EP0154144A2 - Moteur à combustion interne refroidi par air - Google Patents

Moteur à combustion interne refroidi par air 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
Authority
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
Other languages
German (de)
English (en)
Other versions
EP0154144B1 (fr
EP0154144A3 (en
Inventor
Werner Dr.-Ing. Haas
Dieter Hilker
Pavel Jan Slezak
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Khd Canada Inc Deutz R & D Division
Kloeckner Humboldt Deutz AG
Original Assignee
Khd Canada Inc Deutz R & D Division
Kloeckner Humboldt Deutz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 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/de
Publication of EP0154144A2 publication Critical patent/EP0154144A2/fr
Publication of EP0154144A3 publication Critical patent/EP0154144A3/de
Application granted granted Critical
Publication of EP0154144B1 publication Critical patent/EP0154144B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • 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.

Landscapes

  • 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)
EP19850100754 1984-03-09 1985-01-25 Moteur à combustion interne refroidi par air Expired - Lifetime EP0154144B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85100754T ATE51433T1 (de) 1984-03-09 1985-01-25 Luftgekuehlte hubkolbenbrennkraftmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843408624 DE3408624A1 (de) 1984-03-09 1984-03-09 Luftgekuehlte hubkolbenbrennkraftmaschine
DE3408624 1984-03-09

Publications (3)

Publication Number Publication Date
EP0154144A2 true EP0154144A2 (fr) 1985-09-11
EP0154144A3 EP0154144A3 (en) 1986-08-27
EP0154144B1 EP0154144B1 (fr) 1990-03-28

Family

ID=6229994

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19850100754 Expired - Lifetime EP0154144B1 (fr) 1984-03-09 1985-01-25 Moteur à combustion interne refroidi par air

Country Status (5)

Country Link
US (1) US4633823A (fr)
EP (1) EP0154144B1 (fr)
AT (1) ATE51433T1 (fr)
CA (1) CA1238540A (fr)
DE (2) DE3408624A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111075589A (zh) * 2019-12-30 2020-04-28 重庆品恒动力机械有限公司 强制风冷柴油机机体

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3540487A1 (de) * 1985-11-15 1987-05-21 Kloeckner Humboldt Deutz Ag Luftleitblech fuer luftgekuehlte brennkraftmaschinen
DE3616636A1 (de) * 1986-05-16 1987-11-19 Porsche Ag Luftgekuehlte mehrzylinder-brennkraftmaschine
US5638779A (en) * 1995-08-16 1997-06-17 Northrop Grumman Corporation High-efficiency, low-pollution engine
US20050066916A1 (en) * 2003-09-25 2005-03-31 Cordy Clifford B. Axial flow cooling for air-cooled engines
US7617804B2 (en) * 2003-09-25 2009-11-17 Cordy Jr Clifford B Axial flow cooling for air-cooled engines
JP4568672B2 (ja) * 2005-10-18 2010-10-27 三菱重工業株式会社 強制空冷エンジンの冷却風案内カバー
TWI311897B (en) * 2006-10-26 2009-07-01 Delta Electronics Inc Electronic apparatus with water blocking and draining structure and manufacturing method thereof
RU204384U1 (ru) * 2020-10-20 2021-05-21 ФЕДЕРАЛЬНОЕ ГОСУДАРСТВЕННОЕ КАЗЕННОЕ ВОЕННОЕ ОБРАЗОВАТЕЛЬНОЕ УЧРЕЖДЕНИЕ ВЫСШЕГО ОБРАЗОВАНИЯ Военная академия Ракетных войск стратегического назначения имени Петра Великого МИНИСТЕРСТВА ОБОРОНЫ РОССИЙСКОЙ ФЕДЕРАЦИИ Система воздушного охлаждения двигателя внутреннего сгорания с управляемым замкнутым контуром охлаждения

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DE366305C (de) * 1923-01-02 Gustav Roehr Zylinderblock fuer mehrzylindrige Verbrennungskraftmaschinen
GB200938A (en) * 1922-04-26 1923-07-26 Gordon Henry John Templeman Improved air cooled internal combustion engine cylinder
US1622015A (en) * 1921-03-29 1927-03-22 Jr John M Williams Internal-combustion engine
CH179201A (de) * 1934-09-06 1935-08-31 Bernhard Gabrielson John Einrichtung zum Kühlen von Brennkraftmaschinen mittelst Luft.
DE705247C (de) * 1936-10-15 1941-04-22 John Bernhard Gabrielson Luftkuehlanordnung fuer mehrzylindrige Verbrennungsmotoren mit seitlich zu den Zylindern angeordneten Auslaessen fuer die Abgase
FR874201A (fr) * 1940-07-27 1942-07-31 Ets Ringhoffer Tatra Sa Dispositif de construction des ailettes de renoidissement des cylindres des moteurs à explosion ou à combustion refroidis par l'air
DE733191C (de) * 1937-07-29 1943-03-20 Bayerische Motoren Werke Ag Einrichtung zur Kuehlung von luftgekuehlten Brennkraftmaschinen in Reihenbauart
GB877560A (en) * 1958-11-07 1961-09-13 Daimler Benz Ag Improvements relating to air-cooled four-stroke injection combustion engines
GB1110453A (en) * 1965-07-19 1968-04-18 Schoenebeck Dieselmotoren Improvements in or relating to cooling systems for air-cooled internal combustion engines
DE2921925A1 (de) * 1979-05-30 1981-03-12 Klöckner-Humboldt-Deutz AG, 5000 Köln Luftgekuehlte brennkraftmaschine mit luftfuehrungs- und luftleitblechen.

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CH100547A (de) * 1918-05-02 1923-08-01 Waermekraft Ges Mit Beschraenk Verfahren zum Betriebe von luftgekühlten Verbrennungsmotoren und Einrichtung zur Ausübung des Verfahrens.
US1398849A (en) * 1920-11-01 1921-11-29 Bristol Aeroplane Co Ltd Cylinder for internal-combustion engines
US1506950A (en) * 1921-11-12 1924-09-02 John W Smith Internal-combustion engine
DE1300344B (de) * 1963-07-06 1969-07-31 Volkswagenwerk Ag Luftgekuehlter Zylinderkopf fuer eine mehrzylindrige Brennkraft-maschine
DE6906207U (de) * 1968-08-15 1969-07-10 Tovarna Motornih Vozil T O M O Zylinder mit getrenntem zylinderkopf
US4047508A (en) * 1975-12-08 1977-09-13 Avco Corporation Cooling air distribution system for reciprocating aircraft engines
AT365743B (de) * 1977-06-07 1982-02-10 List Hans Zylinderkopf fuer eine luftgekuehlte brennkraftmaschine
US4515111A (en) * 1984-04-19 1985-05-07 Khd Canada Inc. Air-cooled, reciprocating piston, internal combustion engine with cylinder heads forming arcuate or S-shaped cooling ducts therebetween

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE366305C (de) * 1923-01-02 Gustav Roehr Zylinderblock fuer mehrzylindrige Verbrennungskraftmaschinen
US1622015A (en) * 1921-03-29 1927-03-22 Jr John M Williams Internal-combustion engine
GB200938A (en) * 1922-04-26 1923-07-26 Gordon Henry John Templeman Improved air cooled internal combustion engine cylinder
CH179201A (de) * 1934-09-06 1935-08-31 Bernhard Gabrielson John Einrichtung zum Kühlen von Brennkraftmaschinen mittelst Luft.
DE705247C (de) * 1936-10-15 1941-04-22 John Bernhard Gabrielson Luftkuehlanordnung fuer mehrzylindrige Verbrennungsmotoren mit seitlich zu den Zylindern angeordneten Auslaessen fuer die Abgase
DE733191C (de) * 1937-07-29 1943-03-20 Bayerische Motoren Werke Ag Einrichtung zur Kuehlung von luftgekuehlten Brennkraftmaschinen in Reihenbauart
FR874201A (fr) * 1940-07-27 1942-07-31 Ets Ringhoffer Tatra Sa Dispositif de construction des ailettes de renoidissement des cylindres des moteurs à explosion ou à combustion refroidis par l'air
GB877560A (en) * 1958-11-07 1961-09-13 Daimler Benz Ag Improvements relating to air-cooled four-stroke injection combustion engines
GB1110453A (en) * 1965-07-19 1968-04-18 Schoenebeck Dieselmotoren Improvements in or relating to cooling systems for air-cooled internal combustion engines
DE2921925A1 (de) * 1979-05-30 1981-03-12 Klöckner-Humboldt-Deutz AG, 5000 Köln Luftgekuehlte brennkraftmaschine mit luftfuehrungs- und luftleitblechen.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111075589A (zh) * 2019-12-30 2020-04-28 重庆品恒动力机械有限公司 强制风冷柴油机机体

Also Published As

Publication number Publication date
EP0154144B1 (fr) 1990-03-28
ATE51433T1 (de) 1990-04-15
EP0154144A3 (en) 1986-08-27
US4633823A (en) 1987-01-06
DE3408624A1 (de) 1985-09-12
DE3576842D1 (de) 1990-05-03
CA1238540A (fr) 1988-06-28

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