EP0154144A2 - Air-cooled internal-combustion piston engine - Google Patents

Air-cooled internal-combustion piston engine Download PDF

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Publication number
EP0154144A2
EP0154144A2 EP85100754A EP85100754A EP0154144A2 EP 0154144 A2 EP0154144 A2 EP 0154144A2 EP 85100754 A EP85100754 A EP 85100754A EP 85100754 A EP85100754 A EP 85100754A EP 0154144 A2 EP0154144 A2 EP 0154144A2
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EP
European Patent Office
Prior art keywords
cylinder
air
cooling
tubes
internal combustion
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.)
Granted
Application number
EP85100754A
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German (de)
French (fr)
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EP0154144B1 (en
EP0154144A3 (en
Inventor
Werner Dr.-Ing. Haas
Dieter Hilker
Pavel Jan Slezak
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Khd Canada Inc Deutz R & D Division
Kloeckner Humboldt Deutz AG
Original Assignee
Khd Canada Inc Deutz R & D Division
Kloeckner Humboldt Deutz AG
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Application filed by Khd Canada Inc Deutz R & D Division, Kloeckner Humboldt Deutz AG filed Critical Khd Canada Inc Deutz R & D Division
Priority to AT85100754T priority Critical patent/ATE51433T1/en
Publication of EP0154144A2 publication Critical patent/EP0154144A2/en
Publication of EP0154144A3 publication Critical patent/EP0154144A3/en
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Publication of EP0154144B1 publication Critical patent/EP0154144B1/en
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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 
    • F02F1/02—Cylinders; Cylinder heads  having cooling means
    • F02F1/04—Cylinders; Cylinder heads  having cooling means for air cooling
    • F02F1/06—Shape or arrangement of cooling fins; Finned cylinders
    • 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
    • F02F1/26—Cylinder heads having cooling means
    • F02F1/28—Cylinder heads having cooling means for air cooling
    • F02F1/30—Finned cylinder heads
    • F02F1/34—Finned cylinder heads with means for directing or distributing cooling medium 

Definitions

  • the invention relates to an air-cooled reciprocating internal combustion engine with two or more cylinder tubes arranged side by side on a crankcase, which have cooling fins running at least on a partial circumference substantially transversely to the longitudinal axis of the cylinder tube and are provided with cylinder heads, the inlet channels of which are preferably on the cooling air inflow side and the outlet channels of which are preferably on the side Cooling air outflow side open, and with one or more air guiding devices provided on the cooling air outflow side of the cylinder tubes.
  • the T 924 diesel engine from Tatra-Werke, CSSR is known, for example, as an air-cooled reciprocating piston internal combustion engine of the type mentioned above and is described in the specialist book "Air-Cooled Vehicle Engines" by J. Mackerle, Frank'sche Verlagsbuch Kunststoff, Stuttgart, 1964 on pages 171 to 173.
  • the cylinder tubes are provided on the entire circumference and over the entire length with cooling fins running transversely to the longitudinal axis of the cylinder tube, and cooling air flows uniformly on the inflow side.
  • the cooling air flow flowing laterally around the cylinder tubes or flowing between adjacent cylinder tubes is fed on the cooling air outflow side from the cooling air guide devices to the downstream (rear) cooling fin area of the cylinder tubes.
  • cooling air flow to be supplied is to be adapted to the cooling air requirement of the cylinder tube regions which are most thermally stressed, even with limited outputs, undercooling cannot be avoided at certain loads on the internal combustion engine in the front (inflow-side) region of the cylinder tubes. These in turn justify incomplete combustion with increased pollutant emissions.
  • the air-cooled multi-cylinder reciprocating internal combustion engine according to the invention is characterized in that the cylinder tubes on the cooling air outflow side are provided with cooling fins running essentially parallel to the longitudinal axis of the cylinder tube and that at least one is provided by means of the air guiding devices Part of the cylinder tubes laterally flowing around and between adjacent Z ylinderrohren cooling air flowing in the direction parallel to the cylinder tube longitudinal axis fins is deflected.
  • a large part of the cooling air flow supplied to the internal combustion engine can be used to cool the rear thermally highly stressed cylinder tube regions and also the cylinder tube sections on the cylinder head side that are subjected to the greatest thermal stress.
  • the cooling air flow is guided in the direction of the cylinder heads, ie in the direction of the hottest points of the cylinder tubes, by means of the cooling fins running parallel to the longitudinal axis of the cylinder tube.
  • This far better utilization of the total cooling air supplied compared to the known reciprocating piston internal combustion engine and because of the much more intensive cooling of the hot cylinder tube areas and the possibility of also being able to use the cooling air of the cylinder tubes for cooling the cylinder heads, is the basis for a higher power yield in one Internal combustion engine created.
  • the air guiding devices can be designed as sheets which, in one piece, preferably delimit a row of cylinders laterally and downstream.
  • the cylinder tubes themselves do not require any additional manufacturing effort, but rather offer the possibility of far more rational and cost-effective production due to special configurations which are characterized and described in more detail in the dependent claims and in the following.
  • the cooling air mass flow to be supplied to the cooling fins running parallel to the longitudinal axis of the cylinder tube can be further increased due to the reduced flow resistances.
  • the transversely to the longitudinal axis of the cylinder tube cooling fins have a continuously decreasing fin height or also have one or more crankcase-side sections with cooling fins constantly reduced fin height.
  • the height of the cylinder tube section provided with cooling fins running transversely to the longitudinal axis of the cylinder tube is preferably adapted to the length of the cooling fins running parallel to the longitudinal axis of the cylinder tube, so that cylinder tubes with non-ribbed sections and ribbed sections according to the invention are also used in production engineering terms.
  • these can be Design of the cylinder tubes according to the invention on the basis of the same cooling fan output achieve increases in the cooling air mass flow to be promoted of approximately 50% compared to known cylinder tube configurations of reciprocating piston internal combustion engines.
  • the cylinder tubes are preferably formed in a circumferential area on the cooling air inflow side without cooling ribs or with transverse to . Providing cooling fins of reduced fin height running along the longitudinal axis of the cylinder tube, which can make a further contribution to the homogenization of the cylinder tube temperatures and reduction of the flow resistances. The risk of hypothermia in individual cylinder tube areas and sections and thus the risk of excessively high pollutant emissions is thus effectively reduced.
  • valve stems of the intake and exhaust valves machine in a manner analogous to the known Hubkolbenbrennkraft Tatra T 924 ühl Kunststoffzuström- at K or cooling air outflow side and arranged such that the valve stems extending through the Mut.in twisted at an acute angle to the cylinder row longitudinal axis is disposed, is the cooling air inflow-side circumferential region of the cylinder tubes preferably formed without fins, the cooling fins extending transversely to the longitudinal axis of the cylinder tube in the adjacent circumferential region being connected in a heat-conducting manner, so that a continuous heat flow of the cooling fins provided in the area of an exhaust valve of the cylinder is adjacent to those in the region of the inlet valve of the be Cylinders provided cooling fins in a geous manner contributes to the equalization of the temperatures of adjacent cylinder tubes of a cylinder series.
  • cooling fins of the cylinder tubes Due to the arrangement and design of the cooling fins of the cylinder tubes according to the invention
  • the production (casting mold, mechanical processing methods, casting cores, etc.) is far less complex, and furthermore the maintenance effort is considerably easier, for. B. due to simplified cleaning of significantly fewer fin surfaces.
  • the cooling fins are also arranged in areas that are easily accessible for cleaning even in reciprocating internal combustion engines with a V-shaped arrangement of the cylinder rows.
  • the air guiding devices themselves are components that are easy to manufacture.
  • the air guiding devices are preferably designed in such a way that the cooling air, which is already heated on the circumferential areas of the cylinder tubes on the cylinder head side due to the higher temperature level prevailing there, can be discharged into the surroundings through outflow openings provided in the air guiding devices, so that only those from the crankcase-side cylinder tube sections flowing relatively cold cooling air is used to cool the rear hot cylinder tube areas.
  • higher cooling air velocities and thus higher cooling air mass flows can also be achieved in the cylinder tube peripheral regions.
  • the air-guiding devices on the cylinder head side in areas of the cylinder row and in the areas to be allocated in the interspaces of adjacent cylinder tubes have a cross-sectional structure that extends essentially up to close to the cooling air outflow-side end faces of cooling ribs running transversely to the longitudinal axis of the cylinder tube. This can be accomplished in a structurally simple manner, for example, by indentations, offsets, etc.
  • the development of the invention according to claim 11 promotes due to the position of the outflow openings in relation to the respective exhaust valves or exhaust ducts, the equalization of the cylinder tube temperatures by achieving higher air velocities in the vicinity of the exhaust duct than in the vicinity of the intake duct.
  • the cylinder heads in the area of the end of the cylinder tube on the cooling air outflow side are also provided with cooling fins oriented parallel to the longitudinal axis of the cylinder tube and are provided with air baffles, so that the cooling air flow of the rear cylinder tube areas is provided by the special design of the air guide devices of the cylinder tubes and the air guide plates of the cylinder heads Outflow from the cooling fins of the cylinder tubes, which run parallel to the longitudinal axis of the cylinder tube, also for cooling the rear cylinder head region on the end of the cylinder tube, ie. H. essentially in the area of the outlet channel or outlet valve, can be used for cooling.
  • the air-guiding plates in areas near the outlet duct can also contain additional cooling-air outlet openings in order to have more intensive cooling achieved here through increased cooling-air mass flows.
  • the cylinder tubes are usually braced as special components with the crankcase via tie rods, significant savings in main machining steps can thus be achieved, so that in addition to the functional advantages of the internal combustion engine according to the invention, there is also an overall much lower manufacturing and assembly effort and thus ultimately realize significant cost advantages.
  • a circumferential reinforcing rib provided in the respective cylinder head end regions of the cylinder tubes can also contribute, as proposed in a further embodiment of the invention.
  • FIGS. 1 to 3 generally designates an air-cooled reciprocating piston internal combustion engine, which is provided with a crankcase 2, cylinder tubes 3 arranged next to one another and single cylinder heads 4.
  • the cylinder tubes 3 are formed in one piece with the crankshaft housing 2 and the outlet channels 5 of the individual cylinder heads 4 extend, as can be seen from FIGS. 1 and 2, on the cooling air outflow side.
  • the inlet duct lies on the cooling air inflow side and opens into the area of the cooling air inflow side, the valves of the outlet and inlet ducts 5 and 6, which are not shown in detail, being arranged such that the planes running through the valve stems are at an acute angle (approx . 30 °) to the cylinder axis 7.
  • the cylinder tubes 3 In a cylinder tube section on the cylinder head side, the cylinder tubes 3 have cooling fins 9 running transversely to the cylinder tube longitudinal axes 8, these cooling fins 9 running transversely to the cylinder tube longitudinal axis 8, as can be seen from the various views according to FIGS. 1 to 3, only in a rear (downstream) side Circumferential region of the cylinder head section on the cylinder head side are provided.
  • the cylinder tubes 3 are thus formed without cooling ribs.
  • the cooling fins which run essentially parallel to the longitudinal axis 8 of the cylinder tube 11 are arranged, which essentially extend to the end faces 12 of the cylinder tubes 3 on the end side of the cylinder head and are provided on the cylinder tubes 3 at an axial distance from the crankshaft housing 2.
  • the cooling fins 11 running parallel to the longitudinal axis 8 of the cylinder tube and the cooling fins 9 of the cylinder tubes 3 of a row of cylinders 3 extending transversely to the longitudinal axis 8 of the cylinder tube are formed in one piece.
  • the air guiding device 13 On the cooling air outflow side of the cylinder tubes 3, the air guiding device 13 is provided, which is kinked on the last cylinder tubes 3 of the row of cylinders, so that the cylinder row is completely encased on the side and on the outflow side by the air guiding device with a sufficient throughflow distance 14 (FIG. 3).
  • the air guiding device 13 At the locations of the cylinder tubes 3 at which cooling fins 9 are provided which run transversely to the longitudinal axis 8 of the cylinder tube, the air guiding device 13 has a cross-sectional structure (indentations 15) on the cylinder head side that extends close to the downstream end faces of the cooling fins 9.
  • Outflow openings 16 are provided in these indentations 15, so that the cooling air (arrows 20a) flowing in these upper hot cylinder tube sections can flow directly into the surroundings.
  • the outflow openings 16 for cooling air flowing between the cylinder tubes are arranged asymmetrically to the central planes 21 of adjacent cylinder tubes 3, namely offset to the respective outlet ducts 5, so that the peripheral regions of the cylinder tubes or their cooling fins 9 near the outlet duct are cooled more intensively than the opposite peripheral regions of the Cooling fins (inlet duct areas) of the neighboring cylinder tube.
  • the supplied cooling air is deflected after flowing through the respective non-ribbed front and side areas of the cylinder tubes 3 from the air guiding device 13 on the cooling air outflow side in the direction of the cooling fins 11 running parallel to the longitudinal axis 7 of the cylinder tube (arrows 20b), so that this total cooling air flow, which is a relatively low one Has temperature level, can be used to cool the rear hot cylinder tube area and is led through the parallel cooling fins 11 to the hottest area of the cylinder tubes 3 on the cylinder head side. Since the transverse cooling fins 11 are arranged at a distance from the crankshaft housing 2, it is to a high degree ensured that air accumulations, backflows, swirls etc. are avoided in the downstream flow space 14 of the air guiding device.
  • This design of the cooling air duct and the arrangement and design of the cooling fins 9 and 11 results in an optimal utilization of the total cooling air to be supplied and a substantial homogenization of the overall cylinder tube temperatures, so that this optimally fulfills the requirements for an increase in performance of the internal combustion engine and a reduction in temperature voltages given are.
  • the connection of the cooling fins 9 of adjacent cylinder tubes 3 running transversely to the longitudinal axis 8 of the cylinder tube ensures that a steady heat flow takes place from the hot peripheral region of a cylinder tube 3 (outlet channel 5) to the colder peripheral region (inlet channel 6) of the neighboring cylinder tube 3.
  • the cylinder heads 4 also have cooling fins 17 oriented parallel to the cylinder tube axis 8 at their end region on the cylinder tube side and are provided with air baffles 18 on the cooling air outflow side.
  • the air guiding device 13 and the extending also over the cylinder heads 4 of the entire row of cylinders air guide plate 18 have on the downstream side to each other at a distance and are bent over at their edges at about 90 0, so that the cooling air of the cylinder tubes after flowing arranged parallel to the cylinder tube longitudinal axis 8
  • Cooling fins 11 is directed in the direction of the parallel oriented cooling fins 17 of the cylinder heads 4 and can flow together with the cooling air (arrows 20c) of the cylinder heads in this area into the environment (FIG. 3).
  • the cooling air of the cylinder tubes 3 also makes a contribution to cooling the hot end regions of the cylinder heads 4 on the end of the cylinder tubes 4.
  • the air baffles 18 of the cylinder heads 4 additionally have outlet openings 22, so that the cooling air can flow directly into the surroundings in regions of the outlet ducts 5.
  • the reciprocating piston internal combustion engine 1 Due to the one-piece design of the cylinder tubes 3, the crankshaft housing 2 and the cooling fins 9 and 11, the reciprocating piston internal combustion engine 1 according to the invention is designed as an overall unit with excellent stability properties that is simple to manufacture and therefore inexpensive to manufacture.
  • the stability structure of the cylinder tubes 3 in the region 12 on the end of the cylinder head can be improved by a reinforcing rib 19 extending over the entire circumference of the cylinder tubes 3.

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

Abstract

An air-cooled, reciprocating piston, internal combustion engine has at least two adjacent cylinder barrels with a plurality of cooling ribs lying substantially perpendicular to the longitudinal axes of the barrels on at least part of the periphery thereof. The intake ports of the cylinder heads are located on the cooling air inlet side while the exhaust ports are located on the cooling air outlet side, and an air deflection cover overlies the cylinder barrels on the cooling air outlet side. The cylinder barrels are provided on the cooling air outlet side with cooling ribs lying substantially parallel to the longitudinal axes of the cylinder barrels. The air deflecting cover is of a configuration such that at least some of the cooling air flowing, in the area adjoining the crankcase, around and between adjacent cylinder barrels, is deflected toward these parallel lying ribs, so that essentially the total flow of cooling air supplied may be used to cool the hottest area of a cylinder barrels.

Description

Die Erfindung bezieht sich auf eine luftgekühlte Hubkolbenbrennkraftmaschine mit zwei oder mehreren an einem Kurbelgehäuse nebeneinander angeordneten Zylinderrohren, die zumindest an einem Teilumfang im wesentlichen quer zur Zylinderrohrlängsachse verlaufende Kühlrippen aufweisen sowie mit Zylinderköpfen versehen sind, deren Einlaßkanäle bevorzugt auf der Kühlluftzuströmseite und deren Auslaßkanäle bevorzugt auf der Kühlluftabströmseite münden, und mit einer oder mehreren auf der Kühlluftabströmseite der Zylinderrohre vorgesehenen Luftleiteinrichtungen.The invention relates to an air-cooled reciprocating internal combustion engine with two or more cylinder tubes arranged side by side on a crankcase, which have cooling fins running at least on a partial circumference substantially transversely to the longitudinal axis of the cylinder tube and are provided with cylinder heads, the inlet channels of which are preferably on the cooling air inflow side and the outlet channels of which are preferably on the side Cooling air outflow side open, and with one or more air guiding devices provided on the cooling air outflow side of the cylinder tubes.

Als luftgekühlte Hubkolbenbrennkraftmaschine der vorstehend genannten Gattung ist beispielsweise der Dieselmotor T 924 der Tatra-Werke, CSSR, bekannt und in dem Fachbuch "Luftgekühlte Fahrzeugmotoren" von J. Mackerle, Frank'sche Verlagsbuchhandlung, Stuttgart, 1964 auf den Seiten 171 bis 173 beschrieben. Hierbei sind die Zylinderrohre am gesamten Umfang und über die gesamte Länge mit quer zur Zylinderrohrlängsachse verlaufenden Kühlrippen versehen und werden zuströmseitig gleichmäßig von Kühlluft angeströmt. Der die Zylinderrohre seitlich umströmende bzw. zwischen benachbarten Zylinderrohren strömende Kühlluftstrom wird auf der Rühlluftabströmseite von den Kühlluftleiteinrichtungen dem abströmseitigen (hinteren) Kühlrippenbereich der Zylinderrohre zugeführt.The T 924 diesel engine from Tatra-Werke, CSSR, is known, for example, as an air-cooled reciprocating piston internal combustion engine of the type mentioned above and is described in the specialist book "Air-Cooled Vehicle Engines" by J. Mackerle, Frank'sche Verlagsbuchhandlung, Stuttgart, 1964 on pages 171 to 173. Here, the cylinder tubes are provided on the entire circumference and over the entire length with cooling fins running transversely to the longitudinal axis of the cylinder tube, and cooling air flows uniformly on the inflow side. The cooling air flow flowing laterally around the cylinder tubes or flowing between adjacent cylinder tubes is fed on the cooling air outflow side from the cooling air guide devices to the downstream (rear) cooling fin area of the cylinder tubes.

Bedingt durch die Lage des Auslaßkanals der Brennkraftmaschine auf der Kühlluftabströmseite sind naturgemäß die kühlluftabströmseitigen (hinteren) Bereiche der Zylinderrohre und hierbei insbesondere die zylinderkopfseitigen Zylinderrohrabschnitte thermisch am höchsten belastet. Diesen Bereichen kann allerdings bei der bekannten Hubkolbenbrennkraftmaschine ausschließlich bereits an den seitlichen und insbesondere zylinderkopfseitigen Umfangsbereichen der Zylinderrohre zur Kühlung genutzte und somit erwärmte Kühlluft zugeführt werden. Somit steht diese vorbekannte Hubkolbenbrennkraftmaschine im Hinblick auf mögliche Uberhitzungen nur für begrenzte Leistungen zur Verfügung. Da darüber hinaus selbst bei begrenzten Leistungen der zuzuführende Kühlluftstrom dem Kuhlluftbedarf der thermisch am stärksten beanspruchten Zylinderrohrbereiche anzupassen ist, sind bei bestimmten Belastungen der Brennkraftmaschine im vorderen (zuströmseitigen) Bereich der Zylinderrohre Unterkühlungen nicht zu vermeiden. Diese wiederum begründen eine unvollständige Verbrennung mit erhöhter Schadstoffemission.Due to the position of the exhaust duct of the internal combustion engine on the cooling air outflow side, the cooling air outflow-side (rear) regions of the cylinder tubes and, in particular, the cylinder head-side cylinder tube sections are naturally subjected to the greatest thermal stress. In the known reciprocating piston internal combustion engine, however, these areas can only be supplied to the lateral and in particular the cylinder head-side circumferential areas of the cylinder tubes used for cooling and thus heated cooling air. This known reciprocating piston internal combustion engine is therefore only available for limited outputs with regard to possible overheating. In addition, since the cooling air flow to be supplied is to be adapted to the cooling air requirement of the cylinder tube regions which are most thermally stressed, even with limited outputs, undercooling cannot be avoided at certain loads on the internal combustion engine in the front (inflow-side) region of the cylinder tubes. These in turn justify incomplete combustion with increased pollutant emissions.

Es ist daher Aufgabe der vorliegenden Erfindung, die Kühlung der Zylinderrohre mit einem geringstmöglichen Fertigungsaufwand bei einer luftgekühlten Hubkolbenbrennkraftmaschine der eingangs genannten Art soweit zu verbessern, daß Leistungssteigerungen der Hubkolbenbrennkraftmaschine möglich sind.It is therefore an object of the present invention to improve the cooling of the cylinder tubes with the least possible production outlay in an air-cooled reciprocating piston internal combustion engine of the type mentioned at the outset, so that increases in performance of the reciprocating piston internal combustion engine are possible.

Zur Lösung dieser Aufgabe ist die luftgekühlte mehrzylindrige Hubkolbenbrennkraftmaschine nach der Erfindung dadurch gekennzeichnet, daß die Zylinderrohre auf der Kühlluftabströmseite mit im wesentlichen parallel zur Zylinderrohrlängsachse verlaufenden Kühlrippen versehen sind und daß mittels der Luftleiteinrichtungen zumindest ein Teil der die Zylinderrohre seitlich umströmenden bzw. zwischen benachbarten Zylinderrohren strömenden Kühlluft in Richtung der parallel zur Zylinderrohrlängsachse verlaufenden Kühlrippen umlenkbar ist. Damit kann ein Großteil des der Brennkraftmaschine zugeführten Kühlluftstroms zur Kühlung der hinteren thermisch hoch belasteten Zylinderrohrbereiche und auch der thermisch am stärksten beanspruchten zylinderkopfseitigen Zylinderrohrabschnitte herangezogen werden. Der Kühlluftstrom wird dabei mittels der parallel zur Zylinderrohrlängsachse verlaufenden Kühlrippen in Richtung der Zylinderköpfe, d. h. also in Richtung der heißesten Stellen der Zylinderrohre geführt. Durch diese gegenüber der bekannten Hubkolbenbrennkraftmaschine weit verbesserte Ausnutzung der insgesamt zugeführten Kühlluft und aufgrund der wesentlich intensiveren Kühlung der heißen Zylinderrohrbereiche sowie der Möglichkeit, die Kühlluft der Zylinderrohre auch noch zur Kühlung der Zylinderköpfe heranziehen zu können, ist damit die Grundlage für eine höhere Leistungsausbeute bei einer Brennkraftmaschine geschaffen. Die Luftleiteinrichtungen können als Bleche ausgebildet sein, die bevorzugt in einstückiger Ausbildung eine Zylinderreihe seitlich und abströmseitig begrenzen. Die Zylinderrohre selbst erfordern durch die erfindungsgemäße Anordnung und Gestaltung von Kühlrippen keinen Fertigungsmehraufwand, sondern bieten durch besondere Ausgestaltungen, die in Unteransprüchen und im Nachfolgenden näher gekennzeichnet und beschrieben sind, sogar die Möglichkeit einer weit rationelleren und kostengünstigeren Herstellung.To achieve this object, the air-cooled multi-cylinder reciprocating internal combustion engine according to the invention is characterized in that the cylinder tubes on the cooling air outflow side are provided with cooling fins running essentially parallel to the longitudinal axis of the cylinder tube and that at least one is provided by means of the air guiding devices Part of the cylinder tubes laterally flowing around and between adjacent Z ylinderrohren cooling air flowing in the direction parallel to the cylinder tube longitudinal axis fins is deflected. Thus, a large part of the cooling air flow supplied to the internal combustion engine can be used to cool the rear thermally highly stressed cylinder tube regions and also the cylinder tube sections on the cylinder head side that are subjected to the greatest thermal stress. The cooling air flow is guided in the direction of the cylinder heads, ie in the direction of the hottest points of the cylinder tubes, by means of the cooling fins running parallel to the longitudinal axis of the cylinder tube. This far better utilization of the total cooling air supplied compared to the known reciprocating piston internal combustion engine and because of the much more intensive cooling of the hot cylinder tube areas and the possibility of also being able to use the cooling air of the cylinder tubes for cooling the cylinder heads, is the basis for a higher power yield in one Internal combustion engine created. The air guiding devices can be designed as sheets which, in one piece, preferably delimit a row of cylinders laterally and downstream. Due to the arrangement and design of cooling fins according to the invention, the cylinder tubes themselves do not require any additional manufacturing effort, but rather offer the possibility of far more rational and cost-effective production due to special configurations which are characterized and described in more detail in the dependent claims and in the following.

Um insbesondere den relativ kalten Kühlluftstrom aus den unteren kurbelgehäuseseiten Zylinderrohrabschnitten zur Kühlung des hinteren Zylinderrohrbereiches heranziehen zu können, reichen die parallel zur Zylinderrohrlängsachse verlaufenden Kühlrippen bevorzugt bis zu den zylinderkopfseitigen Endflächen der Zylinderrohre und sind mit einem axialen Abstand zum Kurbelgehäuse an den Zylinderrohren vorgesehen (Patentanspruch 2).In order to be able in particular to use the relatively cold cooling air flow from the lower crankcase-side cylinder tube sections for cooling the rear cylinder tube region, they are sufficient parallel to the longitudinal axis of the cylinder tube extending cooling fins preferably up to the cylinder head end faces of the cylinder tubes and are provided with an axial distance from the crankcase on the cylinder tubes (claim 2).

Durch die Weiterbildung der Erfindung nach Patentanspruch 3 kann der den parallel zur Zylinderrohrlängsachse verlaufenden Kühlrippen zuzuführende Kühlluftmassenstrom aufgrund der verringerten Strömungswiderstände weiter erhöht werden. In Anpassung an die sich in Richtung des Kurbelgehäuses verringernden thermischen Belastungen der Zylinderrohre können dabei z. B. die quer zur Zylinderrohrlängsachse verlaufenden Kühlrippen eine kontinuierlich abnehmende Rippenhöhe aufweisen oder aber auch einen oder mehrere kurbelgehäuseseite Abschnitte mit KÜhlrippen konstant verringerter Rippenhöhe aufweisen. Ein weiterer wesentlicher Vorteil dieser Ausgestaltung der Erfindung besteht darin, daß in idealer Weise dem unterschiedlichen Kühlbedarf der einzelnen Zylinderrohrabschnitte Rechnung getragen ist, was eine Vergleichmäßigung der Zylinderrohrtemperaturen ermöglicht.Through the development of the invention according to claim 3, the cooling air mass flow to be supplied to the cooling fins running parallel to the longitudinal axis of the cylinder tube can be further increased due to the reduced flow resistances. In adaptation to the decreasing thermal loads on the cylinder tubes in the direction of the crankcase, z. B. the transversely to the longitudinal axis of the cylinder tube cooling fins have a continuously decreasing fin height or also have one or more crankcase-side sections with cooling fins constantly reduced fin height. Another significant advantage of this embodiment of the invention is that the different cooling requirements of the individual cylinder tube sections are taken into account in an ideal manner, which enables the cylinder tube temperatures to be equalized.

Im Hinblick auf die angestrebte optimierte Kühlung der heißesten Bereiche der Zylinderrohre und die Vergleichmäßigung der Zylinderrohrtemperaturen hat sich auch die Weiterbildung der Erfindung nach Patentanspruch 4 als sehr vorteilhaft herausgestellt. Die Höhe des mit quer zur Zylinderrohrlängsachse verlaufenden Kühlrippen versehenen Zylinderrohrabschnittes ist hierbei bevorzugt der Länge der-parallel zur Zylinderrohrlängsachse verlaufenden Kühlrippen angepaßt, so daß auch in fertigungstechnisch vorteilhafter Weise Zylinderrohre mit unverrippten Abschnit ten und erfindungsgemäß verrippten Abschnitten Verwendung finden. Wie Versuche gezeigt haben, lassen sich bei diesen erfindungsgemäßen Gestaltungen der Zylinderrohre unter Zugrundelegung einer gleichen Kühlgebläseleistung Steigerungen des zu fördernden Kühlluftmassenstromes von annähernd 50 % gegenüber bekannten Zylinderrohrausbildungen von Hubkolbenbrennkraftmaschinen erzielen. Da die Einlaßkanäle auf der Kühlluftzuströmseite vorgesehen sind, sind die Zylinderrohre bevorzugt in einem Umfangsbereich auf der Kühlluftzuströmseite kühlrippenfrei ausgebildet oder mit quer zur.Zylinderrohrlängsachse verlaufenden Kühlrippen verringerter Rippenhöhe versehen, wodurch ein weiterer Beitrag zur Vergleichmäßigung der Zylinderrohrtemperaturen und Verringerung der Strömungswiderstände geleitet werden kann. Die Gefahr von Unterkühlungen einzel-τer Zylinderrohrbereiche und -abschnitte und somit die Gefahr von übermäßig hoher Schadstoffemission ist damit wirksam verringert.In view of the desired optimized cooling of the hottest areas of the cylinder tubes and the equalization of the cylinder tube temperatures, the development of the invention according to claim 4 has also proven to be very advantageous. The height of the cylinder tube section provided with cooling fins running transversely to the longitudinal axis of the cylinder tube is preferably adapted to the length of the cooling fins running parallel to the longitudinal axis of the cylinder tube, so that cylinder tubes with non-ribbed sections and ribbed sections according to the invention are also used in production engineering terms. As experiments have shown, these can be Design of the cylinder tubes according to the invention on the basis of the same cooling fan output achieve increases in the cooling air mass flow to be promoted of approximately 50% compared to known cylinder tube configurations of reciprocating piston internal combustion engines. Since the inlet channels are provided on the cooling air inflow side, the cylinder tubes are preferably formed in a circumferential area on the cooling air inflow side without cooling ribs or with transverse to . Providing cooling fins of reduced fin height running along the longitudinal axis of the cylinder tube, which can make a further contribution to the homogenization of the cylinder tube temperatures and reduction of the flow resistances. The risk of hypothermia in individual cylinder tube areas and sections and thus the risk of excessively high pollutant emissions is thus effectively reduced.

Sind die Ventilschäfte des Einlaß- und Auslaßventils in analoger Weise wie bei der bekannten Hubkolbenbrennkraft maschine Tatra T 924 auf der Kühlluftzuström- bzw. Kühl luftabströmseite derart angeordnet, daß die durch die Ventilschäfte verlaufende Ebene.in einem spitzen Winkel zur Zylinderreihenlängsachse verdreht angeordnet ist, ist der kühlluftzuströmseitige Umfangsbereich der Zylinderrohre bevorzugt kühlrippenfrei ausgebildet, wobei die quer zur Zylinderrohrlängsachse verlaufenden Kühlrippen im benachbarten Umfangsbereich in wärmeleitender Ver bindung stehen, so daß ein stetiger Wärmefluß der im Be reich eines Auslaßventils eines Zylinders vorgesehenen Kühlrippen zu den im Bereich des Einlaßventils des be nachbarten Zylinders vorgesehenen Kühlrippen in vor teilhafter Weise einen Beitrag zur Vergleichmäßigung der Temperaturen auch benachbarter Zylinderrohre einer Zylin derreihe leistet. Durch die erfindungsgemäße Anordnung und Gestaltung der Kühlrippen der Zylinderrohre gestaltet sich darüber hinaus die Fertigung (Gießform, mechanische Bearbeitungsverfahren, Gußkerne etc.) weit weniger aufwendig, und ferner ist der Wartungsaufwand erheblich erleichtert, z. B. aufgrund vereinfachter Reinigung von wesentlich weniger Kühlrippenoberflächen. Des weiteren sind die Kühlrippen auch noch in Bereichen angeordnet, die auch bei Hubkolbenbrennkraftmaschinen mit V-förmiger Anordnung der Zylinderreihen für eine Reinigung leicht zugänglich sind.If the valve stems of the intake and exhaust valves machine in a manner analogous to the known Hubkolbenbrennkraft Tatra T 924 ühlluftzuström- at K or cooling air outflow side and arranged such that the valve stems extending through the Ebene.in twisted at an acute angle to the cylinder row longitudinal axis is disposed, is the cooling air inflow-side circumferential region of the cylinder tubes preferably formed without fins, the cooling fins extending transversely to the longitudinal axis of the cylinder tube in the adjacent circumferential region being connected in a heat-conducting manner, so that a continuous heat flow of the cooling fins provided in the area of an exhaust valve of the cylinder is adjacent to those in the region of the inlet valve of the be Cylinders provided cooling fins in a geous manner contributes to the equalization of the temperatures of adjacent cylinder tubes of a cylinder series. Due to the arrangement and design of the cooling fins of the cylinder tubes according to the invention In addition, the production (casting mold, mechanical processing methods, casting cores, etc.) is far less complex, and furthermore the maintenance effort is considerably easier, for. B. due to simplified cleaning of significantly fewer fin surfaces. Furthermore, the cooling fins are also arranged in areas that are easily accessible for cleaning even in reciprocating internal combustion engines with a V-shaped arrangement of the cylinder rows.

Die Luftleiteinrichtungen selbst sind einfach herzustellende Bauteile. Bevorzugt sind die Luftleiteinrichtungen derart gestaltet sind, daß die Kühlluft, die an den zylinderkopfseitigen Umfangsbereichen der Zylinderrohre aufgrund des dort herrschenden höheren Temperaturniveaus bereits aufgeheizt ist, durch in den Luftleiteinrichtungen vorgesehene Abströmöffnungen in die Umgebung abgeführt werden kann, so daß nur die aus den kurbelgehäuseseitigen Zylinderrohrabschnitten strömende relativ kalte Kühlluft zur Kühlung der hinteren heißen Zylinderrohrbereiche herangezogen wird. Hierdurch lassen sich auch in den zylinderkopfseitigen Zylinderrohrumfangsbereichen höhere Kühlluftgeschwindigkeiten und somit höhere Kühlluftmassenströme realisieren. Um Verwirbelungen bei der durch die Abströmöffnungen abzuführenden Kühlluft weitgehend zu vermeiden, weisen die Luftleiteinrichtungen zylinderkopfseitig in Zylinderreihenendbereichen und in den Zwischenräumen benachbarter Zylinderrohre zuzuordnenden Bereichen eine im wesentlichen bis nahe an kühlluftabströmseitige Endflächen von quer zur Zylinderrohrlängsachse verlaufenden Kühlrippen reichende Querschnittsstruktur auf. Dies kann beispielsweise durch Einbuchtungen, Abkröpfungen etc. auf baulich einfache Weise bewerkstelligt werden. Die Weiterbildung der Erfindung nach Patentanspruch 11 fördert durch die zu den jeweiligen Auslaßventilen bzw. Auslaßkanälen versetzte Lage der Abströmöffnungen die Vergleichmäßigung der Zylinderrohrtemperaturen, indem in Auslaßkanalnähe höhere Luftgeschwindigkeiten erreicht werden als in Einlaßkanalnähe.The air guiding devices themselves are components that are easy to manufacture. The air guiding devices are preferably designed in such a way that the cooling air, which is already heated on the circumferential areas of the cylinder tubes on the cylinder head side due to the higher temperature level prevailing there, can be discharged into the surroundings through outflow openings provided in the air guiding devices, so that only those from the crankcase-side cylinder tube sections flowing relatively cold cooling air is used to cool the rear hot cylinder tube areas. As a result, higher cooling air velocities and thus higher cooling air mass flows can also be achieved in the cylinder tube peripheral regions. In order to largely avoid turbulence in the cooling air to be discharged through the outflow openings, the air-guiding devices on the cylinder head side in areas of the cylinder row and in the areas to be allocated in the interspaces of adjacent cylinder tubes have a cross-sectional structure that extends essentially up to close to the cooling air outflow-side end faces of cooling ribs running transversely to the longitudinal axis of the cylinder tube. This can be accomplished in a structurally simple manner, for example, by indentations, offsets, etc. The development of the invention according to claim 11 promotes due to the position of the outflow openings in relation to the respective exhaust valves or exhaust ducts, the equalization of the cylinder tube temperatures by achieving higher air velocities in the vicinity of the exhaust duct than in the vicinity of the intake duct.

Entsprechend der Ausgestaltung der Erfindung nach Patentanspruch 12 sind auch die Zylinderköpfe im zylinderrohrendseitigen Bereich auf der Kühlluftabströmseite mit parallel zur Zylinderrohrlängsachse ausgerichteten Kühlrippen und mit Luftleitblechen versehen, so daß durch die besondere Gestaltung der Luftleiteinrichtungen der Zylinderrohre und der Luftleitbleche der Zylinderköpfe der Kühlluftstrom der hinteren Zylinderrohrbereiche nach Abströmen von den parallel zur Zylinderrohrlängsachse verlaufenden Kühlrippen der Zylinderrohre noch zur Kühlung des zylinderrohrendseitigen hinteren Zylinderkopfbereiches, d. h. also im wesentlichen im Bereich des Auslaßkanals bzw. Auslaßventils, zur Kühlung herangezogen werden kann. In analoger Weise wie die Luftleiteinrichtungen der Zylinderrohre können dabei auch die Luftleitbleche in Bereichen nahe des Auslaßkanals noch zusätzliche Kühlluftauslaßöffnungen enthalten, um hier eine intensivere Kühlung durch erhöhte Kühlluftmassenströme realisiert zu haben.According to the embodiment of the invention according to claim 12, the cylinder heads in the area of the end of the cylinder tube on the cooling air outflow side are also provided with cooling fins oriented parallel to the longitudinal axis of the cylinder tube and are provided with air baffles, so that the cooling air flow of the rear cylinder tube areas is provided by the special design of the air guide devices of the cylinder tubes and the air guide plates of the cylinder heads Outflow from the cooling fins of the cylinder tubes, which run parallel to the longitudinal axis of the cylinder tube, also for cooling the rear cylinder head region on the end of the cylinder tube, ie. H. essentially in the area of the outlet channel or outlet valve, can be used for cooling. In an analogous manner to the air-guiding devices of the cylinder tubes, the air-guiding plates in areas near the outlet duct can also contain additional cooling-air outlet openings in order to have more intensive cooling achieved here through increased cooling-air mass flows.

Durch die Vorteile und Wirkungen der Erfindung (verbesserte Kühlung, Vergleichmäßigung der Zylinderrohrtempera- turen, verringerter Fertigungsaufwand) ist in idealer Weise bei einer luftgekühlten Brennkraftmaschine die Möglichkeit geschaffen, die Zylinderrohre und das Kurbelgehäuse einstückig auszubilden, wobei auch die quer zur Zylinderrohrlängsachse verlaufenden Kühlrippen benachbarter Zylinderrohre in diese einstückige Ausbildung mit einbezogen sein können, so daß das Kurbelgehäuse und die Zylinderrohre sich als einfach herzustellende Kompakteinheit darstellen.Due to the advantages and effects of the invention (improved cooling, homogenization ylinderrohrtempera- structures of Z, reduced manufacturing complexity) is provided in an ideal manner in an air-cooled internal combustion engine, the possibility of forming the cylinder tubes and the crank in one piece, wherein the transverse to the cylinder tube longitudinal axis fins of adjacent Cylinder tubes can be included in this one-piece design, so that the crankcase and the cylinder tubes are a compact unit that is easy to manufacture.

Gegenüber bekannten luftgekühlten Brennkraftmaschinen, bei denen die Zylinderrohre üblicherweise als besondere Bauteile mit dem Kurbelgehäuse über Zuganker verspannt sind, sind somit wesentliche Einsparungen an Hauptbearbeitungsschritten zu erzielen, so daß sich neben den funktionellen Vorteilen der erfindungsgemäßen Brennkraftmaschine auch noch ein ingesamt weit verringerter Fertigungs- und Montageaufwand und somit letztlich erhebliche Kostenvorteile realisieren lassen. Durch die einstückige Ausbildung der Zylinderrohre mit dem Kurbelwellengehäuse und die Verbindung benachbarter Zylinder zueinander durch die quer zur Zylinderrohrlängsachse verlaufenden Kühlrippen läßt sich auch die Stabilität der Zylinderrohre und des Kurbelwellengehäuses verstärken, so daß diese in hohem Maße geeignet sind, z. B. höheren Torsionsbeanspruchungen standzuhalten. Zur weiteren Verbesserung dieser Stabilitätsstruktur kann darüber hinaus auch noch, wie in einer weiteren Ausgestaltung der Erfindung vorgeschlagen, eine in den jeweiligen Zylinderkopfendbereichen der Zylinderrohre vorgesehene umlaufende Verstärkungsrippe beitragen.Compared to known air-cooled internal combustion engines, in which the cylinder tubes are usually braced as special components with the crankcase via tie rods, significant savings in main machining steps can thus be achieved, so that in addition to the functional advantages of the internal combustion engine according to the invention, there is also an overall much lower manufacturing and assembly effort and thus ultimately realize significant cost advantages. Due to the one-piece design of the cylinder tubes with the crankshaft housing and the connection of adjacent cylinders to each other through the cooling fins extending transversely to the longitudinal axis of the cylinder tube, the stability of the cylinder tubes and the crankshaft housing can also be strengthened, so that they are highly suitable, e.g. B. withstand higher torsional loads. To further improve this stability structure, a circumferential reinforcing rib provided in the respective cylinder head end regions of the cylinder tubes can also contribute, as proposed in a further embodiment of the invention.

Zur weiteren Erläuterung der Erfindung wird auf die Zeichnungen verwiesen, in denen ein Ausführungsbeispiel der Erfindung vereinfacht dargestellt ist. Es zeigen:

  • Fig. l eine Ansicht einer Zylinderreihe eines Ausführungsbeispiels der Brennkraftmaschine von der Kühlluftabströmseite;
  • Fig. 2 einen Schnitt durch zwei Zylinderrohre und zwei Zy-- linderköpfe der Zylinderreihe entsprechend der Linie II-II in Fig. l;
  • Fig. 3 eine Seitenansicht eines Zylinderrohres mit montiertem Zylinderkopf und angebauten Luftleiteinrichtungen bzw. Luftleitblechen gemäß Fig. 1.
To further explain the invention, reference is made to the drawings, in which an embodiment of the invention is shown in simplified form. Show it:
  • 1 shows a view of a row of cylinders of an exemplary embodiment of the internal combustion engine from the cooling air outflow side;
  • 2 shows a section through two cylinder tubes and two cylinder heads of the row of cylinders according to the line II-II in FIG. 1;
  • 3 shows a side view of a cylinder tube with a mounted cylinder head and attached air guiding devices or air guiding plates according to FIG. 1.

Soweit im einzelnen dargestellt, sind in den Fig. 1 bis 3 grundsätzlich gleichwirkende Teile mit gleichen Bezugsziffern versehen. Mit 1 ist allgemein eine luftgekühlte Hubkolbenbrennkraftmaschine bezeichnet, die mit einem Kurbelgehäuse 2, nebeneinander angeordneten Zylinderrohren 3 und Einzelzylinderköpfen 4 versehen ist. Die Zylinderrohre 3 sind einstückig mit dem Kurbelwellengehäuse 2 ausgebildet und die Auslaßkanäle 5 der Einzelzylinderköpfe 4 erstrecken sich, wie aus Fig. 1 und 2 ersichtlich, auf der Kühlluftabströmseite. Der im einzelnen nicht näher dargestellte Einlaßkanal liegt auf der KühlluftzustrBmseite und mündet im Bereich der Kühlluftzuströmseite, wobei die nicht im einzelnen dargestellten Ventile der Aus- und Einlaßkanäle 5 und 6 derart angeordnet sind, daß die durch die Ventilschäfte verlaufende Ebenen in einem spitzen Winkel (ca. 30 °) zur Zylinderreihenlängsachse 7 verlaufen.As far as shown in detail, parts with the same effect are given the same reference numbers in FIGS. 1 to 3. 1 generally designates an air-cooled reciprocating piston internal combustion engine, which is provided with a crankcase 2, cylinder tubes 3 arranged next to one another and single cylinder heads 4. The cylinder tubes 3 are formed in one piece with the crankshaft housing 2 and the outlet channels 5 of the individual cylinder heads 4 extend, as can be seen from FIGS. 1 and 2, on the cooling air outflow side. The inlet duct, not shown in detail, lies on the cooling air inflow side and opens into the area of the cooling air inflow side, the valves of the outlet and inlet ducts 5 and 6, which are not shown in detail, being arranged such that the planes running through the valve stems are at an acute angle (approx . 30 °) to the cylinder axis 7.

Die Zylinderrohre 3 weisen in einem zylinderkopfseitigen Zylinderrohrabschnitt quer zu den Zylinderrohrlängsachsen 8 verlaufende Kühlrippen 9 auf, wobei diese quer zur Zylinderrohrlängsachse 8 verlaufenden Kühlrippen 9, wie aus den verschiedenen Ansichten nach den Fig. 1 bis 3 hervorgeht, ausschließlich in einem hinteren (abströmseitigen) seitlichen Umfangsbereich des zylinderkopfseitigen Zylinderrohrabschnittes vorgesehen sind. Auf der durch die durchgezogenen Pfeile 10 in den Fig. 2 und 3 angedeuteten Kühlluftzuströmseite und auch in dem kurbelgehäuseseitigen Zylinderrohrabschnitt auf der Kühlluftabströmseite sind somit die Zylinderrohre 3 kühlrippenfrei ausgebildet.In a cylinder tube section on the cylinder head side, the cylinder tubes 3 have cooling fins 9 running transversely to the cylinder tube longitudinal axes 8, these cooling fins 9 running transversely to the cylinder tube longitudinal axis 8, as can be seen from the various views according to FIGS. 1 to 3, only in a rear (downstream) side Circumferential region of the cylinder head section on the cylinder head side are provided. On the cooling air inflow side indicated by the solid arrows 10 in FIGS. 2 and 3 and also in the crankcase-side cylinder tube section on the cooling air outflow side, the cylinder tubes 3 are thus formed without cooling ribs.

Auf der Kühlluftabströmseite (Pfeile 20a, 20b) der Zylinderrohre 3 sind erfindungsgemäß die im wesentlichen parallel zur Zylinderrohrlängsachse 8 verlaufenden Kühlrippen 11 angeordnet, die im wesentlichen bis zu den zylinderkopfendseitigen Endflächen 12 der Zylinderrohre 3 reichen und mit einem axialen Abstand zum Kurbelwellengehäuse 2 an den Zylinderrohren 3 vorgesehen sind. Die parallel zur Zylinderrohrlängsachse 8 verlaufenden Kühlrippen 11 und die quer zur Zylinderrohrlängsachse 8 verlaufenden Kühlrippen 9 der Zylinderrohre 3 einer Zylinderreihe sind insgesamt einstückig ausgebildet.According to the invention, on the cooling air outflow side (arrows 20a, 20b) of the cylinder tubes 3 are the cooling fins which run essentially parallel to the longitudinal axis 8 of the cylinder tube 11 are arranged, which essentially extend to the end faces 12 of the cylinder tubes 3 on the end side of the cylinder head and are provided on the cylinder tubes 3 at an axial distance from the crankshaft housing 2. The cooling fins 11 running parallel to the longitudinal axis 8 of the cylinder tube and the cooling fins 9 of the cylinder tubes 3 of a row of cylinders 3 extending transversely to the longitudinal axis 8 of the cylinder tube are formed in one piece.

Auf der Kühlluftabströmseite der Zylinderrohre 3 ist die Luftleiteinrichtung 13 vorgesehen, die an den letzten Zylinderrohren 3 der Zylinderreihe abgeknickt ist, so daß die Zylinderreihe seitlich und abströmseitig vollständig von der Luftleiteinrichtung mit einem ausreichenden Durchströmabstand 14 (Fig. 3) ummantelt wird. An den Stellen der Zylinderrohre 3, an denen quer zur Zylinderrohrlängsachse 8 verlaufende Kühlrippen 9 vorgesehen sind, weist die Luftleiteinrichtung 13 zylinderkopfseitig eine bis nahe an abströmseitige Endflächen der Kühlrippen 9 reichende Querschnittsstruktur (Einbuchtungen 15) auf. In diesen Einbuchtungen 15 sind Abströmöffnungen 16 vorgesehen, so daß die in diesen oberen heißen Zylinderrohrabschnitten strömende Kühlluft (Pfeile 20a) unmittelbar in die Umgebung abströmen kann. Die Abströmöffnungen 16 für zwischen den Zylinderrohren strömende Kühlluft sind dabei asymmetrisch zu den Mittelebenen 21 benachbarter Zylinderrohre 3 angeordnet, und zwar versetzt zu den jeweiligen Auslaßkanälen 5, so daß die auslaßkanalnahen Umfangsbereiche der Zylinderrohre bzw. deren Kühlrippen 9 intensiver gekühlt werden als die gegenüberliegenden Umfangsbereiche der Kühlrippen (Einlaßkanalbereiche) des Nachbarzylinderrohres.On the cooling air outflow side of the cylinder tubes 3, the air guiding device 13 is provided, which is kinked on the last cylinder tubes 3 of the row of cylinders, so that the cylinder row is completely encased on the side and on the outflow side by the air guiding device with a sufficient throughflow distance 14 (FIG. 3). At the locations of the cylinder tubes 3 at which cooling fins 9 are provided which run transversely to the longitudinal axis 8 of the cylinder tube, the air guiding device 13 has a cross-sectional structure (indentations 15) on the cylinder head side that extends close to the downstream end faces of the cooling fins 9. Outflow openings 16 are provided in these indentations 15, so that the cooling air (arrows 20a) flowing in these upper hot cylinder tube sections can flow directly into the surroundings. The outflow openings 16 for cooling air flowing between the cylinder tubes are arranged asymmetrically to the central planes 21 of adjacent cylinder tubes 3, namely offset to the respective outlet ducts 5, so that the peripheral regions of the cylinder tubes or their cooling fins 9 near the outlet duct are cooled more intensively than the opposite peripheral regions of the Cooling fins (inlet duct areas) of the neighboring cylinder tube.

Ansonsten wird die zugeführte Kühlluft nach Durchströmen der jeweils unverrippten vorderen und seitlichen Bereiche der zylinderrohre 3 von der Luftleiteinrichtung 13 auf der Kühlluftabströmseite in Richtung der parallel zur Zylinderrohrlängsachse 7 verlaufenden Kühlrippen 11 umgelenkt (Pfeile 20b), so daß dieser gesamte Kühlluftstrom, der ein relativ niedriges Temperaturniveau aufweist, zur Kühlung des hinteren heißen Zylinderrohrbereiches herangezogen werden kann und durch die parallel verlaufenden Kühlrippen 11 zum heißesten zylinderkopfseitigen Bereich der Zylinderrohre 3 geführt wird. Da die quer verlaufenden Kühlrippen 11 mit einem Abstand zum Kurbelwellengehäuse 2 angeordnet sind, ist dabei in hohem Maße gewährleistet, daß in dem abströmseitigen Durchströmraum 14 der Luftleiteinrichtung 13 Luftansammlungen, Rückströmungen, Verwirbelungen etc. vermieden werden.Otherwise, the supplied cooling air is deflected after flowing through the respective non-ribbed front and side areas of the cylinder tubes 3 from the air guiding device 13 on the cooling air outflow side in the direction of the cooling fins 11 running parallel to the longitudinal axis 7 of the cylinder tube (arrows 20b), so that this total cooling air flow, which is a relatively low one Has temperature level, can be used to cool the rear hot cylinder tube area and is led through the parallel cooling fins 11 to the hottest area of the cylinder tubes 3 on the cylinder head side. Since the transverse cooling fins 11 are arranged at a distance from the crankshaft housing 2, it is to a high degree ensured that air accumulations, backflows, swirls etc. are avoided in the downstream flow space 14 of the air guiding device.

Durch diese Gestaltung der Kühlluftführung und durch die Anordnung und Gestaltung der Kühlrippen 9 und 11 ergibt sich eine optimale Ausnutzung der insgesamt zuzuführenden Kühlluft und eine wesentliche Vergleichmäßigung der Gesamtzylinderrohrtemperaturen, so daß hierdurch in optimaler Weise die Voraussetzungen für eine Leistungserhöhung der Brennkraftmaschine und die Herabsetzung von Temperaturspannungen gegeben sind. Durch die Verbindung der quer zur Zylinderrohrlängsachse 8 verlaufenden Kühlrippen 9 benachbarter Zylinderrohre 3 ist dafür Sorge getragen, daß ein stetiger Wärmefluß vom heißen Umfangsbereich eines Zylinderrohrs 3 (Auslaßkanal 5) zu dem kälteren Umfangsbereich (Einlaßkanal 6) des Nachbarzylinderrohrs 3 stattfindet.This design of the cooling air duct and the arrangement and design of the cooling fins 9 and 11 results in an optimal utilization of the total cooling air to be supplied and a substantial homogenization of the overall cylinder tube temperatures, so that this optimally fulfills the requirements for an increase in performance of the internal combustion engine and a reduction in temperature voltages given are. The connection of the cooling fins 9 of adjacent cylinder tubes 3 running transversely to the longitudinal axis 8 of the cylinder tube ensures that a steady heat flow takes place from the hot peripheral region of a cylinder tube 3 (outlet channel 5) to the colder peripheral region (inlet channel 6) of the neighboring cylinder tube 3.

Die Zylinderköpfe 4 weisen an ihrem zylinderrohrseitigen Endbereich ebenfalls parallel zur Zylinderrohrachse 8 ausgerichtete Kühlrippen 17 auf und sind auf der Kühlluftabströmseite mit Luftleitblechen 18 versehen. Die Luftleiteinrichtung 13 und das sich ebenfalls über die Zylinderköpfe 4 der gesamten Zylinderreihe erstreckende Luftleitblech 18 weisen auf der Abströmseite zueinander einen Abstand auf und sind an ihren Rändern um etwa 90 0 umgebogen, so daß die Kühlluft der Zylinderrohre nach Durchströmen der parallel zur Zylinderrohrlängsachse 8 angeordneten Kühlrippen 11 in Richtung der parallel ausgerichteten Kühlrippen 17 der Zylinderköpfe 4 gelenkt wird und gemeinsam mit der Kühlluft (Pfeile 20c) der Zylinderköpfe in diesem Bereich in die Umgebung abströmen kann (Fig.3). Somit leistet die Kühlluft der Zylinderrohre 3 auch noch einen Beitrag zur Kühlung der zylinderrohrendseitigen heißen Endbereiche der Zylinderköpfe 4. Die Luftleitbleche 18 der Zylinderköpfe 4 weisen zusätzlich noch Auslaßöffnungen 22 auf, so daß in Bereichen der Auslaßkanäle 5 die Kühlluft direkt in die Umgebung abströmen kann.The cylinder heads 4 also have cooling fins 17 oriented parallel to the cylinder tube axis 8 at their end region on the cylinder tube side and are provided with air baffles 18 on the cooling air outflow side. The air guiding device 13 and the extending also over the cylinder heads 4 of the entire row of cylinders air guide plate 18 have on the downstream side to each other at a distance and are bent over at their edges at about 90 0, so that the cooling air of the cylinder tubes after flowing arranged parallel to the cylinder tube longitudinal axis 8 Cooling fins 11 is directed in the direction of the parallel oriented cooling fins 17 of the cylinder heads 4 and can flow together with the cooling air (arrows 20c) of the cylinder heads in this area into the environment (FIG. 3). Thus, the cooling air of the cylinder tubes 3 also makes a contribution to cooling the hot end regions of the cylinder heads 4 on the end of the cylinder tubes 4. The air baffles 18 of the cylinder heads 4 additionally have outlet openings 22, so that the cooling air can flow directly into the surroundings in regions of the outlet ducts 5.

Durch die einstückige Ausbildung der Zylinderrohre 3, des Kurbelwellengehäuses 2 und der Kühlrippen 9 und 11 gestaltet sich die erfindungsgemäße Hubkolbenbrennkraftmaschine 1 als auf fertigungstechnisch einfache und somit kostengünstige Weise herzustellende Gesamteinheit mit hervorragenden Stabilitätseigenschaften. Die Stabilitätsstruktur der Zylinderrohre 3 im zylinderkopfendseitigen Bereich 12 kann durch eine sich über den gesamten Umfang der Zylinderrohre 3 erstreckende Verstärkungsrippe 19 verbessert werden.Due to the one-piece design of the cylinder tubes 3, the crankshaft housing 2 and the cooling fins 9 and 11, the reciprocating piston internal combustion engine 1 according to the invention is designed as an overall unit with excellent stability properties that is simple to manufacture and therefore inexpensive to manufacture. The stability structure of the cylinder tubes 3 in the region 12 on the end of the cylinder head can be improved by a reinforcing rib 19 extending over the entire circumference of the cylinder tubes 3.

Claims (15)

1. Luftgekühlte Hubkolbenbrennkraftmaschine (1) mit zwei oder mehreren an einem Kurbelgehäuse (2) nebeneinander angeordneten Zylinderrohren (3), die zumindest an einem Teilumfang im wesentlichen quer zur Zylinderrohrlängsachse (8) verlaufende Kühlrippen (9) aufweisen sowie mit Zylinderköpfen (4), deren Einlaßkanäle (6) bevorzugt auf der Kühlluftzuströmseite (10) und deren Auslaßkanäle (5) bevorzugt auf der Kühlluftabströmseite (20) münden, und mit einer oder mehreren auf der Kühlluftabströmseite (20) der Zylinderrohre (3) vorgesehenen Luftleiteinrichtungen (13),
dadurch gekennzeichnet, daß die Zylinderrohre (3) auf der KühlluftabstrBmseite (20) mit im wesentlichen parallel zur Zylinderrohrlängsachse (8) verlaufenden Kühlrippen (11) versehen sind und daß mittels der Luftleiteinrichtungen (13) zumindest ein Teil der die Zylinderrohre (3) seitlich umströmenden bzw. zwischen benachbarten Zylinderrohren (3) strömenden Kühlluft in Richtung der parallel zur Zylinderrohrlängsachse (8) verlaufenden Kühlrippen (11) umlenkbar ist.1. Air-cooled reciprocating piston internal combustion engine (1) with two or more cylinder tubes (3) arranged next to one another on a crankcase (2), which have cooling fins (9) running at least on a partial circumference essentially transversely to the longitudinal axis of the cylinder tube (8), and with cylinder heads (4), whose inlet ducts (6) preferably open on the cooling air inflow side (10) and whose outlet ducts (5) preferably open on the cooling air outflow side (20), and with one or more air guiding devices (13) provided on the cooling air outflow side (20) of the cylinder tubes (3),
characterized in that the cylinder tubes (3) ühlluftabstrBmseite at K are provided with extending substantially parallel to the cylinder tube longitudinal axis (8) cooling ribs (11) (20) and that (13) at least a portion of the cylinder tubes (3) side by means of the louvers Cooling air flowing around or flowing between adjacent cylinder tubes (3) can be deflected in the direction of the cooling fins (11) running parallel to the longitudinal axis of the cylinder tube (8). 2. Luftgekühlte Brennkraftmaschine nach Anspruch 1, dadurch gekennzeichnet, daß die parallel zur Zylinderrohrlängsachse (8) verlaufenden Kühlrippen (11) im wesentlichen bis zu den zylinderkopfseitigen Endflächen (12) der Zylinderrohre (3) reichen und mit einem axialen Abstand zum Kurbelgehäuse (2) an den Zylinderrohren (3) beginnen.2. Air-cooled internal combustion engine according to claim 1, characterized in that the cooling ribs (11) extending parallel to the longitudinal axis of the cylinder tube (8) extend substantially up to the end faces (12) of the cylinder tubes (3) on the cylinder head side and with an axial distance from the crankcase (2). start at the cylinder tubes (3). 3. Luftgekühlte Brennkraftmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die quer zur Zylinderrohrlängsachse (8) verlaufenden Kühlrippen (9) in einem kurbelgehäuseseitigen Zylinderrohrabschnitt eine geringere Rippenhöhe aufweisen als in einem zylinderkopfseitigen Zylinderrohrabschnitt und/oder in Richtung des Kurbelgehäuses (2) eine im wesentlichen laufend abnehmende Rippenhöhe aufweisen.3. Air-cooled internal combustion engine according to claim 1 or 2, characterized in that the transverse to the longitudinal axis of the cylinder tube (8) extending cooling fins (9) in a crankcase-side cylinder tube section have a lower rib height than in a cylinder head-side cylinder tube section and / or in the direction of the crankcase (2) one have a continuously decreasing rib height. 4. Luftgekühlte Brennkraftmaschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Zylinderrohre (3) in einem kurbelgehäuseseitigen Zylinderrohrabschnitt kühlrippenfrei ausgebildet sind.4. Air-cooled internal combustion engine according to one of claims 1 to 3, characterized in that the cylinder tubes (3) are formed in a crankcase-side cylinder tube section free of cooling fins. 5. Luftgekühlte Brennkraftmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Zylinderrohre (3) in einem Umfangsbereich auf der Kühlluftzuströmseite (10) kühlrippenfrei ausgebildet und/oder mit KÜhlrippen (9) verringerter Rippenhöhe versehen sind.5. Air-cooled internal combustion engine according to one of the preceding claims, characterized in that the cylinder tubes (3) in a circumferential region on the cooling air inflow side (10) are formed without cooling fins and / or with cooling fins (9) are provided with a reduced fin height. 6. Luftgekühlte Brennkraftmaschine nach einem der vorangehenden Ansprüche, bei der die durch die Ventilschäfte des Einlaß- und Auslaßventils verlaufende Ebene in einem spitzen Winkel zur Zylinderreihenlängsachse (7) verdreht angeordnet sind,
dadurch gekennzeichnet, daß im wesentlichen der kühlluftzuströmseitige Umfangsbereich der Zylinderrohre (3) kühlrippenfrei ausgebildet ist.6. Air-cooled internal combustion engine according to one of the preceding claims, in which the plane extending through the valve stems of the intake and exhaust valve is arranged rotated at an acute angle to the cylinder row longitudinal axis (7),
characterized in that the peripheral region of the cylinder tubes (3) on the cooling air inflow side is essentially free of cooling fins. 7. Luftgekühlte Brennkraftmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet daß die quer zur Zylinderrohrlängsachse (8) verlaufenden Kühlrippen (9) in benachbarten Umfangsbereichen in wärmeleitender Verbindung stehen.7. Air-cooled internal combustion engine according to one of the preceding claims, characterized in that the cooling ribs (9) extending transversely to the longitudinal axis of the cylinder tube (8) are in heat-conducting connection in adjacent peripheral regions. 8. Luftgekühlte Brennkraftmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die quer zur Zylinderrohrlängsachse (8) verlaufenden Kühlrippen (9) benachbarter Zylinderrohre (3) einstückig ausgebildet sind.8. Air-cooled internal combustion engine according to one of the preceding claims, characterized in that the transverse to the longitudinal axis of the cylinder tube (8) extending cooling fins (9) of adjacent cylinder tubes (3) are integrally formed. 9. Luftgekühlte Brennkraftmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Luftleiteinrichtungen (13) Abströmöffnungen (16) für die die Zylinderrohre (3) seitlich in einem zylinderkopfseitigen Zylinderrohrabschnitt umströmende bzw. zwischen benachbarten Zylinderrohren (3) in einem zylinderkopfseitigen Zylinderrohrabschnitt strömende Kühlluft aufweisen.9. Air-cooled internal combustion engine according to one of the preceding claims, characterized in that the air guiding devices (13) outflow openings (16) for the cylinder tubes (3) flowing laterally in a cylinder head-side cylinder tube section or between adjacent cylinder tubes (3) in a cylinder head-side cylinder tube section flowing cooling air exhibit. 10. Luftgekühlte Brennkraftmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Luftleiteinrichtungen (13) zylinderkopfseitig in Zylinderreihenendbereichen und zwischen benachbarten Zylinderrohren (6) eine im wesentlichen mit bis nahe an kühlluftabströmseitige Endflächen von quer zur Zylinderrohrlängsachse (8) verlaufenden Kühlrippen (9) reichenden Querschnittsstruktur (15) aufweisen.10. Air-cooled internal combustion engine according to one of the preceding claims, characterized in that the air-guiding devices (13) on the cylinder head side in the cylinder row end regions and between adjacent cylinder tubes (6) have a cooling ribs (9) running essentially up to close to the cooling-air outflow-side end surfaces of transverse to the longitudinal axis of the cylinder tube (8) have reaching cross-sectional structure (15). 11. Luftgekühle Brennkraftmaschine nach Anspruch 9 oder 10, dadurch gekennzeichnet, daß die Abströmöffnungen (16) für zwischen benachbarten Zylinderrohren (3) strömende Kühlluft asymmetrisch zu senkrecht zur Zylinderreihenlängsachse (7) angeordnete Mittelebenen (21) benachbarter Zylinderrohre und in Richtung der jeweiligen Auslaßkanäle (5) versetzt vorgesehen sind.11. Air-cooled internal combustion engine according to claim 9 or 10, characterized in that the outflow openings (16) for cooling air flowing between adjacent cylinder tubes (3) asymmetrically to perpendicular to the cylinder row longitudinal axis (7) arranged central planes (21) of adjacent cylinder tubes and in the direction of the respective exhaust ports ( 5) are provided offset. 12. Luftgekühlte Brennkraftmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Zylinderköpfe (4) auf der Kühlluftabströmseite (20) mit im zylinderrohrseitigen Endbereich angeordneten, parallel zur Zylinderrohrlängsachse (8) ausgerichteten Kühlrippen (17) und mit Luftleitblechen (18) versehen sind, daß die Luftleiteinrichtungen (13) der Zylinderrohre (3) zylinderkopfendseitig und die Luftleitbleche (18) der Zylinderköpfe (4) zylinderrohrendseitig an ihren Rändern um etwa 90 0 gebogen bzw. abgewinkelt sind, daß die Luftleiteinrichtungen (13) und die Luftleitbleche (18) zumindest im Bereich der parallel zur Zylinderrohrlängsachse (8) verlaufenden KÜhlrippen (11) der Zylinderrohre (3) einen Abstand zueinander aufweisen und daß die Luftleiteinrichtungen (13) der Zylinderrohre (3) bis nahe an die parallel zur Zylinderrohrlängsachse (8) verlaufenden Kühlrippen (17) der Zylinde köpfe (4) reichen.12. Air-cooled internal combustion engine according to one of the preceding claims, characterized in that the cylinder heads (4) on the cooling air outflow side (20) arranged in the cylinder tube end region, parallel to the cylinder axis (8) aligned cooling fins (17) and with air baffles (18) are provided in that the air guiding devices (13) of the cylinder tubes (3) zylinderkopfendseitig and the spoilers (18) of the cylinder heads (4) are zylinderrohrendseitig bent at their edges through about 90 0 and angled such that the air guiding devices (13) and the spoilers (18) at least in the area of the cooling fins (11) of the cylinder tubes (3) running parallel to the cylinder tube longitudinal axis (8) and that the air guiding devices (13) of the cylinder tubes (3) are close to the cooling fins (17) running parallel to the cylinder tube longitudinal axis (8) ) the cylinder heads (4) are enough. 13. Luftgekühlte Brennkraftmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Zy-linderrohre (3) und das Kurbelgehäuse (2) einstückig ausgebildet sind.13. Air-cooled internal combustion engine according to one of the preceding claims, characterized in that the Z y-linderrohre (3) and the crankcase (2) are integrally formed. 14. Luftgekühlte Brennkraftmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß im wesentlichen an dem zylinderkopfseitigen Endbereich (12) der Zylinderrohre (3) eine Verstärkungsrippe (19) vorgesehen ist.14. Air-cooled internal combustion engine according to one of the preceding claims, characterized in that a reinforcing rib (19) is provided essentially on the cylinder head end region (12) of the cylinder tubes (3). 15. Luftgekühlte Brennkraftmaschine nach Anspruch 12, dadurch gekennzeichnet, daß die Luftleitbleche (18) der Zylinderköpfe (4) im Bereich der Auslaßkanäle (5) Kühlluftauslaßöffnungen (22) haben.15. Air-cooled internal combustion engine according to claim 12, characterized in that the air baffles (18) of the cylinder heads (4) in the region of the outlet channels (5) have cooling air outlet openings (22).
EP19850100754 1984-03-09 1985-01-25 Air-cooled internal-combustion piston engine Expired - Lifetime EP0154144B1 (en)

Priority Applications (1)

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AT85100754T ATE51433T1 (en) 1984-03-09 1985-01-25 AIR-COOLED RECIPROCATING ENGINE.

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DE3408624 1984-03-09
DE19843408624 DE3408624A1 (en) 1984-03-09 1984-03-09 AIR COOLED PISTON COMBUSTION ENGINE

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EP0154144A3 EP0154144A3 (en) 1986-08-27
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EP (1) EP0154144B1 (en)
AT (1) ATE51433T1 (en)
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CA1238540A (en) 1988-06-28
DE3408624A1 (en) 1985-09-12
ATE51433T1 (en) 1990-04-15
EP0154144B1 (en) 1990-03-28
US4633823A (en) 1987-01-06
EP0154144A3 (en) 1986-08-27
DE3576842D1 (en) 1990-05-03

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