EP1312782A2 - Pompe à injection à accélération de démarrage à froid pour moteurs à combustion interne à injection directe - Google Patents

Pompe à injection à accélération de démarrage à froid pour moteurs à combustion interne à injection directe Download PDF

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Publication number
EP1312782A2
EP1312782A2 EP02022593A EP02022593A EP1312782A2 EP 1312782 A2 EP1312782 A2 EP 1312782A2 EP 02022593 A EP02022593 A EP 02022593A EP 02022593 A EP02022593 A EP 02022593A EP 1312782 A2 EP1312782 A2 EP 1312782A2
Authority
EP
European Patent Office
Prior art keywords
piston
injection
fuel delivery
delivery unit
unit according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP02022593A
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German (de)
English (en)
Other versions
EP1312782B1 (fr
EP1312782A3 (fr
Inventor
Helmut Simon
Helmut Haberer
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 EP1312782A2 publication Critical patent/EP1312782A2/fr
Publication of EP1312782A3 publication Critical patent/EP1312782A3/fr
Application granted granted Critical
Publication of EP1312782B1 publication Critical patent/EP1312782B1/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
    • 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
    • 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

  • diesel fuel takes a certain amount of time to start to the combustion air an inflammable, self-igniting mixture at high pressure form.
  • the time required between the start of injection and the start of combustion is referred to as ignition delay in self-igniting internal combustion engines. This is determined, among other factors, by the ignitability of the diesel fuel (expressed by the cetane number), the achievable compression ratio of the self-igniting internal combustion engine and the quality of fuel atomization through the fuel injector injector.
  • the ignition delay in self-igniting Internal combustion engines are usually on the order of 1-2 ms. Extended during the cold start phase, especially at low outside temperatures this period of time, which leads to soot formation from unburned fuel the exhaust system gets into the environment.
  • a hydraulic measure for Cold start acceleration is a temporary increase in the Interior pressure of the distributor injection pump during the cold start and the itself immediately igniting immediately after this subsequent cold running phase Internal combustion engines.
  • the Displacement of a sprayer piston causes a displacement of the Injection starts early.
  • the disadvantage of this measure is a late one Injection plunger piston starts to move due to slow pressure build-up in the interior the distributor injection pump.
  • Another way to adjust the start of injection early is through Twisting a component designed as a roller ring during the start and Cold running phase of the self-igniting internal combustion engine, the injection adjuster piston and thus to adjust the start of injection early.
  • Another on mechanical One feasible measure is on one side of the sprayer piston to press by means of an eccentric shaft and thereby close the injection adjuster piston adjust that the start of injection shifts to early.
  • the disadvantage of this measure is that only limited adjustment options can be reached, which find their limits in the mechanical overloading of the components involved and thus only a limited shift in the start of injection is achieved early can be.
  • the displacement of the sprayer piston towards an earlier one Injection begins in the cold phase by opening the inlet bore through a Follower piston.
  • the trailing piston can also be used as a servo piston or as a Control valve should be made.
  • the function of this component lies in opening and Closing the inlet and outlet on the spray adjuster piston.
  • the one assigned to the adjusting piston is The pressure chamber is initially empty; it is filled during the process Warm-up phase of the internal combustion engine with increasing speed. With the increasing filling of the interior of the distributor injection pump increases Interior pressure considerably.
  • the injection adjuster piston is shorter Adjustable response time. In the start phase of the internal combustion engine occurring, extremely low speeds, an earlier start of the Injection adjuster pistons can be reached without a complete high pressure build-up in the Pump interior is required. Since in the solution according to the invention High pressure build-up in the pump room is not required Injection plunger piston in time so early that the first revolutions of the Internal combustion engine an earlier injection timing can be achieved. On earlier injection timing improves fuel atomization during injection considerably so that the ignitability of the fuel air mixture within the Combustion chamber increases significantly. On the one hand, this leads to a reduction in Particle emission during the start and cold phase; on the other hand, with the Solution proposed according to the invention a faster start of the auto-igniting Reach the internal combustion engine.
  • the injection adjuster piston of the distributor injection pump is directed towards "Start of injection early" is adjusted by a trailing piston, which has an inlet bore releases or closes.
  • the trailing piston by a spring-sleeve combination is moved, is supported on a cold start acceleration piston, the end face of which in protrudes into a pressure chamber.
  • the trailing piston which in different Design options both as control slide, as servo or as control piston can be formed, opens and closes the inlet and outlet of the Injection adjuster piston, so that this according to the operating state of the self-igniting internal combustion engine the injection timing accordingly shifts.
  • this pressure chamber is depressurized, so that the end face of the Cold start acceleration piston immersed in this.
  • the side facing away from the face of the cold-start acceleration piston acts as a sliding support surface for the spring-sleeve combination of the trailing piston.
  • the cold start acceleration piston in turn is adjusted by the pressure in the pressure chamber of the cold start acceleration unit.
  • the pressure chamber is the start or during the cold running phase of the internal combustion engine empty and is only filled at the start of the warm-up phase of the internal combustion engine. This increases the pressure in the pressure chamber, which shifts the cold-start acceleration piston such that the trailing piston / control slide takes its normal position and the Injection start is withdrawn from early.
  • a load-dependent Start of funding shift (LFB function).
  • This function is, for example, a Ring groove switched.
  • this external control switched off i.e. e.g. formed as a groove or a corresponding hole remains closed.
  • the load-dependent start of delivery function can be switched on because the internal pressure inside the Distributor injection pump increases. The control of the load-dependent Start of funding is shifted when the opening is open.
  • Fig. 1 shows the side view of the injection distributor pump with flanged Adjustment unit for the injection adjuster piston.
  • FIG. 1 shows an injection distributor pump
  • the Housing 1 is shown in side view.
  • an adjustment unit 2 is flanged to shift the start of injection. This is with flange screws 7 and 8 on the side of the housing 1 of the injection distributor pump attached.
  • the adjustment unit 2 for shifting the start of injection is assigned an actuator in the form of an electromagnet 3.
  • a connecting line 9 for controlling the load-dependent shift start function provided with a Banjo bolt 10 attached to the top of the housing 1 of the injection distributor pump is.
  • the interaction of the Annular groove 16.1 of the cold start acceleration piston 12 with the housing bore 16.2, allows an LFB function to be provided without external circuitry on the adjustment unit 2 to shift the start of injection.
  • the LFB function depending on the operating state of the self-igniting internal combustion engine, i.e. switch off in the cold state and switch on in the heated state without a externally operated external circuit would be required.
  • Fig. 3 can be seen that the housing 1 of the injection distributor pump and the housing the adjustment unit 2 to shift the start of injection to a structural unit are summarized. At a joint extending in the vertical direction, the Sealing of the housing 1 or 2 achieved via a sealing plate 25.
  • An actuator in the form of an electromagnet 3 is arranged at the start of injection. This allows pressure relief of the pressure chamber 11 of the adjustment unit 2 for displacement the start of injection via a relief bore 31 shown here in dashed lines.
  • the injection adjuster piston 17 comprises, for example, two at an angle to one another oriented inlet holes.
  • a rotatably mounted insert is formed in the injection adjuster piston 17 with which in a displacement movement of the injection adjuster piston 17 in Housing 1 of the injection distributor pump bearing ring with regard to the start of injection between early and late depending on the operating condition of the auto-igniting Internal combustion engine is adjustable.
  • a Cold start acceleration piston 12 slidably mounted in the housing of the adjustment unit 2 for shifting the start of injection.
  • the end face 13 of the Cold start acceleration pistons on the one hand and the inside of the housing of the Adjustment unit 2 for shifting the start of entry adjoins a pressure chamber 11.
  • the pressure chamber, on the one hand, through the inside of the cold start acceleration piston 12 and on the other hand is limited by the end face of the injection adjuster piston 17 depressurized.
  • a branch of this pressure chamber e.g. opening 16 provided as a groove which, when closed, has an external control, e.g. the LFB function switches off, but when the distributor injection pump is warmed up, the LFB function connecting them; If the LFB function is activated, e.g. opening designed as a groove 16 open.
  • the support ring 15 is - preferably via fasteners Insert screws - identified by reference number 23 in the housings screwed and fixed in place.
  • On the second stop surface 13.2 on the inside of the Cold start acceleration piston 12 is supported by a spring / sleeve combination 19.
  • the Spring / sleeve combination comprises a sleeve 19.1 and one received on it Spring element 19.2.
  • the spring element 19.2 is supported on the one hand on a first one Stop ring 19.3 of the spring / sleeve combination 19 and on the other hand at one of the first Stop ring 19.3 opposite slotted disc 20.
  • the slotted disc 20 in turn lies on the bottom surface of a recess on an end face of the Injection adjuster piston 17.
  • the first stop ring 19.3 of the sleeve 19.1 Spring / sleeve combination 19 lies on the second stop surface 13.2 of the Cold start acceleration piston 12 and is acted upon by the spring element 19.2.
  • the follower piston / control slide 24 is also connected via a follower piston spring 21 a spring force is applied, the trailing piston spring 21 on one of the third contact surface 13.1 of the cold start acceleration piston 12 supporting ring 22 supported.
  • the trailing piston / control slide 24 is in turn from a channel system pulled through, which has a transverse bore 26 and a connection with this Includes longitudinal bore 28 with diameter gradation.
  • Electromagnetically designed actuator 3 When a self-igniting internal combustion engine starts cold, the is as Electromagnetically designed actuator 3 is preferably switched so that the pressure chamber 11 the actuating unit 2 is depressurized to shift the start of injection.
  • the the Apply cold start acceleration piston 12 to contact surfaces 13.1 and 13.2 Spring elements 14 and 19.2 therefore have no counterforce across the pressure chamber 11 opposite, so that the spring elements mentioned can take their rest position.
  • This is due to the relaxing spring element 19.2 of the spring / sleeve combination 19 and the sleeve 19.1 cooperating with these Trailing piston / control slide 24 on its support plate 27 through the second Stop ring 19.4 of the sleeve 19.1 moved so that the inlet bores with the Channel system 26 or 28 inside the follower piston / control slide 24 in Connect.
  • the injection distributor pump is adjusted so that it closes an early start of fuel injection into the individual combustion chambers of the self-igniting internal combustion engine comes. This allows the Particle emission or the noise development when starting a self-igniting Internal combustion engine and in the subsequent cold running phase considerably decrease.
  • the internal combustion engine and the engine heat up with increasing operating time Distributor injection pump.
  • the Solenoid valve 3 and thereby an inflow of fluid into the pressure chamber 11, whereby it in the pressure chamber 11 there is an increase in pressure, the pressure directly on the end face 13 of the cold-start acceleration piston 12 acts and counteracts the pressure force in applied to its cavity.
  • the external control of a load-dependent delivery start shift described above which by opening or closing a groove or a bore 16 can be done, is mentioned as an example of a function that depends on itself setting operating state of the self-igniting internal combustion engine without to require external wiring, can be controlled.
  • the one with the Realization of components connected as described above, e.g. Drain hole 16, the connection pipe 9 and overflow of the fluid the banjo bolt 10 receiving the connecting pipe are only mentioned by way of example and have no influence on the function of the cold start acceleration piston 12.

Landscapes

  • 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)
EP02022593A 2001-11-16 2002-10-09 Pompe à injection à accélération de démarrage à froid pour moteurs à combustion interne à injection directe Expired - Lifetime EP1312782B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10156338A DE10156338B4 (de) 2001-11-16 2001-11-16 Einspritzpumpe mit Kaltstartbeschleunigung für direkteinspritzende Verbrennungskraftmaschinen
DE10156338 2001-11-16

Publications (3)

Publication Number Publication Date
EP1312782A2 true EP1312782A2 (fr) 2003-05-21
EP1312782A3 EP1312782A3 (fr) 2005-05-18
EP1312782B1 EP1312782B1 (fr) 2008-08-06

Family

ID=7705997

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02022593A Expired - Lifetime EP1312782B1 (fr) 2001-11-16 2002-10-09 Pompe à injection à accélération de démarrage à froid pour moteurs à combustion interne à injection directe

Country Status (3)

Country Link
US (1) US6792922B2 (fr)
EP (1) EP1312782B1 (fr)
DE (2) DE10156338B4 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7350508B1 (en) * 2006-10-12 2008-04-01 Delphi Technologies, Inc. Advance arrangements

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4037574A (en) * 1976-05-21 1977-07-26 Stanadyne, Inc. Timing control for fuel injection pump
US4408591A (en) * 1980-11-15 1983-10-11 Diesel Kiki Co., Ltd. Injection timing control device for distributor-type fuel injection pumps
US4610234A (en) * 1984-06-12 1986-09-09 Diesel Kiki Co., Ltd. Injection timing control device for distributor-type fuel injection pumps
US4798189A (en) * 1986-09-09 1989-01-17 Lucas Industries Public Limited Company Fuel injection pump
US5647327A (en) * 1995-04-07 1997-07-15 Nippon Soken, Inc. Injection timing control device for fuel injection pump

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3897764A (en) * 1973-05-18 1975-08-05 Cav Ltd Liquid fuel injection pumping apparatus
DE2716307A1 (de) * 1977-04-13 1978-10-19 Volkswagenwerk Ag Kraftstoff-einspritzpumpe fuer eine selbstzuendende brennkraftmaschine
JPS60259732A (ja) * 1984-05-09 1985-12-21 Diesel Kiki Co Ltd 分配型燃料噴射ポンプの噴射時期調整装置
GB9226669D0 (en) * 1992-12-22 1993-02-17 Lucas Ind Plc Fuel pump
DE19849925A1 (de) * 1998-10-29 2000-05-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4037574A (en) * 1976-05-21 1977-07-26 Stanadyne, Inc. Timing control for fuel injection pump
US4408591A (en) * 1980-11-15 1983-10-11 Diesel Kiki Co., Ltd. Injection timing control device for distributor-type fuel injection pumps
US4610234A (en) * 1984-06-12 1986-09-09 Diesel Kiki Co., Ltd. Injection timing control device for distributor-type fuel injection pumps
US4798189A (en) * 1986-09-09 1989-01-17 Lucas Industries Public Limited Company Fuel injection pump
US5647327A (en) * 1995-04-07 1997-07-15 Nippon Soken, Inc. Injection timing control device for fuel injection pump

Also Published As

Publication number Publication date
EP1312782B1 (fr) 2008-08-06
EP1312782A3 (fr) 2005-05-18
US6792922B2 (en) 2004-09-21
US20030116139A1 (en) 2003-06-26
DE50212595D1 (de) 2008-09-18
DE10156338A1 (de) 2003-06-05
DE10156338B4 (de) 2005-05-04

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