EP0916017B1 - Vorrichtung zur unterbrechung der kraftstoffversorgung - Google Patents

Vorrichtung zur unterbrechung der kraftstoffversorgung Download PDF

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Publication number
EP0916017B1
EP0916017B1 EP97938877A EP97938877A EP0916017B1 EP 0916017 B1 EP0916017 B1 EP 0916017B1 EP 97938877 A EP97938877 A EP 97938877A EP 97938877 A EP97938877 A EP 97938877A EP 0916017 B1 EP0916017 B1 EP 0916017B1
Authority
EP
European Patent Office
Prior art keywords
internal combustion
combustion engine
pressure
diaphragm
connection
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
EP97938877A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0916017A1 (de
Inventor
Günter Kampichler
Albert Madl
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.)
Motorenfabrik Hatz GmbH and Co KG
Original Assignee
Motorenfabrik Hatz GmbH and Co KG
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 Motorenfabrik Hatz GmbH and Co KG filed Critical Motorenfabrik Hatz GmbH and Co KG
Publication of EP0916017A1 publication Critical patent/EP0916017A1/de
Application granted granted Critical
Publication of EP0916017B1 publication Critical patent/EP0916017B1/de
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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/18—Indicating or safety devices
    • F01M1/20—Indicating or safety devices concerning lubricant pressure
    • F01M1/22—Indicating or safety devices concerning lubricant pressure rendering machines or engines inoperative or idling on pressure failure
    • F01M1/24—Indicating or safety devices concerning lubricant pressure rendering machines or engines inoperative or idling on pressure failure acting on engine fuel system
    • 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 present invention relates to an internal combustion engine, especially with a single cylinder diesel engine Fuel injection system, in which for automatic Interruption of fuel supply at Lack of lubricating oil a mechanical safety device is provided.
  • a sharp drop in oil pressure in internal combustion engines is generally by lowering the oil level in the oil pan, due to blockage of the oil filter, due to defective oil pump or clogging or leakage in the oil circuit.
  • the associated lack of lubricating oil to the Bearing points lead to serious problems within a very short time Damage to the engine leading to complete Destruction of the same.
  • the Oil pressure often on the corresponding display devices Engine operator displayed there is usually a change of the Pressure signal into an electrical signal, which the Display device supplied and e.g. into a mechanical Movement of a pointer is converted.
  • the sensors and the displays are therefore susceptible to malfunction.
  • Another is the quick reaction of the operator Prerequisite for that by switching off the internal combustion engine greater damage to the same is avoided.
  • a negative pressure in the control element can be in be generated in such a way that on the oil circuit side Connection lubricating oil is sucked in, that on the crankcase side Connection due to the in the crankcase prevailing flow and pressure conditions in the Crankcase emerges.
  • an oscillating, pneumatic pressure generated In the crankcase an oscillating, pneumatic pressure generated. This is influenced pneumatic internal pressure from the selected ventilation system and the blowing volume.
  • pressurized oil is a variant possible with pressurized oil. With both variants lack of lubricating oil leads to a change in pressure in the Control line and a controlled fuel cut by the actuator.
  • this Actuator of the control circuit with a vacuum can Membrane for pressurizing a plunger on, being formed by a membrane and vacuum box Pressure chamber is open to the atmosphere.
  • the fuel injection system a fuel injection pump with suction hole, wherein the plunger to close the suction hole is provided.
  • An advantageous embodiment of the invention provides before that the plunger firmly with the membrane connected is.
  • the return spring on the opposite side of the membrane acts on a printing plate. This seals at the same time the fuel area against the negative pressure area.
  • the pressure plate enables one of the spring form adapted recess a fixation of the spring, what a good guidance and exact calculation of the membrane acting spring force, since the forces always be introduced vertically.
  • Closure plunger The formation of a self-centering is also expedient Closure plunger.
  • the plunger can for example be made of elastic Plastic or be designed as a coil spring and a hemispherical or conical one Have valve body, so that the plunger directly in front of the suction hole of the fuel injection pump centered.
  • This measured in the area between the two chokes Pressure is decoupled from the oil pressure of the oil circuit and is always significantly lower in level than this. If the oil pressure between the first and the second throttle drops above a limit value, result from the superimposition of the pneumatic Vacuum peaks resulting pressure values that also have negative pressure peaks. This signal is used in the control loop to trigger the interruption of the Fuel supply needed.
  • Control element one at one end with the vacuum box connected line for evacuating and venting the Pressure chamber is arranged.
  • This line is on theirs check valve with the other end Control line and further via a ventilation throttle associated with the atmosphere.
  • the vacuum peaks already mentioned open in each case the check valve for a short time. This takes one Pressure equalization between the one connected to the line Pressure chamber of the vacuum box and the control line instead of. This leads to a vacuum in the vacuum box.
  • the constant negative pressure in one pressure chamber and the atmospheric pressure in the other pressure chamber cause the plunger over the Membrane is moved in the direction of the suction hole, until he closes it. So that the fuel supply to the injection pump interrupted, causing the engine is turned off.
  • the ventilation throttle enables after the engine stops the return spring resets the membrane and brings the locking plunger back on standby. Because through this throttle even if the parking device comes into action, air is sucked in and the build-up of vacuum in the vacuum can is affected, the diameter of the throttle must the system must be tuned. Influencing factors can the crankcase volume, the dead volume Pipe, the membrane volume and the ventilation system his. By adding a filter, you can the entry of dirt can be prevented.
  • the present invention provides an evacuation device for manual evacuation of the vacuum side the membrane is provided. This can during the start-up phase, i.e. if not yet there is sufficient oil pressure in the vacuum box, by manual actuation of the evacuation device the engine is ready to start by a brief manipulation of the interruption device is made. For this, an additional Vacuum generated in the vacuum can.
  • FIG. 1 schematically shows a fuel injection pump 1 with a fuel supply line 2 and one Fuel return line 3, each one Connection to intake duct 4 with intake bore 5 and the suction hole attachment 6.
  • the pressure plate 7 is a perfect fit and through the O-ring seal 8 arranged sealed against negative pressure. Furthermore, there is an O-ring seal 9 within the Pressure plate 7 for sealing the plunger 10 with his hemispherical sealing head 11 is provided.
  • the plunger 10 is form-fitting with one arranged centrally on the membrane 12 Pressure plate 13 connected. Between the pressure plate 7 and the pressure plate 13 is a coil spring executed return spring 14 arranged by a cylindrical depression in the pressure plate 7 is guided laterally.
  • the membrane 12 divides the Vacuum can 15 in an open to the atmosphere Pressure chamber 16 and one via line 17 with the Control line 18 connected second pressure chamber 19.
  • Die Control line 18 has an oil circuit side Connection 20 with subsequent choke 21 and one crankcase-side connection 22 with preceding Throttle 23 on.
  • the line 17 has at its lower End a connection 24 to the pressure chamber 19 of the vacuum box 15 on.
  • line 17 a branch 25 with a throttle 26, one for Atmosphere open openings 27 and one in front arranged filter 28 on.
  • a check valve 30 before Connection 29 of line 17 is a check valve 30 arranged, which is pressurized by a spring 31 Ball valve body 32 and a valve seat 33 exists.
  • Fig. 1 In the control loop shown in Fig. 1 is a very low partial flow of the lubricating oil circuit branches off and flows through the control line 18.
  • the on Port 20 entering oil flow flows through throttle 21 and the downstream throttle 23 and occurs at port 22 in the crankcase.
  • throttle 21 and Throttle 23 By appropriate Matching the cross sections of throttle 21 and Throttle 23 is reached that the pressure between Throttle 21 and throttle 23 only to a small extent from the Oil viscosity and the delivery rate of the oil pump at one pressure controlled oil supply system depends.
  • This decoupled pressure lies between the two throttles always significantly lower in level than that in the oil pressure circuit.
  • FIG. 2 shows another embodiment of the present Invention. This is instead of Fig. 1 instead the throttle 23 a valve 35 is provided.
  • the valve 35 has a cylindrical housing 36, on the A helical spring 38 supported.
  • the first spring 38 presses on a valve plate 39, facing away from the first spring 38 Side pressurized by a second spring 40 becomes.
  • the second spring 40 in turn is based on hers other end on another valve plate 41.
  • the valve 35 leaves per upward stroke movement of the engine piston only a small amount of air in Flow towards the crankcase by the valve plate 41 is lifted off the pipe opening 42.
  • the Airflow is directed toward the first valve plate 39 the second valve opening 43 moves and closes the Flow path to the crankcase.
  • the negative pressure from the This can cause the crankcase during this suction stroke do not get further to the membrane of the vacuum box.
  • the opening pressure of the ball valve 45 is approximately 0.2 up to 0.5 bar. Only after several strokes of the The vacuum can is evacuated piston (approx. 50 strokes) and via membrane 12, plunger 10 and closure body 11 becomes the fuel supply to the injection pump interrupted. If the functions of the Lubrication system is however after several revolutions (e.g.
  • valve 35 serves primarily to ensure that the engine does not start immediately again because of the oil pressure not yet available is turned off automatically. This will do so achieved that with a stroke movement of the engine piston not the entire volume of the vacuum can at once is evacuated, but gradually.
  • FIG. 3 schematically shows a further embodiment of the present invention.
  • another rubber bellows 65 with check valve 67 as well Ventilation throttle 69 shown as a manual Evacuation device of the vacuum membrane chamber 71 serves.
  • the oil pressure on the membrane 58 on the one hand and a compression spring 59 on the other hand actuates the Valve stem.
  • the valve tappet from the corresponding pressure in the Vacuum can against the force of the compression spring in the drawn position held.
  • the oil pressure drops moves below a required minimum Compression spring the valve body over the valve lifter in Direction suction hole 64 of the pump element 63, so that the Fuel supply to the injection pump is interrupted and the engine is switched off automatically.
  • Fig. 4 shows an embodiment of a hand-operated 3 in section.
  • the Rubber bellows 65 the compression spring 66 and a check valve 67 shown.
  • a base part is also 80 shown, which on the one hand at its upper end receives the spring 66 and one on its outer circumference provides firm and tight hold for the rubber bellows 65.
  • the base part 80 points in its longitudinal direction a bore 81 on the bottom of the Base part opens into a pressure hose 68.
  • the Pressure hose 68 is in turn with the second pressure chamber 71 connected to the vacuum box.
  • FIG. 5 shows detail V from FIG. 4. It concerns around the check valve opening of valve 67, the can simultaneously serve as a throttle 68.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP97938877A 1996-08-05 1997-08-05 Vorrichtung zur unterbrechung der kraftstoffversorgung Expired - Lifetime EP0916017B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19631652A DE19631652A1 (de) 1996-08-05 1996-08-05 Automatische Unterbrechung der Kraftstoffversorgung
DE19631652 1996-08-05
PCT/EP1997/004261 WO1998005852A1 (de) 1996-08-05 1997-08-05 Vorrichtung zur unterbrechung der kraftstoffversorgung

Publications (2)

Publication Number Publication Date
EP0916017A1 EP0916017A1 (de) 1999-05-19
EP0916017B1 true EP0916017B1 (de) 2002-03-27

Family

ID=7801880

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97938877A Expired - Lifetime EP0916017B1 (de) 1996-08-05 1997-08-05 Vorrichtung zur unterbrechung der kraftstoffversorgung

Country Status (5)

Country Link
US (1) US6085716A (ja)
EP (1) EP0916017B1 (ja)
JP (1) JP2001508145A (ja)
DE (2) DE19631652A1 (ja)
WO (1) WO1998005852A1 (ja)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1141531B1 (de) * 1999-01-08 2002-10-02 Siemens Aktiengesellschaft Verfahren zur wiederinbetriebnahme eines zylinders einer mehrzylindrigen brennkraftmaschine
ITTO20010980A1 (it) * 2001-10-16 2003-04-16 Lombardini Srl A Socio Unico Impianto di alimentazione del combustibile per un motore ad iniezione.
US7992541B2 (en) 2006-03-14 2011-08-09 Ford Global Technologies, Llc System and method for controlling auto-ignition
CN100447376C (zh) * 2006-08-10 2008-12-31 江苏常发实业集团有限公司 断油保护器
US8066032B2 (en) * 2007-11-21 2011-11-29 Diversatech, Inc. Apparatus for instantaneously terminating movement of flow material through a conduit
US10443457B2 (en) * 2015-12-11 2019-10-15 Miguel Alfonso POTOLICCHIO Lubrication control in internal combustion engines

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB142049A (en) * 1919-11-22 1920-04-29 Thomas Watson Paterson Improvements in liquid fuel feed controlling devices for internal combustion engines
US2582483A (en) * 1947-03-13 1952-01-15 Theodore W Hallerberg Pressure sensitive switch
US3176672A (en) * 1961-11-02 1965-04-06 Gen Motors Corp Low oil pressure sensitive engine governor
GB1136761A (en) * 1964-12-15 1968-12-18 Harold Albert Sapp Improvements relating to fuel control devices for internal combustion engines
DE1476112A1 (de) * 1965-12-30 1969-09-25 Sapp Harold Albert Sicherheitseinrichtung fuer Brennkraftmaschinen
US4080946A (en) * 1976-12-20 1978-03-28 Lenmar Industries, Inc. Internal combustion engine shut-down control valve
DE2901082A1 (de) * 1979-01-11 1980-07-17 Bbc Brown Boveri & Cie Stellgeraet fuer eine in der ladeluftleitung eines dieselmotors angeordnete luftklappe
GB2069056B (en) * 1980-01-29 1983-04-07 Gehler J J Preventing damage to ic engines through failure of lubricant supply
US4329954A (en) * 1980-04-14 1982-05-18 Dobbs Odis L Engine shut-down device
GB2108726B (en) * 1980-10-29 1984-05-02 Lucas Industries Ltd Fuel injection pumping apparatus
DE3725088C1 (de) * 1987-07-29 1989-01-12 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer Brennkraftmaschinen,insbesondere Reiheneinspritzpumpe fuer Diesel-Brennkraftmaschinen
DE9203916U1 (de) * 1992-03-24 1993-07-22 O & K Orenstein & Koppel Ag, 13581 Berlin Einrichtung zum Abstellen bzw. Starten eines Dieselmotors

Also Published As

Publication number Publication date
US6085716A (en) 2000-07-11
JP2001508145A (ja) 2001-06-19
DE19631652A1 (de) 1998-02-12
DE59706781D1 (de) 2002-05-02
EP0916017A1 (de) 1999-05-19
WO1998005852A1 (de) 1998-02-12

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