EP0253122B1 - Kolbenpumpe für kryogene Flüssigkeiten - Google Patents

Kolbenpumpe für kryogene Flüssigkeiten Download PDF

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Publication number
EP0253122B1
EP0253122B1 EP87108050A EP87108050A EP0253122B1 EP 0253122 B1 EP0253122 B1 EP 0253122B1 EP 87108050 A EP87108050 A EP 87108050A EP 87108050 A EP87108050 A EP 87108050A EP 0253122 B1 EP0253122 B1 EP 0253122B1
Authority
EP
European Patent Office
Prior art keywords
piston
pump
cylinder
pump cylinder
ptfe
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
EP87108050A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0253122A3 (en
EP0253122A2 (de
Inventor
Willi Dipl.-Ing. Nieratschker
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.)
Deutsches Zentrum fuer Luft und Raumfahrt eV
Original Assignee
Deutsches Zentrum fuer Luft und Raumfahrt eV
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 Deutsches Zentrum fuer Luft und Raumfahrt eV filed Critical Deutsches Zentrum fuer Luft und Raumfahrt eV
Publication of EP0253122A2 publication Critical patent/EP0253122A2/de
Publication of EP0253122A3 publication Critical patent/EP0253122A3/de
Application granted granted Critical
Publication of EP0253122B1 publication Critical patent/EP0253122B1/de
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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • 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
    • Y10S417/01—Materials digest
    • 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 relates to a piston pump for cryogenic liquids with a pump cylinder, in which a piston can be sealed and oscillated without additional piston rings, with an inlet and an outlet valve, the dimensions of the pump cylinder and the piston being chosen such that the operating temperature of the piston is sealed against the inner wall of the pump cylinder, and wherein the material of the pump cylinder has a greater coefficient of thermal expansion than the material of the piston.
  • Piston pumps of this type are used to convey cryogenic liquids, for example for liquid nitrogen or liquid hydrogen (C.F. Gottmann, High Pressure Liquid Hydrogen and Helium Pumps, AICE, Advances in Cryogenic Engineering, Volume 5, 1960, pages 289 to 298).
  • the low temperatures cause a very limited choice of materials, lead to shrinkage problems, especially in the piston-cylinder pairing, and prevent the use of additive lubricants.
  • the low kinematic viscosity of the liquid to be conveyed also means a low lubricating property, so that one has to rely on self-lubricating piston-cylinder surfaces.
  • the compression chamber can be sealed either by surfaces with self-lubricating properties or by so-called gas-bearing or non-contact seals.
  • Another indispensable aid is the cooling of the cylinder wall either with the already evaporated leak portion (US-A-4 396 362) or with the main flow on the pressure side through the pump body (US-A-4 156 584).
  • This avoids the accumulation of heat in the cylinder wall. It is transported out with the cryogenic fluid. Downstream of the compression chamber, the supply of heat to the cryogenic medium is far less critical than in the suction chamber, since in particular downstream of the outlet valve, the supply of heat is even noticeable as an increase in pressure. In particular, if the critical pressure is exceeded, there is no longer a risk of a two-phase flow.
  • austenitic steels such as austenitic cold-tough steels, Fe Ni 36, bronze, PTFE (polytetrafluoroethylene), PTFE-carbon, PTFE-bronze, PTFE-graphite, ceramic, carbon fiber reinforced plastic.
  • the use of piston rings is therefore completely dispensed with here.
  • the seal is made in that the entire pump cylinder is made of a material that is normally used for the piston rings.
  • the dimensions are chosen so that an optimal seal takes place at the operating temperature. Since the materials used for the cylinder have a much higher thermal expansion than the cylinder, the gap between the piston and the inner wall of the cylinder increases when it is warmed up. Although the function of the pump is slightly affected by this, there is neither the risk of the piston pressing down nor the risk of deformation of the parts used. It is even advantageous if cryogenic fluid can flow through the small gap between the piston and the cylinder inner wall when the pump is cold, since this accelerates the cooling of all parts.
  • the outlet valve is arranged at the downstream end of the ring channel, so that the same high pressure prevails in the ring channel as in the interior of the pump cylinder. This ensures that the cylinder is acted upon from the inside and outside with the same pressure, that is, the total mechanical stress on the cylinder is reduced to a minimum.
  • the forces acting on the cylinder from the outside inward, at least in the area of the suction chamber are greater than the forces acting from the inside out, so that the cylinder is pressed against the piston in a sealing manner. This measure also contributes to improving the seal between the piston and the cylinder inner wall.
  • Another advantage results from the fact that the area of the self-lubricating cylinder inner wall covered by the piston, which corresponds to the stroke of the piston, is considerably larger than a corresponding contact area of a piston ring on a conventional cylinder, so that the abrasion and wear of the self-lubricating material can be significantly reduced.
  • the cylinder is preferably made of PTFE, PTFE graphite, PTFE bronze, PTFE carbon, carbon fiber reinforced plastic or brass, while the piston is preferably made of stainless steel with low thermal expansion, in particular austenitic low-temperature steels or Fe Ni 36.
  • the piston carries one or more annular shoulders on its outer surface, which lie sealingly against the inner wall of the pump cylinder.
  • Such essentially linear seals reduce the friction between the piston and the cylinder wall and thus also the undesirable heat generated during the pumping process.
  • the piston for training a ring shoulder is spherically ground in the area of this ring shoulder.
  • the piston is hollow and open on one side, and a passage which can be closed by means of a check valve is arranged in the piston.
  • a hollow body has the advantage that the piston has a low mass to be cooled, so that particularly rapid cooling is possible. This is exacerbated by the fact that the cryofluid flows around the outside and inside of this piston during cooling, as does the pump cylinder, which also flows around the inside and outside of the cryofluid during cooling.
  • the annular channel has such a small extent in the radial direction that the volume of the annular channel is small compared to the amount of liquid delivered per piston stroke. In this way, an increased flow velocity in the ring channel and thus a particularly effective heat dissipation from the pump cylinder are achieved.
  • the pump cylinder can be shrunk at one end onto a cylinder head, while it ends freely at its opposite end and the liquid conveyed flows around it in this area.
  • the piston pump shown in the drawing comprises a cylindrical vacuum vessel 1 with flanges 2 and 3 on the top and bottom, respectively. With these flanges 2 and 3 covers 4 and 5 are screwed sealed.
  • the interior of the vacuum vessel can be evacuated via a closed side nozzle 6.
  • a tube 8 made of a glass fiber reinforced plastic is pushed onto a metal sleeve 7 held in the middle on the upper cover 4 and fixed, for example by gluing.
  • the free, flange-shaped outward end 9 of the tube 8 is screwed to a cover plate 10, which in turn closes a thin-walled outer cylinder 11 on the top.
  • This outer cylinder 11 is screwed sealed to a cylinder head 13 on the underside via a fastening ring 12.
  • the cylinder head 13 projects into the lower part of the outer cylinder 11 and has in this area a centrally arranged valve chamber 14, in the upper side of which a valve holder 15 is screwed.
  • a suction line 16 opens into it, which is sealed by the lower cover 5 of the vacuum vessel 1 is passed through and vacuum insulated.
  • the inlet of the suction line 16 into the valve chamber 14 is designed as a valve seat for a spherical cap-shaped valve body 17 which is guided in the valve holder 15 and is pressed against the valve seat by a beryllium-copper spring 18.
  • the valve body 17 can be lifted against the action of the spring 18 from the valve seat.
  • the part of the cylinder head 13 protruding into the outer cylinder 11 has a stepped recess 19 at its upper end.
  • a pump cylinder 20 which is open on both sides, is shrunk onto the cylinder head 13 and forms an annular channel 21 which is narrow in the radial direction between its outer wall and the inner wall of the outer cylinder 11.
  • the end of the pump cylinder 20 opposite the cylinder head 13 is freely arranged at a short distance from the cover plate 10, so that the interior of the pump cylinder 20 is in flow connection with the annular channel 21.
  • Passages 22 in the valve holder 15 continue to connect the interior of the pump cylinder 20 with the valve chamber 14.
  • the annular channel 21 opens into an annular space 23 which is enlarged in the radial direction and is incorporated in the fastening ring 12.
  • an exhaust valve 24 is attached, which connects the annular space 23 to an exhaust line 25, which also passes through the lower cover 5 and is vacuum-insulated.
  • the outlet valve 24 comprises a spherical valve body 26 which is pressed against a valve seat 28 by means of a spring 27.
  • a hollow piston 29 is arranged in the interior of the pump cylinder 20 and has a plurality of spherically ground regions 30 on its outer jacket, which are arranged at a distance from one another in the axial direction and which bear with their circumferential largest part against the inner wall of the pump cylinder 20.
  • the hollow piston 29 is open on one side, on the opposite side it has an opening 32 in an end wall 31 through which a lifting and pulling rod 33 passes.
  • This lifting and pulling rod 33 carries in the interior of the hollow piston 29 a valve body 34 on which a compression spring 35 is supported, the other end of which rests on a snap ring 36 at the open end of the hollow piston 29.
  • the compression spring 35 displaces the valve body 34 in the direction of the passage opening 32. When the valve body 34 abuts the passage opening 32, it closes it.
  • the lifting and pulling rod is passed through the cover plate 10 of the outer cylinder 11 and is surrounded by a thin metal tube 37 in the region of the tube 8 and the metal sleeve 7.
  • This metal tube 37 is sealed in the upper cover 4 by an annular seal 38 with respect to the lifting and pulling rod 33 which passes through the cover 4 towards the top.
  • a reciprocating drive for the lifting and pulling rod is not shown in the drawing.
  • the hollow piston 29 consists of a metal with low thermal expansion, for example austenitic cold-tough steel or Fe Ni 36.
  • the pump cylinder 20 is made of a material which on the one hand has good sliding and self-lubricating properties with respect to the piston material and on the other hand has a much greater thermal expansion than the piston material.
  • the pump cylinder can be made of PTFE, PTFE graphite, PTFE bronze, PTFE carbon, carbon fiber reinforced carbon or brass.
  • the dimensions of the piston and the pump cylinder are chosen so that at the operating temperature, i.e. the temperature of the cryogenic liquid being pumped, the piston in the spherically ground regions 30 lies sealingly against the inner wall of the pump cylinder 20, while at higher temperatures there is a gap between the Hollow piston 29 and the pump cylinder 20 occurs.
  • valve body 34 is lifted from the passage opening 32 in a downward stroke, in which the lifting and pulling rod 33 is moved downward, so that the liquid in the interior of the pump cylinder 20 is separated from the open underside of the hollow piston 29 passes through the passage opening 32 to the top of the hollow piston 29 ( Figure 1).
  • an outward stroke in which the lifting and pulling rod 33 is pulled upward, the passage opening 32 in the hollow piston 29 is closed by the valve body 34.
  • both the inlet valve (valve body 17) and the outlet valve 24 (valve body 26) are opened, so that liquid to be conveyed via the suction line 16 is sucked into the part of the pump cylinder 20 below the hollow piston 29, while at the same time the liquid is out the pump cylinder 20 arranged above the hollow piston 29 is fed through the annular channel 21 and the open outlet valve 24 to the outlet line 25 (FIG. 2).
  • the fluid flowing around the pump cylinder 20 on the inside and on the outside effectively cools the pump cylinder and dissipates heat generated by the friction on the pressure side.
  • the seal between the piston and the pump cylinder is optimal at operating temperature, at higher temperatures there is a slight leak, which is not annoying, on the contrary, it accelerates cooling when the pump is started.
  • the pump By arranging the pump in a vacuum container, it can be operated in a non-immersed state.
  • the only heat-conducting bridges to the outside are the vacuum-insulated suction line 16, the likewise vacuum-insulated outlet line 25, the lifting and pulling rod 33 with the tube 37 enveloping them, and the metal sleeve 7 and the pushed-on tube 8 made of glass-fiber reinforced plastic.
  • These Thermal bridges are designed in such a way that an overall excellent thermal insulation of the actual pump unit from the environment is achieved.
  • the sealing of the lifting and pulling rod 33 takes place in the area of the upper cover 4, that is to say at elevated temperatures, so that a very effective sealing is possible there.
  • the lifting and pulling rod 33 Inside the metal tube 37, the lifting and pulling rod 33 is surrounded by a gas cushion, which remains essentially unchanged there.
  • the dead volume filled with gas between the metal tube 37 and the lifting and pulling rod 33 is chosen to be as small as possible.
  • hollow piston 29 shown in FIGS. 1 and 2 has four spherically ground regions 30 in the axial direction, only two spherically ground regions 30 are provided in the modified hollow piston shown in FIG. 3 at the upper and lower ends of the hollow piston. With this piston, too, an excellent seal between the piston and the pump cylinder can be achieved at operating temperature in the construction according to the invention.
  • pistons of other types can also be used, for example cylindrically ground pistons or compact pistons without a valve-closed passage opening.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP87108050A 1986-06-28 1987-06-04 Kolbenpumpe für kryogene Flüssigkeiten Expired - Lifetime EP0253122B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863621727 DE3621727A1 (de) 1986-06-28 1986-06-28 Kolbenpumpe fuer kryogene fluessigkeiten
DE3621727 1986-06-28

Publications (3)

Publication Number Publication Date
EP0253122A2 EP0253122A2 (de) 1988-01-20
EP0253122A3 EP0253122A3 (en) 1988-08-10
EP0253122B1 true EP0253122B1 (de) 1991-06-05

Family

ID=6303929

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87108050A Expired - Lifetime EP0253122B1 (de) 1986-06-28 1987-06-04 Kolbenpumpe für kryogene Flüssigkeiten

Country Status (4)

Country Link
US (1) US4792289A (enrdf_load_stackoverflow)
EP (1) EP0253122B1 (enrdf_load_stackoverflow)
JP (1) JPS6336068A (enrdf_load_stackoverflow)
DE (1) DE3621727A1 (enrdf_load_stackoverflow)

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JP3341910B2 (ja) * 1992-11-16 2002-11-05 株式会社ユニシアジェックス 液体水素ポンプ
FR2706540B1 (fr) * 1993-06-11 1995-09-01 Europ Propulsion Pompe liquide cryogénique intégrée amovible et autorefroidie.
DE4319990A1 (de) * 1993-06-17 1994-12-22 Messer Griesheim Gmbh Verfahren zum Herstellen von Teilchen aus Kunststoffen
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US5810570A (en) * 1997-01-06 1998-09-22 Chemical Seal & Packing, Inc. Super-low net positive suction head cryogenic reciprocating pump
US6006525A (en) * 1997-06-20 1999-12-28 Tyree, Jr.; Lewis Very low NPSH cryogenic pump and mobile LNG station
US6592338B2 (en) 1998-12-11 2003-07-15 Ovation Products Corporation Rotating compressor
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US8671700B2 (en) * 2009-01-21 2014-03-18 Endocare, Inc. High pressure cryogenic fluid generator
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US8365551B2 (en) * 2010-12-09 2013-02-05 General Electric Company Vacuum insulator for a refrigerator appliance
ITMI20110959A1 (it) * 2011-05-27 2012-11-28 Ceme Spa Elettropompa del tipo a cursore oscillante
US20140169993A1 (en) * 2012-12-18 2014-06-19 Icecure Medical Ltd. Cryogen pump
US10584692B2 (en) * 2014-09-22 2020-03-10 Eagle Industry Co., Ltd. Liquid supply system
US9909576B2 (en) * 2015-01-23 2018-03-06 Caterpillar Inc. Pump drive system with hydraulic tappets
US20160348656A1 (en) * 2015-06-01 2016-12-01 Caterpillar Inc. Support system for a pump
US10024311B2 (en) * 2015-08-06 2018-07-17 Caterpillar Inc. Cryogenic pump for liquefied natural gas
US10190556B2 (en) * 2017-01-09 2019-01-29 Caterpillar Inc. System and method for lubricating a cryogenic pump
US10626856B2 (en) 2017-01-12 2020-04-21 Caterpillar Inc. Cryogenic fluid pump
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Also Published As

Publication number Publication date
US4792289A (en) 1988-12-20
JPS6336068A (ja) 1988-02-16
DE3621727A1 (de) 1988-01-14
EP0253122A3 (en) 1988-08-10
DE3621727C2 (enrdf_load_stackoverflow) 1989-01-19
EP0253122A2 (de) 1988-01-20

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