EP2598743B1 - Pompe haute pression - Google Patents

Pompe haute pression Download PDF

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Publication number
EP2598743B1
EP2598743B1 EP11728881.1A EP11728881A EP2598743B1 EP 2598743 B1 EP2598743 B1 EP 2598743B1 EP 11728881 A EP11728881 A EP 11728881A EP 2598743 B1 EP2598743 B1 EP 2598743B1
Authority
EP
European Patent Office
Prior art keywords
driver element
pump
elevation
pump piston
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
EP11728881.1A
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German (de)
English (en)
Other versions
EP2598743A1 (fr
Inventor
Sascha Ambrock
Marcus Kristen
Stefanie Geiselhart
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 EP2598743A1 publication Critical patent/EP2598743A1/fr
Application granted granted Critical
Publication of EP2598743B1 publication Critical patent/EP2598743B1/fr
Active 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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam

Definitions

  • the invention relates to a high-pressure pump, in particular a radial or linear piston pump. Specifically, the invention relates to the field of fuel pumps for fuel injection systems of air-compression, self-igniting internal combustion engines.
  • a high-pressure pump for a fuel injection of an internal combustion engine has a pump housing, in which a pump element is arranged, which comprises a driven by a drive shaft in a stroke pump piston.
  • the pump piston is slidably guided in a cylinder bore of a part of the pump housing and limited in this one pump working space.
  • the pump piston is supported indirectly via a hollow cylindrical plunger on the drive shaft, wherein the plunger is slidably guided in a bore of a part of the pump housing in the direction of the longitudinal axis of the pump piston.
  • a support element in which a roller is rotatably mounted, which rolls on the cam of the drive shaft.
  • the axis of rotation of the roller is at least approximately parallel to the axis of rotation of the drive shaft.
  • the support member has on its side facing the drive shaft a recess in which the roller is mounted.
  • On the plunger or on the pump piston engages a prestressed return spring, which is supported on the pump housing part.
  • the pump piston may be coupled to the plunger, at least in the direction of its longitudinal axis.
  • the pump piston can not be connected to the plunger, in which case the return of the pump piston is ensured on the plunger.
  • the restoring spring engages, for example via a spring plate, on a piston foot of the pump piston which is enlarged in diameter and which thereby engages System is held on a ram on the plunger of the jacket inwardly projecting flange, which in turn is held in contact with the support element, so that the entire composite of pump piston, plunger and support element is acted upon with roller to the cam of the drive shaft.
  • the from the DE 10 2005 046 670 A1 known high pressure pump has the disadvantage that a game between the serving as a roller shoe support member and the piston of the pump piston can occur. During operation of the high pressure pump, this game is run through, so that the piston foot strikes against the roller shoe. This creates a noise that is undesirable.
  • WO 03/031816 A shows a radial piston pump with a driving element between the piston and the plunger spring. Disclosure of the invention
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that an undesirable noise can be prevented or at least reduced. Specifically, a game between the roller shoe and the pump piston can be prevented or at least avoided.
  • the entrainment element has a central passage opening through which the pump piston extends, that the pump piston has a collar, that the collar of the pump piston is arranged between the entrainment element and a surface of the roller shoe and that the entrainment element has at least one recess, which is arranged next to the central passage opening.
  • the recess arranged next to the central passage opening is designed as a slot-shaped recess and that the slot-shaped recess extends at least approximately in a circumferential direction.
  • a certain bias may be predetermined in an initial state, with which the driving element acts on the pump piston against the roller shoe.
  • the driving element has a plurality of recesses which are arranged distributed radially around the central passage opening, and that elastically deformable webs are configured between the recesses.
  • the elastic deformability can be achieved especially in the region of the webs.
  • a targeted design for a system of the pump piston on the survey or for a system of a plunger spring or the like can be made areas.
  • the embodiment of the driving element can be optimized with respect to the existing, different requirements.
  • the pump piston has a collar, that the collar of the pump piston between the driving element and a surface of the roller shoe is arranged and that the collection of the driving element is provided adjacent to the passage opening, wherein the collar of the pump piston rests against the survey.
  • the elevation provided adjacent to the passage opening is at least partially annular. It is also possible that the elevation provided adjacent to the passage opening surrounds the passage opening in an annular manner.
  • the passage openings can then be provided, which allow the desired flexibility of the driving element.
  • a support surface can then advantageously be designed to support, for example, a plunger spring.
  • the elevation of the entrainment element has a contact surface against which the collar of the pump piston rests, that the entrainment element has an end face which faces away from the abutment surface of the elevation and in that the end face is designed as an at least essentially flat end side.
  • a distance between the contact surface of the survey and the end face of the driving element is not smaller than 0.2 mm.
  • the driving element can be made relatively thin to ensure the desired elasticity.
  • the driving element can thereby be designed relatively easily, which has a favorable effect on the accelerated during operation total mass of the pump assembly.
  • the survey is therefore designed so that the collar of the pump piston is held in contact with the surface of the roller shoe. By a partially resilient design of the driving element in this case also a certain bias can be applied.
  • a plunger spring is provided, that the entrainment element on the front side, which faces away from the roller shoe, an at least approximately having annular support surface and that the plunger spring is supported on the annular support surface.
  • the driving element can fulfill several functions. Firstly, a reliable entrainment of the pump piston can be achieved, wherein a system of the pump piston is ensured with the roller shoe. On the other hand, an advantageous support of the plunger spring can be ensured in order to adjust the plunger body together with the other elements, in particular the roller shoe. This also simplifies the design of the plunger body.
  • roller shoe and the plunger body in which the roller shoe is inserted, are formed from two components. But it is also possible that the roller shoe and the plunger body are designed in one piece and form a component.
  • the passage opening is designed as a circular passage opening.
  • the passage opening can also be configured as a slot-shaped passage opening.
  • the passage opening can be configured as a slot-shaped passage opening.
  • Fig. 1 shows a high-pressure pump 1 in a schematic, partial sectional view according to an embodiment of the invention.
  • the high pressure pump 1 can be designed in particular as a radial or inline piston pump be.
  • the high-pressure pump 1 is suitable as a fuel pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the high pressure pump 1 is for a fuel injection system with a fuel rail, a so-called common rail, which stores diesel fuel under high pressure.
  • the high-pressure pump 1 according to the invention is also suitable for other applications.
  • the high-pressure pump 1 has a multipart pump housing with a housing part 2.
  • a drive shaft 3 is arranged, which is mounted in a suitable manner in the pump housing.
  • the drive shaft 3 can be driven in rotation by an internal combustion engine, so that it rotates about a rotation axis 4.
  • a cam 5 is provided on the drive shaft 3.
  • the cam 5 may be configured as a single or multiple cam.
  • the cam 5 may also be formed by an eccentric portion of the drive shaft 3.
  • the cam 5 is assigned to a pump assembly 6 of the high-pressure pump 1.
  • the high-pressure pump 1 has a cylinder head 7, which is connected to the housing part 2.
  • the cylinder head 7 has a projection 8 which projects into a plunger bore 9 of the housing part 2.
  • the projection 8 has a cylindrical bore 10.
  • the pump assembly 6 comprises a pump piston 11, which is arranged in sections in the bore 10 and is guided in the bore 10 along a longitudinal axis 12 of the bore 10.
  • the longitudinal axis 12 is in this case at least approximately directed to the axis of rotation 4 of the drive shaft 3.
  • the pump piston 11 is in this case in an operating direction 13 and counter to the actuating direction 13 adjustable.
  • An end face 14 of the pump piston 11 defines a pump working space 15 in the cylindrical bore 10.
  • an inlet valve 16 and an outlet valve 17 are provided to first lead under low pressure fuel into the pump working chamber 15 and then acted upon by the pump piston 11, below high pressure fuel through a line 18 to promote a fuel rail or the like.
  • an at least substantially hollow cylindrical plunger body 20 is arranged in the plunger bore 9 in the plunger bore 9.
  • the plunger body 20 is guided in the plunger bore 9 along the longitudinal axis 12.
  • the plunger body 20 has a radially inwardly directed shoulder 21.
  • a roller shoe 22 is used, which is supported on the shoulder 21 of the plunger body 20.
  • the roller shoe 22 serves to receive a roller 23, which rolls on a running surface 24 when the drive shaft 3 rotates about the rotation axis 4. According to the lifting movement of the cam 5, an actuating force is thus transmitted via the roller 23 to the roller shoe 22.
  • a partially plate-shaped driving element 25 is inserted in the plunger body 20 in the plunger body 20, a partially plate-shaped driving element 25 is inserted.
  • the driving element 25 is in this case on a side 26, which faces the roller shoe 22, on the shoulder 21 at.
  • the pump piston 11 has a piston foot 27 on which an end-side collar 28 is provided. An end face 29 of the collar 28 of the pump piston 11 rests against a surface 30 of the roller shoe 22.
  • the driving element 25 is acted upon by a plunger spring 31.
  • the plunger spring 31 is arranged in the plunger bore 9, wherein the plunger spring 31 surrounds the projection 8 of the cylinder head 7 in sections.
  • the driving element 25 has an annular support surface 35, which faces away from the side 26 of the driving element 25.
  • the plunger spring 31 is supported on the one hand on the annular support surface 35 of the driving element 25 from. On the other hand, the plunger spring 31 is supported on an underside 36 of the cylinder head 7.
  • the entrainment element 25 of the pump assembly 6 has a roller shoe 22 facing elevation 37 on its side 26.
  • the collar 28 of the piston foot 27 is supported on the survey 37 of the driving element 25 from.
  • the driving element 25 is designed partially elastic. As a result, a clearance between the piston foot 27 and the surface 30 of the roller shoe 22 is avoided or at least reduced.
  • At least noise which can occur in particular when passing through the top dead center or the bottom dead center by striking the piston foot 27 on the surface 30 of the roller shoe 22, reduced. In this case, in particular, a path of the piston foot 27 relative to the roller shoe 22 can be considerably reduced.
  • a distance between the annular support surface 35, which is an attack plane for serving as a piston return spring plunger spring 31, with respect to the support surface formed by the survey 37 for the collar 28, which is an engagement plane for the piston driving the pump piston 11 be set to a desired value, which is preferably at least 0.2 mm.
  • the driving element 25 has in this embodiment a preferably central passage opening 40, through which the pump piston 11 extends. But there are also other embodiments of the through hole 40 possible.
  • the collar 28 of the pump piston 11 is disposed between the carrier element 25 and the carrier element 25 facing surface 30 of the roller shoe 22.
  • the elevation 37 of the driving element 25 is provided next to the passage opening 40, wherein the collar 28 of the pump piston 11 rests against the elevation 37.
  • Fig. 2 shows the driving element 25 of in Fig. 1 illustrated high-pressure pump 1 in a side view.
  • the annular support surface 35 is formed on an end face 38 of the driving element 25.
  • the annular support surface 35 forms an advantageous contact surface for the plunger spring 31.
  • the end face 38 is preferably designed substantially flat in an initial state.
  • a contact surface 39 is configured.
  • the contact surface 39 and the annular support surface 35 of the end face 38 are remote from each other.
  • On the contact surface 39 is supported in the assembled state of the piston 27 with his collar 28 from.
  • the collar 28 of the piston foot 27 engages behind the contact surface 39 of the survey 37 at least partially.
  • Between the annular support surface 35 of the end face 38 and the contact surface a predetermined distance 32 is realized. The distance 32 is predetermined with respect to the respective application.
  • Fig. 3 shows that in Fig. 2 illustrated entrainment element 25 in a three-dimensional representation.
  • the entrainment element 25 has a central passage opening 40.
  • the collar 28 of the pump piston 11 is then located between the driving element 25 and the surface 30 of the roller shoe 22.
  • the elevation 37 is configured in this embodiment as a circular elevation 37 , This results in an annular configuration of the contact surface 39.
  • the elevation 37 is surrounded by a plurality of slot-shaped recesses 41, 42, 43.
  • the recesses 41 to 43 are arranged adjacent to the central passage opening 40.
  • the slot-shaped recesses 41 to 43 extend in a circumferential direction about the central passage opening 40.
  • webs 44, 45, 46 are formed, which are elastically deformable.
  • the driving element 25 has an outer ring 47 on which the annular support surface 35 is formed for supporting the plunger spring 31.
  • the outer ring 47 is connected via the webs 44 to 46 with an inner ring 48.
  • the inner ring 48 in this case has the elevation 37.
  • a plunger spring 31 is provided, that the entrainment element 25 has an end face 38 which is remote from the roller shoe 22, and that the
  • End face 38 has an at least approximately annular support surface 35 on which the plunger spring 31 is supported.

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

Claims (7)

  1. Pompe à haute pression (1), notamment pompe à pistons radiaux ou en ligne pour systèmes d'injection de combustible de machines à combustion interne à autoallumage de compression d'air, comprenant au moins un sous-ensemble pompe (6) et un arbre d'entraînement (3) qui présente au moins une came (5) associée au sous-ensemble pompe (6), le sous-ensemble pompe (6) présentant un galet (23) qui tourne sur une surface de roulement (24) de la came (5), un patin de galet (22) qui accueille le galet (23), un piston de pompe (11) qui peut être actionné par la came (5) au moyen du galet (23) et par le patin de galet (22) dans un direction d'actionnement (13), et un élément d'entraînement (25) qui entraîne le piston de pompe (11) en sens inverse de la direction d'actionnement (13),
    caractérisée en ce
    que l'élément d'entraînement (25) est réalisé partiellement sous la forme d'un élément d'entraînement (25) résilient et en ce que l'élément d'entraînement (25) présente au moins un bossage (37) faisant face au patin de galet (22), sur lequel s'appuie le piston de pompe (11), en ce que l'élément d'entraînement (25) présente plusieurs évidements (41 - 43) qui sont distribués dans le sens radial autour d'une ouverture de passage (40) de préférence centrale et en ce que des nervures résilientes (44 - 46) sont configurées entre les évidements (41 - 43).
  2. Pompe à haute pression selon la revendication 1, caractérisée en ce que les évidements (41 - 43) sont réalisés sous la forme d'évidements (41 - 43) en forme de fentes et que les évidements (41 - 43) en forme de fentes s'étendent au moins approximativement dans une direction circonférentielle.
  3. Pompe à haute pression selon l'une des revendications 1 ou 2, caractérisée en ce que le piston de pompe (11) s'étend à travers l'ouverture de passage (40) de l'élément d'entraînement (25), en ce que le piston de pompe (11) présente un épaulement (28), en ce que l'épaulement (28) du piston de pompe (11) est disposé entre l'élément d'entraînement (25) et une surface (30) du patin de galet (22) faisant face à l'élément d'entraînement (25) et en ce que le bossage (37) de l'élément d'entraînement (25) est prévu à côté de l'ouverture de passage (40), l'épaulement (28) du piston de pompe (11) reposant sur le bossage (37).
  4. Pompe à haute pression selon la revendication 3, caractérisée en ce que le bossage (37) prévu à côté de l'ouverture de passage (40) est configuré au moins par portions en forme d'anneau et/ou en ce que le bossage (37) prévu à côté de l'ouverture de passage (40) entoure l'ouverture de passage (40) sous la forme d'un anneau.
  5. Pompe à haute pression selon l'une des revendications précédentes, caractérisée en ce que le bossage (37) de l'élément d'entraînement (25) présente une surface d'appui (39) sur laquelle repose l'épaulement (28) du piston de pompe (11), en ce que l'élément d'entraînement (25) présente un côté frontal (38) qui est à l'opposé de la surface d'appui (39) du bossage (37), et en ce que le côté frontal (38) est configuré sous la forme d'un côté frontal (38) au moins sensiblement plan.
  6. Pompe à haute pression selon la revendication 5, caractérisée en ce qu'un écart (32) entre la surface d'appui (39) du bossage (37) et le côté frontal (38) de l'élément d'entraînement (25) est au minimum égal à 0,2 mm.
  7. Pompe à haute pression selon l'une des revendications 3 à 6, caractérisée en ce que le bossage (37) de l'élément d'entraînement (25) est configuré de telle sorte que l'épaulement (28) du piston de pompe (11) est maintenu en appui avec la surface (30) du patin de galet (22).
EP11728881.1A 2010-07-27 2011-07-04 Pompe haute pression Active EP2598743B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010038468 DE102010038468A1 (de) 2010-07-27 2010-07-27 Hochdruckpumpe
PCT/EP2011/061222 WO2012013452A1 (fr) 2010-07-27 2011-07-04 Pompe haute pression

Publications (2)

Publication Number Publication Date
EP2598743A1 EP2598743A1 (fr) 2013-06-05
EP2598743B1 true EP2598743B1 (fr) 2014-11-05

Family

ID=44320389

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11728881.1A Active EP2598743B1 (fr) 2010-07-27 2011-07-04 Pompe haute pression

Country Status (6)

Country Link
EP (1) EP2598743B1 (fr)
JP (1) JP6042809B2 (fr)
CN (1) CN103026048B (fr)
DE (1) DE102010038468A1 (fr)
RU (1) RU2568359C2 (fr)
WO (1) WO2012013452A1 (fr)

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DE102011017573A1 (de) * 2011-04-27 2012-10-31 Robert Bosch Gmbh Federteller für eine Stößelbaugruppe einer Hochdruckpumpe sowie Hochdruckpumpe
ITMI20120270A1 (it) * 2012-02-23 2013-08-24 Bosch Gmbh Robert Pompa di alta pressione per alimentare combustibile ad un motore a combustione interna
DE102013212302A1 (de) * 2013-06-26 2014-12-31 Robert Bosch Gmbh Hochdruckpumpe und Kraftstoffeinspritzanlage mit einer Hochdruckpumpe
EP3205873A4 (fr) * 2014-10-09 2018-04-18 Hitachi Automotive Systems, Ltd. Pompe d'alimentation en carburant haute pression
GB201503591D0 (en) * 2015-03-03 2015-04-15 Delphi International Operations Luxembourg S.�.R.L. High pressure diesel fuel pumps and shoe arrangements
GB201506173D0 (en) * 2015-04-13 2015-05-27 Delphi Internat Operations Luxembourg S � R L Fuel pump
GB2542349A (en) 2015-09-15 2017-03-22 Gm Global Tech Operations Llc Fuel unit pump and internal combustion engine comprising it
CN105370465A (zh) * 2015-12-11 2016-03-02 中国北方发动机研究所(天津) 一种可变形补偿式高压变量泵柱塞
JP6305480B2 (ja) * 2016-09-01 2018-04-04 日機装株式会社 無脈動ポンプ
US20210394524A1 (en) * 2018-12-11 2021-12-23 Hewlett-Packard Development Company, L.P. Displacement pump
EP3742235B1 (fr) * 2019-05-23 2022-01-26 Meco S.A. Systeme de bouton-poussoir, et piece d'horlogerie le comprenant

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SU1224433A1 (ru) * 1984-02-02 1986-04-15 Производственное Объединение "Турбомоторный Завод" Им.К.Е.Ворошилова Топливный насос высокого давлени
DE4241826A1 (de) * 1992-12-11 1994-08-25 Teves Gmbh Alfred Hochdruckpumpe mit Radialkolben und Dämpfungsschicht
DE4401074B4 (de) * 1994-01-15 2007-01-18 Robert Bosch Gmbh Pumpenanordnung, insbesondere zur Förderung von Kraftstoff aus einem Vorratsbehälter zu einer Brennkraftmaschine
IT1289796B1 (it) * 1996-12-23 1998-10-16 Elasis Sistema Ricerca Fiat Perfezionamenti ad un dispositivo a pompa per l'alimentazione del carburante da un serbatoio ad un motore a combustione interna.
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JP4742122B2 (ja) * 2008-07-02 2011-08-10 日本発條株式会社 防振装置

Also Published As

Publication number Publication date
JP6042809B2 (ja) 2016-12-14
EP2598743A1 (fr) 2013-06-05
CN103026048A (zh) 2013-04-03
DE102010038468A1 (de) 2012-02-02
RU2568359C2 (ru) 2015-11-20
CN103026048B (zh) 2015-12-16
RU2013108357A (ru) 2014-09-10
JP2013532792A (ja) 2013-08-19
WO2012013452A1 (fr) 2012-02-02

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