US3405907A - Venturi arrangement - Google Patents

Venturi arrangement Download PDF

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Publication number
US3405907A
US3405907A US455043A US45504365A US3405907A US 3405907 A US3405907 A US 3405907A US 455043 A US455043 A US 455043A US 45504365 A US45504365 A US 45504365A US 3405907 A US3405907 A US 3405907A
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Prior art keywords
fluid
annular
arrangement
venturi
axial
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Expired - Lifetime
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US455043A
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English (en)
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Lutz T Kayser
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    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D11/00—Control of flow ratio
    • G05D11/006—Control of flow ratio involving a first fluid acting on the feeding of a second fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02K—JET-PROPULSION PLANTS
    • F02K9/00—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof
    • F02K9/72—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof using liquid and solid propellants, i.e. hybrid rocket-engine plants
    • 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
    • F16K7/00—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves
    • F16K7/12—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with flat, dished, or bowl-shaped diaphragm
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/01—Control of flow without auxiliary power
    • G05D7/0106—Control of flow without auxiliary power the sensing element being a flexible member, e.g. bellows, diaphragm, capsule
    • G05D7/0113—Control of flow without auxiliary power the sensing element being a flexible member, e.g. bellows, diaphragm, capsule the sensing element acting as a valve
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/01—Control of flow without auxiliary power
    • G05D7/0106—Control of flow without auxiliary power the sensing element being a flexible member, e.g. bellows, diaphragm, capsule
    • G05D7/012—Control of flow without auxiliary power the sensing element being a flexible member, e.g. bellows, diaphragm, capsule the sensing element being deformable and acting as a valve

Definitions

  • a venturi arrangement for control of fluid passing therethrough substantially independent of pressure variations downstream of the venturi arrangement in which fluid fed in axial direction of the venturi is deflected at the end of the inlet in direction substantially normal to the axis and passed through a radially outwardly extending annular gap which has a length and width so that its peripheral cross section gradually increases in radially outward direction to a cross section several times larger than its smallest cross section so that the fluid cavitating and partly evaporating in the region of the smallest cross section of the gap will recondense in the latter to produce thereby a constant fluid flow through the venturi arrangement independent of pressure variations downstream of the gap.
  • control means are necessary in which the amount of fluid flow passing through the control means is completely or at least nearly independent from the fluid pressure downstream of the control means.
  • Throttle valves, regulating pumps and complicated regulating arrangements have been used for this purpose, however, the above stated requirements have only to a limited degree been satisfied with such arrangements.
  • cavitating venturi tubes comprising a convergent tube portion and a coaxial divergent tube portion joined to the smallest cross section of the convergent tube portion and diverging at a very small acute angle, have been used for controlling the flow of liquids substantially independent of the pressure downstream of the control arrangement.
  • the venturi arrangement of the present invention basically comprises housing means having an axial inlet passage means for feeding a fluid, for instance liquid under pressure into the housing means, and wall means defining an annular gap extending in radia1 outward direction from the inlet passage means.
  • Deflector means are also provided which extend substantially normal to the axis of the inlet passage means and which are arranged opposite and spaced from the inner end thereof for deflecting the axial stream of fluid passing through the inlet passage means in radial outward direction and the wall means defining the annular gap extend from the space between the inner end of the inlet passage means and the deflector means in radial outward direction to guide the fluid in a sheet-like annular stream in radial outward direction.
  • the adiabatic evaporation taking place in the smallest cross section of the annular gap will produce such an increase of the specific volume of the fluid passing therethrough that the amount of fluid passing per time unit through the arrangement will be substantially constant and substantially independent from the fluid pressure downstream of the arrangement while the downstream fluid pressure is less than the inlet fluid pressure.
  • the cross section of the annular gap downstream of the smallest cross section thereof increases gradually so that the condensation of the mixture of saturated vapor passing therethrough can take place during a sufliciently long time and in a stable manner.
  • the logitudinal cross section of the annular gap has therefore to be formed accordingly in such a manner that the peripheral flow cross section of the annular gap increases gradually in radial outward direction to a cross section which is several times larger than the smallest peripheral cross section.
  • the deflector means may comprise a flexible membrane forming part of the wall means defining the aforementioned annular gap, which membrane is at its outer perighery fixed t0 the housing means. Such an arrangement includes further means engaging substantially central portion of the membrane at the surface thereof facing away from the inner end of the inlet passage means for moving the central portion of the membrane toward or away from the inner end of the inlet passage means to change thereby the axial thickness of the annular gap.
  • the deflector means may also be constituted by an axially movable piston arranged opposite the inner end of the inlet passage means and having preferably a convexly curved surface facing the inner end of the inlet passage means.
  • the arrangement may also comprise spring means having a characteristic changing according to a linear or square function and acting on a central portion of the membrane or on the piston in a direction opposite to the force imparted thereto by the pressure of the fluid passing into the housing through the inlet passage means and impinging on the membrane or the piston.
  • the arrangement may also include fluid passage means communicating with the inlet passage means and guiding fluid with substantially the same pressure as will reside in the inlet passage means to the surface of a central portion of the membrane or to the movable piston which faces away from the inner end of the inlet passage means so that the same pressure will act on opposite sides of the membrane or the piston, whereby the arrangement will become independent from fluid pressure variations upstream of the venturi arrangement.
  • the axial adjustment of the central portion of the membrane or of the piston can also be produced by screw means acting on the rear face of the membrane or the piston.
  • the pitch of the screw thread of the screw means is preferably chosen in such a manner that the total desired adjustment of the axial thickness of the annular gap can be produced with a single revolution of the screw means so that the adjusted axial thickness of the annular gap and therewith the adjusted throughput of fluid can be easily observed, respectively set, by means of a pointer fixed to the screw for rotation therewith and a linear scale cooperating with the pointer.
  • the venturi arrangement of the present invention differs from the venturi arrangements known in the art in which the inflow as well as the outflow of the fluid occurs in axial direction, in that, that in the venturi arrangement of the present invention only the inflow of the fluid occurs in axial direction, whereas the outflow downstream of the smallest cross section of the annular gap occurs in a sheet like flow in radial outward direction.
  • the axial smallest cross section of the annular gap is preferably arranged radially outwardly of the cylindrical inner surface of the inlet passage means.
  • the inner end of the inlet passage means preferably gradually increases to blend into the smallest cross section of the annular gap.
  • FIG. 1 is a schematic axial cross section through the venturi arrangement of the present invention
  • FIG. 2 is a partial cross section through a venturi arrangement according to the present invention and illustrating a different arrangement for adjusting the position of the membrane;
  • FIG. 3 is a partial cross section similar to FIG. 1 and differing therefrom mainly by the configuration of the annular gap;
  • FIG. 4 is a partial cross section similar to FIG. 3 and showing a further modification.
  • the venturi arrangement comprises housing means including a first member 1 having a central tubular portion 2 defining an inlet passage means for feeding a fluid under pressure into the housing means.
  • the first member 1 includes further an annular plate-shaped portion 3 having preferably an inner frustoconical surface 3' of a cone angle which is only slightly smaller than 180 and the annular plate-shaped portion 3 is integrally joined at its inner periphery to the inner end of the tubular portion 2.
  • the annular plate-shaped portion 3 is integrally joined to an annular portion 7 defining an annular chamber 7, and
  • the annular portion 7 has an outer radial flange 9 spaced in axial and radial direction from the annular plateshaped portion 3.
  • the inner surface of the central tubular portion 2 gradually blends into the inner surface of the plate-shaped portion 3 along a curve 4 which may have the shape of a quarter of a circle or a similar configuration so that fluid may pass the inner end of the tubular portion 2 without turbulence.
  • the arrangement includes further, a second annular substantially disc-shaped member 11 having a central cylindrical flange 15 extending in axial direction away from the central tubular portion 2 of the first member 1 and an outer flange 17 arranged opposite the flange 9 of the first member.
  • a flexible membrane 10 overlays the inner surface of the second member 11 and the membrane 10- has an outer peripheral portion tightly clamped between the outer flanges 9 and 17 of the first and second member.
  • a plurality of screws 16 only two of which are shown in FIG.
  • Outlet passage means 8 in form of a tube extending fluid-tightly connected to the transverse wall of the annular portion 7 communicates with the chamber means 7 formed by the annular portion 7 of the first member 1.
  • the inner surface 3' of the annular plate-shaped portion 3 of the first member 1 forms with the inner surface of the membrane 10 facing the surface 3' an elongated annular gap 6 having its narrowest cross section at 5 and the annular gap 6 in the embodiment illustrated in FIG. 1 gradually increases in thickness towards the annular chamber 7'.
  • the arrangement according to the present invention preferably also comprises adjusting means and such adjusting means may include a piston 12 guided for movement in axial direction in the cylindrical flange 15 of the second member 11.
  • the piston 12 engages with its preferably convexly curved end wall 13 a central portion of the flexible membrane 10 so that during axial movement of the piston 12 toward the inner end of the inlet passage means 2 the central portion of the membrane 6 may be inwardly deflected to change thereby the narrowest cross section 5 of the annular gap 6.
  • Inward movement of the piston 12 against the pressure of the liquid passing through the inlet passage 2 into the venturi arrangement may be produced by a screw 14 abutting with one end thereof against the transverse wall 13 of the piston 12.
  • the screw 14 threadingly engages a support member 16 connected in any manner, not shown in the drawing, to the housing of the venturi arrangement and a small wheel 18 may be fixedly connected to the outer end of the screw 14 for turning the latter about its axis.
  • the pitch of the screw thread of the screw 14 is preferably chosen in such a way that the total desired axial adjustment of the piston 12 may be obtained with a single revolution of the screw.
  • a pointer 19 is preferably fixedly connected to the screw 14 and the end of the pointer 19 cooperates with a linear scale 20 provided on the support member 16 about the axis of the screw 14 so that the position of the screw and therewith the axial adjustment of the piston 12 can be easily observed and set.
  • a spring abutting with one end against the transverse wall 13 of the piston 12 and with the other end thereof against a support member similar to the member 16 may also be provided to counteract the forces acting on the inner forces of the central portion of the membrane.
  • a spring may have any desired predetermined characteristic so that the spring pressure changes in any desired manner with the change of the axial position of the piston 12 and the spring pressure may also be adjusted by compressing the spring to varying degree by changing the position of the support member against which one end of the spring abuts.
  • FIG. 2 A slightly modified arrangement is partly shown in FIG. 2 in which the cylindrical flange 15 of the member 11 is closed at its outer end and in which passage means 21 are provided which communicate at one end thereof with the inlet passage means 2 and at the other end thereof with the space between the piston 12 and the outer closed end of the cylindrical portion 15'.
  • a passage 21 may be used in an arrangement in which the piston 12 is pushed inwardly by a rod 22 to which a variable force is applied in axial direction and in which it is desired to change the axial position of the piston 12 and therewith the axial cross section of the annular gap 6 in dependence on the variable force applied against rod 22.
  • the passage means 21 will assure that in this case the axial position of the piston 12 is not influenced by variations of the pressure of the fluid passing through the inlet passage means 2, since the passage means 21 will equalize the pressure acting on opposite sides of the central portion of the membrane 10, so that the axial position of the piston 12 and therefore the position of the central portion of the membrane will depend only on the force applied onto the rod 22.
  • FIG. 1 illustrates an arrangement in which the axial thickness of the annular gap 6 gradually increases in radially outward direction
  • FIG. 3 shows anarrangement in which the inner surface 3" of the plate-shaped portion of the member 1 is parallel to the opposite surface of the second member 11 so that the axial thickness of the annular gap 6 is constant throughout its length
  • FIG. 4 shows a further arrangement in which the inner surface 3 of the member 1" is inclined in the direction opposite to that shown in FIG. 1 so that the axial width of the annular gap 6" decreases gradually in radially outward direction.
  • the inner surface of the membrane 10 and/ or the inner surface 3', 3" or 3" may be roughened to provide for a pressure drop in the fluid passing between these surfaces.
  • venturi arrangement above described may be used for control of fluid (amount of flow and mixture ratio of fuel and a combustion agent) independent of the pressure downstream of the venturi arrangement for rocket engines or other combustion engines, for feed control independent of the load acting on the feed mechanism in hydraulic devices, especially in machine tools.
  • fluid amount of flow and mixture ratio of fuel and a combustion agent
  • metal membranes of appropriate material it is possible to control and adjust the flow of aggressive or very hot liquids, for instance also the flow of molten metals. This is especially possible with the venturi arrangement according to the present invention in which no sealing means which would be attacked by such liquids are necessary and in which the members forming the housing of the venturi arrangement may be welded together.
  • venturi arrangement of the present invention can be used as a regulating valve which is independent from pressure variations downstream of the valve in all such cases Where a simple throttle valve is unsuitable or where axial cavitating venturi tubes, control pumps or other control arrangements would be too expensive or not be suitable in view of the characteristics of the fluid medium to be controlled.
  • housing means having an axial substantially cylindrical inlet passage means for feeding a fluid under pressure into said housing means, said inlet passage means having an inner end; and wall means defining an annular gap, said gap having a radial length which is a multiple of its maximum axial thickness, said annular gap having its smallest peripheral cross section in the region of said inner end of said passage means and said peripheral cross section gradually increasing in radially outward direction to a peripheral cross section which is several times larger than said smallest peripheral cross section, said gap constituting means for causing cavitation and partial evaporation of the fluid in said smallest peripheral cross section and subsequent recondensation of the fluid during radial outward flow thereof for thereby producing a constant fluid flow through the arrangement substantially independent of pressure variations downstream of said gap while the downstream fluid pressure is less than the inlet fluid pressure.
  • a venturi arrangement as set forth in claim 1, and including deflector means extending substantially normal to the axis of said inlet passage means and arranged opposite and spaced from said inner end thereof for deflecting an axial stream of fluid passing through said inlet passage means in radially outward direction, said annular gap extending in radial outward direction from the space between said inner end of said inlet passage means and said deflector means to guide the fluid in a sheet-like stream in radially outward direction.
  • annular chamber means coaxially arranged about said inlet passage means, said annular gap extending from the space between said inner end of said inlet passage means in radially outward direction to said annular chamber means, and outlet passage means communicating with said annular chamber means.
  • adjusting means operatively connected to said deflector means for adjusting the axial position thereof in order to vary the smallest cross section of said gap to change thereby the flow of fluid through the venturi arrangement.
  • said wall means comprises a rigid annular wall integrally joined at the inner and outer periphery thereof to said inner end of said inlet passage means and to said annular chamber means, respectively
  • said deflector means comprises a circular membrane having an inner surface facing an inner surface of said rigid annular wall and being spaced a small distance therefrom and 'fluid-tightly joined at its outer periphery to said annular chamber means, said annular gap being formed between said inner surface of said membrane and said inner surface of said rigid annular Wall, and including means engaging that surface of said membrane which faces away from said rigid wall at a substantially central portion thereof in combination
  • housing means including a first member 1 having a central tubular portion defining an inlet passage means for feeding a fluid under pressure into said housing means, an annular plate-shaped portion extending transverse to the axis of said tubular portion from the inner end of the latter and integrally'joined at its inner periphery to said inner end, and an
  • said adjusting means comprise screw means operatively connected to said piston for adjusting the axial position thereof.
  • said means for connecting said outer flanges comprise weld means for welding said membrane in a fluidtight manner to said outer flanges.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lift Valve (AREA)
US455043A 1964-05-08 1965-05-07 Venturi arrangement Expired - Lifetime US3405907A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEK52891A DE1284648B (de) 1964-05-08 1964-05-08 Steuerventil zur Begrenzung der zeitlichen Durchflussmenge auf eine maximale Groesse

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3642026A (en) * 1970-04-08 1972-02-15 Air Reduction Metering valve
US3680171A (en) * 1970-11-23 1972-08-01 Wright Products Hydraulic door closer
JPS51117332A (en) * 1975-03-26 1976-10-15 Canadian Patents Dev Fluid flow quantity regulating device
WO1990013859A1 (en) * 1989-05-05 1990-11-15 Framo Developments (Uk) Limited Multiphase process mixing and measuring system
US5413311A (en) * 1994-03-01 1995-05-09 Tescom Corporation Gas valve
DE19730035A1 (de) * 1997-07-14 1999-02-18 Troester Guenther Membranventil
CN102884348A (zh) * 2010-04-28 2013-01-16 中央硝子株式会社 卤素气体或卤素化合物气体的填充容器用阀
AU2013315933B2 (en) * 2012-08-30 2017-09-07 Fisher Controls International Llc Valve body with improved lower flow cavity
US9863542B2 (en) 2013-02-01 2018-01-09 Swagelok Company Diaphragm valve with welded diaphragm seat carrier
EP2898204B1 (de) 2012-09-21 2018-11-28 United Technologies Corporation Schmierung einer flexiblen halterung für einen getriebeträger

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0780611A1 (de) * 1995-12-22 1997-06-25 Applied Materials, Inc. Durchflussregelventil

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US234602A (en) * 1880-11-16 Balanced valve
US816280A (en) * 1904-08-02 1906-03-27 Arthur S Tuttle Venturi tube.
US1986600A (en) * 1933-09-06 1935-01-01 Gulf Res & Dev Corp Variable orifice choke valve
DE842565C (de) * 1945-08-30 1952-06-30 Carba Ag Membrankammer
FR1155578A (fr) * 1956-07-06 1958-05-06 Le Clapet Hoerbiger Appareil de contrôle de débit
GB795192A (en) * 1954-12-20 1958-05-21 Alexis Sobolev Improvements in and relating to valves for fluids
US2875977A (en) * 1953-08-19 1959-03-03 Crane Co Diaphragm ballcock
FR1181763A (fr) * 1957-08-29 1959-06-18 Fiordham Pressings Ltd Soc Perfectionnements apportés aux soupapes commandées par flotteur pour chasses d'eau et similaires
FR1187832A (fr) * 1957-09-09 1959-09-16 Cie Generale D Acetylene Robinet pour bouteilles de gaz comprimé
US2918933A (en) * 1952-11-14 1959-12-29 Oil Ct Tool Company Constant volume controls
FR1227692A (fr) * 1959-06-17 1960-08-22 Perfectionnements aux robinets à membrane
US3003743A (en) * 1958-12-22 1961-10-10 Concordia Maschinen & Elek Zit Valve with pressure balancing diaphragms
GB895517A (en) * 1959-09-21 1962-05-02 Bendix Corp Fluid-flow control valve
US3180360A (en) * 1961-06-13 1965-04-27 Bertin Et Cie Soc Compensated valve
US3283767A (en) * 1963-05-31 1966-11-08 Ibm Jet fluid amplifier

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US234602A (en) * 1880-11-16 Balanced valve
US816280A (en) * 1904-08-02 1906-03-27 Arthur S Tuttle Venturi tube.
US1986600A (en) * 1933-09-06 1935-01-01 Gulf Res & Dev Corp Variable orifice choke valve
DE842565C (de) * 1945-08-30 1952-06-30 Carba Ag Membrankammer
US2918933A (en) * 1952-11-14 1959-12-29 Oil Ct Tool Company Constant volume controls
US2875977A (en) * 1953-08-19 1959-03-03 Crane Co Diaphragm ballcock
GB795192A (en) * 1954-12-20 1958-05-21 Alexis Sobolev Improvements in and relating to valves for fluids
FR1155578A (fr) * 1956-07-06 1958-05-06 Le Clapet Hoerbiger Appareil de contrôle de débit
FR1181763A (fr) * 1957-08-29 1959-06-18 Fiordham Pressings Ltd Soc Perfectionnements apportés aux soupapes commandées par flotteur pour chasses d'eau et similaires
FR1187832A (fr) * 1957-09-09 1959-09-16 Cie Generale D Acetylene Robinet pour bouteilles de gaz comprimé
US3003743A (en) * 1958-12-22 1961-10-10 Concordia Maschinen & Elek Zit Valve with pressure balancing diaphragms
FR1227692A (fr) * 1959-06-17 1960-08-22 Perfectionnements aux robinets à membrane
GB895517A (en) * 1959-09-21 1962-05-02 Bendix Corp Fluid-flow control valve
US3180360A (en) * 1961-06-13 1965-04-27 Bertin Et Cie Soc Compensated valve
US3283767A (en) * 1963-05-31 1966-11-08 Ibm Jet fluid amplifier

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3642026A (en) * 1970-04-08 1972-02-15 Air Reduction Metering valve
US3680171A (en) * 1970-11-23 1972-08-01 Wright Products Hydraulic door closer
JPS51117332A (en) * 1975-03-26 1976-10-15 Canadian Patents Dev Fluid flow quantity regulating device
JPS6122194B2 (de) * 1975-03-26 1986-05-30 Kanadeian Patentsu Ando Dev Ltd
WO1990013859A1 (en) * 1989-05-05 1990-11-15 Framo Developments (Uk) Limited Multiphase process mixing and measuring system
US5135684A (en) * 1989-05-05 1992-08-04 Framo Development (Uk) Limited Multiphase process mixing and measuring system
US5413311A (en) * 1994-03-01 1995-05-09 Tescom Corporation Gas valve
WO1995023936A1 (en) * 1994-03-01 1995-09-08 Tescom Corporation Gas valve
DE19730035A1 (de) * 1997-07-14 1999-02-18 Troester Guenther Membranventil
DE19730035C2 (de) * 1997-07-14 1999-10-14 Guenther Troester Membranventil
CN102884348A (zh) * 2010-04-28 2013-01-16 中央硝子株式会社 卤素气体或卤素化合物气体的填充容器用阀
CN102884348B (zh) * 2010-04-28 2014-03-19 中央硝子株式会社 直接接触型隔膜阀及具有该隔膜阀的高压气体填充容器
AU2013315933B2 (en) * 2012-08-30 2017-09-07 Fisher Controls International Llc Valve body with improved lower flow cavity
EP2898204B1 (de) 2012-09-21 2018-11-28 United Technologies Corporation Schmierung einer flexiblen halterung für einen getriebeträger
US9863542B2 (en) 2013-02-01 2018-01-09 Swagelok Company Diaphragm valve with welded diaphragm seat carrier
US10315939B2 (en) 2013-02-01 2019-06-11 Swagelok Company Diaphragm valve with diaphragm seat carrier
US10843947B2 (en) 2013-02-01 2020-11-24 Swagelok Company Diaphragm valve with diaphragm seat carrier

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Publication number Publication date
DE1284648C2 (de) 1969-08-07
DE1284648B (de) 1968-12-05

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