EP0206184B1 - Fourreau cylindrique refroidi par eau - Google Patents

Fourreau cylindrique refroidi par eau Download PDF

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Publication number
EP0206184B1
EP0206184B1 EP86108150A EP86108150A EP0206184B1 EP 0206184 B1 EP0206184 B1 EP 0206184B1 EP 86108150 A EP86108150 A EP 86108150A EP 86108150 A EP86108150 A EP 86108150A EP 0206184 B1 EP0206184 B1 EP 0206184B1
Authority
EP
European Patent Office
Prior art keywords
liner
cooling
liquid
fins
cylinder tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP86108150A
Other languages
German (de)
English (en)
Other versions
EP0206184A3 (en
EP0206184A2 (fr
Inventor
Gerhard Finsterwalder
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
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 Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Publication of EP0206184A2 publication Critical patent/EP0206184A2/fr
Publication of EP0206184A3 publication Critical patent/EP0206184A3/de
Application granted granted Critical
Publication of EP0206184B1 publication Critical patent/EP0206184B1/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
    • F02F1/10—Cylinders; Cylinder heads  having cooling means for liquid cooling
    • F02F1/14—Cylinders with means for directing, guiding or distributing liquid stream
    • 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
    • F02F1/10—Cylinders; Cylinder heads  having cooling means for liquid cooling
    • F02F1/16—Cylinder liners of wet type

Definitions

  • the invention relates to a liquid-cooled cylinder tube for an internal combustion engine according to the preamble of claim 1.
  • a cylinder for a liquid-cooled internal combustion engine is described in US-A-1,904,459, an annular cooling space being provided between the cylinder tube and the motor housing, through which liquid is conveyed during operation of the internal combustion engine and which has a liquid inflow and a liquid outflow.
  • the cylinder tube is provided with a spiral cooling fin for better cooling, which is attached to the outer surface of the cylinder tube.
  • the cooling fins on the cylinder barrel are used to guide the coolant and increase the surface area.
  • US-A-2,078,499 describes a cooling system for an internal combustion engine.
  • the cylinder tube is also provided with cooling fins, which also only serve to guide the coolant and increase the surface area.
  • GB-A-204,106 describes a thick-walled cylinder tube, axial cooling channels being embedded in the cylinder tube wall.
  • the inner cylinder tube wall is thin-walled and connected to the outer cylinder tube wall via ignition pressure-transmitting webs. However, these webs are not in contact with the engine housing, since the axial cooling channels are cast into the cylinder tube wall.
  • the object of this invention is to sufficiently cool even thermally highly stressed cylinder tubes in order to thereby prevent the temperature-related expansion of the cylinder tube end pointing towards the cylinder head.
  • Cooling fins are continuous elevations in the form of ribs or serrations that completely surround the cylinder tube in the circumferential direction. Furthermore, the terms “above” and “below” are used in the following description. Above means towards the cylinder head, and below towards the crankcase.
  • the cylinder tube is thin-walled and the cooling fins lie radially on the engine housing to transmit ignition pressure, completely enclose the cylinder tube in the circumferential direction, are arranged adjacent to one another in the cylinder axial direction and have axial liquid passages, a temperature-related expansion of the upper end of the cylinder tube is due to the good heat transfer from the cylinder tube via the Cooling fins on the liquid and also avoided by clamping the thin-walled cylinder tube through the motor housing.
  • a cylinder tube that remains cylindrical during operation of the internal combustion engine enables the cylinder piston to have small warm cycles. This minimizes piston tipping noises, thermal stress on the cylinder barrel and cylinder piston, blow-through quantity and harmful space, which reduces noise and pollutant emissions as well as fuel and lubricant consumption.
  • the cylinder tube Since the ignition pressure is passed on to the engine housing via the cooling fins, the cylinder tube is made thin-walled and thus has a lower thermal conductivity than a thicker cylinder tube carrying the ignition pressure.
  • the thin wall of the cylinder tube means that only a small temperature gradient occurs in the cylinder tube; d. H. there is a large temperature difference between the outer wall of the cylinder tube and the coolant, which increases the amount of heat that can be dissipated compared to thicker cylinder tubes and at the same time reduces the temperature of the inner wall of the cylinder tube.
  • An annular channel in the cylinder head is expediently arranged as a liquid inflow, which consists of an annular groove which is open to the cooling space and which lies above the cooling space of the cylinder tube and has approximately its radial width.
  • the liquid drain is advantageously arranged on the side of the cooling chamber facing the crankcase.
  • the cooling fins should be dimensioned such that the temperature of the outside of the cylinder tube is lowered to the temperature of the cooling liquid up to the tip of the cooling fin.
  • Engine lubricating oil is particularly suitable as a coolant.
  • the cooling liquid also absorbs the heat of combustion well
  • the liquid passages are arranged in such a way that a labyrinthine path results for the cooling liquid.
  • a labyrinthine path results for the cooling liquid.
  • the liquid passages in all cooling fins are arranged with the same cover with respect to the cylinder tube axis.
  • the top cooling fin located below the cylinder head has fewer liquid passages than the cooling fins of the other levels. This results in a labyrinthine flow of the coolant on the cylinder tube and thus an improved cooling.
  • Optimal cooling of the uppermost cooling fin is achieved when the cooling liquid enters the annular groove from the cylinder head through inlet openings which are arranged between the liquid passages of the uppermost cooling fin.
  • the top one facing the cylinder head Section of the cylinder tube requires the most intensive cooling. For this reason, it makes sense to provide only this section of the cooling space with cooling ribs and to arrange liquid-impermeable, pressure-resistant material in the other section, except for cooling channels running in the axial direction.
  • the cylinder tube with an interference fit is advantageously inserted in the engine housing in order to transmit the internal cylinder pressure to the engine housing.
  • the cylinder tube expediently has a collar-free end on the side facing the cylinder head and is axially supported on the engine housing at the end facing the crankcase.
  • Fig. 1 shows a cylinder tube 13 which is expediently embedded in an engine housing 12 with a press fit and is supported on the engine housing 12 at the end facing the crankcase 14.
  • annular cooling space 9 is arranged, which is open to the cylinder head 16 and there has a liquid inflow formed as an annular groove 7, while the liquid outflow 11 is formed by a slot between the cylinder tube and the motor housing, which is formed by the support 24 of the cylinder tube on the engine housing leads to the crankcase 14.
  • the cylinder tube wall is thinner below the support 24 in the direction of the crankcase 14 than above the support. The difference is just the thickness of the cylinder tube with which it is supported on the motor housing.
  • Cooling fins 10 are arranged on the outer wall of the cylinder tube, said cooling fins completely projecting through the cooling space 9 in the radial direction and resting radially on the motor housing 12. These cooling fins transmit the ignition pressure to the engine housing during the combustion process.
  • the cylinder tube alone, without the cooling fins, is so thin-walled that it cannot withstand the ignition pressure in the radial direction, but very well the axially acting sealing force of the cylinder head 16.
  • the cylinder tube is supported on the motor housing. It may be appropriate if the support width is equal to the width of the cooling fins. During installation, the thin-walled cylinder tube with its cooling fins is inserted into the engine housing from the cylinder head side.
  • the cylinder tube is honed only after it has been shrunk into the motor housing 12. If the entire wall thickness of the cylinder tube with the cooling fins is supported on the motor housing, the cylinder tube and motor housing are machined together during honing.
  • the cylinder head 16 which is seated on the engine housing, is located above the cylinder tube and the engine housing.
  • the seal between the cylinder head 16 and the cylinder tube 13 is achieved by metallic contact of the parts to be sealed with a slight protrusion of the cylinder tube.
  • the oil seal to the outside is done by a seal 8.
  • an exhaust valve (not shown) with its valve seat 4 and a bore for the valve stem 2 is arranged in the cylinder head 16.
  • An exhaust duct 3 leads from the valve seat 4 to the edge of the cylinder head 16. Two spaces 1, in which coolant is conducted, surround the exhaust duct 3.
  • Channels 5 are arranged in the cylinder head base 25, which lead from the outside of the cylinder head to the valve seat 4. These channels 5 are sealed to the outside by a plug 6. Above the annular cooling space 9 in the cylinder tube, which is open towards the cylinder head, there is an annular groove 7 open towards the cooling space in the cylinder head. This annular groove is in fluid connection with the channels 5 at four points through inlet openings 17, which result from the intersections of the channels 5 with the annular groove 7 (see description of FIGS. 3 to 6).
  • FIG. 2 shows an enlarged detail of the cylinder head base 25 with the channel 5 and the annular groove 7, which is arranged above the cooling space 9 in the cylinder head 16 and the cooling fins 10 located in the cylinder tube.
  • the channel 5 is liquid-carrying at four points by means of inlet openings 17 the annular groove 7 connected, which in turn is open to the cooling chamber 9.
  • the cooling fins of the cylinder tube are arranged in the cooling chamber. These extend completely through the cooling space and lie radially on the motor housing 12 and have liquid passages 19. It is expedient if the cooling fins are dimensioned such that the temperature of the outside of the cylinder tube up to the cooling fin tip 22 is reduced approximately to the temperature of the cooling liquid.
  • FIG. 3 shows a plan view of a cylinder tube with cooling fins seen in the axial direction
  • FIG. 4 shows a section through this cylinder tube along the line IV-IV in FIG. 3
  • FIG. 5 shows a section along the line VV in FIG. 3
  • FIG. 6 a development of this cylinder tube with a part of the adjacent cylinder head.
  • the inlet openings 17 are provided at four locations evenly distributed over the circumference. It can also be expedient to provide more or fewer inlet openings.
  • the uppermost cooling fin facing the cylinder head has four liquid passages that lie between the inlet openings. If a different number of inlet openings is present, then the number of liquid passages in the uppermost cooling fin is correspondingly such that a liquid passage is always arranged between the inlet openings. These liquid passages run axially up to a section of the cooling space which is filled with liquid-impermeable, pressure-resistant material 20.
  • cooling ribs only one section of the cylinder tube facing the cylinder head is provided with cooling ribs, while in the other section, liquid-impermeable, pressure-resistant material 20 is arranged except for cooling channels 18 running in the axial direction.
  • cooling channels 18 running in the axial direction.
  • the liquid passages 19 are arranged so that there is a labyrinthine path for the liquid.
  • the uppermost cooling fin located in this area has fewer liquid passages than the cooling fins of the other levels.
  • the coolant flows from the channels 5 in the cylinder head 16 via the inlet openings 17 into the annular groove 7, which is open to the annular cooling space 9 in the cylinder tube 13. From there, the cooling liquid flows through the liquid passages 19 of the uppermost cooling fin arranged between the inlet openings and then either through one of the axial cooling channels 18 located below the inlet openings 17 or through an axial cooling channels arranged between the inlet openings in the direction of the crankcase 14.

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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)

Claims (10)

1. Fourreau cylindrique (13) refroidi par eau pour un moteur à combustion interne, une chambre de refroidissement (9) de forme annulaire étant prévue entre le fourreau cylindrique et le carter (12) du moteur, à travers laquelle on fait circuler du liquide, lorsque le moteur à combustion interne est, en fonctionnement, qui est pourvue d'une amenée de liquide et d'une sortie d'écoulement (11) du liquide, des ailettes de refroidissement (10) y étant prévues, qui sont formées sur la surface extérieure du fourreau cylindrique (13), fourreau cylindrique caractérisé en ce que les ailettes de refroidissement (10) entourent entièrement, en direction périphérique, le fourreau cylindrique (13), sont disposées voisines dans la direction axiale du cylindre et comportent des passages de liquide (19) axiaux qui sont disposés de telle manière, qu'il en résulte pour le liquide de refroidissement une trajectoire à la manière d'un labyrinthe, et en ce que le fourreau cylindrique (13) est constitué à paroi mince, et les ailettes de refroidissement s'appliquent, en transmettant la pression d'allumage, en direction radiale, contre le carter (12) du moteur.
2. Fourreau cylindrique selon la revendication 1, comportant une amenée de liquide constituée sous la forme de canal annulaire, caractérisé en ce que le canal annulaire est constitué par une gorge annulaire (7) ménagée dans la culasse de cylindre et ouverte sur la chambre de refroidissement, et qui est située au-dessus de cette chambre (9) du fourreau cylindrique (13) et présente à peu près la largeur radiale de la chambre de refroidissement.
3. Fourreau cylindrique selon l'une des revendications 1 ou 2, caractérisé en ce que la sortie d'écoulement (11) du liquide est prévue du côté de la chambre de refroidissement (9) situé en regard de l'enveloppe (14) du vilebrequin.
4. Fourreau cylindrique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que les ailettes de refroidissement (10) sont dimensionnées de telle manière, que la température de la face extérieure du fourreau cylindrique (13) est, jusqu'à la pointe (22) des ailettes de refroidissement, abaissée à peu près à la température du liquide de refroidissement.
5. Fourreau cylindrique selon l'une quelconque des revendications 1 à 4, caractérisé en ce que les passages de liquide (19) sont disposés de façon à se correspondre, dans tous les plans des ailettes de refroidissement par rapport à l'axe (23) du fourreau cylindrique.
6. Fourreau cylindrique selon l'une quelconque des revendications 1 à 5, caractérisé en ce que l'ailette de refroidissement située la plus haute au-dessous de la culasse de cylindre (16) comporte moins de passages de liquide (19) que les ailettes de refroidissement des autres plans.
7. Fourreau cylindrique selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le liquide de refroidissement pénètre par des orifices d'entrée (17), à partir de la culasse de cylindre (16), dans la gorge annulaire (7) et les passages de liquide (19) de l'ailette de refroidissement située la plus haute sont ménagés entre les orifices d'entrée.
8. Fourreau cylindrique selon l'une quelconque des revendications 1 à 7, caractérisé en ce que seul un tronçon, situé en regard de la culasse de cylindre (16) du fourreau cylindrique (13) est pourvu d'ailettes de refroidissement (10) et dans l'autre tronçon, sauf dans les emplacements de canaux de refroidissement (18) s'étendant en direction axiale, il est prévu du matériau (20) résistant à la pression imperméable au liquide.
9. Fourreau cylindrique selon l'une quelconque des revendications 1 à 8, caractérisé en ce que ce fourreau cylindrique (13) est inséré avec ajustage serré dans le carter (12) du moteur.
10. Fourreau cylindrique selon l'une quelconque des revendications 1 à 9, caractérisé en ce que ce fourreau cylindrique (13) comporte du côté situé en regard de la culasse de cylindre (16), une extrémité exempte de collet et, à l'extrémité située en regard de l'enveloppe (14) du vilebrequin, s'appuie en direction axiale sur le carter (12) du moteur.
EP86108150A 1985-06-19 1986-06-14 Fourreau cylindrique refroidi par eau Expired - Lifetime EP0206184B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853521789 DE3521789A1 (de) 1985-06-19 1985-06-19 Fluessigkeitsgekuehltes zylinderrohr
DE3521789 1985-06-19

Publications (3)

Publication Number Publication Date
EP0206184A2 EP0206184A2 (fr) 1986-12-30
EP0206184A3 EP0206184A3 (en) 1988-01-13
EP0206184B1 true EP0206184B1 (fr) 1990-10-03

Family

ID=6273552

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86108150A Expired - Lifetime EP0206184B1 (fr) 1985-06-19 1986-06-14 Fourreau cylindrique refroidi par eau

Country Status (2)

Country Link
EP (1) EP0206184B1 (fr)
DE (2) DE3521789A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3632160A1 (de) * 1986-09-22 1988-03-31 Kloeckner Humboldt Deutz Ag Brennkraftmaschine
SE508983C2 (sv) * 1992-12-30 1998-11-23 Scania Cv Ab Vått cylinderfoder
DE10102644C1 (de) * 2001-01-20 2002-02-21 Bayerische Motoren Werke Ag Kurbelgehäuse für eine flüssigkeitsgekühlte Hubkolben-Brennkraftmaschine, in dem ein für alle Zylinder gemeinsamer Kühlraum angeordnet ist, und in dem mindestens ein strömungsbeeinflussendes Element vorgesehen ist
DE102005040639A1 (de) * 2005-08-27 2007-03-01 Deutz Ag Ölgekühlte Brennkraftmaschine
DE102005040635A1 (de) * 2005-08-27 2007-03-01 Deutz Ag Wassergekühlte Brennkraftmaschine
US7765917B2 (en) 2007-01-12 2010-08-03 Black & Decker Inc. Air compressor
US11174813B1 (en) * 2020-09-30 2021-11-16 Caterpillar Inc. Liner for engine block and systems, assemblies, components, and methods thereof

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB204106A (en) * 1922-06-19 1923-09-19 William Joseph Still Improvements in the construction of internal combustion engine cylinders

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2078499A (en) * 1928-09-01 1937-04-27 Spontan Ab Cooling system for internal combustion engines
US1904459A (en) * 1929-08-21 1933-04-18 Sulzer Ag Cylinder for internal combustion engines
US2238404A (en) * 1939-09-19 1941-04-15 Spencer Aircraft Motors Inc Internal combustion engine
FR1042296A (fr) * 1950-09-22 1953-10-30 Maschf Augsburg Nuernberg Ag Moteur à combustion interne à refroidissement par liquide
DE1916096A1 (de) * 1969-03-28 1970-10-08 Daimler Benz Ag Zylinderblock fuer fluessigkeitsgekuehlte Brennkraftmaschinen mit eingesetzter Zylinderlaufbuechse
NL7004500A (fr) * 1970-03-28 1971-09-30
DE2725059A1 (de) * 1977-06-03 1978-12-14 Kloeckner Humboldt Deutz Ag Wassergekuehlte hubkolbenbrennkraftmaschine mit nassen zylinderlaufbuchsen

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB204106A (en) * 1922-06-19 1923-09-19 William Joseph Still Improvements in the construction of internal combustion engine cylinders

Also Published As

Publication number Publication date
DE3674647D1 (de) 1990-11-08
DE3521789A1 (de) 1987-01-02
EP0206184A3 (en) 1988-01-13
EP0206184A2 (fr) 1986-12-30

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