EP0409943B1 - Pompe d'injection pour moteurs diesel - Google Patents

Pompe d'injection pour moteurs diesel Download PDF

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Publication number
EP0409943B1
EP0409943B1 EP90902108A EP90902108A EP0409943B1 EP 0409943 B1 EP0409943 B1 EP 0409943B1 EP 90902108 A EP90902108 A EP 90902108A EP 90902108 A EP90902108 A EP 90902108A EP 0409943 B1 EP0409943 B1 EP 0409943B1
Authority
EP
European Patent Office
Prior art keywords
control
bore
auxiliary
edge
sleeve
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
EP90902108A
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German (de)
English (en)
Other versions
EP0409943A1 (fr
Inventor
Gerhard Weiss
Peter Baumgartner
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 AG
Original Assignee
Robert Bosch AG
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch AG, Robert Bosch GmbH filed Critical Robert Bosch AG
Priority to AT90902108T priority Critical patent/ATE97996T1/de
Publication of EP0409943A1 publication Critical patent/EP0409943A1/fr
Application granted granted Critical
Publication of EP0409943B1 publication Critical patent/EP0409943B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to a fuel injection pump for diesel engines, in which at least one pump piston forms a high-pressure chamber with a pump piston sleeve and is surrounded by a control sleeve, the angular position between the pump piston and control sleeve being variable for quantity adjustment, and wherein an axial bore in the pump piston provides the high pressure chamber with a control bore or connects with a groove forming a control edge and a control edge for ending the injection process, which cooperates with a control edge or control bore of the control sleeve.
  • DE-OS 35 90 194 describes different variants of a series pump, in one embodiment a radial bore of the piston with a control edge and a control edge of the control sleeve, and in another embodiment a groove on the piston fed by a radial bore with a control bore of the control sleeve cooperates.
  • DE-OS 36 30 647 describes a pump nozzle, in the injection pump of which a groove fed by a radial bore on the piston interacts with a control bore of the control sleeve.
  • a radial bore of the pump piston interacts with the control edges of the control sleeve.
  • the control sleeve can also be moved axially to adjust the start of injection.
  • the throttling effect is also noticeable as damping when the engine is turned off. Although damped shutdown at the end of injection is generally desirable, it is undesirable at the maximum injection amount because it takes the injection process a little too long, resulting in incomplete combustion.
  • a suction or feed bore separate from a discharge bore it is provided that the pump piston or the control sleeve has, in addition to the existing control bore, which serves to terminate the injection process, an auxiliary control bore which is covered earlier than or simultaneously with the control bore by the control edge assigned to it and which is not covered by the control edge in front of the control bore is released, and that the control holes can be connected to the discharge hole.
  • the auxiliary control bore reduces the throttling effect, which leads to the reflection of the pressure wave, and reduces the speed of the decrease in the control cross-section when turning off.
  • pre-delivery only occurs at a much higher speed, which is usually already above the nominal speed.
  • the speed of the cross-sectional decrease is even lower because the auxiliary control bore is completely covered even somewhat earlier than the control bore. Due to the reduced throttling effect, suddenly occurring injections are avoided at zero delivery and higher speeds.
  • the auxiliary control bore is not opened before the control bore during the control, the control times remain unchanged and the useful stroke is fully preserved. The injection process is thus terminated by opening the control bore, a subsequent pressure reduction or opening of the auxiliary control bore at the earliest at the same time making it possible to achieve a faster pressure reduction and an improved closing characteristic.
  • the auxiliary control bore is arranged in a position relative to the control bore which corresponds to a larger injection quantity, and the auxiliary control bore and the control bore cooperate with a common control edge.
  • the diameter of the auxiliary control bore is chosen to be larger than that of the control bore. This is possible without changing the control times because the control edge is at an angle and the auxiliary control bore lies at the position of the control bore corresponding to a larger injection quantity. This further reduces the throttling effect and the dynamic effects, such as pre-delivery or injection at zero delivery, are prevented even more reliably. Furthermore, it is possible to adjust the idling more finely, because the presence of two bores of different diameters at possibly substantially the same height means that only a very small quantity variation can be achieved with a relatively large angle of rotation of the control sleeve or pump piston.
  • control edge can be designed such that its slope decreases at the end corresponding to the maximum injection quantity or becomes zero or negative. As a result, in this extreme state, both control bores are released from the control edge, as a result of which the injection pressure drops faster and the injection duration is somewhat shorter, which prevents incomplete combustion.
  • control bores in the pump piston and the control edges are arranged in the control sleeve, which is advantageous in terms of production technology.
  • the grooves forming the control edges are arranged in the pump piston and the control bores in the control sleeve, and they are both Grooves each connected to the SIMMS axial bore in the pump piston via a separate radial bore.
  • control sleeve has no control edges, but only control bores, and is therefore more rigid. Due to the separate radial bores at different heights of the pump piston, the throttle length of the axial bore is reduced and the possibility is gained to additionally influence the throttling effect, in particular with regard to minimal throttling when opening.
  • the auxiliary control bore is arranged in the direction of the pump axis above or below the control bore in the piston or in the control sleeve and the control sleeve or the pump piston have two control edges at the same distance as the control bore and auxiliary control bore.
  • This version has the further advantage over the first version that the radial bores (control bores or feed lines to the grooves) leading away from the axial SIMMS bore of the piston lie at different heights and the cross-section of the piston is less weakened and the pressure waves in the SIMMS well arrive at the tax openings at different times. The throttle length also decreases.
  • control bores are arranged in the pump piston and the control edges in the control sleeve. If in one variant the control bore and auxiliary control bore are arranged in the control sleeve and the control edges in the piston, the control sleeve is structurally less weakened.
  • a second control edge is preferably arranged in such a way that it is only reached by the auxiliary bore with a maximum injection quantity, as a result of which a shortened injection duration at full load can also be achieved in this embodiment.
  • FIG. 1 denotes a pump piston liner with a recess 2, 3 a control sleeve inserted into this recess, which is rotated, for example, to set the quantity and raised and lowered for spray adjustment, 4 a separating sleeve surrounding the pump piston liner 1, 5 a pump piston driven by a camshaft (not shown), 6 one High-pressure chamber, 7 a schematically indicated inlet bore or feed bore, 8 a high-pressure bore, which is connected to a nozzle needle chamber, not shown, and 9, a discharge bore for the fuel that occurs during the shutdown.
  • Open-up means the closing of the control openings, with which the pressure build-up in the high-pressure chamber 6 and consequently the injection begins; under control, the opening of the control openings, whereby the injection is stopped.
  • the pump piston 5 has an axial bore 11 extending from its end face 10, which is connected to a radial control bore 12 and a likewise radial auxiliary control bore 13.
  • the control sleeve 3 has an upper control edge 15 which extends horizontally all round and forms the control edge, and an inclined control edge 17 which forms a window 16.
  • the control sleeve 3 is shown in a position 14, which corresponds to an early start of injection.
  • the position 14 ', 17' indicated by dashed lines corresponds to a late start of injection.
  • Fig. 2 it can be seen that the control bore 12 and the auxiliary control bore 13 enclose an angle with each other and that the bores are designed as through bores. This corresponds to a doubling of the control elements, even if the control sleeve 3 contains two windows 16 rotated by 180 ° with respect to one another.
  • Fig. 3 shows schematically the associated arrangement of the control members in a settlement.
  • the control sleeve 3 is only symbolized by the control edge 15 and the control edge 17 forming the window 16.
  • One rotation of the control sleeve corresponds to a shift to the left or right in the illustration.
  • the pump piston 5 is only indicated by the control bore 12 and the auxiliary control bore 13 in different positions.
  • the position 20 of the control bore 12 corresponds to the top dead center of the pump piston 5 with zero delivery, the position 23 the bottom dead center. In position 21, the control bore just overlaps the control edge 15 and the control edge 17. However, because of their small distance, it is never completely covered, so that there is no funding (zero funding).
  • the auxiliary control bore 13 occupies the position 22 at this time. Since this is also never completely covered, its free cross-section contributes to the fact that no promotion by dynamic effects takes place even at high speed.
  • the open cross-section is still very large shortly before the shutdown due to the presence of two bores, in other words that the control bore 12 and the auxiliary control bore 13 lie in such a way that they are completely or simultaneously covered, that is, at this moment, the control edge 15 touches both control holes or the auxiliary control hole slightly earlier.
  • the diameter of the auxiliary control bore 13 is selected so that it is not released from the control edge 17 before the control bore 12.
  • the auxiliary control bore 13 is thus “in the shadow” of the control bore 12 with respect to the control edge 17. As a result, it does not come into effect during the control and the entire working area is thus retained.
  • FIG. 4 shows the movement relationships in a variant of the first embodiment, the movement relationships are reversed according to FIG. 4.
  • the control sleeve 3 now has a control bore 40 and an auxiliary control bore 41, but instead the pump piston 5 has a control groove 42 and a control groove 44 on its jacket, which form a control edge 43 and a control edge 45.
  • the grooves 42, 44 are connected to the axial bore 11 in the interior of the piston 5 via a radial bore 46 and possibly also a further radial bore 47.
  • FIG. 5 shows the control bores 40, 41 in cross section, the piston 5 being in the position in which the control groove 42 is at the same height as the control bores 40, 41.
  • FIG. 6 again shows schematically a development of the piston skirt in a somewhat modified form, in which the grooves 42, 44 are not connected to one another, but are each connected to the axial bore 11 by the radial bores 46, 47.
  • the control bore 40 and the auxiliary control bore 41 are shown in dash-dot lines.
  • the control edge 45 merges into a horizontal part 48 for zero delivery on the left and into a horizontal part 49 for maximum injection quantity on the right. Everything else is analogous to FIG. 3.
  • the auxiliary control bore 51 is located under the control bore 50. Both are in this embodiment, for example, in the piston and open into the axial bore 11.
  • the control sleeve 3 has a control edge 52, an auxiliary control edge 53, which with the Auxiliary control bore 51 cooperates, and a control edge 54.
  • the edges 53, 54 form a window 55, which is also offset by 180 ° can be duplicated if it is also the control bores 50, 51.
  • the auxiliary control bore 51 can also be larger than the control bore 50, although the overall height increases somewhat.
  • the associated sequence of movements is shown schematically in FIG.
  • the positions 50, 51 of the control bores correspond to the top dead center of the piston at medium load, the opening in positions 50 ', 51' is just completed, the dotted positions 57, 58 proving immediately beforehand that here too the pre-delivery prevents Effect occurs.
  • the positions 50 ′′, 51 ′′ correspond to the bottom dead center of the piston movement.
  • the positions 70, 71 occur at zero delivery, the throttling effect also being reduced here by the addition of the second bore 71.
  • the positions 80, 81 correspond to the shutdown at full load, with accelerated shutdown also taking place here due to the interaction of the auxiliary control bore 81 with the auxiliary control edge 56, which shortens the injection duration.
  • FIGS. 9 and 10 show a variant of the second embodiment in which the movement conditions are reversed again.
  • the control sleeve 3 has a control bore 60 and an auxiliary control bore 61 and the pump piston 5 on its outer surface has a control groove 62, an auxiliary control groove 63, an expanded control groove 64 and radial bores 65 which connect the control grooves 62, 63, 64 to the axial bore .

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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)

Abstract

Une pompe d'injection de carburant pour moteurs diesel comprend au moins un piston (5) qui forme avec une douille (1) de piston une chambre de haute pression (6) et qui est entouré par un manchon de régulation (3). La position angulaire du piston (5) par rapport au manchon de régulation (3) est variable, ce qui permet de régler la quantité de carburant. Un alésage axial (11) ménagé dans le piston (5) met en communication la chambre de haute pression (6) avec un alésage de régulation (12) ou avec une rainure qui forme un bord de début et de fin de régulation, pour mettre fin à l'injection, et qui coopère avec un bord de régulation (15, 17) ou avec un alésage de régulation du manchon de régulation (3). Un alésage d'évacuation (9) est séparé d'un alésage d'aspiration ou d'alimentation (7). Outre l'alésage de régulation (12), le piston (5) ou le manchon de régulation (3) comprennent un alésage auxiliaire de régulation (13) qui est entièrement recouvert par le bord de début de régulation associé (15) avant ou en même temps que l'alésage de commande (12) et qui n'est pas dégagé par le bord de fin de régulation (17) avant l'alésage de régulation (12). Les alésages de régulation (12, 13) peuvent être reliés à l'alésage d'évacuation (9).

Claims (9)

  1. Pompe d'injection pour moteurs Diesel dans laquelle au moins un piston plongeur (5) forme avec une boîte de piston plongeur (1) un compartiment à haute pression (6) et est entouré d'une douille de commande (3), la position angulaire entre le piston plongeur (5) et la douille de commande (3) étant variable pour le réglage du débit et un alésage axial (11) dans le piston plongeur (5) reliant le compartiment à haute pression (6) à un alésage de commande (12, 50) ou à une rainure (42, 44, 62, 64) qui forme une rampe de commande de fermeture et une rampe de commande d'ouverture pour mettre fin au processus d'injection, laquelle coopère avec une rampe de commande (15, 17, 52, 54) ou avec des alésages de commande (40, 60) de la douille de commande (3), caractérisée en ce qu'elle comprend un alésage d'aspiration ou d'amenée (7) séparé d'un alésage d'évacuation (9), que le piston plongeur (5) ou la douille de commande (3) dispose, en plus de l'alésage de commande existant (12, 40, 50, 60) et servant à mettre fin au processus d'injection, d'un alésage de commande auxiliaire (13, 41, 51, 61) qui est masqué complètement avant ou simultanément avec l'alésage de commande (12, 40, 50, 60), de sorte que l'alésage de commande auxiliaire supplémentaire diminue l'effet d'étranglement lors de la commande de fermeture, que l'alésage de commande auxiliaire n'est pas libéré par la rampe de commande de fermeture (17, 45, 54, 64) avant l'alésage de commande (12, 40, 50, 60), et que les alésages de commande (12, 13, 40, 41, 50, 51, 60, 61) peuvent être mis en communication avec l'alésage d'évacuation (9).
  2. Pompe d'injection de carburant selon la revendication 1, caractérisée en ce que l'alésage de commande auxiliaire (13, 41, 51, 61) se situe dans une position par rapport à l'alésage de commande (12, 40) qui correspond à une quantité d'injection plus grande, et que l'alésage de commande auxiliaire (13, 41, 51, 61) et l'alésage de commande (12, 40, 50, 60) coopèrent avec une rampe de commande d'ouverture (15, 43, 53, 63) commune.
  3. Pompe d'injection de carburant selon l'une des revendications 1 ou 2, caractérisé en ce que l'alésage de commande auxiliaire (13, 41) est plus grand que l'alésage de commande (12, 40).
  4. Pompe d'injection de carburant selon l'une des revendications 1, 2 ou 3, caractérisée en ce que la pente de la rampe de commande de fermeture (17, 45) diminue, devient nulle ou négative à l'extrémité (30, 49) qui correspond à la quantité d'injection maximale.
  5. Pompe d'injection de carburant selon l'une des revendications 1 à 4, caractérisée en ce que les rainures (42, 44) qui forment les rampes de commande de fermeture et d'ouverture sont disposées dans le piston plongeur (5) et que les deux rainures (42, 44) communiquent chacune par un alésage radial propre (46, 47) avec l'alésage axial (11) dans le piston plongeur(5).
  6. Pompe d'injection de carburant selon l'une des revendications 1 à 5, caractérisée en ce que l'alésage de commande auxiliaire (51, 61) est disposé, dans le sens de l'axe de la pompe, au-dessus ou en dessous de l'alésage de commande (50, 60), dans le piston plongeur (5) ou dans la douille de commande (3), et que la douille de commande (3) ou le piston plongeur (5) comporte deux rampes de commande d'ouverture (52, 53, 62, 63) dont l'écartement est égal à la distance entre l'alésage de commande auxiliaire (51, 61) et l'alésage de commande (50, 60).
  7. Pompe d'injection de carburant selon l'une des revendications 1 à 6, caractérisée en ce que l'alésage de commande (12, 50) et l'alésage de commande auxiliaire (13, 51) sont conformés dans le piston plongeur (5) et que les rampes de commande (15, 17, 52, 53) sont réalisées dans la douille de commande (3).
  8. Pompe d'injection de carburant selon l'une des revendications 1 à 7, caractérisée en ce qu'elle comprend une seconde rampe de commande de fermeture (56) qui n'est atteinte par l'alésage auxiliaire que pour la quantité d'injection maximale.
  9. Pompe d'injection de carburant selon l'une des revendications 1 à 8, caractérisée en ce que tous les alésages de commande (12, 13, 40, 41, 50, 51, 60, 61) et toutes les rampes de commande (15, 17, 43, 45, 53, 54, 63, 64) sont prévus en double avec un décalage de 180°.
EP90902108A 1989-01-30 1990-01-30 Pompe d'injection pour moteurs diesel Expired - Lifetime EP0409943B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90902108T ATE97996T1 (de) 1989-01-30 1990-01-30 Einspritzpumpe fuer dieselmotoren.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3902670 1989-01-30
DE3902670A DE3902670A1 (de) 1989-01-30 1989-01-30 Einspritzpumpe fuer dieselmotoren

Publications (2)

Publication Number Publication Date
EP0409943A1 EP0409943A1 (fr) 1991-01-30
EP0409943B1 true EP0409943B1 (fr) 1993-12-01

Family

ID=6373063

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90902108A Expired - Lifetime EP0409943B1 (fr) 1989-01-30 1990-01-30 Pompe d'injection pour moteurs diesel

Country Status (4)

Country Link
US (1) US5160088A (fr)
EP (1) EP0409943B1 (fr)
DE (2) DE3902670A1 (fr)
WO (1) WO1990008892A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5713520A (en) * 1995-11-27 1998-02-03 Caterpillar Inc. Fast spill device for abruptly ending injection in a hydraulically actuated fuel injector
DE10048365B4 (de) * 2000-09-29 2005-01-27 Robert Bosch Gmbh Drosselelement mit Spaltfilter
CA2689820A1 (fr) * 2009-01-13 2010-07-13 Miva Engineering Ltd. Pompe a piston

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE940384C (de) * 1938-07-01 1956-03-15 Messerschmitt Boelkow Blohm Brennstoffeinspritzpumpe fuer Brennkraftmaschinen
DE848438C (de) * 1943-12-12 1952-09-04 Bosch Gmbh Robert Einspritzpumpe, insbesondere fuer Brennkraftmaschinen
CH319362A (de) * 1953-03-05 1957-02-15 Daimler Benz Ag Kolben-Kraftstoffeinspritzpumpe
DD124932A1 (fr) * 1975-12-02 1977-03-23
DE2609724A1 (de) * 1976-03-09 1977-09-15 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3143073A1 (de) * 1981-10-30 1983-05-11 Robert Bosch Gmbh, 7000 Stuttgart Einspritzpumpe mit einstellbarem spritzzeitpunkt
DE3411407A1 (de) * 1984-03-28 1985-10-03 Robert Bosch Gmbh, 7000 Stuttgart Pumpduese fuer die kraftstoffeinspritzung bei brennkraftmaschinen
JPH0541262Y2 (fr) * 1985-04-17 1993-10-19
DE3533014A1 (de) * 1985-09-16 1987-03-26 Avl Verbrennungskraft Messtech Verfahren und einrichtung zur einbringung des kraftstoffes in den brennraum eines dieselmotors
DE3709245A1 (de) * 1986-03-22 1987-09-24 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3630647A1 (de) * 1986-03-24 1988-02-11 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3633899A1 (de) * 1986-10-04 1988-04-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DD256167A1 (de) * 1986-12-24 1988-04-27 Barkas Werke Veb Kraftstoffeinspritzpumpe mit umlaufender steuerkante

Also Published As

Publication number Publication date
DE59003665D1 (de) 1994-01-13
DE3902670A1 (de) 1990-08-02
EP0409943A1 (fr) 1991-01-30
WO1990008892A1 (fr) 1990-08-09
US5160088A (en) 1992-11-03

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