US3665965A - Apparatus for reducing flowing fluid pressure with low noise generation - Google Patents

Apparatus for reducing flowing fluid pressure with low noise generation Download PDF

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US3665965A
US3665965A US40607A US3665965DA US3665965A US 3665965 A US3665965 A US 3665965A US 40607 A US40607 A US 40607A US 3665965D A US3665965D A US 3665965DA US 3665965 A US3665965 A US 3665965A
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transverse wall
wall means
upstream
downstream
noise
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Hans D Baumann
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DRESER INDUSTRES Inc 1505 ELM STREET DALLAS TEXAS 75201 A CORP OF DE
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MASONELLAN INTERNATIONAL Inc
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US case filed in Nevada District Court litigation https://portal.unifiedpatents.com/litigation/Nevada%20District%20Court/case/3%3A20-cv-00040 Source: District Court Jurisdiction: Nevada District Court "Unified Patents Litigation Data" by Unified Patents is licensed under a Creative Commons Attribution 4.0 International License.
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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.
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    • 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
    • F16L55/04Devices damping pulsations or vibrations in fluids
    • 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

Definitions

  • the low noise fluid pressure throttling apparatus [52] 1.1.5. Cl ..138/42, 181/46, 251/127, provides an assembly of a plurality of such plates, and which 181/56 may comprise a segment of or be interposed in a fluid flow [51] It. CI ..FlSd 1/00 containing c ndui[ The low noise throttling plates are [58] Field of Search ..138/42; 181/46, 69, 33.9, 36.2, pasaged by multiple small section rifices producing a h 181/56?
  • References Cited reducing assembly defines with the intervening flow contain- UNITED STATES PATENTS ing means a volume which is dimensioned to produce resonant damping of the noise pressure wave generated 1n the pnmary 1,697,481 1/1929 Sloan.. ..181/69 rifices, Th pressure dro through the reducing apparatus is 2,677,23 1 5/1954 Corneliusx divided into nearly equal ratio drops across each plate, further 2,075,3 Tyden 1 8 noise generation. 2,520,089 8/1950 Lippincott 138/40 1,914,072 6/1933 Boylston ..181/69 12 China, 3 Drawing Figures Patented May 30, 1972 3,655,965
  • the invention pertains to apparatus for reducing the pressure of gaseous or liquid media flowing through a pipe or duct, and more particularly for accomplishing the fluid pressure reduction with minimum or greatly reduced generation of noise, or unwanted sound.
  • the problems attendant upon the annular of noise are well known to include not only the human reaction criteria of annoyance, damage to hearing, and reduction in work efi'lciency, but also the effects on physical structures and equipment, such as structural fatigue, and equipment malfunction.
  • Fluid dynamic theory predicates a high dependence of the herein concerned throttling noise energy on the pressure drop ratio and fluid flow velocity.
  • High pressure differentials across a jet or constriction in the fluid flow generate noise energy which increases at a rate greater than the rate of increase in the pressure drop in ratio.
  • the noise or vibration energy generated also varies with the eighth power of the fluid velocity in the jet. Both a high velocity, and a pressure drop ratio, then, lead to high accoustical efficiency, or high energy conversion to noise.
  • Any solid or fluid medium vibrating in response to noise energy waves will convert a portion of the energy it receives to heat. With fluids it is the fluid viscosity which occasions the conversion, or damping. A similar noise energy damping reaction occurs as well in solids.
  • the amount of energy passed on through such media varies with the negative power of the distance that the energy travels within the medium. And in solids like the metals found in pipes, the attenuation in the medium increases with the frequency of the noise energy.
  • FIG. 1 is a plan view of the invention apparatus
  • FIG. 2 is a section along any bisecting'line of FIG. 1;
  • FIG. 3 is a perspective view of a modified form of the apparatus.
  • FIGS. 1 and 2 of the drawings a herein circular, radially symmetrical conduit C is shown as having an inner wall defining two axially in-line parts 3a, 3b which extend to either side of a ring or annular spacer 4.
  • the spacer 4 has a larger diameter, cylindrical'inner face 5 coaxial with conduit axis A--A', and an intermediate, annular, infacing flange or lip 6 of full circumferential extent.
  • a pair of transverse wall forming means or plates 7, 9 having a tight fit within spacer 4 are held by suitable means, herein the collars 8 and 11, against the opposite faces of lip 6.
  • the collars 8 and 11 are in turn closed against the plates 7, 9 by the ends of smaller diameter shoulders of conduit parts 3a, 3b when the same are assembled with the spacer 4 as by external clamping means which may be conventional and are, therefore, not shown.
  • the plates 7, 9 may be parallel mounted with the ring 4 in a rigid assembly or frame in any desired manner, and wherein the circumferentially containing means 4 is inserted in or is a portion of the conduit C.
  • Upstream plate 7 is passaged by a multiplicity of jet orifices or holes 12.
  • the number of holes 12 is great, and their crosssectional area is small.
  • the holes 12 will be understood to be utilized in a number: cross-sectional area combination which for a given fluid at a given or maximum expected flow rate produces the desired low pressure drop across the plate 7, in
  • This attenuation by the conduit may be expressed as:
  • the frequency is, of course, a direct function of the passages or hole diameter.
  • the diameter of the upstream holes 12, and thereby increasing the frequency of the noise energy generated therein a larger portion of the noise energy is attenuated in the conduit walls, and a corresponding reduction is achieved in the noise radiated to or polluting the environment.
  • the downstream plate 9 has a set of orifices or holes 14 which are seen as offset from the holes 12.
  • the number and cross-sectional area of these holes is again adjusted to the desired pressure drop, for a given fluid and flow rate, and is selected also and novelly to provide, as before, increased frequency of vibration of, and thereby enhanced conduit wall attenuation of, the generated noise.
  • the total cross-sectional area of the holes 14 is made larger than the total cross-sectional area of the holes 12, by the provision either of more or larger holes 14 through the second plate 9.
  • the pressure drop across the perforated plates 7 and 9 is split up into equal or substantially equal ratios. This results in a substantial decrease of the overall noise level, since as above noted, the level of noise energy generated in a jet increases more rapidly than the rate of increase in the pressure drop ratio across the jet. In other words, by thus keeping the pressure drop ratio across each perforated plate smaller, there is achieved a reduction of noise energy generated, over that for a single plate with a higher accoustical efficiency in noise generation due to its higher pressure drop.
  • V the volume of the cavity 21
  • the desired resonant cavity may under the'invention be provided by a volume 21 having shape and proportion other than that defined by the frame spacer 6 and plates 7, 9 herein particularly disclosed and described.
  • FIG. 3 a modified embodiment comprising a plurality of three transverse plates, incorporating upstream plate 7 and a pair of downstream plates 9, 22.
  • the downstream plate 22 will be understood to have openings 23 having the similar position and proportion relationship to the openings 14 of downstream plate 9 as the latter have to the openings 12 of upstream plate 7.
  • the plates 7, 9, 22 will be understood to define resonant cavities, and to divide the frame volume, in accordance with the invention teachings as hereinbefore explained.
  • modified ring 4a may have a lip 6a against which upstream plate 7 is held by collar 8, and downstream plate 9 is engaged by insert ring 24, against the opposite face of which the downstream plate 22 is in turn held by collar 11.
  • modified bolt 16a will be understood to be passed through intermediate plate 9 for threading into downstream plate 22, with the plates being spaced thereat by a pair of the collars 18.
  • FIG. 3 Also shown in FIG. 3 is one expedient for closing the ends of conduit portions 3a, 3b against the sides of the rings 4a, comprising integral flanges 25, 26 on said conduit portions 3a, 3b, and a series of radially disposed nut and bolt or similar fastenings 27 therethrough as shown.
  • the frame hereof may comprise the described plate pluralities and the intervening conduit wall portion as defined by the herein disclosed spacer, or by the securing of the wall forming means or plates to the conduit inner wall and in spaced assembly in any other desired or convenient manner.
  • the plate assembly or frame hereof may be utilized in downstream conjunction with a conventional, single orifice throttling valve. It will be appreciated that in such application the low noise plates hereof operate to filter the major noise emanating from the throttling valve, preventing the noise from travelling into the downstream pipe and hence from radiating through that to the outside environment.
  • said multiple, small, flow throttling passages in said upstream and downstream transverse wall means provided in such determined large number and small cross section as radiates noise energy at a frequency at which it is highly attenuated within said conduit, and whereby it accords the apparatus low accoustical efficiency;
  • said circumferentially containing means comprising, with the one or more pairs of any two adjacent of said upstream and downstream transverse wall means, one or more resonant damping chambers,
  • each said resonant damping chamber defining, by the spacing of said transverse wall means, a volume calculated to produce the resonant frequency of the sound waves generated by the fluid flow through said transverse wall means.
  • transverse wall means are plates, and wherein said throttling passages are holes defining jet orifices in said plates.
  • transverse wall means comprise annular plates
  • circumferential containing means comprises a spacer ring
  • said flow capacity adjusting means comprises means for closing a determined portion of the passages of one or another of said wall means.
  • passage closing means comprise plate means removably supported against the upstream side of said one or another wall means.

Abstract

Fluid pressure reducing apparatus presenting low noise throttling plates. The low noise fluid pressure throttling apparatus provides an assembly of a plurality of such plates, and which may comprise a segment of or be interposed in a fluid flow containing conduit. The low noise throttling plates are passaged by multiple small section orifices producing a high frequency pressure wave whose noise is more readily attenuated by the conduit. The spacing of the plates in the pressure reducing assembly defines with the intervening flow containing means a volume which is dimensioned to produce resonant damping of the noise pressure wave generated in the primary orifices. The pressure drop through the reducing apparatus is divided into nearly equal ratio drops across each plate, further minimizing noise generation.

Description

United States Patent Baumann [4 1 May 30, 1972 541 APPARATUS FOR REDUCING 1,229,434 6/1917 FLockhart .Q ..181/69 FLOWING FLUID PRESSURE WITH Low NOISE GENERATION FOREIGN PATENTS OR APPLICATIONS [72] Inventor: Hans D- Bauma'nn Foxbom' Mass 117,203 7/1918 Great Bntam ..181/69 [73] Assignee: Masoneilan International, Inc., Norwood, Primary Examiner-Samuel B. Rothberg Mass. Anamey-Chittick, Pfund, Birch, Samuels & Gauthier 22 F '1 2 7 red May 6,19 0 ABSTRACT 21 A l. N .2 40 607 1 pp 0 fluid pressure reducing apparatus presenting low noise throttling plates. The low noise fluid pressure throttling apparatus [52] 1.1.5. Cl ..138/42, 181/46, 251/127, provides an assembly of a plurality of such plates, and which 181/56 may comprise a segment of or be interposed in a fluid flow [51] It. CI ..FlSd 1/00 containing c ndui[ The low noise throttling plates are [58] Field of Search ..138/42; 181/46, 69, 33.9, 36.2, pasaged by multiple small section rifices producing a h 181/56? 251/127; 285/49 frequency pressure wave whose noise is more readily attenuated by the conduit. The spacing of the plates in the pressure [56] References Cited reducing assembly defines with the intervening flow contain- UNITED STATES PATENTS ing means a volume which is dimensioned to produce resonant damping of the noise pressure wave generated 1n the pnmary 1,697,481 1/1929 Sloan.. ..181/69 rifices, Th pressure dro through the reducing apparatus is 2,677,23 1 5/1954 Corneliusx divided into nearly equal ratio drops across each plate, further 2,075,3 Tyden 1 8 noise generation. 2,520,089 8/1950 Lippincott 138/40 1,914,072 6/1933 Boylston ..181/69 12 China, 3 Drawing Figures Patented May 30, 1972 3,655,965
2 Sheets-Sheet 1 O IQ INVENTOR HANS D. BAUMANN BY ird, 9 r
ATTORNEYS FIG. 2
Patented May 30, 1972 3,665,965
2 Sheets-Sheet 2 INVENTOR HANS o. BAUMANN cum 1:10:19 SM ATTORNEYS APPARATUS FOR REDUCING FLOWING FLUID PRESSURE WITII LOW NOISE GENERATION BACKGROUND OF THE INVENTION The invention pertains to apparatus for reducing the pressure of gaseous or liquid media flowing through a pipe or duct, and more particularly for accomplishing the fluid pressure reduction with minimum or greatly reduced generation of noise, or unwanted sound. The problems attendant upon the annular of noise are well known to include not only the human reaction criteria of annoyance, damage to hearing, and reduction in work efi'lciency, but also the effects on physical structures and equipment, such as structural fatigue, and equipment malfunction.
In industrial plants, gas pressure reducing stations, and the like where are found the throttling valve or aerodynamically generated sound effects with which the invention is particularly concerned, the noise problems attendant thereon are rapidly intensifying in absolute terms, and have attained more recently a magnitude heightened also be increased human sensibility to noise pollution. But noise control efforts have heretofore been limited generally in this country to the use'of mufflers, attenuation chambers and the like, or devices for absorption or insulation of the generated noise. This invention, in contrast, cuts throttling noise at the source, and thereby achieves superior results both in reducing throttling noise and in reducing mechanical vibration from levels experienced with conventional pressure reducing valves.
BRIEF SUMMARY OF THE INVENTION In view of its novel aspects, the theoretical considerations on which the invention is rested are here set forth in aid of its full and clear understanding by those skilled in the art.
Fluid dynamic theory predicates a high dependence of the herein concerned throttling noise energy on the pressure drop ratio and fluid flow velocity. High pressure differentials across a jet or constriction in the fluid flow generate noise energy which increases at a rate greater than the rate of increase in the pressure drop in ratio. The noise or vibration energy generated also varies with the eighth power of the fluid velocity in the jet. Both a high velocity, and a pressure drop ratio, then, lead to high accoustical efficiency, or high energy conversion to noise.
By far the most efficient way to reduce throttling noise is, of course, todecrease the velocity of the flow. In accomplishing this by increasing the effective flow area only some of the resultant noise reduction is offset by the noise being a function also of flow area.
Any solid or fluid medium vibrating in response to noise energy waves will convert a portion of the energy it receives to heat. With fluids it is the fluid viscosity which occasions the conversion, or damping. A similar noise energy damping reaction occurs as well in solids.
Further, the amount of energy passed on through such media varies with the negative power of the distance that the energy travels within the medium. And in solids like the metals found in pipes, the attenuation in the medium increases with the frequency of the noise energy.
It is thus an object of the present invention to provide apparatus for pressure reduction or throttling of fluid flow with a low accoustical efficiency.
It is a further object of the invention to provide an accoustical filter for absorbing downstream the noise of conventional valves and thereby preventing the radiation of that noise through the fluid conduit walls to its external surroundings.
It is a further object of the invention to provide a device for throttling fluid flow with greatly reduced noise generation by minimum fluid velocity constricting jet means.
It is a further object of this invention to provide a pressure reducing or throttling device having constricting jet means characterized by lowered pressure drop thereacross.
It is a further object of the present invention to provide a pressure reducing apparatus which increases the viscous damping of the noise energy in the flowing fluid.
It is a further object of the present invention to provide a fluid pressure throttling device which generates noise at a frequency which provides for greater attenuation of the noise energy by the fluid conduit.
It is a further object of the invention to absorb part of the aerydynarnically created noise by a process of resonant damping within said throttling device.
BRIEF DESCRIPTION OF DRAWINGS In the drawings:
FIG. 1 is a plan view of the invention apparatus; and
FIG. 2 is a section along any bisecting'line of FIG. 1; and
FIG. 3 is a perspective view of a modified form of the apparatus.
DETAILED DESCRIPTION OF THE INVENTION In the fonn of FIGS. 1 and 2 of the drawings a herein circular, radially symmetrical conduit C is shown as having an inner wall defining two axially in- line parts 3a, 3b which extend to either side of a ring or annular spacer 4. The spacer 4 has a larger diameter, cylindrical'inner face 5 coaxial with conduit axis A--A', and an intermediate, annular, infacing flange or lip 6 of full circumferential extent.
A pair of transverse wall forming means or plates 7, 9 having a tight fit within spacer 4 are held by suitable means, herein the collars 8 and 11, against the opposite faces of lip 6. The collars 8 and 11 are in turn closed against the plates 7, 9 by the ends of smaller diameter shoulders of conduit parts 3a, 3b when the same are assembled with the spacer 4 as by external clamping means which may be conventional and are, therefore, not shown.
Under the invention, the plates 7, 9 may be parallel mounted with the ring 4 in a rigid assembly or frame in any desired manner, and wherein the circumferentially containing means 4 is inserted in or is a portion of the conduit C.
Upstream plate 7 is passaged by a multiplicity of jet orifices or holes 12. The number of holes 12 is great, and their crosssectional area is small. The holes 12 will be understood to be utilized in a number: cross-sectional area combination which for a given fluid at a given or maximum expected flow rate produces the desired low pressure drop across the plate 7, in
the fluid flow traversing, the same in the left-right direction A-A.
Under the invention the holes 12 are made numerous and individually of small cross-sectional area also to increase the vibratory frequency of the noise energy accompanying the pressure drop in said flowing fluid.
Most of the noise energy generated in the upstream set of holes 12 is radiated by pressure waves from a region of noise energy turbulence downstream of plate 7, and tends to proceed out through the walls of the conduit C. In responding to these pressure waves, the conduit C absorbs a portion of the energy from the waves by damping effect of the conduit material.
This attenuation by the conduit may be expressed as:
A 17 log (mf) where m mass density of the wall and f frequency of the vibration.
The frequency is, of course, a direct function of the passages or hole diameter. Under the invention, then, by reducing the diameter of the upstream holes 12, and thereby increasing the frequency of the noise energy generated therein, a larger portion of the noise energy is attenuated in the conduit walls, and a corresponding reduction is achieved in the noise radiated to or polluting the environment.
The downstream plate 9 has a set of orifices or holes 14 which are seen as offset from the holes 12. The number and cross-sectional area of these holes is again adjusted to the desired pressure drop, for a given fluid and flow rate, and is selected also and novelly to provide, as before, increased frequency of vibration of, and thereby enhanced conduit wall attenuation of, the generated noise.
By varying the size and number of the holes 14 in the downstream plate 9, compensation is made for the change in fluid density by the reduction in pressure through the upstream plate 7. Further, the total cross-sectional area of the holes 14 is made larger than the total cross-sectional area of the holes 12, by the provision either of more or larger holes 14 through the second plate 9.
In accordance with the invention, then, the pressure drop across the perforated plates 7 and 9 is split up into equal or substantially equal ratios. This results in a substantial decrease of the overall noise level, since as above noted, the level of noise energy generated in a jet increases more rapidly than the rate of increase in the pressure drop ratio across the jet. In other words, by thus keeping the pressure drop ratio across each perforated plate smaller, there is achieved a reduction of noise energy generated, over that for a single plate with a higher accoustical efficiency in noise generation due to its higher pressure drop.
For example, with a total pressure drop ratio of 4 the accoustical efficiency for a single plate is 36 times greater than the efficiency it would have with a pressure drop ratio of 2 across its set of holes. With two plates each producing a pressure drop ratio of 2 the total noise energy from the two plates in one-eighteenth what it would have been with a single plate.
Centrally, a fastening or bolt 16 having a head 17 is passed through an oversized opening in one of the plates 7, 9 and through an intervening collar 18 and threaded into the other of the plates 7, 9, in part to intermediately clamp the plates 7, 9 together with the spacer 6 in a unitary assembly, or frame.
The bolt 16 may also mount various flow restricting means such as the flow regulating plate 19, which may be positioned between the plates 7 and 9, or upstream of plate 7, the same to effectively block a portion of the first and/or second of the channel sets 12, 14 thereby reducing the flow capacity of the plates so as to maintain the same total pressure drop under different, reduced flow conditions.
The aforementioned offsetting of the downstream holes 14, as clearly shown in FIG. 2, will be understood to improve the pressure reducing capability of the plates 7, 9 and at the same time to enhance the resonant effect in the cavity or volume 21 defined by or within the frame formed by the plates 7, 9 and the spacer 4. The longitudinal or axial length of the collar 18 and the spacer lip 6 then, is calculated to comprehend or contain the desired amount of fluid within the frame volume 21. For a particular conduit, and given that the resonant frequency of the volume 21 varies with its size, the same can be controlled, then, by adjusting the length as aforesaid of the collar 6 and spacer 18.
The equation relating the plates 7, 9 may be stated as:
f Ac/2 Vk where A total area of the holes contained in the first plate 7;
c the speed of sound in the fluid used;
V= the volume of the cavity 21; and
k a constant.
By making a resonant frequency of the volume 21 nearly equal to the frequency of noise energy generated in the holes 12 of the upstream plate 7, large resonant pressure differentials will be built up in the volume 21 at that frequency. Through the process of resonant damping, and due to the viscosity of the fluid, the high resonant pressure differentials result in an increased conversion of noise energy to fluid heat.
It will be understood that the pressure reducing apparatus of the invention may comprise the plates 7, 9 and also any other transverse wall forming means susceptible of channeling by jet passages such as the hole sets 12, 14.
Further, the desired resonant cavity may under the'invention be provided by a volume 21 having shape and proportion other than that defined by the frame spacer 6 and plates 7, 9 herein particularly disclosed and described.
Still further, the resonant cavity may be defined by and within a frame comprising a plurality other or more than the described two spaced transverse plates, or other wall forming means.
Thus, in FIG. 3 is shown a modified embodiment comprising a plurality of three transverse plates, incorporating upstream plate 7 and a pair of downstream plates 9, 22. In this arrangement, the downstream plate 22 will be understood to have openings 23 having the similar position and proportion relationship to the openings 14 of downstream plate 9 as the latter have to the openings 12 of upstream plate 7. Also, the plates 7, 9, 22 will be understood to define resonant cavities, and to divide the frame volume, in accordance with the invention teachings as hereinbefore explained.
To accommodate the additional plate 22, the modified ring 4a may have a lip 6a against which upstream plate 7 is held by collar 8, and downstream plate 9 is engaged by insert ring 24, against the opposite face of which the downstream plate 22 is in turn held by collar 11. And modified bolt 16a will be understood to be passed through intermediate plate 9 for threading into downstream plate 22, with the plates being spaced thereat by a pair of the collars 18.
Also shown in FIG. 3 is one expedient for closing the ends of conduit portions 3a, 3b against the sides of the rings 4a, comprising integral flanges 25, 26 on said conduit portions 3a, 3b, and a series of radially disposed nut and bolt or similar fastenings 27 therethrough as shown.
It will also be understood that the frame hereof may comprise the described plate pluralities and the intervening conduit wall portion as defined by the herein disclosed spacer, or by the securing of the wall forming means or plates to the conduit inner wall and in spaced assembly in any other desired or convenient manner.
Further, in accordance with the invention, the plate assembly or frame hereof may be utilized in downstream conjunction with a conventional, single orifice throttling valve. It will be appreciated that in such application the low noise plates hereof operate to filter the major noise emanating from the throttling valve, preventing the noise from travelling into the downstream pipe and hence from radiating through that to the outside environment.
I claim:
1. Low noise generating apparatus for reducing the pressure of fluid flow in a conduit, comprising:
a. upstream transverse wall means;
b. multiple, small, flow throttling passages of calculated the number and/or size of said multiple, small, flow throttling passages relatively increasing, and said calculated total areas of said passages progressively increasing in constant ratio, from each to the next in the succession of said upstream and downstream transverse wall means,
said multiple, small, flow throttling passages in said upstream and downstream transverse wall means provided in such determined large number and small cross section as radiates noise energy at a frequency at which it is highly attenuated within said conduit, and whereby it accords the apparatus low accoustical efficiency; and
e. means circumferentially containing the fluid flow intermediate said upstream and downstream throttling passages and forming with said transverse wall means a frame supporting and spacing said throttling passages,
said circumferentially containing means comprising, with the one or more pairs of any two adjacent of said upstream and downstream transverse wall means, one or more resonant damping chambers,
each said resonant damping chamber defining, by the spacing of said transverse wall means, a volume calculated to produce the resonant frequency of the sound waves generated by the fluid flow through said transverse wall means.
2. The apparatus of claim 1, wherein the number and/or size of the throttling passages of one is varied from the number and/or size of the throttling passages of other adjacent of said upstream and downstream transverse wall means such as to divide the pressure drop across said apparatus into substantially equal ratio pressure drops across the individual of said upstream and downstream transverse wall means.
3. The apparatus of claim 1, wherein the throttling passages of one are offset in the flow direction from the passages of another of said upstream and downstream transverse wall means.
4. The apparatus of claim 1, wherein said transverse wall means are plates, and wherein said throttling passages are holes defining jet orifices in said plates.
5. The apparatus of claim 1, wherein said transverse wall means comprise annular plates, and wherein said circumferential containing means comprises a spacer ring.
6. The apparatus of claim 1 and means uniting said transverse wall means centrally of said circumferential containing means, said centrally uniting means comprising a fastener engaging and adapted to draw together said transverse wall means.
7. The apparatus of claim 6, and spacer means limiting said drawing together by said fastener, said spacer means comprising one or more collars, and said fastener engaged behind one of said transverse wall means, passed through said one or more collars, and adjustably secured to another said transverse wall means.
8. The apparatus of claim 1, and means positioning said transverse wall means for determined upstream-downstream spacing of said flow throttling passages.
9. The apparatus of claim 1, and means for adjusting the flow capacity of said frame.
10. The apparatus of claim 9, wherein said flow capacity adjusting means comprises means for closing a determined portion of the passages of one or another of said wall means.
11. The apparatus of claim 10 wherein said passage closing means comprise plate means removably supported against the upstream side of said one or another wall means.
12. The apparatus of claim 11, wherein said plate means are carried on fastener means removably securing together said wall means centrally of said circumferential containing means.

Claims (12)

1. Low noise generating apparatus for reducing the pressure of fluid flow in a conduit, comprising: a. upstream transverse wall means; b. multiple, small, flow throttling passages of calcUlated total area in and establishing small fluid pressure drop across and high frequency of noise generation by said upstream wall means; c. one or more downstream transverse wall means; d. multiple, small, flow throttling passages of calculated total area in and establishing small fluid pressure drop across and high frequency of noise generation by said one or more downstream wall means, the number and/or size of said multiple, small, flow throttling passages relatively increasing, and said calculated total areas of said passages progressively increasing in constant ratio, from each to the next in the succession of said upstream and downstream transverse wall means, said multiple, small, flow throttling passages in said upstream and downstream transverse wall means provided in such determined large number and small cross section as radiates noise energy at a frequency at which it is highly attenuated within said conduit, and whereby it accords the apparatus low accoustical efficiency; and e. means circumferentially containing the fluid flow intermediate said upstream and downstream throttling passages and forming with said transverse wall means a frame supporting and spacing said throttling passages, said circumferentially containing means comprising, with the one or more pairs of any two adjacent of said upstream and downstream transverse wall means, one or more resonant damping chambers, each said resonant damping chamber defining, by the spacing of said transverse wall means, a volume calculated to produce the resonant frequency of the sound waves generated by the fluid flow through said transverse wall means.
2. The apparatus of claim 1, wherein the number and/or size of the throttling passages of one is varied from the number and/or size of the throttling passages of other adjacent of said upstream and downstream transverse wall means such as to divide the pressure drop across said apparatus into substantially equal ratio pressure drops across the individual of said upstream and downstream transverse wall means.
3. The apparatus of claim 1, wherein the throttling passages of one are offset in the flow direction from the passages of another of said upstream and downstream transverse wall means.
4. The apparatus of claim 1, wherein said transverse wall means are plates, and wherein said throttling passages are holes defining jet orifices in said plates.
5. The apparatus of claim 1, wherein said transverse wall means comprise annular plates, and wherein said circumferential containing means comprises a spacer ring.
6. The apparatus of claim 1 and means uniting said transverse wall means centrally of said circumferential containing means, said centrally uniting means comprising a fastener engaging and adapted to draw together said transverse wall means.
7. The apparatus of claim 6, and spacer means limiting said drawing together by said fastener, said spacer means comprising one or more collars, and said fastener engaged behind one of said transverse wall means, passed through said one or more collars, and adjustably secured to another said transverse wall means.
8. The apparatus of claim 1, and means positioning said transverse wall means for determined upstream-downstream spacing of said flow throttling passages.
9. The apparatus of claim 1, and means for adjusting the flow capacity of said frame.
10. The apparatus of claim 9, wherein said flow capacity adjusting means comprises means for closing a determined portion of the passages of one or another of said wall means.
11. The apparatus of claim 10 wherein said passage closing means comprise plate means removably supported against the upstream side of said one or another wall means.
12. The apparatus of claim 11, wherein said plate means are carried on fastener means removably securing together said wall means centrally of said circumferential containing means.
US40607A 1970-05-26 1970-05-26 Apparatus for reducing flowing fluid pressure with low noise generation Expired - Lifetime US3665965A (en)

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US4162784A (en) * 1976-03-08 1979-07-31 S.A. Des Anciens Etablissements Paul Wurth Pressure equalization apparatus and method
US4185664A (en) * 1978-04-17 1980-01-29 Dresser Industries, Inc. Low noise fluid pressure reducer
US4241805A (en) * 1979-04-02 1980-12-30 Vibration And Noise Engineering Corporation High pressure gas vent noise control apparatus and method
US4392144A (en) * 1981-07-01 1983-07-05 Keisuke Honda Recording unit
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US4475821A (en) * 1980-10-07 1984-10-09 Bruker-Analytische Messtechnik Gmbh Mixing chamber
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US20080178583A1 (en) * 2007-01-12 2008-07-31 Yuguang Zhang Device with Trace Emission for Treatment of Exhaust Gas
US20090199656A1 (en) * 2008-02-12 2009-08-13 Sunita Rani Systems and methods for managing pressure and flow rate
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FR2958328A1 (en) * 2010-04-06 2011-10-07 Peugeot Citroen Automobiles Sa DEVICE FOR INSULATING A COOLING CIRCUIT
CN102563221A (en) * 2010-12-20 2012-07-11 西安航天远征流体控制股份有限公司 Liquid pressure reduction pipe
US20120281496A1 (en) * 2004-01-09 2012-11-08 Waldron Jack L Mixing apparatus and method for manufacturing an emulsified fuel
US8307943B2 (en) * 2010-07-29 2012-11-13 General Electric Company High pressure drop muffling system
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US8511096B1 (en) 2012-04-17 2013-08-20 General Electric Company High bleed flow muffling system
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US8550208B1 (en) 2012-04-23 2013-10-08 General Electric Company High pressure muffling devices
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WO2014042539A1 (en) 2012-09-17 2014-03-20 Hagevik Paal Irgens Device to reduce the pressure of a liquid flow and a regulating valve
US20160061372A1 (en) * 2014-09-02 2016-03-03 Canada Pipeline Accessories, Co. Ltd. Heated Flow Conditioning Systems And Methods of Using Same
US9399951B2 (en) 2012-04-17 2016-07-26 General Electric Company Modular louver system
US20160341334A1 (en) * 2014-02-07 2016-11-24 Valpres S.R.L. Shutter for a rotary adjustment valve
US20170205015A1 (en) * 2016-01-15 2017-07-20 Emerson Process Management Regulator Technologies, Inc. Noise attenuation apparatus for fluid devices
CN106979432A (en) * 2016-01-15 2017-07-25 艾默生过程管理调节技术公司 Sound attenuation for pressure regulator
US10208880B2 (en) 2016-12-30 2019-02-19 Emerson Process Management Regulator Technologies, Inc. Noise attenuators for use with process control devices
US10495234B2 (en) 2017-09-27 2019-12-03 Fisher Controls International Llc Flow stabilizer for a control valve
WO2020215140A1 (en) * 2019-04-25 2020-10-29 Petróleo Brasileiro S.A. - Petrobras Smooth pressure-reduction device and methods for smooth pressure reduction
US11460140B2 (en) 2017-10-26 2022-10-04 Performance Pulsation Control, Inc. Mini-dampeners at pump combined with system pulsation dampener
US11473711B2 (en) 2017-10-26 2022-10-18 Performance Pulsation Control, Inc. System pulsation dampener device(s) substituting for pulsation dampeners utilizing compression material therein
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Publication number Priority date Publication date Assignee Title
USRE29714E (en) * 1970-11-27 1978-08-01 Sanders Associates, Inc. Fluid flow restrictor
US4130173A (en) * 1971-10-01 1978-12-19 Vought Corporation Apparatus and method for reducing flow disturbances in a flowing stream of compressible fluid
US3878870A (en) * 1974-04-16 1975-04-22 Atomic Energy Commission Orifice design for the control of coupled region flow
US4024891A (en) * 1974-06-29 1977-05-24 Honeywell Inc. Control valve with noise abating features
US4113050A (en) * 1975-09-25 1978-09-12 British Gas Corporation Fluid-flow noise reduction systems
US4162784A (en) * 1976-03-08 1979-07-31 S.A. Des Anciens Etablissements Paul Wurth Pressure equalization apparatus and method
US4067361A (en) * 1976-04-21 1978-01-10 The United States Of America As Represented By The Secretary Of The Navy Silent self-controlled orificial restrictor
US4148337A (en) * 1977-02-08 1979-04-10 Fluid Controls, Inc. Free delivery return valve and associated system
US4185664A (en) * 1978-04-17 1980-01-29 Dresser Industries, Inc. Low noise fluid pressure reducer
US4479510A (en) * 1979-01-10 1984-10-30 Roger Bey Attenuating rotating valve having varying configurations
US4241805A (en) * 1979-04-02 1980-12-30 Vibration And Noise Engineering Corporation High pressure gas vent noise control apparatus and method
US4475821A (en) * 1980-10-07 1984-10-09 Bruker-Analytische Messtechnik Gmbh Mixing chamber
US4402485A (en) * 1981-06-11 1983-09-06 Fisher Controls Company, Inc. Eccentrically nested tube gas line silencer
US4392144A (en) * 1981-07-01 1983-07-05 Keisuke Honda Recording unit
US4922716A (en) * 1988-01-13 1990-05-08 Cincinnati Milacron Inc. Throttled exhaust outlet to reservoir for reducing noise resulting from release hydraulic pressure surges
US5070909A (en) * 1990-06-11 1991-12-10 Davenport Robert G Low recovery rotary control valve
US5209259A (en) * 1991-01-15 1993-05-11 E. I. Du Pont De Nemours And Company Fluid distribution system having noise reduction mechanism
US5400825A (en) * 1991-08-30 1995-03-28 Fisher Controls International, Inc. Rotary noise attenuator
US5332004A (en) * 1991-08-30 1994-07-26 Fisher Controls International, Inc. Rotary noise attenuator
US5193583A (en) * 1991-08-30 1993-03-16 Fisher Controls International, Inc. Rotary noise attenuator
US5180139A (en) * 1991-10-15 1993-01-19 Fisher Controls International, Inc. Rotary ball fluid control valve with noise attenuator
US5437305A (en) * 1992-09-22 1995-08-01 Forward Spin Technologies, Inc. Flow control valve
US5511584A (en) * 1992-09-22 1996-04-30 Leinen; Chris M. Low noise rotary control valve
US5664760A (en) * 1995-04-06 1997-09-09 United Technologies Corporation Pressure regulation valve with integrated downstream pressure tap
US5758689A (en) * 1996-12-12 1998-06-02 Forward Spin Consulting, Inc. Control valve with partial flow diffuser
US5988586A (en) * 1997-03-07 1999-11-23 Dresser Industries, Inc. Low noise ball valve assembly with downstream insert
US5890505A (en) * 1997-04-03 1999-04-06 Dresser Industries, Inc. Low noise ball valve assembly with downstream airfoil insert
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
EP1172594A3 (en) * 2000-07-12 2003-03-12 Wagner Alarm- und Sicherungssysteme GmbH Apparatus for extinguishing fires
US6807986B2 (en) 2002-03-22 2004-10-26 Dresser, Inc. Noise reduction device for fluid flow systems
US20040262553A1 (en) * 2002-03-22 2004-12-30 Dresser, Inc., A Delaware Corporation Noise reductio device for fluid flow systems
US6880579B2 (en) 2002-03-22 2005-04-19 Dresser, Inc. Noise reduction device for fluid flow systems
US8568019B2 (en) * 2004-01-09 2013-10-29 Talisman Capital Talon Fund, Ltd. Mixing apparatus for manufacturing an emulsified fuel
US20120281496A1 (en) * 2004-01-09 2012-11-08 Waldron Jack L Mixing apparatus and method for manufacturing an emulsified fuel
US9033938B2 (en) * 2005-10-05 2015-05-19 Acu Rate Pty Limited Controlled flow administration set
US20110127454A1 (en) * 2005-10-05 2011-06-02 Acu Rate Pty Limited Controlled flow administration set
WO2007108686A1 (en) * 2006-03-22 2007-09-27 Aluheat B.V. Sound reduction provision for heat apparatuses
US20100167220A1 (en) * 2006-03-22 2010-07-01 Aluheat B.V. Sound Reduction Provision for Heat Apparatuses
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
US7857095B2 (en) * 2007-01-12 2010-12-28 Yuguang Zhang Device with trace emission for treatment of exhaust gas
US20080178583A1 (en) * 2007-01-12 2008-07-31 Yuguang Zhang Device with Trace Emission for Treatment of Exhaust Gas
US9038669B2 (en) * 2008-02-12 2015-05-26 Sunita Rani Systems and methods for managing pressure and flow rate
US20090199656A1 (en) * 2008-02-12 2009-08-13 Sunita Rani Systems and methods for managing pressure and flow rate
US20100071793A1 (en) * 2008-07-25 2010-03-25 Hatch Ltd. Apparatus for stabilization and deceleration of supersonic flow incorporating a diverging nozzle and perforated plate
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GB2474147A (en) * 2008-07-25 2011-04-06 Hatch Ltd Apparatus for stabilization and deceleration of supersonic flow incorporating a diverging nozzle and perforated plate
US8176941B2 (en) 2008-07-25 2012-05-15 Hatch Ltd. Apparatus for stabilization and deceleration of supersonic flow incorporating a diverging nozzle and perforated plate
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WO2010009529A1 (en) * 2008-07-25 2010-01-28 Hatch Ltd. Apparatus for stabilization and deceleration of supersonic flow incorporating a diverging nozzle and perforated plate
FR2958328A1 (en) * 2010-04-06 2011-10-07 Peugeot Citroen Automobiles Sa DEVICE FOR INSULATING A COOLING CIRCUIT
EP2375029A1 (en) * 2010-04-06 2011-10-12 Peugeot Citroën Automobiles SA Device for insulating a cooling circuit
US8016071B1 (en) * 2010-06-21 2011-09-13 Trane International Inc. Multi-stage low pressure drop muffler
US8307943B2 (en) * 2010-07-29 2012-11-13 General Electric Company High pressure drop muffling system
CN102563221A (en) * 2010-12-20 2012-07-11 西安航天远征流体控制股份有限公司 Liquid pressure reduction pipe
CN102798423A (en) * 2011-05-27 2012-11-28 克洛纳有限公司 Accessory apparatus for flowmeters
EP2527661A1 (en) * 2011-05-27 2012-11-28 Krohne AG Auxiliary device for flow meters
US8430202B1 (en) 2011-12-28 2013-04-30 General Electric Company Compact high-pressure exhaust muffling devices
US20130220443A1 (en) * 2012-02-22 2013-08-29 The Board Of Trustees Of The University Of Illinois Apparatus and method for flow control
US8511096B1 (en) 2012-04-17 2013-08-20 General Electric Company High bleed flow muffling system
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
US20140069737A1 (en) * 2012-09-10 2014-03-13 Dresser Inc. Noise attenuation device and fluid coupling comprised thereof
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EP2895777A4 (en) * 2012-09-17 2016-07-13 Paal Irgens Hagevik Device to reduce the pressure of a liquid flow and a regulating valve
US10100947B2 (en) * 2014-02-07 2018-10-16 Valpres S.R.L. Shutter for a rotary adjustment valve
US20160341334A1 (en) * 2014-02-07 2016-11-24 Valpres S.R.L. Shutter for a rotary adjustment valve
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US20160061372A1 (en) * 2014-09-02 2016-03-03 Canada Pipeline Accessories, Co. Ltd. Heated Flow Conditioning Systems And Methods of Using Same
US9453520B2 (en) * 2014-09-02 2016-09-27 Canada Pipeline Accessories, Co. Ltd. Heated flow conditioning systems and methods of using same
US20170205015A1 (en) * 2016-01-15 2017-07-20 Emerson Process Management Regulator Technologies, Inc. Noise attenuation apparatus for fluid devices
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US11156317B2 (en) * 2016-12-30 2021-10-26 Emerson Process Management Regulator Technologies, Inc. Noise attenuators for use with process control devices
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US11460140B2 (en) 2017-10-26 2022-10-04 Performance Pulsation Control, Inc. Mini-dampeners at pump combined with system pulsation dampener
US11473711B2 (en) 2017-10-26 2022-10-18 Performance Pulsation Control, Inc. System pulsation dampener device(s) substituting for pulsation dampeners utilizing compression material therein
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