EP3768973B1 - Hubkolbenverdichter mit verbesserter ventilzylinderanordnung - Google Patents

Hubkolbenverdichter mit verbesserter ventilzylinderanordnung Download PDF

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Publication number
EP3768973B1
EP3768973B1 EP18749679.9A EP18749679A EP3768973B1 EP 3768973 B1 EP3768973 B1 EP 3768973B1 EP 18749679 A EP18749679 A EP 18749679A EP 3768973 B1 EP3768973 B1 EP 3768973B1
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EP
European Patent Office
Prior art keywords
valve
reciprocating compressor
axially
cylinder
perimeter
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Application number
EP18749679.9A
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English (en)
French (fr)
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EP3768973A1 (de
Inventor
Scott J. DELMOTTE
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.)
Dresser Rand Co
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Dresser Rand Co
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    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block
    • 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
    • F04B39/14—Provisions for readily assembling or disassembling

Definitions

  • Disclosed embodiments are generally related to gas compressors, and, more particularly to reciprocating compressors cylinders having an improved valve assembly.
  • a reciprocating compressor includes a body or cylinder defining a compression chamber and a piston movably disposed within the cylinder chamber.
  • Linear reciprocating displacement of the piston within the chamber compresses gas (commonly referred to as "process" fluid or gas) located within the chamber, which is subsequently discharged at the increased pressure, such as by way of valves that may be respectively positioned upon respective valve seats constructed in the body (e.g., a wall) of the compressor cylinder that defines a compressor cylinder bore.
  • process gas
  • US 4,661,050 A describes a high-pressure gas transmission compressor having valve chambers incorporating valves located in common valve pockets where the center lines of the valve chambers are non-intersecting with the compressor cylinder.
  • US 2005/0229975 A1 describes a valve arrangement for a reciprocating machine, where the arrangement comprises an in-valve and an out-valve, each valve being a spring-loaded one-way valve designed to open for flow when the pressure differential in the direction of flow provides a force that exceeds the spring tension, wherein the valves are mounted in a casing that forms or is connected to the cylinder head of the reciprocating engine.
  • FIG. 1 is illustrative of one such prior art valve compressor design.
  • These prior art designs typically involve a compressor valve 100 positioned upon a feature 102 (e.g., a valve seat, indent, notch, etc.) constructed in a body 104 (e.g., a wall) of the compressor cylinder that defines a compressor cylinder bore 106.
  • a substantial magnitude of force is generally required from a valve cap 108 to hold the valve in place and resist the differential pressure (e.g., in certain applications this pressure can reach 10,000 psi and higher) that is formed between cylinder bore 106 and a valve passage 110.
  • Thick valve seats 102 constrained to the smallest size valve possible in a given implementation-- have been proposed to attempt to alleviate the stress concentration by limiting the surface area for the pressure to act upon.
  • Thick valve seats 102 constrained to the smallest size valve possible in a given implementation-- have been proposed to attempt to alleviate the stress concentration by limiting the surface area for the pressure to act upon.
  • FIGs. 2 and 3 respectively illustrate a fragmentary side view and a fragmentary end view of a reciprocating compressor 10 that can benefit from a disclosed valve assembly 20.
  • Reciprocating compressor 10 may comprise a cylinder block 12 including a cylinder that defines a cylindrical bore 14 extending longitudinally along a bore axis 16.
  • Cylinder block 12 includes a hollow chamber 15 ( FIG. 4 ) extending longitudinally along a chamber axis 18, which is non-intersecting relative to bore axis 16.
  • valve assembly 20 is disposed in hollow chamber 15.
  • valve assembly 20 comprises an axially-stacked arrangement of components extending along chamber axis 18.
  • the axially-stacked arrangement of components is spaced apart from a wall 22 that forms a perimeter of the cylinder, and thus is free from mechanical interference with the perimeter of the cylinder.
  • a pair of valve covers 24, 26 may be affixed via suitable affixing means 27 (e.g., bolts) to mutually opposed sides 28, 30 of cylinder block 12 to retain in axial compression within the hollow chamber the axially-stacked arrangement of components.
  • an inlet passageway 32 may be formed in cylinder block 12.
  • the axially-stacked arrangement of components includes a suction valve 34, as may be located downstream from a respective valve cage 36.
  • Suction valve 34 is in fluid communication with inlet passageway 32, (as schematically represented by arrows 37).
  • an outlet passageway 38 may also be formed in cylinder block 12.
  • the axially-stacked arrangement of components includes a discharge valve 40 as may be located upstream from a respective valve cage 42. Discharge valve 40 is in fluid communication with outlet passageway, (as schematically represented by arrows 43).
  • the axially-stacked arrangement of components includes a spacer 44 interposed between suction valve 34 and discharge valve 40.
  • a passageway 45 ( FIG. 3 ) is arranged in cylinder block 12 to provide fluid communication through spacer 44 between cylindrical bore 14 with suction valve 34 and discharge valve 40.
  • a perimeter fluid (e.g., gas) seal 46 ( FIG. 3 ) is disposed at a perimeter joint 47 between suction valve 34 and spacer 44.
  • a perimeter fluid seal 48 is disposed at a perimeter joint 50 between discharge valve 40 and spacer 44.
  • This seal arrangement is different than in the prior art design, which is commonly arranged to seal on the face of the valve.
  • high-pressure seal arrangements may include O-rings, Chevron seal arrangements, such as may involve composite metal/polymer Chevron sealing arrangements; non-metallic C-seals, T-seals, labyrinth seals; piston rings seals, etc.
  • the cylinder may comprise a double-action cylinder, and cylinder block 12, may include a further hollow chamber extending longitudinally along a further chamber axis 18' ( FIG. 2 ), which is non-intersecting relative to bore axis 16.
  • further chamber axis 18' is spaced apart from chamber axis 18 along bore axis 16.
  • Bore axis 16 and further chamber axis 18' may be mutually orthogonal axes.
  • a further valve assembly 20' may be disposed in the further hollow chamber.
  • the further valve assembly 20' may comprise a further axially-stacked arrangement of components extending along further chamber axis 18'.
  • the further axially-stacked arrangement of components is spaced apart from wall 22 that defines the perimeter of the cylinder and is thus free from mechanical interference with the perimeter of the cylinder.
  • a further pair of valve covers 24', 26' may be affixed to the mutually opposed sides 28, 30 of cylinder block 12 to retain in axial compression within the further hollow chamber the further axially-stacked arrangement of components.
  • valve assembly 20' includes a further suction valve 34', as may be located downstream from a respective valve cage 36'. Further suction valve 34' is in fluid communication with inlet passageway 32, (as schematically represented by arrows 37' ( FIG. 2 )).
  • the further axially-stacked arrangement of components that makes up valve assembly 20' includes a further discharge valve 40', as may be located upstream from a respective valve cage 42'. Further discharge valve 40' is in fluid communication with outlet passageway, (as schematically represented by arrows 43' FIG. 3 )).
  • the further axially-stacked arrangement of components includes a further spacer 44' interposed between further suction valve 34'and further discharge valve 40'.
  • a further passageway (analogous to passage way 45 in FIG. 3 )) is arranged to provide fluid communication through the further spacer 44' between cylindrical bore 14 with further suction valve 34' and further discharge valve 40'.
  • a further perimeter fluid seal 46' is disposed at a perimeter joint 47' between further suction valve 34' and further spacer 44'.
  • a further perimeter fluid seal 48' disposed at a perimeter joint 50' between the discharge valve 40' and further spacer 44'.
  • respective chamber axes 18 and 18' may be vertical axes and valve assemblies 20 and 20' may be vertically arranged.
  • chamber axes 18 and 18' may be in correspondence with a local gravity vector; and thus, in this case, mutually opposed sides 28, 30 of cylinder block 12 would define respective top and bottom sides of cylinder block 12.
  • valve assembly 20 extends horizontally along chamber axis 18, which in this example is horizontally positioned.
  • chamber axes 18 and 18' would be transverse with respect to a local gravity vector; and thus, in this case, mutually opposed sides 28, 30 of cylinder block 12 would define respective lateral sides of cylinder block 12.
  • Valve assembly 20' would be similarly positioned as valve assembly 20.
  • valve assembly 20' would view valve assembly 20' in the same manner that valve assembly is seen in FIG. 5 . It is contemplated that chamber axes 18 and 18' need not necessarily be vertically, or horizontally positioned, and, could be positioned at a respective angle in a range from -90° to 90° relative to the local gravity vector. Accordingly, without limitation, valve assemblies 20 and 20' may be arranged with a respective tilt angle relative to the local gravity vector. That is, at a respective angle in a range from -90° to 90° relative to the local gravity vector.
  • FIG. 6 and 7 illustrates respective side views of non-limiting examples of inlet passageway 32 or outlet passageway 38 as may be constructed in cylinder block 12.
  • at least respective portions of inlet passageway 32 or outlet passageway 38 may respectively comprise a respective angled arrangement, as shown in FIG. 6 .
  • at least respective portions of inlet passageway 32 or outlet passageway 38 may respectively comprise a T-shaped arrangement, as shown in FIG. 7 .
  • disclosed embodiments effectively provide an arrangement of individual components (e.g., respective valve cages 36, 42, respective valves such as suction valves 34 and discharge valves 40) loaded axially in compression with each other to form a self-supporting valve assembly.
  • individual components e.g., respective valve cages 36, 42, respective valves such as suction valves 34 and discharge valves 40
  • disclosed embodiments do not involve features in the cylinder wall for retaining any of the stacked components.
  • outlet passageway 38 may be located at the bottom of the cylinder (at a lower location relative to inlet passageway 32) to prevent (e.g., by way of gravity action) possible accumulation of liquids in the cylinder.
  • Communication of the gas to the external cylinder connections may be accomplished through the use of standard machined gas passages constructed using techniques well-understood to those skilled in the art.
  • FIGs. 2 and 3 illustrate the use of one axially-stacked valve assembly per end of a given double acting cylinder. It will be appreciated that other alternate embodiments may be realized depending on the needs of a given application. For example, one could arrange multiple assemblies on one or both ends of the compressor cylinder.
  • valve assembly relocates the valves (and associated components) to a location spaced apart from the cylinder.
  • this location is free from any mechanical interference or impingement with cylinder features, as would be the case in prior art designs that involve features (e.g., valve seat, notch, etc.) constructed in the body of the cylinder to support the valves.
  • the force necessary to hold the respective valves against the differential pressure of the cylinder is applied to a purely-axial stack of individual components, none of which impinge upon features in the cylinder wall that defines the cylinder bore.
  • the concept of features that define a valve seat constructed in the cylinder body is no longer applicable. Accordingly, the above-described pressure limitation of prior art cylinder designs resulting from the valve seat stresses is overcome.
  • the arrangement of axially-stacked valve assembly involves a pair of valve covers disposed at mutually opposed axial ends of the assembly. Thus, the anchoring of the axially-stacked valve assembly is fully independent from features in the body of the cylinder.
  • disclosed embodiments provide a cost-effective and reliable technical solution to solve a significant operational issue related to high pressure cylinder operation.
  • Disclosed embodiments are believed to be effective for reliably supplying relatively higher pressures in, for example, double-acting cylinders than have been achievable prior to the present invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Claims (16)

  1. Hubkolbenverdichter, umfassend:
    einen Zylinderblock (12), der einen Zylinder aufweist, welcher eine zylindrische Bohrung (14) definiert, die sich longitudinal entlang einer Bohrungsachse (16) erstreckt, wobei der Zylinderblock (12) eine hohle Kammer (15) aufweist, die sich longitudinal entlang der Kammerachse (18) erstreckt und die bezüglich der Bohrungsachse (16) nicht schneidend ist;
    eine Ventilanordnung (20), die in der hohlen Kammer (15) angeordnet ist, wobei die Ventilanordnung (20) eine axial gestapelte Anordnung von Komponenten umfasst, die sich entlang der Kammerachse (18) erstrecken, wobei die axial gestapelte Anordnung von Komponenten von einer Wand (22) beabstandet ist, die einen Umfang des Zylinders bildet, und somit frei von mechanischer Behinderung mit dem Umfang des Zylinders ist;
    einen Einlassdurchgang (32), der in dem Zylinderblock (12) gebildet ist, wobei die axial gestapelte Anordnung von Komponenten ein Saugventil (34) beinhaltet, das mit dem Einlassdurchgang (32) in fluidischer Verbindung steht;
    einen Auslassdurchgang (38), der in dem Zylinderblock (12) gebildet ist, wobei die axial gestapelte Anordnung von Komponenten ein Auslassventil (40) beinhaltet, das mit dem Auslassdurchgang (38) in fluidischer Verbindung steht;
    wobei die axial gestapelte Anordnung von Komponenten ein Abstandsstück (44) beinhaltet, das zwischen dem Saugventil (34) und dem Auslassventil (40) angeordnet ist; und
    dadurch gekennzeichnet, dass eine Umfangsfluiddichtung (46) an einer Umfangsverbindung (47) zwischen dem Saugventil (34) und dem Abstandsstück (44) angeordnet ist.
  2. Hubkolbenverdichter nach Anspruch 1, wobei die Bohrungsachse (16) und die Kammerachse (18) zueinander orthogonale Achsen sind.
  3. Hubkolbenverdichter nach Anspruch 1, ferner umfassend ein Paar Ventildeckel (24, 26), die an einander gegenüberliegenden Seiten (28, 30) des Zylinderblocks (12) befestigt sind, um die axial gestapelte Anordnung von Komponenten in der hohlen Kammer (15) unter axialem Druck festzuhalten.
  4. Hubkolbenverdichter nach Anspruch 1, ferner umfassend einen Durchgang (45), der dazu angeordnet ist, eine fluidische Verbindung durch das Abstandsstück (44) zwischen der zylindrischen Bohrung (14) mit dem Saugventil (34) und dem Auslassventil (40) bereitzustellen.
  5. Hubkolbenverdichter nach Anspruch 1, ferner umfassend eine Umfangsfluiddichtung (48), die an einer Umfangsverbindung (50) zwischen dem Auslassventil (40) und dem Abstandsstück (44) angeordnet ist.
  6. Hubkolbenverdichter nach Anspruch 1, wobei der Zylinder einen doppeltwirkenden Zylinder umfasst,
    wobei der Zylinderblock (12) eine weitere hohle Kammer aufweist, die sich longitudinal entlang einer weiteren Kammerachse (18') erstreckt, die bezüglich der Bohrungsachse (16) nicht schneidend ist, wobei die weitere Kammerachse (18') von der Kammerachse (18) entlang der Bohrungsachse (16) beabstandet ist.
  7. Hubkolbenverdichter nach Anspruch 6, umfassend eine weitere Ventilanordnung (20'), die in der weiteren hohlen Kammer angeordnet ist, wobei die weitere Ventilanordnung (20') eine weitere axial gestapelte Anordnung von Komponenten umfasst, die sich entlang der weiteren Kammerachse (18') erstrecken, wobei die weitere axial gestapelte Anordnung von Komponenten von der Wand (22) beabstandet ist, die den Umfang des Zylinders definiert, und somit frei von mechanischer Behinderung mit dem Umfang des Zylinders ist.
  8. Hubkolbenverdichter nach Anspruch 7, wobei die Bohrungsachse (16) und die weitere Kammerachse (18') zueinander orthogonale Achsen sind.
  9. Hubkolbenverdichter nach Anspruch 8, umfassend ein weiteres Paar von Ventildeckeln (24', 26'), die an den einander gegenüberliegenden Seiten des Zylinderblocks (12) befestigt sind, um die weitere axial gestapelte Anordnung von Komponenten in der weiteren hohlen Kammer unter axialem Druck festzuhalten.
  10. Hubkolbenverdichter nach Anspruch 6, umfassend einen Einlassdurchgang (32), der in dem Zylinderblock (12) gebildet ist, und wobei die Anordnung von weiteren axial gestapelten Komponenten ein weiteres Saugventil (34') beinhaltet, das mit dem Einlassdurchgang (32) in fluidischer Verbindung steht.
  11. Hubkolbenverdichter nach Anspruch 10, umfassend einen Auslassdurchgang (38), der in dem Zylinderblock (12) gebildet ist, und wobei die weitere axial gestapelte Anordnung von Komponenten ein weiteres Auslassventil (40') beinhaltet, das mit dem Auslassdurchgang (38) in fluidischer Verbindung steht.
  12. Hubkolbenverdichter nach Anspruch 1, wobei die weitere axial beabstandete Anordnung von Komponenten ein weiteres Abstandsstück (44') beinhaltet, das zwischen dem weiteren Saugventil (34') und dem weiteren Auslassventil (40') angeordnet ist.
  13. Hubkolbenverdichter nach Anspruch 11, einen weiteren Durchgang, der dazu angeordnet ist, eine fluidische Verbindung durch das weitere Abstandsstück (44') zwischen der zylindrischen Bohrung (14) mit dem weiteren Saugventil (34') und dem weiteren Auslassventil (40') bereitzustellen.
  14. Hubkolbenverdichter nach Anspruch 10, umfassend eine weitere Umfangsfluiddichtung (46'), die an einer Umfangsverbindung (47') zwischen dem weiteren Saugventil (34') und dem weiteren Abstandsstück (44') angeordnet ist.
  15. Hubkolbenverdichter nach Anspruch 11, ferner umfassend eine weitere Umfangsfluiddichtung (48'), die an einer Umfangsverbindung (50') zwischen dem weiteren Auslassventil (40') und dem weiteren Abstandsstück (44') angeordnet ist.
  16. Hubkolbenverdichter nach Anspruch 1, wobei die Ventilanordnung (20) mit einem jeweiligen Kippwinkel bezüglich eines lokalen Schwerkraftvektors angeordnet ist, wobei der Kippwinkel in einem Bereich von -90° bis 90° bezüglich des lokalen Schwerkraftvektors liegt.
EP18749679.9A 2018-04-25 2018-07-13 Hubkolbenverdichter mit verbesserter ventilzylinderanordnung Active EP3768973B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201862662329P 2018-04-25 2018-04-25
PCT/US2018/042007 WO2019209361A1 (en) 2018-04-25 2018-07-13 Reciprocating compressor with improved valve cylinder assembly

Publications (2)

Publication Number Publication Date
EP3768973A1 EP3768973A1 (de) 2021-01-27
EP3768973B1 true EP3768973B1 (de) 2022-08-24

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EP18749679.9A Active EP3768973B1 (de) 2018-04-25 2018-07-13 Hubkolbenverdichter mit verbesserter ventilzylinderanordnung

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EP (1) EP3768973B1 (de)
WO (1) WO2019209361A1 (de)

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US181168A (en) * 1876-08-15 Improvement in pump-valves
US2845085A (en) * 1955-12-12 1958-07-29 Tokheim Corp Separable, yieldable mounting for valves
US2962975A (en) * 1958-11-19 1960-12-06 George F Camp Fluid cylinder
DE1296007B (de) * 1962-07-26 1969-05-22 Pumpenfabrik Urach Kolbenpumpe, insbesondere Mehrzylinder-Hochdruckkolbenpumpe
US3679332A (en) * 1970-04-10 1972-07-25 Union Pump Co Reciprocating piston pump
US4661050A (en) * 1980-08-13 1987-04-28 Anglo Compression, Inc. High pressure gas transmission compressor
US4477236A (en) * 1982-04-29 1984-10-16 Elliott Robert E Liquid end structure for reciprocating pump
US5011383A (en) 1990-01-02 1991-04-30 Dresser-Rand Company Valve assembly, for use in combination with a straight-cylinder, gas-compression chamber, and in combination therewith
US5148828A (en) * 1991-03-29 1992-09-22 The Ford Meter Box Co., Inc. Check valve assembly
US5209647A (en) 1992-06-17 1993-05-11 Dresser-Rand Company Straight cylinder gas compressor with a reduced diameter compression chamber
US6220282B1 (en) * 1999-11-03 2001-04-24 Hunter Innovations, Inc. Backflow prevention apparatus
NO316090B1 (no) * 2002-03-21 2003-12-08 Nat Oilwell Norway As Anordning ved ventil for stempelmaskin så som pumpe og kompressor
US8826937B2 (en) * 2010-03-17 2014-09-09 Masco Canada Limited Flush valve anti-backflow cartridge
JP7245163B2 (ja) * 2017-01-17 2023-03-23 マイクロフルーイディクス インターナショナル コーポレイション 高圧デュアルチェックバルブを用いた装置及び方法
IT201800002995A1 (it) * 2018-02-23 2019-08-23 Comet Spa Pompa a pistoni con testata semplificata

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US20210079908A1 (en) 2021-03-18
EP3768973A1 (de) 2021-01-27

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