EP3502475A2 - Hubkolbenverdichter und herstellungsverfahren - Google Patents

Hubkolbenverdichter und herstellungsverfahren Download PDF

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Publication number
EP3502475A2
EP3502475A2 EP18212273.9A EP18212273A EP3502475A2 EP 3502475 A2 EP3502475 A2 EP 3502475A2 EP 18212273 A EP18212273 A EP 18212273A EP 3502475 A2 EP3502475 A2 EP 3502475A2
Authority
EP
European Patent Office
Prior art keywords
gas
valve seat
suction
delivery
compressor
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.)
Granted
Application number
EP18212273.9A
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English (en)
French (fr)
Other versions
EP3502475A3 (de
EP3502475B1 (de
Inventor
Federico Cappelli
Gianni ORSI
Paolo Acciai
Federico SORGONA
Alberto Babbini
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.)
Nuovo Pignone Technologie SRL
Original Assignee
Nuovo Pignone Technologie SRL
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Application filed by Nuovo Pignone Technologie SRL filed Critical Nuovo Pignone Technologie SRL
Publication of EP3502475A2 publication Critical patent/EP3502475A2/de
Publication of EP3502475A3 publication Critical patent/EP3502475A3/de
Application granted granted Critical
Publication of EP3502475B1 publication Critical patent/EP3502475B1/de
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Anticipated expiration legal-status Critical

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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
    • F04B39/122—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
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/064—Cooling by a cooling jacket in the pump casing
    • 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
    • F04B39/123—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
    • 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
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0072—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes characterised by assembly or mounting
    • 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

Definitions

  • the subject matter disclosed herein generally relates to compressors and more specifically to reciprocating compressors.
  • embodiments of the present disclosure concern double-acting reciprocating compressors.
  • Reciprocating compressors are used in several industrial fields for compressing a gas, in particular when relatively small gas flow rates require to be compressed with a high compression ratio.
  • a reciprocating compressor comprises a compressor cylinder forming a cylinder chamber therein.
  • a piston is arranged in the cylinder chamber and is driven into reciprocating motion by a prime mover, such as an electric motor, a turbine or a reciprocating internal or external combustion engine, such as a Stirling engine.
  • a crankshaft and a connecting rod mechanism converts the rotary motion of a motor shaft into reciprocating motion of the piston.
  • the connecting rod is usually drivingly coupled to the piston through a cross-head and a piston rod.
  • a valve arrangement provides for gas delivery into the cylinder chamber and gas discharge from the cylinder chamber.
  • the piston divides the cylinder chamber into a first compression chamber and a second compression chamber. At least one suction valve and one delivery valve are fluidly coupled to the first compression chamber, and at least a further suction valve and a further delivery valve are fluidly coupled to the second compression chamber.
  • the reciprocating motion of the piston in the cylinder chamber causes gas to be sucked in one of the compression chambers through the respective suction valve, while gas is compressed in the other compression chamber and discharged through the respective delivery valve, when a delivery pressure is achieved at which the delivery valve is opened.
  • Suction valves and delivery valves are usually automatic valves, which automatically open and close in response to a pressure differential thereacross.
  • the suction valves are fluidly coupled to an inlet plenum, which feeds gas at a lower pressure to the cylinder chamber.
  • the delivery valves are in turn fluidly coupled to a discharge plenum, which collects gas at a higher pressure from the cylinder chamber.
  • Fig.1 illustrates a double-acting reciprocating compressor 100 of the current art.
  • the compressor 100 comprises a compressor head 101, a compressor frame 102 and a distance piece 103, which connects the compressor head 101 to the compressor frame 102.
  • a crankshaft 104 is arranged in the compressor frame 102.
  • the crankshaft 104 rotates around a rotation axis 106.
  • a prime mover not shown, drives the crankshaft 104 into rotation.
  • a connecting rod 108 transmits the motion from the crankshaft 104 to a crosshead 110, which moves reciprocatingly in a crosshead guide 112.
  • a piston rod 114 connects the crosshead 110 to a piston 116, which is adapted to reciprocatingly slide in a chamber 118 of a compressor cylinder 120.
  • the piston 116 divides the chamber 118 in a first compression chamber and a second compression chamber.
  • the first and second compression chambers can be a head-end chamber 118A, and a crank-end chamber 118B.
  • a process gas is selectively sucked into each one of said head-end and crank-end chambers 118A, 118B at a lower pressure (suction pressure), compressed and discharged at a higher pressure (delivery pressure).
  • Said head-end chamber 118A and crank-end chamber 118B are provided each with at least one suction valve and one delivery valve. The suction, compression and discharge process is performed alternatively in the two chambers, i.e. when gas is sucked into one of the head-end chamber 118A and crank-end chamber 118B, gas in the other of said head-end chamber 118A and crank-end chamber 118B is compressed and discharged.
  • Suction valves 122 of both crank-end chamber 118B and head-end chamber 118A are fluidly coupled to an inlet plenum 126, which is in turn fluidly coupled to a gas source 128.
  • Delivery valves 124 of both crank-end chamber 118B and head-end chamber 118A are fluidly coupled to a discharge plenum 130, which is in turn fluidly coupled to a gas output 134.
  • the inlet plenum 126 and the discharge plenum 130 are both formed in a barrel 132, which in turn forms a cylindrical side wall of the chamber 118.
  • the gaseous flow through the inlet plenum 126 and the discharge plenum 130 and respective suction valves and delivery valves is complex and involves sharp bends due to the position of the valves in respective valve seats formed in the barrel 132. Specifically, gas enters the valve seats in a direction orthogonal to the axial direction of the valves, such that the gas flow turns by 90° when flowing from the inlet plenum into the suction valves and when flowing from the delivery valves into the discharge plenum.
  • Cooling ducts 136 are further provided in the barrel 132.
  • the shape of the inlet plenum and discharge plenum is restricted by the structure of the barrel. Mechanical constraints result in suboptimal fluid-dynamic design of the gas inlet and discharge plenums, which in turn causes fluid-dynamic losses and reduction of the overall efficiency of the compressor.
  • cooling of the compressor head is inefficient and manufacturing of the cooling ducts is rendered complicated by the combined presence of valve seats, plenums and cooling arrangements in the barrel.
  • GB1367164 discloses a double acting reciprocating compressor, wherein both the crank-end chamber and the head-end chamber of the compressor are provided with multiple suction valves and discharge valves.
  • the suction valves connecting the low-pressure gas source to the respective chamber are connected to one another by a suction plenum which surrounds annularly the compressor barrel.
  • the discharge valves connecting the high-pressure gas source to the respective chamber of the compressor are fluidly coupled to one another by a discharge plenum which annularly surrounds the compressor barrel.
  • CN104747405 discloses a double-acting reciprocating compressor, wherein each one of the crank-end chamber and head-end chamber of the compressor is provided with two suction valves and two discharge valves, respectively.
  • the pair of suction valves associated to the crank-end chamber are fluidly coupled to a respective suction plenum.
  • the two plenums connected to the suction valves of the head-end chamber and crank-end chamber are in turn coupled to a suction duct.
  • the two plenums connected to the discharge valves of the head-end chamber and crank-end chamber are in turn coupled to a discharge duct.
  • the present disclosure concerns a manufacturing method for manufacturing a cylinder for a reciprocating compressor.
  • the method comprises a step of manufacturing a compressor barrel comprised of a cylinder chamber, a first suction valve seat, fluidly coupled to the cylinder chamber through a respective first gas suction port; and a first delivery valve seat, fluidly coupled to the cylinder chamber through a respective first gas delivery port.
  • the method further comprises the step of manufacturing by additive manufacturing a gas inlet plenum and further manufacturing by additive manufacturing a gas discharge plenum, separately from the compressor barrel.
  • the gas inlet plenum and the gas discharge plenum can be attached around the compressor barrel in fluid communication with the gas suction port and the gas delivery port.
  • the gas inlet plenum and the gas discharge plenum can thus be designed according to optimization criteria, to minimize the gas pressure losses along the gas path, without being subjected to mechanical constraints imposed by the shape of the compressor barrel.
  • a manufacturing method for manufacturing a cylinder for a reciprocating compressor comprises the following steps:
  • a reciprocating compressor comprising a compressor barrel with a cylinder chamber therein and a piston, adapted for reciprocatingly sliding in the cylinder chamber.
  • the compressor further comprises a first suction valve fluidly coupled to the cylinder chamber and a first delivery valve fluidly coupled to the cylinder chamber.
  • the compressor comprises a gas inlet plenum fluidly coupled to the first suction valve and a gas discharge plenum fluidly coupled to the first delivery valve.
  • the gas inlet plenum and the gas discharge plenum are produced by additive manufacturing and are mechanically connected to the compressor barrel and external thereto.
  • the exemplary reciprocating compressors disclosed herein alleviate or solve the drawbacks and limitations of the prior art by separating the gas inlet plenum and gas discharge plenum from the compressor barrel.
  • the design of both the gas inlet plenum and the gas discharge plenum can thus be optimized from a fluid-dynamic and acoustic perspective, since less mechanical constraints are present.
  • the shape of the inlet plenum and discharge plenum do not have to conform to the shape of the barrel, the cooling ducts and valve seats housed therein.
  • the orientation of the inlet plenum and discharge plenum with respect to the position of the suction valves and delivery valves can be optimized. More space is available in the wall of the barrel to accommodate the valve seats and the cooling ducts. Also the shape of the cooling ducts can be ameliorated from the point of view of heat exchange efficiency, as well as from the point of view of machining.
  • the barrel can be more easily manufactured and less expensive production techniques, rather than iron or steel casting, can be used.
  • the barrel can be manufactured by forging or centrifugal casting, which makes the overall manufacturing process quicker, less expensive and less prone to generate scraps.
  • gas inlet plenum and gas discharge plenum are produced by additive manufacturing, optimal design can be achieved, which result in reduction of fluid-dynamic losses in the inlet and discharge gas flows.
  • compressor structure and the manufacturing processes disclosed herein can be beneficial also for the production of single-acting reciprocating compressors, they are particularly beneficial for the production of double-acting reciprocating compressors, where the shape of the gas inlet plenum and gas discharge plenum is particularly complex due to the higher number of suction valves and delivery valves provided at both ends of the compressor barrel.
  • a double-acting reciprocating compressor comprises a cylinder comprised of a compressor barrel and a cylinder chamber formed in the barrel.
  • the cylinder chamber is divided in a so-called head-end chamber and a so-called crank-end chamber by a piston, arranged for reciprocatingly sliding therein.
  • the head-end chamber is fluidly coupled to a first suction valve through a first gas suction port and to a first delivery valve through a first gas delivery port.
  • the crank-end chamber is fluidly coupled to a second suction valve through a second gas suction port and to a second delivery valve through a second gas delivery port.
  • the double-acting reciprocating compressor is adapted to suck gas in one of the crank-end chamber and head-end chamber through the respective suction valve, while gas is compressed in the other of the crank-end chamber and head-end chamber and finally delivered through the respective delivery valve.
  • Each crank-end chamber and head-end chamber can be fluidly coupled to more than one suction valve and one delivery valve.
  • two respective suction valves and two respective delivery valves can be fluidly coupled to each one of said head-end chamber and crank-end chamber, to maximize gas flow and minimize head losses.
  • All suction valves can be fluidly coupled to a single gas inlet plenum. All delivery valves can be fluidly coupled to a single gas discharge plenum.
  • each suction valve and delivery valve is fluidly coupled to a central portion or volume of the respective plenum by an independent, i.e. separate duct.
  • Each duct can be designed independently of the other ducts of the respective plenum, for optimal fluid-dynamic performance and improved acoustic behavior, i.e. reduced pressure waves in the duct. While in some reciprocating compressors of the current art this achieved, for instance, by providing resonators coupled to each valve, which introduce fluid-dynamic losses in the gas flow, designing each duct separately from the other achieves improvements in acoustic conditions in the gas flow, without negatively affecting the fluid-dynamic efficiency of the compressor.
  • the suction valves and the delivery valves can be automatic valves, which open and close responsive to a pressure difference thereacross.
  • the piston can be connected to a rotary crankshaft trough a connecting rod.
  • Large reciprocating compressors, especially double-acting reciprocating compressors as disclosed herein are further provided with a piston rod and a crosshead.
  • the piston, the piston rod and the cross-head are controlled according to a reciprocating rectilinear motion imparted to the crosshead by the rotary crankshaft and the connecting rod.
  • Fig.2 illustrates a schematic sectional view of a cylinder and relevant components of a double-acting reciprocating compressor 1 according to the present disclosure in one embodiment.
  • the section is taken along the axis of the reciprocating compressor cylinder.
  • the compressor 1 can comprise a compressor head 3, a compressor frame 5 and a distance piece 7, which connects the compressor head 3 to the compressor frame 5.
  • the compressor head 3 contains the compression chamber, as will be described below.
  • a crankshaft 9 is arranged in the compressor frame 5 for rotation around a shaft axis 9A.
  • a prime mover not shown, drives the crankshaft 9 into rotation around the axis 9A.
  • the prime mover can be a reciprocating internal combustion engine, such as a Diesel engine. In other embodiments, the prime mover can be a reciprocating external combustion engine, such as a Stirling engine.
  • the reciprocating compressor 1 can also be driven by a gas turbine engine, by a steam turbine, or by an electric motor, for instance.
  • a connecting rod 11 connects the crankshaft 9 to a crosshead 13.
  • the crosshead 13 is guided along cross-head guides 15 housed in the frame 5.
  • the rotation motion of the crankshaft 9 (arrow f9) is thus converted into a reciprocating motion of the crosshead 13 (arrow f13).
  • a piston rod 17 connects the crosshead 13 to a piston 19, which is adapted to reciprocatingly slide in a chamber 21 of a compressor barrel 18.
  • the piston 19 divides the chamber 21 in two compression chambers, namely a head-end chamber 21A, and a crank-end chamber 21B.
  • One or more respective suction valves are provided to fluidly connect the head-end chamber 21A and the crank-end chamber 21B selectively with a gas inlet plenum 20.
  • One or more respective delivery valves are further provided to fluidly connect the head-end chamber 21A and the crank-end chamber 21B selectively with a gas discharge plenum 22.
  • the gas inlet plenum 20 is fluidly coupled to a low-pressure gas source 31, and the gas discharge plenum 22 is fluidly coupled to a high-pressure gas source 33.
  • a single gas suction valve for each chamber 21A, 21B and a single gas delivery valve for each chamber 21A, 21B are visible.
  • a plurality of such gas suction valves and gas delivery valves can be provided for each one of said head-end chamber 21A and crank-end chamber 21B.
  • a first gas suction valve 23A is shown for fluidly connecting the head-end chamber 21A with the gas inlet plenum 22 and a second gas suction valve 23B is shown for fluidly connecting the crank-end chamber 21B to the gas inlet plenum 22.
  • a first gas delivery valve 25A is provided for fluidly connecting the head-end chamber 21A with the gas discharge plenum 25 and a second gas delivery valve 25B is shown for fluidly connecting the crank-end chamber 21B to the gas discharge plenum 22.
  • a total of four gas valves namely two gas suction valves and two gas delivery valves, are shown in fluid communication with the head-end side chamber 21A.
  • a similar arrangement is provided for the crank-end chamber 21B.
  • valves can be provided for each chamber.
  • the gas suction valves 23A, 23B and the gas delivery valves 25A, 25B can be automatic valves, i.e. valves which automatically open and close in response to a pressure differential thereacross.
  • the reciprocating motion of the piston 19 according to double arrow f19 causes gas to be sucked through gas suction valves 23A, 23B from the gas inlet plenum 20 in the head-end chamber 21A and in the crank-end chamber 21B, selectively. Simultaneously, gas is compressed is selectively compressed in the crank-end chamber 21B and in the head-end chamber 21A and discharged through the gas delivery valves 25B, 25A in the discharge plenum 22.
  • the gas suction valves 23A, 23B and the gas delivery valves 25A, 25B can be housed in respective valve seats schematically shown at 27A, 27B for the gas suction valves 23A, 23B and at 29A, 29B for the gas delivery valves 25A, 25B, see also Fig.3 .
  • the valve seats 27A, 27B are in fluid communication with the respective head-end chamber 21A and crank-end chamber 21B through respective gas suction ports 30 ( Fig.3 ).
  • the valve seats 29A, 29B are in fluid communication with the respective head-end chamber 21A and crank-end chamber 21B through respective gas delivery ports 32 ( Fig.3 ).
  • valve seats 27A, 27B and 29A, 29B are arranged in the compressor barrel 18, develop along the thickness thereof and have respective gas inlet apertures 34 and gas outlet apertures 36 on the outer surface of compressor barrel 18.
  • the gas inlet plenum 20 and the gas discharge plenum 22 are mounted on the outer surface of the compressor barrel 18.
  • the gas inlet plenum 20 can be provided with a total number of gas inlet ducts 20A equal to the total number of suction valves 23A, 23B of the compressor head 3.
  • the separate and independent gas ducts 20A depart from a central volume 20B of the gas inlet plenum 20 and extend to the compressor barrel 18, and more specifically towards the relevant suction valves 23A, 23B of both the crank-end and head-end of the compressor.
  • the separate suction ducts 20A provide independent fluid coupling between the central common volume 20B and each suction valve 23A, 23B at both the crank-end side and head-end side of the reciprocating compressor.
  • the gas discharge plenum 22 can in turn be comprised of a total number of gas ducts 22A equal to the total number of delivery valves 25B of the compressor head 3.
  • the separate and independent gas discharge ducts 22A depart from the barrel 18, and more specifically from the respective discharge valves of both the crank-end and head-end of the compressor, and extend towards a central volume 22B of the discharge plenum 22.
  • the separate discharge ducts 22A provide independent fluid coupling between the central common volume 22B and each delivery valve 25A, 25B at both the crank-end side and head-end side of the reciprocating compressor.
  • each separate duct 20A and 22A can be designed and dimensioned independently of the other ducts. It is thus possible to ameliorate the fluid flow conditions and reduce fluid-dynamic losses for each valve and thus improve the overall efficiency of the compressor.
  • the arrangement of the gas ports and apertures of the gas discharge plenum 22, the gas inlet plenum 20 and the valve seats 27A, 27B, 29A, 29B is such that gas flows in a substantially axial direction from the gas outlet 20A of the gas inlet plenum 20 towards and through the valve seats 27A, 27B and the respective gas suction valves 23A, 23B. Moreover, the gas flows in a substantially axial direction through the gas delivery valves 25A, 25B, the valve seats 29A, 29B towards the gas ports 22A of the gas discharge plenum 22.
  • axial direction as used herein can be understood as a direction substantially parallel to an axial extension of the gas suction valves 23A, 23B and gas delivery valves 25A, 25B, along which the gas flows through the respective valves.
  • the gas inlet plenum 20 and the gas discharge plenum 22 By arranging the gas inlet plenum 20 and the gas discharge plenum 22 outside the barrel 18, the gas flow is optimized, since no sharp 90° bent is required for the gas upon entering the valve seats.
  • the gas inlet plenum 20 and the gas discharge plenum 22 can be designed with a higher degree of freedom, as they do not require to be housed in the reduced space available within the thickness of the compressor barrel, as in the reciprocating compressors of the current art.
  • the shape of the inner gas passages in the gas inlet plenum 20 and gas discharge plenum 22 can be optimized for reduced pressure losses.
  • the barrel 18 can have a simple cylindrical shape, and can be obtained by forging or centrifugal casting.
  • the valve seats 27A, 27B and 29A, 29B can be produced by simple machining through the cylindrical wall of the semi-finished barrel 18.
  • cooling ducts 38 can be provided in the semi-finished barrel 18.
  • the cooling ducts 38 extend parallel to the barrel axis, i.e. parallel to the direction of the reciprocating motion of the piston 19 in the chamber 21, as shown in Fig. 3 . Machining of the cooling ducts 38 is simple and inexpensive, if compared to the manufacturing of complex cooling ducts in the barrels of the current art.
  • valve seats 27A, 27B, 29A, 29B and/or the cooling ducts 38 can be produced during casting.
  • the cooling ducts and/or the valve seats are produced by chip-removal machining.
  • the gas inlet plenum, or the gas discharge plenum or both are manufactured by additive manufacturing.
  • This manufacturing technique allows the production of components having a complex shape at low cost.
  • the shape of the gas flow paths inside the gas inlet plenum and the gas discharge plenum can be designed such as to achieve optimum flow conditions and minimize losses.
  • Additive manufacturing allows production of flow ducts of substantially any shape, no matter how complex they are.
  • the additive manufacturing process can be selected from the group comprising: Selective Laser Sintering (SLS), Powder bed fusion (PBF), Selective Laser Melting (SLM), Direct Metal Laser Sintering (DMLS), Electron Beam Melting (EBM), Multi Jet Fusion (MJF).
  • Both the gas inlet plenum and the gas discharge plenum can be manufactured as a single, monolithic piece of machinery, without the need for connecting to one another two or more elements, e.g. by soldering, welding, screwing or the like.
  • the resulting single-piece monolithic plenum meets higher quality standards. Production of scraps or defective components is prevented or limited. The manufacturing process is faster and requires less manufacturing skill.
  • the gas inlet plenum 20 and the gas discharge plenum 22 can be mounted around the compressor barrel 18 and coupled thereto by any suitable means.
  • connecting flanges 34A, 36A can be provided around each inlet aperture 34 and each outlet aperture 36.
  • the flanges can be connected to the compressor barrel 18 e.g. by means of screws, such that the gas inlet plenum and the gas discharge plenum can be easily disassembled from the compressor barrel 18, e.g. in order to repair or replace the suction valves and delivery valves, as required.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP18212273.9A 2017-12-19 2018-12-13 Hubkolbenverdichter und herstellungsverfahren Active EP3502475B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT201700146286 2017-12-19
IT201800010538 2018-11-23

Publications (3)

Publication Number Publication Date
EP3502475A2 true EP3502475A2 (de) 2019-06-26
EP3502475A3 EP3502475A3 (de) 2019-10-16
EP3502475B1 EP3502475B1 (de) 2022-02-23

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT527367A1 (de) * 2023-06-20 2025-01-15 Hoerbiger Wien Gmbh Kontaktlos dichtender Kolben mit Kolbenstange
AT527368A1 (de) * 2023-06-20 2025-01-15 Hoerbiger Wien Gmbh Kontaktlos dichtender Kolben mit Kolbenstange

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Publication number Priority date Publication date Assignee Title
US1791364A (en) * 1929-06-10 1931-02-03 James O Lewis Compressor cylinder
US1998264A (en) * 1932-07-30 1935-04-16 Westinghouse Air Brake Co Compressor
GB555944A (en) * 1941-04-10 1943-09-14 Sulzer Ag Improvements in or relating to air or gas pumps of the reciprocating type
DE2150035A1 (de) * 1970-10-13 1972-04-20 Frenkel Mark Isaakovich Zylinder fuer Hubkolbenverdichter
US4006602A (en) * 1974-08-05 1977-02-08 Fanberg Ralph Z Refrigeration apparatus and method
CN202926543U (zh) * 2012-12-08 2013-05-08 孙继辉 双向进气出气打气筒
US20160341188A1 (en) * 2014-01-31 2016-11-24 Nuovo Pignone Srl A compressed natural gas system and method
DE112015000585T5 (de) * 2014-01-31 2016-11-03 Nuovo Pignone S.R.L. Hubkolben-Motorverdichter mit integriertem Stirlingmotor
US9546660B2 (en) * 2014-06-02 2017-01-17 Ingersoll-Rand Company Compressor system with resonator
CN104747405B (zh) * 2015-02-27 2017-04-26 西安交通大学 液化天然气蒸发气压缩机低温气缸工作腔组件结构

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT527367A1 (de) * 2023-06-20 2025-01-15 Hoerbiger Wien Gmbh Kontaktlos dichtender Kolben mit Kolbenstange
AT527368A1 (de) * 2023-06-20 2025-01-15 Hoerbiger Wien Gmbh Kontaktlos dichtender Kolben mit Kolbenstange

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Publication number Publication date
EP3502475A3 (de) 2019-10-16
EP3502475B1 (de) 2022-02-23

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