EP0400693A2 - Pompe à haute pression - Google Patents

Pompe à haute pression Download PDF

Info

Publication number
EP0400693A2
EP0400693A2 EP90114874A EP90114874A EP0400693A2 EP 0400693 A2 EP0400693 A2 EP 0400693A2 EP 90114874 A EP90114874 A EP 90114874A EP 90114874 A EP90114874 A EP 90114874A EP 0400693 A2 EP0400693 A2 EP 0400693A2
Authority
EP
European Patent Office
Prior art keywords
high pressure
pressure pump
ultra
pump according
membrane
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.)
Withdrawn
Application number
EP90114874A
Other languages
German (de)
English (en)
Other versions
EP0400693A3 (fr
Inventor
Karl Eickmann
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to EP19900114874 priority Critical patent/EP0400693A3/fr
Publication of EP0400693A2 publication Critical patent/EP0400693A2/fr
Publication of EP0400693A3 publication Critical patent/EP0400693A3/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/142—Intermediate liquid-piston between a driving piston and a driven 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0018—Special features the periphery of the flexible member being not fixed to the pump-casing, but acting as a valve
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0054—Special features particularities of the flexible members
    • F04B43/0063—Special features particularities of the flexible members bell-shaped flexible members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
    • F04B43/10—Pumps having fluid drive
    • F04B43/107—Pumps having fluid drive the fluid being actuated directly by a 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/141—Intermediate liquid piston between the driving piston and the pumped liquid

Definitions

  • the invention relates to an ultra-high pressure pump, in particular for pressures up to 4000 bar according to the preamble of claim 1.
  • Such a high pressure pump is already known from DE-OS 35 45 631.
  • a diaphragm is used to transmit a pressure applied to a hydraulic fluid via a piston to a pressure fluid which is fed into and out of the pump via inlet and outlet means.
  • the membrane is deformed either towards the piston or towards the inlet / outlet means.
  • the diaphragm does not act as a pumping element in a generic high-pressure pump, but rather serves only for the liquid-tight separation of the hydraulic fluid from the pressure fluid, and is therefore loaded on both sides with approximately the same pressure.
  • the invention has for its object to develop the generic high pressure pump such that also high delivery rates, a sufficient service life of the high-pressure pump is guaranteed.
  • a particularly compact high pressure pump can be produced.
  • the wall between the outer chamber and the cylinder is supported on both sides by the outer chamber pressure and the cylinder pressure, so that the wall thickness can be minimized.
  • the fatigue strength of the membrane can be significantly increased if, according to a combination of features of claims 3 to 7, the maximum deflections of the membranes are limited by contact surfaces.
  • the increase in the fatigue strength is due to the fact that the maximum deflection of the membrane is reduced with the same stroke compared to the generic state of the art when using contact surfaces.
  • the formation of the contact surfaces makes it possible to minimize the damage space, which is particularly important at high fluid pressures.
  • the inner chamber and outer chamber separated by the membrane are each connected via recesses to the inlet / outlet means or the cylinder, so that the volumes of the flow paths are small.
  • leakage fluid emerging from the outer chamber as well as from the inner chamber is collected and mixing of the hydraulic fluid with the pressurized fluid is prevented.
  • a particularly compact pump arrangement with a high delivery capacity is obtained if, according to patent claims 17 to 19, a plurality of high-pressure pumps according to the invention, which are assigned to a drive device, are combined by common fastening elements.
  • the highest pressures can be easily achieved by using a differential piston.
  • a working chamber 17 is located in a housing 1 and has an inlet and an outlet valve 38 and 39, wherein corresponding connection channels 1509 can be arranged. It is important in the simplest embodiment according to FIG. 1 that the axis of the working chamber is perpendicular. Because at the bottom of the chamber 17, the non-lubricating or rust-causing medium to be pumped, for example water, is to be pumped. Above the chamber part 17 is the chamber part 16 which, according to the invention, is filled with a lubricatable fluid which, compared to the fluid in the chamber part 17, has a lower density or a lower specific weight. This liquid of the lower specific weight is called the first liquid or the hydraulic fluid and the liquid in the chamber part 17 with the higher specific weight is called the second liquid or the pressure fluid.
  • the first is the lubricating liquid
  • the second the non-lubricating liquid.
  • Pump piston 52 can therefore be arranged and reciprocated above chamber part 16.
  • the water or another fluid is now pressed under a slight upstream pressure through the inlet valve 38 into the chamber 17, as a result of which the piston 15 is pressed back into its starting position.
  • the piston 15 could also be pulled back into its original position by a sliding guide or by a spring means.
  • Fig. 2 the same system is shown, but it is indicated by the several stroke eccentrics 13, 23 and 24 that several work units lie one behind the other and are operated in time by a shaft 12 with their stroke parts 13, 23 and 24, i.e. have a common drive device.
  • the stroke eccentric chamber 25 can be filled with pre-pressure fluid, which then temporarily, when the control groove 26 hits the bore or the channel 28 in the piston shoe when the shaft 12 rotates, through the groove 26, channel 28 and the channel penetrating the piston 15 30 can be directed into the medium power 31 in order to fill it with the correct amount of fluid.
  • the central channel 30 leads from the cylinder in which the piston 15 runs, specifically from the cylinder bottom thereof, to the working chamber 32 which is likewise arranged in the housing 1.
  • the follower piston 33 is sealingly and reciprocally supported.
  • the piston 15 is the first piston, while the piston 33 is the second piston.
  • the fluid column filling the central channel 31 is located between the two pistons 31, which transmits the movement of one of the pistons to the other piston.
  • the first piston 15 is the master piston and the second piston 33 is the follower piston.
  • the pistons can have different diameters in order to achieve a force transmission.
  • the first piston of smaller diameter but longer strokes thus produces a greater force of shorter strokes of the follower piston or second piston 33.
  • the fluid or outer chamber 35 is formed, into which the follower piston 33 can dip and which forms the first chamber part, which is filled with the first fluid, that is to say filled with the lubricating fluid, so that the piston 33 and its fit in the bushing 45 cannot be damaged by non-lubricating or rust-causing fluid.
  • the chamber part or the inner chamber 37 which contains the non-lubricating second fluid to be pumped.
  • the inner chamber 37 is accordingly again provided with an inlet valve 38 and an outlet valve 39 - possibly spring-loaded. These valves are connected in this figure to manifolds 41 and 42 for the inlet and outlet of all working units.
  • a separating agent 36 is arranged between the chambers 35 and 37 in order to avoid mixing by splashing the first and the second liquid.
  • the separating means 36 which may be a disk, can be provided with sealing ring groove means 43 for receiving plastic sealing ring means, not shown.
  • FIG. 3 shows the design for the highest pressures as a pump and for practically unlimited service life.
  • the piston drive parts 12, 13, etc. for the transmitter part can be built with the means of the applicant's hydrostatic units for unlimited life because they do not touch any non-lubricating or rusting fluid.
  • the separating body 36 which is already known from FIG. 2, has an unlimited service life because it has no loads is exposed. It only floats between two fluids of the same pressure.
  • the valves and channels like the chambers 35 and 37, are arranged and act analogously as in Fig. 2. Likewise, the connections.
  • the master piston 15 has a relatively small diameter in comparison to the follower piston 49 driven by it via the fluid column in the central channel 31.
  • the follower piston 49 is moved with a multiple force relative to the force of the master piston 15, and that is moved down in the figure.
  • the front or lower end of the follower piston 49 opens into the preferably unpressurized intermediate chamber 50. It may be kept depressurized by the connection 51, which may be connected to the atmosphere or better to a low-pressure chamber of the unit.
  • the special feature of FIG. 3 in comparison to FIG. 2 is that in FIG. 3 the follower piston 49 acts on a high-pressure pump piston 52 of smaller diameter.
  • the high-pressure pump piston 52 reaches a substantially higher pressure in the chambers 35 and 37 than the follower piston could reach therein, because a force transmission is arranged between the follower piston 49 and the high-pressure pump piston 52 due to the cross-sectional differences.
  • the hydrostatic The sensor stage of the first piston 15 works efficiently when the units and parts are installed according to the inventor's patent specifications, with an oil pressure of 500 to 1000 bar. If you now make the cross-section of the high-pressure pump piston 52 about four times smaller than that of the follower piston 49, then you have a four-fold pressure transmission, with the result that the high-pressure pump piston 52 then operates at 2000 or 4000 bar, i.e. in the chamber parts 35 and 37 a pressure of 2000 and 4000 bar is generated when the master piston 15 generates a pressure of 500 and 1000 bar. Other pressure ranges and translations can be chosen as long as the system is sufficiently stable.
  • the separating body 36 of FIGS. 2 and 3 is replaced by a clamped membrane 61. This is held by means of the insert 91 in the housing 1 in seats for its board 62, the screws 92 may be used to fasten the holding insert 91. It should be noted here that it is not a pumping membrane of conventional use, but a fluid separation membrane. Common diaphragms are used as pumps at the high pressures that the invention would be. As a separating membrane for preventing the mixing of the first fluid with the second fluid in the chambers 35 and 37, the membrane is loaded with the same pressure from both ends. It therefore does not carry any pump load and is not exposed to any pump load.
  • This membrane 61 is advantageously made of stainless steel or carbon fiber if you want to drive with water in the chamber part 37. Carbon fiber has the advantage that, by selecting the heat during the production of the fiber, a large selection range for the elastic modulus of the membrane 61 is available.
  • diaphragm pump sets are arranged radially around the shaft 1154, of which FIG. 5 shows a longitudinal section above the shaft.
  • eccentric lifting disks 1153 act on piston shoes 541 of master piston 540
  • eccentric lifting disks 13 indicate the piston shoes of another of the three, five or seven (or more) around shaft 1154, but are not drawn to exact dimensions and are not drawn in position.
  • the line 1150 supplies lubricating fluid from the outside at a sufficiently high pressure to supply the hydrostatic bearings of the piston shoes and / or the master piston 540 with lubricating fluid, which can get into the pressure fluid pockets through the lines 1149.
  • the master piston 540 drives the reciprocating piston 52 for the pressure stroke.
  • each reciprocating piston 52 is assigned two opposing diaphragm pumps with diaphragms 61 between the respective outer chamber 35 and the inner chamber 37.
  • the inventive and technical significance of the unit of the figure is that the spaces containing hydraulic fluid have been restricted to such a minimum volume that the unit can reach several thousand bars instead of the few hundred bars of the known technology and also that the oil space is one received the smallest volume.
  • Fig. 6 shows that in practice it is not always correct to form conical inner chambers 37 above membranes.
  • the head cover 1001 therefore has an arched abutment wall 1151 which is shaped according to an elastic line and against which the membrane 61 with the curve 1152 can rest well without excessive local stresses within the membrane.
  • the contact surfaces will also be formed in FIG. 5, but this is difficult to draw, so that straight cones are drawn in FIG. 5.
  • the head cover 11 is attached to the housing 1 of the unit.
  • the membrane is arranged directly or indirectly between the housing 1 and the head cover 11, the outer chamber 35 being formed on one end of the membrane 61 and the inner chamber 37 being arranged on the other side of the membrane 61.
  • the cylinder (s) 1535 with the reciprocating piston 52 reciprocable therein leads to the outer chamber 35.
  • the inlet channel with the inlet valve 38 leads to the inner chamber 37 and the outlet channel with the outlet valve 39 is arranged away from the inner chamber.
  • Fluid is pressed into the inner chamber and filled by the inlet valve 38. Thereafter, the piston 52 is moved in the cylinder towards the outer chamber 35 and thereby delivers fluid under pressure into the outer chamber 35.
  • the drive of the piston 52 can e.g. as in my parallel patent applications or as in my published patent applications or in any other appropriate and appropriate manner.
  • the fluid in the cylinder 1535 compresses until the pressure in the outer chamber 35 is equal to that in the inner chamber 37.
  • the fluids in the outer chamber 35 and the inner chamber 37 continue to compress until the pressure exceeds the pressure beyond the outlet valve 39 when the inlet valve 38 is closed. If this pressure is exceeded, the outlet valve 39 opens and the fluid from the inner chamber 37 is delivered via the outlet valve 39 until the inner chamber 37 is emptied, all the fluid is conveyed and the membrane 61 is e.g. comes to rest on the bearing surface 1513.
  • the position, the shape and the distance of the contact surfaces 1513, 1514 from the neutral position of the membrane 61 shown in the figures are so dimensioned and arranged that the stresses which arise during the deformation of the membrane 61 remain so low that the fatigue strength of the membrane 61, for example of significantly more than 6 million strokes are achieved.
  • the stainless steel membrane is approximately 1 mm thick or thinner, preferably 0.2 to 0.4 mm, and the maximum distance between the contact surfaces 1513, 1514 is approximately three times shorter in the axial direction than shown in the figures.
  • the axial distance described is drawn in an exaggerated manner so that the two chambers 35 and 37 can be clearly seen in the figures.
  • stainless steel of about 1 mm thickness has a stroke of approximately 1.5 mm in the direction of the surface and the same stroke length to surface 1514 from the neutral position of the membrane, provided that the life is long enough wants to get.
  • the free space 1515 is arranged radially outside the membrane 1506 and the free space 1522 is arranged radially outside the membrane 1520 so that the membrane with its radially outer part is movable in this free space and radially expand and contract therein can.
  • the membrane with its radially outer parts is held between flat surfaces and is radially movable between them, into which ring grooves for inserting the sealing rings (plastic sealing rings) 1528, 1529, 1511, 1512 are incorporated.
  • These flat surfaces 1538, 1539 for holding the membrane are located on the head cover 11 and the housing 1 or on the inserts 1507 and 1508.
  • the narrow are advantageously in the invention Channels 1509 with small cross sections arranged. Their cross sections are advantageously so narrow that the membrane parts cannot be squeezed into them.
  • the cross-sections through the channels 1509 can be kept so narrow that their cross-section is not greater than the cross-sectional surface above or below the channels 1509, directed transversely through the membrane.
  • a corresponding number of channels are arranged, for example in parts 1507 and 1508.
  • Metal membranes must be thin, because previous patent applications by the applicant and inventor show from their mathematical analyzes that thicker membranes suffer significantly higher stresses at the same strokes than thin membranes and high stresses limit the service life. Thin metal membranes would also push into channels 1509 at several thousand bars. Pieces of the diameter of the channels 1509 are then punched out of the membrane 61 under the high fluid pressure and fall into the channels 1509. The membrane is then leaky. It is true that these phenomena can be avoided by passing a little less pressure fluid into the outer chamber 35, thus allowing the piston 52 to travel shorter strokes, so that the upper end face of the membrane does not touch the end face 1513 and thus does not reach the channels 1509. Then, however, dead space arises in the inner chamber 37, in which fluid is compressed under high pressure, and this then leads to Loss of delivery rate and loss of efficiency of the unit.
  • the pump housing part 1 is provided with a recess in which the control body 1716 is arranged to be axially movable, that is to say reciprocal: in the pump housing 1 there is the recess 1714 from which bores 1719 go to the prechamber 1723.
  • the pump housing 1 Radially within the bores 1719, the pump housing 1 has the valve guide surface 1715, which is a cylindrical surface and serves to guide the cylindrical outer surface 1724 of the valve 1716.
  • the stopper eg clamping ring
  • the stopper 1725 which can be moved continuously but not further down in the recess 1714 because its path on the bottom 1761 of the recess 1714 is limited by starting.
  • the bore 1717 in the valve for receiving a weak compression spring 1718, which presses the valve 1716 down at times when there are no opposing forces until the clamping ring 1725 abuts the bottom 1761 of the recess 1714.
  • the prechamber 1723 is formed in the pump housing 1 in that a conical wall 1722 is formed which tapers radially downward and ends in the very short cylindrical end 1720.
  • the valve head is provided with a short cylindrical surface 1710, the adjacent surfaces 1764, 1765 either touching appropriately or having a very narrow gap between them (less than 0.3 mm). Tapering radially upwards is followed by the conical surface 1721, which can finally change into a backward rotation - without reference numerals - and finally the prechamber 1723 is closed on the cylindrical outer surface 1724.
  • the pre-pressure fluid coming from the inlet valve 38 presses the membrane 61 downwards, which may come to rest on the end face 1514. So that it is not pressed into the cylinder and damaged, the collecting chamber 35 may be arranged above the piston 52, from which small bores then extend upwards to the outer chamber 35, the diameter of which is so small that the diaphragm 61 at the low admission pressure cannot penetrate it.
  • the inner chamber 37 is now completely filled with fluid and the membrane 61 is ideally in contact with surface 1514 with its lower end face.
  • the spring 1718 pressed the valve body 1716 downward following the upper end face of the membrane 1704 until the clamping ring 1718 came to rest on the bottom surface of the recess 1714.
  • the inclined surface 1721 moves so far down that a further annular gap opens around it relative to the pump housing 1, through which the inlet fluid can fill the inner chamber 37 comfortably and without great flow resistance under its low admission pressure.
  • the pump stroke now begins, in which the piston 52 runs upward and presses fluid into the outer chamber 35. This fluid pushes the membrane 61 upwards, whereby pressure medium through the opening between the inclined surface 1721 and the pump housing 1 upwards through the prechamber 1723 and the bores 1719 into the recess 1714 and from there through the (in FIG.
  • Exhaust valve 39 flows out of the inner chamber of the pump.
  • the membrane 61 presses the control body (the valve) 1716 upwards until it reaches its upper position at the end of the pump stroke, as in FIG. 8. All fluid is pressed out of the inner chamber 37.
  • the annular gap 1772 between the surfaces 1720 can be formed to a diameter of up to 0.3 mm (or less).
  • membranes can be arranged in a common housing and work on a common manifold. This means that the pump delivery rate can be multiplied according to the number of diaphragms of the same dimensions.
  • FIG. 10 shows a cross section around the radially outer part of a membrane element which is bent twice with radii "" around the circular lines "P" in a radial magnification of ten times and one hundred times axially. This enlargement is chosen in order to be able to see the stresses due to longitudinal changes directly.
  • the middle fiber of the element of the same thickness "t” is drawn in dashed lines, as are the upper and lower outer fibers, which are solid lines.
  • the stroke is "f”. Below you can see the element in unstressed condition in horizontal dashed lines.
  • the membrane element can be kept uniformly thick if it is kept flat on the inner third of the radius and if the control body 1716 of FIG. 8 is installed in the pump, delimiting the inner chamber and forming the run-up wall for the membrane. Metal membranes with a thickness of 0.2 to 0.4 mm then have a long service life.
  • the radial changes in metal elements should not exceed about 0.3% of the original diameter and, if possible, should not exceed 0.9% in the case of Teflon.
  • Teflon or other plastic elements or membranes one must expect that the high pressure compresses the thicknesses of these elements, so that they form waves because they cannot expand radially due to the clamping.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP19900114874 1987-04-07 1987-04-07 Pompe à haute pression Withdrawn EP0400693A3 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP19900114874 EP0400693A3 (fr) 1987-04-07 1987-04-07 Pompe à haute pression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP19870105118 EP0285685A1 (fr) 1987-04-07 1987-04-07 Ensemble d'écoulement de fluide avec des éléments flexibles en direction axiale et délimitant des chambres pour des pressions jusqu'à plusieurs milliers d'atmosphères
EP19900114874 EP0400693A3 (fr) 1987-04-07 1987-04-07 Pompe à haute pression

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP87105118.1 Division 1987-04-07
EP19870105118 Division EP0285685A1 (fr) 1987-04-07 1987-04-07 Ensemble d'écoulement de fluide avec des éléments flexibles en direction axiale et délimitant des chambres pour des pressions jusqu'à plusieurs milliers d'atmosphères

Publications (2)

Publication Number Publication Date
EP0400693A2 true EP0400693A2 (fr) 1990-12-05
EP0400693A3 EP0400693A3 (fr) 1991-02-20

Family

ID=8196902

Family Applications (2)

Application Number Title Priority Date Filing Date
EP19900114874 Withdrawn EP0400693A3 (fr) 1987-04-07 1987-04-07 Pompe à haute pression
EP19870105118 Withdrawn EP0285685A1 (fr) 1987-04-07 1987-04-07 Ensemble d'écoulement de fluide avec des éléments flexibles en direction axiale et délimitant des chambres pour des pressions jusqu'à plusieurs milliers d'atmosphères

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP19870105118 Withdrawn EP0285685A1 (fr) 1987-04-07 1987-04-07 Ensemble d'écoulement de fluide avec des éléments flexibles en direction axiale et délimitant des chambres pour des pressions jusqu'à plusieurs milliers d'atmosphères

Country Status (1)

Country Link
EP (2) EP0400693A3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0905374A1 (fr) * 1997-09-25 1999-03-31 Mitsubishi Denki Kabushiki Kaisha Pompe à piston à haute pression pour injection de carburant avec amortisseurs de pulsation
EP0947691A3 (fr) * 1998-03-31 2002-12-11 Mitsubishi Denki Kabushiki Kaisha Une butée d'arrêt d'un diaphragme pour un accumulateur à haute pression
EP0950809A3 (fr) * 1998-04-15 2002-12-11 Mitsubishi Denki Kabushiki Kaisha Accumulateur à haute pression
WO2006037672A1 (fr) * 2004-10-06 2006-04-13 Siemens Aktiengesellschaft Pompe haute pression
EP1798415A1 (fr) * 2005-12-14 2007-06-20 Siemens Aktiengesellschaft Pompe à haute pression

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5292235A (en) * 1986-09-26 1994-03-08 Karl Eickmann Membranes and neighboring members in pumps, compressors and devices
DE102016210737A1 (de) * 2016-06-16 2017-12-21 Robert Bosch Gmbh Förderpumpe für kryogene Kraftstoffe
CN108543352B (zh) * 2018-06-14 2023-12-12 成都易态科技有限公司 滤芯接头及其组件
CN110845121B (zh) * 2019-11-20 2022-06-07 成都中光电科技有限公司 一种适应高温蠕变的溢流砖结构
CN117907091B (zh) * 2024-03-19 2024-06-07 巴彦淖尔京能清洁能源电力有限公司 一种大型风力发电机主轴硬度检测装置

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB686457A (en) * 1949-10-26 1953-01-28 Howard James Louis Herne Improvements in and relating to diaphragm pumps
FR1188239A (fr) * 1957-06-14 1959-09-21 Andreas Hofer Hochdruck Appbau Compresseur à diaphragmes à plusieurs étages
DE1118011B (de) * 1957-11-27 1961-11-23 Milton Roy Co Pumpe mit Fluessigkeitsantrieb
US3668978A (en) * 1970-06-03 1972-06-13 Duriron Co Diaphragms for high pressure compressors and pumps
DE1728451A1 (de) * 1966-07-28 1972-07-27 Yarway Corp Pumpenanordnung
FR2119364A5 (fr) * 1970-12-21 1972-08-04 Wagner Josef

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3200665A1 (de) * 1981-01-13 1984-02-09 Karl 7180 Crailsheim Eickmann Konische ringelelemente und von fluid durchstromte aggregate
DE3536661A1 (de) * 1984-10-15 1986-04-30 Karl 7180 Crailsheim Eickmann Anordnungen an federbaren konischen ringen
EP0216956A2 (fr) * 1985-09-30 1987-04-08 Karl Eickmann Groupe, écoulé de fluide, avec des éléments flexibles en direction axiale et délimitant des chambres pour des pressions jusqu'à plusieurs milliers d'atmosphères

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB686457A (en) * 1949-10-26 1953-01-28 Howard James Louis Herne Improvements in and relating to diaphragm pumps
FR1188239A (fr) * 1957-06-14 1959-09-21 Andreas Hofer Hochdruck Appbau Compresseur à diaphragmes à plusieurs étages
DE1118011B (de) * 1957-11-27 1961-11-23 Milton Roy Co Pumpe mit Fluessigkeitsantrieb
DE1728451A1 (de) * 1966-07-28 1972-07-27 Yarway Corp Pumpenanordnung
US3668978A (en) * 1970-06-03 1972-06-13 Duriron Co Diaphragms for high pressure compressors and pumps
FR2119364A5 (fr) * 1970-12-21 1972-08-04 Wagner Josef

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0905374A1 (fr) * 1997-09-25 1999-03-31 Mitsubishi Denki Kabushiki Kaisha Pompe à piston à haute pression pour injection de carburant avec amortisseurs de pulsation
US6135734A (en) * 1997-09-25 2000-10-24 Mitsubishi Denki Kabushiki Kaisha High-pressure fuel pump unit for in-cylinder injecting type engine
EP0947691A3 (fr) * 1998-03-31 2002-12-11 Mitsubishi Denki Kabushiki Kaisha Une butée d'arrêt d'un diaphragme pour un accumulateur à haute pression
EP0950809A3 (fr) * 1998-04-15 2002-12-11 Mitsubishi Denki Kabushiki Kaisha Accumulateur à haute pression
WO2006037672A1 (fr) * 2004-10-06 2006-04-13 Siemens Aktiengesellschaft Pompe haute pression
EP1798415A1 (fr) * 2005-12-14 2007-06-20 Siemens Aktiengesellschaft Pompe à haute pression

Also Published As

Publication number Publication date
EP0400693A3 (fr) 1991-02-20
EP0285685A1 (fr) 1988-10-12

Similar Documents

Publication Publication Date Title
DE4138313C2 (de) Radialkolbenpumpe
EP1592887B1 (fr) Pompe haute pression
DE102009038869B4 (de) Vorrichtung zum dosierten Ausgeben eines Schmiermittels
DE4321800C2 (de) Ventiltelleranordnung für ein Rückschlagventil
DE102009036663B4 (de) Innenhochdruckumformwerkzeug und ein Verfahren zum Betreiben dessen
DE102006015845B3 (de) Verfahren zum Betreiben einer oszillierenden Verdrängerpumpe und oszillierende Verdrängerpumpe
DE3934124A1 (de) Druckluftgetriebene pumpenanordnung
DE2833139C2 (de) Hydraulische Pumpenvorrichtung
EP0400693A2 (fr) Pompe à haute pression
DE3042328C2 (de) Kolbenpumpe
EP2464868B1 (fr) Machine à membranes
DE3345436A1 (de) Kanal- und schlitzanordnung fuer ein paar benachbarter zylinder
DE3102506C2 (de) Kolbenpumpe mit geregelter Förderleistung
CH652805A5 (de) Druckumsetzer mit mindestens drei oelhydraulisch angetriebenen kolben.
DE2540879C2 (fr)
DE102004019626B4 (de) Kraftstoffeinspritzpumpe und Dreh-/Linearbewegungsumwandlungsmechanismus mit Sicherungseinrichtung
EP1843040B1 (fr) Procédé d'utilisation d'une pompe volumétrique oscillantes et pompes volumétriques oscillantes
DE2416951A1 (de) Hydraulischer verstaerker
DE3632717A1 (de) Aggregat mit einer membrane
DE3635156A1 (de) Aggregat, zum beispiel pumpe, zum betrieb mit hohen fluid drucken bis zu mehreren tausend bar
DE2218391A1 (de) Radialkolbenpumpe
DE2419220A1 (de) Schmiedepresse
EP0208683A1 (fr) Pompe hydraulique
EP0301303A1 (fr) Pompe à pistons pour la compression de fluides ou de gaz
DE4200576A1 (de) Hochdruck-anordnungen

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19900912

AC Divisional application: reference to earlier application

Ref document number: 285685

Country of ref document: EP

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT CH DE FR GB IT LI NL SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT CH DE FR GB IT LI NL SE

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19921103