EP0063258B1 - Cylinder and piston combination for a diesel engine - Google Patents

Cylinder and piston combination for a diesel engine Download PDF

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Publication number
EP0063258B1
EP0063258B1 EP82102544A EP82102544A EP0063258B1 EP 0063258 B1 EP0063258 B1 EP 0063258B1 EP 82102544 A EP82102544 A EP 82102544A EP 82102544 A EP82102544 A EP 82102544A EP 0063258 B1 EP0063258 B1 EP 0063258B1
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EP
European Patent Office
Prior art keywords
cylinder
piston
diameter
combination
pat
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Expired
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EP82102544A
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German (de)
French (fr)
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EP0063258A1 (en
Inventor
Wolfgang Dipl. Ing. Rein
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Mahle GmbH
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Mahle GmbH
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    • 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 
    • F02F1/18—Other cylinders
    • 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
    • F02B77/00—Component parts, details or accessories, not otherwise provided for
    • F02B77/04—Cleaning of, preventing corrosion or erosion in, or preventing unwanted deposits in, combustion engines
    • 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
    • F02F3/00—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 cylinder for internal combustion engines according to the preamble of claim 1.
  • Such cylinders are known from US Pat. No. 2,515,492.
  • the radial expansion in the upper area of the cylinder has the purpose of preventing the build-up of hard oil coal on the top land of the piston running in the cylinder.
  • the build-up of hard oil coal on the top land of the piston leads to local polishing on the cylinder running surface.
  • the cylinder extension opposite the top land of the piston in its upper dead position is not intended to completely prevent the buildup of oil carbon on the cylinder web, but rather this measure is only intended to ensure that a soft layer of oil carbon builds up. This soft layer should continuously degrade during engine operation or should be kept to a minimum in such a way that the soft oil carbon on the cylinder tread does not cause any polishing points which adversely affect the tread geometry.
  • the upper cylinder extension known per se according to US Pat. No. 2,513,492 is not limited to the minor expansion dimension specified there, but takes place in an order of magnitude like that in US Pat. No. 3 463 057 is specified.
  • the diameter expansion in the cylinder area defined by the preamble of claim 1 is at least 1.0 mm and can go up to 2.5 mm. Diameter expansions between 1.5 and 2 mm have proven to be particularly useful.
  • the solution according to the invention offers the advantage over that of US Pat. No. 3,463,057 in that the relatively large gap space required to avoid the build-up of hard oil coal on the top land area of the piston is only present when the piston is in top dead center. When the piston moves downwards, however, this large gap disappears as soon as the top land of the piston leaves the enlarged area of the cylinder. As a result, the proportion of smoke in the exhaust gas is considerably improved compared to engine operation with a piston designed according to US Pat. No. 3,463,057.
  • the piston 1 is in the cylinder 2 in its top dead center position.
  • the main diameter of the cylinder is indicated with D i .
  • D 2 is the diameter of the enlarged upper region of the cylinder 2.
  • D o is the diameter of the top land of the piston 1.
  • the height of the cylinder extension extends axially to such an extent that the uppermost piston ring 3 of the piston 1 just does not yet reach its top dead center protrudes into the extended area.
  • a diameter of D 100 mm
  • the difference between the diameters is D 2 and D, in the present case 1.6 mm and between the diameters D, and D o in the cold state 0.45 mm.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Description

Die Erfindung betrifft einen Zylinder für Verbrennungsmotoren nach dem Oberbegriff des Anspruchs 1.The invention relates to a cylinder for internal combustion engines according to the preamble of claim 1.

Derartige Zylinder sind aus der US-PS 2 515 492 bekannt. Die radiale Erweiterung im oberen Bereich des Zylinders hat dort den Zweck, den-Aufbau von harter Ölkohle am Feuersteg des in dem Zylinder laufenden Kolbens zu verhindern. Der Aufbau harter Ölkohle an dem Feuersteg des Kolbens führt nämlich zu örtlichen Anpolierungen auf der Zylinderlauffläche. Die dem Feuersteg des Kolbens in seiner oberen Totlage gegenüberliegende Zylindererweiterung soll den Ölkohleaufbau auf dem Zylindersteg nicht vollkommen verhindern, sondern diese Massnahme soll lediglich dazu dienen, dass sich eine weiche Ölkohleschicht aufbaut. Diese weiche Schicht soll sich im Motorbetrieb kontinuierlich abbauen bzw. auf einem Mindestmass gehalten werden können und zwar derart, dass die weiche Ölkohle auf der Zylinderlauffläche keine die Laufflächengeometrie nachteilig beeinflussenden Polierstellen hervorruft. Zu diesem Zweck wird in der US-PS 2 513 492 vorgeschlagen, den oben beschriebenen oberen Zylinderbereich geringfügig zu erweiteren und zwar um ein Mass, das dem sich im Motorbetrieb ergebenden Verschleiss der Zylinderlaufbahn entspricht. Bei einem Kolben mit einem Durchmesser von etwa 300 mm wird eine Erweiterung des Zylinderdurchmessers in dem betreffenden Bereich um 0,5 mm genannt. Es hat sich inzwischen gezeigt, dass die vorgeschlagene geringfügige radiale Zylindererweiterung das gesteckte Ziel der Vermeidung eines harte Reiber in der Zylinderlauffläche verursachenden Ölkohleaufbaus nicht in befriedigender Weise erreichen lässt.Such cylinders are known from US Pat. No. 2,515,492. The radial expansion in the upper area of the cylinder has the purpose of preventing the build-up of hard oil coal on the top land of the piston running in the cylinder. The build-up of hard oil coal on the top land of the piston leads to local polishing on the cylinder running surface. The cylinder extension opposite the top land of the piston in its upper dead position is not intended to completely prevent the buildup of oil carbon on the cylinder web, but rather this measure is only intended to ensure that a soft layer of oil carbon builds up. This soft layer should continuously degrade during engine operation or should be kept to a minimum in such a way that the soft oil carbon on the cylinder tread does not cause any polishing points which adversely affect the tread geometry. For this purpose, it is proposed in US Pat. No. 2,513,492 to slightly expand the upper cylinder region described above, namely by a measure that corresponds to the wear of the cylinder race that results during engine operation. In the case of a piston with a diameter of approximately 300 mm, an extension of the cylinder diameter in the area in question by 0.5 mm is mentioned. In the meantime, it has been shown that the proposed slight radial cylinder expansion does not satisfactorily achieve the goal of avoiding an oil carbon build-up which causes hard friction in the cylinder running surface.

Gelöst wird das Problem eines solchen schädlichen Ölkohleaufbaues im Stand der Technik dagegen recht zufriedenstellend durch eine Massnahme nach der US-PS 3 463 057. Diese Massnahme besteht darin, nicht den oberen Bereich des Zylinders radial zu erweitern, sondern vielmehr den Kolben im Feuerstegbereich radial zu verkleinern. Dabei hat sich gezeigt, dass eine geringfügige Durchmesserverkleinerung des .Kolbens im Feuerstegbereich, etwa in der Grössenordnung wie bei der US-PS 2 513 492 der Zylinderdurchmesser vergrössert wird, das Problem des unschädlichen Ölkohleaufbaus nicht löst. Es ist vielmehr tatsächlich erforderlich, die Durchmesserverkleinerung im Feuerstegbereich des Kolbens in einer Grösse vorzunehmen, wie sie in der US-PS 3 463 057 angegeben ist. Danach muss die Durchmesserverkleinerung mindestens etwa 1,5 mm betragen. Diese Massnahme wird heute in der Motorentechnik mit in bezug auf den Ölkohleaufbau befriedigendem Erfolg eingesetzt. Diese Massnahme hat jedoch auf denVerbrennungsablauf, zumindest in bestimmten Last- und Drehzahlbereichen und damit bezüglich Ausbildung und Zusammensetzung des Abgases sowie des Kraftstoffverbrauchs unerfreuliche Nachteile. So enthalten die Abgase von mit solchen Kolben bestückten Motoren höhere Rauchanteile als Motoren, bei denen der Feuerstegbereich der Kolben nicht in einem derart grossen Masse verkleinert ist. Der Rauchanteil muss nicht nur in bezug auf die Luftreinhaltungsvorschriften gesenkt werden, sondern er zeigt auch an, dass wegen der nicht optimalen Verbrennung der Kraftstoff nicht optimal in Antriebsleistung umgesetzt wird.On the other hand, the problem of such a harmful oil carbon structure in the prior art is solved quite satisfactorily by a measure according to US Pat. No. 3,463,057. This measure consists in not radially expanding the upper region of the cylinder, but rather radially closing the piston in the top land region downsize. It has been shown that a slight reduction in the diameter of the piston in the top land area, approximately in the order of magnitude of the cylinder diameter as in US Pat. No. 2,513,492, does not solve the problem of the harmless oil carbon build-up. Rather, it is actually necessary to reduce the diameter in the top land area of the piston to the size specified in US Pat. No. 3,463,057. After that, the diameter reduction must be at least about 1.5 mm. This measure is used today in engine technology with satisfactory success with regard to the construction of oil coal. However, this measure has unpleasant disadvantages for the combustion process, at least in certain load and speed ranges, and thus with regard to the design and composition of the exhaust gas and the fuel consumption. For example, the exhaust gases from engines equipped with such pistons contain higher proportions of smoke than engines in which the top land area of the pistons is not reduced to such a large extent. The smoke percentage not only has to be reduced in relation to the air pollution control regulations, but it also indicates that the fuel is not optimally converted into drive power due to the non-optimal combustion.

Hier Abhilfe zu schaffen, ist die Aufgabe dervorliegenden Erfindung.To remedy this is the object of the present invention.

Gelöst wird sie nach dem kennzeichnenden Merkmal des Anspruchs 1 dadurch, dass die nach der US-PS 2 513 492 an sich bekannte obere Zylindererweiterung nicht auf das dort angegebene geringfügige Erweiterungsmass beschränkt wird, sondern in einer Grössenordnung erfolgt wie sie in der US-PS 3 463 057 angegeben ist. Dies bedeutet, dass die Durchmessererweiterung in dem durch die Gattung des Anspruchs 1 festgelegten Zylinderbereich mindestens 1,0 mm beträgt und bis auf 2,5 mm hinauf gehen kann. Als besonders zweckmässig haben sich Durchmessererweiterungen.zwischen 1,5 und 2 mm gezeigt.It is solved according to the characterizing feature of claim 1 by the fact that the upper cylinder extension known per se according to US Pat. No. 2,513,492 is not limited to the minor expansion dimension specified there, but takes place in an order of magnitude like that in US Pat. No. 3 463 057 is specified. This means that the diameter expansion in the cylinder area defined by the preamble of claim 1 is at least 1.0 mm and can go up to 2.5 mm. Diameter expansions between 1.5 and 2 mm have proven to be particularly useful.

Die erfindungsgemässe Lösung bietet gegenüber derjenigen nach der US-PS 3 463 057 den Vorteil, dass der zur Vermeidung des Aufbaus einer harten Ölkohle am Feuerstegbereich des Kolbens erforderliche relativ grosse Spaltraum nur bei Lage des Kolbens im oberen Totpunktvorliegt. Bei Abwärtsbewegung des Kolbens verschwindet dieser grosse Spalt jedoch, sobald der Feuersteg des Kolbens den erweiterten Bereich des Zylinders verlässt. Dadurch wird der Rauchanteil im Abgas gegenüber einem Motorbetrieb mit einem nach der US-PS 3 463 057 ausgebildeten Kolben ganz erheblich verbessert.The solution according to the invention offers the advantage over that of US Pat. No. 3,463,057 in that the relatively large gap space required to avoid the build-up of hard oil coal on the top land area of the piston is only present when the piston is in top dead center. When the piston moves downwards, however, this large gap disappears as soon as the top land of the piston leaves the enlarged area of the cylinder. As a result, the proportion of smoke in the exhaust gas is considerably improved compared to engine operation with a piston designed according to US Pat. No. 3,463,057.

Dieses Ergebnis ist insgesamt insofern überraschend, als die Fachwelt bisher annahm, dass der Ölkohleaufbau in dem zur Vermeidung von örtlichen Polierstellen in der Zylinderlauffläche erforderlichen Masse nur durch eine radiale Feuerstegverkleinerung unter Einhaltung der in der US-PS 3 463 057 angegebenen Mindestmasse erreichbar sei, während Zylinderausnehmungen gemäss der US-PS 2 513 492 generell zur Lösung des Ölkohleproblems keine dem durch die US-PS 3 463 057 erreichten neuesten Stand der Technik adäquate Lösung sein könne. Um so überraschender ist es, dass mit einer radialen Erweiterung des Zylinders in seinem oberen Bereich bei richtiger, von den damaligen Werten abweichender Dimensionierung nicht nur gleichwertige, sondern in bezug auf das Abgasverhalten und zum Teil auch auf den Verbrauch zumindest in bestimmten Last- und Drehzahlbereichen sogar bessere Ergebnisse erzielbar sind.Overall, this result is surprising insofar as experts have hitherto assumed that the oil carbon build-up in the mass required to avoid local polishing points in the cylinder running surface can only be achieved by radial reduction of the top land, while observing the minimum mass specified in US Pat. No. 3,463,057, while Cylinder recesses according to US Pat. No. 2,513,492, generally for solving the oil coal problem, could not be an adequate solution to the state of the art achieved by US Pat. No. 3,463,057. It is all the more surprising that with a radial expansion of the cylinder in its upper area with the correct dimensioning deviating from the values at the time, it is not only equivalent, but also in terms of exhaust gas behavior and partly also in terms of consumption, at least in certain load and speed ranges even better results can be achieved.

Ein Ausführungsbeispiel ist in der Zeichnung dargestellt, die den Ausschnitt eines Längsschnittes durch eine Kolben-Zylinderanordnung bei Lage des Kolbens im oberen Totpunkt darstellt.An embodiment is shown in the drawing, which shows the detail of a longitudinal section through a piston-cylinder arrangement with the piston in top dead center.

Der Kolben 1 befindet sich in dem Zylinder 2 in seiner oberen Totpunktlage. Der Hauptdurchmesser des Zylinders ist mit Di angegeben. D2 ist der Durchmesser des erweiterten oberen Bereichs des Zylinders 2. Do ist der Durchmesser des Feuerstegs des Kolbens 1. Axial erstreckt sich die Höhe der Zylindererweiterung maximal so weit, dass der oberste Kolbenring 3 des Kolbens 1 in dessen oberer Totpunktiage gerade noch nicht in den erweiterten Bereich hineinragt. Bei einem Durchmesser von D, = 100 mm beträgt die Differenz zwischen den Durchmessern D2 und D, im vorliegenden Fall 1,6 mm und zwischen den Durchmessern D, und Do im Kaltzustand 0,45 mm.The piston 1 is in the cylinder 2 in its top dead center position. The main diameter of the cylinder is indicated with D i . D 2 is the diameter of the enlarged upper region of the cylinder 2. D o is the diameter of the top land of the piston 1. The height of the cylinder extension extends axially to such an extent that the uppermost piston ring 3 of the piston 1 just does not yet reach its top dead center protrudes into the extended area. With a diameter of D = 100 mm, the difference between the diameters is D 2 and D, in the present case 1.6 mm and between the diameters D, and D o in the cold state 0.45 mm.

Claims (3)

1. Combination of cylinder (2) and piston (1) in a range of cylinder diameters D1 of between 90 mm and 140 mm for diesel engines, wherein the cylinder (2) in its upper zone adjacent the cylinder heat has a larger diameter D2, this range extending axially at most so far into the cylinder (2) that in the top dead centre position of the piston (1) the topmost ring (3) is still not yet protruding into the widened zone, characterised in that in the cold state the difference between the diameter Do of the top land of the piston (1) and the diameter D2 in a range of 0.0045 x D1 + 1.5 to 2.5 mm, D2 - D1 amounting to at least 1 mm.
2. Combination of cylinder (2) with piston (1) according to Claim 1, characterised in that the difference between D2 and D1 amounts to at least 1.5 mm.
3. Combination of cylinder (2) with piston (1) according to Claim 1 or 2, characterised in that the difference between D2 and D1 is between 1.5 and 2.5 mm.
EP82102544A 1981-04-18 1982-03-26 Cylinder and piston combination for a diesel engine Expired EP0063258B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3115709 1981-04-18
DE19813115709 DE3115709A1 (en) 1981-04-18 1981-04-18 CYLINDER FOR COMBUSTION ENGINES

Publications (2)

Publication Number Publication Date
EP0063258A1 EP0063258A1 (en) 1982-10-27
EP0063258B1 true EP0063258B1 (en) 1985-07-03

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ID=6130434

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EP82102544A Expired EP0063258B1 (en) 1981-04-18 1982-03-26 Cylinder and piston combination for a diesel engine

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EP (1) EP0063258B1 (en)
BR (1) BR8202219A (en)
DE (2) DE3115709A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8705785U1 (en) * 1987-04-21 1988-08-18 Stork-Werkspoor Diesel B.V., Amsterdam Piston combustion engine
JP2526947B2 (en) * 1987-12-14 1996-08-21 いすゞ自動車株式会社 Insulation engine structure
GB2284461B (en) * 1993-12-04 1996-06-26 Ae Piston Products Fibre-reinforced metal pistons for diesel engines
KR20010054470A (en) * 1999-12-07 2001-07-02 이계안 Cylinder bore structure to prevent carbon daposit on topland of piston
JP2016211396A (en) * 2015-04-30 2016-12-15 トヨタ自動車株式会社 Internal combustion engine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2447508A (en) * 1944-02-12 1948-08-24 Rudolph B Kleinfeld Engine cylinder

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2513492A (en) * 1944-02-12 1950-07-04 Rudolph B Kleinfeld Engine cylinder
US2624328A (en) * 1949-10-21 1953-01-06 Standard Motor Co Ltd Internal-combustion engine
US3463057A (en) * 1967-03-23 1969-08-26 Int Harvester Co Arrangement of cylinder and piston in engine
US4253435A (en) * 1979-02-26 1981-03-03 International Harvester Company Diesel engine and piston assembly therefor

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2447508A (en) * 1944-02-12 1948-08-24 Rudolph B Kleinfeld Engine cylinder

Also Published As

Publication number Publication date
DE3115709A1 (en) 1982-11-04
BR8202219A (en) 1983-03-29
DE3264515D1 (en) 1985-08-08
EP0063258A1 (en) 1982-10-27

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