US3730479A - Adjustable fluid restrictor - Google Patents

Adjustable fluid restrictor Download PDF

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Publication number
US3730479A
US3730479A US00159745A US3730479DA US3730479A US 3730479 A US3730479 A US 3730479A US 00159745 A US00159745 A US 00159745A US 3730479D A US3730479D A US 3730479DA US 3730479 A US3730479 A US 3730479A
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US
United States
Prior art keywords
plug
ring
ridges
discs
adjustable fluid
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
US00159745A
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English (en)
Inventor
H Baumann
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.)
DRESER INDUSTRES Inc 1505 ELM STREET DALLAS TEXAS 75201 A CORP OF DE
Original Assignee
Masoneilan International 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
Application filed by Masoneilan International Inc filed Critical Masoneilan International Inc
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Publication of US3730479A publication Critical patent/US3730479A/en
Assigned to STUDEBAKER-WORTHINGTON, INC., A CORP. OF DE reassignment STUDEBAKER-WORTHINGTON, INC., A CORP. OF DE ASSIGNMENT OF ASSIGNORS INTEREST. EFFECTIVE DEC. 31, 1980. Assignors: MASONEILAN INTERNATIONAL , INC. A CORP. OF DE
Assigned to EDISON INTERNATONAL, INC. reassignment EDISON INTERNATONAL, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: STUDEBAKER-WORTHINGTON, INC., A CORP. OF DE
Assigned to DRESER INDUSTRES, INC. 1505 ELM STREET, DALLAS, TEXAS 75201, A CORP OF DE. reassignment DRESER INDUSTRES, INC. 1505 ELM STREET, DALLAS, TEXAS 75201, A CORP OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: EDISON INTERATONAL, INC. 1701 GOLF ROAD, ROLLING MEADOWS, IL., 60008, A CORP. OF DE.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86718—Dividing into parallel flow paths with recombining
    • Y10T137/86734—With metering feature
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86718—Dividing into parallel flow paths with recombining
    • Y10T137/86759—Reciprocating
    • Y10T137/86767—Spool

Definitions

  • the amount of sound power produced in a fluid system is generally a function of the fluid velocity. It has been determined, for instance, that the sound level of a free jet increases to the 8th power of the velocity below Mach 1 (sonic velocity) and to the 6.5th power above Mach 1. In practice this means that the sound power produced by a single throttling orifice will increase 256 times, if the throttling velocity across it is doubled. Now, since the velocity in an orifice is a function of V 2gh where h is the created pressure drop, one can state that a 4-time increase in pressure drop could produce 256 times more noise.
  • This invention relates to adjustable fluid restrictor devices such as shown and described in my prior U.S. Pat. No. 3,485,474, and providing a throttling series affording successive friction losses primarily through tortuous turns of a fluid under pressure, so as to limit the speed of throttling of that fluid to a value assuring a low and, in any case, acceptable level of the throttling noise; and also preventing quick wear, by the effects of cavitation, of the throttling elements of the device.
  • a fluid restrictor, or throttling device such as here concerned, has comprised:
  • a housing internally provided with concentric rings axially spaced from one another;
  • a moving stem mounted coaxially in regard to said rings and presenting radially projecting circular discs, arranged or spaced intermediate or in alternation with the rings, and so as to cooperate therewith;
  • the rings and discs of such throttling device provide radially spaced, axially directed passages for fluid flow, and radial flow passages connecting said axially directed passages in an annular labyrinth presenting adjustable restrictions by which is accomplished, through successive throttlings, that is, pressure reduction through a series of sharp turns of fluid under pressure.
  • Such fluid restrictor additionally affords successive throttlings independently of the flow variations of the fluid under pressure, and requires only relatively small movements of the stem discs in relation to the cage rings, to accomplish the needed adjustment of the restrictions of the labyrinth.
  • a fluid restrictor or throttling device of the type described in my prior U.S. Pat. No. 3,485,474, and characterized generally by concentric rings and discs, is utilized for the expansion, in two flows, of a compressible fluid, or gas, under pressure.
  • Increase in flow area between successive stages allows compensation for density changes of a passing gas while gradually reducing in pressure.
  • FIG. 1 is a vertical or axial section of a throttling device in accordance with the invention.
  • FIG. 2 is a fragmentary or detail view on a larger scale of a gas-adapted form of the improved seat ring and plug construction of the present invention.
  • a conventional, double flow valve housing or body 8 has a herein flanged inlet chamber 9, a laterally aligned outlet chamber 10, and therebetween an intermediate wall or partition 1 1 formed and apertured to define vertically aligned, upper and lower valve seat openings 12, 13 from said inlet chamber 9 to the two divided flow ducts 14, 15 discharging to outlet chamber 10, the latter flanged or otherwise formed similarly as inlet chamber 9 for coupling into a pressure fluid line for left-to-right flow therethrough.
  • annular cage means, shells, or seat rings 16, 17 threaded or otherwise received through said openings 12, 13, and stopped thereagainst as at external shoulders 18, 19.
  • the upper and lower cage means or seat rings 16, 17 areinteriorly formed with radially inwardly projecting, annular inlet end ridges 20, 21, and therebeyond with as many radially inwardly projecting, annular, axially spaced ribs or ridges 22, 23 as there are to be throttling stages.
  • the fluid restrictor hereof further has a moving stem comprising a pair of cylindrical, coaxial, integral or interdependently coupled upper and lower plugs 24, 25 mounting annular, radially projecting rings or discs, said circular, upper and lower plug discs comprising the inlet end discs 26, 27 cooperating with the seat ring inlet end ridges 20, 21, and axially spaced upwardly and downwardly therefrom the throttling discs 28, 29 cooperating or functioning with the corresponding or juxtaposed seat ring throttling ridges 22, 23.
  • the ring ridges -23 and plug discs 26-29 may be generally conical or tapering, as herein shown, or they may be variously formed as in my prior U.S. Pat. No. 3,485,474, or otherwise.
  • inlet end plug discs 26, 27 are larger than, and spaced similarly from and on the same (herein lower) side of, the seat ring inlet end ridges 20, 21. Further, for convenient assembly from (herein) below of the plug means 24, within the housing 8 and seat rings 16, 17 as inserted therein, the upper plug inlet end disc 26 is made smaller than the lower ring inlet ridge 21.
  • the upper plug throttling discs 28 are, of course, smaller than lower and upper ring ridges 23, 21, 22, 20; and the lower plug throttling discs 29 are smaller than lower ring ridges 23.
  • the spacing of the stem plug discs 2629 below the seat ring ridges 20-23 may be identical, as well may be the spacing between the upper and lower axial, ring and plug portions 30, 31, 32, 33 intermediate the said ridges and discs thereof.
  • the moving stem plugs 24, 25 further comprise upwardly and downwardly extending, reduced annular guides 34, 35 having a sliding, centering fit within bore passages 36, 37 formed in covers 38, 39 closing as conventionally the top and bottom openings 40, 41 provided as conventionally in the housing 8a for insertion therethrough of the heretofore described restrictor cage ring and stem plug means.
  • the invention plug means 24, 25 may be reciprocated for regulating or variously limiting the pressure fluid flows by a stem 42 coupled in any wise thereto, and extending upwardly through top cover 38 for the indicated axial manipulation by conventional actuator means.
  • the aforementioned cover bore passages are defined behind the guides 34, 35 as balancing or equilibrium chambers 36, 37 by holes or passages 43, 44 admitting to discharge passages 14, 15.
  • the restrictor hereof is seen to define radial reversing, or sharp angular bending, throttling passages formed by the opposed, parallel tapered ridges 20-23 and discs 26-29; by the axial ring portions 30, 31 opposing plug discs 26, 28; 27, 29; and by the axial plug portions 32, 33 opposing the ring ridges 20, 22; 21, 23.
  • the upward movement of stem 42 and plugs 24, 25 from the position of the drawing is to narrow the width, and reduce the area, of the aforesaid passages, and thereby to additionally restrict the two flows through the openings 12, 13.
  • the stern plug disc and seat ring ridge couples are adaptable to the variations of specific volume of a compressible fluid under pressure, that result from the expansion of such fluid.
  • the spaces between the discs and ridges may be calculated to take into consideration the variations of the specific weights of the compressible fluids, such as steam under pressure, this to accomplish, during the expansion of those fluids, the preventing of throttling noise and of the effects of accelerated wear; the successive restrictions by the throttling zones of the invention device assuring a distribution of pressure drops well adapted to such results.
  • the relative positions of the stem plug discs and seat ring ridges may be variously modified, within the scope of theinvention, and depending upon the flow values of the fluid, without disaffecting the results to be achieved by the device.
  • FIG. 2 To compensate for density changes in the successive throttling stages, provision is made, in the FIG. 2 form of the device adapted for gaseous media, for successive enlargement of the flow area used to reduce fluid pressure.
  • FIG. 2 the intermediate partition wall is shown at 45, the upper and lower seat rings generally at 46, 47 and the upper and lower valve plugs at 48, 49.
  • successive enlargements of the flow area in the successive throttling stages are achieved by successively increasing or sharpening the upper and lower face angles of the upper and lower plug discs 50, 52a, 52b, 52c; 51, 53a, 53b, 53c," and similarly the upper and lower face angles of the ring ridges 54, 56a, 56b, 56c; 55, 57a, 57b, 570.
  • a similar distribution, or like successive enlargement of the flow area may be accomplished between the plugs or discs and rings in the lateral direction. This is accomplished by successively decreasing the diameter of the disc-intervening cylindrical plug wall portions 58a, 58b, 58c; 59a, 59b, 59c, and by similarly successively increasing the diameter of the ridge intervening, cylindrical ring wall portions 60a, 60b, 600; 61a, 61b, 61c.
  • restrictor is susceptible of ready assembly and disassembly in the manner described, with (referring to FIG. 1) the rings 16, 17 first being inserted to engage at their shoulders 18, 19 the openings 12, 13, with the plugs 24, 25 then being inserted to the position of the drawings, and with the covers 38, 39 then being installed over the guides 34, 35 and to seal the openings 40, 41 in the usual manner.
  • An adjustable fluid restrictor comprising a. a valve housing
  • lateral pressure fluid inletting means comprising an inlet chamber and opening
  • lateral pressure fluid outletting means comprising two flow ducts and a communicating outlet chamber and opening;
  • upper and lower stem plug means coaxially arranged within and for vertical reciprocation relative to said cage ring means;
  • upper and lower housing covers closing said access openings
  • Adjustable fluid restrictor of claim 1 wherein the lowermost upper plug disc is below the lowermost upper ring ridge, wherein the uppermost lower plug disc is below the uppermost lower ring ridge, and wherein said disc and ridge couples are of overlapping diameter whereby upon reciprocation of said plug means to close said couples together said upper and lower ducts may be closed to said pressure fluid.
  • a adjustable fluid restrictor of claim 2 wherein the disc of one is smaller than the ridge of the other of said couples, whereby the device may be assembled by installing said ring means through said intermediate,
  • said plug means comprise cylindrical guides for engaging in said cover bearing formations, and wherein said bearing formations comprise recesses extending beyond said guides within said covers, said beyond-extending recesses ported to said outletting ducts whereby to define equilibrium chambers.
  • Adjustable fluid restrictor of claim 2 wherein the spacing of said disc and ridge couples is equal whereby the two expansions flows of pressure fluid are simultaneously closed and opened thereby.
  • Adjustable fluid restrictor of claim 1 wherein saidring and plug ridges and discs define radially reversing pressure fluid flow passages, and wherein said plug means comprise a stem extending without said housing for reciprocation by actuator means, whereby to vary the axial distance between said ridges and discs, and thus to regulate the width and area of said flow passages.
  • Adjustable fluid restrictor as set forth in claim 1, wherein the proportioning of and spacing between the upper and lower ring and plug means ridges and discs in so correlated as to order substantially equal flows of said pressure fluids therethrough.
  • Adjustable fluid restrictor as set forth in claim 1, wherein the discs of said upper and lower plugs means are positioned correspondingly above or below the similarly spaced ridges of said upper and lower ring means, and wherein said upper and lower plug and ring means define intermediate said ridges and l'lbS uxtaposed cylindrical surface areas across which the pressure fluid is axially flowed intermediate the radial passages defined by said ridge and disc means.
  • Adjustable fluid restrictor as set forth in claim 1, wherein the upper and lower faces of the upper and lower plug discs are, from the inlet ends of the plugs, of progressively steeper angle, thereby having progressively greater spacing from the juxtaposed ring ridges.
  • Adjustable fluid restrictor as set forth in claim 1, wherein the upper and lower faces of the ring ridges are, from the inlet ends of the rings, of progressively steeper angle, thereby having progressively greater spacing from the juxtaposed plug discs.
  • Adjustable fluid restrictor as set forth in claim 1, wherein said sleeve rings comprise cylindrical portions intervening between said ridges, and wherein said cylindrical portions are, from the inlet ends of said rings, of progressively increasing diameter, thereby havingprogressively greater lateral spacing from the opposing plug portions.
  • Adjustable fluid restrictor as set forth in claim 1, wherein said stern plugs comprise cylindrical portions intervening between said discs, and wherein said cylindrical portions are, from the inlet ends of said plugs, of progressively decreasing diameter thereby having progressively greater lateral spacing from the opposing ring portions.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)
  • Details Of Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Servomotors (AREA)
US00159745A 1970-07-06 1971-07-06 Adjustable fluid restrictor Expired - Lifetime US3730479A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR707025031A FR2134072B2 (de) 1970-07-06 1970-07-06

Publications (1)

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US3730479A true US3730479A (en) 1973-05-01

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ID=9058343

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US00159745A Expired - Lifetime US3730479A (en) 1970-07-06 1971-07-06 Adjustable fluid restrictor

Country Status (7)

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US (1) US3730479A (de)
CA (1) CA934270A (de)
DE (1) DE2133422C3 (de)
ES (1) ES197320Y (de)
FR (1) FR2134072B2 (de)
GB (1) GB1354536A (de)
NL (1) NL7109338A (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4363464A (en) * 1980-07-03 1982-12-14 Spils Richard W Angle globe valve
US4503884A (en) * 1982-06-22 1985-03-12 Spils Richard W Angle globe valve
US4549718A (en) * 1984-05-07 1985-10-29 Smith International, Inc. Low noise valve
US4858515A (en) * 1982-11-11 1989-08-22 Danfoss A/S Priority valve for hydraulic installations
USRE33053E (en) * 1984-05-07 1989-09-12 Cameron Iron Works Usa Inc. Low noise valve
US4971099A (en) * 1989-12-15 1990-11-20 Cooper Industries, Inc. Pressure balanced cartridge choke valve
US6286550B1 (en) * 1996-10-31 2001-09-11 Yamatake Corporation Valve apparatus
WO2006111214A1 (de) * 2005-04-15 2006-10-26 Gestra Ag Ventil, insbesondere zum kontrollierten abgeben von sich in einem dampfkessel ansammelnden salzen und dergleichen
US20080041469A1 (en) * 2004-05-04 2008-02-21 Bosch Rexroth Ag On-Off Valve
GB2506657A (en) * 2012-10-05 2014-04-09 Sev Glocon Ltd Flow trim for a valve
US20140138566A1 (en) * 2007-11-26 2014-05-22 Cameron International Corporation Control valve trim
US20150020903A1 (en) * 2013-07-19 2015-01-22 Control Components, Inc. Cascade trim for control valve

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107461506B (zh) * 2016-06-06 2020-06-23 费希尔控制国际公司 具有弯曲凹口的阀塞

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2737979A (en) * 1952-03-28 1956-03-13 Exxon Research Engineering Co Mixing valve structure and method of operation

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE55338C (de) * Firma C. F. BOEHRINGER & SÖHNE in Waldhof b. Mannheim Verfahren zur Darstellung von Isoecgonin und von Derivaten desselben

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2737979A (en) * 1952-03-28 1956-03-13 Exxon Research Engineering Co Mixing valve structure and method of operation

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4363464A (en) * 1980-07-03 1982-12-14 Spils Richard W Angle globe valve
US4503884A (en) * 1982-06-22 1985-03-12 Spils Richard W Angle globe valve
US4858515A (en) * 1982-11-11 1989-08-22 Danfoss A/S Priority valve for hydraulic installations
US4549718A (en) * 1984-05-07 1985-10-29 Smith International, Inc. Low noise valve
USRE33053E (en) * 1984-05-07 1989-09-12 Cameron Iron Works Usa Inc. Low noise valve
US4971099A (en) * 1989-12-15 1990-11-20 Cooper Industries, Inc. Pressure balanced cartridge choke valve
US6286550B1 (en) * 1996-10-31 2001-09-11 Yamatake Corporation Valve apparatus
US20080041469A1 (en) * 2004-05-04 2008-02-21 Bosch Rexroth Ag On-Off Valve
US7537026B2 (en) * 2004-05-04 2009-05-26 Bosch Rexroth Ag On-off valve
WO2006111214A1 (de) * 2005-04-15 2006-10-26 Gestra Ag Ventil, insbesondere zum kontrollierten abgeben von sich in einem dampfkessel ansammelnden salzen und dergleichen
US20140138566A1 (en) * 2007-11-26 2014-05-22 Cameron International Corporation Control valve trim
US9683667B2 (en) * 2007-11-26 2017-06-20 Cameron International Corporation Control valve trim
GB2506657A (en) * 2012-10-05 2014-04-09 Sev Glocon Ltd Flow trim for a valve
US20150020903A1 (en) * 2013-07-19 2015-01-22 Control Components, Inc. Cascade trim for control valve
US9556970B2 (en) * 2013-07-19 2017-01-31 Control Components, Inc. Cascade trim for control valve

Also Published As

Publication number Publication date
NL7109338A (de) 1972-01-10
CA934270A (en) 1973-09-25
FR2134072A2 (de) 1972-12-08
ES197320Y (es) 1975-10-01
DE2133422C3 (de) 1978-10-12
DE2133422B2 (de) 1978-02-02
ES197320U (es) 1975-04-16
FR2134072B2 (de) 1974-03-01
GB1354536A (en) 1974-06-05
DE2133422A1 (de) 1972-01-20

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Legal Events

Date Code Title Description
AS Assignment

Owner name: DRESER INDUSTRES, INC. 1505 ELM STREET, DALLAS, TE

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:EDISON INTERATONAL, INC. 1701 GOLF ROAD, ROLLING MEADOWS, IL., 60008, A CORP. OF DE.;REEL/FRAME:004393/0550

Effective date: 19850222