EP2315930B1 - Pompe pour un système d'injection de carburant d'un moteur à combustion interne avec une soupape de refoulement améliorée - Google Patents

Pompe pour un système d'injection de carburant d'un moteur à combustion interne avec une soupape de refoulement améliorée Download PDF

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Publication number
EP2315930B1
EP2315930B1 EP09753752A EP09753752A EP2315930B1 EP 2315930 B1 EP2315930 B1 EP 2315930B1 EP 09753752 A EP09753752 A EP 09753752A EP 09753752 A EP09753752 A EP 09753752A EP 2315930 B1 EP2315930 B1 EP 2315930B1
Authority
EP
European Patent Office
Prior art keywords
shut
seat
spring
opening
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.)
Not-in-force
Application number
EP09753752A
Other languages
German (de)
English (en)
Other versions
EP2315930A1 (fr
Inventor
Alessandro De Luca
Nicola Loiudice
Massimiliano Roncone
Wolfgang Stoecklein
Tobias Reiser
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 EP2315930A1 publication Critical patent/EP2315930A1/fr
Application granted granted Critical
Publication of EP2315930B1 publication Critical patent/EP2315930B1/fr
Not-in-force 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
    • F02M59/46—Valves
    • F02M59/462—Delivery valves

Definitions

  • the present invention relates to a pump comprising an improved delivery valve, and preferably to a high-pressure pump for a fuel injection system of an internal combustion engine.
  • a high-pressure pump is generally used in a fuel injection system which comprises a low-pressure branch, a pre-feed pump which draws the fuel from a tank and conveys it to a high-pressure pump via the low-pressure branch and a high-pressure branch which connects a delivery of the high-pressure pump to a group of injectors via an accumulator, commonly called a "common rail".
  • the high-pressure pump comprises a plurality of pumping cylinders operated by a driving shaft via a lobed body or via a cam.
  • the pumping cylinders slide in a reciprocating manner inside respective compression chambers, each of which is connected in flow terms to an intake valve and a delivery or high-pressure valve.
  • the high-pressure or delivery valve is a non-return valve.
  • a high-pressure valve comprises a ball shut-off member biased by means of a coil spring against a conical seat. Upstream the conical seat is connected in flow to the compression chamber and downstream the high-pressure valve is connected in flow to the common rail.
  • the fuel flow which passes through the high-pressure valve exerts a complex hydrodynamic action on the shut-off member which results in wear and a delay in the dynamic response.
  • the hydraulic forces acting on the shut-off member are such as to generate a torque which causes the shut-off member to rotate about the axis of the spring and thus produces both friction of the latter against the spring and a delay in the closing action.
  • a pump for a fuel injection system comprising a seat connected in flow terms to the delivery of a compression chamber and having an axis, an outlet duct for connecting the said seat to a plurality of Injectors, a shut-off member housed inside the said seat, a spring for biasing the said shut-off member against a first contact surface of the said seat in a closed position.
  • Said spring being arranged downstream of the said shut-off member, wherein a first through-opening in the axial direction, arranged downstream of said shut-off member, is present inside the said seat and wherein it comprises fuel flow deviation means arranged inside the said seat upstream of the said outlet duct and configured so that the speed of the fuel flow is greater between the said shut-off member and the said opening than upstream of the said shut-off member.
  • the object of the present invention is to provide a feed pump for a fuel injection circuit which does not have the abovementioned drawbacks.
  • a pump for a fuel injection system of an internal combustion engine comprising a seat connected in flow terms to the delivery of a compression chamber, an outlet duct for connecting the seat to a plurality of injectors, a shut-off member housed inside the seat, a spring for biasing the shut-off member against a first contact surface of the seat in a closed position, the seat being provided with a first through-opening in the axial direction, arranged downstream of the shut-off member, and fuel flow deviation means being provided upstream of the outlet duct and configured so that the speed of the fuel flow is greater between the shut-off member and the opening than upstream of the shut-off member.
  • the fuel flow deviation means are configured so as to direct the flow towards the opening so that the speed of the fuel increases immediately downstream of the shut-off member and a negative pressure is therefore created. This negative pressure pushes the shut-off member against the spring and reduces rotation of the shut-off member. Moreover, when the fluid tends to change direction during the intake phase of the pumping member, the pressure is localized along the axis of the spring and is applied effectively to the shut-off member so as to favour a closing action.
  • 1 denotes generically the head of a reciprocating fuel feed pump.
  • the head defines a compression chamber 2 housing a pumping member 3 and a delivery valve 4 connected to the delivery of the chamber 2.
  • the delivery valve 4 is a non-return valve.
  • the compression chamber 2 has an axis A and is closed axially by a threaded member 5 screwed into the head 1.
  • the valve 4 is connected to the delivery of the compression chamber 2 via a duct 6 having an axis B perpendicular to the axis A.
  • the duct 6 emerges inside a seat 7 of the valve 4 defined by a cylindrical wall 8 coaxial with the duct 6 and by a frustoconical contact surface 9 axially arranged between the duct 6 and the cylindrical wall 8.
  • the seat 7 is also connected to a duct 10 having an axis C parallel to the axis A and connected to the injectors preferably via a common rail, both not shown.
  • the valve 4 comprises a ball shut-off member 11 designed to cooperate selectively with the contact surface 9; a coil spring 12 for keeping the shut-off member 11 pressed against the contact surface 9 in a closed position; and a closing member 13 for pre-stressing the spring 12.
  • the closing member 13 is connected rigidly to the head 1 preferably by means of a threaded connection and comprises, for example in the form of a single body, a closing head-piece 14 screwed into the head 1 in a fluid-type manner and a cylindrical body 15 housed inside the seat 7.
  • the cylindrical body 5 defines preferably a radial through-hole 16 coaxial during use with the axis C and an axial cavity 17 communicating with the hole 16 via an opening 18 and open towards the contact wall 9.
  • the axial cavity 17 houses the spring 12 and is cylindrical with an internal diameter smaller than that of the shut-off member 11.
  • the opening 18 is situated on the opposite side to the shut-off member 11 relative to the spring 12 and is situated in an axial position lying between the axis C and the cavity 17.
  • the cylindrical body 15 Towards the contact wall 9, the cylindrical body 15 comprises an annular end portion 19 which defines a flaring 20 and at least one radial through-goove 21.
  • the spring 12 is housed inside the axial cavity 17 so as to be coaxial with the axis B and the shut-off member 11 makes contact with the contact surface 9 when the valve 4 is closed.
  • the valve 4 opens when the shut-off member 11 separates from the contact surface 9 and is able to reach the fully open condition when the shut-off member 11 makes contact with the flaring 20.
  • the cylindrical body 15 is mounted with radial play of its diameter inside the seat 7 so that the hydraulic resistance defined by the aperture 22 between the cylindrical bod 15 and the cylindrical wall 8 is greater than that defined by the groove 21, the coils of the spring 12, the opening 18 and the hole 16.
  • the diameter of the duct 6 and the dimensions of the groove 21 are such as to ensure that the speed of the fuel inside the cavity 17 is greater than that inside the duct 6.
  • the flow of fuel pumped by the member 3 opens the shut-off member 11 when the pressure upstream of the valve 4 is greater than the sum of the pressure downstream of the shut-off member and the equivalent, in terms of pressure, of the pre-stressing force of the spring 12.
  • shut-off member 11 makes contact against the flaring 20 and most of the flow is directed along a path which leads from the groove 21 to the hole 16 through the coils of the spring 12 and the opening 18 since the hydraulic resistance of this path is less than that defined by the aperture 22 between the annular end portion 19 and the duct 10.
  • the speed of rotation of the shut-off member 11 about the axis B is so high that the shut-off member continues to rotate even when the pumping member 3 reverses its movement and starts the intake phase, preventing closure of the valve also - in the worst of cases - for the entire duration of the intake phase.
  • the number of grooves 21 may be more than one, for example up to five, so as to ensure that the speed of the fuel flow inside the cavity 17 is greater than that inside the duct 6.
  • the aperture 22 may also be completely closed in the case where the part 15 engages precisely with the cylindrical surface 8 of the seat 7. In this case, the hydraulic resistance is practically infinite and the entire flow of fuel which passes through the valve 4 flows through the coils of the spring 12 and the opening 18.

Abstract

L'invention concerne une pompe pour un système d'injection de carburant d'un moteur à combustion interne comprenant un siège (7) en communication fluidique avec le refoulement d'une chambre de compression (2) de la pompe, un conduit de sortie (10) pour relier ledit siège (7) à une pluralité d'injecteurs, un élément d'arrêt (11) logé dans le siège (7), un ressort (12) pour solliciter l'élément d'arrêt (11) contre une surface de contact (9) du siège (7) dans une position fermée, le ressort (12) étant disposé en aval de l'élément d'arrêt (11), une ouverture traversante (18) dans la direction axiale, disposée en aval de l'élément d'arrêt (11), étant présente à l'intérieur dudit siège (7), et des moyens de déviation du flux de carburant (21, 22) étant disposés à l'intérieur du siège (7) en amont du conduit de sortie (10) et étant configurés de telle sorte que la vitesse du flux de carburant soit supérieure entre l'élément d'arrêt (11) et l'ouverture (18) qu'en amont de l'élément d'arrêt (11).

Claims (11)

  1. Pompe pour un système d'injection de carburant d'un moteur à combustion interne, comprenant un siège (7) connecté fluidiquement à l'alimentation d'une chambre de compression (2) et ayant un axe (B), un conduit de sortie (10) pour relier ledit siège (7) à une pluralité d'injecteurs, un organe d'arrêt (11) logé à l'intérieur dudit siège (7), un ressort (12) pour solliciter ledit organe d'arrêt (11) contre une première surface de contact (9) dudit siège (7) dans une position fermée, ledit ressort (12) étant agencé en aval dudit organe d'arrêt (11), une première ouverture traversante (18) dans la direction axiale, agencée en aval dudit organe d'arrêt (11), étant prévue à l'intérieur dudit siège (7) et comprenant des moyens de déviation du flux de carburant (21, 22) agencé à l'intérieur dudit siège (7) en amont dudit conduit de sortie (10) et configuré de telle sorte que la vitesse du flux de carburant soit plus importante entre ledit organe d'arrêt (11) et ladite ouverture (18) qu'en amont dudit organe d'arrêt (11), caractérisée en ce que lesdits moyens de déviation du flux de carburant comprennent une première résistance hydraulique (22) en aval dudit organe d'arrêt (11), connectée en série avec ledit conduit de sortie (10), et une deuxième résistance hydraulique (21) en aval dudit organe d'arrêt (11), agencée en série avec à la fois ladite ouverture (18) et ledit conduit de sortie (10), la valeur de ladite première résistance hydraulique (22) étant supérieure à celle de ladite deuxième résistance hydraulique (21).
  2. Pompe selon la revendication 1, caractérisée en ce qu'une deuxième surface de contact (20) est prévue à l'intérieur dudit siège (7) pour délimiter la course axiale dudit organe d'arrêt (11) dans la direction d'augmentation de la contrainte dudit ressort (12) et en ce que ladite deuxième résistance hydraulique (21) est définie par ladite deuxième surface de contact (20).
  3. Pompe selon la revendication 1 ou 2, caractérisée en ce qu'elle comprend un corps creux (15) monté à l'intérieur dudit siège (7) et définissant une cavité (17) pour recevoir ledit ressort (12) et ladite deuxième résistance hydraulique (21).
  4. Pompe selon les revendications 2 et 3, caractérisée en ce que ledit corps creux (15) comprend une portion d'extrémité (19) définissant ladite deuxième surface de contact (20).
  5. Pompe selon la revendication 4, caractérisée en ce que ladite deuxième résistance hydraulique (21) comprend au moins une deuxième ouverture (21) définie par ladite portion d'extrémité (19).
  6. Pompe selon l'une quelconque des revendications 3 à 5, caractérisée en ce que ladite première résistance hydraulique (22) est définie entre ledit corps creux (15) et une paroi latérale (8) dudit siège (7).
  7. Pompe selon l'une quelconque des revendications 3 à 6, caractérisée en ce que ledit corps creux (15) est monté avec un jeu radial à l'intérieur dudit siège (7) et est amovible.
  8. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que ledit ressort (12) est agencé entre ledit organe d'arrêt (12) et ladite ouverture (18).
  9. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que ladite ouverture (18) a un diamètre plus petit que la dimension maximale dudit organe d'arrêt (12).
  10. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que ledit ressort (12) est du type hélicoïdal et en ce que lesdits moyens de déviation du flux de carburant (21, 22) sont configurés de telle sorte que la plupart de l'écoulement de carburant qui s'écoule vers ledit siège (7) passe à travers les enroulements dudit ressort (12).
  11. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que ledit conduit de sortie (10) est transversal par rapport audit siège (7) et en ce que ladite ouverture (18) est agencée axialement entre ledit organe d'arrêt (11) et ledit conduit de sortie (10).
EP09753752A 2008-05-30 2009-04-20 Pompe pour un système d'injection de carburant d'un moteur à combustion interne avec une soupape de refoulement améliorée Not-in-force EP2315930B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMI20081008 ITMI20081008A1 (it) 2008-05-30 2008-05-30 Pompa per un impianto di iniezione di combustibile con una valvola di mandata perfezionata
PCT/EP2009/054639 WO2009144097A1 (fr) 2008-05-30 2009-04-20 Pompe pour un système d'injection de carburant d'un moteur à combustion interne avec une soupape de refoulement améliorée

Publications (2)

Publication Number Publication Date
EP2315930A1 EP2315930A1 (fr) 2011-05-04
EP2315930B1 true EP2315930B1 (fr) 2012-06-20

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP09753752A Not-in-force EP2315930B1 (fr) 2008-05-30 2009-04-20 Pompe pour un système d'injection de carburant d'un moteur à combustion interne avec une soupape de refoulement améliorée

Country Status (3)

Country Link
EP (1) EP2315930B1 (fr)
IT (1) ITMI20081008A1 (fr)
WO (1) WO2009144097A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2688406B1 (fr) 2011-03-25 2015-04-22 Bayer Intellectual Property GmbH L'utilisation de n-(tétrazol-4-yl)- ou n-(triazol-3-yl)arylcarboxamides ou de leurs sels pour lutter contre les plantes indésirables dans des zones de plantes cultivées transgéniques développant une tolérance aux herbicides inhibiteurs de la hppd
WO2012130684A1 (fr) 2011-03-25 2012-10-04 Bayer Cropscience Ag Utilisation de n-(1,2,5-oxadiazol-3-yl)benzamides pour lutter contre les plantes indésirables dans des zones de plantes cultivées transgéniques développant une tolérance aux herbicides inhibiteurs de la hppd

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB513349A (en) * 1938-07-25 1939-10-10 Bryce Ltd Improvements relating to fuel injection pumps
JP4237560B2 (ja) * 2003-07-03 2009-03-11 カヤバ工業株式会社 流体圧制御弁
DE102004027825A1 (de) * 2004-02-11 2005-09-01 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102005061886A1 (de) * 2005-12-23 2007-07-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
EP1813845A1 (fr) * 2006-01-31 2007-08-01 Centro Studi Componenti per Veicoli S.P.A. Pompe à piston à haute pression pour l'alimentation en carburant d'un moteur à combustion interne

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WO2009144097A1 (fr) 2009-12-03
EP2315930A1 (fr) 2011-05-04
ITMI20081008A1 (it) 2009-11-30

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