US3657973A - High-pressure compressors and pumps - Google Patents

High-pressure compressors and pumps Download PDF

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Publication number
US3657973A
US3657973A US50395A US3657973DA US3657973A US 3657973 A US3657973 A US 3657973A US 50395 A US50395 A US 50395A US 3657973D A US3657973D A US 3657973DA US 3657973 A US3657973 A US 3657973A
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US
United States
Prior art keywords
piston
cylinder
compressor machine
machine according
cross
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
US50395A
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English (en)
Inventor
Hans Jorg Wahrenberger
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 US3657973A publication Critical patent/US3657973A/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
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
    • 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
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/12—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use to obtain high pressure
    • 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
    • F04B39/0005—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 adaptations of pistons
    • F04B39/0022—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 adaptations of pistons piston rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases
    • F02F2007/0097—Casings, e.g. crankcases for large diesel engines
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/901—Cryogenic pumps

Definitions

  • the invention has as its subject an arrangement for the axial longitudinal guiding of the piston of a high-pressure compressor machine within its working cylinder which allows the piston to be guided independently of the usual cross-head guide, and this is achieved by means of a lantern member connected to the frame of the crank drive and having a guide bore, coaxial with the bore of the working cylinder.
  • the outer end of the piston is received in the lantern member and is connected to a cross-head within the crank-drive frame by a resiliant connecting rod which is guided in the guide bore of the lantern member.
  • a principal object of the invention is an arrangement which permits the axial longitudinal guiding of the piston of such a machine independently of any cross-head guide.
  • the length of the piston subjected to pressure action at the end face is determined by the necessary space required for coupling to the cross-head, the overalllength of the cylinder packing elements, and the travel distance.
  • the pressure on the suction side may be extremely high, e.g., more than 1,000 atmospheres, even with a considerable delivery there are relatively small swept volumes and thus, with a given piston travel, slender pistons of relatively small diameter which are subjected to buckling stress, and this, taking into account the piston force resulting from the effective diameter and taking into account the permissible values for the buckling stress, limits the overall length of the piston which is axially mobile longitudinally in the cylinder bore.
  • This length limitation makes it necessary for the piston coupling for transmission of force to the cross-head to come to be situated in the end position of the, piston within the cylinder as near as possible to the pistonentry point of the working cylinder nearest the cross-head. This is achieved in the usual compressors operating with very high pressures by flange-connecting the working cylinder directly to the end face of the crank-drive frame.
  • the spacing of the cylinder connecting flange from the cross-head in this dead centre position in the direction of the cylinder is determined by the necessary space required for the piston coupling elements between the preliminary stuffing-box inserted at the cylinder end and the crosshead end face.
  • the slightest deviation of the piston axisfixed by the cross-head guide from the axis of the cylinder fixedly arranged on the drive frame can, more particularly when the occurrence of tilting movements of the cross-head in the cross-head guideway and as a result of transverse movements of the cross-head within the cross-head shoe clearance and as a result of the influence of uncontrollable thermal expansion, result in longitudinal movements of the piston within the cylinder bore which deviate from the cylinder axis, and thus cause a rapid wear on the piston sealing elements.
  • the compressed medium is a combustible gas
  • this inflow may give rise to serious explosions owing to the formation of a detonating gas mixture in the crank-drive housing.
  • the leakage gas may flow directly out into the compressor room, in which case the entire room is subjected to the risk of an explosion.
  • Compressors which have flanged working cylinders directly connected to the crank-drive frame and which have an axially longitudinally movable, hollow drilled guide piston inserted in the cross-head side end of the working cylinder.
  • the guide piston has a fixed abutment collar and is connected with the coupling at the crosshead by means of a union nut and a relatively short and of itself rigid joining element inserted into the bore of the guide piston and having cup shaped end faces on both sides.
  • a particular disadvantage in this arrangement is that in order to demount the piston, which at its rear end, for pressure against the joint element, comprises a securely arranged collar with a larger diameter than that of the piston, all the cylinder inner parts have to be taken out, and this requires a considerable amount of time. With this arrangement there is also the same disadvantages already mentioned hereinbefore as regards the possibility of entry of conveyed medium and cylinder lubricant into the interior of the drive frame if leakages occur in the sealing elements of the working cylinders.
  • a high-pressure compressor or pump (compressor machine) in accordance with the invention is characterised by an arrangement for the central guiding of the piston in a working cylinder according to which the working piston is received at its end face in a lantern member connected to a crank-drive frame, and the piston is connected releasably to a cross-head within the said frame by means of a resilient connecting rod guided in a guide bore within the lantern member which is coaxial with the piston bore of the working cylinder in the direction determined by the travel of a cross-head pivot pin member, and the construction of the lantern member is such as to obviate entry of the pumped medium into the interior of the crank-drive frame and also mixing of cylinder lubricant with drive lubricant in the event of leakage.
  • a frame-form cross-head 5 is given a reciprocating longitudinal movement on rotation of a crankshaft 3 through the agency of a connecting rod 4.
  • the lantern members 7, which are each provided with a guide cylinder 13, are securely connected to the drive frame 1 together with the working cylinders 17 which are arranged on the end connecting flanges 34 of the said lantern members, at two opposite end connecting flanges 33 of the said frame.
  • the direction-determining precise central position of the axis of the cylinder 17 and thus of the bores of cylinder liner l8 and the piston sealing elements 36 relatively to the guide axis of the cross-head pivot pin member 6 is precisely determined on the one hand by the centering in the housing bore 28 of the frame flange 33 and on the other hand by the centering of the cylinder 17 in the housing bore 27 on the end connecting flange 34 of the lantern member 7.
  • the interior of the lantern member 7 is sub-divided by a partition wall 21 into two chambers 29 and 30.
  • the chamber 29 at the side of the frame connecting flange 33 is at one side bounded by a cover 22 inserted centrally in the left-hand housing bore of the lantern and at the other side by the partition wall 21.
  • the partition wall 21 and the cover 22 are each provided, for the through passage of the connecting rod 10, with an axial bore for receiving rod sealing elements 23, of known type.
  • the chamber 29 communicates with the outside air by way of one or more apertures 24.
  • a connecting aperture 31 for discharging any lubricating oil which may collect is situated at the lowest point.
  • the chamber 30 is bounded at one side by the partition wall 21 and at the other side by the inner end face of the working cylinder 17 arranged centrally on the connecting flange 34.
  • the chamber 30 is provided above or laterally with one or more assembly apertures 25 which are adapted to be closed with covers 26 and which may be left open in the case of subjecting a non-volatile liquid to compression (construction in the form of a high-pressure pump).
  • assembly apertures 25 which are adapted to be closed with covers 26 and which may be left open in the case of subjecting a non-volatile liquid to compression (construction in the form of a high-pressure pump).
  • a connecting aperture 32 for discharging collecting lubricating oil from the cylinder 17.
  • a guide cylinder 13 Also arranged in the chamber 30, connected fast by means of the webs 8, is a guide cylinder 13 whose bore 9 for guiding purposes extends coaxially relatively to the housing bores of the sealing elements 23 inserted in the partition wall 21 and cover 22.
  • the cylinder 17 being concentric within the housing bore 27 at the connecting flange 34, the bore 9 is coaxial with the bores of the cylinder liner 18 and the piston sealing elements 36.
  • the guide piston 12 of the connecting rod 10 which serves as a connection between piston and cross-head 5, which guide piston is adapted to move longitudinally in the axial direction and is connected fast to the shank portion 11, is inserted in the guide bore 9.
  • the dimension of the solid or hollow-drilled shank portion 11, which is preferably made with a round cross-section, are such that under the full action of the pressure acting on the end face of the piston 15 it has sufficient resistance to lateral buckling and such elasticity that the lateral deviations of the shank part 11 occurring at the rod coupling 14 on longitudinal movement at the cross-head 5 can be accepted, while allowing axial longitudinal movement of the guide piston 12 in the bore 9.
  • the sealing elements 23 of known construction surrounding the shank portion 11 on the one hand the chamber 30 and on the other hand the interior of the drive frame 1 are effectively sealed relatively to the chamber 29 which is in direct communication with the outside air.
  • the sealing elements are so inserted that they can follow the lateral movements of the shank 11 when the latter moves longitudinally, while maintaining their sealing ability.
  • the chamber 30 is brought into communication(by means not shown) either with a low-pressure gas holder or, through a large gas discharge conduit, with the outside air.
  • the covers 26 can be provided, as an additional safety measure, with explosion valves in the constructional form known in large diesel engine construction (not shown). In this way the gas pressure in the chamber 30 can be kept very low, so that only extremely small gas traces can pass through the seal 23 into the machine room from the cylinders 17 even in the event of relatively large leakage losses.
  • the releasable connection of the piston 15 to the connecting rod 10 is effected with the coupling element 16 arranged centrally at the end of the guide piston 12.
  • the assembly apertures arranged at the lantern member 7 above the chamber are so dimensioned as to permit the coupling and uncoupling of the piston 15 and also the fitting and dismantling of the cylinder preliminary stuffing-box 20 inserted at the inner end of the cylinder 17.
  • a high-pressure piston compressor machine comprising a working cylinder, a working piston in said cylinder, means for centrally guiding said piston in said cylinder comprising a crank-drive frame, a lantern member connected to said frame receiving the end face of said piston, a cross-head having a cross-head pivot pin member within said frame, a resilient connecting rod releasably connecting said piston to said crosshead, said lantern member having a guide bore coaxial with the piston bore of said working cylinder for guiding said connecting rod in the direction determined by the travel of said cross-head pivot pin member, said lantern member comprising means to prevent entry of the pumped medium into the interior of said crank-drive frame and means to prevent mixing of cylinder lubricant with drive lubricant in the event of leakage.
  • a high-pressure piston compressor machine wherein said frame has a guideway for said cross-head and said connecting rod has an elastic shank portion to follow the axis deviations of said cross-head without prejudicing the axial position of said piston as determined by said guide bore.
  • a high-pressure piston compressor machine according to claim 1 wherein the cylinder-side end of said connecting rod comprises a guide piston longitudinally movable axially in said guide bore and a coupling connecting said guide piston and said connecting rod for the releasable connection of said piston.
  • a high-pressure piston compressor machine wherein a partition wall sub-divides the interior of said lantern member into two chambers, a closure cover on one of said chambers at the side of said drive frame and the other of said chambers being closed by the rear end of said working cylinder.
  • a high-pressure piston compressor machine according to claim 4, wherein one of said chambers has communication with the exterior.
  • a high-pressure piston compressor machine according to claim 5 wherein said chamber communicating with the exterior communicates through a venting device.
  • a high-pressure piston compressor machine according to claim 4, wherein said other chamber has at least one assembly aperture whose size is determined by the space required for operating said coupling.
  • a high-pressure piston compressor machine wherein said one chamber communicates with a lowpressure gas holder.
  • a high-pressure piston compressor machine according to claim 4 wherein said two chambers each have at the lowest point an aperture for the outflow of lubricant flowing into the respective chambers.
  • a high-pressure piston compressor machine according to claim 4 wherein said partition wall and said closure cover have coaxially arranged housing bores and sealing elements are arranged with lateral mobility in said bores for sealing said connecting rod passing therethrough.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US50395A 1969-06-30 1970-06-29 High-pressure compressors and pumps Expired - Lifetime US3657973A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH997769A CH511372A (de) 1969-06-30 1969-06-30 Einrichtung zur zentrischen Führung des Kolbens im Arbeitszylinder von Hochdruck-Kompressoren oder -Pumpen

Publications (1)

Publication Number Publication Date
US3657973A true US3657973A (en) 1972-04-25

Family

ID=4357761

Family Applications (1)

Application Number Title Priority Date Filing Date
US50395A Expired - Lifetime US3657973A (en) 1969-06-30 1970-06-29 High-pressure compressors and pumps

Country Status (6)

Country Link
US (1) US3657973A (https=)
BE (1) BE752684A (https=)
CH (1) CH511372A (https=)
FR (1) FR2051420A5 (https=)
GB (1) GB1310960A (https=)
NL (1) NL6914780A (https=)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040057842A1 (en) * 2002-09-25 2004-03-25 Hitachi Industries Co., Ltd. Reciprocating compressor
US11396868B2 (en) * 2020-03-09 2022-07-26 Schaeffler Technologies AG & Co. KG Linear actuator pumping system
US20230358226A1 (en) * 2022-05-09 2023-11-09 Hoerbiger Wien Gmbh Pressure packing for a reciprocating piston compressor with buffer gas barrier
CN117605648A (zh) * 2023-12-04 2024-02-27 浙江沃克制冷设备有限公司 一种制冷压缩机

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2198304C2 (ru) * 1999-07-15 2003-02-10 Московченко Александр Пантелеевич Двигатель внутреннего сгорания (варианты), цилиндропоршневая группа двигателя внутреннего сгорания, способ воспламенения воздушно-топливной смеси в двигателе внутреннего сгорания
CN102996400A (zh) * 2011-09-16 2013-03-27 固耐重工（苏州）有限公司 一种带直线导轨式活塞压缩机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1037840A (en) * 1906-08-23 1912-09-03 Power And Mining Machinery Company Reciprocating engine.
US2439958A (en) * 1943-10-21 1948-04-20 Air Prod Inc Pump for liquefied gases
US2440216A (en) * 1945-06-04 1948-04-20 Air Prod Inc Reciprocating pump for liquefied gases
US2933049A (en) * 1957-05-03 1960-04-19 Blue Co John Liquid fertilizer metering pump
FR1253173A (fr) * 1960-04-06 1961-02-03 Cooper Bessemer Corp Têtes de piston pour compresseurs ou pompes à fluide
US3391612A (en) * 1965-06-05 1968-07-09 Sneen Franz Piston sealing elements in hydraulic motors

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1037840A (en) * 1906-08-23 1912-09-03 Power And Mining Machinery Company Reciprocating engine.
US2439958A (en) * 1943-10-21 1948-04-20 Air Prod Inc Pump for liquefied gases
US2440216A (en) * 1945-06-04 1948-04-20 Air Prod Inc Reciprocating pump for liquefied gases
US2933049A (en) * 1957-05-03 1960-04-19 Blue Co John Liquid fertilizer metering pump
FR1253173A (fr) * 1960-04-06 1961-02-03 Cooper Bessemer Corp Têtes de piston pour compresseurs ou pompes à fluide
US3391612A (en) * 1965-06-05 1968-07-09 Sneen Franz Piston sealing elements in hydraulic motors

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040057842A1 (en) * 2002-09-25 2004-03-25 Hitachi Industries Co., Ltd. Reciprocating compressor
EP1403515A3 (en) * 2002-09-25 2005-01-26 Hitachi Industries Co., Ltd. Reciprocating compressor
US7052250B2 (en) 2002-09-25 2006-05-30 Hitachi Industries Co., Ltd. Reciprocating compressor
US11396868B2 (en) * 2020-03-09 2022-07-26 Schaeffler Technologies AG & Co. KG Linear actuator pumping system
US20230358226A1 (en) * 2022-05-09 2023-11-09 Hoerbiger Wien Gmbh Pressure packing for a reciprocating piston compressor with buffer gas barrier
US12435716B2 (en) * 2022-05-09 2025-10-07 Hoerbiger Wien Gmbh Pressure packing for a reciprocating piston compressor with buffer gas barrier
CN117605648A (zh) * 2023-12-04 2024-02-27 浙江沃克制冷设备有限公司 一种制冷压缩机
CN117605648B (zh) * 2023-12-04 2024-05-24 浙江沃克制冷设备有限公司 一种制冷压缩机

Also Published As

Publication number Publication date
FR2051420A5 (https=) 1971-04-02
NL6914780A (https=) 1971-01-04
GB1310960A (en) 1973-03-21
BE752684A (fr) 1970-12-01
CH511372A (de) 1971-08-15

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