EP0812384B1 - Pompe d'injection de carburant pour moteur a combustion interne - Google Patents

Pompe d'injection de carburant pour moteur a combustion interne Download PDF

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Publication number
EP0812384B1
EP0812384B1 EP96934435A EP96934435A EP0812384B1 EP 0812384 B1 EP0812384 B1 EP 0812384B1 EP 96934435 A EP96934435 A EP 96934435A EP 96934435 A EP96934435 A EP 96934435A EP 0812384 B1 EP0812384 B1 EP 0812384B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
pump
connection
controlled
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
EP96934435A
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German (de)
English (en)
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EP0812384A1 (fr
Inventor
Christian Taudt
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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Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0812384A1 publication Critical patent/EP0812384A1/fr
Application granted granted Critical
Publication of EP0812384B1 publication Critical patent/EP0812384B1/fr
Anticipated expiration legal-status Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
    • F02D2001/186—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic using a pressure-actuated piston for adjustment of a stationary cam or roller support

Definitions

  • the invention relates to a fuel injection pump for Internal combustion engines according to the preamble of claim 1 out.
  • a fuel injection pump for Internal combustion engines according to the preamble of claim 1 out.
  • DE-A1-43 41 932 Known fuel injection pump is the reset space of the Pressure control valve from a certain temperature that the warm internal combustion engine corresponds to a controlled valve relieved. From this operating point the pressure control valve works as intended Type to adjust the pressure of the pump interior To control the start of spraying depending on the speed.
  • this known device is a special one Setting the start of spraying when the internal combustion engine is cold only controllable depending on temperature.
  • the fuel injection pump with the characterizing features of claim 1 has the advantage that independent of the control of the controlled valve, depending on the temperature, there is also the possibility of relieving the pressure in the interior of the pump to cause relief of the return space, which then the mode of operation of the pressure control valve is converted into the mode of operation which is provided for an internal combustion engine which is at operating temperature, regardless of the actual temperature of the internal combustion engine.
  • the influencing of the start of spraying controlled by the pressure control valve when the internal combustion engine is not at operating temperature is switched off or the particular mode of operation of this pressure control valve is limited as a function of the speed.
  • Claim 2 An advantageous development of the invention Claim 2 is the control of the controlled valve in connection with the control of the Pump interior pressure advantageous to improve such that now both a load-dependent, and temperature and speed-dependent influencing of the pressure in the Pump interior allows control of the start of spraying is.
  • the limiting valve is advantageous as Slider valve designed, which is a particularly exact Switching point setting enabled.
  • More beneficial Embodiments of the invention are in the further Subclaims 3 to 6 and have the advantage that Switching accuracy to control the pump interior pressure too improve. The can compared to the state of the Technology to be provided in addition easily integrate into existing solutions under Use of many existing series parts.
  • FIG. 1 shows a schematic representation of a distributor injection pump in Longitudinal section
  • Figure 2 shows the essential part of the invention
  • Figure 3 shows a modified embodiment of the Embodiment of Figure 2 and Figure 4, a third Execution of the invention with a separately provided Spool.
  • a pump piston 1 In the distributor fuel injection pump shown in Figure 1
  • a pump piston 1 In a known manner, a pump piston 1 is provided, which a cam disk 2 rotating from a drive shaft 3 the fuel injection pump is driven and with it Cam track 4 runs on rollers 5 of a roller ring 6, in a back and forth and at the same time rotating movement offset, by the rotation of the pump piston at the same time as Serves distributor.
  • the pump piston closes in one in the housing 7 of the fuel injection pump arranged cylinder 8 Cylinder bore a pump work space 9 on the front, in the suction stroke of the pump piston via suction grooves 10 and one Suction channel 11 fuel drawn from a pump interior 12 is and in its pressure stroke via a longitudinal channel 14 which of the end of the pump piston, and one with this Longitudinal channel 14 connected distributor groove 15 fuel to one is promoted by a plurality of pressure channels 16.
  • These pressure channels 16 are at regular intervals around the pump piston from the cylinder bore arranged outgoing and insert over each Pressure valve 17 to a not shown Fuel injector.
  • the amount of fuel supplied to this is determined by the axial position of a ring slide 18, the to a part of the projecting into the pump interior 12
  • Pump piston 1 is longitudinally displaceable. Through the front edge of the ring slide 18 becomes one with the longitudinal channel 14 connected cross bore 19 from a certain Pump piston delivery stroke opened so that the Pump work space in the pump interior is relieved and the High-pressure delivery phase with injection is ended.
  • the position of the ring slide is controlled by a speed controller 20 controlled, which has a control lever 21, on the one hand is coupled to the ring slide 18 and on the other hand by a control spring 22 is acted upon by a Regulator lever 23 can be preloaded more or less.
  • an adjusting sleeve 24 acts Centrifugal speed sensor 25, the centrifugal weights 26 about Gear transmission 27, 28 driven by the drive shaft 3 and the regulator sleeve 24 with increasing speed on a sleeve carrier 30 against the force of the control spring 22 push.
  • a spray adjuster 31 is also provided, which in the drawing is shown folded into the plane by 90 °.
  • This has one Spray adjuster piston 32 on the front of a work space 33 encloses in one cylinder bore and on its other End face is acted upon by a return spring 34.
  • the Injection adjuster piston is connected via a pin 36 to the Coupled roller ring 6, which is mounted in the pump housing and at its rotation the start of the stroke of the cam disc 4 and so that the pump piston 1 depending on the direction of rotation earlier or later with respect to the angular position of the drive shaft 3 or the rotational position of the pump piston 1.
  • the adjustment of the Injection adjuster piston 32 takes place in the working space 33 introduced pressure medium, which via a throttle connection 37 in Spray adjuster piston is supplied. Serves as a pressure source the pump interior 12, into which a feed pump 38 which is driven synchronously by the drive shaft 3, Fuel to supply the pump work space 9 is promoted.
  • a pressure control valve 39 controlled, which has a control piston 40 as a control element, which is arranged displaceably in a cylinder bore 51 one end face one with the pump interior connected pressure space 41 and limited to its other Front side of a spring providing a restoring force 42 is applied.
  • the control piston controls a discharge 43 from the front Pump interior 12 to a relief space, the present the suction side of the fuel pump 38 or the Fuel tank 44 can be.
  • the spring 42 receiving space is as a reset space 54 via a throttle 45 in the control piston connected to the pressure chamber 41 and via a Relief line 46 connected to a controlled valve 52. This is shown in more detail in FIGS. 2 to 4.
  • a distributor injection pump with a Lifting cam and a roller ring described by the Injection start adjuster 31 is adjusted to adjust the Start of spraying.
  • a spray start adjuster can also differently ordered cam drives of injection pumps be adjusted, e.g. B. in radial piston pumps a cam ring or facilities, e.g. B. for in-line pumps to adjust the relative cam position to the drive shaft.
  • cam-bearing part which is essentially is fixed
  • a roller-bearing part, which as Cam follower scans the cam track can be adjusted to the to achieve the desired spray start adjustment result.
  • the pressure in the pump interior can preferably be used as an adjustment medium or control pressure for the injection start adjuster which also with increasing speed via its adjusting piston and the cam gear adjusts the start of spraying.
  • Interior pressure depending on other parameters than affect the speed to certain pump functions in relation to the start of spray setting. This can in particular a load dependent factor can be introduced by a variable drain throttle 47 provided on the adjusting sleeve 24 becomes.
  • the adjusting sleeve has an opening in its wall, which in the course of the adjustment of the adjusting sleeve 24 increasingly in Coverage with a drain channel 48 comes within the Sleeve carrier 30 runs. This drainage channel leads over the controlled valve 52 to the relief chamber, the suction side of the Fuel feed pump 38 or the fuel reservoir 44 back.
  • FIG 2 is the pressure control valve 39 which is in connection with the controlled valve 52, a first pressure control device 49 forms, shown in more detail. It is again as above described, representing a second pressure control device 50 Device for additional influencing of the Pump interior pressure consisting of the discharge throttle 47 and the adjusting sleeve 24, through the load-dependent fuel quantities are branched off from the pump interior, reproduced.
  • the controlled valve 52 is in the relief line 46 of the Reset room 54 arranged. It consists of one Ball check valve with a ball 56 as a closing member, the by a spring 57 with a defined preload in Closing direction is kept.
  • the controlled valve 52 is the temperature of the Controlled internal combustion engine characteristic size.
  • FIG temperature-dependent expansion element 59 the for example the cooling water temperature of the internal combustion engines may be exposed or may be electrically heated in Depending on the temperature or a substitute parameter.
  • a slide valve member 61 which acts as a piston a bore 62 coaxial with the controlled valve 52 is arranged displaceably, and by a return spring 63 is loaded towards the expansion element 59.
  • the Slider valve member continues in an adjusting mandrel 64 which axially in a discharge line 46 with the controlled Valve 52 on the one hand and the bore 62 on the other connecting channel protrudes so that with a shift of the slide valve member 61 through the expansion element 59 of the Setting mandrel 64 comes into contact with the ball 56 and this of lifts off its seat and thus opens the control valve. So that will the connection of the relief line 46 to the relief space manufactured.
  • the slide valve member controls the continued drain channel 48 of the second Pressure control device 50.
  • This channel opens into the Hole 62 that he in the cold engine in Figure 2 shown position of the slide valve member 61 by this is closed and when the internal combustion engine is warm which the slide valve member together with the setting mandrel is shifted to open the controlled valve 52, opened is.
  • the channel 48 leads in from the bore 62 electromagnetically operated switching valve 66 for Relief chamber 44. The switching valve, the open or Closed position is then significant when the slide valve member 61 has opened the drain channel 48 is in Dependency on operating parameters other than temperature controlled the internal combustion engine. It then closes if, as mentioned at the beginning, e.g. B.
  • a limit valve 106 is provided, consisting of a Slider 107, which is tight in a cylinder bore is movable and with its front side a work space 109 includes that via a throttle 108 in constant Connection to the pump interior 12 is.
  • the work room 109 opposite one acts on the slide 107 Actuating force in the form of a compression spring 110, which in particular is adjustable.
  • a channel 111 is provided in the slide, the against the corresponding deflection of the slide 107 the force of spring 110 in conjunction with one Connection channel 112 arrives from the relief line 46 branches and thus in constant connection with the Reset room 54 is.
  • channel 111 opens into the space accommodating the spring 110, which in turn has a Line 114 with the relief chamber 44 and the Fuel tank is connected.
  • This valve 106 is part of the first pressure control device 49. With it achieved that from a certain internal pressure in Pump interior 12 a relief connection between the Reset space 54 and the relief space 44 produced becomes. This happens regularly when you reach one certain speed at which a special early adjustment the start of spraying or a special setting of the Start of injection and the fact that the internal combustion engine is not yet warm, is not necessary. With With the help of this limit valve 106, the use of first pressure control device 49 to a specific one Speed resulting from the interior pressure of the pump interior 12 derivable is limited.
  • the load-dependent is basically Influencing the interior pressure allows when the required operating temperature is reached and that Ball check valve 156 constantly through the expansion element 59 is lifted off.
  • FIG. 4 Another embodiment of such an influence shows the embodiment of Figure 4.
  • Pressure control device 49 is shown in Figure 2.
  • Figure 4 is a piston valve 100 provided in a Cylinder bore 101 is slidably arranged and on one side is acted upon by a return spring 103 is closed while its other end face Cylinder bore 101 includes a working space 102 that constantly with the relief line 46 or the reset room 54 is connected. Because of the pressure in this recovery room the spool can move against the force of the return spring 103 to be moved up to a stop 104 such that the leading through the cylinder bore 101 Connection line to the continuing line through the Piston slide is closed.

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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)
  • High-Pressure Fuel Injection Pump Control (AREA)

Claims (6)

  1. Pompe d'injection de carburant pour des moteurs à combustion interne comportant un piston de pompe (1) actionné par un entraínement par cames formé d'une partie (2) rotative entraínée par un arbre d'entraínement (3) et d'au moins une partie (6) essentiellement fixe portant un chemin de cames (4) mobile de manière relative par rapport à l'autre partie, pour créer un mouvement de va et vient transversalement au chemin de cames pour le piston de pompe (1) couplé à l'une des parties, ainsi qu'un piston de réglage de début d'injection (32) pour régler l'une des parties dans le sens de déplacement du chemin de cames (4) ou dans le sens opposé, ce piston de réglage de début d'injection (32) étant actionné contre une force de rappel (34) par une pression de commande d'un agent de pression hydraulique dans le volume intérieur (12) de la pompe d'injection de carburant, la pression de commande étant fournie par une pompe de transfert (38) entraínée en synchronisme de rotation avec la pompe d'injection de carburant et réglée par une première installation de commande de pression (49) comportant une soupape de commande de pression (39), dont l'organe de commande (40) commande la sortie (43) de la chambre intérieure (12) de la pompe et est sollicité par la pression induite contre la force développée par un ressort (42), cette pression régnant dans une chambre de rappel (54) délimitée par l'organe de commande (40) et reliée au volume intérieur (12) de la pompe par l'intermédiaire d'un organe d'étranglement (45), la pression de commande étant en outre réglée par une seconde installation de commande de pression (50) qui comporte un organe d'étranglement de sortie (47) réglable en fonction de la charge du moteur à combustion interne dans une liaison (48) comportant une soupape de commutation (66) commandée de préférence selon les paramètres de fonctionnement, cette liaison étant établie entre la chambre intérieure (12) de la pompe et une chambre de décharge (44), et la chambre de rappel (54) comportant en outre une sortie conduisant à la chambre de décharge (44), sortie qui est réglable par une soupape (52, 152, 252) commandée en fonction d'une grandeur de commande caractérisant la température du moteur à combustion interne, et dont l'actionnement déplace directement ou indirectement un organe de soupape (61, 161, 100) d'une soupape qui commande la communication (48) entre l'organe d'étranglement de sortie (47) et la chambre de décharge (44) de la seconde installation de commande de pression (50) pour que la communication soit ouverte lorsque la soupape commandée (52, 152, 252) est ouverte, la soupape de commutation (66) étant commutée de préférence en fonction d'autres paramètres que la température du moteur à combustion interne,
    caractérisé en ce qu'
    en parallèle à la soupape commandée (52, 152, 252), il est prévu une soupape de limitation de pression (106) établissant une liaison entre la chambre de rappel (54) et la chambre de décharge (44) lorsque la pression dans la chambre intérieure de la pompe dépasse une certaine valeur.
  2. Pompe d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    la soupape de limitation de pression (106) comporte une soupape en forme de tiroir (107) qui délimite par un organe d'étranglement (108) la chambre (109) reliée au volume intérieur de la pompe, et qui peut être déplacé contre une force de rappel réglable (110).
  3. Pompe d'injection de carburant selon la revendication 1 ou 2,
    caractérisée en ce que
    la soupape commandée (52) est une soupape de retenue de pression, dont l'organe (56) est chargé par un ressort (57) et peut être ouvert par un organe d'actionnement (64) réglé en fonction d'une grandeur de commande, et un tiroir (61) est réglé en même temps que la soupape commandée, tiroir qui commande la liaison (48, 65) entre l'organe de sortie (47) et la chambre de décharge (44) de la seconde installation de commande de pression (50) (figure 1).
  4. Pompe d'injection de carburant selon la revendication 1 ou 2,
    caractérisée en ce que
    la soupape commandée (152) est une soupape de retenue de pression, dont l'organe (156) est chargé par un ressort (157) et peut être ouvert par un organe d'actionnement (164) déplacé en fonction d'une grandeur de commande, et un tiroir (161) est déplacé avec l'organe de la soupape, ce tiroir commandant la communication (48, 65) entre l'organe d'étranglement de sortie (47) et la chambre de décharge (44) de la seconde installation de commande de pression (50) (figure 2).
  5. Pompe d'injection de carburant selon la revendication 4,
    caractérisée en ce que
    l'organe de la soupape de retenue de pression est une bille coopérant avec un siège de soupape (70), cette bille venant en appui par son côté opposé au siège de soupape contre le tiroir (161) lui-même sollicité par un ressort (157) (figure 3).
  6. Pompe d'injection de carburant selon la revendication 4,
    caractérisée en ce que
    la soupape commandée (252) est une soupape de retenue de pression, dont l'organe (256) est chargé par un ressort (257) et peut être ouvert par un organe d'actionnement (264) déplacé en fonction de la grandeur de commande, et la soupape commutant la liaison (48, 65) comporte comme organe un tiroir à piston (100), qui délimite dans un cylindre (101) installé dans la liaison (48, 65) entre l'organe d'étranglement de sortie (47) et la chambre de décharge (44), une chambre de travail (102) reliée en permanence à la chambre de rappel (54), et qui peut être coulissé par la pression régnant dans la chambre de travail (102) contre la force d'un ressort de rappel (103) jusqu'à une butée fixe (104), au niveau de laquelle ce tiroir a fermé la liaison (48, 65) entre l'organe d'étranglement de sortie (47) et la chambre de décharge (44) (Figure 4).
EP96934435A 1995-12-28 1996-10-24 Pompe d'injection de carburant pour moteur a combustion interne Expired - Lifetime EP0812384B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19549046A DE19549046A1 (de) 1995-12-28 1995-12-28 Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE19549046 1995-12-28
PCT/DE1996/002014 WO1997024519A1 (fr) 1995-12-28 1996-10-24 Pompe d'injection de carburant pour moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0812384A1 EP0812384A1 (fr) 1997-12-17
EP0812384B1 true EP0812384B1 (fr) 2001-09-26

Family

ID=7781595

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96934435A Expired - Lifetime EP0812384B1 (fr) 1995-12-28 1996-10-24 Pompe d'injection de carburant pour moteur a combustion interne

Country Status (8)

Country Link
EP (1) EP0812384B1 (fr)
JP (1) JPH11501384A (fr)
KR (1) KR100304474B1 (fr)
CN (1) CN1079896C (fr)
BR (1) BR9607437A (fr)
DE (2) DE19549046A1 (fr)
RU (1) RU2166658C2 (fr)
WO (1) WO1997024519A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9725415D0 (en) * 1997-12-02 1998-01-28 Lucas Ind Plc Advance arrangement
CN100436808C (zh) * 2003-04-01 2008-11-26 Avl里斯脱有限公司 一种驱动直接喷射式柴油机的方法和装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3822257A1 (de) * 1988-07-01 1990-01-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4341932A1 (de) * 1993-12-09 1995-06-14 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Also Published As

Publication number Publication date
KR19980702579A (ko) 1998-07-15
BR9607437A (pt) 1998-05-26
DE59607780D1 (de) 2001-10-31
DE19549046A1 (de) 1997-07-03
RU2166658C2 (ru) 2001-05-10
EP0812384A1 (fr) 1997-12-17
WO1997024519A1 (fr) 1997-07-10
JPH11501384A (ja) 1999-02-02
CN1175993A (zh) 1998-03-11
CN1079896C (zh) 2002-02-27
KR100304474B1 (ko) 2001-11-30

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