DE10311776A1 - Parallel twin, 4-piston engine has main crankshaft journals flat in plane with outer journals in same direction, pistons driven by other main journal for cycle charging with mass equalisation - Google Patents

Parallel twin, 4-piston engine has main crankshaft journals flat in plane with outer journals in same direction, pistons driven by other main journal for cycle charging with mass equalisation Download PDF

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Publication number
DE10311776A1
DE10311776A1 DE10311776A DE10311776A DE10311776A1 DE 10311776 A1 DE10311776 A1 DE 10311776A1 DE 10311776 A DE10311776 A DE 10311776A DE 10311776 A DE10311776 A DE 10311776A DE 10311776 A1 DE10311776 A1 DE 10311776A1
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Prior art keywords
cylinder
valves
journals
main
parallel twin
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DE10311776A
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DE10311776B4 (en
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Tjeng Lian The
Rüdiger Ufermann
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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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
    • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
    • F02B23/101—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on or close to the cylinder centre axis, e.g. with mixture formation using spray guided concepts
    • 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
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/02—Other fluid-dynamic features of induction systems for improving quantity of charge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
    • 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
    • F02B75/12—Other methods of operation
    • F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Abstract

The engine has a parallel-twin arrangement with four pistons. The main crankshaft (66) journals lie flat in a plane with the outer journals in the same direction and the pistons of cylinders 3 and 2 are driven by the other main journal via main (64) and auxiliary connecting rods for cylinders 3 and 2 and for cycle charging with simultaneous mass equalisation, whereby the charging air is forced into cylinders via tongue valves.

Description

Die Erfindung betrifft eine Anordnung für eine Verbrennungskraftmaschine mit Fremdzündung zur Direkteinspritzung nach der im Oberbegriff des Anspruchs 1 angegebenen Art.The invention relates to an arrangement for an internal combustion engine with spark ignition for direct injection according to that specified in the preamble of claim 1 Art.

Anordnungen dieser Art werden bereits in einigen Ausführungsformen eingesetzt, die jedoch die Schichtladung auch beim Einsatz einer aufwendigen Steuerungstechnik nicht allen Fahr- Drehzahl- und Lastbereichen genügen.Arrangements of this kind are already being made in some embodiments used, however, the stratified charge even when using a complex control technology not all driving, speed and load ranges suffice.

Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, eine effiziente und funktionssichere zentrale Anordnung mit Druckwellenaufladung in Kombination mit Taktaufladung und strahlgeführter Kraftstoff-Direkteinspritzung mit vierfacher Zündenergie und Heizvorrichtung unter Einsatz einer Anordnung der im Oberbegriff des Anspruchs 1 genannten Art zu schaffen, mit der die vorgegebenen Aktionen erfüllt werden können.Based on this state of the art the invention has for its object an efficient and reliable central arrangement with pressure wave charging in combination with clock charging and beam guided Direct fuel injection with fourfold ignition energy and heating device underneath Use of an arrangement mentioned in the preamble of claim 1 To create the way in which the specified actions are carried out can.

Erfindungsgemäß unterscheidet sich die Anordnung der Eingangs genannten Art vorrangig von bisherigen Technologien dadurch, dass die Aufladung in Kombination einer Druckwellenaufladung mit Taktaufladung in Parallel-Twin-Anordnung der Arbeitszylinder über einen die Einlassventile des Arbeitszylinders verbindenden gemeinsamen Druckraum in Strömungsverbindung stehen, wobei der Druckraum auch über die Zungenventile, die den Totraum der Ladezylindern verkleinern, mit den Ladezylindern in Strömungverbindung steht.According to the invention, the arrangement differs of the type mentioned primarily from previous technologies in that the charging in combination with a pressure wave charging with cycle charging in a parallel twin arrangement of the working cylinders via a common to the intake valves of the working cylinder Pressure chamber in flow connection stand, the pressure chamber also via the reed valves, the reduce the dead space of the loading cylinders with the loading cylinders in flow connection stands.

Gelöst wird diese Aufgabe durch die kennzeichnenden Merkmale des Anspruchs 1. Vorteilhafte Weiterbildungen der Erfindung sind durch die von diesem Anspruch abhängigen Ansprüche gekennzeichnet.This task is solved by the characterizing features of claim 1. Advantageous further developments of the invention are characterized by the claims dependent on this claim.

In folgendem wird die Erfindung anhand eines bevorzugten Ausführungsbeispiels in Verbindung mit acht Zeichnungen beschrieben.In the following the invention is based of a preferred embodiment described in connection with eight drawings.

Dabei zeigt:It shows:

1 eine vereinfachte Draufsicht der Brennkraftmaschine. Die Brennkraftmaschine (1) in Zweirylinder-Viertakt-Parallel-Twin-Anordnung arbeitend, mit integriertem Massenausgleich und insgesamt vier Kolben aufweisend, wobei der Kolben Zylinder 3 (61) und der Kolben Zylinder 2 (67) als Ladepumpen und Massenausgleich fungieren. Die Kolben der Parallel-Twin-Zylinder Kolben-Zylinder 2 (5) und Kolben Zylinder 3 (18) bilden die Ladezylinder, während die Kolben Zylinder 1 (60) und Kolben Zylinder 4 (62) die Arbeitszylinder bilden. Nachdem die Luft über die Einlassventile (40,41,50,51) über den Zylinder 2 (5) und den Zylinder 3 (18) angesaugt worden ist, wird die im Kompressionshub befindliche Luft über die Zungenventile (33) in den Druckraum (17) verbracht und in den sich gerade im Saughub befindenden Zylinder 4 (8) gedrückt, wobei dessen Einlassventile (44,48) noch kurzfristig offen sind. Angenommen Zylinder 4 (8) wurde aufgeladen und der Kolben Zylinder 4 (62) bewegt sich in Richtung UT, sind kurz vor UT die Einlassventile (44,48) noch geöffnet, wobei die Einlassventile (43,47) des Zylinder 1 (26) zeitgleich über die Einlassnocken Zylinder 1 (43',47') kurzfristig im Sinne eines Vorauslasses geöffnet werden und die Auslassventile (42,46) ebenso taktgemäß geöffnet werden, wobei alle vier Ventile des Zylinder 1 (26) offen sind, was zu einer Entlastung der Auslassventile und der Auslassnocken zu gleichzeitiger AGR-Möglichkeit führt. Dadurch wird eine Druckwelle über die geöffneten Einlassventile vom Zylinder 1 (26) in Richtung Druckraum (17) eingelassen. Diese Druckwelle schiebt die im Druckraum (17) vorhandene vorkomprimierte Luft über die noch geöffneten Einlassventile (44,48) im Sinne einer Druckwellennachladung in Richtung Zylinder 4 (8), wodurch gleichzeitig in diesem Zylinder eine gute Verwirbelung erzeugt wird. Die Einlassnocken Zylinder 1 (43',47',48',51') sind mit einem Nebennocken wie in 8 gezeigt, versehen. Dadurch wird verhindert, dass die angesaugte Luft im Arbeitszylinder in die noch geöffneten Einlassventile (siehe auch Ventilüberschneidung) zurückströmt. Wenn die im Arbeitshub befindliche Luftladung komprimiert wird, kann die strahlgeführte Kraftstoffeinspritzung aktiviert werden. Je später die Einspritzung geschieht, desto besser kann die Schichtladung und die Abmagerung optimiert werden. Durch die vierfache Zündenegiebereitstellung der Pluselektroden (24,27,32,52) wird das magere Luft-Kraftstoff-Gemisch zur sicheren Entflammung bei gleichzeitiger guter Abgasqualität gebracht. Dieses Arbeitsprinzip gilt für beide Arbeitszylinder. 1 a simplified top view of the internal combustion engine. The internal combustion engine ( 1 ) working in a two-cylinder, four-stroke parallel twin arrangement, with integrated mass balance and a total of four pistons, the piston being a cylinder 3 ( 61 ) and the piston cylinder 2 ( 67 ) act as charge pumps and mass balancing. The pistons of the parallel twin cylinder piston cylinder 2 ( 5 ) and piston cylinder 3 ( 18 ) form the loading cylinder, while the piston cylinder 1 ( 60 ) and piston cylinder 4 ( 62 ) form the working cylinders. After the air has passed through the intake valves ( 40 . 41 . 50 . 51 ) over the cylinder 2 ( 5 ) and the cylinder 3 ( 18 ) has been sucked in, the air in the compression stroke is released via the reed valves ( 33 ) in the pressure room ( 17 ) and in the cylinder currently in the suction stroke 4 ( 8th ) pressed, its inlet valves ( 44 . 48 ) are still open at short notice. Suppose cylinders 4 ( 8th ) was charged and the piston cylinder 4 ( 62 ) moves towards UT, the inlet valves are just before UT ( 44 . 48 ) still open, with the inlet valves ( 43 . 47 ) of the cylinder 1 ( 26 ) at the same time via the cylinder intake cam 1 ( 43 ' . 47 ' ) are opened at short notice in the sense of a pre-outlet and the exhaust valves ( 42 . 46 ) are also opened in time, with all four valves of the cylinder 1 ( 26 ) are open, which leads to a relief of the exhaust valves and the exhaust cams at the same time EGR possibility. This causes a pressure wave through the open intake valves from the cylinder 1 ( 26 ) towards the pressure chamber ( 17 ) embedded. This pressure wave pushes the pressure 17 ) existing pre-compressed air via the still open inlet valves ( 44 . 48 ) in the sense of a pressure wave recharge towards the cylinder 4 ( 8th ), which also creates a good swirl in this cylinder. The intake cam cylinder 1 ( 43 ' . 47 ' . 48 ' . 51 ' ) are with a secondary cam as in 8th shown, provided. This prevents the intake air in the working cylinder from flowing back into the still open intake valves (see also valve overlap). When the air charge in the working stroke is compressed, the jet-guided fuel injection can be activated. The later the injection occurs, the better the stratified charge and the emaciation can be optimized. Due to the fourfold ignition energy supply of the positive electrodes ( 24 . 27 . 32 . 52 ) the lean air-fuel mixture is brought to a safe ignition with good exhaust gas quality. This working principle applies to both working cylinders.

2 eine vereinfachte Seitenansicht des Motors 2 a simplified side view of the engine

3 entspricht Schnitt B-B 3 corresponds to section BB

4 entspricht Schnitt A-A 4 corresponds to section AA

5 entspricht Schnitt A1-A1 5 corresponds to section A1-A1

6 entspricht Schnitt C1-C1 6 corresponds to section C1-C1

7 entspricht Schnitt C-C 7 corresponds to section CC

8 den Einlassnocken Zylinder 1 und 4 (80) 8th the intake cam cylinder 1 and 4 ( 80 )

(1)(1)
BrennkraftmaschineInternal combustion engine
(2)(2)
Saugrohrsuction tube
(3)(3)
ZylinderkopfschraubeCylinderhead screw
(4)(4)
Drosselklappethrottle
(5) (5)
Zylinder 2 cylinder 2
(6)(6)
ZylinderkopfschraubeCylinderhead screw
(7) (7)
Pluselektrodeplus electrode
(8)(8th)
Zylinder 4 cylinder 4
(9)(9)
Auslasskanalexhaust port
(10)(10)
Auslasskanalexhaust port
(11) (11)
Einspritzdüseinjection
(12)(12)
Pluselektrodeplus electrode
(13) (13)
Heizelementheating element
(14)(14)
ZungenventilgehäuseReed valve housing
(15) (15)
Pluselektrodeplus electrode
(16)(16)
Heizelementheating element
(17) (17)
Druckraumpressure chamber
(18)(18)
Zylinder 3 cylinder 3
(19) (19)
ZylinderkopfschraubeCylinderhead screw
(20)(20)
Drosselklappethrottle
(21) (21)
Einlasskanalinlet channel
(22)(22)
Heizelementheating element
(23) (23)
Druckraumpressure chamber
(24)(24)
Pluselektrodeplus electrode
(25) (25)
Heizelementheating element
(26)(26)
Zylinder 1 cylinder 1
(27) (27)
Pluselektrodeplus electrode
(28)(28)
ZylinderkopfschraubeCylinderhead screw
(29) (29)
Auslasskanalexhaust port
(30)(30)
Auslasskanalexhaust port
(31) (31)
Einspritzdüseinjection
(32)(32)
Pluselektrodeplus electrode
(33) (33)
Zungenventilereed valves
(40)(40)
Einlassventilintake valve
(41) (41)
Einlassventilintake valve
(41')(41 ')
Einlassnocken Zylinder 2 Inlet cam cylinder 2
(42) (42)
Auslassventiloutlet valve
(42')(42 ')
Auslassnocken Zylinder 1 Exhaust cam cylinder 1
(43) (43)
Einlassventilintake valve
(43')(43 ')
Einlassnocken Zylinder 1 Inlet cam cylinder 1
(44) (44)
Einlassventilintake valve
(44')(44 ')
Einlassnocken Zylinder 4 Inlet cam cylinder 4
(45) (45)
Auslassventiloutlet valve
(45')(45 ')
Auslassnocken Zylinder 4 Exhaust cam cylinder 4
(46) (46)
Auslassventiloutlet valve
(46')(46 ')
Auslassnocken Zylinder 1 Exhaust cam cylinder 1
(47) (47)
Einlassventilintake valve
(47')(47 ')
Einlassnocken Zylinder 1 Inlet cam cylinder 1
(48) (48)
Einlassventilintake valve
(48')(48 ')
Einlassnocken Zylinder 4 Inlet cam cylinder 4
(49) (49)
Auslassventiloutlet valve
(49')(49 ')
Auslassnocken Zylinder 4 Exhaust cam cylinder 4
(50) (50)
Einlassventilintake valve
(51)(51)
Einlassventil intake valve
(51') (51 ')
Einlassnocken Zylinder 3 Inlet cam cylinder 3
(52)(52)
Pluselektrode plus electrode
(53) (53)
Pluselektrodeplus electrode
(60)(60)
Kolben Zylinder 1 Piston Cylinder 1
(61) (61)
Kolben Zylinder 3 Piston Cylinder 3
(62)(62)
Kolben Zylinder 4 Piston Cylinder 4
(63) (63)
Pleuelstange Zylinder 1 Connecting rod cylinder 1
(63')(63 ')
Hubzapfencrank pins
(64) (64)
Hauptpleuel Zylinder 3 Main connecting rod cylinder 3
(64')(64 ')
Hubzapfencrank pins
(65) (65)
Pleuelstange Zylinder 4 Connecting rod cylinder 4
(65')(65 ')
Hubzapfencrank pins
(66)(66)
Kurbelwellecrankshaft
(67)(67)
Kolben Zylinder 2 Piston Cylinder 2
(68) (68)
Nebenpleuel Zylinder 2 Secondary connecting rod cylinder 2
(8)(8th)
Einlassnocken Zylinder 1 und 4 Inlet cam cylinder 1 and 4

Claims (1)

Zweizylinder Viertakt-Brennkraftmaschine in Parallel-Twin-Anordnung mit insgesamt vier Kolben dadurch gekennzeichnet, dass die Hubzapfen (63',64',65') der Kurbelwelle (66) plan in einer Ebene liegen, wovon die beiden äußeren Parallel-Twin Hubzapfen (63',65') gleichgerichtet sind, wobei der Kolben Zylinder 3 (61) und der Kolben Zylinder 2 (67) vom Hubzapfen (64') über den Hauptpleuel Zylinder 3 (64) und den Nebenpleuel Zylinder 2 (68) im Sinne einer Taktaufladung bei gleichzeitigem Massenausgleich angetrieben werden, wobei die Ladeluft taktgemäß über Zungenventile (33), die mit dem Zylinder 2 (5) und dem Zylinder 3 (18) in Strömungsverbindung stehen und die Ladeluft über den Druckraum (17) mit den Heizelementen (13,16,22,25) über die Einlassventile (43,44,47,48) in den Zylinder 4 (8) bzw. mit 360° Zündabstand in den Zylinder 1 (26) gedrückt werden, wozu die Einlassnocken (41',51') des Zylinders 2 (5) und des Zylinders 3 (18), die Einlassventile (40,41,50,51) die alle mit 180° Nockenwinkel-Abstand- entsprechend 360° Kurbelwinkel-Abstand- öffnen und die Ladeluft in den sich gerade im Saughub befindlichen Zylinder 4 (8) über die jeweils zugehörigen Einlassventile drückt, wobei kurz vor Ende des Saughubes über die Einlassventile (44,48), die noch kurzfristig geöffnet sind, die sich im Druckraum (17) befindliche Luftsäule durch die von den Nebennocken der Nocken (43',47') kurzfristig angehoben werden und von der Druckwelle des sich im Expansionshub befindlichen Zylinders 1 (26) in Richtung Zylinder 4 (8) über die noch geöffneten Einlassventile (44,48) gedrückt werden, wobei die Auslassventile (42,46) des Zylinders 1 (26) unmittelbar danach geöffnet werden.Two-cylinder four-stroke internal combustion engine in a parallel twin arrangement with a total of four pistons, characterized in that the crank pin ( 63 ' . 64 ' . 65 ' ) the crankshaft ( 66 ) lie flat on one level, of which the two outer parallel twin crank pins ( 63 ' . 65 ' ) are rectified, the piston cylinder 3 ( 61 ) and the piston cylinder 2 ( 67 ) from the crank pin ( 64 ' ) over the main connecting rod cylinder 3 ( 64 ) and the connecting rod cylinder 2 ( 68 ) are driven in the sense of a cycle charge with simultaneous mass balancing, the charge air being clocked via tongue valves ( 33 ) with the cylinder 2 ( 5 ) and the cylinder 3 ( 18 ) are in flow connection and the charge air via the pressure chamber ( 17 ) with the heating elements ( 13 . 16 . 22 . 25 ) via the inlet valves ( 43 . 44 . 47 . 48 ) in the cylinder 4 ( 8th ) or with a 360 ° firing interval in the cylinder 1 ( 26 ) are pressed, for which purpose the inlet cams ( 41 ' . 51 ' ) of the cylinder 2 ( 5 ) and the cylinder 3 ( 18 ), the intake valves ( 40 . 41 . 50 . 51 ) which all open with 180 ° cam angle distance - corresponding to 360 ° crank angle distance - and the charge air into the cylinder currently in the suction stroke 4 ( 8th ) presses on the associated intake valves, with the intake valves (just before the end of the suction stroke 44 . 48 ) that are still open for a short time, that are in the pressure room ( 17 ) located air column through the from the side cams of the cams ( 43 ' . 47 ' ) are raised briefly and by the pressure wave of the cylinder in the expansion stroke 1 ( 26 ) towards the cylinder 4 ( 8th ) via the still open inlet valves ( 44 . 48 ) are pressed, the exhaust valves ( 42 . 46 ) of the cylinder 1 ( 26 ) are opened immediately afterwards.
DE10311776A 2003-03-18 2003-03-18 Parallel twin-engine environment Expired - Fee Related DE10311776B4 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105829678A (en) * 2013-12-19 2016-08-03 沃尔沃卡车集团 Internal combustion engine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011057013B4 (en) * 2011-12-23 2021-08-26 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Internal combustion engine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3007746A1 (en) * 1980-02-29 1981-09-17 Benno Campione Lugano Kaltenegger INTERNAL COMBUSTION ENGINE

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105829678A (en) * 2013-12-19 2016-08-03 沃尔沃卡车集团 Internal combustion engine
US10094273B2 (en) 2013-12-19 2018-10-09 Volvo Truck Corporation Internal combustion engine
CN105829678B (en) * 2013-12-19 2019-10-11 沃尔沃卡车集团 Internal combustion engine

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