WO2005042955A2 - Moteur a combustion interne - Google Patents

Moteur a combustion interne Download PDF

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Publication number
WO2005042955A2
WO2005042955A2 PCT/AT2004/000371 AT2004000371W WO2005042955A2 WO 2005042955 A2 WO2005042955 A2 WO 2005042955A2 AT 2004000371 W AT2004000371 W AT 2004000371W WO 2005042955 A2 WO2005042955 A2 WO 2005042955A2
Authority
WO
WIPO (PCT)
Prior art keywords
cooling space
cooling
internal combustion
combustion engine
cylinder head
Prior art date
Application number
PCT/AT2004/000371
Other languages
German (de)
English (en)
Other versions
WO2005042955A3 (fr
Inventor
Georg Pogatsch
Mad Rivas Navarro
Karl Kirchweger
Andreas Janach
Original Assignee
Avl List Gmbh
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
Priority claimed from AT7672004A external-priority patent/AT414022B/de
Application filed by Avl List Gmbh filed Critical Avl List Gmbh
Priority to DE112004002081.6T priority Critical patent/DE112004002081B4/de
Publication of WO2005042955A2 publication Critical patent/WO2005042955A2/fr
Publication of WO2005042955A3 publication Critical patent/WO2005042955A3/fr

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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 
    • F02F1/24—Cylinder heads
    • F02F1/26—Cylinder heads having cooling means
    • F02F1/36—Cylinder heads having cooling means for liquid cooling
    • F02F1/40—Cylinder heads having cooling means for liquid cooling cylinder heads with means for directing, guiding, or distributing liquid stream 

Definitions

  • the invention relates to liquid-cooled internal combustion engines with at least one cylinder head, with at least two intake and two exhaust port openings per cylinder, which are preferably arranged essentially symmetrically with respect to at least one transverse plane of the cylinder head, with a first cooling space bordering on a fire deck and at least partially with the first Cooling space bordering second cooling space, the first and second cooling space being fluidly connected to one another via at least one flow connection per cylinder, preferably the first cooling space being connectable to a cooling jacket of a cylinder housing via at least one passage opening, and wherein a receiving shaft for an injection device, which is molded with the cylinder head is at least partially surrounded by the second cooling space
  • the invention relates to a liquid-cooled multi-cylinder internal combustion engine with at least one cylinder head with at least two gas exchange channels controlled by intake and exhaust valves per cylinder, with a cooling space arrangement bordering on a fire deck, which through an intermediate deck formed essentially parallel to the fire deck into a lower partial cooling chamber on the fire deck side and an upper partial cooling space adjoining this in the direction of the cylinder axis is divided, the lower and upper partial cooling spaces being fluidly connected to one another by at least one overflow channel per cylinder in the direction of the cylinder axis in the region of an insert tube for a preferably central fuel injection device, and the overflow channel being delimited by the insert tube, and wherein at least one inflow opening per cylinder for the coolant opens into the lower partial cooling space and at least one outflow opening from the upper partial cooling space opening for the coolant.
  • the invention further relates to a liquid-cooled internal combustion engine with at least one cylinder head with a plurality of cylinders with an intake side and an exhaust side, with at least two exhaust port openings per cylinder, with a first cooling space bordering a fire deck and a second cooling space bordering the first cooling space, the first and second The cooling space is fluidly connected to one another by at least one transition opening per cylinder, the first cooling space being connectable to a cooling jacket of the cylinder housing via at least one first opening, and the second cooling space having a second opening on at least one end face.
  • a single cylinder cylinder head for a diesel internal combustion engine which has a lower partial cooling chamber on the fire deck side and an upper partial cooling chamber, a partition being arranged between the lower and the upper partial cooling chamber.
  • the cooling liquid is supplied on the one hand via a feed pipe to the annular cooling channels around the valve seats and on the other hand to the lower part of the cooling chamber.
  • the cooling liquid flows from the cooling channels around the valve seats into a central annular space which surrounds a bushing for a fuel supply device. From there, the cooling medium flows into the upper part of the cooling compartment. In this way, the fire deck and valve seats are to be cooled independently of one another.
  • DE 24 60 972 AI also discloses a single cylinder cylinder head with two superimposed coolant spaces which are connected to one another by openings. However, these constructions are not suitable for a cylinder head for several cylinders of an internal combustion engine.
  • a cylinder head for several cylinders of a diesel internal combustion engine which has a cooling space separated by a partition into a lower and an upper partial cooling space.
  • the lower and upper part of the cooling chamber are connected to one another in terms of flow via a crescent-shaped opening which partially surrounds the mouth of an injection nozzle in the circumferential direction.
  • the coolant flows from the cylinder through inlet openings in the fire deck. Linderblock in the lower part of the cooling room and from there via the crescent-shaped opening into the upper part of the cooling room.
  • the lower part of the cooling chamber is designed to be continuous for several adjacent cylinders, so that a longitudinal flow is also at least partially created. Sufficient heat dissipation cannot be guaranteed here, especially when there is high heat input from the combustion chamber.
  • JP 06-074041 A discloses a cylinder head with a lower and an upper partial cooling space and a centrally arranged injection nozzle sleeve. Directly after the injector sleeve, the intermediate deck has an overflow opening in the area of the webs between two outlet channels.
  • the coolant flowing from the cylinder block into the lower partial cooling space flows radially in the direction of the cylinder center and via the single overflow opening into the upper partial cooling space, similar to EP 1 126 152 A2.
  • the area between the two outlet channels is cooled well, other areas subject to high thermal stress, such as the land area between the inlet channels and the injection device, are only insufficiently cooled.
  • a cylinder head for an internal combustion engine with several cylinders is known.
  • the coolant flows out of the cylinder block via cooling holes in reinforcing ribs of the fire deck in a targeted manner to thermally highly stressed areas between the outlet channel openings, flows around the outlet channels and a tubular slug for a central injection device and flows through the cylinder head essentially in the longitudinal direction.
  • the heat dissipation in the thermally highly stressed area of the fire deck around the mouth of the injection device into the combustion chamber is not sufficiently guaranteed.
  • a cylinder head with an inlet-side and an outlet-side cooling space is known from EP 1 283 345 A2.
  • the coolant flows through connection openings into the inlet-side and the outlet-side cooling space.
  • the outlet-side cooling space is flowed through in the longitudinal direction.
  • the cooling chamber on the inlet side and on the outlet side are separated by a partition in the area of the outlet openings.
  • flow connections are formed in the area of an engine transverse plane between two cylinders between intake ports of adjacent cylinders, so that the intake-side cooling area in the area of the engine transverse plane is flowed through essentially transversely from the outside inwards.
  • the coolant in the inlet-side cooling space essentially flows in the longitudinal direction. Since there are no flow connections between the outlet channels, this thermally highly stressed area is not cooled sufficiently.
  • the object of the invention is to avoid these disadvantages and to improve the cooling in thermally highly stressed areas in a cylinder head of the type mentioned.
  • the receiving shaft is surrounded by an annular cooling space adjacent to the fire deck, which is connected to the second cooling space via at least one connecting channel.
  • the annular cooling space can be flow-connected via at least one first radial bore in a region of the cylinder head directly adjacent to the fire deck with at least one passage opening and / or with the first cooling space, with at least one first connecting duct in the region between an inlet and an outlet duct can be arranged, and in particular a first connecting channel can be provided between each inlet and outlet channel.
  • at least one second connecting channel which is essentially designed in the direction of the cylinder axis, is arranged between two inlet channels.
  • the ring cooling chamber ensures optimal cooling of the area around the mouth of the injection device.
  • the heat is dissipated into the second partial cooling space through the connecting channels.
  • the first cooling space is connected to the second cooling space via at least one second radial bore, the second radial bore preferably being arranged directly above the first radial bore.
  • the second radial bore can be arranged in the area between the outlet channels and open into an extension of the second cooling space that extends between the outlet channels in the direction of the fire deck. This improves cooling in the thermally highly stressed area between the outlet channels. Coolant also passes from the first into the second cooling space via the second radial bore.
  • the first and / or second radial bore are preferably arranged parallel to the cylinder head plane.
  • the first and second radial bores serve for the flow connection of the first to the second cooling space.
  • the coolant flows via the first passage opening through the first radial bore directly into the annular cooling space surrounding the receiving shaft for the injection device and reaches the second cooling space above the first cooling space via the connecting channels.
  • the coolant flows from the first cooling space directly into the second cooling space via the second radial bore.
  • the first and / or second radial cooling bore is arranged on the outlet side, preferably in a region between the two outlet ducts and the fire deck.
  • an overflow channel is arranged between the first and second cooling chambers on both sides of the outlet channels in the region of the outlet flange surface.
  • the coolant thus flows from the first cooling space on the one hand via the first radial bore into the annular cooling space, and from there via the connecting channels into the second cooling space. Furthermore, the coolant flows via the second radial bore and via the overflow channels directly from the first into the second cooling space.
  • the first cooling space is formed by a first water core and the second cooling space
  • the annular cooling space and the at least one connecting channel between the annular cooling space and the second cooling space is formed by a second water core.
  • the first and second cooling compartments are thus molded using separate water core packages, the annular cooling duct and the connecting ducts also being integrated in the second water core.
  • the first and the second core package are spaced apart from one another during the casting process, so that in the raw cylinder head - at least in the area of the annular cooling space - there is no casting connection between the first and the second cooling space. stands.
  • the flow connection between the first and the second cooling space is only established through the radial bores in a separate manufacturing step.
  • At least one support column with a preferably cross-shaped cross section is arranged in the region of a transverse plane between two adjacent cylinders.
  • the overflow channel produced by casting is limited on the cylinder head side at least by one wall of a gas exchange channel, the cylinder head side walls of the overflow channel preferably being formed only by the walls of at least two gas exchange channels.
  • the cylinder head is designed without an intermediate cover, as a result of which the overflow opening can be produced very easily through an inserted cast core.
  • the coolant flows in the lower cooling space through radial flow channels between two gas exchange channels into the area of the insert tube.
  • the overflow channel is divided in the flow direction by webs into preferably four subchannels. Due to the cross-section of the flow channels and the sub-channels, the flow can be precisely preset for each valve land area.
  • the webs can be designed as a guide for the insert tube, it being advantageous if the insert tube rests on at least one web.
  • a coolant flow between two adjacent subchannels can be advantageous for cooling thermally critical areas.
  • a particularly preferred embodiment variant provides that at least two adjacent subchannels are flow-connected to one another via a connecting opening, the connecting opening preferably being formed by a gap between the insert tube and the web.
  • the invention provides that a flow guide wall connected to the intermediate deck is arranged in the area of the flow channel between two gas exchange channels, which radially Coolant flowing in the direction of the overflow channel in the lower cooling space is diverted to the fire deck.
  • At least one first opening and at least one transfer opening are arranged in the area of a transverse engine plane normally formed on the crankshaft between two adjacent cylinders, the first cooling space in each case in the area between two exhaust port openings a longitudinal wall of adjacent cylinders and a coolant channel is arranged between the outlet channels in the area of the outlet channel openings of each cylinder.
  • the first and second cooling compartments are arranged one above the other in the area of the outlet ducts.
  • the lower area of the outlet channels is thus cooled by the first cooling space, the upper area of the outlet channels by the second cooling space.
  • the second cooling space has essentially an L-shaped cross section and is arranged on the outlet side with its longer leg above the first cooling space and on the inlet side with its shorter leg next to the first cooling space, with first and second on the inlet side Cold room are separated from each other by an intermediate wall.
  • the first and second cooling compartments are separated from each other by an intermediate deck. The heights of the first and second cooling space can be approximately the same.
  • the coolant flows out of the cylinder housing through the first openings into the first cooling chamber on the outlet side and is initially deflected in the longitudinal direction by the longitudinal walls between the outlet channels of two adjacent cylinders.
  • the coolant continues to flow through the coolant channel between two outlet channels of a cylinder in the direction of the inlet side and is deflected here by the inlet channel walls and by the intermediate wall between the first and the second cooling chamber in the longitudinal direction to the transition opening into the inlet-side first cooling chamber.
  • This loop-like flow around the outlet channels optimally cools the area between two outlet channels of a cylinder, which represent thermally particularly critical areas.
  • the transfer openings between the first and the second cooling space are advantageously drilled.
  • FIG. 1 shows the cylinder head according to the invention in an oblique view from above
  • Figure 2 shows the cylinder head in an oblique view from below.
  • Figure 3 shows the cylinder head in a plan view.
  • FIG. 4 shows the cylinder head in a side view according to arrow 4 in FIG. 1;
  • Figure 5 shows the cylinder head in a section along the line V-V in Fig. 3.
  • Figure 6 shows the cylinder head in a section along the line VI-VI in Fig. 3.
  • Figure 7 shows the cylinder head in a section along the line VII-VII in Fig. 3.
  • Figure 8 shows the cylinder head in a section along the line VIII-VIII in Fig. 3.
  • Figure 10 shows the cylinder head in a section along the line X-X in Fig. 3.
  • FIG. 11 shows the cylinder head in a section along the line XI-XI in FIG. 3;
  • Figure 12 shows the cylinder head in a section along the line XII-XII in Fig. 3.
  • Figure 13 shows the cylinder head in a section along the line XIII-XIII in Fig. 7.
  • Figure 20 in the water core assembly in a section along the line XX-XX in Fig. 18 .;
  • FIG. 21 shows the water core arrangement in a section along the line XXI-XXI in FIG. 20;
  • FIG. 22 shows the water core arrangement in a section along the line XXII-XXII in FIG. 20;
  • Figure 23 shows the water core arrangement in a section along the line XXIII-XXIII in Fig. 18 .;
  • FIG. 24 shows the water core arrangement in a section along the line XXIV-XXIV in FIG. 18;
  • FIG. 25 shows the water core arrangement in a section along the line XXV-XXV in FIG. 18;
  • 26 shows the water core arrangement in a section along the line XXVI-XXVI in FIG. 18;
  • FIG. 27 shows the water core arrangement in a section along the line XXVII-XXVII in FIG. 18;
  • FIG. 29 shows the cylinder head according to the invention in a section along the line XXIX-XXIX in FIG. 30;
  • FIG. 30 shows the cylinder head in a section along the line XXX-XXX in FIG. 29;
  • FIG. 31 shows the cylinder head in a section along the line XXXI-XXXI in FIG. 29;
  • 33 shows the cylinder head in a section along the line XXXIII-XXXIII in FIG. 30; 34 shows the cylinder head in a section along the line XXXIV-XXXIV in FIG. 30;
  • 35 shows the cylinder head in a section along the line XXXV-XXXV in FIG. 30;
  • FIG. 36 shows the cylinder head in a section along the line XXXVI-XXXVI in FIG. 30;
  • FIG. 41 shows a detail from FIG. 40.
  • FIGS. 1 to 14 show a cylinder head 1 for a diesel internal combustion engine with two intake port openings 2, 3 and two exhaust port openings 4, 5.
  • Separate intake ports 8, 9 leading to the intake port openings 2, 3 lead from an intake flange surface 6 on the intake side 7
  • Inlet and outlet channel openings 2, 3; 4, 5 are essentially symmetrical with respect to a transverse plane ⁇ i of the cylinder head 1 through the cylinder axis 21 and result in a symmetrical valve pattern.
  • Exhaust passages 10, 11 extend from the exhaust port openings 4, 5, which unite within the cylinder head 1 to form a common exhaust port 12 and lead to an exhaust flange surface 13 on an exhaust side 14.
  • the cylinder head 1 has a first cooling chamber 16 which borders on the fire deck 15 and which can be connected to a cylinder block (not shown further) via passage openings 17 in the cylinder head sealing surface 18.
  • Adjacent to the first cooling space 16 is a second cooling space 19, which is separated from the first cooling space 16 by an intermediate deck 20.
  • the second cooling space is located — viewed in the direction of the cylinder axis 21 — above the first cooling space, that is to say between the inlet and outlet channels 8, 9, 10, 11, 12 and the valve actuation space 22 for accommodating valve actuation elements (not shown further).
  • the bearings for camshafts, not shown, are designated by reference numeral 23.
  • the cylinder head 1 has a molded-in receiving shaft 24 for a central injection device (not shown).
  • the axis 25 of the Mesh shaft 24 - viewed in the longitudinal direction of cylinder head 1 - is designed to be slightly eccentric with respect to cylinder axis 21 in order to enable the most favorable arrangement for intake ports 8, 9 and intake port openings 2, 3.
  • the eccentricity with respect to the cylinder axis 21 is designated by e (FIG. 10).
  • the cylinder head 1 has a receiving opening 26 for a glow plug.
  • the valve guide slugs for intake and exhaust valves are designated by reference numerals 28 and 29, the axes of which are identified by reference numerals 28a and 29a.
  • the molded-in receiving shaft 24 is surrounded by an annular cooling space 30 in an area adjacent to the fire deck 15.
  • the annular cooling space 30 is above first connecting cooling channels 31, 32, which are each between an inlet channel 8; 9 and an outlet duct 10; 11 run with the second cooling space 19 in connection.
  • the annular cooling space 30 is connected to the second cooling space 19 via a second connecting cooling passage 33 running between the two inlet channels 8, 9.
  • the annular cooling chamber 30 is connected via a first radial bore 34, which starts from the outlet flange surface 13 and runs essentially parallel to the cylinder head sealing surface 18, to a first passage opening 17a, which can be connected to the cooling jacket of the cylinder block.
  • the first cooling chamber 16 is connected to the second cooling chamber 19 via lateral overflow channels 37 on both sides of the common outlet channel 12. Furthermore, the first cooling space 16 is connected to the flow via a second radial bore 34 with an extension 36 of the second cooling space 19.
  • the first and second radial bores 34, 35, which run essentially parallel to the cylinder head sealing surface 18, are machined into the cylinder head 1 after the casting process.
  • 16 support columns 38 with a cross-shaped cross section are arranged in the first cooling space, which increase the structural rigidity of the cylinder head 1.
  • FIGS. 15 to 28 show a water core arrangement 40 for the cylinder head 1.
  • the water core arrangement 40 consists of a first water core 41 for the first cooling space 16 and a second water core 42 for the second cooling space 19.
  • the water cores 41, 42 are - at least predominantly - spaced from one another and - at least in the area of the annular cooling space 30 - have no connection with one another.
  • Recesses 43, 44 for corresponding cast cores for inlet and outlet channels are formed between the water cores 41, 42.
  • the second water core 42 has corresponding negative shape areas 45, 46, 47 and 48 for the annular cooling space 30 first connecting cooling channels 31, 32 and for the second connecting cooling channel 33.
  • the second water core 42 forms a negative molding area 49 for the first passage opening 17a and a molding area 50 for the first radial bore 34.
  • the shaped area 51 for the extension 36 is also formed by the second water core 42.
  • the second passage openings 17 and the tubular shape for the second radial bore 35 are formed by corresponding shaped areas 53, 52 of the first water core 41.
  • the first water core 41 also forms the shaped areas 54 for overflow channels 37 between the first and second cooling spaces 16, 19 on both sides of the common outlet channel 12.
  • the coolant flow through the cylinder head 1 is explained on the basis of the core arrangement 40 in FIG. 28.
  • the coolant flows out of the cooling jacket of the cylinder block via the first passage opening 17a and the first radial connecting channel 31 into the annular cooling space 30 and reaches the upper second cooling space 19 according to the arrow Si and flows through it in the transverse direction according to the arrow S to the inlet side 7 and leaves the second cooling space 19 via an opening 39b.
  • the coolant reaches the first cooling chamber 16 via second through-openings 17 and flows on the one hand according to the arrows S 2 via lateral overflow channels 37 on both sides of the common outlet channel 12 into the upper cooling chamber 19, where it flows according to the arrow S in the transverse direction to the inlet side 7 and the leaves second cooling space 19 via opening 39b. Furthermore, coolant reaches the first cooling chamber 16 from second through-openings 17b on the inlet side 7, where it flows partly to the outlet side 14, partly to the inlet side 7 and leaves the first cooling chamber 16 via an opening 39a. In addition, there is also a cross flow according to arrow S 3 from the outlet side 14 to the inlet side 7.
  • the cylinder head 101 shown in FIGS. 9 to 36 which is formed in one piece for a plurality of cylinders A, B, C, has a cooling space arrangement 103 bordering on a fire deck 102 on the combustion chamber side, which through an intermediate deck 104 leads into a lower partial cooling chamber 105 on the fire deck side and one in the direction of the cylinder axis 106 adjoining upper partial cooling space 107 is divided.
  • the intermediate deck 104 has at least one overflow channel per cylinder A, B, C.
  • the overflow channels 109 are produced in a simple manner by casting technology, the cylinder head 101 being designed without a cover in a space 127 spanned by the valve axes 124a, 125a.
  • the overflow channel 109 is thus predominantly through the walls 116a, 117a of the gas exchange channels 116, 117 and through the insert tube
  • the overflow channel has 109 has a substantially star-shaped cross section and is divided in the flow direction by means of the webs 126 into subchannels 109a, 109b, 109c, 109d.
  • the webs 126 are molded onto the walls 116a, 117a of the gas exchange channels 116, 117, as shown in FIG. 36.
  • the webs 126 can be designed as guides for the insert tube 110 and support the insert tube 110 laterally.
  • connection opening 128, for example formed by a gap s, can also be formed between the webs 126 and the insert tube 110, as a result of which a coolant exchange between the individual subchannels 109a, 109b, 109c, 109d is made possible.
  • Reference symbols 116b, 117b denote inlet openings or outlet openings of the inlet and outlet channels 116, 117.
  • At least one ventilation hole 108 is provided per cylinder A, B, C between the longitudinal engine plane 123 and a side wall 101a, 101b of the cylinder head 101.
  • Optimal cooling of the thermally highly stressed areas of the valve webs 130, 131 between the inlet channels 116 and the receiving opening 120 in the fire deck 102 on the one hand and the outlet channels 117 and the receiving bore 120 on the other hand is achieved by flow guide walls 132 of the intermediate deck 104 drawn in the direction of the fire deck 102.
  • the cooling medium flows through inflow openings 113 in the region of the side walls 101a, 101b of the cylinder head 101 essentially in transverse directions according to the arrows S into the lower partial cooling space 105 (FIG. 32).
  • the areas around the valve seats 114 of the lift valves and around the receiving opening 120 of the fuel injection device are flowed around and optimally cooled.
  • the cooling medium flows through radial flow channels 133a, 133b, 133c in the direction of the insert tube 110.
  • the coolant is passed through the flow guide walls 132 in the direction of the fire deck 102, the flow rate increasing due to the reduction in cross section.
  • the coolant then flows through the partial channels 109a, 109b, 109c, 109d of the overflow channels 109 into the upper partial cooling space 107 and flows through the upper partial cooling space 107, which is designed to be uniform for all cylinders A, B, C, in the longitudinal direction of the cylinder head 101
  • the drain opening 114 leaves the coolant from the cylinder head 101 the upper partial cooling space 107, a collecting bar for the emerging coolant can also be provided.
  • interrupted intermediate walls 112 are provided in the lower partial cooling space 105, which also enable a coolant exchange between two adjacent cylinders A, B, C in the lower partial cooling space 105.
  • the intermediate walls 112 are each arranged in the region of an engine transverse plane 122 of the cylinder head 101.
  • FIGS. 37 to 41 show the coolant-filled spaces of a cylinder head 201.
  • the cylinder head 201 has an outlet-side first cooling chamber 202 and an inlet-side second cooling chamber 203. With reference numeral 204 outlet ducts opening into the combustion chamber, with reference numeral 205 the inlet ducts.
  • Reference symbol I denotes the intake side
  • reference symbol E the exhaust side of the cylinder head 201.
  • the first cooling chamber 202 is connected via a plurality of first openings 207 in the fire deck 206 of the cylinder head 201 to a cooling jacket of the cylinder block, which is not shown in any more detail.
  • the first cooling chamber 202 is fluidly connected to the second cooling chamber 203 via transfer openings 208 in the cylinder head 201.
  • the transition openings 208 are formed by bores running essentially parallel to the cylinder axis.
  • the areas of the outlet channel openings in a combustion chamber, not shown, are designated by reference numeral 209.
  • At least one first opening 207 and at least one transition opening 208 are each arranged in an engine transverse plane 210 arranged normally on the crankshaft axis between two cylinders.
  • a longitudinal wall 211 crossing the transverse engine plane 210 extends in the area between the outlet channel openings 209 of two adjacent cylinders.
  • the first and second cooling chambers 202, 203 are separated from one another in the region of the engine transverse plane 210 by an intermediate wall 212 which extends essentially in the longitudinal direction of the cylinder head 201.
  • the second cooling space 203 is arranged on the outlet side E essentially above the first cooling space 202.
  • the second cooling space 203 has a substantially “L” -shaped cross section, the shorter leg 203a being arranged on the inlet side I and on it Side extends to fire deck 206.
  • the intermediate wall 212 is arranged between the first cooling space 202 and the shorter leg 203a of the second cooling space 203.
  • the longer leg 203b of the second cooling space 203 is separated from the first cooling space by an intermediate deck 217.
  • the heights h 2 , h 3 of the first and second cooling spaces 202, 203 are approximately the same in the exemplary embodiment.
  • the coolant passes through the first openings 207 from the cooling jacket of the cylinder housing, not shown, into the first cooling chamber 202 of the cylinder head 201 and flows according to the arrows P shown in FIG. 41 on both sides of the connection opening 207 along the longitudinal wall 211, flows around the outlet channels 204 and arrives through a coolant channel 213 between the outlet channels 204 of each cylinder into the area of the cylinder center 214.
  • the coolant flow P is divided through the walls 205a of the inlet channels 205 on both sides of the cylinder center 214 in the longitudinal direction of the cylinder head 201, whereby the coolant is in each case between an outlet channel 204 and flows through an inlet channel 205 and to the transfer opening 208, through which the coolant reaches the second cooling space 203.
  • the coolant essentially flows through the second cooling space 203 in the longitudinal direction of the cylinder head 201.
  • the coolant leaves the cylinder head 201 via the second opening 215 in the region of an end face 216.
  • Reference symbols 207a denote further connection openings to the water jacket of the cylinder housing.
  • the coolant thus enters the first cooling space 202 on the exhaust side and is then led directly to the most critical cooling area between the exhaust ports and the area of a centrally arranged injector, which enables optimal heat dissipation from the hot areas of the cylinder head.
  • Another advantage of the cold room arrangement is that the cast cores for the exhaust gas ducts 204 - similar to the cast cores for the inlet ducts 205 - can be inserted from the top during casting production. As can be seen from FIG. 37, first the core for the first cooling space 202, then the cores for the outlet channels 204, then the core for the second cooling space 203 and finally the cores for the inlet channels 205 in the core box (not shown further) used.

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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)

Abstract

L'invention concerne un moteur à combustion interne refroidi par un liquide, qui comprend une culasse, présentant deux ouvertures de canaux d'admission et deux ouvertures de canaux d'échappement par cylindre qui sont sensiblement symétriques par rapport à au moins un plan transversal de la culasse, ainsi qu'une première chambre de refroidissement, adjacente à un couvercle, et une seconde chambre de refroidissement, au moins partiellement adjacente à la première chambre de refroidissement, la première et la seconde chambre de refroidissement étant en liaison fluidique par l'intermédiaire d'au moins une liaison d'écoulement par cylindre.
PCT/AT2004/000371 2003-11-03 2004-10-28 Moteur a combustion interne WO2005042955A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112004002081.6T DE112004002081B4 (de) 2003-11-03 2004-10-28 Brennkraftmaschine

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
AT7592003 2003-11-03
ATGM759/2003 2003-11-03
AT8442003 2003-11-27
ATGM844/2003 2003-11-27
AT7672004A AT414022B (de) 2004-05-04 2004-05-04 Zylinderkopf für eine flüssigkeitsgekühlte brennkraftmaschine
ATA767/2004 2004-05-04

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Publication Number Publication Date
WO2005042955A2 true WO2005042955A2 (fr) 2005-05-12
WO2005042955A3 WO2005042955A3 (fr) 2006-05-18

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WO (1) WO2005042955A2 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2882791A1 (fr) * 2005-03-07 2006-09-08 Renault Sas Culasse de moteur a combustion interne d'un vehicule automobile comprenant un noyau d'eau en deux parties
WO2007051212A2 (fr) * 2005-11-04 2007-05-10 Avl List Gmbh Culasse
WO2007120424A1 (fr) * 2006-04-13 2007-10-25 Caterpillar Inc. Culasse de moteur
AT500628B1 (de) * 2005-11-04 2007-12-15 Avl List Gmbh Zylinderkopf für eine flüssigkeitsgekühlte brennkraftmaschine
EP1972772A3 (fr) * 2007-03-19 2014-04-09 Bayerische Motoren Werke Aktiengesellschaft Tête de cylindre pour un moteur à combustion interne refroidi par liquide
WO2018037368A1 (fr) * 2016-08-24 2018-03-01 Fpt Industrial S.P.A. Moteur à combustion interne comprenant un circuit de refroidissement par liquide
DE102017109185A1 (de) * 2017-04-28 2018-10-31 Volkswagen Aktiengesellschaft Zylinderkopfgehäuse sowie Verfahren zur Herstellung eines Zylinderkopfgehäuses und Gießkern
DE102006026131B4 (de) 2006-06-03 2018-12-20 Daimler Ag Verfahren zur Herstellung eines Zylinderkopfs für eine flüssigkeitsgekühlte Brennkraftmaschine
WO2020150761A1 (fr) * 2019-01-23 2020-07-30 Avl List Gmbh Culasse refroidie par liquide
DE102019006034A1 (de) * 2019-08-27 2021-03-04 Man Truck & Bus Se Kühlungsoptimierter Zylinderkopf und optimiertes Zylinderkopfkühlverfahren
WO2021253065A1 (fr) 2020-06-18 2021-12-23 Avl List Gmbh Culasse pour moteur à combustion interne

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017212645B4 (de) * 2017-07-24 2022-05-19 Bayerische Motoren Werke Aktiengesellschaft Zylinderkopf für eine Verbrennungskraftmaschine
DE102020111176A1 (de) 2020-04-24 2021-10-28 Bayerische Motoren Werke Aktiengesellschaft Verbrennungskraftmaschine mit einer Kühlvorrichtung zum Kühlen von Zylindern und Kraftfahrzeug mit einer Verbrennungskraftmaschine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4121550A (en) * 1974-08-07 1978-10-24 Motoren-Und Turbinen-Union Friedrichshafen Gmbh Liquid-cooled cylinder head
US4889080A (en) * 1987-05-26 1989-12-26 Kabushiki Kaisha Komatsu Seisakusho Cylinder head for an internal combustion engine
AT5301U1 (de) * 2001-01-29 2002-05-27 Avl List Gmbh Zylinderkopf für mehrere zylinder

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB828014A (en) * 1957-05-20 1960-02-10 Fodens Ltd Improvements in the cooling system of the cylinder head of a diesel engine
DE2460972C2 (de) * 1974-12-21 1982-07-15 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen Flüssigkeitsgekühlter Zylinderkopf
CH614995A5 (en) * 1978-09-25 1979-12-28 Sulzer Ag Arrangement for cooling of the cylinder cover of a four-stroke diesel engine
US4304199A (en) * 1979-12-31 1981-12-08 Fiat Veicoli Industriali S.P.A. Cylinder head for compression-ignition internal combustion engines having precombustion chambers
DE3516453A1 (de) * 1985-05-08 1986-11-13 Audi AG, 8070 Ingolstadt Fluessigkeitsgekuehlter zylinderkopf
DE3802886A1 (de) * 1987-02-04 1988-08-18 Avl Verbrennungskraft Messtech Zylinderkopf fuer wassergekuehlte brennkraftmaschinen
JP2941123B2 (ja) * 1992-08-24 1999-08-25 ダイハツ工業株式会社 四弁式内燃機関におけるシリンダヘッドの構造
DE19508113C2 (de) * 1995-03-08 1997-01-16 Daimler Benz Ag Flüssigkeitsgekühlter Vierventil-Zylinderkopf für eine mehrzylindrige Brennkraftmaschine
US5765282A (en) * 1996-06-26 1998-06-16 Cummins Engine Company, Inc. Internal combustion engine cylinder head method of manufacture
DE19644530C1 (de) * 1996-10-26 1998-02-12 Daimler Benz Ag Zylinderkopf für eine Mehrzylinder-Brennkraftmaschine
AT3139U1 (de) * 1998-11-09 1999-10-25 Avl List Gmbh Zylinderkopf für eine flüssigkeitsgekühlte brennkraftmaschine
JP2000310157A (ja) * 1999-04-27 2000-11-07 Mazda Motor Corp 多気筒エンジンのシリンダヘッド構造
US6279516B1 (en) * 2000-02-16 2001-08-28 Deere & Company Cylinder head with two-plane water jacket
JP2003056343A (ja) * 2001-08-10 2003-02-26 Toyota Industries Corp 内燃機関のシリンダヘッド冷却構造
AT6654U1 (de) * 2002-10-31 2004-01-26 Avl List Gmbh Zylinderkopf für eine flüssigkeitsgekühlte mehrzylinder-brennkraftmaschine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4121550A (en) * 1974-08-07 1978-10-24 Motoren-Und Turbinen-Union Friedrichshafen Gmbh Liquid-cooled cylinder head
US4889080A (en) * 1987-05-26 1989-12-26 Kabushiki Kaisha Komatsu Seisakusho Cylinder head for an internal combustion engine
AT5301U1 (de) * 2001-01-29 2002-05-27 Avl List Gmbh Zylinderkopf für mehrere zylinder

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2882791A1 (fr) * 2005-03-07 2006-09-08 Renault Sas Culasse de moteur a combustion interne d'un vehicule automobile comprenant un noyau d'eau en deux parties
WO2007051212A2 (fr) * 2005-11-04 2007-05-10 Avl List Gmbh Culasse
WO2007051212A3 (fr) * 2005-11-04 2007-07-05 Avl List Gmbh Culasse
AT500628B1 (de) * 2005-11-04 2007-12-15 Avl List Gmbh Zylinderkopf für eine flüssigkeitsgekühlte brennkraftmaschine
US8082894B2 (en) 2005-11-04 2011-12-27 Avl List Gmbh Cylinder head having coolant flow guide device
WO2007120424A1 (fr) * 2006-04-13 2007-10-25 Caterpillar Inc. Culasse de moteur
US7520257B2 (en) 2006-04-13 2009-04-21 Caterpillar Inc. Engine cylinder head
DE112007000918B4 (de) 2006-04-13 2022-09-08 Caterpillar Inc. Zylinderkopf für einen Motor sowie Motor
DE102006026131B4 (de) 2006-06-03 2018-12-20 Daimler Ag Verfahren zur Herstellung eines Zylinderkopfs für eine flüssigkeitsgekühlte Brennkraftmaschine
EP1972772A3 (fr) * 2007-03-19 2014-04-09 Bayerische Motoren Werke Aktiengesellschaft Tête de cylindre pour un moteur à combustion interne refroidi par liquide
US11248556B2 (en) 2016-08-24 2022-02-15 Fpt Industrial S.P.A. Internal combustion engine comprising a liquid cooling circuit
CN114542318A (zh) * 2016-08-24 2022-05-27 Fpt工业股份公司 包括液体冷却回路的内燃发动机
US10907572B2 (en) 2016-08-24 2021-02-02 Fpt Industrial S.P.A. Internal combustion engine comprising a liquid cooling circuit
CN109642517A (zh) * 2016-08-24 2019-04-16 Fpt工业股份公司 包括液体冷却回路的内燃发动机
WO2018037368A1 (fr) * 2016-08-24 2018-03-01 Fpt Industrial S.P.A. Moteur à combustion interne comprenant un circuit de refroidissement par liquide
US11078865B2 (en) 2017-04-28 2021-08-03 Volkswagen Aktiengesellschaft Cylinder head housing, method for producing a cylinder head housing, and casting core
DE102017109185A1 (de) * 2017-04-28 2018-10-31 Volkswagen Aktiengesellschaft Zylinderkopfgehäuse sowie Verfahren zur Herstellung eines Zylinderkopfgehäuses und Gießkern
WO2020150761A1 (fr) * 2019-01-23 2020-07-30 Avl List Gmbh Culasse refroidie par liquide
US11905909B2 (en) 2019-01-23 2024-02-20 Avl List Gmbh Liquid-cooled cylinder head
US11598283B2 (en) 2019-01-23 2023-03-07 Avl List Gmbh Liquid-cooled cylinder head
DE102019006034A1 (de) * 2019-08-27 2021-03-04 Man Truck & Bus Se Kühlungsoptimierter Zylinderkopf und optimiertes Zylinderkopfkühlverfahren
AT523950B1 (de) * 2020-06-18 2022-03-15 Avl List Gmbh Zylinderkopf für eine Brennkraftmaschine
AT523950A1 (de) * 2020-06-18 2022-01-15 Avl List Gmbh Zylinderkopf für eine Brennkraftmaschine
WO2021253065A1 (fr) 2020-06-18 2021-12-23 Avl List Gmbh Culasse pour moteur à combustion interne

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