EP2867520B1 - Pompe à piston haute pression pour carburant - Google Patents

Pompe à piston haute pression pour carburant Download PDF

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Publication number
EP2867520B1
EP2867520B1 EP13730210.5A EP13730210A EP2867520B1 EP 2867520 B1 EP2867520 B1 EP 2867520B1 EP 13730210 A EP13730210 A EP 13730210A EP 2867520 B1 EP2867520 B1 EP 2867520B1
Authority
EP
European Patent Office
Prior art keywords
valve seat
valve
piston pump
pressure fuel
high pressure
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
EP13730210.5A
Other languages
German (de)
English (en)
Other versions
EP2867520A1 (fr
Inventor
Bernd Kellner
Andreas Mair
Lorenz Drutu
Dominik Brunner
Wolfgang Bueser
Christoph Werner
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 EP2867520A1 publication Critical patent/EP2867520A1/fr
Application granted granted Critical
Publication of EP2867520B1 publication Critical patent/EP2867520B1/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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • 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
    • F02M59/464—Inlet valves of the check valve type
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member

Definitions

  • the invention relates to a high-pressure fuel piston pump according to the preamble of claim 1.
  • High-pressure fuel piston pumps are used, for example, in internal combustion engines with a common rail fuel system.
  • the fuel from the high-pressure fuel piston pump is compressed to a very high pressure and conveyed into a fuel rail, from where the fuel is injected directly into combustion chambers of the internal combustion engine.
  • the high-pressure fuel piston pump has for this purpose upstream of a pumping chamber via an inlet valve, which is designed as a check valve. Downstream of the delivery chamber, an outlet valve, which is likewise designed as a check valve, is arranged.
  • the known high-pressure fuel piston pump has a quantity control valve. This is usually the inlet valve, which can be temporarily forced into its open position by an actuator, for example electromagnetically actuated. If this occurs during a delivery stroke of the high-pressure fuel piston pump, the fuel from the delivery chamber is not conveyed to the fuel rail but through the forcibly opened intake valve back into the region (low pressure region) of the fuel system arranged upstream of the high-pressure fuel piston pump.
  • an actuator for example electromagnetically actuated
  • the intake valve various embodiments are known.
  • this describes EP 2 236 809 A2 an intake valve having a disc-like valve seat body which cooperates with a diaphragm-like valve element.
  • the valve seat body may have a plurality of circular passages
  • the movable valve element may consist of a plurality of membrane-like circular individual elements, which are movably held by spring arms.
  • DE 40 23 044 discloses in another context a valve seat body having two arcuately shaped passages and a cooperating with this membrane-like valve element.
  • Piston pumps are also from the DE 10 2010 044 119 A1 , the US 2005/263622 A1 , the EP 1 895 218 A1 , the EP 1 965 069 A2 the DE34 04 520 A1 and the US 1,355,285 known.
  • Object of the present invention is to provide a high-pressure fuel piston pump having a high efficiency.
  • the fuel In the operation of the high-pressure fuel piston pump, there are essentially two cases to be distinguished: In the suction phase, the fuel has to pass from the region located upstream of the inlet valve (low-pressure region) into the downstream region, the delivery chamber of the high-pressure fuel piston pump. To avoid vapor formation, the pressure drop at the valve seat of the inlet valve should be as low as possible. If steam is formed, the delivery rate of the pump may decrease. The largest possible flow area in the valve seat area reduces the pressure drop. The area flowed through in turn is calculated from the valve seat length and the valve lift. The latter should be small for dynamic reasons.
  • the valve element In contrast, in the delivery phase, it should be possible, when no fuel is to be conveyed into the fuel rail, to keep the valve element open against the now acting in the closing direction flow force through the plunger of the quantity control valve.
  • the spring acting on the valve tappet should be as small as possible, and the stroke of the valve element required for the return flow should be as small as possible.
  • the valve seat of the intake valve is significantly longer than in the conventional high-pressure fuel piston pumps.
  • This increased length of the valve seat results in a smaller pressure drop across the inlet valve with the same stroke of the valve element. This has a favorable effect for the filling of the delivery chamber, and thereby increases the delivery rate of the high-pressure fuel piston pump according to the invention.
  • the pressurized area of the valve element is reduced, whereby the dynamics of the intake valve is improved.
  • the extended valve seat line reduces the velocity of the fuel as it flows through the inlet valve, reducing the pressure drop during suction, thereby avoiding vapor formation during the suction phase.
  • the flow forces are also significantly reduced during the return. The reason for this lies again in the smaller pressure drop and the additionally reduced area on which this pressure drop acts.
  • a first development of the high-pressure fuel piston pump according to the invention is characterized in that it comprises a plunger guided by the valve body, with which the valve element can be forcibly acted upon in an open position, and that the plunger with a closed inlet valve by a circumferential and cooperating with the valve element Valve seat line is sealed from a downstream high-pressure region. This ensures that the valve stem in forcibly kept open valve element in the pumping chamber prevailing pressure is applied as little as possible and thus is influenced as little as possible. When the inlet valve is closed, however, no force acts on the plunger from the downstream high-pressure region. This force is absorbed by the valve seat.
  • valve seat line is at least partially formed by a raised web.
  • this creates a defined sealing contour, by means of which the areas of the valve element in which the inlet valve is closed on the one side and on the other side on the high pressure prevail, are kept small. As a result, the dynamics of the intake valve is further improved.
  • valve seat body in the case of an at least partially wave-shaped, meandering, serrated or cloverleaf-shaped valve seat line which is formed on a valve seat body, the valve seat body has a flow channel in a downstream region immediately adjacent to the valve seat line.
  • the flow channel comprises a depression in the valve seat body.
  • This depression may, for example, comprise the entire area present between two adjacent waves or meanders or cloverleaves. This is easy to produce and leads to an optimal outflow of the fuel.
  • valve seat extends along a first radial inner valve seat line and a second radially outer valve seat line
  • valve element has at least one passage opening radially inwardly from the radially inner valve seat line. This also makes the outflow and, in forced open inlet valve, the backflow of the fuel is facilitated again.
  • the valve element has a circular shape. This is particularly easy and therefore inexpensive to produce, and a backup against rotation of the valve element is not required.
  • the valve element has a complementary to the valve seat line, so also wave-shaped meandering or cloverleaf-shaped outer contour and is secured against rotation. In this case, the forces acting on the valve element forces are minimal and the fuel can flow as best as possible or inflow.
  • a fuel system of an internal combustion engine contributes in FIG. 1 Overall, the reference numeral 10. It includes a fuel tank 12, from which a prefeed pump 14 promotes fuel in a low-pressure line 16. This leads to a fuel high-pressure piston pump 18, designated overall by 18.
  • the Combination of inlet valve 20 and electromagnetic actuator 22 is also referred to as a quantity control valve, as a result, the flow rate of the high-pressure fuel piston pump 18 can be adjusted.
  • the inlet valve 20 and its configuration are presently of particular interest. This will therefore be dealt with in more detail below.
  • a pump piston 24 which by a in FIG. 1 not shown eccentric can be placed in a reciprocating motion.
  • a delivery chamber 27 is present between this and a housing 26.
  • a high-pressure line 30 leads to a fuel rail 32, to which a plurality of fuel injectors 34 are connected via an exhaust valve 28 which is likewise designed as a check valve. These inject the fuel directly into each associated combustion chambers (not shown).
  • FIG. 2 A portion of the high-pressure fuel piston pump 18 is in FIG. 2 shown in more detail.
  • the inlet valve 20 comprises a plate-shaped valve element 36, which cooperates with a valve seat body 38.
  • the valve element 36 bears against the valve seat body 38.
  • the valve seat body 38 is a disk-shaped member which is press-fit into the housing 26 of the high-pressure fuel piston pump 18.
  • passage openings 40 are present, which are blocked by the valve element 36 when the inlet valve 20 is closed, but are released by the valve element 36 when the inlet valve 20 is open.
  • the shape and arrangement of the passage openings 40 and of the valve seat 36 cooperating with the valve element are of particular importance in the present case and will be explained further below.
  • a central opening 42 is provided, through which a plunger 44 of the electromagnetic actuator 22 extends therethrough.
  • the plunger 44 has a stop shoulder 46 which cooperates with housing-side stops 48 and 50.
  • At the inlet valve 20 remote end of the plunger 44 is attached to this an armature 52 which cooperates with an electromagnetic coil (not shown).
  • an armature spring 54 is clamped, which acts on the plunger 44 to the inlet valve 20 back. This has the consequence that when the electromagnetic actuator 22 is not energized, the valve element 36 is urged by the force of the armature spring 54 forcibly in the open position via the plunger. If the electromagnetic actuator 22 is energized, however, the plunger 44 is pulled away from the valve member 36 so that it can come into contact with the valve seat body 38 and close within the normal function of a check valve.
  • the inlet valve 20 and here in particular the configuration of the valve seat body 38 with reference to FIG. 3 explained in more detail.
  • the inlet valve 20 is shown in perspective from the direction of the delivery chamber 27. It can be seen that four circular arc segment-shaped recesses are present in the valve seat body 38, which form the passage openings 40. Between the passage openings 40 extend in the radial direction webs 56 which hold a central ring 58 in which the central opening 42 for the plunger 44 is present. In FIG. 3 is also the valve element 36 facing the end of the plunger 44 shown.
  • valve member 36 facing edge is formed as a flattened edge and the extent a valve seat forms for the valve element 36.
  • FIG. 3 Thus, without further ado that the valve seat 60 extends along a clover-shaped valve seat line.
  • recess 62 in the side of the valve seat body 38 facing the valve element 36, which recess extends further in the radial direction than the valve seat 60. This recess 62 forms, as will be explained below, a flow channel for the off and incoming fuel.
  • a mid-plane 64 which is in the area where neither a valve seat 60 nor a recess 62 are present.
  • a second plane which is offset from this median plane 64 away from the valve member 36 and in which the recesses 62 are located.
  • a third plane which is raised relative to the center plane 64 to the valve member 36 and in which the flattened edge of the valve seat 60 is located.
  • the inlet valve 20 operates as follows: If fuel is to flow from the low-pressure line 16 into the delivery space 27, the fuel passes through the passage openings 40. Subsequently, however, it does not only flow in the radial direction through the gap between the radially outer regions (in FIG. 3 one of which is exemplarily provided with the reference numeral 60a) of the valve seat 60 and the valve element 36, but also in the circumferential direction through the radially extending portions of the valve seat 60 (in FIG. 3 one of which is designated by reference numeral 60b). In comparison to previous inlet valves, therefore, the area through which flowed through in the region of the sealing seat 60 is significantly increased, as a result of which the pressure drop occurring there is markedly reduced. As a result, there is less or possibly even not at all steam formation, whereby the high-pressure fuel piston pump 18 has a relatively high degree of delivery.
  • the central opening 42 which guides the tappet 44 with a small clearance, moreover, to allow its axial movement, is located within the circumferential cloverleaf-shaped valve seat 60, whereby the guidance of the plunger 44 in the central opening 42nd always facing the low-pressure region, so that when the inlet valve 20 is closed and the plunger 44 is withdrawn behind the valve seat 60, no leakage occurs across the inlet valve 20.
  • a flow channel for the fluid flowing out over the radially extending sections 60b of the valve seat 60 is created by the recesses 62, so that even with a small stroke of the valve element 36, a sufficient cross section for the outflow of the fuel is available.
  • valve element 36 When forcibly opened inlet valve 20 and a return flow from the pumping chamber 27 into the low pressure line 16 also results from the comparatively long valve seat 60 a lower pressure drop and thus a lower force exerted by the valve element 36 on the plunger 44. How easy FIG. 3 it can be seen, a full-surface circular valve element 36 requires no rotation. However, it is also possible that the valve element 36 also has recesses in the region of the recesses 62, that is to say between the passage openings 40, as in FIG FIG. 3 indicated by dashed lines. In this case, however, the valve element 36 must be secured against rotation.
  • FIG. 4 An embodiment of the inlet valve 20 shows FIG. 4 ,
  • inlet valve 20 is a radially inner valve seat 60c and a radially outer annular valve seat 60d present.
  • the passage openings 40 are provided between these two annular valve seats 60c and 60d.
  • openings 66 are provided radially inwardly of the valve seat 60c in the valve element 36, which allow an axial flow of fuel.
  • the central opening 42 is sealed by a valve seat 60e.
  • the passage openings 40 are formed by a plurality of discrete circular through holes in the valve seat body 38. Also here are openings 66 in the valve element 36, of which in FIG. 5 is shown only by way of example, to allow outflow of fuel in the radially inward region of the intake valve 20.

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

Claims (7)

  1. Pompe à piston haute pression pour carburant (18), en particulier pour un système d'injection de carburant à rampe commune (10) d'un moteur à combustion interne, comprenant une soupape d'admission (20), laquelle comporte un élément de soupape (36) mobile en forme de plaque et au moins un siège de soupape (60) fixe coopérant avec celui-ci, le siège de soupape (60) s'étendant le long d'une ligne de siège de soupape ondulée, sinueuse, dentelée ou en forme de feuille de trèfle au moins dans certaines zones, caractérisée en ce que ladite au moins une ligne de siège de soupape (60) ondulée, sinueuse, dentelée ou en forme de feuille de trèfle au moins dans certaines zones est réalisée sur un corps de siège de soupape (38) et le corps de siège de soupape (38) comprend un canal d'écoulement (62) dans une zone en aval directement adjacente à la ligne de siège de soupape.
  2. Pompe à piston haute pression pour carburant (18) selon la revendication 1, caractérisée en ce qu'elle comporte un poussoir (44) à l'aide duquel l'élément de soupape (36) peut être sollicité de manière forcée dans une position ouverte, et en ce que le poussoir (44) est, lorsque la soupape d'admission (20) est fermée, rendu étanche par rapport à une zone haute pression en aval (27) au moyen d'un siège de soupape (60) périphérique et coopérant avec l'élément de soupape (36).
  3. Pompe à piston haute pression pour carburant (18) selon l'une quelconque des revendications précédentes, caractérisée en ce que le siège de soupape est formé au moins dans certaines zones par une nervure en relief (60).
  4. Pompe à piston haute pression pour carburant (18) selon la revendication 1, caractérisée en ce que le canal d'écoulement comporte un évidement (62) dans le corps de siège de soupape (38).
  5. Pompe à piston haute pression pour carburant (18) selon l'une quelconque des revendications précédentes, dans laquelle le siège de soupape s'étend le long d'une première ligne de siège de soupape (60c) radialement intérieure et d'une deuxième ligne de siège de soupape (60d) radialement extérieure, caractérisée en ce que l'élément de soupape (36) comprend, radialement vers l'intérieur à partir de la ligne de siège de soupape (60c) radialement intérieure, au moins une ouverture traversante (66).
  6. Pompe à piston haute pression pour carburant (18) selon l'une quelconque des revendications précédentes, caractérisée en ce que l'élément de soupape (36) a un contour extérieur circulaire.
  7. Pompe à piston haute pression pour carburant (18) selon l'une quelconque des revendications 1 à 5, caractérisée en ce que l'élément de soupape (36) a un contour extérieur complémentaire à la ligne de siège de soupape (60) et est bloqué en rotation.
EP13730210.5A 2012-06-28 2013-06-17 Pompe à piston haute pression pour carburant Not-in-force EP2867520B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012211106.9A DE102012211106A1 (de) 2012-06-28 2012-06-28 Kraftstoffhochdruck-Kolbenpumpe
PCT/EP2013/062514 WO2014001122A1 (fr) 2012-06-28 2013-06-17 Pompe à piston haute pression pour carburant

Publications (2)

Publication Number Publication Date
EP2867520A1 EP2867520A1 (fr) 2015-05-06
EP2867520B1 true EP2867520B1 (fr) 2019-04-03

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP13730210.5A Not-in-force EP2867520B1 (fr) 2012-06-28 2013-06-17 Pompe à piston haute pression pour carburant

Country Status (4)

Country Link
EP (1) EP2867520B1 (fr)
KR (1) KR20150027127A (fr)
DE (1) DE102012211106A1 (fr)
WO (1) WO2014001122A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014223198A1 (de) * 2014-11-13 2016-05-19 Robert Bosch Gmbh Kraftstoffpumpe mit verbessertem Förderverhalten
DE102018200612B4 (de) 2018-01-16 2019-11-28 Continental Automotive Gmbh Hochdruckanschluss für eine Kraftstoffhochdruckpumpe sowie Kraftstoffhochdruckpumpe

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1355285A (en) * 1919-02-20 1920-10-12 W N Matthews And Brother Inc Pump-valve
DE3404520A1 (de) * 1984-02-09 1985-08-14 Uraca Pumpenfabrik GmbH & Co KG, 7432 Bad Urach Kolben- bzw. plungerpumpe

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4023044A1 (de) 1990-07-20 1992-01-23 Bosch Gmbh Robert Ventil zum dosierten zumischen von verfluechtigtem kraftstoff zum kraftstoffluftgemisch einer brennkraftmaschine
US7124966B2 (en) * 2004-06-01 2006-10-24 Haynes Corporation Fuel injector check valve
EP1724467B1 (fr) 2005-05-20 2016-07-13 Magneti Marelli S.p.A. Pompe à combustible pour moteurs à combustion interne
EP1895218B1 (fr) * 2006-09-04 2010-11-10 Magneti Marelli S.p.A. Vanne d'arrêt pour commander le débit d'une pompe de carburant pour un moteur à combustion interne
US20080203347A1 (en) * 2007-02-28 2008-08-28 Santos Burrola Control valve for a gas direct injection fuel system
IT1396473B1 (it) 2009-03-30 2012-12-14 Magneti Marelli Spa Pompa carburante con una valvola di massima pressione perfezionata per un sistema di iniezione diretta
DE102010044119A1 (de) * 2010-11-18 2012-05-24 Robert Bosch Gmbh Mengensteuerventil eines Kraftstoffsystems

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1355285A (en) * 1919-02-20 1920-10-12 W N Matthews And Brother Inc Pump-valve
DE3404520A1 (de) * 1984-02-09 1985-08-14 Uraca Pumpenfabrik GmbH & Co KG, 7432 Bad Urach Kolben- bzw. plungerpumpe

Also Published As

Publication number Publication date
DE102012211106A1 (de) 2014-01-02
EP2867520A1 (fr) 2015-05-06
WO2014001122A1 (fr) 2014-01-03
KR20150027127A (ko) 2015-03-11

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