WO2012146427A1 - 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
WO2012146427A1
WO2012146427A1 PCT/EP2012/053972 EP2012053972W WO2012146427A1 WO 2012146427 A1 WO2012146427 A1 WO 2012146427A1 EP 2012053972 W EP2012053972 W EP 2012053972W WO 2012146427 A1 WO2012146427 A1 WO 2012146427A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring plate
support ring
inner support
raised
pressure pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2012/053972
Other languages
German (de)
English (en)
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
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
Priority to EP12707348.4A priority Critical patent/EP2702270B1/fr
Priority to CN201280020065.1A priority patent/CN103492714B/zh
Publication of WO2012146427A1 publication Critical patent/WO2012146427A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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 of the type mentioned above or a high-pressure pump with such a spring plate is exemplified in the published patent application DE 103 55 027 A1.
  • the high-pressure pump described herein comprises at least one pump element with a pump piston having a
  • Drive shaft is driven against the force of a return 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 the piston of the foot
  • 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. Due to manufacturing tolerances, an axial clearance is often present between the components, which in particular in the areas of motion reversal of the Pump piston, for example, during the transition from the delivery phase into the suction phase, is passed through dynamically by the pump piston. As a result, the components strike against each other and are therefore subject to increased wear.
  • the stiffness of the spring plate is less than that of
  • Return spring selected so that the deformation of the spring plate by means of the spring force of the return spring is effected.
  • the restoring spring bears against a peripheral region of the spring plate and presses it in the direction of a spring plate support formed on the plunger.
  • the piston base of the pump piston accommodated in the spring plate serves as a die, so that the spring plate is bent around the piston foot. An axial clearance in the area of the piston foot receptacle can be compensated in this way - at least in one direction of movement of the pump piston.
  • Proposed is a spring plate for a plunger assembly a
  • High-pressure pump in a fuel injection system wherein the spring plate is in particular a bending stamped part and a central recess for
  • the spring plate has at least two arcuate recesses arranged around the central recess for forming a radially inner support ring and a radially outer support ring which extends over in the
  • the radially inner support ring has opposite a plane E raised and lowered areas, each at an angular distance to the im
  • Substantially radially extending webs are arranged.
  • 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 also leads to the
  • the load on the spring plate is reduced.
  • 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.
  • the angular distance of an increase or decrease to a web is chosen as large as possible. Further preferred is the angular distance of the raised and lowered
  • Bending beam which ends in an increase or decrease, is therefore 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 separation from the essentially radially extending webs, it follows that the webs are also in the same position
  • 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 substantially radially extending
  • the openings are arranged at the same angular distance from each other, so that equal parts of the radially inner support ring arise. Further preferably, 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.
  • 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 each come at the ends of the spring arms forming portions of the radially inner
  • 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.
  • Through-ground piston can then be inserted through the eccentric recess and at the level of a circumferential groove in the radial direction in the central
  • Diameter 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 smaller than the outer diameter of the
  • Piston leg engages behind or in engagement with the circumferential groove of the pump piston can be brought.
  • 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 solve the aforementioned problem high-pressure pump for a fuel injection system has at least one
  • 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.
  • 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 area of the radially inward lying 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
  • the pump piston is also "soft" intercepted via the elastically deformable spring plate, so that the risk of spring plate fractures is further reduced.
  • the filling efficiency of the high pressure pump is increased because of the
  • the spring plate of a high-pressure pump according to the invention 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 radially inner support ring of the spring plate is compressed by the spring force of the return spring, which may be up to 600 N and above, to an axial dimension, so that the spring plate rests under axial bias on the pump piston. An axial play is thus completely compensated.
  • the spring force of the return spring which may be up to 600 N and above, to an axial dimension, so that the spring plate rests under axial bias on the pump piston.
  • An axial play is thus completely compensated.
  • mirror-symmetrical design of the raised and lowered portions of the radially inner support ring is further ensured that the installation direction of the spring plate is irrelevant. This means that the spring plate shows the same behavior in both installation positions, so that assembly errors are effectively prevented.
  • Figure 1 is a partially perspective sectional view of a
  • Figure 2a is a plan view of a first preferred embodiment of a
  • FIG. 2b shows a partial section through the spring plate of FIG. 2a
  • FIG. 3 a shows a plan view of a second preferred embodiment of a spring plate according to the invention
  • Figure 3b shows a partial section through the spring plate of Figure 3a
  • Figure 4 is a perspective view of a third preferred embodiment
  • High-pressure pump comprises at least one pump element with a
  • 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 herein incorporated
  • 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
  • the area of the Kolbenfuß technique has manufacturing due to an axial play that of the pump piston 4 at a reversal of motion dynamic is going through.
  • the high-pressure pump according to the invention shown in Fig. 1 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 shown in FIGS. 2a and 2b.
  • 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 has, in addition to the central recess 3, three further arcuate running ones
  • 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). Through the raised and lowered areas 9, 10 is in the region of the radially inner
  • Support ring 6 achieves a circular waviness, which leads to an elastic
  • 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 Figure 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, with the
  • Angular distance of the increases or reductions respectively 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.
  • 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 Figure 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 accordingly have the same axial distance to the plane E (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 shown in FIGS. 3a and 3b.
  • the spring plate of FIGS. 3a and 3b has only two arcuate recesses 5 serving as throughflow openings.
  • the spring plate 1 has an eccentric
  • Recess 3 is connected.
  • 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 makes that easier 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
  • the eccentric recess 13 also serves according to the arcuate
  • recesses 5 also as a flow-through.
  • the eccentric recess 13 and the circular recess are each in the region of an im
  • Substantially radially extending web 8 is arranged, which are formed between the two arcuate 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.
  • the illustrated spring plate 1 also has a poka yoke installation behavior. Because the measure a of the increase compared to the
  • Level E is chosen equal to the dimension b of the depression in relation to the level E. In this respect, the installation position of the spring plate 1 is irrelevant.
  • FIG. 4 A further embodiment of a spring plate 1 according to the invention is shown in FIG. 4.
  • the basic form corresponds to that of the embodiment of FIGS. 2a and 2b.
  • the spring plate 1 has three arcuate 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.
  • Deformability of the spring plate 1 further increase, is in each case between one Raising and lowering each formed an opening 1 1.
  • the openings 1 1 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.

Landscapes

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

Abstract

L'invention concerne une 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) comportant en particulier une pièce découpée et pliée et un évidement central (3) destiné à loger un piston de pompe (4). Selon l'invention, la cuvette de ressort (1) comprend au moins deux évidements (5) arqués agencés autour de l'évidement central (3) destinés à former une bague d'appui (6) située radialement à l'intérieur et une bague d'appui (7) située radialement à l'extérieur, lesquelles bagues sont reliées l'une à l'autre par l'intermédiaire d'éléments de liaison (8) s'étendant sensiblement radialement. La bague d'appui (6) située radialement à l'intérieur comprend des zones (9, 10) surélevées et abaissées par rapport à un plan (E) qui sont agencées respectivement à une certaine distance angulaire des éléments de liaison (8) s'étendant sensiblement radialement. L'invention concerne en outre une pompe à haute pression pour un système d'injection de carburant équipé d'une telle cuvette de ressort (1).
PCT/EP2012/053972 2011-04-27 2012-03-08 Cuvette de ressort pour un ensemble poussoir d'une pompe à haute pression et pompe à haute pression Ceased WO2012146427A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP12707348.4A 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
CN201280020065.1A CN103492714B (zh) 2011-04-27 2012-03-08 用于高压泵的推杆组件的弹簧座及高压泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011017573.3 2011-04-27
DE102011017573A DE102011017573A1 (de) 2011-04-27 2011-04-27 Federteller für eine Stößelbaugruppe einer Hochdruckpumpe sowie Hochdruckpumpe

Publications (1)

Publication Number Publication Date
WO2012146427A1 true WO2012146427A1 (fr) 2012-11-01

Family

ID=45808987

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/053972 Ceased 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

Country Status (4)

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

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20131903A1 (it) * 2013-11-15 2015-05-16 Bosch Gmbh Robert Pompa di alta pressione per alimentare combustibile ad un motore a combustione interna
DE202019006192U1 (de) * 2019-01-29 2025-12-09 Rpc Bramlage Gmbh Spender zur Ausgabe von fließfähigen, beispielsweise flüssigen oder pastösen Massen

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5722738A (en) * 1993-07-23 1998-03-03 Itt Automotive Europe Gmbh Hydraulic brake system with brake slip control and traction slip control
WO2003031816A1 (fr) * 2001-09-28 2003-04-17 Siemens Aktiengesellschaft Element d'assemblage pour assembler un piston et un element de rappel
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
WO2012013452A1 (fr) * 2010-07-27 2012-02-02 Robert Bosch Gmbh Pompe haute pression

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5722738A (en) * 1993-07-23 1998-03-03 Itt Automotive Europe Gmbh Hydraulic brake system with brake slip control and traction slip control
WO2003031816A1 (fr) * 2001-09-28 2003-04-17 Siemens Aktiengesellschaft Element d'assemblage pour assembler un piston et un element de rappel
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
WO2012013452A1 (fr) * 2010-07-27 2012-02-02 Robert Bosch Gmbh Pompe haute pression

Also Published As

Publication number Publication date
EP2702270B1 (fr) 2017-07-05
EP2702270A1 (fr) 2014-03-05
CN103492714A (zh) 2014-01-01
CN103492714B (zh) 2016-10-12
DE102011017573A1 (de) 2012-10-31

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