EP1413756B1 - Pompe à combustible - Google Patents

Pompe à combustible Download PDF

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Publication number
EP1413756B1
EP1413756B1 EP20030013669 EP03013669A EP1413756B1 EP 1413756 B1 EP1413756 B1 EP 1413756B1 EP 20030013669 EP20030013669 EP 20030013669 EP 03013669 A EP03013669 A EP 03013669A EP 1413756 B1 EP1413756 B1 EP 1413756B1
Authority
EP
European Patent Office
Prior art keywords
fuel pump
cylinder
valve seat
valve
pump according
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
EP20030013669
Other languages
German (de)
English (en)
Other versions
EP1413756A1 (fr
Inventor
Helmut Rembold
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 EP1413756A1 publication Critical patent/EP1413756A1/fr
Application granted granted Critical
Publication of EP1413756B1 publication Critical patent/EP1413756B1/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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F04B49/22—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 means of valves
    • F04B49/24—Bypassing
    • F04B49/243—Bypassing by keeping open the inlet valve

Definitions

  • the invention relates to a high-pressure fuel pump for a fuel injection system of an internal combustion engine according to the preamble of claim 1.
  • a high-pressure fuel pump is known from the unpublished German patent application 101 34 066.4.
  • Quantity control valve completely integrated into a cylinder head of the high-pressure fuel pump.
  • the quantity control valve takes over the supply of a delivery chamber of the high-pressure fuel pump with fuel and the control of the delivery of the high-pressure fuel pump. This happens because a spring-loaded valve member lifts from its sealing seat as soon as there is a lower pressure in the delivery chamber during the suction stroke of the high-pressure fuel pump than in front of the valve member. When the valve member has lifted from its sealing seat, fuel can flow from a low-pressure fuel line into the delivery chamber.
  • valve member During the subsequent delivery stroke of the high-pressure fuel pump, the valve member is moved in the direction of the sealing seat due to the changed pressure conditions and by a closing spring. When the valve member rests on the sealing seat, the pressure in the delivery chamber during the delivery stroke rises rapidly and the fuel is pushed into a high-pressure fuel line.
  • an electric actuator is provided in the quantity control valve, which can keep the valve member from its sealing seat via a plunger. This means that with a corresponding control of the actuator in the delivery chamber during the delivery stroke of the high-pressure fuel pump, no pressure build-up takes place, but the fuel located in the delivery chamber is pushed back into the low-pressure fuel line. Only when the valve member rests on the sealing seat by a changed control of the actuator, the already described pressure build-up takes place and fuel is discharged from the Delivery chamber promoted in the high-pressure fuel line. Depending on how long the valve member is kept open during the delivery stroke of the high pressure fuel pump, the delivery rate of the high pressure fuel pump changes.
  • the cylinder head is at least partially acted upon by the pressure prevailing in the delivery chamber high pressure.
  • the connection between the cylinder head and the cylinder of the high-pressure fuel pump must transmit large forces, and high demands are placed on the seal between the cylinder head and cylinder of the high-pressure fuel pump.
  • valve seat is designed as a separate plate-shaped component. This plate-shaped component is clamped between the cylinder and the cylinder head.
  • valve seat is mounted in a cylindrical recess of the cylinder or screwed into an internal thread of the cylinder.
  • the construction according to the invention makes it possible to produce the valve seat from a different material than the cylinder.
  • the production of the valve seat is simplified because it is a very simple component in the separate valve seat.
  • the valve seat has a cylindrical portion which forms a press fit with a cylindrical recess of the cylinder.
  • a press fit a cost-effective and reliable connection of the valve seat with the cylinder is guaranteed.
  • the interference fit has a sealing effect, so that valve seat and cylinder need not be additionally sealed.
  • the valve seat is seated so firmly in the cylinder that it does not "migrate” despite the pumping chamber-side loading with very high pressures.
  • a groove for receiving a securing ring, in particular a Seeger ring is present in the cylindrical recess of the cylinder.
  • the valve seat can form fit in addition to the described interference fit be secured in the cylinder, so that even under unfavorable circumstances, a secure attachment of the valve seat is ensured in the cylinder.
  • valve seat can also be caulked with the cylindrical recess of the cylinder.
  • valve seat may also have an external thread and be screwed into an internal thread of the cylinder.
  • an additional seal for example in the form of a biting edge on the end face of the valve seat, is provided between the valve seat and the cylinder.
  • the actuator of the quantity control valve is arranged in a cylinder head of the fuel pump. Since the cylinder head of the high-pressure fuel pump according to the invention and thus also the actuator is no longer subjected to the high pressures of the delivery chamber of the high pressure fuel pump, the actuator can be easily mounted in the cylinder head. For example, the actuator can be caulked in the cylinder head. This caulking is very inexpensive and can be used advantageously especially for large series.
  • the cylinder head with the cylinder screwed, wherein in a particularly preferred variant of the invention, one of the screws for fixing the cylinder head is designed as a hollow screw and this hollow screw fuel is discharged from the relief groove. This eliminates the need to provide a separate discharge channel extending from the relief groove to a low pressure port of the high pressure fuel pump.
  • FIG. 1 shows an embodiment of a high-pressure fuel pump according to the invention is shown in section.
  • the main components of the high-pressure fuel pump 10 are a cylinder 12, a cylinder head 14, which is bolted to the cylinder 12, and a quantity control valve sixteenth
  • the cylinder 12 has a cylinder bore 18 in which a piston 20 oscillates.
  • the movement of the piston 20 is indicated in Figure 1 by a double arrow 22.
  • the piston 20 and the cylinder bore 18 define together with the quantity control valve 16 a delivery chamber 24th
  • a high-pressure fuel line 112 From the delivery chamber 24 is a high-pressure fuel line 112 from.
  • an outlet valve 26 is provided in the cylinder 12.
  • the outlet valve 26 can be designed, for example, as a spring-loaded ball valve.
  • the delivery chamber 24 is filled with fuel during the intake stroke of the high-pressure fuel pump 10.
  • a transverse bore 30 is present, which connects the low pressure port 28 with a central bore 32 of the cylinder head 14,.
  • the transverse bore 30 makes a hydraulic connection to a pressure damper 34, which is also arranged on the cylinder head 14.
  • the pressure damper 34 has the task to dampen the resulting from the movement of the piston 20 and the control of the quantity control valve 16 pressure surges in the low pressure region of the high-pressure fuel pump 10. This improves the operating behavior of the high-pressure fuel pump 10.
  • the quantity control valve 16 consists essentially of an electric actuator 36 and a valve member 38, which cooperates with a valve seat 40. In the position of the valve member 38 shown in FIG. 1, this rests on the valve seat 40, so that there is no hydraulic connection between the delivery chamber 24 and the low-pressure connection 110.
  • the valve member 38 is held by a compression spring 42 in contact with the valve seat 40.
  • the plunger 44 is part of the electric actuator 36 of the quantity control valve 16.
  • the electric actuator 36 includes in addition to the plunger 44 nor an armature 46 which is fixedly connected to the plunger 44, and an electromagnet 48, which exerts a force on the armature 48 in the energized state.
  • armature 46 and plunger 44 move so far in the direction of delivery chamber 24 that the valve member 38 is no longer resting on the valve seat 40.
  • a hydraulic connection between the low-pressure fuel line 110 and the delivery chamber 24 can be maintained by the electric actuator 36.
  • no pressure build-up in the delivery chamber 24 takes place and no fuel is expelled from the delivery chamber 24 into the high-pressure fuel line 110.
  • the delivery rate of the high-pressure fuel pump 10 can be regulated between 0% and 100% of the delivery chamber volume by the suitable control of the electric actuator 36.
  • the valve seat 40 is not integrated in the cylinder head 14, but arranged in the cylinder 12.
  • the valve seat 40 is designed as a separate component with a cylindrical outer surface 54.
  • the cylindrical outer surface 54 of the valve seat 40 forms with a correspondingly shaped cylindrical recess 56 of the cylinder 12 a press fit.
  • the valve seat 40 is securely fastened in the cylinder 12 and no fuel can escape from the delivery space 24 through the contact surface between the cylindrical outer surface 54 and the cylindrical recess 56.
  • a groove 58 is provided, in which a locking ring 60 is inserted.
  • the valve seat 40 is additionally secured in the cylinder 12.
  • valve seat 40 Since the valve seat 40 is designed as a rotationally symmetrical component, it can be very easily manufactured by turning and / or grinding with the required precision. It is also possible to harden the valve seat 40 in order to increase its service life.
  • the first compression spring 42 is supported at one end against the valve member 38 and at the other end against a shoulder 62 of the valve seat 40.
  • the drive of the piston 20, for example via a drive shaft with an eccentric portion (not shown), is not shown in Figure 1.
  • drives are known from the prior art.
  • the cylinder 12 is fastened via a clamping claw 64, which is supported on a cylinder head 66 of the internal combustion engine and engages in a recess 68 of the cylinder 12.
  • the clamping claw 64 is biased by a screw 70.
  • a relief groove 72 is incorporated, via which the leakage between the cylinder bore 18 and piston 20 can be removed.
  • To the relief groove 72 includes a relief hole 74, which cuts a threaded hole 76 in the cylinder 12.
  • a hollow screw 78 is screwed, which fixes the cylinder head 14 on the cylinder 12. Via a longitudinal bore 80 and a transverse bore 82 of the hollow screw 78 thus a hydraulic connection between the relief groove 72 and the low pressure port 28 is produced.
  • FIG. 2 shows a fuel injection system 102.
  • This comprises a fuel tank 104, from which fuel 106 is conveyed by an electric fuel pump 108. Via a low-pressure fuel line 110, the fuel 106 is conveyed to a high-pressure fuel pump 10 with a quantity control valve 16 according to FIG. From the high pressure fuel pump 10, the fuel 106 passes through a high pressure fuel line 112 to a common rail 114.
  • a plurality of injection valves 116 are connected, which inject the fuel directly into combustion chambers 118 of the internal combustion engine (not shown).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (9)

  1. Pompe de carburant notamment haute pression (10), pour une installation d'injection de carburant (102) d'un moteur à combustion à injection directe d'essence comprenant un piston (20), des moyens d'entraînement pour entraîner le piston (20), un cylindre (12) guidant le piston (20), une soupape de sortie (26) ainsi qu'une soupape de dosage (16),
    cette soupape de dosage (16) ayant un siège de soupape (40), un organe de soupape (38) coopérant avec le siège de soupape (40) et un actionneur (36) réglant l'organe de soupape (38) et comprenant un électroaimant (48), et le siège de soupape (40) étant une pièce distincte,
    caractérisée en ce que
    le siège de soupape (40) est fixé dans une cavité cylindrique (56) du cylindre (12).
  2. Pompe à carburant selon la revendication 1,
    caractérisée en ce que
    le siège de soupape (40) comporte une surface extérieure (54) cylindrique, et
    cette surface extérieure cylindrique (54) forme un siège pressé avec la cavité cylindrique (56) du cylindre (12).
  3. Pompe à carburant selon la revendication 1,
    caractérisée en ce que
    le siège de soupape (40) a une surface extérieure (54) cylindrique, et cette surface extérieure (54) cylindrique est matée dans la cavité cylindrique (56) du cylindre (12).
  4. Pompe à carburant selon l'une quelconque des revendications 1 à 3,
    caractérisée en ce que
    la cavité cylindrique (56) du cylindre (12) comporte une rainure (58) pour recevoir un anneau de sécurité (60) notamment un anneau Seeger.
  5. Pompe à carburant selon la revendication 1,
    caractérisée en ce que
    le siège de soupape (40) comporte un filetage extérieur, et le siège de soupape (40) est vissé dans le filetage intérieur du cylindre (12).
  6. Pompe à carburant selon l'une quelconque des revendications précédentes,
    caractérisée par
    une rainure de décharge (72) dans le cylindre (12).
  7. Pompe à carburant selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    l'entraînement de réglage (36) est prévu dans la culasse (14) de la pompe à haute pression de carburant (10).
  8. Pompe à carburant selon la revendication 7,
    caractérisée en ce que
    la culasse (14) est vissée au cylindre (12).
  9. Pompe à carburant selon la revendication 8,
    caractérisée en ce qu'
    une vis servant à la fixation de la culasse (14) est une vis creuse (78), et le carburant est évacué de la rainure de décharge (72) vers le branchement basse pression (28) à travers cette vis creuse (78).
EP20030013669 2002-10-25 2003-06-17 Pompe à combustible Expired - Lifetime EP1413756B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10249688 2002-10-25
DE2002149688 DE10249688A1 (de) 2002-10-25 2002-10-25 Kraftstoff-Hochdruckpumpe für eine Kraftstoffeinspritzanlage, insbesondere eine Common-Rail-Kraftstoffeinspritzanlage, von Brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP1413756A1 EP1413756A1 (fr) 2004-04-28
EP1413756B1 true EP1413756B1 (fr) 2006-10-25

Family

ID=32049603

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20030013669 Expired - Lifetime EP1413756B1 (fr) 2002-10-25 2003-06-17 Pompe à combustible

Country Status (2)

Country Link
EP (1) EP1413756B1 (fr)
DE (2) DE10249688A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4415884B2 (ja) * 2005-03-11 2010-02-17 株式会社日立製作所 電磁駆動機構，電磁弁機構及び電磁駆動機構によって操作される吸入弁を備えた高圧燃料供給ポンプ，電磁弁機構を備えた高圧燃料供給ポンプ
US7540721B2 (en) 2005-07-29 2009-06-02 Wagner Spray Tech Corporation Automatic inlet check valve release
JP4958023B2 (ja) 2010-01-18 2012-06-20 株式会社デンソー 高圧ポンプ
DE102011005487A1 (de) 2011-03-14 2012-09-20 Robert Bosch Gmbh Ventileinrichtung, insbesondere Auslassventil einer Kraftstoff-Hochdruckpumpe einer Brennkraftmaschine
JP6773943B2 (ja) * 2015-02-11 2020-10-21 ドットーレ・インジェニェーレ・マリオ・コッツァーニ・ソシエタ・ア・レスポンサビリタ・リミタータ 往復圧縮機のフロー制御アクチュエータ
DE102017216626B3 (de) 2017-09-20 2018-10-11 Continental Automotive Gmbh Ventil für eine Hochdruckpumpe für ein Kraftfahrzeug und Verfahren zum Herstellen eines Ventils für eine Hochdruckpumpe

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4213798C2 (de) * 1992-04-27 2002-10-24 Bosch Gmbh Robert Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren
DE4401073A1 (de) * 1994-01-15 1995-07-20 Rexroth Mannesmann Gmbh Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren
DE19644915A1 (de) * 1996-10-29 1998-04-30 Bosch Gmbh Robert Hochdruckpumpe
WO2000047888A1 (fr) * 1999-02-09 2000-08-17 Hitachi, Ltd. Pompe d'alimentation en combustible a haute pression faisant partie d'un moteur a combustion interne

Also Published As

Publication number Publication date
DE50305471D1 (de) 2006-12-07
DE10249688A1 (de) 2004-05-06
EP1413756A1 (fr) 2004-04-28

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