EP1760312A2 - Pompe haute pression - Google Patents

Pompe haute pression Download PDF

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Publication number
EP1760312A2
EP1760312A2 EP06026525A EP06026525A EP1760312A2 EP 1760312 A2 EP1760312 A2 EP 1760312A2 EP 06026525 A EP06026525 A EP 06026525A EP 06026525 A EP06026525 A EP 06026525A EP 1760312 A2 EP1760312 A2 EP 1760312A2
Authority
EP
European Patent Office
Prior art keywords
piston
pressure pump
pump according
pressure
space
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
EP06026525A
Other languages
German (de)
English (en)
Other versions
EP1760312B1 (fr
EP1760312A3 (fr
Inventor
Marco Ganser
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.)
Ganser Hydromag AG
Original Assignee
Ganser Hydromag 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 Ganser Hydromag AG filed Critical Ganser Hydromag AG
Publication of EP1760312A2 publication Critical patent/EP1760312A2/fr
Publication of EP1760312A3 publication Critical patent/EP1760312A3/fr
Application granted granted Critical
Publication of EP1760312B1 publication Critical patent/EP1760312B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • 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
    • 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
    • F04B1/0413—Cams
    • 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
    • F04B53/04—Draining
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for

Definitions

  • the invention relates to a high pressure pump according to the preamble of claim 1, which is particularly suitable for use in a fuel injection system for internal combustion engines.
  • a generic high-pressure pump for a fuel injection device for internal combustion engines in which the piston of a piston pump unit is driven harmoniously by an eccentric drive.
  • the piston carries at its end facing away from the working space of the piston pump unit end a sliding shoe, which rests with a sliding surface on a sliding bearing surface of a lifting ring.
  • the cam ring is rotatably mounted on an eccentric pin of a drive shaft and is driven revolving, but not rotating.
  • the drive shaft, the eccentric pin, the cam ring and the shoe are housed in a low-pressure space, which serves as a supply space for the medium to be conveyed, ie fuel.
  • a relief space is formed, which is open to the sliding bearing surface and via a passage which extends in the longitudinal direction of the pump piston, with the working space is in direct hydraulic communication. The discharge space is therefore filled with the fuel to be delivered.
  • the lubrication of the sliding bearing between the shoe and the cam ring is effected by the fuel in the discharge chamber.
  • the bearing between the eccentric pin and the cam ring is lubricated by the located in the low-pressure space fuel.
  • fuel is known to have poor lubricating properties and therefore can only develop a limited lubricating effect.
  • the present invention is now based on the object to provide a high-pressure pump of the type mentioned for very high discharge pressures and large flow rates, the production costs are as low as possible and can meet the high demands on the reliability and life.
  • the inventive design of the high pressure pump significantly improved lubrication of the sliding bearing between the cam and the piston and also the bearing between the cam and the crank drive is possible.
  • the risk of Anfressens this camp is greatly reduced even at high load, which contributes to increased reliability and a long life.
  • the high-pressure pump 1 shown in FIGS. 1 to 4 which is intended for use in a fuel injection system for internal combustion engines, has two diametrically opposed piston pump units 2, 2 '(plunger pump units), which have the same design and operate in push-pull.
  • Each piston pump unit 2, 2 ' has a housing block 3, which is fixedly connected to a pump housing 4 and projects into the interior 5 of this pump housing 4.
  • each Piston pump unit 2, 2 ' has a piston 6 (plunger), which is guided with a tight sliding fit in a cylinder bore 7 in the housing block 3 linearly movable.
  • the piston 6 bounded with an end face 6a a working space 8 and extends at its opposite end to a foot part 9.
  • This foot part 9 has a flat sliding surface 10 which rests on a sliding bearing surface 11 which is provided on a cam ring 12.
  • This cam ring 12 is common to both piston pump units 2, 2 '.
  • a crank drive 13 is provided, which has a drive shaft 14 shown in dashed lines and an eccentric element 15 fixedly connected thereto.
  • the drive shaft 14 is driven circumferentially about its axis of rotation 14a (FIG. 1).
  • the eccentric element 15 is arranged with an eccentricity e (FIG. 1) with respect to the axis of rotation 14a of the drive shaft 14.
  • the eccentric element 15 is rotatable but not co-rotating on the eccentric element 15.
  • the cam ring 12 When rotating the drive shaft 14, the cam ring 12 is moved on the one hand parallel to the slide bearing surfaces 12 and on the other hand perpendicular to the axis of rotation 14a of the drive shaft 14, in each direction by the amount 2e. The cam ring 12 is thus displaced in operation relative to the foot part 9 of the piston 6 back and forth.
  • the pistons 6 of the piston pump units 2, 2a execute a stroke, which is also 2e, ie twice the eccentricity e.
  • an inlet line 18 is formed, which communicates with the working space 8 via a pressure-controlled inlet valve 19 (FIG. 1).
  • the inlet conduit 18 is connected to a supply conduit, not shown, which communicates with a liquid reservoir, i. in the present case with a fuel tank, is connected, for example via a prefeed pump.
  • an outlet line 20 is further provided, which is connected via a pressure-controlled outlet valve 21 with the working space 8 (Fig. 1).
  • the outlet conduit 20 is connected to a high pressure space, e.g. the common rail of a fuel injection system connected.
  • a relief space 22 is formed in the foot part 9 of the piston 6, which is open to the sliding bearing surface 11.
  • a continuous, coaxial passage 23 which is open on the one hand to the working space 8 and on the other hand to the discharge space 22 (the passage 23 could also be desachsiert).
  • This passage 23 whose diameter changes, includes a longitudinal bore 24 in which a control piston 25 is slidably guided with a tight sliding fit, which serves as a pressure transmission element.
  • the control piston 25 rests on a compression spring 26, which is supported at the other end on a spring ring 27 (FIG. 2), which is held in the piston 6.
  • annular groove 28 is formed, which extends around the piston 6 around and to the cylinder bore 7 is open.
  • a transverse bore 29 is present, which passes through the piston 6 and at both ends with the annular groove 28 in connection stands.
  • a drain line 30 is connected, which runs in the housing block 3 and which is connected to a return line, not shown, which leads to a collecting reservoir, which may be the fuel tank.
  • a collecting reservoir which may be the fuel tank.
  • the eccentric element 15 is provided with a lubrication groove 31 which extends along a part of the circumference and is open towards the cam ring 12.
  • the lubrication groove 31 is connected via a radial bore 32 in the eccentric element 15 with a feed channel 33 which extends in the direction of the axis of rotation 14a of the drive shaft 14 and which is connected via a lubricant pump, not shown, with a lubricant reservoir.
  • a lubricant preferably lubricating oil, with a pressure of e.g. 2 - 6 bar supplied.
  • two connecting channels 34, 35 are formed, each of which leads from the inner surface 12 a of the cam ring 12 to one of the sliding bearing surfaces 11.
  • the lubrication groove 31, which is permanently connected to the feed channel 33 is only in certain rotational positions of the eccentric element 15 with a connecting channel 34, 35 in combination, as shown in FIGS. 1-3.
  • FIG. 1 shows the rotational position of the eccentric element 15 in which the piston 6 of the one upper piston pump unit 2 in the figures is in the lower end position, ie, at the end of the suction stroke.
  • the piston 6 of the other, lower piston pump unit 2 'has the end of Delivery stroke and thus reached its upper end position.
  • the connection channels 34, 35 are not in connection with the lubrication groove 31 nor with the associated relief space 22.
  • the delivery stroke begins for the piston 6 of the upper piston pump unit 2, ie the piston 6 is displaced upward in the direction of the arrow A (FIG. 2).
  • the inlet valve 19 is closed, which also applies to the outlet valve 21 at the beginning of the delivery stroke.
  • the pressure in the working space 8 increases.
  • the control piston 25, which is acted upon at its the working space 8 facing end face by the pressure of the liquid in the working chamber 8 is moved against the action of the compression spring 26 downward in the direction of arrow D in Fig. 2. This has the consequence that the pressure of the lubricant, which is located in the relief chamber 22 and in the region of the passage 23 located below the control piston 25, increases.
  • FIGS. 3 and 4 the situation after a rotation of the drive shaft 14 is shown by now a total of 270 °.
  • the piston 6 has reached its center position during the suction stroke.
  • the cam ring 12 now assumes its left end position, which is shown in Fig. 4 in solid lines.
  • This Fig. 4 shows that the cam ring 12 in the direction of the sliding bearing surface 11 performs a total stroke C, which is equal to 2e, so the double eccentricity e.
  • left end position of the cam ring 12 is now the connecting channel 34 in the cam ring 12 with the discharge chamber 22 and the lubrication 31 in connection.
  • liquid (fuel) from the working space 8 can pass over the upper portion of the passage 23 and through the very small gap between the control piston 25 and the wall of the longitudinal bore 24.
  • This leakage liquid passes via the transverse bore 29 in the piston 6 also in the annular groove 28.
  • lubricant lubricating oil
  • This leak lubricant also passes via the transverse bore 29 into the annular groove 28.
  • the mixture of liquid (fuel and lubricant (lubricating oil)) in the annular groove 28 is led away via the drain line 30 and is e.g. into the liquid reservoir, i. the fuel tank, returned.
  • annular groove 36 is additionally formed coaxial with the relief space 22 and to slide bearing surface 11 is open.
  • This annular groove 36 communicates with a cam ring 12 formed in the sliding surface 10 toward open longitudinal groove 37 in conjunction.
  • This longitudinal groove 37 is offset from the cutting plane of FIG. 3 (which runs perpendicular to the rotational axis 14a and in the center of the lifting ring 12) in the direction of the rotational axis 14a of the drive shaft 14 and opens into the interior 5 at both ends the pump housing 4 (Fig. 4).
  • the leakage liquid (lubricating oil) entering this annular groove 36 is returned to the interior 5 via the longitudinal groove 37.
  • the pressure distribution along the sliding surface 10 or the sliding bearing surface 11 is changed from the relief space 22 in the radial direction to the outside, which has a favorable influence on the amount of leakage fluid.
  • the second embodiment of a high-pressure pump 1 'shown in FIG. 5 differs from the first embodiment according to FIGS. 1-4 by another embodiment of the pressure-transmitting element arranged in the piston 6.
  • Fig. 5 which corresponds to the representation of FIG. 2, the same reference numerals are used for parts that are the same in both embodiments as in Figs. 1-4.
  • the piston 6 consists of a piston element 38 guided in the cylinder bore 7 and a ring 39 which is fixedly connected to the end of the piston element 38 at the working space 8, e.g. by pressing or shrinking.
  • the ring 39 rests with a sliding surface 10 on the sliding bearing surface 11 on the cam ring 12 and has a flange 40 on which the compression spring 17 is supported.
  • This compression spring 17 ensures - as described with reference to FIGS. 1 - 3 - that the ring 39 remains in contact with the cam ring 12.
  • the sliding surface 10 is formed on the ring 39.
  • the flange 40 could also be formed as a separate part, analogous to the bearing ring 16 of FIG. 2.
  • an elastically deflectable membrane 41 is arranged along its edge region between the ring 39 and the piston member 38 is sealingly clamped.
  • This serving as a pressure-transmitting element membrane 41 spans the limited by the inner annular wall 39a relief space 22 and separates this relief space 22 formed by a piston member 38 chamber 42.
  • This chamber 42 opens a longitudinal bore 43 which extends in the direction of the longitudinal axis of the piston member 38 and over which the chamber 42 communicates with the working space 8.
  • the longitudinal bore 43 and the chamber 42 form the passage 23.
  • the chamber 42 is filled with the liquid to be conveyed, ie with fuel.
  • the pressure in the chamber 42 changes in the same direction as the pressure in the working space 8.
  • the diaphragm 41 is moved downwards in the direction of pressurization, i. to slide bearing surface 11 out, deflected. This leads to an increase in pressure in the lubricant-containing relief space 22 and thus to a hydrostatic pressure relief, as already described with reference to FIGS. 1-4. Since the pressures on both sides of the diaphragm 41 are practically the same, the stress on the diaphragm 41 is low. This can thus be thin-walled and elastic.
  • annular groove 28 which is present in the first exemplary embodiment according to FIGS. 1-3, together with the outflow line 30 for collecting and removing leakage fluid is not shown, but can also be provided if required.
  • the membrane 41 is attached to the working space 8 facing end surface 6a of the piston 6.
  • the attachment of the membrane 41 could take place by welding the same or, as in FIG. 5, with a screwed, pressed or shrunk holding part.
  • the passage 23 is then below the membrane 41, it is filled with the lubricant and communicates directly with the relief space 22nd
  • the mode of operation of the embodiment shown in FIG. 5 corresponds to the mode of operation described with reference to FIGS.
  • a high-pressure pump 1, 1 ' according to the invention described in connection with FIGS. 1-5 have the advantage that by arranging a pressure-transmitting element, i. a control piston 25 or a membrane 41, in the working space 8 and the discharge chamber 22 connecting passage 23, the media in the working space 8 and the discharge chamber 22 are separated from each other.
  • a pressure-transmitting element i. a control piston 25 or a membrane 41
  • the media in the working space 8 and the discharge chamber 22 are separated from each other.
  • a suitable lubricant in the region of the cam ring 12 and the crank drive 13, regardless of the medium to be pumped (fuel).
  • the desired pressure relief of the sliding bearing which is formed by the sliding surface 10 on the piston 6 and the sliding bearing surface 11 on the cam ring 12, achieved without great design effort.
  • the piston 6 has no transverse bore 29. Due to the tight sliding fit and the present invention achieved pressure conditions on both sides of the control piston 25, the leakage of the working space 8 facing side in the discharge chamber 22 are kept very low.
  • control piston 25 has a larger diameter than shown in FIGS. 1-3.
  • the longitudinal bore 24 for guiding the control piston 25 in close sliding fit can be open towards the top in the direction of the working chamber 8.
  • the narrower in cross section part of the passage 23 is again below the control piston 25 and communicates directly with the relief chamber 22.
  • the control piston 25 is installed from above into the piston 6.
  • a spring ring, analogous to the spring ring 27 according to FIG. 2 then prevents the control piston from exiting above the end surface 6a.
  • the longitudinal bore 24 can also be continuous in the piston 6.
  • the remaining part of the passage 23 has the same diameter as the longitudinal bore 24. It is also conceivable to form the remaining portion of the passage 23 slightly larger than the diameter of the longitudinal bore 24.
  • a separation of foot part 9 and piston 6 into two parts, analogously as in the DE-A-197 05 205 and the corresponding US-A-6,077,056 shown in Fig. 4 is also applicable.
  • the inner surface 12a of the cam ring 12, together with the associated surface of the Exenterides 15, in the direction of the rotation axis 14a slightly convex or even slightly longitudinal in the longitudinal and transverse directions. In this case, it is recommended to design the cam ring 12 in two parts for assembly reasons.
  • piston pump unit 2 instead of two piston pump units 2, 2 'as shown in FIG. 1, only one piston pump unit 2 can be provided.
  • more than two piston pump units with corresponding sliding surfaces 11 of the cam ring 12 can be radially mounted, e.g. 3 by 120 °, or 4 by 90 °, or 6 offset by 60 ° piston pump units with a common cam ring 12th
  • high-pressure pumps 1, 1 are intended for use in fuel injection systems of internal combustion engines, in particular of diesel engines, these pumps can also be used in other fields.
  • control piston 25 is moved solely by acting on the two end faces pressure forces.
  • control piston 25 it is also possible to form the control piston 25 with two different diameters. If the end face facing the working space 8 is then larger than the one facing the relief space, a pressure transmission takes place. In the opposite case, a pressure reduction. In these embodiments, it may be advantageous to form the control piston 25 of two separate parts, each with the appropriate diameter. If the holes with the correspondingly larger diameter and those with the corresponding smaller diameter are not precisely aligned, tolerance and friction problems can thus be prevented.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Fuel-Injection Apparatus (AREA)
EP06026525.3A 2003-02-11 2003-12-04 Pompe haute pression Expired - Lifetime EP1760312B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2022003 2003-02-11
EP03773421A EP1592887B1 (fr) 2003-02-11 2003-12-04 Pompe haute pression

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP03773421A Division EP1592887B1 (fr) 2003-02-11 2003-12-04 Pompe haute pression
EP03773421.7 Division 2003-12-04

Publications (3)

Publication Number Publication Date
EP1760312A2 true EP1760312A2 (fr) 2007-03-07
EP1760312A3 EP1760312A3 (fr) 2007-09-05
EP1760312B1 EP1760312B1 (fr) 2013-05-01

Family

ID=32855128

Family Applications (2)

Application Number Title Priority Date Filing Date
EP06026525.3A Expired - Lifetime EP1760312B1 (fr) 2003-02-11 2003-12-04 Pompe haute pression
EP03773421A Expired - Lifetime EP1592887B1 (fr) 2003-02-11 2003-12-04 Pompe haute pression

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP03773421A Expired - Lifetime EP1592887B1 (fr) 2003-02-11 2003-12-04 Pompe haute pression

Country Status (8)

Country Link
US (2) US7108491B2 (fr)
EP (2) EP1760312B1 (fr)
JP (1) JP2006514195A (fr)
CN (1) CN100392241C (fr)
AT (1) ATE355460T1 (fr)
AU (1) AU2003281906A1 (fr)
DE (1) DE50306704D1 (fr)
WO (1) WO2004072477A1 (fr)

Cited By (1)

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WO2009112308A1 (fr) * 2008-03-13 2009-09-17 Robert Bosch Gmbh Pompe haute pression pour distribuer du carburant à un moteur à combustion interne

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ATE355460T1 (de) * 2003-02-11 2006-03-15 Ganser Hydromag Hochdruckpumpe
ES2355146T3 (es) * 2004-02-25 2011-03-23 Ganser-Hydromag Ag Válvula de inyección de combustible para una máquina de combustión interna.
US7134846B2 (en) * 2004-05-28 2006-11-14 Stanadyne Corporation Radial piston pump with eccentrically driven rolling actuation ring
WO2006037672A1 (fr) * 2004-10-06 2006-04-13 Siemens Aktiengesellschaft Pompe haute pression
US7278443B2 (en) 2004-12-16 2007-10-09 Diversified Dynamics Corporation Pulsation causing valve for a plural piston pump
US7290561B2 (en) 2004-12-16 2007-11-06 Diversified Dynamics Corporation Pulsation causing valve for a plural piston pump
US20060140778A1 (en) * 2004-12-28 2006-06-29 Warren Leslie J Reciprocating positive displacement pump for deionized water and method of cooling and lubricating therefor
FR2904665B1 (fr) * 2006-08-04 2008-10-31 Siemens Automotive Hydraulics Pompe transfert pour injection d'essence a haute pression
DE102007011192A1 (de) * 2007-03-06 2008-09-18 Perma-Tec Gmbh & Co. Kg Dosiervorrichtung für einen Schmierstoffspender
US8328538B2 (en) * 2007-07-11 2012-12-11 Gast Manufacturing, Inc., A Unit Of Idex Corporation Balanced dual rocking piston pumps
ES2542856T3 (es) * 2007-10-12 2015-08-12 Delphi International Operations Luxembourg S.À R.L. Mejoras relacionadas con bombas de combustible
US8986253B2 (en) 2008-01-25 2015-03-24 Tandem Diabetes Care, Inc. Two chamber pumps and related methods
DE102008001713A1 (de) * 2008-05-13 2009-11-19 Robert Bosch Gmbh Radialkolbenpumpe
US8182247B2 (en) * 2008-05-27 2012-05-22 Txam Pumps Llc Pump with stabilization component
US8408421B2 (en) 2008-09-16 2013-04-02 Tandem Diabetes Care, Inc. Flow regulating stopcocks and related methods
WO2010033878A2 (fr) 2008-09-19 2010-03-25 David Brown Dispositif de mesure de la concentration d’un soluté et procédés associés
EP3284494A1 (fr) 2009-07-30 2018-02-21 Tandem Diabetes Care, Inc. Système de pompe à perfusion portable
JP5633387B2 (ja) * 2011-01-24 2014-12-03 株式会社デンソー 燃料供給ポンプ
US9180242B2 (en) 2012-05-17 2015-11-10 Tandem Diabetes Care, Inc. Methods and devices for multiple fluid transfer
US9555186B2 (en) 2012-06-05 2017-01-31 Tandem Diabetes Care, Inc. Infusion pump system with disposable cartridge having pressure venting and pressure feedback
EP2711547B1 (fr) * 2012-09-24 2019-06-05 Continental Automotive GmbH Agencement de piston d'une pompe haute pression
DE102012024924A1 (de) 2012-12-19 2014-06-26 Volkswagen Aktiengesellschaft Vorrichtung zum Antrieb einer Kolbenpumpe
CN103967743A (zh) * 2013-01-29 2014-08-06 王彦彬 磁力式同平面多缸多级组合压缩机
CN103967745A (zh) * 2013-01-30 2014-08-06 王彦彬 同平面多缸多级凸轮组合压缩机
US9173998B2 (en) 2013-03-14 2015-11-03 Tandem Diabetes Care, Inc. System and method for detecting occlusions in an infusion pump
US10302080B2 (en) 2015-05-01 2019-05-28 Graco Minnesota Inc. Two piece pump rod
EP3601777B1 (fr) * 2017-03-29 2021-10-27 Wärtsilä Finland Oy Ensemble pompe à carburant haute pression pour moteur à piston à combustion interne
CN108457853B (zh) * 2018-04-10 2019-08-20 中国北方发动机研究所(天津) 一种高压泵柱塞自增压润滑结构
CN110332104B (zh) * 2019-08-14 2024-05-28 德帕姆(杭州)泵业科技有限公司 一种防咬死电动调量机构的计量泵
CN115807748A (zh) * 2022-12-07 2023-03-17 北京天玛智控科技股份有限公司 柱塞滑靴组件和多边形轮盘驱动的径向柱塞泵

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JP2885133B2 (ja) * 1995-06-12 1999-04-19 トヨタ自動車株式会社 内燃機関のピストン
IT239879Y1 (it) * 1996-12-23 2001-03-13 Elasis Sistema Ricerca Fiat Perfezionamenti ad una pompa a pistoni, in particolare ad una pompa apistoni radiali per il carburante di un motore a combustione interna.
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DE19753593A1 (de) * 1997-12-03 1999-06-17 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
WO2002097268A1 (fr) * 2001-05-26 2002-12-05 Robert Bosch Gmbh Pompe haute pression pour un systeme de carburant d'un moteur a combustion interne
JP2003074439A (ja) * 2001-06-19 2003-03-12 Denso Corp 燃料噴射ポンプ
WO2003014569A1 (fr) 2001-08-08 2003-02-20 Crt Common Rail Technologies Ag Pompe d'alimentation haute pression
DE10345406A1 (de) 2002-10-14 2004-04-22 Crt Common Rail Technologies Ag Hochdruckpumpe, insbesondere für ein Common-Rail-Einspritzsystem
ATE355460T1 (de) * 2003-02-11 2006-03-15 Ganser Hydromag Hochdruckpumpe
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DE4305791A1 (de) * 1993-02-25 1994-09-01 Rexroth Mannesmann Gmbh Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren
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DE50306704D1 (de) 2007-04-12
CN100392241C (zh) 2008-06-04
EP1592887A1 (fr) 2005-11-09
EP1760312B1 (fr) 2013-05-01
US20060275164A1 (en) 2006-12-07
CN1748083A (zh) 2006-03-15
WO2004072477A1 (fr) 2004-08-26
ATE355460T1 (de) 2006-03-15
EP1760312A3 (fr) 2007-09-05
US7108491B2 (en) 2006-09-19
AU2003281906A1 (en) 2004-09-06
US20060062677A1 (en) 2006-03-23
JP2006514195A (ja) 2006-04-27
EP1592887B1 (fr) 2007-02-28

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