EP0162287B1 - Kraftstoffeinspritzpumpe für Brennkraftmaschinen - Google Patents

Kraftstoffeinspritzpumpe für Brennkraftmaschinen Download PDF

Info

Publication number
EP0162287B1
EP0162287B1 EP85104654A EP85104654A EP0162287B1 EP 0162287 B1 EP0162287 B1 EP 0162287B1 EP 85104654 A EP85104654 A EP 85104654A EP 85104654 A EP85104654 A EP 85104654A EP 0162287 B1 EP0162287 B1 EP 0162287B1
Authority
EP
European Patent Office
Prior art keywords
lever
fuel injection
spring
injection pump
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.)
Expired
Application number
EP85104654A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0162287A2 (de
EP0162287A3 (en
Inventor
Wolfgang Braun
Karl Konrath
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 EP0162287A2 publication Critical patent/EP0162287A2/de
Publication of EP0162287A3 publication Critical patent/EP0162287A3/de
Application granted granted Critical
Publication of EP0162287B1 publication Critical patent/EP0162287B1/de
Expired legal-status Critical Current

Links

Images

Classifications

    • 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
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/128—Varying injection timing by angular adjustment of the face-cam or the rollers support

Definitions

  • the invention is based on a fuel injection pump according to the preamble of the main claim.
  • the pressure which loads the movable wall in the sense of a reset is controlled with the aid of a pressure limiting valve on the one hand and with the aid of an electromagnetically actuated switching valve on the other hand.
  • the solenoid-operated switching valve is controlled by a control device as a function of several operating parameters such that it is closed during a cold start and in the warm-up phase.
  • the fuel injection pump according to the invention with the characterizing features of the main claim has the advantage that the spray adjustment is carried out in a simple manner by hydraulic means, without essential mechanical interventions in the drive mechanism of the fuel injection pump are necessary and at the same time a means is given in a simple manner Way to increase the idle speed to produce good idle behavior in the warm-up phase.
  • the measure specified in claim 4 characterizes an advantageous further development and improvement of the solution specified in the main claim.
  • This has the advantage that the idle speed increase to be brought about with the aid of the modified preload of the idle spring can be carried out with only slight forces.
  • the forces to be overcome are only slight here.
  • the forces of a return spring act on the adjusting lever and, on the other hand, the friction of the linkage between the accelerator pedal and the adjusting lever, which may be very complex, acts.
  • FIG. 1 shows a first exemplary embodiment
  • FIG 2 shows a graphical representation of the adjustment path of the injection start control device achieved with the device according to the invention over the speed.
  • a pump piston 3 operates in a cylinder bore 2, which is held on a stimulating cam disk 6 at its end which projects in a fuel-filled suction chamber 4 in the housing 1 of the fuel injection pump by a spring 5 which is supported on the housing.
  • the stimulating cam disk is set in rotary motion by a drive shaft 8 via a clutch 9 and runs over rollers 10 of a roller ring 11, as a result of which the pump piston is set in a reciprocating, pumping and at the same time rotating motion.
  • the pump piston In the cylinder bore 2, the pump piston includes a working space 12 on the end side, which can be connected to the pump suction chamber via a longitudinal bore 14 extending from the end side of the pump piston and a transverse bore 15 located in the region of the part of the pump piston constantly immersed in the suction chamber.
  • the opening of the transverse bore 15 in the suction chamber is controlled by a ring slide 16, the axial position of which is set by a controller 17.
  • the pump piston has suction grooves 18 which alternately come into contact with suction bores 19 during its rotation and serve to fill the pump work space with fuel.
  • a connection to a distribution groove 21 on the outer surface of the pump piston continues from the longitudinal bore 14.
  • the distribution pattern is successively connected to one of several injection lines 22 extending from the cylinder bore 2. These lead via a check valve 23, optionally designed as a relief valve, to an injection valve 24 on the internal combustion engine.
  • the moment at which the delivery stroke of the pump piston begins depends on the relative position of the roller ring 11, which is rotatably mounted in the housing 1 and is adjustable by means of an injection adjuster piston 25. In this way, the start of the stroke of the stimulus cam 6 is adjusted in relation to a specific angle of rotation of the drive shaft 8.
  • the injection adjuster piston is coupled to the cam ring 11 via a bolt 26 and is displaceable in a cylinder 27.
  • the injection adjuster piston On one side of the closed cylinder, the injection adjuster piston includes a working chamber 28, which is connected to the suction chamber 4 via a throttle 29.
  • the injection adjuster piston with working space 28 has been drawn out again separately in a schematic diagram. This part of the drawing also shows the courses of the hydraulic lines, which will be described below.
  • a return spring 30 engages, against which the injection adjuster piston is moved as the pressure in the suction chamber rises.
  • the suction chamber 4 is supplied with fuel from a fuel reservoir 33 by a feed pump 32, which is also driven by the drive shaft 8.
  • a pressure control valve 35 is provided, which consists of a movable wall, here a piston 36, the end face 39 of which encloses a working chamber 38 in a cylinder 37 that guides it. This is connected to the suction chamber 4 and via a discharge line 40 leading laterally to the cylinder 37, the opening of which is controlled by the end face 39 of the piston 36, with a relief chamber, for. B. the reservoir 33 connectable.
  • a throttle connection 41 continues from the end face 39 through the piston 36 to a spring space 42 which is enclosed on the other side by the piston 37 in the cylinder 37 and in which a return spring 43 which acts on the piston is arranged.
  • the spring chamber 42 can also be connected to the relief chamber 33 via a second relief line 44, regardless of the position of the piston.
  • the injection quantity is controlled by the controller 17, which is formed in a known manner as a control lever arrangement consisting of a tensioning lever 48 and a starting lever 49.
  • the tensioning lever is designed as a one-armed lever which rotates about the same, optionally adjustable axis 50 on which the two-armed starting lever is also mounted.
  • One arm of the start lever is coupled to the ring slide 16 while the other arm of the start lever carries a start spring 51 which lies between the tension lever 48 and the start lever 49 and, after their compression, the start lever comes to rest against a stop 52 of the tension lever.
  • a regulating spring 55 is attached to the tensioning lever via an intermediate spring 54 and is attached to a lever arm 56 at its other end.
  • the controller works as follows: at the start, the start lever 49 is held by the start spring 51 on the adjusting sleeve 59 which is in the starting position. The starting spring spreads the starting lever from the tensioning lever 48. The ring slide 16 is brought into its highest position, so that the pump piston is almost. can perform its entire stroke before the transverse bore 15 is opened by the ring slide 16. This corresponds to the maximum fuel injection quantity. With increasing speed, the speed sensor moves the start lever towards the tensioning lever until it comes to rest against the stop 52. The effect of the idle control spring comes into play in the intermediate area. In the partial load range, the position of the adjusting lever 58 or the force exerted by the control spring 55 on the tensioning lever determines the fuel injection quantity.
  • the tension lever is adjusted together with the start lever by the speed sensor against the force of the control spring 55.
  • the fuel quantity is thus regulated in such a way that the set maximum speed is not exceeded.
  • the intermediate spring 54 can come into effect for adjustment.
  • the second relief line 44 is passed in a first branch 44a via a valve 65 and in a second branch 44b via a pressure holding valve 66 which opens to the relief side after the pressure set thereon has been exceeded.
  • the valve 65 is mechanically coupled to the lever 63 via a linkage 67 and can be actuated at the same time or with a delay.
  • the linkage can be actuated by hand or by a temperature-controlled control element or by an control element that is controlled by a control device that detects various operating parameters of the internal combustion engine.
  • the valve 65 closes when the relief line part 44a is actuated and at the same time or delays the pretension the idle spring 61 increased. This has the effect that the amount flowing off through the throttle 41 introduced into the piston 36 builds up a pressure in the spring chamber 42 of the pressure control valve now serving as the control pressure chamber, which pressure is determined by the opening pressure of the pressure-maintaining valve 66. This back pressure causes a simultaneous increase in the pressure in the suction chamber 4 and thus a displacement of the spray adjuster piston in the "early" direction. This pressure increase causes a spray adjuster progression according to curve II as shown in Figure 2. It can be seen from this diagram that an adjustment of the spray adjuster is already takes place at a much lower speed than in normal operation, in which the valve 65 is open.
  • Curve II also shows that, by skillfully designing the control point 46 on the piston 36, the injection adjuster path can be bent over the speed. that there is only a slight increase in pressure in the suction chamber 4 due to the amount flowing off via the relief line 40 and 45, until a spray adjustment curve according to the curve for normal operation is achieved.
  • the control point 46 with the relief line 45 assumes a safety function if the valve 65 despite the warm engine not open et, otherwise the motor will be thermally overloaded.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Fuel-Injection Apparatus (AREA)
EP85104654A 1984-05-18 1985-04-17 Kraftstoffeinspritzpumpe für Brennkraftmaschinen Expired EP0162287B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3418437 1984-05-18
DE19843418437 DE3418437A1 (de) 1984-05-18 1984-05-18 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Publications (3)

Publication Number Publication Date
EP0162287A2 EP0162287A2 (de) 1985-11-27
EP0162287A3 EP0162287A3 (en) 1987-09-09
EP0162287B1 true EP0162287B1 (de) 1989-08-30

Family

ID=6236173

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85104654A Expired EP0162287B1 (de) 1984-05-18 1985-04-17 Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Country Status (4)

Country Link
US (1) US4622943A (ja)
EP (1) EP0162287B1 (ja)
JP (1) JPS60259762A (ja)
DE (2) DE3418437A1 (ja)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3632539C2 (de) * 1986-09-25 1995-12-14 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Kraftfahrzeug-Brennkraftmaschinen
DE3632540A1 (de) * 1986-09-25 1988-03-31 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer eine diesel-brennkraftmaschine in einem kraftfahrzeug
DE3813880A1 (de) * 1988-04-25 1989-11-02 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE3822257A1 (de) * 1988-07-01 1990-01-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3827206A1 (de) * 1988-08-11 1990-02-15 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JP2843614B2 (ja) * 1989-09-29 1999-01-06 ヤマハ発動機株式会社 ２サイクルディーゼルエンジン
DE4117813A1 (de) * 1991-05-31 1992-12-03 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4333778A1 (de) * 1993-10-04 1995-04-06 Bosch Gmbh Robert Drehzahlregler für Kraftstoffeinspritzpumpen von Brennkraftmaschinen
GB9905339D0 (en) * 1999-03-10 1999-04-28 Lucas Ind Plc Fuel injector pump advance arrangement

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2648043C2 (de) * 1976-10-23 1984-05-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE2844910A1 (de) * 1978-10-14 1980-04-30 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE2909559A1 (de) * 1979-03-10 1980-09-11 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE2909456A1 (de) * 1979-03-10 1980-09-18 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US4457284A (en) * 1979-06-07 1984-07-03 Stanadyne, Inc. Cold temperature advance mechanism
JPS6131157Y2 (ja) * 1981-03-12 1986-09-10
DE3138607A1 (de) * 1981-09-29 1983-04-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3148214A1 (de) * 1981-12-05 1983-06-09 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Also Published As

Publication number Publication date
JPH0476028B2 (ja) 1992-12-02
EP0162287A2 (de) 1985-11-27
JPS60259762A (ja) 1985-12-21
US4622943A (en) 1986-11-18
DE3418437A1 (de) 1985-11-21
EP0162287A3 (en) 1987-09-09
DE3572713D1 (en) 1989-10-05

Similar Documents

Publication Publication Date Title
DE2503346C2 (de) Kraftstoffverteilereinspritzpumpe für Brennkraftmaschinen
DE2644042C2 (de) Verstelleinrichtung für den Spritzbeginn bei einer Kraftstoffeinspritzpumpe für eine Brennkraftmaschine
DE2638736C3 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen mit hydraulischem Regler
CH617246A5 (ja)
DE2844910A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
EP0162287B1 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE2931944C2 (ja)
DE2729807C2 (de) Kraftstoffeinspritzpumpe mit Mitteln zur Spritzbeginnverstellung für Brennkraftmaschinen
EP0273225B1 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen
EP0168586B1 (de) Kraftstoffeinspritzpumpe
DE3516456C2 (ja)
DE2402374A1 (de) Drehzahlregler fuer kraftstoffeinspritzpumpen
DE3135477A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE1920417C3 (de) Kraftstoffverteilereinspritzpumpe fur eine Brennkraftmaschine
DE2612940A1 (de) Drehzahlregler fuer eine kraftstoffeinspritzpumpe
DE3019094C2 (de) Verteilerkraftstoffeinspritzpumpe für eine Brennkraftmaschine
DE2931937C2 (ja)
DE2808472A1 (de) Pumpvorrichtung fuer die kraftstoffversorgung einer verbrennungskraftmaschine
DE3203583A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen mit spritzzeitpunktverstellung
DE2813111C2 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE3644148A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
EP0971122B1 (de) Kraftstoffeinspritzpumpe für eine Brennkraftmaschine
EP0150286A1 (de) Kraftstoffeinspritzpumpe
EP0627552A1 (de) Kraftstoffeinspritzpumpe
DE1255389B (de) Regelvorrichtung fuer einen durch eine Brennkraftmaschine angetriebenen hydrostatischen Fahrzeugantrieb

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19850417

AK Designated contracting states

Designated state(s): DE FR GB

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB

17Q First examination report despatched

Effective date: 19890118

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
ET Fr: translation filed
REF Corresponds to:

Ref document number: 3572713

Country of ref document: DE

Date of ref document: 19891005

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19920629

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19920717

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19920824

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19930417

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19930417

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19931229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19940101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST