EP1283366B1 - Pompe à pistons radiaux et méthode de contròle - Google Patents

Pompe à pistons radiaux et méthode de contròle Download PDF

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Publication number
EP1283366B1
EP1283366B1 EP02015316A EP02015316A EP1283366B1 EP 1283366 B1 EP1283366 B1 EP 1283366B1 EP 02015316 A EP02015316 A EP 02015316A EP 02015316 A EP02015316 A EP 02015316A EP 1283366 B1 EP1283366 B1 EP 1283366B1
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EP
European Patent Office
Prior art keywords
drive shaft
adjusting
ring
piston pump
radial piston
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
EP02015316A
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German (de)
English (en)
Other versions
EP1283366A3 (fr
EP1283366A2 (fr
Inventor
Hans-Peter Stiefel
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1283366A2 publication Critical patent/EP1283366A2/fr
Publication of EP1283366A3 publication Critical patent/EP1283366A3/fr
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Publication of EP1283366B1 publication Critical patent/EP1283366B1/fr
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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/125—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
    • F04B49/126—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts with a double eccenter mechanism
    • 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
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft

Definitions

  • the invention first relates to a radial piston pump the preamble of claim 1.
  • Such a radial piston pump is used as a high-pressure fuel pump used in a fuel system. You will Fuel supplied from a feed pump and it promotes the fuel continues into a fuel rail, commonly referred to as "rail". From there comes the Fuel via injectors in combustion chambers of the Internal combustion engine.
  • the present invention has the object, a Radial piston pump of the type mentioned above educate that the fuel system in which they is used, made easier and cheaper can be.
  • Radial piston pump is that with her to control the amount of fuel delivered no pressure and / or Quantity control valves are more required. Instead the quantity control takes place by an adjustment of the stroke the piston or pistons of the radial piston pump.
  • the Radial piston pump according to the invention thus builds easier.
  • the amount of fuel delivered by the radial piston pump can be set very precisely, that can be done at the Fuel manifold existing pressure relief valve and the corresponding return line smaller fail, or it can possibly even completely on such a pressure relief valve be waived. Also an example. To the fuel tank Returning leakage line is when using the Radial piston pump according to the invention no longer required. Thus, by the radial piston pump according to the invention Costs saved in the construction of a fuel system and the Fuel system builds easier overall, as it is less Includes components.
  • the drive shaft Due to the arrangement of the adjusting coaxial with the axis of rotation the drive shaft is an adjustment for the Adjustment created, which builds for a small and the other due to the between the adjusting shaft and the Adjusting ring arranged gear a favorable translation, possibly also a self-locking between adjusting ring and Adjusting shaft allows. Such an adjustment is also to save space in the radial piston pump accommodate and allows a reliable and precise adjustment of the Adjusting ring.
  • a stop is present, which is a Such angular position of the adjusting ring relative to the Drive shaft defined in which the cam ring at least is approximately coaxial with the axis of rotation of the drive shaft.
  • the radial piston pump works with Zero discharge. The stop becomes this operating point the radial piston pump defined in a simple manner.
  • the stop can be formed by the fact that the Internal toothing on the adjusting ring in the circumferential direction in one Range of about 185 ° to 195 °, preferably over a Range of about 190 °, extends, and the Internal toothing with respect to an axis, which in the plane of the adjusting ring, through the center of the Inner opening of the adjusting ring goes and orthogonal to Symmetry axis of the adjusting ring is symmetrical.
  • the So stop is only by the arrangement and training the internal teeth formed on the adjusting ring, so that on an additional stop element can be dispensed with.
  • an electrical adjustment device provided, which works on the adjusting shaft.
  • a such device can be easily controlled.
  • the electric adjusting device can be an electric motor, preferably a stepper motor.
  • the corresponding supply lines are space-saving possible.
  • a electrical adjusting device, in particular a Stepper motor in addition, work very precise and build relatively small. In principle, however, is also conceivable the use of an electromagnetic or a hydraulic actuator.
  • the stator of the Electric motor with the drive shaft and the rotor of the Electric motor with the adjusting shaft are rotatably connected. Normally, if no adjustment process is currently running, turn the drive shaft, the adjusting shaft and according to the stator and the rotor of the electric motor synchronous. Only if an adjustment of the adjusting ring is required, by the inventive arrangement in a simple way a speed difference between the Drive shaft and the adjusting be generated, which for Adjustment of the adjusting ring leads.
  • the invention also relates to a method for operating a Internal combustion engine in which the fuel is at least also of a radial piston pump is funded, with a housing with at least one cylinder, a drive shaft, in the Housing is mounted and at least one eccentric section comprising, with a cam ring, which around the eccentric section is arranged around and with at least one piston, which is received in the cylinder and is supported on the lifting ring wherein the eccentricity of the cam ring relative to the axis of rotation the drive shaft in response to at least one Operating parameters of the internal combustion engine is adjusted.
  • Essential parameters for those of the radial piston pump too promoting fuel quantity are the desired torque and the instantaneous speed of the internal combustion engine. That will according to the invention thereby taken into account that from a desired torque and a speed of Internal combustion engine, a parameter is determined which for the setting of such eccentricity of the cam ring is required with respect to the axis of rotation of the drive shaft, in which the radial piston pump the torque request and the Speed corresponding amount of fuel promotes.
  • the invention further relates to a computer program and a Control and / or regulating device for controlling and / or Control of at least one function of an internal combustion engine.
  • a fuel system carries the reference numeral 10 in FIG.
  • a fuel tank 12 one of which electric fuel pump 14 via a filter 16 Fuel promotes.
  • a low-pressure fuel line 18 is the electric fuel pump 14 with a High pressure fuel pump 20 connected.
  • a Branch line 22 is between electric fuel pump 14 and high pressure pump 20 branches from the low pressure fuel line 18 a Branch line 22 from, in which a pressure control valve 24th is arranged.
  • the high pressure fuel pump 20 delivers the fuel in a fuel manifold 26.
  • the Fuel stored under very high pressure.
  • To the Fuel manifold 26 are a plurality of injectors 28th connected the fuel directly into combustion chambers 30 inject.
  • the high pressure fuel pump 20 includes an electric motor 32, which of a control and / or regulating device 34th is controlled. This is the input side with a Sensor 36, which picks up the speed of the internal combustion engine and a sensor 38, the a desired torque of the Internal combustion engine provides appropriate signals, connected.
  • the High pressure fuel pump 20 is a Radial piston pump with three star-shaped arranged Cylinders 40a, 40b and 40c ( Figure 3). Cylinder heads 42a, 42b and 42c close the cylinders 40a, 40b and 40c, respectively radially outside. In the cylinder heads 42a, 42b and 42c, respectively are liners 44a, 44b and 44c, respectively, in which Pistons 46a, 46b and 46c are slidably received.
  • the cylinders 40a, 40b and 40c are part of a housing 48. In the center between the cylinders 40a, 40b and 40c is in Housing 48 has received a drive shaft 50. Over a Clutch 52 is this with a camshaft (not shown) of the internal combustion engine connected. The in FIG 2 left end of the drive shaft 50 is opposite the housing 48 supported by a ball bearing 53.
  • the drive shaft 50 has in the region of the cylinder 40a, 40b and 40c has an eccentric section 54. This is relative to the axis of rotation 56 of the drive shaft 50 to a Eccentricity 58 replaced ( Figure 5). Radial outside is on the eccentric portion 54 of the drive shaft 50 a Adjusting ring 60 attached. Radial outside is on the Adjusting ring 60, in turn, a lifting ring 62 placed. Of the Hub ring 62 carries around its Hubringbohrung 63 a to radially inwardly extending circumferential collar 65th through this is the cam ring 62 between the adjusting ring 60 and a shaft collar 67 provided on the drive shaft 50 held axially.
  • the outer surface of the cam ring 62 has three at 120 ° flattened areas 64a, 64b and 64c offset from one another on. Against this is a shoe 66a, 66b and 66c by a spring 68 a, 68 b and 68 c, respectively, located on the Bushing 44a, 44b and 44c supported, pressed. Of the Slide shoe 66a, 66b and 66c is with the radially inner End of the piston 46 a, 46 b and 46 c connected.
  • the drive shaft 50 is in its right in Figure 2 Area hollow executed. In this recess is a Adjusting shaft 70 introduced. At her left in Figure 2 End carries the adjusting shaft 70 has a circumferential toothing 72nd
  • end face of the eccentric 54 of the drive shaft 50 is in the range of the largest Eccentric 58 a milled recess 74 available.
  • a gear 76 is arranged, which is a in the Exzenterabêt 54 fixed axle 78 rotatably mounted is.
  • the gear 76 is connected to the toothing 72 on the Adjusting shaft 70 in engagement.
  • the adjusting ring 60 is with an inner opening 80 on the eccentric portion 54 of the Drive shaft 50 mounted ( Figures 4 and 5).
  • the central axis 81 of the inner opening 80 is opposite to circular outer contour of the adjusting ring 60 to a Eccentricity 82 arranged offset ( Figure 5).
  • an internal toothing 84 is present on one Area of the inner circumferential surface of the inner opening 80 of the Adjusting ring 60 .
  • the Gear 76 is also with this internal toothing 84 in Intervention.
  • the internal teeth 84 on the adjusting ring 60th extends circumferentially over a range of about 190 °.
  • the internal toothing 84 is opposite an axis 86, which in the plane of the adjusting ring 60th is located, through the center 81 of the inner opening of the Verstellrings goes and orthogonal to the axis of symmetry 88 of the Adjusting ring 60 is symmetrical ( Figure 5).
  • the reference numeral 89 carries.
  • a shaft journal 90 From the eccentric portion 54 of the drive shaft 50 extends 2, to the right, a shaft journal 90. On this a bearing bush 92 is pressed on. The associated Bearing ring 94 is pressed with the housing 48. The Bearing bushing 92 and the bearing ring 94 together form a Plain bearing, over which the right in Figure 2 end the drive shaft 50 is supported relative to the housing 48.
  • the adjusting shaft 70 is simultaneously the axis of the Electric motor 32.
  • a stator 104 of the Electric motor 32 surrounds the rotor 102.
  • the stator 104 is rotatably on a disc-shaped support plate 106 with the Bearing bush 92 connected.
  • the disk-shaped retaining plate 106 may be injection-molded onto the bearing bush 92, for example.
  • the stator 104 is rotationally fixed with the Drive shaft 50 connected.
  • the stator 104 is from a Cover 108 surrounded, the edge of the housing 48th pressure-tight crimped. In the cover 108 are Plug contacts 110 inserted, which via sliding contacts (not numbered) power the stator 104 can.
  • the fuel system 10 with the radial piston pump 20th works like this: before starting the Internal combustion engine, for example.
  • the electric motor 32 from the control and / or regulating device 34 so controlled that the gear 76 against the stop 89 of Internal toothing 84 on the adjusting ring 60 runs.
  • the adjustment of the adjusting ring 60 takes place by a relative rotation of the rotor 102 relative to the stator 104. This also rotates the adjusting shaft 70 and the Gear 76. This in turn leads to a relative rotation of the Adjusting ring 60 relative to the eccentric portion 54 of Drive shaft 50.
  • the adjusting ring 60 of the control and regulating device 34 is rotated in the position shown in Figure 5.
  • the adjusting ring 60 adds the Eccentricity 58 of the eccentric 54 of the Drive shaft 50 to the eccentricity 82 of the inner opening 80 of the adjusting ring 60.
  • the circular path on which upon rotation of the drive shaft 50 now the cam ring 62nd now has maximum radius so that the pistons 46a, 46b and 46c perform the maximum lifting movement.
  • the High-pressure fuel pump 20 pumps so now the maximum possible fuel quantity.
  • each angular position of the adjusting ring 60th relative to the eccentric portion 54 of the drive shaft 50th a very specific delivery rate of the high-pressure fuel pump 20 corresponds. These angular positions are with the associated delivery rates in the control unit 34 stored.
  • the according to the desire of the user Performance of the internal combustion engine, in particular torque and speed, are from the control and regulation unit 34 in the required amount of fuel and the associated Angular position of the adjusting ring 60 relative to the Exzenterabêts 54 of the drive shaft 50 converted and the electric motor 32 driven accordingly.
  • the angular position changes the adjusting ring 60 relative to the eccentric portion 54 only when the adjusting shaft 60 with another Speed rotates as the drive shaft 50. Should a constant delivery rate with the high-pressure fuel pump 20 are achieved, the turn Drive shaft 50 and the adjusting shaft 70 with the same Rotation speed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Claims (11)

  1. Pompes à pistons radiaux (20) pour la production d'une haute pression de carburant dans des systèmes de carburant (10) de moteurs à combustion interne, en particulier dans un système d'injection à rampe commune, comprenant un corps (48), au moins un cylindre (40a, 40b, 40c), un arbre d'entraínement (50) monté dans le corps (48) et qui présente au moins un segment excentrique (54), un anneau de poussée (62) disposé autour du segment excentrique (54) et au moins un piston (46a, 46b, 46c) logé dans le cylindre (40a, 40b,40c) et qui s'appuie sur l'anneau de poussée (62), avec entre le segment excentrique (54) et l'anneau de poussée (62) une bague de réglage (60) dont l'ouverture intérieure (80) est excentrée par rapport au profil extérieur, et qui peut être déplacée par rotation autour de l'axe central (81) de l'ouverture intérieure (80) dans une position angulaire souhaitée par rapport au segment excentrique (54), la pompe à pistons radiaux (20) comprenant un arbre de réglage (70) qui coopère avec la bague de réglage (60) par l'intermédiaire d'une denture (72),
    caractérisée en ce que
    l'arbre de réglage (70) est disposé coaxialement à l'axe de rotation (56) de l'arbre d'entraínement (50) et à un côté frontal du segment excentrique (54) de l'arbre d'entraínement (50), dans une position excentrée par rapport à l'axe de rotation (56) de l'arbre d'entraínement (50), est montée une roue dentée (76) qui coopère, d'une part, avec une denture extérieure (72) formée sur l'arbre de réglage (70) et, d'autre part, avec une denture intérieure (84) prévue sur la bague de réglage (60).
  2. Pompe à pistons radiaux (20) selon une des revendications précédentes,
    caractérisée en ce que
    l'excentricité (82) de l'ouverture intérieure (80) de la bague de réglage (60) et l'excentricité (58) du segment excentrique (54) de l'arbre d'entraínement (50) sont sensiblement égales.
  3. Pompe à pistons radiaux (20) selon la revendication 2,
    caractérisée en ce que
    sur la bague de réglage (60) est prévue une butée (89) qui définit pour la bague de réglage (60) par rapport à l'arbre d'entraínement (50), une position angulaire dans laquelle l'anneau de poussée (62) est au moins à peu près coaxial à l'axe de rotation (56) de l'arbre d'entraínement (50).
  4. Pompe à pistons radiaux (20) selon une des revendications précédentes,
    caractérisée en ce que
    la denture intérieure (84) prévue sur la bague de réglage (60) s'étend dans la direction circonférencielle sur une région d'environ 185° à 195°, de préférence sur une région d'environ 190°, et la denture intérieure (84) est symétrique par rapport à un axe (86) qui se trouve dans le plan de la bague de réglage (60), qui passe par le point central (81) de l'ouverture intérieure (80) de la bague de réglage (60) et qui est orthogonal à l'axe de symétrie (88) de la bague de réglage (60).
  5. Pompe à pistons radiaux (20) selon une des revendications précédentes,
    caractérisée en ce que
    elle comprend un dispositif de réglage électrique (32) qui agit sur l'arbre de réglage (70).
  6. Pompe à pistons radiaux (20) selon la revendication 5,
    caractérisée en ce que
    le dispositif de réglage électrique comprend un moteur électrique (32), de préférence un moteur pas à pas.
  7. Pompe à pistons radiaux (20) selon la revendication 6,
    caractérisée en ce que
    le stator (104) du moteur électrique (32) est relié solidairement en rotation à l'arbre d'entraínement (50) et le rotor (102) du moteur électrique (32) à l'arbre de réglage (70).
  8. Procédé pour faire fonctionner un moteur à combustion interne, dans lequel le carburant est refoulé en supplément au moins par une pompe à pistons radiaux (20) comprenant un corps (48), au moins un cylindre (40a, 40b, 40c), un arbre d'entraínement (50) montée dans le corps (48) et qui présente au moins un segment excentrique (54), un anneau de poussée (62) disposé autour du segment excentrique (54) et au moins un piston (46a, 46b, 46c) logé dans le cylindre (40a, 40b,40c) et qui s'appuie sur l'anneau de poussée (62), l'excentricité de l'anneau de poussée (62) par rapport à l'axe de rotation (56) de l'arbre d'entraínement (50) étant réglé en fonction d'au moins un paramètre de fonctionnement du moteur à combustion interne,
    caractérisé en ce que
    sur la base d'un couple souhaité et d'une vitesse de rotation du moteur à combustion interne, on obtient un paramètre nécessaire pour le réglage d'une excentricité de la bague de poussée (62) par rapport à l'axe de rotation (56) de l'arbre d'entraínement (54), par lequel la pompe à pistons radiaux (20) refoule la quantité de carburant qui correspond au souhait de couple et à la vitesse de rotation.
  9. Procédé selon la revendication 8,
    caractérisé en ce qu'
    avant le démarrage du moteur à combustion interne, une bague de réglage (60) est réglée par rapport à une butée mécanique (81) qui définit pour la bague de réglage (60) par rapport à l'arbre d'entraínement (50) une position angulaire dans laquelle la bague de poussée (62) est au moins à peu prés coaxiale à l'axe de rotation (56) de l'arbre d'entraínement (50), et dans cette position, une compensation d'une électronique de commande (34) est effectuée.
  10. Programme d'ordinateur,
    caractérisé en ce qu'
    il est programmé pour appliquer un procédé selon une des revendications 8 ou 9.
  11. Dispositif de commande et/ou de réglage pour un moteur à combustion interne,
    caractérisé en ce qu'
    il est programmé pour appliquer un procédé selon l'une des revendications 8 à 9.
EP02015316A 2001-08-10 2002-07-10 Pompe à pistons radiaux et méthode de contròle Expired - Lifetime EP1283366B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10139519 2001-08-10
DE10139519A DE10139519A1 (de) 2001-08-10 2001-08-10 Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung, sowie Verfahren zum Betreiben einer Brennkraftmaschine, Computerprogramm und Steuer- und/oder Regelgerät

Publications (3)

Publication Number Publication Date
EP1283366A2 EP1283366A2 (fr) 2003-02-12
EP1283366A3 EP1283366A3 (fr) 2004-05-12
EP1283366B1 true EP1283366B1 (fr) 2005-11-09

Family

ID=7695149

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02015316A Expired - Lifetime EP1283366B1 (fr) 2001-08-10 2002-07-10 Pompe à pistons radiaux et méthode de contròle

Country Status (4)

Country Link
US (1) US6872056B2 (fr)
EP (1) EP1283366B1 (fr)
JP (1) JP2003097383A (fr)
DE (2) DE10139519A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013010458A1 (fr) * 2011-07-14 2013-01-24 Neo Mechanics Limited Pompe d'injection de carburant de moteur diesel dont les pistons sont étanchéifiés à l'aide de bagues d'étanchéité entièrement métalliques

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DE10349310B3 (de) * 2003-10-23 2005-05-19 Siemens Ag Radialkolbenpumpe für Common Rail Einspritzsysteme
JP4297859B2 (ja) * 2004-09-28 2009-07-15 三洋電機株式会社 電動車輪用ハブユニット及び該ハブユニットを具えた乗物
DE102005061456B4 (de) * 2005-12-22 2015-09-24 Magna Powertrain Bad Homburg GmbH Zylinderblock einer Hubkolbenmaschine mit durch Spannring gehaltenen Zylinderköpfen
DE102006000832B4 (de) * 2006-01-05 2011-12-01 Continental Automotive Gmbh Radialkolbenpumpe mit Fördermengenregelung
DE102006006823B3 (de) * 2006-02-14 2007-03-15 Siemens Ag Verfahren und Vorrichtung zum Einspritzen von Kraftstoff
JP4624961B2 (ja) * 2006-06-13 2011-02-02 株式会社ニッキ 燃料供給システム
US8122811B2 (en) * 2007-11-12 2012-02-28 Denso Corporation Fuel injection pump and method for assembling the same
EP2093421B1 (fr) * 2008-02-22 2013-04-17 Robert Bosch GmbH Pompe haute pression pour fournir du carburant à un système d'injection de carburant
DE102009000964A1 (de) * 2009-02-18 2010-08-19 Robert Bosch Gmbh Hochdruckkraftstoffpumpe für eine Brennkraftmaschine
ES2523271T3 (es) * 2009-08-11 2014-11-24 Prominent Gmbh Dispositivo de accionamiento para máquinas de desplazamiento oscilantes
DE102009049354A1 (de) * 2009-10-14 2011-04-21 Robert Bosch Gmbh Hydromaschine
US9618129B2 (en) * 2010-10-07 2017-04-11 Vanderbilt University Normally closed microvalve and applications of the same
DE102015214837A1 (de) * 2015-08-04 2017-02-09 Zf Friedrichshafen Ag Hydraulische Radialkolbenmaschine
CN105179218B (zh) * 2015-10-12 2016-11-30 杭州电子科技大学 一种数字式径向柱塞变量泵
JP6305480B2 (ja) * 2016-09-01 2018-04-04 日機装株式会社 無脈動ポンプ
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EP1283366A3 (fr) 2004-05-12
DE50204834D1 (de) 2005-12-15
EP1283366A2 (fr) 2003-02-12
JP2003097383A (ja) 2003-04-03
DE10139519A1 (de) 2003-02-27
US20030031568A1 (en) 2003-02-13
US6872056B2 (en) 2005-03-29

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