EP0610641B1 - Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen - Google Patents

Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen Download PDF

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Publication number
EP0610641B1
EP0610641B1 EP93810077A EP93810077A EP0610641B1 EP 0610641 B1 EP0610641 B1 EP 0610641B1 EP 93810077 A EP93810077 A EP 93810077A EP 93810077 A EP93810077 A EP 93810077A EP 0610641 B1 EP0610641 B1 EP 0610641B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
pump
pressure
piston
pressure chamber
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
EP93810077A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0610641A1 (de
Inventor
Patrick Genier
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.)
Wartsila Finland Oy
Original Assignee
Wartsila NSD Schweiz 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 Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to DK93810077.3T priority Critical patent/DK0610641T3/da
Priority to DE59307709T priority patent/DE59307709D1/de
Priority to EP93810077A priority patent/EP0610641B1/de
Priority to KR1019940001826A priority patent/KR100283932B1/ko
Priority to FI940546A priority patent/FI106397B/fi
Priority to CN94101418A priority patent/CN1096568A/zh
Priority to JP6014700A priority patent/JPH10205411A/ja
Publication of EP0610641A1 publication Critical patent/EP0610641A1/de
Application granted granted Critical
Publication of EP0610641B1 publication Critical patent/EP0610641B1/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
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons

Definitions

  • the invention relates to a fuel injection pump for a reciprocating piston internal combustion engine according to the preamble of claim 1.
  • An injection pump of this type is known from EP-A-0 267 894.
  • the cylinder is moved against the force of a spring by means of fuel in order to postpone the injection timing.
  • a pressure medium is applied to the end face of the cylinder as a function of operating variables such as speed, boost pressure, temperature and / or load, the pressure of the pressure medium being subjected to regulation.
  • the invention has for its object to provide an injection pump which is simple in design and which can optionally be switched between two fixed injection times.
  • the injection pump is switched directly and simply from one injection time to the other.
  • the fuel injection pump has a housing 1, which is sealed at its upper end in FIG. 1 by a cover 2.
  • a cylinder 3 is arranged in the housing 1, into which an axially movable piston 4 projects in FIG. 1 from below.
  • the lower end of the piston 4 in FIG. 1 is operatively connected to a camshaft drive in a known, not shown manner.
  • the top end of the piston 4 in FIG. 1 forms a first control edge 5, which cooperates with a bore 6 extending transversely through the cylinder 3 and which determines the start of delivery of the pump.
  • the piston 4 has a second control edge 7, which extends obliquely to the piston axis, which also interacts with the bore 6 and determines the delivery end of the injection pump.
  • the delivery chamber 8 of the pump which is delimited by the cylinder 3 and a central extension 9 of the cover 2 which projects into the bore of the cylinder.
  • a central channel 10 which is connected at its upper end to a pressure line, not shown, which leads to the injection nozzle of a reciprocating internal combustion engine of the diesel type and is injected into the working cylinder of the machine via the cyclical fuel.
  • the reciprocating piston internal combustion engine is installed as a drive motor in a sea-going ship.
  • the cylinder 3 In the area of the delivery chamber 8, the cylinder 3 is surrounded on the outside by an annular space 11, into which the transverse bore 6 of the cylinder 3 opens.
  • a channel 12 which is provided in the housing 1 and through which fuel (arrow A) is supplied in a known, not shown manner, opens into the annular space 11. Excess fuel is returned from the annular space 11 via a channel 13 in the housing 1 and a line (not shown) to a collecting container (arrow B).
  • annular pressure chamber 15 is provided in the pump housing 1 below the annular space 11, separated from the latter, and is connected to a supply line 17 for a hydraulic pressure medium via a channel 16 provided in the housing 1.
  • the outer diameter D of the cylinder 3 is reduced to the diameter d, a shoulder 18 being formed, which in FIG. 1 rests on a flat annular surface 19 of the pressure chamber 15.
  • the annular surface 19 has an outer diameter D 'which is larger than the diameter d, but smaller than the outer diameter D of the cylinder.
  • a line 20 branches off, which contains a two-way switch valve 21 and which opens into a channel 22 which is located in the housing 1 in the region of the upper end of the cylinder 3 and opens into a pressure chamber 25.
  • the pressure chamber 25 is located between the top face of the cylinder 3 in FIG. 1 and the cover 2.
  • the pressure chamber 25 is in the form of an annular disk and has an outside diameter equal to the outer diameter D of the cylinder 3 and an inner diameter which is equal to the outer diameter d 'of the extension 9 of the cover 2 projecting into the cylinder.
  • the injection pump described functions as follows: In the position of the changeover valve 21 shown in FIG. 1, hydraulic pressure medium is introduced both into the pressure chamber 15 and into the pressure chamber 25. Since the differential area (D - D ') acted upon by the pressure medium on the shoulder 18 is smaller than the end face of the cylinder 3 (D - d') in the upper pressure chamber 25, the cylinder is pressed onto the annular surface 19 because the pressure force in the upper pressure chamber 25 predominates. When the piston 4 moves upward, the fuel enclosed in the delivery chamber 8 is brought to a higher pressure from the moment in which the first control edge 5 passes the upper limit of the transverse bore 6.
  • the fuel is conveyed via the central channel 10 to the injection nozzle already mentioned, via which the fuel is then injected into the working cylinder when the injection pressure is reached.
  • the injection is interrupted when the second control edge 7 passes the lower limit of the transverse bore 6.
  • the pressure in the fuel in the delivery chamber 8 is relieved and the fuel can escape via the transverse bore 6, the annular chamber 11 and the channel 13.
  • the injection described occurs when the ship is sailing on the open sea, the operation of the drive motor being based on the good efficiency and the NO x content being relatively high.
  • the changeover valve 21 is moved to the right, for example by hand or pneumatically or by an electrical signal, into that shown in FIG position shown moved.
  • the upper pressure chamber 25 is relieved, and the hydraulic Pressure medium escapes from this room into a collection container.
  • the pressure medium that continues to be supplied via line 17 then only acts on shoulder 18 in lower pressure chamber 15.
  • cylinder 3 moves upward until the upper end face of the cylinder rests on cover 2.
  • the transverse channel 6 is also displaced upward and, when the piston 4 moves upward, the delivery and injection also begin later than before, because it takes longer for the first control edge 5 to pass the upper limit of the transverse bore 6.
  • the NO x content of the exhaust gases leaving the drive motor is thus lower.
  • This position of the cylinder 3 is maintained until the ship leaves the coastal waters. Then, by resetting the changeover valve 21 to the position shown in FIG. 1, the cylinder 3 is moved back to its lower end position, and the operation takes place again with an earlier start of injection.
  • the lower pressure chamber is included in the annular space 11, so that the shoulder 18 is acted upon by the pressure of the fuel in the annular space.
  • a line 31 is connected, which contains a two-way switch valve 32. Via the changeover valve 32, the line 31 and thus the pressure chamber 25 can be connected to a line 33 for the supply of a hydraulic pressure medium.
  • the pressure medium connection exists in the drawn position of the changeover valve 32, so that the pressure medium in the pressure chamber 25 holds the cylinder 3 in the lower end position against the fuel pressure acting on the shoulder 18.
  • the injection pump works as described in Fig.1, ie the injection takes place with an earlier start of injection and the ship is in the open sea. Drives the ship into coastal waters, the changeover valve 32 is shifted to the right in FIG. 2, so that the line 31 and thus the pressure chamber 25 are relieved of pressure.
  • the pressure force of the fuel on the shoulder 18 now shifts the cylinder 3 into its upper end position, which corresponds to that shown in Fig.1a.
  • the transverse bore 6 in the cylinder 3 is now higher than that shown in FIG. 2, that is to say the delivery of the injection pump takes place later and the formation of NO x is reduced.
  • the hydraulic pressure medium supplied via lines 17 and 33 can be diesel fuel, but the supply thereof is independent of the fuel supplied via channel 12 of the injection pump.
  • fuel is branched off as the hydraulic pressure medium from the diesel fuel supplied to the pump.
  • a channel 36 is provided in the housing 1 in the area of the annular space 11, to which a line 37 is connected which opens into the channel 22 via a two-way switch valve 38, which is connected to the upper pressure chamber 25.
  • a channel 39 is provided in the housing 1, which also communicates with the pressure chamber 25 and to which a line 40 is connected, which opens into a line 13 'which is connected to the outlet channel 13 for the fuel.
  • Throttles 41 and 42 are located in lines 13 'and 40, respectively.
  • the exemplary embodiment according to FIG. 4 shows a fuel injection pump which does not fall under claim 1. It largely corresponds to the example according to FIG. 2, but the hydraulic force acting on the shoulder 18 in FIG. 2 is replaced by a helical spring 30.
  • the spring 30 surrounds the lower end of the piston 4 and presses on the lower end face of the cylinder 3 in FIG. 4. In this embodiment, there is therefore no need to form a special annular surface in the housing 1 below the shoulder 18.
  • the cylinder 3 In the operation of the pump, the cylinder 3 is held in the lower end position by the hydraulic force in the pressure chamber 25 in the drawn position of the changeover valve 32, and this corresponds to an early start of injection.
  • the changeover valve 32 When the ship is traveling near the coast, the changeover valve 32 is shifted to the right in FIG. 4, as a result of which the pressure chamber 25 is relieved of the pressure. The compressive force of the coil spring 30 then presses the cylinder 3 into its upper end position, so that the start of injection takes place later.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP93810077A 1993-02-08 1993-02-08 Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen Expired - Lifetime EP0610641B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
DK93810077.3T DK0610641T3 (da) 1993-02-08 1993-02-08 Brændstofindsprøjtningspumpe til stempelbrændkraftmaskiner
DE59307709T DE59307709D1 (de) 1993-02-08 1993-02-08 Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen
EP93810077A EP0610641B1 (de) 1993-02-08 1993-02-08 Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen
KR1019940001826A KR100283932B1 (ko) 1993-02-08 1994-02-01 왕복동내연기관의연료분사펌프
FI940546A FI106397B (fi) 1993-02-08 1994-02-07 Polttoaineen ruiskutuspumppu iskumäntäpolttomoottoreita varten
CN94101418A CN1096568A (zh) 1993-02-08 1994-02-07 一种用于往复式内燃机的燃油喷射泵
JP6014700A JPH10205411A (ja) 1993-02-08 1994-02-08 レシプロ式内燃機関のための燃料噴射ポンプ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP93810077A EP0610641B1 (de) 1993-02-08 1993-02-08 Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0610641A1 EP0610641A1 (de) 1994-08-17
EP0610641B1 true EP0610641B1 (de) 1997-11-19

Family

ID=8214915

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93810077A Expired - Lifetime EP0610641B1 (de) 1993-02-08 1993-02-08 Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen

Country Status (7)

Country Link
EP (1) EP0610641B1 (fi)
JP (1) JPH10205411A (fi)
KR (1) KR100283932B1 (fi)
CN (1) CN1096568A (fi)
DE (1) DE59307709D1 (fi)
DK (1) DK0610641T3 (fi)
FI (1) FI106397B (fi)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6773240B2 (en) 2002-01-28 2004-08-10 Visteon Global Technologies, Inc. Single piston dual chamber fuel pump

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19719800C1 (de) * 1997-05-10 1998-12-17 Kurt Wilhelm Einspritzanlage für Freikolbenmotore mit Niederdruckpumpe
JP3814245B2 (ja) * 2002-11-21 2006-08-23 ヤンマー株式会社 燃料噴射ポンプ
CN1312395C (zh) * 2003-12-12 2007-04-25 上海交通大学 用于柴油机共轨喷油器的密封装置
GB2549141A (en) * 2016-04-08 2017-10-11 Delphi Int Operations Luxembourg Sarl Fuel pump

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3360320D1 (en) * 1982-03-25 1985-08-01 Deere & Co Injector pump unit with a sleeve-valve controlled floating piston for internal-combustion engines
EP0267894A1 (de) * 1986-10-30 1988-05-18 VOEST-ALPINE AUTOMOTIVE Gesellschaft m.b.H. Pumpedüsebaueinheit für die Einspritzung von Kraftstoff in Brennkraftmaschinen
US5090378A (en) * 1991-02-22 1992-02-25 The Cessna Aircraft Company Dual nozzle single pump fuel injection system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6773240B2 (en) 2002-01-28 2004-08-10 Visteon Global Technologies, Inc. Single piston dual chamber fuel pump

Also Published As

Publication number Publication date
CN1096568A (zh) 1994-12-21
FI940546A0 (fi) 1994-02-07
FI106397B (fi) 2001-01-31
FI940546A (fi) 1994-08-09
EP0610641A1 (de) 1994-08-17
DK0610641T3 (da) 1997-12-22
JPH10205411A (ja) 1998-08-04
DE59307709D1 (de) 1998-01-02
KR100283932B1 (ko) 2001-10-22
KR940019984A (ko) 1994-09-15

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