US3545492A - Multiple plate throttling orifice - Google Patents

Multiple plate throttling orifice Download PDF

Info

Publication number
US3545492A
US3545492A US3545492DA US3545492A US 3545492 A US3545492 A US 3545492A US 3545492D A US3545492D A US 3545492DA US 3545492 A US3545492 A US 3545492A
Authority
US
Grant status
Grant
Patent type
Prior art keywords
orifice
plate
pressure
plates
orifices
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
Inventor
Charles H Scheid Jr
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Armco Inc
Original Assignee
Armco 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
Grant date

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16LPIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L55/00Devices or appurtenances for use in, or in connection with, pipes or pipe systems
    • F16L55/02Energy absorbers; Noise absorbers
    • F16L55/027Throttle passages
    • F16L55/02709Throttle passages in the form of perforated plates
    • F16L55/02718Throttle passages in the form of perforated plates placed transversely

Description

' 0 United States Patent 11113,545,492

[72] Inventor Charles H. Scheid, Jr. [56] References Cited Middletown, Ohio UNITED STATES PATENTS [21] l 3*12 1,078,834 11/1913 Cook 48/180 [221 e 3,111,091 1 H1963 Hopkinson 13s/44x [45] Patented Dec. 8,1970 FORE N P TEN S [73] Assignee Armco Steel Corporation [G A T Middletown, Ohio 520,083 4/1940 Great Britain 138/40 3 corporafion of Ohio Primary Examiner-Laverne D. Geiger Assistant Examiner-R. J. Sher Attorney-Melville, Strasser, Foster and Hoffman ABSTRACT: A throttling device for hydraulic systems which prevents the cavitation of metal conduits by liquids under dif- [54] MULTIPLE PLATE THROTTLING ORIFICE ferential pressure comprising a series of orifice plates spaced 7 claimss Drawing Figs at intervals along the axis of the conduits, each plate having [52] U.S. Cl. 138/42, n or r rifi s her in t lower the pressure of the liquid 138/44 passing therethrough, the axes of the orifices being displaced [5]] 1115.] 1/02 radially and circumferentially about the plate centers so as to [50] 138/42, 44; be in l m n i h he xe f he rifi es in adjacent modate water must allowfor MULTIPLE PLATE rrmorrunc onmce BACKGROUND OF THE INVENTION ferentialpressure.

2. Description ofthe lemma.

Hydraulic systems such as thosefound on presses and the like have generally heretrifo're utilized oil' as the hydraulic .medium, and throttle valves, such as globe-type throttle valves, have proved generally satisfactory. Due to the fact that -oil as the hydraulic fluid is relatively dangerous, many newer,

hydraulic systems have. adopted water rather than oil as the hydraulic fluid. However, the cavitation problem is much greater with water sincethe vapor pressure of oil is lower than that of water. Also, since hydraulic oils are more compressible than water and thus exhibit more deflection under thesame pressure, the design of conduits and other vessels to accoma greater dissipation of energy through the walls. I r

By cavitation is meant the gradual erosion of a surface caused by the collapse of vapor bubbles in a fluid. These bubble's form whenthe staticpressure in a fluid is lowered to the vapor pressure of the fluid. When the bubbles collapse the fluid slaps the surface, causing a'small part of the surface to be stressed beyond its yield point. This eventually results in fatigue and pitting of the surface. 7 v i Cavitation, of course, causes frequent shutdowns of hydraulic systems so that new valves may be installed. The shutdowns become very expensive in terms of man hours of maintenance because of the general inaccessibility of the valves.

Prior art devices have offered no solution to this problem. Indeed, the prior art'does not seem to even recognize the cavitation problem. For example, U.S. Pat, No. l,078,834,'in the'name of Cook, discloses afgaseous fuel mixer which cornprises a numberofagitating plates within a tubular housing.

The plates arefmounted on'ashank and may be rotated to properly mix the gas flowing therethrough. Each of the plates has a number of apertures, the number of apertures increasing from the first to last plate, with respect to the flow, while the size of the apertures decreases as the number of holes increasesfiCookdoes not'indic'ate that the rotating orifice plates are to serve any other purpose than to properly mix the gaseous fuel. l b b j Another exemplary prior art patent U.S. Pat. No. 2,125,245

. in the name of McCray,.which discloses an apparatus for dispersingthermoplastichydrocarbon materials in water. The

are positioned between the dispersing plates and are formed 7 with restricted passages through which the materials being dispersed are passed. McCray makes no mention of the cavitation problem. I

The aforementioned references are simply exemplary of prior art teachings which disclose multiple orifice plates. The references are not concerned with the problem of cavitation and its prevention, and themultiple orifice plates are primarily used to mix various materials passing therethrough.

SUMMARY or Tris INVENTION The present invention. provides a throttling device for hydraulic systems which prevents the cavitation of metal conduits by liquids under differential pressure. Broadly speaking,

therethrough, and the axes of the orifices-are displaced radiallyand circumferentially about the plate centers so as to be in FIG. 1.

misalignment with the axes of the orifices in adjacent plates. This prevents the jet leaving one orifice plate from entering directly an orificein an adjacentplate. The orifice, plates are positioned such that the upstream plate provides the greatest pressure drop thereaCt'OSS and each succeeding plate provides a gradually decreasing pressure drop, whereby the static pressure in the liquid under differential pressure is at all points greater than the vapor pressure of the liquid.

The spaced intervals between orifice plates will preferably be such as to allow the most length for dissipation where the pressure drop is greatest, so that the flow entering thenext orifice plate will be as undisturbed as possible. I

In practice, the throttling device of the present invention will prevent the cavitation of metal conduits by any liquid under differential pressure. However, since in practice it has been found that cavitation is much more serious when water is utilized as the hydraulic fluid, the present invention will be most applicable in this connection. I

In a preferred embodiment, the number of orifice plates was found to be five."The first four orifice plates were provided with sharp edge orifices and thelastorifice plate was a short tube orifice type.

BRIEF DESCRIPTION OETHE DRAWING FIG. 1 is a cross section taken through the center of a multiple plate throttling orifice according to the presentinvention.

FIG. 2 is an end elevation of the multiple plate throttling orifice of FIG. g

FIG. 3 is a cross-sectional view. taken along the line 3-3v of FIG].

FIG. 4 is a cross-sectional view taken along the line 4-4 of FIG. 5 is a cross-sectional view taken along the line 5-5 of FIG. 1.

FIG. 6 is a cross-sectional view taken along the line 6-6 of FIG. 7 is a cross-sectional view taken along the line 7-7 of FIG].

FIG. 8 is a cross-sectional view taken along the line 8-8 of DESCRIPTION OF THE PREFERRED EMBODIMENTS As was previously explained, the cavitation problem is much greater when water is used as a fluid in an hydraulic system than when oil is used as the fluid. This is so because the orifice of this invention. This throttling device was designed to replace an existing globe-type throttle valve and to throttle.

water, which was used as the hydraulic fluid, to slightly above atmospheric pressure.

For purposes of explanation, the multiple plate throttling device 10 of this invention is heldwithina housing 12 having a from 4,200 p.s.i.

bore 12a therein. The housing 12 may join two conduits in a hydraulic system. It is, of course, obvious that the throttling device 10 of this invention maybe used in any hydraulic system where it is desired to throttle the flow across a large pressure drop and where cavitation is a problem.

The housing 12 hasbeen designed ,such that both the upstream and downstream ends thereof have flanged connections which permitthem to be joined to other sections of com duit by bolts and the like through the bolt holes 12c.

As can be seen from FIG l,the multiple plate throttling orifice of this invention comprises a series of orifice plates 13 through 17 which are separated by the spacers 18 through 21.

.therethrough. The axesof the orifices in each of the plates 14 through 17 are displaced radially and circumferentially about the respective plate centers so as to be in misalignment with the axes of theorifices inadjacentplates. This preventsthe jet leaving one orifice plate, the upstreamplate, from entering directly an orifice in an adjacent downstream plate.

It will be observed that the orifice plates 13 through 17 are positioned such .that. the upstream plate 13 provides the greatest pressure dropthereacross and ,each succeeding plate provides a gradually deereasingpressure drop. In this manner the static pressureinthe quid under differential pressure is at all points greater than the vapor pressure of the liquid.

It is, of course, well =know n that for a single orifice plate the flow rate Q is equal to CA*?"2g (Ah), where C is the coefficient of discharge, which is a combination of a velocity coefficient C,,) and a contraction coefficient (C A is the total cross-sectional area of the orifice, g is the coefficient for gravity, and Ah is the difference in head upstream of the orifice and downstream at the vena contracta. The velocity head which is recovered is equal to the standard orifice-differential pressure (Ah in the above formula) minus the net head loss due to me- ,tering; Thus, the static pressure at the vena contracta is less than the static pressurefurther downstream and will in fact decrease towards a staticpressure reading of zero. In actual practice, the sta'tic pressure atthe vena contracta may not be lowerthanthe-vapor pressure of the liquid, because once this V happens abubble forms and cavitation occurs.

Since theabove formula is for a single orifice ,plate, and the present inventionutilizes a number of orifice plates in series, a certain desired flow rate was assumed. This flow rate and the elevated position of {the fluid system utilizing this throttling device, a hydraulic press, resulted in a certain inherent back head. The area of the orifices in the furthest downstream orifice plate was determined so that the static pressure at the vena contracta, taking into a'ccountthe inherent back head and the velocity head recovered, was above the vapor pressure of the liquid. The area of the orifices in the next orifice plate upstream was then determined in the same manner using the inherent back head plus the'rret head loss due to metering of the 'farthest downstream orifice. The total pressure 'drop across'the multiplate throttling orifice plates could then be calculated as the sumof the net headloss due to metering for each orificeplate. It was then necessary to make several iterations of the whole calculation until the total calculated pressure drop for the throttling device was equal to the available pressure drop supplied by thehydraulic system, at which time the initially assumed flow rate was proved;

As may be seen from FIG. 1 and FIGS. 4 through 8, all but the last orifice platefhav'e' sharp edge orifices while the last plate is of the short tube orifice type. Appropriate orifice coefficients. were used for each in the aforementioned calculations/However, it should be'emphasized that the type of orifice which is ultimately selected'is merely a matter of design so long as'the appropriate orifice coeff cients are utilized in the aforementioned calculations.

It should be pointed out that. the number of orifices in each orifice plate is not important, only their total area. Thus plates with multiplate holes were considered as having a single hole,

the area of which was equal to the sum of the area of the multiple holes. The reason for using multiple holes and their specific location was to prevent the jet leaving one orifice plate from entering directly a hole in the next plate.

Obviously, if the static pressure ofthe liquid at any point in the housing is too close to the vapor pressurethereof, some cavitation will occur. It then becomes necessary to increase the number of orifice plates.

The distance between the orifice plates 13 through 17,

established by the spacers 18 through 21; has not been found .10 be critical..However, it has been found preferable to allow ,themost length for dissipation where the pressure drop is -the greatest in order that the flow entering the next orifice plate will beas'undisturbed as possible.

.vals along the axes of said conduits each plate having one or more orifices therein to lower the pressure of the liquid passing therethrough, the axesof said orifices being displaced radially and circumferentially about the plate centers so as to be in misalignment with the axes of the orifices in adjaceirt plates and to prevent the jet leaving one orifice plate from entering directlyan orifice in anadjacent plate, the total area 'of said orifices in each succeeding orirce plate on the downstream side being successively larger so that the u'pstream plate provides the greatest pressure drop thereacross and each succeeding plate provides a gradually decreasing pressure drop, whereby the static piessure in said liquid under differential pressure is at all points greater than the vapor pressure of said liquid.

' and to ensure that the flow entering the next adjacent orifice plate will be as undisturbed as possible.

3. The throttling device according to claim 1, wherein the total area of the orifices in each'on'fice plate is determined so that the minimum static pressure between said orifice plates is above the vapor pressure of the fluid according to the formula Q Ca**2g (8h), where Q is the fidw rate, C is the coefficient of discharge and is a combination of a velocity coefficient and a contraction coefficient, A is the total cross-sectional area of the orifice, g. is the coefficient for gravity, and 8h is the difference in head upstream of the orifice plate and downstream UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3,5 6,492 Dated December 8, 1970 Inventorfl!) CHARLES H. SCHEID, JR.

It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

Column 3, Line 22, please amend "CA 2g 11)" to read CA V 2g (Ah) Column 3, Line 2 4, please amend "C to read --(C Column 4, Line 50 in claim 3, please amend "Ca 2g (811)" to read --CA 2g (Ah Column 4, Line 53, in claim 3, please cancel "811" and insert Ah SEALED 161971 (SEMI Am Mum mun. swam. an.

more mine:- at We

US3545492A 1968-05-16 1968-05-16 Multiple plate throttling orifice Expired - Lifetime US3545492A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US72970968 true 1968-05-16 1968-05-16

Publications (1)

Publication Number Publication Date
US3545492A true US3545492A (en) 1970-12-08

Family

ID=24932259

Family Applications (1)

Application Number Title Priority Date Filing Date
US3545492A Expired - Lifetime US3545492A (en) 1968-05-16 1968-05-16 Multiple plate throttling orifice

Country Status (1)

Country Link
US (1) US3545492A (en)

Cited By (60)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3878870A (en) * 1974-04-16 1975-04-22 Atomic Energy Commission Orifice design for the control of coupled region flow
US3983903A (en) * 1974-12-23 1976-10-05 Combustion Engineering, Inc. Multiple orifice assembly
US4060194A (en) * 1976-03-08 1977-11-29 Lutz George H Heating system and element therefor
JPS5330410A (en) * 1976-09-02 1978-03-22 Kawasaki Heavy Ind Ltd Gas duct
USRE29714E (en) * 1970-11-27 1978-08-01 Sanders Associates, Inc. Fluid flow restrictor
US4109680A (en) * 1977-01-03 1978-08-29 Lavender Ardis R Plate type fluid distributing device
US4127332A (en) * 1976-11-19 1978-11-28 Daedalean Associates, Inc. Homogenizing method and apparatus
US4194966A (en) * 1975-07-25 1980-03-25 Atlantic Richfield Company Apparatus and method for improved fluid distribution in a tube of a direct fired heater
US4275766A (en) * 1978-02-06 1981-06-30 Aronson Harvey G Fluid control system
WO1981003053A1 (en) * 1980-04-21 1981-10-29 H Engberg A slide valve for direct acting shutting-off of a pressure medium in case of a hose rupture
EP0164503A2 (en) * 1984-05-16 1985-12-18 Gebrüder Sulzer Aktiengesellschaft Fluid-conveying conduit with at least one choke
US4715395A (en) * 1986-06-30 1987-12-29 United Technologies Corporation Fluid flow regulator
GB2227754A (en) * 1988-10-14 1990-08-08 Pilkington Plc Gas flow restrictor for glass coating apparatus
DE4107969A1 (en) * 1991-03-13 1992-09-24 Heimeier Gmbh Metall Theodor Thermostat valve lower part - has valve seat integral with housing, and has plastics sleeve with through-flow hole, and pre-setting control with flow restrictor holes
US5495872A (en) * 1994-01-31 1996-03-05 Integrity Measurement Partners Flow conditioner for more accurate measurement of fluid flow
EP0745803A2 (en) * 1995-06-02 1996-12-04 Qe International B.V. Noise damper, a coke oven gas plant equipped therewith, and a baffle for the noise damper
US5605399A (en) * 1995-10-17 1997-02-25 Komax Systems, Inc. Progressive motionless mixer
US5855355A (en) * 1997-03-10 1999-01-05 The Horton Company Quiet and constant flow control valve
WO2000065222A1 (en) * 1999-04-26 2000-11-02 Quantum Energy Technologies Fuel delivery system for combusting fuel mixtures
US6379035B1 (en) * 1999-03-05 2002-04-30 Fujikin Incorporated Static mixing and stirring device
US6530684B1 (en) * 1998-12-07 2003-03-11 Roche Vitamins Inc. Preparation of liquid dispersions
US20030188586A1 (en) * 2002-04-09 2003-10-09 Orleskie Charles Theodore Averaging orifice primary flow element
US20050263199A1 (en) * 2002-11-26 2005-12-01 David Meheen Flow laminarizing device
US20060006022A1 (en) * 2002-09-18 2006-01-12 Savant Measurement Corporation Apparatus for filtering ultrasonic noise within a fluid flow system
US20060096650A1 (en) * 2004-03-18 2006-05-11 Sawchuk Blaine D Non-linear noise suppressor for perforated plate flow conditioner
US7051765B1 (en) * 2003-12-19 2006-05-30 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Balanced orifice plate
US20060141614A1 (en) * 2002-12-23 2006-06-29 Technische University Munchen Device and method for parallel, automated cultivation of cells in technical conditions
US20070294935A1 (en) * 2004-01-09 2007-12-27 Waldron Jack L Mixing apparatus and method for manufacturing an emulsified fuel
US20080142548A1 (en) * 2006-12-13 2008-06-19 Frozen Beverage Services Of California, Inc. Method and Apparatus for Combination and Delivery of Beverages for Consumption
US20100020632A1 (en) * 2008-07-25 2010-01-28 The Procter & Gamble Company Apparatus And Method for Mixing by Producing Shear, Turbulence and/or Cavitation
US7845688B2 (en) * 2007-04-04 2010-12-07 Savant Measurement Corporation Multiple material piping component
US20110172137A1 (en) * 2010-01-13 2011-07-14 Francesc Corominas Method Of Producing A Fabric Softening Composition
US20110186655A1 (en) * 2009-11-17 2011-08-04 The University Of Salford Spray discharge assembly
US20120103451A1 (en) * 2009-07-09 2012-05-03 Niagara Conservation Corp. Pressure compensation device
WO2012130060A1 (en) * 2011-03-30 2012-10-04 上海锅炉厂有限公司 Throttling device
WO2012136890A1 (en) * 2011-04-04 2012-10-11 Metso Automation Oy Device for reducing flow noise and valve
WO2012136891A1 (en) * 2011-04-04 2012-10-11 Metso Automation Oy Device for reducing flow noise and valve
US8307943B2 (en) * 2010-07-29 2012-11-13 General Electric Company High pressure drop muffling system
US8430202B1 (en) 2011-12-28 2013-04-30 General Electric Company Compact high-pressure exhaust muffling devices
US20130186493A1 (en) * 2012-01-24 2013-07-25 United Technologies Corporation Bi-directional fluid flow regulator with funnel shaped baffles
CN103256447A (en) * 2013-06-06 2013-08-21 兰州理工大学 Pipeline depressurization device
US8550208B1 (en) 2012-04-23 2013-10-08 General Electric Company High pressure muffling devices
US20130333800A1 (en) * 2010-12-23 2013-12-19 Sidel S.P.A. Con Socio Unico System and method for filling a container with a pourable product
CN103574082A (en) * 2013-11-12 2014-02-12 无锡杰尔压缩机有限公司 Throttling and pressure-reducing combined device of rhombic valve
US20140299216A1 (en) * 2013-04-08 2014-10-09 Kuo-Chen Tsai Water hammer arrestor
US20150083262A1 (en) * 2013-09-26 2015-03-26 Paul D. Van Buskirk Orifice plates
US9046115B1 (en) * 2009-07-23 2015-06-02 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Eddy current minimizing flow plug for use in flow conditioning and flow metering
US20150184806A1 (en) * 2012-07-03 2015-07-02 Caltec Limited Apparatus and method for reducing the effect of joule-thomson cooling
CN105042264A (en) * 2015-07-13 2015-11-11 北京航空航天大学 Circulation water channel
US20160010778A1 (en) * 2014-07-09 2016-01-14 Nadeem Ahmad Malik Sparse 3d-multi-scale grid turbulence generator
CN105444478A (en) * 2015-12-28 2016-03-30 重庆美的通用制冷设备有限公司 Throttling device for air conditioner
US9399951B2 (en) 2012-04-17 2016-07-26 General Electric Company Modular louver system
US9605695B2 (en) 2013-05-21 2017-03-28 Canada Pipeline Accessories, Co. Ltd. Flow conditioner and method of designing same
US9625293B2 (en) 2015-05-14 2017-04-18 Daniel Sawchuk Flow conditioner having integral pressure tap
CN107013784A (en) * 2017-06-14 2017-08-04 西安交通大学 Congealed water hammer restraining device and restraining system
US20170241574A1 (en) * 2015-09-21 2017-08-24 SYNCRUDE CANADA LTD. in trust for the owners of the Syncrude Project as such owners exist now & in Polymer-lined pipes and fittings with replaceable components
US9752729B2 (en) 2014-07-07 2017-09-05 Canada Pipeline Accessories, Co. Ltd. Systems and methods for generating swirl in pipelines
US9765279B2 (en) 2015-10-14 2017-09-19 Arisdyne Systems, Inc. Method for reducing neutral oil losses during neutralization step
US9845244B2 (en) 2015-09-17 2017-12-19 Arisdyne Systems, Inc. Method of forming graphene material by graphite exfoliation
US20180154326A1 (en) * 2016-12-01 2018-06-07 Phillips 66 Company Equalizing vapor velocity for reactor inlet

Cited By (91)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE29714E (en) * 1970-11-27 1978-08-01 Sanders Associates, Inc. Fluid flow restrictor
US3878870A (en) * 1974-04-16 1975-04-22 Atomic Energy Commission Orifice design for the control of coupled region flow
US3983903A (en) * 1974-12-23 1976-10-05 Combustion Engineering, Inc. Multiple orifice assembly
US4194966A (en) * 1975-07-25 1980-03-25 Atlantic Richfield Company Apparatus and method for improved fluid distribution in a tube of a direct fired heater
US4060194A (en) * 1976-03-08 1977-11-29 Lutz George H Heating system and element therefor
JPS5330410A (en) * 1976-09-02 1978-03-22 Kawasaki Heavy Ind Ltd Gas duct
US4127332A (en) * 1976-11-19 1978-11-28 Daedalean Associates, Inc. Homogenizing method and apparatus
US4109680A (en) * 1977-01-03 1978-08-29 Lavender Ardis R Plate type fluid distributing device
US4275766A (en) * 1978-02-06 1981-06-30 Aronson Harvey G Fluid control system
WO1981003053A1 (en) * 1980-04-21 1981-10-29 H Engberg A slide valve for direct acting shutting-off of a pressure medium in case of a hose rupture
EP0164503A3 (en) * 1984-05-16 1987-07-15 Gebrüder Sulzer Aktiengesellschaft Fluid-conveying conduit with at least one choke
EP0164503A2 (en) * 1984-05-16 1985-12-18 Gebrüder Sulzer Aktiengesellschaft Fluid-conveying conduit with at least one choke
FR2607275A1 (en) * 1986-06-30 1988-05-27 United Technologies Corp Method and apparatus for regulation of the flow of a fluid
US4715395A (en) * 1986-06-30 1987-12-29 United Technologies Corporation Fluid flow regulator
GB2227754A (en) * 1988-10-14 1990-08-08 Pilkington Plc Gas flow restrictor for glass coating apparatus
DE4107969A1 (en) * 1991-03-13 1992-09-24 Heimeier Gmbh Metall Theodor Thermostat valve lower part - has valve seat integral with housing, and has plastics sleeve with through-flow hole, and pre-setting control with flow restrictor holes
US5495872A (en) * 1994-01-31 1996-03-05 Integrity Measurement Partners Flow conditioner for more accurate measurement of fluid flow
US5529093A (en) * 1994-01-31 1996-06-25 Integrity Measurement Partners Flow conditioner profile plate for more accurate measurement of fluid flow
EP0745803A2 (en) * 1995-06-02 1996-12-04 Qe International B.V. Noise damper, a coke oven gas plant equipped therewith, and a baffle for the noise damper
EP0745803A3 (en) * 1995-06-02 1997-01-22 Qe International B.V. Noise damper, a coke oven gas plant equipped therewith, and a baffle for the noise damper
US5605399A (en) * 1995-10-17 1997-02-25 Komax Systems, Inc. Progressive motionless mixer
US5855355A (en) * 1997-03-10 1999-01-05 The Horton Company Quiet and constant flow control valve
US6722780B2 (en) 1998-12-07 2004-04-20 Roche Vitamins Inc. Preparation of liquid dispersions
US6530684B1 (en) * 1998-12-07 2003-03-11 Roche Vitamins Inc. Preparation of liquid dispersions
US6536940B1 (en) 1998-12-07 2003-03-25 Roche Vitamins Inc. Preparation of liquid dispersions
US6379035B1 (en) * 1999-03-05 2002-04-30 Fujikin Incorporated Static mixing and stirring device
WO2000065222A1 (en) * 1999-04-26 2000-11-02 Quantum Energy Technologies Fuel delivery system for combusting fuel mixtures
US6520767B1 (en) 1999-04-26 2003-02-18 Supercritical Combusion Corporation Fuel delivery system for combusting fuel mixtures
US20070214896A1 (en) * 2002-04-09 2007-09-20 Dieterich Standard, Inc. Averaging orifice primary flow element
US7406880B2 (en) 2002-04-09 2008-08-05 Dieterich Standard, Inc. Averaging orifice primary flow element
US7284450B2 (en) 2002-04-09 2007-10-23 Dieterich Standard, Inc. Averaging orifice primary flow element
US20030188586A1 (en) * 2002-04-09 2003-10-09 Orleskie Charles Theodore Averaging orifice primary flow element
US20060011413A1 (en) * 2002-09-18 2006-01-19 Savant Measurement Corporation Method for filtering ultrasonic noise within a fluid flow system
US7303048B2 (en) 2002-09-18 2007-12-04 Savant Measurement Corporation Method for filtering ultrasonic noise within a fluid flow system
US7303047B2 (en) 2002-09-18 2007-12-04 Savant Measurement Corporation Apparatus for filtering ultrasonic noise within a fluid flow system
US7303046B2 (en) 2002-09-18 2007-12-04 Savant Measurement Corporation Apparatus for filtering ultrasonic noise within a fluid flow system
US20060006022A1 (en) * 2002-09-18 2006-01-12 Savant Measurement Corporation Apparatus for filtering ultrasonic noise within a fluid flow system
US20060011412A1 (en) * 2002-09-18 2006-01-19 Savant Measurement Corporation Apparatus for filtering ultrasonic noise within a fluid flow system
US7089963B2 (en) * 2002-11-26 2006-08-15 David Meheen Flow laminarizing device
US20050263199A1 (en) * 2002-11-26 2005-12-01 David Meheen Flow laminarizing device
US20060141614A1 (en) * 2002-12-23 2006-06-29 Technische University Munchen Device and method for parallel, automated cultivation of cells in technical conditions
US7051765B1 (en) * 2003-12-19 2006-05-30 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Balanced orifice plate
US8568019B2 (en) 2004-01-09 2013-10-29 Talisman Capital Talon Fund, Ltd. Mixing apparatus for manufacturing an emulsified fuel
US20070294935A1 (en) * 2004-01-09 2007-12-27 Waldron Jack L Mixing apparatus and method for manufacturing an emulsified fuel
US8192073B1 (en) * 2004-01-09 2012-06-05 Waldron Jack L Mixing apparatus and method for manufacturing an emulsified fuel
US20060096650A1 (en) * 2004-03-18 2006-05-11 Sawchuk Blaine D Non-linear noise suppressor for perforated plate flow conditioner
US20080142548A1 (en) * 2006-12-13 2008-06-19 Frozen Beverage Services Of California, Inc. Method and Apparatus for Combination and Delivery of Beverages for Consumption
US7845688B2 (en) * 2007-04-04 2010-12-07 Savant Measurement Corporation Multiple material piping component
US20100020632A1 (en) * 2008-07-25 2010-01-28 The Procter & Gamble Company Apparatus And Method for Mixing by Producing Shear, Turbulence and/or Cavitation
US8950435B2 (en) * 2009-07-09 2015-02-10 Niagara Conservation Corp. Pressure compensation device
US20120103451A1 (en) * 2009-07-09 2012-05-03 Niagara Conservation Corp. Pressure compensation device
US9046115B1 (en) * 2009-07-23 2015-06-02 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Eddy current minimizing flow plug for use in flow conditioning and flow metering
US20110186655A1 (en) * 2009-11-17 2011-08-04 The University Of Salford Spray discharge assembly
US9296549B2 (en) * 2009-11-17 2016-03-29 The Salford Valve Company Limited Spray discharge assembly
US8759278B2 (en) 2010-01-13 2014-06-24 The Procter & Gamble Company Method of producing a fabric softening composition
US20110172137A1 (en) * 2010-01-13 2011-07-14 Francesc Corominas Method Of Producing A Fabric Softening Composition
US8307943B2 (en) * 2010-07-29 2012-11-13 General Electric Company High pressure drop muffling system
US20130333800A1 (en) * 2010-12-23 2013-12-19 Sidel S.P.A. Con Socio Unico System and method for filling a container with a pourable product
WO2012130060A1 (en) * 2011-03-30 2012-10-04 上海锅炉厂有限公司 Throttling device
CN103582774B (en) * 2011-04-04 2015-07-15 美卓自动化有限公司 Device for reducing flow noise and valve
US9677687B2 (en) * 2011-04-04 2017-06-13 Metso Automation Inc. Device for reducing flow noise and valve
WO2012136890A1 (en) * 2011-04-04 2012-10-11 Metso Automation Oy Device for reducing flow noise and valve
CN103582774A (en) * 2011-04-04 2014-02-12 美卓自动化有限公司 Device for reducing flow noise and valve
WO2012136891A1 (en) * 2011-04-04 2012-10-11 Metso Automation Oy Device for reducing flow noise and valve
US20140021383A1 (en) * 2011-04-04 2014-01-23 Metso Automation Oy Device for reducing flow noise and valve
US8430202B1 (en) 2011-12-28 2013-04-30 General Electric Company Compact high-pressure exhaust muffling devices
US20130186493A1 (en) * 2012-01-24 2013-07-25 United Technologies Corporation Bi-directional fluid flow regulator with funnel shaped baffles
US9399951B2 (en) 2012-04-17 2016-07-26 General Electric Company Modular louver system
US8550208B1 (en) 2012-04-23 2013-10-08 General Electric Company High pressure muffling devices
US20150184806A1 (en) * 2012-07-03 2015-07-02 Caltec Limited Apparatus and method for reducing the effect of joule-thomson cooling
US9004110B2 (en) * 2013-04-08 2015-04-14 Kuo-Chen Tsai Water hammer arrestor
US20140299216A1 (en) * 2013-04-08 2014-10-09 Kuo-Chen Tsai Water hammer arrestor
US9605695B2 (en) 2013-05-21 2017-03-28 Canada Pipeline Accessories, Co. Ltd. Flow conditioner and method of designing same
CN103256447B (en) * 2013-06-06 2015-04-01 兰州理工大学 Pipeline depressurization device
CN103256447A (en) * 2013-06-06 2013-08-21 兰州理工大学 Pipeline depressurization device
US9410565B2 (en) 2013-09-26 2016-08-09 Paul D. Van Buskirk Orifice plates
US20150083262A1 (en) * 2013-09-26 2015-03-26 Paul D. Van Buskirk Orifice plates
CN105829836A (en) * 2013-09-26 2016-08-03 保罗·范巴斯科克 Orifice plates
US9200650B2 (en) * 2013-09-26 2015-12-01 Paul D. Van Buskirk Orifice plates
CN103574082A (en) * 2013-11-12 2014-02-12 无锡杰尔压缩机有限公司 Throttling and pressure-reducing combined device of rhombic valve
US9752729B2 (en) 2014-07-07 2017-09-05 Canada Pipeline Accessories, Co. Ltd. Systems and methods for generating swirl in pipelines
US20160010778A1 (en) * 2014-07-09 2016-01-14 Nadeem Ahmad Malik Sparse 3d-multi-scale grid turbulence generator
US9599269B2 (en) * 2014-07-09 2017-03-21 Nadeem Ahmad Malik Sparse 3D-multi-scale grid turbulence generator
US9625293B2 (en) 2015-05-14 2017-04-18 Daniel Sawchuk Flow conditioner having integral pressure tap
CN105042264A (en) * 2015-07-13 2015-11-11 北京航空航天大学 Circulation water channel
US9845244B2 (en) 2015-09-17 2017-12-19 Arisdyne Systems, Inc. Method of forming graphene material by graphite exfoliation
US20170241574A1 (en) * 2015-09-21 2017-08-24 SYNCRUDE CANADA LTD. in trust for the owners of the Syncrude Project as such owners exist now & in Polymer-lined pipes and fittings with replaceable components
US9765279B2 (en) 2015-10-14 2017-09-19 Arisdyne Systems, Inc. Method for reducing neutral oil losses during neutralization step
CN105444478A (en) * 2015-12-28 2016-03-30 重庆美的通用制冷设备有限公司 Throttling device for air conditioner
US20180154326A1 (en) * 2016-12-01 2018-06-07 Phillips 66 Company Equalizing vapor velocity for reactor inlet
CN107013784A (en) * 2017-06-14 2017-08-04 西安交通大学 Congealed water hammer restraining device and restraining system

Similar Documents

Publication Publication Date Title
US3524467A (en) Fluid expanded disk valve
US3314290A (en) Shunt flow meter
US3380517A (en) Plate type heat exchangers
Anderson et al. Two-phase (gas—liquid) flow phenomena—I Pressure drop and hold-up for two-phase flow in vertical tubes
US3113615A (en) Heat exchanger header construction
US3349619A (en) Laminar flow element and flow meter
US3234959A (en) Check valve device
US3692064A (en) Fluid flow resistor
US3185181A (en) Diffuser swirl eliminator
US2865397A (en) Hydraulic governor
US2736332A (en) simmons
US5437784A (en) Injector for a flotation device
US4402485A (en) Eccentrically nested tube gas line silencer
US3332442A (en) Apparatus for mixing fluids
US2929248A (en) Flow meter
US3513864A (en) High pressure fluid control means
US5971604A (en) Mixing valve with adjustable regulating elements and central chamber
US2419278A (en) Insulated pipe
US4068389A (en) Gas-diffusion plate for fluidized bed apparatus
US4003398A (en) Pressure limiter device
Ting et al. Slender jets and thin sheets with surface tension
US2789797A (en) Heat exchanger fin structure
US2251066A (en) Heat exchange apparatus
US6016865A (en) Plate heat exchanger
US2127501A (en) Fluid flow measuring means