EP0323591A2 - Dispositif de réglage de l'injection à 2 points - Google Patents

Dispositif de réglage de l'injection à 2 points Download PDF

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Publication number
EP0323591A2
EP0323591A2 EP88120941A EP88120941A EP0323591A2 EP 0323591 A2 EP0323591 A2 EP 0323591A2 EP 88120941 A EP88120941 A EP 88120941A EP 88120941 A EP88120941 A EP 88120941A EP 0323591 A2 EP0323591 A2 EP 0323591A2
Authority
EP
European Patent Office
Prior art keywords
control
hydraulic tappet
check valve
line
piston
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.)
Withdrawn
Application number
EP88120941A
Other languages
German (de)
English (en)
Other versions
EP0323591A3 (fr
Inventor
Albert Nolte
Toni Kleinschmidt
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz AG
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 Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Publication of EP0323591A2 publication Critical patent/EP0323591A2/fr
Publication of EP0323591A3 publication Critical patent/EP0323591A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • 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
    • 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
    • F02M59/30—Varying fuel delivery in quantity or timing with variable-length-stroke 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 two-point spray adjuster according to the preamble of claim 1.
  • a spray adjustment is required in slow-running industrial and truck diesel engines essentially to reduce noise during acceleration and to improve exhaust after the cold start, the adjustment when accelerating simultaneously with the adjustment of the injection pump control rod, i. H. very quickly, should be done. Injection systems with electromagnetic control of the injection times are too expensive and not yet ready for series production.
  • EP-A 0 017 413 describes a two-point spray adjuster for variation of the forward stroke in the form of a controllable hydraulic tappet which is intended for use with open pump nozzles.
  • the pump plunger serves to deliver the fuel and at the same time serves as a closing element for the spray holes. For this reason, it is conical on its delivery side, the cone as a sealing cone at the end of the delivery stroke being seated firmly on the appropriately designed sealing surface in the injection valve body.
  • This arrangement requires exact compliance with the plunger stroke, since if the plunger stroke is exceeded the tip of the injection valve is destroyed and when the plunger stroke is undershot, combustion gases can penetrate into the delivery chamber of the pump nozzle and contaminate it. Advancing the injection timing by reducing the advance stroke is therefore only possible with this type of pump nozzle if it is ensured that the contact force of the pump plunger at the end of the delivery stroke does not exceed a permissible value.
  • a safety valve is provided in the hydraulic tappet according to EP-A 0 017 413, which responds after the hydraulic tappet has been adjusted prematurely if the permissible oil pressure is exceeded and thereby avoids overstressing the pump nozzle.
  • the hydraulic tappet is compressed again to its initial length, from which it is pumped up to a greater or lesser extent before each delivery stroke, depending on the control oil pressure.
  • An advantage of this solution is that a pre-stroke and thus a spray adjustment from stroke to stroke is possible, which is a prerequisite for avoiding the acceleration noise, especially when accelerating the diesel engine.
  • a disadvantage of this solution is that the working piston in the hydraulic tappet is moved frequently, which promotes its wear.
  • the invention has for its object to develop a generic, controllable two-point spray adjuster such that the working piston in the hydraulic tappet must be moved as rarely as possible and still a spray adjustment from stroke to stroke remains possible.
  • the working piston of the hydraulic tappet according to the invention is only adjusted when the pressure of the control fluid changes in accordance with the changing engine and operating parameters. As a result, the working piston is subject to practically no wear.
  • the arrangement according to claim 2 allows rapid relief of the hydraulic tappet due to the small required stroke of the control piston to open the check valve. This ensures an injection adjustment effective from injection stroke to injection stroke, which effectively reduces the acceleration noise of the diesel engine.
  • control slide described in claims 3 and 4 is characterized by a simple structure and achieves the desired control functions according to the invention with purely mechanical means.
  • the arrangement according to claim 5 allows a spray adjustment depending on the lubricating oil temperature. As a result, when the engine is warming up, it is one for low Hydrocarbon and carbon dioxide emissions secured the desired early adjustment of the start of production.
  • the arrangement according to claim 8 offers, in particular for internal combustion engines with electronic control and the motor and operating parameter detection required for this, the advantage of controlling the two-point spray adjuster as a function of all these parameters with only little additional effort.
  • the hydraulic tappet 1 shown in FIG. 1 has a tappet bushing 2 in which a working piston 3 is located.
  • the working piston 3 is acted upon by a compression spring 14, which is supported on a check valve carrier 4, which in turn rests in the tappet bushing 2 on a shoulder 2a.
  • the working piston 3 can move back and forth between a snap ring 13 and the check valve carrier 4.
  • Ram sleeve 2, working piston 3 and check valve carrier 4 enclose a pressure chamber 23 which can be filled with oil via a check valve 25.
  • a bore 27 which is controlled by the check valve 25.
  • the check valve 25 consists of the valve cage 18, which is pressed by the compression spring 14 onto the check valve carrier 4, the compression spring 19 and the valve ball 20, which is pressed onto its seat by the compression spring 19.
  • the control piston 6 has a central extension 21, the diameter of which is smaller than the diameter of the bore 27 in the check valve carrier 4 and the length of the closed valve Check valve 25 with little play up to the valve ball 20 extends when the control piston 6 is at the stop 26.
  • Tappet sleeve 2 check valve carrier 4 and control piston 6 delimit an oil chamber 6a, which is supplied with pressure oil from the oil line 16 via the bore 15, the oil groove 17 and the inlet bore 17a.
  • the control piston 6 is acted on its underside by a control spring 7, which is located in the spring chamber 7a, which is provided with a drain hole 22.
  • a tappet roller 8 which is mounted on a bearing pin 9.
  • a bumper 17 is arranged, which transmits the plunger forces to the injection pump, which is provided as a single injection pump for each cylinder.
  • the hydraulic tappet 1 is in the position of the smallest forward stroke of the injection pump, ie. H. shown with early start of funding.
  • the working piston 3 and control piston 6 are in their outer dead position, i.e. Working piston 3 rests on snap ring 13 and control piston 6 on stop 26.
  • FIG. 2 shows a control unit 27a which consists of a control housing 28 and a control slide 29.
  • the control slide 29 can be located in the control housing 28 move back and forth in a hole 28 a, which is provided with control grooves 41 and 42. It consists of an outer slide part 33 with the control bores 34, 35 and the drain bores 36 and the inner slide part 37 with the control bores 38, the control groove 39 and the throttle bore 40.
  • the inner slide part 37 which is pressed by a compression spring 43 against a snap ring 37a is, can move relative to the outer slide part 33.
  • the control slide 29 is actuated by a speed adjusting lever 32, which is connected to an adjusting cam 32a and sits on a common shaft 56 with the latter.
  • control housing 28 there is the pressure line 30, from which the branch 44 and the inflow line 47 branch off.
  • a check valve 45 is arranged in the branch line 44 and opens towards the oil chamber 46.
  • control housing 28 there is also an outflow bore 50 which leads to a thermostat 51 which controls a valve 53.
  • a compression spring 52 which is supported on a cover 54, presses on the valve 53.
  • FIG. 3 shows a simple version of the control unit 27a.
  • the outer slide part 33 is only provided with the control holes 35 and the drain holes 36.
  • the drain holes 36 open directly into the housing space 55, since the thermostat 51 with the valve 53 is missing in this version.
  • the inner slide part 37 is shown in FIG. 3, with one half resting against the snap ring 37a, with the other half at a distance from the snap ring 37a.
  • FIG. 4 shows a further, simplified version of the control unit 27a, in which the outer slide part 33 is provided with the control bores 34, 35 and the drain bore 36.
  • FIG. 4 shows the control slide 29 and the speed adjustment lever 32 with the adjustment cam 32a in two different positions, which correspond to different engine speeds.
  • the two-point spray adjuster works as follows:
  • the control liquid preferably lubricating oil, passes from the control unit 27a via the control line 31, the oil line 16, the bore 15, the oil groove 17 and the bore 17a into the oil space 6a of the hydraulic tappet 1.
  • control piston 6 If the control oil pressure drops in the control oil line 31 and consequently also in the oil space 6a, the control piston 6 is pressed under the action of the control spring 7 against the spacers 5, as a result of which the extension 21 of the control piston 6 pushes open the valve ball 20 of the check valve 25.
  • the working piston 3 is pressed against the force of the compression spring 14 against the stop 24, the oil from the pressure chamber 23 passing through the open check valve 25 into the oil chamber 6a, from where it passes between the spacers 5 and through the bore 17a flows off.
  • the oil pressure is controlled by means of the control unit 27a.
  • the control oil is supplied to the control unit 27 a through the pressure line 30. From there it reaches the control line 31 via the inflow line 47, the throttle 48 and the control groove 41.
  • the control line 31 leads to the oil line 16 and thus to the hydraulic tappet 1.
  • the function of the control spool 29 shown in FIG. 3 will be explained.
  • the position of the control slide 29 is determined by the position of the speed adjustment lever 32 and the adjustment cam 32a connected to it.
  • the location of the interior Slider part 37 also depends on the oil pressure of the oil space 46.
  • the oil chamber 46 which is connected to the pressure line 30 via the check valve 45, the oil pressure of the pressure line 30 prevails when the control slide 29 is at a standstill.
  • the inner slide part 37 is pressed by the compression spring 43 against the snap ring 37a into the position "A" . In position "A", the inner slide part 37 closes off the control bores 35.
  • control slide 29 differs from that according to FIG. 3 by the additional control bores 34 in the outer slide part 33.
  • the control bores 34 are mounted in such a way that they then overlap with the control groove 39 and the control bore 38 of the inner slide part 37 are when the inner slide member 37 abuts the snap ring 37a. Oil is drained from the control line 31 and thus the start of delivery is adjusted to "late” when the control bore 34 overlaps with the control groove 41. This state occurs when the control slide 29 is in position "A" in FIG. H. is in the range of low engine speeds. At higher engine speeds, the spool 29 is moved in the direction "B".
  • control slide 29 complements the thermostat 51 with the valve 53 in the outflow line 50.
  • the valve 53 remains closed and thereby blocks the outflow of the control oil from the control unit 27a.
  • a high control pressure remains in the control oil line 31, which results in the early start of delivery, as is desirable for emission reasons when the engine is cold.
  • the two-point spray adjuster according to the invention thus enables the desired "early” or “late” adjustment of the start of delivery for important operating states of an internal combustion engine, such as warming up, accelerating, low and high speed.
  • the start of delivery is only fixed in two positions by the two-point spray adjuster according to the invention, but these positions are reached quickly and are observed with close tolerances in all cylinders.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
EP88120941A 1987-12-17 1988-12-15 Dispositif de réglage de l'injection à 2 points Withdrawn EP0323591A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873742831 DE3742831A1 (de) 1987-12-17 1987-12-17 Zweipunkt-spritzversteller
DE3742831 1987-12-17

Publications (2)

Publication Number Publication Date
EP0323591A2 true EP0323591A2 (fr) 1989-07-12
EP0323591A3 EP0323591A3 (fr) 1989-10-25

Family

ID=6342849

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88120941A Withdrawn EP0323591A3 (fr) 1987-12-17 1988-12-15 Dispositif de réglage de l'injection à 2 points

Country Status (2)

Country Link
EP (1) EP0323591A3 (fr)
DE (1) DE3742831A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5094215A (en) * 1990-10-03 1992-03-10 Cummins Engine Company, Inc. Solenoid controlled variable pressure injector
EP0676538A2 (fr) * 1994-04-05 1995-10-11 Cummins Engine Company, Inc. Dispositif de poussoir de commande de l'instant d'injection des moteurs à combustion interne
US5655501A (en) * 1996-05-09 1997-08-12 Caterpillar Inc. Rate shaping plunger/piston assembly for a hydraulically actuated fuel injector
WO2018053892A1 (fr) * 2016-09-22 2018-03-29 西华大学 Poussoir de soupape variable

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10052073B4 (de) * 2000-10-19 2005-04-07 Deutz Ag Förderbeginn-Verstellung

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB406383A (en) * 1931-09-03 1934-03-01 Bendix Aviat Corp Improvements in method and means for controlling the burning of fuel in internal combustion engines
US3951117A (en) * 1974-05-30 1976-04-20 Cummins Engine Company, Inc. Fuel supply system for an internal combustion engine
EP0017413A1 (fr) * 1979-03-23 1980-10-15 Eaton Corporation Système d'injection de carburant et dispositif de réglage de l'avance de l'injection pour un tel système
US4249499A (en) * 1980-01-21 1981-02-10 Cummins Engine Company, Inc. Timing mechanism for a fuel supply system
US4337739A (en) * 1980-03-24 1982-07-06 Jordan Edgar R Valve control mechanism for internal combustion engines
EP0070222A1 (fr) * 1981-07-13 1983-01-19 The Bendix Corporation Injecteur controlé par le temps et la pression
GB2155560A (en) * 1984-03-14 1985-09-25 Bosch Gmbh Robert A fuel injection pump for internal combustion engines
JPS6166811A (ja) * 1984-09-07 1986-04-05 Odai Tekko Kk 内燃機関における休止機能付動弁機構
FR2584773A1 (fr) * 1985-07-15 1987-01-16 Peugeot Dispositif de commande variable d'une soupape de moteur a combustion interne

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE889092C (de) * 1939-02-18 1953-09-07 Friedrich Wilhelm Deckel Dipl Einrichtung zur selbsttaetigen Spritzbeginnverstellung an Einspritzpumpen fuer Brennkraftmaschinen
DE1107025B (de) * 1956-07-09 1961-05-18 Napier & Son Ltd Kraftstoffeinspritzpumpe mit UEberstroemregelung fuer Brennkraftmaschinen
US2997994A (en) * 1959-12-07 1961-08-29 Gen Motors Corp Fuel injection apparatus
US3859973A (en) * 1971-12-27 1975-01-14 Allis Chalmers Timing device for fuel injector
MX146686A (es) * 1976-12-30 1982-07-28 Cummins Engine Co Inc Aparato para variar la regulacion de la inyeccion de combustible de un motor de combustion interna
DE3141653A1 (de) * 1981-10-21 1983-05-05 L'Orange GmbH, 7000 Stuttgart Kraftstoffeinspritzpumpe, insbesondere fuer eine dieselbrennkraftmaschine
DE3510223A1 (de) * 1985-03-21 1986-10-02 Daimler-Benz Ag, 7000 Stuttgart Hydraulische verstelleinrichtung zur beeinflussung des einspritzbeginns einer fuer selbstzuendende brennkraftmaschinen vorgesehenen einspritzpumpe

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB406383A (en) * 1931-09-03 1934-03-01 Bendix Aviat Corp Improvements in method and means for controlling the burning of fuel in internal combustion engines
US3951117A (en) * 1974-05-30 1976-04-20 Cummins Engine Company, Inc. Fuel supply system for an internal combustion engine
EP0017413A1 (fr) * 1979-03-23 1980-10-15 Eaton Corporation Système d'injection de carburant et dispositif de réglage de l'avance de l'injection pour un tel système
US4249499A (en) * 1980-01-21 1981-02-10 Cummins Engine Company, Inc. Timing mechanism for a fuel supply system
US4337739A (en) * 1980-03-24 1982-07-06 Jordan Edgar R Valve control mechanism for internal combustion engines
EP0070222A1 (fr) * 1981-07-13 1983-01-19 The Bendix Corporation Injecteur controlé par le temps et la pression
GB2155560A (en) * 1984-03-14 1985-09-25 Bosch Gmbh Robert A fuel injection pump for internal combustion engines
JPS6166811A (ja) * 1984-09-07 1986-04-05 Odai Tekko Kk 内燃機関における休止機能付動弁機構
FR2584773A1 (fr) * 1985-07-15 1987-01-16 Peugeot Dispositif de commande variable d'une soupape de moteur a combustion interne

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Band 10, Nr. 234 (M-507)(2290), 14. August 1986; & JP-A-61 066 811 (ODAI TEKKO K.K.) 05-04-1986 *

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5094215A (en) * 1990-10-03 1992-03-10 Cummins Engine Company, Inc. Solenoid controlled variable pressure injector
USRE37241E1 (en) 1990-10-03 2001-06-26 Cummins Engine Company, Inc. Solenoid controlled variable pressure injector
EP0676538A2 (fr) * 1994-04-05 1995-10-11 Cummins Engine Company, Inc. Dispositif de poussoir de commande de l'instant d'injection des moteurs à combustion interne
EP0676538A3 (fr) * 1994-04-05 1997-08-13 Cummins Engine Co Inc Dispositif de poussoir de commande de l'instant d'injection des moteurs à combustion interne.
US5655501A (en) * 1996-05-09 1997-08-12 Caterpillar Inc. Rate shaping plunger/piston assembly for a hydraulically actuated fuel injector
WO2018053892A1 (fr) * 2016-09-22 2018-03-29 西华大学 Poussoir de soupape variable
GB2568621A (en) * 2016-09-22 2019-05-22 Univ Xihua Variable valve tappet
GB2568621B (en) * 2016-09-22 2019-10-09 Univ Xihua Variable valve tappet

Also Published As

Publication number Publication date
DE3742831A1 (de) 1989-07-13
EP0323591A3 (fr) 1989-10-25

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