EP0294322B1 - Pumpe zum Pumpen eines verflüssigtes Gas aufweisenden fluids - Google Patents

Pumpe zum Pumpen eines verflüssigtes Gas aufweisenden fluids Download PDF

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Publication number
EP0294322B1
EP0294322B1 EP88810290A EP88810290A EP0294322B1 EP 0294322 B1 EP0294322 B1 EP 0294322B1 EP 88810290 A EP88810290 A EP 88810290A EP 88810290 A EP88810290 A EP 88810290A EP 0294322 B1 EP0294322 B1 EP 0294322B1
Authority
EP
European Patent Office
Prior art keywords
piston
valve
end member
fluid
pump
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
EP88810290A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0294322A3 (en
EP0294322A2 (de
Inventor
Claudio Tschopp
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.)
Cryopump AG
Original Assignee
Cryopump 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 Cryopump AG filed Critical Cryopump AG
Publication of EP0294322A2 publication Critical patent/EP0294322A2/de
Publication of EP0294322A3 publication Critical patent/EP0294322A3/de
Application granted granted Critical
Publication of EP0294322B1 publication Critical patent/EP0294322B1/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
    • 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
    • F04B39/0016—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 with valve arranged in the piston
    • 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

Definitions

  • the invention relates to a pump designed according to the preamble of claim 1 for pumping a fluid containing liquefied gas.
  • a pump also referred to as a cryogenic pump
  • the fluid to be pumped should preferably be at least largely in the liquid state.
  • the pump should, for example, be able to increase the pressure of the cryogenic fluid, which is originally at most relatively little above the ambient air pressure, typically about 0.1 to 0.5 MPa, to, for example, 20 to 50 MPa or even more.
  • single-stage, cryogenic pumps have an inlet and an outlet for the fluid to be pumped, a housing, a piston which is displaceably guided therein and a drive device which serves to displace it.
  • An end part of the housing located on the side of the piston facing away from the drive device has a first check valve, through which fluid supplied to the inlet can be sucked into the pumping chamber present between said end part and the piston.
  • a casing part of the housing enclosing the pump chamber is provided with a passage at a peripheral point, which is connected to the outlet of the pump via a second check valve connected is.
  • a cryogenic multiple pump known from WO-A-82/03337 has several single-stage pumps connected in parallel in terms of flow. Each of these has a cylindrical housing with a jacket and a multi-part head inserted into one end thereof with an end part adjoining the interior of the housing. A piston is slidably guided in the interior.
  • the fluid supply line has an angled passage running through the jacket and the end part, which opens into the pump chamber between the piston and the surface of the end part facing the piston. The mouth of this passage forms, together with a ring arranged in the interior of the housing, a first check valve which allows fluid to flow into the pump chamber when the piston moves away from the end part.
  • the fluid discharge line has an axial, stepped passage which penetrates the end part and which, together with a spring-loaded, cylindrical valve element, forms a second check valve through which fluid can be pressed out of the pump chamber when the piston approaches the end part.
  • the multiple pump known from WO-A-82/03337 has a disadvantage similar to that of the previously described single-stage pumps known on the market.
  • a pump of this type is known for example from EP-A-174 269 and has one through a partition into two cylindrical interiors divided housing, in each of which a piston is slidably guided.
  • the two pistons are fastened to a common piston rod penetrating a hole in the partition wall provided with a seal and are connected by this to a drive device.
  • the piston further away from the latter, together with a sleeve of the housing containing it and open at the end facing away from the drive device, serves as a pre-compressor in order to pump the liquefied gas through passages present in the partition into the pump chamber belonging to the high-pressure compressor.
  • the partition, the two pistons and the piston rod part connecting them must be cooled from the normal room temperature when pumping to temperatures of around - 200 ° C, depending on the type of fluid to be pumped, and because when pumping between the pre-compressor and the pumping chamber of the high-pressure compressor creates a large pressure difference, the seal required to seal the passage of the piston rod through the partition, in particular if the piston rod part penetrating the partition is relatively thin, is complex to manufacture and prone to failure. Even if the piston rod is dimensioned relatively thin, it still increases the space requirement of the pump for a given delivery rate, whereby a two-stage pump in itself requires more space than a single-stage pump with the same delivery rate.
  • this pump Because the essential part of the Partition and the casing of the housing surrounding the piston of the high-pressure compressor is located outside a container containing liquefied gas from the inlet, this pump also has the disadvantages that the high-pressure compressor is not insulated from the environment and that of the piston of the high-pressure compressor as a result of the friction generated heat can be dissipated poorly.
  • a cryogenic, likewise two-stage pump known from DE-A-2 844 719 has a housing with a cylindrical jacket. The interior of the housing is closed at one end by a bottom connected to the jacket and at the other end by a cover which is detachably fastened.
  • a first piston which is arranged displaceably in the interior, is connected to a piston rod penetrating the cover and can be displaced by it. The first piston is provided on its side facing away from the piston rod with a sleeve coaxial to the jacket.
  • a second piston which is displaceable with respect to this but is fixed with respect to the housing, is arranged in this and is fixed rigidly to the floor with a tube piece.
  • the area of the interior space between the cover and the first piston is referred to in the cited publication as a suction chamber and forms a first pump chamber belonging to the first pump stage.
  • the space between the two pistons inside the sleeve is referred to in the publication as a compression chamber and forms a second pumping chamber belonging to the second pumping stage.
  • a fluid supply line opens into the suction chamber via a first check valve with a passage penetrating the jacket in the radial direction. This is connected to the compression chamber via a check valve, which has passages penetrating the first piston and a spring-loaded ring.
  • the the latter is connected to a fluid discharge line via a check valve arranged in the second piston through said pipe section and through the base.
  • the suction chamber is still connected to an overflow line by a passage penetrating the jacket and an overflow valve.
  • the area of the interior space between the bottom and the first piston, surrounding the sleeve and the pipe back, is also connected to the overflow line through the opening in the jacket.
  • the invention is therefore based on the object of avoiding and in particular enabling disadvantages of the known pumps, for example starting from the single-stage pump known from WO-A-82/03337, to keep the evaporation of liquid fluid in the pumping chamber as low as possible, without having to precede a pump stage with this pump chamber.
  • the pump shown in FIG. 1 has a base 1 which carries a drive device 3 and a sleeve-shaped connecting piece 5 provided with ribs.
  • An elongated housing, designated as a whole by 11, is detachably fastened to the latter, which has an elongated support 13 designed as a continuously open sleeve, one end section of which is screwed to the connecting piece 5 and the other end section having a radially outwardly projecting collar 13a is provided.
  • a bushing 15 which can be seen particularly clearly in FIG.
  • the continuously open bushing 15 has a cylindrical inner surface 15c which extends over most of its length and an extension 15d in its end section facing away from the drive device 3, to which a further extension 15e adjoins.
  • the end of the bushing 15 facing away from the drive device 3 is closed off by an end wall consisting of a separate end part 17, or in short, wall of the housing 11, which has a projection protruding into the extension 15e and is sealed with an annular seal 19.
  • a clamping ring 21 is provided by threaded bolts and nuts Fastening elements 23 releasably connected to the collar 13a and presses the end part 17 serving as the end wall against the collar 15b and this against the collar 13a, as a result of which the end part 17 is detachably connected to the bush 15 and this is detachably connected to the sleeve-shaped carrier 13.
  • the housing 11 contains an elongated inner space designated as a whole by 31, in the cylindrical part of which is limited by the bushing 15, a piston 35 is displaceably guided and sealed with annular seals 37.
  • the piston 35 is connected to a crank of the drive device 3 by means of a piston rod 39, which consists at least in part of it with a one-piece body, a portion of the carrier 13 being designed as a passage 13b and two ring-shaped seals 41 and a sleeve-shaped seal 43 for sealing the piston rod contains.
  • the carrier 13, the bushing 15, the end part 17, the interior 31, the piston 35 and the piston rod 39 have a common, horizontal axis 45 or, more precisely, the longitudinal central axis 45 and are at least generally rotationally symmetrical to this.
  • the area of the interior 31 located between the end part 17 and the piston is referred to below as the pump chamber 33.
  • the largest part of the housing 11 and in particular at least its part that contacts and seals the piston 35, ie the bush 15, and the housing end part 17 are located in the interior 53 of a container 51, which is sealed off from the environment.
  • the container 51 has a heat-insulating wall an inner wall and an outer wall separated therefrom by a preferably evacuated intermediate space. Otherwise, the wall of the container 51 consists of two parts, one of which, the first near the Connection piece 5 is tightly attached to the sleeve-shaped carrier 13 and the other, second detachable by releasable connecting means and tightly attached to the first part.
  • the lowermost portions of the housing 11 are located slightly above the lowest point of the container interior 53 and the axis 45 of the housing 11 and piston 35 is in the lower half of the container interior 53 and thus below the horizontal longitudinal central axis 55 of the generally cylindrical Container 51.
  • a nozzle serving as an inlet 57 for the fluid to be pumped opens, for example in the lowest region of the container 51, into the interior 53 thereof.
  • the end part 17 has at least one passage 59, namely at least two and preferably even more passages 59 distributed around the axis 45 Together with the container interior 53, these form fluid supply means 53, 59 which connect the inlet 57 to the pump chamber 33.
  • a plate-shaped valve element 61 has a central through-opening 61a which is coaxial with the axis 45 and is guided in the pump chamber 33 so as to be displaceable along the axis 45 and thus in the direction of displacement of the piston 35, the possible displacement path of the valve element 61 on one side through the end part 17 of the housing and on the other side is limited by the end of the extension 15d facing the drive device 3.
  • the passages 59 together with the valve element 61 serve as the first check valve 63, the valve seat of which is formed by the flat end face of the end part 17 facing the piston 35.
  • the end part 17 of the housing 11 is further provided with a central passage 65 which is coaxial with the axis 45 and which has a section which widens away from the pump chamber 33 and forms a valve seat.
  • a spherical valve element 67 is movably held, which is pressed against the valve seat by a spring 69.
  • the passage 65 serves together with the valve element 67 and the spring 69 as a second check valve 71.
  • a line 75 fastened to the end part 17 and tightly connected to the passage 65 and consisting, for example, of a tube leads through the container interior 53 to a wall of the container 51 penetrating bushing and forms there together with this an outlet 77 for the pumped fluid.
  • the passage 65 forms, together with the line 75, fluid discharge means 65, 75 which connect the pump chamber 33 to the outlet 77.
  • the diameter of the section of the piston rod 39 adjoining the piston 35 is smaller than the diameter of the piston and of the inner surface 15c of the bush.
  • the sleeve-shaped carrier 13 is provided between the bushing 15 and the bushing 13b with at least one hole 79 penetrating its jacket, namely with at least two holes 79 distributed over its circumference. These open into a free area of the interior 31 of the housing 11 that surrounds the piston rod 39.
  • the piston 35 has a blind hole 81 drilled into it from its end facing the pump chamber 33. This has a hole in the direction of the end part 17 of the housing 11 conically widening mouth section, which serves as valve seat 83.
  • the piston on its side facing the drive device 3 and facing away from the pumping chamber 33 between its cylindrical outer surface and the piston rod 39 is delimited by a conical annular surface, from which inclined holes 85 are drilled in the piston, which open into the base section of the blind hole 81.
  • a guide body 87 is inserted between the base section and the valve seat 83, which has a bushing and / or has hub-like middle section. From this, rib-like or wing-like projections distributed around it protrude outward, the free edges of which are pressed into the blind hole 81 and hold the guide body therein, additional securing means and / or fastening means possibly being present to secure the guide body 87 and rigidly fixed in the piston.
  • Channels 89 are distributed between the mutually adjacent, rib-like or wing-like projections of the guide body around its hub-like central section.
  • the number of channels 89 is, for example, equal to the number of holes 85 and can be, for example, approximately four to eight, depending on the size and intended delivery capacity of the pump.
  • a valve element 91 has a plate which is coaxial with the axis 45 and has a conical section which fits into the conical valve seat 83 and on its side facing the end part 17 has a short, cylindrical projection, the diameter of which is somewhat smaller than the diameter of the through opening 61a of the valve element 61 first check valve.
  • the valve element 91 is rigidly connected to a bolt 93 and, for example, is formed together with this from a one-piece body.
  • the bolt 93 penetrates the guide hole 87a of the guide body 87, is displaceably guided therein parallel to the direction of displacement of the piston and is provided with a thread on its end facing away from the valve element 91, onto which a nut 95 is screwed.
  • there is at least one spring 97 namely a helical spring surrounding the bolt 93, which exerts a force on the nut 95 and on the bolt 93 a force directed away from the end part 17 towards the drive device 3 on the valve element 91 .
  • the free areas of the blind hole 81 form a passage together with the holes 85 and the channels 89.
  • the housing 11 consists at least essentially of metallic, preferably made of stainless steel parts, the bushing 15 being made, for example, of hardened stainless steel.
  • the piston 35 consists, for example, of a beryllium-copper alloy.
  • the valve element 61 is made of, for example, stainless steel, the valve element 67 is made of metallic material, such as stainless steel, and / or polytetrafluoroethylene, and the valve element 91 is made of a metallic material, such as a beryllium-copper alloy or the copper known under the name Monel. Nickel alloy.
  • the input 57 is connected, for example, to a reservoir which contains the fluid to be pumped, ie liquefied gas.
  • the pressure present in the reservoir is at least equal to the ambient air pressure and preferably somewhat greater than this, so that the fluid is pressed into the reservoir 57 to the inlet 57 and into the interior 53 of its container 51 by the pressure present in the reservoir.
  • the container 51 is also provided with a gas outlet 101, the inner end of which is in the vicinity of the uppermost region of the container interior 53.
  • the gas outlet 101 is connected, for example, to the aforementioned reservoir via a gas return line or to the surroundings via a pressure relief valve.
  • the outlet 77 for the liquefied and compressed by the pump gas can, for example, with an evaporation and filling device be connected to fill the now gaseous but highly compressed fluid in a pressure vessel.
  • fluid consisting at least mainly of liquefied gas flows into the interior 53 of the container 51 through the inlet 57.
  • the liquefied gas rises in the container, for example, to level 111, above which level evaporation then returns to the gaseous state.
  • the parts of the housing 11 located within the container interior 53, and in particular its bush 15 and end part 17, which together form the actual pump cylinder, are of low pressure, i.e. surrounded by the feed, not yet pumped, liquefied gas.
  • the drive device 3 When pumping, the drive device 3 alternately pushes the piston 35 back and forth along the horizontal axis 45. If the piston moves to the left in FIGS. 1 and 2, ie away from the end part 17 in the time interval referred to below as the suction stroke, as was assumed when drawing the valve elements, it sucks fluid out of the container interior 53 in the manner indicated by arrows through the first check valve 63 as well as through the holes 79 and the passage of the third Check valve 99 into the pump chamber 33. If the piston then moves in the opposite direction in the time interval referred to below as the compression stroke, it pushes fluid out of the pump chamber 33 via the second check valve 71 to the outlet 77.
  • both the first and third check valves When both the first and third check valves are open, they together make one proportionate large passage cross-section, which also counteracts the development of pressure drops and the vaporization of liquefied gas.
  • the valve element 91 can, for example, be designed such that the annular surface of its conical section facing the end part 17, when it rests on the valve seat 83 in its closed position, is approximately flush with the end face of the piston. Furthermore, the displacement path of the piston can be determined such that it and the said annular surface of the valve element 91 at the end of the compression stroke, when the valve element 61 abuts the end part 17, in turn lie at least approximately on the valve element 61 and that the projection of the valve element 91 into the central one Opening 61a of valve element 61 projects into it. If these conditions are met, the free volume of the pumping chamber is reduced to almost zero at the end of the compression stroke, so that there is practically no dead space in the pumping chamber 33 and between it and the valve seats of the three check valves.
  • the pump can of course be modified in various ways.
  • the inlet 57 can open parallel to the piston axis through the end wall of the container 51 located on the right in FIG. 1 and into its interior 53.
  • a filter screen can also be arranged, which can be conical, for example, to achieve a large surface area.
  • the passages of the three check valves and their remaining training can be changed in a variety of ways.
  • the end part 17 serving as the end wall of the housing 11 can be replaced, for example, by a thicker end part, measured in the axial direction, the outer surface of which is provided with an annular groove which widens outwards from the bottom thereof.
  • the passages corresponding to the passages 59 can then, at their ends facing away from the pump chamber 33, open into the end face of the end part 17 facing away from the bushing 15 into the annular groove provided in the lateral surface thereof, as in FIG.
  • At least one spring can be provided which acts on the movable valve element of the first check valve with a force directed away from the piston 35 towards the housing end part 17.
  • the valve element of the first check valve can be provided, for example, on its side facing away from the piston with at least one finger protruding into a hole in the housing end part, onto the end of which a nut is screwed away from the piston.
  • a helical spring can then be held on the finger, which engages on one end on a radial surface of the housing end part and on the other end on said nut.
  • the finger-receiving and guiding hole of the housing end part can be arranged, for example, coaxially to the piston in the housing end part and therefore at the point at which the passage 65 of the second check valve is located in FIG.
  • the passage of the second check valve could then, for example open in the radial direction through the jacket of the bushing 15 into the pump chamber 33.
  • the movable valve element 67 of the second check valve 71 can consist of a differently shaped body, for example a sleeve, instead of a ball, which is closed at the valve seat end by an end wall and in the other, open end of a spring corresponding to the spring 69 attacks.
  • the guide body 87 used to guide the bolt 93 of the third check valve can be formed from a bushing which has a cylindrical outer surface that is connected around its axis.
  • the bushing can be pressed into the blind hole 81 in a manner analogous to that described for the guide body 87 and additionally fixed in the piston with securing and / or fastening means.
  • the latter can have, for example, at least one grub screw and, for example, several such, which are screwed in under one of the seals of the piston distributed over its circumference in radial threaded bores of the piston jacket and engage with their, for example, conical ends facing the piston axis in holes in the bushing forming the guide body .
  • the channels 89 shown in FIG. 2 can then be formed by holes, preferably bores, distributed around the axis and the hole of the bush corresponding to the guide hole 87a.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Compressor (AREA)
EP88810290A 1987-05-19 1988-05-04 Pumpe zum Pumpen eines verflüssigtes Gas aufweisenden fluids Expired - Lifetime EP0294322B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1923/87A CH672354A5 (enrdf_load_stackoverflow) 1987-05-19 1987-05-19
CH1923/87 1987-05-19

Publications (3)

Publication Number Publication Date
EP0294322A2 EP0294322A2 (de) 1988-12-07
EP0294322A3 EP0294322A3 (en) 1990-02-28
EP0294322B1 true EP0294322B1 (de) 1993-01-27

Family

ID=4221754

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88810290A Expired - Lifetime EP0294322B1 (de) 1987-05-19 1988-05-04 Pumpe zum Pumpen eines verflüssigtes Gas aufweisenden fluids

Country Status (4)

Country Link
US (1) US4915602A (enrdf_load_stackoverflow)
EP (1) EP0294322B1 (enrdf_load_stackoverflow)
CH (1) CH672354A5 (enrdf_load_stackoverflow)
DE (1) DE3877832D1 (enrdf_load_stackoverflow)

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CA2362881C (en) * 2001-11-30 2004-01-27 Westport Research Inc. Method and apparatus for delivering pressurized gas
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WO2011090504A1 (en) * 2010-01-20 2011-07-28 Endocare, Inc. High pressure cryogenic fluid generator
DE102010002283A1 (de) * 2010-02-24 2011-08-25 Continental Teves AG & Co. OHG, 60488 Kolbenpumpe
EP2600001B1 (en) * 2011-11-29 2014-11-19 Cryostar SAS Cryogenic pumps
CN104956064B (zh) 2012-10-25 2019-02-19 比克喷射有限公司 燃料喷射系统
US20140127036A1 (en) * 2012-11-02 2014-05-08 Caterpillar Inc. Plunger with outlet valve assembly for plunger pumps
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US10041484B2 (en) * 2015-01-30 2018-08-07 Caterpillar Inc. Pump having inlet reservoir with vapor-layer standpipe
US20170030341A1 (en) * 2015-07-27 2017-02-02 Caterpillar Inc. Multi-plunger cryogenic pump having intake manifold
US10024311B2 (en) * 2015-08-06 2018-07-17 Caterpillar Inc. Cryogenic pump for liquefied natural gas
WO2017197282A1 (en) 2016-05-12 2017-11-16 Briggs & Stratton Corporation Fuel delivery injector
CN109790806B (zh) 2016-07-27 2021-05-25 布里格斯斯特拉顿有限责任公司 往复式泵喷射器
RU2703048C1 (ru) * 2016-08-29 2019-10-15 ЭЙСИДИ, ЭлЭлСи Насос высокого давления для топливного газа
US10947940B2 (en) 2017-03-28 2021-03-16 Briggs & Stratton, Llc Fuel delivery system
US11668270B2 (en) 2018-10-12 2023-06-06 Briggs & Stratton, Llc Electronic fuel injection module
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CN110425106B (zh) * 2019-08-16 2020-09-08 成都正升能源技术开发有限公司 一种直线压缩机用活塞组件
CN112177918B (zh) * 2020-09-30 2025-08-01 杭州青谷小象科技有限公司 一种直流式泵的密封结构

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Also Published As

Publication number Publication date
EP0294322A3 (en) 1990-02-28
US4915602A (en) 1990-04-10
DE3877832D1 (de) 1993-03-11
CH672354A5 (enrdf_load_stackoverflow) 1989-11-15
EP0294322A2 (de) 1988-12-07

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