US3309014A - Coaxial suction and delivery valve arrangement for high pressure compressors and pumps - Google Patents

Coaxial suction and delivery valve arrangement for high pressure compressors and pumps Download PDF

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Publication number
US3309014A
US3309014A US478716A US47871665A US3309014A US 3309014 A US3309014 A US 3309014A US 478716 A US478716 A US 478716A US 47871665 A US47871665 A US 47871665A US 3309014 A US3309014 A US 3309014A
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United States
Prior art keywords
cylinder
suction
valve
pressure
high pressure
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
US478716A
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English (en)
Inventor
Bauer Helmut
Aesch Anton Leitgeb
Strebel Albert
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.)
Burckhardt Compression AG
Original Assignee
Maschinenfabrik Burckhardt AG
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 Maschinenfabrik Burckhardt AG filed Critical Maschinenfabrik Burckhardt AG
Application granted granted Critical
Publication of US3309014A publication Critical patent/US3309014A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125—Cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1013—Adaptations or arrangements of distribution members the members being of the poppet valve type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/102—Adaptations or arrangements of distribution members the members being disc valves
    • F04B39/1033—Adaptations or arrangements of distribution members the members being disc valves annular disc valves
    • 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
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/06—Check valves with guided rigid valve members with guided stems
    • F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
    • F16K15/066—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring with a plurality of valve members
    • 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
    • F16K2200/00—Details of valves
    • F16K2200/20—Common housing having a single inlet, a single outlet and multiple valve members
    • F16K2200/202—Common housing having a single inlet, a single outlet and multiple valve members one valve arranged inside of the valve member of a second valve, e.g. nested valve members
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7838—Plural
    • Y10T137/7841—One valve carries head and seat for second valve
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7859—Single head, plural ports in parallel
    • Y10T137/786—Concentric ports

Definitions

  • Such high pressure valve arrangements are known wherein a central body carrying the valve is provided with an axial channel or bore cooperating with the delivery valve and, round said axial channel or bore, with sloping channels leading to the suction valve. Said sloping channels connect an annular chamber inside which the suction pressure prevails and which surrounds the central body with the seat of the suction valve.
  • valves of such a type intended for pumps and compressors operating under service pressures which may reach several thousand atmospheres the material forming the different parts of the valve elements is subjected to stresses which are much higher than the stresses which are generally allowed in the execution of machines under conventional pressures.
  • the constant modifications in the value of the pressure during the suction and compression strokes produce, in particular in registry with the sharp ridges and acute angles in the fluid conveying channels in the valve arrangement, load peaks which may lead readily through excess straining to breakage. It is possible to reduce such stresses by suitably rounded connecting surfaces and by machining the sharp ridges, but it is impossible thus to cut out completely the stresses.
  • the present invention has for its object a coaxial suction and delivery valve arrangement operating under high pressures, wherein the detrimental action of the variations in stresses and consequently the shearing efforts, in particular as concerns the channels formed in the central body of the valve-carrying arrangement, are considerably reduced while the risk of breaking after a certain time is cut out to a large extent.
  • the outer periphery of the central body extending between the packing which is to make the central body fiuidtight with reference to the valve casing and the seat of the suction valve and including the sloping channels, is subjected to a constant suction pressure over a length substantially equal to the length of the central passage or channel subjected to the varying pressure prevailing in the cylinder.
  • the present invention also provides, according to a further advantageous feature, a reduction in the shearing action by giving the surface ensuring fluidtightness with the annular suction valve a part-spherical shape, whereas the bearing surface forming an extension of said spherical surface of the central body is urged under pressure against a ring constituted by a material having a high modulus of elasticity.
  • the arrangement illustrated forms an assembly of coaxial suction and delivery valves for high pressure compressors and pumps.
  • the fluid passes during the suction stroke of the piston into the cylinder bore 4 through the sloping channels 2 arranged in the central body 1, said channels2 being distributed round the axial channel 3.
  • the fluid passes through the axial channel 3 in the central body.
  • the fluid passing out of an annular chamber 5 formed in the valve casing subjected to the suction pressure and surrounding the central body 1, enters the sloping passages or channels 2 so as to reach the seat 7 of the member 8 forming the suction valve, following which the fluid passes over the latter and the stop 9 projecting into the bore 4 of the cylinder so as to reach finally the said bore 4.
  • the fluid to be compressed passes through the channel 3 into the central body 1, passes over the plate-shaped member 10 forming the delivery valve and reaches the annular chamber 11 beyond said valve, said annular chamber 11 being subjected to the compressor pressure.
  • the central body 1 By reason of the pressure prevailing in the annular chamber 11 and acting on the front surface 12 of the coaxial suction and delivery arrangement projecting into the annular chamber 11, the central body 1 is urged towards the front surface 6 of the inner ring 14 fitted inside the intermediate ring 13.
  • the front surface 6 and the cooperating surface of the body 1 engaging said surface 6 are machined in a manner such that the pressure acting in said central body allows obtaining fluidtightness.
  • an elastic member 16 as known per se.
  • the area of the central body 1, registering with the central channel 3 subjected to the variable pressure prevailing inside the cylinder and extending between the incurved surface 7 closing the annular body 8 forming the suction valve and the fluidtight surface on the member 10 forming the delivery valve, is sujected together with the oblique channels to a constant suction pressure over a length which is substantially equal to its outer'periphery between the packing 17 and the bearing surface 6.
  • the deformations of the ring 14 are reduced by reason of its high modulus of elasticity and the friction exerted on the bearing surface 6 also reduces the deformation of the adjacent area of the body 1.
  • the strain to which the central body 1 is subjected and which is proportional to the modifications in shape are reduced in conformity with Hookes law.
  • the fluidtig-ht seat surface 7 and the corresponding surface on the annular body 8 forming the suction valve are curvilinear.
  • the axes of the sloping channels vcoincide preferably with radii of said incurved surfaces so as to reduce the risk of shearing.
  • the pressure exerted on the bearing surface 6 and the higher modulus of elasticity of the ring 14 with reference to the modulus of the material forming the central body are such that the peaks of the stresses arising in registry with the incurved fluidtight surface 7 and ascribable to a shearing action, are reduced in a manner suflicient to cut out in practice any risk of a break.
  • a coaxial suction and delivery valve arrangement adapted to equip high pressure compressors and pumps valve and the surface fluidtightly engaging the delivery valve, is equal to the length of the axial channel subjected to the pressure prevailing inside the cylinder.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressor (AREA)
US478716A 1964-08-11 1965-08-10 Coaxial suction and delivery valve arrangement for high pressure compressors and pumps Expired - Lifetime US3309014A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH1049664A CH419755A (de) 1964-08-11 1964-08-11 Konzentrisches Saug- und Druckventil für Hochdruckkompressoren und -pumpen

Publications (1)

Publication Number Publication Date
US3309014A true US3309014A (en) 1967-03-14

Family

ID=4363838

Family Applications (1)

Application Number Title Priority Date Filing Date
US478716A Expired - Lifetime US3309014A (en) 1964-08-11 1965-08-10 Coaxial suction and delivery valve arrangement for high pressure compressors and pumps

Country Status (5)

Country Link
US (1) US3309014A (de)
CH (1) CH419755A (de)
DE (1) DE1985815U (de)
GB (1) GB1091324A (de)
NL (1) NL6510383A (de)

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3702624A (en) * 1968-09-17 1972-11-14 Pumpenfabrik Urach Piston pump
US4174194A (en) * 1976-07-12 1979-11-13 Paul Hammelmann Reciprocating pump
DE2824184A1 (de) * 1978-06-02 1979-12-06 Burghardt Vossen Ventilvorrichtung fuer hochdruckpumpen
US4239463A (en) * 1978-09-28 1980-12-16 Worthington Pump, Inc. Reciprocating plunger pump with improved liquid end valve assembly
US4313570A (en) * 1979-11-20 1982-02-02 Flow Industries, Inc. High pressure cutting nozzle with on-off capability
US4371001A (en) * 1977-10-31 1983-02-01 Flow Industries, Inc. Check valve assembly
US4412792A (en) * 1981-01-21 1983-11-01 The Oilgear Company Intensifier pump with integrated check valve
US4456440A (en) * 1981-03-25 1984-06-26 Uhde Gmbh Valve assembly for high-pressure pumps
US4616983A (en) * 1984-02-09 1986-10-14 Uraca Pumpenfabrik Gmbh & Co. Kg Piston or plunger pump
EP0398845A2 (de) * 1989-05-19 1990-11-22 Nti Jet Cutting Systems Ag Zylinderabschluss einer Höchstdruckpumpe
US5064354A (en) * 1990-06-04 1991-11-12 Robertson Walter W High pressure fluid pump
US5230363A (en) * 1991-04-10 1993-07-27 Dowell Schlumberger Incorporated Suction valve for high pressure slurry pump
US5411380A (en) * 1993-07-27 1995-05-02 Apv Gaulin, Inc. High pressure homogenizing pump having removable check valve modules
US5609477A (en) * 1993-03-12 1997-03-11 Forgesharp Limited Inlet/outlet valve arrangement for a fluid pressure intensifying apparatus
US5636975A (en) * 1994-04-04 1997-06-10 Reynolds Metals Company Inlet and discharge valve arrangement for a high pressure pump
US5904179A (en) * 1997-11-14 1999-05-18 Waterjet Service, Inc. Inlet check valve
US6021810A (en) * 1997-11-14 2000-02-08 Waterjet Service, Inc. Inlet check valve
US20040108000A1 (en) * 2002-12-06 2004-06-10 Flow International Corporation Ultrahigh-pressure check valve
US20050276712A1 (en) * 2004-06-15 2005-12-15 Waterjet Service, Inc. Inlet check valve with removable seat
US20070095405A1 (en) * 2004-06-09 2007-05-03 Uwe Nigrin Check valve
US20130121860A1 (en) * 2011-11-10 2013-05-16 Gene Bluhm Retrofit of a reciprocating compressor with a concentric valve
WO2021160797A1 (en) * 2020-02-12 2021-08-19 Maersk Container Industry A/S A flow guide for a reciprocating-type compressor of a cooling system and a reciprocating-type compressor for a cooling system comprising said flow guide
US20220243724A1 (en) * 2021-02-04 2022-08-04 Yantai Jereh Petroleum Equipment & Technologies Co., Ltd. Fluid splitter, fluid end and plunger pump
US20240003446A1 (en) * 2022-07-01 2024-01-04 Siemens Energy, Inc. Anti-spin outer diameter guided compressor valve

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1614851A (en) * 1924-10-16 1927-01-18 H J West And Company Ltd High-pressure gas compressor
US1719572A (en) * 1928-01-23 1929-07-02 Stoll Albert Valve construction for compressors and refrigerating pumps

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1614851A (en) * 1924-10-16 1927-01-18 H J West And Company Ltd High-pressure gas compressor
US1719572A (en) * 1928-01-23 1929-07-02 Stoll Albert Valve construction for compressors and refrigerating pumps

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3702624A (en) * 1968-09-17 1972-11-14 Pumpenfabrik Urach Piston pump
US4174194A (en) * 1976-07-12 1979-11-13 Paul Hammelmann Reciprocating pump
US4371001A (en) * 1977-10-31 1983-02-01 Flow Industries, Inc. Check valve assembly
DE2824184A1 (de) * 1978-06-02 1979-12-06 Burghardt Vossen Ventilvorrichtung fuer hochdruckpumpen
US4239463A (en) * 1978-09-28 1980-12-16 Worthington Pump, Inc. Reciprocating plunger pump with improved liquid end valve assembly
US4313570A (en) * 1979-11-20 1982-02-02 Flow Industries, Inc. High pressure cutting nozzle with on-off capability
US4412792A (en) * 1981-01-21 1983-11-01 The Oilgear Company Intensifier pump with integrated check valve
US4456440A (en) * 1981-03-25 1984-06-26 Uhde Gmbh Valve assembly for high-pressure pumps
US4616983A (en) * 1984-02-09 1986-10-14 Uraca Pumpenfabrik Gmbh & Co. Kg Piston or plunger pump
EP0398845A2 (de) * 1989-05-19 1990-11-22 Nti Jet Cutting Systems Ag Zylinderabschluss einer Höchstdruckpumpe
EP0398845A3 (de) * 1989-05-19 1991-07-31 Nti Jet Cutting Systems Ag Zylinderabschluss einer Höchstdruckpumpe
US5064354A (en) * 1990-06-04 1991-11-12 Robertson Walter W High pressure fluid pump
US5230363A (en) * 1991-04-10 1993-07-27 Dowell Schlumberger Incorporated Suction valve for high pressure slurry pump
US5609477A (en) * 1993-03-12 1997-03-11 Forgesharp Limited Inlet/outlet valve arrangement for a fluid pressure intensifying apparatus
US5411380A (en) * 1993-07-27 1995-05-02 Apv Gaulin, Inc. High pressure homogenizing pump having removable check valve modules
US5636975A (en) * 1994-04-04 1997-06-10 Reynolds Metals Company Inlet and discharge valve arrangement for a high pressure pump
US5904179A (en) * 1997-11-14 1999-05-18 Waterjet Service, Inc. Inlet check valve
US6021810A (en) * 1997-11-14 2000-02-08 Waterjet Service, Inc. Inlet check valve
US20040108000A1 (en) * 2002-12-06 2004-06-10 Flow International Corporation Ultrahigh-pressure check valve
US20070095405A1 (en) * 2004-06-09 2007-05-03 Uwe Nigrin Check valve
US20050276712A1 (en) * 2004-06-15 2005-12-15 Waterjet Service, Inc. Inlet check valve with removable seat
US7278838B2 (en) 2004-06-15 2007-10-09 Waterjet Service, Inc. Inlet check valve with removable seat
US20130121860A1 (en) * 2011-11-10 2013-05-16 Gene Bluhm Retrofit of a reciprocating compressor with a concentric valve
WO2021160797A1 (en) * 2020-02-12 2021-08-19 Maersk Container Industry A/S A flow guide for a reciprocating-type compressor of a cooling system and a reciprocating-type compressor for a cooling system comprising said flow guide
US20220243724A1 (en) * 2021-02-04 2022-08-04 Yantai Jereh Petroleum Equipment & Technologies Co., Ltd. Fluid splitter, fluid end and plunger pump
US11867171B2 (en) * 2021-02-04 2024-01-09 Yantai Jereh Petroleum Equipment & Technologies Co., Ltd. Fluid splitter in a fluid end or plunger pump
US20240003446A1 (en) * 2022-07-01 2024-01-04 Siemens Energy, Inc. Anti-spin outer diameter guided compressor valve
US11913556B2 (en) * 2022-07-01 2024-02-27 Siemens Energy, Inc. Anti-spin outer diameter guided compressor valve

Also Published As

Publication number Publication date
NL6510383A (de) 1966-02-14
CH419755A (de) 1966-08-31
GB1091324A (en) 1967-11-15
DE1985815U (de) 1968-05-22

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