EP0646217B1 - Commande de distribution - Google Patents

Commande de distribution Download PDF

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Publication number
EP0646217B1
EP0646217B1 EP94913559A EP94913559A EP0646217B1 EP 0646217 B1 EP0646217 B1 EP 0646217B1 EP 94913559 A EP94913559 A EP 94913559A EP 94913559 A EP94913559 A EP 94913559A EP 0646217 B1 EP0646217 B1 EP 0646217B1
Authority
EP
European Patent Office
Prior art keywords
rocker arm
cam
injection pump
pump
speed
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
EP94913559A
Other languages
German (de)
English (en)
Other versions
EP0646217A1 (fr
Inventor
Erich Absenger
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 EP0646217A1 publication Critical patent/EP0646217A1/fr
Application granted granted Critical
Publication of EP0646217B1 publication Critical patent/EP0646217B1/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
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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 cam drive via a camshaft for the exhaust and intake valve and for actuating the injection pump in a diesel engine, only one cam being provided for actuating the three functions per cylinder.
  • valve control system is concerned with the fact that the inlet valve is sufficiently long open when it reaches top dead center and the outlet valve when bottom dead center is reached, so that good filling or emptying of the cylinder can be achieved. Accordingly, the designer strives for a rather elongated, ideally rectangular curve between top and bottom dead center. Due to a curve shape approximating to such a rectangular profile, those occurring on the side of the valve train can Mass accelerations and Hertzian forces are limited.
  • the ideal curve for the stamp speed is here a curve which rises particularly steeply up to the top dead center, for the speed of the stamp of the injection pump;
  • the three phases of the pump control are lined up within this increasing branch of the speed curve, namely the preliminary stroke during which the intake duct is closed, an intermediate stroke during which the relief volume in the injection pump is filled and finally the one shortly before top dead center of the Pump stamp ended injection stroke.
  • the falling branch of the speed profile can be described as uncritical.
  • the patent FR-A-1 563 362 describes a cam drive according to the preamble of the main claim.
  • the aim of the present invention is to provide a simple multifunctional camshaft drive that requires reduced design effort and enables a compact design, so that it particularly meets the requirements for very small diesel units.
  • This object is achieved according to the proposal according to the invention in that the actuation of the injection pump by the cam takes place via a rocker arm, and in that the distance of the rocker arm pivot axis from the connecting line between the rolling point of the rocker arm with the cam and the rolling point of the rocker arm with the plunger is less than 40% of the length of the connecting line, and that this distance and the lever ratio with respect to the rocker arm pivot axis are selected such that, with a pump stroke of at most 10 mm, the speed profile for the plunger speed of the injection pump, based on the cam angle, rises more steeply than for the two valves.
  • the formation of the rocker arm for the actuation of the injection pump is of particular importance. While the rocker arm for the actuation of the exhaust and intake valve can be designed in the usual way as a rocker arm, the design of the rocker arm for the injection pump is about the design and arrangement of the above-described steep speed profile for the punch speed.
  • the invention is based on the consideration that the spatial arrangement of the rocker arm pivot axis is decisive for the course of the piston speed of the injection pump in addition to the lever ratio with respect to the rocker arm pivot axis, such that the piston speed, based on the cam angle, the steeper the course, the smaller the distance of the rocker arm pivot axis from the connecting line between the two rolling points of the rocker arm is chosen; this distance can even assume a negative value, ie the rocker arm pivot axis travels over the connecting line on the side on which the camshaft is also located.
  • the rocker arm assumes an approximately linearly elongated shape, ie the pivot axis of the rocker arm has less than 10% lateral displacement, based on the length of the connecting line between the cam-side and the stamp-side rolling point of the rocker arm. In this way, a high relative speed between the rotating cam and the assigned rolling point is ensured.
  • the return spring for the rocker arm which actuates the injection pump, can either be by the plunger spring in the injection pump or by a separate compression spring attached to an extension of the cam-side end of the rocker arm or by a appropriately positioned tension spring be formed so that constant contact with the cam is ensured.
  • the two valves are supported in the usual way by valve springs.
  • Fig. 1 shows a cross section through a camshaft 1 with a single cam 2 on the one hand for the actuation of the rocker arm 3, with which the valve tappet 4 for the inlet and the exhaust valve are controlled, on the other hand for the actuation of a rocker arm 5, with which the injection pump 6 is controlled.
  • This sits with its pump cylinder 7 directly in a corresponding bore of the cylinder head 8 in which the corresponding channels for the fuel flow are incorporated, namely a channel 9 for the fuel supply and a channel 10 for the fuel return line.
  • a connection thread 12 is provided at the upper end of the pump head 11 for connecting the pressure line.
  • the pump ram 13 is connected with its rocker arm end 14 via a driver 15 to a scanning roller 17 mounted on the shaft 16.
  • the rocker arm 5 for actuating the injection pump 13 can be pivoted about a rocker arm pivot axis 20.
  • the contact between the scanning roller 18 and the cam 2 of the camshaft 1 is ensured by a compression spring 22 attached to an extended end 21 of the rocker arm 5, which is clamped between the end 21 of the rocker arm 5 and a seat 23 fixed to the housing.
  • three functions are operated in succession by the same cam 2, namely the rocker arm 5 for actuation the injection pump and the two rocker arms 3 for actuating the valve lifters 4 for the inlet valve and the outlet valve.
  • a control curve, not shown, at the inner end of the pump plunger 13 controls the usual functions associated with fuel injection when it is actuated.
  • rocker arm pivot axis 20 is, based on the drawing, below the connecting line of the two rolling points 25, 26 on the rocker arm 5; 4, however, is more angled inwards, ie the rocker arm pivot axis 20 is, based on the drawing, above the connecting line. If these relationships based on the visual appearance are related to the geometric center of the above three embodiments of the rocker arm, then the center points lie approximately on the connecting line (FIG.
  • the rocker arm pivot axis 20 is offset most inward (or upward), with the result that the relative speed caused by the rotation of the cam 2 in the assigned rolling point 26 is significantly higher than that in FIG. 2 or 3.
  • Numerous intermediate positions are conceivable between the angled rocker arm shape and its elongated shape; the person skilled in the art will choose the suitable shape of the rocker arm 5 in adaptation to the desired course of the punch speed, for example between the two extreme curves shown in FIG. 5.
  • the curve with the solid line shows the profile of the punch speed with an approximately extended rocker arm according to Fig.
  • the curve with the chain-dotted line shows the profile of the stamp speed with an outwardly angled rocker arm according to FIG. 3.
  • the curve with the dashed line shows the profile of the stamp speed with a slightly inwardly angled rocker arm according to FIG. 4.
  • the curves illustrate the influence of the rocker arm shape or the selected position of the rocker arm pivot axis on the speed curve. 2 to 4, the rocker arm 5 is shown with a solid line in the contact position on the cam 2; the rocker arm position shown with a dash-dotted line shows its maximum deflection by the cam 2, the pump plunger 13 always being in the maximum retracted position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

Avec une commande à cames destinée à assurer le fonctionnement de la soupape d'admission et de la soupape d'échappement, ainsi que celui de la pompe d'injection (6) d'un moteur Diesel, il est prévu que la commande des trois fonctions soit assurée, pour chaque cylindre, par la même came (2) et s'opère indirectement par l'intermédiaire d'un culbuteur (3, 5).

Claims (3)

  1. Commande de distribution par l'intermédiaire d'un arbre à cames pour la soupape d'échappement et la soupape d'admission ainsi que pour l'actionnement de la pompe d'injection (6) dans un moteur Diesel, une came (2) unique par cylindre étant prévue pour la commande des trois fonctions, laquelle came agit chaque fois de manière indirecte par l'intermédiaire de leviers pivotants, caractérisée par le fait que l'actionnement de la pompe d'injection (6) par la came (2) a lieu par l'intermédiaire d'un culbuteur (5), par le fait que la distance de l'axe de pivotement (20) du culbuteur par rapport à la droite joignant le point de contact (26) du culbuteur (5) sur la came (2) et le point de contact (25) du culbuteur (5) sur le piston (13) est inférieure à 40 % de la longueur de ladite droite et par le fait que cette distance ainsi que l'amplification du levier par rapport à l'axe de pivotement du culbuteur sont choisies de telle sorte que, pour une course de pompe de 10 mm maximum, la courbe de vitesse pour la vitesse du piston de pompe d'injection, rapportée à l'angle de came, présente une pente plus forte que pour les deux soupapes.
  2. Commande de distribution selon revendication 1, caractérisé par le fait que la distance est comprise entre 5 % et 15 %.
  3. Commande de distribution selon revendication 2, caractérisé par le fait que le culbuteur (5) a une conformation allongée sensiblement linéaire.
EP94913559A 1993-04-10 1994-04-08 Commande de distribution Expired - Lifetime EP0646217B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4311877 1993-04-10
DE4311877A DE4311877C2 (de) 1993-04-10 1993-04-10 Nockenwellenantrieb
PCT/EP1994/001097 WO1994024419A1 (fr) 1993-04-10 1994-04-08 Commande de distribution

Publications (2)

Publication Number Publication Date
EP0646217A1 EP0646217A1 (fr) 1995-04-05
EP0646217B1 true EP0646217B1 (fr) 1997-12-29

Family

ID=6485261

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94913559A Expired - Lifetime EP0646217B1 (fr) 1993-04-10 1994-04-08 Commande de distribution

Country Status (8)

Country Link
US (1) US5540207A (fr)
EP (1) EP0646217B1 (fr)
JP (1) JP3388745B2 (fr)
CN (1) CN1047820C (fr)
AU (1) AU6566594A (fr)
DE (2) DE4311877C2 (fr)
ES (1) ES2111299T3 (fr)
WO (1) WO1994024419A1 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5957673A (en) * 1993-03-11 1999-09-28 Motorenfabrik Hatz Gmbh & Co. Kg. Injection pump for diesel engines
DE19836540B4 (de) * 1998-08-06 2006-02-09 Herbert Naumann Hubventilsteuerung
US6405707B1 (en) 2000-12-18 2002-06-18 Caterpillar Inc. Integral engine and engine compression braking HEUI injector
SE521189C2 (sv) * 2002-02-04 2003-10-07 Volvo Lastvagnar Ab Anordning för att tillföra EGR-gas
US6988473B2 (en) * 2003-06-26 2006-01-24 Delphi Technologies, Inc. Variable valve actuation mechanism having an integrated rocker arm, input cam follower and output cam body
JP4221327B2 (ja) * 2004-04-13 2009-02-12 三菱ふそうトラック・バス株式会社 内燃機関の可変動弁装置
CN100387393C (zh) * 2005-06-08 2008-05-14 大连机床集团有限责任公司 四曲线低冲击高速抬起机构
CN100425805C (zh) * 2006-06-02 2008-10-15 李明 发动机气门驱动装置
KR20090117795A (ko) * 2007-02-06 2009-11-12 클로이세 엠 하란 유압 스프링 구동 장치
US20080230036A1 (en) * 2007-03-23 2008-09-25 Bauman William D Roller actuator for a mechanical fuel pump
US7610902B2 (en) * 2007-09-07 2009-11-03 Gm Global Technology Operations, Inc. Low noise fuel injection pump
US20100316506A1 (en) * 2009-06-11 2010-12-16 Gm Global Technology Operations, Inc. Engine fuel pump drive system
CN103786001B (zh) * 2014-03-03 2016-03-02 重庆全润动力机械有限公司 一种柴油机油泵杠杆的制造方法
WO2016094396A1 (fr) * 2014-12-08 2016-06-16 Harlan Cloyce M Appareil de commande à ressorts hydrauliques
US10641140B2 (en) * 2017-05-12 2020-05-05 Caterpillar Inc. Hydraulic early engine exhaust valve opening system
US20240003340A1 (en) * 2022-06-30 2024-01-04 Cloyce Milton Harlan Spring drive apparatus

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2090911A (en) * 1980-11-28 1982-07-21 Yanmar Diesel Engine Co Overhead cam type diesel engine
DE3700405A1 (de) * 1986-01-08 1987-07-09 Honda Motor Co Ltd Dieselmotor

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB662172A (en) * 1948-04-07 1951-12-05 List Hans Improvements in and relating to fuel injection internal combustion engines
FR1563362A (fr) * 1967-04-22 1969-04-11
US3413965A (en) * 1967-07-13 1968-12-03 Ford Motor Co Mechanism for varying the operation of a reciprocating member
NL154807B (nl) * 1968-10-04 1977-10-17 Werkspoor Amsterdam Nv Nokschijf- of dergelijk aandrijfmechanisme voor de brandstofinspuitpomp van een verbrandingsmotor.
FR2094565A5 (fr) * 1970-06-25 1972-02-04 Loby Gilbert
US3814067A (en) * 1971-02-08 1974-06-04 Guadalajara De La Fuente Internal combustion engine combustion chamber design and air/fuel mixture supply means
AT379865B (de) * 1980-02-08 1986-03-10 Simmering Graz Pauker Ag Wassergekuehlte brennkraftmaschine
DE3325510A1 (de) * 1983-07-15 1985-01-24 Ernst 6940 Weinheim Weidmann Steuerung fuer viertakt-brennkraftmaschinen mit einem nocken zur betaetigung von ein- und auslassventil und einspritzpumpe
AT391165B (de) * 1984-05-22 1990-08-27 Steyr Daimler Puch Ag Nockentrieb fuer eine luftverdichtende, selbstzuendende hubkolben-brennkraftmaschine
FR2643676B1 (fr) * 1989-02-28 1991-06-07 Peugeot Culbuteur pour l'actionnement d'une soupape a tige d'un moteur a combustion interne
DE4212255C2 (de) * 1992-04-11 1996-12-19 Daimler Benz Ag Anordnung einer Kraftstoff-Einspritzvorrichtung am Gehäuse einer Brennkraftmaschine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2090911A (en) * 1980-11-28 1982-07-21 Yanmar Diesel Engine Co Overhead cam type diesel engine
DE3700405A1 (de) * 1986-01-08 1987-07-09 Honda Motor Co Ltd Dieselmotor

Also Published As

Publication number Publication date
DE4311877C2 (de) 1996-05-15
US5540207A (en) 1996-07-30
AU6566594A (en) 1994-11-08
CN1047820C (zh) 1999-12-29
CN1104833A (zh) 1995-07-05
EP0646217A1 (fr) 1995-04-05
JPH07508817A (ja) 1995-09-28
WO1994024419A1 (fr) 1994-10-27
ES2111299T3 (es) 1998-03-01
DE4311877A1 (de) 1994-10-13
DE59404878D1 (de) 1998-02-05
JP3388745B2 (ja) 2003-03-24

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