EP1413756A1 - Pompe à combustible - Google Patents

Pompe à combustible Download PDF

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Publication number
EP1413756A1
EP1413756A1 EP03013669A EP03013669A EP1413756A1 EP 1413756 A1 EP1413756 A1 EP 1413756A1 EP 03013669 A EP03013669 A EP 03013669A EP 03013669 A EP03013669 A EP 03013669A EP 1413756 A1 EP1413756 A1 EP 1413756A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
fuel pump
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.)
Granted
Application number
EP03013669A
Other languages
German (de)
English (en)
Other versions
EP1413756B1 (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, in particular with common rail and gasoline direct injection, with a piston, with drive means for driving the piston, with a cylinder in which the piston is guided, with an exhaust valve and Quantity control valve, the quantity control valve having a valve seat, a valve member interacting with the valve seat and an actuator comprising an electromagnet that adjusts the valve member.
  • Such a high-pressure fuel pump is known from the unpublished German patent application 101 34 066.4. This is with this high-pressure fuel pump Volume control valve fully integrated in a cylinder head of the high pressure fuel pump.
  • the volume control valve takes over the supply of a delivery chamber of the high-pressure fuel pump with fuel and the control of the delivery rate of the high-pressure fuel pump. This happens because a spring-loaded valve member lifts off its sealing seat as soon as a lower pressure prevails 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 into the delivery chamber from a low-pressure fuel line.
  • 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. If the valve member rests on the sealing seat, the pressure in the delivery chamber increases rapidly during the delivery stroke and the fuel is pushed out into a high-pressure fuel line.
  • an electric actuator is provided in the volume control valve, which can keep the valve member away from its sealing seat via a tappet. This means that if the actuator in the delivery chamber is actuated accordingly, no pressure build-up takes place during the delivery stroke of the high-pressure fuel pump, but the fuel in the delivery chamber is pushed back into the low-pressure fuel line. Only when the valve member rests on the sealing seat due to a modified control of the actuator does the pressure build-up already described take place and fuel is produced from the Conveyed into 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 subjected to the high pressure prevailing in the delivery chamber.
  • the connection between the cylinder head and the cylinder of the high-pressure fuel pump must transmit large forces and high demands are made on the seal between the cylinder head and the cylinder of the high-pressure fuel pump.
  • a high-pressure fuel pump for a fuel system of an internal combustion engine with gasoline direct injection with a piston, with drive means for driving the piston, with a cylinder in which the piston is guided, with an outlet valve and with a quantity control valve, wherein the quantity control valve has a valve seat, a valve member interacting with the valve seat and an actuator comprising an electromagnet that adjusts the valve member, the valve seat is arranged in the cylinder.
  • the quantity control valve has a valve seat, a valve member interacting with the valve seat and an actuator comprising an electromagnet that adjusts the valve member, the valve seat is arranged in the cylinder.
  • valve seat is designed as a separate component and is fastened in the cylinder.
  • valve seat can be made of a different material than the cylinder and the manufacture of the valve seat is simplified since the separate valve seat is a very simple component.
  • the valve seat has a cylindrical section which forms an interference fit with a cylindrical recess in the cylinder.
  • a press fit ensures an inexpensive and reliable connection of the valve seat to the cylinder.
  • the press fit also has a sealing effect, so that the valve seat and cylinder do not have to be sealed additionally. With a suitable choice of press fit, the valve seat sits so firmly in the cylinder that it does not "wander" despite the fact that very high pressures are applied to the delivery chamber.
  • a groove for receiving a securing ring is present in the cylindrical recess of the cylinder. This allows the valve seat to be form-fitting in addition to the press fit described are attached in the cylinder, so that a secure attachment of the valve seat in the cylinder is guaranteed even under the most unfavorable circumstances.
  • valve seat can also be caulked with the cylindrical recess of the cylinder.
  • valve seat can also have an external thread and can be screwed into an internal thread of the cylinder. In this case, an additional seal must be provided between the valve seat and the cylinder, for example in the form of a biting edge on the end face of the valve seat.
  • 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 are no longer subjected to the high pressures of the delivery chamber of the high-pressure fuel pump, the actuator can be fastened in a simple manner in the cylinder head. For example, the actuator can be caulked in the cylinder head. This caulking is very inexpensive and can be used to advantage, particularly in large series.
  • the cylinder head with the cylinder screwed wherein in a particularly preferred variant of the invention, one of the screws for fastening the cylinder head is designed as a hollow screw and fuel is discharged from the relief groove via this hollow screw. This eliminates the need to provide a separate relief channel that runs from the relief groove to a low-pressure connection of the high-pressure fuel pump.
  • FIG. 1 an embodiment of a high-pressure fuel pump according to the invention is shown in section.
  • the essential assemblies of the high-pressure fuel pump 10 are a cylinder 12, a cylinder head 14 which is screwed to the cylinder 12, and a quantity control valve 16.
  • 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.
  • a high-pressure fuel line 112 extends from the delivery chamber 24.
  • an exhaust valve 26 is provided in the cylinder 12.
  • the exhaust valve 26 can be designed, for example, as a spring-loaded ball valve.
  • the delivery chamber 24 is filled with fuel during the suction stroke of the high-pressure fuel pump 10.
  • transverse bore 30 which connects the low-pressure connection 28 to a central bore 32 of the cylinder head 14.
  • transverse bore 30 establishes a hydraulic connection to a pressure damper 34, which is also arranged on the cylinder head 14.
  • the pressure damper 34 has the task of damping the pressure surges resulting from the movement of the piston 20 and the actuation of the quantity control valve 16 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, it 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 in contact with the valve seat 40 via a compression spring 42. When the piston 20 moves in the direction of the valve member 38 (delivery stroke), the pressure in the delivery chamber 24 rises until the outlet valve 26 opens and fuel is pushed out of the delivery chamber 24 into the high-pressure fuel line 112.
  • the electric actuator 36 also comprises an armature 46, which is firmly connected to the tappet 44, and an electromagnet 48, which exerts an actuating force on the armature 48 in the energized state.
  • the electromagnet 48 is energized, so that the armature 46 moves away from the valve member 38 against a force exerted by a second compression spring 50.
  • this removal from the valve member 38 corresponds to an upward movement of the armature 46 and thus also of the tappet 44.
  • the second compression spring 50 is supported at one end against the armature 46 and at the other end against a cover 52 of the quantity control valve 16.
  • the cover 52 is caulked to the cylinder head 14. This type of connection, which is very simple in terms of production technology, is sufficient in the high-pressure fuel pump 10 according to the invention, since only the pressure of the low-pressure connection 110 prevails in the cylinder head.
  • the valve seat 40 is not integrated in the cylinder head 14, but is 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 an interference fit with a correspondingly shaped cylindrical recess 56 of the cylinder 12.
  • the valve seat 38 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 the cylindrical recess 56, into which a retaining ring 60 is inserted.
  • the valve seat 38 is additionally secured in the cylinder 12.
  • valve seat 38 Since the valve seat 38 is designed as a rotationally symmetrical component, it can be produced very simply 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.
  • drives are known from the prior art.
  • the cylinder 12 is fastened by means of a clamping claw 64, which is supported on a cylinder head 66 of the internal combustion engine and engages in a recess 68 in the cylinder 12.
  • the clamping claw 64 is prestressed by a screw 70.
  • a relief groove 72 is incorporated in the cylinder bore 18, via which the leakage between the cylinder bore 18 and the piston 20 can be removed.
  • a relief bore 74 adjoins the relief groove 72, which cuts a threaded bore 76 in the cylinder 12.
  • a hollow screw 78 is screwed into the threaded bore 76 and fastens the cylinder head 14 to the cylinder 12.
  • a hydraulic connection between the relief groove 72 and the low-pressure connection 28 is thus established via a longitudinal bore 80 and a transverse bore 82 of the hollow screw 78.
  • a fuel injection system 102 is shown in FIG. 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. 1. From the high-pressure fuel pump 10, the fuel 106 reaches a common rail 114 via a high-pressure fuel line 112.
  • a plurality of injection valves 116 are connected to the common rail 114 and 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)
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 true EP1413756A1 (fr) 2004-04-28
EP1413756B1 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)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2282044A1 (fr) * 2005-03-11 2011-02-09 Hitachi Ltd. Pompe d'alimentation en carburant haute pression
US8529220B2 (en) 2010-01-18 2013-09-10 Denso Corporation High-pressure pump
CN107532582A (zh) * 2015-02-11 2018-01-02 工学博士马里奥·科扎尼有限责任公司 用于往复式压缩机的流量控制致动器
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
DE112006001910B4 (de) 2005-07-29 2021-12-23 Wagner Spray Tech Corp. Automatische Freigabeeinrichtung für eine Farbpumpe mit einem Einlasssperrventil

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011005487A1 (de) 2011-03-14 2012-09-20 Robert Bosch Gmbh Ventileinrichtung, insbesondere Auslassventil einer Kraftstoff-Hochdruckpumpe einer Brennkraftmaschine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4213798A1 (de) * 1992-04-27 1993-10-28 Rexroth Mannesmann Gmbh Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren
DE4401073A1 (de) * 1994-01-15 1995-07-20 Rexroth Mannesmann Gmbh Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren
US6116870A (en) * 1996-10-29 2000-09-12 Robert Bosch Gmbh High pressure pump with solenoid operated valve
EP1162365A1 (fr) * 1999-02-09 2001-12-12 Hitachi, Ltd. Pompe d'alimentation en combustible a haute pression faisant partie d'un moteur a combustion interne

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4213798A1 (de) * 1992-04-27 1993-10-28 Rexroth Mannesmann Gmbh Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren
DE4401073A1 (de) * 1994-01-15 1995-07-20 Rexroth Mannesmann Gmbh Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren
US6116870A (en) * 1996-10-29 2000-09-12 Robert Bosch Gmbh High pressure pump with solenoid operated valve
EP1162365A1 (fr) * 1999-02-09 2001-12-12 Hitachi, Ltd. Pompe d'alimentation en combustible a haute pression faisant partie d'un moteur a combustion interne

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2282044A1 (fr) * 2005-03-11 2011-02-09 Hitachi Ltd. Pompe d'alimentation en carburant haute pression
DE112006001910B4 (de) 2005-07-29 2021-12-23 Wagner Spray Tech Corp. Automatische Freigabeeinrichtung für eine Farbpumpe mit einem Einlasssperrventil
US8529220B2 (en) 2010-01-18 2013-09-10 Denso Corporation High-pressure pump
CN107532582A (zh) * 2015-02-11 2018-01-02 工学博士马里奥·科扎尼有限责任公司 用于往复式压缩机的流量控制致动器
CN107532582B (zh) * 2015-02-11 2019-07-16 工学博士马里奥·科扎尼有限责任公司 用于往复式压缩机的流量控制致动器
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

Also Published As

Publication number Publication date
DE10249688A1 (de) 2004-05-06
DE50305471D1 (de) 2006-12-07
EP1413756B1 (fr) 2006-10-25

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