WO1993016355A1 - Debitmetre a turbine - Google Patents

Debitmetre a turbine Download PDF

Info

Publication number
WO1993016355A1
WO1993016355A1 PCT/US1993/001690 US9301690W WO9316355A1 WO 1993016355 A1 WO1993016355 A1 WO 1993016355A1 US 9301690 W US9301690 W US 9301690W WO 9316355 A1 WO9316355 A1 WO 9316355A1
Authority
WO
WIPO (PCT)
Prior art keywords
turbine meter
rotor
blades
meter
turbine
Prior art date
Application number
PCT/US1993/001690
Other languages
English (en)
Inventor
Helmut Zenger
Bob E. Kubin
Franklin Dale Goodson
Zaki Din Husain
Charles R. Allen
Original Assignee
Daniel Industries, Inc.
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
Priority claimed from US07/834,601 external-priority patent/US5325729A/en
Application filed by Daniel Industries, Inc. filed Critical Daniel Industries, Inc.
Priority to JP5511989A priority Critical patent/JPH07500189A/ja
Priority to AU37781/93A priority patent/AU673162B2/en
Publication of WO1993016355A1 publication Critical patent/WO1993016355A1/fr
Priority to NO933646A priority patent/NO933646L/no

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F1/00—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow
    • G01F1/05—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow by using mechanical effects
    • G01F1/10—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow by using mechanical effects using rotating vanes with axial admission
    • G01F1/115—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow by using mechanical effects using rotating vanes with axial admission with magnetic or electromagnetic coupling to the indicating device
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F1/00—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow
    • G01F1/05—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow by using mechanical effects
    • G01F1/10—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow by using mechanical effects using rotating vanes with axial admission
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F1/00—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow
    • G01F1/05—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow by using mechanical effects
    • G01F1/10—Measuring the volume flow or mass flow of fluid or fluent solid material wherein the fluid passes through a meter in a continuous flow by using mechanical effects using rotating vanes with axial admission
    • G01F1/12—Adjusting, correcting, or compensating means therefor

Definitions

  • the invention relates to flow measurement devices and in particular, to flow measurement devices using turbine meters as a basis of the flow measurement.
  • Pipes are used to transport fluids of all sorts. Because the measurement of these fluids is important, various types of fluid measuring devices such as orifice plates, flow meters, turbine meters, etc. are installed in-line with pipe sections. The use of such a measurement for flow has been known since ancient times.
  • Turbine flow meters usually include a measuring chamber having a flow guide in the front of such chamber, a measuring wheel supported for rotation in the chamber and includes a magnetic device which counts the blade turnings for blades mounted on the hub of the measuring wheel.
  • the basic theory with regard to electronic turbine meters is that fluid flow through the meter impinges upon the turbine blades which are free to rotate about an axis along the center line of the turbine housing.
  • the angular (rotational) velocity of the turbine rotor is directly proportional to the fluid velocity through the turbine.
  • the output of the turbine meter is measured by an electrical pickup mounted in the meter body.
  • the output frequency of this electrical pickup is proportional to the flow rate.
  • each electrical pulse is proportional to a small incremental volume of flow. This incremental output is digital in form, and as such, can be totalized with a maximum error of one pulse regardless of the volume measured.
  • An additional object of the present invention is to inhibit intrusion of dirt within the mechanism of the measuring wheels supported for rotation in the chamber.
  • the present invention discloses a turbine meter that is suitable for either liquid or gas flow which can be installed for use over a large pressure range, such as, for example, ambient to 1500 p.s.i. while maintaining a rangeability of, for example, 10:1 for ambient and 13:1 at 300 p.s.i.
  • the present invention includes a body or housing in which is contained a bilateral or symmetrical configuration of a flow meter.
  • the flow meter includes flow diffusers at each end located in the flow passage of the body and a detector at an interior wall of the body.
  • a rotor is mounted on a rotor shaft between the two flow diffusers.
  • the rotor optimally has twelve flat blades with optimal blade angles of 45°.
  • a close clearance is maintained between the blades and the interior of the meter body which is optimally between .008" and .012". This is achieved through use of specific stiffness of the blade which stems from the use of a set of notches to form the blades having optimal size for oval notches of width to height ratio of 1.5 to 2.0, such as .169" x .094" for a two inch meter. The notches for most meters would be oval in shape but at the extreme small and large sizes may be other shapes, such as tear drop.
  • a magnetic pick-up is located in the magnet housing immediately juxtaposed with the blades and separated from the blade by the interior wall of the body and the small clearance discussed above. The magnetic strength of such magnet located in the interior wall of the body is between 50 and 200 gauss.
  • Blade thickness may vary between .01 and .025 of the rotor diameter, such as .020" and .050" for a two inch meter while maintaining the small size of the turbine meter.
  • Figure 1 is a perspective view of the preferred embodiment of the present invention of the turbine meter
  • Figure 2 is a side, partial cross-sectional view of the preferred and alternate embodiment of the present invention of the turbine meter
  • Figure 3 is a partial side cross-sectional view of a portion of the preferred and alternate embodiment of Fig. 2;
  • Figure 4 is a plan view of the rotor shaft of the preferred embodiment of the present invention of the turbine meter;
  • Figure 5 is a cross-sectional view of the housing of the preferred embodiment of the present invention of the turbine meter;
  • Figure 6 is a plan view of the rotor of the preferred embodiment of the present invention of the turbine meter prior to the formation of the blade configuration;
  • Figure 7 is an enlarged view of the portion of Figure 6 labelled "A";
  • Figure 8 is a side view of the rotor shaft lock washer of the preferred embodiment of the present invention of the turbine meter;
  • Figure 9 is an exploded view of the alternate embodiment of the turbine meter of the present invention.
  • Figure 10 is an exploded view of the preferred embodiment of the turbine meter of the present invention.
  • Turbine meter 1 is shown in Figure 1 having sealing faces 10 for appropriate mounting in line.
  • Turbine meter 1 further includes interior opening 11 surrounded by interior wall 12 of body 13.
  • Substantially identical diffusers 15 (Fig. 9) are mounted in opening 11 by spacers 20 which extend from diffusers 15 to an interior hub 14 sized to fit in interior wall 12 of body 13.
  • turbine meter 1 is symmetrical and can be installed with either end facing the upstream.
  • Locator pins 16 hold hubs 14 onto the interior wall 12.
  • Retainer rings 17 engages grooves 18 in wall 12 to lock hubs 14 in place. Hubs 14 abut interior shoulders 21 formed in wall 12. Referring to Figs.
  • the diffusers 15 are shown in two different configurations for contrast only.
  • the alternate configuration of diffuser 15 is designated by indicator 30 (see Fig. 9)
  • the diffuser of the current design which is preferred is indicated by indicator 25 (see Fig. 10) .
  • the difference between the diffuser types is in the back edge 35, 40 of the diffusers 25, 30, respectively.
  • the back edge 35 of diffuser 25 extends inwardly much farther than the back edge 40 of diffuser 30.
  • rotor shaft 45 is located such that its longitudinal axis is substantially identical with the longitudinal axis of the diffusers 15.
  • the ends 50,-.59.-of rotor shaft 45 extend into interior openings 55 of diffusers 15. Openings 55 have a first bore 60 and a second bore 65 being substantially coaxial, with bore 60 having a larger diameter than bore 65. Bores 60, 65 form a shoulder 70 therebetween.
  • Rotor shaft 45 is positioned to be substantially coaxial with opening 55 by bearings 75 mounted in bore 60 and abutting shoulder 70 at one end.
  • Rotor shaft 45 is shaped to include shoulders 80, 89. Shoulder 80 is formed between extended shaft portion 50 and raised portion 85. Shoulder 89 is formed between extended portion 59 and raised portion 88.
  • Rotor hub or shaft 45 also includes a central extended diameter raised portion 100, one side 105 of which faces extended portion 85, and the other side 110 of which faces extended section 88.
  • a bearing 75 also abuts shoulder 80 on the side of face 105, and a second bearing 75 abuts shoulder 89 on the side of face 110, thereby centering extended shafts 50, 59 of rotor shaft 45 in opening 55. Because of bearings 75, rotor shaft 45 is rotatably mounted within opening 55.
  • Bearings 75 are preferably precision ball bearings, instead of other bearings such as jewel bearings. Precision ball bearings increase life at high speeds and because of the remainder of the features of the preferred embodiment of the present invention, may be used at low flow rates instead of jewel bearings. Jewel bearings and shaft assembly operating at high revolutions per minute do not last very long.
  • Rotor 120 is slidably mounted on enlarged shaft portion 88 by sliding an opening 130 formed in the center of rotor 120 to fit over extended portions 59, 88.
  • openings or notches 140 are formed in a rotor 120 blank comprising a circular piece of metal.
  • the notches 140 for most meters would be oval in shape but at the extreme small and large sizes may be other shapes, such as tear drop.
  • the width to height ratio would be preferably 1.5 to 2.0.
  • the dimensions would be .169" x .094".
  • the notches 140 are located symmetrically about the center of rotor 120 and radially displaced from the center of rotor 120 by at least twenty-five percent of the radius of the rotor 140.
  • the interior end 160 and the opposing exterior end 155 of notches 140 have a radius of curvature of, for example, .047 inches for a two inch meter, and the outer end 155 of each of the notches 140 includes a narrow channel 145, having a width less than or equal to the material thickness of the blades, for example, .025 inches for a two inch meter, extending to the outer circumference 150 of rotor 120.
  • these notches 140 extend above the interior end curved portion 160, approximately starting at .315 inches from the center (for a two inch turbine meter) of opening 130 and end at the beginning of the exterior end curved portion 155 which typically starts .484 inches from the center (for a two inch turbine meter) of opening 130.
  • the material between openings 140 forms a shaft 170 leading to flat blade portions 180 that extend from the exterior curved surface of the exterior end 155 to the outer circumference 150 of rotor 120.
  • blade thickness is preferably in the range of .01 and .025 of the rotor diameter, such as .020 inches to .050 inches for a two inch meter.
  • Shaft 170 permits the flexibility to twist the blade portion 180 relative to the interior of rotor 120.
  • the blanks for the rotor 120 are not preferably formed by a stamping die.
  • the edges 350 of the flat blade portions 180 are important to the performance of the turbine meter rotor 120 and must be sharp. Sharp edges 350 are needed for liquid as well as gas meters. Accordingly, with a single stage stamping die, care cannot be taken as to what type of edge 350 can be provided, and whether the edges 350 may have to be machined or have additional stamping die stages to be sharp.
  • milling or laser cutting will be preferably used for sharpness of leading and trailing edges 350 which effect linearity.
  • the openings or notches 140 effect the stiffness of the flat blade portion 180. Stiffness is important in a turbine meter to minimize clearances and thus lower weight and size and cost of substantially all components while maintaining accuracy.
  • the preferred notch 140 size ratio for an oval notch is, as set out above, preferably 1.5 to 2.0, for example, .169 inches by .094 inches for a two inch turbine meter.
  • the number of blades may be increased.
  • the flat blade portions 180 may retain the stiffness because of notches 140 while increasing the number of flat blade portions 180, such as above six flat blade portions, such as a range between six to and including twelve flat blade portions 180 with the optimal being twelve flat blade portions 180. The larger number of blades in combination with blade angle gives a greater resolution or frequency to the signal produced by the turbine meter.
  • the blade angles of flat blade portions 180 are turned in a range between 30° and 60° with respect to the longitudinal axis of the flow path, with an optimal angle of 45°.
  • the angle determines to some extent the speed of the turning of the rotor, which as the angle increases, the speed increases. Slower turning decreases resolution. However, speed decreases bearing life, and speed must be chosen to optimize bearing life and resolution.
  • the use of a 45° angle yields the frequency which typically for a meter of the preferred embodiment is 3000 hertz which is believed to be significantly higher than meters of the prior art.
  • the 45° angle requires the extra stiffness in order to be functional at maximum speeds. In addition, lower angles are much less responsive at low flows, and thus cut the rangeability of the meter at low flow rates and low pressures.
  • the length of the flat blade portions 180 may be increased, thereby reducing the clearance between the outer surface 150 of blade 180 and the interior surface 360 of portion 320 of interior wall 12.
  • Such clearance in the preferred embodiment is in a range between .008 and .012 inches. The smaller this distance is; the closer the flat blade portions 180 come to the pick-up coil 400 to obtain accurate readings because at high pressures the thickness of portion 320 must be sufficient to withstand the high pressure in the interior opening 11 of the body or housing 13.
  • the weight of the flat blade portions 180 is important so that at low end flow rates, magnetic drag is not experienced as greatly.
  • flexing of the blades 180 can cause collision with the interior surface 360 or alternately may open the gap to surface 360 thereby decreasing signal strength.
  • magnetic drag is a factor, increasing weight is not the solution to the stiffening, but the optimizing of the notch 140 is required as discussed above.
  • a large free diameter of the flat blade portions 180 may be used, such as preferable a diameter of five times the diameter of extension 100 to surface 240. This causes significant weight saving.
  • Rotor 120 is attached to enlarged diameter portion 100 by small welds 200 or with special bonding agents such that one side of rotor 120 securely abuts surface 110.
  • the other side of rotor 120 abuts a lock washer 210 which is fastened to rotor 120 by a small weld 230 or with special bonding agents.
  • lock washer 210 and rotor 120 are rotatably mounted about the center axis of opening 55.
  • resistance welding would be used in manufacture instead of spot welding.
  • the welding 200, 230 of the rotor 120 shaft assembly also improves the attachment of the rotor 120.
  • the welding 200, 230 eliminates potential problems with other type of bonding agents, such as LoctiteTM, although LoctiteTM may be used as a bonding agent.
  • the problems of other type of bonding agents would include improper assembly procedures and part cleaning which are necessary for a bonding of this type to perform the appropriate tasks.
  • the welds 200, 230 or other welding techniques unlike other techniques, can be visually inspected to determine acceptability, whereas incorrect procedures of assembly and bonding cannot be detected until the equipment falls apart. Because the meter l may be used in bi ⁇ directional flow, the welding 200, 230 also becomes important because thrust forces on the rotor 120 are transmitted to the lock washer 210 in the reverse flow mode. Further, a welded rotor 120 may increase the maximum temperature limit of the meter 1. Care should be taken to insure that a flat surface of rotor 120 abuts the flat surface 110 of extension 100.
  • the preferred diffuser 25 includes interior surface 35 which extend substantially over the entire outer circumference 240 of extension 100.
  • a machine cut 250 into surface 35 may also be formed, but surface 35 would still cover outer circumference 240.
  • the clearance between outer circumference 240 and the interior surface 250 of extension 35 is very close.
  • dust would tend not to leak into the bearing 75 area of the mounting of the rotor 120 and rotor shaft 45 with the preferred diffusers 25.
  • these surfaces will tend to capture the rotor 120 should the bearings fail, preventing damage to the interior 11 of body or housing 13.
  • a diffuser 25 is used on both sides in place of diffuser 30 (shown on one side of Fig. 2) , it would substantially cover the outer circumference of lock washer 210.
  • the diffuser modification will hold the rotor 120 in place longer after failure of and bearings 75, giving some indication of flow for a longer period of time and preventing the rotor 120 from damaging the bore or interior wall 12 of body 13 and, especially the thin wall 320 under the coil 400.
  • the housing 13 includes a pressure tap 300 centrally located for which a pressure transducer and transmitter may be attached to measure the pressure in the interior 11 close to the flat blade portions 180.
  • the housing or body 13 further includes an indented exterior portion 310 that houses the pick-up coil 400 graphically depicted in Fig. 1 and shown in Figs. 9 and 10 which, except as described below, is standard in the art.
  • the pick-up coil 400 includes coils typical of the art which are wound and placed within opening 330. In the preferred embodiment of the present invention, because the blades are so close to the interior wall 360 of the housing 13, and there are so many flat blade portions 180, magnetic strength of the pick-up coil 400 should be optimized to improve meter performance at low flow rates and avoid magnetic drag.
  • the magnetic strength of the pick-up coil 400 is preferably between 50 and 200 gauss as a function of the number of windings and the wire size of the pick-up coil 400.
  • the thickness 320 below the opening 330 for the pick-up coil 400 must be sufficient to contain the pressure within the interior 11 of the housing or body 13.
  • flow may be introduced on either diffuser 25 of meter 1 which will deflect the flow against the surface of flat blade portions 180 facing the flow.
  • the impingement of the flat blade portions 180 cause flat blade portions 180 to rotate around the axis of rotor shaft 45.
  • the presence of the flat blade portions 180 of the rotor 120 will be detected as pulses having a width dependant on the time that surface 150 is juxtaposed in whole or in part with pick-up coil 400.
  • the pulses are subject to signal smoothing and shaping and amplification and other conditioning by preamplification and ultimately used for flow rate and/or flow volume measurement.
  • the shift on the meter curve as a function of line pressure is dependent on the ratio of the total drag on the rotor to the turning moment on the rotor.
  • Major contributors to the drag are mechanical, frictional, viscous, and magnetic.
  • the main source of drag is from the drive. Therefore, a shift of the meter curve occurs at a higher line pressure.
  • With magnetic pick-up the drag is significantly reduced.
  • the shift on the meter curve occurs at a much lower line pressure than that of a turbine meter with mechanical drive.
  • a significant contribution of drag is from the magnetic field of the pick-up coil.
  • the combination of magnetic pick-up coil strength, choice of bearing, blade thickness, blade angle, and blade clearance has a synergistic effect to minimize the shift of the meter curve to line pressures as low as ambient condition.
  • the curve shift is insignificant and included within the accuracy of the meter.

Landscapes

  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Measuring Volume Flow (AREA)
  • Thermistors And Varistors (AREA)
  • Investigating Or Analysing Materials By Optical Means (AREA)

Abstract

Débitmètre à turbine miniaturisé (1) présentant une très large gamme de pressions d'utilisation. Ce débitmètre à turbine comprend un corps (10) bilatéral ou symétrique. Des diffuseurs (15) sont compris dans le débitmètre (1) pour maintenir le rotor (45) en position et empêcher que la poussière ne pénètre dans le paliers (75). Le rotor (15) comporte de manière optimale douze ailettes plates (150), chacune formant un angle de 45° par rapport au plan de l'ébauche (12). On maintient un écartement serré entre les ailettes (150) et l'intérieur (11) du débitmètre. On forme des encoches (140) à l'extrémité inférieure des ailettes (150), de manière à créer les tiges (170) des ailettes (150) dont les dimensions sont optimalisées pour augmenter la rigidité. Le genre de la résistance magnétique du capteur magnétique (400) est réduit afin d'éviter la traînée magnétique.
PCT/US1993/001690 1992-02-12 1993-02-11 Debitmetre a turbine WO1993016355A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP5511989A JPH07500189A (ja) 1992-02-12 1993-02-11 ガスタービンメータ
AU37781/93A AU673162B2 (en) 1992-02-12 1993-02-11 Gas turbine meter
NO933646A NO933646L (no) 1992-02-12 1993-10-11 Gassturbinm}ler

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
US83461592A 1992-02-12 1992-02-12
US83569492A 1992-02-12 1992-02-12
US83441892A 1992-02-12 1992-02-12
US834,615 1992-02-12
US07/834,601 US5325729A (en) 1992-02-12 1992-02-12 Gas turbine meter
US834,418 1992-02-12
US834,601 1992-02-12
US835,694 1992-02-12

Publications (1)

Publication Number Publication Date
WO1993016355A1 true WO1993016355A1 (fr) 1993-08-19

Family

ID=27505886

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1993/001690 WO1993016355A1 (fr) 1992-02-12 1993-02-11 Debitmetre a turbine

Country Status (6)

Country Link
EP (1) EP0579825A4 (fr)
JP (1) JPH07500189A (fr)
AU (1) AU673162B2 (fr)
CA (2) CA2089345A1 (fr)
NO (1) NO933646L (fr)
WO (1) WO1993016355A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2460891A (en) * 2008-06-17 2009-12-23 Philip John Campbell Apparatus and method for characterising fluid flow through a pipe
US9109931B2 (en) 2009-04-23 2015-08-18 Elster Metering Limited Inductive fluid flow meter having an inductive target provided on the shaft
CN108952836A (zh) * 2017-05-18 2018-12-07 福特全球技术公司 用于可变喷嘴涡轮机的喷嘴叶片设计

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2649243A (en) * 1948-08-05 1953-08-18 Edward A Stalker Axial flow compressor construction
US3301053A (en) * 1964-02-28 1967-01-31 Rockwell Mfg Co Flow meter
CA757815A (en) * 1967-05-02 E. J. Hingston Robert Turkey lifter
US3979957A (en) * 1975-02-12 1976-09-14 Foss America, Inc. Flow meter
US3999432A (en) * 1974-08-23 1976-12-28 Compteurs Schlumberger Flowmeter
JPS5412766A (en) * 1977-06-29 1979-01-30 Toshiba Corp Hot-wire flow meter
EP0094352A2 (fr) * 1982-05-10 1983-11-16 Ottorino Barbuti Débitmètre pour des fluides avec sensor de données électriques et procédé pour la fabrication
US4649756A (en) * 1985-06-07 1987-03-17 Feller Murray F Flow sensors

Family Cites Families (3)

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Publication number Priority date Publication date Assignee Title
GB162685A (en) * 1920-06-18 1921-05-12 Alexander Constantine Ionides Improvements in or relating to rotary fluid meters
BE785256A (fr) * 1972-06-22 1972-10-16 Cooper Thomas G Dispositif pour le controle de la vitesse d'un fluide et la determination d'une vitesse predeterminee.
AU511066B2 (en) * 1978-07-03 1980-07-24 Scitec Corp. Pty. Ltd. Computerised electronic spirometer

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA757815A (en) * 1967-05-02 E. J. Hingston Robert Turkey lifter
US2649243A (en) * 1948-08-05 1953-08-18 Edward A Stalker Axial flow compressor construction
US3301053A (en) * 1964-02-28 1967-01-31 Rockwell Mfg Co Flow meter
US3999432A (en) * 1974-08-23 1976-12-28 Compteurs Schlumberger Flowmeter
US3979957A (en) * 1975-02-12 1976-09-14 Foss America, Inc. Flow meter
JPS5412766A (en) * 1977-06-29 1979-01-30 Toshiba Corp Hot-wire flow meter
EP0094352A2 (fr) * 1982-05-10 1983-11-16 Ottorino Barbuti Débitmètre pour des fluides avec sensor de données électriques et procédé pour la fabrication
US4649756A (en) * 1985-06-07 1987-03-17 Feller Murray F Flow sensors

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0579825A4 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2460891A (en) * 2008-06-17 2009-12-23 Philip John Campbell Apparatus and method for characterising fluid flow through a pipe
US9109931B2 (en) 2009-04-23 2015-08-18 Elster Metering Limited Inductive fluid flow meter having an inductive target provided on the shaft
GB2470104B (en) * 2009-04-23 2018-02-07 Elster Water Metering Ltd Fluid flow meter
CN108952836A (zh) * 2017-05-18 2018-12-07 福特全球技术公司 用于可变喷嘴涡轮机的喷嘴叶片设计

Also Published As

Publication number Publication date
CA2089345A1 (fr) 1993-08-13
NO933646D0 (no) 1993-10-11
AU3778193A (en) 1993-09-03
JPH07500189A (ja) 1995-01-05
CA2096938A1 (fr) 1993-08-13
NO933646L (no) 1993-10-11
EP0579825A1 (fr) 1994-01-26
AU673162B2 (en) 1996-10-31
EP0579825A4 (fr) 1994-03-21

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