EP2399031B1 - Pompe à carburant - Google Patents

Pompe à carburant Download PDF

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Publication number
EP2399031B1
EP2399031B1 EP09801210.7A EP09801210A EP2399031B1 EP 2399031 B1 EP2399031 B1 EP 2399031B1 EP 09801210 A EP09801210 A EP 09801210A EP 2399031 B1 EP2399031 B1 EP 2399031B1
Authority
EP
European Patent Office
Prior art keywords
throttle
pump
fuel pump
duct
fuel
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
EP09801210.7A
Other languages
German (de)
English (en)
Other versions
EP2399031A1 (fr
Inventor
Marcus Kristen
Armin Merz
Markus Grieb
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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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2399031A1 publication Critical patent/EP2399031A1/fr
Application granted granted Critical
Publication of EP2399031B1 publication Critical patent/EP2399031B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/12—Combinations of two or more pumps the pumps being of different types at least one pump being of the rotary-piston positive-displacement type
    • 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
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • F04B23/103—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being a radial piston pump
    • 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

Definitions

  • the invention relates to a fuel pump, in particular a low-pressure pump of a pump arrangement with a low-pressure pump and a high-pressure pump. Specifically, the invention relates to the field of fuel injection systems of air compressing, self-igniting internal combustion engines.
  • the known pump arrangement is particularly suitable for a common rail injection system.
  • the known pump arrangement comprises a radial piston pump with a drive shaft mounted in a pump housing and a low pressure pump upstream of the radial piston pump.
  • the supply of a fuel from the low-pressure pump to the high pressure pump via a running through an intake manifold inlet channel and a connecting channel, which are located in the pump housing.
  • the inlet channel extends in a first direction and the connecting channel extends in a direction which deviates from the direction of the inlet channel.
  • the inlet channel opens laterally into the blind channel configured as a connecting channel.
  • the fuel pump according to the invention with the features of claim 1 has the advantage that an operation is improved. Specifically, a fuel pump can be created, which has a throttle for limiting flow, with an advantageous mode of operation of the throttle and at the same time a deflection for a fuel is realized.
  • a throttle may be designed as a diaphragm or nozzle.
  • the length is much larger than a throttle diameter.
  • the throttle is not configured as such a laminar throttle.
  • a ratio of a length of the throttle to a diameter of the throttle is less than about 1.5.
  • the ratio of the length of the throttle to the diameter of the throttle may also be greater than 1.5, in particular slightly greater than 1.5.
  • the throttle may be arranged in the extension of the inlet channel. This allows the design of the inlet channel together with the throttle by means of a step tool.
  • a configuration can be realized in which a flow separation in the region of the throttle is prevented or at least reduced, whereby the full throttle diameter is effective. Together with a subsequent large connection channel or the like. This can be achieved a good throttle effect.
  • the inlet channel has a conical end section and that the throttle adjoins the conical end section.
  • the throttle is at least approximately aligned with an axis of the inlet channel.
  • the throttle is designed as a throttle bore.
  • an advantageous positioning of the throttle is given.
  • a simple configuration by means of a step tool is possible.
  • the inlet channel can be configured in an advantageous manner as an inlet bore, which extends at least in sections through an inlet connection.
  • the inlet channel can be configured in a housing part of the high-pressure pump, wherein the inlet nozzle can be an integral part of the housing part.
  • the throttle and the connecting channel can be integrated in an advantageous manner in a housing part of an external gear pump.
  • Fig. 1 shows a fuel pump 1 in a side view according to an embodiment of the invention.
  • the fuel pump 1 can in particular be configured as a pump arrangement with a low-pressure pump, for example an external gear pump 2, and a high-pressure pump 3 for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • the fuel pump 1 can also be designed as another gear pump, in particular internal gear pump, or as a vane pump.
  • a preferred use of the fuel pump 1 is for a fuel injection system having a fuel rail which stores diesel fuel under high pressure.
  • the fuel pump 1 according to the invention is also suitable for other applications.
  • the fuel pump 1 of the exemplary embodiment has a first pump part 2, which is designed as an external gear pump 2, and a second pump part 3, which is designed as a high-pressure pump 3, on.
  • the second pump part 3 lies behind the first pump part 2 and is partially covered by the first pump part 2.
  • a feed or intake 4 is provided, can be supplied via the fuel from a tank or the like. From the inlet nozzle 4, the fuel passes through the housing of the second pump part 3 to the gear pump forming the first pump part 2, that of the second pump part 3 forming high-pressure pump is connected upstream.
  • the first pump part 2 therefore has the function of a low-pressure pump, while the second pump part 3 has the function of a high-pressure pump.
  • the high-pressure pump of the second pump part 3 can be designed in particular as a radial piston pump.
  • the first pump part 2 has gears 5, 6, whose position in the Fig. 1 represented by broken lines.
  • the gears 5, 6 are covered by a housing part 7 of the external gear pump 2, which is designed as a housing 7 of the external gear pump 2.
  • the housing part 7 is connected to fixed points 8A, 8B, 8C, 8D with a housing part 9 of the second pump part 3.
  • the housing part 9 is designed as a high-pressure pump housing 9.
  • the inlet nozzle 4 is part of the housing part 9.
  • the housing part 7 at four fixed points 8 A, 8 B, 8 C, 8 D is connected to the housing part 9 of the second pump part 3.
  • different arrangements for the fixed points 8A, 8B, 8C, 8D are possible.
  • a different number of fixed points may be provided, in particular, three fixed points may be provided to connect the housing parts 7, 9 with each other.
  • Fig. 2 shows an excerpted section through the housing part 9 of FIG Fig. 1 shown fuel pump 1 along the designated II cutting line according to a conventional embodiment.
  • an inlet channel 15 is formed, which is designed as a blind hole.
  • the inlet channel 15 extends in sections through the inlet nozzle 4, wherein the inlet channel 15, in particular in the region of the inlet nozzle 4, can be configured as a stepped bore.
  • the inlet channel 15 extends in a direction 16 through the housing part 9.
  • the inlet channel 15 has an axis 17 along which the inlet channel 15 extends in the direction 16.
  • the inlet channel 15 has a bore bottom 18, on which the inlet channel 15 designed as a blind hole ends.
  • the bore bottom 18 is designed conical.
  • a connecting channel 19 is also formed, which is configured by a bore.
  • the connecting channel 19 opens into the inlet channel 15 at the bore bottom 18.
  • the connecting channel 19 has an axis 21 along which the connecting channel 19 extends in one direction 22.
  • fuel is fed via the inlet channel 15 and the connecting channel 19 to the external gear pump 2.
  • the fuel flows in the direction 16 through the inlet channel 15 and in the direction 22 through the connecting channel 19.
  • the direction 16 of the inlet channel 15 includes with the direction 22 of the connecting channel 19 an angle 23 of about 90 °. That is, the axis 17 of the inlet channel 15 closes with the axis 21 of the connecting channel 19, the angle 23 of about 90 °.
  • the external gear pump 2 is preferably operated in suction-throttled operation in order to limit a flow rate.
  • the throttle effect required for this purpose is achieved through the connecting channel 19.
  • a cross section of the connecting channel 19 is set relatively small, so that the connecting channel 19 as a throttle acts.
  • acting as a throttle connection channel 19 is seated at an angle of approximately 90 ° to the inlet channel 15.
  • the flow from the wall of the connecting channel 19 comes off in a region 24 of the connecting channel 19.
  • the full cross section of the connecting channel 19 no longer acts as a throttle. The effect of the throttle is thereby changed and possibly undetermined.
  • the throttling action of the connecting channel 19 is dependent on the transition of the inlet channel 15 in the connecting channel 19 at the bottom of the hole 18.
  • the transition depending on the configuration of the intersection between the channels 15, 19 vary. Possible reasons for varying transitions between the inlet channel 15 and the connecting channel 19 are, for example:
  • the connecting channel 19 meets in the bore bottom 18 or in a cylindrical part 25 of the inlet channel 15.
  • the angle 23 between the inlet channel 15 and the connecting channel 19 may vary, for example due to interference contours.
  • the diameter or cross section of the inlet channel 15 at the transition to the connecting channel 19 may vary due to interference contours.
  • the throttle effect of the throttle formed by the connecting channel 19 can vary. As a result, the throttle behavior of the connection channel 19 is not determined, so that no ideal throttle behavior is present.
  • the above points may also result in that for each variant of the high-pressure pump, in particular for legal and Linksmoortagen, a separate throttle diameter for the connecting channel 19 must be specified and votes are required.
  • Fig. 3 shows the in Fig. 2 shown section of the housing part 9 of the fuel pump 1 according to the embodiment of the invention.
  • the connecting channel 19 extends in a direction 22 which deviates from a direction 16 of the inlet channel 15. However, adjoining the inlet channel 15 in the direction 16, a throttle 30, which is aligned in this embodiment of the axis 17, the inlet channel 15.
  • the connecting channel 19 is configured in the form of a blind bore, which has a bore base 31.
  • the connecting channel 19 has a cylindrical portion 32.
  • the throttle 30 opens laterally into the connecting channel 19 and indeed into the cylindrical portion 32 of the connecting channel 19.
  • the inlet channel 15 has a conical end portion 33.
  • the conical end portion 33 connects in the direction 16 to the cylindrical part 25 of the inlet channel 15.
  • the throttle 30 connects.
  • a transition from the cylindrical part 25 of the inlet channel 15 is formed in the throttle 30.
  • the connecting channel 19 has a diameter or cross section which is relatively large compared to a diameter or cross section of the throttle 30. This results in a favorable intersection between the throttle 30 and the connecting channel 19, wherein a reproducible in the production of the intersection line 34, which preferably deviates only slightly from a circular intersection line.
  • Both the Inlet channel 15 and the connecting channel 19 have essentially no throttle effect.
  • a specific throttle effect of the throttle 30 is predetermined.
  • the effective length of the throttle 30 is therefore obtained uniformly along the circumference of the throttle 30. Thereby, a defined throttle effect of the throttle 30 is given.
  • the effect of the throttle 30 can be specified in a simple manner.
  • the diameter or cross section of the throttle 30 can be specified. Since the throttle 30 directly adjoins the inlet channel 15 in the direction 16, the inlet channel 15 can be produced together with the throttle 30 by means of a stepping tool.
  • the throttle 30 can also be integrated into the housing part 7 of the external gear pump 2. In this case, defined ratios for the throttle 30 can also be created.
  • the angle 23 between the inlet channel 15 and the connecting channel 19 is preferably equal to 90 °. This is production technology advantageous. However, a beneficial throttling effect can also be applied to other angles 23 not equal to 90 ° are reached. It is particularly advantageous if the angle 23 is equal to or greater than 90 °, for example equal to 110 °. This is Strömsstochnisch advantageous.

Landscapes

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

Claims (8)

  1. Pompe à carburant (1) pour un agencement de pompe comprenant une pompe basse pression et une pompe haute pression pour des installations d'injection de carburant de moteurs à combustion interne à auto-allumage et compression d'air, comprenant un canal d'alimentation (15) et un canal de liaison (19) du côté d'aspiration de la pompe à carburant, le canal de liaison (19) s'étendant dans une direction (22) qui s'écarte d'une direction (16) du canal d'alimentation (15), le canal d'alimentation (15) débouchant latéralement dans le canal de liaison (19) configuré sous forme d'alésage borgne, caractérisée en ce qu'il est prévu un étranglement (30) se raccordant dans la direction (16) du canal d'alimentation (15) au canal d'alimentation (15) et débouchant latéralement dans le canal de liaison (19), lequel débouche perpendiculairement dans une section cylindrique (32) du canal de liaison (19), et en ce qu'une section transversale du canal de liaison (19) est plus grande qu'une section transversale de l'étranglement (30).
  2. Pompe à carburant selon la revendication 1, caractérisée en ce que le canal d'alimentation (15) présente une section d'extrémité conique (33) et en ce que l'étranglement (30) se raccorde à la section d'extrémité conique (33).
  3. Pompe à carburant selon l'une quelconque des revendications 1 ou 2, caractérisée en ce que le canal d'alimentation (15) présente un axe (17) et en ce que l'étranglement (30) est aligné avec l'axe (17) du canal d'alimentation (15).
  4. Pompe à carburant selon l'une quelconque des revendications 1 à 3, caractérisée en ce que l'étranglement (30) est configuré sous forme d'alésage d'étranglement.
  5. Pompe à carburant selon l'une quelconque des revendications 1 à 4, caractérisée en ce que le canal de liaison (19) est configuré en tant que canal de liaison non étranglé (19).
  6. Pompe à carburant selon l'une quelconque des revendications 1 à 5, caractérisée en ce que le canal d'alimentation (15) est configuré sous forme d'alésage d'alimentation qui s'étend en partie à travers une tubulure d'alimentation (4).
  7. Pompe à carburant selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le canal d'alimentation (15), l'étranglement (30) et le canal de liaison (19) sont réalisés dans une partie de boîtier (9) d'une pompe haute pression (3).
  8. Pompe à carburant selon l'une quelconque des revendications 1 à 5, caractérisée en ce que l'étranglement (30) et le canal de liaison (19) sont intégrés dans une partie de boîtier (7) d'une pompe basse pression (2) et/ou en ce que la partie de boîtier (7) de la pompe basse pression (2) est configurée sous forme de boîtier (7) de pompe à denture externe (2).
EP09801210.7A 2009-02-18 2009-12-22 Pompe à carburant Active EP2399031B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009000945A DE102009000945A1 (de) 2009-02-18 2009-02-18 Brennstoffpumpe
PCT/EP2009/067745 WO2010094366A1 (fr) 2009-02-18 2009-12-22 Pompe à carburant

Publications (2)

Publication Number Publication Date
EP2399031A1 EP2399031A1 (fr) 2011-12-28
EP2399031B1 true EP2399031B1 (fr) 2015-08-05

Family

ID=41632302

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09801210.7A Active EP2399031B1 (fr) 2009-02-18 2009-12-22 Pompe à carburant

Country Status (4)

Country Link
EP (1) EP2399031B1 (fr)
CN (1) CN102325997B (fr)
DE (1) DE102009000945A1 (fr)
WO (1) WO2010094366A1 (fr)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19719265A1 (de) * 1997-05-07 1998-11-12 Deutz Ag Einspritzsystem einer Brennkraftmaschine
DE19736160A1 (de) 1997-08-20 1999-02-25 Bosch Gmbh Robert Pumpenanordnung zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen
JP2001214829A (ja) * 2000-01-31 2001-08-10 Bosch Automotive Systems Corp 燃料噴射ポンプ
JP3861835B2 (ja) * 2003-03-31 2006-12-27 株式会社デンソー 燃料噴射ポンプ
DE10357612A1 (de) * 2003-12-10 2005-07-07 Robert Bosch Gmbh Ventilanordnung, insbesondere Einlassventil einer Hochdruck-Kraftstoffpumpe
DE102004037132A1 (de) * 2004-07-30 2006-03-23 Robert Bosch Gmbh Korrosionsverhindernde Maßnahmen in Hochdruckbohrungen, insbesondere bei Injektoren, Common-Rails sowie Einspritzpumpen

Also Published As

Publication number Publication date
CN102325997A (zh) 2012-01-18
WO2010094366A1 (fr) 2010-08-26
DE102009000945A1 (de) 2010-08-19
EP2399031A1 (fr) 2011-12-28
CN102325997B (zh) 2015-05-20

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