EP2702270B1 - Cuvette de ressort pour un ensemble poussoir d'une pompe à haute pression et pompe à haute pression - Google Patents

Cuvette de ressort pour un ensemble poussoir d'une pompe à haute pression et pompe à haute pression Download PDF

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Publication number
EP2702270B1
EP2702270B1 EP12707348.4A EP12707348A EP2702270B1 EP 2702270 B1 EP2702270 B1 EP 2702270B1 EP 12707348 A EP12707348 A EP 12707348A EP 2702270 B1 EP2702270 B1 EP 2702270B1
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EP
European Patent Office
Prior art keywords
spring plate
support ring
inner support
radially inner
pump 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.)
Active
Application number
EP12707348.4A
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German (de)
English (en)
Other versions
EP2702270A1 (fr
Inventor
Eberhard Maier
Gerhard Meier
Markus Kunz
Frank Scholz
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
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Publication of EP2702270A1 publication Critical patent/EP2702270A1/fr
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Publication of EP2702270B1 publication Critical patent/EP2702270B1/fr
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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
    • F04B1/0439—Supporting or guiding means for the pistons
    • 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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • 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
    • F04B1/0435—Arrangements for disconnecting the pistons from the actuated cam
    • 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
    • F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement

Definitions

  • the present invention relates to a spring plate for a plunger assembly of a high pressure pump having the features of the preamble of claim 1. Furthermore, the invention relates to a high pressure pump with such a spring plate.
  • a spring plate of the aforementioned type or a high-pressure pump with such a spring plate is through the DE 10 2009 027 689 A1 known.
  • the high-pressure pump described herein has at least one pump element with a pump piston which delimits a pump working space and which can be driven at least indirectly by a drive shaft against the force of a restoring spring in a lifting movement.
  • the pump piston is indirectly supported via a sleeve-shaped plunger on the drive shaft.
  • a spring plate is provided, which engages behind the piston of the pump piston.
  • plunger and pump piston are held in contact with the drive shaft.
  • the plunger has a radially inwardly extending annular collar on which on the one hand the spring plate and on the other hand abut a support member for rotatably supporting a roller. Between the support element and the spring plate, the piston foot of the pump piston comes to rest.
  • the known spring plate has a central recess for receiving the pump piston and a plurality of arranged around the central Aushemung arcuate recesses for forming a radially inner support ring and a radially outer support ring has, which are interconnected via substantially radially extending webs. The radially inner support ring abuts against the pump piston.
  • a high pressure pump in which also a spring plate is present, which is supported on a pump piston.
  • the spring plate has a radially outer support ring and a radially inner support ring. From the inner support ring four radially inwardly projecting engagement surfaces are bent out of the plane of the support ring, which are positively connected to the pump piston. The engagement surfaces are arranged in a common plane. An elastic deformability of the spring plate is not provided here.
  • the object is achieved by a spring plate with the features of claim 1.
  • Advantageous developments of the invention are specified in the dependent claims.
  • the object is further achieved by a high pressure pump having the features of claim 9.
  • a spring plate for a plunger assembly of a high-pressure pump in a fuel injection system wherein the spring plate is in particular a bending stamped part and has a central recess for receiving a pump piston.
  • the spring plate has the radially inner support ring with respect to a plane E raised and lowered areas, which are each arranged at an angular distance to the substantially radially extending webs. Due to the increases and decreases of the radially inner support ring, the spring plate has a circular waviness, which allows the compensation of a production-related axial play in the region of the recording of the pump piston or the piston foot of the pump piston. Because the circular waviness causes elastic deformability of the spring plate, so that it is axially biased.
  • the spring plate is therefore used in such a plunger assembly of a high pressure pump that it rests under axial bias on the pump piston.
  • the piston foot of the pump piston is preferably clamped between the spring plate and a support member of the plunger assembly.
  • the required for biasing the spring plate axial force is further preferably effected by a return spring, which holds the plunger assembly in abutment with the cam or eccentric drive shaft.
  • the elastic deformability of the spring plate is increased. Because as a bending beam is not only the radially extending web, but also each lying in the range of the angular distance portion of the radially inner support ring available. Preferably, therefore, the angular distance of an increase or decrease to a web is chosen as large as possible.
  • the angular distance of the raised and lowered regions is selected to be equal to the substantially radially extending webs.
  • the length of a bending beam that ends in an increase or decrease, therefore, is always the same size, so that the effect on the raised and lowered areas effected elastic deformability of the spring plate, regardless of the installation direction of the spring plate is also the same size.
  • the number of elevations corresponds to those of the subsidence, wherein further preferably, the elevations and depressions are each arranged at the same angular distance from each other. If the elevations and depressions also have the same angular spacing from the essentially radially extending webs, it follows that the webs are also arranged at the same angular distance from one another. By the same angular distance of the raised and lowered areas and the webs to each other a uniform elastic deformation of the spring plate is ensured when subjected to an axial force.
  • the raised portions are raised by a dimension a from the plane E, the dimension a being 0.2 mm or less.
  • the maximum over the increases of the radially inner support ring axial clearance is therefore 0.2 mm.
  • the lowered regions are lowered by a dimension b with respect to the plane E, wherein the dimension b may be 0.2 mm or less.
  • the maximum compensation over the subsidence of the radially inner support ring axial play is therefore also 0.2 mm.
  • the radially inner support ring has openings.
  • the openings divide the radially inner support ring into sections, which together with the essentially radially extending webs form elastically deformable spring arms.
  • the openings are in arranged equal angular distance from each other so that equal parts of the radially inner support ring arise.
  • the number of openings corresponds to the number of webs.
  • the angular spacing of the apertures from the webs be selected to be the same.
  • an opening is arranged in each case between two webs.
  • the openings are each formed between a raised and a lowered portion of the radially inner support ring.
  • the raised and lowered portions of the radially inner support ring come to lie at the ends of the spring arms forming portions of the radially inner support ring.
  • each section preferably has a raised area at one end and a lowered area at the other end, with a raised area and a lowered area opposite one another at the opposite ends of two sections in the region of an opening.
  • Each increase or decrease forms a support surface, with which the spring plate preferably rests as a component of a plunger assembly under bias on the pump piston. The bias is effected by an elastic deformation of the spring plate in the region of the elevations and / or lowering of the radially inner support ring. An axial clearance can thus be completely compensated.
  • the radially inner support ring has an opening which connects the central recess for receiving the pump piston with an eccentrically arranged recess.
  • the eccentrically arranged recess is intended to simplify the insertion of a pump piston in the spring plate. This is especially true when a through-ground piston is to be used.
  • the piston can first be inserted into the eccentric recess and then moved laterally in the direction of the central recess, so that the radially inner support ring engages behind the piston foot or engages in a circumferential groove of the pump piston.
  • the eccentrically arranged recess has a larger diameter than the central recess.
  • the through-ground piston can then be inserted through the eccentric recess and at the level of a circumferential groove in radial direction are moved into the central recess.
  • the two different diameters of the two recesses lead to a keyhole-like shape of the piston receiving.
  • the diameter of the central recess of the spring plate is preferably chosen smaller than the outer diameter of the pump piston, so that the radially inner support ring engages behind the piston or is engageable with the circumferential groove of the pump piston.
  • the elevations and depressions of the radially inner support ring can already be formed when cutting the spring plate by means of the cutting die. In this way, the spring plate according to the invention is also easy and inexpensive to produce.
  • the further proposed to achieve the object mentioned high-pressure pump for a fuel injection system has at least one pump element with a spring plate according to the invention.
  • the spring plate is part of a plunger assembly, via which a hubbeweglich guided pump piston of the pump element is indirectly supported on a cam or eccentric drive shaft, via which the pump piston against the spring force of a return spring is driven to a lifting movement.
  • About the increases and reductions in the region of the radially inner support ring of the spring plate can compensate for an axial play in the piston receiving area. Because the increases and decreases cause elastic deformability of the spring plate, so that it can be biased in the axial direction to clamp the piston foot between the spring plate and a support member.
  • the clamping action prevents the pump piston from abutting the adjoining components when there is a reversal of motion and sounding banging occurs.
  • the movement of the pump piston is also "soft" intercepted via the elastically deformable spring plate, so that further the risk of spring plate fractures is reduced.
  • the filling efficiency of the high-pressure pump is increased because the pump piston is always tracked.
  • the spring plate of a high-pressure pump is supported via the radially inner support ring on the pump piston and via the radially outer support ring on a plunger body of the plunger assembly.
  • a clamping connection of the pump piston with the plunger assembly can be realized.
  • the high-pressure pump comprises at least one pump element with a pump piston 4 which can be moved in terms of lifting motion and which is supported via a plunger assembly 2 on a cam 14 of a drive shaft 15.
  • the plunger assembly 2 causes a conversion of the rotational movement of the drive shaft 15 in a translational movement of the pump piston 4.
  • the plunger assembly 2 comprises a sleeve-shaped plunger body 17 and a support member 18 received therein, in which a roller 19 is rotatably mounted. With the roller 19, the plunger assembly 2 is located on the outer peripheral side of the cam 14 of the drive shaft 15 at.
  • a return spring 16 holds the plunger assembly 2 in abutment with the cam 14.
  • the sleeve-shaped plunger body 17 has on the inner circumference an annular collar 20 on which on the one hand, the support member 18, on the other hand, a spring plate 1 is supported.
  • the spring plate 1 has a central recess 3 for receiving the pump piston 4. This is inserted into the spring plate 1 such that the radially inner support ring engages behind a piston 21 of the pump piston. In this way, a positive connection of the spring plate 1 with the pump piston 4 is effected.
  • the spring plate 1 is made of metal, in particular steel, preferably spring steel.
  • illustrated high-pressure pump has an elastically deformable spring plate 1, which is able to compensate for axial play by the spring plate 1 is installed under axial bias, so that the piston 21 is clamped between the spring plate 1 and the support member 18.
  • FIGS. 2a and 2b A first embodiment of an elastically deformable spring plate 1 according to the invention is in the FIGS. 2a and 2b shown.
  • the spring plate is designed as a bending stamped part, which has a plane E raised and lowered areas 9, 10.
  • the raised and lowered portions 9, 10 are formed and arranged so that a circular ripple is effected, which ensures the elastic deformability of the spring plate.
  • the elastic deformability of the spring plate 1 in turn allows the installation of the spring plate 1 under an axial bias, wherein the force required for the axial preload force on the spring force of the return spring 16 is effected.
  • the spring force or stiffness of the return spring 16 is greater than that of the spring plate 1 selected.
  • the voltage applied under an axial bias on the pump piston 4 elastically deformable spring plate 1 not only leads to the compensation of existing axial play, but also leads to a reversal of movement of the pump piston 4 to the fact that the movements of the pump piston 4 are "soft" intercepted.
  • the spring plate 1 in addition to the central recess 3, three further arcuate recesses 5, which are arranged concentrically to the central recess 3 and at the same angular distance from each other.
  • the arcuate recesses 5 serve as flow openings.
  • radially extending webs 8 form, which connect a radially inner support ring 6 and a radially outer support ring 7.
  • the spring plate 1 is preferably located with the radially outer support ring 7 on an annular collar 20 of a sleeve-shaped plunger body 17 and with the radially inner support ring 6 on a pump piston 4 at.
  • the radially inner support ring has raised and lowered areas 9, 10 with respect to a plane E (see FIG. 2b ).
  • a circular waviness is achieved in the region of the radially inner support ring 6, which leads to an elastic deformability of the spring plate 1.
  • the raised and lowered portions 9, 10 are each at an angular distance to the radially extending webs 8.
  • the circular waviness is formed such that in each case a raised and a lowered portion 9, 10 in the center between two webs 8 lies.
  • the spring plate of the FIG. 2a has a total of three webs 8, which are at the same angular distance from each other.
  • the angular distance is present 120 °.
  • the number of increases or decreases is therefore also three, wherein the angular distance of the increases or decreases each to each other and to the webs 8 is always the same.
  • the angular distance of the raised and lowered portions 9, 10 to the webs 8 leads to increased elasticity of the spring plate 1 according to the invention with respect to a spring plate 1, which would have, for example, an increase or decrease in extension of the webs 8. Because the bending beam has a greater length when it extends not only radially, but also over a partial circumferential region of the radially inner support ring (see dot-dash-dot lines in FIG. 2a ).
  • the increase takes place by a dimension a and the reduction by a dimension b, which are chosen to be the same size.
  • the raised areas 9 and the lowered areas 10 therefore have the same axial distance to the plane E. on (see FIG. 2b ). In this respect, it is irrelevant in which mounting position the spring plate 1 is installed. Installation errors can thus be avoided.
  • FIGS. 3a and 3b A second embodiment of a spring plate 1 according to the invention is the FIGS. 3a and 3b refer to.
  • the spring plate of the FIGS. 3a and 3b only two arcuate recesses 5 serving as throughflow openings.
  • the spring plate 1 has an eccentric recess 13, which is connected via an opening 12 with the central recess 3.
  • the diameter of the recess 13 is selected larger than the diameter of the recess 3, so that the recesses 3 and 13 together have a keyhole-like shape. It facilitates the insertion of a particular through-ground pump piston, which has only one circumferential groove for positive connection with the spring plate 1.
  • the pump piston is first introduced into the eccentric recess 13 and displaced radially in the direction of the central recess 3 at the level of the circumferential groove, so that the radially inner support ring 6 engages with the circumferential groove of the pump piston.
  • the eccentric recess 13 also serves in accordance with the arcuate recesses 5 also as a flow-through.
  • the eccentric recess 13 and the circular recess are each arranged in the region of a substantially radially extending web 8, which are formed between the two arc-shaped recesses 5.
  • the number of increases or decreases of the radially inner support ring 6 corresponds to the number of arcuate recesses 5. In each case an increase and a reduction are arranged substantially centrally between the two webs 8.
  • Fig. 3b can also be seen, the spring plate 1 shown on a Poka Yoke installation behavior.
  • a of the elevation with respect to the plane E is chosen equal to the dimension b of the lowering in relation to the plane E. In this respect, the installation position of the spring plate 1 is irrelevant.
  • FIG. 4 Another embodiment of a spring plate 1 according to the invention is the FIG. 4 refer to.
  • the basic form corresponds to that of the embodiment of FIGS. 2a and 2b ,
  • the spring plate 1 has three arcuate running Recesses 5, which are separated by substantially radially extending webs 8.
  • the arcuate recesses 5 lead to the formation of a radially outer support ring 7 and a radially inner support ring 6, the latter comprising areas 9, 10 which are raised relative to a plane E by a dimension a and a dimension b are lowered.
  • the dimension a is chosen equal to the dimension b. It is presently 0.2 mm.
  • the elevations and depressions are each arranged at an angular distance from the webs 8, so that the longest possible bending beam is achieved.
  • an opening 11 is formed between an increase and a reduction.
  • the openings 11 divide the radially inner support ring 6 in three sections, which form together with the webs 8 elastically deformable spring arms.
  • Each spring arm or each section of the radially inner support ring thus has at one end an increase and at the other end a reduction, so that regardless of the installation position of the spring plate 1 each spring arm has a raising or lowering to rest on the pump piston.
  • Same angular intervals of the increases or the reductions to each other lead to a rotationally symmetrical design of the spring plate 1.
  • the angular distance in the present case is 120 °.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (10)

  1. Cuvette de ressort pour un ensemble poussoir (2) d'une pompe à haute pression dans un système d'injection de carburant, la cuvette de ressort (1) étant en particulier une pièce estampée-cintrée et la cuvette de ressort (1) présentant un évidement central (3) pour recevoir un piston de pompe (4), la cuvette de ressort (1) possédant en outre au moins deux évidements (5) s'étendant sous forme arquée et disposés autour de l'évidement central (3) pour réaliser une bague de support (6) située radialement à l'intérieur et une bague de support (7) située radialement à l'extérieur, qui sont connectées l'une à l'autre par le biais de nervures (8) s'étendant essentiellement radialement, caractérisée en ce que la bague de support (6) située radialement à l'intérieur possède des régions (9, 10) rehaussées et renfoncées par rapport à un plan (E) qui sont à chaque fois disposées à une distance angulaire par rapport aux nervures (8) s'étendant essentiellement radialement et qui causent une ondulation circulaire de la bague de support située à l'intérieur (6) et une capacité de déformation élastique de la cuvette de ressort (1).
  2. Cuvette de ressort selon la revendication 1,
    caractérisée en ce que la distance angulaire des régions rehaussées et renfoncées (9, 10) par rapport aux nervures s'étendant essentiellement radialement (8) est choisie de manière à être à chaque fois identique.
  3. Cuvette de ressort selon la revendication 1 ou 2,
    caractérisée en ce que les régions rehaussées (9) sont rehaussées d'une dimension (a) par rapport au plan (E), la dimension (a) étant au maximum d'environ 0,2 mm.
  4. Cuvette de ressort selon l'une quelconque des revendications précédentes,
    caractérisée en ce que les régions renfoncées (10) sont renfoncées d'une dimension (b) par rapport au plan (E), la dimension (b) étant au maximum d'environ 0,2 mm.
  5. Cuvette de ressort selon l'une quelconque des revendications précédentes,
    caractérisée en ce que la bague de support (6) située radialement à l'intérieur présente des orifices (11) qui sont de préférence disposés à la même distance angulaire les uns des autres.
  6. Cuvette de ressort selon la revendication 5,
    caractérisée en ce que les orifices (11) sont à chaque fois réalisés entre une région rehaussée et une région renfoncée (9, 10).
  7. Cuvette de ressort selon l'une quelconque des revendications précédentes,
    caractérisée en ce que la bague de support (6) située radialement à l'intérieur présente un orifice (12) qui relie l'évidement central (3) à un évidement (13) disposé de manière excentrique.
  8. Cuvette de ressort selon la revendication 7,
    caractérisée en ce que l'évidement (13) disposé de manière excentrique présente un plus grand diamètre que l'évidement central (3).
  9. Pompe à haute pression pour un système d'injection de carburant comprenant au moins un élément de pompe comprenant une cuvette de ressort (1) selon l'une quelconque des revendications précédentes, la cuvette de ressort (1) faisant partie d'un ensemble poussoir (2) par le biais duquel un piston de pompe (4) guidé avec un mouvement alternatif est supporté de manière indirecte sur une came (14) ou un excentrique d'un arbre d'entraînement (15), par le biais duquel le piston de pompe (4) peut être entraîné avec un mouvement alternatif à l'encontre de la force de ressort d'un ressort de rappel (16).
  10. Pompe à haute pression selon la revendication 9,
    caractérisée en ce que la cuvette de ressort (1) est supportée par le biais de la bague de support (6) située radialement à l'intérieur sur le piston de pompe (4) et par le biais de la bague de support (7) située radialement à l'extérieur sur un corps de poussoir (17) de l'ensemble poussoir (2).
EP12707348.4A 2011-04-27 2012-03-08 Cuvette de ressort pour un ensemble poussoir d'une pompe à haute pression et pompe à haute pression Active EP2702270B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011017573A DE102011017573A1 (de) 2011-04-27 2011-04-27 Federteller für eine Stößelbaugruppe einer Hochdruckpumpe sowie Hochdruckpumpe
PCT/EP2012/053972 WO2012146427A1 (fr) 2011-04-27 2012-03-08 Cuvette de ressort pour un ensemble poussoir d'une pompe à haute pression et pompe à haute pression

Publications (2)

Publication Number Publication Date
EP2702270A1 EP2702270A1 (fr) 2014-03-05
EP2702270B1 true EP2702270B1 (fr) 2017-07-05

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EP12707348.4A Active EP2702270B1 (fr) 2011-04-27 2012-03-08 Cuvette de ressort pour un ensemble poussoir d'une pompe à haute pression et pompe à haute pression

Country Status (4)

Country Link
EP (1) EP2702270B1 (fr)
CN (1) CN103492714B (fr)
DE (1) DE102011017573A1 (fr)
WO (1) WO2012146427A1 (fr)

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ITMI20131903A1 (it) * 2013-11-15 2015-05-16 Bosch Gmbh Robert Pompa di alta pressione per alimentare combustibile ad un motore a combustione interna
DE102019132343A1 (de) * 2019-01-29 2020-07-30 Rpc Bramlage Gmbh Spender zur Ausgabe von fließfähigen, beispielsweise flüssigen oder pastösen Massen

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DE59402095D1 (de) * 1993-07-23 1997-04-17 Teves Gmbh Alfred Hydraulische bremsanlage mit bremsschlupf- und antriebsschlupfregelung
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.
DE19804275A1 (de) * 1998-02-04 1999-08-12 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
DE10147981A1 (de) * 2001-09-28 2003-04-24 Siemens Ag Verbindungselement zur Verbindung eines Kolbens mit einem Rückstellelement
DE10355027A1 (de) 2003-11-25 2005-06-23 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102009027689A1 (de) * 2009-07-14 2011-01-20 Robert Bosch Gmbh Kraftstoffhochdruckpumpe
DE102010038468A1 (de) * 2010-07-27 2012-02-02 Robert Bosch Gmbh Hochdruckpumpe

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Publication number Publication date
CN103492714A (zh) 2014-01-01
WO2012146427A1 (fr) 2012-11-01
DE102011017573A1 (de) 2012-10-31
EP2702270A1 (fr) 2014-03-05
CN103492714B (zh) 2016-10-12

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