for example FemMapung
  • multi-range valves according to the invention can be advantageously used everywhere where greatly varying demands are placed on the valves.
  • FIG. 2 shows the characteristics of the valve according to FIG. 2,
  • FIG. 5 shows the characteristics of the valve according to FIG. 4,
  • Fig. 6b shows a variant according to Fig. 6a with a connecting channel 7 shows a spherical, semi-open throttle body
  • FIG. 9 is a schematic of a district heating with a dual-range valve
  • 1 1 is a diagram of a Stell Schemes cels small - large
  • FIG. 14 shows the openings shifted in the x and y directions
  • Fig. 15 shows a circuit arrangement with a valve according to the invention.
  • Fig. 16a-e another embodiment of a spherical throttle body in three mutually rotated 90 ° positions, in the equatorial section and in a perspective view.
  • Fig. 1 shows a characteristic K for a valve according to the prior art.
  • Fig. 2 shows some details of a throttle body 10, which consists of two in a valve chamber surface sealingly superposed discs 12, 14.
  • the first disc 12 is fixedly mounted in a valve chamber of known type or integrated into the valve housing (44 in Figure 7). It is recessed a substantially trapezoidal flow opening 16, which extends in the present case over an angle of about 20 °.
  • the in the Valve chamber coaxially on the first disc 12 lying freely rotatable second disc 14 has in the same peripheral region three arranged in each circle sector of 90 ° differently sized flow openings 18, 20, 22.
  • the boundaries of the flow openings 18, 20, 22 directed towards the center of the second disk 14 are in the direction of rotation or in a tangential direction of the disk. 14 of equal length.
  • the disc 14 is connected via a shaft to a drive motor, not shown, which can rotate the disc 14 positionable clockwise and counterclockwise.
  • the second disc 14 may be fixedly mounted or integrated and the first disc 12 may be rotatable.
  • the flow openings 18, 20, 22 of the second disc 14 extend in the same peripheral region as the flow opening 16 of the first disc 12. All three flow openings 18, 20, 22 extend in a tangential direction counterclockwise, continuously or stepwise, according to the grid of the flow opening 16 of the fixed disc 12. If the second disc 14 is placed coaxially on the first disc 12 and rotated in a clockwise direction, the flow opening formed by both discs extends disproportionately. Obviously, with the flow opening 18, the largest flow cross sections 78 (FIGS. 13, 14) can be achieved, with the flow opening 22 being the smallest.
  • the mentioned drive motor rotates the disc 14 autonomously so that the optimum setting range I, II or III results.
  • Fig. 3 the characteristics of the three control ranges I, II, III of the disc 14 are recorded when the flow opening 18, 20 or 22 moves on the flow opening 16 of the first disc 12.
  • the value 100% for the flow cross-section 78 corresponds to the maximum possible flow rate when the largest portion of the flow opening 18 is in the region of the flow opening 16.
  • With the characteristic K 18 can be achieved by turning the disc 14 by an angle ⁇ of 90 °, a flow rate of 0 - 100%.
  • the characteristic K 20 shows that with the flow opening 20 with a rotation by an angle ⁇ of 90 °, a flow rate of only 40% of the maximum possible flow cross section 78 can be achieved in the adjustment range of the flow opening 22 by an angle ⁇ of 90 ° only a flow rate of almost 20% of the maximum flow cross section 78.
  • a valve with three is the same large adjustment ranges (rotation of the disc 14 by 90 ° in each case) realized, wherein all adjustment ranges continuously adjustable and different control ranges for the flow rate (I: 0 - 100%, II: 0 - have 40% and III: 0 - 20%).
  • the drive motor autonomously selects the operating point on the matching curve K 20 and rotates the disc 14 in the corresponding adjustment range II of the flow opening 20 or III of the flow opening 22nd
  • the discs 12, 14 suitably made of a ceramic or a mechanically strong plastic, such as Teflon. Essential is a good lubricity and the sealing of the flat superimposed discs 12, 14th
  • Fig. 2 shows the discs 12, 14 of a two-way valve
  • Fig. 4a those of a three-way valve are shown.
  • the three-way valve 15 according to FIG. 4b has two inputs A and B and an output AB.
  • Inputs A and B open and close in opposite directions, ie when input A is closed, input B is fully open and vice versa. In all intermediate positions, the media flowing through inputs A and B are mixedly directed to output AB.
  • the fixed disc 12 according to FIG. 4a for a three-way valve has a first flow opening 16 and a second flow opening 24, which is offset by an angle of 120 ° - 150 °.
  • the rotatable disc 14 is designed so that two adjustment ranges I and II result. As shown in FIG. 2, disc 14 may be fixedly mounted or integrated, disc 12 may be rotatable.
  • the flow opening 18 moves via the flow opening 16 in order to set the flow cross section 78 (FIGS. 13, 14) through the inlet A.
  • flow port 20 moves across flow port 24 to adjust the flow through port B.
  • the flow opening 20 moves via the flow opening 16 in order to set the flow cross-section 78 through the inlet A.
  • flow opening 22 via flow opening 24 to adjust the flow through input B.
  • Adjustment range I! is traversed opposite to the adjustment range I in the opposite direction.
  • the characteristics can be adapted to the particular problem by modifying the openings 16-24.
  • FIG. 6 a shows a schematic variant of a throttle body 10.
  • This cylindrical throttle body 10 is rotatable about a rotation axis A, which is indicated by a double arrow 26. Further, this cylindrical throttle body 10 is displaceable in the axial direction A, which is indicated by a further double arrow 28.
  • This cylindrical throttle body 10 has three actuating regions in the axial direction A, which are designated by I, II and III. These three control areas have flow openings of different geometry, in the present school example, the flow opening 32 in the control range I has an elliptical cross-section, the flow opening 34 in the control range Il a rectangular and the flow opening 36 in the control range III a triangular. In industrial practice, the adjustment ranges are of similar geometric shape.
  • the flowing through an inlet 43 and an outlet 45 of a pipe 42 medium 38 is characterized by an arrow.
  • the drive motor initially selects the setting range I, II or III and then rotates the throttle body 30 until the operating point is reached.
  • the two movements can be performed by the same or by two different drive motors.
  • the shape of the characteristic curves in the setting areas I, II and III is determined by the geometric shape of the flow openings 32, 34, 36 and the flow cross section 78 (FIGS. 13, 14) in the valve.
  • Fig. 6b substantially corresponds to Fig. 6a, but it is a fine channel 30 is formed, which extends in the axial direction A and the control areas I, II and III connects. The function of the valve remains unchanged, but it only has one flow opening.
  • the throttle body 10 is spherical, which is freely rotatable about the rotational axis A and positionable by the drive motor, not shown.
  • the semi-open spherical throttle body 10 has a column-shaped large flow opening 47 and a likewise columnar small
  • the large flow opening 47 forms the control range I
  • the small flow opening 49 the control range II.
  • the sealing part 48 of the spherical throttle body 10 against the valve housing 44 is annular and shown with a dashed line. The ball is rotated in both directions by 90 °.
  • Fig. 8 shows a section along the plane E in Fig. 7, wherein in the spherical throttle body 10, the large flow opening 47 and the small flow opening 49 are formed substantially prismatic. The ball is only rotated by 60 ° in one direction or the other. It is a recess 50 for the drive port 46 (Fig. 7) recognizable.
  • FIG. 9 shows one of the numerous uses of the valve 66 according to the invention.
  • the flow temperature in a district heating line 56 is much higher in winter than in summer. This results in completely different operating points for the direct temperature control of domestic hot water in a building 64 with a tap 68.
  • cold water from the drinking water supply is brought directly to a desired temperature via a heat exchanger 62 via a line 54. Due to the strongly fluctuating hot water demand, the regulation is made even more difficult. If the control vibration is too strong, the user may contract burn injuries in a shower, for example.
  • a valve 66 according to the invention is installed, in the present case a two-way valve in throttle circuit.
  • Fig. 10 and Fig. 1 1 describe switching conditions of a control range I with a large flow opening on a control range Il with small flow opening and back. Shown is the time course of the position setpoint S for a valve, which may result from a room temperature control.
  • the valve initially operates in setting range I. If the position setpoint S falls below the threshold value S k and remains below it for an adjustable time period ⁇ t, the throttle body is guided into the setting range II.
  • the valve now operates in adjustment range II to at most the conditions according to FIG be fulfilled.
  • Fig. 1 the opposite case is shown, the control operates initially in the small control range II. As soon as the position setpoint S exceeds the threshold S g , the throttle body changes immediately in the large control range I, otherwise the consumer to be controlled would be under-supplied. The valve now works in setting range I until the conditions according to FIG. 10 are at most met again.
  • a throttle body 10 which comprises a fixed first plate 70 with a rectangular flow opening 74 and a longitudinally and transversely, in the x and y direction, displaceable second plate 72 with a presently congruent flow opening 76.
  • the flow openings do not have to be the same size or the same geometric shape.
  • the two sealingly superimposed plates 70, 72 form depending on the position of the displaceable plate 72 an adjustable flow cross-section 78.
  • the displaceable plate 72 is located on the fixed plate 70, that in the position 0 no flow occurs .
  • the maximum flow cross section 78 is reached at 100%, where the two flow openings 74, 76 are congruent to one another.
  • the flow area 78 is about 30% of the maximum possible value.
  • the drive motor has switched over into the setting range II.
  • the maximum flow cross section 78 is only about 35% of the maximum value at 100% as shown in FIG. 13.
  • the control in the x-direction can be performed much more accurately in the adjustment range II if the flow cross-section 78 drops below a predetermined value.
  • Fig. 15 shows a circuit arrangement according to the invention.
  • a valve module 80 regulates the flow through the conduit 82.
  • a sensor 84 e.g. the temperature measured.
  • the signal from the sensor is sent to the central control circuit 86, which generates the so-called system control signal V (t) in a manner not of further interest here.
  • V (t) the so-called system control signal
  • This is the input signal for the control circuit 88 according to the invention of the valve module 80.
  • the control circuit contains a calculation algorithm which determines the suitable characteristic of the valve 92 and the position x of the throttle body. With these two parameters, the drive motor 90 is controlled, which drives the throttle body in the position which achieves the desired hydraulic cross section.
  • the module can be marketed as a self-contained product. But it is also possible to implement the valve, the motor and the control circuit as separate units.
  • FIGS. 16a to 16e show a further preferred embodiment.
  • the throttle body is formed by a centered with a channel 102 ball 100, which sits in a ball valve housing, as it is z. B. is shown schematically in Fig. 7.
  • the channel 102 forms on each of two opposite surface areas of the ball 100 each a mouth opening 104 and 106, respectively.
  • Each of these mouth openings 104, 106 has an edge region 105, 107 with a contour which (in conjunction with the circular inlet or outlet of the valve housing) Characteristic curve for the rotational position-dependent free (or hydraulic) cross-section forms.
  • a surface closing area 108 (preferably arranged symmetrically with respect to the equatorial plane EE) (compare, in particular, the equatorial section according to Figure 16d), which is sufficiently large so that it can close the inlet and outlet of the valve housing ,
  • the supervisor Area closing region 108 includes a circle in geometric terms corresponding to the diameter of the inlet and outlet. (If the inlet or outlet is not circular but otherwise limited, the surface closure area must accordingly contain a different geometric shape so that it can close at least the cross-sectional area of the inlet or outlet.)
  • the arrangement of the surface closure area 108 thus defining the closed position of the valve.
  • the contour of the edge region 105 provided for the small adjustment range (control range 0 - u%, u ⁇ 100%) encloses a first surface area which is first strip-shaped and then widens wedge-shaped thereafter. Said area is symmetrical in the present example with respect to the equatorial plane E-E of the ball.
  • the contour of the edge region 107 provided for the large adjustment range (control range 0-100%) encloses a circle-like second surface region. Also, this surface area is symmetrical in the present example with respect to the equatorial plane of the sphere.
  • the ball 100 has at the "north pole" on a recess 1 10, in which a (not dargesteller) coupling part of a valve axis can engage against rotation.
  • the adjustment ranges can be realized by differently sized rotation angle ranges of the throttle body. They can be separated or connected directly to each other. The zero position can be provided between the two control ranges, that is the position in which the valve blocks.
  • FIGS. 7, 8 and 16 can also be circular-cylindrical instead of spherical.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Electrically Driven Valve-Operating Means (AREA)

Abstract

L'invention concerne une soupape (66) pour fluides (38) liquides et/ou gazeux en écoulement, qui présente un boîtier (44) de soupape ainsi qu'une chambre de soupape dotée d'au moins une entrée (43) et d'au moins une sortie (45). Un corps d'étranglement (10) qui peut être placé et déplacé dans la soupape sert à réguler la section transversale d'écoulement (78). Lorsqu'il se déplace de manière alternée dans la chambre de soupape, le corps d'étranglement (10) forme au moins deux lignes caractéristiques différentes. Le corps d'étranglement (10) présente au moins deux zones de réglage (I, II, III) separées et qui peuvent être sélectionnées au moyen d'au moins un moteur d'entraînement et qui présentent différentes ouvertures d'écoulement (18, 20, 22, 32, 34, 36, 47, 49). Dans une variante, le corps d'étranglement (10) présente une ouverture d'écoulement (16, 18, 74, 76) qui présente au moins deux zones de réglage (I, II, III) qui peuvent être sélectionnées au moyen d'un moteur d'entraînement. Les oscillations (S) dans un circuit de régulation sont éliminées par la soupape (66) par le fait que pour sélectionner le point de fonctionnement, le corps d'étranglement (10) est amené de manière autonome par le moteur d'entraînement commandé en fonction du processus dans une autre zone de réglage (I, II, III), la ligne caractéristique (K) adaptée étant établie de manière motorisée.
PCT/CH2007/000104 2006-03-01 2007-03-01 Soupape de régulation du debit et procede d'elimination des oscillations WO2007098630A1 (fr)

Applications Claiming Priority (2)

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CH324/06 2006-03-01
CH3242006 2006-03-01

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011144195A1 (fr) * 2010-05-20 2011-11-24 Porep Gmbh Vanne à tiroir rotatif destinée à mélanger un carburant à faible viscosité avec un carburant très visqueux

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1540302A (en) * 1975-12-11 1979-02-07 Gestra Ksb Vertrieb Gmbh Throttle valve comprising apertured sleeves fitting one inside another
EP0376502A2 (fr) * 1988-12-30 1990-07-04 Neles-Jamesbury Oy Méthode de changement de la ligne caractéristique d'une soupape de réglage sous pression et soupape de réglage
US5957377A (en) * 1994-06-17 1999-09-28 Nippondenso Co., Ltd. Flow control valve and hot-water type heater apparatus employing the same
US20040021115A1 (en) * 2000-05-24 2004-02-05 Thierry Lemmonier Faucet with secondary opening
US6837480B1 (en) * 1999-08-17 2005-01-04 Belimo Holding Ag Ball valve with adjustable flow coefficient

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1540302A (en) * 1975-12-11 1979-02-07 Gestra Ksb Vertrieb Gmbh Throttle valve comprising apertured sleeves fitting one inside another
EP0376502A2 (fr) * 1988-12-30 1990-07-04 Neles-Jamesbury Oy Méthode de changement de la ligne caractéristique d'une soupape de réglage sous pression et soupape de réglage
US5957377A (en) * 1994-06-17 1999-09-28 Nippondenso Co., Ltd. Flow control valve and hot-water type heater apparatus employing the same
US6837480B1 (en) * 1999-08-17 2005-01-04 Belimo Holding Ag Ball valve with adjustable flow coefficient
US20040021115A1 (en) * 2000-05-24 2004-02-05 Thierry Lemmonier Faucet with secondary opening

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011144195A1 (fr) * 2010-05-20 2011-11-24 Porep Gmbh Vanne à tiroir rotatif destinée à mélanger un carburant à faible viscosité avec un carburant très visqueux

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